CN115593505A - Overflow shut-off valve, steering device, steering gear, steering system and vehicle - Google Patents

Abstract

The application provides an overflow trip valve, turns to device, steering gear, a steering system and vehicle. The overflow cut-off valve comprises a shell, a first oil inlet, a second oil inlet, a first oil outlet, a second oil outlet, a control oil port and an oil drainage port, wherein the shell is provided with the first oil inlet, the second oil inlet, the first oil outlet, the second oil outlet, the control oil port and the oil drainage port; the valve core is arranged in the shell and provided with a communication position and a disconnection position, when the pressure of oil flowing into the control oil port is smaller than a preset pressure value, the valve core is in the communication position, the first oil inlet is communicated with the first oil outlet, the second oil inlet is communicated with the second oil outlet, and the control oil port is disconnected with the oil drainage port; when the pressure of the oil flowing into the control oil port is larger than a preset pressure value, the valve core is located at a disconnection position, the first oil inlet is disconnected with the first oil outlet, the second oil inlet is disconnected with the second oil outlet, and the control oil port is communicated with the oil drainage port. The application provides an overflow trip valve can realize overflow function and function of opening a circuit.

Description

Overflow shutoff valve, steering device, steering gear, steering system and vehicle

Technical Field

The embodiment of the application relates to an overflow cut-off valve, a steering device, a steering gear, a steering system and a vehicle.

Background

Valves (also known as valves) are used as control elements in hydraulic systems to perform functions such as opening and closing lines, controlling flow direction, and regulating parameters of the transport medium. There are a large variety of valves, and different valves often have different functions in order to meet various control requirements in a hydraulic system.

Disclosure of Invention

In a first aspect of the present application, an overflow shutoff valve for a hydraulic system is provided. This overflow trip valve includes: the oil pump comprises a shell, a first oil inlet, a second oil inlet, a first oil outlet, a second oil outlet, a control oil port and an oil drainage port, wherein the shell is provided with the first oil inlet, the second oil inlet, the first oil outlet, the second oil outlet, the control oil port and the oil drainage port; the valve core is arranged in the shell and provided with a communication position and a disconnection position, when the pressure of oil flowing into the control oil port is smaller than a preset pressure value, the valve core is located at the communication position, the first oil inlet is communicated with the first oil outlet, the second oil inlet is communicated with the second oil outlet, and the control oil port is disconnected with the oil drainage port; when the pressure of oil flowing into the control oil port is larger than the preset pressure value, the valve core is located at the disconnection position, the first oil inlet is disconnected with the first oil outlet, the second oil inlet is disconnected with the second oil outlet, and the control oil port is communicated with the oil drainage port.

With reference to the first aspect, in some embodiments, a surface of the valve element is provided with a groove, wherein when the valve element is in the communication position, the groove is communicated with the control oil port and is not communicated with the oil drain port; when the valve core is in the off position, the groove enables the control oil port to be communicated with the oil drainage port.

With reference to the first aspect, in some embodiments, the valve element includes a large-diameter portion and a small-diameter portion, and the groove is disposed between the large-diameter portion and the small-diameter portion, so that an oil pressure acting area at a first side end of the groove connected to the small-diameter portion is smaller than an oil pressure acting area at a second side end of the groove connected to the large-diameter portion, so that when a pressure of oil flowing from the control oil port is greater than the preset pressure value, a difference between oil pressures applied to the first side end and the second side end moves the valve element from the communication position to the disconnection position.

With reference to the first aspect, in some embodiments, the inner wall of the casing includes a first section of inner wall, a second section of inner wall, and a third section of inner wall that are sequentially connected and have sequentially increasing inner diameters; the shell is also provided with a first oil way and a second oil way, one end of the first oil way extends to the control oil port, and the other end of the first oil way extends to the inner wall of the second section to form a first opening; one end of the second oil path extends to the oil drainage port, and the other end of the second oil path extends to the inner wall of the third section to form a second opening; the small diameter part is arranged in and guided by the first section inner wall, and when the valve core is at the communication position, the large diameter part is in contact with the second section inner wall; when the valve core is at the disconnection position, the large-diameter part is separated from the second section inner wall so that the first opening and the second opening are communicated through the groove.

In combination with the first aspect, in some embodiments, the first oil passage includes at least three oil passages that are narrowed in sequence from the control oil port to the first opening, and/or the second oil passage includes at least three oil passages that are narrowed in sequence from the oil drain port to the second opening.

With reference to the first aspect, in some embodiments, a spring cavity is disposed in the housing, the spring cavity is located at one end of the valve core close to the inner wall of the third section, a spring is disposed in the spring cavity, and the spring is configured to keep the valve core at the communication position when the pressure of the oil flowing from the control oil port is smaller than the preset pressure value, where the spring cavity is communicated with the oil drain port through the second opening.

In combination with the first aspect, in some embodiments, the side surface at the first side end is a flat surface, and the side surface at the second side end is a tapered surface.

In combination with the first aspect, in some embodiments, the small diameter portion is provided with a first contact portion, a first ring groove, a second contact portion, a second ring groove and a third contact portion in sequence from the groove, wherein when the valve spool is in the communication position, the first oil inlet and the first oil outlet are communicated through the first ring groove, the second oil inlet and the second oil outlet are communicated through the second ring groove, and the first oil inlet and the first oil outlet are isolated from the second oil inlet and the second oil outlet through the second contact portion; when the valve core is located at the disconnection position, the first oil inlet and the first oil outlet are blocked by the second contact part, and the second oil inlet and the second oil outlet are blocked by the third contact part.

With reference to the first aspect, in some embodiments, a passage with an orifice is provided inside the spool to communicate the pressures of the spring chamber and the closing chamber on both axial sides of the spool.

With reference to the first aspect, in some embodiments, the preset pressure value is greater than a maximum allowable working pressure of the hydraulic system.

In a second aspect of the present application, a steering system is provided. This a steering system includes hydraulic pump, steering gear, flow amplification valve and steering cylinder, the flow amplification valve includes priority valve and switching-over valve, wherein works as when the steering gear moves, some fluid of hydraulic pump output passes through in proper order the priority valve with the switching-over valve flows in the steering cylinder, another part fluid warp the steering gear reachs the both ends of the case of switching-over valve, in order to control the warp the switching-over valve flows in the flow and the flow direction of the fluid of steering cylinder, steering system still includes as the first aspect of this application the overflow trip valve, the overflow trip valve sets up the steering gear with between the switching-over valve.

With reference to the second aspect, in some embodiments, the steering cylinder includes a first working chamber and a second working chamber, the flow amplifying valve includes a shuttle valve, a first oil inlet of the shuttle valve is communicated with the first working chamber, a second oil inlet of the shuttle valve is communicated with the second working chamber, and an oil outlet of the shuttle valve is communicated with a control oil port of the overflow shutoff valve and a control oil port of the priority valve.

In a third aspect of the present application, a steering gear for a hydraulic system is provided. The steering gear comprises: the steering gear comprises a steering gear shell, wherein an oil inlet, a first working oil port, a second working oil port and an oil return port are formed in the outer wall of the steering gear shell; the overflow cut-off valve comprises a shell of the overflow cut-off valve, a control oil port of the overflow cut-off valve is integrally formed in the shell of the steering gear, an oil drain port of the overflow cut-off valve is communicated with an oil return port, the steering gear is provided with a first working oil path and a second working oil path, the first working oil path extends to the first working oil port from the inside of the steering gear and passes through a first oil inlet and a first oil outlet of the overflow cut-off valve, and the second working oil path extends to the second working oil port from the inside of the steering gear and passes through a second oil inlet and a second oil outlet of the overflow cut-off valve.

In a fourth aspect of the present application, a steering apparatus for a hydraulic system is provided. The steering device includes: the steering gear is provided with an oil inlet, a first working oil port, a second working oil port and an oil return port; and the overflow cut-off valve according to the first aspect, wherein the overflow cut-off valve is connected to the steering gear, a first oil inlet of the overflow cut-off valve is connected to a first working oil port of the steering gear, and a second oil inlet of the overflow cut-off valve is connected to a second working oil port of the steering gear.

With reference to the fourth aspect, in some embodiments, the overflow cut-off valve is a plate and is directly fixed to the steering gear from the outside, the casing of the overflow cut-off valve is further provided with an oil inlet through hole and an oil return through hole which are directly communicated with an oil inlet and an oil return port of the steering gear, and an oil drain port of the overflow cut-off valve is communicated with the oil return through hole.

