EP2360380A2 - Hydraulic control valve for a single-acting differential cylinder with five control edges - Google Patents
Hydraulic control valve for a single-acting differential cylinder with five control edges Download PDFInfo
- Publication number
- EP2360380A2 EP2360380A2 EP11000886A EP11000886A EP2360380A2 EP 2360380 A2 EP2360380 A2 EP 2360380A2 EP 11000886 A EP11000886 A EP 11000886A EP 11000886 A EP11000886 A EP 11000886A EP 2360380 A2 EP2360380 A2 EP 2360380A2
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- Prior art keywords
- piston
- connection
- control
- valve
- control valve
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- 239000012530 fluid Substances 0.000 claims abstract description 45
- 238000006073 displacement reaction Methods 0.000 claims description 91
- 230000000903 blocking effect Effects 0.000 claims description 7
- 230000001172 regenerating effect Effects 0.000 claims description 4
- 230000001419 dependent effect Effects 0.000 description 4
- 238000011084 recovery Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
Definitions
- the invention relates to a hydraulic control valve for controlling a piston having a one-sided piston rod having double-acting working cylinder, the piston valve constructed in the control valve at least four external connections with associated formed in the valve housing ring channels, namely a pump port (P), a port (A1) for a supply and discharge line to the large displacement of the working cylinder, a connection (B) for a supply and discharge line to the small displacement of the working cylinder and a tank connected to the tank port (T1) and wherein the control piston of the control piston has piston collars with control edges arranged thereon , via which the connections (P, A1, B, T1) in the two positions of the control piston can be connected to one another in such a way that during the working stroke of the working cylinder a return of the fluid displaced from the small displacement during extension of the piston rod into the large lifting cylinder m of the working cylinder and for hubunablindigen switching the working cylinder from the power stroke on slow travel with subsequent holding state for pressure relief of the small displacement of the working cylinder
- a control valve with the aforementioned features is in the DE 10 2008 059 436 B3 described.
- the well-known design of the control valve to a method of the piston of the working cylinder with differential action, ie with a fast piston movement, allow by a return of the working stroke of the differential cylinder, ie at Extending the piston rod, from the small displacement of the working cylinder displaced fluid is provided in the line leading from the control valve to the large displacement of the working cylinder, so that the pump both during the working stroke of the working cylinder and in its return stroke with a retraction of the piston rod only the same flow rate must deliver.
- a fifth internal annular channel is formed in the known control valve in the valve housing, which is connected via an internal bridge formed in the valve housing with the terminal A associated annulus.
- the invention is therefore based on the object for a different phases during the working stroke, namely at fast forward travel of the piston and the subsequent holding phase, designed control valve according to the generic features set up so that the hydraulic clamping of the working cylinder by the control valve to the respective flowing volume flows is adjusted.
- the invention provides in its basic idea that are arranged on the at least three piston collars with five control edges having control valve two separate lines for the displaced during the working stroke of the piston from the small displacement fluid, of which a first, trained for the return line conduction connected to the small displacement supply and discharge line via a recess acting as remindyogisungs tenukante recess with the large displacement of the working cylinder and the second formed to connect the small displacement with the tank line path via a formed on an associated piston collar of the control valve pressure relief control edge, wherein the Pressure relief control edge forming recess designed in the associated control piston on the displaced during slow travel from the small displacement of the working cylinder fluid flow and is smaller than the other control edges forming n recesses of the piston collars.
- the invention has the advantage that the working phase of holding the piston with full holding force is now a suitable, because corresponding to the smaller volume flow smaller control edge is assigned to the control piston, whereby an accurate hydraulic clamping of the working cylinder is ensured during all phases.
- the circuit with the only required check valve is also easier to implement, than the use of the provided in the prior art directional control valve.
- the separate conduit paths for the displaced during the working stroke of the piston from the small displacement fluid are established by a corresponding branching of the supply and discharge line in front of the associated control edges of the control piston.
- the connected to the small displacement supply and discharge line branched in a branch in two, forming the two cable routes line strands and the first line path forming wiring harness of the piston collar associated with the ventheisungs Kunststoffkante and the second line path forming the wiring harness Is associated with pressure relief control edge having piston collar, wherein in the current for the working stroke of the cylinder position of the control piston demomoniungs Kunststoffkante the connection of the first wiring harness to the large capacity of the working cylinder and in the wiring harness, the check valve is turned on with a large capacity directed passage direction and the pressure relief control edge Connection of the second line strand to the tank via a switched on therein externally controllable check valve for switching the working cylinder receiving discharge line h created.
- each wiring harness an additional valve housing formed in the annular channel is assigned, of which an additional annular channel of the remindrekante forming piston collar for blocking or connection of the opening into the annular channel, the check valve having wiring for large displacement and the other additional annular channel of the pressure relief control edge forming piston collar for blocking or connection of the outgoing from the annular channel, the check valve having discharge line with the Terminal B is assigned to leading wiring harness.
- the inventive construction can be realized with different valve designs with a different number of external terminals; this is ultimately dependent on whether the respectively required connections between the annular spaces of the standard connections T1, A1, P, B and / or further housing connections and the additional annular spaces according to the invention are arranged inside or outside the valve housing. It is essential that the control piston used in each case has at least five control edges, of which two differently sized control edges are assigned as scrubglaisungs tenukante and as a pressure relief control edge coming from the small displacement of the working cylinder supply and discharge line.
- the branch of the supply and discharge line connected to the small displacement, the two line strands as well as the discharge line having the check valve are formed to the tank inside the valve housing.
- Such an arrangement can be first realized in a control valve with four external terminals T1, A1, P and B by the connection of the additional ring channel to the large displacement by means of a to be connected to the ring channel via the feedback control edge further internal annular channel and one outgoing and gepurintern is made to the connection to the A1 associated annular space leading bridge, wherein in the bridge, a check valve is turned on with a direction of passage A1 directed to the direction of passage.
- control valve over the four standard ports T1, A1, P and B also have a fifth external port A2, now in contrast to a four external connections having control valve, the connection of the additional ring channel to the large displacement by means of a with the Ring channel over the Regenerating control edge to be connected, the further port A2 associated annular space and is made by means of a connected to the external port A2 and leading to the large displacement of the working cylinder connecting line.
- Characteristic of the inventive design of the control valve with five control edges is that during the return stroke of the piston in the working cylinder displaced from the large displacement of the working cylinder large amount of fluid must be performed over the control edge of A1 to T1, which is therefore interpreted to be correspondingly large.
- an additional sixth port T2 which is connectable to the leading to the small displacement of the working cylinder connecting line port A2 via an additional piston collar with a sixth control edge, so that the connection line to or from the large cavity of the working cylinder can also be used for the return flow of a part of the fluid displaced during the return stroke from the large displacement to the tank.
- the control valve is provided with the required number of external terminals.
- the external terminals T1, A1, P, B, A2 and T2 of the non-return valve line branch from the branch out to a formed on the valve housing seventh external and connected to the annulus connection B1 and connected to the connected by the pressure relief control edge controlled additional annulus port T2 is connected via the check valve having discharge line to the tank.
