EP1219831A2 - Dispositif de réglage de la course pour une machine hydrostatique à débit variable - Google Patents

Dispositif de réglage de la course pour une machine hydrostatique à débit variable Download PDF

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Publication number
EP1219831A2
EP1219831A2 EP01128167A EP01128167A EP1219831A2 EP 1219831 A2 EP1219831 A2 EP 1219831A2 EP 01128167 A EP01128167 A EP 01128167A EP 01128167 A EP01128167 A EP 01128167A EP 1219831 A2 EP1219831 A2 EP 1219831A2
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EP
European Patent Office
Prior art keywords
control
spring
piston
control piston
pressure
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
EP01128167A
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German (de)
English (en)
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EP1219831A3 (fr
EP1219831B1 (fr
Inventor
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1219831A2 publication Critical patent/EP1219831A2/fr
Publication of EP1219831A3 publication Critical patent/EP1219831A3/fr
Application granted granted Critical
Publication of EP1219831B1 publication Critical patent/EP1219831B1/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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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

Definitions

  • the invention is based on an adjusting device the genus of the main claim.
  • Adjustment devices that have an actuating piston, the on the displacement of a hydrostatic machine acts are known. By a pressure difference between two signal pressure chambers, each at one end Apply pressure to the actuating piston and steer the actuating piston from its neutral position and thus change that Displacement. From DE 195 40 654 C1 For example, a device is known in which the Deflection of the actuating piston via a feedback lever counteracting force generated.
  • the position is supported by a swivel Depending on the direction of the deflection, return lever to one of transfer two rocker arms arranged opposite each other.
  • the rocker arms are spring-loaded and thus generate one of the Deflection of the control piston opposing force.
  • In the control piston is a recess for receiving the Rocker arm introduced by which the restoring force on the Control piston is transmitted.
  • To generate a The pressure difference between the signal pressure chambers is the Control piston by a control pressure that in the Control pressure chambers on the front side of the control piston acts, deflects and gives the flow path of one Supply pressure line to one of the two signal pressure chambers free.
  • the adjustment device also has a centering valve and an attached switching valve. At a Pressure drop in both control lines under one through the Switching valve predetermined value is opened by opening a Relaxation line activates the centering valve. Thereby the higher pressure in the supply line to the Signal pressure chambers relieved until a pressure equilibrium is reached. The actuating piston is in its neutral position returned and the displacement of the hydrostatic machine is zero.
  • the disadvantage of the specified adjustment device is high technical effort.
  • a centering valve and a switching valve are required.
  • the spool is on its opposite ends in the valve housing.
  • the high pressures require precise processing, so no undesired leakage gaps due to component tolerances occur.
  • the production of bores at right angles to each other in the valve housing and the corresponding sealing and Bearing areas on the control piston also increase the Production expense.
  • control piston has no possibility Centering on.
  • the installation dimension is due to the manufacturing dimensions of the components. Subsequent adjustment on fully assembled valve is not provided.
  • the invention has for its object a Adjustment device to create larger tolerances are possible in the manufacture of the components without this leads to a functional impairment.
  • the multi-part control piston can cause angular errors in the Storage areas occur due to its short guide length the side of the control valve.
  • Preloading by means of centering springs is an advantage and adjusting springs is brought onto the control piston.
  • the control piston is therefore always in a through Force balance defined starting point by the Adjustment of the spring tension is adjustable and thereby on the exact installation conditions of the used Components can be tuned.
  • the independent setting option is equally advantageous the neutral position of the control valve by an in axial Directional control socket. This can according to the total length of the control spool and thus connected position of the control grooves the position of the Control valve are adjusted. The resulting one greater tolerance in the manufacture of components lowers again the cost.
  • the adjustment device can be operated with a hydraulic Control as well as with the help of proportional magnets operate. This makes a stake that is already on existing systems with control lines, possible.
  • electrical controls with Proportional solenoids or pilot valves is one additional clarification of the adjustment process by the Integration of a displacement sensor on the actuating piston possible. By correcting the control signal, a higher one Positioning accuracy achieved.
  • Fig. 1 shows schematically a first embodiment an adjusting device 1 according to the invention with a Control valve 2 and a control piston 3. With a fixed the actuating piston 3 connected return lever 4 is Control piston 3 with the control valve 2 mechanically in Operatively connected.
