JP5740774B2 - Chain transmission device and sediment scraping device - Google Patents

Description

  The present invention relates to a chain transmission device and a sediment scraping device equipped with such a chain transmission device, and can be used to scrape sludge as sediment.

  In a sewage treatment facility such as a sedimentation basin, as a sludge scraping device, a scraping plate is stretched between a pair of endless chains arranged in parallel at a predetermined interval, and is positioned along the lower surface of the processing tank by driving the chain There is a scraping device in which a scraping plate (also referred to as a flight) is moved toward a sludge pit along the bottom surface of the treatment tank, and the sludge accumulated on the bottom surface of the treatment tank can be scraped to the sludge pit. Although there is a normal sprocket engagement type as a chain (Patent Document 1), there are many so-called notch chains recently (Patent Document 2) from an installation example in a public sewage system. The notch chain has a structure in which a series of links are connected endlessly with a connecting pin in the same way as a normal sprocket chain. However, a notch is formed on the side of the link facing the drive wheel, and the drive wheel is replaced with a sprocket wheel. In addition, one having drive pins spaced apart at equal intervals in the circumferential direction between a pair of disks is used. The notch chain transmits power by engaging the connecting pin with the notch in the drive part. In the driven part, the inner peripheral surface of the link is in contact with the surface of the driven wheel (sheave). It is said that there is an advantage that the life of the chain is extended as compared with the case where a normal sprocket wheel is used. On the other hand, since the engagement between the drive pin and the notch in the notch chain is shallower than that of a normal sprocket wheel, the drive wheel prevents the notch from being removed from the drive pin at the drive wheel portion (so-called tooth skipping). A chain guard is installed along the outer periphery of the.

JP-A-11-290846 JP 2006-326383 A

  In the drive system using a chain, the scraping plate moves in one direction along the bottom surface of the processing tank to scrape (transfer) the sludge accumulated on the bottom surface of the processing layer such as a sedimentation basin. The sludge that accumulates in the sedimentation basin is basically in the form of mud and does not have a large resistance to scratching, but the sludge sometimes contains a lump of stone, and it locks when the scraping plate bites. There was a case. In this case, if the chain can be reversed, it may be possible to return to the normal state by releasing the lock by reverse rotation, but in the case of the conventional notch chain, the notch is connected to the drive pin in the reverse direction. It is shaped so that it can be disengaged from the notch, and basically it cannot be reversed. For this reason, when the scraping plate is locked, it is necessary to stop and drain the device, and to remove the biting stones.

  The present invention has been made in view of the problems of the prior art, and an object of the present invention is to enable reverse rotation in a chain of a drive system using notch-drive pins.

According to the present invention, the chain includes a chain and a wheel that engages the chain, and the chain is formed by connecting a plurality of links in series with a connection pin, and a pair of plate-like portions of each link is opposed to at least the drive wheel. On the other hand, notches are formed on the side where the wheels extend in the axial direction and are spaced apart at equal intervals in the circumferential direction according to the pitch of the links in the chain. It has a drive pin that engages, and the drive pin is configured to be able to transmit power by engaging with the notch during both forward and reverse rotation of the wheel, and each link is at least between the pair of plate-shaped parts facing the drive wheel An opening is formed on the side where the wheel is provided, while the wheel extends radially through the opening and is provided at equal intervals according to the pitch of the links at intervals in the circumferential direction. In each link, the notch is biased to the connecting pin side in the drive direction of the chain, and during forward rotation of the wheel, the engagement between the tooth portion and the barrel and the engagement between the drive pin and the notch Provided with a chain transmission that transmits power from the wheel to the chain by both sides, and transmits power from the wheel to the chain by both engagement of the teeth and the barrel and engagement of the drive pin and notch when the wheel reverses Is done.

  The notch can be provided with an engaging surface with the driving pin and a flank surface connected to the engaging surface before and after the rotation direction, and a reliable engagement between the notch and the driving pin can be obtained in both forward and reverse rotations. In addition, the drive pin can be smoothly removed from the notch when the drive wheel is removed.

  Each link has an opening formed at least on the side facing the drive wheel between a pair of plate-like portions, while the wheel extends radially through the opening and is equally spaced according to the link pitch. In the forward rotation of the wheel, power is transmitted from the wheel to the chain by both engagement between the tooth portion and the barrel and engagement between the drive pin and the notch. However, it is possible to prevent the engagement between the tooth portion and the barrel during the reverse rotation of the wheel.

