EP1502027B1 - Regulatory device comprising a threshold value control valve - Google Patents

Regulatory device comprising a threshold value control valve Download PDF

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Publication number
EP1502027B1
EP1502027B1 EP03724958A EP03724958A EP1502027B1 EP 1502027 B1 EP1502027 B1 EP 1502027B1 EP 03724958 A EP03724958 A EP 03724958A EP 03724958 A EP03724958 A EP 03724958A EP 1502027 B1 EP1502027 B1 EP 1502027B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control valve
control
delivery
threshold value
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 - Fee Related
Application number
EP03724958A
Other languages
German (de)
French (fr)
Other versions
EP1502027A1 (en
Inventor
Roland Belser
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 EP1502027A1 publication Critical patent/EP1502027A1/en
Application granted granted Critical
Publication of EP1502027B1 publication Critical patent/EP1502027B1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control

Definitions

  • the invention relates to a control device for controlling a delivery volume for a variable in its delivery pump.
  • a control device for adjusting the delivery volume of a pump in the form of a hydrostatic piston machine in which the delivery volume of the hydrostatic piston engine is controlled by a control unit as input both the delivery-side working line pressure, as well as the consumer after a throttle point supplied consumer input pressure is supplied.
  • the control unit consists of two arranged in a valve block control valves, which are each acted upon at a first measuring surface with the delivery-side working line pressure. In the opposite direction, a spring acts on a first control valve and on the second control valve of the consumer supply line removed consumer input pressure.
  • control valves are adjusted so that a control pressure chamber of an actuating unit is depressed by the first control valve from the working line when a limit is exceeded, which is adjustable by the spring. By pressing the control pressure chamber, the hydrostatic piston engine is adjusted in the direction of lower flow rate.
  • the control is carried out by the second control valve, wherein the control pressure chamber of the actuator is either depressed from the working line, or is expanded relative to the tank volume.
  • the control pressure chamber of the actuator is either depressed from the working line, or is expanded relative to the tank volume.
  • a constant pressure ratio between the delivery side working pressure and the consumer input pressure is maintained. Because the differential pressure between the working line and the consumer input is proportional to is the delivery volume, the hydrostatic piston engine is controlled to a constant delivery volume with the described circuit.
  • the control device has the disadvantage that at vanishing consumer input pressure through the second control valve of the control pressure chamber of the actuator is depressed, so that the pressure in the working line can drop to almost zero. If additional consumer or control devices are connected to the working line, which require a minimum pressure, then these devices are no longer operable.
  • control device according to the invention with the features of claim 1.
  • the control device has the advantage that for controlling a first and second control valve, which together form the control unit, not the same input pressure is used.
  • a first control range in which a minimum pressure is adjustable by the limit value control
  • a second control range in which above a limit value, which is set by the limit value control, the control a constant flow rate of the pump through the flow control valve.
  • the control of the constant flow rate is effected by the flow control valve in response to the consumer input pressure and a pressure applied to a measuring surface, wherein the applied pressure is the output pressure of the limit value control valve.
  • control device 1 acts on the pivot angle of an adjustable pump in the form of a hydrostatic piston machine 2.
  • a control valve unit 3 is provided, by means of which the control pressure prevailing in a return member 5 is controllable.
  • the pivot angle of the hydrostatic piston machine 2 is set, which is driven via a drive shaft 6.
  • the hydrostatic piston engine 2 conveys a pressure medium into a working line 7. Via the working line 7, the pressure medium reaches a consumer supply line 8, to which an illustrated consumer is not connected. Between the working line 7 and the consumer supply line 8, a throttle 9 and an adjustable throttle 10 are arranged in series. The throttle 9 need not be explicitly carried out, but can also be generated by the throttling effect of the line length. With the Consumer supply line 8 is further connected to a pressure limiting device 11. The consumer supply line 8 is via the pressure limiting device 11 against a tank volume 13 relaxed, with a relaxation takes place when the pressure in the consumer supply line 8 via a presettable by means of a setting spring 12 threshold increases.
  • the actuator 4 can also be dispensed with the actuator 4 and an adjustment in the direction of greater deflections are generated by acting on the return member 5 spring.
  • the actuator 4 is connected via a connecting line 14 to the working line 7.
  • the prevailing in the working line 7 pressure is thus supplied to a pressure chamber 15 of the first actuator 4, where it acts together with the force of a biasing spring 16 on an actuating piston 17.
  • the applied in the control pressure chamber 15 of the first actuator 4 to the actuator piston 17 force is directed so that it adjusts the hydrostatic piston engine 2 in the direction of larger pivot angle.
  • control valve unit 3 By means of the control valve unit 3, a control pressure which acts in the second actuator 5, regulated. To regulate the control pressure, the control valve unit 3 is connected by means of a further connecting line 18 with the working line 7 on the one hand and with the consumer supply line 8 via a consumer input pressure supply line 19. Via the further connecting line 18 and the consumer input pressure supply line 19, the control valve unit 3 is supplied to the prevailing pressure before or after the throttle bodies 9 and 10. The control valve unit 3 thus controls due to the falling at the throttle points 9 and 10 pressure.
  • the control valve unit 3 is connected via a control pressure line 20 with a control pressure chamber 21 which is arranged in the actuator 5.
  • the control pressure prevailing in the control pressure chamber 21 acts on a control piston 42 and adjusts the hydrostatic piston engine 2 in the direction of smaller swivel angles.
  • a spring may be arranged in the second actuator 5, which acts on the actuating piston 42 with a force acting against the pressure of the control pressure chamber 21 force.
  • the control valve unit 3 consists of a limit value control valve 22 and a flow control valve 23.
  • the limit value control valve 22 is biased by a first spring 24, so that it is in its depressurized state in its starting position shown in FIG.
  • the flow control valve 23 is also biased by a second spring 25, and is also in a depressurized state in its initial position.
  • the limit value control valve 22 has a spelltikmeßanschluß 26, wherein the voltage applied to the spelltikmeßanschluß 26 pressure of the force of the first spring 24 is opposite. With increasing pressure, the limit value control valve 22 is deflected from its initial position in the direction of its second end position.
  • the force of the second spring 25 is counteracted by a hydraulic force which is generated by the pressure applied to a regulating pressure measuring connection 27.
  • the force of the second spring 25 is supplemented by a force acting on a comparison pressure port 29 force.
  • the pressure of the consumer supply line 8 which is supplied via the Disereangstikzutechnisch 19 of the measuring surface at thewherestikmeßanschluß 29.
  • the crizeldmeßanschluß 27 of the flow control valve 23 is connected via a control pressure channel 30 with the limit value control valve 22.
  • a first control pressure port 31 of the flow control valve 23 is connected to a flash line 32 which is connected to a relaxation port 33 of the flow control valve 23.
  • the expansion line 32 is connected to the tank volume 13.
  • the limit value control valve 22 has a second control pressure connection 34 and a third control pressure connection 35 via which the control pressure chamber 21 is connected via the control pressure line 20 to the first control pressure connection 31 to the first control pressure connection 31 of the flow control valve 23.
  • the return pressure chamber 21 is connected to the tank volume 13.
  • the pressure taken over the further connecting line 18 from the working line 7 pressure is supplied on the one hand the winning sloganßanschluß 26 and on the other hand connected via a branching line from the supply line to a delivery pressure input 26 of the limit value control valve 22.
  • the delivery pressure input 36 is connected to a delivery pressure outlet 37 in the second end position of the limit value control valve 22.
  • the delivery pressure output 37 is connected via the control pressure channel 30 with both the crizeldmeßanschluß 27 and with a Stelltikzu Switzerlandanschluß 38.
  • the hydrostatic piston machine 2 In the unpressurized state, the hydrostatic piston machine 2 is first pivoted to a large delivery volume by the biasing spring 16 of the actuator 4. If the hydrostatic piston engine 2 is driven via the drive shaft 6, this generates a pressure in the working line 7, which pressure is supplied via the connecting line 14 in the control pressure chamber 15 of the first actuator 4. The first actuator 4 therefore tries to adjust the hydrostatic piston engine 2 with increasing pressure in the working line 7 in the direction of larger pivot angle. The rising pressure in the working line 7 is supplied via the further connecting line 18 to the limit value control valve 22 and acts on the beneficiatikmeßanschluß 26 with a hydraulic force.
  • the actuating pressure chamber 21 of the second actuator 5 is connected to the tank volume 13 in the initial position of the limit value control valve 22 and the flow control valve 23, so that no force is generated by the second actuator 5, which counteracts the actuating force of the first actuator 4.
  • the applied to the originally founded hereinßanschluß 26 pressure of the working line 7 shifts the limit value control valve 22 in the direction of its second end position and thus connects at a predetermined by the adjustable spring 24 limit the delivery pressure input 36 to the delivery pressure outlet 37.
  • the limit value of the flow control valve 23 supplied control pressure in this area in addition the flow control valve 23.
  • the flow control valve 23 is adjusted with increasing control pressure by the pressurization of crizeldruckmeßanschluß 27 towards its second end position, so that via the Stelltikzu technologicalanschluß 38 and in the course of the first, second and third control pressure port 31, 34th and 35 the control pressure chamber 21 is acted upon by a control pressure.
  • the loading of the control pressure chamber 21 with a control pressure is as described above an adjustable by the limit value control valve 22 limit for the pressure in the working line 7, so that a restoring force, which is opposite to the actuating force of the actuator 4, only above a certain minimum pressure in the working line. 7 is produced.
  • a minimum pressure is maintained in the working line 7, even if in the consumer supply line 8, the pressure drops to zero.
  • the control pressure in the control pressure chamber 21 is adjusted by the flow control valve 23 so that at the flow control valve 23, a balance of forces is set.
  • the equilibrium of forces is composed of the force of the second spring 25 and the two hydraulic forces which act on the regulating pressure measuring connection 27 and the comparison pressure connection 29.
  • Above the predetermined by the limit value control valve 22 so that a restoring control pressure is regulated, with which a constant pressure difference between the working line 7 and the consumer supply line 8 is set.
  • a constant pressure difference is equivalent to a constant delivery volume.
