JPS61262260A - Deceleration rectilinear movement output apparatus - Google Patents

Abstract

PURPOSE:To reduce the energy loss by interposing a band-shaped body between a guide body and a cam and decelerating the rotary movement by utilizing the difference of number of gears between the guide body and the band-shaped body and taking out rectilinear movement. CONSTITUTION:A band-shaped body 6 having external gears 22 is interposed between a guide body 1 having internal gears 21 and a cam 2. The engagement dimension from the limit point E to the limit point F is set EAF, and the dimension of the inner peripheral circle of the guide body 1 is set Com, and the number of press-contact parts of the cam is set 1, (Com/1)-EAF is set as the dimension of inner periphery of the guide body 1. Therefore, the turning movement is decelerated by utilizing the difference of number of gears between the guide body and the band-shaped body, and the rectilinear movement can be taken out as the shift of the band-shaped body. Therefore, the movement conversion can be carried out by a same mechanism, and the energy loss can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a decelerated linear motion output device that decelerates rotational motion and converts it into direct linear motion for output.

[Subject skill]

The rotary motion output generated by a general motor, main engine, etc. is converted into a low rotation, high torque output using a reduction gear and used. In addition, when outputting rotational motion as linear motion, it is usually configured to be decelerated by a reduction gear that combines gears, and then output as linear motion using a rack-pinion mechanism or a gear-chain mechanism. There is. However, when the speed reduction device and the linear motion output mechanism are combined in this way, the number of output transmission parts has a drawback that a large amount of energy is lost. Furthermore, since the deceleration mechanism and the linear motion conversion mechanism are separate, they are heavy and thick, and there are significant restrictions on storage space.

In particular, in the case of a so-called power window, an automatic vehicle window opening/closing device, as an example, the above drawbacks have become a particularly important problem. In other words, this type of power window currently has a configuration in which the rotation of the motor is decelerated by a dual reduction device consisting of a worm gear, rack and pinion, and a link mechanism is used to convert the rotary motion into vertical linear motion. In order to increase the interior space of a vehicle, it is desirable to make the door thickness as thin as possible, and in order to increase the running efficiency of a vehicle, it is necessary to reduce the weight of the vehicle, so a reduction in the weight of the door is required. Furthermore, in order to reduce production costs, there was a strong desire to reduce the number of mechanical parts and create a mechanism that was easy to assemble.

In addition to the power windows mentioned above, we also offer belt conveyor drive mechanisms, automatic door drive mechanisms, and winches.

For all linear motion output mechanisms such as chain drive mechanisms, there has been a desire for mechanisms that are small, lightweight, and have a high degree of freedom in design with low energy loss.

[Purpose of the invention]

The present invention has been made in view of the above circumstances, and provides a small, lightweight, thin, and low-cost deceleration linear motion output device that is capable of decelerating the rotational speed and converting it into linear motion using the same mechanism. The purpose is to provide.

[Key points of the invention]

A guide body having teeth on the inner periphery, a band-like body having retaining teeth that partially engages with the teeth, and a cam for bringing the band-like body into pressure contact with the guide body. The guide body and the cam are provided to sandwich the belt-like body on the moving path of the belt-like body, and the belt-like body is moved between the points where the belt-like body pushed by the cam and the guide body engage. This method uses the principle that if there is a difference in the circumferential length of the guide body and the guide body, when the cam rotates while pushing the band-shaped body, the band-shaped body moves by being decelerated by the circumferential length difference.

[Embodiments of the invention]

The embodiments of the present invention will now be described in detail with reference to the drawings.

FIGS. 1 and 2 (a) are explanatory diagrams showing the structure and usage of the reduction gear of the present invention using an elliptical cam type and an eccentric cam type, respectively, and (b) is a cross-sectional view thereof. l is an internal tooth In FIG. 1, a guide body 21, 6 a belt-shaped body having external teeth 22 that continuously and partially engage with the internal teeth 21, and 5 a motor! An elliptical plate fixed to the shaft 4 of 0, and an elliptical bearing 15 that is elastically deformed and fitted into the outer periphery of this elliptical plate 5.
is located.

The elliptical plate 5 and the elliptical bearing 15 are collectively called a cam 2. Second
In the figure, reference numeral 5 indicates an eccentric disk, and "δ" is attached to the shaft 4 of the motor 10.
“It is fixed eccentrically.

