Patent Application
20190071118
The present invention relates to a device and a method for maintaining a produced hydraulic pressure and in particular to a hydraulic proportional valve for a steering control and an electrically operated hydraulic power steering.
In various hydrostatic servo drives for steering gear controls there are believed to be two problems which have only been inadequately solved thus far. One involves the maintaining of high pressure loads, such as occur during a continuous loading. A second problem involves the significant steering resistance upon system failure, which drivers must exert in order to steer the vehicle in the case of conventional systems.
The first problem mentioned above comes about if one wheel of the vehicle is blocked during a steering demand (for example, it is pressing against a curb stone) and the motor 51 must maintain the high pressure. The same applies if the vehicle is driving along a long curve, where the pressure needed for this has to be provided constantly by the motor 51. This constitutes an unwanted constant strain on the corresponding pump or the motor. Even if the steering pressure abates, the motor must convert the decreasing pressure for this system. The corresponding power loss during the relaxation process is thus provided by the pump/motor or transformed there into heat. This results in long-lasting permanent strain on the motor or the pump, which impairs the reliability and increases the wear.
The second problem mentioned above arises during a system failure, such as when the pump provides no steering assistance due to a power outage. In this case, the driver must expend additional force, besides the steering force, in order to move the pump 50 and still be able to steer the vehicle.
Hence there is a need for alternative solutions in order to maintain a hydraulic pressure without this placing a strain on the motor or the pressure generator.
The aforementioned technical problem is solved by a device as described herein and a method as described herein. The further embodiments pertain to advantageous modifications of the device as described herein.
The present invention relates to a device which is suitable for maintaining a hydraulic pressure, which can be set by a pressure generator. The device comprises an inlet for coupling to the pressure generator, an outlet for providing the hydraulic pressure, at least a first check valve, which is configured to open a flow path from the inlet to the outlet when a first opening pressure is exceeded and to prevent flow in the opposite direction. Furthermore, the device comprises a switching apparatus between the inlet and the outlet, wherein the switching apparatus is configured to hold the hydraulic pressure at the outlet if a pressure produced by the pressure generator is greater than a switching pressure, and to reduce the hydraulic pressure at the outlet if a pressure produced by the pressure generator is less than the switching pressure, wherein the switching pressure is less than the first opening pressure.
The inlet and the outlet of the device need not be an independent component, but instead can also constitute a connector to a pump or any given branch point along the (hydraulic) flow. The check valve should be interpreted broadly in the context of the present invention and will encompass any device which provides the defined function, i.e., one which enables an opening of the flow path when a minimum pressure is exceeded and prevents an opposite flow. Therefore, check valve may also be configured generally as a check fitting (e.g., a check flap). The defined, predetermined switching pressure merely constitutes a parameter which triggers the switching behavior of the switching apparatus. If the pressure produced is greater than the switching pressure, the switching apparatus is closed, and conversely it will be opened. The switching of the switching apparatus may occur independently of the hydraulic pressure at the outlet (the switching pressure does not depend directly on the pressure at the outlet).
In the context of the present invention the term “coupling” should be interpreted broadly and should encompass any connection by which an energy flow can be transferred (e.g., a fluidic flow of a hydraulic liquid). Furthermore, it is understood that an arrangement of one element A between two other elements B, C does not necessarily mean that element A is physically situated between elements B and C. Instead, it should also encompass arrangements where a hydraulic flow between elements B and C via element A is possible. The connections/couplings may be direct (without intervening elements) or indirect connections/couplings. In the latter case, one or more elements/components may be provided between the components connected.
In further sample embodiments, the switching apparatus comprises a control valve with a displaceable piston. The piston in a first position can open a flow path between the outlet and the inlet and in a second position close the flow path between the outlet and the inlet. The control valve may be configured to shift the piston into the first position if the pressure produced (at the inlet) is less than the switching pressure, and to shift it into the second position if the pressure produced (at the inlet) is greater than the switching pressure. Insofar as the pressure produced is equal to the switching pressure, either the first position or the second position can be taken up.
In further sample embodiments, the control valve has at least a first chamber and a spring. The device may further comprise a first control line, which connects the first chamber fluidically to the inlet, wherein the first control line brings about a pressure equalization between the first chamber and the inlet and the spring brings about a biasing of the piston in the direction of the first position, so that the switching pressure is defined by the spring.
