CN102713353B - Hybrid drive device - Google Patents

Hybrid drive device Download PDF

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Publication number
CN102713353B
CN102713353B CN201180005585.0A CN201180005585A CN102713353B CN 102713353 B CN102713353 B CN 102713353B CN 201180005585 A CN201180005585 A CN 201180005585A CN 102713353 B CN102713353 B CN 102713353B
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China
Prior art keywords
axle
ring
friction wheel
mentioned
line
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CN201180005585.0A
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Chinese (zh)
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CN102713353A (en
Inventor
香山和道
神谷美纱纪
梅田秀行
高桥昭次
前野克弘
榊原文彦
小川亮太
白井久则
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Aisin AW Co Ltd
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Aisin AW Co Ltd
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Publication date
Priority to JP2010-050645 priority Critical
Priority to JP2010050645A priority patent/JP5099154B2/en
Priority to JP2010051486A priority patent/JP5051254B2/en
Priority to JP2010-051486 priority
Priority to JP2010-053764 priority
Priority to JP2010053764A priority patent/JP5029716B2/en
Priority to JP2010-077895 priority
Priority to JP2010077894 priority
Priority to JP2010-077894 priority
Priority to JP2010077895 priority
Priority to JP2011019176A priority patent/JP5263311B2/en
Priority to JP2011-019176 priority
Application filed by Aisin AW Co Ltd filed Critical Aisin AW Co Ltd
Priority to PCT/JP2011/054125 priority patent/WO2011111544A1/en
Publication of CN102713353A publication Critical patent/CN102713353A/en
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Publication of CN102713353B publication Critical patent/CN102713353B/en
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    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/60Other road transportation technologies with climate change mitigation effect
    • Y02T10/62Hybrid vehicles

Abstract

A cone ring CVT is applied to the disclosed hybrid drive device, and a compact arrangement is used for the device as a whole. An input-side friction gear (22) is disposed on a first shaft (I) that is coaxial with an engine output shaft, an output-side friction gear (23) is disposed on a second shaft (II), and an electric motor (2) is disposed on a third shaft (III) that is parallel to the first and second shafts. The electric motor (2) and the cone ring CVT (3) are disposed in a manner so as to partially overlap in the axial direction. Viewed in the axial direction, the third shaft (III) is disposed on the same side as the friction gear (23) that is not enclosed by the ring with respect to a line (v-v) that is perpendicular to a line (p-p) that connects the first shaft (I) and the second shaft (II) and that passes through the center (t) of the ring (25) when the ring has moved maximally towards the shaft center (II) of the friction gear (23) that is not enclosed by said ring.

Description

Hybrid drive
Technical field
The present invention relates to and utilize motor and electric motor to drive the hybrid drive of wheel, in detail, relate to the hybrid drive being assembled with electric motor and conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) integratedly.
Background technique
All the time, as everyone knows utilizing motor and electric motor in the hybrid drive driving wheel, an electric motor and stepless speed changes devices are combined.In general, use belt-drive variable-speed transmission as the stepless speed changes devices of this hybrid drive, this belt-drive variable-speed transmission is made up of with the metal tape (or chain) being wound in these belt wheels a pair belt wheel, carries out stepless change by the effective diameter changing belt wheel.
On the other hand, as we all know there are conical ring formula CVT, the metal ring that this conical ring formula CVT comprises a pair cone shape friction wheel and is installed between these friction wheels, carries out stepless change (such as with reference to patent documentation 1) by making ring move in the mode of the contacting part changing ring and above-mentioned two friction wheels.
Recently, the patent documentation (with reference to patent documentation 2) above-mentioned conical ring formula CVT being applied to hybrid drive is disclosed.This hybrid drive, on first axle coaxial with the output shaft of explosive motor, be configured with the friction wheel of the cone shape of the input side of above-mentioned conical ring formula CVT, electric motor is configured on above-mentioned first axle or on other axles.
Patent documentation 1: Japanese Unexamined Patent Application Publication 2006-501425 publication (JP2006-501425A)
Patent documentation 2: Japanese Unexamined Patent Application Publication 2010-519470 publication (WO2008/104142A1)
In general, hybrid drive is configured with the primary pulley of electric motor and belt-drive variable-speed transmission on the first axle coaxial with engine output shaft.Although also consider above-mentioned conical ring formula CVT to be applied to hybrid drive, but the friction wheel of the cone shape of this conical ring formula CVT is configured to axially longer, input side friction wheel and electric motor being jointly configured on the first axle coaxial with above-mentioned engine output shaft to cause the first axle to increase, undesirable in vehicle boarded.And, in above-mentioned patent documentation 2, although also describe mode of execution electric motor being configured in the axle beyond the first axle, no matter in which mode of execution, electric motor is all configured in and conical ring formula CVT nonoverlapping position vertically, needs the special axial space as electric motor.As the hybrid drive combinationally using conical ring formula CVT and electric motor groups, require the raising of formation and vehicle boarded property compactly.
Summary of the invention
Therefore, the object of the present invention is to provide the hybrid drive improving vehicle boarded property by configuring conical ring formula stepless speed changer and electric motor compactly.
Hybrid drive of the present invention (1) possesses: input shaft (6), and this input shaft (6) and engine output shaft (54) link; Electric motor (2); And conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) (3), this conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) (3) has: the input side friction wheel (22) of cone shape and outlet side friction wheel (23), this input side friction wheel (22) and outlet side friction wheel (23) be configured in be parallel to each other axle (l-l), on (n-n), and configure contrary mode with side, large footpath and path side and be configured; Ring (25), this ring (25) is clamped by the opposed plane of inclination of two friction wheels in the mode of surrounding the side in above-mentioned two friction wheels; and variable speed operation unit (60), this variable speed operation unit (60) carries out variable speed operation by making this ring move, the rotation of above-mentioned input shaft (6) is passed to carry-out part via above-mentioned conical friction wheel ring type stepless speed changes devices (3), and the transmission of power of above-mentioned electric motor (2) is to described carry-out part (39l, 39r), and by the transmission of power of above-mentioned electric motor (2) to above-mentioned carry-out part (39l, 39r), the feature of above-mentioned hybrid drive (1) is, above-mentioned input side friction wheel (22) and above-mentioned input shaft (6) are configured on the first axle (I) coaxial with engine output shaft, above-mentioned outlet side friction wheel (23) is configured on the second axle (II) parallel with above-mentioned first axle (I), above-mentioned electric motor (2) is configured on the 3rd axle (III) parallel with above-mentioned first axle (I) and the second axle (II), above-mentioned conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) (3) and above-mentioned electric motor (2) to be configured to when observing from radial direction at least partially overlapping (such as with reference to Fig. 2) vertically, when from (such as with reference to Fig. 5 ~ Fig. 9) during end on observation, above-mentioned 3rd axle (III) is configured in compares the position that following vertical line (v-v) is close to above-mentioned friction wheel (the 23 or 22) side do not surrounded by above-mentioned ring (25), above-mentioned vertical line (v-v) to move to by above-mentioned variable speed operation unit (60) through excessive above-mentioned ring (25) that to be close to the above-mentioned friction wheel do not surrounded by above-mentioned ring most (be 23 in Fig. 5 ~ Fig. 7, at Fig. 8, be 22 in Fig. 9) axle center (p 1) side time should
Ring current distribution (t), and with vertical with the line (p-p) of the second axle through above-mentioned first axle.
