JP4577626B2 - Belt drive - Google Patents

Description

  The present invention relates to a belt transmission device used as transmission means for various mechanical devices, and more particularly to a belt transmission device having a flat belt and two pulleys for stretching the flat belt.

In a belt transmission device using a flat belt, it is necessary to increase the accuracy of the parallelism of the axes between a plurality of pulleys that stretch the flat belt. If the parallelism between the pulleys is not sufficient, the belt will be offset to one side on the pulley belt suspension surface and protruded on both sides of the pulley belt suspension surface. A clean room where not only the side of the flat belt is in sliding contact with the side of the flat belt, but also the side of the flat belt is worn and the service life is significantly reduced. Cannot be used inside. Therefore, the use of barrel-shaped crown pulleys that can be expected to achieve self-aligning effects on the belt-suspended peripheral surface of the pulley and that do not require flanges for preventing belt detachment on both sides of the belt-suspended peripheral surface are also considered. However, in any case, it is fundamentally necessary to improve the accuracy of the axial parallelism between the pulleys. For this reason, a belt transmission device capable of adjusting the angle of the pulley is required. However, as this type of belt transmission device known in the art, as described in Patent Document 1, a fixed support shaft itself that supports the pulley is used. A pulley angle adjustment mechanism that adjusts the angle, a pulley angle adjustment mechanism that adjusts the angle of the rotation axis of the pulley with respect to a fixed support shaft supported at a fixed position, and the like are known.
JP 2004-84709 A

  As described above, in the conventional well-known pulley angle adjusting mechanism described in Patent Document 1, the angle of the fixed support shaft itself that supports the pulley is adjusted at the fixed support shaft intermediate position that is laterally separated from the pulley. By adjusting the angle of the fixed support shaft with one end of the fixed support shaft as a fulcrum by the rotation operation of the ring-shaped eccentric cam fitted on the fixed support shaft. As a result, the position of the pulley itself fluctuates greatly. As a result, the tension of the flat belt stretched between the pulley and other pulleys fluctuates greatly, and the belt tension needs to be adjusted again. Also, in the case of adjusting the angle of the rotation axis of the pulley itself with respect to the fixed support shaft, a ring shape interposed between one of the bearings supporting the two locations in the direction of the rotation axis of the pulley and the fixed support shaft. By rotating the eccentric cam, the angle of the rotation axis of the pulley is adjusted with the center position of the other bearing as a fulcrum. Although the amount of variation in position is small, the belt tension adjustment is the same. Therefore, when the belt transmission is operated after adjusting the belt tension to observe the degree of lateral movement of the belt and the angle of the pulley is adjusted according to the result, it is essential to adjust the belt tension each time. The workability is very bad.

An object of the present invention is to provide a belt transmission device that can solve the above-described conventional problems, and the belt transmission device according to claim 1 uses reference numerals of the embodiments described later. In addition, the belt transmission device 1 includes a flat belt 9 and two pulleys 6 and 8 that stretch the flat belt 9, and at least one of the pulleys 6 and 8 includes: It is supported by the bearing body 14 supported by the support members 13a and 13b via the angle adjusting means (30, 39, 48), and the swing center axis 50c when the angle of the bearing body 14 is adjusted is the bearing. The center point P of the belt tension peripheral surface 15 in the angle adjustment target pulley 8 supported by the body 14, that is, the center point P of the virtual cylinder formed by the belt tension peripheral surface 15 (the virtual cylinder Axis and virtual cylinder Rotation axis 6a of the central points of the thickness), the street and two pulleys 6 and 8, the belt transmission device configured so as to be orthogonal to the virtual plane S including the 8a, the bearing body 14, Both side plates 31a and 31b are provided so as to sandwich the pulley 8 pivotally supported by the bearing body 14, and the support members 13a and 13b are disposed so as to be adjacent to the outer sides of the both side plates 31a and 31b. The both side plates 31a and 31b of the bearing body 14 are pivotally supported on the support members 13a and 13b by the support shafts 50 concentric with the swing center axis 50c, and the both side plates of the bearing body 14 are supported. Angle adjusting means (30, 39, 48) are interposed between each of 31a, 31b and each of the supporting members 13a, 13b adjacent to the outside thereof. Plate 31a, which is 31b and each of said support members 13a adjacent to the outer side, the fastening means (50,51,52a, 52b) for fastening each and 13b the configuration provided with.

  The present invention having the above-described configuration is preferably implemented using a barrel-shaped crown pulley as each of the pulleys 6 and 8 as described in claim 2, and each pulley as described in claim 3. 6 and 8 are provided with belt detachment preventing flanges 16 on both sides of the belt hanging peripheral surface 15, and the flat belt 9 has a width such that both sides thereof do not contact the belt detachment preventing flanges 16. Is preferred.

