JPH06300093A - Rotation transmitting mechanism - Google Patents

Abstract

PURPOSE:To prevent the input of the torque in the normal and reverse direction from a side to be driven by interposing a constraining means in a gear train, which is formed by combining plural gears, so that the output from a driving side to a side to be driven is enabled but that the input from the side to be driven is constrained. CONSTITUTION:In a rotation transmitting mechanism, which is formed of small gears 12, 33 and large gears 32, 21 having equal pitch diameter, in the case where the rotation in any one of the normal and reverse direction is input to the gear 21 to be driven of a side 20 to be driven, a part of the rotation driving torque to be applied to the gear 21 to be driven works as the rotating force (f) for rotating an intermediate gear 33 to be driven, and on the other hand, other of the rotation driving torque works as a component force (fb) to be escaped to a wheel 41 to be constrained by the constraining means 40 through a bearing ball 42. A resistance component between the gear 21 to be driven and the wheel 41 to be constrained is therefor enlarged to constrain the input from the side 20 to be driven in spite of the condition that the friction resistance is not generated because of the interposition of the ball 42.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary transmission mechanism, and more specifically, it is possible to input a drive torque from each of the forward and reverse rotations from the drive side, and the positive side from the driven side.
The present invention relates to a rotation transmission mechanism configured so as to disable and prohibit input of drive torque due to each rotation in opposite directions.

[0002]

2. Description of the Related Art Generally, a rotary transmission mechanism, which is constructed by connecting and engaging a plurality of individual gears as expected, has hitherto been known as a drive torque (hereinafter referred to as a drive torque) due to rotation in a required direction input from a drive side. , "Driving force", or simply "torque"), the same rotational speed corresponding to the input of driving torque to the driven side by the combination of the gear ratios of the gears meshed with each other, And the same drive torque is transmitted and output from the driven side, or the rotational speed increased in response to the input of the drive torque, and the drive torque reduced by this speed increase, or the input of the drive torque. Is transmitted at a rotational speed that is decelerated corresponding to the above, and a drive torque that is increased by this deceleration, and is also often used as a mechanical means for outputting from the driven side.

With respect to a general rotary transmission mechanism of this type, as described above, a desired simple and simple meshing combination of only individual gears, that is, a so-called "gear train ( As long as it is simply configured with only a gear train), it is well known that the forward direction from the driving side (for example, clockwise direction) is used.
Or input of driving torque or driving force by each rotation to the selected one in the reverse direction (eg, counterclockwise direction), that is, in the forward direction, which is arbitrarily selected as necessary. Input of driving torque or driving force due to rotation and driving torque due to rotation in the opposite direction or input of driving force (hereinafter, for convenience of explanation, "driving torque due to rotation in both forward and backward directions from the driving side, or Driving force input ", and the synonymous expression on the driven side is also called" driving torque or driving force input from the driven side by each rotation in both forward and reverse directions ") Is possible individually, and therefore, under the limited condition that it is simply constructed with only such a gear train, the result is “driving torque due to each rotation in both forward and reverse directions from the driven side, Or driving force Input "is also to be individually, not was 俟 the theory Te daringly, there is also quite natural thing.

Further, in the general rotary transmission mechanism configured as described above, it has nothing to do with the intended purpose of the present invention, but as an example to be referred to here, for example, , Allows input of drive torque from rotation in the forward rotation direction from the drive side, and disables input of drive torque from rotation in the reverse rotation direction, and conversely, the drive side from the driven side. The means for enabling the input of the drive torque by the rotation in the reverse rotation direction and the input of the drive torque by the rotation in the normal rotation direction, that is, in other words, as seen from the drive side, At this time, as the so-called reverse rotation preventing means, various reverse rotation direction restraining means can be considered when facilitating the complication of the configuration, but the simplest means is a so-called reverse rotation preventing means. A ratchet toothed ring which is connected form a ratchet tooth, backstop configuration of a combination of a ratchet pawl to be engaged in elastic contact with the respective ratchet teeth are well known in the art.

Here, as described above, the rotation transmission mechanism according to the present invention enables the input of the driving torque from each of the forward and reverse rotations from the driving side, and the forward and reverse directions from the driven side. The present invention is intended for a configuration for achieving the action of making it impossible to input the driving torque by each rotation in both directions. In the conventional case, there is no rotation transmission mechanism capable of achieving such action.

Therefore, conventionally, there has been a demand for a mechanism that enables the input of the driving torque from the driving side by the rotation in both the forward and reverse directions and the input by the driven side by the rotation of the forward and reverse directions. If so, it is conceivable to add a braking means to the system of the gear train based on the above-mentioned general rotary transmission mechanism as a basic configuration. For example, the input of the corresponding drive torque from the driven side is detected. There is one that uses an electromagnetic braking means that operates by doing so and makes the corresponding input impossible.

