EP0301310B1 - Machine à piston axiaux du type à plateaux ou axes inclinés avec des lumières de distribution et des canaux de compensation de pression - Google Patents

Machine à piston axiaux du type à plateaux ou axes inclinés avec des lumières de distribution et des canaux de compensation de pression Download PDF

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Publication number
EP0301310B1
EP0301310B1 EP88111136A EP88111136A EP0301310B1 EP 0301310 B1 EP0301310 B1 EP 0301310B1 EP 88111136 A EP88111136 A EP 88111136A EP 88111136 A EP88111136 A EP 88111136A EP 0301310 B1 EP0301310 B1 EP 0301310B1
Authority
EP
European Patent Office
Prior art keywords
passage
axial piston
piston machine
machine according
control
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
EP88111136A
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German (de)
English (en)
Other versions
EP0301310A1 (fr
Inventor
Heinz Berthold
Josef Beck
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik GmbH
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Filing date
Publication date
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0301310A1 publication Critical patent/EP0301310A1/fr
Application granted granted Critical
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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
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • 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
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0469—Other heavy metals
    • F05C2201/0475—Copper or alloys thereof
    • F05C2201/0478—Bronze (Cu/Sn alloy)

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the purpose of the pressure equalization channels is to mitigate the sudden effect of the pressure changes occurring in the cylinder chambers in the transition area between the low pressure area and the high pressure area.
  • the pressure compensation channels are used for this purpose, by means of which the cylinder chamber pressures are adapted to one another relatively gently before the cylinder opening of the respective cylinder chamber lies in the cross-sectional area of the HP channel.
  • the pressure equalization channels known from the document FR-A 2 102 718 can reduce the running noise of the axial piston machine, the pressure equalization channels lead to sealing damage to the axial piston machine, namely to erosions on the walls, which the fluid jets emanating from the pressure equalization channels hit, namely in particular beam erosion on the control channel walls in the cylinder, and cavitation erosion on the control mirror or on the control plate running surface. This damage occurs both in the pump operation and in the motor operation of the axial piston machine.
  • the invention has for its object to avoid or at least significantly reduce an above-described erosion in an axial piston machine of the type described in the introduction.
  • an additional interference jet channel the mouth of which is directed so that the liquid flows emerging from the pressure compensation channel and the interference jet channel during operation intersect, whereby at least the erosion energy of the flow of the pressure compensation channel is substantially reduced.
  • the flow energy of the interference jet channel is reduced, so that even a conceivable erosion caused by this flow can be prevented or substantially reduced.
  • the directed currents are swirled, so to speak.
  • the interference jet channel in such a way that it opens into the pressure compensation channel or also opens at a distance from the pressure compensation channel or its mouth.
  • the first case there is an intersection of the flows in the area of the pressure equalization channel
  • the second case the flows or jets intersect outside the pressure equalization channel.
  • the erosion energy of the flow or currents or the jet or jets can be significantly reduced.
  • the prerequisite is that the currents or rays intersect, i.e. the flow or jet direction of the interference jet channel is directed transversely to the flow or jet of the pressure compensation channel.
  • the flows or jets can not only enclose an essentially right angle between them, but also an acute angle or an obtuse angle. In the latter case, the effectiveness of the interference jet is more efficient than in the first case, due to the opposite flow or jet direction.
  • the configuration according to the invention is preferably suitable for pressure compensation channels in the form of notches in the control mirror which converge in particular in the direction of flow and which, owing to their particular extension, lead to the above-described jet or cavitation erosion on the wall of the control channels in the cylinder or on the control mirror surface.
  • Axial piston machines with the configuration according to the invention are therefore suitable in particular for the promotion of people-serving vehicles, especially motor vehicles, because of low running noise.
