Conveyor device

Abstract

To prevent wear of a friction roller of a friction roller type driving device for catch-up from being promoted.SOLUTION: The conveyor device A is provided with a friction roller type driving device 1 for catching up, a guide means 2 for supporting the friction roller type driving device 1 movably along the conveying direction T of a truck, and an energizing means 3 for imparting energizing force for energizing the friction roller type driving device 1 in a downstream direction D, and the friction roller type driving device 1 is moved in the upstream direction U against the energizing force by force in the upstream direction U acting on the friction roller type driving device 1 when a following truck separated from a rear end truck of a conveying line in the upstream direction. The urging means 3 is composed of a spring 4 which is a generation source of the urging force, and an urging force adjusting mechanism 5 which adjusts the urging force and maintains the magnitude of the urging force substantially constant.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a conveyor system including a friction roller drive device for catch-up, which supplies a follow-up carriage separated upstream from a trailing carriage on a conveyor line. [Background technology]

[0002] In a conveying line in which a procession of carriages consisting of multiple non-self-propelled carriages connected by couplers, or a procession of carriages consisting of multiple non-self-propelled carriages in a compressed state without couplers, is continuously conveyed at a constant conveying speed by a carriage driving device, there is a conveyor device equipped with a friction roller type drive device for catch-up, which conveys a following carriage separated upstream from the rear end carriage of the conveying line at a speed faster than the conveying speed and supplies it to the conveying line.

[0003] In the conveyor device, it is common to detect that the trailing carriage has caught up with the trailing carriage by an increase in the load on the drive device of the trailing carriage (for example, by detecting the motor current of the friction roller drive device), and to control the speed of the trailing carriage to the conveying speed (for example, paragraph

[0002] of Patent Document 1).

[0004] In the conveyor device having the above configuration, when the trailing carriage catches up with the trailing carriage, slippage occurs between the friction rollers of the friction roller type drive device and the trailing carriage, which accelerates wear of the friction rollers. Also, in a state where slippage occurs between the friction rollers and the trailing carriage, a load is placed on the reducer of the friction roller type drive device, which reduces the durability of the reducer (for example, see paragraph 1 of Patent Document 1):

[0005] ).

[0005] To solve the above-mentioned problems, the invention described in Patent Document 1 includes guide means for supporting a friction roller drive device for catch-up so as to be movable along the carriage conveyance direction, and biasing means for biasing the friction roller drive device in the downstream direction. A follow-up carriage, which is spaced upstream from a trailing carriage on a conveyance line that is continuously conveyed at a constant conveyance speed by a carriage drive device, is conveyed by the friction roller drive device, and when the follow-up carriage catches up with the trailing carriage, an upstream force acting on the friction roller drive device causes the friction roller drive device to move upstream against the biasing force of the biasing means (see, for example, paragraph

[0008] of Patent Document 1). [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Japanese Patent Application Laid-Open No. 2007-161428 Summary of the Invention [Problem to be solved by the invention]

[0007] The conveyor device of Patent Document 1 uses an air cylinder (for example, air cylinder 12 in FIGS. 3 and 5) as an example of the biasing means. When an air cylinder is used, the biasing force of the biasing means is generated by air pressure, and therefore a relief mechanism can be used to keep the secondary pressure approximately constant, so the biasing force (thrust in the downstream direction) of the biasing means received when the friction roller type drive device moves upstream can be kept approximately constant. This makes it difficult for slippage to occur between the friction roller of the friction roller type drive device and the following carriage, thereby suppressing wear on the friction roller.

[0008] However, when an air cylinder is used as the biasing means, an air pressure generator such as an air compressor, a relief regulator, air piping, etc. are required, and the piping work requires a lot of man-hours, which increases costs. Furthermore, it cannot be adapted to the so-called airless system, which achieves energy savings by eliminating the power-intensive air compressor and has a significant effect on reducing CO2 emissions in line with the promotion of carbon neutrality to reduce greenhouse gases.

[0009] On the other hand, Patent Document 1 states that a compression coil spring or the like may be used as the biasing means (paragraph

[0028] of Patent Document 1). When a spring such as a compression coil spring is used as the biasing means, it can be adapted to the airless design.

