WO2013060573A1 - Dispositif valve notamment destiné à commander une valve de coupure de pression - Google Patents

Dispositif valve notamment destiné à commander une valve de coupure de pression Download PDF

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Publication number
WO2013060573A1
WO2013060573A1 PCT/EP2012/070026 EP2012070026W WO2013060573A1 WO 2013060573 A1 WO2013060573 A1 WO 2013060573A1 EP 2012070026 W EP2012070026 W EP 2012070026W WO 2013060573 A1 WO2013060573 A1 WO 2013060573A1
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WO
WIPO (PCT)
Prior art keywords
valve
valve body
pressure
valve device
pressure port
Prior art date
Application number
PCT/EP2012/070026
Other languages
German (de)
English (en)
Inventor
Markus Gepraegs
Hakan Camurdan
Juergen Gintner
Original Assignee
Robert Bosch Gmbh
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
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2013060573A1 publication Critical patent/WO2013060573A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—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
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves

Definitions

  • Valve device in particular for activation
  • the invention relates to a valve device, in particular for a
  • a hydraulic consumer In hydrostatic drive systems such as a closed hydraulic circuit, a hydraulic consumer is supplied by means of a hydraulic pump with funding. In the operation of such a system, it may happen that the amount of liquid delivered by the hydrostatic machine exceeds the capacity of the hydraulic consumer. As a result, there is an increase in pressure in the delivery-side working line. In order to avoid the undesirable increase in pressure, it is known by means of a so-called.
  • Pressure cut valve unit to reduce the set flow rate of the hydrostatic pump.
  • a shuttle valve is connected to a pressurized with the output pressure of the shuttle valve pressure reducing valve.
  • the pressure reducing valve reduces the pressure acting in an actuator by means of the pressure supplied via the shuttle valve.
  • the hydrostatic machine is adjusted in the direction of lower delivery volume as the pressure in the working line increases, which leads to the higher pressure.
  • Such a device is known for example from DE 10 2004 061 861 B4.
  • the shuttle valve can fix in a middle position. In this middle position, the two body leading to the hydraulic consumer working lines are connected to each other via the valve body of the shuttle valve.
  • Such a so-called. Bypass position is advantageous if, for example, the hydrostatic drive belongs to a traction drive. The center position of the shuttle valve body is then adjusted when the vehicle must be towed. An involvement of the adjusting device or the hydraulic pump is therefore not required.
  • valve body of the shuttle valve must be locked in a central position to allow the bypass function.
  • locking device shown there by means of a pin requires a special expression of the housing, in which the direction of displacement of the valve body is arranged perpendicular to the direction of movement of the locking means.
  • the required for the shuttle valve function holes are all to be arranged in the valve housing. This is especially a considerable effort when multi-stage shuttle valves are provided.
  • a precise production is also required to allow a centering by the locking means. It may be particularly critical when it comes to the damage to the outer edges of the valve body in the locking. In the subsequent operation, in which the shuttle valve body is again to select the higher of two operating line pressures, this can lead to a deteriorated response of the shuttle valve.
  • the invention is therefore based on the object to provide a valve device in which a high degree of integration is ensured, but the functionality of the pressure weighing, ie the selection of the higher of at least two pressures, by the function of generating a hydraulic short circuit (" Bypass ”) and is easy to make.
  • the valve device according to the invention has a valve housing in which a valve body is arranged displaceably. In the valve body is at least one Connecting line, which is connected to a first connection point of the valve body is formed.
  • a selector valve device for weighing a first pressure supplied via a first pressure connection of the valve housing to the first connection point of the valve body and a second pressure supplied via a second pressure connection of the valve housing is now arranged in the valve body.
  • the first pressure port of the valve housing in a first position of the valve body is separated from the second pressure port of the valve housing and connected in a second position of the valve body with at least the second pressure port through-flow.
  • the selector valve device is preferably a changeover valve.
