CN103982602A - Automatic speed change gear with torsion limiting clutch and speed change shaft - Google Patents
Automatic speed change gear with torsion limiting clutch and speed change shaft Download PDFInfo
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- CN103982602A CN103982602A CN201410238462.7A CN201410238462A CN103982602A CN 103982602 A CN103982602 A CN 103982602A CN 201410238462 A CN201410238462 A CN 201410238462A CN 103982602 A CN103982602 A CN 103982602A
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- gear
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- driving
- dish
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
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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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
- F16D43/213—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces
- F16D43/218—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with axially applied torque-limiting friction surfaces with conical friction surfaces
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/14—Inputs being a function of torque or torque demand
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
- F16H61/148—Control of torque converter lock-up clutches using mechanical control means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/14—Inputs being a function of torque or torque demand
- F16H2059/144—Inputs being a function of torque or torque demand characterised by change between positive and negative drive line torque, e.g. torque changes when switching between coasting and acceleration
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses an automatic speed change gear with a torsion limiting clutch and a speed change shaft. The speed change gear comprises a high-speed drive gear, a low-speed drive gear, a high-speed driven gear and a low-speed driven gear, wherein the high-speed drive gear and the low-speed drive gear are arranged on a drive shaft, the high-speed driven gear and the low-speed driven gear are arranged on a driven shaft, and the high-speed drive gear, the low-speed drive gear, the high-speed driven gear and the low-speed driven gear are correspondingly and constantly meshed. The drive shaft is provided with the normally-closed torsion limiting clutch used for power connection of the high-speed drive gear and the drive shaft. A connection structure capable of synchronously rotating is formed by the low-speed drive gear and the drive shaft. A one-way overrunning clutch or a two-way overrunning clutch is arranged between the high-speed driven gear and the driven shaft and between the low-speed driven gear and the driven shaft respectively. The speed change shaft comprises the drive shaft, the high-speed drive gear, the low-speed drive gear and the normally-closed torsion limiting clutch, wherein the high-speed drive gear and the low-speed drive gear are arranged on the drive shaft and the normally-closed torsion limiting clutch is used for power transmission between the high-speed drive gear and the drive shaft. The drive end of the clutch is connected with the drive shaft through a spiral spline structure. The automatic speed change gear and the speed change shaft have the advantages that the speed change gear enables the automatic two-gear shifting function of forward transmission and the inverted transmission function to be achieved and is simple in structure and rapid in gear shifting; the high-speed inverted output torsion of the speed change shaft is larger than the forward output torsion.
Description
Technical field
The present invention relates to a kind of speed change gear for electric motor car transmission case, particularly a kind of for limitting automatic transimission and the variable-speed shaft of turning round clutch containing of electric motor car transmission case.
Background technique
Electric motor car refers to, by motor-driven motorcycle, comprise two-wheeled, three-wheel and four-wheel in this application, and it is mainly to realize speed change by the mode of controller control motor speed.Along with the development of vehicle technology, some electric motor cars at present also dispose the gear gearbox of mechanical structure, it mainly provides speed change to carry out power by electromagnet etc., drives executive component to realize shift speed change by electromagnet, and shift speed change is operated by the personnel of riding conventionally.Mechanical type shift speed change or the automatically controlled shift speed change of existing electric motor car are all realized by driver's operation mostly, in the time that gearbox has automatic gear shifting structure, can realize automatic speed changing.Existing automatic gearbox complex structure, can not be advantageously used in electric motor car.Although those skilled in the art has also developed the automatic transmission for electric motor car, be all the shift speed change of realizing by rotation speed change conventionally.This is to control motor speed by rotating speed control one, the 2nd, load increases and decreases the rotating speed causing and changes, it is initiatively that power increases and decreases the rotation speed change causing, but initiatively increase and decrease the variation that rotating speed obviously directly causes energy consumption, its time point initiatively increasing and decreasing is controlled by driver, obviously can cause part power to be lost in vain, or increase and decrease affect travelling speed not in time.And the rotation speed change that load variations causes is passive, then implement speed change by the result of variations of rotating speed, it lags behind on time point.
In automatic gear shifting speed changing system or device, conventional mono-directional overrun clutch also claims one-way element, double rolling key clutch, controllable overrunning clutch and friction type limit to turn round clutch etc.Free wheel device belongs to the clutch configuration of coaxial transmission, and the driving link of mono-directional overrun clutch can drive driven member towards direction initialization one-way rotation, and in like manner, driven member can drive driving link to rotate backward; The driving link of double rolling key clutch can drive the forward and reverse rotation of driven member, and driven member can not drive driving link to rotate.In controllable overrunning clutch, be provided with control unit, separate the combination and the disengagement that realize clutch with the mode of combination by the frictional engagement element of control elements solenoidoperated cluthes with principal and subordinate's moving part.In the mechanical variable speed device of existing electric motor car, realize shift speed change control by the control panel of magnet control controllable overrunning clutch.Limit is turned round clutch and is claimed again safety clutch, and it refers to that load torque encloses when interior in restriction, and the initiative taper dribbling of clutch is moving synchronously rotates from mantle dish; In the time that load torque meets or exceeds limit value, initiative taper dish with from mantle dish form relatively rotate.It is more that limit is turned round the structural type of clutch, longer use be friction clutch structure.The limit of friction clutch structure is turned round clutch, meets or exceeds limit when limit value at load torque, and initiative taper dish synchronously rotates can not drive from mantle dish, but initiative taper dish still contacts and forms fretting wear in relative rotation with the rubbing surface from mantle dish.Therefore, need a kind of at this moment by initiative taper dish and the structure separating from mantle dish so that initiative taper dish and being separated from each other from mantle dish.
In prior art, although also occurred that some turn round clutch by limit and overrunning clutch is realized self-shifting speed change gear, conventionally all there is complex structure, the deficiency that manufacture cost is high; Can't realize in addition reverse output.For this reason, need to continue to improve.
Summary of the invention
Object of the present invention is exactly for the deficiencies in the prior art, and a kind of speed change gear with forward two-gear automatic speed changing and reversion output is provided, and this device, in the time of driving shaft forward, is realized shift speed change automatically according to load torque size variation; It is skillfully constructed, simple in structure and various informative.
For achieving the above object, the present invention adopts following technological scheme.