[0010] However, when a spring is used as the biasing means, the restoring force of the spring increases as the amount of deformation of the spring increases, so the biasing force (thrust in the downstream direction) of the biasing means received by the friction roller drive device when it moves in the upstream direction cannot be maintained at a substantially constant level, which causes slippage between the friction roller of the friction roller drive device and the drive surface driven by the friction roller of the trailing bogie that has caught up with the trailing bogie, accelerating wear of the friction roller.

[0011] The present invention aims to prevent accelerated wear of the friction rollers of the friction roller drive device in a conveyor system that includes a friction roller drive device for catch-up, guide means that supports the friction roller drive device so that it can move along the transport direction of the carriage, and biasing means that biases the friction roller drive device in a downstream direction, even if the biasing force of the biasing means is generated by a spring. [Means for solving the problem]

[0012] A conveyor according to a first aspect of the present invention is a conveyor apparatus for a conveyor line in which a procession of carts is continuously conveyed at a constant conveying speed by cart drive devices, the conveyor apparatus comprising: a catch-up friction roller drive device that presses a rotationally driven friction roller against a drive surface of a following cart spaced upstream from a trailing cart of the conveyor line, thereby conveying the following cart at a speed faster than the conveying speed and supplying it to the conveyor line; guide means that support the friction roller drive device movably along the cart conveying direction; and biasing means that imparts a biasing force that biases the friction roller drive device in a downstream direction, wherein when the following cart catches up with the trailing cart, an upstream force acting on the friction roller drive device causes the friction roller drive device to move upstream against the biasing force. The biasing means comprises a spring that is a source of the biasing force, and a biasing force adjustment mechanism that adjusts the biasing force to maintain a substantially constant magnitude.

[0013] A conveyor according to a second aspect of the present invention is the conveyor according to the first aspect, wherein the biasing force adjustment mechanism comprises a first member and a second member. One of the first member and the second member is a fixed member that does not move with the friction roller drive device, and the other is a movable member that moves with the friction roller drive device. A restoring force of the spring acts on one of the fixed member and the movable member, and the restoring force is transmitted to the other of the fixed member and the movable member.

[0014] A conveyor according to a third aspect of the present invention is the conveyor according to the second aspect, wherein one of the fixed-side member and the movable-side member is a swing arm that swings about a horizontal axis perpendicular to the conveying direction, and a roller attached to the free end of the swing arm that is rotatable about a horizontal axis parallel to the horizontal axis. The other of the fixed-side member and the movable-side member is a roller abutment body that has a curved surface that displaces vertically in the conveying direction and against which the roller abuts. The restoring force of the spring acts on the swing arm so as to press the roller against the curved surface of the roller abutment body.

[0015] A conveyor according to a fourth aspect of the present invention is the conveyor according to any one of the first to third aspects, wherein the spring is installed on a fixed side that does not move together with the friction roller type drive device.

[0016] A conveyor device according to a fifth aspect of the present invention is the conveyor device according to any one of the first to third aspects, wherein the spring is a compression coil spring, and a restricting means is provided to restrict deformation of the compression coil spring so that it is along the center line of the coil when the compression coil spring is compressed.

[0017] A conveyor device according to a sixth aspect of the present invention is the conveyor device according to any one of the first to third aspects, wherein the spring is a tension coil spring.

[0018] A conveyor according to a seventh aspect of the present invention is the conveyor according to the first aspect, wherein peripheral members of a conveyor rail that guides the carriage along the conveying path are arranged so as to sandwich the friction roller drive device for catch-up and the guide means from the front and rear in the conveying direction.

[0019] A conveyor according to an eighth aspect of the present invention is the conveyor according to the first aspect, wherein the guide means comprises a rail member in the conveying direction arranged on a fixed side that does not move together with the friction roller drive device, and a guide roller arranged on a moving side that moves together with the friction roller drive device and that follows the rail member. [Effects of the Invention]

[0020] In the conveyor according to the present invention, the spring is the source of the biasing force that biases the friction roller drive device for catch-up in the downstream direction. Therefore, it is possible to achieve energy savings by eliminating the need for an air compressor, which consumes a lot of power, and to respond to the so-called airless system, which is effective in reducing CO2 emissions and is promoting carbon neutrality to reduce greenhouse gases.