[0007]

However, it is possible to input the driving torque from the drive side by the rotations in both the forward and reverse directions and drive the driven side by the rotations in both the forward and reverse directions. In the structure in which the electromagnetic braking means is added to make it impossible to input the torque, an electric input detecting means for promptly detecting the input of the corresponding drive torque from the driven side is required, and the electromagnetic braking means is required. , And a power supply for supplying an operating current to each means such as input detection means, and further, there is a need for safety measures due to lack of reliability peculiar to such electric / mechanical means. However, there are various unfavorable problems that the structure itself becomes unnecessarily complicated and large, and that maintenance is not easy.

Therefore, in view of such problems of the prior art, the object of the present invention is to mechanically and serially incorporate into the system of the gear train to obtain the corresponding drive torque from the drive side. It is an object of the present invention to provide a rotation transmission mechanism that can restrict and inhibit only an input of a corresponding drive torque from a driven side regardless of an input at all.

[0009]

Based on the above-mentioned object, the present inventor is able to input a driving torque from each of the positive and negative rotations from the driving side, and positive from the driven side. As a result of continuous research and development efforts over many years on a rotary transmission mechanism that has the effect of not being able to input drive torque due to each rotation in opposite directions, the machinery in the gear train system that constitutes this rotary transmission mechanism has been developed. It can be installed in a simple and continuous manner, and has no relation to the input of the corresponding drive torque from the drive side, and it acts so as to restrict and inhibit only the input of the corresponding drive torque from the driven side. The present invention has been completed by applying a restraining means having a new structure.

The constituent features of the rotary transmission mechanism according to the present invention are as follows, and operate as expected based on the basic principle described subsequently. 1 and 2 are a plan view and a cross-sectional view taken along the line AA of FIG. 1 schematically showing a basic configuration of a rotary transmission mechanism according to the present invention.
3 and 4 are a conceptual explanatory diagram and a reference explanatory diagram for explaining the basic principle of the rotation transmission mechanism.

As shown in FIGS. 1 and 2, the rotary transmission mechanism according to the present invention is constructed as follows. That is, first, as the driving side 10 that enables the input of the driving torque by each rotation in both the forward and reverse directions, the driving gear 12 and the driven side 20 that are integrally provided on the driving shaft 11 are provided. Of the driving gear 12 of the former type is relatively small. effective outer diameter (in this case, for example, D ₁₂₎ (corresponding to the pitch circle) effective radius by at R _12, a relatively small gear (in this case, for example,
N ₁₂ ), and the latter restraining actuating wheel 41 is set to an effective radius (corresponding to approximately the outer diameter) R ₄₁ with a medium effective outer diameter (in this case, for example, D ₄₁ = 2D ₁₂ ). There is.

In addition, the drive torque by each rotation in both the forward and reverse directions.
The driven side 20 that restricts and prohibits Luk's input to make it impossible
As a bearing on the restraining working wheel 41.
Circle through ball 42 (or bearing roller)
The restraint means 4 is fitted so that it can rotate smoothly.
0 has a driven gear 21 which is also the other part,
The gear 21 has a relatively large effective outer diameter (in this case,
If, for example, D_{twenty one}= 3D ₁₂) Effective radius (Pitch
Equivalent to the vehicle) R_{twenty one}And a relatively large number of teeth (in this case,
For example, N_{twenty one}= 3N₁₂) Is set.

Further, as the intermediate reduction gear stage 30 connecting the driving side 10 and the driven side 20, the driving shaft 11
On the intermediate shaft 31 arranged in parallel with the driving gear 12, there is a driving-side intermediate gear 32 that meshes with the driving gear 12, and a driven-side intermediate gear 33 that meshes with the driven gear 21.

The intermediate shaft 31 is parallel to the drive shaft 11, and the former drive-side intermediate gear 32 has a relatively large effective outer diameter (in this case, for example, D ₃₂ = 3D ₁₂ ) effective radius ( R ₃₂ (corresponding to a pitch circle) is set to a relatively large number of teeth (in this case, for example, N ₃₂ = 3N ₁₂ ), and for the latter driven side intermediate gear 33, a relatively small effective outer diameter (in this case, For example, an effective radius (corresponding to a pitch circle) R ₃₃ according to D ₃₂ = D ₁₂ is set to a relatively small number of teeth (in this case, N ₃₃ = N ₁₂ ).

