EP0666418B1 - Pompe à piston - Google Patents

Pompe à piston Download PDF

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Publication number
EP0666418B1
EP0666418B1 EP95100277A EP95100277A EP0666418B1 EP 0666418 B1 EP0666418 B1 EP 0666418B1 EP 95100277 A EP95100277 A EP 95100277A EP 95100277 A EP95100277 A EP 95100277A EP 0666418 B1 EP0666418 B1 EP 0666418B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
piston
spring
piston pump
recesses
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
EP95100277A
Other languages
German (de)
English (en)
Other versions
EP0666418A1 (fr
Inventor
Edgar Ing. Grad. Schmitt
Harald Dipl.-Ing. Ott
Barbara Dipl.-Ing. Schwind-Grellmann
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Priority claimed from DE4427612A external-priority patent/DE4427612A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0666418A1 publication Critical patent/EP0666418A1/fr
Application granted granted Critical
Publication of EP0666418B1 publication Critical patent/EP0666418B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/40—Heat treatment
    • F05B2230/41—Hardening; Annealing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to a reciprocating pump according to the type of the main claim.
  • German published patent application 22 43 138 discloses a reciprocating piston pump with a housing, with two pistons arranged displaceably in the housing opposite one another, with an eccentric between the pistons, with transverse bores arranged in ends of the pistons pointing to the eccentric, and with an im made of spring steel wire essentially semicircular bow spring, the ends of which engage in the transverse bores of the piston ends and press these piston ends against the eccentric.
  • the bow spring is inexpensive to manufacture, but it is very difficult to align and keep the cross holes substantially parallel to each other so that the ends of the bow spring can be inserted. This may be difficult because an eccentric chamber located in the housing is only open on one side, for example.
  • the bow spring ends are to be secured against migration out of the transverse bores, which could be done, for example, by bending their ends after being pushed through the transverse bores.
  • a groove is made in the housing, starting from the eccentric chamber, into which the bow spring is immersed. If such a reciprocating pump is to be light and therefore the housing is made of aluminum, it cannot be ruled out that aluminum is torn off from the housing and the reciprocating pump becomes dirty and, as a result, may cause malfunctions over time.
  • a further reciprocating piston pump is known with a housing which has an eccentric space, with pistons arranged opposite one another relative to an eccentric, on the ends of which pointing towards the eccentric, annular grooves are arranged, into the fork-shaped ends of a bow spring immerse, the bow spring curving around the axis of the eccentric.
  • This publication does not disclose the manner in which oscillations of the bow spring about the longitudinal axis of the pistons are limited and striking of the bow spring on the housing could be avoided.
  • the reciprocating pump according to the invention with the characterizing features of claim 1 has the advantages that after an easily carried out assembly of the bow spring ends on the piston and after the installation of the stop washer in the housing, pendulum movements of the bow spring about the longitudinal axes of the pistons are limited in a low-wear manner.
  • the characterizing features of claim 2 result in a stop disk which is pre-combined with the eccentric shaft and can be installed together with the latter in the housing for the purpose of saving assembly time on the assembly line.
  • the characterizing features of claim 3 result in an embodiment which is inexpensive to manufacture and works with little wear.
  • the characterizing features of claim 4 give the advantage that while maintaining a constructively chosen axial distance of the working side of the stop disk from the longitudinal axes of the pistons, the force or elasticity of the bow spring can be selected by varying the width of a central region of the bow spring. This makes it possible, for example, to deviate from a pre-planned spring plate thickness and a spring plate with such for producing the bow spring To use thickness as it is quickly available in the trade or from the rolling mill.
  • the characteristic features of claim 5 result in the assembly of the reciprocating pump the advantage that the bow spring with the recesses can be inserted into an eccentric chamber of the reciprocating pump and, after the snap connection with the piston necks has come about, can be swivel-aligned for the subsequent insertion of the eccentric between the pistons .
  • the characterizing features of claim 6 result in the advantage that the recesses can be formed long enough to achieve the elasticities required to produce the snap connections at the ends of the bow spring.
  • the characterizing features of claim 7 result in the advantage that the bow spring with its recesses can be inserted into the eccentric chamber of the reciprocating pump with an orientation which, for example, corresponds essentially to those pivoting orientations that occur during the operation of the reciprocating pump. This facilitates automatic assembly of the bow spring. Immediately after the bow spring has been combined with the pistons, the eccentric can be installed together with the stop disk, the stop disk possibly completing the swivel alignment.
