CN104791451A - Differential stop device for vehicle - Google Patents
Differential stop device for vehicle Download PDFInfo
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- CN104791451A CN104791451A CN201510214805.0A CN201510214805A CN104791451A CN 104791451 A CN104791451 A CN 104791451A CN 201510214805 A CN201510214805 A CN 201510214805A CN 104791451 A CN104791451 A CN 104791451A
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- gear
- shaft
- relay
- synchronizer
- pto
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a differential stop device for a vehicle. The differential stop device comprises a differential mechanism, a synchronizing device enabling two power output shafts of the differential mechanism to be synchronous, a left wheel axle and a right wheel axle. The synchronizing device comprises a synchronizing shaft, a linkage mechanism inserted into one end of the synchronizing shaft, and a second linkage gear fixedly arranged at the other end of the synchronizing shaft. The left wheel axle and the right wheel axle are meshed with the two power output shafts of the differential mechanism respectively through the linkage mechanism and the second linkage gear. When one drive wheel of the vehicle gets stuck, the synchronizing device enables the left wheel axle and the right wheel axle to be synchronous, the differential function of the differential mechanism is isolated, the left wheel axle and the right wheel axle can obtain identical power and torque, and after the stuck wheel obtains the power, the vehicle can get out of the trap more easily.
Description
Technical field
The present invention relates to a kind of automobile-used differential short stopping device.
Background technique
At present a lot of vehicle all installs differential mechanism additional, improve the stability of turn inside diameter, but to be stuck or vehicle is fallen at a driving wheel of vehicle, the wheel be stuck can not get power, and there is no mad turn of stuck wheel, vehicle is caused to get rid of poverty, and do not install the words of differential mechanism additional, the wheel of turn inside diameter or both sides needs the effect that can not reach again distribution according to need power when different dynamic, therefore also bring some problems when the application of differential mechanism adds power to vehicle run stability simultaneously, the tire that is limited of vehicle can not be made to obtain enough power.
Summary of the invention
The object of the invention is to the defect overcoming prior art, a kind of device can cancelling differential mechanism function according to actual needs is at any time provided, improve the ability of getting rid of poverty of vehicle and the automobile-used differential short stopping device of passing capacity.
For solving the problem, the technical solution used in the present invention is:
A kind of automobile-used differential short stopping device, it comprises differential mechanism, can make two of differential mechanism synchronizers that pto＝power take-off is synchronous and two, left and right wheel shaft; Described synchronizer comprises synchronizing shaft, is inserted into the linking mechanism of synchronizing shaft one end and is arranged on the second linkage gear of the synchronizing shaft the other end, and two, described left and right wheel shaft engages with two pto＝power take-offs of differential mechanism respectively by linking mechanism and the second linkage gear.
Furtherly, described linking mechanism is synchronizer or shifting fork piece, the first linkage gear be sleeved on synchronizing shaft and the synchronizer be inserted into by spline on synchronizing shaft is comprised when described linking mechanism is synchronizer, described synchronizer side is fixedly connected with the first linkage gear, opposite side and synchronizing shaft clamping; Comprise when described linking mechanism is shifting fork piece and be inserted into the first linkage gear on synchronizing shaft by spline and be arranged on the shifting fork piece of the first linkage gear side, described shifting fork piece side is provided with shift fork, and the moving tooth holding of described shift fork is in shifting fork piece both sides.
Furtherly, described synchronizing shaft is the transmission shaft connected by clutch.
Furtherly, also comprise relay facility, described linking mechanism engages with wheel shaft and differential mechanism pto＝power take-off respectively by two relay facilities, and described relay facility is gear train or transmission shaft group.
Furtherly, described gear train is located by back shaft and be slidably connected two relay gears, and two one of them relay gears of described relay gear engage with wheel shaft, and another engages with differential mechanism pto＝power take-off.
Furtherly, described two relay gears are identical, and described relay gear is cylindrical gears or trapezoidal gear.
Furtherly, described transmission shaft group comprises relay axis and relay gear, described relay axis one end is engaged with synchronizing shaft, the other end is connected with relay gear and pto＝power take-off respectively, described wheel shaft is engaged with relay axis by relay gear, and gear and the relay gear at described relay axis two ends are umbrella gear.
