CN103982602B - A kind of containing limited automatic transimission and the variable-speed shaft turning round clutch - Google Patents
A kind of containing limited automatic transimission and the variable-speed shaft turning round clutch Download PDFInfo
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- CN103982602B CN103982602B CN201410238462.7A CN201410238462A CN103982602B CN 103982602 B CN103982602 B CN 103982602B CN 201410238462 A CN201410238462 A CN 201410238462A CN 103982602 B CN103982602 B CN 103982602B
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- driving shaft
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- 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
Abstract
The invention discloses a kind of containing limited automatic transimission and the variable-speed shaft turning round clutch, speed change gear comprises high low-speed active gear and the driven gear of corresponding normal engagement on difference driving shaft and driven shaft, driving shaft is provided with normally closed limit and turns round clutch, and this clutch is used for top gear driving gear and is connected with the power between driving shaft; Bottom gear driving gear and driving shaft are formed can the linkage structure of synchronous axial system; Top gear and be respectively equipped with unidirectional or double rolling key clutch between bottom gear driven gear and driven shaft.Variable-speed shaft comprises driving shaft and is located at top gear driving gear, the bottom gear driving gear on driving shaft, and turn round clutch for the normally closed limit of the transmission of power between top gear gear and driving shaft, the drive end of clutch is connected with driving shaft by helical spline structure.The invention has the beneficial effects as follows, speed change gear can realize two gear self shifter and reversing drive functions of forward transmission, and its structure is simple, and gearshift is quick; The high-speed reverse output torque of variable-speed shaft is greater than forward output torque.
Description
Technical field
The present invention relates to a kind of speed change gear for electric motor car transmission case, particularly a kind of automatic transimission and the variable-speed shaft of turning round clutch containing limit for 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 its mode mainly controlling motor speed by controller realizes speed change.Along with the development of vehicle technology, some electric motor cars at present are also configured with the gear gearbox of mechanical structure, it provides speed change to perform power mainly through electromagnet etc., and drive executive component to realize shift speed change by electromagnet, shift speed change is usually by the human users that rides.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, when 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 also develops the automatic transmission for electric motor car, be all the shift speed change realized by rotation speed change usually.This is control motor speed by rotating speed control one, two is that load increases and decreases the rotating speed caused and changes, it is initiatively that power increases and decreases the rotation speed change caused, but initiatively increase and decrease the change that rotating speed obviously directly causes energy consumption, its time point initiatively increased and decreased is controlled by driver, obviously partial power can be caused 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 is delayed on time point.
In automatic gear shifting speed changing system or device, conventional mono-directional overrun clutch turns round clutch etc. also known as one-way element, double rolling key clutch, controllable overrunning clutch and friction type limit.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.Be provided with control unit in controllable overrunning clutch, be separated by the frictional engagement element of control elements solenoidoperated cluthes the combination and the disengagement that realize clutch with the mode combined with principal and subordinate's moving part.Realize shift speed change by the control panel of magnet control controllable overrunning clutch in the mechanical variable speed device of existing electric motor car to control.Limit turns round clutch also known as safety clutch, and it refers to that load torque is when restriction is enclosed interior, and the initiative taper dribbling of clutch is dynamic from mantle dish synchronous axial system; When load torque meets or exceeds limit value, initiative taper dish relatively rotates with being formed from mantle dish.The structural type that limit turns round clutch is more, and longer is friction clutch structure.The limit of friction clutch structure turns round clutch, and when load torque meets or exceeds limit limit value, initiative taper dish can not drive from mantle dish synchronous axial system, but initiative taper dish still contacts with the rubbing surface from mantle dish and forms fretting wear in relative rotation.Therefore, need a kind of at this moment by the structure that initiative taper dish is separated with from mantle dish, to make initiative taper dish and to be separated from each other from mantle dish.
In prior art, although also occurred that some turn round clutch by limit and overrunning clutch realizes self-shifting speed change gear, usually all there is complex structure, the deficiency that manufacture cost is high; Reverse output can't be realized in addition.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 provide a kind of and have the speed change gear rotating forward two-gear automatic speed changing and reversion output, this device, when driving shaft rotates forward, realizes shift speed change automatically according to load torque size variation; It is skillfully constructed, and structure is simple and various informative.
For achieving the above object, the present invention adopts following technological scheme.
