CN106594109B - The dual one-way clutch and speed changer of idle running control - Google Patents

Abstract

The dual one-way clutch of the idle running control of the present invention includes：It drive shaft, can receive to be rotated from the revolving force of driving source transmission that can be just anti-driven, and be formed on the outer periphery inner side containment surfaces；Carrier, two sides is provided to predetermined phase angular difference and equally spaced with radial for positive obligatory point and inverted constraint body；Positive output ring and reverse output ring, respectively positioned at the outside of the positive obligatory point and the inverted constraint body, according to the direction of rotation of the drive shaft, as between the outboard containment face of inner peripheral surface and the inner side containment surfaces, the positive obligatory point or the inverted constraint body are optionally constrained, exports revolving force；Control pin, penetrated in a manner of not interfering with the drive shaft along radial direction and both ends is fixed on the carrier；And control shaft, penetrate and rotate integrally along the axis center of the drive shaft, rotation-sliding of the control pin relative to the drive shaft is controlled according to axial location.

Description

The dual one-way clutch and speed changer of idle running control

Technical field

The present invention relates to idle running control dual one-way clutch and possess the idle running control dual one-way from The speed changer (Dual one way clutch and transmission having the same) of clutch, especially as Following device and a kind of three-wheel or four-wheel electric motor car or ship for being applied to be equipped with motor that can be just anti-driven can be finally provided Oceangoing ship etc. and the manual and automatic transmission for realizing cramped construction, described device improve can be transferred according to the positive and reverse return of driving source to The dual one-way clutch of direction output in forward or backwards, it is directed to so as to as needed positive and reversely can turns Idling conditions is changed to, on the other hand, is applied to the speed changer for possessing differential function, from being not limited solely to the pattern of advancing at utmost speed Or low-speed forward pattern, and the comprehensive speed change including " fall back " mode" can be realized.

Background technology

In general, in order to improve the behavior in service of industrial machinery comprehensively, or receiving manpower biography equipped with wheel Bicycle, wheelchair, automobile, trail bike, motorcycle, the ship etc. passed or travelled using the various driving forces such as driving force Equipped with the speed changer for improving driving performance in conveying arrangement.

This speed changer can implement speed change according to the operation of driver, and required torsion is obtained according to running environment Square or speed.

Recently, use always and be equipped with the planetary gearsets being made up of central gear, planetary gear, gear ring and carrier In the speed changer in hub shell and with multi gear to speed progress speed change.

But compared with the speed changer of the structure of complexity, the quantity of this speed changer shelves is few, particularly driven in load When carrying out variable speed operation under dynamic transport condition, can not successfully it control by the ratchet of driving load strength constraint, existing can not be soft The technical problem of speed change is realized with ground.

As the alternative solution for the speed changer that make use of the planetary gearsets that this problem be present, variable speed is developed Device, buncher (Continuously variable transmission；CVT) have not by gear set in advance Restriction and the advantages of continuously can freely change gear ratio.

But compared with existing gear type inverter, volume is big and complicated, so as to which manufacturing cost is high, particularly Need based on frictional force, make revolving force speed change and export, thus when relatively large load is acted on, durability declines, more It is important that the technical problem that the power loss caused by inscape is skidded each other easily occurs be present.

Particularly recently, it is used as the quick of the electric motor car with two wheels such as the bicycle of driving source, trail bike with by motor Increase, though in practice require that it is a kind of with less gear number but the structure compact, durability is high speed changer.

This customer demand is catered to, applicant has developed the compact speed changer of application dual one-way clutch and is led to Korean patent application is crossed to be applied.

But control of the conventional speed changer for possessing dual one-way clutch due to not needing other gear, Simply by virtue of making the direction of rotation of driving source be converted to forward or backwards, to implement to the pattern of advancing at utmost speed or low-speed forward pattern Speed change.

As noted previously, as not possessing other gear, output is only carried out to a direction set in advance, thus Existing fatal defects are, even if allowing inverse input, can not also to realize the control of " fall back " mode".

That is, the conventional speed changer for possessing dual one-way clutch is applied to not need the electric motor car with two wheels of " fall back " mode".

Recently, the exploitation using motor as the light-duty three-wheel or four-wheel electric motor car of driving source is rapidly developing, still, just For the electric car of three-wheel or four-wheel, " fall back " mode" or differential gear are required, thus presence can not possess using conventional The problem of in the prior art of the speed changer of dual one-way clutch.

The content of the invention

Problem to be solved

The present invention is described for solving the problems, such as, it is desirable to provide the dual one-way clutch and possess that following idle running controls The speed changer of the dual one-way clutch of idle running control, it is positive and reversely can change for dual one-way clutch For idling conditions, under this idling conditions, one in being directly connected to forward or backwards can be forced, after thus allowing for Move back and regenerative braking, and differential function can be assigned, therefore can finally provide suitable for be equipped with can be just anti-driven The manual and automatic transmission of the cramped construction of the three-wheel or four-wheel electric motor car of motor or ship etc..

The solution of problem

The dual one-way clutch of this idle running control of the invention including such as lower part by realizing：Drive shaft, It can receive to be rotated from the revolving force of driving source transmission that can be just anti-driven, and be formed on the outer periphery inner side and constrain Face；Carrier, two sides is provided in predetermined phase angular difference and equally spaced with radial for positive obligatory point and inverted constraint body； Positive output ring and reverse output ring, respectively positioned at the outside of the positive obligatory point and the inverted constraint body, according to described The direction of rotation of drive shaft, as between the outboard containment face of inner peripheral surface and the inner side containment surfaces, optionally constrain institute Positive obligatory point or the inverted constraint body are stated, exports revolving force；Control pin, the edge in a manner of not interfering with the drive shaft Radial direction insertion and both ends is fixed on the carrier；And control shaft, penetrated along the axis center of the drive shaft And rotate integrally, rotation-sliding of the control pin relative to the drive shaft is controlled according to axial location.

Wherein, formed with the slit for penetrating and configuring for the control pin, the slit bag preferably in the control shaft Include：The fixed part axially formed with width corresponding with the diameter of the control pin；And with than the fixed part width The permission portion that wider width is formed.

Also, it is preferred that in the side of the control shaft, equipped with the actuator that the control shaft is pushed to a direction, The opposite side of the control shaft, equipped with the elastomer for resetting the control shaft.

Furthermore the movable end of preferably described actuator is shaped with semi-spherical shape or cone shape, thus reduce and the control The contact area of the tip of the axis processed.

