EP0549628B1 - Control device for hydraulic piston/cylinder unit - Google Patents

Control device for hydraulic piston/cylinder unit Download PDF

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Publication number
EP0549628B1
EP0549628B1 EP91915901A EP91915901A EP0549628B1 EP 0549628 B1 EP0549628 B1 EP 0549628B1 EP 91915901 A EP91915901 A EP 91915901A EP 91915901 A EP91915901 A EP 91915901A EP 0549628 B1 EP0549628 B1 EP 0549628B1
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EP
European Patent Office
Prior art keywords
valve
bore
valve body
appliance according
pilot control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91915901A
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German (de)
French (fr)
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EP0549628A1 (en
Inventor
Hartmut Sandau
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot 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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • 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

Definitions

  • the invention is based on a control device with a proportional control valve according to the preamble of claim 1.
  • a proportional control valve according to the preamble of claim 1.
  • an electromagnetically pilot-controlled proportional control valve which has a pilot valve element actuated by a proportional magnet.
  • This pilot valve member controls the pressure in a pressure chamber arranged between the valve body of the proportional control valve and its valve housing, by the action of which the valve body is pressed against the valve seat.
  • Proportional control valves of this type have the disadvantage that the controlled or regulated pressure medium flow is subject to strong fluctuations since, in particular, the fine controllability is not sufficient for applications in which a high control quality is required. Due to the poor fine controllability of these proportional control valves, neither high control stabilities nor continuous pressure medium flows can be set.
  • the control device according to the invention with the characterizing features of claim 1 has the advantage that a short, finely controllable outflow of the pressure medium is made possible with short actuation paths for the proportional control valve and low actuation forces.
  • a stable course of the valve characteristic curve is also achieved over a large range.
  • This high control stability of the valve leads to a low-vibration mode of operation, which also reduces snarling and whistling noises.
  • the device according to the invention is particularly suitable as a so-called lowering brake valve, in which the pressure medium flowing back from the consumer (hydraulic cylinder) is throttled, so that - as mentioned at the beginning - the load does not advance or "jerky".
  • 10A denotes an approximately cup-shaped valve housing of a proportional control valve 10, which with its open end face 11 bears against a housing 12 of a proportional magnet 13.
  • Two circumferential annular grooves 15, 16 are formed in the interior of the valve housing.
  • the annular groove 15 is connected via a bore 18 and a pressure medium supplying connection 19 to a pressure medium source, and the annular groove 16 is connected via a bore 20 to a connection 21 leading to a consumer and discharging pressure medium.
  • a cylindrical bushing 23 is inserted into the valve housing 10A and fixed in the housing with a locking nut 24 with an external thread 25.
  • the valve housing has a corresponding internal thread 26 in the region of its end face 11, which starts from a cylindrical recess 27 on the end face, into which a sealing ring 28 is inserted. This seal seals the connection of the valve housing to the proportional solenoid from the outside.
  • Axially through the bushing 23 are two bores 30, 31 which merge into one another, of which the bore 31 facing the end face 11 has the smaller diameter.
  • annular groove 32 is formed in the region of the transition to the bore 31, which is connected via transverse bores 33, 34 to an annular channel 36 formed by the annular groove 15 and the bushing 23.
  • the bore 31 is penetrated by a transverse bore 37 formed in the bushing 23, which connects the bore 31 to an annular channel 38 formed by the annular groove 16 and the bushing 23.
  • a valve body 40 is guided in a tightly sliding manner in the bore 30 of the bushing 23. This interacts with a valve seat 41 formed at the transition of the bore 30 into the bore 31.
  • the valve body 40 is formed in the region of the valve seat 41 as a flat cone 42 which merges into a fine control cone 43.
  • the transition 44 from the cone to the fine control cone is not designed in the form of an edge, but as a concave curve.
  • the valve body 40 is penetrated by three merging bores 45, 46, 47 which merge into one another.
  • the bore 47 opening at the fine control cone 43 has the smallest diameter
  • the bore 45 opening at the opposite end face has the largest diameter.
  • the valve body is closed on one side by a screw 49 on the end face opposite the fine control cone.
  • the threaded part 50 of the screw projects into the bore 46, which has an internal thread over a corresponding part of its length.
  • the screw head 52 lies against the end face of the valve body in such a way that an annular channel 54 is created through the bore 45 and the screw 49.
  • an annular groove 55 is formed, into which a sealing ring 56 is inserted, which seals the annular channel 54 against the bore 46.
  • a blind bore 57 is made on the side facing away from the valve body, from the bottom of which a throttle bore 58 extends, which opens into the annular channel 54.
  • the ring channel 54 is connected via the bores 57, 58 to a pressure chamber 60 formed between the bottom of the housing 10A and the valve body 40.
  • two blind bores 61, 62 which extend from the outer circumference and are arranged in the area of the annular groove 32, run radially.
  • a throttle bore 63, 64 which both open into the bore 47, extends from the bottom thereof.
  • the bore 61 has an internal thread 65 in the region of the outer circumference of the valve body, into which a screwing throttle 66 is inserted.
  • the bore 62 is closed in the region of the outer circumference of the valve body by a plug 68.
  • the blind hole 61 is connected to the annular channel 54 via a longitudinal channel 67 and the blind hole 62 via a longitudinal channel 70.
  • the bore 47 is penetrated by a third radially extending blind bore 69, which likewise extends from the outer circumference of the valve body and is closed there by a stopper 59 (see FIG. 2).
  • a pilot valve 71 In the bore 47, a pilot valve 71 is guided in a tightly sliding manner. It projects on one side with a conically expanded valve cone 72 into the bore 46 and interacts there with a valve seat 73 formed at the transition from the bore 46 into the bore 47.
  • the pilot spool protrudes into a hexagonal opening 74 of the locking nut 24 and interacts there with an actuating plunger 75 projecting into the opening 74 from the proportional magnet 13.
  • the pilot spool 71 penetrates the bottom of a pot-shaped spring guide element 78 which projects into the bore 31 and abuts the front side of the bush 23 with a ring-shaped edge 79.
  • the spring guide element 78 is fixed in position by the lock nut 24.
  • this has an annular groove 80, the diameter of which corresponds to that of the collar-shaped edge 79.
  • the spring guide element 78 can also be fixed in the radial direction by the edges of the opening 74; for this purpose the outer circumference of the edge 79 should then correspond to the inner circle diameter of the hexagonal opening 74.
  • One end of a compression spring 82 is supported on the inside of the spring guide element 78, the other end of which rests on a disk 83 pushed over the pilot valve 71. This disc is secured against being pushed off by a locking ring 85 which is fitted into an annular groove 84 at the end of the pilot spool.
  • the pilot spool 71 is penetrated by a transverse bore 87.
  • a longitudinal blind bore 88 which starts from the pilot valve cone 72, opens into this transverse bore.
  • Two annular grooves 90, 91 are formed on the outer circumference of the pilot valve, between which a narrow collar 92 remains. This closes the throttle bores 63, 64 when the pilot valve cone 72 bears against the valve seat 73.
  • the annular groove 90 extends from the collar 92 to the valve cone 72, which starts from the bottom of this groove.
  • two annular channels 94, 95 are formed, which in each of the blind bore 69 Working position of the spool are connected.
  • the diameter of the blind bore 69 is so large that the two ring channels are connected even when the pilot spool is lifted.
  • the proportional control valve 10 is closed when the proportional magnet 13 is not energized. Due to the action of the compression spring 82, the valve cone 72 of the pilot valve 71 is pulled to its seat 73 and thus also the valve body 40 against its seat 41. At the same time, the collar 92 closes the throttle bores 63, 64.
  • the pressure medium connection 19 is connected to the screw-in throttle 66 via the bore 18, the annular channel 36 and the bores 33, 34 and the annular groove 32. From there, pressure medium reaches the annular space 54 via the longitudinal channel 67 and from there via the throttle bore 58 and the bore 57 into the pressure space 60. At the same time, there is a connection from the annular channel 54 to the bore 62 via the longitudinal channel 70.