[0021] Furthermore, in the conveyor according to the present invention, the biasing means for applying a biasing force (a thrust force in the downstream direction) to the friction roller drive device for catch-up comprises the spring and a biasing force adjustment mechanism for adjusting the biasing force and maintaining the magnitude of the biasing force at a substantially constant level. As a result, even if the biasing force of the biasing means is generated by a spring, the biasing force adjustment mechanism can maintain the biasing force of the biasing means, which is applied to the friction roller drive device when it moves upstream, at a substantially constant level.

[0022] Therefore, slippage is less likely to occur between the friction rollers of the friction roller drive device and the drive surface of the following bogie that is driven by the friction rollers, and this makes it possible to suppress accelerated wear of the friction rollers. [Brief explanation of the drawings]

[0023] [Figure 1] FIG. 1 is a perspective view of a friction roller drive device for catch-up use in a conveyor device according to an embodiment of the present invention; [Figure 2] This is an oblique view showing a state in which a following carriage that is separated upstream from the rear-end carriage of a conveying line is driven by the friction roller drive device, and when the following carriage catches up with the rear-end carriage, the friction roller drive device moves upstream due to the upstream force acting on the friction roller drive device, with the carriage omitted. [Figure 3] FIG. 2 is an enlarged front view of a main part of FIG. [Figure 4] FIG. 3 is an enlarged front view of a main part of FIG. 2. [Figure 5] 2 is a plan view showing the main parts around the friction roller type driving device corresponding to FIG. 1.

[0023] FIG. [Figure 6] 6 is a cross-sectional view taken along the line X1-X1 of FIG. 5. [Figure 7] 6 is a cross-sectional view showing the state of FIG. 2; [Figure 8] FIG. 4 is a cross-sectional view taken along the arrow ZZ in FIG. [Figure 9]This is a front view to explain the method of adjusting the biasing force by the biasing force adjustment mechanism, and shows the moment when the trailing cart driven by the friction roller drive device catches up with the rear end cart of the conveying line, i.e., the state when the friction roller drive device is not moving upstream (X=0), with the cart omitted. [Figure 10] FIG. 10 is a front view illustrating a method for adjusting the biasing force by the biasing force adjustment mechanism, showing the state in which the friction roller type drive device has moved the furthest in the upstream direction (X=L) with the carriage omitted. [Figure 11] 10 is a graph showing the biasing force (thrust in the downstream direction) of the biasing means that the friction roller type drive device receives when moving in the upstream direction, with the horizontal axis representing the position of the friction roller type drive device. [Figure 12] FIG. 2 is a perspective view corresponding to FIG. 1, showing a first modified example of the biasing means. [Figure 13] FIG. 3 is a perspective view showing the first modified example and corresponding to FIG. 2. [Figure 14] FIG. 4 is a front view showing the first modified example and corresponding to FIG. 3. [Figure 15] FIG. 5 is a front view showing the first modified example and corresponding to FIG. 4. [Figure 16] FIG. 10 is a perspective view corresponding to FIG. 1 and showing a second modified example of the biasing means. [Figure 17] FIG. 3 is a perspective view showing the second modified example and corresponding to FIG. 2. [Figure 18] FIG. 4 is a front view corresponding to FIG. 3 and showing the second modified example. [Figure 19] FIG. 5 is a front view corresponding to FIG. 4 and showing the second modified example. DETAILED DESCRIPTION OF THE INVENTION

[0024] An embodiment of the present invention will be described below with reference to the drawings. In the drawings, arrows T, D, and U indicate the "conveying direction," "downstream direction," and "upstream direction," respectively. Front, back, left, and right are defined as viewed in the conveying direction T (downstream direction D) of the carriage, and a view from the right is a front view. Fixing members such as anchor bolts for fixing to the floor surface FL are omitted from the drawings.

[0025] [Conveyor device] A conveyor device A according to an embodiment of the present invention, shown in FIGS. 1 to 5, transports multiple non-self-propelled carriages along a loop-shaped conveyor line, for example, as shown in the layout diagram of FIG. 1 of Patent Document 1. For example, the conveyor line (L1, L2) in the layout diagram of FIG. 1 of Patent Document 1 is a conveyor line that continuously transports a procession of carriages at a constant conveying speed using carriage drive devices, such as friction roller drive devices. In the conveyor line, the carriages are coupled together by couplers or compressed without using couplers. The multiple non-self-propelled carriages in the conveyor device A according to an embodiment of the present invention move, for example, along a conveyor rail R, a portion of which is shown in FIGS. 1 to 4. The carriage drive devices that continuously transport the procession of carriages may be chain drive devices that pull the carriages using a drive chain, or the like.

