JP2022020321A - Reciprocating liner motion mechanism of can forming device and can forming device - Google Patents

Abstract

To stably supply oil to a bearing that couples a first rotator and a second rotator.SOLUTION: A reciprocating linear motion mechanism of a can forming device is equipped with a housing 15 that has an internal gear 16, a first rotator 21 that is located inside the housing 15, a second rotator 22 that has an external gear 23 engaged with the internal gear 16, a bearing 32 that couples the first rotator 21 and the second rotator 22 so as to relatively rotate, a ram shaft coupling portion that is connected to the second rotator 22 and performs a reciprocating linear motion mechanism in a predetermined direction, and an oil supply path 37 that penetrates the internal gear 16 and the external gear 23, and supplies oil to the bearing 32. The oil supply path 37 is equipped with an internal gear channel 37a that opens at least to an internal tooth 16a of the internal gear 16, and an external gear channel 37b that has a part opening to an external tooth 23a of the external gear 23 and a part opening toward the bearing 32. The internal gear channel 37a and the external gear channel 37b are communicated with each other through an engaging part between the internal tooth 16a and the external tooth 23a.SELECTED DRAWING: Figure 7

Description

The present invention relates to a reciprocating linear motion mechanism of a can molding apparatus and a can molding apparatus.

Conventionally, a DI (Drawing & Ironing) can having a bottomed cylinder is known. The DI can is manufactured by subjecting a disk-shaped blank made of an aluminum alloy to cupping processing, DI processing, and the like. In the cupping process, the blank is drawn to form a cup-shaped body. In DI processing, while pressing the cup-shaped body with the cup holder, it is squeezed and squeezed between the punch and the die.

As a can molding apparatus that performs DI processing on a cup-shaped body, for example, the one described in Patent Document 1 is known. In this can forming apparatus, a reciprocating linear motion mechanism causes a punch to reciprocate linearly in a predetermined stroke direction via a ram axis.
Specifically, the reciprocating linear motion mechanism includes a mechanism frame (housing) having an internal gear centered on the first central axis, and a first rotating body rotatably supported by the mechanism frame around the first central axis. , The second rotating body having an external gear that is rotatably supported by the first rotating body around the second central axis separated in parallel with the first central axis and meshes with the internal gear, and the second rotating body. It is provided and includes a working portion (ram shaft connecting portion) that reciprocates linearly along a predetermined direction orthogonal to the first central axis.

JP-A-2018-54065

The reciprocating linear motion mechanism of the conventional can forming device has been improved in that oil is stably supplied to the bearing that rotatably supports the second rotating body around the second central axis with respect to the first rotating body. There was room.

One object of the present invention is to provide a reciprocating linear motion mechanism of a can forming apparatus capable of stably supplying oil to a bearing connecting a first rotating body and a second rotating body, and a can forming apparatus.

One aspect of the reciprocating linear motion mechanism of the can forming apparatus of the present invention is a housing having an internal gear about the first central axis and the housing in a first radial direction orthogonal to the first central axis. A first rotating body located inside and rotatably connected to the housing around the first central axis, and an outer gear that meshes with the internal gear about a second central axis parallel to the first central axis. A second rotating body having a tooth gear, a bearing connecting the first rotating body and the second rotating body so as to be relatively rotatable around the second central axis, and a second rotating body connected to the second rotating body. It is provided with a ram shaft connecting portion that is reciprocated linearly along a predetermined direction in one radial direction, and an oil supply path that penetrates the internal gear and the external gear and supplies oil to the bearing. The oil supply path extends inside the internal gear and extends at least to the internal gear flow path that opens to the internal teeth of the internal gear and the inside of the external gear and opens to the external teeth of the external gear. A portion to be provided and an external gear flow path having a portion to open toward the bearing are provided, and the external gear is arranged at a predetermined position around the first central axis with respect to the internal gear. Occasionally, the internal gear flow path and the external gear flow path communicate with each other via the meshing portion between the internal tooth and the external tooth.
Further, one aspect of the can molding apparatus of the present invention includes a reciprocating linear motion mechanism of the can molding apparatus described above, a ram shaft extending in a predetermined direction, and a ram shaft connecting portion connected to one end thereof, and the ram. It includes a punch arranged at the other end of the shaft, a die having a through hole into which the punch is inserted, and a cup holder pressed against an end surface of the die through which the through hole opens.

In the present invention, the external gear revolves around the first central axis along the inner peripheral portion of the internal gear while rotating around the second central axis, and is arranged at a predetermined position around the first central axis. At that time, the internal gear flow path and the external gear flow path are connected through the meshing portion between the internal tooth and the external tooth, and the oil in the internal gear flow path flows into the external gear flow path. The oil that has flowed into the external gear flow path is discharged from the external gear flow path toward the bearing. According to the present invention, oil can be stably supplied to the bearing connecting the first rotating body and the second rotating body even while the can forming apparatus is in operation. The oil stably cools and lubricates the bearing and maintains good bearing performance.

In the reciprocating linear motion mechanism of the can forming apparatus, the first rotating body projects from a surface of the first rotating body facing one side in the axial direction to one side in the axial direction, and a convex portion centered on the second central axis. The second rotating body has a recessed portion in the axial direction from a surface of the second rotating body facing the other side in the axial direction, and a concave portion into which the convex portion is inserted, and the bearing has the convex portion. It is preferable to connect the portion and the recess so as to be relatively rotatable around the second central axis.

In this case, the first rotating body and the second rotating body are connected by a convex portion, a concave portion, and a bearing interposed between them. Therefore, the structure of the reciprocating linear motion mechanism can be simplified.

In the reciprocating linear motion mechanism of the can forming apparatus, it is preferable that the external gear flow path penetrates the external gear in the second radial direction orthogonal to the second central axis.

In this case, the external gear flow path can be formed into a simple shape such as a linear hole, the friction loss (resistance) of the oil flowing in the external gear flow path can be reduced, and the oil can be stably supplied to the bearing. ..

According to the reciprocating linear motion mechanism of the can forming apparatus according to one aspect of the present invention and the can forming apparatus, oil can be stably supplied to the bearing connecting the first rotating body and the second rotating body.

FIG. 1 is a schematic view schematically showing the can molding apparatus of this embodiment. FIG. 2 is a perspective view showing a reciprocating linear motion mechanism of the can molding apparatus of the present embodiment. FIG. 3 is a front view showing a reciprocating linear motion mechanism of the can molding apparatus of the present embodiment. FIG. 4 is a cross-sectional view showing the IV-IV cross section of FIG. FIG. 5 is a perspective view showing a first rotating body, a convex portion, a first weight portion, and a shaft body. FIG. 6 is a perspective view showing a second rotating body, a recess, a second weight portion, and a ram shaft connecting portion. FIG. 7 is a partial cross-sectional view showing a state in which the external gear is arranged at a predetermined position around the first central axis with respect to the internal gear, and shows the internal gear flow path and the external gear of the second oil supply path. The flow path and the flow path represent a state in which they communicate with each other.

The can forming apparatus 1 of the embodiment of the present invention and the reciprocating linear motion mechanism 10 of the can forming apparatus 1 (hereinafter, may be simply referred to as a reciprocating linear motion mechanism 10) will be described with reference to the drawings.
As shown in FIG. 1, the can forming apparatus 1 of the present embodiment is a DI can manufacturing apparatus in which a cup-shaped body W, which is a work, is subjected to DI processing to obtain a DI can 100.

First, the DI can 100 will be described.
The DI can 100 has a bottomed tubular shape. The DI can 100 is used for a can body such as a two-piece can or a bottle can in which the contents such as a beverage are filled and sealed. In the case of a two-piece can, the can body includes a DI can 100 and a disk-shaped can lid wrapped around the open end of the DI can 100. In the case of a bottle can, the can body includes a bottle can body in which the DI can 100 is necked, screwed, or the like, and a cap screwed to the open end of the bottle can body.

