JP2006226533A - Connecting structure for reduction gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a connecting structure for a reduction gear device, adaptable to the condition of another machine and to the condition of a reduction gear ratio of itself. <P>SOLUTION: The structure of connecting a planetary reduction gear 104 to a perpendicular reduction gear 105 is provided for the reduction gear device 103 which consists of the planetary reduction gear 104 having a sun gear 106, a planetary gear 108, an internal gear 110, and a carrier 112, and the perpendicular reduction gear 105 having a transmission shaft 46 connected to the carrier 112, a bevel pinion (an input side bevel gear) 116 coaxially provided on the transmission shaft 46, and a bevel gear (an output side bevel gear) 118 meshing therewith. A cylindrical joint flange 44 is laid between the planetary reduction gear 108 and the perpendicular reduction gear 105 for connecting an output side mounting face 50 of the planetary reduction gear 108 to an input side mounting face 124B of the perpendicular reduction gear via input and output side connection faces 44A, 44B formed at both ends of itself. The transmission shaft 46 axially provided on the bevel pinion 116 and the carrier connected to the transmission shaft 46 are rotatably arranged on the inner periphery of the joint flange 44. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a reduction gear connecting structure suitable for, for example, preparing a plurality of various geared motors as a product group based on a technically rational idea.

  The present inventor has proposed a geared motor 1 as shown in FIG. 6 in the process of obtaining the idea of the present invention (see, for example, Patent Document 1). The geared motor 1 includes various motors 2 (not shown) and a reduction gear 3. The speed reducer 3 is prepared as a series of various specifications. The motor 2 is selected from the plurality of types of speed reducers 3 in consideration of the capacity of the motor 2 and the mating dimensions of the counterpart machine. It comes to be combined with.

  The speed reducer 3 includes a planetary speed reducer 4 having a simple planetary gear structure and a quadrature speed reducer 5 having a one-stage orthogonal transmission structure connected to the output side of the planetary speed reducer 4. The planetary reduction gear 4 includes a sun gear 6 that is coaxially connected to the motor shaft 2A of the motor 2, a planet gear 8 that is arranged around the sun gear 6 and is externally meshed with the sun gear 6. An internal gear 10 that is arranged concentrically with the motor shaft 2A and in mesh with the planetary gear 8 and a carrier 12 that takes out only the revolution component of the planetary gear 8 and outputs it to the orthogonal reduction gear 5 side are provided.

  The internal gear 10 is constituted by a cylindrical member and also serves as a casing of the planetary speed reducer 4. Therefore, a motor mounting surface 10A for mating with the flange 2B of the motor 2 is formed on the input side end surface of the internal gear 10, and an output side mounting surface for mating with the orthogonal reduction gear 5 is formed on the other end surface. 10B is formed.

  Each of the planetary gears 8 is formed with an axial carrier hole 14 at the center thereof. A carrier pin 12A of the carrier 12 is inserted into the carrier hole 14 via a pin roller 12B, and only the revolving motion of the planetary gear 8 is taken out.

  In the planetary reduction gear 4, when the sun gear 6 rotates together with the motor shaft 2 </ b> A, the planetary gear 8 engaged with the planetary gear 4 attempts to revolve around the sun gear 6. However, since this planetary gear 8 is in mesh with the internal gear 10, “free” revolution is restricted, resulting in a revolution motion accompanied by a rotation motion. That is, the revolution movement is delayed by the amount of rotation of the planetary gear 8 itself, and the rotation of the carrier 12 that takes out this revolution movement is decelerated from the rotation speed of the motor shaft 2A.

  In the planetary speed reducer 4 exemplified here, the structure in which the carrier 12 outputs to the orthogonal speed reducer 5 side is shown. However, in actuality, the structure in which the rotational power is taken out by the internal gear 10 or the sun gear 6 is used. It is also possible to adopt a structure for taking out power.

