JP3172615B2 - Continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission.

[0002]

2. Description of the Related Art A conventional V-belt type continuously variable transmission is disclosed in JP-A-3-204436. The continuously variable transmission shown therein has a driven pulley including a fixed cone member fixed in the axial direction and a movable cone member facing the same and movable in the axial direction. The movable cone member is provided with a hydraulic working chamber for pressing the movable cone member in the direction of the fixed cone member, and a pressure correction chamber for canceling a hydraulic pressure generated by centrifugal force acting on oil in the hydraulic working chamber. . The pressure compensation chamber is always filled with a predetermined amount of oil, and the hydraulic pressure generated by the centrifugal force acting on the pressure compensation chamber acts in the opposite direction to the force by the hydraulic pressure of the hydraulic working chamber. Some of the oil in the pressure compensation chamber leaks when the rotation of the driven pulley stops, so it is necessary to constantly replenish the oil. One method for this is to provide an orifice in the wall between the hydraulic working chamber and the pressure compensation chamber and supply oil from the hydraulic working chamber. However, this method has a problem that the oil pressure in the hydraulic working chamber decreases due to the oil flowing out of the orifice.
Therefore, as another method, there is a direction in which a special oil passage is formed from the lubricating oil passage and the oil is guided to the pressure compensation chamber. In this case, the separate plate of the control valve is provided with an orifice for connecting the lubricating oil passage and the special oil passage. The oil that has passed through the orifice passes through the oil passage of the control valve, a hole provided in the casing,
The pressure is supplied to the pressure compensation chamber through the inner diameter of the driven shaft.

[0003]

However, in the conventional continuously variable transmission, since the position of the pressure compensation chamber and the position of the orifice are far from each other, the resistance of the pipe in the middle becomes large, and it is necessary to use the pressure compensation chamber. In order to obtain a sufficient amount of oil, the diameter of the orifice must be increased. As the diameter of the orifice increases, the oil pressure in the lubricating oil passage decreases. In order to prevent this, it is necessary to increase the set oil pressure of the lubricating oil passage. Since the lubricating oil passage is the most downstream oil passage, if the set oil pressure is increased, it is necessary to increase the oil pressure of other upstream oil passages as well, and there is a problem that the oil pump loss increases. . The present invention is to solve such a problem.

[0004]

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems by providing an orifice for outputting oil supplied to a pressure compensation chamber to a cap facing an end of an axial hole of a shaft. That is, the continuously variable transmission according to the present invention includes the shaft (2).
8) A fixed cone member (30) that rotates integrally with the shaft and does not move in the axial direction, and a movable cone member (34) that rotates integrally with the shaft (28) and moves in the axial direction. A V-shaped groove is formed, and the movable cone member (34) acts on a hydraulic working chamber (32) for pressing the movable cone member in a direction approaching the fixed cone member (30) and oil on the hydraulic working chamber (32). Pressure compensation chamber (8
2), the shaft (28) includes:
An axial hole (84) opened at one end thereof and a radial hole (86) communicating therewith are formed, and the radial hole (86) is formed on the inner periphery of the pressure compensation chamber (82). It is arranged so that the side opening and the axial position coincide with each other.
A cap (88) is fixed to the casing (74) so as to face the end on the side provided with the axial hole (84) in 8), and the small-diameter portion (92) of the cap (88) is An orifice (96) is provided at the tip of the small-diameter portion (92), and oil from the oil passage of the casing (74) is introduced into the orifice (96). From an axial hole (84). The numbers in parentheses indicate the corresponding members in the embodiments described later.

[0005]

The orifice for outputting the oil supplied to the pressure compensation chamber is provided on the cap facing the end of the axial hole of the shaft communicating with the pressure compensation chamber. Therefore,
The oil output from the orifice need only move to the pressure compensation chamber via the axial hole and the radial hole of the shaft. Since the movement distance of the oil is short, the resistance of the oil passage is small. Therefore, a required flow rate can be obtained even if the hydraulic pressure before the output of the orifice is reduced. Since the oil pressure before the orifice output can be reduced, this does not affect the other upstream oil pressure. Thereby, the loss of the oil pump can be reduced.

