EP2276927A1 - Tambour de cylindre à écoulement optimisé pour machines hydrostatiques à pistons - Google Patents

Tambour de cylindre à écoulement optimisé pour machines hydrostatiques à pistons

Info

Publication number
EP2276927A1
EP2276927A1 EP09730381A EP09730381A EP2276927A1 EP 2276927 A1 EP2276927 A1 EP 2276927A1 EP 09730381 A EP09730381 A EP 09730381A EP 09730381 A EP09730381 A EP 09730381A EP 2276927 A1 EP2276927 A1 EP 2276927A1
Authority
EP
European Patent Office
Prior art keywords
cylinder bore
cylinder
kidney
cylinder drum
transition
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Withdrawn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
EP09730381A
Other languages
German (de)
English (en)
Inventor
Joachim Rentschler
Peter Schlotter
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2276927A1 publication Critical patent/EP2276927A1/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Withdrawn legal-status Critical Current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
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • 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
    • F04B1/2035—Cylinder barrels
    • 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

Definitions

  • the invention relates to a cylinder drum for a hydrostatic piston engine with at least one control kidney-cylinder bore transition, which opens into a cylinder bore for receiving a piston axially displaceable therein.
  • a hydrostatic piston machine which has a cylinder drum, in which at least one cylinder bore is formed, in which a piston is moved up and down.
  • the movement of the piston is controlled by a swash plate on which the piston is supported by means of a sliding shoe.
  • the cylinder drum has at the end face from which the piston does not protrude, a contact surface with which the
  • Cylinder drum rests against a control mirror.
  • two control kidneys are formed.
  • a control kidney is designed as Zulauf ⁇ réelle while the other control kidneys is designed as a drain opening.
  • a kidney-cylinder bore transition is formed between the cylinder bore and the contact surface on the front side of the cylinder drum from which the piston does not protrude.
  • the kidney-cylinder bore transition connects the cylinder bore alternately with the Zulauf ⁇ réelle, which is connected in the case of a pump with a suction port, and the drain opening, which then with a
  • Pressure port is connected.
  • hydraulic fluid is delivered through the kidney-cylinder bore transition into the cylinder bore.
  • hydraulic fluid is delivered from the cylinder bore via the kidney-cylinder bore transition out of the cylinder bore.
  • the disclosed cylinder drum has the disadvantage that only a relatively small amount of hydraulic fluid is delivered into the cylinder bore during a downward movement of the piston in the cylinder bore.
  • only relatively little hydraulic fluid can be conveyed from one control kidney to the other.
  • the invention is therefore based on the object to provide a cylinder drum for hydrostatic piston engines, with a higher volumetric efficiency is achieved.
  • the cylinder drum according to the invention for hydrostatic piston machines comprises at least one kidney-cylinder bore transition, which opens into a cylinder bore for receiving a piston axially displaceable therein.
  • the kidney-cylinder bore transition is formed step-free and edge-free perpendicular to the flow direction.
  • the flow resistance of the kidney-cylinder bore transition is particularly low.
  • a thus flow-optimized kidney-cylinder bore transition allows faster and energetically less complex and thus more favorable Hydrauliklikkeitslust. Pressure fluid flow through the kidney-cylinder bore transition. Due to the reduced energy expenditure in the pressure medium transport, the energy efficiency of a cylinder drum according to the invention using hydrostatic piston engine is increased. A pressure medium transport into and out of the cylinder bore via the flow-optimized kidney-cylinder bore transition is thus facilitated.
  • the cylindrical drum is sintered.
  • sintering e.g. by re-applying high pressures after fabrication, a high dimensional stability or e.g. Compliance with technical tolerances or shape tolerances possible.
  • a high quality and a particularly advantageous geometric shape of the flow-optimized control kidney-cylinder bore transition are easy to manufacture.
  • a machining operation in the region of the transition from the cylinder bores to the inlet drainage openings can then be omitted.
  • the geometry of the pilot-to-cylinder bore transition is preferably selected so that the curvature of the boundary surfaces becomes minimal. In particular, there is no flat surface area.