  Instead of this, power is transmitted from the wheel to the chain by engaging the drive pin and the notch during forward rotation of the wheel. However, both of the engagement between the tooth portion and the barrel and the engagement between the drive pin and the notch are performed during the reverse rotation of the wheel. Power transmission from the wheel to the chain by engagement may be performed.

  In addition, when the wheel rotates forward, power is transmitted from the wheel to the chain by both engagement between the tooth portion and the barrel and engagement between the drive pin and the notch, and when the wheel reverses, the engagement between the tooth portion and the barrel and the drive pin Power transmission from the wheel to the chain by both engagement with the notch may be performed.

  In the sludge scraping device by the chain transmission device of the present invention, the chain is wound endlessly between the driving wheel and the driven wheel in the settling tank, and the driving wheel is connected to the rotational driving means to be connected to the driving wheel. The chain is driven by the rotation, and the scraping plate attached to the links spaced in the length direction of the chain circulates and moves in one direction in the processing tank to scrape the precipitate.

  According to the present invention, the notch formed on at least the side of the pair of plate-shaped portions facing the drive wheel is configured to engage with the drive pin in both forward and reverse rotations. When used as a chain transmission device for a feeder, when the scraping plate is locked by a block of stone on the bottom of the sedimentation tank, the lock can be released by reversing it to improve workability at the treatment plant. be able to.

FIG. 1 is a side view of the scraping device of the present invention installed in a sedimentation basin. FIG. 2 is a front view of the scraping device of the present invention installed in the sedimentation basin (arrow view taken along line II-II in FIG. 1). FIG. 3 is a sectional view of each part before connecting adjacent links in a chain using the wheel of the present invention. 4 is a front view of a connecting pin that is a component of the chain of FIG. 3, and is a view taken along the line IV-IV of FIG. 5 is a front view of a locking ring that is a component of the chain of FIG. 3, and is a view taken along the line VV of FIG. 6 is a front view of the lock piece which is a component of the chain of FIG. 3, and is a view taken along the line VI-VI of FIG. 7 is a cross-sectional view of the assembled state of the chain of FIG. 8 is a side view of a link that is a component of the chain of FIG. 3, and is a view taken along the line VIII-VIII of FIG. FIG. 9 is a front view of the drive wheel during forward rotation in mesh with the chain of FIGS. 3 to 8 and is an arrow view along line IX-IX in FIG. FIG. 10 is a cross-sectional view of the drive wheel, and is an arrow view taken along line XX in FIG. FIG. 11 is a view showing an engagement state of the wheel of the present invention with a drive pin and a tooth portion in a chain, and is a view as seen from a direction XI in FIG. FIG. 12 is the same as FIG. 9 but shows the meshing state of the chain and the drive wheel in the reverse direction. In this invention, it is a figure explaining the positional relationship of the tooth | gear part and barrel which can drive the chain in both the normal rotation and reverse rotation direction by a drive wheel, and a drive pin and a notch. FIG. 14 is a front view of a drive wheel in the second embodiment of the present invention in which the chain is driven only by drive pins. FIG. 15 is a diagram showing the positional relationship between the drive pin and the notch during reverse rotation in the second embodiment of the drive shown in FIG.

