EP2174010A1 - Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage - Google Patents

Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage

Info

Publication number
EP2174010A1
EP2174010A1 EP08785145A EP08785145A EP2174010A1 EP 2174010 A1 EP2174010 A1 EP 2174010A1 EP 08785145 A EP08785145 A EP 08785145A EP 08785145 A EP08785145 A EP 08785145A EP 2174010 A1 EP2174010 A1 EP 2174010A1
Authority
EP
European Patent Office
Prior art keywords
valve
hydrostatic machine
adjusting
machine according
return element
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Withdrawn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
EP08785145A
Other languages
German (de)
English (en)
Inventor
Michael Dürr
Clemens Krebs
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 EP2174010A1 publication Critical patent/EP2174010A1/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Withdrawn legal-status Critical Current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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0686—Control by changing the inclination of the swash 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks

Definitions

  • Hydrostatic machine with adjusting device with return element for controlling a control valve.
  • the invention relates to a hydrostatic machine with an adjusting device for adjusting the stroke volume of the hydrostatic machine, wherein the adjusting device has a return element for controlling a control valve.
  • the axial piston machine has an adjusting device for adjusting the stroke volume.
  • the adjusting device for adjusting the stroke volume has a return element and a control valve.
  • the return element and the control valve cooperate to control a control pressure of the adjusting device. Due to the mechanical interaction of the return element with the control valve, a control pressure acting in the adjusting device is set.
  • the control pressure is controlled in such a way that a hard impact against a stop region is prevented.
  • further adjustment is prevented by an additional valve device by hydraulic means.
  • the valve device Upon reaching a certain position of the adjusting device, the valve device is actuated by the return element.
  • the valve device works in such a way that a further adjustment of the adjusting device in the same direction of movement is counteracted.
  • the adjusting device with a first adjusting piston, which controls the axial piston machine in the direction of larger displacement and on which the return element is arranged.
  • This feedback element performs a movement with a directional component along the first actuator piston axis.
  • Position change information of the first actuating piston are passed on mechanically through the feedback element to the control valve axial piston machine.
  • the provision of the return element with an adjusting bushing has the advantage that additional elements for exercising a pressure-dependent return force can be displaceably guided within this adjusting bushing.
  • An arm is preferably formed on the adjusting bush for actuating the valve device.
  • the valve device Through the arm of the actuating sleeve, the valve device is mechanically acted upon by a force to its activation.
  • To provide the valve means with a valve sleeve allows locking of the valve means in an adjustable position by means of the positive locking. An adjustment of the valve device is thus given in a simple manner.
  • An adjustable positive locking of the valve sleeve is used for a reliable and adjustable positioning of the valve sleeve with respect to the receiving housing. By adjusting the position of the positive locking the valve sleeve can be adjusted in its housing position such that the actuation of the valve device is set.
  • the mode of action can advantageously be selected as a hydraulic limitation of the minimum delivery volume V 9n U n .
  • a valve piston can be displaceably arranged to realize the action as a hydraulic limitation of the minimum delivery volume Vg m i n , which can be mechanically displaced by mechanical Kraftbeauschlagung by the arm of the adjusting sleeve of the return element.
  • a radially tapered portion is formed, which forms an annular gap with the valve sleeve.
  • the pressure medium can flow in the direction of the contact point between the arm of the actuating sleeve and the valve piston in a housing tank.
  • An actuating pressure chamber of the adjusting device is thereby relaxed and the function realized as a hydraulic limitation of the minimum delivery volume Vg m i n or hydraulic zero stop.
  • Fig. 1 is a perspective view of a section of a first embodiment of an axial piston according to the invention
  • FIG. 2 shows a partial section of a control valve of the axial piston machine from FIG. 1;
  • FIG. 3 shows a second partial section of the valve block from FIG. 1;
  • Fig. 5 is a perspective view of a
  • Partial section of the valve block of Figures 2 and 3. 6 shows a third section of the valve block from FIGS. 2 and 3;
  • FIGS. 7 shows a fourth section of the valve block from FIGS. 2 and 3;
  • FIG. 8 shows a fifth section of the valve block from FIG. 1;
  • FIG. 9 is another perspective view of a section of the valve block of FIG. 1;
  • FIG. 10 shows a further section of the first embodiment of an axial piston machine according to the invention.
  • FIG. 11 shows a further side view of a section of the first embodiment of an axial piston machine according to the invention.
  • Fig. 12 is a front view of the valve block of Fig. 1;
  • FIG. 13 is a side view of the front part of the valve block of FIG. 1.
  • Fig. 1 shows a hydrostatic machine according to the invention in the form of an axial piston machine 1 with a Ausschwenkkolben 2, on which a return element 3 is arranged.
  • the Ausschwenkkolben 2 forms a first actuating piston of an adjusting device and is acted upon in a control pressure chamber with a control pressure for adjusting the axial piston machine 1 in the direction of larger delivery volume.
  • an arm 5 of the adjusting bush 4 is formed.
  • the adjusting bushing 4 and the arm 5 of the adjusting bushing 4 are guided in a housing groove 19 along a valve axis of a subsequently explained valve device and Ausschwenkkolbenl Kunststoffsachse.
  • the arm 5 is arranged laterally on the adjusting bush 4 and extends in the longitudinal direction thereof.
  • the adjusting sleeve 4 is substantially perpendicular to the first actuating piston.
  • the arm 5 of the adjusting bush 4 is designed so that it can act on a movable element of the valve device 6 with a force to act together with it as a hydraulic limit, for example, a minimum delivery volume Vg 1nIn the axial piston machine 1.
