JP5115861B2 - Driving device for transport cart - Google Patents

Description

  The present invention relates to a drive device for a transport carriage that uses a screw shaft supported along a travel path of the transport carriage and a driven roller that is supported by the transport carriage so as to be engaged with the screw shaft.

  Conventionally, for example, Patent Document 1 and the like have been known as such conveying cart driving devices using a screw shaft. As described in Patent Document 1, when the feed pitch of the screw shaft is constant, two driven rollers can be provided on the conveying carriage side with an interval in the axial direction of the screw shaft. As a result, even if there is a space where the driven roller cannot engage with the intermediate position in the axial direction of the screw shaft due to the intermediate bearing between the screw shafts alone, either the front or rear driven roller is engaged with the screw shaft. The transport cart can be continuously driven at a constant speed. On the other hand, as described in Patent Document 1 above, when a plurality of sections with different feed pitches are provided on the screw shaft and the traveling speed of the transport carriage is changed for each section, the two front and rear driven rollers have different feeds. In order to avoid the inconvenience of engaging the screw shaft section of the pitch, the number of driven rollers on the transport carriage side must be one. In this case, one long screw shaft that does not require intermediate bearings between the screw shafts alone should be configured so that there is no space where the driven roller cannot be engaged with the intermediate position in the axial direction of the screw shaft. Don't be.

Japanese Patent Laid-Open No. 9-58463

  However, the length of the long screw shaft that can be supported only at both ends is limited in terms of strength and manufacturing. In other words, in practice, a plurality of screw shafts are concentrically connected by an intermediate bearing to form a long screw shaft, so there is a space for bearings between the screw shafts alone. Inevitable. Therefore, in the past, in order to transfer the driven roller between the screw shafts, it was considered that the screw shaft dedicated to the transfer and the driven roller were arranged side by side while being shifted in the lateral direction. Inevitably a significant cost increase.

  The present invention proposes a drive device using a screw shaft that can solve the above-described problems, and the drive device according to the first aspect of the present invention is a reference numeral of an embodiment described later. The screw shaft 3 driven by the motor 5 is supported along the travel path 2 of the transport carriage 1, and a driven roller that engages the screw shaft 3 is pivotally supported on the transport carriage 1. In the transporting carriage driving apparatus, the screw shaft 3 is configured by concentrically connecting a plurality of screw shafts 9A and 9B by an intermediate bearing 12A. The screw shaft on the opposite side of the intermediate bearing 12A from the side where the support portion 38 extends from the screw shaft 3 when viewed from the direction. A movable body 16 pivotally supported around a rotational axis 20a orthogonal to the axis of the movable body 16 is provided, and follower rollers 17A to 17C of the movable body 16 move the screw shaft 3 from the axial direction. When viewed, the intermediate bearing 12A is pivotally supported at at least three locations in the circumferential direction along the blade plate 14 of the screw shaft 3 in the circumferential region not including the support portion 38 extending from the screw shaft 3; When the three driven rollers 17A to 17C pass through the screw shafts 9A, 9B on both sides of the intermediate bearing 12A relatively sequentially, the two driven rollers are always engaged with the blade plate 14 of the screw shaft 3. It is configured.

  In the case of carrying out the driving device for the transport carriage according to the present invention, the three driven rollers 17A to 17C in the circumferential direction can each be constituted by a single roller loosely fitted between the blade plates 14 of the screw shaft 3. However, as described in claim 2, each of the three circumferentially driven rollers 17 </ b> A to 17 </ b> C is preferably composed of a pair of roller single bodies 21 that sandwich the blade plate 14 of the screw shaft 3. According to a third aspect of the present invention, the movable body 16 includes a biasing means (an embodiment) at an initial position where the three driven rollers 17A to 17C are axially supported along the blade plate 14 of the screw shaft 3. The torsion coil spring 32 is used, but it can be biased and held by another spring or an elastic material such as rubber.

  Further, as described in claim 4, the three driven rollers 17 </ b> A to 17 </ b> C include the position of the rotation axis 20 a of the movable body 16 and the rotation shaft when the screw shaft 3 is viewed from the axial direction. It can be arranged at a position approximately 90 degrees away from the position of the center 20a in both forward and reverse directions.

  Furthermore, as described in claim 5, the support portion 38 of the intermediate bearing 12 </ b> A is made of a plate material that is thinner than the width of the bearing body 37 in the axial direction and orthogonal to the axial direction of the screw shaft 3. The cylindrical shaft portions 13a and 13b of the screw shafts 9A and 9B can be covered with the bearing body 37 protruding in the axial direction of the screw shaft 3 from the support portion 38 of the intermediate bearing 12A. In this case, as described in claim 6, the screw shaft single body 9B, which is covered with the cylindrical end portion 13b on the bearing main body 37 of the intermediate bearing 12A, is located on at least one side of the intermediate bearing 12A. An end shaft portion 43 that protrudes from the bearing main body 37 and is rotatably attached to and disengaged in the axial direction with respect to the transmission shaft 42 that rotates integrally with the screw shaft unit 9A on the opposite side, and one end supported by the next bearing 12B. And a relay shaft portion 44 that connects the main body shaft portion 45 and the end shaft portion 43. The relay shaft portion 44 includes the main body shaft portion 45 and the end shaft. It can attach to the part 43 so that it can fit in and remove in the radial direction with respect to the axial direction of the screw shaft 3.