- a division of the return stroke of Pistons from the large displacement displaced fluids did not take place on two partial flows.
- a further eighth connection in the form of an additional terminal T3 be provided, the terminal T2 via a fourth piston collar with an additional sixth control edge to the terminal A2 connectable and the port T3 is connected to the additional annulus controlled by the pressure relief control edge and connected to the tank via the discharge line having the check valve.
- the external connections A2, T2 are arranged adjacent to the connection B with respect to the standard connections T1, A1, P, B and the additional annular spaces are arranged in the valve housing 21 between the connection B and the connection A2.
- an identical control piston can be used for the valve with six and one with eight external connections, wherein the annular spaces to be bored in the valve housing are identical.
- connections A2, T2 with respect to the standard terminals T1, A1, P, B arranged adjacent to the terminal T1 and the one outer annular space outside adjacent to the terminal B associated annulus and the second additional annulus outside adjacent to the terminal A2 associated annulus is arranged. Also in This case can be kept identical regardless of the design of the valve housing with six or eight ports of the control piston as well as the bore of the annular spaces.
- a first off FIG. 1 apparent working cylinder 10 has a displaceable therein and on both sides different surfaces having piston 11 with a piston rod 12.
- the piston 11 divides the working cylinder 10 in a large displacement 13 and a small displacement 14.
- Each displacement 13, 14 is connected via a connected thereto supply and at the same discharge line 15 and 16 for the fluid with the load ports A1, B of a control valve 20 wherein the control valve 20 is further associated with a tank 17 and a pump 18.
- valve housing 21 of the control valve 20 initially four standard ports T1, A1, P, B are formed on the valve housing 21 of the control valve 20, wherein the port P to the pump 18, the port A1 via the supply and discharge line 15 with the large displacement 13 of the working cylinder 10th and the port B is connected via the supply and discharge line 16 with the small displacement 14 of the working cylinder 10.
- the tank connection T1 is assigned to the tank 17.
- a fifth external terminal A2 is formed on the valve housing 21, which is connected via a running outside of the control valve external connection line 22 with the large displacement 13 of the working cylinder or with the supply and discharge line 15.
- the individual abovementioned housing connections are each assigned annular spaces, namely an annular space 23 for the connection P, an annular space 24 for the connection A1, an annular space 25 for the connection B, an annular space 26 for the connection A2 and an annulus 27 for port T1.
- a first additional annular space 29 and a second additional annular space 29 a are still arranged between the associated to the terminals B and A2 annular spaces 25, 26, which, however, no external connections are assigned in the valve housing 21.
- a control piston 30 is displaceable having a total of three provided with five recesses designed as control edges piston collars 31, 31 recesses 32 and 33, 34 are milled in a corresponding arrangement on the outer sides of the piston collars.
- the recess 34 has a smaller dimension than the recesses 32, 33.
- two piston collars 31 respectively block the ports A1 and B.
- each corresponding pilot controls wherein by acting on the pilot controls with appropriate control oil of the control piston 30 in the valve housing 21 can be displaced in both directions, so that the formed on the control piston 30 piston collars 31 interconnect the existing on the valve housing 21 five housing connections with respect to the desired valve function. This is known in the art.
- the port A2 is provided, the in a manner to be described with the connection B interconnect and is connected by means of the external connection line 22 with the large displacement 13 of the working cylinder 10.
- branch 40 is provided for the guided over the port B fluid from which provided for the return line harness 41st and provided for the pressure relief wiring harness 42 take its output.
- the wiring harness 41 is connected to the first additional annular space 29, which is arranged adjacent to the connection A2 and can be connected thereto via a recess 33 formed on an associated piston collar 31 and acting as a regenerative control edge.
- valve housing 21 discharge line 37 between the second and adjacent to the connection B associated annular space 25 second additional annular space 29a and the tank port T1, in which a check valve 38 is turned on.
- the check valve 38 is opened.
- the pressure conditions applied to the supply and discharge line 16 change in such a way that now the port B is relieved via the wiring harness 42, the pressure relief control edge (recess 34), the additional annular space 29a and the discharge line 37 to the tank port T1, so that also in the valve-internal wiring harness 41 no pressure is applied, which would be sufficient to open the check valve 36.
- the small displacement 14 of the working cylinder 10 to port T1 pressure relieved while the guided over the wiring harness 41 feedback of the displaced from the small displacement 14 fluid is interrupted by the remaining in the closed position check valve 36.
- valve housing 21 only the four external standard housing connections T1, A1, P, B, so that from FIG. 1 apparent fifth connection A2 has been omitted.
- the port A2 in FIG. 1 assigned annular space 26 replaced by a valve-internal annulus V, which in turn is connected via a formed in the interior of the valve housing 21 bridge 50 with the A1 associated with the annulus annulus 24.
- the wiring harness 41 which can be connected by means of the feedback control edge (recess 33) with the valve-internal annulus V.
- additional annular space 29 and the bridge 50 are available, so that the displaced from the small displacement 14 fluid is directed to port A 1. Otherwise, the flow paths take place as to FIG. 1 described.
- FIG. 3 illustrated embodiment differs from that FIG. 1 Exception example described only by the fact that an additional drainage path for the displaced from the large displacement 13 during the return stroke of the piston 11 fluid is provided to the tank 17 by a line branch 60 is turned on in the supply and discharge line 15, from which a discharge line 61 directly to Tank 17 is guided.
- a pressure-dependent switching valve 62 is turned on in this discharge line 61.
- a throttle 63 is switched into the line 19 leading from the connection T1 to the tank 17, wherein a sensing line 64 leading to the switching valve 62 is connected to the line section located between the throttle 63 and the connection T1.
- control edge from A1 to T1 in the form of the associated recess 32 can now be of the same size as the further control edges 32 on the valve piston 30, so that a correspondingly symmetrical design of the control piston is provided.
- Valve housing 21 now a sixth housing connection T2 is provided, which is adjacent to the housing connected to the large displacement 13 via the connecting line 22 housing connection A2 and with this via an additional sixth, formed on an additional fourth piston collar control edge (recess 32).
- the fluid displaced from the large displacement 13 during the return stroke of the piston 11 can be subdivided into two partial flows which, on the one hand, flow via the line 15, the port A1 to the tank port T1 and via the line 22, the port A2 to the tank port T2.
- connection of the connection A2 to the first outer annular space 29 and the adjoining wiring harness 41 is simultaneously blocked so that the fluid coming from the conduit 22 can not flow to the connection B via the valve-internal wiring harness 41.
- this connection is additionally blocked by the check valve 36.
- FIG. 5 shows an embodiment of the invention, in which now the branch 40 for the two strands of lines 41 and 42 and the check valve 38 having discharge line to the tank outside the valve housing are arranged, whereby a corresponding number of housing connections is conditional.
- a seventh external housing connection B1 is provided, which is now assigned to the first additional annular space 29 and to which extent the outer wiring harness 41 is connected to the check valve 36.
- the terminal T2 is no longer associated with the port A2 and provides so far for a discharge of the displaced from the large displacement 13 fluid, but the terminal T2 is associated with the additional annular space 29a, so that at the terminal T2 now an external discharge line 45 is connected with the blocking valve 38 turned on therein.