With reference to the fourth aspect, in some embodiments, the overflow shutoff valve is tubular and is connected to the diverter by a hydraulic line.

In a fifth aspect of the present application, a steering system is provided. The steering system comprises a steering gear according to the third aspect or comprises a steering device according to the fourth aspect.

In a sixth aspect of the present application, a vehicle is provided. The vehicle comprises an overflow shut-off valve as described in the first aspect of the present application, or comprises a steering system as described in the second aspect of the present application, or comprises a steering gear as described in the third aspect of the present application, or comprises a steering device as described in the fourth aspect of the present application, or comprises a steering system as described in the fifth aspect of the present application.

The overflow trip valve of this application embodiment can be when the pressure of the fluid of inflow control hydraulic fluid port is greater than the predetermined pressure value, will control the hydraulic fluid port and communicate to the draining port to realize the overflow function, and break off the intercommunication between first oil inlet and the first oil-out and the intercommunication between second oil inlet and the second oil-out simultaneously, in order to realize the oil circuit cutting-off function.

Drawings

To facilitate understanding of the invention, the present application is described in more detail below on the basis of exemplary embodiments and with reference to the attached drawings. The same or similar reference numbers in the drawings may identify the same or similar elements. It should be understood that the drawings are merely schematic and that the sizes and proportions of elements in the drawings are not necessarily precise.

FIG. 1 shows a schematic of the construction of an overflow shutoff valve according to some embodiments of the present application.

FIG. 2 shows a cross-sectional view of the spill shutoff valve of FIG. 1 with the valve spool in the open position.

Fig. 3 shows a cross-sectional view of the spill shutoff valve of fig. 1 with the valve spool in the shutoff position.

Fig. 4 shows a schematic view of the valve body of the overflow shutoff valve shown in fig. 1.

FIG. 5 shows a cross-sectional view of the housing of the overflow shutoff valve shown in FIG. 1.

FIG. 6 shows another cross-sectional view of the spill shutoff valve of FIG. 1 with the valve spool in the communication position.

Fig. 7 shows another cross-sectional view of the spill shutoff valve of fig. 1 with the valve spool in the shutoff position.

FIG. 8 shows a schematic of the construction of an overflow shutoff valve according to other embodiments of the present application.

Fig. 9 shows a schematic view of the overflow shutoff valve of fig. 8 in another view.

Fig. 10 shows a cross-sectional view of the spill shutoff valve of fig. 8 with the valve spool in the communication position.

Fig. 11 shows a cross-sectional view of the spill shutoff valve of fig. 8 with the valve spool in the shutoff position.

Fig. 12 shows a cross-sectional view of the housing of the overflow shutoff valve shown in fig. 8.

FIG. 13 shows another cross-sectional view of the housing of the overflow shutoff valve shown in FIG. 8.

Fig. 14 shows another cross-sectional view of the housing of the overflow shutoff valve of fig. 8.

FIG. 15 illustrates a schematic structural view of a steering apparatus according to some embodiments of the present application.

FIG. 16 illustrates a schematic structural diagram of a steering apparatus according to further embodiments of the present application.

FIG. 17 illustrates a schematic structural view of a diverter according to some embodiments of the present application.

FIG. 18 shows a cross-sectional view of the diverter of FIG. 17 with the spool of the spill shutoff valve in the open position.

FIG. 19 shows a cross-sectional view of the diverter of FIG. 17 with the spool of the spill shutoff valve in the shutoff position.

FIG. 20 shows a cross-sectional view of the housing of the diverter shown in FIG. 17.

Fig. 21 shows another cross-sectional view of the housing of the diverter shown in fig. 17.

FIG. 22 illustrates a hydraulic schematic of a steering system according to some embodiments of the present application.

FIG. 23 illustrates a hydraulic schematic of a steering system according to further embodiments of the present application.

FIG. 24 illustrates a hydraulic schematic of a steering system according to further embodiments of the present application.

Detailed Description

Exemplary Overflow shut-off valve

The embodiment of the application provides an overflow cut-off valve which can be applied to a hydraulic system to provide an overflow function and a circuit breaking function. The overflow shutoff valve of the embodiment of the present application will be described below by way of example with reference to the accompanying drawings.

FIG. 1 shows a schematic of the construction of an overflow shutoff valve 10 according to some embodiments of the present application.

Referring to fig. 1, the overflow shutoff valve 10 includes a housing 11. The housing 11 is provided with a first oil inlet 111, a first oil outlet 112, a second oil inlet 113, a second oil outlet 114, a control oil port 115, and an oil drain port 116.

Fig. 2 and 3 show the internal structure of the overflow shutoff valve 10 shown in fig. 1.

Referring to fig. 1-3, the spill shut-off valve 10 may further include a valve spool 12, the valve spool 12 being disposed within the housing 11. The spool 12 is movable by oil flowing into the control port 115 to switch between a plurality of operating positions. The operating position of the spool 12 may include a connected position and a disconnected position. In fig. 2, the spool 12 is in the communication position. In fig. 3, the spool 12 is in the open position.

When the pressure of the oil flowing into the control port 115 is less than the preset pressure value, the spool 12 is maintained at the communication position. At this time, the first oil inlet 111 is communicated with the first oil outlet 112, the second oil inlet 113 is communicated with the second oil outlet 114, and the control oil port 115 is disconnected (i.e., not communicated) with the oil drainage port 116.

When the pressure of the oil flowing into the control oil port 115 is greater than a preset pressure value, the spool 12 is switched to the off position. At this time, the first oil inlet 111 and the first oil outlet 112 are disconnected, the second oil inlet 113 and the second oil outlet 114 are disconnected, and the control oil port 115 and the oil drain port 116 are communicated.

In this way, the overflow trip valve of this application embodiment can control the hydraulic fluid port and communicate to the draining port when the pressure of the fluid of inflow control hydraulic fluid port is greater than preset pressure value to realize the overflow function, and break off the intercommunication between first oil inlet and the first oil-out and the intercommunication between second oil inlet and the second oil-out simultaneously, in order to realize the oil circuit cut-off function.

It should be understood that, for the preset pressure value, the embodiment of the present application is not particularly limited, and those skilled in the art may set the preset pressure value according to actual requirements.

For example, in some embodiments, the preset pressure value may be set to be greater than the maximum allowable operating pressure of the hydraulic system in which the spill shut-off valve is located. Therefore, when the pressure of the hydraulic system is lower than the maximum allowable working pressure, the hydraulic system can normally operate, and when the pressure of the hydraulic system is higher than the maximum allowable working pressure, the overflow cut-off valve can cut off the oil circuit and carry out overflow protection.

Fig. 4 shows a schematic view of the valve body 12 of the overflow shutoff valve 10 shown in fig. 1.

In some embodiments, referring to fig. 1-4, the surface of the spool 12 may be provided with a groove 121. When the spool 12 is in the communication position, the groove 121 is in communication with the control port 115 and is not in communication with the drain port 116. The groove 121 communicates the control port 115 with the drain port 116 when the spool 12 is in the open position.

Specifically, a first oil passage 131 and a second oil passage 132 may be provided in the housing 11. One end of the first oil passage 131 may extend to the control oil port 115, and the other end may extend to an inner wall of the housing 11 to form the first opening 141. One end of the second oil passage 132 may extend to the oil drain port 116, and the other end may extend to an inner wall of the housing 11 to form a second opening 142.

As shown in fig. 2, when the spool 12 is in the communication position, the groove 121 and the inner wall around the first opening 141 form a relatively sealed cavity (hereinafter referred to as a control cavity). The second opening 142 is isolated from the control chamber. At this time, the control oil port 115 is communicated with the groove 121 through the first opening 141, and the oil release port 116 is not communicated with the groove 121, so that the control oil port 115 is not communicated with the oil release port 116.

As shown in fig. 3, when the spool 12 moves to the open position, the control chamber is turned from closed to open, so that the first opening 141 and the second opening 142 are communicated through the groove 121, and the control oil port 115 is communicated with the drain oil port 116.

Through the mode, the oil port and the oil drainage port are not communicated when the valve core is in the communication position, and the oil port and the oil drainage port are communicated when the valve core is in the disconnection position.

In some embodiments, referring to fig. 4, the spool 12 may include a large diameter portion 122 and a small diameter portion 123. The groove 121 may be disposed between the large diameter portion 122 and the small diameter portion 123.

