Balancer and manufacturing method thereof

Abstract

The invention discloses a balancer and a manufacturing method thereof, and relates to the field of crane pipe equipment. The balancer comprises a spring cylinder which comprises a pull rod, a sleeve and a main rebound assembly. The auxiliary springback assembly comprises a shell, auxiliary springs, a sliding rail and a pulley, the shell is fixedly connected with the sleeve, the auxiliary springs are fixedly arranged on the inner wall of the shell, the sliding rail is arranged on the auxiliary springs in the moving direction of the pull rod, the pulley is arranged on the abutting face of the sliding rail and fixedly connected with the pull rod, the abutting face is an inclined face, one end of the abutting face is close to the pull rod, and the other end of the abutting face is close to the sliding rail. The other end is far away from the pull rod; when the pull rod moves in the direction of increasing the elastic force of the main rebound assembly, the pulley moves towards the end, close to the pull rod, of the abutting face. The auxiliary springback assembly promotes the elastic force provided by the main springback assembly to be reduced, and the reduction degree can be changed, so that under the condition that the height of a pipeline of the crane pipe is changed, the service life of a connector flange of the crane pipe and the service life of a tank car connector flange are prolonged, and the sealing performance of the crane pipe and the tank car connector flange are improved.

Description

Technical Field

[0001] The invention relates to the field of crane equipment, and in particular to a balancer and a manufacturing method thereof. Background Art

[0002] In the existing crane technology, see Figure 1 As shown, a balancer will be installed on the pipeline of the crane pipe, and the balancer is generally a cylinder, a hydraulic cylinder or a spring cylinder. When the spring cylinder is used as the balancer, the specific structure is that the spring cylinder connecting plate is fixed, and one end of the pipeline and the spring cylinder connecting plate are rotatably connected. The pull rod of the spring cylinder is connected to the other end of the spring cylinder connecting plate by a first hinge, and a second hinge is fixedly arranged at the middle section of the pipeline. The function of the balancer is to offset the gravity of the pipeline to avoid greater stress at the interface flange of the crane pipe and the interface of the tank truck, resulting in reduced service life and sealing of the interface flange of the crane pipe and the interface flange of the tank truck.

[0003] However, the existing crane pipe technology uses a spring cylinder as a balancer, and there are problems in that: when the interface flange of the crane pipe needs to dock with different vehicles, the docking height will change, so the height of the end of the pipe close to the interface flange needs to be adjusted. When the pipe is lifted upward, the pull rod needs to be retracted into the spring cylinder sleeve to shorten the entire spring cylinder, but at this time the elastic force provided by the spring cylinder is reduced, and there is a problem that it is not enough to offset the gravity of the pipe, which causes the pipe to tilt downward in advance, and will generate a downward force on the interface connection; when the pipe is pressed downward, the pull rod needs to extend out of the spring cylinder sleeve to increase the entire spring cylinder, but at this time the elastic force provided by the spring cylinder is increased, and there is a problem that even after offsetting the gravity of the pipe, the spring still has residual elastic force, which pulls the pipe upward, thereby causing the pipe to be lifted upward in advance, which will generate an upward force on the interface connection. Therefore, after the height of the pipe changes, the service life and sealing of the crane pipe interface flange and the tank truck interface flange will be reduced. Summary of the invention

[0004] In view of the defects existing in the prior art, the technical problem solved by the present invention is: how to improve the service life and sealing performance of the interface flange of the crane pipe and the interface flange of the tank truck when the pipeline height changes.

[0005] To achieve the above objectives, in a first aspect, the present invention provides a balancer, comprising: The spring cylinder comprises a pull rod, a sleeve and a main rebound assembly, wherein the pull rod is arranged inside the sleeve, and one end of the pull rod is located outside the sleeve, and a baffle is fixedly arranged on the other end of the pull rod, and the main rebound assembly is sleeved on the pull rod, and one end of the main rebound assembly abuts against the baffle, and the other end abuts against the inner end of the sleeve; A secondary rebound assembly, comprising a housing, a secondary spring, a slide rail and a pulley, wherein the housing is fixedly connected to the sleeve, a plurality of secondary springs are fixedly arranged on the inner wall of the housing, the slide rail is arranged on the secondary spring along the moving direction of the pull rod, the pulley is arranged on the abutment surface of the slide rail, and the pulley is fixedly connected to the pull rod, the abutment surface is an inclined surface, one end of the abutment surface is close to the pull rod, and the other end is far away from the pull rod; When the pull rod moves in a direction to increase the elastic force of the main rebound component, the pulley moves toward the abutment surface close to one end of the pull rod.

