JPH08312733A - Gear transmission - Google Patents

Abstract

PURPOSE: To smoothly mesh an idle gear in a short time without applying shock to a gear and without damaging it. CONSTITUTION: A gear transmission 10 is provided with an input gear 12, an output gear 104, and an idle gear 106 for transmitting torque of the input gear 12 to the output gear 104. The input gear 12 is provided with a first gear 16 in which four projecting parts 14 are formed on the side surfaces, a second gear 20 arranged in parallel with the first gear 16, having insertion holes 18 into which the projecting parts 14 of the first gear 16 can be inserted with play, and able to be rotated around the same rotary shaft as the first gear 16 within the specified angle range in relation to the first gear 16, and an energizing means provided between the first gear 16 and the second gear 20, and for always energizing the relative position of the second gear 20 in relation to the first gear 16 to the intermediate range in the angle range. The idle gear 106 performs the approaching and separating motion and can be meshed with the output gear 104 and the first gear 16 or the second gear 20.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission device, and more particularly to a gear transmission device which uses an idle gear to transmit the rotational force of an input gear to an output gear or to stop the transmission.

[0002]

2. Description of the Related Art An example of a gear transmission device using a conventional idle gear will be described with reference to FIG. This gear transmission 100 is provided with an input gear 102, an output gear 104, an input gear 102 and an output gear 104 that are movable in and out of contact with each other, and an idle gear 106 that can mesh with both the input gear 102 and the output gear 104 at the same time. It consists of and.
Explaining each constituent element in more detail, the input gear 102 is integrated so that two spur gears 108 and 110 (first spur gear and second spur gear, respectively) having different diameters have the same rotation axis A. Has been formed. Further, the output gear 104 includes a third spur gear 114 having the same diameter as the second spur gear 110 on the cylindrical body 112, the center axis of the cylindrical body 112 and the third spur gear 1.
It is integrally formed so that the rotation axis of 14 corresponds. Further, the outer diameter of the tubular body 112 can be inserted into the through hole 116 provided at the center of the input gear 102 without rattling, and when the tubular body 112 is inserted, the input gear 102 can be inserted.
Is formed to be slidable on the outer peripheral surface of the. Further, the input gear 102 externally fitted to the cylindrical body 112 is formed by a retaining pin (or a distal end of the cylindrical body 112 bent outwardly) provided at the distal end of the cylindrical body 112 protruding from the third spur gear 114 and the through hole 116. It is impossible to remove from the cylindrical body 112 due to the protruding piece) 118. The shaft 120 is inserted into the cylinder 112 of the output gear 104, and the cylinder 112 is the shaft 1
It is rotatable on 20.

The idle gear 106 is, for example, the second spur gear 110 in the input gear 102 with the swing center B as the center.
And a meshing state C in which both the output gear 104 and the third spur gear 114 mesh, and the input gear 102 and the output gear 10
It is possible to move in an arc between the non-meshing state D in which none of the four meshes. The moving direction may be a non-meshing state by linearly moving from the meshing state C to the left in FIG. 11, instead of the arc shape. This idle gear 106
In order to move the state between the meshed state C and the non-meshed state D, for example, a structure in which the actuator is driven by, for example, an electromagnetic solenoid or an electric motor is generally used. With the above configuration, only when the idle gear 106 is in the meshing state C, the rotational force of the input gear 102 becomes the second
Output gear 104 via spur gear 110 and idle gear 106
Conveyed to.

[0004]

However, the above-mentioned conventional gear transmission device has the following problems. Input gear 1
When 02 is constantly rotating, when the idle gear 106 is meshed with each other, the tooth portions of both the idle gear 106 that is stopped and the input gear 102 that is rotating come into contact with each other to generate an abnormal noise. In some cases, the wear of the tooth portion becomes severe, and in some cases, excessive force is applied to the tooth portion, resulting in a lack of teeth. Therefore, when the idle gear 106 is moved to the meshing state C, the rotation of the input gear 102 is temporarily stopped, or the rotation speed is reduced to reduce the idle gear 10.
The impact between 6 and the idle gear 106 is meshed,
After that, it is necessary to increase the rotation speed of the input gear 102 to a predetermined rotation speed, and there is a problem that it takes time to transmit the predetermined rotation force to the output gear 104. Therefore, the present invention has been made to solve the above problems, and an object of the present invention is to provide a gear transmission device capable of smoothly engaging idle gears in a short time without damaging the gears.

