JPH02233897A - Oscillation control device for electric fan - Google Patents

Abstract

PURPOSE: To obtain a desired oscillation by forming a crank in such a way that a planetary gear turns around a sun gear due to the rotation of a carrier relative to a spindle to change a distance between an eccentric pin fixed on the planetary gear and the spindle. CONSTITUTION: Power from an electric fan motor is transmitted to a main gear 5 through a warm 2, a worm gear 1, and a worm gear shaft 3, a sun gear 12 of a spindle 7 rotates through a friction disc 16, and a planetary gear 11 supported pivotally by a pin 13 turns around the sun gear 12 due to the turn of a carrier 9 attached to a hollow shaft 6 integral with the main gear 5 so that an electric fan oscillates through an eccentric pin 10 and a connection bar 14. A cable 21 is pulled, the friction disc 16 is lifted against a spring 17 on an operation lever 19 to disengage it from the main gear 5 in order to adjust a crank length between the eccentric pin 10 and the spindle 7.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a device for controlling the swing angle of an electric fan, and more particularly to a device suitable for controlling the magnitude of the swing angle when the fan swings its head. .

(Left below) [Prior Art] Conventional electric fans operate with a motor in either a fixed mode or an oscillating mode. That is, the air flow is provided in a fixed direction or in a partial area corresponding to a fixed swing angle. If you blow wind on a person for a long time, you can make that person feel cool in a relatively short period of time, but if the wind blows on you for a long time, it will make you feel uncomfortable.
Fixed mode is also rarely used in the case of a single person. If people are gathered in a relatively small area, the oscillation interval of the oscillation mode may be too long to satisfy them. Therefore, it will be understood that there is a need for an electric fan whose swing angle can be adjusted and controlled as necessary.

The oscillating device in a conventional electric fan is usually a link mechanism consisting of four bars. To change the magnitude of the oscillation angle, the length of one of the bars, usually the length of the crank, is changed. Previous proposals have been made to achieve such length changes. According to this proposal, the pin or sliding bar moves freely in the slot, and the length of the crank and the parameters of the four-bar linkage are changed accordingly, thereby adjusting the swing angle. It is now possible.

[Problems to be Solved by the Invention] However, this mechanism has several problems because the pin or sliding bar is moved and positioned in the slot by the force obtained from the spring and the adjustment mechanism. There is. On the one hand, it is desirable that the elastic force due to the spring or the frictional force between the pin and the throft be as small as possible in order to facilitate the movement of the pin or sliding part. On the other hand, the above-mentioned forces are preferably large enough to counteract the reaction forces induced by the connecting bar during rotation of the crank, so as to ensure that the pins are positioned and fixed after adjustment. It has become. Unfortunately, finding a compromise is very difficult due to the limited space available in the gearbox of the oscillating device. Therefore, in the oscillating device based on the above-mentioned idea, adjustment is very difficult or the oscillating angle shifts during operation. SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a fan oscillation control device that solves the above-mentioned problems existing in the prior art.

[Means for Solving the Problems] The oscillating device of the present invention is not only easy to adjust, but also allows the length of the crank to be kept constant, so that the fan is always kept at a predetermined angle. It can make you shake your head.

The object of the present invention is achieved based on the operating principle described below using a planet gear system consisting of a sun gear, a planet gear, and a planetary carrier.
An eccentric pin is fixed to the planet gear, and the sun gear meshes with the planet gear during operation. The planet gear is rotatably attached to a planetary carrier connected to the hollow shaft. The sun gear is fixedly connected to a spindle arranged coaxially with the hollow shaft. When the planetary carrier rotates with respect to the spindle, the planet gear rotates around the sun gear. Therefore, the distance between the axis of the eccentric pin fixed to the planet gear and the axis of the sun gear, that is, the axis of the spindle, changes continuously, and there is a variable length between the two axes. A crank is formed. When the rotation of the planetary carrier is synchronized with the rotation of the sun gear, the distance between the two axes, that is, the length of the crank is kept constant. If the distance between the pin axis and the planet gear axis is equal to the distance between the planet gear axis and the sun gear axis, the crank length can be changed from 0 to the maximum value. be. The maximum length of the crank is 2 times the distance between the axis of the planet gear and the axis of the sun gear.
It's double.

