EP0935069A2 - Machine à piston axial comportant une ouverture pour pression moyenne dans le disque de commande - Google Patents

Machine à piston axial comportant une ouverture pour pression moyenne dans le disque de commande Download PDF

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Publication number
EP0935069A2
EP0935069A2 EP99101492A EP99101492A EP0935069A2 EP 0935069 A2 EP0935069 A2 EP 0935069A2 EP 99101492 A EP99101492 A EP 99101492A EP 99101492 A EP99101492 A EP 99101492A EP 0935069 A2 EP0935069 A2 EP 0935069A2
Authority
EP
European Patent Office
Prior art keywords
pressure
opening
medium
medium pressure
pressure opening
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
EP99101492A
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German (de)
English (en)
Other versions
EP0935069A3 (fr
EP0935069B1 (fr
Inventor
Ralf Dr. Lemmen
Joachim Schmitt
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 Hydromatik GmbH
Original Assignee
Brueninghaus 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0935069A2 publication Critical patent/EP0935069A2/fr
Publication of EP0935069A3 publication Critical patent/EP0935069A3/fr
Application granted granted Critical
Publication of EP0935069B1 publication Critical patent/EP0935069B1/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
    • 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

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • Such axial piston machines usually have a cylinder drum Cylinder bores in which pistons are axially displaceable.
  • the Cylinder bores open out on a control disk via cylinder openings, which for connecting the cylinder bores with a low pressure connection and a High pressure connection is used.
  • the control disk usually has at least one in approximately kidney-shaped low-pressure opening and also approximately kidney-shaped High pressure opening.
  • a disadvantage of this training is that the further Opening is arranged exactly in the dead center position.
  • the additional injection of Pressure medium causes a pressure pulse here, which creates additional noise evokes.
  • the pressure in the pre-compression tank is also not at a defined level but depends on the frequency of emptying the Pre-compression tank and thus the speed of the axial piston machine and further from the flow rate of the pressure fluid from the high pressure line and thus from the throttle cross section of the feed line.
  • an axial piston machine to be specified, which causes only low operating noise, at which cavitation occurs the control disc is reduced and which is also suitable for very high operating pressures.
  • the object is in connection with the characterizing features of claim 1 solved with the generic features.
  • the invention is based on the knowledge that both noise development and cavitation damage can also be effectively reduced by the fact that a medium pressure opening between the dead center position and the high pressure opening is provided, the pressure on a suitable control device predetermined medium pressure is set, which is lower than that at the high pressure opening prevailing high pressure is.
  • This medium pressure level ensures that the Pressure change in the area of reversal does not suddenly change from the low pressure level to the high pressure level, but in at least two stages first of all Low pressure level to the medium pressure level and then from the medium pressure level to the high pressure level. The pressure jumps that occur are therefore smaller and thus are noise and cavitation damage are also reduced.
  • predetermined medium pressure at the medium pressure opening ensures that the pressure at the medium pressure opening of leakage losses, the speed of the Axial piston machine and the like is largely independent.
  • the mean pressure is preferably the arithmetic mean from the high pressure and low pressure. This ensures that the jump from the low pressure level to the medium pressure level is the same as the jump from that Medium pressure level to the high pressure level and the pressure jumps thus occurring are as low as possible.
  • the low pressure opening and the High pressure opening it is also possible between the low pressure opening and the High pressure opening to provide several medium pressure openings, which in the direction of rotation Cylinder drum are arranged offset from one another.
  • This has the advantage that the Change from the low pressure opening to the high pressure opening in more than two Pressure jumps is carried out. The height of the individual pressure jumps is even lower and noise and cavitation damage are counteracted even better.
  • Claim 4 advantageous if the pressures at the medium pressure openings in the direction of rotation rise from the dead center position to the high pressure opening.
  • the pressure difference between the individual medium pressure openings is according to claim 5 preferably constant, so that equidistant medium pressure levels arise.