- the fluid guided during the pressure relief via the connection B and the pressure relief control edge (recess 34) is discharged via the connection T2 directly to the tank.
- FIG. 5 illustrated embodiment provided with the ability to perform the entire, displaced from the large displacement 13 fluid flow through the control valve 20, it must be in accordance with the in FIG. 6 illustrated embodiment, a further and thus eighth external terminal T3 are provided.
- the terminal T2 is in the same way as FIG. 4 already described via an associated control edge (recess 32) to connect to the terminal A2, to which in turn the coming from the large displacement 13 connecting line 22 is connected.
- connection B 1 is arranged adjacent to the connection A2 and is to be connected to it via the feedback control edge (recess 33).
- the flow paths in the individual positions of the control piston 30 also take place here as described.
- FIGS. 4 and 6 shown execution parts correspond to one another insofar as six control edges (recesses 32, 33, 34) are formed on the control piston 30. From a comparison of FIGS. 4 and 6 It can also be seen that the design and arrangement of the additional annular spaces 29 and 29a in the valve housing 21 as well as the formation of the control piston 30 with the six control edges formed thereon (recesses 32, 33, 34) are identical.
- FIGS. 7 and 8th illustrated embodiments differ from those in FIGS. 4 and 6 illustrated embodiments only in that the terminals A2, T2 with respect to the standard terminals T1, A1, P, B are adjacent to the terminal B.
- the additional annular spaces 29 and 29a between the annular space 25 belonging to the connection B and the annular space 27 belonging to the connection A2 are arranged to carry out the described control functions.
- FIG. 7 leads the one, set up for the return feed and trained again inside the valve housing 21 line 41 from the branch 40 in the coming from the small displacement of the working cylinder 10 supply and discharge line 16 to the additional annular space 29, which is applicable in the control piston position for the working stroke opens via the associated piston collar 30 with the recess 33 acting as feedback control edge to the port A2, so that when fed back the displaced from the small displacement 14 fluid via the port B, the branch 40, the wiring harness 41 to the terminal A2 and from there via the connecting line 22 flows to the large displacement 13. Accordingly, the non-return valve 36 opening to the additional annular space 29 is turned on in the wiring harness 41.
- the other, at pressure relief of the small displacement 14 effective wiring harness 42 leads from the branch 40 to the terminal B associated annular space 25 which is connected via a piston collar 31 with acting as a pressure relief control edge smaller recess 34 with the second additional annular space 29 a, of which the valve-internal discharge line 37 with the involvement of the check valve 38 leads to the tank port T1 associated annulus 26.
- the fluid displaced after opening of the check valve 38 from the displacement 14 flows through the connection B, the branch 40, the wiring harness 42 and the valve internal discharge line 37 to the tank port T1 associated annulus 26 and from there to the tank 17.
- FIG. 8 illustrated embodiment agrees with the FIG. 7 described embodiment with the proviso that in turn the additional annular spaces 29 and 29 a external terminals B1 and T3 are assigned, so that the in FIG. 8 illustrated control valve in comparison with in FIG. 7 shown control valve has eight external connections. Also in this embodiment with eight external control terminals, the flow paths for the guided over the control valve fluid to perform according to the FIG. 7 given description.
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Abstract
Description
Die Erfindung betrifft ein hydraulisches Steuerventil zur Steuerung eines einen Kolben mit einseitiger Kolbenstange aufweisenden doppelt wirkenden Arbeitszylinders, wobei das in Kolbenschieberbauweise ausgebildete Steuerventil wenigstens vier externe Anschlüsse mit zugeordneten, im Ventilgehäuse ausgebildeten Ringkanälen, nämlich einen Pumpenanschluss (P), einen Anschluss (A1) für eine Zu- und Abfuhrleitung zum großen Hubraum des Arbeitszylinders, einen Anschluss (B) für eine Zu- und Abfuhrleitung zum kleinen Hubraum des Arbeitszylinders und einen mit dem Tank verbundenen Tankanschluss (T1) aufweist und wobei der Steuerkolben des Steuerventils Kolbenbunde mit daran angeordneten Steuerkanten aufweist, über die die Anschlüsse (P, A1, B, T1) in den beiden Stellungen des Steuerkolbens derart miteinander verbindbar sind, dass beim Arbeitshub des Arbeitszylinders eine Rückspeisung des beim Ausfahren der Kolbenstange aus dem kleinen Hubraum verdrängten Fluides in den großen Hubraum des Arbeitszylinders erfolgt und zur hubunabängigen Umschaltung des Arbeitszylinders von dem Arbeitshub auf Langsamfahrt mit anschließendem Haltezustand zur Druckentlastung des kleinen Hubraumes des Arbeitszylinders eine Verbindung des kleinen Hubraumes mit dem Tank schaltbar ist.The invention relates to a hydraulic control valve for controlling a piston having a one-sided piston rod having double-acting working cylinder, the piston valve constructed in the control valve at least four external connections with associated formed in the valve housing ring channels, namely a pump port (P), a port (A1) for a supply and discharge line to the large displacement of the working cylinder, a connection (B) for a supply and discharge line to the small displacement of the working cylinder and a tank connected to the tank port (T1) and wherein the control piston of the control piston has piston collars with control edges arranged thereon , via which the connections (P, A1, B, T1) in the two positions of the control piston can be connected to one another in such a way that during the working stroke of the working cylinder a return of the fluid displaced from the small displacement during extension of the piston rod into the large lifting cylinder m of the working cylinder and for hubunabängigen switching the working cylinder from the power stroke on slow travel with subsequent holding state for pressure relief of the small displacement of the working cylinder, a connection of the small displacement with the tank is switchable.
Ein Steuerventil mit den vorgenannten Merkmalen ist in der
Darüber hinaus ist bei dem aus der
Bei einem derartigen Steuerventil ergibt sich das Problem, daß das beim Arbeitshub des Arbeitszylinders aus dessen kleinem Hubraum verdrängte Fluid während des gesamten Arbeitshubes jeweils über die gleiche Steuerkante des Steuerkolbens von B nach A1 bzw. T1 geführt ist. Während bei der schnellen Kolbenbewegung des Steuerkolbens ein entsprechend großer Volumenstrom aus dem kleinen Hubraum verdrängt und über den Anschluss B und die zugehörige Steuerkante von B nach A1 in den großen Hubraum zurückgespeist wird, ist dieser Volumenstrom während der Haltephase bzw. während des Übergangs dazu deutlich geringer, so daß für diese Arbeitsphase des Arbeitszylinders die bei dem bekannten Steuerventil vorgesehene Steuerkante von B nach A1 zu groß ausgelegt ist.In such a control valve there is the problem that the displaced during the working stroke of the working cylinder from the small displacement fluid during the entire working stroke is guided in each case over the same control edge of the control piston from B to A1 or T1. While in the rapid piston movement of the control piston, a correspondingly large volume flow is displaced from the small displacement and fed back via the port B and the associated control edge from B to A1 in the large capacity, this volume flow during the holding phase or during the transition to significantly lower , so that designed for this working phase of the working cylinder, the control edge provided in the known control valve from B to A1 is too large.
