Detailed hydraulic cylinders Working pressure:16Mpa ISO9001:2000 Reliable quality hydraulic cylindersOur company was founded in 1984.We have more than 20 years experience for making cylinders.We have passed ISO9001:2000 certificated.
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Detailed hydraulic jack Red hydraulic jack with standard export package Hydraulic jack . Model: Hydraulic bottle jack /hydraulic jack / jack / jack stand / power jack / air bottle jack 2. The jack capacity: From 2T to 100T 3. The power jack is mini height: 148mm-340mm 4. The car jack man heigh.
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Detailed Hydraulic cylinder: double acting for push and pull Double acting hollow plunger cylinders combine all of the design features a single role and the way the superiority of the role of design to enhance the operation and use of speed, especially in a long journey operations can take advantag.
Detailed the hydraulic cylinders are similar to ENERPAC models cylinder capacity (ton):50 - 1000 stroke:50- 300mm pressure:700 bar Mechanical nut locking hydraulic cylinder combines the functions of the other cylinder, cylinder mechanical bearing security is suitable for the Pistons continued .
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Detailed CRL-6300 two post lift Dual hydraulic cylinders ensure steady lifting and lowering CE approval Italy seal kits of cylinder CRL-6300 two post lift 1) 4T lifting capacity2) Symmetric arm structure 3) Automatic arm restraints 4) Dual hydraulic cylinders ensure steady lifting and lowering.
Detailed TLT235SCA Clear Floor Two Post car Lift(auto lift) Rated Capacity: 3.5Ton Dual hydraulic cylinders drive, stable lifting TLT235SCA Clear Floor Two Post car Lift: Feature Dual hydraulic cylinders drive, stable lifting and lowering.
Detailed 1.Single-acting hydraulic cyliderder: 2.Lifting capacity:5-100T 3.Lifting Height:16-364mm 4.Max working pressure:70MPa 1.Single-acting hydraulic cyliderder:2.Lifting capacity:5-100T3.Lifting Height:16-364mm4.
Detailed Its design had registed in patent, its key hydraulic cylinders technology came from Japan, named diameter direction pump Product numbernametypeRated output(Mpa)Weight(kg)0049hydraulic pumpDYB-6370MPa30.
Detailed 6 Ton hydraulic bottle jacks packed in blow case typical red color,fluent frame of the jacks. 6 Ton hydraulic bottle jackshydraulic bottle jack with stable quality, 100 degree high temperature test.
Detailed 1.Lift Capacity 4T 2.two post car lift 3.Lift Europe CE 4.auto lift Type: Double Cylinder Hydraulic Lift Launch Economical Floorplate TLT240SB2-post auto Lift(car lift)- Rated Capacity: 4TonDual hydraulic cy Feature:Dual hydraulic cylinders drive.
Detailed 1) Asymmetric clear floor design 2) Dual hydraulic cylinders ensure steady lifting Clear floor design makes easy working under beneath the vehicle.Manual release from two sidesDual cylinders with Italian combination seals.Aluminum motor prevents overheated.24V control system.24V limit.
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New Outfall Bridge Structures At Bonneville Dam - 1. Introduction
Organization: Deep Foundations Institute
Jan 1, 2001
New high and low double outfall bridge structures for a juvenile fish bypass system have been constructed on the Washington Shore approximately two miles downstream from the Bonneville Dam on the Columbia River. The high and low outfalls each extend approximately 400 feet into the river from the Washington shore and are designed to release juvenile salmon into the river at above-water discharge elevations for improved survival rates. The two outfall structures include post-tensioned concrete double box flume girders approximately 7 feet high by 13 feet wide, which will be submerged in river flows as high as 15 feet per second. Each of the 6 offshore foundation piers is composed of a single 10-foot diameter reinforced concrete drilled shaft with a permanent steel casing embedded into the river bottom approximately 100 feet. Challenging outfall design conditions included designing the entire structures to be submerged for long periods of time in 15-feet-per-second river water flow with a 60-foot cantilever at the end of each outfall, and with the superstructure 70 to 80 feet above the river bottom. Figures 1-1,1-2, and 1-3 show the high and low outfall structure overhead photos and elevation view.


need to write energy equation, considering pump and you have to guess your volumetric flow rate by using chart (b) and equation found. Then you can find the pump power requirement by using efficiency of pump, stated in chart (b).
Output power (Pout)
Pout = ṁgH = ρgQH
where: ρ is fluid density, g is the acceleration due to gravity, Q is the volumetric flow rate, H is the pump head, ṁ is the mass flow rate.
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Sinotech have been involved in constructing physical and numerical models for numerous pump station inlet
structures and inlet towers
Description of model
Berg River Consultants
Berg River Project - Water supply to Cape Town, South Africa. Outlet works. (Flow rate = 220 m³/s) Scale – 1:20
Resolving the failure of the Paris Dam inlet works: Vortex formation and pressure fluctuations in the inlet pipes
Model study of the Maguga dam regulating weir – Stabilisation of the releases
Model study of the Vortex Protection Measures at Vereeniging Pump Station (ER 2), Filter House 2 suction manifold (Flow in manifold between 3,4 and 4,0 m³/s). Scale - 1:13,5
Grootfontein Pump station in South Africa, (Flow per pump = 2,1 m³/s – four pumps). Scale - 1:6,5
Problems were experienced since the commissioning of the pump station. The high wear on the pumps has been investigated before and model studies have previously been conducted to determine the
probable factors that contributed to the pump failures.
This model study investigated the following: oEvaluate the flow regime in the vertical shaftoInvestigate the pre-rotation at the pumpsoEvaluate the influence of proposed remedial works to the
vertical shaft to improve the pump operation.
Ashkelon Seawater Pump station, Israel. (Flow per pump = 2,4 m³/s, five pumps modelled). Scale 1:8
In a pump station the three-dimensional flow regime in the sump can influence the efficiency of the pump and might even endanger its long-term operation. These flow conditions can be evaluated by
conducting a model study with the objective to:•Evaluate the flow regime and vortex formation tendency in the screen and pump sumps •Evaluate the rotational characteristics of the flow as
it enters the pump and•Investigate the velocity distribution in the pump shaft.
Sheikh Zayed Pump Station in Egypt, (Flow per pump = 8,5 m³/s – 7 pumps). Scale 1:10
The client has requested that a model study had to be performed with the objective to:o Evaluate the flow regime and vortex tendency in the pump sumpo Investigate the formation of vortices
o Evaluate the influence of the turning vanes on the inlet flow conditions and the velocity profile in the pump.
Chanza Pump Station in Spain, (Flow per pump = 3,33 m³/s – 6 pumps). Scale 1:11,5. These pumps are vertical risers with a double entry
Numerical and physical modelling of discontinuity requirements under an air valve for effective de-aeration performed in collaboration with the CFD lab of the University of Pretoria
Knight Piésold Consulting Engineers
Hydraulic assessment of the spillway and energy dissipation of the Neckertal Dam - Namibia
HydroAfrica, Maputo - Mozambique
Umbelusi pump station - solving the cavitation induced conditions upstream from the pump inlets
Please contact our Webmaster with questions or comments. © Copyright 2017 Sinotech CC. All rights reserved.


WESTON Weston has restored normal water service to its 300-plus city customers after a mudslide ripped out a section of the main water line Saturday, July 28.
The city flowed water at low pressure to its customers from the Smith Frozen Foods, Inc. well until the repairs were made. The mudslide was caused by a leaking 14 inch Smith Frozen Foods, Inc. pipe.
According to Weston Police Sgt. Joshua Henningsen, the water pipes were installed about 40 years ago. There are an estimated 13,000 feet of pipe on the main line with over 760 fittings. During the summer, daily water flow through the system is approximately 200,000 gallons.


Seismic response analysis of tailing dam foundation on discontinuous rock masses and counter measure design
Sasaki, Takeshi*; Koshigai, Masaru*; Horikawa, Shigeo*; Fukushima, Shigeru ; Ohara, Yoshiyuki
The authors report an earthquake response analysis of a tailing dam with the foundation of the jointed rock masses. The non-linear deformation characteristics of the rock joints are assumed the combination of different angle of joint sets as Multiple Yield Model introduced by Sasaki et al. (1994). The geology of dam foundation of granite is classified as CH, CM, CL and D with two joint sets. The vertical and the horizontal angle of joints are combined in the granite. The height of the tailing dam is 10 meters and the width is 30 meters. The water gathering basin is constructed in front of the dam to collects the leakage water throw the rock joints of dam foundation with gravity type retaining wall. The input earthquake motion is assumed the several faults existing around the dame site were moved and the wave motions is calculating the statistic green function theory (Irikura et al.,1991). The non-linear deformation of joint of the normal and the shear direction are both depends on of the confining pressure presented by Bandis et al. (1981) and Kulhawy (1975), respectively. The two section models of the flowing down direction are analyzed by finite element method as the present state and the measures state. Collapse of the water gathering basin is fear misgivings by the earthquake motions. Therefore, in order to control of the collapse of water gathering basin with gravity type retaining wall, the additional new small gravity dam will be planed in front of the gravity wall. And section of the orthogonal axes of the dam is analyzed. According to the results, the tailing dam is sound, and the water gathering basin with gravity type wall is collapsed. And the additional small gravity dam considering counter measures is sound and the acceleration at the gravity type wall is one/ third reduction compare with non-counter measures. Therefore, the effect of the additional small gravity dam is very well for the strong earthquake in this analysis.


