EP0044070B1 - Pompe à pistons axiaux avec deux courants d'écoulement - Google Patents

Pompe à pistons axiaux avec deux courants d'écoulement Download PDF

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Publication number
EP0044070B1
EP0044070B1 EP81105478A EP81105478A EP0044070B1 EP 0044070 B1 EP0044070 B1 EP 0044070B1 EP 81105478 A EP81105478 A EP 81105478A EP 81105478 A EP81105478 A EP 81105478A EP 0044070 B1 EP0044070 B1 EP 0044070B1
Authority
EP
European Patent Office
Prior art keywords
pitch circle
circle diameter
tilting disc
pistons
cylindrical drum
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
EP81105478A
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German (de)
English (en)
Other versions
EP0044070A1 (fr
Inventor
Franz Forster
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.)
Linde GmbH
Original Assignee
Linde 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 Linde GmbH filed Critical Linde GmbH
Publication of EP0044070A1 publication Critical patent/EP0044070A1/fr
Application granted granted Critical
Publication of EP0044070B1 publication Critical patent/EP0044070B1/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
    • F04B1/20—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 rotary cylinder block
    • F04B1/22—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 rotary cylinder block having two or more sets of cylinders or pistons

Definitions

  • the invention relates to an axial piston pump for generating two flow rates, the size of which can be set independently of one another, with a rotating cylinder drum connected to a shaft, in which cylinder bores are arranged on two different pitch circle diameters, all of which open into the same end face of the cylinder drum, one in each cylinder bore Piston is displaceable and the pistons in the cylinders arranged on a smaller pitch circle diameter are supported against an adjustable swash plate formed on a swash plate body and the pistons in the cylinders arranged on a larger pitch circle diameter are supported against a second adjustable swash plate formed on a second swash plate body, whereby on the a control rotary valve is formed on the end face of the cylinder drum from which the pistons emerge, on the opposite end face of the cylinder drum.
  • a swash plate which are supported on a swash plate body designed as a circumferential ring, this ring being supported via a roller bearing against a swivel body which, on the one hand, is arranged against a roller-shaped one arranged outside the axis of rotation Support body is supported and on the other hand is supported against an adjusting device which is axially displaceable so that the inclination of the swash plate body relative to the axis of rotation can be adjusted.
  • the pistons which are arranged on a larger pitch circle diameter, are supported against a swash plate which is formed on an annular swash plate body, which in turn is designed as a circumferential ring and is mounted in a swivel body by means of a roller bearing, which in turn is eccentric to the axis of rotation against a roller-shaped body is supported on the other side of the axis of rotation as the support body arranged first and is also supported against an axially displaceable adjusting member (FR-A-1 340 850).
  • a swash plate which is formed on an annular swash plate body, which in turn is designed as a circumferential ring and is mounted in a swivel body by means of a roller bearing, which in turn is eccentric to the axis of rotation against a roller-shaped body is supported on the other side of the axis of rotation as the support body arranged first and is also supported against an axially displaceable adjusting member (FR-A-1 340 850).
  • This type of support for the swashplate body requires a large installation space relative to the forces that can be absorbed, so that for a given installation space only relatively small forces can be absorbed, that is to say either one can only work with a low working pressure or the pistons have a small diameter must have, and moreover, this embodiment allows only small angles of inclination for the swash plate body.
  • the known pump therefore requires a relatively large amount of space.
  • the present invention has for its object to provide an axial piston machine of the type mentioned, which can be manufactured with as few components and thus low construction costs and which also has relatively small dimensions in terms of performance and requires a correspondingly small installation space.
  • the swash plate body on which the swash plate is formed against which the pistons arranged on a smaller pitch circle diameter are supported, has a spherical cap-shaped surface on its side facing away from the swash plate and with this spherical cap-shaped surface in a spherical cap-shaped recess Swashplate body is mounted on which the swashplate is formed, against which the pistons arranged on a larger pitch circle diameter are supported.
  • This spherical cap-shaped surface and spherical cap-shaped counter surface can absorb large piston forces.
  • this configuration is the smallest spatial shape, which on the one hand enables a sufficient swash plate surface for supporting the pistons arranged on a smaller pitch circle diameter, the pitch circle diameter of the pistons arranged on a larger pitch circle diameter also being as small as possible, that is to say that the two pitch circle diameters are as tight should lie next to each other, as is possible with regard to the strength of the cylinders on the one hand and the space required for the piston supports on the other.
  • the spherical bearing surface enables the adjustment device for the pivoting of the swash plate body associated with the piston arranged on a smaller pitch circle diameter to be designed in such a way that this adjustment device additionally swivels this swash plate body a small amount about a second, to the first pivot axis and the axis of rotation vertical axis of the cylinder drum can be effected.
  • Such a small, arbitrarily brought about additional pivoting about the second pivot axis makes it possible to achieve a small pre-compression or pre-expansion while smoothing over the separating webs while keeping the separating webs in the control rotary valve in the same position and thus avoiding them operating noise.
