JPH02271142A - Frictional type continuously variable transmission - Google Patents

Abstract

PURPOSE:To prevent the release of engagement between a planetary rotor and an input disc by installing a torsional spring so that an output disc rotation- shifts in the direction separating from a pressing part and pressing the output disc even with the output disc speed change ratio of zero. CONSTITUTION:Revolution is speed-change-transmitted from a planetary rotor 5 to an output disc 4 through the sliding of a speed change ring 13 by the revolution of an input disc 2, and the output disc is shifted in the direction separating from a pressing hub 32 for the pressing hub 32 by the riding over onto the aslant surface of a steel ball 33, and pressed onto the planetary rotor 5, and speed change is performed. An annular recessed part is formed on the output disc 4 opposed to the hub 2, and a torsional coil spring 35 is arranged, and the output disc 4 is energized in the direction separating in the peripheral direction from the the hub 32. Therefore, even if the speed change ring 13 moves to the right edge, and the speed change ratio of the disc 4 becomes zero, an energizing force for energizing the output disc towards the planetary rotor is generated, and the release of engagement between the rotor 5 and the input disc 2 is prevented.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a continuously variable friction transmission.

[Conventional technology]

Conventionally, as this type of continuously variable transmission, for example, a planetary rotor type continuously variable transmission has been known, and its configuration was disclosed in Japanese Patent Publication No. 57-13.
It is disclosed in Publication No. 221. To explain with reference to FIG. 13, an input shaft 1 and an output shaft 3 are arranged on the same axis A, and a plurality of cone-shaped planetary rotors 5 are provided between these two shafts, and this planetary rotation The input disc 2 fixed to the input shaft 1 is mounted on the first transmission surface 10 of the child 5, the output disc 4 connected to the output shaft 3 is mounted on the second transmission surface 11, and the output disc 4 connected to the output shaft 3 is mounted on the third transmission surface 12. Frictionally engaging the speed change rings 13,
This speed change ring 13 is moved in the direction of the central axis A of the input shaft 1 and output shaft 3, and the third transmission surface 12 of the planetary rotor 5 is
By changing the engagement position with the input shaft 1 and the output shaft 3
I am trying to change the gear ratio between the two. In the transmission shown in FIG. 13, the gear ratio becomes smaller as the gear ring 13 is displaced to the right in the figure, and when the gear ring 13 is at the position indicated by the two-dot chain line in the figure, the gear ratio becomes O, and the input disk 2 rotates. is not transmitted to the output disk 4. Reference numeral 30 denotes a pressing force generating means in the form of a running cam, which includes a cam disk 50 that rotates integrally with the output disk 4, a hub 32 that rotates integrally with the output shaft 3, and a steel sandwiched between the cam disk 50 and the hub 32. A ball 33 is provided. When the output disk 4 rotates, a phase difference occurs between the cam disk 50 and the hub 32 in the rotational direction, and this causes the steel ball 33 to move toward the cam disk 5.
The output disk 50 rides on the cam roller formed on the opposing surfaces of the hub 32 and the cam disk 50, and is displaced to the left in FIG. 13, thereby urging the output disk 4 against the planetary rotor 5. A preload spring 20 disposed on the facing surface of the output disk 4 and the cam disk 50 presses and urges the output disk 4 in the left direction in the figure, and applies frictional force to each part of the planetary rotor 5 when the output disk 4 starts rotating. It gives a resultant force.

