EP0924438B1 - Ensemble soupape combiné - Google Patents

Ensemble soupape combiné Download PDF

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Publication number
EP0924438B1
EP0924438B1 EP98121507A EP98121507A EP0924438B1 EP 0924438 B1 EP0924438 B1 EP 0924438B1 EP 98121507 A EP98121507 A EP 98121507A EP 98121507 A EP98121507 A EP 98121507A EP 0924438 B1 EP0924438 B1 EP 0924438B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve assembly
piston
cylinder
radial opening
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
EP98121507A
Other languages
German (de)
English (en)
Other versions
EP0924438A3 (fr
EP0924438A2 (fr
Inventor
Dieter Dittmann
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0924438A2 publication Critical patent/EP0924438A2/fr
Publication of EP0924438A3 publication Critical patent/EP0924438A3/fr
Application granted granted Critical
Publication of EP0924438B1 publication Critical patent/EP0924438B1/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
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B49/225—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 with throttling valves or valves varying the pump inlet opening or the outlet opening

Definitions

  • the invention relates to a valve assembly, both for the formation of a Power control valve as well as for the formation of an externally pressure-controlled control valve suitable is.
  • a capacity control valve that has no effects on the pressure to be regulated the controlling working pressure occur is in the patent specification GB 1 501 761 presented.
  • the output of the hydraulic pump is determined on the one hand by the speed of the pump and on the other hand by eccentric adjustment of the Pump cross section set. If the pump pressure is above the set one If the setpoint increases, the pump pressure is used to deflect a valve piston its stationary rest position. The deflection of the valve piston causes a pressure drop in a second valve, which is then caused by eccentric Adjusting the pump cross-section reduces the pump delivery volume and thus a regulation of the hydraulic power achieved. In reverse Operating case of the pump pressure falling below the setpoint the same valve piston is deflected in the opposite direction by the pump pressure. This causes an increase in pressure in the second valve by switching the Pump pressure in the second valve, what about the reverse eccentric Adjustment of the pump cross-section to increase the pump delivery volume and thus leads to a regulation of the hydraulic power.
  • the invention is based on the finding that when using one in the Valve piston integrated measuring piston a particularly precise control characteristic or Control characteristic results.
  • the volumetric flask can be used both for the design the valve assembly as a power control valve as well as for the design as externally pressure-controlled control valve are used.
  • Capacity control valve is the inside face of the volumetric flask over a Connection hole with the recess of the lateral surface and thus with the Working pressure of the working line connected to the valve assembly Hydraulic pump connected.
  • the volumetric flask is therefore subjected to working pressure.
  • the outside face of the volumetric flask is supported on a fixed abutment, so that the valve piston is acted upon by the working pressure against the return spring becomes.
  • valve assembly as an externally pressure-controlled control valve
  • the inside end face of the measuring piston is supported on the valve piston and the control pressure is applied to the outside end face of the volumetric flask.
  • the valve piston is therefore against the measuring spring postponed.
  • valve assembly can be used both for the design and Power control valve as well as for the design as a control valve almost identical prefabricated and used in almost the same way.
  • the connecting hole between the recess on the lateral surface and the inside end face of the Volumetric flasks can also be designed as external pressure-controlled control valves basically be present, so that the valve piston for both uses can be manufactured identically. In the case of an external pressure-controlled configuration The control valve must then seal or close this connection bore become.
  • the valve assembly Design flows as a pressure valve controlled control valve in the opposite direction than in the design as a power control valve.
  • This has the advantage that one use other control edge on the valve piston for the two configurations Can be found. This makes sense because the control characteristic for the two Applications are different: when designing as a power control valve it is The valve is in the basic position and is opened with increasing working pressure in the Work management closed; in the configuration as an externally pressure-controlled control valve on the other hand, the valve is closed in the basic position and increases with increasing Control pressure opened.
  • the radial openings of the valve cylinder can be advantageous be axially offset from each other.
  • the connecting hole between the inside end face of the volumetric flask and the recess on the outer surface of the Valve piston can advantageously according to claim 6 from an axial Assemble the longitudinal bore and at least one radial cross bore. The The connection hole is then particularly easy to manufacture.
  • valve housing, the valve cylinder and the are advantageous Valve piston designed so that the valve cylinder in a hollow bore of the Valve housing is axially insertable and the valve piston in the valve cylinder as well is axially insertable.
  • the hollow hole is through a suitable cover body closable.
  • the cover body can at the same time as a fixed abutment for the volumetric flask if the valve assembly is used as a power control valve serve.
  • An adjusting element according to claim 9 is advantageous on the cover body provided for the axial adjustment of the position of the abutment for the volumetric flask.
  • the return spring preferably engages according to claim 11 on the volumetric flask opposite end face of the valve piston.
