EP0565982A1 - Valve arrangement - Google Patents

Valve arrangement Download PDF

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Publication number
EP0565982A1
EP0565982A1 EP19930105594 EP93105594A EP0565982A1 EP 0565982 A1 EP0565982 A1 EP 0565982A1 EP 19930105594 EP19930105594 EP 19930105594 EP 93105594 A EP93105594 A EP 93105594A EP 0565982 A1 EP0565982 A1 EP 0565982A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve arrangement
bore
arrangement according
piston
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
EP19930105594
Other languages
German (de)
French (fr)
Other versions
EP0565982B1 (en
Inventor
Dieter Tischer
Bernd Niethammer
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.)
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hilite Germany GmbH
Original Assignee
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hydraulik Ring 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 HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH, Hydraulik Ring GmbH filed Critical HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Publication of EP0565982A1 publication Critical patent/EP0565982A1/en
Application granted granted Critical
Publication of EP0565982B1 publication Critical patent/EP0565982B1/en
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
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • 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
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to a valve arrangement according to the preamble of claim 1.
  • Such a valve arrangement is known, for example, to actuate cylinders operating in push-pull mode.
  • the cylinder selection with fluid supply or fluid discharge is made via the solenoid-operated directional valve.
  • the infeed movement is carried out by applying the fluid flow to the full cylinder surface.
  • the return movement of the switching piston is carried out by the load or a return spring.
  • the cylinders can generate a force that corresponds to the product of the full cylinder surface and system pressure.
  • a pressure relief valve is provided on the pump side, with which the pressure of one cylinder can be adjusted. Should the other cylinder be with another one, can.
  • the invention has for its object to design the generic valve assembly so that a pressure limitation can be achieved inexpensively with minimal parts and without additional volume.
  • the pressure valve is accommodated within the construction volume of the directional valve. Due to a slight modification of the switching piston of the directional control valve and installation of the valve member as the only additional component, the additional pressure valve and its system connection required in the known valve arrangement are eliminated.
  • the valve arrangement according to the invention fulfills the requirements that are placed on such a mass product, namely a small construction volume, a small number of components, low susceptibility to malfunction and extremely inexpensive production.
  • the directional control valve 1 has a directional control valve 1 which is attached to a connecting plate 2.
  • the directional control valve 1 has a switching piston 3, which is mounted axially displaceably in a bore 4.
  • the switching piston 3 has control edges 5 to 10.
  • connection plate 2 is provided with a working connection A, a working connection B, a pressure connection P and a return T to the tank in a known manner.
  • a cylinder 12 and 13 is connected to the working ports A and B, respectively.
  • these two cylinders 12, 13 work in push-pull. They each have a piston 14, 15, each of which is acted upon by hydraulic medium.
  • the piston rod 16, 17 carrying the piston 14, 15 is under the force of a compression spring 18, 19 which loads the piston rod 16, 17 in the direction of its retracted position. With the hydraulic medium, the corresponding piston 14, 15 is thus counter to the force of this return spring 18, 19 postponed.
  • a magnet 20 is connected to the directional control valve 1, the magnet plunger 21 of which cooperates with the adjacent end of the switching piston 3. If the magnet 20 is switched on, then the magnetic plunger 21 is extended in a known manner, so that it axially moves the switching piston 3 against the force of a return spring 22 into the desired switching position.
  • the return spring 22 is provided at the other end of the switching piston 3 and is supported at one end on a cover 23 which is screwed onto the housing of the directional control valve 1 and covers the bore 4 to the outside. With its other end, the return spring 22 is supported on a spring plate 24 which is seated on an additional piston 25 which projects axially displaceably into an axial bore 26 of the switching piston 3.
  • the bore 26 is guided to approximately half the length of the switching piston 3 and opens into a diametral bore 27 which passes through the switching piston 3 in the area between the control edges 8 and 9.
  • the bore 26 is crossed by a further diametral bore 28 which passes through the switching piston 3 in the area between the edge 11 and the adjacent switching piston end.
  • the directional control valve 1 has a relief bore 29 lying parallel to the switching piston 3, into which the tank connection T opens.
  • the relief bore 29 extends between two spaces 30 and 31. In the space 31, which is delimited at one end by the cover 23, there is the spring plate 24.
  • connection plate 2 has bores 32 to 35 which are connected to the corresponding connections A, B, P and T and to which corresponding bores 36 to 39 of the directional control valve 1 are connected.
  • the holes 36 and 38 of the directional control valve 1 assigned to the working connections A and B each open into an annular space 40 and 41 of the bore 4.
  • annular space 42 In the area between the two annular spaces 40 and 41 there is an annular space 42 with a smaller diameter in which the pressure connection P associated hole 37 opens.
  • the bore 39 assigned to the tank connection T finally opens into an annular space 43 in the bore 4, which has the same diameter as the annular space 42.
  • the cylinder 13 In the position shown in Fig. 1, the cylinder 13 is relieved, that is, its compression spring 19 has pushed the piston rod 17 into its initial position.
  • the other cylinder 12 is under the pressure of the hydraulic medium, so that its piston 14 is pushed back against the force of the spring 18.
  • the magnet 20 If the other cylinder 13 is now to be pressurized, the magnet 20 is actuated so that the magnet plunger 21 is axially displaced against the switching piston 3 in a known manner.
  • the magnetic plunger or armature 20 has performed its preliminary stroke VH, it comes to rest on the free end of the switching piston 3 and moves it during the subsequent working stroke into a switching position in which the hydraulic medium can flow to the cylinder 13.
  • the hydraulic medium flows via the pressure connection P and the bores 33 and 37 into the annular space 42.
  • the switching piston 3 is then displaced to the right in FIG. 1, that the control edge 7 closes the access of the hydraulic medium to the annular space 40, while the control edge 8 clears the way for the hydraulic medium to the annular space 41.
  • the hydraulic medium can pass from the annular space 42 into the annular space 41 and from there via the bores 38 and 34 to the working connection B.
  • the piston 15 is then moved by the hydraulic medium against the force of the spring 19.
  • the other cylinder 12 is now relieved, so that the spring 18 can move the piston 14 in FIG. 1 to the right into its end position.
  • the hydraulic medium When the cylinder 13 is pressurized, the hydraulic medium also enters the diametral bore 27 of the switching piston 3. This diametral bore 27 is arranged such that it is still in the region of the annular space 41. The hydraulic medium thus flows via this diametral bore 27 also into the axial bore 26 of the switching piston 3.
  • the additional piston 25 mounted in it is thus under the pressure of the hydraulic medium and the force exerted by the magnetic tappet 21, which counteracts the force of the return spring 22.
  • the magnetic plunger 21 moves against an end stop (not shown). Then the magnetic force has its greatest value.
  • the pressure acting on the additional piston 25 becomes greater than the restoring force, so that it is displaced against the force of the restoring spring 22 (stroke 47).