Furtherly, described transmission shaft group comprises relay axis and a connecting shaft, and described relay axis one end is engaged with synchronizing shaft, and the other end engages with a connecting shaft one end, described the connecting shaft the other end engages with differential mechanism pto＝power take-off and wheel shaft respectively, and the gear at described relay axis two ends is umbrella gear.
Furtherly, described wheel shaft and differential mechanism pto＝power take-off concentric are arranged, and are provided with the back shaft of locating also sliding bearing and being connected between described wheel shaft with differential mechanism pto＝power take-off.
Furtherly, described differential mechanism pto＝power take-off is engaged with synchronizer by trapezoidal gear, described wheel shaft is engaged with synchronizer by trapezoidal gear, described first linkage gear and the second linkage gear are multi-joint trapezoidal gears, connect trapezoidal described first linkage gear and/or the second linkage gear slides and is located on synchronizing shaft, and described synchronizing shaft is provided with the spline for clamping linkage gear at the axle head of the first linkage gear and/or the second linkage gear engagement synchronizer.
The beneficial effect adopting technique scheme to produce is: time vehicle driving wheel is stuck, synchronizer is by synchronous for two, left and right wheel shaft, now the differential function of differential mechanism is just isolated, revolver axle and right wheel shaft can obtain identical power and moment of torsion, after being obtained power by the wheel of card, vehicle is got rid of poverty easier.
Left and right sides pto＝power take-off and wheel shaft are interrupted separately again by can the synchronizer of folding be connected, so just can realize the effect isolating synchronous two wheel shafts of differential mechanism, the folding of synchronizer can use shift fork to drive folding, also can pass through synchronizer folding, these two kinds of open-close ways can complete the folding requirement of synchronizer.
The two ends of synchronizing shaft can also be connected by clutch, and add the flexibility of synchronizer and the smoothness of folding, folding with convenience is controlled, with differential mechanism with the use of the flexibility that can increase vehicle power and export.
Relay facility can be set up between synchronizing shaft and wheel shaft, differential mechanism pto＝power take-off, first the Steering of each axle gear-driven can be improved, secondly the length of whole driving mechanism can be adjusted, reduce length, i.e. whole driving mechanism relative distance, driving cog ratio can also be made to have Multiple Combination, be applicable to the multiple requesting of complex road condition.
Gear train can be four relay gears, two pto＝power take-offs, two wheel shafts are engaged with synchronizer, synchronizer is again by synchronous by two wheel shafts about clutch for clutch control of shift fork or synchronizer, four gear apportion synchronizing shaft two ends, arrange back shaft between adjacent two, back shaft does not only have transmission for location.
When relay gear during trapezoidal gear, can change the moment of torsion that pto＝power take-off is passed to wheel shaft, such wheel can obtain multiple even twisting moment, increases the ability that vehicle adapts to various special circumstances.
Increase and use relay axis to coordinate turning to of the such pto＝power take-off of taper relay gear just identical with wheel axle steer again, change minimum to existing automotive power transmission system, the spacing of synchronizer and differential mechanism can be widened, simple structure, high reliability.
Two relay gears can also replace with one connecting shaft, such pto＝power take-off and wheel shaft stable with same meshed transmission gear, fast response time.
All concentric gears in the technical program or axle, can install back shaft additional between adjacent gear and axle, or the gear of single greater depth can install back shaft additional, and whole like this transmission system is more stable, and reliability is high.
Change into multiple different moment of torsion in order to make the moment of torsion of pto＝power take-off by synchronizer to export, second linkage gear and the first linkage gear are the wheels (nest) of fixing series winding, be coordinate with trapezoidal gear to switch and pitch wheel group, stir the moment of torsion that just can change wheel shaft and obtain like this along with the second linkage gear and/or the first linkage gear.
