JP2001012570A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of shortening an input shaft, eliminating an accurate machining, and feeding lubricating oil smoothly to a primary pulley side. SOLUTION: An input shaft 3a and a primary pulley 50 are disposed in the state of being separated from each other, and a lubricating oil guide member 28 mounted on either of the input shaft and primary pulley is installed between an oil passage 3b of the input shaft 3a and an oil passage 52c of the primary pulley 50 so that lubricating oil passes through these oil passage. The lubricating oil guide member 28 eliminates the need that the input shaft 3a must be inserted engagedly into the oil passage 52c of the primary pulley to guide lubricating oil and also eliminates a highly accurate machining, making this transmission economical. Even if a rotating difference occurs between the input shaft and the primary pulley 50 by reverse operation, because the input shaft 3a and the primary pulley 50 are in the state of being separated from each other, the input shaft 3a is prevented from being in contact eccentrically with the primary pulley 50. In addition, a seal ring between both of them can be eliminated.

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a continuously variable transmission having two pulleys and a belt wound between the two pulleys, and more particularly to a continuously variable transmission having a structure in which lubricating oil flows from an input shaft to the pulleys. .

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 6, oil is bored in an input shaft 200 between an input shaft for transmitting an engine driving force from a torque converter of a continuously variable transmission to a primary pulley and a primary pulley. In order to connect the passage 200a and the oil passage 201a formed in the primary pulley 201,
The input shaft 200 is connected to the oil passage 201a of the primary pulley 201.
In this case, a structure that is fitted and engaged through a seal ring 202 has been used.

[0003] A part of the lubricating oil flowing through the oil passage 200a is sent from the oil hole 203 to the forward / reverse switching device according to the rotation of the input shaft, and is used for lubrication of the planetary gears, etc. It flows into the oil passage 201a of the primary pulley and is used for lubricating the belt. The lubricating oil sent to the forward / reverse switching device does not directly flow into the gap 206 due to the bush 204, whereas a small amount of the lubricating oil sent to the oil passage 201a leaks out of the seal ring 202 and flows into the gap 206. However, there is no backflow by the bush 204.

As shown in FIG. 7, the leading end of an input shaft 200 is connected to a primary pulley 20 via a gap GP3.
A structure that is disposed immediately before one oil passage 201a and does not directly engage with each other is also used.

[0005]

However, in the case of the structure shown in FIG. 6, when the vehicle starts to retreat, reverse rotation with respect to the input shaft 200 occurs in the primary pulley 201 and the planetary gear 205 directly connected thereto. During traveling, a large load (high hydraulic pressure, belt tension, etc.) or vibration is applied to the primary pulley 201, causing significant deformation. Further, torque and vibration from the engine are transmitted to the input shaft 200. Therefore, the input shaft 200 and the primary pulley 20
1 is rotated with an eccentricity / interference state, and the function of the seal ring 202 may be reduced.
Further, the planetary gear 205 is directly connected to the primary pulley 201 through a spline connecting portion, and the carrier 2
Since 05 is fitted to the input shaft 200 through the bush 204, vibration and deformation of the input shaft 200 and the primary pulley 201 are transmitted to the bush 204, and the bush 204 may be deteriorated.

The input shaft 200 is connected to the primary pulley 2
In order to engage with 01, it is necessary to work with a long shaft length and with high accuracy, which is not only time-consuming but also uneconomical.

In the case of a structure as shown in FIG.
Since the input shaft 200 does not directly engage with the primary pulley 201, the problem such as a one-sided contact of the input shaft 200 is solved, but the flow of the lubricating oil through the oil passage 200a is disturbed in the gap GP3. In addition, there arises a problem that sufficient lubricating oil cannot be supplied to the oil passage 201a side of the primary pulley 201. Furthermore, since the primary pulley 201 and the input shaft are fitted and engaged, the shaft length still has to be increased.

In view of the above, the present invention provides a continuously variable transmission that requires a short input shaft, does not require high-precision machining, and can smoothly supply lubricating oil to the primary pulley. It is intended to provide.

