High-precision grinding apparatus for sealing pair of triple eccentric butterfly valve

Abstract

Provided is a high-precision grinding apparatus for a sealing pair of a triple eccentric butterfly valve, belonging to the technical field of grinding apparatuses. The high-precision grinding apparatus comprises an apparatus body (51), an apparatus base (10), a rotating base (101), a cross beam (52), a grinding-head slide carriage (54), an operating platform (56), a hydrostatic‑hydrodynamic grinding-head motorized spindle (103), an X-axis movement assembly, a Z-axis movement assembly (55), and a swing-angle driving mechanism, wherein the X-axis movement assembly is configured to drive a transverse slide carriage (53) to move, and the swing-angle driving mechanism is configured to drive the rotating base (101) to rotate relative to the apparatus base (10). By means of providing the swing-angle driving mechanism, the X-axis movement assembly and the Z-axis movement assembly (55), a grinding wheel (104) always moves on a sealing surface, which is subjected to grinding, of a workpiece during grinding, that is, following grinding is performed. The ideal surface finish of the ground surface of the sealing pair reaches Ra0.2 or less, and the roundness of inner and outer ground circles reaches 0.003 mm. The machining time is fully utilized, improving the grinding efficiency; the grinding force is uniform, improving the grinding precision; and the compatibility and sealing performance of the sealing pair of the triple eccentric butterfly valve are ensured, thereby achieving 100％ sealing pair interchangeability.

Description

A high-precision grinding equipment for triple eccentric butterfly valve sealing pairs Technical Field

[0001] This application belongs to the field of grinding equipment technology and relates to a high-precision grinding equipment for a triple eccentric butterfly valve sealing pair. Background Technology

[0002] Triple eccentric butterfly valves, as a new type of high-performance valve, are increasingly widely used in various industries. These valves offer a range of advantages, including excellent sealing performance, low opening resistance, wear compensation, and self-locking upon closure. However, the shape, size, and surface quality of the sealing surface are key factors affecting sealing performance, and achieving high-quality machining of the sealing surface has always been a challenge for manufacturers.

[0003] Currently, the grinding process for triple eccentric butterfly valves mainly adopts multi-axis interpolation, which results in frequent feed and discharge actions, which is not conducive to ensuring accuracy and causes excessively long ineffective grinding time. Summary of the Invention

[0004] To improve grinding accuracy and efficiency by performing follow-up grinding on the sealing pair, a high-precision grinding device for triple eccentric butterfly valve sealing pairs is provided.

[0005] This application provides a high-precision grinding equipment for triple eccentric butterfly valve sealing pairs, specifically implemented using the following technical solution: A high-precision grinding equipment for triple eccentric butterfly valve sealing pairs includes a machine body, a machine base, a rotating base, a crossbeam, a grinding head slide, a worktable for clamping the triple eccentric butterfly valve sealing pairs, a hydrostatic grinding head electronic shaft, an X-axis moving assembly, a Z-axis moving assembly, and a swing angle driving mechanism. The crossbeam is mounted on the machine body, and the machine base is fixed with a transverse slide, which slides horizontally with the crossbeam. The X-axis moving assembly drives the transverse slide to move, and the machine base is fixed with a horizontally positioned fixed shaft. The rotating base is equipped with a rotating sleeve, which is coaxially rotatably connected to the fixed shaft. The swing angle driving mechanism drives the rotating base to rotate relative to the machine base. The grinding head slide slides in a sliding engagement with the rotating base, and the Z-axis moving assembly drives the grinding head slide to move. The grinding head slide is equipped with a hydrostatic grinding head electronic shaft, and a grinding wheel is provided at the end of the hydrostatic grinding head electronic shaft. The worktable is mounted on the machine body and located below the hydrostatic grinding head electronic shaft.

[0006] Through the above technical solution, by setting up a swing angle drive mechanism, an X-axis moving component, and a Z-axis moving component, the worktable can achieve workpiece position control. When grinding the conical surface of the sealing pair, the traditional interpolation grinding method can be eliminated. The swing angle drive mechanism drives the rotating seat, Z-axis moving component, grinding head slide, hydrostatic grinding head electronic axis, and grinding wheel to rotate and position as a whole according to the workpiece taper requirements. Only one coordinate needs to be moved along the Z-axis to complete the following grinding of the conical surface. This avoids the grinding errors caused by the differences in dynamic response characteristics and motion accuracy of each coordinate axis in the traditional interpolation grinding method. Higher grinding shape accuracy and grinding surface quality can be obtained, so that the ideal surface finish of the grinding surface of the sealing pair can reach Ra0.2 or less.

[0007] Secondly, the grinding wheel always moves on the workpiece's grinding sealing surface during the grinding process, making full use of the processing time, improving grinding efficiency, ensuring uniform grinding force, improving grinding accuracy, and also ensuring the compatibility and sealing performance of the triple eccentric butterfly valve sealing pair, achieving 100% interchangeability of the sealing pair.

[0008] Optionally, it also includes a first locking mechanism. The swing angle driving mechanism includes a drive motor, a first gear, and an arc-shaped rack. The drive motor is mounted on the base, the first gear is mounted on the output shaft of the drive motor, and the arc-shaped rack is fixed to the rotating seat. The curvature center of the arc-shaped rack is located on the axis of the rotating sleeve. The arc-shaped rack meshes with the first gear. The first locking mechanism includes a first driving assembly and two first driving discs. The fixed shaft is provided with the first driving discs. The first driving discs are coaxially arranged with the rotating sleeve. The outer edge of the first driving disc is provided with a first conical surface. The inner wall of the rotating sleeve is coaxially fixed with two first fixing rings. The inner diameter of the first fixing ring is provided with a second conical surface. The first driving assembly is used to drive the two first driving discs to move closer to each other until the first conical surface and the second conical surface are engaged.

[0009] Through the above technical solution, firstly, the gear matching accuracy is higher than that of traditional worm gear matching accuracy through the cooperation of the arc rack and the first gear, which can improve the swing angle accuracy and grinding accuracy of the grinding wheel. Secondly, after the swing angle is adjusted, the two first drive discs approach each other through the first locking mechanism to clamp the first fixed ring, thereby realizing the fixed connection between the fixed shaft and the rotating sleeve, locking the rotating sleeve, so as to cope with the impact load and reduce the wear caused by the impact load on the arc rack and the first gear, thus ensuring the stability of the matching accuracy.

