EP0061405B1 - Hydraulische Pumpe mit variablem Hub und Druckflüssigkeitserzeuger, der eine solche Pumpe verwendet - Google Patents

Hydraulische Pumpe mit variablem Hub und Druckflüssigkeitserzeuger, der eine solche Pumpe verwendet Download PDF

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Publication number
EP0061405B1
EP0061405B1 EP82400513A EP82400513A EP0061405B1 EP 0061405 B1 EP0061405 B1 EP 0061405B1 EP 82400513 A EP82400513 A EP 82400513A EP 82400513 A EP82400513 A EP 82400513A EP 0061405 B1 EP0061405 B1 EP 0061405B1
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EP
European Patent Office
Prior art keywords
piston
pump
chamber
hydraulic pump
engine
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
Application number
EP82400513A
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English (en)
French (fr)
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EP0061405A1 (de
Inventor
Auguste Moiroux
Maurice Bouvier
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.)
Poclain Hydraulics France SA
Airmachines SA
Original Assignee
Poclain Hydraulics France SA
Airmachines SA
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 Poclain Hydraulics France SA, Airmachines SA filed Critical Poclain Hydraulics France SA
Priority to AT82400513T priority Critical patent/ATE13932T1/de
Publication of EP0061405A1 publication Critical patent/EP0061405A1/de
Application granted granted Critical
Publication of EP0061405B1 publication Critical patent/EP0061405B1/de
Expired 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines

Definitions

  • Such engines essentially comprise a combustion chamber into which are introduced a liquid or gaseous fuel and an oxidizer, according to suitable cycles.
  • an appropriate zone of the piston evolves in a cylinder and defines there two chambers.
  • the first, said pumping chamber is capable of being placed in communication with the atmosphere with a view to filling it with air; the latter is then partially discharged into the combustion chamber to ensure the role of the oxidant there.
  • the second chamber, called the mattress chamber also capable of being supplied with atmospheric air, constitutes an elastic element repelling the piston of the engine and thus ensuring the compression of the fuel-oxidant mixture before it explodes. It is known that one of the main advantages of this type of engine is to avoid the need for a mechanical connection of the piston with the fixed casing while allowing high security with respect to the risks presented by the free piston.
  • the invention therefore firstly relates to a double-acting hydraulic pump, the piston of which can be provided by a variable-stroke motor member.
  • the flow rate supplied is of course a function of the outward and return stroke of the piston, at least in the vicinity of the maximum load of the pump and more precisely up to approximately 60% of this maximum load. Below this load, it can be seen that it generally becomes impossible to adjust the stroke of the drive member.
  • the piston rod of the pump is extended beyond the piston and evolves, outside the cylinder, in a variable volume capacity formed in the body of the pump, communicating with the control member. a bypass device connecting the two chambers of the pump cylinder.
  • This bypass device can be produced in various ways, but, according to an advantageous characteristic of the invention, it is constituted by a drawer moving in front of two orifices communicating respectively with each of the chambers of the cylinder, this drawer being subjected, against the action of an adjustable spring (depending on the flow rate requested from the pump), the action of the pressure prevailing in the variable volume capacity.
  • the pump according to the invention may comprise, on the delivery pipe, a fluid accumulator situated downstream of the delivery valves of each of the chambers. @ (at the bottom of the page)
  • the invention however provides, in the case of such a generator, to advantageously produce the auxiliary motor of the booster pump of the hydraulic pump.
  • Such an auxiliary engine is driven by the pressurized air existing in the mattress chamber of the free piston engine.
  • the auxiliary engine will itself be a single-acting piston engine whose piston is subjected, against the action of a return spring, to the action of the pressure prevailing in the mattress chamber.
  • a generator according to the invention essentially comprises a free piston engine designated by the general reference 1 and a hydraulic pump designated by the general reference 2.
  • the engine 1 is constituted, as is known, by a combustion chamber 3 in which a piston 4 operates.
  • the engine is of the two-stroke Diesel type.
  • the piston 4 has at its end opposite to the combustion chamber an annular portion 5 evolving in a cylinder 6 and delimiting on the one hand, a chamber 7, called pumping, and, on the other hand, a chamber 8, called chamber -mattress.
  • Valves 9 allow the chamber 7 to communicate with the atmosphere, while valves 10 open onto conduits 11 communicating with the combustion chamber, when the piston 4 releases the corresponding lights.
  • a duct 13 schematically shown and provided with a valve 13 allows the filling of the metelas chamber 8 from the air contained in the pumping chamber 7, in particular to compensate for the air leaks occurring in this mattress chamber at during operation.
  • the hydraulic pump 2, which is driven by the motor 1, is constituted by a body 14, fixed to the body of the motor, in which a cylinder 15 is preferably provided. coaxial with the cylinder 6 of the engine and its combustion chamber 3.
  • the cylinder 15 is constituted by an attached jacket, mounted in the bore 14a of the body 14.
  • the piston 16 and the pump is coupled to the piston 4 of the engine by means of a piston rod 17, coaxial with the latter and constituting with it a one-piece assembly.
  • the piston 16 thus defines in the cylinder 15 two chambers 18 and 19, each of them being provided with at least one suction valve 20 and one discharge valve 21.
  • Two sealing rings 25set 25a close the chambers 18 and 19 and also ensure the immobilization of the cylinder 15 in the axial direction, while allowing the passage of the piston rod 17 under conditions which will be specified even further .
  • FIG. 1 represents an engine 1 whose piston 4 receives the rod 17 of the piston 16 of the pump on its face opposite to the combustion chamber
  • FIG. 1a shows an alternative embodiment which makes it possible to reduce the longitudinal dimensions of the generator.
  • the face of the piston 4 opposite the combustion chamber is open and allows the latter to cover, at least in part, the body 14 of the pump, when the movable assembly is in the position shown in FIG. 1.
  • the mattress chamber 8 then partially extends inside the piston 4 , however that the rod 17 of the piston 16 of the hydraulic pump is coupled to the piston 4 on its face limiting the combustion chamber.
  • the piston rod 17 On the side opposite the piston 16, the piston rod 17 is extended by a coaxial rod 23 which moves outside the chamber 19 in a capacity 24 formed in a part 14b fixed to the body 14 of the pump.