In addition, as shown in Fig. 5 ~ Fig. 7, not surrounded the friction wheel of side by ring (25) can be outlet side friction wheel (23), and as shown in FIG. 8 and 9, and the friction wheel not surrounded side by ring (25) also can be input side friction wheel (22).Further, the first axle, the second axle and the 3rd axle (also comprising the 4th axle described later) represent special axle (not comprising shared axle) independently, and each axle represents its axle center.Further, electric motor (2) can via above-mentioned conical ring formula CVT(3) drives with above-mentioned carry-out part (39l), (39r) and links, and also direct and above-mentioned carry-out part can not drive and link via this conical ring formula CVT.
Such as with reference to Fig. 5 and Fig. 6 or Fig. 8, when from end on observation, above-mentioned 3rd axle (III) is configured in compares the position that following vertical line (s-s) is close to the above-mentioned friction wheel side (22 or 25) surrounded by above-mentioned ring (25), above-mentioned vertical line (s-s) is with vertical with the line (p-p) of the second axle (II) through above-mentioned first axle (I), and the axle center (p of above-mentioned friction wheel (be 23 at Fig. 5, Fig. 6, be 22 in fig. 8) through not surrounded by above-mentioned ring (25) 1).
Such as with reference to Fig. 5 or Fig. 8, the periphery (2c) of the housing (2) of above-mentioned electric motor is configured to crossing with following line (u-u), when from end on observation, this line (u-u) is tangent with the periphery of this ring within the scope of the whole show of the above-mentioned ring (25) undertaken by (60) above-mentioned variable speed operation unit, and parallel with the line (p-p) linking above-mentioned first axle (I) and the second axle (II).
Such as with reference to Fig. 5 or Fig. 8, when from end on observation, preferably above-mentioned 3rd axle (III) is configured in the line segment (p connecting above-mentioned first axle (I) and the second axle (II) 1-p 2) vertical bisector (q-q) and the axle center (p of above-mentioned friction wheel (23 or 22) through not surrounded by above-mentioned ring (25) 1) and between the line (s-s) vertical with the line (p-p) through above-mentioned first axle (I) and the second axle (II).
Such as with reference to Fig. 2, Fig. 5, above-mentioned hybrid drive (1) possesses differential cross pin (5), this differential cross pin (5) input is from the power of the output shaft (24) linked with above-mentioned outlet side friction wheel (23), and export the above-mentioned carry-out part (39l of left and right to, 39r), above-mentioned differential cross pin (5) is configured in and above-mentioned first axle (I), on second axle (II) and parallel the 4th axle (IV) of the 3rd axle (III), input side friction wheel (22) is made by the friction wheel that above-mentioned ring (25) surrounds, when from end on observation, above-mentioned 4th axle (IV) is configured in the side contrary with above-mentioned 3rd axle (III) relative to above-mentioned first axle (I) of connection with the line (p-p) of the second axle (II), and be configured in the side contrary with above-mentioned first axle (I) relative to above-mentioned vertical bisector (q-q).
In addition, the reference character in above-mentioned bracket, for contrasting accompanying drawing, therefore can not have any impact to the structure described in Patent right requirement scope.
According to the present invention involved by technological scheme 1, because electric motor is configured at the first axle for configuring conical ring formula CVT and three axle parallel with the second axle, and conical ring formula CVT and electric motor are configured to overlapping in the axial direction at least partially, therefore, it is possible to prevent the axle of a part for the first such as coaxial with engine output shaft axle etc. from increasing, axial miniaturization can be realized, and, due to from end on observation, the 3rd axle for configuring electric motor is configured in than the position of line (v-v) near the friction wheel side do not surrounded by ring, above-mentioned line (v-v) moves to the central authorities of this ring of the center axis near the friction wheel do not surrounded by this ring through the ring of conical ring formula CVT, and it is vertical with the line of the second axle with link first axle, therefore, electric motor can near not configured by the friction wheel that ring surrounds, to avoid and conical ring formula CVT, particularly the ring of movement is vertically interfered, also radial miniaturization can be realized, thus, can provide and utilize compact structure to improve the hybrid drive of vehicle boarded performance.
According to the present invention involved by technological scheme 2, from end on observation, because the 3rd axle is configured to than the position of friction wheel side of vertical line (s-s) by being surrounded by ring, the axle center of friction wheel of this vertical line (s-s) through not surrounded by ring, and with vertical with the line of the second axle through the first axle, therefore, electric motor can be configured near the input side of conical ring formula CVT and two friction wheels of outlet side.
According to the present invention involved by technological scheme 3, ring is clamped by the opposed plane of inclination of two friction wheels, and move vertically, due to this ring periphery with link the first axle and the second axle line parallel mobile, and within the scope of its whole show, crossing with the outer tangent line of above-mentioned parallel ring, be configured with this housing to electric motor, therefore, it is possible to be configured to by electric motor as far as possible near conical ring formula CVT, the miniaturization of hybrid drive can be realized.
According to the present invention involved by technological scheme 4, between the vertical bisection (q-q) that the 3rd axle for configuring electric motor is configured in link first axle and the line segment of the second axle and vertical line (s-s), this vertical line (s-s) is not through being surrounded the axle center of the friction wheel of side by ring, and it is vertical with the line through above-mentioned first axle and the second axle, therefore from end on observation, electric motor is arranged in the recess of the gourd shape of a pair friction wheel of the cone shape of conical ring formula CVT, and be configured in the friction wheel side do not surrounded by ring, therefore, electric motor can not with conical ring formula CVT, particularly the ring of movement is vertically interfered, and can be configured near conical ring formula CVT, more reliably can realize radial miniaturization thus.
According to the present invention involved by technological scheme 5, owing to ring to be configured to surround input side friction wheel, the differential cross pin linked by output shaft via conical ring formula CVT is configured in the outlet side friction wheel side do not surrounded by ring, and be the side contrary with electric motor, therefore, match with the configuration of the conical ring formula CVT together with electric motor, ring and variable speed operation mesh merging, differential cross pin can be configured in the position of gathering as non-interfering entirety, hybrid drive entirety can be formed compactly.
Accompanying drawing explanation
Fig. 1 is the sketch that hybrid drive involved in the present invention is shown.
Fig. 2 illustrates the expansion sectional view applying hybrid drive of the present invention.
Fig. 3 is the side view of the gear drive that this hybrid drive is shown.
Fig. 4 is the side view that this conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) is shown.
Fig. 5 is the figure of the configuration relation from end on observation that the electric motor of mode of execution involved in the present invention, conical ring formula CVT and differential cross pin are shown.
Fig. 6 is the figure of the configuration relation that the mode of execution changing a part is shown.
Fig. 7 is the figure of the configuration relation that the mode of execution changing a part is shown.
Fig. 8 is the figure of the configuration relation of each device that other mode of executions involved in the present invention are shown.
Fig. 9 is the figure of the configuration relation that the mode of execution changing a part is shown.
Figure 10 is the plan view after the partly cut-away of the variable speed operation cell mesh that above-mentioned conical ring formula CVT is shown.
Embodiment
Be described applying hybrid drive of the present invention by reference to the accompanying drawings.As shown in Figure 1 and Figure 2, hybrid drive 1 has electric motor 2, conical friction wheel ring type stepless speed changes devices (conical ring formula CVT) 3, differential cross pin 5, the input shaft 6 linked with the output shaft 54 of not shown motor via clutch 4 and gear drive 7.Each device above-mentioned and axle are accommodated in the housing 11 formed by being combined by two housing parts 9,10, and this housing 11 utilizes partition wall 12 to be divided into the first space A and second space B with liquid-tight shape.