  • Adjustment device 1 is described in more detail with reference to 1, the structure of the adjusting device 1 in Neutral position are explained.
  • the adjusting piston 3 is with its two cylindrical ends in a first or second actuating pressure chamber recess 5a or 5b performed in a first or second Signal pressure chamber housing 6a and 6b are introduced. That from the actuating piston 3 and the first or second Signal pressure chamber recess 5a or 5b formed volume forms a first and second signal pressure chamber 7a and 7b.
  • the adjusting piston 3 has a recess 79 in which one first and second return springs 8a and 8b are arranged.
  • the return springs 8a and 8b are in the form of spirals Compression springs run with their ends on a first and second spring bearings 9a and 9b arranged one inside the other.
  • the actuating piston 3 has an end face a piston cover 10, which in the piston 3 screwed in and fixed by a locking ring.
  • the force of the return springs 8a and 8b makes the first Spring bearing 9a against the bottom of the recess 79 of the Set piston 3 pressed, the opposite second Spring bearing 9b against the actuating piston cover 10.
  • the spring bearings 9a and 9b each have a continuous, stepped receiving opening 82a and 82b, in each a spacer rod 11a and 11b protrude into the radial stage of the receiving opening 82a and 82b a corresponding increase in their radial extent exhibit.
  • the spacer rods 11a and 11b penetrate the Actuating piston 3 or the actuating piston cover 10 and are in contact each to an adjuster 12, the axial position of an adjusting sleeve 13 fixed with a lock nut 14 is changeable.
  • a cover cap 85 is on the Screwed adjusting sleeve 13.
  • the adjuster 12 becomes the relative neutral position of the Adjusting piston 3 with respect to that in a common housing fixed signal pressure chamber housings 6a and 6b set.
  • the housing is shown by the dash-dotted lines indicated.
  • the spacer bars 11a and 11b are in the actuating piston 3 and Adjusting piston cover 10 slidable in the axial direction.
  • In the illustrated neutral position of the adjusting device 1 are the two spacer rods 11a and 11b both on the respective adjuster 12 as well as at the respective level in the receiving opening 82a or 82b of the spring bearing 9a or 9b on, the spring bearings 9a and 9b simultaneously with the Piston cover 10 and the bottom of the recess 79 of the Actuating piston 3 in contact.
  • the control valve 2 has a control piston 17 on, which consists of a first spool part 18 and a second control piston part 19, which is in the axial direction are arranged sequentially and by one Piston tappets 20 are operatively connected to one another.
  • a control piston 17 on which consists of a first spool part 18 and a second control piston part 19, which is in the axial direction are arranged sequentially and by one Piston tappets 20 are operatively connected to one another.
  • In the ends of the Spool parts 18 and 19 are recesses for receiving of the piston rod 20 introduced, at least one Recess, e.g. B.
  • Control piston part 18 is in one hand Control valve cover 22 and on the opposite side in a guide recess 25 of a control bush 23 guided.
  • the control socket 23 is in one Control valve housing 24 screwed in and with a Lock nut 14 fixed.
  • the control bushing 23 has at least three holes, each with a circumferential Channel 26a to 26c connected to the guide recess 25 is.
  • Feed line 27 opens into a first rotating one Channel 26a out, a connecting line 28 into a second circumferential channel 26b and a third circumferential channel 26c is connected to a tank via a return line 29, e.g. formed by the inner volume of the housing is.
  • the feed line 27 has the in each operating state Adjustment device to a minimum pressure by a not shown device is generated, and on the the description of Fig. 3 will be discussed.
  • the second control piston part 19 forms together with the Control bush 23 a throttle valve 47 and is in the Guide recess 25 of the control bush 23 guided and points two circumferential control grooves 30a and 30b, which are spaced in the axial direction so that the Part formed in between the control grooves 30a and 30b Neutral position of the throttle valve 23 to the middle circumferential channel 26b symmetrical bore closes.
  • the axial extent of the control grooves 30a and 30b is so large that by axially moving the second control piston part 19 a connection between the Connection line 28 and the feed line 27 or between the connecting line 28 and the return line 29 can be produced.
  • the second control piston part 19 projects with the first Spool part 18 facing away from the Guide recess 25 out into a first spring space 86a the control bushing 23 and has a collar-shaped Extension 32 on which a centering spring 33 supported.
  • the first spring chamber 86a is not closer to described way connected to the tank volume to a To allow pressure equalization.
  • the second end of the Centering spring 33 is supported on an abutment 34, the the front end of one on the control bushing 23 attached proportional magnet 31 forms.
  • a sleeve 35 is arranged, the relative axial position to the abutment 34 is adjustable, and which serves as a limitation for an adjusting spring 36, the second end also on the collar-shaped Extension 32 supports.
  • a central recess of the Abutment 34 is guided by a magnetic plunger 37, the one Control force on the front end of the second Control piston part 19 transmits, which is proportional to the electrical control signal is and from that Proportional magnet 31 is generated.
