Disc valve pre-tightening structure

Abstract

The utility model provides a pre-tightening structure of a disc valve, which adopts a non-self-locking sealing scheme and is characterized in that a static valve core is indirectly provided by a fastening bolt which is responsible for fixedly connecting a valve cover with a valve body bolt and is used for locking extrusion force; the skirt edge body of the valve cover upwards presses the static valve element to provide pressing sealing of the second sealing ring between the static valve element and the valve body, and therefore sealing of an oil channel is guaranteed. Low-pressure oil is connected into the main oil duct holes communicated with the auxiliary oil duct holes and flows into the clearance space through the auxiliary oil duct holes and the clearance groove, and the rest main oil duct holes are connected with high-pressure oil, so that the arc-shaped groove in the upper surface of the movable valve element is internally provided with a high-pressure area, and the clearance space below the arc-shaped groove is a low-pressure area; sealing can be guaranteed as long as the jacking force of the elastic piece is larger than the jacking force of the high-pressure arc-shaped groove. The friction torque of the movable valve element and the static valve element is smaller when the vertical pressure difference of the movable valve element is larger during operation, and due to the fact that the maximum friction torque is smaller than that of a self-locking sealing scheme, the requirements for an actuator and related transmission parts are reduced, and the effects of reducing cost, prolonging service life and the like are achieved.

Description

Technical Field

[0001] The utility model belongs to the technical field of multi-way disc valves, in particular to a disc valve pre-tightening structure. Background Art

[0002] Among the types of fluid control valves, disc valves are unique in their lower internal leakage and longer service life.

[0003] There are also precedents for using disc valves in automotive thermal management systems, most of which use motors to reduce speed and then drive the valve core to control the direction or on / off of the fluid. In order to ensure internal leakage requirements, thermal management disc valves almost all use self-locking sealing, that is, the pressure difference force of the fluid is used to press the dynamic and static valve cores tighter. The greater the pressure difference, the lower the internal leakage. As long as the internal leakage is guaranteed when the pressure difference is 0 and only the pre-tightening force is used to seal, the internal leakage of this solution can be reliably guaranteed. However, when the pressure difference is large, the friction torque of the dynamic and static valve cores will rise sharply, and the driving force requirement will increase sharply, which puts higher requirements on the motor power and the strength of the reduction mechanism.

[0004] For example Figure 1 The structure of an existing disc valve shown in the figure has a pipe on the left side of the disc valve as an inlet, and the fluid flows out from the bottom of the static valve core 4' after passing through the valve port between the moving valve core 5' and the static valve core 4'. The valve body 1' and the valve cover 2' of the disc valve are laser welded, the static valve core 4' and the valve body 1' are sealed and fixed by the sealing ring 6', the moving valve core 5' and the transmission shaft 3' are fixed and can rotate as a whole, and the spring 7' in the middle supports the two, and the pre-tightening force of the spring 7' ensures that the moving valve core 5' and the static valve core 4' are tightly fitted, and the sealing ring 6' needs to be compressed to a certain extent when the pressure difference is zero to prevent leakage from here.

[0005] from Figure 1 From the structure, it can be seen that the spring only needs a small preload to make the dynamic and static valve cores fit tightly, but a large preload is required to compress the sealing ring to the extent that the seal is guaranteed, so the preload must be the larger one. Since the preload of the spring is large, the pressure between the dynamic and static valves also increases, and the friction torque during rotation also increases, so the motor power and the strength of the reduction gear need to be strengthened. This makes the product cost relatively large and the life of the valve core will also be reduced. Utility Model Content

[0006] In view of the problems existing in the prior art, the utility model provides the following technical solutions:

[0007] A pre-tightening structure of a disc valve, wherein a valve body is provided with a receiving cavity, a valve cover seals and plugs the cavity opening, and coaxially arranged static valve core, dynamic valve core and transmission valve core are stacked in sequence from the top wall surface to the valve cover in the receiving cavity. A transmission shaft extends into the receiving cavity and is fixedly connected with the transmission valve core coaxially. The static valve core is prevented from rotating around the center by an anti-rotation structure, and the dynamic valve core is kept in synchronous rotation with the transmission valve core through a synchronous rotation structure;