Der Erfindung liegt daher die Aufgabe zugrunde, ein für unterschiedliche Phasen beim Arbeitshub, nämlich bei schneller Vorwärtsfahrt des Kolbens und bei der anschließenden Haltephase, ausgelegtes Steuerventil gemäß den gattungsgemäßen Merkmalen so einzurichten, daß die hydraulische Einspannung des Arbeitszylinders durch das Steuerventil an die jeweils fließenden Volumenströme angepasst ist.The invention is therefore based on the object for a different phases during the working stroke, namely at fast forward travel of the piston and the subsequent holding phase, designed control valve according to the generic features set up so that the hydraulic clamping of the working cylinder by the control valve to the respective flowing volume flows is adjusted.
Die Lösung dieser Aufgabe ergibt sich einschließlich vorteilhafter Ausgestaltungen und Weiterbildungen der Erfindung aus dem Inhalt der Patentansprüche, welche dieser Beschreibung nachgestellt sind.The solution to this problem arises, including advantageous refinements and developments of the invention from the content of the claims, which are adjusted to this description.
Die Erfindung sieht in ihrem Grundgedanken vor, dass an dem wenigstens drei Kolbenbunde mit fünf daran ausgebildeten Steuerkanten aufweisenden Steuerventil zwei getrennte Leitungswege für das beim Arbeitshub des Kolbens aus dem kleinen Hubraum verdrängte Fluid eingerichtet sind, von denen ein erster, für die Rückspeisung ausgebildeter Leitungsweg die an den kleinen Hubraum angeschlossene Zu- und Abfuhrleitung über eine als Rückspeisungssteuerkante wirkende Ausnehmung mit dem großen Hubraum des Arbeitszylinders verbindet und der zweite zur Verbindung des kleinen Hubraums mit dem Tank ausgebildete Leitungsweg über eine an einem zugeordneten Kolbenbund des Steuerventils ausgebildete Druckentlastungssteuerkante führt, wobei die die Druckentlastungssteuerkante bildende Ausnehmung in dem zugeordneten Steuerkolben auf den bei Langsamfahrt aus dem kleinen Hubraum des Arbeitszylinders verdrängten Fluidstrom ausgelegt und kleiner bemessen ist als die die weiteren Steuerkanten bildenden Ausnehmungen der Kolbenbunde.The invention provides in its basic idea that are arranged on the at least three piston collars with five control edges having control valve two separate lines for the displaced during the working stroke of the piston from the small displacement fluid, of which a first, trained for the return line conduction connected to the small displacement supply and discharge line via a recess acting as Rückfüisungssteuerkante recess with the large displacement of the working cylinder and the second formed to connect the small displacement with the tank line path via a formed on an associated piston collar of the control valve pressure relief control edge, wherein the Pressure relief control edge forming recess designed in the associated control piston on the displaced during slow travel from the small displacement of the working cylinder fluid flow and is smaller than the other control edges forming n recesses of the piston collars.
Mit der Erfindung ist der Vorteil verbunden, daß der Arbeitsphase des Haltens des Kolbens mit voller Haltekraft nun eine passende, weil entsprechend dem geringeren Volumenstrom kleinere Steuerkante an dem Steuerkolben zugeordnet ist, wodurch eine exakte hydraulische Einspannung des Arbeitszylinders während aller Arbeitsphasen sichergestellt ist. Die Schaltung mit dem nur noch erforderlichen Sperrventil ist dabei auch einfacher zu realisieren, als der Einsatz des beim Stand der Technik vorgesehenen Wegeventils.The invention has the advantage that the working phase of holding the piston with full holding force is now a suitable, because corresponding to the smaller volume flow smaller control edge is assigned to the control piston, whereby an accurate hydraulic clamping of the working cylinder is ensured during all phases. The circuit with the only required check valve is also easier to implement, than the use of the provided in the prior art directional control valve.
Nach einem Ausführungsbeispiel der Erfindung kann vorgesehen sein, dass die getrennten Leitungswege für das beim Arbeitshub des Kolbens aus dem kleinen Hubraum verdrängte Fluid durch eine entsprechende Verzweigung der Zu- und Abfuhrleitung vor den zugeordneten Steuerkanten des Steuerkolbens eingerichtet sind. Hierzu ist vorgesehen, dass sich die an den kleinen Hubraum angeschlossene Zu- und Abfuhrleitung in einer Verzweigung in zwei, die beiden Leitungswege ausbildenden Leitungsstränge verzweigt und dem den ersten Leitungsweg bildenden Leitungsstrang der Kolbenbund mit der Rückspeisungssteuerkante zugeordnet und dem den zweiten Leitungsweg bildenden Leitungsstrang der die Druckentlastungssteuerkante aufweisende Kolbenbund zugeordnet ist, wobei in der für den Arbeitshub des Zylinders geltenden Stellung des Steuerkolbens die Rückspeisungssteuerkante die Verbindung des ersten Leitungsstranges zum großen Hubraum des Arbeitszylinders herstellt und in den Leitungsstrang das Rückschlagventil mit einer zum großen Hubraum gerichteten Durchlassrichtung eingeschaltet ist und die Druckentlastungssteuerkante die Verbindung des zweiten Leitungsstranges mit dem Tank über eine ein darin eingeschaltetes extern ansteuerbares Sperrventil zur Umschaltung des Arbeitszylinders aufnehmende Abfuhrleitung herstellt.According to one embodiment of the invention can be provided that the separate conduit paths for the displaced during the working stroke of the piston from the small displacement fluid are established by a corresponding branching of the supply and discharge line in front of the associated control edges of the control piston. For this purpose, it is provided that the connected to the small displacement supply and discharge line branched in a branch in two, forming the two cable routes line strands and the first line path forming wiring harness of the piston collar associated with the Rückfüisungssteuerkante and the second line path forming the wiring harness Is associated with pressure relief control edge having piston collar, wherein in the current for the working stroke of the cylinder position of the control piston Rückfüisungssteuerkante the connection of the first wiring harness to the large capacity of the working cylinder and in the wiring harness, the check valve is turned on with a large capacity directed passage direction and the pressure relief control edge Connection of the second line strand to the tank via a switched on therein externally controllable check valve for switching the working cylinder receiving discharge line h created.