  • the outlet side is through the valve body on one side closed bore 31 via the bore 37, the annular channel 38 and the bore 20 with the pressure medium connection 21 in connection. Since the end face A S of the valve body acted upon by pressure medium - corresponding to the area of the bore 30 - is larger than the annular area A R - corresponding to the area difference between the bore 30 and 31, the valve body is additionally pressed against its seat 41. The leakage losses in the closed position of the check valve are very low due to the seat valves used and the long sliding guide of the pilot spool 71 in the bore 47.
  • the pilot valve 71 moves to the left through the plunger 75 of the proportional magnet 13, so that the pilot valve cone 72 lifts off its valve seat 73 and the throttle bores 63, 64 previously closed on one side by the collar 92 are opened.
  • pressure medium flows from the inlet-side connection bore 19, as previously described, to the bores 61, 62 and from there via the throttle bores 63, 64 into the ring channel 95 From there, the pressure medium passes through the opened valve seat 73 into the bore 46 which is closed on one side.
  • the bore 46 is connected to the bore 31 via the longitudinal bore 88 and the transverse bore 87 in the valve slide 71, which bore, as described above, is connected to the outlet end Pressure medium connection 21 is.
  • the pressure in the bore 61 and thus also in the pressure chamber 60 drops. If the pressure in the pressure chamber 60 falls so far that the pressure forces on the opposite valve body face ( Ring area A R ) predominate, the valve body 40 moves to the left. Pressure medium then flows out of the annular groove 32 past the opened valve seat 41 into the bore 31 and from there to the pressure medium connection 21. If the pilot valve 71 follows the plunger 75 due to the action of the spring 82 with a corresponding movement to the right, the valve body 40 also follows (Sequence control).
  • This movement of the valve body results from the changing pressure conditions on the end faces of the valve body and the mechanical guidance by the pilot spool.
  • the force to move the pilot spool is determined by the compression spring 82 and the friction in the bore 47. Since the pressure in the ring channels 94, 95 is balanced by the bore 69, no hydraulic forces act on the pilot valve. The actuating forces for the pilot spool are therefore low. If the pressure at port 19 is so low that the valve cone 40 alone cannot be moved, the pilot spool supports the movements.
  • the pilot spool 71 strikes the end face of the Valve plug 72 - after fully opening the throttle bores 63 and 64 - against the screw 52 and thus supports the movement to the left.
  • the valve body 40 is carried along by the valve cone 72 of the pilot valve.
  • FIG. 3 shows a modification of the embodiment of Figure 1, in which the valve body is made in two parts. The same parts are again provided with the same numbers.
  • This embodiment offers advantages in terms of production technology, since the cone serving as the seat cone and the fine control cone can be machined separately.
  • the valve body 40A which is tightly guided in the bush 23, is composed of an inner cylindrical valve body sleeve 100 and an outer cylindrical valve body sleeve 101.
  • the outside diameter of the valve body sleeve 101 corresponds to the diameter of the bore 30 in the bushing 23.
  • This valve body sleeve 101 is penetrated axially by two bores 102, 103 which merge into one another in the same axis, of which the bore 103 opening in the region of the valve seat 41 has the smaller diameter.
  • the diameter of this bore 103 is smaller than the diameter of the bore 31 in the bushing 23.
  • the end face of the valve body sleeve 101 facing the valve seat 41 is designed as a flat cone 105. This runs in the region of the diameter of the bore 31, ie in the region of the valve seat 41, into a concavely rounded transition 107 such that an annular shoulder 108 remains on the end face of the valve body sleeve, the outer diameter of which is slightly smaller than the diameter of the bore 31.
  • In the valve body sleeve 101 there is a radially extending blind bore 109 extending from the outer circumference, from the bottom of which a throttle bore 110 extends, which opens into the bore 102.
  • the bore 102 and the annular groove 32 are connected to one another via the bores 109, 110.
  • the inner valve body sleeve 100 consists of a fine control cone 111 which projects into the bore 31 and a cylindrical section 112 which projects through the bore 103 into the bore 102.
  • the outer circumference of the section 112 corresponds to the diameter of the bore 103
  • the outer diameter of the fine control cone 111 corresponds to the outer diameter of the ring shoulder 108.
  • the fine control cone lies flush against the ring shoulder, so that there is a smooth transition from the cone 105 via the concave transition 107 to the fine control cone 111 trains.
  • Two inner bores 114, 115 run axially through the inner valve body sleeve 100, of which the bore 115 opening at the fine control cone 111 has the smaller diameter.
  • two radial, opposite blind bores 116, 117 run, from the bottom of which a throttle bore 118, 119 extends, both of which open into bore 115.
  • the bore 115 is penetrated again by a blind bore 120, which likewise starts from the outer circumference of the section 112 and is closed there by a plug, not shown.
  • the valve body 40A is closed on one side on the side opposite the fine control cone by a screw 49A.
  • the threaded part 50A of the screw projects into the bore 114 of the inner valve body sleeve, which has an internal thread 122 over a corresponding part of its length.
  • the screw head 52A lies against the end face of the outer valve body sleeve 101 in such a way that the inner valve body sleeve is braced against the outer one.
  • An annular space 123 delimited by the screw is formed between the two valve body sleeves in the area of the bore 102 and the section 112.
  • an annular groove 55A is formed, into which a sealing ring 56A is inserted, which seals the bore 114 on one side.
  • In the screw head 52A is on the fine control cone facing away from a blind bore 57A, from the bottom of which a throttle bore 58A emerges, which opens into the annular space 123.
  • a pilot valve 71A corresponding to the exemplary embodiment described above is guided in the bore 115 in a tightly sliding manner. It extends with its valve cone 72A into the bore 114 and interacts there with a valve seat 125 formed at the transition of the bores 114, 115.
  • the collar 92A on the outer circumference of the pilot valve closes the throttle bores 118, 119 when the valve cone 72A is in contact with the seat 125.
  • the annular grooves 90A, 91A together with the wall of the bore 115 form two annular channels 126, 127, which pass through the blind bore 120 in each working position of the spool are connected to each other.
  • FIG. 4 shows a further exemplary embodiment, which differs from the ones described above in that the valve body and pilot spool are designed differently.
  • the same parts are provided with the same numbers here.
  • the valve cone 40B differs from the valve cones 40, 40A in that it has a displaced valve seat 73B for the pilot valve 71B.
  • the bore 46B is a longitudinal bore consisting of three bore sections 130, 131, 132 which merge into one another with the same axis.
  • the bore section 130 starting from the bore 46B corresponds to the bore 47.
  • the bore section 131 is formed, which has a larger diameter and merges into the bore section 132, which opens at the fine control cone .
  • the diameter of the bore section 132 is smaller than that of the bore section 130.
  • the transition between the bore sections 131, 132 is designed as a valve seat 73B.
  • the pilot spool 71B essentially consists of two cylindrical spool sections 134, 135, of which the section 135 projects through the fine control cone to the plunger 75 and interacts with it and the spring guiding device in a prescribed manner.
  • the slide section 135 has a diameter which is smaller than that of the bore section 132, so that an annular space 138 remains between the slide section and the bore section.
  • the slide section 135 In the area of the bore section 131, the slide section 135 has a narrow collar 137 which interacts with the valve seat 73B. The diameter of this collar is as large as that of the bore section 130.
  • the slide section 135 merges in the region of the throttle bore 63B, 64B into the slide section 134, which is guided in the bore section 130 in a tightly sliding manner and projects into the bore 46B.
  • a further annular space 139 remains between the slide section 135 and the bore section 130.
  • the slide section 134 is designed such that the throttle bores 63B, 64B are closed by it when the collar 137 abuts the valve seat 73B.
  • pilot valve 71B there is also a longitudinal bore 88B which extends from the bore 46B and opens into the transverse bore 87B.
  • the valve seat 41 is opened and closed analogously to the exemplary embodiments according to FIG. 1.

