JP2014000619A - Centrifugal barrel polishing machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve workability when attaching/removing a gear.SOLUTION: A centrifugal barrel polishing machine is provided with: a planetary gear 27 (low-speed side gear) that is provided for a planetary shaft 14 (a driven side shaft) in an integrally rotatable attachable/removable manner and is removed by being displaced to a right end part 14R (one end) side of the planetary shaft 14; a small-diameter gear 32 (a high-speed side small-diameter gear) rotating around a deceleration shaft 29 (a driving side shaft); and a large-diameter gear 33 (a high-speed side large-diameter gear) which rotates integrally with the small-diameter gear 32 and is placed nearer the right end part 14R side than the small-diameter gear 32. When viewed from the right end part 14R side, a part 27A of an outer peripheral part of the planetary gear 27 is hidden by an outer peripheral part of the large-diameter gear 33. When a spacer 40 attached between the planetary shaft 14 and the planetary gear 27 is removed, the planetary gear 27 can be displaced in the radial direction with respect to the planetary shaft 14.

Description

  The present invention relates to a centrifugal barrel polishing machine.

  Patent Document 1 discloses a centrifugal barrel polishing machine in which a plurality of barrel tanks are rotatably attached to an eccentric position of a turret that is rotationally driven. In this centrifugal barrel polishing machine, as a means for rotating the barrel tank planetarily, there is a structure in which a sun gear driven by a motor arranged concentrically with the turret and a planetary gear provided so as to rotate integrally with the barrel tank are engaged. It is used.

  In a structure in which the barrel tank is rotated by planetary gears using a gear, a structure in which a reduction gear 102 is interposed between the sun gear 100 and the planetary gear 101 as shown in FIG. Can be considered. The reduction gear 102 is configured by connecting a large-diameter gear 103 that meshes with the sun gear 100 and a small-diameter gear 104 that meshes with the planetary gear 101 in an axial direction so as to be integrally rotatable. In this speed reduction structure, the sun gear 100, the speed reduction gear 102, and the planetary gear 101 are disposed at the tip end portions (the right end portion in FIG. 6) of the sun shaft 105, the speed reduction shaft 106, and the planetary shaft 107, respectively. In the axial direction of the shafts 105, 106, and 107, the large diameter gear 103 is preferably disposed on the tip side of the planetary gear 101. The positional relationship between the large diameter gear 103 and the planetary gear 101 is as follows.

  The planetary shaft 107 that supports the barrel tank 108 has a variation in the center of gravity due to the flow of mass (a collective term for workpieces and grinding stones) in the barrel tank 108, and the planetary gear 101 fixed to the tip of the planetary shaft 107. May cause slight deformation due to the mass of the material. When the planetary shaft 107 that has been bent and deformed contacts the small-diameter gear 104 illegally, abnormal noise may be generated. Occurrence of abnormal noise can be suppressed by setting the position of the planetary gear 101 to the center side (barrel tank 108 side) with respect to the tip of the planetary shaft 107 in the axial direction. In addition, if the planetary gear 101 is set to the center side of the end of the planetary shaft 107 in the axial direction, the curved deformation can be suppressed even if the planetary shaft 107 is made thin. It is also possible to reduce the weight. For this reason, the planetary gear 101 is arranged at a position closer to the center in the axial direction than the large-diameter gear 103.

JP-A-62-251066

However, the small-diameter gear 104 with which the planetary gear 101 meshes has a smaller outer diameter than the large-diameter gear 103, so that when viewed from the tip side of the shafts 105, 106, 107, a part of the planetary gear 101 is large-diameter gear. It will be hidden behind 103. When removing the planetary gear 101 from the planetary shaft 107 for replacement or maintenance, the planetary gear 101 is slid to the tip side of the planetary shaft 107 and removed, so that the planetary gear 101 is attached or detached. Needs to remove the large-diameter gear 103 from the reduction shaft 106. Therefore, there is a problem that work is troublesome.
The present invention has been completed based on the above circumstances, and an object thereof is to improve workability when a gear is attached and detached.

