EP0582859A1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP0582859A1
EP0582859A1 EP93111555A EP93111555A EP0582859A1 EP 0582859 A1 EP0582859 A1 EP 0582859A1 EP 93111555 A EP93111555 A EP 93111555A EP 93111555 A EP93111555 A EP 93111555A EP 0582859 A1 EP0582859 A1 EP 0582859A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
hydraulic
pump
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
EP93111555A
Other languages
German (de)
French (fr)
Other versions
EP0582859B1 (en
Inventor
Rudolf Brunner
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Publication of EP0582859A1 publication Critical patent/EP0582859A1/en
Application granted granted Critical
Publication of EP0582859B1 publication Critical patent/EP0582859B1/en
Anticipated expiration legal-status Critical
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1 and a screw-in valve cartridge according to the preamble of claim 8.
  • control valve allows so much pressure medium to flow into the return line that the pump line is supplied at least with the quantity of pressure medium that the directional control valve requires to adjust the hydraulic consumer at the respectively desired speed when the pump is constantly pumping. Since the control valve works as a pressure compensator, there is a load-independent speed control of the hydraulic consumer.
  • control devices are e.g. used in cranes, mobile cranes or hoists, whereby a constant pump with a control valve usually supplies several directional control valves for several hydraulic consumers. The amount of pressure medium or the pressure in the pump line is then based on the highest load pressure or the highest speed at one of the directional control valves or hydraulic consumers.
  • Hydraulic control devices for similar applications are known from: DE-A-3 425 304, DE-U-9 111 569, DE-A-3 420 920, US-A-5 107 753.
  • the invention has for its object to provide a control device of the type mentioned and a screw-in valve cartridge for a control valve to effectively dampen system-related pressure vibrations and to prevent noise in the control valve.
  • the damping device works in relation to the current control pressure in the control circuit, i.e. regardless of the level of the control pressure. If, on the other hand, the pressure difference is exceeded, which is usually the case when the control pressure is reduced intentionally or by switching off at a load or stroke limit, the damping device switches off automatically. The control valve then executes the control movement quickly. There is no annoying noise.
  • the screw-in valve cartridge according to claim 8 ensures in the control valve that pressure fluctuations occurring within the pressure difference cause - if at all - only more damped control movements of the control valve which stabilize quickly. If, on the other hand, the pressure difference is exceeded, then the preloaded ball check valve responds by an opening movement to enable the control valve to move properly.
  • the screw-in valve cartridge is structurally simple, compact and reliable in its effect on the control behavior of the control valve. Thanks to its compactness, it can be arranged directly next to the control valve or in the control valve. The control movement must not be delayed or dampened; therefore the first ball check valve works without any significant preload.
  • the control movement on the other hand, should be damped within the predetermined pressure difference in order to reduce the small, rapid and disturbing pressure fluctuations as quickly as possible.
  • the biased second ball check valve does not respond within the predetermined pressure difference; however, the pressure medium is forced to pass the throttle section.
  • the preloaded ball check valve responds only when the pressure difference is exceeded for the necessary control and allows the pressure medium to flow away. This results in a raised pressure threshold for the damping, above which the damping is canceled.
  • the damping device engages again when the pressure difference is undershot. This takes place independently of the control pressure in the control circuit, because the relative pressure difference between the control pressure in the control circuit and the higher control pressure prevailing on the control side is taken into account. This results in a desirable damping of the opening movement at the end of an intended opening movement.
  • the damping throttle section responsible for damping the small and rapid pressure vibrations. Since the damping throttle section is inoperative when the predetermined pressure difference is exceeded, it can be designed for optimal and possibly strong damping of the small pressure fluctuations. Control movements of the control valve can be controlled without hindrance via the check valve opening on the control pressure side. If an upward movement of the control valve is deliberately controlled by the control circuit and the pressure difference is exceeded, the preloaded check valve with the opening direction to the control circuit bypasses the damping throttle section. The control device can automatically differentiate whether damping of the opening movement is required or not.
  • the embodiment according to claim 4 is structurally simple.
  • a spring-preloaded ball check valve is functionally reliable, compact and easily adjustable.
  • the pressure difference value of 20 bar specified in claim 5 sets the pressure threshold for the damping just as high as is required in practice for most small and rapid pressure fluctuations. Under special operating conditions of the control device, however, the pressure difference value can also be set lower or higher.
  • a particularly useful embodiment is set out in claim 6.
  • the screw-in valve cartridge, which forms the damping device, is arranged directly next to the control valve in the connection block, as a result of which long and resilient pressure medium columns between the control side of the control valve and the damping device are avoided.
  • the embodiment of the screw-in valve cartridge according to claim 9 is technically simple.
  • the valve body is an easily manufactured rotating part.
  • the ball check valves are installed in easy-to-manufacture bores that cut the channels and partially form the flow paths.
  • a hydraulic control device 1 according to FIG. 1 is used, for example, for load-independent speed control a hydraulic consumer 50, e.g. B., a double-acting cylinder in a crane or hoist in which load fluctuations or movements of components moved by the hydraulic consumer 50 may occur during operation.
  • a hydraulic consumer 50 e.g. B., a double-acting cylinder in a crane or hoist in which load fluctuations or movements of components moved by the hydraulic consumer 50 may occur during operation.
  • a constant pump 11 and a tank 51 are connected to a connection block 2 indicated by a broken line.
  • the connection block 2 is connected to at least one further connection block 3 (indicated by dashed lines), which has a directional control valve 4, here a proportional 4/2-way slide valve.
  • Two consumer lines 5, 6 lead from the directional control valve 4 to the hydraulic consumer 50.
  • the directional control valve 4 is connected to a pump line 7 and a return line 8, the pump line 7 via a main pump line 9 with the constant pump 11 and the return line 8 via a main return line 10 with the Tank 51 is connected.
  • Further directional control valves or other control valves, which are supplied by the constant pump 11, can be connected in parallel to the pump and return main lines 9, 10.
  • connection block 2 between a secondary line 9a connected to the main pump line 9 and a secondary line 10a connected to the main return line 10, a control valve 12 operating in the manner of a pressure compensator and a system pressure limiting valve 13 connected in parallel with it. Furthermore, a pressure reducing valve 14 is provided downstream of the system pressure limiting valve 13. In the connection block 2 there is a control movement damping device 15 for the control valve 12 directly next to the control valve 12.
  • an inflow controller 16 can be provided which, in addition to the control valve 12, also measures the amount of pressure medium required by the directional control valve 4.
  • a conventional pressure limiting or bias valve 17 secures the connection of a control circuit 20, 20 'to the return line 8.
  • the control circuit 20 ', 20 is supplied via load pressure tapping points 18, 19 in the consumer lines 5, 6 with a control pressure representing the respective load pressure, specifically in the control positions of the directional control valve 4.
  • the control pressure present in the control circuit 20, 20' is at the inlet regulator 16 and at the pressure relief valve 17.
  • a control valve is provided in the control circuit 20, 20 ', in the event that further connection blocks 3 with further directional control valves (not shown) are connected to the main pump and return lines 9, 10, e.g. as indicated at 20 ′′ in order to give the control valve 12 the highest control pressure in each case.
  • the control circuit 20, 20 'guided in the connection block 2 is connected via the upward movement damping device 15 to an actuating pressure side 49 of the control valve 12, specifically via a control line 25, which branches into three line branches 29, 30, 31.
  • the control valve 12 contains a valve body 22 which is infinitely adjustable between a shut-off position and a through position and which (not shown) is usually used as an orifice control piston between the secondary lines 9a, 10a and is relieved of pressure in relation to the pressures in the secondary lines 9a, 10a.
  • the two ends of the valve body 22 define a control side 49 and a control side 48.
  • a control line 23 is connected to the control pressure side 48 of the control valve 12, in which the pressure in the secondary line 9a (the pump pressure) is effective via a throttle.
  • the control line 25 is connected to the control pressure side 49.
  • the force of a control spring 24 acts on the control side 49.
  • the control valve 12 works as a pressure compensator, which weighs the pressures in the control lines 23 and 25 plus the force of the spring 24 against one another and, depending on the pressure difference between the two sides 48, 49, a specific one Takes position automatically.
  • a throttle section 26 is provided in the branch line 29, which can be bypassed in the flow direction to the control pressure side 49 by a check valve 28. In the opposite flow direction, the throttle section 26 can be bypassed by a prestressed pressure limiting valve 27 or a prestressed check valve, the prestressing being generated mechanically by a spring 42.
  • a throttle 32 is assigned to the control movement damping device 15 in the control circuit 20.
  • the control device 1 works as follows: Assuming that the directional control valve 4 is in the neutral position shown and any other directional control valves provided are also in their neutral positions, the control circuit 20 is relieved. The pressure in the control line 23 overcomes the force of the spring 24, the valve member 22 is in the open position. The secondary lines 9a, 10a are connected to one another; the entire delivered quantity of the constant pump 11 flows out to the tank 51.
  • the pump line 7 is connected to the consumer line 5 and the consumer line 6 to the return line 8.
  • the inflow controller 16 opens because, for example, a control pressure builds up in the control circuit 20 ′, 20 via the load pressure tap 18.
  • the shuttle valve 21 assumes the position shown, in which the control pressure is applied via the check valve 28 and the control line 25 on the control pressure side 49.
  • the force of the spring 24 and the pressure on the control side 49 overcome the force in the control line 23 on the control pressure side 48; the valve member 22, for example, initially goes into the shut-off position.
  • the delivery rate of the constant pump 11 reaches the main pump line 9. From this, the inflow controller 16 measures the amount required to move the hydraulic consumer 50 to the directional control valve 4.
  • the valve member 22 assumes an intermediate position in which the inflow controller 16 is supplied with at least the amount that it has to meter to the directional control valve 4.
  • the preloaded pressure relief valve 27 blocks. Should, for example, caused by the load on the hydraulic consumer 50, small rapid pressure fluctuations in the consumer line 5 are caused, they propagate into the control circuit 20. They then take effect in the control line 25 on the control pressure side 49. At any amplitude of a pressure fluctuation at which the control pressure in the control circuit 20 drops relative to the pressure present on the control pressure side 49, the pressure medium must flow back from the control pressure side 49 via the throttle section 26 in the branch line 29 to the control circuit 20. The amplitude is attenuated.
  • control movement damping device 15 for a control valve 12 is described with reference to FIG. 2.
  • the control valve 12 is contained in the connection block 2.
  • a screw-in valve cartridge 44 is screwed into a threaded bore 33 of the connection block 2 that cuts the control line 25 to the supply pressure side 49 and has a screw-shaped valve body 47 with an internal external threaded section 35 and a further external threaded section used for screwing in and sealing the threaded bore 33.
  • the threaded bore 33 is penetrated axially spaced apart from the control line 25 by the control circuit 20.
  • mutually offset bores 38, 39 are made, which cut the branch lines 30, 31 and define valve seats 54, 53 for two check valves 27, 28 opening in opposite directions with bore shoulders.
  • a strong and long closing spring 42 is provided for the check valve 27.
  • a weak closing spring 43 is provided for the check valve 28.
  • a flow path is provided in the interior of the valve body 47 between two axially spaced connections 36 and 37 (the connection 37 simultaneously forms the throttle 32). which branches into two channels, each channel containing one of the ball check valves 27, 28.
  • the throttle section 26, which is parallel to the check valves 27, 28, is formed by the external thread section 35 of the valve body 47, which cooperates with an internal thread 34 of the threaded bore 33.
  • the result is a slim and short screw-in valve cartridge 44 which is sealed in the threaded bore 43 by means of a sealing ring 45 under a widened head of the valve body 47.
  • the throttle section 26 could also be formed by other throttling elements (throttle channel, throttle valve, orifice openings, throttle gap or the like).
  • the pressure medium from the control circuit 20 enters the bore 38 through the throttle 32 and the connection opening 37.
  • the check valve 27 is closed.
  • the pressure medium then reaches the branch line 31 and opens the check valve 28, past which it reaches the connection opening 36 and thus the control line 25.
  • the pressure medium is present at both ends of the external thread section 35. If the pressure in the control circuit 20 is lower than the control pressure on the pilot pressure side 49, pressure medium flows into the connection opening 36.
  • the check valve 28 closes.
  • the closing spring 42 prevents the check valve 27 from opening until the predetermined pressure difference is reached.
  • the pressure medium is forced to bypass the closed check valve 27 via the throttle section 26 and then to flow back into the control circuit 20 via the bore 38, the connection opening 37 and the throttle 32.
  • the check valve 27 only opens when the preset pressure difference (force of the closing spring (42) is overcome.
  • the control pressure side 49 becomes rapid relieved.
  • the check valve 27 closes again.
  • the pressure medium flows in a damped manner via the throttle section 26.
  • the throttle section 26 is designed in such a way that it produces an optimal damping of the amplitudes in the event of pressure fluctuations within the predetermined pressure difference, and is largely independent of viscosity.
  • the check valves 27, 28 and the throttle section 26 could be formed in separate control elements.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