Accompanying drawing explanation
Accompanying drawing 1 is the embodiment of the present invention one structural representation;
Accompanying drawing 2 is the embodiment of the present invention two structural representations;
Accompanying drawing 3 is the embodiment of the present invention three structural representations;
Accompanying drawing 4 is the embodiment of the present invention four structural representations;
Accompanying drawing 5 is the embodiment of the present invention five structural representations;
Accompanying drawing 6 is the embodiment of the present invention six structural representations;
Accompanying drawing 7 is the embodiment of the present invention seven structural representations;
Accompanying drawing 8 is that the embodiment of the present invention eight becomes moment of torsion linkage structure schematic diagram;
Accompanying drawing 9 is the embodiment of the present invention eight even twisting moment linkage structure schematic diagram;
Accompanying drawing 10 is that the embodiment of the present invention nine becomes moment of torsion linkage structure schematic diagram;
Accompanying drawing 11 is the embodiment of the present invention nine even twisting moment linkage structure schematic diagram;
Accompanying drawing 12 is that the present invention pulls out shaft type shift fork clutch separation status architecture schematic diagram;
Accompanying drawing 13 is that the present invention pulls out shaft type shift fork clutch bonding state structural representation;
Accompanying drawing 14 is that the present invention pulls out shaft type shift fork clutch bushing profile status structural representation;
Accompanying drawing 15 is that the present invention pulls out shell type shift fork clutch separation status architecture schematic diagram;
Accompanying drawing 16 is that the present invention pulls out shell type shift fork clutch bonding state structural representation;
Accompanying drawing 17 is that the present invention pulls out shell type shift fork clutch bushing profile status structural representation;
Accompanying drawing 18 is that synchronizer clutch of the present invention is from status architecture schematic diagram;
Accompanying drawing 19 is synchronizer clutch bonding state structural representations of the present invention;
Accompanying drawing 20 is synchronizer clutch bushing profile status structural representations of the present invention;
Accompanying drawing 21 is the present invention different axle center pulling axis clutch combining structure schematic diagram;
Accompanying drawing 22 is the present invention different axle center pulling axis clutch separation structural representations;
Accompanying drawing 23 is the embodiment of the present invention ten structural representations;
Accompanying drawing 24 is the embodiment of the present invention five shifting fork piece linkage structure schematic diagram;
Accompanying drawing 25 is the embodiment of the present invention six shifting fork piece linkage structure schematic diagram;
Accompanying drawing 26 is the embodiment of the present invention seven shifting fork piece linkage structure schematic diagram;
In the accompanying drawings: 1 differential mechanism, 11 pto＝power take-offs, 12 wheel shafts, 21 relay axis, 22 relay gears, 23 connecting shafts, 3 synchronizing shafts, 31 second linkage gears, 32 first linkage gears, 33 synchronizers, 34 shift forks, 35 shifting fork pieces, 4 clutches, 5 back shafts, 36 connecting bushings, 37 splines.
Embodiment
Below in conjunction with accompanying drawing 1-26, detailed further describing is carried out to the present invention.
As shown in accompanying drawing 1-11, a kind of automobile-used differential short stopping device, it comprises differential mechanism 1, can make two of differential mechanism 1 synchronizers that pto＝power take-off 11 is synchronous and two, left and right wheel shaft 12; Described synchronizer comprises synchronizing shaft 3, is inserted into the linking mechanism of synchronizing shaft 3 one end and is fixedly installed on the second linkage gear 31 of the synchronizing shaft the other end, and two, described left and right wheel shaft 11 engages with two pto＝power take-offs 11 of differential mechanism 1 respectively by linking mechanism and the second linkage gear 31.Time vehicle driving wheel is stuck, synchronizer is synchronous by two, left and right wheel shaft, and now the differential function of differential mechanism is just isolated, and revolver axle and right wheel shaft can obtain identical power and moment of torsion, and after being obtained power by the wheel of card, vehicle is got rid of poverty easier.
Linking mechanism is synchronizer or shifting fork piece, the first linkage gear 32 be sleeved on synchronizing shaft 3 and the synchronizer 33 be inserted into by spline on synchronizing shaft 3 is comprised when described linking mechanism is synchronizer, described synchronizer 33 side is fixedly connected with the first linkage gear 32, opposite side and synchronizing shaft 3 clamping; Comprise when described linking mechanism is shifting fork piece 35 and to be inserted on synchronizing shaft 3 by spline and can part and rigid the first linkage gear 32 linked of synchronizing shaft and the shifting fork piece 35 being arranged on the first linkage gear 32 side, described shifting fork piece 35 side is provided with shift fork 34, and the moving tooth holding of described shift fork 34 is in shifting fork piece 35 both sides.Output power axle and wheel shaft separately by can the synchronizer of folding be connected, so just can realize the effect isolating synchronous two wheel shafts of differential mechanism, the folding of synchronizer can use shift fork to drive folding, also can pass through synchronizer folding, these two kinds of open-close ways can complete the folding requirement of synchronizer.
