CN101014785A - Variable torque biasing device - Google Patents
Variable torque biasing device Download PDFInfo
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- CN101014785A CN101014785A CN 200580025750 CN200580025750A CN101014785A CN 101014785 A CN101014785 A CN 101014785A CN 200580025750 CN200580025750 CN 200580025750 CN 200580025750 A CN200580025750 A CN 200580025750A CN 101014785 A CN101014785 A CN 101014785A
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Abstract
Various embodiments of a torque biasing device for a rotating transmission are disclosed, and which are operable to vary the proportion of the output torque transmitted to one or more output shafts. Multiple planetary gear sets are provided for speeding-up or slowing-down of one shaft with respect to another, under the control of a computer. The invention is particularly applicable to motor vehicles.
Description
The present invention relates to torque biasing device, relate in particular to the sort of device of the moment of torsion between each wheel that is applied to the dispenser motor vehicle.
Torque biasing device typically is used in the ratio that increases the driving torque of distributing to one of two live axles on the motor vehicle.A kind of device that is used to change a left side/right driving torque of each wheel that is delivered to motor vehicle has been described among the EP-A-0575121.This device typically comprises the planetary pinion train, and train has the control gear that is suitable for increasing and/or reducing some gear train element speeds, and the moment of torsion with scaling up is delivered to a live axle rather than another live axle thus.
Controllable torque biasing device is used on the motor vehicle, with in the turn inside diameter process by according to for example about sway rate, sway the relevant control algorithm of the time diffusion of acceleration and vehicle slip angle and distribute driving torque, with the influence traction with about the stability of swaying.
In the application on vehicle, an important requirement is to guarantee that each component parts is as far as possible reasonably little, so that the artificer of vehicle can have maximum design freedom.Also have, also must pay close attention to length/width ratio, weight, manufacturing and the complexity of assembling, the inertia and the cooling of rotational parts.
According to an aspect of the present invention, a kind of input that has is provided, two outputs and a torque biasing device that is in the planetary differential module between them, this planetary differential module comprises a gear ring that can be connected in described input, the central gear that can be connected in one of described two outputs, and another planetary pinion load-bearing member that can be connected in described two outputs, described planetary pinion load-bearing member has the dual planetary gear that in series is operated between described gear ring and the central gear
And this device also comprises a gear module and a control module, described gear module comprise two side by side planetary pinion and have two central gears that link together with common rotation, a gear ring of gear module is the planetary pinion load-bearing member that is connected in described differential module, and another gear ring of gear module can be connected in one of described two outputs
And control module is the speed that is suitable for changing the gear module load-bearing member, and the described differential module of setovering thus offers the big of another so that in use offer the torque ratio of one of described two outputs.
In this manual, so-called " control module " comprises " actuating module ".
According to a kind of modification of first aspect, gear module can have connection with the central gear on each gear ring of common rotation, the planetary pinion load-bearing member that is connected to differential module and another central gear that can be connected in one of described two outputs.
Preferably, this control module is suitable for both can increasing the rotating speed that also can reduce the load-bearing member of gear module.This control module can comprise break, and this break can be operated the load-bearing member of gear module is stopped operating.This control module can comprise the planetary pinion train, the gear ring of the planetary pinion load-bearing member that it has the central gear that is connected to break, be connected to described gear module and the planetary pinion load-bearing member that can be connected to described input.In such structure arrangement, can make the planetary pinion load-bearing member speedup of gear module with single break.
Preferably, one of described two outputs are axles, and two central gears of described gear module are coaxial with it.The central gear of described differential module also can be coaxial with the central gear of gear module.
In a preferred embodiment, another in described two outputs is axle, and two outputs are coaxial, but direction is opposite.
Control module preferably comprises a planetary pinion train, and it has the driving connection to one of described input and output.
In a preferred embodiment, control module comprises two breaks that can work independently and a planet control module train, two breaks can be with direct and indirect pattern operation, in Direct Model, a break is to connect into the load-bearing member of described gear module is stopped operating, and in indirect pattern, another break is to connect into the load-bearing member speedup that can make described gear module by described planet control module train.
In first embodiment, control module comprises the gear ring that can be connected to described input, the central gear that is connected to the load-bearing member of described gear module, dual planetary gear and planetary pinion load-bearing member, wherein, described two breaks are connected respectively on the planetary pinion load-bearing member of the planetary pinion load-bearing member of gear module and control module train.
In a second embodiment, control module comprise the planetary pinion load-bearing member that can be connected to described input, the central gear of the planetary pinion load-bearing member that is connected to gear module in the lump that is connected to described two breaks and be connected to another gear ring in described two breaks.
In the 3rd embodiment, control module comprises a planetary pinion load-bearing member that can be connected to described input, be connected to the central gear of one of described two breaks and be connected in the described break another and be connected to the gear ring of the planetary pinion load-bearing member of gear module.
In the 4th embodiment, control module comprises the planetary pinion load-bearing member and the gear ring that is connected to one of described break that are connected to gear module, be connected in the described break another central gear and the planetary pinion load-bearing member that can be connected to one of described two outputs.
In the 5th embodiment, control module comprises the planetary pinion load-bearing member and the central gear that is connected to one of described break that are connected to described gear module, be connected in the described break another gear ring and the planetary pinion load-bearing member that can be connected to one of described two outputs.
In the 6th embodiment, control module comprises a break and a planet control module train, the gear ring of the load-bearing member that this train comprises the load-bearing member that can be connected to described input, be connected to described gear module and the central gear that is connected to described break, thus can be directly and indirect pattern operate described break, in Direct Model, break is to connect into the load-bearing member of described gear module is stopped operating, and in indirect pattern, break is to connect into the load-bearing member speedup that can make described gear module by described planet control module train.
In the 7th embodiment, be provided with second gear module, it have two side by side the planetary pinion train and two central gears of binding with common rotation are arranged, a gear ring of second gear module can be connected to described input, and another gear ring of second gear module can be connected to described one in described two outputs, and control module comprises a break, and this break operationally directly makes in the planetary pinion load-bearing member of gear module one or another stop operating.
In a preferred embodiment, but break connects by the digital clutch of two independent actuation, one of them clutch operating is at the input side of the load-bearing member of described planet control module train, and the break side of another clutch connection that to be operation do between the load-bearing member of the gear ring of planet control module train and gear module.This device also can comprise two torque-limiter clutches, and they are series at described digital clutch respectively.In this preferred embodiment, the planetary pinion load-bearing member of described planet control module train can radially be in outside the planetary pinion load-bearing member of described gear module.
According to the present invention, a kind of transmission device comprises differential module, gear module and the control module that the common rotating shaft line is arranged, and these module arrangement become the bosom of axial series in gear module.Preferably, these modules comprise each planetary pinion that directly adjoins.
A first aspect of the present invention relates to a kind of transmission device with gear module, and gear module has connection each central gear with common rotation.
In a second aspect of the present invention, each gear ring connects with common rotation, and a central gear is to be connected on the planetary pinion load-bearing member of differential module, and another central gear is to be connected to one of described two outputs.In above-mentioned arbitrary embodiment, control module all can act on the planetary pinion load-bearing member of gear module.
