EP1163454B1 - Hydraulische vorsteuerung - Google Patents

Hydraulische vorsteuerung Download PDF

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Publication number
EP1163454B1
EP1163454B1 EP00910754A EP00910754A EP1163454B1 EP 1163454 B1 EP1163454 B1 EP 1163454B1 EP 00910754 A EP00910754 A EP 00910754A EP 00910754 A EP00910754 A EP 00910754A EP 1163454 B1 EP1163454 B1 EP 1163454B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
handle
hydraulic pilot
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.)
Revoked
Application number
EP00910754A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1163454A1 (de
Inventor
Heinz Habermann
Wilhelm Kastel
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1163454A1 publication Critical patent/EP1163454A1/de
Application granted granted Critical
Publication of EP1163454B1 publication Critical patent/EP1163454B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0406—Valve members; Fluid interconnections therefor for rotary valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—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 manually-operated pilot valves, e.g. joysticks
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/07—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors in distinct sequence
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G1/00—Controlling members, e.g. knobs or handles; Assemblies or arrangements thereof; Indicating position of controlling members
    • G05G1/04—Controlling members for hand actuation by pivoting movement, e.g. levers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86638—Rotary valve
    • Y10T137/86646—Plug type
    • Y10T137/86654—For plural lines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust

Definitions

  • the invention is based on a hydraulic pilot control, which has the features from the preamble of claim 1.
  • Such hydraulic pilot control is e.g. known from DE 196 30 798 A1.
  • This pilot control includes a pilot control device that has several pressure reducing valves contains a pilot pressure with each of them at a control outlet can be generated.
  • the pilot control device has a control lever which from a neutral position to the adjustment of a first pressure reducing valve in a first direction and for adjusting a second pressure reducing valve in one the second direction opposite to the first direction can be pivoted can.
  • After swiveling the control lever by one certain angle in the first direction that is then present at the first control output Pilot pressure different from that at the second control output Pilot pressure when the control lever is at the same angle in the second direction is deflected. This is due to the tolerances with to which the individual components of a pressure reducing valve are afflicted. In particular The tolerances of the control spring of a pressure valve go into the pilot pressure on.
  • the invention has for its object a hydraulic pilot control to further develop the features from the preamble of claim 1, that you can easily regardless of the direction of the pivot Handle a certain pilot pressure after a certain swivel angle on one of the two control outputs.
  • the well-known is also sought to make hydraulic pilot control more cost-effective.
  • a hydraulic pilot control the features from the preamble of claim 1 according to the characterizing Part of this claim, a pressure valve that is pivoted the handle in the first direction and when pivoting the handle is adjustable in the same direction in the second direction, and one Directional control valve has that depending on the swivel direction of the handle from a rest position, which it assumes in the neutral position of the handle, in a first switching position in which it is the control output of the pressure valve with the connects first control output, or switchable into a second switching position is in which it is the control output of the pressure valve with the second control output combines.
  • a hydraulic pilot control according to the invention for Two swivel directions of the handle provided only one pressure valve.
  • the pilot pressure is also independent of the swivel direction. If you want a certain one at a certain swivel angle Have pilot pressure, only a single pressure valve needs to be adjusted.
  • a directional control valve can also generally be produced with less effort as a multi-part pressure valve.
  • An inventive Hydraulic pilot control can therefore also be manufactured more cost-effectively become.
  • the directional valve has a movable control element preferably a rotary slide valve, the axis of which coincides with the axis of rotation
  • the handle is aligned and the handle is in a valve bore in a valve housing is rotatable. Even with large swivel angles of the handle no difficulties here control of the directional valve and handle to couple with each other.
  • the rotary valve is advantageously with a Axial stop pressed by a spring against a stop of the valve housing, so that it always takes the same axial position and the connections reliably controls between individual channels opening into the valve bore.
  • the configuration according to claim 7 is particularly preferred there is a fixed pressure reducing valve available, that of the internal control pressure supply serves and saves space in an axial bore as a slide trained control element of the directional valve is housed. From one Internal control pressure supply is spoken when a pressure reducing valve trips out a high system pressure produces a much lower control pressure that an adjustable pressure valve is supplied.
  • a certain pilot pressure at a certain swivel angle can be adjust in a particularly simple manner in that the pressure valve according to Claim 12 after the assembly of its components in a housing from the outside is adjustable.
  • the claims 13 and 14 show two advantageous Possibilities of adjusting the pressure valve.
  • the pre-tensioning by an adjustable stop is changeable so that one derives from the force of the control spring and from the Total spring force acting on the control element, resulting from the force of the adjusting spring can be adjusted.
  • the housing-fixed for adjustment Control edges axially displaced so that the control position of the movable Control element and thus for a given axial position of the plunger the bias of the control spring changes in the control position of the control element.
  • An embodiment according to claim 15 is particularly preferred the plunger is guided in a guide sleeve.
  • the tax cartridge, the change the position of the control edges fixed to the housing inserted into a housing is extended beyond the control edges and takes the guide sleeve captive on.
