JP2010242812A - Power transmission mechanism of working device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission mechanism of a working device enhanced in lubricating performance by lubricating any position. <P>SOLUTION: A first eccentric cam 13 and a second eccentric cam 14 are provided on both surfaces of a driven gear 12 engaged with a drive gear with a phase difference of 180 degrees in the rotational direction. The driven gear 12 is provided by stacking a plurality of gear plates 50-55 in the thickness direction. Through-holes 50a-55a are formed at plane surfaces of the gear plates 50-55, and the gear plates 50-55 are welded so that the through-holes 50a-55a communicate with one another with phases shifted. Therefore, the through-holes 50a-55a are opened on a phase plane different in phase at one surface of the driven gear 12 the other surface of the gear. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a power transmission mechanism of a working device that converts power of a driving source into reciprocating linear motion, such as used in a hand-held work machine represented by a hedge trimmer and a brush cutter.

  In a conventional double-edged hedge trimmer, a pair of blades are arranged facing each other, and a predetermined operation is performed by performing a relative reciprocating linear motion. Such a double-edged hedge trimmer includes a gear that rotates by receiving power from a drive source, a pair of eccentric cams provided on both sides of the gear, and a crank that connects a blade to each of the eccentric cams. A power transmission mechanism including a member is provided.

  In the power transmission mechanism, the accommodation chamber that accommodates the gear is filled with a lubricant so that the sliding contact surfaces of the gear, the eccentric cam, and the crank member are lubricated. In the power transmission mechanism shown in Patent Document 1, a recess is formed at a predetermined position of the gear so that the lubricant is reliably supplied to the sliding contact surface between the eccentric cam and the crank member. Further, in the power transmission mechanism shown in Patent Document 2, a concave portion is formed on the sliding contact surface between the eccentric cam and the crank member, and the volume change of the storage chamber (the pressure change of the storage chamber) accompanying the swing of the crank member. Is used to discharge the lubricant into the recess.

JP-A-10-136784 JP 2006-254785 A

  The power transmission mechanism as described above is based on the premise that a concave portion is formed on the sliding contact surface between the gear and the crank member, or a through hole is formed on the gear. There will be restrictions. That is, the lubricant can be positively supplied to the sliding contact surface and the location along the through hole. However, in order to supply the lubricant to any other location, the lubrication agent can be supplied along the sliding contact surface. A recess must be formed and a complex supply oil path must be formed.

  Here, in order to efficiently form the supply oil passage, it is preferable to form an oil passage inside the gear. However, since such a gear requires strength, it has been conventionally produced by forging or cutting. There was a problem that an oil passage could not be formed at an arbitrary location inside the gear.

  It is an object of the present invention to provide a power transmission mechanism for a working device in which lubrication performance is improved by lubricating an arbitrary portion.

  The present invention provides a power transmission mechanism for a working device that converts rotational power transmitted from a driving source into reciprocating linear motions of a first blade and a second blade supported by a case, and is provided in the case. The rotation transmission body housed in the storage chamber and rotated by receiving power from the drive source, and the first surface and the second surface, which are the end surfaces of the rotation transmission body, are provided eccentric to each other. The first eccentric cam and the second eccentric cam, a first crank member whose one end is slidably connected to the sliding surface of the first eccentric cam and the other end is connectable to the first blade, and one end is A second crank member that is slidably connected to the sliding surface of the second eccentric cam and whose other end is connectable to the second blade.

Here, in the present invention, the shape and the power transmission structure are not particularly limited as long as the rotation transmission body rotates by receiving the power of the drive source. The rotation transmission body may be, for example, a disk-like member that is directly connected to and linked to the drive source, or may be a gear that meshes with and rotates with another gear linked to the drive source.
In the present invention, the first blade and the second blade perform predetermined work by reciprocating linear motion, but the shape and structure of the blade or the action provided by the blade is not particularly limited.

  In the present invention, the first crank member (second crank member) connects the first eccentric cam (second eccentric cam) and the first blade (second blade), and the rotational movement of the rotation transmitting body is both performed. Convert to reciprocating linear motion of the blade. At this time, the connection structure between the crank members, the eccentric cams, and the blades is not particularly limited. For example, an eccentric cam may be slidably inserted into the end of the crank member, or may be connected by another method. In any case, the connection structure is not particularly limited as long as the rotational motion of the rotation transmitting body is converted into the reciprocating linear motion of the first blade and the second blade.

The invention according to claim 1 is configured such that the rotation transmission body is formed by laminating a plurality of rotation plates having through holes formed in a plane in a thickness direction, and the rotation transmission body includes the plurality of rotation transmission bodies. A communication path that opens on a different phase plane is formed on at least one of the first surface and the second surface of the rotation transmission body by a through-hole of an adjacent rotation plate among the rotation plates. It is characterized by that.
According to a second aspect of the present invention, in one or both of the first surface and the second surface where the communication passage opens, the opening of the communication passage is a sliding surface of the first eccentric cam and It faces one or both of the sliding surfaces of the second eccentric cam.
According to a third aspect of the present invention, the rotation transmission body is configured by laminating a plurality of rotation plates having through holes formed in a plane in the thickness direction, and the rotation transmission body includes the plurality of rotation plates. By communicating through the through holes of adjacent rotating plates among the rotating plates, communication paths that open on different phase planes are formed on the first surface and the second surface of the rotation transmitting body. Features.

The invention according to claim 4 is characterized in that the opening of the communication path faces one or both of the sliding surface of the first eccentric cam and the sliding surface of the second eccentric cam.
The invention described in claim 5 is characterized in that the communication path is configured such that through holes of adjacent rotating plates are out of phase with each other.
The invention described in claim 6 is characterized in that a concave portion communicating with the communication path is provided on an outer peripheral surface of one or both of the first eccentric cam and the second eccentric cam.
The invention according to claim 7 is characterized in that the rotating plate is constituted by a metal plate, and adjacent rotating plates are laminated by welding.
According to an eighth aspect of the present invention, either one or both of the first eccentric cam and the second eccentric cam are configured by laminating a plurality of cam plates in the thickness direction, and are integrated with the rotation transmission body. It is characterized by being fixed.
The invention according to claim 9 is characterized in that the plurality of cam plates are constituted by metal plates, and the adjacent cam plates and the cam plates and the rotation transmission body are laminated by welding.