Um ventilintern die erforderlichen Anschlüsse für die beiden unterschiedlichen, bei dem Arbeitshub des Arbeitszylinders jeweils in Funktion bringbaren Leitungsstränge zu schaffen, ist nach einem Ausführungsbeispiel der Erfindung vorgesehen, dass jedem Leitungsstrang ein zusätzlicher im Ventilgehäuse ausgebildeter Ringkanal zugeordnet ist, von denen dem einen zusätzlichen Ringkanal der die Rückspeisungssteuerkante ausbildende Kolbenbund zur Sperrung bzw. Verbindung des in den Ringkanal mündenden, das Rückschlagventil aufweisenden Leitungsstranges zum großen Hubraum und dem anderen zusätzlichen Ringkanal der die Druckentlastungssteuerkante ausbildende Kolbenbund zur Sperrung bzw. Verbindung der von dem Ringkanal abgehenden, das Sperrventil aufweisenden Abfuhrleitung mit dem zum Anschluss B führenden Leitungsstrang zugeordnet ist.To valve internally to provide the necessary connections for the two different, in the working stroke of the working cylinder in each functioning line strands is provided according to an embodiment of the invention that each wiring harness an additional valve housing formed in the annular channel is assigned, of which an additional annular channel of the Rückfüisungssteuerkante forming piston collar for blocking or connection of the opening into the annular channel, the check valve having wiring for large displacement and the other additional annular channel of the pressure relief control edge forming piston collar for blocking or connection of the outgoing from the annular channel, the check valve having discharge line with the Terminal B is assigned to leading wiring harness.
Die erfindungsgemäße Ausbildung lässt sich bei unterschiedlichen Ventilbauformen mit einer unterschiedlichen Anzahl von externen Anschlüssen verwirklichen; dies ist letztlich davon abhängig, ob die jeweils erforderlichen Verbindungen zwischen den Ringräumen der Standardanschlüsse T1, A1, P, B und/oder weiterer Gehäuseanschlüsse sowie den erfindungsgemäßen zusätzlich ausgebildeten Ringräumen innerhalb oder außerhalb des Ventilgehäuses angeordnet sind. Wesentlich ist, dass der jeweils eingesetzte Steuerkolben wenigstens fünf Steuerkanten aufweist, von denen zwei unterschiedlich große Steuerkanten als Rückspeisungssteuerkante und als Druckentlastungssteuerkante der vom kleinen Hubraum des Arbeitszylinders herkommenden Zu- und Abfuhrleitung zugeordnet sind.The inventive construction can be realized with different valve designs with a different number of external terminals; this is ultimately dependent on whether the respectively required connections between the annular spaces of the standard connections T1, A1, P, B and / or further housing connections and the additional annular spaces according to the invention are arranged inside or outside the valve housing. It is essential that the control piston used in each case has at least five control edges, of which two differently sized control edges are assigned as Rückfüisungssteuerkante and as a pressure relief control edge coming from the small displacement of the working cylinder supply and discharge line.
Gemäß einer ersten Ausführungsform der Erfindung kann vorgesehen sein, dass die Verzweigung der mit dem kleinen Hubraum verbundenen Zu- und Abfuhrleitung, die beiden Leitungsstränge wie auch die das Sperrventil aufweisende Abfuhrleitung zum Tank innerhalb des Ventilgehäuses ausgebildet sind.According to a first embodiment of the invention it can be provided that the branch of the supply and discharge line connected to the small displacement, the two line strands as well as the discharge line having the check valve are formed to the tank inside the valve housing.
Eine derartige Anordnung lässt sich zunächst bei einem Steuerventil mit vier externen Anschlüssen T1, A1, P und B verwirklichen, indem die Verbindung des zusätzlichen Ringkanals zum großen Hubraum mittels eines mit dem Ringkanal über die Rückspeisungssteuerkante zu verbindenden weiteren internen Ringkanal und einer davon abgehenden und gehäuseintern zu dem zum Anschluss A1 gehörigen Ringraum führenden Brücke hergestellt ist, wobei in die Brücke ein Rückschlagventil mit einer zum Anschluss A1 gerichteten Durchlassrichtung eingeschaltet ist.Such an arrangement can be first realized in a control valve with four external terminals T1, A1, P and B by the connection of the additional ring channel to the large displacement by means of a to be connected to the ring channel via the feedback control edge further internal annular channel and one outgoing and gehäuseintern is made to the connection to the A1 associated annular space leading bridge, wherein in the bridge, a check valve is turned on with a direction of passage A1 directed to the direction of passage.
Gemäß einer Weiterbildung der Erfindung kann das Steuerventil über die vier Standardanschlüsse T1, A1, P und B hinaus einen fünften externen Anschluss A2 aufweisen, wobei nun im Unterschied zu einem vier externe Anschlüsse aufweisenden Steuerventil die Verbindung des zusätzlichen Ringkanals zum großen Hubraum mittels eines mit dem Ringkanal über die Rückspeisungssteuerkante zu verbindenden, dem weiteren Anschluss A2 zugeordneten Ringraums sowie mittels einer an den externen Anschluss A2 angeschlossenen und zum großen Hubraum des Arbeitszylinders führenden Anschlussleitung hergestellt ist.According to one embodiment of the invention, the control valve over the four standard ports T1, A1, P and B also have a fifth external port A2, now in contrast to a four external connections having control valve, the connection of the additional ring channel to the large displacement by means of a with the Ring channel over the Regenerating control edge to be connected, the further port A2 associated annular space and is made by means of a connected to the external port A2 and leading to the large displacement of the working cylinder connecting line.
Kennzeichnend für die erfindungsgemäße Ausbildung des Steuerventils mit fünf Steuerkanten ist, dass beim Rückhub des Kolbens im Arbeitszylinder die aus dem großen Hubraum des Arbeitszylinders verdrängte große Fluidmenge über die Steuerkante von A1 nach T1 geführt werden muss, die demzufolge entsprechend groß auszulegen ist. Um dies zu vermeiden und insofern gleiche Durchflusswege zu schaffen, kann nach einem Ausführungsbeispiel der Erfindung einer zusätzlicher sechster Anschluss T2 angeordnet sein, der mit dem der zum kleinen Hubraum des Arbeitszylinders führenden Verbindungsleitung zugeordneten Anschluss A2 über einen zusätzlichen Kolbenbund mit einer sechsten Steuerkante verbindbar ist, sodass die Verbindungsleitung zum bzw. vom großen Hohlraum des Arbeitszylinders auch für die Rückströmung eines Teils des beim Rückhub aus dem großen Hubraum verdrängten Fluids zum Tank nutzbar ist.Characteristic of the inventive design of the control valve with five control edges is that during the return stroke of the piston in the working cylinder displaced from the large displacement of the working cylinder large amount of fluid must be performed over the control edge of A1 to T1, which is therefore interpreted to be correspondingly large. To avoid this and to provide the same flow paths, can be arranged according to an embodiment of the invention, an additional sixth port T2, which is connectable to the leading to the small displacement of the working cylinder connecting line port A2 via an additional piston collar with a sixth control edge, so that the connection line to or from the large cavity of the working cylinder can also be used for the return flow of a part of the fluid displaced during the return stroke from the large displacement to the tank.