Secondly, the speed changer of the dual one-way clutch for possessing idle running control of the invention can be by including such as bottom Divide and realize：The dual one-way clutch of described idle running control；Driven member, its final output revolving force；First power Transmitting assembly, it receives to carry out speed change from the revolving force that the positive output ring transmission comes, and is transferred to the driven member；With And second power transfer assembly, it receives from the revolving force that output ring transmission comes described reversely and is transferred to the driven member, And to implement speed change from the first power transfer assembly identical direction of rotation but different gear ratio.

Now, preferably described first power transfer assembly and second power transfer assembly include multiple gears or Belt and belt wheel, speed change is realized according to the diameter of the gear ratio of the gear or belt pulley ratio.

Formed with obligating particularly preferably in first power transfer assembly or second power transfer assembly Tooth form, in the control shaft equipped with can with it is described obligate that tooth form engages obligate pin, according to the control The axial location of axle, tooth form is obligated described in control and obligates whether engaging for pin with described.

Also, it is preferred that additional composition has control unit, the control unit can just countercharged to the direction of rotation of driving source While processed, the haul distance relative to actuator movable end can be controlled.

Finally, preferably described driven member is known differential gear set.

The effect of invention

It is positive and reversely can be converted to idle running shape for the present invention as described above is directed to dual one-way clutch State, under this idling conditions, one in being directly connected to forward or backwards can be forced, can retreated and regenerative braking, and And differential function can be assigned, so as to can finally provide the three-wheel for being applied to be equipped with motor that can be just anti-driven or four-wheel electricity The manual and automatic transmission of the cramped construction of motor-car or ship etc..

Brief description of the drawings

Fig. 1 is the stereogram for the dual one-way clutch for representing the idle running control of the present invention.

Fig. 2 has been the positive output ring of separation and reversely output in the dual one-way clutch of the idle running control of the present invention The exploded perspective view of ring.

Fig. 3 is the exploded perspective view of the dual one-way clutch of the idle running control of the present invention.

Fig. 4 is the operating condition figure of the dual one-way clutch of the idle running control of the present invention.

Fig. 5 is the bonding state for eliminating drive shaft for the dual one-way clutch for representing the idle running control of the present invention Stereogram.

Fig. 6 is the vertical view of an example of the control shaft for the dual one-way clutch for representing the idle running control of the present invention Figure.

Fig. 7 is the vertical view of another example of the control shaft for the dual one-way clutch for representing the idle running control of the present invention Figure.

Fig. 8 is the vertical view of the another example of control shaft in the dual one-way clutch for represent the idle running control of the present invention Figure.

Fig. 9 is the stereogram for the speed changer for representing the dual one-way clutch that the idle running for possessing the present invention controls.

Figure 10 is the left side for having separated cover body of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention Side exploded perspective view.

Figure 11 is the right side for having separated cover body of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention Side exploded perspective view.

Figure 12 is the left side for having separated bearing of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention Side exploded perspective view.

Figure 13 is the right side for having separated bearing of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention Side exploded perspective view.

Figure 14 is that the first power of the speed changer of the dual one-way clutch for the idle running control for representing to possess the present invention passes Pass the figure of the bonding state of component and the second power transfer assembly.

Figure 15 is that the speed changer of the dual one-way clutch for representing to possess the idle running control of the present invention obligates tooth The figure of shape.

Figure 16 is the driven structure of conduct for the speed changer for representing the dual one-way clutch that the idle running for possessing the present invention controls The exploded perspective view of the differential gear set of part.

In figure：

1-dual one-way clutch, 10-driving source (motor), 11-axle sleeve, 20-cover body, 100-drive shaft, 101-spline, 102-axis hole, 110-inner side containment surfaces, 120-through hole, 130-bullport, 140-bearing, 200-hold Carrier, 210-positive obligatory point, 211-holding tank, 220-inverted constraint, 221-holding tank of body, 300-positive output ring, 400-reverse output ring, 310,410-outboard containment face, 500-control pin, 501-steady pin, 600-control shaft, 610- Slit, 611-fixed part, 612-permission portion, 620-actuator, 621-movable end, 630-elastomer, 640-force about Beam pin, 650-obligate tooth form, the 700-the first power transfer assembly, 710-gear, the 720-the first rotary shaft, 721- First gear wheel, the 722-the first little gear, 723-bearing, the 800-the second power transfer assembly, 810-gear, 820-the Two rotary shafts, the 821-the second gear wheel, the 822-the second little gear, 823-bearing, 900-driven member, 901-bearing, 910-rotary shaft, the 920-the first bevel gear, the 930-the second bevel gear, 940-lid, 950-connection unit.

Embodiment

Fig. 1 is the stereogram for the dual one-way clutch for representing the idle running control of the present invention, Fig. 2 be the present invention can be empty Turn the separation of the dual one-way clutch of the control exploded perspective view of positive output ring and reverse output ring, Fig. 3 is the present invention Idle running control dual one-way clutch exploded perspective view.

Moreover, operating condition figures of the Fig. 4 as the dual one-way clutch of the idle running control of the present invention, Fig. 4 (a) are represented Control pin 500 is located at the state in permission portion 612, and Fig. 4 (b) represents that control pin 500 is located at the state in fixed part 611, and Fig. 5 is Represent the stereogram of the bonding state for eliminating drive shaft of the dual one-way clutch of the idle running control of the present invention.

In addition, Fig. 6 is shown as one of control shaft of the dual one-way clutch for the idle running control for representing the present invention The top view of example, Fig. 6 (a) is the state in the permission portion 612 that control pin 500 is located at slit 610, and Fig. 6 (b) is control pin 500 In the state of the fixed part 611 of slit 610.

Vertical views of the Fig. 7 as another example of the control shaft of the dual one-way clutch for the idle running control for representing the present invention Figure, Fig. 7 (a) is the state in the permission portion 612 that control pin 500 is located at slit 610, and Fig. 7 (b) is that control pin 500 is located at slit 610 Fixed part 611 state.

Moreover, Fig. 8 is as the another example of control shaft of the dual one-way clutch for the idle running control for representing the present invention Top view, Fig. 8 (a) are the states for the first fixed part 611a that control pin 500 is located at slit 610, and Fig. 8 (b) is control pin 500 State in the permission portion 612 of slit 610, Fig. 8 (c) are the shapes for the second fixed part 611b that control pin 500 is located at slit 610 State.

In addition, Fig. 9 is the stereogram for the speed changer for representing the dual one-way clutch that the idle running for possessing the present invention controls, Figure 10 is that the left surface for having separated cover body of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention decomposes Stereogram, Figure 11 are the right sides for having separated cover body of the speed changer for the dual one-way clutch for possessing the idle running control of the present invention Face exploded perspective view.