Busalla - Italy
PHASE 1: Acquedotto Nicolay S.p.A. - Genoa PHASE 2-3: Mediterranea delle Acque S.p.A.
1965-1986 / 1991-2002 / 2005-2008
Description for Busalletta Dam (Italy)
Dam built to provide a
reservoir for the urban water supply of Genoa.
The concrete gravity dam is a special structure on deformable foundations.
- Gravity dam ( H = 50 m, L = 222 m, V = 155'000 m³ )
- Spillway on dam crest ( Q = 230 m³/s )
- Bottom outlet ( Q = 50 m³/s, L = 211 m, D = 2.4 m )
- Preliminary design
- Final design
- Supervision of construction (with full technical responsibility)
- Consultancy during trial impounding and operation
- Preliminary and Final design of the outlet works
- Supervision of Construction
- Preliminary design for reservoir augmentation
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Yacht Harbour is on the right side of the Tevere River floodplain, about 1 km...
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The ambitious Tana Beles project was located in the Metekel district of...
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Hydropower cascade including the existing plants of Karjali (IP = 106 MW),...
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Mulembo-Lelya is a hydropower project located...
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The prestigious project of Batoka Gorge, with...
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Most Popular Product
|Home||» Products||» butterfly valves|
Based on their design, these Butterfly Valves can be used under different working conditions where abrasion, exposure to harsh chemical and low temperature is common occurrence. Available in different specifications, these metal valves are equipped with bolt holes around its diameter for trouble free attachment with pipe flanges. Light in weight, these valves are light in weight. Compact shape, open port based structure, excellent high pressure recovery performance, low pressure drop rate and high flow co efficiency level are the main features of Butterfly Valves. Application of these valves can be noticed in waste water treatment plants, power generation plants, chemical and oil processing plants.


The composition of the small house lift:
- Power system: hydraulic pump station
- Lifting device: hydraulic cylinder, pulley block, and steel wire rope
- Passenger (cargo) carrying device: car
- Guiding device: guide rail
- Control System
The small house lift have the following characteristics:
- There is no need to set up a machine room with high requirements and costs above the shaft.
- The computer room is set flexibly. The hydraulic transmission system relies on the oil pipe to transmit power so that the machine room can be arranged within 5m away from the shaft
The area occupied by the computer room is only 4-5 square meters.
- The requirement of shaft structure strength is low. Due to the vertical load, such as the self-weight and load of the hydraulic elevator car, all of them act on the shaft through the hydraulic cylinder
On the foundation, the requirement of building performance on the top of the shaft is low.
- Good safety and high reliability.
- Large load capacity. The hydraulic elevator lifts the car based on the principle of a hydraulic jack. Multiple oil cylinders can be used to lift the car at the same time
- Low noise. The hydraulic system can be set far away from the shaft to isolate the noise source.
Use and maintenance
For the hydraulic small house lifts, the structure is simple, and the failure rate is low.
It is convenient for rescue. When the hydraulic elevator goes down, it is driven by the pressure generated by its own weight. In case of power failure or failure, it only needs to open the emergency drop valve. Visit us now!


