A structure and hydraulic valve for balancing hydraulic power

Abstract

The utility model relates to the technical field of hydraulic systems, and discloses a structure for balancing hydraulic power and a hydraulic valve using the structure for balancing hydraulic power. The hydraulic valve includes a structure for balancing hydraulic power, and the structure for balancing hydraulic power includes a valve sleeve and a valve core arranged in the valve sleeve, a valve cavity for fluid flow is arranged in the valve sleeve, the valve core is slidably arranged in the valve cavity to achieve fluid cut-off or conduction, and a wing plate is convexly arranged on the circumference of the valve core or a wing plate is convexly arranged on the inner wall of the valve cavity of the valve sleeve. By convexly arranging a wing plate on the circumference of the valve core or convexly arranging a wing plate on the inner wall of the valve cavity of the valve sleeve, the hydraulic power can be balanced, the influence of the hydraulic power can be reduced, and the flow limit of the hydraulic valve can be improved.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulic systems, in particular to a structure for balancing hydraulic power and a hydraulic valve. Background Art

[0002] A hydraulic valve is a valve structure that can open or close the hydraulic oil circuit. It can be used in hydraulic systems in various fields such as industrial hydraulics, engineering machinery hydraulics, offshore hydraulics, or wind power hydraulics. The hydraulic valve opens or closes the valve port by moving the valve core relative to the valve sleeve, thereby opening or closing the hydraulic oil circuit.

[0003] Existing hydraulic valves have flow limitations, that is, when the flow exceeds a certain value, the hydraulic force on the valve core increases, and if it exceeds the electromagnetic force or the spring force, the hydraulic valve cannot be effectively switched, causing the hydraulic valve to lose its switching performance.

[0004] Therefore, there is an urgent need to provide a structure and a hydraulic valve for balancing the hydraulic force to solve the above problems. Utility Model Content

[0005] One purpose of the utility model is to provide a structure for balancing hydraulic force, which can balance the hydraulic force exerted on the valve core and improve the flow limit of the hydraulic valve.

[0006] Another object of the utility model is to provide a hydraulic valve, which can balance the hydraulic force exerted on the valve core and improve the flow limit of the hydraulic valve by providing the above-mentioned structure for balancing the hydraulic force.

[0007] In order to achieve the above object, the utility model is implemented through the following technical solutions:

[0008] A structure for balancing fluid power comprises a valve sleeve and a valve core arranged in the valve sleeve, wherein the valve sleeve is provided with a valve cavity for fluid flow, the valve core is slidably arranged in the valve cavity to achieve fluid cutoff or conduction, and a wing plate is convexly provided on the circumferential side of the valve core or on the inner wall of the valve cavity of the valve sleeve.

[0009] As an optional solution, a row of oil ports 1 connected to the valve cavity is provided on the side wall of the valve sleeve, and multiple oil ports 1 in the row are arranged at intervals along the circumference of the valve sleeve. The valve core is provided with a wing plate, and the wing plate can seal part of the inner opening of each oil port 1.

[0010] As an optional solution, the valve sleeve is provided with two rows of oil ports 1 respectively connected to the valve cavity, the two rows of oil ports 1 are arranged at intervals along the axial direction of the valve sleeve, and the multiple oil ports 1 in each row are arranged at intervals along the circumferential direction of the valve sleeve, and the wing plate is located between the two rows of oil ports 1 and can cut off the two rows of oil ports 1.

[0011] As an optional solution, the two rows of oil ports are staggered.

[0012] As an optional solution, the side wall of the valve sleeve is further provided with an oil port 2, the valve cavity comprises an inner hole 1, an inner hole 2 and an inner hole 3 which are sequentially connected in the axial direction, the oil port 1 is connected with the inner hole 2, the oil port 2 is connected with the inner hole 3, the valve core is located on the circumferential side of the inner hole 2 and the wing plate is convexly provided, or the circumferential side wall of the inner hole 2 is convexly provided with the wing plate

[0013] The valve core can switch between a first position and a second position. In the first position, the valve core seals the orifice of the inner hole three, and the inner hole one is connected with a row of oil ports one near it; in the second position, the valve core seals the orifice of the inner hole one, and the oil port two is connected with another row of oil ports one near it.

[0014] As an optional solution, the valve sleeve includes a main valve sleeve and a limiting sleeve, the limiting sleeve is detachably connected to the main valve sleeve, and the main valve sleeve and the limiting sleeve together form the valve cavity.

