EP0110024B1 - Einrichtung zum Verändern der auf ein Stellglied einwirkenden Kraft - Google Patents

Einrichtung zum Verändern der auf ein Stellglied einwirkenden Kraft Download PDF

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Publication number
EP0110024B1
EP0110024B1 EP83108660A EP83108660A EP0110024B1 EP 0110024 B1 EP0110024 B1 EP 0110024B1 EP 83108660 A EP83108660 A EP 83108660A EP 83108660 A EP83108660 A EP 83108660A EP 0110024 B1 EP0110024 B1 EP 0110024B1
Authority
EP
European Patent Office
Prior art keywords
actuator
control
pressure
piston
chamber
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
Application number
EP83108660A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0110024A1 (de
Inventor
Helmut Göttling
Walter Brausfeld
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.)
Wabco Westinghouse Steuerungstechnik and Co GmbH
Original Assignee
Wabco Westinghouse Steuerungstechnik and Co 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 Wabco Westinghouse Steuerungstechnik and Co GmbH filed Critical Wabco Westinghouse Steuerungstechnik and Co GmbH
Priority to AT83108660T priority Critical patent/ATE27639T1/de
Publication of EP0110024A1 publication Critical patent/EP0110024A1/de
Application granted granted Critical
Publication of EP0110024B1 publication Critical patent/EP0110024B1/de
Expired 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/70—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
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86919—Sequentially closing and opening alternately seating flow controllers