In further sample embodiments, the pressure generator comprises a first pressure connector and a second pressure connector, wherein the inlet is coupled to the first pressure connector. The device may furthermore comprise a further inlet for coupling to the second pressure connector, a further outlet for providing a further hydraulic pressure, and a third check valve. The third check valve is adapted to open a flow path from the further inlet to the further outlet when a third opening pressure is exceeded and to prevent a flow in the opposite direction. The switching apparatus may also connect the further outlet and the further inlet and is adapted to reduce the further hydraulic pressure at the further outlet if a pressure produced by the pressure generator at the further inlet is less than the switching pressure, wherein the switching pressure is less than the third opening pressure.
The switching pressure defined here may also be chosen to be different from the previously defined switching pressure, so that the switching apparatus has asymmetrical behavior, i.e., it may require a higher (or lower) switching pressure for a movement into the first position than for the opposite movement. However, when used in a steering system, it is advisable to select both switching pressures the same.
Thanks to the defined function, the device can be used to relieve the pressure generator yet still maintain the hydraulic pressure at the outlet. The pressure generator only needs to maintain the switching pressure, but this is generally much less than a typical pressure produced by the pressure generator, resulting in the mentioned relieving.
In further sample embodiments, the switching apparatus comprises a second chamber and a further spring. The device furthermore comprises a second control line, which fluidically connects the second chamber to the further inlet. The second control line brings about a further pressure equalization between the second chamber and the further inlet. The further spring brings about a biasing of the piston in the direction of the second position, so that the switching pressure depends on the spring. Thus, the piston can move back and forth between a first opening position (first position) and a second opening position (second position). Furthermore, the piston may have passages which produce the connection between the outlet and the inlet or between the further outlet and the further inlet during the displacement.
In further sample embodiments, the device comprises an optional first throttling device along the first control line to bring about a throttling of the pressure equalization. Furthermore, the device may comprise a second throttling device along the second control line to bring about a throttling of the further pressure equalization. These throttlings bring about a dampening in order to prevent an unwanted excessive oscillation during the movement of the piston.
In further sample embodiments, the device may comprise an optional second check valve, which is configured between the switching apparatus and the inlet in order to make possible a flow from the switching apparatus when a second opening pressure is exceeded and to prevent a flow in the opposite direction, wherein the second opening pressure is greater than the switching pressure. Therefore, the first check valve and the second check valve open only above the pressure at which the piston is already moving in order to prevent the back flow from the outlet or from the further outlet.
Furthermore, the device may comprise a fourth check valve, which is configured between the switching apparatus and the further inlet in order to make possible a flow from the switching apparatus when a fourth opening pressure is exceeded and to prevent a flow in the opposite direction. The fourth opening pressure may be greater than the switching pressure.
In further sample embodiments, the second opening pressure of the second check valve is equal to the first opening pressure of the first check valve. Furthermore, the fourth opening pressure of the fourth check valve may be equal to the third opening pressure of the third check valve.
In further sample embodiments, the pressure generator is further adapted to make possible a back flow through the pressure generator from the one pressure connector when an idling pressure is exceeded at one of its pressure connectors, the switching pressure being chosen greater than the idling pressure. For example, the idling pressure is the pressure required in a currentless state to move the pressure generator passively so that higher pressures can be dissipated.
The present invention also relates to a hydraulic system with a pressure generator for producing a hydraulic pressure at a pressure connector and with one of the previously described devices. The pressure generator may comprise a hydraulic gear pump and the outlet and further outlet of the device may be coupled for example to a steering gear. The hydraulic gear pump may also be operated in reversed directions of running.
The hydraulic system with the device can be both an open hydraulic system and a closed hydraulic system.
The present invention also relates to a power steering with a steering gear and with the hydraulic system. The present invention furthermore relates to a vehicle with the power steering.
The present invention furthermore relates to a method for maintaining a hydraulic pressure which can be set by a pressure generator. The method involves the steps: opening a flow path from the pressure generator to an outlet if a first opening pressure is exceeded, in order to thereby build up the hydraulic pressure at the outlet; preventing a flow in an opposite direction; holding the hydraulic pressure until a pressure produced by the pressure generator is greater than a switching pressure; and reducing the hydraulic pressure if a pressure produced by the pressure generator is less than the switching pressure, wherein the switching pressure is less than the first opening pressure.
The present invention solves the aforementioned technical problem therefore by a switching apparatus (e.g., control valve) for an open or closed hydraulic system, wherein the working spaces of a gear pump, for example, are actuated. After reaching a target pressure—at permanently high system pressure—the gear pump can be largely relieved of pressure. Furthermore, this solution makes it possible to bypass the gear pump in a backup mode, so that the driver does not have to turn the gear pump with the motor in event of a system failure.
