WO1995016584A1 - Systeme de transfert - Google Patents
Systeme de transfert Download PDFInfo
- Publication number
- WO1995016584A1 WO1995016584A1 PCT/JP1994/002122 JP9402122W WO9516584A1 WO 1995016584 A1 WO1995016584 A1 WO 1995016584A1 JP 9402122 W JP9402122 W JP 9402122W WO 9516584 A1 WO9516584 A1 WO 9516584A1
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- WO
- WIPO (PCT)
- Prior art keywords
- gear
- output member
- sun gear
- transfer structure
- carrier
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
- B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
- B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
- B60K17/3467—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H2048/02—Transfer gears for influencing drive between outputs
- F16H2048/04—Transfer gears for influencing drive between outputs having unequal torque transfer between two outputs
Definitions
- the present invention relates to a transfer structure that distributes driving force to a front wheel side and a rear wheel side in a four-wheel drive vehicle, and particularly relates to a transfer structure configured to perform driving force distribution using a planetary gear mechanism.
- a four-wheel drive vehicle is provided with a transfer that distributes the driving force from the engine to the front wheel side and the rear wheel side, but there is a conventional transfer structure as shown in FIG. 18, for example. .
- a transfer structure as shown in FIG. 18, between the input shaft 101, the front wheel output shaft 102, and the rear wheel output shaft 103, a high-speed One switching planetary gear 104 and a planetary gear type center differential (hereinafter, differential is abbreviated as differential) 105 are provided.
- the engine torque input to the input shaft 101 is switched to high-speed rotation (high) or low-speed rotation (low) by turning on / off the dog clutch 106. Output.
- the engine torque set to high or low by the high-to-one switching planetary gear 104 is applied to the planetary carrier through the shaft 107, and the engine torque
- the planetary gear type center differential 105 is provided with a lock clutch 110 so that the differential between the front and rear wheels can be completely restricted to enable direct four-wheel drive travel. .
- this transfer structure consists of an input shaft 201, a front wheel output shaft (front propeller shaft) 202, and a rear wheel output shaft (propeller shaft) 203.
- a high-low switching mechanism 204 as a sub-transmission, a viscous coupling 222 that limits the differential between the center differential 205 and the center differential 205, and a high-mouth switching mechanism
- An axis 206 is provided to communicate 204 and the center differential 205.
- the high / mouth switching mechanism 204 includes a gear 201 A provided on the input shaft 201, a gear 206 A provided on the drive transmission shaft 206, and a counter shaft 200.
- Gears 2 0 7A which are shifted at a lower speed than the gear 2 0 1 A of the input shaft 2 1 provided on the input shaft 2 It is composed of a sleeve 208 provided so as to be able to cope with 206 A and 200 A, and by moving the sleeve 208 in the axial direction, the gear 206 A is shifted to the gear 210.
- a high-speed mode that couples to gear A a low-speed mode that couples gear 206 A to gear 206 A, and a sleeve 208 that only engages with gear 206 A, Neither 206 A nor 207 A can select a neutral mode in which neither is linked.
- the center differential 205 is a bevel gear type, and has input pinions 205 A, 205 A provided at the rear end of the drive transmission shaft 206, and these input pinions 205 A, 200. It has a front wheel output pinion 205 B and a rear wheel output pinion 205 C that combine with 5 A.
- the front wheel output pinion 205B is provided at the rear end of the hollow shaft 209, and the hollow shaft 209 is connected to the front drive gear 211A via the 2WD / 4WD switching mechanism 210. Sa It is.
- the rear wheel output pinion 205 C is provided at the front end of the rear wheel output shaft 203.
- 2 WDZ 4WD switching mechanism 210 includes a gear 206 B provided at an intermediate portion of the drive transmission shaft 206, a gear 209 A provided at a front end of the hollow shaft 209, and a front drive.
- the gear 2 11 B provided at the front end of the hollow shaft 2 1 1 provided with the gear 2 11 A and the gear 2 06 B, 2 0 9 A, 2 1 1 B
- a four-wheel drive mode (4WD mode) in which the front and rear differential is allowed to integrally connect the hollow shaft 209 and the hollow shaft 211, and the drive transmission shaft 206, the hollow shaft 209 and the hollow It is possible to select a four-wheel drive mode (4WD lock mode) in which the front and rear differentials in which the shaft 211 is integrally connected together are completely regulated.
- the hollow shaft 209 and the hollow shaft 211 rotate integrally, the differential function of the center differential 205 is exhibited, and the transmission 211 to the transmission 211 to the high
- the engine torque transmitted to the drive transmission shaft 206 through the mouth-to-mouth switching mechanism 204 is transmitted from the rear wheel output pinion 205 C to the rear wheel output shaft 203, and Front wheel output pinion 205 B force, etc., hollow shaft 209, 2 WDZ 4 WD switching mechanism 210, hollow It is sent to the front drive gear 2 11 A via the shaft 2 11.
- the engine torque distributed to the rear-wheel output shaft 203 is transmitted through the above-described path to drive the rear wheels 218 L and 218 R, but the front drive gear 2
- the engine torque distributed to 11 A is transmitted to the front wheel side output shaft 202 through the transfer chain 220 and then to the front wheel drive shaft 22 23 through the bevel gear mechanism 22 1 and the front differential 22 2.
- L, 223R, and the front wheels 224L, 224R are driven.
- 2 25 is a free wheel mechanism. In this case, the differential between the front and rear wheels is allowed, but the differential regulation of the viscous coupling 2 26 is performed according to the differential between the front and rear wheels, and the torque distribution state to the front and rear wheels is changed. .
- the drive transmission shaft 206, the hollow shaft 209, and the hollow shaft 211 rotate integrally, so that the center differential 205 is locked, and the engine torque is reduced. And the drive transmission shaft 206, the center differential 205 and the rear wheel side output shaft 203.
- the drive transmission shaft 206, the center differential 205 and the hollow shaft 209, 2WDZ 4 The transmission is transmitted to the front drive gear 211A via the WD switching mechanism 210 and the hollow shaft 211, and along the same route as described above, the rear wheels 21 8L, 21 18R and the front wheels 22 Sent to 4 L, 2 24 R. At this time, since differential is not allowed between the front and rear wheels, the engine torque is reliably sent to the front and rear wheels.
- the transfer 300 is provided at an output portion of a 4-speed automatic transmission 303 connected to the engine 302, and is provided with a compound planetary gear. And a plurality of clutches 312, 313 and a brake 314.
