JP4619381B2 - Fluid path structure of automatic transmission - Google Patents

Description

  In the present invention, a planetary gear mechanism and a wet multi-plate clutch are arranged adjacent to each other, and a liquid path formed in a pinion shaft of the planetary gear mechanism using a gap between the carrier of the planetary gear mechanism and the centrifugal canceller of the wet multi-plate clutch. The present invention relates to a fluid path structure of an automatic transmission that supplies fluid.

  For example, FIG. 5 shows a liquid path structure of a conventional automatic transmission, and FIG. 5 is a cross-sectional view of a main part illustrating a forward 6-speed automatic transmission including the oil path structure.

  The automatic transmission disclosed in FIG. 5 has two sets of pinions 216 and 217 rotatably supported by a pinion shaft 215 provided on a carrier 214 between two sun gears 211 and 212 and one ring gear 213. A Ravigneaux type planetary gear mechanism 210 that enables transmission of power between the individual sun gears 211 and 212, the ring gear 213 and the carrier 214, and an input shaft 30 to which power from an engine (not shown) is input. A piston 223 for fastening or releasing the clutch plates P1 and P2 provided on the rotating drum 221 (221a and 221b) to be engaged and the rotating hub 222 coupled to the carrier 214 of the Ravigneaux type planetary gear mechanism 210 is provided inside the rotating drum 221. A slidable housing that forms a hydraulic chamber Ro for piston operation. The wet multi-plate clutch 220 provided with a centrifugal canceller 224 at a position opposite to the piston working hydraulic chamber Ro is obtained by adjacently arranged while.

  The centrifugal canceller 224 includes a seal member S1 that holds the piston 223 via a return spring 225 and seals between the piston 223 and the inner periphery of the piston 223. The centrifugal member canceller 224 is centrifuged together with the piston 223 and the centrifugal canceller 224 by the seal member S1. A cancellation room Rc0 is defined. The centrifugal cancel chamber Rc0 is for stabilizing the piston operation by stabilizing the centrifugal hydraulic pressure acting on the piston 223 from the side facing the piston operating hydraulic chamber Ro.

  In the automatic transmission, an oil passage 31 through which oil flows is formed in the input shaft 30, and the oil in the oil passage 31 is discharged using a centrifugal force generated by the rotation of the input shaft 30. It is supplied as hydraulic oil or lubricating oil to various places around the input shaft 30 via 31h.

Among these, the pinion shaft 215 and the pinions 216 and 217 of the Ravigneaux type planetary gear mechanism 210 are one of the parts that need to be lubricated, and therefore an oil passage 218 through which oil flows is also formed inside the pinion shaft 215. A carrier 214 of the Ravigneaux type planetary gear mechanism 210 is brought into contact with the oil passage 218 so as to face the centrifugal canceller 224 via partition plates 227 and 228 fixed to the inner peripheral portion of the rotary drum 221, so that the carrier 214 and the centrifugal A gap ΔCo is formed between the cancellers 224, and oil discharged from the discharge holes 31h through the oil passage 31 of the input shaft 30 is supplied using the gap ΔCo (see, for example, Patent Document 1).
JP 2000-220705 A

  However, in such a conventional oil passage structure, an oil catch plate P is separately provided on the side surface of the carrier 214, and oil flowing through the gap ΔCo between the carrier 214 and the centrifugal canceller 224 is separated by the oil catch plate P. Since the oil passage 218 formed in the pinion shaft 215 is introduced, the axial dimension of the entire automatic transmission is increased by the amount of the oil catch plate P, and at the same time, the number of parts is increased. It was.

  In addition, such an oil catch plate P does not seal the gap ΔCo between the carrier 214 and the centrifugal canceller 224, but simply forms oil that flows through the gap ΔCo between the carrier 214 and the centrifugal canceller 224 in the pinion shaft 215. Since it is for guiding to the path 218, there is room for improvement so that oil can be introduced more efficiently into the oil path 218 formed in the pinion shaft 215 from the gap between the carrier 214 and the centrifugal canceller 224.

