JPH02134450A - Lubrication device of continuous variable transmission with belt - Google Patents

Abstract

PURPOSE:To eliminate shortage of lubrication by supplying preloaded lubricant to a bearing, which supports a secondary side rotary shaft situated between a belt type continuous transmission and a sub-transmission wherein the preloaded lubricant is fed from a lubricant path provided in a support wall of a housing. CONSTITUTION:One end of an output shaft 34, which transmits the output torque from a belt type continuous transmission over to a sub-transmission 14, is borne by a bearing 126 furnished in No.2 case (support wall) 74b. This No.2 case 74b is equipped with an oil path 162, which supplies the working oil pressure to a hydraulic actuator of a forward motion clutch 72 while passing through the gap between the outside surface of a sleeve 158 and the inside surface of a through hole 156, and also with a lubricant path 164 leading to a spline shaft part 148. Part of the lubricant supplied to the bore of this sleeve 158 shall pass through the fit gap between the output shaft 34 and sleeve 158 to be supplied forcedly to the bearing 126, which supports the output shaft 34 in a place close to the acting point of transmission belt. This eliminates shortage of lubrication.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a lubricating device for a vehicle power transmission device equipped with a belt-type continuously variable transmission and an auxiliary transmission, and particularly to a lubricating device for a vehicle power transmission device equipped with a belt-type continuously variable transmission and an auxiliary transmission. This relates to technology for lubricating bearings in locations where it is difficult to lubricate.

Conventional technology In vehicle power transmission devices that shift and transmit power from a drive source such as an engine to a desired gear ratio, there is a main transmission that exclusively changes gears over a wide range, and a main transmission that exclusively switches the direction of rotation. It is generally configured in combination with an auxiliary transmission (also called a forward/reverse switching device). As one type of such system, various power transmission devices for vehicles have been developed in which a belt-type continuously variable transmission is used as the main transmission, and a forward/reverse switching device having a planetary gear unit and a direct-coupled flange is used as the auxiliary transmission. JP-A No. 60-252857
No. 61-130656, etc.

In such a vehicle power transmission device, in order to smoothly and quietly shift and transmit power, and to ensure the durability of the device, bearings that support the respective rotating shafts that make up the main and sub-transmissions are used. It is desirable to have sufficient lubrication.

Problems to be Solved by the Invention However, even if all the bearing parts in the transmission are sufficiently lubricated as described above, the bearing itself is inevitably located close to the center of the rotating shaft, and the power transmission In the case of a bearing that is located relatively high in a device and is subjected to a relatively high load, there is a problem that it tends to suffer from insufficient lubrication.

For example, in a vehicle power transmission system in which a forward/reverse switching device is connected to a belt-type continuously variable transmission,
Due to the configuration of the power transmission device, the secondary rotating shaft of the belt-type continuously variable transmission is necessarily located in the middle upper part of the power transmission device, so lubrication is provided by stirring the oil collected at the bottom of the device. I hardly expected it.

The present invention has been made against the background of the above circumstances,
The object is to provide a lubricating device for a belt-type continuously variable transmission that can lubricate bearings in locations where high loads are applied and where it is difficult to supply lubricating oil.

Means for Solving the Problems The gist of the present invention for achieving the object is as follows: (a) a rotatably supported primary rotating shaft and a secondary rotating shaft; and the primary rotating shaft. and a primary variable pulley and a secondary variable pulley provided on the secondary rotating shaft, each having a variable groove width, and a power transmission belt wound around the primary variable pulley and the secondary variable pulley. (b) a sub-transmission connected to the shaft end of the secondary rotating shaft; (C) the belt-type continuously variable transmission; (d) a support wall of a housing that is located between the machine and the sub-transmission and supports the secondary rotating shaft via a bearing; This is because a lubricating oil path is provided to supply the bearings.

Operation and Effects of the Invention With this arrangement, lubricating oil is forcibly supplied to the bearing from the lubricating oil passage provided in the support wall of the housing that supports the secondary rotating shaft via the bearing. Therefore, insufficient lubrication of the bearing can be prevented. This solves the problem that the bearings in the belt-type continuously variable transmission, which are located relatively high in the power transmission device and are subject to a relatively high load, tend to lack lubrication.

EXAMPLE Hereinafter, an example of the present invention will be described in detail based on the drawings.

