EP0021315A1 - Machine à piston, notamment pompe à piston - Google Patents

Machine à piston, notamment pompe à piston Download PDF

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Publication number
EP0021315A1
EP0021315A1 EP80103359A EP80103359A EP0021315A1 EP 0021315 A1 EP0021315 A1 EP 0021315A1 EP 80103359 A EP80103359 A EP 80103359A EP 80103359 A EP80103359 A EP 80103359A EP 0021315 A1 EP0021315 A1 EP 0021315A1
Authority
EP
European Patent Office
Prior art keywords
space
pump
piston
lubricant
working
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.)
Granted
Application number
EP80103359A
Other languages
German (de)
English (en)
Other versions
EP0021315B1 (fr
Inventor
Bernhard Frey
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.)
Hydrowatt Systems Ltd
Original Assignee
Hydrowatt Systems Ltd
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 Hydrowatt Systems Ltd filed Critical Hydrowatt Systems Ltd
Priority to AT80103359T priority Critical patent/ATE14915T1/de
Publication of EP0021315A1 publication Critical patent/EP0021315A1/fr
Application granted granted Critical
Publication of EP0021315B1 publication Critical patent/EP0021315B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/084—Machines, pumps, or pumping installations having flexible working members having tubular flexible members the tubular member being deformed by stretching or distortion

