TWI457482B - The planetary gear type weaving device of the loom - Google Patents

Description

Planetary gear type edging device for loom

The present invention relates to a planetary gear type selvedge device for a loom, and more particularly to a planetary gear type selvedge device having the following components, comprising: a planetary support rotatably disposed about an axis of the central axis, The planet carrier is symmetrically disposed to the axis of the central axis and includes a disk-shaped support disk that rotatably supports a pair of support shafts; a sun gear that is coaxially disposed coaxially with the planet carrier; a pair of intermediate gears that rotate Removably supported on the support disk and meshed with the sun gear; a pair of planetary gears mounted on respective one ends of the pair of support shafts at one end of a bobbin holder, the pair of planetary gears Each of the intermediate gears meshes with the intermediate gear, and a cover member that surrounds at least an outer peripheral portion of the gear train formed by the sun gear, the planetary gear, and the intermediate gear.

For example, the planetary gear type selvage device (hereinafter referred to as "planetary selvedge device") for use in a weaving machine is, for example, a device described in Patent Document 1.

A well-known planetary selvedge device for a loom includes: a sun gear that is non-rotatably disposed in the device, a planet carrier, a disk-shaped support plate that is coaxially disposed with the sun gear and is rotationally driven, and a pair of planets The gear is disposed at a symmetrical position with respect to the center of rotation of the planet carrier (support disk), and is rotatably supported on the support disk by the support shaft. Further, each of the planetary gears meshes with an intermediate gear provided corresponding to each of the planetary gears and rotatably supported on the support plate, and the intermediate gear meshes with the sun gear. Further, the other end of the support shaft which is supported by the planetary gear and is rotatably supported on the support plate at one end is attached with a bobbin holder for holding the bobbin bobbin in which the side yarn is wound.

Further, in the planetary selvage device of the above configuration, by rotating the drive support plate (planetary support), the bobbin bracket supported by the support plate is mounted on the support shaft supporting the bobbin carrier while revolving When the intermediate gear is indirectly meshed with the fixed sun gear, the main shaft rotates around the support shaft by the revolution, and the bobbin bracket performs the planetary motion of the rotation while rotating. Thereby, a pair of side yarns which are taken out from the side bobbins of the respective bobbin holders and which are connected to the woven end (head cloth) of the woven fabric in the weaving process are joined together while performing the opening movement, and thus are woven. The head cloth forms a twisted edge.

However, since the sun gear, the planetary gear, the intermediate gear, and the like are rotationally driven at a high speed, it is necessary to supply lubricating oil to the gears of these gear trains. When the lubrication of the gears is insufficient, the backlash increases due to the engagement of the gears with each other, and the impact of the gears at the start of rotation and stop increases, resulting in damage to the gear and the bobbin bracket. Therefore, it is necessary to maintain the lubrication state of the above gear train.

In a conventional planetary selvage device, a grease as a lubricant is supplied to a tooth surface of a gear such as a sun gear to lubricate the gear train. However, in such a conventional lubrication method, since the centrifugal force generated by the high-speed rotation of the gears and the meshing of the gears cause the lubricant to splash from between the tooth surfaces, the actual situation is that the lubricant cannot be continued. It is maintained between the tooth faces of the gears and cannot be maintained for a long time to maintain the lubrication effect. Further, in the case of the water jet type loom, water accompanying the beating splash adheres to the tooth surface, and the lubrication effect cannot be continuously maintained due to the influence. Therefore, in the conventional planetary selvedge device, it is necessary to periodically supply the lubricant in a short cycle.

In addition, since the grease for the tooth surface is splashed as the gear rotates at a high speed, there is still a concern that the warp yarn may be contaminated.

In the planetary selvage device disclosed in Patent Document 1, a partition plate is interposed between a cover covering a gear train composed of a wheel gear (a planetary carrier or a support plate according to the present invention) and a sun gear, and The structure in which the gear train is surrounded by the wheel gear, the cover and the partition is used. Further, Patent Document 1 discloses that a grease as a lubricant is filled in a region (space) surrounded by a wheel gear, a cover, and a partition.

According to the configuration disclosed in Patent Document 1, since the gear train composed of the sun gear or the like is completely surrounded by the cover or the like, there is no need to worry about the grease splashing and contaminating the warp yarn. However, as a result of the verification by the inventors of the present invention, it is understood that even if the grease is filled into the space around the gear train as disclosed in Patent Document 1, the lubrication effect on each gear cannot be continued for a long time.

Specifically, even if the grease is filled between the tooth surfaces of the gear according to the configuration of Patent Document 1, the grease is rotated from the teeth due to the meshing of the gears during the weaving. The surface is splashed and is gradually splashed away from the outer peripheral surface of the gear (the front end of the tooth portion) with the high-speed rotation of the gear. In this case, since the grease has high viscosity, the grease moving away from the outer peripheral surface of the gear stays at this position, and as a result, there is no grease in the vicinity of the outer peripheral portion of the gear between the tooth faces including the gear. status. Further, although a plurality of oil films are formed on the tooth surface of the gear, the only way is that the lubrication effect is insufficient. Therefore, even according to the structure disclosed in Patent Document 1, it is necessary to frequently perform the operation of supplying (refilling) the lubricant.

Further, in the content disclosed in Patent Document 1, the structure in which the grease is filled in the space is described for the purpose of preventing entry of the wind, and the lubrication effect is not mentioned.

[Patent Document 1] Japanese Patent Laid-Open No. Hei 10-077547

Therefore, an object of the present invention is to provide a planetary selvage device capable of maintaining a gear composed of a sun gear, a planetary gear, and an intermediate gear for a long period of time even if the supply of the lubricant is not frequently performed. The structure of the lubrication effect.

As described above, the present invention is premised on a planetary selvedge device for a weaving machine that forms a kneading edge in a woven fabric, and is particularly premised on a planetary gear type selvedge device including the following components: a planetary carrier that is rotatably provided on a shaft center of the shaft, the planetary bracket being symmetrically disposed on an axis of the central axis and including a disk-shaped support disk that rotatably supports a pair of support shafts; and coaxially disposed with the planetary carrier a sun gear that is not rotatably disposed; a pair of intermediate gears rotatably supported on the support plate and meshed with the sun gear; and a pair of planetary gears mounted on each of the pair of support shafts that fix the wire shaft bracket at one end At the other end, the pair of planetary gears mesh with the intermediate gear, respectively, and a cover member surrounding at least the outer peripheral portion of the gear train constituted by the sun gear, the planetary gear and the intermediate gear.