  • the maximum displacement of the valve piston according to claim 11 is also preferred and the bias of the return spring according to claim 13 adjustable.
  • the preload of the return spring is the control power of the Capacity control valve adjustable.
  • Fig. 1 shows an embodiment of the valve assembly according to the invention in one cut illustration. In the configuration shown in Fig. 1, the Valve assembly designed as a power control valve.
  • the valve assembly generally provided with the reference number 1, points in the illustrated Embodiment four connections, namely one with the upstream Section 2 of a work line connected work line input P, one with a downstream line 3 of the working line connected working line output A, a connected to the pressure fluid tank 4 tank port T and one with a Signal line 4 connected signal connector X.
  • the upstream section 2 of the Working line is connected via a connection B to a hydraulic pump 5, which Sucks pressurized fluid from the pressurized fluid tank 4 and into the upstream section 2 feeds the work management.
  • the downstream working line section 3 Consumers, e.g. B. hydraulic motors or actuators connected.
  • the on that Signaling port X of the valve assembly 1 connected signal line leads to a Signaling port X of the control block 7 of the hydraulic pump 5 to be described in more detail.
  • the signal line 6 branches inside the housing 7 from the downstream working line section 3.
  • the Signaling connection X and the working line output A also to a common Output connection can be combined, in which case the message line 6 outside the Valve assembly 1 branches off from the downstream working line section 3.
  • the housing 7 of the valve assembly 1 has a hollow bore 8 in which Valve cylinder 9 can be inserted in the axial direction.
  • the valve cylinder 9 in turn has a hollow bore 10 into which a valve piston 11 can be inserted in the axial direction is.
  • a step 12 in the hollow bore 8 of the housing 7 forms a stop for the valve cylinder 9.
  • the valve assembly 1 according to the invention can therefore in particular can be easily assembled.
  • the hollow bore 8 of the housing 7 is after Inserting the valve cylinder 9 and the valve piston 8 through a cover body 13 locked.
  • In the valve cylinder 9 there is a first radial opening 14 and a second, second radial opening 15 axially offset from the first radial opening 14 educated.
  • the recess 16 can, for. B. be formed by an annular groove. alternative However, flats, axial grooves or the like are also suitable.
  • a Volumetric flask 19 In a receiving bore 40 on a first end face 18 of the valve piston 11 is a Volumetric flask 19 guided.
  • An inside end face 20 of the volumetric flask 19 borders on one Connecting hole 21, which is a connection between the inside end face 20th of the measuring piston 19 with the recess 16 on the lateral surface 17 of the valve piston 11 creates.
  • the connecting bore 21 is preferably divided into a longitudinal bore 21a, which extends parallel to the longitudinal axis 22 of the valve assembly 1 and at least one Cross bore 21b, which extends radially to the longitudinal axis 22 of the valve assembly 1. On in this way, the production of the connecting bore 21 is possible in a particularly simple manner.
  • the outside end face 23 of the volumetric piston 19 is supported on a stationary Abutment.
  • the stationary abutment is on the Cover body 13 of the valve assembly 1 arranged and through the end face 25 of the Set screw 24 formed.
  • the set screw 24 can be screwed into the cover body 13, so that the axial position of the end face 25 forming the abutment is adjustable.
  • the set screw 24 can be fixed by means of a nut 26 and a lock nut 27.
  • a spring plate 29 On the end face 28 of the valve piston 11 opposite the measuring piston 19 overlaps a spring plate 29 a only schematically drawn return spring 30.
  • the return spring 30 from a spring assembly consisting of two Individual springs 30a and 30b formed.
  • a pin 31 formed, which cooperates with a pin 32 on a threaded bolt 33.
  • the Position of the pin 32 on the threaded bolt 33 is by turning the threaded bolt 33 adjustable and lockable by tightening the nut 34. In this way, the Distance between the pins 31 and 32 can be adjusted so that u. a. the maximum stroke of the valve piston 11 is adjustable against the restoring force of the restoring spring 30.
  • the return spring 30 On the side opposite the spring plate 29, the return spring 30 is in one Pot-shaped spring receptacle 35 is held, which can be screwed into the housing 7.
  • Adjustment of the screw-in depth of the spring receptacle 35 together with the pin 32 can be done Vary preload of return spring 30 and then by nut 36 fix.
  • the Specify control output of the capacity control valve Through the threaded bolt 24 can determine the maximum throttle cross-section of the power control valve and thus that Limit the maximum delivery volume of the hydraulic pump 5.
  • valve assembly 1 Before the function of the valve assembly 1 according to the invention in FIG. 1 shown configuration of the power control valve is discussed below First, the hydraulic circuitry shown in FIG. 1 as an example Valve assembly 1 described.
  • the delivery volume of the hydraulic pump 5 is determined by an adjusting device in the illustrated embodiment from a first actuating cylinder 50, a second Actuating cylinder 51, a first actuating piston 52 and a second actuating piston 53.
  • the actuating piston 53 is acted upon by a spring 54.
  • the control chamber 55 via a connecting line 56 to the upstream section 2 of the working line connected.
  • the valve unit 7 consists of a flow control valve 57 and a Pressure relief valve 58.
  • the flow control valve 57 and that Pressure limiting valve 58 are each in the exemplary embodiment as 3/2-way valves educated.
  • the flow control valve 57 is connected to the pressurized fluid tank via a connecting line 59 4 connected and via a connecting line 60 to the upstream Working line section 2 connected. The same applies to the pressure relief valve 58.