Radial dimension d of large diameter portion 122 ₁ May be larger than the radial dimension d of the small diameter portion 123 ₂ Thus, an oil hydraulic pressure acting area at a side end (hereinafter referred to as a first side end) of the groove 121 connected to the small diameter portion 123 is smaller than an oil hydraulic pressure acting area at a side end (hereinafter referred to as a second side end) of the groove 121 connected to the large diameter portion 122.

Or, due to the radial dimension d of the small diameter portion 123 ₂ Smaller than the radial dimension d of the large diameter portion 122 ₁ Therefore, the area of the orthographic projection of the first side end in the axial direction of the spool 12 is smaller than the area of the orthographic projection of the second side end in the axial direction of the spool 12.

Based on this, when the spool 12 is in the communication position, see fig. 2, the oil hydraulic pressure received at the first side end is smaller than the oil hydraulic pressure received at the second side end in the axial direction of the spool 12.

When the pressure of the oil flowing into the control oil port 115 is greater than the preset pressure value, the difference between the oil pressures received at the first and second lateral ends drives the spool 12 to move in the direction from the small diameter portion 123 to the large diameter portion 122, so that the spool 12 moves from the communication position shown in fig. 2 to the disconnection position shown in fig. 3.

In this way, when the pressure of the oil flowing into the control oil port is greater than the preset pressure value, the valve core can be switched from the communication position to the disconnection position.

The implementation mode has better use effect. Particularly, utilize the pressure differential of first side and second side to drive the valve core, the drive power that the valve core received is less, and the removal of valve core is comparatively mitigateed to can avoid the valve core to strike other structures, reduce the noise when the valve core switches, reduce the possibility that the overflow trip valve damaged, improve the life of overflow trip valve.

Fig. 5 shows a sectional view of the housing 11 of the overflow shutoff valve 10 shown in fig. 1.

In some embodiments, referring to fig. 1-5, the inner wall of the housing 11 of the overflow shutoff valve 10 may include a first section 143, a second section 144, and a third section 143, which are connected in series and have successively larger inner diameters145. That is, the radial dimension D of the first section inner wall 143 ₁ Is smaller than the radial dimension D of the second section inner wall 144 ₂ Radial dimension D of second segment inner wall 144 ₂ Is less than the radial dimension D of the third segment inner wall 145 ₃ . The first opening 141 may be provided on the second section inner wall 144. The second opening 142 may be provided on the third-section inner wall 145.

The small diameter portion 123 of the spool 12 may be guided by the first-stage inner wall 143. Alternatively, the small diameter portion 123 of the spool 12 may be in contact engagement with the first-stage inner wall 143.

When the spool 12 is in the communication position, as shown in fig. 2, the small diameter portion 123 of the spool 12 is in contact engagement with the first section inner wall 143, and the large diameter portion 122 is in contact engagement with the second section inner wall 144, whereby the groove 121 is in engagement with the inner wall of the housing 11 to form a control chamber. At this time, the control oil port 115 is communicated with the control cavity through the first opening 141 opened on the second section inner wall 144.

When the pressure of the oil flowing into the control oil port 115 is greater than the preset pressure value, the spool 12 moves in the direction from the first-stage inner wall 143 to the second-stage inner wall 144 by the pressure difference received at the first and second lateral ends of the groove 121.

When the spool 12 moves to the off position, as shown in fig. 3, the small diameter portion 123 of the spool 12 still contacts and engages with the first section inner wall 143, the large diameter portion 122 separates from the second section inner wall 144 and enters the third section inner wall 145, and the control cavity is opened from the closed state. At this time, the second opening 142 opened on the third-stage inner wall 145 communicates with the first opening 141 through the groove 121, thereby controlling the oil port 115 to communicate with the oil release port 116.

Through setting up consecutive and the internal diameter increases in proper order the inner wall and be located the recess between major diameter portion and the minor diameter portion for the case can be greater than when presetting the pressure value at the pressure of the fluid of the inflow control hydraulic fluid port, surely removes to the disconnection position from the intercommunication position, and will control hydraulic fluid port and draining port and switch to the intercommunication by the disconnection.

In some embodiments, referring to fig. 5, the first oil path 131 may include three oil paths 131a,131b,131c narrowed in sequence from the control oil port 115 to the first opening 141. In other words, the inner diameters of the three sections of oil passages 131a,131b and 131c decrease in sequence, that is, the inner diameter of the oil passage 131a is larger than that of the oil passage 131b, and the inner diameter of the oil passage 131b is larger than that of the oil passage 131c. The oil passage 131c may serve as a damping function as a narrowest oil passage.

Similarly, the second oil passage 132 may include three- stage oil passages 132a,132b,132c that narrow in order from the drain port 116 to the second opening 142. In other words, the inner diameters of the three oil passages 132a,132b and 132c decrease in sequence, that is, the inner diameter of the oil passage 132a is larger than that of the oil passage 132b, and the inner diameter of the oil passage 132b is larger than that of the oil passage 132c. The oil passage 132c may serve as a damping function as a narrowest section of the oil passage.

It should be understood that although in this embodiment, the first oil passage 131 includes only three- stage oil passages 131a,131b,131c. However, in other embodiments of the present application, the first oil path 131 may also include more oil paths that are narrowed in sequence, for example, four oil paths that are narrowed in sequence, or five oil paths that are narrowed in sequence, wherein the narrowest oil path may play a role in damping.

Similarly, in other embodiments of the present application, the second oil path 132 may also include more oil paths that are narrowed in sequence, wherein the narrowest oil path may play a role in damping.

By the mode, the moving speed of the valve core during position switching can be reduced, so that the response speed of the overflow cut-off valve is controlled, and the difficulty in position switching of the valve core caused by overlarge hydraulic power is prevented.

In some embodiments, referring to fig. 2 and 3, the overflow shutoff valve 10 may also include a spring 151. The spring 151 may be provided at one end of the spool 12 near the large diameter portion 122. Further, in certain embodiments, the overflow shutoff valve 10 may also include a spring seat 152. One end of the spring 151 may be installed in the spring seat 152, and the other end may abut against an end surface of the valve element 12.

When the pressure of the oil flowing into the control oil port 115 is less than the preset pressure value, as shown in fig. 2, the pressing force applied by the spring 151 maintains the spool 12 at the communication position.

When the pressure of the oil flowing into the control oil port 115 is greater than the preset pressure value, as shown in fig. 3, the difference between the pressures received at the first and second lateral ends of the groove 121 is greater than the pressing force provided by the spring 151, the spring 151 is compressed, and the spool 12 moves from the connected position to the disconnected position.

In this way, when the pressure of the oil flowing into the control oil port is smaller than the preset pressure value, the valve core can be kept at the communication position. In addition, this realization drives the valve core through the pressure differential of recess both sides end and removes, and drive power is less and comparatively soft, consequently can adopt less spring to can reduce the cost of overflow trip valve, reduce the volume of overflow trip valve, alleviate the weight of overflow trip valve. Simultaneously, because drive power is less and comparatively soft, the spring is not fragile to can prolong the life of overflow trip valve.

In some embodiments, referring to fig. 2 and 3, the position of the spring seat 152 may be adjustable. The degree of compression of the spring 151 can be adjusted by adjusting the position of the spring seat 152, thereby adjusting the pressing force that the spring 151 exerts on the spool 12. As one implementation, the spring seat 152 may be threadably engaged with the housing 11 such that its position may be adjusted by rotating the spring seat 152.

In this way, the user can set the pressure value (i.e., the preset pressure value) required for switching the overflow shutoff valve from the communication position to the shutoff position by adjusting the position of the spring seat.

In some embodiments, referring to fig. 2 and 3, a spring cavity 161 may be disposed within the housing 11 of the overflow shutoff valve 10 and the spring 151 may be disposed in the spring cavity 161. The spring chamber 161 may communicate with the drain port 116 through the second opening 142. As one implementation, the spring chamber 161 may be collectively defined by the spring seat 152, an end surface of the spool 12 facing the spring seat 152, and a portion of the inner wall of the housing 11 (the third-stage inner wall 145).

The spring cavity is communicated with the oil drainage port, so that a closed space can be prevented from being formed in the spring cavity. When the spool moves from the on position to the off position, the space within the spring chamber is compressed. At this time, if a closed space is formed in the spring cavity, the oil infiltrated into the spring cavity cannot be smoothly removed, which may cause the valve element to be stuck, thereby causing a failure.

