EP0051728A1 - Dispositif de commande pour un vérin hydraulique - Google Patents

Dispositif de commande pour un vérin hydraulique Download PDF

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Publication number
EP0051728A1
EP0051728A1 EP81107401A EP81107401A EP0051728A1 EP 0051728 A1 EP0051728 A1 EP 0051728A1 EP 81107401 A EP81107401 A EP 81107401A EP 81107401 A EP81107401 A EP 81107401A EP 0051728 A1 EP0051728 A1 EP 0051728A1
Authority
EP
European Patent Office
Prior art keywords
valve
control valve
bore
piston
shut
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
Application number
EP81107401A
Other languages
German (de)
English (en)
Other versions
EP0051728B1 (fr
Inventor
Heinz Ing.Grad. Siegel
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0051728A1 publication Critical patent/EP0051728A1/fr
Application granted granted Critical
Publication of EP0051728B1 publication Critical patent/EP0051728B1/fr
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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve

Definitions

  • the invention relates to a control device according to the preamble of the main claim.
  • a control device according to the preamble of the main claim.
  • the load acting on a consumer does not lead ahead of the pressure medium flow which is directed to it.
  • This device also enables fine control of the pressure medium flow supplied to the consumer.
  • it has the disadvantage that under unfavorable operating conditions it is excited to so-called snaring, i.e. the control valve is made to vibrate, causing excessive noise and erosion.
  • the device according to the invention with the characterizing features of the main claim has the advantage over the fact that under practically all occurring operating states a perfect fine control of the pressure medium flow to the consumer is possible, undesirable noises being prevented. This will be there achieved by that the opening movement of the control valve is properly damped.
  • Advantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims.
  • the control valve works as a pilot valve.
  • FIG. 1 shows a hydraulic control device with a shut-off valve in longitudinal section
  • FIGS. 2 and 3 modifications of the exemplary embodiment according to FIG. 1.
  • a pump 10 draws in pressure medium from a container 11, which is fed via a 4/3-way valve to a consumer 13 - here a double-acting working cylinder - directly or via a hydraulically unlockable shut-off valve 14.
  • the working cylinder 13 has two pressure chambers 15, 16, in which a piston 17 with a piston rod 18 is guided.
  • a line 19 leads directly to the pressure chamber 15 and a line 20 to a bore 21 of the housing 22 of the check valve i4.
  • a line 24 branches off from line 19 and leads to a second bore 25 in housing 22.
  • a longitudinal bore 26 is formed, in one section of which an unlocking piston 27 is guided in a tightly sliding manner.
  • the bore 21 opens into the longitudinal bore 26.
  • this receives a valve member 30 which rests with a conical collar 31 on a likewise conical valve seat 32 which is part of the bore section 26'.
  • the valve member 30 has a stepped bore 33 which essentially consists of three bore sections 34 to 36 of decreasing diameter.
  • An annular groove 38 is formed on the valve member 30, from which a plurality of radial bores 39 lead into the bore section 35.
  • the radial bores 39 are connected to a transverse bore 40 in the housing 22, from which a line 41 leads to the pressure chamber 16 of the working cylinder 13.
  • the opening of the transverse bore 40 in the bore section 26 'lies directly next to the valve seat 32.
  • the bore section 26' forms a damping space 42 and is closed by a screw plug 43.
  • One end of a compression spring 44 bears against its inner end, the other end of which plunges into a central blind bore 45 of a control valve 46.
  • the control valve 46 is guided with its rear valve part 47 tightly sliding in the bore section 34 of the valve member 30.
  • a cylindrical valve part 48 with a much smaller diameter adjoins the cylindrical valve part 47 and protrudes into the bore section 35.
  • the valve part 48 has a conical collar 49, with which it is by the force of Fe 44 is pressed onto a valve seat 50 which is formed by the shoulder of the two bore sections 35 and 36.
  • An annular groove 52 adjoins the conical collar 49, followed by a fine control pin 53 as the third valve part.
  • the fine control pin 53 is guided with a narrow cylindrical section 53 'in the bore section 36.
  • the fine control pin 53 is followed by a fourth and last valve part, followed by a push-up piston 54, which comes close to the locking piston 27 when it reaches its one end position.
  • a short blind bore 56 with a substantially smaller diameter follows from the blind bore 45 receiving the spring 44, from which a plurality of transverse bores 57 lead to the outside.
  • a throttle notch 58 which leads to the shoulder formed by the valve parts 47, 48. This is always at a certain distance from the shoulder formed from the bore sections 34, 35. In this area, the bore section 34 is expanded to a bore section 34 '.
  • the directional control valve can assume three switch positions I, II and III. If it is brought from its neutral position II into the switching position I, pressure medium flows via the line 20 to the bore 21, and the valve member 30 is lifted together with the control valve 46 against the force of the spring 44 from its valve seat 32, so that pressure medium through the bore 40 and line 41 can penetrate into the pressure chamber 16 of the working cylinder 13.
  • the control valve remains in its position, ie the conical collar 49 remains on the valve seat 50.