A hydraulic control device (1), comprising at least one directional control valve (4) which is connected to a pump and return line (7, 9; 8, 10) and from which at least one consumer line (5, 6) leads to a hydraulic consumer (50), a fixed displacement pump (11) supplying a pump line (7, 9) via a regulating valve (12), and a control-pressure circuit (20) in which a control pressure dependent upon the load pressure in the consumer line (5, 6) can be controlled, the regulating valve (12) of which can be acted upon on a closing-pressure side (49) by the control pressure from the control circuit (20) and by spring force (24) as well as on an opening-pressure side (48) by the pump pressure, has a hydraulic, mechanically preloaded, opening-movement damping device (15) between the closing-pressure side (49) and the control circuit (20), which opening-movement damping device (15) can be automatically cut out if a predetermined pressure difference between the higher control pressure applied to the closing-pressure side (49) and the lower control pressure prevailing in the control circuit (20) is exceeded. <IMAGE>

Description

Die Erfindung betrifft eine hydraulische Steuervorrichtung der im Oberbegriff des Anspruchs 1 angegebenen Art sowie eine Einschraubventilpatrone gemäß Oberbegriff von Anspruch 8.The invention relates to a hydraulic control device of the type specified in the preamble of claim 1 and a screw-in valve cartridge according to the preamble of claim 8.

Bei solchen Steuervorrichtungen läßt das Regelventil soviel Druckmittel in die Rücklaufleitung abströmen, daß bei konstant fördernder Pumpe die Pumpenleitung zumindest mit der Druckmittelmenge versorgt wird, die das Wegesteuerventil benötigt, um den Hydroverbraucher mit der jeweils gewünschten Geschwindigkeit zu verstellen. Da das Regelventil als Druckwaage arbeitet, ergibt sich eine lastunabhängige Geschwindigkeitssteuerung des Hydroverbrauchers. Diese Steuervorrichtungen werden, z.B. in Kränen, Mobilkränen oder Hebezeugen verwendet, wobei eine Konstantpump mit einem Regelventil zumeist mehrere Wegesteuerventile für mehrere Hydroverbraucher versorgt. Die Druckmittelmenge oder der Druck in der Pumpenleitung richtet sich dann nach dem höchsten Lastdruck bzw. der größten Geschwindigkeit bei einem der Wegesteuerventile bzw. Hydroverbraucher. In der Praxis lassen sich Lastdruckschwankungen nicht vermeiden, die zum Regelventil zurückwirken, was wiederum zu Druckschwingungen in der Pumpenleitung fuhren kann. Besonders unerwünscht sind relativ kleine und rasche Druckschwingungen im Steuerkreis, auf die das Regelventil mit zuckenden Aufsteuerbewegungen reagiert, was am Hydroverbraucher spürbar sein kann und sich durch eine beunruhigende Geräuschentwicklung im Regelventil bemerkbar macht.In such control devices, the control valve allows so much pressure medium to flow into the return line that the pump line is supplied at least with the quantity of pressure medium that the directional control valve requires to adjust the hydraulic consumer at the respectively desired speed when the pump is constantly pumping. Since the control valve works as a pressure compensator, there is a load-independent speed control of the hydraulic consumer. These control devices are e.g. used in cranes, mobile cranes or hoists, whereby a constant pump with a control valve usually supplies several directional control valves for several hydraulic consumers. The amount of pressure medium or the pressure in the pump line is then based on the highest load pressure or the highest speed at one of the directional control valves or hydraulic consumers. In practice, load pressure fluctuations can not be avoided, which affect the control valve, which in turn can lead to pressure fluctuations in the pump line. Relatively small and rapid pressure fluctuations in the control circuit, to which the control valve reacts with jerky control movements, are particularly undesirable, which can be felt by the hydraulic consumer and is noticeable by a disturbing noise development in the control valve.