  • the flow control valve 57 is the pressure difference between the upstream working line section 2 and the downstream Working line section 3 is applied via the signal line 6.
  • the between that Flow control valve 57 and the actuating chamber 61 of the actuating cylinder 50 arranged Pressure relief valve 58 is dependent on the pressure in the upstream Working line section 2, which is generated directly by the hydraulic pump 5, driven.
  • the flow control valve 57 controls the pressure drop at the Valve assembly 1 to a constant value.
  • the output from the hydraulic pump 5 The flow rate is adjusted to a constant value adapted to the consumer.
  • the hydraulic power output by the hydraulic pump 5 exceeds. H. the product of the working pressure prevailing in the working line and the valve assembly 1 flowing flow, a predetermined maximum value, so that a Overload of the hydraulic pump 5 threatens, which works as a power control valve Valve assembly 1 the flow, so that the product of working pressure and Flow rate remains at least approximately constant.
  • Acts through the connecting bore 21 the working pressure on the inside end face 20 of the measuring piston 19. Since the Measuring piston 19 is supported on the threaded bolt 24, the valve piston 11 pushes in Fig. 1 against the return spring 30 upwards.
  • the control edge 62 on the recess 16 of the valve piston 11 reduces the throttle cross section on the second radial Opening 15 of valve cylinder 9 with increasing displacement of valve piston 11. If the working pressure increases further, the throttle cross-section becomes correspondingly higher further decreased.
  • the return spring 30 is not linear but degressive, the result is a functional relationship such that the product of working pressure and Flow rate is kept constant. If the return spring 30 as a spring package with If several partial springs are formed, the ideal power hyperbole can also be one stepwise linearized approximation with several linearly working partial springs. For some applications it is also sufficient to use the hyperbolic functional one Approximating the relationship between the working pressure and throttle cross-section linearly, see above that a simple, linear spring is sufficient as a return spring 30. It is also an alternative possible to design the radial opening 15 so that the opening cross section does not linearly changed, but changes so that the product of working pressure and Throttle cross section is constant, as is basically the case in DE-OS 24 61 897 is known.
  • FIG. 2 Another major advantage is that with the valve assembly 1 with only very minor modifications in a simple way, also an external pressure-controlled Control valve can be realized.
  • the application of the externally pressure controlled control valve is illustrated in Fig. 2.
  • the illustration in FIG. 2 is compared to the illustration 1 mirror image. Elements already described are matching Provide reference numerals, so that a repetitive description is unnecessary.
  • the control valve shown in FIG. 2 serves in contrast to that shown in FIG. 1 Power control valve not for limiting the power of the hydraulic pump 5, but for Setting a throttle cross section depending on one on one Control pressure connection 80 pending control pressure, for. B. one at the downstream working line section 3 connected consumers depending to measure a specific flow rate of the hydraulic pump 5 from the control pressure.
  • the power control valve shown in FIG. 1 In contrast to the power control valve shown in FIG. 1, the power control valve shown in FIG shown control valve of the same valve assembly 1 the upstream Working line section 2 not with the first radial opening 14 of the valve cylinder 9, but connected to the second radial opening 15 of the valve cylinder 9. Accordingly, the downstream one leading to the consumer Working line section 3 with the first radial opening 14 of the valve cylinder 9 connected.
  • the connection bore 21 is in the configuration of the valve assembly 1 not designed as a control valve, as can be seen from FIG. 2.
  • the Connecting hole 21 may be formed but closed. This would have the advantage that the valve piston 11 can be manufactured in the same way as the valve piston 11 for the formation of a power control valve according to FIG. 1 and that there is thus another Reduction in the number of different components results.
  • the outside face 23 of the measuring piston 19 adjoins an adjoining the control pressure connection 80 Control pressure chamber 81, so that the outer end face 23 of the measuring piston 19 with the control pressure is applied.
  • the inside end face 20 of the volumetric piston 19 is supported on the valve piston 11 and acts on the valve piston 11 pending control pressure against the return spring 30.
  • the displacement of the Valve piston 11 is proportional to the control pressure.
  • the control edge 82 of the recess 16 acts with the first radial opening 14 of the valve cylinder 9 together.
  • the valve piston 11 in the in Fig. 2nd shown control valve axially offset so far that the control valve in its not acted upon by control pressure the flow between the radial Opening 15 and the radial opening 14 blocks.
  • the throttle cross section increases at the control edge 82.
  • the volumetric flask 19 is, for. B. by an annular seal 83 relative to the lid body 13 sealed.
  • the control pressure connection 80 and the control pressure chamber 81 are preferably formed in the lid body 13.
  • valve assembly 1 both with only minor modifications a power control valve as well as an external pressure-controlled control valve leaves.
  • the only necessary modifications are additional training or sealing of the connecting bore 21 and the replacement of the cover body 13. All other components can be taken over unchanged.
  • the unit cost can therefore by Valve assembly 1 according to the invention can be considerably reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Control Of Fluid Pressure (AREA)

