Self-resetting connection mechanism of shoe and ball piston

Abstract

The utility model relates to the field of multi -freedom degree heavy -duty test equipment discloses the self-resetting connecting mechanism of sliding shoe and ball head piston, sets up between sliding shoe and ball head piston, including spring reset subassembly and positioning subassembly, spring reset subassembly is composed of the lateral support of circumferential even distribution, longitudinal support and pre -tightening's tensile spring, and the two ends of tensile spring are connected sliding shoe and ball head piston respectively, and overcomes the sliding shoe dead weight through spring tension when stopping, resets it to the neutral position automatically, ensures the evenness of oil film clearance, and the stable static pressure oil film can be quickly reconstructed when restarting, and the test preparation time is shortened significantly. Positioning subassembly includes horizontal, and longitudinal locking nut, respectively with the outer thread cooperation of lateral support and longitudinal support, is used for fixing the relative position of support and sliding shoe, ball head piston, realizes the stable assembly and adjustment of structure. The mechanism realizes sliding shoe automatic reset and accurate positioning, improves equipment start -stop efficiency and running stability, is applicable to high -precision loading test system.

Description

Technical Field

[0001] This solution relates to the field of multi-degree-of-freedom heavy-load testing equipment, specifically to the self-resetting connection mechanism between the slipper and the ball-head piston. Background Technology

[0002] In the multi-degree-of-freedom mechanical performance testing of key components of high-power wind turbine generators, traditional loading tests generally adopt the parallel axis loading method. This method requires large custom bearings (such as four-point contact ball bearings) to be connected in series in the transmission chain to withstand complex multi-directional loads, and to connect the drive motor to the component under test. However, since megawatt-level test bearings need to be customized according to the parameters of the loading device, the cost of a single set can reach several million yuan; moreover, the customization process involves multiple stages such as design, forging, machining, and heat treatment, and the production cycle can be as long as several months, which is difficult to meet the needs of rapid iterative testing of wind power equipment. At the same time, the custom bearings are tightly integrated with the transmission chain and loading components. When the bearings need to be replaced due to pitting, wear, raceway spalling, or other faults caused by alternating loads, the entire transmission chain (including the drive motor, coupling, and component under test) must be disassembled first, and then the surrounding support structure must be removed. The operation process is cumbersome and takes several weeks. In addition, the maintenance process requires the cooperation of a professional team, which makes the operation and maintenance costs high, and disassembly and reassembly can easily lead to the coaxiality deviation of the transmission chain, affecting the accuracy of subsequent tests. In the multi-degree-of-freedom mechanical performance testing of key components of high-power wind turbine generators, traditional loading tests generally adopt the parallel axis loading method. This method requires large custom bearings (such as four-point contact ball bearings) to be connected in series in the transmission chain to withstand complex multi-directional loads, and to connect the drive motor to the component under test. However, since megawatt-level test bearings need to be customized according to the parameters of the loading device, the cost of a single set can reach several million yuan; moreover, the customization process involves multiple stages such as design, forging, machining, and heat treatment, and the production cycle can be as long as several months, which is difficult to meet the needs of rapid iterative testing of wind power equipment. At the same time, the custom bearings are tightly integrated with the transmission chain and loading components. When the bearings need to be replaced due to pitting, wear, raceway spalling, or other faults caused by alternating loads, the entire transmission chain (including the drive motor, coupling, and component under test) must be disassembled first, and then the surrounding support structure must be removed. The operation process is cumbersome and takes several weeks. In addition, the maintenance process requires the cooperation of a professional team, which makes the operation and maintenance costs high, and disassembly and reassembly can easily lead to the coaxiality deviation of the transmission chain, affecting the accuracy of subsequent tests.