In the present invention, the rotation transmitting body is configured by laminating a plurality of rotating plates in the thickness direction, but the method for fixing each rotating plate is not particularly limited. However, when the rotating plates are stacked and fixed, the communication path must be formed by a through hole formed in each rotating plate.
At this time, the communication path opens on different phase planes. This is because the through-holes of adjacent rotating plates among the stacked rotating plates shift the phase and position or change the hole shape. This is realized by communicating. Each rotating plate may be stacked so that the phase of all adjacent through holes is shifted, or only the phase of the through holes of any two adjacent rotating plates may be stacked. What is necessary is just to determine suitably according to the position which opens a communicating path.
Further, the rotating plates to be stacked may all be the same member, or may have different through hole shapes, for example.

According to the first to ninth aspects of the present invention, the communication path can be easily formed at an arbitrary position inside the rotation transmission body, and the communication path is opened at an arbitrary position on the end face of the rotation transmission body. Can be provided respectively. Therefore, the communication path as the lubrication path can be efficiently configured, and it is possible to provide a power transmission mechanism for a working device with improved lubrication performance.
In addition, since the communication passage is formed inside the rotation transmission body, the passage portion other than the opening is not slid by sliding parts such as a crank member, and a stable oil passage can be supplied.

In particular, according to the invention described in claims 2 and 4, since the opening of the communication path faces the sliding surfaces of the first and second eccentric cams that particularly need to be lubricated, the lubricity of these eccentric cams is improved. Thus, wear deterioration can be reduced.
In particular, according to the invention described in claim 5, since the communication plates can be formed by stacking the same shape of the rotating plates, it is not necessary to use various types of rotating plates, thereby reducing the manufacturing cost of the rotation transmitting body. be able to.

In particular, according to the sixth aspect of the present invention, since the concave portion communicating with the communication path is provided on the outer peripheral surface of the first eccentric cam or the second eccentric cam, the sliding between the eccentric cam and the crank member via the communication path. Lubricant is supplied to the moving contact surface, and the recess receives the lubricant, so that the lubricating performance can be improved.
In addition, extremely high lubrication performance can be realized by supplying the lubricant to the concave portion using the change in volume of the storage chamber (change in pressure in the storage chamber). For example, it is assumed that the first eccentric cam and the second eccentric cam are provided with a phase difference of 180 degrees, and the communication paths are opened in front of the rotational direction of both the eccentric cams. In this case, the volume of the storage chamber is contracted with the swing of the first crank member, and the lubricant is discharged from the opening on the first surface side to the communication path, so that a recess formed on the outer peripheral surface of the eccentric cam. The lubricant is led to After that, when the rotation transmission body rotates 180 degrees, the volume of the storage chamber is contracted with the swing of the second crank member, and the lubricant is discharged from the opening on the second surface side to the communication path. The lubricant is again introduced into the recess. Thus, since the communicating path communicates with the first surface and the second surface of the rotation transmission body, the lubricant is supplied twice to the same recess while the rotation transmission body makes one rotation. Therefore, extremely high lubrication performance can be realized by supplying the lubricant to the recess using the change in volume of the storage chamber (change in pressure in the storage chamber).

In particular, according to the seventh aspect of the invention, since the rotating plates constituted by the metal plates are laminated by welding, the rotation transmission body can be easily manufactured.
In particular, according to the invention described in claim 8, since the eccentric cam is formed by laminating a plurality of cam plates in the thickness direction, it is possible to share parts for design changes such as thickness changes. Can do.
In particular, according to the ninth aspect of the present invention, the cam plate constituted by the metal plate and the rotation transmission body are laminated by welding, so that the eccentric cam and the rotation transmission body can be easily and integrally manufactured.

The hedge trimmer provided with the power transmission mechanism of this invention is shown, The figure (a) is a bottom view of a hedge trimmer, The figure (b) is the bb sectional view taken on the line of the figure (a). It is a component expanded view of a power transmission device. FIG. 3 is a development view of parts of a driven gear and an eccentric cam. It is an assembly drawing of a driven gear and an eccentric cam. It is a figure for demonstrating the volume fluctuation | variation of a driven gear accommodation chamber. It is a component expanded view of the driven gear and eccentric cam of other embodiment. It is an assembly drawing of the driven gear and eccentric cam of other embodiment. It is a top view in the state where a driven gear and an eccentric cam were assembled.

Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings. In this embodiment, the power transmission mechanism of the present invention is applied to a hedge trimmer that cuts branches and leaves.
1A and 1B show a bottom view and a cross-sectional view of the hedge trimmer H. FIG. The hedge trimmer H includes a case 3 formed by joining the main body case 1 and the bottom case 2 with bolts. The case 3 is continuously formed with a drive gear storage chamber 3a, a driven gear storage chamber 3b, which is a storage chamber of the present invention, and a blade storage chamber 3c. Various members are provided in each of the storage chambers 3a to 3c. Be contained.

A first blade 4 and a second blade 5 having a large number of blades on both side surfaces in the longitudinal direction are supported in the blade housing chamber 3c so as to be capable of reciprocating. These both blades 4 and 5 repeat reciprocating linear motion in a face-to-face arrangement, and perform cutting work of branches and leaves by alternately appearing and retracting from the case 3.
The first blade 4 and the second blade 5 are operated by a driving force of a driving source (not shown) (for example, an engine or an electric motor) that is fixed to the upper surface of the main body case 1. The power transmission device 10 provided in the case 3 transmits to the 4 and the second blade 5.