  • a shut-off valve 40 is further provided, which connects the consumer supply line 8 with the comparison pressure connection 29 in normal operation.
  • the shut-off valve 40 can be actuated via an actuating lever 41, so that the comparison pressure connection 29 is to be connected to the tank volume 13 via the consumer input pressure supply line 19.
  • An actuation of the actuating lever 41 leads to a relaxation at the comparison pressure port 29.
  • the limit value control valve 22 is thus adjusted in the direction of its initial position, so that the control pressure channel, a lower pressure is supplied. Due to the lower control pressure, which is fed to the control pressure measuring 27 via the control pressure channel 30, the flow control valve 23 is also adjusted in the direction of its initial position, so that the control pressure chamber 21 is relaxed by falling below the limit by the working line pressure in the tank volume 13. In the working line 7 there is thus always a presettable by the setting of the limit value control valve 22 minimum pressure. This can be used to operate more actuators or other consumers that require a minimum pressure.
  • One application is, for example, when the control of the mobile slide is supplied via pressure reducer from the working pressure in mobile devices and their function must be maintained even at standstill (standby).
  • FIG. 2 A preferred structural design is shown in FIG. 2.
  • the limit value control valve 22 and the delivery flow control valve 23 are arranged in a control valve block 43.
  • a first receiving bore 44 and a second receiving bore 45 is introduced, wherein the center axes of the receiving bores 44 and 45 are preferably aligned parallel.
  • a limit value control valve piston 46 is arranged in the first receiving bore 44 and in the second receiving bore 45, a flow control valve piston 47 is arranged.
  • the Grenzwertregelventilkolben 46 and the flow control valve piston 47 are smaller in their radial extent than the respective diameters of first receiving bore 44 and second receiving bore 45 and disposed axially displaceably in the receiving bores 44 and 45.
  • the flow control valve piston 47 has at its ends in each case a first guide portion 48 and a second guide portion 49, wherein the radial extent of the guide portions 48 and 49 with the radial extent of the second receiving bore 45 corresponds, so that the flow control valve piston 47 is guided in the receiving bore 45 , Between the first and second guide sections 48 and 49, a control section 50 is provided on the flow control valve piston 47, on which a first control edge 51 and a second control edge 52 are formed.
  • a control pressure chamber 53 is formed due to the different radial extent of the flow control valve piston 47 and the second receiving bore 45. Furthermore, between the control section 50 and the second guide section 49, a further guide section 55 may be provided.
  • the Grenzwertregelventilkolben 46 is formed according to the flow control valve piston 47 and has a first guide portion 56 and at its second end a second guide portion 57, with which the limit value control valve piston 46 is guided in the first receiving bore 44. Between the first guide section 56 of the limit value control valve piston 46 and a control section 58 of the limit value control valve piston 46, a delivery pressure chamber 61 is likewise formed by the different radial expansions of the limit value control valve piston 46 and the first receiving bore 44.
  • the control section 58 of the limit value control valve piston 46 also has a first control edge 59 and a second control edge 60.
  • a first pressure chamber 63 is formed, which is connected via an overflow 62 with the discharge pressure chamber 61.
  • the pressure prevailing in the delivery pressure chamber 61 pressurizes the limit control valve piston 46 on an end face 64 with a hydraulic force which acts on the limit value control valve piston 46 in the axial direction.
  • the force of the first spring 24 which is supported on a spring bearing 65, wherein the spring bearing 65 is connected to the limit value control valve piston 46 in operative connection.
  • a seat 66 is formed on the end face of the second guide portion 57, wherein the spring bearing 65 has a recess 66 corresponding to the seat.
  • an abutment 67 is arranged, which is supported on an adjusting screw 68.
  • the distance between the spring bearing 65 and the thrust bearing 67 is variable, so that the bias of the first spring 24 can be adjusted.
  • a lock nut 69 is provided for fixing the adjusting screw 68.
  • the open end of the adjusting screw 68 is covered with a cap nut 70 and thus protected from contamination.
  • the lock nut 69 and the cap nut 70 are each sealed via a sealing element, preferably an O-ring 71, against a housing component or against each other.
  • the anvil 67, the adjusting screw 68, the lock nut 69 and the cap nut 70 together form an adjustment device 72.
  • a spring chamber 43 is provided in the control valve block 43.
  • a connecting bore 74 is introduced from the spring chamber 73 into the control valve block 43.
  • the Connecting bore 74 opens into a tank connection bore 75, wherein on the outside of the control valve block 43, a tank connection piece 76 is located.
  • a return line is connected, which is in communication with the tank volume 13.
  • a delivery pressure port 78 is provided on the outside of the control valve block 43.
  • the pressure of the working line 7 supplied via the further connecting line 18 is supplied to the control valve block 73.
  • the delivery pressure connection 78 communicates with a delivery pressure channel 79, which opens into the delivery pressure chamber 61.
  • the control device 1 If the pressure in the working line 7 increases, this increased pressure is forwarded via the delivery pressure connection 78 and the delivery pressure channel 79 into the delivery pressure chamber 61.
  • the delivery pressure chamber 61 communicates with the first pressure chamber 63, so that the increased pressure of the working line 7 acts on the end face 63 of the limit value control valve piston 46.
  • the first receiving bore 44 is closed with a closure member 83, wherein the closure member 83 is preferably fixed with a screw in the control valve block 43.
  • a sealing element 84 is provided for sealing.
  • the limit value regulating valve piston 46 is acted upon by an axial force which moves the limit value regulating valve piston 46 in FIG. 2 to the right against the force of the first spring 24.
  • the first control edge 59 is also moved to the control section 58 of Grenzwertregelventilkolbens 46 to the right, wherein it exceeds a limit value, via the adjusting 72nd is adjustable, a flow channel from the discharge pressure chamber 61 in the control pressure channel 30 releases.
  • the limit value control valve piston 46 engages in the pressure of the tank volume 13 prevailing in the spring chamber 73.
  • the pressure medium supplied via the control pressure channel 30 to the control pressure chamber 53 is conducted via a further overflow channel 80 into a second pressure chamber 81 which is formed on the end face of the flow control valve piston 47 and in which the pressure exerts a force on the end face 82 of the flow control valve piston 47.
  • the second receiving bore 45 is also provided with a closure piece 83 and a sealing element 84, wherein the closure piece 83 is also secured with a screw in the control valve block 43.
  • the flow control valve piston 47 is deflected from its initial position shown in FIG. 2 to the right until an equilibrium of forces has been established between the control pressure acting on the end face 82 and the opposing forces.
  • a further spring bearing 94 is arranged, which is in operative connection with the conical seat 93 of the flow control valve piston 47.
  • a second spring 25 is supported, wherein the second spring 25 can be supplemented by an additional spring 25 ', which is also supported on the other spring bearing 94.
  • the second spring 25 and the additional spring 25 ' are supported on an abutment of a further adjustment device 95, which is constructed in accordance with the adjustment device 72 and is dispensed with its further description.
  • the second spring 25 and additional spring 25 ' are arranged in a spring chamber 96.
  • the spring chamber 96 is over a Consumer input pressure supply port 97 and a consumer pressure channel 98 via the described in Fig. 1 consumer pressure supply line 19 connected to the consumer supply line 8.
  • the flow control valve piston 47 is shifted from its starting position shown in FIG. 2 to the right.
  • a flow channel from the control pressure chamber 53 is released into a control pressure channel 85 by the first control edge 51.
  • the signal pressure channel 85 is formed as a bore in the control valve block 43.
  • a flow path between the control pressure duct 85 and the tank connection bore 75 is interrupted via the second control edge 52 of the flow control valve piston 47.
  • the tank port bore 75 and the control pressure channel 85 are connected to each other in the initial position of the flow control valve 23 by the different diameter of the flow control valve piston 47 and the second receiving bore 45.
  • the control pressure channel 30, the control pressure channel 85 and the tank connection bore 75 are introduced as holes in the control valve block 43.
  • the three holes lie in a plane and are connected to each other with the connecting hole 74, wherein the connecting hole 74 is divided into several sections.
  • a second portion of the connecting bore 74 is formed, between the control pressure channel 85 and the control pressure channel 30, however, a third portion of the connecting hole 74th
  • a first plug 86 is used, which is provided by the actuating pressure channel 85 with a blind bore 87.
  • the plug 86 has a throttle opening 88 and a connection opening 89.
  • a flow-through connection between the third section 74b of the connecting channel 74 and the actuating pressure channel 85 is established via the blind bore 87.
  • the throttle opening 88 is brought by twisting the plug 86 in partial overlap with the second portion 74 a the first portion of the connecting hole 74, so that at this point an adjustable throttle between the actuating pressure channel 85 and the connecting hole 74 is formed.
  • control valve block 43 The likewise formed as a bore in the control valve block 43 control pressure channel 30 is closed with a further stopper 90, in which a further blind bore 92 is introduced from the outside, the further blind bore 92 via a further connection opening 90 with the third portion 74b of the connecting hole 74th connected is.
  • the pressing of the actuator 5 described in Fig. 1 is carried out starting from the above-described movement of Grenzwertregelventilkolbens 46 and the randomlystromregelventilkolbens 47 from the signal pressure channel 85 via the blind bore 87 and the connecting opening 89 and the third section 74b of the connecting hole 74 on the further connection opening 91st and the further blind bore 92, from where an unillustrated line section, which corresponds to the control pressure line 20 of FIG. 1, leads to the control pressure chamber 21 of the actuator 5.
  • the actuation of the shut-off valve 40 leads to a reduction of the pressure in the other spring chamber 96.
  • the resulting adjustment movement of the flow control valve piston 47 to the right is at decreasing pressure in the working line 7 prevents by the first control edge 59 at the control section 58 of the limit value control valve piston 46 closes the flow path between the discharge pressure chamber 61 and the control pressure channel 30.
  • the pressure in the second pressure chamber 81 is expanded via the throttle opening 88 in the tank volume 13, so that the flow control valve piston 47 is moved in the direction of its initial position due to the forces of the two springs 25 and 25 '.
  • By the return movement of the flow control valve piston 47 is released from the second control edge 52 of the control section 50, the flow path from the control pressure channel 85 into the tank connection bore 75.
  • the control pressure chamber 21 is thus relaxed in the tank volume 13, so that, as described for Fig. 1, the actuator 4 opposing force is reduced and thus the pivot angle of the hydrostatic piston engine 2 is adjusted so that a certain minimum pressure in the working line 7 prevail