  • the additional piston 25 thus releases the diametral bore 28 of the switching piston 3, so that the hydraulic medium can now flow through the bore 26 and the diametral bore 28 into the space 31 and from there via the relief bore 29 to the bore 39, which connects to the tank connection T of the connecting plate 2 is connected.
  • the additional piston 25 thus forms in connection with the diametral bore 28 a pressure relief valve 67 which limits an impermissibly high pressure build-up.
  • This pressure relief valve 67 is housed within the switching piston 3, so that it has no additional space requirement.
  • an additional intermediate plate device is not required, as is provided in the known valve arrangement.
  • the magnet 20 is switched off, so that the magnetic plunger 21 is moved back into its starting position under the force of a return spring (not shown) or the return spring 22.
  • the return spring 22 pushes the additional piston 25 back into the in via the spring plate 24 Figure 1 shown locking position back, in which the additional piston closes the diametral bore 28.
  • the spring plate 24 comes into contact with the switching piston 3, it is moved again into the other switching position shown in FIG. 1 under the force of the return spring 22. Now the connection from the pressure port P to the working port B of the cylinder 13 is closed, while the annular space 40 is in communication with the annular space 42.
  • the hydraulic medium can therefore pass from the pressure connection P via these annular spaces into the bores 36 and 32 and thus to the working connection A of the cylinder 12. Its piston 14 is then moved by the hydraulic medium against the force of the return spring 18 into the pressure position shown in FIG. 1. The return spring 19 of the other cylinder 13 now pushes the piston 15 into the relief position shown in FIG. 1. The hydraulic medium which is no longer under pressure is then displaced from the annular space 41 into the annular space 43 via the working connection B and the bores 34, 38 and from there via the bores 39, 35 to the tank connection T.
  • the working stroke 46 of the switching piston 3 is between the stop points 44 and 45 of the magnetic plunger 21.
  • the opening stroke 47 of the additional piston 25 connects to the working stroke 46.
  • This opening stroke ensures that the hydraulic pressure acting on the piston 15 of the cylinder 13 does not assume impermissibly high values, but is limited to a predetermined value.
  • the level of this pressure can be adjusted by the restoring force of the spring 22.
  • the cover 23 can be provided with a threaded part (not shown) on which the Return spring 22 is supported. By screwing this threaded part into the cover 23 to a greater or lesser extent, the force of the return spring 22 can then be adjusted sensitively.
  • the valve arrangement can be easily and precisely adapted to the most varied of applications. This makes it possible to set the maximum allowable pressure exactly.
  • the additional piston 25a is also mounted in the bore of the switching piston 3a, the end of which is adjacent to the cover 23a of the directional control valve 1a is formed by an adapter piece 48.
  • the adapter piece 48 has the advantage that the diameter of the additional piston 25a is not dependent on the dimensions of the switching piston 3a.
  • the switching piston 3a has an annular groove 49 adjacent to the adapter piece 48, into which the adapter piece 48 engages with a flanged edge 50.
  • the adapter piece 48 has a socket part 51 with which it sits on the end of a base body 68 of the switching piston 3a and the free end face of which is flanged.
  • the bottom 52 of the socket part 51 lies flat against the end face 53 of the base body 68.
  • the socket part 51 is followed by an extension 54, which is advantageously formed in one piece with the socket part 51 and whose outer diameter is smaller than the outer diameter of the socket part 51 and preferably also smaller than the outer diameter of the base body 68.
  • the extension 54 serves as a bearing and guide for the additional piston 25a and thus for the spring plate 24a, on which one end of the return spring 22a is supported for the switching piston 3a. With its other end, the return spring 22a in turn rests on the cover 23a.
  • the approach 54 is centrally penetrated by a longitudinal bore 55, which also penetrates the bottom 52 of the socket part 51.
  • the axial longitudinal bore 55 is aligned with the bore 26a of the base body 68, thus forming a continuation of this bore 26a.
  • the additional piston 25a is mounted axially displaceably in the longitudinal bore 55.
  • the longitudinal bore 55 penetrates a diametral bore 56 which penetrates the shoulder 54 of the adapter piece 48.
  • the bore 26a of the base body 68 is thus connected to the space 31a via the longitudinal bore 55 and the diametral bore 56 of the adapter piece 48.
  • the spring plate 24a is designed as a sleeve which has a bottom 57. It is penetrated by a central bore 58, in which the additional piston 25a is held axially.
  • the end of the spring plate 24a facing away from the bottom 57 is provided with a conical surface 59 opening towards the bottom 52 of the socket part 51, which together with the opposite underside of the bottom 52 of the socket part 51 has an obliquely outwardly tapering flow area 60 for the hydraulic medium forms.
  • the spring plate 24a surrounds the shoulder 54 of the adapter piece 48 with a slight radial play 61.
  • a space 62 is formed between the bottom 57 of the spring plate 24a and the end face of the shoulder 54, the volume of which is in Dependence on the stroke of the additional piston 25a changes.
  • This space 62 is connected to the tank connection T via the annular gap 61.
  • the hydraulic medium can only flow through with a pressure gradient. This ensures excellent damping of the additional piston 25a, which, as a result, cannot oscillate during operation of the valve arrangement.
  • This valve arrangement is therefore characterized by a very high level of noise damping. Also, no pressure pulsations occur due to the damping of the additional piston 25a.
  • the valve arrangement according to FIG. 3 is otherwise of the same design as the exemplary embodiment according to FIG. 1.
  • the mode of operation of this valve arrangement is basically the same as in the previous exemplary embodiment. If the magnet plunger 21 of the magnet 20 comes into the stop position at the stop of the magnet, the additional piston 25a is then displaced by the hydraulic medium against the force of the return spring 22a in the bore 55 of the adapter piece 48, whereby the diametral bore 56 is released.
  • the hydraulic medium can then flow in the manner described via the diametral bore 27 (FIG. 1) of the switching piston 3a, the bores 26a and 55 into the diametral bore 56. There, the hydraulic medium enters the space 31a, in which the relief bore 29a opens.
  • the embodiment according to FIG. 3 is again characterized by its simple construction.
  • the additional piston 25a in connection with the diametral bore 56 in turn forms a pressure relief valve 67a, which is accommodated within the installation space of the directional control valve 1a.
  • this valve arrangement like the embodiment according to FIG. 1 - takes up very little space and can now also be used where space is tight or the construction volume cannot be exceeded.
  • this valve arrangement is characterized by the described high damping of the additional piston 25a and the associated high noise damping, the reduction of the pressure pulsations and the extremely low additional costs for the pressure limiting valve.
  • annular channel can also be provided instead of the diametrical bores 28 and 56.
  • annular channel can also be provided instead of the diametrical bores 28 and 56.
  • the flow gain can be substantially greater than with radial bores.
  • the additional piston 25, 25a can be a simple and inexpensive bearing needle in the embodiments according to FIGS. 1 and 3.
  • Fig. 4 shows two embodiments of valve members that can be used instead of the additional piston for the pressure relief valve.
  • the valve member 25b is designed as a ball, on which the spring plate 24b for the return spring 22b is supported.
  • the ball 25b closes the bore 26b of the switching piston 3b.
  • valve member is designed as a cone 25c. It is advantageously formed in one piece with the spring plate 24c for the return spring.
  • valve members 25b, 25c release the bore 26b of the switching piston 3b when the force generated by the return spring is exceeded, so that the hydraulic medium can flow out via the space 31a and the relief bore 29a to the tank connection T in the manner described.