By replacing the fixed-length crank of the conventional oscillating device with the variable-length crank of the present invention, the oscillating angle of the electric fan can be adjusted from 0 to the maximum value.

A main gear is attached to one of the spindle and the hollow shaft, and the main gear meshes with the worm gear shaft of a conventional oscillating device. This worm gear shaft transmits the power for swinging the electric fan and for changing the length of the crank.

Allow relative rotation between the hollow shaft and spindle while adjusting the length of the crank, and its fixation after engaging the clutch to obtain the desired crank length so that the hollow shaft and spindle rotate synchronously A clutch is provided between the hollow shaft and the spindle to ensure the length. The clutch may be of the ratchet type, friction disc type, or any other suitable type of clutch. When the clutch is engaged, the spindle and the hollow shaft are locked together, so that the planetary gear system becomes a gear system with a fixed shaft, sun gear, planet gear, etc. The planetary carrier and eccentric pin all rotate about the axis of the sun gear, and the crank rotates a preset fixed length. When the clutch is released, the spindle and the hollow shaft are uncoupled, and the rotation of the other one of the spindle and the hollow shaft that is not connected to the main gear is stopped, so that the gear system with a fixed shaft is reactivated. It becomes a planet gear system, and as a result, the planet gear rotates around the sun gear. Therefore, the distance between the axis of the sun gear and the axis of the eccentric pin fixed to the planet gear is changed, and the length of the crank is also changed.

Engagement and disengagement of the clutch is accomplished by an adjustment mechanism. The adjustment mechanism of the present invention may be manual or automatic.

The principle of the manual adjustment mechanism is as follows. First, the clutch is released by the user's hand, and the length of the crank is changed. The change in length is then fed back by electrical or mechanical means and indicated on some type of display. Once the desired crank length corresponding to the oscillation angle is indicated, the clutch is manually engaged;
The electric fan swings within the adjusted angle range.

The operating principle of the automatic adjustment mechanism is as follows. Instructions for adjusting to a desired swing angle are input to the adjustment mechanism. The automatic adjustment mechanism then automatically disengages the clutch and adjusts the length of the crank. When the adjusted crank length corresponds to the desired swing angle, the clutch is automatically engaged by the adjustment mechanism. Thus, the electric fan oscillates within the desired oscillation angle range.

According to one type of automatic adjustment mechanism according to the invention, a sun gear and a planetary carrier are fixed to the spindle and the lower end of the hollow shaft, respectively, and a main gear meshing with the worm gear shaft is fixed to the upper end of the hollow shaft. A closing cam surface is integrally formed on the main gear, and a carrier is secured to the upper end of the spindle. The clutch is of the ratchet-pawl type, the ratchet being formed from the main gear described above, and the pawl mounted on the carrier being biased into engagement by spring means. A support member is mounted on the carrier, rotating in a horizontal plane about a vertical pin. The support member consists of a push plate and a rocker bar rotatable in a vertical plane about a horizontal pin and biased downwardly by spring means. A baffle is attached to the casing of the device and is reciprocatable in only one direction, e.g. vertically. A cutout is formed in the side surface of the baffle, and only through this cutout can the free end of the swing bar rotate together with the carrier. The front end of the push plate abuts the pawl.

The push plate is integrally formed with a stop that cooperates with a stop surface formed on the carrier, thereby limiting movement of the support member. A reciprocating flat lower is mounted on the carrier. One end of the bent lower abuts the swing bar, and the other end is slidable along the above-mentioned cam surface. With this configuration, the raised and lowered cam surface causes the lower flange to reciprocate in a generally vertical direction. It will be appreciated that the cam surface may be laterally corrugated, thereby causing the lower flute to reciprocate in a generally horizontal direction. In the latter arrangement, by eliminating the rocker bar, the horizontally movable flanged lower can cooperate directly with the generally horizontally reciprocating baffle notch.