  • the control cartridge, the guide sleeve and the movable Parts of the pressure valve a structural unit that is handled as a whole and can be easily assembled as a whole in a housing.
  • the design of a pressure valve according to Claim 15 is also advantageous if this pressure valve in conventional pilot control devices is used, in which in general for each An adjustable pressure valve is present in the pivoting direction of the handle.
  • a winch 10 can be seen, which is adjustable by a gear 11 Hydraulic motor 12 can be driven in opposite directions.
  • Hydraulic motor 12 can be driven in opposite directions.
  • a brake 13 Between the output shaft of the hydraulic motor and the transmission is a brake 13 arranged, which is actuated by a single-acting hydraulic cylinder 14.
  • the Hydraulic cylinder 14 is constructed in the manner of a differential cylinder, the piston and piston rod displaceable by a spring in the sense of engagement of the brake are.
  • the swallowing volume of the hydraulic motor 12 can be applied as a function of one applied to the control input 16 Infinitely variable control pressure and the smaller the larger the Control pressure is.
  • a differential cylinder Actuating cylinder 17 and a pump control valve 18 available.
  • This has one Tank connection, which is connected to a leak oil line 19, a pressure connection, of the two check valves 20, each with the motor connection 21 or 22nd is connected, and one with the piston rod-side pressure chamber of the Actuating cylinder 17 connected cylinder connection.
  • the pressure chamber on the piston rod side of the actuating cylinder 17 is connected to the pressure connection of the pump control valve 18th connected.
  • the spool of the pump control valve 18 is in the sense of a Connection of the cylinder connection with the pressure connection from the control pressure and in the sense of connecting the cylinder connection to the tank connection from a first compression spring set to a fixed value and from a acted upon by the second compression spring, the pretension of which changes with the position of the Piston and the piston rod of the actuating cylinder 17 changes.
  • Piston and piston rod of the actuating cylinder 17 each take such a position that the force generated by the applied control pressure and the force generated by the springs Force balance on the piston of the pump control valve 18. In this way, the control pressure allows a certain swallowing volume of the hydraulic motor 12.
  • a variable displacement pump is the source of the pressure medium that is supplied to the hydraulic motor 12 25, which sucks hydraulic oil from a tank 26 and into an inlet line 27 issues.
  • the variable displacement pump 25 is provided with a pressure regulator 28, thus pivots when the one set on the pressure regulator 28 in the feed line 27 Pressure is reached back to a stroke volume that is sufficient to the set Maintain pressure in the feed line 27.
  • a pressure relief valve 29 To secure the whole Control arrangement against excessive pressures is a pressure relief valve 29 the feed line 27 connected.
  • the maximum displacement of the variable pump is designed so that it has not yet swung out to the stop, albeit taking into account the simultaneous actuation of several hydraulic Consumer maximum pressure medium quantity is requested.
  • the speed at which the hydraulic motor 12 rotates and the direction of rotation are with a proportional adjustable directional valve 35 controllable. This is in a middle position spring centered and can be operated hydraulically. It owns a total six connections, namely an inlet connection 36, the pressure medium the inlet line 27 can flow via a pressure compensator 37, an outlet connection 38, which is connected directly to a tank line 39, a second drain connection 40, which is connected to the tank line 39 via a brake valve 41 is a first consumer connection 42, which has a consumer line 43 with the motor connection 21 is connected, a second consumer connection 44, the is connected to the motor connection 22 via a consumer line 45 and a Brake port 46 through which the annular space 15 of the hydraulic cylinder 14 with Pressure medium can be acted upon.
  • connection 38 In the spring-centered central position of the directional control valve 35, its connections are 36, 40 and 44 cordoned off.
  • the connections 42 and 46 are connected to the connection 38 and connected to the tank 26.
  • the consumer connection 42 and the brake connection 46 are common via a metering orifice 48, the Opening cross-section depends on the degree of displacement of the valve piston, connected to the inlet connection 36.
  • the consumer connection 44 is a Drain throttle 49 connected to the drain port 40.
  • valve piston of the directional control valve 35 moves out of the central position to different degrees in a second working position, in which the consumer connection 42 is unthrottled connected to the drain port 38.
  • the brake connection and the other consumer connection 44 are common via the metering orifice 48 connected to the inlet connection 36.
  • the drain port 40 is shut off.
  • the maximum displacement of the valve piston in the two opposite Directions is limited by adjustable stops 51.
  • the pressure compensator 37 is in accordance with the connections described between the various connections of the directional control valve 35 in its two working positions each arranged upstream of the metering orifice 48.
  • the control piston of the Pressure compensator 37 is in the direction of closing of the pressure upstream of the metering orifice and acted upon in the direction of opening by a compression spring 52 and by a pressure, which is applied via a control line 53 which is connected to the brake connection of the directional control valve and thus with the one in the flow to the hydraulic motor 12 lying consumer port 42 or 44 of the directional control valve 35 is connected.
  • the pressure is therefore equal to the pressure downstream of the metering orifice 48.
  • the pressure compensator 37 a certain, the force of the spring 52 equivalent Pressure difference across the orifice 48.
  • the flowing over the orifice 48 The amount of pressure medium therefore only depends on the opening cross section of the metering orifice and is independent of the load pressure and the pump pressure.
