EP0879374B1 - Distributeur - Google Patents

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Publication number
EP0879374B1
EP0879374B1 EP97919246A EP97919246A EP0879374B1 EP 0879374 B1 EP0879374 B1 EP 0879374B1 EP 97919246 A EP97919246 A EP 97919246A EP 97919246 A EP97919246 A EP 97919246A EP 0879374 B1 EP0879374 B1 EP 0879374B1
Authority
EP
European Patent Office
Prior art keywords
valve
main piston
control valve
directional control
pressure
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 - Lifetime
Application number
EP97919246A
Other languages
German (de)
English (en)
Other versions
EP0879374A2 (fr
Inventor
Georg Rausch
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0879374A2 publication Critical patent/EP0879374A2/fr
Application granted granted Critical
Publication of EP0879374B1 publication Critical patent/EP0879374B1/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
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7764—Choked or throttled pressure type
    • 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
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7787—Expansible chamber subject to differential pressures
    • Y10T137/7788—Pressures across fixed choke

Definitions

  • the invention relates to a directional valve according to the preamble of claim 1 and with such a directional valve provided pressure reducing and flow control valves.
  • Fig. 1 is an embodiment of such a directional control valve executed as a 2-way cartridge valve 2 is.
  • This has a valve bushing 4 in which a main piston 6 is guided axially.
  • the valve bushing 4 can be known Way fixed in a control block and thus Be part of a hydraulic circuit, to which further is discussed in more detail.
  • the valve socket 4 has two connections A and B, the Port B is usually the input port and is radial or laterally branching connection. Of the Output port A is arranged coaxially with the main piston 6. On the circumferential wall of the main piston 6 are radial bores 8 provided, through which the flow through the main piston 6 of the Port B can be connected to port A. With the shown Exemplary embodiment are the connection B and the radial bores 8 each designed as a bore star.
  • the starting position is the main piston 6 via a spring 10 biased against a stop position in which the connection opened from B via the main piston 6 to the outlet port A. is. That is, in the starting position of the main piston 6 the hydraulic fluid flows through the connection in the radial direction B enters through the radial bores 8 into the interior of the Main piston 6 and is deflected by about 90 ° to port A.
  • control block and Valve cover can be a control pressure to the Lead the spring side of the main piston 6, over which this additionally is biased towards its starting position.
  • This Control pressure can be, for example, from the output port A branching control pressure line can be applied.
  • Such valve arrangements in 2/2-way valve design include to the group of so-called logic elements, which as the main stage, for example for pressure limitation, pressure control, Pressure switching valves etc. are used.
  • the Main stage pilot valves are assigned, for example on the valve cover, integrated in the valve cover or on can be arranged at another location of a control block.
  • a circuit example is shown in which the built-in valve 2 is a component of a pilot-controlled pressure reducing valve 12. This essentially exists from built-in valve 2 and a directly controlled pilot valve 14, which is designed as a pressure relief valve.
  • the flow direction on installation valve 2 is from port B to port A, being as shown in Fig. 1 in the starting position a free volume flow is guaranteed.
  • the pressure at the output port A is via a control line 16 tapped and via two consecutive nozzles 18 and 20 led to the spring side of the main piston 8.
  • Desired outlet pressure at outlet connection A can be made via adjust the spring of the pilot valve 14.
  • This output pressure acts on the piston underside of the main piston 6 and is about the control line 16 and the nozzles 18 and 20 to the spring side of the Main piston 6 out.
  • the main piston 6 remains in its spring 10 Starting position in which the connection between A and B is complete is controlled. If the pressure at outlet port A - and thus the one between the two nozzles 18 and 20 - the exceeds the preset value, the pilot valve 14 is opened, so that control fluid via the pilot valve 14 to one Tank T flows.
  • the outlet pressure at the outlet port A is over the throughput
  • the vertical, dotted lines show the performance limits represent that when using different springs 10 set.
  • the power limit is approximately 4 bar when using a spring at 120 L / min, so that at higher volume throughputs stronger spring must be used.
  • a stronger spring 10 contains a number of Disadvantages, such as a lack of response and a lack of fine control in itself, especially at low Volume flows come into play and are not acceptable are.
  • the minimum adjustable pressure at port A increases disadvantageous through the use of stronger springs.
  • the invention is based on the object Directional valve, as well as provided with such a directional valve Pressure reducing / flow control valves to create the minimum device effort an increased performance limit have and sufficient even at low volume flows Show responsiveness.
  • the impulse force F I acting on the main piston can be at least partially compensated, so that the Performance limit compared to the conventional solutions is raised without the need to use a stronger spring.
  • This additional, resulting force acting in the opening direction on the surface difference effective surface arises due to the pressure drop occurring in the flowing hydraulic fluid when flowing through the radial bores.
  • the active surface is designed as a radial shoulder on the outer circumference of the main piston, so that it is widened in a step-like manner.
  • the bore of the valve bushing is of course also designed accordingly.
  • the radial shoulder is preferably in the area arranged between the radial bore star and the piston underside.
  • the radial shoulder (area difference) by means of an annular groove is formed, the radial shoulder an end face of the Ring groove forms. The other end face is then preferred trained as a sloping shoulder.
