CN205226159U - Two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system - Google Patents
Two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system Download PDFInfo
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- CN205226159U CN205226159U CN201520982211.XU CN201520982211U CN205226159U CN 205226159 U CN205226159 U CN 205226159U CN 201520982211 U CN201520982211 U CN 201520982211U CN 205226159 U CN205226159 U CN 205226159U
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Abstract
The utility model discloses a two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system, the clutch is including rotating the suit at the epaxial driving part of power, the driving part has the spiral spline cover through the cooperation of spiral spline structure, the spiral spline cover is respectively through being located its both ends and forming first one -way separation and reunion structure and the one -way separation and reunion structure of second respectively with fixed first terminal surface dish and the second terminal surface dish of power shaft, two one -way separation and reunion structures are used for respectively moving the positive and negative rotation of power shaft by spiral spline cuff belt, the spiral spline cover makes first one -way separation and reunion structure and the one -way separation and reunion structure of second form the normal close respectively and normally open through elastic element, spiral spline cover outside is equipped with only when spiral spline cover reverse rotation, to its one -way retention device who applys the resistance. The variable speed axle becomes and fast system includes this clutch. The beneficial effects of the utility model are that, the horizontal section size of clutch is little, bearing force is strong, variable speed axle and variable speed system have two fenders of forward and reverse output.
Description
Technical field
The utility model relates to a kind of clutch, particularly a kind of spiral double rolling key clutch structure, variable-speed shaft and automatic speed-changing system.
Background technique
In automatic shifting speed variator, conventional mono-directional overrun clutch is also known as one-way element, spiral double rolling key clutch structure, controllable overrunning clutch etc.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 spiral double rolling key clutch structure can drive the forward and reverse rotation of driven member, and driven member can not drive driving link to rotate.For the unidirectional and spiral double rolling key clutch structure of the drive mechanism of inside and outside suit, it forms high auxiliary driving by ball, roller or voussoir and cam working face, the requirement of its accuracy of manufacturing is high, mechanical efficiency is low, working life is low, simultaneously, also there is the defect that sectional dimension is large, application places is subject to larger restriction.For this reason, it is CN201510198365.4 that the applicant have submitted application number on April 24th, 2015 to State Intellectual Property Office, invention and created name is the application for a patent for invention of a kind of double rolling key clutch, speed change gear and automatic speed-changing system, this application is open on July 29th, 2015, and its publication number is CN104806656A.That application discloses a kind of spiral double rolling key clutch, this clutch forms bidirectional overtaking clutch structure by the engagement system of screw-casing and end-tooth, and wherein, screw-casing, by an additional fricting resistance device effect, makes spline housing form clutch campaign.Although this structure is simple, compact, and moment of torsion transmission efficiency is high, long service life.But its surface friction drag acted on forms certain consumption for power always, particularly for electric drive, its reactive power consumption accounting is comparatively large, there is uneconomic defect.In addition, after helical spline structure clutch has engagement, before disconnected power, keep the characteristic of self-locking, be not fully used.For this reason, require further improvement.
Summary of the invention
The utility model object first object is for the deficiencies in the prior art, a kind of spiral double rolling key clutch structure is provided, the first end-engaging clutch that this clutch utilizes helical spline cooperating structure and elastic element to be used in rotating forward often engages, and only needs to form engagement by surface friction drag at the second end-engaging clutch for reversing.For this clutch for vehicle drive system, can have and significantly reduce power consumption, reduce user cost.Second object of the present utility model is to provide a kind of variable-speed shaft with spiral double rolling key clutch structure, and its load capacity is strong, is applicable to the place that installing space is narrow and small.3rd object of the present utility model is to provide a kind of automatic speed-changing system, and this system has aforementioned variable-speed shaft, can realize two-gear automatic speed changing.
For realizing the first object, the utility model adopts following technological scheme.
A kind of spiral double rolling key clutch structure, comprise the rotating plate-like driving link be sleeved on line shaft, driving link is combined with helical spline cover by helical spline structure, helical spline cover both sides are respectively equipped with first end face and the second end face disk, first end face is all fixedly connected with described line shaft with the second end face disk, helical spline cover is respectively by first end face and the second end face disk, and the unidirectional tooth of intermeshing end face, form the first one-way clutch structure and the second one-way clutch structure respectively, first one-way clutch structure and the second one-way clutch structure are respectively used to be overlapped by helical spline drive line shaft synchronously rotate forward and synchronously reverse, helical spline structure between helical spline cover and driving link, has and promotes the Hand of spiral of helical spline cover towards the movement of first end face when driving link rotates forward, be provided with an elastic element between helical spline cover and described second end face disk, form normally closed and normally open respectively to make the first one-way clutch structure and the second one-way clutch structure, helical spline cover is outside is provided with one only when helical spline overlaps counterrotating by a static component, applies the one-way check device of resistance to helical spline cover.
