Patent Application
20250067351
The invention concerns a valve slide according to claim 1, a control valve according to the preamble of claim 16, a vehicle according to claim 19 and a method according to claim 20.
It has been proposed that closed volumes which are displaced or filled by a movement of a valve slide are equipped with large leakages in bearing gaps in order to compensate the surplus or deficient volumes.
The objective of the invention is in particular to provide a generic device with advantageous damping properties. The objective is achieved according to the invention by the features of claims 1, 16, 19 and 20, while advantageous implementations and further developments of the invention may be gathered from the subclaims.
A flow-through hydraulic valve slide, in particular for a control valve for regulating damping characteristics of shock absorbers, is proposed, with at least one hydraulic link valve for influencing a flow-through of the valve slide, wherein the hydraulic link valve comprises at least one first control port, at least one second control port, at least one entry and at least one exit, preferably at least two exits, which can be opened in an interchangeable manner at least towards the entry. In this way, advantageous damping properties are achievable. Advantageously, a damping characteristic for shock absorbers is achievable, which at the same time has high dynamics and low overall leakage. Advantageously, a conflict of objectives between dynamics and leakage, which occurs in known control valves (there, high dynamics generally means high leakage) can be resolved by the invention. Advantageously, due to low overall leakage, regulation is enabled even at low damper speeds, in particular as a particularly low opening point of the control valve is achievable. Advantageously, the overall leakage can be optimized independently of the dynamics to be achieved, for example as it is possible either to significantly reduce leakage (functional advantage) with a constant manufacturing tolerance or as it is advantageously possible to augment manufacturing tolerances without producing particularly disadvantageous effects (cost advantage).
In particular, the valve slide implements a component of the control valve for regulating the damping characteristics of shock absorbers. The valve slide in particular separates a pressure side of a shock absorber comprising the control valve from a pressure-free side of the shock absorber. In particular, the pressure side may change depending on the application of a tensile force or of a compressive force. Opening of the separation of pressure side and pressure-free side by the valve slide will induce damping by means of an oil flow. In particular, the valve slide comprises hydraulic effective surfaces. In particular, the valve slide comprises at least one hydraulic effective surface and at least one further hydraulic effective surface, wherein the hydraulic effective surface and the further hydraulic effective surface(s) are arranged on the valve slide relative to each other in such a way that they hydraulically counteract each other, in particular during a damping process, and wherein the tensile or compressive forces of the shock absorber that are to be damped in particular act on the hydraulic effective surfaces. In particular, the valve slide can be at least section-wise flowed through by a fluid, for example an oil, preferably a hydraulic oil. In particular, the flow-through capability of the valve slide achieves that oil, in particular hydraulic oil, can be pumped back and forth between a pressure fluid reservoir of the control valve and a pressure-free (pressure fluid) tank of the shock absorber. Herein in particular the assignment of the pressure-free region, i.e. of the pressure-free (pressure fluid) tank, changes depending on the flow-through direction. This switchover is advantageously achieved substantially without substantial leakage losses and without undesired build-up of substantial counter-forces. This advantageously allows achieving high switching dynamics of the control valve with a chassis regulation starting already at small chassis vibrations. In particular, the valve slide can be flowed through bidirectionally. In particular, the valve slide comprises at least four different flow-through paths. In particular, the hydraulic link valve is configured for influencing a flow-through of at least two of the four flow-through paths, preferably of all four flow-through paths. In particular, the link valve is integrated in the valve slide. In particular, the link valve is completely enclosed by the valve slide. In particular, at least one of the control ports, preferably all control ports, at the same time forms/form entries of the link valve. In particular, the hydraulic pressures applied at the control ports of the link valve control the link valve, in particular the valve position of the link valve. In particular, the link valve is free of an electronic, magnetic and/or mechanical control. In particular, the link valve is controlled/operated in a purely fluid-mechanical manner. In particular, the link valve is flowed through by the pressure fluid. In particular, the control ports are actuatable/actuated by pressure signals. In particular, the entry may coincide with at least one of the control ports. In particular, the link valve may comprise two entries, wherein the two entries may coincide with respectively different control ports. Alternatively, it is conceivable that at least one entry is realized separately from a control port and/or that at least one control port does not form an entry into which a fluid flowing through the link valve can enter.
