US3713755A - Pumping device - Google Patents

Pumping device Download PDF

Info

Publication number
US3713755A
US3713755A US00134606A US3713755DA US3713755A US 3713755 A US3713755 A US 3713755A US 00134606 A US00134606 A US 00134606A US 3713755D A US3713755D A US 3713755DA US 3713755 A US3713755 A US 3713755A
Authority
US
United States
Prior art keywords
piston
valve
pumping device
thrust
chamber
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.)
Expired - Lifetime
Application number
US00134606A
Other languages
English (en)
Inventor
H Scheffer
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.)
Harry Krueger GmbH
Original Assignee
Harry Krueger GmbH
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 Harry Krueger GmbH filed Critical Harry Krueger GmbH
Application granted granted Critical
Publication of US3713755A publication Critical patent/US3713755A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0075—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series
    • F04B11/0083—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series the pistons having different cross-sections
    • 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
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
    • F04B19/022—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders reciprocating cylinders
    • 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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • 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
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/126—Ball 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/123—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
    • F04B9/125—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting elastic-fluid motor

Definitions

  • ABSTRACT A pumping device having a piston pump and a drive constituted by a thrust-piston motor means actuated by a fluid motive medium, wherein at least one pump is arranged within the motor means.
  • the invention relates to a pumping device having a piston pump and a drive constituted by a piston motor means actuated by a fluid motive medium.
  • the thrust-piston motor means In pumping devices to be found on the market, the thrust-piston motor means generally has a relatively large diameter in comparison with the pump.
  • the invention aims at the creation of a pumping device which substantially avoids the disadvantages of the known pumping devices, but makes possible operations at the desired transmission ratios.
  • the invention proceeds from the point that in pumping devices driven by a thrust-piston motor means, the effective cross-sections of the pump always take up only a relatively small fraction of the effective crosssections of the compressed-air motor means.
  • At least one pump will be arranged within the motor means.
  • At least one piston-rod with bores and valves is fixedly arranged in a casing, and the thrustpiston drive is formed in such a way and displaceably positioned in such a manner on the piston-rod that between the thrust-piston and the piston-rod a pumping space is delimited the size of which is variable by displacement of the thrust-piston along the piston-rod.
  • the thrust-piston therefore concurrently constitutes the movable pumping plunger displaceably borne on the fixed piston-rod of the pump.
  • two bores or ducts are formed within the piston-rod to connect the pumping space and the external space around the casing, and in each of the said ducts a nonreturn valve is located.
  • the non-return valves are so arranged that one duct can be employed as a suction duct, and the other as a delivery or discharge duct.
  • the piston-rod extends right through the casing and has two sections of differeing diameter, and the thrust-piston consists of at least a pumping plunger and an operative flange.
  • the pumping device is characterized by a valve seat which separates a first and a second valve chamber within the piston-rod, there being positioned on the valve seat a spring-loaded valve body constituting a second valve (the pressure valve), while a spring-loaded valve body constituting a first valve (the suction valve) is located on a valve seat on the bottom of the valve chamber formed in a section of the piston-rod of smaller diameter, the valve chambers in each case being connected to the outside through the bores.
  • the internal diameter of the plunger is substantially equal to the diameter of the section of the piston-rod of larger diameter, and the first valve chamber is connected through passages with the pumping space.
  • the diameter of the section of piston-rod of larger diameter is substantially equal to the internal diameter of the plunger, in this case a single-acting pump is obtained. If the diameters of the two sections only differ slightly from each other, then the transmission ratio obtained is a particularly high one.
  • the internal diameter of the plunger is greater than the diameter of the piston-rod section of larger diameter, and a third piston-rod section is provided between the two previous piston-rod sections, the diameter of the third section being substantially equal to the internal diameter of the plunger, the'first valve chamber being connected through passages to the suction space and the second valve chamber being connected through passages to the delivery space, the suction and delivery spaces being separated by the third section of the piston-rod.
  • the pump with differential pistons operates with a single action on the suction side and a double action on the delivery side. Utilizing this pump, particularly high transmission ratios can therefore be obtained.
  • the third section of the differential-piston rod should preferably be formed in one piece with the cross-section of piston-rod having the larger diameter.
  • At least two sections of piston-rod should be capable of being connected together. Such an interconnected combination renders possible simple assembly of the arrangement.