The permanently high system pressure can therefore withstand a continuous loading (e.g., during a blocking by a curb stone) without an increased power loss being sustained in the motor or at the pump.
The sample embodiments of the present invention will be better understood from the following detailed description and the accompanying drawings of the different sample embodiments, although these should not be understood to mean a limiting of the disclosure to the specific embodiments, and only serve for explanation and for comprehension.
The sample embodiment shown in
The hydraulic system shown differs from the conventional system of
The pressure generator 50 once again may comprise a gear pump and for example a first and a second pressure connector, to which the device 100 is coupled by its inlet 110 and further inlet 112. The overall system may be a fully encapsulated hydraulic system, so that the inlets 110, 112 and outlets 120, 122 can be defined for example as defined points along the hydraulic flow.
In the sample embodiment shown, the device 100 comprises a first check valve 131, a second check valve 132, a third check valve 133, a fourth check valve 134, the switching apparatus 140 and two throttling devices 151, 152. These components are fluidically situated between the inlet 110, the outlet 120, the further inlet 112 and the further outlet 122. The inlet 110 of the device 100 is coupled to the first pressure connector and the further inlet 112 to the second pressure connector of the pressure generator 50, so that the pressure generator 50 provides a controllable pressure p0 at the inlet 110 and/or at the further inlet 112.
Between the inlet 110 and the outlet 120 is situated the first check valve 131. Between the further inlet 112 and the further outlet 122 is situated the third check valve 133. Furthermore, the switching apparatus 140 connects the outlet 120 to the inlet 110 as well as the further outlet 122 to the further inlet 112, while between the switching apparatus 140 and the inlet 110 is configured the second check valve 132 and between the switching apparatus 140 and the further inlet 112 is configured the fourth check valve 134.
The first check valve 131 provides a flow path from the inlet 110 to the outlet 120 if a pressure is present at the inlet 110 which is above a first opening pressure p1 (and prevents an opposite flow). In the same way, the third check valve 133 provides a flow path from the further inlet 112 to the further outlet 122 if a pressure is present at the further inlet 112 which is above the third opening pressure p3 (and prevents an opposite flow). The second check valve 132 provides a flow path from the switching apparatus 140 to the inlet 110 if a pressure is present from the switching apparatus 140 which is above a second opening pressure p2 (and prevents an opposite flow). The fourth check valve 134 provides a flow path from the switching apparatus 140 to the further inlet 112 if a pressure is present from the switching apparatus 140 which is above a fourth opening pressure p4 (and prevents an opposite flow). The second opening pressure p2 for example may be equal to the first opening pressure p1 (e.g., around 8 bar). Furthermore, the third opening pressure p3 may for example be equal to the fourth opening pressure p4 (e.g., around 8 bar).
The switching apparatus 140 comprises a movable piston 142, a first chamber 141 and a second chamber 145, the first chamber 141 being situated opposite the second chamber 145 in the direction of movement of the movable piston 142. The piston 142 by its displacement changes the available volumes in the chambers 141, 145. Furthermore, the switching apparatus 140 comprises a spring 144 in the second chamber 145 and a further spring 143 in the first chamber 141. The spring 144 exerts a biasing on the displaceable piston 142, which forces the piston 142 into the first chamber 141. Likewise, the further spring 143 exerts a biasing on the piston 142, which forces the piston 142 into the second chamber 145.
The piston 142 in the switching apparatus 140 may in particular be displaced between the following positions: a first opening position, a second opening position and a middle position. In the first opening position, the switching apparatus 140 opens only the flow path from the outlet 120 to the inlet 110. In the second opening position, the switching apparatus 140 opens only the flow path from the further outlet 122 to the further inlet 112 and in the middle position both mentioned flow paths are opened. The first opening position constitutes a first stop position, in which the piston 142 is situated the furthest to the left, while the second opening position constitutes a second stop position, in which the piston 142 is situated the furthest to the right. Furthermore, in the middle position, the outlet 120 can be connected to the further outlet 122 via a channel 148 in the switching apparatus 140. In a further middle position, although the two mentioned flow paths are opened, the outlet 120 is still not connected to the further outlet 122 (this situation is shown for example in
In order for the flow paths to be provided by the switching apparatus 140, the displaceable piston 142 may have for example two depressions/bulges along its circumference, forming two passages. Thus, in the second opening position (displacement to the right in
In order to displace the piston 142, as shown in
Furthermore, the device 100 as shown in
In this way, the movable piston 142 can make possible a fluid flow from the outlet 120 to the inlet 110 and/or from the further outlet 122 to the further inlet 112 in dependence on the pressure relations in the first control line 158 and/or in the second control line 159. These fluid flows, however, are only possible if a pressure prevails along these flow paths which is above the second opening pressure p2 for the second check valve 132 or above the fourth opening pressure p4 of the fourth check valve 134. In the resting phase (middle position), the switching apparatus 140 is thus opened from both the outlet 120 and from the further outlet 122, wherein the two outlets are at the same time joined together via the channel 148.