  • connection of the respective higher pressure line leading from two lines to a third line can also be effected by means of two check valves, one of which opens from the first line to the third line and the second from the second line to the third line , The two check valves then form the selector valve device.
  • the at least one selector valve device is arranged overall in the valve body and thus not affected in its function when the position of the valve body is changed. Above all, the production is considerably simplified since all channels to be created in the valve body for producing the selector valve can be introduced into an easily accessible component, namely the valve body.
  • connection line to connect the first connection point to a second connection point.
  • the bypass function can thus be achieved via the valve body.
  • the second connection point is formed by the mouth of the connecting line on an end face of the substantially cylindrical valve body.
  • the valve body in a bore which is arranged in the valve housing are arranged longitudinally displaceable. If this substantially cylindrical valve body is seated on the bottom of the bore designed as a blind bore, the second connection point of the connecting line is closed by the bottom of the blind bore.
  • valve body lifted from the bottom of the blind hole, so can be added or removed via the resulting free space on the end face pressure medium when the resulting space is connected by the end face, for example, with a working line.
  • the connecting line can then be connected to each other via the first and second pressure port two working lines.
  • the first connection point is formed by the other opening of the connection line, this being formed on a lateral surface of the cylindrical shape. It is particularly advantageous if the first connection point is located in a pocket.
  • the pocket is formed on the lateral surface, and extends in the axial direction of the valve body so far that a flow-through connection of the first connection point with the first pressure port in the valve housing is maintained upon displacement of the valve body from its first position to its second position.
  • the use of such a bag in particular has the advantage that distributed over the circumference of several such connection points can be formed and so with several connecting lines several working lines z. B. different hydraulic circuits can be connected to each other nen.
  • the use of the pockets ensures that an undesired overlap between working lines that are not to be connected to one another is particularly important. is excluded in the first position of the valve body.
  • the selector valve device is preferably formed in a line section which connects the lateral surface of the substantially cylindrical valve body with the connection line.
  • the mouth of the line section is located on the lateral surface so that at least in the first position of the valve body in the valve housing a connection between the mouth of the Kirsab- section and the second pressure port is present.
  • the line section preferably has a stepped reduction in its cross section at its end facing the connecting line.
  • the step-shaped reduction of the cross section simultaneously forms a sealing seat for a selector valve closing body, so that the selector valve device can be arranged in a simple manner in the line section. It is particularly preferred if a cross-sectional compensation element is inserted in the line section on its side facing the lateral surface of the substantially cylindrical valve body side. Thereby, the line can be made to the lateral surface with a cross section, so that a selector valve closing body can be inserted into it. Thereafter, the portion of the line section facing the lateral surface is closed with the cross-sectional compensation element.
  • the flow-through cross-section of the cross-sectional compensation element is preferably the same size as the cross-section of the local section facing the connecting line. This facilitates the assembly.
  • the valve device is not only provided for weighing two pressures, for example a first working line and a second working line, but also for weighing at least two further pressures.
  • bypass functions for the lines leading to the pressures to be weighed can also be provided.
  • a second connecting line is formed in the valve body and a second selection valve device is arranged. net.
  • the first and the second connecting line as well as the first and the second selector valve device are in particular the same in their construction and designed in the valve body that results in a twofold symmetry for the valve body. That is, the conduit assemblies within the valve body are such that rotation through 180 ° about the direction of displacement between the first and second positions interleave the first and second communication lines and selector valve assemblies, respectively.
  • Such a two-fold symmetry makes it easier to form the channels in the valve body, since in a simple manner during manufacture the tensioned valve body can be rotated by 180 ° and the corresponding second bore can be arranged.
  • the second pressure connection and a fourth pressure connection are also located in the same axial position with respect to the longitudinal extension of the recess.
  • This second and fourth pressure port are preferably opposite in the region of the bottom of the recess for receiving the valve body. This allows a connection between the second and fourth pressure port when lifting the valve body from the bottom of the valve body easily reach. The second and fourth pressure port are then connected to each other when lifting the valve body from the bottom of the recess via the resulting at the end face of the valve body volume.
