JPH0223743B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to a housing for an automatic transmission for an automobile. (Prior Art) Conventionally, automatic transmissions for automobiles have a plurality of planetary gear sets and friction engagement elements such as brakes and clutches connected to each element of the planetary gear sets. Each gear stage is achieved by selectively engaging the gears. Each of the above-mentioned frictional engagement elements is constructed by laminating a large number of thin plates mutually, and a hydraulic servo is provided to engage and disengage the thin plates. Oil is supplied from the valve. In addition to the hydraulic oil for operating the hydraulic servo, lubricating oil for cooling and lubricating the thin plate of the friction engagement element or the planetary gear set is supplied from the hydraulic control device. The hydraulic control device, ie, the valve body, is usually disposed at the bottom of the automatic transmission, and an oil reservoir is formed by an oil pan covering the valve body (see Japanese Patent Laid-Open No. 160617/1983). However, recently, four-speed transmissions are becoming more common, and as a result, valve bodies tend to become larger, but the space below the automatic transmission is limited, making it impossible to obtain a sufficient mounting surface. Therefore, there has been proposed a valve body with a laminated structure to reduce the mounting surface, but this increases the height of the valve body and lowers the bottom surface of the valve body and the bottom surface of the oil pan. As a result, the possibility that the vehicle will come into contact with an obstacle while driving increases. Therefore, a valve body has been proposed in which the valve body is placed in the upper part of the case and an oil reservoir is formed in the lower part of the case (see British Patent No. 1,518,092). (Problems to be Solved by the Invention) However, in the automatic transmission with the above configuration, since the valve body is simply moved to the upper part of the case, there is not enough space for installation.
The valve body has no choice but to have a laminated structure. Therefore, the height of the valve body and the height of the case increase, and the overall height of the automatic transmission also increases. Therefore, it is conceivable to arrange the valve body on the upper part of the case without forming it into a laminated structure. In that case, when controlling each valve in the valve body, the drain oil discharged from each valve normally falls from various parts of the valve body, so the valve body is placed in the upper part of the case as described above. If this happens, drain oil will fall onto the input gear of the differential and be agitated, reducing torque transmission efficiency. In particular, since the differential is usually disposed at the bottom of the case, if drain oil accumulates below the differential, the loss due to agitation of the oil is large. The present invention solves the above-mentioned problems of the conventional automatic transmission, and allows a large valve body to be mounted, so that the transmission device can drain the drain oil discharged from the valve body without lowering the valve body and the bottom of the case. The purpose of the present invention is to provide a housing for an automatic transmission that does not cause stirring. (Means for Solving the Problems) To this end, the automatic transmission housing 110 of the present invention includes a transmission 10 disposed coaxially with the fluid transmission device 200 and a transmission disposed parallel to the transmission 10. The fluid transmission device 20 is integrally formed with an underdrive device 50 to which the output of the transmission device 10 is transmitted, and a differential device 70 disposed in parallel with the underdrive device 50.
0, a front housing 120 that accommodates the output gear 4 and the differential device 70, a rear housing 130 that is integrally formed and accommodates the transmission 10 and the underdrive device 50, and has an oil reservoir section 138 below; The output gear 4 is arranged and fixed opposite to the housing 120.
and a partition wall 140 that isolates the differential gear 70 , and a hydraulic control device case 150 that is located above the transmission 10 and accommodates a valve body, and the hydraulic control device case 150 is located above the differential gear 70 . It has an overhang H that extends to . (Operations and Effects of the Invention) According to the present invention, as described above, the fluid transmission device 2
A transmission 10 coaxially arranged with the transmission 10, and an underdrive device 5 arranged parallel to the transmission 10 and to which the output of the transmission 10 is transmitted.
0, a differential device 70 disposed parallel to the underdrive device 50, and a front housing 120 that is integrally formed and houses the fluid transmission device 200, the output gear 4, and the differential device 70. Formed transmission device 10 and underdrive device 50
There is an oil reservoir section 138 below.
a rear housing 130 having a rear housing 130; and a partition wall 14 arranged and fixed opposite to the front housing 120 and separating the output gear 4 and the differential device 70.