Definitions

  • the invention relates to an engine or working machine, in particular a piston pump, with at least one piston-cylinder arrangement to form a pulsating working space, in particular with a flexible, preferably tubular, sealing member serving to seal the working space, which is in contact with a liquid, in particular a lubricant, slidably supported on a support surface, a rotating device being provided, in particular, for the pistons.
  • Machines of this type are known, for example from DE-OS 25 54 733.
  • Piston machines which generally have a crank or eccentric drive, are generally associated with a comparatively high construction cost and space requirement for the drive device in relation to the usable stroke volume.
  • the devices for the design with support of the elastically deformable sealing hose by means of pressure lubrication have a similar influence. There is therefore a need in general for piston machines and in particular for those of the aforementioned type to reduce the space requirement, if possible without substantial increase in construction costs or while maintaining a comparatively simple construction.
  • the object of the invention is therefore to create a piston power or working machine which is characterized by a comparatively short overall length of the piston-cylinder arrangement including the adjacent parts of the drive device.
  • the inventive solution to this problem is characterized by the features specified in claim 1.
  • the subsequent design, encompassing the cylinder, of the drive member, for example a ram or the like which is conventional per se and which cooperates with an eccentric drive device makes it possible, with the same support and guide length, for this drive member, which oscillates in accordance with the working movement, to substantially shorten the overall length of the Piston-cylinder arrangement.
  • the easily possible, thin-walled design of the portion of the drive member encompassing the cylinder makes it possible to avoid a substantial increase in the diameter of the piston-cylinder arrangement.
  • the reduction in the overall length of the piston-cylinder arrangement is particularly noticeable in the case of star-shaped multi-cylinder arrangements, because this overall length reduces the overall diameter of the pump.
  • a pulsating secondary space results, corresponding to the oscillating working movement of the latter, which, in the case of conventional pistons, is leaked can fill the work area or in the case of hermetic work space sealing with the outflowing lubricant by means of the elastically deformable sealing hose with pressure lubrication support mentioned.
  • an advantageous development of the invention provides at least one compensating channel with a large cross-section between the pulsating secondary space and a pressure equalizing space.
  • a development of the invention based on the aforementioned aspects provides that the pulsating secondary space is connected to a space located at the end of the cylinder within the drive member and pulsating in accordance with the oscillating working movement by a throttle channel.
  • the pulsating space between the cylinder end and the drive member, into which the lubricant or the leakage liquid flowing out of the cylinder or the sealing hose collects from the work space is used as a pump or auxiliary work space for the continuous discharge of the accumulating liquid, whereby the throttle channel the backflow of the liquid in a particularly simple manner limited to a small extent by the pressure-relieved adjoining room at the other end of the drive element.
  • the throttle channel thus acts like a check valve.
  • this development of the invention is characterized by an overflow channel connecting the storage space to the return collecting space with an adjustable or controllable actuator for a Limitation of the flow from the storage room to the return collecting area.
  • This design enables a safe filling and thus a trouble-free operation of the return pump and thus the maintenance of the lubricant pressure, which is essential for the overall operational safety, in a simple manner. This is particularly important in the case of high-pressure pumps with a lubricated sealing hose because failure of the lubrication on the support surface can very quickly result in damage to the sealing hose.
  • Power and working machines, in particular piston machines, of the type in question require, at high power densities, special measures for reliable lubrication of the highly loaded bearing points and the piston sliding surfaces.
  • pressure circulation lubrication with a lubricant cooling device is generally provided.
  • the task of the invention namely primarily to reduce the space requirement while maintaining a comparatively low construction cost, accordingly extends to the design of the pressure lubrication system and in particular the cooling device, because these assemblies - especially the cooling device - have comparatively large dimensions in conventional designs.
  • the invention provides that the cooling device has at least one heat exchanger charged with the lubricant and with the working medium of the machine.
  • the cooling device has at least one heat exchanger charged with the lubricant and with the working medium of the machine.
  • a further development of the invention relates to that known type of machine designed as a pump, in which a prefeed pump for the pressure supply of the working medium is provided on the inflow side of the pump.
