A clearance valve and its control method

Abstract

The present invention discloses a clearance valve, which includes a valve body, a first driving rod and a second driving rod. Both the first driving rod and the second driving rod are slidably connected to the valve body up and down. The clearance valve further includes a linkage driving device. Both the first driving rod and the second driving rod are connected to the linkage driving device. The linkage driving device includes a rotating body, and the rotating body includes a variable diameter portion. The variable diameter portion includes a first position and a second position, and the relative heights of the first position and the second position are different. Both the first driving rod and the second driving rod are in contact with the variable diameter portion. By using a single linkage driving device, the present invention can realize the linkage control of two driving rods. Compared with the method of individually controlling a single valve core by a single driving member, the present invention not only has a lower cost, but also has a lower error and higher precision. At the same time, the present invention also provides a control method for the above-mentioned clearance valve.

Description

Technical Field

[0001] The present invention relates to a valve structure, in particular to a gap valve used in a coater. Background Art

[0002] In the production process of lithium-ion batteries, the coating process is the most important step in determining the initial morphology of the surface of the electrode sheet in the electrode sheet production link, and is also a key process directly affecting various performances such as the safety, capacity, and consistency of the battery. Coating is to evenly, continuously or intermittently coat the prepared paste-like viscous slurry on a substrate (aluminum foil or copper foil) to ensure the thickness consistency at each coating position and control the coating thickness within the tolerance range required by the process. Currently, there are mainly two methods for lithium-ion coating: transfer type and extrusion type. Among them, the extrusion type is a method of achieving intermittent coating by using a coater. In extrusion coating, the structure of the gap valve is crucial for controlling the dimensional accuracy and thickness consistency of intermittent coating.

[0003] However, the existing gap valves usually control the lifting of the valve core through a cylinder driven by lifting, so as to control the on-off of the discharge port. Since the piston rod in the cylinder body of the cylinder is supported by the air pressure in the cylinder body, and the liquid input from the feed port in the buffer cavity of the valve itself has pressure, the pushing stroke of the piston rod will be affected, the piston rod cannot be accurately controlled, and the discharge is inaccurate. Even if the method of driving the screw to lift by a motor to control the valve core can alleviate the above problems to a certain extent, it will still affect the output. In addition, the existing gap valves all drive the movement of two valve cores through two independent driving units respectively, resulting in a large number of driving units and high costs; and the movement of the two valve cores will be related, and there will inevitably be errors in the start-stop relationship between different driving units. Summary of the Invention

[0004] The technical problem to be solved by the present invention is: to provide a gap valve to solve one or more technical problems existing in the prior art, and at least provide a beneficial choice or creation condition

[0005] The solution of the present invention to solve its technical problem is: a gap valve, including: a valve body, a first driving rod, a second driving rod, and a linkage driving device. The first driving rod and the second driving rod are both slidably connected to the valve body along a first direction. The linkage driving device includes a rotating body, the rotating body is provided with a guiding portion, the first driving rod and the second driving rod are both in contact with the guiding portion, the guiding portion includes a first position and a second position, there is a distance between the first position and the second position along the first direction, and the rotating body rotates to move the first driving rod or the second driving rod.

[0006] The beneficial effects of the present invention are as follows: By using a linkage driving device, the present invention can achieve the linkage control of two driving rods. Compared with the method of individually controlling a single valve core by a single driving member, it not only has a lower cost, but also has a lower error and higher precision. Moreover, through the rigid connection between the rotating body and the driving rod, the stroke of the driving rod can be accurately controlled, ensuring a stable output during coating.

[0007] As a further improvement of the above technical solution, the rotating body is a disc, the axis of the disc is parallel to the first direction, and a chute is provided on the circumferential side of the disc. It can be understood that the disc includes an upper surface, a lower surface, and a circumferential side surface, and the upper surface and the lower surface are connected by the circumferential side surface. The circumferential side surface is provided with a chute, and the surface of the chute facing the first driving rod or the second driving rod forms the guiding portion. Using the disc as the rotating body, during use, by simultaneously abutting the two opposite surfaces of the chute against the relative parts of the first driving rod and the second driving rod, a stable supporting effect can be achieved.

