JPS6032060B2 - Continuously variable transmission - Google Patents

Description

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

There are various types of conventional mechanical double-speed transmissions, each of which is used depending on the purpose and use.
There are some machines that cannot be shifted unless the vehicle is stopped, and even if the shift operation can be performed whether the vehicle is running or stopped, it requires a large space for installation.

For example, in order to obtain a convenient rotation speed, it may be necessary to use a reduction gear in addition to a trout-stage transmission, or even if a chicken-stage transmission is used between each transmission mechanism, the input shaft and output shaft If the installation space is large because the dorsal cores are not the same, or if you want to install a manual handle for idling for inspection when starting a general machine with a high reduction ratio, we recommend using a worm reducer. However, in such cases, it was necessary to install a clutch after the output of the worm reducer.

Furthermore, even if a gear type type has a high reduction ratio, its rotational force becomes large and extra force is required, and a dedicated speed increasing gear must be installed separately. Since the gear transmission has the above-mentioned problems and drawbacks, it is desired by those skilled in the art to develop an ideal bonito gear transmission that meets the conditions listed below. * Compact and can be directly connected to the motor in the same space as a motor with a reducer * The input shaft and output shaft are on the same axis so that it can be mounted with a through-hole * The speed change operation can be performed regardless of whether it is in operation or stopped. * Those that can be controlled remotely * Those equipped with a mechanism that reduces the rotation speed of the output shaft relative to the rotation speed of the input shaft without using a reducer * Those that have a wide speed change range * Multiple units For independent and synchronous operation of the machine, the output shaft can be moved freely by another power source even when the input ball is stopped. * There are no restrictions on the mounting/installation direction. * The entire device is sealed. For example, those that do not have belt wear or layer scattering, such as V-belt type gear transmission*
The mechanism is simple, the number of manufacturing steps is reduced, and the device can be manufactured at low cost.Therefore, the present invention is an ideal continuously variable transmission device that can satisfy the above-mentioned conditions as a result of studies in view of the defects and shortcomings of the above-mentioned subordinate mechanisms. The purpose of this is to provide an input shaft on the same axis as the output shaft, and a groove with a certain eccentricity on the input shaft. A crank mechanism consisting of a cam is installed to convert the rotational motion of the input shaft into a first reciprocating motion, which is further increased or decreased in distance by a second reciprocating motion, and by adjusting the fulcrum of the reciprocating muscle. Measure the increase or decrease in momentum, transmit the momentum to the output shaft via a one-way clutch by a swinging link muscle, and use the increase/decrease ratio during at least a part of the reciprocating motion to change the phase by arranging it radially. The intermittent motion of each link node is sequentially utilized and extracted as an intermittent rotational motion, and the output shaft is variably driven and rotated in one direction.

The present invention will be explained below with reference to one embodiment shown in the drawings.

1 to 7, an input shaft 1 is supported by a bearing 3 incorporated in a casing 2, and the casing 2 is fixed to a bolt 4 on the output side of a motor (not shown). The input shaft 1 has a pipe shape and is connected to a motor output shaft (not shown) by a saddle connection using a key (not shown) so that rotational force is transmitted coaxially.

A grooved plate 5 is provided on the input shaft 1 integrally or fixed as appropriate, and an eccentric groove 6 is provided in the grooved plate 5 in a circular shape with an eccentricity amount of S from the maricenter of the input koji. It is designed to rotate in synchronization with the input shaft 1. And in the eccentric groove 6 there is a slider 7.
In the illustrated example, a plurality of sliders 7 are placed in competition with each other at predetermined intervals, as shown in FIG. Radial guide holes 11 are provided in the adjustment plate 10 so that the roller 9 can be moved freely.
. . . are provided in the same number as the sliding elements 7, and are adapted to be moved by the rollers 9. Radial guide hole 11
. . . may be provided in a straight line as shown in Fig. 2, or may be provided in a curved form as shown in Fig. 7A, or may be freely rotatable around the pond edge as shown in Fig. 7B. Alternatively, if the roller 9 is of a sliding type, the roller may be formed into a round pin as shown in FIG. 7C in alignment with the guide hole 11.

The adjustment plate 10 is rotatably fixed to the casing 2 or 12 as will be described later, and as shown in FIG.
When the eccentric groove 6 rotates around the center O of the input shaft 1,
Even if the pin 8 passes through the slider 7 and is in the guide groove 11, the pin 8 is the shaft ○○
The crank mechanism 13 is configured to move sequentially with the input shaft 1 as a center, and thus constitutes a so-called crank mechanism 13 that converts the rotational motion of the input shaft 1 into a first reciprocating motion.