Furthermore, it is proposed that the flow-through hydraulic valve slide comprises a sealing surface that is configured to tightly sit on a valve seat of the control valve, wherein the first control port is hydraulically connected to a first side of the valve slide, wherein the second control port is hydraulically connected to a second side of the valve slide, and wherein the two sides to which the control ports are hydraulically connected are arranged on the valve slide in such a way that the first side and the second side can be sealed relative to each other by the sealing surface. In this way, advantageous damping properties are achievable. Advantageously, in this way a controlling of the link valve, in particular a connection to the exit of the link valve, is achievable, depending on the pressures applied to the two sides from an outside. In particular, the sides of the valve slide are hydraulically separate from each other when the valve slide sits on the valve seat in a sealing manner. In particular, there is always one of the control ports arranged on a pressure side of the valve slide, while the other one of the control ports is arranged on a pressure-free side of the valve slide. In particular, the opening point of the shock absorber is the point in which the valve slide is lifted from the valve seat. The valve slide is configured to generate, depending on its opening position, a damping of an applied tensile or compressive force. If an acting tensile or compressive force is large enough to lift the valve slide from the valve seat, a pressure fluid will flow between the two sides, as a result of which a damping of the acting tensile or compressive forces will be generated. The control valve is configured to adjust, for example by means of magnetic fields, the damping force/damping hardness by influencing the opening movement of the valve slide. The valve slide is connected to a magnet armature of an electromagnet. The electromagnet is configured to generate a force opposed to an opening movement of the valve slide. “Configured” is in particular to mean specially programmed, designed and/or equipped. In particular, the sealing surface is arranged on a side of the valve slide facing away from the electromagnet, wherein a reverse implementation is generally also conceivable.
By an object being configured for a specific function is in particular to be understood that the object fulfils and/or carries out this specific function in at least one application state and/or operation state.
In addition, it is proposed that the exit, which is preferably different from the control ports, is hydraulically connected to a third side of the valve slide, which is arranged opposite the sealing surface as viewed in a designated movement direction of the valve slide. In this way, advantageous damping properties are achievable. Advantageously, a regulatable (at least section-wise axial) flow-through of the valve slide is attainable. In particular, the exit, which is different from the control ports, is open to a side of the valve slide that is arranged opposite the sealing surface in the axial direction of the valve slide. In particular, the exit is connected either to a hydraulic effective surface, in particular a hydraulic effective surface differing from the hydraulic effective surfaces onto which chassis vibrations are exerted, or to the pressure fluid reservoir.
If the hydraulic link valve is realized as a two-pressure valve, which is in particular configured to open and/or keep open the entry to which the control port having the lower pressure is assigned, in particular the control port of the two control ports at which a lower pressure is applied, towards the exit, which is in particular different from the control ports, preferably the exit of the two-pressure valve, advantageous damping properties are achievable. Advantageously, a selective regulation of the flow-through of the valve slide is achievable. Advantageously, in this way an exchange, which is as resistance-free as possible, is enabled between the pressure fluid reservoir of the control valve and the pressure-free (pressure fluid) tank of the shock absorber. Advantageously, leakage can be kept low while enabling high-grade dynamics. The valve slide in particular comprises at least one flow channel with at least one branching, wherein preferably each branch path forms respectively one of the four flow-through paths. At the branching, a first sub-channel of the flow channel, a second sub-channel of the flow channel and a third sub-channel of the flow channel meet. Preferably the first sub-channel of the flow channel and the second sub-channel of the flow channel together form the first flow-through path of the valve slide. Preferably the first sub-channel of the flow channel and the third sub-channel of the flow channel together form the second flow-through path of the valve slide. The two-pressure valve is in particular arranged in the branching of the flow channel and is configured to open and/or keep open the first sub-channel towards that one of the two further sub-channels at which a lower pressure is applied. Preferably, the two-pressure valve at the same time closes the first sub-channel towards that one of the two further sub-channels that has the higher pressure.
Furthermore, it is proposed that the exit of the two-pressure valve is hydraulically connected to a region of the valve slide which at least partially delimits the pressure fluid reservoir of the control valve, wherein the pressure fluid reservoir is in particular configured to be filled and/or emptied during a movement of the valve slide via a flow-through path that is controlled at least by the two-pressure valve. In this way, advantageous damping properties are achievable. Advantageously, a selective regulation of the flow-through of the valve slide is achievable. Advantageously, in this way an exchange, which is as resistance-free as possible, is enabled between the pressure fluid reservoir of the control valve and the pressure-free (pressure fluid) tank of the shock absorber. In particular, the two-pressure valve ensures that the flow-through path always opens into the currently pressure-free (pressure fluid) tank and thus the filling and emptying of the pressure fluid reservoir during a movement of the valve slide proceeds at least substantially in a resistance-free manner.