[0008] As a further improvement of the above technical solution, it further includes a first connecting rod and a second connecting rod; the head end of the first connecting rod is fixed on the first driving rod, and the tail end is embedded in the chute; the head end of the second connecting rod is fixed on the second driving rod, and the tail end is embedded in the chute. Using the first connecting rod and the second connecting rod to realize the connection between the driving rod and the disc can simplify the structure of the gap valve.

[0009] As a further improvement of the above technical solution, the chute is an inclined annular structure, and the included angle between the central normal of the chute and the axis of the rotating body is α, where 0° < α < 90°, and the first position and the second position are respectively located on opposite sides of the disc. The chute is a complete inclined ring, so that after the disc rotates one circle, the relative moving distances of the first driving rod and the second driving rod are the same.

[0010] In addition to adopting the inclined annular structure, the chute includes a first horizontal section, a second horizontal section, and an inclined section. There is a distance between the first horizontal section and the second horizontal section along the first direction, and the inclined section connects the first horizontal section and the second horizontal section. The first position is located on the first horizontal section, and the second position is located on the second horizontal section. By setting the chute as a structure of two horizontal sections and an inclined section, it is convenient to adjust the action rhythm of the first driving rod and the second driving rod by adjusting the lengths of the first horizontal section and the second horizontal section.

[0011] As a further improvement of the above technical solution, the first driving rod is located on the left side of the disc, and the second driving rod is located on the right side of the disc. During use, since the first driving rod and the second driving rod will be subjected to the reaction force of the material, when the chute is inclined, the two driving rods respectively abut against both sides of the chute. The acting forces of the two driving rods on the chute will cause the disc to have a tendency to rotate, but the directions of the rotational tendencies of the disc caused by the two driving rods are opposite, which plays a role of mutual restraint, thereby preventing the disc from rotating due to the reaction force of the material, and further preventing the disc from rotating due to the thrust of the material on the driving rod, thereby improving the control accuracy of the gap valve.

[0012] As a further improvement of the above technical solution, the cross-section of the chute is semi-circular, and a hemispherical body is provided at the end of the first connecting rod, and the hemispherical body is embedded in the chute. By setting the chute to be semi-circular and simultaneously providing a hemispherical body at the end of the first connecting rod, the friction between the first connecting rod and the chute can be reduced, and the control accuracy of the gap valve can be improved.

[0013] The rotating body can be a cylinder in addition to a disc. The cylinder includes a left side surface, a right side surface and an outer end surface. The outer end surface includes a cam portion or a groove. The bottoms of the first driving rod and the second driving rod both include abutting heads, and the abutting heads abut against the cam portion or the groove. By using a cylinder, the first driving rod and the second driving rod can directly abut against the outer end surface of the cylinder, eliminating the structure of the connecting rod.

[0014] As a further improvement of the above technical solution, a rotation angle detection unit is further included, and the rotation angle detection unit is connected to the rotating body. By adding a rotation angle detection unit, the rotation angle of the rotating body can be monitored in real time, which is convenient for control.

[0015] As a further improvement of the above technical solution, the rotation angle detection unit includes a pressure sensor and an elastic member. One end of the elastic member abuts against the rotating body, and the other end abuts against the pressure sensor. By using the elastic member and the pressure sensor, the rotation angle of the rotating body can be detected in real time, thereby improving the control accuracy of the gap valve. At the same time, the elastic member can also play a buffering role in the movement of the first driving rod and the second driving rod.

[0016] At the same time, the present invention also provides a control method for a gap valve, which includes the above-mentioned gap valve. This method controls the rotation speed of the rotating body to control the discharge frequency of the gap valve. The specific control method will be discussed in detail in the following embodiments. Description of the Drawings

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly describe the drawings required for use in the description of the embodiments. Obviously, the described drawings are only a part of the embodiments of the present invention, rather than all embodiments. Without creative efforts, those skilled in the art can also obtain other design solutions and drawings based on these drawings.