  • a prefeed pump for the pressure supply of the working medium is provided on the inflow side of the pump.
  • the pre-feed pump which is present anyway, is used for a forced circulation of the cooling working fluid in the lubricant heat exchanger.
  • a particularly advantageous embodiment results in this connection by designing the working medium system of the heat exchanger as a second return flow between the outflow side and the inflow side of the pre-feed pump.
  • a throttle preferably an adjustable throttle, can be arranged in the heat exchanger backflow branch according to an expedient embodiment of the invention.
  • the drive device 10 of the pump consists of a shaft 1 with an eccentric 2 coupled to a motor (not shown) on which a non-rotating, translationally rotating sliding piece 3 with a number of tangential pressure surfaces 4 corresponding to the number of cylinders - here for example five - is mounted .
  • a pressure surface is in operative connection with a drive member 30 Piston 20 indicated, which is connected to an elastically deformable sealing tube 22.
  • a coil spring 23 presses the piston 20 against the bottom portion 30b of the sleeve-shaped drive member 30 and sets the sealing hose under axial tension.
  • the sealing hose sits in the bore of a cylinder 25, with which it is firmly connected at the upper end, and thus hermetically seals the working space 24 formed in the hose interior.
  • This working space changes its volume in accordance with the oscillating movement of the drive member 30 and generates the pumping action in connection with check valves 26 and 27, which are connected to a delivery and suction channel 28.
  • the lubrication system of the pump is in the form of pressure circulation lubrication with a gear pressure lubrication pump 100, a return collecting space 120 surrounding the eccentric 3 of the drive device and with an annular storage space 110 concentrically surrounding the axis of rotation XX of the drive device and with one from the return collecting space 120 into the Storage pump 110 promoting return pump 105 is formed.
  • This design and arrangement of the storage space enables a particularly space-saving multi-cylinder pump construction with a symmetrical distribution of the connections to the individual cylinders over the circumference of the ring.
  • the inclusion of the storage space in the cylindrical housing of the star-shaped multi-cylinder arrangement also serves the same purpose.
  • the pressure lubrication pump 100 delivers from the storage space 110 via channels 103 and 104 and a filter 102 into an annular distributor channel 101, from where pressure channels 90 and 95 lead to the individual cylinders 25 with adjusting throttles 90a and 95a.
  • the pressurized lubricant from the channel 90 is supplied to support the sliding movement of the outer surface of the sealing hose 22 and flows in the axial direction of the cylinder (downwards according to FIG. 1) into a pulsating space 42 formed in the area of the lower piston and cylinder end .
  • This space is connected via a throttle duct 45, which is designed as a gap space between the inner surface of the cylindrical section 30a of the drive member 30 and the outside of the cylinder 25, to a likewise pulsating secondary space 35 formed at the upper end of the cylindrical section 30a.
  • the throttle channel 45 acts as a quasi check valve, so that the space 42 essentially acts as a low-pressure space for an undisturbed outflow of the lubricant from the gap between the sealing hose and the cylinder bore or support surface acts.
  • low pressure is also required in the adjoining room 35.
  • the latter is connected to the storage space 110 via a compensation channel 40 with a large cross section, which thus serves as a pressure compensation space.
  • the lubricant supplied via the channel 95 reaches the outer surface of the cylindrical section 30a of the drive member 30, where the latter is guided so as to be displaceable coaxially with the cylinder 25.
  • the lubricant then flows via lubrication channels 47 to the pressure surfaces 4 and further into the return collecting space 120. This lubricant circuit is thus also closed.
  • the return pump 105 draws in from the lower part of the collecting space 120 via a channel 115 and delivers via an ascending return channel 106 in the apex region 110a of the storage space 110. This results in an effective ventilation of the lubricant flow entering the storage space.
  • the suction space of the latter i.e. the lower part of the collecting space 120, with the storage space 110 connecting overflow channel 130 is provided, which prevents this area from being sucked empty.
  • An actuator is provided for limiting the overflow, for which an adjustable throttle 135a may be sufficient, for example.
  • an overflow control with a controllable valve 135 as an actuator and with a float 140 as a control device is provided. This allows an optimal filling level to be maintained in the suction space of the return pump 105. Sufficient filling of the return pump is essential, in particular, to avoid foaming, which would impair reliable pressure circulation lubrication.
  • FIG. 2 The pressure circulation lubrication system of the pump is shown schematically in a clear form in FIG. 2, the essential functional elements being shown symbolically, but with the same reference numerals as in FIG. 1.
  • the avoidance of foam formation in the delivery system of the circulating pressure lubrication is essential for a perfect function.