[Problem to be solved by the invention]

However, in such a continuously variable transmission, the speed change ring 1
3 is at the position shown by the two-dot chain line in FIG. 13, and the gear ratio is O. Since the output disk 4 does not rotate, the pressing force generating means 30 does not generate a pressing force, and therefore the output disk 4 is moved to the planetary rotor 5. The only pressing force that urges toward is the spring force of the preload spring 20. The biasing force of the preload spring 20 is sufficient to provide the frictional engagement force necessary to start the rotation of the output disk 4, and therefore the frictional engagement force provided by the preload spring 20 is small. on the other hand,
At the position where the gear ratio is 0, the revolution speed of the planetary rotor 5 is the highest, and therefore the centrifugal force acting on the planetary rotor 5 is maximum. In particular, when the engine is rotated at a high speed and the input shaft 1 is rotated at a high speed when the gear ratio is 0, a large centrifugal force FA acts on the planetary rotor 5 as shown in FIG. Therefore, the planetary rotor 5 attempts to displace in the direction of the arrow J° in the figure, using the contact point 60 with the speed change ring 13 as a fulcrum. As a result, a force K acts on the output disk 4 in the right direction in the figure, and as mentioned above, when the gear ratio is 0, the force pushing the output disk 4 in the left direction in the figure is small.
The planetary rotor 5 is displaced in the direction of arrow J in the figure, and thus the planetary rotor 5 cannot maintain a normal orbit,
There is a possibility that the input disk 2 and the planetary rotor 5 may become disengaged.

[Means to solve the problem]

In order to solve the above-mentioned problems, the present invention provides a drive shaft that is rotatably provided around an axis, a drive-side rotational force transmission element that is provided on the drive shaft and rotates integrally with the drive shaft, and a drive shaft that is rotatable around an axis. A driven shaft is provided on the drive shaft and is provided coaxially with the drive shaft, facing the drive shaft, and a driven side rotational force that is provided on the driven shaft and can be relatively displaced in the axial direction and circumferential direction of the driven shaft. a transmission element, a transmission means provided between the driving side rotational force transmission element and the driven side rotational force transmission element, and configured to frictionally engage with the driving side and driven side rotational force transmission elements to transmit rotational force; a pressing force generating means for urging the driving side rotational force transmission element toward the driving side rotational force transmission element and transmitting the rotation of the driven side rotational force transmission element to the driven shaft, the pressing force generating means: The driven side rotational force transmission element has a suppressing part that is arranged opposite to the driven side rotational force transmission element and rotates integrally with the driven shaft, and the driven side rotational force transmission element and the pressing part rotationally displace each other. In a friction continuously variable transmission in which the driven side rotational force transmission element is displaced in the direction away from the pressing part to bias the driving side rotational force transmission element toward the driving side rotational force transmission element, the driven side rotational force transmission element is displaced in the direction away from the pressing part. In addition, the rotational force transmission element on the driven side and the pressing portion are biased with a rotational torque larger than the rotation start time of the driven shaft so as to mutually rotationally displace the rotational force transmission element and the pressing portion.

[For production]

The biasing means biases the driven side rotational force transmission element and the pressing part to rotate relative to each other so that the driven side rotational force transmission element is displaced in a direction away from the pressing part. Therefore, even when starting rotation of the drive shaft, a frictional engagement force can be applied to each frictional engagement portion of the transmission means.

Even when the gear ratio is O and the force that causes the driven side rotational force transmission element to approach the pressing part is greater than the force in the opposite direction caused by the biasing means, the driven side rotational force transmission element The force that attempts to bring the drive unit closer toward the pressing part rotates the driven shaft via the biasing means, thereby causing mutual rotational displacement between the driven-side rotational force transmission element and the pressing part. A new urging force is generated that urges the driven side transmission element toward the drive side transmission element.

〔Example〕

Referring to FIG. 1, reference numeral 1 denotes an input shaft, which is a drive shaft, on which an input disk 2, which is a drive-side rotational force transmission element, is integrally formed.A pulley 181 is attached via a hub 180. Rotational force is transmitted from the vehicle running engine through the vehicle. Reference numeral 3 denotes an output shaft that is a driven shaft provided coaxially with the input shaft 1, has an output disk 4 that is a driven-side rotational force transmission element, and also serves as the shaft of the refrigerant compressor 100. The output disk 4 is movable relative to the output shaft 3 in the direction of the axis A and in the circumferential direction. 5 is a planetary rotor, which is provided around the axis A of the input shaft 1 and output shaft 3, rotates on its own axis and revolves around the planet, and changes the rotational speed from the input shaft by changing the revolution speed of the planetary rotor 5. can do. Reference numeral 6 denotes a continuously variable transmission housing, which is fixed to the front side 101 of the compressor 100 by bolts (not shown).