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

Abstract

The valve arrangement has a directional control valve (1), the control piston (3) of which can be displaced against a restoring force by a plunger (21) of a magnet (20). Furthermore, a pressure valve (67) is provided which has a valve member (25) which can be adjusted against a restoring force. The valve member (25) of the pressure valve (67) is arranged on the control piston (3). The pressure valve (67) therefore lies within the overall volume of the directional control valve (1), as a result of which the valve arrangement has a small overall volume. In addition, it consists of a small number of components and is inexpensive to produce. <IMAGE>

Description

Die Erfindung betrifft eine Ventilanordnung nach dem Oberbegriff des Anspruches 1.The invention relates to a valve arrangement according to the preamble of claim 1.

Eine derartige Ventilanordnung ist bekannt, um beispielsweise im Gegentakt arbeitende Zylinder zu betätigen. Die Zylinderauswahl mit Fluidbeaufschlagung bzw. Fluidentlastung erfolgt über das magnetbetätigte Wegeventil. Die Zustellbewegung erfolgt durch Beaufschlagen der Zylindervollfläche mit dem Fluidstrom. Die Rückholbewegung des Schaltkolbens erfolgt durch die Last oder eine Rückstellfeder. Die Zylinder können beim Ausfahren eine Kraft erzeugen, die dem Produkt aus Zylindervollfläche und Systemdruck entspricht. Zur Systemdruckbegrenzung ist pumpenseitig ein Druckbegrenzungsventil vorgesehen, mit dem der Druck des einen Zylinders eingestellt werden kann. Soll der andere Zylinder mit einem anderen, kann. Soll der andere Zylinder mit einem anderen, niedrigeren Druck baaufschlagt werden, ist ein zusätzliches Druckbegrenzungsventil zwischen dem Wegeventil und diesem Zylinder notwendig. Es besteht aus einer Vielzahl von Teilen, durch welche die Ventilanordnung erheblich verteuert wird. Zudem wird durch dieses zusätzliche Druckbegrenzungsventil das Bauvolumen der Ventilanordnung wesentlich vergrößert.Such a valve arrangement is known, for example, to actuate cylinders operating in push-pull mode. The cylinder selection with fluid supply or fluid discharge is made via the solenoid-operated directional valve. The infeed movement is carried out by applying the fluid flow to the full cylinder surface. The return movement of the switching piston is carried out by the load or a return spring. When extended, the cylinders can generate a force that corresponds to the product of the full cylinder surface and system pressure. To limit the system pressure, a pressure relief valve is provided on the pump side, with which the pressure of one cylinder can be adjusted. Should the other cylinder be with another one, can. If the other cylinder is to be pressurized with a different, lower pressure, an additional pressure relief valve between the directional control valve and this cylinder is necessary. It consists of a large number of parts which make the valve arrangement considerably more expensive. In addition, this additional pressure relief valve increases the overall volume of the valve arrangement significantly enlarged.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäße Ventilanordnung so auszubilden, daß eine Druckbegrenzung mit minimalem Teileaufwand und ohne zusätzliches Bauvolumen kostengünstig erreicht werden kann.The invention has for its object to design the generic valve assembly so that a pressure limitation can be achieved inexpensively with minimal parts and without additional volume.

Diese Aufgabe wird bei der gattungsgemäßen Ventilanordnung erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This object is achieved according to the invention in the generic valve arrangement with the characterizing features of claim 1.

Bei der erfindungsgemäßen Ventilanordnung ist das Druckventil innerhalb des Bauvolumens des Wegeventils untergebracht. Durch eine geringfügige Modifizierung des Schaltkolbens des Wegeventils und Einbau des Ventilgliedes als einziges zusätzliches Bauteil entfällt das bei der bekannten Ventilanordnung erforderliche zusätzliche Druckventil und dessen Systemverbindung. Somit erfüllt die erfindungsgemäße Ventilanordnung die Voraussetzungen, die an ein derartiges Massenprodukt gestellt werden, nämlich geringes Bauvolumen, geringe Zahl von Bauteilen, geringe Störanfälligkeit und äußerst kostengünstige Fertigung.In the valve arrangement according to the invention, the pressure valve is accommodated within the construction volume of the directional valve. Due to a slight modification of the switching piston of the directional control valve and installation of the valve member as the only additional component, the additional pressure valve and its system connection required in the known valve arrangement are eliminated. Thus, the valve arrangement according to the invention fulfills the requirements that are placed on such a mass product, namely a small construction volume, a small number of components, low susceptibility to malfunction and extremely inexpensive production.

Weitere Merkmale der Erfindung ergeben sich aus den weiteren Ansprüchen, der Beschreibung und den Zeichnungen.Further features of the invention result from the further claims, the description and the drawings.

Die Erfindung wird nachstehend anhand einiger in den Zeichnungen dargestellter Ausführungsbeispiele näher erläutert.
Es zeigen

Fig. 1
im Schnitt eine erfindungsgemäße Ventilanordnung,
Fig. 2
in einem Diagramm eine Kraft-Weg-Kennlinie eines Magneten sowie eine Kraft-Weg-Kennlinie einer Rückstellfeder der erfindungsgemäßen Ventilanordnung gemäß Fig. 1,
Fig. 3
im Schnitt einen Teil einer zweiten Ausführungsform einer erfindungsgemäßen Ventilanordnung,
Fig. 4
weitere Ausführungsformen von erfindungsgemäßen Ventilanordnungen.
The invention is explained in more detail below with the aid of a few exemplary embodiments illustrated in the drawings.
Show it
Fig. 1
on average a valve arrangement according to the invention,
Fig. 2
1 shows a force-displacement characteristic curve of a magnet and a force-displacement characteristic curve of a return spring of the valve arrangement according to the invention according to FIG. 1,
Fig. 3
in section part of a second embodiment of a valve arrangement according to the invention,
Fig. 4
further embodiments of valve arrangements according to the invention.

Die Ventilanordnung gemäß Fig. 1 hat ein Wegeventil 1, das auf einer Anschlußplatte 2 befestigt ist. Das Wegeventil 1 weist einen Schaltkolben 3 auf, der in einer Bohrung 4 axial verschiebbar gelagert ist. Der Schaltkolben 3 hat Steuerkanten 5 bis 10.1 has a directional control valve 1 which is attached to a connecting plate 2. The directional control valve 1 has a switching piston 3, which is mounted axially displaceably in a bore 4. The switching piston 3 has control edges 5 to 10.

Die Anschlußplatte 2 ist mit einem Arbeitsanschluß A, einem Arbeitsanschluß B, einem Druckanschluß P und einem Rücklauf T zum Tank in bekannter Weise versehen. An die Arbeitsanschlüsse A und B ist jeweils ein Zylinder 12 und 13 angeschlossen. Im dargestellten Ausführungsbeispiel arbeiten diese beiden Zylinder 12, 13 im Gegentakt. Sie haben jeweils einen Kolben 14, 15, der jeweils mit Hydraulikmedium beaufschlagt wird. Die den Kolben 14, 15 tragende Kolbenstange 16, 17 steht unter der Kraft einer Druckfeder 18, 19, welche die Kolbenstange 16, 17 in Richtung auf ihre eingefahrene Stellung belastet. Mit dem Hydraulikmedium wird somit der entsprechende Kolben 14, 15 gegen die Kraft dieser Rückstellfeder 18, 19 verschoben.The connection plate 2 is provided with a working connection A, a working connection B, a pressure connection P and a return T to the tank in a known manner. A cylinder 12 and 13 is connected to the working ports A and B, respectively. In the illustrated embodiment, these two cylinders 12, 13 work in push-pull. They each have a piston 14, 15, each of which is acted upon by hydraulic medium. The piston rod 16, 17 carrying the piston 14, 15 is under the force of a compression spring 18, 19 which loads the piston rod 16, 17 in the direction of its retracted position. With the hydraulic medium, the corresponding piston 14, 15 is thus counter to the force of this return spring 18, 19 postponed.

An das Wegeventil 1 ist ein Magnet 20 angeschlossen, dessen Magnetstößel 21 mit dem benachbarten Ende des Schaltkolbens 3 zusammenwirkt. Wird der Magnet 20 eingeschaltet, dann wird in bekannter Weise der Magnetstößel 21 ausgefahren, so daß er den Schaltkolben 3 axial gegen die Kraft einer Rückstellfeder 22 in die gewünschte Schaltstellung verschiebt. Die Rückstellfeder 22 ist am anderen Ende des Schaltkolbens 3 vorgesehen und stützt sich mit einem Ende an einem Deckel 23 ab, der am Gehäuse des Wegeventiles 1 angeschraubt ist und die Bohrung 4 nach außen abdeckt. Mit ihrem anderen Ende stützt sich die Rückstellfeder 22 an einem Federteller 24 ab, der auf einem Zusatzkolben 25 sitzt, der axial verschiebbar in eine axiale Bohrung 26 des Schaltkolbens 3 ragt. Die Bohrung 26 ist etwa bis zur halben Länge des Schaltkolbens 3 geführt und mündet in eine Diametralbohrung 27, die den Schaltkolben 3 im Bereich zwischen den Steuerkanten 8 und 9 durchsetzt.A magnet 20 is connected to the directional control valve 1, the magnet plunger 21 of which cooperates with the adjacent end of the switching piston 3. If the magnet 20 is switched on, then the magnetic plunger 21 is extended in a known manner, so that it axially moves the switching piston 3 against the force of a return spring 22 into the desired switching position. The return spring 22 is provided at the other end of the switching piston 3 and is supported at one end on a cover 23 which is screwed onto the housing of the directional control valve 1 and covers the bore 4 to the outside. With its other end, the return spring 22 is supported on a spring plate 24 which is seated on an additional piston 25 which projects axially displaceably into an axial bore 26 of the switching piston 3. The bore 26 is guided to approximately half the length of the switching piston 3 and opens into a diametral bore 27 which passes through the switching piston 3 in the area between the control edges 8 and 9.