  In the case of adopting the configuration according to claim 6, as described in claim 7, the transmission shaft 42 has a rotation transmission end portion protruding from the end shaft portion 43 toward the relay shaft portion 44. 42g is provided, and the main shaft 45 is provided with a rotation transmission projecting shaft 50a concentrically projecting toward the relay shaft 44, and at both ends of the relay shaft 44, the transmission shaft 42 is provided. Rotation transmitting recesses 47a and 48a are provided in the rotation transmitting end portion 42g and the rotation transmitting protruding shaft portion 50a of the main body shaft portion 45 so as to be detachable in the radial direction. Rotation of the transmission shaft 42 is performed at both ends of the relay shaft portion 44 in which the recess portions 47a and 48a are fitted to the rotation transmission end portion 42g of the transmission shaft 42 and the rotation transmission protruding shaft portion 50a of the main body shaft portion 45. The transmission end portion 42g and the rotation transmission protruding shaft portion 50a of the main body shaft portion 45. It can be provided a fastener for fixing (bolts and nuts 51A～53b) to.

  In the drive device for the transport carriage of the present invention, a thrust in a predetermined direction acts on the transport cart via three driven rollers that engage with the blades of the screw shaft by rotating the screw shaft by motor drive. The transport carriage can be driven in a predetermined direction and at a predetermined speed. However, when the configuration of the present invention according to claim 1 is carried out, the conveyance carriage is arranged along the vane between the screw shafts on both sides of the intermediate bearing. Spacing in the circumferential direction is smaller than the spacing in the direction along the blades between the three driven rollers arranged in the circumferential direction along the blades of the screw shaft (the minimum spacing when the distances between the driven rollers are not equal). As long as it is configured in this way, two of the three driven rollers will not fit into the gap between the screw shafts on both sides of the intermediate bearing.

  That is, according to the configuration of the present invention described in claim 1, when the three driven rollers on the conveyance carriage side sequentially pass between the screw shafts on both sides of the intermediate bearing, the two driven rollers are always always The spacing between the screw shafts is so set as to straddle the blades of the upper screw shaft alone, the blades of the screw shaft on both sides of the gap, or to engage the blades of the lower screw shaft alone. Just by narrowing, when the driven roller relatively moves from the upper side to the lower side through the gap between the screw shafts on both sides of the intermediate bearing, there is always one driven in the gap between the screw shafts. Only the roller will enter, and the position of one driven roller that has entered the gap between this screw shaft alone will be the other two Held in position by the engagement of the driven roller and the vane can be engaged smoothly and securely engaged with the slats of the screw shaft single downstream side.

  Therefore, even if the screw shaft is composed of a plurality of screw shafts whose ends are supported by the intermediate bearings, the conveyance cart runs smoothly as it is when using one continuous long screw shaft. Can be made. In addition, there is no need to add a transfer-specific screw shaft and a transfer-dedicated driven roller that engages with the transfer-specific screw shaft in the transfer section between the screw shafts alone, and a significant cost reduction can be achieved. Further, since the movable body on which the three driven rollers are pivotally supported can swing around the rotation axis at an angle corresponding to the blade plate pitch, sections having different blade plate pitches can be used as screw shafts. It is also possible to change the traveling speed of the transport carriage for each section. Of course, in this case, between two sections with different blade pitches, the amount of change in the blade pitch with respect to the unit rotation angle is extremely set so that the blade pitch is completely changed by multiple rotations of the screw shaft. In addition to reducing the size, it is necessary to provide an appropriate play space between each driven roller and the blade.

  In addition, although the said three circumferential direction driven rollers can also be comprised from the one roller single-piece | unit fitted loosely between the blades of a screw shaft, respectively, according to the structure of Claim 2, it sandwiches a driven roller 2 Since the screw shaft can be configured by replacing one row of blade plates with one row of blade plates, the screw shaft itself can also be configured to be lightweight and inexpensive.

  The movable body that pivotally supports the three driven rollers basically has an angle (attitude) around the rotation axis determined by each driven roller engaging with a blade plate of the screw shaft. Although it is not necessary to urge and hold the movable body with a spring at a specific angle (posture), in particular, according to the configuration of claim 3, the driven roller rattles in the play space between each driven roller and the blade plate. This makes it possible to suppress the generation of abnormal noise and to facilitate the operation of introducing the transport carriage into the travel route with the screw shaft, compared to the case where the movable body (driven roller) is free around the rotation axis. It can be done.

  Further, according to the configuration described in claim 4, since the circumferential interval (angle) along the blade shaft of the screw shaft between the three driven rollers can be maximized, it is allowed between the screw shafts alone. It is not necessary to extremely reduce the thickness of the support portion of the intermediate bearing between the screw shafts alone, and the support strength by the intermediate bearing can be increased.

  The intermediate bearing structure between the single screw shafts is not particularly limited, but according to the configuration of claim 5, the thickness of the support portion extending from the gap between the single screw shafts in the axial direction of the screw shaft. As the bearing body for supporting the screw shafts on both sides simply by reducing the thickness, one having a necessary and sufficient length in the axial direction of the screw shaft can be adopted. In other words, a conventional general bearing body can be used as long as the bearing body has a diameter that can be loosely fitted into the cylindrical end of the screw shaft alone.

