EP0648931B1 - Arrangement de soupape - Google Patents

Arrangement de soupape Download PDF

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Publication number
EP0648931B1
EP0648931B1 EP94114490A EP94114490A EP0648931B1 EP 0648931 B1 EP0648931 B1 EP 0648931B1 EP 94114490 A EP94114490 A EP 94114490A EP 94114490 A EP94114490 A EP 94114490A EP 0648931 B1 EP0648931 B1 EP 0648931B1
Authority
EP
European Patent Office
Prior art keywords
valve
closing body
valve arrangement
accordance
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
EP94114490A
Other languages
German (de)
English (en)
Other versions
EP0648931A1 (fr
Inventor
Randolf Körtge
Thomas Nied-Menninger
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co 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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP0648931A1 publication Critical patent/EP0648931A1/fr
Application granted granted Critical
Publication of EP0648931B1 publication Critical patent/EP0648931B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • the invention relates to a valve arrangement for a hydraulic delivery device, in particular for a power steering pump, with a pressure limiting valve arranged in a control piston of a flow control valve.
  • a valve arrangement is known from e.g. WO-A-93 00514.
  • the flow control valve and the pressure relief valve are directly coupled to one another, that is to say they are formed in one piece.
  • the pressure relief valve is inserted into the piston of the flow control valve.
  • the control line connecting the pressure side and the pressure limitation side is produced through several bores arranged in the valve housing.
  • the disadvantage here is that these holes must be made with precision tools and can therefore only be realized with great effort. So that the pressure side can be connected to the pressure limiting side, it is necessary to arrange a plurality of bores which are offset from one another and which then together form the control line. Since not all areas of the holes to be drilled are required for the control line, there is also the problem of adequate sealing of the holes to the outside.
  • the invention is therefore based on the object of providing a valve arrangement of the generic type in which a control line can be provided in a simple manner.
  • control piston of the flow limiting valve has a blind bore in which the closing body of the pressure limiting valve is arranged and the closing body of the pressure limiting valve has a through opening which is aligned with a through opening of the control piston of the flow control valve, which is in the pressure side of the flow control valve flows.
  • the blind bore of the valve piston of the flow control valve is closed by a stopper which has a through opening and which at the same time serves as an abutment for the closing body of the pressure relief valve.
  • FIG. 1 shows a valve arrangement, generally designated 10, which has an interior space 14 that extends axially in a valve housing 12.
  • the interior 14 is closed by a plug 20 having a through bore (working connection) 18.
  • the plug 20 is introduced into the interior 14 in a suitable manner, for example by means of a thread 22.
  • the through hole 18 leads to a consumer (not shown), for example a steering system of a motor vehicle.
  • the plug 20 has an area 24 with a smaller diameter and protruding into the interior 14, the end face 26 of which has an opening 28.
  • a control piston 30 of a flow control valve 32 is mounted axially displaceably against the force of a spring element 34 within the interior 14.
  • the spring element 34 is supported on a base 36 of the interior 14 and a collar 38 of the control piston 30.
  • the control piston 30 also has sealing surfaces 40, with which it bears in a sealing manner on the wall 42 of the interior 14.
  • the control piston 30 also has an axial extension 44 which projects into the opening 28 of the plug 20 and ends there in an interior 46.
  • the diameter of the extension 44 is smaller than the diameter of the opening 28, so that there is a gap 48.
  • the extension 44 has a conical extension 50.
  • the extension 44 also has an axial bore 52 which opens into the interior 46 via a smaller-diameter diaphragm 54.
  • the interior 46 is connected via the gap 48 to an annular space 56, into which a channel 58 opens.
  • the channel 58 is not one with the pressure or delivery side shown hydraulic conveyor, for example, a power steering pump connected.
  • the control piston 30 is pressed by the force of the spring element 34 against a stop 59. This is implemented here, for example, by a snap ring inserted into a groove, which projects into the interior 14.
  • the control piston 30 also has a blind bore 60, at the bottom 62 of which the bore 52 opens.
  • the blind bore 60 is closed by a stopper 64 which is designed as a sleeve 66 which extends into the vicinity of the base 62.
  • the plug 64 is fastened in a suitable manner, for example via a thread 68, in the valve piston 30.
  • the sleeve has an interior 70 in which a closing body 72 of a pressure limiting valve 74 is guided.
  • a ring element 76 is fitted into the interior space 70, for example via an interference fit.
  • a spring element 78 is supported on the ring element 76 and, on the other hand, bears against a collar 80 of the closing body 72.
  • the spring element 78 presses a conically extending outer surface 82 of the closing body 72 against an edge 84 of an annular shoulder 86 formed on the sleeve 66 and pointing radially inwards.
  • the lateral surface 82 forms, together with the edge 84, a seat valve of the pressure limiting valve 74.
  • the closing body 72 has an extension 88 with which it is guided in a sealing manner within the ring element 76.