  • This is particularly useful for the design of the rotor 105a of the return pump 105 shown in FIGS. 3 and 4 with a plurality of slots designed as storage spaces 105b, which are arranged in the manner of a radial centrifugal pump and extend over a radius difference with respect to the axis of rotation XX of the pump .
  • the lubricant located in these storage spaces is subject to a separation between lubricant with a greater or lesser liquid content or, conversely, a lower and greater gas or foam content.
  • Abström control port 108 of the exhaust flow is discharged from the pump substantially only that part of the lubricant from the storage areas 105b radially at a suitable slowing down or throttling, which has only a very small gas or foam content.
  • the stowage spaces then connect to an outflow control opening 109b which is rich in gas or foam
  • FIG. 4 Another mechanism that contributes to gas and foam cut-off within the rotor of the return pump is indicated in FIG. 4.
  • a radial circular flow with a course indicated at A can then be generated by means of a comparatively wide gap space 109a arranged axially next to the rotor 105a, which is shown here in a strongly distorting manner, which prevents the accumulation of the low-gas lubricant in the radially outer regions of the storage spaces 105b favored and possibly also a partial return of the foam accumulated in the radially inner storage space areas in the direction of the suction chamber of the pump.
  • a cooling device for the lubricant is accommodated within the annular lubricant storage space 110.
  • This cooling device essentially consists of a heat exchanger 210 which has a channel system 212 through which the working medium of the pump flows and which can be seen in detail in FIG. 6.
  • the flow of the working medium in this channel system is achieved by means of the feed pump 150 already mentioned, which is accommodated coaxially with the annular storage space 110 and with an axial overlap in its inner recess space 140.
  • the inflow side 160 of the feed pump 150 lies in the region of an axial end cover 155 of the pump housing, which is aligned with an end wall 230 closing off the storage space 110.
  • the prefeed pump is designed as an axial flow pump, the rotor of which is seated on the pump shaft 1 in the manner shown schematically in FIG. 5 and the outflow side 170 of which is connected to an annular channel 174 by radial channels 172.
  • Axial branch channels 176 lead from the latter (only one of these is shown in FIG. 5) Channels) to the individual, star-shaped pump cylinders (not shown).
  • the piston-cylinder arrangements of the pump receive the working fluid with a pre-pressure of, for example, a few atmospheres, which is sufficient for safe filling in the suction stroke of the pistons.
  • Channel sections 178 which are lengthened at the rear connect the outflow side 170 of the pre-feed pump 150 to an annular channel 180 in a central, section-like section 232 of the end wall 230.
  • a radial channel 182 leads to an inflow distributor 216 of the heat exchanger which is inserted in the outer part of the end wall 230 210.
  • the inflow distributor arranged in the lower apex area of the storage space 110 From this inflow distributor arranged in the lower apex area of the storage space 110, the partial flow of the cool working fluid branched off from the outflow side of the pre-feed pump passes via a channel system 212 of the heat exchanger 210, which can be seen in detail in FIG Inflow distributor 216 arranged outflow collector 218. The latter is also used in the outer part of the end wall 230.
  • the outflow collector is connected to the suction side 160 of the prefeed pump via a radial channel 184. This results in a return flow circuit parallel to the main delivery flow for the branched-off part of the delivery flow of the prefeed pump 150, which is fed to the inflow side of the main pump.
  • a throttle screw 220 is inserted into the end wall 230, the tip of which engages in the channel 182 and here forms an adjustable throttle point in the partial feed flow to the inflow distributor 216.
  • the design of the heat exchanger can be seen in detail in FIG. 6.
  • the channel system 212 of the heat exchanger is then practically completely submerged within the lubricant storage space 110 and below the lubricant level.
  • a lubricant flow results in the annular storage area, which flows downward in essentially both circumferential directions from the upper apex area lower apex runs.
  • the channel system 212 of the heat exchanger 210 comprises a plurality of ring-shaped heat exchanger tubes 214 which extend in the circumferential direction of the storage space 110 and which, as mentioned, essentially below the lubricant level and therefore enable heat exchange over their entire surface.
  • a plurality of heat exchanger tubes 214 connected in parallel, arcuate and adapted to the ring shape of the storage space 110 are connected.
  • the result is an essentially cylindrical arrangement of heat exchanger tubes lying side by side in the cylinder axis direction, i.e. a large-scale arrangement of heat transfer surfaces adapted to the spatial conditions of the storage space and the lubricant flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP80103359A 1979-06-20 1980-06-17 Machine à piston, notamment pompe à piston Expired EP0021315B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80103359T ATE14915T1 (de) 1979-06-20 1980-06-17 Kolbenmaschine, insbesondere kolbenpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH577979A CH645435A5 (de) 1979-06-20 1979-06-20 Kolbenpumpe.
CH5779/79 1979-06-20