[0026] The conveyor device A is equipped with a friction roller type drive device 1 for catch-up, which presses a rotationally driven friction roller FR against the drive surface O (Figure 5) of a follower cart N that is spaced in the upstream direction U from the rear end cart of the conveying line, and conveys the follower cart N at a speed faster than the conveying speed and supplies it to the conveying line.

[0027] The friction roller drive device 1 is supported by a bracket I that swings about a vertical axis V relative to a movable base B2. When the friction roller FR of the friction roller drive device 1 abuts against the drive surface O of the following bogie N, the compression coil spring J between the movable base B2 and the bracket I is compressed. Therefore, the restoring force of the compression coil spring J presses the friction roller FR against the drive surface O.

[0028] [Guiding means] As shown in Figures 1 to 4 and 8, conveyor device A includes guide means 2 that supports friction roller type drive device 1 so that it can move along the carriage transport direction T. Guide means 2 is made up of rail members 21 in the transport direction T, which are arranged on the fixed side and do not move together with friction roller type drive device 1, and guide rollers 22A and 22B that are arranged along rail member 21 and move together with friction roller type drive device 1.

[0029] As shown in Fig. 8, the left and right rail members 21, 21 have a U-shaped cross section with opposing openings, and have upper flange portions 21A and lower flange portions 21B extending horizontally. As shown in Figs. 3, 4 and 8, vertical guide rollers 22A are provided on the front, rear, left and right sides of the support body W, and horizontal guide rollers 22B are provided on the front, rear, top and bottom of the support body W. The vertical guide rollers 22A are located between the upper flange portion 21A and the lower flange portion 21B and roll on the lower flange portion 21B. The horizontal guide rollers 22B are located between the left and right upper flanges 21A, 21A and between the left and right lower flanges 21B, 21B.

[0030] By configuring the guide means 2 with a rail member 21 and guide rollers 22A, 22B that run along the rail member 21, manufacturing costs can be reduced, and maintenance is easy because there are no products with long delivery times, thereby increasing the operating rate.

[0031] [Energy applying means] As shown in FIGS. 1 to 4, the conveyor device A includes a biasing means 3 that applies a biasing force to the friction roller type driving device 1 to bias the friction roller type driving device 1 in the downstream direction D.

[0032] When the trailing carriage N catches up with the rear end carriage of the conveying line, the friction roller type drive device 1 moves in the upstream direction U against the biasing force of the biasing means 3 due to the force acting on the friction roller type drive device 1 in the upstream direction U.

[0033] The biasing means 3 comprises a compression coil spring C, which is a spring 4 that generates the biasing force, and a biasing force adjustment mechanism 5 that adjusts the biasing force and keeps the magnitude of the biasing force substantially constant. The direction in which the compression coil spring C compresses is substantially parallel to the conveying direction T.

[0034] [Biasing force adjustment mechanism] As shown in FIGS. 1 to 4, the biasing force adjustment mechanism 5 is made up of a first member 11 and a second member 12. The first member 11 is a fixed-side member F that does not move together with the friction roller type driving device 1. The second member 12 is a moving-side member M that moves together with the friction roller type driving device 1. The restoring force of a compression coil spring C acts on the fixed-side member F, and the restoring force is transmitted to the moving-side member M.

[0035] The fixed-side member F is a swing arm 6 that swings around a horizontal axis H1 perpendicular to the conveying direction T, and a roller 7 that is attached to the free end of the swing arm 6 and is rotatable around a horizontal axis H2 parallel to the horizontal axis H1. The movable-side member M is a roller abutment body 8 that has a curved surface 9 that the roller 7 abuts against and that displaces vertically as it moves in the conveying direction T. The restoring force of the compression coil spring C acts on the swing arm 6 so as to press the roller 7 against the curved surface 9 of the roller abutment body 8.

