JPH0571615A - Power train construction of vehicle - Google Patents

Abstract

(57) [Abstract] [Purpose] While ensuring the oil tightness of the clutch, the transmission and the power transmission device share an oil circulation path to simplify the oil circulation path. A structure is assumed in which an engine and a transmission are arranged in parallel, a clutch 11 is provided at one end of a crankshaft of the engine, and a power transmission device is provided at a side of the clutch 11 opposite to the engine. And Then, the input shaft 21 of the transmission is connected to the power transmission device through the outside of the clutch 11. An oil passage 87 is formed on the outer circumference of the input shaft 21 so that oil can flow between the case 70 of the transmission and the case 81 of the power transmission device. The oil passage 87
An oil seal 88 seals between the above and the clutch 11 in an oil-tight manner.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle powertrain structure in which an engine and a transmission are mounted in parallel.

[0002]

2. Description of the Related Art Conventionally, in vehicles such as four-wheel drive vehicles and FR (front engine / rear drive) type vehicles, when arranging an engine and a transmission in an engine room at the front of the vehicle body There are various modes depending on whether the device is mounted vertically or horizontally. Among these, particularly when both the engine and the transmission are horizontally arranged, there is a problem that if both of them are arranged in series, the axial length of the entire power train becomes considerably long. Therefore, for example, as disclosed in Japanese Patent Laid-Open No. 1-316561,
A transmission is arranged in parallel behind the engine, and both are connected so that power can be transmitted by a power transmission device such as a gear or chain, and a clutch is arranged between the engine and the power transmission device on the crankshaft of the engine. Those that have been done have been developed and put into practical use.

[0003]

By the way, in such a power train structure, when lubricating the bearings and the like of the transmission and the power transmission device, there is a clutch that must ensure oil tightness between them. Since they are arranged, it is necessary to supply lubricating oil from an oil pump or the like provided on the engine side to the transmission and the power transmission device through separate oil circulation paths. For this reason, there are problems in that many oil circulation routes are complicated and manufacturing costs are high.

The present invention has been made in view of the above points, and an object of the present invention is to share the oil circulation path between the transmission and the power transmission device while ensuring the oil tightness of the clutch. Then, the object is to provide a power train structure for a vehicle, which can simplify the oil circulation route and further reduce the manufacturing cost.

[0005]

In order to achieve the above object, the invention according to claim 1 is a power train structure for a vehicle, in which an engine and a transmission are arranged in parallel,
A clutch is provided at one end of the crankshaft of the engine, and a power transmission device that transmits engine power output through the clutch to the input shaft of the transmission is provided on the side of the clutch opposite to the engine. It is assumed that it is provided. The input shaft of the transmission is connected to the power transmission device through the outside of the clutch, and the oil is provided on the outer periphery of the input shaft between the inside of the transmission case and the inside of the power transmission device. Form a fluid oil passage. Further, the oil passage and the clutch are oil-tightly sealed.

The invention according to claim 2 is dependent on the invention according to claim 1, and the oil passage is provided so as to penetrate through the inside of the clutch case.

A third aspect of the invention is dependent on the first aspect of the invention, wherein the oil passage is concentric with the input shaft from a shaft support member that supports the input shaft of the transmission. And an extension portion extending toward the power transmission device side with a predetermined gap from the outer peripheral surface thereof.

A fourth aspect of the invention is dependent on the third aspect of the invention, wherein the case of the power transmission device is concentric with the input shaft of the transmission from the vicinity of a gear connected to the input shaft of the transmission. Moreover, an extending portion extending toward the transmission is formed with a predetermined gap from the outer peripheral surface of the input shaft, and the extending portion is fitted with the extending portion of the shaft support member. The oil passage and the clutch are sealed.

A fifth aspect of the invention is dependent on the third aspect of the invention, wherein the case of the engine and the transmission is integrally formed, and the case and the shaft support member are separately formed. Is.

A sixth aspect of the invention is dependent on the first aspect of the invention, wherein the clutch case is formed in a substantially bowl shape so as to surround the outer periphery of the clutch body, and the oil passage is provided outside the clutch case. The configuration.

The invention according to claim 7 is dependent on the invention according to claim 6, wherein an oil pump which is operated by the rotation of the output shaft is provided at one end of the output shaft of the transmission, and the transmission and An oil supply passage for supplying the oil discharged from the oil pump into the case of the power transmission device is formed on the output shaft. Further, when the oil in the case of the power transmission device becomes equal to or higher than the reference oil level, the oil is returned to the case of the transmission through the oil passage.