  The problem to be solved by the present invention has been made in view of the above-mentioned facts, and the pinion of the planetary gear mechanism is formed by using a gap formed between the carrier of the planetary gear mechanism and the centrifugal canceller of the wet multi-plate clutch as a liquid path. In the fluid passage structure of the automatic transmission that supplies fluid to the fluid passage formed in the shaft, the gap between the carrier and the centrifugal canceller is not increased without increasing the axial dimension and the number of parts of the entire automatic transmission. An object of the present invention is to enable efficient introduction of a circulating fluid into a liquid passage formed in a pinion shaft.

  For this reason, the liquid passage structure of the automatic transmission according to the present invention includes a planetary gear mechanism that rotatably supports a pinion disposed between a sun gear and a ring gear by a pinion shaft provided on a carrier, a rotating drum, and a rotating hub. A piston operating fluid pressure chamber is formed between the piston and the rotating drum by slidably storing a piston for fastening or releasing the provided friction members to each other inside the rotating drum. A centrifugal canceling fluid pressure that cancels the centrifugal fluid pressure generated in the piston actuating fluid pressure chamber is defined between the piston and the inner peripheral portion of the rotating drum facing the working fluid pressure chamber via the piston. A wet multi-plate clutch provided with a centrifugal canceller, and the carrier and the centrifugal canceller face each other between the wet multi-plate clutch and the planetary gear mechanism. In the liquid passage structure of the automatic transmission that forms a gap between the carrier and the centrifugal canceller and supplies fluid to the liquid passage formed in the pinion shaft using the gap, the centrifugal canceller and the carrier Between the side surface of the centrifugal canceller and the side surface of the carrier, and a seal member is formed between the side surface of the centrifugal canceller and the inner peripheral portion of the piston. It is formed integrally with a seal member that defines a centrifugal cancel chamber between the inner peripheral portion and the centrifugal canceller.

  In the present invention, the centrifugal canceller preferably has a through hole for supplying a fluid to the liquid chamber.

  For this reason, in the liquid passage structure of the automatic transmission according to the present invention, a sealing member that defines a liquid chamber by sealing a gap formed between the centrifugal canceller and the carrier is integrated between the centrifugal canceller and the carrier. Therefore, the axial dimension of the entire automatic transmission can be shortened and the number of parts can be reduced at the same time as compared with the case where a separate oil catch plate is attached. Moreover, since the sealing member seals the gap formed between the carrier and the centrifugal canceller, the fluid in the gap can be efficiently introduced into the liquid path formed in the pinion shaft.

  Therefore, according to the present invention, the fluid in the gap formed between the carrier and the centrifugal canceller is efficiently transferred to the liquid passage formed in the pinion shaft without causing an increase in the axial dimension and the number of parts of the entire automatic transmission. Can be introduced.

  Further, according to the present invention, the seal member provided in the centrifugal canceller is integrally formed with the seal member that defines the centrifugal cancel chamber between the inner peripheral portion of the piston and the centrifugal canceller by contact with the inner peripheral portion of the piston. Thus, the centrifugal canceller and the seal member are more firmly fixed. Therefore, according to the present invention, a high-pressure fluid can be supplied into the gap formed between the carrier and the centrifugal canceller, so that the liquid passage formed in the pinion shaft further passes through the gap formed between the carrier and the centrifugal canceller. A fluid can be efficiently introduced.

  Furthermore, if a through hole for supplying a fluid to the liquid chamber is formed in the centrifugal canceller according to the present invention, the lubricating liquid can be introduced more efficiently into the liquid passage formed in the pinion shaft.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings with reference to an automatic transmission having six forward speeds.

  FIG. 1 is a sectional view showing a power train equipped with a forward 6-speed automatic transmission having an oil passage structure according to a first embodiment of the present invention, and FIG. 2 is on a first axis O1 shown in FIG. 1 is a skeleton diagram of an automatic transmission according to the present invention arranged in FIG. FIG. 3 is an enlarged sectional view showing a main part of the forward 6-speed automatic transmission according to the present invention.

