CN216009415U

CN216009415U - Asymmetric damping tensioner

Info

Publication number: CN216009415U
Application number: CN202121810826.6U
Authority: CN
Inventors: 阮恩昌; 王会
Original assignee: Litens Automotive Suzhou Co ltd
Current assignee: Litens Automotive Suzhou Co ltd
Priority date: 2021-08-04
Filing date: 2021-08-04
Publication date: 2022-03-11
Anticipated expiration: 2031-08-04

Abstract

The present application relates to an asymmetric damping tensioner comprising: base, tensioning arm, spring, damping piece and support ring, wherein: the damping piece comprises a first damping ring and a second damping ring, the first damping ring is sleeved on the outer side of the second damping ring, the first side face of the first damping ring is attached to the inner side face of the base, the second side face of the first damping ring is in meshing contact with the first side face of the second damping ring, the meshing contact face comprises a first contact face and a second contact face, the first contact face is parallel to the radial direction of the first damping ring or the second damping ring and is a plane, the included angle between the tangent of any point on the second contact face and the first contact face is theta, and 0< theta <90 deg. The first damping ring and the second damping ring are meshed, so that the second contact surface in the loading direction is inclined to the rotating direction, the first contact surface in the unloading direction is perpendicular to the rotating direction, the slip rate of the belt can be effectively controlled, the damping range is large, and the swing amplitude of the tensioning arm can be reduced.

Description

Asymmetric damping tensioner

Technical Field

The present invention relates to tensioners, and more particularly to an asymmetric damping tensioner.

Background

The tensioner is a commonly used holding device on a belt and chain transmission system and is characterized in that the belt and the chain can be kept to have proper tension in the transmission process, so that the belt is prevented from slipping, or the synchronous belt is prevented from being dragged out due to tooth skipping and tooth stripping. Or the chain is prevented from loosening and falling off, and the abrasion of the chain wheel and the chain is reduced. Belt tensioners typically have a mechanism that dampens and causes movement of the tensioner arm due to fluctuations in belt tension. The desired amount of damping depends on many driving factors including geometry, accessory load, accessory inertia, engine duty cycle, and others. The damping of the tensioner is required to change along with the dynamic load change of an engine, and the too high damping can cause the slow response speed of the tensioner, so that the slip rate of a train belt is increased, the abrasion loss of the belt is increased, and the durability is poor. If the damping of the tensioner is too small, the amplitude of oscillation of the tensioner arm increases, and the vibration of the gear train cannot be effectively suppressed.

The common symmetrical damping tensioner requires large belt tension to overcome the problem of belt slip in order to keep working efficiency in the dynamic working process of an engine gear train, the swing amplitude of a tensioning arm is large, so that the requirement on the quality of a belt is high, the energy consumption of an engine accessory system can be increased, other damping devices are required to be matched to avoid the resonance problem under most conditions, and the overall design cost of the gear train is high. And the damping of the common tensioner can only be changed within a small range, and the system performance requirement of the engine under different working conditions can not be met. Therefore, it is highly desirable to design a tensioner that has superior performance and low cost.

Disclosure of Invention

The problem that current damping tensioning ware can't satisfy system performance requirement under the different operating modes has mainly been solved in this application.

In order to solve the technical problem, the application provides the following technical scheme:

the present application provides an asymmetric damping tensioner comprising: the device comprises a base, a first connecting piece and a second connecting piece, wherein an accommodating space is arranged in the base, a first opening is formed in the first end of the base, a first through hole is formed in the second end of the base, and the accommodating space is communicated with the first through hole and the first opening; the pivot penetrates through the first through hole, the accommodating space and the first opening in sequence; a tensioning arm having a first end sleeved over a first end of the pivot shaft and rotating about the pivot shaft; the spring is arranged in the accommodating space and sleeved on the pivot, a first end face of the spring is tightly attached to the first end part of the base, and a second end face of the spring is tightly attached to the first end part of the tensioning arm; the damping part is arranged in the accommodating space of the base and comprises a first damping ring and a second damping ring, the first damping ring is sleeved on the outer side of the second damping ring, a first side surface of the first damping ring is attached to the inner side surface of the base, a second side surface of the first damping ring is in meshing contact with a first side surface of the second damping ring, the meshing contact surface comprises a first contact surface and a second contact surface, the first contact surface is parallel to the radial direction of the first damping ring or the second damping ring and is a plane, the included angle between the tangent of any point on the second contact surface and the first contact surface is theta, and the included angle is 0< theta <90 degrees; a support ring sleeved outside the spring and having a first side surface contacting an outer side surface of the spring.

