EP1502027A1 - Regeleinrichtung mit grenzwertregelventil - Google Patents
Regeleinrichtung mit grenzwertregelventilInfo
- Publication number
- EP1502027A1 EP1502027A1 EP03724958A EP03724958A EP1502027A1 EP 1502027 A1 EP1502027 A1 EP 1502027A1 EP 03724958 A EP03724958 A EP 03724958A EP 03724958 A EP03724958 A EP 03724958A EP 1502027 A1 EP1502027 A1 EP 1502027A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- control valve
- control
- delivery
- connection
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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 regulating device for regulating a delivery volume for a pump with an adjustable delivery volume.
- 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 machine is controlled by using a control unit as input variables both the delivery line pressure and that of the consumer after one Throttle point supplied consumer input pressure is supplied.
- the control unit consists of two control valves arranged in a valve block, each of which is acted upon by the working line pressure on the delivery side on a first measuring surface. In the opposite direction, a spring acts on a first control valve and the consumer input pressure taken from the consumer supply line acts on the second control valve.
- the control valves are set in such a way that an actuating pressure space of an actuating unit from the working line is depressed by the first control valve when a limit value that can be set by the spring is exceeded.
- the hydrostatic piston machine is adjusted in the direction of lower delivery capacity.
- the control is carried out by the second control valve, the actuating pressure chamber of the actuator either being depressed from the working line or being released from the tank volume.
- a constant pressure ratio between the delivery-side working pressure and the consumer input pressure is maintained in this control range. Because the differential pressure between the working line and the consumer input is proportional to the delivery volume, the circuit described regulates the hydrostatic piston machine to a constant delivery volume.
- the control device has the disadvantage that when the consumer input pressure disappears, the control pressure chamber of the actuator is depressed by the second control valve, so that the pressure in the working line can drop to almost zero. If other consumer or control devices that require a minimum pressure are connected to the work line, these devices can no longer be actuated.
- control device according to the invention with the features of claim 1.
- the control device has the advantage that the same inlet pressure is not used to control a first and second control valve, which together form the control unit.
- a first control range in which a minimum pressure can be set by the limit control valve
- a second control range in which the control is above a limit value that is defined by the limit control valve a constant flow rate of the pump through the flow control valve.
- the constant flow rate is controlled by the flow control valve as a function of the consumer inlet pressure and a pressure applied to a measuring surface, the pressure present being the outlet pressure of the limit control valve. This prevents the flow control valve from disappearing
- FIG. 1 shows a hydraulic circuit diagram of a control device according to the invention.
- Fig. 2 shows a section through a control valve unit according to the invention arranged in a control valve block.
- the control device 1 acts on the swivel 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 reset element 5 can be regulated.
- the pivoting angle of the hydrostatic piston machine 2, which is driven via a drive shaft 6, is set by means of the reset element 5.
- the hydrostatic piston machine 2 conveys a pressure medium into a working line 7. Via the working line 7, the pressure medium arrives at a consumer feed line 8, to which a shown consumer is not connected.
- a throttle 9 and an adjustable throttle 10 are arranged in series between the working line 7 and the consumer feed line 8.
- the throttle 9 does not have to be designed explicitly, but can also be generated by the throttling effect of the line length.
- the A pressure limiting device 11 is also connected to the consumer feed line 8.
- the consumer supply line 8 can be expanded against a tank volume 13 via the pressure limiting device 11, relaxation taking place when the pressure in the consumer supply line 8 rises above a threshold value which can be predetermined by means of an adjusting spring 12.
- the swivel angle of the hydrostatic piston machine 2 is adjusted by means of an actuator 4 and the reset element 5.
- the actuator 4 can also be dispensed with and an adjustment in the direction of larger deflections can be generated by a spring acting on the reset element 5.
- the actuator 4 is connected to the working line 7 via a connecting line 14.
- the pressure prevailing in the working line 7 is thus supplied to a pressure chamber 15 of the first actuator 4, where it acts on an actuating piston 17 together with the force of a biasing spring 16.
- the force applied to the actuating piston 17 in the actuating pressure chamber 15 of the first actuator 4 is directed such that it adjusts the hydrostatic piston machine 2 in the direction of a larger swivel angle.