- Senyu Def 3 01 is a 4-speed automatic transmission 3 0 3 Between the input shaft 304 that receives the engine torque from the engine, the front drive gear 300 that is combined with the gear 300 A of the front wheel output shaft 300, and the rear wheel output shaft 300.
- a first element comprising a first sun gear 301A, a second element comprising a second sun gear 301B, a first pinion gear 301C and a second pinion gear 3 integrated with each other.
- a third element consisting of 0 1 D.
- the first sun gear 301A is coupled to the input shaft 304 so as to rotate integrally therewith.
- the first pinion gear 301C and the second pinion gear 301D rotate by the planetary carrier 301E.
- the first sun gear 301A and the second sun gear 301B are freely and integrally supported with the shaft, respectively.
- the front drive gear 303 is coupled so as to rotate integrally with the planetary carrier 301 E.
- the drive transmission shaft 310 is coupled to the planetary carrier 301 E.
- a hollow drive transmission shaft 309 is connected to the second sun gear 301B.
- a clutch 3 1 2 for realizing the wheel drive mode is interposed.
- the clutch 312 When the clutch 312 is engaged, the second sun gear 310B is coupled to the rear wheel output shaft 307, and the engine torque input from the first sun gear 301A is applied to the first pinion gear.
- the transmission is transmitted from 301 C through the planetary carrier 310 E to the front drive gear 303, while the first pinion gear 310 C transmits to the second pinion gear 310 D and the second sun gear 3.
- the clutch 312, and the drive transmission shaft 309 are transmitted to the rear wheel output shaft 307.
- 315 is a bevel gear mechanism
- 316 is a front differential
- 317L and 317R are front wheel drive shafts.
- a front-rear differential limiting clutch 313 is interposed between the drive transmission shaft 310 of the center differential 301 and the drive transmission shaft 310 of the rear wheel output shaft 307. Have been.
- the front-rear differential limiting clutch 3 13 is engaged, the front drive gear 30 6 and the rear wheel side are passed through the drive transmission shaft 3 08, the clutch 3 13, and the rear wheel output shaft 3 07. Since the output shaft 307 tries to rotate together, the differential between the front and rear wheels is limited.
- a brake 314 is provided between the drive transmission shaft 309 on the side of the center differential 301 and the mission case 311.
- the second sun gear 3 0 1 ⁇ ⁇ does not rotate, so the engine torque input from the 1st sun gear 3 0 1 ⁇ is reduced from the 1st pinion gear 3 0 1 C to the planetary carrier 3 0
- the rotation is transmitted only to the 1E side, and the rotational speed of the planetary carrier 301E is increased.
- the Sen-Yu differential 301 functions as a sub-transmission that outputs the rotational torque from the 4-speed automatic transmission 303 at a higher speed. Therefore, the center differential 301 as the auxiliary transmission realizes an overdrive fifth speed higher than the fourth speed, which is the highest shift speed of the four-speed automatic transmission 303. I'm wearing
- the auxiliary transmission for high-to-mouth switching and the gear device for the center differential are separately provided, so that the transfer is large and heavy. Will be bigger.
- the sub-transmission and the center differential are integrally configured using a three-element two-degree-of-freedom planetary gear mechanism, thereby realizing a smaller and lighter device.
- the brake 314 in normal four-wheel drive running with center differential operation that allows front and rear differentials, the brake 314 is in the free (disengaged) state, that is, the sub-transmission is in the low-speed state.
- the brake 314 is engaged, that is, when the auxiliary transmission is in the high-speed state, the state is limited to the front-wheel drive or the directly connected four-wheel drive state.
- four-wheel drive vehicles such as off-road vehicles can realize direct four-wheel drive when the auxiliary transmission is set to a low speed state and when the auxiliary transmission is set to a high speed state. Is required to be able to realize four-wheel drive with a center differential operation, and the conventional example shown in FIG. 20 cannot cope with this.
- the present invention has been made in view of such a problem, and by integrating the function of the sub-transmission and the function of the center differential, the size of the sub-transmission is reduced while promoting the miniaturization and weight reduction of the transfer portion.
- the present invention has been made in view of the above-described problems, and has a first output member that outputs a driving force to one of a front wheel-side rotating member and a rear wheel-side rotating member; a front wheel-side rotating member; A second output member that outputs a driving force to the other of the wheel-side rotating members, and transfers the driving force transmitted from the input member to the first output member and the second output member.
- It has a compound planetary gear mechanism having four rotatable elements that can be driving force transmitting elements or reaction force elements.
- One of each of the above four elements, the input member, the first output member, and the The first output member and the second output member are configured to be connectable to each of the four members of the two output members and the fixed member.
- the driving force transmitted from the input member is distributed to the first output member and the second output member via each component of the compound planetary gear mechanism, and the front wheel side rotation member and the rear wheel side rotation Transmitted to the member.
- the first output member and the first output member are connected to each other according to the connection state of the components of the compound planetary gear mechanism and the members of the input member, the first output member, the second output member, and the fixed member. The state of driving force distribution to the second output member is adjusted.
- the function of the sub-transmission and the function of the center differential can be integrated through the planetary gear mechanism, which makes it possible to promote the miniaturization and weight reduction of the transfer section, and to switch between high-speed and low-speed, and to drive two-wheel and four-wheel drives.
- the four-wheel drive that can easily switch between the two-wheel drive can realize direct-coupled four-wheel drive when the sub-transmission is in the low-speed state, and can realize center-definition four-wheel drive when the sub-transmission is in the high-speed state. This has the effect of satisfying the requirements for cars.
- the first specific configuration of the compound planetary gear mechanism described above is a ring gear.
- a sun gear and a carrier that rotatably supports the first pinion gear and the second pinion gear can be provided.
- the above four elements correspond to the ring gear, the first sun gear, the second sun gear, and the carrier.
- between the ring gear and the input member, between the first sun gear and the first output member, between the second sun gear and the fixed member, and between the carrier and the second output member. are desirably configured to be connectable.
- the first output member includes a front drive sprocket disposed coaxially with the compound planetary gear mechanism, a front propeller shaft that transmits driving force to the front wheels, and a front propeller shaft.
- a front-wheel-side output member including a front drive sprocket provided on the shaft, and a front drive chain connecting the front drive sprocket and the front drive sprocket so as to transmit power.
- the above-described front drive sprocket, the front drive sprocket, and the front drive tune can also be arranged near the rear of the vehicle with the composite planetary gear mechanism and the engagement member.
