JP5422060B2 - Waste collection device - Google Patents

Description

  The present invention relates to a dust collecting apparatus including a dust loading mechanism that compresses dust thrown from a dust inlet box and pushes it into a dust container.

  Conventionally, a refuse having a rotation support member rotatably supported on the opposite side wall of the dust input box, and a pushing plate supported rotatably about a rotation shaft provided eccentrically with respect to the rotation center of the rotation support member. There is known a so-called planetary rotary push-plate type dust collecting device that includes a loading mechanism and is configured such that the push plate rotates by half in the same direction during one rotation of the rotation support member (for example, a patent Reference 1).

  In this refuse collection device, an embodiment in which the partition plate on the front side of the dust input box is fixed and an embodiment in which the lower part of the partition plate is movable are disclosed. Among these, in the embodiment of the fixed partition plate, the surface of the pushing plate is configured such that the lower end of the partition plate always contacts the surface of the pushing plate regardless of the rotation of the pushing plate. Further, in the embodiment of the movable partition plate, the lower side partition plate is rotatably provided at the lower end of the fixed upper side partition plate, and the lower end of the lower side partition plate is always on the pushing plate by the action of the spring. It is configured to touch. The rotation center of the lower side partition plate is provided at a position far away from the position of the tip edge locus of the push plate.

  As described above, conventionally, the gap between the lower end of the partition plate and the pushing plate is eliminated to prevent the dust in the dust container box from flowing back to the dust input box side.

JP-A-48-100100

  However, in the case of the fixed partition plate of Patent Document 1, it is necessary to form the surface of the push plate smoothly throughout. In this case, if it is going to manufacture an indentation board with a metal, since it is necessary to form by cutting out from a metal lump, or if it is a can-making product, it is necessary to process and form a welded part smoothly, manufacturing cost will increase. It became a factor to become high. Moreover, there existed a problem that a pressing plate and a partition plate interfered with the manufacturing error of a pressing plate, or the deformation | transformation at the time of use.

  On the other hand, even if a slight gap is provided between the lower end of the partition plate and the pushing plate, the gap is sufficiently small with respect to the dust to be loaded, or the gap between the lower end of the partition plate and the pushing plate is covered with an elastic member such as packing. When a biting prevention mechanism is provided separately, it is conceivable that no dust backflow occurs.

  Therefore, it is conceivable to form the push plate so that there is a slight gap between the lower end of the partition plate and the push plate, but the push plate performs a complex motion involving rotation and revolution, so the gap is It was difficult to form properly. For example, even if the lower end position of the partition plate is set so that a desired gap is obtained at a predetermined rotation angle of the push plate, if the push plate rotates from there, the gap disappears and the push plate and the partition plate interfere with each other. There was a case. Moreover, it has been difficult to produce a strong and lightweight pushing plate while appropriately forming the gap.

  When the movable partition plate of Patent Document 1 is used, the lower end of the lower side partition plate is made to follow so as to always contact the surface of the push plate even if the surface shape of the push plate is freely formed to some extent.

  However, in the actual structure of the movable partition plate, the lower radius of the lower partition plate and the range of rotation are large, so the movement of the lower partition plate may not be able to follow the rotation of the push plate, and the dust bites. And backflow problems occurred.

  The present invention has been made in view of such points, and the object of the present invention is to form a gap between the lower end of the fixed partition plate and the pushing plate appropriately, and to be strong and lightweight and easy to manufacture. Another object of the present invention is to provide a planetary rotary push-in plate type dust collecting device equipped with a push-in plate.

  In order to achieve the above object, according to the present invention, the gap between the partition plate and the pushing plate is minimized.

  Specifically, in the first aspect of the present invention, a dust input box connected to the opening of the dust storage box, a partition plate provided on the side of the dust input box facing the opening, and the dust input box The present invention is directed to a dust collecting device that is provided with a dust loading mechanism that is provided and compresses dust thrown from the throwing port of the dust throwing box and pushes the dust into the opening side from below the partition plate.

And the dust loading mechanism is
A rotation support member rotatably supported on the opposite side wall of the dust box,
A pressing plate that is rotatably supported around a rotation axis provided eccentrically with the rotation center of the rotation support member;
The push plate is
The rotation support member is configured to rotate halfway in the same direction during one rotation, and to rotate while the surface faces and approaches the fixed lower end of the partition plate,
The relationship between the amount of eccentricity a from the rotation center of the rotation support member to the axis of the rotation shaft and the distance b from the axis of the rotation shaft to the tip of the push plate is such that b ≧ 2a. Yes.

  According to the above configuration, the relationship between the amount of eccentricity a and the distance b is such that b ≧ 2a, so that the trajectory of the pair of tip edges of the push-in plate does not become a cross loop. This prevents the gap between the lower end of the fixed partition plate and the surface of the push plate from becoming unnecessarily large when the direction connecting the pair of leading edges of the push plate coincides with the extending direction of the partition plate. be able to. As a result, a gap between the lower end of the partition plate and the pushing plate can be appropriately formed. In addition, when the locus of the leading edge of the pushing plate becomes a cross loop, the leading edge of the pushing plate once moved from the downward extension line of the dividing plate to the dust throwing space side will immediately leave a gap with the dividing plate. Since it moves from the downward extension line of the partition plate to the dust container side again while spreading, there is a problem that dust becomes easy to bite. If the pressing plate is formed so as to have a relationship of b ≧ 2a as in the present invention, such a problem does not occur.

In the second invention, in the first invention,
The surface of the push plate is formed using a plurality of plate-like members,
When viewed from the axial direction of the rotary shaft, the plate-like member that is arranged point-symmetrically with the axis of the rotary shaft and that constitutes the pushing surface of the dust is more than the plate-like member that forms the other surface. The structure is also strong.

  According to said structure, while ensuring the intensity | strength of the pushing surface which requires high intensity | strength, the place which does not require high intensity | strength can be reduced in weight to the extent that intensity | strength is weakened, and it can be formed lightweight as the whole pushing board. As a result, a dust collecting device having a strong and lightweight pushing plate is obtained.

In the third invention, in the second invention,
A plurality of ribs are provided inside the push plate, and the rib and the plate-like member are joined to the surface of the surface facing the push surface more firmly.

  According to the above configuration, the number of manufacturing man-hours can be reduced and the weight can be reduced by the small number of joints between the ribs and the plate-like member on the pushing surface side. Further, since only the compressive force is applied to the pushing surface side, deformation of the pushing plate can be sufficiently suppressed even if the number of joints between the rib on the pushing surface side and the plate-like member is small. On the other hand, the surface side facing the pressing surface to which a tensile force is applied can sufficiently secure the strength by strong bonding.

In a fourth invention, in any one of the first to third inventions,
Reinforcing members are respectively attached to the pair of tip portions of the push plate as viewed from the axial direction of the rotating shaft.

