KR101527475B1 - Series of gear device - Google Patents

Abstract

A gear unit with a low reduction ratio to a high reduction ratio can be constructed at a lower cost.
Internal gears (116, 216) having internal gear bodies (117, 217) and a plurality of pin members (119, 219) disposed in the internal gear body and the pin members forming internal teeth, A first gear device and a second gear device, which are a series of gear devices including a first gear device (110) and a second gear device (210) provided with cover members (150, 250) And the cover member is provided with the support grooves 160 and 260. The second gear device has more pin members than the first gear device and the pin member is smaller in diameter. The internal gear main body of the first gear unit has support holes (164, 264) for supporting the entire circumferential side surface of a part of the pin member in the axial direction, and the pin member of the first gear unit And is supported by the support hole of the internal gear body. The internal gear main body of the second gear unit is not provided with the support hole of the pin member, and the pin member of the second gear unit is supported by the support groove of the cover member.

Description

Series of gear devices {Series of gear device}

The present application claims priority based on Japanese Patent Application No. 2013-223768, filed on October 28, 2013. The entire contents of which are incorporated herein by reference.

The present invention relates to a series of gear devices.

Patent Document 1 discloses a gear device of an eccentric oscillation type that is engaged with and engages with an internal gear while the external gear is swinging and the relative rotation between the external gear and the internal gear is taken out as a deceleration output .

The internal gear in this gearing includes an internal gear body and a plurality of pin members disposed in the internal gear body, and the pin member constitutes an internal tooth of the internal gear.

The internal gear body is provided with a support hole for supporting the pin member, and the pin member is supported by the internal gear body in such a manner that a part of the side surface of the pin member is supported by the support hole.

Prior art literature

(Patent Literature)

Patent Document 1: JP-A-8-6784 (FIG. 4)

The reduction ratio of the gear device having such an internal gear is determined depending on the difference in dimension and dimension between the external gear and the internal gear. The gear unit with a high reduction ratio tends to have a smaller number of internal teeth (the number of pin members) and a smaller diameter of the pin member as compared with a gear unit with a low reduction ratio. As a result, the gear device with a high reduction gear ratio can not avoid machining a large number of support holes having a small diameter at the time of machining the support hole for supporting the pin member of the internal gear main body.

SUMMARY OF THE INVENTION The present invention has been made in order to solve such a conventional problem, and it is an object of the present invention to provide a gear device capable of configuring a gear device with a low reduction ratio to a high reduction ratio at a lower cost.

The present invention relates to an internal gear member comprising an internal gear member and an inner gear member having a plurality of pin members disposed in the inner gear member main body and constituting an inner teeth of the pin member and a cover member connected to the inner gear member main body, Wherein the first gear device and the second gear device are common to the cover member and the cover member is provided with a support groove for supporting the pin member Wherein the pin member of the second gear unit is smaller in diameter than the pin member of the first gear unit, and the pinion of the second gear unit is smaller in diameter than the pin member of the first gear unit, Wherein the pinion of the first gear unit is not supported by the support groove of the cover member, and the pinion of the first gear unit is not supported by the support groove of the cover member, strike The pin member of the second gear unit is supported by the support hole of the cover member so that the pin member of the second gear unit is supported by the support groove of the cover member, The above problem is solved.

A series of gear devices according to the present invention includes a first gear device having a small number of pin members (having a small number of internal teeth) and a large diameter, and a second gear device having a large number of pin members (having a large number of internal teeth) , And is included as a component thereof.

The first gear device and the second gear device are common to a cover member connected to the internal gear body. The cover member is provided with a support groove for supporting the pin member. In this series, only the internal gear main body of the first gear unit is formed with a support hole for supporting the entire circumferential side surface of a part of the pin member in the axial direction.

The pin member of the first gear device is not supported by the support groove of the cover member but is supported by the support hole of the internal gear main body while the pin member of the second gear device is supported by the support groove of the cover member .

As a result, both the first gear device and the second gear device can be manufactured at low cost.

