JP2003106415A - Belt lubrication structure of continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a compact layout in which the temperature rise of a lubricating oil to lubricate a belt is suppressed, excellent belt lubrication is performed, the routing distance of the lubricating oil is reduced, and the possibility of mixing any impurities is reduced. SOLUTION: A hydraulic oil discharged from an oil pump is input in a control valve 72 disposed on a lower side of a case body 11a, the lubricating oil for a V-belt output from the control valve 72 is fed to a mating surface of a side cover 11c through internal oil passages 76 and 77, and fed to an injection nozzle 55 facing the V-belt of a V-belt type continuously variable transmission mechanism through an oil passage 78 inside the side cover and an outer pipe 79 via an oil cooler 73 and an oil filter 74 fitted to an outer surface of the side cover 11c, and further via an oil passage 81 in the side cover and oil passages 82 and 83 in the case body 11a.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention comprises a drive pulley to which a driving force is input and a driven pulley connected to the drive pulley via an endless belt, and the pulley groove width of the drive pulley and the driven pulley is changed. The present invention relates to a belt lubrication structure for a continuously variable transmission that performs continuously variable transmission.

[0002]

2. Description of the Related Art In a belt lubrication structure for a continuously variable transmission of this type, it is necessary to cool the lubricating oil with an oil cooler in order to suppress the temperature rise of the belt contact surfaces of the drive pulley and the driven pulley. Since the belt contact surface is mirror-finished, contaminants such as spatter and debris are mixed into the lubricating fluid and carried to the belt contact surface, which prevents damage to this belt contact surface. Need to be provided.

Therefore, in the conventional belt lubrication structure of the continuously variable transmission, as shown in FIG. 8, the lubricating oil output from the control valve 2 arranged at the bottom of the case body 1 of the continuously variable transmission is After being cooled from the side cover 3 of the case body 1 by the radiator 4 arranged outside the case body 1, it again passes through the side cover 3 and is returned to the inside of the case body 1, and again through the oil filter 5 to the control valve 2 again. It is configured to feed through the inside to the belt contact surfaces of the drive pulley and the driven pulley of the continuously variable transmission.

[0004]

By the way, in the conventional belt lubrication structure of the continuously variable transmission, the oil filter 5 is provided inside the case body 1, which is the case body 1.
In order to efficiently distribute the lubricating oil cooled by the radiator 4 arranged outside, the lubricating oil cooled by the radiator 4 is returned to the control valve 2 again and distributed inside the control valve 2, and then the oil filter 5 This is because it is supplied to the belt contact surfaces of the drive pulley and the driven pulley of the continuously variable transmission via the. However, in this structure, the lubricating oil cooled by the outside radiator 4 is affected by the high temperature oil passing through the inside and outside of the high temperature control valve, and the lubricating oil temperature rises, so that the belt lubrication can be efficiently performed. There is an unsolved problem that you cannot do it. In addition, by equipping the radiator with an oil cooler, there is an unsolved problem that the lubricating oil has a long handling distance and the possibility that foreign matters are mixed into the lubricating oil increases.

Therefore, the present invention has been made by paying attention to the unsolved problem of the above-mentioned conventional example, and it is possible to suppress the temperature rise of the lubricating oil for the belt lubrication and to perform the good belt lubrication. At the same time, it is an object of the present invention to provide a belt lubrication structure for a continuously variable transmission, which can shorten the routing distance of the lubricating oil to reduce the possibility of mixing foreign matters and realize a compact layout.

[0006]

To achieve the above object, in a belt lubrication structure for a continuously variable transmission according to a first aspect of the present invention, a drive pulley to which a driving force is input and an endless belt are provided to the drive pulley. In a belt lubrication structure of a continuously variable transmission that continuously changes gears by changing the pulley groove widths of a driven pulley and a driven pulley connected to each other, the control valve discharges the endless belt. The feature is that the lubricating oil is directly supplied through an oil cooler and an oil filter.

According to the first aspect of the present invention, the lubricating oil discharged from the control valve is directly supplied to the endless belt inserted between the drive pulley and the driven pulley via the oil cooler and the oil filter. Can
Lubricating oil cooled by the oil cooler can be directly supplied to the endless belt, a large cooling effect can be exerted on the endless belt, and contaminants can be reliably removed.