Nahe dem beim Federteller 24 liegenden Ende wird die Bohrung 26 von einer weiteren Diametralbohrung 28 gekreuzt, welche den Schaltkolben 3 im Bereich zwischen der Kante 11 und dem benachbarten Schaltkolbenende durchsetzt.Near the end lying at the spring plate 24, the bore 26 is crossed by a further diametral bore 28 which passes through the switching piston 3 in the area between the edge 11 and the adjacent switching piston end.

Das Wegeventil 1 hat eine parallel zum Schaltkolben 3 liegende Entlastungsbohrung 29, in die der Tankanschluß T mündet. Die Entlastungsbohrung 29 erstreckt sich zwischen zwei Räumen 30 und 31. Im Raum 31, der an einem Ende durch den Deckel 23 begrenzt ist, befindet sich der Federteller 24.The directional control valve 1 has a relief bore 29 lying parallel to the switching piston 3, into which the tank connection T opens. The relief bore 29 extends between two spaces 30 and 31. In the space 31, which is delimited at one end by the cover 23, there is the spring plate 24.

Die Anschlußplatte 2 hat Bohrungen 32 bis 35, welche mit den entsprechenden Anschlüssen A, B, P und T verbunden sind und an welche entsprechende Bohrungen 36 bis 39 des Wegeventils 1 angeschlossen sind. Die den Arbeitsanschlüssen A und B zugeordneten Bohrungen 36 und 38 des Wegeventils 1 münden jeweils in einen Ringraum 40 und 41 der Bohrung 4. Im Bereich zwischen den beiden Ringräumen 40 und 41 befindet sich ein im Durchmesser kleinerer Ringraum 42, in welchen die dem Druckanschluß P zugehörige Bohrung 37 mündet. Die dem Tankanschluß T zugeordnete Bohrung 39 schließlich mündet in einen Ringraum 43 der Bohrung 4, der gleichen Durchmesser wie der Ringraum 42 hat.The connection plate 2 has bores 32 to 35 which are connected to the corresponding connections A, B, P and T and to which corresponding bores 36 to 39 of the directional control valve 1 are connected. The holes 36 and 38 of the directional control valve 1 assigned to the working connections A and B each open into an annular space 40 and 41 of the bore 4. In the area between the two annular spaces 40 and 41 there is an annular space 42 with a smaller diameter in which the pressure connection P associated hole 37 opens. The bore 39 assigned to the tank connection T finally opens into an annular space 43 in the bore 4, which has the same diameter as the annular space 42.

In der in Fig. 1 dargestellten Lage ist der Zylinder 13 entlastet, das heißt, seine Druckfeder 19 hat die Kolbenstange 17 in ihre Ausgangslage eingeschoben. Der andere Zylinder 12 steht unter dem Druck des Hydraulikmediums, so daß dessen Kolben 14 gegen die Kraft der Feder 18 zurückgeschoben ist. Soll nun der andere Zylinder 13 mit Druck beaufschlagt werden, wird der Magnet 20 betätigt, so daß der Magnetstößel 21 in bekannter Weise gegen den Schaltkolben 3 axial verschoben wird. Sobald der Magnetstößel bzw. Magnetanker 20 seinen Vorhub VH ausgeführt hat, kommt er am freien Ende des Schaltkolbens 3 zur Anlage und verschiebt ihn beim anschließenden Arbeitshub in eine Schaltstellung, in der das Hydraulikmedium zum Zylinder 13 strömen kann. In diesem Falle strömt das Hydraulikmedium über den Druckanschluß P und die Bohrungen 33 und 37 in den Ringraum 42. Der Schaltkolben 3 ist dann in Fig. 1 so weit nach rechts verschoben, daß die Steuerkante 7 den Zutritt des Hydraulikmediums zum Ringraum 40 verschließt, während die Steuerkante 8 den Weg für das Hydraulikmedium zum Ringraum 41 freigibt. Dadurch kann das Hydraulikmedium vom Ringraum 42 in den Ringraum 41 und von dort über die Bohrungen 38 und 34 zum Arbeitsanschluß B gelangen. Der Kolben 15 wird dann vom Hydraulikmedium gegen die Kraft der Feder 19 verschoben. Gleichzeitig wird nunmehr der andere Zylinder 12 entlastet, so daß die Feder 18 den Kolben 14 in Fig. 1 nach rechts in seine Endlage verschieben kann.In the position shown in Fig. 1, the cylinder 13 is relieved, that is, its compression spring 19 has pushed the piston rod 17 into its initial position. The other cylinder 12 is under the pressure of the hydraulic medium, so that its piston 14 is pushed back against the force of the spring 18. If the other cylinder 13 is now to be pressurized, the magnet 20 is actuated so that the magnet plunger 21 is axially displaced against the switching piston 3 in a known manner. As soon as the magnetic plunger or armature 20 has performed its preliminary stroke VH, it comes to rest on the free end of the switching piston 3 and moves it during the subsequent working stroke into a switching position in which the hydraulic medium can flow to the cylinder 13. In this case, the hydraulic medium flows via the pressure connection P and the bores 33 and 37 into the annular space 42. The switching piston 3 is then displaced to the right in FIG. 1, that the control edge 7 closes the access of the hydraulic medium to the annular space 40, while the control edge 8 clears the way for the hydraulic medium to the annular space 41. As a result, the hydraulic medium can pass from the annular space 42 into the annular space 41 and from there via the bores 38 and 34 to the working connection B. The piston 15 is then moved by the hydraulic medium against the force of the spring 19. At the same time, the other cylinder 12 is now relieved, so that the spring 18 can move the piston 14 in FIG. 1 to the right into its end position.

Bei der Druckbeaufschlagung des Zylinders 13 gelangt das Hydraulikmedium außerdem in die Diametralbohrung 27 des Schaltkolbens 3. Diese Diametralbohrung 27 ist so angeordnet, daß sie sich noch im Bereich des Ringraumes 41 befindet. Das Hydraulikmedium strömt somit über diese Diametralbohrung 27 auch in die axiale Bohrung 26 des Schaltkolbens 3. Der in ihr gelagerte Zusatzkolben 25 steht somit unter dem Druck des Hydraulikmediums und der vom Magnetstößel 21 ausgeübten Kraft, die der Kraft der Rückstellfeder 22 entgegengerichtet ist. Der Magnetstößel 21 fährt gegen einen (nicht dargestellten) Endanschlag. Dann hat die Magnetkraft ihren größten Wert.When the cylinder 13 is pressurized, the hydraulic medium also enters the diametral bore 27 of the switching piston 3. This diametral bore 27 is arranged such that it is still in the region of the annular space 41. The hydraulic medium thus flows via this diametral bore 27 also into the axial bore 26 of the switching piston 3. The additional piston 25 mounted in it is thus under the pressure of the hydraulic medium and the force exerted by the magnetic tappet 21, which counteracts the force of the return spring 22. The magnetic plunger 21 moves against an end stop (not shown). Then the magnetic force has its greatest value.

