EP1723335A1 - Machine a piston axial - Google Patents

Machine a piston axial

Info

Publication number
EP1723335A1
EP1723335A1 EP05715429A EP05715429A EP1723335A1 EP 1723335 A1 EP1723335 A1 EP 1723335A1 EP 05715429 A EP05715429 A EP 05715429A EP 05715429 A EP05715429 A EP 05715429A EP 1723335 A1 EP1723335 A1 EP 1723335A1
Authority
EP
European Patent Office
Prior art keywords
pressure
axial piston
piston machine
housing
cylinder
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.)
Withdrawn
Application number
EP05715429A
Other languages
German (de)
English (en)
Inventor
Jörg Dantlgraber
Rudolf SCHÄFFER
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1723335A1 publication Critical patent/EP1723335A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04B1/24—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 inclined to the main shaft axis

Definitions

  • the invention relates to an axial piston machine according to the preamble of patent claim 1.
  • Such, for example from WO 03/058034 AI known axial piston machines have two cylinder drums, in each of which a plurality of cylinders is formed.
  • the two cylinder drums are penetrated by a shaft which is connected in a rotationally fixed manner to a large number of pistons which each delimit a pressure space with the cylinders of the cylinder drums.
  • the cylinder drums are each supported on inclined surfaces, the inclination of which is selected such that the axis of rotation of the cylinder drums is set to the shaft axis.
  • the inclined surfaces supporting the cylinder drums do not rotate with the shaft or the cylinder drum, so that the pistons traverse an elliptical movement path with respect to the plane of the inclined surfaces supporting the cylinder drums.
  • the cylinder drums with the pistons lie between the two inclined surfaces, wherein these are each formed on control disks which are supported on the housing of the axial piston pump and via which the pressure medium supply and discharge takes place.
  • control disks which are supported on the housing of the axial piston pump and via which the pressure medium supply and discharge takes place.
  • the invention has for its object to provide an axial piston machine which is comparatively simple and in which the
  • two cylinder drums of the axial piston machine are each formed on an inclined surface, these inclined surfaces being in the center, i.e. are arranged in the area between the two cylinder drums and a pressure channel and a tank channel open into these inclined surfaces. Due to this central arrangement of the inclined surfaces, the ducting can be simplified considerably compared to conventional solutions, so that the costs for producing the axial piston machine are comparatively low.
  • the central arrangement means that the compressive forces acting on the two inclined surfaces essentially cancel each other out, so that the compressive forces introduced into the housing via the inclined surfaces are very low and, accordingly, the noise emissions are reduced, which is the case with conventional ones Solutions can take on an unacceptable level due to the forces introduced via the external control disks into the housing with its large noise-radiating surfaces.
  • the two end faces are formed on a control disk which is inserted centrally in the housing and which is penetrated by a shaft carrying the pistons.
  • control disk has an anti-rotation device, which is formed, for example, by a flattened portion.
  • the control disk has two control kidneys, one of which is assigned to a pressure connection and the other to a tank connection.
  • the channels connected to the pressure and tank connection open tangentially into the control kidneys.
  • the axial piston machine can also be operated as a hydraulic transformer. However, this presupposes that the control disk is rotatably received in the housing and that it has three control kidneys.
  • Figure 1 is a schematic longitudinal section through a first embodiment of an axial piston machine
  • FIG. 2 shows a simplified sectional illustration of the axial piston machine from FIG. 1;
  • Figure 3 is an enlarged detail view of the axial piston machine of Figure 1 and
  • Figures 4, 5 representations corresponding to Figures 1 and 2 of a second embodiment of an axial piston machine.
  • FIG. 1 shows a simplified longitudinal section through a first exemplary embodiment of an axial piston machine 1, for example a hydraulic pump.
  • FIG. 2 shows a geometrically imprecise section along the dash-dotted vertical line y in FIG. 1. Accordingly, the axial piston machine 1 has a housing 2 in which one
