CN112727944A - Controlled disengagement type clutch under high rotating speed - Google Patents
Controlled disengagement type clutch under high rotating speed Download PDFInfo
- Publication number
- CN112727944A CN112727944A CN202011565145.8A CN202011565145A CN112727944A CN 112727944 A CN112727944 A CN 112727944A CN 202011565145 A CN202011565145 A CN 202011565145A CN 112727944 A CN112727944 A CN 112727944A
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- CN
- China
- Prior art keywords
- metal cylinder
- cylindrical roller
- roller bearing
- cylinder
- ball bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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- 239000002184 metal Substances 0.000 claims abstract description 83
- 238000003466 welding Methods 0.000 claims abstract description 7
- 238000009434 installation Methods 0.000 claims abstract description 3
- 238000000034 method Methods 0.000 claims description 6
- 235000017166 Bambusa arundinacea Nutrition 0.000 claims 1
- 235000017491 Bambusa tulda Nutrition 0.000 claims 1
- 241001330002 Bambuseae Species 0.000 claims 1
- 235000015334 Phyllostachys viridis Nutrition 0.000 claims 1
- 239000011425 bamboo Substances 0.000 claims 1
- 239000003921 oil Substances 0.000 description 9
- 238000013270 controlled release Methods 0.000 description 3
- 239000010727 cylinder oil Substances 0.000 description 2
- 239000002783 friction material Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/04—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube
- F16D25/042—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch
- F16D25/046—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch and causing purely radial movement
Abstract
The invention provides a controlled disengagement type clutch at high rotating speed, which comprises an input shaft sleeve, an expansion cylinder, an output shaft, a rotary seal and a bearing which are sequentially connected, wherein the expansion cylinder consists of an outer metal cylinder and an inner metal cylinder, the outer metal cylinder and the inner metal cylinder are equal in width and are concentrically arranged, a hollow annular groove is formed in the middle of the joint surface of the outer metal cylinder and the inner metal cylinder to form an expansion cylinder cavity, the two ends of the joint surface of the outer metal cylinder and the inner metal cylinder are welded together by adopting end surface welding seams, the inner metal cylinder of the expansion cylinder is fixedly connected with an installation shaft section of the output shaft, the expansion cylinder and the input shaft sleeve are concentrically arranged, and a disengagement gap exists between friction layers of the friction cylinders of the outer metal cylinder and the. The invention can instantly switch the clutch to a disengagement state according to the control instruction when the driving host runs at a high speed, avoids the driving host from being influenced by a failed load to stop, and improves the adaptability and the vitality of the driving host.
Description
Technical Field
The present invention relates to a clutch operable at high rotational speeds, and more particularly to a clutch capable of controlled rapid load disengagement at high rotational speeds.
Background
At present, known clutches such as synchronous automatic clutches, sleeve tooth clutches and other tooth clutches are very suitable for high-speed rotation, but under the working condition of high-speed torque transmission, as tooth surfaces of driving teeth and driven teeth are in a compact state, the friction force of the tooth surfaces enables sliding parts of the clutches not to move axially, and the clutches cannot be disengaged. The driving main machine adopts double-extension shafts, the two shaft extensions respectively drive two sets of loads, and when the driving main machine runs at a high speed and the failed loads need to be quickly disconnected, the function cannot be realized by adopting a tooth type clutch.
Disclosure of Invention
The invention aims to provide a controlled disengagement type clutch at a high rotating speed in order to meet the functional requirement of a double-extension-shaft main engine for quickly disconnecting a failed load.
The purpose of the invention is realized as follows: the expansion cylinder comprises an input shaft sleeve, an expansion cylinder, an output shaft, a rotary seal and a bearing which are sequentially connected, wherein the expansion cylinder consists of an outer metal cylinder and an inner metal cylinder, the outer metal cylinder and the inner metal cylinder are equal in width and are concentrically arranged, a hollow annular groove is formed in the middle of the joint surface of the outer metal cylinder and the inner metal cylinder to form an expansion cylinder cavity, the outer metal cylinder and the inner metal cylinder are welded together at two ends of the joint surface of the outer metal cylinder and the inner metal cylinder by adopting end face welding seams, the inner metal cylinder of the expansion cylinder is fixedly connected with an installation shaft section of the output shaft, the expansion cylinder and the input shaft sleeve are concentrically arranged, and a separation gap exists between friction.