Abstract

The invention relates to a regulatory device for a pump (2), whose delivery volume can be adjusted, said device comprising a control valve unit (3) for regulating a control pressure that operates in a control pressure chamber (21) of an actuator (4, 5). The control valve unit (3) comprises a threshold value control valve (22) and a delivery flow control valve (23). The threshold value control valve (22) is subjected to a pressure from a working line (7) on the delivery side and the delivery flow control valve (23) can be subjected to a consumer input pressure taken from a consumer supply line (8), at a comparison pressure connection (29). In addition, the delivery flow control valve (23) is subjected to a control pressure that counteracts the consumer input pressure, at a regulatory pressure measurement connection (27). A control pressure feed connection (38) of the delivery flow control valve (23) can be connected to the working pressure line (7) on the delivery side in a variable manner, by means of the threshold value control valve (22).

Description

Die Erfindung betrifft eine Regeleinrichtung zur Regelung eines Fördervolumens für eine in ihrem Fördervolumen einstellbare Pumpe.The invention relates to a control device for controlling a delivery volume for a variable in its delivery pump.

Aus der DE 43 29 164 A1 oder der DE 10 006 659 A1 ist eine Regeleinrichtung zum Verstellen des Fördervolumens einer Pumpe in Form einer hydrostatischen Kolbenmaschine bekannt, bei der das Fördervolumen der hydrostatischen Kolbenmaschine geregelt wird, indem einer Regeleinheit als Eingangsgrößen sowohl der förderseitige Arbeitsleitungsdruck, als auch der dem Verbraucher nach einer Drosselstelle zugeführte Verbrauchereingangsdruck zugeführt wird. Die Regeleinheit besteht aus zwei in einem Ventilblock angeordneten Steuerventilen, welche jeweils an einer ersten Meßfläche mit dem förderseitigen Arbeitsleitungsdruck beaufschlagt werden. In entgegengesetzter Richtung greift an einem ersten Steuerventil eine Feder an und an dem zweiten Steuerventil der der Verbraucherzuleitung entnommene Verbrauchereingangsdruck. Die Steuerventile sind dabei so eingestellt, daß durch das erste Steuerventil ein Stelldruckraum einer Stelleinheit aus der Arbeitsleitung bedrückt wird, wenn ein Grenzwert überschritten wird, der durch die Feder einstellbar ist. Durch Bedrücken des Stelldruckraums wird die hydrostatische Kolbenmaschine in Richtung kleinerer Förderleistung verstellt.From DE 43 29 164 A1 or DE 10 006 659 A1 discloses a control device for adjusting the delivery volume of a pump in the form of a hydrostatic piston machine is known in which the delivery volume of the hydrostatic piston engine is controlled by a control unit as input both the delivery-side working line pressure, as well as the consumer after a throttle point supplied consumer input pressure is supplied. The control unit consists of two arranged in a valve block control valves, which are each acted upon at a first measuring surface with the delivery-side working line pressure. In the opposite direction, a spring acts on a first control valve and on the second control valve of the consumer supply line removed consumer input pressure. The control valves are adjusted so that a control pressure chamber of an actuating unit is depressed by the first control valve from the working line when a limit is exceeded, which is adjustable by the spring. By pressing the control pressure chamber, the hydrostatic piston engine is adjusted in the direction of lower flow rate.

Bleibt der Grenzwert unterschritten, so wird die Regelung durch das zweite Steuerventil durchgeführt, wobei der Stelldruckraum des Stellgliedes entweder aus der Arbeitsleitung bedrückt wird, oder gegenüber dem Tankvolumen entspannt wird. In diesem Regelbereich wird ein konstantes Druckverhältnis zwischen dem förderseitigen Arbeitsdruck und dem Verbrauchereingangsdruck aufrechterhalten. Da der Differenzdruck zwischen der Arbeitsleitung und dem Verbrauchereingang proportional zu dem Fördervolumen ist, ist mit der beschriebenen Schaltung die hydrostatische Kolbenmaschine auf ein konstantes Fördervolumen geregelt.If the limit falls below the limit, the control is carried out by the second control valve, wherein the control pressure chamber of the actuator is either depressed from the working line, or is expanded relative to the tank volume. In this control range, a constant pressure ratio between the delivery side working pressure and the consumer input pressure is maintained. Because the differential pressure between the working line and the consumer input is proportional to is the delivery volume, the hydrostatic piston engine is controlled to a constant delivery volume with the described circuit.

Die Regeleinrichtung hat den Nachteil, daß bei verschwindendem Verbrauchereingangsdruck durch das zweite Stellventil der Stelldruckraum des Stellgliedes bedrückt wird, so daß der Druck in der Arbeitsleitung bis nahezu auf Null absinken kann. Sind an die Arbeitsleitung noch weitere Verbraucher- oder Steuereinrichtungen angeschlossen, welche einen Mindestdruck benötigen, so sind diese Einrichtungen nicht mehr betätigbar.The control device has the disadvantage that at vanishing consumer input pressure through the second control valve of the control pressure chamber of the actuator is depressed, so that the pressure in the working line can drop to almost zero. If additional consumer or control devices are connected to the working line, which require a minimum pressure, then these devices are no longer operable.

Es ist Aufgabe der Erfindung, eine Regeleinrichtung zum Regeln eines konstanten Fördervolumens einer Pumpe zu schaffen, welche unabhängig von dem Verbrauchereingangsdruck einen Mindestdruck in einer Arbeitsleitung aufrechterhält.It is an object of the invention to provide a control device for controlling a constant displacement of a pump, which maintains a minimum pressure in a working line independent of the consumer input pressure.

Die Aufgabe wird durch die erfindungsgemäße Regeleinrichtung mit den Merkmalen des Anspruchs 1 gelöst.The object is achieved by the control device according to the invention with the features of claim 1.

Die erfindungsgemäße Regeleinrichtung hat den Vorteil, daß zum Regeln eines ersten und zweiten Regelventils, welche gemeinsam die Regeleinheit bilden, nicht derselbe Eingangsdruck verwendet wird. Durch die Aufgabenverteilung auf ein Grenzwertregelventil sowie ein Förderstromregelventil ist es möglich, einen ersten Regelbereich zu definieren, in dem durch das Grenzwertregelventil ein Mindestdruck einstellbar ist, sowie einen zweiten Regelbereich vorzusehen, in dem oberhalb eines Grenzwerts, der durch das Grenzwertregelventil festgelegt ist, die Regelung einer konstanten Fördermenge der Pumpe durch das Förderstromregelventil erfolgt. Die Regelung der konstanten Fördermenge erfolgt durch das Förderstromregelventil in Abhängigkeit von dem Verbrauchereingangsdruck und einem an einer Meßfläche anliegenden Druck, wobei der anliegende Druck der Ausgangsdruck des Grenzwertregelventils ist.The control device according to the invention has the advantage that for controlling a first and second control valve, which together form the control unit, not the same input pressure is used. By the distribution of tasks on a limit value control valve and a flow control valve, it is possible to define a first control range in which a minimum pressure is adjustable by the limit value control, and to provide a second control range, in which above a limit value, which is set by the limit value control, the control a constant flow rate of the pump through the flow control valve. The control of the constant flow rate is effected by the flow control valve in response to the consumer input pressure and a pressure applied to a measuring surface, wherein the applied pressure is the output pressure of the limit value control valve.

Dadurch wird verhindert, daß durch das Förderstromregelventil bei verschwindendem Verbrauchereingangsdruck der Stelldruckraum einer Stelleinheit solange bedrückt wird, bis das Fördervolumen der hydrostatischen Kolbenmaschine auf Null gestellt ist.This prevents that the control pressure chamber of a control unit is depressed by the flow control valve at vanishing consumer input pressure until the delivery volume of the hydrostatic piston engine is set to zero.

In den Unteransprüchen sind vorteilhafte Weiterbildungen der erfindungsgemäßen Regeleinrichtung ausgeführt.In the dependent claims advantageous refinements of the control device according to the invention are carried out.

Ein Ausführungsbeispiel einer erfindungsgemäßen Regeleinrichtung ist in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen hydraulischen Schaltplan einer erfindungsgemäßen Regeleinrichtung; und
Fig. 2
einen Schnitt durch eine in einem Regelventilblock angeordnete erfindungsgemäße Regelventileinheit.
An embodiment of a control device according to the invention is shown in the drawings and explained in more detail in the following description. Show it:
Fig. 1
a hydraulic circuit diagram of a control device according to the invention; and
Fig. 2
a section through an arranged in a control valve block inventive control valve unit.

In Fig. 2 ist ein hydraulischer Schaltplan der erfindungsgemäßen Regeleinrichtung 1 dargestellt. Die Regeleinrichtung 1 wirkt dabei auf den Schwenkwinkel einer verstellbaren Pumpe in Form einer hydrostatischen Kolbenmaschine 2. Zur Verstellung des Schwenkwinkels ist eine Regelventileinheit 3 vorgesehen, mittels derer der in einem Rückstellglied 5 herrschende Stelldruck regelbar ist. Mittels des Rückstellgliedes 5 wird der Schwenkwinkel der hydrostatischen Kolbenmaschine 2 eingestellt, die über eine Antriebswelle 6 angetrieben wird.2, a hydraulic circuit diagram of the control device 1 according to the invention is shown. The control device 1 acts on the pivot angle of an adjustable pump in the form of a hydrostatic piston machine 2. To adjust the pivot angle, a control valve unit 3 is provided, by means of which the control pressure prevailing in a return member 5 is controllable. By means of the return member 5, the pivot angle of the hydrostatic piston machine 2 is set, which is driven via a drive shaft 6.

Die hydrostatische Kolbenmaschine 2 fördert ein Druckmittel in eine Arbeitsleitung 7. Über die Arbeitsleitung 7 gelangt das Drucksmittel zu einer Verbraucherzuleitung 8, an die nicht ein dargestellter Verbraucher angeschlossen ist. Zwischen der Arbeitsleitung 7 und der Verbraucherzuleitung 8 sind eine Drossel 9 sowie eine einstellbare Drossel 10 in Serie angeordnet. Die Drossel 9 muß dabei nicht explizit ausgeführt sein, sondern kann auch durch die drosselnde Wirkung der Leitungslänge erzeugt werden. Mit der Verbraucherzuleitung 8 ist weiterhin eine Druckbegrenzungseinrichtung 11 verbunden. Die Verbraucherzuleitung 8 ist über die Druckbegrenzungseinrichtung 11 gegen ein Tankvolumen 13 entspannbar, wobei eine Entspannung erfolgt, wenn der Druck in der Verbraucherzuleitung 8 über einen mittels einer Einstellfeder 12 vorgebbaren Schwellwert steigt.The hydrostatic piston engine 2 conveys a pressure medium into a working line 7. Via the working line 7, the pressure medium reaches a consumer supply line 8, to which an illustrated consumer is not connected. Between the working line 7 and the consumer supply line 8, a throttle 9 and an adjustable throttle 10 are arranged in series. The throttle 9 need not be explicitly carried out, but can also be generated by the throttling effect of the line length. With the Consumer supply line 8 is further connected to a pressure limiting device 11. The consumer supply line 8 is via the pressure limiting device 11 against a tank volume 13 relaxed, with a relaxation takes place when the pressure in the consumer supply line 8 via a presettable by means of a setting spring 12 threshold increases.

Im dargestellten Ausführungsbeispiel erfolgt die Verstellung des Schwenkwinkels der hydrostatischen Kolbenmaschine 2 mittels eines Stellglieds 4 sowie des Rückstellglieds 5. Alternativ hierzu kann auch auf das Stellglied 4 verzichtet werden und eine Verstellung in Richtung größere Auslenkungen durch eine auf das Rückstellglied 5 wirkende Feder erzeugt werden.In the illustrated embodiment, the adjustment of the pivot angle of the hydrostatic piston engine 2 by means of an actuator 4 and the return member 5. Alternatively, can also be dispensed with the actuator 4 and an adjustment in the direction of greater deflections are generated by acting on the return member 5 spring.