[0006] By adopting the above technical solution, when the pull rod is extended and retracted, the degree to which the auxiliary rebound component offsets the elastic force of the main rebound component will change with the movement of the pull rod, so that the crane pipe is always in a balanced state. Therefore, when the height of the pipeline changes, the service life and sealing performance of the interface flange of the crane pipe and the tank truck interface flange are improved.

[0007] In combination with the first aspect, in one embodiment, a baffle adjustment assembly is provided on the baffle, the adjustment assembly includes a thread opened on the pull rod and a nut abutting against the baffle, the nut is threadedly connected to the pull rod, and the thread is used to adjust the position of the baffle on the pull rod.

[0008] By adopting the above technical solution, since the nut is abutted against one side of the baffle and the nut is threadedly connected to the pull rod, the nut can be moved on the pull rod by screwing the nut, thereby driving the baffle to move on the pull rod, that is, changing the position of the baffle on the pull rod. Since the baffle is abutted against the main rebound assembly, the initial elastic force of the main rebound assembly is changed. At the same time, the baffle will drive the pulley to move on the slide rail, thereby changing the initial elastic force of the auxiliary spring. The position of the baffle on the pull rod can be adjusted according to actual needs, thereby improving the applicability of the crane pipe.

[0009] In one embodiment, a plurality of support rods are provided on one side of the slide rail having the auxiliary spring, one end of the support rod is fixed on the slide rail, the other end of the support rod is inserted into the auxiliary spring, and there is always a gap between the other end of the support rod and the inner wall of the shell.

[0010] By adopting the above technical solution, it is avoided that the middle part of the auxiliary spring bends to the side when the auxiliary spring is compressed. Therefore, a support rod is installed on the slide rail to achieve normal compression of the auxiliary spring along the support rod.

[0011] In one embodiment, the number of the support rods is the same as the number of the auxiliary springs; Alternatively, the number of the support rods and the auxiliary springs are different.

[0012] By adopting the above technical solution, it can be determined whether the auxiliary spring needs to be sleeved on the support rod according to actual needs and design conditions.

[0013] In one embodiment, the sleeve is provided with a slide groove along the moving direction of the pull rod, the baffle is fixedly connected to the pulley through a connecting rod, and the connecting rod is movably provided on the slide groove.

[0014] By adopting the above technical solution, the pulley and the pull rod can be kept in a relatively static state, and the structural design will not affect the normal operation of the main rebound component.

[0015] In one embodiment, a plurality of the pulleys are evenly arranged around the baffle, and the number of the slide grooves is the same as the number of the connecting rods.

[0016] By adopting the above technical scheme, the number of auxiliary rebound components can be designed according to actual needs and design conditions. The more auxiliary rebound components there are, the greater the degree of reduction in the elastic force provided by the main rebound component, and the force of the auxiliary rebound components on the pull rod is uniform. However, the number of slide grooves must be the same as the number of connecting rods, so as to realize the normal movement of the pulley driven by the baffle, thereby further improving the applicability of the crane pipe.

[0017] In one embodiment, the main rebound assembly includes a plurality of main springs, a plurality of retaining rings are arranged on the pull rod along its axial direction, and a main spring is arranged between two adjacent retaining rings.

[0018] By adopting the above technical solution, the design can place main springs of different types between two adjacent baffle rings to meet more needs. At the same time, if a baffle adjustment assembly is set on this basis, it will only affect the initial elastic force of the main spring set between the baffle and the baffle ring closest to it, thereby allowing for more subtle adjustments.

[0019] In one embodiment, a main spring is provided between the baffle and the baffle ring closest thereto; Alternatively, there is no main spring between the baffle and the baffle ring closest to it.

[0020] By adopting the above technical solution, it can be determined whether to install the main spring between the baffle and the baffle ring closest to it according to actual needs and design conditions.

