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EP1219831B1 - 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
EP1219831B1
EP1219831B1 EP01128167A EP01128167A EP1219831B1 EP 1219831 B1 EP1219831 B1 EP 1219831B1 EP 01128167 A EP01128167 A EP 01128167A EP 01128167 A EP01128167 A EP 01128167A EP 1219831 B1 EP1219831 B1 EP 1219831B1
Authority
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.)
Expired - Lifetime
Application number
EP01128167A
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German (de)
English (en)
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EP1219831A2 (fr
EP1219831A3 (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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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
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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 relates to an adjusting device according to the preamble of the main claim.
  • Adjusting devices which have an actuating piston, which acts on the displacement volume of a hydrostatic machine are known.
  • a device is known, for example, in which the deflection of the actuating piston via a return lever generates a force counteracting the setting direction.
  • the position is transmitted by a rotatably mounted return lever depending on the direction of the deflection on one of two oppositely arranged rocker arms.
  • the rocker arms are spring-loaded and thus generate a force opposing the deflection of the control piston.
  • a recess for receiving the rocker arm is introduced, through which the restoring force is transmitted to the control piston.
  • To generate a pressure difference between the control pressure chambers of the control piston is deflected by a control pressure acting in the control pressure chambers on the end face of the control piston, and releases the flow path from a supply pressure line to one of the two control pressure chambers.
  • the adjusting device furthermore has a centering valve and a switching valve attached thereto. At a pressure drop in both control lines under one through the Switching valve predetermined value is activated by opening an expansion line, the centering valve. As a result, the respective higher pressure in the supply line to the control pressure chambers is relieved until a pressure equilibrium is reached. The actuator piston is returned to its neutral position and the displacement volume of the hydrostatic machine is zero.
  • a disadvantage of the specified adjustment is the high technical complexity.
  • a centering valve and a switching valve are required.
  • control piston is guided at its opposite ends in the valve housing.
  • the high pressures require precise processing, so that component tolerances no unwanted leakage gaps occur.
  • the production of angle-true bores in the valve housing and the corresponding sealing and bearing surfaces on the control piston also increase the production cost.
  • control piston has no possibility for centering.
  • the installation dimension is determined by the manufacturing dimensions of the components. A subsequent adjustment to the fully assembled valve is not provided.
  • the invention has for its object to provide an adjustment, in which larger tolerances in the manufacture of the components are possible without this leading to a functional impairment.
  • the multi-part spool can compensate for angular errors that occur in the bearing areas due to its short guide length on the side of the control valve.
  • the admission of only one control piston part alone with the counterforce generated by the return lever is advantageous.
  • the counterforce is transmitted from the first control piston part to the second control piston part by a control piston plunger, whereby only thrust forces are transmitted.
  • the second control piston part which makes the adjustment of the throttle valve, is thus completely free of lateral forces, which can lead to premature wear.
  • An advantage is the bias, which is brought by centering springs and adjusting springs on the control piston.
  • the control piston is thus always in a defined by a balance of power starting position, which is adjustable by the adjustment of the spring tension and thus tuned to the exact installation conditions of the components used.
  • the adjusting device can be operated both with a hydraulic control and with the aid of proportional magnets.
  • an application that is based on existing systems with control lines, possible.
  • electrical controls with proportional solenoids or pilot valves an additional clarification of the setting process by the integration of a transducer on the actuator piston is possible.
  • By correcting the control signal a higher positioning accuracy is achieved.
  • Fig. 1 shows schematically a first embodiment of an adjusting device 1 according to the invention with a control valve 2 and a control piston 3.
  • the control piston 3 is mechanically in operative connection with the control valve 2.
  • the adjusting piston 3 is guided with its two cylindrical ends in a first and second Stelltikschausriseung 5a and 5b, which are introduced into a first and second Stelltikschgephase 6a and 6b.