In prior art, helical spline cooperating structure has following fundamental characteristics, it is mainly used in transmitting torque, there is the characteristic of the corresponding movement on a large scale of Small-angle Rotation simultaneously, therefore, lead angle for helical spline is all inevitable comparatively large, and the spline housing by promoting to be engaged in splined shaft moves and realizes spline housing or splined shaft rotation.
Adopt the utility model of preceding solution, utilize the aforementioned fundamental characteristics of screw thread spline housing, driving link rotates under external force drives, helical spline forms certain integrated motion with axis movement that relatively rotates with driving link under being enclosed within the surface friction drag effect of braking device applying, its movement direction is determined by the sense of rotation of Hand of spiral and driving link, and its sense of rotation is identical with driving link.Driven member is driven synchronously to rotate forward and synchronously reverse because the first one-way clutch structure and the second one-way clutch structure are only respectively used to helical spline cover.Therefore, when driving link and line shaft all rotate forward, second one-way clutch structure is in separated state at elastic element and helical spline mating reaction line, now, when line shaft rotating speed is greater than driving link and helical spline cover rotating speed, first one-way clutch structure is in by unidirectional tooth and elastic element and surmounts state, and forms the first mono-directional overrun clutch.When driving link reverses, driving link drives the reversion of helical spline cover, the rotation of helical spline cover is limited by the effect of one-way check device, helical spline is formed under being enclosed within helical spline effect and moves axially, first one-way clutch structure is separated, then the second one-way clutch structure combines, and realizes oppositely driving line shaft reverse function.When the unpowered input of driving link, because driving link empty set is on line shaft, therefore, no matter the defeated forward or reverse of power all can not drive driving link to rotate, thus realizes the function of spiral double rolling key clutch structure.This programme is exactly the aforementioned fundamental characteristics utilizing screw thread spline housing, rotary motion is converted to the clutch configuration moving axially and realize end face engagement.Engage unidirectional tooth by end face and be mutually engaged the reliable power transmission arrangment of formation.And one-way check device only applies resistance when driving link reverses to helical spline cover, for this clutch being applied to the vehicle class traffic tool, its counterrotating is only suitable for when moveing backward, under vehicle forward state, do not apply resistance.In terms of existing technologies, greatly reduce reactive power consumption, energy utilization rate is high.Wherein, elastic element can be cylindroid helicalcoil compression spring, disc spring, or any one in the elastic sleeve be made up of elastomeric material etc.
Preferably, described helical spline puts and is set with by frictional connection mode the C shape snap ring having and stop handle, described one-way check device comprises an active block stop, on the hinged stopper seat of active block stop, stopper seat is fixedly connected on static component, is provided with block torsion spring between active block stop and stopper seat; When described helical spline cover rotates forward, C shape snap ring overcomes block torsion spring elastic force by stop, and oppresses active block stop beat and formed and dodge space to C shape snap ring.One-way check device is stopped by C shape snap ring, and restriction helical spline cover rotates, and by C shape snap ring to helical spline cover applying one surface friction drag.Its structure is simple, low cost of manufacture, and one-way function is reliable.During use, the position that facilitates on gear box class static component arranges stopper seat.
Further preferred, the spin axis that the hinging shaft axis being parallel of described active block stop overlap in helical spline, what active block stop reverse at C shape snap ring is head-on notch, and has the prevent surface of preseting length along the axis that described helical spline overlaps movement.To adapt to helical spline cover displacement distance Len req, and form the stable structure applying surface friction drag.
Further preferred, the hinge point of described active block stop is in rear end, and active block stop upper side is by articulated section to notch portion, and the direction that the axis along the movement of described helical spline cover increases gradually by size extends.With when helical spline cover rotates forward, oppress active block stop smoothly.
Preferably, the spin axis that the hinging shaft axes normal of described active block stop overlaps in helical spline, active block stop C shape snap ring rotate forward head-on in skewed.To provide another kind of barrier structure, and structure can be simplified more.
