JP7475230B2 - Reciprocating linear motion mechanism for can forming device and can forming device - Google Patents

Description

The present invention relates to a reciprocating linear motion mechanism for a can forming device and a can forming device.

Conventionally, bottomed cylindrical DI (Drawing & Ironing) cans are known. DI cans (hereinafter sometimes simply referred to as cans) are manufactured by subjecting a circular aluminum alloy blank to cupping, DI, and other processes. In cupping, the blank is drawn into a cup-shaped body. In DI, the cup-shaped body is pressed with a cup holder and drawn and ironed between a punch and a die. After DI, air is expelled from the punch into the inside of the can to release it from the punch.

Known can forming apparatuses for performing DI processing on a cup-shaped body include those described in Patent Documents 1 and 2. The can forming apparatus uses a reciprocating linear motion mechanism to linearly reciprocate a punch in a predetermined stroke direction via a ram shaft. The can forming apparatus also uses an air ejection mechanism to release (blow off) the formed can from the punch.
In Patent Documents 1 and 2, an air discharge mechanism supplies air to the punch through a ram shaft from outside the reciprocating linear motion mechanism.

JP 2005-169485 A Patent No. 3158312

Conventional can forming devices have many moving parts in the structure that supplies air to the ram shaft from outside the reciprocating linear motion mechanism, which requires frequent maintenance and part replacement. To solve this problem, a structure that supplies air to the ram shaft through the inside of the reciprocating linear motion mechanism has been considered, but simply forming an air flow path inside the reciprocating linear motion mechanism causes a large pressure drop when the can is released from the punch and the air flow path is opened to the atmosphere, which can make it difficult to stably release the next can from the punch.

One of the objectives of the present invention is to provide a reciprocating linear motion mechanism for a can forming device, and a can forming device, that can supply air to the ram shaft through the inside of the reciprocating linear motion mechanism while minimizing the pressure drop in the air flow path, and can stably release the formed can from the punch.

One aspect of the reciprocating linear motion mechanism of the can forming apparatus of the present invention comprises a housing having an internal gear centered on a first central axis, a first rotating body located inside the housing in a radial direction perpendicular to the first central axis and connected to the housing for relative rotation about the first central axis, a second rotating body having an external gear that meshes with the internal gear and is centered on a second central axis parallel to the first central axis and connected to the first rotating body for relative rotation about the second central axis, a ram shaft connecting part connected to the second rotating body and capable of linearly reciprocating along a predetermined direction of the radial direction, and an air supply passage that passes through each of the interiors of the first rotating body, the second rotating body, and the ram shaft connecting part, wherein the air supply passage is disposed at least inside the ram shaft connecting part and inside the second rotating body, and has an air chamber in which air is stored.
Furthermore, one aspect of the can forming apparatus of the present invention comprises a reciprocating linear motion mechanism of the can forming apparatus described above, a ram shaft extending in the predetermined direction and having one end connected to the ram shaft connecting portion, a punch arranged at the other end of the ram shaft, a die having a through hole through which the punch is inserted, a cup holder pressed against the end face of the die into which the through hole opens, and an air discharge mechanism that supplies air to the punch through an interior of the reciprocating linear motion mechanism of the can forming apparatus and the ram shaft, and the air discharge mechanism includes the air supply path.

In the present invention, the air supply passage passes through the inside of the reciprocating linear motion mechanism, so air can be supplied to the punch from inside the reciprocating linear motion mechanism through the ram shaft. Compared to the conventional structure in which air is supplied to the ram shaft from outside the reciprocating linear motion mechanism, the present invention reduces the number of moving parts and the frequency of maintenance and part replacement.

And according to the present invention, the air supply passage has an air chamber, so by temporarily storing air in the air chamber, it is possible to minimize the pressure drop when the can is released from the punch and the air supply passage is opened to the atmosphere. In other words, the air chamber can mitigate the sudden pressure drop in the air supply passage caused by blowing off (releasing) the molded can, and the pressure in the air supply passage can be restored to a predetermined value or higher in a short period of time. This stabilizes the air supply pressure from the air supply passage to the punch, and the next molded can can be stably released from the punch. It becomes possible to mold and blow off cans at high speed, making it possible to efficiently manufacture cans with stable quality and improving productivity.

In more detail, since the air chamber is provided at least inside the ram shaft connecting portion or inside the second rotor, the air chamber can be positioned close to the ram shaft and punch. By shortening the length of the air flow path from the air chamber to the punch, the air supply pressure to the ram shaft and punch can be made more stable. The function of the air chamber described above can be stably obtained, and the effects of the present invention can be stably achieved.

In the reciprocating linear motion mechanism of the can forming device, it is preferable that the ram shaft connecting portion is cylindrical and centered on a third central axis parallel to the second central axis, and the air chamber is a cylindrical chamber formed inside the ram shaft connecting portion.

In this case, a cylindrical air chamber is provided to match the shape of the internal space (chamber) of the cylindrical ram shaft connection part. The air chamber provides the above-mentioned effects while reducing the weight of the ram shaft connection part, which is reciprocated linearly in a specified direction (stroke direction).

In the reciprocating linear motion mechanism of the can forming device, it is preferable that the air chamber has a first chamber disposed inside the ram shaft connecting portion and a second chamber disposed inside the second rotor.

In this case, since the air chamber has a first chamber and a second chamber, a larger volume is ensured for the air chamber as a whole. The air chamber can reduce the pressure drop in the air supply path when the can is blown off from the punch. The can can be stably released from the punch.

According to one embodiment of the reciprocating linear motion mechanism of a can forming device and a can forming device of the present invention, it is possible to supply air to the ram shaft through the inside of the reciprocating linear motion mechanism while minimizing the pressure drop in the air flow path, and the formed can can be stably released from the punch.

FIG. 1 is a schematic diagram showing a can forming apparatus according to the present embodiment. FIG. 2 is a perspective view showing a reciprocating linear motion mechanism of the can forming apparatus of this embodiment. FIG. 3 is a cross-sectional view showing a reciprocating linear motion mechanism of the can forming apparatus of this embodiment. FIG. 4 is an enlarged cross-sectional view of a portion of FIG. FIG. 5 is a cross-sectional view showing the V-V section of FIG. Figure 6 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 relative to the internal gear, and shows a state in which the internal gear flow passage and the external gear flow passage of the oil supply passage are connected to each other. FIG. 7 is a perspective view illustrating the operation of the reciprocating linear motion mechanism of the can forming apparatus. FIG. 8 is a perspective view illustrating the operation of the reciprocating linear motion mechanism of the can forming apparatus. FIG. 9 is a perspective view illustrating the operation of the reciprocating linear motion mechanism of the can forming apparatus.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A can forming apparatus 1 according to one embodiment of the present invention and a reciprocating linear motion mechanism 10 (hereinafter, may be simply referred to as the reciprocating linear motion mechanism 10) of the can forming apparatus 1 will be described with reference to the drawings.
As shown in FIG. 1, the can forming apparatus 1 of this embodiment is a DI can manufacturing apparatus that performs DI processing on a cup-shaped body W, which is a workpiece, to produce a DI can 100.

First, the DI can 100 will be described.
The DI can 100 is a cylindrical shape with a bottom. The DI can 100 is used for can bodies such as two-piece cans and bottle cans in which contents such as beverages are filled and sealed. In the case of a two-piece can, the can body includes the DI can 100 and a disk-shaped can lid that is 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 formed by necking and threading the DI can 100, and a cap that is screwed onto the open end of the bottle can body.

The DI can 100 is formed into a bottomed cylindrical shape by performing a cupping process (drawing process) and a DI process (drawing and ironing process) on a disk-shaped blank punched out of a plate material such as an aluminum alloy. Specifically, in the case of a two-piece can, for example, the DI can 100 is manufactured through a plate material punching process, a cupping process, a DI process, a trimming process, a printing process, a painting process, a necking process, and a flanging process, in that order.

In the process of manufacturing the DI can 100, a blank is drawn (cupped) using a cupping press to form a cup-shaped body W. In other words, the cup-shaped body W is a formed intermediate body produced in the process of transitioning from the blank to the DI can 100 in the cupping process. The cup-shaped body W is a bottomed cylinder with a smaller peripheral wall height (length along the can axis) and a larger diameter than the DI can 100.