[0018] Figure 1 is a three-dimensional schematic diagram of the clearance valve of the present invention;

[0019] Figure 2 is a sectional view of the clearance valve of the present invention;

[0020] Figure 3 is a front view of the disc of the present invention;

[0021] Figure 4 is a three-dimensional schematic diagram of the disc of the present invention;

[0022] Figure 5 is a developed view of the end face of the disc of the present invention; Figure 6 is a partial structural schematic diagram of the present invention;

[0023] Figure 7 is a structural schematic diagram of another embodiment of the rotating body of the present invention. Specific Embodiments

[0024] The following will clearly and completely describe the concept, specific structure and technical effects generated by the present invention in combination with the embodiments and drawings, so as to fully understand the purpose, features and effects of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, other embodiments obtained by those skilled in the art without creative efforts all fall within the scope of protection of the present invention. The preferred embodiments of the present invention are shown in the drawings. The role of the drawings is to supplement the description in the text part of the specification, enabling people to intuitively and vividly understand each technical feature and the overall technical solution of the present invention, but it cannot be understood as a limitation on the scope of protection of the present invention.

[0025] In the description of the present invention, it should be understood that for the orientation description, such as the orientation or positional relationship indicated by up, down, front, back, left, right, etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0026] In the description of the present invention, "several" means one or more, "multiple" means more than two, and understandings such as "greater than", "less than", and "exceeding" do not include the corresponding number, while understandings such as "above", "below", and "within" include the corresponding number. If there is a description of "first" and "second", it is only for the purpose of distinguishing technical features and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence relationship of the indicated technical features.

[0027] In the description of the present invention, unless otherwise clearly defined, words such as "arrangement", "installation", and "connection" should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above words in the present invention in combination with the specific content of the technical solution. At the same time, each technical feature in the present invention can be interactively combined on the premise of not conflicting with each other.

[0028] The following further elaborates on the embodiments of the present application in conjunction with the accompanying drawings.

[0029] Embodiment 1: Refer to Figures 1 to 2 , the present application provides a gap valve for a coating machine. The gap valve mainly includes a valve body 100. The valve body 100 includes a valve seat 130 and a first valve cavity 110 and a second valve cavity 120 located on the left and right sides of the valve seat 130 respectively. The first valve cavity 110 includes a first buffer cavity 111, a first valve core 112, and a discharge port 113. The second valve cavity 120 includes a second buffer cavity 121, a second valve core 122, a feed port 123, and a return port 124. The first buffer cavity 111 and the second buffer cavity 121 are in communication with each other. The first valve core 112 is located between the first buffer cavity 111 and the discharge port 113, the second valve core 122 is located between the return port 124 and the second buffer cavity 121, and the feed port is in communication with the second buffer cavity 121.

[0030] A first driving rod 210 is provided in the first valve cavity 110, and a second driving rod 220 is provided in the second valve cavity 120. The top end of the first driving rod 210 is fixedly connected to the first valve core 112, and the lower end of the first driving rod 210 passes through the first valve cavity 110 and is slidably connected to the valve seat 130; the top end of the second driving rod 220 is fixedly connected to the second valve core 121, and its lower end passes through the second valve cavity 120 and is slidably connected to the valve seat 130.

[0031] In this embodiment, both the first driving rod 210 and the second driving rod 220 are slidably connected to the valve seat 130 along the up and down direction. Here, the up and down direction is defined as the first direction. It can be understood that the up and down direction is a relative direction and does not refer to the direction of gravity.

[0032] In the existing gap valve, two independent driving mechanisms (such as cylinders, etc.) are used to control the rising and falling of the first driving rod 210 and the second driving rod 220 respectively, so as to control the on-off state change of the discharge port 113 and the return material port 124. However, using two independent driving mechanisms will not only increase the cost of the equipment, but also there is a certain correlation between the movements of the two valve cores according to the actual production requirements. However, since the two driving mechanisms are independently controlled, there will inevitably be a deviation between the actual start-stop time of each driving mechanism and the start-stop time set by the controller, which will further lead to the relative positions of the driving rods driven by the two driving mechanisms cannot be effectively controlled. For the convenience of understanding, an example is given: If the program set in the controller is to make the second driving rod 220 descend instantaneously when the first driving rod 210 ascends, in fact, the driving mechanism controlling the descent of the second driving rod 220 may have a delayed drive or an early drive. When the first driving rod 210 ascends instantaneously, the second driving rod 220 does not immediately descend, or starts to descend before the first driving rod 210 ascends. Then, the relative position relationship between the first driving rod 210 and the second driving rod 220 cannot be accurately controlled. If the movements of the first driving rod 210 and the second driving rod 220 are controlled by the same driving mechanism, even if there is a deviation between the actual start-stop time of the driving mechanism and the start-stop time set by the controller, the movements of the first driving rod 210 and the second driving rod 220 are advanced or delayed simultaneously, and their relative positions will not be affected by the delay or advance of the driving work of the driving mechanism, which improves the accuracy of the interlocking control of the feed port and the discharge port, and further improves the production accuracy of the product.