Definitions

  • the invention relates to a device for changing the force acting on an actuator according to the preamble of claim 1.
  • Such a device is previously known from DE-A-1 776 078.
  • several pressure-operated control pistons are provided, which act directly on the actuator via their piston rod.
  • the control pistons have different active surfaces. With the selection of the number of control pistons and / or the selection of the respective effective surface area which is acted upon by the pressure medium, different forces can thus be generated which are exerted by the control piston on the actuator.
  • the actuator is used in the known device for actuating a pilot valve for a servomotor. The pressure exerted by the pilot valve acts as a restoring force on the actuator.
  • DE-A 2531 904 discloses an electro-hydraulic adjustment device in which an actuator is actuated by a control element via an intermediate spring. With this device, however, no stop is visible that can make the actuator largely independent of control pressure fluctuations.
  • the invention has for its object to provide a device of the type mentioned, which is independent of control force fluctuations, works precisely and can be implemented with simple means.
  • the device according to the invention offers the advantage of being able to change the jumps between the individual switching stages of the forces acting on the actuator in a simple manner by exchanging the spring acting on the control element or the control piston. If several control elements are provided, these are arranged in such a way that a tilting movement of the actuator is prevented.
  • the pressure control valve shown in FIG. 11 has a pressure medium inlet 29 arranged in a housing 23 and a pressure medium outlet 22.
  • the pressure medium inlet 29 is connected to a pressure medium source and the pressure medium outlet 22 is connected to a consumer.
  • a valve insert 24 provided with two seals 27, 33 is arranged in a bore 28 running in the direction of the longitudinal axis of the housing 23.
  • the valve insert 24 has a valve seat 31 which, together with a valve closure body 30, forms a first valve 30, 31, via which the pressure medium inlet 29 can be connected to the pressure medium outlet 22.
  • the valve closure member 30 is loaded by a spring 25, which is guided in a bore 26, in the direction of the valve seat 31.
  • the pressure medium outlet 22 is connected to a control chamber 20 via a bore 21.
  • the control chamber 20 is delimited by a piston 18 provided with a sealing ring 19.
  • a disk-shaped traverse serving as an actuator 16 is fastened, which, when the piston 18 is lifted in the direction of the control chamber 20, can be brought into contact with a step 17 serving as stop 17 of the housing bore receiving the actuator 16 is.
  • the side of the housing recess opposite the stop 17 is closed off by a disk-shaped seal 14.
  • a stepped bore is arranged centrally in the piston 18 and is designed as a valve seat 36 in the area of the stepping.
  • a valve closure member 34 forms, together with the valve seat 36, a second valve 34, 36 serving as an outlet valve, via which the space above the piston 18 can be connected to the control chamber 20.
  • the second valve 34, 36 also serves as an outlet valve for the control chamber 20.
  • the valve closing body 34 of the second valve 34, 36 is fixedly connected to the valve closing body 30 of the first valve 30, 31 by means of a rod 32.
  • a housing 9, provided with a cover 5, of a device for actuating the actuator 16 is fastened by means of screws 6, 47.
  • a seal 51 is arranged between the cover 5 and the housing 9.
  • the pressure medium chambers are arranged in the housing 9, of which only three pressure medium chambers 8, 46 and 45 are shown here.
  • the pressure medium chambers are related to the central axis of the actuator 16 arranged symmetrically.
  • the pressure medium chamber 8 is delimited by a first control piston 11 provided with a sealing ring 10, which can be displaced in the direction of the actuator 16 against the force of a spring 13.
  • the control piston 11 On its side facing away from the pressure medium chamber 8, the control piston 11 has an extension serving as a stop 12.
  • the spring 13 is guided through a recess provided in the disk-shaped seal 14 and is supported on the actuator 16 with its end facing away from the control piston 11.
  • a second control piston 40 provided with a sealing ring 43 delimits the pressure medium chamber 46.
  • a spring 38 is arranged between the side of the second control piston 40 facing away from the pressure medium chamber 46 and the actuator 16.
  • the second control piston 40 has, on its side facing the spring 38, an extension serving as a stop 39, which comes into contact with the disk-shaped seal 14 when the control piston 40 is moved in the direction of the actuator 16.
  • the pressure medium chamber 45 is delimited by a third control piston 42 which is provided with a sealing ring 44 and which can be displaced in the direction of the actuator 16 against the force of a spring 50.
  • the third control piston 42 also has an extension designed as a stop 41, which cooperates with the disk-shaped sealing element 14.
  • the springs arranged between the control piston and the actuator are of identical design. In order to be able to change the stroke of the control pistons, it is conceivable to design the stops formed from the extensions of the control pistons and the seal so that they can be changed.
  • solenoid valves 1, 2, 3, 4 are arranged on the cover 5 of the housing 9.