  • This shaft 6 (drive shaft for a pump) carries two cylinder drums 12, 14, the axes of rotation ZI and Z2 of which are inclined to the axis of rotation X of the shaft 6.
  • Cylinder drums 12, 14 are supported on a control disk 16 received in the center (view according to FIG. 1) in the housing 2.
  • the end faces of this control disc 16 are formed by two inclined surfaces 18, 20. According to FIG. 1, these inclined surfaces 18, 20 are set in relation to one another in such a way that the control disk 16 tapers conically downwards from the region of the housing 2 lying radially at the top.
  • Each cylinder drum 12, 14 has a plurality of cylinders 22 and 24, in each of which a piston 26, 28 is immersed.
  • the pistons 26 and 28 assigned to the cylinder drums 12, 14 are each arranged axially parallel to the shaft axis X and fastened to a flange 30, 32 which is formed in one piece with the shaft 6 or is placed thereon.
  • the pistons 26, 28 each define a pressure chamber 34, 36 with the cylinders 22, 24, which - as described in more detail below - can be connected to a pressure port P or a tank port T.
  • the two connections T, P are arranged on the cylinder housing 2 in the central plane containing the central axis Y.
  • the two connections P, T are each connected to a control kidney (tank control kidney 42 and pressure control kidney 44) via a tank channel 38 and a pressure channel 40.
  • the two channels 38, 40 each open tangentially in the associated control kidneys 42 and 44.
  • the latter encompass the shaft 6 in sections, so that a web 46 is located between their end sections located at the top in FIG. 2 and their end sections located at the bottom in FIG. 2 , 48 of the control disk 16 remains.
  • the two control kidneys 42, 44 each open into the two inclined surfaces 18, 20.
  • Axial piston machine 1 has a structure which is symmetrical with respect to the axis Y, the control disk 16 being arranged in the center, on the inclined surfaces 18, 20 of which the two
  • Cylinder drums 12, 14 are supported. This Cylinder drums interact with the pistons 26, 28, which are connected to the shaft 6 in a rotationally fixed manner via the flange 30 and 32, respectively. Since the structure of the two cylinder drums 12, 14 is identical, the constructional details are explained below with reference to the enlarged illustration according to FIG. 3, which shows the cylinder drum 14. Accordingly, this has a drum plate 50, which is supported with its left-hand end face 52 in FIG. 3 on the inclined surface 20 of the control disk 16. The drum plate 50 has a fastening hub 54 which is supported on a spherical, ie convexly curved bearing section 59 of the shaft 6 via a self-aligning bearing 56 or the like.
  • This self-aligning bearing 56 enables the axis Z2 of the axis of rotation of the cylinder drum 14 to be inclined relative to the shaft axis X.
  • An annular drum body 60 on which the cylinders 24 of the cylinder drum 14 are formed, is supported on an annular end face 58 of the drum plate 50 delimited internally by the fastening hub 54.
  • This drum body 60 can be composed of a large number of individual elements. In the solution known from WO 03/058034 AI, this drum body 60 is formed, for example, from a multiplicity of cylinder sleeves which are connected to one another via a retaining ring. The cylinder sleeves can also be supported on the drum plate 50 via spring preload and a joint. In principle, the drum body 60 can also be formed in one piece.
  • the drum body 60 or its individual body that forms the cylinders 24 lies
  • Elements do not lie flat on the ring end face 58, but only via a contact section formed by a projection 62.
  • a multiplicity of cylinders 24 are formed in the drum body 60, into which the end sections of the pistons 28 are immersed, so that a pressure space 24, 36 is delimited by the cylinders 24 and the pistons 28.
  • the pressure chamber 36 located at the bottom in FIG. 3 has the maximum volume (piston at its outer dead center, while in the relative position between piston 28 and cylinder 24 shown in FIG. 3 above, the pressure chamber 36 has its minimum volume (piston at its inner dead center).
  • connection bushings 62 which penetrate the bottom of the cylinder spaces 24 and which are slidably supported with a radial projection 64 on the inner end face of the respective cylinder 24 of the drum body 60.
  • the end section of the connecting socket 62 which is removed from the radial projection 64 is inserted into a correspondingly designed receptacle 66 of the drum plate 50.
  • a connection channel 68 opens, which, depending on the rotational position of the cylinder drum 14, can be connected to the pressure control kidney 44 or the tank control kidney 42.