0, and a hydraulic control device case 150 that is located above the transmission 10 and accommodates a valve body, and the hydraulic control device case 150 has an overhang H that extends to a position above the differential device 70. Therefore, a large valve body can be mounted using the overhang H. Furthermore, since the valve body is not disposed on the underside of the automatic transmission case, ground clearance can be secured. The drain oil discharged from the valve body is blocked by the partition wall and is prevented from entering the differential gear chamber 70A, so the oil in the differential gear chamber 70A is not stirred and the return of the oil is delayed. This prevents oil levels from dropping or air being sucked into the oil pump. In the above description, each element is given a reference numeral for convenience of explanation, but these do not limit the configuration of the present invention. (Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings. FIG. 1 is a side view of a housing of an automatic transmission according to the present invention, FIG. 2 is a sectional view of an automatic transmission using the housing, and FIG. 3 is a skeletal diagram of a transmission of the automatic transmission. In the figure, an automatic transmission 100 is composed of a fluid transmission device, that is, a fluid torque converter 200, a transmission 300, and a hydraulic control device 400. The transmission 300 includes a first planetary gear set 30, a second planetary gear set 40,
Two multi-disc clutches operated by hydraulic servos
C ₁ , C ₂ , one belt brake B ₁ , two multi-disc brakes B ₂ , B ₃ , two one-way clutches F ₁ ,
1st gear train with F ₂ , i.e. forward 3
a second gear train comprising a transmission 10 with one reverse gear, a third planetary gear set 60, one multi-disc clutch C ₃ operated by a hydraulic servo, one multi-disc brake B ₄ and one one-way clutch F ₃ ; That is, the underdrive device 50,
It has a differential gear 70 , and a speed reduction gear 80 configured with an output gear 71 of an underdrive device, an input gear 9 of the differential gear 70 , and an idler gear 8 . The automatic transmission housing 110 of the present invention includes a front housing 120 and a rear housing 13.
0, it has a partition wall 140 and a hydraulic control device case 150. The front housing 120 includes a torque converter housing 121 whose front side (engine side) is open, and the torque converter housing 121.
The torque converter chamber 200A is installed at the rear of the
and an intermediate support wall 122 that constitutes a partition wall 140 of the transmission chamber 10A. The intermediate support wall 122 is formed with a cylindrical portion 123 that is a cylindrical transmission front case. Further, the front housing 120 is integrally formed with the output gear 71 of the underdrive device 50, the idler gear 8, and the front cases 124, 125, and 126 of the differential device 70, respectively. On the other hand, a rear housing, that is, a transmission case 130 is fitted onto the cylindrical portion 123 and connected to the rear end of the torque converter housing 121. The transmission case 130 is a transmission rear case 13 that is cylindrical and has a rear side wall 132.
1. Contains an underdrive device case 138 that is cylindrical and has a rear side wall 134 and is continuously adjacent to the side of the transmission rear case 131, a differential gear rear cover 135, a transmission rear case 131, and an underdrive device case 133. An opening 137 is formed in the upper part, and an oil reservoir 138 having a sufficient capacity is formed in the lower part. The partition wall 140 includes a rear case 1 for the output gear 71, the idler gear 8, and the differential gear 70.
41, 142, and 143 are integrally formed.
The rear cases 141, 142, and 143 support the output shaft 7, the fourth shaft 81, and the differential gear input section 701, respectively. Output shaft 7, 4th
Shaft 81 and differential gear input section 701
The other end is supported by front housing 120. In the automatic transmission housing 110,
The connecting portion of the front housing 120 and the partition wall 140 is formed in a ferrule structure, and the corresponding portions of the front cases 124 and 1 are connected to each other.
25, 126 and the partition walls 141, 142, 143
are fitted and fastened with bolts 144. Then, a differential housing chamber 70A having an output gear chamber 71A, an idler gear chamber 8A, and a differential device 70 that communicate with each other is formed, forming a torque converter/differential housing 500 that is a strong fastening body between the two. A transmission case 130 is connected to the rear portion of the torque converter differential housing 500, forming a transmission chamber 10A and an underdrive device chamber 50A. Furthermore, a hydraulic control device 4 consisting of various valve bodies, communication oil passages, etc. is provided in an opening 137 of the box body 136.
A hydraulic control device case 150 accommodating the 00 is connected to form a housing 110 of the automatic transmission. The torque converter 200 has a front cover 20
1, a turbine runner 203 connected to the output shaft 1 through a turbine hub, and a one-way clutch 204 fitted into the center hole 122A of the intermediate support wall 122. It consists of a stator 206 engaged with a tubular fixed shaft, that is, a stator shaft 205, and a direct coupling clutch 207 connected to a turbine hub, and is installed in a torque converter case 121. The oil pump 90 has an annular space formed between the stator shaft 205 and a cylindrical protrusion 95 provided around the outer circumferential side of the intermediate support wall 122 on the torque converter 200 side, that is, a pump body fitting portion 96.