  • the volume formed by the actuating piston 3 and the first and second actuating pressure chamber openings 5a and 5b forms a first and second actuating pressure chamber 7a and 7b, respectively.
  • the adjusting piston 3 has a recess 79 in which a first and second return spring 8a and 8b are arranged.
  • the return springs 8a and 8b are designed as spiral compression springs, are based on their ends on a first and second spring bearings 9a and 9b and are arranged inside each other.
  • the adjusting piston 3 has an end face a Stellkolbendeckel 10, which is screwed into the actuating piston 3 and fixed by a locking ring.
  • a Stellkolbendeckel 10 By the force of the return springs 8a and 8b, the first spring bearing 9a is pressed against the bottom of the recess 79 of the adjusting piston 3, the opposite second spring bearing 9b against the adjusting piston cover 10th
  • the spring bearings 9a and 9b each have a continuous, stepped receiving opening 82a and 82b, in each of which a spacer bar 11a and 11b protrude, which at the radial step of the receiving opening 82a and 82b have a corresponding increase in their radial extent.
  • the spacer rods 11a and 11b penetrate the adjusting piston 3 and the adjusting piston cover 10 and are in each case adjoining an adjuster 12 whose axial position can be changed by means of an adjusting sleeve 13 fixed with a lock nut 14. To protect a cap 85 is screwed onto the adjusting sleeve 13.
  • the relative neutral position of the actuating piston 3 is fixed relative to the adjusting pressure chamber housings 6a and 6b fastened in a common housing.
  • the housing is indicated in the illustration by the dotted lines.
  • the spacer rods 11a and 11b are displaceable in the adjusting piston 3 and the adjusting piston cover 10 in the axial direction. In the illustrated neutral position of the adjusting device. 1
  • the two spacer rods 11a and 11b are located both on the respective adjuster 12 and at the respective stage in the receiving opening 82a and 82b of the spring bearing 9a and 9b, wherein the spring bearings 9a and 9b simultaneously with the adjusting piston cover 10 and the bottom of the recess 79 of the actuating piston 3 are in contact.
  • control valve 2 has a control piston 17, which consists of a first control piston part 18 and a second control piston part 19, which are arranged successively in the axial direction and are in operative connection with each other by a control piston plunger 20.
  • a control piston 17 which consists of a first control piston part 18 and a second control piston part 19, which are arranged successively in the axial direction and are in operative connection with each other by a control piston plunger 20.
  • recesses for receiving the control piston plunger 20 are introduced, wherein at least one recess, for. B.
  • Control piston part 18 is guided on the one hand in a control valve cover 22 and on the opposite side in a guide recess 25 of a control sleeve 23.
  • the control sleeve 23 is screwed into a control valve housing 24 and fixed with a lock nut 14.
  • the control bushing 23 has at least three bores, with each of which a circumferential channel 26a to 26c is connected to the guide recess 25.
  • a fed into the control valve housing 24 feed line 27 opens into a first circumferential channel 26a, a connecting line 28 in a second circumferential channel 26b and a third circumferential channel 26c is connected via a return line 29 to a tank, for example through the inner volume of the housing educated is.
  • the feed line 27 has in each operating state of the adjusting device to a minimum pressure which is generated by a device, not shown, and will be discussed in the description of Fig. 3 yet.
  • the second control piston member 19 forms together with the control sleeve 23 from a throttle valve 47 and is guided in the guide recess 25 of the control sleeve 23 and has two circumferentially introduced control grooves 30a and 30b, which are spaced in the axial direction, that between the control grooves 30a and 30b formed part in the neutral position of the throttle valve 23 which closes the leading to the central circumferential channel 26b bore symmetrically.
  • the axial extent of the control grooves 30a and 30b is so large that a connection between the connecting line 28 and the feed line 27 or between the connecting line 28 and the return line 29 can be produced by axial displacement of the second control piston part 19.