A bearing 3 is fixed to this eccentric disk 5. Eccentric plate 5
, bearing 3 and drive disk 14 are collectively referred to as cam 2. In both the configurations shown in Figures 1 and 2, the cam 2 is equipped with a bearing 3 and an elliptical bearing 1.5, respectively, so it can rotate freely in the circumferential direction, so no force acts in the circumferential direction. . Additionally, frictional force is extremely low since rolling bearings are used.

The rotation of the motor 10 generates only the direction shown by the arrows in FIGS. 1 and 2, that is, the long sleeve direction (radial force). This radial force causes the strip 6 to
The driving force is transmitted to.

In the long direction of the cam 2, where the distance from the rotating shaft 4 of the motor 10 to the outer periphery increases, a part of the external teeth 22 of the band-shaped body 6 is deeply pushed into the internal teeth 21 of the guide body 1 and pressed into contact.

In the elliptical cam system shown in Figure 1, points A and B are shown by arrows.
In the eccentric cam system shown in Fig. 2, they are deeply engaged at one point (point A). FIG. 2 shows a case where the pulley 8 is rotated for explanation.

In this reduction gear device, as will be described later, even if the motor is rotated at a constant speed, the moving speed of the strip 6 varies every half rotation in FIG. 1 and every one rotation in FIG. . Tension spring 16 is used to absorb this speed fluctuation.
The tension roller 13 and the spring are further provided with a damper (not shown).

In the eccentric cam system shown in Fig. 2, as will be described later, there is only one press-fitting engagement portion between the inner teeth (21) of the guide body (21) and the outer teeth (22) of the band-shaped body (6). The outlet for taking out the body 6 becomes smaller.For this reason, a guide roller 9 is provided.In the elliptical cam system shown in FIG. No rollers needed.

In order to illustrate the principle of the present speed reduction device, the shape 30 of the external teeth 22 of the elliptical cam type band body 6 shown in FIG. The shapes 31 of the guide body I and the internal teeth 21 are shown in FIG.

FIG. 4 shows an enlarged 1/4 portion on the circumference of FIG. 3.

The circle passing through the bottom of the internal teeth 21 of the guide body 1 is Civ 115°, the circle passing through the top of the internal teeth is C1m117, and the circle (pitch circle) representing the internal teeth 21 is C1116. Further, the curve passing through the peak of the external tooth 22 of the band-shaped body 6 is Coff1118. external teeth 22
The curve passing through the bottom of Cow 120. The curve representing the external tooth 31 was designated as Co119. In the direction indicated by the arrow, the external teeth 22 and the internal teeth 21 are pressed against each other by the cam 2 and are deeply engaged. The intersection of the circle Ci1.16 and the curve 119 is the engagement point. It is indicated by point A in FIG.

In this speed reduction device, in order to obtain a smooth deceleration effect, the engaging portions for transmitting power must exist without interruption.

In this embodiment, the area from point A to point E33 becomes an engaging portion for transmitting power. Its dimensions are from point A to point E3
In the state shown in the figure, there are two positions above and below, and when the rotation is perpendicular to 90 degrees, the engagement dimension is the dimension from point A to point E33 x 2. In addition, in this reduction gear device, it is a necessary condition that there is no interference between teeth. If there is no tooth interference,
When the elliptical cam 2 is rotated, the engagement point A moves with the rotation of the elliptical cam. As shown in FIG. 3, when the elliptical cam 2 is rotated half a turn and the engagement point is moved from point A to point B, the occlusal state becomes the same as at point A. The elliptical cam 2 is a band-shaped body 6
As the elliptical cam 2 rotates while always pushing the outer teeth 22 deeply into the inner teeth 21 of the guide body l, when the elliptical cam 2 rotates by half a rotation, the circumferential length of the outer teeth 22 between engagement points A and B and the circumferential length of the inner teeth 21 changes. The strip 6 moves by the difference. Since the external teeth 22 of the band-shaped body 6 and the internal teeth 21 of the guide body l engage with each other at engagement points A and B, the difference in circumferential length must be an integral multiple of the pitch between the teeth. After the belt-shaped body 6 exits the present reduction gear, it moves in a straight line;

The internal reduction ratio is as follows.

That is, becomes.