A kind of containing the limited automatic transimission turning round clutch, comprise driving shaft and driven shaft, driving shaft and driven shaft are 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, be provided with the normally closed cone dish limit that rubs between top gear driving gear and driving shaft and turn round clutch, the loading spring that friction limit turns round clutch be connected to driving shaft and friction limit turn round clutch initiative taper dish between, also be provided with between initiative taper dish and described driving shaft for powerdriven torque transfer arrangement, this torque transfer arrangement is used at least when driving shaft rotates forward and the load torque of driven shaft reaches setting value, initiative taper dish is formed and moving axially of throwing off from mantle dish, friction limit turns round forming one from mantle dish and top gear driving gear or being coaxially fixedly connected with of clutch, being formed with the two between the bottom gear driving gear of described bottom gear gear mesh and described initiative taper dish can the linkage structure of synchronous axial system, 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 is used for top gear driven gear and drives described driven shaft forward synchronous axial system, and this first double rolling key clutch is used for top gear driven gear and drives the forward and reverse synchronous axial system of described driven shaft, the second double rolling key clutch or the second overrunning clutch is provided with between the bottom gear driven gear of described bottom gear gear mesh and driven shaft, this second double rolling key clutch is used for bottom gear driven gear and drives the forward and reverse synchronous axial system of driven shaft, or this second overrunning clutch is used for bottom gear driven gear and drives driven shaft forward synchronous axial system.
Adopt the present invention of preceding solution, be provided with in the scheme of the second double rolling key clutch between bottom gear driven gear and driven shaft, driving shaft rotates forward or counterrotating under motor drives.When driving shaft rotates 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, when loading moment is less than setting value, driving shaft is turned round clutch by friction limit and is driven top gear gear mesh to rotate forward by top gear, 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 rotate forward by top gear; Now, rotate forward although bottom gear driven gear rotates 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 by double rolling key clutch and driven shaft and surmounts; When loading moment meets or exceeds setting value, output speed declines, the friction limit initiative taper dish of turning round clutch relatively rotates with being formed 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 to move axially and away from driven disc with throwing off from mantle dish.When 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 by bottom gear gear mesh and the second double rolling key clutch and rotates forward by bottom gear, now, the unpowered output of top gear driving gear; The situation of the first mono-directional overrun clutch and the first double rolling key clutch is provided with between top gear driven gear and driven shaft, top gear driven gear declines to rotating speed under the surface friction drag effect of structure self and gradually lower than output speed, until stall, top gear driven gear is formed by the first mono-directional overrun clutch and the first double rolling key clutch and driven shaft and surmounts; The situation be coaxially fixedly connected with is formed at top gear driven gear and driven shaft, top gear driven gear and driven shaft synchronous axial system, now, top gear driven gear drives top gear driving gear to dally in the same way to be formed lower than the rotating speed of driving shaft and driving shaft, realizes by the automatic speed changing of top gear to bottom gear with this.Be in bottom gear running at driven shaft, load variations is to when being less than setting value, driving shaft is turned round clutch by friction limit and is driven top gear driving gear to rotate forward, driven shaft is directly driven by top gear driven gear, or, driven by the first mono-directional overrun clutch or the first double rolling key clutch and press top gear forward High Rotation Speed, 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 by double rolling key clutch and surmount.When driving shaft rotates forward as vehicle progression power input mode, this programme can be applicable to the two-gear automatic speed changing that vehicle advances easily, without the need to carrying out manual control, avoids the improper problem on opportunity of manual control speed change; And gearshift is changed by load and directly causes velocity variations, velocity variations is caused because load changes relative in prior art, the mode of being carried out speed change again by velocity variations is more direct, its speed change response time shortens, speed change is more quick, eliminates electric motor car burns out motor hidden danger because shifting gears not in time.When driving shaft counterrotating, top gear driving gear and driving shaft synchronous axial system, when top gear driven gear is fixedly connected with driven shaft or is 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 second double rolling key clutch are formed 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, when top gear driven gear is connected with driven shaft by the first double rolling key clutch, vehicle has reversing wheel function, when top gear driven gear and driven shaft pass through 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 by the first mono-directional overrun clutch and driven shaft and surmounts, 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 safety of moveing backward.The torque transfer arrangement arranged between initiative taper dish and driving shaft has driving shaft and reverses, and the load torque of driven shaft reaches setting value, the friction limit initiative taper dish of turning round clutch by this torque transfer arrangement formed with throw off from mantle dish move axially function.At initiative taper dish and after throwing off from mantle dish, bottom gear driving gear drives bottom gear driven gear synchronous backward to slowly run by the second twin-direction clutch, when top gear driven gear is fixedly connected with driven shaft or is connected with driven shaft by the first mono-directional overrun clutch, the counterrotating under driven shaft drives of top gear driven gear, or driven by mono-directional overrun clutch and reversely rotate at low speed, corresponding top gear driving gear rotates relative to dallying with driving shaft in the same way with the rotating speed lower than driving shaft, 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 by the first twin-direction clutch and driven shaft and surmounts, the electric motor car of this kind of situation has low-speed heave-load car-backing function.Therefore, when being provided with mono-directional overrun clutch between top gear driven gear and driven shaft, 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 quick car-backing function, guarantee to move backward safety; 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 during the second double rolling key clutch, electric motor car has the wheel function that moves ahead; On driven shaft and between high speed driven gear during the first single-direction and dual-direction clutch, on driven shaft and between low speed driven gear during the second double rolling key clutch, electric motor car has backward skating function.The program is applicable to tricycle or four-wheel wagon.
