CN103133550B - Axial locking type overload protection shaft - Google Patents
Axial locking type overload protection shaft Download PDFInfo
- Publication number
- CN103133550B CN103133550B CN201310048452.2A CN201310048452A CN103133550B CN 103133550 B CN103133550 B CN 103133550B CN 201310048452 A CN201310048452 A CN 201310048452A CN 103133550 B CN103133550 B CN 103133550B
- Authority
- CN
- China
- Prior art keywords
- axle
- valve
- shaft
- overload protection
- piston
- 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.)
- Active
Links
Landscapes
- Actuator (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention discloses an axial locking type overload protection shaft. The axial locking type overload protection shaft comprises a first shaft and a hollow second shaft, wherein the first shaft and the hollow second shaft are coaxially arranged and connected together in rotation mode, the first shaft is provided with a connecting seat relatively fixed with the first shaft, the second shaft is provided with a cylinder body seat relatively fixed with the second shaft, the cylinder body seat is provided with at least two pairs of hydraulic cylinders along the circumferential direction of the second shaft and towards the connecting seat, an energy storage valve is connected between each pair of hydraulic cylinders, sliding top blocks are arranged in the hydraulic cylinders, and bumps leaning against the top blocks are arranged on the connecting seat. The invention aims at providing a radial locking type overload protection shaft which can cut off power transmission when a device is overloaded so as to prevent a drive shaft from fracturing, and simultaneously is good in reliability.
Description
Technical field
The invention belongs to through-drive field, especially relate to a kind of transmission shaft structure with overload protective function.
Background technology
In mechanical transmission fields, particularly on motor vehicle, the power that engine produces needs to rely on transmission system to be finally passed on wheel.For the automobile that front engine front wheel drives, the power of engine to be delivered on propons two semiaxis by speed changer, main reducing gear, differential mechanism etc. thus to drive rotation of wheel, and the automobile that engine rear drives, power needs the main reducing gear being delivered to back axle by final drive shaft after speed changer.For offroad vehicle and lorry, in order to increase vehicle grade climbing performance and by performance, usually adopt front-rear axle multiaxis to drive.
The transmission system of vehicle designs according to the requirement of setting.When normally travelling, the stressed of transmission system is less than its maximum load value usually, but when vehicle travel road conditions be not very desirable area as potted road surface time, the stressing conditions of tire becomes comparatively severe, after tire force exceedes design maximum load, the power transmission shaft in transmission system and other parts easily damage.On Hyundai Motor, be arranged on the clutch between engine and speed changer, during for ensureing automobile balance starting and shifting gears, transmission system work is smooth-going, another one function is that limiting drive train is united the torque capacity of bearing, wherein mainly transmit power by the friction of the driving and driven part of clutch, when exceeding the maximum friction moment of clutch, will there is relative sliding friction in the driving and driven part of clutch.Can clearly find out; when power transmission shaft transships;, by the Relative friction of clutch main secondary part, kinetic transformation is heat energy thus the protection of raising to power transmission shaft; therefore when the road surface that road conditions are poor travels for a long time; clutch is often in overload conditions; the bulk deposition of heat makes the temperature of clutch constantly raise, and not only reduces transmission efficiency, and very easily causes it to burn.
At present, for the protection of the structure of power transmission shaft overload, as Chinese Patent Application No.: CN 201010230513.3; disclosed a kind of power transmission shaft; it is made up of interior central siphon, outer central siphon and press-in rubber, and the press-in vulcanization of rubber is at the outer surface of interior central siphon, and the interior central siphon of sulfuration press-in rubber is pressed into outer central siphon.Therefrom can find out, be to be rubbed transmission by rubber between interior central siphon and outer central siphon, the active force of power transmission shaft when transshipping between interior central siphon and outer central siphon overcomes rubber stiction thus relatively rotates.And in process in relative rotation, rubber wearing and tearing are very fast, become loosening between interior central siphon and outer central siphon, the time one is long then loses gearing.