The power transmission device 10 converts the rotational power transmitted from the drive source into a reciprocating linear motion of the first blade 4 and the second blade 5 and transmits the drive power 11, and the rotational transmission body of the present invention. A driven gear 12, eccentric cams 13 and 14, and crank members 15 and 16 are provided.
As shown in FIG. 2, the drive gear 11 has a shaft portion 11 a and a tooth portion 11 b formed on the outer periphery of the tip of the shaft portion 11 a, and rotates to the drive gear housing chamber 3 a via a bearing 20. It is supported freely. The drive gear 11 is linked with an output shaft of a drive source fixed above the main body case 1 and rotates by receiving power from the drive source.

  The driven gear 12 is accommodated in the driven gear accommodating chamber 3b of the case 3 so as to be rotatable. The driven gear 12 has a rotating shaft 22 inserted through a shaft hole 21 formed at the center thereof, and the rotating shaft 22 is fixed to the case 3 so that the driven gear 12 is rotatably accommodated in the driven gear accommodating chamber 3b. Is done. The driven gear 12 meshes with the driving gear 11 and rotates together with the driving gear 11. The driven gear 12 has a larger diameter than the driving gear 11, and is driven from the driving gear 11. In the process of transmitting power to the driven gear 12, a deceleration action is generated.

  A first eccentric cam 13 is provided on the first surface 12a, which is one plane of the driven gear 12, and the second surface 12b corresponding to the back surface of the first surface 12a is provided with the first surface 12a. A second eccentric cam 14 identical to the first eccentric cam 13 is provided. The first eccentric cam 13 and the second eccentric cam 14 are formed in a disc shape that is slightly thinner than the driven gear 12, and the center thereof is eccentrically positioned outside the rotational axis center of the driven gear 13. ing.

At this time, the centers of the first eccentric cam 13 and the second eccentric cam 14 are positioned 180 degrees out of phase in the rotational direction of the driven gear 12. Further, shaft holes 21 are also provided in the first eccentric cam 13 and the second eccentric cam 14, respectively, and a rotating shaft 22 is provided in each shaft hole 21 of the driven gear 12, the first eccentric cam 13, and the second eccentric cam 14. Is inserted.
As will be described in detail later, the driven gear 12 is configured by laminating a plurality of metal gear plates such as iron in the thickness direction, and the first eccentric cam 13 and the second eccentric cam 14 are also configured as follows. A plurality of metal cam plates are laminated in the thickness direction. All these gear plates and cam plates are welded with a brazing material such as copper, and the driven gear 12, the first eccentric cam 13 and the second eccentric cam 14 are integrally formed.

The first crank member 15 and the second crank member 16 convert the rotational power of the driven gear 12 into the reciprocating linear motion of the first blade 4 and the second blade 5. Since the first crank member 15 and the second crank member 16 are composed of the same member, the first crank member 15 will be described here.
As shown in FIGS. 1 and 2, the first crank member 15 is made of a thin metal member having the same thickness as the first eccentric cam 13, and has a fitting ring portion 15b at one end of the rod portion 15a. ing. The fitting ring part 15b is the first eccentric cam 13 and the insertion hole 15b ₁ to relatively rotatably inserted is formed, the outer circumferential surface and the inner circumferential surface of the insertion hole 15b ₁ of the first eccentric cam 13 is in contact Face to face. On the other hand, a small ring portion 15c having a smaller diameter than the fitting ring portion 15b is provided at the other end of the rod portion 15a. This is the small ring portion 15c, the outer peripheral surface and the insertion hole 16c ₁ of the first connecting pin 4a provided on the proximal end of the blade 4 has insertion holes 15c ₁ to relatively rotatably inserted is formed, the connecting pin 4a The inner peripheral surface of the is facing in contact.

Thus, when the driven gear 12 and the first blade 4 are connected via the first crank member 15, the first crank member 15 swings as the driven gear 12 rotates, and the first blade 4. Will reciprocate linearly.
In addition, although the 1st crank member 15 was demonstrated here, the 2nd crank member 16 similarly has the rod part 16a, the fitting ring part 16b, and the small ring part 16c. Then, the second eccentric cam 14 into the insertion hole 16b ₁ of the fitting ring part 16b is rotatable relative to the insertion, the insertion hole 16c ₁ of the small ring portion 16c, the connecting pin 5a provided on the second blade 5 relative It is inserted in a rotatable manner.
Further, as already described, the first eccentric cam 13 and the second eccentric cam 14 are provided on both surfaces 12a and 12b of the driven gear 12 with a phase shifted by 180 degrees in the rotational direction of the driven gear 12. Therefore, the first blade 4 and the second blade 5 always move in the opposite direction, such that when one protrudes from the case 3, the other enters the case 3. In other words, the first blade 4 and the second blade 5 are alternately raised and retracted, whereby the blades provided on the sides of the blades 4 and 5 are engaged with each other, and a cutting action is brought about.

In the power transmission device 10 configured as described above, friction occurs in various portions including sliding contact surfaces between the crank members 15 and 16 and the eccentric cams 13 and 14 and the connecting pins 4a and 5a. Therefore, each sliding contact portion is lubricated by filling the storage chambers 3a to 3c with a lubricant such as grease.
In the present embodiment, the driven gear 12, the first eccentric cam 13, and the second eccentric cam 14 are configured as follows, so that the first eccentric cam 13 and the first crank member 15 (insertion hole 15b ₁ ) High lubrication performance is realized on the sliding contact surface and the sliding contact surface between the second eccentric cam 14 and the second crank member 16 (insertion hole 16b ₁ ).