Therefore, in the rotation transmission mechanism having the above-mentioned structure, the rotational speed n ₁₂ =, for example, the rotational speed n ₁₂ = with respect to the drive side 10, in this case, the drive gear 12, depending on the selected one of the forward and reverse directions. 1. When the rotation of the rotational drive torque t ₁₂ = 1 is input, the drive gear 12 → the drive side intermediate gear 32 (first deceleration and boosting force in the intermediate stage) → the driven side intermediate gear 33 (the intermediate stage in the intermediate stage) (2nd deceleration, boosting) → The driven side 20 is driven by the gear train of the route by the driven gear 21 which is decelerated and increased in rolling on the peripheral surface of the restraining working wheel 41 which rotates at the peripheral speed corresponding to the input rotation speed. , In this case, from the driven gear 21, the rotational speed n ₂₁ = 1/9 in the same direction, the rotational drive torque t ₂₁ = (R ₃₂ / R ₁₂ ) × (R ₃₂ / R ₁₂ ).
The rotation of × t ₁₂ is output, which is not related to the rotation direction of the input drive torque.

However, the frictional resistance of each part including the frictional resistance between the restraining working wheel 41 and the driven gear 21 is set to 0. On the other hand, with respect to the driven side 20, in this case, the driven gear 21,
Conventionally, a rotation transmission mechanism using a gear train of this type is used when a rotation is input in either one of the forward and reverse directions, for example, rotation speed n ₂₁ = 1 and rotation drive torque t ₂₁ = 1. From the common sense point of view, even if the restraint means 40 is interposed in the gear train, the presence of the restraint means 40 is ignored, and the drive gear 12 and, by extension, the drive gear 12 are driven by the opposite route. It is apt to be thought of as getting the output from the side 10.

However, according to the research results of many trial experiments conducted by the present inventor, in practice, in the gear train constituting the rotation transmission mechanism, the intermediate reduction gear stage 30 connected to the drive side 10 is less than the intermediate reduction gear stage 30. On the driven side 20, a combination of the restraining actuating wheel 41 as the restraining means 40 and the driven gear 21 is interposed, and therefore, the following principle is actually used as the basic principle of the rotational driving at this time. It was confirmed that the driving torque input from the driven side 20 due to each rotation in both the forward and reverse directions is restricted and prohibited, which makes it impossible.

Next, regarding the phenomenon that the input of the driving torque from the driven side 20 due to each rotation in both the forward and reverse directions is prohibited, referring to FIGS. 3 and 4 in addition to FIG. 1 and FIG. Will be described in detail.

First of all, in the structure of the gear train by the rotation transmission mechanism according to the present invention described above, the combination of the restraining working wheel 41 as the restraining means 40 and the driven gear 21 is not present in the gear train. The rotation transmission mechanism in 1), in other words, the case where the respective gears are meshed with each other, and by extension, the case of the gear train by the combination of the gears shown in the reference diagram of FIG.

The reference rotary transmission mechanism 50 shown in FIG. 4 includes a first shaft 51 having a first small-diameter gear 52 corresponding to the drive gear 12 and a relatively small number of teeth, and the driven gear. The first large diameter gear 53 having a relatively large number of teeth corresponding to the gear 21 is integrally provided, and the first shaft 5
The second large diameter gear 54 is meshed with the first small diameter gear 52 corresponding to the drive side intermediate gear 32 and has the same number of teeth as the first large diameter gear 53 with respect to the second shaft 54 parallel to the first large diameter gear 53. A gear 55 and a second small-diameter gear 56, which meshes with the first large-diameter gear 53 corresponding to the driven-side intermediate gear 33 and has the same number of teeth as the first small-diameter gear 52, are integrally provided. Is.

In the rotation transmission mechanism of the gear train having the above-mentioned structure, the first shaft 51 is provided commonly to the first shaft 51.
The small diameter gear 52, the first large diameter gear 53, the second large diameter gear 55 and the second small diameter gear 56 that are commonly provided on the second shaft 54 are the first small diameter gear 52 and the second small diameter gear 52. Large diameter gear 55 of
The first large-diameter gear 53 and the second small-diameter gear 56 are meshed with each other, and the combination of these meshes has the same gear ratio. For example, when viewed from the first shaft 51 side. In this case, on the same axis, deceleration is performed on one side and acceleration is performed on the other side, so that they cannot rotate relative to each other.

In other words, as a practical matter, it can be said that the structure of the gear train formed by combining the respective gears like the rotary transmission mechanism 50 has no value and should not exist as a result. However, it is a good reference for understanding the basic principle of the present invention.

Next, the basic principle of the present invention will be examined. As described above, with respect to the driven gear 21 on the driven side 20 in the rotation transmission mechanism here, for example, the rotational speed n ₂₁ = 1 the rotational driving torque t depending on the selected one of the forward and reverse directions. _When the rotation of ₂₁ = 1 is input, the rotational driving torque t ₂₁ applied to the driven gear 21 acts as follows.