  According to the above configuration, it is possible to partially reinforce the front end portion of the pushing plate that requires particularly strong strength, for example, the dust biting occurs between the bottom edge of the dust throwing box and the pushing plate. it can. As a result, a strong and lightweight pushing plate can be formed.

In a fifth invention, in any one of the first to third inventions,
The pushing plate includes the eccentric amount a, the thickness W of the pushing plate, the distance L ₀ between a pair of tip edges of the pushing plate viewed from the axial direction of the rotating shaft, and the dimensions of the pushing plate. And the relationship with the manufacturing error δ is L ₀ = 4a + W + δ,
The position of the lower end of the partition plate is such that the relationship between the distance L ₁ from the lower end to the rotation center, the eccentricity a, the thickness W, and the gap α is L ₁ = a + W / 2 + α + δ. Set,
In the partition switching plate facing the on the surface of the pushing plate, the distance L ₂ from the point through the straight line connecting the lower end and the rotation center of the partition plate to the center of rotation, the rotation of the pressing write plate Regardless, the shape of the surface of the pushing plate is always formed so that 0 <L ₂ ≦ L ₁ . The size of the push plate and the manufacturing error δ are values smaller than the gap α.

  According to the above configuration, the lower end of the fixed partition plate and the push plate are fixed in both cases where the direction connecting the pair of leading edges of the push plate and the extending direction of the partition plate coincide with each other. The gap with the surface can be kept within a predetermined value and its error range. Regardless of the rotation of the push plate, the gap between the lower end of the partition plate and the surface of the push plate can always be kept within the predetermined gap α. As a result, it is possible to provide a dust collecting device that is less susceptible to dust biting and backflow.

  As described above, according to the present invention, in the dust collecting apparatus, the amount of eccentricity a from the rotation center of the rotation support member to the axis of the rotation shaft, and the distance from the axis of the rotation shaft to the tip of the pushing plate By forming the relationship with b so that b ≧ 2a, the trajectory of the pair of tip edges of the push plate is prevented from becoming a cross loop, and the lower end of the fixed partition plate and the push plate in the dust collecting device Can be appropriately formed, and a strong, lightweight and easily manufactured push plate can be provided.

It is a perspective view which shows the outline | summary inside the refuse input box concerning embodiment. It is a side view of a garbage truck. It is a perspective view which shows the state which removed the rear side of the dust input box. It is a side view which shows the drive part and its periphery of a dust loading mechanism. It is the VV line expanded sectional view of FIG. It is a hydraulic circuit diagram of a dust collector. It is a side view which shows a mode that the dust was thrown into the dust throwing-in box in the standby state of the pushing board. It is a side view which shows a mode that a pressing plate rotates, while the surface of a pressing plate adjoins the lower end of a partition plate. It is a side view which shows a mode that a pressing plate rotates further, while the surface of a pressing plate adjoins the lower end of a partition plate. It is a side view when one end of a pushing board has come to a recessed part. It is a side view which shows a mode that dust is further pushed in in a dust storage box from the downward direction of a partition plate, preventing a back flow of dust with a protrusion. It is a perspective view which shows a pushing board. It is a perspective view which shows the state by which two opposite side plate-shaped members were welded by the vertical rib. It is a disassembled perspective view which shows the state which welds a side member and a horizontal rib. It is a disassembled perspective view which shows the state which welds a pressing surface side plate-shaped member and a reinforcement member. It is explanatory drawing which shows the cardioid which is one of the epicycloids. FIG. 17 is a view corresponding to FIG. 16 in a case where the tip edge locus of the pushing plate is a cardioid. FIG. 17 is a view corresponding to FIG. 16 in the case of a pushing plate with b> 2a and L ₀ = 4a + W. FIG. 17 is a view corresponding to FIG. 16 in the case of a pushing plate with b = 2a and L ₀ ≠ 4a + W. FIG. 17 is a view corresponding to FIG. 16 in the case of a pushing plate with b <2a and L ₀ ≠ 4a + W.

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

-Structure of garbage truck-
FIG. 2 shows a refuse collection vehicle 1 provided with a dust collection device according to an embodiment of the present invention. A dust storage box 3 is mounted on a chassis 2 of the dust collection vehicle 1. A driver's cab 2 a is provided on the front side of the chassis 2. The rear opening 4 of the dust container 3 is provided with a dust input box 6 that is pivotally supported by an input box support pin 5 above it. Although not shown in detail, the dust input box 6 is a rotating cylinder 9 (shown in FIG. 3 and the like) that is a hydraulic cylinder (or an electric cylinder) provided between the dust storage box 3 and the dust input box 6. Thus, it is configured to be rotatable around the input box support pin 5. The dust container 3 is configured to be tiltable (can be dumped) around a tilting shaft on the rear side of the chassis 2 by extending and contracting a tilting cylinder 12 (shown only in FIG. 6) provided on the chassis 2.

  As shown in FIG. 1, a throwing port 7 is opened at the rear of the dust throwing box 6, and a dust loading mechanism 20 is provided therein. The dust loading mechanism 20 is for compressing and loading the dust 55 put into the dust throwing box 6 through the loading port 7 into the dust containing box 3.

  A partition plate 21 is provided on the side facing the rear opening 4 in the dust container 6 so as to extend from above. The partition plate 21 partitions the dust input space 6d in the dust input box 6 and the inside of the dust container 3 and, for example, a connecting portion that covers the upper half of the rear opening 4 of the dust container 3. 21a and a lower end portion 21b which is continuous with the connecting portion 21a and is inclined rearwardly downward. The dust 55 is compressed by the dust loading mechanism 20 from below and below the lower end 21c of the lower end 21b of the partition plate 21 and is pushed into the rear opening 4 side.

  As shown in FIGS. 3 to 5, the dust loading mechanism 20 includes a pair of circular rotation support members 22 that are rotatably supported by the pair of opposed side walls 6 a of the dust box 6. . Although various configurations are conceivable as a method of rotating the rotation support member 22, for example, in this embodiment, a drive motor 14 made of a hydraulic motor is attached to the inside of the left and right side walls 6a of the dust box 6, and this drive is performed. A speed reduction mechanism 24 is provided between the drive sprocket 31 provided on the output shaft 14 a of the motor 14 and the rotation support member side sprocket 32 provided on the outer surface of the side wall 6 a of the rotation support member 22. Accordingly, the drive motor 14 is configured to rotate the rotation support member 22 at a predetermined deceleration rate.

  A stepped portion 223 including a small diameter portion 221 and a large diameter portion 222 is formed on the circumferential surface of the circular rotation support member 22. In addition, a hole 224 is provided at the center of rotation on the outer surface of the rotation support member 22. A center shaft 22a is fitted into the hole 224 of the rotation support member 22 through a center hole 32a provided in the rotation support member side sprocket 32, and the rotation support member 22 is rotatably supported by the center shaft 22a.