- the control valve unit 3 is connected by means of a further connecting line 18 to the working line 7 on the one hand and to the consumer feed line 8 via a consumer input pressure feed line 19.
- the pressure prevailing before or after the throttling points 9 and 10 is fed to the control valve unit 3 via the further connecting line 18 and the consumer input pressure supply line 19.
- the control valve unit 3 thus regulates on the basis of the pressure drop at the throttle points 9 and 10.
- the control valve unit 3 is connected via a signal pressure line 20 to a signal 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 machine 2 in the direction of a smaller swivel angle.
- a spring can also be arranged in the second actuator 5, which acts on the actuating piston 42 with a force acting against the pressure of the actuating pressure chamber 21.
- the control valve unit 3 consists of a limit control valve 22 and a flow control valve
- the limit control valve 22 is with a first spring
- the flow control valve 23 is also biased by a second spring 25, and is also in its depressurized state in its starting position.
- the limit control valve 22 has one
- the force of the second spring 25 is countered by a hydraulic force which is generated by the pressure applied to a control pressure measuring connection 27.
- the force of the second spring 25 is supplemented by a force acting on a comparison pressure connection 29.
- the pressure of the consumer feed line 8 which is fed via the consumer inlet pressure feed line 19 to the measuring surface at the comparison pressure measurement port 29, acts on the comparison pressure measurement port 29.
- the control pressure measuring connection 27 of the flow control valve 23 is connected to the limit control valve 22 via a control pressure channel 30.
- a first signal pressure connection 31 of the flow control valve 23 is connected to an expansion line 32 which is connected to a relaxation connection 33 of the flow control valve 23.
- the expansion line 32 is connected to the tank volume 13.
- the limit 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 reset pressure chamber 21 is therefore connected to the tank volume 13.
- the pressure withdrawn from the working line 7 via the further connecting line 18 is supplied on the one hand to the delivery pressure measuring connection 26 and on the other hand is connected to a delivery pressure inlet 26 of the limit value control valve 22 via a line branching off the supply line.
- the delivery pressure inlet 36 is connected to a delivery pressure outlet 37 in the second end position of the limit control valve 22.
- the delivery pressure outlet 37 is connected via the regulating pressure channel 30 both to the regulating pressure measuring connection 27 and to a signal pressure supply connection 38.
- control pressure supply connection 38 is connected to the first control pressure connection 31 so that the reset pressure chamber 21 via the limit control valve 22 and the flow control valve 23 from the working line 7 is depressed.
- Another adjustable throttle 39 is arranged between the control pressure line 20 and the expansion line 32.
- the hydrostatic piston machine 2 In the depressurized 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 machine 2 is driven via the drive shaft 6, it 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 machine 2 further in the direction of a larger swivel angle with increasing pressure in the working line 7. The increasing pressure in the working line 7 is supplied to the limit control valve 22 via the further connecting line 18 and acts on the delivery pressure measuring connection 26 with a hydraulic force. As already stated, the control pressure chamber 21 of the second actuator 5 is connected to the tank volume 13 in the starting 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 pressure of the working line 7 applied to the delivery pressure measuring connection 26 displaces the limit control valve 22 in the direction of its second end position and thus connects the delivery pressure inlet 36 to the delivery pressure outlet 37 at a limit value specified by the adjustable spring 24. This regulates the control pressure supplied to the delivery flow control valve 23 above the limit value In this area, the flow control valve 23 is also adjusted.
- the flow control valve 23 is adjusted with increasing control pressure by the pressurization of the control pressure measurement connection 27 in the direction of its second end position, so that via the signal pressure supply connection 38 and later on via the first, second and third signal pressure connections 31, 34 and 35 the signal pressure chamber 21 is subjected to a signal pressure.
- the loading of the signal pressure chamber 21 with a signal pressure takes place, as described, above a limit value for the pressure in the working line 7 that can be set by the limit value control valve 22, so that a restoring force that opposes the positioning force of the actuator 4 only occurs above a certain minimum pressure in the working line 7 is produced.
- This measure ensures that a minimum pressure is maintained in the working line 7, even if the pressure in the consumer supply line 8 drops to zero.