[0008] An elastic member is arranged between the dynamic valve core and the transmission valve core, and is used to provide an upward abutting force for the dynamic valve core to fit the static valve core;

[0009] A plurality of main oil passage holes are opened on the valve body. One end opening of each main oil passage hole is opened on the side wall surface of the valve body, and the other end opening is opened on the top wall surface of the receiving cavity that abuts against the upper surface of the static valve core. Corresponding to each main oil passage hole on the static valve core, there is a static valve core oil passage hole that vertically penetrates the static valve core and is in direct communication. The upper surface of the dynamic valve core is provided with a plurality of arc-shaped oil passage grooves, and each arc-shaped oil passage groove matches a pair of static valve core oil passage holes; A ring-shaped skirt body extending into the receiving cavity is formed on the upper surface of the valve cover. The top end of the skirt body abuts against the lower surface of the static valve core, and the screwing direction of the fastening bolt that fixes the valve cover and the valve body is parallel to the direction in which the skirt body abuts against the static valve core;

[0010] A secondary oil passage hole is further opened inside the valve body. The inlet of the secondary oil passage hole is communicated with a main oil passage hole, and the outlet is opened on the top wall surface of the receiving cavity. The static valve core is formed with a clearance groove for communicating the outlet of the secondary oil passage hole and the clearance space jointly formed by the clearances between the dynamic valve core, the elastic member, the transmission valve core and the valve cover below the static valve core; The orifices of other main oil passage holes that are not communicated with the secondary oil passage hole are all clamped and sealed by seals on the periphery of the orifices between the top wall surface of the receiving cavity and the static valve core;

[0011] The oil pressure introduced into the main oil passage hole communicated with the secondary oil passage hole is lower than the oil pressure introduced into other main oil passage holes.

[0012] Furthermore, the anti-rotation structure for preventing the static valve core from rotating around the center is: blind holes are respectively opened on the top wall surface of the receiving cavity and the upper surface of the static valve core, and the upper part of a cylindrical pin is inserted into the blind hole on the top wall surface of the receiving cavity, and the lower part of the cylindrical pin is inserted into the corresponding blind hole on the upper surface of the static valve core.

[0013] Furthermore, the anti-rotation structure for preventing the static valve core from rotating around the center is: a boss and a pit for corresponding embedded fit are respectively arranged on the top wall surface of the receiving cavity and the upper surface of the static valve core.

[0014] Furthermore, the synchronous rotation structure for keeping the dynamic valve core and the transmission valve core in synchronous rotation is: blind holes for respectively accommodating cylindrical pins are correspondingly opened on the lower surface of the dynamic valve core and the upper surface of the transmission valve core, and the upper part of the cylindrical pin is inserted into the blind hole on the lower surface of the dynamic valve core, and the lower part of the cylindrical pin is inserted into the corresponding blind hole on the upper surface of the transmission valve core.

[0015] Further, the synchronous rotation structure for keeping the moving valve core and the driving valve core rotating synchronously is that a boss and a pit which are correspondingly embedded and fitted are respectively provided on the lower surface of the moving valve core and the upper surface of the driving valve core.

[0016] Further, as the moving valve core rotates, each arc-shaped oil passage groove can be directly aligned and communicated with a pair of static valve core oil holes corresponding to it, so as to connect two corresponding main oil passage holes; or at least one of the pair of static valve core oil holes is out of the communication range with the arc-shaped oil passage groove, so as to disconnect the communication between the corresponding two main oil passage holes.

[0017] Further, the accommodation groove formed by enclosing the skirt body accommodates the moving valve core and the driving valve core therein and has a clearance fit.

[0018] Further, the outlet of the secondary oil passage hole is located on the top wall surface of the accommodation cavity between the main oil passage hole and the axis of the static valve core.

[0019] Further, a friction sleeve is slidably sleeved on the transmission shaft, and the upper and lower parts of the friction sleeve are respectively embedded in the shaft hole of the valve body and the axis hole of the static valve core. The friction sleeve reduces the friction force for the rotation of the transmission shaft.

