JP2004019770A - Oil feeder of continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent both bushes from being offset in the axial direction, in supporting a bearing boss part projected on a clutch hub of an output clutch fixed to a secondary output shaft and a shaft end part of a secondary output shaft to which the clutch hub is journaled on the inner wall surface of a transmission case through the bushes. <P>SOLUTION: The clutch hub 31 of the output clutch 13 is journaled slightly inward from the shaft end part of the secondary output shaft 9h, and the bearing boss part 31b projected from the clutch hub 31 is disposed in the direction of enlarged diameter of the secondary output shaft 9h. The shaft end part of the secondary output shaft 9h and the bearing boss part 31b are rotatably supported on the inner wall surface of the transmission case 9a through the bushes 24, 25. The bearing boss part 1b is increased in diameter, whereby even if both bushes 24, 25 are disposed on the same flat surface, they are prevented from interfering with each other, so that the transmission case 9a is reduced in the cross direction by that much to realize reduction of size of the apparatus body. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an oil supply device that supplies oil to a shaft of a continuously variable transmission in which clutch means is interposed between a secondary pulley shaft and a secondary output shaft.
[0002]
[Prior art]
Generally, as a continuously variable transmission mounted on a vehicle such as an automobile, a drive belt is provided between a primary pulley provided on an engine-side primary pulley shaft and a secondary pulley provided on a drive wheel-side secondary pulley shaft. A belt-driven continuously variable transmission in which the number of revolutions of a secondary pulley shaft is continuously changed by changing the diameter of each pulley by hydraulic pressure is used.
[0003]
Also, in this type of continuously variable transmission, as disclosed in, for example, JP-A-2000-220721 and JP-A-2001-124189, a clutch means is provided between a secondary pulley shaft and a reduction drive gear. At the time of mounting, sudden deceleration, or sudden stop, the clutch means is disengaged to reduce the load on the drive belt to prevent wear, and to enable shift control such as downshifting even while the vehicle is stopped. Techniques for doing so are known.
[0004]
In these belt-type continuously variable transmissions, a plurality of oil paths such as a hydraulic oil path to a pulley hydraulic chamber, a hydraulic oil path to a clutch, and a lubricating oil path are provided on a secondary pulley shaft. Hydraulic oil, lubricating oil, and the like corresponding to the oil passages are supplied from the transmission case side, which is a fixing member, via a shaft end and the like.
[0005]
[Problems to be solved by the invention]
However, in the above-described prior art, supply of hydraulic oil and the like to a clutch and a pulley hydraulic chamber provided on a secondary pulley shaft is performed by a plurality of oil supply units provided at shaft ends of the secondary pulley shaft. , And the plurality of oil supply units are arranged side by side in the axial direction. For this reason, the axial dimension of the oil supply unit is increased, and the axial dimension of the transmission case that supports the secondary pulley shaft is increased. Further, the configuration of the oil supply unit is also complicated.
[0006]
As shown in FIG. 4, the shaft end of the secondary output shaft 51 is supported on the inner wall of the transmission case 52 via a bush 53, and the secondary output shaft 51 rotatably supports the secondary pulley shaft 54. In a structure in which the clutch hub 55a of the clutch means 55 is spline-engaged with the shaft end of the secondary output shaft 51, while the clutch drum 55c is spline-engaged with the secondary pulley shaft 54, A secondary pressure based on a discharge pressure from an oil pump (not shown) flows through an oil passage 52a formed in the transmission case 52 into an oil passage 51b formed in the secondary output shaft 51 from an end of the shaft. Is done.
[0007]
On the other hand, for the clutch cylinder chamber 55b of the clutch means 55, the clutch pressure regulated by using the secondary pressure as the original pressure is supplied from the oil passage 52b formed in the transmission case 52 to the secondary output shaft 51 and the clutch hub 55a. Is supplied to the clutch cylinder chamber 55b provided in the clutch drum 55c that is spline-engaged with the secondary pulley shaft 54 through the spline missing tooth portion. The outer periphery of a boss 55d protruding outside the clutch hub 55a is rotatably supported by the transmission case 52 via a bush 56.
[0008]
In this case, since the clutch hub 55a is mounted on the outer periphery of the secondary output shaft 51, the outer shape of the bush 53 that supports the outer periphery of the secondary output shaft 51 is close to the inner diameter of the bush 56 that supports the clutch hub 55a. Therefore, in order to avoid mutual interference, it is necessary to dispose both bushes 53 and 56 in a state of being offset in the axial direction.