  According to a fourth aspect of the present invention, there are two pulleys, a motor-driven transmission pulley 8 and a passive pulley 6 that drives a driven body (traveling wheel 3), and the bearing body 14 transmits the pulley. The pulley 8 is pivotally supported, and the motor 2 for driving the transmission pulley 8 is attached to the bearing body 14 so that the angle of the motor 2 and the transmission pulley 8 can be adjusted integrally.

According to a fifth aspect of the present invention, in the angle adjusting means (30, 39, 48), the support members 13a, 13b are rotatably fixed around an axis parallel to the swing center axis 50c. A rotating body 44 supported by the rotating body 44, an eccentric rotating cam 46 projecting at an eccentric position of the rotating body 44, and a passive hole 39 provided in the bearing body 14 so that the eccentric rotating cam 46 is fitted. The passive hole 39 may be formed as a long hole that is long in the direction connecting the pivot center axis 50 c and the axis of the rotating body 44.

Furthermore, as described in claim 6 , the support members 13a and 13b that support the bearing body 14 so that the angle thereof can be adjusted are fixedly movable and fixed in a belt tension direction connecting the pulleys 6 and 8. 12a, 12b can be supported. In this case, as described in claim 7 , the fixed machine frames 12a and 12b, the support members 13a and 13b adjusted in position relative to the fixed machine frames 12a and 12b, and the support members 13a and 13b Fastening means (50, 51, 52a, 52b) for fastening and fixing the three members of the bearing member 14 whose angles are adjusted to each other can be provided. Further, when adopting the configuration described in claim 6 or 7 , as described in claim 8 , the pulley is connected to the motor-driven transmission-side pulley 8 and the traveling wheel drive shaft 5 of the transport traveling body. Two of the attached passive pulleys 6 are provided, the transmission pulley 8 is disposed directly above the passive pulley 6, and the fixed machine frames 12a and 12b are bases for supporting the traveling wheel drive shaft 5. 10, the support members 13 a and 13 b can be supported by the support height adjustment bolts 40 so that the lower sides of the support members 13 a and 13 b can be adjusted in height.

  According to the belt transmission device according to the present invention having the above-described configuration, when the angle of the pulley is adjusted in order to increase the accuracy of the parallelism between the axes of the pulleys, the pulley is the center point of the belt hanging peripheral surface. That is, the belt is transmitted using the center point of the virtual cylinder formed by the belt-suspended peripheral surface (the center point of the virtual cylinder body and the center point of the thickness of the virtual cylinder body) as a fulcrum. Since it tilts along a virtual plane including the rotational axes of the two pulleys, there is no change in the distance between the center points of both pulleys, and in reality the angle to be adjusted is very small. The distance between the belt tension peripheral surfaces in contact with the belt hardly changes. Therefore, even after adjusting the belt tension, the belt transmission is operated to observe the degree of lateral movement of the belt relative to the pulley, and even if the angle of the pulley is adjusted according to the result, the belt tension varies as before. There is almost nothing to do, and the work of increasing the accuracy of the axial parallelism between the pulleys can be performed easily and efficiently.

Further, according to the configuration of the present invention, the angle adjustment of the pulley must be performed by operating the two angle adjusting means in the same manner, but the pulley whose angle is adjusted can be stably supported with sufficient strength. . Therefore, large torque transmission can be performed reliably and stably. In addition, in Claim 1, although it conditioned about the rocking | fluctuation center axis at the time of angle adjustment of the angle adjustment object pulley, the conditions regarding this rocking | fluctuation center axis do not have to be numerically perfect, If the conditions described in claim 1 are substantially satisfied to such an extent that the above-described action can be substantially expected, it is included in the technical scope of the present invention.

  In addition, the structure of this invention of Claim 1 is especially effective when each pulley is a barrel-shaped crown pulley which can anticipate the self-alignment effect with respect to a belt like Claim 2. Of course, it may be a combination of a toothed timing belt and a grooved barrel crown pulley, or a combination of a toothless flat belt and a grooveless barrel crown pulley. Furthermore, according to the configuration of the third aspect, even if some sudden accident occurs such that the belt largely moves on the belt-hanging peripheral surface of the pulley, the belt is prevented from coming off from the pulley. Sudden stopping of the driven body driven by the belt transmission device and secondary accidents due to the detached belt can be prevented in advance. Of course, during normal operation, the accuracy of the axial parallelism between the pulleys is increased, and sliding contact between the side of the bell and the flange on the pulley side does not occur.

  According to the fourth aspect of the present invention, since the passive side pulley for driving the driven body has the rotational axis at a fixed position, the passive side pulley and the driven body are interlocked using any transmission means. The transmission-side pulley that can be connected to the motor is angle-adjusted integrally with the motor, so that the transmission-side pulley can be directly attached to the output shaft of the motor. That is, the structure of the transmission system through the belt transmission device from the motor to the driven body is simplified and can be implemented at low cost.

