CN102840249A - Clutch and engineering machinery - Google Patents
Clutch and engineering machinery Download PDFInfo
- Publication number
- CN102840249A CN102840249A CN2012103356413A CN201210335641A CN102840249A CN 102840249 A CN102840249 A CN 102840249A CN 2012103356413 A CN2012103356413 A CN 2012103356413A CN 201210335641 A CN201210335641 A CN 201210335641A CN 102840249 A CN102840249 A CN 102840249A
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- China
- Prior art keywords
- plunger
- clutch
- oil duct
- plunger cavity
- disc
- 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.)
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/061—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having interengaging clutch members
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
- F16D11/16—Clutches in which the members have interengaging parts with clutching members movable otherwise than only axially
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
Abstract
The invention discloses a clutch and engineering machinery. The clutch comprises a driving disc, a driven disc, an output shaft and a hydraulic control mechanism, wherein the driving disk is coaxially linked with an input shaft and is provided with a plunger chamber; a plunger is arranged in the plunger chamber and is hermetically fit with the inner wall of the plunger chamber; the driven disk is arranged outside the driving disc in a sleeving manner and is provided with a plunger groove which is opposite to the plunger chamber; the output shaft is coaxially linked with the driven disk; and the hydraulic control mechanism is used for supplying oil to the plunger chamber. According to the clutch, the plunger on the driving disc directly acts on the driven disc to implement the transmission of power, and the hydraulic control mechanism controls the linkage relationship between the plunger and the driven disc, so that the power input and switch off functions of the clutch can be realized. The clutch has the advantages of smooth power combination, and small abrasion between the plunger and a cylinder.
Description
Technical field
The present invention relates to engineering machinery field, particularly a kind of clutch and engineering machinery.
Background technique
Clutch is arranged on a kind of device that is used to transmit or cut off engine power between motor and the gearbox.Clutch is the vitals of automobile dynamic system, and it is being undertaken and is cutting off and the work that is connected between power and the motor.
At present, the employed engaging and disengaging gear of mechanical field power transmission process is lamella clutch mostly.Lamella clutch of a great variety; But its basic functional principle is roughly the same, is specially: during linkage status, active force does not promote withdrawal fork; Release bearing is pushed in intermediate portion to diaphragm spring; The intermediate portion of diaphragm spring is pushed into, and near one group of pin the spring outside makes spring that platen is drawn back from clutch disk, and clutch separates from the motor that is rotating thus.During linkage status, spring can promote platen to the clutch disk direction, thereby the extruding flywheel can lock motor on the transmission input shaft thus, makes them with identical speed rotation.The defective of this kind clutch mainly is: the smoothness that power combines during gearshift is not good, and clutch plate is easy to wear, and working life is shorter.
Summary of the invention
In view of this, the present invention proposes a kind of clutch and engineering machinery, and is not good with the smoothness that solves existing clutch power combination, the problem that clutch plate is easy to wear.
The present invention provides a kind of clutch, and it comprises: with the driving disc of the coaxial interlock of input shaft; Said driving disc is provided with plunger cavity, is provided with plunger in the said plunger cavity; The airtight applying of the inwall of said plunger and said plunger cavity; Be sheathed on the outside driven disc of said driving disc, said driven disc is provided with plunger slot, and said plunger slot and said plunger cavity are oppositely arranged; Output shaft with the coaxial interlock of said driven disc; Hydraulic control is used for fuel feeding in said plunger cavity.
Further, said hydraulic control comprises: fuel tank; With the control valve that said fuel tank communicates, said control valve communicates with said plunger cavity; One-way valve, its filler opening communicates with said fuel tank, and oil outlet communicates with said plunger cavity.
Further, said hydraulic control also comprises: relief valve, and its filler opening communicates with said plunger cavity, and oil outlet communicates with said fuel tank.
Further, said control valve is the solenoid-operated proportional control valve.