  When the configuration described in claim 5 is adopted, according to the configuration described in claim 6, when assembling the screw shaft alone, the end shaft portion is axially aligned with the transmission shaft protruding from the bearing body of the intermediate bearing. By fitting and attaching, the cylindrical end portion of the end shaft portion is put on the bearing main body, and then one end of the long main body shaft portion is projected concentrically from one end of the main body shaft portion. To the other bearing (intermediate bearing or end bearing) in the axial direction, etc., and finally, the relay shaft portion is placed between the end shaft portion and the other end of the main body shaft portion in the radial direction. Can be fitted and attached. Further, if necessary, the screw shaft alone can be removed from the bearings on both sides by a procedure reverse to this work procedure. In this way, at least one of the bearings that support both ends of the screw shaft is integral with the screw shaft alone, although it is necessary to cover at least one cylindrical end portion in the axial direction with respect to the bearing body of the intermediate bearing. Compared with the case where it is necessary to assemble and remove the screw shaft, the assembly and removal of the single screw shaft can be performed easily and easily.

  Furthermore, when adopting the configuration according to claim 6, according to the configuration according to claim 7, one end of the relay shaft portion is supported by the intermediate bearing and directly connected to the transmission shaft that supports the end shaft portion. Since it can be supported, the strength of the assembled screw shaft can be increased compared to the case where one end of the relay shaft portion is connected to the free end portion of the end shaft portion supported by the transmission shaft. The operation of connecting the relay shaft portion between the end shaft portion and the main body shaft portion so that the blades are continuous with each other in phase can be performed easily and easily. In addition, it is easy to increase the connection strength and transmission torque compared to the structure in which the end portions of the cylindrical body to which the blades of the end shaft portion, the relay shaft portion, and the main body shaft portion are fixed are connected to each other. .

FIG. 1 is a plan view showing a screw shaft of a transport carriage travel route. FIG. 2 is a longitudinal front view showing the driving device of the transport carriage. FIG. 3 is a plan view showing a main part of the transport carriage. FIG. 4A is a longitudinal front view showing the screw shaft and the driven roller unit, and FIG. 4B is a plan view of the screw shaft connecting portion. FIG. 5 is a longitudinal side view of the driven roller unit. FIG. 6 is a cross-sectional plan view of the driven roller unit. FIG. 7 is a longitudinal side view of the screw shaft connecting portion. FIG. 8 is a plan view of the screw shaft connecting portion. FIG. 9 is a cross-sectional plan view for explaining a method of assembling and disassembling the screw shaft connecting portion. FIG. 10 is a longitudinal front view showing a connecting structure of one end of the relay shaft of the screw shaft connecting portion. FIG. 11 is a longitudinal front view showing a connecting structure of the other end of the relay shaft of the screw shaft connecting portion.

  As shown in FIG. 1 and FIG. 2, a screw shaft 3 is disposed in a linear travel path 2 of the transport carriage 1 at a position below the transport carriage 1 and on one side of the left and right. It is supported in parallel. The screw shaft 3 is linked to a motor 5 at one end via a chain transmission means 4 and can be driven to rotate in either the forward or reverse direction by the motor 5. 2, in a layout in which an outbound route and a return route are arranged side by side and a traverser that laterally feeds the transport carriage 1 is provided between the ends of both routes, each travel route 2 (the outbound route and The screw shaft 3 supported by the return path) is driven to rotate in only one direction.

  A pair of left and right guide rails 6 are installed on the travel route 2 of the transport carriage 1 via a base arranged at appropriate intervals, and the transport carriage 1 is fitted to the pair of left and right guide rails 6. Two pairs of left and right front and rear support wheels 7 supported by left and right horizontal support shafts, and two pairs of left and right front and rear shafts supported by vertical support shafts so as to be adjacent to the inner sides of the pair of left and right guide rails 6 An anti-sway roller 8 is provided and supported so as to be able to travel along the travel route 2. Although the workpiece support structure of the transport carriage 1 is not shown, an appropriate one is adopted depending on the workpiece to be handled. Of course, the support structure of the transport carriage 1 is not limited to the illustrated one.

  The screw shaft 3 shown in FIG. 1 is configured by connecting four screw shafts 9 </ b> A to 9 </ b> D, but this number can be appropriately changed according to the total length of the travel path 2. The free ends of the screw shafts 9A and 9D at both ends are connected to the screw shafts 9A and 9D via support shafts 10a and 10b that are fixedly projected from the free ends of the screw shafts 9A and 9D. Outside the free end, it is supported by end bearings 11A and 11B, and the support shaft 10a of the screw shaft unit 9A is linked to the motor 5 through the chain transmission means 4. The adjacent ends of the screw shafts 9A and 9B, the adjacent ends of the screw shafts 9B and 9C, and the adjacent ends of the screw shafts 9C and 9D are supported by intermediate bearings 12A to 12C, respectively.

  Each of the screw shafts 9A to 9D has a blade plate 14 fixedly protruding in a spiral shape with a predetermined feed pitch on the peripheral surface of a cylindrical body 13 having an appropriate outer diameter, and is adjacent to each screw shaft 9A to 9D. The parts are connected and integrated with each other so as to draw a spiral in which the blades 14 are continuous with a gap d between the cylindrical bodies 13 of the screw shafts 9A to 9D. In the embodiment shown in FIG. 1, a high speed traveling section A1 in which the feed pitch of the blades 14 is large and a low speed traveling section A2 in which the feed pitch of the blades 14 is small are alternately arranged, and the intermediate bearings 12A to 12C are It is not at a position between the travel section A1 and the travel section A2, but at an intermediate position between the travel section A1 and / or the travel section A2. In addition, although the travel route 2 is configured by combining the two sections of the high speed travel section A1 and the low speed travel section A2, the travel path 2 is configured by combining three sections with different feed pitches of the blades 14 or more. It can also be configured.