In some embodiments, referring to fig. 2-4, surface 1211 at a first lateral end of groove 121 may be planar and surface 1212 at a second lateral end may be tapered.

The surface at the second side end is a conical surface, so that oil can smoothly flow out of the groove, and sharp noise can be avoided.

Fig. 6 and 7 show the internal structure of the overflow shutoff valve 10 from another angle. In fig. 6, the spool 12 is in a communication state. In fig. 7, the spool 12 is in the off position.

In some embodiments, referring to fig. 4 to 7, the small diameter portion 123 of the spool 12 is provided with a first contact portion 124, a first ring groove 125, a second contact portion 126, a second ring groove 127, and a third contact portion 128 in this order from the groove 121. The first section of the inner wall 143 of the housing 11 may be provided with a third opening 146, a fourth opening 147, a fifth opening 148 and a sixth opening 149.

As shown in fig. 6, when the valve spool 12 is located at the communication position, the third opening 146 and the fourth opening 147 face the first ring groove 125, the first oil inlet 111 communicates with the first ring groove 125 through the third opening 146, and the first oil outlet 112 communicates with the first ring groove 125 through the fourth opening 147, so that the first oil inlet 111 communicates with the first oil outlet 112 through the first ring groove 125.

Meanwhile, the fifth opening 148 and the sixth opening 149 face the second ring groove 127, the second oil inlet 113 communicates with the second ring groove 127 through the fifth opening 148, and the second oil outlet 114 communicates with the second ring groove 127 through the sixth opening 149, so that the second oil inlet 113 communicates with the second oil outlet 114 through the second ring groove 127.

Meanwhile, the third and fourth openings 146 and 147 are isolated from the fifth and sixth openings 148 and 149 by the second contact portion 126. Therefore, both the first oil inlet 111 and the first oil outlet 112 are isolated from both the second oil inlet 113 and the second oil outlet 114 by the second contact portion 126.

As shown in fig. 7, when the valve spool 12 is located at the open position, the third opening 146 and the fourth opening 147 face the second contact portion 126, and the second contact portion 126 blocks the third opening 146 and the fourth opening 147, so that the first oil inlet 111 and the first oil outlet 112 are blocked by the second contact portion 126 and no communication therebetween is established.

Meanwhile, the fifth opening 148 and the sixth opening 149 face the third contact portion 128, and the second contact portion 128 blocks the fifth opening 148 and the sixth opening 149, so that the second oil inlet 113 and the second oil outlet 114 are blocked by the second contact portion 126 and no communication is established therebetween.

Further, as shown in fig. 6 and 7, the first contact portion 124 isolates the groove 121 from the first ring groove 125 to prevent the control oil passage 115 from communicating with the first oil inlet 111 and the first oil outlet 112 regardless of whether the spool 12 is in the communication position or the disconnection position.

By the mode, the first oil inlet and the first oil outlet can be communicated when the valve core is at the communication position, the second oil inlet and the second oil outlet can be communicated, and the first oil inlet and the first oil outlet are disconnected and the second oil inlet and the second oil outlet are disconnected when the valve core is at the disconnection position.

In some embodiments, referring to fig. 2-4, the interior of the spool 12 is also provided with a passage 129. The passage 129 may extend through the spool 12 from one end surface to the other end surface of the spool 12. The spring chamber 161 and the closing chamber 162 located on both axial sides of the spool 12 may be pressure-communicated through the passage 129.

Thus, when the valve core moves, the oil in the spring cavity and the closed cavity can be communicated with the oil drainage port through the second opening, so that faults such as clamping stagnation of the valve core can be avoided.

In some embodiments, referring again to fig. 4, passage 129 may be provided with an orifice 1291 to provide appropriate damping as oil flows through passage 129.

Because of the existence of the throttling port, the oil cannot flow through the passage quickly, thereby reducing the moving speed of the valve core and avoiding the valve core from violently impacting other structures.

In some embodiments, referring to FIG. 1, the spill shut-off valve 10 may be in the form of a pipe for connection to other hydraulic devices in the hydraulic system via a hydraulic line. As an implementation, the housing 11 of the overflow shutoff valve 10 may include a first tubular portion 11a and a second tubular portion 11b. A first oil inlet 111 and a first oil outlet 112 may be provided at both ends of the first tubular portion 11a, respectively. A second oil inlet 113 and a second oil outlet 114 may be respectively provided at both ends of the second tubular portion 11b. When installed, the first tubular part 11a and the second tubular part 11b may be connected in series to two hydraulic lines of a hydraulic system, respectively, so as to connect the overflow shutoff valve 10 to other devices through the hydraulic lines.

Through setting up the overflow trip valve into the tubular for it can be through hydraulic line connection to hydraulic system in, thereby richened the mounting means of overflow trip valve, make the installation of overflow trip valve more nimble.

Fig. 8 and 9 illustrate an overflow shutoff valve 20 according to other embodiments of the present application. Fig. 10 and 11 show the internal structure of the overflow shutoff valve 20. In fig. 10, the spool of the relief cut valve 20 is in the communication position. In fig. 11, the spool of the spill shutoff valve 20 is in the open position. Fig. 12 to 14 show a plurality of cross-sectional views of the housing 21 of the overflow shutoff valve 20.

The overflow shutoff valve 20 has many elements (e.g., a first oil inlet, a first oil outlet, a control oil port, an oil drain port, a spool, etc.) substantially identical to the overflow shutoff valve 10. The description of these elements in the overflow shutoff valve 10 applies equally to the overflow shutoff valve 20 without conflict. For the sake of brevity, the same reference numerals are used for these elements (i.e., the reference numerals in the foregoing embodiments are used), and the corresponding descriptions are appropriately omitted.

In some embodiments, referring to fig. 8-14, the spill shut-off valve 20 may be of the plate type for direct mounting on other hydraulic devices in the hydraulic system. As one implementation, the housing 21 of the overflow shutoff valve 20 may be plate-shaped and have opposing first and second end faces 21a, 21b. The first and second oil inlets 111 and 113 may be provided on the first end surface 21a, and the first and second oil outlets 112 and 114 may be provided on the second end surface 21b. In addition, the housing 21 may be further provided with an oil inlet through hole 211 and an oil return through hole 212. The oil inlet through hole 211 and the oil return through hole 212 may extend from the first end face 21a to the second end face 21b, penetrating the housing 21. The drain port 116 may communicate with the oil return through hole 212. As one implementation, as shown in fig. 14, the oil drain 116 may be opened on an inner wall of the oil return through hole 212.

Through setting up the overflow trip valve to the board-like for it can the direct mount on other hydraulic means, thereby richened the mounting means of overflow trip valve, make the installation of overflow trip valve more nimble.

In some embodiments, referring again to fig. 8-14, the housing 21 of the overflow shutoff valve 20 may also be provided with at least one mounting through hole 213. The mounting through-hole 213 may extend from the first end surface 21a to the second end surface 21b of the housing 21, penetrating the housing 21.

During installation, a bolt can be penetrated into the installation through hole and then is in threaded connection with a threaded hole in the hydraulic device, so that the overflow stop valve is directly fixed on the hydraulic device.

Exemplary steering device

Work vehicles, such as loaders or mine cars, typically employ a steering system that includes a steering gear and a flow amplifying valve, which may be referred to as a flow amplifying steering system.

The driver can drive the steering gear to operate by rotating the steering wheel. The steering gear is used as a pilot valve in a steering system, and the output oil controls the flow direction and flow of the oil flowing into the steering oil cylinder through the flow amplifying valve by controlling the working state of the flow amplifying valve, so that the steering operation is realized in a mode of controlling large flow with small flow.

However, conventional flow amplifying steering systems lack extreme position feedback. After the steering cylinder reaches the extreme position, the driver can still continue to rotate the steering wheel in the direction of the extreme position. Since it is impossible to sense whether the steering cylinder has reached the limit position, the driver may always turn the steering wheel, so that the steering system is in a high pressure state. This not only results in wasted energy, but also damages the steering system, e.g. reducing the service life of the seals.

In view of the above, embodiments of the present application provide a steering apparatus suitable for a steering system to solve the above problems. The diverting means may comprise a diverter and an overflow shutoff valve as in the above embodiments. The following describes a steering device according to an embodiment of the present application, with reference to the drawings.

FIG. 15 illustrates a steering device 40 according to some embodiments of the present application.

Referring to fig. 15, the diverter means 40 may include a diverter 30 and an overflow shutoff valve 10.