Claims (14)

  1. Groupe combiné de valves (1) susceptible d'être configuré à titre de valve de régulation de puissance (figure 1), comprenant
    un cylindre de valve (9) qui présente une première ouverture radiale (14) et une seconde ouverture radiale (15),
    un piston de valve (11) axialement mobile dans le cylindre de valve (9), lequel piston présente à sa surface enveloppe (17) un évidement (16) qui comporte une arête de commande (62, 82) dans la région de l'une au moins des deux ouvertures radiales (14, 15) du cylindre de valve (9),
    un piston de dosage (19) qui est guidé dans un passage de réception (40) du piston de valve (11) et au moins un ressort de rappel (30) qui applique au piston de valve (11) une force de rappel,
    dans lequel, dans la configuration du groupe combiné de valves (1) à titre de valve de régulation de puissance (figure 1) une surface frontale extérieure (23) du piston de dosage (19) s'appuie sur une butée stationnaire (25) et la surface frontale intérieure (20) du piston de dosage (19) est en liaison avec l'évidement (16) du piston de valve (11) via un perçage de liaison (21),
    caractérisé en ce que
    un perçage creux (10) du cylindre de valve (9) destiné à recevoir le piston de valve (11) est refermé par un couvercle interchangeable (13), de sorte que le groupe combiné de valves (1) est susceptible d'être configuré aussi bien à titre de valve de régulation de puissance (figure 1) qu'à titre de valve de commande (figure 2) sous la commande d'une pression extérieure.
  2. Groupe combiné de valves selon la revendication 1, caractérisé en ce que dans la configuration à titre de valve de commande sous la commande d'une pression extérieure (figure 2), la surface frontale extérieure (23) du piston de dosage (19) est attaquée par une pression de commande, et la surface frontale intérieure du piston de dosage (19) s'appuie contre le piston de valve (11).
  3. Groupe combiné de valves selon l'une ou l'autre des revendications 1 et 2, caractérisé en ce que :
    dans la configuration du groupe combiné de valves (1) à titre de valve de régulation de puissance (figure 1) un tronçon de conduite de travail (2) disposé en amont et relié à une pompe hydraulique (5) est raccordé à la première ouverture radiale (14) du cylindre de valve, et un tronçon de conduite de travail (3) disposé en aval et menant à un appareil utilisateur est raccordé à la seconde ouverture radiale (15) du cylindre de valve (9), et
    en ce que dans la configuration du groupe combiné de valves (1) à titre de valve de commande sous la commande d'une pression extérieure (figure 2), un tronçon de conduite de travail (2) disposé en amont et relié à une pompe hydraulique (5) est raccordé à la seconde ouverture radiale (15) du cylindre de valve (9), et un tronçon de conduite de travail (3) disposé en aval et menant à un appareil utilisateur est raccordé à la première ouverture radiale (14) du cylindre de valve (9).
  4. Groupe combiné de valves selon l'une des revendications 1 à 3, caractérisé en ce que :
    l'évidement (16) au niveau de la surface enveloppe (17) du piston de valve (11) comporte une première arête de commande (82) dans la région de la première ouverture radiale (14) du piston de valve (11) et une seconde arête de commande (62) dans la région de la seconde ouverture radiale (15) du piston de valve (11), et
    dans la configuration du groupe combiné de valves (1) à titre de valve de régulation de puissance (figure 1) la seconde arête de commande (62) du piston de valve (11) coopère avec la seconde ouverture radiale (15) du cylindre de valve (9) de telle manière que la seconde ouverture radiale (15) du cylindre de valve (9) est progressivement fermée au fur et à mesure du déplacement du piston de valve (11) à l'encontre de la force de rappel du ressort de rappel (30), et
