JP4020240B2 - Lubrication structure in continuously variable transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a lubrication structure in a continuously variable transmission that lubricates a second shaft and a third shaft in a continuously variable transmission.
[0002]
[Prior art]
As a lubricating structure in a conventional continuously variable transmission, for example, a structure described in Japanese Patent Application Laid-Open No. 8-28666 is known.
In this conventional example, the oil supplied to the right end side of the secondary pulley shaft serving as the second shaft is supplied to the hydraulic pressure correction chamber through the secondary pulley shaft and supplied to the rib forming the oil reservoir formed in the lower part. The output gear is lubricated.
[0003]
By the way, in the above conventional example, the oil supply system to the reduction shaft serving as the third shaft is not described, but as the oil supply system to the third shaft, as shown in FIGS. Lubricating oil output from the control valve 111 disposed on the lower surface side of the case 110 is received on the converter housing 115 side by a transfer portion 114 below the fourth shaft 104 serving as an output shaft of the differential gear 113 through the oil passage 112. And is supplied to the right end of the reduction shaft 117 serving as the third shaft 103 and an intermediate position between the fourth shaft 104 by a pipe 116 disposed in a U-shape so as to surround the differential gear 113 in the converter housing 115, The third shaft 103 and the differential through this pipe 116 through the branch oil passage 118. They are respectively supplied to the bearing 119 of Rugiya 113.
[0004]
Further, an orifice is formed at a position corresponding to the upper side of the fourth shaft 104 in the pipe 116 disposed in the converter housing 115, and as shown in FIG. 9, the differential gear is formed from the injection hole 120 formed in the pipe 116. It is comprised so that lubricating oil may be injected with respect to 113 pinions.
[0005]
[Problems to be solved by the invention]
However, in the above-described conventional example, since the transfer portion 114 from the transmission case 110 to the converter housing 115 for the lubricant output from the control valve 111 is formed below the fourth shaft 104, the first shaft When the distance between the first shaft 104 and the fourth shaft 104 is short, the lubricating oil delivery section 114 to the transmission case 110 and the converter housing 115 is subject to layout restrictions depending on the size of the differential gear 113 and the size of the control valve 111. There is an unresolved issue that the degree of freedom is low.
[0006]
Further, since an orifice is formed in the pipe 116 disposed in the converter housing 115 so that the lubricating oil is injected to the pinion of the differential gear 113, the lubrication balance at other lubrication points is not stable. There is also a problem to be solved.
Accordingly, the present invention has been made paying attention to the unsolved problems of the above-described conventional example, and the transfer portion from the transmission case of the lubricating oil output from the control valve to the converter housing is subject to layout restrictions. Another object of the present invention is to provide a lubrication structure for a continuously variable transmission that can stabilize the lubrication balance by separating the lubrication to the differential gear from the lubrication path to the other third shaft or the like.
[0007]
[Means for Solving the Problems]
To achieve the above object, a continuously variable transmission lubrication structure according to claim 1 is configured such that power from a rotary drive source is transmitted to a transmission case and a converter housing coupled to each other and a drive pulley is formed. A first shaft, a second shaft disposed in parallel with the first shaft and forming a driven pulley connected to the drive pulley via a V-belt, and connected to the second shaft via a power transmission means In the continuously variable transmission that supports the third shaft that is formed and the fourth shaft that forms a differential gear connected to the third shaft via a differential ring gear, the transmission case is coupled to the converter housing. An intermediate wall that rotatably supports the third shaft and the fourth shaft is provided on the surface end side, and one end is provided in a gap portion between the intermediate wall and the differential ring gear. A lubricating oil passage that communicates with a lubricating oil outlet of a control valve disposed in the transmission case and has the other end extending outside the outermost peripheral range of the differential ring gear is formed, and the lubricating oil is formed on a mating surface with the converter housing. Forming a lubricating oil delivery portion communicating with the road, and forming a lubricating oil passage communicating with the lubricating oil passage of the second shaft and the third shaft in the converter housing and communicating with the lubricating oil delivery portion. It is a feature.