[0033] Therefore, the present invention innovatively utilizes a set of interlocking driving device 300, and by using this interlocking driving device 300, the accurate movement of the first driving rod 210 and the second driving rod 220 can be realized, and the associated movement of the two can be achieved.

[0034] Specifically, this interlocking driving device 300 includes a driving motor 310, a disc 320 and a rotating shaft. The valve seat 130 includes a lower fixing plate 131 and an upper fixing plate 132. The driving motor 310 is installed on the lower fixing plate 131, and the disc 320 is installed on the upper fixing plate 132 through a bearing. The driving motor 310 is drivingly connected to the disc 320 through the rotating shaft. The disc 320 is located between the first valve cavity 110 and the second valve cavity 120.

[0035] See Figure 3, the disc 320 is a flat disc-shaped structure. The center line of the disc 320 is vertically upward, that is, parallel to the first direction and also parallel to the centers of the two driving rods. The disc 320 includes a lower surface 321, an upper surface 322, and a peripheral side 323. The upper surface 321 and the lower surface 322 are circular (of course, without affecting the function, the shapes of the upper and lower surfaces can be variable), and the peripheral side 323 is an annular shape. A chute 330 that is recessed inward is machined in the peripheral side 323. The chute 330 is an inclined annular structure, that is, the central normal of the chute 330 forms a certain angle with the center line of the disc, and this angle is greater than 0° and less than 90°. Specifically, the cross-section of the chute 330 is semi-circular. Since the chute 330 is inclined relative to the disc 320, a first position 331 and a second position 332 are formed on the disc 320. Among them, the first position 331 is located at the uppermost end of the disc 320, and the second position 332 is located at the lowermost end of the disc. Two inclined semi-annular arc surfaces are formed between the first position 331 and the second position 332, and the two semi-annular arc surfaces form the chute 330.

[0036] Refer back to Figures 1 to 2 , first connecting rods 211 and second connecting rods 221 are respectively fixedly provided at the lower parts of the first driving rod 210 and the second driving rod 220. The first connecting rod 211 and the second connecting rod 221 both extend along the left-right direction. The first connecting rod 211 can be integrally formed with the first driving rod 210, or fixed to the first driving rod 210 by means such as welding, bonding, and bolt fixing.

[0037] The head end of the first connecting rod 211 is tightly fixed together with the first driving rod 210, and a hemisphere is provided at the tail end of the first connecting rod 211. The outer diameter of the hemisphere is equal to the inner diameter of the chute 330, or the hemisphere is in clearance fit with the chute, and at the same time, the hemisphere abuts against the chute 330. Similarly, the second connecting rod 221 has the same structure as the first connecting rod 211.

[0038] So far, through the first connecting rod 211 and the second connecting rod 221, the linkage driving device 300 can be connected to the driving of the two valve cores. The following describes how this linkage driving device controls the two valve cores.

[0039] See Figure 2, after the installation of the entire gap valve is completed, it is assumed that the hemisphere of the first connecting rod 211 is just located at the first position 331 of the chute 330, and the hemisphere of the second connecting rod 221 is just located at the second position 332 of the chute 330. That is, the first driving rod 210 is at the highest point of its own stroke, and the first valve core 112 is in the open state; while the second driving rod 220 is at the lowest point of its own stroke, and the second valve core 122 is in the closed state. At this time, the material can enter from the feed port 123, and then pass through the second buffer chamber 121 and the first buffer chamber 111 in sequence and be discharged from the discharge port 113. At this time, the return port 124 is in the closed state.

[0040] When it is necessary to switch the working states of the first valve core 112 and the second valve core 122, only need to control the disc 320 to rotate 180° by the driving motor 310. When the disc 320 rotates, under the action of the chute 320, the hemisphere of the first connecting rod 211 gradually moves from the first position 331 to the second position 332. On the contrary, the hemisphere of the second connecting rod 221 gradually moves from the second position 332 to the first position 331. After the disc 320 rotates 180°, the first driving rod 210 reaches the lowest point of its own stroke, and the first valve core 112 is in the closed state; while the second driving rod 220 reaches the highest point of its own stroke, and the second valve core 122 is in the open state. At this time, the material continues to enter from the feed port 123, and then is discharged from the return port 124 after passing through the second buffer chamber 121. At this time, the discharge port 113 is in the closed state.