Electric motor 2 has the stator 2a being fixed on the first housing parts 9 and rotor 2b being arranged at output shaft 8, one side's side end of output shaft 8 is supported on the first housing parts 9 via bearing 13 in rotatable mode, and the opposing party's side end is supported on the second housing parts 10 via bearing 15 in rotatable mode.Be formed with in a side side of output shaft 8 output gear 16 be made up of gear (small gear), this output gear 16 engages with the intermediate gear (gear) 19 being arranged at input shaft 6 via idler gear 17.The stator 2a of electric motor 2 is covered by the motor casing 9a of the bottomed cylindrical utilizing the first housing parts 9 to be formed, and as shown in Figure 3, the local of output gear 16 is covered by the motor part 10d of the second housing parts 10, this motor part 10d engages with the end face of said motor housing 9a, and is cut open to engage with idler gear 17.
Conical ring formula CVT3 comprises: (taper shape of a side) friction wheel 22 as the cone shape of input side, (taper shape of the opposing party) friction wheel 23 being similarly cone shape as outlet side and metal ring 25.Above-mentioned two friction wheels 22,23 are configured to each axle l-l, n-n and are parallel to each other, and large side, footpath and path side are in axial opposed, above-mentioned ring 25 is configured to be clamped by the opposed plane of inclination of above-mentioned two friction wheels 22,23, and any one party of surrounding in two friction wheels, such as input side friction wheel 22.There is larger thrust at least one party's effect of two friction wheels, utilize the larger clamping pressure based on above-mentioned thrust to clamp above-mentioned ring 25.Specifically, axle power applying unit 28 is formed between outlet side friction wheel 23 and stepless speed changes devices output shaft 24, this axle power applying unit 28 is made up of (with reference to Fig. 1) tilting cam mechanism spheroid being installed in face opposed vertically, this axle power applying unit (cam mechanism) 28 pairs of outlet side friction wheels 23 produce the thrust in the arrow D direction corresponding with transmitting torque, between this outlet side friction wheel 23 and the input side friction wheel 22 supported along the direction of resisting this thrust, larger clamping pressure is produced to ring 25.
One side side (side, the large footpath) end of input side friction wheel 22 is supported on the first housing parts 9 via roller bearing 26, and the opposing party side (path side) end is supported on partition wall 12 via tapered roller bearing 27.One side side (path side) end of outlet side friction wheel 23 is supported on the first housing parts 9 via roller (radial direction) bearing 29, and the opposing party side (side, large footpath) end is supported on partition wall 12 via roller (radial direction) bearing 30.The opposing party's side end applying the output shaft 24 of the thrust in above-mentioned arrow D direction to this outlet side friction wheel 23 is supported on the second housing parts 10 via tapered roller bearing 31.The opposing party's side end of input side friction wheel 22 utilizes stepped part and nut 32 to clamp the inner ring of bearing 27, is carried by above-mentioned tapered roller bearing 27 from the thrust acting on the outlet side friction wheel 23 of this input side friction wheel 22 via ring 25.On the other hand, the reaction force acting on the thrust of outlet side friction wheel 23 acts on output shaft 24 along the opposite direction of arrow D, and this thrust counterforce is carried by above-mentioned tapered roller bearing 31.
Above-mentioned ring 25 moves vertically based on variable speed operation unit (aftermentioned), by changing the contact position of input side friction wheel 22 and outlet side friction wheel 23, carries out stepless change thus to the speed ratio between input block 22 and output block 23.The thrust D corresponding with above-mentioned transmitting torque cancels out each other in the housing 11 of one via above-mentioned two tapered roller bearings 27,31, does not need hydraulic pressure etc. as the equilibrant of external force.
Differential cross pin 5 has differential casing 33, and side's side end of this differential casing 33 is supported on the first housing parts 9 via bearing 35, and the opposing party's side end is supported on the second housing parts 10 via bearing 36.In the inside of this differential casing 33, axle orthogonal to the axial direction is installed, this axle engages with the bevel gear 37,37 as differential carrier, and support left and right live axle (carry-out part) 39l, 39r, be fixed with the bevel gear 40,40 engaged with above-mentioned differential carrier at above-mentioned live axle.In addition, the differential mechanism gear ring (input part) 41 in large footpath is installed in the outside of above-mentioned differential casing 33.
Be formed with gear (small gear) 44 at above-mentioned stepless speed changes devices output shaft 24, above-mentioned differential mechanism gear ring 41 engages with this gear 44.Said motor output gear (small gear) 16, idler gear 17 and intermediate gear (gear) 19 and stepless speed changes devices output gear (small gear) 44 and differential mechanism gear ring (gear) 41 form said gear transmission device 7.Said motor output gear 16 and differential mechanism gear ring 41 are configured at axial overlap, and in addition, intermediate gear 19 and stepless speed changes devices output gear 44 are configured to motor output gear 16 and differential mechanism gear ring 41 at axial overlap.In addition, the gear 45 engaged with stepless speed changes devices output shaft 24 spline is the parking gears locking output shaft at the parking position of speed change lever.Further, although so-called gear represents that the engagement comprising gear and sprocket wheel rotates transfer unit, in the present embodiment, gear drive is the gear drive be all made up of gear.In addition, also can at gear drive usage chain and sprocket wheel, and, also can only via gear drive 7(therefore not via conical ring formula CVT3), the output of electric motor 2 is passed to output gear 44.
Above-mentioned input shaft 6 utilizes ball bearing 46 to be supported on the second housing parts 10, and utilize spline S to engage with the input block 22 of stepless speed changes devices 3 (drive and link) in its one end, further, link with the output shaft 54 of motor via the clutch 4 be accommodated in the 3rd space C utilizing the second housing parts 10 formation in another side.The above-mentioned 3rd C side, space of the second housing parts 10 is opened wide, and links with not shown motor.
Between the axial direction that said gear transmission device 7 is accommodated in electric motor 2 and above-mentioned first space A and the 3rd space C in part that is second space B, this second space B utilizes the second housing parts 10 and partition wall 12 to be formed.The axle supporting portion (27,30) of above-mentioned partition wall 12 is divided with liquid-tight shape by oil sealing 47a, 47b, and the axle supporting portion of the second housing parts 10 and the first housing parts 9 also utilizes oil sealing 47c, 47d, 47e to carry out shaft seal, above-mentioned second space B is configured to liquid-tight shape, in this second space B, be filled with the lubricant oil such as the ATF of established amount.The the first space A utilizing the first housing parts 9 and partition wall 12 to be formed is configured to liquid-tight shape too, and the traction being filled with shearing force under shearing force, particularly the extreme pressure state of established amount larger in the A of this first space is oily.
The stator 2a of above-mentioned electric motor 2 and conical ring formula CVT3 is accommodated in the first housing parts 9 equally, as shown in Figure 2, is configured to (observing from radial direction) overlap vertically.In addition, in fig. 2, although the stator 2a of electric motor 2 is completely overlapping with this conical ring formula CVT3 in the mode being contained in the axial range of conical ring formula CVT3, as long as electric motor 2 and conical ring formula CVT3 are overlapping vertically at least partially.
As Fig. 1 schematically illustrates, clutch 4 is made up of dry single disc clutch, there is the clutch driven plate 4a linked with the engine output shaft 54 and platen 4b becoming outlet side linked with above-mentioned input shaft 6 via damping spring 55, utilize diaphragm spring 56 pairs of platen forces, be connected with clutch driven plate under making this platen normality.Further, release bearing 57 abuts with the core of rotatable mode with above-mentioned platen, by utilizing withdrawal fork 58 to press this bearing 57, carries out rupturing operation thus to above-mentioned clutch 4.Withdrawal fork 58 links with worm gear 50 via connecting rod 53, is engaged with the worm screw 52 of linking with the output shaft of electric actuator that is electric motor A1 at this wheel.
Above-mentioned electric motor A1, worm screw 52, worm gear 50 and connecting rod 53 form clutch operating unit 51, utilize based on the operation of this clutch operating unit 51 of above-mentioned electric actuator (electric motor) A1, above-mentioned clutch 4 is cut off, attended operation, and be maintained at because clamping the worm screw 52 and worm gear 50 that are made up of above-mentioned non-reversible mechanism electric motor A1 stop after the operating position (connect or cut off) of clutch 4 under state.
