JPH0246814B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to an automatic transmission for automobiles. (Prior Technology) Conventionally, front-engine, front-drive (hereinafter referred to as FF) vehicles have been provided with the aim of reducing fuel consumption or making them smaller and lighter. Machines are also available that are small, lightweight, and easy to mount, especially those with a short overall length with a shortened axial dimension. In an automatic transmission equipped with a torque converter, transmission, oil pump, and hydraulic control device, the oil pump is disposed between the torque converter and the transmission, and is driven by the drive shaft connected to the torque converter. It consists of a pump gear that rotates, a pump body that houses the pump gear, and a pump cover. Here, the torque converter housing that houses the torque converter and the transmission case that houses the transmission are usually made of a lightweight material such as aluminum to reduce weight. Furthermore, in the oil pump, the pump gear rotates at high speed, causing metal contact between the pump gear and the pump cover, and between the pump gear and the pump body, resulting in wear. Therefore, pump covers and pump bodies are now made of cast iron. (Problem to be Solved by the Invention) However, in the automatic transmission with the above configuration, the oil pump is formed by combining the pump body and the pump cover, and both are made of cast iron to prevent wear between them and the pump gear. Because of this, the weight increases. Further, since the oil pump is formed by combining the pump body and the pump cover, it has a structure independent of the torque converter housing, transmission case, etc. Therefore, a seal structure, piping space, etc. are required to connect the pipe through which the discharged oil flows to the oil pump, which increases the work cost and increases the size of the automatic transmission. The present invention solves the problems of the conventional automatic transmission described above, and provides an automatic transmission that can simplify the structure of the oil pump, improve sealing performance and ease of assembly, and reduce weight. The purpose is to (Means for solving the problem) For this purpose, in the automatic transmission of the present invention,
The torque converter housing includes a torque converter, a transmission, an oil pump, and a hydraulic control device, and a torque converter housing housing the torque converter and a transmission case housing the transmission can be separated. The torque converter housing forms a torque converter chamber that houses the torque converter, and the transmission case forms a transmission chamber that houses the transmission. A partition wall is integrally formed with the torque converter housing between the torque converter chamber and the transmission chamber, and the oil pump includes a pump gear, a pump body in which a recess is formed to accommodate the pump gear, and a pump body that covers the recess. The pump body has a thin annular steel plate disposed along the pump body, and the pump body is fixed via the annular thin steel plate. Further, the partition wall is formed with a pump body fitting portion having an ingot structure in which a cylindrical protrusion facing the torque converter side is formed, and a connection portion between the torque converter housing and the transmission case is an ingot structure. It has a solder structure or a knock pin structure to ensure concentricity between the torque converter housing and the transmission case. A groove is formed on the torque converter side of the partition wall, and an oil passage is formed by closing the groove with the annular steel plate. (Operations and Effects of the Invention) According to the present invention, as described above, the torque converter housing includes a torque converter, a transmission, an oil pump, and a hydraulic control device, and houses a torque converter housing that houses the torque converter and houses the transmission. In an automatic transmission with a splittable transmission case, the torque converter housing forms a torque converter chamber that houses the torque converter, and the transmission case forms a transmission chamber that houses the transmission. has formed,
A partition wall is formed integrally with the torque converter housing between the torque converter chamber and the transmission chamber, and the oil pump includes a pump gear, a pump body in which a recess is formed to accommodate the pump gear, and a pump body that covers the recess. Since the pump body is fixed to the partition wall via the annular thin plate made of steel, there is no need to provide a separate pump cover. Moreover, since the bulkhead is made of aluminum like the torque converter housing and transmission case, it can be made lighter. Further, the partition wall is formed with a pump body fitting portion having an ingot structure in which a cylindrical protrusion facing the torque converter side is formed, and a connection portion between the torque converter housing and the transmission case is an ingot structure. Since it has a solder structure or a knock pin structure, concentricity between the torque converter housing and the transmission case can be ensured. A groove is formed on the torque converter side of the partition wall, and an oil passage is formed by closing the oil passage groove with the steel annular thin plate, so there is no need to form a separate oil passage structure. , work costs can be reduced. Furthermore, since the number of seal parts is reduced, the seal structure and piping space can be simplified. (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 the external appearance of the automatic transmission of the present invention;
FIG. 2 is a diagram showing its internal structure, and FIG. 3 is a skeleton diagram of the transmission of the automatic transmission. In the figure, an automatic transmission 100 includes a hydraulic torque converter 200 and a transmission 300.
and a hydraulic control device 400. The transmission 300 includes a first planetary gear set 30 and a second planetary gear set 4.