As means for achieving the above object, the present invention provides:
A reduction mechanism that reduces and transmits rotational force to a plurality of barrel tanks rotatably provided at an eccentric position of the turret,
The deceleration mechanism is
A driven shaft,
A low-speed side gear that is provided on the driven side shaft so as to be integrally rotatable and detachable, and is disengaged from the driven side shaft by being displaced toward one end side of the driven side shaft;
A drive-side shaft arranged in parallel with the driven-side shaft;
A high-speed side small-diameter gear that is rotatable about the drive-side shaft and meshes with the low-speed side gear;
The high-speed side small-diameter gear can be integrally rotated, and is configured to include a high-speed side large-diameter gear that is shifted from the high-speed side small-diameter gear toward the one end side of the driven shaft.
When viewed from the one end side of the driven shaft, the centrifugal barrel polishing machine is configured such that a part of the outer peripheral edge portion of the low speed side gear is hidden by the outer peripheral edge portion of the high speed side large diameter gear. And
A spacer provided detachably between the outer periphery of the driven shaft and the inner periphery of the low speed gear;
In a state where the spacer is removed from between the driven side shaft and the low speed side gear, the corresponding portion of the low speed side gear with the high speed side large diameter gear is radially away from the high speed side large diameter gear. It is characterized in that it can be displaced to the position.

  According to this configuration, when removing the low-speed side gear from the driven-side shaft, the spacer is removed from between the driven-side shaft and the low-speed side gear, and the space vacated by removing the spacer is used to make the low-speed side gear. The portion corresponding to the high-speed large-diameter gear can be displaced in the radial direction so as to move away from the high-speed large-diameter gear. According to the present invention, when the low speed side gear is attached to and detached from the driven side shaft, it is not necessary to remove the high speed side large-diameter gear from the drive side shaft, so that workability is good.

Configuration diagram of centrifugal barrel polishing machine of this embodiment Enlarged sectional view showing the planetary gear mounting structure An enlarged cross-sectional view showing a state where the spacer is removed from between the planetary shaft and the planetary gear. Enlarged sectional view showing the planetary gear tilted with the spacer removed FIG. 4 is an enlarged sectional view showing a state where the planetary gear is further inclined from the state of FIG. Cross section of spacer Configuration diagram of conventional centrifugal barrel polishing machine

The centrifugal barrel polishing machine of the present invention is
The spacer may include coupling means for coupling the driven shaft and the low-speed gear so as to rotate together.
According to this configuration, the number of parts can be reduced as compared with the case where a dedicated coupling means is used separately from the spacer.

The centrifugal barrel polishing machine of the present invention is
The driven shaft is rotatably supported by a bearing portion;
The low speed side gear is disposed on the one end side of the driven side shaft with respect to the bearing portion;
Between the bearing portion and the high-speed large-diameter gear, the low-speed gear can be tilted so that the axis is inclined with respect to the driven-side shaft in a state where the spacer is removed. A displacement allowable space may be provided.
According to this configuration, the outer diameter of the low-speed gear can be increased, so that the barrel tank can be rotated at a slower speed.

<Example 1>
A first embodiment of the present invention will be described below with reference to FIGS. As shown in FIG. 1, the centrifugal barrel polishing machine of the present embodiment is configured to revolve the turret 11 around the solar shaft 10 and a pair of turrets 11 that rotate about the solar shaft 10 with the axis line oriented horizontally. A revolving drive mechanism 16, a plurality of barrel tanks 12 arranged in an eccentric position between the turrets 11, and a rotation drive mechanism 21 for rotating the barrel tank 12 relative to the turret 11. Has been. The barrel tank 12 is planetarily rotated about the solar shaft 10 by the revolution drive mechanism 16 and the rotation drive mechanism 21. Due to the planetary rotation of the barrel tank 12, polishing processing such as deburring and gloss finishing of the surface of the workpiece using the polishing stone is performed inside the barrel tank 12.

  The sun shaft 10 is rotatably supported by the base 13. The turret 11 is supported by the sun shaft 10 so as to be relatively rotatable. A pair of planetary shafts 14 (a driven shaft which is a constituent element of the present invention) protrudes in parallel with the sun shaft 10 from both end surfaces of the barrel tank 12, and the planetary shaft 14 is connected to a bearing portion 15 provided in the turret 11. It is supported so that it can rotate relative to the turret 11 while being penetrated.