  The one-stage orthogonal reduction gear 5 is connected to a bevel pinion 16 integrally connected to the carrier 12, a bevel gear 18 meshing with the bevel pinion 16, and coaxially and integrally connected to the bevel gear 18. A hollow type (hollow shaft type) output shaft 20 and a gear box 24 that rotatably supports the output shaft 20 via two bearings 22 and accommodates the bevel pinion 16 and the bevel gear 18 therein. .

  On the input side of the gear box 24, a mounting flange portion 26 is formed integrally with the cylindrical protrusion and the tip is spread outward, and the internal gear 10 ( The output side mounting surface 10B) is connected. A transmission shaft 16A is connected to the bevel pinion 16, and the transmission shaft 16A is splined to a shaft hole 12C formed in the carrier 12. Further, the transmission shaft 16A is rotatably supported by a bearing 28 installed on the inner peripheral side of the mounting flange portion 26, and the carrier 12 is similarly installed on the inner peripheral side of the mounting flange portion 26. The bearing 30 is rotatably supported. Because of these structures, the carrier 12 and the bevel pinion 16 rotate together, so that the rotation of the carrier 12 is transmitted to the bevel pinion 16.

  According to the geared motor 1, the rotational power of the motor 2 is decelerated by the planetary speed reducer 4, and the power after the deceleration is input to the one-stage orthogonal speed reducer 5. The power is decelerated by the bevel pinion 16 and the bevel gear 18, the direction of the rotation shaft is changed so as to be orthogonal to the motor shaft 2 </ b> A, and output from the output shaft 20.

JP 2000-110895 A

  The orthogonal speed reducer 5 having the orthogonal transmission structure has a characteristic that the “power transmission capability” is relatively low because the pair of bevel gears are each subjected to a reaction force in the thrust direction and are separated from each other. Accordingly, the rigidity of the gear box 24 and the bearing 22 is set to be slightly higher than the predetermined frame number P of the reduction gear 3 in order to resist the reaction force in the thrust direction. On the other hand, the planetary speed reducer 4 transmits power while a plurality of planetary gears 8 are simultaneously meshed with each other, so that a high power transmission capability is secured in terms of structure. That is, in all the frame numbers P in the plurality of reduction gears 3 prepared as a series, a combination in which the orthogonal reduction gear 5 is slightly larger and the planetary reduction gear 4 is slightly smaller is employed.

  However, for example, when a torque limiter is installed in the reduction gear 3 so that rotational power exceeding a predetermined torque is not transmitted (guaranteed), the rigidity of the orthogonal reduction gear 5 is not necessarily “increased” as described above. In other words, conventionally, the manufacturing cost and the transmission efficiency are unnecessarily increased.

  On the other hand, for example, when a braking mechanism (brake) is installed on the input side of the reduction gear 3 and the rotation of the counterpart machine needs to be stopped reliably (when receiving a strong inertial reaction force), or a large load is applied. However, when it is necessary to maintain the stopped state, the rigidity of the orthogonal reduction gear 5 corresponding to the conventional frame number P is not always sufficient.

  This situation is peculiar to the structure in which the reaction torque of the counterpart machine is directly received by the bevel gear 18 and the bevel pinion 16, and is considered to be a problem that occurs because of this structure. .

  The present invention has been made in view of the above-mentioned problems, and flexibly responds to specifications (requirements) such as a counterpart machine and a rotational power source, and reduces the size of the entire apparatus while maintaining the power transmission efficiency in an optimum state. It aims at obtaining the connection structure of the reduction device which was aimed.

  The present invention includes a sun gear that rotates integrally with an input shaft, a planetary gear that is disposed around the sun gear and externally meshes with the sun gear, and that is fixed and internally meshes with the planetary gear. A planetary speed reducer having a simple planetary gear structure including an internal gear and a carrier for taking out the revolution component of the planetary gear, a transmission shaft connected to the carrier of the planetary speed reducer and receiving rotational power, and the transmission shaft Of the planetary speed reducer and the orthogonal speed reducer in a speed reducer comprising: an input side bevel gear provided coaxially to the input side bevel gear; In the connecting structure, a cylindrical joint flange capable of connecting the output side mounting surface of the planetary reduction gear and the input side mounting surface of the orthogonal reduction gear by the input and output side connecting surfaces formed at both ends of the connecting structure. The planetary reducer and The transmission shaft provided coaxially with the entry side bevel gear and the carrier connected to the transmission shaft are rotatably disposed on the inner periphery of the joint flange and interposed between the orthogonal reduction gears. As a result, the above object is achieved.