Further, in the belt lubrication structure for a continuously variable transmission according to a second aspect of the present invention, in the invention according to the first aspect, the oil cooler and the oil filter are attached to the outside of the case body of the continuously variable transmission. It is characterized by being. In the invention according to claim 2, since the oil cooler and the oil filter are assembled on the outside of the case body, a compact layout can be achieved.

Further, in the belt lubrication structure for a continuously variable transmission according to a third aspect of the present invention, in the invention according to the first aspect, the oil cooler and the oil filter are attached to an outer side cover of a case body rear portion of the continuously variable transmission. It is characterized by being. In the invention according to claim 3, since the oil cooler and the oil filter are assembled on the outside of the side cover of the case body, the length of the oil path between the oil cooler and the control valve can be shortened, and impurities are mixed. The possibility can be reduced and the layout can be made compact.

[0010]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. 1, 2 and 3 are a front view, a plan view and a right side view showing a V-belt type continuously variable transmission 10 showing an embodiment of the present invention, in which 11 is a case body. As shown in FIG. 1, it is composed of a case body 11a at the center, a converter housing 11b attached to the left end side thereof, and a side cover 11c attached to the right end side.

In the converter housing 11b, FIG.
As shown in Fig. 1, the output shaft 1 of the engine as a rotational drive source
A torque converter 12 connected to 1 is provided. A lockup mechanism is added to the torque converter 12, and the torque converter 12 is mechanically fastened to the pump impeller 12b on the input side and the turbine runner 12c on the output side by controlling the hydraulic pressure in the lockup oil chamber 12a. And a released state in which the pump impeller 12b and the turbine runner 12c are separated from each other can be selected. The turbine runner 12c of the torque converter 12 is connected to one end or the converter housing 11b, and the other end is connected to the output shaft 13 rotatably supported by the case body 11a.

The output shaft 13 is connected to the forward / reverse switching mechanism 15 in the case body 11a.
Has a planetary gear mechanism 17, a forward clutch 40, and a reverse brake 50. The planetary gear mechanism 17
It is composed of a sun gear 19, a pinion carrier 25 having a pinion gear 21, and an internal gear 27. Here, the sun gear 19 is always connected so as to rotate integrally with the output shaft 13. Also, the pinion gear 2
1 meshes with both the sun gear 19 and the internal gear 27.

The pinion carrier 25 can be connected to the output shaft 13 by a forward clutch 40, and the internal gear 27 can be fixed to the case body 11a by a reverse brake 50. The pinion carrier 25 is coaxially arranged on the torque converter housing side of the output shaft 13, one end of which is connected to the case body 11a and the other end of which is connected to the drive shaft 14 which is rotatably supported by the side cover 11c. A drive pulley 16 is provided on the shaft 14.

The drive pulley 16 has a fixed conical plate 18 which rotates integrally with the drive shaft 14, and a hydraulic cone which is arranged opposite to the fixed conical plate 18 to form a V-shaped pulley groove and which acts on the drive pulley cylinder chamber 20. And a movable conical plate 22 that is movable in the axial direction of the drive shaft 14. The drive pulley 16 is connected to a driven pulley 26 via a V belt 24 so as to be able to be transmitted.

The driven pulley 26 is provided on the driven shaft 28. One end of the driven pulley 26 is the case body 11a.
In addition, a fixed conical plate 30 that rotates integrally with the driven shaft 28, the other end of which is rotatably supported by the side cover 11c, and a V-shaped pulley groove that is disposed so as to face the fixed conical plate 30 and that is driven by It is composed of a movable conical plate 34 that is movable in the axial direction of the driven shaft 28 by the hydraulic pressure acting on the pulley cylinder chamber 32.

The driving pulley 16, the V belt 24, and the driven pulley 26 constitute a V belt type continuously variable transmission mechanism 29. A drive gear 46 is fixed to the driven shaft 28 in the torque converter housing 11b. The drive gear 46 has an idler shaft rotatably supported at one end on the case body 11a and at the other end by the torque converter housing 11b. It meshes with an idler gear 48 fixed on 52. The pinion gear 54 provided on the idler shaft 52 always meshes with the final gear 44. The final gear 44 includes a pair of pinion gears 58 and 60 and a pair of side gears 62 and 64 that form the differential device 56.
Are meshed with each other, and the side gears 62 and 64 are connected to the output shafts 66 and 68, respectively.