The first opening position may be achieved, for example, in that the displaceable piston 142 is forced into the first chamber 141 against the spring force of the further spring 143. The second opening position may be adopted, for example, in that the displaceable piston 142 is forced into the second chamber 145 against the spring force of the spring 144. In order to enable a secure middle position, one of the two springs may be stronger, for example, but only act up to an end stop, so that the opposite, weaker spring forces the piston 142 against this end stop from the opposite side and thus secures the middle position for the displaceable piston 142.
In the sample embodiment of
A first throttling device 151 is configured optionally along the first control line 158. Likewise, a second throttling device 152 may be configured along the second control line 159. These throttling devices 151, 152 throttle the pressure equalization and constitute a dampening. They thus prevent a disruptive oscillation of the displaceable piston 142, for example during a pressure venting. Without these throttling devices 151, 152, the pressure might change suddenly and thereby cause an “excessive oscillation” of the piston 142. Especially in the case of hot oil with low viscosity, these oscillations of the piston 142 (valve piston) may occur. In order to effectively suppress such oscillatory behavior, throttling devices 151, 152 are adapted accordingly to the switching pressure pS.
The expansion tank 60 is configured in its size such that it can take up excess oil (hydraulic fluid) when heated by way of the leakage or drain line 62 from the pressure generator. A pressure of 5 bar may prevail here, for example, in the resting state. The two further check valves 70, 80 have for example an opening pressure of 6 bar and serve during active pump operation for draining the leak rates produced by the gear pump to the respective pressureless working cylinder side. In this way, furthermore, a pressure build-up is prevented in the expansion tank 60 and the oil supply of the system is assured.
The functioning of the system shown as an example in
According to sample embodiments, the pressure generator 50 can be relieved of load while maintaining such a target pressure. For this, the pressure generator 50 may be switched off, for example, until a pressure lower than the first opening pressure p1 of the first check valve 131 is established. However, as long as the pressure at the inlet 110 is still greater than the switching pressure pS, the piston 142 will remain at the right end stop (second opening position) and thus prevent a pressure dissipation in the working cylinder 91 of the exemplary steering gear 90, since the flow path between the outlet 120 and the inlet 110 (still) remains closed.
This is especially advantageous if the pressure in the first working cylinder 91 needs to be maintained for a lengthy time (for example, if the steered wheel strikes against a curb stone or also when driving along lengthy curves), so that the steering action continues to be ensured, yet the pressure generator 50 is not under load.
The pressure dissipation at the inlet 110 may occur, for example, by way of leakage rates of the pressure generator 50, wherein this pressure dissipation at the pressure connectors is often slow in its occurrence. In order to speed up the pressure dissipation, for example, the switching pressure pS may be chosen such that it is able to turn the motor or the pump 50 backward solely by the available pressure at the pressure connector and in this way produce a pressure equalization on both sides of the pressure generator 50.
This process may be continued in order to drain the hydraulic fluid, for example, through the pressure generator 50. The dissipated energy of the system pressure will be released in the form of heat in the switching apparatus 140. Only a minimal power loss occurs in this phase at the pressure generator 50 itself and, in particular, at an electric motor for example (not shown).
The device 100 may have a mirror symmetrical design, so that the above described functions (pressure dissipation, load relief) are also carried out for a steering in the opposite direction. Hence, the target pressure in the second working cylinder 92 is likewise maintained upon reaching a target pressure, even if the pressure generator 50 is switched off and the pressure drops at the further inlet 112. However, if the pressure at the further inlet 112 drops below the switching pressure pS, this causes the further spring 143 to move the displaceable piston 142 to the second opening position and thus open a flow path from the further outlet 122 to the inlet 112. This, once again, results in a pressure dissipation at the further outlet 122. But since the pressure at the further inlet 112 is increased in this case, the pressure in the second chamber 145 likewise rises and, when the switching pressure pS is reached, the piston 142 returns to the first opening position. Therefore, the pressure at the further inlet 112 remains constant during this pressure dissipation phase.