When the elliptical cam 2 rotates between the engagement points of the band-shaped body 6, (the number of internal teeth between the engagement points - the number of external teeth) is at least 1. In order to further reduce the reduction ratio, increase the number of internal teeth,
In other words, the pitch of the teeth can be reduced. This naturally reduces the amount of movement of the strip 6 and increases the deceleration effect. The internal teeth 21 and the external teeth 22 usually have the same tooth profile and the same pitch, but the external teeth 22 are engaged with the internal teeth 21 near the engagement point,
Moreover, as long as there is no interference between the teeth, any material may be used. For example, the belt-shaped body 6 is a roller chain.

In addition to silent chains, there are those in which the strip has slits 32 at equal intervals, as shown in Fig. 8, and those in which a tooth profile is formed in the center of the strip by plastic working in the longitudinal direction, as shown in Fig. 12. I can think of things. In this case, if the rigidity when bending the strip becomes too large and it is difficult to bend and fit around the cam, it is possible to provide a hole such as a slit at the top of the tooth (not shown). .

Figure 5 shows an eccentric cam type speed reducer with a guide body 141V.
The shape 31 of the external teeth 22 of the band-shaped body 6 that is bent along the V-I Qll Yakuhesu-hachi 21 of tshi+Koyamagō 91 is shown. In this case, the intersection of the pitch circle Ci of the internal teeth and the external tooth curve Co, that is, the number of pressure contact parts of the cam 2 is only point A.

Moreover, the engagement dimension for transmitting power, that is, the engagement dimension between the internal teeth 21 and the external teeth 22 is "E33-A-E33
” dimensions.

Therefore, the inner circumferential dimension of the guide body l is set to be greater than the value obtained by the inner circumferential dimension of the guide body - the engagement dimension. On the other hand, the reduction ratio and the moving speed of the strip can be calculated using the same formula as in the case of an elliptical cam, but in the case of an eccentric cam, there is only one engagement point, so the distance between engagement points is These are the inner circumference of the guide body 1 returning to point A and the circumference of the outer teeth 22 of the temporary band-shaped body 6. As shown in the figure, the strip 6 exits from the exit and returns again, but the circumference is based on the assumption that the strip does not come out and is bent along the entire circumference of the eccentric cam. It is the circumference of the time. In the eccentric cam system, the length between the gathering points is longer and the number of teeth is therefore larger, so the reduction ratio is smaller and the reduction effect is higher.

Although an elliptical cam and an eccentric cam have been described as the shape of the cam, a triangular cam as shown in FIG. 8 or other shapes may be used. In this deceleration linear motion output device, the inner circumferential dimension of the guide body (1) can be made smaller as the number of pressure contact parts of the cam increases, that is, as the shape becomes triangular, quadrilateral, and polygonal, but in order to operate as a deceleration device, The inner circumferential dimensions of the guide body must be set as above.

In addition, no matter what shape there is, there is a difference in the circumferential length between the external and internal teeth between the engagement points, and this difference is an integral multiple of the pitch of the teeth, and furthermore, the internal and external teeth interfere with each other during that time. It's fine if you don't have it.

Since the strip 6 enters and exits this reduction gear,
You will need that entrance. The dimensions of the entrance and exit are strip 6
It can be calculated inversely from the dimensions required to drive.

In order for the outer teeth 22 of the band-shaped body 6 to engage with the inner teeth 1i121 of the guide body l, the ridges of the outer teeth 22 must be located outside of the ridges of the inner teeth 21. That is, the circle C1 passing through the peak of the internal tooth 21
The intersection point E between ff1 and the curve co111 connecting the peaks of the external teeth 22 is the limit point of engagement. Figure 6 shows the case of an eccentric cam type reduction gear, and the intersection of Cim and Cow is E33 and F.
34, 2 points. This is called the engagement limit point. If the engagement point A is in the direction of the arrow in the figure, the engagement portion will be reduced.

Even at this time, in order for the external teeth 31 of the band-shaped body 6 to engage with the internal teeth 30, the circumferential length of the internal teeth 21 of the guide body l must be at the engagement limit point E3.
3 and F34 or higher. If the circumferential length or inner circumferential dimension of the internal teeth 21 of the guide body 1 is such that the external teeth 22 of this band-shaped body 6 do not engage with the internal teeth 21 at all, the band-shaped body 6 cannot be driven at that time. It disappears. Therefore, the inner peripheral dimension of the guide body 1 must be at least equal to or larger than the engagement limit point. In this embodiment, the engagement dimension is the sum of the range from point A to limit point E and from point A to limit point F, that is, from limit point E to limit point F.