[0005]

The present invention has the following constitution in order to achieve the above object. That is, the first gear transmission device according to the present invention is provided so that it can move toward and away from the input gear, the output gear, and the input gear and the output gear, and when meshed with both the input gear and the output gear. In the gear transmission device having an idle gear for transmitting the rotational force of the input gear to the output gear, the input gear has a first gear having at least one protrusion formed on a side surface thereof, and the first gear is parallel to the first gear. The first gear is provided with an insertion hole into which the protrusion of the first gear can be inserted with play, and the first gear rotates about the same rotation axis as the first gear within a predetermined angle range. A possible second gear, and a biasing means that is provided between the first gear and the second gear and that constantly biases the relative position of the second gear to the first gear to an intermediate position within the angular range. And the idle gear corresponds to that of the first gear or the second gear. Wherein the deviation or a one and can mesh. When this configuration is adopted, for example, in the case where the second gear of the input gears always rotates and the idle gear meshes with both the first gear and the output gear, the first gear is Since it can freely move within the predetermined angle range in the rotation direction, it can smoothly mesh with the idle gear, and also reduces the impact at the time of meshing, and does not hinder the rotation of the second gear. The transmission of rotational force to the output gear is quick.

A second gear transmission device according to the present invention is provided so that it can move in and out of the input gear, the output gear, the input gear and the output gear, and is meshed with both the input gear and the output gear. In that case, in a gear transmission device having an idle gear that transmits the rotational force of the input gear to the output gear,
The input gear is a main gear in which a first cylindrical body is provided on one side surface of the main gear and extends along the rotation axis direction, and the input gear is arranged in parallel with the main gear and is rotatable about the rotation axis. The side surface on the gear side is provided with a sub gear having a second cylindrical body extending along the rotational axis direction, and a coil spring fitted over the first cylindrical body and the second cylindrical body. The idle gear is meshable with the sub gear. When this configuration is adopted, by making the winding tightening direction of the coil spring coincide with the rotation direction of the main gear of the input gear, when the idle gear is out of mesh with the auxiliary gear, the auxiliary gear is The main gear rotates idly following the main gear by the rotating force transmitted through the coil spring wound around the first cylinder of the main gear around the main gear. Further, when the idle gear meshes with the auxiliary gear and a difference in rotational speed occurs between the rotational speed of the auxiliary gear and the rotational speed of the main gear and the coil spring that is about to rotate at the same rotational speed, The frictional force between the cylindrical body and the coil spring increases, and the coil spring is tightened. When the coil spring is completely wound up, the auxiliary gear and the main gear rotate at the same rotation speed, and therefore the output gear also rotates at the same rotation as the main gear via the idle gear. In this way, when the idle gear meshes, the sub gear can rotate independently of the main gear until the coil spring is tightened, so that the idle gear can be meshed smoothly and Since the shock at the time is softened and the rotation of the main gear is not hindered, the rotational force of the main gear is transmitted to the output gear quickly.

[0007]

[Operation] The operation will be described. In the first gear transmission according to the present invention, for example, a rotational force is constantly transmitted from the other gear to the second gear in the input gear, and the idle gear has a structure capable of meshing with both the first gear and the output gear. Then, in the state where the idle gear is not meshed, the first gear rotates with the second gear through the biasing means at the same rotation, but the rotational force is not transmitted to the output gear. Further, when the idle gear tries to mesh with the first gear and both teeth come into contact with each other, the first gear moves in both rotation directions with respect to the second gear via the urging means, and the protrusion is inserted into the insertion hole. Since there is a play over a predetermined angular range until it comes into contact with the end face, the first gear freely rotates with respect to the second gear during that time and can mesh with the idle gear. Further, as long as the first gear rotates within a predetermined angle range, the rotation speed of the second gear is not affected.