Hereinafter, an embodiment in which the present invention is used in a sludge scraping apparatus for scraping sludge as a precipitate in a sewage treatment plant will be described. It can be used for general scraping.
1 and 2 schematically show a sludge scraping device. In FIG. 1, 1 is a sedimentation basin (sedimentation tank of the present invention) in sewage treatment, a sludge pit 2 is provided at the bottom of the sedimentation basin 1, and sludge deposited on the bottom surface 1A of the sedimentation basin 1 Is scraped to the sludge pit 2 by the sludge scraping device 3. The sludge scraping device 3 is a drive wheel 4, driven wheels 5, 6, 7, a drive wheel 4, a chain 8 wound endlessly on the driven wheels 5, 6, 7, and a rotation that imparts a rotational driving force to the drive wheel 4. The chain transmission device is composed of a driving means 9 and a scraping plate (also referred to as a flight) 10 that is connected to the chain 8 at an interval and circulates and moves in one direction to scrape sludge. The drive wheel 4 and the driven wheel 7 are provided in the upper part of the settling basin 1, and the driven wheels 5 and 6 are provided near the bottom surface of the settling pond 1. A pair of chains 8 are provided in parallel with each other in the width direction of the sedimentation basin 1 (see FIG. 2). Although the detailed structure of the chain 8 will be described later, a series of links are connected by a connecting pin, and a notch is formed on the side of the link facing the drive wheel. The scraping plate 10 is attached so as to extend in the width direction of the settling basin 1 as schematically shown in FIG. 2, and is formed on the opposite side of the notch of the opposed link in a pair of chains spaced in the width direction, as will be described later. It is fixed to the connected part. And the part facing the bottom face 1A (FIG. 1) of the sedimentation basin in the chain 8 when the chain 8 is driven and the scraping plate 10 connected thereto are along the resin rail 11 fixed on the bottom face 1A of the sedimentation basin. Sludge that is slid and guided as indicated by an arrow a and accumulated on the bottom surface 1A of the sedimentation basin is scraped to the sludge pit 2. On the other hand, a steel rail 12 is provided in the upper part of the sedimentation basin, and the scraping plate 10 is slidably guided on the steel rail 12 as indicated by an arrow b at a portion along the liquid level L in the chain 8. The rotational drive means 9 includes a rotational drive motor 9-1 and a power transmission mechanism 9-2 such as a chain-sprocket wheel or a belt-pulley that transmits the rotational motion of the output shaft of the rotational drive motor 9-1 to the drive wheel 4. Consists of.

  Next, the detailed structure of the chain 8 of the sludge scraping device 3 will be described. FIG. 3 shows the adjacent links of the chain 8 in a disassembled state from the front. All the parts of the chain are molded parts made of synthetic resin, and the link 16, the connecting pin 17, the locking ring 18, and the lock piece 19 are basic components. The connecting pin 17 has a head 20 at one end and a reduced diameter portion 22 at the other end. The head 20 has a width across flats as shown in FIG. The reduced diameter portion 22 of the connecting pin 17 is formed with a pair of locking protrusions 24 extending radially until the connecting pin outer diameter is flush with the connecting pin outer diameter (see FIG. 7). Each locking projection 24 extends from the end face of the connecting pin 17 along the axis, but terminates with some separation from the large diameter portion of the connecting pin 17.

  As shown in FIG. 5, the locking ring 18 has a bottomed engagement formed between the insertion groove 29 and a pair of insertion grooves 29 diametrically opposed to each other extending in the entire axial length on the inner periphery thereof. A stop groove 30 is provided. The insertion groove 29 and the locking groove 30 have a width that allows the locking projection 24 of the connecting pin 17 to be inserted freely in the axial direction without substantial play. The insertion groove 29 extends the entire length in the axial direction, but the locking groove 30 terminates in the axial direction from the outer surface of the locking ring 18 (see FIG. 3).

  As shown in FIG. 6, the lock piece 19 has a cutout portion 19 </ b> A formed by cutting a ring whose inner diameter R is somewhat larger than the outer diameter of the reduced diameter portion 22 of the connecting pin 17 in the circumferential direction by about 30 degrees. The Therefore, the lock piece 19 presents a bifurcated portion 32 when viewed from the front. Since the cut portion 19A has a central angle of about 30 degrees, the connection pin 17 is attached to the reduced diameter portion 22 by elastically deforming the bifurcated portion 32. After the attachment, the bifurcated portion 32 is elastically deformed. Returning to the original inner diameter R, the tip of the bifurcated portion 32 becomes a protruding portion radially inward with respect to the outer diameter of the connecting pin (the outer diameter of the reduced diameter portion 22), and the engagement state with the reduced diameter portion 22 is elastic. Maintain below. Further, the tip 32A of the bifurcated portion 32 is tapered as shown in FIG. 3, and the insertion work of the lock piece 19 is smooth. The lock piece 19 is provided with an overhang portion 34 on the outer periphery at a position opposite to the diameter of the cutout portion 19A, the overhang portion 34 projects in the radial direction, and the overhang portion 34 is the remaining portion of the lock piece 19 on the inner surface side However, the outer surface slightly protrudes outward in the axial direction, and an engagement recess 36 (FIG. 6) for the punching tool is formed in the axial protrusion.

