JP2020016313A - Speed reduction device - Google Patents

Abstract

To provide a speed reduction device capable of reducing an inertial load of an output member.SOLUTION: A speed reduction device (1) comprises a speed reduction mechanism, and an output member (29) for outputting rotation whose speed is reduced by the speed reduction mechanism. The output member (29) and a driven member (62) are coupled to each other by plural bolts (B1). Adhesive is applied to a coupling face of the output member (29) and the driven member (62). A relationship between a total sum X[mm] of a product of PCD radiuses and effective cross section areas of the plural bolts (B1) and an acceleration time peak torque Y[Nm] is Y>0.024×X.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a reduction gear transmission.

  FIG. 1 of Patent Document 1 shows a reduction gear (G4) that transmits a rotational motion to a driven member (15). The speed reducer (G4) includes an output member (34) that outputs a reduced rotational motion, and the output member (34) is connected to the driven member (15) via a bolt (44).

JP 2014-161952 A

  Generally, the output member and the driven member of the reduction gear transmission are firmly connected by using a number of bolts so that no slippage occurs between them. However, since many bolts have a large weight, they increase the inertial load (moment of inertia of load) of the output member. When a rotational motion is input from the motor to the speed reducer, an increase in the inertial load of the output member affects the characteristics of the motor and increases the power consumption of the motor.

  An object of the present invention is to provide a speed reducer capable of reducing the inertial load of an output member.

である構成とした。 The present invention is a reduction gear transmission, comprising: a reduction mechanism, and an output member that outputs rotation reduced by the reduction mechanism, wherein the output member and the driven member are connected by a plurality of bolts,
An adhesive is applied to a connection surface between the output member and the driven member,
The relationship between the sum X [mm ³ ] of the product of the PCD radius of the plurality of bolts and the effective sectional area and the peak torque during acceleration Y [Nm] is as follows:
Y> 0.024 × X

Was adopted.

  ADVANTAGE OF THE INVENTION According to this invention, the effect that the inertial load of an output member can be reduced is acquired.

It is a sectional view (A) showing a reduction gear concerning a first embodiment of the present invention, and an enlarged drawing (B) of a part thereof. It is the top view which looked at the reduction gear transmission of Embodiment 1 from the load side in the axial direction. It is sectional drawing which shows the reduction gear of Embodiment 1 with which the driven member was connected. It is a graph which shows the relationship between the thickness of an adhesive layer and shear strength. It is the graph which showed the relationship between the characteristic value of the bolt connection part, and the peak torque at the time of acceleration about the existing several types of reduction gears. The contour diagram which shows the ratio of the adhesion area which satisfies the peak torque at the time of acceleration is shown. It is sectional drawing (A) which shows the speed reducer which concerns on Embodiment 2 of this invention, and its enlarged view (B). It is the top view which looked at the reduction gear of Embodiment 2 from the load side in the axial direction. It is sectional drawing (A) which shows the reduction gear which concerns on Embodiment 3 of this invention, and its enlarged view (B). It is the top view which looked at the reduction gear of Embodiment 3 from the load side in the direction of an axis.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

(Embodiment 1)
FIG. 1 is a cross-sectional view (A) showing a reduction gear transmission according to Embodiment 1 of the present invention, and an enlarged view (B) of a part thereof. In this specification, a direction along the rotation axis O1 is defined as an axial direction, a direction perpendicular to the rotation axis O1 is defined as a radial direction, and a rotation direction about the rotation axis O1 is defined as a circumferential direction. FIG. 1 is a sectional view taken along line AA of FIG.

  The reduction gear transmission 1 according to the first embodiment includes an input shaft 10 to which a rotational motion is input, a reduction mechanism that reduces the rotational motion of the input shaft 10, and an output member that is connected to a driven member and outputs a reduced rotational motion. 29. Although the speed reduction mechanism is not particularly limited, in the present embodiment, the external gear 12 is a bending engagement type gear mechanism in which the rotational motion is transmitted by bending deformation. The speed reduction mechanism includes an exciter 10A, an exciter bearing 15, an external gear 12, a first internal gear 22g, a second internal gear 23g, bearings 31, 32, and a main bearing 33 provided on the input shaft 10. Prepare. The reduction gear transmission 1 further includes a first internal gear member 22, a second internal gear member 23, a casing 24, a first cover 26, and a second cover 27. Among them, the second internal gear member 23 and the second cover 27 correspond to the output member 29.