0, forward movement 3 with two multi-disc clutches C ₁ , C ₂ operated by hydraulic servo, one belt brake B ₁ , two multi-disc brakes B ₂ , B ₃ and two one-way clutches F ₁ , F ₂ A transmission 10 with one reverse speed, a third planetary gear set 60, and one multi-disc clutch C ₃ operated by a hydraulic servo.
an underdrive device 50 comprising one multi-disc brake B ₄ and one one-way clutch F ₃ ;
It is composed of a differential gear 70, and a speed reduction gear 80 that is composed of an output gear 71 of an underdrive device 50, an input gear 9 of the differential gear 70, and an idler gear 8. The automatic transmission housing 110 includes a front housing 120 on the front side (engine side), a rear housing 130 on the rear side, and a bearing retainer 140.
and a hydraulic control device cover 150. The front housing 120 is provided with a torque converter housing 121 whose front side is open, and a rear part of the torque converter housing 121,
It has a partition wall between the torque converter chamber 200A and the transmission chamber 300A, that is, an intermediate support wall 122. 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 connected to an output gear 7 of an underdrive device that is continuously adjacent to the side of the torque converter housing 121.
1. The idler gear 10 and the front cases 124, 125, 126 of the differential device 70 are integrally formed. On the other hand, the rear housing, that is, the transmission case 130 is the cylindrical front case 1.
23 and torque converter housing 12
It is connected to the rear end of 1. The transmission case 130 is a transmission rear case 13 that is cylindrical and has a rear side wall 132.
1. An underdrive device case 138 having a cylindrical shape and having a rear wall 134 that is continuously adjacent to the side of the transmission rear case 131, a rear cover 135 of the differential gear 70, a transmission rear case 131, and an underdrive device case. 138, and is integrally formed with a hydraulic control device cover connecting portion 136 having an opening at the top. The bearing retainer 140 is connected to the output gear 7
1. The idler gear 8 and the rear cases 141, 142, 143 for the differential gear 70 are integrally formed. In the automatic transmission housing 110,
The connecting portions of the front housing 120 and the bearing retainer 140 are formed in a ferrule structure, and the corresponding portions of the front cases 124, 125, 126 and the rear case 14
1, 142, 143 are fitted, and the bolt 1
It is concluded at 44. Then, a differential housing 70A is formed, which includes an output gear chamber 71A, an idler gear chamber 8A, and a differential device 70 that communicate with each other.
A torque converter/differential housing 500 is formed which is a strong connection between the two. The transmission case 130 is connected to the rear of the torque converter differential housing 500 to form a transmission chamber 70A and an underdrive device chamber 50A, and a hydraulic control device cover 150 is connected to the cover connection portion 136. ,
An automatic transmission housing 110 is formed. 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. In the oil pump 90, a cylindrical projection 95 provided around the outer peripheral side of the intermediate support wall, that is, the partition wall 122 on the torque converter side, is connected to an annular space formed between the stator shafts 205, that is, a pump body fitting portion 96. , is rotatably fitted onto the fixed shaft 205. The oil pump 90 has a pump body 91, a recess is formed in the pump body 91, and a pump gear 93 driven by a cylindrical pump drive shaft 94 integral with the pump impeller 202 is accommodated in the recess. . The pump body 91 and pump gear 93 are fastened to the partition wall 122 via an annular thin plate 92 made of steel. The annular thin plate 92 is made of a wear-resistant material and is connected to the pump gear 93 and the partition wall 122.