The DI can 100 is formed into a bottomed tubular shape by subjecting a disk-shaped blank punched from a plate material such as an aluminum alloy to a cupping step (squeezing step) and a DI step (squeezing ironing step). Specifically, in the case of a two-piece can, for example, the DI can 100 is manufactured through a plate material punching step, a cupping step, a DI step, a trimming step, a printing step, a painting step, a necking step, and a franging step in this order.

In the process of manufacturing the DI can 100, the blank is drawn (cupping) by a cupping press and formed into a cup-shaped body W. That is, the cup-shaped body W is a molding intermediate produced in the process of transferring from the blank to the DI can 100 in the cupping step. The cup-shaped body W is a bottomed cylinder having a smaller peripheral wall height (length along the can axis direction) and a larger diameter than the DI can 100.

Next, the can molding apparatus 1 will be described.
The can forming apparatus 1 is used in the above DI step, and the cup-shaped body W is subjected to DI processing, that is, drawing (re-drawing) ironing processing, and the height of the peripheral wall is larger than that of the cup-shaped body W and the diameter is large. Is molded into a small DI can 100. Further, in the DI step, the can forming apparatus 1 forms the can bottom of the DI can 100 into a dome shape.

The can forming apparatus 1 extends in a predetermined direction (hereinafter, may be referred to as stroke direction S) in which the reciprocating linear motion mechanism 10 and the ram shaft connecting portion 35 described later of the reciprocating linear motion mechanism 10 are reciprocated linearly, and one end thereof. The ram shaft 3 to which the ram shaft connecting portion 35 is connected, the punch 2 arranged at the other end of the ram shaft 3, and the ram shaft 3 reciprocate along the axial direction of the central axis O of the ram shaft 3. Di A dormer 11 that sandwiches the bottom of the can 100 and forms it into a dome shape is provided.
The ram shaft 3, the punch 2, the ram bearing 5, the through hole 7 of the die 8, the cup holder 6, and the central shaft O of the dormer 11 are arranged coaxially with each other. In the present embodiment, the central axis O, which is a common axis of these members, extends in the horizontal direction.

Further, the can forming apparatus 1 has a cup feeder (not shown) that supplies the cup-shaped body W on the end surface 9 of the die 8, a receiving seat (not shown) that holds the cup-shaped body W on the end surface 9, and molding. Air is discharged from the can transport mechanism (not shown) that transports the DI can 100 to the outside of the apparatus and the air discharge hole that opens at least one of the tip surface and the outer peripheral surface of the punch 2, and the DI can 100 is discharged from the punch 2. The cup holder 6 has a stroke length different from that of the ram shaft connecting portion 35 of the reciprocating linear motion mechanism 10 and is driven in synchronization with the air discharge mechanism (not shown) for releasing the mold. It includes a cup holder drive mechanism (not shown) that reciprocates in the axial direction, and a drive source (not shown) such as a drive motor.

The reciprocating linear motion mechanism 10 converts the rotational driving force around the first central axis C1 input from the drive source into a reciprocating linear motion in the stroke direction S along the central axis O, and outputs it to the ram axis connecting portion 35. do. The specific configuration of the reciprocating linear motion mechanism 10 will be described later separately.
The ram axis 3 has an axial shape extending along the central axis O. The ram shaft 3 is slidably supported by a pair of ram bearings 5 arranged apart from each other in the axial direction of the central shaft O.
The punch 2 is a cylinder or a cylinder extending along the central axis O.

The pair of ram bearings 5 are arranged between the reciprocating linear motion mechanism 10 and the die 8 in the axial direction of the central axis O. Of the pair of ram bearings 5, one ram bearing 5 arranged at a position close to the die 8 is the front bearing 5F, and the other ram bearing 5 arranged at a position close to the reciprocating linear motion mechanism 10 is the rear bearing 5. Bearing 5R. The front bearing 5F and the rear bearing 5R have a fluid bearing structure called, for example, a hydrostatic bearing or a hydrostatic bearing.

A plurality of dies 8 are provided side by side in the axial direction of the central axis O. Each of the plurality of dies 8 has a through hole 7 having a circular cross section that penetrates the die 8 in the axial direction of the central axis O. The plurality of dies 8 include one re-squeezing die 8A and a plurality of ironing dies (ironing dies) 8B located on the dormer 11 side of the re-squeezing die 8A. Although not particularly shown, a pilot ring is arranged on the dormer 11 side of each ironing die 8B. By providing the pilot ring, it is possible to prevent the punch 2 from coming into contact with each ironing die 8B due to the impact when the DI can 100 comes off (passes) from each ironing die 8B during molding.
Further, at the time of molding, a coolant liquid is supplied to the redrawing die 8A and each ironing die 8B for lubrication and cooling.

The cup holder 6 has a cylindrical cup holder sleeve 6a extending in the axial direction of the central axis O. The cup holder sleeve 6a is fitted to the outside of the punch 2 and can slide and move in the axial direction of the central axis O with respect to the punch 2. The cup holder sleeve 6a is inserted into the cup-shaped body W arranged on the end surface 9 of the redrawing die 8A, and presses and holds the bottom wall of the cup-shaped body W against the end surface 9. That is, the cup holder 6 supports the bottom wall of the cup-shaped body W by pressing it against the end surface 9 of the die 8 facing the reciprocating linear motion mechanism 10 side.
Although not particularly shown, the cup holder drive mechanism converts the rotational driving force transmitted from the drive source via the reciprocating linear motion mechanism 10 into reciprocating motion in the axial direction of the central axis O, and centers the cup holder 6. It is reciprocated linearly in the axial direction of the axis O.

The dormer 11 is a mold for molding the bottom of the DI can 100. The dormer 11 has a substantially cylindrical shape extending in the axial direction of the central axis O. When the punch 2 is arranged at the forward end position in the stroke direction S, the dormer 11 faces the punch 2 in the axial direction of the central axis O.

The air discharge mechanism includes an air discharge hole (not shown) that opens on the outer surface of the punch 2, an air supply path 28 (see FIG. 4) described later of the reciprocating linear motion mechanism 10, and an air discharge hole and an air supply path 28. It has an air communication passage (not shown) and an air supply source (not shown).
Although not particularly shown, the air communication passage has a ram shaft flow path extending inside the ram shaft 3 along the axial direction of the central axis O. The air supply source is, for example, an air compressor or the like, and air (compressed air) is supplied to the air supply path 28.

DI processing into the cup-shaped body W by the can forming apparatus 1 is performed as follows.
First, the cup-shaped body W, which is a work, is arranged between the punch 2 and the redrawing die 8A in a posture in which the cup shaft (can shaft) is extended in the horizontal direction and the opening thereof is directed toward the punch 2. The bottom wall of the cup-shaped body W faces the end surface 9 of the redraw die 8A.

The cup holder 6 and the punch 2 are moved forward with respect to the cup-shaped body W in the axial direction of the central axis O. That is, the cup holder 6 and the punch 2 move from the reciprocating linear motion mechanism 10 toward the die 8 side, that is, the front side in the stroke direction S. Then, while the cup holder 6 presses the bottom wall of the cup-shaped body W against the end surface 9 of the re-drawing die 8A to perform the cup pressing operation, the punch 2 pushes the cup-shaped body W into the through hole 7 of the re-drawing die 8A. By pushing it in, the cup-shaped body W is redrawn.

By the redrawing process, the cup-shaped body W is formed into a small diameter and has a large length in the cup axial direction. Further, the cup-shaped body W is pushed in by the punch 2, and ironing is performed while sequentially passing through the through holes 7 of the plurality of ironing dies 8B. That is, the peripheral wall of the cup-shaped body W is squeezed and stretched to increase the height of the peripheral wall and reduce the thickness of the peripheral wall to form a bottomed cylindrical DI can 100. The DI can 100 is cold-work-hardened by squeezing the peripheral wall, and the strength is increased.