The configuration of the angle adjusting means is not particularly limited. However, according to the configuration of claim 5 , the angle adjusting means can be easily configured between two adjacent plates, and the rotating operation of the rotating body and the operation after the operation are performed. Since the angle adjustment is completed with the fixing operation, an angle adjusting means excellent in operability can be obtained.

Further, according to the configuration of the sixth aspect , the belt tension adjusting means and the pulley angle adjusting means can be combined and integrated, so that the entire belt transmission device can be compared with the case where each is configured independently. Can be configured in a simple and compact manner. In this case, according to the configuration described in claim 7 , the number of parts can be further reduced to simplify the structure, and the operability can be improved. Moreover, according to the structure of Claim 8 , not only the whole driving | running | working wheel drive system of the conveyance traveling body using a belt transmission apparatus can be comprised compactly, but the operation of belt tension adjustment and pulley angle adjustment is also easy. Thus, by combining the configuration described in claim 2 with this configuration, it is possible to configure an optimum transport facility for use in a clean room.

  Specific embodiments of the present invention will be described below with reference to the accompanying drawings. In FIGS. 1 to 3, 1 is a means for transmitting the rotational force of a motor 2 with a speed reducer to a traveling wheel 3 of a transport traveling body. A belt transmission device of the present invention that is used, and includes a passive pulley 6 fixed to a driving rotating shaft 5 of a traveling wheel 3 that rolls on a traveling guide rail 4 laid on a floor surface, etc., and a deceleration It comprises a transmission-side pulley 8 fixed to the output shaft 7 of the motor-equipped motor 2 and a flat belt 9 stretched between the pulleys 6 and 8.

  Reference numeral 10 denotes a base provided on the traveling body for conveyance, and a driving rotary shaft 5 of the traveling wheel 3 is supported by a bearing unit 11 attached to the base 10. 12a and 12b are a pair of left and right fixed machine frames installed on the base 10, and the bearing body 14 is interposed between the pair of left and right fixed machine frames 12a and 12b via a pair of left and right support members 13a and 13b. The motor 2 with a speed reducer is attached to the bearing body 14 so that the output shaft 7 is substantially parallel to the drive shaft 3 of the traveling wheel 3.

  As shown in FIG. 2B, the passive pulley 6 and the transmission pulley 8 in this embodiment use a barrel crown pulley having a belt-hanging peripheral surface 15 inflated into a barrel shape. A toothed timing belt is used as the flat belt 9, and the passive pulley 6 and the transmission pulley 8 are provided with grooves in which the toothed portions of the toothed timing belt are fitted to the belt tension peripheral surface 15. A timing pulley can be used. Further, the passive pulley 6 and the transmission pulley 8 can be provided with hooks 16 for preventing belt detachment on both the left and right sides of the belt tension peripheral surface 15. Of course, the belt tension peripheral surface 15 is sufficiently wider than the width of the flat belt 9, and the width of the belt tension peripheral surface 15 is slightly increased from the state in which the flat belt 9 is automatically centered on the center of the belt tension peripheral surface 15. Even if it laterally moves in the direction, the side of the flat belt 9 is configured not to be in sliding contact with the flange portion 16.

  4 to FIG. 11, the fixed machine frames 12a and 12b have a bilaterally symmetric structure, and a vertical plate 18 is fixedly erected on a horizontal mounting plate 17. Thus, the horizontal mounting plate 17 is inserted into the screw holes 21 on the substrate 19 side through the mounting holes 20 provided in the horizontal mounting plate 17 on the pair of left and right substrates 19 fixed on the base 10. Each of them is attached by two bolts 22 to be screwed together. The vertical plate 18 is provided with a pair of upper and lower shallow concave grooves 23 on the inner side surface thereof, and a notch hole 24 is formed in the central region of the lower side, and further in the vicinity of the four corners. Long holes 25a to 25f that are long in the vertical direction are provided at a total of six locations, two near the center of the position and height.