  A disc-shaped flange 22b is integrally formed on the left and right outer sides of the central shaft 22a, and, for example, four screw holes 22c are formed in the flange 22b. Through holes 6b having an inner diameter slightly larger than the outer diameter of the rotation support member 22 are formed in the left and right side walls 6a concentrically with the central axis 22a, respectively, and a stepped portion 223 of the rotation support member 22 is formed in the through hole 6b. The small-diameter portion 221 is accommodated. A T-shaped fixing bracket 23 (indicated by a two-dot chain line in FIG. 4) is fixed around the through hole 6b in the side wall 6a, and a bolt 22e is inserted into a bolt hole 22d of the fixing bracket 23. The central shaft 22a is fixed to the side wall 6a by fastening to the screw hole 22c. Thereby, the rotation support member 22 is directly supported by the side wall 6a so that the small diameter part 221 of the stepped part 223 can be rotated in the through hole 6b. Moreover, the rotation support member 22 is indirectly supported by the side wall 6a via the fixed bracket 23 and the center shaft 22a. Further, the rotation support member 22 is restricted from moving in the left-right direction by the large-diameter portion 222 of the stepped portion 223 and the central shaft 22a.

  The reduction mechanism 24 includes, for example, a reduction sprocket 24a having an outer diameter larger than that of the drive sprocket 31, and the drive sprocket 31 and the reduction sprocket 24a are connected by a first reduction chain 24b. A sprocket 24c (shown only by a broken line in FIG. 4) on the side wall 6a side (right and left inner side) of the speed reduction sprocket 24a and the rotation support member side sprocket 32 are connected by a second speed reduction chain 24d.

  Between the pair of rotation support members 22, one rotation shaft 25 is rotatably supported at a position eccentric from the center shaft 22a. A push plate 26 extending between the left and right side walls 6a is attached to the rotary shaft 25 so as to be integrally rotated.

  As shown in FIGS. 12 to 15, the pushing plate 26 has a leaf-like form with both ends sharpened with respect to the cross section, and is constituted by, for example, a steel plate can product. Specifically, the surface of the pushing plate 26 is formed by using a plurality of (four in this embodiment) plate-like members 40 and 41. For example, the plate-like members 40 and 41 are press-formed products of steel plates. Further, of the plate-like members 40 and 41, the pressing surface side plate which is disposed point-symmetrically with the axis of the rotating shaft 25 and serves as the pressing surface of the dust 55 when viewed from the axial direction of the rotating shaft 25 of the pressing plate 26. The shaped member 40 is set to have a higher strength than the opposite side plate-like member 41 that forms the other surface 26 a of the pushing plate 26. For example, it is desirable to make the pushing surface side plate-like member 40 a steel plate thicker than the opposite side plate-like member 41 or a high-tensile steel having a high mechanical strength.

  As shown in FIG. 13, the opposite side plate-like member 41 is bent so that the base end portion thereof becomes a vertical rib 43 a extending in the axial direction of the pushing plate 26. The two opposite plate-like members 41 are firmly joined by welding or the like at the portion of the vertical rib 43a. A plurality of bent portions 41a extending in the axial direction are formed at predetermined intervals in a portion of the opposite side plate-like member 41 forming the surface 26a. Further, as shown in FIG. 14, the vertical ribs 43 b having a U-shaped cross section are joined to the back surface of the opposite plate-like member 41 by welding or the like so as to be aligned at the bent portion 41 a. Here, since there is sufficient space for inserting the welding rod, the opposite plate-like member 41 and the vertical rib 43b are firmly welded. Further, the opposite side plate-like member 41 and the vertical rib 43b are firmly welded to the side member 47 including the boss portion 46, and the opposite side plate-like member 41 includes a plurality of trapezoidal transverse ribs extending perpendicularly in the axial direction. Both 44 are firmly welded.

  On the other hand, as shown in FIG. 15, when welding the pressing surface side plate-like member 40, the opposite side plate-like member 41 has already closed the opposite side, so welding with the vertical rib 43 b and the horizontal rib 44 is sufficient. Can not do. For this reason, for example, an opening (not shown) is provided on the pressing surface side plate-like member 40 side, and from that portion, welding with the vertical rib 43b and the horizontal rib 44 or keyhole welding is performed. It is desirable to perform welding. As a result, the manufacturing man-hours can be reduced and the weight can be reduced by the amount of welding points between the pressing surface side plate-like member 40 and the vertical ribs 43b and the horizontal ribs 44. Since only the compressive force is applied to the pressing surface side plate-like member 40, the deformation of the pressing plate 26 can be sufficiently suppressed even if there are few welded portions between the pressing surface side plate-like member 40 and the vertical ribs 43b and the horizontal ribs 44. On the other hand, since the opposite side plate-like member 41 to which a tensile force is applied is sufficiently welded, the strength is sufficiently ensured.

  Further, as shown in FIG. 15, reinforcing members 45 each having a substantially L-shaped cross section are welded to the pair of tip portions of the push plate 26. The reinforcing member 45 may be detachably attached so that it can be replaced when worn or damaged. It is possible to partially reinforce the distal end portion of the pushing plate 26 that requires particularly strong strength, such as the biting of the dust 55 between the throwing edge side edge at the bottom of the dust throwing box 6 and the pushing plate 26. Since the reinforcing member 45 covers the joint surface between the pressing surface side plate-like member 40 and the opposite side plate-like member 41, the strength and rigidity of the pressing plate 26 are improved. The reinforcement member 45 can suppress an increase in the entire mass by increasing the area on the side of the pressing surface side plate-like member 40 to which the compressive force is applied and decreasing the opposite side. As a result, a strong and lightweight pushing plate 26 can be formed. If only the reinforcing member 45 can be replaced, it is not necessary to replace the entire pushing plate 26, and repair is easy and desirable.

  Then, on the pair of surfaces 26a facing the thickness direction of the pushing plate 26 manufactured in this way, as shown in FIG. 1 and the like, respectively, in the axial direction of the rotating shaft 25 (vehicle width direction, left-right direction). A plurality of (in the present embodiment, 14) protrusions 33 are arranged at intervals. In this embodiment, each protrusion 33 has substantially the same shape, and is formed so as to extend in a direction orthogonal to the axial direction of the rotating shaft 25. Further, the protrusion 33 has an arcuate outer peripheral edge in which the height from the surface 26a of the pushing plate 26 gradually changes when viewed from the axial direction. Correspondingly, a notch 34 through which each protrusion 33 passes is formed at the lower end 21 b of the partition plate 21. The cross-sectional shape of the protrusion 33 of the present embodiment is a thin plate shape, but is not limited to this, and the cross-sectional shape may be a triangle or a trapezoid in order to improve the strength. In addition, unevenness may be integrally formed on the surface of the pressing plate 26 by pressing, casting, or the like, and the protrusion 33 may be configured by the protruding portion. The protrusion 33 is joined to the surface 26a by welding or the like.

