EP0197467A2 - Soupape de descente freinée et maintenu sans fuites. - Google Patents

Soupape de descente freinée et maintenu sans fuites. Download PDF

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Publication number
EP0197467A2
EP0197467A2 EP19860104323 EP86104323A EP0197467A2 EP 0197467 A2 EP0197467 A2 EP 0197467A2 EP 19860104323 EP19860104323 EP 19860104323 EP 86104323 A EP86104323 A EP 86104323A EP 0197467 A2 EP0197467 A2 EP 0197467A2
Authority
EP
European Patent Office
Prior art keywords
check valve
valve
piston
control piston
control
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
EP19860104323
Other languages
German (de)
English (en)
Other versions
EP0197467A3 (en
EP0197467B1 (fr
Inventor
Hubert Häussler
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.)
Beringer-Hydraulik AG
Original Assignee
Beringer-Hydraulik 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
Priority claimed from DE19853514007 external-priority patent/DE3514007A1/de
Application filed by Beringer-Hydraulik AG filed Critical Beringer-Hydraulik AG
Publication of EP0197467A2 publication Critical patent/EP0197467A2/fr
Publication of EP0197467A3 publication Critical patent/EP0197467A3/de
Application granted granted Critical
Publication of EP0197467B1 publication Critical patent/EP0197467B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve

Definitions

  • the invention relates to a hydraulically controllable, leak-free brake check valve according to the preamble of claim 1.
  • Such a valve is known. It is used in particular for line break protection and is preferably flanged directly to a working cylinder.
  • Such safety valves are prescribed in accordance with DIN 24093 when lifting hydraulic baffles, so that, for example, the boom or the like does not drop uncontrollably in the event of a line break. So that the line rupture protection works automatically, the brake check valve has a check valve that closes the flow connection between the working cylinder and a switching valve, through which the working cylinder can be connected to a hydraulic pump and a storage tank for the hydraulic medium, in lifting and lowering operation.
  • a known further brake shut-off valve has a hollow control slide, which is axially displaceably mounted in a valve housing and in which the check valve is arranged, and a second closing element connected in parallel, which can be actuated by the plunger of a pilot piston.
  • the control piston and the second control piston connected in series in the flow path are acted upon by the same control pressure of a pilot control device.
  • the known brake check valve which has a second pilot-operated closing element for leak-free sealing of the flow bores in the valve housing, requires a great deal of structural effort for leak-free sealing of the hydraulic medium from the consumer connection due to the additional functional elements and control lines, which also results in an increased space requirement for the accommodation of the components.
  • the leak-free brake check valve according to the invention is characterized in particular by the fact that the seat function and the control function are integrated in the control piston, while it is ensured that the control spring effecting the seal is sufficient to counteract the hydraulic piston acting on the valve cone To close forces, but on the other hand can be designed weak enough to be overcome by the pressure forces acting on the control face of the control piston.
  • Experts had a prejudice against a design of the controlled check valve, in which the control piston performs the function of the leak-free seat valve in addition to its throttling function, which is why several valves with the various functions are generally connected in series (e.g. DE-A 32 39 930).
  • the annular surface of the closing member for example valve cone on the control piston, is designed large enough that on the one hand large surface pressures and jamming or jamming of the control piston in the longitudinal bore of the valve housing are avoided.
  • the ring area is so small that the spring force is greater than the hydraulic force on the ring area even at the maximum permissible load pressure, so that there is always a sufficient closing force for leak-free closing.
  • the spring force is in turn limited by the maximum control force that can be applied by the control pressure to the effective control piston surface.
  • the diameter difference on the annular surface of the valve cone is therefore preferably 0.2 to 0.5 mm.
  • the spring acting on the control piston and clamped in the spring chamber is designed in such a way that the hydraulic axial force is smaller than that on the control piston even at the maximum permissible pressure on the ring surface of the control piston acting, opposite spring force.
  • the control piston remains pressed in the closed position even at the maximum permissible pressure and the flow connection remains shut off.
  • the load pressure on the consumer can be controlled in a controlled manner by applying the control pressure to the control piston to a desired lower value.
  • the measure according to claim 3 can be achieved in a particularly advantageous manner that the valve seat, for which a hardenable material is generally preferably used, can be formed in a sleeve made of a suitable, surface-hardenable material, which can be exchanged in the corresponding bore of the valve housing used, in particular screwed.
  • the bushing is not divided and includes all functional elements of the valve including the spring chamber connected to the control piston in a cartridge design and is sealingly inserted into the valve housing as a whole unit. This avoids that the entire valve housing is made of a suitable hardenable material or that other precautions have to be taken to provide a hardened valve seat in the valve housing.
  • the brake check valve is further developed in an advantageous manner by the features specified in the further dependent claims. Attention is drawn in particular to claims 8 and 9, the features of which achieve an additional securing function in the event of a spring break.
  • the special nature of the helical spring according to claim 9 prevents the spring windings adjacent to the breaking point from being pushed into one another when one of the springs breaks. Since it can be assumed that a simultaneous breakage of two or more springs is not to be feared, it can be achieved by the proposed measure that if a single spring breaks, a predeterminable force is retained which prevents the control piston, the flow connection on the control piston suddenly to release. This predeterminable force should preferably be greater than the hydraulic force effective at the maximum load pressure on the ring surface.
  • the brake valve 1 shown in the drawing in longitudinal section consists of a valve housing 2 with a blind hole 3 multiply graduated in diameter, into which transverse bores 4 and 5, preferably at a right angle, open at an axial distance to which the Hydraulic consumers 46 (Fig. 3) on the one hand and a Weqevetil 43 (Fig. 3) on the other.
  • the valve housing 2 is constructed in such a way that its consumer connection 4 can be connected directly to a hydraulic working cylinder or the like, while the transverse bore 5 leads through pipe or hose line to a directional valve through which the brake check valve 1 can either be connected to a hydraulic pressure source, for example a pump 41 (FIG. 3) or the like, or to a reservoir 40 (FIG. 3).
  • control connection 6 At the bottom of the blind bore 3 there is another cross bore (control connection) 6 with a diameter, into which a filter element 7 is inserted.
  • the transverse bore 6 is provided for the connection of a control line 50 (FIG. 3) for the purpose of applying a control pressure to the end face of the control piston 8 of the brake check valve 1.
  • a connecting plug 9 with a sealing ring is inserted in a circumferential groove and on its end face facing the control connection 6.
  • This connector plug 9 has two axial pressure medium passages, one of which is provided for a certain direction of flow and is blocked by an associated check valve 10a / b for opposite flow directions.
  • a throttle 11a / b for damping vibrations.
  • Axially supported on the plug 9 is screwed into the blind hole 3, a correspondingly graduated, non-divided bushing 12 with thread 13, in which all the essential functional elements of the brake check valve 1 are received in a cartridge-like manner.
  • the socket 12 is axially closed at its end protruding from the valve housing 2 by a locking screw 15 locked with a nut 14.
  • annular channel 16 is provided in the area of the consumer connection 4 and is connected to an annular channel 18 on the inner circumferential surface of the socket 12 to create a flow connection through a transverse bore 17.
  • a corresponding flow connection is made in the area of the directional valve connection 5, but here there is a ring channel 16
  • Corresponding ring channel 19 through the diameter reduction of the bushing 12 and the axially offset, radial step 20 of the blind hole 3 of the valve housing 2.
  • the ring channels 16 and 19 are against each other and against the thread 13 and the connecting plug 9 by unspecified and by in with an axial distance arranged radial grooves used radial seals hydraulically separated.
  • the bushing 12 also has several stages of its longitudinal bore 21a to 21b on its inner lateral surface in the axial direction, the spring chamber 22 being formed in the region 21a with the largest inside and outside diameter of the bushing 12.
  • the control springs 23 are preferably helical springs which are wound from spring wire with a rectangular or square cross section in cross section, so that in the event of a spring breakage it is prevented that the windings are pushed into one another at the breaking point.
  • the springs 23 are biased by axial adjustment on the locking screw 15 so that the spring force at maximum pressure permitted at the consumer port 4 outweighs the hydraulic axial force that occurs on the annular surface 8.1 of the valve seat for the control piston 8.