That is, based on the physical principle of force distribution, as shown in FIG. 3, on the other hand, a part of the rotational driving torque t ₂₁ applied to the driven gear 21 on the driven side 20 is an intermediate reduction gear. On the other hand, the other part of the rotational driving torque t ₂₁ tries to act as a rotational force fa for rotating the driven side intermediate gear 33 of the step 30, and the other part of the rotational driving torque t ₂₁ of the restraining means 40 of the restraining means 40 is interposed via the bearing balls 42. It tries to act as a component force fb that tries to escape to the side.

That is, regarding the driving torque acting on the driven intermediate gear 33 side from the driven gear 21 in the former case,
The driven gear 21 has a relatively large effective outer diameter D ₂₁ = 3D ₁₂
With an effective radius R ₂₁ and a relatively large number of teeth N ₂₁ = 3N
_{While the} driven side intermediate gear 33 meshing with this is set to ₁₂ , the effective radius R ₃₃ due to the relatively small effective outer diameter D ₃₃ = D ₁₂ , and the relatively small number of teeth N ₃₃ = N. On the other hand, the driving side intermediate gear 32 which is set to ₁₂ and is integrated with the driven side intermediate gear 33 has an effective radius R ₃₂ with a relatively large effective outer diameter D ₃₂ = 3D ₁₂ , and With a relatively large number of teeth N ₃₂ = 3N ₁₂ ,
The drive gear 12 meshing with the driven-side intermediate gear 33 is set to have an effective radius R ₁₂ with a relatively small effective outer diameter D ₁₂ and a relatively small number of teeth N ₁₂ , and between these gears, Driven gear 21 → driven side intermediate gear 33 (first speed increase / reduction in intermediate stage) → drive side intermediate gear 32
(Second speed increase / reduction in the intermediate stage) → It is assumed that the driven gear 21 is a speed increase / reduction resistance path in which it is extremely difficult to dissipate the force.

Therefore, in this case, according to the experimental results of the present inventor, the rotational force fa toward the driven side intermediate gear 33 side in the former case and the restraining operation wheel 41 in the latter case here.
The inner position of the constraining working wheel 41 at which the force components fb that try to escape to the side can be balanced with each other, that is, in the substantial meshing condition of the respective gears, outside the constraining working wheel 41. As shown by the diagonal line to the right in FIG. 3, the dispersed area A of the escaped force spreads and the dispersion of the force D ₄₁ and the outer diameter D ₁₂ of the drive gear 12 are inwardly extended. Between the area range A and the shaft center, that is, the center of the drive shaft 11, the restrainable range B at this time is set as shown by the diagonal line to the left in FIG. The resistance component between the gear 21 and the restraining working wheel 41 is enlarged,
In spite of the fact that the frictional resistance is not generated as much as possible due to the interposition of the bearing balls 42, these two are in close contact with each other as in the case of the reference diagram of FIG. 4 described above. It is considered that the input and output of the driving torque from the driven side 20 due to each rotation in both the forward and reverse directions is restricted and prohibited to become impossible.

Thus, the driven gear 21 and the restraining working wheel 41 are tightly integrated with each other, and the driving torque is input from the driven side 20 by both forward and reverse rotations. The phenomenon of being restrained cannot be understood at all by merely interpreting an ordinary gear train, and is present on the driven side 20 of the intermediate reduction gear stage 30 following the drive side 10 in the gear train. , The point where the combination of the constraining actuating wheel 41 and the driven gear 21 forming the constraining means 40 is interposed, and the rotational driving torque t ₂₁ to be applied to the driven gear 21 of the driven side 20 is the driven side intermediate gear. This can be understood for the first time when considering the fact that the rotational force fa toward the 33 side and the component force fb that tries to escape to the restraining working wheel 41 side are dispersed and balanced.

The inventor of the present invention was also able to grasp a phenomenon by repeating many trials while actually prototyping a number of corresponding mechanisms under different conditions, and at present, the theoretical analysis has been completed completely. It can be said that, for example, a strain detection element or the like is attached to the force dispersion region range A and the restrainable range B of the restraining working wheel 41, and the rotational driving torque t ₂₁ in the restraining working wheel 41 is attached. By accurately measuring the range of the component force fb associated with the addition of C, the force dispersion limit line C shown by the thick two-dot chain line in FIG.
Can be determined relatively easily.

By the way, the present inventor, when such a phenomenon was confirmed, as one trial means for making a theoretical elucidation thereof, the outer diameter D ₃₃ of the driven side intermediate gear ₃₃ , and by extension, the drive gear. When the experiment was repeated assuming that the outer diameter D ₁₂ of No. ₁₂ was gradually increased, the following facts could be confirmed.