Summary of the invention
The present invention is in order to when overcoming overload, power transmission shaft ruptures; or cause the deficiency that in the damage of associated actuator parts and prior art, antioverloading structure easily lost efficacy because of wearing and tearing; provide one can cut off power transmission thus prevent drive shafts fracture when transshipping, the axial lock compact form overload protection shaft of wearing and tearing less during use.
To achieve these goals, the present invention is by the following technical solutions:
A kind of axial lock compact form overload protection shaft, comprise the first axle and the second hollow axle, first axle and the second axle coaxially arranged and both be rotationally connected, the first described axle is provided with and the relatively-stationary Connection Block of the first axle, the second described axle is provided with and the relatively-stationary cylinder block of the second axle, described cylinder block is provided with at least two pairs of openings all towards the hydraulic cylinder of Connection Block along the circumferencial direction of the second axle, an accumulator valve is connected with between every pair of hydraulic cylinders, the jacking block of slip is provided with in described hydraulic cylinder, described Connection Block is provided with the projection offseted with jacking block.Power can import into from the first axle or the second axle, spreads out of from an other axle, and wherein hydraulic cylinder is connected by accumulator valve with adjacent or relative hydraulic cylinder.When the moment of torsion of power transmission shaft is less than setting value, jacking block and projection contact, the first axle and the second axle synchronous rotary, transmit power; When moment of torsion raises, the jacking block in cylinder body slides in cylinder body, has small relatively rotating between diaxon, but still can normal delivery power; And when moment of torsion exceedes design load, projection can just on move to the top of jacking block, the power therefore between projection and jacking block is disconnected, and occurs afterwards relatively to rotate between the first axle and the second axle, transships to prevent power transmission shaft.When moment of torsion between the first axle and the second axle is returned within setting value, under the effect of accumulator valve, jacking block declines, and makes the first axle and the second axle recover synchronous rotary.When road conditions are not good, ground drag is excessive, the present invention can play cushioning effect to power transmission shaft, and the situation that can prevent power transmission shaft from twisting off by the mode cutting off power transmission when load is excessive, also reduces the load of clutch during power transmission shaft overload simultaneously.In addition, the power from engine can also be relaxed, reduce power when shifting gears and, for the impact of power transmission shaft, make power transmission also more smooth-going.For the automobile that front-rear axle drives simultaneously, when turning to, the impact produced can be cushioned and be regulated, also can play good protective effect to main reducing gear and transfer gear between front and back wheel due to speed discrepancy.
As preferably, described Connection Block is arranged in opposite directions on the first axle, the second described axle is arranged between the Connection Block on the first axle, described cylinder block is separately positioned on the two ends of the second axle, connected by framework between cylinder block, framework extends to form and the first axle axis body in relative rotation along the axis of the first axle.Between the Connection Block of the first axle, arrange the second axle, the cylinder block at the second axle two ends is corresponding with Connection Block, and such first axle and the stressed of the second axle comparatively balance, and improve the maximum load between the first axle and the second axle, are applicable to the truck that load is larger.
As the replacement scheme of above-mentioned preferred version, described cylinder block is separately positioned on the both sides of Connection Block, and Connection Block is equipped with projection on the two sides of cylinder block, is connected between cylinder block by framework.Such first axle and the second axle can reach the effect of stress balance equally, and overall structure also seems more compact, are therefore relatively applicable to cyclecar and use.
As preferably, described accumulator valve comprises valve body and is positioned at the piston of valve body, and described piston is connected with valve body by back-moving spring, and described valve body is provided with the valve port of two homonymies.When the pressure of hydraulic cylinder is larger, the piston upwards in accumulator valve, compresses back-moving spring, arrives poised state; When the hydraulic fluid pressure in hydraulic cylinder diminishes, piston moves downward under the action of the spring, promotes hydraulic oil and flow back in hydraulic cylinder.Accumulator valve can absorb the impact energy from road surface and play accumulation of energy effect, thus plays the effect of overload protection to power transmission shaft.