  • the control piston of the brake valve 41 is in the opening direction from the consumer connection 42 of the directional control valve 35 and thus also in the consumer line 43 and at the motor connection 21 pressure and in the closing direction of the Force of a compression spring 54 and applied by a control line 55 Pilot pressure applied which is constant in the range of e.g. 40 bar.
  • the two pressures act on surfaces of the same size, so that the brake valve 41st when pulling load together with the throttle 49, the discharge of pressure medium from Hydraulic motor 12 throttles through the consumer line 45 so strongly that in the consumer line 43 a pressure is built up on the control piston of the Brake valve generates a force that the force of the compression spring 54 and the Pilot pressure generated force keeps the balance.
  • the speed of the hydraulic motor 12 is thus the pulling load through the opening cross section Orifice 48 determined.
  • the pressure at the brake port 46 of the Directional control valve 35 so high even with a pulling load that the brake 13 is released remains.
  • pressure relief valve between the two consumer lines 43 and 45 60 arranged, which is set to a pressure that by 10 - 20 bar above the pressure regulated by the variable pump 25, but below the set pressure of the pressure relief valve 29.
  • the directional control valve 35, the pressure compensator 37, the brake valve 41 and the pressure relief valve 60 are accommodated in a valve plate 61.
  • a nozzle 67 is located in the bypass line 66 and is located in the plate 61 and by the amount of pressure medium, which the hydraulic motor 12 via the bypass line 66 can flow, is limited to about 10% of the amount of pressure medium, the at maximum opening of the orifice 48 via the directional control valve 35 to the hydraulic motor 12 flows.
  • the pilot control device 65 contains two pressure reducing valves 68 and 69, a directional control valve 70, a check valve 71, various shuttle valves 72, 73, 74 and 75, two Damping nozzles 76, two relief nozzles 77 and different channels for Connection of the valves to each other.
  • the check valve 71 is in the Bypass line 66 and blocks to the inlet line 27. Downstream of the check valve 71 is the pressure reducing valve 68 with its pressure connection to the Bypass line 66 connected.
  • a relief port on the pressure control valve 68 is connected to a leakage channel 78.
  • the pressure reducing valve 68 is open set a fixed value and regulates at its control output and in one Pilot pressure supply channel 79, to which also leads to the brake valve 41 Control line 55 is connected, e.g. the pressure mentioned above of 40 bar.
  • the second pressure reducing valve 69, with its pressure connection to channel 79, with its relief connection to channel 78 and with its Control output is connected to a pilot pressure channel 80 is through Swiveling a control lever 81 adjustable from a neutral position.
  • the pivot axis of the control lever 81 is designated 82.
  • the control curve is designed so that at a pivoting of the control lever from the neutral position initially independent from the pivoting direction, the pressure reducing valve 69 in the same way is adjusted.
  • the pilot pressure in channel 80 increases from a swivel angle of approximately 8 degrees to a swivel angle of 45 degrees continuously, although not necessarily with the same slope everywhere.
  • the pivot angle of the control lever 81 limited to about 50 degrees. In this direction, the joystick becomes a yoke thus pivoted to unroll the hawser from the winch 10.
  • a swivel the control lever in the other direction is for hoisting when So the hawser should be rolled up on the winch 10.
  • the control lever returns 81 both when swiveling in the direction of Fieren and when Swiveling in the direction of Hieven due to a reset device acting on it back to its neutral position when it is released.
  • the control lever is towards Hieven, however, up to a swivel angle of can be swiveled about 100 degrees, and when swiveled over about 54 Degrees remains in the position he then occupies, even if he is released. In this area, the winch 10 is operated in the mooring.
  • the three angular ranges Fieren, Hieven and Mooring are shown hatched in Figure 1 and with the reference numerals 85 for fiering, 86 for heaving and 87 provided for the mooring.
  • the control disc 83 is designed so that in Mooring angle range 87 the pressure in the channel 80 with increasing pivot angle of the control lever 81 decreases.
  • the directional control valve 70 is actuated mechanically by the control lever 81.
  • Its agile Valve element is designed as a rotary slide valve 181 (see FIGS. 9 and 10), whose axis of rotation coincides with the axis 82 of the control lever 81.
  • the pilot pressure channel 80 leads to a connection 90.
  • a connection 91 is connected to the leakage channel 78.
  • the three remaining connections 92, 93 and 94 each lead to a first input of a shuttle valve 72 and 73, respectively or 74.
  • the second input of the shuttle valve 74 is with the brake connection 46 of the directional control valve 35 connected.
  • the second entrance each of the two shuttle valves 72 and 73 each has an external connection 95 connected, which is closed in the present case, but offers the possibility of Control the winch with a second pilot that is remote from that the plate 61 and the pilot control 65 existing block is arranged.
  • this remote control and for the case of low pilot pressures Line between the connection 46 of the directional control valve 35 and the shuttle valve 74 necessary, because then the annular space 15 of the hydraulic cylinder 14 with this line Pressure can be applied.
  • the shuttle valve 75 is located with one input at the outlet of the shuttle valve 72 and with its other Input at the outlet of the shuttle valve 73. Its output is via a control line 98 connected to the control input 16 of the hydraulic motor 12.
  • the directional control valve 70 takes a position in the neutral position of the control lever 81 one in which ports 88, 89 and 90 are cordoned off and the other ports are connected to the tank channel 78.
  • the bypass line 66 is therefore blocked.
  • Control lines 95, 96, 97 and 98 are relieved of pressure to channel 78.
  • the directional control valve 35 is thus in its central position.
  • the hydraulic motor 12 stands for maximum swallowing volume.
  • the brake 13 has gripped.
  • the control lever for gearing is now adjusted in the angular range 85.
  • the directional control valve 70 reaches a switching position in which the connections 89 and 94, the terminals 90 and 93 and the terminals 91 and 92 with each other are connected.
  • the connections 90 and 93 and that Shuttle valve 73 and the control line 97, the control chamber 47 of the directional valve 35 applied with a control pressure.