  • the valve device 6 is arranged in a valve block 18 which is fastened to the housing of the axial piston machine 1.
  • the valve device 6 has a valve bushing 7 and a valve piston 8 displaceable therein along the valve axis.
  • the valve piston 8 is acted upon by a compression spring 9, which is supported at its opposite end to a screw plug 10 in the direction of a rest position.
  • At least one channel 24 is formed.
  • the channel 24 connects the valve device 6 with a second control pressure chamber 28 of the adjusting device, which is simultaneously (parallel) connected to a control valve 15.
  • a second actuating piston which is designed as Einschwenkkolben 27, acted upon by a hydraulic force.
  • About the control valve X acting in the second control pressure chamber 28 pressure is adjustable.
  • a roller 13 is movably mounted, which acts on a lever 14 of a hyperbola controller for controlling the control valve 15 variably with a dependent of the delivery pressure of the axial piston machine 1 force.
  • the lever 14 of the hyperbola controller is variably loaded by the roller 13 of the return element 3 at a jointly formed contact point with a force which is proportional to the pressure which acts on the adjusting device in the first actuating pressure chamber in the direction of maximum delivery volume.
  • the position of the common contact point between the roll 13 and the lever 14 of the Hyperbelreglers depends on the position of the Ausschwenkkolbens along the Ausschwenkkolbenachse and thus from the set delivery volume.
  • the lever 14 of the hyperbola controller is part of an angle element 30, which is rotatably mounted in a rotation axis 31.
  • the torque generated by the application of force at the point of contact between lever 14 and roller 13 is proportional to the power of the axial piston machine 1 designed as an axial piston pump.
  • valve 2 shows a side view of a partial section of a control valve X with guided in a groove 19 'of the valve block 18 actuating sleeve 4.
  • the housing groove 19 and the groove 19' are formed so that they lead the return element 3 with the valve block 18 mounted.
  • the valve sleeve 7 is slidably inserted along the valve axis in the valve block 18 and is held by a locking element 12 adjustable in a desired position relative to the valve block 18.
  • the valve piston 8 is slidably disposed along the valve axis and has a control edge 11.
  • the channel 24 of the valve sleeve 7 is connected depending on the position of the control edge 11 of the valve piston 8 with the space 29 or separated from it.
  • the space 29 has connection with the housing tank / leakage oil space.
  • a flow-through connection between the channel 24 and the housing tank thus exists when actuated valve means 6.
  • the connection is disconnected.
  • the adjustment of the pressure in the second control pressure chamber 28 for adjusting the axial piston machine 1 in the direction of minimum delivery volume then takes place exclusively by the control valve 15.
  • the space of the compression spring 9 is connected by a longitudinal and transverse bore in the piston 8 to the housing tank. Upon movement of the piston 8, a pressure equalization in the space of the compression spring 9 is ensured.
  • annular gap 29 is formed between the valve piston 8 and the valve sleeve 7, which is connected to the housing tank or a leakage oil chamber.
  • the direction of the valve block outside directed opening of the valve sleeve 7 is closed by the screw plug 10, which also forms a spring bearing for the compression spring 9.
  • the arm 5 of the adjusting bushing 4 acts on the valve piston 8 via a contact point 16 at the front end of the valve piston 8 against the resistance of the compression spring 9 in the direction of the screw plug 10 with a force along the line III-III in Fig. 2.
  • the second actuating piston 27 In a loading of the second Adjustment chamber 28 with pressure via the control valve 15, the second actuating piston 27 is acted upon by a force which exceeds the force of the first actuating piston 2.
  • the second adjusting piston 27 moves to the left in direction Vg 1nIn and, because of the resulting movement of the pivoting cradle , takes the first adjusting piston 27 to the right.
  • the valve means 6 When adjusting the Ausschwenkkolbens 2 in FIG. 2 to the right and thus an adjustment of the designed as a hydraulic pump axial piston 1 towards smaller delivery volume, the valve means 6 is actuated by the arm 5 when reaching a certain position Vgmin.
  • the second signal pressure chamber which leads to the adjustment required in the direction of minimum delivery volume, the Einschwenkkolben acting signal pressure is thereby relaxed in the housing tank. The excess of force against the first adjusting piston 2 is then no longer achieved and prevented further pivoting back.
  • the groove 19 corresponds to the housing groove 19 in position and size and leads alone or together with the housing groove 19, the adjusting bushing 4 with the guide portions 23 along the valve axis 20. In order to avoid jamming of the actuating sleeve 4, the groove 19 is made wider. The guide therefore only takes place in one of the two grooves 19, 19 ". In the sectional plane, further valves can also be seen, which are arranged in the valve block 18. Such valves can be eg pressure or delivery flow control valves of the control valve X for controlling the axial piston pump.
  • a transverse bore can be seen at the end of the valve piston 8 oriented towards the return element 3.
  • This transverse bore is connected to a relief bore introduced as a blind bore from the opposite end into the valve piston 8.
  • Fig. 4 is a perspective view of the control valve X.
  • the locking element 12 which is adjustably screwed deep into the valve block 18, locks the valve sleeve 7 in a form-locking manner by removing part of the locking element 12, e.g. a head of a socket screw with hexagon socket with minimal play, engages in a lateral recess 17 of the valve sleeve 7. It is achieved by the lock that the valve sleeve 7 assumes a fixed adjustable position relative to the valve block 18 and not by any forces or torques, which originate, for example, from the operation, axially displaced along the valve axis 20 or rotated about it.
  • the locking element 12 is fixed by means of a lock nut 32 fixed in its position in the valve block 18.
  • FIG. 5 shows a partial section of the perspective external view of the control valve X of FIG. 4.
