JPH0921449A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the slip loss, and to realize the quick change of speed. SOLUTION: This continuously variable transmission continuously changes the rotating speed ratio between an input shaft 11 and an output shaft 15. A sun gear 12 is integrally fitted with the input shaft 11, and an annular ring gear 13 having an inner gear and an outer gear is supported by the same shaft with the input shaft 11, freely to be rotated. Epicyclic gears 14 are engaged between the sun gear 12 and the inner gear of the ring gear 13, and the output shaft 15 having a bearing part 15a, which supports the epicyclic gears 14 freely to be rotated, is supported by the same shaft with the input shaft 11. A control gear 16 is engaged with the outer gear of the ring gear 13, and an operating shaft of a control motor is connected to a shaft 17 of the control gear 16. In the case where the constant rotation is given to the input shaft 11 by an external driving source, the rotation of the ring gear 13 is controlled by the control motor through the control gear 16 so as to desirably control the rotation of the output shaft 15.

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 for continuously changing a rotational speed ratio between input and output shafts, and more particularly to a continuously variable transmission using a planetary gear device.

[0002]

2. Description of the Related Art A planetary gear system is a device in which a pair of gears rotate by meshing with each other, and at the same time, a bearing portion supporting the shaft of one gear rotates about the shaft of the other gear. Generally, a sun gear, a planetary gear, an internal gear (ring gear) and the like are provided, and the planetary gear revolves around the sun gear attached to the central shaft while rotating around the sun gear.

As a speed reducer using such a planetary gear device, those shown in FIGS. 4 (a) to 4 (c) are known.

In FIG. 1A, the rotational power is input to the sun gear 1, the internal gear 2 is fixed, and the bearing member 4 of the planetary gear 3 is fixed.
FIG. 1B shows a planetary type speed reducer configured to output rotational power decelerated from the planetary gear 3 by fixing the sun gear 1 by inputting the rotational power to the internal gear 2. The solar type speed reducer configured to output the rotational power decelerated from the member 4 is shown in FIG. 1C, in which the rotational power is input to the sun gear 1 and the bearing member 4 of the planetary gear 3 is fixed. 1 shows a star-type speed reducer that outputs rotational power reduced from the internal gear 2.

In these speed reducers, the rotational speed ratio (speed reduction ratio) between the input and output shafts is fixed and cannot be changed arbitrarily.

As a continuously variable transmission capable of arbitrarily changing the rotation speed ratio between the input and output shafts, there is a continuously variable transmission in which a planetary mechanism is constituted by using a friction wheel or a combination of a friction wheel and a gear. , A mechanism for positionally moving the constituent members (friction wheels or gears) is provided and its relative position is changed, for example, the revolution orbit radius of the planetary wheel (friction wheel) is changed to change the speed. Things are known.

[0007]

As described above, there are various speed reducers using the planetary gear device.
There has been no continuously variable transmission using a planetary gear device.

Further, in the conventional continuously variable transmission using a planetary mechanism using a friction wheel, slip loss at the frictional contact portion cannot be ignored, and the power transmission efficiency is low and the gear shift cycle is short. However, there is a problem in that the structure is complicated because a mechanism for positionally moving the constituent members is required.

Particularly, in a press machine or the like, from the viewpoint of suppressing noise or improving product quality,
It is desired to freely change the moving speed of the ram (the member to which the moving side of the mold is attached) according to the material to be processed (work), but as a continuously variable transmission used for this,
Since it is necessary that the slip loss is small and the shift response is excellent, it is not possible to meet such a demand at present.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a continuously variable transmission which has a small slip loss and is suitable for high speed shifting.

[0011]

In order to solve the above-mentioned problems, a continuously variable transmission for continuously changing the rotation speed ratio between the input shaft and the output shaft is constructed as follows.

That is, a sun gear having external teeth is rotatably provided, a control gear having external teeth is rotatably provided, and at least one planetary gear having external teeth meshed with the external teeth of the sun gear. Bearing means for rotatably supporting the planetary gears are provided rotatably coaxially with the sun gear so as to rotate with the revolution of the planetary gears, and external teeth meshed with the control gears are provided. An annular ring gear, which has an inner tooth meshed with each outer tooth of the planetary gear, is rotatably provided coaxially with the sun gear.