  • the closing body 72 is designed as a hollow body, that is to say it has an axial through opening 90 which connects a region 92 of the interior 70 to a region 94 of the interior 14.
  • annular space 96 is formed, which is simultaneously sealed against the area 92.
  • the annular space 96 is connected to an annular space 100 by at least one bore 98.
  • the bore 98 is formed by aligned, radially arranged bores of the control piston 30 and the sleeve 66.
  • a channel 102 opens into the annular space 100 and leads, for example, to a tank or the suction side of the hydraulic delivery device, not shown.
  • the annular space 100 is formed by a recess in the control piston 30.
  • valve arrangement 10 shown in FIG. 1 performs the following function:
  • valve arrangement 10 The general functioning of the valve arrangement 10 is known per se and is used to assign a predetermined fluid flow to a consumer and to limit this to a predeterminable value of, for example, 8 liters per minute. This limitation should also be ensured if the pressure prevailing in the channel 58 and thus in the annular space 56 increases.
  • a working pressure is established in the through bore 18 (work connection) and thus on the consumer connected there.
  • This working pressure also acts on the pressure-limiting side of the flow control valve 32 via the orifice 54, the bore 52, the area 92 and the passage opening 90, which thus result in a control line.
  • the working pressure also acts on the closing body 72 of the area 92 forming an annular space Pressure relief valve 74.
  • a pump pressure results from the sum of the working pressure and a volume pressure-dependent pressure difference at the annular gap 48 forming a flow resistance.
  • This pump pressure acts in the annular space 56 on the pressure side of the flow control valve 32.
  • the flow control valve 32 is thus clamped by the working pressure and the pump pressure thus forms a pressure compensator. If the working pressure increases, this acts on both sides of the pressure compensator.
  • the closing body 72 of the pressure relief valve 74 moves and opens a cross section to an interior of the pressure relief valve 74, which is about the openings 98 is connected to the low pressure side (suction side of the hydraulic conveying device). This limits the pressure on the pressure limiting side of the flow control valve 32. Because of the pressure compensator, the control piston 30 of the flow control valve 32 also moves against the force of the spring 34 and releases a flow cross section from the annular space 56 to the channel 102, through which the volume flow can flow.
  • control line which ensures the necessary pressure equalization between the interior 46 and the area 94, is implemented in a simple manner by means of centrally arranged through openings or bores.
  • the special design of the pressure relief valve 74 on the one hand ensures that the control line can be used for connecting the pressure side and the pressure relief side of the control piston 30 and, on the other hand, this ensures the pressure compensator for the control piston 30.
  • FIG. 2 shows an embodiment variant of a valve arrangement 10, which shows a pressure limiting valve 74 in a so-called "rider position".
  • the same parts as in Figure 1 are given the same reference numerals and are not explained again here.
  • the blind bore 60 of the control piston 30 is closed here by a plug 110 which is fastened in a suitable manner, for example by means of a thread 112.
  • the plug 110 has an axial through opening 114 into which a tubular sleeve 116 is fitted.
  • the sleeve 116 extends over the entire depth of the blind bore 60 and is supported by means of a centering ring 118 in the vicinity of the base 62 of the blind bore 60.
  • a closing body 120 of the pressure relief valve 74 is slidably mounted on the sleeve 116.
  • the closing body 120 is designed as a hollow body so that the sleeve 116 can pass through it.
  • the closing body 120 is by a spring element 122, which on the one hand supported on the centering ring 118 and on the other hand on a collar 124 of the closing body 120, pressed against the stopper 110.
  • the plug 110 has a recess 126 into which a cone 128 of the closing body 120 partially engages.
  • the cone 128 is pressed with an outer surface 130 against an edge 132 of the plug 110 and thus forms a seat valve.
  • the sleeve 116 has at least one through opening 134 which opens into the recess 126 of the plug 110.
  • the control piston 30 has a through opening 136, which connects the annular space 100 to an interior 138 of the control piston 30.
  • the function of the valve arrangement 10 shown in FIG. 2 is the same as already explained for FIG. 1.
  • the control line connecting the pressure side of the control piston 30 to the pressure limiting side is formed here by the orifice plate 54, the bore 52 and the sleeve 116.
  • this control line can in turn be produced in a simple manner by means of easily machined turned parts, without complex and complicated solutions being necessary.
  • the sleeve 116 having the through openings 134 a possibly occurring high pressure can be applied to the closing body 120 of the pressure limiting valve 74. If the pressure rises above a predeterminable value, the closing body 130 is pressed into the interior 138 against the force of the spring element 122, so that a connection to the annular space 100 is released via the passage opening 136.
  • the pressure via the channel 102 can thus be reduced, as already mentioned above.
  • FIGS. 1 and 2 can be used to create a valve arrangement of the generic type which requires very few components. These components are also designed as rotationally symmetrical parts, so that they are simple and therefore inexpensive to manufacture. It is no longer necessary to drill external holes that take over the function of the control line.