  The support members 13a and 13b are made of a rectangular plate material, and are fitted to a pair of upper and lower concave groove portions 23 provided on the vertical plate 18 of the stationary machine frames 12a and 12b on the outer side surfaces of the support members 13a and 13b. A pair of upper and lower rectangular projections 26 are integrally projected. The rectangular protrusions 26 are of a height that does not prevent the support members 13 a and 13 b from coming into contact with the inner surface of the vertical plate 18, and the support members 13 a and 13 b are rectangular protrusions in the groove 23. 26 is vertically overlapped with the vertical plate 18 of the stationary machine frames 12a and 12b with 26 vertical movements. In the support members 13a and 13b, when the support members 13a and 13b are in the vicinity of the lower end of the vertical movement range with respect to the vertical plate 18, they are near the upper ends of the pair of upper and lower long holes 25a and 25b near the front side of the vertical plate 18. A pair of upper and lower screw holes 27a and 27b that overlap with the position, a pair of upper and lower play holes 28a and 28b that overlap with positions near the upper ends of the pair of upper and lower long holes 25c and 25d near the rear side of the vertical plate 18, and A support shaft insertion hole 29 that overlaps with the position near the upper end of the central front long hole 25e, and a rotary body loose fitting hole 30 that is an angle adjusting means that overlaps with the position near the upper end of the long hole 25f on the central rear side of the vertical plate 18 are provided. Yes.

  As shown in FIGS. 2 to 4, the bearing body 14 includes a pair of left and right side plates 31 a and 31 b that overlap inside the pair of left and right support members 13 a and 13 b, and a pair of front and rear that connect and integrate the both side plates 31 a and 31 b. The vertical connection plates 32a and 32b and a pair of upper and lower horizontal connection plates 33a and 33b installed between the side plates 31a and 31b so as to block the upper and lower sides between the vertical connection plates 32a and 32b. As shown in FIG. 2A, the motor 2 with a speed reducer is in a state where a part of the motor 2 is housed between a pair of front and rear vertical connection plates 32a and 32b and is fixed to the rear vertical connection plate 32b by bolts 34. The output shaft 7 protrudes from the front vertical connecting plate 32a.

  Thus, the pair of left and right side plates 31a and 31b of the bearing body 14 having the above-described structure are provided with support members 13a and 13b at a central position in the vicinity of the front side protruding in a U shape as shown in FIGS. A support shaft insertion hole 37 is provided so as to overlap with the support shaft insertion hole 29, and a pair of upper and lower screws overlapping the play holes 28a, 28b of the support members 13a, 13b in a state where the both support shaft insertion holes 29, 37 overlap. Passive holes 39 that overlap the holes 38a, 38b and the rotary member loose fitting holes 30 of the support members 13a, 13b are provided near the rear sides of the side plates 31a, 31b. The passive hole 39 is fitted with an eccentric rotating cam of the angle adjusting means and is long in the horizontal front-rear direction.

  Further, as shown in FIGS. 1A, 9 and 10, the pair of left and right fixing machine frames 12a and 12b are provided with support height adjusting bolts 40 for supporting the lower sides of the support members 13a and 13b. ing. The support height adjusting bolt 40 is placed on the base 19 side substrate 19 via a bolt insertion hole 41 provided in the horizontal mounting plate 17 so as to be positioned in the notch hole portion 24 of the vertical plate 18. The vertical screw hole 42 is screwed into the vertical screw hole 42 to stand vertically, and is fixed on the horizontal mounting plate 17 by a lock nut 43 after height adjustment.

  Between the both side plates 31a and 31b of the bearing body 14 and the support members 13a and 13b overlapping the outside, angle adjusting means is interposed. The angle adjusting means includes a rotating body 44 that is loosely fitted into the rotating body loose fitting holes 30 of the support members 13a and 13b so as to allow only rotation, and is concentrically projected from the outer surface of the rotating body 44 and is fixed to the fixed machine frame 12a. , 12 b through the long hole 25 f of the vertical plate 18, and the passive hole 39 of the both side plates 31 a, 31 b of the bearing body 14 protruding from the inner surface eccentric position of the rotating body 44 in the front-rear direction A cam unit 48 comprising an eccentric rotary cam 46 that is loosely fitted only to the screw shaft and a nut 47 that is screwed to the screw shaft portion 45 is used. Note that, on the side surface of the front end of the screw shaft portion 45, a wrench engaging flat surface portion 45a for rotating the eccentric rotation cam 46 via the screw shaft portion 45 is formed.

  An assembly method and a usage method of the belt transmission device 1 having the above configuration will be described. The support members 13a and 13b and the fixed machine frame 12a are disposed outside the side plates 31a and 31b of the bearing body 14 to which the motor 2 with a speed reducer is attached by a bolt 34. , 12b. That is, as shown in FIG. 10, the support members 13a and 13b are fitted inside the vertical plates 18 of the fixing machine frames 12a and 12b, and the square protrusions 26 are fitted into the concave groove portions 23 so that they can be moved up and down. Then, fastening bolts 49a and 49b (see FIG. 1A) inserted from the outside into the pair of front upper and lower long holes 25a and 25b of the vertical plate 18 are screwed into the pair of front upper and lower screw holes 27a and 27b of the support members 13a and 13b. The support members 13a and 13b are temporarily fixed inside the vertical plate 18 of the fixing machine frames 12a and 12b. In this state, as shown in FIGS. 6 and 11, the cam unit 48 of the angle adjusting means is inserted into the elongated hole 25f of the vertical plate 18 of the fixing machine frames 12a and 12b outwardly from the inside as shown in FIGS. Thus, the rotating body 44 is fitted into the rotating body loose fitting holes 30 of the support members 13a and 13b from the inside, and the nut 47 is screwed onto the screw shaft portion 45 protruding outward from the long hole 25f of the vertical plate 18. By doing so, the fixing machine frames 12a and 12b and the support members 13a and 13b are temporarily fixed.