[0009]
As a result, the bush 53 supporting the secondary output shaft 51 has a shape protruding outward from the bush 56 supporting the boss 55d of the clutch hub 55a, and the width dimension of the transmission case 52 is accordingly increased. There is an inconvenience.
[0010]
The present invention has been made in view of the above circumstances, and a plurality of hydraulic oil passages provided on a fixed member such as a transmission case, and a plurality of hydraulic oil passages provided on the shaft side via a shaft end. It is an object of the present invention to provide an oil supply device of a continuously variable transmission that simplifies the configuration of an oil supply connection portion that connects the oil supply and the oil supply without increasing the axial dimension of the transmission.
[0011]
[Means for Solving the Problems]
In order to achieve the above object, an oil supply device for a continuously variable transmission according to the present invention includes a primary pulley connected to the engine side, a secondary pulley connected to the driving wheel side, and a drive belt wound between the two pulleys. A continuously variable transmission having a secondary output shaft rotatably mounted on the pulley shaft of the secondary pulley, a first clutch member rotatable integrally with the secondary output shaft, and an integral member with the secondary pulley shaft A clutch means having a rotatable second clutch member and a clutch part capable of connecting and disengaging the two clutch members, from the transmission case wall at the shaft end provided with the clutch means to the shaft side In the oil supply device for a continuously variable transmission that supplies oil, the shaft end of the secondary output shaft is rotatably supported on the inner wall surface of the transmission case via a first bush, and Expansion A bearing boss protruding from the first clutch member in the direction, and rotatably supporting the bearing boss on an inner wall surface of the transmission case via a second bush; A case-side oil passage is connected to an oil passage formed on the shaft side of the second bush portion.
[0012]
In such a configuration, a bearing boss protruding from the first clutch member that is rotatable integrally with the secondary output shaft is disposed in the radially enlarged direction of the shaft end of the secondary output shaft. The bearing and the bearing boss are rotatably supported on the inner wall surface of the transmission case via the first bush and the second bush, so that the bearing protrudingly provided on the secondary output shaft and the second clutch member. The boss can be arranged coaxially and on the same plane in the direction orthogonal to the axis, and the width of the transmission can be reduced accordingly.
[0013]
In this case, preferably, the oil supply device is arranged such that the first oil passage provided in the secondary output shaft and the second oil passage provided on the outer peripheral side of the secondary output shaft are arranged from the shaft end case side. It supplies oil, and the first and second bushes are seal members for the first and second oil passages.
[0014]
Still preferably, the first clutch member is a clutch hub, and the second clutch member is a clutch drum.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows an overall configuration diagram of the continuously variable transmission.
[0016]
Reference numeral 1 in the figure denotes an engine, and an output shaft 2 of the engine 1 is connected to a drive shaft 6 that supports a drive wheel 5 via a continuously variable transmission unit 3 and a final reduction unit 4 that constitute a continuously variable transmission. Have been. The continuously variable transmission unit 3 includes a torque converter 7, a forward / reverse switching device 8, and a continuously variable transmission 9 from the input side. The output shaft 2 of the engine 1 is connected to an impeller 7 a of the torque converter 7. A turbine 7 b of the torque converter 7 is connected to a planetary input shaft 8 a of the forward / reverse switching device 8.
[0017]
The forward / reverse switching device 8 incorporates a planetary gear 10 and is in a neutral state when both the forward clutch 11 and the reverse brake 12 are open. When only the forward clutch 11 is engaged, the planetary gear 10 rotates integrally, and the power from the turbine 7 b of the torque converter 7 is transmitted to the continuously variable transmission 9 as it is.
[0018]
On the other hand, when the forward clutch 11 is released and the reverse brake 12 is engaged, the power from the turbine 7 b of the torque converter 7 is transmitted to the continuously variable transmission 9 via the planetary gear 10 in a state where the power is reversed.
[0019]
A primary pulley 9c is axially mounted on a primary pulley shaft 9b of the continuously variable transmission 9, a secondary pulley 9d opposed to the primary pulley 9c is axially mounted on a secondary pulley shaft 9k, and is rotatable about a secondary output shaft 9h. A drive belt 9e made of metal is wound around the pulleys 9c and 9d. A primary pulley cylinder chamber 9f and a secondary pulley cylinder chamber 9g are provided on the movable sheave side of each of the pulleys 9c and 9d. The shift control is performed by setting the groove width of 9d in an inversely proportional state.