Next, the work of above-mentioned hybrid drive 1 is described.This hybrid drive 1 is combined with explosive motor by making the 3rd C side, space of housing 11, and makes the output shaft of this motor link with input shaft 6 via clutch 4 and use.The rotation of the input shaft 6 that the power from motor transmits is passed to the input side friction wheel 22 of conical ring formula CVT3 via spline S, is passed to outlet side friction wheel 23 via ring 25 further.
Now, act between two friction wheels 22,23 and ring 25 owing to being compared to for the contact pressure that the thrust in the arrow D direction of outlet side friction wheel 23 is large, and the first space A is filled with traction oil, therefore, the extreme pressure state forming the oil film clamping this traction oil at above-mentioned two between friction wheel and ring is become.In this condition, because traction oil has larger shearing force, the shearing force of this oil film is therefore utilized to carry out transmission of power at two between friction wheel and ring.Thus, although metal contacts with each other, the moment of torsion of regulation can be transmitted also non-skidly, and can not Wear Friction take turns and ring, further, by making ring 25 move smoothly vertically, stepless change is carried out to change with the mode of the contact position of two friction wheels thus.
The rotation of the outlet side friction wheel 23 after this stepless change is passed to the differential casing 33 of differential cross pin 5 via its output shaft 24, output gear 44 and differential mechanism gear ring 41, distributed to live axle 39l, 39r of left and right by power, drive wheel (front-wheel) thus.
On the other hand, the power of electric motor 2 is passed to input shaft 6 via output gear 16, idler gear 17 and intermediate gear 19.Identical with previous explanation, the rotation of this input shaft 6 via conical ring formula CVT3 by stepless change, further via output gear 44, differential mechanism gear ring 41 and be passed to differential cross pin 5.The gear drive 7 be made up of each gear 16,17,19,44,41,37,40 above-mentioned is accommodated in the second space B filling lubricant oil, and when each gears meshing, lubricant oil is mediate and carry out transmission of power smoothly.Now, the differential mechanism gear ring 41 being configured in the lower position of second space B is made up of large diameter gear and lubricant oil of kicking up, reliably and provide lubricant oil to other gears 16,17,19,44 and bearing 27,30,20,21,31,46 fully.
About this point, composition graphs 3 is described in detail.Each gear 41,16,17,19,44 configures as follows in second space B.In the middle of multiple gears 17,19,44 of motor output gear 16, differential mechanism gear ring 41 and formation gear drive 7, differential mechanism gear ring 41 is positioned at bottom.That is, the central shaft IV of differential cross pin 5 is positioned at than motor drive shaft III and input shaft I, even specific output axle II and pony axle V position more on the lower.Further, a part for differential mechanism gear ring 41 is dipped in the oil conservator 48 of lubricant oil, and, be configured to this part and give prominence to upward from the pasta 48a of oil conservator 48.Further, motor output gear 16 and multiple gears 17,19,44 are configured to than pasta 48a by the top, and motor output gear 16 is wherein positioned at the position of the top.Thus, motor output gear 16 is the top gears being positioned at the top in each gear 16,17,19,44.In addition, in order to reduce the rotational resistance of differential mechanism gear ring 41, preferred pasta 48a be set to than differential mechanism gear ring 41 running shaft IV on the lower.That is, make to be dipped in oil conservator 48 than the horizontal line N part on the lower of the running shaft IV through differential mechanism gear ring 41.
Further, differential mechanism gear ring 41 is positioned at than the position of each gear 16,17,19,44 by the left of Fig. 3, rotates along the sense of rotation of regulation that is arrow β direction when vehicle advances.Further, motor output gear 16, idler gear 17 and intermediate gear 19 is utilized to form gear train Y.Idler gear 17 and intermediate gear 19 configure in order in the below of motor output gear 16, and the central shaft (pony axle V, input shaft I) of each gear 17,19 is positioned at and leans on the position with differential mechanism gear ring 41 opposite side than vertical line (line of the Vertical direction) γ of the central shaft (motor drive shaft III) through motor output gear 16.From end on observation, motor drive shaft III in the horizontal direction (left and right directions of Fig. 3) is configured between the central shaft IV of input shaft I and differential cross pin 5.Further, output gear 44 is configured to more lean on above this differential mechanism gear ring 41 than intermediate gear 19 in differential mechanism gear ring 41 side.In addition, the maximum gear of the external diameter in each gear 41,16,17,19,44 above-mentioned is differential mechanism gear ring 41.On the other hand, the external diameter of output gear 44 is than each gear 41,17,19 little a lot (path).
Although the configuration about radial direction of each gear 41,16,17,19,44 is described above, in the axial direction, as shown in Figure 1, the toothed portion being configured to each gear above-mentioned is overlapping vertically.That is, differential mechanism gear ring 41 is configured to, at least partially with motor output gear 16 and multiple gear 17,19,44 overlapping vertically.In this case, the whole or major part of the axial width of the toothed portion of each gear 16,17,19,44 exists in the width range of the axis of the toothed portion of differential mechanism gear ring 41.
To differential mechanism gear ring 41, gear train Y be utilized and guide the space of wall g encirclement to be set to space segment X.Thus, output gear 44 is configured in this space segment X.When the present embodiment so formed, differential mechanism gear ring 41 is rotated along forward direction β, to kick up from differential mechanism side wall surface e along guiding wall f lubricant oil, this lubricant oil can be supplied to motor output gear 16 and multiple gear 17,19,44, also can be supplied to each bearing 15,20,21,46,31,27,30 be present in second space B in addition.Namely, the diameter of differential mechanism gear ring 41 is larger than the diameter of other gears, utilize larger centrifugal force to make to be present in lubricating oil splash in the recess that is formed between the tooth of outer circumferential face and tooth by rotation, effect has the lubricant oil of centrifugal force to kick up along guiding wall g, along this guiding wall g, or disperse in the space segment X of the inner side of this guiding wall g.A part for the lubricant oil dispersed via space segment X is also supplied to each gear 17,19,44, and, the lubricant oil arriving motor output gear 16 flows downwards, is also supplied to each gear 17,19,44 of the below being positioned at motor output gear 16.Further, the lubricant oil utilizing differential mechanism gear ring 41 to kick up in the above described manner is also supplied to each bearing 15,20,21,46,31,27,30 be present in second space B.In addition, that supports the bearing 35,36 of differential casing 33 is dipped in lubricant oil at least partially.
The working method of above-mentioned motor and electric motor, namely can to adopt in various manners as required as the working method of hybrid drive 1.As an example, when vehicle start, cut off clutch 4 and make engine stop, only utilize the moment of torsion of electric motor 2 to start to walk, when reaching fixing speed, piloting engine and clutch 4 is connected, the power of motor and electric motor is utilized to accelerate, when reaching cruising speed, electric motor being set to and rotating freely or regeneration mode, only utilizing motor to advance.When slowing down, braking, electric motor is regenerated, battery is charged.Further, also clutch 4 can be used as start clutch, utilize the power of motor, motor torsional moment is used as auxiliary starting.
When reverse gear, cut off clutch 4 and make engine stop, and in reverse direction rotary actuation being carried out to electric motor 2.Thus, the reversion of motor output shaft 8 is via gear 16,17,19 and be in the conical ring formula CVT3 of lower-speed state and be passed to output shaft 24.And then, be passed to differential cross pin 5 via gear 44,41, make live axle 39l, 39r reversion of left and right, make vehicle rollback.