[0009]

According to a first aspect of the present invention, there is provided a pair of pulleys including a primary pulley (50) and a secondary pulley (51), and a belt (57) wound around the pair of pulleys. And the primary pulley (5
0) is transmitted to the input shaft (3a) via the forward / reverse switching device (3), and the input shaft (3a) and the primary pulley (50) are provided with an oil passage (3b) in the axial direction thereof. In the continuously variable transmission (1) formed to communicate with each other, the input shaft (3a) and the primary pulley (5)
0) are arranged so as to be separated from each other, and the oil passage (3b) of the input shaft and the oil passage (52c) of the primary pulley are arranged.
And a lubricating oil guide member (28) attached to either the input shaft or the primary pulley so that the lubricating oil flows.

According to a second aspect of the present invention, in the continuously variable transmission (1) according to the first aspect, the lubricating oil guide member (28) is
The lubricating oil guide member has a base end (28a) fixed to the primary pulley (50) side and a distal end (2) of the lubricating oil guide member (28).
The auxiliary oil passage is formed between 8b) and the tip portion (3c) of the input shaft.

According to a third aspect of the present invention, in the continuously variable transmission according to the first aspect, the lubricating oil guide member (28) is formed of a cylindrical member, and a base end portion of the lubricating oil guide member. Is fixed to a tip portion (3c) of the input shaft (3a), and a tip portion (3c) of the lubricating oil guide member (28) is inserted into an oil passage (52c) of the primary pulley (50). And a tip (28b) of the lubricating oil guide member (28).
The secondary oil passage (GP2) is formed between the first and the second pulleys.

According to a fourth aspect of the present invention, in the continuously variable transmission (1) according to the first aspect, the lubricating oil guide member (28) is
The lubricating oil guide member has an outer peripheral portion fixed to the primary pulley, and an inner peripheral portion of the lubricating oil guide member and a tip portion of the input shaft (3c).
, The auxiliary oil passage (GP2) is formed.

According to a fifth aspect of the present invention, in the continuously variable transmission (1) according to the first aspect, a sleeve (3d) is provided at a tip portion (3c) of the input shaft (3a), and the lubrication is performed. The oil guide member (28) is formed from an annular member, and the outer peripheral portion of the lubricating oil guide member is fixed to the primary pulley (50). The auxiliary oil passage (GP2) is formed between the sleeve and the sleeve.

[0014]

According to the first aspect of the invention, the lubricating oil guide member (28) ensures the flow of the lubricating oil between the oil passage (3b) of the input shaft and the oil passage (52c) of the primary pulley. Since the oil passage (3b) of the input shaft (3a) and the forward / reverse switching device (3) are connected by the sub-oil passage (GP2), the tip of the input shaft (3a) is connected to the primary pulley as in the related art. There is no need to insert and engage in the oil passage (52c). Thus, even if the input shaft and the primary pulley (50) rotate relative to each other due to, for example, backward movement of the vehicle, the load or vibration applied to the input shaft (3a) and the primary pulley (50) causes the input shaft (3a) to vibrate. Can be prevented from hitting against the primary pulley (50). In addition, the input shaft (3a) and the primary pulley (5
0) are separated from each other, so that not only is the seal ring unnecessary, but also it is not necessary to machine the input shaft (3a) into the primary pulley (50) for a long and accurate process. It is economical with no hassle.

According to the second and third aspects of the present invention, since the cylindrical lubricating oil guide member (28) is merely mounted on the primary pulley (50) or the input shaft (3a) side, the structure is simple and the assembly is easy. is there.

According to the fourth and fifth aspects of the present invention, the lubricating oil guide member can be made simpler by forming the lubricating oil guide member in an annular shape.

The numbers and the like in parentheses are for convenience showing the corresponding elements in the drawings, and therefore, the present description is not limited to the description on the drawings.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. First, the general configuration of a continuously variable transmission to which the present invention is applied and its operation will be described,
Next, the main part of the present invention will be described.

As shown in FIG. 1, an automatic continuously variable transmission 1 for a vehicle to which the present invention is applied has a fluid coupling (torque converter) 2, a forward / reverse switching device 3, and a belt-type continuously variable transmission (CVT). ) 5 and a differential device 6. These fluid couplings 2 and the like are housed in a split type case 7.