  • the geometry is selected such that a first and a second cutting line of the control-cylinder bore transition with a plane containing the cylinder bore axis each have a first radius and a second radius.
  • the centers of the two radii are formed on different sides of the respective cutting line, wherein in addition the two radii directly merge into each other. That is, there is no rectilinear section of the section line between the two radii, but the transition from the first to the second radius forms a turning point of the section line.
  • the two radii of a cutting line are each the same size.
  • Cylinder barrel Such a straight portion improves the flow transition between the opening of the cylinder barrel and the control kidney of the control plate.
  • the opening in the cylinder drum is also kidney-shaped, and thus between the cylinder bore and the control kidney of the control plate, a kidney-shaped opening portion is formed in the cylinder barrel.
  • This kidney-shaped opening portion extends along a circumferential circle about the cylinder drum axis, which is preferably identical to the circumferential circle on which the cylinder bores are arranged. In the radial direction, therefore, the kidney-shaped opening portions are arranged approximately centrally with respect to the cylinder bores. In the circumferential direction of this circumferential circle, the longitudinal extent of the kidney-shaped opening portions is selected so that here a straight transition between the opening portion and the cylinder bore is formed. Consequently, in this area the first and second radius are infinite.
  • the kidney-cylinder bore transition consists of several sections of different geometry in the axial direction. Each section can be used for each
  • Optimizing the flow of the kidney-cylinder bore transition be designed geometrically advantageous.
  • the sections are preferably matched to one another for flow optimization.
  • at least one section is designed as a cone section or as an ellipsoid section or, more particularly, as a ball section or as a paraboloid section or as a hyperboloid section.
  • the proposed geometrical configurations of the sections give a variety of advantageous possibilities to the design of flow optimization sections.
  • a particularly flow-optimized kidney-cylinder bore transition can be achieved with a gradual adaptation of the flow cross section.
  • the exact geometric shape of a section and / or the entire kidney-cylinder bore transition can be adapted to the shape of the inlet or drain opening.
  • FIG. 1 shows a cross section through a cylindrical drum of the prior art.
  • Fig. 2 is a perspective view of a
  • FIG. 3 shows a cross section through a cylinder drum according to the invention
  • FIG. 4 shows a perspective view of a cylinder drum according to the invention
  • Cylindrical drum of the prior art with particle trajectories of a filling flow shows a cross section through a region of a further cylindrical drum of the prior art with particle trajectories of a filling flow;
  • FIG. 7 shows a cross section through a region of a cylinder drum according to the invention with particle trajectories of a filling flow
  • FIG. 8 shows a cross section through a region of a further cylinder drum according to the invention with particle trajectories of a filling flow
  • Fig. 10 is a view of the turned to a control plate
  • Fig. 1 shows a cross section through a cylindrical drum 1 of the prior art.
  • the illustrated known cylindrical drum 1 has a
  • Base 10 a neck 9 and the neck 9 with the base 10 connecting neck-body transition 11.
  • a rotationally symmetrical central recess 6 and in the neck 9, a hub 7 are formed in the base body 10, which are arranged coaxially and in succession along a common cylinder drum axis 8.
  • an opening portion 4 which may be kidney-shaped, a second portion 50 and a cylinder bore 2 arranged coaxially and sequentially in the enumerated sequence along a common cylinder bore axis 3.
  • the cylinder bore axis 3 and the cylinder drum axis 8 are arranged in parallel.
  • a cross-section of the cylinder bore 2 is larger than that of the opening portion 4.
  • the cylinder bore 2 serves to receive a piston, not shown, which in the cylinder bore 2 axially along the cylinder bore axis 3 is displaceable.
  • the piston is supported on a sliding shoe, not shown, which in turn is slidably supported on a swash plate, not shown.
  • pressure medium is conveyed through the first section 4 and the kidney-cylinder bore transition 5 into or out of the cylinder bore 2.
  • Both between the opening portion 4 and the second portion 50 and between the second portion 50 and the cylinder bore 2 are each formed perpendicular to the flow direction steps or edges. As edges are in this description