[0006]

FIG. 2 shows a power transmission mechanism of a continuously variable transmission. The continuously variable transmission includes a torque converter 12 (which may be a fluid coupling), a forward / reverse switching mechanism 15, a V-belt continuously variable transmission mechanism 29, and a differential device 56.
The rotation of the output shaft 10 of the engine can be transmitted to the drive shafts 66 and 68 at a predetermined speed ratio and a predetermined rotation direction. The continuously variable transmission includes a torque converter 12 (a pump impeller 12a, a turbine runner 12a).
b, a stator 12c, a lock-up clutch 12d, etc.), a rotating shaft 13, a forward / reverse switching mechanism 15 (comprising a planetary gear unit 19, a forward clutch 40, a reverse brake 50, etc.), a drive shaft 14, Drive pulley 16 (consisting of fixed cone member 18, drive pulley cylinder chamber 20, movable cone member 22, etc.), V-belt 24, driven pulley 26 (fixed cone member 30, driven pulley cylinder chamber 3)
2 (comprising a hydraulic working chamber), a movable cone member 34, etc.), a driven shaft 28 (shaft), a drive gear 46, an idler gear 48, an idler shaft 52, a pinion gear 54, a final gear 44, a pinion gear 58, a pinion gear 60, It comprises a side gear 62, a side gear 64, a drive shaft 66, a drive shaft 68, and the like.

The driven pulley 26 of the continuously variable transmission shown in FIG.
1 is shown in detail in FIG. The driven shaft 28 is rotatably supported on the casing 74 by bearings 70 and 72. A fixed cone member 30 is provided integrally with the driven shaft 28. A movable cone member 34 is provided so as to form a V-shaped groove interval facing the fixed cone member 30. The movable cone member 34 is supported on the driven shaft 28 via a ball spline 76 so as to be movable in the axial direction. Fixed cone member 30 at the outer periphery of movable cone member 34
A driven pulley cylinder chamber 32 is provided on the side opposite to the facing side. The driven pulley cylinder chamber 32 is constituted by a portion surrounded by the movable cone member 34, the cylinder member 78, and the fixed piston member 80. The outer diameter end of the cylinder member 78 is integrally connected to the movable cone member 34. The fixed piston member 80 has an inner diameter portion fixed to the driven shaft 28 and an outer diameter portion fitted to the inner peripheral surface of the outer diameter portion of the cylinder member 78. The supply of oil pressure to the driven pulley cylinder chamber 32 is performed by supplying oil to the driven shaft 28 in the axial hole 98 and the radial hole 100 formed from the left end in FIG. 1 and the movable cone member 34. This is performed through the hole 102. A pressure correction chamber 82 for correcting centrifugal force is formed between the cylinder member 78 and the fixed piston member 80. The pressure compensation chamber 82 has an axial hole 84 formed from the right end of the driven shaft 28 in FIG. 1, a radial hole 86 communicating therewith, and a fixed piston member 80 that is axially restrained. Oil can be supplied through a groove provided in a plate 107 for storing the oil. A cap 88 is provided so as to face the right end of the driven shaft 28 in FIG. The cap 88 has a large-diameter portion 90 described later fixed to the casing 74 and a small-diameter portion 92 inserted into the hole 84 of the driven shaft 28. The space 109 between the casing 74 and the cap 88 is connected to a lubricating oil passage. Cap 88
As shown in FIGS. 3 and 4, a ring-shaped large diameter portion 9 is provided.
0 and a small diameter portion 92 protruding in the axial direction therefrom. A passage 94 communicating with the internal space of the large diameter portion 90 is formed inside the small diameter portion 92. An orifice 96 smaller in diameter than the passage 94 is formed at the tip of the small diameter portion 92.