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

Claims (11)

  1. Arrangement de soupape pour un dispositif de refoulement hydraulique, notamment pour une pompe d'assistance de direction avec une soupape de limitation de pression disposée dans un piston de commande d'une soupape de régulation de débit, caractérisé en ce qu'on fait passer une conduite de commande, qui relie un branchement de travail (18) à un côté de limitation de pression de la soupape de régulation de débit (32), par le piston de commande (30) de la soupape de régulation de débit (32) et par un obturateur (72) de la soupape de limitation de pression (74).
  2. Arrangement de soupape selon la revendication 1, caractérisé en ce que le piston de commande (30) possède un trou borgne (60) dans lequel est disposé l'obturateur (72), et ce dernier présente une ouverture débouchante (90), qui est en alignement avec une ouverture débouchante (perçage 52) du piston de commande (30) qui débouche sur le branchement de travail (18).
  3. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que le trou borgne (60) est fermé par un bouchon (64, 110), qui possède une ouverture débouchante menant à une région (94) d'un espace intérieur (14) d'un boîtier de soupape (12).
  4. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que le bouchon (64) est réalisé sous la forme d'une douille (66) traversant un espace intérieur du piston de commande (30), douille à l'intérieur de laquelle l'obturateur (72) peut être déplacé en coulissement axial contre la force d'un élément de ressort (78).
  5. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce qu'un élément annulaire (76) est emmanché dans la douille (66), élément contre le côté frontal duquel s'appuie l'élément de ressort (78) qui sollicite l'obturateur (72) par une force de ressort.
  6. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que l'obturateur (72) présente un prolongement axial (88) qui assure le guidage de l'obturateur (72) à l'intérieur de l'élément annulaire (76).
  7. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que le piston de commande (30) et la douille (66) présentent au moins un perçage traversant radial (98) en alignement, qui débouche dans un espace annulaire (100) qui communique avec un canal (102) menant à un niveau de basse pression.
  8. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que le bouchon (110) est traversé par une douille centrée (116), qui occupe l'étendue du trou borgne (60).
  9. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que l'obturateur (120) est monté à coulissement axial sur la douille (116) contre la force d'un élément de ressort (122).
  10. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que le bouchon (64, 110) présente un bord (84, 132) qui forme une soupape à siège avec une face d'enveloppe (82, 130) de l'obturateur (72, 120).
  11. Arrangement de soupape selon une des revendications précédentes, caractérisé en ce que la douille (116) présente au moins une ouverture débouchante (134), qui communique avec un évidement (126) du bouchon (110) qui peut être fermé par la soupape à siège.
EP94114490A 1993-10-16 1994-09-15 Arrangement de soupape Expired - Lifetime EP0648931B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4335376 1993-10-16
DE4335376A DE4335376A1 (de) 1993-10-16 1993-10-16 Ventilanordnung

Publications (2)

Publication Number Publication Date
EP0648931A1 EP0648931A1 (fr) 1995-04-19
EP0648931B1 true EP0648931B1 (fr) 1996-11-20

Family

ID=6500352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94114490A Expired - Lifetime EP0648931B1 (fr) 1993-10-16 1994-09-15 Arrangement de soupape

Country Status (2)

Country Link
EP (1) EP0648931B1 (fr)
DE (2) DE4335376A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19529807A1 (de) * 1995-08-14 1997-02-20 Luk Fahrzeug Hydraulik Flügelzellenpumpe
GB2320955B (en) 1997-01-03 1999-08-04 Hobourn Automotive Ltd Flow control valve
CN106523354B (zh) * 2016-12-01 2019-02-19 徐州科源液压股份有限公司 实现恒流功能的齿轮泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES488092A0 (es) * 1980-01-31 1980-11-01 Bendiberica Sa Valvula protectora de circuitos hidraulicos con senal de mando por ausencia de caudal
US4570667A (en) * 1984-09-17 1986-02-18 General Motors Corporation Demand responsive flow regulator valve
DE9002722U1 (de) * 1990-03-08 1990-05-31 Vickers Systems GmbH, 6380 Bad Homburg Lenkhilfpumpe mit Stromregelventil
DE4120360A1 (de) * 1991-06-20 1992-12-24 Zahnradfabrik Friedrichshafen Stromregelventil
DE4126217A1 (de) * 1991-08-08 1993-02-11 Zahnradfabrik Friedrichshafen Regeleinrichtung fuer verdraengerpumpen

Also Published As

Publication number Publication date
DE59401078D1 (de) 1997-01-02
DE4335376A1 (de) 1995-04-20
EP0648931A1 (fr) 1995-04-19

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