  Conventionally, the orthogonal speed reducer and the speed reducer are connected by “one (one) mating surface (connecting surface)”. This is considered to be a condition that the transmission capacity has to be determined with the speed reducer as a whole. This is because the transmission capacity of the reduction gear is comprehensively determined from the thickness and size of the gearbox, but it is often reflected in the size of the mating surface (connection surface). is there.

  Therefore, in the present invention, a joint flange is interposed between the speed reducer and the orthogonal speed reducer so that they are connected by “two connecting surfaces”, and the orthogonal speed reducer is made “independent” with respect to the specific planetary speed reducer. Multiple types can be prepared, and a combination of these is possible.

  In this case, for example, if a joint flange is replaced (that is, if an appropriate joint flange is selected) for a specific planetary speed reducer (that is, a speed reducer having a specific output side mounting surface dimension), two or more. It becomes possible to easily combine orthogonal reducers (that is, orthogonal reducers having two or more different input side mounting surface dimensions).

  As a result, for example, when the planetary speed reducer or the orthogonal speed reducer is configured such that each mounting surface dimension corresponds (reflects) to the transmission capacity, for example, the following modes can be selected.

  (1) When using a torque limiter, etc., reduce the transmission capacity of the orthogonal reduction gear by one rank while maintaining the transmission capacity of the planetary reduction gear (that is, reduce the dimension of the input side mounting surface by one rank). Aspect

  (2) When a braking mechanism (brake) is adopted, the transmission capacity of the orthogonal speed reducer is increased by one rank while maintaining the transmission capacity of the planetary speed reducer (that is, the dimension of the input side mounting surface is increased by 1). (Raising the rank)

  (3) In the case where the mounting surface dimension on the counterpart machine side is “already determined”, an orthogonal reduction gear that matches the mounting surface dimension was selected unavoidably, but the planetary reduction gear side had the optimum transmission capacity (its output Freely select and combine without limiting the size of the side mounting surface

  (4) In the case where the mounting surface dimension on the rotational power source (eg, motor) side is “already determined”, a planetary reduction gear that matches the mounting surface size is unavoidably selected. To select and combine (without restrictions on the input side mounting surface dimensions)

  (5) A mode in which a planetary speed reducer having a predetermined capacity is combined with a one-stage speed reducer having an optimum transmission capacity in accordance with the “reduction ratio” selected by the planetary speed reducer.

  (6) The distribution of the reduction ratio of the single-stage reduction gear and the reduction ratio of the planetary reduction gear is optimized, and the transmission capacity that is optimal according to the transmission torque that is distributed as a result is restricted by the connection surface. Without selecting each independently

  Although not all of the above aspects, such a configuration makes it possible to respond more flexibly to the user's request, thereby increasing transmission efficiency and reducing manufacturing costs. This is obtained as a result of a thorough examination of the characteristics of the simple planetary gear structure and the orthogonal transmission structure, and the characteristics when combining them to constitute a reduction gear.

  FIG. 1 shows, for example, a schematic example of a series that can be configured using such a reduction gear connecting structure. As a result of the conventional connecting structure with one connecting surface, the output side mounting surface dimensions S1, S2, S3... (Corresponding to the transmission capacities Y1, Y2, Y3. Orthogonal speed reducers (corresponding to transmission capacities X1, X2, X3...) Having input side mounting surface dimensions T1, T2, T3. It is considered that only A1, A2, A3,... Located on the diagonal line are prepared as components of the series. If the present invention is adopted, for example, A1 and B1 that can be combined with the planetary reducer S1 can be combined with the orthogonal reducers T1 and T2, and the orthogonal reducers T1, T2, and T3 can be combined with the planetary reducer S2. A series of reduction gears having C1, A2, B2, etc. as constituent elements can be obtained, and the above-mentioned merits can be obtained.