The invention also includes such structural features:
1. the bearings comprise a 1# ball bearing, a 1# cylindrical roller bearing, a 2# cylindrical roller bearing, a 3# cylindrical roller bearing and a 2# ball bearing; the 1# ball bearing, the 1# cylindrical roller bearing, the 2# cylindrical roller bearing, the 3# cylindrical roller bearing and the 2# ball bearing are on the same axis; the input shaft sleeve is supported by a 1# ball bearing and a 1# cylindrical roller bearing, an input method column of the input shaft sleeve is connected with the driving host, and when the driving host works, the input shaft sleeve rotates at a high speed simultaneously with the driving host; the output shaft is supported through 2# cylindrical roller bearing, 3# cylindrical roller bearing, 2# ball bearing, and the output flange and the load of output shaft are connected.
2. The rotary seal is positioned between the 2# cylindrical roller bearing and the 3# cylindrical roller bearing, and the rotary seal and the outer surface of the shaft section of the output shaft form a rotary matching surface.
3. The release clearance is larger than the radial clearance of the 1# ball bearing and the 1# cylindrical roller bearing, and the release clearance is also larger than the different core quantities of the 1# ball bearing and the 2# cylindrical roller bearing.
Compared with the prior art, the invention has the beneficial effects that: the invention provides a controlled disengagement type clutch at high rotating speed, which solves the problem of fault load when a double-extension-shaft high-speed driving host is quickly disconnected, avoids the driving host from being stopped due to the influence of the fault load, and improves the adaptability and the vitality of the driving host
Drawings
FIG. 1 is a disengaged condition of the present invention;
FIG. 2 is a bonding state of the present invention;
fig. 3 is the invention in the process of disengagement.
In the figure, 200 is a controlled release clutch at high rotating speed, 20.1# ball bearing, 30.1# cylindrical roller bearing, 40.2# cylindrical roller bearing, 50.3# cylindrical roller bearing, 60 is a deep groove ball bearing, 300 is an input shaft sleeve, 310 is an input flange 320, an input shaft section 330, a connecting flange, 340 is a friction cylinder, 342 is a friction layer, 350 is a supporting flange, 360 is a release gap, 400 is an expansion cylinder, 405 is an inner metal cylinder, 410 is an outer metal cylinder, 420 is an end welding line, 430 is an end welding line, 440 is an expansion cylinder cavity, 450 is an inner metal cylinder oil inlet channel, 500 is an output shaft, 510 is an output shaft flange, 510 is an output shaft section, 520 is a clutch mounting shaft section, 530 is an output shaft oil channel, and 600 is a rotary seal.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
A controlled disengagement type clutch at high rotating speed is formed by sequentially connecting an input shaft sleeve, an expansion cylinder, an output shaft, a rotary seal, a bearing and the like, wherein the expansion cylinder consists of an outer metal cylinder and an inner metal cylinder, the outer metal cylinder and the inner metal cylinder have the same width and are concentrically arranged, and a hollow annular groove is formed in the middle of the combined surface of the outer metal cylinder and the inner metal cylinder to form an expansion cylinder cavity; two ends of the joint surface of the outer metal cylinder and the inner metal cylinder are welded together by adopting end surface welding seams; when the cavity of the expansion cylinder is communicated with a high-pressure medium, the end face weld joint cannot leak; an inner metal cylinder of the expansion cylinder is fixedly connected with the mounting shaft section of the output shaft, the expansion cylinder and the input shaft sleeve are concentrically arranged, and a disengagement gap is formed between the outer metal cylinder and a friction layer of the friction cylinder of the input shaft sleeve; when the output shaft and the input shaft sleeve are static or operate at a small rotating speed difference, the rotary seal provides a high-pressure medium for the cavity of the expansion cylinder through the oil passage of the output shaft and the oil inlet passage of the inner metal cylinder, the outer metal cylinder expands outwards and is contacted with the friction layer of the friction cylinder, when the input shaft sleeve is driven by the driving host to rotate at a high speed, the contact surface of the outer metal cylinder and the friction cylinder has a relative rotation trend, so that friction torque is generated, and the friction torque transmits the power of the driving host to the expansion cylinder through the input shaft sleeve so as to transmit the power to the output shaft and drive the load to rotate at; when the driving host rotates at a high speed, the rotary seal stops providing high-pressure media, the outer metal cylinder recovers elastically quickly, the media in the cavity of the expansion cylinder are extruded out, the disengagement gap recovers quickly, the clutch disengages, and the input shaft sleeve continues to rotate at a high speed under the driving of the driving host.