In a third aspect of the present invention, each planetary pinion of gear module is to connect with common rotation, and a central gear is to be connected on the planetary pinion load-bearing member of differential module, and another central gear is to be connected in one of described two outputs.In above-mentioned arbitrary embodiment, control module all can act on the planetary pinion load-bearing member of gear module.
According to a forth aspect of the invention, provide a kind of torque biasing device that comprises gear module, and gear module has three planetary pinion trains, each train comprises central gear, planetary pinion, planetary pinion load-bearing member and gear ring; Member one of in centre tooth wheels and the gear ring group connects with common rotation; The member of another in centre tooth wheels and the gear ring group provides first output, second output and first control unit respectively; Two planetary pinion load-bearing members connect to one and second control unit are provided; First and second control units can be connected to the control module with revolution speed control device; And first input and second to import be the output that is suitable for being connected to differential gear respectively.
According to a fifth aspect of the invention, the gear module of fourth aspect can have the planetary pinion of connection with common rotation, and each central gear provides described first input, described second input and described first control unit respectively, and has omitted gear ring.
Preferably, a plurality of planetary pinion trains are side by side directly adjoined.
Control module can comprise first and second breaks, but or comprise that alternately is connected in the single break of first and second control units, perhaps can comprise the whirligig that rotating speed can raise and reduce, such as motor, and electric motor preferably.In a preferred embodiment, motor acts between first and second control units, need promptly answer ground to raise or the reduction relative rotation speed so that can have.
In order to lock this transmission device, can apply braking to first and second control units simultaneously, thereby stopping brake or emergency brake are provided.
Preferably, differential gear is the planetary differential device that common rotation axis is arranged with described gear module.This differential gear preferably has on described spin axis two output shafts in the opposite direction.
Preferably, this actuator or each break are arranged to round described axis and comprise the element that at least one can rotate on described axis.Two breaks can axially be provided with in succession along described axis, or center on described axis an inside that is arranged in another.In one situation of back, between two breaks a public base components can be arranged.
Preferably, be provided with the digital clutch that is series at this actuator or each break.So-called digital clutch is meant that here two states promptly mesh the clutch with disengaged condition.Such clutch can be used for alternately single break is connected to one or another control unit.Or disconnect driving simply to arbitrary break, to eliminate its internal drag or wearing and tearing.
According to a sixth aspect of the invention, a kind of transmission device is provided, it can have need carry out from live axle to the not moment of torsion transmission of driven wheel shaft under normal conditions with promptly answering, this transmission device comprises the input that is used to be connected to live axle, be used to have and promptly be connected to the output that is driven wheel shaft with answering, and gear module, this gear module comprises two planetary pinion trains side by side and that can rotate around common axis, connection with each central gear of the gear module of common rotation is, each gear ring of described input and described output can be connected respectively to, and a public planetary pinion load-bearing member that is constructed to be permeable to change the control module of its rotating speed can be connected to.
In a preferred embodiment, control module comprises a break, and it is used to have and need the planetary pinion load-bearing member is stopped operating, and makes the rear-wheel spindle hypervelocity thus thereupon.Correspondingly, the rear-wheel spindle of f-w-d vehicle can receive that one has the moment of torsion input that need promptly answer and makes its hypervelocity.Can give the vehicle that mainly has the front wheel driving characteristic with this rear driving characteristic.
According to a seventh aspect of the present invention, a kind of transmission device is provided with an input and an output, being driven into output thus is by the torque biasing module, this module comprises two planetary pinion trains side by side, each central gear of each gear train is to connect with common rotation, a gear ring is connected to input, and another gear ring is to be connected to output, the planetary pinion load-bearing member of each gear train is public, and this transmission device also comprises a break that is used for the planetary pinion load-bearing member, applies braking with break thus and can allow to carry out transmission between input and output.
Such transmission device can be from any motive force source has to a moment of torsion user need promptly provide variable moment of torsion with answering.
In another embodiment, input drives two outputs by the corresponding torque biasing module, each module comprises two planetary pinion trains side by side, each central gear of each gear train connects with common rotation, a gear ring of each gear train is connected to input, and another gear ring of each gear train is to be connected to corresponding output, and the public planetary pinion load-bearing member of each gear train is a break that is connected in separately, and break applies braking and can allow to carry out from being input to the transmission of output thus.
Such transmission device can offer driving the relative wheel of a wheel shaft, and need not common differential gear.
According to an eighth aspect of the invention, providing a kind of is used between two inputs, usually one of them is not driven wheel shaft of vehicle, the transmission device of driving torque, this transmission device comprises a gear module and a control module, gear module comprise two side by side and have the planetary pinion train of connection with two gear rings of common rotation, a central gear of each planetary pinion train is connected to corresponding input, and two planetary pinion load-bearing members connect to one, and control module comprises the planetary pinion train, this planetary pinion train has the gear ring of each gear ring that is connected to described connection, be connected to the central gear of first break, and be connected to second break and be connected to the planetary pinion load-bearing member of the planetary pinion load-bearing member of gear module, first break applies braking and can make driving torque be delivered to another input from an input thus, and second break applies braking and can make moment of torsion be delivered to a described input from described another input.
Preferably, these two inputs all are live axles and coaxial.Each planetary pinion train is preferably coaxial with these two live axles.
In first kind of replacement to eight aspect, each gear ring of gear module is connected on the planetary pinion load-bearing member of control module, and the planetary pinion load-bearing member of gear module is connected to the gear ring of control module, and the planetary pinion load-bearing member of gear module can be operated and directly act on to each break by the central gear of control module.
In second kind of replacement, each gear ring of gear module is to be connected to corresponding input, and each central gear of gear module connects with common rotation, the gear ring of control module is connected to the planetary pinion load-bearing member of gear module and is connected on first break, the central gear of control module is connected on second break, and the planetary pinion load-bearing member of control module is connected to the convenience center gear of gear module
In the third is replaced, the central gear of gear module and control module all connects with rotation together, each gear ring correspondingly is connected to first input, second input and is connected to first break, and the planetary pinion load-bearing member of gear module and control module all is connected to second break.
Comprising a planetary control module though eight aspect and various replacement thereof have been described, also is to adopt the part of this gear as gear module, is connected with necessary Mechanical Driven so that control module includes only each break.
According to a ninth aspect of the invention, can be coupling together according to a plurality of transmission devices of above All aspects of mode with cascade, each transmission device has an input and two outputs, and the input of a plurality of outputs as next transmission device in the cascade unit.
Such layout allows according to moment of torsion input to make a plurality of outputs have separately torque biasing, thereby for example is applicable to all the propulsion system and the various mechanical processing machine of the vehicle of wheel drive, boats and ships and need any device that need distribute be arranged to input torque with promptly answering between a plurality of parts or a plurality of full-time user.
