EP1069317B1 - Tranche de distributeur hydraulique, surtout pour un véhicule automobile - Google Patents

Tranche de distributeur hydraulique, surtout pour un véhicule automobile Download PDF

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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)
English (en)
Other versions
EP1069317A2 (fr
EP1069317A3 (fr
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/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1069317A2 publication Critical patent/EP1069317A2/fr
Publication of EP1069317A3 publication Critical patent/EP1069317A3/fr
Application granted granted Critical
Publication of EP1069317B1 publication Critical patent/EP1069317B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular 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)
  • Sliding Valves (AREA)
  • Feeding Of Workpieces (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Compressor (AREA)

Claims (23)

  1. Une tranche (20) de distributeur,
    qui peut être assemblée avec d'autres tranches (21) de valve similaires pour former un bloc (14) de distribution, en particulier un bloc de distribution load sensing, pour une machine productrice à travail mobile,
    qui possède un corps (40) de valve en forme de tranche,
       lequel présente un premier alésage (41) de valve,
          à l'intérieur duquel sont formées deux chambres (49, 50) de raccordement extérieur, qui sont distantes l'une de l'autre dans la direction de l'axe de l'alésage (41) de valve et desquelles une première (49) est reliée à un premier orifice (53) extérieur par un premier canal (51) de raccordement extérieur et la deuxième (50) est reliée à un deuxième orifice (45) extérieur par un deuxième canal (54) de raccordement extérieur, une chambre (48) d'alimentation, qui est disposée entre les deux chambres (49, 50) de raccordement extérieur, et deux chambres (56, 57) d'évacuation, qui sont disposées chacune de l'autre côté d'une des deux chambres (49, 50) de raccordement extérieur considérées à partir de la chambre (48) d'alimentation,
       et lequel présente un deuxième alésage (82) de valve parallèle au premier alésage (41) de valve,
          à l'intérieur duquel sont formées une première chambre (86) annulaire, qui est coupée par un alésage (46) orienté dans la direction perpendiculaire au plan de la tranche, à peu près à la hauteur de la première chambre (49) de raccordement extérieur du premier alésage (41) de valve, et une deuxième chambre (87) annulaire, qui est reliée à la chambre (48) d'alimentation par un troisième canal (88), à peu près à la hauteur de la chambre (48) d'alimentation du premier alésage (41) de valve,
    et qui possède un tiroir (42) de valve pouvant coulisser à l'intérieur du premier alésage (41) de valve, dans la direction axiale,
       lequel permet au moins de commander la communication fluide entre la première chambre (49) de raccordement extérieur et la chambre (48) d'alimentation,
    caractérisée en ce qu'un élément (91, 111) de séparation, qui sépare la première chambre (86) annulaire et la deuxième chambre (87) annulaire l'une de l'autre, est disposé dans le deuxième alésage (82) de valve,
    qu'un alésage (98) d'alimentation, qui peut être raccordé à une source (10) de fluide de pression, débouche dans la cavité d'alimentation formée par la deuxième chambre (87) annulaire, le troisième canal (88) et la chambre (48) d'alimentation,
    et que la première chambre (49) de raccordement extérieur et la première chambre (86) annulaire sont reliées par voie fluide par un quatrième canal (89).
  2. Une tranche de distributeur selon la revendication n° 1, caractérisée en ce que au moins une chambre (49, 50) de raccordement extérieur est isolée de la chambre (48) d'alimentation dans la position neutre du tiroir (42) de distributeur.
  3. Une tranche de distributeur selon la revendication n° 2, caractérisée en ce que une chambre (49, 50) de raccordement extérieur, qui est isolée de la chambre (48) d'alimentation, est raccordée par voie fluide à une chambre (56, 57) d'évacuation dans la position neutre du tiroir (42) de distributeur.
  4. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que le premier orifice (53) extérieur est obturé par un moyen (52) de fermeture.
  5. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que le tiroir (42) de distributeur présente des fentes (73) de progressivité pour le raccordement d'une chambre (50) de raccordement extérieur, en particulier de la deuxième chambre de raccordement extérieur, à la chambre (48) d'alimentation.
  6. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que le deuxième alésage (82) de valve présente une chambre (94) de pression, qui est distante de la deuxième chambre (87) annulaire et qui en particulier peut être soumise à la pression régnant dans une chambre (50) de raccordement extérieur, laquelle peut être reliée à la chambre (48) d'alimentation par des fentes (73) de progressivité du tiroir (42) de distributeur, et que le deuxième alésage (82) de valve présente un deuxième élément (92, 112) de séparation, qui isole la chambre (94) de pression et la deuxième chambre (87) annulaire l'une de l'autre.
  7. Une tranche de distributeur selon la revendication n° 6, caractérisée en ce que l'élément (92, 112) de séparation peut venir s'appuyer à l'aide d'une tige (95, 115) contre le fond (83) du deuxième alésage (82) de valve.
  8. Une tranche de distributeur selon la revendication n° 6 ou n° 7, caractérisée en ce que le premier élément (91, 111) de séparation et le deuxième élément (92, 112) de séparation sont constitués de pair, d'une seule pièce.