- the signal pressure in the signal pressure chamber 21 is set by the flow control valve 23 so that a balance of forces is set on the flow control valve 23.
- the equilibrium of forces is composed of the force of the second spring 25 and the two hydraulic forces which act on the control pressure measuring connection 27 and the comparison pressure connection 29.
- a resetting signal pressure is thus 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 synonymous with a constant delivery volume.
- a shutoff valve 40 is also provided in the consumer input pressure supply line 19, which connects the consumer supply line 8 to 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 via the
- Consumer inlet pressure supply line 19 is to be connected to the tank volume 13.
- An actuation of the actuation lever 41 leads to a relaxation at the comparison pressure connection 29.
- the force applied to the flow control valve 23 at the control pressure measurement connection 27 predominates, so that the control pressure chamber 21 is depressed and the hydrostatic Piston machine 2 is adjusted in the direction of a smaller swivel angle.
- the pressure in the working line 7 drops and thus the hydraulic force which acts on the limit control valve 22 in the delivery pressure measuring connection 26.
- the force of the first spring 24 consequently moves the limit control valve 22 in the direction of its starting position, so that a lower pressure is supplied to the control pressure channel.
- the delivery flow control valve 23 Due to the lower control pressure, which is supplied to the control pressure measuring connection 27 via the control pressure channel 30, the delivery flow control valve 23 is also adjusted in the direction of its starting position, so that the control pressure chamber 21 is released into the tank volume 13 when the working line pressure falls below the limit value. In the working line 7 there is therefore always a minimum pressure which can be predetermined by the setting of the limit control valve 22. This can be used to operate additional control devices or additional consumers that require a minimum pressure.
- One application is, for example, when the control of the mobile slide valve is supplied from the working pressure by pressure reducers in mobile devices and its function must be maintained even when the machine is at a standstill.
- FIG. 2 A preferred design is shown in FIG. 2.
- the limit control valve 22 and the flow control valve 23 are arranged in a control valve block 43.
- a first receiving bore 44 and a second receiving bore 45 are made in the control valve block 43, the central axes of the receiving bores 44 and 45 preferably being aligned in parallel.
- a limit value control valve piston 46 is arranged in the first receiving bore 44 and a delivery flow control valve piston 47 is arranged in the second receiving bore 45.
- the limit control valve piston 46 and the delivery flow control valve piston 47 are smaller in their radial dimensions than the respective diameters of the first receiving bore 44 and second receiving bore 45 and axially displaceably arranged in the receiving bores 44 and 45.
- the flow control valve piston 47 has at its ends a first guide section 48 and a second guide section 49, the radial extension of the guide sections 48 and 49 corresponding to the radial extension of the second receiving bore 45, 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 between the first guide section 48 and the control section 50 due to the different radial expansion of the flow control valve piston 47 and the second receiving bore 45. Furthermore, a further guide section 55 can be provided between the control section 50 and the second guide section 49.
- the limit control valve piston 46 is designed corresponding to the flow control valve piston 47 and has a first guide section 56 and at its second end a second guide section 57 with which the limit control valve piston 46 is guided in the first receiving bore 44.
- a delivery pressure chamber 61 is also formed 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 due to the different radial dimensions 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 likewise has a first control edge 59 and a second control edge 60.
- a first pressure chamber 63 is formed on the end face of the first guide section 56 and is connected to the delivery pressure chamber 61 via an overflow channel 62. The pressure prevailing in the delivery pressure chamber 61 acts on the limit value 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, is applied to the limit value control valve piston 46, the spring bearing 65 being in operative connection with the limit value control valve piston 46.
- a seat 66 is formed on the end face of the second guide section 57, the spring bearing 65 having a recess corresponding to the seat 66.
- a counter bearing 67 is arranged, which is supported on an adjusting screw 68.
- a lock nut 69 is provided to fix the adjusting screw 68. Furthermore, the open end of the adjusting screw 68 is covered with a cap nut 70 and thus protected from dirt.
- 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 one another.
- the counter bearing 67, the adjusting screw 68, the lock nut 69 and the cap nut 70 together form an adjusting device 72.
- a spring chamber 43 is provided in the control valve block 43 for receiving the first spring 24.