  • Each piston 28 has a fastening section 70, via which it is mounted in the flange 32 of the shaft 6. Following the fastening section 70, the piston 28 is set back radially and then merges into a conical section 72, through which the piston 28 is expanded up to its maximum cross section. This maximum cross section is provided with the reference symbol 74 in FIG. Following this maximum cross section 74, the piston is then somewhat tapered again. This waisted shape of the pistons 28 is required to be at the inner dead center (FIG. 3 above) do not collide with the cylinder walls. According to FIG. 3, the pistons 28 rest against the inner circumferential surfaces of the cylinders 24 along their maximum cross section. To improve the seal, a piston ring can be provided in each case on the outer circumference of the piston 28 in this contact area.
  • the pistons 26, 28 rotate about the shaft axis X, while the two cylinder drums 12, 14 rotate about their axis ZI and Z2.
  • the cylinder drums are supported on the central control disk 16. Due to the inclined position of the cylinder drums 12, 14, the pressure space at the top in FIG. 3 is enlarged during further rotation (suction), while the pressure chamber 36 at the bottom is reduced (pressure build-up).
  • the control disk 16 is arranged such that the tank kidney 42 is connected to the increasing pressure chambers and the pressure control kidney 44 is connected to the decreasing pressure chambers. In the area of the dead centers (FIG.
  • the connection to the two connections P, T is blocked off via the webs 46, 48, so that a switchover between the pressure connection and the tank connection and vice versa can take place.
  • the pistons 26, 28 Due to the inclined position of the cylinder drums 12, 14, the pistons 26, 28 pass through an elliptical orbit with reference to the assigned inclined surfaces 18, 20.
  • the drum body 60 is designed such that the elements forming the cylinders can slide somewhat along the ring end face 58 in order to compensate for these relative movements.
  • the noise emission during the operation of the axial piston machine can be further improved with the exemplary embodiment explained with reference to FIGS. 4 and 5.
  • the exemplary embodiment shown in FIGS. 4 and 5 differs from the previously described exemplary embodiment essentially only in the configuration of the control disk 16 and the channel guide in the control disk 16.
  • the structure of the cylinder drum 12, 14 and the shaft 6 is identical to the previously described exemplary embodiment, so that only the differences are discussed below.
  • the control disk 16 is not fastened directly in the housing 2 or is formed integrally therewith, but is designed as a separate component, an insulating layer being formed between the housing 2 and the control disk 16 in the assembled state.
  • This can for example consist of an elastic Be made of plastic material that has soundproofing properties.
  • control disk 16 To prevent the control disk 16 from rotating, it is provided with a flattened portion 78, and a receptacle 80 of the housing 2 is designed accordingly.
  • the elastic insulating layer 76 is inserted into this receptacle 80 and encompasses the outer circumference of the control disk 16.
  • the control disk 16 is decoupled from the housing 2, the noise emissions can be reduced further, but in unfavorable operating conditions, it can be flattened due to the elasticity of the insulating layer 76 come to a relative rotation between the control disk 16 and the housing 2.
  • the connections T, P are placed in such a way that the pressure forces acting on the control disk 16 via the two connections T, P (in particular P) can compensate for this torque.
  • the center distance a and the cross-sectional area of the pressure channel 40 are selected, for example, such that the pressure force FH transmitted to the control disk 16 via the pressure medium at the control port P generates a torque (FH xa) which the radial force and which acts on the control disk 16 during operation the resulting torque is compensated.
  • FH xa a torque which the radial force and which acts on the control disk 16 during operation the resulting torque is compensated.
  • other measures for torque support can also be provided.
  • an axial piston machine with two cylinder drums guided in a housing, each of which can be rotated about a drum axis and which are each supported on an inclined surface which is set to a shaft axis of rotation.
  • these inclined surfaces are arranged in the area between the two cylinder drums and the channels for pressure medium supply and pressure medium discharge open into these two inclined surfaces, ie pressure medium supply and discharge occur in the center.