Soweit nun gemäß einer alternativen Ausführungsform die Verzweigung der an den kleinen Hubraum angeschlossenen Zu- und Abfuhrleitung, die beiden Leitungsstränge sowie die das Sperrventil aufweisende Abfuhrleitung zum Tank jeweils außerhalb des Ventilgehäuses angeordnet sind, ist das Steuerventil mit der erforderlichen Anzahl von externen Anschlüssen zu versehen. So kann vorgesehen sein, dass zusätzlich zu den externen Anschlüssen T1, A1, P, B, A2 und T2 der das Rückschlagventil aufweisende Leitungsstrang von der Verzweigung außen zu einem am Ventilgehäuse ausgebildeten siebten externen und mit dem Ringraum verbundenen Anschluss B1 geführt und der an den von der Druckentlastungssteuerkante gesteuerten zusätzlichen Ringraum angeschlossene Anschluss T2 über die das Sperrventil aufweisende Abfuhrleitung mit dem Tank verbunden ist. Insofern findet bei diesem Ausführungsbeispiel eine Aufteilung des beim Rückhub des Kolbens aus dem großen Hubraum verdrängten Fluids auf zwei Teilströme nicht statt.If, according to an alternative embodiment, the branch of the supply and discharge line connected to the small displacement, the two strands and the discharge valve having discharge line to the tank are each arranged outside the valve housing, the control valve is provided with the required number of external terminals. Thus, it can be provided that, in addition to the external terminals T1, A1, P, B, A2 and T2 of the non-return valve line branch from the branch out to a formed on the valve housing seventh external and connected to the annulus connection B1 and connected to the connected by the pressure relief control edge controlled additional annulus port T2 is connected via the check valve having discharge line to the tank. In this respect, in this embodiment, a division of the return stroke of Pistons from the large displacement displaced fluids did not take place on two partial flows.
Entsprechend kann in einer Weiterbildung zur Aufteilung des aus dem großen Hubraum verdrängten Fluidstromes in zwei gleiche Teilströme ein weiterer achter Anschluss in Form eines zusätzlichen Anschlusses T3 vorgesehen sein, wobei der Anschluss T2 über einen vierten Kolbenbund mit einer zusätzlichen sechsten Steuerkante mit dem Anschluss A2 verbindbar und der Anschluss T3 an den von der Druckentlastungssteuerkante gesteuerten zusätzlichen Ringraum angeschlossen und über die das Sperrventil aufweisende Abfuhrleitung mit dem Tank verbunden ist.Accordingly, in a development for dividing the displaced from the large displacement fluid flow into two equal partial flows, a further eighth connection in the form of an additional terminal T3 be provided, the terminal T2 via a fourth piston collar with an additional sixth control edge to the terminal A2 connectable and the port T3 is connected to the additional annulus controlled by the pressure relief control edge and connected to the tank via the discharge line having the check valve.
Soweit bei den Ausführungsbeispielen der Erfindung mit sechs bzw. acht externen Anschlüssen zusätzlich zu den Standardanschlüssen T1, A1, P, B weitere Anschlüsse A2, T2 vorgesehen sind, ergibt sich bei diesen Steuerventilen eine unterschiedliche Anordnung der ventilinternen zusätzlichen Ringräume, und zwar unabhängig davon, ob es sich um ein Ventil mit sechs oder mit acht externen Anschlüssen handelt.As far as in the embodiments of the invention with six or eight external terminals in addition to the standard terminals T1, A1, P, B further connections A2, T2 are provided, results in these control valves, a different arrangement of the valve internal additional annular spaces, regardless of whether it is a valve with six or eight external connections.
So ist nach einem ersten Ausführungsbeispiel der Erfindung vorgesehen, dass die externen Anschlüsse A2, T2 bezüglich der Standardanschlüsse T1, A1, P, B dem Anschluss B benachbart und die zusätzlichen Ringräume im Ventilgehäuse 21 zwischen dem Anschluss B und dem Anschluss A2 angeordnet sind. In diesen beiden Fällen lässt sich für das Ventil mit sechs und ein solches mit acht externen Anschlüssen jeweils ein identischer Steuerkolben verwenden, wobei auch die im Ventilgehäuse auszubohrenden Ringräume identisch sind.Thus, according to a first embodiment of the invention, it is provided that the external connections A2, T2 are arranged adjacent to the connection B with respect to the standard connections T1, A1, P, B and the additional annular spaces are arranged in the
Alternativ kann vorgesehen sein, dass die Anschlüsse A2, T2 bezüglich der Standardanschlüsse T1, A1, P, B benachbart dem Anschluss T1 angeordnet und der eine zusätzliche Ringraum außenliegend neben dem zum Anschluss B zugehörigen Ringraum und der zweite zusätzliche Ringraum außenliegend neben dem zum Anschluss A2 zugehörigen Ringraum angeordnet ist. Auch in diesem Fall kann unabhängig von der Bauform des Ventilgehäuses mit sechs oder acht Anschlüssen der Steuerkolben wie auch die Ausbohrung der Ringräume identisch gehalten sein.Alternatively it can be provided that the connections A2, T2 with respect to the standard terminals T1, A1, P, B arranged adjacent to the terminal T1 and the one outer annular space outside adjacent to the terminal B associated annulus and the second additional annulus outside adjacent to the terminal A2 associated annulus is arranged. Also in This case can be kept identical regardless of the design of the valve housing with six or eight ports of the control piston as well as the bore of the annular spaces.
In der Zeichnung sind Ausführungsbeispiele der Erfindung wiedergegeben, welche nachstehend beschrieben sind. Es zeigen:
- Fig. 1
- ein fünf externe Gehäuseanschlüsse mit fünf Steuerkanten aufweisendes hydraulisches Steuerventil mit daran angeschlossenem Arbeitszylinder in einer schematischen Darstellung,
- Fig. 2
- ein funktionell dem Steuerventil gemäß
Figur 1 entsprechendes Steuerventil mit vier externen Gehäuseanschlüssen und fünf Steuerkanten, - Fig. 3
- das gemäß
Figur 1 aufgebaute Steuerventil unter Einschluss eines druckabhängigen Umschaltventils für die Rückführung des aus dem großen Hubraum des Arbeitszylinders verdrängen Fluides zum Tank, - Fig. 4
- ein sechs externe Gehäuseanschlüsse aufweisendes Steuerventil mit sechs Steuerkanten,
- Fig. 5
- ein sieben externe Gehäuseanschlüsse aufweisendes hydraulisches Steuerventil mit fünf Steuerkanten,
- Fig. 6
- das gemäß
Figur 4 aufgebaute Steuerventil mit sechs Steuerkanten und mit acht externen Gehäuseanschlüssen und außenliegenden Verbindungsleitungen, - Fig. 7
- das Steuerventil gemäß
Figur 4 mit sechs externen Gehäuseanschlüssen und sechs Steuerkanten in einer anderen Ausführungsform, - Fig. 8
- das gemäß
Figur 7 aufgebaute Steuerventil mit acht externen Gehäuseanschlüssen und außenliegenden Verbindungsleitungen,
- Fig. 1
- a five external control connections with five control edges hydraulic control valve with connected thereto working cylinder in a schematic representation,
- Fig. 2
- a functional according to the control valve
FIG. 1 corresponding control valve with four external housing connections and five control edges, - Fig. 3
- according to
FIG. 1 constructed control valve including a pressure-dependent switching valve for the return of the displaced from the large displacement of the working cylinder fluid to the tank, - Fig. 4
- a control valve with six control edges, which has six external housing connections,
- Fig. 5
- a hydraulic control valve with seven control edges, which has seven external housing connections;
- Fig. 6
- according to
FIG. 4 constructed control valve with six control edges and with eight external housing connections and external connection lines, - Fig. 7
- the control valve according to
FIG. 4 with six external housing connections and six control edges in another embodiment, - Fig. 8
- according to
FIG. 7 constructed control valve with eight external housing connections and external connection lines,
Die vorstehende Zeichnung gibt lediglich die Ausgangsstellung für die nachstehende Funktionserläuterung ohne Rücksicht auf die maßliche Ausführung des Steuerventils wieder, so dass die konstruktive Auslegung und Wahl der Abmessungen von dem Durchschnittsfachmann in Kenntnis der von der Erfindung gewollten Funktionszusammenhänge festzulegen ist.The above drawing provides only the starting position for the following explanation of functions without regard to the dimensional design of the control valve again, so that the structural design and choice of dimensions by the average person skilled in the knowledge of the intention of the invention functional relationships is set.
