JPH09211593A - Planetary gear mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obviate the occurrence of operation defects and damage by a simple improvement by provide a sun gear with a planetary gear in such a manner that the inter-shaft distance thereof may be varied. SOLUTION: A friction member 9 is acted as a coil spring between the sun gear 1 and a planetary carrier 8. The planetary gear 2 fits into an oblong hole 8a formed at the planetary carrier 8 and is further mounted at the shaft 2b of the planetary gear 2 to prevent the detachment of the planetary gear 2 from the planetary carrier 8. A spring 22 is acted between a washer 21 and a projection 8b formed at the planetary carrier 8 to energize the planetary gear 2 in the direction where the planetary gear parts from the sun gear 1 along the oblong hole 8b. As a result, the planetary gear 2 is energized in the direction where the planetary gear 2 parts from the sun gear 1 by acting the spring 22 therein in the state of the supporting structure, as simple as heretofore, for supporting the planetary gear 2 at the planetary carrier 8 coaxial with the sun gear 1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear mechanism,
In particular, the sun gear, the planetary gear supported so as to revolve around the sun gear while rotating around the sun gear, and the planetary gear that is supported along the revolution path of the planetary gear. The present invention relates to a planetary gear mechanism including an appropriate number of driven gears that mesh with each other at a predetermined revolution position.

[0002]

2. Description of the Related Art FIG. 15 shows the simplest structure of such a planetary gear mechanism. A planet carrier b coaxial with the sun gear a supports a planet gear c that meshes with the sun gear a. When the driving force is transmitted to the sun gear a, the planetary carrier b is accompanied by the planetary gear c by the action of the friction member that acts between the sun gear a and the planetary carrier b or between the planetary carrier b and the planetary gear c. The sun gear a rotates together. At this time, the planetary gear c revolves around the sun gear a. Therefore, if there is a driven gear d provided along the revolution path of the planetary gear c, the planetary gear c will move to the driven gear d by the revolution. The meshing is released at the position, and the meshing is released by moving to a position other than the predetermined position.
When the planet carrier b is stopped by a stopper or the like in the meshed state, the rotation of the sun gear a is transmitted to the planet gear c, and the planet gear c drives the meshed driven gear d. Therefore, the planetary gear c can be connected to and disconnected from the driven gear d as required, and the driven gear d can be driven at any time in the connected state. This drive need only drive the sun gear a and can be performed by drive control of one motor. Japanese Unexamined Patent Publication No. 1-287648 discloses such a planetary gear mechanism.

[0003]

The feature of the planetary gear mechanism as described above is that the planetary gear c is selected from a plurality of driven gears d provided around the planetary gear c as shown in FIG. It can also be used to transmit driving force by connecting them in series. As a result, a sequence operation of performing a plurality of operations in a predetermined order or at a predetermined timing can be achieved by drive control of one motor, and thus is desired for practical use.

However, such a planetary gear mechanism sometimes causes malfunction. The driven gear d is shown in FIG.
In order to allow the planetary gear c to selectively mesh with any of them by the revolution when there are three or more as shown in FIG. 15, the planetary gear c is the sun gear a as shown in FIG. It is necessary to transmit the driving force to a predetermined driven gear d in a state where they and the driven gear d mesh with each other in series (hereinafter referred to as a planetary series state). As a result, the planet gear c
Is a position where it can mesh with a predetermined driven gear d to drive it, or passes through such a meshing position,
The other driven gear d can be driven by freely revolving to a position where it meshes with another driven gear d.

However, in the planetary gear mechanism having such a planetary series state, the planetary gear c goes to the planetary series state between the driven gears d and the driven gears d, as shown in FIGS.
At the beginning of meshing as shown in Fig. 11, the planetary gear c and the driven gear d are pushed together by the tips of two teeth as shown in Fig. 11 (b), or in Fig. 15 (c). It is easy for the tips of one tooth to stick together. If the tooth tips stick to each other in this way, the planetary gear c and the driven gear d cannot rotate in either direction and are mechanically stable. Once stabilized, the sun gear a cannot be released unless it is reversed. Will stop. This is the cause of the malfunction. When the driving force is large and it is difficult to stop, the gear support shaft and gear teeth are damaged and repair is required.