  • the illustrated known cylindrical drum 1 has the disadvantage that the kidney-cylinder bore transition 5 is not flow-optimized. This means that the flow conditions in the pressure medium flow through the kidney-cylinder bore transition 5 are unfavorable due to its geometric design with steps and edges.
  • the kidney-cylinder bore transition 5 has in particular due to the running perpendicular to the flow direction steps on unfavorable throttle properties.
  • an abrupt transition between the kidney-cylinder bore transition 5 and the cylinder bore 2 is formed by the steps or edges.
  • a flowing pressure medium can not spread so that the cylinder bore 2 completely and is filled evenly with pressure medium. There remains a first vacuum volume 14 left, which is not filled with pressure medium (see Fig. 5).
  • the degree of filling of the cylinder bore 2 is thus relatively low after completion of the pressure medium inflow.
  • emptying the cylinder bore 2 is given by the abrupt transition in the kidney-cylinder bore transition 5 the pressure medium a particular hurdle, which leads to a throttle resistance of the kidney-cylinder bore transition 5.
  • both the volumetric efficiency of the filling process of the cylinder bore 2 and the energy efficiency of the pressure medium conversion processes can be improved.
  • FIG. 2 is a perspective view of a
  • Cylinder drum 1 shown in the prior art corresponds to the known cylindrical drum 1 shown in FIG. 1.
  • the main body 10 the neck 9, the hub 7 formed in the neck 9 and the exits of the
  • Cylinder bore 2 particularly easy to recognize.
  • the neck-body transition 11 is also clearly visible.
  • FIG. 3 shows a cross section through a cylinder drum 1 'according to the invention.
  • Cylinder drum 1 ' is basically constructed similar to the known cylinder drum 1.
  • the cylinder drum 1' according to the invention comprises a basic body 10 'according to the invention and also one with this on a In the basic body 10 'according to the invention, for example, a kidney-shaped opening section 4, a flow-optimized second section 50' according to the invention and a cylinder bore 2 ', which have a first cylinder bore section 2'a and a second cylinder bore section 2 'b, arranged coaxially and in the enumerated order along the common axis 3.
  • the first and second cylinder bore portions 2'a and 2'b are produced by machining. In particular, in the second cylinder bore portion 2'b a high-quality surface is generated, since this cooperates sealingly with the piston.
  • a cylindrical drum blank is sintered, which is then machined.
  • the available volume for receiving pressure fluid in the cylinder bore 2 ' is varied by the movement of the piston.
  • the piston is supported via a sliding shoe, not shown, on a swash plate, not shown.
  • the kidney-cylinder bore transition 5 ' accordinging to the invention connects the kidney-shaped opening section 4 via the flow-optimized kidney-cylinder bore transition 5' the first cylinder bore portion 2'a.
  • the kidney-shaped opening portion 4, the flow-optimized kidney-cylinder bore junction 5 'and the first cylinder bore portion 2'a are arranged coaxially and in this order along the cylinder bore axis 3.
  • the kidney-shaped opening portion 4 has a smaller extent in the radial direction than the first cylinder bore portion 2'a of the cylinder bore 2 '.
  • the flow-optimized kidney-cylinder bore transition 5 ' has the advantage that it ensures favorable flow conditions at a pressure medium flow through the cylinder bore transition 5' due to its geometric configuration. There is no abrupt transition formed by steps or edges, which otherwise leads to vortex formation. The explained to the known cylinder drum 1 disadvantages thus do not occur. Due to the improved geometry, on the one hand, an increased degree of filling of the cylinder bore 2 'when pressure medium flows into the cylinder bore 2' and, on the other hand, less heat development in the kidney-cylinder bore transition 5 'is achieved by the lower one
  • Throttle resistance achieved. In this way, both the volumetric efficiency in the operation of the cylinder drum 1 'according to the invention and the energy efficiency of the pressure medium conversion process are increased. Overall, this increases the overall efficiency of a hydrostatic piston engine which uses the cylinder drum 1 'according to the invention.
  • FIG. 4 shows a perspective view of a cylinder drum 1 'according to the invention.
  • the cylinder drum 1' according to the invention from FIG. 4 corresponds to the cylinder drum 1 'according to the invention shown in FIG. 4 shows the basic body 10 'according to the invention, on which the neck 9 is formed.