Synchronizing shaft 3 is the concentric shafts connected by clutch 4.The two ends of synchronizing shaft are connected by clutch, and add the flexibility of synchronizer, folding with convenience is controlled, coordinate the flexibility that can increase Power output with differential mechanism; Clutch 4 can be choosing dress, also can be the critical piece replacing whole linking mechanism function, and when clutch 4 is critical piece, each gear can or should be then that can only rotate can not being fixedly installed of displacement; Clutch 4 can be existing various applicable structural type in the market, also can be the structural type in rear attached instance graph.
It can be part spline joint also can be the Connecting format such as multicolumn hole that first linkage gear and synchronizing shaft rigid links.
Linking mechanism engages with differential mechanism 1 pto＝power take-off 11 with wheel shaft 12 respectively by two relay facilities, and described relay facility is gear train or transmission shaft group.Relay facility can be set up between synchronizing shaft and wheel shaft, differential mechanism pto＝power take-off, first the Steering of each axle gear-driven can be improved, secondly the length of whole driving mechanism can be made to reduce, driving cog ratio can also be made to have Multiple Combination, be applicable to the multiple requesting of complex road condition.
Gear train to be located by back shaft 5 and be slidably connected two relay gears 22, two described relay gears 22 1 engage with wheel shaft 12, and another engages with differential mechanism 1 pto＝power take-off 11.Gear train can be four relay gears, two pto＝power take-offs, two wheel shafts are engaged with synchronizer, synchronous again by two wheel shafts about shift fork, synchronizer or clutch for clutch control of synchronizer, four gear apportion synchronizing shaft two ends, arrange back shaft between adjacent two, back shaft does not only have transmission for location.
Two relay gears 22 are identical, and described relay gear 22 is trapezoidal gears.When relay gear during trapezoidal gear, can change the moment of torsion that pto＝power take-off is passed to wheel shaft, such wheel can obtain multiple even twisting moment, increases the ability that vehicle adapts to various special circumstances.
Transmission shaft group comprises relay axis 21 and relay gear 22, described relay axis 21 one end is engaged with synchronizing shaft 3, the other end is connected with relay gear 22 and pto＝power take-off 11 respectively, described wheel shaft 12 is engaged with relay axis 21 by relay gear 22, and gear and the relay gear 22 at described relay axis 21 two ends are umbrella gear.Increasing relay axis coordinates turning to of the such pto＝power take-off of relay gear just identical with wheel axle steer again, changes minimum, the spacing of synchronizer and differential mechanism can be widened, simple structure, high reliability existing automotive power transmission system.
Transmission shaft group comprises relay axis 21 and a connecting shaft 23, described relay axis 21 one end is engaged with synchronizing shaft 3, the other end engages with connecting shaft 23 one end, and described connecting shaft 23 the other end engages with differential mechanism pto＝power take-off 11 and wheel shaft 12 respectively, and the gear at described relay axis 21 two ends is umbrella gear.Two relay gears can also replace with one connecting shaft, such pto＝power take-off and wheel shaft stable with same meshed transmission gear, fast response time.
Wheel shaft 12 is arranged with differential mechanism 1 pto＝power take-off 11 concentric or parallel axle center, is provided with the back shaft 5 of locating also sliding bearing and being connected between described wheel shaft 12 with differential mechanism 1 pto＝power take-off 11.Can install back shaft additional between the gear of all adjacent concentric in the technical program or axle, back shaft 5 is only played a supporting role, and do not produce with the gear be connected or axle and link, be slidably connected, whole like this transmission system is more stable, and reliability is high.In following all embodiments back shaft 5 setting and effect do not repeating.