Further, said clutch also comprises the elastic element that is used to support said plunger, and said elastic element is arranged in the said plunger cavity, and its outer end is arranged with said plunger.
Further, the number of said plunger cavity is a plurality of, and circumferentially evenly being provided with along said driving disc; The number of the plunger slot of said driven disc is a plurality of, and the inner circumference of the said driven disc in edge is to even setting.
Further, rounding off between adjacent said plunger slot.
Further, said clutch also comprises the shell that is installed on said driven disc outside, and said shell comprises: be arranged at the protecgulum of said input shaft one side and the housing that removably connects with said protecgulum.
Further, said input shaft is provided with the input bearing; Said protecgulum is provided with the input bearing groove, and said input bearing is installed in the said input bearing groove.
Further, said hydraulic control is installed on the outside of said protecgulum, and is covered with first oil duct that communicates with said control valve and said one-way valve before said, and the 3rd oil duct that communicates with said first oil duct and said plunger cavity is set in the said driving disc.
Further, said clutch also comprises the seal ring that is arranged between said protecgulum and the said driving disc, and said seal ring is provided with second oil duct, and the two ends of said second oil duct communicate with said first oil duct and said the 3rd oil duct respectively.
The present invention also provides a kind of engineering machinery, is provided with above-mentioned any described clutch.
The present invention provides a kind of clutch, and it utilizes plunger and driven disc on the driving disc directly to be used as the mode of transmission of power, and passes through the interaction relation of hydraulic control control plunger and driven disc, realizes the power input of clutch and the function of cutting off.With respect to existing technology, the present invention has following advantage:
When power combined, the hydraulic oil in the plunger cavity increased gradually, and the oil pressure in the plunger cavity raises gradually, and plunger also is to be locked in gradually in the plunger slot, and it is big that the moment of torsion that driven disc receives also becomes thereupon gradually, so power combines comparatively smooth-going.
Only plunger and driven disc just have relative movement when power combines, and gearshift finishes back-plunger and driven disc rotates with speed, and the two no relative movement effectively reduces the wearing and tearing of plunger and cylinder body, improves the reliability of clutch, has prolonged the working life of clutch.
Further, if hydraulic control is if also be provided with relief valve, when clutch output terminal load was excessive, relief valve also can play overload protective function to motor.
The embodiment of the invention also provides a kind of engineering machinery, and this project machinery is provided with above-mentioned any clutch, because above-mentioned any clutch has above-mentioned technique effect, therefore, the engineering machinery that is provided with this clutch also should possess the corresponding techniques effect.
Description of drawings
The accompanying drawing that constitutes a part of the present invention is used to provide further understanding of the present invention, and illustrative examples of the present invention and explanation thereof are used to explain the present invention, does not constitute improper qualification of the present invention.In the accompanying drawings:
The schematic representation of the clutch that Fig. 1 provides for the embodiment of the invention 1;
Fig. 2 is the explosive view of clutch shown in Figure 1;
Fig. 3 is the structural representation of driving disc;
Fig. 4 is the structural representation of driven disc.
Description of reference numerals:
1 control valve, 2 relief valves
3 one-way valves, 4 fuel tanks
5 protecgulums, 6 input shafts
7 input bearings, 8 seal rings
9 plungers 112 the 3rd oil duct
10 springs, 11 driving discs
111 plunger cavities, 12 driven discs
121 plunger slot, 13 output shafts
14 output bearings, 15 housings
Embodiment
Need to prove that under the situation of not conflicting, embodiment and the characteristic among the embodiment among the present invention can make up each other.
Basic thought of the present invention is: utilize plunger and driven disc on the driving disc directly to be used as the mode of transmission of power, and pass through the interaction relation of hydraulic control control plunger and driven disc, realize the power input of clutch and the function of cutting off.
Below in conjunction with accompanying drawing, each preferred embodiment of the present invention is described further.