If the hydraulic link valve is realized as a shuttle valve, which is in particular configured to open and/or keep open the entry to which the control port having the higher pressure is assigned, in particular to open and/or keep open that control port of the two control ports at which a higher pressure is applied, towards the exit, which is in particular different from the control ports, preferably the exit of the shuttle valve, advantageous damping properties are achievable. Advantageously, a selective regulation of the flow-through of the valve slide is achievable.
Advantageously, in this way a transmission of forces, in particular shock absorber tensile forces and/or shock absorber compressive forces, which is as efficient and/or dynamic as possible, is enabled to the hydraulic effective surface of the valve slide, which is configured to generate a counterforce to the forces. In particular, the hydraulic effective surface is larger than the further hydraulic effective surface(s), in particular independently of whether further connectable hydraulic effective sub-surfaces are connected to the hydraulic effective surface or not. The valve slide in particular comprises at least one further flow channel with at least one branching, wherein preferably each branch path forms respectively one of the four flow-through paths. At the branching, a first sub-channel of the further flow channel, a second sub-channel of the further flow channel and a third sub-channel of the further flow channel meet. Preferably the first sub-channel of the further flow channel and the second sub-channel of the further flow channel together form the third flow-through path of the valve slide. Preferably the first sub-channel of the further flow channel and the third sub-channel of the further flow channel together form the fourth flow-through path of the valve slide. The shuttle valve is in particular arranged in the branching of the further flow channel and is configured to open and/or keep open the first sub-channel towards that one of the two further sub-channels at which a higher pressure is applied. Preferably the two-pressure valve at the same time closes the first sub-channel towards that one of the two further sub-channels that has the lower pressure. The shuttle valve is in particular configured to hydraulically separate the respectively currently pressure-free side from the first sub-channel of the further flow channel. The shuttle valve in particular ensures that a flow-through path of the exit of the further flow channel always opens into the currently pressure-loaded tank and thus the pressure also acts on the (upper) hydraulic effective surface, which is in particular configured to generate a counterforce to the shock absorber tensile forces and/or shock absorber compressive forces.
In the following, it is proposed that the exit of the shuttle valve is hydraulically connected to a hydraulic effective surface, in particular of the valve slide, which is situated opposite a further hydraulic effective surface, in particular of the valve slide, which is realized on the side of the valve slide towards which the shuttle valve, in particular the control port of the shuttle valve, is currently open. In this way, advantageous damping properties are achievable. Advantageously, in this way a transmission of forces, in particular shock absorber tensile forces and/or shock absorber compressive forces, which is as efficient and/or dynamic as possible, is enabled to the hydraulic effective surface of the valve slide, which is configured to generate a counterforce to said forces.
Beyond this, it is proposed that the opposite-situated hydraulic effective surfaces have different dimensions. In this way, advantageous damping properties are achievable. Advantageously, a pressure-dependent force difference between the opposite-situated sides of the valve slide is achievable. In particular, the hydraulic effective surface is larger than each of the further hydraulic effective surfaces. In particular, the hydraulic effective surface, preferably a totality of all hydraulic effective sub-surfaces of the hydraulic effective surface, is by at least 3%, preferably by at least 5%, advantageously by at least 10%, preferably by at least 15% and preferentially by at most 25% larger than the respective opposite-situated further hydraulic effective surface on the pressure side or tension side.
In addition, it is proposed that the flow-through hydraulic valve slide comprises at least one further hydraulic link valve, which in particular differs from the hydraulic link valve in a functional principle, for influencing a flow-through of the valve slide, wherein the further hydraulic link valve comprises at least one first control port and at least one second control port and in particular has at least one exit, which can be opened in an interchangeable manner towards at least one of the control ports. In this way, advantageous damping properties are achievable. As a result, advantageous flow-through properties of the valve slide are achievable for the damping. In particular, the hydraulic link valve and the further hydraulic link valve have different exits, which are in particular realized separately from each other and/or are sealed with respect to one another.
If herein the hydraulic link valve is realized as a two-pressure valve and the further hydraulic link valve is realized as a shuttle valve, high dynamics can advantageously be achieved with at the same time low leakage. In particular, the two-pressure valve and the shuttle valve are respectively enclosed by the valve slide. In particular, the two-pressure valve and the shuttle valve are realized separately from each other. In particular, the respective movement axes of the valve elements of the two-pressure valve and the shuttle valve extend in directions which are not parallel to each other.