A kind of containing the limited automatic transimission of turning round clutch, comprise driving shaft and driven shaft, on driving shaft and driven shaft, be respectively equipped with top gear gear mesh and the bottom gear gear mesh of corresponding normal engagement, the top gear driving gear of described top gear gear mesh is rotatably connected on described driving shaft, between top gear driving gear and driving shaft, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring that friction limit is turned round clutch is connected to driving shaft and rubs to limit and turn round between the initiative taper dish of clutch, between initiative taper dish and described driving shaft, be also provided with for powerdriven torque transfer arrangement, this torque transfer arrangement is at least in the time that the load torque of driving shaft forward and driven shaft reaches setting value, initiative taper dish forms and moving axially of throwing off from mantle dish, friction limit is turned round forming one or be coaxially fixedly connected with top gear driving gear from mantle dish of clutch, between the bottom gear driving gear of described bottom gear gear mesh and described initiative taper dish, be formed with the two and can synchronize the linkage structure of rotating, or bottom gear driving gear is coaxially fixedly connected on driving shaft, described top gear driven gear is coaxially connected on driven shaft by the first mono-directional overrun clutch or the first double rolling key clutch, or top gear driven gear is coaxially fixedly connected on driven shaft, this first mono-directional overrun clutch drives described driven shaft forward synchronously to rotate for top gear driven gear, and this first double rolling key clutch drives the forward and reverse synchronous rotation of described driven shaft for top gear driven gear, between the bottom gear driven gear of described bottom gear gear mesh and driven shaft, be provided with the second double rolling key clutch or the second overrunning clutch, this second double rolling key clutch drives the forward and reverse synchronous rotation of driven shaft for bottom gear driven gear, or this second overrunning clutch drives driven shaft forward synchronously to rotate for bottom gear driven gear.
Adopt the present invention of aforementioned techniques scheme, be provided with in the scheme of the second double rolling key clutch between bottom gear driven gear and driven shaft, driving shaft is rotated in the forward or counterrotating under motor drives.When driving shaft is rotated in the forward, load first by driven shaft, top gear driven gear and top gear driving gear be loaded into friction limit turn round clutch from mantle dish, in the time that loading moment is less than setting value, driving shaft is limit and is turned round clutch and drive top gear gear mesh to be rotated in the forward by top gear by friction, and top gear driven gear is by the first mono-directional overrun clutch, the first double rolling key clutch or directly drive driven shaft to be rotated in the forward by top gear; Now, although bottom gear driven gear rotates forward rotation under bottom gear driving gear drives, its rotational velocity is lower than the rotational velocity of driven shaft, and the two sense of rotation is identical, and bottom gear driven gear is formed and surmounted by double rolling key clutch and driven shaft; In the time that loading moment meets or exceeds setting value, output speed declines, friction limit is turned round the initiative taper dish of clutch and is formed and relatively rotate from mantle dish, initiative taper dish and from the friction torque between mantle dish by the torque transfer arrangement between initiative taper dish and driving shaft, initiative taper dish is formed and throws off and move axially and away from driven disc from mantle dish.In the time that output speed drops to bottom gear rotating speed, loading moment is loaded on bottom gear driving gear by the second double rolling key clutch and bottom gear driven gear, driven shaft is driven and is rotated in the forward by bottom gear by bottom gear gear mesh and the second double rolling key clutch, now, the unpowered output of top gear driving gear; Between top gear driven gear and driven shaft, be provided with the situation of the first mono-directional overrun clutch and the first double rolling key clutch, top gear driven gear declines to rotating speed under the surface friction drag effect in structure self and gradually lower than output speed, until stall, top gear driven gear is formed and is surmounted by the first mono-directional overrun clutch and the first double rolling key clutch and driven shaft; Form the situation being coaxially fixedly connected with at top gear driven gear and driven shaft, top gear driven gear is synchronizeed and is rotated with driven shaft, now, top gear driven gear drives top gear driving gear to form idle running in the same way with the rotating speed lower than driving shaft and driving shaft, realizes the automatic speed changing to bottom gear by top gear with this.At driven shaft in bottom gear running, load variations is when being less than setting value, driving shaft is limit and is turned round clutch and drive top gear driving gear to be rotated in the forward by friction, driven shaft is directly driven by top gear driven gear, or, driven and pressed top gear forward High Rotation Speed by the first mono-directional overrun clutch or the one the first double rolling key clutchs, driven shaft is automatically converted to high speed rotating by low speed.Now, bottom gear driven gear rotating speed is lower than output speed, and bottom gear driven gear and driven shaft are formed and surmounted by double rolling key clutch.When driving shaft forward rotation is during as vehicle progression power input mode, this programme can be applicable to the two-gear automatic speed changing that vehicle advances easily, without carrying out manual control, has avoided the improper problem on opportunity of manual control speed change; And gearshift is changed and directly caused velocity variations by load, with respect to causing velocity variations because load changes in prior art, the mode of being carried out again speed change by velocity variations is more direct, its speed change response time shortens, speed change is more quick, has eliminated electric motor car and has burnt out not in time the hidden danger of motor because of gearshift.In the time of driving shaft counterrotating, top gear driving gear is synchronizeed and is rotated with driving shaft, when being fixedly connected with driven shaft at top gear driven gear or being connected with driven shaft by the first double rolling key clutch, top gear driven gear directly drives driven shaft synchronous backward high speed rotating, bottom gear driving gear drives bottom gear driven gear synchronous backward to slowly run, now, bottom gear driven gear and driven shaft the second double rolling key clutch form and surmount, the electric motor car of this kind of situation only has high-reverse function, and without low-reverse function, for only needing the situation of reversing fast, in the time that top gear driven gear is connected with driven shaft by the first double rolling key clutch, vehicle has reversing wheel function, at top gear driven gear and driven shaft during by the first mono-directional overrun clutch, top gear driving gear and driving shaft synchronous backward high speed rotating, bottom gear driving gear drives bottom gear driven gear synchronous backward to slowly run, and top gear driven gear is formed and surmounted by the first mono-directional overrun clutch and driven shaft, the electric motor car of this kind of situation, vehicle only has low-speed heave-load car-backing function, and without quick car-backing function, can guarantee the safety of moveing backward.The torque transfer arrangement arranging between initiative taper dish and driving shaft has driving shaft reversion, and the load torque of driven shaft reaches setting value, the initiative taper dish that friction limit is turned round clutch forms with from the situation that moves axially function of mantle dish disengagement by this torque transfer arrangement.At initiative taper dish and from mantle dish is thrown off, bottom gear driving gear drives bottom gear driven gear synchronous backward to slowly run by the second twin-direction clutch, when being fixedly connected with driven shaft at top gear driven gear or being connected with driven shaft by the first mono-directional overrun clutch, the counterrotating under driven shaft drives of top gear driven gear, or drive and reversely rotate at low speed by mono-directional overrun clutch, corresponding top gear driving gear with the rotating speed lower than driving shaft with driving shaft in the same way relative to rotating, or, bottom gear driving gear drives bottom gear driven gear synchronous backward to slowly run by the second twin-direction clutch, top gear driven gear is formed and is surmounted by the first twin-direction clutch and driven shaft, the electric motor car of this kind of situation has low-speed heave-load car-backing function.Therefore, be provided with mono-directional overrun clutch between top gear driven gear and driven shaft time, no matter initiative taper dish with whether be combined from mantle dish, can guarantee that vehicle only possesses bottom gear car-backing function, and without car-backing function fast, the safety of guaranteeing to move backward; Meanwhile, on driven shaft and between high speed driven gear when the first mono-directional overrun clutch or the first twin-direction clutch, on driven shaft and between low speed driven gear, when the second double rolling key clutch, electric motor car has the wheel function of moving ahead; On driven shaft and between high speed driven gear when the first single-direction and dual-direction clutch, on driven shaft and between low speed driven gear, when the second double rolling key clutch, electric motor car has backward skating function.This scheme is applicable to tricycle or four-wheel wagon.