  • a second connecting line and a second selector valve device are formed in the valve body, it is preferable to provide a third selector valve device having two input ports.
  • Each of the two input terminals is connected to an output terminal of each of the first selector valve device and the second selector valve device.
  • the highest system pressure of the total of four supplied pressures is available at the outlet of the third selection valve device.
  • Pressure cut valve unit is provided in a double pump and to be controlled via the multi-stage selector valve. This will become clearer in the following explanation of the embodiments.
  • an actuating device In order to move the valve body to actuate the bypass function between its first position and its second position, an actuating device is preferably provided. This has a relative to the valve housing fixedly arranged fixing means, wherein the second position of the valve body is fixed by moving the valve body relative to and until it rests against the fixing means. By setting the second position, it is ensured that a connection between the first end of the connecting line and the first pressure port can be ensured. As a stop serves in the second position facing away from the end face of the valve body, which bears against the fixing means. In order to ensure a correct installation position with respect to a rotation of the valve body, a valve body is preferably a
  • Positioning device formed. This engages in a recess on the part of the valve housing.
  • the recess extends in the longitudinal direction, so that when the valve body is displaced from the first to the second position, the positioning device can slide therein.
  • valve device 1 shows a hydraulic circuit for explaining the function of a Druckabschneideventiliser with the valve device according to the invention.
  • Fig. 3a) - d) is a schematic representation of the valve device according to the invention with a single-stage selector valve and a mechanical, electromagnetic, hydraulic or pneumatic actuation of the bypass function.
  • valve device 4 shows a section through a valve device according to the invention for explaining the routing in the valve housing
  • FIG. 5 shows a first side view 5 of the functional part of the valve device according to the invention
  • FIG. 6 shows a second view rotated by 90 ° about the longitudinal axis of the functional unit of FIG. 5;
  • FIG. 7 shows a third view rotated by a further 90 ° of the functional unit of FIG. 5;
  • FIG. 8 shows a view of the end face of the functional unit of FIG. 5 oriented toward the base of the recess;
  • FIG. 10 shows a second partial section along the line X - X of FIG. 8;
  • Fig. 1 1 is a section along the line XI - XI of Fig. 6;
  • Fig. 12 is a perspective view of the functional unit of the valve device according to the invention.
  • the pump assembly 1 shows a first pump 2 and a second pump 3.
  • the two pumps 2, 3 are driven together by a drive shaft 4 and are arranged in the same housing.
  • the two pumps 2, 3 are each made adjustable. While the first pump 2 promotes into a first working line 5 or a second working line 6, which at the pump Depending on the conveying direction, the second hydraulic pump 3 conveys into a third working line 7 or a fourth working line 8, depending on the conveying direction.
  • the third and the fourth working line 7, 8 are correspondingly connected to the connections A2, B2 , designated.
  • a first adjusting device 9 For adjusting the delivery volume and a conveying direction of the pump 2 designed for delivery in two opposite directions, a first adjusting device 9 is provided.
  • the first adjusting device 9 comprises an actuating piston which can be acted upon by pressure on two sides, whose adjusting movement is transmitted to the adjusting mechanism of the pump 2.
  • a control valve 1 1 For adjusting the pressure prevailing on both sides of the actuating piston, a control valve 1 1 is provided.
  • the control valve 1 1 is based on a neutral position in two directions deflected.
  • a control pressure chamber of the adjusting device 9 is connected to a control pressure supply line 13 for supplying pressure medium or the tank volume for discharging pressure medium. In the corresponding other end position of the control valve 1 1, the assignment is reversed.
  • a corresponding second adjusting device 10 and a corresponding second control valve 12 is provided for adjusting the delivery volume and the conveying direction of the second pump 3. Also this second control valve 12 is supplied via a further adjusting pressure supply line 14 which is provided for acting on the actuating piston pressure medium.