[0021] In a second aspect, the present invention provides a method for manufacturing a balancer, comprising the following steps: Select the elastic coefficient and number of sections of the main spring and install it inside the sleeve; Design the abutment surface curve of the slide rail; Select the elastic coefficient and installation quantity of the auxiliary spring, and install it between the slide rail and the inner wall of the housing; The pulley is fixedly connected to the baffle plate through a connecting rod, and the pulley is rollably arranged on the slide rail to form a secondary rebound component; The auxiliary rebound component is sleeved on the sleeve to form a balancer.

[0022] In conjunction with the second aspect, in one implementation, designing the abutment surface curve of the slide rail specifically includes: The surface curve equation of the slide rail abutment surface is obtained by using a calculation formula, wherein the calculation formula is: Wherein, a coordinate system is established with the starting point of the curved surface of the slide rail contact surface as the origin, the direction parallel to the pull rod as the x-axis, and the direction perpendicular to the pull rod as the y-axis, and θ is the angle between the tangent line of the contact surface between the slide rail and the pulley and the x-axis; 2N x +F1=F Among them, N x is the force on the point on the surface in the x direction generated by the secondary spring force F2, F1 is the elastic force of the main spring, and F is the resultant force generated by the balancer; If the resultant force F does not change within a certain stroke, that is, ΔF = 0, then 2ΔN x =ΔF1 2×ΔF2 cosθ=ΔF1 This equation is the surface curve equation, where a is the pre-compression of the auxiliary spring, k1 is the elastic coefficient of the main spring, and k2 is the elastic coefficient of the auxiliary spring.

[0023] By adopting the above technical solution, the curved surface shape of the slide rail can be designed according to actual needs to adapt to different crane pipes and construction requirements.

[0024] In summary, the present invention includes at least one of the following beneficial technical effects: 1. Through the structural design of the auxiliary rebound component, the rebound force of the auxiliary spring acting on the pulley can be divided into a thrust along the pull rod axis and a clamping force of the pulley close to the baffle. The thrust in the axis direction causes the baffle to move inside the sleeve, that is, the elastic force provided by the main rebound component is reduced, thereby solving the problem that the pipeline will generate an upward or downward force on the pipeline after the height is adjusted. Therefore, when the height of the crane pipe changes, the service life and sealing performance of the interface flange of the crane pipe and the tank truck interface flange are improved; 2. The thrust in the axial direction will change with the selection of different models and quantities of auxiliary springs, as well as the slope design of the slope of the slide rail. The above variables can be designed according to actual needs to meet more usage requirements, thereby improving the applicability of the crane pipe. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 A schematic diagram of the structure of a crane pipe using a spring cylinder as a balancer in the related art; Figure 2This is a schematic diagram of the structure of a crane pipe according to an embodiment of the present invention; Figure 3 It is a structural schematic diagram of a balancer according to an embodiment of the present invention; Figure 4 for Figure 3 perspective drawing; Figure 5 for Figure 4 Enlarged view of part A.

[0026] In the figure: 1- bracket, 2- pipe, 3- spring cylinder connecting plate, 4- spring cylinder, 401- pull rod, 402- sleeve, 403- slide groove, 404- main spring, 405- retaining ring, 406- baffle, 407- nut, 408- thread, 5- first hinge, 6- second hinge, 7- rotating pipe joint, 8- auxiliary rebound assembly, 801- housing, 802- support rod, 803- auxiliary spring, 804- slide rail, 805- pulley, 806- connecting rod, 9- interface flange. DETAILED DESCRIPTION

[0027] The embodiments of the present invention are further described in detail below with reference to the accompanying drawings.