[0010] Furthermore, the coaxiality of the fixed shaft and the rotating sleeve is improved by the cooperation of the first and second conical surfaces, thereby improving the rotational accuracy of the rotating sleeve.

[0011] Optionally, the first drive assembly includes a first lead screw, a first drive structure, and a guide rod, wherein the first lead screw is coaxially arranged with the rotary sleeve, the first lead screw is threadedly connected to the first drive disc, the threads of the two first drive discs are arranged in opposite directions, the first drive structure is used to drive the first lead screw to rotate, the guide rod is fixedly connected to the fixed shaft, and the guide rod slides through the first drive disc.

[0012] With the above technical solution, when the first drive structure drives the first lead screw to rotate, it drives the two first drive discs to move towards each other through a threaded connection, thereby clamping the first fixed ring. The guide rod is used to limit the spin of the first drive disc.

[0013] Optionally, the first drive assembly includes a first lead screw, a first drive structure, and a rotating ring. The rotating ring is coaxially fixed with the first drive disk, and the outer circumferential surface of the rotating ring is in contact with the inner circumferential surface of the rotary sleeve. The first lead screw is eccentrically disposed with the rotary sleeve and is threadedly connected to the first drive disk. The threads of the two first drive disks are arranged in opposite directions. The first drive structure is used to drive the first lead screw to rotate.

[0014] With the above technical solution, when the first drive structure drives the first lead screw to rotate, it drives the two first drive discs to move towards each other through a threaded connection, thereby clamping the first fixed ring.

[0015] By ensuring the contact between the rotating ring and the inner circumferential surface of the slewing sleeve, the eccentric rotation of the first drive disc under the frictional force of the first lead screw is restricted, thereby ensuring that the first lead screw can stably drive the first drive disc to move axially.

[0016] Optionally, a second locking mechanism is also included. The second locking mechanism comprises a second driving assembly and two second driving discs. The fixed shaft is provided with the second driving discs, which are coaxially arranged with the rotating sleeve. The two second driving discs are located above and below the first driving disc, respectively. A third conical surface is provided at the outer edge of each second driving disc. Two second fixing rings are coaxially fixed to the inner wall of the rotating sleeve, located above and below the first fixing ring, respectively. A fourth conical surface is provided at the inner diameter of each second fixing ring. The second driving assembly is used to drive the two second driving discs to move away from each other until the third conical surface engages with the fourth conical surface. The first driving assembly includes a first lead screw and a first driving structure. The second driving assembly includes a second lead screw and a... The second drive structure has a first lead screw and a second lead screw, both parallel to the axis of the rotating sleeve. Both the first and second lead screws are eccentrically positioned relative to the rotating sleeve. The first lead screw is threadedly connected to the first drive disc, and the threads of the two first drive discs are arranged in opposite directions. The first drive structure drives the first lead screw to rotate. The second lead screw is threadedly connected to the second drive disc, and the threads of the two second drive discs are arranged in opposite directions. The second drive structure drives the second lead screw to rotate. The first drive disc has a through-hole, and the outer circumferential surface of the second lead screw has a second mating portion that conforms to the inner wall of the first guide hole. The second drive disc has a through-hole, and the outer circumferential surface of the first lead screw has a first mating portion that conforms to the inner wall of the second guide hole.

[0017] Through the above technical solution, firstly, by setting a first locking mechanism and a second locking mechanism, the first driving disc and the second driving disc respectively cooperate with the first fixed ring and the second fixed ring, with a large cooperation area, thereby greatly improving the braking effect on the rotating sleeve; furthermore, by setting a first cooperation part, a first guide hole, a second cooperation part and a second guide hole, that is, by setting a second lead screw to prevent the first driving disc from rotating, and the first lead screw to prevent the second driving disc from rotating, thereby ensuring that the first driving disc and the second driving disc can move axially stably.

[0018] Optionally, the first conical surface is provided with a ring of serrated first biting teeth, the second conical surface is provided with a ring of serrated second biting teeth, the third conical surface is provided with a ring of serrated third biting teeth, and the fourth conical surface is provided with a ring of serrated fourth biting teeth; the tips of the second biting teeth of the first fixing ring and the tips of the fourth biting teeth of the second fixing ring are located in the same radial plane, the tips of the first biting teeth of the first driving disk and the recesses of the third biting teeth of the second driving disk are located in the same radial plane, the moving distances of the two first driving disks are the same, the moving distances of the two second driving disks are the same, the inclined surface of the second biting tooth is used for the inclined surface of the first biting tooth to be engaged, and the inclined surface of the fourth biting tooth is used for the inclined surface of the third biting tooth to be engaged.

[0019] Through the above technical solution, by setting a first biting tooth, a second biting tooth, a third biting tooth, and a fourth biting tooth and defining the position of their respective tips, when two first biting teeth approach each other to contact the second biting tooth, and two third biting teeth move away from each other to contact the fourth biting tooth, one of the inclined surfaces of the two first biting teeth simultaneously abuts against the corresponding inclined surfaces of the two second biting teeth (the two first biting teeth move in the same direction), and the circumferential component force on the corresponding inclined surface is set as f2; one of the inclined surfaces of the two third biting teeth simultaneously abuts against the corresponding inclined surfaces of the two fourth biting teeth (the two third biting teeth move in the same direction), and the circumferential component force on the corresponding inclined surface is set as f1. Since the inclination direction of the corresponding inclined surface of the fourth biting tooth is opposite to that of the corresponding inclined surface of the second biting tooth, the direction of f1 is opposite to that of f2. f1 and f2 abut against each other, that is, the first biting teeth and the third biting teeth circumferentially limit the rotating sleeve, thereby greatly improving the locking and braking effect of the rotating sleeve.