Differential mechanism 1 pto＝power take-off 11 is engaged with synchronizer by trapezoidal gear, described wheel shaft 12 is engaged with synchronizer by trapezoidal gear, described first linkage gear 32 and the second linkage gear 31 are trapezoidal gears of series connection, connect trapezoidal described first linkage gear 32 and/or the second linkage gear 31 slides and is located on synchronizing shaft 3, and described synchronizing shaft 3 engages synchronizer (synchronizing shaft 3) one end at the first linkage gear 32 and/or the second linkage gear 31 and is provided with spline for clamping synchronizing shaft 3 and the first linkage gear 32 and/or the second linkage gear 31.Change into multiple different moment of torsion in order to make the moment of torsion of pto＝power take-off by synchronizer to export, second linkage gear and the first linkage gear are that the degree of fixing series winding goes out wheels, be coordinate with trapezoidal gear to switch and pitch wheel group, stir the moment of torsion that just can change wheel shaft and obtain like this along with the second linkage gear and/or the first linkage gear.Described differential mechanism pto＝power take-off is engaged with synchronizer by nest, and described wheel shaft is engaged described wheel shaft by trapezoidal gear with synchronizer and engaged with synchronizer by nest.
Embodiment one: as shown in Figure 1, the pto＝power take-off 11 of differential mechanism 1 is engaged with relay gear 22 by the gear of relay axis 21 one end, wheel shaft 12 is passing through to engage with relay gear 22 again, like this when synchronizing shaft does not work, power is passed to wheel shaft 12 by pto＝power take-off 11, and the sense of rotation of wheel shaft 12 is identical with pto＝power take-off 11 sense of rotation; Shift fork 34 is stirred shifting fork piece 35 and is moved, thus the first linkage gear 32 is close and engage to the gear of relay axis 21 the other end, after engagement, two pto＝power take-offs 11 of differential mechanism 1 are by synchronously, thus two wheel shafts 12 are also by synchronously, now differential mechanism is by isolation functionally, but also in transferring power, just differential function is by locking; Clutch 4 on synchronizing shaft 3 is choosing dresses, can not have; In time having clutch 4, when synchronizer work, whether clutch 4 can also work by control synchronization device.The folding of single installation clutch 4 control synchronization device is also passable.When installing separately clutch 4, clutch can be with stirring the splined shaft and internal splined shaft bushing that connect, also can be synchronizer biting type or other clutch forms, and each gear when installing separately clutch 4 in this differential locking-device can be and is fixedly installed.
Embodiment two: as shown in Figure 2, be with embodiment one difference, shift fork 34 and shifting fork piece 35 are replaced by synchronizer 33, like this when synchronizer does not work, the side of the first linkage gear 32 and synchronizer 33 is synchronous with the wheel shaft 12 of homonymy, the opposite side of synchronizing shaft 3 and synchronizer 33 is another synchronous with the wheel shaft 12 of opposite side, and synchronizer 33 starts rear interlock first linkage gear 32 and synchronizing shaft 3 thus synchronous two wheel shafts 12.Synchronizer 33 one end and synchronizing shaft 3 clamping, the other end is fixedly connected with the first linkage gear 32, be synchronizer 33 two ends (side) each spinning when synchronizer does not start, synchronizer 33 starts the object that rear locked linkage gear and synchronizing shaft 3 reach synchronous two wheel shafts 12.
Embodiment three: as shown in Figure 3, be with embodiment one difference, wheel shaft 12 and homonymy pto＝power take-off 11 are engaged on one end of same connecting shaft 5, and connecting shaft 5 the other end is engaged by the second linkage gear 31 of relay axis 21 and synchronizer and the first linkage gear 32.
Embodiment four: as shown in Figure 4, identical with the difference of embodiment one with embodiment two with the difference of embodiment three (embodiment three is identical with the distinctive points of embodiment two with embodiment one with the distinctive points of embodiment four).Shift fork 34 and shifting fork piece 35 are replaced by synchronizer 33, like this when synchronizer does not work, second linkage gear 31 is synchronous with the wheel shaft 12 of side, and synchronizing shaft 3 is another synchronous with the wheel shaft 12 of side, and synchronizer 33 starts rear synchronous second linkage gear 31 and synchronizing shaft 3 thus synchronous two wheel shafts 12.