The ironed DI can 100 is pushed out from the through hole 7 of the die 8 to the dormer 11 side by the punch 2. Then, the bottom of the DI can 100 (the portion that becomes the bottom of the can) is sandwiched between the punch 2 and the dormer 11 and pressed, so that the bottom of the DI can 100 is formed into a dome shape.

Next, the reciprocating linear motion mechanism 10 will be described.
As shown in FIGS. 2 to 4, the reciprocating linear motion mechanism 10 includes a housing 15 having an internal gear 16, a first rotating body 21 having a convex portion 25, a first bearing 31, and an internal gear 16. A second rotating body 22 having an external gear 23 and a recess 27 that mesh with each other, a second bearing (bearing) 32, an air joint member 40, a ram shaft connecting portion 35, a first weight portion 51, and a second weight portion. A 52, a shaft body 26, an air supply path 28, a first oil supply path 36, a second oil supply path (oil supply path) 37, and a gear (not shown) are provided.

The housing 15, its internal gear 16, the first rotating body 21 (parts other than the convex portion 25), the first bearing 31, the shaft body 26, and the gear are centered on the first central shaft C1, that is, the first center. The shaft C1 is used as a common shaft and is arranged coaxially with each other. The convex portion 25, the second rotating body 22 and its external gear 23, the concave portion 27, the second bearing 32, and the air joint member 40 are centered on the second central axis C2, that is, the second central axis C2 is used as a common axis. They are arranged coaxially with each other.
The first central axis C1 and the second central axis C2 are arranged parallel to each other and separated from each other. In the present embodiment, the first central axis C1 and the second central axis C2 extend in the horizontal direction.

In the following description, the direction in which the first central axis C1 extends and the direction in which the second central axis C2 extends are simply referred to as axial directions. In the axial direction, the first rotating body 21 and the ram shaft connecting portion 35 are arranged at different positions from each other. Of the axial directions, the direction from the first rotating body 21 toward the ram shaft connecting portion 35 is referred to as one axial direction, and the direction from the ram shaft connecting portion 35 toward the first rotating body 21 is referred to as the other axial direction. In addition, one side in the axial direction may be paraphrased as the front side, and the other side in the axial direction may be paraphrased as the rear side.

The direction orthogonal to the first central axis C1 is called the first radial direction. Of the first radial directions, the direction closer to the first central axis C1 is called the inner side in the first radial direction, and the direction away from the first central axis C1 is called the outer side in the first radial direction.
The direction that orbits around the first central axis C1 is called the first circumferential direction. Of the first circumferential direction, the direction in which the first rotating body 21 is rotated with respect to the housing 15 when the can forming apparatus 1 is operating is referred to as the first rotation direction T1.

The direction orthogonal to the second central axis C2 is called the second radial direction. Of the second radial directions, the direction closer to the second central axis C2 is called the inner side in the second radial direction, and the direction away from the second central axis C2 is called the outer side in the second radial direction.
The direction that orbits around the second central axis C2 is called the second circumferential direction. Of the second circumferential directions, the direction in which the second rotating body 22 is rotated with respect to the first rotating body 21 when the can forming apparatus 1 is operating is referred to as the second rotating direction T2.

As shown in FIG. 4, the housing 15 has a cylindrical shape centered on the first central axis C1. The housing 15 has an internal gear 16 and a housing body 17.

The internal gear 16 is an annular shape centered on the first central axis C1. The internal gear 16 has a cylindrical shape and extends in the axial direction. The internal gear 16 is arranged at one end of the housing 15 on one axial direction. The internal gear 16 is located in the opening on one side of the housing 15 in the axial direction.

The internal gear 16 has a plurality of internal teeth 16a arranged in the first circumferential direction on the inner peripheral portion of the internal gear 16. The internal teeth 16a are arranged on the inner peripheral portion of the internal gear 16 over the entire length in the axial direction. In the present embodiment, the internal teeth 16a are exposed to the outside of the reciprocating linear motion mechanism 10 through the opening on one side in the axial direction of the housing 15.

The housing body 17 has a cylindrical shape centered on the first central axis C1 and extends in the axial direction. A first rotating body 21 and a first bearing 31 are arranged inside the housing main body 17. An internal gear 16 is fixed to one end of the housing body 17 in the axial direction.

The housing body 17 has a first outer ring support portion 17g. The first outer ring support portion 17g projects inward in the first radial direction from the inner peripheral surface of the housing body 17, and extends in the first circumferential direction. The first outer ring support portion 17g has an annular plate shape centered on the first central axis C1. The pair of plate surfaces of the first outer ring support portion 17 g face in the axial direction.

The first rotating body 21 is located inside the housing 15 in the first radial direction. The first rotating body 21 is rotatably connected to the housing 15 around the first central axis C1.
As shown in FIGS. 4 and 5, the first rotating body 21 has a substantially cylindrical shape centered on the first central axis C1. The first rotating body 21 is arranged in the housing main body 17. The first rotating body 21 is housed in the housing 15.

The first rotating body 21 has a hole portion 21a, a flange portion 21b, and a convex portion 25.
The hole portion 21a is recessed in the axial direction from the surface 21e of the first rotating body 21 facing the other side in the axial direction, and extends in the axial direction. The hole portion 21a has a circular hole shape centered on the first central axis C1. Specifically, the hole portion 21a is recessed in one side in the axial direction from a portion other than the outer peripheral portion of the surface 21e facing the other side in the axial direction of the first rotating body 21. That is, the hole portion 21a opens on the other side in the axial direction.

The flange portion 21b is arranged at one end of the outer peripheral portion of the first rotating body 21 in the axial direction. The flange portion 21b has an annular plate shape centered on the first central axis C1. The flange portion 21b projects outward in the first radial direction from the outer peripheral surface of the first rotating body 21 and extends in the first circumferential direction. The pair of plate surfaces of the flange portion 21b face in the axial direction. Of the pair of plate surfaces of the flange portion 21b, the plate surface facing the other side in the axial direction comes into contact with the inner ring 31a of the first bearing 31 from one side in the axial direction.
The convex portion 25 will be described later.

The first bearing 31 is, for example, a tapered roller bearing or the like. The first bearing 31 can support a load from the first radial direction (radial load) and a load from the axial direction (axial load). The first bearing 31 connects the housing 15 and the first rotating body 21 so as to be relatively rotatable around the first central axis C1.

The first bearing 31 has an inner ring 31a, a spacer 31d, an outer ring 31b, and a rolling element 31c.
The inner ring 31a has a cylindrical shape centered on the first central axis C1. The inner ring 31a fits on the outer peripheral surface of the first rotating body 21. A plurality of inner rings 31a are provided side by side in the axial direction. In this embodiment, the first bearing 31 has a pair of inner rings 31a arranged so as to be spaced apart from each other in the axial direction. Spacers 31d are arranged between the pair of inner rings 31a. The spacer 31d has a cylindrical shape centered on the first central axis C1. The spacer 31d fits on the outer peripheral surface of the first rotating body 21.

Of the pair of inner rings 31a, one inner ring 31a located on one side in the axial direction is arranged between the flange portion 21b and the spacer 31d in the axial direction. The flange portion 21b comes into contact with the end surface of one inner ring 31a facing one side in the axial direction. The spacer 31d comes into contact with the end face of one inner ring 31a facing the other side in the axial direction.
Of the pair of inner rings 31a, the other inner ring 31a located on the other side in the axial direction is in contact with the end face facing one side in the axial direction with the spacer 31d.

