EP0144787A2 - Pompe à pistons axiaux à disque oblique rotatif - Google Patents

Pompe à pistons axiaux à disque oblique rotatif Download PDF

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Publication number
EP0144787A2
EP0144787A2 EP84113472A EP84113472A EP0144787A2 EP 0144787 A2 EP0144787 A2 EP 0144787A2 EP 84113472 A EP84113472 A EP 84113472A EP 84113472 A EP84113472 A EP 84113472A EP 0144787 A2 EP0144787 A2 EP 0144787A2
Authority
EP
European Patent Office
Prior art keywords
swash plate
spring
piston pump
pump according
axial piston
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
EP84113472A
Other languages
German (de)
English (en)
Other versions
EP0144787A3 (en
EP0144787B1 (fr
Inventor
Ludwig Wagenseil
Manfred Lotter
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.)
Hydromatik GmbH
Original Assignee
Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0144787A2 publication Critical patent/EP0144787A2/fr
Publication of EP0144787A3 publication Critical patent/EP0144787A3/de
Application granted granted Critical
Publication of EP0144787B1 publication Critical patent/EP0144787B1/fr
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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means

Definitions

  • the invention relates to a swash plate axial piston pump according to the preamble of claim 1.
  • a swash plate axial piston pump with several pistons can be seen, the piston heads of which are kept in contact with the swash plate by means of a retraction plate.
  • a compression spring is used for this purpose, which acts indirectly on the retraction plate and is supported on a component of the axial piston pump which is fixed to the housing.
  • a control valve is arranged centrally between the pistons, which can be acted upon by the pressure in the pressure chamber against a spring force and which creates a connection between the pressure chamber and the suction chamber above a certain pressure.
  • the spring force of the control valve is generated by a compression spring that acts on the valve slide and is indirectly supported on the retraction plate.
  • a swash plate axial piston pump of this type is described and shown in DE-AS 10 01 593.
  • the retraction plate is mounted on a ball head and is fixed in the direction of the feed movement of the piston by a device provided specifically for this purpose, namely a flange on the swash plate.
  • a device provided specifically for this purpose, namely a flange on the swash plate.
  • Such an embodiment is not only complex in terms of production costs and for reasons of assembly, but it is also to be expected in particular after a longer running time (wear) with a strong running noise due to rattling of the retraction plate.
  • the invention has for its object to find a structurally simple and inexpensive and advantageous for assembly reasons to fix the retraction plate on the swash plate.
  • the spring force of the spring acting on the valve body in the pressure regulating valve is used to fix the retraction plate on the swash plate.
  • This definition is an elastic, so that a bearing play z. B. can not form due to wear and therefore the running noise can be kept low.
  • no special device provided for this purpose is required, but rather an existing device that is designed according to the invention.
  • valve spring is between the valve spring and the Retraction plate used a spring piston, which is advantageous for manufacturing and assembly reasons.
  • Eder piston in the F namely required for storage of the recoil plate spherical sliding surface -Can be formed.
  • support surfaces for the valve spring can be formed in a simple manner on the spring piston.
  • the design according to claim 6 then leads to a support of the force with which the retraction plate is acted against the swash plate when the pressure control valve opens. This support is based on the dynamic pressure that builds up when the hydraulic fluid flows through the channel in the hollow cylinder.
  • the embodiment according to claim 7 is advantageous because a channel in the spring piston can be produced simply and inexpensively as a small separate component.
  • Claim 9 contains an embodiment which is also advantageous for both manufacturing and assembly reasons.
  • the processing surfaces to be produced with relatively high precision are concentrated in one pump block, in which they can be efficiently incorporated.
  • the Pump block the sensitive wear parts of the swash plate axial piston pump, so that when these wear out, these parts can be replaced easily and simply.
  • the pump block automatically separates the suction and pressure chamber after it is installed.
  • the configuration described above also enables the assignment of a diaphragm valve plate in a simple manner if the pressure channels are designed according to claim 10.
  • valve body has a proven cone or ball head in a manner known per se.
  • An embodiment of the suction space, as described in claim 12, is advantageous because it can be provided from the outset in a casting and therefore requires no special processing. To connect the work rooms with the suction chamber, all that is required is short radial bores that can be easily and quickly worked into the pump block.
  • the pressure control valve is a pressure relief valve that is closed up to a predetermined working pressure and only opens when this pressure is exceeded, for example for safety reasons, so that hydraulic fluid flows back from the pressure chamber to the suction chamber and therefore no higher pressure can build up in the pressure chamber.
  • the force of the valve spring and the opening surface on the cone or ball head are therefore coordinated with one another in a predetermined manner.
  • the swash plate axial piston pump comprises a housing, generally denoted by 1, a drive shaft 2, a pump mechanism, generally denoted by 3, a suction chamber 4 to which a suction line 5 shown as an arrow can be connected, and a pressure chamber 6 to which one is also shown as an arrow Pressure line 7 is connectable.
  • the pump mechanism 3 consists of a swash plate 8, which is arranged at the end of the drive shaft 2 and can be set in rotation by it, a plurality of pistons 9 arranged in a circle, which are guided along the pump axis 11 in hollow cylinders 12 and work spaces in front of their free end faces 13 form, a retraction plate 14 to be described later, a pressure relief valve, generally designated 15, a diaphragm valve plate 16 and a pump block 17, in which the movable parts of the pump mechanism 3 are accommodated.
  • the pressure relief valve 15 is arranged centrally along the pump axis 11 and consists of a valve body 18, the cone head 19 of which cooperates with a valve seat (bore) 21 and a valve spring 22, which on the one hand engages the cone head 19 and on the other hand is received in a coaxial bore 23 of a spring piston 24 is.
  • the spring piston 24 can be moved along the pump axis 11 in a hollow cylinder 25, the bottom of which forms the valve seat 21.
  • the retraction plate 14 and the spring piston 24 have concave sliding surfaces 26, 27 opposite one another and shaped in the sense of a spherical section, between which a ball 28 is mounted.
  • the rotating swash plate 8 causes the pistons 9 to move back and forth.
  • the retraction movement 29 of the pistons 9 takes place in each case through the retraction plate 14, which engages behind flanges 31 of sliding shoes 32 which grip spherically shaped heads 33 of the pistons 9. Since the valve spring 22 is supported on the spring piston 24, the spring force generated by it is transmitted to the retraction plate 14 with the aid of the ball 28, as a result of which the latter is pressed onto the swash plate 8 and is thus fixed.
  • the spring force of the pressure relief valve 15 is thus used at the same time to fix the retraction plate 14.
  • valve body 18 of the pressure relief valve 15 opens, so that hydraulic fluid can flow back through the hollow cylinder 25 and through an axial channel 39 and radial channels 41 in the spring piston 24 into the suction chamber 4.
  • the pump block 17 has a flange 42 which forms shoulders 43, 44. With these shoulders 43, 44 is the Pump block 17 clamped between a first housing part 45 and a second housing part 46, wherein it is encompassed in a form-fitting manner on its circumference and is thus fixed both axially and radially. This clamping also serves at the same time for fastening the diaphragm valve plate 16, which is overlapped by the shoulder 44.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP84113472A 1983-11-08 1984-11-08 Pompe à pistons axiaux à disque oblique rotatif Expired EP0144787B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3340333A DE3340333C1 (de) 1983-11-08 1983-11-08 Taumelscheiben-Axialkolbenpumpe
DE3340333 1983-11-08