[0015] As an optional scheme, the main valve sleeve is provided with an internal thread at one end close to the limit sleeve, and the limit sleeve is provided with an external thread at one end close to the main valve sleeve. The limit sleeve is inserted into the main valve sleeve and is fastened to the main valve sleeve through the external thread and the internal thread. The inner hole two, the inner hole three, the oil port one and the oil port two are all opened on the main valve sleeve, and the inner hole one is opened in the limit sleeve.

[0016] As an optional scheme, an external thread is provided at one end of the main valve sleeve close to the limit sleeve, and an internal thread is provided at one end of the limit sleeve close to the main valve sleeve. The limit sleeve is sleeved outside the main valve sleeve and is fastened to the main valve sleeve through the internal thread and the external thread. The inner hole one, the inner hole two and the oil port one are all opened on the limit sleeve, and the inner hole three and the oil port two are opened on the main valve sleeve.

[0017] As an optional scheme, the valve core includes a valve stem and a valve core body connected to each other, the aperture of the inner hole two is larger than the aperture of the inner hole three, the valve stem is located in the inner hole three, and the valve core body is located in the inner hole two, and the valve core body can seal the opening of the inner hole three when in the first position and can seal the opening of the inner hole one when in the second position.

[0018] As an optional solution, conical sealing surfaces or arc-shaped sealing surfaces are provided at both axial ends of the valve core body.

[0019] As an optional solution, when the wing plate is convexly arranged on the circumferential side of the valve core located at the second inner hole, the wing plate is guided and matched with the second inner hole; or

[0020] When the wing plate is protrudingly arranged on the circumferential side wall of the second inner hole, the wing plate cooperates with the valve core guide.

[0021] A hydraulic valve comprises the above-mentioned structure for balancing hydraulic force.

[0022] As an optional solution, the hydraulic valve is an electromagnetic reversing valve, and the valve core is a cone valve core or a sliding valve core.

[0023] The beneficial effects of the utility model are:

[0024] The utility model provides a structure for balancing hydraulic force, wherein a valve core is arranged in a valve cavity of a valve sleeve, and the valve core can open or close the valve port of the valve cavity by sliding along the valve cavity, thereby realizing the conduction or cutoff of the fluid. For example, when a wing plate is convexly provided on the circumferential side of the valve core, when the valve core slides from left to right or from right to left to open the valve port, the fluid flows in a certain direction in the valve cavity and generates an impact force on the wing plate, and the impact force is opposite to the direction of the hydraulic force on the valve core, which can offset a part of the hydraulic force, thereby balancing the hydraulic force when the flow rate increases, so as to increase the flow limit of the hydraulic valve. When a wing plate is convexly provided on the circumferential side wall of the valve cavity, the wing plate can avoid excessive hydraulic force due to cross-flow during the sliding and reversing process of the valve core, reducing the influence of the hydraulic force, and thus can also play a certain role in balancing the hydraulic force, so that the flow limit of the hydraulic valve is increased.

[0025] The utility model also provides a hydraulic valve, which can balance the hydraulic force exerted on the valve core and improve the flow limit of the hydraulic valve by arranging the structure for balancing the hydraulic force. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to explain the embodiments of the utility model or the technical solutions in the prior art more clearly and easily, the following is a brief introduction to the drawings required for use in the embodiments or the description of the prior art. The drawings described below are some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0027] Figure 1 It is a structural schematic diagram of the hydraulic valve provided in the first embodiment of the utility model in a power-off state;

[0028] Figure 2 It is a structural schematic diagram of the hydraulic valve provided in the first embodiment of the utility model in the energized state;

[0029] Figure 3 yes Figure 2A partial enlarged view of the middle A;

[0030] Figure 4 It is a structural schematic diagram of the valve core provided in the first embodiment of the utility model;

[0031] Figure 5 It is a structural schematic diagram of the main valve sleeve provided in the first embodiment of the utility model;

[0032] Figure 6 It is a structural schematic diagram of a hydraulic valve provided in Embodiment 2 of the present utility model;

[0033] Figure 7 yes Figure 6 A partial enlarged view of point B in the middle.

[0034] In the figure:

[0035] 10. Valve sleeve; 11. Main valve sleeve; 111. Oil port 1; 112. Oil port 2; 113. Inner hole 2; 114. Inner hole 3; 12. Limit sleeve; 121. Inner hole 1;

[0036] 20. valve core; 21. valve stem; 22. valve core body; 221. wing plate; 222. conical sealing surface;

[0037] 30. Magnetic sleeve; 40. Copper welding ring; 50. Moving iron; 60. Push rod; 70. Spring; 80. Spring seat. DETAILED DESCRIPTION

[0038] The present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the present invention. It should also be noted that, for ease of description, only the parts related to the present invention, rather than all structures, are shown in the accompanying drawings.