According to the present invention, it is possible to obtain a gear device having a low reduction ratio to a high reduction ratio at a lower cost.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing the entire configuration of a first gear device of a series of gear devices according to an example of an embodiment of the present invention. Fig.
2 is a partially enlarged cross-sectional view taken along the line II-II in the direction of the arrow in Fig.
Fig. 3 is a partially enlarged cross-sectional view showing a configuration in the vicinity of the internal gear of Fig. 1;
4 is a partially enlarged cross-sectional view showing a configuration in the vicinity of an internal gear of a second gear unit of the gear unit.
5 is a sectional view taken along the line VV in the direction of the arrow in Fig.
6 is a sectional view taken along the line VI-VI in the direction of the arrow in Fig.

Hereinafter, the configuration of a series of gear devices according to an example of the embodiment of the present invention will be described in detail with reference to the drawings.

Briefly described, a series of gearing devices according to the present invention includes a first gear device and a second gear device, each of which comprises an internal gear of an internal gear as a pin member.

Since the first gear device and the second gear device have a common configuration except for the structure of the periphery of the internal gear, the entire configuration of the first gear device will be described first, and then, The difference between the device and the second gear device will be described with attention paid to it.

Fig. 1 is a cross-sectional view showing the entire configuration of a first gear device 110 of a gear device series according to an example of the embodiment of the present invention. Fig. 2 is a sectional view taken along the line II- FIG.

The first gear device 110 includes two internal gears 116 and two external gears 114 that are in contact with and meshed with the internal gears 116 while swinging two external gears 114 by means of two eccentric bodies 112, 114 as an output.

The input shaft 111 of the first gear device 110 is integrated with the motor shaft 120 of the motor 118. An eccentric body axis 124 is connected to the input shaft 111 through a key 122. [ On the eccentric body axis 124, the two eccentric bodies 112 are formed integrally. An external gear 114 is mounted on the outer periphery of the eccentric body 112 via an eccentric body bearing 126 so as to be oscillatable. The external gear 114 is in contact with and meshes with the internal gear 116 while rocking.

That is, the first gear device 110 is an eccentric rocking type gear device referred to as a center crank type in which only one eccentric body shaft 124 exists in the center in the radial direction of the internal gear 116. The reason why two shout gears 114 are provided in parallel is that securing the required transfer capacity and shifting the eccentric phase are intended to secure rotational balance.

The tooth profile of the external gear 114 is a trochoid tooth profile, and the tooth profile of the internal gear 116 is a circular tooth profile. 3, the internal gear 116 includes, in this embodiment, an internal gear body 117 integrated with the casing 128, and a plurality of cylindrical bodies 117 arranged in the internal gear body 117 And an internal tooth of the circular tooth is constituted by a pin member 119. The pin member 119 has a pin member 119, A roller member 119S is fitted on the outer periphery of the pin member 119 as a sliding facilitating member so as to smoothly slide the pinion member 119 relative to the external gear 114. Therefore, in this embodiment, it can be understood that the roller member 119S substantially constitutes the internal teeth of the internal gear 116. As described above, in the first gear device 110 of the present embodiment, the pin member 119 fitted outside the roller member 119S constitutes an internal tooth. That is, in the present invention, " the pin member constitutes the internal teeth " means not only the case where the pin member itself directly forms the internal teeth but also the case where the roller member is fitted to the pin member on the outside, .

The number of internal teeth of the internal gear 116 (the number of pin members 119 or the number of the roller members 119S) is slightly larger than the number of external teeth of the external gear 114 (1 in this example).

The configuration in the vicinity of the internal gear 116 will be described in detail later.

The external gear 114 has an inner pin hole 114A penetrating the external gear 114. In the pinhole 114A, the inner pin 132 is inserted with sufficient clearance. On the outer periphery of the inner pin 132, an inner roller 138 is disposed as a sliding promoting member. A gap delta 1 equivalent to twice the eccentricity of the eccentric body 112 is ensured between the inner roller 138 and the inner pinhole 114A. A flange body 134 is disposed on the axial side of the external gear 114 and the inner pin 132 is press-fitted into the inner pin support hole 134A of the flange body 134. [ The flange member 134 is integrated with the output shaft 136 (Fig. 1). The output shaft 136 is supported by a pair of tapered roller bearings 137.