  Next, a pair of left and right members having the support members 13a and 13b and the cam unit 48 temporarily fixed inside as described above on the outside of the side plates 31a and 31b of the bearing body 14 to which the motor 2 with a speed reducer is attached with bolts 34. The fixing machine frames 12a and 12b are combined and integrated. That is, as shown in FIG. 6, the bearings are arranged so that the eccentric rotating cams 46 of the cam unit 48 projecting inwardly from the support members 13a, 13b fit into the passive holes 39 of the side plates 31a, 31b of the bearing body 14. The support members 13a and 13b are overlapped on the outside of the side plates 31a and 31b of the body 14, and as shown in FIG. 8, the support shaft insertion holes 37 of the side plates 31a and 31b and the support shaft insertion holes of the support members 13a and 13b. 29 and a long shaft 25 of the vertical plate 18 of the fixing machine frames 12a and 12b, a bolt-support shaft 50 is inserted from the inside of the both side plates 31a and 31b, and a long hole of the vertical plate 18 of the fixing machine frames 12a and 12b is inserted. The nut 51 is screwed into the tip screw shaft portion 50a of the support shaft 50 protruding from the shaft 25e, and the side plates 31a and 31b on the bearing body 14 side, the support members 13a, 13b, And the vertical plates 18 of the fixing machine frames 12a and 12b are temporarily fastened, and as shown in FIG. 6, a pair of upper and lower slots 25c and 25d on the rear side of the vertical plates 18 of the fixing machine frames 12a and 12b. The fastening bolts 52a and 52b are screwed into the pair of rear upper and lower screw holes 38a and 38b of the both side plates 31a and 31b of the bearing body 14 through a pair of upper and lower play holes 28a and 28b on the rear side of the support members 13a and 13b. After fastening, the three overlapping plates of the side plates 31a and 31b of the bearing body 14, the support members 13a and 13b, and the vertical plate 18 of the fixed machine frames 12a and 12b are temporarily fastened.

  As described above, in the state in which the support members 13a and 13b, the fixed machine frames 12a and 12b, and the cam unit 48 of the angle adjusting means are assembled on both sides of the bearing body 14 to which the motor 2 with a speed reducer is attached, the support member 13a. , 13b, a pair of left and right support shafts 50 that support the bearing body 14 are, as shown in FIGS. 1 and 2A, the rotational axis of the output shaft 7 of the motor 2 with a speed reducer, that is, the transmission side pulley 8 of the transmission side pulley 8. The rotating body 44 of the cam unit 48 is concentrically opposed to one swinging central axis 50c orthogonal to the rotational axis 8a.

  Thus, as shown in FIGS. 6 and 10, the horizontal mounting plates 17 of the pair of left and right solid machine frames 12a and 12b are placed on the substrate 19 on the base 10 side, and 2 respectively as described above. The bolts 22 are fixed. Thereafter, the fastening bolts 49a, 49b, 52a, 52b temporarily fastening the support members 13a, 13b and the bearing body 14 to the vertical plates 18 of the solid machine frames 12a, 12b, the fastening nuts 47 of the cam unit 48, and In the state where the support nuts 51 are loosened and the support members 13a and 13b are lifted and raised with respect to the vertical plate 18 of the solid machine frames 12a and 12b together with the bearing body 14, the support height adjusting bolt 40 is As described above, the support height (the height of the bolt head) is mounted on the horizontal mounting plate 17 of the pair of left and right solid machine frames 12a and 12b. In this state, the lifted bearing body 14 is lowered together with the support members 13a and 13b, and the lower sides of the support members 13a and 13b are received by the support height adjusting bolts 40.

  As a result of the above operation, the reduction gear motor 2 is installed at the minimum height on the base 10, and in this state, the deceleration projecting forward from the vertical connecting plate 32a on the front side of the bearing body 14 is achieved. A transmission side pulley 8 is attached to a fixed position of the output shaft 7 of the motor 2 with a machine. Since the mounting position of the transmission pulley 8 in the direction of the rotation axis is important at this time, as shown in FIG. 2A, the boss portion of the transmission pulley 8 fitted to the output shaft 7 is connected to the motor 2 with a speed reducer. By attaching the transmission side pulley 8 to the output shaft 7 in a state of contacting the side surface of the end portion via a spacer ring as required, the transmission side pulley 8 can be attached to a fixed position of the output shaft 7. It is desirable to configure.