  As shown in FIGS. 3 and 4, the rotation shaft 25 is configured to rotate half in the same direction while the rotation support member 22 makes one rotation by the pushing plate reduction mechanism 27 provided at the end thereof. Has been. Specifically, in the push-in plate speed reduction mechanism 27, a first sprocket 27a that is rotated and integrated with the central shaft 22a, a second sprocket 27b that is rotated and integrated with the rotary shaft 25, and an idler sprocket 28a of the auto tensioner 28 are adjusted for rotation. It is connected by a chain 27c. A lever-shaped auto tensioner main body 28b of the auto tensioner 28 is rotatably supported on the rotation support member side sprocket 32 around the rotation pin 28c, and the tension of the rotation adjusting chain 27c is adjusted by adjusting the rotation amount adjusting bolt 28d. Can be adjusted. The auto tensioner body 28b is fixed to the rotation support member side sprocket 32 by a fixing nut 28e after tension adjustment. The ratio of the pitch circle diameter of the first sprocket 27a and the pitch circle diameter of the second sprocket 27b is 1: 2. In the drawings, each chain and each sprocket are depicted in a simplified manner.

  Accordingly, as shown in FIGS. 7 to 11, the pair of tip edge trajectories of the pushing plate 26 viewed from the axis of the rotating shaft 25 has a so-called cardioid curve 29 b and a substantially cardioid curve 29 c similar thereto. It comes to draw. The cardioid curve 29b and the substantially cardioid curve 29c are heart-shaped trajectories, and these trajectories form the bottom of the dust throwing space 6d and follow the arc-shaped wall 6c as viewed from the left and right side surfaces of the vehicle. By arranging in this way, the pushing plate 26 is configured to be surely pushed down the partition plate 21 while compressing the dust 55 put into the bottom of the dust throwing space portion 6d.

  As described above, in the present embodiment, the circular rotation support member 22 fitted into the through hole 6b of the side wall 6a is used as a mechanism for drawing the cardioid curve 29b and the substantially cardioid curve 29c on the tip edge of the pushing plate 26. Use. The circular rotation support member 22 is fitted into the through-hole 6b, so that the following problem is solved as compared with a case where a rod-shaped rotation support member is attached between the side wall 6a and the pushing plate 26 (see Patent Document 1). Has been. That is, the rod-shaped rotation support member has a problem that the effective length of the push-in plate in the direction of the rotation axis is short, but the circular rotation support member 22 can increase the effective length. Further, in the rod-shaped rotation support member, there is a problem that a gap is formed between the side wall 6a and the pushing plate 26, and the dust easily flows backward. However, in the circular rotation support member 22, there is a gap between the side wall 6a and the pushing plate 26. Can be made as small as possible. In addition, the rod-shaped rotation support member has a problem of being easily twisted, but the circular rotation support member 22 is less likely to be twisted, and the rotation of the pushing plate 26 can be stabilized.

  Next, the cardioid curve 29b and the substantially cardioid curve 29c have a concave portion (recess 29a). In this embodiment, the recess 29a substantially coincides with the lower end 21c of the lower end 21b of the partition plate 21. Placed in position. Therefore, for example, in the standby state shown in FIG. 7, the longitudinal center of the pushing plate 26 viewed from the axial direction of the rotating shaft 25 is close to the lower end 21 c, and in the state shown in FIG. 10, the leading edge of the pushing plate 26 Is close to the lower end 21c, and the gap with the lower end 21c is eliminated as much as possible during the rotation of the pushing plate 26. In order to do this, a predetermined relational expression must be considered for the position of the lower end 21c of the partition plate 21 and the shape of the push plate 26.

First, epicycloids and cardioids will be described. As shown in FIG. 16, while circumscribing the circle _{C a} radius _r 1 -r _2, when the circle _{C r2} of the radius _{r 2} is gradually rotated without slipping, moving points on the circumference of radius _{r 2} P The curve drawn by is called epicycloid. 16, the circle _{C r2} rotates while circumscribing the circle _{C a,} the center T of the circle _{C r2} is to come to a position such that ∠TOD = θ _r1. At this time, the point on the circle C _r2 that was first in contact with the circle C _a at the point A comes to the point P ₁ . Since the moving point P moves so that the line segment PP ₁ has the diameter of the circle C _r2 , the moving point P reaches a position where ∠PTB ′ = θ _r1 + θ _r2 .

At this time, since the circle C _a and the circle C _r2 always move so as to contact each other, the lengths of the arc DV and the arc P ₁ V are equal. Therefore, since the arc DV = (r ₁ −r ₂ ) θ _r1 and the arc P ₁ V = r ₂ θ _r2 , (r ₁ −r ₂ ) θ _r1 = r ₂ θ _r2 and θ _r2 = (( r ₁ −r ₂ ) / r ₂ ) θ _r1 is obtained, and the following equation (1) is established.

When the circle C _r2 makes one round around the circle C _a , the moving point P makes two turns and returns to the point A. When θ _r1 = 2π, ∠PTB ′ = (r ₁ / r ₂ ) θ _r1 is 4π. From equation (1), it becomes _{(r 1 / r 2) ×} 2π = 4π, r 2 = r 1/2, ∠PTB' = 2θ r1 is obtained.

Since the center T of the circle C _r2 is located on the circumference of the radius r _{1 by} an angle θ _r1 from the x axis, the vector OT = r ₁ (cos θ _r1 , sin θ _r1 ).

Moving point P is, since the upper circumference of radius _r 2 = _{r 1/2} circle _{C r2} in a position turned by an angle θ _r1 + θ _r2 = 2θ _r1 from B', vector _{TP = (r 1/2)} ( cos2θ _r1 , sin2θ _r1 ).

Therefore, the vector OT + vector TP = (r ₁ (cos θ _r1 + (1/2) cos 2θ _r1 ), r ₁ (sin θ _r1 + (1/2) sin 2θ _r1 )), from which the x coordinate of the point P The following formula (2) is established for the y coordinate.

Expression (2) is an expression generally called a cardioid parameter display in mathematics. The trajectory represented by Expression (2) has a vertically symmetric shape in the range of 0 ≦ θ _r1 ≦ 2π. In FIG. 16, the recess has a shape facing left.

Next, an expression representing half of the cardioid in the range of 0 ≦ θ _r1 ≦ 2π will be described. In the equation (1), consider a case where the moving point P makes one turn and returns to the point A when the circle C _r2 makes two turns around the circle C _a . In this case, when the circle C _r2 makes one turn around the circle C _a , the moving point P makes a half turn, meaning that a half shape of the cardioid is drawn in the range of 0 ≦ θ _r1 ≦ 2π. become. That is, when θ _r1 = 4π, ∠PTB ′ = (r ₁ / r ₂ ) θ _r1 becomes 2π. From equation (1), (r ₁ / r ₂ ) × 4π = 2ππr ₂ = 2r ₁ , and PTB ′ = θ _r1 / 2.

Since the center T of the circle C _r2 is located on the circumference of the radius r _{1 by} an angle θ _r1 from the x axis, the vector OT = r ₁ (cos θ _r1 , sin θ _r1 ).