Further, based on the above task, the planetary selvedge device of the present invention is characterized by comprising: a non-rotating member which is non-rotatably provided and has an opposite surface opposite to a circumferential surface of the planetary carrier along the entire circumference in a radial direction of the rotating shaft And accommodating the retractable space of the gear train, wherein the retractable space is defined by the planetary support and the non-rotating member; and the radius of the planetary space and the non-rotating member that are rotatably driven by the accommodating space A contact type oil seal is provided between the opposite faces of the direction to maintain liquid tightness, and a lubricating oil for lubrication is stored therein. In other words, the entire circumference of the gear train including the sun gear or the like is surrounded by the non-rotating member and the planetary carrier, and the internal region that is formed by the surrounding, that is, the storage space is sealed to the outside and is oiled. .

Further, in the above, the circumferential surface of the planetary carrier is a partial outer circumferential surface or inner circumferential surface constituting at least a portion of the planetary carrier, and extends in parallel with the central axis and is circular in the axial direction of the central axis. Face. Further, as described above, the opposite surface of the non-rotating member is a surface that faces the circumferential surface of the planetary carrier in the radial direction along the entire circumference, and a sealing member as a contact type is interposed between the circumferential surface and the circumferential surface. The face of the oil seal. Therefore, the opposing surface is also a circular surface in the axial direction of the central axis, and is a surface concentric with the circumferential surface. Further, the oil stored in the above-mentioned storage space is not a grease used as a lubricant in the past, but is a lubricating oil generally called an oil, and has lower viscosity than grease and high fluidity.

Further, in the invention, it is preferable that the oil seal is provided such that an inner peripheral surface thereof is crimped to an outer peripheral surface of the support disk or a peripheral portion of a planetary support having an outer diameter equal to or larger than an outer diameter of the support disk. a surface that is crimped to revolve around the axis of the central axis of the planetary gear, and the diameter of the circular trajectory depicted by the front end of the tooth of the planetary gear, that is, the line and the planets passing through the center of the two planetary gears The distance between the outer intersections of the planetary gears (the intersection point of the teeth) in the point where the outer edges of the teeth of the gears intersect (intersection point) is larger than the diameter.

Further, it is preferable that the oil seal is disposed in the axial direction of the center shaft and closer to the bobbin bracket than the gear train. For example, the surface of the planetary bracket and the non-rotating member in which the oil seal is disposed may be supported as a planetary support. The outer peripheral surface of the disk and the inner peripheral surface of the fixed gear cover surrounding the support disk. Further, in this case, the support disk is not driven by the drive gear in the outer peripheral portion, but is driven by the drive gear, and the outer peripheral surface is formed into a flat surface and is rotatably mounted on the central shaft that is rotationally driven to be driven to rotate.

According to the present invention, a space for forming a gear train that is formed by a sun gear, a planetary gear, and an intermediate gear is defined by a planetary carrier and a non-rotating member, and is a planet that is a boundary portion with the outside of the above-mentioned storage space. The gap between the bracket and the non-rotating member becomes a mutually opposing surface in the radial direction of the central axis and the oil seal is interposed between the opposing faces. According to this configuration, the above-mentioned retractable space is kept liquid-tight, and even if a highly fluid lubricating oil (oil) is stored therein, the oil does not leak to the outside. Therefore, according to this configuration, a lubrication method capable of lubricating the gear train by the oil stored in the above-mentioned accommodation space is formed. Further, according to such a lubrication method, unlike the conventional grease lubrication, since the stored lubricating oil is brought up by the rotation of the gear to be scattered and supplied, the tooth surface of the gear is always supplied with lubrication. The state of the oil can maintain the lubrication effect for a long time.

Further, as described above, in order to maintain the liquid tightness of the storage space, the contact sealing member, that is, the oil seal is interposed between the planetary carrier and the non-rotating member that define the storage space. That is, between the non-rotating member and the planet carrier that rotates relative to the non-rotating member, a member that comes into contact with the two is interposed. As a result, the planetary carrier receives rotational resistance due to sliding with the oil seal or sliding of the oil seal and the non-rotating member when it rotates. As a result, when the planetary selvage device uses the main shaft (primary motor) of the loom as the driving source, the vibration of the planetary carrier in the rotational direction is absorbed by the rotation fluctuation of the main shaft, and the wear of the gear can be prevented from being accelerated and the bobbin bracket can be prevented. Damage and so on. The details are as follows.

The internal mechanism (planetary gear mechanism) of the planetary selvedge device including the gear train composed of the sun gear, the planetary gear, and the intermediate gear is composed of a combination of a plurality of gears, and there is a backlash (play) between the meshed gears. As for the entire planetary gear mechanism, there is a large play corresponding to the total amount of backlash (the total amount of backlash between the gears). On the other hand, the spindle of the loom does not always mean to rotate at a constant speed even in the normal operation state, which is caused by the load applied to the spindle by the beating and opening movement of the crucible, and the rotation speed is rotated one revolution. Make changes. Therefore, in the case of the planetary selvage device using the main shaft of the loom as the driving source, vibration in the rotational direction (rotational unevenness) is generated in the planetary carrier that is rotationally driven by the rotation fluctuation of the main shaft. Further, if the rotation of the planetary carrier is uneven in rotation, the tooth surfaces of the meshing gears collide with each other to cause an impact on the tooth surface due to the above-described play, and thus the entire planetary selvage device is also greatly impacted. As a result, the tooth surface wear of the gear is accelerated, or the shock to the entire device is transmitted to the bobbin bracket to cause damage to the bobbin bracket.

On the other hand, if a structure for imparting rotational resistance to the planetary carrier is employed, since the uneven rotation of the planetary carrier is absorbed, it is possible to prevent the wear of the gear as described above from being accelerated and the damage of the bobbin bracket. Further, if the diameter of the oil seal is made larger, that is, if the rotational resistance is imparted at a position farther away from the center of rotation of the planet carrier, the rotation unevenness of the planetary carrier can be more effectively absorbed, and the rotation is further improved. The effect of one layer. Therefore, if the oil seal is formed to be in pressure contact with the outer peripheral surface (which may be the outer peripheral surface of the support disk) of the portion having the outer diameter of the planetary support plate or the like, the above effect can be further enhanced.

Further, in terms of the enlargement of the oil seal, the oil seal is interposed between the inner peripheral surface of the planetary support having a diameter larger than the non-rotating member and the outer peripheral surface of a portion of the planetary carrier (for example, the support disk). In the case where the oil seal is made to have a larger inner diameter than the distance between the tooth ends of the pair of planetary gears, and the planetary bracket is made closer to the planetary gear side than the oil seal contact portion, the diameter is not in contact with the oil seal. The structure of the larger diameter portion enables the planetary bracket to be removed from the planetary selvedge device in the original state of supporting the planetary gear and the bobbin bracket, thereby improving the maintenance performance.

Further, if the oil seal is interposed between the surfaces of the radial direction of the planetary carrier and the non-rotating member, the elastic deformation of the oil seal can absorb and suppress the vibration in the radial direction of the planetary carrier caused by the vibration of the loom. Effect.