[0020] Optionally, the second biting tooth includes a first half tooth and a second half tooth that are separately disposed. The first half tooth and the second half tooth are both integrally formed and connected to the second conical surface through a first tooth root. There are gaps between the first half tooth and the second half tooth and the second conical surface, and there are gaps between the first half tooth and the second half tooth. The fourth biting tooth includes a third half tooth and a fourth half tooth that are separately disposed. The third half tooth and the fourth half tooth are both integrally formed and connected to the fourth conical surface through a second tooth root. There are gaps between the third half tooth and the fourth half tooth and the fourth half tooth, and there are gaps between the third half tooth and the fourth half tooth.

[0021] Through the above technical solution, by separately setting the second and fourth biting teeth, both the second and fourth biting teeth have elastic deformation capabilities. When subjected to the circumferential force of the first and third biting teeth, the second and fourth biting teeth will undergo adaptive elastic deformation, thereby making the occlusal effect stronger.

[0022] Optionally, one end of the rotating sleeve is fixed with an end cap, and the surface of the end cap is coaxially provided with an annular groove. One end of the first lead screw and the second lead screw are rotatably connected to the fixed shaft, and the other end of the first lead screw and the second lead screw are located in the annular groove. The ends of the first lead screw and the second lead screw away from the fixed shaft are connected to a connecting plate, and the two ends of the connecting plate are respectively for the first lead screw and the second lead screw to pass through and rotatably connect.

[0023] By using the above technical solution, and by setting an annular groove and a connecting plate, the free ends of the first and second lead screws are multi-directionally limited, thereby improving the positional stability of the first and second lead screws and thus improving the braking effect on the rotating sleeve.

[0024] Optionally, a central rod is coaxially fixed inside the rotating sleeve. A through hole for the central rod to pass through is formed at the center of the first and second driving disks. A plurality of ring pieces corresponding one-to-one with the first and second driving disks are fixed on the outer circumferential surface of the central rod. The outer edge of the ring piece abuts against the outer circumferential surface of the first and second lead screws. An inclined spring piece is integrally formed at the outer edge of the ring piece. The spring pieces are evenly distributed around the circumference. A guide ring is coaxially fixed at the opening of the through hole. The inner diameter of the guide ring abuts against the inclined surface of the spring piece. When the first and second driving disks retract, the spring piece undergoes elastic compression deformation.

[0025] Through the above technical solution, the cooperation between the guide ring and the inclined surface of the spring plate plays a stabilizing role on the first and second drive plates, so that the first and second drive plates and the rotating sleeve remain coaxial, thereby improving the clamping effect of the first and second drive plates; and the elastic force of the spring plate will be applied to the first and second drive plates through the guide ring, thereby reducing the axial movement of the first and second drive plates caused by the threaded fit clearance.

[0026] Optionally, a first rubber layer is provided at the mating position of the first conical surface and the second conical surface, and a second rubber layer is provided at the mating position of the third conical surface and the fourth conical surface.

[0027] The above technical solution, through the first rubber layer and the second rubber layer, can improve the contact friction, thereby improving the braking effect.

[0028] The beneficial effects of this application are: 1. By setting up a swing angle drive mechanism, an X-axis moving component and a Z-axis moving component, the worktable can realize workpiece position control. When grinding the conical surface of the sealing pair, the traditional interpolation grinding method can be eliminated. The swing angle drive mechanism drives the rotating seat, Z-axis moving component, grinding head slide, hydrostatic grinding head electronic axis and grinding wheel to rotate and position as a whole according to the workpiece taper requirements. Only one coordinate needs to be moved on the Z-axis to complete the following grinding of the conical surface. This avoids the grinding error caused by the difference in dynamic response characteristics and motion accuracy of each coordinate axis in the traditional interpolation grinding method. Higher grinding shape accuracy and grinding surface quality can be obtained, so that the ideal surface finish of the grinding of the sealing pair reaches Ra0.2 or less, and the roundness of the inner and outer circles reaches 0.003mm. 2. The grinding wheel always moves on the workpiece's grinding sealing surface during the grinding process, making full use of the processing time, improving grinding efficiency, ensuring uniform grinding force, improving grinding accuracy, and guaranteeing the compatibility and sealing performance of the triple eccentric butterfly valve sealing pair, achieving 100% interchangeability of the sealing pair; 3. Through the cooperation of the arc-shaped rack and the first gear, the gear cooperation accuracy is higher than that of the worm gear, which can improve the swing angle accuracy of the grinding wheel and the grinding accuracy. Secondly, after the swing angle is adjusted, the two first drive discs approach each other through the first locking mechanism to clamp the first fixed ring, thereby realizing the fixed connection between the fixed shaft and the rotating sleeve, locking the rotating sleeve, thus coping with the impact load, reducing the wear caused by the impact load on the arc-shaped rack and the first gear, and ensuring the stability of the cooperation accuracy. Attached Figure Description

[0029] Figure 1 is a schematic diagram of the overall structure of Embodiment 1.

[0030] Figure 2 is a cross-sectional view of the base of Embodiment 1.

[0031] Figure 3 is a partial cross-sectional view of the rotating sleeve of Example 1.

[0032] Figure 4 is a magnified view of part A in Figure 3.

[0033] Figure 5 is a partial cross-sectional view of the rotating sleeve of Embodiment 2.

[0034] Figure 6 is a magnified view of part B in Figure 5.

[0035] Figure 7 is a partial cross-sectional view of the rotating sleeve of Example 3.

[0036] Figure 8 is a magnified view of point C in Figure 7.

[0037] Figure 9 is a partial cross-sectional view of the rotating sleeve of Example 4.

[0038] Figure 10 is a partial cross-sectional view of the rotating sleeve of Example 5.

[0039] Figure 11 is a magnified view of part D in Figure 10.

[0040] Figure 12 is a schematic diagram of Embodiment 5 illustrating the cooperation relationship between the guide ring and the spring piece.

[0041] Figure 13 is a schematic diagram of Example 6 illustrating the positional relationship between the first occlusal tooth, the second occlusal tooth, the third occlusal tooth, and the fourth occlusal tooth.

[0042] Figure 14 is a magnified view of a portion of point E in Figure 13.

[0043] Figure 15 is a magnified view of part F in Figure 13.

[0044] Figure 16 is a schematic diagram of Embodiment 7 illustrating the positional relationship between the first occlusal tooth and the second occlusal tooth.

[0045] Figure 17 is a schematic diagram of Example 7 illustrating the positional relationship between the third and fourth occlusal teeth.

