EP0044070A1 - 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
EP0044070A1
EP0044070A1 EP81105478A EP81105478A EP0044070A1 EP 0044070 A1 EP0044070 A1 EP 0044070A1 EP 81105478 A EP81105478 A EP 81105478A EP 81105478 A EP81105478 A EP 81105478A EP 0044070 A1 EP0044070 A1 EP 0044070A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
pitch circle
circle diameter
plate body
pistons
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
EP81105478A
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German (de)
English (en)
Other versions
EP0044070B1 (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 according to the preamble of patent claim 1.
  • 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 with little construction and which also has relatively small dimensions, especially in the axial direction and a correspondingly small Installation space required.
  • the configuration with a cylinder drum according to the invention while avoiding the disadvantages of the prior art described at the outset, enables two flow rates to be generated, each flow rate being set independently of the other by adjusting the associated swashplate body is cash.
  • the combination of the characteristic features thus makes it possible to use the characteristic feature a), which is known per se for gearboxes, for generating two currents which can be set independently of one another, all features interacting expediently to achieve the goal.
  • Another swash plate pump is also known. with a revolving cylinder drum, in which cylinder bores are arranged on two pitch circle diameters and which serves to convey two flows. Although there is a control rotary valve, additional valves are required for this pump, the pumped current is discharged through the shaft. All pistons run together against a single swash plate. This has the consequence on the one hand that there is no adjustability, on the other hand that the problems arising from the requirement for separate adjustability of the piston strokes do not occur at all in such a cylinder drum (GB-PS 1 127 291).
  • an axial piston pump which is used to deliver two mutually adjustable flow rates which are independent of one another with respect to the pressure, and in which two approximately semi-circular channels ("kidneys") in pairs in the control mirror on two diameters are arranged and the mouths of the with the.
  • Cylinder drums communicating channels are arranged on two corresponding pitch circle diameters in such a way that the mouth of every second cylinder is on the small pitch circle diameter and the mouth of each intermediate cylinder on the large pitch circle diameter.
  • the semicircular channels of large diameter belong to a pressure medium circuit, which are in between lying channels belong to another (DE-OS 16 53 634).
  • each flow rate is half as large as would be possible with a cylinder drum of the same dimensions with a normal design. Since all pistons have to run against a swash plate, it is not possible to set one circle independently of the other.
  • the swashplate body, against the swashplate of which the pistons, which are arranged on the smaller pitch circle diameter, are supported, on the rear side be designed in the form of a spherical cap, since a semi-cylindrical configuration of the swash plate body as usual would have the consequence that the outer corners of this swash plate body protrude very far outwards.
  • the inner diameter of this running surface for the pistons arranged on the large pitch circle diameter would have to be very large and this would achieve the desired goal with the smallest possible Installation space to get along, run counter.
  • the rear side of the swash plate body associated with the pistons arranged on a smaller diameter has a different shape, such as that of a double cone or in particular that of an ellipsoid, so that the swash plate has an elliptical boundary, which takes into account the oblique angle of the pistons relative to one another provided swash plate would be cheap.
  • the swashplate body associated with the piston / arranged on a large pitch circle diameter can be carried out in any known manner. This means that, as is known, it can have a semi-cylindrical shape or be mounted in pins or, like the swash plate body associated with the pistons arranged on a small pitch circle diameter, can be spherical cap-shaped on its rear side.
  • the feature of claim 2 allows the storage of the swash plate body associated with the piston arranged on a small pitch circle such that it can be pivoted not only about an axis for adjusting the stroke, but also about the third axis perpendicular to this axis and to the axis of rotation in one small angular amount can be adjusted.
  • Such an additional pivoting means that the piston dead center position can be shifted relative to the center of the separating web and the pre-compression or pre-expansion can be brought about by the processes in the cylinder when grinding over the separating web, that is to say during the reversal process, can be improved.
  • This pivoting about the second axis can take place depending on the delivery pressure, so that the pre-compression or pre-expansion takes place depending on the pressure drop and thus an optimal situation is achieved both in terms of efficiency and in terms of noise generation.