[0020] Further, a shaft convex part protrudes from the center of the lower surface of the driving valve core, a receiving groove is provided at the center of the upper surface of the valve cover located in the accommodation cavity, a friction pad is fixedly installed in the receiving groove, a supporting groove is formed on the upper surface of the friction pad, and the friction pad is clamped between the shaft convex part of the driving valve core and the receiving groove of the valve cover. The friction pad is used to support the rotation of the driving valve core and reduce the rotational friction force.

[0021] The present utility model adopts a non-self-locking sealing solution, which has the following beneficial effects compared with the self-locking solution of the prior art:

[0022] The static valve core indirectly receives and locks the extrusion force provided by the fastening bolts responsible for bolt-fixing the valve cover and the valve body. The skirt body of the valve cover presses the static valve core upward to provide the pressing seal of the second sealing ring between the static valve core and the valve body, thereby ensuring the sealing of the oil passage and eliminating the influence of the seal reaction force on the friction torque of the moving and static valve cores.

[0023] The main oil passage hole communicated with the secondary oil passage hole accesses low-pressure oil, and flows into the clearance space through the secondary oil passage hole and the clearance groove. The remaining main oil passage holes access high-pressure oil, so that the arc-shaped groove on the upper surface of the moving valve core is a high-pressure area, and the clearance space below the moving valve core is a low-pressure area. The top pressing force of the elastic member only needs to be larger than the top opening force of the high-pressure arc-shaped groove to ensure sealing. In this non-self-locking sealing solution, the greater the pressure difference between the upper and lower parts of the moving valve core during operation, the smaller the friction torque of the moving and static valve cores. Since the maximum friction torque is smaller than that of the self-locking sealing solution, the requirements for the actuator and related transmission components are reduced, and the effects of cost reduction and service life extension are achieved. Description of the Drawings

[0024] The attached drawings, which form a part of the present utility model, are used to provide a further understanding of the present utility model. The schematic embodiments and descriptions thereof of the present utility model are used to explain the present utility model and do not constitute an improper limitation to the present utility model. For those of ordinary skill in the art, other related attached drawings can also be obtained based on these attached drawings without creative efforts.

[0025] Figure 1 It is a schematic diagram of a disc valve structure in the prior art;

[0026] Figure 2 It is a partial cross-sectional schematic diagram of the present utility model from the front view perspective;

[0027] Figure 3 It is a partial cross-sectional schematic diagram of the present utility model from the side view perspective;

[0028] Figure 4 It is Figure 2 an enlarged schematic diagram of a part of

[0029] Figure 5 It is Figure 3 an enlarged schematic diagram of a part of

[0030] The reference numerals in the drawings: valve body 1; valve cover 2; transmission shaft 3; static valve core 4; moving valve core 5; transmission valve core 6; elastic member 7; friction pad 8; friction sleeve 9;

[0031] main oil passage hole 11; secondary oil passage hole 12; static valve core oil passage hole 41; arc oil passage groove 51;

[0032] shaft convex portion 61; support groove 81;

[0033] accommodation cavity 100; clearance space 101;

[0034] skirt body 21; static valve core through hole 41; clearance groove 42; moving valve core flow passage groove 51;

[0035] actuator 900; expansion valve 910; plug 920; fastening bolt 930; first sealing ring 941; second sealing ring 942; cylindrical pin 951; cylindrical pin 952. Specific embodiments

[0036] It should be noted that, without conflict, the embodiments and features in the embodiments of the present utility model can be combined with each other.

[0037] In the description of the embodiments of the present utility model, it should be noted that the indicated orientation or positional relationship is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of this application is habitually placed during use, or the orientation or positional relationship commonly understood by those skilled in the art. It is only for the convenience of describing the present utility model or simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed or operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model.

[0038] The "multiple" that appears in the present utility model refers to two or more (including two). Terms such as "first" and "second" are only used for distinguishing descriptions and should not be construed as indicating or implying relative importance.

[0039] Unless otherwise clearly specified and limited, the terms "set", "installed", and "connected" 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 direct connection or an indirect connection through an intermediate medium.

[0040] The present utility model will be described in detail below with reference to the drawings and in conjunction with the embodiments.

[0041] As shown in the figure, the disk valve of the present utility model includes a valve body 1, a valve cover 2, a plug 920, an actuator 900, and an expansion valve 910, and also includes a transmission shaft 3, a friction sleeve 9, a static valve core 4, a dynamic valve core 5, a transmission valve core 6, an elastic member 7, a friction pad 8, etc.