Next, composition graphs 4 pairs of conical friction wheel ring type stepless speed changes devicess (conical ring formula CVT) 3 are described.As mentioned above, this stepless speed changes devices 3 is made up of input side friction wheel 22, outlet side friction wheel 23 and ring 25, and above-mentioned two friction wheels and ring are made up of metals such as steel.Two friction wheels 22,23 are configured to, and its axle l-l, n-n(are with reference to Fig. 2) be configured in the horizontal direction be parallel to each other, and plane of inclination is made up of the cone shape utilizing straight line to form, and ring 25 is clamped between two opposed plane of inclination.Ring 25 is configured to any one party in encirclement two friction wheels, specifically surround input side (taper shape of a side) friction wheel 22, the cross section in the face vertical with its circumferential direction is made up of almost parallel quadrilateral, and its surface of revolution m-m is set as roughly orthogonal relative to axle l-l (with reference to Figure 10).
Above-mentioned conical ring formula CVT3 utilizes has the first housing parts 9 of bottom tube-like to cover end side and its complete cycle side, and the opening side of said first shell parts 9 is covered by partition wall 12, is accommodated in the first space A with liquid-tight shape.Configure two friction wheels obliquely, with the position making the axle 23a of outlet side (taper shape of the opposing party) friction wheel 23 be positioned at the axle 22a established amount by the top than input side (taper shape of a side) friction wheel 22, input side friction wheel 22 is configured to above it, below and side reciprocal with outlet side friction wheel 23, and has interval between housing parts 9.The ring 25 surrounding above-mentioned input side friction wheel 22 is configured in the space between this input side friction wheel and housing parts 9, and is configured with the variable speed operation unit (device) 60 making this ring 25 movement vertically.In addition, in the diagram, the upper section 9A of housing parts 9 is the parts for configuring electric motor 2,9B is the part for configuring differential cross pin 5, form said motor housing 9a at above-mentioned upper section 9A, its lower surface periphery 2c forms the containing section of conical ring formula CVT3 that is a part for Pear Shaped.Further, the underlying space J-shaped of the above-mentioned input side friction wheel 22 and between above-mentioned housing parts 9 becomes the oil conservator 59(drawn with oil and utilizes 59a to represent pasta).
Fig. 5 is the figure from end on observation electric motor 2, conical ring formula CVT3 and differential cross pin 5.The input side friction wheel 22 of conical ring formula CVT3 is configured in on engine output shaft and coaxial the first axle I of input shaft 6, and outlet side friction wheel 23 is configured on the second axle II.Ring 25 is in the most UD(gearing down contacted with the most minor diameter part of input side friction wheel 22 and the maximum diameter portion of outlet side friction wheel 23) position (is denoted as 25 2), the most OD(overdrive that contacts with the maximum diameter portion of input side friction wheel 22 and the most minor diameter part of outlet side friction wheel 23) position (is denoted as 25 1) between, move vertically to make the center of this ring 25 mode consistent with the line p-p of axle I, II of linking two friction wheels 22,23.The 3rd axle III for configuring electric motor 2 is configured in the position leaning on outlet side friction wheel 23 side do not surrounded by ring 25 than following line v-v, line v-v perpendicular to the line p-p of link first axle I and the second axle II, and moves to the center t of this ring 251 of the P1 side, axle center (namely again OD position) near outlet side friction wheel 23 through above-mentioned ring 25.In addition, the axle such as the first axle, the second axle, the 3rd axle represents axle center (the 4th axle, the 5th axle are also identical).Further, the first axle, the second axle, the 3rd axle (the 4th axle and the 5th axle) expression are all configured to parallel, and independent axle (line) independently.
Thus, prevent the interference of electric motor 2 and the ring 25 of movement vertically, and electric motor 2 is configured in the outlet side friction wheel 23 that do not surrounded by ring 25 around, thus is formed in the also compact hybrid drive of radial direction.
Above-mentioned 3rd axle III is configured in than through above-mentioned ring 25 1the line v-v of center t be not limited to the mode of execution shown in Fig. 5 by the relation of outlet side friction wheel 23 side do not surrounded by ring 25, also there is the mode of execution shown in Fig. 6 or Fig. 7.In the embodiment shown in fig. 6,3rd axle III is positioned at the position close with the line v-v through above-mentioned center t, in this position, although electric motor 2 is configured in the position be slightly separated with conical ring formula CVT3, to avoid interfering with ring 25, but because above-mentioned 3rd axle III moves from above-mentioned line v-v to the second axle II side, therefore electric motor 2 can configure near conical ring formula CVT3.
In the embodiment shown in figure, the 3rd axle III is positioned at the side contrary with the first axle I relative to line s-s, and this line s-s is through the second axle II, and vertical with the line through the second axle II and the 3rd axle III.3rd axle III is configured in the position using the second axle II as the arc-shaped at center in the mode of the periphery around outlet side friction wheel 23, avoids the interference of electric motor 2 and ring 25.In the present embodiment, although also input shaft 6 can be passed to via chain from the power of electric motor 2, preferably output shaft 24 is directly passed to.
And, preferably, as shown in figs.5 and 6, above-mentioned 3rd axle III is configured in than the position of input side friction wheel 22 side of line s-s by being surrounded by ring, this line s-s is with to be connected the first axle I vertical with the line p-p of the second axle II, and the axle center p of outlet side friction wheel 23 through not surrounded by ring 25 1.That is, the 3rd axle III configures between online v-v and line s-s.
Thus, prevent the interference of the ring of electric motor 2 and movement vertically, and configure electric motor 2 near two friction wheels 22,23 of input side and outlet side, thus the miniaturization of width direction can be realized.
As shown in Figure 5, the above-mentioned 3rd axle III being preferred for configuring electric motor 2 is further configured in the line segment p linking above-mentioned first axle I and the second axle II 1-p 2vertical bisector q-q and line s-s between, above-mentioned line s-s is through the axle center p of the friction wheel contrary with the friction wheel surrounded by ring 25 (input side friction wheel) 22 that is outlet side friction wheel 23 1, and vertical with the line (p-p) linking above-mentioned first axle and the second axle (II).The periphery 2c of the said motor housing 9a of electric motor 2 is configured to crossing with line u-u, and this line u-u is tangent with the periphery of this ring within the scope of the whole show of ring 25, and parallel with the line p-p connecting above-mentioned first axle and the second axle.
According to configuring formation above, although electric motor 2 is configured to and conical ring formula CVT3, particularly the input side friction wheel of coaxial with engine output shaft (I) is overlapping vertically, form compactly vertically, but from end on observation, electric motor 2 is positioned at the concave portion of the input side friction wheel 22 of the cone shape utilizing conical ring formula CVT3 and the gourd shape of outlet side friction wheel 23 formation, and is configured in outlet side friction wheel 23 side do not surrounded by ring 25.Thus, based on the above-mentioned circumscribed parallel lines u-u of ring 25 in the whole show scope overall region of the ring relation parallel with the line p-p linking above-mentioned first axle and the second axle, electric motor 2 can not be interfered with this ring in the whole show scope of this ring 25, and can configuration be positioned as close to, the miniaturization of hybrid drive can be realized.
In addition, in the mode of execution shown in Fig. 5, the 4th axle IV being configured with differential cross pin 5 is positioned at the side contrary with above-mentioned 3rd axle III relative to the line p-p of link first axle I and the second axle II, and relative to above-mentioned vertical bisector q-q, be configured in the side that is outlet side friction wheel 23 side that are not surrounded by ring.
Therefore, differential cross pin 5 also configures near conical ring formula CVT, to avoid interfering with conical ring formula CVT3, particularly ring 25, from end on observation, the compact unit of centralized configuration electric motor 2, conical ring formula CVT3 and differential cross pin is utilized to form rational configuration structure, thus the height of hybrid drive entirety can be suppressed, realize miniaturization.