As a further improvement of the present application, the second side surface of the first damping ring is in meshing contact with the first side surface of the second damping ring in a manner that a meshing groove is formed on the second side surface of the first damping ring, and a matching portion attached to the meshing groove is formed on the first side surface of the second damping ring, or a meshing groove is formed on the first side surface of the second damping ring, and a matching portion attached to the meshing groove is formed on the second side surface of the first damping ring.

As a further improvement of the present application, the number of the engaging grooves is at least 1, and the fitting portions fitted to the engaging grooves correspond to the engaging grooves one to one.

As a further improvement of the present application, a plurality of convex or concave lattice point microstructures are disposed on the second contact surface, and/or a plurality of convex or concave strip structures are disposed on the second contact surface.

As a further improvement of the application, a fixing part is further arranged in the accommodating space of the base, the fixing part and the inner side surface of the base fix the spring together, and the shape of the fixing part is matched with that of the spring.

As a further improvement of the present application, the holding portion is formed extending from the bottom of the base adjacent to the edge side of the first through hole toward the inside of the accommodating space in the direction of the pivot.

As a further improvement of the present application, the holding portion may be one or more.

As a further improvement of the present application, a bushing is further provided between the holding portion and the pivot.

As a further improvement of the application, the bottom of the pivot is also provided with a shaft seat.

As a further improvement of the present application, a pulley is also provided, the pulley being disposed on a second end opposite the first end of the tensioner arm, the pulley being in close proximity to the engine belt.

The beneficial effect of this application lies in that an asymmetric damping tensioning ware is provided, includes: base, tensioning arm, spring, damping piece and support ring, wherein: the damping piece includes first damping ring and second damping ring, first damping ring overlaps to be established the outside of second damping ring, and the first side laminating of first damping ring is in on the medial surface of base, the second side of first damping ring and the first side meshing contact of second damping ring, meshing contact surface include first contact surface and second contact surface, and first contact surface is on a parallel with the radial direction of first damping ring or second damping ring, and the contained angle between second contact surface and the first contact surface is theta, and 0< theta <90 °. The meshing structure between the first damping ring and the second damping ring is designed, so that the second contact surface in the loading direction is inclined to the rotating direction, and the first contact surface in the unloading direction is perpendicular to the rotating direction; therefore, the slack side and the tight side of the belt are kept with non-zero tension, the slip rate of the belt can be effectively controlled, and the swing amplitude of the tensioning arm can be reduced due to the large damping range of the belt.

Drawings

FIG. 1 is a schematic diagram of an asymmetric damping tensioner;

FIG. 2 is a schematic structural diagram of a base;

FIG. 3 is a schematic view of the structure of the damping member and the support ring;

FIG. 4 is a schematic view of the connection of the tensioning arm and spring;

FIG. 5 is a schematic view of a clamping structure of the second damping ring and the support ring;

FIG. 6 is a schematic structural view of a support ring;

FIG. 7 is a schematic structural view of a second damping ring;

in the figure: 1. a base; 2. a pivot; 3. a tensioning arm; 4. a spring; 5. a first damping ring; 6. a second damping ring; 7. a support ring; 8. a belt pulley; 11. a first through hole; 12. an accommodating space; 13. a first opening; 14. a holding part; 15. a first retaining part; 16. a first blocking portion; 21. a shaft sleeve; 22. a shaft seat; 31. a first end of a tensioning arm; 32. a second end of the tensioning arm; 33. a second chucking part; 51. a first contact surface; 52. a second contact surface; 81. a bearing; 82. a dust cover; 83. a bolt; 61. a first inner clamping block; 62. a second inner clamping block; 63. a fourth positioning bayonet; 71. a first positioning bayonet; 72. a second positioning bayonet; 73. and a third positioning bayonet.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the technical solutions of the present application will be described in detail and completely with reference to the following specific embodiments of the present application and the accompanying drawings. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