  • the solenoid valves are used to control the fifteen pressure medium chambers.
  • the solenoid valves are connected to a pressure medium source via pressure medium lines, not shown here.
  • the solenoid valves are controlled electrically by a 16-position switch.
  • the pressure medium chamber 45 is connected to the solenoid valve 2 via a bore 48 and a corresponding recess in the seal 51.
  • the solenoid valve 3 is connected to the pressure medium chamber 8 via a channel 7 and a corresponding recess in the seal 51.
  • FIG. 2 the pressure medium chamber arrangement of the device shown and described in Fig. For changing a manipulated variable is shown in section.
  • the parts that are the same as the parts shown in FIG. 1 are provided with the same reference numerals.
  • Fifteen cylindrical pressure medium chambers 52, 53, 54, 55, 56, 57, 58, 59, 8, 60, 45, 61, 62, 63, 46 are provided in the housing 9, in which control pistons, not shown here, can be displaced against the force of springs are arranged.
  • the pressure medium chambers are arranged symmetrically to the central axis of the actuator 16 shown in FIG. 1.
  • the first pressure medium chamber 46 is arranged centrally and is connected to a first solenoid valve via a channel (not shown here).
  • Two further pressure medium chambers 62, 63 are arranged in mirror image to one another and lie on an imaginary axis running through the center.
  • the two pressure medium chambers 62, 63 are connected to one another via a channel 67, which is connected via a channel 68 to a second solenoid valve.
  • Four pressure medium chambers 8, 60, 45, 61 which are connected via a channel 64 and to one another, are arranged in relation to the pressure medium chambers 62, 63 in such a way that, together with these, they form an inner ring around the centrally arranged pressure medium chamber 46.
  • the four pressure medium chambers 8, 60, 45, 61 are connected via the channel 64 to the solenoid valve 3 shown in FIG. 1.
  • the remaining pressure medium chambers 52, 53, 54, 55, 56, 57, 58, and 59 form an outer ring around the centrally arranged pressure medium chamber 46.
  • These pressure medium chambers are connected to one another via a channel 66.
  • Another channel 65 connected to the chamber 57 leads to a solenoid valve, not shown here.
  • the branches leading from the individual channels to the associated pressure medium chambers are identified by dots.
  • the pressure control valve should control a pressure of 2 bar.
  • the 16-position switch is set to level 1 and a voltage is thus applied to the solenoid valve connected to the centrally arranged pressure medium chamber 46.
  • the solenoid valve opens and pressure medium flows into the pressure medium chamber 46 from the pressure medium source.
  • the control piston 40 is displaced towards the actuator 16 by the pressure building up in the pressure medium chamber 46 until its stop 39 comes into contact with the seal 14.
  • the space below the control piston 40 is vented via the second valve serving as the outlet valve 34, 36.
  • the spring 38 arranged between the actuator 16 and the control piston 40 causes the piston 18 connected to the actuator 16 to move toward the control chamber 20 when the control piston 40 moves downward.
  • the stroke of the piston 18 is ended when the actuator 16 comes to rest against the stop 17.
  • the outlet valve 34, 36 comes into the closed position and the first valve 30, 31 serving as the inlet valve is moved into the open position by means of the rod 32 brings.
  • the pressure medium inlet 29 of the pressure control valve is now connected to the pressure medium outlet 22 via the inlet valve 30, 31.
  • Pressure medium flows from the pressure medium source to the consumer.
  • the pressure building up in the control chamber 20 via the bore 21 in connection with the pressure medium outlet 22 moves the piston 18 against the force of the spring 38 in the direction of the control piston 40.
  • the inlet valve 30, 31 reaches the closed position.
  • the pressure medium supply to the consumer is interrupted.
  • the 16-position switch is switched to position 4.
  • the solenoid valve 3 connected to the four pressure medium chambers 8, 60, 45, 61 is brought into the open position and the solenoid valve connected to the centrally arranged pressure medium chamber 46 is brought into the closed position.
  • the control pistons 11, 42 arranged in the four pressure medium chambers 8, 60, 46, 61 are displaced in the direction of the actuator 16 until they come to rest against the seal 14 with their stops 12, 41.
  • the centrally arranged pressure medium chamber 46 is simultaneously vented via the associated solenoid valve, the control piston 40 is moved upwards by the spring 38.
  • the actuator 16 and the piston 18 connected to it are displaced downward due to the disturbance of the balance of forces.
  • the inlet valve 30, 31 returns to the open position and the consumer is connected to the pressure medium source again via the pressure medium outlet 22, the inlet valve 30, 31 and the pressure medium inlet 29. If the pressure in the consumer and thus also the pressure in the control chamber 20 has risen to such an extent that there is a balance between the forces acting in opposite directions on the actuator 16, the inlet valve 30, 31 comes into the closed position as a result of the preceding continuous upward movement of the piston 18.
  • the 16-position switch is set to position 0.
  • the four pressure medium chambers 8, 60, 45, 61 are vented, the control pistons 11, 42 move upwards.