In detail, during the weaving process, the loom generates intense vibration, and the rotating shaft vibrates in the radial direction, and the planetary carrier also vibrates in the radial direction. Therefore, by providing the elastically deformable oil seal in pressure contact with the outer peripheral surface of the rotating shaft and/or the planetary carrier, displacement (vibration) in the radial direction of the rotating shaft and the planetary carrier can be absorbed and suppressed. In particular, it is possible to further improve the effect by providing an oil seal that generates the above-described action at a position close to the bobbin carrier as a weight, specifically, closer to the bobbin bracket than the gear train. That is, the rotating shaft receives the weight of the bobbin bracket and the planetary carrier as the weight at a position farther away from the point supporting the own in the axial direction, and is easily affected by the vibration on the side of the planetary carrier (more easily displaced in the radial direction). )status. Therefore, the effect of suppressing the vibration of the planetary carrier can be further enhanced by providing the oil seal that suppresses the above-described vibration effect at a position that is more susceptible to vibration.

[The best form for implementing the invention]

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

1 to 3 are views showing an embodiment of the present invention, Fig. 1 is a partial side sectional view showing an embodiment of a planetary selvage device to which the present invention is applied, and Fig. 2 is a planetary gear mechanism portion of a planetary selvage device. Rear view of the share. 3 is an enlarged cross-sectional view showing a peripheral portion of the planetary gear mechanism of the present invention as a main part of the present invention. Further, the planetary gear mechanism portions of Figs. 1 and 3 are shown as a cross-sectional view taken along line B-B of Fig. 2 seen in the direction of the arrow, and Fig. 2 is a cross-sectional view taken along line A-A of Fig. 1 seen in the direction of the arrow. However, FIG. 2 is a pulley or the like which is not originally shown by an imaginary line for reference. In addition, FIG. 3 omits the following bobbin bracket shown in FIG.

As described previously, the planetary selvedge device 1 to which the present invention is applied includes: a rotary shaft 2 as a central shaft, a planetary carrier 3, a sun gear forming member 4 including a sun gear 41, a pair of planetary gears 5, 5, and a pair of intermediate Gears 6, 6 and a pair of spool brackets BH. In addition, the bobbin bracket BH is a well-known bobbin bracket disclosed in, for example, Japanese Laid-Open Patent Publication No. Hei 9-137334. Therefore, in the following description, the description of the spool bracket will be omitted. In the following description, the front (front side) refers to the bobbin bracket BH side in the axial direction of the rotary shaft 2 (the right side of the drawing of FIG. 1), and the rear (rear side) means the opposite of the bobbin bracket BH. Side (left side of the drawing in Figure 1). In addition, the axial direction means a direction parallel to the central axis (rotational axis) of the rotating shaft 2 (in the direction of the axis), and the radial direction means a direction orthogonal to the axial direction.

As described above, in the present embodiment, the center shaft referred to in the present invention is provided as a rotary shaft 2 that is rotationally driven by a drive mechanism that penetrates the through hole 44 formed in the sun gear forming member 4, The bearing disposed in the through hole 44 is rotatably supported by the sun gear forming member 4.

The sun gear forming member 4 is formed with a portion on the front side, a sun gear 41 that is a gear portion that forms gear teeth on the outer peripheral portion, a shaft portion 42 that extends rearward of the sun gear 41, and a radial direction from the shaft portion 42. A flange portion 43 formed in a radially expanded manner. Further, the through hole 44 is formed to penetrate the shaft portion 42 and the sun gear 41. Further, in the through hole 44, a sealing member 46 such as an oil seal is interposed in a gap between the inner circumferential surface of the through hole 44 and the rotating shaft 2 at the rear end portion.

Further, a cylindrical gear cover 7 as a cover member is attached to the sun gear forming member 4. The gear cover 7 is provided to surround the gear train 19 composed of the sun gear 41, the planetary gear 5, and the intermediate gear 6, and the planetary gear mechanism including the planetary carrier 3. Further, the gear cover 7 has a through hole 74 that is inserted into and fitted to the shaft portion 42 of the sun gear forming member 4, and the through hole 74 is fitted to the shaft portion 42 of the sun gear forming member 4, and is inserted through the flange portion 43. The screw member 45 that is screwed together is fixed integrally with the sun gear forming member 4. Further, a suitable sealant is applied to the contact surface of the sun gear forming member 4 and the gear cover 7 to perform sealing.

The sun gear forming member 4 and the gear cover 7 which are integrally formed as described above are supported by the support bracket 11. The support bracket 11 is erected on the upper surface of a stay or the like which is placed between the frames of the loom not shown, and is formed in a box shape to accommodate the following drive mechanism. Further, in the sun gear forming member 4 and the gear cover 7, the flange portion 43 of the sun gear forming member 4 is inserted into and fitted into the through hole formed in the side wall on the front side of the support bracket 11, the gear cover 7 The rear surface around the through hole 74 is in contact with the outer wall surface around the through hole of the support bracket 11 and, in a state of being positioned, a plurality of screw members inserted and screwed through the side wall of the front side of the support bracket 11 (not The support bracket 11 is fixed. Therefore, the sun gear forming member 4 (planetary gear 41) is disposed on the planetary selvedge device 1 in a state in which it is not rotatable, and in the present embodiment, the gear cover 7 is also formed integrally with the sun gear forming member 4 Set to a state where it cannot be rotated.

In the illustrated example, the planetary carrier 3 is composed of a disk-shaped support disk 31 and a flange portion 32 integrally formed at a front end portion of the support disk 31 so as to be radially enlarged in the radial direction. The support disk 31 has a disk shape in which a flange is formed on the outer circumference, and a through hole 31a into which the rotary shaft 2 is inserted and fitted is formed in the center portion. Further, in the illustrated example, the diameter of the support disk 31 is larger than the distance between the tooth ends of the pair of planetary gears 5, 5.

Further, in the planetary carrier 3, a portion forming the through hole 31a of the support disk 31 (a portion into which the rotary shaft 2 is inserted and fitted) and a portion supporting the support shaft of the planetary gear 5 or the like to be supported are formed. A raised portion that is thicker than other portions of the wall. Further, a key groove 31d fitted to the key 23 attached to the rotary shaft 2 is formed in the through hole 31a into which the rotary shaft 2 is inserted and fitted. Therefore, the planetary carrier 3 is assembled so as not to be rotatable relative to the rotating shaft 2, and is rotatably supported by the sun gear forming member 4 together with the rotating shaft 2. That is, in the planetary selvedge device 1, the planetary carrier 3 is in a state of being rotatable around the axis of the rotation axis (central axis) 2.