Since the moving point P is located at a position that is rotated by θ _r1 + θ _r2 = θ _r1 / 2 from A ′ on the circumference of a circle C _r2 having a radius r ₂ = 2r ₁ , the vector TP = 2r ₁ (cos (θ _r1 / 2), sin (θ _r1 / 2)). From this, the vector OT + vector TP = (r ₁ (cos θ _r1 +2 cos (θ _r1 / 2)), r ₁ (sin θ _r1 +2 sin (θ _r1 / 2))) holds.

  Thus, the following equation (3) is established for the x coordinate and y coordinate of the point P.

Next, consider the locus of the leading edge of the pushing plate 26. The pushing plate 26 of the dust collecting device revolves around the revolution center O and rotates in the same direction as the revolution direction at half the revolution speed. As shown in FIG. 17, the rotation center of the push plate 26 is S, the eccentric distance of the push plate 26 is a, the length from the rotation center of the push plate 26 to the tip is b, and the tip of the push plate 26 is P. The angle is θ _r1 and the rotation angle is θ _r2 .

At this time, the vector OS = a (cos θ _r1 , sin θ _r1 ), the vector SP = b (cos θ _r2 , sin θ _r2 ), and the coordinates of the point P are calculated from the vector sum of the vector OS and the vector SP, and the vector OP = vector OS + vector SP = the _{(acosθ r1 + bcosθ r2, asinθ} r1 + bsinθ r2).

  Therefore, the xy coordinates of the point P are expressed by the following formula (4).

It is expressed.

In the equation (4), θ _r2 = θ _r1 / 2, so the following equation (5) is obtained.

Since the above formula (3) and formula (5) represent the x coordinate and y coordinate of the same point P, when the two formulas are compared, the following formula (6) is obtained from a = r ₁ and b = 2r _1. can get.

That is, when the length b from the rotation center to the tip of the push plate 26 is twice the eccentric distance a, the tip edge P of the push plate 26 is the locus of the upper half of the cardioid in the range of 0 ≦ θ _r1 ≦ 2π. Will be drawn.

Here, if the point Q, which is point-symmetric with the tip edge P of the pushing plate 26 with respect to the revolution center O, is considered in the same manner as the point P, the lower half of the cardioid is drawn in the range of 0 ≦ θ _r1 ≦ 2π. become.

Thus, the point P and the point Q are combined to draw a complete cardioid locus. When θ _r1 = 2π, the positions of the point P and the point Q are interchanged with the case where θ _r1 = 0.

Next, when the length of the SP is obtained, the coordinates of the point S are (acos θ _r1 , asin θ _r1 ), so the following equation (7) is established.

  Thereby, it can be seen that the length of SP always maintains 2a irrespective of the revolution angle and the rotation angle of the push-in plate 26.

Similarly, since the length of SQ can be calculated as 2a, it can be seen that the length of PQ always maintains 4a regardless of the revolution angle and rotation angle of the push-in plate 26. This indicates that the pushing plate 26 with the total length L ₀ = 4a rotates so that its two leading edges always move on the cardioid curve 29b.

  Next, the basic formula of the tip edge locus of the pushing plate 26 will be described. That is, as shown in FIG. 18, consider the case of b> 2a in equation (5). The partition plate 21 is disposed on the x axis so as to extend in the x axis direction.

  In this case, it can be expressed as b = 2a + c. By substituting this into equation (5), the x-coordinate and y-coordinate of the point P are expressed by the following equation (8).

The length of the _{SP, SP = √ ((acosθ r1} + (2a + c) cos (θ r1 / 2) -acosθ r1) 2 + (asinθ r1 + (2a + c) sin (θ r1 / 2) -asinθ r1) 2) = √ ((2a + c) ² (cos ² (θ _r1 / 2) + sin ² (θ _r1 / 2)) = √ (2a + c) ² = 2a + c, whereby the length of SP is the revolution angle of the pushing plate 26 It can be seen that 2a + c is always maintained regardless of the rotation angle.

  Similarly, since the length of SQ can be calculated as 2a + c, it can be seen that the length of PQ always maintains 4a + 2c regardless of the revolution angle and rotation angle of the push-in plate 26.

Accordingly, the total length L ₀ of the pushing plate 26 is expressed by the following equation (9).

The two leading edges always move on the same substantially cardioid curve 29c.

When the total length L ₀ of the pushing plate 26 is set in the equation (9), the x coordinate and the y coordinate of the pushing plate 26 take the following values according to the change of θ _r1 from the equation (8).

If θ _r1 = 0, x = cos (0) + (2a + c) cos (0) = a × 1 + (2a + c) × (1) = 3a + c and y = asin (0) + (2a + c) sin (0) = A * (0) + (2a + c) * 0 = 0.

If θ _r1 = π, then x = acos (π) + (2a + c) cos (π / 2) = a × (−1) + (2a + c) × 0 = −a and y = asin (π) + (2a + c ) Sin (π / 2) = a × 0 + (2a + c) × 1 = 2a + c.

If θ _r1 = 2π, the following formula (10) is established.

Next, not only the movement of the leading edges P and Q of the pushing plate 26 but also the width W of the pushing plate 26 will be considered. W is set so that the gap α between the push plate 26 and the partition plate 21 is appropriate when θ _r1 = π where the longitudinal direction of the push plate 26 is parallel to the y-axis direction. When θ _r1 = π, the x-coordinate and y-coordinate of the rotation center S ′ of the pushing plate 26 are expressed as x = −a, y = 0, and therefore the surface of the pushing plate 26 facing the partition plate 21 and x The x coordinate and y coordinate of the intersection with the axis are expressed by the following equation (11).

Next, when θ _r1 = 2π where the longitudinal direction of the pushing plate 26 is parallel to the x-axis direction, the clearance between the pushing plate 26 and the partition plate 21 is set to be the same as when θ _r1 = π. Then, the relational expression of -ac = -aW / 2 needs to be established from the expressions (10) and (11).

  Therefore, the following formula (12) is established.

c = W / 2 (12)
As a result, from Equation (9) and Equation (12),

If this is the case, the gap α between the pushing plate 26 and the partition plate 21 can be set to be the same regardless of whether the longitudinal direction of the pushing plate 26 is parallel to the x-axis direction or parallel to the y-axis direction. I understand. For this reason, it is theoretically understood that satisfying the equation (13) is desirable in terms of managing the gap between the partition plate 21 and the pushing plate 26.

Then, change in the shape of the pushing plate 26 due to the values of b and L ₀ will be described.

First, as shown in FIG. 19, in the case of the pushing plate 26 with b = 2a and L ₀ ≠ 4a + W, when θ _r1 = π where the longitudinal direction of the pushing plate 26 is parallel to the y-axis direction, The coordinates of the intersection of the surface of the pushing plate 26 on the 21st side and the x-axis are (−a−W / 2, 0), and the gap with the partition plate 21 is α.