Between bottom gear driven gear and driven shaft, be provided with in the scheme of the second mono-directional overrun clutch, top gear gear mesh is by the first mono-directional overrun clutch, the first double rolling key clutch or while directly driving driven shaft to be rotated in the forward, and bottom gear driven gear is formed and surmounted by the second overrunning clutch or the second double rolling key clutch and driven shaft; In the time that bottom gear driven gear drives driven shaft to rotate by the second mono-directional overrun clutch or the second double rolling key clutch, normally closed friction-disc clutch disconnects, unpowered transmission between top gear gear mesh, but input shaft can not reverse.During for electric motor car, vehicle has two gear self shifter and the wheel function of advancing, and without gear reversing function.This scheme is applicable to electric motor car with two wheels.
In this programme, the two formation between bottom gear driving gear and initiative taper dish can be synchronizeed the linkage structure of rotating and be comprised, bottom gear driving gear is integral with initiative taper dish type or be coaxially fixedly connected with, or between bottom gear driving gear and initiative taper dish, spline fitted structure is set, in spline fitted structure, comprise straight spline and helical spline, in the time adopting helical spline structure, between the two, also need to arrange axial limit structure, to guarantee in the time that the two relatively rotates desired location, bottom gear driving gear and initiative taper dish form synchronizes rotation.
Unidirectional and double rolling key clutch in this programme includes ball type, roller type and wedge block type.
Friction limit in this programme is turned round in clutch, can inlay friction material in the frictional engagement face position of driving disc or driven disc as required; Meanwhile, also can be set to inner cone dish or external cone plate according to driving disc, corresponding driven disc is set to the structure corresponding with driving disc.
Therefore, this programme carries out ingenious combination by turning round clutch, unidirectional super clutch and double rolling key clutch etc. to limit of the prior art, realize the adaptive shift speed change mode of shift speed change and load torque, and there is car-backing function, simultaneously, it is simple in structure, be skillfully constructed, low cost of manufacture.
Preferably, described torque transfer arrangement is the first helical spline cooperating structure being located between driving shaft and initiative taper dish, this the first helical spline cooperating structure is in the time that the load torque of driving shaft forward and driven shaft reaches setting value, and the initiative taper dish that friction limit is turned round clutch forms and moving axially of throwing off from mantle dish by this torque transfer arrangement.Make in the time that load torque reaches setting value, the initiative taper dish that friction limit is turned round clutch takes off fast from mantle dish, to realize the agility of shift speed change.Certainly, the lead angle of the first helical spline should be greater than Self-locking angle corresponding to the two relative wiping coefficient of driving shaft and initiative taper dish, belongs to those skilled in the art's basic general knowledge.
Further preferred, it is the second helical spline cooperating structure forming between the two that the two formation between described bottom gear driving gear and described initiative taper dish can be synchronizeed the linkage structure of rotating, bottom gear driving gear is sleeved on described initiative taper dish by this second helical spline cooperating structure, and the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure; Bottom gear driving gear is limited in the axial desired location of described driving shaft by axial limit structure.In the time that driving disc produces axial displacement, there is not axial float in bottom gear driving gear, moving from the forward and reverse rubbing contact of mantle dish and the state of oppositely throwing off and in process to guarantee in initiative taper dribbling, bottom gear driving gear does not slide, reduce reactive loss, improve transmission efficiency.Equally, the lead angle of the second helical spline should be greater than Self-locking angle corresponding to the two relative wiping coefficient of bottom gear driving gear and initiative taper dish, belongs to those skilled in the art's basic general knowledge.
Preferably, described torque transfer arrangement is end cam auxiliary structure, comprise and be fixedly connected on driving shaft epirelief wheel set driving link, be fixedly connected with or be integrally formed in friction limit and turn round the cam sub-quilt moving part on clutch initiative taper dish, on end face one of in the driving link of this cam pair and Passive part, be formed with V-shaped groove camming surface, on another part, be formed with and the end face projection that stretches into this V-shaped groove camming surface sunk part.Between the driving link of cam pair and Passive part, form higher pair, in load torque change procedure, in the time that load torque reaches certain setting value, between driving link and Passive part, form axial mutual movement and radial misalignments, to guarantee initiative taper disk detachment mantle dish; In the time that load torque reaches larger setting value, the axis shift between driving link and Passive part forms and skids apart from making the two depart from moment of torsion transmit mode, can realize the object of load-limiting, eliminates the potential safety hazard that overload of vehicle travels.
Further preferred, on the end face in opposite directions of the secondary driving link of described cam and cam sub-quilt moving part, be equipped with V-shaped groove camming surface, the end face projection of the driving link of cam pair and Passive part and corresponding V-shaped groove be recessed to form complementation and inclined-plane, the both sides symmetry of V-shaped groove.Guarantee forward and reverse load-limiting, further guarantee vehicle driving safety.
Preferably, the loading spring that described friction limit is turned round clutch is connected with described initiative taper dish by end face bearing.While reducing gearshift, initiative taper dish, with respect to the surface friction drag of driving shaft rotation, improves gearshift agility, meanwhile, reduces reactive loss, improves transmission efficiency.