A cylindrical pump drive shaft 9 is rotatably fitted onto the stator shaft 205 and is integral with the pump impeller 202.
A pump body 91 housing a pump gear 93 driven by a pump gear 93 is formed by fastening an annular steel plate 92 therebetween. Further, the annular thin plate 92 closes an oil passage groove 97 formed on the torque converter 200 side of the partition wall 122 to form an oil passage 98 . In the transmission chamber 10A, a forward-facing cylindrical rear center support 11 is protruded from the center of the rear side wall 132, and a large cylindrical rear center support 11 formed integrally with the stator shaft 205 is provided at the center rear surface of the intermediate support wall 122. A diametrically cylindrical front center support 12 is coaxially fixed to the rear center support 11 so as to face rearward. The rear center support 11 and the stator shaft 205
An input shaft 1, which is the output shaft of the torque converter 200 and the input shaft of the transmission 10 and the transmission 100, is rotatably supported inside the input shaft 1. It is rotatably mounted on the intermediate shaft 2. A cylindrical sun gear shaft 3 is rotatably mounted on the outside thereof, and an output gear 4 of a transmission 10 spline-coupled to the tip of the first intermediate shaft 2 is rotatably supported on the front center support 12. . The input shaft 1 of the transmission 300 is
At its rear part, it is spline-fitted to an annular hydraulic servo center drum 21 that is rotatably fitted onto the tip of the forward-facing rear center support 11 . The hydraulic servo center drum 21 is open at the front, has a rearward-facing cylindrical protrusion 211 formed in the middle, and is located between an inner circumferential wall 212 and an outer circumferential wall 213 that are fitted onto the tip of the rear center support 11. The annular piston 22 is fitted into a multi-plate clutch.
A hydraulic servo C1 of _C1 is formed, and the ring gear 33 of the first planetary gear set ₃₀ is connected via a multi-plate clutch C1 formed in the outer peripheral wall 213.
is connected to. The first planetary gear set 30 is provided on the front side of the hydraulic servo C1, and includes a sun gear 31 formed at the rear end of the sun gear shaft 3, a planetary gear set 32 spline-coupled to the rear end of the first intermediate shaft 2, and the The sun gear 31 is rotatably supported by a ring gear 33 and a carrier 32 which are connected to the center drum 21 via a multi-plate clutch _C1 .
and a planetary gear 34 that meshes with the ring gear 33.
Consists of. An annular hydraulic servo rear drum 23 is rotatably fitted onto the rear center support 11 between the center drum 21 and the rear side wall 132. The rear drum 23 for hydraulic servo is open at the front, and an annular piston 24 is fitted between an inner circumferential wall 231 and an outer circumferential wall 232 to form a hydraulic servo C2 of a multi-plate clutch _C2 . It is connected to the cylindrical protrusion 211 of the center drum 21 through a multi-plate clutch _C2 , and connected to the front side of the sun gear 31 of the sun gear shaft 3 through a connecting drum 25 connected to the rear end of the outer peripheral wall 232. ing. The connecting drum 25 covers the center drum 21 and the first planetary gear set 30, and has a belt brake operated by a hydraulic servo (not shown) on the outside of its outer peripheral wall 251.
A friction engagement plate 252 of _B1 is attached. Rear case 131 on the front side of the connecting drum 25
A front drum 26 for a hydraulic servo, which is annular and open at the front, is fitted into the rear end of the inner surface of the cylindrical front case 123, which is fitted into the front drum 2.
An annular piston 27 is fitted into the inner part 6 to form a hydraulic servo _b2 of the multi-disc brake _B2 . A spline groove 123A is formed on the inner surface of the cylindrical front case 123, and a multi-disc brake B ₂ is mounted in front of the hydraulic servo B ₂ , a one-way clutch F _{2 connected by an outer race FD is mounted in front of the multi-disc brake B 2} , and a reverse brake is mounted in front of the multi-disc brake B 2 . Multi-disc brake _B3 is fitted. An annular reverse brake hydraulic cylinder 28 is formed on the rear surface of the intermediate support wall 122 of the front housing 120, which is the front wall of the transmission chamber 10A, and a multi-disc brake _B3 extending rearward from the outer periphery is pressed into the cylinder 28. An annular piston 29 with a protruding cylindrical pressure transmission ring 291 is fitted into the hydraulic servo of the reverse brake _{B3 .}
is formed. Further, the spline groove 12 is provided on the outside of the rear end of the pressure transmission ring 291 of the piston.
A protrusion 292 is provided to prevent rotation of the annular piston 29 that is engaged with the ring 3A. Inside the multi-disc brake B ₂ above, there is a sun gear shaft 3.