On the other hand, when θ _r1 = 0, 2π in which the longitudinal direction of the pushing plate 26 is parallel to the x-axis direction, the coordinates of the leading edge of the pushing plate 26 on the partition plate 21 side are (−a, 0), The gap with the partition plate 21 is α + W / 2.

In the case of b = 2a, L ₀ = 4a from FIG. 19, and therefore the width of the pushing plate 26 cannot be set so that L ₀ = 4a + W. In addition, when the longitudinal direction of the pushing plate 26 is parallel to the y-axis direction and when it is parallel to the x-axis direction, a difference of W / 2 occurs in the gap with the partition plate 21. However, if the width W is formed as thin as possible, the gap difference can be reduced.

Next, the case of the pushing plate 26 with b> 2a and L ₀ = 4a + W shown in FIG. 18 will be briefly described. When θ _r1 = π in which the longitudinal direction of the pushing plate 26 is parallel to the y-axis direction, the partitioning is performed. The coordinates of the intersection of the surface of the pushing plate 26 on the plate 21 side and the x axis are (−a−W / 2, 0), and the gap with the partition plate 21 is α. On the other hand, when θ _r1 = 0, 2π in which the longitudinal direction of the pushing plate 26 is parallel to the x-axis direction, the coordinates of the leading edge of the pushing plate 26 on the partition plate 21 side are (−W / 2, 0). Thus, the gap with the partition plate 21 is α.

Although not shown, the case of the pushing plate 26 where b> 2a and L ₀ ≠ 4a + W will be briefly described. In this case, when θ _r1 = π where the longitudinal direction of the pushing plate 26 is parallel to the y-axis direction, the coordinates of the intersection of the surface of the pushing plate 26 on the partition plate 21 side and the x axis are (−a−W / 2, 0), and the gap with the partition plate 21 is α. On the other hand, when θ _r1 = 0, 2π in which the longitudinal direction of the pushing plate 26 is parallel to the x-axis direction, the coordinates of the leading edge of the pushing plate 26 on the partition plate 21 side are (−W / 2, 0). The gap with the partition plate 21 is α + γ. That is, a difference of γ occurs in the gap with the partition plate 21 when the longitudinal direction of the push plate 26 is parallel to the y-axis direction and when it is parallel to the x-axis direction.

  In the case of b> 2a, as the value of b increases, the approximate cardioid curve 29c becomes closer to a circle (not shown) with the concave portion becoming gentler.

Next, as shown in FIG. 20, consider the case of the pushing plate 26 where b <2a and L ₀ ≠ 4a + W. In this case, in Formula (5), it can represent with b = 2a-c. By substituting this into equation (5), the x-coordinate and y-coordinate of the point P are expressed by the following equation (14).

It is expressed.

At this time, SP = √ ((acos θ _r1 + (2a−c) cos (θ _r1 / 2) −acos θ _r1 ) ² + (asin θ _r1 + (2a−c) sin (θ _r1 / 2) −asin θ _r1 ) ² ) = √ ((2a−c) ² (cos ² (θ _r1 / 2) + sin ² (θ _r1 / 2)) = √ (2a−c) ² = 2a−c.

  Thereby, it can be seen that the length of the SP always maintains 2a-c regardless of the revolution angle and the rotation angle of the pushing plate 26.

  Similarly, since the length of SQ can be calculated as 2a-c, it can be seen that the length of PQ always maintains 4a-2c regardless of the revolution angle and rotation angle of the push-in plate 26.

  Accordingly, the total length of the pushing plate 26 is expressed by the following equation (15).

If set to, the two leading edges always move on the same curve. The curve becomes a cross loop 29d (a form of so-called Limason).

When the total length of the pressing plate 26 is set to the total length L ₀ = 4a-2c, the x coordinate and y coordinate of the pressing plate 26 take the following values according to the change of θ _r1 from the equation (8).

If θ _r1 = 0, x = cos (0) + (2a−c) cos (0) = a × 1 + (2a−c) × (1) = 3a−c and y = asin (0) + ( 2a−c) sin (0) = a × (0) + (2a−c) × 0 = 0,
If θ _r1 = π, then x = acos (π) + (2a−c) cos (π / 2) = a × (−1) + (2a−c) × 0 = −a and y = asin (π ) + (2a−c) sin (π / 2) = a × 0 + (2a−c) × 1 = 2a−c.

When θ _r1 = 2π, the following equation (16) is established.

  As shown in FIG. 20, when the trajectory of the pair of leading edges of the push plate 26 is an intersecting loop 29 d, the direction connecting the pair of leading edges of the push plate 26 matches the extending direction of the partition plate 21. In addition, the gap between the lower end of the fixed partition plate 21 and the surface of the pushing plate 26 becomes larger than necessary. That is, as compared with the case of b = 2a, an extra gap β (β = W / 2 in FIG. 20) due to the intersection of the intersection loop 29d in FIG. 20 is generated. The thickness W of the pushing plate 26 is necessary to some extent for securing the strength, and there is a limit to reducing it. Further, when the locus of the leading edge of the pushing plate 26 becomes an intersecting loop 29d, the dust throwing space 6d side (for example, the x axis in FIG. 20) from the lower extension line of the partition plate 21 (on the x axis in FIG. 20) once. The tip edge of the pushing plate 26 that has moved to the lower region) immediately expands the gap with the partition plate 21 immediately after that, again from the downward extension line of the partition plate 21 (for example, the x-axis in FIG. 20). Since there is a problem that the dust is easily bitten. From this, it can be seen that the generation of the gap β due to the intersection of the intersection loop 29d is a big problem.

As described above, it is ideal that the relationship of Expression (13) is established, but in reality, a dimensional error and a manufacturing error δ occur in the push plate 26. For this reason, in this embodiment, as shown in FIG. 18, the pushing plate 26 includes an eccentric amount a from the rotation center of the rotation support member 22 to the rotating shaft 25, a thickness W of the pushing plate 26, and a pair of tips. The relationship between the distance (overall length) L ₀ between the edges, the size of the pushing plate 26 and the manufacturing error δ is expressed by the following equation (17).

  The size and the manufacturing error δ are of a size that can occur in a normal manufacturing process, and means that some error is allowed in the equation (17).

The position of the lower end 21c of the partition plate 21, the distance L ₁ to the rotational center from the lower end 21c, and eccentricity a, and the thickness W, and the gap alpha, sized and manufacturing error δ of push plate 26 The relationship is set so as to be the following expression (18).

  Here, the gap α takes into consideration the dimensional error of the constituent members and the minimum diameter of the target dust as the lower end 21c of the metal portion of the partition plate 21 and the metal surface of the push plate 26 move relatively smoothly. To a predetermined value. For example, the gap α is set to 0 mm <α ≦ 50 mm, but preferably 2 mm ≦ α ≦ 20 mm. Even in the case where the gap α is formed, by attaching a packing to the lower end portion 21b of the metal portion of the partition plate 21, the lower end 21c of the metal portion of the partition plate 21 and the metal of the pushing plate 26 are made. It is possible to substantially eliminate the gap between the front surface 26a.