  Also, in exactly the same manner, for example, A1 and C1 that can be combined with the planetary reduction gears S1 and S2 with respect to the orthogonal reduction gear T1, and the planetary reduction gears S1, S2, and S3 can be combined with the orthogonal reduction gear T2. It is also possible to obtain a series of reduction gears having B1, A2, C2, etc. as constituent elements.

  It is preferable that the joint flange, the transmission shaft, and the carrier can be integrated and removed integrally with the remaining portion of the reduction gear.

  In this way, the orthogonal reducer side, the joint flange portion (including elements of both the orthogonal reducer and the planetary reducer), and the planetary reducer side are assembled independently, and the three bodies are finally assembled. Since the speed reducer can be constructed by assembling, manufacturing and assembly costs are suppressed and maintainability is improved. Further, the speed reducer can be disassembled via the joint flange even when the orthogonal speed reducer is connected to the counterpart machine side or the planetary speed reducer is connected to the power source. This is particularly suitable when constructing a series, and even if the orthogonal speed reducer is connected to the other machine, if the planetary speed reducer is replaced with another one (within the series) It becomes possible to change to a device.

  According to the present invention, on the basis of a technically rational basis, when configuring a reduction gear series that can flexibly respond to specifications of a counterpart machine, a rotational power source, etc., and can maintain transmission efficiency in an optimum state. Therefore, it is possible to obtain a speed reducer connecting structure suitable for the above.

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

  FIG. 2 shows a speed reducer 103 in which an example of a reduction gear device connection structure according to the present invention is employed. The speed reducer 103 includes a planetary speed reducer 104 having a transmission capacity Y and a simple planetary gear structure, and an orthogonal speed reducer 105 connected to the output side of the planetary speed reducer 104 and having a transmission capacity X. The orthogonal reduction device 105 is an orthogonal transmission structure using a pair of bevel gears including a bevel pinion 116 and a bevel gear 118, and converts rotational power into a right angle direction with a predetermined reduction ratio (about 1/3 here). Except for the configuration or operation specifically described below, it is substantially the same as the reduction gear 3 already shown in the conventional example, and therefore the same or similar members / parts are the same as the reduction gear 3 and the lower two digits. By attaching the same reference numerals, detailed description of the configuration and operation will be omitted.

  The planetary speed reducer 104 includes a sun gear 106 that is coaxially connected to the motor shaft (input shaft) 102A, and (four) planetary gears 108 that are arranged around the sun gear 106 and externally mesh with the sun gear 106. An internal gear 110 that is arranged concentrically with the motor shaft 102A and in mesh with the planetary gear 108, and a carrier 112 that extracts the revolution component of the planetary gear 108 are provided.

  A gear box 124 that accommodates the bevel gear 118 and the bevel pinion 116 and rotatably supports the output shaft 120 is formed with an input side mounting surface 124B having bolt holes 42 formed at predetermined intervals in the circumferential direction. Has been. An opening 40 is formed in the input side mounting surface 124B, and a part of a joint flange 44 described later is inserted therein. The bevel pinion 116 is coaxially connected (or formed) to one end of the transmission shaft 46 that is splined to the carrier 112. Here, the diameter of the circular locus in which the bolt hole 42 of the input side mounting surface 124B is formed is defined as T, and this is defined as the dimension T of the input side mounting surface in the present embodiment.

  On the output side end surface of the internal gear 110, an output side mounting surface 50 having bolt holes 48 formed at regular intervals in the circumferential direction is formed. The diameter of the circular orbit where the bolt hole 48 is formed is defined as S, and this S is defined as the dimension S of the output side mounting surface 50 in the present embodiment. The concept of the dimensions S and T of the mounting surface is not limited to the above.

  Next, the connection structure of the planetary reduction gear 104 and the one-stage orthogonal reduction gear 105 in the reduction gear 103 will be described.