  • the associated springs 13, 50 relax. Now that the force exerted on the actuator 16 by the pressure in the control chamber 20 via the piston 18 predominates, the piston 18 continues to move upward.
  • the second valve 35, 36 serving as the outlet valve comes into the open position and the consumer is vented via the pressure medium outlet 22, the bore 21 and the control chamber 20 and the outlet valve 34, 36.
  • the pressure to be controlled by the pressure control valve can be increased or decreased in stages.
  • the solenoid valves connected to the pressure medium chambers can be designed as pulse valves.
  • Fig. Shows a working cylinder whose piston position is specified by means of a device for changing a manipulated variable.
  • a working piston 89 connected to a piston rod 91 is arranged displaceably in a cylinder 74.
  • the piston rod 91 is led out of the cylinder 74 through an opening 92 provided in the end wall of the cylinder 74 and provided with a sealing ring 93.
  • the working piston 89 divides the cylinder 74 into a working chamber 90 on the piston rod side and a spring chamber 94 lying opposite the working chamber 90 on the piston rod side on the other side of the working piston 89.
  • a compression spring 88 is arranged in the spring chamber 94 and has one end on the working piston 89 and is supported at its other end on a disk-shaped actuator 84.
  • the actuator 84 has on its side facing away from the spring chamber 94 rods 87, 108 which are guided in corresponding bores provided in the cylinder cover 105.
  • the rods 87, 108 extend through the cylinder cover 105 into a cup-shaped cap 107.
  • a plate 109 is fastened, which has a centrally arranged recess 69 with a valve seat 70.
  • a further valve seat 111 is arranged in the cylinder cover 105 coaxially with the valve seat 70.
  • a double valve body 112, 114, 71 forms an inlet valve 111, 112 with the valve seat 111 and an outlet valve 70, 71 with the valve seat 70.
  • the double valve body 112, 114, 71 is held on the inlet valve seat 111 by a spring 113.
  • a pressure medium line 77 leads from the outlet of the inlet valve 111, 112 to the working chamber 90 of the cylinder 74.
  • the inlet of the inlet valve 111, 112 is connected via a channel 102 to a pressure medium source, which is not shown here.
  • a bellows 72 is arranged between the plate 109 and the cylinder cover 105.
  • a plurality of pressure medium chambers are provided in the cylinder cover 105, only four pressure medium chambers 79, 80, 99, 101 being shown in the illustration for the sake of a better overview. Each pressure medium chamber is delimited by a control piston 78 or 81 or 98 or 100.
  • a spring 82 or 83 or 95 or 97 is assigned to each control piston 78, 81, 98, 100.
  • the springs are supported on the one hand on the actuator 84 and on the other hand on the associated control piston.
  • the stroke of each control piston is limited in the direction of the actuator 84 by a stop 86, 85, 110, 96.
  • Via bores 75, 76, 103, 104, which are provided in the cylinder cover 105, the pressure medium chambers 79, 80, 99, 101 are connected to solenoid valves.
  • solenoid valves 106 and 73 are shown in the figure.
  • the solenoid valves are connected to a pressure medium source.
  • the solenoid valves can be individually connected to a voltage source via a multi-position switch.
  • the solenoid valve 73 opens and thus connects the pressure medium chambers 79, 99 to the pressure medium source.
  • the pressure building up in the pressure medium chambers 79, 99 displaces the control pistons 78, 98 in the direction of the actuator 84.
  • the force exerted on the control pistons 78, 98 is transmitted to the actuator 84 and thus the actuator 84 is displaced in the direction of the working piston 89.
  • the outlet valve seat 70 arranged on the plate 109 connected to the actuator 84 rests on the double valve body 71, 114, 112 and takes it along.
  • the outlet valve 70, 71 is now closed and the inlet valve 111, 112 reaches the open position.
  • pressure medium reaches the working chamber 90 from the pressure medium source.
  • the pressure building up in the working chamber 90 displaces the working piston 89 against the force of the spring 88 in the direction of the actuator 84.
  • the pressure medium chambers 79, 99 are vented via the solenoid valve 73.
  • the control pistons 78, 98 move upwards and the springs 82, 95 relax. Now that the force exerted on the actuator 84 by the spring 88 predominates, the actuator 84 is displaced further upward.
  • the exhaust valve seat 70 lifts off from the double valve body 71, 114, 112.
  • the working chamber 90 is vented through the pressure medium line 77, the opened outlet valve 70, 71 and the outlet 69.
  • the spring 88 brings the working piston 89 into its original position.
  • armatures of electromagnets designed as control members can act directly on the springs acting on the actuator.
  • control pistons pneumatically, hydraulically or manually switchable valves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Vehicle Body Suspensions (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Valve Device For Special Equipments (AREA)
  • Body Structure For Vehicles (AREA)
EP83108660A 1982-12-04 1983-09-02 Einrichtung zum Verändern der auf ein Stellglied einwirkenden Kraft Expired EP0110024B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83108660T ATE27639T1 (de) 1982-12-04 1983-09-02 Einrichtung zum veraendern der auf ein stellglied einwirkenden kraft.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823244920 DE3244920A1 (de) 1982-12-04 1982-12-04 Einrichtung zum veraendern der auf ein stellglied einwirkenden kraft
DE3244920 1982-12-04