- the shaft length of the front propeller shaft can be extended, so that, for example, the bend angle at the connection between the front propeller shaft and the bevel gear mechanism of the front differential connected thereto is reduced.
- the rotational vibration of the front propeller shaft and the bevel gear mechanism can be reduced, and the vibration noise of the vehicle can be reduced.
- the above engagement member is thus c can be configured by a wet multi-plate clutch, the use of the wet multiple disk clutch, can be adjusted easily engage the clutch Ri by the example, a hydraulic or the like, the clutch Switching control can be easily realized, for example, switching between high-speed and low-speed and switching between two-wheel drive and four-wheel drive can be performed according to the running state of the vehicle without depending on a driver's command.
- the sections may be configured to be connectable.
- an engagement member is interposed between the second sun gear and the first output member, and between the first sun gear and the fixed member.
- the engaging member in this case can also be constituted by a wet multi-plate clutch.
- the second specific configuration of the compound planetary gear mechanism includes a first ring gear, a first sun gear, a first pinion gear that meshes with the first ring gear and the first sun gear, and a rotation of the first pinion gear.
- a first planetary gear mechanism composed of three elements, a first carrier, which is freely supported; a second ring gear; a second sun gear; a second pinion gear that meshes with the second ring gear and the second sun gear; It consists of three elements, a second carrier that rotatably supports the second pinion gear, and any two of the three elements are respectively connected to any two of the three elements of the first planetary gear mechanism. And the completed second planetary gear mechanism.
- the two elements connected to each other, the remaining one of the three elements of the first planetary gear mechanism, and the remaining one of the three elements of the second planetary gear mechanism,
- the first output member is configured to be connectable to each one of the four members of the input member, the first output member, the second output member, and the fixed member.
- the second output member are connectable.
- the second ring gear and the first carrier and the input member are connected to each other, between the first sun gear and the first output member, between the second sun gear and the fixed member, and It is preferable that the first ring gear and the second carrier and the second output member are configured to be connectable to each other.
- an engagement member is interposed between the first sun gear and the first output member, and between the first ring gear and the second carrier and the fixing member.
- the engaging member can also be constituted by a wet multi-plate clutch.
- C between the first ring gear and the second sun gear, and between the first sun gear and the second carrier, respectively. You may comprise so that it may be connected.
- first sun gear and the second carrier are connected to the input member, and the first ring gear and the second sun gear are connected to the first output member, and the first carrier and the fixed member are connected to each other. Between the second ring gear and the second output member. Noh.
- the engaging member in this case can also be constituted by a wet multi-plate clutch.
- C Further, the connection between the first carrier and the second carrier and the connection between the first ring gear and the second ring gear are respectively performed. May be.
- first carrier and the second carrier are connected between the input member and the second carrier, and the input member is connected between the second sun gear and the first output member, and between the first sun gear and the fixed member. It is desirable that the first ring gear and the second ring gear and the second output member can be connected to each other.
- an engagement member is interposed between the first sun gear and the first output member and between the second sun gear and the fixing member.
- the engagement member can also be configured by a wet multi-plate clutch of the case may be configured to interposed the engagement member between the first output member and the second output member.
- the first output member may be configured to output the driving force to the front wheel side rotation member, said first output member May be configured to output a driving force to the rear wheel side rotating member.
- FIG. 1 is a schematic configuration diagram showing a transfer structure according to a first embodiment of the present invention.
- FIG. 2 shows components and circuits of the transfer structure according to the first embodiment of the present invention.
- FIG. 5 is a velocity diagram schematically showing a rotation restricting unit and an engagement unit.
- FIG. 3 is a schematic configuration diagram showing a drive system of a vehicle having a transfer structure according to the first embodiment of the present invention.
- FIG. 4 is a schematic diagram showing the flow of the driving force in the high-speed two-wheel drive mode using the transfer structure of the first embodiment of the present invention.
- FIG. 5 is a schematic diagram showing the flow of the driving force in the high-speed four-wheel drive mode using the transfer structure of the first embodiment of the present invention.
- FIG. 6 is a schematic diagram showing the flow of the driving force in the low-speed four-wheel drive mode using the transfer structure of the first embodiment of the present invention.
- FIGS. 7 (A) to 7 (C) are speed diagrams schematically showing the concept of the transfer structure studied in the process of devising the first embodiment of the present invention.
- FIGS. 8 (A) to 8 (C) are velocity diagrams illustrating the advantages of the transfer structure of the first embodiment of the present invention.
- FIG. 9 is a schematic configuration diagram showing a transfer structure according to a second embodiment of the present invention.
- FIG. 10 is a velocity diagram schematically showing components of a transfer structure according to a second embodiment of the present invention, rotation restricting means, and engaging means.
- FIG. 11 is a schematic diagram showing a transfer structure according to a third embodiment of the present invention.
- FIG. 12 is a velocity diagram schematically showing components of a transfer structure according to a third embodiment of the present invention, a rotation restricting means, and an engaging means.
- FIG. 13 is a schematic configuration diagram showing a transfer structure according to a fourth embodiment of the present invention.
- FIG. 14 is a velocity diagram schematically showing components of a transfer structure according to a fourth embodiment of the present invention, a rotation restricting means, and an engaging means.
- FIG. 15 is a schematic view showing a transfer structure according to a fifth embodiment of the present invention.
- FIG. 16 is a velocity diagram schematically showing components of the transfer structure, rotation restricting means, and engaging means of the fifth embodiment of the present invention.
- FIG. 17 is a schematic diagram showing a transfer structure according to a sixth embodiment of the present invention.
- FIG. 18 is a schematic configuration diagram showing a conventional transfer structure.
- C FIG. 19 is a schematic configuration diagram of a drive system showing another conventional transfer structure.
- FIG. 20 is a schematic configuration diagram showing still another conventional transfer structure. BEST MODE FOR CARRYING OUT THE INVENTION
- the transfer 1 receives the output torque (driving force) from the engine 2 via the transmission 3.
- Member 4 a front propeller shaft 5 as a front wheel side output member for transmitting the input driving power to the front wheel side, and a propeller shaft as a rear wheel side output member for transmitting the input driving force to the rear wheel side.
- It has a function as an auxiliary transmission, which is interposed between the transmission 6 and the transmission 6 to further shift the driving force from the transmission 3, and a function as a center differential that allows a differential between the front and rear wheels.
- the input member 4 is a name mainly considering the present transfer, and the output shaft itself of the transmission 3 may be the input member 4.