Publications (3)

Publication Number Publication Date
EP0144787A2 true EP0144787A2 (fr) 1985-06-19
EP0144787A3 EP0144787A3 (en) 1986-02-19
EP0144787B1 EP0144787B1 (fr) 1987-09-02

Family

ID=6213736

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84113472A Expired EP0144787B1 (fr) 1983-11-08 1984-11-08 Pompe à pistons axiaux à disque oblique rotatif

Country Status (4)

Country Link
US (1) US4576554A (fr)
EP (1) EP0144787B1 (fr)
JP (1) JPS60116881A (fr)
DE (2) DE3340333C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103362767A (zh) * 2012-03-29 2013-10-23 三菱电机株式会社 燃料供给装置

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3440850A1 (de) * 1984-11-08 1986-05-22 Mannesmann Rexroth GmbH, 8770 Lohr Axialkolbenpumpe
DE3638890A1 (de) * 1986-07-31 1988-02-04 Hydromatik Gmbh Axial-kolbenmaschine mit einer einrichtung zum spuelen des kreislaufs
JPS63205469A (ja) * 1987-02-20 1988-08-24 Sanden Corp 容量可変型斜板式圧縮機
GB8716494D0 (en) * 1987-07-14 1987-08-19 Apsley Metals Ltd Manufacture of tyres
JPH0489873U (fr) * 1990-12-15 1992-08-05
DE4209461C2 (de) * 1992-03-24 1994-10-06 Elektra Beckum Ag Axialkolbenpumpe, insbesondere für Wasser-Hochdruckreiniger
US5540556A (en) * 1994-06-01 1996-07-30 Du; Benjamin R. Positive displacement pump including modular pump component
US5749709A (en) * 1996-05-15 1998-05-12 Du; Benjamin R. Positive displacement pump including modular pump component
JP2001227465A (ja) * 2000-02-18 2001-08-24 Toyota Autom Loom Works Ltd 圧縮機用中空ピストンの製造方法
JP2002332961A (ja) 2000-10-20 2002-11-22 Nippon Soken Inc 流体ポンプ
US8469677B1 (en) * 2007-10-01 2013-06-25 Sauer-Danfoss Inc. Check valve pump with electric bypass valve
US7887302B2 (en) * 2009-03-31 2011-02-15 General Electric Company High pressure variable displacement piston pump
DE102009038462A1 (de) * 2009-08-21 2011-03-03 Dürr Systems GmbH Taumelkolbenpumpe zur Dosierung eines Beschichtungsmittels
DE102010015073A1 (de) * 2010-04-15 2011-10-20 Robert Bosch Gmbh Axialkolbenmaschine mit einer Rückzugplatte sowie Verfahren zu deren Herstellung
US9140244B2 (en) 2011-08-31 2015-09-22 Caterpillar Inc. Piston pump with cam actuated valves
WO2013030408A1 (fr) * 2011-09-02 2013-03-07 Alfmeier Präzision AG Baugruppen und Systemlösungen Pompe, notamment pompe pneumatique
JP5063823B1 (ja) * 2012-04-13 2012-10-31 株式会社小松製作所 斜軸式アキシャルピストンポンプ・モータ
JP5746393B1 (ja) * 2014-04-28 2015-07-08 三菱電機株式会社 電動ポンプ
DE102019113536B4 (de) * 2019-05-21 2022-04-21 Danfoss A/S Vorrichtung zur Bereitstellung von Anschlüssen an einen Maschinenbereich einer hydraulischen Maschinenanordnung
CN112032009B (zh) * 2020-09-17 2021-09-17 上海交通大学 一种阀配流轴向柱塞泵
CN114893375B (zh) * 2020-10-09 2024-06-25 王小安 一种无复位弹簧的斜盘式柱塞水泵的驱动连接结构
CN114060245B (zh) * 2021-12-09 2024-04-05 华中科技大学 一种固定间隙回程式高压柱塞水泵