If herein moreover the hydraulic link valve is assigned to the flow channel (one of the exits) realized at least partially by the valve slide and the further hydraulic link valve is assigned to the further flow channel (other of the exits) realized at least partially by the valve slide, wherein the two flow channels are realized completely separate from each other, in particular without connection to each other, it is advantageously possible to achieve high dynamics and at the same time low leakage.
Alternatively, it is proposed that the hydraulic link valve is realized as a single valve, which has at least one further exit and which combines the function of a shuttle valve with the function of a two-pressure valve in one valve. This advantageously allows further reducing complexity, in particular by further reduction of a number of components. Advantageously, costs can be kept low as a result. In particular, in such a case the valve slide is free of further valves, such as further shuttle valves or further two-pressure valves. In particular, the single valve is arranged at the same time in the first flow channel and in the second flow channel of the valve slide.
It is further proposed that the single valve is embodied as a 4/2 shuttle valve, which is configured to open and/or keep open the entry assigned to that control port of the two control ports at which, in particular viewed relatively, a higher pressure is applied, towards the exit, in particular towards the exit of the link valve which is hydraulically connected to the hydraulic effective surface, and at the same time to open and/or keep open the entry assigned to that control port of the two control ports at which, in particular viewed relatively, a lower pressure is applied, towards the further exit, in particular towards the exit of the link valve which is hydraulically connected to the pressure fluid reservoir. In this way, the functions of a shuttle valve and of a two-pressure valve can advantageously be combined in a single valve. In this way, complexity and costs are advantageously reducible.
Furthermore, it is proposed that the hydraulic link valve that is embodied as a 4/2 shuttle valve comprises a combination-valve valve slide which is at least section-wise capable of being flowed through. In this way, high compactness is advantageously achievable. Moreover, an advantageous valve configuration is achievable, which is in particular suitable for combining the functions of a two-pressure valve and a shuttle valve in a single valve. In particular, the combination-valve valve slide comprises an, in particular internal, flow channel which extends at least over a large portion of a longitudinal extent of the combination-valve valve slide.
It is also proposed that, in particular apart from the hydraulic link valve and/or apart from the further hydraulic link valve, the flow-through hydraulic valve slide has an orifice-free configuration. This advantageously allows keeping a complexity and in particular a number of components at a low level. An “orifice” is in particular to mean a local flow resistance element with a step-like cross-section constriction, in which a ratio of length to diameter is comparably small, preferably smaller than 1.5.
Furthermore, a—preferably proportional—bidirectional control valve is proposed for regulating damping characteristics, in particular of shock absorbers, with the flow-through hydraulic valve slide. This allows providing advantageous damping properties and/or damping characteristics. In particular, the bidirectional control valve is configured for a regulation of the damping characteristics in two directions, preferably in a rebound direction and in a compression direction. A “proportional bidirectional control valve” is in particular to mean a bidirectional control valve configured for regulating a damping force, preferably of a shock absorber, in a current-proportional manner. In particular, the bidirectional control valve is configured, with a bidirectional flow-through, to always conduct a compensation of a fluid volume into a space having a lower pressure, while at the same time the compensation of the fluid volume with a space having a higher pressure is blocked. In a customary implementation with orifices, this would result in that, in contrast to a unidirectional control valve, a double number of orifices requiring installation space would be necessary. The implementation according to the invention thus allows keeping installation space, number of components and thus costs at a low level.
It is moreover proposed that the bidirectional control valve is specifically implemented for achieving a capability for regulating a pressure drop at the valve slide, starting from a volume flow of less than 10 l/min, preferably less than 5 l/min and preferably less than 2 l/min. In this way, advantageous damping properties/damping characteristics are achievable. In particular, an opening point/inflection point of the bidirectional control valve is below 10 l/min, preferably below 5 l/min and preferentially below 2 l/min.
Furthermore, it is proposed that the bidirectional control valve comprises a first tank, in particular for a shock absorber rebound stage, and a second tank that is separable from the first tank by the valve slide, in particular for a shock absorber compression stage, the bidirectional control valve further comprising a pressure fluid reservoir the volume of which is variable by a movement of the valve slide, which is realized separately from the tanks and which is partially fillable and/or partially emptyable by a flow-through of the valve slide, wherein the hydraulic link valve that is realized as a two-pressure valve is configured to automatically and dynamically create a valve-slide flow-through connection between the pressure fluid reservoir and only that one of the two tanks which currently has a lower pressure load, in particular which is currently pressure-free. In this way, advantageous damping properties/damping characteristics are achievable, which preferably permit high dynamics with low leakages. In particular, the first tank is realized as a first chamber of a piston rod of a shock absorber. In particular, the second tank is realized as a second chamber of the piston rod of the shock absorber.