Embodiment five to the open-and-close mechanism shifting fork mechanism of the synchronizer of embodiment nine or synchronizer structure all the same with function, and the structure of clutch 4 on synchronizing shaft 3 and act on also identical, just no longer too much repeats in following embodiment.Figure 24 corresponding diagram 5 is its shifting fork piece linkage structure form, and Figure 25 corresponding diagram 6 is its shifting fork piece linkage structure form, and Figure 26 corresponding diagram 7 is its shifting fork piece linkage structure form.
Embodiment five: as shown in Figure 5, two pto＝power take-offs 11 directly engage with the second linkage gear 31 and the first linkage gear 32 respectively, two wheel shafts 12 also with respectively directly engage with the second linkage gear 31 and the first linkage gear 32 simultaneously, and the simple volume of structure is little.
Embodiment six: as shown in Figure 6, with the difference of embodiment five in, two pto＝power take-offs 11 and two wheel shafts 12 engage with synchronizing shaft 3 respectively by four relay gears 22.
Embodiment seven: as shown in Figure 7, with the difference of embodiment six in, four relay gears 22 are trapezoidal gears, are passed to the moment of torsion of wheel shaft 12 for changing pto＝power take-off 11.
Embodiment eight: as shown in Figure 8,9, with the difference of embodiment six in, relay gear 22, second linkage gear 31 and the first linkage gear 32 are all the trapezoidal gears of coupling mutually, different nip station can change wheel shaft 12 moment of torsion, as shown in Figure 8, now add the moment of torsion of wheel shaft, as shown in Figure 9, do not change the moment of torsion passing to wheel shaft 12 of pto＝power take-off 11.
Embodiment nine: as shown in Figure 10,11, with the difference of embodiment eight in, there is no relay gear, second linkage gear 31 and the first linkage gear 32 be all be inserted on synchronizing shaft 3 can folding and/or change the Gear combination of moment of torsion, as shown in Figure 10, now the moment of torsion simultaneously adding wheel shaft opened by synchronizer, and as shown in figure 11, now synchronizer does not work and do not change the moment of torsion passing to wheel shaft 12 of pto＝power take-off 11.
Embodiment ten, as shown in figure 23, be with embodiment nine difference, shift fork 34 drives the direction of the second linkage gear 31 and the engagement of the first linkage gear 32 contrary, this state is non-engagement state as shown in figure 23, when needing engagement, two shift forks 34 by the second linkage gear 31 and the first linkage gear 32 in the middle of clutch 4() stir, namely can complete engagement.
Axle in the technical program and gear can be all be arranged in a shell chamber by bearing, and clutch and synchronizer outside this shell chamber, can use oil sealing with joint, shell chamber.
Synchronizer has input end output terminal.Trapezoidal gear is also referred to as T-shaped gear, stepped gear, and umbrella gear is also referred to as bevel gear; Trapezoidal linkage gear of connecting refers to two trapezoidal gears be fixedly connected with, also referred to as the nest of T-shaped duplicate gear or series connection; Spline 37 prolongs circumference on a shaft to arrange more than one chute, and the gear be inserted into can move freely the torsion (moment of torsion) that can also obtain axle simultaneously and transmit.Multi-joint trapezoidal gear is that multiple trapezoidal gear series winding is arranged.
Change into multiple different moment of torsion in order to make the moment of torsion of pto＝power take-off by master lock locking apparatus to export, first linkage gear can be the duplicate gear be slidably connected on synchronizing shaft, coordinate with T-shaped gear and switch and engage each other, like this along with the first linkage gear to be combined the moment of torsion of the torque power that wheel shaft just can be made to be changed that links with synchronizing shaft, and locking differential function simultaneously.
Change into multiple different moment of torsion in order to make the moment of torsion of pto＝power take-off by master lock locking apparatus to export, second linkage gear and the first linkage gear can be the nests of contacting that slides, coordinate with T-shaped gear and switch and engage each other, stirring and/or stirring the moment of torsion that just can change wheel shaft and obtain in the other direction while the first linkage gear like this along with the second linkage gear, and locking differential function.