Furthermore Figure 12 is that the speed changer for the dual one-way clutch for possessing the idle running control of the present invention has separated bearing Left surface exploded perspective view, Figure 13 be possess the present invention idle running control dual one-way clutch speed changer separation The right flank exploded perspective view of bearing, Figure 14 is as the dual one-way clutch for the idle running control for representing to possess the present invention The figure of first power transfer assembly of speed changer and the bonding state of the second power transfer assembly, Figure 14 (a) represent to pass through forward direction The output state of output ring 300, Figure 14 (b) represent the output state by reverse output ring 400.

Figure 15 is that the speed changer of the dual one-way clutch for representing to possess the idle running control of the present invention obligates tooth The figure of shape, Figure 16 are the driven structures of conduct in the speed changer for represent the dual one-way clutch that the idle running for possessing the present invention controls The exploded perspective view of the differential gear set of part.

Specific structure or even functional description disclosed in embodiments of the invention, it is general based on the present invention to be only in order at explanation Exemplary for the purpose of the embodiment of thought to enumerate, the embodiment based on concept of the present invention can be implemented in the form of various.Separately Outside, shall not be construed as being defined in embodiment described in this specification, it is thus understood that including be contained in the present invention thought and The product that has altered, equivalent product and substitute products in technical scope.

On the other hand, in the present invention, the first and/or second grade term can be used for illustrating various inscape, but The inscape is not limited to the term.The term is only used for an inscape being different from other inscapes Purpose, for example, in the range of without departing from the interest field based on concept of the present invention, the first inscape can be named as second Inscape, similarly, the second inscape can also be named as the first inscape.

When referring to certain inscape " connection " or " continuing " in another inscape, it is thus understood that both can directly connect Another inscape is connect or be connected in, there can also be other inscapes in centre.A certain inscape is referred on the contrary, working as " being directly connected to " or " directly continuing " is when another inscape, it is thus understood that other inscapes are not present in centre.For saying Other performances of relation between bright inscape, i.e. "~between " and "~directly between " or " adjacent~" and " abut directly against ~" etc. performance also should similarly explain.

The term used in this specification is merely to illustrate specific embodiment, does not really want to limit the meaning of the present invention.As long as It is not known on unity and coherence in writing and represents different, the performance of odd number also includes the performance of plural number.In this manual, " comprising " or " having " Deng term it will be appreciated that being intended merely to specify feature, numeral, step, action, inscape, the components or groups thereof of implementation to deposit One or the further feature more than it or numeral are not being excluded in advance, step, action, inscape, components or groups thereof are deposited Or additional possibility.

With regard to the present invention idle running control dual one-way clutch and possess the idle running control dual one-way from For the speed changer of clutch, its is technical to be essentially characterized in that, positive and reversely can turn for dual one-way clutch 1 Idling conditions is changed to, under this idling conditions, one in being directly connected to forward or backwards can be forced, can be retreated And regenerative braking, and differential function can be assigned, so as to can finally provide suitable for be equipped with can be just anti-driven horse The manual and automatic transmission of the compact composition of the three-wheel or four-wheel electric motor car that reach or ship etc..

With reference to the accompanying drawings, embodiments of the invention are described in detail.

For the dual one-way clutch of the idle running control of the present invention, preferably include as shown in Figure 1 to Figure 3：Drive Moving axis 100, it can receive to be rotated from the revolving force of the transmission of driving source 10 that can be just anti-driven, and in periphery shape The containment surfaces 110 on the inside of having；Carrier 200, its for positive obligatory point 210 and inverted constraint body 220 with predetermined phase angular difference and Equally spaced configured on two sides with radial；Positive output ring 300 and reversely output ring 400, it is located at the forward direction about respectively The outside of beam body 210 and the inverted constraint body 220, according to the direction of rotation of the drive shaft 100, as the outer of inner peripheral surface Between side containment surfaces 310,410 and the inner side containment surfaces 110, the positive obligatory point 210 or described anti-is optionally constrained To obligatory point 220, and export revolving force；Control pin 500, it with the drive shaft 100 in a manner of not interfering in radius side Insertion upwards, and the carrier 200 is fixed at both ends；And control shaft 600, in its axle along the drive shaft 100 The heart is penetrated and rotated integrally, and is controlled the control pin 500 to be slided relative to the rotation of the drive shaft 100 according to axial location Move.

That is, the dual one-way clutch of idle running control of the invention generally comprises drive shaft 100, carrier 200, forward direction Output ring 300, reverse output ring 400, control pin 500 and control shaft 600.

First, drive shaft 100 is can to receive the driving source 10 from can be just anti-driven, more specifically, can receive from The revolving force that positive and negative drive motor transmission comes is come the rotary shaft that is rotated.

Wherein, so-called positive and negative drive motor is to refer to be supplied according to power supply and rotate output shaft, and according to automatically controlled letter Number and make the output shaft in one direction or its opposite direction positive and negative rotation.

Also, it is preferred that formed in the side of the drive shaft 100 formed with spline 101 on the output shaft of driving source 10 Axle sleeve 11 be engaged in the spline 101, so that the revolving force of driving source 10 non-skidly is passed into drive shaft 100.

Now, in the center of the drive shaft 100, axis hole 102 has been formed through along axis center, has made what is be described below Control shaft 600 is located in the axis hole 102.

Particularly in a part of section of this drive shaft 100, more specifically, in the periphery of substantial middle, formed with One or more inner side containment surfaces 110, when forming multiple inner side containment surfaces 110, be preferably formed into across it is radial at equal intervals.

It is exemplary to illustrate the situation that 60 degree of phase angle differences are set and form six inner side containment surfaces 110, but this in figure The edge of containment surfaces 110 is preferably connected with each other with gentle curve on the inside of kind.

Be configured with carrier 200 in the outside of this inner side containment surfaces 110, for the carrier 200, two sides with Predetermined phase angular difference is set and across radial equally spaced mode equipped with positive obligatory point 210 and inverted constraint body 220.

As shown in figure 3, the carrier 200 is mutually set in advance as positive holding tank 211 and the holding tank 221 at the back side Phase bit angular difference and the ring bodies asymmetricly formed, positive obligatory point 210 are located in positive holding tank 211, inverted constraint Body 220 is located in the holding tank 221 at the back side.

For the positive obligatory point 210 and the inverted constraint body 220, its form and dimension is mutually identical, because Installation site and produce function difference, thus divide into positive obligatory point 210 or inverted constraint body 220.

As illustrated, this positive obligatory point 210 and inverted constraint body 220 can have generally cylindrical shaped drum-shape State, although it is not shown, but can also apply just spherical.