It is according to determining from the signal of vehicle and other sensor by an outer computer that control module (actuating module) is applied to all embodiments.These sensors can provide about the steering angle of for example vehicle, about sway rate, wheel braking and vehicle wheel rotational speed information, and external information is for example about the information of vehicle location (for example GPS location) and pavement friction.Like this, in use, computer will determine whether the wheel of vehicle needs relative speedup or reduction of speed, and send control signal to torque biasing device, so that vehicle is made response according to predefined algorithm, and a kind of algorithm can be effectively thereby can continuously change according to each influence factor.Certainly user mode as requested provides several algorithms.The moment of torsion input can be provided by the torque sensor at the described of control module or each speed regulator place, so each output can have a torque sensor that feedback is provided.
Various types of breaks are all applicable to control module.A kind of preferable selection is the sort of multi-disc wet brake, and it has the disc-shaped component around a spin axis layout of several alternately plug-in mountings.Another kind of preferable layout is with a kind of magnetogenerator rheology break, wherein the working fluid between counterrotating parts can become thick hard and cause transmission between the rotary component, such break need be connected to a power supply, can avoid hydraulic pressure, pneumatic or mechanically actuated intrinsic complexity like this.
From convenient, brake assembly or other change the device of rotating speed should be installed around the spin axis of transmission device, and by one or more axially extended connections for example one or more form of sleeve interconnect function thereon.It is preferable that the device that brake assembly or other are changed rotating speed is installed in end, because easy of like this circumference and annular end face, for example is convenient to carry out power supply and control connects.
In the situation that two breaks are set, one of them can be inlaid in another inside or both be arranged side by side.In both of these case, all a public base components should be set preferably between two breaks.In the situation that a break and two digital clutches are set, also two clutch setting-ins can be got up or be arranged side by side, or be contained in the cylindrical housings of break.
According to the tenth aspect of the invention, a kind of magnetogenerator rheology break is provided, it comprises a plurality of alternately discoid driving element and the base components of plug-in mounting, driving element is suitable for driving from inboard radially, the device that is used to generate an electromagnetic field is arranged on the outside radially, the magnetogenerator Pheological fluid be can between described each disk, and be suitable for when described electromagnetic field generation device is energized, Pheological fluid is just set up the transmission between each disk.
Such layout can provide compact break, and it is suitable for being mounted to the driving axis around transmission device.By the diameter of increase discoid element or at the axial component number that increases, be easy to increase the torque capacity of this break.
In preferred embodiment, each element be annular and limit cylindrical inner volume, a double-action clutch is contained in this space, but this clutch has the public output that is connected to described break and two alternatelies to be connected to the input of corresponding rotatable driving component.
This layout can be break have need promptly answer ground connect and one of two rotatable members being modulated to transmission device provide the device of a compactness and the torque biasing transmission device that is specially adapted to describe in this specification.
Clutch preferably comprises the wind spring clutch that respectively adjoins, and each clutch has to have need promptly answer the ground engagement to drive the basic component of public output.In this preferred embodiment, public outlet is between the wind spring clutch of two symmetries, and driving component is tubulose, and is coaxial and be arranged on a side.
With a calutron each basic component is preferably meshed, this calutron is suitable for making the free element of wind spring to stop the rotation, and this will further describe later.
Display in the explanation of each preferred embodiment that other characteristics of the present invention will be below carried out with reference to accompanying drawing by example, in each accompanying drawing:
Fig. 1 is first embodiment's of torque biasing device a principle schematic.
Fig. 2 is second embodiment's of torque biasing device a principle schematic.
Fig. 3 is the 3rd embodiment's of torque biasing device a principle schematic.
Fig. 4 is the 4th embodiment's of torque biasing device a principle schematic.
Fig. 5 is the 5th embodiment's of torque biasing device a principle schematic.
Fig. 6 is the 6th embodiment's of torque biasing device a principle schematic.
Fig. 7 is the 7th embodiment's of torque biasing device a principle schematic.
Fig. 8 is the sectional view that embodies the transmission device of principle of the present invention as shown in fig. 1.
Fig. 9 has schematically shown magnetogenerator rheology break suite.
Figure 10 and 11 schematically shows the operation of wind spring clutch.
Figure 12 schematically shows and is used for the driving setting that having of wheel axle need promptly be answered.
Figure 13 and Figure 14 illustrate some embodiments with the half section of signal again, and these embodiments have two train gear modules.
Figure 15-18 illustrates the similar embodiment that some has two train gear modules with the half section of signal.
Figure 19-21 illustrates the control module of some replacement with the half section of signal.
Figure 22-27 illustrates the transmission device of the diagrammatic layout principle that embodies Figure 20 with end elevation, axial section and horizontal section.
Figure 28-30 illustrates some control module with the half section of signal, and they have the input from this actuator drives side.
Figure 31-34 illustrates some control module that is used for not being driven embodiment with the half section of signal.
Figure 35 and 36 half section with signal illustrate and are used to be driven some folk prescription of embodiment to the biasing setting.
Figure 37 shows the in-line driving setting that need promptly answer that has.
Figure 38 shows the embodiment that need promptly answer that has of two outputs, and
Figure 39 shows the tandem type of multiple arrangement and arranges that it can provide a plurality of controllable outputs from single input.
With reference to Fig. 1, input shaft 11 has apply the greatly cone gear 12 of gear ring 13 of planet differential of dot and dash line 14 expression of driving.This differential gear 14 has relative output shaft 15 and 16 (they can be the live axles of the wheel axle of vehicle).As shown in the figure, gear ring 13 drives central gear 18 by dual planetary gear 17, and central gear 18 and output shaft 16 couplings; Planetary pinion load-bearing member 19 and another output shaft 15 couplings.
A torque biasing device of showing dotted line 21 expressions greatly comprises three planetary pinion trains that are arranged side by side around output shaft 16.
Each planetary gear train comprises gear ring, planetary pinion, planetary pinion load-bearing member and central gear, and each element of each train connects in the following manner.
In use, can make an output shaft with respect to another output shaft speedup or reduction of speed with break 61 and 62 by alternately.
Fig. 2 illustrates the arrangement of gears identical with Fig. 1, but in this situation, single break 63 can be respectively digital clutch 64 and 65 by correspondence be connected in the 3rd gear ring 51 or planetary pinion load-bearing member 33.These two digital clutches are the wind spring clutches that for example can start by energized solenoids when needed, but also can adopt any other proper device.Break 61,62,63 can be any suitable type, such as having the multi-disc disc brake of magnetogenerator Pheological fluid as working medium.
As shown in Figure 2, break and digital clutch element can be arranged as break module 66, and this is convenient to make and be assembled to differential module 14 and be assembled to planetary pinion module 67.
The embodiment's of Fig. 2 operation is identical with Fig. 1's, just must be the digital clutch of correspondence and corresponding element 51,53 engagements.
Fig. 3 shows another embodiment of the present invention, and wherein planetary pinion module 167 comprises each gear ring that is connected into common rotation.The feature similar label identical with the embodiment of Fig. 1 and 2, the label in correspondence adds 100 exactly.
The embodiment of Fig. 3 comprises the break module of having described in differential module 14 and front 66.