  When the transmission-side pulley 8 is attached to the fixed position of the output shaft 7 in this way, as shown in FIGS. 1 and 2A, a pair of left and right which is the center of swinging of the bearing body 14 with respect to the support members 13a and 13b. The pivot center axis 50c of the support shaft 50 is the center point P of the belt-suspended peripheral surface 15 of the transmission pulley 8, that is, the center point P of the virtual cylinder formed by the belt-suspended peripheral surface 15 (the relevant point It is configured to be orthogonal to a virtual plane S passing through the axis of the virtual cylinder and the center point of the thickness of the virtual cylinder and including the rotation axes 6a and 8a of the two pulleys 6 and 8. ing.

  If the transmission-side pulley 8 is attached to the fixed position of the output shaft 7 of the motor 2 with a speed reducer as described above, the passive-side pulley 6 in which the rotational axis centers are located substantially parallel to each other directly below the transmission-side pulley 8. A flat belt 9 is wound between the two. Thereafter, with the fastening bolts 49a, 49b, 52a, 52b, the fastening nut 47 of the cam unit 48, and the spindle fastening nut 51 being loosened, the support height adjusting bolt 40 is unscrewed. The support member 13a, 13b supported by the support height adjusting bolt 40 and the bearing body 14 connected to the support member 13a, 13b via the support shaft 50 and the cam unit 48 are raised, The transmission-side pulley 8 that is supported by the bearing body 14 is raised in parallel to adjust the tension of the flat belt 9 that is stretched between the passive-side pulley 6. At this time, the relative movement in the vertical direction of the support members 13a and 13b and the bearing body 14 with respect to the vertical plate 18 of the solid machine frames 12a and 12b is within the long holes 25a to 25d of the vertical plate 18 of the solid machine frames 12a and 12b. Relative fastening movement of the fastening bolts 49a, 49b, 52a, 52b, and the shafts 50 and the screw shafts of the cam unit 48 in the long holes 25e, 25f of the vertical plates 18 of the solid machine frames 12a, 12b. 45 is allowed by relative movement in the vertical direction.

  When an appropriate tension is applied to the flat belt 9, the lock nut 43 is fastened to fix the support height adjusting bolt 40, and the fastening bolts 49a, 49b, 52a, 52b, and the cam unit 48 are fastened. The support member 13a, 13b and the bearing body 14 are fixed to the vertical plate 18 of the solid machine frames 12a, 12b by tightening the nut 47 and the support shaft fastening nut 51. At this time, as shown in FIG. 6, the cam unit 48 of the angle adjusting means has a shaft center of the eccentric rotation cam 46 at the same level as the shaft center of the rotating body 44 and supports the support members 13a and 13b. A bearing body 14 that is supported so as to be adjustable in the vertical direction around the shaft 50 is substantially at the center of the angle adjustment range. As shown in FIG. 2A, the rotational axis of the transmission pulley 8 and the passive side The rotation axis of the pulley 6 is basically in a substantially parallel state.

  Next, the motor 2 with a speed reducer is operated, and a test operation is performed in which the rotating shaft 5 for driving the traveling wheel 3 is driven via the belt transmission device 1. At this time, if the rotation axis 8a of the transmission pulley 8 and the rotation axis 6a of the passive pulley 6 are completely parallel and the relative positions of the pulleys 6 and 8 in the rotation axis direction are correct, the barrel shape By the self-aligning action of the crown pulley, the flat belt 9 basically rotates while being held at the center position in the width direction of the belt tension peripheral surface 15 of each pulley 6, 8. The side edges of the flat belt 9 are not in sliding contact with the belt detachment preventing flange portions 6 and 8.

  If the rotational axes 6a and 8a of the pulleys 6 and 8 are not parallel to each other and the rotational axes 6a and 8a of the pulleys 6 and 8 are viewed from the side (see FIG. 2), the passive pulley 6 When the rotation axis 8a of the transmission side pulley 8 is inclined in the vertical direction (the direction along the virtual plane S including the rotation axes 6a and 8a of the pulleys 6 and 8) with respect to the rotation axis 6a, the flat belt 9 is moved laterally so as to deviate from the center position in the width direction of the belt hanging peripheral surface 15 of each pulley 6, 8, and the cam unit 48 of the angle adjusting means is operated so as to eliminate this lateral movement. That is, the fastening bolts 52a and 52b fastening the bearing body 14 to the vertical plate 18 of the solid machine frames 12a and 12b via the support members 13a and 13b, the fastening nut 47 of the cam unit 48, and the spindle fastening nut. 51 is loosened, and the screw shaft portion 45 of the cam unit 48 is rotated in either the forward or reverse direction using the wrench engaging flat surface portion 45a, and the rotating body 44 (screw shaft portion 45) shown in FIG. The eccentric rotating cam 46 with respect to the rotational axis 44a is within the range from the lowest level L at which the axial center 46a is displaced to the lowest level to the highest level U at which the axial center 46a is displaced to the uppermost side. The rotary body 44 is moved up and down while revolving around a rotation axis 44a. Since the cam unit 48 is disposed on both the left and right sides of the bearing body 14, two spanners are used in which the screw shaft portions 45 of both cam units 48 are engaged with the respective flat surface portions 45a for engaging the spanner. At the same time, it is desirable to rotate the same direction.