In addition, a vehicle with the bidirectional control valve is proposed, which has an advantageously comfortable chassis.
Furthermore, a method for an automatic adjustment of instantaneous flow-through directions by means of flow-through valve slides is proposed, wherein the instantaneous flow-through directions are automatically adjusted dynamically by the two-pressure valve, which is in particular at least partially integrated in the valve slide, and by the shuttle valve, which is in particular at least partially integrated in the valve slide, or by the 4/2 shuttle valve, which is in particular at least partially integrated in the valve slide. In this way, advantageous damping properties are achievable. Advantageously, a damping characteristic for shock absorbers is achievable which at the same time has high dynamics and low overall leakage.
The valve slide according to the invention, the control valve according to the invention, the vehicle according to the invention and the method according to the invention shall not be limited to the above-described application and implementation. In particular, in order to fulfil a functionality that is described here, the valve slide according to the invention, the control valve according to the invention, the vehicle according to the invention and the method according to the invention may have a number of individual elements, components, method steps and units that differs from a number given here.
Further advantages will become apparent from the following description of the drawings. Two exemplary embodiments of the invention are illustrated in the drawings. The drawings, the description and the claims contain a plurality of features in combination. Someone skilled in the art will purposefully also consider the features individually and will find further expedient combinations.
In the drawings:
The control valve 10a comprises an electromagnet 92a. The electromagnet 92a comprises a magnet coil 94a. The electromagnet 92a is configured to adjust a force required for lifting the valve slide 14a from the valve seat 24a. Depending on a magnetic field strength generated by the magnet coil 94a, the force required for lifting the valve slide 14a from the valve seat 24a increases. The electromagnet 92a is realized as a reluctance magnet. The electromagnet 92a comprises a magnetic core 96a. The magnetic core 96a is to a large portion arranged in an interior of the magnet coil 94a. The magnetic core 96a protrudes from the interior of the magnet coil 94a towards the valve slide 14a. The control valve 10a comprises a main armature 98a. The main armature 98a is realized as a magnet armature comprising a ferromagnetic material. The main armature 98a is arranged in the interior of the magnet coil 94a. The main armature 98a is movably supported in the interior of the magnet coil 94a. An air gap 100a of the electromagnet 92a that is realized as a reluctance magnet is arranged between the main armature 98a and the magnetic core 96a. The main armature 98a is pulled towards the magnetic core 96a and/or held in a position close to the magnetic core 96a by the magnetic field of the magnet coil 94a. On a side opposite the magnetic core 96a, the main armature 98a is supported on an upper side of the control valve 10a by a compression spring 102a. The electromagnet 92a comprises a magnet housing 104a that surrounds the magnet coil 94a. The valve housing 88a and the magnet housing 104a are sealingly connected to each other. The control valve 10a, in particular the electromagnet 92a, comprises a tappet element 106a. The tappet element 106a is fixedly connected to the main armature 98a or is supported on the main armature 98a. The tappet element 106a is configured to transmit a force generated by the main armature 98a to the valve slide 14a. The tappet element 106a protrudes from the interior of the magnet coil 94a towards the valve slide 14a. The tappet element 106a can be operated by the magnet coil 94a. The tappet element 106a is configured to adjust, in an energized (normal) operation state, a variable damping characteristic of the control valve 10a depending on the magnetic field strength generated by the magnet coil 94a. The control valve 10a comprises a pressure fluid reservoir 42a. The pressure fluid reservoir 42a is variable with respect to its volume by a movement of the valve slide 14a. The pressure fluid reservoir 42a is partially fillable and partially emptyable by the flow-through of the valve slide 14a with the pressure fluid (for example oil). The pressure fluid reservoir 42a is realized separately from the tanks 66a, 68a. Furthermore, with regard to the implementation and functionality of the control valve 10a, reference is made to the German patent application with the application number 10 2021 134 565.0, the content of which is herewith entirely incorporated into the present patent application.
