CN107387691B - Asymmetric damping structure tensioning wheel bearing unit - Google Patents
Asymmetric damping structure tensioning wheel bearing unit Download PDFInfo
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- CN107387691B CN107387691B CN201710579345.0A CN201710579345A CN107387691B CN 107387691 B CN107387691 B CN 107387691B CN 201710579345 A CN201710579345 A CN 201710579345A CN 107387691 B CN107387691 B CN 107387691B
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- Prior art keywords
- spring
- spring seat
- axial
- mandrel
- bearing unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
- F16H7/0831—Means for varying tension of belts, ropes, or chains with vibration damping means of the dry friction type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Abstract
The invention discloses an asymmetric damping structure tensioning wheel bearing unit which comprises a mandrel, a sleeve arranged on the mandrel and a bearing arranged on the sleeve, wherein a spring damping mechanism is further arranged on the mandrel, the spring damping mechanism comprises a first spring seat, a second spring seat and a rectangular spring which are combined together, the rectangular spring is fixed with the first spring seat and is in clearance fit with the second spring seat, a limiting groove which extends partially along the circumferential direction is formed in the first axial side of the sleeve, a limiting boss which is inserted into the limiting groove is arranged at the second axial end of the second spring seat, and the circumferential length of the limiting groove is larger than that of the limiting boss. The invention reduces the vibration of the belt in the running process, prolongs the service life of the bearing and the belt, and reduces the noise of the automobile in the speed change process.
Description
Technical Field
The invention relates to automobile parts, in particular to a tensioning wheel.
Background
The existing tensioning wheel has higher technical requirements for installers, if the positions of the tensioning wheel are not installed correctly, two problems of squeaking and belt vibration of the tensioning wheel occur in the working process, the belt running on the tensioning wheel possibly excites vibration in a tensioning spring, the tensioning wheel and the belt can be worn out too early, and the service lives of products and the belt are affected.
Disclosure of Invention
The technical problem to be solved by the invention is to provide the asymmetric damping structure tensioning wheel bearing unit, so that the damping structure can rotate clockwise in the working process, and only the reserved position can be rotated in the opposite direction, and the tensioning wheel can be gradually and automatically adjusted to the optimal position.
In order to solve the technical problems, the invention adopts the following technical scheme: the utility model provides an asymmetric damping structure take-up pulley bearing unit, the dabber is still installed spring damping mechanism, spring damping mechanism is including first spring holder, second spring holder and the rectangle spring that makes up together, the rectangle spring is fixed with first spring holder, rectangle spring and second spring holder are clearance fit, the sleeve is equipped with the spacing groove that extends along circumference local, the axial second end of second spring holder is equipped with the spacing boss of inserting spacing groove, the circumference length of spacing groove is greater than the circumference length of spacing boss, the dabber is equipped with the jump ring of the first spring holder axial first end of restriction, the end cover of carrying out axial spacing to spring damping mechanism is installed to the axial first end of dabber, the axial second end of dabber is equipped with the location flange that outwards circle protrusion in order to carry out axial spacing to spring damping mechanism.
Preferably, a plurality of hooks are uniformly distributed at the axial second end of the first spring seat along the circumferential direction, and a clamping protrusion is arranged at the inner hole of the second spring seat at the axial first end along the circumferential direction and is clamped into the hooks.
Preferably, the two circumferential sides of the clamping hook are provided with inner convex ribs protruding to the inner side in the radial direction.
Preferably, the inner hole of the first spring seat is provided with a limiting convex ring, and the mandrel is provided with a limiting step which is matched with the limiting convex ring to limit the first spring seat to move towards the second axial end.
Preferably, a bending head is arranged at the first end of the rectangular spring, a positioning hole is formed in the first spring seat, and the bending head penetrates into the positioning hole.