Next, the can forming apparatus 1 will be described.
The can forming apparatus 1 is used in the DI process, and performs DI processing, i.e., drawing (redrawing) and ironing, on the cup-shaped body W to form a DI can 100 having a peripheral wall greater in height and a smaller in diameter than the cup-shaped body W. Furthermore, in the DI process, the can forming apparatus 1 forms the bottom of the DI can 100 into a dome shape.

The can forming apparatus 1 includes a reciprocating linear motion mechanism 10, a ram shaft 3 extending in a predetermined direction (hereinafter may be referred to as a stroke direction S) in which a ram shaft connecting part 35 of the reciprocating linear motion mechanism 10, which will be described later, is caused to linearly reciprocate, and having one end connected to the ram shaft connecting part 35, a punch 2 arranged at the other end of the ram shaft 3, a ram bearing 5 supporting the ram shaft 3 so as to be able to reciprocate along the axial direction of a central axis O of the ram shaft 3, a die 8 having a through hole 7 into which the punch 2 is inserted, a cup holder 6 pressed against an end face 9 into which the through hole 7 of the die 8 opens, a domer 11 that sandwiches the bottom of a DI can 100 between the punch 2 and the domer 11 to form it into a dome shape, and an air discharge mechanism 70 that supplies air to the punch 2 through the inside of the reciprocating linear motion mechanism 10 and the ram shaft 3.
The central axes O of the ram shaft 3, punch 2, ram bearing 5, through hole 7 of the die 8, cup holder 6, and domer 11 are arranged coaxially with one another. In this embodiment, the central axis O, which is the common axis of these members, extends in the horizontal direction.

The can forming device 1 also includes a cup feeder (not shown) that supplies a cup-shaped body W onto 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, a can conveying mechanism (not shown) that conveys the formed DI can 100 to the outside of the device, a cup holder driving mechanism (not shown) that is driven in synchronization with the reciprocating linear motion mechanism 10 and moves the cup holder 6 back and forth in the axial direction of the central axis O with a stroke length different from that of the ram shaft connection part 35 of the reciprocating linear motion mechanism 10, and a driving source (not shown) such as a drive motor.

The reciprocating linear motion mechanism 10 converts a rotational driving force about a first central axis C1 input from a driving source into reciprocating linear motion in a stroke direction S along a central axis O, and outputs the reciprocating linear motion to a ram shaft connecting portion 35. A specific configuration of the reciprocating linear motion mechanism 10 will be described separately later.
The ram shaft 3 has a shaft shape extending along the central axis O. The ram shaft 3 is slidably supported by a pair of ram bearings 5 that are arranged spaced apart from each other in the axial direction of the central axis O.
The punch 2 has a cylindrical or columnar shape extending along a 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 closer to the die 8 is the front bearing 5F, and the other ram bearing 5 arranged closer to the reciprocating linear motion mechanism 10 is the rear bearing 5R. The front bearing 5F and the rear bearing 5R have a fluid bearing structure, such as a hydrostatic bearing or hydrostatic bearing.

A plurality of dies 8 are provided in line 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 penetrating the die 8 in the axial direction of the central axis O. The plurality of dies 8 includes one redrawing die 8A and a plurality of ironing dies (ironing dies) 8B located closer to the domer 11 than the redrawing die 8A. Although not shown in particular, a pilot ring is disposed on the domer 11 side of each ironing die 8B. The provision of the pilot ring prevents the punch 2 from contacting each ironing die 8B due to the impact when the DI can 100 leaves (passes through) each ironing die 8B during molding.
During forming, 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 onto the outside of the punch 2 and is slidable in the axial direction of the central axis O relative to the punch 2. The cup holder sleeve 6a is inserted into the inside of a cup-shaped body W arranged on an end face 9 of the redrawing die 8A and holds the bottom wall of the cup-shaped body W by pressing it against the end face 9. In other words, the cup holder 6 supports the cup-shaped body W by pressing the bottom wall of the cup-shaped body W against the end face 9 facing the reciprocating linear motion mechanism 10 of the die 8.
Although not specifically shown, the cup holder drive mechanism converts the rotational drive 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, thereby moving the cup holder 6 back and forth in a linear manner in the axial direction of the central axis O.

The domer 11 is a mold that forms the bottom of the DI can 100. The domer 11 is substantially cylindrical and extends in the axial direction of the central axis O. When the punch 2 is positioned at the forward end position in the stroke direction S, the domer 11 faces the punch 2 in the axial direction of the central axis O.

The air discharge mechanism 70 discharges air from an air discharge hole 71 opening on at least one of the tip surface and the outer peripheral surface of the punch 2, thereby releasing the DI can 100 from the punch 2. The air discharge mechanism 70 has an air discharge hole 71 that passes through the inside of the punch 2 and opens on the outer surface of the punch 2, an air supply path 28 (see FIG. 3 ), which will be described later, that passes through the inside of the reciprocating linear motion mechanism 10, an air communication path 72 that passes through the inside of the ram shaft 3 and communicates between the air discharge hole 71 and the air supply path 28, and an air supply source (not shown). In other words, the air discharge mechanism 70 includes the air supply path 28.
The air communication passage 72 has a ram shaft passage 72a that is connected to the air discharge hole 71 and extends inside the ram shaft 3 along the axial direction of the central axis O, and a piping passage 72b that extends inside a piping member 73 such as a hose and connects the ram shaft passage 72a to the air supply passage 28. The air supply source is, for example, an air compressor, and supplies air (compressed air) to the air supply passage 28.

The 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 the workpiece, is placed between the punch 2 and the redrawing die 8A with the cup axis (can axis) extended horizontally and its opening facing the punch 2. The bottom wall of the cup-shaped body W faces the end surface 9 of the redrawing die 8A.

The cup holder 6 and punch 2 are moved forward in the axial direction of the central axis O relative to this cup-shaped body W. That is, the cup holder 6 and punch 2 move in the stroke direction S from the reciprocating linear motion mechanism 10 toward the die 8, i.e., toward the front. Then, while the cup holder 6 presses the bottom wall of the cup-shaped body W against the end face 9 of the redrawing die 8A to perform a cup pressing operation, the punch 2 pushes the cup-shaped body W into the through hole 7 of the redrawing die 8A, thereby subjecting the cup-shaped body W to the redrawing process.

The redrawing process reduces the diameter of the cup-shaped body W and increases its length in the axial direction of the cup. The cup-shaped body W is then pressed into the punch 2 and ironed as it passes through each of the through holes 7 of the ironing dies 8B in sequence. That is, the peripheral wall of the cup-shaped body W is ironed and stretched, increasing the peripheral wall height and reducing the peripheral wall thickness, and is formed into the shape of a cylindrical DI can 100 with a bottom. The DI can 100 is cold-work hardened by ironing the peripheral wall, increasing its strength.

The ironed DI can 100 is pushed out by the punch 2 from the through hole 7 of the die 8 toward the domer 11. The bottom of the DI can 100 (the part that will become the bottom of the can) is then sandwiched and pressed between the punch 2 and the domer 11, 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 Figures 2 and 3, 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, a second rotating body 22 having an external gear 23 that meshes with the internal gear 16 and a concave portion 27, a second bearing 32, an air coupling member 40, a ram shaft connecting portion 35, a connecting bearing 54, a first weight portion 51, a second weight portion 52, a shaft body 26, a valve portion 80, an air supply passage 28, and an oil supply passage 37.

The housing 15 and its internal gear 16, the first rotor 21 (a portion thereof other than the convex portion 25), the first bearing 31, and the shaft 26 are centered on the first central axis C1, i.e., are arranged coaxially with each other about the first central axis C1. The convex portion 25, the second rotor 22 and its external gear 23, the concave portion 27, the second bearing 32, and the air coupling member 40 are centered on the second central axis C2, i.e., are arranged coaxially with each other about the second central axis C2. The ram shaft connecting portion 35 and the valve portion 80 are centered on the third central axis C3, i.e., are arranged coaxially with each other about the third central axis C3.
The first central axis C1 and the second central axis C2 are parallel to each other and spaced apart from each other. The second central axis C2 and the third central axis C3 are parallel to each other and spaced apart from each other. Note that Figs. 2 and 3 show a state in which the first central axis C1 and the third central axis C3 are coaxial with each other, that is, a state in which the first central axis C1 and the third central axis C3 coincide with each other. In this embodiment, the first central axis C1, the second central axis C2, and the third central axis C3 extend in the horizontal direction.

