[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP1069317B1 - Directional control valve section, especially for mobile equipment - Google Patents

Directional control valve section, especially for mobile equipment Download PDF

Info

Publication number
EP1069317B1
EP1069317B1 EP00112754A EP00112754A EP1069317B1 EP 1069317 B1 EP1069317 B1 EP 1069317B1 EP 00112754 A EP00112754 A EP 00112754A EP 00112754 A EP00112754 A EP 00112754A EP 1069317 B1 EP1069317 B1 EP 1069317B1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
bore
inlet
plate according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00112754A
Other languages
German (de)
French (fr)
Other versions
EP1069317A2 (en
EP1069317A3 (en
Inventor
Peter BÜTTNER
Thassilo Maxeiner
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
Priority claimed from DE19948232A external-priority patent/DE19948232A1/en
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1069317A2 publication Critical patent/EP1069317A2/en
Publication of EP1069317A3 publication Critical patent/EP1069317A3/en
Application granted granted Critical
Publication of EP1069317B1 publication Critical patent/EP1069317B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/2264Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267Valves or distributors
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/2203Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/226Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/2264Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271Actuators and supports therefor and protection therefor
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/2278Hydraulic circuits
    • E02F9/2296Systems with a variable displacement pump
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401Valve members; Fluid interconnections therefor
    • F15B13/0402Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds

Definitions

  • the invention relates to a directional valve disc, which has several similar Valve disks used to control various hydraulic consumers
  • Direction and speed serve to a control block, in particular can be assembled into a load sensing control block and, seen in terms of flow, between a hydraulic pump and the directional valve disks of the control block is arranged.
  • valve disc From DE 43 24 177 A1 or DE 197 14 141 A1 it is known such Design the valve disc so that it fulfills an emergency stop function.
  • the valve or valves contained in the valve disc come into one State in which one runs between the hydraulic pump and the valve disc Pump line and an outgoing from the input disc and through the Directional valve disks leading inlet line are blocked against each other. Also in the event of an inadvertent actuation of a directional valve disc, one of them is activated connected hydraulic consumer not adjusted.
  • the input valve disc can also have the function that is controlled by the control block leading supply line and another supply line leading to another Directional control valve or to other directional control valves, which also form a control block can be summarized, or directly to a hydraulic consumer leads to the pump line in different ways depending on the position connect. For example, both in a neutral position of the input valve disc Inlet lines to the pump line must be shut off. Depending on the direction of the Adjustment from the neutral position is only the one feed line or only the other supply line connected to the pump line. Then it hangs depending on the condition of the inlet valve disc, which hydraulic consumers can be operated. It is also conceivable that in the neutral position of the input valve disc both supply lines are connected to the pump line.
  • Directional valve disks are from the data sheet RD 64 282 / 01.97 from the applicant known that have the features from the preamble of claim 1.
  • These directional valve disks are proportional valves based on the load-sensing principle, with which the hydraulic consumers regardless of the respective Load pressure only in dependence on those that can be changed by adjusting the valve pistons Flow cross sections of measuring throttles are controllable.
  • These directional valve disks are used in conjunction with an adjustable hydraulic pump, which is controlled by the highest load pressure so that in the pump line one above the highest load pressure by a certain pressure difference Pump pressure is present.
  • the control piston of a pressure compensator which is at a simultaneous actuation of several directional valve disks the pump pressure one by a certain pressure difference over the individual load pressure of a hydraulic consumer throttled pressure, provided that this individual Load pressure is not the highest load pressure.
  • the pressure compensator is therefore the respective one Measuring choke upstream.
  • the disc-shaped valve housings are cast from iron and as a blank then finished. When casting a valve housing becomes formation the cavities inside use a sand core.
  • the invention has for its object an input valve disc, the one Emergency stop function or the function of a connection of different supply lines with the pump line has to manufacture in an inexpensive manner.
  • the set goal is achieved according to the invention by a directional valve disc, which, in addition to the characteristics from the generic term, also with the characteristics is equipped from the characterizing part of claim 1.
  • the invention is based on the idea for the valve housing of the inlet valve disc, which differs in function from the function of the LS directional valve disks, nevertheless as a raw part that also for the LS directional valve disks in large To use the number of cast raw parts. This eliminates the manufacturing of separate sand cores as well as those with treatment and storage logistical and organizational costs associated with different raw parts.
  • the directional valve disc Due to the features from the characterizing part of patent claim 1 the directional valve disc is designed in a relatively simple way so that it Functions of the input valve disc fulfilled and easily with LS directional control valve discs of the known type assembled into a control block can be.
  • So according to claim 2 is preferably in the neutral position of the valve piston at least one outer connection chamber shut off to the inlet chamber.
  • this external connection chamber and one connected to it Inlet line fulfills an emergency stop function.
  • This emergency stop function is special sure if according to claim 3 in the neutral position of the valve piston an external connection chamber, which is shut off from the inlet chamber, fluidically a drain chamber is connected. So a creeping movement is one hydraulic consumer excluded if a mere isolation of a Inlet line to the pump line due to the valve disc on the inlet side leakage would take place.
  • the first external connection in parallel Directional control valves or a hydraulic consumer pressure medium supply.
  • the first external connection closed by locking means so that in a position of the valve piston, in which the first outer connection chamber with the inlet chamber connects the hydraulic consumers that can then be operated in parallel each with the aligned holes of the valve discs Pressure medium are supplied.
  • the input valve disc can also be used to control the speed, with which a hydraulic consumer can be moved.
  • the valve piston according to claim 5 for connecting an external connection chamber, in particular the second external connection chamber with the inlet chamber Control grooves on a very specific in a position of the valve piston Flow cross-section between the inlet chamber and the outer connection chamber to open.
  • the valve piston can also be continuously adjustable, to change this flow area.
  • a load-dependent Signal to the pump controller to be reported to speed to be able to adjust the hydraulic load independently of the load.
  • the inlet bore opens outside of the first valve bore in the inlet cavity.
  • the first valve bore from the inlet bore the diameter of which is normally chosen to be larger is the axial extension of the inlet chamber through the inlet bore not interrupted and the guidance of the valve piston in the first valve bore unaffected.
  • Annular chamber of the second valve bore cutting through a in the valve housing screwed plug is closed on one side. The pressure prevailing in the bore acts on the plug Valve body in one direction, while the pressure in the as a blind hole trained inlet bore acts in the opposite direction.
  • the tie rods holding the control block together are essentially the same loaded, as if only directional control valve discs of the known type to one Control block would be summarized.
  • the fourth channel is advantageously a blind hole according to claim 12, through the first external connection, the first external connection channel and the first valve bore is made in the valve housing. Different to when drilling in the opposite direction, there is no plug necessary.
  • the first is Separating element or a one-piece separating piston in the second valve bore so arranged that at most a very small axial movement takes place can.
  • a known hydraulic system is used Control arrangement an additional throttle present in the supply line can be switched between the hydraulic pump and the control block.
  • a directional valve disc according to the invention can be in the supply line switchable choke in a very economical and space-saving manner realize that a separating piston according to claim 15 in the second valve bore is used, the one the second annular chamber from another section has the second valve bore separating piston section, and that the separating piston for setting flow cross sections of different sizes of the inlet fluid path between the inlet bore and the first annular chamber cutting bore between two end positions controlled axially is movable.
  • the inlet bore opens in the area of the second Valve bore in the inlet cavity and with the separating piston are different large flow cross sections between the inlet bore and the third Channel adjustable.
  • the separating piston different flow cross sections between the first annular chamber and the fourth channel and / or the first Ring chamber cutting hole can be adjustable.
  • the separating piston is in particular hydraulically adjustable according to claim 19.
  • a pilot valve for this purpose, through which a pressure chamber at the first End face of a second piston section with an annular chamber Pressure can be applied and pressure can be relieved.
  • the Pressure chamber for pressurizing the fluid path between the inlet bore and the bore cutting the first annular chamber and for pressure relief connected to a tank channel.
  • a Tank channel in the directional valve disc, so that when the pilot valve according Claim 22 is attached to the disc housing for control of the separating piston no externally visible lines are necessary.
  • a pressure relief valve allows the pressure in an external connection chamber a directional valve disc according to the invention limited to a maximum value become. According to claim 22, such a pressure relief valve is now in particular the pressure relief valve connected to the first outer connection chamber, when the separating piston is moved to another Adjustable pressure value. So it can then, for example, exceed the normal level additional loads can be moved with care.
  • a variable displacement pump 10 sucks with a load-sensing regulator 11 pressure medium from a tank 12 and there into a pump line 13 leading to a control block 14. This is over a series of disks composed by not shown Tie rods are held together.
  • a connecting washer 15 serves to be flexible or to be able to connect rigid lines to the control block. It is this the section of the pump line 13 between the variable displacement pump 10 and the Control block 14 runs.
  • this is a tank line 16 by a Tank connection leads to the tank 12, and a load reporting line 17 by a LS connection to LS controller 11 leads.
  • the pump line 13 settles in the connection plate 15 and in the following directional valve disc 20, which the inventive Directional valve disc is.
  • Directional valve disks 21 constructed according to the load-sensing principle, which are used for controlling various hydraulic consumers of a mobile implement, e.g. a fire brigade ladder, and of which only a single directional valve disc is shown.
  • Each of these directional valve disks 21 contains a proportional adjustable directional valve 22, with which the direction can be determined in which the corresponding hydraulic consumer moves, and with one metering throttle determining the speed of the hydraulic consumer can be opened to different degrees, and one upstream of the metering throttle Pressure compensator 23, which is independent of the load via a certain pressure difference maintains the metering throttle.
  • Each LS directional valve disc 21 also has two continuously adjustable by a proportional electromagnet 24 and pilot valves 25 and 25 that function on the basis of pressure reducing valves 26 with a pressure input to a control pressure supply line 27, with a tank outlet with a control pressure relief line 28 and with a Control output on one control side or the other control side of the directional valve 22 are connected.
  • the control pressure supply line 27 and the Control pressure relief line 28 pass through all disks 20 and 21 to an end plate 29 in which a pressure reducing valve 30, the control output is connected to the control pressure supply line 27, and a pressure relief valve 31 are housed, the pressure in the control pressure supply line 27 secured.
  • a connection Y is present.
  • a terminal X of the end plate 29, which enables an external control oil supply is closed.
  • the pressure reducing valve 30 reduces the pressure in the pump line 13 to maximum control pressure.
  • its pressure input is on a control oil supply line 32 connected, also through all valve disks 20 and 21 leads into the end plate 29 and within the plate 20 to the Pump line 13 is connected.
  • a tank channel 33 also passes through the disks 15, 20 and 21 to the end plate 29.
  • the directional valve disc 20 of the two embodiments a disc-shaped valve housing 40, through which a first valve bore 41 passes.
  • a valve spool 42 axially movable.
  • the length of the valve spool 42 is correct with the length of the valve bore 41 from one end face 43 to the other Face 44 of the valve housing 40 match.
  • the valve bore 41 is five axially spaced control chambers surrounding the control the inflow of pressure medium from the pump line 13 to an external connection 45 of the valve housing 40 or to a perpendicular to the disc plane running bore 46 serve to corresponding holes 47 in the Directional valve disks 21 is open.
  • the bore 46 and the bores 47 in the Directional valve disks 21 form an inlet line closed at both ends for the LS directional valve disks 21.
  • the middle of the five control chambers is as Inlet chamber 48 designated because you the pressure medium pumped by the pump 10 accrues.
  • On each external connection chamber 49 and 50 there follows a drain chamber 56 or 57, which leads to that through the valve housing 40 passing tank channel 33 is open.
  • the valve spool 42 takes due to two centering springs 60 which in the End faces 43 and 44 of the valve housing 40 fastened and the valve bore 41 covers 61 and 62 which close to the outside are accommodated, a middle position on.
  • two slide collars 63 and 64 lock the Valve slide 42, between which there is an inlet chamber 48 Slider neck 65 is located, the two outer connection chambers 49 and 50 against the inlet chamber 48.
  • it is the outer connection chamber 49 over the Annulus around a further slide neck 66 with the drain chamber 56 and the outer connection chamber 50 via an annular space around a slide neck 67 connected to the drain chamber 57. Closes the slide neck 66 another slide collar, which holds the spring chamber in one cover 62 seals against the drain chamber 56.
  • slide collar 68 is longer than the slide collar on the other spring chamber and has an annular groove 69, which is in the range of three axially from each other spaced annular chambers 70, 71 and 72 of the valve bore 41 is located.
  • the valve spool 42 has 64 control grooves 73 in the slide collar, which for Inlet chamber 48 are open and with which a flow cross-section between the inlet chamber 48 and the outer connection chamber 50 by different wide movement of the valve spool 42 out of its central position into one first direction can be opened to different degrees.
  • This flow cross section represents a metering throttle, which is shown in the circuit diagrams according to FIGS and 4 is designated by the reference number 73 of the fine control grooves.
  • Between Fine control grooves 73 are made in the slide collar 64 cross bores 74, which are closed in the middle position of the valve spool and which are in an axial bore 75 open.
  • annular chamber 72 also serves to together with grooves 77 and 78 in the valve slide 42, the annular chamber 71 to the drain chamber 57 out of pressure to relieve when the valve spool 42 in the shown in Figures 2 and 5 Middle position or in the opposite direction to the first direction, second direction has been moved to the stop.
  • valve spool 42 becomes like that of a switching valve each moved to an end position in which a maximum flow cross-section present between the inlet chamber 48 and the outer connection chamber 49 is.
  • the valve spool 42 is pressurized into the spring chambers Lids 61 and 62 operated hydraulically.
  • One pilot valve 80 is a through the electromagnet continuously adjustable pressure reducing valve, one of which Control pressure in the spring chamber of the cover 62 can be controlled to the valve slide 42 continuously adjustable.
  • the pilot valve 81 is a switching valve that to actuate the valve slide 42, the spring chamber in the cover 61 with the control pressure supply line 27 connects and otherwise this spring space Control pressure relief line 28 relieved.
  • It can also be a modified valve spool 42 and a modified cover 62 can be used, which allow the valve slide can also be adjusted manually using a hand lever.
  • valve bore 41 From the end face 44 of the valve housing 40, this is parallel to the first Valve bore 41 introduced a second valve bore 82, which is used as a blind bore is formed and in the near its bottom 83 one of the annular chamber 71 of the first valve bore 41 outgoing housing channel 84 opens.
  • a screw plug 85 By a screw plug 85, the valve bore 82 is closed to the outside.
  • Slightly offset axially to the outer connection chamber 49 of the valve bore 41 has the Valve bore 82 has a first annular chamber 86. This is perpendicular to the the sectional plane according to Figures 2 and 5 extending bore 46 cut.
  • valve bore 41 displaces a second annular chamber 87, which via a channel 88 is fluidly connected to the inlet chamber 48 of the valve bore 41.
  • this is the third channel.
  • valve housing 40 As far as the valve housing 40 so far with regard to the valve bores Chambers and with regard to the channels has been described, it agrees the valve housing of the directional valve disks 21.
  • a fourth channel 89 is present, through which the first annular chamber 86 of the second valve bore 82 fluidly with the outer connection chamber 49 of the first valve bore 41 connected is.
  • This fourth channel is as a circular hole or as elongated hole through the outer connection 53, the channel 51 and the valve bore 41 introduced into the material of the valve housing 40.
  • a one-piece Separating piston 90 is used, which is axially aligned with a first piston section 91 located between the two annular chambers 86 and 87 and these against each other seals.
  • a second piston section 92 is located via a rod 93 connected to the piston section 91, beyond the annular chamber 87 and seals it against a pressure chamber 94 of the valve bore 82, which in the valve housing 40 built-in shuttle valve 35 is connected and in which in the Central position of the valve slide 42 and when it is displaced, according to FIG. 2 considered, tank pressure to the right and in the case of a shift to the left External connection 45 prevailing pressure.
  • a one-piece Separating piston 110 is used, which is connected to a first piston section 111 located axially between the two annular chambers 86 and 87 and these against each other seals.
  • the piston section 111 is axially somewhat larger than the corresponding one Piston section 91 of the separating piston 90 and protrudes in the position shown of the separating piston 110 slightly into the annular chamber 87.
  • a second Piston section 112 of the separating piston 110 is located via a rod 113 connected to the piston section 111, beyond the annular chamber 87 and seals this against the pressure chamber 94 of the valve bore 82, which as in the first Embodiment continuously on the shuttle valve installed in the valve housing 40 35 is connected and in the middle position of the valve spool 42 and when it is shifted, viewed according to FIG. 2, to the right tank pressure and in the event of a shift to the left, the one prevailing in the external connection 45 There is pressure.
  • piston section 112 is shown in FIG Towards the bottom 83 of the valve bore 82 a rod 115.
  • the separating piston 110 is moved in the direction of the position shown in FIG Compression spring 118 loaded between the piston portion 112 and the bottom 83 of the valve bore 82 is clamped, and can hydraulically against the compression spring 118 be operated.
  • a pressure chamber 119 available to the control connection 125 of a pilot valve 130 designed as a 3/2 way switching valve is.
  • Its housing 131 is directly on the opposite of the external connections Flanged side of the valve housing 40.
  • the pilot valve 130 has in addition to the control port 125, a pressure port 132, which Bores in the housings 40 and 131 internally with the bore 46 ( Figure 5) or alternatively is fluidly connected to a bore 98 (FIG.
  • a tank connection 133 which also has holes in the housings 40 and 131 is fluidly connected internally to the drain chamber 56 of the housing 40.
  • the pressure chamber 119 In the shown rest position of the pilot valve, the pressure chamber 119 is above the Tank connection 133 relieved of pressure. If the pilot valve by control an electromagnet is brought into the switched position, the pressure chamber 119 with the pressure prevailing in the bore 46 or 98 and the separating piston 110 against the force of the compression spring 118 in a second end position brought in which he with the rod 115 at the bottom 83 of the valve bore 82nd abuts. In the second end position, the piston sections 111 and 117 protrude far into the annular chambers 86 and 87 and narrowing compared to that shown in FIG.
  • the separating piston 110 Position of the separating piston 110 the flow cross sections between the Hole 98 and channel 88 and between channel 89 and the bore 46.
  • the separating piston 110 can thus be part of a 2/2 way valve with a wide open position and a throttle position. In Figure 4 this is Valve, but only with its part located upstream of valve bore 41, drawn and provided with the reference number 110 of the movable separating piston. This also indicates that not both piston sections are necessary 111 and 117 must have a throttling effect.
  • the piston section 117 can be made shorter than shown in Figure 5, so that it also in the second end position of the separating piston does not protrude into the annular chamber 86. This will be made dependent on the desired throttling effect.
  • the pressure in the external connection 45 is indicated by an in in the valve housing 40 screwed pressure relief valve 127 to one limited value.
  • the outer connection channel 51 is through a another pressure relief valve secured against excessive pressure.
  • this further pressure relief valve 128 like the pressure relief valve 127 by hand to a certain value adjustable, which is maintained during operation.
  • the further pressure relief valve 129 of the embodiment according to FIGS. 4 and 5, on the other hand, is a pressure relief valve with pressure connection stage. By pressurizing one in a spring supported on the valve of Cologne's valve becomes stronger preloaded and thereby set a higher pressure value.
  • Such pressure relief valves are generally known, e.g.
  • Control of the pressure connection stage of valve 129 runs through a control line 134 between the housing 131 of the pilot valve and the valve 129. Within the Housing 131, this control line 134 is connected to the control connection 125.
  • the bore 98 is in both embodiments as an inlet pocket bore of the side facing away from the directional valve disks in the valve housing 40 in Area of the second annular chamber 87 of the second valve bore 82, thus runs parallel to the bore 46.
  • the bore 98 is to the annular chamber 87 open towards. It is also open to one of the terminal P of the connecting washer 15 outgoing channel and thus forms part of the pump line 13.
  • the Bore 46 closed with a threaded plug 99, as can be seen in Figure 3 is. For this purpose, an internal thread has been cut into the bore 46.
  • the plug 52 is also omitted in the outer connection 53, so that the fourth channel 89 can be seen.
  • pilot control channel 32 In addition to the channels 27 and 28 used for pilot control, this also works the pilot control channel 32 through the valve housing 20 and Directional valve disks 21 and into the end disk 29. On this channel the pressure input of the pressure reducing valve 30 is connected. Within the connecting disc 15, the channel 32 is connected to the pump line 13. The pilot control is supplied with control oil via it, regardless of which position the valve slide 42 is.
  • the LS directional valve disks 21 are intended for hydraulic consumers to operate the working hydraulics of a mobile working device.
  • the pump 10 conveyed pressure medium flow to one or more hydraulic cylinders 101, with to e.g. Supports of the mobile implement are operated.
  • the direction in the piston of the hydraulic cylinder 101 is moved by the position of a 4/3-way valve 102 determines that with an inlet connection with the external connection 45 of the directional valve disc 20 and with a drain connection with tank 12 connected is.
  • the directional control valve 102 is spring-centered in a central position in which its inlet, its outlet and its two cylinder connections against each other are cordoned off. Depending on the working position, the piston rods of the hydraulic cylinders move 101 off or on.
  • pilot valve 80 If neither the pilot valve 80 nor that in the two exemplary embodiments Pilot valve 81 is actuated by the respective electromagnet, the Valve slide 42 in the rest position shown in the figures, in which the two External connection chambers 49 and 50 against the inlet chamber 48 and thus against the pump line is shut off and connected to the tank line 33.
  • the Directional valve disc 20 fulfills an emergency stop function insofar as after actuation of an emergency stop button, both pilot valves 80 and 81 assume their rest position and neither via the directional valve disks 21 nor via the valve 102 hydraulic consumer can be operated.
  • the valve spool 42 is off the middle position shown in Figures 1 and 2 moved in the other direction, the metering throttle 73 is opened in accordance with the movement distance, while the outer connection chamber 49 is separated from the inlet chamber 48 remains.
  • Pressure medium delivered by the pump 10 can now be delivered via the pump line 13 including bore 98, via channel 88 and the inlet chamber 48, via the metering throttle 73, the outer connection chamber 50, the channel 54 and get the external connection 45 to the inlet connection of the directional valve 102.
  • the pressure medium flows through a lowering brake valve 103 to the pressure chamber of the hydraulic cylinders 101 on the piston rod side, so that the piston rods extend.
  • the pressure downstream of the metering throttle 73 So the load pressure, the transverse bores 74, the axial bore 75, the Damping nozzle 76, the annular chamber 71 and the channel 84, the pressure chamber 94, the shuttle valve 35 of the disk 20 and the load signal line 17 to the pump controller 11 reported.
  • the variable displacement pump 10 delivers just as much pressure medium, that in the pump line 13 a by a certain pressure difference on the pump regulator 11 is set, pressure above the reported load pressure prevails.
  • the pressure difference across the orifice 73 is independent of reported load pressure, so that the amount of pressure fluid flowing through the metering throttle depends solely on the flow cross section of the metering throttle. This is also in the other working position of the directional valve 102, the Lowering brake valve 103 ensures that in the piston rod-side, annular Pressure space of the hydraulic cylinder 101 a certain pressure is maintained.
  • the directional valve disk 20 If there are no further consumers 101 connected to the external connection the directional valve disk 20 are to be supplied with pressure medium, so will the port 45 closed with a plug. The directional valve disk 20 is satisfied then an emergency stop function for the directional valve disks 21, a modified one Valve slide without fine control grooves and without load reporting holes used becomes.
  • the above operation is the only one for the first embodiment possible and normal operation for the second embodiment.
  • the exemplary embodiment takes the pilot valve 130 in FIGS. 4 and 5 position shown.
  • the pressure chamber 119 is relieved, so that the spring 118 the Separating piston 110 holds in the first end position shown.
  • the pressure connection stage of valve 129 is deactivated.
  • the pilot valve is only switched when the valve spool 42 in the sense of a fluid connection between the inlet chamber 48 and the outer connection chamber 49 is actuated. By switching the pilot valve 130, the pressure chamber 119 pressurized and the separating piston 110 in the second end position brought.
  • the fluid path between the inlet bore 98 and the bore 46 is now throttled so that the inflow of pressure medium to the directional valve disks 21 is reduced compared to normal operation.
  • the Pilot valve 130 activates the pressure connection stage of the pressure limiting valve 129, so the maximum pressure of z. B. 270 bar increased to 350 bar. It can now be high Loads are moved with care.
  • the pilot valve 130 is also possible if the valve slide 42 in the sense of a fluidic connection between the Inlet chamber 48 and the outer connection chamber 50 has been actuated. Then can also be one or more hydraulic via the external connection 45 The amount of pressure medium flowing to consumers can be reduced.
  • the pilot valve 130 is only activated when the valve slide 42 is actuated in the sense of a fluidic connection between the inlet chamber 48 and the External connection chamber 50 switched.
  • the pressure relief valve is 129 with pressure connection stage through a simple pressure relief valve 128 replaced.
  • the pressure port 132 of the pilot valve 130 fluidically preferred with the bore 98, but possibly also with the through the second annular chamber 87 of the valve bore 82, the channel 88 and the inlet chamber 48 of the valve bore 41 formed inlet cavity in which the pressure because of the throttling in the second end position of the separating piston somewhat lower is connected as in the bore 98, because when the valve spool is actuated 42 in the sense of a fluidic connection between the inlet chamber 48 and the outer connection chamber 50 in the bore 46 tank pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Compressor (AREA)
  • Feeding Of Workpieces (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Sliding Valves (AREA)