[0039] In the description of the present invention, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0040] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0041] In the description of this embodiment, the terms "upper", "lower", "left", "right" and other directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplified operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

[0042] Embodiment 1

[0043] This embodiment provides a structure for balancing hydraulic force and a hydraulic valve, wherein the hydraulic valve includes the structure for balancing hydraulic force. The hydraulic valve may be a solenoid reversing valve, a one-way valve, a pressure reducing valve or other hydraulic valve structure, which is not specifically limited here.

[0044] Among them, Figure 1 As shown, the structure of balancing the hydraulic force mainly includes a valve sleeve 10 and a valve core 20 arranged in the valve sleeve 10. The valve sleeve 10 is provided with a valve cavity for fluid flow. The valve core 20 is slidably arranged in the valve cavity to achieve fluid cut-off or conduction. The wing plate 221 is convexly provided on the circumference of the valve core 20. The wing plate 221 and the valve core 20 are an integrally formed structure. The valve core 20 can open or close the valve port of the valve cavity by sliding along the valve cavity, thereby achieving fluid conduction or cut-off. When the valve core 20 slides from left to right or from right to left to open the valve port, the fluid flows in the valve cavity in a certain direction and generates an impact force on the wing plate 221. The impact force is opposite to the direction of the hydraulic force on the valve core 20, which can offset a part of the hydraulic force, thereby balancing the hydraulic force when the flow rate increases, so as to increase the flow limit of the hydraulic valve.

[0045] In an optional embodiment, if Figure 3 and Figure 5As shown, the valve sleeve 10 is provided with two rows of oil ports 111 respectively connected to the valve cavity, the two rows of oil ports 111 are arranged at intervals along the axial direction of the valve sleeve 10, and the multiple oil ports 111 in each row are arranged at intervals along the circumferential direction of the valve sleeve 10, and the wing plate 221 is located between the two rows of oil ports 111 and can cut off the two rows of oil ports 111, thereby cutting off the valve cavity located on both sides of the wing plate 221. For ease of understanding, the right row of oil ports 111 is defined as oil port 111a, and the left row of oil ports 111 is defined as oil port 111b. When the valve core 20 is switched to Figure 1 When the valve core 20 is in the position shown, the end of the valve core 20 is used to close the valve port of the left valve cavity. At this time, the oil port 111a is connected to the valve cavity on the right, and the oil port 111b is cut off from the valve cavity on the left. Figure 2 and Figure 3 When the position is shown, the end of the valve core 20 is used to close the valve port of the right valve cavity, at which time the oil port 111b is connected to the left valve cavity, and the oil port 111a is cut off from the valve cavity on the right. In this way, during the reversal of the valve core 20, the wing plate 221 can cut off the oil ports 111a and 111b, thereby cutting off the valve cavities on the left and right sides of the wing plate 221, so that the oil flowing into the right valve cavity can only flow out through the oil port 111a, and the oil flowing into the left valve cavity can only flow out through the oil port 111b, thereby avoiding excessive hydraulic force due to the cross-flow between the valve cavities on both sides during the reversal of the valve core 20, and reducing the influence of the hydraulic force. Through experiments, it is verified that the wing plate 221 cooperates with the two rows of oil ports 111 on the valve sleeve 10 to increase the flow limit to more than 40L / min, and the flow rate can be greatly increased.

[0046] For ease of understanding, the hydraulic valve being an electromagnetic reversing valve is taken as an example, and the working principle of the above-mentioned structure for balancing the hydraulic force is described in detail in combination with the working process of the electromagnetic reversing valve.

[0047] Specifically, Figure 1 and Figure 2 As shown, the electromagnetic reversing valve includes the valve sleeve 10 and the valve core 20 mentioned above, and the electromagnetic reversing valve also includes a magnetic sleeve 30, which is threadedly connected to one end of the valve sleeve 10, and a movable moving iron 50 is arranged in the magnetic sleeve 30, and the moving iron 50 abuts against the valve core 20 through the push rod 60. A brazing ring 40 is embedded on the circumference of the magnetic sleeve 30, which can play a magnetic isolation role. The electromagnetic reversing valve also includes a spring 70 and a spring seat 80, and the spring seat 80 is fixedly connected to one end of the valve core 20 close to the push rod 60. The spring 70 is sleeved on the valve core 20, and one end of the spring 70 abuts against the spring seat 80, and the other end abuts against the valve sleeve 10.