  As shown in FIG. 3, each link 16 includes a pair of plate-like portions 38, each plate-like portion 38 includes a narrowed portion 38-1 and an enlarged portion 38-2, and the pair of plate-like portions 38 is narrowed. The portion 38-1 and the expanded portion 38-2 are arranged so as to face each other, and a connecting pin insertion hole 42 that is aligned is formed. The widened portion 38-2 of the plate-like portion 38 forms a cylindrical protruding portion 38-2A on the outer surface side. A barrel 44 (tubular portion) having a connecting pin insertion hole 40 is integrally formed between the narrowed portions 38-1 of the pair of plate-like portions 38. Between the pair of plate-like portions 38, an opening S is formed between the barrel and the facing expanded portion 38-2, and the link adjacent to the opening S between the expanded portions 38-2 of this one link. Sixteen constricted portions 38-1 are inserted as shown in FIG. 7, and the connecting pin insertion holes 40 and 42 are aligned between adjacent links 16. Then, the connecting pin 17 is inserted into the pin inserting hole 42 on one side, the connecting pin inserting hole 40 on the barrel 44 and the pin inserting hole 42 on the opposite side from the reduced diameter portion 22, and the head 20 of the connecting pin 17 faces. The tip of the connecting pin 17 protrudes from the cylindrical protrusion 38-2A on the side surface of the opposite plate-like portion 38, abutting against the cylindrical protrusion 38-2A on the side surface of the outer plate-like portion 38.

  The locking ring 18 is inserted into the tip of the connecting pin 17 protruding from the side surface of the plate-like portion 38. At this time, the locking ring 18 can be inserted until it completely comes out of the locking projection 24 of the connecting pin 17 by aligning the insertion groove 29 of the locking ring 18 with the locking projection 24. Then, the locking ring 18 is turned 90 degrees with respect to the connecting pin 17, and the locking ring 18 is moved on the connecting pin 17 so as to be pulled slightly outside in the axial direction. The locking ring 18 can be engaged with the bottom surface 30 </ b> A of the bottomed locking groove 30. The lock piece 19 has a cylindrical protrusion 38-2A on the side surface of the plate-like portion 38 of the link 16 so that the bifurcated portion 32 straddles the reduced diameter portion 22 of the connecting pin 17 and the tapered tip 32A of the bifurcated portion 32. And the locking ring 18 so as to be positioned from the outside in the radial direction. The lock piece 19 is configured so that the thickness δ of the bifurcated portion 32 is appropriately set with respect to the gap between the cylindrical projecting portion 38-2A and the opposing surface of the locking ring 18, whereby It can be installed smoothly and without substantial play. Therefore, the engagement state between the locking protrusion 24 and the locking groove 30 can be maintained. When the lock piece 19 is mounted, the tip of the bifurcated portion 32 is first brought into contact with the reduced diameter portion 22 of the connecting pin 17 in the cutout portion 19A. Thus, the bifurcated portion 32 is expanded against its elasticity, the bifurcated portion 32 is passed through the connecting pin 17, and the bifurcated portion 32 is restored to its original state by elasticity. The insertion of the lock piece 19 simultaneously displaces the locking ring 18 in the axial direction by an amount corresponding to the thickness of the locking piece 19, which includes the locking protrusion 24 of the connecting pin 17 and the bottomed locking groove 30 of the locking ring 18. Deepen the engagement (does not loosen in the axial direction). Therefore, when the lock piece 19 is mounted, the engagement state between the locking protrusion 24 and the locking groove 30 is firmly maintained. The lock piece 19 is engaged with the reduced diameter portion 22 of the connecting pin 17 on the entire circumference except for the cut portion 19A of 30 degrees when the bifurcated portion 32 is returned to its original position due to elasticity. Is not disengaged, and the adjacent link 16 is maintained in the connected state by the connecting pin 17. FIG. 7 shows a state where the connection of the adjacent links 16 by the connection pins 17 is completed.

  As shown in FIG. 1, in a state where the chains 8 are assembled in an endless state, the links 16 having the connecting portions of the scraping plates 10 described in FIG. FIG. 8 shows a link 16 having a connecting portion 49 of such a scraping plate 10, and the connecting portion 49 is formed integrally with the plate-like portion 38 and protrudes upward from the plate-like portion 38. The link 16 having the connecting portion 49 is also shown in FIG. 9, and the link 16 having the connecting portion 49 is installed oppositely between the pair of chains 8 spaced in the width direction of the settling basin. In the meantime, the scraping plate 10 of FIG. 1 is fixed (the attachment state of the scraping plate 10 to the connecting portions 49 of the links 16 in an appropriate number in the longitudinal direction of the chain 8 is schematically shown in FIG. 9). As a result, a structure in which the scraping plate 10 is located at intervals along the loop of the chain 8 as described in FIG. 1 is realized.