[0008]
In the first aspect of the invention, the lubricating oil output from the lubricating oil outlet of the control valve is guided along the intermediate wall to the outside of the outermost peripheral range of the differential gear by the lubricating oil passage, and the other end side of the lubricating oil passage In this case, the lubricant oil is transferred to the converter housing side by the lubricating oil transfer portion formed on the mating surface with the converter housing, so that the lubricating oil transfer portion is not affected by the size of the differential gear or the size of the control valve. The degree of freedom can be remarkably improved, and since there is no need to provide a lubricating oil delivery part in the vicinity of the differential gear, the differential gear can be disposed on the bottom side of the case body, and the lubrication accumulated in the lower part of the case body It is no longer necessary to supply lubricating oil separately in a soaked state.
[0009]
The lubricating structure of the continuously variable transmission according to claim 2 is the invention according to claim 1, wherein the lubricating oil passage of the transmission case passes through the intermediate wall and one end communicates with the lubricating oil outlet of the control valve. A through oil passage penetrating the intermediate wall, communicating with the through oil passage, along the intermediate wall, and between the first shaft and the fourth shaft, and between the third shaft and the fourth shaft. It is composed of a gap portion, a pipe disposed through the third shaft and the outside of the second shaft, and a through oil passage that communicates with the pipe and communicates with the lubricating oil delivery portion through the intermediate wall. It is characterized by having.
[0010]
In the invention according to claim 2, the lubricating oil output from the lubricating oil outlet of the control valve is guided to the upper side from the third shaft through the through oil passage and the pipe, and is further connected to the converter housing through the through oil passage. Guided by the lubricating oil delivery portion formed on the mating surface and delivered to the converter housing, the lubrication path from the control valve to the delivery portion can be freely set by the pipe.
[0011]
Furthermore, the lubricating structure of the continuously variable transmission according to claim 3 is the invention according to claim 1 or 2, wherein the lubricating oil passage of the converter housing communicates with a lubricating oil passage transferring portion formed at one end of the transmission case. A through oil passage whose other end passes through the converter housing and extends to the intermediate position of the support portion of the second shaft and the third shaft, a pipe communicating with the through oil passage, and a second communicating with the pipe. It is characterized by comprising a distribution oil passage communicating with the lubricating oil passage of the shaft and the third shaft, respectively.
[0012]
In the invention according to claim 3, the lubricating oil delivered from the transmission case is guided to the intermediate portion between the second shaft and the third shaft through the through oil passage, and then, the second shaft through the pipe and the distribution oil passage. In addition, since it is guided by the third shaft, it is possible to freely set the lubricating path from the lubricating oil delivery section to the second shaft and the third shaft.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic front view of a V-belt type continuously variable transmission showing an embodiment of the present invention, and FIGS. 2 and 3 are a right side view and a left side view of FIG.
The V-belt type continuously variable transmission includes a transmission case 11a at the center as seen in FIG. 1, a converter housing 11b attached to the left end side thereof, and a side cover 11c attached to the right end side of the mission case 11a. ing.
[0014]
In the converter housing 11b, as shown in FIG. 7, a torque converter 12 connected to the output shaft 10a of the engine 10 as a rotational drive source is disposed. The torque converter 12 is provided with a lockup mechanism, and is a fastening state in which the input-side pump impeller 12b and the output-side turbine runner 12c are mechanically fastened by controlling the hydraulic pressure of the lockup oil chamber 12a. And, the release state in which the pump impeller 12b and the turbine runner 12c are separated 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 to an output shaft 13 rotatably supported by the transmission case 11a.
[0015]
The output shaft 13 is connected to a forward / reverse switching mechanism 15 in the mission case 11a. The forward / backward switching mechanism 15 includes a planetary gear mechanism 17, a forward clutch 40, and a reverse brake 50.