Hydraulische Steuervorrichtungen für ähnliche Anwendungsfälle sind bekannt aus: DE-A-3 425 304, DE-U-9 111 569, DE-A-3 420 920, US-A-5 107 753.Hydraulic control devices for similar applications are known from: DE-A-3 425 304, DE-U-9 111 569, DE-A-3 420 920, US-A-5 107 753.

Der Erfindung liegt die Aufgabe zugrunde, eine Steuervorrichtung der eingangs genannten Art sowie eine Einschraubventilpatrone für ein Regelventil zu schaffen, um systembedingte Druckschwingungen wirksam abzudämpfen und um eine Geräuschentwicklung im Regelventil zu verhindern.The invention has for its object to provide a control device of the type mentioned and a screw-in valve cartridge for a control valve to effectively dampen system-related pressure vibrations and to prevent noise in the control valve.

Die gestellte Aufgabe wird mit den im Patentanspruch 1 und den im nebengeordneten Anspruch 8 enthaltenen Merkmalen gelöst.The object is achieved with the features contained in claim 1 and in the independent claim 8.

Solange bei Druckschwingungen im Steuerkreis die Druckschwingungsamplituden die vorbestimmbare Druckdifferenz nicht erreichen, werden sie rasch abgedämpft, so daß das Regelventil zuckende Aufsteuerbewegungen unterläßt. Dabei arbeitet die Dämpfeinrichtung jeweils in Relation zum momentanen Steuerdruck im Steuerkreis, d.h., unabhängig von der Höhe des Steuerdrucks. Wird hingegen die Druckdifferenz überschritten, was in der Regel im bei einer gewollten Absenkung des Steuerdrucks oder durch Abschalten an einer Lastoder Hubgrenze erfolgt, dann schaltet sich die Dämpfeinrichtung selbsttätig aus. Das Regelventil führt dann die Aufsteuerbewegung zügig aus. Eine störende Geräuschentwicklung unterbleibt.As long as the pressure oscillation amplitudes do not reach the predeterminable pressure difference in the case of pressure vibrations in the control circuit, they are quickly damped, so that the control valve stops twitching control movements. The damping device works in relation to the current control pressure in the control circuit, i.e. regardless of the level of the control pressure. If, on the other hand, the pressure difference is exceeded, which is usually the case when the control pressure is reduced intentionally or by switching off at a load or stroke limit, the damping device switches off automatically. The control valve then executes the control movement quickly. There is no annoying noise.

Die Einschraubventilpatrone gemäß Anspruch 8 sorgt im Regelventil dafür, daß innerhalb der Druckdifferenz ablaufende Druckschwingungen wegen der Drosselstrecke - wenn überhaupt - nur mehr gedämpfte Aufsteuerbewegungen des Regelventils bewirken, die sich rasch stabilisieren. Wird hingegen die Druckdifferenz überschritten, dann spricht das vorgespannte Kugelrückschlagventil durch eine Öffnungsbewegung an, um die ordnungsgemäße Aufsteuerbewegung des Regelventils zu ermöglichen. Die Einschraubventilpatrone ist baulich einfach, kompakt und in ihrer Auswirkung auf das Regelverhalten des Regelventils zuverlässig. Dank ihrer Kompaktheit läßt sie sich unmittelbar beim Regelventil oder im Regelventil anordnen. Die Zusteuerbewegung darf nicht verzögert oder gedämpft werden; deshalb arbeitet das erste Kugelrückschlagventil ohne nennenswerte Vorspannung. Die Aufsteuerbewegung soll hingegen innerhalb der vorbestimmten Druckdifferenz gedämpft erfolgen, um die kleinen, raschen und störenden Druckschwingungen möglichst schnell abzubauen. Deshalb spricht das vorgespannte zweite Kugelrückschlagventil innerhalb der vorbestimmten Druckdifferenz nicht an; das Druckmittel wird jedoch zum Passieren der Drosselstrecke gezwungen. Erst wenn zum erforderlichen Aufsteuern die Druckdifferenz überschritten wird, spricht das vorgespannte Kugelrückschlagventil an und läßt das Druckmittel abströmen. Es ergibt sich sozusagen eine hochgesetzte Druckschwelle für die Dämpfung, oberhalb deren die Dämpfung aufgehoben ist.The screw-in valve cartridge according to claim 8 ensures in the control valve that pressure fluctuations occurring within the pressure difference cause - if at all - only more damped control movements of the control valve which stabilize quickly. If, on the other hand, the pressure difference is exceeded, then the preloaded ball check valve responds by an opening movement to enable the control valve to move properly. The screw-in valve cartridge is structurally simple, compact and reliable in its effect on the control behavior of the control valve. Thanks to its compactness, it can be arranged directly next to the control valve or in the control valve. The control movement must not be delayed or dampened; therefore the first ball check valve works without any significant preload. The control movement, on the other hand, should be damped within the predetermined pressure difference in order to reduce the small, rapid and disturbing pressure fluctuations as quickly as possible. Therefore, the biased second ball check valve does not respond within the predetermined pressure difference; however, the pressure medium is forced to pass the throttle section. The preloaded ball check valve responds only when the pressure difference is exceeded for the necessary control and allows the pressure medium to flow away. This results in a raised pressure threshold for the damping, above which the damping is canceled.

Bei der Ausführungsform der Steuervorrichtung gemäß Anspruch 2 greift die Dämpfvorrichtung wieder ein, wenn die Druckdifferenz unterschritten wird. Dies erfolgt unabhängig vom Steuerdruck im Steuerkreis, weil die relative Druckdifferenz zwischen dem Steuerdruck im Steuerkreis und dem an der Zusteuerseite herrschenden höheren Steuerdruck berücksichtigt wird. Dadurch ergibt sich am Ende einer gewollten Aufsteuerbewegung eine wünschenswerte Abdämpfung der Aufsteuerbewegung.In the embodiment of the control device according to claim 2, the damping device engages again when the pressure difference is undershot. This takes place independently of the control pressure in the control circuit, because the relative pressure difference between the control pressure in the control circuit and the higher control pressure prevailing on the control side is taken into account. This results in a desirable damping of the opening movement at the end of an intended opening movement.

Bei der Ausführungsform gemäß Anspruch 3 ist die Dämpfdrosselstrecke für die Dämpfung der kleinen und raschen Druckschwingungen verantwortlich. Da die Dämpfdrosselstrecke ab Überschreiten der vorbestimmten Druckdifferenz außer Funktion ist, läßt sie sich für eine optimale und gegebenenfalls kräftige Dämpfung der kleinen Druckschwingungen auslegen. Zusteuerbewegungen des Regelventils lassen sich über das zur Zusteuerdruckseite öffnende Rückschlagventil ungehindert einsteuern. Wird eine Aufsteuerbewegung des Regelventils bewußt vom Steuerkreis her eingesteuert und dabei die Druckdifferenz überschritten, dann umgeht das vorgespannte Rückschlagventil mit Öffnungsrichtung zum Steuerkreis die Dämpfdrosselstrecke. Die Steuervorrichtung kann selbsttätig unterscheiden, ob eine Dämpfung der Aufsteuerbewegung gebraucht wird, oder nicht.In the embodiment according to claim 3, the damping throttle section responsible for damping the small and rapid pressure vibrations. Since the damping throttle section is inoperative when the predetermined pressure difference is exceeded, it can be designed for optimal and possibly strong damping of the small pressure fluctuations. Control movements of the control valve can be controlled without hindrance via the check valve opening on the control pressure side. If an upward movement of the control valve is deliberately controlled by the control circuit and the pressure difference is exceeded, the preloaded check valve with the opening direction to the control circuit bypasses the damping throttle section. The control device can automatically differentiate whether damping of the opening movement is required or not.

Baulich einfach ist die Ausführungsform gemaß Anspruch 4. Ein federvorgespanntes Kugelrückschlagventil ist funktionssicher, kompakt und leicht einstellbar.The embodiment according to claim 4 is structurally simple. A spring-preloaded ball check valve is functionally reliable, compact and easily adjustable.