Diese Verhältnisse sind in Fig. 2 im Magnetkraft-Weg-Diagramm durch eine gestrichelte Linie dargestellt. Am Punkt 44 kommt der Magnetstößel 21 nach beendetem Vorhub VH zur Anlage am Schaltkolben 3. Mit zunehmendem Verschiebeweg 46 des Magnetstößels 21 und damit des Schaltkolbens 3 nimmt die Magnetkraft zu. Am Punkt 45 erreicht der Magnetstößel 21 seinen Endanschlag, so daß nunmehr die Magnetkraft stark ansteigt. In Fig. 2 ist außerdem die Kraft-Weg-Kennlinie der Rückstellfeder 22 des Wegeventiles 1 dargestellt. Diese Kraft nimmt stetig zu, sobald der Magnetstößel 21 verschoben wird. Sobald der Magnetstößel 21 seine Endlage 45 erreicht hat und das Hydraulikmedium über den Druckanschluß P weiter zugeführt wird, wird der auf den Zusatzkolben 25 wirkende Druck größer als die Rückstellkraft, so daß er gegen die Kraft der Rückstellfeder 22 verschoben wird (Hub 47). Der Zusatzkolben 25 gibt damit die Diametralbohrung 28 des Schaltkolbens 3 frei, so daß das Hydraulikmedium nunmehr über die Bohrung 26 und die Diametralbohrung 28 in den Raum 31 und von dort über die Entlastungsbohrung 29 zur Bohrung 39 strömen kann, welche mit dem Tankanschluß T der Anschlußplatte 2 verbunden ist. Somit kann das Hydraulikmedium zum Tankanschluß strömen und den Hydraulikdruck begrenzen. Der Zusatzkolben 25 bildet somit in Verbindung mit der Diametralbohrung 28 ein Druckbegrenzungsventil 67, das einen unzulässig hohen Druckaufbau begrenzt. Dieses Druckbegrenzungsventil 67 ist innerhalb des Schaltkolbens 3 untergebracht, so daß es keinen zusätzlichen Platzbedarf hat. Insbesondere ist bei der beschriebenen Ventilanordnung ein zusätzliches Zwischenplattengerät nicht erforderlich, wie es bei der bekannten Ventilanordnung vorgesehen ist.These relationships are shown in Fig. 2 in the magnetic force-displacement diagram by a dashed line. At point 44, the magnetic plunger 21 comes into contact with the switching piston 3 after the preliminary stroke VH has ended. As the displacement 46 of the magnetic plunger 21 and thus the switching piston 3 increases, the magnetic force increases. At point 45, the magnetic plunger 21 reaches its end stop, so that now the magnetic force rises sharply. 2 also shows the force-displacement characteristic of the return spring 22 of the directional valve 1. This force increases steadily as soon as the magnetic plunger 21 is moved. As soon as the magnetic plunger 21 has reached its end position 45 and the hydraulic medium is supplied via the pressure connection P, the pressure acting on the additional piston 25 becomes greater than the restoring force, so that it is displaced against the force of the restoring spring 22 (stroke 47). The additional piston 25 thus releases the diametral bore 28 of the switching piston 3, so that the hydraulic medium can now flow through the bore 26 and the diametral bore 28 into the space 31 and from there via the relief bore 29 to the bore 39, which connects to the tank connection T of the connecting plate 2 is connected. This allows the hydraulic medium to flow to the tank connection and limit the hydraulic pressure. The additional piston 25 thus forms in connection with the diametral bore 28 a pressure relief valve 67 which limits an impermissibly high pressure build-up. This pressure relief valve 67 is housed within the switching piston 3, so that it has no additional space requirement. In particular, in the valve arrangement described, an additional intermediate plate device is not required, as is provided in the known valve arrangement.

Soll wiederum der Zylinder 12 beaufschlagt werden, wird der Magnet 20 abgeschaltet, so daß der Magnetstößel 21 unter der Kraft einer (nicht dargestellten) Rückstellfeder oder der Rückstellfeder 22 wieder in seine Ausgangslage zurückgefahren wird. Die Rückstellfeder 22 schiebt über den Federteller 24 den Zusatzkolben 25 wieder in die in Figur 1 dargestellte Sperrstellung zurück, in welcher der Zusatzkolben die Diametralbohrung 28 verschließt. Sobald der Federteller 24 am Schaltkolben 3 zur Anlage kommt, wird dieser unter der Kraft der Rückstellfeder 22 wieder in die in Figur 1 dargestellte andere Schaltstellung verschoben. Nunmehr ist die Verbindung vom Druckanschluß P zum Arbeitsanschluß B des Zylinders 13 geschlossen, während der Ringraum 40 mit dem Ringraum 42 in Verbindung steht. Das Hydraulikmedium kann darum vom Druckanschluß P über diese Ringräume in die Bohrungen 36 und 32 und damit zum Arbeitsanschluß A des Zylinders 12 gelangen. Sein Kolben 14 wird dann vom Hydraulikmedium gegen die Kraft der Rückstellfeder 18 in die in Fig. 1 dargestellte Druckstellung verschoben. Die Rückstellfeder 19 des anderen Zylinders 13 schiebt nunmehr den Kolben 15 in die in Fig. 1 dargestellte Entlastungsstellung. Das nicht mehr unter Druck stehende Hydraulikmedium wird dann über den Arbeitsanschluß B und die Bohrungen 34, 38 vom Ringraum 41 in den Ringraum 43 und von dort über die Bohrungen 39, 35 zum Tankanschluß T verdrängt.If the cylinder 12 is to be acted upon again, the magnet 20 is switched off, so that the magnetic plunger 21 is moved back into its starting position under the force of a return spring (not shown) or the return spring 22. The return spring 22 pushes the additional piston 25 back into the in via the spring plate 24 Figure 1 shown locking position back, in which the additional piston closes the diametral bore 28. As soon as the spring plate 24 comes into contact with the switching piston 3, it is moved again into the other switching position shown in FIG. 1 under the force of the return spring 22. Now the connection from the pressure port P to the working port B of the cylinder 13 is closed, while the annular space 40 is in communication with the annular space 42. The hydraulic medium can therefore pass from the pressure connection P via these annular spaces into the bores 36 and 32 and thus to the working connection A of the cylinder 12. Its piston 14 is then moved by the hydraulic medium against the force of the return spring 18 into the pressure position shown in FIG. 1. The return spring 19 of the other cylinder 13 now pushes the piston 15 into the relief position shown in FIG. 1. The hydraulic medium which is no longer under pressure is then displaced from the annular space 41 into the annular space 43 via the working connection B and the bores 34, 38 and from there via the bores 39, 35 to the tank connection T.