A drive means for rotationally driving the control gear and a control means for controlling the drive means are provided to connect the sun gear to the input shaft and the bearing means to the output shaft.

In the above construction, the drive means for rotationally driving the control gear and the control means for controlling the drive means are eliminated, and the drive means for rotationally driving the sun gear and the control means for controlling the drive means. And the control gear can be connected to the input shaft.

[0015]

According to the present invention, the rotational power input to the input shaft is transmitted to the output shaft through the sun gear (or control gear and ring gear), the planet gear and the bearing means, and the drive gear and the control means control the gear. By driving and controlling the rotation of the ring gear (or the sun gear) via the, the revolution of the planetary gear is controlled and the rotation of the output shaft is arbitrarily changed.

Therefore, since the device is composed of gears without using any friction wheel, there is no slip loss, and the output shaft can be rotated at any rotation speed by controlling the rotation of the ring gear (or sun gear) by the drive means. Can be obtained, and high speed shifting is possible. Further, unlike the prior art, there is no need to move the relative position between the members for shifting, so the structure is simple.

According to the continuously variable transmission of the present invention, it is theoretically possible to stop the output shaft in a state where the input shaft is rotated at a constant speed. In some cases, however, it may be necessary to provide a braking means for braking the output shaft, as it may not stop completely and cause inconvenience.

Further, if a detecting means for detecting the rotational speed of the output shaft is provided and the rotation of the control gear (or the sun gear) by the driving means is feedback-controlled based on the detection value of the detecting means, Even if the rotation of the input shaft is not constant, it is possible to realize highly accurate constant rotation of the output shaft.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First, the schematic construction of an embodiment of the present invention will be described with reference to FIGS. In FIG.
Is an input shaft to which the rotational driving force to be changed is input, the input shaft 11 is rotatably supported, and the sun gear 12 having external teeth is coaxially rotated integrally with the input shaft 11. Is installed as. Reference numeral 13 is a ring gear having outer teeth and inner teeth, and the ring gear 13 is rotatably supported coaxially with the input shaft 11 (sun gear 12).

Reference numeral 14 denotes a plurality of (three) planetary gears having external teeth, and the planetary gears 14 have their outer teeth meshed with the outer teeth of the sun gear 12 and the inner teeth of the ring gear 13. Reference numeral 15 denotes an output shaft that outputs rotational power that has been changed in speed.
Is rotatably supported coaxially with the input shaft 11 (sun gear 12). Further, the output shaft 15 is integrally formed with the bearing portion 15
The bearing portion 15a rotatably supports the planetary gear 14.

Reference numeral 16 is a control gear having external teeth, and the external teeth of the control gear 16 are meshed with the external teeth of the ring gear 13. A control shaft 17 is integrally fixed to the control gear 16, and the control shaft 17 is rotatably supported. Also,
Although not shown, the control shaft 17 is connected to an operating shaft of a control motor whose rotation can be freely controlled by a control means such as a microcomputer.

The figure shows a case where the continuously variable transmission configured as described above is applied to a press working machine, in which a general-purpose motor as a rotary power source for constant rotation is connected to the input shaft 11 and output. The crank shaft 18 of the crank mechanism of the press machine is connected to the shaft 15. Control gear by control motor 1
By appropriately controlling the rotation of the ring gear 13 via 6, it is possible to arbitrarily control the vertical movement of the ram (which mounts the moving side of the mold) connected to the crankshaft 18 of the crank mechanism. .

Next, with reference to FIG. 2 and FIG. 3, the specific constitution of the embodiment of the present invention will be described in detail. It should be noted that the same reference numerals are given to the substantially same components as those shown in FIG. 1 for description.

In the figure, 21 is a casing that accommodates the main part of the continuously variable transmission, and 22 is a flywheel for transmitting input power. The flywheel 22 has a plurality of grooves 22a for the V belt, and the plurality of V belts are wound between the flywheel 22 and a wheel of a general-purpose motor (not shown) as a drive source (input power source). The rotation driving force of the general-purpose motor is transmitted to the flywheel 22 by being rotated.