Preferably, a spring sheath is sleeved on the radial outer side of the rectangular spring, a positioning groove is formed in the first axial side of the spring sheath, and a positioning protrusion penetrating into the positioning groove is arranged at the first axial end of the first spring seat.
Preferably, the first spring seat is provided with a ring groove for placing the snap spring.
Preferably, the inner hole of the snap spring is in interference fit with the mandrel, bending sections which are outwards opened are arranged at the two ends of the opening of the snap spring,
preferably, the first spring seat is provided with a clamp spring groove for enabling the bending section to be clamped and enter.
Preferably, the inner hole of the end cover is provided with a bending part bending towards the second axial side, and the bending part is tightly matched with the outer diameter of the mandrel.
Preferably, the first spring seat is formed by injection molding of PA66 material, and the second spring seat is formed by injection molding of PA66+GF 30.
According to the invention, a set of damping mechanism is added in the automatic tensioning wheel, and the rectangular spring is fixed with the first spring seat, so that the first spring seat can rotate together with the rectangular spring, and the rectangular spring is in clearance fit with the second spring seat, so that the automatic tensioning wheel can freely rotate during working.
Because the cooperation of spacing boss and spacing groove is equipped with between second spring holder and the sleeve, damping structure can rotate clockwise, and the opposite direction is because the circumference length of spacing groove is greater than the circumference length of spacing boss, in the course of the work, damping structure can rotate clockwise, and opposite direction can only rotate the reservation position, gradually automatic with take-up pulley adjustment to the optimal position.
The beneficial effects of the invention are as follows: the belt tensioner bearing structure has the advantages of ensuring small friction damping during acceleration, reducing vibration of the belt during operation, prolonging service lives of the bearing and the belt, reducing noise of an automobile during speed change, being reasonable in structure, convenient to process, reliable in product performance and the like, and meeting requirements of the belt tensioner bearing of an automobile engine.
Drawings
The invention is further described with reference to the drawings and detailed description which follow:
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a schematic cross-sectional view of a first spring seat;
FIG. 3 is an axial schematic view of a second spring seat;
FIG. 4 is a schematic cross-sectional view of a second spring seat;
FIG. 5 is a schematic radial view of a second spring seat;
FIG. 6 is a schematic view of a rectangular spring;
FIG. 7 is a schematic structural view of a mandrel;
FIG. 8 is a schematic structural view of a snap spring;
fig. 9 is a schematic structural view of a spring sheath.
Detailed Description
An asymmetric damping structure tensioner bearing unit as shown in fig. 1 to 9 comprises a mandrel 4, a sleeve 7 mounted on the mandrel, a bearing 8 mounted on the sleeve 7, and a tensioner spring 72. Meanwhile, a set of spring damping mechanism is added in the tensioning wheel, and the spring damping mechanism comprises: the automatic tensioning wheel comprises a first spring seat 1, a second spring seat 2 and a rectangular spring 3, wherein the first spring seat 1, the second spring seat 2 and the rectangular spring 3 are combined together and mounted on a mandrel 4, the rectangular spring 3 is fixed with the first spring seat 1, the first spring seat 1 and the rectangular spring 3 rotate together, the rectangular spring 3 and the second spring seat 2 are in clearance fit, and free rotation of the automatic tensioning wheel during operation is guaranteed. The first side of telescopic axial is equipped with the spacing groove 71 that extends along circumference part, the axial second end of second spring holder is equipped with the spacing boss 23 of inserting the spacing groove, the circumference length of spacing groove 71 is greater than the circumference length of spacing boss 23, and spacing boss 23 is spacing rotatory in spacing groove 71, in the course of the work, because the spacing groove 71 is to the blocking effect of spacing boss 23, spring damping structure opposite direction can only rotate the reservation position. In the present embodiment, as shown in fig. 3, the limit boss 23 extends by 90 ° in the circumferential direction for limiting rotation. The mandrel 4 is provided with a clamp spring 5 for limiting the first end of the first spring seat, an inner hole of the clamp spring is in interference fit with the mandrel 4, and the clamp spring is reliably fixed and reliably positioned to the first spring seat 1.