Be provided with in the scheme of the second mono-directional overrun clutch between bottom gear driven gear and driven shaft, top gear gear mesh is by the first mono-directional overrun clutch, the first double rolling key clutch or when directly driving driven shaft to rotate forward, and bottom gear driven gear is formed by the second overrunning clutch or the second double rolling key clutch and driven shaft and surmounts; When 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 advance wheel function, and without gear reversing function.The program 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 the linkage structure of synchronous axial system comprise, bottom gear driving gear is integral with initiative taper dish type or be coaxially fixedly connected with, or spline fitted structure is set between bottom gear driving gear and initiative taper dish, in spline fitted structure, comprise straight spline and helical spline, when adopting helical spline structure, therebetween also need to arrange axial limit structure, to guarantee when the two relatively rotates desired location, bottom gear driving gear and initiative taper dish form synchronous axial system.
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 as required in the frictional engagement face position of driving disc or driven disc; Meanwhile, also can be set to inner cone dish or external cone plate according to by 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, achieve shift speed change and the adaptive shift speed change mode of load torque, and there is car-backing function, simultaneously, its structure is simple, be skillfully constructed, low cost of manufacture.
Preferably, described torque transfer arrangement is the first helical spline cooperating structure be located between driving shaft and initiative taper dish, this the first helical spline cooperating structure is used for when driving shaft rotates forward and the load torque of driven shaft reaches setting value, and the initiative taper dish that friction limit turns round clutch is formed and moving axially of throwing off from mantle dish by this torque transfer arrangement.Make when load torque reaches setting value, the initiative taper dish that friction limit turns round clutch is de-from mantle dish fast, to realize the agility of shift speed change.Certainly, the lead angle of the first helical spline should be greater than that driving shaft is relative with both initiative taper dishes wipes Self-locking angle corresponding to coefficient, belongs to the basic general knowledge of those skilled in the art.
Preferred further, the two formation between described bottom gear driving gear and described initiative taper dish can the linkage structure of synchronous axial system be the second helical spline cooperating structure formed therebetween, 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.When driving disc produces axial displacement, there is not axial float in bottom gear driving gear, to guarantee to move from the forward and reverse rubbing contact of mantle dish and reverse state of throwing off and in process 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 that bottom gear driving gear is relative with both initiative taper dishes wipes Self-locking angle corresponding to coefficient, belongs to the basic general knowledge of those skilled in the art.
Preferably, described torque transfer arrangement is end cam auxiliary structure, comprise the secondary driving link of the cam be fixedly connected on driving shaft, be fixedly connected with or be integrally formed in friction and limit the cam sub-quilt moving part turned round on clutch initiative taper dish, end face one of in the driving link of this cam pair and Passive part is formed with V-shaped groove camming surface, another part is formed and divides with the end lobes stretching into this V-shaped groove camming surface sunk part.Form higher pair between the driving link of cam pair and Passive part, in load torque change procedure, when load torque reaches certain setting value, form axial mutual movement and radial misalignments between driving link and Passive part, to guarantee initiative taper disk detachment mantle dish; When load torque reaches larger setting value, the axis shift distance between driving link and Passive part makes the two depart from torque transmission status and form skidding, can realize the object of load-limiting, eliminates the potential safety hazard that overload of vehicle travels.
Further preferred, the end face in opposite directions of the secondary driving link of described cam and cam sub-quilt moving part is equipped with V-shaped groove camming surface, the driving link of cam pair and the end lobes of Passive part divide with corresponding V-shaped groove be recessed to form complementation, and the inclined-plane, both sides of V-shaped groove is symmetrical.Guarantee forward and reverse load-limiting, guarantee vehicle driving safety further.
Preferably, the loading spring that described friction limit turns round clutch is connected with described initiative taper dish by end face bearing.Reduce the surface friction drag that when shifting gears, initiative taper dish rotates relative to driving shaft, improve gearshift agility, meanwhile, reduce reactive loss, improve 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, roller is connected with for making it away from the first elastic element of star-wheel external cylindrical surface, pusher dog is provided with between two adjacent roller, multiple pusher dog is formed on same driver plate, this driver plate and described star-wheel form coaxial rotation and are connected, driver plate is connected with elastic resistance members, and this elastic resistance members is used for applying a drag torque to driver plate; Described out star wheel is made up of the bottom gear driven gear being provided with convex wheel face; Described star-wheel and driven shaft are formed one or are fixedly connected with described driven shaft by spline fitted structure.By out star wheel and bottom gear driven gear being formed one, guarantee that structure is simple, bottom gear driven gear drives the forward and reverse spinfunction of driven shaft reliable.