The two-pressure valve 38a comprises a valve slide 120a, which is configured to adjust the opening position of the two-pressure valve 38a. The hydraulic link valve 12a is configured for an influencing of the flow-through of the valve slide 14a. The hydraulic link valve 12a comprises a first control port 16a. The hydraulic link valve 12a comprises a first entry 20a. In the case shown in
The first control port 16a is hydraulically connected to a first side 28a of the valve slide 14a. The second control port 18a is hydraulically connected to a second side 30a of the valve slide 14a. The two sides 28a, 30a which the control ports 16a, 18a are hydraulically connected to are arranged relative to the valve slide 14a/on the valve slide 14a in such a way that the first side 28a and the second side 30a can be sealed (in a fluid-tight manner) against each other by the sealing surface 26a of the valve slide 14a. The exit 22a of the hydraulic link valve 12a of
The two-pressure valve 38a is configured to open and/or keep open the entry 20a, 36a, to which the control port 16a, 18a having the lower pressure is assigned, towards the exit 22a. The valve slide 14a comprises a flow channel 56a. The flow channel 56a is configured as a recess in the valve slide 14a. The hydraulic link valve 12a (the two-pressure valve 38a) is assigned to the flow channel 56a. The flow channel 56a comprises three partial flow channels: one partial flow channel connected to the first entry 20a of the hydraulic link valve 12a, one partial flow channel connected to the second entry 36a of the hydraulic link valve 12a and one partial flow channel connected to the exit 22a of the hydraulic link valve 12a. The partial flow channels of the flow channel 56a may be realized as bores in the valve slide 14a. The flow channel 56a has a branching 110a. In the branching 110a, three sub-channels of the flow channel 56a meet, which respectively open into one of the aforementioned partial flow channels. The flow channel 56a comprises a first flow-through path 112a. The first flow-through path 112a extends via the branching 110a between the partial flow channel connected to the first entry 20a of the hydraulic link valve 12a and the partial flow channel connected to the exit 22a of the hydraulic link valve 12a. The flow channel 56a comprises a second flow-through path 114a. The second flow-through path 114a extends via the branching 110a between the partial flow channel connected to the second entry 36a of the hydraulic link valve 12a and the partial flow channel connected to the exit 22a of the hydraulic link valve 12a. Both flow-through paths 112a, 114a of the flow channel 56a open into the partial flow channel that is connected to the exit 22a of the hydraulic link valve 12a. The partial flow channel which starts from the exit 22a extends obliquely/at an angle relative to the designated movement direction 34a of the valve slide 14a.
The exit 22a of the two-pressure valve 38a is hydraulically connected to a region 44a of the valve slide 14a that is configured to at least partially delimit the pressure fluid reservoir 42a of the control valve 10a. The pressure fluid reservoir 42a is configured to be filled and/or emptied during a movement of the valve slide 14a via one of the flow-through paths 112a, 114a that is controlled at least by the two-pressure valve 38a. The pressure fluid reservoir 42a is partially delimited by the valve housing 88a. The pressure fluid reservoir 42a is realized by an interaction of the valve slide 14a and the valve housing 88a. In the state of the two-pressure valve 38a shown by way of example in
The first control port 16′a of the further hydraulic link valve 54a is hydraulically connected to the first side 28a of the valve slide 14a. The second control port 18′a of the further hydraulic link valve 54a is hydraulically connected to the second side 30a of the valve slide 14a. The two sides 28a, 30a, to which the control ports 16′a, 18′a of the further hydraulic link valve 54a are hydraulically connected, are arranged relative to the valve slide 14a/on the valve slide 14a in such a way that the first side 28a and the second side 30a can be sealed (in a fluid-tight manner) against each other by the sealing surface 26a of the valve slide 14a. The exit 22′a of the further hydraulic link valve 54a of
The shuttle valve 48a is configured to open and/or keep open the entry 20′a, 36′a, to which the control port 16′a, 18′a having the higher pressure is assigned, towards the exit 22′a. The valve slide 14a comprises a further flow channel 58a. The further flow channel 58a is realized as a recess in the valve slide 14a. The further hydraulic link valve 54a (the shuttle valve 48a) is assigned to the further flow channel 58a. The two flow channels 56a, 58a are completely separate from each other. The two flow channels 56a, 58a are realized without connection to each other. The further flow channel 58a comprises three partial flow channels: one partial flow channel connected to the first entry 20′a of the further hydraulic link valve 54a, one partial flow channel connected to the second entry 36′a of the further hydraulic link valve 54a, and one partial flow channel connected to the exit 22′a of the further hydraulic link valve 54a. The further flow channel 58a comprises a further branching 46a. In the further branching 46a, three sub-channels of the further flow channel 58a meet, which respectively open into one of the aforementioned partial flow channels. The further flow channel 58a comprises a third flow-through path 108a. The third flow-through path 108a extends via the branching 46a between the partial flow channel connected to the first entry 20′a of the further hydraulic link valve 54a and the partial flow channel connected to the exit 22′a of the further hydraulic link valve 54a. The further flow channel 58a comprises a fourth flow-through path 116a. The fourth flow-through path 116a extends via the branching 46a between the partial flow channel connected to the second entry 36′a of the further hydraulic link valve 54a and the partial flow channel connected to the exit 22′a of the further hydraulic link valve 54a. Both flow-through paths 108a, 116a of the further flow channel 58a open into the partial flow channel that is connected to the exit 22′a of the further hydraulic link valve 54a. The partial flow channel which starts from the exit 22′a of the further hydraulic link valve 54a extends parallel to the designated movement direction 34a of the valve slide 14a.