  • the characterizing features of claim 8 give the advantage that, despite the inevitable shape error of the bow spring, a uniform transmission of the spring force to the respective piston end is possible.
  • FIG. 1 shows a section through a first embodiment of the reciprocating piston pump according to the invention transversely to the axis of an eccentric shaft in the region of an eccentric
  • FIG. 2 shows a step-like section transversely to a piston of the reciprocating piston pump according to the invention according to FIG. 1 and parallel to the axis of the eccentric shaft
  • FIG 1 in a reference plane lying in the axes of the piston and the eccentric shaft
  • FIG. 4 shows a cut for a component of this piston pump according to the invention
  • FIG. 5 shows a section through a second embodiment of the piston pump according to the invention
  • FIG. 6 shows a cut for a component according to the invention of the second exemplary embodiment
  • FIG. 7 a further component for the second exemplary embodiment.
  • the reciprocating piston pump 2 has a housing 3, two cylinders 4, 5, two pistons 6, 7, one of one Eccentric shaft 8 outgoing eccentric 9, a roller bearing 10 surrounding the eccentric 9, an essentially U-shaped bow spring 11 and a stop disk 12.
  • a roller bearing 15 which surrounds a partial length of the eccentric shaft 8 and supports it rotatably.
  • a further shaft part length 16 adjoins the roller bearing 15, which leads to a second bearing, not shown.
  • the shaft part length 16 is, for example, a component of the eccentric shaft 8 overall and preferably also a motor shaft of an electric motor (not shown), as is known, for example, from large numbers of anti-lock devices for motor vehicles, which means anti-lock devices of the so-called return type.
  • the eccentric 9 projects into the Eccentric chamber 13 into it.
  • the roller bearing 10 consists, for example, of an outer ring 18, the eccentric 9, which is hardened, and between the roller bodies 19, which are guided at a distance, for example, by means of a guide cage 20.
  • the rolling elements 19 are preferably designed as so-called bearing needles.
  • An axial stop ring 21 is next to that Rolling bearing 10 is pressed onto the eccentric 9 and ensures that the outer ring 18 and the rolling bodies 19 remain in a desired axial alignment with the eccentric 9.
  • a hub 22 from which the stop disk 12 extends radially, pressed onto the eccentric shaft 8 and thus fixed in a rotationally fixed manner relative to the latter.
  • the cylinders 4 and 5 are coaxial and aligned transversely to the eccentric shaft 8 and installed in the housing 3 in a sealed manner. Both cylinders 4 and 5 end at the eccentric chamber 13.
  • the pistons 6 and 7 are sealed and displaceably arranged in them. Aligned with the eccentric 9 or the outer ring 18 rotatably mounted around it, the pistons 6 and 7 have piston ends 23 and 24. In addition to the piston ends 23 and 24, annular grooves 25 and 26 are machined into the pistons 6 and 7, so that, for example, cylindrical piston necks 27 and 28 remain between the pistons 6 and 7 and the piston ends 23 and 24, respectively.
  • the bow spring 11 is produced by bending an essentially strip-like cut part 29 shown in FIG. 4.
  • the cut part 29 consists of a spring material suitable for producing, for example, leaf springs.
  • the spring material can be a heat-treatable steel grade.
  • the cut part 29 has a central area 30, to which a first bow spring end 31 and opposite a second bow spring end 32 connect.
  • the first bow spring end 31 is fork-shaped and for this purpose has two resilient arms 33, 34 with a recess 35 in between, which extends from the central region 30 and thereby forms the resilient arms 33 and 34.
  • the arms 33 and 34 In the area of the free ends 36 and 37 of the resilient arms 33 and 34, the arms 33 and 34 have projections 38 and 39 directed towards one another.
  • the two projections 38 and 39 Adjacent to the projections 38 and 39, the recess is shaped such that it later moves the piston neck 27 with or surrounds without play.
  • the second bow spring end 32 has a resilient arm 34 with a projection 39 and a free end 37.
  • a second resilient arm 33a of the second bow spring end 32 differs from the resilient arm 33 of the first bow spring end 31 in that, starting with a projection 38a, which is arranged opposite the described projection 39, an extension 40 is formed in the extension of the resilient arm 33a.
  • the extension 40 has a free end 36a which is a greater distance from the associated projection 38a than the free end 37 of the second bow spring end 32 from its projection 39. If one speaks of fork-like bow spring ends, the extension 40 could be considered an extended one Introduce the forks.
  • the extension 40 is, for example, straight and parallel to an imaginary connecting line between the two recesses 35.
  • this imaginary boundary line lies outside the central region 30 of the cut part 29.
  • a further extension 41 extends from the central region 30 transversely to the imaginary connecting line of the recesses 35, which extends the reference edge of the first-mentioned extension 40 ends.