The bearings comprise a 1# ball bearing, a 1# cylindrical roller bearing, a 2# cylindrical roller bearing, a 3# cylindrical roller bearing and a 2# ball bearing; the 1# ball bearing, the 1# cylindrical roller bearing, the 2# cylindrical roller bearing, the 3# cylindrical roller bearing and the 2# ball bearing are on the same axis.
The input shaft sleeve is supported by a 1# ball bearing and a 1# cylindrical roller bearing, an input method column of the input shaft sleeve is connected with the driving host, and when the driving host works, the input shaft sleeve rotates at a high speed simultaneously with the driving host; the output shaft is supported through 2# cylindrical roller bearing, 3# cylindrical roller bearing, 2# ball bearing, and the output flange and the load of output shaft are connected.
The rotary seal is positioned between the 2# cylindrical roller bearing and the 3# cylindrical roller bearing, and the rotary seal and the outer surface of the output shaft section form a rotary matching surface, so that high-pressure media are not leaked or slightly leaked while the output shaft section rotates at a high speed.
The disengagement gap is larger than the radial gap between the 1# ball bearing and the 1# cylindrical roller bearing, the disengagement gap is also larger than different core amounts of the 1# ball bearing and the 2# cylindrical roller bearing, when the clutch is disengaged, the disengagement gap is always kept to be larger than 0, the outer metal cylinder is not contacted with the friction layer, the disengagement gap is filled with air, only small air friction resistance exists between the outer metal cylinder and the friction layer, and the input shaft sleeve can rotate at high speed for a long time under the driving of the driving host machine.
In fig. 1, the controlled release clutch 200 at a high rotational speed is composed of a # 1 ball bearing 20, a # 1 cylindrical roller bearing 30, a # 2 cylindrical roller bearing 40, a # 3 cylindrical roller bearing 50, a # 2 ball bearing 60, an input shaft sleeve 300, an expansion cylinder 400, an output shaft 500, and a rotary seal 600. The 1# ball bearing 20, the 1# cylindrical roller bearing 30, the 2# cylindrical roller bearing 40, the 3# cylindrical roller bearing 50 and the 2# ball bearing 60 are on the same axis.
The input shaft sleeve 300 is formed by sequentially connecting an input flange 310, an input shaft segment 320, a connecting flange 330, a friction cylinder 340 and a support flange 350. The outer ring of the 1# cylindrical roller bearing 30 is fixedly connected with the support flange 350, and the inner ring of the 1# cylindrical roller bearing 30 is fixedly connected with the output shaft section 510. The input shaft sleeve 300 is supported by the # 1 ball bearing 20 and the # 1 cylindrical roller bearing 30. The input method bar 310 is connected to the driving host, and the input shaft sleeve 300 rotates at a high speed simultaneously with the driving host when the driving host works.