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP84108027.8 Division-Into 1984-07-09

Publications (2)

Publication Number Publication Date
EP0021315A1 true EP0021315A1 (fr) 1981-01-07
EP0021315B1 EP0021315B1 (fr) 1985-08-14

Family

ID=4299196

Family Applications (2)

Application Number Title Priority Date Filing Date
EP84108027A Expired - Lifetime EP0153982B1 (fr) 1979-06-20 1980-06-17 Machine à piston, particulièrement pompe à piston
EP80103359A Expired EP0021315B1 (fr) 1979-06-20 1980-06-17 Machine à piston, notamment pompe à piston

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP84108027A Expired - Lifetime EP0153982B1 (fr) 1979-06-20 1980-06-17 Machine à piston, particulièrement pompe à piston

Country Status (16)

Country Link
US (1) US4671743A (fr)
EP (2) EP0153982B1 (fr)
JP (2) JPS5627086A (fr)
AR (1) AR219466A1 (fr)
AT (2) ATE51683T1 (fr)
AU (1) AU5935080A (fr)
BR (1) BR8003711A (fr)
CA (1) CA1142030A (fr)
CH (1) CH645435A5 (fr)
CS (1) CS229656B2 (fr)
DD (1) DD151487A5 (fr)
DE (2) DE3070978D1 (fr)
HU (1) HU183151B (fr)
PL (1) PL130376B1 (fr)
SU (1) SU1380617A3 (fr)
ZA (1) ZA803580B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3332355C1 (de) * 1983-09-08 1984-11-15 Hemscheidt Maschf Hermann Zylinderkolben-Anordnung für eine Kolbenmaschine

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4997344A (en) * 1988-06-15 1991-03-05 Deere & Company Rotor bearing pre-load for a radial piston pump
US5709536A (en) * 1995-01-30 1998-01-20 Titan Tool, Inc. Hydro mechanical packingless pump and liquid spray system
DE19804275A1 (de) * 1998-02-04 1999-08-12 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
JP3349945B2 (ja) 1998-03-13 2002-11-25 日本電気株式会社 信号変換装置及び信号変換装置を用いた光伝送方式
EP1058001B1 (fr) * 1999-05-31 2005-02-16 CRT Common Rail Technologies AG Pompe d'alimentation haute pression
DE10228552B9 (de) * 2002-06-26 2007-08-23 Siemens Ag Radialkolbenpumpeneinheit
DE102009060733A1 (de) 2009-12-29 2011-06-30 European Charcoal Ag Vorrichtung zur kontinuierlichen Umwandlung von Biomasse und System zur Energiegewinnung daraus
US9752590B2 (en) 2013-03-13 2017-09-05 Ghsp, Inc. Two pump design with coplanar interface surface
US11015585B2 (en) 2014-05-01 2021-05-25 Ghsp, Inc. Submersible pump assembly
US10087927B2 (en) 2014-05-01 2018-10-02 Ghsp, Inc. Electric motor with flux collector

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB224013A (en) * 1924-04-23 1924-11-06 William Thomas Shannon Improvements in engine lubricating systems
FR666890A (fr) * 1929-01-03 1929-10-07 Cem Comp Electro Mec Dispositif de refroidissement de l'huile de graissage des machines actionnant des pompes
US1750170A (en) * 1926-04-15 1930-03-11 Frisch August Pumping apparatus
DE530598C (de) * 1927-11-28 1931-07-30 Drysdale & Co Ltd Umlaufschmiervorrichtung
GB524199A (en) * 1938-10-26 1940-08-01 Hamilton Neil Wylie Improvements in variable stroke radial pumps
GB549670A (en) * 1941-01-23 1942-12-07 Clement Brown Improvements in or relating to rotary pumps
US2523543A (en) * 1946-04-29 1950-09-26 James E Smith Variable stroke radial pump
GB650312A (en) * 1946-02-09 1951-02-21 Poul Haahr Improvements in or relating to high-pressure pumps
FR1095226A (fr) * 1954-03-12 1955-05-31 Régulateur de niveau d'huile
US2917003A (en) * 1957-04-22 1959-12-15 James E Smith Variable stroke variable pressure pump or compressor
US2963886A (en) * 1958-01-02 1960-12-13 Carrier Corp Lubricant cooling system
CH422524A (de) * 1963-04-23 1966-10-15 Philips Nv Zum Fördern siedender Flüssigkeiten geeignete Kreiselpumpe
US3289651A (en) * 1963-12-10 1966-12-06 Yanmar Diesel Engine Co Cooling device for rotary piston engines
GB1114680A (en) * 1964-05-18 1968-05-22 Sibany Mfg Corp Apparatus for pumping fluids