  • the essential individual parts of the axial piston machine are a housing 4 consisting of a cup-shaped housing part 2 and a housing cover 3, a housing 4 that penetrates the cup-shaped housing part 2 or the cavity 5 of the housing 4 along the central axis 6 and in the radial direction Wall 7 of the housing part 2 and in the housing cover 3 mounted drive shaft 8, a cylinder 9 with a plurality of diametrically opposed or star-shaped, substantially axially extending piston bores 11, in which appropriately sized pistons 12 are slidably supported by a supported on the housing 4 , if necessary in their angle of inclination adjustable swash plate 13 or the inclined sliding surface 14 can be driven.
  • the cylinder 9 is formed by a cylinder drum, which is arranged on the drive shaft 8 by means of a central hole and is connected in a rotationally fixed manner by a tooth coupling 15, and with its end face 16 facing away from the sliding surface 14 bears against a control mirror 17 which is on a control plate 18 is formed, which is fastened by screws or centering pins on the housing cover 3, and two supply and discharge lines 19, 21 for the fluid, in the present case hydraulic oil, the are connected to the piston bores 11 by kidney-shaped control channels 22, 23 in the control plate 18 and axial throughput channels 24, 25.
  • the kidney-shaped control channel 23 of the HD side is divided into three sections by two webs 26.
  • pressure equalization channels are present in the transition areas between the HD and LP areas, which in the present exemplary embodiment are arranged by notches 28 in the surface 29 of the control mirror 17.
  • the pressure compensation channels 27 1 , 27 2 or notches 28 extend counter to the direction of rotation 31 of the cylinder 9, specifically from the high-pressure control channel 23 in the direction of the adjacent end of the opposite low-pressure control channel 22 and in the other transition region from the low-pressure control channel 22 in the direction to the adjacent end of the opposite HP control channel 23.
  • the triangular cross section of the pressure compensation channels 27 1 , 27 2 in the present case diverges towards the associated control channel 22, 23, ie in the direction of the rotary movement (direction of rotation 31) of the cylinder 9.
  • the divergence of the pressure compensation channels 27 1 , 27 2 is achieved in that they are inclined in the direction of the associated control channel 22, 23 relative to the control mirror surface 29.
  • the length 1 of the pressure compensation channels 27 1 , 27 2 can be shorter or longer (FIG. 3) than the thickness d of the wall 32 covering them between two adjacent throughput channels 24, 25.
  • the arrangement can preferably also be such that the wall 32 clears the mouth 33 of the pressure equalization channel 27 1 extending from HD before the throughput channel 24, into which the pressure from the HD area propagates through the pressure equalization channel 27, Control channel 22 leaves. That is, at a point at which the connection between the LP control channel 22 and the throughput channel 24/25 located in the transition region is closed (see FIG. 3), the mouth 33 of the associated pressure compensation channel 27 1 is already slightly open
  • the mouth 36 of an interference jet channel, generally designated 37 is provided, which is based on the high pressure containing discharge line 21 or here from the HD control channel 22 and thus intersects the pressure compensation channel 27 1 .
  • the interference beam channel 37 is formed by an axial through-bore 38, from which a radial groove 39 leads to the discharge line 21 on the side of the control plate 18 facing away from the control mirror 17.
  • the distance a of the mouth 36 of the interference jet channel 37 from the adjacent end of the LP control channel 23 is preferably dimensioned approximately as large as the diameter b of the throughput channels 24, 25. This ensures that the interference jet channel 37 through the adjacent control edge 41 of the associated one Throughput channel 24/25 is essentially only released when the throughput channel 24/25 has left the LP control channel 22. This avoids additional volumetric losses.
  • the mouth 36 of the interference jet channel 37 in the beam direction behind the mouth 33 of the pressure compensation channel 27, namely at 46.
  • the resulting jets intersect one another outside the pressure equalization channel 27.
  • This also effectively prevents jet erosion on the piston bore wall, which is particularly important because a cylinder drum 9 is made of a relatively soft material, namely a bearing metal, for reasons of the lowest possible wear resistance like bronze.
  • the effectiveness of preventing jet erosion on the control mirror surface 17 is less efficient than when the interference jet channel 37 emerges in the pressure compensation channel 27 1 .
  • a previously described interference jet channel 37 can be omitted, because the flows or jets resulting in the operation of the axial piston pump 30 in this transition area 30 have a lesser harmful effect.
  • the configuration according to the invention is also suitable for the motor operation of an axial piston machine.
  • a pressure equalization channel 27 3 with an interference jet channel 37 in a corresponding configuration starting from the high pressure must be arranged in the transition area designated by 30, see the illustration shown.
  • both pressure equalization channels 27 1 , 27 3 are to be arranged with interference jet channels 37, the interference jet channel 27 2 not being arranged in order to avoid losses.