The expansion cylinder 400 is composed of an outer metal cylinder 410 and an inner metal cylinder 405. The outer metal cylinder 410 and the inner metal cylinder 405 are equal in width and are concentrically arranged, and a hollow annular groove is formed in the middle of the combination surface of the outer metal cylinder and the inner metal cylinder to form an expansion cylinder cavity 440. The end face weld 420 and the end face weld 430 are arranged at two ends of the joint surface of the outer metal cylinder 410 and the inner metal cylinder 405, the two ends are welded together, and when the expansion cylinder cavity 440 is communicated with high-pressure media, the end face weld 420 and the end face weld 430 cannot leak. The inner metal sleeve 405 of the expansion cylinder 400 is fixedly connected to the clutch mounting shaft segment 520, the expansion cylinder 400 is arranged concentrically with the input shaft sleeve 300, and a disengagement gap 360 is provided between the outer metal sleeve 410 and the friction layer 342.
The output shaft 500 is formed by sequentially connecting an output shaft flange 510, an output shaft section 510, and a clutch mounting shaft section 520. The output shaft section 510 and the clutch mounting shaft section 520 are formed with an output shaft oil gallery 530. The output shaft oil passage 530 communicates with the rotary seal 600 and the inner barrel oil intake passage 450, respectively. The output shaft 500 is supported by the 2# cylindrical roller bearing 40, the 3# cylindrical roller bearing 50, and the 2# ball bearing 60, and the output flange 510 of the output shaft 500 is connected to a load.
The rotary seal 600 is positioned between the 2# cylindrical roller bearing 40 and the 3# cylindrical roller bearing 50, and the rotary seal 600 and the outer surface of the output shaft section 510 form a rotary matching surface, so that high-pressure media are not leaked or slightly leaked while the output shaft section 510 rotates at a high speed.
In fig. 2, when the output shaft 500 and the input shaft sleeve 300 are at rest or operate with a small difference in rotation speed, the rotary seal 600 provides a high-pressure medium to the expansion cylinder cavity 440 through the output shaft oil passage 530 and the inner metal cylinder oil inlet channel 450, the outer metal cylinder 410 expands outward and contacts with the friction layer 342 of the friction cylinder 340, when the input shaft sleeve 300 is driven by the driving host to rotate at a high speed, the contact surface between the outer metal cylinder 410 and the friction cylinder 340 has a relative rotation tendency, so that a friction torque is generated, and the friction torque transmits the power of the driving host from the input shaft sleeve 300 to the expansion cylinder 400 and further to the output shaft 500 and drives the load to rotate at a high speed.
In fig. 3, when the driving main machine rotates at a high speed, the rotary seal 600 stops providing the high-pressure medium, the outer metal cylinder 410 rapidly and elastically recovers to extrude the medium in the expanding cylinder cavity 440, the disengagement gap 360 rapidly recovers to the state in fig. 1, and the input shaft sleeve 300 continues to rotate at a high speed under the driving of the driving main machine.
The disengagement gap 360 is larger than the radial gaps of the # 1 ball bearing 20 and the # 1 cylindrical roller bearing 30. The disengagement gap 360 is also larger than the different amounts of the 1# ball bearing 20 and the 2# cylindrical roller bearing 40. Therefore, when the clutch is disengaged, the disengagement gap 360 is always maintained at a value greater than 0, and the outer metal cylinder 410 does not come into contact with the friction layer 342. After the controlled release clutch 200 is released at a high rotating speed, the release gap 360 is filled with air, the outer metal cylinder 410 and the friction layer 342 only have small air friction resistance, the input shaft sleeve 300 can be driven by the driving host to rotate at a high speed for a long time without the phenomena of friction collision, belt displacement and the like, and the adaptability and the vitality of the driving host are improved.