That is, in this embodiment, the above is the inner peripheral dimension of the guide body l. In reality, it is desirable that the strip 6 is always driven by the engagement of as many teeth as possible, so the dimension is set to be greater than or equal to the engagement limit point. In the case of the eccentric cam type shown in FIG. 2, the guide roller 9 is provided because the dimension of the internal teeth 21 of the guide body 1 is considerably larger than the dimension between the critical points. Figure 7 shows C1Ill of the guide body I of the elliptical cam type reduction gear.
and showed Com and Cov of Civ band 6. In the case of the elliptical cam 2, there are two engagement points, point A and point B. The worst occlusal condition is when the long sleeves are in the vertical direction, as shown in the figure. The occlusion' limit points are the intersection points E33 and F34 of the circle Cim passing through the crests of the internal teeth 21 of the guide body 1 and the curve Com passing through the crests of the external teeth 22 of the band-shaped body 6. The engagement dimensions are from the intersection A to the engagement limit point E33 and from the intersection B to the engagement limit point F34. This engagement dimension becomes X2 when the cam 2 rotates 90 degrees (from A to E33). Therefore, if the inner peripheral dimension of the guide body 1 is shorter than this limit point distance EF, the outer teeth 22 of the band-like body 6 will not engage with the inner teeth 2I of the guide body 1, and therefore it will not be able to function as a deceleration device. Can not. Guide body! The required minimum inner peripheral dimension of the internal teeth 21 of the guide body 1 is obtained by dividing the circumference of the internal teeth 21 by 2 and subtracting the above-mentioned engagement dimension from the remainder.

According to this method, the distance between the limit points can be made smaller, that is, the inner peripheral dimension of the guide body 1 can be made smaller, compared to the aforementioned eccentric cam method having only one engagement point.

If it can be made small, the present speed reduction device can be incorporated into a part of the belt movement path in a normal belt drive mechanism to provide a speed reduction effect. An elliptical bearing 15 is used in the elliptical cam system, and a bearing 3 is used in the eccentric cam system, so that the cam 2 and the strip 6 can be freely displaced in the circumferential direction. Although not shown in the case of the triangular cam of FIG. 8, the sliding resistance between the cam 2 and the strip 6 can be reduced by providing bearings at each vertex of the triangle.

In the case of the eccentric cam system, since the eccentric cam 2 performs circular motion around the drive shaft 4, the distance between the driven pulley 8 and the eccentric cam varies. Further, when a guide roller 9 is provided at the exit as shown in FIG. 2, the distance between the guide roller 9 and the eccentric cam 2 changes momentarily with each rotation angle of the eccentric cam. Thereby, the moving speed of the strip 6 changes in accordance with the rotation of the eccentric cam 2. In order to absorb this as much as possible, a tension roller 13 supported by a spring 12 is provided. Although not shown, a damper may also be used. In the case of the elliptical cam system, the center of the cam does not move, but the distance between the elliptical cam and the pulley 8 changes slightly depending on the rotation angle of the cam 2. When the strip 6 moves back and forth, as shown in FIG. 10, a tension spring 16 is provided on a part of the strip 6 to absorb speed fluctuations, but the aforementioned tension roller may also be used.

If the eccentricity "δ" of the eccentric cam is small and the difference between the circumference of the internal teeth of the guide body and the circumference of the external teeth of the band body becomes small between the engagement points, and in the case of an elliptical cam, the pitch circle Ci of the internal teeth The smaller the difference from the curve Co of the external teeth of the band, the smaller the speed fluctuation. As can be seen from the above, this also makes it possible to reduce the reduction ratio and increase the reduction effect.

The minimum difference between the circumferential length of the internal teeth and the circumferential length of the external teeth between the engagement points is 1 tooth.
Therefore, in order to lower the reduction ratio and reduce speed fluctuations, it is necessary to reduce the pitch of the teeth. In addition, in order to prevent the internal teeth and external teeth from interfering between the engagement points, the shape of the teeth must be adapted to the shape of the cam 2.

Although FIG. 4 shows teeth that are normally used as the tooth profile, a flat triangular tooth profile is suitable in order to prevent mutual interference between the teeth near the engagement point (point A). In order to reduce speed fluctuations, it is better for the shape of the cam 2 to be close to the shape of the inner periphery of the guide body. For this purpose, it is desirable to make the depth of the tooth profile as shallow as possible.