Represented similar among gear module 167 and Fig. 1 and 2, but inner the connection be different.Specifically, three gear rings the 131,141, the 151st connect into a unit, and digital break 64 and 65 is to be connected to public planetary pinion load-bearing member 33 and the 3rd central gear 152.
A live axle 16 is connected in second central gear 142, and another live axle (by differential planet gear load-bearing member 19) is connected in first central gear 132.
Its operation is same as described above, and available break 63 makes an output shaft with respect to another output shaft speedup or reduction of speed by the connection of or another digital clutch 64,65.
Fig. 4 expresses a kind of setting, and differential gear is installed at its center that is applicable to four-wheel drive vehicle, also is applicable between each wheel of wheel axle and operates.Shared feature also is to adopt shared label, and represented layout is very closely corresponding to the layout (wherein each central gear connects into common rotation) of Fig. 2.The label of each corresponding part has added 200.
An input shaft 211 drives a differential gear module 214, and planetary pinion module 67 is to be connected in module 214, and a break module 66 comprises break 63 and digital clutch 64,65.
This gear module is identical with the gear module of Fig. 2, and has same inside and outside driving to connect, as shown in the figure.An output shaft 16 (for example being used for rear-wheel spindle) passes module 66,67 coaxially.Another output shaft (for example being used for front wheel spindle) can be drawn from one of two position 217a and 217b.In a kind of layout 217a, output gear 220 is bearing on the input shaft 211 and by the casing 200 of center gear ring 41 by differential module 214 with bearing and drives.Will be understood that because input shaft 211 is to be connected in this differential gear ring the output by this differential planet gear load-bearing member is prevented from.Suitable gear is connected with live axle moment of torsion is delivered to needed position from gear 220.But,, will be understood that also the output transmission can draw from any appropriate location along the outside of planetary pinion module 67 because this driving output is in the outside of first gear ring 31; Expressed a suitable alternative site 217b.
This embodiment's work is with above-mentioned identical.
Fig. 5 expresses a kind of setting corresponding to Fig. 4, but the public gear ring that it has is as shown in Figure 3 arranged.The similar label of shared part, the label in correspondence adds 300 exactly.
As shown in the figure, differential module 314 load-bearing member that has the central gear that is connected in input shaft 311 and be connected in first central gear of gear module 167.An output shaft 16 is driven by differential gear ring.Identical as shown in Figure 3, another output 217a need be driven by the differential planet gear load-bearing member, and this is the same with the embodiment of Fig. 4, is to realize by being connected to drive with axle with output gear 220 and then by suitable gear by differential casing 200 from position 217a.
Though will be understood that among the figure not show,,, have same possibility such as the 217b among Fig. 4 for the driving part of a replacement.
Fig. 6 and 7 expresses two replacement aspects of the present invention, and wherein the planetary pinion module does not have gear ring.The setting of Fig. 6 is similar to the setting of Fig. 3 in some aspects, and the similar label of common part, and Dui Ying label adds 400 exactly.
In Fig. 6, identical among differential module and break module 14,66 and Fig. 3.The planetary pinion module 467 of some simplification comprises and being arranged side by side but without any three planetary pinion trains of gear ring.These three trains have the public planetary pinion load-bearing member 33 that is connected in digital clutch 65, and another digital clutch 64 is to be connected in the 3rd central gear 452.
The difference of the layout of Fig. 6 and the layout of Fig. 3 is that its each planetary pinion connects into common rotation.Gear module each the input with Fig. 3 in be provided with identical, promptly from output shaft 16 to revenue centre gear 442 and from output shaft 15 to interior central gear 432.
As above-mentioned, the layout of this break can make output shaft 15,16 relative speedup or reductions of speed by one or another digital clutch 64,65.
The embodiment of Fig. 7 can be applicable to the central vehicle position of Fig. 5 equally corresponding to the embodiment of Fig. 6.The similar label of common means, Dui Ying label adds 500 exactly.With the embodiment of Fig. 6 roughly the same, gear module 567 does not have gear ring, but each planetary pinion is to connect into common rotation.Identical among break module 66 and differential module 314 and Fig. 5.
Except that the center portion, the embodiment's of Fig. 7 work is identical with Fig. 6's, as previously mentioned, for output position 217a, exists other possibility.
Transmission device shown in Fig. 8 is the embodiment of a reality of the principle arrangement shown in Fig. 1.Same part is with identical label.
Fig. 8 expresses a transmission device casing 10, and input shaft 11 and two output shafts 15,16 are with the bearing supporting within it; Each has with spline for example and is fixed into the therewith driven flange 71 of rotation.Input cone gear 12 drives output bevel gear 72, and gear 72 is gear ring 13 rotations that are tightened to planetary differential device 14.
Three planetary pinion trains are arranged to a module 67 abreast around output shaft 16, and connection each central gear 60 with common rotation is arranged.These gear trains between differential motion 14 and the break module 66 that constitutes by magnetogenerator rheology element, can with magnetogenerator rheology element optionally (by digital clutch) be engaged in each break input of transmission device casing 10.
A digital clutch can be connected to break on the public planetary pinion load-bearing member 33 of gear module 67, and another digital clutch can be connected to break on the gear ring 51 of the planetary gear train that adjoins.At input side, center gear ring 41 is driven by output shaft 15, and the gear ring 31 that adjoins differential gear 14 is driven by output shaft 16.
As required, suitable block bearing (roller bearing, ball bearing or sliding bearing) can be set, and spline is used in the connection between each adjacent part usually.As shown in FIG., casing 10 is made of three parts 10a, 10b, 10c, like this, allows load module individually 14,67,66 and tests.
As shown in Figure 8, moment of torsion guiding unit of the present invention can be very compact, and be convenient to one or another transmission shaft setting around vehicle axles.This device is from complete, and is easy to from the outside near break module 66, so that connect suitable power source.Each break that will be understood that this module can adopt hydraulic pressure, electronic, pneumatic or mechanically actuated, and by the outside at transmission device the connection that the break module can be convenient to carry out suitable control mechanism is set.
Fig. 9 illustrates the break that is applicable to the transmission device shown in Fig. 2-8 with the half section form of signal.Dot and dash line 80 expression center lines, in actual applications, it is the center line of output shaft 16.
Each digital clutch comprises a wind spring clutch, its can have by suitable electromagnetic coil need promptly answer ground engage and one in the input 87,88 or another be connected in gear ring 86.An advantage of clutch 64,65 is, when not engaging, disc assembly 82 is static relatively with respect to casing 10, and thereby reduce additional drag, and then can avoid the unnecessary shearing of magnetogenerator Pheological fluid.
Figure 10 and 11 schematically shows the operation of wind spring clutch.
At disengaged condition (Figure 10), live axle 90 has the wind spring 91 that stretches out and center on spin axis 92 from it.Driven shaft 93 can and put in the spring 91 around axis 92 rotations, but spaced radial is arranged between them.
The free end of this spring has a tongue handle 94 that axially stretches out, and this tongue handle is engaged on can be in a hole on the collar 95 of driven shaft 93 rotation and can be with respect to the hole axial motion.
The far-end of tongue handle has a static relatively electromagnet 96, and the optional for example low friction ring 97 of PTFE is contained between the collar 95 and the electromagnet 96.