  When the eccentric rotating cam 46 of the cam unit 48 is moved up and down while revolving as described above, the eccentric rotating cam 46 moves back and forth in the passive holes 39 of the side plates 31a and 31b of the bearing body 14 while moving up and down. Is transmitted to both side plates 31a and 31b of the bearing body 14, and the angle of the bearing body 14 is adjusted in the vertical direction around a pair of left and right concentric support shafts 50. As a result, the transmission-side pulley 8 pivotally supported by the bearing body 14 is adjusted in the vertical direction around the support shaft 50 together with the motor 2 with a speed reducer. As described above, the swing center axis 50c, that is, the swing center axis 50c of the support shaft 50 passes through the center point P of the belt tension peripheral surface 15 in the transmission pulley 8, and the two pulleys 6, 8 is perpendicular to the virtual plane S including the rotational axes 6a and 8a, so even if the transmission-side pulley 8 is angle-adjusted around the oscillation center axis 50c, the angle adjustment amount is actually Since there is a slight amount, there is substantially no change in the distance between the belt tension peripheral surfaces 15 with which the flat belts 9 of the pulleys 6 and 8 are in contact. Therefore, even if the angle of the rotational axis 8a of the transmission pulley 8 is adjusted as described above, the tension of the flat belt 9 stretched between the pulleys 6 and 8 is not affected, and the flat belt is not affected. The tension of 9 is kept at the initial tension adjusted beforehand.

  By adjusting the angle of the rotational axis 8a of the transmission-side pulley 8 as described above, the flat belt 9 is caused to rotate around the belt tension of the pulleys 6 and 8 by the self-aligning action of the original barrel-shaped crown pulley. When the surface 15 is held at the center position in the width direction, the loosened fastening bolts 52a and 52b, the fastening nut 47 of the cam unit 48, and the support fastening nut 51 are tightened, and the solid machine frame 12a is tightened. , 12b, the support plate 13a, 13b, and the side plates 31a, 31b of the bearing body 14 may be fastened together to fix the bearing body 14 to the base 10 completely.

  When the angle of the transmission pulley 8 is adjusted, that is, when the angle of the bearing body 14 is adjusted, the pair of upper and lower fastening bolts 52a and 52b of the both side plates 31a and 31b of the bearing body 14 are connected to the both side plates 31a and 31b. And the vertical holes of the support holes 13a and 13b through which the fastening bolts 52a and 52b pass and the vertical plates of the solid machine frames 12a and 12b. The 18 long holes 25c and 25d are formed with a large diameter or a wide width so as to allow the vertical movement of the fastening bolts 52a and 52b. Moreover, in the said embodiment, the transmission side pulley 8 is arrange | positioned just above the passive side pulley 6, and the fixed machine frame 12a, 12b was standingly installed on the base 10 which supports the said driving | running | working wheel drive shaft 5. However, as shown in FIG. 12, the transmission pulley 8 is disposed directly above the passive pulley 6, and the flat belt 9 is stretched in an oblique direction so that the overall height of the belt transmission device 1 is increased. You may comprise low.

1 shows an embodiment of a belt transmission device according to the present invention used in a drive system of a traveling wheel of a conveying traveling body. FIG. A is a side view of the belt transmission device, and FIG. B is a front view of the belt transmission device. FIG. 3A is a side view showing the main part of the belt transmission device in a longitudinal section, and FIG. 2B is an enlarged longitudinal sectional view showing a contact point between a pulley and a belt used. It is a top view of FIG. 1B. It is a disassembled side view which shows a bearing body, the one side supporting member which supports this, and a fixing machine frame. It is a decomposition | disassembly longitudinal cross-sectional front view in the XX line position of FIG. 4 which shows a bearing body, the one side supporting member which supports this, and a fixing machine frame. It is a vertical front view which shows the assembly state in the vertical position shown in FIG. It is a decomposition | disassembly longitudinal cross-sectional front view in the YY line position of FIG. 4 which shows a bearing body, the one side supporting member which supports this, and a fixing machine frame. It is a vertical front view which shows the assembly state in the vertical position shown in FIG. It is a decomposition | disassembly longitudinal cross-sectional front view in the ZZ line position of FIG. 4 which shows a bearing body, the one side supporting member which supports this, and a fixing machine frame. It is a vertical front view which shows the assembly state in the vertical position shown in FIG. It is the front view explaining the cam unit of an angle adjustment means, and a vertical side view. It is a side view which shows a modification.