  • the control piston 8 is axially displaceably mounted in the longitudinal bores 21c and 21d. This is designed as a stepped piston and is equipped at its step according to the invention with the preferably conical ring surface 8.1, which interacts with a corresponding valve seat on the bushing 12.
  • the control piston 8 is made on its outer surface with a narrow manufacturing tolerance compared to the longitudinal bore 21.
  • the surface is ground and hardened at least in the area of the ring surface 8.1 because of its function and construction as a closing member, in particular surface hardened.
  • the control piston 8 is equipped with a blind hole 25, which is connected to the outer circumferential surface of the control piston by a plurality of axially spaced transverse bores 26 and 27 and 28 to 30.
  • the transverse bore 26 is in the range of R ingkanä- le 16 and 18 of the bushing 12 and the area of consumer port 4 of the valve housing.
  • the transverse bore 27 lies in the area of the annular channel 19 and the directional valve connection 5.
  • the remaining transverse bores 28 to 30 lie in the axial direction between the transverse bores 26 and 27 and have different flow cross sections, namely with increasing distance from the valve annular surface 8.1 of the control piston 8 larger cross sections.
  • the blind hole 25 in the interior of the control piston 8 is stepped in diameter and forms at its step a seat 31 for the closing member 32 of a check valve, which is pressed against its seat 31 by a closing spring 33.
  • the closing spring 33 is biased by a support screw 34 which is screwed into the axially open end face of the control piston 8.
  • the spring plate 24 with the spherical body 35 mounted therein on the end face rests against a dome-shaped recess in the end face of the support screw 34 and is pressed by the spring force of the control springs 23a / b.
  • the closing member 32 has a transverse bore 36 so that its interior is acted upon by the pressure at the consumer connection 4 of the valve housing 2.
  • FIG. 2 shows a hydraulic circuit diagram of the brake lock valve according to FIG. 1.
  • Fig. 3 shows the brake check valve 1 in a highly schematic .
  • the hydraulic consumer 46 in particular a cylinder-piston unit on an excavator, a hydraulic elevator or the like. And a suitable control circuit for actuating the consumer 46.
  • the brake check valve 1 for similar components of FIG. 1st corresponding reference numbers are used.
  • the spring chamber 22 is ventilated and vented here through the vent hole 38 in the sealing plug 15 of the valve housing 2.
  • a filter 39 is arranged in the connected line to the tank 40.
  • the lowering line 45 is attached, at the lower connection the lifting line 47, 48 with the interposition of the brake check valve 1.
  • the line section 47 of the lifting line is of course omitted.
  • Lowering line 45 and lifting line 48 are connected to the hydraulic pump 41 via a four-way valve 43 and to the tank 40 via return line 49, the entire system being secured against overloading by an adjustable pressure relief valve 42.
  • the control line 50 which leads to the. Control port 6 of the brake check valve leads.
  • the pump line and the tank line 49 are connected internally by line 44, so that a pressure-free circulation takes place.
  • the brake check valve 1 With regard to the function of the brake check valve 1, it should be mentioned that when a sufficiently high pressure is applied to the directional valve connection 5 (directional valve 43 shifted to the right), the hydraulic force lifts the check valve 31 to 33 from the seat surface 31 and the way to the transverse bore 26 of the control piston 8 or to the working cylinder 46 connected to the consumer connection 4 directly or through a double screw nipple. In the opposite direction of flow, the check valve acts in the shut-off direction and closes the flow through the axial bore or the interior 25 of the control piston 8.
  • the brake check valve 1 is controlled via the control line 50 and control connection 6 are acted upon by a control pressure (pump pressure) which acts on the end face of the control piston 8 and axially displaces it against the force of the control spring (s) 23 to such an extent that its valve cone 8.1 is lifted off its valve seat (shown in greatly enlarged form) .
  • a control pressure pump pressure
  • the control piston 8 is axially displaced, and via the transverse bores 28 to 30 and the axial bore 25, the connection to the directional valve connection 5 and via this to the reservoir for the pressure medium is made, so that the load on the consumer 46 with the desired Working speed is reduced.
  • a pipe rupture in line 45 causes the control pressure in line 50 to drop and thus the brake shut-off valve 1 on valve plug 8.1 and its seat to be closed by spring 23.
  • a pipe rupture in line 48 causes hydraulic medium to flow out in the return flow to the unpressurized tank 40 without increasing the rate of descent.
  • the control piston is therefore designed as a stepped piston. It has an axial region with a large cross section and a large diameter and an axial region with a smaller cross section and a smaller diameter. Both areas of the control piston are sealingly guided in correspondingly designed areas of the cylinder. As a result of the difference in diameter, a step is created on the piston and cylinder between the area with a large diameter and correspondingly large cross section and the area with a smaller diameter and correspondingly smaller cross section. This step forms ring faces 8.1 on the piston and on the cylinder, each pointing in the axial direction. According to the invention, these ring surfaces are designed as seat valves.
  • the annular surface of the cylinder lies on the lower edge of the annular channel 18, which faces the directional valve connection 5 of the cylinder.
  • the appropriately designed annular surface on the control piston 8 is in the closed position as a seat valve on the annular surface of the cylinder.
  • the difference between the large diameter of the control piston and the small diameter of the control piston is very small. In practice, the difference is less than 1/10 of the small diameter.
  • the hydraulically effective annular surface 8.1, which is created on the control piston 8 in the region of the annular channel 18, is smaller than 1/20 of the control surface 51 of the control piston 8, which is pressurized via control line 50.
  • the difference is the hydraulically effective ring surface between the piston cross section with a large diameter (large piston step) and the piston cross section with a small diameter (small piston step).
  • the piston cross-section with a small diameter is equal to the control surface 51 of the piston. The following is thereby achieved: When the consumer 46 is lowered, the lowering line 45 is pressurized by connection to the pump 41. The valve seat 8.1 on the control piston 8 remains closed until the pressure forces on the control surface 51 of the control piston 8, on which the pressure of the lower line 45 acts via control line 50, outweighs the spring force 23.
  • control piston 8 If the pressure forces outweigh the spring force, the control piston 8 is raised and through the transverse bores 28, 29 of the control piston and the interior of the piston a connection is established between the lifting line 47 with consumer connection 4 and the lifting line 48 with directional valve connection 5.
  • the control piston 8 thus controls the passage of the lifting line 47, 48 during the lowering operation as a function of the pressure in the lowering line 45. If the lowering operation is now terminated, it must be ensured that the consumer 46 does not drop unintentionally and uncontrollably as a result of leakages . This is achieved in that the spring 23 presses the control piston 8 against the valve seat 8.1. However, it must be borne in mind that the consumer pressure, which is proportional to the load of the consumer 46, is still present in the lifting line 47.
  • this relatively weak design of the spring 23 ensures that the pressure forces acting on the control surface 51 against the spring force 23 can also be correspondingly low during lowering operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Check Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Control Valves For Brake Systems (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Safety Valves (AREA)
EP19860104323 1985-04-11 1986-03-27 Soupape de descente freinée et maintenu sans fuites. Expired - Lifetime EP0197467B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3512894 1985-04-11
DE3512894 1985-04-11
DE3514007 1985-04-18
DE19853514007 DE3514007A1 (de) 1985-04-18 1985-04-18 Leckfreies brems-sperrventil