The planetary gear mechanism 17 includes 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 to the output shaft 13 so as to rotate integrally. Further, the pinion gear 21 meshes with both the sun gear 19 and the internal gear 27.
[0016]
The pinion carrier 25 can be connected to the output shaft 13 by the forward clutch 40, and the internal gear 27 can be fixed to the transmission case 11a by the reverse brake 50. The pinion carrier 25 is coaxially disposed on the torque converter housing side of the output shaft 13, and is connected to a drive shaft 14 having one end rotatably connected to the transmission case 11a and the other end rotatably supported to the side cover 11c. 14 is provided with a drive pulley 16. Here, the output shaft 13 and the drive shaft 14 correspond to the first shaft 101.
[0017]
The drive pulley 16 has a fixed conical plate 18 that rotates integrally with the drive shaft 14, a V-shaped pulley groove that is disposed opposite to the fixed conical plate 18, and a drive shaft that is driven by hydraulic pressure acting on the drive pulley cylinder chamber 20. 14 and a movable conical plate 22 that is movable in the axial direction. The drive pulley 16 is connected to a driven pulley 26 via a V-belt 24 so as to be capable of transmission.
[0018]
One end of the driven pulley 26 is provided on a driven shaft 28 that is a second shaft 102 that is rotatably supported by the mission case 11a by a bering 27a and the other end is rotatably supported by a bearing 27b on the side cover 11c. Yes. The driven pulley 26 has a fixed conical plate 30 that rotates integrally with a driven shaft 28 that is rotatably supported at one end on the transmission case 11a and the other end on the side cover 11c, and is disposed opposite the fixed conical plate 30. A movable conical plate 34 is formed which forms a letter-shaped pulley groove and is movable in the axial direction of the driven shaft 28 by hydraulic pressure acting on the driven pulley cylinder chamber 32. Reference numeral 33 denotes a pressure correction chamber formed to face the driven pulley cylinder chamber 32 with the piston 32a interposed therebetween, and the working oil is passed through a central lubricating oil passage 28a formed in the driven shaft 28 as will be described later. The hydraulic pressure generated by the centrifugal force is generated so as to cancel the increase in the hydraulic pressure due to the centrifugal force generated in the hydraulic oil in the driven pulley cylinder chamber 32 as the driven pulley 26 rotates.
[0019]
The drive 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 a third shaft rotatably supported at one end by the transmission case 11a and at the other end by the torque converter housing 11b. 103 is meshed with an idler gear 48 fixed on an idler shaft 52. A pinion gear 54 provided on the idler shaft 52 always meshes with the differential ring gear 44. The differential ring gear 44 meshes with a pair of pinion gears 58 and 60 that constitute a differential gear 56 and a pair of side gears 62 and 64, and the side gears 62 and 64 respectively have output shafts 66 and 68 that constitute a fourth shaft 104. It is connected.
[0020]
The rotational force input from the output shaft 10a of the engine 10 to the power transmission mechanism as described above is transmitted to the forward / reverse switching mechanism 15 via the torque converter 12 and the output shaft 13, and the forward clutch 40 is fastened. When the reverse brake 50 is released, 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 When 40 is released and the reverse brake 50 is engaged, 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.
[0021]
The rotational force of the drive shaft 14 is transmitted to the differential gear 54 via the drive pulley 16, the V belt 24, the driven pulley 26, the driven shaft 28, the drive gear 46, the idler gear 48, the idler shaft 52, the pinion gear 54, and the differential ring gear 44. The output shafts 66 and 68 as the fourth shaft rotate in the forward direction or the reverse direction. When both the forward clutch 40 and the reverse brake 50 are released, the power transmission mechanism is in a neutral state.
[0022]
When the power is transmitted 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, thereby driving the drive pulley. The rotation ratio between the pulley 16 and the driven pulley 26 can be changed. For example, if the width of the V-shaped pulley groove of the driving 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 driving pulley 16 side is reduced, and the driven pulley is driven. The contact position radius of the V-belt on the pulley 26 side becomes large, so that a large gear ratio is obtained. If the movable conical plates 22 and 34 are moved in the opposite directions, the gear ratio is reduced in the opposite manner.