However, the driven gear d for transmitting the driving force
There are only two or less, and a line e connecting the axes of the sun gear a and the planet gear c and a line f connecting the axes of the planet gear c and the driven gear d are shown in FIG. Even if the planetary gear mechanism is such that the planetary gear c meshes with the driven gear d to transmit the driving force in the non-serial planetary state where the planetary gear c does not become a straight line as shown in the above, the abutting of the teeth as described above cannot be completely prevented and a problem remains. However, as the angle between the line e and the line f approaches a planet straight line state where the angle is 180 °, the above-mentioned bracing of the tooth tips is more likely to occur. Those which mesh in these planetary non-series states are also the subject of the present invention.

SUMMARY OF THE INVENTION An object of the present invention is to provide a planetary gear mechanism which is a simple improvement and does not cause the above-mentioned malfunction or damage.

[0008]

In order to achieve the above object, the present invention provides a sun gear and a planetary gear that is supported by the sun gear so as to rotate around the sun gear and revolve around the sun gear. And an appropriate number of driven gears, which are provided along the revolution path of the planet gear and mesh at a predetermined revolution position of the planet gear, in the planet gear mechanism, It is characterized in that the distance is variable.

In such a structure, as is conventional, the sun gear is driven as required to revolve the planetary gear around itself and selectively engage with a predetermined number of predetermined driven gears. Can be driven, and the meshing can be canceled to disconnect the two. In particular, when the tooth tips of both teeth are pressed against each other when the planetary gear starts to mesh with a predetermined driven gear, the planetary gear tends to be prevented from further revolution by interference with the driven gear. At this time, if it is conventional, it will be stable as it is, but the planetary gear is retracted to the sun gear side until there is no play with the sun gear within this variable range because the axial distance to the sun gear is variable. It escapes from the interference and revolves further, getting out of the state of being in tension with the driven gear,
The driven gear can be smoothly meshed and driven. Further, it becomes smooth to pass through the driven gears provided by three or more gears and meshing with them in the planetary series state. Therefore, malfunction can be eliminated and reliability can be improved by simply improving the planetary gear.

According to a second aspect of the present invention, in addition to the first aspect of the present invention, the planet gear is supported on a planet carrier coaxially provided with the sun gear, and the planet carrier has a direction in which the planet gear is separated from the sun gear. The urging means for urging is activated.

According to the second aspect of the present invention, in addition to the first aspect of the present invention, the planetary gear is supported by a simple conventional supporting structure for supporting the planetary gear on a planet carrier coaxial with the sun gear. The urging means can be urged in the direction away from the sun gear, and even if the tips of the planet gears bulge at the beginning of the meshing with the driven gear, the planet gear will not move to the sun gear due to the urging. Since the play between the two is the largest and the driven gear is out of the thrust state with the driven gear, a large retreat allowance is always secured, so the planetary gear can be pulled out from the thrust state. Easy and simple structure improves operation stability.

According to a third aspect of the present invention, in addition to the first aspect of the present invention, the planetary gear is provided on a lever provided on the planet carrier coaxially with the sun gear so as to swing in the radial direction of the sun gear. Supported, the lever is actuated by a biasing means that biases the planetary gear away from the sun gear.

According to the structure of the invention of claim 3, in addition to the invention of claim 1, the planetary gear is further urged in a direction away from the sun gear to stabilize the operation similarly to the invention of claim 2. In order to improve the property, since it is possible to support the planetary gear so as to move more stably by utilizing the swing around the pivotal support part of the lever provided on the planetary carrier coaxial with the sun gear,
The operation stability is improved as compared with the invention of claim 2.

According to a fourth aspect of the present invention, the sun gear, the planetary gear supported so as to revolve around the sun gear and revolve around the sun gear, and the revolution path of the planetary gear are provided. In a planetary gear mechanism provided with an appropriate number of driven gears that mesh with each other at a predetermined revolving position of the planetary gear, the planetary gear mechanism meshes with the planetary gear at a position before the planetary gear starts to mesh with the driven gear by the revolution. It has a matching means for matching it with a predetermined rotation phase.