  • a connecting device is provided, by means of which the swash plate bodies, which can be adjusted independently of one another during operation, can be arbitrarily connected to one another for the purpose of common adjustment during certain operating states. That is, in operating states in which it is desired that the flow rates of both pumps are changed to the same extent, the connection is established by this connecting device, this connection being releasable, so that in other operating states the goal is two independent flow rates to generate can be tracked.
  • the swash plate body assigned to the piston arranged on a smaller pitch circle diameter is in operative connection with a swash plate body which extends through a recess of the swash plate body assigned to the piston arranged on a larger pitch circle diameter, that is to say the adjustment of the one arranged on the smaller pitch circle diameter
  • Piston-associated swash plate body is not provided by a device that acts parallel to the axis of rotation, but by a device that extends through the outer swash plate body.
  • both swashplate bodies have a central recess through which the shaft connected to the cylinder drum projects to a free connection.
  • control base 2 and the cradle bearing part 3 are attached to the middle part of the housing. These parts are connected to each other by anchor bolts, not shown in the drawing.
  • the cylinder drum 4 is mounted in the middle part 1 of the housing by means of a roller bearing 55. With its end face 5, the cylinder drum 4 bears against a control plate 6, which in turn is rotatably mounted on the control base part 2.
  • the cylinder drum 4 has a longitudinal bore 7 which, in the part on the left in the drawing, is provided with an internal toothing 8 which engages in the toothing of a drive shaft which in turn by means of a bearing 10 (which is preferably designed as a pair of roller bearings) in the control floor 2 is stored.
  • the cover 12 serves to secure the bearing 10 and carries the seal 11.
  • a pin 13 is provided coaxially to the shaft 9 and has a collar 14 and a ball head 15.
  • a plate spring assembly 16 is supported against the collar 14, which is supported on the other hand against the cylinder drum 4.
  • the ball head 15 lies in a corresponding recess in the pressure plate 17, which has bores through which the sliding shoes 18 of the pistons 19, which are arranged with a small pitch circle diameter, protrude.
  • the sliding shoes 18 have a base part 20 against which the pressure plate 17 presses.
  • the pistons 19, which are arranged on a smaller pitch circle diameter, are displaceable in cylinder bores 21, each cylinder bore 21 being provided with an orifice channel 22 which opens into the end face 5 of the cylinder drum 4, specifically in relation to an at least approximately semicircular channel 23 in the control plate 6, which is located in continues a channel 24 in the control floor 2, the channel 24 leading to a connection, not shown in the drawing, lying next to the plane of the drawing.
  • the pistons 25 are arranged on a larger pitch circle diameter than the pistons 19, each of the pistons 25 being displaceable in a cylinder bore 26 which has an orifice channel 27, the orifice channels 27 being opposite an approximately semicircular channel 28 in the control plate 6, the channel 28 connects to a channel 29 in the control floor part 2, which leads to a connecting flange 30 for a delivery pressure line, not shown in the drawing.
  • Each piston 25 is supported against a slide shoe 31, the base part 32 of which is pressed against the swash plate 34 by a hold-down ring 33, the hold-down ring 33 being held by a pressure ring 35 which is screwed against the swash plate body 36.
  • the swash plate 34 assigned to the piston 25 arranged on a larger pitch circle diameter is thus formed on the swash plate body 36.
  • the pistons 19, which are arranged on a smaller pitch circle diameter are supported by means of their sliding shoes 18 against the swash plate 37, which is formed on the swash plate body 38 and has a spherical cap-shaped surface 39 on its rear side, which rests in a hollow spherical surface of the swash plate body 36.
  • the swash plate body 36 has a semi-cylindrical surface 40 on a rear side, which rests in a hollow cylindrical surface of the cradle bearing part 3.
  • the swashplate body 36 has a recess 41 through which an adjusting pin 42 extends, which is provided with a ball head 43 which is guided in a bore 64 in the swashplate body 38.
  • the adjusting pin 42 is on the other hand fastened in the adjusting piston 44, which is displaceable in the adjusting cylinder 45, which is formed in a corresponding extension of the cradle bearing part 3 and is closed on both sides by a cover 46, through which the hydraulic fluid lines, not shown in the drawing, pass, by means of which the actuating piston 44 can be acted upon arbitrarily with pressure medium.
  • a further extension is formed on the cradle bearing part 3, in which an actuating cylinder 47 is arranged, in which an actuating piston 48 is displaceable is.
  • the actuating cylinder 47 is also closed by two covers 46.
  • a setting pin 49 is fastened in the adjusting piston 48 and engages with its spherical head part 50 in a bore 51 of the swash plate body 36.
  • a suction channel 52 is provided in the control floor part 2, which opens into a wide opening 53 of the control plate 6, the opening 53 extending in the radial direction so far that it both before the Mouth channels 27 and in front of the mouth channels 22. In the circumferential direction, the opening 53 extends just as far as the approximately semicircular channels 23 and 28 on the other side.
  • two approximately semicircular channels can also be formed in front of the mouth of the suction channel 52, which channels correspond to the channels 23 and 28, the side of the control plate 6 facing the suction channel 52 being designed to be streamlined.
  • the control floor part 2 is designed symmetrically on both sides, that is, instead of the suction channel 52 and the opening 53, two separate channels are formed in the control floor part 2 and correspondingly two approximately semicircular channels corresponding to the channels 23 and 28 in the control plate 6 , so that the pump is designed for two closed circuits.
  • control base part 2 is shown rotated by 90 ° about the axis of the shaft 9, because in the cutting plane, which is perpendicular to the swivel axis of the swash plate bodies 36 and 38, the separating webs lie in the control plate 6, that is to say no openings in the The drawing would be recognizable if the cut were placed through it