Further, a spring sheath 6 is sleeved on the radial outer side of the rectangular spring, and the spring sheath 6 is formed by injection molding of PA66 material. As shown in fig. 9, the spring sheath is provided with a detent 61 on an axial first side. As shown in fig. 2, the first end of the first spring seat in the axial direction is provided with a positioning protrusion 15 penetrating into the positioning groove 61. After the first spring seat 1, the second spring seat 2 and the rectangular spring 3 are assembled, the positioning protrusion 15 is assembled with the positioning groove 61, so that the spring damping structure is protected.
Because the cooperation of limit boss 23 and spacing groove 71 is equipped with between second spring holder 2 and the sleeve 7, the damping structure can rotate clockwise, and the opposite direction is because the circumference length of spacing groove is greater than the circumference length of limit boss, can only rotate the reservation position, gradually automatic adjust the take-up pulley to the best position, reaches damping structure asymmetric damping characteristic. The belt tensioner bearing structure has the advantages of ensuring small friction damping during acceleration, reducing vibration of the belt during operation, prolonging service lives of the bearing and the belt, reducing noise of an automobile during speed change, being reasonable in structure, convenient to process, reliable in product performance and the like, and meeting requirements of the belt tensioner bearing of an automobile engine.
As shown in fig. 2 to 5, the axial second end of the first spring seat is uniformly provided with a plurality of hooks 11 along the circumferential direction, the inner hole of the second spring seat is provided with a clamping protrusion 21 along the circumferential direction at the axial first end, and the clamping protrusion 21 is clamped into the hooks 11, so that the first spring seat 1 and the second spring seat 2 are assembled together through a simple clamping structure, and the disassembly is convenient. In addition, the two sides of the periphery of the hook are provided with inner convex ribs 111 protruding to the inner side in the radial direction, so as to enhance the structural strength of the hook 11.
The first axial end of first spring holder is equipped with first fender step 16 along circumference, and the axial second end of second spring holder is equipped with second fender step 22 along circumference, and after first spring holder 1 and the equipment of second spring holder 2, first fender step 16 and second fender step 22 cooperate and carry out spacingly to rectangular spring 3's both ends face, prevent rectangular spring 3 axial float. As shown in fig. 6, a bending head 31 is disposed at a first end of the rectangular spring, a positioning hole 13 that is axially penetrated is disposed at the first gear step 16 of the first spring seat, and the bending head 31 penetrates into the positioning hole 13 to fix the rectangular spring 3 and the fixed first spring seat 1 together. The second end of the rectangular spring is free from bending, and the inner circle of the rectangular spring is in clearance fit with the outer diameter of the second spring seat 2.
In order to limit the axial movement of the first spring seat 1, a limiting convex ring 14 is arranged in an inner hole of the first spring seat, and as shown in fig. 7, a limiting step 41 which is matched with the limiting convex ring 14 to limit the movement of the first spring seat 1 to the axial second end is arranged on the mandrel 4 so as to limit the axial second end of the first spring seat. The axial second end of the mandrel 4 is provided with a positioning flange 42 protruding towards the outer circle, and the first end of the spring damping mechanism is axially limited. Simultaneously, end cover 9 is installed to the axial first end of dabber, and the end cover hole is equipped with the portion of bending 91 of bending to axial second side, and the portion of bending 91 and dabber external diameter close-fitting installation is spacing to the axial first end of first spring holder through end cover 9, also carries out the axial spacing to the axial first end of spring damper simultaneously.
As shown in fig. 2, the inner hole of the first spring seat 1 is provided with a ring groove 12 for placing a snap spring. As shown in fig. 8, two ends of the opening of the snap spring are provided with bending sections 51 which are outwards opened, and the first spring seat is provided with a snap spring groove into which the bending sections are clamped. The inner diameter of the clamp spring is in interference fit with the mandrel, and the opening of the bending section 51 is the same as the angle of the clamp spring groove on the first spring seat, so that the clamp spring is convenient to assemble.