  • the described cutting part 29 is bent so that the bow spring 11 is formed.
  • This bending can be imagined, starting from the position of the cut part 29 in FIG. 4, in such a way that the first bow spring end 31 and the second bow spring end 32 are bent upward from the plane of illustration, the central region 30 having a concave curvature between the upstanding ones Bow spring ends 31 and 32 receives.
  • the first extension 40 is also bent in the direction of curvature of the central region 30.
  • the bow spring 11 can be found in FIG. 3.
  • the extension 40 is clearly visible above the outer ring 18 next to the piston end 24 of the piston 7.
  • FIG. 3 also clearly shows that the projections 38 and 39 over grip the piston neck 28 of the piston 7.
  • FIG. 1 shows the bow spring 11 and its extension 40 in a drawing plane folded through 90 ° with a view of the eccentric 9 and the eccentric shaft 8 behind it and therefore shown in broken lines.
  • FIG. 2 shows the piston neck 28 in cross section as well as the resilient arms 33a and 34, as they adjoin the piston neck 28 and together with their projections 38 and 39 receive the piston neck 28 between them.
  • the cylinders 4 and 5 with their pistons 6 and 7 are first installed in the housing 3. Then the bow spring 11 is moved and pressed through the bore 14 with the free ends 36, 36a and 37 substantially in advance against the piston necks 27, 28, whereby the resilient arms 33, 33a and 34 are elastic because of the projections 38, 38a and 39 are moved apart so that the projections 38 and 39 slide over the piston necks 27 and 28 and can snap together behind their centers. As a result, the piston necks 27 and 28 are engaged in the bow spring ends 31 and 32. The bow spring 11 is now pivoted into the orientation that is particularly clearly visible in FIGS. 2 and 3.
  • the eccentric shaft 8 with the conical stop rig 21 designed for this purpose can be inserted in advance between the piston ends 23 and 24, the bow spring 11 being elastically expanded.
  • the outer ring 18 With further movement of the eccentric shaft 8, the outer ring 18 finally passes between the piston ends 23 and 24, the roller bearing 15 also completely immersed in the bore 14.
  • the stop disk 12 then has its place adjacent to the two extensions 40 and 41. In FIG. 2, an equally large distance is drawn between these extensions 40 and 41 and the stop disk 12, but this is not maintained during the operation of the reciprocating pump according to the invention.
  • the eccentric 9 is preferably driven in a direction of rotation via the eccentric shaft 8 by means of the drive motor (not shown), which is identified in FIG. 1 by the direction arrow 42 drawn on the stop disk 12.
  • the drive motor not shown
  • a reference point located on the stop disk 12 moves away from the piston 7 to the free end 36a of the first extension 40 and from there finally to the opposite piston 6.
  • recesses 35a and 36a of the second embodiment of the bow spring 11a are aligned transversely to the curvature of the bow spring or to the main dimension of a cut part 29a.
  • a wider extension 40a can extend from a bow spring end 32a in the circumferential direction.
  • a central region 30a of the second exemplary embodiment can likewise have an extension 41a which points inside the reciprocating piston pump against the stop disk 12, which can be removed from the first exemplary embodiment.
  • projections 38b and 39b directed towards one another, which delimit the recesses 35a are, for example, so far apart that a piston neck 28a can be moved between the projections 38b and 39b, for example without constraints.
  • the spring clip ends 31a and 32a are not necessary to design the spring clip ends 31a and 32a in a special manner.
  • the recesses 35a are adjoined by circular contact surfaces 45 which are inclined, for example, by 45 ° relative to the reference plane of the cut part 29a.
  • the enclosed arc can, for example, essentially comprise 270 °.
  • the contact surfaces 45 which are of a hollow conical shape in this way, are formed on the respective piston 6a, starting from its piston neck 28a, in the manner of a spherical layer, with piston ends 24a.
  • the bow spring 11a When assembling the reciprocating piston pump, the bow spring 11a can be inserted with the open areas of its recesses 35a ahead and essentially parallel to the bore 14 of the eccentric chamber 13, as a result of which the recesses 35a finally receive the piston necks 6a. During insertion, the bow spring 11a can therefore have a pivoting orientation which essentially corresponds to the pivoting orientation shown in FIG. Therefore, in the next step, an axial stop ring 21 and subsequently an eccentric 9 together with an outer ring 18 can be inserted between the pistons 6a. The stop disc 12 then approaches the bow spring 11a and, if necessary, can fully align it. A special operation "swiveling the spring clip by hand or by automatic assembly machine" required in the first embodiment is not required for the second embodiment.
  • the orientations of the recesses 35 of the first embodiment can also be transferred to the second embodiment and vice versa.
  • more than the two exemplary embodiments shown can be designed by means of the individual features shown.