[0048] Among them, Figure 3As shown, the side wall of the valve sleeve 10 is provided with an oil port 111 and an oil port 2 112, and the valve cavity of the valve sleeve 10 includes an inner hole 121, an inner hole 2 113 and an inner hole 3 114 which are sequentially connected in the axial direction, that is, the inner hole 2 113 is connected between the inner hole 121 and the inner hole 3 114, the oil port 111 is connected to the inner hole 2 113, and the oil port 2 112 is connected to the inner hole 3 114; the valve core 20 can switch between the first position and the second position, as shown in FIG. Figure 1 As shown, in the first position, the valve core 20 seals the opening of the inner hole 114, and the oil port 111 is connected to the inner hole 121; Figure 2 As shown, in the second position, the valve core 20 seals the orifice of the inner hole 121, and the oil port 2 112 is connected to the oil port 1 111. Among them, the end where the inner hole 3 114 is connected to the inner hole 2 113 is the orifice of the inner hole 3 114, that is, the valve port of the left valve cavity, and the end where the inner hole 121 is connected to the inner hole 2 113 is the orifice of the inner hole 121, that is, the valve port of the right valve cavity.

[0049] like Figure 1 As shown, when the coil (not shown) of the electromagnetic reversing valve is not energized, the valve core 20 is pushed to move leftward under the action of the spring 70, so that the valve core 20 switches to the first position. At this time, the valve core 20 seals the orifice of the inner hole 3 114 and opens the orifice of the inner hole 1 121, so that the oil port 1 111 and the oil port 2 112 are cut off, and the oil port 1 111 is connected with the inner hole 1 121. Figure 1 In the direction of the arrows, the oil flows to the oil port 111 through the inner hole 121 and the inner hole 2 113 in sequence; Figure 2 and Figure 3 As shown, when the coil is energized, the moving iron 50 and the magnetic sleeve 30 are magnetized and attract each other, and the moving iron 50 pushes the valve core 20 to overcome the elastic force of the spring 70 and move to the right through the push rod 60, so that the valve core 20 switches to the second position. At this time, the valve core 20 seals the orifice of the inner hole 121 and opens the orifice of the inner hole 3 114, so that the oil port 111 and the inner hole 121 are cut off, and the oil port 111 is connected with the oil port 2 112, as shown in FIG. Figure 2 and Figure 3 In the direction of the arrow, the oil flows to the oil port 1 111 through the oil port 2 112, the inner hole 3 114 and the inner hole 2 113 in sequence, thereby realizing the switching of the oil circuit.

[0050] It is understandable that when the valve core 20 opens the corresponding orifice, the hydraulic oil will generate a force on the valve core 20 during the flow process, that is, the hydraulic force. According to the principles of fluid mechanics, the direction of the hydraulic force on the valve core 20 is to close the orifice. Figure 1When the valve core 20 switches to the first position to open the orifice of the inner hole 121, the hydraulic oil flows from right to left through the inner hole 121 to the oil port 111. At this time, the hydraulic force applied to the valve core 20 is to the right, that is, the valve core 20 tends to close the inner hole 121. At this time, the valve core 20 maintains a balanced state. When the flow rate exceeds a certain value, the hydraulic force applied to the valve core 20 increases. If it exceeds the electromagnetic force or the spring force, the electromagnetic valve cannot be effectively switched, thereby prompting the valve core 20 to close the orifice of the inner hole 121, resulting in the valve core 20 being unable to switch to the first position. Similarly, referring to Figure 2 When the valve core 20 switches to the second position to open the orifice of the inner hole three 114, the hydraulic oil flows from left to right through the oil port two 112 to the oil port one 111. At this time, the hydraulic force on the valve core 20 is to the left, that is, the valve core 20 tends to close the inner hole three 114. At this time, the valve core 20 maintains a balanced state. When the flow exceeds a certain value, the hydraulic force on the valve core 20 increases. If it exceeds the electromagnetic force or spring force, the electromagnetic valve cannot be effectively switched, thereby prompting the valve core 20 to close the orifice of the inner hole three 114, resulting in the valve core 20 being unable to switch to the second position. In summary, the existing reversing valve has the problem of flow limitation, that is, when the flow exceeds a certain value, the valve core 20 cannot be switched, resulting in the reversing valve losing its reversing performance. The traditional electromagnetic reversing valve usually cannot be switched when the flow exceeds 15L / min.