As shown in Figure 10, live axle 90 can not rotate freely with respect to driven shaft 93 with not transmitting any moment of torsion, shown in arrow 98.
Figure 11 expresses closed state, and at this state, electromagnet is energized and attracts the collar 95.As a result, spring 91 binds round on driven shaft 93 and transmission of drive force tightly, shown in arrow 99.
In order clearly to represent working principle, the gap shown in Figure 10 and 11 has been exaggerated, and in the practical application, the radial clearance of wind spring is very little, and is suitable for almost just meshing with driven shaft at once.
The layout of Fig. 9 is expressed two digital clutches and is in same radius abreast.Perhaps, shown in Fig. 2-7, two clutches can be arranged on different radius, usually an inside that is inlaid in another.The number of the disk in the break of Fig. 9 should be chosen as certainly and adapt to desirable usefulness, and the volume of magnetogenerator Pheological fluid, the gap of necessity and the maximum magnetic field strength of coil also should be done same selection.All these variablees can be determined by suitable calculating and/or test experience ground.Figure 12 illustrates another embodiment of the present invention, and it is applicable to that the sort of a pair of wheel for good and all is driven and another is to the driven as required vehicle of wheel.
A kind of vehicle of front-wheel drive has rear vehicle shaft 500, and it comprises differential motion 501, relative semiaxis 502,503 and at the crown wheel/small gear 504 of input side.
The planetary driving device 505 of one two train have an output that is connected in rear-wheel spindle 500 506, one from the input 507 of front wheel spindle/motor and one can be as required promptly should be connected in the common carrier part 508 of break 509.Break 509 is the sort of magnetogenerator rheology type shown in Fig. 9 typically, and in order to reduce resistance as far as possible when not needing to brake, correspondingly is provided with a digital clutch 510 at input side.
This transmission device comprises a convenience center gear 511, each planetary pinion that can rotate freely around common carrier part 508 and is connected to input 507 and exports 506 gear ring 512,513.As shown in the figure, this transmission device is passed in output 506 coaxially.
In use, when break 509 was thrown off, transmission device can not transmitting torque, and correspondingly, trailing wheel is not driven.Like this, two semiaxis and each element of this transmission device all become freewheel, and vehicle is only by front-wheel drive.
But as long as break 509 1 engagement, load-bearing member will reduction of speed or is stopped, and produces the effect that makes the rear-wheel spindle speedup thereupon.Like this, can utilize hypervelocity that vehicle is had has the rear wheel drive characteristic that need promptly answer, thereby helps vehicle is turned rapidly.By the modulating brake device, can change output torque (the same) according to demand with other embodiment as herein described.
At the input side of break 509, and in the upstream of digital clutch 510, also comprise torque-limiter clutch 514, it can avoid transmission device is produced sudden surge when very unexpected meshing characteristic appears in a single day digital clutch.Torque-limiter clutch can comprise for example Belleville spring washer, to limit its transient load ability.
This embodiment is applicable to vehicle front-wheel axle or rear-wheel spindle is applied with the driving that need promptly answer, or the two-wheel drive under the normality of vehicle obtains the four-wheel drive that need promptly answer, or a kind of power output that need promptly answer that has is provided simply.
Figure 13 illustrates another embodiment of the present invention with the half section that is symmetrical in center line 600.
This embodiment comprises a differential module 601, a gear module 602 and an actuating (control) module 603.Input shaft 604 is drawn from the moment of torsion supplier (such as explosive motor), and this transmission device two output shafts 605 and 606 of having that direction stretches out on the contrary.
Actuating module comprises 621,622 and breaks 623 of two digital clutches, and they all are the above-mentioned types.Each digital clutch 621,622 all is connected with a torque-limiter clutch 624,625 with reference to Fig. 12 described the sort of types, and the input side of break 623 is provided with moment of torsion and speed probe 626.
Also be provided with a planetary pinion between two torque path relevant with each digital clutch, it comprises common gear ring 627, central gear 628, planetary pinion 629 and planetary pinion load-bearing member 630.
In use, two output shafts are delivered to front wheel spindle and rear-wheel spindle to moment of torsion, and this device allows to change torque ratio.Like this, for the acceleration performance that obtains, for example the torque distribution of front wheel spindle/rear-wheel spindle can be 40: 60; , it can be 60: 40 perhaps in order to obtain stable turn performance.
The connection description of the transmission device of Figure 13 is as follows.Input 604 drives differential gear ring 607 and the moment of torsion input is provided for one of digital clutch 621.First output 605 is gear rings 615 that are connected in gear module by differential planet gear load-bearing member 609.Another gear ring 614 is to be connected to output shaft 606, and it is also connected to differential central gear 608.The planetary pinion load-bearing member 619 of gear module provides the input of the second digital clutch 622, and also is connected in gear ring 627.At last, the output of digital clutch 621 is to be connected to break 623 by planetary pinion load-bearing member 630, planetary pinion 629 and central gear 628.
In operation, will directly distribute to this two axles according to the resistance of output shaft 605,606 to the ratio of rotating speed by differential module 601 from the driving torque of input 604, on vehicle, this ratio is decided by surface resistance.
If digital clutch 622 has meshed, and has applied resistance with break 623, load-bearing member 619 will be with respect to output shaft 606 reductions of speed, so it will be around 618 rotations of convenience center gear so.The planetary unequal velocity ratio that gear module is 602 li will cause the rotating speed deviation, and it will rely on interconnect function from gear ring 615 in differential load-bearing member 609.This gives output shaft 605 torque distribution from output shaft 606 with the bias difference moving gear then.
Break away from and under the situation of digital clutch 621 engagements at digital clutch 622, break 623 can provide resistance by the planetary pinion of actuating module 603, it has the effect of the rotating speed that increases load-bearing member 619, gives output shaft 606 torque distribution from output shaft 605 then.
Yes for break 623 under the control of an outer computer, and can be had and need lock or modulation with promptly answering, so that load-bearing member 619 has appropriate velocity variations, and distributing to another output shaft progressively from the moment of torsion of an output shaft.
Can obtain the locking of stopping by closed two digital clutches 621,622 and lockup brake 623.
Following form has been listed the state with the available non-limit of transmission device of Figure 13.
| | Clutch | 621 | |
|
Modulation |
| Bias |
Throw off | Throw off | Do not brake | Do not carry out | |
| The |
Closed | Closed | Do not brake | Do not carry out | |
| Starting or slow creep mode on parking lot or the hillside | Closed | Closed | | Lockup brake | 623 with provide the parking effect carry out/do not modulate with provide slowly creep or the hillside on starting select |
| Moment of torsion preferentially is directed to |
Throw off | Closed | Braking | Increased moment of torsion from |
|
| Moment of torsion preferentially is directed to |
Closed | Throw off | Braking | Increased moment of torsion from |
Figure 14 illustrates the transmission device corresponding to a kind of replacement of Figure 13, and wherein shared part is with identical label.Like this, differential module 601 is identical with the embodiment of Figure 13 with gear module 602, and identical connection is arranged.