  Between the planetary reduction gear 104 and the orthogonal reduction gear 105, a cylindrical joint flange 44 is disposed. The joint flange 44 has a so-called both-flange structure in which an inlet side connecting surface 44A and an outlet side connecting surface 44B are formed at both ends thereof. Therefore, the output side mounting surface 50 of the planetary reduction gear 104 is connected to the inlet side connection surface 44A of the joint flange 44 by the bolt, while the input side mounting surface 124B of the one-stage orthogonal reduction gear 105 is connected to the joint flange 44. It connects with the output side connection surface 44B with the volt | bolt.

  Further, a transmission shaft 46 to which the bevel pinion 116 is integrally connected via a bearing 128 is rotatably disposed on the inner periphery of the joint flange 44, and the carrier 112 is also rotated via the bearing 130. Arranged freely. More specifically, the carrier 112 is formed with a spline-shaped shaft hole 112 </ b> C and is splined to one end of the transmission shaft 46. Since the bevel pinion 116 is coaxially provided at the other end of the transmission shaft 46, the rotation of the carrier 112 is transmitted to the bevel pinion 116 via the transmission shaft 46 from the above configuration. Note that the arrangement of the bearings 128 and 130 is not limited to this case, and one bearing may support all (the transmission shaft 46 and the carrier 112). You may make it support with one bearing. In short, on the inner peripheral side of the joint flange 44, the carrier 112 and the transmission shaft 46 may be held rotatably in an integrated state. In this way, the joint flange 44, the transmission shaft 46, and the carrier 112 can be integrally incorporated into or removed from the remaining portion of the speed reducer 103.

  According to the reduction gear 103 described above, since the joint flange 44 is interposed between the planetary reduction gear 104 and the orthogonal reduction gear 105, the dimension S of the output side mounting surface 50 and the dimension of the input side mounting surface 124B. T can be changed independently. This is accomplished by replacing the joint flange 44 with another. That is, in the joint flange 44, the inlet side connecting surface 44A and the outlet side connecting surface 44B are formed so as to coincide with these dimensions S and T.

  In this reduction gear 103, the diameter K of the circular orbit in which the carrier pin 112A in the carrier 112 is arranged also varies in conjunction with the transmission capacity Y of the planetary reduction gear 104. That is, the dimension K is set so as to decrease as the dimension S of the output side mounting surface 50 decreases. On the other hand, the outer diameter D of the transmission shaft 46 is also interlocked with the transmission capacity X of the input side mounting surface 124B of the orthogonal reduction gear 105. That is, when the dimension T of the input side mounting surface 124B is decreased, the dimension D is also set to be decreased.

  Here, for the sake of convenience, a reduction gear series configured by preparing a plurality of reduction gears employing the above-described connection structure will be described. The speed reducer will be described based on the reference numerals of the speed reducer 103 shown in FIG.

  In this speed reducer series, a plurality of planetary speed reducers 104 are prepared so that their output side mounting surfaces 50 have different dimensions S (that is, S1 <S2 <S3...). A plurality of planetary reduction gear groups G and orthogonal reduction gears 105 are prepared and configured so that the dimension T of the input side mounting surface 124B thereof is different from each other (that is, T1 <T2 <T3...). And the joint flange 44 disposed so as to be interposed between the planetary reducer 104 and the orthogonal reducer 105 are the dimensions of the inlet side connecting surface 44A and the outlet side connecting surface 44B (that is, the above-mentioned And a plurality of joint flange groups F prepared and configured so that combinations of dimensions S and T) are different.

  Specifically, as shown in FIG. 3, a planetary reduction gear group G having dimensions S1, S2, S3, S4... And an orthogonal reduction gear group I having dimensions T1, T2, T3, T4. Thus, the matrix M is formed. Since each joint flange is prepared corresponding to each cell U (where the speed reducer 103 is prepared as a series) in the matrix M, the plurality of joint flanges are gathered to form a joint flange group F. Is configured. In other words, in this example, the number of joint flanges in the joint flange group F matches the number of reduction gears prepared by the reduction gear series.