Abstract

Path valve disk has a cast housing with a design that accommodates the disk itself which is also a mass produced cast part. The valve housing accommodates the valve disk, which operates on the load sensing principle. The design has a new sand core for use in the casting process to accommodate the valve disk. In a second valve bore of a regulating piston a pressure scale is incorporated.

Description

Die Erfindung betrifft eine Wegeventilscheibe, die mit mehreren gleichartigen Ventilscheiben, die zur Steuerung verschiedener hydraulischer Verbraucher hinsichtlich Richtung und Geschwindigkeit dienen, zu einem Steuerblock, insbesondere zu einem Load Sensing Steuerblock zusammengebaut werden kann und, strömungsmäßig gesehen, zwischen einer Hydropumpe und den Wegeventilscheiben des Steuerblocks angeordnet ist.The invention relates to a directional valve disc, which has several similar Valve disks used to control various hydraulic consumers Direction and speed serve to a control block, in particular can be assembled into a load sensing control block and, seen in terms of flow, between a hydraulic pump and the directional valve disks of the control block is arranged.

Aus der DE 43 24 177 A1 oder der DE 197 14 141 A1 ist es bekannt, eine solche Ventilscheibe so auszubilden, daß sie eine Not-Aus-Funktion erfüllt. Bei einem Not-Aus kommen das oder die in der Ventilscheibe enthaltenen Ventile in einen Zustand, in der eine zwischen der Hydropumpe und der Ventilscheibe verlaufende Pumpenleitung und eine von der Eingangsscheibe ausgehende und durch die Wegeventilscheiben führende Zulaufleitung gegeneinander abgesperrt sind. Auch bei einer versehentlichen Betätigung einer Wegeventilscheibe wird somit ein daran angeschlossener hydraulischer Verbraucher nicht verstellt.From DE 43 24 177 A1 or DE 197 14 141 A1 it is known such Design the valve disc so that it fulfills an emergency stop function. At a In an emergency stop, the valve or valves contained in the valve disc come into one State in which one runs between the hydraulic pump and the valve disc Pump line and an outgoing from the input disc and through the Directional valve disks leading inlet line are blocked against each other. Also in the event of an inadvertent actuation of a directional valve disc, one of them is activated connected hydraulic consumer not adjusted.

Die Eingangsventilscheibe kann auch die Funktion haben, die durch den Steuerblock führende Zulaufleitung und eine weitere Zulaufleitung, die zu einem weiteren Wegeventil oder zu weiteren Wegeventilen, die ebenfalls zu einem Steuerblock zusammengefaßt sein können, oder auch direkt zu einem hydraulischen Verbraucher führt, je nach Stellung in unterschiedlicher Weise mit der Pumpenleitung zu verbinden. So können z.B. in einer Neutralstellung der Eingangsventilscheibe beide Zulaufleitungen zur Pumpenleitung abgesperrt sein. Je nach Richtung der Verstellung aus der Neutralstellung heraus wird nur die eine Zulaufleitung oder nur die andere Zulaufleitung an die Pumpenleitung angeschlossen. Dann hängt es vom Zustand der Eingangsventilscheibe ab, welche hydraulischen Verbraucher betätigt werden können. Denkbar ist es auch, daß in der Neutralstellung der Eingangsventilscheibe beide Zulaufleitungen mit der Pumpenleitung verbunden sind.The input valve disc can also have the function that is controlled by the control block leading supply line and another supply line leading to another Directional control valve or to other directional control valves, which also form a control block can be summarized, or directly to a hydraulic consumer leads to the pump line in different ways depending on the position connect. For example, both in a neutral position of the input valve disc Inlet lines to the pump line must be shut off. Depending on the direction of the Adjustment from the neutral position is only the one feed line or only the other supply line connected to the pump line. Then it hangs depending on the condition of the inlet valve disc, which hydraulic consumers can be operated. It is also conceivable that in the neutral position of the input valve disc both supply lines are connected to the pump line.