As shown in FIG. 3, one ends of the two links 14 and 15 are connected by a pin 16, the other end of one link 14 is rotatably connected to the pin 8 of the slider 7, and the other link The pond end 15 is rotatably fixed to a member 18 fixed to the casing 17 with a fixing pin 19, and as described above, the two links 14 and 15 are connected as a pair to the pin 8 of each slider 7 and the above. They are respectively fixed to the members 18 and constitute swing link units 20 that convert the first reciprocating motion into a second reciprocating motion.

That is, since the pin 8 of the slider 7 is guided by the guide hole 11 and performs the first reciprocating motion, as the slider 7 moves, the momentum 8' of the link joint 16 of the links 14 and 15 is as shown in FIG. As shown, it operates as a second reciprocating movement around the fixed pin 19.

More specifically, as shown in FIG. 6, the roller 9 in the guide hole 11 reciprocates between point a and point b at a rate of one reciprocation per revolution of the input shaft and the rotating grooved plate 5. Then,
The pins 16 of the links 14 and 15, which are chained to the roller 9 and the fixed pin 19, reciprocate at a rotation angle of 8'.

Therefore, in this working relationship, now the radial guide hole 1
Suppose that the adjusting plate 10 having a diameter of 1 is shifted from a point A to an end point in the figure with the crane center O of the input shaft 1 as the center. However, the position of the fixing pin 19 is assumed to be immovable. Then, the operating range of the pin 16 becomes H2, and when the guide position of the guide hole 11 is shifted to the position C, the operating range of the pin 15 of the link node becomes 83-, and in the same way, the position of the guide hole 11 is changed to In the position , the operating range of the pin 16 of the link node is equal to zero.

In this way, by steplessly changing the set position of the adjustment plate 10 from 2 to C, the operating range of the link pin 16 can be changed steplessly. Another method is to make the fixing pin 19 movable and adjust the adjustment plate 10.
Even if it is fixed, the same operating range as above can be obtained.

The above-mentioned link unit is a combination of at least two units, and the operation of each unit corresponding to the speed increase/decrease of each link pin 16 is sequentially synthesized and utilized. Then, an externally toothed ratchet 2 is provided on the output shaft 21 with the axis 0 as the center.
Attach the claw arm 2 to the pin 16 of each link node so that the claw arm 2 engages with the pin 16 of each link node.
3 are connected, and the pawl arm 23 is always pressed into engagement with the ratchet 22 by a spring 24 grounded to the link 14 or 15.

Further, the ratchet 22 may have internal teeth, but in this case, the amount of rotation of the output shaft is reduced. In this way, the one-way clutch 25 is configured to transmit the second reciprocating motion to the output shaft 21 as an intermittent rotational motion. And in this specific example, ratchet 2
The ratchets are arranged in a row in order to increase the strength, and the phases of the peaks and valleys of each ratchet are shifted as shown in Figure 8. It is set as.

In addition, since the power transmission method of the claw arm 23 is to operate by pushing or pulling, the shape of the tip of the claw arm 23 is appropriately used as shown in A or B in FIG. Things or how to use speed curves, etc.
Furthermore, it can be arbitrarily determined depending on the rotational direction of the eccentric groove 6 and the rotational direction of the output shaft.

Also, steel balls 26 are attached to the inner flaps of the ratchets 22' and 22''.
A groove 27 into which the ratchets are inserted approximately half way is provided, and the rotational force of the ratchets 22', 22'' is transmitted to the output shaft 21 via a steel ball 26.
The transmission force is adjusted by the strength of a spring 28 interposed to push the steel ball 26 into the groove 27, and the spring 28 is used as a torque limiter.

The speed change control is made possible by changing the phase of the adjusting plate 10. As for the phase changing method, the pin 31 disposed on the feed nut 31 incorporated in the adjusting screw 29 in FIGS. 9 and 5 is connected to the adjusting plate 10. 101 is fixed, and the adjustment plate 10
This is done by rotating the adjustment plate, whose outer peripheral surface is rotatably fitted into the casing 12 and is the same as the core of the input/output shafts 1 and 21, by the rotation of the adjustment screw 29. There is.

As explained above, in the present invention, the driving input shaft 1 having the grooved plate 5 on the outer periphery of one end and the output bag 21 having the adjusting plate 10 arranged on the outer periphery of one end are connected to both shafts. The core wires are aligned in a straight line, and the grooved plate 5 and adjustment plate 10
The grooved plate 5 is disposed relative to each other so as to face each other, and an eccentric groove 6 having an eccentricity with respect to the above-mentioned both axes D line is formed on the plate surface of the grooved plate 5 facing the adjusting plate 10. Adjustment plate 1
A guide hole 11 is bored in the plate surface of the pin 9, which is radial with respect to both axes. In the engaged state, it is slidably inserted into the guide hole 11 of the adjustment plate 10, and a clutch 25 for rotating the output shaft is installed on the outer periphery of the output ball 21, and the clutch 25 and the The other end of the sliding pin 9 is connected via a swinging link unit 20 that swings parallel to the plate surface of the adjustment plate 10, so that the following effects can be obtained. It will be done.