  • the medium pressure can according to claim 6 of that in the high pressure opening prevailing high pressure can be derived by a pressure control valve between the High pressure opening and the at least one medium pressure opening is arranged. If the Pressure at the medium pressure opening exceeds the specified medium pressure level, the pressure control valve closes until the pressure falls below the specified medium pressure falls off. In this way, the medium pressure is exactly at the specified pressure level adjusted.
  • the relationship between the high pressure and the medium pressure is given by the Area ratio on a valve spool of the pressure control valve in a simple manner definable.
  • the pressure in the medium-pressure opening can also be achieved by a conveying process the axial piston machine because every cylinder bore in the area the medium pressure opening arranged between the dead center position and the high pressure opening emits a partial volume flow to the medium pressure opening and thus to the Medium pressure opening builds up a pressure level.
  • This pressure level is then appropriate Claim 8 by a suitable pressure relief valve on the given Limit medium pressure.
  • a pressure control valve be provided to provide a connection between the medium pressure opening and a hydraulic unit, in particular an adjusting device for adjusting the Displacement of the axial piston machine, then interrupt if the pressure at the medium pressure opening exceeds a predetermined pressure level.
  • the medium pressure openings over the Arrange low pressure opening and the high pressure opening radially offset.
  • the length of the Cylinder openings in the area of overlap with the medium pressure openings are then determined the time interval during which the respective mean pressure at the cylinder openings is held. From DE 42 29 544 A1 it is known a radial extension of the Use cylinder bores to fill a pre-compression tank. In the In contrast, the present invention will link to the Medium pressure circuit manufactured and by this arrangement the for the multi-stage Reversal in the circumferential direction reduces the installation space required.
  • FIG. 1 shows the typical structure of an axial piston machine, in which the further development according to the invention can be implemented.
  • the axial piston machine generally provided with the reference number 1, comprises a Housing 13 in which a cylinder drum 3 is rotatably mounted.
  • a cylinder drum 3 In the cylinder drum 3, essentially axially extending cylinder bores 4 are formed, in which pistons 5 are movable, which slide shoes 6 on one in their Support the tilt swashplate 7.
  • a connection block In a connection block is a Low pressure connection 16 and a high pressure connection 17 are formed.
  • a control disc 8 is arranged in which has a substantially kidney-shaped high pressure opening 18 and also in the substantially kidney-shaped low pressure opening 19 are formed.
  • the cylinder drum 3 is rotatably connected to a shaft 10.
  • the shaft 10 is by means of a first bearing 11 and a second bearing 14 in the housing 13 and the connection block 9 rotatable stored.
  • An adjusting device 12 is used to adjust the angle of inclination Swashplate 7 and thus for adjusting the displacement volume Axial piston machine 1.
  • the invention relates to a development on the control disc 8.
  • the direction of rotation Cylinder openings 15 are illustrated by arrow 38.
  • the control disk 8 is in accordance with a first embodiment of the invention in Fig. 2 is shown again in a plan view with the hydraulic circuit.
  • the Dash-dot line 20 in FIG. 2 marks the first dead center position and the second dead center position 22 of the pistons 5.
  • the pistons 5 return at the dead center positions 21 and 22, respectively their direction of movement.
  • the pistons 5 reach the first dead center position 21 their maximum piston stroke with the maximum volume of the cylinder bores 4.
  • the pressure fluid is released from the Cylinder bores 4 via the cylinder openings 15 shown in FIG. 1 and the Openings of the control disk 8 pushed out.
  • the second dead center position 22 reverses the movement of the pistons 5 in turn and the pistons 5 begin with a suction movement.
  • Control device is provided, which the pressure at the medium pressure opening 23 to a predetermined medium pressure MD between the one with the low pressure connection 16 connected low pressure opening 19 prevailing low pressure ND and that at the high pressure opening 18 prevailing high pressure HD regulates. It is preferably at the Medium pressure opening 23 prevailing medium pressure MD approximately the arithmetic mean of the at the high pressure opening 18 prevailing high pressure HD and that at the low pressure opening 19 prevailing low pressure ND or about half of that at the High pressure opening 18 prevailing high pressure HD.
  • the control device comprises in the embodiment shown in FIG. 2 a pressure regulating valve to the medium pressure MD from the high pressure HD to derive.
  • the pressure control valve 24 is provided with a throttle point 25 first connecting line 26 with the high-pressure opening 18 or the high-pressure connection 17 and connected to the medium pressure opening 23 via a second connecting line 27.