  • the valve member 30 thus has only the function of a check valve. By pressurizing the pressure chamber 16, the piston 17 is extended against a load, pressure medium being discharged from the pressure chamber 15 via the line 19 to the container 11.
  • the directional control valve 12 is brought into its switching position III. It is important that this process must be carried out silently, smoothly and in such a way that the load does not lead ahead of the pressure medium flow now entering the lines 19. This is achieved by the check valve 14.
  • pressure medium passes through the line 24 into the longitudinal bore 26, whereupon the unlocking piston 27 moves toward the valve part.
  • the control valve 46 or its conical collar 49 is lifted off the valve seat 50 via the push piston 54.
  • the damping space 42 is connected to the bore section 35 and the radial bores 39 via the blind bore 56 and the transverse bore 57.
  • the same parts as in the previous exemplary embodiment are designated with the same numbers. It differs essentially in that when the load is lowered, i.e. when the directional control valve is in its switching position III, both valve cones stand out from their seats, the internal valve forming a pilot valve for the main control valve.
  • a damping piston 61 acts on the pilot valve 60 via the compression spring 44, ie it lies on the valve stem 50 under the force of this spring.
  • the hollow damping piston 61 there is a longitudinal bore 62 which has a longitudinal blind bore formed in the pilot valve 60 63 is in operative connection.
  • One or more transverse bores 64 lead outward from the bore 63.
  • the pilot valve is penetrated by a longitudinal bore 65. This is connected to a damping chamber 67 outside the pilot valve 60.
  • the throttle notch 58 is again in the same place.
  • the main control valve 70 receiving the pilot valve 60 has a throttle bore 71 which penetrates its wall, and also a fine control pin 72 which adjoins the conical collar 73. If the directional control valve is in its switching position III, in which the load is lowered and pressure medium enters the line 19, both the pilot control valve 60 and the main control valve 70 rise from their seats.
  • the valve part 48 reduces the pressure in the damping chamber 67 via the longitudinal bore 65 to such an extent that the main control valve 70 opens by the action of the load pressure prevailing in line 41.
  • the pilot valve opens, the pressure medium contained in the damping chamber 42 flows out through the bores 62, 63 and 64 and the throttle notch 58. This is the same process as before.
  • the control valve - designated 75 is in turn arranged in a valve member 76, which is similar to that according to the embodiment of Figure 1, i.e. it only has a conical collar 7T with which it rests on a valve seat 78.
  • a sleeve 80 acts on the valve member 76, which in turn presses a spring 81 which is arranged in the rear part of the valve.
  • the control valve 75 is guided with its shaft-like end 82 in the bore 83 of the sleeve 80 and there delimits a pressure chamber 85 in which a pressure spring 86 acting on the control valve 75 is arranged.
  • control valve The entire length of the control valve is penetrated by a bore 87, which therefore leads from the pressure chamber 85 to the bore 21.
  • the control valve At its end facing the unlocking piston 27, the control valve has an outwardly directed collar 88, on the end face of which a transverse throttle notch 89 is formed.
  • the control valve 75 in turn has a fine control pin 90 and a conical collar 91, with which it rests on a valve seat 92 formed in the valve member 76 - see also FIG. 4. Between the fine control pin 90 and the conical collar 91 of the valve member 76 there is again an annular groove 93. From the Querboh tion 40 of the housing 14 leads an inclined bore 95 to the bore 96 in the valve member 76, where the sleeve 80 is received. A transverse bore 80 ′ is formed in the sleeve 80, which leads to an annular groove 97 on the control valve 75, as a result of which a connection is made between the bore 96 receiving the valve member 76 or a pressure chamber 98 formed there and the bore 40.
  • the mode of operation is again largely similar to that in the exemplary embodiment according to FIG. 1.
  • the end of the unlocking piston 27 presses against the collar 88 of the control valve 75, as a result of which the throttle point 89 is formed.
  • the control valve 75 is raised, pressure medium can only flow out of the pressure chamber 85 throttled via the notch 89. Only when the fine control pin 90 has passed through the valve seat 92 can pressure medium flow out of the consumer via the control valve 75 in a more or less throttled manner.
  • the valve member 76 remains in turn on its valve seat 78 during this process. From this it can be seen that the control valve 75 has no pilot control function for the valve member 76, as is the case with the exemplary embodiment according to FIG. 1.
  • This embodiment thus represents a differential area valve, whereby the impact force by the unlocking piston 27 can be kept small, similar to a pilot valve, i.e. the difference in area between the bore 83 and the valve seat 92 can be kept small.
  • the diameter of the bore 83 is smaller than the diameter of the valve seat. Due to the connection to the annular groove 97, the load pressure acts on the differential surface and keeps the control valve 75 together with the compression spring 86 closed until the unlocking piston opens.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
EP81107401A 1980-11-08 1981-09-18 Dispositif de commande pour un vérin hydraulique Expired EP0051728B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803042277 DE3042277A1 (de) 1980-11-08 1980-11-08 Steuervorrichtung fuer einen hydraulischen arbeitszylinder
DE3042277 1980-11-08