If the depth of the teeth is too shallow, the driving force will decrease.
The optimal tooth profile can be selected depending on the intended use.

[Effects of the present invention]

In this speed reduction device, a band-shaped body is sandwiched between a guide body and a cam, and the difference in the number of teeth between the guide body and the band-shaped body is used to decelerate rotational movement, and the movement of the band-shaped body is Since linear motion is extracted as movement, the rotational motion is decelerated and the rotational motion is converted into linear motion at the same time.

The shapes of the guide body, cam, and band-shaped body constituting this speed reduction device are extremely simple, and the number of parts is small, since these three components are the only necessary components. Therefore, assembly work is also easy. Furthermore, as shown in Figures 1 and 2, the thickness of this reduction gear device is essentially the same as the width of the strip, so it is extremely thin, so there is only a narrow space, and the rotation of the motor can be converted into linear motion. It can be used where conversion is required.

Motor-driven power windows are used to open and close automobile windows. In order to make the interior space of an automobile as large as possible, efforts are being made to make the doors thicker. In addition, efforts have been made to simplify the mechanism in order to reduce the weight of the vehicle body to save fuel, reduce the number of parts, and reduce the assembly process.

Power windows reduce motor rotation using a worm gear.
An additional rack pinion is used to reduce the speed, and a four-bar parallel link mechanism is used to convert rotational motion into linear motion for opening and closing the window. For this reason, the number of parts is large, the mechanism is complicated, and the thickness of the power window mechanism is increasing. For this reason, it is currently not used in light vehicles with thin doors.

This speed reduction device is suitable for automobile window opening/closing mechanisms that require the above improvements. The window can be easily opened and closed simply by connecting the strip of this reduction gear to the glass window that moves up and down along the rail.

As mentioned above, there are only three main mechanical parts of this reduction gear, and all of them are made of easily available parts with simple shapes that can be processed by conventional methods. Processing and assembly costs are reduced, and the weight of the switchgear is significantly reduced.

In Figures 1 and 2, the motor is installed separately from the reduction gear for the sake of explanation, but since the inside of the cam is wasted space, it is actually possible to incorporate a clutch in this area. Become. Therefore, the thickness of the mechanism is considerably thinner than that of conventional power windows.

Since this speed reduction device has the above-mentioned advantages, it can also be used as an automatic opening/closing mechanism for building doors.

Since it is a mechanism that uses the rotational force of a motor to move linearly, it can be used, for example, to drive a conveyor, or to drive a chain on a bicycle or motorcycle.

[Brief explanation of the drawing]

Figures 1 and 2 are a configuration diagram and a sectional view showing an embodiment of the reduction gear according to the present invention, Figure 3 is an explanatory diagram showing the principle of the reduction gear, and Figure 4 is a partial enlargement of Figure 3. Figure 5 is the second
FIG. 2 is an explanatory diagram showing the principle of the speed reduction device shown in the figure. FIG. 6, FIG. 7, and FIG. 8 are explanatory diagrams for explaining the necessary minimum dimensions of the guide body, and FIG. 9 and FIG. 10 are explanatory diagrams showing the causes of speed fluctuations. FIG. 11 and FIG. 12 are a plan view and a sectional view showing an embodiment of the band-shaped body. (Explanation of symbols) 1. Guide 2. Cam 3, bearing 4゜pongee 5, disc 6. Band-shaped body 7, shaft 8. Pulley 9, guide roller 10. Motor 11, base
12. Spring 13, tension roller 1
40 disc 15, oval bearing shaft 16. Tension spring 21, internal teeth 22. External tooth 30, external tooth shape 31. Internal tooth shape 32, slit 33. Engagement limit point 34, engagement limit point
115. Internal tooth bottom circle 116, internal tooth pitch circle 1
17. Internal gear Yamada 118, external gear mountain curve 119. External tooth pitch curve 120, external tooth bottom line Patent applicant: Advance Development Institute Co., Ltd. Figure 4 Figure 5 Figure 6 Figure 8

Claims (1)

[Scope of Claims] A guide body having internal teeth on its inner periphery, a band-like body having external teeth that partially continuously engage with the internal teeth, and a device for bringing the band-like body into pressure contact with the guide body. 1. A deceleration linear motion output device comprising a cam, wherein the inner circumferential dimension of the guide body is set to be equal to or larger than "(inner circumferential circular dimension of the guide body/number of pressure-contact parts of the cam) - engagement dimension".