That is, the outer diameter D of the drive gear 12
_{When 12} is moved from within the restrainable range B of the restraint working wheel 41 into the force dispersion region range A over a certain limit line C and closer to the outer diameter D ₄₁ thereof, between these two. Although there is a relatively large frictional resistance, and eventually a restraining force, by applying a rotational driving torque that exceeds the frictional resistance to the driven gear 21, it is possible to make a rotation that overcomes the restraining force, although it is extremely small. It has been confirmed that the driving gear 12 has an outer diameter D ₁₂ that is further increased, whereby the frictional resistance as a restraining force generated in the driven gear 21 is gradually reduced and the driving gear 12 is When the outer diameter D ₁₂ of the driven actuating wheel 41 exceeds the outer diameter D ₄₁ of the restraint working wheel 41, in other words, when the outer diameter D ₃₃ of the driven-side intermediate gear 33 also exceeds the outer diameter D ₄₁ of the restraint working wheel 41. Then, the binding force is completely eliminated. Te, here the problem is the driven side 2
It became impossible to input the drive torque from 0 in each rotation in both forward and reverse directions.

In summary, according to the present invention, the restraining means 4 is provided in the meshed gear train in which a plurality of gears are combined.
0 is interposed and the rotation input from the driving side 10 is applied to the driven side 20.
A rotation transmission mechanism that transmits the rotation input to the driving side 10 and outputs the rotation to the driving side 10 while restraining the rotation input from the driven side 20 by the restraining means 40.
The drive gear 12 has a relatively small effective outer diameter and a relatively small number of teeth on the drive shaft 11, and an effective outer diameter larger than the effective outer diameter of the drive gear 12. , A restraining working wheel 41 serving as a main part of the restraining means 40 is integrally provided, and the driven side 20 has an effective outer diameter larger than an effective outer diameter of the restraining working wheel 41, and at least the concerned working diameter. The driven gear 21 is provided which is rotatable on the restraining working wheel 41 and has a relatively large number of teeth, which is also the other part of the restraining means 40.
The intermediate shaft 31 equilibrated in 1 has at least the same effective outer diameter and the same number of teeth as the driven gear 21, and has a drive-side intermediate gear 32 meshed with the drive gear 12 and the drive gear 12 A rotary transmission mechanism having the same effective outer diameter and the same number of teeth as that of the intermediate reduction gear stage 30 including a driven intermediate gear 33 meshed with the driven gear 21. .

[0032]

Therefore, according to the first and second aspects of the invention, the rotation input from the driving side 10, that is, the driving gear 12
When the rotation with the required drive torque is input to,
After the first and second decelerations and boosts in each intermediate reduction gear stage 30 by the drive-side intermediate gear 32 and the driven-side intermediate gear 33, the peripheral speed corresponding to the rotation of the drive gear 12 is rotated. On the peripheral surface of the constraining actuating wheel 41, the driven gear 21 which is decelerated and increased in this way to rotate, here, from the driven gear 21 of the driven side 20, finally,
The decelerated and increased rotation is output.

On the other hand, when the rotation input from the driven side 20, that is, the rotation by the arbitrary driving torque is input to the driven gear 21, a part of the driving torque applied is driven by the intermediate reduction gear stage 30. Since the other portion of the drive torque acts as a rotational force of the side intermediate gear 33 and acts as a component force to escape to the restraining working wheel 41 of the restraining means 40, in the restraining working wheel 41, Of the driving gear 12 to the inner position where the rotational force and the component force of the driving gear 12 can be balanced with each other. The dispersion area of the generated force expands, and the restrainable range is set between the force shaft core and the drive shaft. As a result, the resistance component between the driven gear 21 and the restraining actuating wheel 41 increases, and the two are mutually reciprocated. Close to One integrated is, the driven-side 20
The input of the driving torque from is restricted and prohibited.

In the third aspect of the present invention, the rotation of the driven shaft 12 is reduced and increased through the driven gear 21.
It can be output from 2. In the invention according to claim 4,
By the speed-increasing gear stage, the rotation decelerated and increased through the driven gear 12 can be accelerated to the input rotation and output.

According to the fifth aspect of the invention, the bearing 4 interposed between the restraining working wheel 41 and the driven gear 21.
According to 2, the rotation of the driven gear 21 relative to the restraining working wheel 41 is smoothed at the time of the rotation input from the driving side 10, and when there is the rotation input from the driven side 20, the driven gear 21 side shifts to the restraining working wheel 41. Promote the escape of the component of the rotational force of.

Further, in the invention of claim 6, the effective outer diameter ratio among the drive gear 12, the restraining working wheel 41 and the driven gear 21 is 1: 2: 3, or approximately 1: 2: 3. By setting the ratio to the ratio, it is possible to empirically and satisfactorily and effectively set the spread of the force dispersion region in the restraining working wheel 41 and the restrainable range.