Claims (8)

  1. Pompe à pistons alternatifs comportant un carter, des pistons qui peuvent coulisser en étant disposés en regard l'un de l'autre dans le carter, un excentrique entre les pistons, un arbre d'excentrique qui supporte et entraîne l'excentrique, des rainures annulaires usinées dans les extrémités des pistons tournées vers l'excentrique et qui délimitent tout autour des cols de piston, et un ressort d'étrier qui est recourbé dans le sens périphérique de l'excentrique et a des extrémités de ressort d'étrier présentant des évidements qui viennent en prise dans les rainures annulaires et pressent les extrémités du piston contre l'excentrique,
    caractérisée en ce que
    du côté de l'arbre d'excentrique part un prolongement (40, 40a), sensiblement en forme de bande, d'une extrémité du ressort d'étrier, sensiblement dans son prolongement, prolongement (40, 40a) qui se trouve à coté d'une rondelle de butée (12) associée et orientée dans ce cas perpendiculairement à l'arbre d'excentrique (8), rondelle de butée (12) qui est réalisée en une matière s'usant facilement et qui agit, pour le ressort d'étrier (11, 11a), comme un limiteur de l'angle de pivotement.
  2. Pompe à pistons alternatifs selon la revendication 1,
    caractérisée en ce que
    la rondelle de butée (12) est pourvue d'un moyeu (22), et le moyeu (22) est réuni de façon solidaire en rotation à l'arbre d'excentrique (8).
  3. Pompe à pistons alternatifs selon la revendication 1 ou 2,
    caractérisée en ce que
    la rondelle de butée (12) est constituée sous la forme d'une pièce constitutive frittée en acier, et est trempée.
  4. Pompe à pistons alternatifs selon les revendications 1 à 3,
    caractérisée en ce qu'
    un second prolongement (41) part perpendiculairement à la bande d'une zone frontale (30) du côté qui est tourné vers la rondelle de butée (12), zone constituée sensiblement sous la forme d'une bande se trouvant entre les extrémités de ressort d'étrier (31, 32), et en ce que les deux prolongements (41, 41) se terminent sur un premier plan de référence qui s'étend parallèlement à un second plan de référence passant par les évidements (35) des extrémités (31, 32) de ressort d'étrier.
  5. Pompe à pistons alternatifs selon l'une des revendications 1 à 4,
    caractérisée en ce que
    dans les évidements (35), il y a des saillies (38, 39) orientées l'une vers l'autre et qui viennent en prise à la manière d'assemblages à enclenchement autour des cols de piston (27, 28).
  6. Pompe à pistons alternatifs selon l'une des revendications 1 à 5,
    caractérisée en ce que
    les évidements (35, 35a) sont orientés de façon à s'étendre dans le sens périphérique du ressort d'étrier (11a).
  7. Pompe à pistons alternatifs selon l'une des revendications 1 à 5,
    caractérisée en ce que
    les évidements (35a) sont disposés perpendiculairement à la périphérie du ressort d'étrier (11, 11a).
  8. Pompe à pistons alternatifs selon l'une des revendications 1 à 4,
    caractérisée en ce qu'
    en partant des cols de piston (28a), les extrémités des pistons (24a) sont formées à la manière de couches sphériques et en ce qu'en direction des extrémités des pistons (24a), les évidements présentent des surfaces de contact s'étendant en forme d'arc de cercle.
EP95100277A 1994-01-29 1995-01-11 Pompe à piston Expired - Lifetime EP0666418B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4402650 1994-01-29
DE4402650 1994-01-29
DE4427612 1994-08-04
DE4427612A DE4427612A1 (de) 1994-01-29 1994-08-04 Hubkolbenpumpe

Publications (2)

Publication Number Publication Date
EP0666418A1 EP0666418A1 (fr) 1995-08-09
EP0666418B1 true EP0666418B1 (fr) 1997-04-23

Family

ID=25933373

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95100277A Expired - Lifetime EP0666418B1 (fr) 1994-01-29 1995-01-11 Pompe à piston

Country Status (3)

Country Link
US (1) US5573386A (fr)
EP (1) EP0666418B1 (fr)
JP (1) JPH07224755A (fr)

Families Citing this family (23)