- the front differential 8 is provided with a differential limiting mechanism 11.
- the differential limiting mechanism 11 is capable of adjusting a differential limiting state, for example, a hydraulic multi-plate clutch, and is capable of adjusting the transmission torque capacity while adjusting the differential limiting.
- the driving force output to the propeller shaft 6 is transmitted to the Lyadeff 13 via the bevel gear mechanism 12 and is transmitted to the left and right rear wheels 14L and 14R. 5L, 15R.
- the differential 13 is provided with a differential limiting mechanism 16 and a differential lock mechanism 17.
- the differential limiting mechanism 16 is also capable of adjusting a differential limiting state, for example, a hydraulic multi-plate clutch, so that the transmission torque capacity can be adjusted while adjusting the differential limiting.
- the differential lock mechanism 17 can completely inhibit the left and right differential.
- the transfer structure will be described in detail.
- a Ravigneaux type planetary gear mechanism 18 is provided at the end of the input member 4, a Ravigneaux type planetary gear mechanism 18 is provided.
- the planetary gear mechanism 18 includes a ring gear 19, a first pinion gear 20 that meshes with the ring gear 19, and a first pinion gear 20 that is disposed closer to the axis than the first pinion gear 20.
- a second pinion gear 21 that meshes with the first pinion gear 21; a first sun gear 22 that is disposed inside the second pinion gear 21 and meshes with the second pinion gear 21;
- Carriers (Braneta Carriers) 24 Carriers (Braneta Carriers) 24.
- the ring gear 19 is connected so as to rotate integrally with the input member 4, and the first sun gear 22 is connected so as to rotate integrally with the hollow shaft 25 communicating with the front propeller shaft (front wheel side output member) 5.
- Connected to the carrier 2 4 Is connected so as to be able to rotate integrally with a shaft 26 connected to a propeller shaft (rear wheel side output member) 6.
- the revolution speed and the revolution speed of the pinion gears 20 and 21 are, for example, when the revolution speed decreases, the revolution speed decreases.
- the sun gear 2 2 increases in speed and the carrier 24 decreases, or if the rotation speed decreases, the revolving speed increases and the 1st sun gear 22 decreases in speed and the carrier 24 increases speed. However, they can freely change relative to each other, allowing the front and rear wheels to be differential.
- a brake (hereinafter referred to as a clutch) is provided as rotation restricting means for selectively restricting the rotation of the second sun gear 23. 28) are interposed.
- the brake 28 can be engaged and disengaged arbitrarily.
- the second sun gear 23 stops rotating, so the pinion gears 20 and 21 rotate at their own rotational speeds. And the revolving speed is reduced, so that the output rotation to the rear wheel side output member 6 is reduced.
- a clutch 29 as an engagement means, a front drive gear (or a front drive sprocket) 30 and a transfer chain (or a front drive chain) are provided between the hollow shaft 25 and the front propeller shaft 5.
- a gear (front drive valve) 32 provided integrally with the front propeller shaft 5.
- the driving force transmitted to the hollow shaft 25 is provided by a clutch. From 29, it is sent to the gear 32 via the front drive gear 30 and the transfer chain 31 and transmitted to the front-probe shaft 5.
- the clutch 29 is an engagement means capable of selectively interrupting the transmission of driving force from the hollow shaft 25 to the front propeller shaft 5, and the clutch 29 can be engaged and disengaged arbitrarily.
- the clutch 29 When the clutch 29 is engaged, the driving force is transmitted to the front propeller shaft 5, but when the clutch 29 is not engaged, the driving force is transmitted to the front propeller shaft 5. The transmission of the driving force is not performed.
- a clutch 33 is provided as an engagement means that can link the rotational state between the front propeller shaft 5) as a member and the rear wheel side (that is, the propeller shaft 6 as a rear wheel output member).
- the clutch 33 can be engaged and disengaged arbitrarily. When the clutch 33 is engaged, the rotational states of the front propeller shaft 5 and the propeller shaft 6 are linked to each other. The differential is restricted, and if the clutch 33 is not engaged, the front propeller shaft 5 and the propeller shaft 6 can freely differentially operate without linking the rotational state.
- a clutch 34 is interposed between the hollow shaft 25 on the first sun gear 22 side and the second sun gear 23.
- the clutch 34 can also be engaged and disengaged arbitrarily. By engaging the clutch 34, the two sun gears 22 and 23 can rotate. And You. When the clutch 34 is engaged, the first pinion gear 20 and the second pinion gear 21 no longer rotate, and the rotation of the ring gear 19 is transmitted to the shafts 25 and 26 as it is. ing.
- the clutch 33 is a variable transmission capacity clutch, for example, a hydraulic multi-plate clutch.
- lock mode that transmits torque without causing it to occur
- free mode that does not transmit torque, as well as between members that rotate relative to each other
- the other clutch systems 28, 29, and 34 do not consider the slip transmission mode, and are set to either the lock mode or the free mode.
- a dog clutch may be used for the brake 28. Further, the case where these clutches are locked is called on, and the case of freeing them is called off.
- FIG. 2 shows a velocity diagram for each element of such a transfer structure, and here, the clutch 34 is omitted.
- A denotes a ring gear 19
- S denotes a first sun gear 22
- S2 denotes a second sun gear 23
- C denotes a carrier 24, respectively.
- ⁇ indicates the clutch 29, ⁇ and 2 indicate the brake 28, and Cr 3 indicates the clutch 33
- T i is the input torque
- T f is the output torque to the front wheel side
- Tr indicates the output torque to the rear wheel side.
- FIG. 2 shows a case where the clutch 29 and the clutch 33 are on and the brake 28 is off.
- the transfer structure of the present embodiment is configured such that the clutch 29, the clutch 33, and the brake 28 are engaged and disengaged, respectively.
- various drive modes can be set, for example, as shown in TABLE 1 below.
- Mode No. 1 in TAB L E.1 corresponds to FIG. 4.
- High speed two-wheel drive mode in which the sub-transmission is set to high-speed state and drive state is set to two-wheel drive (2WD) with only rear wheels It is.
- members to which the driving force is transmitted are indicated by solid lines, while members to which the driving force is not transmitted are indicated by chain lines.
- Mode NO.2 in TAB LE E.1 corresponds to FIG. 5 and the auxiliary transmission is set to high speed, and the driving state is set to four-wheel drive (4WD), which transmits driving force to both front and rear wheels High-speed four-wheel drive mode.