As preferably, described valve body is provided with the oil storage chamber be connected with valve port, be provided with in described oil storage chamber and can relatively slide and the piston rod be fixedly connected with piston by oil storage chamber, described piston is provided with compression valve and rebound valve, described compression valve and rebound valve reversed arrangement on piston.Valve pocket is divided into uuper valve chamber and lower valve chamber by piston, when hydraulic oil enters in oil storage chamber from valve port, piston rod promotes piston upwards, uuper valve chamber is squeezed, when the oil pressure difference of upper lower valve chamber has exceeded the unlatching threshold values of compression valve, compression valve and opening, hydraulic oil passes through compression valve, enter in lower valve chamber, piston moves simultaneously; When the oil pressure of hydraulic cylinder reduces, back-moving spring promotes piston and moves downward, and now rebound valve is opened, and hydraulic oil is flow in uuper valve chamber from lower valve chamber by rebound valve.Therefore, when power transmission shaft is about to overload occurs, compression valve is opened, and sheds oil pressure, and the first axle and the second axle can be relatively rotated.
As preferably, on described jacking block and the one side that contacts of projection spherically.Such jacking block and projection are more smooth in relative motion, and jacking block can bear larger contact stress simultaneously, improves the stressing conditions of jacking block.
As preferably, described projection is cylindrical, and the first described axle is provided with the groove mated with projection.Projection can roll in groove, thus reduces, with the wearing and tearing of jacking block, to improve service life further.
As preferably, described rebound valve comprises upholds spool and rebound valve spring, and described compression valve comprises compression spool and is in the compression valve spring of compressive state.Compression valve spring is when assembling by compressive state in advance, and when so only in valve pocket, oil pressure is higher, compression valve just can be opened thus play cushioning effect, and when low moment of torsion, the first axle is less with the relative rotational steps of the second axle, can improve transmission efficiency.
As preferably, the device of spring stiffness coefficient of described compression valve spring is greater than the stiffness factor of rebound valve spring.Like this when the oil pressure in hydraulic cylinder reduces, piston is returning quickly under back-moving spring promotes, and ensures normal power transmission.
Therefore, the present invention has following beneficial effect: (1) can effectively prevent ground drag excessive and cause power transmission shaft to twist off; (2) loss of clutch in transmission system is alleviated; (3) relax power during gearshift to the impact of power transmission shaft, promote smooth gear shifting; (4) wear and tear when using less, service life is longer; (5) moment impact that front and back wheel speed discrepancy produces main reducing gear and transfer gear is cushioned when turning to.
Accompanying drawing explanation
Fig. 1 is the structural representation of the embodiment of the present invention 1;
Fig. 2 is the profile of the embodiment of the present invention 1;
Fig. 3 is the structural representation of valve body in the embodiment of the present invention 1.
Fig. 4 is the profile of the embodiment of the present invention 2;
Fig. 5 is the structural representation of valve body in the embodiment of the present invention 2.
In figure, the first axle 1, Connection Block 1c, cylinder block 3c, the first Connection Block 1a, second Connection Block 1b, hydraulic cylinder 2, the second axle 3, first cylinder block 3a, the second cylinder block 3b, pipeline 4, projection 5, jacking block 6, accumulator valve 7, valve body 7a, valve port 7b, lower valve chamber 7c, uuper valve chamber 7d, oil storage chamber 7e, piston 71, back-moving spring 72, piston rod 73, compression valve 74, rebound valve 75, framework 8a, axis body 8b, centring ring 9, rolling bearing 10, needle bearing 11.
Detailed description of the invention
Below in conjunction with the drawings and specific embodiments, the present invention will be further described.