In terms of material selection, the mandrel 4 is formed by adopting powder metallurgy material through die casting, the first spring seat 1 is formed by adopting PA66 material through injection molding, the second spring seat 2 is formed by adopting PA66+GF30 mixed injection molding, the rectangular spring 3 is made of 65Mn rectangular section material, and the section size of the material is 1.5mmX1.3mm and needs to be designed in a left-hand manner. The snap spring is made of 65Mn material, and the structure of the raw material is rectangular in section, and the size is 3.2mm and 3.2mm. Through reasonable selection of materials, the balance of reducing cost and meeting the use requirement is achieved.
In addition to the above preferred embodiments, the present invention has other embodiments, and various changes and modifications may be made by those skilled in the art without departing from the spirit of the invention, which shall fall within the scope of the invention as defined in the appended claims.
Claims (9)
1. The utility model provides an asymmetric damping structure take-up pulley bearing unit, includes dabber, installs in the epaxial sleeve of dabber and installs the bearing on the sleeve, its characterized in that: the spring damping mechanism is further installed on the mandrel, the spring damping mechanism comprises a first spring seat, a second spring seat and a rectangular spring which are combined together, the rectangular spring is fixed with the first spring seat, the rectangular spring is in clearance fit with the second spring seat, the sleeve is provided with a limiting groove which locally extends along the circumferential direction, the axial second end of the second spring seat is provided with a limiting boss which is inserted into the limiting groove, the circumferential length of the limiting groove is greater than that of the limiting boss, the mandrel is provided with a clamping spring which limits the axial first end of the first spring seat, the axial first end of the mandrel is provided with an end cover which axially limits the spring damping mechanism, the axial second end of the mandrel is provided with a positioning flange which protrudes towards the outer circle to axially limit the spring damping mechanism, the inner hole of the end cover is provided with a bending part which is bent towards the axial second side, and the bending part is installed in close fit with the outer diameter of the mandrel.
2. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the axial second end of first spring holder has a plurality of pothook along circumference equipartition, the hole of second spring holder is equipped with the card protruding along the hoop at axial first end, the card protruding card goes into the pothook.
3. An asymmetric damping structure tensioner bearing unit in accordance with claim 2, wherein: the two sides of the periphery of the clamping hook are provided with inner convex ribs protruding towards the inner side in the radial direction.
4. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the inner hole of the first spring seat is provided with a limiting convex ring, and the mandrel is provided with a limiting step which is matched with the limiting convex ring to limit the first spring seat to move towards the axial second end.
5. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the first end of the rectangular spring is provided with a bending head, the first spring seat is provided with a positioning hole, and the bending head penetrates into the positioning hole.
6. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the radial outside cover of rectangle spring is equipped with the spring sheath, the axial first side of spring sheath is equipped with the constant head tank, the axial first end of first spring holder is equipped with the location arch that penetrates the constant head tank.
7. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the first spring seat is provided with an annular groove for placing the clamp spring.
8. An asymmetric damping structure tensioner bearing unit in accordance with claim 7, wherein: the inner hole of the clamp spring is in interference fit with the mandrel, bending sections which are outwards opened are arranged at the two ends of the opening of the clamp spring,
the first spring seat is provided with a clamp spring groove for enabling the bending section to enter in a clamping mode.