In the following description, the direction in which the first central axis C1 extends, the direction in which the second central axis C2 extends, and the direction in which the third central axis C3 extends are simply referred to as the axial direction. The Z-axis direction shown in each drawing corresponds to this axial direction. In the axial direction, the first rotating body 21 and the ram shaft connecting part 35 are disposed at different positions from each other. In the axial direction, the direction from the first rotating body 21 to the ram shaft connecting part 35 (+Z side) is referred to as one axial side, and the direction from the ram shaft connecting part 35 to the first rotating body 21 (-Z side) is referred to as the other axial side. Note that the one axial side may be referred to as the front side, and the other axial side may be referred to as the rear side.

A direction perpendicular to the first central axis C1 is referred to as a first radial direction. In the first radial direction, a direction approaching the first central axis C1 is referred to as an inner side of the first radial direction, and a direction away from the first central axis C1 is referred to as an outer side of the first radial direction.
The direction of rotation around the first central axis C1 is referred to as a first circumferential direction. Within the first circumferential direction, the direction in which the first rotor 21 is rotated relative to the housing 15 during operation of the can forming apparatus 1 is referred to as a first rotational direction T1.

A direction perpendicular to the second central axis C2 is referred to as a second radial direction. In the second radial direction, a direction approaching the second central axis C2 is referred to as an inner side of the second radial direction, and a direction away from the second central axis C2 is referred to as an outer side of the second radial direction.
The direction of rotation around the second central axis C2 is referred to as a second circumferential direction. Of the second circumferential directions, the direction in which the second rotor 22 is rotated relative to the first rotor 21 during operation of the can forming apparatus 1 is referred to as a second rotation direction T2.

A direction perpendicular to the third central axis C3 is referred to as a third radial direction. In the third radial direction, a direction approaching the third central axis C3 is referred to as an inner third radial direction, and a direction away from the third central axis C3 is referred to as an outer third radial direction.
The direction of rotation around the third central axis C3 is referred to as a third circumferential direction. Of the third circumferential directions, the direction in which the ram shaft connecting portion 35 is rotated relative to the ram shaft 3 during operation of the can forming apparatus 1 is referred to as a third rotational direction T3.

As shown in FIG. 3, the housing 15 is cylindrical and centered on the first central axis C1. The housing 15 has an internal gear 16, a housing body 17, an outer ring holding member 18, an oil receiver 20, and an oil reservoir 30.

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

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

The housing body 17 is a cylindrical member with a bottom and centered on the first central axis C1. The housing body 17 has a peripheral wall portion 17a, a bottom wall portion 17b, and an outer ring receiving portion 17c.

The peripheral wall portion 17a is generally cylindrical and has a center on the first central axis C1 and extends in the axial direction. The internal gear 16 is fixed to one axial end of the peripheral wall portion 17a. The bottom wall portion 17b is connected to the other axial end of the peripheral wall portion 17a.
The bottom wall portion 17b is annular and extends in a direction perpendicular to the first central axis C1. An outer periphery of the bottom wall portion 17b is connected to an end portion of the peripheral wall portion 17a on the other axial side. In this embodiment, the peripheral wall portion 17a and the bottom wall portion 17b are integrally formed.

The outer ring receiving portion 17c is disposed on the inner periphery of the peripheral wall portion 17a. The outer ring receiving portion 17c has a circular annular surface centered on the first central axis C1 and faces one side in the axial direction.

The outer race holding member 18 is annular about the first central axis C1. The outer race holding member 18 is generally cylindrical and extends in the axial direction. The outer race holding member 18 fits into the peripheral wall portion 17a and is fixed to the peripheral wall portion 17a by screws or the like (not shown). The outer race holding member 18 is disposed on one axial side of the outer race receiving portion 17c. The end face of the outer race holding member 18 facing one axial side faces the end face of the internal gear 16 facing the other axial side with a gap in the axial direction.

The outer race pressing member 18 has a radial pressing portion 18a and an axial pressing portion 18b.
The radial pressing portion 18a is cylindrical and centered on the first central axis C1. The outer peripheral surface of the radial pressing portion 18a contacts the inner peripheral surface of the peripheral wall portion 17a. In the illustrated example, the outer peripheral surface of the radial pressing portion 18a is a tapered surface located inward in the first radial direction toward the other axial side. In addition, the part of the inner peripheral surface of the peripheral wall portion 17a that contacts the outer peripheral surface of the radial pressing portion 18a is a tapered surface located inward in the first radial direction toward the other axial side. Therefore, when assembling the reciprocating linear motion mechanism 10, the radial pressing portion 18a of the outer ring pressing member 18 is inserted between the peripheral wall portion 17a and the first bearing 31 toward the other axial side, so that the first bearing 31 can be pressed from the outside in the first radial direction without rattling.

The axial pressing portion 18b is annular plate-shaped and centered on the first central axis C1. A pair of plate surfaces of the axial pressing portion 18b face in the axial direction. The axial pressing portion 18b is connected to one axial end of the radial pressing portion 18a. The inner peripheral portion of the axial pressing portion 18b protrudes inward in the first radial direction from the radial pressing portion 18a. The outer peripheral portion of the axial pressing portion 18b protrudes outward in the first radial direction from the radial pressing portion 18a. The axial pressing portion 18b is fixed to the peripheral wall portion 17a by screws or the like (not shown).

As shown in Figures 2 and 3, the oil receiver 20 is attached to an end face of the internal gear 16 facing one axial direction. The oil receiver 20 covers at least the lower end of the opening on one axial side of the housing 15. The oil receiver 20 is approximately semicircular when viewed from the axial direction.

An oil reservoir 30 for storing oil is provided inside the housing 15. The oil reservoir 30 is an oil storage chamber defined by the lower end of the peripheral wall portion 17a, the lower end of the bottom wall portion 17b, and the oil receiver 20. At least the lower end of the first bearing 31 is placed (immersed) in the oil stored in the oil reservoir 30. Furthermore, at least a portion of the second bearing 32 passes through the oil in the oil reservoir 30 when the can forming device 1 is in operation.

The first rotor 21 is located inside the housing 15 in the first radial direction. The first rotor 21 is coupled to the housing 15 so as to be capable of relative rotation about a first central axis C1.
3, the first rotating body 21 has a generally cylindrical shape centered on a first central axis C1. The first rotating body 21 is disposed within the housing main body 17. The first rotating body 21 is accommodated within the housing 15.

The first rotating body 21 has a flange portion 21 b and a protrusion 25 .
The flange 21b is disposed at one axial end of the outer periphery of the first rotor 21. The flange 21b is annular and has a first central axis C1 as its center. The flange 21b protrudes outward in a first radial direction from the outer periphery of the first rotor 21 and extends in a first circumferential direction. A pair of plate surfaces of the flange 21b face the axial direction. The plate surface of the pair of plate surfaces of the flange 21b facing the other axial side contacts the inner ring 31a of the first bearing 31 from one axial side.
The protrusion 25 will be described later.

The first bearing 31 is, for example, a tapered roller bearing. The first bearing 31 can support a load from a first radial direction (radial load) and a load from an axial direction (axial load). The first bearing 31 connects the housing 15 and the first rotor 21 so that they can rotate relative to each other around the first central axis C1.

The first bearing 31 has an inner ring 31a, an outer ring 31b, and rolling elements 31c.
The inner ring 31a is cylindrical and centered on the first central axis C1. The inner ring 31a is fitted onto the outer circumferential surface of the first rotor 21. The flange portion 21b contacts an end surface of the inner ring 31a that faces one axial side.

The outer ring 31b is cylindrical and 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 onto the inner peripheral surface of the radial pressing portion 18a. The end face of the outer ring 31b facing one axial side is in contact with the plate surface of the axial pressing portion 18b facing the other axial side. The end face of the outer ring 31b facing the other axial side is in contact with the outer ring support portion 17c. In other words, the outer ring 31b is sandwiched between the axial pressing portion 18b and the outer ring support portion 17c in the axial direction.

The rolling elements 31c are cylindrical rollers or the like. The rolling elements 31c are arranged between the inner ring 31a and the outer ring 31b in the first radial direction. The rolling elements 31c are held between the inner ring 31a and the outer ring 31b so that they can roll. A plurality of the rolling elements 31c are arranged side by side in the first circumferential direction. A plurality of rows of the rolling elements 31c arranged in the first circumferential direction (hereinafter simply referred to as rows of the rolling elements 31c) are arranged side by side in the axial direction. In this embodiment, the first bearing 31 has a pair of rows of the rolling elements 31c arranged at a distance from each other in the axial direction.