Embodiment 1
In embodiment 1 as shown in Figure 1 and Figure 2, a kind of axial lock compact form overload protection shaft, comprise the first axle 1 and the second axle 3, wherein the second axle is hollow-core construction, and both are coaxially arranged.First axle is provided with two Connection Block 1c be oppositely arranged, and is respectively the first Connection Block 1a and the second Connection Block 1b.Second axle is between first, second Connection Block, and two ends are connected with the first axle by rolling bearing 10, controls axial slip simultaneously, can relatively rotate between such first axle and the second axle between the second axle and Connection Block by centring ring 9.Second axle two ends are respectively equipped with cylinder block 3c, i.e. the first cylinder block 3a and the second cylinder block 3b, first cylinder block and the second cylinder block are respectively equipped with three pairs of hydraulic cylinders 2, hydraulic cylinder distributes along the circumferencial direction of the second axle on cylinder block, and the axis of hydraulic cylinder is parallel with the pivot center of the second axle.Hydraulic cylinder adjacent on same cylinder block is connected with pipeline 4 respectively, and two pipelines are connected with an accumulator valve 7.In the cylinder body of hydraulic cylinder, be provided with jacking block 6, jacking block can slide in hydraulic cylinder, and and is seal between hydraulic cylinder.First, second Connection Block is respectively equipped with projection 5, and projection is corresponding with the position of jacking block.The one side that projection contacts with jacking block is arc surface, and the contact surface of jacking block is sphere.As shown in Figure 2, be connected with framework 8a between the first cylinder block and the second cylinder block, framework extends to the first cylinder block side in the axial direction, and is formed and the first axle axis body 8b in relative rotation, arranges needle bearing between axis body and the first axle, reduces rotary resistance.
As shown in Figure 3, accumulator valve comprises valve body 7a and piston 71, and piston can be up and down in valve body, and the two ends of piston are connected with valve body respectively by back-moving spring 72.Valve body is provided with two valve port 7b, and these two valve ports are positioned at the same side of valve body, are connected with the cylinder body of hydraulic cylinder by pipeline.Valve pocket divides in order to uuper valve chamber 7d and lower valve chamber 7c by piston, wherein, have hydraulic oil in lower valve chamber, and uuper valve chamber is air.
Because power is from the first axle and one of them input of the second axle, below for from the first axle input power, be described from the second axle outputting power operation of the present invention: when first be coupling receive input power rotate time, projection on first axle contacts with jacking block, jacking block promotes hydraulic cylinder sidewall, drive the second axle synchronous rotary, power exports eventually through axis body through framework, thus drives load.In the course of the work, jacking block in hydraulic cylinder hydraulic oil produce pressure, by pipeline by hydraulic pressure transfer to accumulator valve, promote piston upwards, because there is the air pressure effect of back-moving spring and uuper valve chamber at piston two ends, therefore when stress balance, jacking block position remains unchanged.The resistance be subject to when the second axle continues to increase, when reaching transmission shaft design maximum load, jacking block continues to be promoted by projection, until the tip contact of the top of jacking block sphere and projection arc surface, just no longer transmit power between jacking block and projection, relatively rotate between the first axle and the second axle.Therefore, the power transmission between the first axle and the second axle can be cut off, and can not cause damage, play the effect of overload protection to other parts of power transmission shaft and transmission system.And when load is less than overload values, under action of reset spring, piston slide downward, jacking block also moves downward, and the power transmission between the first axle and the second axle recovers.