Next, the operation of this embodiment will be described. The hydraulic pressure is supplied to the driven pulley cylinder chamber 32 through the holes 98 and 100 of the driven shaft 28 and the oil hole 102 of the movable cone member 34. The oil output from the orifice 96 of the cap 88 into the hole 84 is supplied through the hole 86 into the pressure correction chamber 82. When the driven pulley 26 rotates, centrifugal force acts on the oil in the driven pulley cylinder chamber 32, and the driven pulley cylinder chamber 32
Will increase. At the same time, the centrifugal force acts on the oil in the pressure correction chamber 82, and the hydraulic pressure generated by the centrifugal force acts on the oil in the driven pulley cylinder chamber 32 to cancel the hydraulic pressure generated. . Thereby, the hydraulic pressure based on the centrifugal force generated in the driven pulley cylinder chamber 32 is corrected. Pressure compensation chamber 82
The oil supplied into the shaft is output from an orifice 96 located at the end of the driven shaft 28, but the oil output from the orifice 96 passes through the short distance of the holes 84 and 86 of the driven shaft 28 to compensate for the pressure. The chamber 82 can be reached. For this reason, the resistance acting on the oil from the orifice 96 to the inside of the pressure compensation chamber 82 is smaller than in the case where the orifice is provided in the conventional separate plate. Thus, the required oil amount in the pressure compensation chamber 82 can be obtained without increasing the oil pressure in the lubricating oil passage.

[0009]

According to the present invention, the orifice for outputting the oil supplied to the pressure compensation chamber is provided on the cap provided to face the end of the axial hole of the shaft communicating with the pressure compensation chamber. Therefore, the movement distance of the oil output from the orifice to the pressure correction chamber is short. Thus, since the resistance acting on the oil during movement is small, the required oil amount can be secured even if the diameter of the orifice is reduced. The lubricating oil passage is the most downstream oil passage, and there is no need to increase the oil pressure, so that this does not affect the oil pressure of other upstream oil passages. Thereby, the loss of the oil pump can be reduced.

[Brief description of the drawings]

FIG. 1 is a diagram showing an embodiment of the present invention.

FIG. 2 is a diagram showing a configuration of the present invention.

FIG. 3 is a front view of a cap.

FIG. 4 is a sectional view taken along line 4-4 of FIG. 3;

[Explanation of symbols]

 Reference Signs List 28 driven shaft (shaft) 30 fixed cone member 32 driven pulley cylinder chamber (hydraulic working chamber) 34 movable cone member 82 pressure compensation chamber 84, 86 hole 88 cap 92 small diameter section 96 orifice

Continuation of front page (72) Inventor Hirofumi Okahara 2 Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor Co., Ltd. (56) References JP-A-60-104848 (JP, A) JP-A-63-199960 (JP) , A) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16H 9/00-9/26 F16H 57/00-57/12

Claims (1)

(57) [Claims] 1. A fixed cone member (30) rotating integrally with a shaft (28) and not moving in the axial direction, and a movable cone member (34) rotating integrally with the shaft (28) and movable in the axial direction. , A V-shaped groove for winding the V-belt is formed, and the movable cone member (34) is fixed to the fixed cone member (30).
A continuously variable transmission provided with a hydraulic working chamber (32) for pressing in a direction approaching the pressure and a pressure correction chamber (82) for canceling a centrifugal force acting on oil in the hydraulic working chamber (32). The shaft (28) is formed with an axial hole (84) opened at one end thereof and a radial hole (86) communicating with the axial hole (84). Room (82)
The cap (88) is arranged so that the axial position coincides with the inner peripheral opening of the shaft (28), and faces the end of the shaft (28) on the side where the axial hole (84) is provided. The small-diameter portion (92) of the cap (88) is fixed to the casing (74), enters the axial hole (84) of the shaft (28), and the tip of the small-diameter portion (92) has an orifice (9).
6), wherein the oil from the oil passage of the casing (74) is configured to be supplied from the orifice (96) into the axial hole (84). .