  • At the opposite end of the first Control piston part 18 is one Control device 38, the structure of the above Description of the second spool part 19 side equivalent.
  • the collar-shaped extension 32 a disc 39 on the first control piston part 18, which is attached to a radial gradation of the first control piston part 18 is supported.
  • first Spring seat body 40a and a second spring seat body 40b postponed On the first control piston part 18 are a first Spring seat body 40a and a second spring seat body 40b postponed.
  • the two spring seat bodies 40a and 40b by a control spring 45 arranged between them pressed apart until the first spring seat body 40a one placed on the first control piston part 18 Limiting sleeve 41 abuts, for example, by a Snap lock in a groove 87 of the first Control piston part 18 secured against axial displacement is.
  • the second spring seat body 40b is by the Spring force pressed against a stop surface 42 by a radial expansion of the first control piston part 18 is formed.
  • the bottom 88 of the spring sleeve 43 and the stop disk 44 have central recesses that are larger than that radial dimensions of the stop surface 42 or Limit sleeve 41 and smaller than the largest radial Expansion of the spring seat body 40a and 40b are.
  • the Spring sleeve 43 is against the spring force of the control spring 45 relative to the first spool part 18 in both Directions shiftable.
  • the spring sleeve 43 has an approximately cylindrical Outer geometry and penetrates a clamping device 46, the at the end facing away from the actuating piston 3 Return lever 4 is arranged.
  • Clamping device 46 is the return lever 4 on the Spring sleeve 43 slidably and thus the relative position of return lever 4 and spring sleeve 43 to each other adjustable.
  • the clamping device 46 is in the illustrated embodiment as a slotted Eye running.
  • the movement of the control piston 17 lifts the Spring seat body 40a from the bottom 88 of the spring sleeve 43.
  • the second spring seat body 40b is supported on the Stop disc 44 and lifts through the relative to the Spring sleeve 43 displacing control piston 17 from the Contact surface 42 from.
  • the one between the two Spring seat bodies 40a and 40b build tensioned control spring 45 a counterforce against the control force of the deflecting proportional magnet 31 is until the forces are in a new state of equilibrium.
  • the opposite Spring bearing 9b is supported on the actuating piston cover 10.
  • the compression of the return springs 8a and 8b causes one Restoring force on the control piston 3.
  • Spacer bar 11a or 11b is required is one Compensating bore 89 introduced into the actuating piston 3, through a pressure equalization between the recess 79 of the Adjusting piston 3 and the interior of the housing takes place.
  • the deflection of the control piston 3 is due to the rigid Connection of the return lever 4 to the spring sleeve 43 transfer.
  • the direction of movement of the spring sleeve 43 is Deflection of the control piston 17 opposite.
  • the relative position of the spring sleeve 43 to the control piston 3 changes in the same direction as described above relative movement of the control piston 3 by the control force of the proportional magnet 31.
  • the control spring 45 is thereby further compressed and against the control force of the Proportional magnets 31 acting counterforce increases. With increasing travel of the control piston 3 is therefore the equilibrium position of the control piston 3 in the direction shifted to its neutral position.
  • the throttle valve 47 is closed further.
  • Closing the throttle valve 47 reduces the per unit time to the second Signal pressure chamber 7b replenished amount of hydraulic fluid, whereby the with increasing travel of the control piston 3 Movement of the adjusting piston 3 slows down.
  • the movement of the Actuating piston 3 is ended when the control spring 45 generated force between the spring sleeve 43 and the Control piston 17 is so large that the resulting Counterforce on the magnetic plunger 37 of the same size Taxpayer is.
  • the control piston 17 then moves through the centering springs 33 and adjusting spring 36 in its Neutral position and the throttle valve 47 is closed.
  • the actuating piston 3 reaches the differential control signal proportional deflection without overshoot.
  • the deflection takes place in the opposite direction reversed analog by a differential control signal Sign, wherein the first spool part 18 by the Proportional magnets 31 acted upon by an actuating force is that by the piston rod 20 to the second Control piston part 19 is transmitted.
  • the tax groove 30 connects the connecting line 28 with the Return line 29 and so relaxes the second Signal pressure chamber 7b in the tank.
  • the pressure in the first Signal pressure chamber 7a is larger than that in the second Signal pressure chamber 7b, so that the resulting actuating force Actuating piston 3 in the direction of the second actuating pressure chamber 7b deflects.
  • the control piston 17 has one that cannot be influenced Total length that fluctuate due to manufacturing tolerances can. So that both proportional magnets 31 in their ideal Distance can be adjusted.
  • the Proportional magnet 31 on the first side Control piston part 18 is for this purpose via a threaded connection connected to the control valve cover 22 and with a Fix lock nut 14.
  • the position of the throttle valve-side proportional magnet 31, which with the Control bush 23 is connected, relative to the control piston 17 is relative to that by the position of the control bushing 23 Control housing 24 adjustable by a threaded connection.