Incidentally, the inner diameter of the through hole 31a on the rear end side is enlarged, and the step portion 31e is formed in the through hole 31a. Further, the front end of the rotating shaft 2 is a small diameter portion 21 corresponding to a portion having a smaller inner diameter of the through hole 31a, and the rear side portion is formed as a large diameter portion 22 having a larger diameter than the front end portion. Therefore, according to this configuration, when the planetary carrier 3 is assembled to the rotary shaft 2, first, in a state where the position of the key 23 embedded in the rotary shaft 2 coincides with the position of the key groove 31d of the planetary carrier 3, from the front end side The through hole 31a of the planetary carrier 3 is fitted into the small diameter portion 21. Then, the planetary holder 3 is positioned to the rotating shaft 2 by bringing the step portion 31e in the through hole 31a into contact with the front surface of the large diameter portion 22 of the rotating shaft 2. Further, in this state, the front end of the rotating shaft 2 is located inside the through hole 31a. In this state, the screw member 25 that is inserted into the front end surface of the rotary shaft 2 and screwed by the washer 24 having a larger diameter than the through hole 31a is fastened, and the large diameter portion 22 of the rotary shaft 2 is tightened. The planet carrier 3 is clamped to the washer 24, and the axial direction of the planetary carrier 3 is fixed relative to the position of the rotary shaft 2.

Further, a pair of support shaft pairs 51, 51 and 61, 61 respectively disposed at symmetrical positions with respect to the axis of the rotation axis are supported on the planetary carrier 3.

The pair of support shafts 51, 51 are provided with a wired shaft bracket BH at one end thereof and penetrate the support tray 31, and the planetary gear 5 is supported at the other end side. Each of the support shafts 51 supports the bobbin holder BH and the planetary gear 5 so as to be rotatable relative to each other, and is rotatably supported by the support disc 31 through the bearing. Therefore, each of the bobbin brackets BH and the planetary gears 5 is rotatably supported by the support plate 31 by the support shaft 51. Further, in the through hole 31b through which the support shaft 51 of the support disk 31 passes, a sealing member 52 such as an oil seal is interposed between the inner circumferential surface of the through hole 31b and the support shaft 51 at the end portion on the front side.

Further, the arrangement of the planetary gears 5, 5 is at a position that is not meshed with the sun gear 41 of the sun gear forming member 4 in a state of being supported by the support shaft 51. In other words, the arrangement of the support shaft 51 on the support disk 31 is set to a position where the distance from the axis of the rotary shaft 2 is larger than the sum of the radius of the sun gear 41 and the radius of the planetary gear 5.

In addition, a pair of support shafts 61, 61 are respectively used to support the intermediate gear 6. Each of the support shafts 61 is inserted into and engaged with the through hole formed in the support disk 31 at a position where the intermediate gear 6 supported by the intermediate gear 6 meshes with the two gears of the sun gear 41 and the planetary gear 5. Each of the support shafts 61 is rotatably supported on the support disk 31, and the intermediate gear 6 is rotatably supported by the support shaft 61 by bearings. Therefore, the intermediate gear 6 is also supported on the support disk 31 via the support shaft 61 in a state where the intermediate gear 6 is rotatable relative to the support disk 31.

In the planetary gear mechanism having such a configuration, the planetary carrier 3 is driven to rotate around the axial center of the rotating shaft 2, so that the pair of the planetary carrier 3 is supported at a position deviated from the center of the rotating shaft 2 The planetary gears 5, 5 and the pair of intermediate gears 6, 6 revolve around the axis of the rotary shaft 2. At this time, since each of the intermediate gears 6 performs the above-described revolution in a state of meshing with the sun gear 41, each of the intermediate gears 6 rotates around the axis of the support shaft 61 in accordance with the revolution. Thereby, the planetary gear 5 meshing with the intermediate gear 6 also rotates (rotates) around the axis of the support shaft 51 in accordance with the rotation of the intermediate gear 6. As a result, the bobbin bracket BH attached to the support shaft 51 that supports the planetary gear 5 in a relatively rotatable manner rotates around the axis of the rotary shaft 2 as the rotary shaft 2 (the planetary bracket 3) rotates. Planetary movement.

In the illustrated example, the rotary shaft 2 located at the center of rotation of the planetary carrier 3 is passed through the sun gear forming member 4 and is relatively rotatable with respect to the rotational driving of the planetary carrier 3 for causing the above-described bobbin carrier BH to perform planetary motion. It is disposed on the sun gear forming member 4. Further, the rotating shaft 2 is configured to support the planetary carrier 3 so as not to be rotatable relative thereto, and the planetary carrier 3 is rotated by the rotation of the driving rotary shaft 2.

As a drive mechanism for driving the rotation of the rotary shaft 2, in the illustrated example, the rotation of the rotary drive shaft 12 is transmitted to the rotary shaft 2 by using a spindle (primary motor) of a loom (not shown) as a drive source. mechanism. Specifically, the driven pulley 13 is assembled with respect to the rotating shaft 2 at a rear end portion thereof, and the driven pulley 13 is connected to the driving pulley 14 provided on the drive shaft 12 by the timing belt 16. Therefore, the rotation of the drive shaft 12 is transmitted to the rotary shaft 2 through the drive pulley 14, the timing belt 16 and the driven pulley 13, and the rotary shaft 2 is driven to rotate to rotate the planetary carrier 3.

Further, in the illustrated drive mechanism, the drive shaft 12 supports the bracket 11 by a bearing bush, and the drive pulley 14 is permeable to a pulley that can be fixed at any position in the axial direction of the drive shaft 12 by a separately fixed configuration. The support member 14a is attached to the drive shaft 12, and is disposed in a state where the center of rotation thereof coincides with the axial center of the drive shaft 12.

Further, as described above, the rotating shaft 2 is supported by the sun gear forming member 4 by bearings, and the sun gear forming member 4 is fixed to the support bracket 11 by the gear cover 7, but in the illustrated structure, Even in the above-described drive mechanism, the position of the driven pulley 13 in the axial direction of the rotary shaft 2 is supported by the bearing.

More specifically, on the driven pulley 13, an annular groove 13a having a rear side opening is formed between the base portion fitted to the rotating shaft 2 and the outer peripheral portion of the winding timing belt 16, and on the other hand, the support is provided. A bearing housing 15 that forms a cylindrical portion 15a extending toward the front side (pulley side) is attached to the rear end surface of the bracket 11. In a state in which the bearing housing 15 is assembled to the support bracket 11, the cylindrical portion 15a is in a state of entering the groove 13a of the driven pulley 13. Further, the bearing is interposed between the inner circumferential surface of the cylindrical portion 15a of the bearing housing 15 and the outer circumferential surface of the base portion of the driven pulley 13, and with this configuration, the rotary shaft 2 is transmitted through the base of the driven pulley 13 by the bearing. The support is not only a portion that penetrates the sun gear forming member 4, but also the rear end portion is also supported by the bearing. Therefore, the support in the radial direction of the rotary shaft 2 is in a stable state, and the vibration (the swing of the shaft) accompanying the high-speed rotation of the rotary shaft 2 can be sufficiently suppressed. Further, in the planetary selvage device 1 having the above configuration as an example, the space in which the gear train 19 composed of the sun gear 41, the pair of planetary gears 5, 5, and the intermediate gears 6, 6 is accommodated is kept liquid-tight. The sealed space in which the lubricating oil (oil) MO is stored and the oil bath is formed. In the illustrated configuration, the space in which the gear train 19 is housed (receiving space RS) is mainly defined by the support disk 31 of the planetary carrier 3 and the gear cover 7 as a non-rotating member.