The flywheel 22 rotates integrally with the input shaft 11 by a key 23, an end cap 24 and a mounting bolt 25 near one end of the input shaft 11 provided inside and outside the casing 21. It is installed.

The input shaft 11 has a bearing 26 at its middle portion.
The input shaft 11 is rotatably supported by the casing 21, and the vicinity of the end of the input shaft 11 on the inner side of the casing 21 is supported by a hollow portion hollowed out of the output shaft 15 via a pair of bearings 27. There is. Output shaft 15 is bearing 2
8 is rotatably supported by a brake casing 29 that also serves as a lid of the open portion of the casing 21. At the end of the input shaft 11 on the inner side of the casing 21, the input shaft 1
A nut 30 with a slit is screwed to prevent the bearing 1 from coming off from the bearing 27. The brake casing 29 is fixed to the casing 21 with bolts 31.

The sun gear 12 is mounted on the input shaft 11 via a key 32 so as to rotate integrally therewith.
A plurality of planet gears 14 are meshed with the sun gear 12, and these planet gears 14 are rotatably supported by a planet shaft 34 via a slide bearing 33. One end of the planet shaft 34 is one end of the output shaft 15. Bearing part (flange part) 15 formed on
a is supported by a and the other end is supported by the bearing 35 on the input shaft 11.
It is supported by a support arm 36 that is rotatably attached via. With such a configuration, the planetary gear 14 rotates about the planetary shaft 34 and revolves around the outer periphery of the sun gear 12.

An annular ring gear 13 is provided so as to position each planet gear 14 inside thereof. The ring gear 13 has an inner tooth 13a and an outer tooth 13b, and each planet gear 14 is meshed with the inner tooth 13a. The inner teeth 13a and the outer teeth 13b are not necessarily integral with the main body of the gear, but the main body and the tooth may be separately configured and integrated by a bolt or the like. The external teeth 13b are not necessarily spur gears, but may be helical gears, bevel gears, or the like.
The ring gear 13 is formed with three snap ring pressing holes 13c.

One end of the ring gear 13 is rotatably supported by the input shaft 11 via a bearing 37, and the other end of the ring gear 13 has a ring gear cap 3
8 is integrally attached by a bolt 38a,
The ring gear cap 38 is rotatably supported on the output shaft 15 via a bearing 39.

An idle gear 40 is meshed with the outer teeth 13b of the ring gear 13. The idle gear 40 is rotatably supported by an idle shaft 41 fixedly provided in the casing 21 via a slide bearing 42, and the idle gear 40 is in mesh with the control gear 16. The control gear 16 is integrally attached to the control shaft 17 via a key 43, and the control shaft 17 has a pair of bearings 44.
It is rotatably supported by the casing 21 via.

The casing 21 is formed with a push-in port required when the idle gear 40 and the control gear 16 are assembled, and this push-in port is closed by attaching an upper lid 45 to the casing 21 with a bolt 46. .
Further, the casing 21 includes an idle shaft 41 and a control shaft 1.
The push ports required for assembly of 7 are formed,
These push-in ports are closed by attaching caps 47 and 48 to the casing 21 with bolts 49, respectively.

A motor mounting portion is formed near the control shaft 17 of the casing 21, and a control motor (servo motor, pulse motor, hydraulic motor, etc.) 50 is detachably mounted on the motor mounting portion. There is. The operating shaft of the control motor 50 is at one end of the control shaft 17 of the control gear 16,
For example, they are connected by a coupling (shaft coupling).
The control motor 50 is provided with a lock mechanism that selectively locks or unlocks the operating shaft of the control shaft in the state where no voltage is applied, and the rotation speed, the rotation direction, and the lock mechanism are controlled by a control unit such as a microcomputer not shown. Is controlled.