A further exemplary embodiment of the invention is shown in
The 4/2 shuttle valve 60b is configured to open and/or keep open the entry 20b, 36b, to which the control port 16b, 18b having the lower pressure is assigned, towards the exit 22b. The 4/2 shuttle valve 60b is configured to at the same time open and/or keep open the entry 20b, 36b, to which the control port 16b, 18b having the higher pressure is assigned, towards the further exit 40b. The valve slide 14b comprises a flow channel 56b and a further flow channel 58b. The 4/2 shuttle valve 60b is assigned to both flow channels 56b, 58b. The flow channel 56b comprises a first flow-through path 112b. The first flow-through path 112b extends between a partial flow channel connected to the first entry 20b of the 4/2 shuttle valve 60b and to a first tank 66b of the control valve 10b and a partial flow channel connected to the exit 22b of the 4/2 shuttle valve 60b and to a hydraulic effective surface 50b that is situated opposite the first tank 66b. The flow channel 56b comprises a second flow-through path 114b. The second flow-through path 114b extends between a partial flow channel connected to the second entry 36b of the 4/2 shuttle valve 60b and to the second tank 68b of the control valve 10b and a partial flow channel connected to the exit 22b of the 4/2 shuttle valve 60b and to the hydraulic effective surface 50b. Both flow-through paths 112b, 114b of the flow channel 56b thus open into the partial flow channel that is connected to the exit 22b of the 4/2 shuttle valve 60b.
The further flow channel 58b comprises a third flow-through path 108b. The third flow-through path 108b extends between a partial flow channel connected to the first entry 20b of the 4/2 shuttle valve 60b and to the first tank 66b of the control valve 10b and a partial flow channel connected to the second exit 40b of the 4/2 shuttle valve 60b and to a pressure fluid reservoir 42b of the control valve 10b. The further flow channel 58b comprises a fourth flow-through path 116b. The fourth flow-through path 116b extends between a partial flow channel connected to the second entry 36b of the 4/2 shuttle valve 60b and to the second tank 68b of the control valve 10b and the partial flow channel connected to the second exit 40b of the 4/2 shuttle valve 60b and to the pressure fluid reservoir 42b of the control valve 10b. Both flow-through paths 108b, 116b of the further flow channel 58b thus open into the partial flow channel that is connected to the further exit 40b of the 4/2 shuttle valve 60b.
The 4/2 shuttle valve 60b is thus configured to open and/or keep open the entry 20b, 36b, which is assigned to that control port 16b, 18b of the two control ports 16b, 18b at which the higher pressure is applied, towards the exit 22b and at the same time to open and/or keep open the entry 20b, 36b, which is assigned to that control port 16b, 18b of the two control ports 16b, 18b at which the lower pressure is applied, towards the further exit 40b.