  • Directional control valves result from a pilot operated pressure reducing valve according to claim 8 or a flow control valve according to claim 10.
  • FIG. 4 is a partial section of a cartridge valve according to the invention 2, wherein in the following representations the same reference numerals for corresponding components as used in Fig. 1.
  • the cartridge valve 2 according to the invention can, for example in the case of a pilot-controlled pressure reducing valve according to FIG. 3 or use a flow control valve according to FIG. 5, to which in following is discussed.
  • the cartridge valve 2 has a Valve bushing 4, in the valve bore 28 of which a main piston 6 is guided axially. This is via a spring 10 biased into its initial position, in the one on the outer circumference of the main piston 6 attached stop ring 30 on a Stop surface of the valve bush 4 is present.
  • the valve bush 4 is by means of a mounting bush 32 in a control block 26 attached and closed with a valve cover, not shown, in or on which the other indicated in FIGS. 3 and 5 Components can be arranged.
  • the mounting bush 32 has an inner bore that is coaxial to the valve bore 28 is arranged, and which has such a diameter, that the spring-side part (top in Fig. 4) of the main piston 6 can dip into it without colliding.
  • valve bushing 4 could be installed according to FIG. 1 be trained.
  • An input connection B is on the valve bushing 4 as a bore star, that is, as a plurality of radial bores 36 educated. In addition, several are staggered, preferably two smaller holes 38 are provided.
  • Fine control takes place via the smaller bores 38 at low volume flows, if the connection from B to A is controlled.
  • the main piston 6 designed as a hollow piston, with a piston crown approximately in the central region 40 is formed.
  • This piston crown 40 engages the spring 10 to the main piston 6 in its open position (Fig. 4) to bias.
  • radial bores 8 formed below the piston crown 40, that is, in that of the spring 10 part of the piston jacket facing away are radial bores 8 formed, via which the hydraulic fluid from port B (Bores 36, 38) can enter the interior of the piston.
  • This Radial bores 8 are shown in the same way as in Fig. 1 formed as a bore star, which the jacket of the Main piston 6 passes through.
  • the radial shoulder 42 is by means of an annular groove 44 formed in the base of the radial bores 8th open and their other end face executed as an inclined shoulder 46 is.
  • valve bore 28 of the valve bush 4 is above (View according to Fig. 4) of the connection B according to the diameter ratio d / D expanded radially, being in the range of radial expansion a circumferential groove 48 is formed over the lower, enlarged part of the valve bore (diameter D) from the upper, narrowed part of the valve bore 28 (diameter d) is separated.
  • the circumferential groove 48 and the annular groove 44 are made of manufacturing technology Reasons provided, since the adjacent to the two grooves Surfaces (peripheral surface of the main piston 6; inner peripheral surface the valve bore 28) finely machined by grinding be avoided by the grooves that the Grinding wheel when grinding the smaller piston diameter or the larger valve bore diameter up to the radial shoulders must be brought there.
  • Annular gap 50 is formed between main piston 6 and valve bushing 4.
  • the magnitude of the force F depends on the diameter ratio on the one hand d / D and on the other hand from the pressure drop in the radial bores 8 from. Because of this, one will endeavor the depth the annular groove 44 to be as small as possible, since the pressure drop also depends on the remaining wall thickness of the main piston 6. The same applies to the depth of the circumferential groove 48 and the annular gap 50, which is also made as small as possible should be so that the hydraulic fluid when flowing through the Installation valve 2 not to a significant extent through the annular gap 50 can flow into the circumferential groove 48, so that ensures is that a suitable pressure on the outer circumference of the Main piston 6 is present and thus the pressure drop along the Radial bores also have the required size arrangement having.
  • valve 3 is the built-in valve in a control block 2 provided with a valve cover 22 in which the above described components, such as the nozzles 18, 20 and the pilot valve 14 can be provided.
  • FIG. 5 schematically shows another application example of a cartridge valve shown in FIG. 4. It will Insert valve 2 used in a 2-way flow control, whereby a pressure compensator is assigned to a throttle point for load compensation which is formed by the cartridge valve 2.
  • the Throttle point is designed as an adjustable throttle valve 52, which is provided downstream of the built-in valve 2.
  • a control line branches downstream of the throttle valve 52 54 from a throttle 18 to the spring side of the main piston is led.
  • the one at the outlet port A of the cartridge valve 2 applied pressure is - as in the embodiment described above - on the underside of the piston (Output connection side).
  • the built-in valve 2 as a pressure compensator with a pressure reducing function used.
  • the cartridge valve is 2 open in the starting position so that the hydraulic fluid from Port B via cartridge valve 2 to A and on from there via the throttle valve 52 to the consumer, for example a Hydraulic cylinder or a hydraulic motor (not shown) flows.
  • the pressure at the outlet of the throttle valve 52 is due to axial displacement of the main piston 6 and the associated Changes in the volume flow cross-section influenced so that the Pressure drop across the throttle valve 52 always remains constant. This pressure drop depends on the strength of the spring Piston.
  • the maximum is the built-in valve 2 enforceable volume flow by pushing it up the performance limit compared to conventional solutions significantly enlarged.
  • the solution according to the invention therefore enables minimal device-related effort, pushing the performance limit up, so that the cartridge valve according to the invention without Change of spring 10 can be used in a further volume flow range is.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)