The fluid coupling 2 includes a pump impeller 10 connected to the engine output shaft 9, a turbine liner 11 connected to the input shaft 3 a of the forward / reverse switching device 3,
A lock-up clutch 12 that directly connects the input shaft 3a and the engine output shaft 9;

The forward / reverse switching device 3 includes a sun gear 15 fixed to the input shaft 3a, a ring gear 16 rotatably supported, a pinion gear 17 meshed with the sun gear 15, and a carrier 19 supporting the pinion gear 17. A planetary gear 20 is provided.

A forward clutch 22 operated by a hydraulic actuator 21 is interposed between the input shaft 3a and the carrier 19. The forward clutch 22 is engaged with the input shaft 3a to engage with the input shaft 3a. The carrier 19 is directly connected. The other end of the carrier 19 is spline-connected to the fixed sheave 52.

Further, a reverse brake 25 is connected to the ring gear 16.
Is operated by the hydraulic actuator 23 so that the rotation of the ring gear 16 can be stopped.

On the other hand, as shown in FIG. 1, the CVT 5 has a primary pulley 50 and a secondary pulley 51, and a metal belt 57 is wound between the pulleys 50 and 51. .

The primary pulley 50 has a fixed sheave 52. The fixed sheave 52 has a substantially thick cylindrical first boss 52a extending toward the forward / reverse switching device 3; A substantially thick cylindrical second member extending to the opposite side
And a boss 52b. A bearing 59 is interposed on the outer peripheral portion of the first boss portion 52a, and a bearing 61 is interposed between the second boss portion 52b and the case 7. As a result, the fixed sheave 52 Is
The two bearings 59 and 61 rotatably support the case 7.

As shown in detail in FIG. 2, the first boss 52a is formed with a spline connecting portion 58 with the carrier 19 so as to overlap the large-diameter bearing 59 in the axial direction. The carrier 1 is connected via the connecting portion 58
9 is connected to the fixed sheave 52 and rotates integrally, so that rotation from the forward / reverse switching device 3 is transmitted to the primary pulley 50.

On the other hand, the second boss 52b of the fixed sheave 52
Supports a movable sheave 55 via a ball spline 64, and the movable sheave 55 can move in the axial direction of the fixed sheave 52 and rotate integrally with the fixed sheave 52. In addition, this movable sheave 55
Is configured to be moved in the axial direction by a double piston type hydraulic actuator 70.

The other secondary pulley 51 has substantially the same structure as the primary pulley 50, and has a fixed sheave 53 rotatably supported by the case 7 (FIG. 1).
reference). The fixed sheave 53 supports a movable sheave 56 via a ball spline 91. The movable sheave 56 can move in the axial direction of the fixed sheave 53 and rotates integrally with the fixed sheave 53. It has become. Further, the movable sheave 56 is configured to be moved in the axial direction by a hydraulic actuator 92 disposed on the back surface thereof.

An output gear 93 is fixed to the boss 53a of the fixed sheave 53. Below the output gear 93, a reduction gear mechanism 95 and a differential gear 6 are provided.
And are arranged. Among them, the reduction gear mechanism 95
Large gear 95 coaxially arranged to rotate integrally
a differential gear 6 has a ring gear 63 fixed to the differential case 62 so as to rotate integrally with the differential case 62, and a pair of gears 63 supported through a shaft in the differential case 62. , And sun gears 66, 66 meshed with the differential gears 65, 65, respectively. The sun gears 66, 66 are respectively connected to left and right front axles 96, 96 of the vehicle. The differential rotation is output. The output gear 93 on the fixed sheave side is meshed with the large gear 95a of the reduction gear mechanism 95, and the small gear 95b
Are meshed with the ring gear 63 of the differential device 6.

The general structure of the continuously variable transmission 1 to which the present invention is applied has been described above. Next, the operation will be briefly described.

The rotation of the engine output shaft 9 is transmitted to the input shaft 3a via the fluid coupling 2. In this state, the forward clutch 22 is engaged and the reverse brake 25 is engaged.
Is released, the input shaft 3a is directly connected to the fixed sheave 52, and the rotation of the input shaft 3a is transmitted to the fixed sheave 52 via the carrier 19 as it is. Thus, the primary pulley 50 is driven to rotate forward, and the rotation is transmitted to the differential device 6 via the belt 57, the secondary pulley 51, the output gear 93, and the reduction gear mechanism 95.