  • the pressure cutoff valve unit includes a pressure control valve 15 which is connected to the set pressure supply lines 13, 14. In its basic position shown in FIG. 1, the pressure regulating valve 15 connects the actuating pressure supply lines 13, 14 with a feed pressure line 18.
  • the feed system comprises a feed connection 16, via which pressure medium is supplied.
  • this feed connection 16 is connected to the delivery-side working line of a feed pump (not shown in FIG. 1).
  • a feed pressure limiting valve 17 is provided in order to have a constant feed pressure available from a certain delivery quantity of the feed pump.
  • largely constant pressure conditions prevail in the feed pressure line 18, which represent the maximum setting pressure available in the adjusting device 9 or in the second adjusting device 10.
  • valve device 18 comprises a shuttle valve device 19 and a bypass valve device 20.
  • Suction line 21 and a second extraction line 22 connected, which open as a first pressure port and as a second pressure port on the valve device.
  • the output of the shuttle valve device 19 is connected via a supply line 23 to the pressure regulating valve 15. If the pressure in the supply line 23 rises above a threshold value, the pressure valve 15 is actuated from the basic position of the pressure regulating valve 15 against the force of an adjustable spring. With the actuation of the pressure regulating valve 15, the adjusting pressure supply lines 13, 14 are connected to a tank volume. As a result, the effective available control pressure decreases and approaches the pressure of the tank volume.
  • the valve device 18 comprises, in addition to the shuttle valve device 19, the bypass valve device 20.
  • the removal lines 21 and 22 can be connected directly to one another in the sense of a bypass function.
  • Such a position of the bypass valve device 20 is advantageous if, for example, bypassing the pump 3, the hydraulic circuit should be closed briefly. This can for example be the case during a towing process.
  • the supply system has per pump 2, 3 still have two known in their function feed valve units 24, 15 and 26, 27.
  • the set pressure of the feed valve units 24, 15 and 26, 27 is for protection at occurring pressure peaks about 30 bar above the pressure threshold of the pressure control valve 15th
  • FIG. 2a shows a valve device schematically for a double pump, which, as shown in Figure 1, promotes in two separate circuits.
  • the connections to the working lines of the individual pumps 2, 3 are again denoted by the connections A1, B1, A2 and B2.
  • the higher of the two pressures prevailing at the pressure connections A2, B2 is determined via the second shuttle valve device 19.2 and fed to a third shuttle valve device 19.3.
  • the third shuttle valve device 19.3 selects between the supplied pressures and in turn outputs the higher of these two pressures via the supply line 23.
  • the first change-over valve tion 19.1 determined higher pressure of the pressure ports A1, B1 can also be output and used for example for measurement purposes.
  • the higher pressure weighed by the second shuttle valve device 19.2 can also be output separately.
  • bypass valve device 20.1 In addition to the multi-stage shuttle valve assembly is still a bypass valve device 20.1 available. This is hydraulically actuated and connects all of the pressure ports A1, A2, B1 and B2 in a switched position with each other. In the basic position, which is shown in FIG. 2a), on the other hand, all four pressure ports A1, B1 and A2, B2 are separated from one another.
  • FIG. 2b) is a basically coincident with the figure 2a) arrangement shown.
  • a pneumatic actuation of the connecting valve device 20. 2 is provided here.
  • FIG. 3a An exemplary embodiment of a valve device 18.3, which, as shown in FIG. 1, only weighs the pressure from one of the hydraulic circuits, is shown in FIG. 3a). It is shown here only a shuttle valve device, which weighs the higher of the prevailing at the pressure ports A2, B2 or A1, B1 pressures. The higher pressure is then supplied via the supply line 23 to the pressure reducing valve 15 as already described.
  • the valve device 18.3 further comprises a connecting valve device 20.3, which is mechanically operated in the illustrated embodiment and the pressure ports A1, B1 or A2, B2 can connect to each other.
  • FIGS. 3 b) - 3 d) 15 Alternative forms of actuation for the mechanical actuation of FIG. 3 a) are shown in FIGS. 3 b) - 3 d) 15.