[0041] It can be seen from this that the gap valve of this embodiment only needs a driving motor to drive the disc 320 to rotate to realize the linkage control of the two valve cores. Compared with the structure of two driving parts adopted in the prior art, it is obvious that one driving part can be saved, effectively reducing the overall cost of the gap valve. Moreover, the actions between the two valve cores are realized by physical rigid connection for linkage control, and there is almost no starting error in the actions, so the synchronization is better, and the processing accuracy of the coater is higher after being applied to the coater.

[0042] In this embodiment, the first valve cavity 110 and the second valve cavity 120 are symmetrically arranged on the valve seat 130 with respect to left and right, so that the phase angle between the first driving rod 210 and the second driving rod 220 is 180°. In this embodiment, since the chute 330 is relatively inclined, the two driving rods respectively abut against both sides of the chute. When working, under the pressure of the material, the two driving rods will generate a force along the first direction on the chute. Since the direction of this force has a certain angle with the central normal of the chute, this force will cause the disc to have a tendency to rotate. However, in this embodiment, the two driving rods are arranged on both sides of the disc. Since the directions of the rotation tendencies generated by the forces of these two driving rods on the disc are opposite, a mutual restraint effect is achieved, thereby preventing the disc from rotating due to the reaction force of the material, and further preventing the disc from rotating due to the thrust of the material on the driving rod, thereby improving the control accuracy of the gap valve.

[0043] In some other embodiments, the relative positions of the first valve cavity 110 and the second valve cavity 120 can be adjusted. For example, the phase angle between the first driving rod 210 and the second driving rod 220 is 90°. Accordingly, by simply adjusting the shape and trajectory of the chute 330 on the disc 320, the control of the linkage relationship between the first valve core 112 and the second valve core 122 can also be achieved.

[0044] In addition, in this embodiment, when the disc 320 rotates at a constant speed, the opening and closing cycles of the first valve core 112 and the second valve core 122 are the same. Thus, when applied to a coater, the length of the coated part is the same as the length of the uncoated part.

[0045] However, under some processing requirements, the lengths of the coated part and the uncoated part need to be different. In order to achieve the above function, in this embodiment, it can be achieved by controlling the speed of the disc 320 at different time periods or by the operation mode of "pause - rotate - pause". Through the above control method, the on - off times of the first valve core 112 and the second valve core 122 can be made different. For example, if the length of the coated part needs to be larger, then by extending the opening time of the first valve core 112 and shortening the opening time of the second valve core 122. That is, when the hemisphere of the first connecting rod 211 is in the first position 331, the rotation of the disc 320 is paused for a time T1, and when the hemisphere of the second connecting rod 221 is in the first position 331, the rotation of the disc 320 is paused for a time T2. As long as T1 > T2, the length of the coated part can be made larger. Or, adjust the rotation speed of the disc 320 at different positions. For example, slow down the speed of the first connecting rod 211 from the first position 331 to the second position 332, while speed up the speed of the second connecting rod 221 from the first position 331 to the second position 332.

[0046] It can be seen from this that when it is necessary to adjust the rotation state or speed of the disc 320 in order to achieve the on-off time difference between the first valve core 112 and the second valve core 122. This places higher requirements on the drive motor 310 and indirectly increases the procurement cost of the motor.

[0047] In order to reduce the requirements on the drive motor 310 and further reduce costs. The present invention discloses a gap valve with another structure.

[0048] Embodiment 2, a gap valve, see Figure 4 , in this embodiment, the overall structure of the gap valve is basically the same as that of Embodiment 1, and also includes a valve body 100, two drive rods and a basically the same linkage drive device 300. The main difference lies in the different structure of the chute 330.