The engine 10 is incorporated in the power transmission mechanism as described above.
The rotational force input from the output shaft 10a is transmitted to the forward / reverse switching mechanism 15 via the torque converter 12 and the output shaft 13, the forward clutch 40 is engaged, and the reverse brake 50 is released. In this case, the rotational force of the output shaft 13 is transmitted to the drive shaft 14 in the same rotational direction via the planetary gear mechanism 17 that is in an integrally rotating state, while the forward clutch 40 is released and the reverse brake is also applied. When 50 is fastened, the rotational force of the rotary shaft 13 is transmitted to the drive shaft 14 in the state where the rotational direction is reversed by the action of the planetary gear mechanism 17.

The rotational force of the drive shaft 14 is the drive pulley 16, V
Belt 24, driven pulley 26, driven shaft 28, drive gear 4
6, the idler gear 48, the idler shaft 52, the pinion gear 54, and the final gear 44 are transmitted to the differential gear 54, and the output shafts 66 and 68 rotate in the forward or reverse direction. When both the forward clutch 40 and the reverse brake 50 are released, the power transmission mechanism is in a neutral state.

During the power transmission as described above, the movable conical plate 22 of the drive pulley 16 and the movable conical plate 34 of the driven pulley 26 are moved in the axial direction to change the contact position radius with the V belt 24. The rotation ratio between the drive pulley 16 and the driven pulley 26 can be changed. For example, if the width of the V-shaped pulley groove of the drive pulley 16 is increased and the width of the V-shaped pulley groove of the driven pulley 26 is reduced, the contact position radius of the V belt 24 on the drive pulley 16 side is reduced, and the driven pulley is driven. The radius of contact position of the V-belt on the pulley 26 side becomes large, so that a large gear ratio is eventually obtained. If the movable conical plates 22 and 34 are moved in the opposite directions, the gear ratio is reduced in the opposite manner to the above.

Then, the V-belt type continuously variable transmission mechanism 29 is used.
Lubricating oil supplied from the lubricating oil supply system 70 is injected to the V belt 24. In this lubricating oil supply system, as shown in FIG. 7, the lubricating oil discharged from the oil pump 71 is supplied to the control valve 72 arranged at the lower portion of the case body 11a as shown in FIG. The lubricating oil output from the control valve 72 is passed from the injection nozzle 75 to the V-belt 24 of the V-belt type continuously variable transmission mechanism 29 via the oil cooler 73 and the oil filter 74, which are arranged in a built-in manner on the outer surface of the side cover 11c. Inject lubricating oil to.

As shown in FIG. 6, the control valve 72 is, for example, an oil pump 7 provided near the mating surface of the case body 11a and the torque converter housing 11b.
1 is supplied with the lubricating oil, and a pressure regulator valve PR that forms a control pressure for controlling the groove width of the drive pulley 16 and the driven pulley 26, and a control pressure regulated by the pressure regulator valve PR are controlled. Shift control valve SC for supplying to the cylinder chamber 20 of the drive pulley 16 and clutch regulator valve for forming clutch hydraulic pressure for the forward clutch 40 and the reverse brake 50 to which the control pressure regulated by the pressure regulator valve PR is supplied. CR, a manual valve MV that selectively supplies the control pressure regulated by the clutch regulator valve CR to the forward clutch 40 and the reverse brake 50, and the control pressure regulated by the clutch regulator valve CR are supplied. Torque converter 12 The torque converter regulator valve TR that forms the control pressure and the control pressure regulated by the torque converter regulator valve TR are supplied to control the lock-up function of the torque converter 12 and to control the V in the V-belt continuously variable transmission mechanism 29. A lock-up control valve RC that outputs lubricating oil to the belt 24.

The control pressure output from the lockup control valve RC is supplied to the lockup chamber 12a and the lockup control valve RC is
The V-belt lubricating oil output from the oil cooler 73
Is output to. That is, this control valve 72
1 is a case body 11 as shown by a dotted line in FIGS.
The lubricating oil output from the lock-up control valve RC of the control valve 72, which is disposed in the lower part of the
6 and an oil passage 77 which communicates therewith and extends toward the side cover 11c, is supplied to the mating surface with the side cover 11c as shown in FIG. 4, and is formed to face the oil passage 77 and penetrate the side cover 11c. It is supplied to the oil cooler 73 built in above the side cover 11c through the oil passage 78 and the outer pipe 79 formed at the outer end of the side cover 11c.