[0046] Explanation of reference numerals in the attached drawings: 1. First drive disc; 2. Second drive disc; 10. Machine base; 101. Rotating seat; 103. Electronic shaft of dynamic and static pressure grinding head; 104. Grinding wheel; 105. Arc rack; 106. First gear; 107. Drive motor; 11. First lead screw; 110. Fixed shaft; 111. Second gear; 112. First rack; 113. First fixed ring; 114. First conical surface; 115. Second conical surface; 116. First rubber layer; 117. Rotating ring; 1100. Guide rod; 120. Rotating sleeve; 121. End cap; 1210. Ring groove; 1211. Connecting plate; 1212. Center bar; 130. Fixed cylinder; 140. Bearing; 15. First guide. 20. Hole; 20. Third conical surface; 201. Second rubber layer; 21. Second lead screw; 211. Third gear; 212. Second rack; 22. Second fixing ring; 221. Fourth conical surface; 23. Second guide hole; 24. Through hole; 241. Ring piece; 242. Spring piece; 243. Guide ring; 31. First meshing tooth; 32. Second meshing tooth; 321. First half tooth; 322. Second half tooth; 323. First tooth root; 33. Third meshing tooth; 34. Fourth meshing tooth; 341. Third half tooth; 342. Fourth half tooth; 343. Second tooth root; 51. Machine body; 52. Crossbeam; 53. Transverse slide; 54. Grinding head slide; 55. Z-axis moving assembly; 56. Worktable. Detailed Implementation

[0047] The embodiments of this application are described in detail below, and examples of the embodiments are shown in Figures 1-17.

[0048] In the description of this specification, the references to "certain embodiments," "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples" indicate that a specific feature, structure, material, or characteristic described in connection with an embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0049] Example 1 Example 1 discloses a high-precision grinding equipment for triple eccentric butterfly valve sealing pairs, as shown in Figures 1, 2, and 3. The high-precision grinding equipment for triple eccentric butterfly valve sealing pairs includes a machine body 51, a machine base 10, a rotating seat 101, a crossbeam 52, a grinding head slide 54, a worktable 56, an X-axis moving assembly (not shown in the figure), a Z-axis moving assembly 55, a swing angle driving mechanism, and a first locking mechanism. The worktable 56 is mounted on the machine body 51 and is used to clamp the triple eccentric butterfly valve sealing pairs. Driven by the spindle of the machine body 51, the worktable 56 drives the triple eccentric butterfly valve sealing pairs to rotate.

[0050] The base 10 is fixed with a transverse slide 53, which slides horizontally with the crossbeam 52. The X-axis moving component is used to drive the transverse slide 53 to move, thereby driving the base 10 to move along the X-axis. In this embodiment, the X-axis moving component is a combination of a ball screw structure and a servo motor to convert the rotational motion into linear motion, thereby driving the base 10 to move along the X-axis.

[0051] The base 10 is fixed with a horizontally arranged fixed shaft 110, and the rotating seat 101 is fixed with a rotating sleeve 120. The rotating sleeve 120 is coaxially rotatably connected to the fixed shaft 110. In order to improve rotational stability, a fixed cylinder 130 is also fixed on the surface of the base 10. The rotating sleeve 120 passes through the fixed cylinder 130, and the rotating sleeve 120 is coaxially rotatably connected to the fixed cylinder 130 through a bearing 140.

[0052] The swing angle drive mechanism is used to drive the rotating seat 101 to rotate relative to the base 10, and the rotation range of the rotating seat 101 is ±25°. Specifically, the swing angle drive mechanism includes a drive motor 107, a first gear 106 and an arc rack 105. The drive motor 107 is mounted on the base 10, the first gear 106 is mounted on the output shaft of the drive motor 107, the arc rack 105 is fixed to the rotating seat 101, and the curvature center of the arc rack 105 is located on the axis of the rotating sleeve 120. The arc rack 105 meshes with the first gear 106.

[0053] The grinding head slide 54 is slidably engaged with the rotating seat 101. The Z-axis moving component 55 is used to drive the grinding head slide 54 to move. In this embodiment, the Z-axis moving component 55 is a combination of a ball screw structure and a servo motor to convert the rotary motion into linear motion, so as to drive the grinding head slide 54, the dynamic and static pressure grinding head electronic shaft 103 and the grinding wheel to move along the Z-axis direction.

[0054] The grinding head slide 54 is equipped with a dynamic and static pressure grinding head electronic shaft 103. The power of the dynamic and static pressure grinding head electronic shaft 103 can be configured to 30KW or 15KW according to the grinding requirements. The axial runout error of the dynamic and static pressure grinding head electronic shaft 103 is ±0.003mm, and the radial runout error of the dynamic and static pressure grinding head electronic shaft 103 is ±0.003mm.

[0055] The electronic shaft 103 of the dynamic and static pressure grinding head is located above the worktable 56, and a grinding wheel 104 is provided at the lower end of the electronic shaft 103 of the dynamic and static pressure grinding head.

[0056] As shown in Figures 3 and 4, the first locking mechanism includes a first driving assembly and two first driving disks 1. The first driving assembly includes a first lead screw 11, a first driving structure and a guide rod 1100. The first lead screw 11 is coaxially arranged with the rotating sleeve 120. One end of the first lead screw 11 is rotatably connected to the fixed shaft 110, and the other end of the first lead screw 11 abuts against the end cover 121 of the rotating sleeve 120.

[0057] The first drive disk 1 is coaxially arranged with the rotary sleeve 120. The two first drive disks 1 are distributed vertically. The outer edge of the first drive disk 1 is provided with a first conical surface 114, and the first conical surface 114 is covered and fixed with a first rubber layer 116.

[0058] One end of the guide rod 1100 is fixedly connected to the fixed shaft 110. The guide rod 1100 is parallel to the axis of the rotating sleeve 120. The guide rod 1100 passes through the two first drive discs 1, so that the first drive discs 1 and the guide rod 1100 slide axially.