Abstract

The control device described for a hydraulic piston/cylinder unit comprises a check valve (10) in which a valve-obturation body (40; 40A; 40B) acts in conjunction with a valve seat (41) forming an integral part of the housing. Fitted in the valve-obturation body is a pre-control element (72; 72A; 72B) which acts in conjunction with a valve seat (73; 73A; 73B), also located in the valve-obturation body, and chock bores (63, 64; 118, 119; 63B, 64B). The compressive forces acting on the pre-control element are balanced out so that this element can be operated by a proportional-action magnet (13).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuervorrichtung mit einem Proportionalsteuerventil nach der Gattung des Anspruchs 1. Aus der GB-A-875 402 ist ein elektromagnetisch vorgesteuertes Proportionalsteuerventil bekannt, das ein von einem Proportionalmagneten betätigtes Vorsteuerventilglied aufweist. Dieses Vorsteuerventilglied steuert den Druck in einem zwischen dem Ventilkörper des Proportionalsteuerventils und dessen Ventilgehäuse angeordneten Druckraum, durch dessen Wirkung der Ventilkörper gegen den Ventilsitz gedrückt wird. Derartige Proportionalsteuerventile haben den Nachteil, daß der gesteuerte bzw. geregelte Druckmittelstrom starken Schwankungen unterworfen ist, da insbesondere die Feinsteuerbarkeit für Anwendungsfälle, in denen eine hohe Regelgüte erforderlich ist, nicht ausreicht. Aufgrund der nur schlechten Feinsteuerbarkeit dieser Proportionalsteuerventile sind weder hohe Regelstabilitäten noch kontinuierliche Druckmittelströme einstellbar. Weiterhin ist aus der DE-OS 30 42 277 bereits eine Steuervorrichtung bekannt, bei der mit Hilfe eines feinsteuerbaren Sperrventils - eines sogenannten Senkbremsventils erreicht wird, daß beispielsweise die an einem Verbraucher wirksame Last beim Absenken dem ihm zugeordneten Druckmittelstrom nicht vorauseilt. Dieses Sperrventil weist ein Steuerventilglied auf, das in dessen Ventilschieber geführt ist. Dieses Steuerventilglied ragt mit einem Steuerzapfen in eine Abflußbohrung. Ein derartiges Sperrventil hat den Nachteil, daß Druckmittel erst abfließen kann, wenn der Steuerzapfen aus der Abflußbohrung austaucht. Der Betätigungsweg, über den eine Stelleinrichtung das Sperrventil bewegen muß, bevor überhaupt Druckmittel fließen kann, ist sehr lang.The invention is based on a control device with a proportional control valve according to the preamble of claim 1. From GB-A-875 402 an electromagnetically pilot-controlled proportional control valve is known which has a pilot valve element actuated by a proportional magnet. This pilot valve member controls the pressure in a pressure chamber arranged between the valve body of the proportional control valve and its valve housing, by the action of which the valve body is pressed against the valve seat. Proportional control valves of this type have the disadvantage that the controlled or regulated pressure medium flow is subject to strong fluctuations since, in particular, the fine controllability is not sufficient for applications in which a high control quality is required. Due to the poor fine controllability of these proportional control valves, neither high control stabilities nor continuous pressure medium flows can be set. Furthermore, from DE-OS 30 42 277 a control device is already known in which, with the help of a finely controllable shut-off valve - a so-called lowering brake valve, it is achieved that, for example, the load acting on a consumer does not lead the pressure medium flow assigned to it when lowering. This check valve has a control valve member which is guided in the valve slide. This control valve member projects into a drain hole with a control pin. Such a check valve has the disadvantage that pressure medium can only drain when the control pin emerges from the drain hole. The actuation path over which an actuating device must move the check valve before pressure medium can flow at all is very long.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Steuervorrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß bei kurzen Betätigungswegen für das Proportionalsteuerventil und geringen Betätigungskräften ein kontinuierliches, feinsteuerbares Abströmen des Druckmittels ermöglicht wird. Durch das Zusammenwirken des Vorsteuerschiebers mit den Drosselbohrungen im Ventilkörper wird darüber hinaus ein stabiler Verlauf der Ventilkennlinie über einen großen Bereich erreicht. Diese hohe Regelstabilität des Ventils führt zu einer schwingungsarmen Arbeitsweise, wodurch auch schnarrende und pfeifende Geräusche vermindert werden. Die erfindungsgemäße Vorrichtung eignet sich besonders als sogenanntes Senkbremsventil, bei dem das vom Verbraucher (Hydrozylinder) zurückfließende Druckmittel gedrosselt wird, so daß - wie eingangs erwähnt - kein Vorauseilen der Last oder "Ruckeln" erfolgt.The control device according to the invention with the characterizing features of claim 1 has the advantage that a short, finely controllable outflow of the pressure medium is made possible with short actuation paths for the proportional control valve and low actuation forces. Through the interaction of the pilot spool with the throttle bores in the valve body, a stable course of the valve characteristic curve is also achieved over a large range. This high control stability of the valve leads to a low-vibration mode of operation, which also reduces snarling and whistling noises. The device according to the invention is particularly suitable as a so-called lowering brake valve, in which the pressure medium flowing back from the consumer (hydraulic cylinder) is throttled, so that - as mentioned at the beginning - the load does not advance or "jerky".

Zeichnungdrawing

Drei Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung und Zeichnung näher erläutert. Letztere zeigt in Figur 1 einen Längsschnitt durch ein Sperrventil in etwas vereinfachter Darstellung, in Figur 2 einen Schnitt längs II-II nach Figur 1, in den Figuren 3 und 4 je einen Längsschnitt durch je eine Abwandlung des Ausführungsbeispiels.Three embodiments of the invention are explained in more detail in the following description and drawing. The latter shows in Figure 1 a longitudinal section through a check valve in a somewhat simplified representation, in Figure 2 a section along II-II of Figure 1, in Figures 3 and 4 each a longitudinal section through a modification of the embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist mit 10A ein etwa topfförmiges Ventilgehäuse eines Proportionalsteuerventils 10 bezeichnet, das mit seiner offenen Stirnseite 11 an einem Gehäuse 12 eines Proportionalmagneten 13 anliegt. Im Inneren des Ventilgehäuses sind zwei umlaufende Ringnuten 15, 16 ausgebildet.In FIG. 1, 10A denotes an approximately cup-shaped valve housing of a proportional control valve 10, which with its open end face 11 bears against a housing 12 of a proportional magnet 13. Two circumferential annular grooves 15, 16 are formed in the interior of the valve housing.

Die Ringnut 15 steht über eine Bohrung 18 und einen Druckmittel zuführenden Anschluß 19 mit einer Druckmittelquelle in Verbindung, und die Ringnut 16 ist über eine Bohrung 20 mit einem zu einem Verbraucher führenden und Druckmittel abführenden Anschluß 21 verbunden.The annular groove 15 is connected via a bore 18 and a pressure medium supplying connection 19 to a pressure medium source, and the annular groove 16 is connected via a bore 20 to a connection 21 leading to a consumer and discharging pressure medium.

In das Ventilgehäuse 10A ist eine zylindrische Buchse 23 eingesetzt und mit einer Verschlußmutter 24 mit Außengewinde 25 im Gehäuse fixiert. Das Ventilgehäuse weist dazu im Bereich seiner Stirnseite 11 ein entsprechendes Innengewinde 26 auf, das von einer zylindrischen Ausnehmung 27 an der Stirnseite ausgeht, in die ein Dichtring 28 eingelegt ist. Durch diese Dichtung wird die Anbindung des Ventilgehäuses an den Proportionalmagneten nach außen abgedichtet. Durch die Buchse 23 verlaufen axial zwei ineinander übergehende Bohrungen 30, 31, von denen die der Stirnseite 11 zugewandte Bohrung 31 den kleineren Durchmesser aufweist. In der Wandung der Bohrung 30 ist im Bereich des Übergangs zur Bohrung 31 eine Ringnut 32 ausgebildet, die über Querbohrungen 33, 34 mit einem durch die Ringnut 15 und die Buchse 23 gebildeten Ringkanal 36 in Verbindung steht. Die Bohrung 31 ist von einer in der Buchse 23 ausgebildeten Querbohrung 37 durchdrungen, die die Bohrung 31 mit einem durch die Ringnut 16 und die Buchse 23 gebildeten Ringkanal 38 verbindet.A cylindrical bushing 23 is inserted into the valve housing 10A and fixed in the housing with a locking nut 24 with an external thread 25. For this purpose, the valve housing has a corresponding internal thread 26 in the region of its end face 11, which starts from a cylindrical recess 27 on the end face, into which a sealing ring 28 is inserted. This seal seals the connection of the valve housing to the proportional solenoid from the outside. Axially through the bushing 23 are two bores 30, 31 which merge into one another, of which the bore 31 facing the end face 11 has the smaller diameter. In the wall of the bore 30, an annular groove 32 is formed in the region of the transition to the bore 31, which is connected via transverse bores 33, 34 to an annular channel 36 formed by the annular groove 15 and the bushing 23. The bore 31 is penetrated by a transverse bore 37 formed in the bushing 23, which connects the bore 31 to an annular channel 38 formed by the annular groove 16 and the bushing 23.