  • the second control piston part 19 projects with its side facing away from the first control piston part 18 from the guide recess 25 out into a first spring chamber 86a of the control sleeve 23 and has a collar-shaped extension 32 on which a centering spring 33 is supported.
  • the first spring chamber 86a is connected in a manner not described in detail with the tank volume to allow pressure equalization.
  • the second end of the centering spring 33 is supported on an abutment 34 which forms the front end of a proportional solenoid 31 attached to the control sleeve 23.
  • a sleeve 35 is arranged, the relative axial position is adjustable to the abutment 34, and which serves as a limit for a setting spring 36, the second end is also supported on the collar-shaped extension 32.
  • a magnetic plunger 37 is guided, which transmits a control force to the front end of the second control piston member 19, which is proportional to the is electrical control signal and is generated by the proportional magnet 31.
  • a control device 38 which corresponds in its construction to the above description of the side of the second control piston part 19.
  • the guide of the first control piston part 18 and the formation of the second spring chamber 86 b are taken over by the control valve cover 22.
  • a disc 39 is pushed onto the first control piston member 18 instead of the collar-shaped extension 32, which is supported on a radial gradation of the first control piston member 18.
  • first spring seat body 40a and a second spring seat body 40b are pushed.
  • the two spring seat body 40a and 40b are pushed apart by a control spring 45 arranged between them until the first spring seat body 40a rests against a mounted on the first control piston member 18 limiting sleeve 41 which secured, for example by a snap closure in a groove 87 of the first control piston member 18 against axial displacement is.
  • the second spring seat body 40 b is pressed by the spring force against a stop surface 42, which is formed by a radial extension of the first control piston part 18.
  • the mutually remote surfaces of the spring seat body 40a and 40b are supported on the inside of the bottom 88 of a spring sleeve 43 on the one hand and on the other hand on a stop plate 44, which is used up to a paragraph in the spring sleeve 43 and is protected by a locking ring against axial movement ,
  • the bottom 88 of the spring sleeve 43 and the stopper plate 44 have central recesses which are larger than the radial expansions of the abutment surface 42 and the limiting sleeve 41 and smaller than the largest radial extent of the spring seat body 40a and 40b.
  • the spring sleeve 43 is displaceable against the spring force of the control spring 45 relative to the first control piston part 18 in both directions.
  • the spring sleeve 43 has an approximately cylindrical outer geometry and penetrates a clamping device 46 which is arranged on the end remote from the actuating piston 3 of the return lever 4.
  • a clamping device 46 which is arranged on the end remote from the actuating piston 3 of the return lever 4.
  • the two proportional solenoids 31 receive via their electrical plug contact 48 two identical control signals, so that the forces acting on the control piston 17 by the magnetic plunger 17 forces cancel and the control piston 17 remains in its predetermined by the adjusting springs 36 and the centering springs 33 neutral position.
  • a difference is generated between the two control signals, for example, by increasing the signal for the throttle valve side proportional solenoid 31.
  • the throttle valve side proportional solenoid 31 By the throttle valve side proportional solenoid 31, a control force on the magnetic plunger 37 is transmitted to the control piston 17, against the spring force of the opposite Centering spring 33 and adjusting spring 36 is deflected.
  • the actuating piston 3 is still in neutral position and the spring sleeve 43 is also held in its initial position via the rigidly connected to the actuating piston 3 return lever 4.
  • the spring seat body 40a lifts from the bottom 88 of the spring sleeve 43 from.
  • the second spring seat body 40b is supported on the stop plate 44 and lifts off by the relative to the spring sleeve 43 sliding control piston 17 from the contact surface 42.
  • the tensioned between the two spring seat bodies 40a and 40b control spring 45 builds up a counterforce, which is opposite to the control force of the deflecting proportional solenoid 31 until the forces are in a new state of equilibrium.
  • the control groove 30a connects the feed line 27 with the connecting line 28 and thus ensures a pressure equalization in the two control pressure chambers 7a and 7b.