  As a result of adopting the above configuration, this reduction gear series includes, for example, planetary reduction gears in specific reduction gears A1, A2, A3, and A4 (planetary reduction gears 104 whose output-side mounting surface dimensions are S1, S2, S3, and S4. ), By interposing a predetermined joint flange 44 selected from the joint flange group F, at least two of the orthogonal reduction gear group I have different input side mounting surface dimensions T. It is in a state where it is possible to combine orthogonal reduction gears (see below for details).

  That is, in the series of planetary reduction devices shown in FIG. 3, two orthogonal reduction devices 105 with dimensions T1 and T2 are combined with the planetary reduction device 104 with a specific dimension S1, and A1, A reduction gear 103 of B1 is configured. Further, for the planetary reduction gear 104 having a specific dimension S2, three orthogonal reduction gears 105 of T1, T2, and T3 selected are combined to form a reduction gear device 103 of C1, A2, and B2. . Further, for the planetary reduction gear 104 having a specific dimension S3, three orthogonal reduction gears having dimensions T2, T3, and T4 are combined to form a reduction gear device 103 having C2, A3, and B3. For the planetary reduction gear 104 having a specific dimension S4, a C3, A4 reduction gear 103 is configured by combining the orthogonal reduction gears 105 having the dimensions T3 and T4. This is because the predetermined joint flange 44 is prepared corresponding to each cell U as already described.

  Further, for example, a predetermined reduction flange 44 is interposed in the orthogonal reduction device (orthogonal reduction device having the input side mounting surface dimension T4) in the specific reduction device A4, so that the selection is made from the planetary reduction device group G. The three planetary decelerators 104 (in this case, the three planetary decelerators 104 having dimensions S3, S4, and S5 are selected) having different dimensions S on the three output side mounting surfaces 50 can be combined. Thus, the reduction gears 103 of B3, A4, and C4 are configured. In addition, when considering the orthogonal reduction gear T2 in the reduction gear A2, it can be said that it can be combined with the planetary reduction gears S1, S2, and S3.

  Previously, the reduction gear 103 in a state in which the planetary reduction gear 104 and the orthogonal reduction gear 105 were combined was regarded as an integral unit, and the “total” transmission capacity was changed stepwise, thereby forming a series. Therefore, if it is assumed to correspond to the matrix in FIG. 3, only the series of A1, A2, A3, A4. However, according to the reduction gear series according to the first embodiment, the reduction gears 103 of B1, B2, B3..., C1, C2, C3, C4. Therefore, it becomes possible to flexibly cope with the situation as shown below. This can be considered that the dimension S of the output side mounting surface 50 and the dimension T of the input side mounting surface 124B generally reflect the transmission capacities Y and X of the planetary reduction gear 104 and the orthogonal reduction gear 105. Because.

  (1) For example, when the reduction gear A2 is normally applied, a torque limiter is installed in the planetary reduction gear 104 so that the transmission torque input to the one-stage orthogonal reduction gear 105 is always below a predetermined value. Is ensured, the input side mounting surface dimension T2 of the one-stage orthogonal reduction gear 105 is reduced to T1, and the C1 reduction gear 103 in which the transmission capacity X of the orthogonal reduction gear is set to be small is used. Like

  (2) Normally, the reduction gear A2 is adopted, but since the braking mechanism (brake) is adopted on the power source side, it is necessary to securely hold the stop state of the counterpart machine, and the one-stage orthogonal reduction gear 105 A mode in which the B2 reduction device in which the transmission capacity X of the orthogonal reduction gear is set large is adopted by increasing the dimension T2 of the cylinder to T3.

  (3) The mounting surface size on the counterpart machine side has already been determined, and the only one-stage orthogonal reduction gear 105 that can cope with this is T3, and if it is conventional, the reduction gear A3 must be selected. For the reason that the transmission capacity Y on the 104 side is unnecessarily large, a mode in which S2 is lowered by one rank and the B2 speed reduction device 103 in which the transmission capacity Y is set small is selected as S2.