Second gear module, 650 minute surfaces are symmetrical in gear module 602.Like this, with regard to module 602, an input of gear ring 654 is from output shaft 606.The input of another gear ring 655 of second module is from input shaft 604.Each central gear 658 of second gear ring is fixed together with common rotation, and load-bearing member 659 provides the input of digital clutch 621.
With aforementioned the same, according to modulating brake device 623 available braking torques, the engagement of or another digital clutch just can change the moment of torsion that is biased to output shaft 605,606.
The technician can understand, and the layout of Figure 14 is some shortcoming, because supply with the driving input that the power of actuating module 640 must stride across second gear module 650.Like this, for power supply, need with suitable slip ring or similar thing.The input of control computer (ECU) can be provided with torque sensor 626.
Figure 15-21 illustrates the face of land that several embodiments of the present invention are shown with half section figure.Common part is with identical label.
Figure 15 expresses a transmission device, and it has spin axis 700, differential gear module 710, torque biasing gear module 720 and activates (control) module 730.
Torque distribution gear module 720 comprises two planetary pinion trains side by side, and they have connection 727,729 and public planetary pinion load-bearing members 723 of central gear with common rotation.Also expressed planetary pinion 726,728, gear ring 724,725, they are connected respectively to differential planet gear load-bearing member 718, and are connected on the output shaft 713.Control module 730 acts on planetary pinion load-bearing member 723 to cause reduction of speed or speedup, changes the torque biasing from differential gear 710 thus, as aforementioned.
The embodiment of Figure 16 is similar to Figure 15, but gear ring 724,725 is linked together with common rotation.Thereby to connect be different, is exactly that the central gear 729,727 of torque biasing gear module is connected respectively to differential planet gear load-bearing member 718, and is connected on the output shaft 713.Equally, can operate the rotating speed that actuating module 730 changes planetary pinion load-bearing member 723.
Among Figure 17, the planetary pinion the 726, the 728th of biasing module 720 fuses, and gear ring 724,725 is not set.Connect with Figure 16 in identical.
Among Figure 18, planetary pinion 726,728 fuses, and central gear 727,729 is not set.Connect with Figure 15 in identical.
The embodiment of Figure 15-18 illustrates several different arrangement of gears, and according to the speed of estimating and the moment of torsion of available installation housing, predetermined application, these layouts can be to be suitable for separately.
Each embodiment of Figure 19-21 expresses the several different embodiments of the actuating module 730 of the biasing module 720 that is applied to convenience center gear (as shown in Figure 15).Be readily appreciated that these different actuating modules also can be applicable to public gear ring scheme (Figure 16) and public planetary pinion scheme (Figure 17 and 18).
Figure 19 is corresponding to Figure 15 and express a suitable actuating module 730 for example.Planetary pinion load-bearing member 723 can be connected in basis (transmission device casing typically) by one of two breaks 731,732 that can take turns flow operation.A break 731 directly acts on planetary pinion load-bearing member 723, and another works by planet actuating train 740.Like this, train 740 comprises that one is connected in input 711 planetary pinion load-bearing member 741, a gear ring 742 and a central gear 743 that is connected in second break 732 that is connected in planetary pinion load-bearing member 723.The effect of train 740 is to make planetary pinion load-bearing member 723 speedups when break 732 applies braking.
How Figure 20 can be connected in break 731,732 to the module 710,720 of Figure 18 respectively if illustrating.Specifically, break 732 is to be connected in gear ring 742, and load-bearing member 741 is to be connected in input 711.Equally, when break 732 applied braking, train 740 had the effect that makes planetary pinion load-bearing member 723 speedups.
Figure 21 illustrates how module 710,720 is connected in break 732 by a dual planetary gear.In this case, gear ring 742 is to be connected in input 711, and planetary pinion load-bearing member 741 is to be connected in break 732.
The layout of Figure 21 has provided bigger operation symmetry properties, has increased but shortcoming is the planetary pinion of 740 li of trains, and planetary pinion load-bearing member 741 is also more complicated.By adopting dual planetary gear, break 732 can act on planetary pinion load-bearing member 723 with the velocity ratio that is approximately identical to break 731.
Figure 22-27 expresses an embodiment corresponding to the schematic diagram of Figure 20.Corresponding part adopts identical label.
The end elevation of Figure 22 shows the conical shaped shape of this transmission device, and the axial sectional view of Figure 23 shows and how each parts is contained in the unit of a compactness easily, and wherein two coaxial breaks 731 and 732 are inlaid within another round 700 1 of spin axiss.
Figure 23 usually expresses the spin axis of each element of how arranging transmission device to obtain the device of a compactness.The planetary pinion the 727, the 729th of gear module links up with representational teeth groove structure.The axis of the axis of the planetary pinion load-bearing member of differential module 710, the axis of gear module 720 and actuating module 730 is the radius that reducing successively.The radius of gear ring 724 that adjoins differential module 710 is greater than the radius of the gear ring 725 that adjoins actuating module 730, thereby is provided with the spacer element of an annular.
Break the 731, the 732nd, radially one is inlaid in another inside and a public intermediate base element is arranged, as shown in the figure.All parts of this device all are contained in the housing of a substantial cylindrical, and each module 710,720,730,740 can assemble before general assembly and test individually.
Figure 24 is the cross section of differential module 710, and shows the dual planetary gear 715 and 716 between gear ring 714 and central gear 717.Output shaft 712 is connected in central gear 717 with spline, and input shaft 711 is connected in gear ring 714.Dual planetary gear load-bearing member 718 is to be connected on the gear ring 725 of the gear module 720 that adjoins control module 730.
Figure 25 is the first planetary cross section of gear module 720, and shows gear ring 724, central gear 729 and planetary pinion 726.Planetary pinion load-bearing member 723 is shared with second planetary pinion.
Figure 26 is corresponding to Figure 25 and express second planetary pinion of gear module, and it comprises gear ring 725, central gear 727, planetary pinion 728 and planetary pinion load-bearing member 723.
Figure 27 is the cross section of the planetary gear train of control module 730, and comprises gear ring 742, central gear 743, planetary pinion 744 and planetary pinion load-bearing member 741.
Connect identical shown in the schematic diagram with Figure 20.
Among Figure 28, another alternative embodiment provides from one of output shaft 713 rather than from importing 711 inputs to actuating module.Like this, the planetary pinion of this actuating module has a gear ring 742 and a planetary pinion load-bearing member 741 that is connected in output shaft 713 that is connected in planetary pinion load-bearing member 723.Break 731 and central gear 743 couplings, and break 732 acts on gear ring 742.
A kind of replacement that Figure 29 shows the layout that is used for Figure 28 connects, and wherein, break 732 is to be connected in planetary pinion load-bearing member 723.Break 731 works by a differential gear, and wherein gear ring 742 is to be connected in break 731, and planetary pinion load-bearing member 741 is driven by output shaft 713, and central gear 743 also is to be connected on the planetary pinion load-bearing member 723.