Aus dem Datenblatt RD 64 282/01.97 der Anmelderin sind Wegeventilscheiben bekannt, die die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweisen. Diese Wegeventilscheiben sind Proportionalventile nach dem Load-Sensing-Prinzip, mit denen die hydraulischen Verbraucher unabhängig vom jeweiligen Lastdruck allein in Abhängigkeit von den durch Verstellung der Ventilkolben veränderbaren Durchflußquerschnitten von Meßdrosseln steuerbar sind. Diese Wegeventilscheiben werden in Verbindung mit einer verstellbaren Hydropumpe verwendet, die vom höchsten Lastdruck derart gesteuert wird, daß in der Pumpenleitung ein um eine bestimmte Druckdifferenz über dem höchsten Lastdruck liegender Pumpendruck ansteht. In der zweiten Ventilbohrung der bekannten Wegeventilscheiben befindet sich der Regelkolben einer Druckwaage, die bei einer gleichzeitigen Betätigung mehrerer Wegeventilscheiben den Pumpendruck auf einen um eine bestimmte Druckdifferenz über dem individuellen Lastdruck eines hydraulischen Verbrauchers liegenden Druck abdrosselt, sofern dieser individuelle Lastdruck nicht der höchste Lastdruck ist. Die Druckwaage ist also der jeweiligen Meßdrossel vorgeschaltet.Directional valve disks are from the data sheet RD 64 282 / 01.97 from the applicant known that have the features from the preamble of claim 1. These directional valve disks are proportional valves based on the load-sensing principle, with which the hydraulic consumers regardless of the respective Load pressure only in dependence on those that can be changed by adjusting the valve pistons Flow cross sections of measuring throttles are controllable. These directional valve disks are used in conjunction with an adjustable hydraulic pump, which is controlled by the highest load pressure so that in the pump line one above the highest load pressure by a certain pressure difference Pump pressure is present. In the second valve bore of the known directional valve disks is the control piston of a pressure compensator, which is at a simultaneous actuation of several directional valve disks the pump pressure one by a certain pressure difference over the individual load pressure of a hydraulic consumer throttled pressure, provided that this individual Load pressure is not the highest load pressure. The pressure compensator is therefore the respective one Measuring choke upstream.

Die scheibenförmigen Ventilgehäuse werden als Rohteil aus Eisen gegossen und anschließend fertigbearbeitet. Beim Gießen eines Ventilgehäuses wird zur Bildung der Hohlräume in seinem Innern ein Sandkern verwendet.The disc-shaped valve housings are cast from iron and as a blank then finished. When casting a valve housing becomes formation the cavities inside use a sand core.

Der Erfindung liegt die Aufgabe zugrunde, eine Eingangsventilscheibe, die eine Not-Aus-Funktion oder die Funktion einer Verbindung verschiedener Zuleitungen mit der Pumpenleitung hat, auf eine kostengünstige Weise herzustellen. The invention has for its object an input valve disc, the one Emergency stop function or the function of a connection of different supply lines with the pump line has to manufacture in an inexpensive manner.

Das gesetzte Ziel wird erfindungsgemäß durch eine Wegeventilscheibe erreicht, die außer mit den Merkmalen aus dem Oberbegriff zusätzlich mit den Merkmalen aus dem kennzeichnenden Teil des Patentanspruchs 1 ausgestattet ist. Die Erfindung fußt zunächst auf dem Gedanken, für das Ventilgehäuse der Eingangsventilscheibe, die in ihrer Funktion von der Funktion der LS-Wegeventilscheiben abweicht, trotzdem als Rohteil das auch für die LS-Wegeventilscheiben in großen Stückzahlen gegossene Rohteil zu verwenden. Damit entfallen die mit der Herstellung von gesonderten Sandkernen sowie die mit der Behandlung und Lagerung unterschiedlicher Rohteile verbundenen logistischen und organisatorischen Kosten. Durch die Merkmale aus dem kennzeichnenden Teil des Patentanspruchs 1 wird die Wegeventilscheibe auf relativ einfache Weise so gestaltet, daß sie die Funktionen der Eingangsventilscheibe erfüllt und ohne weiteres mit LS-Wegeventilscheiben der bekannten Art zu einem Steuerblock zusammengebaut werden kann.The set goal is achieved according to the invention by a directional valve disc, which, in addition to the characteristics from the generic term, also with the characteristics is equipped from the characterizing part of claim 1. The invention is based on the idea for the valve housing of the inlet valve disc, which differs in function from the function of the LS directional valve disks, nevertheless as a raw part that also for the LS directional valve disks in large To use the number of cast raw parts. This eliminates the manufacturing of separate sand cores as well as those with treatment and storage logistical and organizational costs associated with different raw parts. Due to the features from the characterizing part of patent claim 1 the directional valve disc is designed in a relatively simple way so that it Functions of the input valve disc fulfilled and easily with LS directional control valve discs of the known type assembled into a control block can be.

Vorteilhafte Ausgestaltungen einer erfindungsgemäßen Wegeventilscheibe kann man den Unteransprüchen entnehmen.Advantageous embodiments of a directional valve disk according to the invention can one can see from the subclaims.

So ist gemäß Patentanspruch 2 bevorzugt in der Neutralstellung des Ventilkolbens zumindest eine Außenanschlußkammer zur Zulaufkammer abgesperrt. Somit wird hinsichtlich dieser Außenanschlußkammer und einer mit ihr verbundenen Zulaufleitung eine Not-Aus-Funktion erfüllt. Diese Not-Aus-Funktion ist besonders sicher, wenn gemäß Patentanspruch 3 in der Neutralstellung des Ventilkolbens eine zur Zulaufkammer abgesperrte Außenanschlußkammer fluidisch mit einer Ablaufkammer verbunden ist. Somit ist eine schleichende Bewegung eines hydraulischen Verbrauchers ausgeschlossen, die bei einer bloßen Absperrung einer Zulaufleitung zur Pumpenleitung aufgrund von über die eingangsseitige Ventilscheibe stattfindender Leckage möglich wäre. Ist eine erfindungsgemäße Wegeventilscheibe mit Ventilscheiben bekannter Bauweise zu einem Steuerblock zusammengefaßt, so fluchtet die die erste Ringkammer der zweiten Ventilbohrung anschneidende und senkrecht zur Scheibenebene verlaufende Bohrung mit den entsprechenden Bohrungen in den anderen Wegeventilscheiben. Diesen fließt dann Druckmittel über die erste Ringkammer der zweiten Ventilbohrung und die diese Ringkammer anschneidende Bohrung zu. Grundsätzlich ist es möglich, parallel dazu über den ersten Außenanschluß weiteren Wegeventilen oder auch direkt einem hydraulischen Verbraucher Druckmittel zuzuführen. Üblicherweise ist jedoch gemäß Patentanspruch 4 der erste Außenanschluß durch Verschlußmittel verschlossen, so daß in einer Stellung des Ventilkolbens, in der dieser die erste Außenanschlußkammer mit der Zulaufkammer verbindet, die dann parallel zueinander betreibbaren hydraulischen Verbraucher jeweils über die miteinander fluchtenden Bohrungen der Ventilscheiben mit Druckmittel versorgt werden.So according to claim 2 is preferably in the neutral position of the valve piston at least one outer connection chamber shut off to the inlet chamber. Thus, regarding this external connection chamber and one connected to it Inlet line fulfills an emergency stop function. This emergency stop function is special sure if according to claim 3 in the neutral position of the valve piston an external connection chamber, which is shut off from the inlet chamber, fluidically a drain chamber is connected. So a creeping movement is one hydraulic consumer excluded if a mere isolation of a Inlet line to the pump line due to the valve disc on the inlet side leakage would take place. Is a directional valve disc according to the invention with valve disks of known construction combined into a control block, the first ring chamber is aligned the second valve bore cutting and perpendicular to the disc plane running hole with the corresponding holes in the other directional valve disks. This then flows pressure medium through the first annular chamber of the second valve bore and the bore cutting this annular chamber. Basically, it is possible to use the first external connection in parallel Directional control valves or a hydraulic consumer pressure medium supply. Usually, however, according to claim 4, the first external connection closed by locking means so that in a position of the valve piston, in which the first outer connection chamber with the inlet chamber connects the hydraulic consumers that can then be operated in parallel each with the aligned holes of the valve discs Pressure medium are supplied.

Die Eingangsventilscheibe kann auch dazu benutzt werden, um die Geschwindigkeit, mit der ein hydraulischer Verbraucher verfahrbar ist, festzulegen. Dazu weist der Ventilkolben gemäß Patentanspruch 5 zur Verbindung einer Außenanschlußkammer, insbesondere der zweiten Außenanschlußkammer, mit der Zulaufkammer Steuernuten auf, die in einer Stellung des Ventilkolbens einen ganz bestimmten Durchflußquerschnitt zwischen der Zulaufkammer und der Außenanschlußkammer öffnen. Insbesondere kann der Ventilkolben auch stetig verstellbar sein, um diesen Durchflußquerschnitt zu verändern. Dabei kann zusätzlich ein lastabhängiges Signal an den Pumpenregler gemeldet werden, um die Geschwindigkeit des hydraulischen Verbrauchers lastunabhängig einstellen zu können.The input valve disc can also be used to control the speed, with which a hydraulic consumer can be moved. To do so the valve piston according to claim 5 for connecting an external connection chamber, in particular the second external connection chamber with the inlet chamber Control grooves on a very specific in a position of the valve piston Flow cross-section between the inlet chamber and the outer connection chamber to open. In particular, the valve piston can also be continuously adjustable, to change this flow area. In addition, a load-dependent Signal to the pump controller to be reported to speed to be able to adjust the hydraulic load independently of the load.

Wie verschiedene Druckräume, die in der zweiten Ventilbohrung ausgebildet sind und in denen verschieden hohe Drücke anstehen, auf vorteilhafter Weise voneinander getrennt werden, ist in den Patentansprüchen 6 bis 9 angegeben. Like different pressure chambers that are formed in the second valve bore and in which different pressures are present, advantageously from one another are separated is specified in claims 6 to 9.

Bevorzugt mündet die Zulaufbohrung gemäß Patentanspruch 10 außerhalb der ersten Ventilbohrung in den Zulaufhohlraum. Auf diese Weise wird die erste Ventilbohrung von der Zulaufbohrung, deren Durchmesser normalerweise größer gewählt ist als die axiale Erstreckung der Zulaufkammer, durch die Zulaufbohrung nicht unterbrochen und die Führung des Ventilkolbens in der ersten Ventilbohrung nicht beeinflußt. Es ist vorteilhaft, wenn gemäß Patentanspruch 11 die die erste Ringkammer der zweiten Ventilbohrung anschneidende Bohrung durch einen in das Ventilgehäuse eingeschraubten Verschlußstopfen einseitig verschlossen ist. Der in der Bohrung herrschende Druck wirkt über den Verschlußstopfen auf das Ventilgehäuse in die eine Richtung, während der Druck in der als Sackbohrung ausgebildetenZulaufbohrung in die entgegengesetzte Richtung wirkt. Dadurch werden die den Steuerblock zusammenhaltenden Zuganker im wesentlichen genauso belastet, als ob nur Wegeventilscheiben der bekannten Bauart zu einem Steuerblock zusammengefaßt wären.Preferably, the inlet bore opens outside of the first valve bore in the inlet cavity. In this way, the first valve bore from the inlet bore, the diameter of which is normally chosen to be larger is the axial extension of the inlet chamber through the inlet bore not interrupted and the guidance of the valve piston in the first valve bore unaffected. It is advantageous if the first according to claim 11 Annular chamber of the second valve bore cutting through a in the valve housing screwed plug is closed on one side. The pressure prevailing in the bore acts on the plug Valve body in one direction, while the pressure in the as a blind hole trained inlet bore acts in the opposite direction. Thereby the tie rods holding the control block together are essentially the same loaded, as if only directional control valve discs of the known type to one Control block would be summarized.

Der vierte Kanal ist vorteilhafterweise gemäß Patentanspruch 12 eine Sackbohrung, die durch den ersten Außenanschluß, den ersten Außenanschlußkanal und die erste Ventilbohrung hindurch in das Ventilgehäuse eingebracht ist. Anders als bei einem Bohren in die entgegengesetzte Richtung ist dann kein Verschlußstopfen notwendig.The fourth channel is advantageously a blind hole according to claim 12, through the first external connection, the first external connection channel and the first valve bore is made in the valve housing. Different to when drilling in the opposite direction, there is no plug necessary.

Gemäß den Ausgestaltungen nach den Patentansprüchen 13 und 14 ist das erste Trennelement bzw. ein einstückig ausgebildeter Trennkolben in der zweiten Ventilbohrung so angeordnet, daß allenfalls eine sehr kleine axiale Bewegung stattfinden kann.According to the configurations according to claims 13 and 14, the first is Separating element or a one-piece separating piston in the second valve bore so arranged that at most a very small axial movement takes place can.

Bei einer Load Sensing Steuerung eines hydraulischen Verbrauchers ergibt sich die Druckmittelmenge, die dem Verbraucher zufließt, also die Geschwindigkeit des hydraulischen Verbrauchers, üblicherweise aus dem einstellbaren Durchflußquerschnitt der diesem Verbraucher zugeordneten Meßdrossel und der durch einen Pumpenregler vorgegebenen Druckdifferenz zwischen dem Lastdruck des Verbrauchers und dem Pumpendruck. Für manche Betriebszustände, zum Beispiel bei Krane, wird gewünscht, daß bei gleicher Stellung der Meßdrossel wie vorher dem hydraulischen Verbraucher, insbesondere einem hydraulischen Verbraucher mit einer hohen Last, eine geringere Druckmittelmenge zufließt als im Normalbetrieb. Es kann dann feinfühliger gesteuert werden.This results in a load sensing control of a hydraulic consumer the amount of pressure medium that flows to the consumer, i.e. the speed of the hydraulic consumer, usually from the adjustable flow cross section the measuring choke assigned to this consumer and the by a pump regulator predetermined pressure difference between the load pressure of the Consumer and the pump pressure. For some operating conditions, for example in the case of cranes, it is desired that the measuring throttle be in the same position before the hydraulic consumer, especially a hydraulic consumer with a high load, a smaller amount of pressure medium flows in than in Normal operation. It can then be controlled more sensitively.