In the technical program, relate to synchronizer and clutch, enumerate several synchronizer and the clutch that are applicable to the technical program below in conjunction with accompanying drawing 12-20;
As shown in accompanying drawing 12,13,14, one pulls out shaft type shift fork clutch, synchronizing shaft 3 is connected by clutch 4, the synchronizing shaft 3 of one end is directly fixedly connected with connecting bushing 36 one end, and the axle head of the synchronizing shaft 3 of the other end arranges spline 37, and this end is fixedly installed shifting fork piece 35, when clutch 4 needs to connect, shifting fork piece 35 stirred by shift fork 34 thus in the hole driving spline 37 end to be inserted into match, i.e. connecting bushing 36 the other end, two-part like this synchronizing shaft 3 is just fixed and reaches synchronous.The other end of the axle of certain slip is also slidably connected, and remains the transmission of moment of torsion.
As shown in accompanying drawing 15,16,17, one pulls out shell type shift fork clutch, with pull out shaft type unlike, shifting fork piece 35 is fixedly installed on connecting bushing 36, clutch 4 in conjunction with time, what shift fork 34 was stirred is, and connecting bushing 36 moves engages with spline 37 axle head, now two parts of synchronizing shaft 3 are motionless, connecting bushing 36 moves and two parts is connected, therefore the synchronizing shaft (one end of engaging with connecting bushing 36 all the time) of the other end is darker in the connecting bushing 36 plug-in mounting degree of depth, there is free activity space, move at connecting bushing 36 that to engage with spline 37 be to depart from.
As shown in accompanying drawing 18,19,20, a kind of synchronizer clutch, this scheme is separately positioned in two parts of synchronizing shaft 3 by two of synchronizer ends, two parts keep the running of concentric by connecting bushing 36, but do not link, in conjunction with time as the same synchronizer two ends of former synchronizer working principle combine, need movement one end equally by spline realization move axially.
As shown in accompanying drawing 21,22, a kind of different axle center pulling axis clutch, synchronizing shaft 3 is divided into the semiaxis of two all hearts of difference, a semiaxis arranges shifting fork structure, the engagement completing two semiaxis be separated, the other end of the semiaxis of movement arranges spline 37 and is connected with driving gear, and whether shift fork 34 is engaged by two parts being fixed on the shifting fork piece 35 control synchronization axle 3 on synchronizing shaft 3.
The above mode of execution is only the preferred embodiments of the present invention, and and the feasible enforcement of non-invention exhaustive.For persons skilled in the art, to any apparent change done by it under the prerequisite not deviating from the principle of the invention and spirit, all should be contemplated as falling with within claims of the present invention.
Claims (10)
1. an automobile-used differential short stopping device, is characterized in that: it comprises differential mechanism (1), the synchronizer that two pto＝power take-offs (11) of differential mechanism (1) can be made synchronous and two, left and right wheel shaft (12); Described synchronizer comprises synchronizing shaft (3), is inserted into the linking mechanism of synchronizing shaft (3) one end and is arranged on second linkage gear (31) of the synchronizing shaft the other end, and two, described left and right wheel shaft (12) is engaged with two pto＝power take-offs (11) of differential mechanism (1) respectively by linking mechanism and the second linkage gear (31).
2. one according to claim 1 automobile-used differential short stopping device, it is characterized in that: described linking mechanism is synchronizer or shifting fork piece, the first linkage gear (32) be sleeved on synchronizing shaft (3) and the synchronizer (33) be inserted into by spline on synchronizing shaft (3) is comprised when described linking mechanism is synchronizer, described synchronizer (33) side is fixedly connected with the first linkage gear (32), opposite side and synchronizing shaft (3) clamping; Comprise when described linking mechanism is shift fork and be inserted into the first linkage gear (32) on synchronizing shaft (3) by spline (37) and be arranged on the shifting fork piece (35) of the first linkage gear (32) side, described shifting fork piece (35) side is provided with shift fork (34), and the moving tooth holding of described shift fork (34) is in shifting fork piece (35) both sides.
3. one according to claim 1 and 2 automobile-used differential short stopping device, is characterized in that: described synchronizing shaft (3) is the transmission shaft connected by clutch (4).
4. one according to claim 3 automobile-used differential short stopping device, it is characterized in that: also comprise relay facility, described linking mechanism engages respectively by the pto＝power take-off (11) of two relay facilities with wheel shaft (12) and differential mechanism (1), and described relay facility is gear train or transmission shaft group.
5. one according to claim 4 automobile-used differential short stopping device, it is characterized in that: described gear train is located by back shaft (5) and be slidably connected two relay gears (22), two one of them relay gear of described relay gears (22) (22) are engaged with wheel shaft (12), and another engages with the output shaft (11) of differential mechanism (1) power.