- a connecting bore 74 is made in the control valve block 43 starting from the spring chamber 73.
- the Connecting bore 74 opens into a tank connection bore 75, with a tank connector 76 being on the outside of the control valve block 43.
- a return line, not shown, is connected to the tank connection piece 76 and is connected to the tank volume 13.
- a delivery pressure connection 78 is also provided on the outside of the control valve block 43. At the delivery pressure connection 78, the pressure of the working line 7 fed via the further connecting line 18 is fed to the control valve block 73.
- the delivery pressure connection 78 is connected to a delivery pressure channel 79 which opens into the delivery pressure chamber 61.
- the above-described mode of operation of the control device 1 is to be briefly explained again on the basis of the constructive exemplary embodiment from FIG. 2. If the pressure in the working line 7 increases, this increased pressure is passed on via the delivery pressure connection 78 and the delivery pressure channel 79 into the delivery pressure chamber 61.
- the delivery pressure chamber 61 is in communication 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 control valve piston 46.
- the first receiving bore 44 is closed with a closure piece 83, the closure piece 83 preferably being fixed in the control valve block 43 with a screw connection.
- a sealing element 84 is provided for sealing.
- the limit control valve piston 46 Due to the pressure prevailing in the first pressure chamber 63, the limit control valve piston 46 is subjected to an axial force which moves the limit control valve piston 46 to the right in FIG. 2 against the force of the first spring 24. As a result, the first control edge 59 on the control section 58 of the limit value control valve piston 46 is likewise moved to the right, and when a limit value is exceeded, which is via the adjusting device 72 is adjustable, releases a flow channel from the delivery pressure chamber 61 into the control pressure channel 30. In addition to the force of the first spring 24, the pressure of the tank volume 13 acting in the spring chamber 73 acts on the limit control valve piston 46.
- the pressure medium supplied to the control pressure chamber 53 via the control pressure channel 30 is passed 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, the closure piece 83 likewise being secured with a screw connection in the control valve block 43.
- the delivery flow control valve piston 47 is deflected to the right from its starting position shown in FIG. 2 until a balance 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 on the second guide section 69 of the flow control valve piston 47 and is operatively connected to the conical seat 93 of the flow control valve piston 47.
- a second spring 25 is supported on the further spring bearing 94, the second spring 25 also being able to be supplemented by an additional spring 25 ′, which is likewise supported on the further spring bearing 94.
- the second spring 25 and the additional spring 25 ' are supported on a counter bearing of a further adjusting device 95, which is constructed in accordance with the adjusting device 72 and the further description of which is dispensed with.
- 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 line connection 97 and a consumer pressure channel 98 are connected to the consumer supply line 8 via the consumer pressure supply line 19 described in FIG. 1.
- both the forces of the two springs 25 and 25 ′ act in the spring chamber 96, as well as a hydraulic force which is proportional to the consumer input pressure, as long as the shutoff valve 40 is not operated.
- the delivery flow control valve piston 47 is displaced to the right from its initial position shown in FIG. 2.
- a flow channel from the control pressure chamber 53 into a signal pressure channel 85 is released by the first control edge 51.
- the control pressure channel 85 is designed as a bore in the control valve block 43.
- a flow path between the control pressure channel 85 and the tank connection bore 75 is interrupted via the second control edge 52 of the delivery flow control valve piston 47.
- the tank connection bore 75 and the control pressure channel 85 are connected to one another in the starting position of the flow control valve 23 by the different diameters 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 bores in the control valve block 43.
- the three bores lie in one plane and are connected to one another with the connecting bore 74, the connecting bore 74 being divided into a plurality of sections.
- a second section of the connecting bore 74 is formed between the tank connection bore 75 and the actuating pressure channel 85, while a third section of the connecting bore 74 is formed between the actuating pressure channel 85 and the regulating pressure channel 30.
- a first plug 86 is inserted into the control pressure channel 85 and is provided with a blind bore 87 on the side of the control pressure channel 85.
- the plug 86 has a throttle opening 88 and a connecting opening 89 in the radial direction.
- a flow-through connection between the third section 74b of the connection channel 74 and the actuating pressure channel 85 is established via the blind hole 87 via the connection opening 89.