|Publication number||US3739810 A|
|Publication date||Jun 19, 1973|
|Filing date||Dec 9, 1971|
|Priority date||Dec 9, 1971|
|Publication number||US 3739810 A, US 3739810A, US-A-3739810, US3739810 A, US3739810A|
|Original Assignee||Jacuzzi Bros Inc|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (4), Referenced by (16), Classifications (13), Legal Events (3)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Wnited States Patent 1 Horan, Jr.
[ 1 June 19, 1973 PRESSURE CONTROLLED WATER SYSTEM WITH ISOLATABLE PRESSURE SWITCH  lnventor: Raymond E. Horan, Jr., Little Rock,
[ 7 3] Assignee: Jacuzzi Bros., Incorporated, Little Rock, Ark.
 Filed: Dec. '9, 1971 ] Appl. No.: 206,310
 US. Cl. 137/568, 417/38  Int. Cl. E03b 11/16, F04b 1 1/00  Field of Search 137/568; 417/30,
 References Cited UNITED STATES PATENTS 3,141,475 7/1964 Guinard et al 137/568 3,150,684 9/1964 Guinard et al 137/568 3,394,733 7/1968 Vacuzzi 137/568 3,572,381
3/l971 Nash 137/568 Primary Examiner-William RQCline Att0rnpy-Edward Brosler 57 7 ABSTRACT A water system with a pressure controlling valve, includes a pressure switch responsive to full closing of said valve to disconnect the pump in the system, and having its cut-in responsive pressure set sufficiently close to the cutout pressure, to assure delivery to service at pressure which is indistinguishably constant.
4 Claims, 6 Drawing Figures Patented June 19, 1973 3,739,810
2 Sheets-Sheet 1 FIG. 2
INVENTOK RAYMOND E. HORAN, JR.
Bug/M M ATTORNEY Patented June 19, 1973 2 Sheets-Sheet 2 INVENTOR.
ATTORNEY G. P M.
PRESSURE CONTROLLED WATER SYSTEM WITH ISOLATABLE PRESSURE SWITCH The present invention relates to Water Systems and more particularly to pressure control in such systems, and is particularly related to the automatic water system forming the subject matter of patent application Ser. No. 28,637, filed'Apr. 25, 1970 for TANKLESS AUTOMATIC WATER SYSTEM.
The system of the aforementioned Nash application is self starting in response to opening of a service line, and the pump continues pumping and meeting the demands of service, so long as service demands are in effect. Upon closing of the service line, the resulting increase in pressure is then coupled into a pressure switch which disconnects the pump motor to shut down the system.
In such system, the pump pressure varies with load, in accordance with the pressure head curve of the pump used, and it might at times exceed a pressure at lower flow rates, which might adversely afiect components in such systems, which are not designed to withstand such pressures.
Among the objects of the present invention are:
1. To provide a novel and improved water system.
2. To provide a novel and improved water system of the tankless type in which service pressure can never reach the full pressure capacity of the pump supplying the water in such system, throughout the high pressure portion of the pump head curve.
3. To provide a novel and improved water system wherein the service pressure remains substantially the same throughout the useful portion of the pump discharge capacity and particularly throughout the lower flow rates of the system, so long as the service demand does not exceedthe capacity of the pump.
4. To provide a novel and improved water system wherein the service pressure remains substantially the same regardless of the service demand, within the capacity of the pump to supply such service.
Additional objects of the invention will be brought out in the following description of a preferred embodiment of the same, taken in conjunction with the accompanying drawings wherein,
FIG. 1 is a view depicting a water system embodying the present invention; t
FIG. 2 is a view in section through a'valve assembly constituting an important component in the system combination of FIG. 1;
FIG. 3, 4 and 5 are fragmentary enlarged views depicting a feature in the functioning of the valve assembly of FIG. 2; and
FIG. 6 is a graph depicting the manner in which the system fucntions to alter the head capacity curve of the pump in accomplishing the purpose of the present invention.
Referring to the drawings for details of the invention in its preferred form, the system as illustrated involves a pump 1 of the submersible type driven by a motor 3 coupled thereto, the pump and motor being submerged below water level 5 in a well 7 and discharging through a discharge line 9 to a point above ground level 1 l. The water thus discharged, enters a service line 13, from which others may branch off, each terminating in a closed srvice valve 15, which may be a spigot or equivalent.
A switch means assembly including a pressure switch 19 connected in circuit with the pump motor, and a variable pressure device 21 installed in the service line, is responsive to the opening of the service line, to cause the pump to start and immediately deliver water to service at substantially a constant pressure, depending on the rate of flow of water to service.
The pressure switch may be any one of a conventional type normally employed in water pressure systems to control the pumping cycles of the pump, and the variable pressure device involves an expansible tube 23 of any elastic material disposed in a protective housing 25, this expansible tube being flow connected to the service line, and pressure connected via the water in the system, to the pressure switch by way of a valve assembly 29, such as depicted in detail in FIG. 2, which is installed intermediate the pump dishcarge line and the service line.
The capacity of the variable pressure device 21 is suf ficiently small as to respond to the opening of a service line and quickly drop the pressure therein to the lower pressure setting of the pressure switch at each opening of the service line. Thus the pump will function in response to the opening of a service line for essentially each and every demand from service.
As thus far described, except for the valve assembly of FIG. 2, the system incorporates features of the system illustrated and described in the application Ser. No. 28,637, filed Apr. 15, 1970, for Tankless Automatic Water System, the valve assembly of FIG. 2 introducing into the system certain marked features and advantages not realizable in the prior system.
The valve assembly involves a valve body 33 having open ends 35, 37, the pump discharge line being connected at one end 35 and the service line to the other end 37, the valve body including an enlarged midsection traversed by a partition 39 including a horizontal section which is provided with a main valve opening 41.
In line with this valve opening, is an opening 43 above in the upper wall of the housing.
-A valve 45 adapted to close this partition opening from below, is provided with a valve stem 47 extending upwardly through the upper opening. This valve stem terminates in an enlargement 49 at its upper end, which is slidably sealed with respect to adjacent surrounding wall by an O-ring 51.
While the partition itself may serve as the valve seat for such valve, and the wall of the upper opening as the wall with respect to which the stem enlargement is slidably sealed, I prefer to install a cylindrical insert 53 slidably fitting at its lower end into the valve opening in the partition and threadedly secured in the wall of the upper opening, the lower end of this insert providing a seat 55 for the main valve, while the interior cylindrical wall surface of the insert permitting a sliding fit of the stem extension as sealed by the O-ring.
In the closed position of the valve, the valve stern defines with the sleeve, a chamber 57, access to which from the pump discharge line, is provided through an opening 59 in the sleeve.
At its upper end, the sleeve terminates in a diaphragm support rim 61 of increased diameter, between which and a spring housing 63 is clamped a diaphragm 67 of expandable material, which in turn is affixed at its center to the enlarged end of the valve stem, by a flat head screw 69.
An established pressure is maintained on the diaphragm and valve stem by a compression spring 71 installed within the spring housing, between the diaphragm screw and an adjusting screw 73 extending through the upper end of the spring housing, to enable adjustment of the spring pressure against the valve stem and thereby determine maximum service pressure.
The main valve structurally involves a valving disc 75 of resilient compressible material of low durometer, surrounding a depending threaded extension 77 of the valve stem, and retained in its installed position by a backing disc 79 threaded onto this valve stem extension.
The diaphragm defines the upper wall of a chamber 80 which is placed in communication with the service line connection to the valve assembly, by means of a passageway 81 extending axially upwardly through the valve stem to the enlarged end thereof, where its direction is changed to cause it to emerge at a point above the O-ring seal.
In the lower wall of the valve assembly housing, is an opening 83 connecting interiorly of the service line side of the housing by a small passageway 85 terminating within the housing in a valve seat 87 directly below and in line with the valve stem passageway. To the housing at this opening 83 is coupled the pressure switch, which thus places the pressure switch in pressure communication with the pressure conditions existing in the service line.
With the pressure switch so coupled, provision is made for rendering the pressure switch ineffective while the pump is functioning and supplying service, by blocking the passageway 85, such provision taking the form of a pressure switch trip valve 91 having a valve stem 93 extending up into the lower end of the axial passageway and then bent at right angles to enter a side opening 95 provided in the lower extension of the valve stem. A compression spring 97 between the valve and the lower end of the main valve stem extension, serves to urge the pressure switch valve toward its seating position, and cause it to function as a spring loaded check valve should the pressure at the pressure switch exceed the pressure in the service line.
Such seating is permitted when the main valve is driven down to its open position, the length of the valve stem of the pressure switch trip valve being such that when the main valve establishes initial closing contact, the trip valve is still seated, but the over-ride permitted by the compressability of the valving disc, is sufficient to permit the main valve stem to lift the trip valve off its valve seat and put the pressure switch in pressure communication with the service line.
The condition of the pressure switch trip valve as illustrated in FIG. 2, represents the condition existing with all service line valves closed, thus representing no demand from service, and the expansible tube of the variable pressure device is expanded to the point of maintaining a pressure in the system above the cut off pressure setting of the pressure switch. The pressure switch is thus exposed to the pressure in the variable pressure device and the pump motor is disconnected from its source of power. The prevailing pressure in the service line due to the variable pressure device, will likewise be transmitted to the main valve and the diaphragm chamber, thereby serving to maintain the main valve in its fully closed condition and to assure that the trip valve will remain open.
With all conditions existing as thus described, the opening of a service line valve will permit the variable pressure device to collapse and immediately drop the pressure on the service line side of the valve assembly, whereby the pressure at the pressure switch will drop to its lower pressure setting to connect the pump motor and start the pump.
The main valve, due to this drop in pressure, will, in the meantime have opened.
Such opening of the main valve produces two effects, namely:
1. It places the pump in flow communication with the service line, and
2. It simultaneously closes the pressure switch valve and renders and pressure switch ineffective while the pump is supplying service.
Upon demand for service, the pump pressure will develop to a value such that the service line pressure approaches a desired value, as determined by the pressure setting of the spring 71, and without neccessarily lifting the pressure switch trip valve 91, since this valve is lifted only in response to the override of the main valve as permitted by the compressibility of the sealing disc of such main valve. Any tendancy of the line pressure to fluctuate for any reason, will be smoothed out by the action of the variable pressure device, which will serve to maintain a substantially constant pressure in the service line throughout the range in which the pump has the ability to supply the demands of service at such pressure. This is represented by the curve 96 of FIG. 6.