The lubricating oil cooled by the oil cooler 73 is supplied to the oil filter 74 connected to the lower left side of the oil cooler 73 in FIG. 3 through the oil passage 79 formed inside the side cover 11c, As shown in FIG. 1, clean lubricating oil from which contaminants such as spatter and cutting debris are removed by the oil filter 74 communicates with the oil outlet at the center of the oil filter 74 and is formed in the side cover 11c. It is supplied to the mating surface with the case main body 11 through 81, and is supplied to the converter housing 11b side through the oil passage 82 formed inside the case main body 11 so as to face the oil passage 81 as shown in FIGS. , Through the oil passage 83 formed on the converter housing 11b side to the converter housing 11b side shown in FIGS. 2, 4 and 5. The injection nozzle is extended to the side cover 11c side is set to a position facing the V-belt 24 5
5, and is jetted toward the V-belt 24 from the spray port 55a of the spray nozzle 55.

Next, the operation of the above embodiment will be described.
Now, it is assumed that the engine 10 is stopped and the parking range (P range) is selected by the shift lever. In this parking state, as shown in FIG. 6, the V-belt type continuously variable transmission mechanism 29 has the minimum contact position radius of the V-belt 24 on the drive pulley 16 side and the driven pulley 26.
The gear position is at the maximum gear ratio with the maximum contact position radius on the side.

When the ignition switch is turned on and the engine 10 is started from this parking state to the idling state, the oil pump 71 connected to the output shaft 13 of the torque converter 12 is correspondingly driven to rotate. The hydraulic oil discharged from the oil pump 71 is supplied to the control valve 72 arranged below the case body 11a. In the control valve 72, the hydraulic oil supplied from the oil pump 71 is supplied to the pressure regulator valve PR to form a pulley control pressure required when changing the groove widths of the drive pulley 16 and the driven pulley 26, By supplying this pulley control pressure to the cylinder chamber 20 of the drive pulley 16 via the shift control valve SC, the drive pulley 16
It is possible to change the groove width of.

On the other hand, the pressure regulator valve P
The control pressure regulated by R is the clutch regulator valve C
When the drive range (D range) is selected by the shift lever by supplying the clutch pressure to the V, the clutch pressure is supplied to the forward clutch 40 via the manual valve MV, so that the forward clutch 4
0 gradually shifts to the engaged state.

Further, the control pressure regulated by the clutch regulator valve CR is supplied to the torque converter regulator valve TR to form a torque converter control pressure, which is supplied to the torque converter 12 via the lockup control valve RC. The lockup function is controlled. Further, from the lockup control valve RC to the V-belt 24 of the V-belt type continuously variable transmission mechanism 29.
V belt lubricating oil is output to the case main body 1 shown in FIG. 4 through oil passages 76 and 77 formed in the case main body 11a as shown in FIG.
Oil supplied to the mating surface of the side cover 11c of 1a, and then built in above the side cover 11c through an oil passage 78 formed in the side cover 11c and an outer pipe 79 formed at the outer end. It is supplied to the cooler 73 and cooled by a cooling medium such as cooling water.

The V cooled by the oil cooler 73
The belt lubricating oil is supplied to the oil filter 74 through an oil passage 80 formed in the side cover 11c, and the oil filter 74 removes impurities such as spatter and cutting debris, and removes and cleans the impurities. The converted V-belt lubricating oil is returned from the lubricating oil outlet formed in the central portion of the oil filter 74 to the mating surface with the case body 11a through the oil passage 81 formed in the side cover 11c.
It is supplied to the torque converter housing 11b side through the oil passage 82 formed in 1a, and then is supplied to the injection nozzle 75 extending to the side cover 11c side through the oil passage 83. From the injection port 75a of this injection nozzle 75, as shown in FIG. As described above, the sufficiently cleaned and cooled V-belt lubricating oil is sprayed on the V-belt 24 on the driven pulley 26 side.