[0003] To solve the above problems, such as Figure 1 , Figure 2As shown, the inventor designed a loading mechanism 4, which includes a base support 410, a loading disk 440, and a support actuation unit. The loading disk 440 is rigidly connected to the component under test 1 and is connected to a drive motor 2 via a coupling 3. The annular area at the edge of the support end face on both sides of the loading disk 440 is the axial bearing surface, and the circumferential surface is the radial bearing surface. The support actuation unit includes an axial actuation component 420, a radial actuation component 430, and a lubrication supply component. The axial actuation component 420 and the radial actuation component 430 are respectively disposed between the base support 410 and the axial bearing surface and the radial bearing surface, respectively. Under the action of the lubrication supply component, lubricating oil is output between the slipper section and the loading disk, forming a... Figure 3 The structure shown supports the axial and radial bearing surfaces of the loading disk 440 through a hydrostatic support oil film 500. During the test, the actuator applies a corresponding loading force through the piston ball head, decomposing the required x / y / z direction force and x / y direction bending moment of the tested component 1 into independent output commands of each axial actuator component 420 and radial actuator. The force is transmitted to the axial and radial bearing surfaces of the loading disk 440 by the support actuator unit. The loading disk 440 integrates all the actuation forces and the torque transmitted by the drive motor 2 to form a six-degree-of-freedom (x / y / z direction force, x / y / z direction bending moment, torque) load, which is then transmitted to the tested component 1 to complete the multi-degree-of-freedom mechanical performance test.

[0004] During the loading test, to compensate for the displacement of the loading disk 440 in the x / y / z directions and to maintain a constant gap on both sides of the hydrostatic support oil film 500 during attitude changes during deflection, a ball joint is required between the slipper and the actuator. However, since the slipper and the ball piston are only connected by a simple hinge without any additional external force constraint structure, when the loading mechanism stops, the hydraulic system is unloaded, the hydrostatic oil film disappears, and the slipper naturally sags due to the loss of support under its own weight. This causes the preset gap (usually 0.02-0.05mm) between the slipper end face and the bearing surface of the loading disk to become severely misaligned, resulting in excessive gaps in some areas, making it difficult for the oil film to form. In some areas, the slipper even comes into direct contact with the loading disk, leading to frictional wear between the slipper and the loading disk during restart. This misalignment directly disrupts the conditions for the formation of the hydrostatic support oil film. When restarting the loading device, it is necessary to adjust the hydraulic system pressure for a long time to recalibrate the clearance. This not only prolongs the test preparation time, but may also cause the oil film to rupture due to improper clearance adjustment, which will aggravate the wear of the slipper and the loading disc, affecting the test accuracy and component life. Utility Model Content

[0005] The present invention aims to provide a self-resetting connection mechanism between the slipper and the ball head piston to avoid the problem of misalignment of the gap after the loading mechanism stops, thereby reducing the preparation work for the test.

[0006] To achieve the above objectives, this utility model adopts the following technical solution: a self-resetting connection mechanism between the sliding shoe and the ball head piston, disposed between the sliding shoe and the ball head piston, includes a spring reset assembly and a positioning assembly. The spring reset assembly includes multiple sets of transverse supports, longitudinal supports, and a tension spring. The transverse supports are evenly distributed along the circumference of the sliding shoe, with one end fixedly connected to the outer edge of the sliding shoe and the other end having a first connecting hole for connecting the tension spring. The longitudinal supports are evenly distributed along the circumference of the ball head piston, with one end threadedly connected to the end face of the ball head piston and the other end having a second connecting hole for connecting the tension spring. The two ends of the tension spring are detachably connected to the first connecting hole and the second connecting hole, respectively, and the tension spring is in a pre-tightened state. The positioning assembly includes a transverse locking nut and a longitudinal locking nut; the connection end between the transverse support and the slide shoe is provided with an external thread, and the transverse locking nut engages with the external thread of the transverse support to lock the relative position of the transverse support and the slide shoe; the connection end between the longitudinal support and the ball head piston is provided with an external thread, and the longitudinal locking nut engages with the external thread of the longitudinal support to lock the relative position of the longitudinal support and the ball head piston.

[0007] The beneficial effects of this solution are as follows: When the machine is stopped, the tension of the pre-tensioned spring overcomes the weight of the slipper, accurately resetting the slipper to the neutral position and maintaining a uniform oil film gap. When restarting, there is no need for a long time to calibrate the gap, and a stable hydrostatic oil film can be quickly rebuilt, which greatly shortens the test preparation time. At the same time, the threaded connection depth of the longitudinal support can be adjusted, and the locking function of the longitudinal locking nut can achieve precise control of the tension spring preload. This can adapt to the reset requirements of slippers of different weights, and the preload does not decay during long-term operation, resulting in strong structural stability.