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Publication number Priority date Publication date Assignee Title
DE4443868A1 (de) * 1994-12-09 1996-06-13 Teves Gmbh Alfred Radialkolbenmaschine
DE19503621A1 (de) * 1995-02-03 1996-08-08 Bosch Gmbh Robert Hubkolbenpumpe
US5820167A (en) * 1995-12-22 1998-10-13 Kelsey-Hayes Company Quick-connect arrangement for high density hydraulic lines for anti-lock brake and/or traction control systems
US5769611A (en) * 1996-09-06 1998-06-23 Stanadyne Automotive Corp. Hydraulic pressure supply pump with multiple sequential plungers
DE19650276A1 (de) 1996-12-04 1998-06-10 Teves Gmbh Alfred Hubkolbenpumpe
US5785430A (en) * 1996-12-16 1998-07-28 General Motors Corporation Eccentric bearing assembly
AU2973099A (en) 1998-02-23 1999-09-06 Robert L. Jackson Oscillating spring valve fluid pumping system
DE19813302A1 (de) * 1998-03-26 1999-09-30 Bosch Gmbh Robert Kolbenpumpe bzw. Bremsanlage mit Kolbenpumpe
DE19816044C2 (de) * 1998-04-09 2002-02-28 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung
DE19827653A1 (de) * 1998-06-22 1999-12-23 Continental Teves Ag & Co Ohg Exzenteranordnung
DE19948447A1 (de) * 1999-10-08 2001-04-12 Continental Teves Ag & Co Ohg Radialkolbenpume mit seitlich elastisch abgestützten Koppelelement
DE50015708D1 (de) * 1999-10-25 2009-09-17 Continental Teves Ag & Co Ohg Motor-Pumpen-Aggregat
JP3593081B2 (ja) * 2001-10-02 2004-11-24 三菱電機株式会社 燃料供給装置
DE10236853A1 (de) * 2002-08-10 2004-02-26 Continental Teves Ag & Co. Ohg Radialkolbenpumpe, insbesondere für eine schlupfgeregelte Bremsanlage
DE10256525A1 (de) * 2002-12-04 2004-06-24 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
GB0329585D0 (en) * 2003-12-20 2004-01-28 Itw Ltd Pumps
ITVI20040051A1 (it) * 2004-03-12 2004-06-12 Gentilin Srl Compressore volumetrico alternativo
KR100907867B1 (ko) 2004-08-11 2009-07-14 주식회사 만도 브레이크시스템의 모터 실링장치
DE202009003133U1 (de) * 2009-03-09 2009-06-04 Baudat Gmbh & Co. Kg Kolbenpumpe mit mehreren Kolben
DE102009027576A1 (de) * 2009-07-09 2011-01-13 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
CN106958525B (zh) * 2016-01-12 2020-09-29 固瑞克明尼苏达有限公司 具有盖帽凹部的活塞杆
DE102019106531A1 (de) * 2019-03-14 2020-09-17 Baier & Köppel GmbH & Co. KG Schmierstoffpumpe mit automatisch ankoppelnder Pumpeinheit und Verfahren zum Ankoppeln einer Pumpeinheit an eine Schmierstoffpumpe
CN110778474B (zh) * 2019-11-21 2022-02-11 燕山大学 一种可回收废弃流体中压力能的径向活塞式流体泵

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US2309551A (en) * 1939-11-03 1943-01-26 Automotive Prod Co Ltd Pump
US2271570A (en) * 1940-07-31 1942-02-03 Harvey S Pardee Pump
FR989658A (fr) * 1944-02-22 1951-09-12 Olaer Marine Dispositif d'étanchéité
US3259074A (en) * 1963-02-16 1966-07-05 Teves Kg Alfred Radial-piston machines
FR1417269A (fr) * 1964-09-29 1965-11-12 Perfectionnements apportés aux pompes et compresseurs du type alternatif à excentrique
DE2102761C3 (de) * 1971-01-21 1974-11-07 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe
DE2243138A1 (de) * 1972-09-01 1974-03-07 Langen & Co Radialkolbenpumpe
DE3701857A1 (de) * 1987-01-23 1988-08-04 Teves Gmbh Alfred Radialkolbenpumpe
DE3722988A1 (de) * 1987-07-11 1989-01-19 Teves Gmbh Alfred Radialkolbenpumpe
DE4027794C2 (de) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulische Radialkolbenpumpe
DE4102364A1 (de) * 1991-01-28 1992-07-30 Teves Gmbh Alfred Kolbenpumpe
DE4102384A1 (de) * 1991-01-28 1992-07-30 Huebner Handel Huewa Abstandhalter - 360(grad) um die stabaufnahme stuetzend

Also Published As

Publication number Publication date
US5573386A (en) 1996-11-12
JPH07224755A (ja) 1995-08-22
EP0666418A1 (fr) 1995-08-09

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