Preferably, described one-way check device comprises and is located on static component and is enclosed within the outside electromagnetic coil of described helical spline cover.Utilize the helical spline cover be made up of ferromagnetic material, or helical spline puts the collar being provided with magnet ring or ferromagnetic material and making, and helical spline is overlapped and forms electromagnet structure with electromagnetic coil, the iron core of helical spline cover formation electromagnet.With when helical spline cover reverses, it is applied in an electromagnetic resistance under electromagnetic field environment, reaches the object moving axially commutation, and its structure is simple, control is convenient, low cost of manufacture.Be applicable to the spiral bidirectional clutch structure being located at shaft end position.
Preferably, described helical spline cover is engaged in the side that described driving link is positioned at the second end face disk; The helical spline cover the other end is provided with multiple circumference uniform distribution, and the connection pawl that can be passed by the hollow part in driving link epiplastron portion, helical spline cover forms described first end-engaging clutch structure by this connection pawl and described first end face.Connect pawl to be passed by the hollow part in driving link epiplastron portion, can abundant compact structure, saving topology layout space.
Preferred further, described helical spline cover is in internal spline structure, and helical spline cover is engaged on the helical spline axle journal of described driving link.Can guarantee that structure is simple further, easy to process.
Preferred further, described helical spline cover is in external splines structure, and helical spline cover is engaged in the Turbo Flora keyhole of described driving link.Can be integrally formed on the body of driving link in Turbo Flora keyhole, also can be formed on the 3rd component that is fixedly connected with driving link.It has larger sectional dimension, can form the helical spline of larger cross-section size, is applicable to relatively large variable speed drive system.
For realizing the second object, the utility model adopts following technological scheme.
A kind of variable-speed shaft, comprise the spiral double rolling key clutch structure realizing the utility model first object, the driving link of this structure forms bottom gear driven gear, and line shaft is also provided with top gear driven gear, and top gear driven gear is connected with line shaft by mono-directional overrun clutch; Or be formed with mono-directional overrun clutch structure between top gear driven gear and line shaft.
Adopt the utility model of preceding solution, utilize said spiral double rolling key clutch structure, and mono-directional overrun clutch or mono-directional overrun clutch structure, formed high relative to its transmission efficiency of higher pair drive clutch of prior art, driving torque is large, long service life, and the variable-speed shaft that reactive power consumption is low.When driving link rotates forward under outside motivational drive, mainly under low-speed conditions, driving link drives line shaft low speed to rotate forward by spiral double rolling key clutch structure, and top gear driven gear is formed by mono-directional overrun clutch or mono-directional overrun clutch structure and line shaft and surmounts state; When external impetus is by the input of top gear driven gear, as under mainly high-speed condition, top gear driven gear drives line shaft forward High Rotation Speed by mono-directional overrun clutch or mono-directional overrun clutch structure, and line shaft surmounts state by being formed between spiral double rolling key clutch structure and driving link.Driving link counterrotating under outside motivational drive, driving link drives line shaft reversion by spiral double rolling key clutch structure, and top gear driven gear is formed by mono-directional overrun clutch or mono-directional overrun clutch structure and line shaft and surmounts state
Preferably, described mono-directional overrun clutch structure forms unidirectional super conjunction device by drive end and the intermeshing unidirectional end-tooth of driven end; Drive end is integrally formed on driving disc, and what driven end can be moved axially by helical spline structure is engaged on line shaft; Driven end is connected with centrifugal delivery device, for pushing driven end to drive end under setting speed condition; Have push rod by pinned connection in the middle part of driven end, push rod is engaged in the mider hole of line shaft, line shaft is formed with push rod and moves and run through groove with space; Be provided with Returnning spring between bottom push rod bottom and mider hole, the outer end that push rod stretches out the corresponding axle head of line shaft is fixedly connected with magnet steel.Because the driven end of push rod and spiral overrunning clutch is synchronizing moving state, and stretch out the corresponding axle head of line shaft.Therefore, push rod outer end can be utilized easily to obtain the position signal of clutch driven end, when corresponding with clutch state information in the position of driven end, clutch state information can be obtained, to utilize this signal automatically to control the speed variator system with this mono-directional overrun clutch structure.Push rod position information can utilize position detecting element of the prior art, position transducer etc. all can obtain easily.Wherein drive end be integrally formed in scheme on driving disc can effective simplified structure.And centrifugal delivery device engages under setting speed for this mono-directional overrun clutch structure, formed by low speed to gearshift at a high speed.
For realizing the 3rd object, the utility model adopts following technological scheme.