In der Bohrung 30 der Buchse 23 ist ein Ventilkörper 40 dicht gleitend geführt. Dieser wirkt mit einem am Übergang der Bohrung 30 in die Bohrung 31 ausgebildeten Ventilsitz 41 zusammen. Der Ventilkörper 40 ist im Bereich des Ventilsitzes 41 als flacher Konus 42 ausgebildet, der in einen Feinsteuerkegel 43 übergeht. Der Übergang 44 vom Konus zum Feinsteuerkegel ist nicht in Form einer Kante, sondern als konkave Rundung ausgeführt.A valve body 40 is guided in a tightly sliding manner in the bore 30 of the bushing 23. This interacts with a valve seat 41 formed at the transition of the bore 30 into the bore 31. The valve body 40 is formed in the region of the valve seat 41 as a flat cone 42 which merges into a fine control cone 43. The transition 44 from the cone to the fine control cone is not designed in the form of an edge, but as a concave curve.

Der Ventilkörper 40 wird von drei ineinander übergehenden, achsgleich verlaufenden Bohrungen 45, 46, 47 durchdrungen. Die am Feinsteuerkegel 43 mündende Bohrung 47 weist den geringsten Durchmesser auf, die an der gegenüberliegenden Stirnseite mündende Bohrung 45 weist den größten Durchmesser auf. Der Ventilkörper ist auf der dem Feinsteuerkegel gegenüberliegenden Stirnseite durch eine Schraube 49 einseitig verschlossen. Der Gewindeteil 50 der Schraube ragt in die Bohrung 46, die auf einem entsprechenden Teil ihrer Länge ein Innengewinde hat. Der Schraubenkopf 52 liegt an der Stirnseite des Ventilkörpers so an, daß durch die Bohrung 45 und die Schraube 49 ein Ringkanal 54 entsteht. Im Gewindeteil 50 der Schraube ist eine Ringnut 55 ausgebildet, in die ein Dichtring 56 eingelegt ist, der den Ringkanal 54 gegen die Bohrung 46 abdichtet. Im Schraubenkopf 52 ist auf der dem Ventilkörper abgewandten Seite eine Sackbohrung 57 angebracht, von deren Grund eine Drosselbohrung 58 ausgeht, die in den Ringkanal 54 mündet. Über die Bohrungen 57, 58 steht der Ringkanal 54 mit einem zwischen dem Boden des Gehäuses 10A und dem Ventilkörper 40 gebildeten Druckraum 60 in Verbindung.The valve body 40 is penetrated by three merging bores 45, 46, 47 which merge into one another. The bore 47 opening at the fine control cone 43 has the smallest diameter, the bore 45 opening at the opposite end face has the largest diameter. The valve body is closed on one side by a screw 49 on the end face opposite the fine control cone. The threaded part 50 of the screw projects into the bore 46, which has an internal thread over a corresponding part of its length. The screw head 52 lies against the end face of the valve body in such a way that an annular channel 54 is created through the bore 45 and the screw 49. In the threaded part 50 of the screw, an annular groove 55 is formed, into which a sealing ring 56 is inserted, which seals the annular channel 54 against the bore 46. In the screw head 52, a blind bore 57 is made on the side facing away from the valve body, from the bottom of which a throttle bore 58 extends, which opens into the annular channel 54. The ring channel 54 is connected via the bores 57, 58 to a pressure chamber 60 formed between the bottom of the housing 10A and the valve body 40.

Im Ventilkörper 40 verlaufen radial zwei vom Außenumfang ausgehende, im Bereich der Ringnut 32 angeordnete, gegenüberliegende Sackbohrungen 61, 62. Von deren Grund geht jeweils eine Drosselbohrung 63, 64 aus, die beide in die Bohrung 47 münden. Die Bohrung 61 weist im Bereich des Außenumfangs des Ventilkörpers ein Innengewinde 65 auf, in das eine Einschraubdrossel 66 eingesetzt ist. Die Bohrung 62 ist im Bereich des Außenumfangs des Ventilkörpers durch einen Stopfen 68 verschlossen. Die Sackbohrung 61 ist über einen Längskanal 67 und die Sackbohrung 62 über einen Längskanal 70 mit dem Ringkanal 54 verbunden. Im Bereich der Mündungen der Drosselbohrungen 63, 64 wird die Bohrung 47 von einer dritten radial verlaufenden Sackbohrung 69 durchdrungen, die ebenfalls vom Außenumfang des Ventilkörpers ausgeht und dort durch einen Stopfen 59 verschlossen ist (siehe Figur 2).In the valve body 40, two blind bores 61, 62, which extend from the outer circumference and are arranged in the area of the annular groove 32, run radially. A throttle bore 63, 64, which both open into the bore 47, extends from the bottom thereof. The bore 61 has an internal thread 65 in the region of the outer circumference of the valve body, into which a screwing throttle 66 is inserted. The bore 62 is closed in the region of the outer circumference of the valve body by a plug 68. The blind hole 61 is connected to the annular channel 54 via a longitudinal channel 67 and the blind hole 62 via a longitudinal channel 70. In the area of the orifices of the throttle bores 63, 64, the bore 47 is penetrated by a third radially extending blind bore 69, which likewise extends from the outer circumference of the valve body and is closed there by a stopper 59 (see FIG. 2).

In der Bohrung 47 ist ein Vorsteuerschieber 71 dicht gleitend geführt. Er ragt auf der einen Seite mit einem konisch erweiterten Ventilkegel 72 in die Bohrung 46 und wirkt dort mit einem am Übergang der Bohrung 46 in die Bohrung 47 ausgebildeten Ventilsitz 73 zusammen. Auf der anderen Seite ragt der Vorsteuerschieber bis in eine sechskantige Öffnung 74 der Verschlußmutter 24 und wirkt dort mit einem vom Proportionalmagneten 13 in die Öffnung 74 ragenden Betätigungsstöβel 75 zusammen. Der Vorsteuerschieber 71 durchdringt den Boden eines topfförmigen Federführungselementes 78, das in die Bohrung 31 ragt und mit einem kranzförmigen Rand 79 an der Stirnseite der Buchse 23 anliegt. Das Federführungselement 78 wird durch die Verschlußmutter 24 in seiner Lage fixiert. Diese weist dazu eine Ringnut 80 auf, deren Durchmesser dem des kragenförmigen Randes 79 entspricht. Das Federführungselement 78 kann in radialer Richtung auch durch die Kanten der Öffnung 74 fixiert werden; dazu sollte dann der Außenumfang des Randes 79 dem Innenkreisdurchmesser der sechskantigen Öffnung 74 entsprechen. An der Bodeninnenseite des Federführungselementes 78 stützt sich das eine Ende einer Druckfeder 82 ab, deren anderes Ende an einer über den Vorsteuerschieber 71 geschobenen Scheibe 83 anliegt. Diese Scheibe wird durch einen Sicherungsring 85, der in eine Ringnut 84 am Ende des Vorsteuerschiebers eingepaßt ist, gegen Abschieben gesichert.In the bore 47, a pilot valve 71 is guided in a tightly sliding manner. It projects on one side with a conically expanded valve cone 72 into the bore 46 and interacts there with a valve seat 73 formed at the transition from the bore 46 into the bore 47. On the other hand, the pilot spool protrudes into a hexagonal opening 74 of the locking nut 24 and interacts there with an actuating plunger 75 projecting into the opening 74 from the proportional magnet 13. The pilot spool 71 penetrates the bottom of a pot-shaped spring guide element 78 which projects into the bore 31 and abuts the front side of the bush 23 with a ring-shaped edge 79. The spring guide element 78 is fixed in position by the lock nut 24. For this purpose, this has an annular groove 80, the diameter of which corresponds to that of the collar-shaped edge 79. The spring guide element 78 can also be fixed in the radial direction by the edges of the opening 74; for this purpose the outer circumference of the edge 79 should then correspond to the inner circle diameter of the hexagonal opening 74. One end of a compression spring 82 is supported on the inside of the spring guide element 78, the other end of which rests on a disk 83 pushed over the pilot valve 71. This disc is secured against being pushed off by a locking ring 85 which is fitted into an annular groove 84 at the end of the pilot spool.