Landscapes

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

Abstract

La présente invention concerne une machine à piston axial comprenant deux tambours à cylindre guidés dans un logement, qui peuvent respectivement tourner autour d'un axe de tambour et s'appuient respectivement sur une surface inclinée disposée en direction d'un axe de rotation d'arbre. Selon cette invention, ces surfaces inclinées se trouvent dans la zone située entre les deux tambours à cylindre et les canaux d'alimentation et d'évacuation d'agent de pression débouchent dans ces deux surfaces inclinées, c'est-à-dire que l'alimentation et l'évacuation d'agent de pression s'effectuent de manière centrale.
EP05715429A 2004-03-03 2005-02-21 Machine a piston axial Withdrawn EP1723335A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004010373A DE102004010373A1 (de) 2004-03-03 2004-03-03 Axialkolbenmaschine
PCT/EP2005/001786 WO2005085635A1 (fr) 2004-03-03 2005-02-21 Machine a piston axial

Publications (1)

Publication Number Publication Date
EP1723335A1 true EP1723335A1 (fr) 2006-11-22

Family

ID=34877304

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05715429A Withdrawn EP1723335A1 (fr) 2004-03-03 2005-02-21 Machine a piston axial

Country Status (5)

Country Link
US (1) US20080159879A1 (fr)
EP (1) EP1723335A1 (fr)
CN (1) CN1926332A (fr)
DE (1) DE102004010373A1 (fr)
WO (1) WO2005085635A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005058938A1 (de) * 2005-11-11 2007-05-16 Brueninghaus Hydromatik Gmbh Hydrostatische Kolbenmaschine
DE102007024174B4 (de) 2006-12-11 2022-09-08 Robert Bosch Gmbh Axialkolbenmaschine mit einer Verdrehsicherung für die Steuerplatte
US20110072811A1 (en) * 2009-09-30 2011-03-31 Rs Drawings, Llc Engine driven lift gate power system
DE102010026157A1 (de) * 2010-07-06 2012-01-12 Robert Bosch Gmbh Hydrostatische Maschine, insbesondere Axialkolbenmaschine
CN107278242A (zh) * 2014-11-08 2017-10-20 蒙尼有限公司 具有改进的摆动轴向缸体的液压机器
EP3020967B1 (fr) 2014-11-11 2017-09-27 Danfoss A/S Dispositif de pompage
CN107299843A (zh) * 2015-10-07 2017-10-27 熵零控股股份有限公司 一种柱塞流体机构
CN106567740A (zh) * 2015-10-09 2017-04-19 熵零控股股份有限公司 一种柱塞流体机构
CN106567741A (zh) * 2015-10-10 2017-04-19 熵零控股股份有限公司 一种柱塞流体机构
CN106567742A (zh) * 2015-10-13 2017-04-19 熵零控股股份有限公司 一种柱塞流体机构
CN106593536B (zh) * 2015-10-14 2021-08-24 熵零控股股份有限公司 小余隙柱塞流体机构
CN106593535B (zh) * 2015-10-14 2021-06-22 熵零控股股份有限公司 主动驱动流体机构
CN106593537B (zh) * 2015-10-15 2019-04-19 熵零控股股份有限公司 柱塞流体机构
CN106593800A (zh) * 2015-10-16 2017-04-26 熵零控股股份有限公司 正反馈柱塞流体机构
CN106855108A (zh) * 2015-12-09 2017-06-16 熵零技术逻辑工程院集团股份有限公司 高压腔能量调整系统
EP4424985A1 (fr) * 2023-03-03 2024-09-04 Innas B.V. Transformateur hydraulique

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3630026A (en) * 1969-04-15 1971-12-28 Lucas Industries Ltd Hydraulic pumps and motors
DE3578004D1 (de) * 1984-02-29 1990-07-05 Shimadzu Corp Axialkolbenpumpe oder -motor mit geneigter achse.
US4624175A (en) * 1985-08-28 1986-11-25 Wahlmark Gunnar A Quiet hydraulic apparatus
DE20015343U1 (de) * 2000-09-05 2002-01-17 Liebherr-Machines Bulle S.A., Bulle Hydrostatische Axialkolbenmaschine
NL1020932C2 (nl) 2002-01-12 2003-07-15 Innas Bv Hydraulische inrichting.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005085635A1 *

Also Published As

Publication number Publication date
CN1926332A (zh) 2007-03-07
US20080159879A1 (en) 2008-07-03
WO2005085635A1 (fr) 2005-09-15
DE102004010373A1 (de) 2005-09-22

Similar Documents

Publication Publication Date Title
EP0162238B1 (fr) Machine à pistons axiaux, en particulier pompe du type à plateau incliné
EP1723335A1 (fr) Machine a piston axial
DE3015628A1 (de) Drucklager/kopplungseinrichtung und damit ausgeruestete schneckenmaschine
WO2004055369A1 (fr) Machine a piston axiaux
DE69719169T2 (de) Nockenbetriebener motor
EP2504579A2 (fr) Pompe à palettes
DE3914552A1 (de) Waelzlagerung
EP0752530A1 (fr) Machine à piston alternatif et entraînement par plateau oscillant
DE102017208755A1 (de) Hydrostatische unterstützungs- und schmierausnehmungen auf valv- segmentslauffläche
DE102013208454A1 (de) Hydrostatische Axialkolbenmaschine mit einer Zylindertrommel mit schräg zu deren Axialrichtung gelagerten Arbeitskolben und einem ebenen Steuerspiegel
EP0809736B1 (fr) Mecanisme vireur pour benne preneuse
DE3733083C2 (fr)
DE102021208481A1 (de) Förderpumpe und Kraftfahrzeug mit einer derartigen Förderpumpe
DE102021200205A1 (de) Axialkolbenmaschine mit hoher Antriebdrehzahl
EP0329208B1 (fr) Machine de nettoyage à haute pression entraînée hydrauliquement
DE10028336C1 (de) Axialkolbenmaschine
WO2015018648A1 (fr) Machine à plateau oscillant
DE102013008677A1 (de) Hydropumpe und Kolben für eine solche Hydropumpe
DE8136101U1 (de) "kupplung zur reibschluessigen drehverbindung von maschinenteilen, wie z.b. nabe und welle"
DE102018205446A1 (de) Hydrostatische Axialkolbenmaschine
DE102018205884A1 (de) Axialkolbenmaschine mit Druckentlastung in den Durchtriebsraum
DE1653492C3 (de) Als Flüssigkeits-Pumpe und/oder -Motor verwendbare Axialkolben-Einheit
DE19653591C1 (de) Fluidverteilungsapparat für hydraulische Kolbenpumpen oder -motoren
EP1178209B1 (fr) Transformateur hydraulique
DE102022201865A1 (de) Ventil und Axialkolbenmaschine mit einem Ventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20060921

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20070330

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20071010