  • Fig. 6 shows a section through the control valve X of FIG. 1. This is also the interaction of the Recognize return element 3 with the control valve 15.
  • the return element 3 leads in its adjusting bushing 4 a measuring piston 22, which is displaceable along the actuating sleeve longitudinal axis.
  • a guide section 23 formed on the outside of the measuring piston 22 serves to guide the adjusting bushing 4, which in turn is guided in the groove 19 'of the valve block 18.
  • the roller 13 is always aligned in the direction of travel.
  • the measuring piston 22 acts on the roller 13 of the return element 3 in the direction of the lever 14 of the hyperbola regulator with a force which is proportional to the delivery pressure of the pump.
  • FIG. 7 A section of the control valve X along the line VII-VII is shown in Fig. 7, below the control valve 15, the valve sleeve 7 and the valve screw 10 of the valve device 6 can be seen.
  • FIG. 8 Another section through the valve block 18 is shown in Fig. 8.
  • a recess 17 On the valve sleeve 7 is a recess 17 for the engagement of the locking element
  • FIG. 9 A perspective partial section through the valve block 18 is shown once again in FIG. 9.
  • the arm 5 and the guide portions 23 ' form a space for receiving the head portion of volumetric flask 22 with its guide surfaces 23.
  • the groove 19' of the valve block 18 leads the adjusting bush 4 along the axis 20, by a rotation of the actuating sleeve 4th about its longitudinal axis and a component of movement of the adjusting bushing 4 perpendicular to the axis 20 is prevented.
  • FIGS. 10 and 11 each show a longitudinal section of a first exemplary embodiment of an axial piston machine 1 according to the invention. For better clarity, not all reference numerals are indicated in FIGS. 10 and 11.
  • Fig. 10 shows a side view of the control valve X, Fig. 11, however, a section in a side view of the control valve X.
  • the valve block 18 of the control valve X is mounted as in Fig.l on the Axialkobenmaschine 1 such that the valve axis 20 and AusschwenkkolbenlCodesachse parallel and lie in one plane.
  • the return element 3 is arranged on Ausschwenkkolben 2 and guided in the groove 19 'of the valve block 18 and the groove 19 of the housing of the axial piston machine 1.
  • the return element 3 is approximately perpendicular to the Ausschwenkkolben 2 and is in the same plane as the AusschwenkkolbenlFigsachse and the valve axis.
  • FIG. 12 A front view of the valve block 18 is shown in FIG. 12.
  • a member 26 is formed or fixed to a second valve sleeve 7 'extending radially outward from the valve sleeve 7' and having first and second locking members 12 'and 12''. interacts.
  • the plug 10 is screwed into the valve sleeve 7 '.
  • the first locking element 12 ' is used to introduce the valve sleeve 7' in the valve block 18 and provides an adjustable positive lock against displacement of the valve sleeve 7 'from the valve block 18 out.
  • the second locking element 12 '' As a counterpart to the locking element 12' is the second locking element 12 '', which adjustable and positive locking a displacement of the valve sleeve 7 'in the valve block 18 into it.
  • the two locking elements 12 'and 12'' are designed as screws.
  • the first locking element 12 ' is screwed into a thread introduced in the valve block 18.
  • the underside of the screw head forms a stop for the element 26.
  • the second lock element 12 " likewise designed as a barrier, is screwed into a thread of the element 26.
  • the end face of the screw then acts as a stop, which is supported on the surface of the valve block 18.
  • Fig. 13 shows in a second perspective view also the inserted into the valve block 18 and held with the locking elements 12 'and 12' 'and formed on her element 26 in position valve sleeve 7'.
  • the abutment of the element 26 on the screw head and the support of the end face of the screw on the housing is clearly visible.
  • the control valve X includes a pressure, flow and power controller, which are connected in series.
  • the series circuit of pressure, flow and power controller is connected at its first end to the tank volume, at the other second end to the control pressure chamber 28 of Einschwenkkolbens 27.
  • the pressure, flow rate and power controller are each designed so that the control pressure 28 of Einschwenkkolbens 27 pressure is supplied or the other valves are relieved to the tank out.
  • the power regulator is realized by the control valve 15.
  • the second end of the series connection of the pressure flow and power regulator, which is connected to the control pressure chamber 28 of Einschwenkkolbens 27, has a parallel connection to the valve means 6, via which the pressure in the control pressure chamber 28 is supplied to the channel 24.
  • leads a connection of the channel 26 to the tank thus to the fact that in the control pressure chamber 28, a pressure build-up is not possible, or discharge takes place towards the tank.
  • the valve device 6 described acts with the return element 3, which is arranged on Ausschwenkkolben 2 of the actuator of the axial piston 1, together so that a hydraulic stop for the limitation of the minimum delivery volume V 91nIn is realized.
  • the control pressure chamber 28 on Einschwenkkolben 27 of the adjusting device of the axial piston machine 1 is connected to the channel 24 of the valve device 6. If it is so oppressed by supplying pressure medium via the control valve 15 that thereby the Ausschwenkkolben 2 and the return element 3 are moved along the valve axis 20 in the direction of the valve means 6, the arm 5 approaches the box 4 of the return element 3 the valve piston 8 of Valve device 6 on.
  • control pressure chamber 28 of the Einschwenkkolbens 27 may be connected to the operating pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Safety Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une machine hydrostatique avec un dispositif de réglage pour le réglage d'une cylindrée de la machine hydrostatique, dans laquelle le dispositif de réglage comprend un élément de retour (3) pour la commande d'une soupape de réglage (15) en fonction d'une position du dispositif de réglage. De plus, il est prévu un dispositif de soupape (6) pour le réglage d'une pression de réglage du dispositif de réglage, lequel est actionné par l'élément de retour (3).
EP08785145A 2007-08-07 2008-07-28 Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage Withdrawn EP2174010A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007037104 2007-08-07
PCT/EP2008/006195 WO2009018934A1 (fr) 2007-08-07 2008-07-28 Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage

Publications (1)

Publication Number Publication Date
EP2174010A1 true EP2174010A1 (fr) 2010-04-14

Family

ID=39865015

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08785145A Withdrawn EP2174010A1 (fr) 2007-08-07 2008-07-28 Machine hydrostatique avec dispositif de réglage avec élément de retour pour la commande d'une soupape de réglage

Country Status (6)

Country Link
US (1) US9297369B2 (fr)
EP (1) EP2174010A1 (fr)
JP (1) JP5410427B2 (fr)
CN (1) CN101772645B (fr)
DE (1) DE102008035133B4 (fr)
WO (1) WO2009018934A1 (fr)

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DE102006062065A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse
JP5982115B2 (ja) * 2011-11-25 2016-08-31 Ｋｙｂ株式会社 斜板式ピストンポンプ
DE102012021320A1 (de) * 2012-10-31 2014-04-30 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung
DE102012022694A1 (de) 2012-11-20 2014-05-22 Robert Bosch Gmbh Regelventil, insbesondere für eine elektroproportionale Schwenkwinkelregelung einer Hydromaschine
CN114934897A (zh) * 2022-03-17 2022-08-23 广东科达液压技术有限公司 基于变量柱塞泵的控制机构
DE102022203309A1 (de) 2022-04-04 2023-10-05 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Kolbenmaschine mit zweigeteilter Stellkammer

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Also Published As

Publication number Publication date
CN101772645A (zh) 2010-07-07
JP5410427B2 (ja) 2014-02-05
JP2010535963A (ja) 2010-11-25
CN101772645B (zh) 2016-09-28
WO2009018934A1 (fr) 2009-02-12
DE102008035133A1 (de) 2009-02-12
US20100202900A1 (en) 2010-08-12
DE102008035133B4 (de) 2016-10-06
US9297369B2 (en) 2016-03-29

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