Another kind of again replacement that Figure 30 expresses the layout that is used for Figure 28 connects.In this case, first central gear of differential planet gear load-bearing member 718 actuation gear modules 720.Second central gear is connected on the output shaft 713.Two gear rings of gear module 720 couple together and the gear ring 742 of the planetary gear train of 730 li of drive control modules.The planetary pinion load-bearing member 741 of control module is connected to the planetary pinion load-bearing member of gear module 720, and is connected on the break 732.The central gear 743 of control module is connected on another break 731, as shown in the figure.
Each embodiment of Figure 28-30 expresses several alternatives, according in the predetermined applicable cases available installing space, can adopt these alternatives.
Figure 31-34 expresses several not driven embodiments with the half section of signal, and these embodiments are configured for changing the moment of torsion between two output shafts 801 and 802.Output shaft 801,802 connects by a moment of torsion guide gear module 810, and is under the control of actuating module 820.These two axles have common rotating shaft line 800.
As shown in the figure, the gear ring 822 of train 821 is connected to public gear ring 811,812, and central gear 823 is to be connected on one of two breaks 827.Another break 828 is to be connected on the planetary pinion load-bearing member 824, and the latter is connected on the public planetary pinion load-bearing member 815.
In operation, can be owing to the friction of output terminal, for example the corresponding tire of road vehicle and the friction between the road surface produce moment of torsion on each output shaft.By one or another break 827 or 828 are applied braking, can be between two axles the biased torque ratio.Like this, break 827 applies braking will make load-bearing member 815 speedups, and moment of torsion is delivered to another output shaft from an output shaft.Break 828 applies braking will make load-bearing member 815 reductions of speed, and produce opposite transfer function.
Figure 32 arranges corresponding to Figure 31 and a kind of replacement of expressing the differential gear of actuating module 820.Identical part is with same label.Change connection and make public gear ring 811,812 drive planetary pinion load-bearing members 824, and public planetary pinion load-bearing member 815 drives gear rings 822.Operational circumstances is with described identical with reference to Figure 31, and break 828 works to make planetary pinion load-bearing member 815 reductions of speed, and break 827 works to make its speedup.
One the 3rd embodiment shown in Figure 33 has the planetary pinion 817,818 that fuses in gear module 810, be connected to the output shaft 801,802 of gear ring 811,812, and central gear 813,814 connects the central gear 813,814 with common rotation.Like this, the input of actuating module 820 is to come from planetary pinion load-bearing member 815 and convenience center gear 813,814.
In this actuating module, planetary pinion has the gear ring 822 and the planetary pinion load-bearing member 824 that is driven by convenience center gear 813,814 that are driven by planetary pinion load-bearing member 815.Break 828,827 is connected respectively on planetary pinion load-bearing member 815 and the central gear 823.Working condition is same as described above, and break 828 plays the reduction of speed effect, and break 827 plays the speedup effect.
Another embodiment is shown in Figure 34, and it also has the output shaft 801,802 that drives gear ring 811,812 respectively.For illustrative purposes, the planetary gear train of gear module 810 comprises among the embodiment of Figure 23-25 and is expressed as the will that do star wheel series of the part of actuating module, thereby has three train axial series.
In these trains, public planetary pinion load-bearing member 815,824 is connected on the break 828.Central gear 813,814,823 links with common rotation, and the 3rd gear ring is to be connected on the break 827.Operational circumstances is same as described above.
901 and two of the inputs that are furnished with of Figure 35 export 902,903, are to represent with the half section that is symmetrical in spin axis 900.
The gear rings 913 that differential module 910 has dual planetary gear 911,912, driven by input 901, the central gears 914 that drive by output 903 and the planetary pinion load-bearing members 915 that drive by another output 902.
Figure 35 allows to make planetary pinion load-bearing member 925 reductions of speed (although also can realize speedup with the embodiment of one of the various embodiments described above and Figure 36, this will be described hereinafter) and can be used in the center differential motion of four-wheel drive vehicle, to reach the changeless torque biasing that is different between common front wheel spindle and the rear-wheel spindle.Shown in this embodiment in, biasing is unidirectional, because break 931 can only work to make planetary pinion load-bearing member 925 reductions of speed.
The embodiment of Figure 36 also provides a kind of unidirectional biasing, and it is similar to the layout of Figure 35.But in this case, actuating module is provided with a planetary gear train 940 for 930 li, and it acts on planetary pinion load-bearing member 925 by gear ring 941.The input of the planetary pinion load-bearing member 942 of train 940 is from input 901, and central gear 943 is and break 931 couplings.
Figure 37 expresses a kind of driving of throwing off with the half section of signal, for example throw off driven front wheel spindle and with mesh at the not driven rear-wheel spindle of normality or PTO (power output).
The gear module 953 of the planetary pinion train by having two series connection can have input shaft 950 and output shaft 951 need promptly to couple together with answering.Central gear the 954, the 955th connects into rotation together, and gear ring the 956, the 957th, is connected to input 950,951.Public planetary pinion load-bearing member 958 drives single break 959.In use, break 959 applies braking can put on moment of torsion output shaft 952, and can be arranged to and make rear-wheel spindle hypervelocity, is that the vehicle of front-wheel drive has the rear wheel drive characteristic thereby make in normality.
Figure 38 expresses a transmission device with half section, and it does not comprise differential gear, but the operation of dependence break realizes the driving of this transmission device.
The transmission device of Figure 38 is about spin axis 960 symmetries, and comprise an input gear 961, two output shafts 962,963 and be in therebetween with the gear module 964,965 of minute surface symmetry separately.Also can be included in the shared property of the gear module among above-mentioned other each embodiment in such layout.
Each module 964,965 comprises two planetary pinion trains side by side, and central gear 966 connects with common rotation.Corresponding gear ring 967,968 is connected to input gear 961 and corresponding output shaft 962,963.Each module also has the public planetary pinion load-bearing member 969 that is connected in corresponding break 970.
Will be understood that this transmission device just can not transmit driving if two breaks 970 are not modulated into resistance to separately planetary pinion load-bearing member 969 is provided.But under the control of the suitable computer that appropriate sensor input is arranged, continuous modulation will allow certain differential action.
Figure 39 expresses and how can combine various embodiments of the present invention and provide a plurality of outputs.Like this, can couple together a plurality of transmission device modules 980, make the output of a module become the input of next module successively.Can three modules be connected into can from one the input 981 provide four output 983, and five modules connect into can provide eight output 984, or the like.Such system can be used in the transmission device of boats and ships for example, wherein may require to drive several propulsion devices and thruster by single power source.
In this specification, digital clutch is optionally in each embodiment, wherein in control module or the title actuating module two speed regulators can be set.Adopting digital clutch among these embodiments is in order to provide a kind of absolute driving to interrupt, and then eliminates speed regulator itself interior energy loss or decline.Like this, typically can avoid resistance and idle running wearing and tearing in the break.Term " digital clutch " comprises having need promptly answer ground to engage or disconnect any appropriate device of driving, but is used in particularly among the described embodiment, be meant the clutch that does not almost have thermal capacity, thereby such clutch can be that size is very compact.In each situation, digital clutch can comprise the element of certain damping, to guarantee its steady engagement.