Next, the first gear device 110 and the second gear device 210 in the gear device series of the present embodiment will be described in detail. It should be noted that the first gear device 110 is denoted by 100 symbols, the second gear device 210 is denoted by 200 symbols, and the first gear device 110 already described The same reference numerals as those of the second gear unit of the second gear unit 210 will be described.

In order to meet various demands of the user, a plurality of gear devices having different sizes (transfer capacities) and reduction ratios are often provided as a " series ". The first gear device 110 and the second gear device 210 of the series of gear devices according to the present embodiment have different reduction ratios and the second gear device 210 has a high reduction ratio (input shafts 111 and 211 The rotational speed of the output shaft 236 of the second gear device 210 is slower than the rotational speed of the output shaft 136 of the first gear device 110).

First, in order to facilitate understanding of the reduction gear ratio, the deceleration action of the first gear device 110 will be briefly described. This deceleration action is also the same in the second gear device 210.

1, when the input shaft 111 of the first gear unit 110 integrated with the motor shaft 120 is rotated by the rotation of the motor shaft 120 of the motor 118, The eccentric body shaft 124 connected to the input shaft 111 rotates through the first and second gears 122 and 122. When the eccentric body axis 124 rotates, the eccentric body 112 integrally formed with the eccentric body axis 124 rotates, and the eccentric body bearing 126 rotates once each time the input shaft 111 rotates. The shout gear 114 swings once. As a result, there occurs a phenomenon that the engagement positions of the external gear 114 and the internal gear 116 are sequentially shifted, and the external gear 114 is separated from the internal gear 116 by a dimension difference, (Rotates) relative to the internal gear 116 in the fixed state. The rotating component is transmitted to the flange 134 disposed on the axial side of the shout gear 114 via the pinion 132 so that the output shaft 136 integrated with the flange 134 rotates. As a result, deceleration of the reduction ratio corresponding to the difference in dimension between the internal gear 116 and the external gear 114 / the dimension of the external gear 114 can be realized.

In the first and second gear devices 110 and 210 of the series of gear devices according to the present embodiment, since the dimensional difference is "1", the reduction ratio is 1 / (the dimensions of the external gears 114 and 214 ), That is, 1 / (the dimension of the internal gears 116 and 216 - 1).

In other words, the first gear device 110 with a low reduction ratio has a small internal tooth size (the number of pin members) and a large tooth length (the diameter of the pin member 119) of the internal gear 116. Conversely, the second gear device 210 having a high reduction ratio has a large internal value of the internal gear 216 and a large tooth length (the diameter of the pin member 219), as compared with the first gear device 110 small. That is, the second gear device 210 having a high reduction ratio has a larger number of pin members 219 than the first reduction gear ratio first gear device 110, and the pin member 219 of the second gear device 210 And is smaller than the pin member 119 of the first gear unit 110. [

Conventionally, in the internal gear, a support hole in which a pin member can be fitted along the axial direction is first formed in the form of a through hole in the material to be the internal gear body, and then the radially inward portion , And cut into a semicircular semicircular " pin groove " to engage the pin member and the external gear in the cut portion. However, this manufacturing method is disadvantageous in that, when the internal gear of the second gear device with a high reduction ratio is manufactured, the number of the support holes to be formed is large, and " burr " generated at the edge of the pin groove at the time of cutting is removed There is a problem that the number of processing steps becomes very large, which is costly.

On the other hand, recently, a technique has also been adopted in which a pin groove having a semicircular cross section is directly formed on a material to be an internal gear body by using a gear shaper. In this type of gear device, particularly when the dimensional difference is " 1 ", since the pin member is disposed between the pin groove and the shout gear, the pin member does not fall out from the pin groove in this method. However, in this method, since the pin member is merely disposed between the pin groove and the shout gear, the pin member is likely to move in the radial direction due to eccentric oscillation of the shout gear, and noise may be generated during operation There was a problem.

Therefore, in the series of gear devices according to the present embodiment, the internal gears 116 and 216 of the first gear device 110 and the second gear device 210, in particular, are formed in the following configuration Or differentiated), so that both sides can be manufactured simply and at low cost.

3 is a partially enlarged cross-sectional view showing a configuration in the vicinity of the internal gear 16 1 of the first gear device 110 as described above. Fig. 4 is an enlarged sectional view of the internal gear 16 of the second gear device 210 And Fig.