Ein zunächst aus
Insofern sind an dem Ventilgehäuse 21 des Steuerventils 20 zunächst vier Standard-Anschlüsse T1, A1, P, B ausgebildet, wobei der Anschluss P mit der Pumpe 18, der Anschluss A1 über die Zu- und Abfuhrleitung 15 mit dem großen Hubraum 13 des Arbeitszylinders 10 und der Anschluss B über die Zu- und Abfuhrleitung 16 mit dem kleinen Hubraum 14 des Arbeitszylinders 10 verbunden ist. Dem Tankanschluss T1 ist der Tank 17 zugeordnet. Ferner ist an dem Ventilgehäuse 21 ein fünfter externer Anschluss A2 ausgebildet, der über eine außerhalb des Steuerventils verlaufende außenliegende Anschlussleitung 22 mit dem großen Hubraum 13 des Arbeitszylinders oder mit der Zu- und Abfuhrleitung 15 verbunden ist.In this respect, initially four standard ports T1, A1, P, B are formed on the
Im Inneren des Ventilgehäuses 21 sind den einzelnen vorgenannten Gehäuseanschlüssen jeweils Ringräume zugeordnet, und zwar ein Ringraum 23 für den Anschluss P, ein Ringraum 24 für den Anschluss A1, ein Ringraum 25 für den Anschluss B, ein Ringraum 26 für den Anschluss A2 und ein Ringraum 27 für den Anschluss T1. Zusätzlich sind zwischen den zu den Anschlüssen B und A2 gehörigen Ringräumen 25, 26 noch ein erster zusätzlicher Ringraum 29 und ein zweiter zusätzlicher Ringraum 29a angeordnet, denen jedoch keine externen Anschlüsse im Ventilgehäuse 21 zugeordnet sind.In the interior of the
In der zugeordneten Bohrung des Ventilgehäuses 21 ist ein Steuerkolben 30 verschiebbar, der insgesamt drei mit zusammen fünf als Ausnehmungen ausgebildeten Steuerkanten versehene Kolbenbunde 31 aufweist, wobei in einer entsprechenden Anordnung auf den Außenseiten der Kolbenbunde 31 jeweils Ausnehmungen 32 beziehungsweise 33, 34 ausgefräst sind. Dabei weist die Ausnehmung 34 eine kleinere Abmessung als die Ausnehmungen 32, 33 auf. In der schematisch dargestellten Ausgangsstellung des Steuerkolbens 30 sperren zwei Kolbenbunde 31 jeweils die Anschlüsse A1 und B ab.In the associated bore of the
Wie im einzelnen nicht weiter dargestellt, weil als bekannt zu unterstellen, sind zur Herbeiführung der Steuerbewegungen des Steuerkolbens 30 an beiden Enden des Steuerkolbens 30 in dem Ventilgehäuse 21 jeweils entsprechende Vorsteuerungen ausgebildet, wobei durch Beaufschlagung der Vorsteuerungen mit entsprechendem Steueröl der Steuerkolben 30 in dem Ventilgehäuse 21 jeweils in beiden Richtungen verschoben werden kann, so dass die an dem Steuerkolben 30 ausgebildeten Kolbenbunde 31 die an dem Ventilgehäuse 21 vorhandenen fünf Gehäuseanschlüsse im Hinblick auf die gewünschte Ventilfunktion zusammenschalten. Dies ist im Stand der Technik bekannt.As not shown in detail, because to be assumed to be responsible for bringing about the control movements of the
Um eine Rückspeisung des bei dem Arbeitshub des Arbeitszylinders 10, dass heißt bei dem Ausfahren der Kolbenstange 12 aus dem Arbeitszylinder 10, aus dem kleinen Hubraum 14 verdrängten Fluids in den großen Hubraum 13 des Arbeitszylinders 10 durchführen zu können, ist der Anschluss A2 vorgesehen, der in einer noch zu beschreibenden Weise mit dem Anschluss B zusammenzuschalten und mittels der außenliegenden Anschlussleitung 22 mit dem großen Hubraum 13 des Arbeitszylinders 10 verbunden ist.In order to perform a return of the working stroke of the working
Zur Einstellung unterschiedlicher, bei der Rückspeisung einerseits und bei der Druckentlastung des kleinen Hubraums 14 zum Tank 17 andererseits wirksamer Leitungsstränge ist eine innerhalb des Ventilgehäuses 21 ausgebildete Verzweigung 40 für das über den Anschluss B geführte Fluid vorgesehen, von der ein für die Rückspeisung vorgesehener Leitungsstrang 41 und ein für die Druckentlastung vorgesehener Leitungsstrang 42 ihren Ausgang nehmen. Der Leitungsstrang 41 ist in Form einer im Ventilgehäuse ausgebildeten Verbindungsbohrung mit dem ersten zusätzlichen Ringraum 29 verbunden, der insoweit dem Anschluss A2 benachbart angeordnet und mit diesem über eine an einem zugeordneten Kolbenbund 31 ausgebildete, als Rückspeisungssteuerkante wirkende Ausnehmung 33 verbindbar ist.To set different, in the recovery on the one hand and in the pressure relief of the
Weiterhin ist bei dem in
Soweit in einer beim Arbeitshub des Arbeitszylinders 10 nach links versetzten Stellung des Steuerkolbens 30 eine Verbindung zwischen dem Anschluss P und dem Anschluss A1 hergestellt und der Anschluss T1 durch den entsprechenden Kolbenbund blockiert ist, ist in dieser Kolbenstellung die Rückspeisungsverbindung von B nach A2 dadurch hergestellt, dass das Fluid in den an der Verzweigung 40 abgehenden Leitungsstrang 41 in Richtung des ersten zusätzlichen Ringraumes 29 strömt und dabei das in den Leitungsstrang 41 eingeschaltete Rückschlagventil 36 mit seiner zum ersten Ringraum 29 gerichteten Durchlassrichtung öffnet. Soweit gleichzeitig in der nach links versetzten Stellung des Steuerkolbens 30 eine Verbindung des zum Anschluss B gehörigen Ringraumes 25 mit dem zweiten zusätzlichen Ringraum 29a über die Ausnehmung 34 geschaltet ist, befindet sich das in die von dem zusätzlichen Ringraum 29a abgehende Abfuhrleitung 37 eingeschaltete Sperrventil 38 in seiner Sperrstellung, so dass über diesen Weg kein Fluid abströmen kann. Somit ist nur gegeben, dass das Fluid vom Anschluss B über die Verzweigung 40, den Leitungsstrang 41, den ersten zusätzlichen Ringraum 29 und die als Rückspeisungssteuerkante ausgebildete Ausnehmung 33 in den zum Anschluss A2 gehörigen Ringraum 27 und vom Anschluss A2 über die Verbindungsleitung 22 in den großen Hubraum 13 des Arbeitszylinders 10 strömen kann. Demnach wird der von der Pumpe P über den Anschluss A1 gelieferte Volumenstrom um die Rückspeisungsmenge an Fluid aus dem kleinen Hubraum 14 des Arbeitszylinders 10 erhöht, und es ist ein Schnellgang des Kolbens 11 im Arbeitszylinder 10 gegeben.As far as in a working stroke of the working