The protrusion 25 protrudes in the axial direction from the surface 21d facing one axial side of the first rotor 21 and extends in the axial direction. The protrusion 25 is cylindrical with the second central axis C2 as its center. Specifically, the protrusion 25 protrudes in the axial direction from the outer portion in the first radial direction of the surface 21d facing one axial side of the first rotor 21.

The protrusion 25 has an outer circumferential step 25a and a hole 25b.
The outer peripheral step 25a constitutes a part of the outer periphery of the protrusion 25. In the illustrated example, the outer peripheral step 25a is disposed at the other axial end of the outer periphery of the protrusion 25. The outer peripheral step 25a has an annular shape centered on the second central axis C2 and faces one axial side.
The hole 25b is a circular hole centered on the second central axis C2. The hole 25b is recessed from a surface of the protrusion 25 facing one axial side to the other axial side.

The second rotor 22 is disposed on one axial side of the first rotor 21. The second rotor 22 is coupled to the first rotor 21 so as to be capable of relative rotation about a second central axis C2.
The second rotating body 22 has a generally cylindrical shape with a top and a bottom, and is centered on the second central axis C2. The second rotating body 22 has an external gear 23, a top wall portion 22b, a joint insertion hole 22c, a recess 27, and an outer ring retaining ring 24. In this embodiment, the external gear 23 and the top wall portion 22b of the second rotating body 22 and the ram shaft connecting portion 35 are integrally formed by a single member.

The external gear 23 is cylindrical and centered on the second central axis C2, and extends in the axial direction. A portion of the surface 22e of the external gear 23 facing the other axial side faces a portion of the surface 21d of the first rotor 21 facing one axial side, with a gap in the axial direction.

The external gear 23 has a plurality of external teeth 23a arranged in the second circumferential direction on the outer periphery of the external gear 23. In this embodiment, the external teeth 23a are exposed to the outside of the reciprocating linear motion mechanism 10 through an opening on one axial side of the housing 15.
At least one of the plurality of external teeth 23a meshes with at least one of the plurality of internal teeth 16a. The pitch circle diameter of the external teeth 23a of the external gear 23 is half the pitch circle diameter of the internal teeth 16a of the internal gear 16.

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

The top wall portion 22b is disposed on one axial side of the external gear 23. The top wall portion 22b is plate-shaped and extends in a direction perpendicular to the second central axis C2. As shown in FIG. 3, the top wall portion 22b is connected to the end portion on one axial side of the external gear 23 and the end portion on the other axial side of the ram shaft connecting portion 35. In other words, the top wall portion 22b connects the external gear 23 and the ram shaft connecting portion 35. The top wall portion 22b may also be referred to as the blocking wall portion 22b or the front wall portion 22b.

The joint insertion hole 22c penetrates the top wall portion 22b in the axial direction. The joint insertion hole 22c is a substantially circular hole centered on the second central axis C2.

The recess 27 is recessed from the surface 22e facing the other axial side of the second rotor 22 toward one axial side and extends in the axial direction. The recess 27 is a circular hole centered on the second central axis C2. Specifically, the recess 27 is recessed from the inner portion in the second radial direction of the surface 22e facing the other axial side of the external gear 23 toward one axial side. In other words, the recess 27 opens to the other axial side. The inner diameter of the end of the recess 27 on the other axial side, i.e., the opening, is larger than the inner diameter of the portion of the recess 27 other than the opening. The end of the recess 27 on the one axial side is closed by the top wall portion 22b. The protrusion 25 is inserted into the recess 27.

The recess 27 has an inner peripheral step 27a.
The inner peripheral step 27a constitutes a part of the inner peripheral portion of the recess 27. In the illustrated example, the inner peripheral step 27a is disposed at one axial end of the inner peripheral portion of the recess 27. The inner peripheral step 27a has an annular surface shape centered on the second central axis C2 and faces the other axial side.

The outer ring retaining ring 24 is a circular ring centered on the second central axis C2. The outer ring retaining ring 24 is disposed at the other axial end of the recess 27, i.e., at the opening. The outer ring retaining ring 24 is fixed to the external gear 23 by a bolt member (not shown).

The second bearing 32 is, for example, a tapered roller bearing. 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 that they can rotate relatively around the second central axis C2. In other words, the second bearing 32 connects the first rotating body 21 and the second rotating body 22 so that they can rotate relatively around the second central axis C2.

The second bearing 32 has an inner ring 32a, an outer ring 32b, and rolling elements 32c.
The inner ring 32a is cylindrical and centered on the second central axis C2. The inner ring 32a fits onto the outer peripheral surface of the protrusion 25. An inner ring pressing portion 41 (described later) of the air coupling member 40 contacts an end face of the inner ring 32a facing one axial side. An outer peripheral step 25a contacts an end face of the inner ring 32a facing the other axial side. In other words, the inner ring 32a is sandwiched between the inner ring pressing portion 41 and the outer peripheral step 25a in the axial direction.

The outer ring 32b is cylindrical and centered on the second central axis C2. The outer ring 32b is positioned outside the inner ring 32a in the second radial direction. The outer ring 32b fits into the inner peripheral surface of the external gear 23, i.e., the inner peripheral surface of the recess 27. The inner peripheral step 27a contacts the end face of the outer ring 32b facing one axial side. The end face of the outer ring 32b facing the other axial side contacts the surface of the outer ring pressing ring 24 facing one axial side. In other words, the outer ring 32b is sandwiched between the inner peripheral step 27a and the outer ring pressing ring 24 in the axial direction.

The rolling elements 32c are cylindrical rollers or the like. The rolling elements 32c are arranged between the inner ring 32a and the outer ring 32b in the second radial direction. The rolling elements 32c are held between the inner ring 32a and the outer ring 32b so that they can roll. A plurality of the rolling elements 32c are arranged side by side in the second circumferential direction. A plurality of rows of the rolling elements 32c arranged in the second circumferential direction (hereinafter simply referred to as rows of the rolling elements 32c) are arranged side by side in the axial direction. In this embodiment, the second bearing 32 has a pair of rows of the rolling elements 32c arranged at a distance from each other in the axial direction.

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

The inner ring holding portion 41 is annular plate-shaped and centered on the second central axis C2. The plate surface of the inner ring holding portion 41 facing the other axial side contacts the surface of the convex portion 25 facing one axial side. The inner ring holding portion 41 is fixed to the convex portion 25 by screwing or the like. The outer periphery of the inner ring holding portion 41 protrudes outward in the second radial direction beyond the outer periphery of the convex portion 25. The outer periphery of the inner ring holding portion 41 contacts the inner ring 32a of the second bearing 32 from one axial side. In other words, the inner ring holding portion 41 holds the inner ring 32a of the second bearing 32 from one axial side.

The inner ring pressing portion 41 has a fitting protrusion 41a.
The fitting protrusion 41a has a cylindrical shape centered on the second central axis C2, and protrudes toward the other axial direction from a plate surface facing the other axial direction of the inner ring pressing portion 41. The fitting protrusion 41a fits into the hole portion 25b.

The inner tube 42 is a multi-stage cylindrical shape centered on the second central axis C2 and extends in the axial direction. The inner tube 42 protrudes toward one axial side from a plate surface facing one axial side of the inner ring holding portion 41. The inside of the inner tube 42 communicates with the inner periphery, i.e., the inside, of the inner ring holding portion 41. The inner tube 42 is fixed to the inner ring holding portion 41 by screwing or the like. That is, the inner tube 42 is fixed to the protrusion 25 via the inner ring holding portion 41.

The outer tube 43 is a cylindrical shape with a top centered on the second central axis C2 and extends in the axial direction. The inside of the outer tube 43 opens toward the other axial side. The outer tube 43 is inserted into the joint insertion hole 22c. The outer tube 43 fits into the inner peripheral surface of the joint insertion hole 22c. The outer tube 43 is fixed to the top wall portion 22b by screwing or the like. The inside of the outer tube 43 fits into a portion of one axial side of the inner tube 42. The outer tube 43 and the inner tube 42 can rotate relative to each other in the second circumferential direction. The inside of the outer tube 43 is connected to the inside of the inner tube 42.

The outer cylinder 43 has an outer cylinder air hole 43a.
The outer cylinder air hole 43a penetrates in the second radial direction through the peripheral wall of the outer cylinder 43. When viewed in the axial direction, the outer cylinder air hole 43a is located on an imaginary line connecting the third center axis C3 and the second center axis C2 of the ram shaft connecting portion 35.