  FIG. 3 is an exploded perspective view of the driven gear 12, the first eccentric cam 13, and the second eccentric cam 14. FIG. As shown in FIG. 3, the driven gear 12 includes a plurality of gear plates 50 to 55 (rotary plates or gear plates of the present invention) made of metal thin circular members having teeth around the periphery at a predetermined pitch. In the embodiment, 6 sheets) are stacked in the thickness direction. In the present embodiment, the gear plates 50 and 55 are the same member, and the gear plates 51 to 54 are the same member, but all the gear plates 50 to 55 have the same tooth pitch. And the driven gear 12 will be comprised by laminating | stacking and welding the gear plates 50-55 in the thickness direction so that a tooth surface may correspond.

In the gear plates 50 and 55, curved elliptical through holes 50a and 55a penetrating the plane are formed in the vicinity of the outer periphery, and in the vicinity of the through holes 50a and 55a, small diameter introduction holes 50b, 55b is formed.
Further, the gear plates 51 to 54 are formed with through holes 51a to 54a and through holes 51b to 54b penetrating the plane in the vicinity of the outer periphery. The through holes 51a to 54a are arc-shaped (crescent-shaped) holes that are curved along the peripheral surfaces of the gear plates 51 to 54, and the length of the through holes is from the through holes 50a and 55a formed in the gear plates 50 and 55. Is longer (about twice). On the other hand, the through holes 51b to 54b are provided at positions facing the through holes 51a to 54a, that is, positions shifted in phase by 180 degrees from the through holes 51a to 54a in the rotation direction of the gear plates 51 to 54. These through holes 51b to 54b are both smaller in width and length than the through holes 51a to 54a.
Each of the gear plates 50 to 55 has a shaft hole 21 formed at the center thereof, and each of the through holes 50a to 55a and the through holes 51b to 54b has the same distance from the shaft hole 21. is doing.

As shown in FIG. 3, the six gear plates 50 to 55 having the above-described configuration are stacked with phases slightly shifted in the rotation direction. Specifically, the gear plate 50 and the gear plate 55 are 180 degrees out of phase in the rotational direction, and the through hole 50a of the gear plate 50 and the through hole 55a of the gear plate 55 face each other with a 180 degree phase shift. Yes.
The gear plate 51 is disposed so that the through hole 51a faces the through hole 50a and the introduction hole 50b of the gear plate 50, and the gear plate 54 has the through hole 54a in the through hole 55a and the introduction hole 55b of the gear plate 55. Arranged to face. Thus, the through hole 50a and the introduction hole 50b of the gear plate 50 communicate with each other via the through hole 51a of the gear plate 51, and the through hole 55a and the introduction hole 55b of the gear plate 55 are communicated with the through hole of the gear plate 54. It will communicate via 54a.

  The gear plate 52 and the gear plate 53 are rotated in a range in which the through hole 52a and the through hole 53a formed in the gear plate 52 and the through hole 53a partially face, in other words, in a range in which the through hole 52a and the through hole 53a communicate with each other. Are arranged out of phase. In addition, at this time, the gear plate 52 is arranged so that the through hole 52 a communicates with the through hole 51 a of the gear plate 51, and the gear plate 53 has the through hole 53 a also connected to the through hole 54 a of the gear plate 54. It arrange | positions so that it may communicate. That is, by arranging the gear plates 51 to 54 with the phases shifted in the rotation direction little by little, the through holes 50a to 55a of all the gear plates 50 to 55 are communicated.

When the gear plates 50 to 55 are welded in this manner, the driven gear 12 is configured as shown in FIG. According to the driven gear 12, the communication path 60 is formed by the through holes 50a to 55a, and the communication path 60 opens (60a) on the first surface 12a side and the second surface 12b side of the driven gear 12. It will be. As described above, the introduction hole 50b of the gear plate 50 faces the through hole 51a of the gear plate 51, and the introduction hole 55b of the gear plate 55 faces the through hole 54a of the gear plate 54 (FIG. 3). ). Therefore, both the introduction hole 50 b of the gear plate 50 and the introduction hole 55 b of the gear plate 55 communicate with the communication path 60.
In addition, since the through holes 51b to 54b formed in the gear plates 51 to 54 are blocked by the planes of the gear plates 50 and 55, in a state where the driven gear 12 is configured by laminating the gear plates 50 to 55, I can't confirm.

Further, as shown in FIG. 3, the first eccentric cam 13 and the second eccentric cam 14 include a plurality of cam plates made of a thin metal circular member having a smaller diameter than the gear plates 50 to 55 (this embodiment). 4 in the form) are stacked in the thickness direction. In the present embodiment, cam plates 70 to 73 are stacked in the thickness direction to form the first eccentric cam 13, and cam plates 74 to 77 are stacked in the thickness direction to form the second eccentric cam 14. These cam plates 70 to 77 are all the same member.
The cam plates 70 to 77 have a diameter that is about half that of the gear plates 50 to 55, and the thickness thereof is substantially equal to that of the gear plates 50 to 55. The cam plates 70 to 77 are formed with shaft holes 21 through which the rotary shaft 22 is inserted at positions shifted from the centers thereof.
In addition, notches 70a to 77a are formed on the outer peripheral surfaces of the cam plates 70 to 77 by partially cutting away them.

The first eccentric cam 13 is formed by welding the cam plates 70 to 73 in a state where the shaft hole 21 and the notches 70a to 73a are aligned. Similarly, the second eccentric cam 14 The cam plates 74 to 77 are welded in a state where the shaft hole 21 and the notches 74a to 77a are matched.
The first eccentric cam 13 and the second eccentric cam 14 are fixed to the first surface 12a and the second surface 12b of the driven gear 12, respectively. This fixing method is also performed by welding. Therefore, in the present embodiment, the gear plates 50 to 55 and the cam plates 70 to 77 are all laminated by welding, and the driven gear 12, the first eccentric cam 13, and the second eccentric cam 14 are integrally configured. .