Landscapes

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

Claims (8)

1. Machine à pistons axiaux (1) du genre de construction à plateau oblique ou à axes inclinés, avec commande à fente et un canal (271-273) d'égalisation de pression à l'extrémité d'entrée de la fente de commande (23) à haute pression, caractérisée en ce qu'il est prévu, à l'extrémité d'entrée de la fente de commande (23) à haute pression, un canal de jet perturbateur (37) partant de la haute pression, dont l'embouchure (36) est agencée de telle sorte que les courants de fluide sortant du canal (271-273) d'égalisation de pression et du canal de jet perturbateur (37) soient sécants entre eux.
2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que l'embouchure (36) du canal de jet perturbateur (37) est disposée près de l'embouchure (33) du canal d'égalisation de pression (271-273) ou dans celle-ci.
3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le canal d'égalisation de pression (271-273) est constitué par une encoche (28) partant de la fente de commande (23) à haute pression, cette encoche étant en particulier divergente en direction de ladite fente et étant plus courte, ou de préférence plus longue, que l'épaisseur (d) de la paroi (32) entre deux canaux de débit voisins (24, 25) dans le barillet (9) des cylindres.
4. Machine à pistons axiaux selon la revendication 3, caractérisée en ce que l'embouchure (36) du canal de jet perturbateur (37) est disposée dans le canal (271-273) d'égalisation de pression, et de préférence de telle sorte que le dégagement de son recouvrement se produise seulement lorsque le canal à basse pression (22) est quitté par le canal de passage (24/25) correspondant, ou ensuite.
5. Machine à pistons axiaux selon une des revendications 1 à 4, caractérisée en ce que le sens d'écoulement de l'embouchure de sortie du canal de jet perturbateur (37) est dirigé à peu près perpendiculairement au sens d'écoulement du canal (271-27s) d'égalisation de pression.
6. Machine à pistons axiaux selon une des revendications 1 à 5, caractérisée en ce que le canal de jet perturbateur (37) présente un tronçon (39) partant à peu près tangentiellement de la haute pression (21, 23) et un tronçon (38) se prolongeant à peu près axialement.
7. Machine à pistons axiaux selon une des revendications 1 à 6, caractérisée en ce que les fentes de commande (22, 23) sont prévues dans un plateau de commande (18) et en ce que le canal de jet perturbateur (37) s'étend à l'intérieur du plateau de commande (18).
8. Machine à pistons axiaux selon la revendication 7, caractérisée en ce que le canal de jet perturbateur (37) est constitué par une forure axiale (38) et par un tronçon de canal sensiblement radial, en particulier par une rainure (39) dans la face du plateau de commande (18) éloignée des ouvertures des cylindres (24, 25).
EP88111136A 1987-07-30 1988-07-12 Machine à piston axiaux du type à plateaux ou axes inclinés avec des lumières de distribution et des canaux de compensation de pression Expired - Lifetime EP0301310B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873725361 DE3725361A1 (de) 1987-07-30 1987-07-30 Axialkolbenmaschine in schraegscheiben- oder schraegachsenbauart mit schlitzsteuerung und druckausgleichskanaelen
DE3725361 1987-07-30

Publications (2)

Publication Number Publication Date
EP0301310A1 EP0301310A1 (fr) 1989-02-01
EP0301310B1 true EP0301310B1 (fr) 1990-11-22