2 to 4, the ram shaft connecting part 35 is connected to the second rotor 22 and is caused to perform reciprocating linear motion along a predetermined direction (stroke direction S) of the first radial direction while rotating around the third central axis C3. That is, when the can forming apparatus 1 is in operation, the ram shaft connecting part 35 performs reciprocating linear motion along the stroke direction S while rotating (rotating) in the third rotation direction T3 of the third circumferential direction. In this embodiment, when the reciprocating linear motion mechanism 10 is viewed from one axial side, the second rotation direction T2 of the second rotor 22 is a clockwise direction centered on the second central axis C2, and the third rotation direction T3 of the ram shaft connecting part 35 is a clockwise direction centered on the third central axis C3. However, this is not limited thereto, and when the reciprocating linear motion mechanism 10 is viewed from one axial side, the second rotation direction T2 may be a counterclockwise direction centered on the second central axis C2, and the third rotation direction T3 may be a counterclockwise direction centered on the third central axis C3.

The ram shaft connecting portion 35 is cylindrical and has a third central axis C3 as its center and extends in the axial direction. The ram shaft connecting portion 35 is cylindrical and has a bottom and an opening on one axial side. The opening on one axial side of the ram shaft connecting portion 35 is closed by a valve portion 80.
The ram shaft connecting portion 35 protrudes from the top wall portion 22b to one side in the axial direction. The ram shaft connecting portion 35 is located on one axial side of the housing 15. The ram shaft connecting portion 35 protrudes from the top wall portion 22b to the outside in the second radial direction.

The second radial distance between the third central axis C3 and the second central axis C2 of the ram shaft connecting portion 35 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 third central axis C3 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 hole 35a.
The air hole 35a has a circular hole shape centered on the third central axis C3 and is recessed toward the other axial side from a surface facing one axial side of the ram shaft connecting portion 35. The air hole 35a is capable of storing air therein.

The ram shaft connecting portion 35 is connected to a connecting rod located at one end of the ram shaft 3 via a connecting bearing 54 provided on the outer periphery of the ram shaft connecting portion 35. The connecting bearing 54 connects the ram shaft connecting portion 35 and the ram shaft 3 so that they can rotate relatively around the third central axis C3.

The connecting bearing 54 is, for example, a tapered roller bearing. The connecting bearing 54 can support a load from the third radial direction (radial load) and a load from the axial direction (axial load).

As shown in FIG. 4, the connecting bearing 54 has an inner ring 54a, an outer ring 54b, and rolling elements 54c.
The inner ring 54a is cylindrical and has its center on the third central axis C3. The inner ring 54a is fitted onto the outer circumferential surface of the ram shaft connecting portion 35.
The outer ring 54b is cylindrical and centered on the third central axis C3. The outer ring 54b is positioned outward of the inner ring 54a in the third radial direction. The outer ring 54b is fitted into a hole that penetrates one end of the ram shaft 3 in the axial direction.

The rolling elements 54c are cylindrical rollers or the like. The rolling elements 54c are arranged between the inner ring 54a and the outer ring 54b in the third radial direction. The rolling elements 54c are held between the inner ring 54a and the outer ring 54b so that they can roll. A plurality of the rolling elements 54c are arranged side by side in the third circumferential direction. A plurality of rows of the rolling elements 54c arranged in the third circumferential direction (hereinafter simply referred to as the rows of the rolling elements 54c) are arranged side by side in the axial direction. In this embodiment, the connecting bearing 54 has a pair of rows of the rolling elements 54c arranged at a distance from each other in the axial direction.

2 and 3, the first weight 51 and the second weight 52 are each connected to the first rotor 21 and are located on the opposite side of the second center axis C2 in the first radial direction, sandwiching the first center axis C1 therebetween. The first weight 51 and the second weight 52 function as so-called counterweights to maintain good rotational balance in the first circumferential direction when the first rotor 21 and its protruding portion 25, the second bearing 32, the second rotor 22 and its recessed portion 27, the ram shaft connecting portion 35, and the valve portion 80 rotate around the first center axis C1.

The first weight portion 51 is disposed on one axial side of the first rotating body 21. The first weight portion 51 protrudes from the surface 21d of the first rotating body 21 facing the one axial side toward the one axial side. The first weight portion 51 is semicircular. The first weight portion 51 is formed integrally with the first rotating body 21. The outer end portion of the first radial direction of the first weight portion 51, i.e., the outer periphery, protrudes outward in the first radial direction beyond the outer periphery of the first rotating body 21. The outer periphery of the first weight portion 51 overlaps with the first bearing 31 when viewed from the axial direction.

As shown in FIG. 3, the second weight portion 52 is disposed on the other axial side of the first rotating body 21. The second weight portion 52 is fixed to the end portion on the other axial side of the first rotating body 21 by a bolt member or the like. The second weight portion 52 extends in a semicircular arc shape centered on the first central axis C1.

The shaft body 26 is a multi-stage cylindrical shape centered on the first central axis C1 and extends in the axial direction. The shaft body 26 is disposed on the other axial side of the first rotating body 21. The shaft body 26 protrudes from the surface of the first rotating body 21 facing the other axial side toward the other axial side. The shaft body 26 is formed integrally with 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 shaft body 26 is supported by a third bearing (not shown) so as to be rotatable about the first central axis C1. A rotational driving force in a 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 rotational direction T1 relative to the housing 15 by the rotational driving force of the driving source.

4 and 5 , the valve unit 80 is connected to the ram shaft connecting portion 35. The valve unit 80 is disposed on one axial side of the ram shaft connecting portion 35. The valve unit 80 is attached to the ram shaft connecting portion 35 and the ram shaft 3. The valve unit 80 allows air to flow therethrough, and constitutes part of the flow path of the air supply passage 28.
The valve unit 80 can be switched between a flow mode (the state shown in FIGS. 4 and 5) in which air can pass through the interior, and a blocking mode (not shown) in which air cannot pass through the interior, depending on the rotational position of the ram shaft connecting part 35 about the third central axis C3.

The valve portion 80 has a ram shaft fixing portion 81 , a rotating portion 82 , and a valve bearing 83 .
The ram shaft fixing portion 81 is fixed to the ram shaft 3 (see FIG. 2). Specifically, the ram shaft fixing portion 81 is fixed to one end (connecting rod) of the ram shaft 3 by a bolt member 84.

The ram shaft fixing portion 81 has a fixing plate portion 85 , a fixing cylinder portion 86 , an outer cylinder portion 87 , an air slot 87 a , and a fixing screw 88 .
The fixing plate portion 85 is shaped like a plate extending in a direction perpendicular to the third central axis C3. In this embodiment, the fixing plate portion 85 is shaped like a substantially rectangular plate. The fixing plate portion 85 is attached to one end of the ram shaft 3 by a plurality of bolt members 84.

The fixed cylinder portion 86 is cylindrical and centered on the third central axis C3, and extends in the axial direction. The fixed cylinder portion 86 protrudes to one axial side from a plate surface facing one axial side of the fixed plate portion 85. The fixed cylinder portion 86 is fixed to the ram shaft 3 via the fixed plate portion 85.

The fixed cylinder portion 86 has an adjustment slot 86a and an air connection port 86b.
The adjustment elongated hole 86a penetrates the fixed cylinder portion 86 in the third radial direction and extends around the third central axis C3. In the illustrated example, the adjustment elongated hole 86a is disposed in an upper portion of the fixed cylinder portion 86 in the vertical direction.
The air connection port 86b is a hole that penetrates the fixed cylinder portion 86 in the third radial direction. In the illustrated example, the air connection port 86b is disposed in a lower portion of the fixed cylinder portion 86 in the vertical direction. One end of a piping member 73 such as a hose is connected to the air connection port 86b (see FIG. 1). The other end of the piping member 73 is connected to a piping connection port of the ram shaft 3.

The outer tube portion 87 is tubular about the third central axis C3 and extends in the axial direction. The outer tube portion 87 is cylindrical. The outer tube portion 87 is slidably fitted into the fixed tube portion 86. The outer peripheral surface of the outer tube portion 87 is in sliding contact with the inner peripheral surface of the fixed tube portion 86 in the third circumferential direction so as to be freely rotatable. In other words, the fixed tube portion 86 is located outside the outer tube portion 87 in the third radial direction.