With such a structure, as in the case of the invention of claim 1, as in the conventional case, the planetary gear is selectively meshed with a predetermined number of predetermined driven gears to drive them, and the meshing is performed. It is also possible to cancel the connection and disconnect both sides. In particular, the planetary gear meshes with the alignment means at a position before starting to mesh with the predetermined driven gear and is aligned with the predetermined rotation phase. By making the meshing phase coincide with each other, the planetary gear can smoothly mesh with the driven gear after passing through the aligning means, and the aligning means need only be provided with the pin as in the invention of claim 5. With an extremely simple structure, malfunctions can be eliminated and reliability is improved. According to the invention of claim 6, in any one of the inventions of claims 4 and 5, the aligning means is movably supported in a direction away from the planetary gear and is biased in a direction close to the planetary gear. ing.

According to such a constitution of the invention of claim 6, in addition to any one of the inventions of claims 4 and 5, further, when the planet gears start to engage with the aligning means, the teeth of the planet gears are Even if the tip of the tooth sticks against the aligning means, the aligning means moves the planetary gear out of the tensioned state while escaping to the planetary gear, and at the same time, meshes with the aligning means to match the predetermined rotation phase, It is possible to smoothly mesh with the driven gear, and the stability of operation is further improved.

According to a seventh aspect of the present invention, in addition, in the sixth aspect of the invention, the aligning means meshes with the planetary gear up to a position after the planetary gear starts to mesh with the driven gear by the revolution.

According to the structure of the invention of claim 7, in addition to the invention of claim 6, the aligning means further moves by engaging the planetary gear to a position after the planetary gear has started to mesh with the driven gear, thereby allowing the planetary gear to move. It is possible to prevent the once-matched rotation phase of the gears from being changed before meshing with the driven gears, thereby further improving the operation stability.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, some embodiments of the present invention will be described in detail with reference to the drawings.

(Embodiment 1) The present embodiment 1 is shown in FIG.
A planetary gear mechanism having a sun gear 1 and a planetary gear 2 that meshes with the sun gear 1 and revolves around the sun gear 1 as shown in FIG. The planetary gear 2 can be driven by selectively meshing it at a predetermined revolution position. It is a series of cameras such as film winding, film rewinding, lens zoom operation, shutter release related operation. The sequence operation of is performed. However, various operations of the cassette of the VCR, such as loading, pulling out the tape and winding it on the cylinder, winding the tape, rewinding the tape, fast-forwarding the tape, rewinding the tape, and ejecting the cassette in a predetermined order or It is said to be performed at a predetermined timing, or various movements of a wiper such as an automobile.
It can be applied to any other sequence operation. In addition,
An appropriate number of driven gears may be provided according to the number of elements to be driven.

In the planetary gear mechanism of the first embodiment, as shown in FIG. 5, a planet carrier 8 is provided coaxially with the sun gear 1 via a friction member 9, and the planet carrier 8 is provided.
The planetary gear 2 is supported by the shaft 2b. The friction member 9 has the same function when it is operated between the planet carrier 8 and the planet gear 2. In the illustrated state, when a motor (not shown) is rotated in the normal direction, the sun gear 1 is rotated counterclockwise.
At this time, the action of the friction member 9 also tends to rotate the planet carrier 8 counterclockwise. However, the planet carrier 8 is in contact with the stopper 11 and is prevented from rotating, and the planet gear 2 stops in a state of meshing with the driven gear 3 and becomes stable. When the planet carrier 8 is stopped as described above, the counterclockwise rotation of the sun gear 1 is transmitted to the planet gear 2, and the driven gear 3 meshed with the planet gear 2 is rotationally driven counterclockwise. . As a result, the indexing mechanism IND as a load connected to the driven gear 3 is advanced.

Here, when it is desired to perform the indexing operation so as to drive the load connected to the driven gear 4, first, the indexing mechanism IND is advanced by the forward rotation of the motor to move the rotation position of the planet carrier 8 to the stopper 12. Select the position and stop the motor. At this time, the stopper 12 corresponding to the selected rotation position enters the rotation path of the planet carrier 8 through the indexing mechanism IND and stands by. Next, when the motor is rotated in the reverse direction, the sun gear 1 rotates clockwise, the planet carrier 8 rotates clockwise by the action of the friction member 9, and when it comes into contact with the stopper 12, it rotates further. Is stopped and stopped. At this time, the planet gear 2 meshes with the driven gear 4 and rotates counterclockwise in response to the rotation of the sun gear 1, so that the driven gear 4 is driven clockwise. As a result, the load series connected to the driven gear 4 can be operated to perform a predetermined operation.