[0028] The balancer in the embodiment of the present invention is shown in FIG. Figure 2-4 As shown, the balancer includes a spring cylinder 4, which includes a pull rod 401, a sleeve 402, a main rebound component and a secondary rebound component 8. The pull rod 401 is movably arranged inside the sleeve 402, and one end of the pull rod 401 close to the spring cylinder connecting plate 3 is located outside the sleeve 402, and the other end of the pull rod 401 is fixedly provided with a baffle 406. The main rebound component is sleeved on the pull rod 401, and one end of the main rebound component is against the baffle 406, and the other end thereof is against the inner end of the sleeve 402, and the secondary rebound component 8 is arranged on the baffle 406; The auxiliary rebound component 8 includes a shell 801, an auxiliary spring 803, a slide rail 804 and a pulley 805. The shell 801 is sleeved on the end of the sleeve 402 away from the spring cylinder connecting plate 3. The sleeve 402 is provided with a slide groove 403 along its axial direction. The baffle 406 is fixedly connected to the pulley 805 through a connecting rod 806, and the connecting rod 806 is movably arranged on the slide groove 403. The inner wall of the shell 801 is provided with a slide rail 804 through a plurality of auxiliary springs 803. The pulley 805 can be rotatably arranged on the slide rail 804. The slide rail 804 has abutment surfaces from low to high. The abutment surface of the slide rail 804 away from the spring cylinder connecting plate 3 is the lowest, and the abutment surface of the slide rail 804 close to the spring cylinder connecting plate 3 is the highest.

[0029] It can be seen that, based on the existing method of the present invention of counteracting the gravity of the pipeline 2 by the pull rod 401, the sleeve 402 and the main rebound component, a shell 801 of the auxiliary rebound component 8 is set at the end of the sleeve 402 away from the spring cylinder connecting plate 3, and a slide rail 804 is set on the inner wall of the shell 801 through the auxiliary spring 803, and a pulley 805 is movably set on the slide rail 804, and the non-rolling part of the pulley 805 is fixedly connected to the baffle 406 through the connecting rod 806, and the connecting rod 806 passes through the slide groove 403 provided on the sleeve 402. Therefore, when the baffle 406 moves in the sleeve 402, it will drive the pulley 805 to move on the slide rail 804, and because the slide rail 804 has a contact surface from low to high, the pulley 805 05 During the movement on the slide rail 804, the length of the connecting rod 806 is unchanged, so it will squeeze the auxiliary spring 803 between the slide rail 804 and the housing 801, and the auxiliary spring 803 will generate a rebound force. The rebound force acting on the pulley 805 can be divided into a thrust along the axial direction of the pull rod 401 and a clamping force of the pulley 805 close to the baffle 406. The thrust in the axial direction prompts the baffle 406 to move toward the inside of the sleeve 402, that is, it prompts the elastic force provided by the main rebound component to decrease, so that the thrust in the axial direction will work together with the main rebound component to offset the gravity of the pipeline 2, and the thrust in the axial direction will change with the selection of different models and quantities of the auxiliary spring 803 and the slope design of the slope of the slide rail 804.

[0030] Therefore, when the pipeline 2 is lifted upward, although the elastic force provided by the main rebound component is reduced, the secondary rebound component 8 causes the degree of reduction of the elastic force provided by the main rebound component to decrease, so the elastic force provided by the main rebound component is sufficient to offset the gravity of the pipeline 2, avoiding the pipeline 2 from tilting downward in advance, resulting in a downward force at the interface connection; when the pipeline 2 is pressed downward, although the elastic force provided by the main rebound component is increased, the secondary rebound component 8 causes the degree of reduction of the elastic force provided by the main rebound component to increase, so the elastic force provided by the main rebound component is only enough to offset the gravity of the pipeline 2, avoiding the pipeline 2 from lifting upward in advance, resulting in an upward force at the interface connection. Therefore, when the height of the pipeline 2 changes, the crane pipe improves the service life and sealing performance of the interface flange 9 of the crane pipe and the interface flange 9 of the tank truck.

[0031] Preferably, see Figure 2 As shown, the crane pipe also includes a bracket 1, a rotating pipe joint 7, a pipe 2 and an interface flange 9. The pipe 2 is fixedly installed on the bracket 1. Two adjacent pipes 2 are connected by a rotating pipe joint 7, and the pipe 2 and the interface flange 9 are connected by a rotating pipe joint 7. A spring cylinder connecting plate 3 is provided on the rotating pipe joint 7. The spring cylinder connecting plate 3 is connected to the pull rod 401 of the spring cylinder 4 through a first hinge 5. A second hinge 6 is fixedly provided at the middle section of the pipe 2, and the second hinge 6 is rotatably connected to the middle section of the spring cylinder 4.