The outer ring 31b has a cylindrical shape centered on the first central axis C1. The outer ring 31b is located outside the inner ring 31a in the first radial direction. The outer ring 31b fits on the inner peripheral surface of the housing body 17. A plurality of outer rings 31b are provided side by side in the axial direction. In this embodiment, the first bearing 31 has a pair of outer rings 31b arranged axially spaced apart from each other. A first outer ring support portion 17g is arranged between the pair of outer rings 31b.

Of the pair of outer rings 31b, the first outer ring support portion 17g comes into contact with the end face of one of the outer rings 31b located on one side in the axial direction facing the other side in the axial direction.
Of the pair of outer rings 31b, the first outer ring support portion 17g comes into contact with the end face of the other outer ring 31b located on the other side in the axial direction and facing one side in the axial direction.

The rolling element 31c is a columnar roller or the like. The rolling element 31c is arranged between the inner ring 31a and the outer ring 31b in the first radial direction. A plurality of rolling elements 31c are provided side by side in the first circumferential direction. A plurality of rows of rolling elements 31c arranged in the first circumferential direction (hereinafter, simply referred to as rows of rolling elements 31c) are provided side by side in the axial direction. In this embodiment, the first bearing 31 has a row of a pair of rolling elements 31c arranged axially spaced apart from each other.

Of the rows of the pair of rolling elements 31c, the row of one rolling element 31c located on one side in the axial direction is rotatably held between one inner ring 31a and one outer ring 31b.
Of the rows of the pair of rolling elements 31c, the row of the other rolling elements 31c located on the other side in the axial direction is rotatably held between the other inner ring 31a and the other outer ring 31b.

The convex portion 25 protrudes from the surface 21d of the first rotating body 21 facing one side in the axial direction to one side in the axial direction and extends in the axial direction. The convex portion 25 is a columnar shape centered on the second central axis C2. Specifically, the convex portion 25 projects from the outer portion in the first radial direction of the surface 21d facing one side in the axial direction of the first rotating body 21 to one side in the axial direction.

The convex portion 25 has an outer peripheral step portion 25a.
The outer peripheral step portion 25a constitutes a part of the outer peripheral portion of the convex portion 25. In the illustrated example, the outer peripheral step portion 25a is arranged at the end of the outer peripheral portion of the convex portion 25 on the other side in the axial direction. The outer peripheral step portion 25a has an annular surface shape centered on the second central axis C2 and faces one side in the axial direction.

The second rotating body 22 is arranged on one side in the axial direction of the first rotating body 21. The second rotating body 22 is connected to the first rotating body 21 so as to be relatively rotatable around the second central axis C2.
As shown in FIGS. 4 and 6, the second rotating body 22 has a substantially ecstatic cylinder shape centered on the second central axis C2. The second rotating body 22 has an external gear 23, a top wall portion 22b, a bolt member 24, a joint insertion hole 22c, and a recess 27.

The external gear 23 has a cylindrical shape centered on the second central axis C2 and extends in the axial direction. A part of the surface 22e of the external gear 23 facing the other side in the axial direction faces a part of the surface 21d of the first rotating body 21 facing the other side in the axial direction with a gap in the axial direction. The other part of the surface 22e of the external gear 23 facing the other side in the axial direction faces a part of the first bearing 31 with a gap in the axial direction.

The external tooth gear 23 has a plurality of external teeth 23a arranged in the second circumferential direction on the outer peripheral portion of the external tooth gear 23. The external teeth 23a are arranged on a portion of the outer peripheral portion of the external gear 23 other than the end portion on one side in the axial direction. In the present embodiment, the external teeth 23a are exposed to the outside of the reciprocating linear motion mechanism 10 through the opening on one side in the axial direction of the housing 15.
At least one or more of the plurality of external teeth 23a and at least one or more of the plurality of internal teeth 16a mesh with each other. The pitch circle diameter of the external teeth 23a of the external gear 23 is ½ of the pitch circular diameter of the internal teeth 16a of the internal gear 16.

The external tooth gear 23 has a second outer ring support portion 23b. The second outer ring support portion 23b projects inward in the second radial direction from the inner peripheral surface of the external gear 23 and extends in the second circumferential direction. The second outer ring support portion 23b has a cylindrical shape centered on the second central axis C2. The pair of end faces of the second outer ring support portion 23b face in the axial direction.

In FIG. 2, when the can forming apparatus 1 is in operation, the external gear 23 rotates (revolves) in the first rotation direction T1 along the inner peripheral portion of the internal gear 16 and rotates in the second rotation direction T2. (Rotate). In the present embodiment, the reciprocating linear motion mechanism 10 is viewed from one side in the axial direction, that is, when the reciprocating linear motion mechanism 10 is viewed from the front, the first rotation direction T1 is counterclockwise about the first central axis C1. The second rotation direction T2 is a clockwise direction about the second central axis C2. However, not limited to this, when the reciprocating linear motion mechanism 10 is viewed from one side in the axial direction, the first rotation direction T1 is a clockwise direction about the first central axis C1 and the second rotation direction T2 is. It may be in the counterclockwise direction about the second central axis C2.

The top wall portion 22b is arranged on one side in the axial direction of the external gear 23. The top wall portion 22b has a plate shape extending in a direction perpendicular to the second central axis C2. As shown in FIG. 4, the top wall portion 22b is connected to one end in the axial direction of the external gear 23 and the other end in the axial direction of the ram shaft connecting portion 35. That is, the top wall portion 22b connects the external gear 23 and the ram shaft connecting portion 35. The top wall portion 22b closes the opening on one side in the axial direction of the external gear 23. The top wall portion 22b may be paraphrased as a closing wall portion 22b or a front wall portion 22b.

The top wall portion 22b has a fitting cylinder portion 22d.
The fitting cylinder portion 22d projects from the surface of the top wall portion 22b facing the other side in the axial direction to the other side in the axial direction. The fitting cylinder portion 22d has a cylindrical shape centered on the second central axis C2. The fitting cylinder portion 22d is inserted into the external gear 23. The fitting cylinder portion 22d is fitted to the inner peripheral surface of the external gear 23.

As shown in FIGS. 2 and 3, the top wall portion 22b is fixed to the external gear 23 by a plurality of bolt members 24 arranged in the second circumferential direction. Each bolt member 24 extends axially. Each bolt member 24 is inserted into a bolt insertion hole that penetrates the top wall portion 22b in the axial direction, and is screwed into the female screw hole of the external gear 23.

As shown in FIG. 4, the joint insertion hole 22c penetrates the top wall portion 22b in the axial direction. The joint insertion hole 22c has a circular hole shape centered on the second central shaft C2.

The recess 27 is recessed in the axial direction from the surface 22e of the second rotating body 22 facing the other side in the axial direction, and extends in the axial direction. The recess 27 has a circular hole shape centered on the second central axis C2. Specifically, the recess 27 is recessed in one side in the axial direction from the inner portion in the second radial direction of the surface 22e facing the other side in the axial direction of the external gear 23. That is, the recess 27 opens on the other side in the axial direction. One end of the recess 27 in the axial direction is closed by the top wall portion 22b. The convex portion 25 is inserted into the concave portion 27.

The second bearing 32 is, for example, a tapered roller bearing or the like. The second bearing 32 can support a load from the second radial direction (radial load) and a load from the axial direction (axial load). The second bearing 32 connects the convex portion 25 and the concave portion 27 so as to be relatively rotatable around the second central axis C2. That is, the second bearing 32 connects the first rotating body 21 and the second rotating body 22 so as to be relatively rotatable around the second central axis C2.