Moreover, the holding tank 211,221 for being formed at the carrier 200 accommodate respectively described positive obligatory point 210 and Inverted constraint body 220, and be configured to guide as follows：Under 200 non-rotary state of carrier, limitation accommodates Obligatory point 210,220 in groove 211,221 along the circumferential direction moves about, and makes it be only capable of carrying out trickle move about along radial direction.

Now, it is formed at the positive holding tank 211 of the carrier 200 and is formed at the holding tank 221 at the back side, although Its form and dimension is mutually identical, but for its forming position, has mutually predetermined phase angle difference.

It is positive obligatory point 210 and inverted constraint in drive shaft 100 on its inside for this phase angle difference Body 220 is each positioned at the intramarginal degree in one side of inner side containment surfaces 110.

Therefore, on a carrier 200 formed with multiple holding tanks 211,221, each positive obligatory point 210 and reversely Obligatory point 220 is located in the holding tank 211,221.

It is exemplary in figure to illustrate using the drive shaft 100 formed with six inner side containment surfaces 110, thus apply six The situation of positive obligatory point 210 and six inverted constraint bodies 220, but its number does not limit, and can suitably add and subtract.

Then, in the front and back of the carrier 200, positive output ring 300 and reverse output ring are respectively equipped with 400。

The ring bodies of this positive output ring 300 and reverse output ring 400 as the section with generally L-shaped shape, Inner circumferential surface is respectively formed with outboard containment face 310,410.

Therefore, for the positive obligatory point 210 and inverted constraint body 220 of the carrier 200, it is formed at drive shaft 100 inner side containment surfaces 110 are located at its inner circumferential side, in its outer circumferential side, the outboard containment face 310 of positive output ring 300 and reversely The outboard containment face 410 of output ring 400 is respectively positioned at front and the back side.

According to this composition, in Fig. 4, as the drive shaft 100 rotates forward, i.e. in figure counterclockwise Rotation, positive obligatory point 210 are restrained to the inner side containment surfaces 110 of drive shaft 100 and the outboard containment face of positive output ring 300 Between 310, so as to by the positive output ring 300, make revolving force export counterclockwise.

Now, inverted constraint body 220 is placed in the outside of the inner side containment surfaces 110 of drive shaft 100 and reverse output ring 400 about Not restrained position between beam face 410, so as to not transmit revolving force to reverse output ring 400.

In contrast, as the drive shaft 100 reversely rotates, i.e. rotated clockwise in figure, inverted constraint Body 220 is restrained between the inner side containment surfaces 110 of drive shaft 100 and the outboard containment face 410 of reverse output ring 400, so as to By the reversely output ring 400, revolving force is set to export clockwise.

Now, positive obligatory point 210 is placed in the outside of the inner side containment surfaces 110 of drive shaft 100 and positive output ring 300 about Not restrained position between beam face 310, so as to not transmit revolving force to positive output ring 300.

As set forth above, it is possible to including drive shaft 100, carrier 200, positive output ring 300 and reversely output ring 400 and Form basic dual one-way clutch 1.

As a result, for dual one-way clutch 1, when the drive shaft 100 rotates forward, only make positive output ring 300 rotate forward, and when the drive shaft 100 reversely rotates, only reversely rotate reverse output ring 400.

Moreover, as shown in figure 15, on the positive output ring 300 and the reverse output ring 400, connect respectively in addition Gear 710,810, can by this gear 710,810 come realize output.

Cut-off is present, the composition and effect of basic dual one-way clutch 1 is illustrated, below to as described above The slip control of dual one-way clutch 1 illustrate.

For the slip control of dual one-way clutch 1, further requirement control pin 500 and control shaft 600.

First, control pin 500 is fixed on the carrier 200 with the circular pin-shaped composition of small diameter, its both ends.

Now, in order to make the control pin 500 be fixed on the carrier 200, formed on the carrier 200 Hole, after inserting control pin 500 in the hole, it can prevent control pin 500 from separating with two other steady pins 501.

Therefore, as shown in Figures 4 and 5, the center of the control pin 500 penetrate the drive shaft 100 along radial direction and Configuration, now, along the inner side containment surfaces 110 of the radial direction insertion drive shaft 100 formed with through hole 120, so that institute Control pin 500 is stated not to be in contact or interfere each other with the drive shaft 100.

It is optionally straight without any rotation-sliding when the drive shaft 100 rotates for this control pin 500 Connect and pass to the carrier 200 and rotated integrally, so that in the dual one-way clutch 1, positive obligatory point 210 And the both of which of inverted constraint body 220 is able to maintain that not restrained idling conditions.

That is, described output forward or backwards is usually performed in order to maintain the dual one-way clutch 1, or As needed not implement the idling conditions to positive and reverse any output, it is desirable to the rotation-sliding of control pin 500 Whether it is controlled.

That is, the rotation-sliding of the control pin 500 occurs if over the rotation usually of drive shaft 100, then institute State dual one-way clutch 1 to export as implementing in the past, but if control is with rotation when needing of drive shaft 100 Turn, rotate integrally the control pin 500 in a manner of any rotation-sliding does not occur, then the dual one-way clutch 1 Maintain idling conditions.

Wherein, so-called rotation-sliding means on the basis of the rotation of the drive shaft 100, until the control pin 500 Start sliding during rotation, that is, dally.

For example, so-called sliding is not rotated mean that the drive shaft 100 and the control pin 500 rotate integrally.

Rotate sliding on the contrary, so-called and mean during the drive shaft 100 is rotated to first retainer, the control Cotter 500 is not rotated, and the drive shaft 100 is rotated more than first retainer, so that the control pin 500 rotates together with.

As the unit of the rotation-sliding for controlling this control pin 500, the drive shaft 100 can be inserted into The control shaft 600 of axis hole 102.

Axis center insertion configuration of the control shaft 600 along drive shaft 100, can also use other connecting pin, so as to It can be rotated integrally with the drive shaft 100.

It is described below, but pin 640 is obligated due to using, thus other connecting pin can be omitted.

Particularly preferably described control shaft 600 controls the control pin according to the axial location in the drive shaft 100 500 relative to the drive shaft 100 rotation-sliding.

For example, it can be controlled as follows：As the control shaft 600 axially towards moving to the right, do not rotate Sliding, on the contrary, with axially towards moving to the left, rotating sliding.

Especially, in the present invention, as shown in Fig. 4 and Fig. 6, formed with for the control preferably in the control shaft 600 The slit 610 that pin 500 is penetrated and configured, the slit 610 are included vertically with corresponding with the diameter of the control pin 500 wide Spend the fixed part 611 formed and the permission portion 612 to be formed than the width wider width of fixed part 611.