Following a closing of the main valve in response to an increase in the service line pressure sufficient to trip the pressure switch valve, any subsequent demands of service will bring about a rapid reduction in pressure in the diaphragm chamber, thereby permitting the main valve to unseat and allow delivery from the pump. Should the pump continue to deliver water at excessively high pressure, the main valve will hover about its closing position to preclude service pressure rising above the predetermined safe value, as determined by the pressure setting of the spring 71, despite the head capacity curve characteristic of the pump which might otherwise deliver water to service at pressures exceeding values which the components of the system can safely tolerate.
This is particularly pertinent to the service demands of low flow rate, which can be readily appreciated by referring to the curves of FIG. 6 wherein is depicted a conventional head/capacity curve 97 for a pump which, when plotted in terms of pounds per square inch against gallons per minute flow rate, will result in a pressure curve which rises rather steeply from its maximum capacity to the point where its discharge is throttled to zero.
For the particular pump represented by the head/- capacity curve of FIG. 6, the pressure developed at shut-off would be in the neighborhood of 104 pounds per square inch. If the desired service pressure is around 35 pounds (curve 96), the pump in question will be able to deliver, in the system as thus far described, at a flow rate up to approximately 25 gallons per minute. The maximum permissible pressure remains substantially the same to a point approaching shut-off of all service, when the pressure rises a pound or so per square inch as indicated by the sudden rise 98 in the pressure curve 96. This is attributable to sealing stress being built up in the compressible seat 75, during which the seat bleeds high pressure water to the service line, thereby causing a build up in pressure which reacts on the diaphragm, sealing off the flow more tightly until zero flow results. 7
In conventional pressure water systems, pressure switches are set to function at widely separated pressure values, such as a high setting of 50 p s i for opening and a low setting of p s i for closing, and such systems were said to have a pressure range between 50 p s i and 20 p s i. Such systems include storage capacity, and a wide pressure range is essential to preclude excessive cycling of the pump.
In the present system, and contrary to prior conventional practice, it becomes practical to narrow the pressure range setting of the pressure switch to a very narrow range 99, say of the order of 8 p s i, so that, instead of a high pressure setting of 50 p s i to open and a low pressure setting of 20 p s i to close, the high pressure setting may be lowered to say 35 p s i to open and the low pressure setting raised up to 27 p s i.
Thus the service line pressure cannot fluctuate outside this narrow pressure range, which represents essentially an average of the wide pressure variations capable of being experienced in prior art systems, and as I viewed from the service end of the system, any slight pressure variations occurring within such 8 p s i pressure range are undetectable by the user. Insofar as he is concerned, the system is delivering at a constant pressure, regardless of the service demand, a result which has been strived for but never previously achieved.
Actually, in setting the pressure switch for its higher value aetting, it is preferably set to approximately 40 p s i in the system under consideration, which is about 5 p s i above the desired higher pressure. In the example discussed above, where the desired higher pressure is 35 p s i, the pressure switch will be set to open at say 40 p s i and close at the 27 p s i value. This is to allow for variancesin switch operating points.
With the pressure switch thus set, and the system ready for service, an opening of a service line will immediately, upon drop in pressure to the p s i level, cause the pump to start and promptly build the pressure up to p s i, the pressure setting of the spring 71, the pressure switch in the meantime, having been cut off from pressure communication with the service line and rendered ineffective by the opening of the main valve.
Upon closing off all demand for service, opening of the pressure switch can occur as the discharge to service approaches zero, and being set to open at 40 p s i, the sudden rise as the flow reaches zero assures disconnection of the pump motor.
The 27 to 35 p s i levels referred to above, while representing the preferred range of pressure values, are merely illustrative. The narrow pressure range represented thereby, may be furthr narrowed if desired, and may, if one so wishes, be shifted to a higher or lower level, which in part may be dictated by the capacity of the pump employed in the system.
In order to minimize any adverse effects on the responses of the system to service demands, the main valve and valve stem are so designed that the effective area of the valve exposed to the pump pressure is essentially balanced by the enlarged upper end of the valve stem inclusive of the O-ring seal, thus eliminating any adverse effects which varying high pump input pressures might otherwise have on the operation of the main valve.
From the foregoing description of my invention in its preferred form, it will be apparent that the same is subject to alteration and modification without departing from the underlying principles involved, and I accordingly do not desire to be limited in my protection to the specific details illustrated and described, except as may be necessitated by the appended claims.
1. A pressure water system comprising a pump having a discharge line, motor drive means coupled to said pump, a service line terminating in a service valve and a pressure responsive valve between said discharge line and said service line adapted to close upon a rise in service line pressure to a predetermined value, a pressure switch in circuit with said motor drive means, means pressure coupling said pressure switch to said system on the service side of said pressure responsive valve, valve means adapted to block said pressure coupling during open condition of said pressure responsive valve and while supplying water to service, and unblock said pressure coupling during a minimum and no-flowcondition of said system, and pressure maintaining means in said system responsive to the opening of said service valve causing initial flow with corresponding pressure reduction, to cause said pressure switch to connect said motor drive means in circuit and drive said pump, flow from which causes said pressure responsive valve to open and block said pressure coupling 2. A pressure water system in accordance with claim 1, characterized by said pressure switch being set to disconnect said pump motor from circuit at a pressure value of the order of the closing pressure of said pressure responsive valve and set to connect said pump in circuit at a pressure value of the order of 8 p s i below the circuit opening pressure.
3. A pressure water system comprising a pump, a motor connected to drive the pump, a service line for delivering water to a service valve, a pressure regulating valve between the pump and the service line adapted to regulate the maximum pressure in the service line when the service valve is open and the pump is functioning, a pressure switch in electric circuit with said motor and in hydraulic circuit with said service line, said swith being adapted to close the electric circuit and connect said pump motor when exposed to a predetermined low pressure in the service line of a value below said valve regulated pressure, and to open the electric circuit and disconnect said pump motor when exposed to a service line pressure approximately that of said valve regulated pressure, means responsive to the opening of the pressure regulating valve to close the hydraulic circuit to said pressure switch and thus isolate said pressure switch when the regulating valve opens, and to maintain the hydraulic circuit to said pressure switch closed until the pressure regulating valve is substantially completely closed, whereby said pressure switch may function to disconnect said pump motor at approximately the regulated pressure.
4. The system of claim 3 wherein said pressure regulating valve closes through a disc of resilient, compressible material of low durometer and the motion of the valve in compressing the disc during closing is the motion that opens said hydraulic circuit and expose said pressure switch to service line pressure.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US3141475 *||May 31, 1961||Jul 21, 1964||Andre Guinard Paul||Regulating valve for a pump controlled by a pressure responsive switch|
|US3150684 *||Oct 5, 1962||Sep 29, 1964||Andre Guinard Paul||Device for the delivery of a fluid supplied by a motorpump|
|US3394733 *||Jan 27, 1965||Jul 30, 1968||Jacuzzi Bros Inc||Airless water pressure system|
|US3572381 *||May 26, 1969||Mar 23, 1971||Jacuzzi Bros Inc||Pump pressure system|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US3814543 *||Jan 30, 1973||Jun 4, 1974||Jacuzzi Bros Inc||Pump systems for liquids|
|US3871792 *||Nov 28, 1973||Mar 18, 1975||Jacuzzi Bros Inc||Pump system and valve assembly therefor|
|US3931830 *||Mar 20, 1974||Jan 13, 1976||Jacuzzi Bros. Incorporated||Pump systems for liquids|
|US3973877 *||Nov 26, 1974||Aug 10, 1976||Hitachi, Ltd.||Automatic pumping device|
|US4081621 *||Apr 26, 1976||Mar 28, 1978||Carr-Griff, Inc.||Pressure switch with diaphragm and valve means|
|US4247260 *||Feb 7, 1979||Jan 27, 1981||Siemens Aktiengesellschaft||Pressure regulated water supply system|
|US4519418 *||Feb 17, 1984||May 28, 1985||Fowler L B||Water well pumping system|
|US5295807 *||Mar 1, 1993||Mar 22, 1994||The Coca-Cola Company||Variable output pump adjustment mechanism|
|US5509787 *||Oct 7, 1994||Apr 23, 1996||Valdes; Osvaldo J.||Hydraulic actuator for pressure switch of fluidic system|
|US5947690 *||Jun 4, 1998||Sep 7, 1999||Flexcon Industries||Actuator valve for pressure switch for a fluidic system|
|US5988984 *||Jul 2, 1997||Nov 23, 1999||Austin; Cary M.||Method and apparatus for liquid control system having a valve with a notch in the seal for enabling a sufficient fluid to pass through when the seal is fully closed to cool the pump and/or motor|
|US6062822 *||Jan 22, 1998||May 16, 2000||Alfred Karcher Gmbh & Co.||High-pressure cleaning apparatus|
|US6227241||Aug 25, 1999||May 8, 2001||Flexcon Industries||Actuator valve for pressure switch for a fluidic system|
|US20150192930 *||Apr 16, 2014||Jul 9, 2015||Maxtec Plastics, Inc.||Method for controlling water outgoing from container by pressure and device for achieving the same|
|EP0459434A2 *||May 29, 1991||Dec 4, 1991||Osvaldo Valdes||Hydropneumatic constant pressure device for automatic control of the operation and stopping of electrical motorpumps|
|WO1998057065A1 *||Jun 4, 1998||Dec 17, 1998||Flexcon Industries||Actuator valve for pressure switch for a hydraulic system|
|U.S. Classification||137/565.34, 417/38|
|International Classification||F04D15/02, E03B5/04, G05D16/06, G05D16/04, E03B5/00|
|Cooperative Classification||F04D15/0209, E03B5/04, G05D16/0663|
|European Classification||E03B5/04, G05D16/06H8E, F04D15/02B|
|Jul 8, 1999||AS||Assignment|
Owner name: JACUZZI INC., CALIFORNIA
Free format text: NUNC PRO TUNC ASSIGNMENT EFFECTIVE AS OF 6-30-98;ASSIGNOR:JACUZZI INC.( A FORMER DELAWARE CORPORATION);REEL/FRAME:010061/0874
Effective date: 19990225
|Mar 30, 1999||AS||Assignment|
Owner name: JACUZZI INC., A DELAWARE CORPORATION, CALIFORNIA
Free format text: NUNC PRO TUNC ASSIGNMENT;ASSIGNOR:JACUZZI INC., A FORMER DELAWARE CORPORATION;REEL/FRAME:009866/0373
Effective date: 19880402
|May 21, 1981||AS||Assignment|
Owner name: JACUZZI INC., 11511 NEW BENTON HIGHWAY, LITTLE ROC
Free format text: NUNC PRO TUNC ASSIGNMENT;ASSIGNORS:JACUZZI WHIRLPOOL BATH, INC.;JACUZZI BROS., INC.;REEL/FRAME:003873/0510;SIGNING DATES FROM 19810424 TO 19810508