  • the sealing ring 25 traversed by the rod 23 avoids any communication between the chamber 19 and the capacity 24.
  • the capacity 24 must have a variable volume.
  • an accumulator 26 communicates by a conduit 27 with the capacity 24. It is constituted by a piston 28 evolving in a cylindrical chamber and subjected to the action of a spring 29.
  • the two chambers 18 and 19 of the pump can be put in communication by a bypass device which will now be described.
  • the conduits 30 and 31 communicating respectively with the chambers 18 and 19 open into a drawer distributor 32.
  • the groove 33 of the drawer 32 ensures the communication of the conduits 30 and 31.
  • the drawer 32 is however coupled to a piston 34 subjected to the action of a spring 35 and coming to rest bearing on the body 14 of the pump by its shoulder 34a.
  • a control rod 36 capable of being coupled to a member for use, is slidably mounted in the part 14b of the pump body and allows the setting of the setting force of the spring 35.
  • a chamber 37 formed in the body of the pump and one of the walls of which is constituted by the piston 34, communicates with the capacity 24 by a conduit 38.
  • a pump for this purpose, there is first of all provided, from the supply orifice 39 connected to a fluid reservoir, a pump, called a booster pump, designated by the general reference 40 and at least a accumulator 41 (FIGS. 3 and 5) regulating the discharge pressure of this booster pump.
  • the booster pump is constituted by a piston 42 operating in a cylindrical chamber 43, one of the walls of which, essentially constituted by a plate 43a, comprises a suction valve 44 connected to the supply orifice 39.
  • discharge valves 45 allowing the communication of the chamber 43 with a chamber 46, itself connected to the supply conduits 22 via a conduit 47 ( Figure 3).
  • Bypassed on the conduit 47 is disposed the accumulator 41 comprising a piston 48 evolving in a chamber 49 and subjected to the action of a spring 50.
  • the booster pump 40 or more precisely its delivery chamber 46, is on the other hand connected by a conduit 24a, equipped with a non-return valve 24b (shown diagrammatically by a dotted line in FIG. 3), to the variable volume capacity 24, so as to compensate for any fruits from the latter.
  • a conduit 24a equipped with a non-return valve 24b (shown diagrammatically by a dotted line in FIG. 3), to the variable volume capacity 24, so as to compensate for any fruits from the latter.
  • the piston 42 of the booster pump is driven by an auxiliary motor designated by the general reference 51.
  • this motor comprises a piston 52 coupled to the piston 42 by means of a rod 53 and moving in a chamber 54 against the action of a spring 55 which is supported on a ring 56 fixed to the body of the pump.
  • the piston 52 In its rest position shown in FIG. 1, the piston 52 also bears on the body of the engine 1.
  • the chamber 54, one of the walls of which is constituted by the piston 52 is in communication via a conduit 57 with the chamber- mattress 8 of engine 1.
  • conduits 58 collect the fluid having passed through the valves 21 and are connected to a main discharge conduit 59 intended to be placed in communication with the user devices.
  • a main discharge conduit 59 intended to be placed in communication with the user devices.
  • an accumulator 60 On the conduit 59 is disposed bypass an accumulator 60, which, in the example shown, is of the membrane type.
  • FIGS. 8 and 9 Before explaining the operation of the pump which has just been described with reference to FIGS. 1 to 5, it is necessary to underline certain peculiarities of the advantageous embodiment represented in FIGS. 8 and 9. In these figures, the same references which those already used in FIGS. 1 to 7 to designate the same members. Some additional markers will however be used from the number 100.
  • FIGS. 8 and 9 essentially concern the structure of the body of the hydraulic pump 2, as well as the constitution of the booster pump 40 and of its single accumulator 41, these last two members being arranged coaxially with the rod 17 This arrangement makes it possible to reduce the size of the generator.
  • the cylinder 15 of the pump has an outside diameter smaller than that of the bore 14a of the body 14 of the pump. It has at its left end (motor side) orifices 115, so that the chamber 18 opens into the annular space 118 located between the bore 14a and the cylinder 15. However, at its end opposite to the orifices 115, the cylinder 15 comprises a portion 115a, the outside diameter of which is identical to the inside diameter of the bore 14a: the annular space 118 can thus be isolated in a sealed manner from the chamber 19. Thanks to this arrangement, the suction valves 20 and of delivery 21 corresponding to chamber 18 can be grouped in the vicinity of those corresponding to room 19.
  • This arrangement allows the left part (motor side) of the pump 2 to be released in order to place the booster pump 40 and the accumulator 41 under conditions which will be specified later.
  • the booster pump 40 visible in FIG. 8 has a substantially different constitution from that described above, while comprising the same essential members.
  • a casing 114 fixed to the motor 1 and having a central bore 114a, coaxial with the rod 17.
  • An annular plate 43a is fixed in the space between the body 14 and the casing 114. of the motor 1, the plate 43a defines an annular chamber 43 in which the piston 42 of the booster pump moves.