Im Bereich zwischen Federführungselement 78 und Feinsteuerkegel 43 ist der Vorsteuerschieber 71 von einer Querbohrung 87 durchdrungen. In diese Querbohrung mündet eine längsverlaufende Sackbohrung 88, die vom Vorsteuerventilkegel 72 ausgeht. Am Außenumfang des Vorsteuerschiebers sind zwei Ringnuten 90, 91 ausgebildet, zwischen denen ein schmaler Bund 92 verbleibt. Dieser verschließt bei Anliegen des Vorsteuerventilkegels 72 an den Ventilsitz 73 die Drosselbohrungen 63, 64. Die Ringnut 90 reicht vom Bund 92 bis zum Ventilkegel 72, der vom Grund dieser Nut ausgeht. Durch die Ringnuten 90, 91 werden zusammen mit der Wandung der Bohrung 47 zwei Ringkanäle 94, 95 gebildet, die über die Sackbohrung 69 in jeder Arbeitsstellung des Vorsteuerschiebers miteinander verbunden sind. Der Durchmesser der Sackbohrung 69 ist so groß, daß auch beim Hub des Vorsteuerschiebers die beiden Ringkanäle verbunden sind.In the area between the spring guide element 78 and the fine control cone 43, the pilot spool 71 is penetrated by a transverse bore 87. A longitudinal blind bore 88, which starts from the pilot valve cone 72, opens into this transverse bore. Two annular grooves 90, 91 are formed on the outer circumference of the pilot valve, between which a narrow collar 92 remains. This closes the throttle bores 63, 64 when the pilot valve cone 72 bears against the valve seat 73. The annular groove 90 extends from the collar 92 to the valve cone 72, which starts from the bottom of this groove. By the annular grooves 90, 91 together with the wall of the bore 47, two annular channels 94, 95 are formed, which in each of the blind bore 69 Working position of the spool are connected. The diameter of the blind bore 69 is so large that the two ring channels are connected even when the pilot spool is lifted.

Das Proportionalsteuerventil 10 ist bei nicht erregtem Proportionalmagneten 13 geschlossen. Durch die Wirkung der Druckfeder 82 werden der Ventilkegel 72 des Vorsteuerschiebers 71 an seinen Sitz 73 und damit auch der Ventilkörper 40 gegen seinen Sitz 41 gezogen. Gleichzeitig verschließt der Bund 92 die Drosselbohrungen 63, 64. Zulaufseitig ist der Druckmittelanschluß 19 über die Bohrung 18, den Ringkanal 36 und die Bohrungen 33,34 sowie die Ringnut 32 mit der Einschraubdrossel 66 verbunden. Von dort gelangt Druckmittel über den Längskanal 67 in den Ringraum 54 und von dort über die Drosselbohrung 58 und die Bohrung 57 in den Druckraum 60. Gleichzeitig besteht über den Längskanal 70 eine Verbindung vom Ringkanal 54 zur Bohrung 62. Ablaufseitig steht die durch den Ventilkörper einseitig verschlossene Bohrung 31 über die Bohrung 37, den Ringkanal 38 und die Bohrung 20 mit dem Druckmittelanschluß 21 in Verbindung. Da die mit Druckmittel beaufschlagte Stirnfläche AS des Ventilkörpers - entsprechend der Fläche der Bohrung 30 - größer ist als die Ringfläche AR - entsprechend der Flächendifferenz zwischen Bohrung 30 und 31 wird der Ventilkörper zusätzlich an seinen Sitz 41 gedrückt. Die Leckverluste in Schließstellung des Sperrventils sind aufgrund der eingesetzten Sitzventile und der langen Gleitführung des Vorsteuerschiebers 71 in der Bohrung 47 sehr gering.The proportional control valve 10 is closed when the proportional magnet 13 is not energized. Due to the action of the compression spring 82, the valve cone 72 of the pilot valve 71 is pulled to its seat 73 and thus also the valve body 40 against its seat 41. At the same time, the collar 92 closes the throttle bores 63, 64. On the inlet side, the pressure medium connection 19 is connected to the screw-in throttle 66 via the bore 18, the annular channel 36 and the bores 33, 34 and the annular groove 32. From there, pressure medium reaches the annular space 54 via the longitudinal channel 67 and from there via the throttle bore 58 and the bore 57 into the pressure space 60. At the same time, there is a connection from the annular channel 54 to the bore 62 via the longitudinal channel 70. The outlet side is through the valve body on one side closed bore 31 via the bore 37, the annular channel 38 and the bore 20 with the pressure medium connection 21 in connection. Since the end face A S of the valve body acted upon by pressure medium - corresponding to the area of the bore 30 - is larger than the annular area A R - corresponding to the area difference between the bore 30 and 31, the valve body is additionally pressed against its seat 41. The leakage losses in the closed position of the check valve are very low due to the seat valves used and the long sliding guide of the pilot spool 71 in the bore 47.

Wird der Proportionalmagnet 13 erregt, bewegt sich der Vorsteuerschieber 71 durch den Stößel 75 des Proportionalmagneten 13 nach links, so daß der Vorsteuerventilkegel 72 sich von seinem Ventilsitz 73 abhebt und die zuvor durch den Bund 92 einseitig verschlossenen Drosselbohrungen 63, 64 geöffnet werden.If the proportional magnet 13 is excited, the pilot valve 71 moves to the left through the plunger 75 of the proportional magnet 13, so that the pilot valve cone 72 lifts off its valve seat 73 and the throttle bores 63, 64 previously closed on one side by the collar 92 are opened.

Steht Druck am Druckmittelanschluß 19 an, so fließt Druckmittel von der zulaufseitigen Anschlußbohrung 19, wie zuvor beschrieben, zu den Bohrungen 61, 62 und von dort über die Drosselbohrungen 63, 64 in den Ringkanal 95. Über die verschlossene Sackbohrung 69 besteht Verbindung zum Ringkanal 94. Von dort gelangt das Druckmittel über den geöffneten Ventilsitz 73 in die einseitig verschlossene Bohrung 46. Über die Längsbohrung 88 und die Querbohrung 87 im Ventilschieber 71 ist die Bohrung 46 mit der Bohrung 31 verbunden, die, wie zuvor beschrieben, in Verbindung mit dem ablaufseitigen Druckmittelanschluß 21 steht.If pressure is present at the pressure medium connection 19, pressure medium flows from the inlet-side connection bore 19, as previously described, to the bores 61, 62 and from there via the throttle bores 63, 64 into the ring channel 95 From there, the pressure medium passes through the opened valve seat 73 into the bore 46 which is closed on one side. The bore 46 is connected to the bore 31 via the longitudinal bore 88 and the transverse bore 87 in the valve slide 71, which bore, as described above, is connected to the outlet end Pressure medium connection 21 is.

Entsprechend der Öffnung der Drosselbohrungen 63, 64 durch den Bund 92 im Verhältnis zur Bohrung der Einschraubdrossel 66 fällt der Druck in der Bohrung 61 und damit auch im Druckraum 60. Fällt der Druck im Druckraum 60 so weit, daß die Druckkräfte auf die gegenüberliegende Ventilkörperstirnseite (Ringfläche AR) überwiegen, bewegt sich der Ventilkörper 40 nach links. Druckmittel fließt dann aus der Ringnut 32 am geöffneten Ventilsitz 41 vorbei in die Bohrung 31 und gelangt von dort zum Druckmittelanschluß 21. Folgt der Vorsteuerschieber 71 aufgrund der Wirkung der Feder 82 dem Stößel 75 bei einer entsprechenden Bewegung nach rechts, so folgt der Ventilkörper 40 ebenfalls (Folgesteuerung). Diese Bewegung des Ventilkörpers resultiert aus den sich ändernden Druckverhältnissen an den Stirnseiten des Ventilkörpers und der mechanischen Führung durch den Vorsteuerschieber. Die Kraft, um den Vorsteuerschieber zu bewegen, wird von der Druckfeder 82 und der Reibung in der Bohrung 47 bestimmt. Da der Druck in den Ringkanälen 94, 95 durch die Bohrung 69 ausgeglichen ist, wirken keine hydraulischen Kräfte auf den Vorsteuerschieber. Die Betätigungskräfte für den Vorsteuerschieber sind deshalb gering. Ist der Druck an Anschluß 19 so gering, daß dadurch allein der Ventilkegel 40 nicht bewegt werden kann, so unterstützt der Vorsteuerschieber die Bewegungen. Beim Öffnen (Bewegung nach links) schlägt der Vorsteuerschieber 71 mit der Stirnseite des Ventilkegels 72 - nach dem vollständigen Öffnen der Drosselbohrungen 63 und 64 - gegen die Schraube 52 und unterstützt somit die Bewegung nach links. Beim Schließen wird der Ventilkörper 40 durch den Ventilkegel 72 des Vorsteuerschiebers mitgenommen.Corresponding to the opening of the throttle bores 63, 64 through the collar 92 in relation to the bore of the screw-in throttle 66, the pressure in the bore 61 and thus also in the pressure chamber 60 drops.If the pressure in the pressure chamber 60 falls so far that the pressure forces on the opposite valve body face ( Ring area A R ) predominate, the valve body 40 moves to the left. Pressure medium then flows out of the annular groove 32 past the opened valve seat 41 into the bore 31 and from there to the pressure medium connection 21. If the pilot valve 71 follows the plunger 75 due to the action of the spring 82 with a corresponding movement to the right, the valve body 40 also follows (Sequence control). This movement of the valve body results from the changing pressure conditions on the end faces of the valve body and the mechanical guidance by the pilot spool. The force to move the pilot spool is determined by the compression spring 82 and the friction in the bore 47. Since the pressure in the ring channels 94, 95 is balanced by the bore 69, no hydraulic forces act on the pilot valve. The actuating forces for the pilot spool are therefore low. If the pressure at port 19 is so low that the valve cone 40 alone cannot be moved, the pilot spool supports the movements. When opening (movement to the left), the pilot spool 71 strikes the end face of the Valve plug 72 - after fully opening the throttle bores 63 and 64 - against the screw 52 and thus supports the movement to the left. When closing, the valve body 40 is carried along by the valve cone 72 of the pilot valve.