Aus Fig. 2 ergibt sich, daß der Arbeitshub 46 des Schaltkolbens 3 zwischen den Anschlagpunkten 44 und 45 des Magnetstößels 21 liegt. An den Arbeitshub 46 schließt der Öffnungshub 47 des Zusatzkolbens 25 an. Dieser Öffnungshub stellt sicher, daß der auf den Kolben 15 des Zylinders 13 wirkende Hydraulikdruck nicht unzulässig hohe Werte annimmt, sondern auf einen vorgegebenen Wert begrenzt ist. Die Höhe dieses Druckes kann durch die Rückstellkraft der Feder 22 eingestellt werden. Beispielsweise kann der Deckel 23 mit einem (nicht dargestellten) Gewindeteil versehen sein, an dem sich die Rückstellfeder 22 abstützt. Durch mehr oder weniger weites Einschrauben dieses Gewindeteiles in den Deckel 23 läßt sich dann die Kraft der Rückstellfeder 22 feinfühlig einstellen. Dadurch kann die Ventilanordnung einfach und genau an die unterschiedlichsten Anwendungsfälle angepaßt werden. Es ist dadurch möglich, den jeweils zulässigen Maximaldruck exakt einzustellen.From Fig. 2 it follows that the working stroke 46 of the switching piston 3 is between the stop points 44 and 45 of the magnetic plunger 21. The opening stroke 47 of the additional piston 25 connects to the working stroke 46. This opening stroke ensures that the hydraulic pressure acting on the piston 15 of the cylinder 13 does not assume impermissibly high values, but is limited to a predetermined value. The level of this pressure can be adjusted by the restoring force of the spring 22. For example, the cover 23 can be provided with a threaded part (not shown) on which the Return spring 22 is supported. By screwing this threaded part into the cover 23 to a greater or lesser extent, the force of the return spring 22 can then be adjusted sensitively. As a result, the valve arrangement can be easily and precisely adapted to the most varied of applications. This makes it possible to set the maximum allowable pressure exactly.

Beim Ausführungsbeispiel nach Fig. 3 ist der Zusatzkolben 25a ebenfalls in der Bohrung des Schaltkolbens 3a gelagert, dessen benachbart zum Deckel 23a des Wegeventils 1a liegendes Ende durch ein Adapterstück 48 gebildet ist. Durch das Adapterstück 48 ergibt sich der Vorteil, daß der Durchmesser des Zusatzkolbens 25a nicht abhängig von den Dimensionen des Schaltkolbens 3a ist. Der Schaltkolben 3a hat benachbart zum Adapterstück 48 eine Ringnut 49, in die das Adapterstück 48 mit einem umgebördelten Rand 50 eingreift. Das Adapterstück 48 hat einen Buchsenteil 51, mit dem er auf dem Ende eines Grundkörpers 68 des Schaltkolbens 3a sitzt und dessen freie Stirnseite umgebördelt ist. Der Boden 52 des Buchsenteiles 51 liegt flächig an der Stirnseite 53 des Grundkörpers 68 an. An den Buchsenteil 51 schließt ein Ansatz 54 an, der vorteilhaft einstückig mit dem Buchsenteil 51 ausgebildet ist und dessen Außendurchmesser kleiner ist als der Außendurchmesser des Buchsenteiles 51 und vorzugsweise auch kleiner als der Außendurchmesser des Grundkörpers 68. Der Ansatz 54 dient als Lagerung und Führung für den Zusatzkolben 25a und damit für den Federteller 24a, an dem sich ein Ende der Rückstellfeder 22a für den Schaltkolben 3a abstützt. Mit ihrem anderen Ende liegt die Rückstellfeder 22a wiederum am Deckel 23a an.In the exemplary embodiment according to FIG. 3, the additional piston 25a is also mounted in the bore of the switching piston 3a, the end of which is adjacent to the cover 23a of the directional control valve 1a is formed by an adapter piece 48. The adapter piece 48 has the advantage that the diameter of the additional piston 25a is not dependent on the dimensions of the switching piston 3a. The switching piston 3a has an annular groove 49 adjacent to the adapter piece 48, into which the adapter piece 48 engages with a flanged edge 50. The adapter piece 48 has a socket part 51 with which it sits on the end of a base body 68 of the switching piston 3a and the free end face of which is flanged. The bottom 52 of the socket part 51 lies flat against the end face 53 of the base body 68. The socket part 51 is followed by an extension 54, which is advantageously formed in one piece with the socket part 51 and whose outer diameter is smaller than the outer diameter of the socket part 51 and preferably also smaller than the outer diameter of the base body 68. The extension 54 serves as a bearing and guide for the additional piston 25a and thus for the spring plate 24a, on which one end of the return spring 22a is supported for the switching piston 3a. With its other end, the return spring 22a in turn rests on the cover 23a.

Der Ansatz 54 wird von einer Längsbohrung 55 zentrisch durchsetzt, die auch den Boden 52 des Buchsenteiles 51 durchsetzt. Die axiale Längsbohrung 55 fluchtet mit der Bohrung 26a des Grundkörpers 68, bildet also eine Fortsetzung dieser Bohrung 26a. In der Längsbohrung 55 ist der Zusatzkolben 25a axial verschiebbar gelagert. Die Längsbohrung 55 durchsetzt eine Diametralbohrung 56, welche den Ansatz 54 des Adapterstücks 48 durchsetzt. Somit steht die Bohrung 26a des Grundkörpers 68 über die Längsbohrung 55 und die Diametralbohrung 56 des Adapterstücks 48 mit dem Raum 31a in Verbindung.The approach 54 is centrally penetrated by a longitudinal bore 55, which also penetrates the bottom 52 of the socket part 51. The axial longitudinal bore 55 is aligned with the bore 26a of the base body 68, thus forming a continuation of this bore 26a. The additional piston 25a is mounted axially displaceably in the longitudinal bore 55. The longitudinal bore 55 penetrates a diametral bore 56 which penetrates the shoulder 54 of the adapter piece 48. The bore 26a of the base body 68 is thus connected to the space 31a via the longitudinal bore 55 and the diametral bore 56 of the adapter piece 48.

Der Federteller 24a ist als Hülse ausgebildet, die einen Boden 57 aufweist. Sie wird von einer zentrischen Bohrung 58 durchsetzt, in welcher der Zusatzkolben 25a axial festgehalten ist.The spring plate 24a is designed as a sleeve which has a bottom 57. It is penetrated by a central bore 58, in which the additional piston 25a is held axially.

Das vom Boden 57 abgewandte Ende des Federtellers 24a ist mit einer in Richtung auf den Boden 52 des Buchsenteiles 51 sich öffnenden Kegelfläche 59 versehen, die zusammen mit der gegenüberliegenden Unterseite des Bodens 52 des Buchsenteiles 51 einen schräg nach außen sich verjüngenden Durchflußbereich 60 für das Hydraulikmedium bildet.The end of the spring plate 24a facing away from the bottom 57 is provided with a conical surface 59 opening towards the bottom 52 of the socket part 51, which together with the opposite underside of the bottom 52 of the socket part 51 has an obliquely outwardly tapering flow area 60 for the hydraulic medium forms.

Der Federteller 24a umgibt mit geringem radialem Spiel 61 den Ansatz 54 des Adapterstückes 48. Bei der Relativverschiebung zwischen dem Federteller 24a und dem Adapterstück 48 wird ein Raum 62 zwischen dem Boden 57 des Federtellers 24a und der Stirnseite des Ansatzes 54 gebildet, dessen Volumen sich in Abhängigkeit vom Hub des Zusatzkolbens 25a ändert. Dieser Raum 62 ist über den Ringspalt 61 mit dem Tankanschluß T verbunden. In dem Ringraum 61 kann das Hydraulikmedium nur mit Druckgefälle durchströmen. Dadurch wird eine hervorragende Dämpfung des Zusatzkolbens 25a gewährleistet, der dadurch im Betrieb der Ventilanordnung nicht in Schwingungen geraten kann. Diese Ventilanordnung zeichnet sich darum durch eine sehr hohe Geräuschdämpfung aus. Auch treten infolge der Dämpfung des Zusatzkolbens 25a keine Druckpulsationen auf.The spring plate 24a surrounds the shoulder 54 of the adapter piece 48 with a slight radial play 61. In the case of the relative displacement between the spring plate 24a and the adapter piece 48, a space 62 is formed between the bottom 57 of the spring plate 24a and the end face of the shoulder 54, the volume of which is in Dependence on the stroke of the additional piston 25a changes. This space 62 is connected to the tank connection T via the annular gap 61. In the annular space 61, the hydraulic medium can only flow through with a pressure gradient. This ensures excellent damping of the additional piston 25a, which, as a result, cannot oscillate during operation of the valve arrangement. This valve arrangement is therefore characterized by a very high level of noise damping. Also, no pressure pulsations occur due to the damping of the additional piston 25a.