  • the hub 7 is formed in the neck 9, the hub 7 is formed.
  • An alternative neck-body transition 11 ' is designed so that no cylinder bore 2' passes through it.
  • recesses 110 are formed in the alternative neck-body transition 11 '. Through the recesses 110 open the cylinder bores 2 'in a plane, perpendicular to the cylinder bore axis 3 surface. This will be explained below with reference to FIG. 9.
  • FIG. 5 shows a cross section through an area of a cylindrical drum 1 of the prior art with particle trajectories of a filling flow.
  • the area shown corresponds to the kidney-cylinder bore transition 5 of the known cylinder drum 1. It is illustrated by means of particle trajectories 12, the shape of a first pressure fluid flow 13, as it arises when pressure medium enters the cylinder bore 2.
  • particle trajectories 12 the shape of a first pressure fluid flow 13, as it arises when pressure medium enters the cylinder bore 2.
  • FIG. 6 shows a cross section through a region of a further prior art cylindrical drum 1 with particle trajectories of a filling flow.
  • the illustrated region comprises an opening portion 4 'which is elongated in the circumferential direction of the cylinder drum 2 and which is adapted to the geometry of the control kidneys in the control plate.
  • a second, non-rotationally symmetrical portion 50 '' connects in the further kidney-cylinder bore transition 5 '' the elongated opening portion 4 'with a cylinder bore 2' '.
  • the geometric configuration of the elongated opening portion 4 'and the non-rotationally symmetrical second portion 50' ', the incoming pressure medium in a second fluid flow 13' narrow and thus kept fast.
  • the pressure fluid jet comes at a correspondingly high speed on the piston, not shown. It also creates a non-negligible second vacuum volume 14 ', which leads to a low degree of filling and a low volumetric efficiency.
  • the throttle effect of the further kidney-cylinder bore transition 5 '' leads in this embodiment of a kidney-cylinder bore transition 5 '' to a high heat generation and thus to a low energy efficiency in pressure medium sales processes.
  • FIG. 7 shows a cross section through a region of the cylinder drum 1 'according to the invention with particle trajectories of a filling flow.
  • the illustrated kidney-cylinder bore transition 5 'of the cylinder drum 1' according to the invention is designed to optimize flow. This is the second
  • Section 50 executed step and edge free.
  • An optimized third pressure medium flow 13 '' which flow-optimized in the onset of pressure medium in the cylinder bore 2 'from the step and edge-free geometric design of the kidney-hollow cylinder transition 5 'according to the invention results, is illustrated by particle trajectories 12.
  • the pressure medium jet entering from the kidney-shaped opening section 4 into the second section 50' according to the invention and then into the cylinder bore 2 ' can widen faster than in the case illustrated in FIG. 5. In the cylinder bore 2 'thereby creates a very small third
  • Vacuum volume 14 '' Vacuum volume 14 ''.
  • the cylinder bore 2 ' is at least almost completely filled with pressure medium.
  • the degree of filling of the cylinder bore 2 ' is thus particularly high and the volumetric efficiency of the filling process of the cylinder bore 2' thereby likewise increased accordingly.
  • the jet widens rapidly, the pressure medium velocity in the wide regions of the third pressure medium flow 13 '' also drops.
  • the pressure medium impinges at a lower speed on the piston, not shown.
  • the throttle effect of the flow-optimized kidney cylinder bore transition 5 'according to the invention is reduced overall and thus more favorable. Due to these advantages, heat generation and thus energy losses are reduced. The energy efficiency is thereby increased.
  • FIG. 8 shows a cross section through a region of a further cylinder drum 1 'according to the invention with particle trajectories of a filling flow.
  • the region shown in FIG. 8 has the elongate opening section 4' and a second section connecting the elongate opening section 4 'with the cylinder bore 2'. not rotationally symmetric section 5 '''on.
  • the elongated opening portion 4 'and the second non-rotationally symmetric portion 5''' are formed so that the incoming pressure medium beam in a fourth pressure fluid flow 13 '''widened quickly. This leads to a slowing down of the pressure medium in the fourth Pressure fluid flow 13 '''.
  • the advantages described for FIG. 7 also occur here.
  • FIG. 9 shows a further cross section through the region of the further cylinder drum 1 'according to the invention from FIG. 8.