[0049] In this embodiment, the chute 330 is mainly composed of a first horizontal section 333, a second horizontal section 334 and an inclined section 335. The first horizontal section 333 is close to the upper surface 321 of the disc 320, and the second horizontal section 334 is close to the lower surface 322 of the disc 320, that is, the first horizontal section 333 is located above the second horizontal section 334, and the inclined section 335 is connected to the first horizontal section 333 and the second horizontal section 334. Understandably, in this embodiment, both ends of the first horizontal section 333 are connected to both ends of the second horizontal section 334 through the inclined section 335. The chute 330 is still a closed loop structure connected end to end. The first position 331 is located on the first horizontal section 333, and the second position 332 is located on the second horizontal section 334. Assuming the length of the first horizontal section 333 is D1 and the length of the second horizontal section 334 is D2, when the disc 320 rotates at a constant speed, only by adjusting the lengths of D1 and D2, the on-off time difference between the first valve core 112 and the second valve core 122 can be achieved.

[0050] Compared with Embodiment 1, in this Embodiment 2, only an ordinary constant-speed motor needs to be used to achieve a difference in the on-off time between the first valve core 112 and the second valve core 122, so that the coating machine in application can coat a coating range with different lengths.

[0051] As a further preferred embodiment, in order to improve the control accuracy of the clearance valve, the clearance valve further includes a rotation angle detection unit 400. The rotation angle detection unit 400 can be integrated into the drive motor 310, for example, a servo motor with monitoring is adopted. By adding the rotation angle detection unit 400, the actual rotation angle of the disc 320 is detected in real time by the rotation angle detection unit 400, and the driving member for driving the rotation of the disc is finely adjusted to improve the accuracy of the disc rotation.

[0052] Alternatively, referring to Figure 6 , the rotation angle detection unit 400 includes a pressure sensor 410 and an elastic member 420. The elastic member 420 can be a compression spring. A convex block 324 can be provided on the end face of the disc 320. One end of the compression spring abuts against the convex block, and the other end abuts against the pressure sensor 410.

[0053] When the disc 320 rotates, since the pressure sensor 410 is relatively fixed on the valve seat, the relative position between the convex block and the pressure sensor 410 will change, so that the compression amount of the compression spring changes. When the compression spring is at different compression amounts, its elastic force is also different. The magnitude of the elastic force is obtained by the pressure sensor 410, and then the rotation angle of the disc 320 is calculated. Moreover, since the compression spring is provided, it can play a buffering role in the rotation of the disc 320, and thus buffer the up and down movement of the two drive rods.

[0054] Of course, the above rotation angle detection unit with an elastic member is generally not applicable to a continuously rotating disc. For example, in the first embodiment above, the disc usually rotates in a continuous one-way rotation mode during operation. When the disc rotates locally during operation, the rotation angle of the disc can be monitored by adopting the above rotation angle detection unit with an elastic member. In the above embodiment, the center line of the disc 320 is parallel to the center lines of the two drive rods. In order to enable the disc 320 to synchronously drive the two drive rods to move up and down when rotating, generally a transverse connecting rod structure needs to be added. In some other embodiments, the disc 320 can be replaced by other rotating bodies, so that the connecting rod structure can be omitted.

[0055] For example, referring to Figure 7, the rotating body is a cylinder 320a, the center line of the cylinder 320a is in the left-right direction, the cylinder 320a is provided with a left side surface, an outer end surface 321a and a right side surface, and the outer end surface 321a is connected between the left side surface and the right side surface. At this time, the direction perpendicular to the center line of the cylinder is defined as the first direction, that is, the first direction is still the up-down direction. At the same time, the length of the cylinder should be not less than the distance between the two driving rods, so that the two driving rods can be in contact with the outer end surface at the same time. A driving motor is connected outside the left side surface or the right side surface, and the driving motor directly drives the cylinder to rotate. Of course, the cylinder 320a can rotate relative to the valve seat. Since it is necessary to ensure that the two driving rods can be in contact with the outer end surface at the same time, the two valve cavities can only be arranged along the direction of the center line of the cylinder. In addition, in order to enable the first driving rod and the second driving rod to move in the up-down direction as the cylinder rotates, a guiding portion needs to be provided on the outer end surface of the cylinder. The guiding portion can be a cam structure or a groove. The guiding portion in this embodiment is equivalent to the sliding groove in the above-mentioned Embodiment 1 and Embodiment 2. For example, the guiding portion adopts a groove structure, that is, grooves 330a with different depths are dug on the outer end surface 321a. It can be understood that two grooves 330a can be provided, and the two grooves 330a correspond to the first driving rod and the second driving rod respectively. Define that in the above grooves, the one with the maximum depth is the first position, and the one with the shallowest depth is the second position. In order to enable the first driving rod and the second driving rod to produce different action effects, the shapes of the two grooves should be different. For example, the first position of the groove of the first driving rod can correspond to the second position of the groove of the second driving rod. In this way, when the cylinder rotates, the first driving rod and the second driving rod can obtain different motion effects.