Der in Anspruch 5 angegebene Druckdifferenzwert von 20 Bar legt die Druckschwelle für die Dämpfung gerade so hoch, wie sie in der Praxis für die meisten kleinen und raschen Druckschwingungen erforderlich ist. Unter speziellen Einsatzbedingungen der Steuervorrichtung kann der Druckdifferenzwert jedoch auch niedriger oder höher eingestellt werden.The pressure difference value of 20 bar specified in claim 5 sets the pressure threshold for the damping just as high as is required in practice for most small and rapid pressure fluctuations. Under special operating conditions of the control device, however, the pressure difference value can also be set lower or higher.

Eine besonders zweckmäßige Ausführungsform geht aus Anspruch 6 hervor. Die Einschraubventilpatrone, die die Dämpfeinrichtung bildet, ist unmittelbar beim Regelventil im Anschlußblock angordnet, wodurch lange und federnde Druckmittelsäulen zwischen der Zusteuerseite des Regelventils und der Dämpfeinrichtung vermieden werden.A particularly useful embodiment is set out in claim 6. The screw-in valve cartridge, which forms the damping device, is arranged directly next to the control valve in the connection block, as a result of which long and resilient pressure medium columns between the control side of the control valve and the damping device are avoided.

Eine besonders zweckmäßige, weil kleinbauende und einfache Ausführungsform geht aus Anspruch 7 hervor. Dank der nebeneinanderliegenden Rückschlagventile ergibt sich eine geringe Einbautiefe bei ausreichendem Durchgangsquerschnitt. Da die Dämpfdrosselstrecke sozusagen am Außenumfang der Einschraubventilpatrone angeordnet ist, wird auch in Durchmesserrichtung Platz gespart.A particularly expedient because of its small size and simple embodiment is set out in claim 7. Thanks to the side-by-side check valves, there is a small installation depth with a sufficient passage cross-section. Since the damping throttle section is arranged, so to speak, on the outer circumference of the screw-in valve cartridge, space is also saved in the diameter direction.

Die Ausführungsform der Einschraubventilpatrone gemäß Anspruch 9 ist herstellungstechnisch einfach. Der Ventilkörper ist ein einfach herstellbarer Drehteil. Die Kugelrückschlagventile sind in einfach herstellbaren Bohrungen montiert, die die Kanäle schneiden und die Strömungswege zum Teil ausbilden.The embodiment of the screw-in valve cartridge according to claim 9 is technically simple. The valve body is an easily manufactured rotating part. The ball check valves are installed in easy-to-manufacture bores that cut the channels and partially form the flow paths.

Anhand der Zeichnung wird eine Ausführungsform des Erfindungsgegenstandes erläutert. Es zeigt:

Fig. 1
ein Blockschaltbild eines Teils einer hydraulischen Steuervorrichtung, und
Fig. 2
eine konkrete Ausführungsform einer in der Steuervorrichtung von Fig. 1 vorgesehenen Dämpfeinrichtung in Form einer Einschraubventilpatrone.
An embodiment of the subject matter of the invention is explained with the aid of the drawing. It shows:
Fig. 1
a block diagram of part of a hydraulic control device, and
Fig. 2
a concrete embodiment of a damping device provided in the control device of FIG. 1 in the form of a screw-in valve cartridge.

Eine hydraulische Steuervorrichtung 1 gemäß Fig. 1 dient beispielsweise zur lastunabhängigen Geschwindigkeitssteuerung eines Hydroverbrauchers 50, z. B., eines doppeltwirkenden Arbeitszylinders in einem Kran oder Hebezeug, bei dem im Betrieb Lastschwankungen oder Bewegungen von durch den Hydroverbraucher 50 bewegten Komponenten auftreten können.A hydraulic control device 1 according to FIG. 1 is used, for example, for load-independent speed control a hydraulic consumer 50, e.g. B., a double-acting cylinder in a crane or hoist in which load fluctuations or movements of components moved by the hydraulic consumer 50 may occur during operation.

An einen strichliert angedeuteten Anschlußblock 2 sind eine Konstantpumpe 11 und ein Tank 51 angeschlossen. Der Anschlußblock 2 ist mit wenigstens einem weiteren Anschlußblock 3 (strichliert angedeutet) verbunden, der ein Wegesteuerventil 4, hier ein Proportional-4/2-Wege-Schieberventil, aufweist. Vom Wegesteuerventil 4 führen zwei Verbraucherleitungen 5, 6 zum Hydroverbraucher 50. Ferner ist das Wegesteuerventil 4 an eine Pumpenleitung 7 und eine Rücklaufleitung 8 angeschlossen, wobei die Pumpenleitung 7 über eine Pumpenhauptleitung 9 mit der Konstantpumpe 11 und die Rücklaufleitung 8 über eine Hauptrücklaufleitung 10 mit dem Tank 51 verbunden ist. An die Pumpen- und Rücklaufhauptleitungen 9, 10 können parallel weitere Wegesteuerventile oder andere Steuerventile angeschlossen sein, die von der Konstantpumpe 11 versorgt werden.A constant pump 11 and a tank 51 are connected to a connection block 2 indicated by a broken line. The connection block 2 is connected to at least one further connection block 3 (indicated by dashed lines), which has a directional control valve 4, here a proportional 4/2-way slide valve. Two consumer lines 5, 6 lead from the directional control valve 4 to the hydraulic consumer 50. Furthermore, the directional control valve 4 is connected to a pump line 7 and a return line 8, the pump line 7 via a main pump line 9 with the constant pump 11 and the return line 8 via a main return line 10 with the Tank 51 is connected. Further directional control valves or other control valves, which are supplied by the constant pump 11, can be connected in parallel to the pump and return main lines 9, 10.

Im Anschlußblock 2 ist zwischen einer an die Hauptpumpenleitung 9 angeschlossenen Nebenleitung 9a und einer an die Hauptrücklaufleitung 10 angeschlossenen Nebenleitung 10a ein nach Art einer Druckwaage arbeitendes Regelventil 12 sowie zu diesem parallel ein Systemdruck-Begrenzungsventil 13 eingeschaltet. Ferner ist stromab zum Systemdruck-Begrenzungsventil 13 ein Druckminderventil 14 vorgesehen. Im Anschlußblock 2 befindet sich unmittelbar beim Regelventil 12 eine Aufsteuerbewegungs-Dämpfeinrichtung 15 für das Regelventil 12.In the connection block 2, between a secondary line 9a connected to the main pump line 9 and a secondary line 10a connected to the main return line 10, a control valve 12 operating in the manner of a pressure compensator and a system pressure limiting valve 13 connected in parallel with it. Furthermore, a pressure reducing valve 14 is provided downstream of the system pressure limiting valve 13. In the connection block 2 there is a control movement damping device 15 for the control valve 12 directly next to the control valve 12.

In der Pumpenleitung 7 zum Wegesteuerventil 4 kann ein Zulaufregler 16 vorgesehen sein, der zusätzlich zum Regelventil 12 dem Wegesteuerventil 4 die benötigte Druckmittelmenge zumißt. Ein übliches Druckbegrenzungs- oder Vorspannventil 17 sichert die Verbindung eines Steuerkreises 20, 20' zur der Rücklaufleitung 8.In the pump line 7 to the directional control valve 4, an inflow controller 16 can be provided which, in addition to the control valve 12, also measures the amount of pressure medium required by the directional control valve 4. A conventional pressure limiting or bias valve 17 secures the connection of a control circuit 20, 20 'to the return line 8.

Der Steuerkreis 20', 20 wird über Lastdruck-Anzapfstellen 18, 19 in den Verbraucherleitungen 5, 6 mit einem den jeweiligen Lastdruck repräsentierenden Steuerdruck versorgt, und zwar in den Steuerstellungen des Wegesteuerventils 4. Der im Steuerkreis 20, 20' anstehende Steuerdruck steht am Zulaufregler 16 und am Druckbegrenzungsventil 17 an. Im Steuerkreis 20, 20' ist ein Wechselventil vorgesehen, für den Fall, daß weitere Anschlußblöcke 3 mit weiteren Wegesteuerventilen (nicht gezeigt) an die Pumpen- und Rücklaufhauptleitungen 9, 10 angeschlossen sind, z.B. wie bei 20'' angedeutet, um dem Regelventil 12 den jeweils höchsten Steuerdruck aufzugeben.The control circuit 20 ', 20 is supplied via load pressure tapping points 18, 19 in the consumer lines 5, 6 with a control pressure representing the respective load pressure, specifically in the control positions of the directional control valve 4. The control pressure present in the control circuit 20, 20' is at the inlet regulator 16 and at the pressure relief valve 17. A control valve is provided in the control circuit 20, 20 ', in the event that further connection blocks 3 with further directional control valves (not shown) are connected to the main pump and return lines 9, 10, e.g. as indicated at 20 ″ in order to give the control valve 12 the highest control pressure in each case.