  • first connecting line 26 and the second connecting line 27 there is a valve slide 28, the connection in its right stop position closes between the first connecting line 26 and the second connecting line 27 and when you move to the left, this connection is released.
  • the position of the valve slide 28 is determined by the pressure difference between the Pressure in a first valve chamber 29 and the pressure in a second valve chamber 30.
  • the first valve chamber 29 is connected to the via a third connecting line 31 Medium pressure port 23 connected, while the second valve chamber 30 via the first Connecting line 26 with the high pressure opening 18 or the high pressure connection 17 in Connection is established.
  • the valve slide 28 blocks the connection between the High pressure opening 18 and the medium pressure opening 23, if the at the Medium pressure opening prevailing medium pressure multiplied by the area A1 of the Valve slide 28 on the first valve chamber 29 is larger than that on the high pressure opening 18 prevailing high pressure HD multiplied by the area A2 of the valve spool 28 on the second valve chamber 30.
  • the valve slide 28 opens this connection when the medium pressure MD is lower.
  • the ratio of itself to the Medium pressure opening 23, which adjusts the medium pressure to that at the high pressure opening 18 prevailing high pressure is therefore inversely proportional to the ratio of the Areas A1 and A2.
  • the area A2 is preferably dimensioned twice as large as the area A1, so that the Medium pressure MD half of the high pressure prevailing at the high pressure opening 18 HD is.
  • the control device includes that shown in FIG Embodiment also a pressure relief valve 32 to secure the at the Medium pressure opening 23 prevailing medium pressure compared to one through the adjustable Spring 33 predetermined maximum pressure. If the medium pressure MD exceeds this predetermined maximum pressure, the medium pressure MD does not increase even if the high pressure HD at the high pressure opening 18 increases further.
  • the pressure relief valve 32 can the pressurized fluid into a pressurized fluid tank 34 and / or via a Connection line 35 into the low-pressure opening 19 or the low-pressure connection 16 drain.
  • control plate 8 The function of the control plate 8 further developed according to the invention together with the Control device 24, 32 according to the invention is as follows:
  • the cylinder openings 15 If the cylinder openings 15 exceed the dead center position 21, they do not immediately connected to the high pressure opening 18, but first to the medium pressure opening 23, at which a predetermined medium pressure level prevails, the pressure level between the low pressure ND and the high pressure HD and preferably as arithmetic mean between the high pressure HD and the low pressure ND respectively half of the high pressure HD is dimensioned.
  • the change from the low pressure side to the High-pressure side therefore takes place for the cylinder openings 15 in two pressure jumps first from the low pressure level to the medium pressure level and then from that Medium pressure level to the high pressure level. By grading this pressure change the pressure pulsations that occur are reduced and there is less Noise development. Possible cavitation damage is also counteracted.
  • the medium pressure is the height by the inventive Control device 24, 32 precisely defined and dependent on the high pressure Leakage losses and the speed of the axial piston machine 1 are largely independent.
  • the level of the medium pressure level can therefore be suitably dimensioned Pressure control valve 24 can be optimized.
  • the time interval during which the Medium pressure MD acts on the cylinder openings 15 by suitable dimensioning of the Length of the medium pressure opening 23 can be optimized.
  • each Medium pressure opening 23 can have a pressure control valve 24 assigned.
  • a simplification can be that only that Medium pressure level of the medium pressure opening adjacent to the high pressure opening 18 one pressure control valve 24 is specified and the pressure levels of the other Medium pressure openings each through a throttle section depending on the highest Medium pressure level is set.
  • the medium pressure MD obtained by means of the control valve 24 can correspond to one Further development of the invention according to the invention at the same time to supply further hydraulic units are used because of their constructive design are not suitable for direct connection to the high pressure connection 17.
  • the Task of generating the medium pressure MD for the medium pressure opening 23 and Generation of a suitable reduced pressure to supply the hydraulic Units are then fulfilled by a single pressure control valve 24 at the same time.
  • the Connection line for these hydraulic units, especially for the adjustment device 12 of the axial piston machine 1 is in FIG. 2 through the line 36 illustrated.
  • the medium pressure MD is about Pressure control valve 24 obtained from the high pressure HD.