Preferred further, described elastic resistance members comprises two swing links arranged in opposite directions being positioned at outside, driver plate one end, the linkage structure of male-female is formed between swing link and driver plate, swing link and driver plate are slidably connected by the linkage structure of this male-female, two swing links are connected 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 when bottom gear driven gear rotating speed is a little more than driven shaft, driver plate is made to form relative pause, to change the circumferential position between the convex wheel face on roller and bottom gear driven gear, thus make roller and bottom gear driven gear and star-wheel form frictional connection, realizing this double rolling key clutch combines quick, reaches the object of driven shaft with bottom gear driven gear synchronous axial system.
Preferred further, be provided with annular groove in the middle part of described roller periphery; Described 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 outside C shape ring.Utilize the open annular elastic structure of C shape, make roller keep departing from the trend of double rolling key clutch star-wheel.
Preferred further, 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 and driven shaft are formed one or be fixedly connected with by spline structure; 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, is connected with Compress Spring between two voussoirs.To make voussoir have enough large physical dimension, guarantee transmitting torque and working life.
Based on identical invention thought, present invention also offers a kind of automatic speed changing axle, the top gear reactive torque of this variable-speed shaft exports and is greater than positive torque output.
A kind of automatic speed changing axle, comprise and be located at bottom gear driving gear on driving shaft and top gear driving gear, described top gear driving gear empty set is on described driving shaft, be provided with the normally closed cone dish limit that rubs between top gear driving gear and driving shaft and turn round clutch, the loading spring that friction limit turns round clutch is sleeved on driving shaft, and driving shaft the shaft shoulder and friction limit turn round clutch initiative taper dish tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish and described driving shaft, this torque transfer arrangement be used for driving shaft rotate forward and friction limit turn round clutch reach setting value from the load torque of mantle dish time, initiative taper dish is formed and moving axially of throwing off from mantle dish, one should be formed 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 engagement 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 is used for when 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 load acts on driven disc is less than setting value, high low speed is when driving gear synchronous axial system, when the moment of torsion that load acts on driven disc is more than or equal to setting value, the driving disc of clutch and driven disc are formed and relatively rotate, and make driving disc have 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, bottom gear driving gear is made to be in axial state of rest, and not play.During for transmission device, under there is the configuration scenario adapted at driven shaft, two-gear automatic speed changing can be realized.Meanwhile, when driving shaft reverses, the first helical spline makes initiative taper dish have trend to driven disc movement, thus the reactive torque improving driven disc exports.
This automatic speed changing axle also has another technological scheme.
A kind of automatic speed changing axle, comprise and be located at bottom gear driving gear on driving shaft and top gear driving gear, described top gear driving gear empty set is on described driving shaft, be provided with the normally closed cone dish limit that rubs between top gear driving gear and driving shaft and turn round clutch, the loading spring that friction limit turns round clutch is sleeved on driving shaft, and driving shaft the shaft shoulder and friction limit turn round clutch initiative taper dish tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish and described driving shaft, this torque transfer arrangement be used for driving shaft rotate forward and friction limit turn round clutch reach setting value from the load torque of mantle dish time, initiative taper dish is formed and moving axially of throwing off from mantle dish, one should be formed 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 load acts on driven disc is less than setting value, high low speed is when driving gear synchronous axial system, when the moment of torsion that load acts on driven disc is more than or equal to setting value, the driving disc of clutch and driven disc are formed and relatively rotate, and driving disc is had throw off the trend of driven disc, bottom gear driving gear and initiative taper dish type integral, make variable-speed shaft structure seem very compact.Meanwhile, when driving shaft reverses, the first helical spline makes initiative taper dish have trend to driven disc movement, thus the reactive torque improving driven disc exports.
The present invention's beneficial effect is compared with prior art, 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 the self shifter of advancing and car-backing function and limit for tonnage function; The top gear reactive torque of variable-speed shaft exports and is greater than positive torque output; Its structure is simple, and gearshift is quick, low cost of manufacture.
Accompanying drawing explanation
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 in the embodiment of the present invention 2, driving shaft 1 is provided with friction limit to turn round the structural representations such as clutch.
The torque transfer arrangement schematic diagram of end cam auxiliary structure that Fig. 7 is bottom gear driving gear 3 in the embodiment of the present invention 2 and arranges between driving shaft 1.
Fig. 8 in the embodiment of the present invention 3, driving shaft 1 is provided with friction limit to turn round the structural representations such as clutch.
Fig. 9 in the embodiment of the present invention 4, driving shaft 1 is provided with friction limit to turn round the structural representations such as clutch.