[0008] In addition, the tension spring is detachably connected to the horizontal and vertical supports. When the spring is fatigued, there is no need to disassemble the slipper and ball piston. Only the spring needs to be replaced, which further shortens the maintenance time and reduces the operation and maintenance cost.

[0009] Furthermore, the number of tension springs is the same as the number of transverse and longitudinal supports, and they are evenly distributed along the circumference of the slipper and the ball head piston.

[0010] Furthermore, the axis of the longitudinal support is perpendicular to the axis of the ball head piston, the axis of the transverse support is perpendicular to the axis of the slipper, and the axes of the longitudinal support and the transverse support are in the same plane.

[0011] Furthermore, the transverse support is fixed to the outer edge of the slipper using a welded or integrally formed structure, while the longitudinal support is threaded to the end face of the ball head piston with an adjustable depth. By setting the transverse support to the outer edge of the slipper using a welded or integrally formed structure, and the longitudinal support to the end face of the ball head piston with an adjustable depth, the preload of the tension spring can be changed by adjusting the depth of the threaded connection between the longitudinal support and the ball head piston during use.

[0012] Furthermore, the preload of the tension spring ranges from 500 to 2000 N.

[0013] Furthermore, a first wear-resistant layer is fixed to the ball head end, and the first wear-resistant layer is fixedly disposed on the surface of the ball head base. A lubricating oil channel is opened inside the ball head base. One end of the lubricating oil channel extends to the side of the ball head piston and forms an oil inlet hole. The oil inlet hole is connected to a lubrication supply component for conveying lubricating oil. The other end extends to the outside of the first wear-resistant layer at the ball head end and forms a central oil outlet hole. The oil inlet hole is connected to the central oil outlet hole. A ball socket is opened on the back of the slipper. The inner surface of the ball socket is quenched and carburized to form a second wear-resistant layer. The surface hardness of the second wear-resistant layer is in the range of HRC55-60. The ball head end of the ball head piston is embedded in the ball socket of the slipper to form a ball joint fit. For traditional steel ball joints, the insufficient wear resistance of steel ball joints leads to rapid material wear due to continuous sliding friction between the ball joint and the socket under heavy loads. This friction also generates high-temperature accumulation, significantly reducing component lifespan and performance. This solution improves the hardness of the contact surface between the ball joint and the socket by adding a first and second wear-resistant layer. Furthermore, a lubricating oil channel within the ball joint base allows for direct injection of lubricating oil between the ball joint and the socket, significantly reducing the coefficient of friction and greatly improving wear resistance. Simultaneously, the lubrication supply component and the lubricating oil channel within the ball joint base not only improve the effectiveness of the lubricating oil but also dissipate the large amount of heat generated by friction, preventing high-temperature accumulation in the ball joint-socket contact area, which could exacerbate material wear or even cause thermal deformation of the ball joint or socket. This improves the structural stability of the connection pair and ensures the proper conduct of loading tests.

[0014] Furthermore, the first wear-resistant layer comprises several segmented tin bronze pieces, evenly distributed circumferentially along the ball end, with axial lubrication channels pre-formed between adjacent segments. These axial lubrication channels communicate with the central oil outlet and extend to the outer side of the ball socket. The axial lubrication channels enable dynamic distribution of lubricating oil during the relative sliding process between the ball end and the ball socket, allowing for faster distribution of lubricating oil to the contact surfaces of the ball end and the ball socket, resulting in a more effective lubrication.

[0015] Furthermore, the edges of the segmented tin bronze are rounded with a radius of 1-3mm. This rounding prevents the edges of the segmented tin bronze from cutting the second wear-resistant layer on the inner surface of the ball joint during rotation, significantly reducing the service life of the second wear-resistant layer. Simultaneously, it avoids the edge scraping that hinders the transmission of lubricant to the friction surfaces, preventing uneven lubricant distribution.