The gear cover 7 is formed as a disk-shaped rear wall having a radial shape that is radially expanded from the shaft portion 42 of the sun gear forming member 4 fitted to the through hole 74, that is, the outer peripheral diameter is larger than the pair of planetary gears 5, 5 The rear wall 71 having a large distance between the tooth ends and the cylindrical outer peripheral wall 72 extending forward from the outer peripheral portion of the rear wall 71 are integrally formed. Further, the outer peripheral wall 72 of the gear cover 7 extends to the vicinity of the flange portion 32 of the planetary carrier 3, and expands in diameter beyond the position of the gear train 19 to form the small diameter portion 72a and the large diameter portion 72b.

That is, the gear cover 7 has a cylindrical shape in which the front surface is substantially closed and the front surface is open, and the outer peripheral wall 72 (small diameter portion 72a) surrounds the outer circumference of the gear train 19. As a result, the gear train 19 is housed in a space surrounded by the rear wall 71 of the gear cover 7 and the small diameter portion 72a of the outer peripheral wall 72. Therefore, the storage space RS of the retracting gear train 19 is a space surrounded by the rear wall 71 and the outer peripheral wall 72 of the gear cover 7, and the boundary on the rear side of the retractable space RS and the surface in the radial direction boundary are defined. The front surface 71a of the rear wall 71 of the gear cover 7 and the inner circumferential surface 73 of the outer peripheral wall 72.

Here, if the rear side boundary of the storage space RS is used as the position of the front surface 71a of the rear wall 71 of the gear cover 7, a part of the shaft portion 42 of the sun gear forming member 4 is exposed at this position in the storage space RS. . In detail, the portion of the shaft portion 42 of the sun gear forming member 4 that is inserted into the gear cover 7 and fitted thereto is also larger in diameter than the portion on the side of the sun gear 41. Therefore, a part of the sun gear forming member 4 (the front surface of the large diameter portion of the shaft portion 42) is exposed in the accommodating space RS on the axial center side of the rotating shaft 2 with respect to the gear cover 7. Therefore, in the illustrated example, a part of the sun gear forming member 4 is also a wall surface defining the receiving space RS, and the shaft portion 42 of the sun gear forming member 4 also includes non-rotating in the drawing and receiving space RS. In the part.

Further, in the above-described storage space RS, the front side of the gear cover 7 itself is opened, and the space defined only by the gear cover 7 is open to the front. However, in the illustrated configuration, the support disk 31 of the planetary carrier 3 is disposed in a region surrounded by the outer peripheral wall 72 of the gear cover 7. Therefore, most of the open area of the front portion of the gear cover 7, that is, the area surrounded by the large diameter portion 72b, is closed by the support disk 31 of the planetary carrier 3. Therefore, in the storage space RS of the retracting gear train 19, the surface on which the front side boundary is defined is the end surface (rear surface) 31f on the gear train 19 side of the planetary carrier 3 (support disk 31). In this way, the area between the front surface 71a of the rear wall 71 of the gear cover 7 and the rear surface 31f of the support disk 31 is enclosed by the inner peripheral surface 73 of the outer peripheral wall 72 of the gear cover 7. The space within the area.

However, since the outer diameter of the support disk 31 is smaller than the inner diameter of the small diameter portion 72a of the gear cover 7, a gap exists between the outer circumferential surface 31g of the support disk 31 and the inner circumferential surface 73 of the outer circumferential wall 72 of the gear cover 7. In other words, since the planetary carrier 3 is rotated at a high speed, it is preferable that the planetary carrier 3 is not in direct contact with the gear cover 7 as a non-rotating member, and a gap is necessarily present between the two. As a result, there is a form in which a gap that allows the storage space RS to communicate with the outside between the planetary carrier 3 and the gear cover 7 exists. Therefore, the present invention closes the gap by interposing a contact type sealing member, that is, an oil seal 91, in a gap between the planetary carrier 3 and the gear cover 7, thereby forming a closed state in which the above-mentioned accommodation space is communicated with the outside. .

As described above, the support disk 31 of the planetary carrier 3 is located in a region surrounded by the outer peripheral wall 72 of the gear cover 7. In other words, the outer peripheral surface (corresponding to the above-described circumferential surface) 31g of the planetary carrier 3 and a part of the support disk 31 thereof is surrounded by the gear cover 7 as a non-rotating member, and the outer peripheral surface 31g of the support disk 31 is at the radius of the rotary shaft 2 The direction is opposed to the inner peripheral surface 73a of a portion (large diameter portion 72b) of the gear cover 7 along the entire circumference thereof. Therefore, in the illustrated example, the inner circumferential surface 73a of the large diameter portion 72b of the gear cover 7 corresponds to the opposite surface of the non-rotating member.

Further, in the illustrated configuration, the portion of the outer peripheral wall 72 of the gear cover 7 that surrounds the support disk 31 is made larger than the large diameter portion 72b having a larger diameter than the portion surrounding the gear train 19, that is, the small diameter portion 72a, and is enlarged. A gap is formed between the opposing surface 73a and the outer peripheral surface 31g of the support disk 31, and the oil seal 91 is interposed in the space. Therefore, the gap between the support disk 31 and the gear cover 7 that communicates the above-described accommodation space RS with the outside is closed by the oil seal 91. Incidentally, the oil seal 91 shown in the drawings is known per se, and its outer peripheral surface is press-fitted into the inner peripheral surface 73a of the large-diameter portion 72b of the gear cover 7, the seal lip portion on the inner peripheral surface side, and the like and the support disk 31. Crimp. Further, the outer peripheral surface of the support disk 31 slides relative to the oil seal 91 in accordance with the rotation of the planetary carrier 3.

As described above, in the illustrated planetary selvedge device 1, the gear train 19 composed of the sun gear 41, the planetary gear 5, and the intermediate gear 6 is housed in the planetary gear 3 and the gear cover 7 as a non-rotating member ( The shaft portion 42) of the sun gear forming member 4 is defined in the retracted space RS, and is surrounded by the planetary carrier 3 and the non-rotating member. Further, a gap between the opposing faces of the support disk 31 and the gear cover 7 that are rotationally driven at a high speed is used as a space in which the sealing member can be mounted, and the oil seal 91 is interposed in the space, thereby making the storage space RS liquid-tight. Excellent confined space.