Das Stellglied 4 ist über eine Verbindungsleitung 14 mit der Arbeitsleitung 7 verbunden. Der in der Arbeitsleitung 7 herrschende Druck wird damit einem Druckraum 15 des ersten Stellglieds 4 zugeführt, wo er zusammen mit der Kraft einer Vorspannfeder 16 auf einen Stellkolben 17 wirkt. Die in dem Stelldruckraum 15 des ersten Stellglieds 4 auf den Stellkolben 17 aufgebrachte Kraft ist dabei so gerichtet, daß sie die hydrostatische Kolbenmaschine 2 in Richtung größerer Schwenkwinkel verstellt.The actuator 4 is connected via a connecting line 14 to the working line 7. The prevailing in the working line 7 pressure is thus supplied to a pressure chamber 15 of the first actuator 4, where it acts together with the force of a biasing spring 16 on an actuating piston 17. The applied in the control pressure chamber 15 of the first actuator 4 to the actuator piston 17 force is directed so that it adjusts the hydrostatic piston engine 2 in the direction of larger pivot angle.

Mittels der Regelventileinheit 3 wird ein Stelldruck, der in dem zweiten Stellglied 5 wirkt, geregelt. Zur Regelung des Stelldrucks ist die Regelventileinheit 3 mittels einer weiteren Verbindungsleitung 18 mit der Arbeitsleitung 7 einerseits sowie mit der Verbraucherzuleitung 8 über eine Verbrauchereingangsdruckzuleitung 19 verbunden. Über die weitere Verbindungsleitung 18 sowie die Verbrauchereingangsdruckzuleitung 19 wird der Regelventileinheit 3 der vor bzw. nach den Drosselstellen 9 und 10 herrschende Druck zugeführt. Die Regelventileinheit 3 regelt damit aufgrund des an den Drosselstellen 9 und 10 abfallenden Drucks.By means of the control valve unit 3, a control pressure which acts in the second actuator 5, regulated. To regulate the control pressure, the control valve unit 3 is connected by means of a further connecting line 18 with the working line 7 on the one hand and with the consumer supply line 8 via a consumer input pressure supply line 19. Via the further connecting line 18 and the consumer input pressure supply line 19, the control valve unit 3 is supplied to the prevailing pressure before or after the throttle bodies 9 and 10. The control valve unit 3 thus controls due to the falling at the throttle points 9 and 10 pressure.

Die Regelventileinheit 3 ist über eine Stelldruckleitung 20 mit einem Stelldruckraum 21 verbunden, der in dem Stellglied 5 angeordnet ist. Der in dem Stelldruckraum 21 herrschende Stelldruck wirkt auf einen Stellkolben 42 und verstellt die hydrostatische Kolbenmaschine 2 in Richtung kleinerer Schwenkwinkel.The control valve unit 3 is connected via a control pressure line 20 with a control pressure chamber 21 which is arranged in the actuator 5. The control pressure prevailing in the control pressure chamber 21 acts on a control piston 42 and adjusts the hydrostatic piston engine 2 in the direction of smaller swivel angles.

Wie bereits angedeutet, kann anstelle des ersten Stellgliedes 4 auch eine Feder in dem zweiten Stellglied 5 angeordnet sein, welche den Stellkolben 42 mit einer entgegen dem Druck des Stelldruckraums 21 wirkenden Kraft beaufschlagt.As already indicated, instead of the first actuator 4, a spring may be arranged in the second actuator 5, which acts on the actuating piston 42 with a force acting against the pressure of the control pressure chamber 21 force.

Die Regelventileinheit 3 besteht aus einem Grenzwertregelventil 22 und einem Förderstromregelventil 23. Das Grenzwertregelventil 22 ist mit einer ersten Feder 24 vorgespannt, so daß es sich in drucklosem Zustand in seiner in der Fig. 1 dargestellten Ausgangsposition befindet. Das Förderstromregelventil 23 ist ebenfalls mit einer zweiten Feder 25 vorgespannt, und befindet sich ebenfalls in drucklosem Zustand in seiner Ausgangsposition. Das Grenzwertregelventil 22 weist einen Förderdruckmeßanschluß 26 auf, wobei der an dem Förderdruckmeßanschluß 26 anliegende Druck der Kraft der ersten Feder 24 entgegengerichtet ist. Mit steigendem Druck wird das Grenzwertregelventil 22 aus seiner Ausgangslage in Richtung seiner zweiten Endposition ausgelenkt.The control valve unit 3 consists of a limit value control valve 22 and a flow control valve 23. The limit value control valve 22 is biased by a first spring 24, so that it is in its depressurized state in its starting position shown in FIG. The flow control valve 23 is also biased by a second spring 25, and is also in a depressurized state in its initial position. The limit value control valve 22 has a Förderdruckmeßanschluß 26, wherein the voltage applied to the Förderdruckmeßanschluß 26 pressure of the force of the first spring 24 is opposite. With increasing pressure, the limit value control valve 22 is deflected from its initial position in the direction of its second end position.

Zur Auslenkung des Förderstromregelventils 23 aus seiner Ausgangsposition ist der Kraft der zweiten Feder 25 eine hydraulische Kraft entgegengerichtet, die durch den an einem Regeldruckmeßanschluß 27 anliegenden Druck erzeugt wird. Bei dem Förderstromregelventil 23 wird die Kraft der zweiten Feder 25 durch eine auf einen Vergleichsdruckanschluß 29 wirkende Kraft ergänzt. Im Normalfall wirkt an dem Vergleichsdruckmeßanschluß 29 der Druck der Verbraucherzuleitung 8, der über die Verbrauchereingangsdruckzuleitung 19 der Meßfläche an dem Vergleichsdruckmeßanschluß 29 zugeführt wird.For deflecting the delivery flow control valve 23 from its initial position, the force of the second spring 25 is counteracted by a hydraulic force which is generated by the pressure applied to a regulating pressure measuring connection 27. In the flow control valve 23, the force of the second spring 25 is supplemented by a force acting on a comparison pressure port 29 force. In the normal case acts on the Vergleichdruckmeßanschluß 29, the pressure of the consumer supply line 8, which is supplied via the Verbraucherereangsdruckzuleitung 19 of the measuring surface at the Vergleichsdruckmeßanschluß 29.

Der Regeldruckmeßanschluß 27 des Förderstromregelventils 23 ist über einen Regeldruckkanal 30 mit dem Grenzwertregelventil 22 verbunden. In der durch die einstellbare zweite Feder 25 vorgegebenen Ausgangsposition des Förderstromregelventils 23 ist ein erster Stelldruckanschluß 31 des Förderstromregelventils 23 mit einer Entspannungsleitung 32 verbunden, die an einem Entspannungsanschluß 33 des Förderstromregelventils 23 angeschlossen ist. Die Entspannungsleitung 32 ist mit dem Tankvolumen 13 verbunden.The Regeleldmeßanschluß 27 of the flow control valve 23 is connected via a control pressure channel 30 with the limit value control valve 22. In the predetermined by the adjustable second spring 25 starting position of the flow control valve 23, a first control pressure port 31 of the flow control valve 23 is connected to a flash line 32 which is connected to a relaxation port 33 of the flow control valve 23. The expansion line 32 is connected to the tank volume 13.

Das Grenzwertregelventil 22 weist einen zweiten Stelldruckanschluß 34 sowie einen dritten Stelldruckanschluß 35 auf, über welche der Stelldruckraum 21 über die Stelldruckleitung 20 mit dem ersten Stelldruckanschluß 31 mit dem ersten Stelldruckanschluß 31 des Förderstromregelventils 23 verbunden ist. In der Ausgangsposition des Förderstromregelventils 23 ist daher der Rückstelldruckraum 21 mit dem Tankvolumen 13 verbunden. Der über die weitere Verbindungsleitung 18 aus der Arbeitsleitung 7 entnommene Druck wird einerseits dem Förderdruckmeßanschluß 26 zugeführt und andererseits über eine von der Zuleitung abzweigende Leitung mit einem Förderdruckeingang 26 des Grenzwertregelventils 22 verbunden. Der Förderdruckeingang 36 wird in der zweiten Endposition des Grenzwertregelventils 22 mit einem Förderdruckausgang 37 verbunden. Der Förderdruckausgang 37 ist über den Regeldruckkanal 30 sowohl mit dem Regeldruckmeßanschluß 27 als auch mit einem Stelldruckzuführanschluß 38 verbunden.The limit value control valve 22 has a second control pressure connection 34 and a third control pressure connection 35 via which the control pressure chamber 21 is connected via the control pressure line 20 to the first control pressure connection 31 to the first control pressure connection 31 of the flow control valve 23. In the starting position of the flow control valve 23, therefore, the return pressure chamber 21 is connected to the tank volume 13. The pressure taken over the further connecting line 18 from the working line 7 pressure is supplied on the one hand the Förderdruckmeßanschluß 26 and on the other hand connected via a branching line from the supply line to a delivery pressure input 26 of the limit value control valve 22. The delivery pressure input 36 is connected to a delivery pressure outlet 37 in the second end position of the limit value control valve 22. The delivery pressure output 37 is connected via the control pressure channel 30 with both the Regeleldmeßanschluß 27 and with a Stelldruckzuführanschluß 38.

Wird aufgrund eines steigenden Drucks im Regeldruckkanal 30 der Regeldruckmeßanschluß 27 mit einer höheren hydraulischen Kraft beaufschlagt und damit das Förderstromregelventil 23 in Richtung seiner zweiten Endposition verstellt, so wird der Stelldruckzuführanschluß 38 mit dem ersten Stelldruckanschluß 31 verbunden, so daß der Rückstelldruckraum 21 über das Grenzwertregelventil 22 sowie das Förderstromregelventil 23 aus der Arbeitsleitung 7 bedrückt wird. Zwischen der Stelldruckleitung 20 und der Entspannungsleitung 32 ist eine weitere einstellbare Drossel 39 angeordnet.If due to an increasing pressure in the control pressure channel 30 of the Regeleldmeßanschluß 27 acted upon by a higher hydraulic force and thus the flow control valve 23 is moved in the direction of its second end position, the Stelldruckzuführanschluß 38 is connected to the first control pressure port 31 so that the return pressure chamber 21 via the limit value control valve 22nd and the flow control valve 23 is depressed from the working line 7. Between the control pressure line 20 and the expansion line 32, a further adjustable throttle 39 is arranged.