  • a corresponding actuating force acts on the actuating piston 3 by the correspondingly different piston surfaces, which displaces the actuating piston 3 in the direction of the first actuating pressure chamber 7a.
  • the spring bearing 9a Due to the spacer rod 11a located in contact with the adjuster 12, the spring bearing 9a, which is supported by the gradation of the receiving opening 82 on the change in the radial extent of the spacer rod 11a, can not follow the movement and rises from the bottom of the recess 79 of the actuating piston 3 from.
  • the opposite spring bearing 9b is supported on the adjusting piston cover 10. The compression of the return springs 8a and 8b causes a restoring force on the actuating piston 3.
  • a balancing bore 89 is inserted into the actuating piston 3, through a pressure equalization between the recess 79 of the actuating piston 3 and the interior of the housing takes place.
  • the deflection of the actuating piston 3 is transmitted to the spring sleeve 43 by the rigid connection of the return lever 4.
  • the direction of movement of the spring sleeve 43 is opposite to the deflection of the control piston 17.
  • the relative position of the spring sleeve 43 to the control piston 3 changes in the same direction to the above-described relative movement of the control piston 3 by the control force of the proportional solenoid 31.
  • the control spring 45 is thereby further compressed and counteracting the control force of the proportional solenoid 31 acting counterforce increases. With increasing travel of the actuating piston 3, therefore, the equilibrium position of the control piston 3 is moved in the direction of its neutral position.
  • the throttle valve 47 is closed further.
  • the closing of the throttle valve 47 reduces the amount of hydraulic fluid supplied per unit time into the second actuating pressure chamber 7b, whereby the movement of the actuating piston 3 slows down with increasing travel of the actuating piston 3.
  • the movement of the actuating piston 3 is completed when the force generated by the control spring 45 between the spring sleeve 43 and the control piston 17 is so large that the resulting counterforce on the magnetic plunger 37 is equal to the control force.
  • 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 actuator piston 3 reaches its differential control signal proportional deflection without overshoot.
  • the deflection in the opposite direction is analogous to a differential control signal of opposite sign, wherein the first control piston member 18 is acted upon by the proportional solenoid 31 with a force which is transmitted by the control piston plunger 20 to the second control piston part 19.
  • the control groove 30 connects the connecting line 28 with the return line 29, thus relaxing the second Setting pressure chamber 7b in the tank.
  • the pressure in the first control pressure chamber 7a is greater than that in the second control pressure chamber 7b, so that the resulting actuating force deflects the control piston 3 in the direction of the second control pressure chamber 7b.
  • the control piston 17 has a total length that can not be influenced, which can vary as a result of manufacturing tolerances. So that both proportional solenoids 31 can work in their ideal stroke range, their distance is adjustable.
  • the proportional solenoid 31 on the side of the first control piston part 18 is for this purpose connected via a threaded connection with the control valve cover 22 and fixed with a lock nut 14.
  • the position of the throttle valve side proportional solenoid 31, which is connected to the control sleeve 23, relative to the control piston 17 is adjustable by the position of the control sleeve 23 relative to the control housing 24 by a threaded connection.
  • the balancing of the spring forces for the neutral position is effected by adjusting the relative position of the sleeves 35 to the abutments 34, so that a compensating correction of the bias of the Enstellfedern 36 can be achieved for a changed by adjusting the stroke of the proportional Magente 31 spring tension of the centering springs 33.
  • the connection between the throttle valve side proportional solenoid 31 and the control sleeve 23 can also be made adjustable.
  • the two mutually facing ends of the control piston parts 18 and 19 have for this purpose recesses, wherein the addition of the lengths of the recesses is smaller than the length of the control piston plunger 20.
  • At least one of the recesses is designed as a compensation receptacle 15 and has a radial extent which is large enough is to compensate for the angular error and the offset of the center axes of the two control piston parts 18 and 19 without 18 and 19 transverse forces are transmitted between the two control piston parts.