In addition, as shown in FIG. 4, the notch of the 1st eccentric cam 13 formed by the notches 70a-73a of the cam plates 70-73 is made into the recessed part 13a, and it forms by the notches 74a-77a of the cam plates 74-77. The notch of the second eccentric cam 14 is defined as a recess 14a.
The first eccentric cam 13 is welded to the first surface 12a (gear plate 50) of the driven gear 12 with the recess 13a aligned with the introduction hole 50b. Similarly, the second eccentric cam 14 is welded to the second surface 12b (gear plate 55) of the driven gear 12 with the recess 14a aligned with the introduction hole 55b. As a result, the recesses 13a, 14a provided in the first eccentric cam 13 and the second eccentric cam 14 both communicate with the communication path 60 via the introduction holes 50b, 55b.

Next, a state where the driven gear 12 having the above-described configuration is rotated in the driven gear accommodating chamber 3b will be described with reference to FIG.
Figure _{5 (a 1) ~ (d} 1) is the driven gear 12, the first eccentric cam 13 and the first crank member 15 is a diagram showing a state viewed from the first surface 12a side of the driven gear 12. 5 (a ₂ ) to 5 (d ₂ ) show a state in which the driven gear 12, the second eccentric cam 14, and the second crank member 16 are viewed from the first surface 12a side of the driven gear 12, that is, FIG. 5 and _{(a 1) ~ (d 1} ) is a diagram showing a state viewed from the same direction. However, FIGS. 5 (a ₂ ) to (d ₂ ) show the second eccentric cam 14 and the second crank member 16 as a solid line for the convenience of explaining the relative position displacement with FIGS. 5 (a ₁ ) to (d ₁ ). Is shown.
The driven gear housing chamber 3 b is partitioned by the driven gear 12 into a space on the first surface 12 a side of the driven gear 12 and a space on the second surface 12 b side of the driven gear 12. Here, the space formed on the first surface 12a side of the driven gear 12 will be described as a first space 80, and the space formed on the second surface 12b side of the driven gear 12 will be described as a second space 90 (FIG. 1, see FIG.

As already explained, the first eccentric cam 13 and the second eccentric cam 14, so that provided a 180 degrees phase offset in the direction of rotation of the driven gear 12, the first eccentric cam 13 in FIG. 5 (a ₁₎ The second eccentric cam 14 is in the position shown in FIG. 5 (a ₂ ). In this state, the first crank member 15 protrudes most from the driven gear housing chamber 3b, and the second crank member 16 is most immersed in the driven gear housing chamber 3b.

Further, the gear plate 50 constituting the first surface 12 a of the driven gear 12 and the gear plate 55 constituting the second surface 12 b of the driven gear 12 are also shifted by 180 degrees in the rotational direction of the driven gear 12. Is arranged. Accordingly, the opening of the communication passage 60 for communicating the first surface 12a and second surface 12b through the driven gear 12, i.e., the through hole 50a and the through hole 55a, FIG. 5 _{(a 1)} and 5 ( As shown in a ₂ ), the phase is shifted by 180 degrees.
In this state, as shown in FIG. 5 (a ₂ ), the second space 90 is partitioned into the first chamber 90a and the second chamber 90b by the second crank member 16, and at this time The volumes of both chambers 90a and 90b are substantially equal. The opening of the communication path 60 in the second surface 12b of the driven gear 12 faces the first chamber 90a.

From the above state, when the driven gear 12 rotates 90 degrees in the direction of the arrow in the drawing, the first eccentric cam 13 is displaced and the first crank member 15 swings, resulting in the state shown in FIG. 5 (b ₁ ). . At this time, the first space 80 is partitioned by the first crank member 15 into a first chamber 80a and a second chamber 80b. In the state shown in FIG. 5 (b ₁ ), the first chamber 80a has a larger volume than the second chamber 80b, and the opening of the communication passage 60 in the first surface 12a of the driven gear 12 is not in the first chamber. It faces 80a.
On the other hand, the driven gear 12 as described above is rotated, as shown in FIG. 5 (b _2), the second eccentric cam 14 is swung and the second crank member 16 is positioned displaced, the first chamber 90a While contracting, the second chamber 90b expands. In the state shown in FIG. 5 (b ₂ ), most of the opening (through hole 55a) of the communication passage 60 is closed by the second crank member 16, but part of the opening faces the first chamber 90a. ing.

Since the driven gear storage chamber 3b, that is, the spaces 80 and 90 are filled with a lubricant such as grease, when the volume of the first chamber 90a contracts as described above, the first chamber 90b contracts as the volume decreases. The pressure in the chamber 90a increases. When the pressure in the first chamber 90a rises, the lubricant is discharged from the opening (through hole 55a) of the communication passage 60 facing the first chamber 90a to the communication passage 60 by a pump action.
When the lubricant is discharged to the communication path 60 in this way, the lubricant is guided to the concave portion 14a of the second eccentric cam 14 communicating with the communication path 60. Therefore, the second eccentric cam 14 and the second crank member 16 are guided. The sliding contact surface with is lubricated.

Further, in the above state, the first eccentric cam 13 is positioned as shown in FIG. 5 (b ₁ ), and the opening (through hole 50a) of the communication passage 60 on the first surface 12a side of the driven gear 12 is It faces the first chamber 80a. At this time, the first chamber 80a formed on the first surface 12a side has a larger volume and a lower pressure than the first chamber 90a formed on the second surface 12b side. Therefore, the lubricant discharged from the second surface 12b side of the driven gear 12 to the communication path 60 is also discharged to the first chamber 80a on the first surface 12a side through the communication path 60. Become. And as already explained, since the recess 13a formed in the first eccentric cam 13 communicates with the communication path 60, the lubricant is discharged into the recess 13a in the process of being discharged into the first chamber 80a. Will be guided at the same time.