Im drucklosen Zustand wird zunächst durch die Vorspannfeder 16 des Stellglieds 4 die hydrostatische Kolbenmaschine 2 auf großes Fördervolumen geschwenkt. Wird über die Antriebswelle 6 die hydrostatische Kolbenmaschine 2 angetrieben, so erzeugt diese in der Arbeitsleitung 7 einen Druck, der über die Verbindungsleitung 14 im Stelldruckraum 15 des ersten Stellglieds 4 zugeführt wird. Das erste Stellglied 4 versucht daher mit zunehmendem Druck in der Arbeitsleitung 7 die hydrostatische Kolbenmaschine 2 weiter in Richtung größerer Schwenkwinkel zu verstellen. Der steigende Druck in der Arbeitsleitung 7 wird über die weitere Verbindungsleitung 18 dem Grenzwertregelventil 22 zugeführt und beaufschlagt den Förderdruckmeßanschluß 26 mit einer hydraulischen Kraft. Wie bereits ausgeführt ist in der Ausgangsposition des Grenzwertregelventils 22 sowie des Förderstromregelventils 23 der Stelldruckraum 21 des zweiten Stellglieds 5 mit dem Tankvolumen 13 verbunden, so daß durch das zweite Stellglied 5 keine Kraft erzeugt wird, die der Stellkraft des ersten Stellglieds 4 entgegenwirkt.In the unpressurized state, the hydrostatic piston machine 2 is first pivoted to a large delivery volume by the biasing spring 16 of the actuator 4. If the hydrostatic piston engine 2 is driven via the drive shaft 6, this generates a pressure in the working line 7, which pressure is supplied via the connecting line 14 in the control pressure chamber 15 of the first actuator 4. The first actuator 4 therefore tries to adjust the hydrostatic piston engine 2 with increasing pressure in the working line 7 in the direction of larger pivot angle. The rising pressure in the working line 7 is supplied via the further connecting line 18 to the limit value control valve 22 and acts on the Förderdruckmeßanschluß 26 with a hydraulic force. As already stated, the actuating pressure chamber 21 of the second actuator 5 is connected to the tank volume 13 in the initial position of the limit value control valve 22 and the flow control valve 23, so that no force is generated by the second actuator 5, which counteracts the actuating force of the first actuator 4.

Der an dem Förderdruckmeßanschluß 26 anliegende Druck der Arbeitsleitung 7 verschiebt das Grenzwertregelventil 22 in Richtung seiner zweiten Endposition und verbindet damit bei einem durch die einstellbare Feder 24 vorgegebenen Grenzwert den Förderdruckeingang 36 mit dem Förderdruckausgang 37. Durch diesen oberhalb des Grenzwerts dem Förderstromregelventil 23 zugeführten Regeldruck regelt in diesem Bereich zusätzlich das Förderstromregelventil 23. Das Förderstromregelventil 23 wird mit steigendem Regeldruck durch die Druckbeaufschlagung des Regeldruckmeßanschluß 27 weiter in Richtung seiner zweiten Endposition verstellt, so daß über den Stelldruckzuführanschluß 38 und im weiteren Verlauf über den ersten, zweiten und dritten Stelldruckanschluß 31, 34 und 35 der Stelldruckraum 21 mit einem Stelldruck beaufschlagt wird.The applied to the Förderdruckmeßanschluß 26 pressure of the working line 7 shifts the limit value control valve 22 in the direction of its second end position and thus connects at a predetermined by the adjustable spring 24 limit the delivery pressure input 36 to the delivery pressure outlet 37. By this above the limit value of the flow control valve 23 supplied control pressure in this area in addition the flow control valve 23. The flow control valve 23 is adjusted with increasing control pressure by the pressurization of Regeleldruckmeßanschluß 27 towards its second end position, so that via the Stelldruckzuführanschluß 38 and in the course of the first, second and third control pressure port 31, 34th and 35 the control pressure chamber 21 is acted upon by a control pressure.

Das Beaufschlagen des Stelldruckraums 21 mit einem Stelldruck erfolgt wie beschrieben oberhalb eines durch das Grenzwertregelventil 22 einstellbaren Grenzwerts für den Druck in der Arbeitsleitung 7, so daß eine Rückstellkraft, die der Stellkraft des Stellglieds 4 entgegengerichtet ist, erst oberhalb eines bestimmten Mindestdrucks in der Arbeitsleitung 7 erzeugt wird. Durch diese Maßnahme ist in der Arbeitsleitung 7 ein Mindestdruck aufrechtzuerhalten, selbst wenn in der Verbraucherzuleitung 8 der Druck auf Null fällt. Oberhalb des Grenzwerts wird der Stelldruck in dem Stelldruckraum 21 durch das Förderstromregelventil 23 so eingestellt, daß an dem Förderstromregelventil 23 ein Kräftegleichgewicht eingestellt ist. Das Kräftegleichgewicht setzt sich dabei aus der Kraft der zweiten Feder 25 sowie den beiden hydraulischen Kräften, welche an den Regeldruckmeßanschluß 27 sowie dem Vergleichsdruckanschluß 29 wirken, zusammen. Oberhalb des durch das Grenzwertregelventil 22 vorgegebenen Drucks wird damit ein rückstellender Stelldruck geregelt, mit welchem eine konstante Druckdifferenz zwischen der Arbeitsleitung 7 sowie der Verbraucherzuleitung 8 eingestellt wird. Eine konstante Druckdifferenz ist dabei gleichbedeutend mit einem konstanten Fördervolumen.The loading of the control pressure chamber 21 with a control pressure is as described above an adjustable by the limit value control valve 22 limit for the pressure in the working line 7, so that a restoring force, which is opposite to the actuating force of the actuator 4, only above a certain minimum pressure in the working line. 7 is produced. By this measure, a minimum pressure is maintained in the working line 7, even if in the consumer supply line 8, the pressure drops to zero. Above the limit, the control pressure in the control pressure chamber 21 is adjusted by the flow control valve 23 so that at the flow control valve 23, a balance of forces is set. The equilibrium of forces is composed of the force of the second spring 25 and the two hydraulic forces which act on the regulating pressure measuring connection 27 and the comparison pressure connection 29. Above the predetermined by the limit value control valve 22 so that a restoring control pressure is regulated, with which a constant pressure difference between the working line 7 and the consumer supply line 8 is set. A constant pressure difference is equivalent to a constant delivery volume.

In der Verbrauchereingangsdruckzuleitung 19 ist weiterhin ein Abschaltventil 40 vorgesehen, welches im Normalbetrieb die Verbraucherzuleitung 8 mit dem Vergleichsdruckanschluß 29 verbindet. Das Abschaltventil 40 ist über einen Betätigungshebel 41 betätigbar, so daß der Vergleichsdruckanschluß 29 über die Verbrauchereingangsdruckzuleitung 19 mit dem Tankvolumen 13 zu verbinden ist. Eine Betätigung des Betätigungshebels 41 führt zu einer Entspannung an dem Vergleichsdruckanschluß 29. Dadurch überwiegt die auf das Förderstromregelventil 23 an dem Regeldruckmeßanschluß 27 aufgebrachte Kraft, so daß der Stelldruckraum 21 bedrückt wird und die hydrostatische Kolbenmaschine 2 in Richtung kleineren Schwenkwinkels verstellt wird. In Folge der Verstellung sinkt der Druck in der Arbeitsleitung 7 und damit die hydraulische Kraft, die auf das Grenzwertregelventil 22 in dem Förderdruckmeßanschluß 26 wirkt. Durch die Kraft der ersten Feder 24 wird das Grenzwertregelventil 22 folglich in Richtung seiner Ausgangsposition verstellt, so daß dem Regeldruckkanal ein geringerer Druck zugeführt wird. Durch den geringeren Regeldruck, der über den Regeldruckkanal 30 dem Regeldruckmeßanschluß 27 zugeführt wird, wird das Förderstromregelventil 23 ebenfalls in Richtung seiner Ausgangsposition verstellt, so daß der Stelldruckraum 21 bei Unterschreiten des Grenzwerts durch den Arbeitsleitungsdruck in das Tankvolumen 13 entspannt wird. In der Arbeitsleitung 7 herrscht damit immer ein durch die Einstellung des Grenzwertregelventils 22 vorgebbarer Mindestdruck. Dieser kann genutzt werden, um weitere Stelleinrichtungen oder weitere Verbraucher zu betreiben, welche einen Mindestdruck erfordern.In the consumer input pressure supply line 19, a shut-off valve 40 is further provided, which connects the consumer supply line 8 with the comparison pressure connection 29 in normal operation. The shut-off valve 40 can be actuated via an actuating lever 41, so that the comparison pressure connection 29 is to be connected to the tank volume 13 via the consumer input pressure supply line 19. An actuation of the actuating lever 41 leads to a relaxation at the comparison pressure port 29. As a result, outweighs the applied to the flow control valve 23 at the Regeldruckmeßanschluß 27 force so that the control pressure chamber 21 is depressed and the hydrostatic Piston engine 2 is adjusted in the direction of smaller pivot angle. As a result of the adjustment decreases the pressure in the working line 7 and thus the hydraulic force acting on the limit value control valve 22 in the Förderdruckmeßanschluß 26. By the force of the first spring 24, the limit value control valve 22 is thus adjusted in the direction of its initial position, so that the control pressure channel, a lower pressure is supplied. Due to the lower control pressure, which is fed to the control pressure measuring 27 via the control pressure channel 30, the flow control valve 23 is also adjusted in the direction of its initial position, so that the control pressure chamber 21 is relaxed by falling below the limit by the working line pressure in the tank volume 13. In the working line 7 there is thus always a presettable by the setting of the limit value control valve 22 minimum pressure. This can be used to operate more actuators or other consumers that require a minimum pressure.

Eine Anwendung besteht beispielsweise, wenn bei Mobilgeräten die Steuerung der Mobilschieber über Druckminderer aus dem Arbeitsdruck versorgt wird und deren Funktion auch im Stillstand (Standby) erhalten bleiben muß.One application is, for example, when the control of the mobile slide is supplied via pressure reducer from the working pressure in mobile devices and their function must be maintained even at standstill (standby).

Eine bevorzugte konstruktive Ausführung ist in der Fig. 2 dargestellt. Das Grenzwertregelventil 22 sowie das Förderstromregelventil 23 sind in einem Regelventilblock 43 angeordnet. In dem Regelventilblock 43 ist eine erste Aufnahmebohrung 44 und eine zweite Aufnahmebohrung 45 eingebracht, wobei die Mittelachsen der Aufnahmebohrungen 44 und 45 vorzugsweise parallel ausgerichtet sind.A preferred structural design is shown in FIG. 2. The limit value control valve 22 and the delivery flow control valve 23 are arranged in a control valve block 43. In the control valve block 43, a first receiving bore 44 and a second receiving bore 45 is introduced, wherein the center axes of the receiving bores 44 and 45 are preferably aligned parallel.

In der ersten Aufnahmebohrung 44 ist ein Grenzwertregelventilkolben 46 angeordnet und in der zweiten Aufnahmebohrung 45 ist ein Förderstromregelventilkolben 47 angeordnet. Der Grenzwertregelventilkolben 46 sowie der Förderstromregelventilkolben 47 sind in ihrer radialen Ausdehnung kleiner als die jeweiligen Durchmesser der ersten Aufnahmebohrung 44 bzw. zweiten Aufnahmebohrung 45 und axial verschieblich in den Aufnahmebohrungen 44 und 45 angeordnet.In the first receiving bore 44, a limit value control valve piston 46 is arranged and in the second receiving bore 45, a flow control valve piston 47 is arranged. The Grenzwertregelventilkolben 46 and the flow control valve piston 47 are smaller in their radial extent than the respective diameters of first receiving bore 44 and second receiving bore 45 and disposed axially displaceably in the receiving bores 44 and 45.