  • This control pressure is via the shuttle valve 75 and the control line 98 also at the control input 16 of the hydraulic motor 12 on.
  • the control chamber 50 of the directional control valve 35 is via the control line 96, the shuttle valve 72 and the connections 91 and 92 of the directional control valve 70 or via which a relief nozzle 77 is relieved of pressure.
  • the directional control valve 35 will thus brought into a position in which the inlet connection 36 via the metering orifice 48 with the consumer connection 42 and with the brake connection 46 connected is. Builds up in the consumer line 43 and in the feed line 27 a pressure on the changeover valve 74 also in the annular space 15 of the hydraulic cylinder 14 is pending and is finally sufficient to release the brake. From the hydraulic pump 25 pumped pressure medium can now via the inlet line 27, the Pressure compensator 37, the directional control valve 35 and the consumer line 43 to the hydraulic motor 12 and from there via the consumer line 25, the throttle opening 49 of the Directional control valve 35 and flow via brake valve 41 to tank 26. The hawser is handled by the winch 10.
  • the brake valve 41 for the outflow of pressure medium can only be throttled from the hydraulic motor 12 to the tank, so that in the consumer line 43 a certain pressure is maintained. This is enough to keep the brake 13 released. Also, the speed at which the hawser is unwound, solely by the deflection of the control lever 81 dependent control pressure determined.
  • the speed of the winch 10 influenced in two ways. Approximately up to a deflection angle of 25 degrees only the directional control valve 35 is adjusted, but not the hydraulic motor 12. This remains at maximum swallowing volume and maximum torque.
  • the Torque in FIG. 1 is due to the radial expansion of fields 85, 86 and 87 indicated.
  • the directional valve 70 comes into a position in which in turn the connections 89 and 94 are connected to one another.
  • the Terminal 90 is now with terminal 92 and terminal 91 with Connection 93 connected.
  • the control chamber 47 is relieved of pressure and the control chamber 50 of the directional control valve 35 with a deflection angle of Control lever 81 dependent pilot pressure applied. This is also on Control input 16 of the hydraulic motor 12.
  • the directional valve gets into his second working position, in the pressure medium delivered by the variable displacement pump 25 via the inlet line 27, the pressure compensator 37, the connections 36 and 44 with the intermediate orifice 48 and the consumer line 45 to the Hydromotor 12 can flow.
  • the directional valve 70 reaches a switch position in which the connections 88 and 94 are connected to terminal 89. Accordingly, the Bypass line 66 open for the flow of pressure medium and the annular space 15 of the hydraulic cylinder 14 is connected to the bypass line downstream of the check valve 71 connected. The port 91 of the directional control valve 70 is blocked. The connections 92 and 93 are connected to the control output of the 90 Pressure reducing valve 69 connected. Thus, in both control chambers Directional control valve 35 the same pilot pressure, so that this due to its spring centering returns to the middle position. The pilot pressure is also on Input 16 of the hydraulic motor 12.
  • the control cam is the control disc 83 designed so that the pilot pressure so at the beginning of the mooring angle range What is high is that the hydraulic motor is set to its minimum absorption volume. Thus, the torque that can be exerted by the hydraulic motor 12 is also minimal. With increasing Deflection of the control lever 81 in the mooring angle area 87 takes the pilot pressure decreases continuously, so that the swallowing volume and thus the exertable torque of the hydraulic motor 12 is continuously increased. This is physiologically favorable.
  • connection 22 of the hydraulic motor 12 can have pressure medium only flow via the bypass line 66.
  • This inflow is through the Nozzle 67 limits, so that the speed of the hydraulic motor in mooring mode and thus the speed at which the hawser is wound up is limited. This is important for operational security. Because there the control lever 81 in the mooring angle range 87 maintains its position even without an external force being attacked, there is a possibility that a person first the control lever in the Mooring angle range and then tampered with the hawser or is in the area of the hawser. Through the nozzle 67 is the speed with which the hawser moves, limited to a low speed. Even if the hawser breaks, the speed with which the hawser then remains is wound up, because of the nozzle 67 small, if somewhat higher than with a load may be.
  • the control lever 81 is on one of the housing 101 of the pilot device 65 protruding shaft 183 attached, with, as shown in Figure 2, inside of the housing 101, a cam 102 with one with a reset device 103 interacting cam track 104 and the axially directly the cam disk 102 connecting control disk 83 with one with the tappet 84 of the pressure reducing valve 69 cooperating control curve 105 against rotation are coupled.
  • the cam track 104 and the control cam 105 are each partially cylindrical surfaces that extend axially to a certain extent.
  • the cam 102 and the control disk 83 are in a larger cavity 99 of the housing 101, in the diametrically opposite, but accordingly the axial offset of cam 102 and control disc 83 also two housing bores 106 and 107 open axially offset from one another.
  • the Housing bore 106 receives the parts of the reset device 103.
  • the pressure reducing valve 69 is used in the Housing bore 107.
  • This pressure reducing valve 69 is adjustable from the outside in such a way that a selected one Deflection angle of the control lever 81 in the channel 80 is a very specific one Pilot pressure is present. At this selected deflection angle, the directional valve should 35 be completely open and start the adjustment of the hydraulic motor 12.
  • the Pressure reducing valve 69 has a control cartridge 108 for adjustment, which outwardly open end of the housing bore 107 is screwed into this.
  • the control cartridge 108 is triple stepped on the outside and has one in each step Seal 109, 110 and 111.