As described above, in the present embodiment, the communication path 60 includes the first chamber 80a positioned on the first surface 12a side of the driven gear 12 and the first surface positioned on the second surface 12b side of the driven gear 12. Therefore, the lubricant is easily discharged into the communication passage 60 as the volume contracts. As the volume of the first chamber 90a contracts, the sliding contact surface between the first eccentric cam 13 and the first crank member 15 and the sliding contact between the second eccentric cam 14 and the second crank member 16 are obtained. The surfaces can be lubricated simultaneously, and the lubrication performance can be greatly enhanced.
In general, a partition wall is provided at the boundary between the driven gear storage chamber 3b and the blade storage chamber 3c so that the lubricant does not leak from the driven gear storage chamber 3b. There is a risk of long-term destruction due to the pressure increasing action of the first chamber 90a. However, if the lubricant is discharged into the first chamber 80a having a relatively low pressure on the opposite side surface of the driven gear 12 as in the present embodiment, the pressure in the first chamber 90a becomes high. Can be prevented. That is, the communication path 60 also provides a pressure releasing action so that the pressure in the first chamber 90a does not become too high, and as a result, damage to the case 3 is reduced.

When the driven gear 12 further rotates 90 degrees from the state shown in FIG. 5 (b ₁ ) and FIG. 5 (b ₂ ), the state shown in FIG. 5 (c ₁ ) and FIG. 5 (c ₂ ) is obtained. In this state, as shown in FIG. 5 (c ₁ ), the first space 80 is partitioned into the first chamber 80a and the second chamber 80b by the first crank member 15, and both chambers at this time The volumes of 80a and 80b are almost equal. At this time, as shown in FIG. 5C ₂ , the second space 90 is partitioned into the first chamber 90 a and the second chamber 90 b by the second crank member 16, The volumes of the chambers 90a and 90b are also substantially equal.

When the driven gear 12 further rotates 90 degrees, the state shown in FIG. 5 (d ₁ ) and FIG. 5 (d ₂ ) is obtained. As shown in FIG. 5 (d ₁ ), the first eccentric cam 13 and the first crank member 15 are now displaced on the first surface 12a side of the driven gear 12 and the first chamber 80a contracts. In the state shown in FIG. 5 (d ₁ ), most of the opening (through hole 50a) of the communication passage 60 is closed by the first crank member 15, but a part of the opening faces the first chamber 80a. ing.
When the volume of the first chamber 80a contracts as described above, the pressure in the first chamber 80a increases as the volume contracts. When the pressure in the first chamber 80a increases, the lubricant is discharged from the opening (through hole 50a) of the communication passage 60 facing the first chamber 80a to the communication passage 60 by a pump action.
When the lubricant is discharged into the communication path 60 in this way, the lubricant is guided to the concave portion 13a of the first eccentric cam 13 communicating with the communication path 60. Therefore, the first eccentric cam 13 and the first crank member 15 are guided. The sliding contact surface with is lubricated.

Further, in the above state, as shown in FIG. 5 (d ₂ ), the second eccentric cam 14 is positioned, and the opening (through hole 55a) of the communication passage 60 on the second surface 12b side of the driven gear 12 is It faces the first chamber 90a. At this time, the first chamber 90a formed on the second surface 12b side has a larger volume and a lower pressure than the first chamber 80a formed on the first surface 12a side. Therefore, the lubricant discharged from the first surface 12a side of the driven gear 12 to the communication path 60 is also discharged to the first chamber 90a on the second surface 12b side via the communication path 60. Become. As already described, since the recess 14a formed in the second eccentric cam 14 communicates with the communication path 60, the lubricant is discharged into the recess 14a in the process of being discharged into the first chamber 90a. Will be guided at the same time.

  As described above, in the present embodiment, the lubricant is discharged from the both surfaces of the driven gear 12 to the communication path 60 once each time the driven gear 12 rotates once. The communication path 60 communicates with the recess 13 a of the first eccentric cam 13 and the recess 14 a of the second eccentric cam 14. Therefore, while the driven gear 12 makes one rotation, the lubricant is guided twice to the concave portion 13a of the first eccentric cam 13 and the concave portion 14a of the second eccentric cam 14, respectively. 14 and the sliding contact surface between the crank members 15 and 16 can be reliably supplied in a large amount.

Further, according to the present embodiment, not only the sliding action of the sliding contact surfaces between the eccentric cams 13 and 14 and the crank members 15 and 16 but also the predetermined location in the driven gear accommodating chamber 3b is achieved by the communication passage 60. Pressure relief and weight reduction are realized at the same time.
When the eccentric cams 13 and 14 and the crank members 15 and 16 are changed or the shape of the case 3 is changed, the optimum opening of the communication passage 60 for supplying the lubricant to the recesses 13a and 14a. The position is different. In the present embodiment, when the eccentric cams 13 and 14 are welded to the driven gear 12, the communication path 60 is formed at an optimal position by simply changing the relative positions of the eccentric cams 13 and 14 and the driven gear 12. It can be opened. Therefore, even if a design change or the like occurs, it is possible to configure the driven gear 12 using the same gear plate, which facilitates inventory management and maintains high lubrication performance.

  Further, according to the present embodiment, when welding each of the gear plates 50 to 55, the phase of the gear plate 50 is adjusted to adjust the passage width of the communication passage 60 or to form a throttle in the communication process of the communication passage 60. Can be easily done. This makes it possible to adjust the amount of lubricant flowing between the first surface 12a and the second surface 12b of the driven gear 12, and the amount of lubricant supplied to the recesses 13a and 14a and the pressure relief effect. Can be optimized. In the present embodiment, through holes 51 a to 54 a and through holes 51 b to 54 b are formed in the gear plates 51 to 54. Thus, the optimal communicating path 60 can be comprised by combining suitably the through-hole from which a magnitude | size differs.