Publications (2)

Publication Number Publication Date
EP0051728A1 true EP0051728A1 (fr) 1982-05-19
EP0051728B1 EP0051728B1 (fr) 1985-06-19

Family

ID=6116353

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107401A Expired EP0051728B1 (fr) 1980-11-08 1981-09-18 Dispositif de commande pour un vérin hydraulique

Country Status (3)

Country Link
EP (1) EP0051728B1 (fr)
JP (1) JPS57107402A (fr)
DE (2) DE3042277A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4466336A (en) * 1982-02-08 1984-08-21 Lakeland Hydraulics, Inc. Control valve for hydraulic motor apparatus
GB2149901A (en) * 1983-11-09 1985-06-19 Aisin Seiki Low temperature containers
EP0505349A2 (fr) * 1991-03-20 1992-09-23 HOERBIGER FLUIDTECHNIK GmbH Vérin hydraulique
EP0921321A1 (fr) * 1997-12-06 1999-06-09 Robert Bosch Gmbh Soupape d'arrêt du type soupape à siège
CN103899596A (zh) * 2014-03-31 2014-07-02 雷永志 一种带先导单向阀的液压锁
CN105221755A (zh) * 2014-07-02 2016-01-06 浙江师范大学 一种带阻尼活塞的锥阀式直动大流量水阀
CN113775590A (zh) * 2021-10-18 2021-12-10 山东泰丰智能控制股份有限公司 一种具备缓冲功能的定压差阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4032078C2 (de) * 1990-10-10 1997-08-07 Bosch Gmbh Robert Steuervorrichtung für einen hydraulischen Arbeitszylinder
DE4140604A1 (de) * 1991-12-10 1993-06-17 Bosch Gmbh Robert Steuervorrichtung fuer den volumenstrom eines hydraulischen arbeitsmittels