  • the diameter and center seal 110 is between the control cartridge 108 and the housing 110 forms an annular space, which is part of the number 79 in FIG Control pressure supply channel and in which that of the pressure reducing valve 68 regulated pressure of 40 bar is present. Axially between the Both seals 110 and 111 are located on the outside of the control cartridge 108 a further annular space which belongs to the pilot pressure channel 80 from FIG. 1. Another annular space between the control cartridge 108 and the housing 101 is created in front of the seal 109, this annular space leading to the leakage channel 78 heard from Figure 1.
  • the central passage 112 through the control cartridge 108 has axially one behind the other Sections with different cross sections.
  • a hole section with the smallest diameter is located approximately between the axially Seals 109 and 110 and is via two radial bores 113 to the annulus 79 open. It goes outwards in a slightly larger and partially with an internally threaded bore section from which radial bores 114 go out, which open into the annular space 80.
  • a grub screw 115 is screwed in through the mentioned bore sections are closed to the outside. Beyond the grub screw 115 the passage is designed as an internal polygon on which one can turn and thus to axially adjust the control cartridge 108 with a tool can.
  • the bore section into which the radial bores 113 open merges inwards into a further stepped receiving space 116, from which lead from radial bores 117 into the annular space 78.
  • this recording room 116 is a guide bushing 118 for the tappet 84 of the pressure control valve 69 inserted and secured captively therein by a grub screw 121.
  • the guide bush has radial bores 119, via which together with a annulus located between the control cartridge 108 and the guide bush 118 one between the control cartridge 108, the guide bushing 118 and the Tappet 84 formed spring chamber 120 with the annular space 78 and thus with a tank connected is.
  • the passage section into which the radial bores 113 open serves as Guide bore for a control piston 125 and controls together with the control piston the connections between the different ring spaces 78, 79 and 80.
  • the edges between the radial bores 113 and the bore section on the one hand and the edge between the bore section and the larger spring chamber 120 on the other hand form the control edges.
  • the control piston 125 is a hollow piston with an axial blind bore 126 leading to the radial bores 114 open and via several radial bores 127 with the outside of the Control piston is connected.
  • the radial bores 127 go into an outside Ring groove 128 over.
  • the axial extent of the ring groove including the radial bores 127 is slightly smaller than the clear axial distance between the Control edges on the control cartridge 108 so that it is possible to drill the blind hole 26 with positive overlap of both the radial bores 113 and Separate spring chamber 120.
  • the control piston 125 extends through the spring chamber 120 through and projects with a head 129 into a blind bore 130 of the Ram 84 into it. With his head 129 he engages behind a disc 131 which between the plunger 84 and a spring plate 132 is arranged and in the manner of a slotted locking ring holds the head 129.
  • return spring 133 for the plunger 84 is supported on the one hand the control cartridge 108 and on the other hand via the spring plate 132 and the disc 131 on the tappet 84 and presses the tappet against the cam 105. Furthermore a spring 134 is received by the spring chamber 120, which between a on a shoulder of the control piston 125 resting spring plate 135 and the Spring plate 132 is clamped and which ensures that in the rest position shown of the plunger 84, the head 129 of which rests on the disk 131.
  • the pressure relief valve 69 is so with respect to the axis of the control lever 81 arranged that the axis of the plunger 84 perpendicular to the axis 82 of the control lever 81 cuts.
  • the control curve 105 is based on a central neutral Line in which their distance from the axis 82 is minimal and on which the plunger 84 is in the neutral position of the control lever 81, initially on both sides designed the same. Their distance from the axis 82 increases continuously to. On one side, the control curve 105 ends in a radially outward direction Surface section 140 for which the plunger 84 acts as a stop and the therefore limits the pivot angle of the control lever 81 in one direction.
  • the tappet is located in the neutral position of the control cam 105 shown in FIG. 2 84 and with it the control piston 125 of the pressure reducing valve 69 in a position, in which the annular space 80 via the blind hole 126, the radial bores 127, the spring chamber 120, the radial bores 119 and the radial bores 117 the annular space 78 is fluidly connected. If the control lever is now deflected, the plunger 84 is moved into the control cartridge 108. About the rule spring 134, the control piston 125 is taken, so that the connection interrupted between the blind hole 126 and the annular space 78 and a connection is opened between the blind hole 126 and the annular space 79.
  • the reset device 103 comprises a pressure piece 145 which is cylindrical Section 146 is guided in the housing bore 106 and with a Double 147, the flat surfaces of which are oriented perpendicular to the axis 82, protrudes into the cavity 99 and with its parallel to the axis 82 Front face 148 is pressed against the return cam track 104.
  • a pressing force is exerted in the entire swivel range by a return spring 149. additionally acts in the mooring angle range designated 87 in FIG further pressure spring 150.
  • the springs are located in a spring space between the pressure piece 145 and one screwed into the housing bore 106 Locking screw 151.
  • the pressure piece 146 has a blind hole open towards the screw plug 151 152, between the bottom and the locking screw 151, the return spring 149 is clamped. There is also one within the return spring 149 to the locking screw 151 open bush 153, in the blind hole, the pressure spring 150 is included for the most part. In the shown in Figure 2 Position of the pressure piece 145, in which this is its greatest distance from the screw plug 151, the pressure spring 150 is completely relaxed. Only after one certain path of the pressure piece 145 to the screw 151 the pressure spring 150 takes effect.
  • the pressure piece 145 has on its outside diametrically opposite two axially extending grooves 154 and 155, which are of different lengths, but at the same distance from that of the screw plug 151 end facing the pressure piece 145 begin.
  • the Groove 154 engages with little play a pin 156, which is held in the housing 101 is.
  • the pressure piece 145 is secured against rotation by the pin 156.
  • the Groove 154 is so long that the axial movement of the pressure piece 145 through the pin 156 is not limited.