  • the face 152 of the piston 42 located on the side of the motor 1 closes the mattress chamber 8 and will thus constitute the piston 52 of the motor 51 of the booster pump. It can also be said that the piston 42 of the booster pump and the piston 52 of the motor 51 constitute a one-piece assembly.
  • a ring 101 limits the axial movement of the piston 42-52 under the action of the spring 55 bearing on the plate 43a.
  • the plate 43a On the side of the chamber 43, the plate 43a carries an annular suction valve 44 connected to the supply orifice 39. On the other side, the plate 43a carries an annular discharge valve 45 allowing the communication of the chamber 43 with a chamber 46, itself connected to the suction valves 20 of the pump 2 by the conduits 47 (formed in the casing 114) and 22 shown diagrammatically in FIG. 8.
  • the chamber 46 is closed by the annular piston 48 of the shock absorber 41, this piston 48 being subjected to the action of the spring 50 bearing on the body 14 of the pump 2.
  • the annular arrangement of the booster pump 40 and its accumulator 41 makes it possible to remove many dead spaces, such as the conduit 57 and the chamber 54 of the engine. 51, as well as the chamber 49 of the damper 41 which is here merged with the chamber 46.
  • the conduits 47 and 22 may be shorter and less numerous than in the embodiment according to FIGS. 1 to 5.
  • conduit 24a and its valve 24b the roles of which have been explained above, will be provided in the casing 114 and then in the body 14 of the pump, although they have been shown diagrammatically in punctuated line on the figure 8.
  • the operation of the pump 2 is then carried out in the following manner, whatever the embodiment.
  • the "moving stroke” of the mobile assembly piston 4-rod 17-piston 16-rod 23 will denote its displacement under the effect of an explosion in the combustion chamber 3. In FIG. 1 and in FIG. 8, this displacement is carried out from left to right.
  • the "return race” will designate the movement in the opposite direction of the moving equipment.
  • the pump 2 provides its maximum flow rate, that is to say that the control rod 36 is in the position shown in the drawings, corresponding to the minimum setting force of the spring 35.
  • the minimum pressure in the capacity 24 is sufficient to push the piston 34 completely against the action of the spring 35, the shoulder 34a then coming to bear on the stop 14c.
  • the drawer 32 is thus kept in its closed position of the communication between the conduits 30 and 31.
  • the volume of the chamber 18 increases and fills with fluid coming in particular from the accumulator or accumulators 41 through the suction valve or valves 20.
  • the volume of the chamber 19 decreases and the fluid which it contains is discharged, through the corresponding valve 21, towards the accumulator 60 and from there towards the evacuation duct 59.
  • FIG. 6 shows the graphical representation of instantaneous flow rate Q of pump 2 (that is to say of the quantity of liquid discharged per unit of time) as a function of time. Thanks to the presence of the accumulator 60, the average flow represented by the line A in dotted lines is almost constant despite the significant variations in instantaneous flow, on the one hand during a race of the moving assembly, on the other hand share between the "outward race” and the "return race".
  • the pressure in capacity 24 is close to the minimum pressure.
  • the spring 35 therefore maintains the piston 34 and the slide 32 in the position shown in FIG. 1 or in FIG. 8, thus allowing communication between the two chambers 18 and 19.
  • the fluid discharged from the chamber 19 passes directly into the chamber 18 via the conduits 31 and 30.
  • the installed flow rate delivered by the pump is then zero as seen in FIG. 7.
  • the average partial flow rate B (FIG. 7) of the pump can be adjusted to any desired value, by adjusting the compression of the spring 35 by the control rod 36. If the force of the spring 35 is sufficient to maintain permanently, whatever the pressure in the capacity 24, the slide 32 in the position shown in FIG. 1, the average flow rate of the pump will be zero. The proper regulation of the motor 1 then acts on the latter to maintain its power at a minimum value, no loss of energy being thus recorded.
  • the accumulator 60 is dimensioned in such a way that its capacity makes it possible to absorb and then restore the fluid discharged from the chambers 18 and 19, whatever the variations in the installed flow rate, due to the operation as well at maximum average flow than at partial average flow.
  • the fluid contained in the chamber 42 is then discharged through the valves 45 towards the chamber 46 and, from there, towards the accumulator or accumulators 41 and the supply valves 20 by the conduits 47 and 22.
  • the valves 20 do not open that to the extent that the chambers 18 and 19 need to be filled, which will not be the case during the phases of bringing these two chambers into communication with the drawer 32.
  • the chamber 43 is filled through the valve 44 as a result of the vacuum created by the return of the piston 42, to the position shown in FIG. 1 or in FIG. 8, under the action of the spring 55.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Servomotors (AREA)
  • Nozzles (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lubricants (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Braking Systems And Boosters (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Claims (13)