I.e., it is possible to being formed in the control shaft 600 includes fixed part 611 and the slit 610 in permission portion 612.

Now, the width of the fixed part 611 of slit 610 is formed with the width consistent with the diameter of the control pin 500, institute The width for stating permission portion 612 is formed with the diameter wider width than the control pin 500.

According to this composition, as shown in Fig. 4 (a) and Fig. 6 (a), the shape in left side is moved axially into the control shaft 600 Under state, the control pin 500 is located in the permission portion 612 of slit 610, so as to be revolved relative to the control pin 500 Turn sliding.

According to this control, the dual one-way clutch 1 is in the state that can implement to export forward or backwards.

On the contrary, as shown in Fig. 4 (b) and Fig. 6 (b), in the state of the control shaft 600 moves axially into right side, institute State control pin 500 to be located in the fixed part 611 of slit 610, so as to which the rotation cunning relative to the control pin 500 does not occur Move.

According to this control, the dual one-way clutch 1 is in does not implement output to any direction forward or backwards Idling conditions.

In contrast, as shown in Fig. 7 (a) and Fig. 7 (b), can also realize the control round about, this be do not say and Analogy.

Above example is simply formed with the feelings in a fixed part 611 and permission portion 612 in the slit 610 of control shaft 600 Shape, still, such as shown in figure 8, can also in the center of slit 610 formed with permission portion 612, two in the permission portion 612 Side is respectively formed with the first fixed part 611a and the second fixed part 611b.

Now, as shown in Fig. 8 (a) or Fig. 8 (c), it is located at the first fixed part 611a or of slit 610 in control pin 500 In the case of in two fixed part 611b, it can be idling conditions by dual one-way clutch control, as shown in Fig. 8 (b), control In the case that pin 500 is located at permission portion 612, the action of existing dual one-way clutch can be realized.

In the present invention, it is preferred in the side of the control shaft 600, as illustrated in fig. 5 equipped with by the control shaft 600 Push the actuator 620 in a direction to, the control shaft 600 opposite side equipped with for resetting the control shaft 600 Elastomer 630.

This is for making the unit movable along the axial direction of control shaft 600, so as to control control pin as described above 500。

First, actuator 620 can be controlled according to the control of electric signal known in the haul distance of movable end 621 Element.

This actuator 620 is located at the side of the control shaft 600, and movable end 621 is located side by side at the control shaft 600 Side end simultaneously contacts.

Therefore, with the actuator 620 movable end 621 protrusion, the control shaft 600 can be vertically from left side Move to the right.

Moreover, the elastomer 630 of such as helical spring is to be used to make to be moved to by means of actuator 620 as described above Control shaft 600 on the right side of accompanying drawing resets to the composition in left side again.

Therefore, the elastomer 630 is supported in the axis hole 102 of drive shaft 100, with the control shaft 600 and deploying Put.

, can be easy by means of being located at the actuator 620 and elastomer 630 of the both sides of control shaft 600 respectively as described above Control the axial location of the control shaft 600.

Now, for the movable end 621 of the actuator 620, it is preferably able to convex to its in a manner of more than two benches Go out length to be adjusted.

If the actuator 620 for using the protrusion length of movable end 621 to be controlled with two benches, then, such as Fig. 6 and figure Shown in 7, it is preferably applied to be simply formed with the control in a fixed part 611 and permission portion 612 in the slit 610 of control shaft 600 Axle 600.

But if using the actuator 620 that the protrusion length of movable end 621 is controlled with three stages, then, such as scheme Shown in 8, be preferably applied in the slit 610 of control shaft 600 formed with the first fixed part 611a and the second fixed part 611b and It is formed at the control shaft 600 in permission portion 612 between the two.

Especially, in the present invention, it is preferred to which the movable end 621 of the actuator 620 is shaped with semi-spherical shape or cone shape, So as to reduce the contact area with the end of control shaft 600.

As described above, control shaft 600 is the inscape rotated together with drive shaft 100, on the contrary, the actuator 620 It is fixed inscape.

Therefore, the movable end 621 of the actuator 620 is configured to semi-spherical shape or cone shape etc., thus reduces institute The area that contacts with each other of movable end 621 and the control shaft 600 is stated, this contributes to components damage caused by pre- anti-wear grade.

Cut-off illustrates following situation now, by the control of control shaft 600, implements just when dual one-way clutch 1 is flat To or situation about reversely exporting, and dual one-way clutch 1 is defeated without implementing to either direction forward or backwards as needed The situation of the idling conditions gone out.

Below, the dual one-way clutch 1 for illustrating to control this idle running is applied to the example of speed changer.

For possessing the speed changer of the dual one-way clutch of the idle running of present invention control, as shown in Fig. 9 to Figure 14, Preferably include：The dual one-way clutch 1 of described idle running control；Driven member 900, its final output revolving force；First Power transfer assembly 700, it receives to transmit the revolving force come from the positive output ring 300 and carries out speed change, passes to described Driven member 900；And second power transfer assembly 800, it receives the revolving force for transmitting to come from the reversely output ring 400 simultaneously Be transferred to the driven member 900, and according to from the identical direction of rotation of the first power transfer assembly 700 but different speed changes Than implementing speed change.

That is, the speed changer for possessing the dual one-way clutch of the idle running control of the present invention generally comprises described dual list To clutch 1, driven member 900, the first power transfer assembly 700 and the second power transfer assembly 800.

First, the both ends of drive shaft 100 of the dual one-way clutch 1 are revolvably supported in by means of bearing 140 The inner face of cover body 20.

Wherein, so-called driven member 900 refers to, for making to be fully completed the rotation of speed change by the speed changer of the present invention Power final output, on this driven member 900, such as the wheel of three-wheel or four-wheel electric motor car can be connected.

Moreover, the first power transfer assembly 700 is following structure：Receive from the positive defeated of the dual one-way clutch 1 After going out the revolving force that the transmission of ring 300 comes and implementing acceleration or deceleration iso-variable velocity, the rotation through speed change is transmitted to the driven member 900 Turn power.

Therefore, first power transfer assembly 700 can transmit element by the known power of transmission revolving force Form.

In addition, the second power transfer assembly 800 is following structure：Receive from the reverse defeated of the dual one-way clutch 1 Go out ring 400 to transmit the revolving force come and implement acceleration or deceleration iso-variable velocity, and keep and the identical of the first power transfer assembly 700 Direction of rotation and with different gear ratio implement speed change after, transmit the revolving force through speed change to the driven member 900.

This second power transfer assembly 800 can also transmit element structure by the known power of transmission revolving force Into.