  • the cam track 104 consists essentially of four distinguishable from each other areal curve sections together.
  • a section of curve 160 extends over 180 degrees around axis 82 and is curved in a circular cylinder, has the same distance from the axis 82 everywhere.
  • the control lever 81 and thus the cam track 104 as shown in FIG. 2 is shown, the axial plane 164 through the axis 82 and the ends of the Curve section 160 goes perpendicular to the axis of the pressure piece 145.
  • the two ends of the curve section 160 are three flat, flat curve sections 161, 162 and 163, which run at an angle to each other.
  • the middle curve section 161 of these three curve sections extends in one small distance from the plane 164 parallel to this.
  • the two curve sections 162 and 163 run obliquely from curve section 161 to curve section 160 out.
  • the end face 148 of the pressure piece 145 facing the cam track 104 has two aligned with each other and perpendicular to the axis of the pressure piece 145 standing flat surface sections 168 and 169, which differ from the round side surface sections of the double flat 147 from different distances extend inside.
  • the surface section 169 is much longer than that Surface section 168.
  • Between these two surface sections is in the Front face 148 has a recess 170 running perpendicular to the flat sides introduced, starting from the inner end of the surface section 168 through a uniformly curved surface 171 is limited, the curvature of which is the same the curvature of the curve section 160 of the curve path 104.
  • To the surface 171 is followed by a gutter 172, which is centered in the end face of the pressure piece lies.
  • One side of the channel 171 goes in a flat surface in a stop surface 173 Surface section 169 over.
  • An axial bore opening through the pressure piece 145 opens into the groove 172 174, in the extension of which the bottom of the sleeve 153 also has an axial bore 175 has.
  • the spring space receiving the springs 149 and 150 is constantly fluidly connected to the cavity 99 of the housing 101.
  • the Cavity 99 in turn lies in the leakage line 78.
  • the control lever is used for fiering, ie for unwinding the hawser from the winch 10 81 pivoted into the Fierenwinkel Society 85 of Figure 1.
  • the control disc 83 and the cam plate 102 are thereby in the view according to FIG Twisted clockwise.
  • the corner between the curve sections glides 161 and 163 along the surface section 169 of the pressure piece 145.
  • the pressure piece is thereby displaced in the direction of the screw plug 151, so that the bias of the return spring 149 increases continuously. If the control lever is released at any point, that will reverse Thrust piece 145 and the control lever under the action of the return spring 149 back to the neutral position shown in Figure 2.
  • control lever 81 If the control lever 81 is removed from its neutral position, in which, as can be seen from FIG. the curve section 161 of the curve track 104 and the surface sections 168 and 169 of the pressure piece 145 lie flat against each other, in the direction of Hieven is pivoted, the control disk 83 and the cam disk 102 in the view of Figure 2 rotated counterclockwise.
  • the pressure piece 145 acts on the cam track 104 at the corner between the cam sections 161 and 162, as shown in Figure 4.
  • When swiveling further of the control lever 81 finally reaches the cam section 162 of the cam track 102 in flat contact with the surface section 168 of the pressure piece 145. This state is shown in FIG. 5.
  • the Control lever 81 notices the operator a steep increase in the necessary Actuating force and thus gets a signal that the swallowing volume of the hydraulic motor 12 is adjusted. Finally, the surface 168 of the pressure piece lies 145 at the corner between the curve section 162 and the curve section 160 of the cam track 104, as shown in FIG. 6. There is the Control lever 81 already rotated so far that the plunger 84 of the pressure reducing valve 69 hit the increase 141 of the control curve 105. This does for the operator in a further pressure point during the pivoting of the control lever 81 noticeable. This signals that the next Swiveling out of the control lever the Hievenwinkel Scheme 86 is left. When the control lever 81 is released in the heave angle range, the reset device can 103 return the control lever to its neutral position, because every further deflection of the control lever in this area with an increase the bias of the return spring 149 is connected.
  • the control lever is under increased force, which is used to overcome the increase 141 by the plunger 84 is necessary, further swung out, it arrives first the edge between the two curve sections 168 and 160 and in increasingly higher the curve section 160 in the region of the recess 170 of the pressure piece 145, where the curve section 160 on the surface 171 of the Recess 170 is present.
  • the pressure piece 145 is so far in the direction of the locking screw 151 moved that the pressure spring 150 just barely between the pressure piece and the screw plug.
  • FIG. 7 shows a state in which the plunger 84 has the elevation 141 has just overcome the control curve 105 and the curve section 160 of the Cam track 104 is slightly immersed in the recess 170 and there the surface 171 abuts.
  • the pressure piece 145 is now the force of the spring 149th and additionally from the force of the spring 150 on the cam section 160 of the cam track 104 pressed.
  • the control lever is located in the mooring angle area 87.
  • the distance between the heave angle area and the mooring angle range is about 10 degrees in which the Tappet 84 overcomes the increase 141 of the control curve 105.
  • the one that occurs Increasing the pilot pressure has no effect on the directional valve 35 and the hydraulic motor 12, since at the end of the Hievenwinkel Scheme the directional valve 35 is fully open and the hydraulic motor 12 to its smallest absorption volume is set.
  • the curve section abuts 168 of the cam track 104 against the stop surface 173 of the recess 170, as shown in Figure 8. Another pivoting of the Control lever 81 is no longer possible.
  • control curve 105 is designed in the area 142 in such a way that that with further deflection of the control lever, the tappet 84 continues emerges from the guide bush 118, so that the springs of the pressure reducing valve 69 a torque in the sense of a further deflection on the control lever 81 exercise.