Fig. 1 shows the structure of the clutch that the embodiment of the invention 1 provides, and the concrete structure of this clutch sees also Fig. 2, and this clutch comprises:
Input shaft 6, it is arranged with input bearing 7;
Driving disc 11, itself and input shaft 6 coaxial interlocks; It is provided with plunger cavity 111, is provided with spring 10 in the plunger cavity 111, and the outer end of spring 10 is arranged with plunger 9, the airtight applying of inwall of this plunger 9 and plunger cavity 111; Be provided with the 3rd oil duct 112 that communicates with plunger cavity 111 in the driving disc 11;
Be installed on the outside shell of driven disc 12, this shell comprises: be arranged at the protecgulum 5 of input shaft 6 one sides, the housing 15 that removably connects with this protecgulum 5; Protecgulum 5 is provided with first oil duct that communicates with above-mentioned the 3rd oil duct 112;
Hydraulic control, it is used for fuel feeding in plunger cavity 111; Hydraulic control is installed on the outside of protecgulum 5, specifically comprises: control valve 1, one-way valve 3 and fuel tank 4; Wherein, control valve 1 communicates with fuel tank 4, control valve 1 communicate with first oil duct (promptly identical with plunger cavity 111); The filler opening of one-way valve 3 communicates with fuel tank 4, oil outlet communicate with first oil duct (promptly identical with plunger cavity 111).
The working principle of the clutch that present embodiment provides is following:
Engine drives input shaft 6 and driving disc 11 rotate, and place the plunger 9 in driving disc 11 plunger cavities 111 also to rotate thereupon.Plunger 9 along radially moving reciprocatingly of driving disc 11, or has reciprocating trend under spring 10 and driven disc 12 actings in conjunction.
When control valve 1 is opened; First oil duct, the 3rd oil duct 112 that hydraulic oil in the fuel tank 4 can pass through under the effect of hydraulic difference on control valve 1, the protecgulum 5 successively get in the plunger cavity 111, and part hydraulic oil also can pass through in one-way valve 3, first oil duct, the 3rd oil duct 112 entering plunger cavities 111; Can be full of hydraulic oil gradually in the plunger cavity 111; Simultaneously hydraulic oil can also flow back to fuel tank 4 through the 3rd oil duct 112, first oil duct and control valve 1; Hydraulic oil constantly was inhaled into and discharged plunger cavity 111 this moment; Plunger 9 unrestricted motions still along radially the moving reciprocatingly of driving disc 11, or have reciprocating trend.This moment, plunger 9 was in the state of unlocking, and driven disc 12 remains static, and clutch is linkage status not.
When control valve 1 is closed; Hydraulic oil in the fuel tank 4 can't get into or discharge plunger cavity 111 through control valve 1, and the hydraulic oil in the fuel tank 4 flows in the plunger cavity 111 through one-way valve 3, first oil duct and the 3rd oil duct 112 under the effect of hydraulic difference, because the hydraulic oil in the plunger cavity 111 can't flow back to fuel tank 4 from control valve 1 and one-way valve 3; Therefore the hydraulic oil in the plunger cavity 111 increases gradually; Hydraulic oil 111 promotes plunger 9 to plunger cavity 111 external movement, and plunger 9 is locked in the plunger slot 121, and this moment, plunger 9 was in the lock state; Plunger 9 promotes driven disc 12 and output shaft rotates with speed, and clutch is a linkage status.
When control valve 1 is opened according to a certain percentage; Hydraulic oil in 1 pair of driving disc of control valve, 11 plunger cavities 111 plays throttling action; A certain amount of hydraulic oil can flow back to fuel tank 4 through control valve 1; This moment, plunger 9 was in half lock state, and output shaft 15 has a constant speed poor with input shaft 6, and clutch is the semi-linkage state.