Preferably, described double rolling key clutch comprises out star wheel, star-wheel and multiple circumference uniform distribution roller, roller is between the convex wheel face and the external cylindrical surface of star-wheel of out star wheel, on roller, be connected with for making its first elastic element away from star-wheel external cylindrical surface, between two adjacent rollers, be provided with pusher dog, multiple pusher dogs are formed on same driver plate, this driver plate forms coaxial rotation with described star-wheel and is connected, on driver plate, be connected with elastic resistance members, this elastic resistance members is for applying a drag torque to driver plate; Described out star wheel is made up of the bottom gear driven gear that is provided with convex wheel face; Described star-wheel forms one or is fixedly connected with described driven shaft by spline fitted structure with driven shaft.By out star wheel and bottom gear driven gear are formed to one, to guarantee simple in structurely, bottom gear driven gear drives the forward and reverse spinfunction of driven shaft reliable.
Further preferred, described elastic resistance members comprises two swing links that arrange in opposite directions that are positioned at outside, driver plate one end, between swing link and driver plate, be formed with the linkage structure that convex-concave coordinates, swing link is slidably connected with the linkage structure that driver plate coordinates by this convex-concave, two swing links connect by two extension springs and embrace and are clipped on described driven shaft or on the axle journal of support, this support is fixedly connected on casing, and the through hole empty set that support is provided with by axle journal is on described driven shaft.Guarantee that the drag torque that two swing links apply to driver plate is reliable, this drag torque makes driver plate at bottom gear driven gear rotating speed during a little more than driven shaft, make driver plate form relative pause, to change the circumferential position between the convex wheel face on roller and bottom gear driven gear, thereby make roller and bottom gear driven gear and star-wheel form frictional connection, realize this double rolling key clutch in conjunction with quick, reach driven shaft with the synchronous object of rotating of bottom gear driven gear.
Further preferred, described roller periphery middle part is provided with annular groove; Described the first elastic element is C shape ring, and this C shape ring is connected with described roller by the annular groove of described roller, and roller is positioned at C shape ring outside.Utilize the open annular elastic structure of C shape, make roller keep departing from the trend of double rolling key clutch star-wheel.
Further preferred, described mono-directional overrun clutch comprises unidirectional out star wheel, unidirectional star-wheel, voussoir and Returnning spring, unidirectional out star wheel is made up of top gear driven gear, top gear driven gear is provided with convex wheel face, and unidirectional star-wheel forms one or is fixedly connected with by spline structure with driven shaft; Described voussoir is provided with two, and two wedge slides are engaged in the cross through hole that described unidirectional star-wheel is provided with, and this cross through hole runs through described driven shaft, between two voussoirs, is connected with Compress Spring.So that voussoir has enough large physical dimension, guarantee transmitting torque and working life.
Invention thought based on identical, the present invention also provides a kind of automatic speed changing axle, and the top gear reactive torque output of this variable-speed shaft is greater than positive torque output.
A kind of automatic speed changing axle, comprise the bottom gear driving gear and the top gear driving gear that are located on driving shaft, described top gear driving gear empty set is on described driving shaft, between top gear driving gear and driving shaft, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring that friction limit is turned round clutch is sleeved on driving shaft, and turn round between the initiative taper dish tail end of clutch in the shaft shoulder and the friction limit of driving shaft, between initiative taper dish and described driving shaft, be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish of clutch in driving shaft forward and friction limit, initiative taper dish forms and moving axially of throwing off from mantle dish, should form one from mantle dish and described top gear driving gear, the afterbody of described bottom gear driving gear and described initiative taper dish forms the second helical spline cooperating structure, bottom gear driving gear is contained on described initiative taper dish by this second helical spline structure engage sleeves, and the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure, bottom gear driving gear is limited in the axial desired location of described driving shaft by axial limit structure, axial limit structure, in the time that initiative taper dish produces axial displacement, prevents the axial play of bottom gear driving gear.
Adopt the automatic speed changing axle of this programme, when the moment of torsion that acts on driven disc in load is less than setting value, high low speed is worked as driving gear and is synchronously rotated, when the moment of torsion that acts on driven disc in load is more than or equal to setting value, the driving disc of clutch and driven disc form and relatively rotate, and make driving disc there is the trend of throwing off driven disc, the axial limit structure of shape between bottom gear driving gear and initiative taper dish and between bottom gear driving gear and described driving shaft, make bottom gear driving gear in axial state of rest, and play not.During for transmission device, have at driven shaft under the configuration scenario adapting, can realize two-gear automatic speed changing.Meanwhile, in the time that driving shaft reverses, the first helical spline makes initiative taper dish have the trend moving to driven disc, thereby improves the reactive torque output of driven disc.
This automatic speed changing axle also has another technological scheme.
A kind of automatic speed changing axle, comprise the bottom gear driving gear and the top gear driving gear that are located on driving shaft, described top gear driving gear empty set is on described driving shaft, between top gear driving gear and driving shaft, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring that friction limit is turned round clutch is sleeved on driving shaft, and turn round between the initiative taper dish tail end of clutch in the shaft shoulder and the friction limit of driving shaft, between initiative taper dish and described driving shaft, be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish of clutch in driving shaft forward and friction limit, initiative taper dish forms and moving axially of throwing off from mantle dish, should form one from mantle dish and described top gear driving gear, described bottom gear driving gear is integrally formed in described initiative taper dish tail end.
Adopt the automatic speed changing axle of this programme, when the moment of torsion that acts on driven disc in load is less than setting value, high low speed is worked as driving gear and is synchronously rotated, when the moment of torsion that acts on driven disc in load is more than or equal to setting value, the driving disc of clutch and driven disc form and relatively rotate, and making driving disc there is the trend of throwing off driven disc, bottom gear driving gear and initiative taper dish type are integral, make variable-speed shaft structure seem very compact.Meanwhile, in the time that driving shaft reverses, the first helical spline makes initiative taper dish have the trend moving to driven disc, thereby improves the reactive torque output of driven disc.
The present invention's beneficial effect is compared with prior art that two gear automatic gear shifting speed changings of speed change gear forward transmission, also have reversing drive function, during for electric motor car, can realize self shifter and car-backing function and the limit for tonnage function of advancing; The top gear reactive torque output of variable-speed shaft is greater than positive torque output; It is simple in structure, and gearshift is quick, low cost of manufacture.