FIG. 1 is a schematic diagram showing a power transmission device for a vehicle equipped with a lubricating device according to an embodiment of the present invention. This power transmission device is installed in a transverse transaxle of a front-wheel drive vehicle. In the figure, the power of the engine 8 is transmitted through a fluid coupling 10 with a lock-up clutch, a belt type continuously variable transmission (hereinafter referred to as CVT) 12, an auxiliary transmission (forward/reverse switching device) 14, a reduction gear device 16, and a differential transmission. The signal is transmitted through a gear device 18 to a drive wheel 21 connected to a drive shaft 20.

The fluid coupling 10 connects a pump impeller 24 connected to the crankshaft 22 of the engine 8, a turbine impeller 28 fixed to the input shaft 26 of the CVT 12 and rotated by oil from the pump impeller 24, and a damper 30. input shaft 2 through
6 and a lock-up clutch 32 fixed to the lock-up clutch 32. The lock-up clutch 32 is activated when, for example, the vehicle speed, the engine rotational speed, or the rotational speed of the turbine wheel 28 exceeds a predetermined value, and connects the crankshaft 22 and the input shaft 26 directly.

The CVT 12 includes variable pulleys 36 and 38 provided on the input shaft 26 and output shaft 34, respectively, and a transmission belt 40 wound around the variable pulleys 36 and 38. The variable pulleys 36 and 38 are connected to the input shaft 2
6 and the fixed rotating body 4 fixed to the output shaft 34, respectively.
2 and 44, and movable rotary bodies 46 and 48, which are provided on the input shaft 26 and the output shaft 34, respectively, so as to be movable in the axial direction but not relatively rotatable about the axes. By being moved by the functioning hydraulic cylinders 50 and 52, the groove width, that is, the hanging diameter (effective diameter) of the transmission belt 40 is changed, and the transmission ratio T of the CVT 12 (-human power shaft 2) is changed.
6 rotational speed N, fi/output shaft 34 rotational speed N0. )
is about to change. Therefore, in this embodiment, the input shaft 26 and the output shaft 34 correspond to the primary rotation shaft and the secondary rotation shaft, respectively. The hydraulic cylinder 50 is of a so-called double piston type and is operated exclusively to change the gear ratio T.
is operated so as to obtain the minimum clamping force within a range where the transmission belt 40 does not slip.

The hydraulic pump 54 constitutes a hydraulic power source of a CVT hydraulic control device (not shown), and is constantly driven to rotate by a pump impeller 24 that rotates together with the engine 8. Examples of the above C■T hydraulic control device include JP-A-62-9055 and JP-A-62-196.
The CVT 12 and the auxiliary transmission 14 are controlled by using all or part of those described in No. 445 and Japanese Patent Application Laid-Open No. 1-49749.

The auxiliary transmission 14 is a double pinion type planetary gear device connected in series to the rear stage of the CVT 12 and selectively switched to a forward gear or a reverse gear according to the operating position of a shift lever (not shown). It is provided coaxially with the output shaft 34. This planetary gear device is
A sun gear 56 provided integrally with the output shaft 34, a ring gear 58 provided concentrically with the sun gear 56, and a pair of planetary gears 60 and 62 that mesh with one and the other of the ring gear 58 and the sun gear 56 and mesh with each other. , a boss portion 64 provided concentrically with the sun gear 56 and ring gear 58, a flange portion 66 extending from the boss portion 64 toward the outer circumference, and a flange portion 66 protruding from the flange portion 66 in a direction parallel to the axis of the boss portion 64. Carrier pin 6 rotatably supports a pair of planetary gears 60 and 62
8, and a carrier 70 having a.

Further, this planetary gear device includes a forward clutch 72 that selectively connects between the fixed rotating body 44 of the secondary variable pulley 38 and the carrier 70, and a forward clutch 72 that selectively connects between the ring gear 58 and the housing 74 that is fixed in position. Reverse brake 7 connected to
6.

Therefore, when the forward clutch 72 is engaged, the fixed rotating body 44 and the carrier 70 are connected, and the output shaft 34 and the carrier 70 rotate integrally, so that they are concentric with the boss portion 64 of the carrier 70. A first gear 78 connected to
is rotated in the forward direction. Furthermore, when the reverse brake 76 is engaged, the housing 74 and the ring gear 58 are connected and the ring gear 58 is brought into a non-rotating state. and the first gear 78 is rotated. This first gear 78 functions as an output gear of the sub-transmission 14.