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 see Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, a kind of containing the limited automatic transimission turning round clutch, comprise driving shaft 1 and driven shaft 2, driving shaft 1 and driven shaft 2 are 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, be provided with the normally closed cone dish limit that rubs between top gear driving gear 4 and driving shaft 1 and turn round clutch, the loading spring 63 that friction limit turns round clutch is connected to an axle journal end face of driving shaft 1 and friction is limit between an end face of the initiative taper dish 61 turning round clutch, end face bearing 64 is provided with between this initiative taper dish 61 and loading spring 63, also be provided with between initiative taper dish 61 and described driving shaft 1 for powerdriven torque transfer arrangement, this torque transfer arrangement is the first helical spline cooperating structure, this torque transfer arrangement is used for when driving shaft 1 rotates forward and the load torque of driven shaft 2 reaches setting value, and initiative taper dish 61 is formed and moving axially of throwing off from mantle dish 62, being formed with the two between described bottom gear driving gear 3 and described initiative taper dish 61 can the linkage structure of synchronous axial system, this can the linkage structure of synchronous axial system be the second helical spline cooperating structure formed 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 engagement 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, axial limit structure is formed for limiting the two distance close to each other between bottom gear driving gear 3 and initiative taper dish 61, this axial limit structure comprises the step surface 61a being 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 turned round clutch is formed integrally 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 is used for top gear driven gear 8 and drives described driven shaft 2 forward synchronous axial system, 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 described driven shaft 2, two voussoirs 92 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 on driving shaft 1 and 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 from the end face of mantle dish 62 and be provided with stop collar 64 between mantle dish 62, and this stop collar 64 forms spacing near from mantle dish 62 end face of bottom gear driving gear 3, described driven shaft 2 is provided with output gear 21, be provided with the second double rolling key clutch between the bottom gear driven gear 5 of described bottom gear gear mesh and driven shaft 2, this second double rolling key clutch is used for bottom gear driven gear 5 and drives the forward and reverse synchronous axial system of driven shaft 2, 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 and the external cylindrical surface of star-wheel 71 of out star wheel, roller 72 is provided with annular groove in the middle part of periphery, roller 72 is connected with for making it away from the first elastic element 73 of star-wheel 71 external cylindrical surface, 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 outside C shape ring, pusher dog is provided with between two adjacent roller 72, multiple pusher dog is formed on same driver plate 74, this driver plate 74 forms coaxial rotation with described star-wheel 71 and is connected, driver plate 74 is connected with elastic resistance members, this elastic resistance members comprises two swing links arranged in opposite directions 75 being positioned at outside, driver plate 74 one end, the linkage structure of male-female is formed between swing link 75 and driver plate 74, swing link 75 and driver plate 74 are slidably connected by the linkage structure of this male-female, two swing links 75 connected by two extension springs 76 and embrace be clipped in support 77 axle journal on, 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, the surface friction drag that this elastic resistance members is formed by two swing links 75 and support 77 axle journal applies a drag torque to driver plate 74, described out star wheel is made up of the bottom gear driven gear 5 being 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 and driven shaft 2 can form one in order to the scheme be fixedly connected with by spline structure both replacing, can reduce the number of components, enhancing driving shaft 1 intensity.
In the present embodiment, when driving shaft 1 and motor shaft are coaxially connected or driving gear on motor shaft engages with the power input gear 12 on driving shaft 1, form the power-shift gear box of electric motor car, it has two-gear automatic speed changing and the low-speed heave-load car-backing function of 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 when 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, there will be heavy duty during heavy duty reversing skids; 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 moved forward and backward.
Driven shaft 2 in the present embodiment can be used as output shaft and is connected with load, and also can adopt the mode that output gear 21 is connected with load, its structural type is various.
In the present embodiment, the star-wheel 71 that the first mono-directional overrun clutch arranged between described top gear driven gear 8 and driven shaft 2 connects can be integrally formed on driven shaft 2, to guarantee the intensity of this mono-directional overrun clutch further.
In the present embodiment, two swing links 75 of described second double rolling key clutch also can be embraced and be clipped on described driven shaft 2 to replace the scheme clasped on support 77.
In the present embodiment, see Figure 11, bottom gear driving gear 3 also can be adopted to replace bottom gear driving gear 3 from the end face of mantle dish 62 and from the scheme being provided with stop collar 64 between mantle dish 62 in the scheme arranging Compress Spring 65 between the end face and the step end face 61a of initiative taper dish 61 front end of mantle dish 62.
In the present embodiment, the male cone (strobilus masculinus) that described friction limit turns 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 disc spring, also can adopt cylindrical compression spring.
The aforementioned automatic transimission of embodiment is applicable to three-wheel or four-wheel electric motor car, and it has advance two-gear automatic speed changing and car-backing function.
In the present embodiment, the scheme of the second mono-directional overrun clutch between bottom gear driven gear 5 and driven shaft 2, can be adopted to replace the scheme of the second double rolling key clutch.This gearbox is applicable to electric motor car with two wheels, and it has the two-gear automatic speed changing of advance.
