WO1988000640A1 - Moteur a pistons rotatifs - Google Patents

Moteur a pistons rotatifs Download PDF

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Publication number
WO1988000640A1
WO1988000640A1 PCT/EP1987/000376 EP8700376W WO8800640A1 WO 1988000640 A1 WO1988000640 A1 WO 1988000640A1 EP 8700376 W EP8700376 W EP 8700376W WO 8800640 A1 WO8800640 A1 WO 8800640A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
housing
rotary piston
machine according
piston machine
Prior art date
Application number
PCT/EP1987/000376
Other languages
German (de)
English (en)
Inventor
Peter B. Kathmann
Original Assignee
Rmc Rotary-Motor Co. Ag
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
Priority claimed from DE19863623490 external-priority patent/DE3623490A1/de
Priority claimed from DE19863623489 external-priority patent/DE3623489A1/de
Application filed by Rmc Rotary-Motor Co. Ag filed Critical Rmc Rotary-Motor Co. Ag
Publication of WO1988000640A1 publication Critical patent/WO1988000640A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B31/00—Component parts, details, or accessories not provided for in, or of interest apart from, other groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B57/00—Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
    • F02B57/08—Engines with star-shaped cylinder arrangements
    • 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
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/54—Other sealings for rotating shafts
    • F16J15/545—Other sealings for rotating shafts submitted to unbalanced pressure in circumference; seals for oscillating actuator