Further, in the second gear transmission according to the present invention, the winding direction of the coil spring is made to coincide with the rotation direction of the main gear of the input gear, and the coil spring is always slightly in the winding direction. When the idle gear is in a state where it does not mesh with the auxiliary gear, the auxiliary gear is provided with a coil spring wound around the second cylinder of the first cylinder of the main gear. The rotational force transmitted through the gears causes the main gear to idle, but the rotational force is not transmitted to the output gear. Also, when the idle gear comes into contact with the auxiliary gear in order to mesh with it, there is some time until the coil spring is completely wound up. And can mesh with the idle gear. Further, the rotation speed of the main gear is not affected until the coil spring is completely wound up. After that, when the load of the auxiliary gear increases due to the idle gear and the output gear meshing with the idle gear via the idle gear, the frictional force between the second cylindrical body and the coil spring increases, and the coil The spring is tightened. When the coil spring is completely tightened, the auxiliary gear rotates at the same speed as the main gear.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the gear transmission according to the present invention will be described in detail below with reference to the accompanying drawings. The same components as those in the conventional example are designated by the same reference numerals, and the description thereof will be omitted. (First Embodiment) First, the configuration of the gear transmission 10 will be described with reference to FIGS. This gear transmission 10
1 to 4, the input gear 12, the output gear 104, and the input gear 12 and the output gear 104 are provided so as to be movable toward and away from each other, and can mesh with both the input gear 12 and the output gear 104 at the same time. And an idle gear 106.

The structure of the input gear 12, which is a feature of the present invention, will be described in more detail with reference to FIG. Input gear 1
Reference numeral 2 denotes a first gear 16 having at least one (four in this embodiment) protrusions 14 formed on its side surface, and the first gear 16 and the protrusions 14 of the first gear 16. Is formed with an insertion hole 18 having a play (in this embodiment, four in accordance with the number of protrusions), the first gear 16 is centered on the same rotation axis A as the first gear 16. The second gear 20, which is rotatable within a predetermined angle range θ, the first gear 16 and the second gear 2
The second gear 2 provided between the first gear 16 and the second gear 2
A spring 22 is provided as a biasing unit that constantly biases the relative position of 0 to an intermediate position within the angular range θ. Another gear (not shown) arranged to give a rotational force to the input gear 12 meshes with the second gear 20 as an example, and the first gear 1
6, 6 is arranged between the second gear 20 and the output gear 104 as shown in FIGS. 1, 2 and 4, and the idle gear 106 is configured to mesh with both the first gear 16 and the output gear 104. . Further, the outer diameters of the output gear 104 and the first gear 16 are made the same so that the idle gear 106 is easily meshed at the same time. It should be noted that, contrary to the configuration described above, the second gear 20 is replaced by the first gear 16
And the output gear 104, and the outer diameter of the second gear 20 may be the same as the outer diameter of the output gear 104 so that the idle gear 106 meshes with the second gear 20 and the output gear 104.

The combination structure of the input gear 12 and the output gear 104 is the first structure which constitutes the input gear 12 as shown in FIG.
The tubular body 112 of the output gear 104 is inserted into the through holes 24 and 26 of the gear 16 and the second gear 20 in this order, and thereafter, the insertion side end portion of the tubular body 112 (the right end portion in FIG. 2, FIG.
A retaining pin 118 is attached to the upper end of the input gear 12 to prevent the input gear 12 from coming out of the tubular body 112. Further, as an example, the spring 22 may be the second gear 2 as shown in FIG.
0 is attached between the side surface of the first gear 16 and the protrusion 14 of the first gear 16 protruding from the insertion hole 18, and the urging forces of the two are formed to be substantially the same. It is structured to stop at. When an external force is applied to the other gear with respect to one gear, the other gear is replaced by the spring 2
The protrusion 14 is rotatable within a predetermined angle range θ while contacting both ends of the insertion hole 18 on the rotation direction side against the biasing force of 2. Further, when the rotation direction of the second gear 20 that is driven from the outside and always rotates is determined, the spring 22 biases the first gear 16 with respect to the second gear 20 in only one rotation direction. Alternatively, the protrusion 14 may be located on one inner end surface of the insertion hole 18.