Um diese feinfühligere Steuerung zu ermöglichen, ist bei einer bekannten hydraulischen Steueranordnung eine zusätzliche Drossel vorhanden, die in die Zulaufleitung zwischen der Hydropumpe und den Steuerblock geschaltet werden kann. Bei einer erfindungsgemäßen Wegeventilscheibe läßt sich eine in die Zulaufleitung schaltbare Drossel auf sehr kostengünstige und platzsparende Weise dadurch realisieren, daß gemäß Patentanspruch 15 in die zweite Ventilbohrung ein Trennkolben eingesetzt ist, der einen die zweite Ringkammer von einem anderen Abschnitt der zweiten Ventilbohrung trennenden Kolbenabschnitt aufweist, und daß der Trennkolben zur Einstellung von unterschiedlich großen Durchflußquerschnitten des Zulauffluidpfades zwischen der Zulaufbohrung und der die erste Ringkammer anschneidenden Bohrung zwischen zwei Endstellungen gesteuert axial verschiebbar ist.In order to enable this more sensitive control, a known hydraulic system is used Control arrangement an additional throttle present in the supply line can be switched between the hydraulic pump and the control block. at a directional valve disc according to the invention can be in the supply line switchable choke in a very economical and space-saving manner realize that a separating piston according to claim 15 in the second valve bore is used, the one the second annular chamber from another section has the second valve bore separating piston section, and that the separating piston for setting flow cross sections of different sizes of the inlet fluid path between the inlet bore and the first annular chamber cutting bore between two end positions controlled axially is movable.

Gemäß Patentanspruch 16 mündet die Zulaufbohrung im Bereich der zweiten Ventilbohrung in den Zulaufhohlraum und mit dem Trennkolben sind unterschiedlich große Durchflußquerschnitte zwischen der Zulaufbohrung und dem dritten Kanal einstellbar. Gleichzeitig oder auch alternativ dazu können gemäß Patentanspruch 17 mit dem Trennkolben unterschiedlich große Durchflußquerschnitte zwischen der ersten Ringkammer und dem vierten Kanal und/oder der die erste Ringkammer anschneidenden Bohrung einstellbar sein. According to claim 16, the inlet bore opens in the area of the second Valve bore in the inlet cavity and with the separating piston are different large flow cross sections between the inlet bore and the third Channel adjustable. At the same time or alternatively, according to claim 17 with the separating piston different flow cross sections between the first annular chamber and the fourth channel and / or the first Ring chamber cutting hole can be adjustable.

Der Trennkolben ist gemäß Patentanspruch 19 insbesondere hydraulisch verstellbar. Dazu ist ein Pilotventil vorhanden, über das ein Druckraum an der ersten Ringkammer abgelegenen Stirnfläche eines zweiten Kolbenabschnitts mit einem Druck beaufschlagbar und von Druck entlastbar ist. Vorteilhafterweise wird der Druckraum zur Druckbeaufschlagung an den Fluidpfad zwischen der Zulaufbohrung und der die erste Ringkammer anschneidenden Bohrung und zur Druckentlastung an einen Tankkanal angeschlossen. Außer dem Fluidpfad ist auch ein Tankkanal in der Wegeventilscheibe vorhanden, so daß, wenn das Pilotventil gemäß Patentanspruch 22 an das Scheibengehäuse angebaut ist, zur Steuerung des Trennkolbens keine außen sichtbare Leitungen notwendig sind.The separating piston is in particular hydraulically adjustable according to claim 19. There is a pilot valve for this purpose, through which a pressure chamber at the first End face of a second piston section with an annular chamber Pressure can be applied and pressure can be relieved. Advantageously, the Pressure chamber for pressurizing the fluid path between the inlet bore and the bore cutting the first annular chamber and for pressure relief connected to a tank channel. In addition to the fluid path, there is also a Tank channel in the directional valve disc, so that when the pilot valve according Claim 22 is attached to the disc housing for control of the separating piston no externally visible lines are necessary.

Durch ein Druckbegrenzungsventil kann der Druck in einer Außenanschlußkammer einer erfindungsgemäßen Wegeventilscheibe auf einen Höchstwert begrenzt werden. Gemäß Patentanspruch 22 ist nun ein solches Druckbegrenzungsventil, insbesondere das mit der ersten Außenanschlußkammer verbundene Druckbegrenzungsventil, bei einer Verschiebung des Trennkolbens auf einen anderen Druckwert einstellbar. Es können also dann zum Beispiel über das normale Maß hinausgehende Lasten feinfühlig bewegt werden.A pressure relief valve allows the pressure in an external connection chamber a directional valve disc according to the invention limited to a maximum value become. According to claim 22, such a pressure relief valve is now in particular the pressure relief valve connected to the first outer connection chamber, when the separating piston is moved to another Adjustable pressure value. So it can then, for example, exceed the normal level additional loads can be moved with care.

Zwei Ausführungsbeispiele einer erfindungsgemäßen Wegeventilscheibe sind in den Zeichnungen dargestellt. An Hand der Figuren dieser Zeichnungen wird die Erfindung nun näher erläutert.Two exemplary embodiments of a directional valve disc according to the invention are shown in shown the drawings. Using the figures in these drawings, the Invention now explained in more detail.

Es zeigen

Figur 1
das Schaltbild eines Steuerblocks, der das erste, mit einem nicht verschiebbaren Trennkolben ausgestattete Ausführungsbeispiel einer erfindungsgemäßen Wegeventilscheibe enthält,
Figur 2
einen Längsschnitt durch das erste Ausführungsbeispiel,
Figur 3
eine Draufsicht auf das erste Ausführungsbeispiel in Richtung des Pfeiles A aus Figur 2 mit einem Teilschnitt senkrecht zur Zeichenebene nach Figur 2,
Figur 4
das Schaltbild eines Steuerblocks, der das zweite, mit einem zur Veränderung eines Durchflußquerschnitts für Druckmittel verschiebbaren Trennkolben ausgestattete Ausführungsbeispiel einer erfindungsgemäßen Wegeventilscheibe enthält, und
Figur 5
einen Längsschnitt durch das zweite Ausführungsbeispiel.
Show it
Figure 1
1 shows the circuit diagram of a control block which contains the first exemplary embodiment of a directional valve disk according to the invention equipped with a non-displaceable separating piston,
Figure 2
2 shows a longitudinal section through the first exemplary embodiment,
Figure 3
3 shows a plan view of the first exemplary embodiment in the direction of arrow A from FIG. 2 with a partial section perpendicular to the plane of the drawing according to FIG. 2,
Figure 4
the circuit diagram of a control block which contains the second embodiment of a directional valve disk according to the invention equipped with a separating piston which can be displaced to change a flow cross section for pressure medium, and
Figure 5
a longitudinal section through the second embodiment.

Gemäß den Schaltbildern nach den Figuren 1 und 4 saugt eine Verstellpumpe 10 mit einem Load-Sensing-Regler 11 Druckmittel aus einem Tank 12 an und gibt es in eine Pumpenleitung 13 ab, die zu einem Steuerblock 14 führt. Dieser ist aus einer Reihe von Scheiben zusammengesetzt, die durch nicht näher dargestellte Zuganker zusammengehalten sind. Eine Anschlußscheibe 15 dient dazu, um flexible oder starre Leitungen an den Steuerblock anschließen zu können. Es ist dies der Abschnitt der Pumpenleitung 13, der zwischen der Verstellpumpe 10 und dem Steuerblock 14 verläuft. Außerdem ist dies eine Tankleitung 16, die von einem Tankanschluß zum Tank 12 führt, und eine Lastmeldeleitung 17, die von einem LS-Anschluß zum LS-Regler 11 führt. Die Pumpenleitung 13 setzt sich in der Anschlußplatte 15 und in der dieser folgenden Wegeventilscheibe 20 fort, die die erfindungsgemäße Wegeventilscheibe ist. An diese schließen sich mehrere, nach dem Load-Sensing-Prinzip aufgebaute Wegeventilscheiben 21 an, die zum Steuern verschiedener hydraulischer Verbraucher eines mobilen Arbeitsgerätes, z.B. einer Feuerwehrleiter, dienen und von denen lediglich eine einzige Wegeventilscheibe dargestellt ist. Jede dieser Wegeventilscheiben 21 enthält ein proportional verstellbares Wegeventil 22, mit dem die Richtung festgelegt werden kann, in welche sich der entsprechende hydraulische Verbraucher bewegt, und mit dem eine die Geschwindigkeit des hydraulischen Verbrauchers bestimmende Zumeßdrossel unterschiedlich weit geöffnet werden kann, und eine der Zumeßdrossel vorgeschaltete Druckwaage 23, die lastunabhängig eine bestimmte Druckdifferenz über die Zumeßdrossel aufrechterhält. Jede LS-Wegeventilscheibe 21 weist außerdem zwei durch jeweils einen Proportional-Elektromagneten 24 stetig verstellbare und auf der Basis von Druckreduzierventilen funktionierende Vorsteuerventile 25 und 26 auf, die mit einem Druckeingang an eine Steuerdruckversorgungsleitung 27, mit einem Tankausgang mit einer Steuerdruckentlastungsleitung 28 und mit einem Regelausgang an die eine Steuerseite oder die andere Steuerseite des Wegeventils 22 angeschlossen sind. Die Steuerdruckversorgungsleitung 27 und die Steuerdruckentlastungsleitung 28 gehen durch alle Scheiben 20 und 21 hindurch bis in eine Endscheibe 29, in der ein Druckreduzierventil 30, dessen Regelausgang mit der Steuerdruckversorgungsleitung 27 verbunden ist, und ein Druckbegrenzungsventil 31 untergebracht sind, das den Druck in der Steuerdruckversorgungsleitung 27 absichert. Für die Steuerdruckentlastungsleitung 28 ist in der Endscheibe 29 ein Anschluß Y vorhanden. Ein Anschluß X der Endscheibe 29, der eine externe Steuerölversorgung ermöglicht, ist verschlossen. Das Druckreduzierventil 30 reduziert den in der Pumpenleitung 13 anstehenden Druck auf den maximalen Steuerdruck. Sein Druckeingang ist dazu an einer Steuerölversorgungsleitung 32 angeschlossen, die ebenfalls durch alle Ventilscheiben 20 und 21 hindurch in die Endscheibe 29 führt und die innerhalb der Scheibe 20 an die Pumpenleitung 13 angeschlossen ist.According to the circuit diagrams according to FIGS. 1 and 4, a variable displacement pump 10 sucks with a load-sensing regulator 11 pressure medium from a tank 12 and there into a pump line 13 leading to a control block 14. This is over a series of disks composed by not shown Tie rods are held together. A connecting washer 15 serves to be flexible or to be able to connect rigid lines to the control block. It is this the section of the pump line 13 between the variable displacement pump 10 and the Control block 14 runs. In addition, this is a tank line 16 by a Tank connection leads to the tank 12, and a load reporting line 17 by a LS connection to LS controller 11 leads. The pump line 13 settles in the connection plate 15 and in the following directional valve disc 20, which the inventive Directional valve disc is. This is followed by several Directional valve disks 21 constructed according to the load-sensing principle, which are used for controlling various hydraulic consumers of a mobile implement, e.g. a fire brigade ladder, and of which only a single directional valve disc is shown. Each of these directional valve disks 21 contains a proportional adjustable directional valve 22, with which the direction can be determined in which the corresponding hydraulic consumer moves, and with one metering throttle determining the speed of the hydraulic consumer can be opened to different degrees, and one upstream of the metering throttle Pressure compensator 23, which is independent of the load via a certain pressure difference maintains the metering throttle. Each LS directional valve disc 21 also has two continuously adjustable by a proportional electromagnet 24 and pilot valves 25 and 25 that function on the basis of pressure reducing valves 26 with a pressure input to a control pressure supply line 27, with a tank outlet with a control pressure relief line 28 and with a Control output on one control side or the other control side of the directional valve 22 are connected. The control pressure supply line 27 and the Control pressure relief line 28 pass through all disks 20 and 21 to an end plate 29 in which a pressure reducing valve 30, the control output is connected to the control pressure supply line 27, and a pressure relief valve 31 are housed, the pressure in the control pressure supply line 27 secured. For the control pressure relief line 28 is in the End plate 29, a connection Y is present. A terminal X of the end plate 29, which enables an external control oil supply is closed. The pressure reducing valve 30 reduces the pressure in the pump line 13 to maximum control pressure. For this purpose, its pressure input is on a control oil supply line 32 connected, also through all valve disks 20 and 21 leads into the end plate 29 and within the plate 20 to the Pump line 13 is connected.

Durch die Scheiben 15, 20 und 21 führt außerdem noch ein Tankkanal 33 hindurch bis in die Endscheibe 29. Dort ist an den Tankkanal 33 ein Lastmeldekanal 34 angeschlossen, in dem in jeder Ventilscheibe 20 und 21 ein Wechselventil 35 derart liegt, daß am LS-Anschluß der Anschlußscheibe 15 der höchste Lastdruck aller gleichzeitig angesteuerten hydraulischen Verbraucher ansteht.A tank channel 33 also passes through the disks 15, 20 and 21 to the end plate 29. There is a load reporting channel on the tank channel 33 34 connected in which a shuttle valve 35 in each valve disk 20 and 21 is such that the highest load pressure at the LS connection of the connecting disk 15 of all hydraulic consumers controlled at the same time.