The groove 97 formed on the side surface of the torque converter of the partition wall 122 is covered to form an oil passage 98 through which oil flows. In the transmission chamber 10A, a forward-facing cylindrical rear center support 11 is protruded from the center of the rear wall 132, and a large-diameter support 11, which is integral with the cylindrical stator shaft 205, is provided at the center rear surface of the intermediate support wall 122. A cylindrical front center support 12 is fixed rearward. The rear center support 11 and the cylindrical stator shaft 2
05, an input shaft 1 which is an output shaft of the torque converter 200 and an input shaft of the transmission 10 and transmission 100 is rotatably supported, and a cylindrical first shaft is rotatably supported on the outside of the input shaft 1. It is rotatably mounted on the intermediate shaft 2 of. A cylindrical sun gear shaft 3 is rotatably attached to the outside of the sun gear shaft 3.
The first intermediate shaft 2 is attached to the front center support 12 above.
The output gear 4 of the transmission 10 is spline-coupled to the tip of the transmission gear 10 and is rotatably supported. 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 . On the inner surface of the cylindrical front case 123, there is a multi-disc brake B ₂ on the front side of the hydraulic servo b ₂ , a one-way clutch F ₂ connected to the front side with an outer race FD,
A reverse multi-disc brake _B3 is fitted in front of it. 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. 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 a sun gear 41 formed at the tip of the sun gear shaft 3, an inner race shaft fc of a one-way clutch _F2 , and connected to the cylindrical front case 123 via a multi-disc brake _B3 . A planetary carrier 42 , a ring gear 43 connected to the output gear 4 , and a planetary gear set 42 rotatably support the sun gear 41 and the link gear 4 .
3 and a planetary pinion 44 meshed with. 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. Furthermore, 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 an 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 rotation speed is then reduced to a predetermined speed and transmitted to the differential device 70, and the automatic transmission 1 is transmitted to the automatic transmission 1 via a known differential gear 702.
The wheel shafts 9A and 9B, which are the output shafts of 00, are driven. 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 case of an automatic transmission according to the present invention, FIG. 2 is a sectional view showing the internal structure of the automatic transmission, and FIG. 3 is a skeleton diagram of the transmission of the automatic transmission. 1...Input shaft, 90...Oil pump, 91...
...Pump body, 92...Steel annular thin plate,
93...Pump gear, 94...Pump drive shaft, 9
5... Cylindrical projection, 96... Pump body fitting part,
97... Oil passage groove, 98... Oil passage, 100... Automatic transmission, 121... Torque converter housing, 122... Bulkhead, 130... Transmission case, 200... Torque converter, 30
0...Transmission, 400...Hydraulic control device.

Claims (1)

[Claims] 1. A torque converter, a transmission, an oil pump, and a hydraulic control device are provided, and a torque converter housing that accommodates the torque converter and a transmission case that accommodates the transmission are separable. In the automatic transmission, the torque converter housing forms a torque converter chamber that houses the torque converter, the transmission case forms a transmission chamber that houses the transmission, and the torque converter chamber and the transmission case form a transmission chamber that houses the transmission. A partition wall is integrally formed with the torque converter housing between the transmission chambers, and the oil pump includes a pump gear, a pump body in which a recess is formed to accommodate the pump gear, and a steel annular shape disposed to cover the recess. Along with having a thin plate,
An automatic transmission characterized in that the pump body is fixed via the steel annular thin plate. 2. The automatic transmission according to claim 1, wherein the partition wall has a cylindrical protrusion facing the torque converter side and a pump body fitting portion having a ferrule structure. 3. The connection portion between the torque converter housing and the transmission case has a spigot structure, and the concentricity of the torque converter housing and the transmission case is ensured. automatic transmission. 4. The connection portion between the torque converter housing and the transmission case has a knock pin structure, and the concentricity of the torque converter housing and the transmission case is ensured. Automatic transmission. 5. Claims 1 to 5, wherein a groove is formed on the torque converter side of the partition wall, and an oil passage is formed by closing the groove with the steel annular thin plate.
The automatic transmission according to any of Item 4.