EP1502027B1 - Dispositif de regulation comprenant une soupape de regulation de valeur limite - Google Patents

Dispositif de regulation comprenant une soupape de regulation de valeur limite Download PDF

Info

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)
English (en)
Other versions
EP1502027A1 (fr
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1502027A1 publication Critical patent/EP1502027A1/fr
Application granted granted Critical
Publication of EP1502027B1 publication Critical patent/EP1502027B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

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

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de régulation pour une pompe (2) dont le volume refoulé peut être réglé. Le dispositif de régulation selon l'invention comprend une unité de soupape de régulation (3) servant à réguler une pression de réglage opérant dans une chambre de pression de réglage (21) d'une unité de réglage (4, 5). L'unité de soupape de régulation (3) comprend une soupape de régulation de valeur limite (22) et une soupape de régulation de débit de refoulement (23). La soupape de régulation de valeur limite (22) est soumise à la pression d'une conduite de travail (7) côté refoulement et la soupape de régulation de débit de refoulement (23) peut être soumise, au niveau d'un raccord de pression de comparaison (29), à une pression d'entrée de consommateur prélevée sur une conduite d'alimentation de consommateur (8). La soupape de régulation de débit de refoulement (23) est en outre soumise, au niveau d'un raccord de mesure de pression de régulation (27), à une pression de régulation s'opposant à la pression d'entrée de consommateur. Un raccord d'alimentation de pression de réglage (38) de la soupape de régulation de débit de refoulement (23) peut être relié de manière variable à la conduite de pression de travail (7) côté refoulement au moyen de la soupape de régulation de valeur limite (22).

Claims (14)