  The input shaft 10 has a hollow shaft shape, and a vibrating body 10A whose cross section perpendicular to the rotation axis O1 has an elliptical outer shape, and a cross section provided on both axial sides of the vibration body 10A and perpendicular to the rotation axis O1. Have shaft portions 10B and 10C whose outer shape is circular. The elliptical shape does not need to be a geometrically exact ellipse, but includes a substantially elliptical shape. The input shaft 10 rotates around a rotation axis O1.

  The external gear 12 is a flexible cylindrical member having teeth on the outer periphery.

  The exciter bearing 15 is a roller bearing, and is disposed between the exciter 10 </ b> A and the external gear 12. The exciter 10 </ b> A and the external gear 12 are mutually supported via an exciter bearing 15 so as to be relatively rotatable.

  The first internal gear 22g and the second internal gear 23g mesh with the external gear 12 side by side in the axial direction. The first internal gear 22g is configured by providing teeth on a part of the inner periphery of the first internal gear member 22. The second internal gear 23 g is configured by providing teeth on a part of the inner periphery of the second internal gear member 23.

  The casing 24 is connected to the first internal gear member 22 and covers the outer peripheral side of the second internal gear member 23. The casing 24 and the second internal gear member 23 are mutually supported via a main bearing 33 so as to be relatively rotatable. The main bearing 33 is, for example, a cross roller bearing.

  The first cover 26 is connected to the first internal gear member 22 and covers the outer peripheral portion of the input shaft 10 on the non-load side. The non-load side means the side opposite to the side to which the driven member is connected in the axial direction. The first cover 26 supports the shaft portion 10B of the input shaft 10 via a bearing 31 so as to be relatively rotatable. The second cover 27 is connected to the second internal gear member 23 and covers an outer peripheral portion of the input shaft 10 on the load side. The load side means a side to which the driven member is connected in the axial direction. The second cover 27 supports the shaft portion 10C of the input shaft 10 via a bearing 32 so as to be relatively rotatable. The bearings 31 and 32 are, for example, ball bearings.

<Description of deceleration operation>
When a rotational motion is input from a motor or the like (not shown) and the input shaft 10 rotates, the motion of the vibration generator 10 </ b> A is transmitted to the external gear 12. At this time, the external gear 12 is restricted to a shape along the outer peripheral surface of the vibration generator 10A, and is bent into an elliptical shape having a long axis portion and a short axis portion when viewed from the axial direction. Further, the external gear 12 meshes with the fixed first internal gear 22g at a long axis portion. For this reason, the external gear 12 does not rotate at the same rotational speed as the exciter 10A, and the exciter 10A relatively rotates inside the external gear 12. Then, with this relative rotation, the external gear 12 bends and deforms so that the long axis position and the short axis position move in the circumferential direction. The cycle of this deformation is proportional to the rotation cycle of the input shaft 10.

  When the external gear 12 bends and deforms, the position of its long axis moves, so that the position where the external gear 12 meshes with the first internal gear 22g changes in the rotational direction. Here, assuming that the number of teeth of the external gear 12 is 100 and the number of teeth of the first internal gear 22g is 102, the mesh between the external gear 12 and the first internal gear 22g every time the meshing position goes around once. The fitted teeth are shifted, whereby the external gear 12 rotates (rotates). If the number of teeth is the above, the rotational motion of the input shaft 10 is reduced at a reduction ratio of 100: 2 and transmitted to the external gear 12.