In den Darstellungen nach den Figuren 2, 3 und 5 erkennt man, daß die Wegeventilscheibe 20 der beiden Ausführungsbeispiele ein scheibenförmiges Ventilgehäuse 40 aufweist, durch das eine erste Ventilbohrung 41 hindurchgeht. In dieser ist ein Ventilschieber 42 axial bewegbar. Die Länge des Ventilschiebers 42 stimmt mit der Länge der Ventilbohrung 41 von der einen Stirnseite 43 bis zur anderen Stirnseite 44 des Ventilgehäuses 40 überein. Die Ventilbohrung 41 ist von fünf axial voneinander beabstandeten Steuerkammern umgeben, die der Steuerung des Zuflusses von Druckmittel aus der Pumpenleitung 13 zu einem Außenanschluß 45 des Ventilgehäuses 40 oder zu einer senkrecht zur Scheibenebene verlaufenden Bohrung 46 dienen, die zu entsprechenden Bohrungen 47 in den Wegeventilscheiben 21 hin offen ist. Die Bohrung 46 und die Bohrungen 47 in den Wegeventilscheiben 21 bilden eine an beiden Enden verschlossene Zulaufleitung für die LS-Wegeventilscheiben 21. Die mittlere der fünf Steuerkammern sei als Zulaufkammer 48 bezeichnet, weil ihr das von der Pumpe 10 geförderte Druckmittel zufließt. Beidseits dieser Zulaufkammer befindet sich jeweils eine Außenanschlußkammer 49 bzw. 50, von denen die Außenanschlußkammer 49 über einen ersten Außenanschlußkanal 51 mit einem durch einen Stopfen 52 verschlossenen ersten Außenanschluß 53 des Ventilgehäuses 40 und die Außenanschlußkammer 50 über einen zweiten Außenanschlußkanal 54 mit dem schon erwähnten zweiten Außenanschluß 45 verbunden ist. Auf jede Außenanschlußkammer 49 und 50 folgt noch eine Ablaufkammer 56 bzw. 57, die zu dem durch das Ventilgehäuse 40 hindurchgehenden Tankkanal 33 offen ist.In the representations according to Figures 2, 3 and 5 you can see that the directional valve disc 20 of the two embodiments a disc-shaped valve housing 40, through which a first valve bore 41 passes. In this is a valve spool 42 axially movable. The length of the valve spool 42 is correct with the length of the valve bore 41 from one end face 43 to the other Face 44 of the valve housing 40 match. The valve bore 41 is five axially spaced control chambers surrounding the control the inflow of pressure medium from the pump line 13 to an external connection 45 of the valve housing 40 or to a perpendicular to the disc plane running bore 46 serve to corresponding holes 47 in the Directional valve disks 21 is open. The bore 46 and the bores 47 in the Directional valve disks 21 form an inlet line closed at both ends for the LS directional valve disks 21. The middle of the five control chambers is as Inlet chamber 48 designated because you the pressure medium pumped by the pump 10 accrues. There is an external connection chamber on each side of this inlet chamber 49 and 50, of which the outer connection chamber 49 via a first external connection channel 51 with a plug 52 that closes it first outer connection 53 of the valve housing 40 and the outer connection chamber 50 via a second external connection channel 54 with the second already mentioned External connection 45 is connected. On each external connection chamber 49 and 50 there follows a drain chamber 56 or 57, which leads to that through the valve housing 40 passing tank channel 33 is open.

Der Ventilschieber 42 nimmt aufgrund von zwei Zentrierfedern 60, die in an den Stirnseiten 43 und 44 des Ventilgehäuses 40 befestigten und die Ventilbohrung 41 nach außen verschließenden Deckeln 61 und 62 untergebracht sind, eine Mittelstellung ein. In dieser Mittelstellung sperren zwei Schieberbunde 63 und 64 des Ventilschiebers 42, zwischen denen sich im Bereich der Zulaufkammer 48 ein Schieberhals 65 befindet, die beiden Außenanschlußkammern 49 und 50 gegen die Zulaufkammer 48 ab. Es ist jedoch die Außenanschlußkammer 49 über den Ringraum um einen weiteren Schieberhals 66 herum mit der Ablaufkammer 56 und die Außenanschlußkammer 50 über einen Ringraum um einen Schieberhals 67 herum mit der Ablaufkammer 57 verbunden. An den Schieberhals 66 schließt sich ein weiterer Schieberbund an, der den Federraum in dem einen Deckel 62 gegen die Ablaufkammer 56 abdichtet. Auch zwischen dem Schieberhals 67 und dem Federraum im Deckel 61 befindet sich ein Schieberbund 68 in der Ventilbohrung 41. Dieser Schieberbund 68 ist länger als der Schieberbund am anderen Federraum und besitzt eine Ringnut 69, die sich im Bereich von drei axial voneinander beabstandeten Ringkammern 70, 71 und 72 der Ventilbohrung 41 befindet.The valve spool 42 takes due to two centering springs 60 which in the End faces 43 and 44 of the valve housing 40 fastened and the valve bore 41 covers 61 and 62 which close to the outside are accommodated, a middle position on. In this middle position, two slide collars 63 and 64 lock the Valve slide 42, between which there is an inlet chamber 48 Slider neck 65 is located, the two outer connection chambers 49 and 50 against the inlet chamber 48. However, it is the outer connection chamber 49 over the Annulus around a further slide neck 66 with the drain chamber 56 and the outer connection chamber 50 via an annular space around a slide neck 67 connected to the drain chamber 57. Closes the slide neck 66 another slide collar, which holds the spring chamber in one cover 62 seals against the drain chamber 56. Also between the slide neck 67 and the spring chamber in the cover 61 there is a slide collar 68 in the valve bore 41. This slide collar 68 is longer than the slide collar on the other spring chamber and has an annular groove 69, which is in the range of three axially from each other spaced annular chambers 70, 71 and 72 of the valve bore 41 is located.

Der Ventilschieber 42 besitzt in dem Schieberbund 64 Steuernuten 73, die zur Zulaufkammer 48 hin offen sind und mit denen ein Durchflußquerschnitt zwischen der Zulaufkammer 48 und der Außenanschlußkammer 50 durch verschieden weite Bewegung des Ventilschiebers 42 aus seiner Mittelstellung heraus in eine erste Richtung unterschiedlich weit geöffnet werden kann. Dieser Durchflußquerschnitt stellt eine Zumeßdrossel dar, die in den Schaltbildern nach den Figuren 1 und 4 mit der Bezugszahl 73 der Feinsteuernuten bezeichnet ist. Zwischen den Feinsteuernuten 73 sind in den Schieberbund 64 Querbohrungen 74 eingebracht, die in der Mittelstellung des Ventilschiebers verschlossen sind und die innen in eine Axialbohrung 75 münden. Über eine weitere Querbohrung, in die eine Dämpfungsdüse 76 eingeschraubt ist, besteht eine Verbindung von der Axialbohrung 75 in die Ringkammer 71. Bei einer Verschiebung des Ventilschiebers 42 in die eine Richtung steht also in der Ringkammer 71 der am Außenanschluß 45 herrschende Druck an. Die Ringkammer 70 ist vorliegend ohne Funktion, jedoch vorhanden, weil für die Formung des Ventilgehäuses 40 derselbe Sandkern verwendet wird, wie für die LS-Wegeventile 21, in denen entweder der Druck im Außenanschluß 45 oder der Druck im Außenanschluß 53 in die Ringkammer 71 gemeldet wird und die Möglichkeit bestehen soll, den Druck in der Ringkammer 71 auf unterschiedliche Werte zu begrenzen, indem an die Ringkammern 70 und 72 unterschiedlich eingestellte Druckbegrenzungsventile angeschlossen werden. Die Ringkammer 72 dient vorliegend noch dazu, um zusammen mit Nuten 77 und 78 im Ventilschieber 42 die Ringkammer 71 zu der Ablaufkammer 57 hin von Druck zu entlasten, wenn sich der Ventilschieber 42 in der in den Figuren 2 und 5 gezeigten Mittelstellung befindet oder in die zur ersten Richtung entgegengesetzte, zweite Richtung bis auf Anschlag verschoben worden ist.The valve spool 42 has 64 control grooves 73 in the slide collar, which for Inlet chamber 48 are open and with which a flow cross-section between the inlet chamber 48 and the outer connection chamber 50 by different wide movement of the valve spool 42 out of its central position into one first direction can be opened to different degrees. This flow cross section represents a metering throttle, which is shown in the circuit diagrams according to FIGS and 4 is designated by the reference number 73 of the fine control grooves. Between Fine control grooves 73 are made in the slide collar 64 cross bores 74, which are closed in the middle position of the valve spool and which are in an axial bore 75 open. Via another cross hole in one Damping nozzle 76 is screwed in, there is a connection from the axial bore 75 in the annular chamber 71. When the valve slide 42 is moved one direction is thus in the annular chamber 71 at the outer connection 45 prevailing pressure. In the present case, the annular chamber 70 has no function, however present because the same sand core is used to form the valve housing 40 is, as for the LS directional control valves 21, in which either the pressure in the external connection 45 or the pressure in the external connection 53 is reported in the annular chamber 71 and there should be the possibility of reducing the pressure in the annular chamber 71 to different values by using the annular chambers 70 and 72 differently set pressure relief valves can be connected. The In the present case, annular chamber 72 also serves to together with grooves 77 and 78 in the valve slide 42, the annular chamber 71 to the drain chamber 57 out of pressure to relieve when the valve spool 42 in the shown in Figures 2 and 5 Middle position or in the opposite direction to the first direction, second direction has been moved to the stop.

In diese zweite Richtung wird der Ventilschieber 42 wie derjenige eines Schaltventils jeweils in eine Endstellung bewegt, in der ein maximaler Durchflußquerschnitt zwischen der Zulaufkammer 48 und der Außenanschlußkammer 49 vorhanden ist. Vor der Herstellung einer fluidischen Verbindung zwischen der Zulaufkammer 48 und einer der Außenanschlußkammern 49 und 50 wird deren fluidische Verbindung zu der jeweiligen Ablaufkammer 56 und 57 unterbrochen.In this second direction, the valve spool 42 becomes like that of a switching valve each moved to an end position in which a maximum flow cross-section present between the inlet chamber 48 and the outer connection chamber 49 is. Before establishing a fluid connection between the inlet chamber 48 and one of the outer connection chambers 49 and 50 becomes their fluid Connection to the respective drain chamber 56 and 57 interrupted.

Der Ventilschieber 42 wird durch Druckbeaufschlagung der Federräume in den Deckeln 61 und 62 hydraulisch betätigt. Es sind dazu zwei elektromagnetisch verstellbare Vorsteuerventile 80 und 81 vorhanden, die als Einschraubventile ausgebildet und in den Deckel 61 eingesetzt sind. Das eine Vorsteuerventil 80 ist ein durch den Elektromagneten stetig verstellbares Druckreduzierventil, von dem ein Steuerdruck in den Federraum des Deckels 62 einsteuerbar ist, um den Ventilschieber 42 stetig zu verstellen. Das Vorsteuerventil 81 ist ein Schaltventil, das zur Betätigung des Ventilschiebers 42 den Federraum im Deckel 61 mit der Steuerdruckversorgungsleitung 27 verbindet und ansonsten diesen Federraum zur Steuerdruckentlastungsleitung 28 entlastet. Es kann auch ein modifizierter Ventilschieber 42 und ein modifizierter Deckel 62 verwendet werden, die es erlauben, den Ventilschieber auch über einen Handhebel manuell zu verstellen.The valve spool 42 is pressurized into the spring chambers Lids 61 and 62 operated hydraulically. There are two electromagnetic adjustable pilot valves 80 and 81 available, which are designed as screw-in valves and are inserted in the lid 61. One pilot valve 80 is a through the electromagnet continuously adjustable pressure reducing valve, one of which Control pressure in the spring chamber of the cover 62 can be controlled to the valve slide 42 continuously adjustable. The pilot valve 81 is a switching valve that to actuate the valve slide 42, the spring chamber in the cover 61 with the control pressure supply line 27 connects and otherwise this spring space Control pressure relief line 28 relieved. It can also be a modified valve spool 42 and a modified cover 62 can be used, which allow the valve slide can also be adjusted manually using a hand lever.

Von der Stirnseite 44 des Ventilgehäuses 40 aus ist in dieses parallel zur ersten Ventilbohrung 41 eine zweite Ventilbohrung 82 eingebracht, die als Sackbohrung ausgebildet ist und in die in der Nähe ihres Bodens 83 ein von der Ringkammer 71 der ersten Ventilbohrung 41 ausgehender Gehäusekanal 84 mündet. Durch eine Verschlußschraube 85 ist die Ventilbohrung 82 nach außen verschlossen. Axial zur Außenanschlußkammer 49 der Ventilbohrung 41 leicht versetzt weist die Ventilbohrung 82 eine erste Ringkammer 86 auf. Diese wird von der senkrecht zu der Schnittebene nach den Figuren 2 und 5 verlaufenden Bohrung 46 angeschnitten. Im Abstand zu der Ringkammer 86 befindet sich zwischen dieser und dem Boden 83 der Ventilbohrung 82 und axial leicht gegenüber der Zulaufkammer 48 der Ventilbohrung 41 versetzt eine zweite Ringkammer 87, die über einen Kanal 88 mit der Zulaufkammer 48 der Ventilbohrung 41 fluidisch verbunden ist. Im Sinne der Patentansprüche ist dies der dritte Kanal.From the end face 44 of the valve housing 40, this is parallel to the first Valve bore 41 introduced a second valve bore 82, which is used as a blind bore is formed and in the near its bottom 83 one of the annular chamber 71 of the first valve bore 41 outgoing housing channel 84 opens. By a screw plug 85, the valve bore 82 is closed to the outside. Slightly offset axially to the outer connection chamber 49 of the valve bore 41 has the Valve bore 82 has a first annular chamber 86. This is perpendicular to the the sectional plane according to Figures 2 and 5 extending bore 46 cut. At a distance from the annular chamber 86 is between this and the Bottom 83 of the valve bore 82 and slightly axially opposite the inlet chamber 48 the valve bore 41 displaces a second annular chamber 87, which via a channel 88 is fluidly connected to the inlet chamber 48 of the valve bore 41. For the purpose of of claims this is the third channel.

Soweit das Ventilgehäuse 40 bisher hinsichtlich der Ventilbohrungen mit ihren Kammern sowie hinsichtlich der Kanäle beschrieben worden ist, stimmt es mit dem Ventilgehäuse der Wegeventilscheiben 21 überein. Zusätzlich ist jedoch ein vierter Kanal 89 vorhanden, über den die erste Ringkammer 86 der zweiten Ventilbohrung 82 mit der Außenanschlußkammer 49 der ersten Ventilbohrung 41 fluidisch verbunden ist. Dieser vierte Kanal ist als kreisrunde Bohrung oder auch als längliches Loch durch den Außenanschluß 53, den Kanal 51 und die Ventilbohrung 41 hindurch in das Material des Ventilgehäuses 40 eingebracht.As far as the valve housing 40 so far with regard to the valve bores Chambers and with regard to the channels has been described, it agrees the valve housing of the directional valve disks 21. In addition, however, is a fourth channel 89 is present, through which the first annular chamber 86 of the second valve bore 82 fluidly with the outer connection chamber 49 of the first valve bore 41 connected is. This fourth channel is as a circular hole or as elongated hole through the outer connection 53, the channel 51 and the valve bore 41 introduced into the material of the valve housing 40.