[0023]
As shown in FIG. 4, the first shaft 101 to the fourth shaft 104 are arranged at the substantially central portion in the vertical direction of the right half of the mission case 11a, and the second shaft 102 is Arranged in the upper left half, which is the upper left part with respect to the first shaft 101, the third shaft 103 is disposed in the lower left portion of the second shaft, and the fourth shaft 104 is in the lower right portion of the third shaft 103. From the oil pump 51 disposed on the output shaft 13 of the torque converter 12 shown in FIG. 6 at the lower portion of the left half of the first shaft 101 and further on the lower portion of the right half of the mission case 11a. A control valve 70 to which hydraulic oil is supplied is disposed.
[0024]
Lubricating oil output from the lubricating oil output port 70a of the control valve 70 is transmitted through the lubricating oil passage 71A formed on the mating surface with the mission case side lubricating oil passage 71A, the converter housing 11b, and the converter housing side lubricating oil passage 72. The second shaft 101 and the third shaft 103 are supplied.
As shown in FIG. 6, an intermediate wall 73 is formed in the transmission case 11a in parallel with the mating surface at a position close to the mating surface with the converter housing 11b, and a case 57 of the differential gear 56 is supported on the intermediate wall 73. While supporting the bearing 59, the bearing 88 mentioned later which supports the idler shaft 52 used as the 2nd axis | shaft is supported.
[0025]
As shown in FIGS. 4 and 7, the mission case side lubricating oil passage 71A includes an L-shaped through oil passage 74 formed in the transmission case 11a connected to the lubricating oil output port 70a of the control valve 70, A pipe 75 as a lubricating oil passage connected to the other end of the L-shaped through oil passage 74 and disposed along the intermediate wall 73 and an intermediate wall 73 communicated with the other end of the pipe 75 are passed through. It is composed of an inclined through oil passage 76 that supplies lubricating oil to the lubricating oil delivery portion 71B formed on the mating surface with the converter housing 11b.
[0026]
One end of the L-shaped oil passage 74 communicates with the lubricating oil output port 70a of the control valve 70, and the other end penetrates the intermediate wall 73 of the transmission case 11a as shown in FIG. 4 and the differential gear on the converter housing 11b side. The first shaft 101 and the fourth shaft 104 are opened in an intermediate portion of the space 77 in which the space 56 is accommodated.
As clearly shown in FIG. 4, the pipe 75 is formed between the first shaft 101 and the fourth shaft 104 in the gap 77 between the surface of the intermediate wall 73 on the converter housing 11 b side and the side surfaces of the pinion gear 44 and the differential ring gear 44. It passes between the third shaft 103 and the fourth shaft 104, extends around the outer side of the third shaft 103 in a substantially U shape, and extends to the middle portion of the second shaft 102 and the third shaft 103 above the third shaft 103. Yes.
[0027]
As is particularly apparent in FIG. 6, the inclined through oil passage 76 is inclined and extended to the right from the space 77 of the transmission case 11a to the mating surface with the converter housing 11b, and communicates with the lubricating oil delivery portion 71B. .
Further, as clearly shown in FIG. 6, the converter housing side oil passage 73 is opened at the mating surface with the transmission case 11a so as to communicate with the lubricating oil delivery portion 71B on the transmission case 11a side, and the other end thereof is the converter housing 11b. A through oil passage 82 extending obliquely downward to the right between the bearings 80 and 81 that support the second shaft 102 and the third shaft 103 on the outside through the inside, and communicated with the through oil passage 82 to the right in the axial direction. The connecting pipe 83 extends, and the second shaft 102 and the branch oil passage 84 that branches the lubricating oil to the third shaft 103 are connected to the connecting pipe 83.