  The revolution drive mechanism 16 includes a revolution motor 17 disposed below the turret 11, a revolution drive pulley 18 fixed to the output shaft of the revolution motor 17, and a revolution driven pulley 19 formed on the outer periphery of the turret 11. The revolving drive pulley 18 and the revolving driven pulley 19 are provided with a revolving belt 20 wound around. By this revolution drive mechanism 16, the rotational force of the revolution motor 17 is directly transmitted to the turret 11.

  The rotation drive mechanism 21 includes a rotation motor 22 disposed below the turret 11, a rotation drive pulley 23 fixed to the output shaft of the rotation motor 22, and a rotation attachment attached to the sun shaft 10 so as to rotate integrally. A driven pulley 24 and a rotation belt 25 wound around the rotation drive pulley 23 and the rotation driven pulley 24 are provided, whereby the rotational force of the rotation motor 22 is directly applied to the solar shaft 10. Communicated.

  The rotation drive mechanism 21 includes a speed reduction mechanism 26 for reducing and transmitting the rotational force of the sun shaft 10 to the planetary shaft 14. The reduction mechanism 26 includes the planetary shaft 14, the planetary gear 27 (low-speed side gear that is a component of the present invention), a spacer 40, a sun gear 28, and a reduction shaft 29 (drive side that is a component of the present invention). Shaft) and a reduction gear 30. The planetary gear 27 is disposed at the right end portion 14R of the planetary shaft 14 (one end which is a constituent element of the present invention). The planetary gear 27 attached to the planetary shaft 14 can be detached from the planetary shaft 14 by being displaced to the right, and can be attached to the planetary shaft 14 by being displaced from the right to the left of the planetary shaft 14. it can.

  The inner diameter of the center hole 27H of the planetary gear 27 is set larger than the outer diameter of the planetary shaft 14, and a spacer 40 is mounted between the inner peripheral surface of the planetary gear 27 and the outer peripheral surface of the planetary shaft 14. Yes. By this spacer 40, the planetary gear 27 is provided so as to be able to rotate integrally with the planetary shaft 14 and detachable.

  As shown in FIG. 6, the spacer 40 is structurally configured to include a cylindrical inner ring 41, a cylindrical outer ring 46, and a plurality of bolts 48. In addition, the spacer 40 functionally compensates for the radial dimension difference between the inner peripheral surface of the planetary gear 27 and the outer peripheral surface of the planetary shaft 14, and the relative displacement in the radial direction of the planetary gear 27 with respect to the planetary shaft 14. And the function (coupling means 40B) for coupling the planetary gear 27 so as to be able to rotate integrally with the planetary shaft 14.

  The inner ring 41 is configured by integrally forming a ring main body portion 42 and a flange portion 43 projecting radially outward from the right end in the axial direction of the ring main body portion 42. The outer peripheral surface of the ring main body 42 is a tapered pressing surface 44 that is inclined so that the outer diameter decreases toward the left (the direction opposite to the direction in which the planetary gear 27 is extracted from the planetary shaft 14). . The inner peripheral surface of the outer ring 46 is a pressure-receiving surface 47 having a tapered surface that is inclined so that the inner diameter decreases toward the left. A plurality of through holes 45 are formed in the flange portion 43 at intervals in the circumferential direction. The planetary gear 27 is formed with a recessed right end surface, and is formed with a plurality of female screw holes 49 arranged so as to correspond to the plurality of through holes 45. The ring main body portion 42 and the outer ring 46 constitute a displacement restricting means 40A, and the flange portion 43 and the bolt 48 constitute a coupling means 40B.