In die zweite Ventilbohrung 82 des ersten Ausführungsbeispiels ist ein einstückiger Trennkolben 90 eingesetzt, der sich mit einem ersten Kolbenabschnitt 91 axial zwischen den beiden Ringkammern 86 und 87 befindet und diese gegeneinander abdichtet. Ein zweiter Kolbenabschnitt 92 befindet sich, über eine Stange 93 mit dem Kolbenabschnitt 91 verbunden, jenseits der Ringkammer 87 und dichtet diese gegen einen Druckraum 94 der Ventilbohrung 82 ab, der an das in das Ventilgehäuse 40 eingebaute Wechselventil 35 angeschlossen ist und in dem in der Mittelstellung des Ventilschiebers 42 und bei dessen Verschiebung, nach Figur 2 betrachtet, nach rechts Tankdruck und bei einer Verschiebung nach links der im Außenanschluß 45 herrschende Druck ansteht. Über eine Stange 95 sowie über eine die Ringkammer 86 durchquerende Stange 96 und einen weiteren Kolbenabschnitt 97 kann sich der Trennkolben 90 mit geringem axialen Spiel im Bereich von einigen Zehntel Millimeter zwischen dem Boden 83 der Ventilbohrung 82 und der Verschlußschraube 85 abstützen.In the second valve bore 82 of the first embodiment is a one-piece Separating piston 90 is used, which is axially aligned with a first piston section 91 located between the two annular chambers 86 and 87 and these against each other seals. A second piston section 92 is located via a rod 93 connected to the piston section 91, beyond the annular chamber 87 and seals it against a pressure chamber 94 of the valve bore 82, which in the valve housing 40 built-in shuttle valve 35 is connected and in which in the Central position of the valve slide 42 and when it is displaced, according to FIG. 2 considered, tank pressure to the right and in the case of a shift to the left External connection 45 prevailing pressure. Over a rod 95 as well as over a rod 96 passing through the annular chamber 86 and a further piston section 97 can the separating piston 90 with little axial play in the area of a few tenths of a millimeter between the bottom 83 of the valve bore 82 and support the screw plug 85.

In die zweite Ventilbohrung 82 des zweiten Ausführungsbeispiels ist ein einstückiger Trennkolben 110 eingesetzt, der sich mit einem ersten Kolbenabschnitt 111 axial zwischen den beiden Ringkammern 86 und 87 befindet und diese gegeneinander abdichtet. Der Kolbenabschnitt 111 ist axial etwas größer als der entsprechende Kolbenabschnitt 91 des Trennkolbens 90 und ragt in der gezeigten Position des Trennkolbens 110 geringfügig in die Ringkammer 87 hinein. Ein zweiter Kolbenabschnitt 112 des Trennkolbens 110 befindet sich, über eine Stange 113 mit dem Kolbenabschnitt 111 verbunden, jenseits der Ringkammer 87 und dichtet diese gegen den Druckraum 94 der Ventilbohrung 82 ab, der wie beim ersten Ausführungsbeispiel dauernd an das in das Ventilgehäuse 40 eingebaute Wechselventil 35 angeschlossen ist und in dem in der Mittelstellung des Ventilschiebers 42 und bei dessen Verschiebung, nach Figur 2 betrachtet, nach rechts Tankdruck und bei einer Verschiebung nach links der im Außenanschluß 45 herrschende Druck ansteht. Vom Kolbenabschnitt 112 steht wie bei der ersten Ausführung in Richtung auf den Boden 83 der Ventilbohrung 82 eine Stange 115 ab. Diese ist allerdings kürzer als bei der ersten Ausführung, so daß in der in Figur 5 gezeigten Position des Trennkolbens 110, in der dieser an der Verschlußschraube 85 über eine die Ringkammer 86 durchquerende Stange 116 und einen, vom Kolbenabschnitt 111 gesehen, jenseits der Ringkammer 86 befindlichen weiteren Kolbenabschnitt 117 anliegt, ein lichter Abstand zwischen dem Boden 83 und dem Trennkolben besteht. Um das Maß dieses lichten Abstands kann der Trennkolben 110 in der Ventilbohrung 82 axial bewegt werden. In the second valve bore 82 of the second embodiment is a one-piece Separating piston 110 is used, which is connected to a first piston section 111 located axially between the two annular chambers 86 and 87 and these against each other seals. The piston section 111 is axially somewhat larger than the corresponding one Piston section 91 of the separating piston 90 and protrudes in the position shown of the separating piston 110 slightly into the annular chamber 87. A second Piston section 112 of the separating piston 110 is located via a rod 113 connected to the piston section 111, beyond the annular chamber 87 and seals this against the pressure chamber 94 of the valve bore 82, which as in the first Embodiment continuously on the shuttle valve installed in the valve housing 40 35 is connected and in the middle position of the valve spool 42 and when it is shifted, viewed according to FIG. 2, to the right tank pressure and in the event of a shift to the left, the one prevailing in the external connection 45 There is pressure. As in the first embodiment, piston section 112 is shown in FIG Towards the bottom 83 of the valve bore 82 a rod 115. This is however shorter than in the first embodiment, so that in the shown in Figure 5 Position of the separating piston 110, in which this on the screw 85 a rod 116 crossing the annular chamber 86 and one from the piston section 111 seen, beyond the annular chamber 86 located further piston section 117 is present, a clear distance between the bottom 83 and the Separating piston exists. The separating piston can be adjusted by the measure of this clear distance 110 are axially moved in the valve bore 82.

Der Trennkolben 110 wird in Richtung der in Figur 5 gezeigten Position von einer Druckfeder 118 belastet, die zwischen dem Kolbenabschnitt 112 und dem Boden 83 der Ventilbohrung 82 eingespannt ist, und kann gegen die Druckfeder 118 hydraulisch betätigt werden. Dazu ist zwischen dem Trennkolben 110 und der Verschlußschraube 85 ein Druckraum 119 vorhanden, der an den Steueranschluß 125 eines als 3/2 Wege-Schaltventil ausgebildeten Pilotventils 130 angeschlossen ist. Dessen Gehäuse 131 ist unmittelbar an die den Außenanschlüssen gegenüberliegende Seite des Ventilgehäuses 40 angeflanscht. Das Pilotventil 130 besitzt außer dem Steueranschluß 125 noch einen Druckanschluß 132, der über Bohrungen in den Gehäusen 40 und 131 intern mit der Bohrung 46 (Figur 5) oder alternativ mit einer Bohrung 98 (Figur 4) im Gehäuse 40 fluidisch verbunden ist, und einen Tankanschluß 133, der ebenfalls über Bohrungen in den Gehäusen 40 und 131 intern mit der Ablaufkammer 56 des Gehäuses 40 fluidisch verbunden ist. In der gezeigten Ruhestellung des Pilotventils ist der Druckraum 119 über den Tankanschluß 133 von Druck entlastet. Wenn das Pilotventil durch Ansteuerung eines Elektromagneten in die geschaltete Stellung gebracht ist, wird der Druckraum 119 mit dem in der Bohrung 46 bzw. 98 herrschenden Druck beaufschlagt und der Trennkolben 110 gegen die Kraft der Druckfeder 118 in eine zweite Endstellung gebracht, in der er mit der Stange 115 am Boden 83 der Ventilbohrung 82 anstößt. In der zweiten Endstellung ragen die Kolbenabschnitte 111 und 117 weit in die Ringkammern 86 und 87 hinein und verengen gegenüber der in Figur 5 gezeigten Position des Trennkolbens 110 die Durchflußquerschnitte zwischen der Bohrung 98 und dem Kanal 88 sowie zwischen dem Kanal 89 und der Bohrung 46. Der Trennkolben 110 kann somit als Teil eines 2/2 Wegeventils mit einer weit offenen Stellung und einer Drosselstellung betrachtet werden. In Figur 4 ist dieses Ventil, allerdings nur mit seinem stromauf der Ventilbohrung 41 befindlichen Teil, eingezeichnet und mit der Bezugszahl 110 des beweglichen Trennkolbens versehen. Damit wird auch schon angedeutet, daß nicht unbedingt beide Kolbenabschnitte 111 und 117 Drosselwirkung haben müssen. Zum Beispiel kann der Kolbenabschnitt 117 kürzer als in Figur 5 gezeigt gemacht werden, so daß er auch in der zweiten Endstellung des Trennkolbens nicht in die Ringkammer 86 hineinragt. Man wird dies von der gewünschten Drosselwirkung abhängig machen.The separating piston 110 is moved in the direction of the position shown in FIG Compression spring 118 loaded between the piston portion 112 and the bottom 83 of the valve bore 82 is clamped, and can hydraulically against the compression spring 118 be operated. For this purpose, between the separating piston 110 and the screw plug 85 a pressure chamber 119 available to the control connection 125 of a pilot valve 130 designed as a 3/2 way switching valve is. Its housing 131 is directly on the opposite of the external connections Flanged side of the valve housing 40. The pilot valve 130 has in addition to the control port 125, a pressure port 132, which Bores in the housings 40 and 131 internally with the bore 46 (Figure 5) or alternatively is fluidly connected to a bore 98 (FIG. 4) in the housing 40, and a tank connection 133, which also has holes in the housings 40 and 131 is fluidly connected internally to the drain chamber 56 of the housing 40. In the shown rest position of the pilot valve, the pressure chamber 119 is above the Tank connection 133 relieved of pressure. If the pilot valve by control an electromagnet is brought into the switched position, the pressure chamber 119 with the pressure prevailing in the bore 46 or 98 and the separating piston 110 against the force of the compression spring 118 in a second end position brought in which he with the rod 115 at the bottom 83 of the valve bore 82nd abuts. In the second end position, the piston sections 111 and 117 protrude far into the annular chambers 86 and 87 and narrowing compared to that shown in FIG. 5 Position of the separating piston 110 the flow cross sections between the Hole 98 and channel 88 and between channel 89 and the bore 46. The separating piston 110 can thus be part of a 2/2 way valve with a wide open position and a throttle position. In Figure 4 this is Valve, but only with its part located upstream of valve bore 41, drawn and provided with the reference number 110 of the movable separating piston. This also indicates that not both piston sections are necessary 111 and 117 must have a throttling effect. For example, the piston section 117 can be made shorter than shown in Figure 5, so that it also in the second end position of the separating piston does not protrude into the annular chamber 86. This will be made dependent on the desired throttling effect.

Bei beiden Ausführungsbeispielen ist der Druck im Außenanschluß 45 durch ein in in das Ventilgehäuse 40 eingeschraubtes Druckbegrenzungsventil 127 auf einen bestimmten Wert begrenzt. Ebenso ist der Außenanschlußkanal 51 durch ein weiteres Druckbegrenzungsventil gegen zu hohen Druck abgesichert. Bei der Ausführung nach den Figuren 1 bis 3 ist dieses weitere Druckbegrenzungsventil 128 wie das Druckbegrenzungsventil 127 von Hand auf einen bestimmten Wert einstellbar, der während des Betriebs beibehalten wird. Das weitere Druckbegrenzungsventil 129 der Ausführung nach den Figuren 4 und 5 dagegen ist ein Druckbegrenzungsventil mit Druckzuschaltstufe. Durch Druckbeaufschlagung eines in dem Ventil vorhandenen Kölbchens wird eine sich daran abstützende Feder stärker vorgespannt und dadurch ein höherer Druckwert eingestellt. Derartige Druckbegrenzungsventile sind allgemein bekannt, z. B aus dem Datenblatt RD 64 642/09.98 der Anmelderin, so daß sich eine nähere Beschreibung erübrigt. Zur Steuerung der Druckzuschaltstufe des Ventils 129 verläuft eine Steuerleitung 134 zwischen dem Gehäuse 131 des Pilotventils und dem Ventil 129. Innerhalb des Gehäuses 131 ist diese Steuerleitung 134 mit dem Steueranschluß 125 verbunden.In both embodiments, the pressure in the external connection 45 is indicated by an in in the valve housing 40 screwed pressure relief valve 127 to one limited value. Likewise, the outer connection channel 51 is through a another pressure relief valve secured against excessive pressure. In the Design according to Figures 1 to 3 is this further pressure relief valve 128 like the pressure relief valve 127 by hand to a certain value adjustable, which is maintained during operation. The further pressure relief valve 129 of the embodiment according to FIGS. 4 and 5, on the other hand, is a pressure relief valve with pressure connection stage. By pressurizing one in a spring supported on the valve of Cologne's valve becomes stronger preloaded and thereby set a higher pressure value. Such pressure relief valves are generally known, e.g. B from data sheet RD 64 642 / 09.98 by the applicant, so that a detailed description is unnecessary. to Control of the pressure connection stage of valve 129 runs through a control line 134 between the housing 131 of the pilot valve and the valve 129. Within the Housing 131, this control line 134 is connected to the control connection 125.

Die Bohrung 98 ist bei beiden Ausführungsbeispielen als Zulaufsackbohrung von der den Wegeventilscheiben abgekehrten Seite aus in das Ventilgehäuse 40 im Bereich der zweiten Ringkammer 87 der zweiten Ventilbohrung 82 eingebracht, verläuft somit parallel zur Bohrung 46. Die Bohrung 98 ist zu der Ringkammer 87 hin offen. Sie ist außerdem offen zu einem vom Anschluß P der Anschlußscheibe 15 ausgehenden Kanal und bildet somit ein Teil der Pumpenleitung 13. An der Seite des Ventilgehäuses 40, von der die Zulaufsackbohrung 98 ausgeht, ist die Bohrung 46 mit einem Gewindestopfen 99 verschlossen, wie dies aus Figur 3 ersichtlich ist. Dazu ist in die Bohrung 46 ein Innengewinde eingeschnitten worden. In Figur 3 ist außerdem der Verschlußstopfen 52 im Außenanschluß 53 weggelassen, so daß der vierte Kanal 89 erkennbar ist.The bore 98 is in both embodiments as an inlet pocket bore of the side facing away from the directional valve disks in the valve housing 40 in Area of the second annular chamber 87 of the second valve bore 82, thus runs parallel to the bore 46. The bore 98 is to the annular chamber 87 open towards. It is also open to one of the terminal P of the connecting washer 15 outgoing channel and thus forms part of the pump line 13. At the Side of the valve housing 40, from which the inlet pocket bore 98 extends, is the Bore 46 closed with a threaded plug 99, as can be seen in Figure 3 is. For this purpose, an internal thread has been cut into the bore 46. In Figure 3, the plug 52 is also omitted in the outer connection 53, so that the fourth channel 89 can be seen.