  On the other hand, since the external gear 12 meshes with the second internal gear 23g, the position where the external gear 12 meshes with the second internal gear 23g also changes in the rotation direction by the rotation of the input shaft 10. Here, assuming that the number of teeth of the second internal gear 23g and the number of teeth of the external gear 12 are the same, the external gear 12 and the second internal gear 23g do not relatively rotate and the external gear 23g does not rotate. The rotational motion of the gear 12 is transmitted to the second internal gear 23g at a reduction ratio of 1: 1. As a result, the rotational motion of the input shaft 10 is reduced at a reduction ratio of 100: 2 and transmitted to the output member 29 (the second internal gear member 23 and the second cover 27), and the rotational motion is transmitted to the driven member 62 ( 3).

<Details of output members>
FIG. 2 is a plan view of the reduction gear transmission of the first embodiment as viewed from the load side in the axial direction. FIG. 3 is a cross-sectional view illustrating the reduction gear transmission of Embodiment 1 to which the driven members are connected. A cross section of the reduction gear transmission 1 in FIG. 3 corresponds to a cross section taken along line BB in FIG.

  The output member 29 is configured by connecting the second internal gear member 23 and the second cover 27. As shown in FIG. 2, the output member 29 has a plurality of bolt holes H1 and H2 extending in the axial direction. Further, the second cover 27 has a plurality of pin holes H3 extending in the axial direction. In FIG. 2, only one of the plurality of bolt holes H1 is denoted by a reference numeral, but holes of the same size provided on the same circumference as the holes are also the bolt holes H1. Similarly, only one of the bolt holes H2 and the pin hole H3 is denoted by the same reference numeral, and the holes of the same size provided on the same circumference are also the bolt hole H2 and the pin hole H3.

  The bolt hole H1 is for connecting the driven member 62 to the output member 29, and communicates with the second internal gear member 23 and the second cover 27 as shown in FIG. Of the bolt holes H1, a hole portion of the second cover 27 has a diameter through which the shaft portion of the bolt B1 is inserted, and a female screw is provided in a hole portion of the second internal gear member 23.

  As shown in FIG. 2, the plurality of bolt holes H1 are provided at equal intervals in the circumferential direction on the same circumference centered on the rotation axis O1. In FIG. 2, 16 bolt holes H <b> 1 are provided, but in the present embodiment, some of them (for example, 4) are used to connect the driven member 62. Note that the bolt holes H1 may be provided on different circles around the rotation axis O1, or may be provided at different intervals in the circumferential direction. The unused bolt hole H1 may be omitted, or may be replaced with a lightening hole having no female screw to reduce the weight of the output member 29.

  The bolt hole H2 is for connecting the second internal gear member 23 and the second cover 27, and communicates with the second internal gear member 23 and the second cover 27 as shown in FIG. I have. The hole portion of the second cover 27 in the bolt hole H2 has a space for accommodating the head of the bolt B2 and a space for inserting the shaft of the bolt B2. A female screw is provided in a hole portion of the second internal gear member 23 in the bolt hole H2. The second internal gear member 23 and the second cover 27 are connected by a plurality of bolts B2 via bolt holes H2. The head of the bolt B2 is housed in the bolt hole H2 and does not protrude from the load-side end face of the second cover 27. The connection by the bolt B2 and the bolt hole H2 may be omitted.

  The pin hole H3 is used when removing the second cover 27 from the second internal gear member 23. The pin hole H3 may be omitted.

  The second cover 27 has a concave portion 27m which is concave in the axial direction and is coated with an adhesive on a surface on the load side. The recess 27m is located radially inward of the inscribed circle of the plurality of bolt holes H1, as shown in FIG. The concave portion 27m has an annular shape connected in the circumferential direction, but may be divided into a plurality in the circumferential direction. Further, the recess 27m has a shape in which the distance from the rotation axis O1 and the width in the radial direction are equal at any position in the circumferential direction, but the distance from the rotation axis O1 along the circumferential direction or the radial direction. The width may be changed. The depth of the recess 27m is not less than 20 μm and not more than 30 μm.

<Connection structure between driven member and output member>
The connection between the driven member 62 and the output member 29 is performed by tightening a plurality of bolts B1 and bonding with an adhesive.