The second bearing 32 has an inner ring 32a, a spacer 32d, an outer ring 32b, and a rolling element 32c.
The inner ring 32a has a cylindrical shape centered on the second central axis C2. The inner ring 32a fits on the outer peripheral surface of the convex portion 25. A plurality of inner rings 32a are provided side by side in the axial direction. In this embodiment, the second bearing 32 has a pair of inner rings 32a arranged so as to be spaced apart from each other in the axial direction. A spacer 32d is arranged between the pair of inner rings 32a. The spacer 32d has a cylindrical shape centered on the second central axis C2. The spacer 32d fits on the outer peripheral surface of the convex portion 25.

Of the pair of inner rings 32a, one inner ring 32a located on one side in the axial direction is arranged between the inner ring holding portion 41 described later of the air joint member 40 and the spacer 32d in the axial direction. The inner ring holding portion 41 comes into contact with the end surface of one inner ring 32a facing one side in the axial direction. The spacer 32d comes into contact with the end surface of one inner ring 32a facing the other side in the axial direction. That is, one inner ring 32a is sandwiched from both sides in the axial direction by the inner ring holding portion 41 and the spacer 32d.

Of the pair of inner rings 32a, the other inner ring 32a located on the other side in the axial direction is arranged between the spacer 32d and the outer peripheral step portion 25a in the axial direction. The spacer 32d comes into contact with the end face of the other inner ring 32a facing one side in the axial direction. The outer peripheral step portion 25a comes into contact with the end surface of the other inner ring 32a facing the other side in the axial direction. That is, the other inner ring 32a is sandwiched from both sides in the axial direction by the spacer 32d and the outer peripheral step portion 25a.
Although not particularly shown, the surface 21d of the first rotating body 21 facing one side in the axial direction may come into contact with the end surface of the other inner ring 32a facing the other side in the axial direction. In this case, the other inner ring 32a is sandwiched from both sides in the axial direction by the surface 21d facing one side in the axial direction of the first rotating body 21 and the spacer 32d.

The outer ring 32b has a cylindrical shape centered on the second central axis C2. The outer ring 32b is located outside the inner ring 32a in the second radial direction. The outer ring 32b is fitted to the inner peripheral surface of the external gear 23, that is, the inner peripheral surface of the recess 27. A plurality of outer rings 32b are provided side by side in the axial direction. In this embodiment, the second bearing 32 has a pair of outer rings 32b arranged axially spaced apart from each other. A second outer ring support portion 23b is arranged between the pair of outer rings 32b.

The second outer ring support portion 23b comes into contact with the end face of the pair of outer rings 32b located on one side in the axial direction and facing the other side in the axial direction.
Of the pair of outer rings 32b, the second outer ring support portion 23b comes into contact with the end face of the other outer ring 32b located on the other side in the axial direction and facing one side in the axial direction.

The rolling element 32c is a columnar roller or the like. The rolling element 32c is arranged between the inner ring 32a and the outer ring 32b in the second radial direction. A plurality of rolling elements 32c are provided side by side in the second circumferential direction. A plurality of rows of rolling elements 32c arranged in the second circumferential direction (hereinafter, simply referred to as rows of rolling elements 32c) are provided side by side in the axial direction. In this embodiment, the second bearing 32 has a row of a pair of rolling elements 32c arranged axially spaced apart from each other.

Of the rows of the pair of rolling elements 32c, the row of one rolling element 32c located on one side in the axial direction is rotatably held between the inner ring 32a and the outer ring 32b.
Of the rows of the pair of rolling elements 32c, the row of the other rolling elements 32c located on the other side in the axial direction is rotatably held between the other inner ring 32a and the other outer ring 32b.

When viewed from the second radial direction, the internal gear 16, the external gear 23, the concave portion 27, the second bearing 32, and the convex portion 25 overlap each other. That is, the internal gear 16, the external gear 23, the concave portion 27, the second bearing 32, and the convex portion 25 each include a portion arranged at the same position in the axial direction. Seen from the second radial direction, the second bearing 32 overlaps the internal gear 16 and the external gear 23 over the entire axial length thereof.
When viewed from the axial direction, a part of the second bearing 32 in the second circumferential direction and a part of the first bearing 31 in the first circumferential direction are arranged so as to overlap each other. That is, when viewed from the axial direction, a part of the second bearing 32 and a part of the first bearing 31 overlap each other.

The air joint member 40 is attached to the convex portion 25 and the top wall portion 22b. The air joint member 40 allows air to flow inside and constitutes a part of the flow path of the air supply path 28.
The air joint member 40 has an inner ring holding portion 41, an outer cylinder 42, and an inner cylinder 43.

The inner ring holding portion 41 has a disk shape centered on the second central axis C2 and extends in a direction perpendicular to the second central axis C2. The plate surface of the inner ring holding portion 41 facing the other side in the axial direction comes into contact with the surface of the convex portion 25 facing the other side in the axial direction. The inner ring holding portion 41 is fixed to the convex portion 25 by screwing or the like. The outer peripheral portion of the inner ring holding portion 41 projects outward from the outer peripheral surface of the convex portion 25 in the second radial direction. The outer peripheral portion of the inner ring holding portion 41 comes into contact with one inner ring 32a of the second bearing 32 from one side in the axial direction. That is, the inner ring holding portion 41 presses the inner ring 32a of the second bearing 32 from one side in the axial direction.

The inner ring holding portion 41 has a holding portion air hole 41a.
The holding portion air hole 41a penetrates the inner ring holding portion 41 in the axial direction. The holding portion air hole 41a has a circular hole shape centered on the second central axis C2.

The outer cylinder 42 has a cylindrical shape centered on the second central axis C2 and extends in the axial direction. The outer cylinder 42 is inserted into the joint insertion hole 22c. The outer cylinder 42 fits into the inner peripheral surface of the joint insertion hole 22c. The outer cylinder 42 is fixed to the top wall portion 22b by screwing or the like.

The outer cylinder 42 has an outer cylinder air hole 42a.
The outer cylinder air hole 42a penetrates the peripheral wall of the outer cylinder 42 in the second radial direction. The outer cylinder air hole 42a is located on a virtual straight line connecting the central axis A of the ram shaft connecting portion 35 and the second central axis C2 when viewed from the axial direction.

The inner cylinder 43 has a ridged cylinder shape centered on the second central axis C2 and extends in the axial direction. The end of the inner cylinder 43 on the other side in the axial direction comes into contact with the plate surface of the inner ring holding portion 41 facing the other side in the axial direction. The inside of the inner cylinder 43 communicates with the holding portion air hole 41a of the inner ring holding portion 41. The inner cylinder 43 is fixed to the inner ring holding portion 41 by screwing or the like. That is, the inner cylinder 43 is fixed to the convex portion 25 via the inner ring holding portion 41. The inner cylinder 43 and the outer cylinder 42 can rotate relative to each other around the second central axis C2.

The inner cylinder 43 has an inner cylinder air groove 43a and an inner cylinder air hole 43b.
The inner cylinder air groove 43a is recessed inward in the second radial direction from the outer peripheral surface of the inner cylinder 43 and extends in the second circumferential direction. The inner cylinder air groove 43a is an annular shape centered on the second central axis C2. The inner cylinder air groove 43a communicates with the outer cylinder air hole 42a.

The inner cylinder air hole 43b penetrates the peripheral wall of the inner cylinder 43 in the second radial direction. The inner cylinder air hole 43b extends in the second radial direction and opens to the inner peripheral surface of the inner cylinder 43 and the inner cylinder air groove 43a. The inside of the inner cylinder 43 and the inner cylinder air groove 43a communicate with each other through the inner cylinder air hole 43b. A plurality of inner cylinder air holes 43b are provided side by side in the second circumferential direction. The plurality of inner cylinder air holes 43b are arranged radially with respect to the second central axis C2.