In this state, the hydraulic actuators 70, 92
When the axial positions of the movable sheaves 55 and 56 are changed by the supplied hydraulic pressure, the contact position between the belt 57 and each of the pulleys 50 and 51 changes, and the rotation transmitted from the primary pulley 50 to the secondary pulley 51 is shifted.

On the other hand, when the forward clutch 22 is released and the reverse brake 25 is engaged, the rotation of the ring gear 63 is stopped, so that the rotation in the opposite direction is transmitted to the fixed sheave 52. Then, the rotation is transmitted to the differential device 6 via the belt 57, the secondary pulley 51, the output gear 93, and the reduction gear mechanism 95 as described above.

Next, the main part of the present invention will be described. According to the present invention, the fixed sheave 52 of the primary pulley 50 and the input shaft 3
This relates to a connection portion with a. More specifically, as shown in FIG. 2, the input shaft 3a according to one embodiment of the present invention has an oil passage 3b formed along the axis thereof, and the fixed sheave 52 also has an oil passage 52c. It is formed penetrating in the direction of the center.

The distal end portion 3c of the input shaft 3a is formed to have a slightly smaller diameter than the other portions, and the distal end portion 3c and the fixed sheave 52 are separated from each other in the radial direction without abutting engagement with each other. They are arranged and assembled such that a gap GP is formed between them. Tip portion 3 of input shaft 3a
c is arranged without entering the oil passage 52c,
A lubricating oil guide member 28 formed in a cylindrical shape is provided between the distal end portion 3c and the oil passage 52c in such a manner that the base end portion 28a is fixed to the fixed sheave 52 side.

The tip portion 28b of the lubricating oil guide member 28 is formed so as to surround the tip portion 3c of the input shaft 3a.
Is fitted in the distal end portion 28b, and a gap GP2 as an auxiliary oil passage is formed annularly between the distal end portion 28b and the distal end portion 3c.

Since the connection between the fixed sheave 52 of the primary pulley 50 and the input shaft 3a has the above-described configuration, the lubricating oil supplied into the oil passage 3b of the input shaft 3a is
It is smoothly guided from the tip portion 3c through the lubricating oil guide member 28 into the oil passage 50c of the primary pulley 50, and
A part thereof is supplied to the forward / reverse switching device 3 via a gap GP2 as an auxiliary oil passage. When the continuously variable transmission 1 enters the reverse state, the fixed sheave 52 of the primary pulley 50 rotates in the opposite direction to the input shaft 3a, and a relative rotation occurs between the two. The spline connection 5 between the boss of the carrier 19 and the fixed sheave
8, even if the input shaft 3a and the fixed sheave 52 are slightly vibrated or deformed due to a load, the input shaft 3a and the fixed sheave 52 may not interfere with each other even if the gap GP exists. Absent. Further, the lubricating oil guide member 28 is formed in a cylindrical shape, and the flexibility thereof is the fixed sheave 52.
Therefore, even if the input shaft 3a slightly interferes with the lubricating oil guide member 28, the input shaft 3a is absorbed by the deformation of the lubricating oil guide member 28.

The shape of the lubricating oil guide member 28 is such that the lubricating oil supplied from the oil passage 3b of the input shaft 3a is partially supplied to the forward / reverse switching device 3 while the lubricating oil is supplied to the primary pulley 50. If it can be supplied to the side 52c, the structure of the forward / reverse switching device 3 and the oil passage 52c of the fixed sheave 52
Various modes are conceivable depending on the shape or the like. FIG.
The sun gear 15 is an example of the primary pulley 50.
And the carrier 19 is connected to the input shaft 3a.
Is connected to Even in this case, the distal end portion 3c of the input shaft 3a does not fit into and engage with the fixed sheave 52, and the oil passage 52c on the fixed sheave 52 side does not penetrate through the fixed sheave 52, and is partially fixed sheave. 52 are formed in the axial direction. Then, the input shaft 3a and the fixed sheave 5
Lubricating oil guide member 28 communicating the second oil passages 3b and 52c
The input shaft 3a has a proximal end portion 28a fixed to the distal end portion 3c side of the input shaft 3a, a distal end portion 28b provided in the oil passage 52c, and a slight gap between the outer peripheral portion of the distal end portion 28b and the inner wall of the oil passage 52c. They are fitted and engaged to form GP2. In this case, the lubricating oil is supplied to the forward / reverse switching device 3 via the oil passage 52c and the gap GP2 as the auxiliary oil passage.