[0042] A receiving cavity 100 is formed in the lower part of the valve body 1. The opening of the receiving cavity 100 faces downward, and the opening is sealed by the valve cover 2. The valve cover 2 and the valve body 1 are fixed by fastening bolts 930. Inside the receiving cavity 100 between the top cavity top wall and the bottom valve cover 2, a static valve core 4, a dynamic valve core 5, and a transmission valve core 6 are stacked coaxially from top to bottom. The transmission shaft 3 passes through the shaft hole of the valve body 1 and extends into the receiving cavity 100 from top to bottom. After the transmission shaft 3 passes through the central holes of the static valve core 4 and the dynamic valve core 5 respectively, the bottom end of the transmission shaft 3 is fixedly connected coaxially with the transmission valve core 6. The friction sleeve 9 is sleeved on the transmission shaft 3, and its upper and lower parts are respectively embedded in the shaft hole of the valve body 1 and the central hole of the static valve core 4. The friction sleeve 9 between the valve body 1 and the transmission shaft 3 reduces the friction force for the rotation of the transmission shaft 3.

[0043] As another alternative structural embodiment, the transmission shaft can also directly pass through the valve cover and extend into the receiving cavity, and be directly fixedly connected coaxially with the transmission valve core, without first passing through the valve body, the static valve core, and the dynamic valve core and then being coaxially fixedly connected with the transmission valve core. Correspondingly, the actuator is also adjusted to be located below the valve cover to be connected to the transmission shaft. Since those skilled in the art can understand, no corresponding schematic diagram is provided for this embodiment.

[0044] A shaft convex portion 61 protrudes from the center of the lower surface of the transmission valve core 6. A receiving groove is provided at the center of the upper surface of the valve cover 2 located within the receiving cavity 100. A friction pad 8 is fixedly installed within the receiving groove. A support groove 81 is formed on the upper surface of the friction pad 8. The friction pad 8 is clamped between the shaft convex portion 61 of the transmission valve core 6 and the receiving groove of the valve cover 2. The friction pad 8 is used to support the rotation of the transmission valve core 6 and reduce the rotational friction force.

[0045] As another alternative structural embodiment, in the structural embodiment where the transmission shaft passes through the valve cover and extends into the receiving cavity to be coaxially fixed to the transmission valve core, the transmission shaft also has to pass through the friction pad, which is equivalent to the friction pad acting as a friction sleeve, reducing the friction force for both the transmission shaft and the rotation of the transmission valve core. Since those skilled in the art can understand, no corresponding schematic diagram is provided for this embodiment.

[0046] Blind holes for respectively receiving the upper and lower portions of the cylindrical pin 952 are correspondingly provided on the top wall surface of the receiving cavity 100 and the upper surface of the static valve core 4. The cylindrical pin 952 is used to prevent the static valve core 4 from rotating relative to its axis; the anti-rotation structure between the upper surface of the static valve core 4 and the top wall surface of the receiving cavity 100 can also be realized by a boss and a pit.

[0047] Blind holes for respectively receiving the upper and lower portions of the cylindrical pin 951 are correspondingly provided on the lower surface of the moving valve core 5 and the upper surface of the transmission valve core 6. The cylindrical pin 951 is used to keep the moving valve core 5 rotating synchronously with the transmission valve core 6; the synchronous rotation structure between the lower surface of the moving valve core 5 and the upper surface of the transmission valve core 6 can also be realized by a boss and a pit.

[0048] An elastic member 7 is further provided between the moving valve core 5 and the transmission valve core 6, and is used to provide an upward pressing force for the moving valve core 5 to fit against the static valve core 4.

[0049] The valve body 1 has a plurality of inlets and outlets, which are used to control the flow direction of the refrigerant in the automotive thermal management system, and thus realize heating or cooling of system areas such as the air conditioner and the battery, having the advantages of high integration and low cost.