[0028]
Here, the branch oil passage 84 is formed on the right end side of the converter housing 11 b so as to rise to the left relatively steeply, and one end thereof is opposed to the central lubricating oil passage 28 a formed on the driven shaft 28 that becomes the second shaft 102. Is extended to the lubricating oil supply portion 85 disposed at the other end, and the other end is extended to the lubricating oil supply portion 86 disposed at a position facing the central lubricating oil passage 52 a formed in the idler shaft 52 serving as the third shaft 103. It has been extended.
[0029]
The lubricating oil supplied to the lubricating oil supply unit 85 passes through the central lubricating oil passage 28a formed in the driven shaft 28 serving as the second shaft 102, and the radial oil passages 28b and 28c communicating therewith. The lubricating oil supplied to the hydraulic pressure correction chamber 33 of the bearing 27a and the driven pulley 26 and supplied to the lubricating oil supply unit 86 is directly supplied to the bearing 87 that supports the idler shaft 52 on the converter housing 11b side, and the idler shaft 52. Is supplied through the central lubricating oil passage 52 a of the idler shaft 52.
[0030]
Next, the operation of the above embodiment will be described.
Assume that the engine 10 is in a stopped state and is in a parking state in which a parking range (P range) is selected with a shift lever. In this parking state, as shown in FIG. 7, the V belt type continuously variable transmission mechanism 29 has the smallest contact position radius on the drive pulley 16 side of the V belt 24 and the largest contact position radius on the driven pulley 26 side. It is in the shift position where the maximum gear ratio is achieved.
[0031]
When the ignition switch is turned on from this parking state and the engine 10 is started to be in an idling state, the oil pump 51 connected to the output shaft 13 of the torque converter 12 is rotationally driven in response to this, whereby the oil pump The hydraulic oil discharged from 51 is supplied to the control valve 70 disposed at the lower part of the mission case 11a. In the control valve 70, the hydraulic oil supplied from the oil pump 51 is supplied to the pressure regulator valve PR, and the pressure that forms the pulley control pressure required when the groove widths of the driving pulley 16 and the driven pulley 26 are changed is formed. It is supplied to an operation valve such as a regulator valve and a clutch regulator valve for controlling the forward clutch 40, and finally outputted as a lubricating oil from the lubricating oil outlet 70a.
[0032]
The lubricating oil output from the lubricating oil outlet 70a is guided to the space 77 on the converter housing 11b side through the intermediate wall 73 by the L-shaped oil passage 74 constituting the mission case side lubricating oil passage 71A. Passed from the letter-shaped oil passage 74 to the pipe 75, passes between the first shaft 101 and the fourth shaft 104, passes between the third shaft 103 and the fourth shaft 104, and the outside of the third shaft 103 is substantially U-shaped. It is guided around the middle of the second shaft 102 above the third shaft 103 and is formed on the mating surface with the converter housing 11b through an inclined through oil passage 76 that penetrates the intermediate wall 73 from the pipe 75. The lubricant is supplied up to the lubricant delivery portion 71B.
[0033]
In this lubricating oil delivery part 71B, it is delivered to the penetrating oil passage 82 of the converter housing side lubricating oil passage 73 and guided to the right end side of the converter housing 11b, where it is delivered to the branching oil passage 84 via the connecting pipe 83. It is. In the branched oil passage 84, one of the branched lubricating oils is supplied to a lubricating oil supply portion 85 that faces the end of the driven shaft 28 serving as the second shaft 102, and a central lubricating oil passage 28 a formed in the driven shaft 28. Through the oil passage 28b, and is supplied to the oil pressure correction chamber 33 facing the driven pulley cylinder chamber 32 of the driven pulley 26 through the oil passage 28c. The hydraulic pressure that cancels the hydraulic pressure increase generated in the cylinder chamber 32 is generated by the centrifugal force accompanying the rotation of the cylinder.