The planetary rotor 5 includes a conical portion 5a having an obtuse apex angle, a disk portion 5b coaxially and integrally provided at the bottom of the conical portion 5a, and a disk portion 5b coaxially and integrally provided at the bottom of the disk portion 5b. It is equipped with a mounting shaft 5C. The planetary rotor 5 has three transmission surfaces.

The first transmission surface 10 is a side surface of a disk portion 5b provided coaxially with the conical bottom surface, and its cross-sectional shape is concave so as to frictionally engage with the input disk 2. Second transmission surface 1
Reference numeral 1 denotes the peripheral edge of the bottom surface of the conical portion 5a, which is a flat ml or nearly flat surface, and is frictionally engaged with the output disk 4. Third
The transmission surface 12 is a side surface of the conical portion 5a, and frictionally engages with a speed change ring 13, which will be described later. When the planetary rotor 5 is attached, the generatrix of the conical portion 5a on the side that contacts the speed change ring 13 is substantially parallel to the axis A. Reference numeral 13 denotes a speed change ring surrounding the plurality of planetary rotors 5, which is movable in the direction of the axis A, but is non-rotatably supported by the housing 6, and is frictionally engaged with the third transmission surface 12 of the planetary rotors 5. By moving in the direction of axis A, the gear ratio can be changed. The planetary rotor 5 is rotatably mounted to the holder 14 via a mounting shaft 5c with an appropriate clearance. The holder 14 is annular and has a truncated conical shape,
A plurality of planetary rotors 5 are interconnected and rotatably provided around an axis A.

Referring to FIGS. 1 and 2, the pressing force generating means 30
is a hub 32 disposed opposite to the output disk 4, a steel ball 33 and a torsion coil spring 35 disposed between the output disk 4 and the hub 32, and a torsion coil spring 35 that is press-fitted into the outer periphery of the hub 32 to prevent the steel ball 33 from falling off. A ring 31 is provided for prevention.

Referring to FIGS. 2 and 3, the torsion coil spring 35 is a coil spring made by winding a wire with a rectangular cross section about three turns, and one end 35a and the other end 35b protrude in the radial direction.

Referring to FIGS. 4 and 5, a first annular recess 34 is formed on the output disk 4 facing the hub 32, and a torsion coil spring 35 is disposed within the first annular recess 34. (see figure). A first annular protrusion 36 is formed in contact with the outer periphery of the first annular recess 34, and three first cam grooves 37 are formed on the first annular protrusion 36 at equal intervals. Further, a first locking barrel 38 for locking one end 35a (see FIG. 3) of the torsion coil spring 35 is formed on the first annular convex portion 36. On the other hand, referring to FIGS. 6 and 7, on the hub 32 facing the output disk 4, a second annular four part 39 is formed corresponding to the first annular recess 34 of the output disk 4. A torsion coil spring 35 is disposed within the annular recess 39 (see FIG. 2). Second annular recess 3
A second annular protrusion 40 is formed from the outer periphery of the hub 32 to the outer circumferential edge of the hub 32, corresponding to the first annular protrusion 36 of the output disk 4. , and a second cam groove 41 is formed corresponding to the first cam groove 37. Further, a second locking groove 42 for locking the other end 35b (see FIG. 3) of the torsion coil spring 35 is formed on the second annular convex portion 40.

Referring to FIGS. 5 and 7, the first and second cam grooves 37, 41 have one end 37a formed in an arc shape,
41a, and a linear portion 37b extending linearly and inclined from the arcuate portions 37a and 41a toward the other end.

41b. The steel ball 33 is held between the first and second cam grooves 37 and 41 (see Figs. 8 and 9).
(see figure).