Fig. 8 and Fig. 9 illustrates the figure being configured to the configuration structure surrounding outlet side friction wheel 23 from the ring 25 of the conical ring formula CVT3 of end on observation.Ring 25 is in the most UD(gearing down contacted with the most minor diameter part of input side friction wheel 22 and the maximum diameter portion of outlet side friction wheel 23) position (is denoted as 25 3) and the most OD(overdrive that contacts with the maximum diameter portion of input side friction wheel 22 and the most minor diameter part of outlet side friction wheel 23) position (is denoted as 25 4) between, move vertically to make the center of this ring 25 mode consistent with the line p-p of axle I, II of linking two friction wheels 22,23.In the present embodiment, identical with the mode of execution shown in Fig. 5 ~ Fig. 7, the 3rd axle III for configuring electric motor 2 is configured to the position leaning on input side friction wheel 22 side do not surrounded by ring 25 than line v-v, and this line v-v moves to the axle center p near outlet side friction wheel 22 through above-mentioned ring 25 1this ring 25 of (most UD position) during side 3center, and with vertical with the line p-p of the second axle II through the first axle I.
Thus, prevent the interference of electric motor 2 and the ring 25 of movement vertically, and electric motor 2 is configured in the input side friction wheel 22 that do not surrounded by ring 25 around, thus is formed in the also compact hybrid drive of radial direction.
Further, as shown in Figure 8, preferably, above-mentioned 3rd axle III is configured in than the position of outlet side friction wheel 23 side of line s-s by being surrounded by ring, the axle center p of input side friction wheel 22 of above-mentioned line s-s through not surrounded by ring 25 1, vertical with the line p-p of the second axle II with link first axle I.That is, the 3rd axle III configures between online v-v and line s-s.
Thus, the interference between the ring preventing electric motor 2 and movement vertically, and configure electric motor 2 near two friction wheels 22,23 of input side and outlet side, thus radial miniaturization can be realized.
In the mode of execution shown in Fig. 9, conical ring formula CVT3 is configured to longitudinal direction.That is, input side friction wheel 22 is configured in top, outlet side friction wheel 23 being configured in below, therefore, is the position slightly tilted relative to vertical line through the line p-p of the first axle I and the second axle II.In the present embodiment, because the 3rd axle III is configured in the side contrary with the outlet side friction wheel 23 surrounded by ring 25 relative to input side friction wheel 22, therefore electric motor 2 can not be interfered with above-mentioned ring 25, is being formed radially compact structure.
As shown in Figure 8, being preferred for configuring the above-mentioned 3rd axle III of electric motor 2 is further configured between vertical bisector q-q and line s-s, above-mentioned vertical bisector q-q be link the first axle I for configuring input side friction wheel 22 with for configuring the line segment p of the second axle II of outlet side friction wheel 23 1-p 2vertical bisector, above-mentioned line s-s is through the friction wheel of side that do not surrounded by ring 25 that is the axle center p of input side friction wheel 22 1, and vertical with the line p-p linking above-mentioned first axle and the second axle (I).Further, the periphery 2c of the housing of electric motor 2 is configured to crossing with line u-u, and this line u-u is tangent with the periphery of this ring within the scope of the whole show of ring 25, and is parallel to above-mentioned line p-p.
Therefore, in the present embodiment, identical with the mode of execution shown in Fig. 5, electric motor 2 can not be interfered with ring 25, can configure near conical ring formula CVT3 as far as possible.
Although the 4th axle IV for configuring differential cross pin 5 to be positioned at relative to above-mentioned line p-p the side this point contrary with the 3rd axle III with before mode of execution identical, but in the present embodiment, above-mentioned 4th axle IV is configured in outlet side friction wheel 23 side surrounded by ring 25 relative to above-mentioned vertical bisector q-q.As shown in Figure 2, the gear ring 41 of the largest diameter of differential cross pin 5 is in the position being different from conical ring formula CVT3 vertically can not interfere with this CVT, overall as hybrid drive, can gather compactly.
As shown in Fig. 4 and Figure 10, above-mentioned variable speed operation unit 60 has: ballscrew shaft 61, and this ballscrew shaft 61 is configured in the superjacent air space F of input side friction wheel 22; Guide rail 62, this guide rail 62 is configured in the underlying space J becoming above-mentioned oil conservator 59; And moving member 63, this moving member 63 is configured in space, side G, to surround the face contrary with outlet side friction wheel 23 of input side friction wheel 22.Ballscrew shaft 61 and guide rail 62 are in the upper-lower position clamping above-mentioned input side friction wheel 22, and are configured to be parallel to each other, and two conical friction wheels 22,23 are configured to along opposed inclined-plane parallel.Ballscrew shaft 61 is supported on housing parts 9 in rotatable mode, and in the outside of this housing parts 9, link with electric actuator that is electric motor A2, be suitably driven in rotation based on the wish of the drivers such as accelerator pedal and the drive singal from control device corresponding with the form situation of vehicle.
Moving member 63 is supported to and freely can moves vertically at above-mentioned ballscrew shaft 61 and guide rail 62, be fixed with the ball nut portion 65 screwed togather with ballscrew shaft 61 on the top of moving member 63, and be fixed with in the bottom of moving member 63 that be supported to can at the slide part 66 of above-mentioned guide rail 62 movement vertically.And then, in the face contrary with ball nut portion 65 that is the inner face side of above-mentioned moving member 63, be provided with (first) support unit 67, in contrary side that is the inner face side of above-mentioned slide part, be provided with down (second) support unit 69.Although above-mentioned upper support portion part 67 and lower support parts 69 are relative to comprising the planar configuration of axle l-l, n-n of two friction wheels 22,23 of input side and outlet side at not homonymy, two support units 67,69 are configured to respectively apart from above-mentioned plane position supporting ring 25 farthest.In addition, so-called moving axially of variable speed operation is carried out to above-mentioned ring 25 represent the direction of moving member 63 along the above-mentioned ballscrew shaft 61 be parallel to each other and guide rail 62 movement, namely along the direction on the opposed inclined-plane of two friction wheels 22,23 with loop contacts, different from the axle of two friction wheels.The central shaft of ring 25 is positioned at the position parallel with above-mentioned opposed inclined-plane, and therefore, the upper end of this ring and lower end are moved along the face parallel with the plane (p-p) of axle center I, II of comprising two friction wheels.
Although above-mentioned upper support portion part 67 and lower support parts 69 can support this ring 25 in the mode of carrier ring 25, and move integratedly with moving member 63, ring 25 is moved vertically, but upper support portion part and lower support parts 67,69 are configured to, the upstream side of the sense of rotation drawn in by the contacting part with two friction wheels 22,23 at ring 25 with from two sides supporting ring 25 and the mode limiting (clamping) in the axial direction link, and allow moving axially (vibration) of ring 25 in the sense of rotation downstream side be forced out from above-mentioned contacting part.Therefore, no matter friction wheel carries out positive rotation or despining, ring 25 is all supported in the mode of clamping by the support unit 67 or 69 of any one party being up and down located thereon trip side, located accordingly with based on the movement of moving member 63 or the position of stopping, the support unit 69 or 67 of the opposing party of upper and lower any one party allows the vibration being now in above-mentioned movement or the ring 25 in stopping, and ring 25 supports with being restrained oneself.
Although ring 25 utilizes the support unit 67 or 69 of rotation upstream side and the contacting part of this ring 25 and two friction wheels that limit and move axially to determine its tilt angle (also comprising tilt angle 0 orthogonal to the axis), but because above-mentioned support unit is at the position supporting ring farthest away from contacting part, therefore the tilt angle of ring is stablized, the speed easily can carrying out correct variable speed operation and constant speed maintains operation, and can the tilt angle of the easily and reliably ring that setting is corresponding with the travelling speed of moving member 63, the speed change under rapid response speed can be carried out.