6. one according to claim 5 automobile-used differential short stopping device, is characterized in that: described two relay gears (22) are identical, and described relay gear (22) is cylindrical gears or trapezoidal gear.
7. one according to claim 4 automobile-used differential short stopping device, it is characterized in that: described transmission shaft group comprises relay axis (21) and relay gear (22), described relay axis (21) one end is engaged with synchronizing shaft (3), the other end is connected with relay gear (22) and pto＝power take-off (11) respectively, described wheel shaft (12) is engaged with relay axis (21) by relay gear (22), and gear and the relay gear (22) at described relay axis (21) two ends are umbrella gear.
8. one according to claim 4 automobile-used differential short stopping device, it is characterized in that: described transmission shaft group comprises relay axis (21) and a connecting shaft (23), described relay axis (21) one end is engaged with synchronizing shaft (3), the other end engages with connecting shaft (23) one end, described connecting shaft (23) the other end engages with differential mechanism pto＝power take-off (11) and wheel shaft (12) respectively, and the gear at described relay axis (21) two ends is umbrella gear.
9. the automobile-used differential short stopping of the one according to any one of claim 4-8 device, it is characterized in that: described wheel shaft (12) and differential mechanism (1) pto＝power take-off (11) concentric are arranged, between described wheel shaft (12) with differential mechanism (1) pto＝power take-off (11), be provided with the back shaft (5) of locating also sliding bearing and being connected.
10. one according to claim 3 automobile-used differential short stopping device, it is characterized in that: described differential mechanism (1) pto＝power take-off (11) is engaged with synchronizer by trapezoidal gear, described wheel shaft (12) is engaged with synchronizer by trapezoidal gear, described first linkage gear (32) and the second linkage gear (31) are multi-joint trapezoidal gears, connect trapezoidal described first linkage gear (32) and/or the second linkage gear (31) slides and is located on synchronizing shaft (3), described synchronizing shaft (3) is provided with spline for clamping linkage gear at the axle head of the first linkage gear (32) and/or the second linkage gear (31) engagement synchronizer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510214805.0A CN104791451A (en) | 2015-04-30 | 2015-04-30 | Differential stop device for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510214805.0A CN104791451A (en) | 2015-04-30 | 2015-04-30 | Differential stop device for vehicle |
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| Publication Number | Publication Date |
|---|---|
| CN104791451A true CN104791451A (en) | 2015-07-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510214805.0A Pending CN104791451A (en) | 2015-04-30 | 2015-04-30 | Differential stop device for vehicle |
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| Country | Link |
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| CN (1) | CN104791451A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105257782A (en) * | 2015-10-26 | 2016-01-20 | 扬中市三环电热科技有限公司 | Driven mechanism for semi-automatic powder feeding machine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070135254A1 (en) * | 2005-12-14 | 2007-06-14 | Os Giken Co., Ltd. | Differential gears |
| CN101561038A (en) * | 2008-04-14 | 2009-10-21 | 熊涔博 | Hydraulic coupler type coupling limited slip differential |
| CN103195905A (en) * | 2013-04-08 | 2013-07-10 | 安宏亮 | Limited slip differential |
| CN204729580U (en) * | 2015-04-30 | 2015-10-28 | 郭英杰 | A kind of automobile-used differential short stopping device |
-
2015
- 2015-04-30 CN CN201510214805.0A patent/CN104791451A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070135254A1 (en) * | 2005-12-14 | 2007-06-14 | Os Giken Co., Ltd. | Differential gears |
| CN101561038A (en) * | 2008-04-14 | 2009-10-21 | 熊涔博 | Hydraulic coupler type coupling limited slip differential |
| CN103195905A (en) * | 2013-04-08 | 2013-07-10 | 安宏亮 | Limited slip differential |
| CN204729580U (en) * | 2015-04-30 | 2015-10-28 | 郭英杰 | A kind of automobile-used differential short stopping device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105257782A (en) * | 2015-10-26 | 2016-01-20 | 扬中市三环电热科技有限公司 | Driven mechanism for semi-automatic powder feeding machine |
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Application publication date: 20150722 |