However, the sun gear forming member 4 is formed with a through hole 44 through which the rotating shaft 2 penetrates and supports the rotating shaft 2 through the bearing. The through hole 44 extends rearward from the region (the boundary on the rear side) of the storage space RS, and the rear end portion thereof is open to communicate with the outside. In this case, although a bearing is provided in the space around the rotating shaft 2 in the through hole 44, the bearing is in communication with the outside due to the gap in the bearing. Therefore, in the illustrated configuration, as described above, the sealing member 46 is interposed in the gap between the rear end portion side of the through hole 44 and the rotating shaft 2, and the sealing member 46 is used to close the periphery of the rotating shaft 2 of the through hole 44. The gap maintains the seal to the outside.

Further, in the illustrated example, the sealing member 46 is disposed on the rear side of the bearing as the bearing is supplied from the outside, but the sealing bearing is sealed as a bearing by a lubricant. The sealing member 46 may be disposed at the front end portion of the through hole 44 (near the boundary of the storage space RS).

In this manner, the space in the through hole 44 is closed by the sealing member 46, and the space on the side of the storage space RS in the through hole 44 is sealed to the outside. As a result, the sealed state of the storage space RS is also maintained.

Similarly, the planetary holder 3 is also formed with a through hole 31b through which the support shaft 51 that supports the planetary gear 5 and the bobbin holder BH penetrates and transmits the support shaft 51 through the bearing. However, the through hole 31b also uses a sealing member 52 provided at the front end thereof to close the gap with the support shaft 51. Therefore, the sealed state of the space RS is not damaged.

Further, a sealing member such as an O-ring is interposed between the rotating shaft 2 and the through hole 31a of the planetary bracket 3 into which the rotating shaft 2 is inserted and fitted to seal the gap therebetween. Similarly, a sealing member such as an O-ring is interposed between the through hole 31c into which the support shaft 61 of the intermediate gear 6 is inserted and fitted, and the support shaft 61 to seal a gap therebetween.

In this way, the storage space RS of the retracting gear train 19 is formed as a sealed space that is sealed to the outside, and has high liquid tightness. Further, a lubricating oil (oil) MO as a lubricant is stored in the storage space RS, and an oil bath is formed. Further, the lubricating oil MO is supplied with oil from an oil supply port (not shown) provided on the outer peripheral wall 72 of the gear cover 7. Further, in the illustrated example, the lubricating oil MO is stored to the extent that the lower portion of the sun gear 41 is immersed.

In the planetary selvedge device 1 having the above-described configuration, the storage space RS of the gear train 19 constituted by the sun gear 41 or the like is formed to form an oil bath while maintaining liquid tightness, and thus stored in the collection. The lubricating oil MO inside the discharge space RS is brought up with the revolution of the planetary gear 5 and splashed into the accommodation space RS to be supplied to the gear train 19. Since the lubricating oil MO is carried by the planetary gear 5 every one rotation of the main shaft of the loom, the lubricating oil MO is supplied to the gear train 19 every time the main shaft of the loom rotates, which can be performed for a long time. Maintain continuous lubrication.

Further, in the illustrated configuration, the oil seal 91 that is press-fitted and fixed to the inner circumferential surface of the gear cover 7 is provided at a position surrounding the support disk 31 of the planetary carrier 3. Further, the outer diameter of the support disk 31 of the planetary carrier 3 is larger than the distance between the tooth ends of the pair of planetary gears 5, 5, and there is no diameter at the rear side of the sliding contact portion of the support disk 31 and the oil seal 91. A portion larger than the outer diameter of the support disk 31. Therefore, according to this configuration, by disassembling the screw member 25 and the washer 24 that fix the planetary bracket 3 to the rotating shaft 2, the planetary gear 5 and the bobbin bracket BH supported by the support shaft 51 can be removed from the planetary bracket 3 without being removed. The planet carrier 3 is detached from the rotating shaft 2. Therefore, the maintenance of the bobbin bracket BH and the internal gear is easy.

Further, in the illustrated configuration, the inner circumferential surface of the oil seal 91 is pressed against the outer circumferential surface 31g of the support disk 31, and the outer circumferential surface 31g of the support disk 31 slides with respect to the oil seal 91 in association with the rotation of the planetary carrier 3. Therefore, the planetary carrier 3 is rotationally driven in a state of being subjected to the sliding resistance (rotational resistance) caused by the oil seal 91.

According to this configuration, in the planetary selvedge device 1 that rotationally drives the rotary shaft 2 and the planetary carrier 3 by the drive shaft 12 that uses the main shaft of the loom as the drive source, the rotation of the planetary carrier 3 is caused even if the main shaft is rotated. The vibration is also absorbed and can suppress its influence. Further, in the illustrated example, since the oil seal 91 is in contact with the outer peripheral surface 31g of the support disk 31 having a large diameter, the distance from the center of rotation of the planetary carrier 3 to the contact surface is also large, and the contact area is also large. Therefore, the sliding torque (resistance torque) generated by the sliding resistance of the oil seal 91 acting on the planetary carrier 3 is larger, and the absorption of the vibration in the rotational direction of the planetary carrier 3 can be performed more efficiently.

Further, the oil seal 91 is provided in a state in which it is exposed to the storage space RS in which the lubricating oil MO is stored as described above, and is exposed to the oil MO that is brought up and splashed along with the rotation of the gear. Therefore, in the illustrated configuration, since the lubricating oil MO is also supplied to the oil seal 91, even if the oil seal 91 is in sliding contact with the planetary carrier 3 (supporting disk 31) that rotates at a high speed, the lubricating oil can be supplied through the lubricating oil. The MO suppresses heat generation and wear of the oil seal 91.

Further, in the illustrated configuration, the planetary holder 3 is formed to have a flange portion 32 at the rear end thereof, and the flange portion 32 covers the front surface of the oil seal 91. According to this configuration, in the case of using the planetary selvage device of the present invention in the water jet loom, water splashed by the beating is splashed in front of the oil seal 91, and the present invention can prevent water from entering the retractable space RS. Lubricating oil in MO. That is, the oil seal, as its characteristic, prevents leakage of the fluid from the inside, but does not completely block the entry of the fluid from the outside. Therefore, as shown in the figure, the water can be prevented from entering the water spray by covering the front surface of the oil seal 91 with the flange portion 32. The retractable space RS in the loom. Further, if the grease is filled in the gap between the flange portion 32 and the oil seal 91, the entry of the water can be more reliably prevented.

In the planetary selvage device 1 of the embodiment described above, the cover member around the outer peripheral portion of the gear train 19 including the sun gear 41, the planetary gear 5, and the intermediate gear 6 is formed as a fixed gear cover 7, but it is also possible As shown in Fig. 4, a part of the planetary carrier 3 is instead formed as a cover member. In addition, FIG. 4 is a view showing only the planetary gear mechanism of the planetary selvedge device and its peripheral portion, and is a side view showing a part thereof in a sectional view. Further, in the configuration shown in Fig. 4, the rotating shaft 2, the sun gear forming member 4, and the support disk 31 of the planetary carrier 3 are basically the same as those of the above-described embodiment. However, in the sun gear forming member 4, the flange portion 43 is formed forward in the axial direction from the flange portion of the above-described embodiment.