As shown in fig. 1 and 2, the asymmetric damping tensioner of the present embodiment comprises: base 1, pivot 2, tensioning arm 3, spring 4, damping piece, support ring 7. Be equipped with an accommodation space 12 in the base 1, the bottom of base 1 is equipped with first through-hole 11, first through-hole 11 is located the bottom of accommodation space 12 and link up with accommodation space 12, is equipped with first opening 13 at the top of base 1, and first opening 13 is located the top of accommodation space 12 and link up with accommodation space 12, and pivot 2 runs through first through-hole 11, accommodation space 12 and first opening 13 in proper order, and is preferred, and pivot 2 can be cylinder or the well convex type cylinder.

The first end 31 of the tensioning arm is arranged at the first opening 13 of the base 1 and is sleeved on the first end of the pivot shaft 2 and rotates around the pivot shaft 2, the first end 31 of the tensioning arm is provided with a turning hole, the first end 31 of the tensioning arm is sleeved on the pivot shaft 2 through the turning hole, preferably, a bushing is arranged between the pivot shaft 2 and the turning hole of the first end 31 of the tensioning arm, the shape of the bushing is matched with that of the first end of the pivot shaft 2, the bushing can be a cylindrical ring member or a conical ring member, the inner hole of the bushing is in clearance fit with the pivot shaft 2, the turning hole of the first end 31 of the tensioning arm is in interference fit with the bushing, so that the bushing is tightly attached into the turning hole of the first end 31 of the tensioning arm, and when the first end 31 of the tensioning arm rotates around the pivot shaft 2, the bushing rotates around the pivot shaft 2 along with the first end 31 of the tensioning arm, reducing the friction between the first end 31 of the tensioning arm and the pivot shaft 2; the inner bore of the bushing may be provided with a wear resistant coating to further reduce friction between the first end 31 of the tensioning arm and the pivot shaft 2.

As shown in fig. 1, a spring 4 is disposed in the accommodating space 12 of the base 1, the spring 4 is sleeved on the pivot 2, a first end of the spring 4 is in close contact with the bottom of the base 1, a second end of the spring 4 is in close contact with a first end 31 of the tensioning arm, when the first end 31 of the tensioning arm makes a rotation movement, the first end 31 of the tensioning arm applies a pressure to the second end of the spring 4, and the bottom of the base 1, under the action of the pressure of the spring 4, applies a reverse acting force to the second end of the spring 4, so that the spring 4 is compressed as a whole, thereby providing a force for tensioning the belt of the engine. Preferably, the spring 4 may be a helical torsion spring 4 without a bent leg at both ends. In some preferred embodiments, as shown in fig. 2, the base 1 is provided with a first holding portion 15 at the bottom, the side of the first holding portion 15 is closely attached to the cross section of the spring wire at the first end of the spring 4, as shown in fig. 4, the first end 31 of the tensioning arm is provided with a second holding portion 33, and the side of the second holding portion 33 is closely attached to the cross section of the spring wire at the second end of the spring 4.

As shown in fig. 1 and 3, the damping member is disposed in the accommodating space 12 of the base 1, the damping member includes a first damping ring 5 and a second damping ring 6, the first damping ring 5 is sleeved outside the second damping ring 6, a first side surface of the first damping ring 5 is attached to an inner side surface of the base 1, a second side surface of the first damping ring 5 is in meshing contact with a first side surface of the second damping ring 6, the meshing contact surface includes a first contact surface 51 and a second contact surface 52, the first contact surface 51 is parallel to a radial direction of the first damping ring 5 or the second damping ring 6 and is a plane, an included angle θ is formed between a tangent of any point on the second contact surface 52 and the first contact surface 51, and 0< θ <90 °. In a specific embodiment, the second side surface of the first damping ring 5 and the first side surface of the second damping ring 6 are in meshing contact with each other in such a manner that a meshing groove is formed on the second side surface of the first damping ring 5, a matching portion attached to the meshing groove is formed on the first side surface of the second damping ring 6, or a meshing groove is formed on the first side surface of the second damping ring 6, and a matching portion attached to the meshing groove is formed on the second side surface of the first damping ring 5. The support ring 7 is sleeved outside the spring 4, the second side face of the support ring 7 is attached to the outer side surface of the spring 4, the first side face of the support ring 7 is attached to the second side face of the second damping ring 6, and the support ring 7 is used for fixing the second damping ring 6 and providing rigidity for the second damping ring 6.