  In the present embodiment, the pair of surfaces 26a facing the thickness direction of the push plate 26 are arcuate when viewed from the axial direction of the rotating shaft 25. The shape of the surfaces is expressed by the following relational expression. Is to be determined by.

That is, on the surface 26a of the push plate 26 facing the partition plate 21, the distance L ₂ from the point through the straight line connecting the rotational center of the rotary support member 22 and the lower end 21c of the partition plate 21 to the center of rotation, The shape of the surface 26a of the pushing plate 26 is formed so that the following equation (3) is always obtained regardless of the rotation of the pushing plate 26. Thereby, the surface 26a of the pushing plate 26 is not smoothly formed, and even if there are bent portions in the plate-like members 40 and 41 forming the surface 26a, a gap is not generated more than necessary.

  From the above description, the amount of eccentricity a from the rotation center of the rotation support member 22 to the axis of the rotary shaft 25 of the push plate 26 and the distance b from the axis of the rotary shaft 25 to the tip of the push plate 26. It can be seen that it is desirable to form the pushing plate 26 so that the relationship is b ≧ 2a. By maintaining this relationship, it is possible to avoid the trajectory of the pair of tip edges of the push-in plate 26 from becoming a cross loop 29d as shown in FIG. As a result, it is possible to prevent the movement of the pushing plate 26 that promotes the excessive gap β and the biting of dust described above. As a result, a dust collecting device in which a gap between the lower end of the partition plate 21 and the pushing plate 26 is appropriately formed can be obtained.

  Next, although not shown in detail, the overall configuration of the garbage truck 1 will be described. The garbage collection vehicle 1 includes a generator driven by a vehicle engine, and is configured such that electric power obtained by the generator or electric power stored in a power storage device is supplied to the electric motor 56. FIG. 6 shows a hydraulic circuit 61 of the hydraulic device 60 of the garbage truck 1. The hydraulic device 60 includes a hydraulic pump 57 that is driven by an electric motor 56. The hydraulic oil in the hydraulic oil tank 62 is configured to be sucked up by a hydraulic pump 57 through a hydraulic pipe 64 and distributed to the supply-side hydraulic pipe 61 a and supplied to the control valve 63. The cylinders 9 and 12 and the drive motor 14 are connected to the control valve 63 via a hydraulic pipe 61b. The control valve 63 includes a plurality of solenoid valves (not shown). By switching the opening / closing ports of the solenoid valves, the hydraulic oil discharged from the hydraulic pump 57 rotated by driving the electric motor 56 is supplied to the desired cylinders 9 and 12. Alternatively, it is configured to supply to the drive motor 14. Thus, the switching of the expansion and contraction operations of the cylinders 9 and 12 and the rotation of the drive motor 14 are controlled via the control valve 63, or the operation is stopped. In the garbage collection vehicle 1 of this embodiment, only one drive motor 14 is driven during the dust loading operation, and the dust is loaded like a general press-type dust collection vehicle or a rotary plate-type dust collection vehicle. There is no need for multiple actuators during work.

-How to collect dust with a garbage truck-
First, the refuse collection vehicle 1 moves to the collection place of the dust 55 and opens the insertion port 7.

  Next, as shown in FIG. 7, the center surface 26 a in the longitudinal direction viewed from the axial direction of the push plate 26 is close to the lower end 21 c of the partition plate 21, and one tip edge of the push plate 26 is the back side of the wall surface 6 c. The state located near the end is the standby state. In this standby state, the lower part of the partition plate 21 is blocked, so that the dust 55 pushed into the dust container 3 does not flow back to the dust input box 6 again. In this state, the dust 55 is thrown into the bottom of the dust throwing space 6 d, that is, below the pushing plate 26. At this time, unlike the rotary plate-type dust collecting vehicle in which the position of the rotary shaft is constant, when the dust 55 is thrown in, the rotary shaft 25 of the push plate 26 moves to the dust container 3 side, and the push plate 26 is far from the feed port 7. Therefore, it is possible to throw in the dust 55 having a larger volume than the rotating plate type garbage truck. Moreover, since the bottom of the insertion port 7 is set low by adjusting the trajectory of the pushing plate 26, the dust 55 is easily introduced.

  Next, when the drive motor 14 is rotated, the rotation support member 22 rotates clockwise in FIG. 7, and the pushing plate 26 rotates clockwise at half the speed by the action of the pushing plate reduction mechanism 27. To do. Then, as shown in FIG.8 and FIG.9, the pushing board 26 rotates to the insertion port 7 side. At this time, since the concave portion 29 a of the substantially cardioid curve 29 substantially coincides with the lower end 21 c of the partition plate 21, the dust 55 is difficult to bite between the lower end 21 c and the surface 26 a of the pushing plate 26. In addition, since the protrusion 33 pushes the dust 55 and does not approach the lower end 21c, the dust 55 is prevented from being bitten more effectively.

  When the pushing plate 26 further rotates, as shown in FIGS. 10 and 11, the dust 55 is reliably pushed into the dust container 3 from the rear opening 4 through the lower side 21 c of the partition plate 21 by the protrusion 33. . At this time, the pushing plate 26 and the ridge 33 move so as to approach the wall surface 6c forming the bottom of the dust throwing space portion 6d, so that the function of compressing the dust 55 can be achieved while only rotating the pushing plate 26. Demonstrated.

  Thus, by projecting the protrusion 33 from each surface 26a of the pushing plate 26, when the pushing plate 26 rotates, the surface 26a of the pushing plate 26 forms a gap between the lower end 21c of the partition plate 21 and the pushing plate 26. On the other hand, the dust 55 once pushed into the dust container 3 side can be pushed by the ridge 33 and floated from the surface 26 a of the pushing plate 26. Moreover, since the protrusion 33 moves in the notch 34 of the partition plate 21, even if the protrusion 33 is enlarged, the rotation of the pushing plate 26 is not hindered.

  Next, the pushing plate 26 makes a half turn and returns to the state of FIG. 7, and the operation from FIG. 7 is repeated on the opposite surface 26a side.

  In this embodiment, compared with a general rotary plate type having a push plate for pushing in the dust 55 and a rotary plate for scraping up the dust 55, a single push plate 26 can exert a scraping function and a push function. Therefore, the number of actuators such as hydraulic cylinders can be reduced. By reducing the number of actuators, the weight of the apparatus is reduced, and the load capacity can be increased by the reduction in the weight of the apparatus.

  In addition, in the conventional rotating plate type garbage truck until now, the dust 55 was loaded by two members, the pushing plate and the rotating plate, but in the so-called planetary rotating pushing plate type garbage collecting vehicle 1 of this embodiment, there is one sheet. Since the dust 55 is loaded only by the pushing plate 26, the rotation speed of the pushing plate 26 can be reduced in the same cycle time as compared with the rotating plate type garbage truck. Further, since there is no reversing and lowering operation of the conventional press-type dust collecting vehicle and pushing-in operation of the pushing plate of the rotary plate-type dust collecting vehicle, no waiting time is generated in the loading operation of the dust 55.