[0051] Therefore, in order to solve the above problems, Figure 3 and Figure 4 As shown, in this embodiment, a wing plate 221 is provided around the valve core 20 on the circumferential side of the inner hole 113. Figure 1 As shown in the figure, when the valve core 20 is switched to the first position, a large flow of oil flows from the inner hole 121 to the oil port 111. At this time, the hydraulic force applied to the valve core 20 is to the right, so that the valve core 20 tends to close the inner hole 121. However, the oil has a large flow rate when passing through the gap between the orifice of the inner hole 121 and the valve core 20. This flow generates a leftward impact force on the wing plate 221, which is opposite to the direction of the hydraulic force applied to the valve core 20, and can offset a part of the hydraulic force, thereby balancing the hydraulic force and reducing the influence of the hydraulic force. Similarly, Figure 2 and Figure 3As shown, when the valve core 20 is switched to the second position, a large flow of oil flows from the oil port 2 112 to the oil port 1 111. At this time, the hydraulic force on the valve core 20 is to the left, so that the valve core 20 tends to close the inner hole 3 114. However, the oil has a large flow rate when passing through the gap between the orifice of the inner hole 3 114 and the valve core 20. This flow produces a rightward impact force on the wing plate 221, which is opposite to the direction of the hydraulic force on the valve core 20, and can offset a part of the hydraulic force, thereby balancing the hydraulic force and reducing the influence of the hydraulic force. Therefore, by arranging the wing plate 221 on the valve core 20, the hydraulic force can be balanced when the flow increases, so that the flow limit of the hydraulic valve is increased, so that the hydraulic valve can meet a larger flow demand.

[0052] like Figure 5 As shown, the number of the second oil ports 112 is set to be multiple, and the multiple second oil ports 112 are arranged at intervals along the circumference of the valve sleeve 10.

[0053] like Figure 3 and Figure 5 As shown, it can be known from the above content that in an optional embodiment, the valve sleeve 10 is provided with two rows of oil ports 111 both connected to the inner hole 113, the wing plate 221 is located between the two rows of oil ports 111 and can cut off the two rows of oil ports 111, when in the first position, the inner hole 121 is connected to a row of oil ports 111 adjacent thereto, and when in the second position, the oil port 112 is connected to another row of oil ports 111 adjacent thereto. Among them, a row of oil ports 111 near the inner hole 121 (a row of oil ports 111 on the right) is oil port 111a, and a row of oil ports 111 near the oil port 2 112 (a row of oil ports 111 on the left) is oil port 111b. When the valve core 20 is in the first position, the inner hole 121 is connected to the oil port 111a, and the oil port 2 112 is cut off from the oil port 111b. When the valve core 20 is in the second position, the oil port 2 112 is connected to the oil port 111b, and the inner hole 121 is cut off from the oil port 111a. With such arrangement, during the reversal of the valve core 20, the wing plate 221 can cut off the oil port 111a and the oil port 111b, thereby cutting off the inner hole 121 and the oil port 2 112, so that the oil flowing into the inner hole 121 can only flow out through the oil port 111a, and the oil flowing into the oil port 2 112 can only flow out through the oil port 111b, thereby preventing the oil in the inner hole 121 from flowing into the oil port 2 112 or the oil in the oil port 2 112 from flowing into the inner hole 121 in series during the reversal of the valve core 20, thereby preventing excessive hydraulic force from being generated during the reversal of the valve core 20 and reducing the influence of the hydraulic force. Through experiments, it has been verified that the wing plate 221 cooperates with the two rows of oil holes 111 on the valve sleeve 10 to increase the flow limit to more than 40L / min, which can greatly increase the flow rate compared with the flow limit of about 15L / min of the traditional electromagnetic reversing valve.

[0054] In addition, the wing plate 221 also has a function of guiding in cooperation with the hole wall of the second inner hole 113. In actual processing, the valve core 20 and the valve sleeve 10 cannot be made absolutely axially symmetrical, and the oil in the oil port 111 will eventually flow out through a hole on the valve block, which will generate a radial unbalanced force on the valve core 20. This radial unbalanced force will cause the valve core 20 to swing radially, hindering the valve core 20 from closing the inner hole 121 and the inner hole 3 114, slowing down the closing speed, and even affecting the closing effect of the valve core 20, resulting in a large amount of oil leakage. The guiding effect of the wing plate 221 and the second inner hole 113 can prevent the valve core 20 from swinging radially, so that the valve core 20 can quickly close the inner hole 121 and the inner hole 3 114, and the closing sealing effect is better.

[0055] In an optional embodiment, if Figure 5 As shown, the two rows of oil ports 111 are staggered, that is, oil ports 111a and oil ports 111b are staggered. This arrangement avoids the distance between oil ports 111a and oil ports 111b being too small, which leads to a low structural strength of the valve sleeve 10, thereby ensuring the structural strength of the valve sleeve 10.