  • the casing consists of a first cylinder cover with at least one canister-shaped section, a cylindrical intermediate unit and a second cylinder cover with at least one canistershaped section or a level surface, the admission and discharge of fluid motive medium taking place through apertures in the cylinder covers.
  • the cylindrical intermediate unit defines the working volume of the operative flange of the thrust-piston, while the canistershaped sections serve to accommodate the pump plunger.
  • the entire pumping device apart from the apertures to admit and discharge the fluid motive medium, should each have only a single intake and in a single delivery orifice and should otherwise be hermetically sealed, in certain circumstances, when corrosive or otherwise harmful substances which attach the compressed-air motor means are conveyed, it may be necessary for the material being conveyed not to come into contact with the fluid motive medium.
  • the cylinder covers in the area of the'canister-shaped extensions should be provided with openings and that the working space of the thrust-piston should be sealed between the cylindrical section of casing and the thrust-piston; Leakages between the movable pumping plunger and the fixed piston-rod are able to pass through these openings in the canister-shaped extensions into the open.
  • a seal is arranged around the periphery of the operative flange of the thrust-piston.
  • the thrust-piston is sealed relative to the pistonrod by one or more seals.
  • the piston-rod is similarly sealed relative to the casing.
  • piston-rods or their individual sections will be of differing diameters from rod to rod, and/or that the internal diameter of the associated pumping plungers will be of differing sizes. In this way it is possible to arrive at differing pressures and differing amounts conveyed.
  • the delivery-side coupling of a first pump' may link to the suction-side coupling of a second pump so that, for example, the compression ofa gas under conveyance is possible in stages. Apart from two-stage compression, further stages of compression are also possible.
  • the reversing arrangement which is required to obtain a reciprocating movement of the thrust-piston in the casing forms no part of the invention, and may be one of the already known reversing arrangements.
  • FIG. 1 shows a pumping device with a stepped piston and single-acting operation
  • FIG. 2 is a view of a pumping device with a differential piston which is single-acting on the suction side and double-acting on the delivery side;
  • FIG. 4 shows a pumping device according to the invention with a smooth piston.
  • the casing 10 of the form of embodiment shown in FIG. 1 of the pumping device consists of an upper cylinder cover 11 and a lower cylinder cover 12 which are attached to a cylindrical intermediate unit 13 'by means of bolts 14.
  • the bolts 14 are merely indicated by a center line.
  • the cylinder covers 11 and 12 have canister-type extensions between the ends of which a piston-rod, consisting of two parts 15 and 17, is disposed with the interposition of seals 16 and 18.
  • the diameter d of the piston-rod section 17 is larger than the diameter (1;, of
  • valve seat 19 bounds a valve chamber 15b formed in the upper end of piston-rod 15. At the bottom of the valve chamber there is a valve seat formed on which a valve body 21 is positioned. The valve body 21 is biased by a spring 22 which finds support on one side of the valve seat 19. The bore 17a in valve-rod section 17 alters into a valve chamber 17b bounded by the valve seat 19. In the valve chamber there is a valve body 23 positioned on the valve seat 19. The valve body is biased by a spring 24 which finds support on the end of valve chamber 17b.
  • the piston-rod section 15 has an axial bore 25 which connects the suction side S of the pumping device with the valve chamber 15b and can be sealed off by the valve body 21.
  • the piston-rod 15 In the area of the valve chamber 15b the piston-rod 15 is provided with radial bores 26.
  • piston-rod section 17 there is formed an axial bore 27 which connects valve chamber 17b to the delivery side of the pump.
  • the compressed-air piston 28 consists of a pumping plunger 29 and an operative flange 30 appertaining to the compressed-air piston, the two forming a unified piece in the form of embodiment shown here. It is also conceivable that the two component parts of the thrust-piston will be welded together.
  • the thrust-piston 28 is sealed relative to the inner wall of the cylindrical section 13 of the casing 10 by a seal 31 inserted into a groove in the operative flange, so that the lower working volume 32 is separated from the upper working volume 33 of the thrust-piston motor means.
  • the internal diameter d, of plunger 29 corresponds substantially to the external diameter d of the pistonrod section 17.
  • the plunger 29 is sealed as regards piston-rod section 15 by packing 34 and as regards piston-rod section 17 by packing 35.
  • the pumping space 36 of the present arrangement is defined between the inner wall of plunger 29, the terminal annular surface of piston-section 17 and the surface-area of piston-section 15.
  • inlet openings 11a and 12a which are connected to air-intake and air-discharge lines 37 and 38.
  • the doubleheaded arrows shown in FIG. 1 are intended to indicate that by way of each individual line air will be admitted or exhaust air discharged as the occasion demands.
  • any already known reversing arrangements for thrustpiston motor means actuated by fluid media may be employed.
  • the working volume 33 will be connected by way of line 37 with the exhaust-air outlet, and pressure will be concurrently built up in the working volume 32 by way of line 38.
  • the compressed air will now impinge on the surface of thrust-piston 28 that corresponds to the difference in diameters D d,.
  • the piston 28 moves upward, so that the suction-side space 36 is decreased.
  • the suction valve body 21 alights on the valve seat 15b and closes the suction duct 25.