In the above-mentioned clutch, input shaft 6 links to each other with motor, and the power intake that it is equivalent to clutch is used to drive driving disc 11 and rotates; Output shaft 13 can link to each other with gearbox, is equivalent to the clutch end of clutch, and it is driven by driven disc 15 and rotates.Under the effect of hydraulic control,, realize that interlock rotation, the semi-linkage of output shaft 13 rotated and do not rotated through the interaction relation of control driving disc 11 and driven disc 12.
The driving disc 11 of the clutch that present embodiment provides is provided with plunger cavity 111, is used to be provided with spring 11 and plunger 9, and plunger 9 is sheathed on the outer end of spring 10, and outer end described herein is an end that deviates from plunger cavity 111 bottoms.Driven disc 12 is sheathed on the outside of driving disc 11, and driven disc 12 is that plunger cavity 111 corresponding positions are provided with plunger slot 121.The shape of plunger slot 121 is preferably suitable with the top shape of plunger 9.In the clutch that present embodiment provides, plunger 9 is realized interlock, the semi-linkage of driving disc 11 and driven disc 12 with cooperating of plunger slot 121 and is not linked.The effect of spring 10 is: plunger 9 is played a supporting role; Under the effect that does not have hydraulic coupling (providing) by hydraulic control; The support force deficiency that it provides so that plunger 9 be locked in the plunger slot 121; And under the effect that hydraulic coupling is arranged with the hydraulic oil acting in conjunction, for plunger 9 provides enough support forces it can be locked in the plunger slot 121.It will be understood by those skilled in the art that this spring 10 also can be substituted by other elastic element, can function as described above equally.Plunger 9 is airtight applyings with the inwall of plunger cavity 111, guarantees that thus the hydraulic oil of being sent into by hydraulic control can not leak.In the present embodiment, the bottom of plunger 9 is provided with support slot, and the outer end of spring 10 is arranged in this support slot, can alleviate plunger 9 weight on the one hand thus, also more oil storage space can be provided on the other hand.Certainly plunger 9 also can not established support slot, directly compresses with spring 10 to contact.
In order to improve power transmission efficiency, the number of plunger cavity 111 is preferably a plurality of (seeing Fig. 3 for details), along circumferentially evenly being provided with of driving disc 11.Accordingly, the number of driven disc 12 (seeing Fig. 4 for details) upper plug groove 121 also should be a plurality of, also along the inner circumference of driven disc 12 to even setting.In the clutch working procedure, plunger 9 contacts the most frequent with the interior circle of driven disc 12, for fear of plunger 9 and driven disc 12 transition frictions, rounding off between the adjacent plunger slot 121 of driven disc 12.In order to reduce friction, the end face of plunger 9 is preferably arc surface equally.In addition, plunger 9 and the also preferred high-abrasive material that adopts of driven disc 12.
Shell in the clutch is installed on the outside of driven disc 12, is used for driving disc 11 and driven disc 12 members such as grade are played a protective role, and avoids introduced contaminants to get into the proper functioning of the above-mentioned member of influence.What this shell was concrete is made up of protecgulum 5 and housing 15, and the two can removably connect through fastening pieces such as screws.This protecgulum 5 can be arranged at a side that is provided with input shaft 6 in the both sides (being the both sides of driving disc 11) of driven disc 12.This protecgulum 5 is provided with first oil duct, and this first oil duct communicates with the 3rd oil duct 112 of driving disc 11.Thus, this first oil duct and the 3rd oil duct 112 have constituted the oil-feed drainback passage of hydraulic oil.
Part input shaft 6 is installed in the protecgulum 5, in order to reduce the friction between protecgulum 5 and the input shaft 6, preferably is provided with input bearing 7 on this input shaft 6, and protecgulum 5 is provided with the input bearing groove, and input bearing 7 is installed in this input bearing groove.Similarly, in order to reduce the film material between housing 15 and the output shaft 13, preferably be provided with output bearing 14 on this output shaft 13, housing is provided with the output bearing groove, and output bearing 14 is installed in the output bearing groove.