In summary, the present invention is a controlled disconnect clutch at high rotational speeds. 2 coaxially matched metal cylinders are identical in length, 2 end faces of the inner-layer metal cylinder and the outer-layer metal cylinder are welded into a whole by adopting a welding method, and the middle part of the joint surface of the outer-layer metal cylinder and the inner-layer metal cylinder is made into a cavity structure. The cavity in the middle of the joint surface is communicated with a high-pressure medium through an oil way, and the high-pressure medium makes the outer-layer metal cylinder contact with the inner wall of the input sleeve after expanding. The input sleeve is connected with an output shaft of the driving host, and the inner-layer metal cylinder is connected with a load. The inner wall of the input shaft sleeve is sintered with friction materials, and the outer layer metal cylinder is contacted with the input shaft sleeve to form a radial friction pair which can transmit the power of a driving host. After the high-pressure medium is released, the outer layer metal cylinder is elastically restored, and the original radial friction pair becomes an air gap. Because the volume of the cavity structure in the middle of the joint surface is very small and the elastic restoring force of the outer metal cylinder is very large, the high-pressure medium is quickly released, and the clutch is quickly disengaged. When the driving main engine and the load are static or operate at a small speed difference, the middle cavity of the joint surface is communicated with a high-pressure medium through the rotary seal and the oil way, and the high-pressure medium makes the outer-layer metal cylinder contact with the inner wall of the input sleeve after expanding. The input sleeve is connected with the driving host, and the inner-layer metal cylinder is connected with the load. The inner wall of the input shaft sleeve is sintered with friction materials, and the outer layer metal cylinder is contacted with the input shaft sleeve to form a radial friction pair which can transmit the power of a driving host. At high rotating speed, after the high-pressure medium is released, the elasticity of the outer-layer metal cylinder is recovered, and the original radial friction pair is changed into an air gap. Because the volume of the cavity structure in the middle of the joint surface is small, the elastic restoring force of the outer metal cylinder is large, the high-pressure medium is released quickly, the clutch is disengaged quickly, the driving host is prevented from being stopped due to the influence of fault load, and the adaptability and the vitality of the driving host are improved.
Claims (5)
1. The utility model provides a controlled disengagement type clutch under high rotational speed, includes input shaft sleeve, expansion section of thick bamboo, output shaft, rotary seal, the bearing of connecting gradually which characterized in that: the expansion cylinder is composed of an outer metal cylinder and an inner metal cylinder, the outer metal cylinder and the inner metal cylinder are equal in width and are arranged concentrically, a hollow annular groove is formed in the middle of the combination surface of the outer metal cylinder and the inner metal cylinder, the outer metal cylinder and the inner metal cylinder are welded together at two ends of the combination surface of the outer metal cylinder and the inner metal cylinder through end face welding, the inner metal cylinder of the expansion cylinder is fixedly connected with an installation shaft section of the output shaft, the expansion cylinder and the input shaft sleeve are arranged concentrically, and a disengagement gap exists between the outer metal cylinder and a friction layer of a friction cylinder of the input shaft sleeve.
2. A high speed controlled disconnect clutch as set forth in claim 1 wherein: the bearings comprise a 1# ball bearing, a 1# cylindrical roller bearing, a 2# cylindrical roller bearing, a 3# cylindrical roller bearing and a 2# ball bearing; the 1# ball bearing, the 1# cylindrical roller bearing, the 2# cylindrical roller bearing, the 3# cylindrical roller bearing and the 2# ball bearing are on the same axis; the input shaft sleeve is supported by a 1# ball bearing and a 1# cylindrical roller bearing, an input method column of the input shaft sleeve is connected with the driving host, and when the driving host works, the input shaft sleeve rotates at a high speed simultaneously with the driving host; the output shaft is supported through 2# cylindrical roller bearing, 3# cylindrical roller bearing, 2# ball bearing, and the output flange and the load of output shaft are connected.
3. A high speed controlled disconnect clutch as set forth in claim 2 wherein: the rotary seal is positioned between the 2# cylindrical roller bearing and the 3# cylindrical roller bearing, and the rotary seal and the outer surface of the shaft section of the output shaft form a rotary matching surface.