Figur 3 zeigt eine Abwandlung des Ausführungsbeispiels nach Figur 1, bei der der Ventilkörper zweiteilig ausgeführt ist. Gleiche Teile sind dabei wieder mit gleichen Ziffern versehen. Diese Ausführungsform bietet fertigungstechnische Vorteile, da der als Sitzkegel dienende Konus und der Feinsteuerkegel getrennt bearbeitet werden können. Der in der Buchse 23 dicht gleitend geführte Ventilkörper 40A ist aus einer inneren zylindrischen Ventilkörperhülse 100 und einer äußeren zylindrischen Ventilkörperhülse 101 zusammengesetzt. Der Auβendurchmesser der Ventilkörperhülse 101 entspricht dem Durchmesser der Bohrung 30 in der Buchse 23. Diese Ventilkörperhülse 101 wird axial von zwei achsgleich ineinander übergehenden Bohrungen 102, 103 durchdrungen, von denen die im Bereich des Ventilsitzes 41 mündende Bohrung 103 den kleineren Durchmesser aufweist. Der Durchmesser dieser Bohrung 103 ist kleiner als der Durchmesser der Bohrung 31 in der Buchse 23. Die dem Ventilsitz 41 zugewandte Stirnseite der Ventilkörperhülse 101 ist als flacher Konus 105 ausgebildet. Dieser läuft im Bereich des Durchmessers der Bohrung 31, d. h. im Bereich des Ventilsitzes 41, so in einen konkav gerundeten Übergang 107 aus, daß an der Stirnseite der Ventilkörperhülse eine ringförmige Schulter 108 verbleibt, deren Außendurchmesser etwas kleiner als der Durchmesser der Bohrung 31 ist. In der Ventilkörperhülse 101 ist eine vom Außenumfang ausgehende, radial verlaufende Sackbohrung 109 angebracht, von deren Grund eine Drosselbohrung 110 ausgeht, die in die Bohrung 102 mündet. Über die Bohrungen 109, 110 sind die Bohrung 102 und die Ringnut 32 miteinander verbunden.Figure 3 shows a modification of the embodiment of Figure 1, in which the valve body is made in two parts. The same parts are again provided with the same numbers. This embodiment offers advantages in terms of production technology, since the cone serving as the seat cone and the fine control cone can be machined separately. The valve body 40A, which is tightly guided in the bush 23, is composed of an inner cylindrical valve body sleeve 100 and an outer cylindrical valve body sleeve 101. The outside diameter of the valve body sleeve 101 corresponds to the diameter of the bore 30 in the bushing 23. This valve body sleeve 101 is penetrated axially by two bores 102, 103 which merge into one another in the same axis, of which the bore 103 opening in the region of the valve seat 41 has the smaller diameter. The diameter of this bore 103 is smaller than the diameter of the bore 31 in the bushing 23. The end face of the valve body sleeve 101 facing the valve seat 41 is designed as a flat cone 105. This runs in the region of the diameter of the bore 31, ie in the region of the valve seat 41, into a concavely rounded transition 107 such that an annular shoulder 108 remains on the end face of the valve body sleeve, the outer diameter of which is slightly smaller than the diameter of the bore 31. In the valve body sleeve 101 there is a radially extending blind bore 109 extending from the outer circumference, from the bottom of which a throttle bore 110 extends, which opens into the bore 102. The bore 102 and the annular groove 32 are connected to one another via the bores 109, 110.

Die innere Ventilkörperhülse 100 besteht aus einem Feinsteuerkegel 111, der in die Bohrung 31 ragt, und einem zylindrischen Abschnitt 112, der durch die Bohrung 103 in die Bohrung 102 ragt. Der Außenumfang des Abschnittes 112 entspricht dabei dem Durchmesser der Bohrung 103, der Außendurchmesser des Feinsteuerkegels 111 entspricht dem Außendurchmesser der Ringschulter 108. Der Feinsteuerkegel liegt bündig an der Ringschulter an, so daß sich ein glatter Übergang vom Konus 105 über den konkaven Übergang 107 zum Feinsteuerkegel 111 ausbildet.The inner valve body sleeve 100 consists of a fine control cone 111 which projects into the bore 31 and a cylindrical section 112 which projects through the bore 103 into the bore 102. The outer circumference of the section 112 corresponds to the diameter of the bore 103, the outer diameter of the fine control cone 111 corresponds to the outer diameter of the ring shoulder 108. The fine control cone lies flush against the ring shoulder, so that there is a smooth transition from the cone 105 via the concave transition 107 to the fine control cone 111 trains.

Durch die innere Ventilkörperhülse 100 verlaufen axial zwei ineinander übergehende Bohrungen 114, 115, von denen die am Feinsteuerkegel 111 mündende Bohrung 115 den kleineren Durchmesser aufweist. Vom Außenumfang des Abschnittes 112 ausgehend, verlaufen zwei radiale, gegenüberliegende Sackbohrungen 116, 117, von deren Grund jeweils eine Drosselbohrung 118, 119 ausgeht, die beide in die Bohrung 115 münden. Im Bereich der Mündungen der Drosselbohrungen 118, 119 wird die Bohrung 115 nochmals von einer Sackbohrung 120 durchdrungen, die ebenfalls vom Außenumfang des Abschnittes 112 ausgeht und dort durch einen nicht dargestellten Stopfen verschlossen ist.Two inner bores 114, 115 run axially through the inner valve body sleeve 100, of which the bore 115 opening at the fine control cone 111 has the smaller diameter. Starting from the outer circumference of section 112, two radial, opposite blind bores 116, 117 run, from the bottom of which a throttle bore 118, 119 extends, both of which open into bore 115. In the area of the mouths of the throttle bores 118, 119, the bore 115 is penetrated again by a blind bore 120, which likewise starts from the outer circumference of the section 112 and is closed there by a plug, not shown.

Der Ventilkörper 40A ist auf der dem Feinsteuerkegel gegenüberliegenden Seite durch eine Schraube 49A einseitig verschlossen. Der Gewindeteil 50A der Schraube ragt in die Bohrung 114 der inneren Ventilkörperhülse, die auf einem entsprechenden Teil ihrer Länge ein Innengewinde 122 aufweist. Der Schraubenkopf 52A liegt an der Stirnseite der äußeren Ventilkörperhülse 101 so an, daß die innere Ventilkörperhülse gegen die äußere verspannt ist. Zwischen den beiden Ventilkörperhülsen wird im Bereich der Bohrung 102 und des Abschnittes 112 ein durch die Schraube begrenzter Ringraum 123 gebildet. Im Gewindeteil 50A der Schraube ist eine Ringnut 55A ausgebildet, in die ein Dichtring 56A eingelegt ist, der die Bohrung 114 einseitig dicht verschließt. Im Schraubenkopf 52A ist auf der dem Feinsteuerkegel abgewandten Seite eine Sackbohrung 57A angebracht, von deren Grund eine Drosselbohrung 58A ausgeht, die in den Ringraum 123 mündet.The valve body 40A is closed on one side on the side opposite the fine control cone by a screw 49A. The threaded part 50A of the screw projects into the bore 114 of the inner valve body sleeve, which has an internal thread 122 over a corresponding part of its length. The screw head 52A lies against the end face of the outer valve body sleeve 101 in such a way that the inner valve body sleeve is braced against the outer one. An annular space 123 delimited by the screw is formed between the two valve body sleeves in the area of the bore 102 and the section 112. In the threaded part 50A of the screw, an annular groove 55A is formed, into which a sealing ring 56A is inserted, which seals the bore 114 on one side. In the screw head 52A is on the fine control cone facing away from a blind bore 57A, from the bottom of which a throttle bore 58A emerges, which opens into the annular space 123.