[0036] [Means for restricting deformation of a compression coil spring along the center line of the coil when it is compressed] The compression coil spring C, which is the source of the biasing force, generates a restoring force when compressed. Therefore, in order to reduce the variation in the restoring force due to the amount of deformation when the compression coil spring C is compressed, it is necessary to prevent the compression coil spring C from deforming in the perpendicular direction by preventing the application of a force perpendicular to the center line G of the coil when compressed. Therefore, as shown in FIGS. 5 to 7, a restricting means 10 is provided to restrict the deformation of the compression coil spring C so that it is along the center line G of the coil when compressed. This reduces the variation in the spring force K corresponding to the restoring force, thereby making it possible to maintain a constant biasing force P (according to equations (1) and (2) described below).

[0037] The structure and operation of the restricting means 10 will be described with reference to Figures 6 and 7. The restricting means 10 is made up of a screw shaft 13, a guide cylinder 14, flanges 15A and 15B, swinging bodies 16 and 17, and nuts 18, 19A, 19B and 20.

[0038] Oscillator 16, located in the upstream direction U of compression coil spring C, is supported so as to be able to swing about horizontal axis H3 of fixed base B1, which is parallel to horizontal axis H1 (FIG. 3) that is the swing center of swing arm 6. Oscillator 17, located in the downstream direction D of compression coil spring C, is located above horizontal axis H1 of swing arm 6, and is supported so as to be able to swing about horizontal axis H4 of swing arm 6, which is parallel to horizontal axis H1.

[0039] The screw shaft 13 is inserted through the flange body 15A and the guide cylinder body 14, and the guide cylinder body 14 is inserted into the coil of the compression coil spring C. Nuts 19B, 19A, and 18 are screwed onto the upstream side U of the screw shaft 13, the downstream side D of the guide cylinder body 14 is inserted into the through-hole 17A of the oscillator 17, and the flange body 15B is inserted onto the end of the screw shaft 13 in the downstream direction D, and a nut 20 is screwed onto it. The upstream end U of the screw shaft 13 is fixed to the oscillator 16 with the nut 18.

[0040] The positions of nuts 19B and 20 that screw onto the screw shaft 13 are adjusted and positioned so that the flange bodies 15A and 15B that sandwich both end faces of the guide cylinder body 14 are at a predetermined position relative to the screw shaft 13, and then the nuts are fixed with nut 19A, which forms a double nut relative to nut 19B.

[0041] In this state, the upstream U end face of the compression coil spring C contacts the downstream D side face of the flange body 15A, and the downstream D end face of the compression coil spring C contacts the upstream U side face of the oscillator 17. Then, as shown in Figures 6 and 7, when the compression coil spring C compresses, it deforms along the center line G of the coil.

[0042] Spring Placement In the example shown in Figures 1 to 4, the spring 4 is installed on the fixed side, which does not move with the friction roller type driving device 1. As a result, the spring 4 and its peripheral components, as well as the swing arm 6 and roller 7 of the biasing force adjustment mechanism 5, are also on the fixed side. This allows the moving side to be lighter, making the friction roller type driving device 1 move more smoothly along the guide means 2. In addition, the amount of wear on the roller 7 can be reduced.

[0043] [Explanation of how to adjust the biasing force using the biasing force adjustment mechanism] The specifications shown in Figures 9 and 10 are used. Figure 9 shows the moment when the trailing carriage N (Figure 5) driven by the friction roller drive device 1 catches up with the rear end carriage of the conveyor line, and the coordinate in the direction in which the friction roller drive device 1 moves upstream in the U direction is defined as X. The X coordinate position of the friction roller drive device 1 in Figure 9 is X=0.

[0044] The position of the X coordinate of the friction roller type driving device 1 when the friction roller type driving device shown in FIG. 10 has moved the most in the upstream direction U is set to X=L.

[0045] The roller pressing force Q shown in FIGS. 9 and 10 can be calculated by equation (1) using a and b in FIG. 9 and assuming that the spring force is K.

[0046] Q=(a / b)·K (1)

[0047] When the contact angle θ and the inclination angle α are as shown in Figures 9 and 10, the biasing force P (thrust force in the downstream direction D) that the biasing means 3 applies to the friction roller type driving device 1 in the downstream direction D can be calculated using equation (2).