4. A high speed controlled disconnect clutch as set forth in claim 2 wherein: the release clearance is larger than the radial clearance of the 1# ball bearing and the 1# cylindrical roller bearing, and the release clearance is also larger than the different core quantities of the 1# ball bearing and the 2# cylindrical roller bearing.
5. A high speed controlled disconnect clutch as set forth in claim 3 wherein: the release clearance is larger than the radial clearance of the 1# ball bearing and the 1# cylindrical roller bearing, and the release clearance is also larger than the different core quantities of the 1# ball bearing and the 2# cylindrical roller bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011565145.8A CN112727944A (en) | 2020-12-25 | 2020-12-25 | Controlled disengagement type clutch under high rotating speed |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011565145.8A CN112727944A (en) | 2020-12-25 | 2020-12-25 | Controlled disengagement type clutch under high rotating speed |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112727944A true CN112727944A (en) | 2021-04-30 |
Family
ID=75616356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011565145.8A Pending CN112727944A (en) | 2020-12-25 | 2020-12-25 | Controlled disengagement type clutch under high rotating speed |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112727944A (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB347329A (en) * | 1930-02-04 | 1931-04-30 | Arthur John Fippard | Improvements in or relating to clutch mechanism |
| GB698389A (en) * | 1951-03-23 | 1953-10-14 | Gen Tire & Rubber Co | Expanded clutch or brake |
| GB938538A (en) * | 1962-07-24 | 1963-10-02 | Fawick Corp | Fluid-actuated clutch or brake |
| DE3311225A1 (en) * | 1983-03-28 | 1984-10-04 | Wabco Westinghouse Steuerungstechnik GmbH & Co, 3000 Hannover | Clutch or brake for two components which can be rotated relative to one another |
| FR2594919A3 (en) * | 1986-02-27 | 1987-08-28 | Fritschi Ag Hugo | Clutch actuated by compressed air for accumulation conveyor |
| WO2009096517A1 (en) * | 2008-01-31 | 2009-08-06 | Jtekt Corporation | Torque limiter |
| CN203756799U (en) * | 2013-03-13 | 2014-08-06 | 伊顿公司 | Improved drum and contractile drum type brake assembly |
| CN203926496U (en) * | 2014-06-19 | 2014-11-05 | 东营人造板厂 | Loader dress plate clutch |
| CN206054594U (en) * | 2015-06-15 | 2017-03-29 | 伊顿公司 | Improved contracting type drum brake component and improved drum |
-
2020
- 2020-12-25 CN CN202011565145.8A patent/CN112727944A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB347329A (en) * | 1930-02-04 | 1931-04-30 | Arthur John Fippard | Improvements in or relating to clutch mechanism |
| GB698389A (en) * | 1951-03-23 | 1953-10-14 | Gen Tire & Rubber Co | Expanded clutch or brake |
| GB938538A (en) * | 1962-07-24 | 1963-10-02 | Fawick Corp | Fluid-actuated clutch or brake |
| DE3311225A1 (en) * | 1983-03-28 | 1984-10-04 | Wabco Westinghouse Steuerungstechnik GmbH & Co, 3000 Hannover | Clutch or brake for two components which can be rotated relative to one another |
| FR2594919A3 (en) * | 1986-02-27 | 1987-08-28 | Fritschi Ag Hugo | Clutch actuated by compressed air for accumulation conveyor |
| WO2009096517A1 (en) * | 2008-01-31 | 2009-08-06 | Jtekt Corporation | Torque limiter |
| CN203756799U (en) * | 2013-03-13 | 2014-08-06 | 伊顿公司 | Improved drum and contractile drum type brake assembly |
| CN203926496U (en) * | 2014-06-19 | 2014-11-05 | 东营人造板厂 | Loader dress plate clutch |
| CN206054594U (en) * | 2015-06-15 | 2017-03-29 | 伊顿公司 | Improved contracting type drum brake component and improved drum |
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| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
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| RJ01 | Rejection of invention patent application after publication | ||
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Application publication date: 20210430 |