Hydraulic oil in the hydraulic control gets into plunger cavity 111 through first oil duct on the protecgulum 5 and the 3rd oil duct 112; In order to prevent that hydraulic oil from leaking; Also preferably be provided with seal ring 8 between protecgulum 5 and the driving disc 11; Sealing ring 8 is provided with second oil duct, and the two ends of second oil duct communicate with first oil duct and the 3rd oil duct 112 respectively.Thus, first oil duct, second oil duct and the 3rd oil duct 112 have constituted the oil-feed drainback passage of hydraulic oil jointly.Accordingly, when control valve 1 was opened, the hydraulic oil in the fuel tank 4 can pass through control valve 1, first oil duct, second oil duct and the 3rd oil duct 112 successively and get into and discharge in the plunger cavity 111; When control valve 1 was closed, the hydraulic oil in the fuel tank 4 got in the plunger cavity 111 through one-way valve 3, first oil duct, second oil duct and the 3rd oil duct 112 successively.Above-mentioned seal ring 8 preferably is sheathed on input bearing 7 outsides, and then the structure that makes this clutch reach is more compact.In addition, in order to improve the transfer rate of fluid, and then improve the speed of response of clutch, the individual number average of above-mentioned first oil duct, second oil duct and the 3rd oil duct 112 is preferably a plurality of.
In the clutch that present embodiment provides; Hydraulic control is used to plunger cavity 111 fuel feeding; The hydraulic oil that infeeds can provide its thrust along plunger cavity 111 external movement for plunger 9, realizes i.e. half lock state of the lock state of plunger 9 in plunger slot 121 thus.Control valve 1 is not only as the fuel feeding switch of fuel tank 4, also as the oil return switch of hydraulic oil in the plunger cavity 111.For the ease of the unlatching of control control valve 1, close and ratio is opened, improve control accuracy, above-mentioned control valve 1 is preferably the solenoid-operated proportional control valve.
Further, this hydraulic control also preferably includes relief valve 2, and the filler opening of this relief valve 2 communicates with first oil duct (being indirect communicating with plunger cavity 111), and oil outlet communicates with fuel tank 4, and it can play the effect of overload protection to motor.Particularly, when output terminal overloads suddenly, when driven disc 12 stops operating; Oil pressure in the plunger cavity 111 of driving disc 11 raises suddenly, and this moment, relief valve 2 was opened, and hydraulic oil flows back to fuel tank 4 through relief valve 2; Power obtains discharging with the mode of overflow thus, realizes the protective action to motor.
In sum; The clutch that the embodiment of the invention provides is the direct transfer mode that is used as power through plunger and driven disc; And through hydraulic control realize plunger locking, partly lock and unlock, realize interlock, the semi-linkage of clutch thus and do not link.
Have the following advantages:
When 1, power combines (when control valve is closed), the hydraulic oil in the plunger cavity increases gradually, and the oil pressure in the plunger cavity raises gradually, and plunger also is to be locked in gradually in the plunger slot, and it is big that the moment of torsion that driven disc receives also becomes thereupon, so power combines comparatively smooth-going.
2, only when power combines plunger and driven disc relative movement is just arranged, gearshift finishes back-plunger rotates with speed with driven disc, the two no relative movement effectively reduces the wearing and tearing of plunger and cylinder body, the reliability of raising clutch has prolonged working life of clutch.
When 3, power combined, the point of action of plunger radially distance was bigger, but transfer larger torque.
When 4, control valve was closed fully, flow was 0 in the clutch, and power loss is little, and transmission efficiency is high.
5, hydraulic control is if also be provided with relief valve, and when clutch output terminal load was excessive, relief valve also can play overload protective function to motor.
The embodiment of the invention also provides a kind of engineering machinery; For example road roller, milling machine, hoist etc., this project machinery is provided with above-mentioned any clutch, because above-mentioned any clutch has above-mentioned technique effect; Therefore; The engineering machinery that is provided with this clutch also should possess the corresponding techniques effect, and its practical implementation process is similar to the above embodiments, does not give unnecessary details now.