Embodiment 2 is see 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; Be provided with between described initiative taper dish 61 and described driving shaft 1 for powerdriven torque transfer arrangement, this torque transfer arrangement is end cam auxiliary structure, comprise the secondary driving link 11 of the cam be fixedly connected on driving shaft 1, be integrally formed in friction and limit the cam sub-quilt moving part 41 turned round on clutch initiative taper dish 61, the end face in opposite directions of the secondary driving link 11 of this cam and cam sub-quilt moving part 41 is equipped with V-shaped groove camming surface, the driving link 11 of cam pair and the end lobes of Passive part 41 divide with corresponding V-shaped groove be recessed to form complementation, and the inclined-plane, both sides of V-shaped groove is symmetrical.This torque transfer arrangement is used in driving shaft 1 clockwise and anticlockwise, and when the load torque of driven shaft 2 reaches a setting value, initiative taper dish 61 is formed and moving axially of throwing off from mantle dish 62; When load torque reaches another larger setting value, the secondary driving link 11 of cam and cam sub-quilt moving part 41 form the skidding of relative idle running, 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 for cam driving link 11 or cam sub-quilt moving part 41 can be arranged to the camming surface with V-shaped groove, another part corresponding arranges horizontal straight pin, by the camming surface of this straight pin and V-shaped groove formed higher pair not shown go out.
Embodiment 3 is see Fig. 8, and described bottom gear driving gear 3 is coaxially fixedly connected on driving shaft 1; Described power input gear 12 limits the initiative taper dish 61 turning round clutch to be fixedly connected with described friction; The torque transfer arrangement of the helical spline cooperating structure be 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 the shaft shoulder of initiative taper dish 61 and driving shaft 1.
All the other structures of the present embodiment are identical with embodiment 1, do not repeat them here.
Embodiment 4 is see 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; The torque transfer arrangement of helical spline cooperating structure is provided with between described initiative taper dish 61 and described driving shaft 1; Described power input gear 12 is positioned at outside top gear driving gear 4; Described loading spring 63 is connected between the shaft shoulder of bottom gear driving gear 3 and driving shaft 1.
All the other structures of the present embodiment are identical with embodiment 3, do not repeat them here.
Embodiment 5 is see Figure 10, a kind of automatic speed changing axle, comprise the bottom gear driving gear 3 be 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 set is on described driving shaft 1, be provided with the normally closed cone dish limit that rubs between top gear driving gear 4 and driving shaft 1 and turn round clutch, the loading spring 63 that friction limit turns round clutch is sleeved on driving shaft 1, and driving shaft 1 the shaft shoulder and friction limit turn round clutch initiative taper dish 61 tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish 61 and described driving shaft 1, this torque transfer arrangement be used for driving shaft 1 rotate forward and rub limit turn round clutch reach setting value from the load torque of mantle dish 62 time, initiative taper dish 61 is formed and moving axially of throwing off from mantle dish 62, one should be formed 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.Described power input gear 12 is fixedly connected on driving shaft 1 and is positioned at outside bottom gear driving gear 3.
Embodiment 6 is see Figure 11, a kind of automatic speed changing axle, comprise and be located at bottom gear driving gear 3 on driving shaft 1 and top gear driving gear 4, described top gear driving gear 4 empty set is on described driving shaft 1, be provided with the normally closed cone dish limit that rubs between top gear driving gear 4 and driving shaft 1 and turn round clutch, the loading spring 63 that friction limit turns round clutch is sleeved on driving shaft 1, and driving shaft 1 the shaft shoulder and friction limit turn round clutch initiative taper dish 61 tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish 61 and described driving shaft 1, this torque transfer arrangement be used for driving shaft 1 rotate forward and rub limit turn round clutch reach setting value from the load torque of mantle dish 62 time, initiative taper dish 61 is formed and moving axially of throwing off from mantle dish 62, one should be formed 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 engagement 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, the axial limit structure of both restrictions distance close to each other is formed between bottom gear driving gear 3 and initiative taper dish 61, this axial limit structure comprises the step surface 61a being 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 that driving shaft 1 is coaxially fixedly connected with, and driving shaft 1 forms the axial limiting of described bottom gear driving gear 3 away from the end face from mantle dish 62 side by this power input gear 12, bottom gear driving gear 3 is near being provided with Compress Spring 65 between the end face and the step end face 61a of initiative taper dish 61 front end of mantle dish 62 side.
In the present embodiment, bottom gear driving gear 3 also can be adopted to replace bottom gear driving gear 3 near being provided with Compress Spring 65 between the end face and the step end face 61a of initiative taper dish 61 front end of mantle dish 62 side from the end face of mantle dish 62 and from the scheme being provided with stop collar 64 between mantle dish 62.