According to the invention described in claims 7 and 8, FIG.
As shown in FIG. 2, by inserting an intermediate ring 43 between the driven gear 21 and the restraining working wheel 41, the intermediate ring 43 that can freely rotate with respect to both the driven gear 21 and the restraining working wheel 41, It becomes possible to reduce the driving force of the drive side 10 in the state where a load is applied, and it is experimentally confirmed that in this state, the intermediate side 43 and the restraining working wheel 41 rotate at the boundary.

Further, according to the ninth aspect of the present invention, each element constituting the gear train, that is, the drive gear, the driven gear, the drive side intermediate gear, and the driven side intermediate gear, has the same reason.
It can be replaced with a friction wheel.

According to the tenth aspect of the invention, the winding drum 60 around which the suspension rope is wound has the drive shaft 111.
Only the input from the side is received, and idling due to the weight of the load fixed to the end of the suspension rope is prevented without providing any special stopper means.

Similarly, in the invention as set forth in claim 11, since the drive wheel 71 receives only the output of the engine 70,
It is possible to lock the drive wheels 71 without providing special braking means.

[0041]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the rotary transmission mechanism according to the present invention will be described in detail below with reference to FIG.

FIG. 6 shows a highly preferred embodiment, which can be operated without the need for external support as much as possible, and which has a relatively simple mechanical construction and is maintenance-free. .

Even in the apparatus configuration shown in FIG. 6, positive,
The drive side 110 that enables the input of the drive torque by each rotation in the opposite directions is located on the drive shaft 111 and is integrally provided with the drive gear 112 and the driven side 120 in both the forward and reverse directions. It has a restraining working wheel 141 which is a main part of restraining means 140 for prohibiting the input of the driving force by rotation, and these driving gear 112 and restraining working wheel 1 are provided.
No. 41 is set according to each condition described above.

The driven side 12 restricts and prohibits the input of the driving torque due to the rotations in both the forward and reverse directions to make it impossible.
Reference numeral 0 denotes a cup-shaped driven gear which is fitted on the restraining working wheel 141 via a bearing roller 142 held by a holding screw wheel 143 so as to be smoothly rotated and which is also the other part of the restraining means 140. 121, and the shaft end 113 of the drive shaft 111 is pivotally supported at the center of one end surface of the driven gear 121, and the bearing 1 is provided from the other end.
The driven shaft 122 pivotally supported at 23 is taken out. The drive shaft 111 and the driven shaft 122 are arranged on the same axis, and the driven gear 121 is also set according to the conditions described above.

Further, the driving side 110 and the driven side 120
An intermediate speed reduction gear stage 130 that connects the shaft 13 and the drive shaft 111 is arranged parallel to the drive shaft 111 and both ends of the shaft are the bearings 13.
A drive-side intermediate gear 132 that meshes with the drive gear 112 and a driven-side intermediate gear 133 that meshes with the driven gear 121 are on an intermediate shaft 131 pivotally supported by
The driving-side intermediate gear 132 and the driven-side intermediate gear 133 are also set according to the above-described conditions.

Therefore, in the rotation transmission mechanism of this embodiment having the above-mentioned structure, the rotation of the required drive torque with respect to the drive side 110, in this case, the drive gear 112, in either one of the forward and reverse directions is selected. Is input, the driven side gear 120 rotates by the driving gear 112, the driving side intermediate gear 132, the driven side intermediate gear 133, the driven gear 121 that rotates on the circumferential surface of the restraining working wheel 141, and the driven side 120.
In this case, the driven shaft 122 outputs the decelerated and increased rotation in the same direction.

On the other hand, even if the rotation of the required drive torque is input to the driven side 120, in this case, the driven shaft 122, in either one of the forward and reverse directions, the above-mentioned operation is performed. For that reason, the rotation input is restricted and prohibited by the restricting means 140.

Here, the drive gear 112 (driven intermediate gear 133), the restraining working wheel 141, and the driven gear 121.
The effective outer diameter ratio between the (driving-side intermediate gear 132) and the drive-side intermediate gear 132 is 1: for each of the experiments of the present invention.
Setting the ratio to 2: 3 or approximately 1: 2: 3 was extremely effective in expanding the force dispersion region in the restraining working wheel 141 and setting the restrainable range.

When the drive shaft 111 and the driven shaft 122 are arranged on the same axis as described above, the structure is further simplified from the standpoint of the mechanical structure, and the rotational drive torque is reduced. It was very convenient for input and output.

In the construction of the above embodiment, the output from the driven shaft 122 is decelerated and the force is increased. However, if necessary, an appropriate additional output gear stage may be added to the driven shaft 122. Thus, the output of the driving torque corresponding to the input can be obtained while maintaining the desired effect.