The above is merely preferred embodiment of the present invention, and is in order to restriction the present invention, not all within spirit of the present invention and principle, any modification of being done, is equal to replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (12)
1. a clutch is characterized in that, comprising:
Driving disc (11) with the coaxial interlock of input shaft (6);
Said driving disc (11) is provided with plunger cavity (111), is provided with plunger (9) in the said plunger cavity (111); The airtight applying of inwall of said plunger (9) and said plunger cavity (111);
Be sheathed on the outside driven disc (12) of said driving disc (11), said driven disc (12) is provided with plunger slot (121), and said plunger slot (121) is oppositely arranged with said plunger cavity (111);
Output shaft (13) with the coaxial interlock of said driven disc (12);
Hydraulic control is used for fuel feeding in said plunger cavity (111).
2. clutch according to claim 1 is characterized in that, said hydraulic control comprises:
Fuel tank (4);
The control valve (1) that communicates with said fuel tank (4), said control valve (1) communicates with said plunger cavity (111);
One-way valve (3), its filler opening communicates with said fuel tank (4), and oil outlet communicates with said plunger cavity (111).
3. clutch according to claim 2 is characterized in that, said hydraulic control also comprises:
Relief valve (2), its filler opening communicates with said plunger cavity (111), and oil outlet communicates with said fuel tank (4).
4. clutch according to claim 2 is characterized in that, said control valve (1) is the solenoid-operated proportional control valve.
5. according to any described clutch of claim 1 to 4; It is characterized in that; Said clutch also comprises the elastic element that is used to support said plunger (9), and said elastic element is arranged in the said plunger cavity (111), and its outer end is arranged with said plunger (9).
6. according to any described clutch of claim 1 to 4, it is characterized in that the number of said plunger cavity (111) is a plurality of, and circumferentially evenly being provided with along said driving disc (11); The number of the plunger slot (121) of said driven disc (12) is a plurality of, and the inner circumference of the said driven disc in edge (12) is to even setting.
7. clutch according to claim 6 is characterized in that, rounding off between adjacent said plunger slot (121).
8. according to any described clutch of claim 2 to 4; It is characterized in that; Said clutch also comprises the shell that is installed on said driven disc (12) outside; Said shell comprises: be arranged at the protecgulum (5) of said input shaft (6) one sides and the housing (15) that removably connects with said protecgulum (5).
9. 8 described clutches as requested is characterized in that, said input shaft (6) is provided with input bearing (7); Said protecgulum (5) is provided with the input bearing groove, and said input bearing (7) is installed in the said input bearing groove.
10. clutch according to claim 9; It is characterized in that; Said hydraulic control is installed on the outside of said protecgulum (5); And said protecgulum (5) is provided with first oil duct that communicates with said control valve (1) and said one-way valve (3), and the 3rd oil duct (112) that communicates with said first oil duct and said plunger cavity (111) is set in the said driving disc (11).
11. clutch according to claim 9; It is characterized in that; Said clutch also comprises the seal ring (8) that is arranged between said protecgulum (5) and the said driving disc (11); Said seal ring (8) is provided with second oil duct, and the two ends of said second oil duct communicate with said first oil duct and said the 3rd oil duct (112) respectively.