  A power train 1 shown in FIG. 1 has three axis lines O1, O2, and O3 offset in a transmission case 2, and the forward 6-speed automatic transmission according to the present invention is arranged on the first axis O1. A lockup torque converter 10 to which power from an engine (not shown) is input, an oil pump 20 driven by a pump impeller 10a of the lockup torque converter 10, and a lockup torque converter 10 The input shaft 30 is input via the turbine runner 10b, and the speed change mechanism 100 that performs a shift using the power from the input shaft 30 as an input and outputs it to the output gear 40.

  As shown in FIG. 1, the output gear 40 meshes with a first idler gear 51 attached to an idler shaft 50 disposed on the second axis O2, and the power input to the output gear 40 is idler shaft. 50 is transmitted to a differential gear mechanism 70 disposed on the third shaft by a final drive ring gear 60 which meshes with two sets of second idler gears 52 provided integrally with 50. The differential gear mechanism 70 distributes the power input from the final drive ring gear 60 to the two output shafts 71 and 72 and transmits the power to the wheels.

  As shown in FIG. 2, the speed change mechanism unit 100 inputs the power transmitted to the input shaft 30 to the single type planetary gear mechanism 110 to perform the first speed change, and then outputs the output to the first wet multi-plate clutch. (Low clutch) 130, input to Ravigneaux type planetary gear mechanism 120 via second wet multi-plate clutch (3-speed / 5-speed reverse clutch) 140 and first wet multi-plate brake (2-speed / 6-speed brake) 150 Then, the power input to the Ravigneaux type planetary gear mechanism 120 is operated by operating the third wet multi-plate clutch (high clutch) 160, the second wet multi-plate brake (low and reverse brake) 170, and the one-way clutch OWC. And output to the output gear 40.

  As shown in FIG. 2, the single type planetary gear mechanism 110 has a carrier 113 between a ring gear 111 integrally attached to the input shaft 30 via an intermediate member 32 and a sun gear 112 fixed to the transmission case 2. A pinion 115 rotatably supported by the provided pinion shaft 114 is disposed, and the carrier 113 is drivingly coupled to the ring gear 111 via the pinion 115. Thereby, the single type planetary gear mechanism 110 enables power transmission between the ring gear 111 and the carrier 113, shifts the power input from the input shaft 30 via the ring gear 111, and outputs it from the carrier 113. To do.

  As shown in FIG. 2, the Ravigneaux type planetary gear mechanism 120 has two sets of pinions 125 a and 125 b rotatably supported by a carrier 124 between two sun gears 121 and 122 having different large and small diameters and one ring gear 123. The small-diameter sun gear 121 is drivingly coupled to the ring gear 123 via the two pairs of pinions 125a and 125b, while the large-diameter sun gear 122 is also drivingly coupled to the ring gear 123 via the pinion 125a. In this case, one of the carriers 124 is coupled to the transmission case 2 c via the one-way clutch OWC and the low and reverse brake 170, and the other is drivingly coupled to the input shaft 30 via the high clutch 160. Is coupled to the output gear 40 via the parking gear Gp. Thus, the Ravigneaux type planetary gear mechanism 120 enables power transmission between the individual sun gears 121 and 122 and the ring gear 123, and the power input from the small diameter sun gear 121 or the large diameter sun gear 122 is high clutched. 160 and the low and reverse brake 170 are output from the ring gear 123 by shifting according to the engagement / release.

  The low clutch 130 is disposed adjacent to the single type planetary gear mechanism 110 as shown in FIGS. 2 and 3. The low clutch 130 is coupled to the carrier 113 of the single type planetary gear mechanism 110 and the Ravigneaux type. A piston 133 is slidably housed in the rotary drum 131 to slidably engage or release the clutch plates P1 and P2 which are friction members provided on the rotary hub 132 coupled to the small-diameter sun gear 121 of the planetary gear mechanism 120. A hydraulic chamber R1 for operation is formed, and a centrifugal canceller 134 is provided on the inner periphery of the rotary drum 131.

  The centrifugal canceller 134 includes a seal member 136a that holds the return spring 135 interposed between the piston 133 and the inner periphery of the piston 133. The seal member 136a allows the piston 133 and the rotating drum to be sealed. Together with 131, a centrifugal cancel chamber Rc1 is defined. The centrifugal cancel chamber Rc1 is for stabilizing the piston operation by stabilizing the centrifugal hydraulic pressure acting on the piston 133 from the side facing the piston operating hydraulic chamber R1.