FIG. 8 shows a state in which the pressing force generating means 30 is not generating pressing force, and the steel ball 33 is held between the first cam groove 37 and the arcuate portions 37a and 41a of the second cam groove 41. ing. When the output disk 4 starts rotating, the output disk 4 and the hub 32 are displaced relative to each other in the circumferential direction as shown in FIG.
, 41 and generates a pressing force F in the direction of the axis A and a pressing force F2 in the opposite direction. The magnitudes of Fl and F2 are equal. This pressing force Fl is calculated as follows. Referring to FIG. 10, α is the center angle indicating the displacement of the steel ball 33 from the center of the arcuate portion 37a of the first cam groove 37, γ is the distance from the steel ball 33 to the center of the output disk 4, and is the transmission torque Let T be steel ball 3
The force F3 applied to the first cam groove 37 in the direction of the first cam groove 37 is determined by the following equation.

F ko ” □ eO5α γ Referring to Figure 11, the first and second cam angles are 37°4
If the inclination of the straight portions 37b and 41b of 1 is θ, then the axis A
The pressing force F1 in the direction is calculated by the following equation.

This pressing force F1 is the pressing force F required for friction transmission of the transmission.
. It is set to a slightly larger value.

Referring to FIG. 2, the torsion coil spring 35 has one end 35a.
is locked in the first locking groove 38 and the other end 35b (see FIG. 3) is locked in the second locking spring 42, so that the first and second annular recesses 3
4, 39. The torsion coil spring 35 is connected to the output disk 4 so that the steel ball 33 rides on the linear portions 37b and 41b of the first and second cams 37 and 41, and the pressing force generating means 30 generates a pressing force in the direction of the axis A. The hub 32 is urged to rotate in the direction B in FIG. 4 and in the direction C in FIG. 6, respectively. The rotational torque Ts provided by the torsion coil spring 35 is set to a value slightly larger than the starting torque Tc of the compressor 100.

Referring to the first section, the hub 32 is attached to the output shaft 3 via a half-moon key 43 so as to be movable in the direction of the axis A. Thereby, the rotation of the output disk 4 is transmitted to the output shaft 3 via the steel ball 33, the hub 32, and the half-moon key 43. The right end surface of the hub 32 is supported by the valve plate assembly 107 via a needle type thrust bearing 55.
The thrust force applied to the hub 32 in the right direction of the axis A is received by the valve plate I to the assembly 107 via the thrust bearing 55.

A drive shaft 104 of the compressor 100 is connected to the output shaft 3 so as to rotate integrally therewith. The compressor 100 is a known wave plate type compressor, for example, as disclosed in Japanese Patent Application Laid-Open No. 57-1141.
It is disclosed in Publication No. 84. A disk-shaped wave plate 105 is attached to the drive shaft 104 so as to be integrally rotatable,
Both sides of the wave play 1-105 are formed with wave-shaped concave portions and convex portions along the circumferential direction. piston 1
The two rollers 102 and 103 attached to 06 are
It is rotatable around axes G and H, and a wave plate 105 is sandwiched between these two rollers 102 and 103. A plurality of pistons 106 are arranged along the circumference of the wave plate 105 at equal distance intervals.

The piston 106 can reciprocate left and right in the direction of the axis A. The compressor drive shaft 104 rotates and the wave plate 10
5 rotates, the wavy unevenness of the wave plate 105 causes the bislin 106 to reciprocate. This results in
The refrigerant sucked in from the suction passage 110 passes through the housing 6, is compressed into high-temperature, high-pressure gas refrigerant within the compressor 100, and is discharged from the discharge passage 111, after which it is circulated through the cooling system. .

The input shaft 1 is rotatably attached to the housing 6 via a radial bearing 50, and when the input shaft 1 rotates, the input disk 2 rotates in conjunction with it, causing the plurality of planetary rotors 5 to rotate. Since the speed change ring 13 is attached so that it cannot rotate, that is, cannot be rotated in the circumferential direction, the planetary rotor 5 rotates and the speed change ring 1
3, and frictionally engages with the output disk 4 to transmit rotation thereto.