  • the meaning of the groove 172 in the recess also goes in particular from FIG 170 of the pressure piece 145. Through this channel there is an exchange of pressure medium between the spring chamber with the springs 149 and 150 and the cavity 99 in Housing 101 easily ensured even when the control lever 81 is pivoted to the end of the mooring angle range.
  • the groove 155 in the pressure piece 145 has for a control arrangement with mooring operation the winds don't matter. However, not every winch is also suitable for mooring intended.
  • the groove 155 allows the pressure piece 145 for one Use winch without mooring. It will only compare to that shown in Figure 2 rotated 180 degrees about its longitudinal axis in the Housing 101 installed.
  • the pin 156 then engages in the groove 155. Because of the Shortness of this groove, the pin 156 limits the path that the pressure piece 145 to Locking screw 151 can be moved out. This gives you an attack for the control lever at the end of the heave angle range. At the end of Fierenwinkel Anlagen the pin 156 can also be effective.
  • the groove 155 may have previously been pushed by the plunger 84 against the surface 140 of the control curve 105.
  • the groove 155 thus allows a pilot control unit for one Winch without mooring operation and one winch with mooring operation with the same Build up pressure piece 145. An existing winch can also be converted become.
  • the housing 101 has a valve bore 180, in which the movable control element designed as a rotary slide valve 181 Directional control valve 70 is located and in which the various according to Figure 1 to the directional control valve 70 leading lines or line sections, which as holes in the Housing 101 are formed, as described with reference to Figure 10 will be.
  • the valve bore 180 widens at one end to the cavity 99 in which the cam plate 102 and the control plate 83 are located.
  • Cam 102 and control disc 83 are integral with the Rotary valve 181 manufactured.
  • the cavity 99 is through a Housing cover 182 closed, in the center and in alignment with the axis of the Rotary slide valve 181, the shaft 183 is rotatably mounted, which extends over the cover 182 protrudes and attached to the protruding portion of the control lever 81 is.
  • Shaft 183 and rotary valve 181 are over two pins 185, each of which engages axially in a bore of the rotary valve and the shaft, coupled against rotation.
  • a compression spring 186 is accommodated, which is at the bottom of the blind hole and via a ball 187 on the rotary valve Supports 181 and axially pushes shaft 183 and rotary slide valve 181 apart, so that on the one hand the shaft 183 on the cover 182 and the rotary valve 181 over the cam 102 on the housing 101 and the two parts largely Take fixed axial positions.
  • valve bore 180 opens into an im Radius enlarged end space 188, which is directed outwards by a screw plug 189 is closed.
  • the cavity 99 and the space 188 are as shown in FIG dashed and indicated with the reference number 78 from Figure 1 indicated is connected to each other and to the drain line 19.
  • a stepped blind hole 190 is introduced into which the pressure reducing valve 68 is inserted.
  • the blind bore forms axially in front of the pressure reducing valve 68 90 an axial control connection 191 of the pressure reducing valve 68, in the this regulates a constant pilot pressure of 40 bar.
  • An annulus 192 between the pressure reducing valve 68 and the rotary valve 181, which has two Axial bores 193 connected to the space 188 forms the drain connection of the pressure reducing valve 68.
  • a second annular space 194 is the inlet connection of the Pressure reducing valve.
  • the rotary valve 181 is shown in a position which it in the neutral position of the control lever 81 occupies. It can be seen that the grooves 204 and 209 cover the connections 92 and 93, so that these two connections from Are relieved of pressure. Now the rotary valve is used for the winch operating mode moved down in the view of Figure 10, so the connection 92 separated from the groove 204 and overlaps after a short distance the groove 202. The connection 92 is now with the control output of the pressure reducing valve 69 connected. The connection 93 initially remains in register with the groove 209 and is thus relieved of pressure. This constellation remains to the end of the Hievenwinkel Scheme 86 from Figure 1. Then the connection is made 93 out of the area of the groove 209 and overlaps the groove 213. The same pilot pressure is present on it as on port 92.
  • connection remains when the control lever is pivoted in the direction of Fieren 92 in alignment with the groove 204, while the connection 93 in overlap device with the groove 211.
  • the rotary slide 181 also has a circumferential one Groove 215, from which radial bores 216 start, which are in front of the rotary valve 181 used pressure reducing valve 68 open into the blind bore 190, are connected to the control output of the pressure reducing valve 68.
  • the groove 215 and the radial bores 216 are thus in the channel 79 according to FIG. 1, over the at the inlet connection of the pressure reducing valve 69 a largely constant Supply control pressure is present.
  • a groove 217 runs around the rotary slide valve 181, the axial grooves with two diametrically opposite one another short grooves 218 is connected. If the control lever is within the mooring angle range is pivoted, the grooves 218 overlap with the connections 88, so that pressure medium flows via the bypass line 66 from FIG. 1 can.
  • the grooves 218 and thus the groove 217 are via a further annular groove 219 connected with two diametrically opposite grooves 220, with those when the control lever is pivoted out of the neutral position the connection 94 is in register, so that the annular space 15 of the cylinder 14 of Figure 1 can be acted upon with system pressure.
  • connection 94 via a small radial bore 221 of the Rotary valve 181 connected to the axial bores 193 and thus to the tank relieved.
  • the annular space is via the radial bore 222 open to the annular groove 219 194, ie the pressure input of the pressure reducing valve 68 with the annular groove 217 and connected to the bypass line 66.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • General Physics & Mathematics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Servomotors (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Mechanical Control Devices (AREA)
EP00910754A 1999-03-24 2000-03-02 Hydraulische vorsteuerung Revoked EP1163454B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19913276A DE19913276A1 (de) 1999-03-24 1999-03-24 Hydraulische Vorsteuerung
DE19913276 1999-03-24
PCT/EP2000/001790 WO2000057067A1 (de) 1999-03-24 2000-03-02 Hydraulische vorsteuerung