Der Förderstromregelventilkolben 47 weist an seinen Enden jeweils einen ersten Führungsabschnitt 48 bzw. einen zweiten Führungsabschnitt 49 auf, wobei die radiale Ausdehnung der Führungsabschnitte 48 und 49 mit der radialen Ausdehnung der zweiten Aufnahmebohrung 45 korrespondiert, so daß der Förderstromregelventilkolben 47 in der Aufnahmebohrung 45 geführt ist. Zwischen dem ersten und zweiten Führungsabschnitt 48 und 49 ist an den Förderstromregelventilkolben 47 ein Regelabschnitt 50 vorgesehen, an dem eine erste Steuerkante 51 sowie eine zweite Steuerkante 52 ausgebildet sind.The flow control valve piston 47 has at its ends in each case a first guide portion 48 and a second guide portion 49, wherein the radial extent of the guide portions 48 and 49 with the radial extent of the second receiving bore 45 corresponds, so that the flow control valve piston 47 is guided in the receiving bore 45 , Between the first and second guide sections 48 and 49, a control section 50 is provided on the flow control valve piston 47, on which a first control edge 51 and a second control edge 52 are formed.

Zwischen dem ersten Führungsabschnitt 48 und dem Regelabschnitt 50 ist aufgrund der unterschiedlichen radialen Ausdehnung des Förderstromregelventilkolbens 47 sowie der zweiten Aufnahmebohrung 45 ein Regeldruckraum 53 ausgebildet. Weiterhin kann zwischen dem Regelabschnitt 50 sowie dem zweiten Führungsabschnitt 49 ein weiterer Führungsabschnitt 55 vorgesehen sein.Between the first guide section 48 and the control section 50, a control pressure chamber 53 is formed due to the different radial extent of the flow control valve piston 47 and the second receiving bore 45. Furthermore, between the control section 50 and the second guide section 49, a further guide section 55 may be provided.

Der Grenzwertregelventilkolben 46 ist entsprechend dem Förderstromregelventilkolben 47 ausgebildet und weist einen ersten Führungsabschnitt 56 sowie an seinem zweiten Ende einen zweiten Führungsabschnitt 57 auf, mit dem der Grenzwertregelventilkolben 46 in der ersten Aufnahmebohrung 44 geführt ist. Zwischen dem ersten Führungsabschnitt 56 des Grenzwertregelventilkolbens 46 und einem Regelabschnitt 58 des Grenzwertregelventilkolbens 46 ist ebenfalls durch die unterschiedlichen radialen Ausdehnungen des Grenzwertregelventilkolbens 46 sowie der ersten Aufnahmebohrung 44 ein Förderdruckraum 61 ausgebildet. Der Regelabschnitt 58 des Grenzwertregelventilkolbens 46 weist ebenfalls eine erste Steuerkante 59 sowie eine zweite Steuerkante 60 auf.The Grenzwertregelventilkolben 46 is formed according to the flow control valve piston 47 and has a first guide portion 56 and at its second end a second guide portion 57, with which the limit value control valve piston 46 is guided in the first receiving bore 44. Between the first guide section 56 of the limit value control valve piston 46 and a control section 58 of the limit value control valve piston 46, a delivery pressure chamber 61 is likewise formed by the different radial expansions of the limit value control valve piston 46 and the first receiving bore 44. The control section 58 of the limit value control valve piston 46 also has a first control edge 59 and a second control edge 60.

An der Stirnseite des ersten Führungsabschnitts 56 ist ein erster Druckraum 63 ausgebildet, der über einen Überströmkanal 62 mit dem Förderdruckraum 61 verbunden ist. Der in dem Förderdruckraum 61 herrschende Druck beaufschlagt den Grenzwertregelventilkolben 46 an einer Stirnfläche 64 mit einer hydraulischen Kraft, welche in axialer Richtung auf den Grenzwertregelventilkolben 46 wirkt.On the front side of the first guide portion 56, a first pressure chamber 63 is formed, which is connected via an overflow 62 with the discharge pressure chamber 61. The pressure prevailing in the delivery pressure chamber 61 pressurizes the limit control valve piston 46 on an end face 64 with a hydraulic force which acts on the limit value control valve piston 46 in the axial direction.

In entgegengesetzter Richtung wird auf den Grenzwertregelventilkolben 46 die Kraft der ersten Feder 24, die sich an einem Federlager 65 abstützt, wobei das Federlager 65 mit dem Grenzwertregelventilkolben 46 in Wirkverbindung steht. Hierzu ist ein Sitz 66 an der Stirnseite des zweiten Führungsabschnitts 57 ausgebildet, wobei das Federlager 65 eine mit dem Sitz 66 korrespondierende Ausnehmung aufweist. Am anderen Ende der ersten Feder 24 ist ein Gegenlager 67 angeordnet, das sich an einer Einstellschraube 68 abstützt.In the opposite direction is on the Grenzwertregelventilkolben 46, the force of the first spring 24, which is supported on a spring bearing 65, wherein the spring bearing 65 is connected to the limit value control valve piston 46 in operative connection. For this purpose, a seat 66 is formed on the end face of the second guide portion 57, wherein the spring bearing 65 has a recess 66 corresponding to the seat. At the other end of the first spring 24, an abutment 67 is arranged, which is supported on an adjusting screw 68.

Durch Verdrehen der Einstellschraube 68 ist der Abstand zwischen dem Federlager 65 sowie dem Gegenlager 67 variierbar, so daß die Vorspannung der ersten Feder 24 eingestellt werden kann. Zum Fixieren der Einstellschraube 68 ist eine Kontermutter 69 vorgesehen. Weiterhin wird das offene Ende der Einstellschraube 68 mit einer Hutmutter 70 abgedeckt und damit vor Verschmutzungen geschützt. Die Kontermutter 69 sowie die Hutmutter 70 sind jeweils über ein Dichtelement, bevorzugt ein O-Ring 71, gegen ein Gehäusebauteil bzw. gegeneinander abgedichtet. Das Gegenlager 67, die Einstellschraube 68, die Kontermutter 69 und die Hutmutter 70 bilden zusammen eine Einstellvorrichtung 72 aus.By turning the adjusting screw 68, the distance between the spring bearing 65 and the thrust bearing 67 is variable, so that the bias of the first spring 24 can be adjusted. For fixing the adjusting screw 68, a lock nut 69 is provided. Furthermore, the open end of the adjusting screw 68 is covered with a cap nut 70 and thus protected from contamination. The lock nut 69 and the cap nut 70 are each sealed via a sealing element, preferably an O-ring 71, against a housing component or against each other. The anvil 67, the adjusting screw 68, the lock nut 69 and the cap nut 70 together form an adjustment device 72.

Zur Aufnahme der ersten Feder 24 ist in dem Regelventilblock 43 ein Federraum 43 vorgesehen. Parallel zu der ersten und zweiten Aufnahmebohrung 44 und 45 ist eine Verbindungsbohrung 74 ausgehend von dem Federraum 73 in den Regelventilblock 43 eingebracht. Die Verbindungsbohrung 74 mündet in eine Tankanschlußbohrung 75, wobei sich an der Außenseite des Regelventilblocks 43 ein Tankanschlußstück 76 befindet. An dem Tankanschlußstück 76 ist beispielsweise eine nicht dargestellte Rücklaufleitung angeschlossen, die mit dem Tankvolumen 13 in Verbindung steht.For receiving the first spring 24, a spring chamber 43 is provided in the control valve block 43. Parallel to the first and second receiving bore 44 and 45, a connecting bore 74 is introduced from the spring chamber 73 into the control valve block 43. The Connecting bore 74 opens into a tank connection bore 75, wherein on the outside of the control valve block 43, a tank connection piece 76 is located. At the tank connection piece 76, for example, a return line, not shown, is connected, which is in communication with the tank volume 13.

Ebenfalls an der Außenseite des Regelventilblocks 43 ist ein Förderdruckanschluß 78 vorgesehen. An dem Förderdruckanschluß 78 wird der über die weitere Verbindungsleitung 18 zugeführte Druck der Arbeitsleitung 7 dem Regelventilblock 73 zugeführt. Der Förderdruckanschluß 78 steht mit einem Förderdruckkanal 79 in Verbindung, der in den Förderdruckraum 61 ausmündet.Also on the outside of the control valve block 43, a delivery pressure port 78 is provided. At the delivery pressure connection 78, the pressure of the working line 7 supplied via the further connecting line 18 is supplied to the control valve block 73. The delivery pressure connection 78 communicates with a delivery pressure channel 79, which opens into the delivery pressure chamber 61.

Die vorstehend bereits beschriebene Funktionsweise der Regeleinrichtung 1 soll anhand des konstruktiven Ausführungsbeispiels aus Fig. 2 noch einmal kurz dargelegt werden. Erhöht sich der Druck in der Arbeitsleitung 7, so wird dieser erhöhte Druck über den Förderdruckanschluß 78 und den Förderdruckkanal 79 in den Förderdruckraum 61 weitergeleitet. Der Förderdruckraum 61 steht mit dem ersten Druckraum 63 in Verbindung, so daß der erhöhte Druck der Arbeitsleitung 7 auf die Stirnfläche 63 des Grenzwertregelventilkolbens 46 wirkt. Um den ersten Druckraum als geschlossenes Volumen auszubilden, ist die erste Aufnahmebohrung 44 mit einem Verschlußstück 83 verschlossen, wobei das Verschlußstück 83 vorzugsweise mit einer Schraubverbindung in dem Regelventilblock 43 fixiert ist. Zur Abdichtung ist ein Dichtelement 84 vorgesehen.The above-described operation of the control device 1 will be briefly explained again with reference to the structural embodiment of FIG. If the pressure in the working line 7 increases, this increased pressure is forwarded via the delivery pressure connection 78 and the delivery pressure channel 79 into the delivery pressure chamber 61. The delivery pressure chamber 61 communicates with the first pressure chamber 63, so that the increased pressure of the working line 7 acts on the end face 63 of the limit value control valve piston 46. In order to form the first pressure chamber as a closed volume, the first receiving bore 44 is closed with a closure member 83, wherein the closure member 83 is preferably fixed with a screw in the control valve block 43. For sealing, a sealing element 84 is provided.