[0020]
A secondary pulley 9d is connected to a secondary output shaft 9h via an output clutch 13 which is an example of a clutch means, and the secondary output shaft 9h is driven via a reduction gear train 4a of the final reduction unit 4. It is connected to a differential device 4b mounted on the shaft 6.
[0021]
As shown in FIG. 2, an oil pan 15 provided at the bottom of the continuously variable transmission unit 3 is provided with a control valve unit 16 that controls operating oil pressure required for speed ratio control and transmission torque control of the continuously variable transmission unit 3. An oil pump 17 is fixed to the control valve unit 16. A driven sprocket 18 is mounted on the input shaft 17a of the oil pump 17, and the driven sprocket 18 is disposed between the planetary gear 10 and the torque The drive sprocket 20 is connected to the impeller 7a.
[0022]
As shown in FIG. 3, a secondary output shaft 9h is provided on a secondary pulley 9d. A secondary output shaft 9k is provided on an inner wall of a transmission case 9a. Two types of bearing holes 21 and 22 are formed on the same surface concentrically around the axis of the shaft 9h, and the first and second bearing holes 21 and 22 are formed on the inner periphery of each of the bearing holes 21 and 22. Bushes 24 and 25 are press-fitted.
[0023]
Further, the shaft end of the secondary output shaft 9h is rotatably supported by the small diameter bearing hole 21 via the first bush 24.
[0024]
As shown in FIG. 3, the output clutch 13 interposed in the power transmission system between the secondary output shaft 9h and the secondary pulley shaft 9k includes a clutch hub 31 as a first clutch member and a second clutch A clutch drum 32 is provided as a member, and a clutch plate 33 is provided so as to be able to freely connect and disconnect between the clutch hub 31 and the clutch drum 32.
[0025]
The shaft end of the secondary pulley shaft 9k is slightly retracted in the axial direction with respect to the shaft end of the secondary output shaft 9h. A gap portion 14 is formed between the gap portions, and the clutch output side shaft portion 31a of the clutch hub 31 is inserted into the gap portion 14. Further, the inner periphery of the clutch output side shaft portion 31a is spline-engaged with the secondary output shaft 9h, and the outer periphery of the clutch output side shaft portion 31a is provided with a third bush 34 on the inner periphery of the secondary pulley shaft 9k. It is supported rotatably through the.
[0026]
The clutch hub 31 is fixed at a position where it is slightly inserted in the axial direction with respect to the shaft end of the secondary output shaft 9h. A bearing boss 31b is provided on the outer surface of the clutch hub 31 at a position spaced apart from the shaft end of the secondary output shaft 9h by a predetermined distance in the radially expanding direction of the secondary output shaft 9h. The end surface of the bearing boss 31b and the end surface of the secondary output shaft 9h are set to be substantially the same. The outer periphery of the bearing boss 31b is rotatably supported via a second bush 25 in a large-diameter bearing hole 22 formed in the inner wall of the transmission case 9a.
[0027]
Further, the clutch input side shaft portion 32a of the clutch drum 32 is spline-engaged with the outer periphery of the secondary pulley shaft 9k, and the inner surface of the clutch drum 32 and the back surface of the clutch piston 35 which presses the clutch plate portion 33. A clutch cylinder chamber 36 is formed.
[0028]
In addition, a seal is formed between the shaft end of the secondary output shaft 9h and the inner circumference of the first bush 24, and between the outer circumference of the bearing boss 31b of the clutch hub 31 and the inner circumference of the second bush 25. Sealed via members 37 and 38, respectively.
[0029]
On the other hand, the transmission case 9a is formed with a pulley cylinder oil passage 41 and a clutch oil passage 42 for passing the secondary pressure generated by the control valve unit 16 and the clutch pressure generated by reducing the secondary pressure. I have. Further, the pulley cylinder oil passage 41 communicates with a secondary oil passage 9j formed in the secondary output shaft 9h through a discharge port 41a opened in the bearing hole 21. Further, the secondary oil passage 9j is communicated with a secondary pulley cylinder chamber 9g (see FIG. 1) for variably controlling the groove width of the secondary pulley 9d.