  • the 20.4 - 20.6 actuation of the connecting valve device can accordingly also be electromagnetically, hydraulically or pneumatically.
  • An example of a valve device according to the invention as a structural design is shown in FIG.
  • the valve device shown there corresponds essentially to the arrangement shown in Figure 2, but with a mechanical actuation of the connecting valve means.
  • the valve device has a functional unit 25, which is inserted into a valve housing 26.
  • the valve housing 26 has for receiving a bore 27 designed as a recess.
  • the bore 27 is designed as a blind bore and has a bottom 28.
  • the functional unit 25 is inserted into the bore 27 and consists essentially of a valve body 29 and an actuating device 30 for axially displacing the valve body 29 between a first position and a second position. On the expression of the valve body 29 will be discussed in detail below.
  • the actuating device 30 has a fixing means 31, which is executed in the illustrated embodiment of threaded sleeve.
  • the threaded sleeve 31 is screwed into the bore 27 and has, in addition to the external thread, with which it is fixed in the valve housing 26, an internal thread.
  • a collar can be arranged on the threaded sleeve 31, with which the end position when screwing in the threaded sleeve 31 is fixed.
  • a threaded pin 32 is screwed in the threaded sleeve 31 in the threaded sleeve 31, a threaded pin 32 is screwed.
  • the threaded pin 32 has at its base 28 of the bore 27 facing the end of a cross-sectionally T-shaped geometry 33.
  • the length of the threaded pin 32 is dimensioned so that the threaded pin 32 protrudes in the axial direction on both sides of the threaded sleeve 31 from this.
  • the length of the valve body 29 is dimensioned so that a displacement in the axial direction is possible.
  • An end face 34 of the valve body 29 abuts against the base 28 of the bore 27 in a first position of the valve body 29. From this first position out of the valve body 29 in the direction of the threaded sleeve 31 is displaced.
  • the diameter of the substantially cylindrical valve body 29 is dimensioned such that the end facing away from the end face 34 serves as a stop for an axial displacement. This is what matters the valve body 29 facing the end of the threaded sleeve 31 at.
  • the T-shaped geometry 33 of the threaded pin 32 engages in a T-shaped groove formed on the end of the valve body 29 facing the threaded sleeve 31 ,
  • the thickness of the head of the T-shaped geometry 33 is dimensioned such that a free volume 42 remains in the T-shaped groove. The function of this free volume will be discussed below.
  • a first pressure port A1 and a second pressure port B1 for the first hydraulic circuit and a third pressure port A2 and a fourth pressure port B2 for the second hydraulic circuit of the two pumps 2, 3 are formed.
  • the first and third pressure port A1, A2 open approximately opposite and tangentially into the bore 27.
  • the second and fourth pressure port B1, B2 open into the bore 27 opposite and close to the base 28 and extend in its mouth approximately radially to the bore 27.
  • the second pressure port B1 and fourth pressure port B2 In the axial direction thereto in the direction of the open side of the bore 27 are the second pressure port B1 and fourth pressure port B2 arranged. In the area of the mouth, these channels are approximately tangential.
  • FIG. 4 shows the functional unit 25 in its first position, in which the end face 34 of the valve body 29 seals against the base 28 of the bore 27.
  • a connection between the pressure ports A1, A2, B1 and B2 is prevented by the valve body 29.
  • the valve body 29 is lifted from the base 28 to establish a connection between the pressure connections (bypass function), a volume is created in front of the end face 34 via which the second pressure connection B1 is connected to the fourth pressure connection B2.
  • a bore which, in addition to other channels and channels which connect a first pocket 36 with the end face 34 and a second pocket 37 with the end face 37.
  • connection point of these connection lines lies in the respective pocket 36 or 37 and is therefore permanently connected to the first pressure connection A1 or the third pressure connection A2, the respectively other connection point of the connection lines is by abutment of the end surface 34 on the base 28 of the bore 27 locked.