According to the device of the invention, a branet gear system is used to adjust the length of the crank, so that the length of the crank can be changed from O to the maximum value as desired. That is, the electric fan having the control device of the present invention can swing from O to the maximum swing angle as desired.

Furthermore, since a clutch is used in the device, adjusting the length of the crank is very easy and convenient. Adjustments can be made simply by adjusting the position of the baffle or by pressing a key that controls the engagement or disengagement of the latch. The power for adjusting the length of the crank is provided by the electric fan motor, and is fixed by an engaged clutch so that the adjusted length of the crank does not change. Therefore, the device according to the invention has the advantage that its adjustment is easy and convenient, and its operation is smooth and reliable.

[Examples] Examples of the present invention will be described in detail below with reference to the drawings.

Referring to FIGS. 1 and 2, a worm gear 1 meshes with a worm 2 connected to a motor shaft 1. Power is transmitted to the main gear 5 by the power shaft 3. Well known unloading means and a crutch (not shown) are arranged between the worm gear 1 and its shaft 3. When the load on the worm gear is increased to a certain predetermined value, the release means automatically releases the connection between the worm gear 1 and the worm gear shaft 3, and the clutch means directs the fan in the fixing direction. Control as follows. For simplicity, teeth meshing with the main gear 5 are formed at the upper end of the worm gear shaft 3, by which power is transmitted to the main gear 5. Main gear 5 is attached to the upper end of hollow shaft 6 (or spindle 7). A spindle 7 rotatable with respect to the hollow shaft 6 is arranged coaxially with the hollow shaft 6. The lower end of the hollow shaft 6 is connected to a planetary carrier 9 by a screw 8. Eccentric pin lO
A planetary gear 11 having a diameter is rotatably attached to the planetary carrier 9 by a pin 13. sun gear 1
2 is fixed to the spindle 7. planet gear 1
1 is rotatable around a pin 13 and meshes with the sun gear 12. Thus, the planetary gear system is composed of the sun gear 12, the planet gear l1, and the planetary carrier 9. The spindle 7 rotates relative to a hollow shaft 6 which is connected to a planetary carrier 9. Planet gear 1l has crank pin 1 in an eccentric position
0, and this crank pin lO can be formed integrally with the planet gear 11. One end of the connecting bar 14 is rotatably attached to the pin IO. When the planetary carrier 9 rotates relative to the spindle 7,
The planet gear 11 rotates relative to the sun gear 12, thereby continuously changing the distance between the axis of the crank pin 10 and the axis of the spindle 7, forming a crank of variable length.

Normally, the distance between the axis of crank pin lO and the axis of planet gear 11 is the same as that between sun gear 12 and planet gear 11.
is chosen to be equal to the distance between the centers of .

In this case, the length of the crank can vary from 0 to a maximum value which is twice the distance between the centers of sun gear l2 and planet gear l1. By replacing the fixed-length crank of the four-bar linkage in the conventional electric fan with a variable-length crank, the oscillation angle of the improved electric fan can be increased from 0 to a maximum value, such as 120. ”
changes up to.

Power is provided by a worm 2. from a fan motor (not shown). It is transmitted to main gear 5 via worm gear 1 and worm gear shaft 3. This causes the four-bar linkage to swing, and when one of the four bars swings, the fan hangs. A clutch means is provided between the hollow shaft 6 and the spindle 7 to adjust the length of the crank.

The clutch means may be of the ratchet type or friction type or other suitable type. The engagement and disengagement positions of the clutch are controlled either manually or automatically.

The clutch means used in the first embodiment is a manual friction type, and as shown in FIG. 1, a friction disk l6 is brought into contact with the upper end surface of the main gear 5 via a steel ball l8 by a spring l7. It is energized as follows. One end of the spring 17 is in contact with the cover 15.

The actuating lever l9 is used to raise the friction disc l6, so that it is separated from the main gear 5. A tightening slot 20 is formed in the free end of the lever l9 in order to brake the friction disc l6 after separation. The actuation of the lever 19 is controlled via the tension cable 21 by a key (not shown) attached to the control panel of the fan.