  As shown in FIG. 3, the bolt B1 is tightened in the bolt hole H1, and connects the driven member 62, the second cover 27, and the second internal gear member 23. In the present embodiment, four bolts B1 are tightened into four bolt holes H1 provided at substantially equal intervals. Each bolt B1 is passed through the bolt hole 62h of the driven member 62 and the bolt hole H1 of the second cover 27, and is screwed with the female screw of the bolt hole H1 of the second internal gear member 23. The driven member 62 and the second cover 27 are fastened together between the second internal gear member 23 and the bearing surface of the bolt B1 by the bolt axial force of the bolt B1.

  The bolt B1 is a bolt of the highest strength category among JIS standard steel bolts, and is tightened by a specified tightening torque according to the effective sectional area. The effective sectional area of the bolt B1 is specified in JIS (Japanese Industrial Standards) B1082.

  FIG. 4 is a graph showing the relationship between the thickness of the adhesive layer and the shear strength.

  The end face of the driven member 62 and the end face on the load side of the second cover 27 are adhered by an adhesive applied to the recess 27m. For this bonding, a cyanoacrylate-based adhesive is used. By applying the adhesive according to the volume of the concave portion 27m, the output member 29 and the driven member 62 can be bonded substantially over the entire region of the concave portion 27m without the adhesive protruding from the concave portion 27m. Since the depth of the concave portion 27m is not less than 20 μm and not more than 30 μm as described above, as shown in FIG. 4, a high shear strength can be obtained between the output member 29 and the driven member 62 by the adhesive layer in this portion. Can be

<Relationship between peak torque during acceleration and connection parameter>
In the specification of the reduction gear transmission 1 of the present embodiment, an acceleration peak torque Y [Nm] is specified. The speed reducer 1 is operated with the peak torque during acceleration Y [Nm] limited so as not to exceed a specified value. Here, the peak torque during acceleration is sometimes referred to as an allowable peak torque at start / stop, and is an allowable value of the peak torque applied to the output member during normal start (acceleration) and stop (deceleration). In other words, it can be said that the output peak torque is an allowable value of the output peak torque that can be driven a specified number of times (or a specified time) without causing the gear mechanism to be fatigued and destroyed.

In the reduction gear transmission 1 of the present embodiment, the sum X of the products of the PCD (Pitch Circle Diameter) radius D [mm] and the effective sectional area As [mm ² ] of the plurality of bolts B1, and the acceleration peak torque Y [Nm]. Is as shown in the following equation (1).
Y> 0.024 × X (1)

  The PCD radius refers to the radius of an imaginary circle passing through the center of the bolt and substantially centering on the rotation axis O1, and may be written as PCD / 2. In the present embodiment, as shown in FIG. 2, a plurality of bolt holes H1 to which a plurality of bolts B1 are tightened are arranged on an imaginary circle of the same PCD, and the effective sectional areas of the plurality of bolts B1 are the same. The total number of the plurality of bolts B1 is four. Therefore, the sum X is obtained as in the following equation (2).

X = 4 × D × As (2)
Here, D is the PCD radius [mm] of the plurality of bolts B1, and As is the effective sectional area [mm ² ] of one bolt B1.

ここで、ｎは複数のボルトＢ１の総数、Ｄ_ｉはｉ番目のボルトＢ１のＰＣＤ半径［ｍｍ］、Ａｓ_ｉはｉ番目のボルトＢ１の有効断面積［ｍｍ^２］である。複数のボルトＢ１が、複数のＰＣＤの仮想円上に締め付けられる場合、あるいは、複数のボルトＢ１が異なる有効断面積を有する場合には、式（３）を適用して総和Ｘを求めればよい。 When generalized, the sum X can be obtained as in the following equation (3).

Here, n is the total number of the plurality of bolts B1, the _{D i} PCD radius of i-th bolts B1 [mm], As _i is the effective cross-sectional area of the i-th bolts B1 [mm ^2]. When the plurality of bolts B1 are tightened on the virtual circles of the plurality of PCDs, or when the plurality of bolts B1 have different effective cross-sectional areas, the total sum X may be obtained by applying Expression (3).