[0030]
Further, a clutch oil passage 42 is provided between the inner wall of the transmission case 9a and the wall surface of the bearing boss portion 31b protruding from the clutch hub 31 via a discharge port 42a opening to the large-diameter bearing hole 22. From the oil passage 47 formed in the clutch hub 31 through the inner diameter spline portion 31c of the clutch output side shaft portion 31a and the toothless portion and the spline shaft of the secondary output shaft 9h. . Further, an oil port 43 formed in the secondary pulley shaft 9k at a deep portion of the gap portion 14 and an oil groove 44 communicated with the oil port 43 and formed around the secondary pulley shaft 9k. The clutch drum 32 communicates with the clutch cylinder chamber 36 through an oil port 45 formed in the clutch input shaft 32a of the clutch drum 32. Note that both sides of the oil groove 44 in the axial direction are sealed by seal members 46.
[0031]
Next, the operation of the continuously variable transmission having such a configuration will be described. When the engine 1 is driven, the drive sprocket 20 connected to the impeller 7 a of the torque converter 7 rotates, and the rotational force is transmitted to the driven sprocket 18 via the chain 19.
[0032]
The driven sprocket 18 is mounted on an input shaft 17 a of an oil pump 17. The rotation of the driven sprocket 18 drives the oil pump 17, so that the oil stored in the oil pan 15 is sucked up and the control valve unit 16.
[0033]
The control valve unit 16 uses the discharge pressure from the oil pump 17 as an original pressure, generates a secondary pressure according to the gear ratio and the engine torque, and reduces the secondary pressure to a preset value according to the operating conditions. The primary pressure is generated according to the current shift pattern. Further, a low clutch pressure is generated using the secondary pressure as an original pressure.
[0034]
The secondary pressure passes through a pulley cylinder oil passage 41 formed in the transmission case 9a, a secondary oil passage 9j drilled from the discharge port 41a to the secondary output shaft 9h, and a secondary pressure provided on the secondary pulley 9d. The belt is supplied to the pulley cylinder chamber 9g and applies a belt clamping force necessary for torque transmission to the secondary pulley 9d. The primary pressure is supplied to a primary pulley cylinder chamber 9f of the primary pulley 9c through a primary oil passage (not shown), thereby setting a pulley ratio (speed change ratio) between the two pulleys 9c and 9d, and setting the low to over. Continuous gear ratio control up to the drive is performed.
[0035]
On the other hand, the clutch pressure supplied to the output clutch 13 passes through a clutch oil passage 42 formed in the transmission case 9a and from a discharge port 42a opened in the large-diameter bearing hole 22 to the transmission case 9a. The oil passes through an oil passage 47 formed between the inner wall and the outer wall of the clutch hub 31, and passes between the inner diameter spline groove or the toothless portion of the clutch output shaft 31 a of the clutch hub 31 and the outer periphery of the secondary output shaft 9 h. It reaches the deep part of the cavity 14.
[0036]
The clutch cylinder chamber passes through an oil port 43 formed in the secondary pulley shaft 9k from a deep portion of the gap portion 14 and further passes through an oil port 45 formed in the clutch input side shaft portion 32a of the clutch drum 32. 36.
[0037]
Then, the clutch piston 35 is pressed by the clutch oil pressure supplied to the clutch cylinder chamber 36, pressing the clutch plate 33, and the clutch drum 32 and the clutch hub 31 are connected.
[0038]
As a result, the rotational force of the secondary pulley 9d is transmitted to the secondary output shaft 9h via the output clutch 13 and is decelerated from the secondary output shaft 9h by the final deceleration unit 4 to a predetermined value. Thus, the rotational force is transmitted to the drive wheels 5.
[0039]
On the other hand, at the time of a sudden stop such as a sudden brake, the clutch pressure is drained to open the clutch plate portion 33. Then, the power transmission between the secondary pulley 9d and the secondary output shaft 9h is cut off, so that no reverse load is applied to the drive belt 9e from the drive wheel 5 side, thereby preventing the drive belt 9e from being damaged. be able to. Further, by performing the opening operation of the clutch plate portion 33 of the output clutch 13 at the time of a sudden stop, downshift control of the continuously variable transmission 9 becomes possible, and good restartability can be obtained.