An eighth aspect of the invention is dependent on the first aspect of the invention, wherein the power transmission device is a chain type device in which a chain is wound between two sprockets.

The ninth aspect of the present invention is dependent on the eighth aspect of the invention, and is configured such that the case of the power transmission device is provided with a thrust plate that abuts and supports the respective sprockets in the axial direction.

[0014]

With the above construction, in the invention according to claim 1,
An oil passage is formed on the outer circumference of the input shaft of the transmission that is connected to the power transmission device through the outside of the clutch, and oil can flow between the transmission case and the power transmission device case. Therefore, if either one is supplied with lubricating oil from an oil pump or the like provided on the engine side, both can be lubricated. Moreover, since the oil passage and the clutch are oil-tightly sealed, the oil-tightness of the clutch can be ensured.

Further, in the invention of claim 2, the oil passage is provided so as to penetrate through the inside of the clutch case, and compared with the case where the oil passage is provided outside the clutch case, the shaft of the clutch and the engine and the transmission is provided. The distance becomes shorter.

Further, in the invention according to claim 5, the case of the engine and the transmission is formed as an integral structure, and the case and the shaft supporting member that pivotally supports the input shaft of the transmission are formed separately. Therefore, at the time of assembling the powertrain, the shaft such as the input shaft of the transmission is pivotally supported by the shaft support member to perform the sub-assembly, and thereafter, by assembling the mechanism portion of the transmission into the case, The transmission is easily installed.

According to the seventh aspect of the invention, when the engine power is transmitted to the transmission side, the oil pump operates, and the oil passes through the oil supply passages of the input / output shafts of the transmission to the inside of the case of the power transmission device. And lubricate the lubrication points in the case. Then, when the oil in the case reaches or exceeds the reference oil level, the oil is returned to the case of the transmission through the oil passage on the outer circumference of the input shaft. At the time of this return, oil does not leak from the oil passage to the clutch side due to the seal structure between the oil passage and the clutch.

[0018]

Embodiments of the present invention will be described below with reference to the drawings.

1 to 3 show a power train structure of a four-wheel drive vehicle according to a first embodiment of the present invention, 1 is a vehicle body, and 2 is a vehicle body.
Is an engine room provided in the front part of the vehicle body 1, and the engine room 2 is separated from a vehicle room 4 by a dash panel 3. Inside the engine room 2, a radiator 5 is arranged on the front side thereof, and an engine 6 and a transmission 7 are arranged behind the radiator 5. The engine 6 is a four-cylinder reciprocating engine, and a crankshaft 8 is horizontally arranged in the vehicle width direction. The transmission 7 is horizontally arranged behind the engine 6 and in parallel with the crankshaft 11. It is located in.

Reference numeral 11 denotes a clutch provided at one end of the crankshaft 8 of the engine 6, and 12 denotes the power of the engine 6 (rotational force of the crankshaft 8) output through the clutch 11 of the transmission 7. A power transmission device for transmitting to the input shaft 21, said power transmission device 12
Are arranged on the side of the clutch 11 opposite to the engine 6. The clutch 11 is the crankshaft 8
And a clutch disc 14 arranged to face the support disc 13, and a pressure plate 15 for pressing the clutch disc 14 against the support disc 13. The power transmission device 12 includes a drive gear 16 rotatably connected to a clutch disc 14 of the clutch 11, a driven gear 17 rotatably provided on an input shaft 21 of the transmission 7, and both gears 16. ，
The idle gear 18 is provided between the gears 17 and meshes with them. Then, when the clutch 11 is engaged (that is, the clutch disc 14 becomes the support disc 1).
(When pressed by 3), the power of the engine 6 is transmitted to the input shaft 21 of the transmission 7 via the power transmission device 12, and the input shaft 21 rotates.

The transmission 7 has an input shaft 21 and an output shaft 22 located on the coaxial line, and a counter shaft 23 parallel to these. The input shaft 21 and the counter shaft 23 are drivingly connected via a pair of reduction gears 24, while a gear train 25 for shifting is arranged between the output shaft 22 and the counter shaft 23. .. Thus, the engine power input to the input shaft 21 is transmitted from the input shaft 21 to the counter shaft 23 via the reduction gear 24, and the counter shaft 23 transmits the gear train 2 for shifting.
It is transmitted to the output shaft 22 via any one gear of No. 5 and is appropriately decelerated during this period.