  • the cutting plane runs through the cylinder drum axis 8 and through the cylinder bore axis 3.
  • the kidney-shaped opening portion 4 ' forms a stepped and edgeless transition to the second, non-rotationally symmetrical portion 5' '', which in turn forms a stepped and edgeless transition to the cylinder bore 2 '.
  • Cylinder bore portion 2'a and the second cylinder bore portion 2'b of the cylinder bore 2 ' have approximately the same radius in the illustrated example after the machining of the second cylinder bore portion 2'b.
  • the stepped and edgeless transitions enable a rapid widening of an incoming pressure medium jet, which leads to the advantages explained in FIGS. 8 and 7.
  • a kidney-cylinder bore transition according to the invention consists of one or more successive sections of different geometries in the axial direction with respect to the cylinder bore axis 3.
  • individual sections are in the form of a conical section, in particular for connection of rounded sections following on both sides, as an ellipsoidal section, as a paraboloid section or as a hyperboloid section, a multiplicity of advantageously formed sections or of sequences can be used for flow optimization be achieved by sections.
  • a multiplicity of advantageously formed sections or of sequences can be used for flow optimization be achieved by sections.
  • at least two successive portions in the axial direction are formed, which in a sectional view in the longitudinal direction of the cylinder bore 2 'form a first cutting line 20 and a second cutting line 21 form oppositely curved circular arc sections.
  • the wall of the cylinder bore 2 'and the wall of the opening portion 4' to the control kidney preferably go tangentially into these curvatures.
  • the first and the second cutting lines 20 and 21 therefore have a tangent Ti or T 2 at their respective radius, which results from the boundary of the kidney-shaped opening section 4 '.
  • the cutting lines 20, 21 are formed by cutting the cylindrical drum 1 'with a plane, wherein the plane in the section shown, the cylinder drum axis 8 and the cylinder bore axis 2 contains.
  • this is essentially formed by two circular arc sections with the radii Ri and R 2 , to each of which tangentially the tangent T 2 and the cylinder bore 2 'is connected.
  • the embodiments relate to the illustrated blank of the cylindrical drum 1 ', which is sintered. After the machining, the first and second cylinder bore portions 2'a and 2'b are formed in the cylinder bore 2 ', as already explained.
  • the centers of the merge radii Ri and R 2 of the second section line 21 lie on different sides of the section line 21. In the transition from the first radius Ri in the second radius R 2 , a turning point of the second cutting line 21 is formed.
  • the two radii Ri, R 2 are preferably and as shown in the example the same size and z. B. for typical geometries of cylinder drums 1 '3 millimeters.
  • the two lines denoted by 22 and 23 represent no edges, but merely serve to illustrate the transition of the first radius in the kidney-shaped opening portion 4 'and the second radius in the cylinder bore 2', ie the position of the contact point of the tangents in the radii , In between, the location of the inflection point is indicated by dashed lines.
  • the immediate transition of the two curvatures with the radii Ri, R 2 allows the formation of the largest possible radii. Will the plane used to form the illustrated
  • Section lines 20, 21 leads, rotated about the cylinder bore axis 3, it is readily apparent that the radii Ri, R 2 change. It remains, however, that the two radii Ri, R 2 are preferably the same size.
  • the radii R x and R 2 become infinity, so that here a straight transition from the end of the kidney-shaped opening section 4' in FIG the cylinder bore 2 'takes place.
  • a flat surface 25 is formed on the side facing away from the kidney-shaped opening portion 4 'end of the cylinder bore 2'.
  • This flat surface 25 is formed around the cylinder bore 2 'by machining.
  • the flat surface 25 lies in a plane which is perpendicular to the cylinder bore axis. It serves as a contact surface for tools that are used for further machining of the cylinder bore 2 '.
  • FIG. 10 serves to clarify the position of the kidney-shaped opening sections 4 '.
  • the kidney-shaped opening sections 4 ' extend along a circumferential circle 26.
  • This ümfangsnik 26 is identical to the circumferential circle on which the cylinder bores 2 'are arranged.
  • the extension of the kidney-shaped opening sections 4 'in the radial direction which corresponds to the width of the kidney-shaped opening sections 4', is smaller than the diameter of the cylinder bores 2 '.