1. Doppelwirkende Hydraulikpumpe mit einem sich gemäß einer geradlinigen Umkehrbewegung in einem Zylinder (15) hin- und herbewegenden Kolben (16), wobei jede Kammer (18, 19) des Zylinders (15) mit einem Ansaugventil (20) und mit einem Rückflußventil (21) versehen ist, wobei der Antrieb der Stange (17) des Kolbens (16) durch ein Motororgan mit veränderbarem Hub gewährleistbar ist, dadurch gekennzeichnet, daß die Stange (17) des Kolbens (16) über den Kolben hinaus verlängert (23) ist und sich außerhalb des Zylinders (15) in einem im Gehäuse (14, 14a) der Pumpe vergesehenen Raum (24) mit variablem Volumen hin- und herbewegt, welcher mit dem Steuerorgan (34, 36) einer die beiden Kammern (18, 19) des Zylinders (15) miteinander verbindenden Umgehungseinrichtung (32) kommuniziert.
2. Hydraulikpumpe nach Anspruch 1, dadurch gekennzeichnet, daß der Raum (24) mit variablem Volumen mit einem Fluidspeicher (26) kommuniziert.
3. Hydraulikpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Umgehungseinrichtung durch einen Schieber (32) gebildet ist, der vor zwei, jeweils mit einer der Kammer (18, 19) des Zylinders (15) kommunizierenden Öffnungen (30, 31) hin- und herbewegbar ist und gegen die Kraft einer einstellbaren Feder (35) der Wirkung des im Raum (24) mit variablem Volumen herrschenden Drucks unterworfen ist.
4. Hydraulikpumpe nach Anspruch 3, dadurch gekennzeichnet, daß die Steuerung der Durchflußmenge der Pumpe an das Regelorgan (36) der Feder (35) des Schiebers (32) angekuppelt ist und zwecks Verringerung der Durchflußmenge der Pumpe im Sinne einer Erhöhung der Federkraft wirkt.
5. Hydraulikpumpe nach Anspruch 1, dadurch gekennzeichnet, daß ein von der Pumpe beaufschlagter Fluidspeicher (60) an einer Rückflußleitung (59) stromabwärts von den Rückflußklappen (21) jeder Kammer (18, 19) angeordnet ist.
6. Hydraulikpumpe nach Anspruch 1, dadurch gekennzeichnet, daß mindestens ein Fluidakkumulator (41) an den Zuführungsleitungen (47, 22) jeder Kammer (18, 19) stromaufwärts von der entsprechenden Ansaugklappe (20) jeder Kammer angeordnet ist.
7. Hydraulikpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß eine durch einen Hilfsmotor (51) angetriebene und in einen Fluidbehälter saugende Vorspeisungspumpe (40) über ihre Rückfluß- . kammer (46) einerseits mit der Zuführung jeder Kammer (18, 19) stromaufwärts ihrer Ansaugklappe (20) und des entsprechenden Akkumulators (41), anderseits mit dem Raum mit variablem Volumen (24) verbunden ist.
8. Hydraulikpumpe nach Anspruch 7, dadurch gekennzeichnet, daß die Vorspeisungspumpe (40) im wesentlichen einen Kolben (42) umfaßt, der in einer zylindrischen Kammer (43) beweglich ist, von der die der Seite des Kolbens (42) gegenüberliegende Seite mit einer mit dem Behälter kommunizierenden Ansaugklappe (44) und mit einer mit dem Rückflußleitungssystem (47) kommunizierenden Rückflußklappe (45) ausgestattet ist.
9. Hydraulikpumpe nach Anspruch 8, dadurch gekennzeichnet, daß der Kolben (42) und die Kammer (43) der Vorspeisungspumpe (40) durch ringförmige, im Inneren eines Kastens (114) um einen zylindrischen, vorzugsweise koaxial zum Pumpenkörper verlaufenden Teil des Körpers (14) der Pumpe angeordnete Elemente gebildet ist.
10. Generator für unter Druck befindliches Hydraulikfluid mit einer Hydraulikpumpe nach einem der Ansprüch 1 bis 9, welcher einen Verbrennungsmotor (1) umfaßt, dessen Kolben (4) an den Kolben (16) der Hydraulikpumpe (2) angekuppelt ist, dadurch gekennzeichnet, daß der Motor (1) des an sich bekannten Typs mit freifliegendem Kolben ist, und daß der Kolben (16) der Hydraulikpumpe (2) koaxial zum Kolben (4) des Motors angeordnet ist, um mit diesem ein bewegliches, einstückiges Gerät ohne mechanische Verbindung nach außen zu bilden.
11. Generator nach Anspruch 10, dadurch gekennzeichnet, daß sich der Zylinder (15) der Hydraulikpumpe zumindest zum Teil in das Innere des hohlen Zylinders (4) des Motors erstreckt, und daß die Stange des Kolbens (17) der Hydraulikpumpe am Motorkolben an der die Verbrennungskammer umgrenzenden Wand desselben angekuppelt ist.
12. Generator nach einem der Ansprüche 10 und 11, dadurch gekennzeichnet, daß der Kolben (42) der Vorspeisungspumpe (40) an einen Hilfsmotor (51) mit einfachwirkendem Kolben angekuppelt ist, wobei der Kolben (52) des Hilfsmotors der Wirkung der Druckluft der Dämpfungskammer (8) des Motors (1) unterworfen ist.
13. Generator nach Anspruch 12, dadurch gekennzeichnet, daß der Kolben (52) des Hilfsmotors (51) der Kraft einer Feder (55) unterworfen ist, welche ihn in Ruhestellung zu bringen trachtet.
EP82400513A 1981-03-23 1982-03-22 Hydraulische Pumpe mit variablem Hub und Druckflüssigkeitserzeuger, der eine solche Pumpe verwendet Expired EP0061405B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82400513T ATE13932T1 (de) 1981-03-23 1982-03-22 Hydraulische pumpe mit variablem hub und druckfluessigkeitserzeuger, der eine solche pumpe verwendet.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8105770 1981-03-23
FR8105770A FR2502256A1 (fr) 1981-03-23 1981-03-23 Pompe hydraulique a piston a course variable et generateur faisant application de la pompe