Especially, in the present invention, first power transfer assembly 700 and second power transfer assembly 800 include Multiple gears or belt and belt wheel, speed change can be realized according to the gear ratio of the gear or the diameter ratio of the belt wheel.

This gear or belt and the arrangement of belt pulley or species do not limit, the He of the first power transfer assembly 700 Second power transfer assembly 800 can not mutually be shared and independently embody.

But, as illustrated, a shared part is formed, so as to transmit revolving force to driven member 900 after speed change, this is right For compact speed changer composition more preferably.

Specifically, first power transfer assembly 700 can be by being connected to the gear 710 of positive output ring 300, matching somebody with somebody It is standby to be formed in the first gear wheel 721 of the first rotary shaft 720 and the first little gear 722.

Now, the both ends of the first rotary shaft 720 are supported in cover body 20 by bearing 723 in a manner of revolvable, so that First gear wheel 721 and the first little gear 722 rotate integrally.

By means of this composition, as shown in Figure 14 (a), when the positive output ring 300 and gear 710 rotate forward, The first gear wheel 721 and the first little gear 722 for being engaged in the gear 710 together reversely rotate, and it is small to be engaged in described first The driven member 900 of gear 722 rotates forward.

In addition, second power transfer assembly 800 is configured to, except be connected to reverse output ring 400 gear 810, It is provided to beyond the second gear wheel 821 and the second little gear 822 of the second rotary shaft 820, can also adds including being provided to State the first gear wheel 721 and the first little gear 722 of the first rotary shaft 720.

Now, the both ends of the second rotary shaft 820 are supported in cover body 20 by bearing 823 in a manner of revolvable, so that the Two gear wheels 821 and the second little gear 822 rotate integrally.

According to this composition, as shown in Figure 14 (b), when the reversely output ring 400 and the reverse rotation of gear 810, nibble Together rotated forward together in the second gear wheel 821 and the second little gear 822 of the gear 810, be engaged in the described second small tooth First gear wheel 721 of wheel 822 together reversely rotates with the first little gear 722, is engaged in the driven of first little gear 722 Component 900 rotates forward.

According to this composition, the first power transfer assembly 700 according to dual one-way clutch positive 300 → tooth of output ring The order for taking turns 710 → the first gear wheel 721 → the first, 722 → driven member of little gear 900 transmits revolving force.

In addition, the second power transfer assembly 800 according to dual one-way clutch reverse 400 → gear of output ring 810 → The order of second gear wheel, 821 → the second little gear, 822 → the first gear wheel 721 → the first, 722 → driven member of little gear 900 Transmit revolving force.

That is, for the first power transfer assembly 700, in the positive output of dual one-way clutch, speed change is at a high speed And it is transferred to driven member 900.

On the contrary, for the second power transfer assembly 800, by the second gear wheel 821 and the second little gear 822 and another It is secondary to implement to slow down, so as to which when dual one-way clutch reversely exports, speed change is low speed and is transferred to driven member 900.

Certainly, this is not limited to, two grades of suitable gear ratio can be obtained as needed.

Now, in terms of direction of rotation, in dual one-way clutch output be, when positive output ring 300 rotates forward When, driven member 900 carries out identical and rotated forward.

Output is that, when reverse output ring 400 reversely rotates, driven member 900 rotates forward in addition.

Above example driven member 900 situation of positive output, but also may be used all the time by means of dual one-way clutch 1 To change gear lines etc., reverse output is achieved.

It is described above and the first power transfer assembly 700 or the second power transfer assembly 800 is only formed by gear Example, but belt and belt wheel can certainly be utilized to embody identical operating.

Wherein, symbol 901 is the bearing that the driven member 900 is supported in cover body 20 in a manner of it can rotate, symbol Numbers 622 be the cover body for covering actuator 620.

Now, for the speed changer of the present invention, with the inside of cover body 20 with most of inscape together full of profit The state of lubricating oil, and assembled in a manner of keeping airtight.

Cut-off now illustrate to from dual one-way clutch 1 output forward or backwards carry out speed change and be transferred to from Dynamic component 900, so as to embody the situation of the pattern of advancing at utmost speed and low-speed forward pattern, the embodiment to " fall back " mode" below is said It is bright.

I.e., in the present invention preferably：In first power transfer assembly 700 or second power transfer assembly 800 Tooth form is obligated in middle formation；In the control shaft 600, described the strong of tooth form 650 is obligated equipped with that can be engaged in Restrict beam pin 640；And the axial location according to the control shaft 600, tooth form 650 and the pressure are obligated described in control Whether is the engagement of constraint pin 640.

For example, in second power transfer assembly 800, as shown in figure 15, reverse output ring 400 can be connected to Gear 810 inner peripheral surface formed with obligating tooth form 650.

For tooth form 650 should be obligated, in the inner peripheral surface of the gear 810, a part of area is only formed at vertically Between, and around the inner peripheral surface edge one week of the gear 810, with equal intervals formed with multiple.

At the same time, in the control shaft 600, as shown in figure 5, equipped with can optionally be engaged in the pressure Constraint tooth form 650 obligates pin 640.

Now, the pin 640 of obligating enters joining line along the normal direction insertion control shaft 600, strong by means of this Beam pin 640 is restricted, the drive shaft 100 and the control shaft 600 can be directly connected to integral and rotate.

Therefore, even if without described other connecting pin, the pin 640 of obligating can also play the work of connecting pin With.

Moreover, in order that it is described obligate pin 640 insertion drive shaft 100 configure in the state of, can with positioned at it Internal control shaft 600 is together axially moveable, formed with being available for described obligating pin 640 and moving in the drive shaft 100 Dynamic bullport 130.

Therefore, can be in the axis hole 102 of the drive shaft 100 by means of the length of bullport 130, the control shaft 600 Mobile ultimate range is restricted.

According to this composition, in the axis hole 102 of the drive shaft 100, according to the axial location of the control shaft 600, Tooth form 650 is obligated described in control and obligates whether engaging for pin 640 with described.

That is, when the control shaft 600 such as moves to the right shown in Fig. 6 (b), the pin 640 of obligating is engaged in Described to obligate tooth form 650, when being moved to the left shown in such as Fig. 6 (a), the pin 640 of obligating is from the pressure Constraint tooth form 650 departs from.

As described above, the pin 640 of obligating based on the position of control shaft 600 controls, can be with the control of the control pin 500 System is together realized.

As a result, when the control shaft 600 is mobile to accompanying drawing right side, by means of control pin 500, the dual one-way clutch Device 1 is converted to idling conditions, at the same time, it is described obligate pin 640 and can be engaged in obligate tooth form 650.