Next, the operation will be described. First, when the idle gear 106 is in the non-meshing state D, the first gear 1
6 rotates with the second gear 20 via a spring 22. At this time, since no load is applied to the first gear 16 from the outside, the protrusion 14 of the first gear 16 has the second gear 20 as shown in FIG.
Is located at an intermediate position of the insertion hole 18 of the. Then, the idle gear 10
When 6 moves to the position indicated by the alternate long and short dash line in FIGS. 1 and 2 (meshing state C), the idle gear 106 tries to mesh with the output gear 104 and the first gear 16 substantially at the same time. Here, the output gear 104 does not rotate from the beginning, and meshing can be easily performed. Further, the first gear 16 is the second gear 20 as described above.
On the other hand, since it is rotatable within a predetermined angle range θ (there is some play), when it comes into contact with the idle gear 106, it temporarily rotates independently of the first gear 16, and the idle gear 106 The spring 22 absorbs the shock caused by the abutment with and the smooth engagement can be achieved.

After the idle gear 106 is brought into the meshing state C, the idle gear 106 and the idle gear 10 are attached to the first gear 16.
Since the output gear 104, and further an operating gear (not shown) that meshes with the output gear 104 are connected via 6, the load applied to the first gear 16 increases, and normally the urging force of the spring 22 against the load. The projection 14 of the first gear 16 has a small insertion hole 18 of the second gear 20, as shown in FIG.
Of the first gear 16 moves to the end opposite to the rotation direction (arrow direction) of the first gear 16 and contacts the end, and the first gear 16 is directly pushed by the second gear 20 to rotate. The idle gear 106
Various means such as an electromagnetic solenoid and an actuator driven by an electric motor can be used for the contact / separation movement of. When moving the idle gear 106 from the meshed state C to the non-meshed state D, the output gear 104 in the meshed state C is used.
Since the radial force from the first gear 16 is constantly working, it can be easily performed only by canceling the approaching force by the electromagnetic solenoid or actuator.

(Second Embodiment) First, the configuration of the gear transmission 30 will be described with reference to FIG. The same components as those in the conventional example and the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The gear transmission device 30 includes an input gear 32.
, An output gear 104 and an idle gear 106. More specifically, the input gear 3 which is a feature of the present invention
The structure 2 will be described with reference to FIG. Input gear 32
Is a main gear 36 in which the first cylindrical body 34 extends along the direction of the rotation axis A on one side surface (the left side surface in FIG. 6), and the main gear 36 is arranged in parallel to center the rotation axis A. The second cylindrical body 38 is rotatable on the side surface of the main gear 36 (the right side surface in FIG. 6) and has a second gear 38 extending along the direction of the rotation axis A.
0, and a coil spring 42 fitted over the first cylindrical body 34 and the second cylindrical body 38. Further, the outer diameter of the auxiliary gear 40 is formed to be the same as the outer diameter of the output gear 104, and the idle gear 106 meshes with the output gear 104 and the auxiliary gear 40 when moving to the meshing state C.
Further, the coil spring 42 is
The auxiliary gear 4 is externally fitted so as to match the rotation direction of the main gear 36.
Coil spring 4 when 0 is not loaded
The secondary gear 40 rotates with the main gear 36 by the tightening force of 2. Further, the coil spring 42 is not completely tightened in this state, and the sub gear 40 is rotatable with respect to the main gear 36 in the tightening direction by a predetermined angle θ. It is rotatable in the rewinding direction.