The steering gear 30 may be provided with a first working oil port 311, a second working oil port 312, an oil inlet 313 and an oil return port 314. The first working oil port 311 of the steering gear 30 may be connected to the first oil inlet 111 of the overflow cut-off valve 10, and the second working oil port 312 of the steering gear 30 may be connected to the second oil inlet 113 of the overflow cut-off valve 10.

When the overflow shutoff valve 10 is applied to a steering system, the control oil port 115 of the overflow shutoff valve 10 may be communicated with an oil inlet chamber (i.e., a working chamber into which oil flows) of a steering cylinder of the steering system. When the steering cylinder reaches the limit position, the oil pressure in the oil inlet chamber rises sharply. At this time, the pressure of the oil flowing into the control oil port 115 exceeds a preset pressure value, and the spool of the spill shutoff valve 10 is switched from the on position to the off position. At this time, the oil cannot flow into or out of the steering gear 30 from the first and second working ports 311 and 312, and the driver cannot continue to rotate the steering wheel, thereby knowing that the steering cylinder has reached the limit position. Meanwhile, the control oil port 115 of the overflow cut-off valve 10 is communicated with the oil drain port 116, and oil overflows through the oil drain port 116, so that the steering system is subjected to overflow protection.

Therefore, when the steering device is applied to the steering system, the steering system can be prevented from being in a high-pressure state for a long time, so that the energy consumption of the system is reduced, and the possibility of system damage is reduced.

In some embodiments, referring again to FIG. 15, the overflow shutoff valve 10 may be in the form of a tube and connected to the diverter 30 by hydraulic lines 41, 42. The related description of the tubular overflow shutoff valve can be referred to the previous embodiment, and the description is omitted.

For example, one end of the hydraulic line 41 may be connected to the first oil inlet 111 of the overflow shutoff valve 10, and the other end may be connected to the first working oil port 311 of the steering gear 30. Similarly, one end of the hydraulic line 42 may be connected to the second oil inlet 113 of the overflow shutoff valve 10, and the other end may be connected to the second working oil port 312 of the steering gear 30.

Adopt tubular overflow trip valve to link to each other it with the steering gear through hydraulic line, can make the installation of overflow trip valve more nimble, thereby satisfy installation space's demand better.

FIG. 16 illustrates a steering device 50 according to further embodiments of the present application, which is an exploded schematic view of the steering device 50. The steering device 50 is substantially the same as the steering device 40, and for the sake of brevity, the same elements are denoted by the same reference numerals, and duplicate description is appropriately omitted.

In some embodiments, referring to FIG. 16, the diverter device 50 may include a diverter 30 and an overflow shutoff valve 20. The overflow shutoff valve 20 may be of the plate type and is directly fixed to the diverter 30. For the description of the plate-type overflow shutoff valve, reference may be made to the foregoing embodiments, and the description thereof is omitted.

A first oil inlet of the overflow cut-off valve 20 may be directly connected to the first working oil port 311 of the steering gear 40, and a second oil inlet of the overflow cut-off valve 20 may be directly connected to the second working oil port 312 of the steering gear 40. Meanwhile, the oil inlet through hole 211 of the overflow cut-off valve 20 may be directly connected to the oil inlet 313 of the steering gear 30, and the oil return through hole 212 of the overflow cut-off valve 20 may be directly connected to the oil return port 314 of the steering gear.

For example, the steering gear 30 may be provided with a fitting end surface 31a, and the first working oil port 311, the second working oil port 312, the oil inlet 313 and the oil return port 314 of the steering gear 30 may be opened on the fitting end surface 31 a. A first end surface (i.e., an end surface opposite to the second end surface 21b in the drawing) of the overflow shut-off valve 20 may contact the fitting end surface 31a of the steering gear 30, so that the first oil inlet, the second oil inlet, the oil inlet through hole 211, and the oil return through hole 212 of the overflow shut-off valve 20 are directly connected to the first working oil port 311, the second working oil port 312, the oil inlet 313, and the oil return port 314 of the steering gear 30, respectively.

When the overflow cut-off valve 20 is applied to a steering system, the oil inlet through hole 211 of the overflow cut-off valve 20 can be connected to a hydraulic pump of the steering system, and the oil return through hole 212 can be connected to a hydraulic oil tank of the steering system. Oil output by the hydraulic pump can flow into the steering gear 30 from the oil inlet 313 of the steering gear 30 through the oil inlet through hole 211 of the overflow cut-off valve 20. The oil output by the steering gear 30 and the oil output by the oil discharge port of the overflow cut-off valve 20 when the overflow cut-off valve 20 is in the off position can flow back to the hydraulic oil tank through the oil return through hole 212.

Adopt board-like overflow trip valve to with board-like overflow trip valve direct mount on the steering gear, can satisfy installation space's demand better.

In some embodiments, referring again to fig. 16, the steering device 50 may further include at least one bolt 51. The diverter 30 may also be provided with at least one threaded hole 315. Bolts 51 may be passed through mounting holes 213 in the overflow shutoff valve 20 and engage threaded holes 315 in the diverter 30 to secure the overflow shutoff valve 20 to the diverter 30.

Exemplary steering gear

The embodiment of the application also provides a steering gear. The diverter may include the overflow shutoff valve of the above-described embodiments. The steering gear according to the embodiment of the present application will be described below by way of example with reference to the accompanying drawings.

FIG. 17 illustrates a diverter 60 according to some embodiments of the present application. Fig. 18 and 19 show the internal structure of the diverter 60. In fig. 18, the spool 12 of the relief shutoff valve is in the communication position. In fig. 19, the spool 12 of the relief shutoff valve is in the shutoff position. Fig. 20 and 21 show various cross-sectional views of the diverter housing 61 of the diverter 60.

For the sake of brevity, in the diverter 60, elements related to the overflow shutoff valve are denoted by reference numerals in the above-described embodiment, and the corresponding description is appropriately omitted. The description of these elements in the above embodiments also applies to the diverter 60 without conflict.

Referring to fig. 17-21, the diverter 60 may include a diverter housing 61. A first working oil port 611, a second working oil port 612, an oil inlet 613 and an oil return port 614 are provided on an outer wall of the steering housing 61.

The diverter 60 may also include any of the spill shutoff valves of the embodiments described above. The housing of the overflow shutoff valve may be integrally formed by the diverter housing 61. Alternatively, the overflow shutoff valve can be integrated into the steering housing 61.

A control oil port 115 of the overflow shutoff valve may be provided on an outer wall of the steering gear housing 61. The spill port 116 of the spill shutoff valve may be in communication with the return port 614. As one implementation, as shown in fig. 20, the steering housing 61 may be provided with an oil return passage 614a extending from the oil return port 614 to the inside of the steering 60, and the drain port 116 may be provided on an inner wall of the oil return passage 614 a.

The steering gear 60 may be provided with a first working oil passage and a second working oil passage. The first working oil passage extends from the inside of the steering gear 60 to the first working oil port 611, and passes through the first oil inlet and the first oil outlet of the overflow cut-off valve. The second working oil path extends from the inside of the steering gear 60 to the second working oil port 612, and passes through the second oil inlet and the second oil outlet of the overflow cut-off valve.

Specifically, as shown in fig. 21, the steering housing 61 may be provided with a first accommodation space 61a and a second accommodation space 61b. The steering valve sleeve and the steering valve core of the steering 60 may be accommodated in the first accommodation space 61 a. The spool 12 of the relief shutoff valve may be housed in the second housing space 61b.

As shown in fig. 17 and 21, a seventh opening 621 and an eighth opening 622 may be provided on an inner wall of the first receiving space 61 a. The first working oil passage may extend from the seventh opening 621 to the first working oil port 611 through the third and fourth openings 146 and 147 in order. The second hydraulic fluid passage may extend from the eighth opening 622 to the second hydraulic fluid port 612 through the fifth and sixth openings 148 and 149 in order.

It should be noted that, since the housing of the overflow cut-off valve is integrally formed by the steering housing 61, the first oil inlet, the first oil outlet, the second oil inlet, and the second oil outlet of the overflow cut-off valve are located inside the steering housing 61. For example, on the first working oil path, any point between the seventh opening 621 and the third opening 146 may be regarded as a first oil inlet of the overflow cut-off valve, and any point between the fourth opening 147 and the first working oil port 611 may be regarded as a first oil outlet of the overflow cut-off valve. Similarly, in the second working oil path, any point between the eighth opening 622 and the fifth opening 148 can be regarded as a second oil inlet of the overflow cut-off valve, and any point between the sixth opening 149 and the second working oil port 612 can be regarded as a second oil inlet and outlet of the overflow cut-off valve.