  (4) Since the capacity of the power generation source (motor) is relatively large, in order to employ the planetary reduction gear 104 having the dimension S2, the reduction gear A2 must be selected in the prior art. Since the transmission capacity X of the one-stage orthogonal reduction gear 105 is relatively large because the reduction ratio is set low, the dimension T2 is lowered by one rank to T1, and the reduction gear of C1 in which the transmission capacity X is set small. A mode in which 103 is adopted

  The various aspects described above are only examples, but by configuring the series in this way, it is possible to respond more flexibly to the user's request, and as a result, it is possible to improve transmission efficiency. Further, in the process of devising the present invention, the (total) transmission capacity is set at relatively large intervals such as A1, A2, A3..., But according to the present speed reducer series, A1, C1, (Comprehensive) transmission capacity can be set at fine intervals in the order of A2, C2, A3, C3, etc., and it becomes possible to respond accurately (in an optimal state) to the user's transmission capacity requirements. . Moreover, except that the joint flange 144 according to the present embodiment must be selected by each reduction gear, other parts (for example, a simple planetary gear structure and an orthogonal transmission structure) are used as they are in the process of being devised. -Since it can be shared, it is possible to construct a series very reasonably.

  Next, another reduction gear series will be described. Since the configuration of the speed reducer is the same as that of the previous example, the description will be made according to the reference numerals of the speed reducer 103 shown in FIG.

  As shown in FIG. 4, this reduction gear series includes a planetary reduction gear group G including three planetary reduction gears 104 having a dimension S of S1, S2, and S3, and a dimension T of T1, T2, and T3. An orthogonal reduction gear group I including two orthogonal reduction gears 105.

  For the planetary reduction gear 104 having the dimension S2 corresponding to the specific reduction gear A2 constituting this series, there are three orthogonal reduction devices having the three dimensions (T1, T2, T3) selected from the orthogonal reduction gear group I. As a result, the three reduction gears 103 of B1, A2, and C2 are configured as a series.

  In addition, three planetary gears selected from the planetary gear group G (with dimensions S1, S2, and S3) are selected for the orthogonal speed reducer 105 having the dimension T2 corresponding to the specific reduction gear C1 constituting the series. A reduction gear 104 is combined, and thereby, three reduction gears 103 of C1, A2, and B2 are configured as a series. A predetermined joint flange 44 is prepared for each of the speed reducers A2, B1, B2, C1, and C2 prepared in the speed reducer series, and a joint flange group F is configured by these members as a whole.

  According to this series of speed reducers, the speed reducer 103 of A2 is adopted in a general situation. However, considering the structure of the mounting surface on the counterpart machine side, the speed reduction ratio of the planetary speed reducer 104, etc., as appropriate B1 , B2, C1, and C2 can be shifted. That is, four kinds of variations are further added according to the situation (request), and it can respond flexibly.

  In the case of configuring the speed reducer series as described above, the joint flange 44 must be prepared corresponding to each planetary speed reducer 103. Therefore, as shown in FIG. 2, if the carrier 112 and the transmission shaft 46 accommodated in the joint flange 44 are prepared in correspondence with each other, the number of parts (inventory) that must be prepared is reduced. Because it becomes enormous, it is irrational. Therefore, the number of parts can be greatly reduced by the following means.

  FIG. 5 shows a combination of the carrier 112, the transmission shaft 46, and the bevel pinion 116 corresponding to the speed reducer series of FIG. An increase in the size S of the planetary speed reducer 104 in the speed reduction device 3 means that the transmission capacity Y of the planetary speed reducer 104 is increased, and accordingly, the size K of the carrier 112 is also K1 <K2 <K3. It must be increased to increase rigidity.

  On the other hand, when the dimension T of the orthogonal reduction gear 105 is gradually increased such that T1 <T2 <T3, this means that the transmission capacity X is also gradually increased. The external dimension D of 46 must also be increased to D1 <D2 <D3. In order to realize such a combination, the carrier 112 and the transmission shaft 46 are integrally manufactured (the same number as the joint flange) and each is prepared. .