Die Ventilanordnung gemäß Fig. 3 ist im übrigen gleich ausgebildet wie das Ausführungsbeispiel gemäß Fig. 1. Auch die Arbeitsweise dieser Ventilanordnung ist grundsätzlich gleich wie beim vorigen Ausführungsbeispiel. Kommt der Magnetstößel 21 des Magnetes 20 in Anschlagstellung am Anschlag des Magneten, dann wird der Zusatzkolben 25a durch das Hydraulikmedium anschließend gegen die Kraft der Rückstellfeder 22a in der Bohrung 55 des Adapterstücks 48 verschoben, wodurch die Diametralbohrung 56 freigegeben wird. Das Hydraulikmedium kann dann in der beschriebenen Weise über die Diametralbohrung 27 (Fig. 1) des Schaltkolbens 3a, die Bohrungen 26a und 55 in die Diametralbohrung 56 strömen. Dort gelangt das Hydraulikmedium in den Raum 31a, in welchen die Entlastungsbohrung 29a mündet. Auf diese Weise kann der Druck in der Anschlagstellung des Magnetstößels 21 begrenzt werden, da das Hydraulikmedium in der beschriebenen Weise über die Entlastungsbohrung 29a zum Tankanschluß T strömen kann. Wird dabei die Kegelfläche 59 angeströmt, wird eine gegen die Kraft der Rückstellfeder 22a zusätzlich wirkende Gegenkraft erzeugt, durch welche der Zusatzkolben 25a weiter in seine Öffnungsstellung verschoben wird, ohne daß ein Druckanstieg im Hydrauliksystem erforderlich ist.The valve arrangement according to FIG. 3 is otherwise of the same design as the exemplary embodiment according to FIG. 1. The mode of operation of this valve arrangement is basically the same as in the previous exemplary embodiment. If the magnet plunger 21 of the magnet 20 comes into the stop position at the stop of the magnet, the additional piston 25a is then displaced by the hydraulic medium against the force of the return spring 22a in the bore 55 of the adapter piece 48, whereby the diametral bore 56 is released. The hydraulic medium can then flow in the manner described via the diametral bore 27 (FIG. 1) of the switching piston 3a, the bores 26a and 55 into the diametral bore 56. There, the hydraulic medium enters the space 31a, in which the relief bore 29a opens. In this way, the pressure in the stop position of the magnetic plunger 21 can be limited, since the hydraulic medium can flow in the manner described via the relief bore 29a to the tank connection T. If the conical surface 59 is flowed against, an additional counterforce acting against the force of the return spring 22a is generated, by which the additional piston 25a is moved further into its open position without an increase in pressure in the hydraulic system being necessary.

Das Ausführungsbeispiel gemäß Fig. 3 zeichnet sich wiederum durch seine einfache konstruktive Ausbildung aus. Der Zusatzkolben 25a in Verbindung mit der Diametralbohrung 56 bildet wiederum ein Druckbegrenzungsventil 67a, das innerhalb des Bauraumes des Wegeventiles 1a untergebracht ist. Dadurch hat diese Ventilanordnung - wie auch die Ausführungsform nach Fig. 1 - nur einen sehr geringen Platzbedarf und kann nunmehr auch dort eingesetzt werden, wo enge Platzverhältnisse herrschen bzw. das Bauvolumen nicht überschritten werden kann. Zudem zeichnet sich diese Ventilanordnung durch die beschriebene hohe Dämpfung des Zusatzkolbens 25a und der damit verbundenen hohen Geräuschdämpfung, der Verringerung der Druckpulsationen und den extrem geringen Zusatzkosten für das Druckbegrenzungsventil aus.The embodiment according to FIG. 3 is again characterized by its simple construction. The additional piston 25a in connection with the diametral bore 56 in turn forms a pressure relief valve 67a, which is accommodated within the installation space of the directional control valve 1a. As a result, this valve arrangement - like the embodiment according to FIG. 1 - takes up very little space and can now also be used where space is tight or the construction volume cannot be exceeded. In addition, this valve arrangement is characterized by the described high damping of the additional piston 25a and the associated high noise damping, the reduction of the pressure pulsations and the extremely low additional costs for the pressure limiting valve.

Bei den Ausführungsbeispielen nach den Fig. 1 und 3 kann anstelle der Diametralbohrungen 28 und 56 auch ein Ringkanal vorgesehen sein. Eine solche Ausbildung hat im Gegensatz zu den radial verlaufenden Bohrungen den Vorteil, daß die Durchflußverstärkung wesentlich größer sein kann als bei radialen Bohrungen. Der Zusatzkolben 25, 25a kann bei den Ausführungsformen gemäß den Fig. 1 und 3 eine einfache und kostengünstige Lagernadel sein.In the exemplary embodiments according to FIGS. 1 and 3, an annular channel can also be provided instead of the diametrical bores 28 and 56. In contrast to the radially running bores, such a design has the advantage that the flow gain can be substantially greater than with radial bores. The additional piston 25, 25a can be a simple and inexpensive bearing needle in the embodiments according to FIGS. 1 and 3.

Fig. 4 zeigt zwei Ausführungsformen von Ventilgliedern, die anstelle des Zusatzkolbens für das Druckbegrenzungsventil eingesetzt werden können. In der oberen Hälfte der Fig. 4 ist das Ventilglied 25b als Kugel ausgebildet, auf der sich der Federteller 24b für die Rückstellfeder 22b abstützt. Die Kugel 25b verschließt die Bohrung 26b des Schaltkolbens 3b.Fig. 4 shows two embodiments of valve members that can be used instead of the additional piston for the pressure relief valve. In the top half 4, the valve member 25b is designed as a ball, on which the spring plate 24b for the return spring 22b is supported. The ball 25b closes the bore 26b of the switching piston 3b.

In der unteren Hälfte der Fig. 4 ist das Ventilglied als Kegel 25c ausgebildet. Er ist vorteilhaft einstückig mit dem Federteller 24c für die Rückstellfeder ausgebildet.In the lower half of FIG. 4, the valve member is designed as a cone 25c. It is advantageously formed in one piece with the spring plate 24c for the return spring.

Diese Ventilglieder 25b, 25c geben bei Überschreiten der durch die Rückstellfeder erzeugten Kraft die Bohrung 26b des Schaltkolbens 3b frei, so daß das Hydraulikmedium in der beschriebenen Weise über den Raum 31a und die Entlastungsbohrung 29a zum Tankanschluß T abfließen kann.These valve members 25b, 25c release the bore 26b of the switching piston 3b when the force generated by the return spring is exceeded, so that the hydraulic medium can flow out via the space 31a and the relief bore 29a to the tank connection T in the manner described.

Durch entsprechende Dimensionierung des Ringspaltes 61b, 61c zwischen dem Federteller 24b, 24c und der Bohrungswandung des Deckels 23b, 23c kann auch bei dieser Ausführungsform die anhand der Fig. 3 beschriebene Dämpfung erreicht werden.By appropriate dimensioning of the annular gap 61b, 61c between the spring plate 24b, 24c and the bore wall of the cover 23b, 23c, the damping described with reference to FIG. 3 can also be achieved in this embodiment.