[0050] Specifically, a plurality of main oil passage holes 11 are formed in the valve body 1. One end orifice of each main oil passage hole 11 is formed on the side wall surface of the valve body 1 as an inlet or an outlet, and the other end orifice is formed on the top wall surface of the accommodation cavity 100 opposite to the upper surface of the static spool 4. A second sealing ring 942 is installed on the top wall surface around the orifice through a sealing groove, and the second sealing ring 942 is pressed upward by the static spool 4 to ensure the sealing at the orifice. Corresponding to each main oil passage hole 11 on the static spool 4, there is a static spool oil passage hole 41 vertically penetrating the static spool 4 in a direct communication manner. A plurality of arc-shaped oil passage grooves 51 are formed on the upper surface of the moving spool 5. Each arc-shaped oil passage groove 51 matches a pair of static spool oil passage holes 41. When the moving spool 5 rotates to a corresponding angle, the two ends of the arc-shaped oil passage groove 51 can be respectively in direct communication with the pair of static spool oil passage holes 41, thereby connecting two corresponding main oil passage holes 11; when the moving spool 5 rotates to a position where at least one of a pair of static spool oil passage holes 41 is out of the communication range of the arc-shaped oil passage groove 51, the two corresponding main oil passage holes 11 are disconnected.

[0051] In the present utility model, the upward pressing force for the static spool 4 to press the second sealing ring 942 to ensure the sealing at the orifice is provided by the combination of the skirt body 21 of the valve cover 2 and the fastening bolt 930 used for fastening between the valve cover and the valve body. Specifically: an annular skirt body 21 extending into the accommodation cavity 100 is formed on the upper surface of the valve cover 2. The accommodation groove formed by surrounding the skirt body 21 houses the moving spool 5 and the transmission spool 6 with a clearance fit. The top end of the skirt body 21 abuts against the lower surface of the static spool 4. Refer to Figure 3 As shown, since the screwing and telescoping direction of the fastening bolt 930 is parallel (i.e., in the same direction) to the direction in which the skirt body 21 abuts against the static spool 4, therefore, in addition to fixing the valve cover 2 and the valve body 1, the fastening bolt 930 can also abut against the static spool 4 by the skirt body 21 to provide adjustment and locking for the upward pressing force of the static spool 4 on the second sealing ring 942.

[0052] The outer side surface of the skirt body 21 and the cavity side wall of the accommodation cavity 100 are clamped and sealed by a first sealing ring 941. A sealing ring can also be clamped between the lower surface of the valve body and the upper surface of the valve cover that is pressed against it, so as to realize the sealing and plugging of the accommodation cavity by the valve cover.

[0053] In addition, refer to Figure 3 and Figure 5As shown, an auxiliary oil passage hole 12 is further formed inside the valve body 1. One end orifice (i.e., the "inlet") of the auxiliary oil passage hole 12 is connected to a main oil passage hole 11, and the other end orifice (i.e., the "outlet") is formed on the top wall surface of the accommodation cavity 100. Preferably, the other end orifice of the auxiliary oil passage hole 12 is located on the top wall surface of the accommodation cavity 100 between the main oil passage hole friction sleeve 9; the static spool 4 is formed with a clearance groove 42 for connecting the outlet of the auxiliary oil passage hole 12 and the clearance space 101 jointly formed by the clearances between the moving spool 5, the elastic member 7, the transmission spool 6, and the valve cover 2 below the static spool 4.

[0054] From Figure 4 It can be seen that the static spool and the valve body are tightly sealed by a plurality of second sealing rings 942 to ensure the sealing of the main oil passage hole. A relatively large force is required to ensure the compression of the plurality of second sealing rings 942. This solution is provided by pressing the static spool 4 upward by the skirt body 21 of the valve cover. The moving spool and the transmission spool rotate synchronously. The transmission spool 6 and the transmission shaft 3 are fixedly connected coaxially to rotate synchronously, so that the moving spool 5, the transmission spool 6, and the transmission shaft 3 can rotate integrally. The elastic member 7 between the moving spool 5 and the transmission spool 6 presses the two up and down to ensure that the moving spool 5 is in close contact with the static spool 4. Here, the elastic force of the elastic member 7 only needs to ensure that the moving and static spools are in close contact at 0 pressure difference, so its elastic force is relatively small. At 0 pressure difference, the frictional torque between the moving and static spools is only affected by the elastic force of the elastic member. At high pressure difference, the frictional torque between the static and static spools is affected by the elastic force of the elastic member and the pressure difference force. The frictional torque is not affected by the reaction force of the second sealing ring 942 of the main oil passage hole 11.