Embodiment 2
In embodiment 2 as described in Figure 4, comprise the first axle 1 and the second axle 3, wherein the second axle is hollow-core construction, and both are coaxially arranged.First axle is provided with one and the relatively-stationary Connection Block 1c of the first axle, disconnect, be positioned at Connection Block both sides, and the second axle is connected by needle bearing 11 with the first axle, therefore can relatively rotate between the first axle and the second axle in the middle part of the second axle.Connection Block both sides are respectively equipped with cylinder block 3c, i.e. the first cylinder block 3a and the second cylinder block 3c, and the first cylinder block and the second cylinder block and the second axle are fixed.First cylinder block and the second cylinder block are respectively equipped with three pairs of hydraulic cylinders 2, and hydraulic cylinder distributes along the circumferencial direction of the second axle on cylinder block, and the axis of hydraulic cylinder is parallel with the pivot center of the second axle.Be connected with pipeline 4 between two hydraulic cylinders corresponding on first, second cylinder block, two pipelines are connected with an accumulator valve 7.In the cylinder body of hydraulic cylinder, be provided with jacking block 6, jacking block can slide in hydraulic cylinder, and and is seal between hydraulic cylinder.The two sides of Connection Block towards cylinder block are equipped with projection 5, and projection is corresponding with the position of jacking block, is fixedly connected with both guarantees rotates consistent between first, second cylinder block by framework 8a.The one side that projection contacts with jacking block is arc surface, and the contact surface of jacking block is sphere.
As shown in Figure 5, accumulator valve comprises valve body 7a and piston 71, and piston can be up and down in valve body, and the upper end of piston is connected with valve body one end by back-moving spring 72, and be provided with two valve port 7b on opposite ends, on valve port, connecting pipe is connected with the cylinder body of hydraulic cylinder.Valve body is provided with the oil storage chamber 7e be connected with valve port, is provided with piston rod 73 in oil storage chamber, and piston rod upper end and piston are bolted to connection, and piston can slide by oil storage chamber relatively.Valve pocket be divide into uuper valve chamber 7d and lower valve chamber 7c by piston, has hydraulic oil in upper lower valve chamber.In addition, piston is also provided with compression valve 74 and rebound valve 75, compression valve and rebound valve reversed arrangement on piston.Rebound valve comprises upholds spool and rebound valve spring, compression valve comprises compression spool and compression valve spring, wherein compression valve spring is in compressive state by pretension, and the device of spring stiffness coefficient of compression valve spring is greater than the stiffness factor of rebound valve spring, the sectional area of upholding normal open gap between spool and piston is greater than the sectional area in normal open gap between compression valve and piston.The course of work of accumulator valve is: the hydraulic oil from hydraulic cylinder enters into oil storage chamber by valve port, promote piston rod and drive piston upwards, make pressure increase in uuper valve chamber, when the pressure differential of upper lower valve chamber overcomes the pretightning force of compression valve spring, compression valve is opened, and the hydraulic oil in uuper valve chamber flows in lower valve chamber by compression valve; When the oil pressure that piston rod is subject to reduces, piston moves down under back-moving spring promotes, and rebound valve is opened, and the hydraulic oil of lower valve chamber enters in uuper valve chamber through rebound valve.
In real-world operation process, for from the first axle input power, be described from the second axle outputting power operation of the present invention: when first be coupling receive input power rotate time, projection on first axle contacts with jacking block, jacking block promotes hydraulic cylinder sidewall, thus drive the second axle synchronous rotary, thus drive load.In the course of the work, jacking block in hydraulic cylinder hydraulic oil produce pressure, by pipeline by hydraulic pressure transfer to accumulator valve, oil pressure promote piston rod, thus drive piston upwards.The resistance be subject to when the second axle increases, and namely load increases, until when exceeding the design maximum load of power transmission shaft, compression valve is opened, now jacking block rises to the summit of projection, no longer transmits power between jacking block and projection, relatively rotates between the first axle and the second axle.Therefore, the power transmission between the first axle and the second axle can be cut off, and can not cause damage, play the effect of overload protection to other parts of power transmission shaft and transmission system.And when load is less than overload values, under action of reset spring, piston slide downward, jacking block also moves downward, and the power transmission between the first axle and the second axle recovers.