The second gear 80 and the third gear 82 are integrally connected via a common shaft, and are rotatably provided around an axis parallel to the axis of the first gear 78. 2nd gear 8
0 is meshed with the first gear 78, and the first gear 7
It has a larger diameter than 8.

The third gear 82 has a smaller diameter than the second gear 80 and is meshed with the large gear 84 of the differential gear device 18 . The first gear 78, the second gear 80, and the third gear 82 are
It functions as a reduction gear.

The differential gear device 18 includes a pair of differential small gears 86 that rotate integrally with the large gear 84 and a pair of differential large gears 88 that mesh with the differential small gears 86 and are connected to the drive shaft 20. We are prepared. Therefore, the power transmitted from the sub-transmission 14 is equally distributed to the left and right drive shafts 20 in the differential gear device 18, and then transmitted to the left and right drive wheels 21.

FIG. 2 is a diagram showing the power transmission device shown in the schematic diagram of FIG. 1 in more detail. In the figure, the housing 74 is, for example, an aluminum die-cast product,
First cases 74 integrally connected to each other by bolts
a, a second case 74b, and a third case 74c; the first chamber 9 accommodates the fluid coupling 10;
0, the second chamber 92 that accommodates the CVT 12, and the sub-transmission 1.
4, and a fourth chamber 96 that accommodates the reduction gear device 16 and the differential gear device 18. The bolt 9th shown in the figure is the first case 74a.
and the second case 74b are fixed.

The rotor 100 of the hydraulic pump 54 has a gear shape, and is fitted into the cylindrical portion of the pump impeller 24 in a relatively rotatable and eccentric manner. The hydraulic pump case 102 is
The rotor 100 has internal teeth that mesh with the rotor 100, and the first
It is fixed to the second case 74b with a bolt 104 while being fitted into a hole 103 formed in a portion corresponding to a partition wall between the first chamber 90 and the second chamber 92 of the case 74a.

An opening 106 is provided in a part of the second case 74b. An accumulator 110 is fixed by bolts 107 to a valve body 108 in which a control valve for controlling the forward clutch 72 and reverse brake 76 is incorporated, and the valve body 108 is attached to the opening edge of the opening 106 by bolts 112. By being fixed, the accumulator 110 is accommodated within the second chamber 92. The accumulator 110 includes a bottomed cylindrical main body 114, a piston 116 that is slidably fitted into the main body 114 to change the internal volume, and a spring 118 that biases the piston 116 in a direction to reduce the internal volume. We are prepared. A valve plate 109 for forming a hydraulic oil passage is fixed to one surface of the valve body 108 by bolts 111, and a cover 113 covering it is attached to the bolt 1.
12 and are collinearly fixed.

The accumulator 110 is connected to a hydraulic actuator that drives the forward clutch 72 or the reverse brake 76, and due to a change in internal volume, the accumulator 110 relieves the increase in the hydraulic pressure supplied by the control valve and locks the forward clutch 72 or the reverse brake 76. This is to make it smooth. As described above, since the accumulator 110 is configured separately from the second case 74b, the occurrence of holes in the second case 74b is suppressed, and the yield of the second case 74b or the accumulator 1100 is improved. Wasted meat on the back side of the bottom cylindrical main body 114 is removed. Further, since the accumulator 110 is constructed separately from the second case 74b, it is possible to check the performance of the accumulator 110 as a standalone unit while being removed from the second case 74b. moreover,
By being configured as a separate body as described above, the main body 114
The second case 7 can be easily drilled to fit the piston 116 therein, and the second case 7 corresponds to the drilling process.
One processing station of 4b becomes unnecessary.

The input shaft 26 of the CVT 12 has a bearing 120 fitted into the second case 74b and the third case 74c.
and 122, it is rotatably supported on the same axis as the crankshaft 22. Output shaft 3 of CVT12
4 is rotatably supported around an axis parallel to the input shaft 26 by a ball bearing 124 and a roller bearing 126 fitted in the third case 74c and the second case 74b, and a portion thereof is supported by the bearings. It extends into the sub-transmission 14 from the 126 side. Therefore, in this embodiment, this second case 7
4b corresponds to a support wall that supports the output shaft 34 via the bearing 126. Here, the bearing 12
As can be seen from the figure, the distance from the position of the transmission belt 40 in No. 6 is 1/3 to 1/3 compared to that of the bearing 124.
4, which is significantly smaller. Therefore, the load that the bearing 126 receives via the output shaft 34 due to the tension of the transmission belt 40 is extremely large, and it is placed under stricter conditions than other bearings in terms of performance as a bearing. Adequate lubrication is required.