The internal gears 116 and 216 of the first gear device 110 and the second gear device 210 are connected to the first gear device 110 and the second gear device 210, Internal gear bodies 117 and 217 and a plurality of pin members 119 and 219 disposed in the internal gear main bodies 117 and 217. The pin members 119 and 219 constitute internal teeth have.

The cover members 150 and 250 are connected to the internal gear main bodies 117 and 217 through bolts 152 and 252 from both sides in the axial direction. Specifically, the cover members 150 and 250 include load side cover members 150A and 250A disposed on the axial load side of the internal gears 116 and 216, And the load-side cover members 150B and 250B, which are disposed in the load-side cover members 150A and 150B, respectively. The cover members 150 and 250 are common to the first gear unit 110 and the second gear unit 210.

More specifically, the load side cover member 150A of the first gear device 110 and the load side cover member 250A of the second gear device 210 are common, and the load side cover member 250A of the first gear device 110, (150B) and the load side opposite cover members (250B) of the second gear device (210) are common to each other.

Supporting grooves 160 and 260 for supporting the pin members 119 and 219 are respectively provided on the cover members 150 and 250 (the load side cover members 150A and 250A and the load side opposite cover members 150B and 250B) have.

More specifically, the load side cover members 150A and 250A of the first and second gear devices 110 and 210 are provided on the surfaces 150A1 and 250A1 on the opposite sides of the axial load, Side support grooves 160A and 260A formed in the shape of a ring of the load-side support grooves 160A and 160A, respectively. The cover members 150B and 250B on the opposite sides of the load of the first and second gear devices 110 and 210 are formed on the surfaces 150B1 and 250B1 on the axial load side in an endless ring shape Side support grooves 160B and 260B, respectively.

The load side cover members 150A and 250A and the load side opposite cover members 150B and 250B of the first and second gear devices 110 and 210 are connected to the load side support grooves 160A and 260A and the load side support grooves 160B , And 260B.

The internal gear bodies 117 and 217 also serve as casing bodies of the first and second gear devices 110 and 210 and the internal gear bodies 117 and 217 and the first and second cover members 150 and 250 ), And the casing of the first and second gear devices 110 and 210 is formed. As a result, a large-sized member (or a material) constituting the casing can be used in common, resulting in a large cost reduction effect.

Next, the first gear device 110 and the second gear device 210 are differentiated as follows.

The internal gear main body 117 of the first gear device 110 has a support hole (through hole) 164 for supporting the entire circumferential side surfaces of the axial portions 119A and 119B of the pin member 119 . Specifically, the load side support hole 164A is provided on the load side of the external gear 114 and the external side support hole 164B is provided on the side opposite to the load side of the external gear 114. The pin member 119 of the first gear device 110 is not supported by the load side and the load side opposite side support grooves 160A and 160B of the load side and the load opposite side cover members 150A and 150B, Side support hole 164 (the load-side support hole 164A and the load-side support hole 164B).

However, in this embodiment, since the roller member 119S serving as the sliding promoting member is fitted to the outside of the pin member 119, the both side supports of the pin member 119 are interposed between them to be more reliably supported . However, of course, the pin member 119 itself may also be rotated by interposing the clearance.

On the other hand, as shown in FIG. 4, the internal gear main body 217 of the second gear device 210 is not provided with a support hole for the pin member 219. Only a semicircular pin groove 215 is formed by a gear shaper or the like to restrict the position of the pin member 219 in the circumferential direction. The pin member 219 of the second gear device 210 is supported by the support grooves 260 (the load side support grooves 260A and the load side support grooves 260B) of the load side and the load side opposite cover members 250A and 250B, So that movement in the radial direction is restrained.

Therefore, the pin member 119 of the first gear device 110 (the pin member 119 tends to rotate quickly) is supported by the support hole 164 (the load side support hole 164A and the load side support hole 164B ), The entire circumferential side surfaces of the portions 119A and 119B in the axial direction are supported on both sides, and are securely supported also in the radial direction and the circumferential direction. As a result, the pin member 119 can be reliably supported irrespective of the eccentric swinging state of the external gear 114, thereby making it difficult to generate noises during operation.