As shown in FIGS. 2 to 4, the ram shaft connecting portion 35 is connected to the second rotating body 22 and is reciprocated linearly in a predetermined direction (stroke direction S) in the first radial direction. The ram shaft connecting portion 35 has a bottomed cylindrical shape and extends in the axial direction. The ram shaft connecting portion 35 opens on one side in the axial direction.
The ram shaft connecting portion 35 projects from the top wall portion 22b to one side in the axial direction. The ram shaft connecting portion 35 is located on one side in the axial direction with respect to the housing 15. The ram shaft connecting portion 35 projects outward from the top wall portion 22b in the second radial direction.

The central axis A of the ram axis connecting portion 35 is parallel to the first central axis C1. The central axis A of the ram axis connecting portion 35 is arranged parallel to and apart from the second central axis C2. The second radial distance between the central axis A and the second central axis C2 is equal to the second radial distance between the first central axis C1 and the second central axis C2. When the reciprocating linear motion mechanism 10 is viewed from the axial direction, the central axis A of the ram shaft connecting portion 35 is located on the pitch circle diameter of the external teeth 23a of the external gear 23.

The ram shaft connecting portion 35 has an air cylinder 35a.
The air cylinder 35a is arranged inside the ram shaft connecting portion 35. The air cylinder 35a has a cylindrical shape centered on the central axis A and extends in the axial direction. The air cylinder 35a allows air to flow inside and forms a part of the flow path of the air supply path 28.

In FIG. 1, the ram shaft connecting portion 35 is connected to the ram shaft 3 via a bearing (not shown) provided on the outer peripheral portion of the ram shaft connecting portion 35. This bearing connects the ram shaft connecting portion 35 and the ram shaft 3 so as to be relatively rotatable around the central axis A.

As shown in FIGS. 4 and 5, the first weight portion 51 is connected to the first rotating body 21 and is opposite to the second central axis C2 with the first central axis C1 sandwiched in the first radial direction. Located on the side. In the first weight portion 51, the first rotating body 21 and its convex portion 25, the second bearing 32, the second rotating body 22 and its concave portion 27, the ram shaft connecting portion 35 and the second weight portion 52 are the first central shaft C1. It functions as a so-called counter weight for maintaining a good rotational balance in the first circumferential direction when rotating around.

The first weight portion 51 is arranged on one side in the axial direction of the first rotating body 21. The first weight portion 51 has a semicircular plate shape. The surface of the first weight portion 51 facing the other side in the axial direction comes into contact with the surface 21d of the first rotating body 21 facing the other side in the axial direction. The outer end portion, that is, the outer peripheral portion of the first weight portion 51 in the first radial direction projects outward from the outer peripheral surface of the first rotating body 21 in the first radial direction. The outer peripheral portion of the first weight portion 51 overlaps with the first bearing 31 when viewed from the axial direction.

The first weight portion 51 is fixed to the first rotating body 21 by a plurality of bolt members 53 arranged in the first circumferential direction. Each bolt member 53 extends axially. Each bolt member 53 is inserted into a bolt insertion hole that penetrates the first weight portion 51 in the axial direction, and is screwed into the female screw hole of the first rotating body 21.

As shown in FIGS. 2 to 4 and 6, the second weight portion 52 is connected to the second rotating body 22, and the ram shaft connecting portion 52 sandwiches the second central shaft C2 in the second radial direction. It is located on the opposite side of 35. The second weight portion 52 functions as a so-called counterweight for maintaining a good rotational balance in the second circumferential direction when the second rotating body 22 and the ram shaft connecting portion 35 rotate around the second central axis C2. do.

The second weight portion 52 projects outward from the top wall portion 22b in the second radial direction. The shape of the second weight portion 52 and the top wall portion 22b as a whole is substantially disk-shaped. The second weight portion 52 is formed integrally with a part of the ram shaft connecting portion 35 and the top wall portion 22b.

As shown in FIG. 4, the shaft body 26 is a multi-stage columnar centered on the first central shaft C1 and extends in the axial direction. The shaft body 26 is arranged on the other side in the axial direction of the first rotating body 21. The outer diameter of the shaft body 26 is smaller than the outer diameter of the first rotating body 21. The outer diameter of the end portion on one side in the axial direction of the shaft body 26 is larger than the outer diameter of the portion other than the end portion on one side in the axial direction of the shaft body 26. The end portion on one side in the axial direction of the shaft body 26 fits into the opening of the hole portion 21a of the first rotating body 21. The end portion on one side in the axial direction of the shaft body 26 is fixed to the end portion on the other side in the axial direction of the first rotating body 21 by a screw member or the like. That is, the shaft body 26 is fixed to the first rotating body 21.

The shaft body 26 is rotatably supported around the first central shaft C1 by a third bearing (not shown). A rotational driving force in the first rotational direction T1 is input to the shaft body 26 from a driving source (not shown). The shaft body 26 and the first rotating body 21 are rotated in the first rotation direction T1 with respect to the housing 15 by the rotational driving force of the driving source.

The air supply path 28 is an air flow path formed inside the reciprocating linear motion mechanism 10. The air supply path 28 includes the inside of the shaft body 26, the inside of the first rotating body 21, the inside of the convex portion 25, the inside of the air joint member 40, the inside of the top wall portion 22b of the second rotating body 22, and the ram shaft connecting portion. Extends over the interior of 35.

The air supply path 28 includes a first air flow path 28a, an air chamber 29, a second air flow path 28b, an air joint flow path 28c, a third air flow path 28d, and a fourth air flow path 28e. Has. The first air flow path 28a, the air chamber 29, the second air flow path 28b, the air joint flow path 28c, the third air flow path 28d, and the fourth air flow path 28e communicate with each other. The air supplied to the air supply path 28 from an air supply source (not shown) has the inside of the air supply path 28 directed from the upstream side to the downstream side, the first air flow path 28a, the air chamber 29, the second air flow path 28b, and the like. The air joint flow path 28c, the third air flow path 28d, and the fourth air flow path 28e flow in this order.

The first air flow path 28a is arranged inside the shaft body 26. In the present embodiment, the first air flow path 28a is located at the end of the shaft body 26 on the other side in the axial direction, and extends axially on the first central axis C1.

The air chamber 29 is arranged over the inside of the shaft body 26 and the inside of the first rotating body 21. The air chamber 29 is formed over a portion other than the end portion on the other side in the axial direction of the shaft body 26 and a hole portion 21a of the first rotating body 21. The air chamber 29 extends axially on the first central axis C1. The air chamber 29 has the largest flow path cross-sectional area and the largest volume among the flow paths constituting the air supply path 28. The air chamber 29 can temporarily store air (compressed air) inside the air chamber 29.

The second air flow path 28b is arranged over the inside of the first rotating body 21 and the inside of the convex portion 25. The second air flow path 28b extends axially on the second central axis C2. The end of the second air flow path 28b on the other side in the axial direction opens in the hole 21a. The end portion of the second air flow path 28b on one side in the axial direction opens to the surface of the convex portion 25 facing one side in the axial direction.

The air joint flow path 28c has a holding portion air hole 41a, an inside (internal space) of the inner cylinder 43, an inner cylinder air hole 43b, an inner cylinder air groove 43a, and an outer cylinder air hole 42a. The air flowing into the air joint flow path 28c from the second air flow path 28b passes through the holding portion air hole 41a, the inside of the inner cylinder 43, the inner cylinder air hole 43b, the inner cylinder air groove 43a, and the outer cylinder air hole 42a in this order. It flows and flows out to the third air flow path 28d.

The third air flow path 28d is arranged inside the top wall portion 22b and extends in the second radial direction. The third air flow path 28d extends along a virtual straight line connecting the central axis A of the ram axis connecting portion 35 and the second central axis C2 when viewed from the axial direction. The inner end of the third air flow path 28d in the second radial direction is connected to the outer cylinder air hole 42a. The outer end portion of the third air flow path 28d in the second radial direction is closed by the plug portion 28f.