  When assembling the planetary gear 27 and the spacer 40 to the planetary shaft 14, first, the planetary gear 27 is fitted on the planetary shaft 14 from the right side of the planetary shaft 14, and then the planetary gear 27 is inserted from the right side of the planetary gear 27. The outer ring 46 is inserted between the outer ring 46 and the planetary shaft 14, and then the ring main body 42 of the inner ring 41 is inserted between the inner periphery of the outer ring 46 and the outer periphery of the planetary shaft 14. Then, bolts 48 inserted through the through holes 45 from the right side of the planetary gear 27 are screwed into the female screw holes 49 and tightened. Then, the screwing force of the bolt 48 acts on the tapered pressure receiving surface 47 from the tapered pressing surface 44, and the planetary gear 27, the spacer 40, and the planetary shaft 14 are fixed so as to be able to rotate integrally by a wedge action. The

  As shown in FIG. 1, the sun gear 28 is fixed to the sun shaft 10 so as to rotate integrally. The speed reduction shaft 29 protrudes from the right side surface of the right turret 11 and is fixed in parallel with the sun shaft 10 and the planetary shaft 14. A reduction gear 30 is attached to the reduction shaft 29 via a bearing 31 so as to be relatively rotatable. The reduction gear 30 includes a small-diameter gear 32 (a high-speed side small-diameter gear that is a constituent element of the present invention) and a large-diameter gear 33 (a high-speed-side large-diameter gear that is a constituent element of the present invention). The diameter gear 33 is coupled by a bolt 36 so as to be integrally rotatable.

  The small diameter gear 32 is meshed with the planetary gear 27. The pitch diameter of the small diameter gear 32 is smaller than the pitch diameter of the planetary gear 27. The large diameter gear 33 is engaged with the sun gear 28. The pitch diameter of the large diameter gear 33 is larger than the pitch diameter of the small diameter gear 32. Accordingly, the rotational force of the sun gear 28 (solar shaft 10) is decelerated and transmitted to the planetary gear 27 via the large diameter gear 33 and the small diameter gear 32.

  As shown in FIGS. 2 and 3, the large-diameter gear 33 is on the right side of the planetary gear 27 in the axial direction of the planetary shaft 14 (that is, the same direction as the displacement direction when the planetary gear 27 is removed from the planetary shaft 14). Is arranged. The large diameter gear 33 has a larger pitch diameter than the small diameter gear 32. Therefore, when the shafts 10, 14, and 29 are viewed from the right side, the outer peripheral edge portion of the large-diameter gear 33 covers a part of the outer peripheral edge portion of the planetary gear 27. When the planetary gear 27 is slid (translated) to the right in the axial direction while maintaining the coaxial state with the planetary shaft 14, the corresponding portion 27 </ b> A (in FIGS. 2 and 3) of the planetary gear 27 with the large-diameter gear 33. This means that the planetary gear 27 cannot be removed due to the lower end portion) hitting the large-diameter gear 33. In this embodiment, as a countermeasure, a displacement allowable space 35 is provided in addition to the spacer 40 described above.

  An accommodation space 34 for accommodating the planetary gear 27 is secured between the bearing portion 15 and the large-diameter gear 33. The axial dimension of the accommodation space 34 is larger than the axial dimension of the planetary gear 27. Is also set larger. Thereby, in a state where the planetary gear 27 is attached to the planetary shaft 14, a displacement allowance space 35 for allowing the inclination of the planetary gear 27 is secured between the left outer surface of the planetary gear 27 and the right end of the bearing portion 15. Has been.

  In this embodiment, since the displacement allowance space 35 and the spacer 40 are provided, as shown in FIG. 3, there is a gap between the center hole 27H of the planetary gear 27 and the planetary shaft 14 when the spacer 40 is removed. . By this gap, the planetary gear 27 fitted on the planetary shaft 14 can be tilted so that the axis line is inclined with respect to the planetary shaft 14 (that is, tilted in the radial direction of the planetary shaft 14). At this time, as shown in FIG. 4, first, a portion of the planetary gear 27 opposite to the large-diameter gear 33 (upper side in FIG. 4) across the planetary shaft 14 is displaced so as to be tilted to the right. A part of the center hole 27 </ b> H of the gear 27 is removed from the right end portion 14 </ b> R of the planetary shaft 14.