Next, the operation will be described. The idle gear 1
06 is not meshed with the auxiliary gear 40, the auxiliary gear 4
Zero rotates idly following the main gear 36 by the rotational force transmitted to the second cylinder 38 through the coil spring 42 wound around the first cylinder 34 of the main gear 36. Also,
The idle gear 106 moves to the meshing state C, and meshes with the auxiliary gear 40 between the rotation speed of the auxiliary gear 40 and the rotation speed of the main gear 36 and the rotation speed of the coil spring 42 which is about to rotate at the same rotation speed. When a difference in rotation speed is about to occur, the frictional force between the second cylindrical body 38 and the coil spring 42 increases, and the coil spring 42 is tightened. Secondary gear 4
When 0 rotates with respect to the main gear 36 by a predetermined angle θ and the coil spring 42 is completely wound up, the sub gear 40 and the main gear 36 rotate at the same number of revolutions,
Therefore, the output gear 104 also rotates at the same rotation as the main gear 36 via the idle gear 106. In this way, the idle gear 10
When the auxiliary gear 40 meshes with the auxiliary gear 40,
Since the coil spring 42 can freely rotate in the rotation direction and the reverse rotation direction until the coil spring 42 is tightly wound around the gear 6, the main gear 36 is temporarily stopped when it comes into contact with the idle gear 106.
On the other hand, the coil spring 42 rotates independently to absorb the shock caused by the contact with the idle gear 106, and the coil spring 42 can smoothly mesh.

Further, as shown in FIG. 6, the idle gear 106 swings about the swing center B which is at the position opposite to the auxiliary gear 40 with respect to the output gear 104, and the idle gear 106 and the output gear 104 and the auxiliary gear 40. In the case of a meshing structure, the output gear 104
The involute curve of the tooth profile of the auxiliary gear 40 is changed in advance so that the idle gear 106 can be brought into a state of meshing only with the output gear 104 between the non-meshing state C and the meshing state C. As a result, the idle gear 106 first meshes with the stopped output gear 104 and then meshes with the auxiliary gear 40, so that smoother meshing can be performed. This configuration can also be applied to the case where the input gear has the configuration of the first embodiment.

Further, in the above-described gear transmissions of the first and second embodiments, in order to further reduce the impact when the idle gear 106 meshes with the first gear 16 and the auxiliary gear 40, the following structure is provided. Should be adopted. The first embodiment will be described as an example. However, if the sub gear 40 corresponds to the first gear 16, the auxiliary gear 40 can be similarly applied to the second embodiment.
The impact reducing structure and operation will be described with reference to FIGS. 7 to 9. 44 is the output gear 104 of the idle gear 106
And a pressing spring that moves with the movement toward and away from the first gear 16. The pressing spring 44 is formed in a plate shape by using an elastically deformable material, and a pressing protrusion 46 protruding in the direction of the rotation axis A is formed at the tip thereof.

When the idle gear 106 is in the non-meshing state C, the pressing protrusion 46 is provided with the first gear 16 as shown in FIG.
Does not come into contact with the outer circumferential surface of the braking cylinder 48 extending along the rotation axis A provided in the idle gear 106, the idle gear 106 starts moving in the direction of the first gear 16, and the tip of the idle gear 106 and 1 gear 1
Immediately before the tooth tips of 6 contact the outer peripheral surface of the braking cylinder 48 as shown in FIG. 7, the elastic force of the pressing spring 44 is transmitted to the first gear 16 via the pressing protrusion 46. The one gear 16 is braked. Therefore, the idle gear 106 can mesh with the first gear 16 whose rotational speed has been reduced by this braking, and the impact at the time of meshing is reduced. Further, the idle gear 106 moves in the direction of the first gear 16 until the complete meshing state C is reached, but the meshing is shallow, but the idle gear 106.
Since the first gear 16 and the first gear 16 are in mesh with each other,
After that, smooth meshing can be performed. Also, the idle gear 10
When 6 moves to the meshing state C, the pressing protrusion 46 of the pressing spring 44 is disengaged from the outer peripheral surface of the braking cylinder 46 as shown in FIG. 9, and the braking is released. When the above-described gear transmission according to the present invention is applied to, for example, an electromagnetic clutch, a clutch having a simple structure, a short connection / disconnection time, and no slip can be realized. Further, as shown in FIG. 10, the present invention can be applied to a configuration in which the input gear 12 and the output gear 104 have different rotation axes. The configuration is the output gear 104 and the input gear 12
Are arranged on different rotation axes parallel to each other, and the idle gear 106
Is capable of being brought into contact with and separated from the output gear 104 and the input gear 12 to be in a meshing / non-meshing state (one-dot chain line). In this case, the idle gear 106 is formed so as to be movable on the output gear 104 along the outer circumference of the output gear 104 while always meshing with the output gear 104, and when meshing with the input gear 12, the direction of the input gear 12 The output gear 104 may be rotationally moved around the rotation shaft and mesh with the input gear 12 (two-dot chain line). The same applies to the input gear 32 of the second embodiment.