A brake mechanism for braking the output shaft 15 is housed inside the brake casing 29.
That is, a spline shaft 51 having a plurality of protruding teeth is attached to the output shaft 15 so as to rotate integrally via a key 52, and the spline shaft 51 is provided with spline groove teeth. A pair of brake friction plates 5
3 is attached so as to rotate integrally with the spline groove teeth fitted to the teeth of the spline shaft 51. Reference numeral 54 denotes a cylindrical ring for preventing the movement of the spline shaft 51. The output ring 15 is arranged so as to be inserted therein, and the stop ring 55 is engaged with a stop ring groove formed on the output shaft 15. By combining
It is attached to the output shaft 15.

A fixed-side friction plate 56 is provided so as to be sandwiched between a pair of brake friction plates 53, and the fixed-side friction plate 56 meshes with a plurality of detent pins 57 provided in the brake casing 29. It is in a state and its rotation is prevented. Reference numeral 58 is a cylindrical brake pressing block, and the brake pressing block 58 is
The output shaft 15 and the cylindrical ring 54 are arranged so as to be inserted inside thereof, and are provided so as to be slidable along the output shaft 15 in the axial direction.

The brake pressing block 58 integrally has a receiving portion of the brake spring 59 and a braking portion 58a which also serves as a friction plate for braking, and one of the friction plates for braking 53 has fixed side friction. Board 56 and braking part 5
It is located so as to be sandwiched between 8a and 8a. The brake pressing block 58 is prevented from rotating by meshing with the anti-rotation pin 57 on the circumferential surface of the braking portion 58a.

In normal times, the brake friction plate 53
Since the fixed-side friction plate 56 is pressed by the brake pressing block 58 that is urged by the brake spring 59, the braking frictional force associated therewith causes the output shaft 15 to be in a braking state.

The braking of the output shaft 15 is released by operating the brake releasing air cylinder. That is,
The air cylinder for releasing the brake is the brake casing 29.
A cylinder 61 fixed by a bolt 60 and a piston 62 as an operating portion are provided. A head plate 63 is in contact with the piston 62, and the head plate 63 is integrally attached to the brake pressing block 58 by a bolt 64.

Reference numeral 65 is a piston 62 and a head plate 63.
The spring pin 65 prevents relative displacement in the rotational direction caused by the repeated operation of the piston 62.

The piston 62 has an air port 62a for attaching a pipe joint for sending air for releasing the brake into the cylinder 61. The pressure of the air that has entered through the air port 62a moves the piston 62 toward the head plate 63 side, and moves the head plate 63 and the brake pressing block 58 in the direction in which the brake spring 59 is compressed.

As a result, the pressing force from the braking portion 58a of the brake pressing block 58 to the brake friction plate 53 and the fixed side friction plate 56, that is, the braking force is released. A pair of seals 66a and 66b is provided between the cylinder 61 and the piston 62 to prevent air leakage.

A key 15b is provided at an end of the output shaft 15, and the output shaft 15 is coupled to a crankshaft (not shown) of a press machine as a load via the key 15b, for example, a coupling (shaft coupling). ) Are connected. Or,
A gear (not shown) may be fitted on the output shaft 15 so as to be engaged with the gear of the connecting portion of the crankshaft for connection.

Although not shown, the continuously variable transmission of the present embodiment is an encoder for detecting the rotational speed of the output shaft 15 or the crankshaft of a press machine connected to the output shaft 15, and the like.
A detector such as a tacho-generator is provided, and the detected value of this detector is input to a control means such as a microcomputer, and the control motor 50 is feedback-controlled based on this, thereby realizing highly accurate gear shifting. ing. Further, the control means also controls the supply or stop of supply of air for operating the brake releasing air cylinder.

Incidentally, the casing 21 is formed with a push-in port necessary for assembling the input shaft 11 and the like, and the push-in port is closed by attaching a cap 67 to the casing 21 with a bolt 68.

The operation of the continuously variable transmission of this embodiment will be described below.

The rotational force from a general-purpose motor (not shown) is V
It is transmitted to the flywheel 22 via the belt and the key 2
3 is transmitted to the input shaft 11 and is transmitted to the sun gear 12 via the key 32, and a rotational force is applied to the planetary gear 14 meshed with the sun gear 12. At this time, ring gear 1
3 is in an open state, that is, when the voltage is not applied to the control motor 50 and the lock mechanism of the control motor 50 is in an unlocked state, the planetary gears 14 only rotate and no revolution force is generated. The output shaft 15 is stopped.