Power Machines has announced it has completed modernisation of the hydraulic unit No 19 at RusHydro’s Volzhskaya hydropower plant in Russia, the 21st of 23 units the company has worked on.
For unit 19, Power Machines performed work on replacing the turbine, generator, excitation system, automation system and auxiliary equipment, increasing power output of the unit.
The new turbine has an improved design and is characterized by a high degree of environmental safety, says Power Machines. The updated impeller has five blades instead of the previous six and is designed for increased water flow through the turbine. Improved technical specifications of the unit allow increasing its capacity by 10.5MW in the future.
Work is continuing to modernise the remaining two units at the project, unit no 10 where Power Machines will replace the turbine and generator, and Unit No 19, where the generator will be replaced.
Today, at Volzhskaya HPP Power Machines continues modernization of two remaining hydroelectric units, with one involving the replacement of turbine and generator and the other replacement of the generator.
Once all 23 units are modernised at the plant, capacity will be increased to 2744.5MW.


The Islamic University of GazaFaculty of EngineeringCivil Engineering DepartmentHydraulics - ECIV 3322 Chapter 6 Water Flow in Open Channels 1
Introduction An open channel is a duct in which the liquid flows with a free surface. Open channel hydraulics is of great importance in civil engineers, it deals with flows having a free surface, for example: • Channels constructed for water supply, irrigation, drainage, and • Sewers, culverts, and • Tunnels flowing partially full; and • Natural streams and rivers. 2
Pipe Flow and Open Channel Flow • Open Channel Flow • Flow takes place due to the slope of the channel bed (due to gravity). • The flow must be classified as open channel flow if the liquid has a free surface. Pipe Flow • The liquid completely fills the pipe and flow under pressure. • The flow in a pipe takes place due to difference of pressure (pressure gradient), • The flow in a closed conduit is not necessarily a pipe flow.
Open Channel Flow Pipe Flow
For Pipe flow (Fig. a): • The hydraulic gradient line (HGL) is the sum of the elevation and the pressure head (connecting the water surfaces in piezometers). • The energy gradient line (EGL) is the sum of the HGL and velocity head. • The amount of energy loss when the liquid flows from section 1 to section 2 is indicated by hL. For open channel flow (Fig. b): • The hydraulic gradient line (HGL) corresponds to the water surface line (WSL); where it subjected to only atmospheric pressure which is commonly referred to as the zero pressure reference. • The energy gradient line (EGL) is the sum of the HGL and velocity head. • The amount of energy loss when the liquid flows from section 1 to section 2 is indicated by hL. For uniform flow in an open channel, this drop in the EGL is equal to the drop in the channel bed.
6.1 Classifications of Open Channel Flow Classification based on the time criterion: • Steady Flow (time independent) (discharge and water depth do not change with time) • Unsteady Flow (time dependent) (discharge and water depth at any section change with time) Classification based on the space criterion: • Uniform flow (are mostly steady) (discharge and water depth remains the same at every section in the channel) • Non-uniform Flow (discharge and water depth change at any section in the channel)
Non-uniform flow is also called varied flow ( the flow in which the water depth and or discharge change along the length of the channel), it can be further classified as: • Gradually varied flow(GVF) where the depth of the flow changes gradually along the length of the channel. • Rapidly varied flow (RVF) where the depth of flow changes suddenly over a small length of the channel.
Unsteady uniform flows are very rare in nature • Uniform flow are mostly steady • Steady varied flow • (over a spillway crest) • Unsteady varied flow (flood wave) • Unsteady varied flow (tidal surge)
6.2 Uniform Flow in Open Channel Uniform flow in an open channel must satisfy the following main features: • The water depth y, flow area A, discharge Q, and the velocity distribution V at all sections throughout the entire channel length must remain constant. • The slope of the energy gradient line (Se), the water surface slope (Sws), and the channel bed slope (S0) are equal. Se = Sws = S0
This is possible when the gravity force (W sinq)component equal the resistance to the flow (Ff) The Chezy Formula
Rh = hydraulic radius or hydraulic mean depth • C = Chezy coefficient (Chezy’s resistance factor), m1/2/s, varies in relation of both the conditions of channel and flow. • Manning derived the following empirical relation: • where n = Manning’s coefficient for the channel roughness • See the next table for typical values of n.
Manning’s formula • Substituting into Chezy equation, we obtain the Manning’s formula for uniform flow: OR Where: • Q in m3/sec, • V in m/sec, • Rh in m, • Se in (m/m), • n is dimensionless
Example 1 Open channel of width = 3m as shown, bed slope = 1:5000, d=1.5m find the flow rate using Manning equation, n=0.025.
Example 2 The cross section of an open channel is a trapezoid with a bottom width of 4 m and side slopes 1:2, calculate the discharge if the depth of water is 1.5 m and bed slope = 1/1600. Take Chezy constant C = 50.
Example 2 Open channel as shown, bed slope = 69:1584, find the flow rate using Chezy equation, take C=35.
6.3 Hydraulic Efficiency of open channel sections Based on their existence, an open channel can be natural or artificial: • Natural channels: such as streams, rivers, valleys, etc. These are generally irregular in shape, alignment and roughness of the surface. • Artificial channels: built for some specific purpose, such as irrigation, water supply, wastewater, water power development, and rain collection channels. These are regular in shape and alignmentwith uniform roughness of the boundary surface.
Based on their shape, an open channel can be prismatic or non-prismatic: • Prismatic channels: the cross section is uniform and the bed slop is constant. • Non-prismatic channels: when either the cross section or the slope (or both) change, the channel is referred to as non-prismatic. It is obvious that only artificial channel can be prismatic. • The most common shapes of prismatic channels are rectangular, parabolic, triangular, trapezoidal and circular; see the next figure.
Most economical section is called the best hydraulic section or most efficient section as the discharge, passing through a given cross-sectional area A, slope of the bed S0 and a resistance coefficient, is maximum. • Hence the discharge Q will be maximum when the wetted perimeter P is minimum.
Economical Rectangular Channel P should be minimum for a given area; So, the rectangular channel will be most economical when either: the depth of the flow is half the width, or the hydraulic radius is half the depth of flow.
Other criteria for economic Trapezoidal section • When a semi-circle is drawn with the trapezoidal center, O, on the water surface and radius equal to the depth of flow, D, the three sides of the channel are tangential to the semi-circle”. • To prove this condition, using the figure shown, we have: using triangle KMN, we have:
using equation to replace the numerator , we obtain: Thus, if a semi-circle is drawn with O as center and radius equal to the depth of flow D, the three sides of a most economical trapezoidal section will be tangential to the semi-circle.
Now, from equations: squaring both sides The best side slope is at 60o to the horizontal, i.e.; of all trapezoidal sections a half hexagon is most economical. However, because of constructional difficulties, it may not be practical to adopt the most economical side slopes
Circular section In the case of circular channels, the area of the flow cannot be maintained constant. Indeed, the cross-sectional area A and the wetted perimeter P both do not depend on D but they depend on the anglea. Referring to the figure shown, we can determine the wetted perimeter P and the area of flow A as follows: • Thus in case of circular channels, for most economical section, two separate conditions are obtained: • Condition for maximum discharge, and • Condition for maximum velocity.
Condition for Maximum Discharge for Circular Section: (Using the Chezy formula) (Using Manning’s formula) • Condition for Maximum Velocity for Circular Section:
6.4 Energy Principle in Open Channel Flow The total energy of a flowing liquid per unit weight is given by: If the channel bed is taken as the datum, then the total energy per unit weight will be: Specific energy(Es)of a flowing liquid in a channel is defined as energy per unit weight of the liquid measured from the channel bed as datum. It is a very useful concept in the study of open channel flow.
Ep = potential energy of flow = y Ek= kinetic energy of flow = Valid for any cross section Specific Energy Curve: It is defined as the curve which shows the variation of specific energy (Es ) with depth of flow y.
Specific Energy Curve (Rectangular channel) Considera rectangular channel in which a constant discharge q = discharge per unit width = = constant ( since Q and B are constants) EK Es EP yc
T T Sub-critical, critical, and supercritical flow The criterion used in this classification is what is known by Froude number, Fr, which is the measure of the relative effects of inertia forces to gravity force: V = mean velocity of flow of water, Dh = hydraulic depth of the channel
Referring to the energy curve, the following features can be observed: • The depth of flow at point C is referred to as critical depth, yc. • (It is defined as that depth of flow of liquid at which the specific energy is minimum, The flow that corresponds to this point is called critical flow (Fr = 1.0). • For values of Es greater than Emin , there are two corresponding depths. One depth is greater than the critical depth and the other is smaller then the critical depth, for example; These two depths for a given specific energy are called the alternate depths. • If the flow depth the flow is said to be sub-critical (Fr < 1.0). In this case Es increases as y increases. • If the flow depth the flow is said to be super-critical (Fr > 1.0). In this case Es decreases as y increases.
Critical depth, yc for rectangular channel Critical depth, yc , is defined as that depth of flow of liquid at which the specific energy is minimum, Emin, The mathematical expression for critical depth is obtained by differentiating energy equation with respect to y and equating the result to zero;
Critical depth, yc, for Non- Rectangular Channels OR (constant discharge is assumed) dA/dy = the rate of increase of area with respect to y = T (top width). condition must be satisfied for the flow at the critical depth. Recalling that The equation may also be written in terms of velocity The velocity head is equal to one-half the hydraulic depth for critical flow.
This equation represents the critical state The general equation for the specific energy in critical state applicable to channels of all shapes. OR Rectangular section Trapezoidal section Circular section Triangle section
Constant Specific Energy The specific energy was varied and the discharge was assumed to be constant. Let us now consider the case in which the specific energy is kept constant and the discharge Q is varied. The discharge will maximum if dA/dy = T
but Thus for a given specific energy, the discharge in a given channel is a maximum when the flow is in the critical state. The depth corresponding to the maximum discharge is the critical depth.
6.5 Hydraulic Jump • A hydraulic jump occurs when flow changes from a supercritical flow (unstable) to a sub-critical flow (stable). • There is a sudden rise in water level at the point where the hydraulic jump occurs. • Rollers (eddies) of turbulent water form at this point. These rollers cause dissipation of energy. • A hydraulic jump occurs in practice at the toe of a dam or below a sluice gate where the velocity is very high.
General Expression for Hydraulic Jump: In the analysis of hydraulic jumps, the following assumptions are made: (1) The length of hydraulic jump is small. Consequently, the loss of head due to friction is negligible. (2) The flow is uniform and pressure distribution is due to hydrostatic before and after the jump. (3) The slope of the bed of the channel is very small, so that the component of the weight of the fluid in the direction of the flow is neglected.
Location of hydraulic jump • Generally, a hydraulic jump occurs when the flow changes from supercritical to subcritical flow. • The most typical cases for the location of hydraulic jump are: • Jump below a sluice gate. • Jump at the toe of a spillway. • Jump at a glacis. • (glacis is the name given to sloping floors provided in hydraulic structures.)
The net force in the direction of flow = the rate of change of moment in that direction The net force in the direction of the flow, neglecting frictional resistance and the component of weight of water in the direction of flow, R = F1 - F2 . Therefore, the impulse-moment yields Where F1 and F2are the pressure forces at section 1 and 2, respectively. = the distance from the water surface to the centroid of the flow area
Comments: • This is the general equation governing the hydraulic jump for any shape of channel. • The sum of two terms is called specific force (M). So, the equation can be written as: • M1 = M2 • This equation shows that the specific forcebefore the hydraulic jump is equal to that after the jump.
Hydraulic Jump in Rectangular Channels using , we get


Hydac DFP Series High Pressure Filters
- The filter housings are designed to withstand pressure surges as well as high static pressure loads.
- The screw-in bowl allows the filter element to be easily removed for replacement or cleaning.
- A visual (pop-up), electrical, electrical/visual (lamp), or electronic differential type clogging indicator can be installed.
- DFP filters are available with or without a bypass valve so either high or low collapse pressure elements may be used.
- Multiple indicator port locations (DFP330/660/1320 only) also allow two different types of indicators to be installed into the filter. Indicators of the same type, but with different trip pressures can also be installed.
- Fatigue pressure rating equals maximum allowable working pressure rating.


Thermal-hydraulic model for axial piston pump with leakage and friction and its application
Industrial Lubrication and Tribology
Article publication date: 29 May 2019
Issue publication date: 22 August 2019
This paper aims to carry out a thermal-hydraulic simulation model for pump and hydraulic system to predict the temperature increasing and pump performance. Based on the model, how to alleviate the temperature is introduced. Besides, the optimization of piston is carried out.
This paper analyzes the heat generation in lubricating interfaces of the pump with energy conversion theory. The heat transfer inside the pump is analyzed with the control volume method. The simulation model is constructed in AMESim because of its operating friendly nature. The experiment is carried out to prove the validity and accuracy of the simulation model.
Temperature has less effect on the mechanical loss of pump. However, it has a great impact on volumetric efficiency. To reduce the temperature on the piston surface, the size of the piston should be optimized.
This paper fulfills a novel thermal-hydraulic model to evaluate the temperature of the pump. Based on the model, the performance of the pump is determined and optimization is carried out.
Shi, G. and Wang, H. (2019), "Thermal-hydraulic model for axial piston pump with leakage and friction and its application", Industrial Lubrication and Tribology, Vol. 71 No. 6, pp. 810-818. https://doi.org/10.1108/ILT-02-2018-0085
Emerald Publishing Limited
Copyright © 2019, Emerald Publishing Limited