Claims (10)

  1. Soupape à 2 voies comportant un piston principal (6), qui est guidé dans un manchon de soupape (4) et peut être traversé par un fluide hydraulique et au moyen duquel un raccord d'entrée (B) peut être relié à un raccord de sortie (A) et qui est précontraint dans sa position initiale au moyen d'un ressort (10), caractérisée en ce que le piston principal (6) comporte en amont d'un point d'étranglement (8) , une surface active (42, D-d) formée d'une différence de surfaces et au moyen de laquelle, lors de la circulation d'un écoulement, la composante de force de compression, qui charge le piston principal (6) en direction de sa position initiale, agit sur le piston.
  2. Soupape à 2 voies selon la revendication 1, caractérisée en ce que la surface active est réalisée sous la forme d'un épaulement radial (42) sur la circonférence extérieure du piston principal (6), et le manchon de soupape (4) est élargi de façon correspondante avec une forme étagée.
  3. Soupape à 2 voies selon la revendication 2, caractérisée en ce que le piston principal (6) comporte des perçages radiaux (8) qui constituent la zone d'étranglement et à l'aide desquels le fluide hydraulique peut circuler depuis le raccord d'entrée (D) jusqu'au raccord de sortie (A), les épaulements radiaux (42) étant formés dans la zone comprise entre les perçages radiaux (8) et la face inférieure du piston, qui est tournée vers le raccord de sortie (A).
  4. Soupape à 2 voies selon la revendication 2 ou 3, caractérisée en ce que le diamètre du piston principal est élargi de 3-10 % en raison de la présence de l'épaulement radial (42).
  5. Soupape à 2 voies selon la revendication 3 ou 4, caractérisée en ce que l'épaulement radial (42) est formé par une gorge annulaire (44), dans laquelle débouchent les perçages radiaux (8) du piston principal (6).
  6. Soupape à 2 voies selon la revendication 5, caractérisée en ce que la surface principale, qui est éloignée de l'épaulement radial (42), est agencée sous la forme d'un épaulement oblique (46).
  7. Soupape à 2 voies selon l'une des revendications 2 à 6, caractérisée en ce que le manchon de soupape (4) possède une gorge circonférentielle (48) dans la zone de l'élargissement de forme étagé.
  8. Soupape de réduction de pression à commande pilote comportant une soupape à 2 voies selon l'une des revendications précédentes, dans laquelle la pression au niveau du raccord de sortie (A) est appliquée par l'intermédiaire d'une buse (18) au côté du piston principal (6), sur lequel est situé le ressort, et la pression du côté du ressort peut être limitée par l'intermédiaire d'une soupape de limitation de pression (14) à commande pilote.
  9. Soupape de réduction de pression à commande pilote selon la revendication 8, caractérisée en ce que la soupape de commande pilote est une soupape de limitation de pression (14) à commande directe ou à commande pilote.
  10. Soupape de régulation d'écoulement comportant une soupape d'étranglement réglable (52), en amont de laquelle une soupape à 2 voies (2) conforme aux revendications 1 à 7 est branchée en tant que balance de pression, la pression en amont de la soupape d'étranglement (52) étant appliquée au côté, se lequel est situé le ressort, du piston principal (6) de la soupape à 2 voies (2).
EP97919246A 1996-02-16 1997-02-06 Distributeur Expired - Lifetime EP0879374B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19605862 1996-02-16
DE1996105862 DE19605862A1 (de) 1996-02-16 1996-02-16 Wegeventil
PCT/DE1997/000237 WO1997030306A2 (fr) 1996-02-16 1997-02-06 Distributeur

