EP0052405A1 - Dispositif pour régler la différence de pression d'un moteur hydraulique - Google Patents

Dispositif pour régler la différence de pression d'un moteur hydraulique Download PDF

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Publication number
EP0052405A1
EP0052405A1 EP81201259A EP81201259A EP0052405A1 EP 0052405 A1 EP0052405 A1 EP 0052405A1 EP 81201259 A EP81201259 A EP 81201259A EP 81201259 A EP81201259 A EP 81201259A EP 0052405 A1 EP0052405 A1 EP 0052405A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
hydraulic motor
der
lines
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.)
Withdrawn
Application number
EP81201259A
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German (de)
English (en)
Inventor
Pierre Dr. Bohler
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.)
Rheinmetall Air Defence AG
Original Assignee
Werkzeugmaschinenfabrik Oerlikon Buhrle AG
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 Werkzeugmaschinenfabrik Oerlikon Buhrle AG filed Critical Werkzeugmaschinenfabrik Oerlikon Buhrle AG
Publication of EP0052405A1 publication Critical patent/EP0052405A1/fr
Withdrawn legal-status Critical Current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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • 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
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members

Definitions

  • the invention relates to a device for regulating the differential pressure on a hydraulic motor, which has two connections, to each of which an absolute pressure sensor is connected.
  • each connection of the hydraulic motor to a separate control valve is connected which has a control piston with only one pressure edge and only one return edge and that each control valve has only one connection to the hydraulic motor apart from the connections to a pump and to a container.
  • the known device has a hydraulic motor 1 and a servo valve 2.
  • Two lines 3 and 4 connect the servo valve 2 to the hydraulic motor 1.
  • Two further lines 5 and 6 connect the servo valve 2 to a pressure medium source 7, for example a pressure oil pump, and a further line 8 leads to a pressure medium tank 9.
  • the lines 3 and 4 prevailing Pressures are labeled p A and p B.
  • the servo valve 2 contains two control pistons 10 and 11, which are rigidly connected to one another by a piston rod 12. The two pistons 10 and 11 can be shifted to the right and left from the starting position shown by a control member 13.
  • the pressure p A increases from approximately p / 2 to p / 2 + ⁇ p / 2 and the pressure p B decreases from approximately p / 2 to p / 2 - ⁇ p / 2.
  • 4p p A - p B is the differential pressure which, as is known, depends on the deflection of the pistons and the flow rate per unit of time.
  • the course of the pressures p A and p B in the lines 3 and 4 for the central position and for the deflections of the pistons 10 and 11 to the left and to the right is shown in FIG. 3.
  • the trailing edges R of the pistons 10 and 11 have been ground back, as a result of which the throttle cross sections between the trailing edges R of the pistons 10 and 11 and the control edges of the connections 3 'and 4' have become larger.
  • the pressure p A and p in the lines 3 and 4 can be reduced and a smaller clamping pressure of, for example, 100 bar arises, since the throttle cross sections between the pressure edges D of the pistons 10 and 11 and the control edges of the connections 3 'and 4' are the same are.
  • the servo valve according to FIG. 2 is similar to the servo valve shown in FIG. 1.
  • FIG. 4 The course of the pressures p A and p B in the lines 3 and 4 for the central position and for the deflections of the pistons 10 and 11 to the left and right of the servo valve according to FIG. 2 is shown in FIG. 4.
  • the control pistons 10 and 11 are shifted to the right, the pressure p A increases and the pressure p B decreases, although p A increases more than p B decreases.
  • the curves of the pressures p A and p are no longer symmetrical to the pressure of 50 bar mentioned.
  • the "clamping pressure" or “total pressure” p A + p B is no longer constant equal to 100 bar as shown in FIG. 3, but variable and increases with increasing ⁇ p as shown in FIG. 4.
  • a differential pressure ⁇ p O
  • the clamping pressure is approx. 100 bar at a pump pressure of 200 bar.
  • the clamping pressure is also greater than 100 bar.
  • the servo valve according to FIG. 2 also has the disadvantage that the smaller clamping pressure can only be achieved with great manufacturing effort. In the case of series production of such valves, a tolerance of ⁇ 30% can also be expected.
  • the servo valve according to FIG. 2 also has the disadvantage that the clamping pressure is dependent on the pump pressure. If, for example, the pump pressure changes by ⁇ 20%, the clamping pressure also changes by this amount.