Claims (7)
1. an axial lock compact form overload protection shaft, it is characterized in that, comprise the first axle (1) and hollow the second axle (3), first axle (1) and the second axle (3) coaxially arranged and both be rotationally connected, described the first axle (1) is provided with and the first axle (1) relatively-stationary Connection Block (1c), described the second axle (3) is provided with and the second axle (3) relatively-stationary cylinder block (3c), described cylinder block (3c) is provided with at least two pairs of openings all towards the hydraulic cylinder (2) of Connection Block (1c) along the circumferencial direction of the second axle (3), the axis of hydraulic cylinder (2) is parallel with the pivot center of the second axle (3), an accumulator valve (7) is connected with between every pair of hydraulic cylinders, the jacking block (6) of slip is provided with in described hydraulic cylinder (2), described Connection Block (1c) is provided with the projection (5) offseted with jacking block (6), described Connection Block (1c) is oppositely arranged on the first axle (1), described the second axle (3) is arranged between the Connection Block on the first axle (1), described cylinder block (3c) is separately positioned on the two ends of the second axle (3), connected by framework (8a) between cylinder block, framework extends to form and the first axle (1) axis body (8b) in relative rotation along the axis of the first axle (1).
2. axial lock compact form overload protection shaft according to claim 1; it is characterized in that; described accumulator valve (7) comprises valve body (7a) and is positioned at the piston (71) of valve body (7a); described piston (71) is connected with valve body (7a) by back-moving spring (72), and described valve body (7a) is provided with the valve port (7b) of two homonymies.
3. axial lock compact form overload protection shaft according to claim 2; it is characterized in that; described valve body (7a) is provided with the oil storage chamber (7e) be connected with valve port (7b); be provided with in described oil storage chamber (7e) and can relatively slide and the piston rod (73) be fixedly connected with piston (71) by oil storage chamber (7e); described piston (71) is provided with compression valve (74) and rebound valve (75), and described compression valve (74) and rebound valve (75) are in the upper reversed arrangement of piston (71).
4. axial lock compact form overload protection shaft according to claim 1 and 2, is characterized in that, the one side that described jacking block (6) is gone up and projection (5) contacts spherically.
5. axial lock compact form overload protection shaft according to claim 1 and 2, is characterized in that, described projection (5) is cylindrical, and described the first axle (1) is provided with the groove mated with projection (5).
6. axial lock compact form overload protection shaft according to claim 3, is characterized in that, described rebound valve (75) comprises upholds spool and rebound valve spring, and described compression valve (74) comprises compression spool and is in the compression valve spring of compressive state.
7. axial lock compact form overload protection shaft according to claim 6, is characterized in that, the device of spring stiffness coefficient of described compression valve spring is greater than the stiffness factor of rebound valve spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310048452.2A CN103133550B (en) | 2013-02-07 | 2013-02-07 | Axial locking type overload protection shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310048452.2A CN103133550B (en) | 2013-02-07 | 2013-02-07 | Axial locking type overload protection shaft |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103133550A CN103133550A (en) | 2013-06-05 |
| CN103133550B true CN103133550B (en) | 2015-03-25 |
Family
ID=48493826
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310048452.2A Active CN103133550B (en) | 2013-02-07 | 2013-02-07 | Axial locking type overload protection shaft |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103133550B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111878520A (en) * | 2020-05-20 | 2020-11-03 | 李涛涛 | Hydraulic loading type internal friction overload protection synchronous pulley device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1442324A (en) * | 2002-08-08 | 2003-09-17 | 周苗长 | Control method and device of valve open pressure change of absorber |