Soll nun von der schnellen Vorwärtsfahrt des Kolbens 11 auf Langsamfahrt beziehungsweise die anschließende Haltephase umgeschaltet werden, so wird das Sperrventil 38 geöffnet. Damit verändern sich die an der Zu- und Abfuhrleitung 16 anliegenden Druckverhältnisse dergestalt, dass nun der Anschluss B über den Leitungsstrang 42, die Druckentlastungssteuerkante (Ausnehmung 34), den zusätzlichen Ringraum 29a und die Abfuhrleitung 37 zum Tankanschluss T1 entlastet ist, so dass auch in dem ventilinternen Leitungsstrang 41 kein Druck mehr anliegt, der ausreichen würde, das Rückschlagventil 36 zu öffnen. Insofern ist nach Öffnung des Sperrventils 38 der kleine Hubraum 14 des Arbeitszylinders 10 zum Anschluss T1 druckentlastet, während die über den Leitungsstrang 41 geführte Rückspeisung des aus dem kleinen Hubraum 14 verdrängten Fluids durch das in der Schließstellung verbleibende Rückschlagventil 36 unterbrochen ist.If now be switched from the fast forward travel of the
Zum Rückhub des Kolbens 11 im Arbeitszylinder 10 wird der Steuerkolben 30 gegenüber der in
Wie aus der vorstehend beschriebenen Ausbildung des Steuerventils 20 ersichtlich, wird während der Schnellfahrt des Kolbens 11 das aus dem kleinen Hubraum 14 verdrängte Fluid über die Rückspeisungssteuerkante (Ausnehmung 33) zur Rückspeisung abgeleitet, während bei Umschaltung der schnellen Vorwärtsfahrt des Kolbens 11 durch Öffnung des Sperrventils 38 und die damit verbundene Druckentlastung des kleinen Hubraums 14 zum Tank 17 die auf einen kleineren Volumenstrom ausgelegte, als Druckentlastungssteuerkante wirkende Ausnehmung 34 am Steuerkolben 30 wirksam ist.As can be seen from the above-described design of the
Bei dem in
Das in
Bei dem in
Will man das in
Die in den
Die in den
Entsprechend
Der andere, bei Druckentlastung des kleinen Hubraumes 14 wirksame Leitungsstrang 42 führt von der Verzweigung 40 zum dem Anschluss B zugeordneten Ringraum 25, der über einen Kolbenbund 31 mit der als Druckentlastungssteuerkante wirkenden kleineren Ausnehmung 34 mit dem zweiten zusätzlichen Ringraum 29a verbunden ist, von dem die ventilinterne Abfuhrleitung 37 unter Einschaltung des Sperrventils 38 zu dem zum Tankanschluss T1 zugehörigen Ringraum 26 führt. Somit fließt das nach Öffnung des Sperrventils 38 aus dem Hubraum 14 verdrängte Fluid über den Anschluss B, die Verzweigung 40, den Leitungsstrang 42 und die ventilinterne Abfuhrleitung 37 zu dem zum Tankanschluss T1 gehörigen Ringraum 26 und von dort zum Tank 17. Im Übrigen stellen sich die Fließwege für das über das Steuerventil 20 geführte Fluid entsprechend der Beschreibung zu
Das in
Die in der vorstehenden Beschreibung, den Patentansprüchen, der Zusammenfassung und der Zeichnung offenbarten Merkmale des Gegenstandes dieser Unterlagen können einzeln als auch in beliebigen Kombinationen untereinander für die Verwirklichung der Erfindung in ihren verschiedenen Ausführungsformen wesentlich sein.The features disclosed in the foregoing description, the claims, the abstract and the drawings of the subject matter of these documents may be essential individually as well as in any combination with each other for the realization of the invention in its various embodiments.
Claims (11)
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DE201010009085 DE102010009085B3 (en) | 2010-02-24 | 2010-02-24 | Hydraulic control valve for controlling double-action operating cylinder, has recess laid out in collar on fluid flow squeezed out of small volume of cylinder during slow movement and exhibiting dimension smaller than remaining recesses |
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EP2360380A2 true EP2360380A2 (en) | 2011-08-24 |
EP2360380A3 EP2360380A3 (en) | 2014-07-30 |
EP2360380B1 EP2360380B1 (en) | 2016-11-30 |
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EP11000886.9A Active EP2360380B1 (en) | 2010-02-24 | 2011-02-04 | Hydraulic control valve for a single-acting differential cylinder with five control edges |
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CN114810583A (en) * | 2021-01-27 | 2022-07-29 | 爱塞威汽车有限责任公司 | Control valve with optimized cross section |
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WO2014106229A1 (en) | 2012-12-31 | 2014-07-03 | Vanderbilt University | Spool and body architectures for three-position directional control valves |
CN112555299B (en) * | 2020-12-02 | 2022-06-14 | 安徽江淮汽车集团股份有限公司 | Double-control electromagnetic valve and hydraulic clutch system |
Citations (1)
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DE102008059436B3 (en) | 2008-11-27 | 2010-01-07 | Parker Hannifin Gmbh & Co. Kg | Hydraulic control valve for controlling double acting working cylinder, has annular channel formed in housing, and recess producing connection of contacts, where dimension of recess is twice larger than another recesse |
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US3273468A (en) * | 1965-01-26 | 1966-09-20 | Fawick Corp | Hydraulic system with regenerative position |
US6116142A (en) * | 1996-07-05 | 2000-09-12 | Parker Hannifin Gmbh | Controller for a fluid cylinder |
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DE102008059436B3 (en) | 2008-11-27 | 2010-01-07 | Parker Hannifin Gmbh & Co. Kg | Hydraulic control valve for controlling double acting working cylinder, has annular channel formed in housing, and recess producing connection of contacts, where dimension of recess is twice larger than another recesse |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN114810583A (en) * | 2021-01-27 | 2022-07-29 | 爱塞威汽车有限责任公司 | Control valve with optimized cross section |
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EP2360380A3 (en) | 2014-07-30 |
DE102010009085B3 (en) | 2011-03-10 |
EP2360380B1 (en) | 2016-11-30 |
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