In the configuration shown in FIG. 4, as described above, the planetary carrier 3 includes a gear cover portion 34 as a cover member. The gear cover portion 34 is formed separately from the support disk 31 and the flange portion 32, and is fixed to the flange portion 32 by a screw member.

The gear cover portion 34 has a cylindrical outer peripheral wall 34a that extends rearward from the flange portion 32 around the gear train 19 and the support disk 31, and extends radially inward from the rear end of the outer peripheral wall 34a toward the rotary shaft 2. The rear wall 34b is integrally formed. Further, a through hole 34c having an inner diameter larger than the outer diameter of the flange portion 43 of the sun gear forming member 4 is formed in the rear wall portion 34b of the gear cover portion 34.

As shown in the drawing, the position of the rear wall portion 34b of the gear cover portion 34 in the axial direction coincides with the position of the flange portion 43 of the sun gear forming member 4. Therefore, the inner circumferential surface 34d of the through hole 34c formed in the rear wall 34b faces the outer circumferential surface 43a of the flange portion 43 of the sun gear forming member 4 in the radial direction along the entire circumference. Therefore, in such a configuration, the inner peripheral surface 34d of the through hole 34c corresponds to the circumferential surface of the planetary holder 3, and the outer peripheral surface 43a of the flange portion 43 corresponds to the opposing surface of the non-rotating member.

Further, a space surrounded by the support disk 31 of the planetary carrier 3, the gear cover portion 34, and the flange portion 43 of the sun gear forming member 4 serves as a storage space RS for the retracting gear train 19. More specifically, in the illustrated example, the storage space RS of the retracting gear train 19 is the rear surface 31f of the support disk 31 of the planetary carrier 3, the inner circumferential surface of the outer peripheral wall 34a of the gear cover portion 34, and the rear wall 34b. The front surface and the front surface of the flange portion 43 of the sun gear forming member 4 are defined.

In order to form the sealed space RS into a sealed space, the oil seal 92 as a contact type sealing member is interposed in the inner peripheral surface (circumferential surface) of the through hole 34c formed in the gear cover portion 34 of the planetary carrier 3. 34d is a gap between the outer peripheral surface (opposing surface) 43a of the flange portion 43 of the sun gear forming member 4, that is, a gap between the planetary carrier 3 and the sun gear forming member 4 as a non-rotating member, and is a space for retracting The space in which the RS communicates with the outside. Therefore, the storage space RS is in a sealed state in which communication with the outside is blocked by the oil seal 92. Further, the lubricating oil MO is stored in the sealed space RS in the sealed state, and the same lubricating effect as that of the above embodiment can be obtained.

Further, in the above example, the planetary carrier 3 is supported on the rotating shaft so as not to be rotatable relative thereto, and the planetary carrier 3 is rotated by the rotation of the driving rotary shaft. However, the planetary selvedge device to which the present invention is applied is not limited thereto. As shown in FIGS. 5 and 6, the planetary carrier 3 can be directly driven to rotate. 5 is a side cross-sectional view showing the same portion as that of FIG. 4, and FIG. 6 is a cross-sectional view taken along line C-C of FIG. 5 seen in the direction of the arrow.

In the configuration shown in FIGS. 5 and 6 , the sun gear forming member 4 has a shaft portion 47 that matches the sun gear 41 with the center axis and extends forward of the sun gear 41 . Further, the planetary carrier 3 is rotatably supported by the shaft portion 47 via a bearing. That is, in the illustrated example, the planetary carrier 3 is rotatably provided on a fixed central axis (shaft portion 47). Further, unlike the previous embodiment, the sun gear forming member 4 does not have a through hole through which a shaft or the like penetrates.

Further, in the illustrated configuration, the support disk of the planetary carrier 3 is formed as a support gear 33 in the form of a gear in which gear teeth (tooth portions) are formed on the outer peripheral portion. Further, a drive gear 17 for driving the rotation of the planetary carrier 3 meshes with the support gear 33. The position of the drive gear 17 is fixed to the drive shaft 12 and is set to be incapable of rotating relative to the drive shaft 12.

The gear cover 8 as a cover member is integrally assembled to the sun gear forming member 4 in the same manner as the gear cover 7 of the previous embodiment. However, since the gear cover 8 still houses the drive gear 17 meshing with the above-described support gear 33 therein, a part of the rear wall 81 thereof is extended downward as compared with the prior embodiment. Further, the drive shaft 12 extends in the form of a through gear cover 8. Therefore, a through hole 81a through which the drive shaft 12 penetrates is formed in the rear wall 81 of the gear cover 8, and a seal member for closing the gap is interposed in the gap between the inner circumferential surface of the through hole 81a and the drive shaft 12 In order to make the internal space of the gear cover 8 a closed state.

Further, the gear cover 8 extends from the outer peripheral wall 82 extending forward from the outer peripheral portion of the rear wall 81 to a position beyond the front surface of the support gear 33, and the gear cover 8 also has a front wall covering the space front surface of the retracting drive gear 17. 83. The front wall 83 is formed to cover the front surface of the space surrounded by the outer peripheral wall 82 from the inner circumferential surface 82a of the outer peripheral wall 82 to the space between the drive shaft 12 and the support gear 33. Further, a through hole 83a through which the drive shaft 12 penetrates is formed in the front wall 83, and a sealing member is attached to a gap between the inner circumferential surface of the through hole 83a and the drive shaft 12.

Further, a cylindrical portion 35 that protrudes from the front surface of the support gear 33 is integrally formed with the support gear 33 on the planetary carrier 3. The cylindrical portion 35 is formed with an outer diameter of the outer peripheral surface 35a which is located radially inward of the distal end of the tooth portion formed on the outer peripheral portion of the support gear 33, and has a radially extending end portion in the distal end portion. The flange portion 35b.

Further, an oil seal 93 as a contact type sealing member is interposed between the outer peripheral wall 82 of the gear cover 8 and the cylindrical portion 35 of the planetary carrier 3. Specifically, the outer peripheral wall 82 of the gear cover 8 extends forward beyond the position of the support gear 33 of the planetary carrier 3, and the front end portion of the inner peripheral surface 82a faces the outer peripheral surface 35a of the cylindrical portion 35 of the planetary carrier 3. Further, the oil seal 93 is interposed between the front end portion of the inner circumferential surface 82a of the outer peripheral wall 82 of the gear cover 8 and the outer circumferential surface 35a of the cylindrical portion 35 of the planetary carrier 3. Further, as in the previous embodiment, the oil seal 92 is covered on the front side by the flange portion 35b of the cylindrical portion 35 formed on the planetary carrier 3.