  • the internal diameter d, of plunger unit 29' is larger than the form of embodiment according to FIG. 1, while the diameters D, d and d, are the same.
  • a flange 17c At the upper end of piston-rod section 17 there is formed a flange 17c whose diameter is substantially equal to the diameter d, of the internal space inside the plunger.
  • This flange 17c may also form part of a separate third piston-rod section. In the form of embodiment shown it is, however, constituted in one piece with the piston-rod section 17.
  • the flange 170 is sealed as regards the wall of plunger 29' by packing 39.
  • valve body 21 in the embodiment last described will be located on the valve seat 15a and will be closing off the suction duct S.
  • the substance being conveyed, duly forced from the suction-side space 36 flows when the valve body 23 is lifted partly into the delivery-side space 40 which is increasing during the downward movement of piston 28', but also partly through the bore 27, since space 40 in one terminal position of piston 28' is smaller than space 36 in the other terminal position of piston 28'.
  • the pumping device therefore operates singleacting on the suction side and doubleacting on the delivery side.
  • the cylindrical section 29" of the thrust-piston 28" is displaceable, since it is provided with two cylindrical bores Z, and Z
  • the plungers 29 associated with the individual rods 15 and 17 and 42, 43 are combined to form one component part 29". It is also possible to conceive of arrangements in which the plungers are independently connected to the flange 30".
  • the bores 25 and 27 not shown in FIG. 3, and the corresponding bores in the piston-rod 42, 43 define two suction-side couplings S and S and two couplings Dr, and Dr, on the delivery side.
  • the casing of the pumping device according to FIG. 3 differs from the casing according to FIGS. 1 and 2 due to the fact that the suction-side spaces 32" and 33" are sealed, as regards the plunger-associated section 29" of the thrust-piston 28", by packing 44 and 45.
  • the leakages occurring at packing means 34 and 35 are fed to working volumes 32 and 33 and, passing through exhaust ducts 37 and 38 respectively for the operative medium for the thrust-piston motor means, arrivein the open. This may in many cases be desired, since the pumping device will then have suction-side and delivery-side couplings S, Dr, and will in addition be closed hermetically.
  • FIG. 3 An arrangement according to FIG. 3 is more advantageous.
  • the cylinder covers 1 l and 12" are interrupted by excised areas 46 and 47, so that the leakages occurring at packing means 34 and 35 can be immediately noticed. In this event the working volumes 32 and 33" have to be sealed from the outside space around the pumping device by seals 44 and 45.
  • the effective areas of the thrust-piston motor means both during the upward and the downward movement, may be ascertained from the difference in diameters D d d being the diameter of the plunger component 29".
  • a pumping device in accordance with the invention should be described which is, however, not provided with a stepped piston.
  • a piston-rod 48 made in one piece with the lower cylinder cover 12.
  • the lower cylinder cover has a level outer surface.
  • the thrust-piston 49 consists of a cylindrical part 50 closed at one end and an operative flange 51 provided at the edge of the said cylindrical section, the flange being constituted in this form of embodiment as well in one piece with the canister-shaped part 50.
  • valve bodies 55 and 56 and the associated closure springs 57 and 58 are so positioned in the valve chambers 48a and 48b that, upon the pumping space 59 which is bounded by the terminal surface 54 and the interior wall of the canister-shaped section 50 increasing, the valve body 55 is lifted from its seat, and so the suction duct 52 is opened, and upon a decrease in space 59 the valve body 55 alights on its seat and the valve body '56, against the urging of spring 58, lifts, so that the substance being conveyed and now located in pumping space 59 is able to flow through the delivery-side duct 53 to the delivery-side outlet Dr.
  • the arrangement according to FIG. 4 also displays the features fundamental to the invention.
  • the pump is arranged within the motor means, the piston-rod has been eliminated, and consequently its sealing system as well.
  • the valves are accommodated in a fixed piston.
  • the forms of embodiment according to FIGS. 1 to 3 offer the additional advantage that, with a given diameter D for the thrust-piston motor means and a prescribed diameter d for section of the differential piston-rod, meretliy through an alteratron in the internal diameter d,'an d oft e plunger 28 or 28 respectively and through a corresponding alteration in the diameter d, of section 17 of the differential piston-rod, every conceivable transmission ratio between the pressure of the operative medium for the thrust-piston motor means and the pressure of the substance being conveyed can be achieved. In this process the diameters d, and d, respectively and also d will always be increasingly approaching the diameter d as the transmission ratio increases, without however ever attaining the latter diameter.
  • valve means comprises first and second valves, each valve communicating with a passage.
  • said fixed piston includes a first portion of larger diametrical dimension than said second portion, a third portion defined on said fixed piston intermediate said first and second portions having a diameter greater than that of said first portion and sealingly engaging said inner chamber, said valve means including a first valve communicating with said chamber adjacent said first fixed piston portion and a second valve communicating with said chamber adjacent said second fixed piston portion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
US00134606A 1970-04-25 1971-04-16 Pumping device Expired - Lifetime US3713755A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702020317 DE2020317A1 (de) 1970-04-25 1970-04-25 Pumpvorrichtung