Der in den Anschlußblock 2 geführte Steuerkreis 20, 20' ist über die Aufsteuerbewegungs-Dämpfeinrichtung 15 an eine Zusteuerdruckseite 49 des Regelventils 12 angeschlossen, und zwar über eine Steuerleitung 25, die sich in drei Leitungszweige 29, 30, 31 aufzweigt. Das Regelventil 12 enthält einen zwischen einer Absperrstellung und einer Durchgangsstellung stufenlos verstellbaren Ventilkörper 22, der (nicht gezeigt) üblicherweise als Blenden-Regelkolben zwischen die Nebenleitungen 9a, 10a eingesetzt und gegenüber den Drücken in den Nebenleitungen 9a, 10a druckentlastet ist. Die beiden Enden des Ventilkörpers 22 definieren eine Zusteuerseite 49 und eine Aufsteuerseite 48. Dies bedeutet, daß eine am Ventilkörper 22 an der Zusteuerseite 49 wirkende Kraft das Regelventil 12 in die Absperrstellung zu bringen sucht, in der die gesamte von der Konstantpumpe 11 gelieferte Menge in die Hauptpumpenleitung 9 strömt, während Druck an der Aufsteuerdruckseite 48 den Ventilkörper 22 in eine Durchgangsstellung zu verstellen sucht, in der entweder die gesamte Fördermenge der Konstantpumpe 11 oder nur ein Teil in die Nebenleitung 10a zum Tank 51 abströmt.The control circuit 20, 20 'guided in the connection block 2 is connected via the upward movement damping device 15 to an actuating pressure side 49 of the control valve 12, specifically via a control line 25, which branches into three line branches 29, 30, 31. The control valve 12 contains a valve body 22 which is infinitely adjustable between a shut-off position and a through position and which (not shown) is usually used as an orifice control piston between the secondary lines 9a, 10a and is relieved of pressure in relation to the pressures in the secondary lines 9a, 10a. The two ends of the valve body 22 define a control side 49 and a control side 48. This means that one on the valve body 22 force acting on the control side 49 tries to bring the control valve 12 into the shut-off position, in which the entire quantity supplied by the constant pump 11 flows into the main pump line 9, while pressure on the pilot pressure side 48 tries to move the valve body 22 into a through position, in which either flows the entire flow rate of the constant pump 11 or only a part into the secondary line 10a to the tank 51.

An der Aufsteuerdruckseite 48 des Regelventils 12 ist eine Steuerleitung 23 angeschlossen, in der der Druck in der Nebenleitung 9a (der Pumpendruck) über eine Drossel wirksam ist. An der Zusteuerdruckseite 49 ist hingegen die Steuerleitung 25 angeschlossen. Ferner wirkt an der Zusteuerseite 49 die Kraft einer Regelfeder 24. Das Regelventil 12 arbeitet als Druckwaage, die die Drücke in den Steuerleitungen 23 und 25 zuzüglich der Kraft der Feder 24 gegeneinander abwiegt und abhängig von der Druckdifferenz zwischen den beiden Seiten 48, 49 eine bestimmte Stellung selbsttätig einnimmt.A control line 23 is connected to the control pressure side 48 of the control valve 12, in which the pressure in the secondary line 9a (the pump pressure) is effective via a throttle. On the other hand, the control line 25 is connected to the control pressure side 49. Furthermore, the force of a control spring 24 acts on the control side 49. The control valve 12 works as a pressure compensator, which weighs the pressures in the control lines 23 and 25 plus the force of the spring 24 against one another and, depending on the pressure difference between the two sides 48, 49, a specific one Takes position automatically.

In der Aufsteuerbewegungs-Dämpfeinrichtung 15 ist in der Zweigleitung 29 eine Drosselstrecke 26 vorgesehen, die in Strömungsrichtung zur Zusteuerdruckseite 49 durch ein Rückschlagventil 28 umgehbar ist. In der entgegengesetzten Strömungsrichtung läßt sich die Drosselstrecke 26 durch ein vorgespanntes Druckbegrenzungsventil 27 oder ein vorgespanntes Rückschlagventil umgehen, wobei die Vorspannung durch eine Feder 42 mechanisch erzeugt wird. Im Steuerkreis 20 ist der Aufsteuerbewegungs-Dämpfeineinrichtung 15 eine Drossel 32 zugeordnet.In the control movement damping device 15, a throttle section 26 is provided in the branch line 29, which can be bypassed in the flow direction to the control pressure side 49 by a check valve 28. In the opposite flow direction, the throttle section 26 can be bypassed by a prestressed pressure limiting valve 27 or a prestressed check valve, the prestressing being generated mechanically by a spring 42. A throttle 32 is assigned to the control movement damping device 15 in the control circuit 20.

Die Steuervorrichtung 1 arbeitet wie folgt:
Unter der Annahme, daß das Wegesteuerventil 4 in der dargestellten Neutralstellung steht und eventuell weitere vorgesehene Wegesteuerventile ebenfalls in ihren Neutralstellungen stehen, ist der Steuerkreis 20 entlastet. Der Druck in der Steuerleitung 23 überwindet die Kraft der Feder 24, das Ventilglied 22 steht in der Durchgangsstellung. Die Nebenleitungen 9a, 10a sind miteinander verbunden; die gesamte geförderte Menge der Konstantpumpe 11 strömt zum Tank 51 ab.The control device 1 works as follows:
Assuming that the directional control valve 4 is in the neutral position shown and any other directional control valves provided are also in their neutral positions, the control circuit 20 is relieved. The pressure in the control line 23 overcomes the force of the spring 24, the valve member 22 is in the open position. The secondary lines 9a, 10a are connected to one another; the entire delivered quantity of the constant pump 11 flows out to the tank 51.