Brief description of the drawings
Fig. 1 is the structural representation of the embodiment of the present invention 1.
Fig. 2 is the structural representation axonometric drawing of double rolling key clutch in the present invention.
Fig. 3 is the cross-sectional configuration schematic diagram of double rolling key clutch in the present invention.
Fig. 4 is the decomposition texture signal axonometric drawing of double rolling key clutch in the present invention.
Fig. 5 is the structural representation of mono-directional overrun clutch in the present invention.
Fig. 6 is provided with friction limit to turn round the structural representations such as clutch on driving shaft 1 in the embodiment of the present invention 2.
Fig. 7 is the torque transfer arrangement structural representation of the end cam auxiliary structure that arranges between bottom gear driving gear 3 in the embodiment of the present invention 2 and driving shaft 1.
Fig. 8 is provided with friction limit to turn round the structural representations such as clutch on driving shaft 1 in the embodiment of the present invention 3.
Fig. 9 is provided with friction limit to turn round the structural representations such as clutch on driving shaft 1 in the embodiment of the present invention 4.
Figure 10 is the structural representation of the embodiment of the present invention 5.
Figure 11 is the structural representation of the embodiment of the present invention 6.
Embodiment
Below in conjunction with accompanying drawing, the present invention is further illustrated, but therefore do not limit the present invention among described scope of embodiments.
Embodiment 1 is referring to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, a kind of containing the limited automatic transimission of turning round clutch, comprise driving shaft 1 and driven shaft 2, on driving shaft 1 and driven shaft 2, be respectively equipped with top gear gear mesh and the bottom gear gear mesh of corresponding normal engagement, the top gear driving gear 4 of described top gear gear mesh is rotatably connected on described driving shaft 1, between top gear driving gear 4 and driving shaft 1, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring 63 that friction limit is turned round clutch is connected to an axle journal end face of driving shaft 1 and rubs to limit and turn round between an end face of initiative taper dish 61 of clutch, between this initiative taper dish 61 and loading spring 63, be provided with end face bearing 64, between initiative taper dish 61 and described driving shaft 1, be also provided with for powerdriven torque transfer arrangement, this torque transfer arrangement is the first helical spline cooperating structure, this torque transfer arrangement is in the time that the load torque of driving shaft 1 forward and driven shaft 2 reaches setting value, and initiative taper dish 61 forms and moving axially of throwing off from mantle dish 62, between described bottom gear driving gear 3 and described initiative taper dish 61, be formed with the two and can synchronize the linkage structure of rotating, this linkage structure that can synchronously rotate is the second helical spline cooperating structure forming between bottom gear driving gear 3 and initiative taper dish 61, bottom gear driving gear 3 is contained on described initiative taper dish 61 by this second helical spline structure engage sleeves, the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure, and the lead angle of two helical splines is greater than corresponding Self-locking angle, between bottom gear driving gear 3 and initiative taper dish 61, be formed with axial limit structure for limiting the two close distance mutually, this axial limit structure comprises the step surface 61a that is located at the second helical spline afterbody, and this step surface 61a is for holding the corresponding end-faces at bottom gear driving gear 3, what friction limit was turned round clutch forms one from mantle dish 62 and top gear driving gear 4, described top gear driven gear 8 is connected on driven shaft 2 by the first mono-directional overrun clutch, and this first mono-directional overrun clutch drives described driven shaft 2 forwards synchronously to rotate for top gear driven gear 8, this first mono-directional overrun clutch comprises unidirectional out star wheel, unidirectional star-wheel 91, voussoir 92 and Returnning spring 93, unidirectional out star wheel is made up of top gear driven gear 8, top gear driven gear 8 is provided with convex wheel face, and unidirectional star-wheel 91 is fixedly connected with by spline structure with driven shaft 2, described voussoir 92 is provided with two, and two voussoirs 92 are slidably fitted in the cross through hole that described unidirectional star-wheel 91 is provided with, and this through hole also runs through between 2, two voussoirs 92 of described driven shaft and is connected with Compress Spring 93, described bottom gear driving gear 3 is limited in the axial desired location of described driving shaft 1 by another axial limit structure, this axial limit structure comprises and on driving shaft 1, is coaxially fixedly connected with power input gear 12, driving shaft 1 forms the axial limiting of described bottom gear driving gear 3 away from the end face from mantle dish 62 by this power input gear 12, bottom gear driving gear 3 is near being provided with stop collar 64 from the end face of mantle dish 62 and between mantle dish 62, and this stop collar 64 forms close spacing from mantle dish 62 end faces of bottom gear driving gear 3, described driven shaft 2 is provided with output gear 21, between the bottom gear driven gear 5 of described bottom gear gear mesh and driven shaft 2, be provided with the second double rolling key clutch, this second double rolling key clutch drives the forward and reverse synchronous rotation of driven shaft 2 for bottom gear driven gear 5, this second double rolling key clutch comprises out star wheel, star-wheel 71 and multiple circumference uniform distribution roller 72, roller 72 is between the convex wheel face of out star wheel and the external cylindrical surface of star-wheel 71, roller 72 periphery middle parts are provided with annular groove, on roller 72, be connected with for making its first elastic element 73 away from star-wheel 71 external cylindrical surfaces, this first elastic element 73 is C shape ring, this C shape ring is connected with described roller 72 by the annular groove of described roller 72, and roller 72 is positioned at C shape ring outside, between two adjacent rollers 72, be provided with pusher dog, multiple pusher dogs are formed on same driver plate 74, this driver plate 74 forms coaxial rotation with described star-wheel 71 and is connected, on driver plate 74, be connected with elastic resistance members, this elastic resistance members comprises two swing links 75 that arrange in opposite directions that are positioned at driver plate 74 outsides, one end, between swing link 75 and driver plate 74, be formed with the linkage structure that convex-concave coordinates, swing link 75 is slidably connected with the linkage structure that driver plate 74 coordinates by this convex-concave, two swing links 75 connect by two extension springs 76 and embrace on the axle journal that is clipped in support 77, this support 77 is fixedly connected on casing 78, and the through hole empty set that support 77 is provided with by axle journal is on described driven shaft 2, this elastic resistance members applies a drag torque by two swing links 75 and the surface friction drag that support 77 axle journals form to driver plate 74, described out star wheel is made up of the bottom gear driven gear 5 that is provided with convex wheel face, described star-wheel 71 is fixedly connected with described driven shaft 2 by spline fitted structure with driven shaft 2.