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (6)

1. Pompe à pistons axiaux pour produire deux écoulements, dont les débits sont réglables indépendamment l'un de l'autre, comportant un tambour à cylindres (4) tournant, relié à un arbre (9) et dans lequel sont ménagés des alésages cylindriques (21, 26) qui débouchent tous dans la même surface frontale (5) du tambour (4), un piston (19, 25) pouvant coulisser dans chaque alésage cylindrique (21, 26), les alésages cylindriques (21, 26) étant disposés dans le tambour (4) sur deux cercles partiels de diamètres différents, les pistons (19) se trouvant dans les cylindres (21) placés sur le cercle partiel de petit diamètre s'appuyant contre un disque incliné (37) réglable et formé sur un corps (38) tandis que les pistons (25) situés dans les cylindres (26) placés sur le cercle partiel de grand diamètre s'appuient contre un second disque incliné (34) réglable et formé sur un second corps (36), chacun des deux disques inclinés (34, 37) étant reliés à un dispositif de réglage se composant d'un organe de manoeuvre (44, 48) et d'un élément de manoeuvre (42, 49) pour produire un mouvement de pivotement du corps à disque incliné (36, 38) autour d'un axe de pivotement orienté perpendiculairement à l'axe de rotation du tambour à cylindres (4) en vue du réglage de l'inclinaison du disque incliné (34, 37), déterminant la course du piston associé (19, 25) par rapport à l'axe de rotation du tambour à cylindres (4), un tiroir tournant de distribution étant formé sur la surface frontale du tambour (4) qui est opposée au côté frontal du tambour duquel sortent les pistons (19, 25) et dans laquelle débouchent, sur un cercle partiel de petit diamètre, des canaux (22) qui sont reliés aux alésages cylindriques (21) placés sur le cercle partiel de petit diamètre tandis que, sur un cercle partiel de plus grand diamètre, il est prévu des canaux (27) qui sont reliés aux alésages cylindriques (26) disposés sur le cercle partiel de grand diamètre, ce côté frontal du tambour à cylindres (4) étant placé en regard d'une plaque de distribution (6) dans laquelle sont disposés deux canaux (23) de forme approximativement demi-circulaire, sur un cercle partiel d'un diamètre correspondant à celui du cercle partiel des canaux (22) tandis que deux autres canaux respectivement de forme approximativement demi-circulaire sont disposés sur un cercle partiel d'un diamètre qui correspond à celui du cercle partiel des canaux (27), caractérisée en ce que le corps à disque incliné (38), sur lequel est formé le disque incliné (37) contre lequel s'appuient les pistons (19) placés sur le cercle partiel de petit diamètre comporte, sur son côté opposé au disque incliné (37), une surface (39) en forme de chapeau sphérique à l'aide de laquelle il est monté dans un évidement en forme de calotte sphérique du corps à disque incliné (36) sur lequel est formé le disque incliné (34) contre lequel s'appuient les pistons (25) placés sur le cercle partiel de grand diamètre.
2. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce que l'organe de manoeuvre (44) et l'élément de manoeuvre (42) du dispositif de réglage du mouvement de pivotement autour de l'axe de pivotement du corps à disque incliné (38) associé aux pistons (19) placés sur le cercle partiel de petit diamètre est agencé de telle sorte qu'il soit possible, à l'aide de ce dispositif de réglage, de produire addition- nellement un petit mouvement de pivotement de ce corps à disque incliné (38) autour d'un second axe orienté perpendiculairement à l'axe de pivotement excité en premier et à l'axe de rotation du tambour à cylindres (4).
3. Pompe à pistons axiaux selon la revendication 2, caractérisée en ce qu'également le support, et le dispositif de réglage se composant de l'organe de manoeuvre (48) et de l'élément de manoeuvre (49), du corps à disque incliné (36) associé aux pistons (25) placés sur le cercle partiel de grand diamètre, sont agencés pour permettre un mouvement de pivotement autour de deux axes perpendiculaires entre eux.
4. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce qu'il est prévu un dispositif de liaison à l'aide duquel les deux corps à disques inclinés (38, 36) réglables indépendamment l'un de l'autre, peuvent être reliés entre eux de façon séparable et à volonté en vue d'une manoeuvre commune dans des conditions de marche déterminées.
5. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce que le corps à disque incliné (38) associé aux pistons (19) associés au cercle partiel de petit diamètre est placé en liaison de coopération avec un élément de manœuvre (42, 43) d'un organe de manoeuvre (45, 44) s'accrochant dans un évidement (41) du corps à disque incliné (36) associé aux pistons (25) placés sur le cercle partiel de petit diamètre.
6. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les deux corps à disques inclinés comportent un évidement central dans lequel passe l'arbre relié au tambour à cylindres (4) pour aboutir à un raccord d'arbre libre.
EP81105478A 1980-07-15 1981-07-13 Pompe à pistons axiaux avec deux courants d'écoulement Expired EP0044070B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803026765 DE3026765A1 (de) 1980-07-15 1980-07-15 Axialkolbenpumpe fuer zwei foerderstroeme
DE3026765 1980-07-15