The long air hole 87a penetrates the outer tube portion 87 in the third radial direction and extends around the third central axis C3. The long air hole 87a is a slit-shaped hole that extends over a predetermined range in the third circumferential direction in the peripheral wall of the outer tube portion 87. In the illustrated example, the long air hole 87a is disposed in the lower part of the outer tube portion 87 in the vertical direction. At least a part of the long air hole 87a faces the air connection port 86b in the third radial direction. In other words, the long air hole 87a and the air connection port 86b communicate with each other. The position of the long air hole 87a around the third central axis C3 can be adjusted by rotating the outer tube portion 87 around the third central axis C3 relative to the fixed tube portion 86.

The fixing screw 88 fixes the fixed cylinder portion 86 and the outer cylinder portion 87. The fixing screw 88 is inserted into the adjustment slot 86a and screwed into the outer cylinder portion 87.
The fixing screw 88 has a bolt 88a and a nut 88b. The bolt 88a is inserted into the adjustment elongated hole 86a from the outside in the third radial direction and is screwed into a female threaded hole that opens into the outer circumferential surface of the outer tubular portion 87. The nut 88b is screwed into the male threaded portion of the bolt 88a and comes into contact with the outer circumferential surface of the fixing tubular portion 86 from the outside in the third radial direction.

When the bolt 88a is screwed into the outer cylinder portion 87, the nut 88b is tightened inward in the third radial direction to fix the fixed cylinder portion 86 and the outer cylinder portion 87, restricting the relative movement between the fixed cylinder portion 86 and the outer cylinder portion 87 in the third circumferential direction. This positions the air long hole 87a in the third circumferential direction.

The rotating part 82 is connected to the ram shaft connecting part 35 and can rotate relatively to the ram shaft fixing part 81 around the third central axis C3. In this embodiment, the rotating part 82 is connected to the ram shaft fixing part 81 so as to be rotatable relatively to the ram shaft fixing part 81 in the third circumferential direction by a pair of valve bearings 83 that are arranged apart from each other in the axial direction. The pair of valve bearings 83 are arranged on one axial side and the other axial side of the outer cylinder part 87. In other words, the outer cylinder part 87 is located between the pair of valve bearings 83 in the axial direction.

The rotating portion 82 has an attachment plate 89 , an inner cylinder portion 90 , an axial flow passage 90 a , a radial flow passage 90 b , and an inner ring pressing plate 91 .
The mounting plate 89 is annular and has a center on the third central axis C3 and extends in a direction perpendicular to the third central axis C3. The outer periphery of the mounting plate 89 is fixed to one axial end of the ram shaft connecting portion 35 by screws or the like. In other words, the rotating portion 82 is fixed to the ram shaft connecting portion 35. The outer periphery of the mounting plate 89 presses the inner ring 54a of the connecting bearing 54 from one axial side.

The mounting plate 89 has a fitting portion 89a.
The fitting portion 89a is cylindrical and centered on the third central axis C3, and protrudes in the other axial direction from the plate surface facing the other axial direction of the mounting plate 89. The fitting portion 89a fits into one axial end of the inner circumferential surface of the air hole 35a, i.e., into the opening.

The inner cylinder portion 90 is cylindrical and extends in the axial direction, centered on the third central axis C3. The inner cylinder portion 90 protrudes from the mounting plate 89 to one side in the axial direction. The inner cylinder portion 90 is cylindrical with a top. The inner cylinder portion 90 has a peripheral wall and a top wall connected to the end of the peripheral wall on one side in the axial direction. The inner cylinder portion 90 slidably fits into the outer cylinder portion 87. The outer peripheral surface of the inner cylinder portion 90 slides and rotates freely in the third circumferential direction with the inner peripheral surface of the outer cylinder portion 87. In other words, the inner cylinder portion 90 is located inside the outer cylinder portion 87 in the third radial direction. The other axial end of the inner cylinder portion 90 fits into the inner peripheral portion of the mounting plate 89. The inner cylinder portion 90 and the mounting plate 89 are fixed to each other by screws or the like. In other words, the inner cylinder portion 90 is fixed to the ram shaft connecting portion 35 via the mounting plate 89. Therefore, when the can forming device 1 is in operation, the inner cylinder portion 90 rotates together with the ram shaft connecting portion 35 in the third rotation direction T3 around the third central axis C3.

The axial flow passage 90a extends axially inside the inner cylinder 90. The axial flow passage 90a is disposed on the third central axis C3. One axial end of the axial flow passage 90a is blocked by the top wall of the inner cylinder 90. The other axial end of the axial flow passage 90a opens to a surface of the inner cylinder 90 facing the other axial side. The axial flow passage 90a communicates with the inside of the air hole 35a through the inner periphery (interior) of the mounting plate 89.

The radial flow passages 90b extend inside the inner cylinder portion 90 in the third radial direction and open to the axial flow passages 90a and the outer peripheral surface of the inner cylinder portion 90. When the inner cylinder portion 90 rotates in the third circumferential direction relative to the outer cylinder portion 87, the radial flow passages 90b communicate with the air long holes 87a within a predetermined range around the third central axis C3.

As shown in FIG. 5, the state in which the radial flow passages 90b and the long air holes 87a face each other in the third radial direction and communicate with each other corresponds to the flow mode of the valve unit 80. In the flow mode, the inside of the air hole 35a and the inside of the piping member 73 (piping flow passage 72b) communicate with each other through the inside of the valve unit 80, that is, through the inner periphery of the mounting plate 89, the axial flow passages 90a, the radial flow passages 90b, the long air holes 87a, and the air connection port 86b. Therefore, in the flow mode, air is supplied from the ram shaft connection part 35 to the ram shaft 3 through the inside of the valve unit 80.

Although not specifically shown, the state in which the radial flow passages 90b and the long air holes 87a do not face each other in the third radial direction and communication between the radial flow passages 90b and the long air holes 87a is blocked corresponds to the shutoff mode of the valve unit 80. In the shutoff mode, communication between the inside of the air hole 35a and the inside of the piping member 73 (piping flow passage 72b) through the inside of the valve unit 80 is cut off. Therefore, in the shutoff mode, the supply of air from the ram shaft connection part 35 to the ram shaft 3 through the inside of the valve unit 80 is cut off (stopped).

As shown in FIG. 4, the inner race pressing plate 91 is a disk-shaped plate centered on the third central axis C3 and extending in a direction perpendicular to the third central axis C3. The inner race pressing plate 91 is fixed to one axial end of the inner cylinder portion 90, i.e., the top wall, by means of screws or the like. The outer periphery of the inner race pressing plate 91 presses down on the inner race of one of the pair of valve bearings 83, which is disposed on one axial side of the outer cylinder portion 87, from one axial side.

As shown in FIG. 3, the air supply passage 28 is an air flow path formed inside the reciprocating linear motion mechanism 10. The air supply passage 28 extends through the inside of the shaft body 26, the inside of the first rotor 21, the inside of the convex portion 25, the inside of the air coupling member 40, the inside of the top wall portion 22b of the second rotor 22, the inside of the ram shaft connecting portion 35, and the inside of the valve portion 80. In other words, the air supply passage 28 passes through the insides of the shaft body 26, the first rotor 21, the air coupling member 40, the second rotor 22, the ram shaft connecting portion 35, and the valve portion 80.

The air supply passage 28 has a first air flow path 28a, a second air flow path 28b, a third air flow path 28c, an air joint flow path 28d, a fourth air flow path 28e, a fifth air flow path 28h, an air chamber 29, and a valve portion flow path 28g. The first air flow path 28a, the second air flow path 28b, the third air flow path 28c, the air joint flow path 28d, the fourth air flow path 28e, the fifth air flow path 28h, the air chamber 29, and the valve portion flow path 28g are connected to each other. Air supplied to the air supply passage 28 from an air supply source (not shown) flows from the upstream to the downstream side inside the air supply passage 28 in the order of the first air flow path 28a, the second air flow path 28b, the third air flow path 28c, the air joint flow path 28d, the fourth air flow path 28e, the fifth air flow path 28h, the air chamber 29, and the valve portion flow path 28g.

The first air flow path 28a is disposed inside the shaft body 26 and inside the first rotor 21. In this embodiment, the first air flow path 28a extends in the axial direction on the first central axis C1. One axial end of the first air flow path 28a is blocked by a plug.

The second air flow path 28b is disposed inside the first rotor 21. The second air flow path 28b extends in the first radial direction. The inner end of the second air flow path 28b in the first radial direction is connected to the first air flow path 28a. The outer end of the second air flow path 28b in the first radial direction is blocked by a plug portion.