Although various preferred embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and the shape of the insertion hole is not limited to an arc shape and may be a long hole. However, the number of insertion holes and protrusions is not limited to four, and may be any number as long as it is one or more. Further, the shapes of the input gear and the output gear may be such that the input gear is externally fitted to the shaft body instead of being externally fitted to the tubular body of the output gear. When the input gear is composed of a plurality of two or more gear groups, at least a pair of adjacent gears in the gear group has a structure of the input gear 12 shown in FIG. 4 and a structure of the input gear 32 shown in FIG. As a matter of course, similarly, it is possible to secure the play of the input gear when the idle gear meshes, and it is a matter of course that many modifications can be made without departing from the spirit of the invention.

[0020]

When the gear transmission according to the present invention is used,
When the idle gear is meshed with both the input gear and the output gear, the impact exerted on the gear is reduced and the gear can be smoothly meshed in a short time without damaging the gear.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view showing a configuration of a first embodiment of a gear transmission according to the present invention.

FIG. 2 is a side sectional view taken along the line EE of FIG.

FIG. 3 is a rear view of FIG.

FIG. 4 is an exploded perspective view showing the configuration of the input gear of FIG. 1 and the assembly structure with the output gear.

5 is a front view when the idle gear of FIG. 1 is in a meshed state and the rotational force is transmitted to the output gear.

FIG. 6 is a side sectional view showing the configuration of a second embodiment of the gear transmission according to the present invention.

FIG. 7 is an explanatory view illustrating an impact reducing structure that reduces an impact when meshing an idle gear, and is a diagram when a pressing spring is braking a braking cylinder of an input gear.

8 is an explanatory view showing the relationship between the pressing protrusion of the pressing spring and the braking cylinder when the idle gear of FIG. 7 is in the non-meshing state C. FIG.

9 is an explanatory view showing the relationship between the pressing protrusion of the pressing spring and the braking cylinder when the idle gear of FIG. 7 is in the completely meshed state C. FIG.

FIG. 10 is an explanatory view showing an embodiment in which the input gear and the output gear have different rotation axes.

FIG. 11 is a front sectional view showing the configuration of an example of a conventional gear transmission.

[Explanation of symbols]

 10 gear transmission device 12 input gear 16 first gear 18 insertion hole 20 second gear 22 spring as biasing means 104 output gear 106 idle gear

Claims (2)

[Claims] 1. An input gear, an output gear, and the input gear and the output gear are provided so as to be movable toward and away from each other. When the input gear and the output gear are meshed with each other, the rotational force of the input gear is output to the output gear. In the gear transmission having an idle gear for transmitting to the first gear, the input gear has a first gear having at least one protrusion formed on a side surface thereof, and the first gear is arranged in parallel with the first gear. A second gear that is formed with an insertion hole into which the protrusion can be inserted with play, and is rotatable about the same rotation axis as the first gear within a predetermined angle range with respect to the first gear; And a biasing means that is provided between the first gear and the second gear and that constantly biases the relative position of the second gear with respect to the first gear to an intermediate position within the angular range. Must be able to mesh with either the first gear or the second gear Gear transmission according to claim. 2. An input gear, an output gear, and the input gear and the output gear, which are provided so as to be movable toward and away from the input gear and the output gear, and the rotational force of the input gear is output when meshed with both the input gear and the output gear. In the gear transmission having an idle gear for transmitting to the main gear, the input gear includes a main gear in which a first cylindrical body is provided on one side surface along the rotation axis direction, and the main gear is arranged in parallel with the main gear. A secondary gear that is rotatable about the rotation shaft and has a second cylinder on a side surface on the main gear side, the second gear extending along the rotation axis, and the first cylinder and the second cylinder. A gear transmission, comprising: a coil spring externally fitted over the body, wherein the idle gear is meshable with the sub gear.