When the key is released, the friction disc 16 is connected to the main gear 5.
The hollow shaft 6, the spindle 7, the planetary carrier 9, the planet gear 11, the sun gear 12, and the crank pin lO are integrated, and a certain crank length determines the swing angle of the electric fan. This results in a fixed shaft gear system with . The solid line in FIG. 2 indicates the position of the gear system at maximum crank length.

If it is desired to change the oscillation angle to the position shown by the broken line in FIG. 2, press the key so that the lever l9 separates the friction disk l6 from the main gear 5.

The clamping slot 20 then brakes the friction disc 16. Since the planetary carrier 9 is continuously driven by the motor, the planetary gear 11 and the crank pin 10 are forced to rotate around the pin 13, thereby changing the length of the crank. When the crank length is changed to the appropriate value, the key is released and the friction clutch is engaged. This causes the electric fan to oscillate at an oscillation angle determined by the changed length of the crank.

FIG. 3 shows the geometric relationship between the length of the crank, the hollow shaft 6, the spindle 7, etc.

As you can see from Figure 3, e'-R2+R2-28-Rcos ae-F■7T▼
[Here, if α=nβ, then e--rT-R--cos nI.

However, R is the distance between the centers of planet gear 11 and sun gear l2, e is the length of the crank, α is the difference in phase angle between planet gear 11 and sun gear l2, and β is the phase angle between spindle 7 and hollow shaft 6. The difference, n, is the ratio (nJ, 2.3, 4, . . .) between the number of teeth of the sun gear l2 and the number of teeth of the planet gear 11.

A second device for controlling the swing angle of the electric fan according to the present invention.
An example of this is shown in FIG. In this embodiment, the adjustment mechanism with a ratchet-type clutch is manually operated. Since the configuration and operation of the branet gear system are similar to those in the first embodiment, their explanation will be omitted here.

Referring to FIG. 4, a driven gear 23 having the same number of teeth and the same module as the main gear 105 is provided.

This driven gear 23 is provided on a hollow shaft 106, and the main gear 105 is provided on a spindle 107. The clutch means is an escapement lever rotating about a pinion 25 and a pin 26.
ver) 24. The pinion 25 is rotatably attached to a relief lever 24 having a tip at one end. Normally, the spring force from spring 27 engages the pinion 25 with the main gear 105 and the driven gear 23, which becomes the engaged position of the clutch means as shown in FIG. The power of the motor is directly transmitted to either main gear 105 or gear 23. In this embodiment, power from a motor (not shown) is transmitted to main gear 105. When the swing angle is adjusted, the cable 121 is pulled to rotate the release lever 24. As a result, the pinion 25 is disengaged from the main gear 105 and the driven gear 23, and at the same time, the tip of the relief lever 24 is transferred to the driven gear 23 (if the power is directly transmitted to the driven gear 23, the main gear l05).
between the teeth and stop its rotation as shown in FIG.

7 to 11 show another embodiment of the invention in which the swing angle is automatically adjusted. Upon inputting the desired oscillation angle signal, the adjustment mechanism of the equipment automatically controls the engagement and disengagement positions of the clutch means;
This gives the corresponding crank length. Since the branet gear system of this embodiment is similar to the embodiment described above, the explanation thereof will be omitted.

Referring to FIGS. 37 to 11, the gear 202 connected to the motor is the worm gear 20! are meshed with each other. Power is transmitted to the main gear 205 by a shaft 203. Well-known unloading means and a clutch (not shown) are arranged between the worm gear 201 and its shaft 203. When the load on the worm gear 201 is increased to a predetermined value, the opening means automatically opens the connection between the worm gear 201 and the shaft 203. The clutch is used to control the electric fan to stop at this orientation position.

For simplicity, the teeth that mesh with the main gear 205 are formed directly on the upper end of the worm gear shaft 203, which is rotatably mounted to the casing of the device. Main gear 205 is fixed to either hollow shaft 206 or spindle 207. That is,
Power is transmitted to either hollow shaft 206 or spindle 207. In this embodiment, the power of the motor is transmitted to the hollow shaft 206, so that the carrier 206
8 is attached to the spindle 207.