[0056] In another optional embodiment, the side wall of the valve sleeve 10 may also be provided with only one row of oil ports 111 connected to the inner hole 2 113, and the multiple oil ports 111 in the row are arranged at intervals along the circumference of the valve sleeve 10, and the wing plate 221 on the valve core 20 can block part of the inner opening of each oil port 111. The inner opening of the oil port 111 is the opening formed by the oil port 111 on the inner wall of the valve sleeve 10. When the valve core 20 is switched to the first position, the valve core 20 moves to the left to seal the orifice of the inner hole three 114 and open the inner hole one 121, and at the same time, the wing plate 221 moves to the left to block the left half of the inner opening of the oil port 111. At this time, the right half of the inner opening of the oil port one 111 is connected to the inner hole one 121, and the oil port two 112 is cut off from the oil port one 111; when the valve core 20 is switched to the second position, the valve core 20 moves to the right to seal the orifice of the inner hole one 121 and open the inner hole three 114, and at the same time, the wing plate 221 moves to the right to block the right half of the inner opening of the oil port 111. At this time, the left half of the inner opening of the oil port one 111 is connected to the oil port two 112 through the inner hole three 114, and the inner hole one 121 is cut off from the oil port one 111. Therefore, in this embodiment, the form of an oil outlet 111 can also realize the switching of the oil circuit, and in this embodiment, the wing plate 221 on the valve core 20 can also balance the hydraulic force when the flow increases, so as to achieve the purpose of increasing the flow limit of the hydraulic valve.

[0057] like Figure 1 and Figure 2As shown, the valve sleeve 10 includes a main valve sleeve 11 and a limiting sleeve 12. The limiting sleeve 12 is detachably connected to the main valve sleeve 11, and the main valve sleeve 11 and the limiting sleeve 12 together form the above-mentioned valve cavity. When assembling the valve core 20, the valve core 20 is first installed in the main valve sleeve 11, and then the limiting sleeve 12 is installed on the main valve sleeve 11 to enclose the valve core 20 inside and realize the action control function of the valve core 20. The above arrangement makes the installation of the valve core 20 convenient and quick.

[0058] In an optional embodiment, if Figure 2 and Figure 3 As shown, one end of the main valve sleeve 11 close to the limiting sleeve 12 is provided with an internal thread, and one end of the limiting sleeve 12 close to the main valve sleeve 11 is provided with an external thread. The limiting sleeve 12 is inserted into the main valve sleeve 11, and is fastened to the main valve sleeve 11 through the external thread and the internal thread, thereby achieving a stable connection between the main valve sleeve 11 and the limiting sleeve 12, and convenient and quick disassembly. In this embodiment, the inner hole three 114, the inner hole two 113, the oil port one 111 and the oil port two 112 are all opened on the main valve sleeve 11, the inner hole one 121 is opened on the limiting sleeve 12, the orifice of the inner hole one 121 is the port of the limiting sleeve 12, and the threaded section is located on the right side of the oil port one 111.

[0059] In another optional embodiment, if Figure 1 As shown, one end of the main valve sleeve 11 close to the limiting sleeve 12 is provided with an external thread, and one end of the limiting sleeve 12 close to the main valve sleeve 11 is provided with an internal thread. The limiting sleeve 12 is sleeved outside the main valve sleeve 11, and is fastened to the main valve sleeve 11 through the internal thread and the external thread, thereby also realizing a stable connection between the main valve sleeve 11 and the limiting sleeve 12, and convenient and quick disassembly. In this embodiment, the inner hole 121, the inner hole 2 113 and the oil port 1 111 are all provided on the limiting sleeve 12, the oil port 2 112 and the inner hole 3 114 are all provided on the main valve sleeve 11, the orifice of the inner hole 3 114 is the port of the main valve sleeve 11, and the threaded section is located on the left side of the oil port 1 111.

[0060] like Figure 2 and Figure 3 As shown, the valve core 20 includes a valve stem 21 and a valve core body 22 connected to each other. The radial dimension of the valve core body 22 is greater than the radial dimension of the valve stem 21. The aperture of the second inner hole 113 is greater than the aperture of the third inner hole 114. The valve stem 21 is located in the third inner hole 114 and abuts against the push rod 60. The valve core body 22 is located in the second inner hole 113. The wing plate 221 is arranged on the valve core body 22. The valve core body 22 can seal the aperture of the third inner hole 114 in the first position and can seal the aperture of the first inner hole 121 in the second position. By moving the valve core body 22 in the second inner hole 113, the valve core body 22 can seal the inner hole 121 and the inner hole 3 114, thereby realizing the switching of the oil circuit.