The fourth air flow path 28e is arranged inside the ram shaft connecting portion 35. The fourth air flow path 28e extends axially on the central axis A of the ram shaft connecting portion 35. The other end of the fourth air flow path 28e in the axial direction is connected to the third air flow path 28d. One end of the fourth air passage 28e in the axial direction is connected to an air passage (not shown). The portion of the fourth air flow path 28e other than the end on the other side in the axial direction is composed of the air cylinder 35a (internal space).

The first oil supply path 36 penetrates the housing 15 and supplies oil to the first bearing 31. In the present embodiment, the first oil supply path 36 penetrates the peripheral wall of the housing body 17. The outer end of the first oil supply path 36 in the first radial direction opens to the outer peripheral surface of the housing body 17. The inner end of the first oil supply path 36 in the first radial direction opens to the inner peripheral surface of the housing body 17. That is, the first oil supply path 36 extends inside the housing 15 and opens toward the first bearing 31. Oil is supplied to the first oil supply path 36 from the outside of the housing 15 via the first oil supply port 36a (see FIG. 2) provided on the outer peripheral portion of the housing main body 17.

A plurality of first oil supply paths 36 are provided. The plurality of first oil supply paths 36 are arranged so as to be spaced apart from each other in the first circumferential direction. The plurality of first oil supply paths 36 include one first oil supply path 36 that extends linearly in the housing body 17, and another first oil supply path 36 that bends in the housing body 17 and extends in a crank shape. And, are included.

In the present embodiment, at least one first oil supply path 36 is arranged in a portion of the housing body 17 located above the first central axis C1 in the vertical direction. Therefore, the oil supplied from the upper side to the first bearing 31 can be stably distributed over the entire first bearing 31.

As shown in FIGS. 4 and 7, the second oil supply path 37 penetrates the internal gear 16 and the external gear 23 to supply oil to the second bearing 32. The second oil supply path 37 has an internal gear flow path 37a and an external gear flow path 37b.

The internal gear flow path 37a penetrates the peripheral wall of the internal gear 16. In the present embodiment, the internal gear flow path 37a penetrates the internal gear 16 in the first radial direction. The outer end portion of the internal gear flow path 37a in the first radial direction opens on the outer peripheral surface of the internal gear 16. The inner end of the internal gear flow path 37a in the first radial direction opens to the inner peripheral surface of the internal gear 16, that is, the internal tooth 16a. That is, the internal gear flow path 37a extends inside the internal gear 16 and opens at least to the internal teeth 16a. Oil is supplied to the internal gear flow path 37a from the outside of the housing 15 via the second oil supply port 37c provided on the outer peripheral portion of the internal gear 16.

The external gear flow path 37b penetrates the peripheral wall of the external gear 23. In the present embodiment, the external gear flow path 37b penetrates the external gear 23 in the second radial direction. The outer end portion of the external gear flow path 37b in the second radial direction opens to the outer peripheral surface of the external gear 23, that is, the external tooth 23a. The inner end of the external gear flow path 37b in the second radial direction opens to the inner peripheral surface of the second outer ring support portion 23b. That is, the external gear flow path 37b has a portion extending inside the external gear 23 and opening to the external teeth 23a and a portion opening toward the second bearing 32.

A plurality of second oil supply paths 37 are provided. That is, a plurality of sets of the internal gear flow path 37a and the external gear flow path 37b are provided. In this embodiment, for example, three or more second oil supply paths 37 are provided. That is, three or more sets of the internal gear flow path 37a and the external gear flow path 37b are provided. The plurality of internal gear flow paths 37a are arranged at intervals in the first circumferential direction. The plurality of external gear flow paths 37b are arranged so as to be spaced apart from each other in the second circumferential direction.

As shown in FIG. 7, when the external gear 23 is arranged at a predetermined position around the first central axis C1 with respect to the internal gear 16, the internal gear flow path 37a and the external gear flow path 37b are , Facing each other in the first radial direction and communicating with each other. Specifically, when the external gear 23 rotates in the second circumferential direction and revolves in the first circumferential direction along the inner peripheral portion of the internal gear 16 and is arranged at a predetermined position in the first circumferential direction. In addition, the internal gear flow path 37a and the external gear flow path 37b communicate with each other via the meshing portion between the internal teeth 16a and the external teeth 23a. As a result, the oil in the internal gear flow path 37a flows into the external gear flow path 37b, and the oil flowing into the external gear flow path 37b flows inward in the external gear flow path 37b in the second radial direction. It flows and is discharged toward the second bearing 32.

The number of internal teeth 16a possessed by the internal gear 16 is twice the number of external teeth 23a possessed by the external gear 23. Therefore, the internal gear flow path 37a and the external gear flow path 37b face each other at the predetermined positions at each rotation around the first central axis C1 of the external gear 23, that is, at each revolution. That is, the inflow of oil from the internal gear flow path 37a to the external gear flow path 37b and the discharge of oil from the external gear flow path 37b to the second bearing 32 are performed every revolution of the external gear 23. Will be.

In the present embodiment, at least one internal gear flow path 37a is arranged in a portion of the internal gear 16 located above the first central axis C1 in the vertical direction. Further, at least one external gear flow path 37b faces and communicates with the internal gear flow path 37a in a portion of the external gear 23 located above the second central axis C2 in the vertical direction. That is, when the internal gear flow path 37a and the external gear flow path 37b communicate with each other, the oil flowing through the internal gear flow path 37a is supplied to the second bearing 32 from above through the external gear flow path 37b. Therefore, the oil is stable and easy to spread over the entire second bearing 32.

Although not particularly shown, the gear has an annular plate shape centered on the first central axis C1. The inner peripheral surface of the gear fits with the outer peripheral surface of the end portion on one side in the axial direction of the shaft body 26. The surface of the gear facing one side in the axial direction comes into contact with the surface 21e of the first rotating body 21 facing the other side in the axial direction. The gear is fixed to the surface 21e of the first rotating body 21 facing the other side in the axial direction by screwing or the like. That is, the gear is provided on the first rotating body 21. The gear may be fixed to the shaft body 26. At least a portion of the gear is exposed to the outside of the housing 15. The gear is connected to a cup holder drive mechanism (not shown) or the like via a connecting gear (not shown). The gear outputs the rotational driving force around the first central axis C1 of the first rotating body 21 and the shaft body 26 to the outside of the reciprocating linear motion mechanism 10.

In the reciprocating linear motion mechanism 10 of the present embodiment described above, when the rotational driving force around the first central axis C1 is transmitted from a drive source (not shown) to the shaft body 26 and the first rotating body 21, the housing 15 is subjected to rotation driving force. The first rotating body 21 is rotated around the first central axis C1. When the first rotating body 21 is rotated around the first central axis C1, the second rotating body 22 supported by the first rotating body 21 is also rotated around the first central axis C1.

At this time, since the external gear 23 of the second rotating body 22 and the internal gear 16 of the housing 15 mesh with each other, the second rotating body 22 is rotated (revolved) around the first central axis C1. At the same time, it is also rotated (rotated) around the second central axis C2. When the reciprocating linear motion mechanism 10 is viewed from the axial direction, the second rotating body 22 rotates around the first central axis C1 in the first rotating direction T1 and the second rotating body 22 rotates around the second central axis C2. The second rotation direction T2 is opposite to each other.

The ram shaft connecting portion 35 connected to the second rotating body 22 reciprocates linearly in a predetermined direction in the first radial direction, that is, in the stroke direction S.
In this way, the reciprocating linear motion mechanism 10 of the present embodiment converts the rotational driving force input to the first rotating body 21 into a reciprocating linear motion in the stroke direction S and outputs it to the ram shaft connecting portion 35. .. As a result, the punch 2 connected to the ram shaft connecting portion 35 via the ram shaft 3 is reciprocated linearly in the stroke direction S. The cup-shaped body W can be subjected to DI processing by the punch 2, the die 8, the cup holder 6, and the like, and the cup-shaped body W can be formed into the DI can 100.