[0059] The first lead screw 11 is threadedly connected to the first drive disc 1. The threads of the two first drive discs 1 are arranged in opposite directions. Correspondingly, the first lead screw 11 has two threaded segments with opposite directions. The first drive structure is used to drive the first lead screw 11 to rotate. The guide rod 1100 is fixedly connected to the fixed shaft 110. Specifically, the first drive structure includes a first hydraulic cylinder (not shown in the figure), a first rack 112, and a second gear 111. The second gear 111 is coaxially fixed to the end of the first lead screw 11. The first hydraulic cylinder is installed at the bottom of the machine base 10. The first rack 112 is fixed on the piston rod of the first hydraulic cylinder. The first rack 112 is perpendicular to the first lead screw 11. The first rack 112 meshes with the second gear 111. By extending and retracting the first hydraulic cylinder, the first lead screw 11 is driven to rotate in the forward or reverse direction, thereby controlling the movement of the two first drive discs 1 towards each other or away from each other.

[0060] Two first fixing rings 113 are coaxially fixed on the inner wall of the rotating sleeve 120. The first fixing rings 113 are located in the axial gap between the two first driving discs 1. A second conical surface 115 is provided at the inner diameter of the first fixing rings 113.

[0061] The implementation principle of Example 1 is as follows: By setting up a swing angle drive mechanism, an X-axis moving component, and a Z-axis moving component 55, the worktable 56 can realize workpiece position control. When grinding the conical surface of the sealing pair, the traditional interpolation grinding method can be avoided. According to the workpiece taper requirements, the swing angle drive mechanism drives the rotating seat 101, the Z-axis moving component 55, the grinding head slide 54, the hydrostatic grinding head electronic shaft 103, and the grinding wheel 104 to rotate and position as a whole. Only one coordinate needs to be moved along the Z-axis to complete the following grinding of the conical surface. This avoids the grinding error caused by the difference in dynamic response characteristics and motion accuracy of each coordinate axis in the traditional interpolation grinding method. Higher grinding shape accuracy and grinding surface quality can be obtained, so that the ideal surface finish of the grinding of the sealing pair reaches Ra0.2 or less, and the roundness of the inner and outer circles reaches 0.003mm.

[0062] Secondly, the grinding wheel 104 always moves on the workpiece's grinding sealing surface during the grinding process, making full use of the processing time, improving grinding efficiency, ensuring uniform grinding force, improving grinding accuracy, and also ensuring the compatibility and sealing performance of the triple eccentric butterfly valve sealing pair, achieving 100% interchangeability of the sealing pair.

[0063] Secondly, through the cooperation of the arc-shaped rack 105 and the first gear 106, the gear cooperation accuracy is higher than that of the worm gear cooperation accuracy, which can greatly improve the swing angle adjustment accuracy and grinding accuracy of the grinding wheel 104. Secondly, after the swing angle is adjusted, by activating the first drive structure, the first drive disc 1 is driven to move closer to each other to clamp the first fixed ring 113 (the first conical surface 114 and the second conical surface 115 cooperate and the first rubber layer 116 has great frictional resistance), thereby realizing the fixed connection between the fixed shaft 110 and the rotating sleeve 120, locking the rotating sleeve 120, thereby coping with the impact load of the rotating seat 101, thereby reducing the wear caused by the impact load on the arc-shaped rack 105 and the first gear 106, and thus ensuring the stability of the cooperation accuracy.

[0064] Furthermore, the coaxiality of the fixed shaft 110 and the rotating sleeve 120 is improved by the cooperation of the first conical surface 114 and the second conical surface 115, thereby improving the rotation accuracy of the rotating sleeve 120.

[0065] Example 2 The difference between Example 2 and Example 1 is that, as shown in Figures 5 and 6, the first lead screw 11 and the rotary sleeve 120 are eccentrically arranged, and a rotating ring 117 is fixed on the surface of the first drive disk 1 away from the other first drive disk 1. The rotating ring 117 is coaxially arranged with the first drive disk 1, and the outer peripheral surface of the rotating ring 117 is in contact with the inner peripheral surface of the rotary sleeve 120.

[0066] When the first drive structure drives the first lead screw 11 to rotate, it drives the two first drive discs 1 to move towards each other through a threaded connection, thereby clamping the first fixed ring 113. Furthermore, the contact between the outer circumferential surface of the rotating ring 117 and the inner circumferential surface of the rotating sleeve 120 restricts the first drive disc 1 from rotating eccentrically under the frictional force of the first lead screw 11, thereby ensuring that the first lead screw 11 can stably drive the first drive disc 1 to move axially.

[0067] Example 3 differs from Example 1 in that, as shown in Figures 7 and 8, the high-precision grinding equipment for the triple eccentric butterfly valve sealing pair also includes a second locking mechanism. The second locking mechanism includes a second drive assembly and two second drive discs 2. The second drive discs 2 are coaxially arranged with the rotary sleeve 120. The two second drive discs 2 are located on the upper and lower sides of the first drive disc 1, respectively. A third conical surface 20 is provided at the outer edge of the second drive disc 2, and a second rubber layer 201 is fixedly covered on the third conical surface 20. The second drive assembly is used to drive the two second drive discs 2 to move apart. Specifically, the second drive assembly includes a second lead screw 21 and a second drive structure. The end of the second lead screw 21 is rotatably connected to the fixed shaft 110. The first lead screw 11 and the second lead screw 21 are both parallel to the axis of the rotary sleeve 120. The first lead screw 11 and the second lead screw 21 are both eccentrically arranged with respect to the axis of the rotary sleeve 120. In this example, the first lead screw 11 and the second lead screw 21 are symmetrically arranged with respect to the axis of the rotary sleeve 120.

[0068] The second lead screw 21 is threadedly connected to the second drive disc 2. The threads of the two second drive discs 2 are arranged in opposite directions. Correspondingly, the second lead screw 21 has two threaded sections with opposite directions. The second drive structure is used to drive the second lead screw 21 to rotate. Specifically, the second drive structure includes a second hydraulic cylinder (not shown in the figure), a second rack 212, and a third gear 211. The third gear 211 is coaxially fixed to the end of the second lead screw 21. The second hydraulic cylinder is installed at the bottom of the machine base 10. The second rack 212 is fixed on the piston rod of the second hydraulic cylinder. The second rack 212 is perpendicular to the second lead screw 21. The second rack 212 meshes with the third gear 211. By extending and retracting the second hydraulic cylinder, the second lead screw 21 is driven to rotate in the forward or reverse direction, thereby controlling the movement of the two second drive discs 2 toward each other or away from each other.