Above-mentioned moving member 63 has the linking department extended in circular arc in the mode in the outside along input side friction wheel 22 between the ball nut portion 65 in upper end and the slide part 66 in lower end, the groove 71 of Rack and prescribed depth is formed, to receive above-mentioned ring 25 at the inner peripheral surface of this linking department.Further, oily conductor 72 is fixed with in the front end, underpart of above-mentioned moving member 63.Oil conductor 72 is made up of sheet metal parts, and its cross section is " コ " font and is made up of the arc-shaped of predetermined angular, receives above-mentioned ring 25 at its recess.The front end of this oily conductor 72 is positioned at the position of the contacting part of close ring and friction wheel in the scope of not interfering with outlet side friction wheel 23, and form free end, the periphery along above-mentioned ring 25 extends.In addition, the recess of above-mentioned groove 71 and oily conductor 72 is set to: even if the width that ring 25 deflection also can not be interfered with this ring when carrying out variable speed operation.Further, due to moving member 63 within it side face have storage ring 25 groove 71, therefore, it is possible to correspondingly reduce, to the outstanding size of ring outside diameter, the compactedness of conical ring formula CVT3 can be improved.
And then the guide rail 62 of above-mentioned variable speed operation unit 60 and slide part 66 are axially dipped in above-mentioned oil conservator 59 within the scope of (movement direction) whole show.In addition, lower support parts 69 are also dipped in above-mentioned oil conservator 59 within the scope of the axis of moving member 63 (movement direction) whole show.On the other hand, be positioned at the ball nut portion 65 on the top of moving member 63 and ballscrew shaft 61 axially (movement direction) whole show scope be positioned at the top of pasta 59a.In addition, upper support portion part 67 is also positioned at the top of pasta 59a within the scope of the axis of moving member 63 (movement direction) whole show, is not dipped in oil conservator 59.In addition, before vehicle and then when conical ring formula CVT3 rotates forward, input side friction wheel 22 rotates towards the arrow K direction of Fig. 4, above-mentioned ring 25, axially within the scope of (movement direction) whole show, rotates from the state being dipped in oil conservator 59 upward in the mode of the contacting part towards this ring 25 and two friction wheels 22,23.And, in the above-described embodiment, although guide rail 62 and slide part 66 are dipped in oil conservator 59 within the scope of its movement direction whole show, also can be dipped in above-mentioned oil conservator 59 within the scope of whole show, the axial part that also can be configured to guide rail 62 is positioned at the top of pasta 59a.
Therefore, no matter conical ring formula CVT3 carries out rotating forward or reversing, any shift position during from maximum speed position to lowest speed position, guide rail 62 and the slide part 66 of variable speed operation unit 60 are always dipped in oil conservator 59, and the feed screw mechanism be made up of ballscrew shaft 61 and ball nut portion 65 is positioned at the top of pasta 59a.Although when utilizing the rotation of ballscrew shaft 61 to make moving member 63 move abreast along the opposed plane of inclination of two friction wheels 22,23, the slide mechanism be made up of guide rail 62 and slide part 66 is always positioned at oil conservator, moving member 63 is moved in parallel smoothly, but feed screw mechanism is always positioned at the top of pasta 59a, and do not stir the oil of oil conservator 59, the energy loss caused because this oil stirs can not be produced.And then when vehicle advances, ring 25 also rotates along the arrow K direction of Fig. 4, this ring 25 is kicked up oil in oil conservator 59, is directed to oily conductor 72, and is directed to the contacting part with above-mentioned two friction wheels 22,23 by the oil that this endless belt rises.The traction oil of the substantial amount produced by this oily conductor 72 is installed in the contacting part of ring 25 and two friction wheels 22,23, carry out the reliable frictional power transmission based on above-mentioned shearing force thus, and carry out moving axially along with the smooth ring 25 rotated, carry out quick variable speed operation exactly thus.In addition, a part for oil is driven and is supplied to upper support portion part 67 together with ring 25, and disperses by centrifugal force, is supplied to ballscrew shaft 61 and ball nut portion 65.And then the part oil being attached to ring 25 is directed to the groove 71 of moving member 63, returns oil conservator 59.
To disperse and the oil being supplied to ballscrew shaft 61 is fed into the above-mentioned thread spindle 61 wanting to carry out with ball nut portion 65 screwing togather from above-mentioned ring 25, correspondingly accurately be supplied to the position of being undertaken screwing togather by ballscrew shaft and nut portions form according to the movement of above-mentioned ring 25 and need the above-mentioned ball screw shaft portion that carries out lubricating, even if ballscrew shaft is positioned at the top of pasta 59a, suitable lubrication also can be utilized to make moving member 63 move smoothly.Further, guide rail 62 and slide part 66 are dipped in oil conservator 59, thus utilize lubrication fully to guide moving member 63 smoothly, and even if above-mentioned slide part 66 is dipped in oil conservator 59, the slip work of above-mentioned slide part 66 also not too affects the stirring of oil conservator.
When conical ring formula CVT3 rotates forward, the lower support parts 69 being dipped in oil conservator 59 become the working part moved axially of limit collar 25, and this working part can make ring 25 rotate smoothly in oil conservator 59, and limits moving axially of this ring 25.On the other hand, because upper support portion part 67 allows moving axially of ring 25, the oil being therefore attached to ring 25 lubricates fully, can not damage the rotation of ring 25.
On the other hand, when vehicle rollback, ring 25 rotates along the opposite direction of arrow K, and the groove 71 that the oil that the ring 25 being dipped in oil conservator 59 is kicked up is moved parts 63 guides and drives and guide to upper support portion part 67.When conical ring formula CVT3 reverses, upper support portion part 67 becomes the working part moved axially of limit collar, utilizes the more sufficient oil by above-mentioned groove 71 guides to lubricate, ring 25 is rotated smoothly, and limits moving axially of this ring 25.And then the oil driven further along with the rotation of ring 25 is supplied to the contacting part of ring and friction wheel, carries out based on the friction driving of above-mentioned shearing force and moving axially of ring 25.Now, compared with during rotating forward, when reversing, although the oil mass becoming the upper support portion part 67 of the axially locating working part of ring and the contacting part of ring and friction wheel is less, but compared with during advance, the service time of the fallback state of vehicle is a lot of less, and necessary torque capacity and speed change region also smaller, therefore, even above-mentioned fewer oil mass, also can not counteract frictional power transmission and variable speed operation, can accurately and carry out transmission of power and variable speed operation smoothly.
In addition, although variable speed operation unit 60 carries out variable speed operation by movement vertically, so that the part being positioned at the upstream side of rotation of carrier ring 25, but be not limited thereto, also can operate ring 25 and make it tilt, this ring is moved axially along tilt angle (for example, referring to WO2005/061928 publication).
The present invention relates to explosive motor and the electric motor hybrid drive as driving source, can utilize and all automobiles such as riding vehicle, bus, truck, and these operation vehicles such as operation car for building such as agricultural operation car, bulldozer etc. of tractor etc.
Description of reference numerals
1: hybrid drive; 2: electric motor; 3: conical friction wheel ring type stepless speed changes devices (conical ring formula CVT); 5: differential cross pin; 6: input shaft; 22: input side friction wheel; 23: outlet side friction wheel; 25: ring; 39l, 39r: carry-out part; 41: input part (gear ring); 54: engine output shaft; 60: variable speed operation unit; I: the first axle; II: the second axle; III: the three axle; IV: the four axle; P-p: through the line of the first axle and the second axle; p 1-p 2: line segment; Q-q: vertical bisector; S-s: perpendicular to the line of p-p; T: Ring current distribution; V-v: through the vertical line of t; U-u: the line parallel with p-p; L-l, n-n: axle.