Publications (3)

Publication Number Publication Date
EP0197467A2 true EP0197467A2 (fr) 1986-10-15
EP0197467A3 EP0197467A3 (en) 1988-12-21
EP0197467B1 EP0197467B1 (fr) 1992-01-29

Family

ID=25831198

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860104323 Expired - Lifetime EP0197467B1 (fr) 1985-04-11 1986-03-27 Soupape de descente freinée et maintenu sans fuites.

Country Status (5)

Country Link
US (1) US4727792A (fr)
EP (1) EP0197467B1 (fr)
JP (1) JPH0613881B2 (fr)
DE (1) DE3683666D1 (fr)
DK (1) DK166040C (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996029517A1 (fr) * 1995-03-23 1996-09-26 Mannesmann Rexroth Gmbh Clapet d'arret automatique
EP1598560A1 (fr) 2004-05-19 2005-11-23 Sauer-Danfoss ApS Dispositif de soupape hydraulique
CN100334361C (zh) * 2004-07-06 2007-08-29 株式会社三千里机械 液压缸
CN108999828A (zh) * 2018-08-22 2018-12-14 东莞海特帕沃液压科技有限公司 一种平衡阀
CN109058215A (zh) * 2018-08-22 2018-12-21 东莞海特帕沃液压科技有限公司 一种插装式平衡阀
DE102017008562A1 (de) 2017-09-12 2019-03-14 Daimler Ag Hydraulikventil, insbesondere für ein hydraulisches Parksperrensystem, und hydraulisches Parksperrensystem mit dem Hydraulikventil

Families Citing this family (20)