Landscapes

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

Abstract

L'invention concerne un tambour de cylindre (1') pour une machine hydrostatique à pistons présentant au moins une transition (5', 5'', 5''') entre l'élément de commande réniforme et l'alésage du cylindre qui débouche dans un alésage de cylindre (2', 2'a) pour recevoir un piston qui peut s'y déplacer axialement, la transition (5', 5'', 5''') entre l'élément de commande et l'alésage du cylindre étant configurée sans gradin et sans arête perpendiculairement à la direction d'écoulement.
EP09730381A 2008-04-11 2009-04-08 Tambour de cylindre à écoulement optimisé pour machines hydrostatiques à pistons Withdrawn EP2276927A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008018384 2008-04-11
PCT/EP2009/002604 WO2009124745A1 (fr) 2008-04-11 2009-04-08 Tambour de cylindre à écoulement optimisé pour machines hydrostatiques à pistons

Publications (1)

Publication Number Publication Date
EP2276927A1 true EP2276927A1 (fr) 2011-01-26

Family

ID=40764267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09730381A Withdrawn EP2276927A1 (fr) 2008-04-11 2009-04-08 Tambour de cylindre à écoulement optimisé pour machines hydrostatiques à pistons

Country Status (6)

Country Link
US (1) US8777588B2 (fr)
EP (1) EP2276927A1 (fr)
JP (1) JP5065522B2 (fr)
CN (1) CN101990601B (fr)
DE (1) DE102009016978B4 (fr)
WO (1) WO2009124745A1 (fr)

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US8668469B2 (en) * 2011-04-28 2014-03-11 Caterpillar Inc. Hydraulic piston pump with reduced restriction barrel passage
US8919113B2 (en) 2011-06-28 2014-12-30 Caterpillar Inc. Hydraulic control system having energy recovery kit
US9068575B2 (en) 2011-06-28 2015-06-30 Caterpillar Inc. Hydraulic control system having swing motor energy recovery
US8850806B2 (en) 2011-06-28 2014-10-07 Caterpillar Inc. Hydraulic control system having swing motor energy recovery
US8776511B2 (en) 2011-06-28 2014-07-15 Caterpillar Inc. Energy recovery system having accumulator and variable relief
US9139982B2 (en) 2011-06-28 2015-09-22 Caterpillar Inc. Hydraulic control system having swing energy recovery
CN105134583B (zh) * 2015-09-21 2017-05-10 福州大学 一种斜盘式柱塞泵的柱塞副润滑冷却结构

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JPH0486379A (ja) * 1990-07-25 1992-03-18 Toyota Autom Loom Works Ltd アキシャルピストンポンプ
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US5829960A (en) * 1996-04-30 1998-11-03 Tecumseh Products Company Suction inlet for rotary compressor
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KR100922213B1 (ko) * 2003-06-13 2009-10-20 엘지전자 주식회사 밀폐형 압축기

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Also Published As

Publication number Publication date
CN101990601B (zh) 2013-12-11
US8777588B2 (en) 2014-07-15
JP2011516783A (ja) 2011-05-26
DE102009016978A1 (de) 2009-10-15
DE102009016978B4 (de) 2018-02-01
JP5065522B2 (ja) 2012-11-07
US20110030644A1 (en) 2011-02-10
CN101990601A (zh) 2011-03-23
WO2009124745A1 (fr) 2009-10-15

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