The second gear device 210 (having a large number of pin members 219) is not provided with a support hole serving as a through hole for supporting the entire circumference of the side surface of the pin member 219, 217 can be greatly reduced. The pin member 219 of the second gear device 210 is restricted in its circumferential position by the semicircular pin groove 215 formed in the internal gear main body 217, The movement in the radial direction is restrained by being supported on both sides by the support grooves 260 (the load side support grooves 260A and the load side support grooves 260B) of the members 250A and 250B, It is possible to reliably support the pin member 219 regardless of the state of the swinging motion.

This configuration is also applicable to a structure in which the pin member is supported from the radially inward side by, for example, an insert ring or the like when the pin member 219 of the second gear device 210 is restrained from moving in the radial direction, No "separate member" is required. That is, when the pin member is supported from the inside in the radial direction by the insert ring or the like, since the diameter of the pin member is different when the reduction ratio is different, it is necessary to prepare a dedicated insert ring for each reduction ratio, The increase in the number of components does not occur.

However, in this regard, if the pin member is mounted so that the innermost diameter of the pin member is unified, it is possible to provide only one type of insert ring. In this case, however, the pitch diameter of the pin member of the second gear device having the high reduction ratio tends to be smaller than the pitch diameter of the pin member of the first gear device having the low reduction ratio, which is not preferable.

However, this series also has a favorable tendency in this respect.

That is, in this series, the support grooves 160 and 260 (the load side support grooves 160A and 260A) of the cover member 150 (the load side cover members 150A and 250A and the load side opposite cover members 150B and 250B) (The diameter of the center of the innermost circumferential circle d2 and the center of the outermost circumferential circle d2) d3 of the first gear device 110 (the opposite side support grooves 160B, 260B) (Twice the distance from the center of the internal gear 116 to the center of the support hole 164). This is because the pitch diameter Pcd2 (? D3) of the pin member 219 of the second gear device 210 engaged with the support groove 260 is smaller than the pitch diameter Pcd2 (? D3) of the pin member 219 of the first gear device 110 (See Fig. 5 and Fig. 6 together), which is larger than the pitch circle diameter Pcd1 (? D4) of the pitch circle 119.

The pinion 219 of the second gear device 210 having a smaller diameter can be formed so as to transmit the pitch diameter Pcd2 of the pinion 219 of the smaller diameter smaller than the pinion diameter Pcd2 of the pinion 219 of the first gear device 110, Can be made larger than the pitch circle diameter (Pcd1) of the member (119). As a result, the durability of the pin member 219 of the second gear device 210 can be secured with more margin, and a very reasonable tendency can be obtained from the viewpoint of strength.

In this series, as described above, in order to facilitate sliding between the pinion gear 119 of the first gear unit 110 and the pinion gear 114, a sliding member (119S) is fitted outside. On the other hand, on the pin member 219 of the second gear device 210, the roller member is not fitted on the outside. This differentiation can effectively reduce the sliding resistance of the pin member 119 of the first gear unit 110 that tends to increase the sliding between the external gear 114 and the pin member 119 in particular, In the second gear device 210 in which the sliding is relatively small and the number of pin members is large, the manufacturing cost can be reduced (by not providing the roller member). That is, it is possible to reasonably assure both the securing of the action effect of reducing the sliding resistance and the cost reduction. However, the outer fitting of the roller member may be employed in both of the first and second gear devices 110 and 210 (without differentiation) when the effect of reducing the sliding resistance is emphasized, It is not necessary to adopt both of them.

In this series, in the first gear device 110 in which the roller member 119S is fitted outside on the outer periphery of the pin member 119, the forming portion of the load side support hole 164A of the internal gear main body 117 (The distance from the center of the internal gear 116 to the inner periphery of the forming portion 117A) of the roller member 117A is larger than the innermost diameter D2 of the roller member 119S fitted to the outside of the pin member 119 (The minimum value of the distance from the shaft center of the internal gear 116 to the outer periphery of the roller member 119S). Thereby, the shout gear 114 can be easily mounted from the load side regardless of the presence of the roller member 119S. The problem of the attachment of the external gear 114 does not occur with respect to the internal diameter D3 of the forming portion 117B of the bearing opposite side support hole 164B of the internal gear body 117, And is formed to be smaller than the innermost diameter D2, thereby increasing the strength of the forming portion 117B. This configuration is particularly advantageous in a gear device in which a roller member is fitted outside. As a result, the external gear is easily mounted from the side on which the relationship is established (the side where the inner diameter of the forming portion of the support hole is larger than the innermost diameter of the roller member fitted outside the pin member: the load side or the load opposite side) can do. However, the inner diameter D3 of the forming portion 117B, the innermost diameter D2 of the roller member 119S, and the inner diameter D1 of the forming portion 117A may be used.