[0069] Furthermore, the first drive disc 1 is provided with a first guide hole 15, the outer peripheral surface of the second lead screw 21 has a second mating part (not shown in the figure) that fits against the inner wall of the first guide hole 15, the second drive disc 2 is provided with a second guide hole 23, and the outer peripheral surface of the first lead screw 11 has a first mating part (not shown in the figure) that fits against the inner wall of the second guide hole 23.

[0070] Two second fixing rings 22 are coaxially fixed on the inner wall of the rotating sleeve 120. The two second fixing rings 22 are located on the upper and lower sides of the first fixing ring 113, respectively. A fourth conical surface 221 is provided at the inner diameter of the second fixing ring 22, which is used to cooperate with the third conical surface 20.

[0071] First, by setting a first locking mechanism and a second locking mechanism, the first driving disc 1 and the second driving disc 2 respectively cooperate with the first fixed ring 113 and the second fixed ring 22, with a large cooperation area, thereby greatly improving the braking effect on the rotating sleeve 120.

[0072] Furthermore, by setting the first mating part, the first guide hole 15, the second mating part, and the second guide hole 23, the second lead screw 21 can play a role in preventing the first drive disk 1 from rotating, and the first lead screw 11 can play a role in preventing the second drive disk 2 from rotating, thereby ensuring that the first drive disk 1 and the second drive disk 2 can move axially in a stable manner.

[0073] Secondly, the first drive disc 1 and the second drive disc 2 can also provide radial support for the first lead screw 11 and the second lead screw 21, thereby greatly improving the rigidity of the first lead screw 11 and the second lead screw 21 and thus improving their ability to resist impact loads.

[0074] Example 4 The difference between Example 4 and Example 3 is that, as shown in Figure 9, the surface of the end cap 121 is coaxially provided with an annular groove 1210. The ends of the first lead screw 11 and the second lead screw 21 that are away from the fixed shaft 110 are located in the annular groove 1210. That is, when the rotating sleeve 120 rotates, the first lead screw 11 and the second lead screw 21 can rotate around the axis of the rotating sleeve 120 in the annular groove 1210.

[0075] The ends of the first lead screw 11 and the second lead screw 21 that are away from the fixed shaft 110 are connected to a connecting plate 1211. The two ends of the connecting plate 1211 are respectively for the first lead screw 11 and the second lead screw 21 to pass through and rotate.

[0076] In this way, by setting the annular groove 1210 and the connecting plate 1211, the free ends of the first lead screw 11 and the second lead screw 21 are multi-directionally limited (the free ends of the first lead screw 11 and the second lead screw 21 are the ends away from the fixed shaft 110), so as to improve the positional stability of the first lead screw 11 and the second lead screw 21, thereby improving the braking effect on the rotating sleeve 120.

[0077] Example 5 The difference between Example 5 and Example 3 is that, as shown in Figures 10, 11 and 12, a central rod 1212 is coaxially fixed inside the rotating sleeve 120, and a through hole 24 for the central rod 1212 to pass through is passed through the center of the first driving disk 1 and the second driving disk 2. The diameter of the through hole 24 is larger than the diameter of the central rod 1212.

[0078] Multiple ring pieces 241, corresponding one-to-one with the first drive disk 1 and the second drive disk 2, are fixed on the outer peripheral surface of the center rod 1212. The outer edge of the ring piece 241 abuts against the outer peripheral surface of the first lead screw 11 and the second lead screw 21. An inclined spring piece 242 is integrally formed on the outer edge of the ring piece 241. The spring pieces 242 are evenly arranged around the circumference. A guide ring 243 is coaxially fixed to the opening of the through hole 24. That is, both the first drive disk 1 and the second drive disk 2 are fixed with guide rings 243. The inner diameter of the guide ring 243 abuts against the inclined surface of the spring piece 242.

[0079] When the first drive disk 1 and the second drive disk 2 retract, the spring 242 is elastically compressed and deformed. The elastic force of the spring 242 is applied to the first drive disk 1 and the second drive disk 2 through the guide ring 243, so that the first drive disk 1 and the second drive disk 2 remain coaxial with the rotating sleeve 120.

[0080] Furthermore, when the first drive disk 1 and the second drive disk 2 move forward (the first drive disk 1 and the second drive disk 2 move toward the first fixed ring 113 and the second fixed ring 22 respectively), the elastic force of the spring piece 242 will be applied to the first drive disk 1 and the second drive disk 2 through the guide ring 243, so as to improve the tightness of the fit between the first conical surface 114 and the second conical surface 115 and the tightness of the fit between the third conical surface 20 and the fourth conical surface 221, thereby reducing the occurrence of axial movement of the first drive disk 1 and the second drive disk 2 due to the thread fit clearance.

[0081] Example 6 The difference between Example 6 and Example 3 is that, as shown in Figures 13, 14 and 15 (the two dashed arrows in Figures 13, 14 and 15 represent the moving directions of the first drive disk 1 and the second drive disk 2, respectively, and the two solid arrows represent the directions of the forces f1 and f2, respectively), a ring of sawtooth-shaped first engagement teeth 31 is fixed on the first conical surface 114, a ring of sawtooth-shaped second engagement teeth 32 is fixed on the second conical surface 115, a ring of sawtooth-shaped third engagement teeth 33 is fixed on the third conical surface 20, and a ring of sawtooth-shaped fourth engagement teeth 34 is fixed on the fourth conical surface 221.

[0082] The tip of the second biting tooth 32 of the first fixing ring 113 and the tip of the fourth biting tooth 34 of the second fixing ring 22 are located in the same radial plane, and the tip of the first biting tooth 31 of the first drive disk 1 and the recess of the third biting tooth 33 of the second drive disk 2 are located in the same radial plane.