In a specific embodiment, during the loading process of the tensioner, the support ring 7 and the second damping ring 6 are used as driving parts, the driven part, the first damping ring 5, is driven to rotate by engaging the contact surfaces, the rotation direction during the loading process is close to the second contact surface 52, and the rotation resultant force generates a radial component force to act on the second damping ring 6, so that the contact positive pressure between the second damping ring 6 and the base 1 is increased, and the effect of increasing the damping during the loading process of the tensioner is achieved. In the unloading process of the tensioner, the support ring 7 and the second damping ring 6 are still active components, the rotation direction is close to the second contact surface 52 in the unloading process, and because the second contact surface 52 is perpendicular to the rotation direction, the first damping ring 5 is directly pushed by the second contact surface 52 without generating radial force components.

In a specific embodiment, the second side surface of the first damping ring 5 and the first side surface of the second damping ring 6 are in meshing contact with each other in such a manner that a meshing groove is formed on the second side surface of the first damping ring 5, a matching portion attached to the meshing groove is formed on the first side surface of the second damping ring 6, or a meshing groove is formed on the first side surface of the second damping ring 6, and a matching portion attached to the meshing groove is formed on the second side surface of the first damping ring 5. Preferably, the number of the engaging grooves is at least 1, and the matching parts attached to the engaging grooves correspond to the engaging grooves one to one. In some preferred embodiments, a plurality of convex or concave dot microstructures and/or convex or concave stripe structures may be further disposed on the second contact surface 52. The lattice point microstructure can be, but not limited to, a pyramid structure, a frustum structure or an arc structure, and the arc structure is any one of a partial spherical surface, an ellipsoid or an elliptic paraboloid; the strip-shaped structure is one or more of prism strips, cylindrical strips or trapezoidal strips. The above structural design can increase the damping of the damping member, and the second contact surface 52 is individually designed by using the above mesh point microstructure and/or the strip-shaped structure according to the requirements of system performance under different working conditions.

In some embodiments, as shown in fig. 2, a holding portion 14 is further disposed in the accommodating space 12 of the base 1, the holding portion 14 fixes the spring 4 together with the inner side surface of the base 1, and the shape of the holding portion 14 matches the shape of the spring 4. Preferably, the holding portion 14 is formed to extend from the bottom of the base 1 adjacent to the edge side of the first through hole 11 into the accommodating space 12 along the direction of the pivot 2, and the holding portion 14 may be one or more. Preferably, the holding portion 14 is integrally formed with the base 1. In some preferred embodiments, as shown in fig. 1, a shaft seat 22 is further provided at a second end of the pivot shaft 2 opposite to the first end of the pivot shaft 2, and the cross-sectional area of the shaft seat 22 is larger than that of the second end of the pivot shaft 2; preferably, the shaft seat 22 is embedded in the bottom of the base 1, and the bottom of the base 1 is provided with a groove for embedding the shaft seat 22, so that the structural design is beneficial to axially limiting the pivot shaft 2 and is beneficial to connecting the pivot shaft 2 and the base 1 together. Preferably, the axle seat 22 is integrally formed with the pivot axle 2.

In some preferred embodiments, as shown in fig. 1, a bushing 21 is further disposed between the holding portion 14 and the pivot shaft 2, and the bushing 21 is in interference fit with the pivot shaft 2. The sleeve 21 is shaped to match the pivot 2, such as: when the pivot 2 is a cylinder, the shaft sleeve 21 is a ring-shaped element matched with the cylinder; when the pivot 2 is a medium-convex cylinder, the sleeve 21 is an annular member that mates with the medium-convex cylinder.

The asymmetric damping tensioner of the embodiment of the present application, as shown in fig. 1, further comprises a pulley 8, wherein the pulley 8 is disposed on a second end 32 of the tensioner arm opposite to the first end 31 of the tensioner arm, and the pulley 8 is tightly attached to the engine belt. Pulley 8 is mounted on the opposite second end of tensioner arm first end 31 by means of bearing 81, dust cap 82, bolt 83, bearing 81 being a rolling bearing 81.