The third air flow path 28c is disposed within the first rotor 21 and the protrusion 25. The third air flow path 28c extends axially on the second central axis C2. The other axial end of the third air flow path 28c is connected to the second air flow path 28b. The one axial end of the third air flow path 28c is connected to the air joint flow path 28d through the hole 25b.

The air joint flow path 28d has the inside (internal space) of the inner ring holding part 41, the inside of the inner cylinder 42, the inside of the outer cylinder 43, and the outer cylinder air hole 43a. Air that flows into the air joint flow path 28d from the third air flow path 28c through the hole 25b flows through the inside of the inner ring holding part 41, the inside of the inner cylinder 42, the inside of the outer cylinder 43, and the outer cylinder air hole 43a in that order, and flows out into the fourth air flow path 28e.

The fourth air flow passage 28e is disposed inside the top wall portion 22b and extends in the second radial direction. When viewed in the axial direction, the fourth air flow passage 28e extends along an imaginary straight line connecting the third central axis C3 and the second central axis C2 of the ram shaft connecting portion 35. The inner end of the fourth air flow passage 28e in the second radial direction is connected to the outer cylinder air hole 43a. The outer end of the fourth air flow passage 28e in the second radial direction is blocked by the plug portion 28f.

The fifth air flow passage 28h is disposed within the top wall portion 22b and the ram shaft connecting portion 35. The fifth air flow passage 28h extends in the axial direction on the third central axis C3. The other axial end of the fifth air flow passage 28h is connected to the fourth air flow passage 28e. The one axial end of the fifth air flow passage 28h is connected to the air chamber 29.

The air chamber 29 is disposed at least inside either the ram shaft connecting portion 35 or the second rotor 22. In this embodiment, the air chamber 29 is disposed inside the ram shaft connecting portion 35. The air chamber 29 is a cylindrical chamber formed inside the ram shaft connecting portion 35. The air chamber 29 extends in the axial direction about the third central axis C3. Among the flow paths that constitute the air supply passage 28, the air chamber 29 has the largest flow path cross-sectional area and the largest volume. The air chamber 29 is capable of temporarily storing air (compressed air) inside the air chamber 29. In other words, air is stored in the air chamber 29.

The volume of the air chamber 29 is equal to or greater than the total volume of the air flow paths located downstream of the air chamber 29, specifically, equal to or greater than the sum of the volumes of the valve flow path 28g, the air communication passage 72, and the air discharge hole 71.

As shown in FIG. 4, the valve section flow path 28g has the interior (internal space) of the mounting plate 89, the axial flow path 90a, the radial flow path 90b, the air long hole 87a, and the air connection port 86b. Air that flows into the interior of the valve section 80 from the air chamber 29 flows through the interior of the mounting plate 89, the axial flow path 90a, the radial flow path 90b, the air long hole 87a, and the air connection port 86b in that order, only when the valve section 80 is in the flow mode, and flows out into the piping flow path 72b.

As shown in Figures 3 and 6, the oil supply passage 37 passes through the housing body 17, the internal gear 16, and the external gear 23, and supplies oil to the second bearing 32. The oil supply passage 37 has a housing flow passage 37d, a circumferential flow passage 37e, an internal gear flow passage 37a, and an external gear flow passage 37b.

The housing flow passage 37d penetrates the peripheral wall of the housing body 17. The outer end of the housing flow passage 37d in the first radial direction opens to the outer peripheral surface of the housing body 17. The inner end of the housing flow passage 37d in the first radial direction opens to the inner peripheral surface of the housing body 17. In the illustrated example, the housing flow passage 37d bends and extends in a crank shape inside the housing body 17. Oil is supplied to the housing flow passage 37d from outside the housing 15 via an oil supply port (not shown).

The circumferential flow passage 37e is recessed inward in the first radial direction from the outer peripheral surface of the internal gear 16 and extends in the first circumferential direction. The circumferential flow passage 37e is an annular groove centered on the first central axis C1. The inner end of the housing flow passage 37d in the first radial direction is connected to the circumferential flow passage 37e.

The internal gear flow passage 37a penetrates the peripheral wall of the internal gear 16. In this embodiment, the internal gear flow passage 37a penetrates the internal gear 16 in the first radial direction. The outer end of the internal gear flow passage 37a in the first radial direction is connected to the circumferential flow passage 37e. The inner end of the internal gear flow passage 37a in the first radial direction opens to the inner peripheral surface of the internal gear 16, i.e., the internal teeth 16a. In other words, the internal gear flow passage 37a extends inside the internal gear 16 and opens to at least the internal teeth 16a.

The external gear flow passage 37b penetrates the peripheral wall of the external gear 23. In this embodiment, the external gear flow passage 37b penetrates the external gear 23 in the second radial direction. The outer end of the external gear flow passage 37b in the second radial direction opens to the outer peripheral surface of the external gear 23, i.e., the external teeth 23a. The inner end of the external gear flow passage 37b in the second radial direction opens to a portion of the inner peripheral surface of the external gear 23 that faces the second bearing 32. In other words, the external gear flow passage 37b extends inside the external gear 23 and has a portion that opens to the external teeth 23a and a portion that opens toward the second bearing 32.

Multiple pairs of internal gear flow passages 37a and external gear flow passages 37b are provided. In this embodiment, two pairs of internal gear flow passages 37a and external gear flow passages 37b are provided, but three or more pairs may be provided. The multiple internal gear flow passages 37a are arranged at intervals from each other in the first circumferential direction. The multiple external gear flow passages 37b are arranged at intervals from each other in the second circumferential direction.

As shown in FIG. 6, when the external gear 23 is disposed at a predetermined position around the first center axis C1 with respect to the internal gear 16, the internal gear flow passage 37a and the external gear flow passage 37b face each other in the first radial direction and communicate with each other. In more detail, when the external gear 23 rotates in the second circumferential direction and revolves in the first circumferential direction along the inner periphery of the internal gear 16, and is disposed at a predetermined position in the first circumferential direction, the internal gear flow passage 37a and the external gear flow passage 37b communicate with each other through the meshing portion between the internal teeth 16a and the external teeth 23a. As a result, the oil in the internal gear flow passage 37a flows into the external gear flow passage 37b, and the oil that flows into the external gear flow passage 37b flows inward in the second radial direction through the external gear flow passage 37b and is discharged toward the second bearing 32.

The number of internal teeth 16a of the internal gear 16 is twice the number of external teeth 23a of the external gear 23. Therefore, the internal gear flow path 37a and the external gear flow path 37b face each other at the predetermined position for each revolution around the first center axis C1 of the external gear 23, i.e., each revolution. In other words, oil flows from the internal gear flow path 37a to the external gear flow path 37b, and oil is discharged from the external gear flow path 37b to the second bearing 32, for each revolution of the external gear 23.

In this embodiment, at least one internal gear flow passage 37a is disposed in a portion of the internal gear 16 that is located above the first central axis C1 in the vertical direction. At least one external gear flow passage 37b faces and communicates with the internal gear flow passage 37a in a portion of the external gear 23 that is located above the second central axis C2 in the vertical direction. In other words, when the internal gear flow passage 37a and the external gear flow passage 37b are connected, the oil flowing through the internal gear flow passage 37a is supplied to the second bearing 32 from above through the external gear flow passage 37b, making it easier for the oil to be distributed stably throughout the entire second bearing 32.

In the reciprocating linear motion mechanism 10 of the present embodiment described above, when a rotational driving force about the first central axis C1 is transmitted from a driving source (not shown) to the shaft body 26 and the first rotating body 21, the first rotating body 21 is rotated about the first central axis C1 relative to the housing 15, as shown in Figures 2, 7, 8, and 9. When the first rotating body 21 is rotated about the first central axis C1, the second rotating body 22 supported by the first rotating body 21 is also rotated about the first central axis C1.

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

The ram shaft connecting portion 35 connected to the second rotating body 22 and the rotating portion 82 of the valve portion 80 rotate in a third rotational direction T3 around the third central axis C3 while performing a reciprocating linear motion along a predetermined direction in the first radial direction, i.e., 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 rotor 21 into reciprocating linear motion in the stroke direction S and outputs it to the ram shaft connecting part 35. As a result, the punch 2 connected to the ram shaft connecting part 35 via the ram shaft 3 is caused to perform reciprocating linear motion in the stroke direction S. The punch 2, die 8, cup holder 6, etc. make it possible to perform DI processing on the cup-shaped body W, and the cup-shaped body W can be formed into a DI can 100.