[0055] Therefore, this solution eliminates the influence of the reaction force of the second sealing ring 942 on the frictional torque between the moving and static spools, makes the frictional torque relatively low, reduces the requirements for the actuator and related transmission components, and has the effects of reducing costs and extending the service life.

[0056] Furthermore, in the present utility model, the oil pressure accessed by the main oil passage hole communicating with the secondary oil passage hole should be lower than the oil pressures accessed by other main oil passage holes. That is, the fluid pressure in the clearance spaces such as the main oil passage hole and the clearance groove communicating with the secondary oil passage hole is the lowest in the whole system. The pressures in the other main oil passage holes on the valve body and the communicating arc-shaped grooves are relatively higher. Therefore, the pressure in the high-pressure arc-shaped groove has a tendency to push the moving valve core open. If the moving valve core is pushed open, the high-pressure fluid in the arc-shaped groove will leak into the clearance space. Therefore, the function of the elastic member is to hold the moving valve core to prevent it from being pushed open. Since the area ratio of the high-pressure part of the arc-shaped groove to the entire large plane area of the moving valve core is relatively small, under the same pressure difference, the opening force of the high-pressure arc-shaped groove in the non-self-locking sealing solution of the present utility model is much smaller than the pressure difference force of the entire large plane of the moving valve core in the prior art self-locking sealing solution. As long as the tightening force of the elastic member is greater than the opening force of the high-pressure arc-shaped groove and has a sufficient safety factor, the sealing can be ensured. Obviously, the tightening force of the elastic member can be made smaller than the pressure difference force of the entire large plane of the moving valve core in the self-locking sealing solution. When the pressure difference is 0 during the operation of this non-self-locking sealing solution, that is, the friction torque between the moving and static valve cores is the largest. The greater the pressure difference, the smaller the friction torque between the moving and static valve cores. Since the maximum friction torque is smaller than that of the self-locking sealing solution, the requirements for the actuator and related transmission components are reduced, and effects such as cost reduction and service life extension are achieved.

[0057] It should be noted that the orifices of each of the other main oil passage holes not communicating with the secondary oil passage hole between the top wall surface of the accommodation cavity and the static valve core need to be sealed, that is, clamped and sealed by the sealing rings on the periphery of the orifice; the orifice of the main oil passage hole communicating with the secondary oil passage hole between the top wall surface of the accommodation cavity and the static valve core can be optionally clamped and sealed by a sealing ring or not sealed. Even if it is not sealed, the liquid leaking into the clearance space 101 also belongs to the low pressure and will not damage the function of the present utility model.

[0058] The above are only the preferred embodiments of the present utility model and are not intended to limit the present utility model. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present utility model shall be included in the protection scope of the present utility model.

Claims

1. A pre-tightening structure for a disc valve, characterized in that, The valve body is provided with a receiving cavity, and the valve cover seals the cavity opening. Inside the receiving cavity, a static valve core, a dynamic valve core, and a transmission valve core that are coaxially arranged are stacked in sequence from the top wall surface to the valve cover. A transmission shaft extends into the receiving cavity and is fixedly connected to the transmission valve core coaxially. The static valve core is prevented from rotating around the center by an anti-rotation structure, and the dynamic valve core is kept in synchronous rotation with the transmission valve core through a synchronous rotation structure; An elastic member is provided between the dynamic valve core and the transmission valve core to provide an upward elastic force for the dynamic valve core to abut and fit against the static valve core; The valve body is provided with multiple main oil passage holes. One end orifice of each main oil passage hole is opened on the side wall surface of the valve body, and the other end orifice is opened on the top wall surface of the receiving cavity that abuts against the upper surface of the static valve core. Corresponding to each main oil passage hole on the static valve core, there is a static valve core oil passage hole that vertically penetrates the static valve core and is in direct communication. The upper surface of the dynamic valve core is provided with multiple arc-shaped oil passage grooves, and each arc-shaped oil passage groove matches a pair of static valve core oil passage holes; on the upper surface of the valve cover, there is a ring-shaped skirt body that extends into the receiving cavity. The top end of the skirt body abuts against the lower surface of the static valve core, and the screwing direction of the fastening bolt that fixes the valve cover to the valve body is parallel to the direction in which the skirt body abuts against the static valve core; A secondary oil passage hole is also opened inside the valve body. The inlet of the secondary oil passage hole is in communication with a main oil passage hole, and the outlet is opened on the top wall surface of the receiving cavity. The static valve core is formed with a clearance groove for communicating the outlet of the secondary oil passage hole and the clearance space jointly formed by the gaps between the dynamic valve core, the elastic member, the transmission valve core, and the valve cover below the static valve core; the orifices of the other main oil passage holes that are not in communication with the secondary oil passage hole are tightly sealed by seals on the circumferences of the orifices between the top wall surface of the receiving cavity and the static valve core; The oil pressure introduced into the main oil passage hole in communication with the secondary oil passage hole is lower than the oil pressure introduced into the other main oil passage holes.