Claims (14)

Ventilanordnung mit einem Wegeventil, dessen Schaltkolben durch einen Stößel eines Magneten gegen eine Rückstellkraft verschiebbar ist und mit einem Druckventil, das ein Ventilglied aufweist, das gegen eine Rückstellkraft verstellbar ist,
dadurch gekennzeichnet, daß am Schaltkolben (3, 3a, 3b) des Wegeventils (1, 1a, 1b) das Ventilglied (25, 25a, 25b) des Druckventils (67,67a, 67b) angeordnet ist.Valve arrangement with a directional control valve, the switching piston of which can be displaced against a restoring force by a plunger of a magnet and with a pressure valve which has a valve member which can be adjusted against a restoring force,
characterized in that the valve member (25, 25a, 25b) of the pressure valve (67, 67a, 67b) is arranged on the switching piston (3, 3a, 3b) of the directional valve (1, 1a, 1b). Ventilanordnung nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilglied (25, 25a, 25b) des Druckventils ( 67, 67a, 67b) bei Überschreiten eines vorgegebenen Hydraulikdruckes gegen eine Rückstellkraft zur Öffnung eines Durchflußquerschnittes (28, 56, 56b) zum Tank relativ zum Schaltkolben (3, 3a, 3b) verstellbar ist.Valve arrangement according to claim 1, characterized in that the valve member (25, 25a, 25b) of the pressure valve (67, 67a, 67b) when a predetermined hydraulic pressure is exceeded against a restoring force to open a flow cross-section (28, 56, 56b) relative to the tank Switching piston (3, 3a, 3b) is adjustable. Ventilanordnung nach Anspruch 1 oder 2,, dadurch gekennzeichnet, daß das Ventilglied (25, 25a, 25b) ein in einer Bohrung (26; 26a, 55; 26b, 55b) des Schaltkolbens (3, 3a, 3b) verschiebbarer Kolben ist.Valve arrangement according to claim 1 or 2, characterized in that the valve member (25, 25a, 25b) is a piston which is displaceable in a bore (26; 26a, 55; 26b, 55b) of the switching piston (3, 3a, 3b). Ventilanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Ventilglied (25, 25a, 25b) ein mit einer Bohrung (26; 26a, 55; 26b, 55b) des Schaltkolbens (3, 3a, 3b) zusammenwirkender Ventilkörper, wie eine Kugel, ein Kegel und dgl., ist.Valve arrangement according to Claim 1 or 2, characterized in that the valve member (25, 25a, 25b) is a valve body, such as a ball, which interacts with a bore (26; 26a, 55; 26b, 55b) of the switching piston (3, 3a, 3b) , a cone and the like. Ventilanordnung nach Anspruch 4, dadurch gekennzeichnet, daß die Bohrung (26; 26a, 55; 26b, 55b) des Schaltkolbens (3, 3a, 3b) einen endseitigen Ventilsitz für den Ventilkörper (25, 25a, 25b) aufweist.Valve arrangement according to claim 4, characterized in that the bore (26; 26a, 55; 26b, 55b) of the switching piston (3, 3a, 3b) has an end valve seat for the valve body (25, 25a, 25b). Ventilanordnung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Schaltkolben (3) mindestens eine Querbohrung (28), vorzugsweise eine Diametralbohrung, aufweist, die den Durchflußquerschnitt für das Hydraulikmedium bildet.Valve arrangement according to one of claims 1 to 4, characterized in that the switching piston (3) has at least one transverse bore (28), preferably a diametral bore, which forms the flow cross section for the hydraulic medium. Ventilanordnung nach einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, daß die axial verlaufende Bohrung (26) über eine weitere Diametralbohrung (27) mit einem der Anschlüsse (A, B, P) der Ventilanordnung verbunden ist und in die Querbohrung (28) mündet.Valve arrangement according to one of claims 3 to 6, characterized in that the axially extending bore (26) is connected via a further diametral bore (27) to one of the connections (A, B, P) of the valve arrangement and opens into the transverse bore (28) . Ventilanordnung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß auf dem Ventilglied (25, 25a, 25b) ein Federteller (24, 24a, 24b) für eine Rückstellfeder (22, 22a, 22b) sitzt.Valve arrangement according to one of claims 1 to 7, characterized in that a spring plate (24, 24a, 24b) for a return spring (22, 22a, 22b) is seated on the valve member (25, 25a, 25b). Ventilanordnung nach Anspruch 8, dadurch gekennzeichnet, daß der Federteller (24, 24a, 24b) in einem mit dem Tankanschluß (T) verbundenen Raum (31, 31a, 31b) der Ventilanordnung vorgesehen ist.Valve arrangement according to claim 8, characterized in that the spring plate (24, 24a, 24b) is provided in a space (31, 31a, 31b) of the valve arrangement which is connected to the tank connection (T). Ventilanordnung nach einem der Ansprüche 1 und 3, 6 bis 9, dadurch gekennzeichnet, daß das eine Ende des Schaltkolbens (3a, 3b) durch ein Adapterstück (48, 48b) gebildet ist, in dem der Kolben (25a, 25b) des Druckventils (67a, 67b) axial verschiebbar angeordnet ist.Valve arrangement according to one of claims 1 and 3, 6 to 9, characterized in that the one end of the switching piston (3a, 3b) is formed by an adapter piece (48, 48b) in which the piston (25a, 25b) of the Pressure valve (67a, 67b) is arranged axially displaceable. Ventilanordnung nach Anspruch 10, dadurch gekennzeichnet, daß das Adapterstück (48, 48b) als Durchflußquerschnitt mindestens eine Querbohrung (56, 56b), vorzugsweise eine Diametralbohrung, aufweist.Valve arrangement according to Claim 10, characterized in that the adapter piece (48, 48b) has at least one transverse bore (56, 56b), preferably a diametral bore, as the flow cross section. Ventilanordnung nach Anspruch 10 oder 11, dadurch gekennzeichnet, daß der Federteller (24a, 24b) über den Kolben (25a, 25b) des Druckventils (67a, 67b) am Adapterstück (48, 48b) verschiebbar gelagert ist und mit geringem Abstand (61) das Adapterstück (48, 48b) umgibt.Valve arrangement according to claim 10 or 11, characterized in that the spring plate (24a, 24b) is displaceably mounted on the adapter piece (48, 48b) via the piston (25a, 25b) of the pressure valve (67a, 67b) and at a small distance (61) surrounds the adapter piece (48, 48b). Ventilanordnung nach Anspruch 12, dadurch gekennzeichnet, daß bei der Relativverschiebung zwischen dem Federteller (24a, 24b) und dem Adapterstück (48, 48b) ein über den Ringspalt (61) mit dem Tankanschluß (T) verbundener Dämpfungsraum (62) gebildet wird.Valve arrangement according to claim 12, characterized in that during the relative displacement between the spring plate (24a, 24b) and the adapter piece (48, 48b) a damping space (62) is formed which is connected to the tank connection (T) via the annular gap (61). Ventilanordnung nach Anspruch 12 oder 13,
dadurch gekennzeichnet, daß der Federteller (24a, 24b) an seinem dem Schaltkolben (3a, 3b) zugewandten Ende eine Kegelfläche (59, 59b) aufweist, die im angeströmten Zustand bei verschobenem Ventilglied (25a, 25b) eine gegen die auf den Federteller (24a, 24b) wirkende Rückstellkraft gerichtete Gegenkraft erzeugt.Valve arrangement according to claim 12 or 13,
characterized in that the spring plate (24a, 24b) has at its end facing the switching piston (3a, 3b) a conical surface (59, 59b) which, when the valve element (25a, 25b) is displaced, moves one against the spring plate (25a, 25b). 24a, 24b) acting restoring force produces directed counterforce.
EP19930105594 1992-04-15 1993-04-05 Valve arrangement Expired - Lifetime EP0565982B1 (en)

Applications Claiming Priority (2)

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DE19924212550 DE4212550C2 (en) 1992-04-15 1992-04-15 Valve arrangement with a directional valve
DE4212550 1992-04-15

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Also Published As

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EP0565982B1 (en) 1997-07-09
US5417241A (en) 1995-05-23
DE59306854D1 (en) 1997-08-14
DE4212550A1 (en) 1993-10-21
DE4212550C2 (en) 1998-12-10

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