Hydraulic transmission of injection molding machines uses hydraulic oil as a working medium and uses the pressure energy of hydraulic oil in sealed working volume to transmit energy or power or signals. The quality of hydraulic oil and seals directly affects the stable work of the hydraulic system and indirectly affects the product quality. To prevent and reduce the faults of the hydraulic system, reduce wear and prolong service life, we should strictly use and maintain hydraulic oil.
Generally speaking, 70% of hydraulic device failures are caused by incorrect or improper use and maintenance of hydraulic oil. Maintaining good maintenance habits and preventive maintenance is the most effective way to reduce and prevent hydraulic failures of machines. Therefore, fine maintenance of hydraulic oil and hydraulic system is very important. Therefore, it is necessary to introduce the characteristic requirements of hydraulic oil.
The most important properties of hydraulic oil are viscosity and cleanliness, as well as good anti-oxidation, anti-wear, anti-foam, anti-corrosion, and good lubrication.
The viscosity of hydraulic oil is expressed by the average kinematic viscosity at 40℃. Our commonly used No. 46 anti-wear hydraulic oil (46csT/40℃) means that the average kinematic viscosity of this hydraulic oil is 46m2/S at 40℃.
The relationship between the viscosity of hydraulic oil and pressure and temperature is as follows: The viscosity decreases with the increase of the temperature; while the viscosity increases with the increase of the pressure.
Periodic testing of hydraulic oil performance. If the oil is polluted or deteriorated, the service life of the injection molding machine will be shortened, and faults may occur. Therefore, it is necessary to periodically test the oil to detect the change in oil performance. Based on this, whether to change the oil may be decided. (If conditions permit, the data value detected by a professional laboratory is the best) We can use simple visual methods to understand the oil status:
Appearance test: New oil samples and used oil samples are put into their own test tubes, and their color, clarity, floating objects, and water precipitation at the bottom of test tubes are compared.
Dropping test: The old oil drops are put on the filter paper (oil-absorbing paper) and observed after one hour. If the oil is dirty or obviously deteriorated, the pollutants will be easy to be observed.
Finger rubbing: The used oil can be rubbed on fingers. If the viscosity decreases and deteriorates, the hand feels rough and there is no sticky feeling. The oil drops fall from fingers smoothly and there is no sticky rebound.
Hydraulic maintenance starts from the following aspects
(1) Replace the old hydraulic oil
In principle, the hydraulic oil should be changed every 5,000 machine operating hours or at most one year. No matter how good the hydraulic oil is, after being used for a certain period of time, the worn metal and rubber particles of pumps and other moving parts will enter the oil, which will cause the formation of sludge and dirt. During the normal maintenance, some pollutants will stick to the parts and be brought into the hydraulic oil.
Even if the hydraulic oil is used correctly, it is generally considered that its service life is one year, up to two to three years. Once it deteriorates, it is required to be replaced with new oil without hesitation. Good oil quality is the cornerstone to maintaining the stability of the hydraulic system.
Hydraulic oil is filled with a special oil filter truck instead of a pumping unit refitted with a pump. The author has seen many simple oil pump trucks refitted with pumps, which pump wastewater and waste oil, and also add new oil.
The pump that has pumped wastewater and oil has no filter screen, and the dirtiest impurities lurk in the pump and pipeline, which are mixed with the new oil and added into the oil tank. The author has used boxes many times to observe that the new oil that has just started pumping contains a lot of pollutants. These pollutants will only pollute the new oil and damage the pump and valves.
The precision of the filter screen of a professional oil filter truck is usually 125um (micron), and there are generally two filter screens, double protection filtering, to protect the cleanliness of oil products.
(2) Clean the inside of the oil tank
Hydraulic maintenance is not as simple as pumping old oil, or just adding some new oil. It is important not only to replace new oil but also to clean hydraulic equipment.
After the old oil is pumped clean, the oil tank should not be wiped with rags to prevent the thread ends from blocking the filter screen. Using professional cleaning agents is expensive, and there are residues. An experience taught by a 20-year-old mechanic: Ordinary flour can be used to be kneaded into a dry dough by adding an appropriate amount of clean water, and then it can be divided into several pieces to smear oil, impurities, and metal powder in the oil tank. It is clean and economical, and has no residues.
The magnetic frame and filter screen in the oil tank can be cleaned with kerosene and a copper brush; afterwards, they can be cleaned and dried with an air gun.
(3) Clean the air filter
The air filter outside the oil tank makes it easy for the air inside the oil tank to get in and out according to the change of the oil level inside the oil tank. Every time the oil is changed and maintained, the air filter should be taken out, cleaned with kerosene and dried with an air gun. If it is not cleaned, the dirt may enter the oil tank and affect the oil quality.
(4) Clean the inner and outer walls of the oil-water cooler
The scale inside and outside the cooler tube should be cleaned with a weak hydrochloric acid solution, rinsed with water and dried with an air gun.
The dirt on the baffle plate should be cleaned with a copper brush.
(5) Clean the oil valve
First, the dirt outside the valve can be cleaned with a waste cloth and an air gun. The plug can be unplugged and the oil valve can be disassembled. The valve core and the oil sludge and sundries on the valve body can be cleaned with a kerosene brush and dried with an air gun. Attention should be paid to avoid installing the valve core upside down and O-ring missing.
(6) Clean the oil cylinder
After disassembling the mold locking, thimble, pedestal, and glue injection cylinder, the cylinder block and piston can be cleaned with kerosene, and the worn and damaged oil seal, dust seal, and O-ring can be replaced. The reasons for disassembling the oil cylinder, checking the oil seal, and making replacements are shown as follows:
1. The stability of injection pressure is a major factor that determines the quality of finished products. Every 20,000 machine working hours or at most five years, the sealing ring and wear ring should be replaced. Although the oil seal used for five years is not badly damaged, it must also be replaced. It cannot be repaired until the occurrence of oil leakage, carbonization, or pressure relief, or when the machine is broken down.
2. Whether the piston rod is loose can be checked.
3. Cleaning the equipment parts is also a maintenance method.
(7) Replace the bypass filter element.
(8) Check whether the fastening oil pipe joints are loose, and replace the aging leaking oil pipes.


Wandfluh poppet valves are available as direct operated and pilot operated, with flange-, sandwich- and cartridge construction and electric- pneumatic-, hydraulic- and mechanical actuation. They are used where tight closing is essential – like leak-free load holding, clamping or gripping.
Maximum pressures are up to 350 bar, with flows up to 300 litres/minute.
Other features of Wandfluh poppet valves include:
- Nominal sizes: NG3-Mini, NG4-Mini, NG6 and NG10
- Screw-in cartridges: M18x1.5, M22x1.5 and M33x2
- Very good tightness in both flow directions
- Optional venting
- Valve through-flow in both directions
- ATEX, explosion-proof versions available
The range includes:
- 2-way: SDEPM20-X5 | SDEPU08-X5 | SVEPM20-X5 | SVEPU08-X5 | 2203 | 2204 | 2206 | 2210 | SDSPM18-35 | SDSPM18 | SDYPM18 | SDZPM18 | SDSPM22-35 | SDSPM22 | SDSPM22-K9 | SDYPM22 | SLYPM22-FG | SLYPM22-FG-K9 | SVSPM18 | SVSPM22 | SVYPM22 | SVYPM33 | SVSPM42 | B-2203 | B-2204 | A-2206 | A-206-Z | A-3206rr | A-2210 | A-210-Z | Z-2203 | Z-2204 | Z-2206 | Z-2210 | G-2204 | G-2206 | G-2210 | BEXd2204 | AEXd-06 | AEXd-206-K9 | AEXd-206-Z104 | AEXd3206rr | BH2204 | AH2206 | AG2206 | AH2210 | BK2204 | AK2206 | AK2210 | A-3206-S1779
- 3-way: A-4306
- 4-way: B-2203 | B-2204 | A-2206 | A-2210 | BEXd2204 | AEXd-06 | BH2204 | AH2206 | AG2206 | AH2210 | BK2204 | AK2206 | AK2210
Please contact us for further technical details and configuration options, or if you cannot see the Wandfluh poppet valves that you need – we’ll be delighted to help!


Source Water Planning
Source Water Policy- Québec
Back to Compare
Jurisdiction implements this indicator
Jurisdiction does not implement this indicator
Jurisdiction partially implements this indicator
Groundwater protection planning is required
Watershed scale protection planning is required
Watershed management plans incorporate aspects of source water protection planning.
Dedicated protection plans are required at the community water supply scale
Dedicated funding is available to implement plans
Periodic updates to plans are required
Periodic updates to source water plans are not required.
In the U.S. for Fiscal Year 2022, State Revolving Fund set-asides were used for source water protection programs


In the public sector the water supply is one of the major consumers of electrical energy. At the same time, for means of pressure control in the water pipelines, energy has to be “destroyed” constantly by converting it into useless noise and thermal energy. The project EWID shows new ways of reducing this energy loss. Turbine-driven pumps (pump as turbine, PaT) assume the function of conventional pressure reducers in the water distribution system and, at the same time, produce electrical energy. Hereby the energy balance in the water system is improved and a contribution to the energy self-supply is made.
The delivery of water follows typical seasonal and daily profiles, which are usually overlaid with current supply fluctuations. This leads to constant pressure fluctuations, especially in the lower areas of the network located in close vicinity to the consumers. Under these conditions, only a part of the pressure energy can be converted to electrical energy if a turbine is “simply” installed in the pipeline. Therefore, one goal of EWID is to design a system that adapts itself to the current situation dynamically and intelligently.
Fig. 1: Height differences for energy production in model region Bavarian uplands
This research project contributes significantly to energy efficiency and energy generation in the water management sector. The intelligent pressure control also contributes to the reduction of material stress and water loss, thereby promoting the sustainable use of natural water resources.
The aim of this project is the replacement or the implementation of the “classic” energy-dissipation-based pressure management in the water distribution system (by means of valves) with an energy-generation-based pressure management. The advantages of this approach are twofold: first, new chances of electrical energy production can be developed; second, new ways of improving the energy efficiency in the water sector can be identified.
In the research project a PaT-System (pump as turbine) will be developed. It is composed of a pressure control unit plus an energy production unit (running backward pump + generator) and a higher-level control for the intelligent pressure management. This system configuration constitutes the testing device. For the different development stages of the PaT-system with its additional components, extensive testing on a test stand (test track and testing facility) is required. The design of this system is accompanied by the compilation of the process principles for the internal control of the unit. Here, algorithms for the optimized pressure control in the distribution network must be developed. In order to define the testing configuration for the system, the boundary conditions of the application partners must be defined and suitable pilot areas must be selected. The network data from GIS and process control systems will be provided by the network operators. If the data are not sufficient, additional measuring must be carried out beforehand. For the comparability of the total recorded data, it must be transferred into a common data structure in a unified way.
The aim here is the decentralized compilation, transfer and processing of data in the network of the water suppliers. Hard- and Software components must therefore be developed. These must enable a secure and efficient data transfer between the communication units (Com-Units) in the network (inclusive cross-communication) and the central control system, through the implementation of different interfaces, as well as the linking of sensors, control units and analog/digital input/output signals to decentralized network stations. Due to the dynamics in the water distribution system, this must happen in “quasi real time”. While the dynamic model adaptation takes place, the transferred information must be used for deriving control logics and commands for the intelligent pressure management for controlling the hydraulic PaT-units (testing device and field tests).
Fig. 2: Technical plant for pressure increase/reduction
The objective here is the link between optimized demand-based pressure control for the distribution system with the maximum energy production performed by the PaT-unit (testing device and later in field tests). The “near real time” modeling of the water network combined with optimization strategies must therefore be tested. Control strategies for the “intelligent” pressure management, based on physical real-time-measured parameters, such as pressure and flow, as well as model-based data have to be developed und validated.
In addition, data regarding potential energy production and investment costs will be collected, and recommendations for the energy use in island operation will be worked out. After the design and validation of the “novel system unit”, it will be installed in a real network. Hereby the system control with installed pressure sensors at critical points must take place, in order to test a decentralized pressure management. After a successful start-up, the system must be calibrated and optimized, and its performance must be adapted for continuous operation.
Based on the results of the testing device and on the verification of the system in a real network, a guideline will be presented by means of a final report, as a practical working tool for professional associations (DVGW), water suppliers, municipalities and planers. For enabling the application of the designed system in other companies in the water sector, a detailed compilation of the technical and administrative boundary conditions will be carried out. Topography, population density, hydrogeology and climate act a decisive part. Also the supply structures (centralized/decentralized) and network size will be considered here.


