EP1486674A1 - Pumpe mit veränderlicher Verdrängung - Google Patents

Pumpe mit veränderlicher Verdrängung Download PDF

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Publication number
EP1486674A1
EP1486674A1 EP03253669A EP03253669A EP1486674A1 EP 1486674 A1 EP1486674 A1 EP 1486674A1 EP 03253669 A EP03253669 A EP 03253669A EP 03253669 A EP03253669 A EP 03253669A EP 1486674 A1 EP1486674 A1 EP 1486674A1
Authority
EP
European Patent Office
Prior art keywords
positive displacement
variable displacement
pump
displacement pump
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03253669A
Other languages
English (en)
French (fr)
Inventor
Bruce A. Maki
Daniel A. Beilke
Robert Hosfield
David G. Vensland
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hypro LLC
Original Assignee
Hypro LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hypro LLC filed Critical Hypro LLC
Priority to EP03253669A priority Critical patent/EP1486674A1/de
Publication of EP1486674A1 publication Critical patent/EP1486674A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F04B1/182—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/109—Valves; Arrangement of valves inlet and outlet valve forming one unit

Definitions

  • This invention relates generally to fluid handling pumps, and more particularly to an improved, multi-cylinder, variable displacement, positive-displacement pump that permits adjustment of the plunger's stroke while the pump is being driven to thereby vary the flow rate of the fluid being pumped.
  • variable displacement, positive-displacement pumps that use a non-rotating swash plate whose angle is adjustable.
  • the cylinder barrel rotates and the pistons rotate with the barrel and one end thereof rides on the tilted swash plate to thereby impart reciprocating motion to the pistons.
  • the hydraulic fluid being pumped is very clean and lubricious, it is possible to provide porting to the cylinders as the top of the barrel rotates across appropriate suction and discharge ports.
  • such a design can only be used when pumping clean, lubricating fluids, such as, hydraulic oil.
  • check valves By keeping the cylinders stationary and rotating the swash plate, check valves can be used which allows for the pumping of non-lubricating and dirty fluids.
  • One type of axial piston/plunger pump that is designed to pump non-lubricating fluids typically has a fixed cylinder block and a rotating swash plate that coacts with the pistons to impart reciprocating action due to the inclination of the rotating swash plate relative to the drive shaft used to rotate the swash plate.
  • Many refrigeration unit compressors use a rotating swash plate to impart reciprocatory displacement of plural pistons.
  • the angle of inclination of the swash plate is controlled as a function of the pressure in the pump's crank housing.
  • a return spring is provided on the piston's connecting rod to force a smoothly rounded end of the connecting rod against the surface of the swash plate.
  • the spring pressure is present in both the suction and discharge stroke of the piston/plunger and thus adds to the force in the discharge stroke.
  • the interface between the connecting rods and the swash plate must tolerate the rotational velocity and the orbital motion as it is forced against the swash plate by the return spring. This results in a very high PV (pressure, velocity) wear rate of the swash plate and the mating end of the connecting rod.
  • the return spring is limited to the speed at which the pump is made to operate, based on the spring mass relationship for a first critical frequency. If the pump is made to run too fast or the return spring loses its resiliency over time, then the pistons/plungers will, for part of the travel, lose contact with the swash plate, causing rapid destruction of the pump. In addition, the spring will fatigue over time and will eventually fail.
  • the base of the piston assembly must have the C-form recess which necessarily increases the mass of the reciprocating piston/plunger assembly and the loads. It is also necessary to precisely align the piston so that the C-form slot formed in it does not slowly rotate and eventually strike the swash plate. Moreover, the C-form must protrude to the outside of the diameter of the engagement circle with the connecting rod, thus increasing the overall diameter of the pump or compressor.
  • FIG. 7 of the drawings there is schematically shown a conventional valve arrangement used in prior art pumps.
  • the suction valves 302 open during the suction stroke of their respective plungers, to allow the fluid being pumped to be drawn into the plunger bores as the plungers leave its top dead center position.
  • the suction check valves 302 close and the discharge valve 304 opens allowing the pressurized fluid to flow through the discharge manifold and out the pump's discharge port.
  • valve area to piston area is limited, causing high fluid velocities on both the suction and discharge phases. These high velocities translate into poor suction characteristics and pump inefficiencies.