Next, the case where the driven gear 5 is driven will be described. First, to disengage from the driven gear 4, the motor is normally rotated. Then, the sun gear 1 rotates counterclockwise, and the planetary carrier 8 rotates counterclockwise from the state in which the planetary carrier 8 abuts on the stopper 12 by the action of the friction member 9, and abuts on the stopper 11. Stop.

As a result, the planetary gear 2 is disengaged from the driven gear 4 and reengages with the driven gear 3. The motor continues to rotate normally, the driven gear 3 is rotationally driven counterclockwise, and the indexing mechanism IND is further advanced. As the indexing mechanism IND advances, the previously selected rotational position is escaped, and the position of the stopper 14 corresponding to the next rotational position is selected. As a result, the stopper 12 retracts through the indexing mechanism IND to a position that does not interfere with the rotation of the planet carrier 8, and the stopper 13 corresponding to the next selected rotation position is caused to enter the rotation trajectory of the planet carrier 8. Waiting In this state, when the motor is rotated in the reverse direction, the planet carrier 8 rotates clockwise from the position in contact with the stopper 11 to disengage the planet gear 2 from the driven gear 3,
It passes through the position of the driven gear 4 and comes into contact with the stopper 13 to be stopped. At this time, the planetary gear 2 meshes with the driven gear 5, and the planetary carrier 8 stops to receive the rotation of the sun gear 1 to drive the driven gear 5 clockwise and connect it to the driven gear 5. The specified load sequence can be operated to perform a predetermined operation.

In this case, the planetary gear 2 passes the position of the driven gear 4 as described above while the planetary carrier 8 is rotating clockwise. Here, when the reverse drive of the load series connected to the driven gear 4 is light, the driven gear 4 is rotated slightly counterclockwise by the meshing of the planet gears 2, and when it is heavy, the driven gear 4 is stopped. As it is, the friction member 9 causes the planetary gear 2 to rotate in the clockwise direction together with the planetary carrier 8 while rotating in the counterclockwise direction so as to rotate in contact with the driven gear 4.

When the driving of the driven gear 5 is completed and the user wants to move to the next operation, when the motor is rotated in the forward direction, the sun gear 1 rotates counterclockwise, and the friction member 9 causes the planet carrier to move. 8 is rotated counterclockwise. As a result, the planet carrier 8 is separated from the stopper 13 to disengage the planet gear 2 from the driven gear 5, and then passes through the driven gear 4 and comes into contact with the stopper 11 to be stopped. As a result, the planet gear 2 meshes with the driven gear 3 and the sun gear 1
Further counterclockwise rotation of the indexing mechanism IN
D is advanced, and the stopper 14 corresponding to the next rotation position
Is selected. Also in this case, the planet gear 2 meshes with the driven gear 4 in the counterclockwise revolution, but in this case it is the same as that described above except that the driven gear 4 is driven clockwise. When the next rotation position is selected,
According to this selection, the stoppers 12 and 13 are the planet carrier 8
Is evacuated to the outside of the turning locus. When the motor is rotated in the reverse direction, the sun gear 1 and the planet carrier 8 rotate and rotate clockwise, and the planet gear 2 disengages from the driven gear 3 and then sequentially passes through the positions of the driven gears 4 and 5. Then, the planet carrier 8 comes into contact with the stopper 14 that is always protruding and is stopped. As a result, the planetary gear 2 meshes with the driven gear 6, and by further reverse rotation of the motor, the clockwise rotation of the sun gear 1 is transmitted to the driven gear 6 via the planetary gear 2 and is driven clockwise. As a result, the load series connected to the driven gear 6 can be operated to perform a predetermined operation. To disengage from this driving state, the motor may be rotated in the normal direction.

Here, the planetary gear 2 is repeatedly meshed with the driven gears 3 to 6, but the planetary gear 2 is driven by each of the driven gears 3 to 6.
When the meshing with the gear 6 starts toward the planetary in-series state, the planetary gear 2 and the driven gears 3 to 6 are engaged with each other by the tips of the two teeth as shown in FIG. 11B. Alternatively, as shown in FIG. 11C, the tips of one tooth tend to stick together, which causes the above-mentioned malfunction. When the driving force is large and it is difficult to stop, the gear support shaft and gear teeth are damaged and repair is required.