An output gear 26 is mounted on the end of the output shaft 22 so as to rotate integrally therewith, and the power output from the output gear 26 is transmitted to a center differential 31 and is connected to the front wheel side by the center differential 31. It is divided into the rear wheel side. Then, the power on the front wheel side is transmitted to the front differential 41, which is a front wheel-to-wheel differential, and the front differential 4 is transmitted.
After being split left and right by 1, drive axles 42L, 42R respectively
It is transmitted to the left and right front wheels 9 via. On the other hand, the power on the rear wheel side is generated by the power transmission gear device 44 and the propeller shaft 45.
Is transmitted to a rear differential (not shown) which is an inter-wheel differential on the rear wheel side at the rear of the vehicle body.

The center differential 31 and the front differential 41 are arranged in parallel on the drive axles 42L and 42R, which are separate from the output shaft 22 of the transmission 7, and the front differential 4 is provided.
1 is arranged on the drive axles 42L, 42R near the transmission 7 near the center line of the vehicle front-rear direction, and the center differential 31 is arranged on the opposite side of the transmission 7 with the front differential 41 interposed therebetween. Also,
The center differential 31 is of a planetary gear type, and is provided with a ring gear 32 as an input portion having a gear portion that meshes with the output gear 26 on the outer periphery, a ring gear 32 provided concentrically with the ring gear 32, and a rear wheel side output. A sun gear 34 that is rotationally integrally connected to the gear 33, a planetary gear 35 that meshes with both the ring gear 32 and the sun gear 34, and a carrier that supports the planetary gear 35 and that is rotationally integrally connected to the differential case of the front differential 41. And 37. On the other hand, the front differential 41 is of a bevel gear type.

Further, the power transmission gear device 44 constituting the power take-out portion of the propeller shaft 45 is provided with a gear drive shaft 46 extending in the vehicle width direction, and is provided at one end of the gear drive shaft 46, and the output gear 33 is provided.
A gear 47 that meshes with the gear drive shaft 46
And a pair of hypoid gears 4 provided at the front end of a shaft 49 connected to the propeller shaft 45.
8 and 48 are provided.

As shown in FIG. 2, the engine 6 is horizontally arranged with its cylinder axis slightly inclined forward of the vehicle body. The case 70 of the engine 6 is composed of a head cover 71, a cylinder head 72, an upper crankcase 73, a lower crankcase 74 and an oil pan 75 from the upper side, and a mating surface F1 between the upper crankcase 73 and the lower crankcase 74. Is provided substantially orthogonal to the cylinder axis on a plane that passes through the center of the crankshaft 8. The transmission 7 is accommodated in the upper crankcase 73 and the lower crankcase 74 of the engine 6 so as to straddle the input / output shafts 21 and 22 in the upper crankcase 73 and the countershaft 23 in the lower portion. It is pivotally supported by the crankcase 74.

The mating face F2 between the lower crankcase 74 and the oil pan 75 passes through the center of the center differential 31, the front differential 41 and the drive axles 42L, 42R of the front wheels, and sandwiches the drive axles 42L, 42R. It is designed to be supported by. Both of the differentials 31 and 41 are accommodated so as to straddle the lower crankcase 74 and the oil pan 75. The power transmission gear device 44 is housed in an oil pan 75. As described above, all the cases of the engine 6, the transmission 7, the center differential 31, the front differential 41, and the power transmission gear device 44, which constitute the power train 10, are integrally configured.