  About this, the "material" of the carrier 112 and the transmission shaft 46 can be made as common as possible by appropriately processing only the carrier hole 112C formed in the carrier 112.

  That is, first, considering the reduction gears 3 corresponding to B1, A2, and C2 in the series, three orthogonal reduction gears (orthogonal reduction gears having a dimension T of T1, T2, and T3) 105 in the orthogonal reduction gear group I 105 Corresponding to the three types of transmission shafts 46 of the outer diameters D1, D2, and D3, respectively, the carrier 112 included in the planetary reduction device 104 having the dimension S2 in the specific reduction gear A2 (the material and the dimension K2 are made common). A plurality of shaft holes 112C may be prepared so that the inner diameters of the shaft holes 112C are different from each other (that is, coincident with D1, D2, and D3) so that the carrier 112 and each transmission shaft 46 can be connected.

  Next, considering the reduction gears 103 of C1, A2 and B2 in the series, the planetary reduction gears correspond to the outer diameter D2 of the transmission shaft 46 of the orthogonal reduction gear 105 having the dimension T2 in the specific reduction gear device A2. A common shaft hole 112 </ b> C corresponding to the outer diameter D <b> 2 of the transmission shaft 46 is used for the carriers 112 having different sizes such that the sizes of the two planetary speed reducers 104 having the dimensions S <b> 1 and S <b> 3 in the group G are K <b> 1 <K <b> 3. The carriers 112 having different sizes and the “common” transmission shaft 46 can be connected to each other. In this way, even if a dimensional variation on the carrier 112 side occurs, the transmission shaft 46 can always use a common material.

  From the above, by “using the joint flange”, the sharing of parts or “materials” is achieved, and the series can be configured extremely rationally.

  The present invention can be applied to a speed reducer having a planetary gear speed reducer and an orthogonal speed reducer.

The matrix which shows typically the structure of the series of the speed reducer which can be constructed | assembled using the connection structure of the speed reducer which concerns on this invention Sectional drawing which shows the reduction gear which comprises the same reduction gear series Matrix showing the configuration of the reduction gear series Matrix showing the configuration of other reduction gear series Conceptual diagram showing the specifications of the carrier and transmission shaft when configuring the reduction gear series Sectional drawing which shows the reduction gear device in the process of devising this invention

Explanation of symbols

DESCRIPTION OF SYMBOLS 103 ... Speed reducer 104 ... Planetary speed reducer 105 ... Orthogonal speed reducer 116 ... Bevel pinion 118 ... Bevel gear 44 ... Joint flange 44A ... Inlet side connecting surface 44B ... Outlet side connecting surface 112C ... Shaft hole 50 ... Output side attaching surface 124B ... Input Side mounting surface

Claims (2)

A sun gear that rotates integrally with the input shaft, a planetary gear that is arranged around the sun gear and externally meshes with the sun gear, an internal gear that is fixed and internally meshes with the planetary gear, And a planetary speed reducer having a simple planetary gear structure comprising a carrier for extracting the revolution component of the planetary gear,
A transmission shaft connected to the carrier of the planetary reduction gear to receive rotational power, an input side bevel gear provided coaxially with the transmission shaft, and an output side bevel gear meshing with the input side bevel gear An orthogonal reducer with an orthogonal transmission structure;
In the connecting structure of the planetary speed reducer and the orthogonal speed reducer in a speed reducer comprising:
A cylindrical joint flange capable of connecting the output side mounting surface of the planetary reduction gear and the input side mounting surface of the orthogonal reduction gear by means of an input side and an output side connection surface formed at both ends of the planetary speed reducer. The transmission shaft provided coaxially with the entry side bevel gear and the carrier connected to the transmission shaft are freely rotatable on the inner periphery of the joint flange. A reduction gear connecting structure characterized by being arranged in In claim 1,
The joint structure of the speed reducer, wherein the joint flange, the transmission shaft, and the carrier can be integrally incorporated into and removed from the remaining part of the speed reducer.

Images