The load sense system is the least used and the least understood system of the three, but offers perhaps the most potential for efficient use of energy.
The load sense system is also controlled by pressure like the constant pressure system, but not in direct proportion, which usually results in greater system efficiency.
The load sense system has a control pressure of 200 psi.
2 shows, the load sense system is 50% efficient at a very low pressure of 200 psi, regardless of the flow usage rate.
This gives the load sense system a significant efficiency advantage over the constant flow system, especially in higher-pressure and low-to medium-flow situations.
3 indicates, the load sense system provides better efficiency than the constant pressure system at all pressures up to 3800 psi.
At low-pressure standby, a load sense system is at control pressure.


INSTALLATION OF FIRE SUPPRESSION SPRINKLER SYSTEMS AT THREE FACILITIES IN ROCK CREEK PARK
The uphill slope from Military Road to the three facilities would reduce water pressure in the new water main, which would compromise the efficacy of the sprinkler systems. To fix this condition, a diesel water pump would be installed at each location to increase water pressure to that location's fire suppression sprinkler system. The first pump would be installed at the Horse Center. In order to accommodate this pump, the former tack room at the Horse Center would be enlarged and extended outward from the current building, maintaining the existing roofline to preserve architectural continuity. Diesel water pump installations at the Maintenance Yard and Nature Center would be postponed pending a performance review of the pump at the Horse Center and the availability of additional funding.
Environmental Protection Specialist
Rock Creek Park
3545 Williamsburg Lane, NW
Washington, DC 20008
NPS proposes to install fire suppression sprinkler systems at the Nature Center, the Public Horse Center, and the Maintenance Yard, fed by a new water main. The water main would run from Military Road, NW, to the Nature Center, the Public Horse Center, and the Maintenance Yard. Its installation would roughly parallel an existing (but limited) water main that already serves these facilities. In order to minimize the ecological impact (e.g., felled trees), approximately 2430 linear feet of water main piping would be installed using a jack-and-bore approach with directional, underground drilling. Boring pits would be located in previously disturbed areas, if possible.


Hydraulic flow meters measure the linear, nonlinear, mass, and volumetric flow rate of hydraulic fluids. The three parts of a hydraulic flow meter are the device, transducer, and transmitter. The transducer senses the movement of the hydraulic fluid, while the transmitter produces a flow signal from the transducer’s sensed signal. The calculation of the volume and flow is based on the concept that the passing fluid volume is proportional to the cross-sectional area and the fluid velocity. Read More…
Hydraulic Flow MetersHydraulic flow meters measure the flow rate or volume of liquid inside a hydraulic system. Their general applications are testing, troubleshooting and maintaining hydraulic systems. Using hydraulic flow meters, operators of hydraulic systems can measure how efficiently and effectively their systems are running and properly address any problems into which they run.
Sierra manufacturers high performance mass flow meters and controllers for nearly any gas, liquid or steam. Customers choose Sierra when they need an accurate and repeatable flow measurement, short delivery lead times, expert flow advice and long term support. When it matters, choose Sierra. Visit www.sierrainstruments.com.
SIKA is a developer and manufacturer of flow control products and a wide variety of other measuring and monitoring systems. Our inventory includes flow sensors, flow meters, flow switches, and many more. We know that flow solutions aren't one-size-fits-all, which is why we provide consultation and flow management solutions that are individualized and customized to your requirements. When you...
MAC Instruments has been a manufacturer leader of steam flow rate meters and industrial moisture analyzers for over 30 years. Our expertise helps provides our customers with high-quality products and exceptional customer service.
It is our primary goal that we are able to treat each and every customer as if they were number one in hopes of turning first time customers into lifelong connections as well as to exceed customer expectation one hundred percent of the time in order to keep you coming back to us for all of your diaphragm valve needs! To receive more information about our company get in touch with our customer...
Blue-White Industries specializes in providing high-quality flowmeters, water flow meters, air flowmeters and ultrasonic flow meters. Our extensive line of flowmeters is sure to meet any requirement you may have. We are committed to ensuring that our customers succeed with our products. For more information, please call or visit our website today!
Measuring flow is essential to perfecting and improving the efficiency of a process and is a part of the dynamics and mechanics of fluids. It involves the movement of fluids subjected to unbalanced forces, which continue the motion of fluids as long as they remain unbalanced. Fluids measured by hydraulic flow meters are incompressible, meaning their density does not change when an external force is applied.
Flow is the measurement of the volume of a fluid as it passes a fixed point at an established unit of time. For hydraulic applications, flow is calculated in liters or gallons per minute. Fluid flow is the foundation of hydraulic systems and must be monitored carefully since hydraulic fluids transfer energy from one part of the system to another.
Functions of Hydraulic Fluids
Since not all hydraulic systems are the same, their fluids are chosen following the needs of an application. The properties of hydraulic fluids include viscosity, lubrication, demulsibility (the ability to release water), and chemical and environmental stability. Hydraulic fluids have five functions:
In a hydraulic system, the incompressible fluid transfers energy from one point to another to generate power. The pump initiates fluid flow, and pressure develops at the point of restriction.
One of the primary functions of hydraulic fluid is to remove contaminants, which can damage the system or reduce its productivity. The flow of hydraulic fluid removes any forms of foreign particles by moving them to the filtration system.
The constant movement of the various components of a hydraulic system creates friction that can cause wear and failure. The smooth flow of hydraulic fluids reduces friction by creating a lubricating film.
Sealing the System
Because all hydraulic systems operate under pressure, each system must have a tight seal. The proper hydraulic fluid forms an additional seal between mechanical parts.
The friction of hydraulic components produces heat that has to be cooled. The smooth and controlled flow of hydraulic fluids carries away any generated heat.
Types of Hydraulic Flow Meters
The selection of a hydraulic flow meter is a critical aspect of a system's function since an incorrect choice can lead to errors in diagnosis. The factors to be examined when making the selection are fluid properties, operating condition of the system, flow measurement, accuracy, effect of the flow meter on the fluid and vice versa, and cost. As with all flow meters, there are several types of hydraulic flow meters to choose from, with each type designed to perform with a certain type of hydraulic fluid.
Variable Orifice Flow Meter
A variable orifice hydraulic flow meter has a piston or ring connected to a spring. The force of the fluid displaces the piston or ring, which increases the size of the flow meter's orifice. The flow rate is indicated on an analog readout connected by a magnet to the piston or ring.
Gear Flow Meter
Gear type hydraulic flow meters are types of positive displacement flow meters that look like gear motors with intermeshed, rotating gears. The fluid flow rotates the gears, one of which is connected to the transducer. An increase or decrease in the fluid flow causes the gears to rotate faster or slower, providing the flow rate reading. More accurate gear type hydraulic flow meters have two transducers that measure direction and improve resolution.
Turbine Flow Meter
Turbine hydraulic flow meters are a very common type of mechanical flow meter. The turbine rotor is placed in a shaft between flow straighteners, and the flow of the hydraulic fluid turns the turbines. The transducer, connected to the turbine rotors, senses the movement of the blades, which is the flow rate.
Choosing the Correct Hydraulic Flow Meter Manufacturer
To ensure the most constructive outcome when purchasing hydraulic flow meters from a hydraulic flow meter manufacturer, it is important to compare several companies using our directory of hydraulic flow meter manufacturers. Each hydraulic flow meter manufacturer has a business profile page highlighting their areas of experience and capabilities, along with a contact form to directly communicate with the manufacturer for more information or request a quote. Review each hydraulic flow meter company website using our patented website previewer to quickly learn what each business specializes in. Then, use our simple RFQ form to contact multiple hydraulic flow meter businesses with the same form.
Hydraulic Flow Meter Informational Video
Flow Meters Power Pages
Coriolis Flow Meters
A Coriolis flow meter measures mass by the inertia of a liquid or gas flowing through a vibrating tube that is equipped with a set of sensors at the inlets and outlets of the meter. The increased movement of the flow produces measurable oscillation that is proportional to the mass...
A flow switch is a device that measures the flow rate and liquid pressure within a duct, loop, or system. Flow sensor and flow indication are other names for this switch. The primary purpose of a flow switch is to continually...
A level switch is an electrical or mechanical method for measuring the level of a liquid, powder, or granule material. It is designed to activate an alarm if the material level in a container passes a predetermined height or depth...
Magnetic Flow Meters
A magnetic flow meter is a volumetric flow meter that uses electrodes connected to the liquid flow to measure the velocity of fluids in a tube or pipe. The unique design of magnetic flow meters allows them to take their readings without the need for any moving parts...
Mass Flow Meters
A mass flow meter is a way of measuring the volume or mass of a gas or liquid passing through a system at a specific point in the flow system. They are used to measure linear, nonlinear, mass, and volumetric flow rates...
Ultrasonic Flow Meters
An ultrasonic flow meter measures the flow of a liquid or gas by sending ultrasonic waves across a pipe, containing the flow in the direction of the flow and in the opposite direction of the flow. The ultrasonic waves and the velocity of...
Types of Flow Meters
A flow meter is a flow rate measuring device used to determine the linear or nonlinear mass and volumetric flow of a liquid or a gas. The many names of flow meters include flow gauge, flow indicator, liquid meter, and flow rate sensor...
A metering pump is a precision machine that moves or pumps a measured amount of fluid in a predetermined time to create volumetric flow. The term “metering pump” covers a wide range of pumping methods, each designed to meet...
A rotameter is a device that measures the flow of fluid volume per unit time in a closed tube. There are diverse rotameters applications, including chemical injection/dosing and tank blanketing. A rotameter can be said...
Water Filtering Systems
A water filtering system is a mechanism that is designed to remove solid particles, tiny or large, from inside a liquid through the use of a filter medium that only allows the liquid to pass but restricts solid particles....
A leak detector is a sensor used for monitoring a system that contains liquids, gasses, or other substances to ensure that the contained materials do not escape, leak, or otherwise leave the system. The leak detection process involves...
A centrifugal pump is defined as a hydraulic machine that changes mechanical energy into hydraulic energy by the use of centrifugal force acting on the fluid. This is a machine that uses rotation to enforce velocity on a liquid...