  A roller unit 15 that engages with a blade 14 of the screw shaft 3 (each screw shaft unit 9A to 9D) is provided at the bottom of the transport carriage 1. The roller unit 15 includes a portal movable body 16 that covers the screw shaft 3 and three driven rollers 17 </ b> A to 17 </ b> C that are pivotally supported inside the portal movable body 16.

  Hereinafter, the detailed structure of the roller unit 15 will be described with reference to FIGS. 2 to 6. The roller-shaped movable unit 15 is provided below the roller unit support 19 attached to the frame 18 of the transport carriage 1 so as to be adjustable in height. A body 16 is attached via a vertical support shaft 20, and the portal movable body 16 is arranged around an axis of the vertical support shaft 20, that is, a vertical rotation axis 20 a orthogonal to the axis of the screw shaft 3. It is rotatably supported. The driven rollers 17A to 17C are arranged along the blade plate 14 in the circumferential direction of the screw shaft 3, and when viewed from the axial direction of the screw shaft 3 (see FIG. 4), the driven roller 17B at an intermediate position is Positioned in the vicinity of the rotational axis 20a of the portal movable body 16, the driven rollers 17A and 17C on both sides are disposed at positions 90 degrees apart in the circumferential direction from the driven roller 17B at the intermediate position. These three driven rollers 17 </ b> A to 17 </ b> C are composed of a pair of roller single bodies 21 that sandwich the blade plate 14 of the screw shaft 3 from both sides in a direction perpendicular to the both side surfaces of the blade plate 14. The shaft 22 fixed to the portal movable body 16 is supported so as to be able to rotate only in parallel to the radial direction of the screw shaft 3 passing between the pair of rollers 21.

  The roller unit support 19 includes a bearing member 23 that fixes and supports the upper half of the vertical support shaft 20 and is fixed by bolts and nuts 24 from both left and right sides. A pair of left and right vertical plates 25a and 25b extending upward. The pair of left and right vertical plates 25a and 25b are provided in the pair of left and right angle members 26a and 26b provided on the frame 18 side of the transport carriage 1 and are elongated holes provided in the vertical plates 25a and 25b in the vertical direction. 27 and a bolt nut 28 penetrating through the long hole 27 are attached so as to be adjustable in height, and a pair of left and right which is penetrated and locked to the roller unit support body 19 from the lower side outside the pair of left and right angle members 26a and 26b. The suspension bolt 29 is fixed to a pair of left and right angle members 26a, 26b with an operation nut 30a and a lock nut 30b. Accordingly, by tightening the operation nut 30a with the bolt nut 28 and the lock nut 30b loosened, the roller unit support 19 suspended by the suspension bolt 29 is raised, and conversely, the operation nut 30a is loosened. The roller unit support 19 that is suspended by the suspension bolt 29 is lowered to adjust the height of the roller unit support 19, that is, in the vertical direction of the driven rollers 17 </ b> A to 17 </ b> C with respect to the blade 14 of the screw shaft 3. The roller unit support 19 can be fixed by adjusting the engagement position and finally fastening the bolt nut 28 and the lock nut 30b. Of course, by the above operation, the driven rollers 17A to 17C of the roller unit 15 are raised and fixed to a height at which they do not interfere with the blades 14 of the screw shaft 3, and the transport carriage 1 is freely pushed and moved on the travel path 2. You can also.

  The pair of roller single bodies 21 of the driven rollers 17 </ b> A to 17 </ b> C are spaced apart from each other by 90 degrees in the circumferential direction by the biasing means 31 interposed between the portal movable body 16 and the roller unit support body 19. The urging is held in the initial posture to be clamped by. The biasing means 31 includes a portal movable body 16 having a torsion coil spring 32 loosely fitted to the vertical support shaft 20 between the roller unit support body 19 and an upper end fixed to the roller unit support body 19 side. The vertical pins 33 and the vertical pins 34 whose lower ends are fixed to the portal movable body 16 side are provided, and both ends 32a and 32b of the torsion coil spring 32 in a state where no torsional stress is applied. The two vertical pins 33 and 34 are engaged with each other. Therefore, the portal movable body 16 twists the torsion coil spring 32 through either one of the vertical pins 33 and 34 from either side of the initial posture to the front or back, and resists the reaction force. Thus, it can rotate around the vertical support shaft 20 (rotation axis 20a). The range of rotation of the gate-shaped movable body 16 at this time includes projections (bolt heads) 35a and 35b that protrude from the upper surface of the portal-shaped movable body 16 at an appropriate interval in the circumferential direction of the vertical support shaft 20. It can regulate by contact with the stopper plate 36 fixed to the bearing member 23 so that the lower end portion is positioned between the two protrusions 35a and 35b.

  Next, the support structure of the screw shafts 9A to 9D on both sides by the intermediate bearings 12A to 12C will be described with reference to FIGS. The intermediate bearings 12A to 12C include an outer diameter bearing body 37 that can be easily loosely fitted inside the cylindrical body 13 constituting the screw shafts 9A to 9D, and the center of the axial width of the bearing body 37. A support portion 38, which is fixed to a position and extends to one side of the bearing main body 37, is made of a plate material perpendicular to the axial direction of the bearing main body 37, and is fixed to the outer end of the support portion 38. The mounting plate 39 is installed on the gantry 41 via the buffer member 40.