Publications (1)

Publication Number Publication Date
US3713755A true US3713755A (en) 1973-01-30

Family

ID=5769390

Family Applications (1)

Application Number Title Priority Date Filing Date
US00134606A Expired - Lifetime US3713755A (en) 1970-04-25 1971-04-16 Pumping device

Country Status (4)

Country Link
US (1) US3713755A (enrdf_load_stackoverflow)
DE (1) DE2020317A1 (enrdf_load_stackoverflow)
FR (1) FR2090612A5 (enrdf_load_stackoverflow)
GB (1) GB1342011A (enrdf_load_stackoverflow)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5064802A (enrdf_load_stackoverflow) * 1973-10-11 1975-06-02
US4044745A (en) * 1973-03-14 1977-08-30 Holec, N.V. Injector pump
US4131397A (en) * 1977-04-14 1978-12-26 Offshore Devices Inc. Pumps
US4334833A (en) * 1980-10-28 1982-06-15 Antonio Gozzi Four-stage gas compressor
EP0118615A1 (en) * 1983-02-07 1984-09-19 Caterpillar Industrial Inc. Pump arrangement in a piston for a linear fluid operated device
US4478561A (en) * 1982-03-25 1984-10-23 Hydra-Rig, Incorporated Hydraulic intensifier
US4735051A (en) * 1984-06-07 1988-04-05 Veb Kombinat Orsta-Hydraulik Double admitting pressure intensifier
US4776774A (en) * 1985-07-17 1988-10-11 Anastasia Julio C Hydraulic double-acting hydropneumatic pressure multiplying device
US4895492A (en) * 1982-09-27 1990-01-23 Veb Kombinat Orsta-Hydraulik Double acting and automatically reversing pressure intensifier
US5538407A (en) * 1993-01-26 1996-07-23 Groeneveld Transport Efficiency B.V. Proportioner and fluid proportioning system
US20080286120A1 (en) * 2007-05-15 2008-11-20 Jan Noord Reciprocating piston pump operating on pressure medium
US20090047144A1 (en) * 2006-02-16 2009-02-19 Gasfill Limited Fluid Compressor and Motor Vehicle Refuelling Apparatus
US20090242471A1 (en) * 2008-03-31 2009-10-01 Ebara Corporation Power recovery chamber
US9803660B1 (en) * 2014-02-04 2017-10-31 Danfoss Power Solutions Inc. Low friction compact servo piston assembly
CN109372714A (zh) * 2018-10-29 2019-02-22 中国石油集团渤海钻探工程有限公司 一种采用压缩空气驱动的高压注水泵

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1411978A (en) * 1972-08-31 1975-10-29 Lister Co Ltd R A Lubricating pump
EP0340201A1 (de) * 1988-03-25 1989-11-02 Josef Brosowitsch Hydraulisch betriebene Kolbenpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US496898A (en) * 1893-05-09 Air-pump
DE809885C (de) * 1950-03-23 1951-08-02 Gerhard Sandmann Doppeltwirkende Hochdruckkolbenpumpe
US3205825A (en) * 1963-11-18 1965-09-14 Kojabashian Charles Proportioning pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US496898A (en) * 1893-05-09 Air-pump
DE809885C (de) * 1950-03-23 1951-08-02 Gerhard Sandmann Doppeltwirkende Hochdruckkolbenpumpe
US3205825A (en) * 1963-11-18 1965-09-14 Kojabashian Charles Proportioning pump

