EP0342410A2 - Soupape de sûreté - Google Patents

Soupape de sûreté Download PDF

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Publication number
EP0342410A2
EP0342410A2 EP89107713A EP89107713A EP0342410A2 EP 0342410 A2 EP0342410 A2 EP 0342410A2 EP 89107713 A EP89107713 A EP 89107713A EP 89107713 A EP89107713 A EP 89107713A EP 0342410 A2 EP0342410 A2 EP 0342410A2
Authority
EP
European Patent Office
Prior art keywords
connection
valve
channel
control
working
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Withdrawn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
EP89107713A
Other languages
German (de)
English (en)
Other versions
EP0342410A3 (fr
Inventor
Helmut Motzer
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.)
Herion Werke KG
Original Assignee
Herion Werke KG
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 Herion Werke KG filed Critical Herion Werke KG
Publication of EP0342410A2 publication Critical patent/EP0342410A2/fr
Publication of EP0342410A3 publication Critical patent/EP0342410A3/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Withdrawn legal-status Critical Current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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/001—Double valve requiring the use of both hands simultaneously
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor
    • Y10T137/87225—Fluid motor

Definitions

  • the invention relates to a hydraulically actuated safety valve, consisting of a valve housing with two valve bodies which can be moved in opposite directions to one another in a bore in the housing, two e.g. Electromagnetically actuated pilot valves, a pump connection, a working connection and a tank connection, the valve bodies each having a working piston, which can be acted upon by the pressure medium via the pilot valves and control channels, as well as control pistons connected to the working piston, which control the connections between the working connection, pump connection and tank connection , in the event of a malfunction the work connection can be connected to the tank connection.
  • a safety valve of the aforementioned type is known from German Patent 31 04 957. It is e.g. used to control the brake and clutch of a mechanical press.
  • This known safety valve consists of two directional control valves, so that the braking process is still guaranteed in the event of a valve failure.
  • the directional control valves are monitored automatically without additional, e.g. electrical monitoring elements are required.
  • the invention is then based on the object of developing a safety valve of the type mentioned at the outset such that the speed and pressure increase can be controlled at the consumer connected to the work connection.
  • one of the two pilot valves is designed as a proportional pressure difference valve and the control piston assigned to it is provided with fine control notches.
  • Fig. 1 shows the proportional pressure differential valve 14, hereinafter called the proportional valve.
  • the proportional valve 14 has a central bore in which a piston 98, which is connected to the proportional magnet 118 of the valve, can be moved axially back and forth.
  • the piston 98 is centered in the housing of the proportional valve 14 by compression springs 112, the one compression spring 112 being arranged in a spring chamber 108 and the other in a spring chamber 110.
  • the piston 98 is guided in the housing by means of collars 99, which abut against disks, which are not designated in any more detail, which are arranged in the spring chambers and acted upon by the compression springs 112.
  • Ring channels 90, 92 and 94 are also formed in the housing, ring channel 90 being connected to a control channel 54, ring channel 92 being connected to a control channel 58 and ring channel 94 being connected to a control channel 62. Furthermore, the spring chamber 108 is connected to the ring channel 90 via a connecting channel 114 and the spring chamber 110 is connected to the ring channel 92 via a connecting channel 116.
  • the proportional valve 14 according to FIG. 1 forms one of the pilot valves of the safety valve 10 shown in the basic position in FIG. 2, to which a further pilot valve 12 is flanged in addition to the aforementioned.
  • the pilot valve 12 has a conventional piston 96, which is connected to the electromagnet of the pilot valve 12 and which is centered in the housing of the pilot valve 12 by compression springs 104, which are arranged in spring chambers 100, 102.
  • the two spring chambers 100, 102 are connected to one another by a connecting channel 106.
  • ring channels 84, 86 and 88 are also formed in the housing of the pilot valve 12, the ring channel 84 being connected to a control channel 56, the ring channel 86 being connected to a control channel 52 and the ring channel 88 being connected to a control channel 60 of the safety valve 10 are.