The rotation directions of the planetary gear 14 and the ring gear 13 are opposite to the rotation direction of the sun gear 12 at this time. In this state, the ring gear 13 is included in the idle gear 40 meshed with the outer teeth 13b of the ring gear 13 and the control gear 16 meshed with the idle gear 40.
Rotational force is applied from the side.

When driving the crankshaft of a press machine, a large load is normally applied to the output shaft 15, so it is considered that the planetary gear 14 will not revolve, but safety and the like. From this viewpoint, it is necessary to obtain a complete stop state, so in this embodiment, the operation of the brake releasing air cylinder is released to forcibly brake the output shaft 15. The brake release air cylinder is operated in a state other than the state in which the output shaft 15 is stopped,
The output shaft 15 is in a non-braking state.

Next, when the ring gear 13 is stopped, that is, when no voltage is applied to the control motor 50 and the lock mechanism of the control motor 50 is locked, the planetary gear 14 revolves around its own axis. This revolution number is output shaft 1
The number of rotations is 5. At this time, the output shaft 15 rotates in the same direction as the sun gear 12.

When the control motor 50 applies the same direction and the same rotational speed as the sun gear 12 to the ring gear 13 from the control gear 16 side, the output shaft 15 has the same rotational speed and rotational direction as the sun gear 12. In addition, when the control motor 50 gives the ring gear 13 a rotation speed faster than that of the sun gear 12, the output shaft 15 has a speed-up effect. On the other hand, the control motor 50
As the ring gear 13 is rotated in the opposite direction to the sun gear 12 and the speed thereof is gradually increased, the output shaft 15 decelerates, then stops, and further reverses to increase its speed.

Here, the number of teeth of the sun gear 12 is Za, the number of revolutions of the sun gear 12 (the number of revolutions of the input shaft 11) is Ra, the number of teeth of the planetary gear 14 is Zb, and the revolution number of the planetary gear 14 is Rb.
If the number of inner teeth 13a of the ring gear 13 is Zc, the number of outer teeth 13b of the ring gear 13 is Zd, the rotation speed of the ring gear 13 is Rc, and the rotation speed of the output shaft 15 is Rz (Rz = Rb). The rotation conditions of the output shaft 15 are as follows. The rotation direction of the sun gear 12 is positive (+) and the opposite direction is negative (-).

(A) Constant velocity condition (Rz = Ra) The rotation of the control motor 50 is controlled so that the rotation speed Rc of the ring gear 13 becomes Rc = Ra. In addition,
In this case, the ring gear 13 rotates in the same direction as the sun gear 12.

(B) Deceleration condition (Rz <Ra) The rotation of the control motor 50 is controlled so that the rotational speed Rc of the ring gear 13 is-(Za / Zc) .Ra <Rc <Ra. In addition,
In this case, the ring gear 13 rotates in the same direction as the sun gear 12 or in the opposite direction. In particular, when the ring gear 13 is stopped, that is, the rotation speed of the ring gear 13 is Rc =
When set to 0, the rotation speed of the output shaft 15 is Rz = {1 / [(Zc / Za) +1]} · Ra.

(C) Stopping condition (Rz = 0) The control motor 50 is controlled so that the rotation speed Rc of the ring gear 13 is Rc =-(Za / Zc) .Ra. In this case, the ring gear 13 rotates in the opposite direction to the sun gear 12.

(D) Reverse rotation condition (Rz <0) The control motor 50 is controlled so that the rotation speed Rc of the ring gear 13 is Rc <-(Za / Zc) .Ra. In this case, the ring gear 13 rotates in the opposite direction to the sun gear 12.

(E) Speed-up condition (Rz> Ra) The control motor 50 is controlled so that the rotation speed Rc of the ring gear 13 is Rc> Ra. In this case, the ring gear 13 rotates in the same direction as the sun gear 12.