Definitions

  • the present invention relates to a rotary piston machine
  • a housing which forms an essentially cylindrical rotor chamber which has two end walls and an annular peripheral wall,
  • a disk-shaped rotor which is arranged in the rotor chamber so as to be rotatable about an axis
  • pistons which are each slidably mounted in an essentially radially extending recess of the rotor and are sealed with respect to the latter and which adjoin an operating area with an end face,
  • a guide device for controlling the radial position of the pistons in the rotor when it rotates with respect to the housing
  • Fluid channels for supplying and discharging fluid to and from the work area.
  • Such a rotary piston machine is known, for example, from FIGS. 8 to 15 of EP-A 48 415.
  • the pistons or “power parts” mounted radially displaceably in the disk-shaped rotor are positively guided with respect to the rotor chamber by a guide device which has an annular groove in each end wall of the rotor chamber.
  • the rotor is sealed with respect to the inner wall of the housing by a relatively complicated sealing arrangement.
  • the guide device on the one hand contains an annular one that surrounds the rotor Guide surface and on the other hand a removal member at the radially outer end of each piston, which engages the guide surface, and each piston adjoins with its radially inner end face on its own working space, which is located inside the rotor.
  • the sealing device ensures a secure, low-wear and high pressure-resistant seal between the mutually rotating surfaces of the rotor and the housing, at which the fluid lines or channels open.
  • FIG. 1 shows an axial section of a rotary piston machine according to an exemplary embodiment of the invention, here the control device for the pistons is shown in more detail;
  • Fig. 2 shows a cross section in a plane A-B of Fig. 1;
  • FIG. 3 shows a simplified axial section of a rotary piston machine according to a further embodiment of the invention; here the sealing device is shown in more detail;
  • FIG. 4A shows an axial section of two sealing parts of the rotary piston machine according to FIG. Fig. 1;
  • FIG. 4B is a view of the rotor-side sealing part in the direction of arrows B-B of FIG. 4A,
  • 4C is a view of the seal side of the housing in the direction of arrows C-C of FIG. 4A,
  • FIGS. 4A, 4B and 4C are views corresponding to FIGS. 4A, 4B and 4C of a modified dressing device; 6 shows a partial view of a third exemplary embodiment of the invention with a preferred sealing arrangement;
  • Fig. 7 is an end view of a rotor-side sealing part in a plane A-B of Fig. 6;
  • Fig. 8 is an end view of a housing-side sealing part in a plane C-D of Fig. 6 and
  • the housing (10) forms an essentially cylindrical rotor chamber (12) in which an essentially disk-shaped rotor (14) is located.
  • the rotor (14) is wedged onto one end of a shaft (18) by means of a wedge (16) and fixed by means of a screw (20) screwed into the relevant front end of the shaft.
  • the shaft (18 ) is supported on one side in the housing part (10a), for. B. by rolling bearings (22).
  • the rotor has at least one, generally a plurality of radial recesses (24) with a circular cross section, in each of which a piston (26) is axially displaceably mounted.
  • the pistons (26) are each sealed by piston rings (28) with respect to the wall of the associated recess.
  • an odd number of pistons is preferred, e.g. B. five, in the drawing four pistons are shown to show the two dead centers of the pistons and the connection of the associated work spaces with the fluid channels serving for supplying or discharging working fluid.
  • the pistons (16 ) each border with their own end face (30) on their own working space (32), which is formed by a radially inner part of the recess (24) in question.
  • Each working space (32) is connected to the through an essentially axial channel (34)
  • Cover part (10b) facing end face of the rotor in connection.
  • two fluid channels (36, 38 ) for supplying or discharging a fluid to or from the work spaces are formed.
  • the fluid channels (36, 38) open on the side facing the rotor end face (40) of the cover part (10b) at the same radial height as the circular mouths of the channels (34) and put in bogenförmi ⁇ ge depressions or recesses (36a) or (38a) in the end face (40).
  • the distance between the ends of the recesses (36a, 38a) is equal to the diameter of the circular mouths of the channels (34).
  • a sealing device (42) is located between the mutually facing end faces of the rotor (14) and the cover part (10b). The sealing of the rotor with respect to the housing is discussed in more detail with reference to FIGS. 3 to 5.
  • a rotary lobe machine of the type described above can work as a pump or motor.
  • the pistons (26) perform a lifting movement when the rotor (14) rotates with respect to the housing (10).
  • a guide device is provided which, in the case of the present rotary piston machine, has an annular guide surface (44) which eccentrically surrounds the rotor (14) and a respective removal member (46) which is attached to the radially outer end of each piston (26) is contains.
  • the guide surface is formed by a steel ring (48) with a hardened inner surface, which is fastened in an annular insert (50) by a snap ring (52).
  • the guide surface (44) could also be arranged on the peripheral wall of the rotor chamber (12), which would then have to be eccentric to the axis of the shaft (18).
  • the removal members (46) are formed in the illustrated embodiment by rollers (54), each of which is formed by a roller bearing, eg. B. a needle bearing, are mounted on a pin (56) which passes through the respective piston at its radially outer end in the axial direction.
  • the insert (50) has an inwardly projecting cross section on the side facing away from the cover part (10b) L-shaped part (50a) with an inner leg (50b) projecting towards the rotor, which cooperates with a roller (62) which sits on the end of each bolt (56) facing away from the cover part (10b).
  • the leg (50b) forms a remindholring which moves together with the roller (62) the piston concerned forcibly outwardly if the centrifugal force is not sufficient, which 'will, however, be at the usual operating speeds generally the case.
  • the rollers (62) are each guided radially displaceably in a radial slot ( 60 ) of the rotor, so that rotation of the rollers (54 ) is prevented.
  • the insert (50) can be moved diametrically with respect to the rotor (14) in order to be able to adjust the stroke of the pistons.