  A bearing member for fixing the base end portion of the transmission shaft 42 concentrically with the cylindrical body 13 to the end portion on the intermediate bearing 12A to 12C side of the single screw shaft 9A to 9C adjacent to one side of the intermediate bearings 12A to 12C. 49a is fixed to a position that is a certain distance inside from the end of the cylindrical body 13, and the transmission shaft 42 is inserted into a self-aligning bearing 37a included in the bearing body 37 of the intermediate bearings 12A to 12C, thereby screw shaft The end portion of the cylindrical body 13 of the single body 9A to 9C, that is, the cylindrical end portion 13a is put on a portion protruding from the support portion 38 of the bearing body 37 to one side, and the cylindrical end portion 13a is supported by the support portion. 38. The screw shafts 9B to 9D adjacent to the opposite sides of the intermediate bearings 12A to 12C include a short end shaft portion 43 connected to the protruding end portion 42a of the transmission shaft 42 protruding from the intermediate bearings 12A to 12C, and this end. The relay shaft portion 44 is connected to the shaft portion 43, and the long main body shaft portion 45 is connected to the relay shaft portion 44.

  The end shaft portion 43 is formed on the projecting end portion 42a of the transmission shaft 42 projecting from the bearing body 37 of the intermediate bearings 12A to 12C at a substantially central position in the axial direction of the cylindrical body 13 with the blade plate 14 fixed to the outer peripheral surface. An outer fitting bearing member 46 is fixed concentrically. The bearing member 46 is fitted on the protruding end portion 42a of the transmission shaft 42, cylindrical spacers 42b and 42c are fitted on the protruding end portion 42a of the transmission shaft 42 so as to sandwich the bearing member 46, and the transmission shaft 42. It is fixed at a fixed position on the projecting end portion 42a of the transmission shaft 42 by a fastening nut 42d that is detachably screwed to the projecting end portion 42a, and transmission from the transmission shaft 42 to the end shaft portion 43 is performed. This is carried out via a key 42e fitted between the key grooves provided in the protruding end portion 42a of the transmission shaft 42 and the bearing member 46. The key 42e is fixed by a key fixing bolt 42f screwed in the radial direction from the outside of the cylindrical body 13 of the end shaft portion 43. Thus, the end shaft portion 43 to which the bearing member 46 is fixed at a fixed position on the protruding end portion 42a of the transmission shaft 42 is an end portion of the cylindrical body 13 on the intermediate bearings 12A to 12C side, that is, a screw shaft. The cylindrical end portions 13b of the single bearings 9B to 9D on the side of the intermediate bearings 12A to 12C cover portions protruding from the support portions 38 of the bearing main bodies 37 of the intermediate bearings 12A to 12C, and the cylindrical end portions 13b are supported by the support portions 38. Is approaching. Accordingly, between the screw shafts 9A and 9B located on both sides of the intermediate bearings 12A to 12C, between the screw shafts 9B and 9C, and between the screw shafts 9C and 9D, the bearing body 37 of each of the intermediate bearings 12A to 12C. There is only a gap d that is sufficiently narrower than the width in the axial direction and slightly wider than the support portion 38.

  The relay shaft portion 44 is formed by fitting and fixing coupling members 47 and 48 to both ends of the cylindrical body 13 with the blade plate 14 fixed to the outer peripheral surface. The connecting members 47 and 48 and the cylindrical body 13 on the outer side thereof have recesses 47a and 48a that are opened radially outward and axially outward by a radial cut reaching the axial position. And the radial direction is the same. The transmission shaft 42 supported by the intermediate bearings 12 </ b> A to 12 </ b> C and attached with the end shaft portion 43 is rotated so as to protrude outward from the end shaft portion 43 outside the screw shaft portion into which the fastening nut 42 d is screwed. A transmission end 42g is projected. The rotation transmission end portion 42g is formed by cutting a flat surface on both sides in the diameter direction of the shaft portion having a smaller diameter than the screw shaft portion into which the fastening nut 42d is screwed, and connecting members 47 at one end of the relay shaft portion 44. This is a flat shaft portion having a thickness that can be just fitted into the recessed portion 47a. On the other hand, the main body shaft portion 45 has a bearing member 49b fitted and fixed to an end portion of the cylindrical body 13 to which the blade plate 14 is fixed to the outer peripheral surface and connected to the relay shaft portion 44, and is rotated from the bearing member 49b. A transmission shaft 50 having a transmission projecting shaft portion 50a is concentrically fixedly projected. The rotation transmission protruding shaft portion 50a protrudes from the main body shaft portion 45, and is formed by cutting a flat surface on both sides in the diameter direction of the shaft portion having a diameter larger than the rotation transmission end portion 42g of the transmission shaft 42. Thus, a flat shaft portion having a thickness that can be just fitted into the recessed portion 48a of the connecting member 48 at the other end of the relay shaft portion 44 is provided. The concave portion 47a in which the small-diameter rotation transmission end portion 42g is fitted in the radial direction and the concave portion 48a in which the large-diameter rotation transmission protruding shaft portion 50a is fitted in the radial direction are fitted. The depth in the radial direction is changed according to the diameter (width) of the rotation transmission end portion 42g and the rotation transmission protruding shaft portion 50a, and the direction of the relay shaft portion 44 is changed to change the axial center position in the recessed portion 47a. The projecting shaft portion 50a for rotation transmission cannot be fitted up to.