According to the continuously variable transmission of this embodiment, the rotational force input through the V-belt and the flyhole 22 from the general-purpose motor whose rotation speed and rotation direction are constant is applied to the sun gear 1.
2, the rotation of the ring gear 13 transmitted to the output shaft 15 via the planetary gear 14 and the control gear 16 and the idle gear 40
By controlling with the control motor 50 via
Since the output shaft 15 is provided with an arbitrary rotation speed and rotation direction and only the gear is used for transmitting power in the continuously variable transmission, there is no slip loss as in the prior art and a high speed is achieved. Gear shifting is possible. Moreover, unlike the prior art, the members are not moved in position, so that the structure is simple.

Further, since the rotation speed and rotation speed of the output shaft 15 and the like are detected and the control motor 50 is controlled based on the detected values, the rotation of the general-purpose motor as a power input source is accurately constant. Even if it does not happen, it is possible to obtain the required rotation of the output shaft 15.

Further, this continuously variable transmission is very suitable for driving the crank shaft of a press working machine, and the rotation of the crank shaft can be controlled accurately and freely, so that the press working during the working work can be performed. The vibration and noise of the machine can be suppressed, and the processing accuracy of the workpiece (workpiece) and the productivity can be improved.

In the above embodiment, the power from the general-purpose motor is transmitted to the input shaft 11 integrated with the sun gear 12, and the control shaft 17 of the control gear 16 is controlled to rotate by the control motor 50. , On the contrary, the control gear 16
It is possible to transmit power from a general-purpose motor to control the rotation of the input shaft 11 integrated with the sun gear 12 by the control motor.

Further, in the above-mentioned embodiment, the case where the present invention is applied to the press working machine is taken as an example, but the present invention is not limited to this, and when applied to an automobile or a ship, the rotation of the input shaft (power source) is changed. Forward, backward, without changing the number,
The present invention can be applied to all types of power devices, such as deceleration and acceleration, and further various driving operations by applying to bicycles and the like.

[0061]

Since the present invention is configured as described above, it is possible to provide a continuously variable transmission which has a small slip loss and is suitable for high speed shifting.

[Brief description of drawings]

1A and 1B are diagrams schematically showing a schematic configuration of an embodiment of the present invention, in which FIG. 1A is a sectional view, and FIG. 1B is a sectional view taken along the line AA of FIG.

FIG. 2 is a side sectional view showing a specific configuration of the embodiment of the present invention.

FIG. 3 is a sectional view taken along line BB of FIG. 2;

FIG. 4 is a diagram showing a configuration of a speed reducer using a general planetary gear device, in which (a) shows a planetary type, (b) a solar type, and (c) a star type.

[Explanation of symbols]

 11 input shaft 12 sun gear 13 ring gear 14 planetary gear 15 output shaft 15a bearing part 16 control gear 17 control shaft 18 crankshaft 19 ram 21 casing 22 flywheel 29 brake casing 34 planetary shaft 40 idle gear 50 control motor 53 brake friction Plate 56 Fixed side friction plate 58 Brake pressing block 59 Brake spring 61 Air cylinder 62 Piston

Claims (4)

[Claims] 1. A continuously variable transmission for continuously changing a rotational speed ratio between an input shaft and an output shaft, wherein a sun gear having external teeth is rotatably provided and a control gear having external teeth is rotatably provided. Providing at least one or more planetary gears having external teeth meshed with the external teeth of the sun gear, and bearing means for rotatably supporting the planetary gears so as to rotate with the revolution of the planetary gears. Provided rotatably coaxially with the sun gear, having an outer tooth meshed with the control gear, and an annular ring gear having inner teeth meshed with each outer tooth of the planetary gear, A rotatably provided coaxially with a gear, a drive means for rotationally driving one of the sun gear and the control gear, and a control means for controlling the drive means are provided, and the other of the sun gear and the control gear is provided with the input shaft. With coupling, continuously variable transmission, characterized in that the concatenation of the bearing means to the output shaft. 2. The continuously variable transmission according to claim 1, wherein at least one idle gear is interposed between the control gear and the ring gear. 3. The continuously variable transmission according to claim 1, further comprising braking means for braking the output shaft. 4. The detection means for detecting the rotation speed of the output shaft is provided, and the control means controls the drive means based on a detection value of the detection means. Continuously variable transmission.