<Operation of relational expression (1)>
FIG. 5 is a graph showing the relationship between the characteristic value of the bolt connection portion and the peak torque during acceleration for a plurality of types of existing reduction gears. The horizontal axis indicates the total sum X of the products of the PCD radii of the plurality of bolts connecting the driven members and the effective sectional area, and the vertical axis indicates the specified peak torque during acceleration Y.

The relationship between the specified peak torque during acceleration Y [Nm] and the sum X [mm ³ ] of the products of the PCD radii and the effective cross-sectional areas of the plurality of bolts connecting the driven members, for a plurality of types of existing reduction gears. Is found to have a substantially linear relationship as shown in the following equation (4). Here, the existing reduction gear transmission has a configuration in which the driven member is connected to the output member using only bolts.
Y ≒ 0.024 × X (4)

  In the existing speed reducer, the number, position and size of bolts are determined by calculation and tests so that the specification of the peak torque during acceleration Y is satisfied within a range where the coupling force of the driven member does not cause a large excess or deficiency. ing. That is, according to the relationship of Expression (4), the frictional force is generated on the contact surface between the driven member and the output member due to the axial force of the plurality of bolts, and even if a specified acceleration peak torque is applied to the contact surface. No slip is expected.

  On the other hand, the speed reducer in which the value of (X, Y) is in the region R1 above the graph line in FIG. Indicates that the connection of the driving member is weak. In other words, it indicates that the limit of the torque that does not cause slip on the contact surface between the output member and the driven member based on the axial force of the bolt is low. Conversely, the reduction gear having the value (X, Y) in the region R2 below the graph line in FIG. Indicates that the connection of the driven member by the is strong.

  In the reduction gear transmission 1 of the first embodiment, an adhesive force is added to the coupling force between the driven member 62 and the output member 29. As a result, the relationship between the coupling force of the plurality of bolts B1 and the acceleration peak torque Y is set to be Y> 0.024 × X while satisfying the specification of the acceleration peak torque Y. The value of (X, Y) is determined by reducing the inertial load of the output member 29 to the standard value of the existing speed reducer, for example, by reducing the number of bolts B1 as compared with the connection of the driven member by a standard bolt. It works to reduce it. Therefore, according to the reduction gear transmission 1 of the present embodiment, an effect is obtained that the inertial load on the output member 29 is reduced as compared with the conventional reduction gear transmission having the same peak torque during acceleration.

<Position and area of bonding surface>
As shown in FIG. 4, the shear strength of the adhesive layer is high. For example, when bonding of the same area as the head of one bolt is performed on the same PCD circumference as the bolt, the retention obtained by the adhesive layer is obtained. The torque is higher than the holding torque of one bolt. The holding torque means a maximum torque at which the driven member is fixed in a stationary state and no slip occurs on the contact surface between the driven member and the output member when a torque is applied to the output member. For example, when the holding torque by one bolt B1 is 36 Nm, the holding torque by adhesion is 59 Nm.

  Therefore, the position and area of the bonding surface that satisfies the peak torque Y during acceleration are set such that the sum of the holding torque by the plurality of bolts B1 and the holding torque by the bonding layer exceeds the peak torque during acceleration with a predetermined margin. It can be obtained by calculation, test, and the like. The position and the area of the bonding surface correspond to the position and the area of the concave portion 27m of the second cover 27 to which the adhesive is applied. Since the adverse effect caused by an excessively large bonding area is small, the area of the bonding surface may be determined to be relatively large.

  In the reduction gear transmission 1 of the first embodiment, the recess 27m is located radially inward of the inscribed circle of the plurality of bolt holes H1 (see FIG. 2). The depth of the recess 27m is not less than 20 μm and not more than 30 μm. The area of the recess 27m is determined so that the sum of the holding torque of the plurality of bolts B1 and the holding torque of the adhesive layer exceeds the peak torque during acceleration with a predetermined margin.