  • a second embodiment is shown, wherein instead of the control means 38 with proportional solenoids 31, a hydraulic solution is provided.
  • the control means 38 instead of the control means 38 with proportional solenoids 31, a hydraulic solution is provided.
  • non-designated components correspond in design and function to those described in FIG.
  • a control pressure chamber 51 is arranged.
  • the control pressure chamber 51 is formed by a recess of the control sleeve 23, which is closed by a screwed-in spring tensioner 53.
  • the spring tensioner 53 has a cylindrical extension which projects into the interior of the centering spring 33.
  • an analog control device 38 is arranged in the control valve cover 22.
  • a pilot valve 49 is connected to a supply bore 50.
  • the pilot valve 49 is electrically controllable and may for example consist of two proportional pressure relief valves or a servo pilot valve according to nozzle-baffle plate principle.
  • the at the end facing away from the throttle valve 47 end of the control piston 17 correspondingly constructed control device 38 is connected via a control pressure line 54 to the pilot valve 49.
  • the pilot valve 49 generates between the control pressure chambers 51 a pressure difference corresponding to an electric signal obtained from the pilot valve 49.
  • pressure difference of the control piston 17 is acted upon by an axial control force, which leads to a deflection of the control piston 17 and an opening of the throttle valve 47.
  • the adjusting movement of the actuating piston 3 and the structure of restoring forces corresponds to the functionality of the adjusting device 1 described in FIG.
  • a displacement sensor 55 is arranged on the adjusting device 1.
  • the transducer 55 is fixedly connected to the housing of the adjusting device 1 and has a spring-loaded stylus tip 56 which protrudes from the housing of the displacement sensor 55 and is displaceable in the axial direction.
  • the stylus tip 56 is held by the spring force into contact with a sensing surface 57, which includes with the central axis of the actuating piston 3 a non-zero angle.
  • a deflection of the actuating piston 3 from its neutral position thus leads to a relative change in the position of the probe tip 56 with respect to the transducer 55.
  • the change in position is converted by the transducer 55 into an electrical signal.
  • the control signal predetermines a desired position for the actuating piston 3. However, due to frictional forces and hysteresis, the position actually assumed by the actuating piston 3 may deviate slightly from the desired position. This deviation is detected by the comparison of the signals and a second control signal corrected by a control unit, not shown, correspondingly corrected to the pilot control valve 49. The positioning accuracy of the adjusting device 1 is thus increased.
  • the two spacer bars 11a and 11b are approximately cylindrical and have no change in the radial extent.
  • As an abutment surface for the spring bearings 9a and 9b serve the front ends of the spacer rods 11a and 11b, which are supported on the bottom of the receiving openings 82a and 82b.
  • a compensation bore 89 is introduced into the spring bearings 9a and 9b, which connect the receiving openings 82a and 82b to the interior of the actuating piston 3.
  • Fig. 3 is a detail of a hydraulic circuit diagram of an adjusting device 1 according to the invention is shown.
  • a drive shaft 90 is a.
  • Pump 58 is connected, which is provided for two flow directions and whose displacement volume by means of the adjusting piston 3 is adjustable.
  • a first and a second main line 61 and 62 is connected, wherein in each case a main line 61 or 62 is provided for each one conveying direction.
  • a first and second supply line 74 and 81 which are connected to the two main lines 61 and 62, connected to a feed line 65, wherein the check valves 63 and 64 at positive pressure difference of the respective supply line 74 and 81 opposite the feed line 65 open.
  • the feed line 65 is connected via the control pressure line 16a to the first control pressure chamber 7a and to a first port 126a of the control valve 2, which is the first circulating.
  • Channel 26a of FIG. 1 corresponds.
  • the second actuating pressure chamber 7b is connected via the connecting line 28, an intermediate line 78 and the control pressure line 16b to a second terminal 126b of the control valve 2, which corresponds to the second circumferential channel 26b.