A kind of automatic speed-changing system, comprises the variable-speed shaft realizing the second goal of the invention, the line shaft of this variable-speed shaft is fixedly connected with output gear, and the driving link on line shaft forms bottom gear driven gear; The power input front end of line shaft is also provided with input shaft, this input shaft is provided with can with the synchronous bottom gear driving gear initiatively of input shaft and top gear driving gear, and bottom gear driving gear and top gear driving gear respectively corresponding driving link with described formation bottom gear driven gear and top gear driven gear often engage.
In this programme, speed variator system is driven for motor, after startup mair motor, motor power is inputted by input shaft by gear, sprocket wheel or belt pulley, under low speed rotating forward condition, bottom gear driving gear drives the driving link forming bottom gear driven gear to rotate forward, and top gear driving gear drives top gear driven gear to rotate forward; Driving link drives line shaft to rotate forward by double rolling key clutch structure.Now, line shaft rotating speed, lower than driving disc rotating speed, utilizes the structural relation of top gear driven gear empty set on line shaft, and the two formation surmounts relation in relative rotation.When input power axle rotating speed increases to setting value, the rotary shaft rotating speed correspondence arranging speed increase driving gear increases, the position that speedup driven gear makes centrifugal block for clutch use promotion driven end combine to mono-directional overrun clutch structure, form the combination with drive end, line shaft and top gear driven gear synchronous forward are rotated, and line shaft turns to identical driving link to be formed surmount relation by surmounting twin-direction clutch with lower than its rotating speed.When input shaft counterrotating, line shaft forms synchronous axial system by double rolling key clutch and driving link; During low speed, the driven end of mono-directional overrun clutch structure is under action of reset spring, and pushed in the position away from drive end by the bearing pin on push rod, the two separated state, driven end is with line shaft synchronous axial system; Top gear driven gear is driven by top gear driving gear and is formed by the structure of empty set on line shaft and line shaft and relatively rotates.When input shaft reverse speed reaches setting value, driven end is pushed to binding site under centrifugal block for clutch use effect, but due to the meshing relation that drive end and driven end are unidirectional tooth, now, the two does not engage, drive end is overcome the elastic force of loading spring by driven end pushing and retreats, and the two is formed to skid and have and surmounts state in relative rotation.Double rolling key clutch structure in this programme, utilize the following characteristic of double rolling key clutch in prior art to form bidirectional overtaking function, namely 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.
For the scheme being formed with mono-directional overrun clutch structure between top gear driven gear and line shaft, by Hall element, utilize the magnet steel on push rod detect push rod position and obtain position signal, control system can utilize this signal to carry out corresponding control, is beneficial to the automatic control of the system of realization.As under top gear condition, cut off the main drive motor several seconds, input shaft is run out of steam, the driven end of overrunning clutch return and being separated with drive end under action of reset spring, when telegram in reply starts again, self-assembling formation low speed rotation and realizing by the automatic speed changing at a high speed to low speed speed change.
Preferably, described top gear driving gear is connected by spline fitted with between input shaft, and the spline width of keyway on top gear driving gear is greater than the spline width of input shaft spline shaft, and top gear driving gear and input shaft are provided with vibration damping torsion spring.With when bottom gear, input shaft makes top gear driving gear circumference form a windup-degree by the elastic force of torsion spring, and input shaft is by torsion spring and make top gear driving gear form the driving of the top gear driven gear to idle running; When being transformed to top gear, load overcomes torsion spring elastic force, top gear driving gear is formed by the direct transmitting torque of spline, thus in shift process, plays the effect slowing down impact.
Preferred further, described input shaft is also fixedly connected with speed increase driving gear; Described vibration damping torsion spring set is contained on input shaft, and vibration damping torsion spring two ends are fixedly connected in top gear driving gear and speed increase driving gear respectively.With the other end utilizing speed increase driving gear to connect torsion spring, to form compact structure layout; Speed increase driving gear can drive power, to make its rotating speed higher than place axle for being provided by the one-way spiral free wheel device of centrifugal control high speed rotating.
The beneficial effects of the utility model are, clutch cross-sectional dimension is little, mechanical efficiency is high, load capacity is strong, long service life, and frictional loss is little; Variable-speed shaft has forward two and keeps off and oppositely export; Speed variator system can realize forward two-gear automatic speed changing and reverse output function.
Accompanying drawing explanation
Fig. 1 is the structural representation of the utility model embodiment 1.
Fig. 2 is the structural representation axonometric drawing that one-way check device in the utility model embodiment 1 and helical spline overlap annexation.