  As can be seen from FIGS. 1 and 7, an opening S is formed between a pair of plate-like portions 38 of one link 16 in a state where the adjacent link 16 is connected to one link 16 by the connecting pin 17. In this embodiment, the opening S is open on both sides, and a tooth portion of a wheel for driving the chain extends to the opening S as will be described later. If the engagement between the tooth portions of the wheel 38 described below is possible, the opening S may be closed on the opposite side of the drive wheel as long as the teeth can be engaged between the plate-like portions 38. In the side view of one link 16 shown in FIG. 8, the plate-like portion 38 is provided with a notch 50 between the connecting pin insertion hole 42 and the barrel 44, and the notch 50 has a first engagement at one end in the circumferential direction. A mating surface 50-1 is provided, and the upper part of the mating surface 50-1 has a shape that engages with the outer periphery of the drive pin 62 (circumferential surface of about 90 °) and is forward of the rotational direction (forward rotation) with respect to the engaging surface 50-1. The constricted part 50-1 ′ forms a tapered surface for escape. The other end in the circumferential direction of the notch 50 has conventionally formed a gently inclined surface (the shape of the imaginary line 50 '). This was to facilitate the escape (or removal) of the drive pin 62 from the notch 50 during the forward rotation of the drive wheel. Therefore, the rotation of the drive wheel is transmitted to the chain during the reverse rotation. There was no. In the present invention, the other end in the circumferential direction of the notch also forms the engaging surface 50-2, and the upper portion of the engaging surface 50-2 is configured to engage with the outer periphery of the drive pin 62 (about 90 °). A portion 50-2A which forms a circumferential surface) and continues downward with respect to the engaging surface 50-2 forms a tapered surface for escape. The surface 38A facing the drive wheel of the plate-like portion before and after the notch 50 is somewhat concave, and this concave shape is the circumferential surface of the sheave wheel when the driven wheel in the chain transmission system is a sheave wheel. When it is wound around, the surface 38A facing the drive wheel of the plate-like portion of the adjacent link exhibits a concave surface shape that smoothly follows the circumferential surface shape of the sheave wheel (see FIG. 9).

  Next, the detailed structure of the drive wheel 4 in the scraping device 3 of FIG. 1 will be described with reference to FIGS. 9 to 11. In this embodiment, the drive wheel 4 is a tooth portion in a conventional sprocket wheel-chain transmission device. And the transmission by the drive pin in the notch chain transmission device are sequentially or simultaneously performed. That is, as shown in FIG. 10, the drive wheel 4 includes a disk-shaped support body 54, and a rotation shaft 56 is inserted into the central hub portion 54-1, and the support body 54 and the rotation shaft 56 are made of a key or the like. It is fixed by appropriate means. The rotary shaft 56 is connected to a sprocket wheel, a pulley or the like in the power transmission mechanism 9-2 of FIG. 1 so that the rotational driving force from the rotational driving motor 9-1 is transmitted to the driving wheel 4. In FIG. 10, annular drive pin support plates 57 and 58 are disposed concentrically with the rotating shaft 56 on both sides of the support body 54. An annular sprocket disk 60 is positioned adjacent to the support body 54. The sprocket disk 60 has teeth (sprocket parts) 60A arranged on the outer periphery at equal intervals in the circumferential direction at a pitch equal to the pitch of the chain links. Provide (see also FIG. 9). The drive pins 62 are arranged at equal intervals in the circumferential direction at a pitch equal to the pitch of the chain links on the inner side of the tooth portion 60A, and the drive pins 62 are inserted through the sprocket disk 60 at the intermediate portion and are externally attached to both ends thereof. A screw portion 62-1 having a reduced diameter is provided, and the screw portion 62-1 protrudes outward of the shaft on both sides from openings formed in the drive pin support plates 57 and 58. The bolt 66 has a spacer 64 interposed between the drive pin support plate 58 and the sprocket disk 60, and a spacer 63 interposed between the support body 54 and the drive pin support plate 57, respectively. 58, the sprocket disk 60, the support body 54 and the drive pin support plate 57 are inserted in this order, and a nut 68 is screwed onto the end of the bolt 66 protruding from the drive pin support plate 57. Further, a nut 70 is screwed and fastened to the screw portion 62-1 protruding from the drive pin support plates 57 and 58, and assembled as a drive wheel for the chains of FIGS.