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE736165C (de) * 1939-08-12 1943-06-09 Askania Werke Ag Kolbenpumpe
DE1001593B (de) * 1957-01-24 Societe d Inventions Aeronautiques et Mecaniques SIAM, Freiburg (Schweiz) Taumelscheibenpumpe mit automatischer druckabhangiger Forderregelung
DE1228513B (de) * 1960-03-10 1966-11-10 Kloeckner Humboldt Deutz Ag Einrichtung zur Geraeuschminderung bei Druckfluessigkeits-Axialkolbenmaschinen
DE1939242A1 (de) * 1968-08-02 1970-07-30 Corpet Louvet & Cie Hydraulische Pumpe mit variierender Foerdermenge der Bauart mit Kolben und Ventilen
DE1947641B2 (de) * 1968-09-21 1973-11-15 Dowty Technical Developments Ltd., Brockhampton, Cheltenham, Gloucester (Grossbritannien) Als Pumpe oder Motor ausgebildete Maschine veränderlicher Verdrängung

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2138194A (en) * 1936-03-11 1938-11-29 Blackhawk Mfg Co Hydraulic pump
CH297542A (de) * 1951-12-28 1954-03-31 Buehrer Fritz Kolbenpumpe.
US2797647A (en) * 1954-01-19 1957-07-02 Detroit Harvester Co Hydraulic pump
FR1201441A (fr) * 1957-11-14 1959-12-30 Rech Etudes Production Sarl Pompe auto-régulatrice avec tiroir central de régulation
US2990781A (en) * 1957-11-25 1961-07-04 Gen Motors Corp Wobble plate pump
FR1189369A (fr) * 1957-12-30 1959-10-02 Rech Etudes Production Sarl Pompe à barillet avec tiroir central d'auto-régulation
FR1344108A (fr) * 1963-01-18 1963-11-22 Compresseur à débit variable
FR2307983A1 (fr) * 1975-04-17 1976-11-12 Leray Jules Perfectionnements aux pompes a huile pour transmissions hydrauliques
US4290345A (en) * 1978-03-17 1981-09-22 Sankyo Electric Company Limited Refrigerant compressors
US4236878A (en) * 1978-09-29 1980-12-02 Sankyo Electric Company Limited Lubrication system for compressor unit

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1001593B (de) * 1957-01-24 Societe d Inventions Aeronautiques et Mecaniques SIAM, Freiburg (Schweiz) Taumelscheibenpumpe mit automatischer druckabhangiger Forderregelung
DE736165C (de) * 1939-08-12 1943-06-09 Askania Werke Ag Kolbenpumpe
DE1228513B (de) * 1960-03-10 1966-11-10 Kloeckner Humboldt Deutz Ag Einrichtung zur Geraeuschminderung bei Druckfluessigkeits-Axialkolbenmaschinen
DE1939242A1 (de) * 1968-08-02 1970-07-30 Corpet Louvet & Cie Hydraulische Pumpe mit variierender Foerdermenge der Bauart mit Kolben und Ventilen
DE1947641B2 (de) * 1968-09-21 1973-11-15 Dowty Technical Developments Ltd., Brockhampton, Cheltenham, Gloucester (Grossbritannien) Als Pumpe oder Motor ausgebildete Maschine veränderlicher Verdrängung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103362767A (zh) * 2012-03-29 2013-10-23 三菱电机株式会社 燃料供给装置

Also Published As

Publication number Publication date
DE3465760D1 (en) 1987-10-08
US4576554A (en) 1986-03-18
DE3340333C1 (de) 1985-06-27
EP0144787A3 (en) 1986-02-19
JPH0435629B2 (fr) 1992-06-11
JPS60116881A (ja) 1985-06-24
EP0144787B1 (fr) 1987-09-02

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