Publications (2)

Publication Number Publication Date
EP0879374A2 EP0879374A2 (fr) 1998-11-25
EP0879374B1 true EP0879374B1 (fr) 1999-11-17

Family

ID=7785641

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97919246A Expired - Lifetime EP0879374B1 (fr) 1996-02-16 1997-02-06 Distributeur

Country Status (6)

Country Link
US (1) US6068021A (fr)
EP (1) EP0879374B1 (fr)
JP (1) JP2000505864A (fr)
CA (1) CA2246709A1 (fr)
DE (2) DE19605862A1 (fr)
WO (1) WO1997030306A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110067781A (zh) * 2018-01-22 2019-07-30 派克汉尼汾(欧洲、中东和非洲)公司 用于阀组块的内置阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10145975A1 (de) * 2000-11-10 2002-08-29 Mannesmann Rexroth Ag Vorgesteuertes Druck-Einspeiseventil
JP6621225B1 (ja) * 2018-12-07 2019-12-18 ニッタン株式会社 負圧湿式予作動スプリンクラー設備における流量制御弁

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2594626A (en) * 1946-09-09 1952-04-29 Clarence E Earle Safety valve
FR1210120A (fr) * 1958-09-02 1960-03-07 Canadian Patents Dev Régulateur de pression pour canalisations de fluide
GB1096434A (en) * 1964-01-24 1967-12-29 Plessey Uk Ltd Improvements in or relating to automatic regulating valves for fluid flow
US3439696A (en) * 1966-12-15 1969-04-22 Bendix Westinghouse Automotive Fluid pressure control valve
DE2949231C2 (de) * 1979-12-07 1984-12-13 Mannesmann Rexroth GmbH, 8770 Lohr Druckmittelventil, insbesondere Druckreduzierventil
JPS59112316A (ja) * 1982-12-20 1984-06-28 Kayaba Ind Co Ltd 減圧弁
DE3625428A1 (de) * 1985-08-10 1988-02-04 Rexroth Mannesmann Gmbh Proportional-drosselventil
DE3701572A1 (de) * 1987-01-21 1988-08-04 Danfoss As Druckbegrenzungsventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110067781A (zh) * 2018-01-22 2019-07-30 派克汉尼汾(欧洲、中东和非洲)公司 用于阀组块的内置阀
CN110067781B (zh) * 2018-01-22 2021-09-03 派克汉尼汾(欧洲、中东和非洲)公司 用于阀组块的内置阀

Also Published As

Publication number Publication date
WO1997030306A2 (fr) 1997-08-21
US6068021A (en) 2000-05-30
JP2000505864A (ja) 2000-05-16
CA2246709A1 (fr) 1997-08-21
DE19605862A1 (de) 1997-08-21
WO1997030306A3 (fr) 1997-09-25
DE59700719D1 (de) 1999-12-23
EP0879374A2 (fr) 1998-11-25

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