A one-way clutch F1 is provided with an inner race fa and an outer race fd connected to the cylindrical case ₁₂₃ via a brake _B2 , and a second planetary gear set 40 is provided in front of the one-way clutch _F1 . . The second planetary gear set 40 is connected to the inner race shaft fc of the one-way clutch _F2 , and is connected to the output gear 4 and a planetary carrier 42 connected to the cylindrical front case ₁₂₃ via the multi-disc brake B3. It consists of a ring gear 43 and a planetary pinion 44 rotatably supported by a planetary carrier 42 and meshed with the sun gear 41 and the ring gear 43. Further, a forward-facing cylindrical rear center support 51 is protruded from the center of the rear wall 134 of the underdrive device chamber 50A, and a rearward-facing cylindrical front center support 52 is protruded from the center of the rear case 141 of the output gear. In the center, the output shaft 7 with the output gear 71 formed in the front part is located in the output gear chamber 71A.
It is rotatably supported by a tapered roller bearing 72 installed in the. Further, a cylindrical second intermediate shaft 6 is rotatably fitted on the outside of the rear side of the output shaft 7 and the rear center support 51, and the input gear 5 is rotatably fitted on the front center support 52. is supported by The rear wall 13 of the underdrive device chamber 50A
An annular hydraulic cylinder 53 is formed on the front surface of the cylinder 4, and a multi-disc brake is mounted on the outer circumference of the cylinder 53.
An annular piston 54 having a tooth-like protrusion 541 surrounding it that presses B ₄ is fitted, forming a hydraulic servo b ₄ of a multi-disc brake B ₄ . The hydraulic servo b ₄
On the front side, the rear end portion of the second intermediate shaft 6 is an inner race fe, and the outer race ff is connected to the toothed projection 5.
A one-way clutch _F3 is provided which is connected to the underdrive device case 133 via a connecting ring 55 passing through the underdrive device case 133. A multi-disc brake _B4 is formed inside the case 133 on the front side of the connecting ring 55. Further, on the front side of the one-way clutch _F3 , a rearward-facing cylindrical portion 561 is protruded from the intermediate portion thereof, and a hydraulic servo annular drum 56 which is open toward the front is connected thereto. An annular piston 57 is fitted between the outer peripheral wall 562 of the annular drum 56 for hydraulic servo and the outer surface of the second intermediate shaft 6, forming a hydraulic servo _c3 of a multi-plate clutch _C3 . Further, the annular drum 56 has an outer peripheral wall 56
2 through a multi-plate clutch _C3 formed in the third
It is connected to the carrier 62 of the planetary gear set 60, and further connected to the case 133 via a multi-disc brake _B4 formed outside the cylindrical portion 561. A third planetary gear set 60 is provided in front of the hydraulic servo _c3 . The third planetary gear set 60 is a sun gear 61 formed at the tip of the second intermediate shaft 6, or a planetary gear spline-fitted to the output shaft 7 and connected to the annular drum ₅₆ via the multi-plate clutch C3. It is comprised of a rear 62, a ring gear 63 connected to the input gear 5, and a planetary gear 64 that is rotatably supported by the planetary carrier 62 and meshed with the sun gear 61 and the ring gear 63. The output gear 4 of the transmission 10 and the input gear 5 of the underdrive device 50 are directly meshed with each other, or as shown in the figure, a chain 160 is provided for drivingly connecting them. And the chain 16
0 is two notches 161 provided at predetermined positions of the pressure transmission ring 291 of the annular piston 29, two notches 162 provided at predetermined positions of the cylindrical portion 123 which is the front case of the transmission, and the transmission. Two notches 163 provided at predetermined positions in the case 130 extend through two communication holes formed respectively. The speed reducer 80 includes a tapered roller bearing 72
The output gear 71 of the underdrive device rotatably supported in the output gear chamber 71A, and the front case 125 and rear case 1 of the idler gear chamber 8A.
42, is rotatably supported by a tapered roller bearing 82 mounted on the fourth shaft 81, and meshes with the output gear 71.
and an input gear 9 that is formed on the rear outer periphery of a differential gear input section 701 that is rotatably supported within the differential device chamber 70A by a tapered roller bearing 901 and meshes with the idler gear 8. The differential device 70 is a differential gear 702
The wheel shafts 9A and 9B, which are the output shafts of the automatic transmission, are attached to the wheels. The transmission 300 controls the hydraulic control device 40 according to vehicle running conditions such as vehicle speed and throttle opening.