Wird das Wegesteuerventil 4 in Fig. 1 nach unten verstellt, dann wird die Pumpenleitung 7 mit der Verbraucherleitung 5 und die Verbraucherleitung 6 mit der Rücklaufleitung 8 verbunden. Der Zulaufregler 16 öffnet, da sich z.B. über die Lastdruckanzapfung 18 im Steuerkreis 20', 20 ein Steuerdruck aufbaut. Das Wechselventil 21 nimmt die dargestellte Lage ein, in der der Steuerdruck über das Rückschlagventil 28 und die Steuerleitung 25 an der Zusteuerdruckseite 49 ansteht. Die Kraft der Feder 24 und der Druck an der Zusteuerseite 49 überwinden die Kraft in der Steuerleitung 23 an der Aufsteuerdruckseite 48; das Ventilglied 22, geht z.B. zunächst, in die Absperrstellung. Die Fördermenge der Konstantpumpe 11 gelangt in die Pumpenhauptleitung 9. Daraus mißt der Zulaufregler 16 die zum Bewegen des Hydroverbrauchers 50 erforderliche Menge dem Wegesteuerventil 4 zu. In Abhängigkeit von dem sich im Steuerkreis 20 aufbauenden Steuerdruck nimmt das Ventilglied 22 eine Zwischenstellung ein, in der dem Zulaufregler 16 jeweils mindestens die Menge zugeführt wird, die er dem Wegesteuerventil 4 zuzumessen hat. Das vorgespannte Druckbegrenzungsventil 27 sperrt. Sollten nun, z.B. veranlaßt durch die Last am Hydroverbraucher 50, kleine rasche Druckschwankungen in der Verbraucherleitung 5 hervorgerufen werden, so pflanzen sich diese in den Steuerkreis 20 fort. Sie werden dann in der Steuerleitung 25 an der Zusteuerdruckseite 49 wirksam. Bei jeder Amplitude einer Druckschwankung, bei der der Steuerdruck im Steuerkreis 20 relativ zum an der Zusteuerdruckseite 49 anstehenden Druck abfällt, muß das Druckmittel von der Zusteuerdruckseite 49 über die Drosselstrecke 26 in der Zweigleitung 29 zum Steuerkreis 20 zurückströmen. Dabei wird die Amplitude abgedämpft. Erst wenn die Druckdifferenz zwischen dem höheren Steuerdruck an der Zusteuerdruckseite 49 und dem Steuerkreis 20 die durch die Feder 42 eingestellte Druckdifferenz überschreitet, wird das Druckbegrenzungsventil 27 geöffnet; das Druckmittel strömt unter Umgehung der Drosselstrecke 26 ab. Eine derart starke Druckabsenkung im Steuerkreis 20 wird entweder dadurch hervorgerufen, daß das Wegesteuerventil 4 in die gezeigte Grundstellung zurückgeführt oder daß der Steuerdruck im Steuerkreis 20 durch ein nicht dargestelltes Überlastventil an einer Last- oder Hubgrenze rasch und weitgehend abgebaut wird. Das Regelventil 12 öffnet rasch, um die Konstantpumpe 11 mit dem Tank zu verbinden. Gegen Ende der Aufsteuerbewegung des Ventilgliedes 22 nach einer solch großen Druckdifferenz schließt das Druckbegrenzungsventil 27 wieder, so daß dann die Drosselstrecke 26 erneut zur Wirkung kommt und die Zusteuerbewegung am Ende abdämpft.If the directional control valve 4 in FIG. 1 is adjusted downward, then the pump line 7 is connected to the consumer line 5 and the consumer line 6 to the return line 8. The inflow controller 16 opens because, for example, a control pressure builds up in the control circuit 20 ′, 20 via the load pressure tap 18. The shuttle valve 21 assumes the position shown, in which the control pressure is applied via the check valve 28 and the control line 25 on the control pressure side 49. The force of the spring 24 and the pressure on the control side 49 overcome the force in the control line 23 on the control pressure side 48; the valve member 22, for example, initially goes into the shut-off position. The delivery rate of the constant pump 11 reaches the main pump line 9. From this, the inflow controller 16 measures the amount required to move the hydraulic consumer 50 to the directional control valve 4. Depending on the control pressure building up in the control circuit 20, the valve member 22 assumes an intermediate position in which the inflow controller 16 is supplied with at least the amount that it has to meter to the directional control valve 4. The preloaded pressure relief valve 27 blocks. Should, for example, caused by the load on the hydraulic consumer 50, small rapid pressure fluctuations in the consumer line 5 are caused, they propagate into the control circuit 20. They then take effect in the control line 25 on the control pressure side 49. At any amplitude of a pressure fluctuation at which the control pressure in the control circuit 20 drops relative to the pressure present on the control pressure side 49, the pressure medium must flow back from the control pressure side 49 via the throttle section 26 in the branch line 29 to the control circuit 20. The amplitude is attenuated. Only when the pressure difference between the higher control pressure on the supply pressure side 49 and the control circuit 20 exceeds the pressure difference set by the spring 42, the pressure limiting valve 27 is opened; the pressure medium flows out bypassing the throttle section 26. Such a sharp drop in pressure in the control circuit 20 is caused either by the fact that the directional control valve 4 is returned to the basic position shown or that the control pressure in the control circuit 20 is rapidly and largely reduced by an overload valve (not shown) at a load or stroke limit. The control valve 12 opens quickly to connect the constant pump 11 to the tank. Towards the end of the opening movement of the valve member 22 after such a large pressure difference, the pressure limiting valve 27 closes again, so that the throttle section 26 then comes into effect again and dampens the control movement at the end.

Unter der Annahme, daß die Vorspannung der Feder 22 des Druckbegrenzungsventils 27 ca. 20 Bar beträgt, werden kleine und rasche Druckschwingungen, in denen diese Druckdifferenz nicht überschritten wird, über die Drosselstrecke 26 wirksam abgedämpft. Ein ansonsten bei den zuckenden oder vibrierenden Bewegungen des Ventilgliedes im Regelventil entstehende störende Geräusch entfällt. Ferner unterbleiben störende Druckschwankungen in der Pumpenhauptleitung 9 und in den Pumpenleitungen 7 zu den Wegesteuerventilen, was der Gleichmäßigkeit der Bewegung der angeschlossenen Hydroverbraucher zugute kommt.Assuming that the bias of the spring 22 of the pressure relief valve 27 is approximately 20 bar, small and rapid pressure fluctuations, in which this pressure difference is not exceeded, are effectively damped via the throttle section 26. An annoying noise that otherwise occurs during the twitching or vibrating movements of the valve member in the control valve is eliminated. Furthermore, there are no disturbing pressure fluctuations in the main pump line 9 and in the pump lines 7 to the directional control valves, which benefits the uniformity of the movement of the connected hydraulic consumers.

Anhand von Fig. 2 wird eine konkrete Ausführungsform der Aufsteuerbewegungs-Dämpfeinrichtung 15 für ein Regelventil 12 beschrieben.A specific embodiment of the control movement damping device 15 for a control valve 12 is described with reference to FIG. 2.

Das Regelventil 12 ist im Anschlußblock 2 enthalten. In eine die Steuerleitung 25 zur Zusteuerdruckseite 49 anschneidende Gewindebohrung 33 des Anschlußblocks 2 ist eine Einschraub-Ventilpatrone 44 eingeschraubt, die einen schraubenförmigen Ventilkörper 47 mit einem innenliegenden Außengewindeabschnitt 35 und einen weiter außenliegenden, zum Einschrauben und Abdichten der Gewindebohrung 33 benutzten Gewindeabschnitt aufweist. Die Gewindebohrung 33 wird axial von der Steuerleitung 25 beabstandet vom Steuerkreis 20 durchsetzt. In den Ventilkörper 47 sind von beiden Enden ausgehende, zueinander versetzte Bohrungen 38, 39 eingebracht, die die Zweigleitungen 30, 31 anschneiden und mit Bohrungsschultern Ventilsitze 54, 53 für zwei in zueinander entgegengesetzten Richtungen öffnende Rückschlagventile 27, 28 definieren. In der Bohrung 38, die endseitig durch einen Verschlußteil 41 dicht abgeschlossen ist, ist eine kräftige und lange Schließfeder 42 für das Rückschlagventil 27 vorgesehen. In der Bohrung 39, die durch einen Verschlußteil 40 abgeschlossen ist, ist eine schwache Schließfeder 43 für das Rückschlagventil 28 vorgesehen. Zwischen zwei axial beabstandeten Anschlüssen 36 und 37 (der Anschluß 37 bildet gleichzeitig die Drossel 32) ist ein Strömungsweg im Inneren des Ventilkörpers 47 vorgesehen, der sich in zwei Kanäle aufzweigt, wobei jeder Kanal eines der Kugelrückschlagventile 27, 28 enthält. Die zu den Rückschlagventilen 27, 28 parallele Drosselstrecke 26 wird durch den mit einem Innengewinde 34 der Gewindebohrung 33 zusammenarbeitenden Außengewindeabschnitt 35 des Ventilkörpers 47 gebildet. Es ergibt sich eine schlanke und kurzbauende Einschraubventilpatrone 44, die in der Gewindebohrung 43 mittels eines Dichtungsringes 45 unter einem verbreiterten Kopf des Ventilkörpers 47 abgedichtet ist. Die Drosselstrecke 26 könnte auch durch andere drosselnd wirkende Elemente (Drosselkanal, Drosselventil, Blendenöffnungen, Drosselspalt oder dgl.) gebildet werden.The control valve 12 is contained in the connection block 2. A screw-in valve cartridge 44 is screwed into a threaded bore 33 of the connection block 2 that cuts the control line 25 to the supply pressure side 49 and has a screw-shaped valve body 47 with an internal external threaded section 35 and a further external threaded section used for screwing in and sealing the threaded bore 33. The threaded bore 33 is penetrated axially spaced apart from the control line 25 by the control circuit 20. Into the valve body 47, mutually offset bores 38, 39 are made, which cut the branch lines 30, 31 and define valve seats 54, 53 for two check valves 27, 28 opening in opposite directions with bore shoulders. In the bore 38, which is sealed off at the end by a closure part 41, a strong and long closing spring 42 is provided for the check valve 27. In the bore 39, which is closed by a closure part 40, a weak closing spring 43 is provided for the check valve 28. A flow path is provided in the interior of the valve body 47 between two axially spaced connections 36 and 37 (the connection 37 simultaneously forms the throttle 32). which branches into two channels, each channel containing one of the ball check valves 27, 28. The throttle section 26, which is parallel to the check valves 27, 28, is formed by the external thread section 35 of the valve body 47, which cooperates with an internal thread 34 of the threaded bore 33. The result is a slim and short screw-in valve cartridge 44 which is sealed in the threaded bore 43 by means of a sealing ring 45 under a widened head of the valve body 47. The throttle section 26 could also be formed by other throttling elements (throttle channel, throttle valve, orifice openings, throttle gap or the like).