  • the servo valve according to FIG. 2 has the disadvantage that the oil losses are relatively large, ie the pistons 10 and 11 flow in the central position a relatively large amount of oil from the pump 7 via the throttle points of the servo valve into the container 9.
  • the known device has a servo valve 25 which is connected to a pump 45 and to a container 49. Furthermore, the servo valve 25 is connected via connections 18 and 19 to the hydraulic motor 1, which is connected to a load 100.
  • the servo valve 25 has two pistons 10 and 11, which are connected to a control member 13 via a piston rod 12.
  • a controller 24 is connected to the control member 13, which delivers a control current i to the control member 13 in order to shift the pistons 10 and 11 to the right or left, whereby the pressure difference ⁇ p on the hydraulic motor 1 can be controlled.
  • an absolute pressure sensor 20 and 21 is connected, with which the pressures p A and p B at the connections 18 and 19 of the hydraulic motor 1 are measured.
  • This Current i is input to the control member 13 of the servo valve 25.
  • the piston 10, 11 of the servo valve is displaced by the control member 13 until a differential pressure 4p is generated at the connections 18 and 19 of the hydraulic motor 1, which pressure corresponds to the target differential pressure ⁇ p s .
  • the device according to the invention for regulating the differential pressure of a hydraulic motor which is connected to a load, has two flow servo valves 28 and 29, which from one of its two outputs via lines 30, 31 to the connections 63, 64 of a hydraulic motor 27 are connected, the hydraulic motor 27 in turn being connected to a load 200.
  • the other output 50, 51 of the two servo valves 28 and 29 is not used and is therefore closed.
  • the two servo valves 28, 29 are connected to a pressure medium source, ie to a pump 44 via lines 40, 41, 42 and 43 and to a container 48 via line 47.
  • the control of the two servo valves 28 and 29, that is to say the displacement of their control pistons 36, 37, 38 and 39 from their central position to the right or to the left, is carried out by currents i A and i B which are supplied by two electronic controllers 52 and 53 via lines 206 and 207 on two electro-hydraulic control members 34 and 35 are supplied.
  • Each of the two electronic controllers 52 and 53 is connected via a line 204 and 205 to the output of a subtractor 54 and 55, respectively.
  • One electrical absolute pressure transmitter 32 and 33, which measures the pressure p A and p B in the lines 30 and 31, is connected via a line 202 and 203 to the minus input of the electronic subtractors 54 and 55 mentioned.
  • Each plus input of the two electronic subtractors 54 and 55 is connected via a line 57 and 58 to the output of an electronic function generator 56 and 56 '.
  • the setpoint of the differential pressure ⁇ p s is entered in the form of an electrical signal to the two function generators 56 and 56 'via a common line 201.
  • the two output signals p As and p Bs correspond to the nominal values of the absolute pressures at the connections 63 and 64 of the hydraulic motor 27.
  • the effectively occurring absolute pressures p A and p B at the connections 63 and 64 of the hydraulic motor are measured by the said absolute pressure sensors 32 and 33 in the form of an electrical voltage pp . passed to subtractors 54 and 55.
  • the subtractors 54 and 55 subtract the actual values p A and p B from the target values p As and p Bs , which are the functions deliver generators.
  • the absolute pressures p A p B measured on the hydraulic motor 27, which are referred to as the control variable always match the setpoints of the pressures p As and p Bs , which are referred to as the control variable, generated by the function generator 56 and 56 ', both the control variables p A p B and the leadership g Rössen as p and p Bs to the subtractors 54 and 55 reach.
  • the course of the absolute pressures p A and p B is determined by the function generator 56, 56 'as a function of the course ⁇ p s .
  • FIGS. 7 and 8 correspond to two different embodiments of the function generator.
  • the clamping pressure ⁇ p on the hydraulic motor increases linearly with the target value of the differential pressure ⁇ p s .
  • the clamping pressure is approx. 20 bar.
  • the internal friction in the hydraulic motor 27 is thus small and its synchronism behavior at low speeds is therefore good.
  • the device according to the invention makes it possible to freely select the clamping pressure ⁇ p in the hydraulic motor 27 with the aid of a suitable function generator, which is to be regarded as an essential advantage.
  • a small clamping pressure in the hydraulic motor 27 the friction in the hydraulic motor is also small, which increases its efficiency and significantly improves its synchronization behavior even at very low speeds, and the clamping pressure ⁇ p is not influenced by the pressure fluctuations in the pressure oil supply.
  • the advantage is that there are no special requirements for the manufacturing accuracy of the servo valves.