  As described above, in the present invention, the chain 8 is provided with a notch 50 similar to a normal notch chain in the link, while the drive wheel is a tooth portion (sprocket portion) 60 </ b> A that engages the barrel 44 of the chain 8. And a drive pin 62 engaged with the notch 50 of the chain 8. Also in the schematic diagram of FIG. 1, the tooth portion 60 </ b> A and the drive pin 62 in the drive wheel 4 are schematically illustrated, and these engage with the barrel and the notch of the chain 8, thereby rotating the drive motor 9-1 (forward rotation). ) Is transmitted to the drive wheel 4, and the rotation of the drive wheel 4 (in the direction of arrow c in FIG. 1) is transmitted to the chain 8. The power transmission system at the time of forward rotation will be described in more detail with reference to FIG. 9. As a result of rotation of the drive wheel 4 in the direction of arrow c, the tooth portion 60A of the sprocket disk 60 of the drive wheel 4 is a link constituting a chain 16 enters the opening S between the pair of plate-like portions 38, and the tooth portion 60A engages with the barrel 44 (see also FIG. 11) with its one end edge 60A-1 serving as a leading edge in the rotational direction. The driving force in the rolling direction (arrow c) is transmitted to the chain. In addition to the engagement of the tooth portion 60A with the barrel 44, the drive pin 62 engages with the first engagement surface 50-1 in the notch 50 of the pair of plate-like portions 38 in the link 16 constituting the chain in the rotational direction. . That is, when the circumference of the drive wheel 4 is reached, the engagement between the tooth portion 60A and the barrel 44 and the engagement between the drive pin 62 and the notch 50 occur in parallel (including both sequentially or simultaneously), and the drive Power is transmitted from the wheel 4 to the chain 8. In the case of a normal notch chain system in which power is transmitted only by engagement between the drive pin and the notch, the engagement between the drive pin and the notch is inevitably shallow, so when the chain goes around the drive wheel, the notch (chain) is driven. The pin (drive wheel) is likely to be detached, and a chain guard is required close to the outer periphery of the drive wheel. In the present invention, when the chain 8 goes around the drive wheel 4, the drive pin 62 and the notch Since the engagement between the tooth 60A and the barrel 44 occurs and the engagement between the tooth 60A and the barrel 44 is similar to that of a normal chain-sprocket, it is necessary for a normal notch chain. Even if there is no chain guard, the chain 8 does not detach from the drive wheel 4. Since the present invention does not require a chain guard, there is no risk of chain biting failure due to entanglement of foreign matters in the chain guard when used as a scraping device in a sedimentation basin.

  The driven side of the chain transmission system may be a normal sprocket wheel or a sheave wheel. In the case of a normal sprocket wheel, teeth on the outer periphery of the sprocket wheel enter the opening S between the pair of plate-like portions 38 in the link 16 constituting the chain and engage with the barrel 44. In the case of a sheave wheel, when the chain goes around the sheave wheel, the connection of the concave surface of the surface 38A facing the drive wheel of the pair of plate-like parts constituting the link of the chain follows the outer periphery of the sheave wheel. Because of the surface contact, the chain can be moved smoothly. As shown in FIG. 1, two driven wheels 5 and 6 are provided along the bottom surface of the settling basin 1, one driven wheel 7 is provided on the liquid level side (upper side) of the settling basin, and the driving side is also included. In the case of a four-wheel system in which a single wheel is installed, it is preferable that the driven wheels 5 and 6 on the bottom surface are sheave wheels and the driven wheel 7 on the liquid surface side is a sprocket wheel. That is, the load applied to the driven wheel is the closest driven wheel 5> the intermediate driven wheel 6> the most spaced driven wheel 7 when viewed from the drive wheel 4 in the direction opposite to the driving direction of the chain (arrow c). Since the sheave wheel is a surface contact, there is an advantage that the wear is small. However, if all the driven wheels are the sheave wheels, the wear may be accelerated. Therefore, the load wheel on the sheave wheel is reduced by using the driven wheels 5 and 6 on the high load side as sheave wheels and only the low load driven wheel 7 as a sprocket wheel, so that the three driven wheels 5, 6, 7 Thus, the load can be balanced between the wheels, and the wear of the wheels including the chain and the drive wheel can be reduced, and the service life can be extended. In FIG. 1, it is possible to arrange three wheels without the driven wheel 7. In this case, the two driven wheels are both sheave wheels.