Fig. 3 is the partial structurtes schematic diagram of one-way check structure in the utility model embodiment 1.
Fig. 4 is the structural representation of the utility model embodiment 2.
Fig. 5 is the structural representation of the utility model embodiment 3.
Fig. 6 is the structural representation of the utility model embodiment 4.
Fig. 7 is the structural representation axonometric drawing that in the utility model embodiment 4, one-way check structure and helical spline overlap annexation.
Fig. 8 is the structural representation of the utility model embodiment 5.
Fig. 9 is the structural representation of the utility model embodiment 6.
Embodiment
Below in conjunction with accompanying drawing, the utility model is further described, but therefore the utility model is not limited among described scope of embodiments.
Embodiment 1, see Fig. 1, Fig. 2, Fig. 3, a kind of spiral double rolling key clutch structure, comprise the rotating plate-like driving link 14 be sleeved on line shaft 2, driving link 14 is combined with helical spline cover 30 by helical spline structure, helical spline overlaps 30 both sides and is respectively equipped with first end face 31 and the second end face disk 32, first end face 31 is all fixedly connected with described line shaft 2 with the second end face disk 32, helical spline cover 30 is respectively by first end face 31 and the second end face disk 32, and the unidirectional tooth of intermeshing end face, form the first one-way clutch structure and the second one-way clutch structure respectively, first one-way clutch structure and the second one-way clutch structure are respectively used to overlap 30 by helical spline and drive line shaft 2 synchronously to rotate forward and synchronous reversion, helical spline structure between helical spline cover 30 and driving link 14, has and promotes the Hand of spiral of helical spline cover 30 towards first end face 31 movement when driving link 14 rotates forward, be provided with an elastic element 33 between described helical spline cover 30 and described second end face disk 32, form normally closed and normally open respectively to make the first one-way clutch structure and the second one-way clutch structure, helical spline cover 30 is set with by frictional connection mode the C shape snap ring 34 having and stop handle 34a, helical spline overlaps 30 outsides and is provided with one only when helical spline overlaps 30 counterrotating by a static component, applies the one-way check device of surface friction drag to helical spline cover 30.Helical spline cover 30 is engaged in the side that described driving link 14 is positioned at the second end face disk 32; Helical spline overlaps 30 the other ends and is provided with multiple circumference uniform distribution, and the connection pawl 30a that can be passed by the hollow out 14a in driving link 14 epiplastron portion, helical spline cover 30 forms described first end-engaging clutch structure by this connection pawl 30a and described first end face 31.Helical spline cover 30 is in internal spline structure, and helical spline cover 30 is engaged on the helical spline axle journal of described driving link 14.
Wherein, one-way check device comprises an active block stop 35, and active block stop 35 is by the hinged stopper seat 36 of hinging shaft 36a, and stopper seat 36 is fixedly connected on static box component, is provided with block torsion spring 37 between active block stop 35 and stopper seat 36; When described helical spline cover 30 rotates forward, C shape snap ring 34 overcomes block torsion spring 37 elastic force by stop handle 34a, and oppresses active block stop 35 beat and formed and dodge space to C shape snap ring 34.The hinging shaft 36a axis being parallel of active block stop 35 in the spin axis of helical spline cover 30, active block stop 35 C shape snap ring 34 reverse head-on in notch, and there is along the axis that described helical spline overlaps 30 movements the prevent surface 35a of preseting length.The hinge point of active block stop 35 is in rear end, and active block stop 35 upper side is by articulated section to notch portion, and the direction axially increased gradually by size along 30 movements of described helical spline cover extends.
Embodiment 2, and see Fig. 4, the hinging shaft 36a axes normal of described active block stop 35 is in the spin axis of helical spline cover 30, and what active block stop 35 rotated forward at C shape snap ring 34 heads in skewed.
All the other structures of the present embodiment are identical with embodiment 1, do not repeat them here.
Embodiment 3, and see Fig. 5, described one-way check device comprises on the casing that is located at and forms static component, and is enclosed within the electromagnetic coil 30b that described helical spline overlaps 30 outsides.Wherein, helical spline cover 30 is made up of ferromagnetic material, or helical spline cover 30 is provided with the collar that magnet ring or ferromagnetic material make, and the electromagnetic coil 30b that helical spline overlaps 30 outsides forms electromagnet structure, and helical spline cover 30 forms the iron core of electromagnet.
All the other structures of the present embodiment are identical with embodiment 1, do not repeat them here.