  • the simple rubber flapper valves found on inexpensive axial diaphragm pumps are not suitable for the higher pressures handled by check valves and, also, they are not as durable. Such flapper valves are limited to applications where low viscosity fluids are being pumped at modest pressures.
  • a positive displacement pump In certain metering applications where a positive displacement pump is to be used to dispense measured quantities of a product, it is desirable that provision be made for varying the pump's displacement and that it be possible to make a displacement adjustment while the pump is running.
  • the most common approach for varying the output of a positive displacement pump is to vary the speed at which the pump is driven.
  • the displacement In positive displacement pumps in which a wobble plate is used to impart reciprocatory motion to the pump's plural plungers, it is also known that the displacement can be varied by adjusting the angle of inclination of the swash plate relative to the drive shaft on which it is mounted. In the compressor technology, this angular adjustment is accomplished by controlling the pressure within the crankcase using a needle valve. While this approach is workable for gaseous fluids, it is wholly ineffective when an incompressible liquid is the medium being pumped.
  • variable displacement, positive displacement pump having a housing to which a cylinder block is attached where the cylinder block has a plurality of bores that are equally radially and circumferentially spaced from a central, longitudinal axis of the cylinder block.
  • a piston/plunger member having first and second ends is disposed in each of the plurality of bores.
  • the pump's drive shaft is journaled for rotation in the housing member along an axis that is aligned with the central axis of the cylinder block.
  • a swash plate is affixed to and rotatable with the drive shaft within the housing member.
  • a non-rotatable wobble plate assembly with a central bore formed therethrough and with an annular bearing disposed in the bore is in concentric, surrounding relation to the swash plate.
  • the pistons/plungers are joined to the non-rotatable wobble plate, using spherical ball joint members that couple a ball on the first end of each of the piston/plunger members to sockets on the wobble plate created by spherical thrust washers.
  • a suction manifold is affixed to the cylinder block and, in turn, a discharge manifold is bolted to the suction manifold.
  • the suction manifold includes an inlet port and the discharge manifold includes a discharge port.
  • Unitary, replaceable in-line, valve cartridges for each of the piston/plunger members are disposed in the discharge manifold.
  • Each valve assembly comprises a suction poppet and a discharge poppet that are disposed in longitudinal alignment with a central axis of its associated piston/plunger.
  • the two poppets are arranged such that the discharge poppet closes to isolate the discharge manifold from the suction manifold during a suction stroke of the plunger member while the suction poppet opens to allow fluid to flow from the suction manifold into a changing volume of the cylinder bore as the plunger member rotates.
  • the discharge poppet opens while the suction poppet closes as the plunger moves in a direction toward the cylinder head.
  • a slide mechanism is provided on the drive shaft and pinned linkages are used to join the slide member to the swash plate.
  • the slide can be displaced from outside of the housing with the pump running.
  • FIG. 10 a perspective view of a variable positive displacement pump constructed in accordance with the present invention. While the preferred embodiment to be described is a piston or plunger pump, it is to be understood that the inventive principles may also be applied to other positive displacement pumps, e.g., diaphragm pumps, as well.
  • the pump may be considered as including a wet end 12 and an oil lubricated end 14.
  • the wet end includes a cylinder block 16 a suction manifold 17 having an inlet or suction port 18 and bolted thereto is a discharge manifold 20.
  • a discharge port 21 is located on the discharge manifold 20.
  • the oil end 14 of the pump includes a lubrication housing 22 having an integrally formed base 24 that is adapted to be bolted to a support frame (not shown). Journaled within the housing is a drive shaft 26. It is journaled for rotation in suitable bearings and the drive shaft has a swash plate 28 affixed to and rotatable with the shaft 26. Also visible in the view of Figure 1 is a wobble plate assembly 30, which surrounds the rotatable swash plate and which is free to nutate, but is precluded from rotating, by an anti-rotation device, indicated generally by numeral 32. The nutating motion of the wobble plate assembly 30 imparts reciprocal, rectilinear movement to a plurality of pistons contained within bores in the cylinder block 16.
  • the pump design depicted in the drawings accommodates five pistons, but a greater or a fewer number can be used.