During normal rotation of the drive wheel, the scraping plate 10 moves along the bottom surface 1A of the settling basin 1 as shown by an arrow a in FIG. In this case, when there is a large lump solid foreign matter (stone) on the bottom surface 1A of the sedimentation basin 1, the scraping plate 10 may bite into the foreign matter and be locked. In the case of the conventional notch chain type, the notch has a shape in which the drive pin and the notch are disengaged in the reverse rotation direction, and basically has a structure in which the reverse rotation cannot be performed. Therefore, in the case of the conventional notch chain type, the driving force is not transmitted to the chain 8 even if the drive wheel 4 is reversed, and the scraping plate 10 does not move. Therefore, once the lock occurs, the sedimentation basin 1 is completely emptied. The work required to remove the stones and release the locks by the workers, and the workability was not good. In the present invention, the rotational driving force of the drive wheel is transmitted to the chain by engaging the drive pin 62 with the notch 50 even during reverse rotation. As shown in FIG. 12, at the time of reverse rotation (arrow c ′), the drive pin 62 is engaged with the second engagement surface 50-2 of the notch 50, so that the drive force in the reverse direction from the drive wheel is obtained. It is applied to the chain 8 via a notch. In this case, with respect to the tooth portion 60A, the second end edge 60-2 serving as the leading edge in the rotation direction does not engage with the barrel 44, and the driving force is not transmitted. This will be described in more detail with reference to FIG. 13 which shows the positional relationship of the adjacent tooth portion and the drive pin with respect to the barrel and the notch. In FIG. At the position 62a, the drive pin is engaged with the first engagement surface 50-1, and at the second extreme position 62b, the drive pin is engaged with the second engagement surface 50-2. Difference (the line connecting the drive pin center O _62a at the position 62a with the center O ₄ of the drive wheel 4 and the line connecting the drive pin center O _62b at the position 62b with the center O ₄ of the drive wheel 4) (Angle difference) is α. On the other hand, the extreme positions that the barrel can take in the circumferential direction between the adjacent tooth portions 60A are indicated by 44a and 44b. At the first limit position 44a, the barrel engages with the first engagement surface 60A-1, and at the second limit position 44b, the barrel engages with the second engagement surface 60A-2. a line segment connecting a line segment connecting the center _{O 44a} of the barrel at an angle difference between the two (the position 44a and the center _{O 4} of the drive wheel 4, the center _{O 44b} of the barrel in the position 44b and the center _{O 4} of the drive wheel 4 Is an angle difference of β. Then, α ≦ β is satisfied. By establishing such a relationship, when α <β, the first drive pin 62 at the first limit position 62a is brought into engagement with the engaging surface 50-1 during forward rotation (arrow c) in FIG. The tooth portion 60A is engaged with the barrel 44 at the first extreme position 44a at the first end edge 60A-1 so that the driving force is notched from the driving pin 62 in the forward rotation direction. 50 is transmitted to the barrel 44 from the tooth portion 60A, and the chain is driven. Further, at the time of reverse rotation (arrow c ′) in FIG. 12, the drive pin 62 at the second limit position 62b is engaged with the notch 50 at the engagement surface 50-2, so that the drive force is driven in the reverse direction. On the other hand, the tooth portion 60A cannot reach the second limit position 44b of the barrel 44 and does not engage with the barrel 44, so that power is not transmitted from the tooth portion 60A. Further, at the time of reverse rotation when α = β, the driving pin 62 at the second limit position 62b is engaged with the notch 50 at the engaging surface 50-2, so that the driving force is notched from the driving pin in the reverse direction. Since the tooth portion 60A reaches the second limit position 44b of the barrel 44 and engages with the barrel 44, power is also transmitted from the tooth portion 60A.

  In the illustrated embodiment, the drive pin 62 has a circular cross section, and the inner peripheral shape of the first engagement surface 50-1 of the notch that engages with the drive pin 62 to transmit power during forward rotation (FIG. 9). And the inner peripheral shape of the second engagement surface 50-2 of the notch that engages with the drive pin 62 and transmits power during reverse rotation (FIG. 12) is a circle of approximately 90 degrees according to the outer peripheral shape of the drive pin 62. If the cross-sectional shape of the drive pin is not circular, the inner peripheral shape of the notch should be a shape that substantially matches the outer peripheral shape of the drive pin so that it closely engages with the drive pin. Needless to say, it is preferable.