[0048] P = (sinα / sinθ)·Q (2)

[0049] That is, the roller pressing force Q, which varies depending on the X coordinate position of the friction roller drive device 1, can be adjusted by (sin α / sin θ), which also varies depending on the X coordinate position, to make the biasing force P approximately constant. In order to achieve this, the shape of the curved surface 9 of the roller contact body 8 that the roller 7 contacts is gradually changed, and the contact angle θ and the tilt angle α are gradually changed so that sin θ and sin α become the required magnitudes depending on the X coordinate position.

[0050] FIG. 11 is a graph showing the biasing force P (solid line) of the biasing means 3, along with the contact angle θ, tilt angle α, spring force K, and roller pressing force Q, with the horizontal axis representing the X coordinate position of the friction roller type driving device 1.

[0051] It can be seen from FIG. 11 that the magnitude of the biasing force P of the biasing means 3 can be maintained substantially constant by the biasing force adjusting mechanism 5 regardless of the X coordinate position of the friction roller type driving device 1.

[0052] [Restrictions due to the arrangement of components around the rail] In order to configure the biasing means 3 using only the spring 4 without using the biasing force adjustment mechanism 5 and obtain the required biasing force while minimizing fluctuations in the magnitude of the biasing force of the biasing means 3, it is necessary to use, for example, a spring with a very long free length as the spring 4.

[0053] 1 and 2, rail peripheral components S, such as the rail support member Y, cable support member, and power supply unit, are arranged around the conveyor rail R, and the rail peripheral components S become obstacles. Therefore, it is difficult to arrange the coil spring with a very long free length in the upstream direction U of the friction roller drive device 1. Therefore, it is not realistic to use a biasing means 3 consisting only of a spring 4 that reduces fluctuations in the magnitude of the biasing force of the biasing means 3. Even if it were possible to arrange a coil spring with a very long free length, it would be impossible to maintain the magnitude of the biasing force of the biasing means 3 at a substantially constant value.

[0054] In contrast, in this embodiment, as shown in Figures 1 and 2, a spring 4 having a relatively short free length, such as a compression coil spring C, is used, and the biasing force is adjusted using a biasing force adjustment mechanism 5. Therefore, in this embodiment, even if a rail peripheral member S is present, it is easy to arrange the friction roller type drive device 1, guide means 2, etc. For example, as shown in Figures 1 and 2, rail support members Y, which are rail peripheral members S, can be arranged so as to sandwich the friction roller type drive device 1 and guide means 2 from the front and rear in the conveying direction T. Then, the biasing force of the biasing means 3 can be adjusted using the biasing force adjustment mechanism 5, and the magnitude of the biasing force can be maintained approximately constant.

[0055] [First Modification of the Urging Means] 12 to 15 show a first modified example of the biasing means 3. In the first modified example, unlike the example shown in FIGS. 1 to 4, the compression coil spring C, which is the spring 4 serving as the source of the biasing force of the biasing means 3, and the swing arm 6, etc. move together with the friction roller type driving device 1, but the roller abutment body 8 does not move together with the friction roller type driving device 1.

[0056] [Biasing force adjustment mechanism] In the first modified example, the first member 11 of the biasing force adjustment mechanism 5 is a movable member M that moves together with the friction roller type driving device 1, and the second member 12 of the biasing force adjustment mechanism 5 is a fixed member F that does not move together with the friction roller type driving device 1. The restoring force of the compression coil spring C acts on the movable member M, and the restoring force is transmitted to the fixed member F.

[0057] The movable member M comprises a swing arm 6 that swings about a horizontal axis H1 perpendicular to the conveying direction T, and a roller 7 attached to the free end of the swing arm 6 and rotatable about a horizontal axis H2 parallel to the horizontal axis H1. The fixed member F comprises a roller abutment body 8 that has a curved surface 9 that displaces vertically in the conveying direction T and against which the roller 7 abuts. The restoring force of a compression coil spring C acts on the swing arm 6 so as to press the roller 7 against the curved surface 9 of the roller abutment body 8. The compression direction of the compression coil spring C is substantially parallel to the conveying direction T.

[0058] In the first modified example, as in the example of Figures 1 to 4, the biasing force adjustment mechanism 5 can maintain the biasing force P, shown in Figures 14 and 15, with which the biasing means 3 biases the friction roller type driving device 1 in the downstream direction D, at a substantially constant value.