Das Druckmittel aus dem Steuerkreis 20 tritt durch die Drossel 32 und die Anschlußöffnung 37 in die Bohrung 38 ein. Das Rückschlagventil 27 ist geschlossen. Das Druckmittel gelangt dann in die Zweigleitung 31 und öffnet das Rückschlagventil 28, an dem vorbei es zur Anschlußöffnung 36 und damit zur Steuerleitung 25 gelangt. Gleichzeitig steht das Druckmittel an beiden Enden des Außengewindeabschnittes 35 an. Ist der Druck im Steuerkreis 20 niedriger als der Steuerdruck an der Zusteuerdruckseite 49, dann strömt Druckmittel in die Anschlußöffnung 36. Das Rückschlagventil 28 schließt. Die Schließfeder 42 verhindert, daß das Rückschlagventil 27 öffnet, bis die vorbestimmte Druckdifferenz erreicht wird. Das Druckmittel wird gezwungen, das geschlossene Rückschlagventil 27 über die Drosselstrecke 26 zu umgehen und dann über die Bohrung 38, die Anschlußöffnung 37 und die Drossel 32 in den Steuerkreis 20 zurückzuströmen. Erst wenn die voreingestellte Druckdifferenz (Kraft der Schließfeder (42) überwunden wird, öffnet das Rückschlagventil 27. Die Zusteuerdruckseite 49 wird rasch entlastet. Bei Unterschreiten der vorbestimmten Druckdifferenz schließt das Rückschlagventil 27 wieder. Das Druckmittel strömt gedämpft über die Drosselstrecke 26 ab.The pressure medium from the control circuit 20 enters the bore 38 through the throttle 32 and the connection opening 37. The check valve 27 is closed. The pressure medium then reaches the branch line 31 and opens the check valve 28, past which it reaches the connection opening 36 and thus the control line 25. At the same time, the pressure medium is present at both ends of the external thread section 35. If the pressure in the control circuit 20 is lower than the control pressure on the pilot pressure side 49, pressure medium flows into the connection opening 36. The check valve 28 closes. The closing spring 42 prevents the check valve 27 from opening until the predetermined pressure difference is reached. The pressure medium is forced to bypass the closed check valve 27 via the throttle section 26 and then to flow back into the control circuit 20 via the bore 38, the connection opening 37 and the throttle 32. The check valve 27 only opens when the preset pressure difference (force of the closing spring (42) is overcome. The control pressure side 49 becomes rapid relieved. When the pressure drops below the predetermined pressure difference, the check valve 27 closes again. The pressure medium flows in a damped manner via the throttle section 26.

Die Drosselstrecke 26 ist konstruktiv so ausgebildet, daß sie eine optimale Dämpfung der Amplituden bei Druckschwingungen innerhalb der vorbestimmten Druckdifferenz erzeugt, und zwar weitestgehend viskositätsunabhängig. Es könnten die Rückschlagventile 27, 28 und die Drosselstrecke 26 in getrennten Steuergliedern ausgebildet sein.The throttle section 26 is designed in such a way that it produces an optimal damping of the amplitudes in the event of pressure fluctuations within the predetermined pressure difference, and is largely independent of viscosity. The check valves 27, 28 and the throttle section 26 could be formed in separate control elements.

Claims (9)