  • the servo valve is easier to manufacture, since the number of tolerances to be observed is smaller (according to FIG. 6) and, moreover, less stringent requirements are placed on these tolerances than before.
  • the device according to the invention is suitable for torque control, speed control and position control. Such application examples are not shown since this is not the subject of the invention. On the other hand, a device according to the invention with specially designed servo valves will be described in detail below.
  • the device according to the invention for regulating the differential pressure on a hydraulic motor 27, which is connected to a load 200, has two servo valves 28 and 29, which are located in a common valve block VB.
  • the hydraulic motor 27 has two connections 63 and 64 which are connected via lines 30 and 31 to a connection 30 'and 31' of the two servo valves 28 and 29, respectively.
  • Two additional ports 40 and 41 of the two servo valves 28 and 29 are connected via a common managerial tu n g 45 to a pump 44th Further, two terminals 46 and 47 of the two servo valves 28 and 2 9 via a common line 49 to a container 48.
  • each servo valve 28 and 29 via lines 217, 218 and 219, 220 are each electrical hydraulic pilot control 221 and 222 connected.
  • Each pilot control element 221 and 222 has an iron core 223 and 224, which is surrounded by a coil 225 and 226, respectively.
  • each pilot control element 221 and 222 each has an armature 227 and 228 which can be pivoted about an axis 240, 241 and which cooperate with its baffle plate with two nozzles 229 and 230 each.
  • These armatures 227 and 228 can be pivoted into a right or left end position in such a way that the baffle plate either closes the nozzle 229 and opens the nozzle 230 or that they open the nozzle 229 and close the nozzle 230.
  • both nozzles 229 and 230 are throttled to the same extent.
  • the armatures 227 and 228 When the armatures 227 and 228 are pivoted out of their central position into the right or left end position mentioned, the one nozzle 229 or 230 is throttled more and more and the other nozzle 230 or 229 is opened more and more.
  • the two coils 225 and 226 are connected to the output of an electronic controller 52 and 53, respectively.
  • the control of the two servo valves 28 and 29, ie the displacement of their control pistons 37 and 39 from their central position to the right or to the left, takes place via currents i A i B from the two electronic controllers 52 and 53 via lines 206 and 207 the columns 225 and 226 will be delivered.
  • Each input of the two controllers 52 and 53 is connected via a line 204 and 205 to the output of a subtractor 54 and 55, respectively.
  • Each is an absolute pressure sensor 32 or 33, which measures the pressure p or p B in the lines 30 or 31 connected via a line 202 or 203 to the negative input of the subtractors 54 or 55 mentioned.
  • the output of a function generator 56, 56 ' is connected to each plus input of the two subtractors 54 and 55 via lines 57 and 58, respectively.
  • the setpoint value of the differential pressure ⁇ p s in the form of an electrical voltage is input to the two function generators 56 and 56 ′ via a common line 201.
  • Each function generator 56, 56 ' forms an output signal in the form of an electrical voltage p As and p Bs from this setpoint signal ⁇ p s .
  • the two servo valves 28 and 29 with the absolute pressure sensors 32, 33 and the two electrical pilot control elements 221 and 222 are accommodated in a housing, the so-called valve block VB.
  • the valve block VB has two hydraulic connections PA and PB to the hydraulic motor 27 and one hydraulic connection to the pump 44 and to the return line 49 to the tank 48.
  • valve block VB has four electrical connections to the control block SB, namely for the electrical lines 202 and 203 from the absolute pressure sensors 32 and 33 to the subtractors 54 and 55, and for the electrical lines 206 and 207 from the electrical coils 225 and 226 to the two controllers 52 and 53. Finally, there is an electrical connection for the control block SB Line 201 is available for entering the desired differential pressure ⁇ p s .
  • a second electrical signal is subtracted from this electrical signal, which is passed from the absolute pressure sensors 32 and 33 via the lines 202 and 203 to the subtractors 54, 55.
  • the controllers 52 and 53 each receive a pos. or neg. electrical control deviation.
  • This control deviation is converted into a control current i A and i B in the controller 52, 53.
  • any pressure difference ⁇ p can be generated in the lines 30 and 31, these pressures being independent of the load and the speed of the hydraulic motor 27.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP81201259A 1980-11-14 1981-11-11 Dispositif pour régler la différence de pression d'un moteur hydraulique Withdrawn EP0052405A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH8462/80 1980-11-14
CH846280 1980-11-14