It is easier to configure such an arrangement to transmit the power of the motor. If the main gear 205 is mounted on the spindle 207 , the carrier 28 must be correspondingly mounted on the hollow shaft 206 . Pawl 2 used as a clutch part
9 is attached to the side of the carrier 28. In normal operating conditions, this pawl 29 is biased by spring means into engagement with the main gear 205, so that the hollow shaft 206 rotates together with a spindle 207, which is disposed coaxially with the hollow shaft 206. Become.

FIG. 10 shows a state in which the main gear 205 is not engaged with the pawl 29, and FIG.
9 is shown engaged. A support member 30 mounted on the carrier 28 pivots about a pivot axis 31 on the support surface. Support member (saboter) 3
0 is the swing bar 32, the push plate 33, and the stopper 3
4, and the push plate 33 and stopper 34 are integrally formed. When the support member 30 swings, the claw 29 is pushed to release the engagement with the main gear 205. The stopper 34 extends in a substantially vertical direction, and a pawl 29 engages the main gear 2 in order to stop the rotation of the support member 30.
When released by the push plate 33 from the teeth of 05,
The stopper 34 cooperates with the side surface of the carrier 28 with an appropriate distance between the stopper 34 and the carrier 28 so that the stopper 34 comes into contact with the side surface of the carrier 28. A closing cam surface 35 is formed at the upper end of the main gear 205. The cam surface 35 faces upward and may have any smooth curved shape. The support member 30 includes a rocking bar 32 that swings together with the support member 30 relative to the carrier 28.

One end of the swing bar 32 is rotatably attached to the support member 30. The tension spring 36 is connected to the swing bar 32
As a result, the cam follower 37 is pushed downward, and one end of the cam follower 37 is always held in contact with the cam surface 35 of the main gear 205. The cam lower 37 is slidably positioned in the guide hole of the carrier 28, and its two ends contact the swing bar 32 and the cam surface 35 of the main gear 205, respectively.

The two ends of the cam follower 37 are formed in the shape of a ball or are provided with rollers to improve the movement ability. When the spindle 207 rotates with respect to the hollow shaft 206, the swing bar 32 swings upward and downward along the curve of the cam surface 35 under the action of the cam shaft lower 37 and the tension spring 36. Shaking bar 3
2 has two functions. The first is to swing along a trajectory determined by the curve of the cam surface 35,
The relative angular displacement between spindle 207 and hollow shaft 20B is thereby displayed.

Second, when the swing bar 32 is prevented from rotating, a torque is generated, which disengages the clutch and stops the rotation of the spindle. To control the relative angular displacement between the spindle 207 and the hollow shaft 206, an adjustable baffle 38 is arranged on the casing and attached to the guide post 40 of the casing. The baffle 38 does not rotate, e.g.
It is controlled by a knob provided on the control panel of the electric fan via a transmission means such as 21, and moves along a straight line substantially parallel to the axis of the cam follower 37. A notch 39 having an appropriate shape, such as a wedge shape, is formed at an appropriate position on the side surface of the baffle 38. The opening of the notch 39 only allows the free end of the rocker bar 32 to pass through. That is, the opening of the notch 39 is formed to be slightly larger than the thickness of the swing bar 32. The swing angle of each fan corresponds to the length of the crank,
The relationship between these is considered to be approximately a linear function. The relationship between crank length and relative angular displacement is a
- 1-cos mouth β becomes. The cam surface 35 is a gap formed in a non-linear shape so that the change in the swing angle of the electric fan and the displacement of the baffle 38 are approximately linear functions.

In this embodiment, an isochronous closed-lobe control system is established, and its operation is as follows.

The main gear 205 is a worm 202. Worm gear 20
1 and 2 are driven by a motor via a shaft 203. The position of the notch 39 is set by displacing the baffle 38 by a predetermined amount, which is controlled by a knob provided on the control panel of the electric fan. This inputs the signal to the control system. The adjusted target crank length value is sampled by the Camoo rocker bar mechanism and amplified by the rocker bar 32. The amplified crank length value is fed back to the baffle 38 via the free end position of the rocker bar 32.