  1. Dispositif de régulation pour une pompe (2) à débit réglable, avec une unité à soupapes de régulation (3) permettant la régulation d'une pression de réglage agissant dans une chambre de pression de réglage (21) d'une unité de réglage (4, 5), l'unité à soupapes de régulation (3) comprenant une soupape de régulation de valeur limite (22), qui est soumise à la pression d'une conduite de travail (7) côté refoulement, et une soupape de régulation de débit (23), qui est soumise à une pression d'entrée d'utilisation provenant d'une conduite d'alimentation d'utilisation (8) au niveau d'un raccord de pression de comparaison (29) et à une pression de réglage opposée à la pression d'entrée d'utilisation au niveau d'un raccord de mesure de pression de réglage (27),
    caractérisé en ce que un raccord d'arrivée de pression de réglage (38) de la soupape de régulation de débit (23) peut être raccordé de façon variable à la conduite de pression de travail (7) côté refoulement par l'intermédiaire de la soupape de régulation de valeur limite (22).
  2. Dispositif de régulation selon la revendication 1,
    caractérisé en ce qu'en cas de dépassement de la limite inférieure d'une valeur limite réglable à l'aide de la soupape de régulation de valeur limite (22), la chambre de pression de réglage (21) de l'unité de réglage (4, 5) est reliée au réservoir (13).
  3. Dispositif de régulation selon la revendication 2,
    caractérisé en ce qu'en cas de dépassement de la valeur limite, la chambre de pression de réglage (21) de l'unité de réglage (4, 5) peut être reliée de façon variable à la conduite de travail (7) côté refoulement en fonction de la différence de pression entre la pression de réglage présente au niveau du raccord de mesure de pression de réglage (27) et la pression d'entrée d'utilisation.
  4. Dispositif de régulation selon l'une des revendications 1 à 3,
    caractérisé en ce que la pression de réglage régnant dans la chambre de pression de réglage (21) de l'unité de réglage (4, 5) et ayant pour effet de rétablir le débit de la pompe (2) agit sur un premier actionneur (4) de l'unité de réglage (4,5).
  5. Dispositif de régulation selon la revendication 4,
    caractérisé en ce que l'unité de réglage (4, 5) comprend un deuxième actionneur (5) qui est soumis à la pression de la conduite de travail (7) côté refoulement et qui ajuste la pompe (2) dans le sens d'un débit supérieur.
  6. Dispositif de régulation selon l'une des revendications 1 à 5,
    caractérisé en ce que la soupape de régulation de valeur limite (22) comprend un piston de soupape de régulation de valeur limite (46) commandé par un premier ressort (24) et la soupape de régulation de débit (23) comprend un piston de soupape de régulation de débit (47) commandé par un deuxième ressort (25), le piston de soupape de régulation de valeur limite (46) et le piston de soupape de régulation de débit (47) étant disposés dans un bloc de soupapes de régulation (43)
    et une première face avant (64) du piston de soupape de régulation de valeur limite (46) étant contiguë à une première chambre de pression (63) qui est reliée à une chambre de pression de refoulement (61) et la chambre de pression de refoulement (61) pouvant être reliée à un passage de pression de régulation (30) par une rampe hélicoïdale (59) formée sur le piston de soupape de régulation de valeur limite (46).
  7. Dispositif de régulation selon la revendication 6,
    caractérisé en ce qu'une deuxième face avant (66) du piston de soupape de régulation de valeur limite (46) dans une première chambre à ressorts (73) est soumise à la pression régnant dans la première chambre à ressorts (73) et en ce que la première chambre à ressorts (73) est reliée au réservoir (13).
  8. Dispositif de régulation selon la revendication 6 ou 7,
    caractérisé en ce qu'une première face avant (82) du piston de soupape de régulation de débit (47) dans une deuxième chambre de pression (81) est soumise à la pression régnant dans le passage de pression de régulation (30).
  9. Dispositif de régulation selon la revendication 8,
    caractérisé en ce que la deuxième face avant (93) du piston de soupape de régulation de débit (47) dans une deuxième chambre à ressorts (96) est soumise à la pression régnant dans la deuxième chambre à ressorts (96) et en ce que la deuxième chambre à ressorts (96) peut être reliée à la conduite d'alimentation d'utilisation (8).
  10. Dispositif de régulation selon l'une des revendications 6 à 9,
    caractérisé en ce que dans le bloc de soupapes de régulation (43) est formé un passage de pression de réglage (85) qui est fermé avec un bouchon (90) et en ce que dans le bouchon (90) sont prévus un orifice de liaison (89) et un point d'étranglement réglable (88), le passage de pression de réglage (85) étant relié à un raccord de pression de réglage par l'orifice de liaison (89) et le passage de pression de réglage (85) étant relié au réservoir (13) par l'étranglement réglable (88).
  11. Dispositif de régulation selon la revendication 10,
    caractérisé en ce que le raccord de pression de réglage est formé dans un deuxième bouchon (90) et en ce que le passage de pression de régulation (30) est fermé avec le deuxième bouchon (90).
  12. Dispositif de régulation selon la revendication 10 ou 11,
    caractérisé en ce que le passage de pression de régulation (30) aboutit dans une chambre de pression de régulation (53) qui peut être raccordée de façon variable au passage de pression de réglage (85) par une deuxième rampe hélicoïdale (51) qui est formée sur le piston de soupape de régulation de débit (47).
  13. Dispositif de régulation selon l'une des revendications 6 à 12,
    caractérisé en ce que la précontrainte du premier et/ou du deuxième ressort (24, 25, 25') peut être ajustée avec le dispositif d'ajustement (72, 95).
  14. Dispositif de régulation selon l'une des revendications 1 à 13,
    caractérisé en ce que le raccord de pression de comparaison (29) de la soupape de régulation de débit (23) peut être reliée au réservoir (13) par une soupape de commande (40).
EP03724958A 2002-05-03 2003-04-04 Dispositif de regulation comprenant une soupape de regulation de valeur limite Expired - Fee Related EP1502027B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10219850A DE10219850B3 (de) 2002-05-03 2002-05-03 Regeleinrichtung mit Grenzwertregelventil
DE10219850 2002-05-03
PCT/EP2003/003542 WO2003093676A1 (fr) 2002-05-03 2003-04-04 Dispositif de regulation comprenant une soupape de regulation de valeur limite

Publications (2)

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

Family

ID=29285082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03724958A Expired - Fee Related EP1502027B1 (fr) 2002-05-03 2003-04-04 Dispositif de regulation comprenant une soupape de regulation de valeur limite

Country Status (4)

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

Families Citing this family (9)