In order to solve this problem, in the first embodiment, as shown in the principle diagrams of FIGS. 1 to 3, the planet gear 2 supports its rotation shaft 2b in the long hole 8a of the planet carrier 8. The sun gear 1 is provided so that the axial distance can be changed. It should be noted that the driven gears 3 to 6 will be described by showing only the driven gear 4 for simplicity of illustration and description. In such a configuration, as described above, by driving the sun gear 1 as necessary, the planetary gear 2 is revolved around itself, and a suitable number of predetermined driven gears 3 to 6 are selectively formed. It is also possible to drive them by meshing them, or to cancel the meshing and disconnect the both.

When the planetary gear 2 starts to mesh with the predetermined driven gears 3 to 6, the tooth tips of the two teeth 2a and 4a have two teeth (or one tooth) as shown by the solid line in FIG. When the planet gears 2 are pressed against each other, the planet gears 2 tend to be prevented from revolving further due to interference with the driven gear 4.
At this time, if it is a conventional case, it may be stable as it is, but the planetary gear 2 of the first embodiment has an axial distance with the sun gear 1 within a range where the meshing of both gears is not disengaged as shown in FIG. By changing the variable range, the sun gear 1 is retracted until there is no play in the variable range, and the sun gear 1 is revolved while running away from the interference as shown by the phantom line in FIG. It is possible to get out of the state in which the gear 4 and the gear 4 are in tension with each other, smoothly mesh with the driven gear 4, and drive the driven gear 4. Further, as in the first embodiment, three or more driven gears 3 to 6 are provided, and it is also smooth to pass the driven gears 4 and 5 in the middle through a state in which they are meshed in a planetary series state. become. Therefore, malfunctions can be eliminated by a simple modification that makes the planetary gear 2 movable,
It will be highly reliable.

Further, in the first embodiment, as shown in FIGS. 1 to 3, the sun gear 1 is formed in a standard gear shape, whereas the sun gear 1 and the planetary gear 2 in which the tension is generated and the driven gear are driven. The teeth 2a and 4a with the gear 4 are formed in a gear having a pointed tip formed by plus dislocation as shown in FIGS. With such a shape, the teeth 2a and 4a are less likely to be braced against each other, and even if the braces are braced against each other, it is possible to easily cancel the bracing, so that the stability of the operation is also improved. .

More specifically, FIG. 4A and FIG. 4B
As shown in, the friction member 9 acts as a coil spring between the sun gear 1 and the planet carrier 8. In addition, the planet gears 2 are formed in the planet carrier 8 and have an elongated hole 8a.
It is fitted inside and is attached to the shaft 2b of the planetary gear 2, and in order to prevent the planetary gear 2 from coming off the planetary carrier 8, a spring is provided between the washer 21 and the projection 8b formed on the planetary carrier 8. The planet gear 2 is urged in a direction away from the sun gear 1 along the elongated hole 8b by operating 22.

As a result, the spring 22 works on the planetary gear 2 while maintaining the simple supporting structure for supporting the planetary gear 2 on the planetary carrier 8 coaxial with the sun gear 1 as in the prior art.
Can be urged away from the planetary gear 2 at the beginning of meshing with the driven gear 4 and its teeth 2a and 4
Even if the tooth tips of a are stretched, the planetary gear 2 is separated from the sun gear 1 by the above-mentioned bias to the maximum extent and the play between them is the largest, and the planetary gear 2 is stretched with the driven gear 4. Since a large withdrawal allowance for getting out of the fitted state is always secured, the planetary gear 2 can easily come out of the struted state, and the operation stability is further improved with a simple structure.

(Second Embodiment) FIG. 6 shows the second embodiment. The planetary gear 2 is supported by a lever 32 pivotally supported by a shaft 31 so as to swing in the radial direction of the sun gear 1 on a planetary carrier 8 provided coaxially with the sun gear 1. A spring 33 for urging the planet gear 2 away from the sun gear 1 is operated between the planet carrier 8 and the planet carrier 8.

In such a structure, when the planetary gear 2 is biased by the spring 33 in the direction away from the sun gear 1, swinging around the pivotal support of the lever 32 provided on the planetary carrier 8 coaxial with the sun gear 1 is performed. Since the planetary gear 2 can be supported so as to move more stably by utilizing the motion, the stability of operation is improved as compared with the case of the first embodiment.