The distance from the axis A of the input shaft l and the output shaft 3 to the contact point between the input disk 2 and the first transmission surface 10 is 8, and the distance to the contact point between the output disk 4 and the second transmission surface 11 is f,
The distance to the contact point between the speed change ring 13 and the third transmission surface 12 is d, the distance from the center of the mounting shaft 5c to the contact point between the input disk 2 and the first transmission surface 10 is b, and the output disk 4 and the contact point of the second transmission surface 11 is e,
If the distance to the contact point between the speed change ring 13 and the third transmission surface 12 is C, the speed change ratio is a(c4-ed)/f (
ac + bd). Therefore, gear ring 1
3 in the central axis direction, the radius C
can be changed and the speed can be changed. Note that the position c=ed/f is the only position where the gear ratio is O. In FIG. 1, if the speed change ring 13 is moved to the right, the speed change ratio becomes smaller, and the speed change ratio becomes 0 at the position indicated by the two-dot chain line in FIG.

The rotation of the output disk 4 is transmitted to the output shaft 3 via the steel ball 33, the hub 32, and the half-moon key 43.

At this time, the output disk 4 and the hub 32 are displaced relative to each other in the circumferential direction according to the load on the output shaft 3, so that the steel ball 33 moves into the straight portion 3 of the 1i and 2nd cam grooves 37°41 as described above.
7b and 4.1b, so the pressing force F in the direction of axis A
, , generate F2. This pressing force F.

As a result, the output disk 4 is pressed against the planetary rotor 5, and a frictional engagement force corresponding to the load is applied to each friction transmission section.

When the gear ratio is not 0 and the rotation of the input shaft 1 is transmitted to the output shaft 3, the output disc 4 and the hub 3 are connected as described above.
2 and 2 rotate relative to each other according to the load on the output shaft 3. Therefore, the output disk 4 is pressed against the planetary rotor 5 with a pressing force F according to the load, and each friction transmission part has friction according to the load. Provides engagement force.

On the other hand, when the speed change ring 13 is in the position shown by the two-dot chain line in FIG. 1 and the speed change ratio is O, the output disk 4 does not rotate. Therefore, the pressing force with which the pressing force generating means 30 presses the output disk 4 against the planetary rotor 5 is the pressing force L generated by the relative displacement in the rotational direction between the output disk 4 and the hub 32 due to the biasing force of the torsion coil spring 35. (See Figure 2).

On the other hand, when the gear ratio is O, the revolution speed Wc of the planetary rotor 5 is the fastest and is given by the following equation.

Wc = (ac/ (ac + bd)) W H where W is the rotational speed of the input shaft 1. Therefore, as shown in FIG. 12, a large centrifugal force FA acts on the planetary rotor 5. Since the slanted planetary rotor 5 attempts to displace upward in the figure (in the J direction in the figure) using the contact point 60 with the speed change ring 13 as a fulcrum, a biasing force K acts on the output disk 4 in the right direction in the figure. 6 If the rotation speed of the human power shaft 1 is relatively low, the planetary rotor 5
The centrifugal force FA acting on is relatively small, and in FIG.
is smaller than the force generated by the torsion coil spring 35 that tends to displace the output disk 4 to the left, the output disk 4 is urged against the planetary rotor 5 with a force of (L-K). A frictional engagement force is applied to each friction transmitting portion, and the planetary rotor 5 can maintain a normal orbit, and there is no fear that the input disk 2 and the planetary rotor 5 will disengage.