Durch den in dem ersten Druckraum 63 herrschenden Druck wird der Grenzwertregelventilkolben 46 mit einer axialen Kraft beaufschlagt, die den Grenzwertregelventilkolben 46 in Fig. 2 nach rechts entgegen der Kraft der ersten Feder 24 bewegt. Dadurch wird die erste Steuerkante 59 an dem Regelabschnitt 58 des Grenzwertregelventilkolbens 46 ebenfalls nach rechts bewegt, wobei sie bei Überschreiten eines Grenzwerts, der über die Einstelleinrichtung 72 einstellbar ist, einen Strömungskanal aus dem Förderdruckraum 61 in den Regeldruckkanal 30 freigibt. Zusätzlich zu der Kraft der ersten Feder 24 greift an den Grenzwertregelventilkolben 46 der in dem Federraum 73 herrschende Druck des Tankvolumens 13 an.As a result of the pressure prevailing in the first pressure chamber 63, the limit value regulating valve piston 46 is acted upon by an axial force which moves the limit value regulating valve piston 46 in FIG. 2 to the right against the force of the first spring 24. As a result, the first control edge 59 is also moved to the control section 58 of Grenzwertregelventilkolbens 46 to the right, wherein it exceeds a limit value, via the adjusting 72nd is adjustable, a flow channel from the discharge pressure chamber 61 in the control pressure channel 30 releases. In addition to the force of the first spring 24, the limit value control valve piston 46 engages in the pressure of the tank volume 13 prevailing in the spring chamber 73.

Das über den Regeldruckkanal 30 dem Regeldruckraum 53 zugeführte Druckmittel wird über einen weiteren Überströmkanal 80 in einen zweiten Druckraum 81 geleitet, der an der Stirnseite des Förderstromregelventilkolbens 47 ausgebildet ist und in dem der Druck eine Kraft auf die Stirnfläche 82 des Förderstromregelventilkolbens 47 ausübt. Zum Ausbilden eines geschlossenen Volumens ist die zweite Aufnahmebohrung 45 ebenfalls mit einem Verschlußstück 83 und einem Dichtelement 84 versehen, wobei das Verschlußstück 83 ebenfalls mit einer Schraubverbindung in dem Regelventilblock 43 gesichert ist.The pressure medium supplied via the control pressure channel 30 to the control pressure chamber 53 is conducted via a further overflow channel 80 into a second pressure chamber 81 which is formed on the end face of the flow control valve piston 47 and in which the pressure exerts a force on the end face 82 of the flow control valve piston 47. To form a closed volume, the second receiving bore 45 is also provided with a closure piece 83 and a sealing element 84, wherein the closure piece 83 is also secured with a screw in the control valve block 43.

Entsprechend dem über den Regeldruckkanal 30 zugeführten Regeldruck wird der Förderstromregelventilkolben 47 aus seiner in Fig. 2 dargestellten Ausgangsposition nach rechts ausgelenkt, bis sich ein Kräftegleichgewicht zwischen dem an der Stirnfläche 82 angreifenden Regeldruck sowie den entgegengesetzten Kräften eingestellt hat. An dem zweiten Führungsabschnitt 69 des Förderstromregelventilkolbens 47 ist ein weiteres Federlager 94 angeordnet, welches mit dem konischen Sitz 93 des Förderstromregelventilkolbens 47 in Wirkverbindung steht. An dem weiteren Federlager 94 stützt sich eine zweite Feder 25 ab, wobei die zweite Feder 25 auch durch eine zusätzliche Feder 25' ergänzt werden kann, die sich ebenfalls an dem weiteren Federlager 94 abstützt. Am gegenüberliegenden Ende stützen sich die zweite Feder 25 sowie die zusätzliche Feder 25' an einem Gegenlager einer weiteren Einstellvorrichtung 95 ab, die entsprechend der Einstellvorrichtung 72 aufgebaut ist und auf deren weitere Beschreibung verzichtet wird.According to the control pressure supplied via the control pressure channel 30, the flow control valve piston 47 is deflected from its initial position shown in FIG. 2 to the right until an equilibrium of forces has been established between the control pressure acting on the end face 82 and the opposing forces. At the second guide portion 69 of the flow control valve piston 47, a further spring bearing 94 is arranged, which is in operative connection with the conical seat 93 of the flow control valve piston 47. At the other spring bearing 94, a second spring 25 is supported, wherein the second spring 25 can be supplemented by an additional spring 25 ', which is also supported on the other spring bearing 94. At the opposite end, the second spring 25 and the additional spring 25 'are supported on an abutment of a further adjustment device 95, which is constructed in accordance with the adjustment device 72 and is dispensed with its further description.

Die zweite Feder 25 und zusätzliche Feder 25' sind in einem Federraum 96 angeordnet. Der Federraum 96 ist über einen Verbrauchereingangsdruckzuleitungsanschluß 97 und einen Verbraucherdruckkanal 98 über die in Fig. 1 beschriebene Verbraucherdruckzuleitung 19 mit der Verbraucherzuleitung 8 verbunden. Entgegen der hydraulischen Kraft, welche an der Stirnfläche 82 auf den Förderstromregelventilkolben 47 wirkt, wirken damit in dem Federraum 96 sowohl die Kräfte der beiden Federn 25 und 25', als auch eine hydraulische Kraft, die proportional zu dem Verbrauchereingangsdruck ist, solange das Abschaltventil 40 nicht betätigt wird.The second spring 25 and additional spring 25 'are arranged in a spring chamber 96. The spring chamber 96 is over a Consumer input pressure supply port 97 and a consumer pressure channel 98 via the described in Fig. 1 consumer pressure supply line 19 connected to the consumer supply line 8. Contrary to the hydraulic force acting on the end face 82 on the flow control valve piston 47, so act in the spring chamber 96, both the forces of the two springs 25 and 25 ', as well as a hydraulic force which is proportional to the load input pressure, as long as the shut-off 40th not operated.

Solange diese Kräfte kleiner sind als die Kraft, die durch den Regeldruck auf den Förderstromregelventilkolben 47 wirkt, wird der Förderstromregelventilkolben 47 aus seiner in der Fig. 2 dargestellten Ausgangsposition nach rechts verschoben. Durch die Verschiebung nach rechts wird durch die erste Steuerkante 51 ein Strömungskanal aus dem Regeldruckraum 53 in einen Stelldruckkanal 85 freigegeben. Der Stelldruckkanal 85 ist als Bohrung in dem Regelventilblock 43 ausgebildet. Gleichzeitig mit dem Ausbilden eines Strömungsweges von dem Regeldruckraum 53 in den Stelldruckkanal 85 wird über die zweite Steuerkante 52 des Förderstromregelventilkolbens 47 ein Strömungsweg zwischen dem Stelldruckkanal 85 und der Tankanschlußbohrung 75 unterbrochen. Die Tankanschlußbohrung 75 und der Stelldruckkanal 85 sind in der Ausgangsposition des Förderstromregelventils 23 durch die unterschiedlichen Durchmesser des Förderstromregelventilkolbens 47 und der zweiten Aufnahmebohrung 45 miteinander verbunden.As long as these forces are smaller than the force acting on the flow control valve piston 47 by the control pressure, the flow control valve piston 47 is shifted from its starting position shown in FIG. 2 to the right. By shifting to the right, a flow channel from the control pressure chamber 53 is released into a control pressure channel 85 by the first control edge 51. The signal pressure channel 85 is formed as a bore in the control valve block 43. Simultaneously with the formation of a flow path from the control pressure chamber 53 in the control pressure channel 85, a flow path between the control pressure duct 85 and the tank connection bore 75 is interrupted via the second control edge 52 of the flow control valve piston 47. The tank port bore 75 and the control pressure channel 85 are connected to each other in the initial position of the flow control valve 23 by the different diameter of the flow control valve piston 47 and the second receiving bore 45.

Der Regeldruckkanal 30, der Stelldruckkanal 85 sowie der Tankanschlußbohrung 75 sind als Bohrungen in den Regelventilblock 43 eingebracht. Die drei Bohrungen liegen in einer Ebene und sind mit der Verbindungsbohrung 74 miteinander verbunden, wobei die Verbindungsbohrung 74 in mehrere Abschnitte unterteilt ist. Zwischen der Tankanschlußbohrung 75 und dem Stelldruckkanal 85 ist ein zweiter Abschnitt der Verbindungsbohrung 74 ausgebildet, zwischen dem Stelldruckkanal 85 sowie dem Regeldruckkanal 30 dagegen ein dritter Abschnitt der Verbindungsbohrung 74.The control pressure channel 30, the control pressure channel 85 and the tank connection bore 75 are introduced as holes in the control valve block 43. The three holes lie in a plane and are connected to each other with the connecting hole 74, wherein the connecting hole 74 is divided into several sections. Between the tank connection bore 75 and the actuating pressure channel 85, a second portion of the connecting bore 74 is formed, between the control pressure channel 85 and the control pressure channel 30, however, a third portion of the connecting hole 74th

In den Stelldruckkanal 85 ist ein erster Stopfen 86 eingesetzt, welcher von Seiten des Stelldruckkanals 85 mit einer Sackbohrung 87 versehen ist. In radialer Richtung weist der Stopfen 86 eine Drosselöffnung 88 sowie eine Verbindungsöffnung 89 auf. Über die Verbindungsöffnung 89 ist eine durchströmbare Verbindung zwischen dem dritten Abschnitt 74b des Verbindungskanals 74 und dem Stelldruckkanal 85 über die Sackbohrung 87 hergestellt. Die Drosselöffnung 88 hingegen wird durch Verdrehen des Stopfens 86 in teilweise Überdeckung mit dem zweiten Abschnitt 74a dem ersten Abschnitt der Verbindungsbohrung 74 gebracht, so daß an dieser Stelle eine einstellbare Drossel zwischen dem Stelldruckkanal 85 und der Verbindungsbohrung 74 ausgebildet ist.In the control pressure channel 85, a first plug 86 is used, which is provided by the actuating pressure channel 85 with a blind bore 87. In the radial direction, the plug 86 has a throttle opening 88 and a connection opening 89. Via the connecting opening 89, a flow-through connection between the third section 74b of the connecting channel 74 and the actuating pressure channel 85 is established via the blind bore 87. The throttle opening 88, however, is brought by twisting the plug 86 in partial overlap with the second portion 74 a the first portion of the connecting hole 74, so that at this point an adjustable throttle between the actuating pressure channel 85 and the connecting hole 74 is formed.

Der ebenfalls als Bohrung in dem Regelventilblock 43 ausgebildete Regeldruckkanal 30 ist mit einem weiteren Stopfen 90 verschlossen, in den eine weitere Sackbohrung 92 von der Außenseite her eingebracht ist, wobei die weitere Sackbohrung 92 über eine weitere Verbindungsöffnung 90 mit dem dritten Abschnitt 74b der Verbindungsbohrung 74 verbunden ist.The likewise formed as a bore in the control valve block 43 control pressure channel 30 is closed with a further stopper 90, in which a further blind bore 92 is introduced from the outside, the further blind bore 92 via a further connection opening 90 with the third portion 74b of the connecting hole 74th connected is.