- This drive To achieve mode as shown in TABL E. 1 and FI G. 5, the brake (C r2) 2 8 was set to turn off the auxiliary transmission is set to a high speed state, the planetary gear mechanism 1 8 works as the original double pinion planetary gear differential mechanism.
- the clutch (C rl ) 29 is set to the ON state so that the driving force is transmitted to the front wheels.
- the clutch ( Cr3 ) 33 is set to the slip state or the on state.
- the clutch ( Cr4 ) 34 is set to off.
- the driving force is transmitted along the route indicated by the arrow in FIG. 5 and the front wheels and the rear wheels are driven.
- the front-rear driving force distribution ratio (T f ZT r) at this time is as follows: Za is the number of teeth of the ring gear 19, Zs is the number of teeth of the first sun gear 22 and Zs 2 is the number of teeth of the second sun gear 23. , As follows:
- Mode No. 3 in TAB L E.1 corresponds to FIG. 6 and the auxiliary transmission is set to low speed, and the driving state is set to four-wheel drive (4WD) that transmits driving force to both front and rear wheels Low-speed four-wheel drive mode.
- 4WD four-wheel drive
- the clutch (and C r J set to 2 9 off, clutch (C r 3) 3 3 By set Bok turn on, and fully restricts the differential between the front and rear wheels - Set to front-rear direct connection four-wheel drive (direct connection 4WD).
- the clutch ( Cr4 ) 34 is set to off.
- FIG-. The path as indicated by arrows in 6, the driving force is transmitted, c that the driving force rotates and the front and rear wheels on which is shifted to the low speed driven reduction ratio P at this time Is as follows.
- the present transfer structure it is possible to realize the direct-coupled four-wheel drive when the sub-transmission is in the low-speed state, while having the function of the sub-transmission and the function of the center differential in an integrated mechanism.
- the auxiliary transmission is in a high-speed state, four-wheel drive with center differential operation can be realized.
- this transfer structure is composed of the ring gear (A) 19, the first sun gear (S! 22, the second sun gear (S 2 ) 23, and the carrier (C) 23 Out of the four elements of 4, one element is connected to the input member, one element is connected to the front-wheel output member, and one element is connected to the rear-wheel output member.
- This is advantageous for miniaturization and weight reduction as compared with the transfer structure. This is described below.
- FI G. 7 is a velocity diagram for explaining the configuration of a three-element transfer structure.
- FI G. 7 (A), (B), and (C) three Is shown.
- the three elements are referred to as a first element, a second element, and a third element in order from the left end.
- FI G. 7 is used to realize a high-speed four-wheel drive mode with center differential operation that sets the sub-shift function at high speed and activates the center differential to allow differential between front and rear wheels.
- the input and output are configured as shown in (A)
- the sub-transmission function is set at low speed
- the center differential is locked
- the front and rear wheels are directly connected
- FIG. The input and output may be configured as shown in ()).
- one of the three elements (the second element) is connected to the input member and driven as shown in Fig. 7 (A).
- the force Ti input one of the remaining two elements (the first element) is connected to the front wheel side output member to output the front wheel side driving force Tf, and the other (the third element) ) May be combined with a rear-wheel-side output member to output rear-wheel-side driving force Tr.
- one of the three elements (the first element) is connected to the input member and the driving force T is set, as shown in Fig. 7 (B).
- the driving force T is set, as shown in Fig. 7 (B).
- one of the remaining two elements (third element) is connected to a non-rotating member to regulate rotation, and the other (second element) is connected to the front wheel side output member and
- the front wheel side driving force Tf and the rear wheel side driving force Tr are output by being coupled to the rear wheel side output member.
- FI G. 8 is a velocity diagram for explaining the configuration of a four-element transfer structure.
- (A), (B), and (C) Shows four elements.
- the four elements are referred to as a first element, a second element, a third element, and a fourth element in order from the left end.
- FI G. 8 is required to realize a high-speed four-wheel drive mode with center differential operation that sets the sub-shift function at high speed and activates the center differential to allow differential between front and rear wheels.
- the FI G. 8 (B It is conceivable to configure the input and output as shown in)
- one of the four elements (the second element) is connected to the input member and driven as shown in Fig. 8 (A).
- the third element or the first element is connected to the front wheel output member to output the front wheel driving force Tf
- One (the first element or the third element) may be connected to the rear-wheel-side output member so as to output the rear-wheel driving force Tr.
- one of the four elements (the second element) is connected to the input member and the driving force T is set, as shown in Fig. 8 (B). i is input, one of the remaining three elements (the fourth element) is connected to the non-rotating member to restrict rotation, and one of the remaining two elements (the fourth element) 3 elements), front wheel side output member and rear wheel side output It is conceivable that the front wheel side driving force Tf and the rear wheel side driving force Tr are output by being connected to members.
- the four-element transfer structure can realize the required drive mode with a smaller number of clutches than the three-element transfer structure, and is advantageous in reducing the size and weight.
- this transfer structure is different from the first embodiment in that a second pinion gear 21 and a first sun gear 22 are provided.
- the coupling element of the input member 4 and the coupling element of the propeller shaft (rear wheel side output member) 6 are exchanged by replacing the arrangement with the second sun gear 23.
- a Ravigneaux type planetary gear mechanism 18 is provided at an end of the input member 4.
- the planetary gear mechanism 18 includes a ring gear 19, a first pinion gear 20 that meshes with the ring gear 19, and a first pinion gear 20 that is disposed closer to the axis than the first pinion gear 20.
- a second sun gear (23) arranged in series with the sun gear (22) and meshing with the first pinion gear (20), and rotatably supports the first pinion gear (20) and the second pinion gear (21).
- Carrier (planetary carrier) 24 is provided at an end of the input member 4.
- the carrier 24 is connected so as to be able to rotate integrally with the input member 4,
- the first sun gear 22 is connected so that it can rotate integrally with the hollow shaft 25 leading to the front propeller shaft (front wheel output member) 5, and the ring gear 19 is propeller shaft (rear wheel side output member) 6 It is connected so as to be able to rotate integrally with the large-diameter hollow shaft 26 A connected to the shaft.
- clutches 29, 33, 34 and a brake 28 are provided.
- a brake (hereinafter referred to as a braking means) is provided as a rotation regulating means capable of selectively regulating the rotation of the second sun gear 23. , Clutch).
- a clutch 29 as an engagement means, a front drive gear 30, a transfer chain 31, and a front propeller shaft 5 are integrally formed between the hollow shaft 25 and the front propeller shaft 5.