  The coupling between the end shaft portion 43 and the relay shaft portion 44, that is, the coupling of the relay shaft portion 44 to the transmission shaft 42 on which the end shaft portion 43 is keyed, is connected to the cylindrical body 13 at the end of the relay shaft portion 44. This is performed by a connecting member 47 and a bolt 51a and a nut 51b passing through a rotation transmitting end 42g on the side of the transmission shaft 42 fitted in the recessed portion 47a of the connecting member 47, and the relay shaft portion 44 is formed. The main body shaft portion 45 is connected to the cylindrical body 13 and the connecting member 48 at the end of the relay shaft portion 44, and the rotation on the main body shaft portion 45 side fitted in the recessed portion 48a of the connecting member 48. This is performed by two bolts 52a and 53a and nuts 52b and 53b in the width direction of the rotation transmission projection shaft portion 50a penetrating the transmission projection shaft portion 50a. Each of the bolts 51a to 53a and the nuts 51b to 53b are configured to be fitted into a recess formed on the relay shaft portion 44 side so as not to protrude from the outer peripheral surface of the tubular body 13 of the relay shaft portion 44. Yes.

  The assembly procedure of the screw shaft 3 configured as described above will be described. The screw shaft single body 9A has the transmission shaft 42 at one end thereof inserted into and supported by the bearing body 37 of the intermediate bearing 12A, and the support shaft at the other end. 10a is supported by the end bearing 11A and supported at a predetermined position. Of course, this screw shaft unit 9A cannot be supported in a state where the bearings 11A, 12A supporting both ends thereof are fixed on the gantry, so that the screw shaft unit 9A is also similar to the other screw shaft units 9B to 9D. It is also possible to configure the end bearing 11A so that only the transmission shaft 42 is inserted and supported.

  The screw shaft single body 9B first attaches the end shaft portion 43 to the transmission shaft 42 protruding from the intermediate bearing 12A. That is, the end shaft portion 43 is externally fitted with the cylindrical spacers 42b and 42c with the key 42e interposed between the end shaft portion 43 and the key 42e therebetween, and the fastening nut 42d is tightened to fix the end shaft to a fixed position on the transmission shaft 42. While fixing the portion 43, the key fixing bolt 42f is tightened to fix the key 42e. Next, the transmission shaft 42 protruding from one end of the body shaft portion 45 is inserted into and supported by the bearing body 37 of the intermediate bearing 12B. At this time, a space in which the relay shaft portion 44 can be fitted is secured between the end shaft portion 43 and the main body shaft portion 45, and the space between the end shaft portion 43 and the main body shaft portion 45 is secured. The relay shaft portion 44 is fitted in the radial direction from the lateral side. At this time, the open end in the radial direction of the one-end recessed portion 47a of the relay shaft portion 44 is opposed to the rotation transmission end portion 42g of the transmission shaft 42 in a state of protruding from the end shaft portion 43, and protrudes from the main body shaft portion 45. The relay shaft portion 44 is connected to the transmission shaft 42 and the main body shaft in a state where the radially open end of the concave recess portion 48a of the other end of the relay shaft portion 44 is opposed to the rotation transmission projecting shaft portion 50a of the transmission shaft 50. The portion 45 is fitted by being translated in the radial direction to the axial center position. Finally, the rotation transmission end portion 42g of the transmission shaft 42 and the end portion (connecting member 47) of the relay shaft portion 44 fitted on the transmission shaft 42 are coupled and integrated by bolts 51a and nuts 51b, and the main body shaft portion 45 is also integrated. The rotation transmission projecting shaft portion 50a and the end portion (connecting member 48) of the relay shaft portion 44 fitted on the rotation shaft are coupled and integrated by bolts 52a and 53a and nuts 52b and 53b.

  Similarly, the screw shaft 3 is assembled by incorporating the screw shaft simple units 9C and 9D. The assembled screw shaft 3 includes the screw shafts 9A and 9B, the screw shafts 9B and 9C, and the screws. The shafts 9C and 9D are supported by the intermediate bearings 12A to 12C, respectively. However, at the positions of the intermediate bearings 12A to 12C, the intermediate bearings 12A to 12B are interposed between the cylindrical bodies 13 constituting the screw shaft 3. Only a narrow gap d in which the 12C plate-like support portion 38 protrudes downward is formed. Further, by assembling the screw shaft single units 9A to 9D as described above, the blade plate 14 is spaced from the gap d between the screw shaft single units 9A to 9D adjacent to both sides of the intermediate bearings 12A to 12C. Further, the cylindrical body 13 is continuous between the end shaft portion 43 and the relay shaft portion 44 and between the relay shaft portion 44 and the main body shaft portion 45 constituting the screw shafts 9B to 9D. The end surfaces of the blades 14 are adjacent to each other, and the end surfaces of the blades 14 are adjacent to each other and are spirally continuous.