In the present embodiment, unidirectional star-wheel 91 can form with driven shaft 2 scheme that one is fixedly connected with by spline structure in order to replace the two, can reduce the number of components, strengthens driving shaft 1 intensity.
In the present embodiment, when driving shaft 1 and motor shaft are coaxial be connected or motor shaft on driving gear while engaging with the power input gear 12 on driving shaft 1, form the power-shift gear box of electric motor car, it has the two-gear automatic speed changing and the low-speed heave-load car-backing function that advance, and the wheel function of advancing.
In the present embodiment, when described top gear driven gear 8 is coaxially fixedly connected on driven shaft 2 or while being coaxially connected on driven shaft 2 by the first double rolling key clutch, electric motor car has quick car-backing function, and without low-speed heave-load car-backing function, when heavy duty reversing, there will be heavy duty to skid; Top gear driven gear 8 is coaxially fixedly connected with driven shaft 2, and vehicle is without wheel function.Top gear driven gear 8 is coaxially connected on driven shaft 2 by the first double rolling key clutch, and vehicle has the wheel function moving forward and backward.
Driven shaft 2 in the present embodiment can be used as output shaft and is connected with load, the mode that also can adopt output gear 21 to be connected with load, and its structural type is various.
In the present embodiment, the star-wheel 71 that the first mono-directional overrun clutch arranging between described top gear driven gear 8 and driven shaft 2 connects can be integrally formed on driven shaft 2, further to guarantee the intensity of this mono-directional overrun clutch.
In the present embodiment, two swing links 75 of described the second double rolling key clutch also can be embraced and be clipped on described driven shaft 2 to replace the scheme of clasping on support 77.
In the present embodiment, referring to Figure 11, the scheme that also can adopt bottom gear driving gear 3 that Compress Spring 65 is set between the end face from mantle dish 62 and the step end face 61a of initiative taper dish 61 front ends replaces bottom gear driving gear 3 at the end face from mantle dish 62 and from being provided with the scheme of stop collar 64 between mantle dish 62.
In the present embodiment, the male cone (strobilus masculinus) that described friction limit is turned round clutch is located on initiative taper dish 61, and its inner conical surface is located at from mantle dish 62; Its loading spring 63 is dish spring, also can adopt cylindrical compression spring.
Embodiment's aforementioned automatic transimission is applicable to three-wheel or four-wheel electric motor car, and it has the two-gear automatic speed changing of advancing and car-backing function.
In the present embodiment, between bottom gear driven gear 5 and driven shaft 2, can adopt the scheme of the second mono-directional overrun clutch to replace the second two-way scheme to free wheel device.This gearbox is applicable to electric motor car with two wheels, and it has the two-gear automatic speed changing advancing.
Embodiment 2 is referring to Fig. 6, Fig. 7, and described bottom gear driving gear 3 forms as one with described initiative taper dish 61; Described end face bearing 64 is connected between loading spring 63 and bottom gear driving gear 3; Between described initiative taper dish 61 and described driving shaft 1, be provided with for powerdriven torque transfer arrangement, this torque transfer arrangement is end cam auxiliary structure, comprise and be fixedly connected on driving shaft 1 epirelief wheel set driving link 11, be integrally formed in friction limit and turn round the cam sub-quilt moving part 41 on clutch initiative taper dish 61, on the end face in opposite directions of the secondary driving link 11 of this cam and cam sub-quilt moving part 41, be equipped with V-shaped groove camming surface, the driving link 11 of cam pair and the end face projection of Passive part 41 and corresponding V-shaped groove be recessed to form complementation and inclined-plane, the both sides symmetry of V-shaped groove.This torque transfer arrangement is in driving shaft 1 clockwise and anticlockwise, and the load torque of driven shaft 2 is while reaching a setting value, and initiative taper dish 61 forms and moving axially of throwing off from mantle dish 62; In the time that load torque reaches another larger setting value, the secondary driving link 11 of cam forms skidding of relative idle running with cam sub-quilt moving part 41, during for vehicle, can limit the limit load of vehicle.
All the other structures of the present embodiment are identical with embodiment 1, do not repeat them here.
In the present embodiment, also the end face of secondary cam driving link 11 or cam sub-quilt moving part 41 can be arranged to have the camming surface of V-shaped groove, on corresponding another part, horizontal straight pin be set, form higher pair without illustrating by the camming surface of this straight pin and V-shaped groove.
Embodiment 3 is referring to Fig. 8, and described bottom gear driving gear 3 is coaxially fixedly connected on driving shaft 1; Described power input gear 12 is fixedly connected with the initiative taper dish 61 that described friction limit is turned round clutch; The torque transfer arrangement of the helical spline cooperating structure being also provided with between initiative taper dish 61 and described driving shaft 1 is located between power input gear 12 and driving shaft 1; Described loading spring 63 is connected between initiative taper dish 61 and the shaft shoulder of driving shaft 1.
All the other structures of the present embodiment are identical with embodiment 1, do not repeat them here.
Embodiment 4 is referring to Fig. 9, and described bottom gear driving gear 3 forms as one with described initiative taper dish 61; Described end face bearing 64 is connected between loading spring 63 and bottom gear driving gear 3; Between described initiative taper dish 61 and described driving shaft 1, be provided with the torque transfer arrangement of helical spline cooperating structure; Described power input gear 12 is positioned at top gear driving gear 4 outsides; Described loading spring 63 is connected between bottom gear driving gear 3 and the shaft shoulder of driving shaft 1.
All the other structures of the present embodiment are identical with embodiment 3, do not repeat them here.
Embodiment 5 is referring to Figure 10, a kind of automatic speed changing axle, comprise the bottom gear driving gear 3 being located on driving shaft 1, top gear driving gear 4 and power input gear 12, it is characterized in that, described top gear driving gear 4 empty sets are on described driving shaft 1, between top gear driving gear 4 and driving shaft 1, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring 63 that friction limit is turned round clutch is sleeved on driving shaft 1, and turn round between initiative taper dish 61 tail ends of clutch in the shaft shoulder and the friction limit of driving shaft 1, between initiative taper dish 61 and described driving shaft 1, be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish 62 of clutch in driving shaft 1 forward and friction limit, initiative taper dish 61 forms and moving axially of throwing off from mantle dish 62, should form one from mantle dish 62 and described top gear driving gear 4, described bottom gear driving gear 3 is integrally formed in described initiative taper dish 61 tail ends.Described power input gear 12 is fixedly connected on driving shaft 1 and is positioned at bottom gear driving gear 3 outsides.