The hydraulic pressure selectively output from 0 to each hydraulic servo engages and releases each clutch and brake, resulting in four forward speeds and one reverse speed change.
Tables 1 to 3 show three examples of the operation of each clutch, brake, and one-way clutch, as well as the gears and reduction ratios achieved.

【table】

【table】

[Table] In Tables 1, 2, and 3, 〇 indicates engagement.
△ indicates the engine brake, and × indicates the released state. In the automatic transmission, the speed is changed as shown in Tables 1, 2, and 3 above, and the rotation output from the output shaft 7 of the underdrive device 50 is controlled by the output gear 71, the idler gear 8, and the input gear 9. The rotational speed is then reduced to a predetermined rotational speed and transmitted to the differential gear 70, which drives the wheel axles 9A and 9B, which are the output shafts of the automatic transmission 100, via a known differential gear 702. In the automatic transmission configured as described above, the hydraulic control device case 150 that houses the hydraulic control device 400 is placed above the box body 136. And box body 13
6 has a lower portion equal to the width of the oil reservoir portion 138, and an upper portion which increases toward the left as shown by the broken line in FIG. 1, forming an overhang portion H.
The projecting portion H extends to the axis of the output shaft 9A of the differential gear 70, and the valve body and oil pan can be made larger by the width of the projecting portion H. The drain oil discharged from the valve disposed in the valve body falls and is stored in the oil reservoir 138, but the drain oil discharged from the valve located in the overhang H is collected in the box body 138.
The oil flows along the wall of the underdrive device 6 to the oil reservoir 138, but some of the oil tends to flow along the bottom of the underdrive device case 133 to the differential device 70 located at a lower position on the engine side of the underdrive device 50. If a large amount of oil enters the differential device 70, it will be agitated by each gear of the differential device 70, causing a delay in the return of the oil, a drop in the oil level, or the oil pump sucking in air. This results in a decrease in efficiency. In the automatic transmission housing of the present invention,
A partition wall 140 faces the front housing 120.
are provided, and the front cases 124, 12
5, 126 and the partition walls 141, 142, 143 are fitted and fastened with bolts 144. Since a differential housing chamber 70A is formed which has an output gear chamber 71A, an idler gear chamber 8A, and a differential device chamber 71A that communicate with each other, the oil that has fallen from the hydraulic control device 400 is transferred to this partition wall 140. This prevents it from entering the differential gear chamber 71A. Note that the present invention is not limited to the above-mentioned embodiments, and various modifications can be made based on the spirit of the present invention, and these are not excluded from the scope of the present invention.

[Brief explanation of drawings]

FIG. 1 is a side view of the automatic transmission housing according to the present invention, FIG. 2 is a sectional view of an automatic transmission using the automatic transmission housing according to the present invention, and FIG. 3 is a skeleton of the transmission of the automatic transmission. It is a diagram. 1...First shaft, 4...Output gear of the first gear train, 5...Input gear of the second gear train, 7...Second gear
shaft, 10...first gear train, 50...second gear train, 110...automatic transmission housing, 130
...Transmission case, 131...Transmission rear case, 133...Underdrive device, 13
6... Box body, 137... Opening, 138... Oil reservoir, 150... Hydraulic control device case, 200... Torque converter, 300... Transmission, 4
00... Hydraulic control device.

Claims (1)

[Scope of Claims] 1. A transmission device disposed coaxially with a fluid transmission device, an underdrive device disposed parallel to the transmission device and to which the output of the transmission device is transmitted, and the above-mentioned underdrive device. a differential device disposed parallel to the device; a front housing integrally formed and housing the fluid transmission device, the output gear, and the differential device; a front housing integrally formed and housing the transmission device and the underdrive device; a rear housing having an oil reservoir below; a partition wall arranged and fixed opposite to the front housing and isolating the output gear and the differential; and a hydraulic control located above the transmission and accommodating a valve body. 1. A housing for an automatic transmission, comprising: a device case, the hydraulic control device case having a projecting portion extending to a position above the differential device. 2 The transmission device is a first gear train provided on a first shaft which is an output shaft of a fluid transmission device and an input shaft of a transmission, and the underdrive device is arranged in parallel with the first shaft. A second gear train is provided on a second shaft, and together they constitute an automatic transmission with four forward speeds or more and one reverse speed. is provided with a differential device, and is provided on a fourth shaft between the output gear of the second gear train, the input gear of the differential device, and the second and third shafts, and meshes with both gears to reduce the speed. 2. The automatic transmission housing according to claim 1, further comprising a device.