On the other hand, the first case 74a includes a fourth case 7 for supporting the first gear 78, the second gear 80, and the third gear 82.
4d is fixed. This fourth case 74d also corresponds to a partition wall between the third chamber 94 and the fourth chamber 96. The shaft portion of the first gear 78 has bearings 128 and 13 fitted into the first case 74a and the fourth case 74d.
0, it is rotatably supported on the same axis as the output shaft 34, and a portion thereof extends into the sub-transmission 14 from the bearing 130 side. Further, the common shaft portion of the second gear 80 and the third gear 82 is also connected to the first gear 78 by bearings 132 and 134 fitted in the first case 74a and the fourth case 74d.
It is rotatably supported around an axis parallel to the The differential case 136, to which the large gear 84 is fixed and the pin that rotatably supports the differential small gear 86, is supported by bearings 138 and 140 fitted into the first case 74a and the second case 74b. Rotatably supported.

Note that a peripheral wall 14 is provided in the fourth chamber 96 of the first case 74a so as to surround a portion of the second gear 80 on the differential gear device 18 side.
4 are provided protrudingly, and a large gear 84, a third gear 82, a second gear
The lubricating oil scraped up from the bottom of the fourth chamber 96 as the gear 80 rotates is received by the peripheral wall 144, and a lubricating oil passage 146 is provided for guiding the lubricating oil to the bearing 138. As a result, the bearing 138 to which a high load is applied is suitably lubricated. Further, the second case 74b is provided with a lubricating oil passage 147 that receives the lubricating oil flowing down the inner wall surface of the fourth chamber 96 and guides it to the bearing 140. This allows the bearing 140 to be suitably lubricated.

FIG. 3 is a diagram showing the sub-transmission 14 and the reduction gear device 16 in detail. In the figure, the second case 74b is
The shaft end of the output shaft (i.e., the input shaft of the sub-transmission r4) 34 that penetrates into the chamber 94 side is formed to have a small diameter, and there is a spline shaft portion 148 having a plurality of spline teeth formed therein. It is provided. The cylinder body 150 and the cylindrical connecting member 152 provided in the forward clutch 72 are
The cylindrical connecting member 152 is integrally connected so as not to be relatively rotatable, and the cylindrical connecting member 152 is spline-fitted to the spline shaft portion 148. An annular piston 154 is slidably fitted into a cylinder body 150 having an annular cylinder bore while being biased by a return spring 155.
4. The return spring 155 etc. are the forward clutch 7.
It functions as a hydraulic actuator to operate 2.

The forward clutch 72 includes a plurality of plates 157 that are engaged with the outer periphery of the cylinder body 150, that is, the clutch drum, so as to be non-rotatable and movable in the axial direction.
The clutch hub 159 is fixed to a part of the carrier 70 and is engaged with the clutch hub 159 so as to be non-rotatable and movable in the axial direction. plate 15
7 and the disk 161 are pressed together by the piston 154, thereby transmitting power.

In order to pass the output shaft 34 to the third chamber 94 side, a second
A sleeve 158 is integrally fitted into a through hole 156 provided in a part of the case 74b, and a part of the cylindrical connecting member 152 is connected to the sleeve 158 and the second case 74b via a bearing 160. Supported. As a result, the output shaft 34 and the cylindrical connecting member 1
The spline fitting with 52 has a significantly larger clearance in the spline groove than normal spline fitting.

In addition, working hydraulic pressure is supplied to the second case 74b through a portion of the outer peripheral surface of the sleeve 158 and the inner peripheral surface of the through hole 156 to the pressure chamber formed by the cylinder body 150 and the piston 154. A forward oil passage 162 is formed for this purpose. Further, a lubricating oil passage 164 for forcibly supplying lubricating oil to the spline shaft portion 148 and the like is provided in the portion of the second case 74b where the through hole 156 is formed, and the sleeve 158 is provided with a lubricating oil passage 164 for forcibly supplying lubricating oil to the spline shaft portion 148 and the like. A through hole 166 forming a part of the lubricating oil passage 164 is provided. This lubricating oil passage 164 contains a portion of the hydraulic oil pumped by the hydraulic pump 54, for example, clutch pressure oil whose pressure is regulated in advance and is supplied to the fluid coupling 10 in order to operate the lock-up clutch 32. A portion of this will be supplied.