  • the region of the second and fourth connection points on the end face 34 there is in each case one groove, which is dovetailed in cross-section at least on one side, around the connection points, into which a sealing O-ring is inserted.
  • a positioning pin 38 is provided, which is inserted into a bore in the valve body 29.
  • the positioning pin 38 projects laterally out of the substantially cylindrical valve body 29 and engages with its protruding part in a groove 27 extending in the longitudinal direction of the bore.
  • Positioning pin 38 and groove together form a positioning device.
  • FIG. 5 shows a side view of the functional unit of the valve device according to the invention.
  • a first connection point 40 in the first pocket 36 opens out a valve body 29.
  • This first pocket 36 is in permanent fluid communication with the first pressure port A1 irrespective of the position of the valve body 29 in the bore 27.
  • the first connection point 40 forms a first end of a connection line still shown in the following drawings.
  • Connected to this connecting line is a line section designed as a stepped bore, the mouth 41 of which opens out on the lateral surface of the substantially cylindrical valve body 29.
  • the distance of the orifice 41 of the line section from the end face 34 of the valve body 29 is so dimensioned 5 that the orifice 41 is in fluid communication with the second pressure port B1.
  • This fluid connection is present at least when the valve body 29 is in its first position.
  • FIG. 6 shows a side view of the functional unit 25 rotated by 90 °.
  • the functional unit 25 is dubbed symmetrical. This means that on the side remote from the first pocket 36 of the valve body 29, a second pocket 37 is formed.
  • the extending in the valve body 29 channels are, as will be explained below, symmetrical to each other.
  • a shuttle valve device is arranged in each of these two line sections.
  • the respective outputs of the shuttle valve means are connected to inputs of a third shuttle valve means 43.
  • the third shuttle valve device 43 is arranged in a through bore which penetrates the valve body 29 along its diameter.
  • FIG. 7 shows a further side view of the functional unit 25, which has once again been rotated by 90 ° in the same direction. It can now be seen that a connection point 45 is likewise formed in the second pocket 37. Further, a second orifice 46 is shown. As the comparison with FIG. 5 shows directly, the arrangement is symmetrical as already described.
  • FIG. 8 shows the position of two sections for explaining the course of the channels in the valve body 29. For this purpose, FIG. 8 shows a plan view of the end face 34 of the functional unit 25.
  • FIG. 9 shows a section along the line X-X.
  • the first connection line is arranged.
  • the first connection line consists of a first bore section 51 .1 and a second bore section 51 .2.
  • the second bore section 51 .2 is introduced from the end face 34 into the valve body 29 and extends in the direction of the longitudinal axis of the valve body 29.
  • the first bore section 51 .1 of the second connecting line is introduced from the first pocket 36 into the valve body 29.
  • a line section 27 is introduced as a stepped bore in the valve body 29.
  • the orifice 46 of the line section 47 also lies in the jacket surface of the valve body 29.
  • the line section 47 opens into the second bore section 51 .2.
  • the connection between the conduit section 47 and the second bore section 51 .2 has a reduced cross section with respect to the orifice 46. From the side of the outlet 46 ago is a
  • Cross-section compensation element 50 inserted into the line section 47.
  • the outer circumference of the cross-sectional compensation element 50 sealingly cooperates with the conduit section 47.
  • a passage opening is provided which has the same cross-section as the connection of the line section 47 to the second bore section 51 .2.
  • a shuttle valve closing body 49 is arranged between the reduced cross section on the side of the second bore portion 51 .2 and the cross-sectional compensation element 50. This acts depending on the position sealingly with the second bore section 51 .2 reduced cross-section of the line section 47 or with the
  • Cross-sectional compensation element 50 together.
  • the thus-weighed pressure is supplied to the third shuttle valve device 43 via an outlet bore, which is indicated in FIG. 9 above the shuttle valve closing body 49. Is located the valve body 29 in its first position, the end face 34 bears sealingly against the base 28 of the bore 27.
