JPH0515639Y2 - - Google Patents

Description

[Detailed Description of the Invention] (1) Purpose of the Invention (Field of Industrial Application) This invention relates to a transmission, particularly a transmission that controls the speed of a reciprocating motion device.

(Prior Art and Issues to be Solved) In a reciprocating motion device using a gear mechanism, as a means for controlling its motion speed, conventionally a stepped transmission mechanism is used that has a gear ratio set in multiple stages. Continuously variable speed is impossible, and if you try to change speeds in multiple stages over a wide speed range in order to achieve something close to continuously variable speed, the number of gears and clutches will increase. The number of parts has increased, the structure has become complicated, and the size has inevitably become larger.

Regardless of such mechanical means, DC is applied to the drive source.
It is possible to achieve continuously variable speed through pulse control using a motor, but of course this requires
It was necessary to separately install a DC motor, a DC power supply for driving the same, and a control circuit, which was disadvantageous compared to the mechanical means mentioned above in terms of space, failure, and heat generation.

The present invention was devised to deal with such a situation, and the object of the present invention is to provide a transmission device that can change speeds relatively easily and steplessly over a wide range by pure mechanical means. be.

(2) Structure of the invention (technical means for solving the problem, its effect) In order to achieve the above object, the invention consists of a gear having a driven shaft, and a first gear that meshes with the gear and is displaced in a fixed direction. a rack, a first guide member that engages with the first rack and extends in a direction perpendicular to the direction of displacement of the first rack, and is movable in the direction of displacement; a second rack having a pin movable in the longitudinal direction thereof;
a second guide member 2 capable of supporting the rack and changing the angle of this rack with respect to the first guide member;
A transmission device comprising a drive shaft attached to a gear that meshes easily with the gear.

With this configuration, the drive side can be maintained at a constant speed with an extremely simple configuration.
The speed of the driven side can be changed steplessly over a wide range.

(Description of Embodiments) Figures 1, 2A, and 2B illustrate the operating principle of the present invention.

In FIG. 1, a gear 1 is attached to the shaft 1a, and the gear 1 meshes with the first rack 2. In FIG. The rack 2 has long holes 2a and 2 formed therein.
It is movable only in the left and right directions in the figure by appropriate guide means such as fixing pins P1 and P2 loosely fitted into the holes b.

A pin P3 is attached to the end of the rack 2, and this pin engages with a first guide member 3 arranged perpendicular to the direction of movement of the rack,
A guide groove 3a is formed in this guide member 3, and a pin 4 is slidably engaged in this groove.

Although not shown, it is assumed that the guide member 3 is supported by a suitable support member and is movable in the left and right directions in the figure.

With this structure, when the pin 4 is moved in the X direction shown in the figure, the guide member 3 and the rack 2 also move, thereby rotating the gear 1, and in this case, the speed of the pin 4 is changed to V1. Then, the speed of the rack will naturally be V1, and the shaft 1a will also rotate at a predetermined speed via the gear 1.

When the pin 4 moves in the groove 3a in the Y direction shown in the figure, the rack 2 remains stationary and the shaft 1a does not rotate either.

Pin 4 speeds in the direction of angle α with respect to the X direction
If the vehicle moves straight at V1, as can be seen from the figure, the speed of rack 2 will be V1 Cosα, and shaft 1a will also rotate at a speed corresponding to this.

Therefore, by changing the speed and direction of the pin 4, the rotational speed of the shaft 1a can be changed steplessly from zero to the speed determined by the speed V1.

2A and 2B show a configuration for changing the direction and speed of the pin 4, and a gear 5 driven by a drive source (not shown) has a second
The racks 6 are engaged with each other, and a pin 4 is attached to the racks 6.

Furthermore, one end edge 6a of the rack 6 is slidably engaged in a groove 7a formed in the end edge of a second guide member 7 pivotally connected to the shaft 5a of the gear 5.

Therefore, when the guide member 7 is rotated in the direction of the arrow A in the figure, the rack 6 also rotates while being engaged with the gear 5. Therefore, when the gear 5 is driven in this rotation position, the rack 6 also rotates in this rotation position. At this position, the pin 4 slides in the groove 7a, and the pin 4 also moves in the same direction.