  • the swash plate body assigned to the piston arranged on a large pitch circle diameter is also designed in the shape of a spherical cap on its rear side and stored in a corresponding pan, this can also be done. This is pivoted independently of the other inner swash plate body about this second axis and the reversing process can thus be improved in accordance with the pressure against which it is conveyed.
  • Both swashplate bodies are expediently secured by elements known per se against turning under the action of the friction of the sliding shoes.
  • the difference between the pitch circle diameters can be chosen to be relatively small, so that in each case offset by half a division between two cylinders arranged on a small pitch circle diameter is a cylinder arranged on a large pitch circle diameter, the inner edge of the cylinder being offset from the axis of rotation of the axis of the cylinder having a large pitch circle diameter has a smaller distance than the outer edge of the cylinder arranged on a small pitch circle diameter.
  • pocket-like recesses connected to pressure medium supply lines can be provided for the purpose of forming pressure pads for a hydrostatic bearing, which reduces the friction between the swash plate body and the bearing and thus an adjustment easier and also ensures that the swash plate body assigned to the pistons arranged on a smaller pitch circle diameter can be adjusted without exerting forces on the swash plate body assigned to the pistons arranged on a large pitch circle diameter.
  • the swash plate body assigned to the piston arranged on a smaller pitch circle diameter being provided with a wing that slides sealingly in a longitudinally extending recess of the other swash plate body, or this other the larger one
  • the swashplate body assigned to the pitch circle diameter of the piston can be provided with a swivel wing that slides sealingly in a corresponding recess in the housing, the swivel wing each dividing the recess into two pressure chambers that can be pressurized arbitrarily.
  • Have die.Zylinderbohrept on a large pitch diameter each have the same bore diameter as the cylinder bores on a small pitch circle diameter, as a greater flow can be generated than with the lying on a smaller pitch circle diameter, because on the larger pitch circle diameter, a larger stroke of the piston with the past on a large 'pitch circle diameter cylinders is achievable, if not for other reasons, for example because of the length of the piston or due to a different pivotability of the swash plate body, there is a limitation. If it is required that both flow rates should be approximately the same size, the cylinders lying on a large pitch circle diameter can be given smaller bore diameters. It should be taken into account that the pistons lying on a large pitch circle diameter or the conditions at the cylinder openings assigned to them will represent the limit for the speed.
  • control base 2 and, on the other hand, the cradle bearing part 3 are attached to the middle part 1 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 is provided in its left part in the drawing with an internal toothing 8 which engages in the toothing of a drive shaft 9, 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 piston 19 arranged on 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, in relation to an at least approximately semicircular one Channel 23 in the control plate 6, which continues in a channel 24 in the control floor 2, the channel 24 leading to a connection, not shown in the drawing, lying next to the drawing plane.
  • 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 sliding block 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 back, 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 swash plate body 36 has a recess 41 through which an adjusting pin 42 extends, which is provided with a spherical head 43 which is guided in a bore 44 in the swash plate 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 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 can be displaced.
  • 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 so far in the radial direction that it lies both in front of the mouth channels 27 and in front of the mouth channels 22.
  • the recess 53 extends 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 one facing the suction channel 52 Side of the control plate 6 is aerodynamically designed.
  • the control floor part 2 is designed symmetrically on both sides, that is, instead of the suction channel 52 and the recess 53, there are two separate channels in the control floor part 2 and correspondingly two approximately semicircular channels corresponding to the channels 23 and 28 in the control plate 6 formed so that the pump for two-closed. Circuit is designed.
  • 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 are located 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
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
DE3026765 1980-07-15
DE19803026765 DE3026765A1 (de) 1980-07-15 1980-07-15 Axialkolbenpumpe fuer zwei foerderstroeme