  In addition, since this embodiment is only a rotary motion, there is less shock and lower noise compared to the press type and rotary plate type using a cylinder, and since there is no switching of the solenoid valve during loading operation, it becomes low noise, Efficiency is good. In addition, there is an advantage that complicated control such as shockless control and switching control is unnecessary.

  Therefore, the dust 55 can be efficiently pushed into the dust storage box 3 with a simple configuration while preventing the dust 55 from backflowing and biting.

(Other embodiments)
The present invention may be configured as follows with respect to the above embodiment.

  That is, in the above-described embodiment, the example in which the dust collecting device is provided in the electric dust collecting vehicle 1 is shown. However, the dust collecting device may be fixedly installed on the floor of a building or a factory. Specifically, the dust collecting device may be placed not on the body frame 2b but on a frame placed on the floor.

  In the above embodiment, the shape of the push plate 26 is formed by joining a plurality of plate-like members 40 and 41 mainly using welding. However, even if a plurality of plate-like members are joined using rivets, Good.

  Moreover, a pipe material may be arrange | positioned in the position used as a pair of front-end edge and center part of a pushing board, and they may be joined with a plate-shaped member, and a pushing board may be formed.

  Moreover, in the said embodiment, although the bending part 41a extended in the axial direction of the pressing board 26 was formed in the plate-shaped members 40 and 41, even if it forms the surface of a pressing board in a smooth curved surface without providing a bending part. Good.

  In the above embodiment, the mechanism for driving the pushing plate 26 is a chain mechanism. However, the gear may be driven directly.

  In the above embodiment, an example of the dust collection vehicle 1 that drives the hydraulic pump using an electric motor is shown. However, the dust collection device is not an electric motor, but uses the driving force of the engine via a power take-out device (PTO). It may be removed from the hydraulic pump. Regarding the method for driving the rotation support member 22, in the present embodiment, the power of the hydraulic drive motor 14 is decelerated and driven, but the power of the electric motor 56 may be used. The power source of the drive motor 14 and the electric motor 56 is not particularly limited.

  Moreover, in the said embodiment, although the drive motor 14 was attached to the inner side of one side wall on either side, you may provide a drive motor in both the side walls on either side. Further, a planetary gear reducer unit may be interposed between the output shaft 14 a of the drive motor 14 and the drive sprocket 31.

  Instead of providing the tilt cylinder 12 and dumping the dust storage box 3 as in the above embodiment, the dust storage box 3 may be provided with a discharge device for discharging the dust in the dust storage box 3. Specifically, a discharge plate may be slidable in the front-rear direction in the dust storage box 3, and may be slid back and forth in the dust storage box 3 by an expansion / contraction operation of the discharge cylinder.

  In the said embodiment, although the rotation support member is comprised with the disc, you may comprise with a rod-shaped and plate-shaped link. In short, any member may be used as long as it rotates around the central axis 22a and supports the rotary shaft 25 at a position eccentric from the central axis 22a.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or a use.

  As described above, the present invention relates to a dust collecting apparatus for mounting having a dust loading mechanism that compresses the dust thrown in from the inlet of the dust throwing box and pushes it into the dust containing box, and this dust collecting apparatus. This is useful for garbage trucks and the like provided at the rear of the vehicle body.

DESCRIPTION OF SYMBOLS 1 Dust collection truck 3 Dust storage box 4 Rear opening 6 Dust input box 20 Dust loading mechanism 21 Partition plate 22 Rotation support member 22a Central axis (rotation center)
25 Rotating shaft 26 Pushing plate 26a Surface 40 Pushing surface side plate-like member 41 Opposite side plate-like member 43 Vertical rib 44 Horizontal rib 45 Reinforcing member 55 Dust L ₀ Distance between a pair of leading edges of the pushing plate L ₁ Rotating from the lower end of the partition plate Distance to the rotation center of the support member L2 From the point passing on the straight line connecting the lower end of the partition plate and the rotation center of the rotation support member on the surface of the pressing plate facing the partition plate _{2 to} the rotation center of the rotation support member Distance P Eccentricity from the rotation center of the rotation support member to the rotation axis of the pushing plate W Thickness of the pushing plate α Clearance δ Dimensions and manufacturing error of the pushing plate

Claims (5)

A dust input box connected to the opening of the dust storage box, a partition plate provided on the side of the dust input box facing the opening, and a dust input box provided in the dust input box, from the input of the dust input box A dust collecting device comprising a dust loading mechanism that compresses the charged dust and pushes it into the opening side from below the partition plate,
The above dust loading mechanism is
A rotation support member rotatably supported on the opposite side wall of the dust box,
A pressing plate that is rotatably supported around a rotation axis provided eccentrically with the rotation center of the rotation support member;
The push plate is
The rotation support member is configured to rotate halfway in the same direction during one rotation, and the surface rotates while facing and approaching the lower end of the partition plate,
The relationship between the amount of eccentricity a from the rotation center of the rotation support member to the axis of the rotation shaft and the distance b from the axis of the rotation shaft to the tip of the push plate is such that b ≧ 2a. A dust collecting device characterized by comprising: In the refuse collection device according to claim 1,
The surface of the push plate is formed using a plurality of plate-like members,
When viewed from the axial direction of the rotary shaft, the plate-like member that is arranged point-symmetrically with the axis of the rotary shaft and that constitutes the pushing surface of the dust is more than the plate-like member that forms the other surface. Dust collection device characterized by high strength. In the refuse collection device according to claim 2,
A plurality of ribs are provided in the inside of the pushing plate, and the rib and the plate-like member are joined firmly on the surface of the surface facing the pushing surface. A dust collector. In the refuse collection device according to any one of claims 1 to 3,
A dust collecting apparatus, wherein a reinforcing member is attached to each of a pair of tip portions of the pushing plate viewed from the axial direction of the rotating shaft. In the refuse collection device according to any one of claims 1 to 4,
The pushing plate includes the eccentric amount a, the thickness W of the pushing plate, the distance L ₀ between a pair of tip edges of the pushing plate viewed from the axial direction of the rotating shaft, and the dimensions of the pushing plate. And the relationship with the manufacturing error δ is L ₀ = 4a + W + δ,
The position of the lower end of the partition plate is such that the relationship between the distance L ₁ from the lower end to the rotation center, the eccentricity a, the thickness W, and the gap α is L ₁ = a + W / 2 + α + δ. Set,
In the partition switching plate facing the on the surface of the pushing plate, the distance L ₂ from the point through the straight line connecting the lower end and the rotation center of the partition plate to the center of rotation, the rotation of the pressing write plate Regardless of the case, the dust collecting device is characterized in that the shape of the surface of the pushing plate is formed so that 0 <L ₂ ≦ L ₁ is always satisfied.

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