[0061] In an optional embodiment, if Figure 3 As shown, both axial ends of the valve core body 22 are provided with a conical sealing surface 222, that is, the valve core 20 in this embodiment is a conical valve core. When the valve core body 22 seals the orifice of the inner hole three 114, the conical sealing surface 222 at one end of the valve core body 22 contacts the orifice of the inner hole three 114 to form a seal, and the sealing surface is a line contact seal formed by the annular line and the conical surface, and the sealing effect is better. When the valve core body 22 seals the orifice of the inner hole one 121, the conical sealing surface 222 at the other end of the valve core body 22 contacts the orifice of the inner hole one 121 to form a seal, and the sealing surface is also a line contact seal formed by the annular line and the conical surface, and the sealing effect is better. In another optional embodiment, the valve core 20 can also be a sliding valve core.

[0062] In another optional embodiment, arc-shaped sealing surfaces may also be provided at both axial ends of the valve core body 22, which can also achieve the above-mentioned line contact sealing effect, and will not be described in detail here.

[0063] Embodiment 2

[0064] The hydraulic valve provided in this embodiment has a substantially same structure as the hydraulic valve provided in the first embodiment, and the similarities are not repeated here. The difference is that: Figure 6 and Figure 7 As shown, a wing plate 221 is protruding on the inner wall of the valve cavity of the valve sleeve 10, specifically, a wing plate 221 is protruding on the circumferential side wall of the inner hole 113, and the wing plate 221 abuts against the side wall of the valve core body 22 to cooperate with the guide of the valve core body 22, thereby avoiding radial swing of the valve core 20, so that the valve core 20 can quickly close the inner hole 121 and the inner hole 3 114, and the closing sealing effect is better.

[0065] Specifically, the valve sleeve 10 is provided with two rows of oil ports 111, which are arranged at intervals along the axial direction of the valve sleeve 10, and a plurality of oil ports 111 in each row are arranged at intervals along the circumferential direction of the valve sleeve 10, and the wing plate 221 is located between the two rows of oil ports 111 and cuts off the two rows of oil ports 111 by abutting against the valve core body 22. Among them, a row of oil ports 111 close to the inner hole 121 is defined as oil port 111a, and a row of oil ports 111 close to the second oil port 112 is defined as oil port 111b. When the valve core 20 is located at the first position, the inner hole 121 is connected to the oil port 111a, and the second oil port 112 is cut off from the oil port 111b. When the valve core 20 is located at the second position, the second oil port 112 is connected to the oil port 111b, and the inner hole 121 is cut off from the oil port 111a. With such arrangement, during the reversal of the valve core 20, the wing plate 221 always blocks the oil port 111a and the oil port 111b, thereby always blocking the inner hole 121 and the oil port 2 112, so that the oil flowing into the inner hole 121 can only flow out through the oil port 111a, and the oil flowing into the oil port 2 112 can only flow out through the oil port 111b, thereby preventing the oil in the inner hole 121 from flowing into the oil port 2 112 or the oil in the oil port 2 112 from flowing into the inner hole 121 in series during the reversal of the valve core 20, thereby preventing excessive hydraulic force from being generated during the reversal of the valve core 20 and reducing the influence of the hydraulic force. Therefore, this embodiment can also play a role in balancing the hydraulic force to a certain extent, thereby increasing the flow limit of the hydraulic valve. However, the effect of balancing the hydraulic force is relatively poorer than the effect of balancing the hydraulic force played by the wing plate 221 arranged on the valve core 20 in the first embodiment.

[0066] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation methods of the present invention. For those skilled in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to list all implementation methods here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the claims of the present invention.

Claims

1. A structure for balancing fluid force, characterized in that: The invention comprises a valve sleeve (10) and a valve core (20) arranged in the valve sleeve (10); the valve sleeve (10) is provided with a valve cavity for fluid flow; the valve core (20) is slidably arranged in the valve cavity to achieve fluid shutoff or conduction; a wing plate (221) is convexly provided on the circumferential side of the valve core (20) or a wing plate (221) is convexly provided on the inner wall of the valve cavity of the valve sleeve (10).

2. The structure for balancing fluid force according to claim 1, characterized in that: A row of oil ports (111) communicating with the valve cavity is provided on the side wall of the valve sleeve (10); a plurality of the oil ports (111) in the row are arranged at intervals along the circumference of the valve sleeve (10); a wing plate (221) is provided on the valve core (20); and the wing plate (221) can block a portion of the inner opening of each of the oil ports (111).