Publications (2)

Publication Number Publication Date
EP0061405A1 EP0061405A1 (de) 1982-09-29
EP0061405B1 true EP0061405B1 (de) 1985-06-19

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EP82400513A Expired EP0061405B1 (de) 1981-03-23 1982-03-22 Hydraulische Pumpe mit variablem Hub und Druckflüssigkeitserzeuger, der eine solche Pumpe verwendet

Country Status (9)

Country Link
US (1) US4461613A (de)
EP (1) EP0061405B1 (de)
JP (1) JPS57210179A (de)
AT (1) ATE13932T1 (de)
BR (1) BR8201628A (de)
CA (1) CA1186947A (de)
DE (1) DE3264219D1 (de)
ES (1) ES8400802A1 (de)
FR (1) FR2502256A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5622142A (en) * 1995-08-08 1997-04-22 Strieber; Louis C. Rotating piston engine with variable effective compression stroke

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE420266C (de) * 1925-10-21 Rudolf Ise Zweitaktmotorpumpe
US689272A (en) * 1899-06-29 1901-12-17 Armand Bailly Blowing-engine.
US1001295A (en) * 1909-08-10 1911-08-22 Albert E Moorhead Automatic by-pass for pumps.
US2387603A (en) * 1940-10-22 1945-10-23 Neugebauer Franz Free piston motor compressor
US2667300A (en) * 1949-06-14 1954-01-26 Participations Soc Et Free piston machine the compressor portion of which includes at least two stages
US3012509A (en) * 1957-03-22 1961-12-12 Mercier Jean Differential pumps
US3065703A (en) * 1960-11-03 1962-11-27 Int Harvester Co Free piston engine pump
NL160632C (nl) * 1968-10-08 1979-11-15 Ir Theodorus Gerhardus Potma Vrije-zuigerpompinstallatie.
GB1332799A (en) * 1970-10-12 1973-10-03 Riekkinen As Hydraulic power unit including a hydraulic pump operated by a free piston internal combustion engine
BE791450A (fr) * 1971-11-18 1973-03-16 Fitzgerald William M B Generateur de puissance
US3995974A (en) * 1974-09-18 1976-12-07 Herron Allen R Internal combustion assisted hydraulic engine
DE2648958C2 (de) * 1976-10-28 1983-02-17 Karl-Heinz 8722 Sennfeld Fengler Hydraulische Kolbenpumpe mit Antrieb durch Freikolben-Verbrennungskraftmaschine
GB1540870A (en) * 1976-12-30 1979-02-14 Dewandre Co Ltd C Hydraulic pumps
US4307999A (en) * 1979-06-25 1981-12-29 Pneumo Corporation Free piston engine pump including variable energy rate and acceleration-deceleration controls
US4382748A (en) * 1980-11-03 1983-05-10 Pneumo Corporation Opposed piston type free piston engine pump unit

Also Published As

Publication number Publication date
BR8201628A (pt) 1983-02-16
ES510632A0 (es) 1983-11-01
ES8400802A1 (es) 1983-11-01
ATE13932T1 (de) 1985-07-15
EP0061405A1 (de) 1982-09-29
JPS57210179A (en) 1982-12-23
FR2502256B1 (de) 1984-07-13
US4461613A (en) 1984-07-24
CA1186947A (en) 1985-05-14
DE3264219D1 (en) 1985-07-25
FR2502256A1 (fr) 1982-09-24

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