Further, as shown in FIGS. 3 and 4, the clutch 11 is covered with a clutch case 81 attached to the case 70 of the engine 6, and on the side of the clutch case 81, A gear case 82 is attached to cover the gears 16 to 18 of the power transmission device 12. Each gear 16 to 1 of the power transmission device 12
8 is the clutch case 81 and the gear case 8 respectively.
The clutch case 81 is rotatably supported by a pair of bearings 83, 83 respectively provided at 2 and 2.
The gear case 82 constitutes a case of the power transmission device 12. The engine case 70 and the clutch case 8
1, a shaft support member 84 is fixedly provided to the engine case 70 in correspondence with the transmission 7.
The input shaft 21 and the counter shaft 23 of the transmission 7 are rotatably supported by bearings 85 and 86, respectively. The input shaft 21 is connected to the clutch case 8 on the outer peripheral side of a mechanism portion such as the clutch disk 14 of the clutch 11.
1 is provided so as to penetrate through 1 to the power transmission device 12 side,
The driven gear 17 of the power transmission device 12 is rotationally integrally mounted to the extending portion by spline coupling. Also,
Power is transmitted to the shaft support member 84 from a portion of the input shaft 21 on the bearing 85 side in the clutch case 81 in a state where the clutch case 81 is concentric with the input shaft 21 and a predetermined space is provided between the input shaft 21 and the outer peripheral surface thereof. Cylindrical extension 8 extending toward the device 12 side
On the other hand, the transmission 4a is formed in the clutch case 81 while being concentric with the input shaft 21 from a portion of the driven gear 17 on the bearing 83 side and being separated from the outer peripheral surface of the input shaft 21 by a predetermined gap. The extending portion 81a extending toward the 7 side is formed, and the extending portions 81a and 84a are fitted to each other with the extending portion 81 on the side of the cracker case 81 facing outward. 81a and 84a allow the inside of the case 70 of the transmission 7 and the power transmission device 1 to be provided on the outer periphery of the input shaft 21.
An oil passage 87 is formed so that oil can flow between the two cases 81 and 82. An oil seal 88 for oil-tightly sealing the oil passage 87 and the mechanism portion of the clutch 11 is provided at a fitting portion between the extending portions 81a and 84. In addition, the shaft portion 16a extending toward the clutch 11 side of the drive gear 16 of the power transmission device 12 and the clutch case 8
An oil seal 89 is also provided between the oil seals 1 and 1.

In FIG. 2, 61 is an intake pipe connected to the intake port of each cylinder of the engine 6 and 62 is the engine 6
Exhaust pipe connected to the exhaust port of each cylinder of
The exhaust pipe 62 is taken out from the upper front side of the engine 6 to the rear of the vehicle body through the lower side of the power train.

Therefore, in the first embodiment described above,
The power transmission device 1 passes through the outer peripheral side of the mechanism portion of the clutch 11.
The input shaft 2 of the transmission 7 connected to the driven gear 17 of No. 2
Since an oil passage 87 is formed on the outer periphery of the engine 1, oil can flow between the case 70 of the transmission 7 and the cases 81 and 82 of the power transmission device 12, so that either one of the engine 6 and Both can be lubricated by supplying lubricating oil from an oil pump or the like provided on the side, and the oil circulation path or the lubricating device can be simplified. Particularly, in the case of the embodiment, the engine 6 and the case 70 of the transmission 7 are integrally formed,
Since the oil in the oil pan 75 can be scraped up by the crankshaft 8 to lubricate the mechanical portion of the transmission 7,
The lubrication device can be further simplified.

Moreover, the oil passage 87 is composed of an extending portion 84a formed on the shaft supporting member 84 for pivotally supporting the input shaft 21 and the counter shaft 23 of the transmission 7 and an extending portion 81a formed on the clutch case 81. Since it is configured, a separate member is not required and the number of parts is small, it is advantageous in terms of cost and assembling workability. Also,
Oil passage 87 and extending portions 81a, 84a constituting the oil passage 87
Is provided so as to penetrate through the clutch case 81, and the axial distance between the clutch 11 and the engine 6 and the transmission 7 can be shortened as compared with the case where the clutch case 81 is provided outside the clutch case 81. The power train 10 can be made compact.

In addition, an oil seal 88 is provided at a fitting portion between the extending portions 81a and 84a, so that the oil passage 8 is formed.
7 and the mechanical portion of the clutch 11 are oil-tightly sealed, the oil-tightness of the clutch 11 can be ensured.

Further, in the case of this embodiment, the engine 6
Also, the case 70 of the transmission 7 is formed as an integral structure, and the case 70 and the shaft support member 84 are formed separately, so that when the power train 10 is assembled, the input shaft 21 of the transmission 7 and the counter shaft 23 may be pivotally supported on the shaft support member 84 to perform a sub-assembly, and then, a method of incorporating the mechanism portion of the transmission 7 into the case 70 can be adopted. It can be done easily.

5 to 8 show a power train structure for a vehicle according to a second embodiment of the present invention. This power train structure is mounted as an FF type vehicle in the engine room at the front of the vehicle body and drives the left and right front wheels.

In FIG. 5 to FIG. 7, 101 is a four-cylinder reciprocating engine, and the engine 101 is arranged horizontally with respect to the vehicle body with its crankshaft 102 oriented in the vehicle width direction. 103 is the engine 10
1 is a transmission that is horizontally arranged behind the crankshaft 102 and in parallel with the crankshaft 102.