  Thereafter, when the planetary gear 27 is further tilted, as shown in FIG. 5, the corresponding portion 27A of the planetary gear 27 with the large-diameter gear 33 advances into the displacement allowable space 35, so that the shaft from the large-diameter gear 33 is pivoted. While moving away to the left in the direction, it moves away from the reduction shaft 29 in the radial direction. If the planetary gear 27 is inclined as described above, the planetary gear 27 can be taken out to the right of the planetary shaft 14 and the large-diameter gear 33 through the space between the large-diameter gear 33 and the planetary shaft 14. Further, when the planetary gear 27 is attached to the planetary shaft 14, the planetary shaft 14 may be externally fitted while the planetary gear 27 is inclined as described above. In this way, the planetary gear 27 can be accommodated in the accommodation space 34 between the planetary shaft 14 and the large-diameter gear 33.

  The centrifugal barrel polishing machine of the present embodiment is provided around a planetary gear 27 and a reduction shaft 29 which are provided on the planetary shaft 14 so as to be integrally rotatable and detachable, and are displaced to the right end 14R side of the planetary shaft 14 and removed. A rotating small-diameter gear 32 and a large-diameter gear 33 that rotates integrally with the small-diameter gear 32 and is displaced from the small-diameter gear 32 toward the right end portion 14R are provided, as viewed from the right end portion 14R side of the planetary shaft 14. At this time, a part of the outer peripheral edge of the planetary gear 27 is in a positional relationship so as to be hidden behind the outer peripheral edge of the large-diameter gear 33. However, since the removable spacer 40 is provided between the outer periphery of the planetary shaft 14 and the inner periphery of the planetary gear 27, the planetary gear 27 is removed when the spacer 40 is removed from between the planetary shaft 14 and the planetary gear 27. The corresponding portion 27 </ b> A with the large-diameter gear 33 can be displaced in the radial direction so as to move away from the large-diameter gear 33. Therefore, according to the present embodiment, when the planetary gear 27 is attached to and detached from the planetary shaft 14, it is not necessary to remove the large-diameter gear 33 from the reduction shaft 29, so that workability is good.

  Further, the planetary shaft 14 that supports the barrel tank 12 is caused by the change in the center of gravity due to the mass flowing in the barrel tank 12 and the mass of the planetary gear 27 fixed to the tip of the planetary shaft 14. Therefore, there is a concern that the film may slightly bend and deform. If the planetary shaft 14 that has been bent and deformed contacts the small-diameter gear 32 illegally, abnormal noise may be generated. However, in the present embodiment, the position of the planetary gear 27 is set to the center side (the barrel tank 12 side) from the tip in the axial direction of the planetary shaft 14, so that the generation of abnormal noise can be suppressed. In addition, if the planetary gear 27 is set at the center side of the tip of the planetary shaft 14 in the axial direction, the curved deformation can be suppressed even if the planetary shaft 14 is thinned. It is also possible to reduce the weight.

In addition, the centrifugal barrel polishing machine of the present embodiment includes the coupling means 40B for coupling the spacer 40 so that the planetary shaft 14 and the planetary gear 27 can rotate integrally. The number of parts is reduced as compared with the case of using the means.
In the centrifugal barrel polishing machine of this embodiment, the planetary shaft 14 is rotatably supported by the bearing portion 15, and the planetary gear 27 is disposed closer to the right end portion 14 </ b> R of the planetary shaft 14 than the bearing portion 15. However, the planetary gear 27 can be inclined between the bearing portion 15 and the large-diameter gear 33 so that the axis is inclined with respect to the planetary shaft 14 with the spacer 40 removed. Displacement allowance space 35 is provided. By providing such a displacement permissible space 35, the outer diameter of the planetary gear 27 can be increased, so that the barrel tank 12 can be rotated at a slower speed.