As shown in fig. 5 to 7, a first positioning bayonet 71 is arranged at a first end of the support ring 7, a first inner fixture block 61 matched with the first positioning bayonet 71 is arranged on a first side surface of the second damping ring 6, and the first inner fixture block 61 is clamped in the first positioning bayonet 71; the second end of the support ring 7 is provided with a second positioning bayonet 72, the first side surface of the second damping ring 6 is provided with a second inner clamping block 62 matched with the second positioning bayonet 72, and the second inner clamping block 62 is clamped in the second positioning bayonet 72. The above structure fixes the second damping ring 6 and the support ring 7 to each other. The first end portion of the support ring 7 is further provided with a third positioning bayonet 73, the second damping ring 6 is provided with a fourth positioning bayonet 63, the first end portion 31 of the tensioning arm is provided with a third positioning fixture block, and the third positioning fixture block is simultaneously clamped in the third positioning bayonet 73 and the fourth positioning bayonet 63. This design allows for better positioning of the support ring 7 and the second damping ring 6. A first stop 16 is also arranged on the inner side of the base 1, and the first stop 16 and the first end 31 of the tensioning arm together limit the first damping ring 5 and the second damping ring 6.

In a specific embodiment, when the spring 4 is twisted to enlarge the outer diameter so as to expand the support ring, the radial pressing force of the support ring expands the second damping ring 6 outwards, the support ring 7, the second damping ring 6 and the third damping ring jointly generate a rotating resultant force F1, the rotating resultant force F1 generates a radial component force F2 on the second contact surface 52 of the engaging groove to act on the second damping ring 6, and the contact positive pressure between the second damping ring 6 and the inner side surface of the base 1 is increased so as to achieve the effect of increasing the damping during the loading process of the tensioner. Preferably, the second damping ring 6 may have the shape of a half ring, which is designed to facilitate the bracing of the support ring 7.

In a specific embodiment, when an automobile engine accelerates, a belt is instantaneously stretched, the tensioning arm 3 performs a rotary motion of pressing the belt of the engine under the action of the spring 4, the outer diameter of the spring 4 contracts, the positive pressure of the second damping ring 6 and the inner side surface of the base 1 is reduced, the rotary resultant force of the damping piece and the inner side surface of the base 1 is greatly reduced, the damping is reduced, the tensioning arm 3 drives the belt pulley 8 to quickly press the belt, the purpose of instantaneously tensioning the belt is achieved, and the belt is effectively prevented from shaking.

In a specific embodiment, when the automobile engine is decelerated, the engine belt is instantly rebounded to be shortened, the tensioning arm 3 pushes the tensioning arm 3 to do reverse rotation motion due to the reaction force of the engine belt, the spring 4 is twisted to increase the outer diameter and expand the support ring, the radial extrusion force of the support ring expands the second damping ring 6 outwards so as to generate high friction damping between the damping member and the inner side surface of the base 1, the friction damping is instantly increased, and the tensioning arm 3 is prevented from violently shaking due to the reaction force of the belt, so that the normal operation of the automobile engine belt pulley 8 system is ensured. After the first damping ring 5 and/or the second damping ring 6 are operated for a long time, abrasion is generated due to the existence of friction force, when the tensioner assembly is assembled, the first damping ring 5 and/or the second damping ring 6 are/is elastically pre-tensioned, so that real-time compensation can be provided when the friction rings are abraded, and the damping performance of the tensioner is enhanced and constant.

In summary, the present application provides an asymmetric damping tensioner comprising: base 1, tensioning arm 3, spring 4, damping piece and support ring 7, wherein: the damping piece includes first damping ring 5 and second damping ring 6, first damping ring 5 cover is established the outside of second damping ring 6, and the first side laminating of first damping ring 5 is in on the medial surface of base 1, the first side meshing contact of the second side of first damping ring 5 and second damping ring 6, meshing contact surface include first contact surface 51 and second contact surface 52, and first contact surface 51 is on a parallel with the radial direction of first damping ring 5 or second damping ring 6, and the contained angle between second contact surface 52 and the first contact surface 51 is theta, and 0< theta <90 °. The engagement structure between the first damping ring 5 and the second damping ring 6 is designed such that the second contact surface 52 in the loading direction is inclined to the rotation direction and the first contact surface 51 in the unloading direction is perpendicular to the rotation direction; therefore, the loose edge and the tight edge of the belt keep non-zero tension, and the common symmetrical damping tensioner only can keep the non-zero tension on one side of the belt and has better performance than the common symmetrical damping tensioner.