Reference numeral 111 denotes a clutch provided at one end of the crankshaft 102 of the engine 101,
12 is an engine 1 which is output through the clutch 111
A power transmission device of the churn type for transmitting the power of 01 (rotational force of the crankshaft 102) to the input shaft 121 of the transmission 103, the power transmission device 112 being connected to a clutch disc 152 of the clutch 111 described later. A drive sprocket 116 that is integrally connected to rotate, a driven sprocket 117 that is integrally provided to the input shaft 121 of the transmission 103, and both the sprockets 116,
And a chain 118 wound between 117.

The transmission 103 has an input shaft 121 and an output shaft 122 located on the coaxial line, and a counter shaft 123 parallel to these. The input shaft 121 and the counter shaft 123 are drivingly connected through a pair of reduction gears 124, while a gear train 125 for shifting is arranged between the output shaft 122 and the counter shaft 123. .. Then, the engine power input to the input shaft 121 is transmitted from the input shaft 121 to the counter shaft 123 via the reduction gear 124, and from the counter shaft 123 via any one gear of the speed change gear train 125. Is transmitted to the output shaft 122 and is appropriately decelerated during this period.

An output gear 126 is rotatably integrated with the output shaft 122 of the transmission 103 at the end thereof.
The gear 26 is meshed with a gear 127 provided integrally with the differential case of the differential gear 131 so as to rotate together. Then, the transmission 1
The power output from the output shaft 122 of No. 03 is transmitted to the differential device 131, divided into left and right by the differential device 131, and then left and right front wheels (not shown) via the drive shafts 132L and 132R, respectively. Be transmitted to.

As shown in FIG. 8, the engine 101 is horizontally arranged with its cylinder axis tilted rearward of the vehicle body. In addition, the case 140 of the engine 101
Is the head cover 141 and the cylinder head 14 from above.
2 and upper crankcase 143 and lower crankcase 1
44 and an oil pan 145, a mating surface F between the upper crankcase 143 and the lower crankcase 144 is provided in a plane that passes through the axial center of the crankshaft 102 and is substantially orthogonal to the cylinder axis. The transmission 103
Are housed in the upper crankcase 143 of the engine 101, the input / output shafts 121, 122 thereof are located in front of the counter shaft 123, and the reverse idle gear 128 is arranged below the both. ing.

On the mating surface F, the transmission 10
3, the drive shaft 132R is provided below the drive shaft 132R, and the differential device 131 located coaxially with the drive shaft 132R is accommodated in the upper crankcase 143 and the lower crankcase 144. ing. As described above, the engine 101, the transmission 103, and the differential device 131 are separated into those chambers (that is, the engine chamber,
The transmission chamber 146 and the differential chamber 147) are partitioned so as to have independent reference oil levels, and the case is integrally molded.

On the other hand, as shown in FIGS. 5 and 6, the clutch 111 includes a support disc 151 that is connected to the crankshaft 102 so as to rotate integrally therewith, and a clutch disc 15 that is arranged to face the support disc 151.
2, a pressure plate 153 for pressing the clutch disc 152 against the support disc 151,
A disc spring 154 that constantly urges the pressure plate 153 in the connecting direction of the clutch 111 (that is, a direction in which the clutch disc 152 is pressed against the support disc 151 to transmit power), and a urging force of the disc spring 154 is resisted. And a release fork 155 that returns the pressure plate 153 to the disengagement direction of the clutch 111 (that is, the direction that disengages the clutch disc 152 from the support disc 151 to shut off power transmission). The clutch 111 is provided with a clutch case 156 that covers the clutch body such as the support disk 151. The clutch case 156 is a separate body from the case 140 such as the engine 101. A chain case 157 for covering the sprockets 116 and 117 and the chain 118 of the power transmission device 112 is attached to the side of the above together with the clutch case 156.

The sprockets 116 and 117 of the power transmission device 112 are respectively provided with the clutch case 156.
Bearings 158 on the inner peripheral surfaces of the corresponding boss portions 163 and 164 of
Is rotatably supported through the bottom surface of the boss portions 163 and 164 and the chain case 157.
The corresponding projecting portions 157a and 157b are axially abutted and supported via the thrust plates 165 and 166, respectively. Also, drive sprocket 116
Is rotatably connected to the clutch disc 152 through a shaft 159 formed integrally therewith, and one end of the input shaft 121 of the transmission 103 is rotatably connected to the driven sprocket 117 by spline coupling. .. The clutch case 156 has a boss portion 16
3, a cylindrical collar portion 160 protruding from the outer periphery of the shaft 159 is formed.
The central portion of the disc spring 154 is axially slidably supported via a release bearing 161.