Hydraulische Steuervorrichtung (1) mit wenigstens einem Wegesteuerventil (4), das an eine Pumpen- und eine Rücklaufleitung (7, 9; 8, 10) angeschlossen ist und von dem zumindest eine Verbraucherleitung (5, 6) zu einem Hydroverbraucher (50) führt, mit einer die Pumpenleitung (7, 9) über ein zwischen der Pumpen- und der Rücklaufleitung (7, 8) angeordnetes Regelventil (12) versorgenden Konstantpumpe (11), und mit einem Steuerdruckkreis (20), in dem ein vom Lastdruck in der Verbraucherleitung (5, 6) abhängiger Steuerdruck einsteuerbar ist, wobei das Regelventil (12) an einer Zusteuerdruckseite (49) mit dem Steuerdruck aus dem Steuerkreis (20) sowie parallel durch Federkraft (24) und entgegengesetzt an einer Aufsteuerdruckseite (48) mit dem Pumpendruck beaufschlagbar ist, dadurch gekennzeichnet, daß zwischen der Zusteuerdruckseite (49) des Regelventils (12) und dem Steuerkreis (20) eine hydraulische, mechanisch vorgespannte AufsteuerbewegungsDämpfeinrichtung (15) vorgesehen ist, die bei Erreichen eines vorbestimmten Druckdifferenzwertes zwischen dem an der Zusteuerdruckseite (49) anstehenden höheren Steuerdruck und dem im Steuerkreis (20) herrschenden niedrigeren Steuerdruck selbsttätig ausschaltbar ist.Hydraulic control device (1) with at least one directional control valve (4), which is connected to a pump and a return line (7, 9; 8, 10) and from which at least one consumer line (5, 6) leads to a hydraulic consumer (50) , with a pump (7, 9) via a control valve (12) supplying a control valve (12) arranged between the pump and the return line (7, 8), and with a control pressure circuit (20) in which one of the load pressure in the Consumer line (5, 6) dependent control pressure can be controlled, with the control valve (12) on a control pressure side (49) with the control pressure from the control circuit (20) and in parallel by spring force (24) and opposite on a control pressure side (48) with the pump pressure can be acted on, characterized in that between the control pressure side (49) of the control valve (12) and the control circuit (20) a hydraulic, mechanically preloaded control movement damping device (15) is provided, which b When a predetermined pressure difference value is reached between the higher control pressure present on the control pressure side (49) and the lower control pressure prevailing in the control circuit (20), it can be switched off automatically. Hydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die ausgeschaltete Aufsteuerbewegungs-Dämpfeinrichtung (15) bei Verringern der Druckdifferenz auf den vorbestimmten Druckdifferenzwert wieder selbsttätig zuschaltbar ist.Hydraulic control device according to Claim 1, characterized in that the open control movement damping device (15) can be switched on again automatically when the pressure difference is reduced to the predetermined pressure difference value. Hydraulische Steuervorrichtung nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß die Aufsteuerbewegungs-Dämpfeinrichtung (15) eine Dämpfdrosselstrecke (26) enthält, die in Strömungsrichtung zur Zusteuerdruckseite (49) durch ein parallel geschaltetes Rückschlagventil (28) mit Öffnungsrichtung zur Zusteuerdruckseite (49) und in der entgegengesetzten Strömungsrichtung durch ein parallel geschaltetes und auf die vorbestimmte Druckdifferenz vorgespanntes Druckbegrenzungsventil (27) ungehbar ist.Hydraulic control device according to claims 1 and 2 , characterized in that the control movement damping device (15) contains a damping throttle section (26) which in the flow direction to the control pressure side (49) through a parallel check valve (28) with opening direction to the control pressure side (49) and in the opposite flow direction through a parallel pressure control valve biased to the predetermined pressure difference ( 27) is impassable. Hydraulische Steuervorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß das Druckbegrenzungsventil (27) ein federvorgespanntes Kugelrückschlagventil mit Öffnungsrichtung zum Steuerkreis (20) ist.Hydraulic control device according to claim 3, characterized in that the pressure relief valve (27) is a spring-loaded ball check valve with opening direction to the control circuit (20). Hydraulische Steuervorrichtung nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, daß der vorbestimmte Druckdifferenzwert ca. 20 Bar beträgt, und vorzugsweise von außen veränderbar ist.Hydraulic control device according to claims 1 to 4, characterized in that the predetermined pressure difference is approximately 20 bar, and is preferably changeable from the outside. Hydraulische Steuervorrichtung nach den Ansprüchen 1 bis 5, dadurch gekennzeichnet, daß das Regelventil (12) in einem Anschlußblock (2) angeordnet ist, in dem ein Steuerdruckkanal (25) vom Steuerkreis (20) zur Zusteuerdruckseite (49) verläuft, und daß die Aufsteuerbewegungs-Dämpfeinrichtung (12) eine in eine den Steuerdruckkanal (25) kreuzende Gewindebohrung (33) eingeschraubte Einschraub-Ventilpatrone (44) ist.Hydraulic control device according to Claims 1 to 5, characterized in that the control valve (12) is arranged in a connection block (2) in which a control pressure channel (25) runs from the control circuit (20) to the control pressure side (49), and in that the control movement -Damping device (12) is a screw-in valve cartridge (44) screwed into a threaded bore (33) crossing the control pressure channel (25). Hydraulische Steuervorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die Einschraubventilpatrone (44) in ihrem Ventilkörper (47) die beiden gegensinnigen Rückschlagventile (27, 28) nebeneinanderliegend aufweist, und daß die Dämpfdrosselstrecke (26) zwischen ineinandergreifenden Gewinden (34, 35) des Ventilkörpers (47) und der Gewindebohrung (33) gebildet ist.Hydraulic control device according to claim 6, characterized in that the screw-in valve cartridge (44) has in its valve body (47) the two opposing check valves (27, 28) lying next to each other, and in that the damping throttle section (26) between interlocking threads (34, 35) of the valve body (47) and the threaded bore (33) is formed. Einschraubventilpatrone (44) für ein Regelventil (12) einer mittels einer Konstantpumpe versorgten, hydraulischen Steuervorrichtung (1), dadurch gekennzeichnet, daß die Einschraubventilpatrone (44) einen schraubenförmigen Ventilkörper (47) mit einem innenliegenden Durchgang aufweist, der zwischen zwei in Axialrichtung beabstandeten Anschlüssen (37, 36) in zwei innerhalb des Querschnitts des Ventilkörpers (47) nebeneinanderliegende Kanäle (30, 31) aufgezweigt ist, daß in einem Kanal (31) ein erstes Kugelrückschlagventil (28) und im anderen Kanal (30) ein durch eine Schließfeder (38) vorgespanntes zweites Kugelrückschlagventil (27) vorgesehen ist, daß die beiden Kugelrückschlagventile (27, 28) in zueinander entgegengesetzten Richtungen öffnen, und daß zwischen den Anschlüssen (36, 37) als das zweite Kugelrückschlagventil (27) innerhalb dessen Vorspannbereiches umgehende Drosselstrecke (26) ein mit einem Gegengewinde (34) einer, vorzugsweise einen Steuerdruckkanal (25) zur Zusteuerseite (49) des Regelventils (12) schneidenden, Gewindebohrung (33) zur Zusammenwirkung bringbarer Außengewindeabschnitt (35) vorgesehen ist.Screw-in valve cartridge (44) for a control valve (12) of a hydraulic control device (1) supplied by means of a constant pump, characterized in that the screw-in valve cartridge (44) has a screw-shaped valve body (47) with an internal passage which is between two axially spaced connections (37, 36) is branched into two channels (30, 31) lying side by side within the cross section of the valve body (47), that in a channel (31) a first ball check valve (28) and in the other channel (30) one by a closing spring ( 38) pretensioned second ball check valve (27) is provided, that the two ball check valves (27, 28) open in opposite directions to each other, and that between the connections (36, 37) as the second ball check valve (27) within its pretensioning area throttle section (26 ) one with a counter thread (34), preferably a control pressure channel (25) r Control side (49) of the control valve (12) intersecting, threaded bore (33) can be brought together to cooperate external thread section (35). Einschraubventilpatrone nach Anspruch 8, dadurch gekennzeichnet, daß die Ventilsitze (53, 54) der beiden Kugelrückschlagventile (27, 28) von Bohrungssschultern in zwei von entgegengesetzten Enden des Ventilkörpers (47) ausgehenden, zueinander versetzten und jeweils einen Kanal (30, 31) anschneidenden Bohrungen (38, 39) gebildet sind, daß jede Bohrung (38, 39) an einem Ende des Ventilkörpers (47) durch einen Verschlußteil (40, 41) dicht abgeschlossen ist, und daß an den Verschlußteilen (40, 41) Rückschlagkugeln beaufschlagende Schließfedern (42, 43) abgestützt sind.Screw-in valve cartridge according to claim 8, characterized in that the valve seats (53, 54) of the two ball check valves (27, 28) of bore shoulders in two starting from opposite ends of the valve body (47), offset from one another and each cutting a channel (30, 31) Bores (38, 39) are formed such that each bore (38, 39) is sealed off at one end of the valve body (47) by a closure part (40, 41), and that closing springs act on non-return balls on the closure parts (40, 41) (42, 43) are supported.
EP93111555A 1992-08-10 1993-07-19 Hydraulic control device Expired - Lifetime EP0582859B1 (en)

Applications Claiming Priority (2)

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DE9210646U 1992-08-10
DE9210646U DE9210646U1 (en) 1992-08-10 1992-08-10 Hydraulic control device

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EP0582859A1 true EP0582859A1 (en) 1994-02-16
EP0582859B1 EP0582859B1 (en) 1997-01-29

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AT (1) ATE148534T1 (en)
DE (2) DE9210646U1 (en)
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ES (1) ES2096809T3 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1477686A1 (en) * 2003-05-15 2004-11-17 Kobelco Construction Machinery Co., Ltd. Hydraulic controller for working machine
CN102032226A (en) * 2010-12-29 2011-04-27 大连华锐股份有限公司 Adjustable superposition type outlet pressure compensator
EP4088051A4 (en) * 2019-01-11 2024-01-17 Dayco IP Holdings, LLC Crankcase ventilation system with a flow control device for on board diagnostics

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DE3420990A1 (en) * 1984-06-06 1985-12-12 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic system
DE3425304A1 (en) * 1984-07-10 1986-01-23 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic control apparatus
DE9111569U1 (en) * 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Control device for at least one hydraulic motor
US5107753A (en) * 1990-08-08 1992-04-28 Nippon Air Brake Kabushiki Kaisha Automatic pressure control device for hydraulic actuator driving circuit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3420990A1 (en) * 1984-06-06 1985-12-12 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic system
DE3425304A1 (en) * 1984-07-10 1986-01-23 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic control apparatus
US5107753A (en) * 1990-08-08 1992-04-28 Nippon Air Brake Kabushiki Kaisha Automatic pressure control device for hydraulic actuator driving circuit
DE9111569U1 (en) * 1991-09-17 1991-11-14 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Control device for at least one hydraulic motor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1477686A1 (en) * 2003-05-15 2004-11-17 Kobelco Construction Machinery Co., Ltd. Hydraulic controller for working machine
US7155909B2 (en) 2003-05-15 2007-01-02 Kobelco Construction Machinery Co., Ltd. Hydraulic controller for working machine
EP1790859A1 (en) * 2003-05-15 2007-05-30 Kobelco Construction Machinery Co., Ltd. Hydraulic controller for working machine
US7594396B2 (en) 2003-05-15 2009-09-29 Kobelco Construction Machinery Co., Ltd. Hydraulic controller for working machine
CN102032226A (en) * 2010-12-29 2011-04-27 大连华锐股份有限公司 Adjustable superposition type outlet pressure compensator
CN102032226B (en) * 2010-12-29 2013-01-23 大连华锐重工集团股份有限公司 Adjustable superposition type outlet pressure compensator
EP4088051A4 (en) * 2019-01-11 2024-01-17 Dayco IP Holdings, LLC Crankcase ventilation system with a flow control device for on board diagnostics

Also Published As

Publication number Publication date
DK0582859T3 (en) 1997-06-30
DE9210646U1 (en) 1993-12-16
ATE148534T1 (en) 1997-02-15
ES2096809T3 (en) 1997-03-16
EP0582859B1 (en) 1997-01-29
DE59305313D1 (en) 1997-03-13

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