- the provided gears 32 are provided.
- a clutch 33 that can arbitrarily engage and disengage is provided as engagement means that can link the rotation states of the clutches. As a result, when the clutch 33 is engaged, the rotational states of the front propeller shaft 5 and the propeller shaft 6 are linked to regulate the mutual differential. If the clutch 33 is not engaged, the front propeller shaft is not engaged.
- the shaft 5 and the propeller shaft 6 can be freely differentiated without linking the rotation states.
- a clutch 34 may be interposed between the first sun gear 22 and the second sun gear 23 as in the first embodiment. In this case, when the clutch 34 is engaged, the first pinion gear 20 and the second pinion gear 21 do not rotate, and the rotation of the sun gear 22 is transmitted to the shafts 25 and 26 as it is.
- the clutch 33 is a variable transmission capacity type clutch
- the other clutch systems 28, 29, and 34 are sleeves.
- the flip transmission mode is not taken into consideration, and is set to either the lock mode or the free mode.
- a dog clutch may be used for the brake 28.
- FIG. 10 shows a velocity diagram for each element of such a transfer structure.
- A denotes a ring gear 19, and S, denotes a first sun gear 22.
- S 2 indicates the second sun gear 23, and C indicates the carrier 24.
- the force torque, Tf, is the output torque to the front wheels
- Tr is the output torque to the rear wheels.
- FIG. 10 shows a case where the clutch 29 and the clutch 33 are on and the brake 28 is off.
- the transfer structure of the present embodiment similarly to the first embodiment, while the clutch 29, the clutch 33, and the brake 28 are engaged and disengaged, respectively.
- various drive modes can be set as shown in TABLE 1.1, which is required for off-road vehicles and other four-wheel drive vehicles while promoting the miniaturization and weight reduction of the transfer section. Each driving mode can be satisfied.
- the configuration of the present embodiment has an advantage that the distribution ratio of the center differential and the auxiliary speed ratio can be easily increased because of the gear structure.
- this transfer structure is configured by arranging two single pinion type planetary gear mechanisms in series. 8 A and the second planetary gear mechanism 38 B.
- the first planetary gear mechanism 38 A includes a ring gear 39 A, a pinion gear 40 A, a sun gear 42 A and a carrier 44 A
- the second planetary gear mechanism 38 B includes a ring gear 39 B and a pinion gear 4. 0 B, sun gear 4 2 B and carrier 4 4 B.
- the ring gear 39 A of the first planetary gear mechanism 38 A and the carrier 44 BA of the second planetary gear mechanism 38 B are connected so as to be able to rotate integrally with the input member 4, and the second planetary gear mechanism 3
- the sun gear 42B of 8B is connected so as to be able to rotate integrally with the hollow shaft 45 communicating with the front-probe shaft (front wheel side output member) 5, and the carrier 44A of the first planetary gear mechanism 38A is formed.
- the propeller shaft (rear wheel side output member) 6 is connected so as to be able to rotate integrally with a shaft 46 connected to the propeller shaft.
- the rotation of the input member 4 is transmitted from the ring gear 39 A and the pinion gear 40 A to the carrier 44 A, and is output to the rear wheel side, while being transmitted from the carrier 44 B and the pinion gear 40 B. It is transmitted to the sun gear 42B and output to the front wheels.
- a brake (hereinafter referred to as a clutch) is provided as a rotation restricting means that can selectively restrict the rotation of the sun gear 42A. 28) are interposed.
- a clutch 29 as an engagement means, a front drive gear 30, a translatory clutch 31, and a front propeller shaft are provided between the hollow shaft 45 and the front propeller shaft 5.
- the gear 32 is provided integrally with the gear 5.
- a clutch 33 that can arbitrarily engage and disengage is provided as engagement means that can link the states.
- the rotational states of the front propeller shaft 5 and the propeller shaft 6 are linked to regulate the mutual differential. If the clutch 33 is not engaged, the front propeller shaft is disengaged.
- the drive 5 and the propeller shaft 6 can be freely differentiated without linking the rotational state.
- a clutch 34 may be interposed between the carrier 44A and the sun gear 42A, for example, as in the first embodiment. in this case, When the clutch 34 is engaged, the first planetary gear mechanism 38 A rotates as a whole, and the rotation of the ring gear 19 is transmitted to the shafts 45, 46 as it is.
- the clutch 33 is a variable transmission capacity clutch.
- Nos. 29 and 34 do not take into account the slip transmission mode, and are set to either the lock mode or the free mode.
- a dog clutch may be used for the brake 28.
- FIG. 12 shows a velocity diagram for each element of such a transfer structure, where is a ring gear 39 A, A 2 is a ring gear 39 B, and S and are sun gears. 4 2 A, S 2 indicates sun gear 4 2 B, C, indicates carrier 44 A, C 2 indicates carrier 44 A, respectively, and C rl indicates clutch 29 , C r 2 indicates Brake 28 , Cr 3 clutch
- T i represents input torque
- T f represents output torque to the front wheels
- Tr represents output torque to the rear wheels.
- FIG. 12 shows a case where the clutch 29 and the clutch 33 are on and the brake 28 is off.
- the first planetary gear mechanism 48A is composed of a ring gear 49A, a pinion gear 50A, a sun gear 52A and a carrier 54A
- the second planetary gear mechanism 48B is a ring gear 49B.
- the carrier 54A of the first planetary gear mechanism 48A is connected so as to be able to rotate integrally with the input member 4, and the sun gear 52A of the first planetary gear mechanism 48A and the second planetary gear mechanism 4A.
- 8 B ring gear 49 B is connected so that it can rotate integrally with hollow shaft 55 communicating with front propeller shaft (front wheel output member) 5, and the first planetary gear mechanism 48 A ring gear 49 A Are connected so as to be able to rotate integrally with a shaft 56 connected to a propeller shaft (rear wheel side output member) 6.
- a brake (hereinafter also referred to as a clutch) is provided as rotation restricting means for selectively restricting the rotation of the carrier 54B. ) 2 8 are interposed.
- a front drive gear 30 is connected to the hollow shaft 55, and the front propeller is connected to the front propeller via a transfer chain 31 and a gear 32 integrated with the front propeller shaft 5. Shaft 5 is connected. As a result, the driving force transmitted to the hollow shaft 55 is sent to the gear 32 via the front drive gear 30 and the transfer chain 31. It is transmitted to the front propeller shaft 5.