As the rotational speed of the input shaft 1 increases, the centrifugal force FA acting on the planetary rotor 5 increases, and the force K that tends to displace the output disk 4 to the right in FIG. If the force trying to displace the wetted output disk 4 to the left is greater than the force, the output disk 4 will be displaced only slightly to the right in the figure. As a result, a force that deforms the torsion coil spring 35 in the direction opposite to the rotational torque generation direction of the torsion coil spring 35 acts on the torsion coil spring 35, but as described above, the biasing torque Ts of the torsion coil spring 35 is equal to the starting torque T of the compressor 100.
Since it is set slightly larger than c, the output shaft 3 is caused to rotate slightly by the force via the torsion coil spring 35.

The rotation of the output shaft 3 causes a relative displacement in the circumferential direction between the output disc 4 and the hub 32, and the steel ball 33 rides on the cam shaft 37°4], causing the output disc 4 to move to the left in FIG. A new stress force M pressing in the direction is generated.

Therefore, the output disk 4 is displaced only slightly to the left in FIG. 12. By repeating the above operations, a frictional engagement force is applied to each frictional engagement portion of the planetary rotor 5. Incidentally, the displacement of the output disk 4 is very small, and therefore the planetary rotor 5 can maintain a normal orbit, and there is no fear that the input disk 2 and the planetary rotor 5 will disengage.

In this embodiment, a torsion coil spring is used as the biasing means, but a thin coil spring, a compression coil spring, etc. may also be used.

Further, the load driven by the output shaft is not limited to the compressor, and may be any other load.

〔Effect of the invention〕

As described above, according to the present invention, even when the gear ratio is O, it is possible to prevent the frictional engagement of various parts of the transmission means from disengaging.

[Brief explanation of drawings]

Figure 1 is a longitudinal sectional view of a friction continuously variable transmission with a compressor attached to the output shaft, Figure 2 is an enlarged sectional view of the pressing force generating means, Figure 3 is a plan view of the torsion coil spring, and Figure 4. is a plan view of the output disk viewed from the direction facing the hub, FIG. 5 is a sectional view taken along line V-V in FIG. 4, FIG. 6 is a plan view of the hub, and FIG. Figures 8 and 9 are side views of the pressing force generating means, with Figure 8 showing a state in which no pressing force is being generated, and Figure 9 showing a state in which no pressing force is being generated. 10 and 11 are diagrams showing a method of calculating the pressing force; FIG. 12 is an enlarged view of the vicinity of the planetary rotor to explain the operation of this embodiment; FIG. 13 is a sectional view of a main part of a conventional i-friction continuously variable transmission. 1...Input shaft, 2...Input disk, 3.
...Output shaft, 4...Output disk, 5...
・Planetary rotor, 30...pressing force generating means, 32・
...Hub, 33... Steel ball, 35... Torsion coil spring.

Claims (1)

[Claims] a drive shaft rotatably provided around an axis; a drive-side rotational force transmission element provided on the drive shaft and rotating integrally with the drive shaft; and a drive-side rotational force transmitting element rotatably provided around the axis and facing the drive shaft. a driven shaft provided coaxially with the driving shaft; a driven side rotational force transmission element provided on the driven shaft and movable relative to the axial direction and circumferential direction of the driven shaft; and the driving side. a transmission means provided between the rotational force transmission element and the driven side rotational force transmission element, and configured to frictionally engage with the driving side and driven side rotational force transmission elements to transmit rotational force;
pressing force generating means for urging the driven side rotational force transmission element toward the driving side rotational force transmission element and transmitting rotation of the driven side rotational force transmission element to the driven shaft, The pressing force generating means includes a pressing part that is arranged opposite to the driven side rotational force transmission element and rotates integrally with the driven shaft, and the driven side rotational force transmission element and the pressing part are mutually rotationally displaced. In the friction continuously variable transmission, the driven-side rotational force transmission element is displaced in a direction away from the pressing portion and biased toward the drive-side rotational force transmission element, by A rotational torque greater than a rotation start torque of the driven shaft is used to rotationally displace the driven-side rotational force transmission element and the pressing part relative to each other so that the force transmission element is displaced in a direction away from the pressing part. A continuously variable friction transmission equipped with a biasing means for biasing.