12. an engineering machinery is characterized in that, is provided with any described clutch of claim 1 to 11.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210335641.3A CN102840249B (en) | 2012-09-12 | 2012-09-12 | Clutch and engineering machinery |
| PCT/CN2012/086026 WO2014040351A1 (en) | 2012-09-12 | 2012-12-06 | Clutch and engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210335641.3A CN102840249B (en) | 2012-09-12 | 2012-09-12 | Clutch and engineering machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102840249A true CN102840249A (en) | 2012-12-26 |
| CN102840249B CN102840249B (en) | 2015-01-14 |
Family
ID=47367898
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210335641.3A Expired - Fee Related CN102840249B (en) | 2012-09-12 | 2012-09-12 | Clutch and engineering machinery |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102840249B (en) |
| WO (1) | WO2014040351A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107327514A (en) * | 2017-08-24 | 2017-11-07 | 安徽江淮汽车集团股份有限公司 | A kind of new type auto speed change box clutch |
| CN114215857A (en) * | 2021-11-19 | 2022-03-22 | 周旭亮 | Hydraulic pump type clutch and vehicle |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6800980B2 (en) | 2015-12-18 | 2020-12-16 | フラウンホーファー−ゲゼルシャフト・ツール・フェルデルング・デル・アンゲヴァンテン・フォルシュング・アインゲトラーゲネル・フェライン | Data signal transmission in wireless communication systems with reduced end-to-end latency |
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| US3904143A (en) * | 1972-05-19 | 1975-09-09 | Bayer Ag | Reeling-up drum |
| CN85101715A (en) * | 1985-04-01 | 1987-04-01 | 南京汽车研究所 | Radial plunger type oil pump or oil motor that shell rotates |
| CN1144308A (en) * | 1995-04-05 | 1997-03-05 | 杜长春 | Static-pressure controlled clutch |
| CN202251534U (en) * | 2011-09-19 | 2012-05-30 | 朱能平 | Hydraulic-control non-friction clutch |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU675225A1 (en) * | 1977-06-23 | 1979-07-25 | Anatolij S Dresvyankin | Reversible coupling |
| DE2827609A1 (en) * | 1978-06-23 | 1980-01-10 | Fichtel & Sachs Ag | RADIAL PISTON PUMP |
| JPH1122638A (en) * | 1997-07-02 | 1999-01-26 | Tochigi Fuji Ind Co Ltd | Radial piston pump and coupling provided with the same |
| JPH1151090A (en) * | 1997-08-07 | 1999-02-23 | Tochigi Fuji Ind Co Ltd | Coupling |
| CN2317119Y (en) * | 1997-12-23 | 1999-05-05 | 郑宏太 | Expanding-contracting type double cone overdrive clutch |
| CN101539178B (en) * | 2008-03-19 | 2010-12-08 | 李礼然 | Deflective transmission-type clutch |
| CN101660576A (en) * | 2008-08-29 | 2010-03-03 | 比亚迪股份有限公司 | Overrunning clutch |
| CN102537118B (en) * | 2010-12-14 | 2015-02-11 | 李占军 | Clutch |
-
2012
- 2012-09-12 CN CN201210335641.3A patent/CN102840249B/en not_active Expired - Fee Related
- 2012-12-06 WO PCT/CN2012/086026 patent/WO2014040351A1/en active Application Filing
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3904143A (en) * | 1972-05-19 | 1975-09-09 | Bayer Ag | Reeling-up drum |
| CN85101715A (en) * | 1985-04-01 | 1987-04-01 | 南京汽车研究所 | Radial plunger type oil pump or oil motor that shell rotates |
| CN1144308A (en) * | 1995-04-05 | 1997-03-05 | 杜长春 | Static-pressure controlled clutch |
| CN202251534U (en) * | 2011-09-19 | 2012-05-30 | 朱能平 | Hydraulic-control non-friction clutch |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107327514A (en) * | 2017-08-24 | 2017-11-07 | 安徽江淮汽车集团股份有限公司 | A kind of new type auto speed change box clutch |
| CN114215857A (en) * | 2021-11-19 | 2022-03-22 | 周旭亮 | Hydraulic pump type clutch and vehicle |
| CN114215857B (en) * | 2021-11-19 | 2023-10-17 | 周旭亮 | Hydraulic pump type clutch and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102840249B (en) | 2015-01-14 |
| WO2014040351A1 (en) | 2014-03-20 |
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