Although describe embodiments of the present invention by reference to the accompanying drawings above, but those of ordinary skill in the art also can recognize in the scope to claims and makes various change or amendment, as the wedge shape working surface of the push rod in the present invention made the mode that ecto-entad increases gradually, realize clutch by pulling push rod and depart from the object surmounting state, bottom the interior edge face of corresponding push rod, can extension spring etc. be set.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 turning round clutch, comprise driving shaft (1) and driven shaft (2), driving shaft (1) and driven shaft (2) are 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), be provided with the normally closed cone dish limit that rubs between top gear driving gear (4) and driving shaft (1) and turn round clutch, the loading spring (63) that friction limit turns round clutch is connected between driving shaft (1) with the initiative taper dish (61) limitting and turn round clutch of rubbing, also be provided with between initiative taper dish (61) and described driving shaft (1) for powerdriven torque transfer arrangement, this torque transfer arrangement is used at least when driving shaft (1) rotates forward and the load torque of driven shaft (2) reaches setting value, initiative taper dish (61) is formed and moving axially of throwing off from mantle dish (62), friction limit turns round forming one from mantle dish (62) and top gear driving gear (4) or being coaxially fixedly connected with of clutch, being formed with the two between the bottom gear driving gear (3) of described bottom gear gear mesh and described initiative taper dish (61) can the linkage structure of synchronous axial system, 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 is used for top gear driven gear (8) and drives described driven shaft (2) forward synchronous axial system, and this first double rolling key clutch is used for top gear driven gear (8) and drives described driven shaft (2) forward and reverse synchronous axial system, be provided with the second double rolling key clutch or the second overrunning clutch between the bottom gear driven gear (5) of described bottom gear gear mesh and driven shaft (2), this second double rolling key clutch is used for bottom gear driven gear (5) and drives driven shaft (2) forward and reverse synchronous axial system, this second overrunning clutch is used for bottom gear driven gear (5) and drives driven shaft (2) forward synchronous axial system.
2. according to claim 1 containing the limited automatic transimission 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 used for when driving shaft (1) rotates forward and the load torque of driven shaft (2) reaches setting value, and the initiative taper dish (61) that friction limit turns round clutch is formed 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 turning round clutch, it is characterized in that, the two formation between described bottom gear driving gear (3) and described initiative taper dish (61) can the linkage structure of synchronous axial system be the second helical spline cooperating structure formed therebetween, bottom gear driving gear (3) is contained on described initiative taper dish (61) by this second helical spline structure engagement 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 turning round clutch, it is characterized in that, described torque transfer arrangement is end cam auxiliary structure, comprise the secondary driving link (11) of the cam be fixedly connected on driving shaft (1), be fixedly connected with or be integrally formed in friction limit and turn round cam sub-quilt moving part (41) on clutch initiative taper dish (61), end face one of in the driving link (11) of this cam pair and Passive part (41) is formed with V-shaped groove camming surface, another part is formed and divides with the end lobes stretching into this V-shaped groove camming surface sunk part.
5. according to claim 4 containing the limited automatic transimission turning round clutch, it is characterized in that, the end face in opposite directions of the secondary driving link (11) of described cam and cam sub-quilt moving part (41) is equipped with V-shaped groove camming surface, the driving link (11) of cam pair and the end lobes of Passive part (41) divide with corresponding V-shaped groove be recessed to form complementation, and the inclined-plane, both sides of V-shaped groove is symmetrical.
6. according in Claims 1 to 5 described in any one claim containing the limited automatic transimission turning round clutch, it is characterized in that, the loading spring (63) that described friction limit turns round clutch is connected with described initiative taper dish (61) by end face bearing (64).
7. according in Claims 1 to 5 described in any one claim containing the limited automatic transimission turning round clutch, 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), roller (72) is connected with for making it away from first elastic element (73) of star-wheel (71) external cylindrical surface, two adjacent roller are provided with pusher dog between (72), multiple pusher dog is formed on same driver plate (74), this driver plate (74) forms coaxial rotation with described star-wheel (71) and is connected, (74) are connected with elastic resistance members with driver plate, this elastic resistance members is used for applying a drag torque to driver plate (74), described out star wheel is made up of the bottom gear driven gear (5) being provided with convex wheel face, described star-wheel (71) and driven shaft (2) are formed one or are fixedly connected with described driven shaft (2) by spline fitted structure.
8. according to claim 7 containing the limited automatic transimission turning round clutch, it is characterized in that, described elastic resistance members comprises two swing links arranged in opposite directions (75) being positioned at driver plate (74) outside, one end, the linkage structure of male-female is formed between swing link (75) and driver plate (74), swing link (75) and driver plate (74) are slidably connected by the linkage structure of this male-female, two swing links (75) connected by two extension springs (76) and embrace be clipped in the upper or support (77) of described driven shaft (2) axle journal on, 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 turning round clutch, it is characterized in that, in the middle part of described roller (72) periphery, be provided with annular groove; Described 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 outside C shape ring.