* Cited by examiner, † Cited by third party
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 (fi) * 2005-04-15 2013-08-30 Sandvik Mining & Constr Oy Menetelmä ja sovitelma kallionporauksen ohjaamiseksi
DE102005035981A1 (de) * 2005-07-28 2007-02-01 Putzmeister Ag Hydraulische Schaltungsanordnung, insbesondere für den Antrieb von Betonverteilermasten
DE102010048070A1 (de) * 2010-04-16 2011-10-20 Robert Bosch Gmbh Druck-Förderstromregler
DE102012218903B4 (de) * 2012-10-17 2023-02-16 Robert Bosch Gmbh Hydraulische Ventilanordnung und hydraulische Maschinenanordnung mit einer derartigen Ventilanordnung
CN104884818B (zh) * 2012-12-21 2017-06-30 伊顿公司 流体泵组件的比例流量控制
CN104912764B (zh) * 2015-05-20 2017-03-15 北京航空航天大学 直驱型电控比例无级调压变量柱塞泵
CN105736491B (zh) * 2015-05-20 2017-09-22 北京航空航天大学 基于自减压恒压阀的恒压变量柱塞泵
DE102016119310B4 (de) 2016-10-11 2024-08-08 Danfoss Power Solution a.s. Verbessertes Fluidsteuerventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine
DE4329164C2 (de) * 1993-08-30 1998-02-19 Brueninghaus Hydromatik Gmbh Hydraulischer Steuerventilblock
DE19742157C2 (de) * 1997-09-24 1999-07-01 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern
DE10006659B4 (de) 2000-02-15 2018-06-28 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine Hydropumpe

Also Published As

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

Similar Documents

Publication Publication Date Title
EP0149787B1 (fr) Dispositif de régulation de débit pour une pompe hydraulique réglable
DE2813486C2 (de) Steuervorrichtung für Hydraulikpumpen
EP1502027B1 (fr) Dispositif de regulation comprenant une soupape de regulation de valeur limite
DE2063318C3 (de) Hydraulischer Unterbrecher
DE69400583T2 (de) Regler für eine Pumpe mit veränderlicher Förderleistung
EP0471166B1 (fr) Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables
DE69937729T2 (de) Ventil zum aufteilen des durchflusses
DE3919175C2 (fr)
EP1934487B1 (fr) Dispositif de commande hydraulique
EP1497559A1 (fr) Systeme de commande hydraulique faisant appel au principe de la sensibilite de charge
DE3508432C2 (fr)
DE3107915C2 (de) Hydraulische Steuereinrichtung, insbesondere Lenkeinrichtung
DE4219552C2 (de) Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit
DE2151837C2 (de) Hydraulische Steuervorrichtung für die lastunabhängige Druchflußregulierung zu einem Verbraucher
DE2508268C3 (de) Steuerkolben fur hydraulische Druckmittelfolgesteuerungen, insbesondere für ein Lenkventil einer Servolenkeinrichtung von Fahrzeugen
WO2005111430A1 (fr) Ensemble soupape hydraulique, en particulier ensemble soupape hydraulique a eau
EP1481167B1 (fr) Dispositif a soupapes
DE3630454C1 (en) Device for controlling hydraulic drives
DE19713934A1 (de) Lastdruckgeführter Förderstromregler mit Spülkreislauf
EP0954703B1 (fr) Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques
WO2009150062A2 (fr) Système d'alimentation hydraulique conçu pour alimenter un consommateur hydraulique comprenant au moins une zone consommatrice
DE10035631C2 (de) Nullastschaltung
DE10004975C2 (de) Mehrstufiges hydraulisches Druckbegrenzungsventil
EP0972940B1 (fr) Dispositif de contrôle de puissance pour la régulation de la puissance hydraulique dans un circuit de travail
DE19646687C1 (de) Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20040528

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20060531

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20060531

REF Corresponds to:

Ref document number: 50303587

Country of ref document: DE

Date of ref document: 20060706

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070301

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120423

Year of fee payment: 10

Ref country code: SE

Payment date: 20120423

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20130627

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20130424

Year of fee payment: 11

Ref country code: FR

Payment date: 20130523

Year of fee payment: 11

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130404

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130405

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130404

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50303587

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50303587

Country of ref document: DE

Effective date: 20141101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140404