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Publication number Priority date Publication date Assignee Title
DE4207803A1 (de) * 1991-05-14 1992-11-19 Bosch Gmbh Robert Druckhalteventil
DE4323998C2 (de) * 1993-07-17 1996-01-11 Bosch Gmbh Robert Steuervorrichtung für einen hydraulischen Verbraucher
DE4420682A1 (de) * 1994-06-14 1996-01-04 Rexroth Mannesmann Gmbh Hydrauliksteuerung für eine teilende Werkzeugmaschine
KR100305742B1 (ko) * 1996-05-25 2001-11-30 토니헬샴 중장비의재생장치
JP3478931B2 (ja) * 1996-09-20 2003-12-15 新キャタピラー三菱株式会社 油圧回路
DE29716577U1 (de) * 1997-09-15 1997-11-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Lasthalteventil
NL1023583C2 (nl) * 2003-06-02 2004-12-03 Actuant Corp Hydraulische bedieningsinrichting.
US8262058B2 (en) * 2008-08-28 2012-09-11 Kot Norbert J Balanced pilot operated check valve
KR101488022B1 (ko) * 2008-12-24 2015-01-30 두산인프라코어 주식회사 홀딩밸브
US10208529B2 (en) 2009-06-23 2019-02-19 Higher Power Hydraulic Doors, Llc Tilt-up door
US9091107B2 (en) 2009-06-23 2015-07-28 Hp Doors, Llc Tilt-up door
US8245446B2 (en) 2009-06-23 2012-08-21 Hp Doors, Llc Tilt-up door
US9428951B2 (en) 2009-06-23 2016-08-30 Hp Doors, Llc Tilt-up door
JP5822233B2 (ja) 2012-03-27 2015-11-24 Ｋｙｂ株式会社 流体圧制御装置
US9611871B2 (en) 2013-09-13 2017-04-04 Norbert J. Kot Pneumatic valve assembly and method
US9631418B2 (en) 2014-06-25 2017-04-25 Phillip A. Crown Hydraulically operated overhead tilt-up door with stabilizer
US9567789B2 (en) 2014-06-25 2017-02-14 Phillip A. Crown Hydraulically operated overhead tilt-up door
JP6397715B2 (ja) * 2014-10-06 2018-09-26 Ｋｙｂ−Ｙｓ株式会社 流体圧制御装置
US10337537B2 (en) * 2017-08-30 2019-07-02 Caterpillar Inc. System and method for determining a health status of a tank
US11035482B2 (en) * 2019-01-31 2021-06-15 Scott Dale Follett Pressure relief valve

Citations (2)

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Publication number Priority date Publication date Assignee Title
CH543028A (de) 1972-11-09 1973-10-15 Beringer Hydraulik Gmbh Hydraulisches Senkbrems-Sperrventil
DE3239930A1 (de) 1982-10-28 1984-05-10 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch steuerbares sperrventil, insbesondere fuer die rohrbruchsicherung

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
FR1588450A (fr) * 1968-10-18 1970-04-10
DE2021857C3 (de) * 1970-05-05 1978-08-10 G.L. Rexroth Gmbh, 8770 Lohr Bremsventil
DE2302355A1 (de) * 1973-01-18 1974-08-08 Ilie Chivari Senkbremsventil
JPS51102037U (fr) * 1975-02-05 1976-08-16
JPS608383B2 (ja) * 1975-02-14 1985-03-02 株式会社多田野鉄工所 カウンタバランス弁
US4172582A (en) * 1977-04-21 1979-10-30 Rexnord Inc. Reverse differential holding valve
US4223693A (en) * 1978-07-27 1980-09-23 Modular Controls Corporation Counterbalance valve
JPS5925753U (ja) * 1982-08-11 1984-02-17 カヤバ工業株式会社 カウンタ−バランス弁

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH543028A (de) 1972-11-09 1973-10-15 Beringer Hydraulik Gmbh Hydraulisches Senkbrems-Sperrventil
DE3239930A1 (de) 1982-10-28 1984-05-10 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch steuerbares sperrventil, insbesondere fuer die rohrbruchsicherung

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996029517A1 (fr) * 1995-03-23 1996-09-26 Mannesmann Rexroth Gmbh Clapet d'arret automatique
US6027095A (en) * 1995-03-23 2000-02-22 Mannesman Rexroth Ag Pipe breakage safety valve
EP1598560A1 (fr) 2004-05-19 2005-11-23 Sauer-Danfoss ApS Dispositif de soupape hydraulique
DE102004025322A1 (de) * 2004-05-19 2005-12-15 Sauer-Danfoss Aps Hydraulische Ventilanordnung
CN100334361C (zh) * 2004-07-06 2007-08-29 株式会社三千里机械 液压缸
DE102017008562A1 (de) 2017-09-12 2019-03-14 Daimler Ag Hydraulikventil, insbesondere für ein hydraulisches Parksperrensystem, und hydraulisches Parksperrensystem mit dem Hydraulikventil
CN108999828A (zh) * 2018-08-22 2018-12-14 东莞海特帕沃液压科技有限公司 一种平衡阀
CN109058215A (zh) * 2018-08-22 2018-12-21 东莞海特帕沃液压科技有限公司 一种插装式平衡阀

Also Published As

Publication number Publication date
EP0197467A3 (en) 1988-12-21
DE3683666D1 (de) 1992-03-12
DK146986A (da) 1986-10-12
JPH0613881B2 (ja) 1994-02-23
DK166040C (da) 1993-08-02
EP0197467B1 (fr) 1992-01-29
US4727792A (en) 1988-03-01
JPS61274103A (ja) 1986-12-04
DK146986D0 (da) 1986-04-01
DK166040B (da) 1993-03-01

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DE3514007A1 (de) Leckfreies brems-sperrventil

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