The release fork 155 is of a lever type having a central portion supported by a pivot pin 162, and one end thereof is engaged with the central portion of the disc spring 154.
The other end is from the inside of the clutch case 156 to the crankshaft 1
It is extended to the outside on the opposite side of the transmission 103 with 02 sandwiched,
The extension part is connected to an operation mechanism part (not shown). The pivot pin 162 is attached to the clutch case 156.
Is erected in

The clutch case 156 is shown in FIGS.
As described in detail in FIG. 1, a substantially bowl-shaped clutch chamber 167 that encloses the outer circumference of the clutch body on one side surface side, and a chain chamber 1 that houses the power transmission device 112 on the other side surface side.
68 are formed respectively. That is,
On the clutch chamber 167 side of the clutch case 156, a cylindrical collar portion 160 to which the above-mentioned release bearing 161 is fitted is formed, and the engine 101
-Side mating surface 16 joined to the side case 140
9 is formed. Further, two boss portions 163 and 164 that support the sprockets 116 and 117 of the power transmission device 112 described above are formed on the chain chamber 168 side of the clutch case 156 so as to project, and are joined to the chain case 157. Each of the boss portions 16 described above
An elliptic ring-shaped mating surface 170 is formed with each of the center points of 3164 as a pole.

Further, the above left and right drive shafts 13
Of 2L and 132R, a drive shaft 132R that transmits power to the front wheel on the right side of the vehicle body, which is separated from the differential 131
Has a joint portion 171 composed of a universal joint at a rear position of the clutch 111 or the clutch case 156. The length of the drive shaft 132R from the joint portion 171 to the front wheel is the differential device of the drive shaft 132L on the left side of the vehicle body. The length from the joint portion 172 provided at a portion close to 131 to the front wheel is set to be substantially equal to the length. The differential chamber 147 accommodating the differential device 131 covers the outer periphery of the drive shaft 132R from the differential device 131 side, and drives the drive shaft 13R.
It is expanded to the vicinity of the 2R joint 171.

Next, the transmission 103 and the power transmission device 1
12 and the differential unit 131, that is, the mission chamber 1
The circulation structure of the lubricating oil with respect to 46, the chain chamber 168 and the differential chamber 147 will be described.

The reference oil levels of the three chambers are set to the lowest in the differential chamber 147, and higher in the order of the mission chamber 146 and the chain chamber 168. A strainer 182 is arranged in the differential chamber 147, and an oil pump 183 which is operated by the rotation of the output shaft 122 is provided at the end of the output shaft 122 of the transmission 103. The oil accumulated at the bottom of the differential chamber 147 by the operation is sucked from the strainer 182 through the strainer pipe 184, and the input / output shaft 12 of the transmission 103 is sucked.
The oil is supplied to the lubrication points in the mission chamber 146 and the chain chamber 168 through the oil supply passages 185 formed in the first and the second 122.

On the other hand, as shown in FIG. 6, the boss portion 164 of the clutch case 156 constituting the chain chamber 168 has a chain chamber 168 when the oil level of the chain chamber 168 becomes higher than the reference oil level. A drain hole 186 that allows the oil inside to flow down naturally is formed, and the oil that flows out from the drain hole 186 is the clutch case 156.
Outside, it is returned to the mission chamber 146 through a return oil passage 187 provided on the outer circumference of the input shaft 121 of the transmission 103. Further, as shown in FIG. 7, in a portion of the case 140 that separates the mission chamber 146 and the differential chamber 147, when the oil level in the mission chamber 146 becomes higher than the reference oil level, the inside of the mission chamber 146 is separated. A drain hole 188 is formed to allow the oil to naturally flow down to the differential chamber 147.

The return oil passage 187 is provided in the transmission 10
A shaft support member 193 that rotatably supports the input shaft 121 and the counter shaft 123 of the third shaft via bearings 191 and 192, respectively, is concentric with the input shaft 121 outside the clutch case 156 from the bearing 191 side portion of the input shaft 121. A cylindrical extending portion 193a extending toward the power transmission device 112 side with a predetermined space between the clutch casing and the outer peripheral surface of the clutch case. It is configured by fitting into the boss portion 164 of 156. The extending portion 193a and the boss portion 16
An oil seal 19 that oil-tightly seals between the return oil passage 187 and the clutch 111 is provided at a fitting portion of
4 are provided.