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4044745A (en) * 1973-03-14 1977-08-30 Holec, N.V. Injector pump
JPS5064802A (enrdf_load_stackoverflow) * 1973-10-11 1975-06-02
US4131397A (en) * 1977-04-14 1978-12-26 Offshore Devices Inc. Pumps
US4334833A (en) * 1980-10-28 1982-06-15 Antonio Gozzi Four-stage gas compressor
US4478561A (en) * 1982-03-25 1984-10-23 Hydra-Rig, Incorporated Hydraulic intensifier
US4895492A (en) * 1982-09-27 1990-01-23 Veb Kombinat Orsta-Hydraulik Double acting and automatically reversing pressure intensifier
EP0118615A1 (en) * 1983-02-07 1984-09-19 Caterpillar Industrial Inc. Pump arrangement in a piston for a linear fluid operated device
US4735051A (en) * 1984-06-07 1988-04-05 Veb Kombinat Orsta-Hydraulik Double admitting pressure intensifier
US4776774A (en) * 1985-07-17 1988-10-11 Anastasia Julio C Hydraulic double-acting hydropneumatic pressure multiplying device
US5538407A (en) * 1993-01-26 1996-07-23 Groeneveld Transport Efficiency B.V. Proportioner and fluid proportioning system
US20090047144A1 (en) * 2006-02-16 2009-02-19 Gasfill Limited Fluid Compressor and Motor Vehicle Refuelling Apparatus
US8840377B2 (en) * 2006-02-16 2014-09-23 Gasfill Limited Fluid compressor and motor vehicle refuelling apparatus
US20080286120A1 (en) * 2007-05-15 2008-11-20 Jan Noord Reciprocating piston pump operating on pressure medium
US20090242471A1 (en) * 2008-03-31 2009-10-01 Ebara Corporation Power recovery chamber
US8277653B2 (en) * 2008-03-31 2012-10-02 Ebara Corporation Power recovery chamber
US9803660B1 (en) * 2014-02-04 2017-10-31 Danfoss Power Solutions Inc. Low friction compact servo piston assembly
CN109372714A (zh) * 2018-10-29 2019-02-22 中国石油集团渤海钻探工程有限公司 一种采用压缩空气驱动的高压注水泵

Also Published As

Publication number Publication date
DE2020317A1 (de) 1971-11-11
GB1342011A (en) 1973-12-25
FR2090612A5 (enrdf_load_stackoverflow) 1972-01-14

Similar Documents

Publication Publication Date Title
US3713755A (en) Pumping device
US7399168B1 (en) Air driven diaphragm pump
US4406596A (en) Compressed air driven double diaphragm pump
US3884597A (en) Reciprocating pump
US6722256B2 (en) Reduced icing valves and gas-driven motor and diaphragm pump incorporating same
US3776665A (en) Two stage fluid pump
US6655935B2 (en) Gas compressor comprising a double acting piston, an elongate chamber, multiple inlets mounted within heads on both sides of the chamber, and one central outlet
US5441281A (en) Shaft seal
US3637330A (en) Multichamber tubular diaphragm pump
US4173433A (en) Two-stage gas compressor
US20070116588A1 (en) Piston compressor for compressing gaseous media in at least two working chambers
US5611678A (en) Shaft seal arrangement for air driven diaphragm pumping systems
US2650018A (en) Compressor
CN111561434A (zh) 一种平衡式气动液压泵
CA2491298A1 (en) Pneumatic reciprocating motor
US5378117A (en) Valve unloading means, and a valve unloading actuator therefor
EP2807374B1 (en) Valveless reciprocating compressor
CN118327926A (zh) 一种活塞式可变级数压缩缸
US3583836A (en) Pump
US740771A (en) Gas-compressing machine.
US3473726A (en) Compressor for a mechanical refrigerator
US2889108A (en) Compressor
US3198425A (en) Inertia type pump or compressor
US9435322B2 (en) Valveless reciprocating compressor
WO2002025111A1 (en) Reciprocating compressor driven by a linear motor