In this state, the revolving force from the driving source 10 is directly delivered to without dual one-way clutch 1 After being connected to the gear 810 of reverse output ring 400, driven member can be transferred to by the second power transfer assembly 800 900。

In this state, if rotating forward driving source 10, revolving force by the second power transfer assembly 800, Reversely rotate driven member 900.

By this control, the " fall back " mode" of speed changer can be embodied.

The following situation of above example：Formed with obligating tooth form on the gear 810 of the second power transfer assembly 800 650, in control shaft 600, the right side that pin 640 is located at slit 610 is obligated, so as to pass through the second power transfer assembly 800 are exported.

But in contrast, if forced although it is not shown, being formed on the gear 710 of the first power transfer assembly 700 Tooth form 650 is constrained, in control shaft 600, as shown in fig. 7, pin 640 is obligated in configuration in the left side of slit 610, then can be led to The first power transfer assembly 700 is crossed to be exported.

In this case, in the slit 610 for being formed at the control shaft 600, by mutually changing the He of fixed part 611 The position in permission portion 612, it is possible to achieve the control of control pin 500.

In this state, if reversely rotating driving source 10, revolving force by the first power transfer assembly 700, Reversely rotate driven member 900.

By this control, the " fall back " mode" of speed changer can be embodied, at this point it is possible to realize higher than the " fall back " mode" The retrogressing of speed.

Moreover, the first power transfer assembly 700 the power transfer assembly 800 of gear 710 and second gear 810 On, formed obligate tooth form 650 respectively, in control shaft 600, as shown in figure 8, can also be on the left side of slit 610 and the right side Side, which is respectively configured, obligates pin 640.

Now, when the control shaft 600 is centrally located, the work(of existing dual one-way clutch 1 can be implemented Energy.

But moved to the left from central such as shown in Fig. 8 (a) by means of the control shaft 600, it is possible to achieve by the The output of one power transfer assembly 700, such as moved to the right from center shown in Fig. 8 (c) by means of the control shaft 600, can To realize the output by the second power transfer assembly 800.

Now, in the slit 610 for being formed at the control shaft 600, centered on permission portion 612, the first fixed part 611a and the second fixed part 611b are located at its both sides, and thereby, it is possible to realize the rotation-sliding control of control pin 500.

By this control, in the " fall back " mode" of speed changer, high speed and low speed two also can be optionally embodied Kind pattern.

On this basis, following control unit (not shown) is most preferably added：Being capable of the just direction of rotation of revertive control drive shaft 100 While, the haul distance of the movable end 621 relative to the actuator 620 can be controlled.

That is, as set forth above, it is possible to control the axial direction of the control shaft 600 on the basis of drive shaft 100 using actuator 620 Position, on the other hand, implement the control of the direction of rotation of driving source 10 using other control unit.

This control unit is for example connected to the gear lever of light-duty three-wheel or four-wheel electric motor car, as driver operates gear lever And forward mode or " fall back " mode" can be selected, it can also enough in forward mode or " fall back " mode", selection high speed or low speed Forward mode.

Finally, in the present invention, as shown in figure 14, most preferably described driven member 900 is known differential gear set.

When the speed changer of the dual one-way clutch for the idle running control for possessing the present invention is applied to light-duty three-wheel or four When taking turns electric car, when this electric car turning driving, nearside wheel and the rotary speed of outboard wheel are mutually internally inconsistent.

In contrast to this, for possessing the speed changer of the dual one-way clutch of the idle running of present invention control, driven structure Part 900 preferably includes known differential gear set.

In the present invention, as shown in figure 16, differential gear set preferably includes：The rotary shaft 910 that both ends are fixed；It is located at respectively First bevel gear 920 at the both ends of rotary shaft 910；And Vertical Meshing is rotated between two the first bevel gears 920 And the second bevel gear 930 for supplying wheel to connect respectively.

Now, by means of the lid 940 of both sides, axle rotation 910 and bevel gear 920,930 is prevented to be exposed to outside, it is this Lid 940 is mutually assembled by means of connection unit 950.

According to this composition, being delivered to the revolving force of driven member 900 rotates rotary shaft 910, in straight-line travelling, the One bevel gear 920 is not rotated, and two the second bevel gears 930 for being connected to wheel are rotated with same speed.

But in turning driving, the first bevel gear 920 rotates at different rates respectively, to be connected to wheel Two the second bevel gears 930 can be rotated with mutually different speed.

As described above, with additional difference in the speed changer of the dual one-way clutch controlled in the idle running for possessing the present invention Moving gear group, when turn inside diameter travels, it is allowed to nearside wheel and the rotational velocity difference of outboard wheel occurs.

With reference to the accompanying drawings, the effect of the present invention is illustrated.

The speed changer for possessing the dual one-way clutch of the idle running control of the invention formed as described above can answer For light-duty three-wheel or four-wheel electric motor car.

Moreover, control unit is connected to the gear lever of driver, the pattern that can carry out advancing at utmost speed, low-speed forward pattern and The operation of " fall back " mode".

[advance at utmost speed pattern]

First, under the pattern of advancing at utmost speed, control unit makes the movable end 621 of actuator 620 non-bulging, on the other hand, makes Driving source 10 rotates forward.

Therefore, for control shaft 600, as shown in Fig. 6 (a), in drive shaft 100, kept by means of elastomer 630 The state being moved on the left of accompanying drawing, control pin 500 is in the permission portion 612 for forming the slit 610 in control shaft 600.

Now, the rotation-sliding relative to control pin 500 not only occurs, and obligates pin 640 and is in not with being connected In the state for obligating the engagement of tooth form 650 of the gear 810 of reverse output ring 400.

As a result, the power that rotates forward from driving source 10 rotates forward drive shaft 100, so as in dual one-way clutch In 1, between inner side containment surfaces 110 and the outboard containment face 310 of positive output ring 300, positive obligatory point 210 is constrained, is realized Exported by the forward direction of positive output ring 300.

Now, the phase angle difference that inverted constraint body 220 is kept by means of carried frame 200 is without restrained.

As described above, for the positive output by positive output ring 300, become by the first power transfer assembly 700 After rapid-result high speed, driven member 900 is transferred to, wheel is transferred to by differential gear set, so that electric car advances at utmost speed.

[low-speed forward pattern]

Then, under low-speed forward pattern, control unit makes the movable end 621 of actuator 620 keep non-salient state, separately On the one hand, reversely rotate driving source 10.

Therefore, for control shaft 600, as shown in Fig. 6 (a), in drive shaft 100, continued by means of elastomer 630 The state being moved on the left of accompanying drawing is kept, control pin 500 continues positioned at the permission portion for forming the slit 610 in control shaft 600 In 612.