  The relationship between the engagement states of the first to third clutches, the first and second brakes, and the operating states of the one-way clutch, which are shift elements, and the individual shift speeds are as shown in the operation diagram of FIG. . However, in FIG. 4, the low clutch 130, the third speed, the fifth speed, the reverse clutch 140, and the high clutch 160 are indicated by the symbols C1, C2, and C3, respectively, while the second speed and the sixth speed brake 150 and the low and reverse brake 170 are respectively indicated. The symbols B1 and B2 indicate that the clutch or brake is engaged at the gear position.

  By the way, in such a forward 6-speed automatic transmission, as shown in FIG. 3, an oil passage 31 through which oil flows is formed inside the input shaft 30, and the oil in the oil passage 31 is rotated by the rotation of the input shaft 30. Utilizing the generated centrifugal force, it is supplied as working oil or lubricating oil to various places around the input shaft 30 through the discharge hole 31h. Among these, the pinion shaft 114 and the pinion 115 of the single type planetary gear mechanism 110 are one of the parts that need to be lubricated, and therefore an oil passage 116 through which oil flows is formed inside the pinion shaft 114.

  In the present embodiment, the carrier 113 of the single type planetary gear mechanism 110 is fixed to the inner peripheral portion of the rotating drum 131 so as to face the centrifugal canceller 134 via the partition plate 137, and therefore, between the carrier 113 and the centrifugal canceller 134. The oil discharged from the oil passage 31 of the input shaft 30 is supplied to the oil passage 116 formed in the pinion shaft 114 using the gap ΔC formed in the above.

  For this reason, in this embodiment, the oil passage structure of the automatic transmission is configured by incorporating the following configuration. That is, as shown in FIG. 3, the centrifugal canceller 134 of the present embodiment is integrally provided with a seal member 136b on the side surface facing the carrier 113, and the seal member 136b seals the gap ΔC by contact with the carrier 113, thereby liquid chamber. Is defined. The seal member 136b is made of a synthetic resin such as synthetic rubber. In this embodiment, the seal member 136b is molded integrally with a seal member 136a that defines a centrifugal cancel chamber Rc1 between the inner peripheral portion of the piston 133 and the centrifugal canceller 134. However, the seal member 136b may be formed separately from the existing seal member 136a.

  According to this oil passage structure, the oil flowing through the oil passage 31 in the input shaft 30 is discharged from the discharge hole 31h of the input shaft 30 by the rotation of the input shaft 30, and then provided on the inner peripheral portion of the rotating drum 131a. It is introduced into the gap ΔC formed between the carrier 113 and the centrifugal canceller 134 through the through-hole 131h and the through-hole 134h provided in the centrifugal canceller 134. At this time, since the seal member 136b provided integrally with the centrifugal canceller 134 is in contact with the carrier 113 to define a liquid chamber, the gap ΔC is almost completely lost in the oil introduced into the liquid chamber. The oil is discharged as lubricating oil between the pinion shaft 114 and the pinion 115 through an oil passage 116 formed in the pinion shaft 114.

  That is, in the oil passage structure of the present embodiment, since the seal member 136b that contacts the carrier 113 is integrally provided on the side surface of the centrifugal canceller 134 that faces the carrier 113, a separate oil is provided as in the prior art shown in FIG. Compared with the case where the catch plate P is attached, the axial dimension of the entire forward 6-speed automatic transmission can be reduced, and at the same time, the number of parts can be reduced. Moreover, in the present embodiment, the seal member 136b provided on the centrifugal canceller 134 contacts the carrier 113 to seal the gap ΔC formed between the carrier 113 and the centrifugal canceller 134. Therefore, the fluid in the gap ΔC is transferred to the pinion shaft 114. Can be efficiently introduced into the liquid passage 116 formed in the above.