In the hydraulic actuator for operating the forward clutch 72, the piston 154 is supplied with hydraulic pressure to the pressure chamber and prevents hydraulic oil from flowing out when the pressure inside the pressure chamber is high. A check valve 168 is provided that allows the hydraulic oil to flow out when the pressure of the hydraulic oil in the pressure chamber is exhausted and becomes low, thereby improving the disengagement characteristics of the forward clutch 72.

In the spline shaft portion 148 of the output shaft 34, the sun gear 56 is also spline-fitted adjacent to the cylindrical connecting member 152. A cylindrical projection 170 is provided on the sun gear 56 side of this cylindrical connection member 152, and a cylindrical projection 172 is also provided on the cylindrical connection member 152 side of the sun gear 56.
and 172 are fitted in a relatively rotatable and fluid-tight manner.

As a result, the sun gear 56 is supported by the clutch case 74b via the bearing 160 in the same manner as the cylindrical connecting member 152, and the clearance is significantly increased when the spline fitting is used as compared to the normal spline fitting. ing. Additionally, since the sun gear 56 can be positioned (centered) even before the output shaft 34 is inserted in the assembly process, assembly is facilitated.

As described above and above, in this embodiment, the cylinder body 150 is
Since the cylindrical connecting member 152 and the like are rotatably supported by the second case 74b, the spline fitting between the output shaft 34, the cylindrical connecting member 152, and the sun gear 56 becomes thicker, resulting in a loose fitting with a clearance. Therefore, even if the output shaft 34 is bent due to the tension of the transmission belt 40, the cylindrical connecting member 152 and the cylinder body 150
, the occurrence of center runout of the sun gear 56, etc. is eliminated. Incidentally, there is no such bearing 160, and the cylindrical connecting member 152, cylinder body 150, and sun gear 5
In the case of relatively tight spline fitting for centering, such as No. 6, center runout is likely to occur in these members as the spline shaft portion 148 whirls around during high-load, high-speed rotation, resulting in noise. This caused a decrease in durability.

In this embodiment, as described above, the cylindrical connecting member 1
52 and the sun gear 56, the lubricating oil supplied from the lubricating oil path 164 to the spline shaft portion 148 in the sleeve 158 through the through hole 166 flows along the spline groove into which the spline is loosely fitted. It is sent out toward sun gear 56. This spline shaft part 1
A portion of the spline teeth 48 are removed as necessary to ensure the flow rate of the lubricating oil. The lubricating oil sent out in this way passes through the fitting part with the sun gear 56, is supplied to the bearing 174 interposed between the sun gear 56 and the boss part 64 of the carrier 70, and further passes through the bearing 174 to the outer periphery. It is designed so that it can flow out to the side.

As a result, in addition to suitably lubricating the entire spline shaft portion 148, the lubricating oil flowing out to the outer circumferential side through the bearing 174 causes the sun gear 56, the planetary gears 60 and 62 located on the outer circumferential side, the ring gear 58, and the reverse brake. 76 etc. is effectively lubricated.

Further, the cylindrical connecting member 152 is provided with a leak hole 175, and a bearing 160 and a sleeve 158 are provided.
The lubricating oil that has passed through the fitting gap between the forward clutch 72 and the cylindrical connecting member 152 is caused to flow out from the leak hole 175 to the outer circumferential side by centrifugal force, thereby lubricating the forward clutch 72. Furthermore, a cylindrical projection 17 formed on the sun gear 56
2 is also provided with a leak port 177 for releasing lubricating oil to lubricate the plate 157, disk 161, etc. of the forward clutch 72.