Then, in the present embodiment, the external gear 23 rotates around the second central axis C2 and revolves around the first central axis C1 along the inner peripheral portion of the internal gear 16, as shown in FIG. 7. When arranged at a predetermined position around the first central axis C1, the internal gear flow path 37a and the external gear flow path 37b are connected through the meshing portion between the internal teeth 16a and the external teeth 23a, and the internal gear flow The oil in the path 37a flows into the external gear flow path 37b. The oil that has flowed into the external gear flow path 37b is discharged from the inside of the external gear flow path 37b toward the second bearing 32. According to this embodiment, oil can be stably supplied to the second bearing 32 connecting the first rotating body 21 and the second rotating body 22 even while the can forming apparatus 1 is in operation. The oil stably cools and lubricates the second bearing 32, and the performance of the second bearing 32 is maintained well.

Further, in the present embodiment, the first rotating body 21 and the second rotating body 22 are connected by the convex portion 25, the concave portion 27, and the second bearing 32 interposed between them, that is, the second bearing 32 is connected. , The convex portion 25 and the concave portion 27 are connected so as to be relatively rotatable around the second central axis C2. Therefore, the structure of the reciprocating linear motion mechanism 10 can be simplified.

Further, in the present embodiment, the external gear flow path 37b penetrates the external gear 23 in the second radial direction.
In this case, the external gear flow path 37b can be formed into a simple shape such as a linear hole, the friction loss (resistance) of the oil flowing in the external gear flow path 37b can be reduced, and the second bearing 32 is stable. Can supply oil.

Further, in the present embodiment, the internal gear 16, the external gear 23, the concave portion 27, the second bearing 32 and the convex portion 25 are arranged so as to overlap each other when viewed from the second radial direction. That is, since the positions of the internal gear 16, the external gear 23, the concave portion 27, the second bearing 32, and the convex portion 25 in the axial direction are the same as each other, the second gear 16 and the external gear 23 are penetrated through the second gear. The second oil supply path 37 that opens toward the bearing 32 can be easily formed, and the flow path length of the second oil supply path 37 can be kept short. Further, it is possible to suppress the bulkiness of the axial dimension of the reciprocating linear motion mechanism 10. The outer shape of the reciprocating linear motion mechanism 10 in the axial direction can be kept small, and the structure can be simplified.

Further, in the present embodiment, the second bearing 32 is arranged so as to overlap the internal gear 16 and the external gear 23 over the entire length in the axial direction when viewed from the second radial direction.
In this case, it is easy to stably supply oil from the second oil supply path 37 over the entire axial direction of the second bearing 32, and the performance of the second bearing 32 becomes more stable. Further, the meshing of the internal gear 16 and the external gear 23 prevents the load acting on the second bearing 32 from the second radial direction from being dispersed at each position in the axial direction of the second bearing 32. Since the load on the second bearing 32 is equalized in the axial direction, the function of the second bearing 32 is well maintained, and the frequency of maintenance and the like can be reduced.

Further, in the present embodiment, a part of the second bearing 32 and a part of the first bearing 31 overlap each other when viewed from the axial direction.
For example, unlike the present embodiment, the first bearing 31 does not overlap with the second bearing 32 when viewed from the axial direction, and is arranged outside the first radial direction of the second bearing 32. According to the above configuration of the embodiment, since the diameter of the first bearing 31 can be kept small, the outer shape of the reciprocating linear motion mechanism 10 in the first radial direction can be kept small.

Further, in the present embodiment, the rotational driving force around the first central axis C1 of the first rotating body 21 can be output to the outside of the reciprocating linear motion mechanism 10 via a gear. For example, a cup holder drive mechanism other than the reciprocating linear motion mechanism 10 provided in the can forming apparatus 1 can be stably operated while synchronizing with the operation of the reciprocating linear motion mechanism 10.

The present invention is not limited to the above-described embodiment, and the configuration can be changed without departing from the spirit of the present invention, for example, as described below.

The method of holding the inner rings 31a, 32a, the outer rings 31b, 32b, and the spacers 31d, 32d of the first bearing 31 and the second bearing 32, that is, the fixing means is not limited to each configuration described in the above-described embodiment.
The shapes of the first weight portion 51 and the second weight portion 52 are not limited to the shapes described in the above-described embodiment.

The present invention may be combined with each of the configurations described in the above-described embodiments and modifications, and the configurations can be added, omitted, replaced, or otherwise changed without departing from the spirit of the present invention. .. Further, the present invention is not limited to the above-described embodiments and the like, but is limited only to the scope of claims.

According to the reciprocating linear motion mechanism of the can forming apparatus of the present invention and the can forming apparatus, oil can be stably supplied to the bearing connecting the first rotating body and the second rotating body. Therefore, it has industrial applicability.

1 ... can forming device, 2 ... punch, 3 ... ram shaft, 6 ... cup holder, 7 ... through hole, 8 ... die, 9 ... end face, 10 ... reciprocating linear motion mechanism, 15 ... housing, 16 ... internal gear, 16a ... internal teeth, 21 ... first rotating body, 21d ... surface facing one side in the axial direction of the first rotating body, 22 ... second rotating body, 22e ... surface facing the other side in the axial direction of the second rotating body, 23. ... External gear, 23a ... External tooth, 25 ... Convex, 27 ... Concave, 32 ... Second bearing (bearing), 35 ... Ram shaft connection, 37 ... Second oil supply path (oil supply path), 37a ... Internal gear flow path, 37b ... External gear flow path, C1 ... 1st central axis, C2 ... 2nd central axis

Claims (4)

A housing with an internal gear centered on the first central axis,
A first rotating body located inside the housing in the first radial direction orthogonal to the first central axis and rotatably connected to the housing around the first central axis.
A second rotating body having an external gear that meshes with the internal gear about the second central axis parallel to the first central axis.
A bearing that connects the first rotating body and the second rotating body so as to be relatively rotatable around the second central axis.
A ram shaft connecting portion connected to the second rotating body and reciprocated linearly along a predetermined direction in the first radial direction, and a ram shaft connecting portion.
An oil supply path that penetrates the internal gear and the external gear and supplies oil to the bearing is provided.
The oil supply path is
An internal gear flow path that extends inside the internal gear and opens at least to the internal teeth of the internal gear.
A portion extending inside the external gear and opening to the external teeth of the external gear and an external gear flow path having a portion opening toward the bearing are provided.
When the external gear is arranged at a predetermined position around the first central axis with respect to the internal gear, the internal gear flow path and the meshing portion between the internal tooth and the external tooth are interposed. The external gear flow path communicates with each other.
Reciprocating linear motion mechanism of can molding equipment. The first rotating body has a convex portion that protrudes from the surface of the first rotating body facing one side in the axial direction to one side in the axial direction and has a convex portion centered on the second central axis.
The second rotating body has a recess that is recessed from the surface of the second rotating body facing the other side in the axial direction to one side in the axial direction, and has a recess into which the convex portion is inserted.
The bearing connects the convex portion and the concave portion so as to be relatively rotatable around the second central axis.
The reciprocating linear motion mechanism of the can molding apparatus according to claim 1. The external gear flow path penetrates the external gear in the second radial direction orthogonal to the second central axis.
The reciprocating linear motion mechanism of the can molding apparatus according to claim 1 or 2. The reciprocating linear motion mechanism of the can molding apparatus according to any one of claims 1 to 3.
A ram shaft extending in a predetermined direction and having the ram shaft connecting portion connected to one end thereof,
A punch arranged at the other end of the ram shaft and
With a die having a through hole into which the punch is inserted,
A cup holder, which is pressed against the end face of the die through which the through hole opens.
Can molding equipment.

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