  Note that the position and area of the bonding surface (recess 27 m) can be variously changed. Subsequently, an example of a method of obtaining the position and the area of the bonding surface satisfying the peak torque at the time of acceleration will be described.

  FIG. 6 is a contour diagram showing the ratio of the bonding area satisfying the peak torque during acceleration. The horizontal axis of the contour diagram indicates the total sum X of the products of the PCD radii of the plurality of bolts B1 and the effective sectional area, and the vertical axis indicates the peak torque during acceleration Y defined in the reduction gear 1. Further, the contour lines indicate the minimum ratio [%] of the bonding area required to satisfy the peak torque during acceleration. The ratio of the minimum required bonding area is calculated from the shear strength of the bonding layer by calculating the bonding area for obtaining the same holding torque as the reduced bolt B1 when the number of bolts B1 is reduced, and calculating the area A1 ( 2 (see FIG. 2). The bonding position is defined as a predetermined angle range within the area A1. The area A1 includes a circle having an outer radius φ1 (= the PCD radius of the plurality of bolts B1 + １ ／ of the effective diameter of the bolt holes H1) and an inner radius φ2 (= PCD radius of the plurality of bolts B1−effectiveness of the bolt holes H1). It is defined as a region surrounded by a circle having a diameter of）). The isovalue line of 0 [%] in FIG. 6 matches the graph line of Y ≒ 0.024 × X in FIG. Here, the effective diameter means a virtual cylinder diameter such that the width of the thread groove measured in the direction of the axis is equal to the width of the thread as defined in JIS B 0205-4. .

  When the set value of the peak torque Y at the time of acceleration, the number of bolts B1, the size (effective area), and the position of the bolt hole H1 (PCD radius) are determined, the value of (X, Y) of the reduction gear 1 is determined. . If the number of bolts B1 is reduced or a small bolt B1 is applied based on a reduction gear having only the bolt connection and the same peak torque Y during acceleration, the value of (X, Y) becomes 0 [in FIG. %] Above the contour line.

  To determine the position and area of the bonding surface, first, the ratio F of the bonding area of the region including the value of (X, Y) of the reduction gear 1 is calculated using the contour diagram of FIG. For example, if it is a region between a contour line of 0 [%] and a contour line of 20 [%], the ratio F of the bonding area may be set to 20 [%]. Contour lines may be drawn at finer intervals, and the bonding area ratio F may be determined at finer intervals.

  If the bonding surface is provided in an arbitrary angle range of the region A1, the bonding area may be the area of the ratio F obtained as described above or an area larger than that. Thus, the connection that satisfies the acceleration peak torque Y is realized by the connection between the bonding surface and the plurality of bolts B1.

  On the other hand, if the bonding surface is provided on the inner circumferential side or the outer circumferential side with respect to the region A1, the bonding area is calculated by dividing the area S represented by the ratio F obtained as described above into the PCD radius R (rotational area) of the bonding surface. The conversion may be made in accordance with a change in the radial position of the bonding surface about the axis O1). That is, the area S represented by the ratio F may be increased or decreased according to the position of the bonding surface in the radial direction so that the bonding area S × the PCD radius R does not change. When a plurality of divided adhesive surfaces are provided at a plurality of locations having different radial positions, the total sum of the adhesive surfaces is represented by a ratio F when conversion is performed to move the individual adhesive surfaces to the area A1. What is necessary is just to calculate each bonding area so as to obtain the area. The connection that satisfies the peak torque during acceleration Y is realized by the connection between the bonding surface and the plurality of bolts B1 thus determined.

<Effects of Embodiment>
As described above, according to the reduction gear transmission 1 of the first embodiment, the adhesive is applied to the connection surface between the output member 29 and the driven member 62. Further, the relationship between the sum X [mm ² ] of the product of the PCD radius of the plurality of bolts B1 and the effective cross-sectional area and the peak torque during acceleration Y [Nm] is Y> 0.024 × X. Therefore, the weight of the bolt B1 can be reduced as compared with a reduction gear having the same specification of the peak torque at the time of acceleration and connected to the driven member only by the bolt. As a result, the effect that the inertial load of the output member 29 is reduced is obtained, and the power consumption of the motor that inputs the rotational motion to the reduction gear 1 can be reduced.