[0016] Furthermore, the tin bronze wear-resistant layer is fixedly connected to the outer surface of the ball head substrate through a diffusion bonding process.

[0017] Furthermore, the segmented tin bronze is made of leaded tin bronze, with a lead content of 5%-8% by mass. The addition of lead allows it to precipitate during friction and form a lubricating film on the surface of the segmented tin bronze, thereby further reducing the friction between the ball end and the socket, and ultimately improving the wear resistance of the connecting structure. Attached Figure Description

[0018] Figure 1 This is an assembly diagram of the disc loading device, drive motor, and tested component mentioned in the background art of this utility model. Figure 2 This is a 3D view of the disc loading device mentioned in the background art after the base support has been removed. Figure 3 This is a schematic diagram of the assembly of the sliding shoe and the loading disk in the background art; Figure 4 This is a three-dimensional view of Embodiment 1 of the present invention; Figure 5 This is a schematic diagram of the structure of the sliding shoe and the ball-head piston in an embodiment of this utility model; Figure 6 This is a schematic diagram of the structure of the ball head end of the ball head piston in Embodiment 2 of this utility model; Figure 7 This is a schematic diagram of the internal structure of the ball head end in an embodiment of this utility model.

[0019] The reference numerals in the accompanying drawings include: 1. Component under test; 2. Drive motor; 3. Coupling; 4. Loading mechanism; 410. Base support; 420. Axial actuation assembly; 430. Radial actuation assembly; 440. Loading disc; 450. Tension spring; 451. Horizontal locking nut; 452. Vertical locking nut; 401. Actuator housing; 402. Ball end; 403. Slipper; 404. Ball socket; 405. Connector; 501. Split-type tin bronze; 502. Lubrication channel; 504. Oil inlet; 503. Center oil outlet; 500. Static pressure support oil film. Detailed Implementation

[0020] Example 1 Example 1 is basically as shown in the appendix. Figure 1-4 As shown, Figure 4-5 The self-resetting connection mechanism between the slipper and the ball head piston shown includes a positioning assembly and a spring return assembly. The positioning assembly includes a horizontal locking nut 451 and a vertical locking nut 452; as shown... Figure 5 As shown, the horizontal locking nut 451 and the vertical locking nut 452 are respectively fixed to the slipper 403 and the side wall of the ball end 402.

[0021] The spring return assembly includes multiple sets of transverse supports, longitudinal supports, and a tension spring 450. The transverse supports are evenly distributed along the circumference of the slipper 403, with one end fixedly connected to the outer edge of the slipper 403 and the other end having a first connecting hole for connecting the tension spring 450. The longitudinal supports are evenly distributed along the circumference of the ball-head piston, with one end threadedly connected to the end face of the ball-head piston and the other end having a second connecting hole for connecting the tension spring 450. The two ends of the tension spring 450 are detachably connected to the first connecting hole and the second connecting hole, respectively. Furthermore, the tension spring 450 is in a pre-tightened state; specifically, the connection end between the transverse support and the slipper 403 is provided with an external thread, and the transverse locking nut 451 engages with the external thread of the transverse support to lock the relative position of the transverse support and the slipper 403; the connection end between the longitudinal support and the ball piston is provided with an external thread, and the longitudinal locking nut 452 engages with the external thread of the longitudinal support to lock the relative position of the longitudinal support and the ball piston, so as to adjust the pre-tightening force of the tension spring 450. In this embodiment, the pre-tightening force range of the tension spring 450 is 500-2000N.

[0022] During operation, the preload of the tension spring 450 is much smaller than the oil film support force, and it is in a flexible following state, which does not interfere with the adaptive attitude adjustment function of the slipper 403, thus ensuring the accuracy of the multi-degree-of-freedom loading test.

[0023] When the machine stops, the hydraulic system is unloaded. The preload of the tension spring 450 overcomes the weight of the slipper 403 and pulls the slipper 403 back to the preset neutral position to maintain the clearance accuracy between the slipper 403 and the loading disc 440, ensuring that the oil film is quickly rebuilt when restarting.