  • the connecting line 28 is connected to the intermediate line 78, the intermediate line 78 in turn connected to the control pressure line 16b via the control valves 67 and 66, respectively.
  • a first end position of the control valves 66 and 67 in which the above-mentioned connections are turned on and every other possible connection is closed. Function and operation of the control valves 66 and 67 will be explained later in detail.
  • the control valve 47 has a third port 126c. which is connected via a return line 29 to a tank 60 and the third circumferential channel 26c corresponds.
  • auxiliary feed line 68 is connected to the feed line 65 via a feed line check valve 69.
  • the auxiliary feed line 68 is depressed by a suitable for only one conveying direction auxiliary pump 59 and supplied at a positive pressure difference between the auxiliary feed line 68 and feed line 65, the feed line 65 with hydraulic fluid.
  • the deflection of the control piston 17 in the throttle valve 47 will cause e.g. the connection 126a is connected to the connection 126b and thus the supply line 65 is connected to the connection line 28.
  • the second actuating pressure chamber 7b thereby the same pressure as in the signal pressure line 16a also connected to the feed line 65 is connected to the first control pressure chamber 7a and the control piston 3 acts on the different oppressed surfaces corresponding actuating force which deflects it.
  • the control valve 66 is provided for the conveying direction of the pump 58 described above.
  • the control valve 66 operates continuously between two end positions.
  • the pressure in the first supply line 74 is compared with the pressure in a first comparison pressure line 70, whose force is supported on the control valve 66 by an adjustable spring.
  • a filter 75 is arranged in the first supply line 74 to the control valve 66.
  • the first supply line 74 is connected via a first comparison pressure throttle 76 with the first comparison pressure line 70.
  • the comparison pressure line 70 is connected to a 3/2-way shuttle valve 72, whose other terminals are connected to a second comparison pressure line 71 for the second control valve 67 and a pressure limiter line 77.
  • each one of the comparison pressure line 70 or 71 is connected to the pressure limiter line 77, in which the greater pressure is present through the shuttle valve 72.
  • the pressure limiting line 77 is expanded by a pressure limiting valve 73 against the tank 60, to which the pressure limiting valve 73 is connected via the return line 29.
  • the pressure relief valve 73 is made adjustable.
  • the intermediate line 78 and the control pressure line 16b are connected to one another in the control valve 66. If the predetermined pressure value in the first supply line 74 is significantly exceeded, the control valve 66 is in its second end position, in which the control pressure line 16b is connected to an expansion line 80. If the pressure in the first main line 61 is too great, a flow path from the second control pressure chamber 7b via the control pressure line 16b, the control valve 66 and the Relaxation line 80 to the tank 60 is opened. The thus achieved relaxation in the second actuating pressure chamber 7b leads to a decrease in the deflection of the actuating piston 3. The displacement volume of the pump 58 is reduced and as a result the pressure in the first main line 61 decreases.
  • control piston 17 If a control signal of opposite sign is applied to the two proportional solenoids 31, the control piston 17 is deflected in the opposite direction to the preceding description and a connection between the terminals 126b and 126c is opened by the control valve 2.
  • the pressure in the second actuating pressure chamber 7b via the control pressure line 16b, the intermediate line 78, the connecting line 28 and the return line 29 is relaxed in the tank 60, initially again the function of the control valves 66 and 67 should be neglected.
  • On the actuating piston 3 acts a force that moves the actuating piston 3 in the direction of the second actuating pressure chamber 7b.
  • the associated adjustment of the pump 58 causes a promotion of the hydraulic fluid in the second main line 62.
  • the check valve 63 opens and the feedline check valve 69 closes.
  • the feed line 65 is supplied by the pump 58 and the second main line 62 via the second supply line 81.
  • the second supply 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 supply line 81 is connected via a second comparison pressure throttle 83 with the second comparison pressure line 71.