[0083] When the two first engagement teeth 31 approach each other to contact the second engagement teeth 32, and the two third engagement teeth 33 move away from each other to contact the fourth engagement teeth 34, one of the inclined surfaces of the two first engagement teeth 31 simultaneously abuts against the corresponding inclined surfaces of the two second engagement teeth 32 (the axial movement stroke of the two first engagement teeth 31 is consistent), and the circumferential component force on the corresponding inclined surface is set as f2; one of the inclined surfaces of the two third engagement teeth 33 simultaneously abuts against the corresponding inclined surfaces of the two fourth engagement teeth 34 (the axial movement stroke of the two third engagement teeth 33 is consistent), and the circumferential component force on the corresponding inclined surface is set as f1. Since the inclination direction of the corresponding inclined surface of the fourth engagement tooth 34 is opposite to that of the corresponding inclined surface of the second engagement tooth 32, the direction of f1 is opposite to that of f2. f1 and f2 abut against each other, that is, the first engagement teeth 31 and the third engagement teeth 33 circumferentially limit the rotating sleeve 120, thereby greatly improving the locking and braking effect of the rotating sleeve 120.

[0084] Example 7 The difference between Example 7 and Example 6 is that, as shown in Figures 16 and 17, the second biting tooth 32 includes a first half tooth 321 and a second half tooth 322 that are separately disposed. The first half tooth 321 and the second half tooth 322 are both integrally formed and connected to the second conical surface 115 through the first tooth root 323. There is a gap between the first half tooth 321 and the second half tooth 322 and the second conical surface 115, and there is a gap between the first half tooth 321 and the second half tooth 322.

[0085] The fourth biting tooth 34 includes a third half tooth 341 and a fourth half tooth 342 that are separately arranged. Both the third half tooth 341 and the fourth half tooth 342 are integrally formed and connected to the fourth conical surface 221 through the second tooth root 343. There is a gap between the third half tooth 341 and the fourth half tooth 342 and the fourth conical surface 221, and there is a gap between the third half tooth 341 and the fourth half tooth 342.

[0086] By separating the second occlusal tooth 32 and the fourth occlusal tooth 34, both the second occlusal tooth 32 and the fourth occlusal tooth 34 have elastic deformation capabilities. When subjected to the circumferential force of the first occlusal tooth 31 and the third occlusal tooth 33, the second occlusal tooth 32 and the fourth occlusal tooth 34 will undergo adaptive elastic deformation, thereby making the occlusal effect stronger.

[0087] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A high-precision grinding device for the sealing pair of a triple eccentric butterfly valve, characterized in that, The machine includes a body (51), a base (10), a rotating seat (101), a crossbeam (52), a grinding head slide (54), a worktable (56) for clamping the sealing pair of the triple eccentric butterfly valve, a dynamic and static pressure grinding head electronic shaft (103), an X-axis moving assembly, a Z-axis moving assembly (55), a swing angle drive mechanism, and a first locking mechanism. The crossbeam (52) is mounted on the body (51), and the base (10) is fixed with a transverse slide (53). The transverse slide (53) and the crossbeam (52) slide horizontally together. The X-axis moving assembly is used to drive the transverse slide (53) to move. The base (10) is fixed with a horizontal setting. The fixed shaft (110) is provided; the rotating seat (101) is provided with a rotating sleeve (120), which is coaxially rotatably connected to the fixed shaft (110). The swing angle drive mechanism is used to drive the rotating seat (101) to rotate relative to the machine base (10); the grinding head slide (54) is slidably engaged with the rotating seat (101), and the Z-axis moving assembly (55) is used to drive the grinding head slide (54) to move. The grinding head slide (54) is provided with the dynamic and static pressure grinding head electronic shaft (103), and the end of the dynamic and static pressure grinding head electronic shaft (103) is provided with a grinding wheel (104); the worktable (56) is installed on the fixed shaft (110); the rotating seat (101) is provided with a rotating sleeve (120), which is coaxially rotatably connected to the fixed shaft (110). The swing angle drive mechanism is used to drive the rotating seat (101) to rotate relative to the machine base (10); the grinding head slide (54) is slidably engaged with the rotating seat (101), and the Z-axis moving assembly (55) is used to drive the grinding head slide (54) to move. The grinding head slide (54) is provided with the dynamic and static pressure grinding head electronic shaft (103), and the end of the dynamic and static pressure grinding head electronic shaft (103) is provided with a grinding wheel (104); the worktable (56) is installed on the machine base (110). The machine body (51) is located below the electronic shaft (103) of the dynamic and static pressure grinding head; the swing angle drive mechanism includes a drive motor (107), a first gear (106) and an arc rack (105), wherein the drive motor (107) is mounted on the machine base (10), the first gear (106) is mounted on the output shaft of the drive motor (107), the arc rack (105) is fixed to the rotating seat (101), and the curvature center of the arc rack (105) is located on the axis of the rotating sleeve (120), the arc rack (105) meshes with the first gear (106), and the first locking mechanism includes The device includes a first drive assembly and two first drive disks (1). The fixed shaft (110) is provided with the first drive disks (1). The first drive disks (1) are coaxially arranged with the rotary sleeve (120). The outer edge of the first drive disks (1) is provided with a first conical surface (114). The inner wall of the rotary sleeve (120) is coaxially fixed with two first fixing rings (113). The inner diameter of the first fixing rings (113) is provided with a second conical surface (115). The first drive assembly is used to drive the two first drive disks (1) to move closer to each other until the first conical surface (114) and the second conical surface (115) cooperate.

2. The high-precision grinding equipment for the triple eccentric butterfly valve sealing pair according to claim 1, characterized in that, The first drive assembly includes a first lead screw (11), a first drive structure, and a guide rod (1100). The first lead screw (11) is coaxially arranged with the rotary sleeve (120), the first lead screw (11) is threadedly connected to the first drive disk (1), the threads of the two first drive disks (1) are arranged in opposite directions, the first drive structure is used to drive the first lead screw (11) to rotate, the guide rod (1100) is fixedly connected to the fixed shaft (110), and the guide rod (1100) slides through the first drive disk (1).

3. The high-precision grinding equipment for the triple eccentric butterfly valve sealing pair according to claim 1, characterized in that, The first drive assembly includes a first lead screw (11), a first drive structure, and a rotating ring (117). The rotating ring (117) is coaxially fixed with the first drive disk (1). The outer circumferential surface of the rotating ring (117) is in contact with the inner circumferential surface of the rotary sleeve (120). The first lead screw (11) is eccentrically set with the rotary sleeve (120). The first lead screw (11) is threadedly connected to the first drive disk (1). The threads of the two first drive disks (1) are set in opposite directions. The first drive structure is used to drive the first lead screw (11) to rotate.