  • Pressure medium is then supplied from the first pressure port A1 via the first bore section 51 .1 and the second bore section 51 .2 to a first input of the shuttle valve device 48. About the orifice 46 of the second to be compared pressure is supplied.
  • a groove which is dovetail-shaped in cross-section at least on one side, is formed around the second connection point 44 of the connection line, into which groove an O-ring is inserted.
  • FIG. 10 shows a partial section along the line X-X.
  • the comparison with Fig. 9 clearly shows the symmetry. Due to the symmetry can be dispensed with a new detailed description. Corresponding elements are provided with reference numerals increased by 10.
  • the position of the third shuttle valve device 43 can be seen clearly in FIG. 11, which shows a section along the line X1-X1 of FIG.
  • the third shuttle valve device 43 is arranged in a stepped transverse bore 65.
  • a shuttle valve closing body is also arranged here in the stepped transverse bore 65.
  • a cross-sectional compensation element 66 is arranged, with which the shuttle valve closing body can cooperate sealingly.
  • the third shuttle valve device 43 thus weighs the pressure prevailing on both sides of the transverse bore 65. To output the weighed pressure, an axial bore 67 is provided.
  • an obliquely extending communication bore 68 or 5 69 respectively leads from the first conduit section 47 to one end the transverse bore 65.
  • a diagonal connecting bore 49 to the other end of the transverse bore 65th
  • FIG. 12 once again shows the functional unit 25 in a perspective representation.
  • the invention is not limited to the illustrated embodiment.
  • only one-stage design is possible instead of the constructively shown multi-stage shuttle valve.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif valve comportant un corps de valve (29) disposé coulissant dans un boîtier de valve (26). Le corps de valve comporte une zone de raccordement et une conduite de liaison reliée à la zone de raccordement. Le corps de valve comporte un dispositif de valve de sélection permettant de doser une première pression fournie au moyen d'un premier raccord de pression (A1) du boîtier de valve et une seconde pression fournie au moyen du second raccord de pression (B1) du boîtier de valve. Dans une première position du corps de valve dans le boîtier de valve, le corps de valve sépare ainsi le premier raccord de pression et le second raccord de pression du boîtier de valve, et dans une seconde position du corps de valve, le premier raccord de pression est relié au second raccord de pression de façon à permettre un écoulement.
PCT/EP2012/070026 2011-10-27 2012-10-10 Dispositif valve notamment destiné à commander une valve de coupure de pression WO2013060573A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011117080.8 2011-10-27
DE102011117080 2011-10-27

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WO (1) WO2013060573A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102014218753A1 (de) 2014-09-18 2016-03-24 Robert Bosch Gmbh Hydraulische Ventileinheit und hydrostatische Einheit mit einer solchen Vetileinheit
IT202100012032A1 (it) * 2021-05-11 2022-11-11 Cnh Ind Italia Spa Collettore migliorato per valvole selettrici, disposizione idraulica e veicolo da lavoro comprendente il medesimo

Citations (2)

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Publication number Priority date Publication date Assignee Title
GB2009327A (en) * 1977-12-02 1979-06-13 Borg Warner Fluid control system with automatically actuated motor port lock-out valves
DE102004061861B4 (de) 2004-12-22 2008-06-19 Brueninghaus Hydromatik Gmbh Druckabschneidungsventileinheit und damit versehener hydraulischer Kreislauf

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Publication number Priority date Publication date Assignee Title
GB2009327A (en) * 1977-12-02 1979-06-13 Borg Warner Fluid control system with automatically actuated motor port lock-out valves
DE2852382C2 (de) * 1977-12-02 1986-06-05 Rexroth Corp., Bethlehem, Pa. Strömungsmittelanlage
DE102004061861B4 (de) 2004-12-22 2008-06-19 Brueninghaus Hydromatik Gmbh Druckabschneidungsventileinheit und damit versehener hydraulischer Kreislauf

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