Therefore, pin 4 in FIGS. 2A and 2B
is engaged with the groove 3a shown in FIG. 1, and as described above, by tilting the rack 6 by the angle α and moving the pin 4 forward and backward in that direction, the pin 4 slides in the groove 3a of the guide member 3. The shaft 1a can be rotated at a reduced speed according to the angle α.

Since the angle α can change continuously between the X and Y directions in Figure 1, the rotation of the axis 1a also has one speed.
It can be changed continuously between the rotational speed corresponding to V1 and zero.

Furthermore, by changing the speed V1, it is also possible to variously change the speed change rate and the maximum speed.

FIGS. 3, 4, and 5 show an embodiment in which the present invention is applied to a means for moving a document table disposed on the top surface of a copying machine.

FIG. 3 is a side view of the main part, showing the document table in its home position.
Reference numeral 10 indicates a drive gear driven by a drive source (not shown), which meshes with a forward gear 11, which in turn meshes with a reverse gear 14.

These gears 11 and 14 are connected to the clutch 1, respectively.
2 and 15 to engage and disengage the forward sprocket 13 and the reverse sprocket 16.

As can be seen from Fig. 4, a shaft 31 is pivotally attached to the bracket BL which is placed in the appropriate position on the main body FL of the copying machine, and a sprocket is integrally attached to the carrier C of the planetary gear mechanism (described later) attached to the shaft. A chain 17 between this sprocket 30 and each of the sprockets 13 and 16 is suspended.

A sun gear S is pivotally connected to the shaft 31, and a control rack drive gear 29 that meshes with a control rack R3, which will be described later, is also provided.

A rack guide 24 that slidably supports a rack R3 that engages with the control rack drive gear 29 is provided near the left end of the shaft 31 in the figure, and a gear 34 provided on the rack guide 24 meshes with the gear 22. , the gear 22 is connected to the stepping motor 19 via the gear 21 and the worm 20.

Therefore, when the motor 19 is driven, the gear 34 rotates through the worm 20 and the gears 21 and 22.
Along with this, the rack R3 remains in mesh with the control rack drive gear 29.
The rack guide 24 holding the rack 3 rotates around the shaft 31.

A rack R2 is slidably disposed on a bent edge 18a provided on one side of a bracket 18 attached to the main body of the copying machine, and the rack R2 is connected to the sun gear S.
is engaged in.

A pin guide 26 is disposed in a direction perpendicular to the rack R2, and a pin 25 provided on the rack R3 is slidably engaged with a groove formed in the pin guide 26.

As can be seen from FIG. 4, a shaft 32 is pivotally connected to the carrier C, and pinions P1, P2 are attached to the shaft.
The pinion P1 meshes with the sun gear S, and the pinion P2 meshes with internal teeth provided on the ring gear L, forming a planetary gear mechanism. Further, the external teeth of the ring gear L mesh with a rack R1 provided on the lower surface of the document table 28.

The operation of the planetary gear mechanism will now be described with reference to FIG. 5.

This figure is a perspective view showing only the planetary gear mechanism of the apparatus shown in FIGS. 3 and 4, and corresponding parts are designated by the same reference numerals.

When the carrier C and sprocket 30 are rotated via the forward sprocket 13 and chain 17 mentioned above, if they rotate at the same speed and in the same direction as the sun gear S image carrier C, both pinions P1 and P2 cannot rotate on their own axis. The ring gear L rotates at the same speed as the carrier C in the same direction.

In addition, when the sun gear S is fixed, both pinions P1 and P2 revolve around the sun gear S while rotating around the shaft 32, and in the case shown in the figure, the number of teeth of P2>the number of teeth of P1, so the ring gear L rotates in the same direction as carrier C, but faster.