Publications (2)

Publication Number Publication Date
EP1163454A1 EP1163454A1 (de) 2001-12-19
EP1163454B1 true EP1163454B1 (de) 2004-01-07

Family

ID=7902205

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00910754A Revoked EP1163454B1 (de) 1999-03-24 2000-03-02 Hydraulische vorsteuerung

Country Status (7)

Country Link
US (1) US6481461B1 (no)
EP (1) EP1163454B1 (no)
JP (1) JP2002540353A (no)
KR (1) KR20010109320A (no)
DE (2) DE19913276A1 (no)
NO (1) NO20014575D0 (no)
WO (1) WO2000057067A1 (no)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102878142A (zh) * 2012-10-31 2013-01-16 南通润邦重机有限公司 一种比例恒张力液压阀组
DE102010048068B4 (de) 2010-04-16 2022-11-10 Robert Bosch Gmbh Ventilanordnung

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DE10213010A1 (de) 2002-03-22 2003-10-02 Bosch Rexroth Ag Steuerung
KR100706497B1 (ko) * 2003-10-01 2007-04-10 현대중공업 주식회사 압력전환 밸브를 이용한 유압장치
US7152627B2 (en) * 2004-04-05 2006-12-26 R. H. Sheppard Co., Inc. Control valve for a hydraulic power steering system
DE102012012297A1 (de) * 2012-03-30 2013-10-02 Atlas Copco Construction Tools Gmbh Ventil
US10207905B2 (en) 2015-02-05 2019-02-19 Schlumberger Technology Corporation Control system for winch and capstan
CN104632746B (zh) 2015-03-04 2017-11-24 徐州重型机械有限公司 切换阀、切换液压系统以及起重机

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DE116080C (no)
US2523532A (en) 1947-04-30 1950-09-26 Peter J Harinck Hydraulic control valve
US3150685A (en) * 1963-02-21 1964-09-29 Caterpillar Tractor Co Hydraulic control with mechanically vented pump unloading means
DE1601720A1 (de) * 1968-01-29 1971-01-07 Fendt & Co Xaver Hydraulikanlage fuer mehrere Verbraucher
DE2003584A1 (de) * 1969-02-26 1970-09-10 Mita Srl Einrichtung zur Druckmittelverteilung
US3847180A (en) * 1971-12-23 1974-11-12 Caterpillar Tractor Co Low effort, proportional control valve
DD116080A2 (no) * 1974-05-29 1975-11-05
US4436020A (en) * 1982-03-11 1984-03-13 Caterpillar Tractor Company Dual input pressure compensated fluid control valve
DE4316229C2 (de) 1993-05-14 1998-08-13 Mannesmann Rexroth Ag Hydraulisches Vorsteuergerät mit wenigstens einem über einen handbetätigbaren Betätigungshebel einstellbaren hydraulischen Druckregelventil
DE19630798A1 (de) * 1996-06-22 1998-01-02 Rexroth Mannesmann Gmbh Vorsteuerung für zwei hydraulisch betätigbare Wegeventile
DE19654547C2 (de) * 1996-12-27 1999-03-18 Kaessbohrer Gelaendefahrzeug Verfahren zum Betreiben einer Winde und zugehörige Vorrichtung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010048068B4 (de) 2010-04-16 2022-11-10 Robert Bosch Gmbh Ventilanordnung
CN102878142A (zh) * 2012-10-31 2013-01-16 南通润邦重机有限公司 一种比例恒张力液压阀组

Also Published As

Publication number Publication date
DE50004983D1 (de) 2004-02-12
KR20010109320A (ko) 2001-12-08
NO20014575L (no) 2001-09-20
EP1163454A1 (de) 2001-12-19
WO2000057067A1 (de) 2000-09-28
NO20014575D0 (no) 2001-09-20
JP2002540353A (ja) 2002-11-26
DE19913276A1 (de) 2000-09-28
US6481461B1 (en) 2002-11-19

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