  • the safety valve 10 has a central bore 16 (FIG. 4) in which two valve bodies 18, 20 can be moved axially in opposite directions to one another.
  • Each of the two valve bodies 28 has a working piston 22, each of which is provided with a blind bore, in which a compression spring 24 is arranged, the two compression springs 24 trying to press the two valve bodies 18 and 20 axially toward one another.
  • Each working piston 22 is also equipped with a transverse bore 36, which connects the blind bore with an annular space outside the respective working piston 22.
  • the valve body 18 is provided with a control piston 26 and the valve body 20 is provided with two control pistons 28, 30 which are axially spaced apart.
  • the control piston 30 is equipped on one end face with fine control notches 32 and on its other end face with fine control notches 34, each of which extends somewhat from the end face in the axial direction into its outer peripheral surface.
  • a channel 38 is formed in the housing of the safety valve 10, which extends from the central bore to the pump connection P, a channel 40 which extends from the central bore to the consumer connection or working connection A, and a channel 42 which extends from the central bore to the tank connection R.
  • a branch duct 44 branches off from the duct 42 and also leads to the central bore; further branch from the channel 38 branch channels 46, one of which opens into the central bore in the area of one of the two working pistons 22.
  • the central bore 16 is provided with ring channels 68, 70, 72, 74, 76, 78.
  • the ring channels 72 and 74 are connected by a connecting channel 48 and the ring channels 70 and 76 are connected by a connecting channel 50.
  • the bore 16 is also provided with one-sided pockets 64, 66, 68 and 80.
  • the channel 40 leading to the working port A opens into the ring channel 70
  • the channel 38 leading to the pump port P opens into an unspecified ring channel between the two valve bodies 18, 20
  • the channel 42 leading to the tank port R opens into the ring channel 78.
  • the branch channel 44 opens into the ring channel 68
  • the two branch channels 46 open directly into the central bore 16.
  • Control channels 52, 54, 56 and 58, 60 and 62 extend from the pockets and ring channels.
  • the control channel 52 leads from the pocket 64 to the ring channel 86 of the pilot valve 12; the control channel 54 leads from the pocket 66 to the ring channel 90 of the proportional valve 14; the control channel 56 leads from the ring channel 68 to the ring channel 84 of the pilot valve 12; the control channel 58 leads from the pocket 82 to the ring channel 92 of the proportional valve 14; the control channel 60 leads from the pocket 80 to the ring channel 88 of the pilot valve 12 and the control channel 62 leads from the ring channel 78 to the ring channel 94 of the proportional valve 14.
  • the safety valve according to the invention works as follows.
  • the two pilot valves 12 and 14 are not energized and their pistons 96, 98 are held in their basic position shown in FIG. 2 by the springs 104 and 112, respectively.
  • the pressure medium flows from the port P via the left branch duct 46, the annular space 124 of the piston 22, pocket 66 and the control duct 54 into the pilot valve 14, then from there via the control duct 58 into the pocket 82, and thereafter from the pocket 82 Cross bore 36 in the blind bore of the right working piston 22 and thus in the right spring chamber 120.
  • the pressure medium also flows via the right branch channel 46, the annular space 123 of the piston 22, pocket 80 and the control channel 60 into the pilot valve 12 and from there via the control channel 52 into the pocket 64 and out of this via the transverse bore 36 into the blind bore of the left working piston 22 and thus into the left spring chamber 120.
  • the two valve bodies 18 and 20 switch into their switching position shown in FIG. 4. In this position, the pump connection P via the channel 38, the central bore 16, the annular space 72, the connecting channel 48, the annular space 74, the annular space 76, the connecting channel 50 and the annular space 70 with the channel 40 and thus with the working connection A. connected to the consumer.
  • the pressure medium flows into the ring via the branch channels 46 branching off from the pump connection P and the control channels 54 and 60 channel 90 of the pilot valve 14 and on the other hand in the ring channel 88 of the pilot valve 12.
  • Fig. 5 shows a malfunction in which the pilot valve 14, i.e. the proportional valve has switched, while the pilot valve 12 has remained de-energized and has therefore not switched.