When the control oil port 115 is applied to a steering system, the control oil port may be communicated with an oil inlet chamber (i.e., a working chamber into which oil flows) of a steering cylinder of the steering system. When the steering cylinder reaches the limit position, the pressure of the oil in the oil inlet cavity is increased sharply. At this time, the pressure of the oil flowing into the control oil port 115 exceeds a preset pressure value, and the spool 12 of the relief cut valve is switched from the on position to the off position.

When the valve core 12 of the overflow cut-off valve moves to the cut-off position, the first oil inlet and the first oil outlet of the overflow cut-off valve are cut off, and the first working oil path is cut off. Meanwhile, a second oil inlet and a second oil outlet of the overflow cut-off valve are disconnected, and a second working oil way is cut off. At this time, the oil cannot flow into or out of the steering gear 60 through the first and second working oil ports 611 and 612, and the driver cannot continue to rotate the steering wheel, thereby knowing that the steering cylinder has reached the limit position. Meanwhile, after the valve core of the overflow cut-off valve is switched to the off position, the control oil port 115 is communicated with the oil drainage port 116, and because the oil drainage port 116 is communicated with the oil return port 614, oil can flow back to the hydraulic oil tank through the oil return port 614, so that the steering system is subjected to overflow protection.

Compared with a traditional steering device, the steering device provided by the embodiment of the application has the overflow function and the cut-off function, so that limit feedback can be provided for a driver when the steering oil cylinder reaches a limit position, and meanwhile, the steering system is subjected to overflow protection.

In this way, the steering system can be prevented from being in a high-pressure state for a long time, so that the energy consumption of the system is reduced, and the possibility of system damage is reduced.

In addition, compare in mutually independent overflow trip valve and steering gear, the steering gear structure of this application embodiment is compacter to can save installation space, optimize steering system's arrangement.

Exemplary steering System

Embodiments of the present application also provide a steering system, which may include the overflow shutoff valve, the steering device, or the steering gear in the above embodiments. The following describes a steering system according to an embodiment of the present application with reference to the drawings.

FIG. 22 illustrates a hydraulic schematic of a steering system 1000 according to some embodiments of the present application.

Referring to fig. 22, the steering system 1000 may include a hydraulic pump 1100, a steering gear 1200, a flow amplifying valve 1300, and a steering cylinder 1400. Further, in some embodiments, steering system 1000 may also include a hydraulic reservoir 1110.

The steering gear 1200 may be provided with an oil inlet 1201, an oil return port 1202, a first working oil port 1203, and a second working oil port 1204. The oil inlet 1201 of the steering gear 1200 may be connected to the hydraulic pump 1100, and the oil return 1202 may be connected to the hydraulic oil tank 1110. According to the direction in which the driver rotates the steering wheel, one of the oil inlet 1201 and the oil return port 1202 of the steering gear 1200 may be communicated with the first working oil port 1203, and the other may be communicated with the second working oil port 1204.

The flow amplifying valve 1300 may include a priority valve 1310 and a directional valve 1320. In addition, the flow amplifying valve 1300 may have an oil inlet 1301, an oil return 1302, a first working port 1303, a second working port 1304, a first control port 1305, and a second control port 1306.

An oil inlet 1301 and an oil return 1302 of the flow amplifying valve 1300 may be connected to the hydraulic pump 1100 and the hydraulic oil tank 1110, respectively, a first working oil port 1303 and a second working oil port 1304 may be connected to the first working chamber 1410 and the second working chamber 1420 of the steering cylinder 1400, respectively, and a first control oil port 1305 and a second control oil port 1306 may be connected to the first working oil port 1203 and the second working oil port 1204 of the steering gear 1200, respectively.

When the steering gear 1200 is operated, that is, when a driver turns a steering wheel, a portion of the oil output from the hydraulic pump 1100 may sequentially flow into the steering cylinder 1400 through the priority valve 1310 and the direction change valve 1320, and another portion of the oil may reach both ends of the spool of the direction change valve 1320 through the steering gear 1200, so as to control the flow rate and the direction of the oil flowing into the steering cylinder 1400 through the direction change valve 1320.

For example, when a driver rotates a steering wheel in a first direction, the oil inlet 1201 of the steering gear 1200 is communicated with the first working oil port 1203, and the oil return port 1202 is communicated with the second working oil port 1204, so that oil output by the hydraulic pump 1100 can sequentially pass through the oil inlet 1201 of the steering gear 1200 and the first working oil port 1203 to reach two ends of a spool of the reversing valve 1320 from the first control oil port 1305 of the flow amplifying valve 1300 and flow out from the second control oil port 1306. After exiting the second control port 1306, the oil may flow back to the hydraulic reservoir 1110 via the second working port 1204 and the return port 1202 of the steering gear 1200, in that order. Since the direction change valve 1320 is provided with the orifice 1320a, a pressure difference is formed across the spool of the direction change valve 1320, thereby pushing the spool to move to the left in the drawing. At this time, the oil inlet 1301 of the flow amplifying valve is communicated with the first working oil port 1303, the oil return port 1302 is communicated with the second working oil port 1304, the oil output from the hydraulic pump 1100 sequentially flows into the first working chamber 1410 of the steering cylinder 1400 through the priority valve 1310 and the reversing valve 1320, the oil in the second working chamber 1420 sequentially flows back to the hydraulic oil tank 1110 through the second working oil port 1304 and the oil return port 1302 of the flow amplifying valve 1300, and the rod of the steering cylinder 1400 moves to the right side in the drawing.

When a driver stops rotating the steering wheel, the oil inlet 1201 and the first working oil port 1203 of the steering gear 1200 are disconnected, the oil return port 1202 and the second working oil port 1204 are disconnected, the pressure difference between two ends of the valve core of the reversing valve 1320 is eliminated, and the valve core returns to the middle position in the drawing. At this time, the oil inlet 1301 and the first working oil port 1303 of the flow amplifying valve 1300 are disconnected, the oil return port 1302 and the second working oil port 1304 are disconnected, and the oil in the steering cylinder 1400 maintains the position of the cylinder rod.

When the driver rotates the steering gear 1200 in a second direction (a direction opposite to the first direction), the oil inlet 1201 of the steering gear 1200 communicates with the second working oil port 1204, the oil return port 1202 communicates with the first working oil port 1203, and the oil output from the hydraulic pump 1100 passes through the steering gear 1200, reaches both ends of the spool of the selector valve 1320 from the second control oil port 1306 of the flow amplifying valve 1300, and flows back to the hydraulic oil tank 1110 from the first control oil port 1305 through the steering gear 1200. At this time, the differential pressure between the two ends of the spool of the reversing valve 1320 moves the spool to the right position in the drawing, the oil inlet 1301 of the flow amplifying valve is communicated with the second working oil port 1304, the oil return port 1302 is communicated with the first working oil port 1303, the oil output by the hydraulic pump 1100 flows into the second working chamber 1420 of the steering cylinder 1400 through the priority valve 1310 and the reversing valve 1320 in sequence, the oil in the first working chamber 1410 flows back to the hydraulic oil tank 1110 through the first working oil port 1303 and the oil return port 1302 of the flow amplifying valve 1300 in sequence, and the rod of the steering cylinder 1400 moves to the left side in the drawing.

Steering system 1000 can also include an overflow shutoff valve 1500. The overflow shutoff valve 1500 may be any of the overflow shutoff valves of the embodiments described above. The overflow shutoff valve 1500 may be disposed between the diverter 1200 and the diverter valve 1320 of the flow amplifying valve 1300. Alternatively, the overflow shutoff valve 1500 may be connected in series in the oil path between the steering gear 1200 and the diverter valve 1320 of the flow amplifying valve 1300.

Specifically, the overflow shutoff valve 1500 may have a first oil inlet 1501 (111), a first oil outlet 1502 (112), a second oil inlet 1503 (113), a second oil outlet 1504 (114), a control oil port 1505 (115), and an oil return 1506 (116). The first oil inlet 1501 may be connected to a first working port 1203 of the steering gear 1200, the second oil inlet 1503 may be connected to a second working port 1204 of the steering gear 1200, the first oil outlet 1502 may be connected to a first control port 1305 of the flow amplifying valve 1300, the second oil outlet 1504 may be connected to a second control port 1306 of the flow amplifying valve 1300, a control port 1505 may be connected to an oil inlet chamber of the steering cylinder 1400 (i.e., a working chamber into which oil in the first working chamber 1410 and the second working chamber 1420 flows), and the oil return 1506 may be connected to the hydraulic tank 1110.