    dans la configuration du groupe combiné de valves (1) à titre de valve de commande sous la commande d'une pression extérieure (figure 2) la première arête de commande (82) du piston de valve (11) coopère avec la première ouverture radiale (14) du cylindre de valve (9) de telle manière que la première ouverture radiale (14) du cylindre de valve (9) est progressivement ouverte au fur et à mesure du déplacement du piston de valve (11) à l'encontre de la force de rappel (30) du ressort de rappel.
  5. Groupe combiné de valves selon l'une des revendications 1 à 4, caractérisé en ce que les deux ouvertures radiales (14, 15) du cylindre de valve (9) sont agencées en décalage axial l'une par rapport à l'autre, la première ouverture radiale (14) étant détournée du piston de dosage (19) et la seconde ouverture radiale (15) étant tournée vers le piston de dosage (19).
  6. Groupe combiné de valves selon l'une des revendications 1 à 5, caractérisé en ce que le perçage de réception (40) pour le piston de dosage (19) est réalisé au niveau d'une surface frontale (18) du piston de valve (11) parallèlement à l'axe longitudinal (22) du piston de valve (11).
  7. Groupe combiné de valves selon l'une des revendications 1 à 6, caractérisé en ce que, dans la configuration du groupe combiné de valves (1) à titre de valve de régulation de puissance (figure 1), le perçage de liaison (21) est constitué par un perçage allongé axial (21a) débouchant dans le perçage de réception (40) pour le piston de dosage (19), et par au moins un perçage transversal radial (21b) qui relie le perçage allongé (21a) à l'évidement (16).
  8. Groupe combiné de valve selon l'une des revendications 1 à 7, caractérisé en ce que le cylindre de valve (9) est susceptible d'être introduit axialement dans un perçage creux (10) d'un boítier de valve (7), et en ce que le piston de valve (11) est susceptible d'être introduit axialement dans le cylindre de valve (9).
  9. Groupe combiné de valves selon la revendication 8, caractérisé en ce que, dans la configuration du groupe combiné de valve (1) à titre de valve de régulation de puissance (figure 1), le piston de dosage (19) s'appuie contre le corps de couvercle (13) qui constitue la butée stationnaire.
  10. Groupe combiné de valves selon la revendication 9, caractérisé en ce qu'un premier élément d'ajustement (24) est prévu sur le corps de couvercle (13) pour le réglage axial de la position de la butée pour le piston de dosage (19).
  11. Groupe combiné de valves selon la revendication 8, caractérisé en ce que, dans la configuration du groupe combiné de valves (1) à titre de valve de commande sous la commande d'une pression extérieure (figure 2) il est prévu un raccord de pression de commande (80) réalisé sur le corps de couvercle (13) et auquel se raccorde une chambre de pression de commande (81), laquelle est adjacente de la surface frontale extérieure (23) du piston de dosage (19).
  12. Groupe combiné de valves selon l'une des revendications 1 à 11, caractérisé en ce que le ressort de rappel (30) attaque une surface frontale (23) du piston de valve (11) située à l'opposé du piston de dosage (19).
  13. Groupe combiné de valve selon l'une des revendications 1 à 12, caractérisé en ce qu'il est prévu un second élément d'ajustement (33) pour régler le déplacement maximum du piston de valve (11) dans le cylindre de valve (9) à l'encontre de la force de rappel du ressort de rappel (30).
  14. Groupe combiné de valve selon l'une des revendications 1 à 13, caractérisé en ce qu'il est prévu un troisième élément d'ajustement (35) pour régler la précontrainte du ressort de rappel (30).
EP98121507A 1997-12-18 1998-11-13 Ensemble soupape combiné Expired - Lifetime EP0924438B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19756599A DE19756599C2 (de) 1997-12-18 1997-12-18 Leistungsregelventil und fremddruckgesteuertes Steuerventil
DE19756599 1997-12-18