Embodiment 4, and see Fig. 6, Fig. 7, described helical spline cover 30 is in external splines structure, and helical spline cover 30 is engaged in the Turbo Flora keyhole of described driving link 14, and are formed in Turbo Flora keyhole on the 3rd component that is fixedly connected with driving link 14.So that process Turbo Flora keyhole separately, improve ease of processing, reduce manufacture cost.
All the other structures of the present embodiment and embodiment 1,2 or 3 identical, do not repeat them here.
Embodiment 5, see Fig. 8, a kind of variable-speed shaft, comprise arbitrary spiral double rolling key clutch structure in embodiment 1 ~ 4, the driving link 14 of this structure forms bottom gear driven gear, line shaft 2 is also provided with top gear driven gear 1, and top gear driven gear 1 is by being formed with mono-directional overrun clutch structure between top gear driven gear 1 and line shaft 2.
Wherein, mono-directional overrun clutch structure forms unidirectional super conjunction device by drive end 3 and the intermeshing unidirectional end-tooth of driven end 4; Drive end 3 is integrally formed on top gear driven gear 1, and what driven end 4 can be moved axially by helical spline structure is engaged on line shaft 2; Driven end 4 is connected with centrifugal delivery device, for pushing driven end 4 to drive end 3 under setting speed condition; Be connected with push rod 6 by bearing pin 5 in the middle part of driven end 4, push rod 6 is engaged in the mider hole of line shaft 2, line shaft 2 is formed with push rod 6 and moves and run through groove 6a with space; Be provided with Returnning spring 7 between bottom push rod 6 bottom and mider hole, the outer end that push rod 6 stretches out the corresponding axle head of line shaft 2 is fixedly connected with magnet steel 8.Drive end 3 is engaged in top gear driven gear 1 side by helical spline structure, during to press direction initialization rotation at top gear driven gear 1, drive drive end 3 to move to desired location towards driven end 4 direction, and be provided with loading spring 9 between drive end 3 and top gear driven gear 1.
Wherein, centrifugal delivery device promotes the binding site of driven end 4 to clutch configuration by L shape centrifugal block for clutch use 10; L shape centrifugal block for clutch use 10 is rotating to be connected on speedup driven gear 11, is provided with reduction torsion spring 10a, is provided with plane bearing 12 between centrifugal block for clutch use 10 and driven end 4 between L shape centrifugal block for clutch use 10 and speedup driven gear 11.This speedup driven gear 11 is only rotating to be sleeved on line shaft 2, and bearing pin 5 is fixedly connected on described push rod 6, and bearing pin 5 is connected to inside driven end 4 by sidepiece.
Mono-directional overrun clutch structure in the present embodiment, also can adopt the mono-directional overrun clutch of the ball of inside and outside suit of the prior art, roller or wedge block type to substitute.
All the other structures of the present embodiment and embodiment 1,2,3 or 4 identical, do not repeat them here.
Embodiment 6, and see Fig. 9, a kind of automatic speed-changing system, comprises the variable-speed shaft described in embodiment 5, and the line shaft 2 of this variable-speed shaft is fixedly connected with output gear 13, and the driving link 14 on line shaft 2 forms bottom gear driven gear; The power input front end of line shaft 2 is also provided with input shaft 15, this input shaft 15 is provided with can with the synchronous bottom gear driving gear 16 initiatively of input shaft 15 and top gear driving gear 17, and bottom gear driving gear 16 and top gear driving gear 17 respectively corresponding driving link 14 with described formation bottom gear driven gear and top gear driven gear 1 often engage.
Wherein, be connected between top gear driving gear 17 with input shaft 15 by spline fitted, the spline width of keyway on top gear driving gear 17 is greater than the spline width of input shaft 15 spline shaft, and top gear driving gear 17 and input shaft 15 are provided with vibration damping torsion spring 19.Input shaft 15 is also fixedly connected with the speed increase driving gear 18 engaged with speedup driven gear 11; Vibration damping torsion spring 19 is sleeved on input shaft 15, and vibration damping torsion spring 19 two ends are fixedly connected in top gear driving gear 17 and speed increase driving gear 18 respectively.
All the other structures of the present embodiment are identical with embodiment 5, do not repeat them here.
Native system can adopt following methods automatically to control, and is obtained the signal of push rod 6 desired location by the Hall element 22 of position probing; The signal of this desired location is combined with the drive motor current detecting information signal of speed variator system and forms this drive motor power switch control signal, this control signal is used for being in desired location at push rod 6, and current of electric is when reaching setting value, after cutting off the drive motor power settings time, restart drive motor.