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015316A (en) * 1959-01-08 1962-01-02 William Waterman Counterbalance valves and the like
GB1044613A (en) * 1962-09-21 1966-10-05 Ohio Brass Co Fluid control valve
DE2214245A1 (de) * 1972-03-23 1973-10-04 Teves Gmbh Alfred Zwillingsrueckschlagventil
US3981479A (en) * 1974-06-14 1976-09-21 Snap-Tite, Inc. Check valve
DE2626611A1 (de) * 1976-06-14 1977-12-22 Siemens Ag Geraet mit einem mittels eines geraeteventils steuerbaren hydraulikmotor
EP0007712A1 (fr) * 1978-07-27 1980-02-06 Modular Controls Corporation Soupape de descente freinée et de maintien

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS427071Y1 (fr) * 1965-10-14 1967-04-03
JPS4933973A (fr) * 1972-07-29 1974-03-28
JPS53126522A (en) * 1977-04-12 1978-11-04 Daikin Ind Ltd Pilot check valve
JPS5932033B2 (ja) * 1978-06-16 1984-08-06 株式会社東芝 工業用テレビカメラ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015316A (en) * 1959-01-08 1962-01-02 William Waterman Counterbalance valves and the like
GB1044613A (en) * 1962-09-21 1966-10-05 Ohio Brass Co Fluid control valve
DE2214245A1 (de) * 1972-03-23 1973-10-04 Teves Gmbh Alfred Zwillingsrueckschlagventil
US3981479A (en) * 1974-06-14 1976-09-21 Snap-Tite, Inc. Check valve
DE2626611A1 (de) * 1976-06-14 1977-12-22 Siemens Ag Geraet mit einem mittels eines geraeteventils steuerbaren hydraulikmotor
FR2355187A1 (fr) * 1976-06-14 1978-01-13 Siemens Ag Appareil comportant un moteur hydraulique pouvant etre commande au moyen d'une soupape
EP0007712A1 (fr) * 1978-07-27 1980-02-06 Modular Controls Corporation Soupape de descente freinée et de maintien

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4466336A (en) * 1982-02-08 1984-08-21 Lakeland Hydraulics, Inc. Control valve for hydraulic motor apparatus
GB2149901A (en) * 1983-11-09 1985-06-19 Aisin Seiki Low temperature containers
EP0505349A2 (fr) * 1991-03-20 1992-09-23 HOERBIGER FLUIDTECHNIK GmbH Vérin hydraulique
EP0505349A3 (en) * 1991-03-20 1993-03-03 Hoerbiger Fluidtechnik Gmbh Hydraulic actuator
US5235896A (en) * 1991-03-20 1993-08-17 Hoerbiger Fluidtechnik Gmbh Hydraulic cylinder/piston mechanism
AT402334B (de) * 1991-03-20 1997-04-25 Hoerbiger Gmbh Hydraulische zylinder/kolben-anordnung
EP0921321A1 (fr) * 1997-12-06 1999-06-09 Robert Bosch Gmbh Soupape d'arrêt du type soupape à siège
CN103899596A (zh) * 2014-03-31 2014-07-02 雷永志 一种带先导单向阀的液压锁
CN103899596B (zh) * 2014-03-31 2016-11-02 雷永志 一种带先导单向阀的液压锁
CN105221755A (zh) * 2014-07-02 2016-01-06 浙江师范大学 一种带阻尼活塞的锥阀式直动大流量水阀
CN105221755B (zh) * 2014-07-02 2019-04-05 浙江师范大学 一种带阻尼活塞的锥阀式直动大流量水阀
CN113775590A (zh) * 2021-10-18 2021-12-10 山东泰丰智能控制股份有限公司 一种具备缓冲功能的定压差阀

Also Published As

Publication number Publication date
JPS57107402A (en) 1982-07-03
DE3042277A1 (de) 1982-06-03
EP0051728B1 (fr) 1985-06-19
DE3171037D1 (en) 1985-07-25

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