- the throttle opening 88 is brought into partial overlap with the second section 74a of the first section of the connecting bore 74 by rotating the plug 86, so that an adjustable throttle is formed between the actuating pressure channel 85 and the connecting bore 74 at this point.
- the control pressure channel 30, which is also designed as a bore in the control valve block 43, is closed with a further plug 90, into which a further blind bore 92 is made from the outside, the further blind bore 92 via a further connection opening 90 with the third section 74b of the connection bore 74 connected is .
- the actuator 5 described in FIG. 1 is pressed on the basis of the movement of the limit control valve piston 46 and the delivery flow control valve piston 47 described above from the actuating pressure channel 85 via the blind bore 87 as well as the connection opening 89 and the third section 74b of the connection bore 74 via the further connection opening 91 and the further blind bore 92, from where a line section, not shown, which corresponds to the signal pressure line 20 from FIG. 1, leads to the signal pressure space 21 of the actuator 5.
- the actuation of the shutoff valve 40 leads to a reduction in the pressure in the further spring chamber 96.
- the resulting adjustment movement of the delivery flow control valve piston 47 to the right becomes falling pressure in the working line 7 is prevented by the first control edge 59 on the control section 58 of the limit control valve piston 46 closing the flow path between the delivery pressure chamber 61 and the control pressure channel 30.
- the pressure in the second pressure chamber 81 is released into the tank volume 13 via the throttle opening 88, so that the delivery flow control valve piston 47 is moved in the direction of its starting position due to the forces of the two springs 25 and 25 '.
- the flow path from the control pressure channel 85 into the tank connection bore 75 is released by the second control edge 52 of the control section 50.
- the signal pressure chamber 21 is thus expanded into the tank volume 13, so that, as described in relation to FIG. 1, the actuating force opposing the actuator 4 is reduced and the pivoting angle of the hydrostatic piston machine 2 is set such that a certain minimum pressure prevails in the working line 7 ,
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10219850 | 2002-05-03 | ||
DE10219850A DE10219850B3 (de) | 2002-05-03 | 2002-05-03 | Regeleinrichtung mit Grenzwertregelventil |
PCT/EP2003/003542 WO2003093676A1 (de) | 2002-05-03 | 2003-04-04 | Regeleinrichtung mit grenzwertregelventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1502027A1 true EP1502027A1 (de) | 2005-02-02 |
EP1502027B1 EP1502027B1 (de) | 2006-05-31 |
Family
ID=29285082
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03724958A Expired - Fee Related EP1502027B1 (de) | 2002-05-03 | 2003-04-04 | Regeleinrichtung mit grenzwertregelventil |
Country Status (4)
Country | Link |
---|---|
US (1) | US7341434B2 (de) |
EP (1) | EP1502027B1 (de) |
DE (2) | DE10219850B3 (de) |
WO (1) | WO2003093676A1 (de) |
Families Citing this family (9)
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 |
WO2014100594A1 (en) * | 2012-12-21 | 2014-06-26 | Eaton Corporation | Proportional flow control of a fluid pump assembly |
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 |
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 |
DE102016119310A1 (de) | 2016-10-11 | 2018-04-12 | Danfoss Power Solution a.s. | Verbessertes Fluidsteuerventil |
Family Cites Families (4)
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 |
-
2002
- 2002-05-03 DE DE10219850A patent/DE10219850B3/de not_active Expired - Fee Related
-
2003
- 2003-04-04 EP EP03724958A patent/EP1502027B1/de not_active Expired - Fee Related
- 2003-04-04 WO PCT/EP2003/003542 patent/WO2003093676A1/de active IP Right Grant
- 2003-04-04 US US10/505,208 patent/US7341434B2/en not_active Expired - Fee Related
- 2003-04-04 DE DE50303587T patent/DE50303587D1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO03093676A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1502027B1 (de) | 2006-05-31 |
DE50303587D1 (de) | 2006-07-06 |
WO2003093676A1 (de) | 2003-11-13 |
US7341434B2 (en) | 2008-03-11 |
DE10219850B3 (de) | 2004-02-05 |
US20050118036A1 (en) | 2005-06-02 |
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