Publications (2)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0090953A2 (fr) * 1982-04-02 1983-10-12 Abex Corporation Machine hydraulique à piston axial
US4617853A (en) * 1983-09-19 1986-10-21 Hydromatik Axial piston machine of the skew axis type with two independent working streams
WO2005042973A1 (fr) * 2003-10-24 2005-05-12 Brueninghaus Hydromatik Gmbh Bloc de raccordement d'une machine a piston hydrostatique
WO2012168083A3 (fr) * 2011-06-09 2013-08-15 Robert Bosch Gmbh Machine à piston axial dans un mode de construction à disque incliné
WO2014111360A1 (fr) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Machine à plateau oscillant
NL2014672A (en) * 2015-04-20 2016-10-24 Forage Innovations Bv Hydraulic fluid distributor and hydraulic fluid distributing method.

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
GB2134188B (en) * 1983-01-27 1986-09-10 Linde Ag An adjustable axial piston machine of the inclined swash plate type
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
US7140343B2 (en) * 2002-05-28 2006-11-28 R. Sanderson Management, Inc. Overload protection mechanism
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
JP4808708B2 (ja) * 2004-05-26 2011-11-02 アール サンダーソン マネージメント インコーポレイテッド 可変ストロークおよびクリアランス機構
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
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
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

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2445281A (en) * 1945-10-04 1948-07-13 Charles H Rystrom Hydraulic pump
US2520632A (en) * 1945-03-22 1950-08-29 Torq Electric Mfg Company Hydraulic pump or motor
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
FR1415392A (fr) * 1964-12-03 1965-10-22 Karl Marx Stadt Ind Werke Machine hydraulique à pistons axiaux
GB1073216A (en) * 1962-11-21 1967-06-21 F W Baggett & Co Ltd Improvements relating to swash plate pumps and motors
GB1176621A (en) * 1968-01-09 1970-01-07 Karl Marx Stadt Ind Werke Improvements in or relating to Reciprocating Hydraulic Pumps or Motors
DE1625073A1 (de) * 1967-05-09 1970-02-05 Detlef Hofmann Triebwerk

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1714148A (en) * 1927-12-21 1929-05-21 Weldy Arthur Sheldon Pump
CH445298A (de) * 1962-10-09 1967-10-15 Hydrospeed Ag Rückzugvorrichtung für hydraulische Axialkolbenmaschinen
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

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
DE1625073A1 (de) * 1967-05-09 1970-02-05 Detlef Hofmann Triebwerk
GB1176621A (en) * 1968-01-09 1970-01-07 Karl Marx Stadt Ind Werke Improvements in or relating to Reciprocating Hydraulic Pumps or Motors

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0090953A2 (fr) * 1982-04-02 1983-10-12 Abex Corporation Machine hydraulique à piston axial
EP0090953A3 (en) * 1982-04-02 1984-03-28 Abex Corporation Hydraulic axial-piston machine
US4617853A (en) * 1983-09-19 1986-10-21 Hydromatik Axial piston machine of the skew axis type with two independent working streams
WO2005042973A1 (fr) * 2003-10-24 2005-05-12 Brueninghaus Hydromatik Gmbh Bloc de raccordement d'une machine a piston hydrostatique
US7437873B2 (en) 2003-10-24 2008-10-21 Brueninghaus Hydromatik Gmbh Connection block for a hydrostatic piston machine
WO2012168083A3 (fr) * 2011-06-09 2013-08-15 Robert Bosch Gmbh Machine à piston axial dans un mode de construction à disque incliné
WO2014111360A1 (fr) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Machine à plateau oscillant
NL2014672A (en) * 2015-04-20 2016-10-24 Forage Innovations Bv Hydraulic fluid distributor and hydraulic fluid distributing method.
EP3085960A1 (fr) * 2015-04-20 2016-10-26 Forage Innovations B.V. Distributeur de fluide hydraulique et procédé de distribution d'un tel fluide

Also Published As

Publication number Publication date
US4449444A (en) 1984-05-22
DE3026765A1 (de) 1982-02-11
JPS5751343A (en) 1982-03-26
EP0044070B1 (fr) 1984-02-08

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