As the driver turns the steering wheel in a certain direction, the cylinder rod of the steering cylinder 1400 moves in a certain direction. After the rod of the steering cylinder 1400 moves to the extreme position, the pressure of the oil in the oil inlet chamber of the steering cylinder 1400 increases continuously. Since the control port 1505 of the spill cut valve 1500 is communicated with the oil inlet chamber of the steering cylinder 1400, the pressure of the oil flowing into the control port 1505 is also continuously increased. After the pressure of the oil flowing into the control oil port 1505 is greater than the preset pressure value, the spill shut valve 1500 is switched from the on position to the off position (i.e., from the right position to the left position in the drawing). At this time, the first oil inlet 1501 and the first oil outlet 1502 of the overflow shutoff valve 1500 are disconnected, and the second oil inlet 1503 and the second oil outlet 1504 are disconnected. Therefore, the first working oil port 1203 and the second working oil port 1204 of the steering gear 1200 are blocked, and a driver cannot rotate the steering wheel, so that the driver can know that the steering cylinder 1400 reaches the limit position. Meanwhile, the control oil port 1505 is communicated with the oil return port 1506, and oil can flow back to the hydraulic oil tank 1110 from the oil return port 1506, so that overflow protection is realized.

Conventional flow amplifying steering systems lack extreme position feedback. After the steering oil cylinder reaches the extreme position, the driver can still continue to rotate the steering wheel in the direction of the extreme position. Because the steering oil cylinder can not be sensed to reach the limit position, a driver can always rotate the steering wheel, so that the steering system is in a high-pressure state. This not only results in lost energy, but also damages the steering system.

In the steering system of this application embodiment, after the steering cylinder reachd extreme position, the oil circuit between the switching-over valve of overflow trip valve cutting-off steering gear and flow amplification valve, the driver knows that the steering cylinder reachd extreme position, no longer continues to rotate the steering wheel, and meanwhile, the oil feed chamber of steering cylinder communicates to hydraulic tank with the overflow trip valve to realize the overflow protection.

In this way, the steering system can be prevented from being continuously in a high-pressure state, so that the energy consumption is reduced, the possibility of damage to the steering system is reduced, and the service life of the steering system is prolonged.

In addition, because the overflow cut-off valve has the overflow function, the overflow valve for performing overflow protection on the oil inlet cavity of the steering oil cylinder is not required to be independently arranged, so that the cost is reduced, and the space occupation of a steering system is reduced.

In some embodiments, referring again to fig. 22, the flow amplifying valve 1300 may further include a shuttle valve 1330. The shuttle valve 1330 may be provided with a first oil inlet 1330a, a second oil inlet 1330b, and an oil outlet 1330c. The shuttle valve 1330 may have a first oil inlet 1330a communicating with the first working chamber 1410 of the steering cylinder 1400, a second oil inlet 1330b communicating with the second working chamber 1420 of the steering cylinder 1400, and an oil outlet 1330c communicating with the control oil port 1505 of the overflow shut-off valve 1500.

By the mode, the oil inlet cavity of the steering oil cylinder can be communicated to the control oil port of the overflow cut-off valve.

In some embodiments, referring again to fig. 22, the control port 1310a of the priority valve 1310 may also be connected to the oil outlet 1330c of the shuttle valve 1330.

So configured, when the oil output from the hydraulic pump 1100 can flow into the steering cylinder 1400 through the direction switching valve 1320 (for example, when the direction switching valve 1320 is at the left position or the right position in the drawing), the priority valve 1310 is switched to the left position in the drawing, so that the oil output from the hydraulic pump 1100 can be preferentially delivered to the steering cylinder 1400, thereby ensuring effective completion of the steering action. When the oil outputted from the hydraulic pump 1100 cannot flow into the steering cylinder 1400 through the direction switching valve 1320 (for example, when the direction switching valve 1320 is in the neutral position in the drawing), the priority valve 1310 is switched to the right position in fig. 22, so that the oil outputted from the hydraulic pump 1100 is preferentially supplied to other hydraulic systems except the steering system 1000 through the output port 1307 of the flow amplifying valve 1300.

In this way, the steering system can be effectively prevented from being in a high-pressure overflow state for a long time, and therefore energy consumption of the system is greatly reduced.

In some embodiments, referring again to fig. 22, steering system 1100 may also be provided with a relief valve 1120. Relief valve 1120 may be provided on an oil path between hydraulic pump 1100 and hydraulic tank 1110 to perform relief protection of steering pump 1100.

FIG. 23 illustrates a hydraulic schematic of a steering system 2000 in accordance with further embodiments of the present application. Steering system 2000 is substantially identical to steering system 1000. For brevity, the same parts will not be described again.

Referring to fig. 23, a steering system 2000 may include a steering apparatus 2100. The steering device 2100 may be any of the steering devices described in the above embodiments.

For example, an oil inlet 2201 (313) and an oil return 2202 (314) of the steering gear 2200 of the steering apparatus 2100 may be connected to the hydraulic pump 1100 and the hydraulic oil tank 1110, respectively. The first oil outlet 2502 (112) and the second oil outlet 2504 (114) of the overflow shutoff valve 2500 of the steering apparatus 2100 may be connected to the first control oil port 1305 and the second control oil port 1306 of the flow amplifying valve 1300, respectively. The control oil port 2505 (115) of the overflow cut-off valve 2500 may be connected to an oil inlet chamber of the steering cylinder 1400, and the drain oil port 2506 (116) may be connected to the hydraulic oil tank 1110.

FIG. 24 illustrates a hydraulic schematic of a steering system 3000 according to further embodiments of the present application. Steering system 3000 is substantially identical to steering system 1000. For brevity, the same parts will not be described again.

Referring to fig. 24, steering system 3000 may include a steering gear 3100. The diverter 3100 may be the diverter provided in the above-described embodiments of the present application.

For example, an oil inlet 3101 (613) and an oil return 3102 (614) of the diverter 3100 may be connected to the steering pump 1100 and the hydraulic tank 1110, respectively, and a first working port 3103 (611) and a second working port 3104 (612) may be connected to the first control port 1305 and the second control port 1306, respectively, of the flow amplifying valve 1300. A control oil port 3105 (115) of an overflow shutoff valve of the steering gear 3100 may be connected to an oil inlet chamber of the steering cylinder 1400.

Further, other embodiments of the present application also provide a vehicle that may include the spill shut-off valve, the steering device, the diverter, or the steering system of the above embodiments. The vehicle provided by the embodiment of the application can be, but is not limited to, a loader, an excavator, a mine car or the like.

In the above embodiments of the present application, the steering gear may be a hydraulic steering gear, or a hydraulic power steering gear, or a full hydraulic steering gear. The embodiments of the present application are not particularly limited with respect to the type of diverter in the above-described embodiments. For example, the diverter in the above embodiment may be a BZZ1 type diverter, i.e., an open-core non-reactive diverter. As another example, the diverter in the above-described embodiment may be a BZZ2 type diverter, i.e., an open-core, reaction type diverter. As another example, the diverter in the above-described embodiment may be a BZZ3 type diverter, i.e., a closed-core, non-reactive type diverter.

It should be understood that the above embodiments are only some of the embodiments of the present application, and not all of the embodiments. The embodiments of the present application should not be construed as limited thereto. For example, although in the above-described embodiment, the relief cut-off valve holds the valve element in the communication position by a spring, in other embodiments of the present application, the relief cut-off valve may hold the valve element in the communication position by an electromagnetic device or a pilot-controlled device. For another example, although the housing of the overflow shutoff valve is tubular or plate-shaped in the above-described embodiments, the housing of the overflow shutoff valve may have other shapes in other embodiments of the present application. As another example, although in the above described embodiments the overflow shutoff valve, the steering device and the steering gear are applied in a steering system, it is clear that in other embodiments of the present application they may also be applied in other hydraulic systems.

It should be understood that although the terms "first" or "second," etc. may be used herein to describe various elements (e.g., oil inlet, oil outlet, opening, and oil passage, etc.), these elements should not be limited by these terms, which are used only to distinguish one element from another.