Further, when it is not particularly necessary to improve the lubrication performance of the sliding contact surfaces between the eccentric cams 13 and 14 and the crank members 15 and 16, the through holes of the respective gear plates are evenly arranged in the rotational direction of the driven gear 12. Should be arranged. By doing in this way, the weight balance of the driven gear 12 can be improved.
Note that the method of welding the gear plates 50 to 55 and the cam plates 70 to 77 is not particularly limited, and may be appropriately determined according to the material of the member to be welded.
In the present embodiment, the first eccentric cam 13 and the second eccentric cam 14 are configured by laminating the cam plates 70 to 77. However, both the eccentric cams do not necessarily have a laminated structure.

Another embodiment is shown using FIGS.
In this embodiment, only the structures of the driven gear and the eccentric cam are different, and the other configurations are the same as those of the above embodiment. Therefore, the configuration different from the above embodiment will be described here, and the description of other configurations will be omitted.
6 is an exploded perspective view of the driven gear 12, the first eccentric cam 13, and the second eccentric cam 14. FIG. In this embodiment, the driven gear 12 is configured by laminating and welding the gear plates 500 to 505 in the thickness direction. Here, the gear plates 500 and 505 are the same member, the gear plates 501 to 504 are the same member, and the gear plates 501 to 504 are located between the gear plates 500 and 505.

The gear plates 500, 505 are formed with curved elliptical through holes 500a, 505a penetrating through the plane in the vicinity of the outer periphery, and in the vicinity of the through holes 500a, 505a, small diameter introduction holes 500b, 505b is formed.
On the other hand, in the gear plates 501 to 504, through holes 501a to 504a and 501b to 504b penetrating through the plane are formed so as to extend from the vicinity of the outer periphery to the center. The gear plates 501 to 504 are laminated in a state in which the phases are adjusted so that the through holes 501a to 504a and the through holes 501b to 504b coincide.
The gear plate 500 and the gear plate 501 are stacked such that the through hole 500a of the gear plate 500 and the vicinity of the outer periphery of the through hole 501a of the gear plate 501 overlap. Further, the gear plate 505 and the gear plate 504 are laminated such that the through hole 505a of the gear plate 505 and the through hole 504b of the gear plate 504 overlap.
At this time, the introduction hole 500b of the gear plate 500 faces a portion extending to the center of the through hole 501a of the gear plate 501, and the introduction hole 505b of the gear plate 505 is a portion extending to the center of the through hole 504b of the gear plate 504. To face.
A shaft hole 21 is formed at the center of each of the gear plates 500 to 505.

As shown in FIG. 6, the gear plates 500 to 505 configured as described above are stacked and welded in a state where the phases of the through holes 500 a to 504 a and the through holes 501 b to 504 b and 505 a are matched. Thereby, as shown in FIG. 8, the through-hole 501a-504a forms the communicating path 600 which connects the through-hole 500a and the introduction hole 500b, and the through-hole 501b-504b forms the through-hole 505a and the introduction hole 505b. A communication path 601 is formed for communicating the. Since the communication path 600 is partitioned by the gear plate 505, the communication path 600 does not open to the second surface 12b of the driven gear 12, and the communication path 601 is also partitioned by the gear plate 500. There is no opening in the first surface 12a.
As described above, in this embodiment, all the communication passages 600 formed in the driven gear 12 have their openings opened on the first surface 12a, and the communication passages 601 all have their openings on the second surface. 12b is opened. That is, in this embodiment, the communication path formed in the driven gear 12 opens at different positions (phases) on the same surface.

Further, each of the first eccentric cam 13 and the second eccentric cam 14 has a plurality of cam plates (four in this embodiment) made of a thin metal circular member having a smaller diameter than the gear plates 500 to 505 in the thickness direction. It is constructed by laminating. In this embodiment, cam plates 700 to 703 having the same diameter are stacked in the thickness direction to form the first eccentric cam 13, and cam plates 704 to 707 having the same diameter are stacked in the thickness direction to form the second eccentric cam. A cam 14 is configured. Of these, the cam plates 701 to 706 are the same member.
The cam plates 700 to 707 have a diameter that is approximately half that of the gear plates 500 to 505, and the thickness is substantially equal to that of the gear plates 500 to 505. The cam plates 700 to 707 are formed with shaft holes 21 through which the rotary shaft 22 is inserted at positions shifted from the centers thereof. Further, notches 701a to 706a are formed on the outer peripheral surfaces of the cam plates 701 to 706 by partially cutting them.

The first eccentric cam 13 is configured to be welded in a state where the shaft holes 21 of the cam plates 700 to 703 are aligned and the notches 701a to 703a of the cam plates 701 to 703 are aligned. Further, the second eccentric cam 14 is configured to be welded in a state where the shaft holes 21 of the cam plates 704 to 707 are aligned and the notches 704a to 706a of the cam plates 704 to 706 are aligned.
The first eccentric cam 13 and the second eccentric cam 14 are fixed to the first surface 12a and the second surface 12b of the driven gear 12 by welding, respectively. Each of the eccentric cam 14 and the driven gear 12 has the same shaft hole 21. At this time, the first eccentric cam 13 and the driven gear 12 are arranged so that the introduction hole 500b and the notch 703a overlap each other, and the second eccentric cam 14 and the driven gear 12 are arranged with the introduction hole 505b and the notch 704a. Are arranged to overlap.

  In this way, as shown in FIG. 8, in the first surface 12a of the driven gear 12, the through hole 500a serves as one opening 600a, and the introduction hole 500b and the notches 701a to 703a serve as the other opening 600b. The communication path 600 is formed. As described above, by providing the notches 701a to 703a, the other opening 600b of the communication path 600 opens so as to face the sliding surface between the first eccentric cam 13 and the first crank member 15. . In the second surface 12b of the driven gear 12, a communication path 601 is formed in which the through hole 505a is one opening 601a and the introduction hole 505b and the notches 704a to 706a are the other opening 601b. . As described above, by providing the notches 701a to 706a, the other opening 600b of the communication path 600 and the other opening 601b of the communication path 601 are in contact with the sliding surface between the first eccentric cam 13 and the first crank member 15. And it opens so that it may face to the sliding surface of the 2nd eccentric cam 14 and the 2nd crank member 16, respectively.