Claims (6)

1. a hybrid drive,
This hybrid drive possesses:
Input shaft, this input shaft and engine output shaft link;
Electric motor; And
Conical friction wheel ring type stepless speed changes devices, this conical friction wheel ring type stepless speed changes devices has: the input side friction wheel of cone shape and outlet side friction wheel, this input side friction wheel and outlet side friction wheel are configured on the axle that is parallel to each other, and are configured in the mode that side, large footpath is contrary with path side; Ring, this ring is clamped by the opposed plane of inclination of two friction wheels in the mode of surrounding the side in described two friction wheels; Variable speed operation unit, this variable speed operation unit carries out variable speed operation by making this ring move,
The rotation of described input shaft is passed to carry-out part via described conical friction wheel ring type stepless speed changes devices, and the transmission of power of described electric motor is to described carry-out part,
The feature of described hybrid drive is,
Described input side friction wheel and described input shaft are configured on the first axle coaxial with engine output shaft,
Described outlet side friction wheel is configured on the second axle parallel with described first axle,
Described electric motor is configured on the 3rd axle parallel with described first axle and the second axle,
Described conical friction wheel ring type stepless speed changes devices and described electric motor are configured to when observing from radial direction overlapping in the axial direction at least partially,
When from end on observation, described 3rd axle is configured in compares the position that following vertical line is close to the described friction wheel side do not surrounded by described ring, described vertical line is with vertical with the line of the second axle through described first axle, and this Ring current distribution when excessive described ring moves to the center axis being close to the described friction wheel do not surrounded by described ring most by described variable speed operation unit.
2. hybrid drive according to claim 1, is characterized in that,
When from end on observation, described 3rd axle is configured in compares the position that following vertical line is close to the described friction wheel side surrounded by described ring, described vertical line is with vertical with the line of the second axle through described first axle, and the axle center of described friction wheel through not surrounded by described ring.
3. hybrid drive according to claim 1, is characterized in that,
The periphery of the housing of described electric motor is configured to crossing with following line, when from end on observation, this line is tangent with the periphery of this ring within the scope of the whole show of the described ring undertaken by described variable speed operation unit, and with link the line parallel of described first axle and the second axle.
4. hybrid drive according to claim 2, is characterized in that,
The periphery of the housing of described electric motor is configured to crossing with following line, when from end on observation, this line is tangent with the periphery of this ring within the scope of the whole show of the described ring undertaken by described variable speed operation unit, and with link the line parallel of described first axle and the second axle.
5., according to the hybrid drive in Claims 1 to 4 described in any one, it is characterized in that,
When from end on observation, described 3rd axle be configured in the line segment linking described first axle and the second axle vertical bisector and through the axle center of described friction wheel that do not surrounded by described ring and between the vertical line vertical with the line through described first axle and the second axle.
6. hybrid drive according to claim 5, is characterized in that,
Described hybrid drive possesses differential cross pin, and the input of this differential cross pin from the power of the output shaft linked with described outlet side friction wheel, and exports the described carry-out part in left and right to,
Described differential cross pin is configured on the 4th axle parallel with described first axle, the second axle and the 3rd axle,
Input side friction wheel by the described friction wheel that described ring surrounds, when from end on observation, described 4th axle is configured in the side contrary with described 3rd axle relative to described first axle of link with the line of the second axle, and is configured in the side contrary with described first axle relative to described vertical bisector.
CN201180005585.0A 2010-03-08 2011-02-24 Hybrid drive device Active CN102713353B (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
JP2010-050645 2010-03-08
JP2010050645A JP5099154B2 (en) 2010-03-08 2010-03-08 Conical friction wheel ring type continuously variable transmission
JP2010051486A JP5051254B2 (en) 2010-03-09 2010-03-09 Hybrid drive unit
JP2010-051486 2010-03-09
JP2010-053764 2010-03-10
JP2010053764A JP5029716B2 (en) 2010-03-10 2010-03-10 Conical friction wheel ring type continuously variable transmission
JP2010-077895 2010-03-30
JP2010077894 2010-03-30
JP2010-077894 2010-03-30
JP2010077895 2010-03-30
JP2011019176A JP5263311B2 (en) 2010-03-30 2011-01-31 Hybrid drive device
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Publication number Priority date Publication date Assignee Title
CN107206892A (en) * 2015-02-12 2017-09-26 爱信艾达株式会社 Automatic transmission
CN107289082B (en) * 2016-03-30 2021-11-30 罗伯特·博世有限公司 Conical ring type stepless gearbox
CN112032275B (en) * 2019-06-03 2021-07-20 哈尔滨工业大学 Mechanical four-axis differential device

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10331935A (en) * 1997-05-19 1998-12-15 Ulrich Rohs Conical friction ring type transmission
JP2004168208A (en) * 2002-11-21 2004-06-17 Nissan Motor Co Ltd Driving device for hybrid vehicle
CN1606669A (en) * 2003-01-06 2005-04-13 乌尔里克·罗斯 Pressing device for tensioning two gearing elements, gearing provided with a pressing device of this type, and method for operating such a friction gearing
WO2005061928A2 (en) * 2003-12-23 2005-07-07 Ulrich Rohs Continuously variable transmission
WO2008104142A1 (en) * 2007-02-26 2008-09-04 GIF Gesellschaft für Industrieforschung mbH Drive arrangement with a continuously variable sub-gear mechanism
CN101392824A (en) * 2002-09-30 2009-03-25 乌尔里克·罗斯 Rotary transmission
JP2009243559A (en) * 2008-03-31 2009-10-22 Aisin Aw Co Ltd Power transmission device
CN100564954C (en) * 2003-12-23 2009-12-02 乌尔里克·罗斯 Infinitely variable speed transmission

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1568406B (en) * 2002-09-30 2011-10-05 乌尔里克·罗斯 Infinitely variable adjustable gearbox
DE102004003716A1 (en) * 2004-01-24 2005-08-11 Zf Friedrichshafen Ag Cone Ring Transmission
JP4203527B1 (en) * 2007-07-18 2009-01-07 アイシン・エィ・ダブリュ株式会社 Hybrid vehicle drive device
JP5246466B2 (en) * 2007-10-19 2013-07-24 アイシン・エィ・ダブリュ株式会社 Hybrid drive device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10331935A (en) * 1997-05-19 1998-12-15 Ulrich Rohs Conical friction ring type transmission
CN101392824A (en) * 2002-09-30 2009-03-25 乌尔里克·罗斯 Rotary transmission
JP2004168208A (en) * 2002-11-21 2004-06-17 Nissan Motor Co Ltd Driving device for hybrid vehicle
CN1606669A (en) * 2003-01-06 2005-04-13 乌尔里克·罗斯 Pressing device for tensioning two gearing elements, gearing provided with a pressing device of this type, and method for operating such a friction gearing
WO2005061928A2 (en) * 2003-12-23 2005-07-07 Ulrich Rohs Continuously variable transmission
CN100564954C (en) * 2003-12-23 2009-12-02 乌尔里克·罗斯 Infinitely variable speed transmission
WO2008104142A1 (en) * 2007-02-26 2008-09-04 GIF Gesellschaft für Industrieforschung mbH Drive arrangement with a continuously variable sub-gear mechanism
CN101663507A (en) * 2007-02-26 2010-03-03 Gif工业研究有限责任公司 The driving arrangement that has the pinion case of continuously variable
JP2009243559A (en) * 2008-03-31 2009-10-22 Aisin Aw Co Ltd Power transmission device

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