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Publication number Priority date Publication date Assignee Title
US781678A (en) * 1904-05-17 1905-02-07 Clarence H Richwood Air-compressing machine.
US2064750A (en) * 1932-04-23 1936-12-15 Bosch Robert Piston pump for the conveyance of liquids
US2179354A (en) * 1935-08-07 1939-11-07 Super Diesel Tractor Corp Pump
US2364111A (en) * 1942-03-20 1944-12-05 John W Tucker Pump and the like
US2472355A (en) * 1946-02-01 1949-06-07 New York Air Brake Co Pump
US3554090A (en) * 1969-04-04 1971-01-12 Arthur G Wallace Fluid pressure actuated motor
US3703342A (en) * 1971-07-30 1972-11-21 Walbro Corp Fuel pump bellows construction
US3854383A (en) * 1972-12-26 1974-12-17 Dynacycle Corp Tension actuated pressurized gas driven rotary motors
IT1042341B (it) * 1975-09-08 1980-01-30 Pirelli Miglioramenti negli impianti di pompaggio per cavi elettrici in o.f.
DE2914694C2 (de) * 1979-04-11 1980-09-11 Hermann Hemscheidt Maschinenfabrik Gmbh & Co, 5600 Wuppertal Zylinderkolben-Aggregat

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB224013A (en) * 1924-04-23 1924-11-06 William Thomas Shannon Improvements in engine lubricating systems
US1750170A (en) * 1926-04-15 1930-03-11 Frisch August Pumping apparatus
DE530598C (de) * 1927-11-28 1931-07-30 Drysdale & Co Ltd Umlaufschmiervorrichtung
FR666890A (fr) * 1929-01-03 1929-10-07 Cem Comp Electro Mec Dispositif de refroidissement de l'huile de graissage des machines actionnant des pompes
GB524199A (en) * 1938-10-26 1940-08-01 Hamilton Neil Wylie Improvements in variable stroke radial pumps
GB549670A (en) * 1941-01-23 1942-12-07 Clement Brown Improvements in or relating to rotary pumps
GB650312A (en) * 1946-02-09 1951-02-21 Poul Haahr Improvements in or relating to high-pressure pumps
US2523543A (en) * 1946-04-29 1950-09-26 James E Smith Variable stroke radial pump
FR1095226A (fr) * 1954-03-12 1955-05-31 Régulateur de niveau d'huile
US2917003A (en) * 1957-04-22 1959-12-15 James E Smith Variable stroke variable pressure pump or compressor
US2963886A (en) * 1958-01-02 1960-12-13 Carrier Corp Lubricant cooling system
CH422524A (de) * 1963-04-23 1966-10-15 Philips Nv Zum Fördern siedender Flüssigkeiten geeignete Kreiselpumpe
US3289651A (en) * 1963-12-10 1966-12-06 Yanmar Diesel Engine Co Cooling device for rotary piston engines
GB1114680A (en) * 1964-05-18 1968-05-22 Sibany Mfg Corp Apparatus for pumping fluids

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3332355C1 (de) * 1983-09-08 1984-11-15 Hemscheidt Maschf Hermann Zylinderkolben-Anordnung für eine Kolbenmaschine

Also Published As

Publication number Publication date
JPS5627086A (en) 1981-03-16
CA1142030A (fr) 1983-03-01
ZA803580B (en) 1981-07-29
CS229656B2 (en) 1984-06-18
AR219466A1 (es) 1980-08-15
PL130376B1 (en) 1984-08-31
EP0153982A2 (fr) 1985-09-11
ATE14915T1 (de) 1985-08-15
EP0153982B1 (fr) 1990-04-04
DD151487A5 (de) 1981-10-21
DE3070978D1 (en) 1985-09-19
CH645435A5 (de) 1984-09-28
EP0021315B1 (fr) 1985-08-14
EP0153982A3 (en) 1985-11-21
JPS6426096A (en) 1989-01-27
JPH0250358B2 (fr) 1990-11-02
ATE51683T1 (de) 1990-04-15
PL225024A1 (fr) 1981-04-24
BR8003711A (pt) 1981-01-13
AU5935080A (en) 1981-01-08
JPS6365830B2 (fr) 1988-12-16
SU1380617A3 (ru) 1988-03-07
DE3072177D1 (de) 1990-05-10
HU183151B (en) 1984-04-28
US4671743A (en) 1987-06-09

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