2. The disk valve pre-tightening structure according to claim 1, characterized in that, The anti-rotation structure for preventing the static valve core from rotating around the center is: blind holes are respectively provided on the top wall surface of the receiving cavity and the upper surface of the static valve core. The upper part of a cylindrical pin is inserted into the blind hole on the top wall surface of the receiving cavity, and the lower part of the cylindrical pin is inserted into the corresponding blind hole on the upper surface of the static valve core.

3. The pre-tightening structure of a disk valve according to claim 1, characterized in that, The anti-rotation structure for preventing the static valve core from rotating around the center is: a convex platform and a concave pit that are correspondingly embedded and fitted are respectively provided on the top wall surface of the receiving cavity and the upper surface of the static valve core.

4. The pre-tightening structure of a disk valve according to claim 1, characterized in that, The synchronous rotation structure for keeping the dynamic valve core and the transmission valve core in synchronous rotation is: blind holes for accommodating cylindrical pins are respectively provided on the lower surface of the dynamic valve core and the upper surface of the transmission valve core. The upper part of a cylindrical pin is inserted into the blind hole on the lower surface of the dynamic valve core, and the lower part of the cylindrical pin is inserted into the corresponding blind hole on the upper surface of the transmission valve core.

5. The pre-tightening structure of a disk valve according to claim 1, wherein, The synchronous rotation structure for keeping the dynamic valve core and the transmission valve core in synchronous rotation is: a convex platform and a concave pit that are correspondingly embedded and fitted are respectively provided on the lower surface of the dynamic valve core and the upper surface of the transmission valve core.

6. The pre-tightening structure of a disk valve according to claim 1, characterized in that, As the dynamic valve core rotates, each arc-shaped oil passage groove can be in direct communication with a corresponding pair of static valve core oil passage holes, thereby connecting two corresponding main oil passage holes; or at least one of the pair of static valve core oil passage holes is out of the communication range with the arc-shaped oil passage groove, thereby disconnecting the connection between the corresponding two main oil passage holes.

7. A pre-tightening structure of a disk valve according to claim 1, characterized in that, The receiving groove formed by the skirt body accommodates the dynamic valve core and the transmission valve core and has a clearance fit.

8. A pre-tightening structure of a disc valve according to claim 1, characterized in that, The outlet of the secondary oil passage hole is located on the top wall surface of the receiving cavity between the main oil passage hole and the axis of the static valve core.

9. The pre-tightening structure of a disk valve according to claim 1, characterized in that A friction sleeve is slidably sleeved on the transmission shaft, and the upper and lower parts of the friction sleeve are respectively embedded in the shaft hole of the valve body and the central hole of the static valve core.

10. A pre-tightening structure of a disc valve according to claim 1, characterized in that, A shaft convex part protrudes from the center of the lower surface of the transmission valve core. A receiving groove is provided at the center of the upper surface of the valve cover located in the receiving cavity. A friction pad is fixedly installed in the receiving groove. A supporting groove is formed on the upper surface of the friction pad. The friction pad is clamped between the shaft convex part of the transmission valve core and the receiving groove of the valve cover. The friction pad is used to support the rotation of the transmission valve core and reduce the rotational friction force.

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