- a clutch 59 as an engagement means is provided in the middle of the shaft 56 communicating with the rear wheel side.
- the clutch 59 is engaged, the driving force transmitted to the shaft 56 is transmitted to the propeller shaft 6, but when the clutch 59 is not engaged, the driving force to the propeller shaft 6 is not transmitted. Communication is not to take place.
- the front wheel side and the rear wheel side are provided between the support portion of the front drive gear 30 which is the transmission path of the driving force to the front wheels and the shaft 56 which is the transmission path of the driving force to the rear wheels.
- a clutch 33 that can arbitrarily engage and disengage is provided as engagement means that can link the rotation state with the wheel side.
- the rotational states of the front propeller shaft 5 and the propeller shaft 6 are linked to regulate the mutual differential. If the clutch 33 is not engaged, the front propeller shaft is not engaged.
- the shaft 5 and the propeller shaft 6 are free to differentially rotate without coordinating the rotation state.
- a clutch 34 may be provided between the carrier 54A and the sun gear 52A, as in the first embodiment. In this case, when the clutch 34 is engaged, the first planetary gear mechanism 38 A rotates as a whole, and the rotation of the ring gear 19 is transmitted to the shafts 55, 56 as it is. You.
- 33 is a variable transmission capacity type clutch, and the other clutch systems 28, 59, and 34 do not consider the slip transmission mode. Is set to.
- a dog clutch may be used for the brake 28.
- FIG-. 1 4 is shows a speed diagram related to the elements of such a transfer construction
- FIG-. In 1 eight 1 Li ring gear 4 9 A, A is ring gear 49 B, S, is sun gear 52 ⁇ , S 2 is sun gear 52 B, C, is carrier 54 A, C 2 is carrier 54 A
- the C rl clutch 5 9, C r2 is the brake 2 8
- C r3 denotes a clutch 3 3 respectively
- T i is the input Tonoreku
- T f is the output torque to the front wheel side
- FIG. 14 showing the output torque to the wheel side shows a case where the clutch 59 and the clutch 33 are on and the brake 28 is off.
- the clutch 59, the clutch 33, and the brake 28 are engaged and disengaged, respectively.
- various drive modes can be set, and while promoting the miniaturization and weight reduction of the transfer part, it can be used for off-road vehicles and other four-wheel drive vehicles.
- Each drive mode required can be satisfied.
- the two-wheel drive mode is a front-wheel drive mode realized by turning off both the clutch 59 and the clutch 33 and cutting off the transmission of the driving force to the rear wheels.
- this transfer structure has a single pinion type first planetary gear mechanism 48 A, similar to the fourth embodiment. And two double pinion type second planetary gear mechanisms 48 B in series.
- the first planetary gear mechanism 48A is composed of a ring gear 49A, a pinion gear 50A, a sun gear 52A and a carrier 54A
- the second planetary gear mechanism 48B is composed of a ring gear 49B. It is composed of an outer pinion gear 50B, an inner pinion gear 51B, a sun gear 52B and a carrier 54B.
- the carrier 54A of the first planetary gear mechanism 48A and the carrier 54B of the second planetary gear mechanism 48B are connected so that they can rotate together with the input member 4.
- the sun gear 52B of the second planetary gear mechanism 48B is connected so as to be able to rotate integrally with the hollow shaft 55A communicating with the front propeller shaft (front wheel side output member) 5, and the first planetary gear.
- the ring gear 49 A of the mechanism 48 A and the ring gear 49 B of the second planetary gear mechanism 48 B rotate integrally with the shaft 56 A connected to the propeller shaft (rear wheel side output member) 6.
- a brake (hereinafter, referred to as a clutch) is provided as rotation restricting means for selectively restricting the rotation of the carrier 54 B. 28) are interposed.
- a clutch 29 as an engagement means, a front drive gear 30, a transfer chain 31, and a front propeller shaft 5 are integrally formed between the hollow shaft 55 A and the front propeller shaft 5.
- the provided gear 32 is provided.
- a clutch 59 as an engagement means is provided in the middle of the shaft 56 communicating with the rear wheel side.
- the clutch 59 is engaged, the driving force transmitted to the shaft 56 is transmitted to the propeller shaft 6, but when the clutch 59 is not engaged, the driving force to the propeller shaft 6 is not transmitted. Communication is not to take place.
- the front wheel side and the rear wheel side are provided between the support portion of the front drive gear 30 which is the transmission path of the driving force to the front wheels and the shaft 56 which is the transmission path of the driving force to the rear wheels.
- a clutch 33 that can arbitrarily engage and disengage is provided as engagement means that can link the rotation state with the wheel side.
- a clutch 34 may be provided between the carrier 54A and the sun gear 52A, as in the first embodiment. In this case, when the clutch 34 is engaged, the first planetary gear mechanism 38 A rotates as a whole, and the rotation of the ring gear 19 is transmitted to the shafts 55 A and 56 A as it is. Is done.
- the clutch 33 is a variable transmission capacity clutch
- the other clutch systems 28, 29, and 34 are sleeves.
- the flip transmission mode is not taken into account, and is set to either the lock mode or the free mode.
- a dog clutch may be used for the brake 28.
- FIG. 16 shows a velocity diagram for each element of such a transfer structure.
- 8 indicates a ring gear 49 A
- a 2 indicates a ring gear 4.
- the 9 B, S is a sun gear 5 2 a
- S 2 is the sub Ngiya 5 2 B
- C is a carrier 5 4 a
- C 2 depicts, respectively Re its the carrier 5 4 a.
- C rl is the clutch 2 9
- the output torque of the C r 2 is the brake 2 8
- C r 3 shows the clutch 3 3 respectively
- T i is the input torque
- T f is the front side
- T r Indicates the output torque to the rear wheels (in this FIG. 16, the clutch 59 and the clutch 33 are on and the —This shows the case where key 28 is off.
- this transfer structure includes a Ravigneaux type planetary gear mechanism 18. It has the same structure.
- the same reference numerals as in the first embodiment denote the same or corresponding members, and here, the differences from the first embodiment will be described.
- the feature of this embodiment is that the front drive gear 30 and the transfer chain (or front drive chain) 31 are arranged behind the planetary gear mechanism 18, the clutch 29, and the clutch 33. It is a point.
- the shaft length of the front propeller shaft 5 can be extended by an amount corresponding to the movement of the front drive gear 30 and the transfer tune 31 to the rear of the vehicle as compared with the first embodiment.