  • the insert has for this purpose two mutually opposite flat surfaces (64, 66) which cooperate with corresponding flat surfaces of the housing running along chords of the rotor chamber cross section.
  • the displacement takes place by means of an adjusting screw (68) which is screwed into a radial threaded bore in the peripheral wall of the housing main part (10a) and with its inner end, for. B. by a snap ring (70), but rotatably but axially immovably attached to the insert (50).
  • the guide surface (44) is eccentric with respect to the axis of rotation of the rotor, so that the pistons execute a stroke cycle with one revolution of the rotor with respect to the guide surface (44) fixed to the housing, as is the case with the four different positions of the pistons in FIG. 2 can be seen ( left: bottom dead center, right: top dead center).
  • the channels (34) of the working spaces of the pistons alternately come into connection with the arcuate recesses (36a, 38a) of the fluid channels (36) and (38).
  • the rotary lobe machine can be used as a pump or as a fluid motor, e.g. B. hydraulic motor work.
  • the eccentricity of the guide surface (48) with respect to the rotor and thus the stroke of the pistons can be adjusted, which is particularly important when the rotary piston machine is operating as a pump for changing the delivery rate at a high speed.
  • the insert (50) beyond the position concentric to the rotor (zero delivery capacity) a reversal of the conveying direction is possible.
  • the guide device and the return device should be designed in such a way that they cannot simultaneously act on a piston.
  • the rollers (54) and (62) should not be able to act on the associated guide surfaces at the same time.
  • the embodiment described above can of course be modified in a variety of ways without going beyond the scope of the invention.
  • the hardened ring forming the guide surface can be attached to the annular peripheral wall of the rotor chamber which is then eccentric with respect to the rotor. If the rotary piston machine is only intended for weaker loads and / or short operating times, the housing wall can be used directly as a guide surface and / or the outer ends of the pistons themselves can be designed as removal members (cams).
  • the pistons can also have a rectangular cross-section, that is to say they can be designed in the manner of a slide, and two or more pistons can also be arranged side by side in the rotor in the axial direction.
  • the rotary piston machine shown in FIGS. 3 and 4A to 4C contains similar to the rotary piston machine according to FIG. 1 and 2 a Housing (110) with a main part (110a) and a cover part (110b) which form a substantially cylindrical rotor chamber (112) in which a rotor (114) is rotatably mounted.
  • the rotor (114) is wedged onto one end of a shaft (118) and fixed to it by means of a screw (120).
  • the shaft is mounted in roller bearings (122), for example tapered roller bearings.
  • the rotor (114) has a preferably odd number of essentially radial bores or recesses (124 ) , in each of which a lifting piston (126) is slidably mounted.
  • the pistons are sealed by piston rings (128) with respect to the associated recess (124 ) and each border with their inner end face ( 130) on their own working space (132), which is essentially formed by the radially inner end of the relevant recess (124) becomes.
  • the working spaces are each connected to a fluid channel (134) which opens into a region of the one end face (140 in FIG. 3, facing away from the shaft (118)) of the rotor that is relatively close to the axis of rotation of the rotor.
  • the pistons (126) are coupled to a guide device, not shown in FIG. 3, which can be and can be designed as described with reference to FIGS. 1 and 2, which causes the pistons to rotate when the rotor rotates Carry out a cyclical lifting movement with respect to the housing.
  • the rotary piston machine is shown in the drawings as if it contained four pistons.
  • Fig. 3 two diametrically opposed pistons can be seen, of which the right piston is at the top dead center and the left piston at the bottom dead center of their stroke movement.
  • an odd number of pistons is generally provided and the pistons would have their dead center in the positions of the inlet and outlet lines shown in FIGS. 4 and 5 in positions which are offset by 90 from FIG. 3 .
  • the pistons are connected to a leakage channel system (147), which is not to be discussed in detail since it does not form part of the present invention.
  • the cover part (110b) of the housing is penetrated by two fluid lines (136, 138).
  • the embodiment of the invention shown in the drawing is provided as a boiler feed water pump which draws boiler feed water through the fluid line (136) at a pressure of 0.2 to 0.3 bar and at an outlet pressure of 30 bar from the outlet fluid line (138) lets out.
  • the fluid lines (136, 138) open at an end face of the rotor chamber opposite the rotor end face (140) and form there arc-shaped recesses (136a and 138a), the azimuthal ends of which have a distance equal to the diameter of the circular mouths of the fluid channels (134) 4B shows.
  • a sealing arrangement which contains a rotor-side part (172) and a statoi— or housing-side part (174).
  • a Mate ⁇ ' alp pairing is used, which ensures a perfect, low-wear sealing of the sliding surfaces under the respective operating conditions.
  • Such material pairings are known from plain bearing technology.
  • the rotor-side sealing part (172) is a ring which is fastened to the rotor body by screws (190) and has axial bores which form the outer part of the fluid channels (134) which opens at the end face (140).
  • the annular part (172) is sealed off from the rotor body by an 0-ring (192) and by 0-rings (194) which surround the channels (134).
  • the housing-side part (174) is guided axially displaceably in the cover part (110b) of the housing by bolts (196) and by springs (198) pressed against the rotor-side part (172).
  • the upper part of the sealing part (174) on the rotor side (ie facing the rotor) in FIG. 3 is concentric to the rotor axis and forms the arcuate recesses (136a and 138a) which are shown in an end view in FIG. 4C.
  • the rotor-side end face of the sealing part (174) slides tightly on the housing-side end face of the sealing part (172).
  • the arcuate recess (136a) communicates with the fluid line (136).