[0032] Preferably, see Figure 4 As shown, a baffle 406 adjustment assembly is provided on the baffle 406 , and the adjustment assembly includes a thread 408 opened on the pull rod 401 and a nut 407 abutting against the baffle 406 , the nut 407 is threadedly connected to the pull rod 401 , and the thread 408 is used to adjust the position of the baffle 406 on the pull rod 401 .

[0033] Specifically, the nut 407 abuts against a side of the spring cylinder connecting plate 3 away from the baffle 406, and the nut 407 is threadedly connected to the pull rod 401. The nut 407 is moved on the pull rod 401 by screwing the nut 407 clockwise or counterclockwise, thereby driving the baffle 406 to move on the pull rod 401, that is, changing the position of the baffle 406 on the pull rod 401. Because the baffle 406 abuts against the main rebound assembly, the initial elastic force of the main rebound assembly is changed. At the same time, the baffle 406 will drive the pulley 805 to move on the slide rail 804, thereby also changing the initial elastic force of the auxiliary spring 803. The position of the baffle 406 on the pull rod 401 can be adjusted according to actual needs, thereby improving the applicability of the crane tube.

[0034] Preferably, see Figure 4 As shown, a plurality of support rods 802 are provided on one side of the slide rail 804 having a secondary spring 803, one end of the support rod 802 is fixed on the slide rail 804, and the other end of the support rod 802 is inserted into the interior of the secondary spring 803, and there is always a gap between the other end of the support rod 802 and the inner wall of the shell 801.

[0035] Specifically, a plurality of support rods 802 are installed on the slide rail 804, and the direction of the support rods 802 is consistent with the direction of the auxiliary springs 803, and one auxiliary spring 803 is sleeved on one support rod 802, so as to prevent the middle part of the auxiliary spring 803 from bending to the side when the auxiliary spring 803 is compressed. Therefore, the support rods 802 play a guiding role for the auxiliary spring 803, so that the auxiliary spring 803 can be normally compressed along the support rods 802; at the same time, there is always a gap between the other end of the support rod 802 and the inner wall of the shell 801, that is, no matter how the auxiliary spring 803 is compressed, the other end of the support rod 802 will not contact the inner wall of the shell 801, and will not affect the compression degree of the auxiliary spring 803, and only plays a guiding role. Therefore, the length of the support rod 802 can be designed according to needs.

[0036] Further, the number of support rods 802 and auxiliary springs 803 is the same; Alternatively, the number of the support rods 802 and the number of the auxiliary springs 803 are different.

[0037] Specifically, whether the auxiliary spring 803 needs to be mounted on the support rod 802 can be determined based on actual needs and design conditions. For example, there are a total of five auxiliary springs 803, three of which have support rods 802 inserted inside, and another two of the auxiliary springs 803 can be arranged between the three support rods 802, or the other two auxiliary springs 803 may not be arranged between the three support rods 802, so as to improve the applicability of the crane tube.

[0038] Preferably, the auxiliary rebound component 8 has multiple groups, that is, multiple pulleys 805 are evenly arranged around the baffle 406, and the number of the sliding grooves 403 is the same as the number of the connecting rods 806.

[0039] Specifically, two groups of auxiliary rebound components 8 are provided. It should be noted that the number of shells 801 is always one, that is, two groups of auxiliary springs 803, slide rails 804 and pulleys 805 are installed on the same shell 801, and the number of slide grooves 403 needs to be the same as the number of groups of pulleys 805 to avoid that the pulleys 805 cannot work normally. The number of auxiliary rebound components 8 can be designed according to actual needs and design conditions. The more auxiliary rebound components 8 there are, the greater the degree of reduction in the elastic force provided by the main rebound component. However, it must be satisfied that the number of slide grooves 403 is the same as the number of groups of auxiliary rebound components 8, so that the baffle 406 drives the pulley 805 to move normally, thereby further improving the applicability of the crane pipe.

[0040] Preferably, see Figure 4 As shown, the main rebound assembly includes a plurality of main springs 404 , a plurality of retaining rings 405 are arranged on the pull rod 401 along its axial direction, and a main spring 404 is arranged between two adjacent retaining rings 405 .