Außer den der Vorsteuerung dienenden Kanälen 27 und 28 geht noch der ebenfalls der Vorsteuerung dienender Kanal 32 durch das Ventilgehäuse 20 und die Wegeventilscheiben 21 hindurch und in die Endscheibe 29 hinein. An diesem Kanal ist der Druckeingang des Druckreduzierventils 30 angeschlossen. Innerhalb der Anschlußscheibe 15 ist der Kanal 32 an die Pumpenleitung 13 angeschlossen. Über ihn wird die Vorsteuerung mit Steueröl versorgt, unabhängig davon, in welcher Stellung sich der Ventilschieber 42 befindet.In addition to the channels 27 and 28 used for pilot control, this also works the pilot control channel 32 through the valve housing 20 and Directional valve disks 21 and into the end disk 29. On this channel the pressure input of the pressure reducing valve 30 is connected. Within the connecting disc 15, the channel 32 is connected to the pump line 13. The pilot control is supplied with control oil via it, regardless of which position the valve slide 42 is.

Die LS-Wegeventilscheiben 21 sind dafür vorgesehen, um hydraulische Verbraucher der Arbeitshydraulik eines mobilen Arbeitsgerätes zu betätigen.The LS directional valve disks 21 are intended for hydraulic consumers to operate the working hydraulics of a mobile working device.

Über den Außenanschluß 45 der Wegeventilscheibe 20 kann von der Pumpe 10 gefördertes Druckmittel einem oder mehreren Hydrozylindern 101 zufließen, mit denen z.B. Stützen des mobilen Arbeitsgeräts betätigt werden. Die Richtung, in der sich der Kolben der Hydrozylinder 101 bewegt, wird durch die Stellung eines 4/3-Wegeventils 102 bestimmt, das mit einem Zulaufanschluß mit dem Außenanschluß 45 der Wegeventilscheibe 20 und mit einem Ablaufanschluß mit Tank 12 verbunden ist. Das Wegeventil 102 ist in einer Mittelstellung federzentriert, in der sein Zulauf-, sein Ablauf- und seine beiden Zylinderanschlüsse gegeneinander abgesperrt sind. Je nach Arbeitsstellung fahren die Kolbenstangen der Hydrozylinder 101 aus oder ein.Via the external connection 45 of the directional valve disk 20, the pump 10 conveyed pressure medium flow to one or more hydraulic cylinders 101, with to e.g. Supports of the mobile implement are operated. The direction in the piston of the hydraulic cylinder 101 is moved by the position of a 4/3-way valve 102 determines that with an inlet connection with the external connection 45 of the directional valve disc 20 and with a drain connection with tank 12 connected is. The directional control valve 102 is spring-centered in a central position in which its inlet, its outlet and its two cylinder connections against each other are cordoned off. Depending on the working position, the piston rods of the hydraulic cylinders move 101 off or on.

Wenn bei den beiden Ausführungsbeispielen weder das Pilotventil 80 noch das Pilotventil 81 durch den jeweiligen Elektromagneten betätigt ist, befindet sich der Ventilschieber 42 in der in den Figuren gezeigten Ruhestellung, in der die beiden Außenanschlußkammern 49 und 50 gegen die Zulaufkammer 48 und somit gegen die Pumpenleitung abgesperrt und mit der Tankleitung 33 verbunden sind. Die Wegeventilscheibe 20 erfüllt insofern eine Not-Aus-Funktion als nach der Betätigung eines Not-Aus-Knopfes beide Pilotventile 80 und 81 ihre Ruhestellung einnehmen und weder über die Wegeventilscheiben 21 noch über das Ventil 102 ein hydraulischer Verbraucher betätigt werden kann.If neither the pilot valve 80 nor that in the two exemplary embodiments Pilot valve 81 is actuated by the respective electromagnet, the Valve slide 42 in the rest position shown in the figures, in which the two External connection chambers 49 and 50 against the inlet chamber 48 and thus against the pump line is shut off and connected to the tank line 33. The Directional valve disc 20 fulfills an emergency stop function insofar as after actuation of an emergency stop button, both pilot valves 80 and 81 assume their rest position and neither via the directional valve disks 21 nor via the valve 102 hydraulic consumer can be operated.

Auch ist es nicht möglich, die Hydrozylinder 101 und die den LS-Wegeventilscheiben 21 zugeordneten hydraulischen Verbraucher gemeinsam zu betätigen. Um letztere mit Druckmittel versorgen zu können, wird nämlich der Ventilschieber 41 der Wegeventilscheibe 20 durch Schalten des Pilotventils 81 in eine Stellung gebracht, in der die Zulaufkammer 48 und die Außenanschlußkammer 49 weit offen miteinander verbunden sind. Von der Pumpe gefördertes Druckmittel kann nun über die Pumpenleitung 13 mitsamt der Bohrung 98, über den Kanal 88, über die Zulaufkammer 48, die Außenanschlußkammer 49, den Kanal 89, die Ringkammer 86 der zweiten Ventilbohrung 82 und die Bohrung 46 nur den Wegeventilscheiben 21 zufließen, über die es dann auf die gerade betätigten hydraulischen Verbraucher aufgeteilt wird. Wird der Ventilschieber 42 aus der in den Figuren 1 und 2 gezeigten Mittelstellung in die andere Richtung bewegt, so wird die Zumeßdrossel 73 entsprechend der Bewegungsstrecke aufgemacht, während die Außenanschlußkammer 49 von der Zulaufkammer 48 getrennt bleibt. Von der Pumpe 10 gefördertes Druckmittel kann nun über die Pumpenleitung 13 inklusive der Bohrung 98, über den Kanal 88 und die Zulaufkammer 48, über die Zumeßdrossel 73, die Außenanschlußkammer 50, den Kanal 54 und den Außenanschluß 45 zum Zulaufanschluß des Wegeventils 102 gelangen. In dessen einen seitlichen Arbeitsstellung fließt das Druckmittel über ein Senkbremsventil 103 zum kolbenstangenabseitigen Druckraum der Hydrozylinder 101, so daß die Kolbenstangen ausfahren. Der Druck stromab der Zumeßdrossel 73, also der Lastdruck, wird über die Querbohrungen 74, die Axialbohrung 75, die Dämpfungsdüse 76, die Ringkammer 71 und den Kanal 84, den Druckraum 94, das Wechselventil 35 der Scheibe 20 und die Lastmeldeleitung 17 an den Pumpenregler 11 gemeldet. Die Verstellpumpe 10 fördert gerade soviel Druckmittel, daß in der Pumpenleitung 13 ein um eine bestimmte Druckdifferenz, die am Pumpenregler 11 eingestellt ist, über dem gemeldeten Lastdruck liegender Druck herrscht. Somit ist die Druckdifferenz über die Zumeßdrossel 73 unabhängig vom gemeldeten Lastdruck, so daß die über die Zumeßdrossel fließende Druckmittelmenge allein von dem Durchflußquerschnitt der Zumeßdrossel abhängt. Dies ist auch in der anderen Arbeitsstellung des Wegeventils 102 der Fall, wobei das Senkbremsventil 103 dafür sorgt, daß im kolbenstangenseitigen, ringförmigen Druckraum der Hydrozylinder 101 ein bestimmter Druck aufrechterhalten wird.It is also not possible to use the hydraulic cylinders 101 and the LS directional valve disks 21 assigned hydraulic consumers together actuate. In order to be able to supply the latter with pressure medium, namely the Valve slide 41 of the directional valve disk 20 by switching the pilot valve 81 in brought into a position in which the inlet chamber 48 and the outer connection chamber 49 are openly connected. Pumped Pressure medium can now via the pump line 13 together with the bore 98 the channel 88, via the inlet chamber 48, the outer connection chamber 49, the Channel 89, the annular chamber 86 of the second valve bore 82 and the bore 46 inflow only the directional valve disks 21, through which it then on the just actuated hydraulic consumer is divided. The valve spool 42 is off the middle position shown in Figures 1 and 2 moved in the other direction, the metering throttle 73 is opened in accordance with the movement distance, while the outer connection chamber 49 is separated from the inlet chamber 48 remains. Pressure medium delivered by the pump 10 can now be delivered via the pump line 13 including bore 98, via channel 88 and the inlet chamber 48, via the metering throttle 73, the outer connection chamber 50, the channel 54 and get the external connection 45 to the inlet connection of the directional valve 102. In one side of the working position, the pressure medium flows through a lowering brake valve 103 to the pressure chamber of the hydraulic cylinders 101 on the piston rod side, so that the piston rods extend. The pressure downstream of the metering throttle 73, So the load pressure, the transverse bores 74, the axial bore 75, the Damping nozzle 76, the annular chamber 71 and the channel 84, the pressure chamber 94, the shuttle valve 35 of the disk 20 and the load signal line 17 to the pump controller 11 reported. The variable displacement pump 10 delivers just as much pressure medium, that in the pump line 13 a by a certain pressure difference on the pump regulator 11 is set, pressure above the reported load pressure prevails. Thus, the pressure difference across the orifice 73 is independent of reported load pressure, so that the amount of pressure fluid flowing through the metering throttle depends solely on the flow cross section of the metering throttle. This is also in the other working position of the directional valve 102, the Lowering brake valve 103 ensures that in the piston rod-side, annular Pressure space of the hydraulic cylinder 101 a certain pressure is maintained.

Sind keine weiteren Verbraucher 101 vorhanden, die über den Außenanschluß der Wegeventilscheibe 20 mit Druckmittel versorgt werden sollen, so wird auch der Anschluß 45 mit einem Stopfen verschlossen. Die Wegeventilscheibe 20 erfüllt dann eine Not-Aus-Funktion für die Wegeventilscheiben 21, wobei ein modifizierter Ventilschieber ohne Feinsteuernuten und ohne Lastmeldebohrungen verwendet wird.If there are no further consumers 101 connected to the external connection the directional valve disk 20 are to be supplied with pressure medium, so will the port 45 closed with a plug. The directional valve disk 20 is satisfied then an emergency stop function for the directional valve disks 21, a modified one Valve slide without fine control grooves and without load reporting holes used becomes.

Der oben geschilderte Betrieb ist für das erste Ausführungsbeispiel der einzig mögliche und für das zweite Ausführungsbeispiel der Normalbetrieb. Beim zweiten Ausführungsbeispiel nimmt dabei das Pilotventil 130 die in den Figuren 4 und 5 gezeigte Stellung ein. Der Druckraum 119 ist entlastet, so daß die Feder 118 den Trennkolben 110 in der gezeigten ersten Endstellung hält. Die Druckzuschaltstufe des Ventils 129 ist deaktiviert. Für die Verstellung des Trennkolbens 110 des zweiten Ausführungsbeispiels in die zweite Endstellung sind drei Fälle denkbar. Im ersten Fall wird das Pilotventil nur dann geschaltet, wenn der Ventilschieber 42 im Sinne einer fluidischen Verbindung der Zulaufkammer 48 mit der Außenanschlußkammer 49 betätigt ist. Durch Schalten des Pilotventils 130 wird der Druckraum 119 mit Druck beaufschlagt und der Trennkolben 110 in die zweite Endstellung gebracht. Der Fluidpfad zwischen der Zulaufbohrung 98 und der Bohrung 46 ist nun gedrosselt, so daß der Zufluß von Druckmittel zu den Wegeventilscheiben 21 gegenüber dem Normalbetrieb verringert ist. Zugleich wird durch Schalten des Pilotventils 130 die Druckzuschaltstufe des Druckbegrenzungsventils 129 aktiviert, also der Maximaldruck von z. B. 270 bar auf 350 bar erhöht. Es können nun hohe Lasten feinfühlig bewegt werden.The above operation is the only one for the first embodiment possible and normal operation for the second embodiment. At the second time The exemplary embodiment takes the pilot valve 130 in FIGS. 4 and 5 position shown. The pressure chamber 119 is relieved, so that the spring 118 the Separating piston 110 holds in the first end position shown. The pressure connection stage of valve 129 is deactivated. For the adjustment of the separating piston 110 of the second embodiment in the second end position, three cases are conceivable. In the first case, the pilot valve is only switched when the valve spool 42 in the sense of a fluid connection between the inlet chamber 48 and the outer connection chamber 49 is actuated. By switching the pilot valve 130, the pressure chamber 119 pressurized and the separating piston 110 in the second end position brought. The fluid path between the inlet bore 98 and the bore 46 is now throttled so that the inflow of pressure medium to the directional valve disks 21 is reduced compared to normal operation. At the same time, by switching the Pilot valve 130 activates the pressure connection stage of the pressure limiting valve 129, so the maximum pressure of z. B. 270 bar increased to 350 bar. It can now be high Loads are moved with care.

Im zweiten Fall ist ein Schalten des Pilotventils 130 zusätzlich auch dann möglich, wenn der Ventilschieber 42 im Sinne einer fluidischen Verbindung zwischen der Zulaufkammer 48 und der Außenanschlußkammer 50 betätigt worden ist. Dann kann auch die über den Außenanschluß 45 einem oder mehreren hydraulischen Verbrauchern zufließende Druckmittelmenge verringert werden. Im dritten Fall schließlich wird das Pilotventil 130 nur bei einer Betätigung des Ventilschiebers 42 im Sinne einer fluidischen Verbindung zwischen der Zulaufkammer 48 und der Außenanschlußkammer 50 geschaltet. In diesem Fall ist das Druckbegrenzungsventil 129 mit Druckzuschaltstufe durch ein einfaches Druckbegrenzungsventil 128 ersetzt. Im zweiten und dritten Fall ist außerdem entgegen der Darstellung nach Figur 5 und in Übereinstimmung mit Figur 4 der Druckanschluß 132 des Pilotventils 130 fluidisch bevorzugt mit der Bohrung 98, eventuell aber auch mit dem durch die zweite Ringkammer 87 der Ventilbohrung 82, den Kanal 88 und die Zulaufkammer 48 der Ventilbohrung 41 gebildeten Zulaufhohlraum, in dem der Druck wegen der Drosselung in der zweiten Endstellung des Trennkolbens etwas niedriger ist als in der Bohrung 98, verbunden, da bei der Betätigung des Ventilschiebers 42 im Sinne einer fluidischen Verbindung zwischen der Zulaufkammer 48 und der Außenanschlußkammer 50 in der Bohrung 46 Tankdruck herrscht. Der bei dieser Betätigung des Ventilschiebers 42 in dem Druckraum 94 herrschende Lastdruck ist geringer als der Druck im Zulaufhohlraum, so daß der Trennkolben 110 von letzterem Druck verstellbar ist. Allerdings darf dann die Stärke der Druckfeder 118 nicht das Kraftäquivalent zur Druckdifferenz überschreiten.In the second case, switching the pilot valve 130 is also possible if the valve slide 42 in the sense of a fluidic connection between the Inlet chamber 48 and the outer connection chamber 50 has been actuated. Then can also be one or more hydraulic via the external connection 45 The amount of pressure medium flowing to consumers can be reduced. In the third case finally, the pilot valve 130 is only activated when the valve slide 42 is actuated in the sense of a fluidic connection between the inlet chamber 48 and the External connection chamber 50 switched. In this case the pressure relief valve is 129 with pressure connection stage through a simple pressure relief valve 128 replaced. In the second and third case is also contrary to the illustration 5 and in accordance with Figure 4, the pressure port 132 of the pilot valve 130 fluidically preferred with the bore 98, but possibly also with the through the second annular chamber 87 of the valve bore 82, the channel 88 and the inlet chamber 48 of the valve bore 41 formed inlet cavity in which the pressure because of the throttling in the second end position of the separating piston somewhat lower is connected as in the bore 98, because when the valve spool is actuated 42 in the sense of a fluidic connection between the inlet chamber 48 and the outer connection chamber 50 in the bore 46 tank pressure. The with this actuation of the valve slide 42 prevailing in the pressure chamber 94 Load pressure is less than the pressure in the inlet cavity, so that the separating piston 110 of the latter pressure is adjustable. However, the strength of the Compression spring 118 does not exceed the force equivalent to the pressure difference.