Publications (1)

Publication Number Publication Date
EP0052405A1 true EP0052405A1 (fr) 1982-05-26

Family

ID=4340744

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81201259A Withdrawn EP0052405A1 (fr) 1980-11-14 1981-11-11 Dispositif pour régler la différence de pression d'un moteur hydraulique

Country Status (5)

Country Link
EP (1) EP0052405A1 (fr)
JP (1) JPS57110802A (fr)
DE (1) DE3133800A1 (fr)
IL (1) IL64179A0 (fr)
NO (1) NO813859L (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4840111A (en) * 1986-01-31 1989-06-20 Moog Inc. Energy-conserving regenerative-flow valves for hydraulic servomotors
EP0454510A1 (fr) * 1990-04-27 1991-10-30 Alliedsignal Europe Services Techniques Circuit de commande d'un vérin hydraulique à double effet et distributeur à tiroir pour un tel circuit
DE4039439A1 (de) * 1990-12-11 1992-06-17 Teves Gmbh Alfred Druckmittelmotor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1923148A1 (de) * 1968-05-08 1969-11-27 Cincinnati Milling Machine Co Hydraulische Steuervorrichtung
DE2305825A1 (de) * 1973-02-07 1974-08-15 Brueninghaus Hydraulik Gmbh Einrichtung zur einstellung der schwenkstellung einer hydrostatischen pumpe
DE2326131A1 (de) * 1973-05-23 1974-12-12 Volkswagenwerk Ag Ventilanordnung fuer eine druckmittelbetaetigte arbeitsmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1923148A1 (de) * 1968-05-08 1969-11-27 Cincinnati Milling Machine Co Hydraulische Steuervorrichtung
DE2305825A1 (de) * 1973-02-07 1974-08-15 Brueninghaus Hydraulik Gmbh Einrichtung zur einstellung der schwenkstellung einer hydrostatischen pumpe
DE2326131A1 (de) * 1973-05-23 1974-12-12 Volkswagenwerk Ag Ventilanordnung fuer eine druckmittelbetaetigte arbeitsmaschine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4840111A (en) * 1986-01-31 1989-06-20 Moog Inc. Energy-conserving regenerative-flow valves for hydraulic servomotors
EP0232014A3 (fr) * 1986-01-31 1989-11-08 Moog Inc. Servomécanisme à conservation d'énergie
EP0454510A1 (fr) * 1990-04-27 1991-10-30 Alliedsignal Europe Services Techniques Circuit de commande d'un vérin hydraulique à double effet et distributeur à tiroir pour un tel circuit
FR2661458A1 (fr) * 1990-04-27 1991-10-31 Bendix Europ Services Tech Circuit de commande d'un verin hydraulique a double effet et distributeur a tiroir pour un tel circuit.
DE4039439A1 (de) * 1990-12-11 1992-06-17 Teves Gmbh Alfred Druckmittelmotor

Also Published As

Publication number Publication date
IL64179A0 (en) 1982-02-28
JPS57110802A (en) 1982-07-09
NO813859L (no) 1982-05-18
DE3133800A1 (de) 1982-06-03

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