Publications (2)

Publication Number Publication Date
EP0110024A1 EP0110024A1 (de) 1984-06-13
EP0110024B1 true EP0110024B1 (de) 1987-06-03

Family

ID=6179811

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83108660A Expired EP0110024B1 (de) 1982-12-04 1983-09-02 Einrichtung zum Verändern der auf ein Stellglied einwirkenden Kraft

Country Status (6)

Country Link
US (1) US4531548A (enrdf_load_stackoverflow)
EP (1) EP0110024B1 (enrdf_load_stackoverflow)
JP (1) JPS59110905A (enrdf_load_stackoverflow)
AT (1) ATE27639T1 (enrdf_load_stackoverflow)
DE (2) DE3244920A1 (enrdf_load_stackoverflow)
ES (1) ES526471A0 (enrdf_load_stackoverflow)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4699355A (en) * 1984-11-01 1987-10-13 Koomey, Inc. Fail-safe fluid piloted valve positioner with hydromechanical position lock
US4630632A (en) * 1984-11-26 1986-12-23 Schrader Bellows Inc. Pressure regulator
DE3607690A1 (de) * 1986-03-08 1987-09-10 Bosch Gmbh Robert Relaisventileinrichtung fuer pneumatische drucksteuerung
DE3803009C2 (de) * 1987-02-04 2002-08-01 Josef Nusser Hydraulischer Antrieb
JPH02154873A (ja) * 1988-12-05 1990-06-14 Takashi Kimura 空圧シリンダ用切換弁
US5261314A (en) * 1988-12-05 1993-11-16 Hirotaka Manufacturing Co., Ltd. Directional control valve for pneumatic cylinder
CA2074514A1 (en) * 1990-02-02 1991-08-03 Andrew B. Dunwoody Digital suspension system
US5487273A (en) * 1993-09-13 1996-01-30 Alliedsignal Inc. Turbocharger having pneumatic actuator with pilot valve
US6202698B1 (en) * 1997-06-18 2001-03-20 Valco Instruments Company, Inc. Multiple port diaphragm valve
US6244739B1 (en) 1999-07-09 2001-06-12 Apv North America, Inc. Valve members for a homogenization valve
US6238080B1 (en) 1999-07-09 2001-05-29 Apv North America, Inc. Homogenization valve with outside high pressure volume
US6305836B1 (en) 1999-07-09 2001-10-23 Apv North America, Inc. Force absorbing homogenization valve
CN118408043B (zh) * 2024-07-01 2024-09-03 余姚市三力信电磁阀有限公司 一种大口径先导式常开电磁阀

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2531904A1 (de) * 1975-07-17 1977-01-20 Elmeg Elektrohydraulische verstelleinrichtung

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Publication number Priority date Publication date Assignee Title
FR602663A (fr) * 1924-12-05 1926-03-24 Perfectionnements apportés aux pompes
US1782595A (en) * 1929-05-14 1930-11-25 Alfred J Amsler Hydraulic press particularly for testing materials
GB408664A (en) * 1932-10-12 1934-04-12 Robert Arthur Chalmers Improvements in or relating to variable pressure intermittent supply pumps
FR1260233A (fr) * 1960-04-08 1961-05-05 Westinghouse Air Brake Co Cylindre moteur à organe actif susceptible d'occuper des positions multiples et dispositif de commande pour ledit cylindre
DE1300442B (de) * 1965-03-12 1969-07-31 Westinghouse Bremsen U Appbau Druckluftgesteuerter Stellmotor
AT266291B (de) * 1965-10-20 1968-11-11 Strojosvit Narodni Pondik Walzmaschine, insbesondere Brückenwalzmaschine oder Durchgangswalzmaschine für die Lederzurichtung
FR1550337A (enrdf_load_stackoverflow) * 1967-11-07 1968-12-20
DE1989293U (de) * 1968-05-02 1968-07-11 Westinghouse Bremsen Apparate Druckmittelstellmotor.
US3593620A (en) * 1969-08-20 1971-07-20 Pneumo Dynamics Corp Redundant control system for actuation of flight control surfaces
US3608434A (en) * 1970-01-13 1971-09-28 Us Army Dual area hydraulic actuator
SE369157B (enrdf_load_stackoverflow) * 1972-12-22 1974-08-12 Asea Atom Ab
GB1431562A (en) * 1973-02-05 1976-04-07 Martonair Ltd Adjustable fluid pressure regulator
JPS5128220A (ja) * 1974-09-04 1976-03-10 Konan Electric Co Atsuryokuseigyoben

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2531904A1 (de) * 1975-07-17 1977-01-20 Elmeg Elektrohydraulische verstelleinrichtung

Also Published As

Publication number Publication date
US4531548A (en) 1985-07-30
JPH0429912B2 (enrdf_load_stackoverflow) 1992-05-20
EP0110024A1 (de) 1984-06-13
ATE27639T1 (de) 1987-06-15
ES8501852A1 (es) 1984-12-01
ES526471A0 (es) 1984-12-01
DE3371931D1 (en) 1987-07-09
DE3244920A1 (de) 1984-06-07
JPS59110905A (ja) 1984-06-27

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