(Third Embodiment) FIG. 7 shows a principle diagram of the third embodiment, and the sun gear 1 is the same as in the first embodiment.
And a planetary gear 2 supported by a planet carrier 8 coaxial with the sun gear 1 so as to revolve around the sun gear 1 while rotating around the sun gear 1, and a revolution path of the planetary gear 2. Installed along this planetary gear 2
Is a planetary gear mechanism provided with an appropriate number of driven gears ... 4 that mesh with each other at a predetermined revolving position, and at a position before the planetary gear 2 starts to mesh with the driven gears ...
This is different from the first embodiment in that an alignment means 41 is provided which meshes with the planetary gear 2 and aligns it with a predetermined rotation phase.

The aligning means 41 may be a single pin as shown in FIG. 7, may be several pins, or may be a partial gear or the like. Also in the third embodiment, it is possible to selectively engage the planetary gear 2 with a predetermined number of predetermined driven gears ... 4 to drive it, and to cancel the engagement to disconnect the two. However, in particular, at a position before the planetary gear 2 starts to mesh with the predetermined driven gears ... 4 ..., the aligning means 41 meshes with the state of the broken line in FIG. 7 and is aligned with a predetermined rotation phase. By making the rotation phase of the planet gear 2 coincide with the meshing phase with the driven gears ... 4 that stop at a fixed origin position, the planetary gear 2 passes through the matching means 41 and then the driven gears ... 4 ... 7 can be meshed smoothly as shown by the solid line. Since the matching means 41 need only be provided with the pins as in the present embodiment, it is possible to eliminate malfunctions with an extremely simple structure.
It will be highly reliable.

More specifically, as shown in FIG. 8, the aligning means 41, which is a pin, can be moved in a direction away from the planetary gear 2 along an elongated hole 42 formed in a base plate (not shown) or the like. And the matching means 41 is provided in the planetary gear 2
Is urged by a spring 43 in a direction approaching the. With this configuration, in addition to the case of the second embodiment, when the planet gear 2 starts to engage with the pin 41, the tip of the tooth 2a of the planet gear 2 should be aligned with the pin 41 that is the alignment means. Even if they are thrust together, the pin 41 escapes from the planetary gear 2 to allow the planetary gear 2 to come out of the thrusted state, and the driven gear ... 4
... can be smoothly meshed with, improving the stability of operation.

Particularly, the matching means formed by the pins 41 and the like is adapted to mesh with the planetary gear 2 to a position after the planetary gear 2 starts to mesh with the driven gears 4 ... As a result, in the aligning means 41, the planet gears 2 are driven gears ... 4 ...
Mesh with the planetary gear 2 to the position after starting to mesh with
It is possible to prevent the once aligned rotation phase from being deviated by the time it meshes with the driven gears 4 ..., and the stability of the operation is further improved.

FIG. 9 shows a more detailed example of the third embodiment, in which the friction member 9 which is a coil spring is made to act between the planet carrier 8 and the planet gear 2, and the matching means 41 such as a pin is at the lower end. Is pivotally supported on the base plate 143 by a shaft 44, and the tip end side is allowed to move in a direction away from the planetary gear 2 along the elongated hole 42 by swinging about the shaft 44, and the pin 41 in the elongated hole 42 A spring 43 for urging the side closer to the gear 2 is operated. (A) of FIG.
Shows a state in which the matching means 41 properly meshes with the planetary gear 2 and is aligned with a predetermined rotation phase, and FIG. 9B shows the planetary gear 2.
The tooth 2a of the above shows the state in which the tooth 2a is in tight contact with the matching means 41,
The planetary gear 2 is pushed out of the aligning means 41 by the teeth 2a, comes out of the tension with the aligning means 41, and then engages with this to align the rotation phase.

(Fourth Embodiment) FIG. 10 shows the fourth embodiment.
The pin-shaped matching means 41 is formed by the one end of the vine winding spring 51 in which the vine winding portion 51a is supported by the substrate 143.
By locking the other end portion 51b to the substrate 143, the pin 41 can be urged in a direction to approach the planet gear 2. As a result, a special urging member for urging the pin-shaped matching means 41 in the direction of approaching the planetary gear 2 is not particularly required, and the configuration is simpler than that of the third embodiment.