In der Bohrung 115 ist ein dem zuvor beschriebenen Ausführungsbeispiel entsprechender Vorsteuerschieber 71A dicht gleitend geführt. Er reicht mit seinem Ventilkegel 72A in die Bohrung 114 und wirkt dort mit einem am Übergang der Bohrungen 114, 115 ausgebildeten Ventilsitz 125 zusammen. Der Bund 92A am Außenumfang des Vorsteuerschiebers verschließt bei Anliegen des Ventilkegels 72A an den Sitz 125 die Drosselbohrungen 118, 119. Die Ringnuten 90A, 91A bilden zusammen mit der Wandung der Bohrung 115 zwei Ringkanäle 126, 127, die über die Sackbohrung 120 in jeder Arbeitsstellung des Vorsteuerschiebers miteinander verbunden sind.A pilot valve 71A corresponding to the exemplary embodiment described above is guided in the bore 115 in a tightly sliding manner. It extends with its valve cone 72A into the bore 114 and interacts there with a valve seat 125 formed at the transition of the bores 114, 115. The collar 92A on the outer circumference of the pilot valve closes the throttle bores 118, 119 when the valve cone 72A is in contact with the seat 125. The annular grooves 90A, 91A together with the wall of the bore 115 form two annular channels 126, 127, which pass through the blind bore 120 in each working position of the spool are connected to each other.

Die Wirkungsweise dieses Proportionalsteuerventils ist analog zu der des zuvor beschriebenen Ausführungsbeispiels.The operation of this proportional control valve is analogous to that of the previously described embodiment.

Die Figur 4 zeigt ein weiteres Ausführungsbeispiel, das sich von den zuvor beschriebenen durch eine geänderte Ausgestaltung von Ventilkörper und Vorsteuerschieber unterscheidet. Gleiche Teile sind auch hier mit gleichen Ziffern versehen. Der Ventilkegel 40B unterscheidet sich von den Ventilkegeln 40, 40A durch einen verlagerten Ventilsitz 73B für den Vorsteuerschieber 71B. Dazu geht von der Bohrung 46B eine aus drei achsgleich ineinander übergehenden Bohrungsabschnitten 130, 131, 132 bestehende Längsbohrung aus. Der von der Bohrung 46B ausgehende Bohrungsabschnitt 130 entspricht dabei der Bohrung 47. Im Bereich zwischen den Drosselbohrungen 63B, 64B und der Stirnseite des Feinsteuerkegels 43B ist der Bohrungsabschnitt 131 ausgebildet, der einen größeren Durchmesser aufweist und in den Bohrungsabschnitt 132 übergeht, der am Feinsteuerkegel mündet. Der Durchmesser des Bohrungsabschnittes 132 ist kleiner als der des Bohrungsabschnittes 130. Der Übergang zwischen den Bohrungsabschnitten 131, 132 ist als Ventilsitz 73B ausgebildet.FIG. 4 shows a further exemplary embodiment, which differs from the ones described above in that the valve body and pilot spool are designed differently. The same parts are provided with the same numbers here. The valve cone 40B differs from the valve cones 40, 40A in that it has a displaced valve seat 73B for the pilot valve 71B. To this end, the bore 46B is a longitudinal bore consisting of three bore sections 130, 131, 132 which merge into one another with the same axis. The bore section 130 starting from the bore 46B corresponds to the bore 47. In the region between the throttle bores 63B, 64B and the end face of the fine control cone 43B, the bore section 131 is formed, which has a larger diameter and merges into the bore section 132, which opens at the fine control cone . The diameter of the bore section 132 is smaller than that of the bore section 130. The transition between the bore sections 131, 132 is designed as a valve seat 73B.

Der Vorsteuerschieber 71B besteht im wesentlichen aus zwei zylindrischen Schieberabschnitten 134, 135, von denen der Abschnitt 135 durch den Feinsteuerkegel bis zum Stößel 75 ragt und mit diesem und der Federführungseinrichtung in vorgeschriebener Weise zusammenwirkt. Der Schieberabschnitt 135 hat einen Durchmesser, der geringer als der des Bohrungsabschnittes 132 ist, so daß zwischen Schieberabschnitt und Bohrungsabschnitt ein Ringraum 138 verbleibt. Im Bereich des Bohrungsabschnittes 131 weist der Schieberabschnitt 135 einen schmalen Bund 137 auf, der mit dem Ventilsitz 73B zusammenwirkt. Der Durchmesser dieses Bundes ist so groß wie der des Bohrungsabschnittes 130. Der Schieberabschnitt 135 geht im Bereich der Drosselbohrung 63B, 64B in den Schieberabschnitt 134 über, der im Bohrungsabschnitt 130 dicht gleitend geführt ist und bis in die Bohrung 46B ragt. Zwischen Schieberabschnitt 135 und Bohrungsabschnitt 130 verbleibt ein weiterer Ringraum 139. Der Schieberabschnitt 134 ist so ausgebildet, daß die Drosselbohrungen 63B, 64B durch ihn verschlossen sind, wenn der Bund 137 am Ventilsitz 73B anliegt.The pilot spool 71B essentially consists of two cylindrical spool sections 134, 135, of which the section 135 projects through the fine control cone to the plunger 75 and interacts with it and the spring guiding device in a prescribed manner. The slide section 135 has a diameter which is smaller than that of the bore section 132, so that an annular space 138 remains between the slide section and the bore section. In the area of the bore section 131, the slide section 135 has a narrow collar 137 which interacts with the valve seat 73B. The diameter of this collar is as large as that of the bore section 130. The slide section 135 merges in the region of the throttle bore 63B, 64B into the slide section 134, which is guided in the bore section 130 in a tightly sliding manner and projects into the bore 46B. A further annular space 139 remains between the slide section 135 and the bore section 130. The slide section 134 is designed such that the throttle bores 63B, 64B are closed by it when the collar 137 abuts the valve seat 73B.

Im Vorsteuerschieber 71B ist wie in den zuvor beschriebenen Ausführungsformen ebenfalls eine von der Bohrung 46B ausgehende Längsbohrung 88B angeordnet, die in die Querbohrung 87B mündet.In the pilot valve 71B, as in the previously described embodiments, there is also a longitudinal bore 88B which extends from the bore 46B and opens into the transverse bore 87B.

Bei nicht erregtem Proportionalmagneten 13 liegt der Bund 137 aufgrund der Wirkung der Feder am Ventilsitz 73B an. Gleichzeitig verschließt der Schieberabschnitt 134 die Drosselbohrungen 63B, 64B. Druckmittel gelangt so vom zulaufseitigen Druckmittelanschluß 19 über die Bohrung 18, den Ringkanal 36 und die Ringnut 32 zur Einschraubdrossel 66. Von dort besteht über die Sackbohrung 61 über den Längskanal 67 Verbindung zum Ringraum 54, der wiederum über den Längskanal 70 mit der Sackbohrung 62 verbunden ist.When the proportional magnet 13 is not energized, the collar 137 bears against the valve seat 73B due to the action of the spring. At the same time, the slide section 134 closes the throttle bores 63B, 64B. Pressure medium thus passes from the inlet-side pressure medium connection 19 via the bore 18, the annular channel 36 and the annular groove 32 to the screwing throttle 66. From there, there is a connection to the annular space 54 via the longitudinal bore 67 via the longitudinal channel 67, which in turn is connected to the blind bore 62 via the longitudinal channel 70 is.

Vom Ringraum 54 besteht - wie zuvor beschrieben - über die Drosselbohrung 58 eine Verbindung zum Druckraum 60. Die Wirkungen der hydraulischen und mechanischen Kräfte sind bei nicht erregtem Proportionalmagneten analog zu denen im Ausführungsbeispiel nach Figur 1.As described above, there is a connection from the annular space 54 to the pressure space 60 via the throttle bore 58. The effects of the hydraulic and mechanical forces are analogous to those in the exemplary embodiment according to FIG. 1 when the proportional magnet is not excited.