On the other hand, a part of the lubricating oil supplied from the lubricating oil passage 164 to the inner peripheral side of the sleeve 158 is transferred to the output shaft 34 and the sleeve 1.
The bearing 126 passes through the fitting gap with the bearing 58 and supports the output shaft 34 at a position close to the point of application of the tension of the transmission belt 40 as described above, and therefore requires particular lubrication.
It is designed to lubricate the

The shaft end of the output gear 78 is fluid-tightly fitted to the end of the output shaft 34, and an oil passage passing through the shaft center of the output gear 7B and the output shaft 34 is used to supply hydraulic oil to the hydraulic cylinder 52. A passage 176 is provided.

Further, a spline shaft portion 178 is also provided at the shaft end of the output gear 78.
is formed, and the boss portion 64 of the carrier 70 is spline-fitted into the spline shaft portion 178.

As described above, a plurality of carrier pins 68 are erected on the disk-shaped flange portion 66 extending from one end of the cylindrical boss portion 64 toward the outer circumferential side, and the planetary gears 60 and 6
2 is connected to the carrier pin 6 via the needle bearing 180.
It is rotatably supported by 8. The distal ends of the carrier pins 68 are connected to each other by an annular connecting plate 182.

The planetary gear 60 is rotatably provided around an axis located on the outer peripheral side of the axis of the planetary gear 62, and meshes with the inner teeth of the ring gear 58. ring gear 5
8 through sliding washers 184 and 186.
It is positioned in the axial direction by being sandwiched between a positioning plate 188 fixed to the case 74b and the flange portion 66 of the carrier 70. The reverse brake 76 includes an annular anchor member 190 fixed to the second case 74b;
A plurality of plates 19 are provided on the inner peripheral surface of this anchor member 190 so as to be relatively non-rotatable and movable in the axial direction.
2 and a plurality of disks 194 which are non-rotatable and movable in the axial direction and are provided alternately with the plate 192 on the outer peripheral surface of the ring gear 5. Rotation of the ring gear 58 is prevented by being pressed. The piston 198 is slidably fitted into an annular cylinder bore 196 formed in the second case 74b, and is returned by a return spring 199. The above cylinder 196, piston 19
8. Return spring 199 etc. are reverse brake 7
It functions as a hydraulic actuator to operate 6.

The carrier bin 6, which is erected in the flange portion 66, has a through hole that penetrates in the axial direction and is closed at one end by a blind cover 200, and a through hole that extends from the middle of the through hole to the inner circumferential side (the axial center of the carrier 70). A through-oil passage 202 consisting of seven holes extending to the side) is provided. This penetrating oil passage 202 is connected to the planetary gear 60
In order to lubricate the inner and outer circumferential parts of the planetary gear 60 and 62, one surface of the flange part 66 on the first gear 78 side is
and 62.

A cylindrical receiver member 204 is attached to the flange portion 66 of the carrier 70 so as to be concentric with the carrier 70 . This receiver member 204 has a hole 2 formed in the fourth case 74d to allow the boss portion 64 to pass therethrough.
a cylindrical portion 208 that is fitted into the cylindrical portion 208 with a predetermined play within the cylindrical portion 206 and whose tip portion is brought close to the bearing 130;
The cylindrical portion 208 includes a conical portion 210 whose diameter becomes larger as the distance from the end of the cylindrical portion 208 increases, and a disc-shaped portion 212 extending toward the outer circumference from the end of the conical portion 210.
is fixed to the first gear 78 side of the flange portion 66 and to the outer peripheral side of the opening of the through oil passage 202 .

With the above configuration, each part of the planetary gear device is lubricated by the lubricating oil supplied from the lubricating oil passage 164 as described above, regardless of whether the vehicle is stopped, and in addition, when the vehicle is running, the receiver member 204 The introduced lubricating oil also lubricates the planetary gears 60 and 62 and the reverse brake 76. That is, while the vehicle is running, the lubricating oil stored in the lower part of the fourth chamber 96 is scraped up along the inner wall surface by the large gear 136.
It reaches the third gear 82 and the second gear 80 and the peripheral wall 144
A relatively large amount of the lubricating oil adhering to the outer peripheral teeth of the second gear 80 is further carried to the meshing portion with the first gear 78 . As a result, lubricating oil flows out from the meshing portion between the outer circumferential teeth of the first gear 78 and the outer circumferential teeth of the second gear 80. Due to this pumping action, the pressure of the lubricating oil is increased in the outer circumference of the first gear 78 surrounded by the first case 74a and the fourth case 74d, and a part of the lubricating oil is absorbed into the first gear 78. It flows out in a direction parallel to the axis,
The cylindrical receiver member 204 passes through the bearing 130.
can be received by The lubricating oil thus received is transferred to the receiver member 2 as shown by the arrow in FIG.
04, the oil reaches the flange portion 66 of the carrier 70, and from there is supplied to the inner circumferential surfaces of the planetary gears 60 and 62 on the sun gear 56 side through the oil passage 202. This directly lubricates the inner peripheral surfaces of the needle bearing 180 and the planetary gears 60 and 62, increasing the durability of the sub-transmission 14. In general, in order to transmit power smoothly and quietly, planetary gear systems need to maintain higher meshing accuracy than normal transmissions, and in particular, the gear accuracy and support accuracy of each planetary gear 60 and 62 must be maintained at high levels. It is required to do so. In addition, due to centrifugal force, the planetary gear 6
The ring gear 58 and the reverse brake 76 are also lubricated by the lubricating oil flowing from 0 and 62 toward the outer circumference.