Now, the rotation-sliding relative to control pin 500 not only occurs, and obligates pin 640 and is in not with being connected In the state for obligating the engagement of tooth form 650 of the gear 810 of reverse output ring 400.

As a result, the reverse rotational force from driving source 10 reversely rotates drive shaft 100, so as in dual one-way clutch In 1, between inner side containment surfaces 110 and reversely the outboard containment face 410 of output ring 400, constraint inverted constraint body 220, realize Pass through the reverse output of reverse output ring 400.

Now, the phase angle difference that positive obligatory point 210 is kept by means of carried frame 200 is without restrained.

As described above, for the reverse output by reverse output ring 400, by the second power transfer assembly 800, with The pattern of advancing at utmost speed is compared, and after becoming rapid-result low speed, is delivered to driven member 900, wheel is passed to by differential gear set, So that electric car can be with low-speed forward.

[" fall back " mode"]

Moreover, under " fall back " mode", control unit protrudes the movable end 621 of actuator 620, on the other hand, makes driving source 10 rotate forward.

Therefore, control shaft 600 is in drive shaft 100, the shown sidesways to the right of such as Fig. 6 (b) by means of movable end 621 Dynamic, control pin 500 is located in the fixed part 611 of the slit 610 formed in control shaft 600.

As a result, by means of the control pin 500, in dual one-way clutch 1, carrier 200 without spin slippingly with Drive shaft 100 rotates integrally, thus positive obligatory point 210 and the both of which of inverted constraint body 220 be not restrained, so as to dual one-way Clutch is converted to the idling conditions for not exporting revolving force.

But now, obligate pin 640 and obligate tooth in the gear 810 with being connected to reverse output ring 400 The state that shape 650 engages.

Therefore, the power that rotates forward from driving source 10 is directly led to from drive shaft 100 not via dual one-way clutch 1 Cross and be connected to the gear 810 of reverse output ring 400 and carry out positive output.

Then, the positive of this gear 810 is exported by the second power transfer assembly 800 and after speed change, back transfer is extremely Driven member 900, wheel is passed to through differential gear set, so that electric car can retreat.

On the basis of this control, it can also additionally implement high speed and ease astern.

Now, can embody in the following way：As shown in figure 8, make the movable end 621 of actuator 620 in three stages While protrusion, in the slit 610 of control shaft 600 is formed at, centered on permission portion 612, forms first in both sides and fix Portion 611a and the second fixed part 611b.

Therefore, the present invention can provide following manual and automatic transmission, thus be the invention with prominent advantages：Can Dual one-way clutch is made positive and reversely can be exchanged into idling conditions, under this idling conditions, can forced directly One in connection forward or backwards, it can retreat and regenerative braking, furthermore, it is possible to differential function be assigned, so as to finally can A kind of hand of the cramped construction of the three-wheel for being applied to be equipped with motor that can be just anti-driven or four-wheel electric motor car or ship etc. is provided Dynamic and automatic transmission.

An example of the embodiment as the technological thought for illustrating the present invention, the scope of the present invention are unlimited Due to the accompanying drawing or embodiment.

Claims (9)

1. A kind of 1. dual one-way clutch of idle running control, it is characterised in that including：

   Drive shaft, it can receive to be rotated from the revolving force of driving source transmission that can be just anti-driven, and in periphery shape Into there is inner side containment surfaces, formed with through hole in a manner of penetrating the inner side containment surfaces in the radial direction；

   Carrier, two are provided to predetermined phase angular difference and equally spaced with radial for positive obligatory point and inverted constraint body Face；

   Positive output ring and reverse output ring, respectively positioned at the outside of the positive obligatory point and the inverted constraint body, according to The direction of rotation of the drive shaft, as between the outboard containment face of inner peripheral surface and the inner side containment surfaces, optionally about Shu Suoshu forward directions obligatory point or the inverted constraint body, export revolving force；

   Control pin, both ends are made to be fixed on the carrier by the through hole in a manner of not interfering with the drive shaft； And

   Control shaft, penetrate and rotate integrally along the axis center of the drive shaft, the control pin is controlled according to axial location Relative to the rotation-sliding of the drive shaft.
2. 2. the dual one-way clutch of idle running control according to claim 1, it is characterised in that

   In the control shaft, formed with the slit for penetrating and configuring for the control pin,

   The slit includes：The fixed part axially formed with width corresponding with the diameter of the control pin；And with than The permission portion that the width wider width of the fixed part is formed.
3. 3. the dual one-way clutch of idle running control according to claim 2, it is characterised in that

   In the side of the control shaft, equipped with the actuator that the control shaft is pushed to a direction, in the control shaft Opposite side, equipped with the elastomer for resetting the control shaft.
4. 4. the dual one-way clutch of idle running control according to claim 3, it is characterised in that

   The movable end of the actuator is shaped with semi-spherical shape or cone shape, is thus reduced and is controlled connecing for the tip of the axis with described Contacting surface is accumulated.
5. A kind of 5. speed changer for the dual one-way clutch for possessing idle running control, it is characterised in that including：

   The dual one-way clutch of the idle running control of claim 1；

   Driven member, its final output revolving force；

   First power transfer assembly, it receives to carry out speed change from the revolving force that the positive output ring transmission comes, and is transferred to institute State driven member；And

   Second power transfer assembly, it receives from the revolving force that output ring transmission comes described reversely and is transferred to the driven structure Part, and to implement speed change from the first power transfer assembly identical direction of rotation but different gear ratio.
6. 6. the speed changer of the dual one-way clutch according to claim 5 for possessing idle running control, it is characterised in that

   First power transfer assembly and second power transfer assembly include multiple gears or belt and belt wheel, root Speed change is realized according to the gear ratio of the gear or the diameter ratio of the belt wheel.
7. 7. the speed changer of the dual one-way clutch according to claim 6 for possessing idle running control, it is characterised in that

   Formed with obligating tooth form in first power transfer assembly or second power transfer assembly,

   In the control shaft equipped with can with it is described obligate that tooth form engages obligate pin,

   According to the axial location of the control shaft, tooth form is obligated described in control and obligates whether engaging for pin with described.
8. 8. the speed changer of the dual one-way clutch according to claim 7 for possessing idle running control, it is characterised in that

   Additional composition has control unit, can while the control unit can carry out positive revertive control to the direction of rotation of driving source Control the haul distance of the movable end relative to actuator.
9. 9. the speed changer of the dual one-way clutch according to claim 8 for possessing idle running control, it is characterised in that

   The driven member is known differential gear set.