  Therefore, according to the present embodiment, the axial dimension and the number of parts of the entire forward 6-speed automatic transmission are not increased, and the clearance ΔC formed between the carrier 113 and the centrifugal canceller 134 of the single type planetary gear mechanism 110 is not increased. This oil can be efficiently introduced into the liquid passage 116 formed in the pinion shaft 114. In this embodiment, since the seal member 136b is integrally provided on the side surface of the centrifugal canceller 134 that does not need to be assembled with other members, it is easy to provide the seal member 136b integrally with the centrifugal canceller 134. There are advantages.

  In the present embodiment, the carrier 113 of the single type planetary gear mechanism 110 and the rotating drum 131 of the low clutch 130 are coupled together, so that relative rotation between the carrier 113 and the centrifugal canceller 134 does not occur. Therefore, according to the present embodiment, the seal between the centrifugal canceller 134 and the carrier 113 is sealed by the seal member 136b provided in the centrifugal canceller 134 regardless of the state of power transmission between the single type planetary gear mechanism 110 and the low clutch 130. Can always be secured. The carrier 113 of the single type planetary gear mechanism 110 and the rotating drum 131 of the low clutch 130 are not coupled together as in the present embodiment, but are provided with gear portions, and the gear portions mesh with each other to drive-couple. You may do.

  Further, in the present embodiment, the seal member 136b provided on the centrifugal canceller 134 is formed integrally with the seal member 136a that defines the centrifugal cancel chamber Rc1 between the inner peripheral portion of the piston 133 and the centrifugal canceller 134. Further, the space between the seal members 136b is more firmly fixed. Therefore, according to the present embodiment, high-pressure oil can be supplied into the gap formed between the carrier 113 and the centrifugal canceller 134, so that the gap ΔC formed between the carrier 113 and the centrifugal canceller 134 can be used in the pinion shaft 114. The oil can be more efficiently introduced into the liquid passage 116 formed in the above.

  In the oil passage structure of the automatic transmission according to the present invention, the carrier 113 of the single type planetary gear mechanism 110 seals the gap ΔC by the contact with the centrifugal canceller 134 on the side facing the centrifugal canceller 134 of the low clutch 130, and the liquid chamber. A seal member that defines

  In this case as well, a separate oil catch plate P (see FIG. 5) is attached to the side surface of the carrier 113 of the single type planetary gear mechanism 110 facing the centrifugal canceller 134 so as to be integrally provided with the sealing member. Compared to the case, the axial dimension of the entire forward 6-speed automatic transmission can be shortened, and at the same time, the number of parts can be reduced. Moreover, in this embodiment, the seal member provided on the carrier 113 of the single type planetary gear mechanism 110 contacts the centrifugal canceller 134 and seals the gap ΔC formed between the carrier 113 and the centrifugal canceller 134. Oil can be efficiently introduced into the liquid passage 116 formed in the pinion shaft 114.

  Accordingly, even in such a configuration, the axial dimension and the number of parts of the entire forward 6-speed automatic transmission are not increased, and the clearance ΔC formed between the carrier 113 and the centrifugal canceller 134 of the single type planetary gear mechanism 110 is not increased. Oil can be efficiently introduced into the liquid passage 116 formed in the pinion shaft 114.

  Further, in this configuration, the carrier 113 and the rotating drum 131 may be integrally coupled. In this case as well, relative rotation between the carrier 113 and the rotating drum 131 does not occur as in the previous embodiment. Therefore, regardless of the state of power transmission between the single type planetary gear mechanism 110 and the low clutch 130, the sealing performance between the centrifugal canceller 134 and the carrier 113 can always be ensured by the seal member provided on the carrier 113.

  The above description is only a preferred embodiment of the present invention, and various modifications can be made by those skilled in the art within the scope of the claims. For example, the power input to the input shaft 30 is not limited to that of the engine as the driving source, but may be of a so-called hybrid type in which the driving source is an electric motor or the driving source is an engine and an electric motor. Good. Further, the method of supplying oil to the gap ΔC formed between the carrier 113 of the planetary gear mechanism 110 and the centrifugal canceller 134 of the low clutch 130 is not limited to the method of discharging oil from the oil passage 31 in the input shaft 30, and an oil pump There is no limitation on the type such as a method of direct introduction from a hydraulic power source such as 20.