  • the medium pressure MD generated can be used simultaneously Supply of other hydraulic units, especially the adjustment device 12 serve the axial piston machine 1.
  • the aggregate is the pressure control valve 24 provided that the medium pressure prevailing at the medium pressure opening 23 with the high pressure HD prevailing at the high pressure opening 18. If the exceeds Medium pressure MD a predetermined threshold, which is determined by the area ratio of the two Areas A1 and A2 are specified, the valve slide 28 closes and the to connecting line 36 supplying hydraulic units.
  • a second medium pressure opening 40 is provided between the second dead center position 22 opposite the first dead center position 21 and the low pressure opening 19 is arranged.
  • the pressure level at this second medium pressure opening 40 is preferably also based on the arithmetic mean the high pressure HD and the low pressure ND or to half the high pressure HD adjusted a control device, not shown.
  • the pressure change in the direction of the high pressure HD to the low pressure ND also takes place in two stages, see above that also counteracts noise in the area of this reversal becomes.
  • the two medium pressure openings 23 and 40 through a connecting line 41 which is preferably a throttle 42 has, connected to each other. Furthermore, at each medium pressure opening 23 or 40 a pressure expansion tank or pressurized fluid reservoir 43 or 44 connected.
  • a damping device is formed, the time constant of the damping device by the product of the storage capacity of the surge tank or pressurized fluid storage tank 43 and 44 and the throttle resistance of the throttle 42 is set. This The time constant is preferably designed so that rapid damping of the pressure pulsations he follows.
  • FIG. 5 shows a further exemplary embodiment of a control disk designed according to the invention 8. Also here are elements already described with matching reference numerals Mistake.
  • the high-pressure opening 18 through a plurality of lattice webs 50 is divided to increase the strength of the high pressure opening 18. Furthermore, both the high-pressure opening 18 and the low-pressure opening 19 counter to the direction of rotation 38 arranged beak-like groove 51 and 52 respectively. This groove 51 and 52 serves also to reduce noise and act to damage cavitation opposite.
  • both between the first dead center position 21 and the high pressure opening 18th arranged medium pressure opening 23 as well as between the second dead center position 22 and the low pressure opening 19 arranged medium pressure opening 40 opposite the High pressure opening 18 and the medium pressure opening 19 are offset radially outwards.
  • the medium-pressure openings 23 and 40 it is of course also possible for the medium-pressure openings 23 and 40 to move radially inward. 5 is the shape of one of the cylinder openings 15 drawn in dashed lines in a rotational position.
  • the cylinder openings 15 are in the embodiment shown in FIG Cross-section approximately L-shaped.
  • the cylinder openings 15 have a first Area 53, which is in a suitable rotational position with the high pressure opening 18 or Low pressure opening 19 overlaps and a second area 54, which is suitable for Rotation position with the medium pressure openings 23 and 40 overlapped.
  • the two areas 53 and 54 are different in their length and their angle of rotation position designed.
  • the length l of the area 54 is therefore independent of the length L. of section 53.
  • the time interval in which area 54 of cylinder opening 15 overlapped with the medium pressure openings 23 and 40 is therefore independent of that Opening cross section of the cylinder openings 15, as in the overlap area of the High pressure opening 18 and the low pressure opening 19 is required, dimensioned.
  • FIG. 6 shows a diagram in which the pressure at the cylinder opening 15 when changing from low pressure ND to high pressure HD is shown as a function of time t.
  • the curve 60 marks the conventional change from the low pressure side to the high pressure side without that medium pressure level MD according to the invention during the time interval ⁇ t ND - HD. Relatively large pressure pulsations can be seen after switching to high pressure.
  • the pressure curve at the cylinder opening 15 corresponds to that of the invention Further training is illustrated by curve 61.
  • the medium pressure level MD is reached.
  • the Pressure maintained at the medium pressure level MD.
  • the changeover from the medium pressure level MD to the high pressure HD takes place. How from Fig. 6 recognizable, the pressure pulsation due to the smaller step size in the reversal made in two steps much less.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP99101492A 1998-02-04 1999-01-27 Machine à piston axial comportant une ouverture pour pression moyenne dans le disque de commande Expired - Lifetime EP0935069B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19804374 1998-02-04
DE19804374A DE19804374B4 (de) 1998-02-04 1998-02-04 Axialkolbenmaschine mit Mitteldrucköffnung