For the spiral double rolling key clutch of embodiment 3, and there is the variable-speed shaft of this clutch and the controlling method of speed variator system, when needs oppositely export; Control system driving power reverse start while, connect apply described electromagnetic resistance electromagnetic coil 30b set time after power-off.
More than describe preferred embodiment of the present utility model in detail.Should be appreciated that those of ordinary skill in the art just can make many modifications and variations according to design of the present utility model without the need to creative work.Therefore, all technician in the art according to design of the present utility model on the basis of existing technology by the available technological scheme of logical analysis, reasoning, or a limited experiment, all should by the determined protection domain of claims.
Claims (14)
1. a spiral double rolling key clutch structure, comprise the rotating plate-like driving link (14) be sleeved on line shaft (2), driving link (14) is combined with helical spline cover (30) by helical spline structure, helical spline cover (30) both sides are respectively equipped with first end face (31) and the second end face disk (32), first end face (31) is all fixedly connected with described line shaft (2) with the second end face disk (32), helical spline cover (30) is respectively by first end face (31) and the second end face disk (32), and the unidirectional tooth of intermeshing end face, form the first one-way clutch structure and the second one-way clutch structure respectively, first one-way clutch structure and the second one-way clutch structure are respectively used to drive line shaft (2) synchronously to rotate forward and synchronous reversion by helical spline cover (30), helical spline structure between helical spline cover (30) and driving link (14), has and promotes the Hand of spiral of helical spline cover (30) towards first end face (31) movement when driving link (14) rotates forward, it is characterized in that, between described helical spline cover (30) and described second end face disk (32), be provided with an elastic element (33), form normally closed and normally open respectively to make the first one-way clutch structure and the second one-way clutch structure, helical spline cover (30) is outside is provided with one only when helical spline cover (30) counterrotating by a static component, applies the one-way check device of resistance to helical spline cover (30).
2. spiral double rolling key clutch structure according to claim 1, it is characterized in that, described helical spline cover (30) is set with a C shape snap ring (34) with stop handle (34a) by frictional connection mode, described one-way check device comprises an active block stop (35), on active block stop (35) hinged stopper seat (36), stopper seat (36) is fixedly connected on static component, is provided with block torsion spring (37) between active block stop (35) and stopper seat (36); When described helical spline cover (30) rotates forward, C shape snap ring (34) by stopping that handle (34a) overcomes block torsion spring (37) elastic force, and is oppressed active block stop (35) beat and is formed and dodge space to C shape snap ring (34).
3. spiral double rolling key clutch structure according to claim 2, it is characterized in that, hinging shaft (36a) axis being parallel of described active block stop (35) is in the spin axis of helical spline cover (30), active block stop (35) C shape snap ring (34) reverse head-on in notch, and there is along the axis of described helical spline cover (30) movement the prevent surface (35a) of preseting length.
4. spiral double rolling key clutch structure according to claim 3, it is characterized in that, the hinge point of described active block stop (35) is in rear end, active block stop (35) upper side is by articulated section to notch portion, and the direction that the axis along the movement of described helical spline cover (30) increases gradually by size extends.
5. spiral double rolling key clutch structure according to claim 2, it is characterized in that, hinging shaft (36a) axes normal of described active block stop (35) is in the spin axis of helical spline cover (30), and what active block stop (35) rotated forward at C shape snap ring (34) heads in skewed.
6. spiral double rolling key clutch structure according to claim 1, is characterized in that, described one-way check device comprises and is located on static component and is enclosed within the outside electromagnetic coil (30b) of described helical spline cover (30).
7. according to the spiral double rolling key clutch structure in claim 1 ~ 6 described in any one claim, it is characterized in that, described helical spline cover (30) is engaged in the side that described driving link (14) is positioned at the second end face disk (32); Helical spline cover (30) the other end is provided with multiple circumference uniform distribution, and the connection pawl (30a) that can be passed by the hollow out (14a) in driving link (14) epiplastron portion, helical spline cover (30) forms described first end-engaging clutch structure by this connection pawl (30a) and described first end face (31).
8. spiral double rolling key clutch structure according to claim 1, is characterized in that, described helical spline cover (30) is in internal spline structure, and helical spline cover (30) is engaged on the helical spline axle journal of described driving link (14).