  • the piston stroke, and therefore, the displacement of the pump cylinders is adjustable by altering the angle at which the swash plate 28 and the surrounding wobble plate 30 are oriented relative to the drive shaft 26.
  • the pump is in its "no flow” state.
  • the stroke adjustment can be made with the pump running.
  • the adjustment may be made manually with a crank or knob or can be electronically controlled using a stepper or servo motor, as at 36, each of which is arranged to drive a worm gear assembly 38 that is coupled to a pair of actuating screws 40.
  • the actuating screws each have a traveling nut 42 that is coupled, via a control yoke as at 43 and through linkages 44 to the swash plate 28. Displacement of the traveling nut along the length of the actuating screws thus adjusts the tilt angle of the swash plate 28 and the wobble plate 30.
  • the worm gear assembly 38 includes a control shaft 46, which, as mentioned, is adapted to be manually or automatically rotated by a crank knob attached to one end of control shaft 46 or a suitable electric motor coupled to the opposite end.
  • Worms 48 and 50 on the control shaft mate with worm gears 52 and 54 that are affixed to the outer ends of actuating screws 56 and 58, respectively.
  • the drive shaft 26 is journaled for rotation in a bore 60 forming a part of the cylinder block 16. More particularly, the bores 60 contain a tapered roller bearing set 62 for journaling the shaft 26. The rearward end of the drive shaft 26 is also journaled for rotation by means of roller bearings 68 located within a cavity 70 at the rear end 72 of the pump body or housing 22.
  • the central portion 27 of the drive shaft 26 may be of a hex-shaped cross-section or may be cylindrical but which has flats machined on diametrically opposed sides of the drive shaft. Fitted onto the drive shaft so as to subtend the flat surfaces is the swash plate 28. As seen in the cross-sectional view of Figure 4, because of the flats, the swash plate can be tipped to have its angle with the shaft adjusted.
  • the swash plate has a tapered central bore 74.
  • a pin 76 passes through aligned holes in the swash plate and the shaft 26, which allows the swash plate 28 to rotate with the drive shaft 26 and to be tipped at a desired angle (within predetermined limits) with respect to the centerline of the shaft due to the taper of the bore 74.
  • Fitted onto a hub portion 78 of the rotating swash plate 28 in surrounding rotation is a set of double-row ball bearings 80 (Figure 5).
  • the wobble plate assembly 30 comprises an outer thrust support plate 82, a rear annular thrust plate 84 and a second or outer thrust plate 86 that sandwich an annular wobble plate 88 surrounding the bearings 80.
  • This assembly is held together by socket head cap screws 85 passing through the assembly and into threaded bores, as at 90 ( Figure 1).
  • FIG. 4 shows one of a plurality of plungers driven by the wobble plate assembly. It is identified by numeral 92.
  • the plunger 92 is shown as being at the bottom of its stroke.
  • the remaining pistons are intermediate top dead center and bottom dead center.
  • a ball joint assembly 94 includes a spherical ball member 96 formed on the end of a threaded connecting rod shaft 98 that fits into an internally threaded bore 100 formed in the bottom end of the piston/plunger 92.
  • the shaft 98 passes through an aperture in the thrust plate 86 and the ball member 96 is captured between spherical thrust washers 102 and 104 that are disposed between the annular thrust plates 84 and 86. Provision is made for an oil lubricant in the housing to reach the mating surfaces of the ball joint with the thrust washers by way of a port formed through the spherical thrust washer 102 leading to the interface of the thrust washer with the ball 96.
  • the actuating screw members 40 and 41 are journaled for rotation in the housing 22. More particularly, and with reference to the actuating screw 41, it has its rearward end 105 disposed in a bronze sleeve bearing 106 that is fitted into a removable end cap 108 bolted to the housing 22. Its other end is journaled in a set of roller bearings 110 disposed in a bearing cup 112 that forms a part of the housing.
  • the actuating screw 40 is mounted in an identical manner such that each is free to rotate about a longitudinal axis that is parallel to and latterly offset from the axis of the drive shaft 26.
  • control yoke member 43 Cooperating with external threads on the actuating screw shafts 40 and 41 are internally threaded travelers 114 that are affixed to a control yoke member 43.
  • the control yoke member 43 cooperates with a control slide 118 that rotates with the shaft 26, but which is isolated from the control yoke 43 by a double row ball bearing set 120.
  • the control yoke 43 is coupled to the rotating swash plate 78 by first and second linkage bars 44 which are joined to the control slide 118 and the rotating swash plate 28 by linkage pins 126 and 128, respectively.
  • control shaft 46 can be rotated manually or automatically to rotate the worm gears 52 and 54, which, in turn, cause longitudinal translation of the control slide 118 to vary the tilt of the swash plate assembly 28 as well as the wobble plate 30 via linkage bars 44. This, in turn, varies the stroke of the piston 92 and the pump's displacement.