  When the screw shaft 3 is assembled as described above, the conveyance carriage 1 is supported on the travel path 2 on the upper side, and the roller unit 15 provided at the bottom of the conveyance carriage 1 is attached to the blade plate of the screw shaft 3. 14 is engaged. That is, the vane plate 14 is sandwiched between each pair of roller units 21 constituting the three driven rollers 17 </ b> A to 17 </ b> C arranged in the circumferential direction along the vane plate 14. At this time, the portal movable body 16 that pivotally supports the three driven rollers 17A to 17C is held at the initial position by the urging force of the torsion coil spring 32, but the three driven rollers 17A at this initial position. If the arrangement direction of ˜17C is configured to substantially coincide with the spiral angle of the blade 14 in any one of the high speed travel section A1 and the low speed travel section A2, for example, the high speed travel section A1, As described above, in the state in which the roller unit 15 is raised to a height that does not interfere with the screw shaft 3, the conveyance carriage 1 is manually pushed to an appropriate position in the high-speed traveling section A1 in the traveling path 2, and then the roller The unit 15 can be lowered to engage the driven rollers 17 </ b> A to 17 </ b> C with the blade 14 of the screw shaft 3. In some cases, at least one end of the travel path 2 is provided with a conveyance carriage standby place that does not include the screw shaft 3, and while rotating the screw shaft 3 in a predetermined direction (low-speed drive or manual rotation with the motor 5), It is also possible to sequentially engage each driven roller 17A to 17C of the roller unit 15 with the blade plate 14 of the screw shaft 3 by manually pushing and moving the transport cart 1 supported at the transport cart standby place toward the screw shaft 3. It is.

  Thus, when the screw shaft 3 is rotationally driven by the motor 5 in a predetermined direction, each of the three driven rollers 17A to 17C of the roller unit 15 engaged with the blade plate 14 of the screw shaft 3 is specifically One of the pair of roller units 21 constituting the driven rollers 17A to 17C is subjected to a feeding action to one of the axial directions of the screw shaft 3 by the vane plate 14, so that the transport carriage 1 is predetermined. The vehicle travels along the travel route 2 at a speed of That is, the vehicle travels at a high speed corresponding to a large feed pitch of the blade 14 in the high speed travel section A1, and travels at a low speed corresponding to a small feed pitch of the blade 14 in the low speed travel section A2. Further, since the feed pitch of the blade plate 14 (the spiral angle of the blade plate 14 with respect to the axis of the screw shaft 3) gradually changes between the high-speed traveling section A1 and the low-speed traveling section A2, the driven rollers 17A to 17C There is play between the pair of roller units 21 of each of the driven rollers 17A to 17C that can absorb the change in the spiral angle of the blade 14 between the driven rollers 17A and 17C located at both ends of the row (approximately 180 degrees). For example, the transfer of the transport carriage 1 from one of the high-speed traveling section A1 and the low-speed traveling section A2 to the other is performed smoothly without difficulty. At this time, when transferring from the high speed travel section A1 to the low speed travel section A2, the portal movable body 16 including the driven rollers 17A to 17C is twisted around the rotation axis 20a and resists the biasing force of the coil spring 32. On the contrary, when moving from the low-speed travel section A2 to the high-speed travel section A1, the portal movable body 16 is twisted around the rotation axis 20a and rotates in the direction in which the urging force of the coil spring 32 acts.

  When the transport carriage 1 driven along the travel path 2 by the rotation of the screw shaft 3 passes through the positions of the intermediate bearings 12A to 12C, the driven rollers 17A to 17C of the roller unit 15 are placed on both sides of the intermediate bearings 12A to 12C. It must pass through the gaps d between the cylindrical bodies 13 between the adjacent screw shafts 9A and 9B, between the screw shafts 9B and 9C, and between the screw shafts 9C and 9D. Thus, as shown in FIG. 4, the circumferential length (angle) θ of the gap d along the blade 14, in other words, the divided length (angle) of the blade 14 divided by the gap d. Since θ is narrow such that the width of the gap d is slightly larger than the thickness of the plate-like support portion 38 of the intermediate bearings 12A to 12C, the circumferential interval between the driven rollers 17A to 17C (approximately 90 degrees). ) And sufficiently smaller than the circumferential interval (approximately 180 degrees) between the driven rollers 17A and 17C at both ends in the circumferential direction. Therefore, when the driven rollers 17A to 17C pass through the gap d between the cylindrical bodies 13 at the positions of the intermediate bearings 12A to 12C (the part where the blade 14 is divided), the three driven rollers 17A to 17C By only entering the gap d between the cylindrical bodies 13 one by one from the rollers, the remaining two driven rollers engage with the upper blade plate 14 of the gap d or the upper blades. The plate 14 and the lower blade 14 are engaged with each other or engaged with the lower blade 14, and the three driven rollers 17 </ b> A to 17 </ b> C are reliably engaged with the blade 14. It will be held in the direction along.

  In the above structure, the circumferential length (angle) θ along the blade 14 of the gap d is such that two of the three driven rollers 17A to 17C enter the gap d. When it is large or the distance between the three driven rollers 17A to 17C in the circumferential direction along the blade plate 14 is narrow, when the two driven rollers enter the gap d, only the remaining one driven roller is the blade plate 14. Because of this thrust, the portal movable body 16 that pivotally supports these three driven rollers 17A to 17C rotates around the rotation axis 20a, and the driven that has entered the gap d is driven by this thrust. The position of the roller deviates from the position along the original blade 14, and the driven roller that has entered the gap d smoothly and smoothly engages the blade 14 on the upper side of the gap d. Theft becomes impossible. Further, even when it is assumed that two driven rollers are axially supported by the portal movable body 16 along the blade plate 14, even if only one driven roller enters the gap d, the blade plate 14 Since there is only one driven roller to be engaged, the same result as described above is obtained, and the driven roller that has entered the gap d cannot be smoothly and smoothly engaged with the blade 14 on the upper side of the gap d. .