Explanation of symbols

2 Motor with a reduction gear 3 Traveling wheel 5 Rotating shaft 6 for driving a traveling wheel Passive pulley 7 Output shaft of a motor with a reduction gear 8 Transmission pulley 9 Flat belt 10 Base 11 Bearing units 12a and 12b Fixed machine frames 13a and 13b Support Member 14 Bearing body 15 Pulling belt peripheral surface 16 Pulley belt detachment preventing flange 17 Fixed machine frame horizontal mounting plate 18 Fixed machine frame vertical plate 19 Substrate 23 Grooves 25a to 25f Long hole 26 Rectangular projection 27a, 27b, 38a, 38b, 42 Screw holes 28a, 28b Play holes 29, 37 Support shaft insertion holes 30 Rotating body free fitting holes 31a, 31b Bearing side plates 32a, 32b Bearing body vertical coupling plates 33a, 33b Bearings Body horizontal connecting plate 39 Passive hole 40 Support height adjusting bolt 44 Rotating body 45 Screw shaft portion 45a Uneven flat portion 46 for spanner engagement Rotating cams 47, 51 Nuts 48 Cam units 49a, 49b, 52a, 52b Fastening bolt 50 Support shaft 50c Swing center axis P of super-angle support P Center point S of belt hanging peripheral surface Virtual axis including rotation axes of both pulleys Plane

Claims (8)

A belt transmission device having a flat belt and two pulleys for stretching the flat belt, wherein at least one of the pulleys is mounted on a bearing member supported by a support member via an angle adjusting means. is supported, the swing center axis during angular adjustment of the bearing body, the on axis of the virtual cylinder is formed by a belt Kakehari Shumen in axially supported by angular adjustment target pulley to the bearing body In the belt transmission device configured to pass through the center point of the thickness of the virtual cylindrical body and to be orthogonal to a virtual plane including the rotational axis of the two pulleys , the bearing body includes a shaft support on the bearing body. Both side plates arranged so as to sandwich the pulley to be sandwiched, and the support member is disposed adjacent to the outside of each side plate, and each side plate of the bearing body is connected to the pivot center axis. The bearing member is pivotally supported by each of the support members, and an angle adjusting means is interposed between each side plate of the bearing body and each of the support members adjacent to the outside thereof, and the bearing body. A belt transmission device provided with fastening means for fastening each of the both side plates and each of the supporting members adjacent to the outside thereof .   The belt transmission according to claim 1, wherein each of the pulleys is a barrel crown pulley.   Each of the pulleys includes a belt detachment preventing flange on both sides of the belt-hanging peripheral surface, and the flat belt has a width that does not contact the belt detachment preventing flange on both sides. The belt transmission device described in 1.   The pulley is composed of a motor-driven transmission-side pulley and a passive-side pulley that drives the driven body. The bearing body supports the transmission-side pulley, and the transmission-side pulley is attached to the bearing body. The belt transmission device according to any one of claims 1 to 3, wherein a motor to be driven is attached, and the angle of the motor and the transmission pulley is integrally adjusted. The angle adjusting means includes: a rotating body supported by the support member so as to be rotatable and fixed around an axis parallel to the pivot center axis; an eccentric rotating cam projecting at an eccentric position of the rotating body; The passive hole is formed in the bearing body so that the eccentric rotary cam is fitted, and the passive hole is long in the direction connecting the pivot center axis and the axis of the rotary body. The belt transmission device according to any one of claims 1 to 4, wherein the belt transmission device is formed in a hole . The said support member which supports the said bearing member so that angle adjustment is possible is supported by the fixing machine frame so that movement and fixing are possible in the belt tension direction which connects the said both pulleys. Belt transmission. Fastening means for fastening and fixing the fixed machine frame, the support member adjusted in position relative to the fixed machine frame, and the bearing member adjusted in angle relative to the support member is provided. The belt transmission device according to claim 6 . The pulley is composed of a motor-driven transmission-side pulley and a passive-side pulley attached to a traveling wheel drive shaft of the transport traveling body, and the transmission-side pulley is disposed directly above the passive-side pulley, The fixed machine frame is erected on a base that supports the traveling wheel drive shaft, and the lower side of the support member is supported by a support height adjustment bolt so that the height can be adjusted. Item 8. The belt transmission device according to Item 6 or 7 .

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