[0041] Specifically, the main rebound assembly includes three main springs 404, which are denoted as the first main spring 404, the second main spring 404 and the third main spring 404. Two retaining rings 405 are arranged on the pull rod 401 along its axial direction, which are denoted as the first retaining ring 405 and the second retaining ring 405. The first main spring 404 is arranged between the first retaining ring 405 and the inner end of the sleeve 402, the second main spring 404 is arranged between the first retaining ring 405 and the second retaining ring 405, and the third main spring 404 is arranged between the second retaining ring 405 and the baffle 406. The models of the first main spring 404, the second main spring 404 and the third main spring 404 can be the same or different to meet more needs. At the same time, if a baffle 406 adjustment assembly is arranged on this basis, it will only affect the initial elastic force of the main spring 404 arranged between the baffle 406 and the retaining ring 405 closest to it, so that more subtle adjustments can be made.

[0042] Furthermore, a main spring 404 is provided between the baffle 406 and the baffle ring 405 closest thereto; Alternatively, there is no main spring 404 between the baffle plate 406 and the baffle ring 405 closest to it.

[0043] Specifically, whether to install the main spring 404 between the baffle 406 and the closest baffle ring 405 can be determined according to actual needs and design conditions, that is, whether the initial elastic force of the main spring 404 will be affected if an adjustment component of the baffle 406 is provided.

[0044] Preferably, the pulley 805 is a concave pulley, and a boss matching the concave pulley is provided on the slide rail 804, and the concave pulley and the boss are connected in a concave-convex manner.

[0045] Specifically, the middle part of the pulley 805 is grooved along its circumference, and the groove matches the boss of the slide rail 804. This design makes the connection between the pulley 805 and the slide rail 804 more stable when the pulley 805 moves, thereby preventing the pulley 805 from falling off the slide rail 804.

[0046] The manufacturing method of the balancer in the embodiment of the present invention comprises the following steps: Select the elastic coefficient and number of sections of the main spring 404 and install it inside the sleeve 402; Designing the abutment surface curve of the slide rail 804; Select the elastic coefficient and installation quantity of the auxiliary spring 803, and install it between the slide rail 804 and the inner wall of the housing; The pulley 805 is fixedly connected to the baffle 406 via a connecting rod 806, and the pulley 805 is rollably arranged on the slide rail 804 to form a secondary rebound component 8; The auxiliary rebound component 8 is sleeved on the sleeve 402 to form a balancer.

[0047] Preferably, the design of the abutment surface curve of the slide rail 804 specifically includes: The first calculation formula is used to obtain the surface curve equation of the abutting surface of the slide rail 804, wherein the first calculation formula is: The starting point of the curved surface of the slide rail 804 abutting surface is taken as the origin, the direction parallel to the pull rod is taken as the x-axis, and the direction perpendicular to the pull rod is taken as the y-axis to establish a coordinate system, θ is the angle between the tangent line of the contact surface between the slide rail 804 and the pulley 805 and the x-axis; 2N x +F1=F Among them, N x is the force on the point on the curved surface in the x direction generated by the elastic force F2 of the secondary spring 803, F1 is the elastic force of the main spring 404, and F is the resultant force generated by the balancer; If the resultant force F does not change within a certain stroke, that is, ΔF = 0, then 2ΔN x =ΔF1 2×ΔF2cosθ=ΔF1 This equation is a surface curve equation, where a is the pre-compression amount of the auxiliary spring 803 , k1 is the elastic coefficient of the main spring 404 , and k2 is the elastic coefficient of the auxiliary spring 803 .

[0048] The above description is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A balancer, characterized in that: It includes: The spring cylinder (4) comprises a pull rod (401), a sleeve (402) and a main rebound assembly, wherein the pull rod (401) is arranged inside the sleeve (402), and one end of the pull rod (401) is located outside the sleeve (402), and a baffle (406) is fixedly arranged on the other end of the pull rod (401), and the main rebound assembly is sleeved on the pull rod (401), and one end of the main rebound assembly abuts against the baffle (406), and the other end of the main rebound assembly abuts against the inner end of the sleeve (402); A secondary rebound assembly (8), comprising a housing (801), a secondary spring (803), a slide rail (804) and a pulley (805); the housing (801) is fixedly connected to the sleeve (402); a plurality of secondary springs (803) are fixedly arranged on the inner wall of the housing (801); the slide rail (804) is arranged on the secondary spring (803) along the moving direction of the pull rod (401); the pulley (805) is arranged on the abutment surface of the slide rail (804); and the pulley (805) is fixedly connected to the pull rod (401); the abutment surface is an inclined surface, one end of the abutment surface is close to the pull rod (401), and the other end is far away from the pull rod (401); When the pull rod (401) moves in a direction to increase the elastic force of the main rebound component, the pulley (805) moves toward the abutment surface close to one end of the pull rod (401).