[0024] Example 2 Based on Example 1, to improve the wear resistance of the connection between the slipper 403 and the ball piston, a wear-resistant structure is also included, such as... Figure 6 , Figure 7As shown, a first wear-resistant layer is fixed to the ball end 402. The first wear-resistant layer includes 4-8 segments of tin bronze 501. The segments of tin bronze 501 are fixed to the surface of the ball end substrate by a diffusion bonding process and are evenly distributed around the ball end 402. An axial lubrication channel 502 is reserved between two adjacent segments of tin bronze 501. The axial lubrication channel 502 is connected to the central oil outlet 503 and extends to the outside of the ball socket 404. The width is 2-5mm. The edges of the segments of tin bronze 501 are machined with a rounded corner with a radius of 1-3mm. In this embodiment, the number of segments of tin bronze 501 is 6, the width of the axial lubrication channel 502 is 3mm, and the radius of the rounded corner of the edge of the segments of tin bronze 501 is 2mm.

[0025] The ball head base has a lubricating oil channel inside. One end of the lubricating oil channel extends to the side of the ball head piston and forms an oil inlet 504. The oil inlet 504 is connected to a lubrication supply component for conveying lubricating oil. The other end extends to the outside of the first wear-resistant layer of the ball head end 402 and forms a central oil outlet 503. Specifically, as shown... Figure 6 As shown, the lubricating oil passage includes a transverse section and a longitudinal section. The transverse section extends radially along the ball piston, and its outer end forms an oil inlet hole 504. The longitudinal section extends axially along the ball piston, and its top end forms a central oil outlet hole 503. The transverse section and the longitudinal section are perpendicularly connected, and the axis of the longitudinal section coincides with the center of the ball end 402 of the ball piston.

[0026] In use, firstly, the lubrication supply assembly is activated. Lubricating oil flows from the side oil inlet 504 through the internal flow channel and out from the central oil outlet 503, flowing along the direction of the interlobular flow channel. As the ball head and the socket 404 move relative to each other, the lubricating oil in the interlobular flow channel passes through the rounded edges of the lobe and is carried into the space between the segmented tin bronze 501 and the second wear-resistant layer, playing a role in auxiliary lubrication. At the same time, through the lubrication flow channel 502 and the rounded edges of the segmented tin bronze 501, the lubricating oil in the lubrication flow channel 502 is transferred to the friction surfaces during the relative sliding process of the ball head and the socket 404. This not only assists in lubrication but also removes the heat generated by friction. In addition, during use, the wear debris generated by the continuous sliding friction between the ball head end 402 and the socket 404 can also be discharged through the lubrication flow channel 502, thus preventing the wear debris generated by the continuous sliding friction between the ball head end 402 and the socket 404 from not being discharged in time, which would scratch the surface of the parts and aggravate wear.

[0027] Example 3 Based on Example 2, the material of the segmented tin bronze 501 is lead-containing tin bronze with a lead content of 5%-8% by mass. The lubrication supply assembly includes a lubricating oil pump, an oil supply pipe and a flow regulating valve. The outlet of the lubricating oil pump is sealed to the oil inlet 504 through the oil supply pipe. The flow regulating valve is connected in series with the oil supply pipe and can adjust the lubricating oil flow rate to 0.5-2L / min.

[0028] In use, the lubricating oil pump is connected to the oil inlet 504 through the branch oil pipe, and the lubricating oil is introduced into the space between the ball end 402 and the ball socket 404 through the oil inlet 504 to achieve lubrication between the ball end 402 and the ball socket 404. At the same time, the first wear-resistant layer of the ball end 401 of the ball piston and the second wear-resistant layer of the ball socket 404 of the slipper 403 cooperate with the lubricating film formed by the precipitation of lead element in tin bronze, which further reduces the sliding friction of the ball joint.

[0029] Example 4 Based on Example 3, the contact area between the ball head section and the ball socket 404 is reduced to less than a hemisphere. Compared with the traditional "greater than a hemisphere" structure, after the contact area is reduced to less than a hemisphere, the material usage of the first wear-resistant layer can be reduced by 30%-40%, and the weight of the component can be significantly reduced, thereby meeting the overall lightweight requirements of the loading device. At the same time, the manufacturing and transportation costs are reduced by 25%-35%.