10. according in Claims 1 to 5 described in any one claim containing the limited automatic transimission turning round clutch, 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) and driven shaft (2) are formed one or be fixedly connected with by spline structure; 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 and be located at bottom gear driving gear (3) on driving shaft (1) and top gear driving gear (4), it is characterized in that, described top gear driving gear (4) empty set is on described driving shaft (1), be provided with the normally closed cone dish limit that rubs between top gear driving gear (4) and driving shaft (1) and turn round clutch, the loading spring (63) that friction limit turns round clutch is sleeved on driving shaft (1), and be positioned at driving shaft (1) the shaft shoulder and friction limit turn round clutch initiative taper dish (61) tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish (61) and described driving shaft (1), this torque transfer arrangement be used for driving shaft (1) rotate forward and friction limit turn round clutch reach setting value from the load torque of mantle dish (62) time, initiative taper dish (61) is formed and moving axially of throwing off from mantle dish (62), one should be formed 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 engagement 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 and be located at bottom gear driving gear (3) on driving shaft (1) and top gear driving gear (4), it is characterized in that, described top gear driving gear (4) empty set is on described driving shaft (1), be provided with the normally closed cone dish limit that rubs between top gear driving gear (4) and driving shaft (1) and turn round clutch, the loading spring (63) that friction limit turns round clutch is sleeved on driving shaft (1), and be positioned at driving shaft (1) the shaft shoulder and friction limit turn round clutch initiative taper dish (61) tail end between, the torque transfer arrangement of the first helical spline is provided with between initiative taper dish (61) and described driving shaft (1), this torque transfer arrangement be used for driving shaft (1) rotate forward and friction limit turn round clutch reach setting value from the load torque of mantle dish (62) time, initiative taper dish (61) is formed and moving axially of throwing off from mantle dish (62), one should be formed 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.
Priority Applications (1)
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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 true CN103982602B (en) | 2016-04-20 |
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| JP6528468B2 (en) * | 2015-03-04 | 2019-06-12 | スズキ株式会社 | Multi-stage transmission |
| CN106481691B (en) * | 2015-08-28 | 2020-11-06 | 约翰迪尔（天津）有限公司 | Bi-directional overrunning clutch and power transmission system including the same |
| CN105276026B (en) * | 2015-12-02 | 2018-04-13 | 傅元才 | A kind of mono-directional overrun clutch structure, two gear speed change systems and control method |
| CN107461464B (en) * | 2016-06-03 | 2024-02-27 | 重庆鸿龙源传动机械有限公司 | Multi-gear transmission of electric vehicle |
| CN107524798A (en) * | 2016-06-22 | 2017-12-29 | 向永川 | Automatic transmission |
| CN106195145A (en) * | 2016-07-13 | 2016-12-07 | 董德强 | A kind of automatic transmission of rotating difference speed ratio |
| CN109267546A (en) * | 2018-11-26 | 2019-01-25 | 国家电网有限公司 | A kind of storage station's bypass valve outlet current-limiting apparatus |
| CN109899509B (en) * | 2019-04-10 | 2020-11-10 | 西南大学 | Self-adaptive automatic speed-changing electric drive system with mechanical double-overrunning clutch main shaft output |
| CN109990057B (en) * | 2019-04-10 | 2022-06-03 | 西南大学 | Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission |
| 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 |
| CN111649109A (en) * | 2019-11-05 | 2020-09-11 | 摩登汽车有限公司 | Speed reducer |
| 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 |
| CN110966368B (en) * | 2019-12-04 | 2022-03-22 | 西南大学 | Intelligent self-adaptive automatic speed change system for super-large load |
| CN110939699B (en) * | 2019-12-04 | 2022-04-22 | 西南大学 | Mechanical self-adaptive automatic transmission adopting multi-piece type large-torque friction clutch |
| CN111577842B (en) * | 2020-05-13 | 2024-04-05 | 北京开云汽车有限公司 | Wet single clutch two-gear transmission |
| CN113969974B (en) * | 2020-07-23 | 2023-06-06 | 宁波圣龙新能源汽车动力有限公司 | Automatic gear shifting system of transmission |
| CN112628375B (en) * | 2020-12-16 | 2022-03-01 | 西南大学 | Central driving self-adaptive speed change assembly of tricycle |
| CN112682480B (en) * | 2021-01-15 | 2021-09-14 | 天津大学 | Gear transmission structure |
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| DE1284714B (en) * | 1966-07-16 | 1968-12-05 | Kaleja Heinrich | Coupling for smooth starting of a driven shaft |
| CN201953978U (en) * | 2011-04-18 | 2011-08-31 | 重庆阿尔迪机电技术开发有限公司 | Electromagnetically controlled overrunning clutch gear-shifting device |
| US8978856B2 (en) * | 2011-05-10 | 2015-03-17 | Delphi Technologies, Inc. | Over-torque protector device for a compressor |
| CN103307222B (en) * | 2013-06-13 | 2016-04-06 | 同济大学 | A kind of automotive dynamoelectric machine formula automatic transmission with free wheel device |
| CN203892476U (en) * | 2014-05-30 | 2014-10-22 | 傅元才 | Automatic speed changing device with torque limit clutch and speed changing shaft |
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