* Since the grooved plate 5 and the adjusting plate 10 are located on the outer periphery of the input shaft 1 and the output shaft 21, respectively, when these two shafts 1 and 21 are arranged in a straight line, it is possible to place the two shafts 1 and 21 in close proximity. Therefore, when compared with this type of device in which a power conversion and transmission mechanism is interposed between the two distances, the device does not become long, and the gear shift adjustment is not performed by sliding the adjustment plate 10 in the direction of the bag.
Since the structure is such that the adjustment is made by rotation, the adjustment space in the ball direction can be omitted in this respect as well, and as a result, compactness can be realized such as direct connection to a motor in the same space as a motor with a reduction gear.

* Since the input shaft 1 and the output shaft 21 are aligned on the same axis in the above state, through-shaft mounting can be performed.

* The speed change adjustment performed via the adjustment plate 10 is possible regardless of whether the machine is in operation or stopped, and the adjustment plate 10 can be easily controlled remotely through an appropriate operating means.

* The shifting range is determined by setting the eccentricity of the individual D grooves 6 in the grooved plate 5, and a wide shifting range can be obtained simply by increasing the eccentricity.

*Even if the input shaft 1 is stopped, the output shaft 21 can be freely moved by other power sources, and can be used depending on the purpose. * No restrictions on mounting or installation direction.

*Unlike the belt method, the entire device can be sealed,
Of course, there is no wear and tear like there is on the belt, and there is no scattering of debris.

* The grooved plate 5, the adjusting plate 10, the pin 9 with the slider 7, the swinging link unit 20, etc. are all parts with a simple structure, so they can be made into a device at low cost by reducing the number of manufacturing steps, and these parts can be made into a three-dimensional structure. The structure does not become complicated when assembled.

* Since the pin 9 with the slider 7 only moves in the guide hole 11 and no centrifugal force acts on it, the adjusted state of the pin 9 is adjusted by the distance D force via the adjustment plate 10. There is no fluctuation in speed, and there is no early structural damage due to centrifugal force, so the stability of the gear shift adjustment state and the durability of the structure can be ensured.

Therefore, according to the present invention, all the ideal conditions for a trout gear transmission can be satisfied.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view showing a concrete example as a first embodiment of the continuously variable transmission according to the present invention, FIG. FIG. 4 is a front view showing the swinging link unit in the continuously variable transmission, FIG. 4 is a cross-sectional view showing the one-way clutch of the continuously variable transmission, and FIG. 5 is a cross-sectional view showing the speed change adjustment mechanism of the continuously variable transmission. A top view, Fig. 6 is a diagram of the operating principle of the continuously variable transmission, Fig. 7A,
B and C are front views showing a modification of the radial guide groove in the same continuously variable transmission; FIGS. 8A and B are front views showing a modification of the pawl arm of the one-way clutch in the same continuously variable transmission;
FIG. 9 is a longitudinal sectional side view showing the speed change adjustment mechanism of the continuously variable transmission. 1... Input shaft, 5... Grooved plate, 6...
... Eccentric groove, 7 ... Sliding element, 9 ... Pin, 10 ... Adjustment plate, 11 ... Guide hole, 14, 15.
... Link, 20 ... Swinging link unit, 21 ... Output shaft, 25 ... Direction clutch, 0
...The center of the input shaft and output shaft. Figure 2 Figure 3 Figure 1 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Figure 9

Claims (1)

[Claims] 1. A driving input shaft having a grooved plate on the outer periphery of one end and an output shaft having an adjustment plate loosely fitted on the outer periphery of one end have their center lines aligned in a straight line, and The grooved plate and the adjusting plate are arranged relative to each other so as to face each other, and an eccentric groove having an eccentricity with respect to the above-mentioned both axis centers is formed on the plate surface of the grooved plate facing the adjusting plate. At the same time, a guide hole is bored in the plate surface of the adjustment plate, and the guide hole is radial with respect to the above-mentioned both axes. In this state, the output shaft is slidably inserted into the guide hole of the adjustment plate, and a one-way clutch for rotating the output shaft is installed on the outer periphery of the output shaft, and the clutch and the other end of the slider pin are connected to each other. A continuously variable transmission characterized by being connected via a swinging link unit that swings parallel to the plate surface of an adjustment plate.