Nach dem Zurückschalten des Pilotventils 130 wird der Druckraum 119 von Druck entlastet, so daß die Druckfeder 118 den Trennkolben 110 wieder in die gezeigte erste Endstellung bringt und wieder Normalbetrieb gefahren wird.After the pilot valve 130 is switched back, the pressure chamber 119 becomes pressurized relieved, so that the compression spring 118 the separating piston 110 again in the shown brings the first end position and normal operation is carried out again.

Claims (23)

  1. A directional valve plate (20) which can be assembled together with other similar valve plates (21) to form a control block (14), in particular a load sensing control block, for a mobile working device, having a plate-type valve housing (40),
       provided with a first valve bore (41),
          in which are formed two outer connection chambers (49, 50) spaced apart in the direction of the valve bore (41) axis, of which the first (49) is connected to a first outer port (53) via a first outer connection channel (51) and the second (50) is connected to a second outer port (45) via a second outer connection channel (54), and between the two outer connection chambers (49, 50) are formed an inlet chamber (48) and, viewed from the inlet chamber (48), beyond each outer connection chamber (49, 50) an outlet chamber (56, 57),
       and provided with a second valve bore (82),
       running parallel to the first valve bore (41), in which, at approximately the level of the first outer connection chamber (49) of the first valve bore (41) is formed a first annular chamber (86), which is intersected by a bore (46) running perpendicular to the plane of the plate, and, at approximately the level of the inlet chamber (48) of the first valve bore (41) is formed a second annular chamber (87) which is connected via a third channel (88) to the inlet chamber (48),
       and having in the first valve bore (41) an axially displaceable valve spool (42),
          with which the fluidic connection of at least the first outer connection chamber (49) to the inlet chamber (48) can be controlled,
    characterized in that
    a separating element (91, 111), separating the first annular chamber (86) and the second annular chamber (87) from each other, is located in the second valve bore (82),
    that an inlet bore (98) which can be connected to a pressure fluid source (10) debouches in the inlet cavity formed by the second annular chamber (87), the third channel (88) and the inlet chamber (48), and that the first outer connection chamber (49) and the first annular chamber (86) are fluidically connected to each other via a fourth channel (89).
  2. A directional valve plate according to Claim 1, characterized in that in the neutral position of the valve spool (42) at least one outer connection chamber (49, 50) is blocked off from the inlet chamber (48).
  3. A directional valve plate according to Claim 2, characterized in that in the neutral position of the valve spool (42) an outer connection chamber (49, 50) that is blocked off from the inlet chamber (48) is fluidically connected to one outlet chamber (56, 57)
  4. A directional control valve plate according to any of the preceding claims, characterized in that the first outer port (53) is closed by closing means (52).
  5. A directional valve plate according to any of the preceding claims, characterized in that the valve spool (42) is provided with control grooves (73) for the purpose of connecting an outer connection chamber (50), in particular the second outer connection chamber, to the inlet chamber (48).
  6. A directional valve plate according to any of the preceding claims, characterized in that the second valve bore (82) has a pressure chamber (94), spaced at a distance from the second annular chamber (87), to which can be applied the pressure prevailing in an outer connection chamber (50), which can be connected to the inlet chamber (48) via the control grooves (73) of the valve spool (42), and that in the second valve bore (82) is located a second separating element (92, 112) which separates the pressure chamber (94) and the second annular chamber (87) from each other.
  7. A directional valve plate according to Claim 6, characterized in that the separating element (92, 112) can be supported on the bottom (83) of the second valve bore (82) by a rod (95, 115).
  8. A directional valve plate according to Claim 6 or 7, characterized in that the first separating element (91, 111) and the second separating element (92, 112) are formed together in one piece.
  9. A directional valve plate according to Claim 8, characterized in that the first separating element (91, 111) and the second separating element (92, 112) are connected to each other via a rod (93, 113) traversing the second annular chamber (87).
  10. A directional valve plate according to any of the preceding claims, characterized in that the inlet bore (98) debouches in the inlet cavity (48, 87, 88) outside the first valve bore (41).
  11. A directional valve plate according to any of the preceding claims, characterized in that the bore (46) intersecting the first annular chamber (86) of the second valve bore (82) is closed at one end by a plug (99) screwed into the valve housing (40).
  12. A directional valve plate according to any of the preceding claims, characterized in that the fourth channel (89) is a blind hole, in particular a blind bore, leading through the first outer port (53), the first outer connection channel (51) and the first valve bore (41) into the valve housing (40).
  13. A directional valve plate according to any of the preceding claims, characterized in that the first separating element (91) is axially supported against axial displacement into one of the ring chambers (86, 87).
  14. A directional valve plate according to any of the preceding claims, characterized in that a separating piston (90) formed in one piece is inserted in the second valve bore (82) and is also axially secured in place with at the most a slight play and by means of which the sections (86, 87, 94) of the second valve bore (82), in which prevail different pressures, are separated from one another.
  15. A directional valve plate according to any of Claims 1 to 12, characterized in that a separating piston (110) is inserted in the second valve bore (82) and has a piston section (111) separating the second annular chamber (87) from the first annular chamber (86) of the second valve bore (82), and that the separating piston (110) is axially displaceable in a controlled manner between two end positions for the purpose of setting cross-sections of different size in the inlet fluid path between the inlet bore (98) and the bore (46) intersecting with the first annular chamber (86).
  16. A directional valve plate according to Claim 15, characterized in that the inlet bore (98) debouches in the inlet cavity (48, 87, 88) in the region of the second valve bore (82) and that flow cross-sections of different size can be set between the inlet bore (98) and the third channel (88) by means of the separating piston (110).
  17. A directional valve plate according to Claim 15 or 16, characterized in that flow cross-sections of different size can be set with the separating piston (110) between the first annular chamber (86) and the fourth channel (89) and/or the bore (46) intersecting with the first annular chamber (86).
  18. A directional valve plate according to Claim 17, characterized in that the separating piston (110) has a piston section (111), separating the first annular chamber (86) and the second annular chamber (87) from each other and which can be displaced into the second annular chamber (87), and has a second piston section (117), beyond the first annular chamber (86), which can be displaced into the first annular chamber (86).
  19. A directional valve plate according to any of Claims 15 to 18, characterized in that the separating piston (110) has a first piston section (111) separating the first annular chamber (86) and the second annular chamber (87) from each other and a second piston collar (117) beyond the first annular chamber (86), and that a pressure chamber (119) before the end face of the second piston section (117) facing away from the first annular chamber (86) can be pressurised in a first direction via a pilot valve (130) for the purpose of displacing the separating piston (110) and can be relieved of pressure for the purpose of displacing the separating piston (110), in particular by means of a spring (118), in the opposite direction.
  20. A directional valve plate according to Claim 19, characterized in that the pressure chamber (119) is connected in a first switching position of the pilot valve (130) to the fluid path from the inlet bore (98) to the bore (46) intersecting with the first annular chamber (86) and in a second switching position of the pilot valve (130) can be relieved to a tank channel (33).
  21. A directional valve plate according to Claim 19 or 20, characterized in that the pilot valve (130) is mounted on the valve housing (40).
  22. A directional valve plate according to any of Claims 15 to 21, characterized by a pressure limiting valve (129) by means of which the pressure in one outer connection chamber, in particular in the first connection chamber (49), can be limited and which is adjustable via a displacement of the separating piston (110).
  23. A directional valve plate according to Claim 22, characterized in that the separating piston (110) and the pressure limiting valve (129) can be adjusted by switching of the same pilot valve (130).
EP00112754A 1999-07-10 2000-06-16 Directional control valve section, especially for mobile equipment Expired - Lifetime EP1069317B1 (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE19932325 1999-07-10
DE19932325 1999-07-10
DE19937226 1999-08-06
DE19937226 1999-08-06
DE19948232A DE19948232A1 (en) 1999-07-10 1999-10-07 Directional valve disc, especially for a mobile working device
DE19948232 1999-10-07

Publications (3)

Publication Number Publication Date
EP1069317A2 EP1069317A2 (en) 2001-01-17
EP1069317A3 EP1069317A3 (en) 2001-11-07
EP1069317B1 true EP1069317B1 (en) 2003-08-13

Family

ID=27219220

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00112754A Expired - Lifetime EP1069317B1 (en) 1999-07-10 2000-06-16 Directional control valve section, especially for mobile equipment

Country Status (3)

Country Link
EP (1) EP1069317B1 (en)
AT (1) ATE247234T1 (en)
DK (1) DK1069317T3 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109592566A (en) * 2018-10-26 2019-04-09 中船华南船舶机械有限公司 A kind of crane hydraulic emergency system
CN110173474A (en) * 2019-05-05 2019-08-27 天津海弗液压技术有限公司 One kind cutting slotting vehicle hydraulic system monoblock type valve block

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004033315A1 (en) * 2004-07-09 2006-02-09 Bosch Rexroth Aktiengesellschaft lifting gear
DE102005050169A1 (en) 2005-06-21 2006-12-28 Bosch Rexroth Ag LS control arrangement and LS directional control valve
DE102006040234A1 (en) * 2006-08-28 2008-03-06 Robert Bosch Gmbh LS control arrangement
CN112780631B (en) * 2021-01-13 2024-07-30 华中科技大学无锡研究院 Multi-way valve with unloading protection function

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3908375A (en) * 1974-09-25 1975-09-30 Gen Signal Corp Hydraulic load sensitive pressure and flow compensating system
US4519419A (en) * 1982-06-15 1985-05-28 Commercial Shearing, Inc. Hydraulic valves
DE3839952C1 (en) * 1988-11-26 1990-04-26 Danfoss A/S, Nordborg, Dk Hydraulic spool valve
DE9210647U1 (en) 1992-08-10 1993-12-16 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulic control device
DE19714141A1 (en) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulic control arrangement

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109592566A (en) * 2018-10-26 2019-04-09 中船华南船舶机械有限公司 A kind of crane hydraulic emergency system
CN110173474A (en) * 2019-05-05 2019-08-27 天津海弗液压技术有限公司 One kind cutting slotting vehicle hydraulic system monoblock type valve block

Also Published As

Publication number Publication date
DK1069317T3 (en) 2003-12-08
EP1069317A2 (en) 2001-01-17
EP1069317A3 (en) 2001-11-07
ATE247234T1 (en) 2003-08-15

Similar Documents

Publication Publication Date Title
EP0760908B1 (en) Control arrangement for at least two hydraulic consumers
DE1601729B2 (en) Hydraulic control valve device working with pilot control
DE3912390C2 (en)
EP0650558B1 (en) Control device for at least one hydraulic consumer
DE69414614T2 (en) Current valve with pilot control and pressure compensation
EP2059683A1 (en) Ls control arrangement
EP1984629B1 (en) Hydraulic control arrangement with regeneration and lowering brake valve
DE19948232A1 (en) Directional valve disc, especially for a mobile working device
EP1069317B1 (en) Directional control valve section, especially for mobile equipment
DE19735482B4 (en) Hydraulic system with a differential cylinder and a rapid-action valve
EP0943057B1 (en) Distributing valve for load-independent control of a hydraulic consumer with regards to direction and speed
EP1360419B1 (en) Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed
EP1170510B1 (en) Hydraulic control arrangement for supplying pressurised fluid preferably to several hydraulic loads
WO2003087585A1 (en) Hydraulic control system using load-sensing technology
EP1996820B1 (en) Hydraulic valve arrangement
DE3611973A1 (en) SHUTTER VALVE
EP1386084B1 (en) Hydraulic control assembly for controlling the direction and speed of a single-action hydraulic consumer and a directional control valve therefor
DE19913277B4 (en) Hydraulic control arrangement, in particular for a winch
DE3408593C2 (en) Hydraulic three-way continuous valve for block installation
DE19503943C2 (en) Brake valve arrangement for a reversible hydraulic consumer
DE19802430A1 (en) Hydraulic system for operation of reversible hydraulic loader
DE102015209657A1 (en) Hydraulic valve assembly, hydraulic valve block with such a valve assembly, and hydraulic drive with it
DE3106532C2 (en)
DE19650465B4 (en) Electrohydraulic control device
DE19900573B4 (en) Hydraulic flow control valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20020411

AKX Designation fees paid

Free format text: AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BOSCH REXROTH AG

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MAXEINER, THASSILO

Inventor name: BUETTNER, PETER

AK Designated contracting states

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030813

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030813

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030813

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20030813

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 50003247

Country of ref document: DE

Date of ref document: 20030918

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20031113

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20031113

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20031124

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20031211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040113

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040616

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040630

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040630

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040630

26N No opposition filed

Effective date: 20040514

BERE Be: lapsed

Owner name: *BOSCH REXROTH A.G.

Effective date: 20040630

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20110630

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20110621

Year of fee payment: 12

Ref country code: AT

Payment date: 20110620

Year of fee payment: 12

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 247234

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120616

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120616

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120616

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120702

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120616

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20130624

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20130621

Year of fee payment: 14

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20140630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140630

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20160810

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50003247

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180103