In the embodiment described above, the bearing 142 is provided between the restraining working wheel 141 and the driven gear 121.
By intervening, the rotation of the driven gear 121 corresponding to the restraining working wheel 141 is smoothed at the time of rotation input from the drive side 110, and when there is a rotation input from the driven side 120, the driven gear 121 side Although the escape of the component of the rotational force to the restraining working wheel 141 is promoted, the interposition of the bearing is not always necessary.

Further, a friction increasing means M for adding frictional resistance to the rotation of the driven gear 121 is provided, and when the rotational driving torque is applied from the driving side 110, the friction increasing means M operates on the non-acting side, and conversely the driven side. When the rotational driving torque is applied from the side 120, the friction increasing means M may be actuated to the working side to give frictional resistance to the rotation of the driven gear 121.

FIG. 7 shows an example thereof, in which the driven gear 1
A friction increasing means M comprising an electromagnetic solenoid S on one side of 21
The drive side 110 is provided at an appropriate position on the drive side 110.
A sensor for detecting the rotational drive torque applied from the driven side 120 and a sensor for detecting the rotational drive torque applied from the driven side 120 are provided at appropriate positions on the driven side 120, and these sensors are connected to each other via a control unit (not shown). It is connected to the electromagnetic solenoid S.

FIG. 8 shows another embodiment of the present invention. In this embodiment, the restraining working wheel 1 is integrally formed with the drive shaft 111.
41 is formed. The outer diameter of the restraining working wheel 141 is set to be at least larger than the outer diameter of the drive gear 112, specifically, to be included in the region of the restrainable range B described above.

Further, an intermediate ring 43 is externally fitted to the outer periphery of the restraining working wheel 141 via a bearing 44, and a driven gear 121 is externally fitted to the outer periphery of the intermediate ring 43 so as to freely rotate.

Under such a structure, when the driving side 120 is driven with the driven shaft 122 being loaded, the restraining working wheel 14 is driven.
Idling occurs at the boundary between 1 and the intermediate ring 43, and the resistance due to the presence of the restraint means 140 is reduced.

In the above description, the drive gear 1
12, the driving side intermediate gear 132, the driven side intermediate gear 133,
The driven gear 121 and the driven gear 121 form a gear train to transmit power, but the invention is not limited to this, and each element may be formed of a friction wheel.

FIG. 9 shows a preferred application example of the rotary transmission mechanism according to the present invention. This embodiment is constructed as a rotation transmission gear mechanism for driving force of a vehicle, and the output of the engine 70 is transmitted through an appropriate transmission device (not shown) to the drive shaft 11.
Connected to 1.

On the other hand, the driven shaft 122 has a differential gear unit 7 attached thereto.
It is connected to the drive wheel 71 via 2. Under this configuration,
Since the drive wheel 71 receives only the output of the engine 70 and does not receive the rotational torque from the drive wheel 71 side, the drive wheel 71 can be locked without providing a special brake device.

The rotation transmission mechanism described above can be applied to various types other than that shown in FIG.
A winding device may be formed by replacing the drive wheel 71 of FIG. 9 with a winding drum 60 and connecting a suitable load with a suspension rope wound around the winding drum 60.

[0061]

As described above in detail, according to the present invention, when the rotation input from the drive side, that is, the rotation by the required drive torque is input to the drive gear, the drive side intermediate In the restraining working wheel that is rotated at the peripheral speed corresponding to the rotation of the drive gear after each deceleration and boosting at each intermediate reduction gear stage by the gear and the driven side intermediate gear,
A rotation output corresponding to the rotation input is obtained from the driven gear that rotates on the peripheral surface.

On the other hand, when the rotation input from the driven side, that is, the rotation by the arbitrary driving torque to the driven gear is about to be input, a part of the driving torque applied is
Since the other part of the driving torque that is applied as the rotational force of the driven-side intermediate gear of the intermediate reduction gear stage acts as a component force that tries to escape to the side of the restraining working wheel of the restraining means, the restraining working wheel is At an inner position where the rotational force and the component force reach a level where they can balance each other, where
When it corresponds to the effective outer diameter of the drive gear, the dispersed area of the escaped force expands to the inner position corresponding to the outer diameter portion larger than this, and the restrainable range is set with the drive shaft core. As a result, the resistance component between the driven gear and the restraining working wheel is increased, and both of them are tightly integrated with each other and the driving force input from the driven side is effective. Is bound and banned by.

[Brief description of drawings]

FIG. 1 is a partially cutaway plan view schematically showing the basic configuration of a rotary transmission mechanism according to the present invention.

FIG. 2 is a horizontal cross-sectional view of the AA line portion in FIG.

FIG. 3 is a conceptual explanatory view for explaining the basic principle of the above rotary transmission mechanism.