Further, in the case of FIG. 4, a sleeve 3d is provided at the tip 3c of the input shaft 3a.
As for d, the tip part is fitted in the oil passage 52c which penetrates the fixed sheave 52 in the axial direction via the gap GP. In this case, the lubricating oil guide member 28 is formed in an annular shape,
The outer peripheral portion of the lubricating oil guide member 28 is fixed to the fixed sheave 52 side, and a gap GP2 as a sub-oil passage is formed between the sleeve 3d and the inner peripheral portion of the lubricating oil guide member 28. FIG. 5 shows an example in which the sleeve 3d of FIG. 4 is formed integrally with the input shaft 3a, and the rest is the same as FIG. Also in this case, a part of the lubricating oil is supplied to the forward / reverse switching device 3 via the gap GP2.

[Brief description of the drawings]

FIG. 1 is a diagram showing an example of the overall configuration of a continuously variable transmission.

FIG. 2 is a diagram showing a main part of the present invention.

FIG. 3 is a diagram showing another embodiment of the present invention.

FIG. 4 is a diagram showing still another embodiment of the present invention.

FIG. 5 is a diagram showing still another embodiment of the present invention.

FIG. 6 is a diagram showing a relationship between a conventional primary pulley and an input shaft.

FIG. 7 is a diagram showing a relationship between a conventional primary pulley and an input shaft.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission 3 ... Forward / backward switching device 3a ... Input shaft 28 ... Lubricating oil guide member 3b, 52c ... Oil passage 3c ... Tip part 28a ... Base end part 28b ... Tip part 50 …… Primary pulley 51 …… Secondary pulley GP2 …… Sub oil passage

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Takahisa Hirano 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd. (72) Takao Terashima, Takane 10, Fujii-machi, Anjo, Aichi Prefecture・ F-term in AW Co., Ltd. (reference) 3J050 AA03 AB03 BA03 BA18 CB07 CB09 3J063 AB23 AC03 BA11 CA01 CB02 CB22 CB41 CB47 XD03 XD45 XD46 XD72 XE15

Claims (5)

[Claims] A pair of pulleys comprising a primary pulley and a secondary pulley; and a belt wound around the pair of pulleys, wherein power from an input shaft is transmitted to the primary pulley via a forward / reverse switching device. In a continuously variable transmission in which an oil passage is formed in the input shaft and the primary pulley so as to communicate with each other in the axial direction thereof, the input shaft and the primary pulley are arranged so as to be separated from each other, Between the oil passage of the input shaft and the oil passage of the primary pulley,
A continuously variable transmission, comprising a lubricating oil guide member attached to one of the input shaft and the primary pulley so that lubricating oil flows. 2. The continuously variable transmission according to claim 1, wherein the lubricating oil guide member is formed of a cylindrical member, and a base end of the lubricating oil guide member is fixed to the primary pulley side. An auxiliary oil passage is formed between the tip of the lubricating oil guide member and the tip of the input shaft. 3. The continuously variable transmission according to claim 1, wherein the lubricating oil guide member is formed of a cylindrical member, and a base end of the lubricating oil guide member is provided at a distal end of the input shaft. The lubricating oil guide member is fixedly inserted, and the distal end of the lubricating oil guide member is inserted into the oil passage of the primary pulley. Further, a sub-oil passage is formed between the distal end of the lubricating oil guide member and the primary pulley. 4. The continuously variable transmission according to claim 1, wherein the lubricating oil guide member is formed of an annular member, and an outer peripheral portion of the lubricating oil guide member is fixed to the primary pulley. An auxiliary oil passage is formed between an inner peripheral portion of the lubricating oil guide member and a tip portion of the input shaft. 5. The continuously variable transmission according to claim 1, wherein a sleeve is provided at a tip portion of the input shaft, the lubricating oil guide member is formed of an annular member, An outer peripheral portion of the oil guide member is fixed to the primary pulley, and a sub-oil passage is formed between an inner peripheral portion of the lubricating oil guide member and the sleeve.