2. The balancer according to claim 1, characterized in that: The baffle (406) is provided with a baffle (406) adjustment component, which includes a thread (408) opened on the pull rod (401) and a nut (407) abutting against the baffle (406), the nut (407) is threadedly connected to the pull rod (401), and the thread (408) is used to adjust the position of the baffle (406) on the pull rod (401).

3. The balancer according to claim 1, characterized in that: A plurality of support rods (802) are arranged on one side of the slide rail (804) provided with the auxiliary spring (803), one end of the support rod (802) is fixed on the slide rail (804), the other end of the support rod (802) is inserted into the interior of the auxiliary spring (803), and there is always a gap between the other end of the support rod (802) and the inner wall of the housing (801).

4. The balancer according to claim 3, characterized in that: The number of the support rods (802) and the number of the auxiliary springs (803) are the same; Alternatively, the number of the support rods (802) and the number of the auxiliary springs (803) are different.

5. The balancer according to claim 1, characterized in that: The sleeve (402) is provided with a slide groove (403) along the moving direction of the pull rod (401), the baffle (406) is fixedly connected to the pulley (805) via a connecting rod (806), and the connecting rod (806) is movably arranged on the slide groove (403).

6. The balancer according to claim 5, characterized in that: The plurality of pulleys (805) are evenly arranged around the baffle (406), and the number of the slide grooves (403) is the same as the number of the connecting rods (806).

7. The balancer according to claim 1, characterized in that: The main rebound assembly comprises a plurality of main springs (404), a plurality of retaining rings (405) are arranged on the pull rod (401) along its axial direction, and a main spring (404) is arranged between two adjacent retaining rings (405).

8. The balancer according to claim 7, characterized in that: A main spring (404) is arranged between the baffle (406) and the baffle ring (405) closest to it; Alternatively, there is no main spring (404) between the baffle (406) and the baffle ring (405) closest to it.

9. A method for manufacturing a balancer according to any one of claims 1 to 8, characterized in that: It includes the following steps: Select the elastic coefficient and number of sections of the main spring (404), and install it inside the sleeve (402); Designing the abutment surface curve of the slide rail (804); Select the elastic coefficient and installation quantity of the auxiliary spring (803), and install it between the slide rail (804) and the inner wall of the housing; The pulley (805) is fixedly connected to the baffle (406) via a connecting rod (806), and the pulley (805) is rollably arranged on the slide rail (804) to form a secondary rebound component (8); The auxiliary rebound component (8) is sleeved on the sleeve (402) to form a balancer.

10. The method for manufacturing a balancer according to claim 9, characterized in that: Design the abutment surface curve of the slide rail, including: The surface curve equation of the abutting surface of the slide rail (804) is obtained by using a calculation formula, wherein the calculation formula is: The coordinate system is established with the starting point of the curved surface of the slide rail (804) abutting the surface as the origin, the direction parallel to the pull rod as the x-axis, and the direction perpendicular to the pull rod as the y-axis, and θ is the angle between the tangent of the contact surface between the slide rail (804) and the pulley (805) and the x-axis. <h2 style=";text-align:left;direction:ltr">2N<h2 style=";text-align:left;direction:ltr"> x <h2 style=";text-align:left;direction:ltr"> +F1=F Among them, N x is the force on the point on the curved surface in the x direction generated by the elastic force F2 of the secondary spring (803), F1 is the elastic force of the main spring (404), and F is the resultant force generated by the balancer; If the resultant force F does not change within a certain stroke, that is, ΔF = 0, then 2ΔN x =ΔF1 2×ΔF2cosθ=ΔF1 This equation is a surface curve equation, wherein a is the pre-compression amount of the auxiliary spring (803), k1 is the elastic coefficient of the main spring (404), and k2 is the elastic coefficient of the auxiliary spring (803).

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