[0030] The above descriptions are merely embodiments of this utility model. Commonly known technical solutions and / or characteristics are not described in detail here. It should be noted that the technical means used to solve problems in the above embodiments of this utility model can be combined to solve multiple technical problems simultaneously. For those skilled in the art, several modifications and improvements can be made without departing from the technical solution of this utility model, and these should also be considered within the scope of protection of this utility model. These modifications will not affect the effectiveness of the implementation of this utility model or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. A self-resetting connection mechanism between the sliding shoe and the ball-head piston, disposed between the sliding shoe and the ball-head piston, characterized in that: The device includes a spring return assembly and a positioning assembly. The spring return assembly includes multiple sets of transverse supports, longitudinal supports, and a tension spring. The transverse supports are evenly distributed along the circumference of the slide shoe, with one end fixedly connected to the outer edge of the slide shoe and the other end having a first connecting hole for connecting the tension spring. The longitudinal supports are evenly distributed along the circumference of the ball head piston, with one end threadedly connected to the end face of the ball head piston and the other end having a second connecting hole for connecting the tension spring. The two ends of the tension spring are detachably connected to the first connecting hole and the second connecting hole, respectively, and the tension spring is in a pre-tightened state. The positioning assembly includes a transverse locking nut and a longitudinal locking nut; the connection end between the transverse support and the slide shoe is provided with an external thread, and the transverse locking nut engages with the external thread of the transverse support to lock the relative position of the transverse support and the slide shoe; the connection end between the longitudinal support and the ball head piston is provided with an external thread, and the longitudinal locking nut engages with the external thread of the longitudinal support to lock the relative position of the longitudinal support and the ball head piston.

2. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 1, characterized in that: The number of tension springs is the same as the number of transverse and longitudinal supports, and they are evenly distributed along the circumference of the slipper and the ball head piston.

3. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 2, characterized in that: The axis of the longitudinal support is perpendicular to the axis of the ball head piston, and the axis of the transverse support is perpendicular to the axis of the slipper. The axes of the longitudinal support and the transverse support are in the same plane.

4. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 3, characterized in that: The transverse support is fixed to the outer edge of the slipper by welding or integral molding, and the longitudinal support is threaded to the end face of the ball head piston with adjustable depth.

5. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 4, characterized in that: The preload of the tension spring ranges from 500 to 2000 N.

6. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 5, characterized in that: A first wear-resistant layer is fixed to the ball head end, and the first wear-resistant layer is fixedly set on the surface of the ball head base. A lubricating oil channel is opened inside the ball head base. One end of the lubricating oil channel extends to the side of the ball head piston and forms an oil inlet hole. The oil inlet hole is connected to a lubrication supply component for conveying lubricating oil. The other end extends to the outside of the first wear-resistant layer at the ball head end and forms a central oil outlet hole. The oil inlet hole is connected to the central oil outlet hole. A ball socket is opened on the back of the slipper. The inner surface of the ball socket is quenched and carburized to form a second wear-resistant layer. The surface hardness of the second wear-resistant layer is in the range of HRC55-60. The ball head end of the ball head piston is embedded in the ball socket of the slipper to form a ball joint fit.

7. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 6, characterized in that: The first wear-resistant layer includes several segmented tin bronzes, which are evenly distributed around the ball end. An axial lubrication channel is reserved between two adjacent segments of tin bronzes. The axial lubrication channel is connected to the central oil outlet hole and extends to the outside of the ball socket.

8. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 7, characterized in that: The edges of the segmented tin bronze are rounded, with a radius of 1-3mm.

9. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 7, characterized in that: The tin bronze wear-resistant layer is fixedly connected to the outer surface of the ball head substrate through a diffusion bonding process.

10. The self-resetting connection mechanism between the slipper and the ball head piston according to claim 7, characterized in that: The material of the segmented tin bronze is lead-containing tin bronze, with a lead content of 5%-8% by mass.

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