Embodiment 6 is referring to Figure 11, a kind of automatic speed changing axle, comprise the bottom gear driving gear 3 and the top gear driving gear 4 that are located on driving shaft 1, described top gear driving gear 4 empty sets are on described driving shaft 1, between top gear driving gear 4 and driving shaft 1, be provided with normally closed cone dish friction limit and turn round clutch, the loading spring 63 that friction limit is turned round clutch is sleeved on driving shaft 1, and turn round between initiative taper dish 61 tail ends of clutch in the shaft shoulder and the friction limit of driving shaft 1, between initiative taper dish 61 and described driving shaft 1, be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish 62 of clutch in driving shaft 1 forward and friction limit, initiative taper dish 61 forms and moving axially of throwing off from mantle dish 62, should form one from mantle dish 62 and described top gear driving gear 4, described bottom gear driving gear 3 forms the second helical spline cooperating structure with the afterbody of described initiative taper dish 61, bottom gear driving gear 3 is contained on described initiative taper dish 61 by this second helical spline structure engage sleeves, and the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure, between bottom gear driving gear 3 and initiative taper dish 61, be formed with and limit the two mutually by in-plant axial limit structure, this axial limit structure comprises the step surface 61a that is located at the second helical spline afterbody, and this step surface 61a is for conflicting at the corresponding end-faces of bottom gear driving gear 3, bottom gear driving gear 3 is limited in the axial desired location of described driving shaft 1 by another axial limit structure, this axial limit structure comprises the power input gear 12 being coaxially fixedly connected with on driving shaft 1, and driving shaft 1 forms the axial limiting of described bottom gear driving gear 3 away from the end face from mantle dish 62 sides by this power input gear 12, bottom gear driving gear 3 is near be provided with Compress Spring 65 between the end face of mantle dish 62 sides and the step end face 61a of initiative taper dish 61 front ends.
In the present embodiment, also can adopt bottom gear driving gear 3 to replace bottom gear driving gear 3 near be provided with Compress Spring 65 between the end face of mantle dish 62 sides and the step end face 61a of initiative taper dish 61 front ends at the end face from mantle dish 62 and from being provided with the scheme of stop collar 64 between mantle dish 62.
Although described by reference to the accompanying drawings above embodiments of the present invention, but those of ordinary skill in the art also can recognize making various variations or amendment in the scope of claims, as the wedge shape working surface of the push rod in the present invention is made to the mode that ecto-entad increases gradually, depart from by pulling push rod to realize clutch the object that surmounts state, the interior edge face bottom of corresponding push rod can arrange extension spring etc.These modifications and variations are interpreted as within scope of the present invention and intention.
Claims (12)
1. one kind contains the limited automatic transimission of turning round clutch, comprise driving shaft (1) and driven shaft (2), on driving shaft (1) and driven shaft (2), be respectively equipped with top gear gear mesh and the bottom gear gear mesh of corresponding normal engagement, it is characterized in that, the top gear driving gear (4) of described top gear gear mesh is rotatably connected on described driving shaft (1), between top gear driving gear (4) and driving shaft (1), be provided with normally closed cone dish friction limit and turn round clutch, the loading spring (63) that friction limit is turned round clutch is connected to driving shaft (1) and rubs to limit and turn round between the initiative taper dish (61) of clutch, between initiative taper dish (61) and described driving shaft (1), be also provided with for powerdriven torque transfer arrangement, this torque transfer arrangement is at least in the time that the load torque of driving shaft (1) forward and driven shaft (2) reaches setting value, initiative taper dish (61) forms and moving axially of throwing off from mantle dish (62), friction limit is turned round forming one or be coaxially fixedly connected with top gear driving gear (4) from mantle dish (62) of clutch, between the bottom gear driving gear (3) of described bottom gear gear mesh and described initiative taper dish (61), be formed with the two and can synchronize the linkage structure of rotating, or bottom gear driving gear (3) is coaxially fixedly connected on driving shaft (1), described top gear driven gear (8) is coaxially connected on driven shaft (2) by the first mono-directional overrun clutch or the first double rolling key clutch, or top gear driven gear (8) is coaxially fixedly connected on driven shaft (2), this first mono-directional overrun clutch drives described driven shaft (2) forward synchronously to rotate for top gear driven gear (8), and this first double rolling key clutch drives the forward and reverse synchronous rotation of described driven shaft (2) for top gear driven gear (8), between the bottom gear driven gear (5) of described bottom gear gear mesh and driven shaft (2), be provided with the second double rolling key clutch or the second overrunning clutch, this second double rolling key clutch drives the forward and reverse synchronous rotation of driven shaft (2) for bottom gear driven gear (5), this second overrunning clutch drives driven shaft (2) forward synchronously to rotate for bottom gear driven gear (5).
2. according to claim 1 containing the limited automatic transimission of turning round clutch, it is characterized in that, described torque transfer arrangement is for being located at the helical spline cooperating structure between driving shaft and initiative taper dish (61), this helical spline cooperating structure is in the time that the load torque of driving shaft (1) forward and driven shaft (2) reaches setting value, and the initiative taper dish (61) that friction limit is turned round clutch forms and moving axially of throwing off from mantle dish (62) by this torque transfer arrangement.
3. according to claim 2 containing the limited automatic transimission of turning round clutch, it is characterized in that, it is the second helical spline cooperating structure forming between the two that the two formation between described bottom gear driving gear (3) and described initiative taper dish (61) can be synchronizeed the linkage structure of rotating, it is upper that bottom gear driving gear (3) is contained in described initiative taper dish (61) by this second helical spline structure engage sleeves, and the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure; Bottom gear driving gear (3) is limited in the axial desired location of described driving shaft (1) by axial limit structure.
4. according to claim 1 containing the limited automatic transimission of turning round clutch, it is characterized in that, described torque transfer arrangement is end cam auxiliary structure, comprise and be fixedly connected on driving shaft (1) epirelief wheel set driving link (11), be fixedly connected with or be integrally formed in friction limit and turn round the cam sub-quilt moving part (41) on clutch initiative taper dish (61), on end face, be formed with V-shaped groove camming surface one of in the driving link (11) of this cam pair and Passive part (41), on another part, be formed with and the end face projection that stretches into this V-shaped groove camming surface sunk part.