  • an anti-rotation assembly 32 is provided. It includes a rocker shaft 132 that is journaled for rotation within a bearing cap 134 on a housing cover plate 136 by bearings 138. Affixed to the rocker shaft 132 is a rocker member 140 having an arcuate groove 142 formed therein. Fitted into the groove 142 is a vane member 144 that projects radially from the wobble plate assembly. As the wobble plate nutates through its range of motion, the rocker member 140 pivots back and forth about its shaft 132 while preventing rotary motion of the wobble plate.
  • the pump's cylinder block 16 includes a plurality of cylinder bores (here numbering five) that are equally circumferentially and radially spaced relative to the longitudinal axis of the pump with which the drive shaft 26 is centered.
  • the cylinder block 16 includes a base plate 150 that bolts to the pump body 11 containing the pump's lubricating oil.
  • the plate 150 has a cylindrical bore, as at 151 in Figure 3, for each of the pistons/plungers utilized in the pump.
  • the suction manifold 17 has a base 152 that also has circumferentially and radially spaced bores formed therethrough which are aligned with the bores in the base plate 150 of the cylinder block 16.
  • FIG. 4 and the enlarged detailed view of Figure 6 illustrate one of the pistons/plungers 92, along with the seal arrangement that is disposed between the piston/plunger 92 and the base plates 150 and 152 of the cylinder block 16 and suction manifold 17, respectively.
  • the plunger rod 92 includes a cylindrical stem portion of a first diameter into which the threaded connecting rod shaft 98 attaches. This stem portion is necked down to a reduced diameter segment 93 and concentrically surrounding the reduced diameter portion 93 is a tubular ceramic plunger 95. An acorn nut 97 holds the tubular plunger 95 in place.
  • the ceramic plunger 95 proves very suitable in terms of its resistance to wear an erosion. It may readily be removed for replacement, however, without the need to uncouple the piston/plunger from the wobble plate.
  • a sleeve bearing 99 Fitted between base or stem portion of the plunger rod 92 and the cylindrical wall of the cylinder block 16 is a sleeve bearing 99 and a stainless steel oil seal retainer 101, a rod seal 103 and a rod wiper seal 105. This seal arrangement inhibits passage of lubricating oil along the plunger stem.
  • a seal cartridge housing 154 is positioned in surrounding relationship to the ceramic plunger 95 and located between it and the outside diameter of the plunger 95 is a lantern ring 156, providing support to a high pressure, elastomeric U-cup seal 158.
  • the lantern ring supports a graphite guide bushing 160 and provides lubrication to the guide bushing from the pumped fluid from the suction side of the pump. Sealing the suction side of the pump from the atmosphere is another low-pressure cup seal 162. It is made of an elastomeric material is held in place by a low-pressure seal retainer 164 and is exposed to atmospheric pressure through a weep hole formed in the cylinder block 16.
  • the seal arrangement just described is held in place by a seal cartridge retainer 166 having external threads for mating with the internal threads formed on the seal cartridge housing.
  • the lantern ring 156 not only supports the high pressure elastomeric cup seal 158, but also provides a path for fluid being pumped to lubricate and cool the plunger journal bearing, the low pressure seal 162 and the O-ring seals 168 and 170.
  • the plunger journal bearing is preferably made of graphite or other bearing material compatible with the fluid being pumped while providing the plunger with linear bearing support.
  • a weep hole 172 ( Figure 4) is formed through the wall of the housing so that any liquid that is not blocked by the aforementioned seal arrangement exits through the weep hole and therefore does not find its way down along the surface of the piston/plunger into the lubrication housing.
  • the annular bushing 151 is disposed in the cylinder bore to allow the lubricant contained in the housing to lubricate the surface of the piston while oil seal assembly 101 inhibits exit of oil out weep hole 172.
  • each cylinder has a compound unitary suction/ discharge valve is incorporated into a replaceable cartridge assembly along with the wet end seal elements.
  • These coaxially disposed cartridge elements provide two unique and novel advantages to the pump design. The first is to provide ease of maintenance by allowing each seal element to be serviced independently, without disassembling the entire pump. The second advantage to the arrangement allows for a much smaller pump head diameter. To gain access to the valve cartridges, one need only remove the bolts, as at 174, that holds cover plates, as at 176, to the discharge manifold.