- This makes it possible to reduce the angle at which the front propeller shaft 5 and the front differential 8 are connected to the bevel gear mechanism 7 in comparison with the first embodiment, so that the front propeller shaft 5 and the front The rotational vibration of the bell gear mechanism 7 can be reduced, and the vibration noise of the vehicle can be reduced.
- the function of the sub-transmission and the function of the center differential are integrated, and the transfer portion is reduced in size and weight.
- Quantification can be pushed forward, and the direct-coupled four-wheel drive can be realized when the auxiliary transmission is in the low-speed state, and the four-wheel drive with center differential operation can be realized when the auxiliary transmission is in the high-speed state.
- It is suitable for making more efficient use of the vehicle space of a four-wheel drive vehicle and for realizing a lighter vehicle.
- It is also suitable for automatically switching between high-speed and low-speed, and between two-wheel drive and four-wheel drive, and can appropriately drive a four-wheel drive vehicle with simple operations. Therefore, four-wheel drive vehicles that can achieve high running performance through four-wheel drive can be widely spread.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69413672T DE69413672T2 (de) | 1993-12-16 | 1994-12-16 | Aufbau eines verteilergetriebes |
EP95902973A EP0684153B1 (en) | 1993-12-16 | 1994-12-16 | Transfer construction |
KR1019950703397A KR960700912A (ko) | 1993-12-16 | 1994-12-16 | 트랜스퍼구조(Transfer structure) |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP31643693 | 1993-12-16 | ||
JP5/316436 | 1993-12-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995016584A1 true WO1995016584A1 (fr) | 1995-06-22 |
Family
ID=18077069
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1994/002122 WO1995016584A1 (fr) | 1993-12-16 | 1994-12-16 | Systeme de transfert |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0684153B1 (ja) |
KR (1) | KR960700912A (ja) |
CA (1) | CA2156187A1 (ja) |
DE (1) | DE69413672T2 (ja) |
WO (1) | WO1995016584A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001315543A (ja) * | 2000-03-03 | 2001-11-13 | Aisin Ai Co Ltd | 四輪駆動車用トランスファ装置 |
WO2012172638A1 (ja) | 2011-06-14 | 2012-12-20 | トヨタ自動車株式会社 | 4輪駆動車用のトランスファ |
KR101538591B1 (ko) * | 2014-08-29 | 2015-07-21 | 현대위아 주식회사 | 4륜구동 차량의 디스커넥트 장치 |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19524682C2 (de) * | 1995-07-06 | 2002-10-31 | Steyr Daimler Puch Ag | Differentialgetriebe mit einem Gruppengetriebe |
US5700222A (en) * | 1996-06-19 | 1997-12-23 | New Venture Gear, Inc. | Full-time transfer case with integrated planetary gear assembly |
US5947858A (en) * | 1997-12-15 | 1999-09-07 | New Venture Gear, Inc. | Full-time transfer case with integrated planetary gear assembly and synchronized range shift mechanism |
WO1999045295A1 (de) * | 1998-03-06 | 1999-09-10 | Voith Turbo Gmbh & Co. Kg | Hydrodynamisch-mechanisches mehrgangverbundgetriebe |
DE10058203A1 (de) * | 2000-11-23 | 2002-05-29 | Zahnradfabrik Friedrichshafen | Allradverteilergetriebe für ein Kraftfahrzeug |
US7172528B2 (en) * | 2003-03-28 | 2007-02-06 | Borgwarner Inc. | Transfer case with overdrive/underdrive shifting |
CN100338376C (zh) * | 2004-07-09 | 2007-09-19 | 上汽集团奇瑞汽车有限公司 | 无级变速器动力切换传动机构 |
AT509721B1 (de) * | 2010-06-25 | 2011-11-15 | Paul Roman Oberaigner | Verteilergetriebe |
WO2018171894A1 (en) * | 2017-03-24 | 2018-09-27 | Volvo Truck Corporation | A transmission assembly |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04300729A (ja) * | 1991-03-28 | 1992-10-23 | Mitsubishi Motors Corp | 4輪駆動車用駆動力配分装置 |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2331980A1 (de) * | 1972-06-23 | 1974-02-07 | Gkn Transmissions Ltd | Planeten-differentialgetriebe |
US5162025A (en) * | 1991-08-15 | 1992-11-10 | Ford Motor Company | T-drive powertrain assembly |
-
1994
- 1994-12-16 EP EP95902973A patent/EP0684153B1/en not_active Expired - Lifetime
- 1994-12-16 WO PCT/JP1994/002122 patent/WO1995016584A1/ja active IP Right Grant
- 1994-12-16 CA CA002156187A patent/CA2156187A1/en not_active Abandoned
- 1994-12-16 KR KR1019950703397A patent/KR960700912A/ko not_active Application Discontinuation
- 1994-12-16 DE DE69413672T patent/DE69413672T2/de not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04300729A (ja) * | 1991-03-28 | 1992-10-23 | Mitsubishi Motors Corp | 4輪駆動車用駆動力配分装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP0684153A4 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001315543A (ja) * | 2000-03-03 | 2001-11-13 | Aisin Ai Co Ltd | 四輪駆動車用トランスファ装置 |
JP4673490B2 (ja) * | 2000-03-03 | 2011-04-20 | アイシン・エーアイ株式会社 | 四輪駆動車用トランスファ装置 |
WO2012172638A1 (ja) | 2011-06-14 | 2012-12-20 | トヨタ自動車株式会社 | 4輪駆動車用のトランスファ |
JP5569651B2 (ja) * | 2011-06-14 | 2014-08-13 | トヨタ自動車株式会社 | 4輪駆動車用のトランスファ |
US8905888B2 (en) | 2011-06-14 | 2014-12-09 | Toyota Jidosha Kabushiki Kaisha | Transfer mechanism for four-wheel drive vehicle |
KR101538591B1 (ko) * | 2014-08-29 | 2015-07-21 | 현대위아 주식회사 | 4륜구동 차량의 디스커넥트 장치 |
Also Published As
Publication number | Publication date |
---|---|
DE69413672T2 (de) | 1999-02-25 |
EP0684153B1 (en) | 1998-09-30 |
EP0684153A1 (en) | 1995-11-29 |
EP0684153A4 (en) | 1996-05-08 |
CA2156187A1 (en) | 1995-06-22 |
KR960700912A (ko) | 1996-02-24 |
DE69413672D1 (de) | 1998-11-05 |
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