5. according to claim 4 containing the limited automatic transimission of turning round clutch, it is characterized in that, on the end face in opposite directions of the secondary driving link of described cam (11) and cam sub-quilt moving part (41), be equipped with V-shaped groove camming surface, the driving link (11) of cam pair and the end face projection of Passive part (41) and corresponding V-shaped groove be recessed to form complementation and inclined-plane, the both sides symmetry of V-shaped groove.
6. according to the limited automatic transimission of turning round clutch that contains described in any one claim in claim 1～5, it is characterized in that, the loading spring (63) that described friction limit is turned round clutch is connected with described initiative taper dish (61) by end face bearing (64).
7. according to the limited automatic transimission of turning round clutch that contains described in any one claim in claim 1～5, it is characterized in that, described double rolling key clutch comprises out star wheel, star-wheel (71) and multiple circumference uniform distribution roller (72), roller (72) is positioned between the convex wheel face of out star wheel and the external cylindrical surface of star-wheel (71), on roller (72), be connected with for making its first elastic element (73) away from star-wheel (71) external cylindrical surface, between two adjacent rollers (72), be provided with pusher dog, multiple pusher dogs are formed on same driver plate (74), this driver plate (74) forms coaxial rotation with described star-wheel (71) and is connected, driver plate is connected with elastic resistance members on (74), this elastic resistance members is for applying a drag torque to driver plate (74), described out star wheel is made up of the bottom gear driven gear (5) that is provided with convex wheel face, described star-wheel (71) forms one or is fixedly connected with described driven shaft (2) by spline fitted structure with driven shaft (2).
8. according to claim 7 containing the limited automatic transimission of turning round clutch, it is characterized in that, described elastic resistance members comprises two swing links (75) that arrange in opposite directions that are positioned at driver plate (74) outside, one end, between swing link (75) and driver plate (74), be formed with the linkage structure that convex-concave coordinates, swing link (75) is slidably connected with the linkage structure that driver plate (74) coordinates by this convex-concave, two swing links (75) connect by two extension springs (76) and embrace on the axle journal that is clipped in the upper or support (77) of described driven shaft (2), this support (77) is fixedly connected on casing (78), and the through hole empty set that support (77) is provided with by axle journal is on described driven shaft (2).
9. according to claim 7 containing the limited automatic transimission of turning round clutch, it is characterized in that, described roller (72) periphery middle part is provided with annular groove; Described the first elastic element (73) is C shape ring, and this C shape ring is connected with described roller (72) by the annular groove of described roller (72), and roller (72) is positioned at C shape ring outside.
10. according to the limited automatic transimission of turning round clutch that contains described in any one claim in claim 1～5, it is characterized in that, described mono-directional overrun clutch comprises unidirectional out star wheel, unidirectional star-wheel (91), voussoir (92) and Returnning spring (93), unidirectional out star wheel is made up of top gear driven gear (8), top gear driven gear (8) is provided with convex wheel face, and unidirectional star-wheel (91) forms one or is fixedly connected with by spline structure with driven shaft (2); Described voussoir (92) is provided with two, two voussoirs (92) are slidably fitted in the cross through hole that described unidirectional star-wheel (91) is provided with, this through hole also runs through described driven shaft (2), is connected with Compress Spring (93) between two voussoirs (92).
11. 1 kinds of automatic speed changing axles, comprise the bottom gear driving gear (3) and the top gear driving gear (4) that are located on driving shaft (1), it is characterized in that, described top gear driving gear (4) empty set is on described driving shaft (1), between top gear driving gear (4) and driving shaft (1), be provided with normally closed cone dish friction limit and turn round clutch, the loading spring (63) that friction limit is turned round clutch is sleeved on driving shaft (1), and the shaft shoulder and the friction limit that are positioned at driving shaft (1) are turned round between initiative taper dish (61) tail end of clutch, between initiative taper dish (61) and described driving shaft (1), be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish (62) of clutch in driving shaft (1) forward and friction limit, initiative taper dish (61) forms and moving axially of throwing off from mantle dish (62), should form one from mantle dish (62) and described top gear driving gear (4), described bottom gear driving gear (3) forms the second helical spline cooperating structure with the afterbody of described initiative taper dish (61), it is upper that bottom gear driving gear (3) is contained in described initiative taper dish (61) by this second helical spline structure engage sleeves, and the helical spline of this second helical spline structure has identical helical pitch and rotation direction with the helical spline of the first helical spline structure, bottom gear driving gear (3) is limited in the axial desired location of described driving shaft (1) by axial limit structure.
12. 1 kinds of automatic speed changing axles, comprise the bottom gear driving gear (3) and the top gear driving gear (4) that are located on driving shaft (1), it is characterized in that, described top gear driving gear (4) empty set is on described driving shaft (1), between top gear driving gear (4) and driving shaft (1), be provided with normally closed cone dish friction limit and turn round clutch, the loading spring (63) that friction limit is turned round clutch is sleeved on driving shaft (1), and the shaft shoulder and the friction limit that are positioned at driving shaft (1) are turned round between initiative taper dish (61) tail end of clutch, between initiative taper dish (61) and described driving shaft (1), be provided with the torque transfer arrangement of the first helical spline, when this torque transfer arrangement reaches setting value for turn round the load torque from mantle dish (62) of clutch in driving shaft (1) forward and friction limit, initiative taper dish (61) forms and moving axially of throwing off from mantle dish (62), should form one from mantle dish (62) and described top gear driving gear (4), described bottom gear driving gear (3) is integrally formed in described initiative taper dish (61) tail end.
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| CN201410238462.7A CN103982602B (en) | 2014-05-30 | 2014-05-30 | A kind of containing limited automatic transimission and the variable-speed shaft turning round clutch |
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| CN201410238462.7A CN103982602B (en) | 2014-05-30 | 2014-05-30 | A kind of containing limited automatic transimission and the variable-speed shaft turning round clutch |
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| CN103982602B CN103982602B (en) | 2016-04-20 |
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| CN110017370A (en) * | 2019-04-18 | 2019-07-16 | 西南大学 | The mechanical double overdrive clutch self-adapting automatic gear shift main shaft assembly of planetary system output |
| CN110017370B (en) * | 2019-04-18 | 2020-12-04 | 西南大学 | Mechanical double-overrunning clutch self-adaptive automatic speed change main shaft assembly for planetary system output |
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| CN111322391B (en) * | 2019-11-29 | 2021-09-14 | 福建中维动力科技股份有限公司 | Speed change control system of off-axis two-gear transmission |
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