  9. Une tranche de distributeur selon la revendication n° 8, caractérisée en ce que le premier élément (91, 111) de séparation et le deuxième élément (92, 112) de séparation sont reliés l'un à l'autre par une tige (93, 113), qui traverse la deuxième chambre (87) annulaire.
  10. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que l'alésage (98) d'alimentation débouche dans la cavité (48, 87, 88) d'alimentation, à l'extérieur du premier alésage (41) de valve.
  11. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que l'alésage (46), qui coupe la première chambre (86) annulaire du deuxième alésage (82) de valve, est obturé unilatéralement par un bouchon (99) de fermeture vissé dans le corps (40) de valve.
  12. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que le quatrième canal (89) est un trou en cul-de-sac et en particulier un alésage en cul-de-sac, qui est réalisé dans le corps (40) de valve en traversant le premier orifice (53) extérieur, le premier canal (51) de raccordement extérieur et le premier alésage (41) de valve.
  13. Une tranche de distributeur selon une revendication précédente, caractérisé en ce que le premier élément (91) de séparation vient s'appuyer, dans la direction axiale, contre un décalage axial à l'intérieur d'une des chambres (86, 87) annulaires.
  14. Une tranche de distributeur selon une revendication précédente, caractérisée en ce que dans le deuxième alésage (82) de valve est inséré un tiroir (90) de séparation, constitué d'une seule pièce, dont la position dans la direction axiale au besoin est assurée par un jeu faible et qui sépare, les unes des autres, les sections (86, 87, 94) du deuxième alésage (82) de valve, à l'intérieur duquel règnent des pressions différentes.
  15. Une tranche de distributeur selon une des revendications n° 1 à n° 12, caractérisée en ce que dans le deuxième alésage (82) de valve est inséré un tiroir (110) de séparation, qui présente une section (111) de tiroir séparant la deuxième chambre (87) annulaire de la première chambre (86) annulaire du deuxième alésage (82) de valve, et que le tiroir (110) de séparation peut être commandé de façon à coulisser dans la direction axiale entre deux positions extrêmes, pour le réglage de sections de débit de tailles différentes pour le chemin d'alimentation en fluide entre l'alésage (98) d'alimentation et l'alésage (46), qui coupe la première chambre (86) annulaire.
  16. Une tranche de distributeur selon la revendication n° 15, caractérisée en ce que l'alésage (98) d'alimentation débouche dans la cavité (48, 87, 88) d'alimentation, dans la zone du deuxième alésage (82) de valve, et que le tiroir (110) de séparation permet de régler des sections de débit de tailles différentes entre l'alésage (98) d'alimentation et le troisième canal (88).
  17. Une tranche de distributeur selon la revendication n° 15 ou n° 16, caractérisée en ce que le tiroir (110) de séparation permet de régler des sections de débit de tailles différentes entre la première chambre (86) annulaire et le quatrième canal (89) et/ou l'alésage (46), qui coupe la première chambre (86) annulaire.
  18. Une tranche de distributeur selon la revendication n° 17, caractérisée en ce que le tiroir (110) de séparation présente une première section (111) de tiroir, qui isole la première chambre (86) annulaire et la deuxième chambre (87) annulaire l'une de l'autre et qui peut être amené à coulisser de façon à pénétrer dans la deuxième chambre (87) annulaire, et présente une deuxième section (117) de tiroir, disposée de l'autre côté de la première chambre (86) annulaire, qui peut être amenée à coulisser de façon à pénétrer dans la première chambre (86) annulaire.
  19. Une tranche de distributeur selon une des revendications n° 15 à n° 18, caractérisée en ce que le tiroir (110) de séparation présente une première section (111) de tiroir, qui isole la première chambre (86) annulaire et la deuxième chambre (87) annulaire l'une de l'autre, et un deuxième épaulement (117) de tiroir, disposé de l'autre côté de la première chambre (86) annulaire, et qu'une valve (130) de pilotage peut soumettre une chambre (119) de pression, qui est située devant la face détournée de la première chambre (86) annulaire de la deuxième section (117) de tiroir, à une pression afin de déplacer le tiroir (110) de séparation dans un premier sens et peut la décharger de toute pression afin de déplacer, en particulier à l'aide d'un ressort (118), le tiroir (110) de séparation dans le sens opposé.
  20. Une tranche de distributeur selon la revendication n° 19, caractérisée en ce que, pour une première position de commutation de valve (130) de pilotage, la chambre (119) de pression est reliée au cheminement du fluide de l'alésage (98) d'alimentation vers l'alésage (46), qui coupe la première chambre (86) annulaire, et, pour une seconde position de commutation de valve (130) de pilotage, elle peut être déchargée vers un canal (33) de réservoir.
  21. Une tranche de distributeur selon la revendication n° 19 ou n° 20, caractérisée en ce que la valve (130) de pilotage est fixée sur le corps (40) de valve.
  22. Une tranche de distributeur selon une des revendications n° 15 à n°21, caractérisée par un limiteur (129) de pression, qui permet de limiter la pression dans une chambre de raccordement extérieur, en particulier dans la première chambre (49) de raccordement, et qui est réglable lors d'un coulissement du tiroir (110) de séparation.
  23. Une tranche de distributeur selon la revendication n° 22, caractérisée en ce que le tiroir (110) de séparation et le limiteur (129) de pression sont réglables par commutation de la même valve (130) de pilotage.
EP00112754A 1999-07-10 2000-06-16 Tranche de distributeur hydraulique, surtout pour un véhicule automobile Expired - Lifetime EP1069317B1 (fr)