As described above, according to this embodiment, as in the above-described embodiment, the communication passages 600 and 601 are provided on the sliding surfaces of the eccentric cams 13 and 14 and the crank members 15 and 16 as a lubricant. It will demonstrate the function that leads.
However, in this embodiment, notches are not provided in the cam plates 700 and 707 corresponding to the end surfaces of the eccentric cams 13 and 14, and the sliding surfaces of the eccentric cams 13 and 14 and the crank members 15 and 16 are provided. Since the communication paths 600 and 601 face each other, the lubricity with respect to the sliding surface can be further enhanced.
In this embodiment, the introduction holes 500b and 505b are configured to be within a range facing the notches 703a and 704a at the joint portions with the eccentric cams 13 and 14, but the introduction holes 500b and 505b are configured. By forming the eccentric cams 13 and 14 so as to extend outward from the outer periphery and overlapping the notches 703a and 704a, the lubricity of the sliding surfaces between the crank members 15 and 16 and the driven gear 12 is improved. It is also possible to increase.
Furthermore, if the end face (communication path) of the driven gear 12 and the shaft hole 21 are communicated, the lubricity of the shaft hole 21 can be improved.

DESCRIPTION OF SYMBOLS 1 Main body case 2 Bottom case 3 Case 3a Drive gear accommodation chamber 3b Drive gear accommodation chamber 3c Blade accommodation chamber 4 First blade 4a Connection pin 5 Second blade 5a Connection pin 10 Power transmission device 11 Drive gear 11a Shaft portion 11b Tooth portion 12 Driven gear 12a first surface 12b second surface 13 first eccentric cam 13a recess 14 second eccentric cam 14a recess 15 first crank member 15a rod portion 15b fitting ring portion 15b ₁ insertion hole 15c small ring portion 15c ₁ insertion Hole 16 Second crank member 16a Rod portion 16b Fitting ring portion 16b ₁ insertion hole 16c Small ring portion 16c ₁ insertion hole 20 Bearing 21 shaft hole 22 Rotating shaft 50 to 55 Gear plates 50a to 55a Through holes 50b and 55b Introduction hole 51b -54b Through-hole 60 Communication path 60a Opening of communication path 70-77 Cam plates 70a-77a Notch 80 1st space 90 2nd space 80a, 90a 1st chamber 80b, 90b 2nd chamber 500-505 Gear plate 500a-505a Through-hole 501b-504b Through-hole 500b, 505b Introduction hole 600,601 Communication path 600a , 600b, 601a, 601b Communication passage opening

Claims (9)

A power transmission mechanism of a working device that converts rotational power transmitted from a drive source into reciprocating linear motion of a first blade and a second blade supported by a case and transmits the rotational power,
A rotation transmission body housed in a housing chamber provided in the case, and rotated by receiving power from the drive source;
A first eccentric cam and a second eccentric cam provided eccentric to each other on each of the first surface and the second surface which are end surfaces of the rotation transmitting body;
A first crank member having one end slidably connected to the sliding surface of the first eccentric cam and the other end connectable to the first blade;
A second crank member having one end slidably connected to the sliding surface of the second eccentric cam and the other end connectable to the second blade;
The rotation transmitting body is configured by laminating a plurality of rotating plates having through holes formed in a plane in a thickness direction, and the rotation transmitting body includes an adjacent rotating plate among the plurality of rotating plates. A power transmission mechanism for a working device, characterized in that a through passage is formed on a different phase plane in at least one of the first surface and the second surface of the rotation transmission body by a through hole. .   In one or both of the first surface and the second surface where the communication path opens, the opening of the communication path corresponds to the sliding surface of the first eccentric cam and the sliding surface of the second eccentric cam. The power transmission mechanism of the working device according to claim 1, which faces either one or both. A power transmission mechanism of a working device that converts rotational power transmitted from a drive source into reciprocating linear motion of a first blade and a second blade supported by a case and transmits the rotational power,
A rotation transmission body housed in a housing chamber provided in the case, and rotated by receiving power from the drive source;
A first eccentric cam and a second eccentric cam provided eccentric to each other on each of the first surface and the second surface which are end surfaces of the rotation transmitting body;
A first crank member having one end slidably connected to the sliding surface of the first eccentric cam and the other end connectable to the first blade;
A second crank member having one end slidably connected to the sliding surface of the second eccentric cam and the other end connectable to the second blade;
The rotation transmitting body is configured by laminating a plurality of rotating plates having through holes formed in a plane in a thickness direction, and the rotation transmitting body includes an adjacent rotating plate among the plurality of rotating plates. A power transmission mechanism for a working device, wherein the first and second surfaces of the rotation transmission body are connected to each other by shifting the through-holes to form communication paths that open on different phase planes. .   4. The power transmission mechanism for a working device according to claim 3, wherein the opening of the communication path faces one or both of the sliding surface of the first eccentric cam and the sliding surface of the second eccentric cam.   The power transmission mechanism for a working device according to any one of claims 1 to 4, wherein the communication path is configured by shifting the through holes of adjacent rotating plates from each other.   The work according to any one of claims 1 to 5, wherein a concave portion communicating with the communication path is provided on an outer peripheral surface of one or both of the first eccentric cam and the second eccentric cam. The power transmission mechanism of the device.   The power transmission mechanism for a working device according to any one of claims 1 to 6, wherein the rotating plate is formed of a metal plate, and adjacent rotating plates are stacked by welding.   One or both of the first eccentric cam and the second eccentric cam are formed by laminating a plurality of cam plates in the thickness direction, and are integrally fixed to the rotation transmission body. The power transmission mechanism of the working device according to claim 1. 9. The power transmission of the working device according to claim 8, wherein the plurality of cam plates are constituted by metal plates, and the adjacent cam plates and the cam plates and the rotation transmission body are laminated by welding. mechanism.

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