  Further, according to the reduction gear transmission 1 of the first embodiment, the output member 29 is provided with the concave portion 27m for applying the adhesive. Accordingly, the bonding position, the depth of the bonding layer, and the bonding area are stabilized by the concave portion 27m, and individual differences in bonding with the driven member 62 can be reduced. In addition, it is possible to suppress the adhesive from flowing to a portion different from the desired position and solidifying. For example, it is possible to suppress the adhesive from hardening in the sliding portion and the contact surface with the driven member 62 from being stained.

  Further, according to the reduction gear transmission 1 of the first embodiment, the recess 27m is located radially inward of the inscribed circle of the plurality of bolt holes H1. That is, the connection by the plurality of bolts B1 is performed radially outward from the bonding surface. Thereby, when a large torque close to the limit torque is applied, the balance of the stress generated between the connecting portion of the bolt B1 and the bonding surface becomes suitable, and the connecting portion of the bolt B1 easily shifts first or the bonding surface becomes It is possible to suppress an imbalance such as a tendency to surrender first.

  Furthermore, according to the reduction gear transmission 1 of the first embodiment, since the depth of the recess 27m is not less than 20 μm and not more than 30 μm, a high shear strength of the adhesive layer can be obtained.

(Embodiment 2)
FIG. 7 is a sectional view (A) showing a reduction gear transmission according to Embodiment 2 of the present invention, and an enlarged view (B) of a part thereof. FIG. 8 is a plan view of the reduction gear transmission of the second embodiment as viewed from the load side in the axial direction.

  The speed reducer 1A according to the second embodiment is different mainly in the position and the planar shape of the concave portion 27mA to which the adhesive is applied, and the other components are the same as those in the first embodiment. The same components are denoted by the same reference numerals, and detailed description is omitted.

  The recessed portion 27mA according to the second embodiment includes an interposition part a1 arranged between one bolt hole (one bolt hole) H1 and another one bolt hole (other bolt hole) H1. In the present embodiment, the interposition portion a1 is disposed between a pair of bolt holes H1 and H1 that are arranged (adjacent) in the circumferential direction on the same PCD radius. However, the present invention is not limited to this. When a plurality of bolt holes H1 are provided on different PCD radii, the pair of bolt holes H1 and the interposed portion a1 of the concave portion 27mA interposed therebetween are arranged side by side in the circumferential direction. It is not necessary.

  Further, the concave portion 27mA of the second embodiment includes a circumferentially continuous annular portion b1 located radially inward of the inscribed circle of the plurality of bolt holes H1. The annular portion b1 and the plurality of intervening portions a1 are continuous. By connecting these, the workability of applying the adhesive can be improved. The recess 27mA may include a plurality of intervening portions a1, but do not include the annular portion b1. Further, the concave portion 27mA may be configured to be divided into a plurality of interposed portions a1 and an annular portion b1.

  The depth of the concave portion 27 mA is 20 μm or more and 30 μm or less as in the first embodiment.

  As described above, according to the speed reducer 1A of the second embodiment, the recessed portion 27mA to which the adhesive is applied includes the interposed portion a1 arranged between the pair of bolt holes H1. As a result, a stronger connection strength based on the adhesive layer can be secured, and accordingly, the bolt B1 can be reduced in the design stage, and the inertial load on the output member 29 can be further reduced.

(Embodiment 3)
FIG. 9 is a cross-sectional view (A) showing a reduction gear transmission according to Embodiment 3 of the present invention and an enlarged view (B) of a part thereof. FIG. 10 is a plan view of the reduction gear transmission of the third embodiment viewed from the load side in the axial direction.

  The speed reducer 1B of the third embodiment is different mainly in the position of the concave portion 27mB to which the adhesive is applied, and the other components are the same as those of the first embodiment. The same components are denoted by the same reference numerals, and detailed description is omitted.