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 (de) 1999-07-10 1999-10-07 Wegeventilscheibe, insbesondere für ein mobiles Arbeitsgerät
DE19948232 1999-10-07

Publications (3)

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

Family

ID=27219220

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00112754A Expired - Lifetime EP1069317B1 (fr) 1999-07-10 2000-06-16 Tranche de distributeur hydraulique, surtout pour un véhicule automobile

Country Status (3)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109592566A (zh) * 2018-10-26 2019-04-09 中船华南船舶机械有限公司 一种起重机液压应急系统
CN110173474A (zh) * 2019-05-05 2019-08-27 天津海弗液压技术有限公司 一种剪插车液压系统整体式阀块

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004033315A1 (de) * 2004-07-09 2006-02-09 Bosch Rexroth Aktiengesellschaft Hubwerksventilanordnung
DE102005050169A1 (de) 2005-06-21 2006-12-28 Bosch Rexroth Ag LS-Steueranordnung und LS-Wegeventil
DE102006040234A1 (de) * 2006-08-28 2008-03-06 Robert Bosch Gmbh LS-Steueranordnung

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 (de) * 1992-08-10 1993-12-16 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulische Steuervorrichtung
DE19714141A1 (de) * 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109592566A (zh) * 2018-10-26 2019-04-09 中船华南船舶机械有限公司 一种起重机液压应急系统
CN110173474A (zh) * 2019-05-05 2019-08-27 天津海弗液压技术有限公司 一种剪插车液压系统整体式阀块

Also Published As

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

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