The 4/2 shuttle valve 60b comprises a first valve part 134b and a second valve part 136b. The first valve part 134b is inserted in a sealing manner into a recess 140b of the valve slide 14b. The first valve part 134b forms five regions 142b, 144b, 146b, 148b, 150b (first region 142b, second region 144b, third region 146b, fourth region 148b, fifth region 150b). The regions 142b, 144b, 146b, 148b, 150b are respectively sealable relative to each other (depending on a position of the second valve part 136b) and/or selectively combinable with respectively one of the further regions 142b, 144b, 146b, 148b, 150b (depending on a position of the second valve part 136b). The first region 142b is arranged in the axial direction 158b of the 4/2 shuttle valve 60b outside the 4/2 shuttle valve 60b on a first axial side 152b of the first valve part 134b. The second valve part 136b is supported so as to be movable in the axial direction 158b. The first region 142b is fluidically connected to the first tank 66b. The first region 142b is sealed at the outer circumference of the 4/2 shuttle valve 60b by a first seal 156b of the first valve part 134b with respect to the further regions 144b, 146b, 148b, 150b. The second region 144b is fluidically connected to the hydraulic effective surface 50b. The second region 144b is sealed at the outer circumference of the 4/2 shuttle valve 60b on one side by the first seal 156b with respect to the first region 142b and on an opposite-situated side by a second seal 160b of the first valve part 134b with respect to the further regions 146b, 148b, 150b. The third region 146b is fluidically connected to the second tank 68b. The third region 146b is sealed at the outer circumference of the 4/2 shuttle valve 60b on one side by the second seal 160b with respect to the first region 142b and the second region 144b and on an opposite-situated side by a third seal 162b of the first valve part 134b with respect to the further regions 148b, 150b. The fourth region 148b is fluidically connected to the pressure fluid reservoir 42b. The fourth region 148b is sealed at the outer circumference of the 4/2 shuttle valve 60b on one side by the third seal 162b with respect to the first region 142b, the second region 144b and the third region 146b and on an opposite-situated side by a fourth seal 164b of the first valve part 134b with respect to the fifth region 150b. The fifth region 150b is arranged in the axial direction 158b of the 4/2 shuttle valve 60b outside the 4/2 shuttle valve 60b on a second axial side 154b of the first valve part 134b. The fifth region 150b is fluidically connected to the second tank 68b. The fifth region 150b is sealed at the outer circumference of the 4/2 shuttle valve 60b by the fourth seal 164b of the first valve part 134b with respect to the further regions 142b, 144b, 146b, 148b.
The second valve part 136b is arranged within the first valve part 134b. The second valve part 136b is arranged so as to be axially movable in the first valve part 134b. The second valve part 136b glides in a sealing manner within a recess 138b of the first valve part 134b. The second valve part 136b forms a combination-valve valve slide 62b that is at least section-wise capable of being flowed through. The second valve part 136b is configured to be moved back and forth between a first valve position 166b and a second valve position 168b. In
The second pressure-application surface 172b is arranged outside the flow-through recess 174b of the second valve part 136b. The second pressure-application surface 172b is arranged on an axial outer surface of the second valve part 136b.
In the second region 144b, the first valve part 134b comprises at least one inflow and/or outflow opening 182b on an outer circumference that is, in particular with respect to the axial direction 158b, situated in the radial direction 180b, said inflow and/or outflow opening 182b permitting a fluidic connection from an inner space of the first valve part 134b to the further hydraulic effective surface 54b. In the third region 146b, the first valve part 134b comprises, on an outer circumference that is, in particular with respect to the axial direction 158b, situated in a radial direction 180b, at least one inflow and/or outflow opening 184b permitting a fluidic connection from the inner space of the first valve part 134b to the second tank 68b. In the fourth region 148b, the first valve part 134b comprises, on an outer circumference that is, in particular with respect to the axial direction 158b, situated in a radial direction 180b, at least one inflow and/or outflow opening 186b permitting a fluidic connection from the inner space of the first valve part 134b to the pressure fluid reservoir 42b. The first region 142b and the fifth region 150b are in each case connected to the inner space of the first valve part 134b by axial inflow and/or outflow openings 188b, 190b.
In the first valve position 166b, the first region 142b is fluidically connected to the second region 144b. In the first valve position 166b, the third region 146b is fluidically connected to the fourth region 148b. In the first valve position 166b, the fifth region 150b is fluidically connected to none of the further regions 142b, 144b, 146b, 148b. In the first valve position 166b, the first region 142b and the second region 144b are fluidically separate from the further regions 146b, 148b, 150b. In the first valve position 166b, the third region 146b and the fourth region 148b are fluidically separate from the further regions 142b, 144b, 150b.
In the second valve position 168b, the first region 142b is fluidically connected to the fourth region 148b. In the second valve position 168b, the second region 144b is fluidically connected to the third region 146b. In the second valve position 168b, the fifth region 150b is fluidically connected to none of the further regions 142b, 144b, 146b, 148b. In the second valve position 168b, the volume of the fifth region 150b is larger than in the first valve position 166b. In the second valve position 168b, the first region 142b and the fourth region 148b are fluidically separate from the further regions 144b, 146b, 150b. In the second valve position 168b, the second region 144b and the third region 146b are fluidically separate from the further regions 142b, 148b, 150b.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 134 609.6 | Dec 2021 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2022/086736 | 12/19/2022 | WO |