4. The high-precision grinding equipment for the triple eccentric butterfly valve sealing pair according to claim 1, characterized in that, It also includes a second locking mechanism, which includes a second driving assembly and two second driving discs (2). The fixed shaft (110) is provided with the second driving discs (2). The second driving discs (2) are coaxially arranged with the rotary sleeve (120). The two second driving discs (2) are located on the upper and lower sides of the first driving disc (1), respectively. The outer edge of the second driving disc (2) is provided with a third conical surface (20). The inner wall of the rotary sleeve (120) is coaxially fixed with two second fixing rings (22). The two second fixing rings (22) are located on the upper and lower sides of the first fixing ring (113), respectively. The inner diameter of the second fixing ring (22) is provided with a fourth conical surface (221). The second driving assembly is used to drive the two second driving discs (2) to move away from each other until the third conical surface (20) and the fourth conical surface (221) are engaged. The first driving assembly includes a first lead screw (11) and a first driving structure. The second driving assembly includes a second lead screw (21) and a second driving structure. The structure includes a first lead screw (11) and a second lead screw (21) that are parallel to the axis of the rotating sleeve (120). The first lead screw (11) and the second lead screw (21) are eccentrically set with respect to the rotating sleeve (120). The first lead screw (11) is threadedly connected to the first drive disk (1). The threads of the two first drive disks (1) are set in opposite directions. The first drive structure is used to drive the first lead screw (11) to rotate. The second lead screw (21) is threadedly connected to the second drive disk (2). The threads of the two second drive disks (2) are set in opposite directions. The second drive structure is used to drive the second lead screw (21) to rotate. The first drive disk (1) has a first guide hole (15) through it. The outer circumferential surface of the second lead screw (21) has a second mating part that fits against the inner wall of the first guide hole (15). The second drive disk (2) has a second guide hole (23) through it. The outer circumferential surface of the first lead screw (11) has a first mating part that fits against the inner wall of the second guide hole (23).

5. The high-precision grinding equipment for the triple eccentric butterfly valve sealing pair according to claim 4, characterized in that, The first conical surface (114) is provided with a ring of sawtooth-shaped first engagement teeth (31), the second conical surface (115) is provided with a ring of sawtooth-shaped second engagement teeth (32), the third conical surface (20) is provided with a ring of sawtooth-shaped third engagement teeth (33), and the fourth conical surface (221) is provided with a ring of sawtooth-shaped fourth engagement teeth (34); the tips of the second engagement teeth (32) of the first fixing ring (113) and the tips of the fourth engagement teeth (34) of the second fixing ring (22) are located on the same diameter. In the inward plane, the tip of the first biting tooth (31) of the first drive disk (1) and the recess of the third biting tooth (33) of the second drive disk (2) are located in the same radial plane. The two first drive disks (1) move at the same distance, and the two second drive disks (2) move at the same distance. The inclined surface of the second biting tooth (32) is used to be engaged by the inclined surface of the first biting tooth (31), and the inclined surface of the fourth biting tooth (34) is used to be engaged by the inclined surface of the third biting tooth (33).

6. The high-precision grinding equipment for the sealing pair of the triple eccentric butterfly valve according to claim 5, characterized in that, The second biting tooth (32) includes a first half tooth (321) and a second half tooth (322) that are separately arranged. The first half tooth (321) and the second half tooth (322) are both integrally formed and connected to the second conical surface (115) through a first tooth root (323). There is a gap between the first half tooth (321) and the second half tooth (322) and the second conical surface (115). There is a gap between the first half tooth (321) and the second half tooth (322). The fourth biting tooth (34) includes a third half tooth (341) and a fourth half tooth (342) that are separately arranged. The third half tooth (341) and the fourth half tooth (342) are both integrally formed and connected to the fourth conical surface (221) through a second tooth root (343). There is a gap between the third half tooth (341) and the fourth half tooth (342) and the fourth conical surface (221). There is a gap between the third half tooth (341) and the fourth half tooth (342).

7. The high-precision grinding equipment for the sealing pair of the triple eccentric butterfly valve according to claim 4, characterized in that, One end of the rotating sleeve (120) is fixed with an end cap (121). The surface of the end cap (121) is coaxially provided with an annular groove (1210). One end of the first lead screw (11) and the second lead screw (21) are rotatably connected to the fixed shaft (110). The other end of the first lead screw (11) and the second lead screw (21) is located in the annular groove (1210). The ends of the first lead screw (11) and the second lead screw (21) away from the fixed shaft (110) are connected to a connecting plate (1211). The two ends of the connecting plate (1211) are respectively for the first lead screw (11) and the second lead screw (21) to pass through and rotatably connect.

8. The high-precision grinding equipment for the sealing pair of the triple eccentric butterfly valve according to claim 4 or 7, characterized in that, A central rod (1212) is coaxially fixed inside the rotating sleeve (120). Through holes (24) are formed at the centers of the first driving disk (1) and the second driving disk (2) for the central rod (1212) to pass through. Multiple annular pieces (241) corresponding one-to-one with the first driving disk (1) and the second driving disk (2) are fixed to the outer circumferential surface of the central rod (1212). The outer edges of the annular pieces (241) abut against the first lead screw (11) and... On the outer circumference of the second lead screw (21), at the outer edge of the ring plate (241), there are inclined spring plates (242) integrally formed. Each spring plate (242) is evenly arranged around the circumference. A guide ring (243) is coaxially fixed to the opening of the through hole (24). The inner diameter of the guide ring (243) abuts against the inclined surface of the spring plate (242). When the first drive disk (1) and the second drive disk (2) retract, the spring plate (242) is elastically compressed and deformed.

9. The high-precision grinding equipment for the triple eccentric butterfly valve sealing pair according to claim 4, characterized in that, A first rubber layer (116) is provided at the mating position of the first conical surface (114) and the second conical surface (115), and a second rubber layer (201) is provided at the mating position of the third conical surface (20) and the fourth conical surface (221).

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