Note that in FIG. 2, the input shaft 26, the output shaft 34, the first gear 78, and the second gear 8 are shown for ease of understanding.
Although the axes of the zero and third gears 82 and the drive shaft 20 are shown in a common plane, in reality, as shown in FIG.
It is arranged three-dimensionally.

The effects of this embodiment will be explained below.

In this embodiment, a portion of the lubricating oil supplied to the inner peripheral side of the cylindrical connecting member 152, which is a part of the input member, through the lubricating oil path 164 and the through hole 166 of the sleeve 158, It passes through the fitting gap between the output shaft 34 and the sleeve 158, and forcibly lubricates the bearing 126 supporting the output shaft 34. This solves the problem that the bearing 126, which is located in the upper middle portion of the power transmission device, tends to lack lubrication.

Furthermore, in this embodiment, since the output shaft 34 is supported at a position close to the point of application of the tension of the transmission belt 40, the bearing 126, which is under a high load, is sufficiently lubricated. The durability of
The life of the entire device can be extended.

Although one embodiment of the present invention has been described above based on the drawings,
The invention also applies in other aspects.

For example, in the above-described embodiment, the lubricating oil that passed through the fitting gap between the output shaft 34 and the sleeve 158 was supplied to the bearing 126, but the second case 74b penetrated near the through hole 166 of the sleeve 158. hole 156
The lubricating oil may be supplied through an oil groove provided in the second case 74b, or another oil passage communicating with the lubricating oil passage 164 may be provided in the second case 74b to supply the bearing 126.

In short, the lubricating oil may be introduced from the lubricating oil passage located near the bearing 126, and the lubricating oil may be introduced from the lubricating oil passage 126.
It is also possible to provide a lubricating oil passage separate from 4 to supply the lubricating oil.

The above-mentioned embodiment is merely one embodiment of the present invention, and various modifications may be made to the present invention without departing from the spirit thereof.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram of a power transmission device including an embodiment of the present invention. FIG. 2 is a diagram showing the power transmission device of FIG. 1 in detail. FIG. 3 is an enlarged view illustrating the sub-transmission shown in FIG. 2. FIG. FIG. 4 is a diagram showing the arrangement of each element as seen from the side of the housing of FIG. 2. 12: Belt type continuously variable transmission 14: Sub-transmission 26: Input shaft (primary side rotating shaft) 34: Output shaft (secondary side rotating shaft): Variable pulley (primary side variable pulley): Variable pulley (secondary side Variable pulley): Transmission belt b: Second case (support wall) 6: Bearing 4: Lubricating oil path

Claims (1)

[Claims] A primary rotating shaft and a secondary rotating shaft are rotatably supported, and a primary variable pulley and a secondary variable pulley are provided on the primary rotating shaft and the secondary rotating shaft, each having a variable V-groove width. A belt-type continuously variable transmission comprising a variable side pulley, a transmission belt wound around the primary variable pulley and the secondary variable pulley, and a sub-transmission connected to the shaft end of the secondary rotating shaft. A vehicle power transmission device including a belt-type continuously variable transmission and an auxiliary transmission,
A support wall of a housing that supports the secondary rotating shaft via a bearing, and a lubricating oil passage provided on the supporting wall of the housing and supplying pre-pressurized lubricating oil to the bearing. Lubricating device for belt type continuously variable transmission