  • the left-hand working piston 22 remained pressurized because it initially had the position which it assumed in the basic position according to FIG. 2.
  • the right-hand working piston 22, on the other hand, has been relieved of pressure since the proportional valve 14 has switched, since, as was explained above with reference to FIG. 4, it communicates via the control channel 58, the proportional valve 14, the control channel 62 and the annular channel 78 to the channel 42 and is thus connected to the tank connection R.
  • the right spring chamber 120 is therefore depressurized, while the left spring chamber 120, as already stated, is under inlet pressure.
  • This position can also not be canceled by subsequently switching the pilot valve 12, since the left spring chamber 120 remains under supply pressure. Furthermore, the right spring chamber 120 can also no longer be pressurized by switching the proportional valve 14, since the pressure connection from the valve 14 is connected to the tank connection R via the channel 54, the pocket 66, the ring channel 68, the channel 44 and the channel 42 is. Therefore, in order to be able to put the valve back into operation, the fault must first be eliminated and the valve brought to its basic position by relieving pressure at P.
  • Fig. 6 shows a malfunction in which the pilot valve 12 has switched, but the proportional valve 14 has not switched over.
  • the left spring chamber 120 is relieved of pressure, while the right spring chamber 120 is under full pump pressure, which is why the two valve bodies 18 and 20 move to the left until the left working piston 22 strikes the housing, while the right valve body 20 on the left valve body, 18 strikes.
  • the working connection A is connected to the channel 42 and thus to the tank connection R via the channel 40, the ring channel 70, the connecting channel 50, the ring channel 76 and the ring channel 78.
  • Fig. 3 shows the control position of the safety valve.
  • the spring force of the left spring 112 plus the pressure force in the left spring chamber 108 the force of the proportional magnet 118 plus the pressure force in the right spring chamber 110.
  • the pressure force in the right spring chamber 110 becomes smaller with increasing force of the proportional magnet 118.
  • the differential pressure between the spring chamber 108 and the spring chamber 110 can thus be set by the proportional magnet. If the latter is de-energized, the differential pressure from the control channel 54 to the control channel 58, i.e. from P to A equal to zero; on the other hand, if the current has a maximum value, this differential pressure reaches its maximum size.
  • Fig. 3 the pilot valve 12 has switched, i.e. it takes the same position as in Fig. 4.
  • the proportional valve 14 has not fully switched, but it is controlled so that its piston 98 assumes a control position in which a pressure drop between the space 16 in the safety valve 10 (this is the part the central bore between the two valve bodies 18, 20) and the right spring chamber 120 arises because there is full pump pressure in the space 16, while the spring chamber 120 via the transverse bore 36 and the annular channel 121 from the piston 22, the annular space 82 Control line 58 and dip control position of the piston 98 is connected to the control line 62, which leads to the tank connection R via the ring channel 78.
  • the drive current of the proportional magnet 118 and thus the control position of the piston 98 is selected so that the fine control notches 34 are just closing (connection from the working connection A to the tank connection R), but the fine control notches 32 are not yet open, ie the connection from the pump connection P to the working connection A is still closed.
  • the fine control notches 32 thus give a corresponding cross-section free from the ring channel 74 to the ring channel 76 and thus from the pump connection P to the working connection A from the channel 38 via the central bore 16, the ring channel 72, the connecting channel 74, the fine control notches 32, the ring channel 76 and the connecting channel 50 to the channel 40 and thus to the working connection A.
  • the fine control notches 34 are closed.
  • the passage cross section of the fine control notches can thus be changed and thus the speed and the pressure build-up on the consumer, which is connected to the working connection A, can be controlled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Servomotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
  • Control Of Presses (AREA)
EP19890107713 1988-05-19 1989-04-27 Soupape de sûreté Withdrawn EP0342410A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3817120A DE3817120A1 (de) 1988-05-19 1988-05-19 Sicherheitsventil
DE3817120 1988-05-19