As shown in FIG. 8, the strainer pipe 184 is attached to the engine case 140 (specifically, the lower crankcase 1 with respect to the upper crankcase 143).
44 assembly), the drive shaft 132R
It is arranged so as to bypass. Also, in FIG.
Reference numeral 1 denotes an air supply pipe arranged on the front side of the engine 101, 202
Is an exhaust pipe arranged on the rear side of the engine 101.

Next, the operation of the oil circulation structure of the second embodiment will be described. The power of the engine 101 is the transmission 1.
When it is transmitted to the No. 03 side, the oil pump 183 operates in accordance with the rotation of the output shaft 122 of the transmission 103. By the operation of the oil pump 183, oil is sucked through the strainer pipe 184 from the inside of the differential chamber 147 having the lowest reference oil level among the mission chamber 146, the differential chamber 147, and the chain chamber 168, and after passing through the oil pump 183, The oil is supplied to the chain chamber 168 having the highest reference oil level through the oil supply passages 185 of the input / output shafts 121 and 122 of the transmission 103. When the oil in the chain chamber 168 reaches or exceeds the reference oil level of the chain chamber 168, the oil naturally flows down to the mission chamber 146 having a low reference oil level through the drain hole 186 and the return oil passage 187. Further, when the oil in the mission chamber 146 becomes equal to or higher than the reference oil level of the mission chamber 146, the oil naturally flows down to the differential chamber 147 having the low reference oil level through the drain hole 188.

Therefore, while the oil tightness of the clutch chamber 167 is ensured by such a single oil circulation structure,
Mission room 146, differential room 147 and chain room 16
Since each of the reference oil levels of 8 can be maintained independently, it is possible to properly perform oil lubrication to the lubrication points of each chamber without excess or deficiency, reduce the manufacturing cost, and make the power train compact. And so on.

Moreover, in the second embodiment, the first
Unlike the case of the embodiment, the clutch case 156 does not include the input shaft 121 of the transmission 103 and the oil passage 187 on the outer periphery thereof, and the clutch chamber 1 of the clutch case 156 is not included.
By forming the 67 side in a substantially bowl shape so as to surround the outer periphery of the clutch body such as the support disk 152, the clutch case 156 can be made smaller and lighter and its rigidity can be increased.

Furthermore, the power transmission device 1 as in the second embodiment.
12 is the drive sprocket 11 on the engine 101 side
6 and the driven sprocket 117 on the side of the transmission 103 are configured by using a chain type in which a chain 118 is wound, as compared with the case of using a gear type as in the first embodiment. Since it is less affected by the processing error and the assembly position accuracy, noise can be reduced. Further, the clutch case 156 is provided with thrust plates 165, 166 for supporting the respective sprockets 116, 117 by abutting them in the axial direction, so that a rotatable support structure by the bearing 158 and a supporting strength of the respective sprockets 116, 117 are provided. Can be sufficiently secured and the axial length of the entire support structure can be shortened, which can contribute to downsizing of the power train structure.

The present invention can be similarly applied to the power train structure of, for example, an FR type vehicle in addition to the four-wheel drive vehicle and the FF type vehicle applied in the first and second embodiments. Of course.

[0055]

As described above, according to the powertrain structure for a vehicle of the present invention, the inside of the transmission case and the power transmission are provided on the outer circumference of the input shaft of the transmission which is connected to the power transmission device through the outside of the clutch. An oil passage is formed between the transmission device and the case so that oil can flow, and an oil-tight seal is provided between the oil passage and the clutch. The machine and the power transmission device can share the oil circulation path, and the simplification of the oil circulation path can reduce the manufacturing cost and make the power train compact.

In particular, according to the second aspect of the present invention, since the oil passage is provided so as to penetrate through the clutch case, the axial distance between the clutch and the engine and the transmission can be shortened as much as possible. The train can be made more compact.

According to the fifth aspect of the invention, at the time of assembling the power train, a shaft such as an input shaft of the transmission is preliminarily supported by a shaft support member to form a sub-assembly, and the mechanical portion of the transmission is cased. By incorporating it into the inside, the transmission can be easily assembled, and the work can be speeded up and efficiency improved.

According to the sixth aspect of the invention, since the clutch case is formed in a substantially bowl shape so as to surround only the clutch body, it has the effects that the size and weight can be reduced and the rigidity can be improved.