  • Balancing the spring forces for the neutral position is done by adjusting the relative position of the Sleeves 35 to the abutments 34, so that a through Setting the stroke range of the proportional solenoids 31 changed spring tension of the centering springs 33 a compensating correction of the preload of the adjusting springs 36 can be achieved.
  • the an influence on the neutral position of the throttle valve 47 can have the connection between the throttle valve-side proportional solenoids 31 and Control socket 23 can also be made adjustable.
  • the two to each other have pointing ends of the spool parts 18 and 19 for this purpose recesses, the addition of the lengths of the Recesses is smaller than the length of the Piston tappet 20.
  • At least one of the recesses is designed as a compensation receptacle 15 and has a radial Expansion that is large enough to accommodate the angular error and the offset of the central axes of the two control piston parts 18 and 19 to be able to compensate, without that between the two Spool parts 18 and 19 transverse forces are transmitted.
  • FIG. 2 shows a second exemplary embodiment, whereby instead of the control devices 38 with Proportional magnets 31 provided a hydraulic solution is. Components not shown in FIG. 2 correspond to in Design and function of those described in Fig. 1.
  • Control piston 17 with a deflecting control force is on the throttle valve-side end of the control piston 17 a Control pressure chamber 51 arranged.
  • the control pressure chamber 51 is formed by a recess in the control bushing 23 is closed by a screwed spring tensioner 53.
  • the spring tensioner 53 has a guide for guiding the centering spring 33 a cylindrical extension that goes into the interior of the Centering spring 33 protrudes.
  • On the opposite Page is an analog control device 38 in the Control valve cover 22 arranged. By changing the axial position of the spring tensioner 53 becomes the preload of the two centering springs 33 in the neutral position of the Control piston 17 set.
  • the control pressure chamber 51 is through a hole, not shown, with a Supply groove 52 connected.
  • pilot valve 49 To generate the required control pressure in the Control pressure chamber 51 is a pilot valve 49 with a Supply hole 50 connected.
  • the pilot valve 49 is electrically controllable and can for example consist of two Proportional pressure relief valves or a servo pilot valve exist according to the principle of the baffle plate.
  • the at the end facing away from the throttle valve 47 Control piston 17 correspondingly constructed control device 38 is connected via a control pressure line 54 to the Pilot valve 49 connected.
  • the pilot valve 49 generates between the Control pressure chambers 51 a pressure difference that one of the Pilot valve 49 received electrical signal equivalent.
  • the Control piston 17 is subjected to an axial control force, to a deflection of the control piston 17 and a Opening of the throttle valve 47 leads.
  • the actuating movement of the Actuating piston 3 and the build-up of restoring forces corresponds to the functionality described in FIG Adjustment device 1.
  • FIG Embodiment a displacement sensor 55 on the Adjustment device 1 arranged.
  • the displacement sensor 55 is firmly connected to the housing of the adjusting device 1 and has a spring-loaded probe tip 56, which from the Housing of the displacement sensor 55 protrudes and in the axial Direction is shiftable.
  • the probe tip 56 is by the Spring force held in abutment with a touch surface 57 which with the central axis of the adjusting piston 3 one of zero includes different angles.
  • a deflection of the Control piston 3 from its neutral position thus leads to a relative change in the position of the stylus 56 in Regarding the displacement sensor 55.
  • the change in position is converted into an electrical signal by the displacement sensor 55 converted.
  • the two spacer bars 11a and 11b approximately cylindrical and show no change in radial Extension to.
  • a contact surface for the spring bearing 9a and 9b serve the front ends of the Spacer rods 11a and 11b, which are located at the bottom of the Support receiving openings 82a and 82b.
  • For pressure equalization is a compensating bore 89 in the spring bearing 9a and 9b introduced, the receiving openings 82a and 82b Connect to the interior of the control piston 3.
  • Fig. 3 is a section of a hydraulic circuit diagram an adjusting device 1 according to the invention.
  • Pump 58 connected, which is provided for two delivery directions and their displacement with the help of Adjusting piston 3 is adjustable.
  • To the pump 58 is one first and second main lines 61 and 62 connected, one main line 61 or 62 for one Direction of funding is provided.
  • About one each Check valves 63 and 64 are first and second Supply line 74 and 81, which on the two main lines 61 or 62 are connected, with a feed line 65 connected, with the check valves 63 and 64 at positive pressure difference of the respective supply lines 74 and 81 open opposite the feed line 65.
  • the feed line 65 is via the signal pressure line 16a with the first Signal pressure chamber 7a and with a first connection 126a Control valve 2 connected to the first rotating. Corresponds to channel 26a from FIG. 1.
  • the second signal pressure chamber 7b is over the Connection line 28, an intermediate line 78 and Signal pressure line 16b with a second connection 126b of the Control valve 2 connected to the second rotating Corresponds to channel 26b.