  However, according to the above-described configuration of the present invention, the three driven rollers 17 </ b> A are also provided when the transport carriage 1 passes through a location where the blade plate 14 of the screw shaft 3 is divided by the gap d (positions of the intermediate bearings 12 </ b> A to 12 </ b> C). -17C is always held in the direction along the blade 14 by the fact that the two driven rollers are always engaged with the blade 14, the driven roller that has entered the gap d It is possible to avoid a phenomenon such as collision or excessive contact with the blade 14 on the upper side of the gap d and forcible contact, and the transport carriage 1 can be smoothly and reliably passed through the portion having the gap d. It is.

  The conveyance cart drive device using the screw shaft of the present invention continuously conveys a work to be worked on a straight traveling path at a relatively low speed, but assembles various products such that the conveyance speed must be changed for each section. It can be used in a line. In this case, the work is supported on the transport carriage, and the travel route of the transport carriage is placed in the pit below the floor so that the column portion of the work support base moves in the slit provided on the floor. It can be arranged.

DESCRIPTION OF SYMBOLS 1 Conveyance cart 2 Traveling path 3 Screw shaft 5 Motor 6 Guide rail 9A-9D Screw shaft single-piece | unit 10a, 10b Support shaft 11A, 11B end bearing 12A-12C Intermediate bearing 13 Cylindrical body 13a, 13b Cylindrical end Portion 14 Blade plate 15 Roller unit 16 Portal movable body 17A to 17C Follower roller 19 Roller unit support body 20 Vertical support shaft 20a Rotating shaft center 21 A pair of rollers 29 Suspension bolt 31 Energizing means 32 Torsion coil spring 37 Intermediate bearing body 38 Intermediate bearing support section 42, 50 Transmission shaft 42a Projection end section 42b, 42c Cylindrical spacer 42d Fastening nut 42e Key 42g Rotation transmission end section 43 End shaft section 44 Relay shaft section 45 Main body shaft section 46 49a, 49b shaft Receiving member 47, 48 Connecting member 47a, 48a Recessed portion 50 Transmission shaft 50a Protrusion shaft portion for rotation transmission 51a-53a Bolt 51b-53b Nut A1 High-speed traveling section A2 Low-speed traveling section d Clearance θ along the blades of clearance d Circumferential length (angle)

Claims (7)

  A motor-driven screw shaft is supported along the travel path of the transport carriage, and the transport carriage is supported by a driven carriage that engages with the screw shaft. The screw shaft alone is concentrically connected by an intermediate bearing, and the transport carriage has a support portion extending from the screw shaft of the intermediate bearing when the screw shaft is viewed from the axial direction. Is provided on the opposite side with a movable body pivotably supported around a rotation axis orthogonal to the axis of the screw shaft, and the driven roller is pivoted on the screw shaft. When viewed from the direction, the screen in the circumferential region does not include the support portion extending from the screw shaft of the intermediate bearing. -When the three driven rollers are sequentially supported between the single screw shafts on both sides of the intermediate bearing, the two driven rollers are always screwed in at least three locations along the shaft blade plate. A drive device for a transport carriage configured to engage with a blade of a shaft.   Each of the said three circumferential direction driven rollers is a drive device of the conveyance trolley of Claim 1 comprised from a pair of roller single-piece | unit which pinches the blade | wing plate of a screw shaft.   3. The transport carriage according to claim 1, wherein the movable body is provided with a biasing means that biases and holds the three driven rollers that are pivotally supported at an initial position where the three driven rollers are aligned along the blade plate of the screw shaft. Drive device.   The three driven rollers are disposed at a rotational axis position of the movable body and a position approximately 90 degrees away from the rotational axis position in both forward and reverse directions when the screw shaft is viewed from the axial direction. The drive apparatus of the conveyance trolley in any one of Claims 1-3 currently performed.   The support portion of the intermediate bearing is formed of a plate material that is thinner than the width of the bearing body in the axial direction and orthogonal to the axial direction of the screw shaft, and the axial direction of the screw shaft extends from the support portion of the intermediate bearing. The drive device of the conveyance trolley in any one of Claims 1-4 with which the cylindrical end part of the screw shaft single-piece | unit has covered the bearing main body which protrudes in this.   A single screw shaft whose cylindrical end covers the bearing body of the intermediate bearing, and the single screw shaft positioned on at least one side of the intermediate bearing protrudes from the bearing body and rotates integrally with the screw shaft on the opposite side. An end shaft portion that is detachably attached to the transmission shaft in the axial direction, a main body shaft portion whose one end is supported by the next intermediate bearing, and a relay shaft that connects the main body shaft portion and the end shaft portion. The relay shaft portion is attached to the main body shaft portion and the end shaft portion so as to be detachable in the radial direction with respect to the axial direction of the screw shaft. Drive device for transport cart.   The transmission shaft is provided with a rotation transmission end portion protruding from the end shaft portion toward the relay shaft portion, and the main body shaft portion is provided with a rotation transmission projecting concentrically toward the relay shaft portion. The projecting shaft portion is provided, and at both ends of the relay shaft portion, the rotation transmission end of the transmission shaft and the rotation transmission projecting shaft portion of the main body shaft portion can be fitted and detached in the radial direction. Both ends of the relay shaft portion provided with a transmission recess portion, and the rotation transmission recess portions at both ends fitted to the rotation transmission end portion of the transmission shaft and the rotation transmission protruding shaft portion of the main body shaft portion. The driving device of the transport carriage according to claim 6, further comprising a fixing member that fixes the rotation transmission end portion of the transmission shaft to the rotation transmission protruding shaft portion of the main body shaft portion.

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