  • a piece (138b) of the outlet line (138) leading to the rotor axis adjoins the arcuate recess (138a).
  • the piece (138b) then merges into a line piece (138c) which runs obliquely outwards and in the direction of the arcuate recess (138a).
  • the oblique piece (138c) is then followed by an axially extending piece ( 138c ), which is eccentric to the rotor axis, of the fluid line (138) serving as an outlet.
  • the eccentric piece of the sealing part on the housing side is sealed by a 0-ring (200) with respect to the cover part (110b) of the housing.
  • the inclined course of the piece (138c) of the outlet line ensures that the pressurized working fluid cannot exert a tilting moment on the housing-side sealing part (174), so that unimpeded axial sliding of the housing-side sealing arrow (174) in the housing ensures a perfect seal and low-wear operation is guaranteed.
  • the modified sealing device shown in FIGS. 5A, 5B and 5C differs from that according to FIGS. 4A to 4C essentially only in that it contains a sealing part (274) on the housing side which only has an opening 238a for the pressure-side outlet line (138 ), while the housing-side part of the suction line (136) is delimited by a recessed, laterally open recess (236a).
  • a correspondingly larger flow cross section is therefore available for the suction line, and the part (274) can also be manufactured more easily and inexpensively.
  • FIGS. 6 to 9 A further preferred embodiment of a sealing arrangement for a rotary piston machine of the present type is shown in FIGS. 6 to 9 shown. Only the parts that are important for understanding are shown, otherwise the rotary piston machine can be constructed essentially as it was explained with reference to FIGS. 1 and 3. 6 have been used for corresponding parts, which are 200 times larger than the corresponding reference numbers in FIG. 3.
  • the housing-side sealing part (174) (FIG. 3) in the sealing arrangement according to FIG. 6 is constructed in several parts and consists of three parts (374a, 374b) and (374c), which are connected by a screw (374d).
  • the parts (274a) and (274b) are sealed with respect to one another by an O-ring (374e) which sits in a groove in the part (374a).
  • the parts (374b) and (374c) are sealed off from one another by an O-ring (374r) which sits between flange-like projections of the parts (374b) and (374c), as can be clearly seen from FIG. 6.
  • the part (374b) consists of a particularly wear-resistant material, e.g. B. a hard metal such as tungsten carbide or silicon carbide. Since the part (374b) has a relatively simple shape, it can also be made of such materials economical hotels with par ti g by sintering presses, Funkenerosio ⁇ sfrasen or similar processing methods produce.
  • the rotor-side sealing part (372) can also consist of a particularly wear-resistant material, whereby, of course, it is important to ensure that the material of the part ( 374b ) is properly paired.
  • the sealing part (372) also has a flange-like extension at its inner opening and is fastened to the rotor by means of a screw (320) on the rotor by means of a part (314 ) which has a complementary, flange-like end.
  • the rotor-side sealing part (372) is fixed to the rotor by a driver pin (351).
  • the lengthening and the shortening can be 15, for example, so that the openings (334) in the rotor-side sealing part (372) only close, for example, at 195 (based on 0 on the left side of the diameter).
  • compressible media the conditions may also be reversed, that is to say that the mouth of the inlet opening is shortened and the mouth of the outlet opening is lengthened.
  • lubrication pockets S can be provided at places where there is no pressure difference, which, for example, consist of a 0.5 mm deep recess and are shown in broken lines in FIGS. 8 and 9 .
  • the parts (372, 374) subject to wear can be easily replaced. If you arrange the flange-like protrusions in the middle of the thickness dimension, you can turn the Te le and use the back surface as a sealing surface when the front surface is worn.
  • the sliding parts (372, 374) both consist of hard metal, such as SiC, different degrees of hardness are expediently used, the rotor-side part (372) preferably being produced from a softer type of the material in question than the stator-side sealing part (374b) .
  • both fluid lines contain an inclined piece
  • the lines can be guided coaxially or with nested or interlocking parts in order to achieve the required symmetry with regard to the compressive forces and to avoid tilting moments about a tilting axis running transverse to the rotor axis.
  • the stationary sealing part can also be an integral part of the rotor or housing, which forms the sealing surface in question.
  • the pistons can also have a rectangular cross section and two or more pistons can also be arranged axially next to one another in the rotor.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Un moteur à pistons rotatifs comprend un carter (110) ayant une chambre de rotor (112) dans laquelle est rotativement monté un rotor (114) en forme de disque. Le rotor contient des pistons alternatifs (126) radialement mobiles dont la surface frontale est adjacente à une chambre de travail correspondante (132) reliée à un canal de fluide (134) qui s'ouvre dans une région, à proximité de l'axe, de la surface frontale (140) du rotor dans un sens opposé à l'arbre. Le carter comprend des conduites de fluide (136, 138) pour amener du fluide de travail aux chambres de travail (132) et pour l'en évacuer. Afin d'assurer une liaison étanche entre les canaux de fluide (134) du carter avec les conduites de fluide du rotor, un dispositif d'étanchéité comprend une partie d'étanchéité (172) faisant face au rotor et une partie d'étanchéité (174) faisant face au carter qui forment deux surfaces d'étanchéité adjacentes. Une conduite de fluide traverse la partie d'étanchéité (174) faisant face au carter et axialement mobile en suivant un trajet incliné allant d'une pièce concentrique par rapport à l'axe du rotor à une pièce excentrique par rapport à l'axe du rotor, de sorte que le fluide de travail sous pression d'évacuation n'exerce pas de couple de renversement sur cette partie d'étanchéité.
PCT/EP1987/000376 1986-07-11 1987-07-13 Moteur a pistons rotatifs WO1988000640A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19863623490 DE3623490A1 (de) 1986-07-11 1986-07-11 Abdichtvorrichtung fuer eine drehkolbenmaschine
DEP3623489.3 1986-07-11
DE19863623489 DE3623489A1 (de) 1986-07-11 1986-07-11 Drehkolbenmaschine
DEP3623490.7 1986-07-11