  • a constant maximum pressure is again generated in the comparison pressure line 71 which, together with a spring force, generates a comparison value for the pressure in the second supply line 81 and thus the second main line 62.
  • the first end position of the second control valve 67 connects the connecting line 28 with the intermediate line 78 when the pressure in the second supply line 81 is below the predetermined reference value. If this value is exceeded, the second control valve 67 shifts toward the second end position and connects a pressure buildup line 84 to the intermediate line 78. This establishes a connection from the feed line 65 via the pressure buildup line 84 and the intermediate line 78 through the first control valve 66 and the control pressure line 16b made to the second adjusting pressure chamber 7b. The resulting pressure increase in the second actuating pressure chamber 7b generates a force opposing the actuating force, which reduces the deflection of the actuating piston 3 and thus the displacement volume of the pump 58. As a result, the pressure in the second main line 62 drops.

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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)

Claims (11)

  1. Dispositif de réglage, qui est destiné au réglage d'un piston de réglage (3), qui est disposé entre deux chambres de pression de réglage et agit sur le volume de poussée d'un moteur hydrostatique et qui, sous l'effet de la force d'au moins un ressort de rappel (8a, 8b), peut être dévié hors d'une position neutre entre deux positions de fin de course, avec une soupape de commande (2) prévue pour le réglage des pressions de réglage dans les chambres de pression de réglage (7a, 7b) et avec un piston de commande (17), qui peut être dévié dans le sens axial de part et d'autre d'une position neutre sous l'effet de forces générées par des dispositifs de commande (38), une force antagoniste corrélée au déplacement du piston de réglage (3) s'opposant dans chaque cas aux forces de commande, caractérisé en ce que le piston de commande (17) est formé dans le sens axial par une première partie (18) et par une deuxième partie (19), lesquelles sont reliées l'une à l'autre au moyen d'un poussoir de piston de commande (20), de telle sorte qu'une force de poussée peut être transmise dans le sens axial au moyen du poussoir de piston de commande (20) depuis chacune des parties de piston de commande (18 ; 19) sur l'autre partie de piston de commande (19 ; 18).
  2. Dispositif de réglage selon la revendication 1, caractérisé en ce que la première et la deuxième partie de piston de commande (18, 19) sont chacune sollicitées au niveau des extrémités détournées l'une de l'autre par une force dirigée l'une vers l'autre au moyen d'au moins un ressort de centrage (33) et/ou un ressort de réglage (36) et en ce qu'un ressort de commande (45) est tendu entre deux corps de siège de ressort (40a, 40b), les corps de siège de ressort (40a, 40b) pouvant être déplacés dans le sens axial vers le ressort à partir de chacune des surfaces d'appui sur le manchon du ressort (43) et d'une surface d'appui sur la première partie de piston de commande (18), de telle sorte que, dans le cas d'une modification de la position du manchon de ressort (43) par rapport à la première partie du piston de commande (18), le ressort de commande (45) peut être tendu entre, d'une part, un corps de siège de ressort (40a, 40b) en appui sur une surface d'appui du manchon de ressort (43) et, d'autre part, le corps de siège de ressort (40a, 40b) en appui sur la surface d'appui sur la première partie de piston de commande (18) et la force du ressort de commande est dirigée à l'encontre du changement de position relatif.
  3. Dispositif de réglage selon la revendication 2, caractérisé en ce que la précontrainte d'au moins un ressort de centrage (33) et/ou d'un ressort de réglage (36) peut être réglée de manière à générer dans la position neutre de la soupape de commande (2) des forces de ressort équilibrées.
  4. Dispositif de réglage selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la position neutre de la soupape de commande (2) peut être réglée au moyen d'un manchon de commande (23), qui est mobile dans le sens axial.
  5. Dispositif de réglage selon l'une quelconque des revendications 1 à 4, caractérisé en ce que, pour générer la force de déviation, un aimant proportionnel (31) est disposé sur chacune des deux extrémités opposées des deux parties de piston de commande (18, 19).