  As a modification of the embodiment described above, the engagement between the tooth portion 60A and the barrel 44 may not be performed during forward rotation but may be performed during reverse rotation. That is, in this modification, the first end edge of the tooth portion 60A during forward rotation is indicated by 60A-1 ′ in FIG. 9, and does not engage with the barrel 44, and power transmission is not performed here. Accordingly, the transmission of the driving force is caused only by the engagement between the driving pin 62 and the notch 50. On the other hand, the second end edge of the tooth portion 60A at the time of reverse rotation is indicated by 60A-2 'in FIG. 12, and is engaged with the barrel 44, so that power is transmitted. Further, the drive pin 62 engages with the notch 50. Therefore, transmission of the reverse driving force is performed in parallel by the engagement of the tooth portion 60 </ b> A and the barrel 44 in addition to the engagement of the drive pin 62 and the notch 50.

  FIG. 14 and FIG. 15 show an embodiment of a chain that transmits power only by drive pins. In this case, the chain is the same as a normal notch chain, and the drive pin of the drive wheel engages with the notch 50 of the chain, so that power is transmitted from the drive wheel to the chain. The tooth portion 60A as in the embodiment of FIGS. 1 to 13 is not provided in this embodiment. During forward rotation in FIG. 14 (the drive wheel rotates as indicated by arrow c), the drive pin 62 engages with the first engagement surface 50-1 of the notch 50, thereby transmitting power from the drive wheel to the chain. Is done. At the time of reverse rotation in FIG. 15 (the drive wheel rotates as indicated by the arrow c ′), the drive pin 62 engages with the second engagement surface 50-2 of the notch 50, thereby transmitting power from the drive wheel to the chain. Is done.

DESCRIPTION OF SYMBOLS 1 ... Sedimentation basin 2 ... Pit 3 ... Scratching device 4 ... Drive wheel
5, 6, 7 ... driven wheel 8 ... chain 9 ... rotation drive means 10 ... scraping plate 16 ... link 17 ... connecting pin 18 ... locking ring 19 ... lock piece 38 ... plate-like portion 32A ... bottom of link
40, 42 ... connecting pin insertion hole 44 ... barrel 50 ... notch 54 ... support body 56 ... rotating shaft
57, 58 ... Drive pin support plate 60 ... Sprocket disc 60A ... Tooth portion 62 ... Drive pin

Claims (3)

The chain consists of a chain and a wheel that engages the chain. The chain is formed by connecting a plurality of links in series with a connecting pin, and a pair of plate portions of each link is formed with a notch on at least the side facing the drive wheel. On the other hand, each of the wheels extends in the axial direction, and is provided at equal intervals in the circumferential direction according to the pitch of the links in the chain, and has a drive pin that engages with the notch during rotation. The drive pin is configured to be able to transmit power by engaging with the notch both during forward rotation and reverse rotation of the wheel, and each link has an opening at least between the pair of plate-shaped portions facing the drive wheel. Formed on the other hand, the wheel extends in the radial direction through the opening, and is provided with teeth that are circumferentially spaced at equal intervals according to the pitch of the link, In the link, the notch is biased to the side of the connecting pin in the chain drive direction. During forward rotation of the wheel, the power from the wheel to the chain by both the engagement between the teeth and the barrel and the engagement between the drive pin and the notch. A chain transmission device in which transmission is performed and power is transmitted from the wheel to the chain by both engagement of the tooth portion and the barrel and engagement of the drive pin and the notch at the time of wheel reverse rotation. 2. The chain transmission according to claim 1 , wherein the notch includes an engagement surface with the drive pin and a flank surface connected to the engagement surface before and after the rotation direction. 3. A sediment scraping device using a chain transmission device according to claim 1 or 2 , wherein the chain is wound endlessly between a driving wheel and a driven wheel in the settling tank, and the driving wheel is connected to a rotational driving means. The chain is driven by the rotation of the drive wheel, and the scraping plate attached to the links spaced in the length direction of the chain circulates in the sedimentation tank in one direction to scrape the sediment. Sediment scraping device.

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