[0059] [Guiding means] 12 to 15, the guide means 2 that supports the friction roller type drive device 1 so that it can move along the carriage transport direction T is a linear guide 23 made up of a guide rail 23A and a guide block 23B that moves along the guide rail. Using the linear guide 23 as the guide means 2 simplifies the structure.

[0060] [Second Modification of the Urging Means] 16 to 19 show a second modified example of the biasing means 3. In the second modified example, unlike the example shown in FIGS. 1 to 4, the spring 4 serving as the source of the biasing force of the biasing means 3 is a tension coil spring E. The direction in which the tension coil spring E extends is substantially parallel to the conveying direction T.

[0061] By using a tension coil spring E as the spring 4, the installation is completed by hooking the hooks F1, F2 at both ends of the tension coil spring E onto the latching projections 24A, 25B. The tension coil spring E deforms along the center line of the coil when it stretches, which simplifies the structure around the tension coil spring E.

[0062] In the present invention, the spring 4, which is the source of the biasing force of the biasing means 3, is not limited to the compression coil spring C and the tension coil spring E. The spring 4 may be a torsion spring, a torsion coil spring, a spiral spring, a leaf spring, or the like.

[0063] [Biasing force adjustment mechanism] 1 to 4, the first member 11 of the biasing force adjustment mechanism 5 in the second modified example is the fixed-side member F that does not move with the friction roller type drive device 1. The second member 12 of the biasing force adjustment mechanism 5 in the second modified example is the same as the example in FIGS. 1 to 4, and is the movable-side member M that moves with the friction roller type drive device 1. Therefore, as in the example in FIGS. 1 to 4, the restoring force of the tension coil spring E acts on the first member 11, which is the fixed-side member F, and the restoring force is transmitted to the second member 12, which is the movable-side member M.

[0064] In the second modified example, as in the example of Figures 1 to 4, the biasing force adjustment mechanism 5 can maintain the biasing force P, shown in Figures 18 and 19, with which the biasing means 3 biases the friction roller type driving device 1 in the downstream direction D at a substantially constant value.

[0065] As described above, the biasing force adjustment mechanism 5 provided in the conveyor device A according to the embodiment of the present invention is made up of the first member 11 and the second member 12. One of the first member 11 and the second member 12 is the fixed-side member F that does not move together with the friction roller type drive device 1, and the other is the movable-side member M that moves together with the friction roller type drive device 1. The restoring force of the spring 4 acts on one of the fixed-side member F and the movable-side member M, and the restoring force is transmitted to the other of the fixed-side member F and the movable-side member M.

[0066] One of the fixed side member F and the movable side member M is a swing arm 6 that swings around a horizontal axis H1 perpendicular to the conveying direction T of the carriage, and a roller 7 that is attached to the free end of the swing arm 6 and is rotatable around a horizontal axis H2 parallel to the horizontal axis H1. The other of the fixed side member F and the movable side member M is a roller abutting body 8 that has a curved surface 9 that displaces up and down as it moves in the conveying direction T, and against which the roller 7 abuts. The restoring force of the spring 4 acts on the swing arm 6 so as to press the roller 7 against the curved surface 9 of the roller abutting body 8.

[0067] [Action and effect] In the conveyor device A according to the embodiment of the present invention, the spring 4 is the source of the biasing force that biases the friction roller drive device 1 for catch-up in the downstream direction D. Therefore, it is possible to achieve energy savings by eliminating the need for an air compressor, which consumes a lot of power, and it is also possible to achieve carbon neutrality, which is known as airless conveyance, which has a significant effect in reducing CO2 emissions.

[0068] Furthermore, in the conveyor device A according to the embodiment of the present invention, the biasing means 3 that applies a biasing force (thrust in the downstream direction D) P to the friction roller drive device 1 for catch-up comprises a spring 4 and a biasing force adjustment mechanism 5 that adjusts the biasing force P to maintain the magnitude of the biasing force P at a substantially constant level. As a result, even if the source of the biasing force P of the biasing means 3 is the spring 4, the biasing force adjustment mechanism 5 can maintain the biasing force P of the biasing means 3, which is applied to the friction roller drive device 1 for catch-up when it moves in the upstream direction U, at a substantially constant level.