9. An asymmetric damping structure tensioner bearing unit in accordance with claim 1, wherein: the first spring seat is formed by injection molding of PA66 material, and the second spring seat is formed by injection molding of PA66+GF 30.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710579345.0A CN107387691B (en) | 2017-07-17 | 2017-07-17 | Asymmetric damping structure tensioning wheel bearing unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710579345.0A CN107387691B (en) | 2017-07-17 | 2017-07-17 | Asymmetric damping structure tensioning wheel bearing unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107387691A CN107387691A (en) | 2017-11-24 |
| CN107387691B true CN107387691B (en) | 2023-06-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710579345.0A Active CN107387691B (en) | 2017-07-17 | 2017-07-17 | Asymmetric damping structure tensioning wheel bearing unit |
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| CN (1) | CN107387691B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116770258A (en) * | 2021-07-29 | 2023-09-19 | 苏州道一至诚纳米材料技术有限公司 | Double-sided reciprocating film plating device |
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| CN201614950U (en) * | 2009-12-18 | 2010-10-27 | 奇瑞汽车股份有限公司 | Tensioner for timing belt of engine |
| CN202301795U (en) * | 2011-07-20 | 2012-07-04 | 杭州雷迪克汽车部件制造有限公司 | Split type automatic tension pulley bearing of automobile engine |
| WO2014198086A1 (en) * | 2013-06-13 | 2014-12-18 | Li Zhimin | Unidirectionally coupled damping pulley |
| CN104358846A (en) * | 2014-10-20 | 2015-02-18 | 杭州诚信汽车轴承有限公司 | Drum-type asymmetric damping automatic belt tensioner |
| CN105508529A (en) * | 2015-12-31 | 2016-04-20 | 温州博立汽车科技有限公司 | Asymmetric high-damping belt tensioning pulley |
| CN205278261U (en) * | 2015-12-31 | 2016-06-01 | 温州博立汽车科技有限公司 | Asymmetric high damping belt tensioner |
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| US8192312B2 (en) * | 2008-01-31 | 2012-06-05 | The Gates Corporation | Isolator with damping |
| CN201575116U (en) * | 2009-10-29 | 2010-09-08 | 上海振华轴承总厂 | Variable-stiffness automatic belt tensioner |
| CN202360693U (en) * | 2011-12-13 | 2012-08-01 | 东风汽车有限公司 | Damping-changing structure of tension wheel |
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| WO2015035508A1 (en) * | 2013-09-11 | 2015-03-19 | Litens Automotive Partnership | Tensioner with increased damping and arm on base cup configuration |
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| CN204533402U (en) * | 2015-04-20 | 2015-08-05 | 宁波裕江特种胶带有限公司 | A kind of tensioner |
| DE102015111809A1 (en) * | 2015-07-21 | 2017-01-26 | Muhr Und Bender Kg | jig |
| CN206943348U (en) * | 2017-07-17 | 2018-01-30 | 杭州雷迪克节能科技股份有限公司 | A kind of automatic tensioner with spring damping mechanism |
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2017
- 2017-07-17 CN CN201710579345.0A patent/CN107387691B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4473362A (en) * | 1981-07-08 | 1984-09-25 | Litens Automotive Inc. | Belt tensioner with variably proportional damping |
| US4473362B1 (en) * | 1981-07-08 | 1991-07-09 | Litens Automotive Inc | |
| CN201614950U (en) * | 2009-12-18 | 2010-10-27 | 奇瑞汽车股份有限公司 | Tensioner for timing belt of engine |
| CN202301795U (en) * | 2011-07-20 | 2012-07-04 | 杭州雷迪克汽车部件制造有限公司 | Split type automatic tension pulley bearing of automobile engine |
| WO2014198086A1 (en) * | 2013-06-13 | 2014-12-18 | Li Zhimin | Unidirectionally coupled damping pulley |
| CN104358846A (en) * | 2014-10-20 | 2015-02-18 | 杭州诚信汽车轴承有限公司 | Drum-type asymmetric damping automatic belt tensioner |
| CN105508529A (en) * | 2015-12-31 | 2016-04-20 | 温州博立汽车科技有限公司 | Asymmetric high-damping belt tensioning pulley |
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| Publication number | Publication date |
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| CN107387691A (en) | 2017-11-24 |
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