Family

ID=6332762

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88111136A Expired - Lifetime EP0301310B1 (fr) 1987-07-30 1988-07-12 Machine à piston axiaux du type à plateaux ou axes inclinés avec des lumières de distribution et des canaux de compensation de pression

Country Status (3)

Country Link
US (1) US4920856A (fr)
EP (1) EP0301310B1 (fr)
DE (2) DE3725361A1 (fr)

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DE4301135C2 (de) * 1993-01-18 1995-04-06 Danfoss As Hydraulische Kolbenmaschine
DE4341846C1 (de) * 1993-12-08 1995-07-13 Danfoss As Steuerspiegel für eine hydraulische Kolbenmaschine
WO1995030833A1 (fr) * 1994-05-06 1995-11-16 Caterpillar Inc. Unite hydraulique a pistons axiaux
US5435016A (en) * 1994-07-25 1995-07-25 Smith; Gregory S. Toilet flush handle cover
DE4442556C2 (de) * 1994-11-30 1999-05-27 Danfoss As Hydraulische Axialkolbenmaschine
US5593285A (en) * 1995-01-13 1997-01-14 Caterpillar Inc. Hydraulic axial piston unit with multiple valve plates
DE19521574A1 (de) * 1995-06-14 1996-12-19 Rexroth Mannesmann Gmbh Hydrostatische Maschine
DE19539442A1 (de) * 1995-10-24 1997-04-30 Sachsenhydraulik Gmbh Steuerscheibe für hydrostatische Kolbenmaschinen
JPH11210878A (ja) 1998-01-20 1999-08-03 Honda Motor Co Ltd 可変容量型油圧式変速機の油圧制御装置
JP3154329B2 (ja) * 1998-07-21 2001-04-09 川崎重工業株式会社 アキシャルピストンポンプ
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DE10251552C5 (de) * 2002-11-05 2010-07-15 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine und Steuerplatte für eine Axialkolbenmaschine
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ITRE20050110A1 (it) * 2005-10-04 2007-04-05 Orles Ferretti Sistema di distribuzione per unita' idrostatica a pistoni
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DE102010045867A1 (de) * 2010-09-17 2012-03-22 Robert Bosch Gmbh Axialkolbenmaschine
US8668469B2 (en) 2011-04-28 2014-03-11 Caterpillar Inc. Hydraulic piston pump with reduced restriction barrel passage
EP2776713B1 (fr) * 2011-11-12 2015-12-30 Robert Bosch GmbH Machine à pistons hydrostatique
US9657726B1 (en) 2013-04-19 2017-05-23 Hydro-Gear Limited Partnership Hydraulic running surface
CN103486016A (zh) * 2013-09-16 2014-01-01 同济大学 一种低噪声抗气蚀柱塞泵用配流盘
EP3056730B1 (fr) * 2015-02-11 2020-05-20 Danfoss A/S Dispositif hydraulique
CH711662A1 (de) * 2015-10-15 2017-04-28 Liebherr Machines Bulle Sa Herstellungsverfahren für Steuerplatten einer hydraulischen Maschine.
CN106368811B (zh) * 2016-08-26 2019-01-18 北京理工大学 一种用于发动机的配流盘、液压输出机构以及发动机
DE102018109630A1 (de) * 2018-01-31 2019-08-01 Danfoss A/S Hydraulische Maschine
CN108916033B (zh) * 2018-06-22 2020-02-11 太原理工大学 可平衡转矩和缓解冲击的四配流窗口配流盘
CN108799036B (zh) * 2018-06-22 2019-08-30 太原理工大学 可平衡转矩和缓解冲击的非对称轴向柱塞泵
DE102020212630A1 (de) 2020-10-07 2022-04-07 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine

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Also Published As

Publication number Publication date
EP0301310A1 (fr) 1989-02-01
DE3725361A1 (de) 1989-02-16
US4920856A (en) 1990-05-01
DE3725361C2 (fr) 1989-07-06
DE3861117D1 (de) 1991-01-03

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