  6. Dispositif de réglage selon la revendication 5, caractérisé en ce qu'au moins l'un des deux aimants proportionnels (31) peut être réglé dans sa position axiale.
  7. Dispositif de réglage selon la revendication 5 ou 6, caractérisé en ce qu'un aimant proportionnel (31) est monté dans une position fixe par rapport au manchon de commande (23).
  8. Dispositif de réglage selon l'une quelconque des revendications 1 à 4, caractérisé en ce que, pour générer la force de déviation, une pression peut être produite dans un logement de ressort (86) réalisé sur chacune des deux extrémités opposées des deux parties de piston de commande (18, 19).
  9. Dispositif de réglage selon la revendication 8, caractérisé en ce qu'une soupape pilote est prévue pour générer la pression dans les logements de ressort (86a, 86b).
  10. Dispositif de réglage selon l'une quelconque des revendications 1 à 9, caractérisé en ce que le dispositif de réglage (1) comporte un capteur de déplacement (55) qui est destiné à détecter la déviation du piston de réglage (3) et dont le signal de mesure permet de corriger un signal de commande électrique.
  11. Dispositif de réglage selon l'une quelconque des revendications 1 à 10, caractérisé en ce que, pour limiter la pression dans une conduite principale, il est prévu deux soupapes de réglage (66, 67), par lesquelles, en cas de dépassement d'une pression de référence maximum déterminée dans une conduite de référence (70, 71), la pression de réglage du piston de réglage (3) peut être modifiée respectivement par la pression dans une conduite principale, de telle sorte que le piston de réglage (3) est sollicité vers sa position neutre par une force de réglage résultante.
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
DE10063525 2000-12-20
DE2000163525 DE10063525B4 (de) 2000-12-20 2000-12-20 Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens

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

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DE102012214620A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
DE102012214619A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214621A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh olrohr für eine Aktoreinrichtung
DE102012214618A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Spule für eine Aktoreinrichtung
DE102012214698A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
WO2014026791A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Dispositif d'actionnement et machine à piston axial
DE102012214655A1 (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
WO2014026789A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Dispositif d'actionnement et machine à piston axial
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

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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
DE102012021320A1 (de) 2012-10-31 2014-04-30 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung
DE102013224657A1 (de) * 2013-12-02 2015-06-03 Robert Bosch Gmbh Hydraulische Anordnung
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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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Publication number Priority date Publication date Assignee Title
DE102012214620A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
DE102012214619A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214621A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh olrohr für eine Aktoreinrichtung
DE102012214618A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Spule für eine Aktoreinrichtung
DE102012214698A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Polrohr für eine Aktoreinrichtung
WO2014026791A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Dispositif d'actionnement et machine à piston axial
DE102012214655A1 (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
WO2014026922A2 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Tube polaire pour un dispositif actionneur
WO2014026789A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Dispositif d'actionnement et machine à piston axial
DE102012214628A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Anker für eine Aktoreinrichtung
WO2014026790A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Induit pour un dispositif actionneur
DE102012214626A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214622A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Aktoreinrichtung und Axialkolbenmaschine
DE102012214696A1 (de) 2012-08-17 2014-02-20 Robert Bosch Gmbh Anker für eine Aktoreinrichtung
WO2014026788A1 (fr) 2012-08-17 2014-02-20 Robert Bosch Gmbh Dispositif d'actionnement et machine à piston axial
CN104685155A (zh) * 2012-08-17 2015-06-03 罗伯特·博世有限公司 致动器装置和轴向活塞机

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DE50112595D1 (de) 2007-07-19
DE10063525B4 (de) 2005-07-07
EP1219831A2 (fr) 2002-07-03
DE10063525A1 (de) 2002-07-04
EP1219831A3 (fr) 2003-12-03

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