If the rotational speed of the carrier C is V1, that of the sun gear is V2, and that of the ring gear is V3, and the overall gear ratio consisting of the sun gear S, pinions P1 and P2, and the internal teeth of the ring gear L is K, then the speed of the ring gear L is V3=V1+(V1-V2)K, and if V1 and K are kept constant, by changing the speed V2 of the sun gear S, the speed of the ring gear L and, therefore, the speed of the document table can be controlled. .

Next, the operation of the apparatus shown in FIGS. 3 and 4 will be explained.

The stepping motor 19 rotates in response to a signal from a control unit (not shown), and the worm 20 and gear 2
1, 22, 34, Rack Guide 24
is rotated by an angle corresponding to the set speed of the document table.

After the rack guide 24 stops, the gears 10, 11, and 14 are rotated in the direction of the arrow by a main motor (not shown).

At this time, by operating the clutch 12, the forward sprocket 13 is activated, and the chain 1
7, the sprocket 30 and carrier C rotate counterclockwise, and the rack R1, and thus the document table 28, are moved in the direction of arrow F in the figure through pinions P1, P2, and ring gear L.

At this time, the gear 29, which is coaxial with the carrier C, also rotates in the same direction, and the rack R3 slides in the rack guide 24, which is at an inclined position corresponding to the preset speed.

As mentioned above, since the rack R3 is operatively connected to the rack R2 via the pin 25 and pin guide 26 provided therein, the pin 25 of the rack R3
slides in the groove of the pin guide 26 and slides into the rack R2.
is run along the bent edge 18a, and the speed of the rack R2 at this time is as shown in FIG. 1, FIG. 2A,
In the same way as explained in FIG. 2B, it is determined by the speed from the chain 17 side and the inclination of the rack R3.

Rack R2 meshes with sun gear S, so
In the end, the sun gear S rotates at a speed determined by the inclination of the rack R3, using the speed of the chain 17 as a reference, and causes the document table 28 to travel via the ring gear L and the rack R1. The speed of the document table can be changed by changing the inclination of the rack R3.

When the document table 28 has traveled a predetermined distance, the forward latch 12 is turned off, the reverse clutch 15 is turned on, the chain 17 runs clockwise, and all the members including the planetary gear mechanism operate in the opposite direction. The document table also moves in the direction of arrow B, reaches the home position, and stops.

In the above embodiments, a cam can be used instead of the stepping motor and gear train, and a belt, wire, etc. can be used instead of the chain.
Furthermore, it is easily understood that a pin guide may be disposed on the document table in a direction perpendicular thereto, and a variable angle rack corresponding to the rack R3 may be connected to the pin guide.

(3) Effects of the invention As explained above, according to the invention, a drive unit that rotates at a constant speed can be continuously variable speed with an extremely small number of parts and a simple configuration, which saves space. Undesirable heat generation can be effectively prevented.

[Brief explanation of the drawing]

FIGS. 1, 2A, and 2B are explanatory diagrams explaining the principle of the present invention, FIG. 3 is a side view of essential parts showing an embodiment in which the present invention is applied to a copying machine, and FIG. 4 is an X-
A sectional view taken along the Y line and FIG. 5 are perspective views showing only the planetary gear mechanism portion of the same. 1... Gear, 2, 6... Rack, 3, 7... Guide member, 4... Pin, 10... Drive gear, 11...
...Forward gear, 14...Reverse gear, 12, 15...
Clutch, 13... Forward sprocket, 16...
Reverse sprocket, 17...Chain, 18...
Bracket, 24...Rack guide, 25...Pin, 26...Pin guide, 29...Gear, 30...
...Sprocket, 31...Shaft, C...Carrier,
S... Sun gear, R1, R2, R3... Easy.

Claims (1)

[Claims for Utility Model Registration] A gear having a driven shaft, a first rack that engages with the gear and is displaced in a certain direction, and a direction that engages with the first rack and is perpendicular to the direction of displacement thereof. a first guide member disposed extending in the direction of displacement and freely displaceable in the displacement direction; a second rack having a pin that engages with the first guide member and is movable in the longitudinal direction thereof; a second guide member that supports a second rack and can change the angle of the rack with respect to the first guide member; and a drive shaft attached to a gear meshing with the second rack. .