  • the connecting line 28 is connected to the Intermediate line 78, the intermediate line 78 in turn with the Signal pressure line 16b via control valves 67 and 66 connected.
  • Control valves 66 and 67 are assumed, in which the above. Connections are switched through and every other possible Connection is closed. Function and mode of operation of the Control valves 66 and 67 will be explained in detail later.
  • the control valve 47 has a third connection 126c. which is connected to a tank 60 via a return line 29 and corresponds to the third circumferential channel 26c.
  • the Auxiliary feed line 68 is of one for only one Delivery direction suitable auxiliary pump 59 depressed and supplies with a positive pressure difference between Auxiliary feed line 68 and feed line 65 the Feed line 65 with hydraulic fluid.
  • a positive difference signal between the two proportional magnets 31 is generated by the Deflection of the control piston 17 in the throttle valve 47 e.g. the connection 126a with the connection 126b and thus the Feed line 65 connected to the connecting line 28.
  • the second signal pressure chamber 7b is thereby the same Pressure as in that through the control pressure line 16a also connected to the feed line 65 first Control pressure chamber 7a generated and acts on the control piston 3 one corresponding to the different printed areas Positioning force that deflected him.
  • the control valve 66 To increase the pressure in the first too high Main line 61 is to prevent for the above delivery direction of the pump 58 described, the control valve 66 intended.
  • the control valve 66 operates continuously between two end positions.
  • the pressure in the first supply line 74 with the pressure in a first Comparative pressure line 70 compared, the force on the Control valve 66 supported by an adjustable spring is.
  • a filter 75 In the first feed line 74 to the control valve 66 a filter 75 is arranged. Between the filter 75 and the Control valve 66 is the first feed line 74 via a first one Comparison pressure throttle 76 with the first Comparative pressure line 70 connected.
  • Comparative pressure line 70 with a 3/2-way Shuttle valve 72 connected the other connections with a second comparison pressure line 71 for the second Control valve 67 and a pressure limiter line 77 connected are.
  • the shuttle valve 72 that comparison pressure line 70 or 71 with the Pressure relief line 77 connected in which the greater pressure is present.
  • the pressure limiter line 77 through Pressure relief valve 73 relaxed against the tank 60, with which the pressure relief valve 73 on the Return line 29 is connected.
  • the Pressure relief valve 73 is adjustable.
  • a control signal is sent to the two proportional magnets 31 given the opposite sign, the control piston 17th in the opposite of the description above Direction deflected and through the control valve 2 a Connection between the ports 126b and 126c opened.
  • the pressure in the second actuating pressure chamber 7b is thus exceeded the signal pressure line 16b, the intermediate line 78, the Connection line 28 and the return line 29 in the Tank 60 relaxes, with the function of Control valves 66 and 67 should be neglected.
  • To the Actuating piston 3 acts an actuating force that the actuating piston 3rd moved in the direction of the second signal pressure chamber 7b.
  • the associated adjustment of the pump 58 causes Delivery of the hydraulic fluid into the second main line 62.
  • the pressure in the second feed line 81 exceeds the pressure in the feed line 65, as in the previous example is initially generated by the auxiliary pump 59, that opens Check valve 63 and that Feed line check valve 69 closes.
  • the Feed line 65 is supplied by the pump 58 and the second Main line 62 supplied via the second feed line 81.
  • the second feed line 81 connects the second main line 62 with the second control valve 67, wherein in the second Supply line 81, a second filter 82 is arranged and the second feed line 81 via a second Comparison pressure throttle 83 with the second Comparative pressure line 71 is connected.
  • a second Comparison pressure throttle 83 with the second Comparative pressure line 71 is connected.
  • About the Shuttle valve 72 and the pressure relief valve 73 is in the comparison pressure line 71 in turn a constant maximum pressure generated together with a spring force a comparison value for the pressure in the second Lead 81 and thus the second main line 62 generated.
  • the first end position of the second control valve 67 connects the connecting line 28 with the intermediate line 78 if the pressure in the second feed line 81 below the specified comparison value. This value exceeded, the second control valve 67 shifts in Direction of the second end position and connects one Pressure build-up line 84 with the intermediate line 78.
  • the feed line 65 via the Pressure build-up line 84 and the intermediate line 78 through the first control valve 66 and the control pressure line 16b to the second signal pressure chamber 7b produced.
  • the one from it resulting pressure increase in the second Signal pressure chamber 7b generates one of the force opposing force that the deflection of the Adjusting piston 3 and thus the displacement of Pump 58 reduced. As a result, the pressure drops in the second Main line 62.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
EP01128167A 2000-12-20 2001-11-27 Dispositif de réglage de la course pour une machine hydrostatique à débit variable Expired - Lifetime EP1219831B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000163525 DE10063525B4 (de) 2000-12-20 2000-12-20 Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens
DE10063525 2000-12-20