It should be understood that in the embodiment of the application, the oil inlet and the oil outlet of the overflow cut-off valve can be interchanged. For example, oil may flow into the first oil inlet and out the first oil outlet, and oil may also flow into the first oil outlet and out the first oil inlet.

It should be understood that the term "communicate" and variations thereof as used herein may refer to fluid communication and the term "disconnect" and variations thereof may refer to fluid disconnection. For example, "control hydraulic fluid port and draining port intercommunication" can mean "fluid can flow to the draining port from controlling the hydraulic fluid port", and "control hydraulic fluid port and draining port disconnection" can mean "fluid can't flow to the draining port from controlling the hydraulic fluid port".

It is to be understood that, as used herein, the terms "includes," including, "and variations thereof are intended to be open-ended, i.e.," including, but not limited to. The term "according to" is "at least partially according to". The term "one embodiment" means "at least one embodiment"; the term "another embodiment" means "at least one additional embodiment".

The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think of the changes or substitutions within the technical scope of the present application, and shall be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims (18)

1. An overflow shutoff valve for a hydraulic system, comprising:

the oil inlet control device comprises a shell, a first oil inlet, a second oil inlet, a first oil outlet, a second oil outlet, a control oil port and an oil drainage port, wherein the shell is provided with the first oil inlet, the second oil inlet, the first oil outlet, the second oil outlet, the control oil port and the oil drainage port; and

a valve core disposed in the housing and having a communication position and a disconnection position, wherein

When the pressure of oil flowing into the control oil port is smaller than a preset pressure value, the valve core is located at the communication position, the first oil inlet is communicated with the first oil outlet, the second oil inlet is communicated with the second oil outlet, and the control oil port is disconnected with the oil drainage port; when the pressure of oil flowing into the control oil port is larger than the preset pressure value, the valve core is located at the disconnection position, the first oil inlet is disconnected with the first oil outlet, the second oil inlet is disconnected with the second oil outlet, and the control oil port is communicated with the oil drainage port.

2. The overflow shutoff valve of claim 1 wherein a surface of the valve spool is provided with a groove, wherein

When the valve core is in the communication position, the groove is communicated with the control oil port and is not communicated with the oil drainage port; when the valve core is in the off position, the groove enables the control oil port to be communicated with the oil drainage port.

3. The overflow shut-off valve according to claim 2, wherein the spool includes a large diameter portion and a small diameter portion, and the groove is disposed between the large diameter portion and the small diameter portion, so that an acting area of oil pressure at a first side end of the groove connected to the small diameter portion is smaller than an acting area of oil pressure at a second side end of the groove connected to the large diameter portion, so that when the pressure of oil flowing from the control oil port is greater than the preset pressure value, a difference between the oil pressures applied to the first side end and the second side end moves the spool from the communicating position to the disconnecting position.

4. The overflow cutoff valve according to claim 3, wherein the inner wall of the housing comprises a first section of inner wall, a second section of inner wall and a third section of inner wall which are connected in sequence and have sequentially increased inner diameters;

the shell is also provided with a first oil way and a second oil way, one end of the first oil way extends to the control oil port, and the other end of the first oil way extends to the inner wall of the second section to form a first opening; one end of the second oil path extends to the oil drainage port, and the other end of the second oil path extends to the inner wall of the third section to form a second opening;

the small diameter part is arranged in and guided by the first section inner wall, and when the valve core is at the communication position, the large diameter part is in contact with the second section inner wall; when the spool is in the off position, the large diameter portion is separated from the second section inner wall to communicate the first opening and the second opening through the groove.

5. The overflow shutoff valve of claim 4, wherein the first oil passage includes at least three oil passages narrowing in sequence from the control oil port to the first opening, and/or the second oil passage includes at least three oil passages narrowing in sequence from the drain oil port to the second opening.

6. The overflow shutoff valve of claim 4, wherein a spring cavity is disposed in the housing, the spring cavity is located at an end of the valve core close to the inner wall of the third section, a spring is disposed in the spring cavity, and the spring is configured to maintain the valve core at the communication position when the pressure of the oil flowing from the control oil port is smaller than the preset pressure value, wherein the spring cavity is communicated with the oil drainage port through the second opening.

7. The overflow shutoff valve of claim 3 wherein the side surface at the first side end is planar and the side surface at the second side end is tapered.

8. The overflow shutoff valve of claim 3 wherein the small diameter portion is provided with a first contact portion, a first annular groove, a second contact portion, a second annular groove, and a third contact portion in this order from the groove, wherein

When the valve core is located at the communication position, the first oil inlet and the first oil outlet are communicated through the first annular groove, the second oil inlet and the second oil outlet are communicated through the second annular groove, and the first oil inlet and the first oil outlet are isolated from the second oil inlet and the second oil outlet through the second contact part;

when the valve core is located at the disconnection position, the first oil inlet and the first oil outlet are blocked by the second contact part, and the second oil inlet and the second oil outlet are blocked by the third contact part.

9. The excess flow shutoff valve of claim 6 wherein a passageway with an orifice is provided within the spool to communicate the pressure of the spring chamber and the closed chamber on either axial side of the spool.

10. The overflow shutoff valve of claim 1 wherein the preset pressure value is greater than a maximum allowable working pressure of the hydraulic system.

11. A steering system comprising a hydraulic pump, a steering gear, a flow amplifying valve and a steering cylinder, the flow amplifying valve comprising a priority valve and a directional valve, wherein

When the steering gear operates, a part of oil output by the hydraulic pump flows into the steering oil cylinder through the priority valve and the reversing valve in sequence, the other part of oil reaches two ends of a valve core of the reversing valve through the steering gear so as to control the flow and the flow direction of the oil flowing into the steering oil cylinder through the reversing valve,

the steering system further comprising an overflow shutoff valve as claimed in any one of claims 1 to 10 disposed between the steering gear and the reversing valve.

12. The steering system of claim 11, wherein the steering cylinder comprises a first working chamber and a second working chamber, the flow amplification valve comprises a shuttle valve, a first oil inlet of the shuttle valve is communicated with the first working chamber, a second oil inlet of the shuttle valve is communicated with the second working chamber, and an oil outlet of the shuttle valve is communicated with a control oil port of the overflow shutoff valve and a control oil port of the priority valve.

13. A steering gear for a hydraulic system, comprising:

the hydraulic steering gear comprises a steering gear shell, wherein an oil inlet, a first working oil port, a second working oil port and an oil return port are formed in the outer wall of the steering gear shell; and

the overflow shutoff valve of any one of claims 1 to 10, a housing of the overflow shutoff valve being integrally formed by the steering gear housing, a control oil port of the overflow shutoff valve being provided on an outer wall of the steering gear housing, an oil drain port of the overflow shutoff valve being communicated with the oil return port, wherein

The steering gear is provided with a first working oil path and a second working oil path, the first working oil path extends from the inside of the steering gear to the first working oil port and passes through a first oil inlet and a first oil outlet of the overflow cut-off valve, and the second working oil path extends from the inside of the steering gear to the second working oil port and passes through a second oil inlet and a second oil outlet of the overflow cut-off valve.

14. A steering device for a hydraulic system, comprising:

the steering gear is provided with an oil inlet, a first working oil port, a second working oil port and an oil return port; and

an overflow shut off valve as claimed in any one of claims 1 to 10 wherein

The overflow cut-off valve is connected to the steering gear, a first oil inlet of the overflow cut-off valve is connected to a first working oil port of the steering gear, and a second oil inlet of the overflow cut-off valve is connected to a second working oil port of the steering gear.

15. The steering device according to claim 14, wherein the overflow cut-off valve is plate-shaped and is directly fixed to the steering gear from the outside, the housing of the overflow cut-off valve is further provided with an oil inlet through hole and an oil return through hole which are directly communicated with an oil inlet and an oil return port of the steering gear, and an oil discharge port of the overflow cut-off valve is communicated with the oil return through hole.

16. Steering device according to claim 14, characterized in that the overflow shut-off valve is tubular and is connected to the steering gear by means of a hydraulic line.

17. A steering system comprising a steering gear according to claim 13 or comprising a steering arrangement according to any one of claims 14 to 16.

18. A vehicle comprising an overflow shutoff valve as claimed in any of claims 1 to 10, or comprising a steering system as claimed in claim 11, 12 or 17, or comprising a steering gear as claimed in claim 13, or comprising a steering arrangement as claimed in any of claims 14 to 16.

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