  The recess 27mB according to the third embodiment is located radially outward of a circumscribed circle of the plurality of bolt holes H1. The concave portion 27mB has an annular shape connected in the circumferential direction, but may be divided into a plurality in the circumferential direction. Further, the recess 27mB has a shape in which the distance from the rotation axis O1 and the width in the radial direction are equal at any position in the circumferential direction, but the distance from the rotation axis O1 along the circumferential direction or the radial direction. May be changed in shape. The depth of the recess 27 mB is not less than 20 μm and not more than 30 μm.

  According to the reduction gear transmission 1B of the third embodiment, even when a plurality of bolt holes H1 are provided near the inner periphery of the output member 29, the bonding surface can be easily secured. In addition, the number, size, and the like of the bolts B1 can be reduced at the time of design, and the inertial load of the output member 29 can be reduced.

  The embodiments of the present invention have been described above. However, the present invention is not limited to the above embodiment. For example, in the above-described embodiment, the speed reduction mechanism of the bending mesh gear device is described as the speed reduction mechanism. However, the speed reduction mechanism according to the present invention is not particularly limited, and for example, a speed reduction mechanism of a so-called cup-type or silk-hat-type flexible meshing gear device may be applied. Furthermore, the reduction mechanism according to the present invention is a so-called eccentric oscillating type eccentric oscillating device in which two or more shafts having an eccentric body are arranged offset from the axis of the speed reducing device. Each reduction mechanism of a mold reduction gear or a simple planetary gear may be applied.

  Further, in the above embodiment, a cyanoacrylate-based adhesive is described as an example of the adhesive, but another type of adhesive may be applied. In the above embodiment, steel is assumed as the material of the output member 29, the driven member 62, and the bolt B1, but the material is not limited to these. In the above embodiment, the output member is provided with the concave portion to which the adhesive is applied. However, a concave portion may be provided in the driven member, or a concave portion may be provided in both the output member and the driven member. Further, the concave portion may not be provided in both the output member and the driven member. A configuration in which the driven member and the reduction gear of the embodiment are combined may be regarded as an example of the reduction gear according to the present invention.

  Further, in the embodiment, a component integrally formed by a single member may be divided into a plurality of members and replaced with a component connected or fixed to each other. Further, a component configured by connecting a plurality of members may be replaced with a component integrally formed by a single member. Other details specifically shown in the embodiments can be appropriately changed without departing from the spirit of the invention.

DESCRIPTION OF SYMBOLS 1, 1A, 1B Reduction gear 10 Input shaft 10A Exciter 12 External gear 15 Exciter bearing 22g First internal gear 23 Second internal gear member 23g Second internal gear 27 Second cover 27m, 27mA, 27 mB recess 29 output member 62 driven member a1 intervening part b1 annular part B1 bolt H1 bolt hole O1 rotating shaft

Claims (5)

A speed reduction device, comprising: a speed reduction mechanism, and an output member that outputs rotation reduced by the speed reduction mechanism, wherein the output member and the driven member are connected by a plurality of bolts,
An adhesive is applied to a connection surface between the output member and the driven member,
The relationship between the sum X [mm ³ ] of the product of the PCD radius of the plurality of bolts and the effective sectional area and the peak torque during acceleration Y [Nm] is as follows:
Y> 0.024 × X

Is a reduction gear.   The reduction gear transmission according to claim 1, wherein at least one of the connection surface of the output member and the connection surface of the driven member has a concave portion to which an adhesive is applied.   The reduction gear transmission according to claim 2, wherein the recess is located radially inward of an inscribed circle of the plurality of bolt holes through which the plurality of bolts are passed.   4. The reduction gear transmission according to claim 2, wherein the recess is located between one of the plurality of bolt holes corresponding to the plurality of bolts and another of the plurality of bolt holes. 5.   The reduction gear according to any one of claims 2 to 4, wherein the depth of the recess is not less than 20 µm and not more than 30 µm.

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