In this embodiment, the air supply passage 28 passes through the inside of the reciprocating linear motion mechanism 10, so air can be supplied to the punch 2 from inside the reciprocating linear motion mechanism 10 through the ram shaft 3. Compared to a conventional structure in which air is supplied to the ram shaft from outside the reciprocating linear motion mechanism, this embodiment reduces the number of moving parts and the frequency of maintenance and part replacement.

According to this embodiment, the air supply passage 28 has an air chamber 29, so that by temporarily storing air in the air chamber 29, the pressure drop when the DI can (can) 100 is released from the punch 2 and the air discharge hole 71, the air communication passage 72, and the air supply passage 28 (hereinafter referred to as the air supply passage 28, etc.) are opened to the atmosphere can be suppressed to a small value. In other words, the air chamber 29 can mitigate the sudden pressure drop in the air supply passage 28, etc. caused by blowing off (releasing) the can 100 after molding, and the pressure of the air supply passage 28, etc. can be restored to a predetermined value or higher in a short time. Therefore, the air supply pressure from the air supply passage 28, etc. to the punch 2 is stabilized, and the next molded can 100 can be stably released from the punch 2. It becomes possible to mold and blow off the can 100 at high speed, and cans 100 with stable quality can be efficiently manufactured, thereby improving productivity.

More specifically, the air chamber 29 is provided at least inside the ram shaft connecting portion 35 or inside the second rotating body 22, and in this embodiment, it is provided inside the ram shaft connecting portion 35. This allows the air chamber 29 to be positioned close to the ram shaft 3 and punch 2. By shortening the length of the air flow path from the air chamber 29 to the punch 2, the air supply pressure to the ram shaft 3 and punch 2 can be made more stable. The function of the air chamber 29 described above is stably obtained, and the effects of this embodiment are stably achieved.

In this embodiment, the air chamber 29 is a cylindrical chamber formed inside the ram shaft connecting portion 35. That is, the cylindrical air chamber 29 is provided to match the shape of the internal space (chamber) of the cylindrical ram shaft connecting portion 35. The air chamber 29 provides the above-mentioned effects while reducing the weight of the ram shaft connecting portion 35, which is caused to move back and forth linearly in a specified direction (stroke direction S).

In this embodiment, the valve unit 80 is switched between a flow mode and a cutoff mode depending on the rotational position of the ram shaft connecting part 35 about the third central axis C3. That is, the supply and cutoff of air from the air supply path 28 to the ram shaft 3 is switched depending on whether the valve unit 80 is in the flow mode or the cutoff mode. In more detail, when the ram shaft connecting part 35 is caused to perform a reciprocating linear motion along a predetermined direction (stroke direction S) while rotating about the third central axis C3, air is supplied to the ram shaft 3 through the valve unit 80 in a predetermined region of the stroke direction S, and the supply of air to the ram shaft 3 through the valve unit 80 is cut off in other regions different from the predetermined region.

Unlike the present embodiment, which uses, for example, a solenoid valve, a sensor, and a control unit to electrically synchronize the discharge of air with the operation of the reciprocating linear motion mechanism, this embodiment can mechanically synchronize with the operation of the reciprocating linear motion mechanism 10 and use a simple structure to timely discharge air from the punch 2 into the inside of the can 100. For example, even if the molding speed of the can 100 is changed, the molded can 100 can be blown off in a timely manner without requiring complex adjustment work to synchronize the timing of the air discharge.

In this embodiment, the rotating portion 82 rotates around the third central axis C3 together with the ram shaft connecting portion 35 relative to the ram shaft fixing portion 81, and while the radial flow path 90b and the long air hole 87a are in communication with each other within a predetermined range around the third central axis C3, the valve portion 80 is in the flow mode, and air is supplied from the air supply path 28 to the ram shaft 3.
In addition, while the rotating part 82 rotates around the third central axis C3 together with the ram shaft connecting part 35 relative to the ram shaft fixing part 81 and communication between the radial flow passage 90b and the long air hole 87a is blocked in a range other than the specified range around the third central axis C3, the valve part 80 is set in the blocking mode, and the supply of air from the air supply path 28 to the ram shaft 3 is blocked.
According to the above-described configuration of this embodiment, the formed can 100 can be blown off stably and timely with a simple structure.

In this embodiment, the position of the long air hole 87a about the third central axis C3 can be adjusted by rotating the outer cylinder portion 87 relative to the fixed cylinder portion 86 about the third central axis C3.
In this case, it is possible to adjust the timing at which the long air holes 87a communicate with the radial flow paths 90b. That is, the timing at which air is discharged into the inside of the can 100 can be adjusted by the simple operation of rotating the outer cylinder portion 87 about the third central axis C3. This allows the formed can 100 to be stably blown off from the punch 2.

In this embodiment, the fixing screw 88 is inserted into the adjustment slot 86 a and screwed into the outer cylinder portion 87 .
In this case, the long air hole 87a can be positioned about the third central axis C3 by rotating the outer cylinder portion 87 relative to the fixed cylinder portion 86 about the third central axis C3 and fixing the fixed cylinder portion 86 and the outer cylinder portion 87 with the fixing screw 88 in a state where the position of the long air hole 87a about the third central axis C3 is adjusted. In other words, with a simple configuration, the position of the long air hole 87a about the third central axis C3 can be adjusted and that position can be fixed.

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

Although not specifically shown, the air chamber 29 may have a first chamber positioned inside the ram shaft connecting portion 35 and a second chamber positioned inside the second rotating body 22.
In this case, since the air chamber 29 has the first chamber and the second chamber, a larger volume is ensured for the air chamber 29 as a whole. The air chamber 29 can further reduce the pressure drop in the air supply path 28 etc. when the can 100 is blown off from the punch 2. The can 100 can be stably released from the punch 2.

The shapes of the first weight portion 51 and the second weight portion 52 are not limited to those described in the above embodiment.

The present invention may be implemented by combining the various configurations described in the above-mentioned embodiments and modifications, etc., without departing from the spirit of the present invention, and addition, omission, substitution, and other modifications of configurations are possible. Furthermore, the present invention is not limited to the above-mentioned embodiments, etc., but is limited only by the scope of the claims.

The reciprocating linear motion mechanism of the can forming device and the can forming device of the present invention can supply air to the ram shaft through the inside of the reciprocating linear motion mechanism while minimizing the pressure drop in the air flow path, allowing the formed can to be stably released from the punch. 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, 21...first rotor, 22...second rotor, 23...external gear, 28...air supply path, 29...air chamber, 35...ram shaft connection, 70...air discharge mechanism, 100...DI can, C1...first central axis, C2...second central axis, C3...third central axis

Claims (4)

a housing having an internal gear centered on a first central axis;
a first rotor located inside the housing in a radial direction perpendicular to the first central axis and coupled to the housing so as to be rotatable relative to the housing about the first central axis;
a second rotating body having an external gear meshing with the internal gear about a second central axis parallel to the first central axis, the second rotating body being connected to the first rotating body so as to be rotatable relative to the second central axis;
a ram shaft connecting portion connected to the second rotor and adapted to perform a reciprocating linear motion along a predetermined direction in the radial direction;
an air supply passage passing through the inside of each of the first rotating body, the second rotating body, and the ram shaft connecting portion;
The air supply passage is disposed at least inside the ram shaft connecting portion or inside the second rotor, and has an air chamber in which air is stored.
Reciprocating linear motion mechanism for can forming equipment. The ram shaft connecting portion has a cylindrical shape centered on a third central axis parallel to the second central axis,
The air chamber is a cylindrical chamber formed inside the ram shaft connecting portion.
2. The reciprocating linear motion mechanism of a can forming apparatus according to claim 1. The air chamber is
A first chamber disposed inside the ram shaft connecting portion;
A second chamber disposed inside the second rotor.
3. The reciprocating linear motion mechanism for a can forming apparatus according to claim 1 or 2. A reciprocating linear motion mechanism for a can forming apparatus according to any one of claims 1 to 3;
a ram shaft extending in the predetermined direction and having one end connected to the ram shaft connecting portion;
a punch disposed at the other end of the ram shaft;
a die having a through hole into which the punch is inserted;
a cup holder that is pressed against an end surface of the die where the through hole is open;
an air discharge mechanism for supplying air to the punch through an interior of the reciprocating linear motion mechanism of the can forming device and through the ram shaft,
The air discharge mechanism includes the air supply passage.
Can forming equipment.

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