Pioneer River and Goosepond Creek Flood Studies
The Goosepond Creek Flood Study commenced in May 2007 and included the Janes Creek, Goosepond Creek and Vines Creek waterways with a combined catchment of 35km2. The Goosepond Creek catchment experienced an extreme flood event on 15 February 2008 and the study was expanded to assess the impact of this extreme flooding event. A draft Goosepond Creek Flood Study report was produced in September 2009.
The Goosepond/Vines Creek Flood Study, 2012 updates the data and flood modelling methodology and found that the Goosepond Creek flood (Feb 2008) was a 1-in-500 year event.
The Goosepond/Vines Creek Flood Study, 2012 provides clarity on the potential impact of climate change (sea level rise, increased rainfall intensity), and the effect of mitigating actions on flood levels in this catchment.
- Goosepond Creek Flood Study Fact Sheet - March 2010 (PDF 3.0 MB)
- Goosepond Creek/Vines Creek Flood Study - February 2012 (PDF 5.6 MB)
Goosepond Creek (Including Pioneer River Flood Study)
The Goosepond Creek (including Pioneer River) Flood Study (WRM, October 2012) assessed the interaction of flood flows between Goosepond Creek and the Pioneer River. This study should be viewed as an addendum report to the Pioneer River Flood Study, 2011 and the Gooseponds/Vines Creek Flood Study, 2012 and be read in conjunction with them.
The Goosepond Creek (including Pioneer River) Flood Study (2012) reviewed findings from the earlier separate Goosepond River and Gooseponds/Vines Creek studies. The study used recently updated Light Detection and Ranging (LiDAR) technology the measure ground levels and determine flood flows. The flood level modelling considered the impact of stormtide events, historical river flood events, the impact of climate change to the year 2100 in estimating flood levels for events between 5 and 500 years.
The flood levels in the combined Goosepond Creek (including Pioneer River) Flood Study, 2012 now override the flood levels of the previous individual reports.
These assist in informing planning controls and consideration of flood risk within the Pioneer and Gooseponds catchments.
- Goosepond Creek (Including Pioneer River Flood Study) - October 2012 (3.27 MB)
Pioneer River Flood Study
The Pioneer River is a major natural feature with a catchment of 1.560 km2 which impacts on planning and development along its waterways.
Since the 1970s, numerous hydrologic and hydraulic studies have been undertaken to assess flood behaviour along the river.
In 2008, Council commissioned the Pioneer River Flood Study to determine flood risk from Mirani to its discharge into the South Pacific Ocean at Mackay City.
The Pioneer River Flood Study, 2011 includes an assessment of the impact of climate change, and provides detail on flood events for a range design flood events between 5 and 500 years. The study provides more accurate estimates of flood events and risk that the previous Pioneer River Flood Study, 2004 by Chaseling McGiffin Pty Ltd.


VERTEX provided oversight on the surety’s behalf for the construction of a new dam on the Upper Kapahi Reservoir on Kauai, Hawaii. The dam was constructed to provide water storage for agricultural use. Large concrete box culverts were constructed and placed with a roadway prism being built up and paved over top. The crest of the structure built is at an elevation of 359 feet with a crest length of approximately 215 feet and a maximum height of about 23 feet. Access roads were graded to facilitate future maintenance of the box culverts and rock slope protection channels. A blanket drain and a toe drain were also constructed on the downstream side of the dam to control seepage and protect against internal erosion. VERTEX’s scope of services included construction relet, conducting weekly Owner/Architect/Contractor (OAC) meetings, monitoring construction progress and cost analysis, reviewing contractor’s schedule of values, processing payment, project closeout, and other construction administration services.


National Program for Inspection of Non-Federal Dams. West Parish Filter Number 3 Dam (MA 00610), Connecticut River Basin, Westfield, Massachusetts. Phase I Inspection Report.
CORPS OF ENGINEERS WALTHAM MA NEW ENGLAND DIV
Pagination or Media Count:
West Parish Filter No. 3 Dam is an earthen embankment structure 37.5 feet high and 800 feet long. A side-channel spillway is located at the right abutment. It has a concrete overflow section which is 23.4 feet long. Outlet piping passes beneath the embankment and connects directly to the water treatment plant which serves the City of Springfield, Mass. The dam is situated on a very small 0.07 sq. mi drainage area, and serves as offstream storage and as a sedimentation basin for water which is piped from other dams. Based on the visual inspection, the dam is judged to be in fair condition. The following deficiencies were observed at the dam a soft, wet area near the downstream toe a row of evergreen trees along the downstream toe with some roots penetrating the embankment rodent holes on the downstream slope wheel tracks on the crest of the dam misaligned riprap and loose rock and trees overhanging the spillway low areas on the top of the dam and no means of controlling flow at the upstream end of the outlet conduit. The spillway capacity is about 335 percent of the routed test flood outflow of 142 cfs. During the test flood, the freeboard would be 1.9 feet.
- Hydrology, Limnology and Potamology
- Civil Engineering


MODEL 400 LIQUID MICROTURBINE
The Model 400 Liquid FLO-CONTROLLER provides low cost liquid flow control. Operating with liquids in the same way MFCs work with gases, an integrated flow sensor and proportional control valve provide a complete package. The heart of the FLO-CONTROLLER is the flow sensor, which provides flow rate feedback for accurate control. A Model 101 microturbine FLO-SENSOR is used for this purpose. The output of the flow sensor is sent to additional processing electronics, which compare the set point (provided remotely by the user) to the actual flow rate and adjust the valve accordingly. A error signal is generated if the FLO-CONTROLLER is unable to control.


Pro Series filters provide efficient flow, totally balanced backwashing and an advanced self-cleaning under-drain system for the best value in filtration.
Features. Durable corrosion-proof filter tank molded of color-fast material for long-lasting, all-weather performance. 7-position Vari-Flo valve provides maximum flow at lower pressure drop. Large pressure sand/water drain for rapid winterizing or servicing. Flange clamp design allows 360 rotation for easy installation. Integral top diffuser ensures even distribution of water over the entire sand bed for maximum use of the filtration area. Precision engineered umbrella-fold self cleaning laterals for balanced flow and backwashing, plus easy serviceability. 20 in.. 6-Position 1.5 in. Top Mount Valve. Requires 200# Sand. Dimension - 21 x 21 x 39 in.


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Pressure reducing valve in ductile iron valve with pilot circuit in stainless steel designed to maintain the secondary pressure of the valve. The valve is drinking water approved. The valve can also be used as a shut-off valve. A number of functions can be added, for example pressure holding and pipe burst protection.Face to face acc. to EN 558-1.


Yuken Sequence Valves
These valves control the sequential operation of two or more actuators. If the inlet pressure exceeds a preset level, they deliver effective pressure to the outlet side. The valves can serve as pressure holding valves to maintain hydraulic pressure in a circuit. When a sequence valve is installed between a directional control valve and a cylinder, it needs reversed free flow; therefore, the valve should contain a check valve. The sequence valves and counterbalance valves, described in the next section, are generally known as H/HC type pressure control valves, and how they are assembled determines the nature of the combined valve, either H or HC type.
Note that a sequence valve with an auxiliary pilot port can provide two-pressure control (high/low) by delivering the pilot pressure of the auxiliary pilot port to the pilot piston. Pressure required for this auxiliary remote control is approximately 1/8 of the adjustment pressure (approximately 1/16 when the adjustment pressure is 7 MPa (1 015 psi) or more). The example is shown in Fig. 3.10.
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What is Sluice?
A water channel to control flow of water or rate of flow on dam or river
Introduction of Sluice
Ipo Bridge Production
SAMIL C&S steel business division gained recognition on sluice production ability through producing 6 gates of roller gate and new environmental scripture on ‘Ipo Bridge’ construction at the third site of the proejct han river restoration.
Various Sluice Construction
SAMIL C&S steel business division distinguish itself based on high technology on various sluice production and installation construction such as sluice construction of spillway of Andong dam and Yeongju dam.
Sluice Construction Process
Sluice Construction Cases
YoungJuDam spillWay floodgate constructionYoungJuDam spillWay floodgate construction
spillWay floodgate constructionspillWay floodgate construction


RPA has served the City of East Helena for nearly 40 years, completing numerous water and wastewater system improvement projects for the City. Professional services have included funding/financial studies, rate studies, sanitary sewer collection, wastewater facilities planning, scheduling, flow monitoring, design and construction administration, and advanced tertiary metals removal. RPA recently completed a solid waste operational analysis and rate study for the City to analyze the solid waste rates, existing revenue, existing expenditures, and to discuss potential solid waste rates for two separate alternatives. RPA has just finished the design for installation of new water distribution mains in two separate locations. In addition, RPA designed a new 1.0MG prestressed concrete water storage tank and appurtenances. Construction will include installing the New Prestressed Tank, new transmission main and bypass piping connecting to the existing transmission piping, new overflow and drain piping connecting to the existing drain piping, demolition of the existing water tanks, and other site and building improvements.


A numerical analysis of the flow in a radial impeller will be presented with experimental validation. The low-pressure stage of a two-stage pump with a seven-blade runner and a vaned diffuser convoy will be under investigation. Initially, the vanes of the diffuser will be removed and only the impeller will be considered in order to emphasize the influence of the runner alone. Successively, the annular cascade of stationary vanes will be inserted. Experimental and numerical comparison will be made at the impeller inlet/outlet, focusing on the changing flow field at part load. The influence of the stator/rotor interactions on the onset of the reverse flow zones will be also analysed.
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Croatia keeps ownership of HEP's hydro components
Croatian ownership will be retained for the already constructed reservoirs, supply and drainage channels and tunnels to ensure continuity of the water flow. HEP will acquire the right of construction on parts of existing hydroelectric facilities built on public waters for 99 years, without compensation. Legal right of management will be acquired over accumulations, inlet and drainage channels and the land under them, during the construction process. In the case of constructing a new hydro power plant, a potential investor has limited options, all of which include the Republic of Croatia to be the owner of accumulations, inlet and drainage tunnels. The Law on waters is available on the pages of the Croatian Government (link).