Publications (3)

Publication Number Publication Date
EP1219831A2 true EP1219831A2 (fr) 2002-07-03
EP1219831A3 EP1219831A3 (fr) 2003-12-03
EP1219831B1 EP1219831B1 (fr) 2007-06-06

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Application Number Title Priority Date Filing Date
EP01128167A Expired - Lifetime EP1219831B1 (fr) 2000-12-20 2001-11-27 Dispositif de réglage de la course pour une machine hydrostatique à débit variable

Country Status (2)

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EP (1) EP1219831B1 (fr)
DE (2) DE10063525B4 (fr)

Cited By (4)

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WO2007017197A1 (fr) * 2005-08-09 2007-02-15 Brueninghaus Hydromatik Gmbh Unite de vanne de regulation a butee alternee
CN104641110A (zh) * 2012-08-17 2015-05-20 罗伯特·博世有限公司 致动器装置和轴向活塞机
WO2015082321A1 (fr) * 2013-12-02 2015-06-11 Robert Bosch Gmbh Système hydraulique
DE102017222355A1 (de) * 2017-12-11 2019-06-13 Robert Bosch Gmbh Ansteuervorrichtung mit elektroproportionalem Regelverhalten und Doppel-Magnetspule

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DE102009006288B4 (de) 2009-01-27 2019-06-19 Robert Bosch Gmbh Verstellvorrichtung einer hydrostatischen Maschine
DE102011113637A1 (de) 2011-09-16 2013-03-21 Robert Bosch Gmbh Hydrostatische Schrägachsenmaschine
DE102012214626A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214655A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Anker für eine Aktoreinrichtung
DE102012214618A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Spule für eine Aktoreinrichtung
DE102012214622A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214628A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Anker für eine Aktoreinrichtung
DE102012214696A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Anker für eine Aktoreinrichtung
DE102012214624A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
DE102012214620A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
DE102012214698A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
DE102012214621A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh olrohr für eine Aktoreinrichtung
DE102012021320A1 (de) 2012-10-31 2014-04-30 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung
JP6912907B2 (ja) 2017-03-13 2021-08-04 Ｋｙｂ株式会社 サーボレギュレータ
JP6913527B2 (ja) 2017-06-22 2021-08-04 株式会社小松製作所 油圧ポンプおよびモータ

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CN101151464B (zh) * 2005-08-09 2010-08-25 布鲁宁赫斯海诺马帝克有限公司 具有交替止动的控制阀单元
CN104641110A (zh) * 2012-08-17 2015-05-20 罗伯特·博世有限公司 致动器装置和轴向活塞机
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CN105934585A (zh) * 2013-12-02 2016-09-07 罗伯特·博世有限公司 液压装置
DE102017222355A1 (de) * 2017-12-11 2019-06-13 Robert Bosch Gmbh Ansteuervorrichtung mit elektroproportionalem Regelverhalten und Doppel-Magnetspule

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DE10063525B4 (de) 2005-07-07
EP1219831A3 (fr) 2003-12-03
EP1219831B1 (fr) 2007-06-06
DE50112595D1 (de) 2007-07-19

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