Wird der Vorsteuerschieber 71B durch den Stößel 75 nach links bewegt, so hebt sich der Bund 137 vom Ventilsitz 73B ab und die zuvor durch den Schieberabschnitt 134 einseitig verschlossenen Drosselbohrungen 63B, 64B werden geöffnet. Druckmittel gelangt so von den Sackbohrungen 61, 62 über die Drosselbohrungen 63B, 64B in den Ringraum 139 und von dort über den Bohrungsabschnitt 131 am geöffneten Ventilsitz 73B vorbei in den Ringraum 138, der zur Bohrung 31 führt. Diese ist - wie zuvor beschrieben - mit dem ablaufseitigen Druckmittelanschluß 21 verbunden.If the pilot valve 71B is moved to the left by the plunger 75, the collar 137 lifts off from the valve seat 73B and the throttle bores 63B, 64B previously closed on one side by the slide section 134 are opened. Pressure medium thus passes from the blind bores 61, 62 via the throttle bores 63B, 64B into the annular space 139 and from there via the bore section 131 past the opened valve seat 73B into the annular space 138, which leads to the bore 31. As described above, this is connected to the outlet-side pressure medium connection 21.

Das Öffnen und Schließen des Ventilsitzes 41 erfolgt analog zu den Ausführungsbeispielen nach Figur 1.The valve seat 41 is opened and closed analogously to the exemplary embodiments according to FIG. 1.

Claims (10)

  1. Control appliance for a hydraulic working cylinder having a proportional control valve (10) with an inlet (19) and an outlet (21), which proportional control valve (10) has a valve body (40; 40A, 40B) which interacts with a valve seat (41) which is connected to the housing and in which is arranged a pilot control valve element (71, 72; 71A, 72A; 71B, 137), which latter can be actuated by a proportional magnet (13) mounted on the proportional control valve and which is in contact, under the force of a spring (82), with a valve seat (73; 73A; 73B) arranged in the valve body and controls the pressure in a pressure space (60) formed between the valve body and the valve housing (10A), the valve body being pressed against the valve seat (41) by the action of this pressure, characterized in that the pilot control valve element has a seat valve body (72; 72A; 137) and a pilot control spool section (90, 91, 92, 90A, 91A, 92A, 134) arranged in series with it, in that the pressure space (60) is in connection with the inlet (19) via two throttle locations (66; 58; 110; 58A) connected in series and in that this pressure space (60) can be connected to the outlet (21) by means of the pilot control valve element arranged between the throttle locations (66; 58; 110; 58A) connected in series and by means of a passage (88, 87; 88B, 87B; 138) to be opened by the pilot control valve element.
  2. Appliance according to Claim 1, characterized in that the two throttle locations (66, 58; 110, 58A) are formed in the valve body (40; 40A; 40B).
  3. Appliance according to Claim 1 and/or 2, characterized in that the two throttle locations (66, 158, 110; 58A) are in connection with one another by means of pressure medium passages (61, 67, 54, 70, 62; 123) arranged in the valve body (40, 40A; 40B).
  4. Appliance according to one of Claims 1 to 3, characterized in that throttle locations (63; 64; 118, 119; 63B, 64B) which can be varied by means of the pilot control spool section (90, 91, 92; 90A, 91A, 92A; 134) and by means of which the pressure in the pressure space (60) is controlled are formed in the valve body (40; 40A; 40B).
  5. Appliance according to one of Claims 1 to 4, characterized in that the spring (82) acts to pull the pilot control valve element (71; 72; 71A, 72A; 71B, 137).
  6. Appliance according to one of Claims 1 to 5, characterized in that the valve body (40; 40A; 40B) has a blunt-angled cone (42; 105; 42B) which merges into a fine control taper (43; 111; 43B) and in that the transition from the cone to the fine control taper is rounded.
  7. Appliance according to one of Claims 1 to 6, characterized in that annular grooves (90, 91; 90A, 91A) are formed on the pilot control spool section and in that the pressure forces acting on the pilot control valve element are balanced.
  8. Appliance according to Claim 7, characterized in that the annular passages (94, 95; 126, 127) formed by the annular grooves (90, 91; 90A, 91A) and the valve body (40; 40A) are connected together by a closed pocket hole (69; 120) in the valve element.
  9. Appliance according to one of Claims 1 to 8, characterized in that the valve element (40A) consists of at least one inner valve body sleeve (100) and one outer valve body sleeve (101).
  10. Appliance according to one of Claims 1 to 6, characterized in that a peripheral collar (137) which interacts with the valve seat (73B) is formed on the pilot control valve element (71B).
EP91915901A 1990-10-10 1991-09-21 Control device for hydraulic piston/cylinder unit Expired - Lifetime EP0549628B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4032078 1990-10-10
DE4032078A DE4032078C2 (en) 1990-10-10 1990-10-10 Control device for a hydraulic working cylinder
PCT/DE1991/000748 WO1992007194A2 (en) 1990-10-10 1991-09-21 Control device for hydraulic piston/cylinder unit

Publications (2)

Publication Number Publication Date
EP0549628A1 EP0549628A1 (en) 1993-07-07
EP0549628B1 true EP0549628B1 (en) 1994-07-27

Family

ID=6415967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91915901A Expired - Lifetime EP0549628B1 (en) 1990-10-10 1991-09-21 Control device for hydraulic piston/cylinder unit

Country Status (5)

Country Link
US (1) US5328148A (en)
EP (1) EP0549628B1 (en)
DE (2) DE4032078C2 (en)
RU (1) RU2082024C1 (en)
WO (1) WO1992007194A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140604A1 (en) * 1991-12-10 1993-06-17 Bosch Gmbh Robert CONTROL DEVICE FOR THE VOLUME FLOW OF A HYDRAULIC WORKING AGENT
WO1996012111A1 (en) * 1994-10-15 1996-04-25 Mannesmann Rexroth Gmbh Process for operating a precontrolled 2/2-way seat valve and precontrolled 2/2-way seat valve for operation according to the process
DE4446860A1 (en) * 1994-12-27 1996-07-04 Herion Werke Kg Control valve used in power generation plants
US5538026A (en) * 1995-03-29 1996-07-23 Parker-Hannifin Corporation Pilot-operated proportional control valve
DE19634319A1 (en) * 1996-08-24 1998-02-26 Bosch Gmbh Robert Electro-hydraulic control device
US5878647A (en) * 1997-08-11 1999-03-09 Husco International Inc. Pilot solenoid control valve and hydraulic control system using same
DE19955521A1 (en) * 1999-11-18 2001-05-23 Bosch Gmbh Robert Device for controlling a hydraulic volume flow of at least one loaded working medium
WO2012091194A1 (en) * 2010-12-28 2012-07-05 볼보 컨스트럭션 이큅먼트 에이비 Holding valve for construction equipment
RU2576828C1 (en) * 2014-12-26 2016-03-10 Открытое акционерное общество "Омское машиностроительное конструкторское бюро" High-pressure valve
RU2686744C1 (en) * 2018-08-13 2019-04-30 Сергей Анатольевич Паросоченко Throttling device

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US2694544A (en) * 1950-07-19 1954-11-16 Atkomatic Valve Company Inc Pressure actuated valve
GB875402A (en) * 1958-01-17 1961-08-16 Franco Belge De Material De Ch Improvements in and relating to a fluid control valve
US3033228A (en) * 1959-03-23 1962-05-08 Lewis K Rimer Low-force valve control
US3667722A (en) * 1970-10-22 1972-06-06 Ite Imperial Corp Proportional valve
DE3042277A1 (en) * 1980-11-08 1982-06-03 Robert Bosch Gmbh, 7000 Stuttgart CONTROL DEVICE FOR A HYDRAULIC WORKING CYLINDER
DE3125143A1 (en) * 1981-06-26 1983-01-13 Mannesmann Rexroth GmbH, 8770 Lohr "PRESSURE REDUCER VALVE"
DE3429218A1 (en) * 1984-08-08 1986-02-20 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart ELECTROMAGNETIC HYDROVALVE
CH671080A5 (en) * 1986-10-01 1989-07-31 Sulzer Ag
US4741364A (en) * 1987-06-12 1988-05-03 Deere & Company Pilot-operated valve with load pressure feedback

Also Published As

Publication number Publication date
WO1992007194A2 (en) 1992-04-30
DE4032078A1 (en) 1992-04-16
DE59102380D1 (en) 1994-09-01
US5328148A (en) 1994-07-12
WO1992007194A3 (en) 1992-05-29
DE4032078C2 (en) 1997-08-07
EP0549628A1 (en) 1993-07-07
RU2082024C1 (en) 1997-06-20

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