Publications (2)

Publication Number Publication Date
EP0044070A1 EP0044070A1 (fr) 1982-01-20
EP0044070B1 true EP0044070B1 (fr) 1984-02-08

Family

ID=6107237

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81105478A Expired EP0044070B1 (fr) 1980-07-15 1981-07-13 Pompe à pistons axiaux avec deux courants d'écoulement

Country Status (4)

Country Link
US (1) US4449444A (fr)
EP (1) EP0044070B1 (fr)
JP (1) JPS5751343A (fr)
DE (1) DE3026765A1 (fr)

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DE3134537C2 (de) * 1981-09-01 1986-03-27 Moskovskoe naučno-proizvodstvennoe ob"edinenie po stroitel'nomu i dorožnomu mašinostroeniju VNIISTROIDORMAŠ, Moskva Hydraulische Axialkolbenmaschine mit rotierenden Verdrängungskörpern
DE3212429A1 (de) * 1982-04-02 1983-10-13 Abex Corp., 10036 New York, N.Y. Hydraulische axialkolbenmaschine
GB2134188B (en) * 1983-01-27 1986-09-10 Linde Ag An adjustable axial piston machine of the inclined swash plate type
DE3333812C2 (de) * 1983-09-19 1986-08-07 Hydromatik GmbH, 7915 Elchingen Schwenktrommel-Axialkolbenmaschine
US4710107A (en) * 1986-04-15 1987-12-01 The Oilgear Company Swashblock lubrication in axial piston fluid displacement devices
DE3725525A1 (de) * 1987-07-31 1989-02-09 Linde Ag Verstellbare axialkolbenmaschine in schraegachsenbauweise
DE4027794C2 (de) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulische Radialkolbenpumpe
US6460450B1 (en) * 1999-08-05 2002-10-08 R. Sanderson Management, Inc. Piston engine balancing
US6446587B1 (en) * 1997-09-15 2002-09-10 R. Sanderson Management, Inc. Piston engine assembly
US7007589B1 (en) * 1997-09-15 2006-03-07 R. Sanderson Management, Inc. Piston assembly
DE19947321A1 (de) * 1999-10-01 2001-04-19 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
DE10055262A1 (de) * 2000-11-08 2002-05-23 Linde Ag Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
US7011469B2 (en) * 2001-02-07 2006-03-14 R. Sanderson Management, Inc. Piston joint
US6854377B2 (en) 2001-11-02 2005-02-15 R. Sanderson Management, Inc. Variable stroke balancing
US6913447B2 (en) * 2002-01-22 2005-07-05 R. Sanderson Management, Inc. Metering pump with varying piston cylinders, and with independently adjustable piston strokes
WO2003100231A1 (fr) * 2002-05-28 2003-12-04 R. Sanderson Management, Inc. Mecanisme de protection contre les surcharges
DE10349599B3 (de) * 2003-10-24 2005-07-07 Brueninghaus Hydromatik Gmbh Anschlussblock für eine hydrostatische Kolbenmaschine
DE10358728B4 (de) * 2003-12-15 2006-01-05 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine zum unabhängigen Fördern in mehrere hydraulische Kreisläufe
US7438029B2 (en) * 2004-03-18 2008-10-21 R. Sanderson Management, Inc. Piston waveform shaping