(Fifth Embodiment) FIG. 11 shows the fifth embodiment.
This is a combination of the configurations of the second embodiment and the third embodiment. Before the planet gear 2 starts to mesh with the driven gear 4, the phase of meshing the rotation phase with the driven gear 4 by the matching means 41 is shown. However, even if the teeth 2a of the planetary gear 2 bulge against the aligning means 41, the planetary gear 2 escapes from the bulging bulge due to the swing against the spring 33 of the lever 32, and is smooth. Since the meshing phase with the matching means 41 is matched with the matching means 41, the matching means 41 may be a fixed pin. The supporting structure of the planetary gear 2 may be that of the first embodiment.

(Sixth Embodiment) FIG. 12 shows the sixth embodiment.
The planetary carrier 8 is biased to one side by the spring 102, and the stop position of the planetary carrier 8 is changed by the planetary carrier restricting cam 101 against this biasing, so that the planetary gear 2 meshes with the driven gear. 4 and the like are switched, and the matching means 41 of the third embodiment is adopted. Instead of this, the configuration that makes the planetary gear 2 movable as in the first and second embodiments, and the embodiment It is also possible to adopt the matching means of No. 4. The planet carrier restriction cam 101 has a contact surface 101.
The stop position of the planet carrier 8 can be returned by which of a and 101b is brought into contact with the planet carrier 8.

(Seventh Embodiment) FIG. 13 shows a seventh embodiment.
The planetary carrier 8 is disengaged from the shaft 1b of the sun gear 1, and the driven gear 4, etc., with which the planetary gear 2 meshes is switched by swinging the lever 103 around a shaft 103a independent of the sun gear 1. There is. Although the matching means of the third embodiment is adopted, instead of this, it is also possible to adopt a configuration in which the planetary gear 2 is movable as in the first and second embodiments, or the matching means of the fourth embodiment. .

(Eighth Embodiment) FIG. 14 shows the eighth embodiment.
Is shown. The eighth embodiment has no planet carrier. The planetary gear 2 is guided by a long hole 104 of a base plate (not shown) and is urged to one side by a spring 105, and the position of the spring-biased planetary gear 2 is switched depending on the rotation position of the planetary gear restriction cam 106. Thus, the driven gear 4 and the like with which the planetary gear 2 meshes can be switched. Due to this switching, the planetary gear control cam 106 has the planetary gear 2
A plurality of contact surfaces 106a, 106b that contact the shaft 2b of the
have. The eighth embodiment also employs the matching means of the third embodiment, but instead of this, the configuration that makes the planetary gear 2 movable as in the first and second embodiments, and the matching means of the fourth embodiment. Can also be adopted.

[0045]

According to the invention of claim 1, by driving the sun gear as necessary, the planetary gear is revolved around itself and selectively meshed with an appropriate number of predetermined driven gears. Even if the tooth tips of both teeth squeeze together when the planetary gear starts to engage with a predetermined driven gear, The gear is further revolved while escaping from the interference until there is no play with the sun gear in the range where the distance between the sun gear and the sun gear is variable. Can be driven by engaging with. Further, it becomes smooth to pass through the driven gears provided by three or more gears and meshing with them in the planetary series state. Therefore, malfunction can be eliminated and reliability can be improved by simply improving the planetary gear.

According to the invention of claim 2, in addition to the invention of claim 1, the planetary gear is urged with the simple conventional supporting structure for supporting the planetary gear on a planet carrier coaxial with the sun gear. The means is operated to urge the sun gear away from the sun gear, and the planet gear is separated from the sun gear by the urging to the maximum extent so that the play between the two is the largest, and the driven gear is separated from the driven gear. Since a large withdrawal allowance is always secured in order to get out of the strut state, the planetary gear can easily come out of the strut state, and the operation stability is improved with a simple structure.

According to the invention of claim 3, in addition to the invention of claim 1, the planetary gear is further urged in a direction away from the sun gear to improve the stability of operation as in the invention of claim 2. However, since the planetary gear can be supported so as to move more stably by utilizing the swing around the pivotal support of the lever provided on the planetary carrier coaxial with the sun gear, the stability of the operation is improved. It is improved compared to the second invention.

According to the invention of claim 4, the planetary gear is selectively meshed with a predetermined number of driven gears to drive it, and the meshing is canceled to disconnect the two. The planetary gear can be smoothly meshed with the driven gear by being aligned with the predetermined rotation phase at a position before starting to mesh with the predetermined driven gear, and the planetary gear can be smoothly meshed with the driven gear. Since it suffices to simply provide such a pin, a malfunction can be eliminated with a very simple structure, and the reliability becomes high.