For this reason, the V belt 24 wound between the drive pulley 16 and the driven pulley 26 of the V belt type continuously variable transmission mechanism 29 is cooled by the oil cooler 53 and cleaned by the oil filter 74. Lubricating oil can be supplied, heat generated at the contact surface between the drive pulley 16 and the driven pulley 26 and the V belt 24 can be effectively cooled, and the V belt 24 of the drive pulley 16 and the driven pulley 26 can be It is possible to reliably prevent foreign matter from adhering to the mirror-finished surface that comes into contact, and it is possible to reliably prevent the mirror-finished surface from being roughened by foreign matter.

As described above, according to the above-described embodiment, after the V-belt lubricating oil output from the control valve 72 is cooled as in the conventional example, the control valve 72 is cooled.
Without being returned to, the oil is directly supplied to the injection nozzle 75 via the oil cooler 73 and the oil filter 74 and sprayed on the V-belt 24 of the V-belt type continuously variable transmission mechanism 29. Therefore, the cooled V-belt lubricating oil is used. Can be reliably prevented from being heated in the control valve 72.

Further, since the oil cooler 73 and the oil filter 74 are assembled to the outside of the side cover 11c, the routing distance of the V-belt lubricating oil can be shortened and the possibility of inclusion of foreign matters can be reduced. , A compact layout can be done.

[0032]

As described above, according to the invention of claim 1, the lubricating oil discharged from the control valve is directly inserted between the drive pulley and the driven pulley via the oil cooler and the oil filter. The lubricating oil can be supplied to the endless belt, the lubricating oil cooled by the oil cooler can be directly supplied to the endless belt, and a great cooling effect can be exerted on the endless belt.
It is possible to obtain an effect that foreign substances can be surely removed.

Further, according to the second aspect of the invention, since the oil cooler and the oil filter are attached to the outside of the case body, there is an effect that a compact layout can be achieved. Further, according to the invention of claim 3, since the oil cooler and the oil filter are assembled to the outside of the side cover at the rear of the case body,
It is possible to reduce the length of the oil passage between the control valve and the control valve, reduce the possibility that foreign matters will be mixed, and achieve a compact layout.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view showing an embodiment of the present invention.

FIG. 2 is a plan view showing a part of FIG. 1 by cutting away.

FIG. 3 is a right side view of FIG.

FIG. 4 is a right side view with the side cover of FIG. 1 removed.

5 is a cross-sectional view taken along the line AA of FIG.

FIG. 6 is a schematic configuration diagram showing a power transmission mechanism in a case body.

FIG. 7 is a hydraulic circuit diagram showing a specific hydraulic circuit of the control valve.

FIG. 8 is a hydraulic circuit diagram showing a conventional example.

[Explanation of symbols]

10 engine 11 case body 11a Case body 11b converter housing 11c side cover 12 Torque converter 15 Forward switching mechanism 16 Drive pulley 17 planetary gears 26 Driven pulley 29 V-belt type continuously variable transmission 40 Forward clutch 50 Reverse brake 71 oil pump 72 Control valve 73 Oil cooler 74 Oil filter 75 injection nozzle 76-78 oil passage 79 Outer pipe 80-83 oil passage

Continued front page    (72) Inventor Hiroki Suzuki             No. 1-1 Yoshiwara Takaracho, Fuji City, Shizuoka Prefecture             Co-Trans Technology Co., Ltd. F term (reference) 3J050 AA03 AB04 BA03 BB13 CE03                 3J063 AA02 AB22 AC04 BA11 BA15                       BB41 CA01 CB22 CB25 CD45                       XD03 XD23 XD32 XD48 XD56                       XD62 XD72 XE04 XE12 XE15                       XF16 XF22 XH02 XH12 XH23                       XH26 XH43

Claims (3)

[Claims] 1. A driving pulley to which a driving force is input, and a driven pulley connected to the driving pulley via an endless belt, wherein the driving pulley and the driven pulley are continuously variable by changing a pulley groove width. In a belt lubrication structure for a continuously variable transmission that performs gear shifting, the lubricating oil discharged from a control valve is directly supplied to the endless belt through an oil cooler and an oil filter. Machine belt lubrication structure. 2. The belt lubrication structure for a continuously variable transmission according to claim 1, wherein the oil cooler and the oil filter are assembled outside a case body of the continuously variable transmission. 3. The belt lubrication structure for a continuously variable transmission according to claim 1, wherein the oil cooler and the oil filter are assembled on the outside of the side cover at the rear of the case body of the continuously variable transmission.