Baffle 38 itself. is a comparator that can calculate the difference between a sample value and a given value. When the sampled value is equal to the given value, the position of the rocker bar 32 corresponds to the position of the notch 39, so that the rocker bar 32
Not all cycles of are blocked by the notch 39. If the sampled value is not equal to the given value, the free end of the rocker bar 32 is stopped by the baffle 38 when the rocker bar 32 is pivoted into the baffle position. This disengages the clutch and stops the spindle 207. As a result, the braneta gear system responds by activating, changing the length of the crank and also changing the angle at which the fan is viewed. At the same time, the cam surface 35 swings the rocker bar 32 and causes the free end of the rocker bar 32 to slide over the side edge of the baffle 38, rAat, to a new sample value of the crank length. and compare it with the given value. Due to the continuity of the curved cam surface, the device described above will eventually find a sample value corresponding to a given value, whether the given value is an increased or decreased value. Once this has been achieved, the free end of the rocker bar 32 will find the notch 39 and pass through it. Therefore, the stopped spindle 207 is released and the clutch is engaged. This completes the crank length adjustment process and the fan operates at the new swing angle.

Although the present invention has been explained above based on preferred embodiments,
The present invention is not limited to these examples, and improvements and modifications thereof are possible without departing from the scope of the claims. For example, smoothly curved cam surfaces may be formed on the sides of the cam. In this case, the cam follower 37 and the rocker bar 32 are integrally formed and arranged horizontally. Baffle 38 is similarly arranged horizontally, with cutout 39 facing downward.

One end of the cam follower that does not contact the cam surface is bent upward. This bent portion of the lower camouflage serves a similar function to the free end of the swing bar 32 of the embodiment described above. The cam follower is mounted in a sleeve formed on the support member 30, and the cam follower is movable along the axis of the sleeve. When the free end of the cam follower (similar to the swing bar 32) is stopped by the baffle, the support member 30 swings against the kisseria and the pawl is pushed away from the main gear 205.

In the pawl-ratchet type clutch means used in the device of the present invention in which the ratchet functions as the main gear, the position where the pawl engages with the ratchet and the position where the main gear engages with the gear are determined by the thickness of the main gear (ratchet). It should be offset in the opposite direction.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a first embodiment of a device for adjusting the swing angle of an electric fan according to the present invention, in which the clutch is of a friction type, and FIG. 2 is a sectional view of a planetary gear system of the device shown in FIG. FIG. 3 is a schematic diagram showing the relationship of parts in the planetary gear system; FIG. 4 is a diagram of a device for controlling the oscillation angle of an electric fan according to the present invention, which has a clutch or radiet type configuration. FIG. 3 is a sectional view of the second embodiment, and the planetary gear system (not shown) is the same as that of the first embodiment. Fig. 5 is a sectional view taken along line A-A of the device shown in Fig. 4 with the ratchet clutch in the engaged position, and Fig. 6 is the same root as Fig. 5 with the ratchet clutch in the disengaged position. Cross-sectional view FIG. 7 is a cross-sectional view of a third embodiment of the present invention, showing the configuration of an apparatus having an automatic adjustment mechanism. Figure 8 is a partial front view of the automatic adjustment mechanism shown in Figure 7; Figure 9 is a partial side view of the automatic adjustment mechanism shown in Figure 7; Figure 10 shows the clutch in the disengaged position. FIG. 7 is a partial plan view of the self-adjusting mechanism shown in FIG. 7; FIG. 11 is a partial plan view similar to FIG. 10 with the clutch in the engaged position; 1,201... Worm gear, 2,202... Worm, 3,203... Worm gear shaft, 5,105
,205...Main gear, 6,106,2H...Hollow shaft, 7,107,207...Spintle, 9
...Branary carrier, IO...Crank pin, 11...Planet gear, l2...Sun gear, l4...Connection bar 16...Friction disc, l9...Operating lever 23... - Driven gear, 24... Relief lever 25... Pinion, 28... Carrier, 29... Pawl, 30... Support member, 32... Rocking lever 33... Push plate, 34... Stopper, 35... Cam, 37... Cam follower, 38... Baffle, 39... Notch. Figure 4 Figure 5 Figure 7 Current status! 8I5 Kaikomenmi Fig. 8 Partial control of Fig. 7 1st doctor Fig. 9 Fig. lO