Das Bedrücken des in Fig. 1 beschriebenen Stellgliedes 5 erfolgt ausgehend von der vorstehend beschriebenen Bewegung des Grenzwertregelventilkolbens 46 und des Förderstromregelventilkolbens 47 aus dem Stelldruckkanal 85 über die Sackbohrung 87 sowie die Verbindungsöffnung 89 und den dritten Abschnitt 74b der Verbindungsbohrung 74 weiter über die weitere Verbindungsöffnung 91 sowie die weitere Sackbohrung 92, von wo aus ein nicht dargestellter Leitungsabschnitt, der der Stelldruckleitung 20 aus Fig. 1 entspricht, zu dem Stelldruckraum 21 des Stellglieds 5 führt.The pressing of the actuator 5 described in Fig. 1 is carried out starting from the above-described movement of Grenzwertregelventilkolbens 46 and the Förderstromregelventilkolbens 47 from the signal pressure channel 85 via the blind bore 87 and the connecting opening 89 and the third section 74b of the connecting hole 74 on the further connection opening 91st and the further blind bore 92, from where an unillustrated line section, which corresponds to the control pressure line 20 of FIG. 1, leads to the control pressure chamber 21 of the actuator 5.

Die Betätigung des Abschaltventils 40 führt zu einer Reduzierung des Drucks in dem weiteren Federraum 96. Die daraus resultierende Stellbewegung des Förderstromregelventilkolbens 47 nach rechts wird bei sinkendem Druck in der Arbeitsleitung 7 verhindert, indem die erste Steuerkante 59 an dem Regelabschnitt 58 des Grenzwertregelventilkolbens 46 den Strömungsweg zwischen dem Förderdruckraum 61 und dem Regeldruckkanal 30 schließt. Der Druck in dem zweiten Druckraum 81 wird über die Drosselöffnung 88 in das Tankvolumen 13 entspannt, so daß der Förderstromregelventilkolben 47 in Richtung seiner Ausgangsposition aufgrund der Kräfte der beiden Federn 25 und 25' bewegt wird. Durch die Rückbewegung des Förderstromregelventilkolbens 47 wird von der zweiten Steuerkante 52 des Regelabschnitts 50 der Strömungsweg von dem Stelldruckkanal 85 in die Tankanschlußbohrung 75 freigegeben. Der Stelldruckraum 21 wird damit in das Tankvolumen 13 entspannt, so daß, wie zu Fig. 1 beschrieben, die dem Stellglied 4 entgegengerichtete Stellkraft verringert wird und damit der Schwenkwinkel der hydrostatischen Kolbenmaschine 2 so eingestellt wird, daß ein bestimmter Mindestdruck in der Arbeitsleitung 7 herrscht.The actuation of the shut-off valve 40 leads to a reduction of the pressure in the other spring chamber 96. The resulting adjustment movement of the flow control valve piston 47 to the right is at decreasing pressure in the working line 7 prevents by the first control edge 59 at the control section 58 of the limit value control valve piston 46 closes the flow path between the discharge pressure chamber 61 and the control pressure channel 30. The pressure in the second pressure chamber 81 is expanded via the throttle opening 88 in the tank volume 13, so that the flow control valve piston 47 is moved in the direction of its initial position due to the forces of the two springs 25 and 25 '. By the return movement of the flow control valve piston 47 is released from the second control edge 52 of the control section 50, the flow path from the control pressure channel 85 into the tank connection bore 75. The control pressure chamber 21 is thus relaxed in the tank volume 13, so that, as described for Fig. 1, the actuator 4 opposing force is reduced and thus the pivot angle of the hydrostatic piston engine 2 is adjusted so that a certain minimum pressure in the working line 7 prevails ,

Claims (14)

  1. Regulatory device for a pump (2) with adjustable delivery volume, with a control valve unit (3) to regulate a control pressure acting in a control pressure chamber (21) of an actuator (4, 5), where the control valve unit (3) comprises a threshold value control valve (22) subjected to the pressure of a delivery-side working line (7), and a delivery flow control valve (23) which is pressurised at a comparison pressure connection (29) with a consumer input pressure taken from a consumer supply line (8) and at a control pressure measurement connection (27) with a control pressure countering the consumer input pressure, characterised in that a control pressure supply connection (38) of the delivery flow control valve (23) can be connected variably by the threshold value control valve (22) with the delivery-side working pressure line (7).
  2. Regulatory device according to Claim 1, characterised in that when the pressure falls below a threshold value which can be set via the threshold value control valve (22), the control pressure chamber (21) of the actuator (4, 5) is connected with the tank volume (13).
  3. Regulatory device according to Claim 2, characterised in that when the threshold value is exceeded, the control pressure chamber (21) of the actuator (4, 5) can be connected variably with the delivery-side working line (7) depending on the pressure difference between the control pressure present at the control pressure measurement connection (27) and the consumer input pressure.
  4. Regulatory device according to any of Claims 1 to 3, characterised in that the control pressure acting in the control pressure chamber (21) of the actuator (4, 5), as the control pressure resetting the delivery volume of the pump (2), acts on a first actuator (4) of the actuator unit (4, 5).
  5. Regulatory device according to Claim 4, characterised in that the actuator unit (4, 5) comprises a second actuator (5) which is pressurised with the pressure of the delivery-side working line (7) and adjusts the pump (2) in the direction of greater delivery volumes.
  6. Regulatory device according to any of Claims 1 to 5, characterised in that the threshold value control valve (22) comprises a threshold value control valve piston (46) loaded with a first spring (24) and the delivery flow control valve (23) comprises a delivery flow control valve piston (47) loaded with a second spring (25), the threshold value control valve piston (46) and the delivery flow control valve piston (47) being arranged in a common control valve block (43), where a first face (64) of the threshold value control valve piston (46) is arranged next to a first pressure chamber (63) which is connected with a delivery pressure chamber (61), and where the delivery pressure chamber (61) can be connected with the control pressure channel (30) via a first control edge (59) formed on the threshold value control valve piston (46) .
  7. Regulatory device according to Claim 6, characterised in that a second face (66) of the threshold value control valve piston (46) is pressurised in a first spring chamber (73) with the pressure predominating in the first spring chamber (73) and the first spring chamber (73) is connected with the tank volume (13).
  8. Regulatory device according to Claim 6 or 7, characterised in that a first face (82) of the delivery flow control valve piston (47) is pressurised in a second pressure chamber (81) with the pressure predominating in the control pressure channel (30).
  9. Regulatory device according to Claim 8, characterised in that the second face (93) of the delivery flow control valve piston (47) is pressurised in a second spring chamber (96) with the pressure predominating in the second spring chamber (96) and the second spring chamber (96) can be connected with the consumer supply line (8).
  10. Regulatory device according to any of Claims 6 to 9, characterised in that in the control valve block (43) is formed a control pressure channel (85) which is closed with a stopper (90) and in the stopper (90) is provided a connecting opening (89) and an adjustable choke point (88), where via the connecting opening (89) the control pressure channel (85) is connected with a control pressure connection and via the adjustable choke (88) the control pressure channel (85) is connected with the tank volume (13).
  11. Regulatory device according to Claim 10, characterised in that the control pressure connection is formed in a second stopper (90) and the second stopper (90) closes the control pressure channel (30).
  12. Regulatory device according to Claim 10 or 11, characterised in that the control pressure channel (30) opens into a control pressure chamber (53) which can be connected variably with the control pressure channel (85) via a second control edge (51) formed on the delivery flow control valve piston (47).
  13. Regulatory device according to any of Claims 6 to 12, characterised in that the pretension of the first and/or second spring (24, 25, 25') can be adjusted with an adjustment device (72, 95).
  14. Regulatory device according to any of Claims 1 to 13, characterised in that the comparison pressure connection (29) of the delivery flow control valve (23) can be connected via a switch valve (40) with the tank volume (13).
EP03724958A 2002-05-03 2003-04-04 Regulatory device comprising a threshold value control valve Expired - Fee Related EP1502027B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10219850A DE10219850B3 (en) 2002-05-03 2002-05-03 Control device with limit control valve
DE10219850 2002-05-03
PCT/EP2003/003542 WO2003093676A1 (en) 2002-05-03 2003-04-04 Regulatory device comprising a threshold value control valve

Publications (2)

Publication Number Publication Date
EP1502027A1 EP1502027A1 (en) 2005-02-02
EP1502027B1 true EP1502027B1 (en) 2006-05-31

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Application Number Title Priority Date Filing Date
EP03724958A Expired - Fee Related EP1502027B1 (en) 2002-05-03 2003-04-04 Regulatory device comprising a threshold value control valve

Country Status (4)

Country Link
US (1) US7341434B2 (en)
EP (1) EP1502027B1 (en)
DE (2) DE10219850B3 (en)
WO (1) WO2003093676A1 (en)

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Publication number Priority date Publication date Assignee Title
US6874318B1 (en) * 2003-09-18 2005-04-05 Sauer-Danfoss, Inc. Automatic remote pressure compensation in an open circuit pump
FI123639B (en) * 2005-04-15 2013-08-30 Sandvik Mining & Constr Oy Method and arrangement for controlling rock drilling
DE102005035981A1 (en) * 2005-07-28 2007-02-01 Putzmeister Ag Hydraulic circuit arrangement, in particular for the drive of concrete distributor masts
DE102010048070A1 (en) * 2010-04-16 2011-10-20 Robert Bosch Gmbh Pressure and flow controller
DE102012218903B4 (en) * 2012-10-17 2023-02-16 Robert Bosch Gmbh Hydraulic valve arrangement and hydraulic machine arrangement with such a valve arrangement
CN104884818B (en) * 2012-12-21 2017-06-30 伊顿公司 The proportional flow control of fluid pump assemblies
CN104912764B (en) * 2015-05-20 2017-03-15 北京航空航天大学 The automatically controlled ratio stepless voltage regulation Variable plunger pump of direct-driving type
CN105736491B (en) * 2015-05-20 2017-09-22 北京航空航天大学 Based on the constant pressure variable plunger pump from pressure-reducing constant pressure valve
DE102016119310A1 (en) 2016-10-11 2018-04-12 Danfoss Power Solution a.s. Improved fluid control valve

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Publication number Priority date Publication date Assignee Title
DE3644769A1 (en) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh CONTROL DEVICE FOR AN ADJUSTABLE HYDROSTATIC MACHINE
DE4329164C2 (en) * 1993-08-30 1998-02-19 Brueninghaus Hydromatik Gmbh Hydraulic control valve block
DE19742157C2 (en) * 1997-09-24 1999-07-01 Brueninghaus Hydromatik Gmbh Control device for an adjustable hydraulic pump with several consumers
DE10006659B4 (en) * 2000-02-15 2018-06-28 Brueninghaus Hydromatik Gmbh Control device for a hydraulic pump

Also Published As

Publication number Publication date
DE10219850B3 (en) 2004-02-05
EP1502027A1 (en) 2005-02-02
DE50303587D1 (en) 2006-07-06
US7341434B2 (en) 2008-03-11
WO2003093676A1 (en) 2003-11-13
US20050118036A1 (en) 2005-06-02

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