Publications (3)

Publication Number Publication Date
EP0924438A2 EP0924438A2 (fr) 1999-06-23
EP0924438A3 EP0924438A3 (fr) 2000-06-28
EP0924438B1 true EP0924438B1 (fr) 2004-01-07

Family

ID=7852565

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98121507A Expired - Lifetime EP0924438B1 (fr) 1997-12-18 1998-11-13 Ensemble soupape combiné

Country Status (2)

Country Link
EP (1) EP0924438B1 (fr)
DE (2) DE19756599C2 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2456404A1 (de) * 1974-11-29 1976-08-12 Bosch Gmbh Robert Druckregler fuer hydropumpe
DE2461897A1 (de) * 1974-12-31 1976-07-08 Bosch Gmbh Robert Regeleinrichtung fuer eine pumpe
DE8107889U1 (de) * 1981-03-18 1981-10-22 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Pneumatische ventilanordnung
DE3812735A1 (de) * 1988-04-16 1989-10-26 Hauhinco Maschf Bauelementensatz fuer 2-wege-einbauventile
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung

Also Published As

Publication number Publication date
DE19756599A1 (de) 1999-09-09
DE19756599C2 (de) 1999-12-09
DE59810544D1 (de) 2004-02-12
EP0924438A3 (fr) 2000-06-28
EP0924438A2 (fr) 1999-06-23

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