WO2005119010A1 (fr) * 2004-05-26 2005-12-15 R. Sanderson Management, Inc. Mecanisme a course et ecartement variables
DE102006021570A1 (de) * 2006-04-10 2007-10-18 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit drehbarer Steuerscheibe
US20100028169A1 (en) * 2008-07-31 2010-02-04 Caterpillar Inc. Hydraulic device having an alignment component
DE102011077253A1 (de) * 2011-06-09 2012-12-13 Robert Bosch Gmbh Axialkolbenmaschine in Schrägscheibenbauweise
DE102013200729A1 (de) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Schrägscheibenmaschine
US9803634B2 (en) * 2014-09-05 2017-10-31 Caterpillar Inc. Valve plate arrangement for an axial piston pump
CN104358657A (zh) * 2014-11-03 2015-02-18 安徽理工大学 一种双侧驱动平衡式低速大扭矩轴向柱塞马达
NL2014672B1 (en) * 2015-04-20 2017-01-20 Forage Innovations Bv Hydraulic fluid distributor and hydraulic fluid distributing method.
DE102021200205A1 (de) 2021-01-12 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Axialkolbenmaschine mit hoher Antriebdrehzahl
CN115523115B (zh) * 2022-09-29 2024-04-19 燕山大学 对顶式超高压轴向柱塞泵

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US1714148A (en) * 1927-12-21 1929-05-21 Weldy Arthur Sheldon Pump
US2520632A (en) * 1945-03-22 1950-08-29 Torq Electric Mfg Company Hydraulic pump or motor
US2445281A (en) * 1945-10-04 1948-07-13 Charles H Rystrom Hydraulic pump
DE1129828B (de) * 1959-09-18 1962-05-17 Citroen Sa Hochdruck-Axialkolbenpumpe mit umlaufender Zylindertrommel und verschwenkbarer Schiefscheibe
FR1340850A (fr) * 1962-07-19 1963-10-25 Perfectionnements aux pompes à piston et analogues
CH445298A (de) * 1962-10-09 1967-10-15 Hydrospeed Ag Rückzugvorrichtung für hydraulische Axialkolbenmaschinen
GB1073216A (en) * 1962-11-21 1967-06-21 F W Baggett & Co Ltd Improvements relating to swash plate pumps and motors
FR1415392A (fr) * 1964-12-03 1965-10-22 Karl Marx Stadt Ind Werke Machine hydraulique à pistons axiaux
DE1625073C3 (de) * 1967-05-09 1978-05-24 Detlef 7531 Kieselbronn Hofmann Druckmittelbetätigte Kolbenmaschine
GB1176621A (en) * 1968-01-09 1970-01-07 Karl Marx Stadt Ind Werke Improvements in or relating to Reciprocating Hydraulic Pumps or Motors
DE2451380C2 (de) * 1974-10-29 1985-08-14 Linde Ag, 6200 Wiesbaden Einstellbarer Axialkolbenmotor mit einem Schwenkflügelstellantrieb
IT1082968B (it) * 1977-04-05 1985-05-21 Gherner Lidio Motore idraulico a pistoni assiali
SU804858A1 (ru) * 1977-12-09 1981-02-15 Уральский Ордена Трудового Красногознамени Политехнический Институтимени C.M.Кирова Аксиально-поршнева гидромашина

Also Published As

Publication number Publication date
JPS5751343A (en) 1982-03-26
DE3026765A1 (de) 1982-02-11
EP0044070A1 (fr) 1982-01-20
US4449444A (en) 1984-05-22

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