[0034]
The other of the lubricating oil branched off in the branch oil passage 84 is supplied to a lubricating oil supply unit 86 facing the end of the idler shaft 52 serving as the third shaft, and the idler shaft 52 can be rotated from the lubricating oil supply unit 86. It is supplied directly to the bearing 87 to be supported, and is also supplied to a bearing 88 that rotatably supports the idler shaft 52 on the opposite transmission case 11a side through a central lubricating oil passage 52a formed on the idler shaft 52.
[0035]
In this way, lubrication and hydraulic oil supply around the second shaft 102 and the third shaft 103 can be performed satisfactorily.
At this time, the delivery of the lubricating oil output from the control valve 71 from the transmission case 11a side to the converter housing 11b side is outside the outermost peripheral range of the differential gear 54, the second shaft 102 above the third shaft 103 and the second shaft 102. Since it is performed by the lubricating oil delivery part 71B provided in the middle part of the three shafts 103, when designing this delivery part 71B, the influence of the size of the differential gear 54 and the size of the control valve 71 as in the conventional example described above. It is possible to set arbitrarily without receiving, and the degree of freedom of layout can be greatly improved.
[0036]
In addition, the mission case side oil passage 71B can supply the lubricating oil to the upper side of the idler shaft 52 while avoiding the differential gear 54 and the idler shaft 52 by using the pipe 75. As shown in FIG. The gear 54 can be disposed at the lowest position of the mission case 11a. Therefore, as shown in FIG. 3, the drop length L of the fourth shaft 104 with respect to the first shaft 101 can be increased, so that the mounting angle with respect to the vehicle body of the automobile can be set to 0 °, and the transmission case 11a The differential gear 54 can be submerged in the vicinity of the pinion gears 58 and 60 in the lubricating oil gathered at the bottom, and it is not necessary to lubricate the differential gear 54 with the lubricating oil output from the control valve 70. It is not necessary to form an orifice in the path 72 as in the conventional example. As a result, the lubrication balance with respect to the second shaft 102 and the third shaft 103 can be stably maintained without being lost.
[0037]
In the above embodiment, the case where the pipe 75 in the transmission case side lubricating oil passage 71A passes between the first shaft 101 and the fourth shaft 104 and between the third shaft 103 and the fourth shaft 104 has been described. However, the present invention is not limited to this, and when the lubricating oil outlet 70a of the control valve 70 is formed on the lower left side in FIG. 4, the lower side and the left side of the fourth shaft 104 pass through the third shaft 103. You may make it arrange | position so that it may reach to the left side.
[0038]
In the above embodiment, the lubricating oil delivery portion 71B between the mission case side oil passage 71A and the converter housing side oil passage 73 is provided between the second shaft 102 and the third shaft 103 at the upper portion of the third shaft 103. However, the present invention is not limited to this, and the lubricating oil delivery section 76 can be formed at an arbitrary position outside the outermost peripheral range of the differential gear 54.
[0039]
【The invention's effect】
As described above, according to the first aspect of the invention, the lubricating oil output from the lubricating oil outlet of the control valve is guided outside the outermost peripheral range of the differential gear by the lubricating oil passage along the intermediate wall of the transmission case. After that, the lubricant oil is supplied to the lubricating oil delivery section formed on the mating surface with the converter housing and delivered to the converter housing side, so that this lubricating oil delivery section may be affected by the size of the differential gear and the size of the control valve. In addition, the degree of freedom in design can be remarkably improved, and since there is no need to provide a lubricating oil delivery part in the vicinity of the differential gear, the differential gear can be disposed on the bottom side of the case body. It is immersed in the lubricating oil that accumulates in the lower part and supplied separately. That it is unnecessary, the effect is obtained that by omitting the provision of the orifice to the transmission case side lubrication oil passage can be ensured good lubrication balance.
[0040]
According to the second aspect of the present invention, the lubricating oil output from the lubricating oil outlet of the control valve is guided to the upper side from the third shaft through the through oil passage passing through the intermediate wall and further through the pipe. Lubricant path from the control valve to the transfer part by the pipe is guided to the lubricant oil transfer part formed on the mating surface with the converter housing through the through oil passage penetrating the wall and transferred to the converter housing side. Can be set freely.