In addition, the double-damper structure can replace an original annular plastic support. The double-damper type asymmetric tensioner can reduce the swing amplitude of the tensioning arm 3 on the premise of reducing the tension of a system belt, reduces the belt slip rate, does not need other damping equipment to be matched for use, and accordingly achieves the purposes of reducing the dynamic resonance of the system and low-cost development and application of a small platform.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various changes and modifications can be made without departing from the inventive concept of the present invention, and these changes and modifications are all within the scope of the present invention.

Claims

1. An asymmetric damping tensioner, comprising:

the device comprises a base, a first connecting piece and a second connecting piece, wherein an accommodating space is arranged in the base, a first opening is formed in the first end of the base, a first through hole is formed in the second end of the base, and the accommodating space is communicated with the first through hole and the first opening;

the pivot penetrates through the first through hole, the accommodating space and the first opening in sequence;

a tensioning arm having a first end sleeved over a first end of the pivot shaft and rotating about the pivot shaft;

the spring is arranged in the accommodating space and sleeved on the pivot, a first end face of the spring is tightly attached to the first end part of the base, and a second end face of the spring is tightly attached to the first end part of the tensioning arm;

the damping part is arranged in the accommodating space of the base and comprises a first damping ring and a second damping ring, the first damping ring is sleeved on the outer side of the second damping ring, a first side surface of the first damping ring is attached to the inner side surface of the base, a second side surface of the first damping ring is in meshing contact with a first side surface of the second damping ring, the meshing contact surface comprises a first contact surface and a second contact surface, the first contact surface is parallel to the radial direction of the first damping ring or the second damping ring and is a plane, the included angle between the tangent of any point on the second contact surface and the first contact surface is theta, and the included angle is 0< theta <90 degrees;

a support ring sleeved outside the spring and having a first side surface contacting an outer side surface of the spring.

2. The asymmetric damping tensioner as claimed in claim 1, wherein the second side surface of the first damping ring is in meshing contact with the first side surface of the second damping ring in a manner that the second side surface of the first damping ring is provided with an engaging groove and the first side surface of the second damping ring is provided with an engaging portion engaging with the engaging groove, or the first side surface of the second damping ring is provided with an engaging groove and the second side surface of the first damping ring is provided with an engaging portion engaging with the engaging groove.

3. The asymmetric damping tensioner as claimed in claim 2, wherein the number of said engagement grooves is at least 1, and the fitting portions fitted to said engagement grooves correspond one-to-one to said engagement grooves.

4. The asymmetric damping tensioner as claimed in claim 1, wherein a plurality of convex or concave lattice point microstructures are provided on said second contact surface, and/or a plurality of convex or concave strip structures are provided on said second contact surface.

5. The asymmetric damping tensioner as claimed in claim 1, further comprising a retaining portion disposed in the receiving space of the base, the retaining portion and the inner side surface of the base jointly fixing the spring, the retaining portion having a shape matching the shape of the spring.

6. The asymmetric damping tensioner as claimed in claim 5, wherein the retaining portion is formed extending from the bottom of the base adjacent to the edge side of the first through hole toward the inside of the receiving space in the direction of the pivot.

7. The asymmetric damping tensioner as claimed in claim 6, wherein said retaining portion may be one or more.

8. The asymmetric damping tensioner as in claim 6, further comprising a bushing between said retaining portion and said pivot shaft.

9. The asymmetric damping tensioner as claimed in claim 1, wherein the bottom of said pivot shaft is further provided with an axle seat.

10. The asymmetric damping tensioner as in claim 1, further comprising a pulley disposed on a second end of said tensioner arm opposite said first end, said pulley being in close proximity to an engine belt.