Claims (1)

[Claims] 1) a casing, a spindle, a hollow shaft, a main gear attached to either the spindle or the hollow shaft and meshing with the shaft of a worm gear, fixed to the lower end of the hollow shaft, a planetary carrier carrying a planet gear rotatable about its axis; a crank pin secured to said planet gear; a connecting bar articulated at one end to said crank pin; A sun gear that is integrally provided and meshes with the planet gear, a clutch means provided between the spindle and the hollow shaft, and an adjustment means for controlling the clutch means. Fan swing control device. 2) The apparatus of claim 1, wherein said clutch means comprises a pawl and a ratchet. 3) The device according to claim 1 or 2, wherein the main gear functions as a ratchet. 4) The adjustment means includes a carrier fixed to the other of the spindle and the hollow shaft, a push plate and a swing bar, and is mounted on the carrier and swings about a vertical pin in a substantially horizontal plane. a support member attached to the casing, a baffle controlled for reciprocating movement in only one direction and having a cutout in its lateral edge, and a closing cam surface formed on the main gear;
A cam follower is provided that is movably mounted on the carrier so that one end is slidably in contact with the cam surface and the other end is in contact with the swing bar, and the swing bar is mounted on the support member. the rocker bar is mounted on and pivotable in a substantially vertical plane about a substantially horizontal pin and is biased by spring means, the free end of said rocker bar being adapted to rotate with said carrier. 4. The pusher plate passes through the baffle via the carrier, the pawl is mounted on the carrier, and the push plate is in contact with the carrier. The device described in. 5) the support member further comprises a stop integrally formed with the pusher plate, the stop extending substantially vertically and cooperating with a stop surface formed on the carrier; 5. The apparatus of claim 4, wherein the range of movement of the support member is limited by the support member. 6) The pawl is biased to engage the ratchet by spring means.
The device described. 7) The device according to claim 4, wherein the cutout formed in the baffle is wedge-shaped, and the width of the opening of the cutout is slightly larger than the thickness of the free end of the rocker bar. . 8) The apparatus of claim 5, wherein the distance between the stop and the stop surface is large enough to allow the push plate to push the pawl out of engagement with the ratchet. 9) A position where the claw engages with the ratchet and a position where the main gear engages with the worm gear are offset in the thickness direction of the main gear. 4. The device according to any one of 4. 10) A roller is provided at one end of the cam follower that is in slidable contact with the cam surface, and the roller is rotatable on the cam surface. Device. 11) The distance between the axis of the sun gear and the axis of the planet gear is equal to the distance between the axis of the planet gear and the axis of the crank pin. Device. 12) The apparatus of claim 1, wherein the crank pin is integrally formed with the planet gear. 13) the clutch means comprises a friction disc fixed to the other one of the spindle and the hollow shaft, the spindle being axially movable with respect to the hollow shaft; Spring means bias the friction disc into frictional engagement with the main gear, and the adjusting means controls the friction disc to simultaneously move the friction disc out of engagement with the main gear and apply a brake to the friction disc. 2. The device according to claim 1, further comprising a lever that allows the device to be moved. 14) Device according to claim 13, characterized in that one end of the lever cooperating with the friction disc is provided with a tightening slot. 15) The clutch means includes a driven gear, which is the same as the main gear, which is fixed to the other one of the spindle and the hollow shaft, a rotatably provided pinion, and a tip end, and the clutch means has a driven gear that is fixed to the other one of the spindle and the hollow shaft, and a rotatably provided pinion and a tip end, and the pinion is rotated by the spring means. a relief lever rotatably attached to the casing, the release lever being biased to mesh with both of the gears;
The relief lever is configured to control the relief lever so that the distal end portion of the relief lever is inserted between the teeth of the driven gear at the same time as the pinion is disengaged from the both gears, and the brake is applied to the driven gear. 2. The device of claim 1, further comprising a connected cable.