9. spiral double rolling key clutch structure according to claim 1, is characterized in that, described helical spline cover (30) is in external splines structure, and helical spline cover (30) is engaged in the Turbo Flora keyhole of described driving link (14).
10. a variable-speed shaft, it is characterized in that, comprise the spiral double rolling key clutch structure in claim 1 ~ 9 described in any one, the driving link (14) of this structure forms bottom gear driven gear, line shaft (2) is also provided with top gear driven gear (1), top gear driven gear (1) is connected with line shaft (2) by mono-directional overrun clutch; Or be formed with mono-directional overrun clutch structure between top gear driven gear (1) and line shaft (2).
11. variable-speed shafts according to claim 10, is characterized in that, described mono-directional overrun clutch structure forms unidirectional super conjunction device by drive end (3) and the intermeshing unidirectional end-tooth of driven end (4); Drive end (3) is integrally formed on driving disc (1), and what driven end (4) can be moved axially by helical spline structure is engaged on line shaft (2); Driven end (4) is connected with centrifugal delivery device, for pushing driven end (4) to drive end (3) under setting speed condition; Driven end (4) middle part is connected with push rod (6) by bearing pin (5), and push rod (6) is engaged in the mider hole of line shaft (2), line shaft (2) is formed with push rod (6) movement space and runs through groove (6a); Be provided with Returnning spring (7) between bottom push rod (6) bottom and mider hole, the outer end that push rod (6) stretches out line shaft (2) corresponding axle head is fixedly connected with magnet steel (8).
12. 1 kinds of automatic speed-changing systems, is characterized in that, comprise variable-speed shaft described in claim 10 or 11, and the line shaft (2) of this variable-speed shaft is fixedly connected with output gear (13), and the driving link (14) on line shaft (2) forms bottom gear driven gear; The power input front end of line shaft (2) is also provided with input shaft (15), this input shaft (15) is provided with can with the synchronous bottom gear driving gear (16) initiatively of input shaft (15) and top gear driving gear (17), and bottom gear driving gear (16) and top gear driving gear (17) distinguish the driving link (14) of correspondence and described formation bottom gear driven gear and top gear driven gear (1) often engages.
13. automatic speed-changing systems according to claim 12, it is characterized in that, described top gear driving gear (17) is connected by spline fitted with between input shaft (15), spline width of keyway on top gear driving gear (17) is greater than the spline width of input shaft (15) spline shaft, and top gear driving gear (17) and input shaft (15) are provided with vibration damping torsion spring (19).
14. automatic speed-changing systems according to claim 13, is characterized in that, described input shaft (15) are also fixedly connected with speed increase driving gear (18); Described vibration damping torsion spring (19) is sleeved on input shaft (15), and vibration damping torsion spring (19) two ends are fixedly connected in top gear driving gear (17) and speed increase driving gear (18) respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520982211.XU CN205226159U (en) | 2015-12-02 | 2015-12-02 | Two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520982211.XU CN205226159U (en) | 2015-12-02 | 2015-12-02 | Two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system |
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| Publication Number | Publication Date |
|---|---|
| CN205226159U true CN205226159U (en) | 2016-05-11 |
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|---|---|---|---|
| CN201520982211.XU Expired - Fee Related CN205226159U (en) | 2015-12-02 | 2015-12-02 | Two -way freewheel clutch structure of spiral, variable speed axle and automatic speed changing system |
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| CN (1) | CN205226159U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107461464A (en) * | 2016-06-03 | 2017-12-12 | 许红英 | Electric car multi-shifting speed variator |
| CN113969974A (en) * | 2020-07-23 | 2022-01-25 | 浙江双菱亿鑫动力科技有限公司 | Self-shifting system of transmission |
| CN114001156A (en) * | 2021-11-23 | 2022-02-01 | 重庆宗申集研机电科技有限公司 | Gear shifting mechanism and two-gear automatic gear shifting system |
-
2015
- 2015-12-02 CN CN201520982211.XU patent/CN205226159U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107461464A (en) * | 2016-06-03 | 2017-12-12 | 许红英 | Electric car multi-shifting speed variator |
| 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 |
| CN113969974A (en) * | 2020-07-23 | 2022-01-25 | 浙江双菱亿鑫动力科技有限公司 | Self-shifting system of transmission |
| CN114001156A (en) * | 2021-11-23 | 2022-02-01 | 重庆宗申集研机电科技有限公司 | Gear shifting mechanism and two-gear automatic gear shifting system |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
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Granted publication date: 20160511 Termination date: 20181202 |