[0041]
Further, according to the invention of claim 3, the lubricating oil delivered from the transmission case side is guided to the intermediate portion between the second shaft and the third shaft through the through oil passage, and then, via the pipe and the distribution oil passage. Since the second shaft and the third shaft are guided, the lubricating path from the lubricating oil delivery section to the second shaft and the third shaft can be freely set.
[Brief description of the drawings]
FIG. 1 is a schematic front view showing an embodiment of the present invention.
FIG. 2 is a right side view of FIG.
FIG. 3 is a left side view of FIG. 1;
FIG. 4 is an end view shown by an arrow A in FIG.
FIG. 5 is an end view shown by arrow B in FIG. 1;
6 is an enlarged cross-sectional view taken along the line CC of FIG. 2 showing the main part of the present invention.
FIG. 7 is a schematic configuration diagram showing a power transmission mechanism in the case body.
FIG. 8 is a cross-sectional view showing a conventional lubricating oil supply system.
FIG. 9 is an end view of a converter housing showing a conventional lubricating oil supply system.
[Explanation of symbols]
10 engine
11 Case body
11a Mission case
11b Converter housing
12 Torque converter
15 Forward switching mechanism
16 Drive pulley
26 Driven pulley
29 V-belt type continuously variable transmission mechanism
40 Forward clutch
50 Reverse brake
51 Oil pump
101 1st axis
102 Axis 2
103 3rd axis
104 4th axis
70 Control valve
71A Mission case side oil passage
71B Lubricating oil delivery section
72 Converter housing side oil passage
73 Middle wall
74 L-shaped oil passage
75 pipe
76 Inclined through oil passage
82 Inclined oil passage
83 Connecting pipe
84 Branch oil passage

Claims (3)

Power from a rotational drive source is transmitted to the transmission case and the converter housing that are coupled to each other, and a first shaft formed with a drive pulley, and arranged in parallel with the first shaft, the drive pulley and the V belt A second shaft formed with a driven pulley connected via a shaft, a third shaft connected to the second shaft via a power transmission means, and a differential gear connected to the third shaft via a differential ring gear In the continuously variable transmission that supports the fourth shaft formed with
In the transmission case, an intermediate wall that rotatably supports the third shaft and the fourth shaft is provided on the end surface of the coupling surface with the converter housing, and in a gap portion between the intermediate wall and the differential ring gear, One end communicates with the lubricating oil outlet of the control valve disposed in the transmission case, and the other end forms a lubricating oil passage extending outside the outermost peripheral range of the differential ring gear, and the mating surface with the converter housing A lubricating oil delivery portion communicating with the lubricating oil passage is formed, and a lubricating oil passage communicating with the lubricating oil passage portion of the second shaft and the third shaft is formed in the converter housing while communicating with the lubricating oil delivery portion. A lubrication structure in a continuously variable transmission. The transmission oil passage of the transmission case passes through the intermediate wall, one end of which communicates with the lubricating oil outlet of the control valve and passes through the intermediate wall, and communicates with the through oil passage. And a pipe disposed through the gap between the first axis and the fourth axis, the gap between the third axis and the fourth axis, and the outside of the third axis and the second axis, 2. The lubrication structure for a continuously variable transmission according to claim 1, wherein the lubrication structure is constituted by a through oil passage that communicates with the pipe and communicates with the lubricant delivery section through the intermediate wall. One end of the lubricating oil passage of the converter housing communicates with a lubricating oil passage passing portion formed in the transmission case, and the other end extends through the converter housing to an intermediate position between the second and third shaft support portions. A through oil passage, a pipe communicating with the through oil passage, and a distribution oil passage communicating with the pipe and communicating with the lubricating oil passages of the second shaft and the third shaft, respectively. A lubricating structure in a continuously variable transmission according to claim 1 or 2.

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