Publications (3)

Publication Number Publication Date
EP0935069A2 true EP0935069A2 (fr) 1999-08-11
EP0935069A3 EP0935069A3 (fr) 2000-05-17
EP0935069B1 EP0935069B1 (fr) 2004-08-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99101492A Expired - Lifetime EP0935069B1 (fr) 1998-02-04 1999-01-27 Machine à piston axial comportant une ouverture pour pression moyenne dans le disque de commande

Country Status (2)

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EP (1) EP0935069B1 (fr)
DE (2) DE19804374B4 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002070716A (ja) * 2000-07-18 2002-03-08 Liebherr Machines Bulle Sa 流体圧作動アキシャルピストン機械
FR2834012A1 (fr) * 2001-12-24 2003-06-27 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR2834011A1 (fr) * 2001-12-24 2003-06-27 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
WO2013068211A1 (fr) * 2011-11-12 2013-05-16 Robert Bosch Gmbh Machine à piston hydrostatique
FR3000770A1 (fr) * 2013-01-08 2014-07-11 Technoboost Machine hydraulique a deux sens de rotation, comportant une chambre de pre-compression
EP2835532A4 (fr) * 2012-03-30 2016-01-27 Mitsubishi Heavy Ind Ltd Pompe hydraulique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106593852B (zh) * 2017-01-20 2018-08-28 太原理工大学 一种三油口轴向柱塞泵配流盘结构

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2333380C2 (de) 1973-06-30 1982-04-08 Eckhard 7120 Bietigheim Aschke Hydraulische Maschine
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps

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Publication number Priority date Publication date Assignee Title
FR1184733A (fr) * 1956-10-01 1959-07-24 Dispositif pour diminuer le bruit des machines à pistons multicylindriques
DE1228929B (de) * 1961-09-11 1966-11-17 Citroen Sa Einrichtung zur Geraeuschminderung bei Druckfluessigkeitsaxialkolbenmaschinen
GB1098982A (en) * 1964-06-12 1968-01-10 Dowty Technical Dev Ltd Hydraulic reciprocating pumps or motors
DE2057891A1 (de) * 1970-09-02 1972-03-09 Orrsta Hydraulik Veb K Einrichtung zur Geraeuschminderung bei einer schlitzgesteuerten hydrostatischen Kolbenpumpe
US3956969A (en) * 1974-12-09 1976-05-18 Caterpillar Tractor Co. Hydrostatic pump including separate noise reducing valve assemblies for its inlet and outlet pressure ports
JPS6085267A (ja) * 1983-09-05 1985-05-14 Daikin Ind Ltd アキシアル・ピストン機械
JPS62135674A (ja) * 1985-12-09 1987-06-18 Hitachi Constr Mach Co Ltd 液圧ポンプ・モ−タ装置
JPH0730940Y2 (ja) * 1990-11-10 1995-07-19 株式会社豊田自動織機製作所 分流ポンプ
JPH0685267A (ja) * 1992-09-04 1994-03-25 Sanyo Electric Co Ltd パワーｍｏｓｆｅｔの製造方法
JPH08284805A (ja) * 1995-04-17 1996-10-29 Hitachi Constr Mach Co Ltd アキシャルピストン型液圧回転機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2333380C2 (de) 1973-06-30 1982-04-08 Eckhard 7120 Bietigheim Aschke Hydraulische Maschine
DE4229544A1 (de) 1991-09-06 1993-03-11 Voac Hydraulics I Trollhaettan Verfahren und vorrichtung zur daempfung von stroemungspulsationen bei hydrostatischen hydraulikmaschinen des verdraengungstyps

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002070716A (ja) * 2000-07-18 2002-03-08 Liebherr Machines Bulle Sa 流体圧作動アキシャルピストン機械
FR2834012A1 (fr) * 2001-12-24 2003-06-27 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR2834011A1 (fr) * 2001-12-24 2003-06-27 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
WO2003056171A1 (fr) * 2001-12-24 2003-07-10 Poclain Hydraulics Industrie Moteur hydraulique a pistons radiaux
WO2003056172A1 (fr) * 2001-12-24 2003-07-10 Poclain Hydraulics Industrie Moteur hydraulique a pistons radiaux
US6978713B2 (en) 2001-12-24 2005-12-27 Poclain Hydraulics Industrie Hydraulic radial piston motor
US7185579B2 (en) 2001-12-24 2007-03-06 Poclain Hydraulics Industrie Hydraulic radial piston motor
WO2013068211A1 (fr) * 2011-11-12 2013-05-16 Robert Bosch Gmbh Machine à piston hydrostatique
EP2835532A4 (fr) * 2012-03-30 2016-01-27 Mitsubishi Heavy Ind Ltd Pompe hydraulique
US10788024B2 (en) 2012-03-30 2020-09-29 Mitsubishi Heavy Industries, Ltd. Fluid pressure pump
FR3000770A1 (fr) * 2013-01-08 2014-07-11 Technoboost Machine hydraulique a deux sens de rotation, comportant une chambre de pre-compression

Also Published As

Publication number Publication date
DE59910088D1 (de) 2004-09-09
EP0935069A3 (fr) 2000-05-17
DE19804374B4 (de) 2004-09-30
EP0935069B1 (fr) 2004-08-04
DE19804374A1 (de) 1999-08-12

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