  Further, the present invention does not limit the planetary gear mechanism disposed adjacent to the wet multi-plate clutch to a single type planetary gear mechanism. For example, in the case of FIG. 5 illustrated as the prior art, that is, the Ravigneaux type planetary gear mechanism 210 and The present invention can also be applied to the case where a fluid such as oil is introduced into the gap ΔCo generated by arranging the wet multi-plate clutch 220 adjacent to each other.

It is sectional drawing which shows the power train carrying the forward 6-speed automatic transmission provided with the oil path structure which is the 1st Embodiment of this invention. FIG. 2 is a skeleton diagram of an automatic transmission according to the present invention disposed on a first axis O1 shown in FIG. 1. It is an expanded sectional view which shows the principal part of the forward 6-speed automatic transmission which concerns on this invention. FIG. 5 is an operation diagram showing the relationship between the engagement states of the first to third clutches, the first and second brakes, the operating state of the one-way clutch, and individual shift speeds in the embodiment. It is principal part sectional drawing which illustrates the forward 6-speed automatic transmission provided with the conventional oil path structure.

Explanation of symbols

1 Powertrain 2a, 2b, 2c Transmission case 10 Lock-up torque converter 10a Pump impeller 10b Turbine runner 20 Oil pump 30 Input shaft 31 Oil passage 31h Discharge hole 32 Intermediate member 40 Output gear 50 Idler shaft 51 First idler gear 52 Second idler gear 60 Final drive ring gear 70 Differential gear mechanism 71, 72 Output shaft 100 Transmission mechanism 110 Single type planetary gear mechanism 111 Ring gear 112 Sun gear 113 Carrier 114 Pinion shaft 115 Pinion 116 Oil passage 120 Ravigneaux type planetary gear mechanism 121 Small diameter sun gear 122 large-diameter sun gear 123 ring gear 124 carrier 125a, 125b pinion 130 first wet multi-plate Pitch (low clutch)
131 Rotating drum 131h Through hole 132 Rotating hub 133 Piston 134 Centrifugal canceller 134h Through hole 135 Return spring 136a Seal member 136b Seal member 137 Partition plate 140 Second wet multi-plate clutch (3-speed, 5-speed, reverse clutch)
150 1st wet multi-plate brake (2-speed / 6-speed brake)
160 Third wet multi-plate clutch 170 Second wet multi-plate brake (low and reverse brake)
ΔC Clearance OWC One-way clutch Gp Parking gear O1, O2, O3 Axis P1, P2 Clutch plate R1 Piston hydraulic chamber Rc1 Centrifugal cancel chamber

Claims (2)

A planetary gear mechanism that rotatably supports a pinion disposed between the sun gear and the ring gear by a pinion shaft provided on the carrier, and a piston that fastens or releases the friction member provided on the rotating drum and the rotating hub are provided inside the rotating drum. The piston operating hydraulic chamber is formed between the piston and the rotary drum by being slidably housed in the piston, while the piston operating hydraulic chamber is opposed to the piston operating hydraulic chamber. A wet multi-plate clutch provided with a centrifugal canceller for defining a centrifugal canceling hydraulic pressure between the piston and a hydraulic pressure generated in the piston operating hydraulic pressure chamber at an inner peripheral portion of the rotating drum; And
The wet multi-plate clutch and the planetary gear mechanism are disposed adjacent to each other so that the carrier and the centrifugal canceller face each other, and a gap is formed between the carrier and the centrifugal canceller, and the pinion shaft is formed using the gap. In the liquid passage structure of the automatic transmission that supplies fluid to the liquid passage formed inside,
A seal member that seals the gap between the centrifugal canceller and the carrier and defines a liquid chamber between a side surface of the centrifugal canceller and a side surface of the carrier;
The seal member is formed integrally with a seal member that defines a centrifugal cancel chamber between the inner peripheral portion of the piston and the centrifugal canceller by contact with the inner peripheral portion of the piston. Liquid passage structure of automatic transmission. 2. The liquid passage structure of an automatic transmission according to claim 1, wherein the centrifugal canceller has a through hole for supplying a fluid to the liquid chamber.

Images