<Other embodiments>
The present invention is not limited to the embodiments described with reference to the above description and drawings. For example, the following embodiments are also included in the technical scope of the present invention.
(1) In the above embodiment, the dimensional difference between the radius of the outer periphery of the driven shaft (planetary shaft 14) and the radius of the inner periphery of the low speed side gear (planetary gear 27) is calculated as the low speed side gear and the high speed side large diameter gear ( Although it is smaller than the radial overlap dimension of the large-diameter gear 33), the dimensional difference between the radius of the outer periphery of the driven shaft and the radius of the inner periphery of the low-speed gear is the diameter of the low-speed gear and the high-speed large-diameter gear. It may be larger than the overlapping dimension in the direction. With this dimensional relationship, it is possible to remove the low speed side gear from the driven side shaft without making it oblique.
(2) In the above embodiment, the spacer 40 includes the coupling means 40B for coupling the driven side shaft (planetary shaft 14) and the low speed side gear (planetary gear 27) so as to be able to rotate integrally. In addition to the spacer, a dedicated coupling means may be provided.
(3) In the above embodiment, the case where the drive-side shaft is the speed reduction shaft 29 arranged at a position eccentric with respect to the sun shaft 10 (that is, the rotation center of the turret) has been described. It can also be applied when the shaft is a solar shaft.
(4) In the above embodiment, the case where the driven shaft is the planetary shaft 14 that supports the barrel tank 12 has been described. However, in the present invention, the driven shaft is composed of a solar shaft (that is, a turret rotation center) and a planet. The present invention can also be applied to the case of a reduction shaft disposed between a shaft (that is, a shaft that supports a barrel tank).
(5) In the above embodiment, the drive side shaft (deceleration shaft 29) is fixed to the turret 11, and the high speed side small diameter gear (small diameter gear 32) and the high speed side large diameter gear (large diameter gear 33) with respect to the drive side shaft. However, the present invention is not limited to this, and the drive side shaft is supported so as to be relatively rotatable with respect to the turret so that the high speed side small diameter gear and the high speed side large diameter gear can rotate integrally with the drive side shaft. May be.

11 ... Turret 12 ... Barrel tank 14 ... Planetary shaft (driven shaft)
14R ... Right end of planetary shaft (one end of driven shaft)
15 ... Bearing part 26 ... Deceleration mechanism 27 ... Planetary gear (low speed side gear)
29 ... Deceleration shaft (drive side shaft)
32 ... Small diameter gear (High speed side small diameter gear)
33 ... Large diameter gear (High speed side large diameter gear)
35 ... Allowable displacement space 40 ... Spacer 40B ... Coupling means

Claims (3)

A reduction mechanism that reduces and transmits rotational force to a plurality of barrel tanks rotatably provided at an eccentric position of the turret,
The deceleration mechanism is
A driven shaft,
A low-speed side gear that is provided on the driven side shaft so as to be integrally rotatable and detachable, and is disengaged from the driven side shaft by being displaced toward one end side of the driven side shaft;
A drive-side shaft arranged in parallel with the driven-side shaft;
A high-speed side small-diameter gear that is rotatable about the drive-side shaft and meshes with the low-speed side gear;
The high-speed side small-diameter gear can be integrally rotated, and is configured to include a high-speed side large-diameter gear that is shifted from the high-speed side small-diameter gear toward the one end side of the driven shaft.
When viewed from the one end side of the driven shaft, the centrifugal barrel polishing machine is configured such that a part of the outer peripheral edge portion of the low speed side gear is hidden by the outer peripheral edge portion of the high speed side large diameter gear. And
A spacer provided detachably between the outer periphery of the driven shaft and the inner periphery of the low speed gear;
In a state where the spacer is removed from between the driven side shaft and the low speed side gear, the corresponding portion of the low speed side gear with the high speed side large diameter gear is radially away from the high speed side large diameter gear. Centrifugal barrel polishing machine characterized in that it can be displaced to   2. The centrifugal barrel polishing machine according to claim 1, wherein the spacer includes coupling means for coupling the driven side shaft and the low speed side gear so as to be integrally rotatable. The driven shaft is rotatably supported by a bearing portion;
The low speed side gear is disposed on the one end side of the driven side shaft with respect to the bearing portion;
Between the bearing portion and the high-speed large-diameter gear, the low-speed gear can be tilted so that the axis is inclined with respect to the driven-side shaft in a state where the spacer is removed. The centrifugal barrel polishing machine according to claim 1 or 2, wherein a displacement permissible space is provided.

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