Publications (2)

Publication Number Publication Date
EP0342410A2 true EP0342410A2 (fr) 1989-11-23
EP0342410A3 EP0342410A3 (fr) 1990-10-17

Family

ID=6354731

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19890107713 Withdrawn EP0342410A3 (fr) 1988-05-19 1989-04-27 Soupape de sûreté

Country Status (4)

Country Link
US (1) US4903727A (fr)
EP (1) EP0342410A3 (fr)
JP (1) JPH0251682A (fr)
DE (1) DE3817120A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103775411A (zh) * 2014-01-08 2014-05-07 浙江大学 一种基于速度差动压反馈液控先导级的伺服阀
CN105201947A (zh) * 2015-10-19 2015-12-30 中国石油大学(北京) 液压保持阀位的电液换向阀

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6478049B2 (en) 1996-12-16 2002-11-12 Ross Operating Valve Company Double valve with anti-tiedown capability
US6155293A (en) 1996-12-16 2000-12-05 Ross Operating Valve Company Double valve with anti-tiedown capability
US5927324A (en) * 1996-12-16 1999-07-27 Ross Operating Valve Company Cross flow with crossmirror and lock out capability valve
JP4016151B2 (ja) * 1997-08-14 2007-12-05 Ｓｍｃ株式会社 ５ポート電磁弁ボディを利用した２ポート電磁弁
JP4072738B2 (ja) * 1997-08-21 2008-04-09 Ｓｍｃ株式会社 ５ポート電磁弁ボディを利用した３ポート電磁弁
EP1346801B1 (fr) 2000-10-20 2011-06-08 Honda Giken Kogyo Kabushiki Kaisha Dispositif de chargement et déchargement d'un anneau métallique
ES2278832T3 (es) 2001-05-04 2007-08-16 Ross Operating Valve Company Sistema de control de valvulas.
DE10320524A1 (de) * 2003-04-30 2004-11-25 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Hydraulikkreis zur Steuerung eines Antriebsstranges
US6996982B2 (en) * 2003-12-09 2006-02-14 The United States Of America As Represented By The Administrator Of The Environmental Protection Agency Method and device for switching hydraulic fluid supplies, such as for a hydraulic pump/motor
US8640723B2 (en) * 2007-02-22 2014-02-04 Raytheon Company First-stage pilot valve
US9903396B2 (en) * 2016-03-08 2018-02-27 Caterpillar Inc. Valve assembly
JP6815103B2 (ja) * 2016-06-10 2021-01-20 川崎重工業株式会社 流量制御弁装置
EP3545221B1 (fr) * 2016-11-22 2025-09-17 Parker-Hannifin Corporation Électrovanne à entraînement ultra faible
TWI665400B (zh) * 2018-12-14 2019-07-11 左天喬 多出口平衡輸出液體的控制閥

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3269416A (en) * 1964-05-25 1966-08-30 American Brake Shoe Co Control valve mechanism with means for reducing hydraulic shock
DE2717384C2 (de) * 1977-04-20 1983-12-22 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch betätigtes Steuerventil
DE3104957C2 (de) * 1981-02-12 1986-12-04 Herion-Werke Kg, 7012 Fellbach Hydraulisch betätigbares Pressensicherheitsventil
DE3205860A1 (de) * 1982-02-18 1983-08-25 Mannesmann Rexroth GmbH, 8770 Lohr Magnetbetaetigtes servoventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103775411A (zh) * 2014-01-08 2014-05-07 浙江大学 一种基于速度差动压反馈液控先导级的伺服阀
CN103775411B (zh) * 2014-01-08 2015-09-23 浙江大学 一种基于速度差动压反馈液控先导级的伺服阀
CN105201947A (zh) * 2015-10-19 2015-12-30 中国石油大学(北京) 液压保持阀位的电液换向阀
CN105201947B (zh) * 2015-10-19 2017-04-12 中国石油大学(北京) 液压保持阀位的电液换向阀

Also Published As

Publication number Publication date
JPH0251682A (ja) 1990-02-21
EP0342410A3 (fr) 1990-10-17
US4903727A (en) 1990-02-27
DE3817120A1 (de) 1989-11-30

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