According to the invention of claim 6, in addition to any one of the inventions of claims 4 and 5, further, when the planetary gear starts to engage with the aligning means, the tips of the teeth of the planetary gear are Even if it is tightly fitted to the matching means, the matching means causes the planetary gear to escape from the tensioned state while escaping to the planetary gear, and at the same time meshes with this to match the predetermined rotation phase and to drive the driven gear. Can be smoothly meshed with, and the stability of operation is further improved.

According to the invention of claim 7, in addition to the invention of claim 6, the aligning means meshes with the planetary gear to a position after the planetary gear starts to mesh with the driven gear, so that the idle gear is temporarily moved. It is possible to prevent the matched rotation phase from being deviated by the time it meshes with the driven gear, and further improve the operation stability.

[Brief description of drawings]

FIG. 1 is a principle diagram for explaining the principle of a first embodiment of the present invention.

FIG. 2 is a view showing a meshing portion between a sun gear and a planet gear of FIG.

3 is a diagram showing a meshing portion between a planetary gear and a driven gear of FIG.

FIG. 4 is a sectional view showing a specific example of the first embodiment of the present invention.

FIG. 5 is a plan view showing a sequence operation mechanism of a camera to which the first embodiment of the invention is applied.

FIG. 6 is a plan view showing a second embodiment which is a modification of the first embodiment of the present invention.

FIG. 7 is a principle diagram showing a third embodiment of the present invention.

FIG. 8 is a plan view showing a specific example of the third embodiment shown in FIG.

9 is a sectional view showing a more detailed specific example of the third embodiment of FIG.

FIG. 10 is a sectional view showing a fourth embodiment of the present invention.

FIG. 11 is a plan view showing a fifth embodiment of the present invention.

FIG. 12 is a plan view showing a sixth embodiment of the present invention.

FIG. 13 is a plan view showing a seventh embodiment of the present invention.

FIG. 14 is a plan view showing an eighth embodiment of the present invention.

FIG. 15 is a principle view showing an operating state of a conventional planetary gear mechanism.

[Explanation of symbols]

 1 Sun Gear 2 Planetary Gears 3 to 6 Driven Gear 8 Planetary Carrier 8a Long Hole 22 Spring 31 Shaft 32 Lever 33 Spring 41 Alignment Means 43 Spring 51 Heel Spring 103 Lever 104 Long Hole

Claims (7)

[Claims] 1. A sun gear, a planetary gear supported so as to revolve around the sun gear while rotating on the sun gear, and a planetary gear provided along the revolution path of the planetary gear. A planetary gear mechanism provided with an appropriate number of driven gears that mesh with each other at a predetermined revolving position of the planetary gear, wherein the planetary gear is provided so that the axial distance is variable with respect to the sun gear. Gear mechanism. 2. The planetary gear is supported on a planetary carrier provided coaxially with the sun gear, and the planetary carrier is provided with a biasing means for biasing the planetary gear away from the sun gear. The planetary gear mechanism according to Item 1. 3. The planetary gear is supported by a lever provided so as to swing in a radial direction of the sun gear on a planet carrier provided coaxially with the sun gear, and the planetary gear is attached to the lever from the sun gear. The planetary gear mechanism according to claim 1, wherein an urging means for urging in a separating direction is operated. 4. A sun gear, a planetary gear supported so as to revolve around the sun gear while rotating around the sun gear, and a planetary gear provided along the revolution path of the planetary gear. In a planetary gear mechanism equipped with an appropriate number of driven gears that mesh with each other at a predetermined revolving position of the planetary gear, at a position before the planetary gear starts to mesh with the driven gear due to the revolution, the planetary gear meshes with the planetary gear and is rotated by a predetermined rotation. A planetary gear mechanism having matching means for matching the phases. 5. The planetary gear mechanism according to claim 5, wherein the aligning means is a pin that meshes with the planetary gear. 6. The planetary gear according to claim 4, wherein the alignment means is movably supported in a direction away from the planetary gear and is biased in a direction close to the planetary gear. mechanism. 7. The planetary gear mechanism according to claim 6, wherein the aligning means meshes with the planetary gear up to a position after the planetary gear starts to mesh with the driven gear by the revolution.