  • the in-line suction and discharge valve assembly is indicated generally by numeral 180. It comprises a suction poppet member 182, which is urged by spring 184 into sealing relation with respect to a valve body member 186 having an annular port 188 formed through it. The port 188 is in fluid communication with the suction manifold 17.
  • a discharge poppet valve 190 is urged by a coil spring 192 into sealing relation with respect to a valve seat member 194 that has a port formed through it. Both the suction poppet 182 and the discharge poppet 190 are seated when the piston 92 is at the bottom of its stroke as illustrated in Figure 4.
  • the volume of the cylinder not occupied by the piston is filled with the liquid being pumped.
  • the nutating plate assembly forces the piston to the right when viewed in Figure 4, increasing the pressure acting on the suction poppet valve 182 to force it to close.
  • the increased pressure acting on the face of discharge poppet 190 also forces it to open against the bias afforded by the spring 192 causing the charge of liquid being displaced by the piston to flow out through the discharge port 21 ( Figure 1).
  • the force of the coil springs 184 and 192 overcome the fluid pressure acting on the respective poppets 182 and 190, again forcing those poppets closed.
  • the piston 92 With continued rotation of the drive shaft, the piston 92 is drawn back from its top dead center position reducing the hydraulic pressure acting against the discharge valve 190 and causing it to seat against the valve seat member 194.
  • the liquid entering the suction port 18 into the suction chamber acts against the suction valve poppet 182 forcing it away from the annular port and allowing flow into the cylinder bore ahead of the free end of the piston 92.
  • the liquid continues to fill this volume until the piston reaches the bottom of its stroke and the cycle then repeats.
  • a variable positive displacement pump cannot be allowed to run against a shut or blocked discharge. This could cause the pump to experience a significant pressure spike that could result in damage to the pump.
  • the wobble plate By providing a pressure feedback signal to the servo motor 36 (Fig. 1) that is coupled to the control shaft of the worm gear assembly, the wobble plate can be repositioned to provide a reduced flow "no-flow" condition, thus protecting the pump from damage due to over pressure conditions. Should such pressure transients or "spikes" occur more rapidly than the feedback mechanism of the pump can respond to, a safety valve arrangement is also incorporated into the present invention which allows for brief internal relief of pressure, thus providing the necessary time for the control mechanism to respond in tilting the nutating plate to a reduced or "no-flow" condition.
  • a safety valve indicated generally by numeral 200 is centrally disposed in the valve plate 202 and it includes a piston 204 that is held seated against the valve plate by a compression spring 206.
  • the piston 204 will be exposed to that pressure through port 210 and will move in a direction to compress the spring 206, unseating the piston 204 and allowing the liquid in the discharge chamber to flow through a port 210 back into the low pressure suction chamber.
  • the spring 206 will again urge the piston 204 back into its seated condition, again blocking the port 210.
  • variable displacement positive displacement pump of the present invention is provided with an oil-end lubrication system illustrated schematically in Figure 8.
  • oil is taken from the pump's oil sump in pump body 22 through a strainer (not shown) and then pumped by an internal oil pump 209 through an oil filter 211 and distributed directly to the linear oil journal bearings 151 for each cylinder and to the unique oil mist lubrication system that is shown in greater detail in Figure 9.
  • the anti-rotation assembly 32 is used to uniformly distribute an oil spray to the pump components. Advantage is taken of the back-and-forth twisting action of the rocker assembly 140.
  • Oil is injected into the anti-rotation assembly 32, via a port 137, and travels to the rocker bearing 138 and the spray nozzles 139 through the hollow shaft 141.
  • the spray nozzles then distribute the oil mist, aided by the back-and-forth twisting action of the rocker member 142.
  • variable positive displacement pump capable of providing a precise metered flow of fluid that is being run at a constant speed by appropriately adjusting the displacement of the pump's cylinders while the pump is running. Because of the design, it effectively isolates the wet end of the pump from the crankcase where all parts requiring lubrication are bathed in oil. As such, the pump of the present invention may be used to pump non-lubricious and corrosive fluids.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP03253669A 2003-06-11 2003-06-11 Pumpe mit veränderlicher Verdrängung Withdrawn EP1486674A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03253669A EP1486674A1 (de) 2003-06-11 2003-06-11 Pumpe mit veränderlicher Verdrängung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03253669A EP1486674A1 (de) 2003-06-11 2003-06-11 Pumpe mit veränderlicher Verdrängung