[0040]
In the present embodiment, the supply of hydraulic oil to the secondary pulley cylinder chamber 9g from the shaft end of the secondary output shaft 9h and the supply of hydraulic oil to the clutch cylinder chamber 36 are formed outside the clutch hub 31. Since the diameter of the bearing boss 31b is larger than that of the conventional boss 55d shown in FIG. 4, the end face of the bearing boss 31b and the end face of the secondary output shaft 9h are arranged on the same plane. In addition, the bearing boss 31b and the shaft end of the secondary output shaft 9h are rotatably mounted on the inner wall surface of the transmission case 9a via the first and second bushes 24 and 25 without interfering with each other. Thus, the width of the transmission case 9a can be reduced by reducing the length of the secondary output shaft 9h, and the overall size of the apparatus can be reduced.
[0041]
Further, at this time, the first and second bushings 24 and 25 have a sealing function, and different hydraulic oils can be reliably supplied so that the bearing boss 31b has a large diameter. Can be rotatably supported in a stable posture.
[0042]
Also, since the diameter of the bearing boss 31b is larger than that of the conventional boss 55d shown in FIG. 4, the oil passage 47 can be secured between the inner wall of the transmission case 9a and the outer wall of the clutch hub 31. Accordingly, the flowability of the clutch pressure is improved, and the response is improved.
[0043]
The present invention is not limited to the above-described embodiment. For example, the output clutch 13 is configured such that the clutch hub 31 is connected to the secondary pulley shaft 9k and the clutch drum 32 is connected to the secondary output shaft 9h. Is also good. In this case, since the directions of the clutch hub 31 and the clutch drum 32 are reversed, the bearing boss portion 31 b protrudes from the outer surface of the clutch drum 32.
[0044]
Also, it goes without saying that the technology disclosed in the present invention can be applied to a continuously variable transmission that employs an output clutch as a so-called starting clutch.
[0045]
【The invention's effect】
As described above, according to the present invention, a plurality of hydraulic oil passages provided on a fixed member such as a transmission case and a plurality of hydraulic oil passages provided on a shaft side are connected via a shaft end. The structure of the oil supply connecting portion can be simplified, and oil can be supplied without increasing the axial dimension of the transmission.
[Brief description of the drawings]
FIG. 1 is an overall configuration diagram of a continuously variable transmission. FIG. 2 is a configuration diagram showing a main part of an oil supply device of the continuously variable transmission. FIG. 3 is an enlarged sectional view of an output clutch. FIG. Enlarged sectional view [Explanation of symbols]
Reference Signs List 1 engine 5 drive wheel 9 continuously variable transmission 9a transmission case 9c primary pulley 9d secondary pulley 9e drive belt 9h secondary output shaft 9k secondary pulley shaft 13 output clutch (clutch means)
24 first bush 25 second bush 31 clutch hub (first clutch member)
31b Bearing boss 32 Clutch drum (second clutch member)
33 Clutch plate part (clutch part)

Claims (3)

A primary pulley connected to the engine side, a secondary pulley connected to the drive wheel side, a drive belt wound between the two pulleys, and a secondary output shaft rotatably mounted on the pulley shaft of the secondary pulley. Continuously variable transmission, a first clutch member rotatable integrally with the secondary output shaft, a second clutch member rotatable integrally with the secondary pulley shaft, and both clutch members capable of being connected to and separated from each other. Clutch means having a simple clutch portion,
With
An oil supply device for a continuously variable transmission that supplies oil to the shaft side from a shaft-side transmission case wall provided with the clutch means,
A shaft end of the secondary output shaft is rotatably supported on an inner wall surface of the transmission case via a first bush,
A bearing boss protruding from the first clutch member is disposed in a radially expanding direction of the first bush;
The bearing boss is rotatably supported on the inner wall surface of the transmission case via a second bush,
An oil supply device for a continuously variable transmission, wherein a case-side oil passage is communicated with an oil passage formed on the shaft side of the first and second bush portions. The oil supply device supplies oil to a first oil passage provided in a secondary output shaft and a second oil passage provided on an outer peripheral side of the secondary output shaft from a shaft end case side. The oil supply device for a continuously variable transmission according to claim 1, wherein the first and second bushes are seal members for the first and second oil passages. 3. The oil supply device for a continuously variable transmission according to claim 1, wherein the first clutch member is a clutch hub, and the second clutch member is a clutch drum.

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