However, in the series of gear devices, a gear device having a center crank type eccentric oscillation type reduction mechanism having an eccentric body shaft for eccentrically swinging the external gear in the radial direction center of the gear device is employed. The deceleration mechanism of the series of gear devices relating to the present invention is not limited to this configuration. For example, a plurality of eccentric shafts having an eccentric body for swinging external gears are provided at positions offset from the radial center of the gear device, and the eccentric body shafts are rotated synchronously to thereby oscillate the external gear. It is also possible to apply to an eccentric rocking type gear device which is referred to as an eccentric rocking type gear device. Further, even if the gear is not an eccentric rocking type gear, the internal gear can be applied to various gears having an arcuate tooth shape.

In the series of gear devices, there is shown an example in which the difference between the external teeth of the external gear and the internal teeth of the internal gear is " 1 ", but the difference in dimension between the external gear and the internal gear may be two or more. In the case of the eccentric rocking type gear device according to the above-described configuration, when the difference in dimension is n or more, the reduction ratio is n / (the dimension of the internal gear-n). Therefore, in the case where the dimensional difference is kept the same, the larger the reduction gear ratio, the larger the number of pin members and the smaller the diameter of the pin member. However, This relationship does not necessarily lead to this tendency. In the series of gear devices according to the present invention, it is defined that the second gear device has more pin members (regardless of the reduction ratio) and the pin member has a smaller diameter. As a result, the first gear device and the second gear device can be manufactured at low cost.

110, 210: first and second gear devices
114, 214: External gear
116, 216: internal gear
117, 217: internal gear body
119, 219: pin member
150, 250: cover member
160, 260: Support groove

Claims (6)

A first gear device having an internal gear body and a plurality of pin members disposed in the internal gear body, an internal gear which forms the internal teeth of the pin member, and a cover member connected to the internal gear body; As a series of gear devices including a two-gear device,
The first gear device and the second gear device are configured such that the cover member is common,
Wherein the cover member is provided with a support groove for supporting the pin member,
The second gear device has more pin members than the first gear device,
The pin member of the second gear unit is smaller in diameter than the pin member of the first gear unit,
Wherein the internal gear main body of the first gear unit has a support hole for supporting a whole circumferential side surface of a part of the pin member in the axial direction,
The pin member of the first gear unit is not supported by the support groove of the cover member but is supported by the support hole of the internal gear body,
Characterized in that the internal gear main body of the second gear unit is not provided with the support hole of the pin member and the pin member of the second gear unit is supported by the support groove of the cover member . The method according to claim 1,
Characterized in that the support groove of the cover member is formed in an endless ring shape. 3. The method according to claim 1 or 2,
Wherein a center circle diameter of the support groove of the cover member is larger than a center circle diameter of the support hole of the first gear unit. 3. The method according to claim 1 or 2,
Wherein the cover member includes a first cover member disposed on an axial load side of the internal gear and a second cover member disposed on an opposite side to the axial load on the side of the internal gear, And the support grooves are provided on both sides. 3. The method according to claim 1 or 2,
On the outer periphery of the pin member, a roller member is fitted outside,
Wherein the inner diameter of the portion of the internal gear main body where the support hole is formed is larger than the innermost diameter of the roller member fitted to the outside of the pin member. 6. The method of claim 5,
The support hole is formed on both the load side and the load side of the internal gear body,
Wherein an inner diameter of a forming portion of one of the support holes is larger than a innermost diameter of the roller member,
And the inner diameter of the other formed portion of the support hole is smaller than the innermost diameter of the roller member.

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