FIG. 4 is a reference explanatory diagram for explaining the basic principle of the same.

FIG. 5 is an explanatory diagram showing a basic configuration of another embodiment of the present invention.

FIG. 6 is a partially longitudinal plan view schematically showing the configuration of a rotary transmission mechanism to which a basic embodiment of the present invention is applied.

FIG. 7 is a plan view of an example in which a friction increasing means is provided on one side of a driven gear.

FIG. 8 is a diagram showing another embodiment of the present invention.

FIG. 9 is a diagram showing a vehicle drive device to which the present invention is applied.

[Explanation of symbols]

 10,110 Drive side 11,111 Drive shaft 12,112 Drive gear 20,120 Driven side 21,121 Driven gear 30,130 Intermediate reduction gear stage 31,131 Intermediate shaft 32,132 Drive side intermediate gear 33,133 Driven side intermediate Gears 40, 140 Restraint means 41, 141 Restraint working wheels 42, 142 Bearing balls 43 Intermediate ring 60 Winding drum 61 Suspension rope 70 Engine 71 Drive wheel 122 Driven shaft

Claims (11)

[Claims] 1. A restraint means is interposed in a gear train in which a plurality of gears are combined and meshed, a rotary input from a drive side is transmitted to a driven side for rotation output, and a rotary input from the driven side is restrained. A rotation transmission mechanism for restraining transmission to the drive side by means of a drive gear having a relatively small effective outer diameter and a relatively small number of teeth on the drive shaft. , And an effective outer diameter that is larger than the effective outer diameter of the drive gear, and integrally provide restraint working wheels that are the main parts of the restraining means. A driven gear having an effective outer diameter larger than the diameter and being rotatable at least on the restraining working wheel and having a relatively large number of teeth, which is also the other portion of the restraining means, is provided. Intermediate shaft arranged parallel to the drive shaft Is has at least the driven gear same effective outer diameter and the number of teeth,
A drive-side intermediate gear that meshes with the drive gear, and an intermediate reduction gear stage that has the same effective outer diameter and the same number of teeth as the drive gear and that is a driven-side intermediate gear that meshes with the driven gear are provided. A rotation transmission mechanism characterized by being configured. 2. A drive shaft and an intermediate shaft arranged in parallel with each other, a drive gear fixed to the drive shaft, and a driven gear arranged concentrically with the drive shaft and having an effective outer diameter larger than that of the drive gear. An intermediate reduction gear stage in which an effective outer diameter is the same as that of the drive gear, a driven side intermediate gear that meshes with the driven gear, and a drive side intermediate gear that meshes with the drive gear are fixed to an intermediate shaft. The driven gear is a rotation transmission mechanism that rotates on a restraining working wheel having an outer diameter larger than the effective outer diameter of the drive gear. 3. The rotary transmission mechanism according to claim 1, wherein the driven gear coaxially has a driven shaft integrally therewith. 4. The driven gear is coupled to the driven shaft via a speed increasing gear stage having a speed increasing ratio corresponding to a reduction ratio of the intermediate reduction gear stage. The rotation transmission mechanism described in 3. 5. The rotation transmission mechanism according to claim 1, wherein a bearing is interposed between the restraining working wheel and the driven gear. 6. The ratio of the effective outer diameter ratio among the drive gear, the restraining working wheel, and the driven gear is 1: 2: 3, or approximately 1: 2: 3. 1, 2,
The rotation transmission mechanism according to 3, 4, or 5. 7. An intermediate ring between the driven gear and the restraining working wheel, which is free to rotate with respect to both the driven gear and the restraining working wheel, is interposed. Alternatively, the rotation transmission mechanism described in 5. 8. The ratio of the effective outer diameter ratio among the drive gear, the intermediate ring and the driven gear is 1: 2: 3, or approximately 1: 2: 3, and the restraining working wheel is at least The rotation transmission mechanism according to claim 7, wherein the diameter is larger than the effective outer diameter of the drive gear. 9. The rotation according to claim 1, wherein the drive gear, the driven gear, the drive side intermediate gear, and the driven side intermediate gear are formed as friction wheels. Transmission mechanism. 10. Claims 1, 2, 3, 4, 5, 6, 7, 8
Alternatively, a device for connecting a take-up drum, which winds a suspension rope, to a driven gear of the rotary transmission mechanism according to 9, winding a suspension rope by applying a rotation input to a drive shaft, and winding the suspension rope. 11. Claims 1, 2, 3, 4, 5, 6, 7, 8
Alternatively, a rotation transmission gear mechanism for vehicle driving force, wherein an engine output is connected to a drive gear of the rotation transmission mechanism according to 9, and a driven shaft of a drive wheel is connected to the driven gear.