Publications (1)

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EP1486674A1 true EP1486674A1 (de) 2004-12-15

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EP03253669A Withdrawn EP1486674A1 (de) 2003-06-11 2003-06-11 Pumpe mit veränderlicher Verdrängung

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013053670A1 (de) * 2011-10-12 2013-04-18 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein hochdruckreinigungsgerät
CN115306695A (zh) * 2022-09-07 2022-11-08 江苏可奈力机械制造有限公司 可调压式防偏磨超高压高速电液多控滑道柱塞泵
CN117605677A (zh) * 2023-11-30 2024-02-27 建湖金拓机械制造有限公司 一种可过滤的压裂车液力端总成

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1224096A (fr) * 1958-01-24 1960-06-22 Perfectionnements aux dispositifs à pression de fluide, et plus spécialement aux pompes
US3180277A (en) * 1963-03-07 1965-04-27 Frank Wheatley Pump & Valve Ma Valve system for reciprocating pump
US3709638A (en) * 1968-02-24 1973-01-09 Japan Steel Works Ltd Plunger pump cylinder for use in treating highly corrosive fluid

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1224096A (fr) * 1958-01-24 1960-06-22 Perfectionnements aux dispositifs à pression de fluide, et plus spécialement aux pompes
US3180277A (en) * 1963-03-07 1965-04-27 Frank Wheatley Pump & Valve Ma Valve system for reciprocating pump
US3709638A (en) * 1968-02-24 1973-01-09 Japan Steel Works Ltd Plunger pump cylinder for use in treating highly corrosive fluid

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013053670A1 (de) * 2011-10-12 2013-04-18 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein hochdruckreinigungsgerät
CN103874854A (zh) * 2011-10-12 2014-06-18 阿尔弗雷德·凯驰两合公司 用于高压清洗设备的活塞泵
CN103874854B (zh) * 2011-10-12 2016-04-20 阿尔弗雷德·凯驰两合公司 用于高压清洗设备的活塞泵
US9932971B2 (en) 2011-10-12 2018-04-03 Alfred Kärcher Gmbh & Co. Kg Swash plate compressor having a curved piston guide wall
CN115306695A (zh) * 2022-09-07 2022-11-08 江苏可奈力机械制造有限公司 可调压式防偏磨超高压高速电液多控滑道柱塞泵
CN115306695B (zh) * 2022-09-07 2023-09-29 江苏可奈力机械制造有限公司 可调压式防偏磨超高压高速电液多控滑道柱塞泵
CN117605677A (zh) * 2023-11-30 2024-02-27 建湖金拓机械制造有限公司 一种可过滤的压裂车液力端总成
CN117605677B (zh) * 2023-11-30 2024-05-28 建湖金拓机械制造有限公司 一种可过滤的压裂车液力端总成

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