[0069] Therefore, slippage is less likely to occur between the friction rollers FR of the friction roller drive device 1 for catch-up and the drive surface O of the following bogie N that is driven by the friction rollers FR, thereby suppressing the acceleration of wear of the friction rollers FR.

[0070] The above description of the embodiments is given by way of example only and is not intended to be limiting, and various improvements and modifications can be made without departing from the scope of the present invention. [Explanation of symbols]

[0071] 1 Friction roller drive for catch-up 2 Guide means 3 Urging means 4 Spring 5 Bias force adjustment mechanism 6 Swing arm 7 Roller 8 Roller contact body 9 Curved surface 10 restricting means 11 first member 12 second member 13 screw shaft 14 Guide cylinder body 15A, 15B Flange body 16,17 Rocking body 17A through hole 18, 19A, 19B, 20 Nut 21 Rail member 21A Upper flange 21B Lower flange 22A Vertical guide roller 22B Horizontal guide roller 23 Linear Guide 23A Guide Rail 23B Guide block 24A, 25B Latching protrusions A Conveyor device B1 Fixed base B2 Moving base C Compression coil spring D Downstream direction E Tension coil spring F Fixed side member F1, F2 Hook FL Floor surface FR Friction roller G Coil center line H1~H4 Horizontal axis I Bracket J Compression coil spring K Spring force M Moving member N Trailing bogie O Drive surface P Thrust (urging force) Q Roller pressing force R Conveyor rail S Rail peripheral parts T Conveying direction U Upstream direction V Vertical axis W Support Y-rail support member

Claims

1. In a conveying line in which a procession of carriages is continuously conveyed at a constant conveying speed by a carriage driving device, a friction roller type drive device for catch-up that presses a rotationally driven friction roller against a drive surface of a follower carriage that is spaced upstream from the rear end carriage of the conveying line, and conveys the follower carriage at a speed faster than the conveying speed and supplies it to the conveying line; a guide means for supporting the friction roller type drive device so as to be movable along the conveying direction of the carriage; and a biasing means for applying a biasing force to bias the friction roller type driving device in a downstream direction, a friction roller type drive device that moves in the upstream direction against the biasing force due to an upstream force acting on the friction roller type drive device when the trailing carriage catches up with the trailing end carriage, The biasing means is a spring that is a source of the biasing force; a biasing force adjusting mechanism that adjusts the biasing force and maintains the magnitude of the biasing force substantially constant; Conveyor equipment.

2. the biasing force adjustment mechanism includes a first member and a second member, The first member and the second member are One of the members is a fixed member that does not move together with the friction roller type drive device, the other is a moving member that moves together with the friction roller type driving device, a restoring force of the spring acts on one of the fixed-side member and the movable-side member, The restoring force is transmitted to the other of the fixed-side member and the movable-side member.

2. The conveyor system of claim 1.

3. One of the fixed-side member and the movable-side member is a swing arm that swings about a horizontal axis perpendicular to the conveying direction, and a roller that is attached to a free end of the swing arm and is rotatable about a horizontal axis parallel to the horizontal axis, The other of the fixed-side member and the movable-side member is a roller contact body having a curved surface that is displaced vertically in the conveying direction and that the roller contacts; a restoring force of the spring acts on the swing arm so as to press the roller against the curved surface of the roller contact body; 3. The conveyor system of claim 2.

4. The spring is installed on a fixed side that does not move together with the friction roller type drive device. The conveyor device according to any one of claims 1 to 3.

5. the spring is a compression coil spring, a restricting means for restricting deformation of the compression coil spring so that the deformation is along the center line of the coil when the compression coil spring is compressed; The conveyor device according to any one of claims 1 to 3.

6. The spring is a tension coil spring. The conveyor device according to any one of claims 1 to 3.

7. The friction roller drive device for catch-up and the guide means are sandwiched between the friction roller drive device and the guide means from the front and rear in the conveying direction. peripheral members of a conveyance rail that guides the carriage along the conveyance path are arranged; 2. The conveyor system of claim 1.

8. The guide means a rail member in the conveying direction, which is disposed on a fixed side that does not move together with the friction roller type driving device; a guide roller disposed on a moving side that moves together with the friction roller type drive device and that follows the rail member; 2. The conveyor system of claim 1.

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