In the situation that adopts a single rotating speed rectifying means (for example Fig. 2), two digital clutches or equivalent are very important, because they disconnect the driving except that being used for, clutch also constitutes the part that need carry out each torque transmission paths of torque biasing.
Some embodiment of the present invention only has the element of gear module with a break need promptly answer ground reduction of speed (Figure 12).Other embodiments express a break of two courses of action (Fig. 2) or two breaks (Fig. 1).These embodiments can provide the reduction of speed or the speedup of gear module.Before point out that other speedup or reduction of speed device also are available, comprise for example oil hydraulic motor, pneumatic motor or electric motor.Like this, electric motor can offer the planetary pinion load-bearing member (for example the embodiment of Figure 15-18) of gear module to single output from actuating module, and this motor can run on the neutral rotating speed that does not require under the moment of torsion guiding situation.In the situation that requires to carry out the moment of torsion guiding, can make motor speedup or reduction of speed according to input signal from control computer.Certainly the output terminal at motor is provided with digital clutch, so that when not needing motor it is broken away from.
The technician also will be understood that in the application of some vehicle, locks a plurality of breaks with regard to the lockable transmission device, and this is for stopping brake or car is parked on the hillside is of great use.Just in case fault has taken place in conventional braking system, locks a plurality of breaks and can realize emergency brake.
Term in this specification " break " is meant and can transmits any device that stops moment of torsion between two member.So will be understood that can adopt many other device such as one chip or multidisc clutch as break.
Should also be understood that in being provided with each embodiment of differential gear, differential ratio can not be 50: 50.Use planet differential, unequal differential ratio is accomplished quite easily, and it is of great use in all kinds of machineries and non-vehicle application.But the great majority among the embodiment of Jie Shiing are to be applied to vehicle drive unit here, are particularly useful for the change of moment of torsion from the front wheel spindle to the rear-wheel spindle, and the biasing of drive shaft torque from this side to that side.Although usually expression all is planet differential,, in certain embodiments, particularly among the embodiment of those dual planetary gears of no use, can change conventional cone gear differential motion into.Can adopt any suitable moment of torsion input device, for example axially or the device of radial drive.
In this specification, some embodiment describes as " between each wheel " embodiment, and some embodiment is as " between each wheel axle " embodiment description.In general, described differential motion is applicable to and is arranged on any position that requirement is provided with the occasion of some I/O.
Each transmission device described herein can be used for various motor vehicle usually.But, should be appreciated that, also can be used for other occasion of non-vehicle, and can be with the direction of each I/O guiding to any requirement.Also have, in many cases, can " turn each layout described herein " around, exactly output is become input.
The technician can select the certain ratio of planetary pinion train to adapt to predetermined application, even in preferred embodiment, and particular dimensions of teeth parts shown in also not limiting or yardstick relatively.
Claims (10)
1. torque biasing device that is used for motor vehicle, has an input, two outputs, and be in planetary differential module between them, this module is suitable for moment of torsion is distributed to described output from described input, described device also comprises gear module and control module, described gear module comprises planetary pinion train side by side and has public planetary pinion load-bearing member, described gear module can be operably connected on the described planetary pinion load-bearing member of described differential module, and described control module is suitable for making the planetary pinion load-bearing member speedup and the reduction of speed of described gear module, with the described differential module of setovering, thereby provide than another bigger moment of torsion to one of described two outputs, wherein, described differential module, gear module and control module have a public spin axis, and are arranged to axially be series at the bosom of described gear module.
2. device as claimed in claim 1, it is characterized in that, described planetary differential module comprises the gear ring that is connected to described input, a central gear that is connected in one of described two outputs, and be connected to another planetary pinion load-bearing member in described two outputs, described planetary pinion load-bearing member has the dual planetary gear that in series operates between described gear ring and the central gear, and wherein said gear module comprise two side by side and the planetary pinion train of binding with two central gears of common rotation arranged, a gear ring of described gear module is connected on the planetary pinion load-bearing member of described differential module, and another gear ring of described gear module is connected to one of described two outputs.
3. device as claimed in claim 2 is characterized in that, one of described two outputs are axles, and each central gear of described gear module is coaxial with it.
4. device as claimed in claim 3 is characterized in that, the central gear of described differential module is coaxial with described each central gear of described gear module.
5. as claim 3 or 4 described devices, it is characterized in that another in described two outputs is axle, and described two outputs are coaxial.
6. device as claimed in claim 5 is characterized in that, described two outputs are opposite directions.
7. each described device of claim as described above, it is characterized in that, described control module comprises two departing breaks and a planet control module train, this train comprises the gear ring that is connected to described input, be connected to the central gear of the described load-bearing member of described gear module, dual planetary gear, and planetary pinion load-bearing member, wherein said two breaks are connected respectively on the planetary pinion load-bearing member of the planetary pinion load-bearing member of described gear module and described control module train, described two breaks can be with Direct Model and indirect pattern work, in Direct Model, a break is to connect into the described load-bearing member of described gear module is stopped operating, and in indirect pattern, another break is to connect into the described load-bearing member speedup that can make described gear module by described planet control module train.
8. device as claimed in claim 7 is characterized in that, the planetary pinion load-bearing member of described planet control module train is radially to be in outside the planetary pinion load-bearing member of described gear module.
9. as claim 7 or 8 described devices, it is characterized in that described two breaks are inside that is in another radially.
10. device as claimed in claim 9 is characterized in that, described two breaks have a common base element that radially is between them.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0417067A GB0417067D0 (en) | 2004-07-30 | 2004-07-30 | Variable torque bias ratio devices |
| GB0417067.6 | 2004-07-30 | ||
| GB0419056.7 | 2004-08-26 | ||
| GB0425495.9 | 2004-11-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101014785A true CN101014785A (en) | 2007-08-08 |
Family
ID=32947752
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200580025750 Pending CN101014785A (en) | 2004-07-30 | 2005-07-28 | Variable torque biasing device |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN101014785A (en) |
| GB (2) | GB0417067D0 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102272483A (en) * | 2009-01-07 | 2011-12-07 | 三菱重工业株式会社 | Transfer incorporating wet brake |
| CN103987999A (en) * | 2011-12-14 | 2014-08-13 | 盖茨公司 | Limited slip planetary gear transmission |
-
2004
- 2004-07-30 GB GB0417067A patent/GB0417067D0/en not_active Ceased
- 2004-08-26 GB GB0419056A patent/GB0419056D0/en not_active Ceased
-
2005
- 2005-07-28 CN CN 200580025750 patent/CN101014785A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102272483A (en) * | 2009-01-07 | 2011-12-07 | 三菱重工业株式会社 | Transfer incorporating wet brake |
| CN102272483B (en) * | 2009-01-07 | 2014-06-11 | 力至优三菱叉车株式会社 | Transfer incorporating wet brake |
| CN103987999A (en) * | 2011-12-14 | 2014-08-13 | 盖茨公司 | Limited slip planetary gear transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| GB0419056D0 (en) | 2004-09-29 |
| GB0417067D0 (en) | 2004-09-01 |
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