3. The structure for balancing fluid force according to claim 1, characterized in that: Two rows of oil ports (111) respectively connected to the valve cavity are provided on the side wall of the valve sleeve (10); the two rows of oil ports (111) are arranged at intervals along the axial direction of the valve sleeve (10); a plurality of oil ports (111) in each row are arranged at intervals along the circumferential direction of the valve sleeve (10); and the wing plate (221) is located between the two rows of oil ports (111) and can cut off the two rows of oil ports (111).

4. The structure for balancing fluid force according to claim 3, characterized in that: The two rows of oil ports 1 (111) are arranged alternately.

5. The structure for balancing fluid force according to claim 3, characterized in that: The side wall of the valve sleeve (10) is also provided with a second oil port (112); the valve cavity comprises an inner hole (121), an inner hole (113) and an inner hole (114) which are sequentially connected in the axial direction; the first oil port (111) is connected to the inner hole (113); the second oil port (112) is connected to the inner hole (114); the wing plate (221) is protrudingly provided on the circumferential side of the inner hole (113) of the valve core (20); or the wing plate (221) is protrudingly provided on the circumferential side wall of the inner hole (113); The valve core (20) can be switched between a first position and a second position. When in the first position, the valve core (20) seals the orifice of the inner hole three (114), and the inner hole one (121) is connected to a row of oil ports one (111) adjacent to it; when in the second position, the valve core (20) seals the orifice of the inner hole one (121), and the oil port two (112) is connected to another row of oil ports one (111) adjacent to it.

6. The structure for balancing fluid force according to claim 5, characterized in that: The valve sleeve (10) comprises a main valve sleeve (11) and a limiting sleeve (12); the limiting sleeve (12) is detachably connected to the main valve sleeve (11); the main valve sleeve (11) and the limiting sleeve (12) together form the valve cavity.

7. The structure for balancing fluid force according to claim 6, characterized in that: An inner thread is provided at one end of the main valve sleeve (11) close to the limiting sleeve (12), and an outer thread is provided at one end of the limiting sleeve (12) close to the main valve sleeve (11). The limiting sleeve (12) is inserted into the main valve sleeve (11) and is fastened to the main valve sleeve (11) via the outer thread and the inner thread. The inner hole 2 (113), the inner hole 3 (114), the oil port 1 (111) and the oil port 2 (112) are all provided on the main valve sleeve (11), and the inner hole 1 (121) is provided in the limiting sleeve (12).

8. The structure for balancing fluid force according to claim 6, characterized in that: An external thread is provided at one end of the main valve sleeve (11) close to the limiting sleeve (12), and an internal thread is provided at one end of the limiting sleeve (12) close to the main valve sleeve (11). The limiting sleeve (12) is sleeved outside the main valve sleeve (11) and is fastened to the main valve sleeve (11) via the internal thread and the external thread. The inner hole one (121), the inner hole two (113) and the oil port one (111) are all provided on the limiting sleeve (12), and the inner hole three (114) and the oil port two (112) are provided on the main valve sleeve (11).

9. The structure for balancing fluid force according to any one of claims 5 to 8, characterized in that: The valve core (20) includes a valve stem (21) and a valve core body (22) connected to each other. The aperture of the inner hole two (113) is larger than the aperture of the inner hole three (114). The valve stem (21) is located in the inner hole three (114). The valve core body (22) is located in the inner hole two (113). The valve core body (22) can seal the opening of the inner hole three (114) when in the first position and can seal the opening of the inner hole one (121) when in the second position.

10. The structure for balancing fluid force according to claim 9, characterized in that: Both axial ends of the valve core body (22) are provided with conical sealing surfaces (222) or arc-shaped sealing surfaces.

11. The structure for balancing fluid force according to any one of claims 5 to 8, characterized in that: When the wing plate (221) is protruding from the valve core (20) and is located on the peripheral side of the second inner hole (113), the wing plate (221) is guided and matched with the second inner hole (113); or When the wing plate (221) is protrudingly disposed on the circumferential side wall of the second inner hole (113), the wing plate (221) is guided and matched with the valve core (20).

12. A hydraulic valve, characterized in that: The invention comprises a structure for balancing fluid force as claimed in any one of claims 1 to 11.

13. The hydraulic valve according to claim 12, characterized in that The hydraulic valve is an electromagnetic reversing valve, and the valve core is a cone valve core or a sliding valve core.

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