[0056] Of course, in order to make the cooperation between the first driving rod and the groove better, the shape of the groove can be set and a contact head can be provided at the bottom of the first driving rod and other structures. For specific methods, reference can be made to the above-mentioned Embodiment 1 or Embodiment 2.

[0057] Similarly, in addition to the groove, a cam may be provided on the outer end surface. The maximum outer diameter of the cam is defined as the first position, and the minimum outer diameter is defined as the second position. The cam may be integrally formed with the cylinder or a peripherally mounted fixed cam. When installed separately, for example, the cam includes a socket hole and is directly sleeved on the outer end surface of the cylinder. The peripherally mounted method facilitates the replacement of the cam to obtain different adjustment effects. It can be understood that generally there are two cams, and the installation positions of the two cams respectively correspond to the first driving rod and the second driving rod. By adjusting the outer contours of the two cams, the movement trajectories of the first driving rod and the second driving rod can be adjusted, thereby controlling the linkage relationship between the first valve core and the second valve core.

[0058] Further preferably, in order to enable the first driving rod to be better connected to the cam, a sheave may be provided at the bottom of the first driving rod. The sheave includes a V-shaped card slot, so that the outer end surface of the cam can be stuck in the card slot. When the cam rotates, the friction between the cam and the first driving rod can be significantly reduced, making the lifting action of the first driving rod more stable and smooth.

[0059] The above specifically describes the preferred embodiments of the present invention, but the present invention is not limited to the described embodiments. Those skilled in the art can make various equivalent variations or substitutions without departing from the spirit of the present invention, and these equivalent variations or substitutions are all included within the scope defined by the claims of this application.

Claims

1. A clearance valve, characterized in that: Comprising: A valve body, a first drive rod, a second drive rod, and a linkage drive device. The first drive rod and the second drive rod are both slidably connected to the valve body along a first direction. The linkage drive device includes a rotating body provided with a guiding portion. The first drive rod and the second drive rod are both in contact with the guiding portion. The guiding portion includes a first position and a second position, and there is a spacing between the first position and the second position along the first direction. The rotating body rotates to move the first drive rod or the second drive rod. The rotating body is a disc, the axis of the disc is parallel to the first direction, and a chute is provided on the circumferential side of the disc. The surface of the chute facing the first drive rod or the second drive rod forms the guiding portion. It further includes a first connecting rod and a second connecting rod. The head end of the first connecting rod is fixed on the first drive rod, and the tail end is embedded in the chute. The head end of the second connecting rod is fixed on the second drive rod, and the tail end is embedded in the chute. The chute is of an annular structure, and the included angle between the central normal of the chute and the axis of the rotating body is α, where 0° < α < 90°. The first position and the second position are respectively arranged on opposite sides of the disc.

2. The clearance valve according to claim 1, characterized in that: The chute includes a first horizontal section, a second horizontal section, and an inclined section. There is the spacing between the first horizontal section and the second horizontal section along the first direction. The first horizontal section and the second horizontal section are connected by the inclined section. The first position is located in the first horizontal section, and the second position is located in the second horizontal section.

3. The clearance valve according to any one of claims 1 to 2, characterized in that: The first drive rod and the second drive rod are relatively distributed on both sides of the disc.

4. The clearance valve according to any one of claims 1 to 2, characterized in that: The cross-section of the chute is semi-circular, and a hemispherical body is provided at the tail end of the first connecting rod. The hemispherical body is embedded in the chute.

5. The clearance valve according to claim 1, characterized in that: It further includes a rotation angle detection unit, and the rotation angle detection unit is connected to the rotating body.

6. The clearance valve according to claim 5, characterized in that: The rotation angle detection unit includes a pressure sensor and an elastic member. One end of the elastic member is in contact with the rotating body, and the other end is in contact with the pressure sensor.

7. A control method for the clearance valve according to any one of claims 1 to 6, characterized in that: By controlling the rotation speed of the rotating body, the discharging frequency of the gap valve is controlled.

Images