| EP2280191A2 (en) * | 2009-07-29 | 2011-02-02 | Liebherr-Werk Biberach GmbH | Drive unit with overload protection for driving a crown gear, set comprising a plurality of such drive units and device comprising such a drive unit |
| CN202413418U (en) * | 2012-01-09 | 2012-09-05 | 陈学福 | Front transmission shaft structure for front wheel drive and rear wheel drive vehicles |
| CN102691734A (en) * | 2012-02-10 | 2012-09-26 | 陈学福 | Transmission shaft structure |
| CN203161879U (en) * | 2013-02-07 | 2013-08-28 | 福建合众机械有限公司 | Axial-locking-type overload protection shaft |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5443866B2 (en) * | 2009-07-14 | 2014-03-19 | 株式会社中村自工 | Hydraulic joint |
-
2013
- 2013-02-07 CN CN201310048452.2A patent/CN103133550B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1442324A (en) * | 2002-08-08 | 2003-09-17 | 周苗长 | Control method and device of valve open pressure change of absorber |
| EP2280191A2 (en) * | 2009-07-29 | 2011-02-02 | Liebherr-Werk Biberach GmbH | Drive unit with overload protection for driving a crown gear, set comprising a plurality of such drive units and device comprising such a drive unit |
| CN202413418U (en) * | 2012-01-09 | 2012-09-05 | 陈学福 | Front transmission shaft structure for front wheel drive and rear wheel drive vehicles |
| CN102691734A (en) * | 2012-02-10 | 2012-09-26 | 陈学福 | Transmission shaft structure |
| CN203161879U (en) * | 2013-02-07 | 2013-08-28 | 福建合众机械有限公司 | Axial-locking-type overload protection shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103133550A (en) | 2013-06-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103352929B (en) | Single-cylinder built-in overload protection shaft | |
| US9764613B2 (en) | Co-axial sway bar for a suspension system | |
| CN106891717B (en) | Duplex drive axle capable of realizing lifting and driving of rear axle | |
| CN203272511U (en) | Overload protection shaft with internally-arranged single cylinder | |
| CN101737478B (en) | Driving limited-slip differential | |
| EP3333001B1 (en) | Shaft connection for a vehicle | |
| CN103939570A (en) | Hydraulic antiskid self-locking differential mechanism | |
| CN206528339U (en) | It is a kind of to realize the double drive axle of back axle lifting and driving | |
| CN102691734B (en) | Transmission shaft structure | |
| WO2005014314A1 (en) | Amphibious vehicle | |
| CN103133551B (en) | Radial locking type over-load protection shaft | |
| CN103133550B (en) | Axial locking type overload protection shaft | |
| CN203161878U (en) | Radial locking type overload protecting shaft | |
| CN203161879U (en) | Axial-locking-type overload protection shaft | |
| CN108045223B (en) | New energy automobile decelerator | |
| CN204692498U (en) | A kind of engagement type automobile differential | |
| CN104203626B (en) | The transmission device and motor of helical teeth engagement | |
| CN105042016A (en) | Hydraulic drive indirect meshing locking differential mechanism | |
| CN105042020A (en) | Hydraulic drive direct-geared lock differential mechanism | |
| CN204391972U (en) | Integrated electric motor-car power syndeton | |
| CN104191964B (en) | A kind of transfer robot based on flexible drive wheel | |
| CN109340343B (en) | Hydraulic locking mechanism on differential mechanism | |
| CN112762169A (en) | Transmission structure and bidirectional buffer mechanism thereof | |
| CN207598901U (en) | Power assisted gearshift failsafe structure | |
| CN202082308U (en) | Dumper nonconstant velocity cardan drive shaft assembly |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20160615 Address after: 354200 No. 176 Renmin Road, Jilin town, Jianyang District, Fujian, Nanping Patentee after: NANPING CITY JIANYANG DISTRICT AUTO FORGING PARTS FACTORY Address before: 354209, No. 183 Renmin Road, Jilin town, Nanping, Fujian, Jianyang Patentee before: Fujian Hezhong Machinery Co., Ltd. Patentee before: Chen Xuefu |
|
| PE01 | Entry into force of the registration of the contract for pledge of patent right |
Denomination of invention: Axial locking type overload protection shaft Effective date of registration: 20161118 Granted publication date: 20150325 Pledgee: Agricultural Bank of China Limited by Share Ltd Nanping Jianyang branch Pledgor: NANPING CITY JIANYANG DISTRICT AUTO FORGING PARTS FACTORY Registration number: 2016350000135 |
|
| PLDC | Enforcement, change and cancellation of contracts on pledge of patent right or utility model |