According to the eighth aspect of the invention, it is possible to contribute to noise reduction by using a chain type power transmission device.

Further, according to the invention of claim 9, each sprocket of the chain type power transmission device is axially abutted and supported by the thrust plate provided on the case, so that the supporting strength is ensured and the axial length is increased. It can be shortened to contribute to compactness.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing an overall configuration of a powertrain structure for a vehicle according to a first embodiment of the present invention.

FIG. 2 is a side view showing the arrangement of power trains in the front part of the vehicle body.

FIG. 3 is a cross-sectional view showing a main part of the power train structure.

FIG. 4 is an enlarged view of the vicinity of the power transmission device of FIG.

FIG. 5 is a view corresponding to FIG. 1 showing a second embodiment.

FIG. 6 is a cross-sectional view showing a structure near a clutch portion of the power train structure.

FIG. 7 is a cross-sectional view showing a structure around a transmission and a differential device of the power train structure.

FIG. 8 is a side view of the power train structure with a part cut away.

FIG. 9 is a side view of the clutch case seen from the mating surface side with the engine.

10 is a cross-sectional view taken along the line AA of FIG.

FIG. 11 is a side view of the clutch case as seen from the mating surface side with the chain case.

[Explanation of symbols]

 6,101 engine 7,103 transmission 8,102 crankshaft 11,111 clutch 12,112 power transmission device 21,121 transmission input shaft 70,140 engine and transmission case 81,156 clutch case 81a clutch case Extension part 82 Gear case (case of power transmission device) 84,193 Shaft support member 84a, 193a Extension part of shaft support member 87,187 Oil passage 88,194 Oil seal 116 Drive sprocket 117 Driven sprocket 117 Chain 122 Transmission Output shaft 157 Chain case (case of power transmission device) 183 Oil pump 185 Oil supply passage

Claims (9)

[Claims] 1. An engine and a transmission are arranged in parallel, a clutch is provided at one end of a crankshaft of the engine, and a clutch is provided on a side of the clutch opposite to the engine. In a powertrain structure of a vehicle provided with a power transmission device for transmitting output engine power to an input shaft of a transmission, the input shaft of the transmission is connected to the power transmission device through an outside of the clutch. An oil passage through which oil can flow between the transmission case and the power transmission case is formed on the outer periphery of the input shaft, and an oil-tight seal is provided between the oil passage and the clutch. A powertrain structure for a vehicle, which is characterized by being mechanically sealed. 2. The powertrain structure for a vehicle according to claim 1, wherein the oil passage is provided so as to penetrate through the clutch case. 3. The oil passage is provided on the power transmission device side while being concentric with the input shaft from a shaft support member that axially supports the input shaft of the transmission and with a predetermined gap from the outer peripheral surface of the input shaft. The powertrain structure for a vehicle according to claim 1, wherein the powertrain structure includes an extending portion that extends. 4. A case of the power transmission device, which is concentric with the input shaft from a vicinity of a gear connected to the input shaft of the transmission and which is spaced apart from the outer peripheral surface of the input shaft by a predetermined gap. An extension portion extending to the transmission side is formed, and the extension portion is fitted to the extension portion of the shaft support member, and the fitting portion seals between the oil passage and the clutch. The powertrain structure for a vehicle according to claim 3, wherein 5. The powertrain structure for a vehicle according to claim 3, wherein the case of the engine and the transmission is integrally formed, and the case and the shaft support member are separately formed. 6. The powertrain structure for a vehicle according to claim 1, wherein the clutch case is formed in a substantially bowl shape so as to surround the outer periphery of the clutch body, and the oil passage is provided outside the clutch case. 7. An oil pump operated by rotation of the output shaft is provided at one end of an output shaft of the transmission, and oil discharged from the oil pump is provided at an input / output shaft of the transmission. Is formed in the case of the power transmission device, and when the oil in the case of the power transmission device reaches a reference oil level or higher, the oil is passed through the oil passage in the case of the transmission. The powertrain structure for a vehicle according to claim 6, wherein the powertrain structure is provided so as to be returned to the vehicle. 8. The powertrain structure for a vehicle according to claim 1, wherein the power transmission device is of a chain type in which a chain is wound between two sprockets. 9. The powertrain structure for a vehicle according to claim 8, wherein a thrust plate that axially abuts and supports each sprocket is provided in a case of the power transmission device.