All of the previously described functions of the devices can be implemented as further optional steps of the method.
Important aspects of sample embodiments may be summarized as follows.
The exemplary hydraulic gear pump 50 produces the hydraulic pressure for the steering gear 90. At the same time, the position of the piston 142 is controlled by the system pressure, wherein corresponding chambers 141, 145 can be actuated or moved by the two end faces of the piston 142 of the gear pump 50. After reaching a target pressure, the pump pressure can be dissipated, wherein the pressure is maintained at the outlet 120 (or the further outlet 122). When the motor is switched off, the piston 142 returns to its middle position on account of the spring forces 143, 144 and the gear pump 50 is released (backup mode). The channel 148 then connects the outlet 120 to the further outlet 122, so that the working cylinders 91, 92 of the steering gear 90 are likewise interconnected. This has the effect that steering movements now only result in a displacing of the working piston 93 inside the steering gear 90, but are not forced to carry along the pressure generator 50. Instead, the pressure generator 50 can remain in the position of rest. The pressure established at the inlet 110 or at the further inlet 112 during the pressure dissipation phase (e.g., 7 bar) should in any case be higher than the pressure for driving the exemplary gear pump 50 in the currentless state, so that the switching pressure pS automatically causes the pump 50 to move back by itself.
In sample embodiments, the spring 144 has for example a spring force of 10 N and the further spring 143 a force of 20 N, these being only examples. In other sample embodiments, the springs provide other forces. However, it makes sense for the spring force of the further spring 143 to be twice or half as strong as the spring force of the spring 144, so that the corresponding switching pressure pS is the same size for movements of the displaceable piston 142 in both directions (but this is not absolutely necessary).
The control valve (switching apparatus 140) present thus serves at the same time as a backup valve, making possible a release of the pump mechanism 50 in the backup mode (for example, during a power outage). In other sample embodiments, the device together with the hydraulic steering system may constitute a fully encapsulated hydraulic system with integrated control valve 140, which can be used for closed as well as for open hydraulic systems.
Hence, sample embodiments of the present invention for both closed as well as open hydraulic systems make possible a complete relieving of the load on the pump/motor unit after reaching a target pressure. According to sample embodiments, no pump pressure is needed for the attainment and dissipation of the pressure.
Since the pump pressure does not need to be permanently maintained, advantageously the motor power loss of the pump 50 can be reduced (for example, cut in half). Furthermore, practically no power losses need to be provided or absorbed by the motor during the pressure maintaining or during a slow pressure dissipation. The pressure generator 50 serves only for producing the system pressure (until the pressure build-up is completed) and for actuating the switching apparatus 140 by way of the control lines 158, 159, where only a relatively slight pressure is needed (e.g., the switching pressure pS). The relieving of the load on the pressure generator 50 decreases the wear and thereby increases the service life of the pressure generator 50. By contrast with the prior art, the energy during the pressure maintaining or the pressure dissipation is released through the valves, so that the motor is not placed under load. But an energy release through the switching apparatus 140 or the valves is not critical, as compared to the motor, which would be subjected to greater wear under the high load. Since the power loss is absorbed by the switching apparatus or the valves, there is less thermal load placed on the pump or the motor, so that no separate cooling is required. Finally, the hydraulic oil is likewise spared.
For the switching apparatus 140 it is possible to use, for example, a slide valve or also a proportional valve, but not a magnetic valve. A magnetic valve generally cannot provide the defined functions.
Sample embodiments may be used for open hydraulic systems and then afford advantages in particular when a high hydraulic pressure needs to be held constant over a lengthy time (for example in crane equipment, hoisting equipment, gripping equipment, etc.).
A further advantage is that the actuation of the system is entirely hydraulic and no electrical actuation is needed. The pump, for example, may be configured in a closed system so that it works in both directions and depending on which side requires pressure the pressure is built up on the one side and dissipated on the other side. In an open system (see
The features of the invention disclosed in the specification, the claims and the figures may be essential to the implementing of the invention either individually or also in any given combination.
The LIST OF REFERENCE NUMBERS is as follows:
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2016 002 555.7 | Mar 2016 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2017/054116 | 2/23/2017 | WO | 00 |