Publications (1)

Publication Number Publication Date
WO1988000640A1 true WO1988000640A1 (fr) 1988-01-28

Family

ID=25845510

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1987/000376 WO1988000640A1 (fr) 1986-07-11 1987-07-13 Moteur a pistons rotatifs

Country Status (3)

Country Link
EP (1) EP0273956A1 (fr)
AU (1) AU7696887A (fr)
WO (1) WO1988000640A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR563834A (fr) * 1923-03-15 1923-12-14 Pompe polycylindrique
FR876485A (fr) * 1941-06-27 1942-11-06 Moteur rotatif à fluide élastique ou non élastique utilisable également comme pompe ou compresseur
US2427224A (en) * 1944-08-03 1947-09-09 James E Morton Rotary hydraulic pump
US2827859A (en) * 1954-07-01 1958-03-25 Bliss E W Co Hydraulic pump
US3056357A (en) * 1958-12-01 1962-10-02 Gen Motors Corp Radial ball piston pump
FR1319986A (fr) * 1962-04-20 1963-03-01 Angus George Co Ltd Perfectionnement aux pompes et moteurs hydrauliques
FR2071218A5 (en) * 1969-12-22 1971-09-17 Swolkien Ladislas Air refrigerator - without compressor-pressure reducer
DE2019549A1 (de) * 1970-04-23 1971-11-11 Lucas Industries Ltd Radial-Kolbenpumpe oder -motor
FR2292854A1 (fr) * 1974-11-29 1976-06-25 Rexroth Sigma Perfectionnements apportes aux machines a fluide a pistons radiaux
FR2367196A1 (fr) * 1976-10-07 1978-05-05 Acf Ind Inc Circuit d'alimentation en carburant a pompe rotative doseuse pour moteur a combustion interne

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR563834A (fr) * 1923-03-15 1923-12-14 Pompe polycylindrique
FR876485A (fr) * 1941-06-27 1942-11-06 Moteur rotatif à fluide élastique ou non élastique utilisable également comme pompe ou compresseur
US2427224A (en) * 1944-08-03 1947-09-09 James E Morton Rotary hydraulic pump
US2827859A (en) * 1954-07-01 1958-03-25 Bliss E W Co Hydraulic pump
US3056357A (en) * 1958-12-01 1962-10-02 Gen Motors Corp Radial ball piston pump
FR1319986A (fr) * 1962-04-20 1963-03-01 Angus George Co Ltd Perfectionnement aux pompes et moteurs hydrauliques
FR2071218A5 (en) * 1969-12-22 1971-09-17 Swolkien Ladislas Air refrigerator - without compressor-pressure reducer
DE2019549A1 (de) * 1970-04-23 1971-11-11 Lucas Industries Ltd Radial-Kolbenpumpe oder -motor
FR2292854A1 (fr) * 1974-11-29 1976-06-25 Rexroth Sigma Perfectionnements apportes aux machines a fluide a pistons radiaux
FR2367196A1 (fr) * 1976-10-07 1978-05-05 Acf Ind Inc Circuit d'alimentation en carburant a pompe rotative doseuse pour moteur a combustion interne

Also Published As

Publication number Publication date
EP0273956A1 (fr) 1988-07-13
AU7696887A (en) 1988-02-10

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