Incidentally, in the case of such a configuration, the inner peripheral surface 82a of the outer peripheral wall 82 corresponds to the opposing surface of the non-rotating member, and the outer peripheral surface 35a of the cylindrical portion 35 corresponds to the circumferential surface of the planetary carrier 3. However, in the portion where the rear wall 81 for accommodating the drive gear 17 is extended, the front wall 83 extending from the front end portion of the outer peripheral wall 82 toward the central axis side is formed, and the inner side surface of the front wall 83 is formed. 83b is in a state of being opposed to the outer peripheral surface 35a of the cylindrical portion 35. Therefore, for this portion, the inner side surface 83b of the front wall 83 corresponds to the opposite surface of the non-rotating member.

Further, in the illustrated configuration, the diameter of the cylindrical portion 35 of the planetary carrier 3 is formed smaller than the support gear 33 located closer to the gear train 19 side than the cylindrical portion 35, and the oil seal 92 and the specific support gear are formed. The front end of the tooth portion of 33 is pressed against the outer peripheral surface 35a on the inner side in the radial direction. However, the cylindrical portion 35 may have a shape in which the diameter is enlarged at a position away from the support gear 33 toward the front, and a portion having a larger outer diameter than the support gear 33 (large diameter portion) may be formed. The oil seal 93 is pressure-bonded to the outer peripheral surface of the large-diameter portion having the outer diameter of the support gear 33 (support disk) or more.

Further, according to the configuration shown in Figs. 5 and 6, the gear train 19 including the sun gear 41 and the like is also housed in the gear cover 8, the shaft portion 42 of the sun gear forming member 4, and the planetary carrier 3. In the accommodating space RS, the accommodating space RS is sealed by externally communicating with the oil seal 93 interposed between the gear cover 8 and the opposing faces 82a and 83b of the planetary carrier 3 and the circumferential surface 35a to form a hermetic seal. space. Further, the lubricating oil MO is stored in the sealed space RS in the sealed state, and the same effects as those of the above embodiment can be obtained.

Further, in the illustrated example, the planetary carrier 3 itself constitutes a part of the drive mechanism, and the space around the outer circumference of the support gear 33 and the drive gear 17 communicates with the above-mentioned accommodation space RS. Therefore, in the illustrated configuration, even the driving mechanism for driving the rotation of the planetary carrier 3 has an effect of the lubricating effect formed by the oil bath as described in the above embodiment. In other words, the illustrated structure has a lubricating effect on the entire planetary gear mechanism.

Further, in the illustrated example, the lubricating oil MO is stored in the storage space RS at a position where the sun gear 41 is flooded. At this time, the meshing portion of the sun gear 41 and the intermediate gear 6 and the meshing portion of the intermediate gear 6 and the planetary gear 5 are always located in the lubricating oil MO. According to this configuration, the impact caused by the vibration of the planetary carrier 3 in the rotational direction is alleviated by the cushioning effect by the lubricating oil MO present between the tooth surfaces of the gears, and the bobbin bracket BH can be further improved. The effect of damage such as.

Further, in the configuration shown in Fig. 5, it is also possible to make the cylindrical portion 35 protrude from the rear of the support gear 33 and to provide the front wall 83 of the gear cover 8 on the rear side of the drive gear 17, so that the oil seal 93 is located at the gear The structure around the periphery of the system 19. Further, in the case of this configuration, the front wall 83 (Fig. 7) of the gear cover 8 may be omitted. However, in the case of this configuration, since the support gear 33 and the drive gear 17 are formed outside the storage space RS, it is necessary to lubricate these gears with another lubricant (grease or the like).

Further, in the above example, the drive shaft 12 is driven by the main shaft of the loom, but the planetary selvedge device of the present invention is not limited thereto, and the drive shaft 12 may be driven by a dedicated motor. Alternatively, the rotary shaft 2 in the previous embodiment can be directly driven by a dedicated motor.

Further, the present invention is not limited to any of the embodiments described above, and various modifications can be made without departing from the spirit and scope of the invention.

1. . . Planetary selvedge device (planetary gear weaving device)

2. . . Rotary axis (central axis)

3. . . Planetary bracket

4. . . Sun gear forming part

5. . . Planetary gear

6. . . Intermediate gear

7. . . Gear cover (cover part)

8. . . Gear cover (cover part)

11. . . Support bracket

12. . . Drive shaft

13. . . Driven pulley

13a. . . groove

14. . . Drive pulley

14a. . . Pulley support

15. . . Bearing housing

15a. . . Cylinder

16. . . Timing belt

17. . . Drive gear

19. . . Gear train

twenty one. . . Small diameter section

twenty two. . . Large diameter section

twenty three. . . key

twenty four. . . washer

25. . . Screw member

31. . . Support plate

31a, 31b, 31c. . . Through hole

31d. . . keyway

31e. . . Step

31f. . . End face (back)

31g. . . Outer peripheral surface (circumferential surface)

32. . . Flange

33. . . Support gear (support plate)

34. . . Gear cover part (cover part)

34a. . . Peripheral wall

34b. . . Rear wall

34c. . . Through hole

34d. . . Inner peripheral surface (circumferential surface)

35. . . Cylinder

35a. . . Outer peripheral surface (circumferential surface)

35b. . . Flange

41. . . Sun gear

42. . . Shaft

43. . . Flange

43a. . . Outer peripheral surface (opposite surface)

44, 74. . . Through hole

45. . . Screw member

46. . . Sealing member

47. . . Shaft

51. . . Support shaft

52. . . Sealing member

61. . . Support shaft

71. . . Rear wall

71a. . . front

72. . . Peripheral wall

72a. . . Small diameter section

72b. . . Large diameter section

73. . . Inner circumference

73a. . . Inner peripheral surface (opposite surface)

81. . . Rear wall

81a, 83a. . . Through hole

82. . . Peripheral wall

82a. . . Inner peripheral surface (opposite surface)

83. . . Front wall

83b. . . Inner side (opposite side)

91, 92, 93. . . Oil seal

BH. . . Spool bracket

RS. . . Retractable space

MO. . . lubricating oil

Figure 1 is a partial side cross-sectional view showing an embodiment of a planetary selvage device to which the present invention is applied;

Figure 2 is a rear elevational view of the planetary selvedge device of Figure 1 taken along line A-A;

Figure 3 is a side cross-sectional view of the main portion of the planetary selvedge device shown in Figure 2 taken along line B-B;

Figure 4 is a partial side cross-sectional view showing the main part of another embodiment of the planetary selvedge device of the present invention;

Figure 5 is a partial side sectional view showing the main part of still another embodiment of the planetary selvedge device of the present invention;

Figure 6 is a rear elevational view of the main portion of the planetary selvedge device shown in Figure 5 taken along line C-C;

Fig. 7 is a partial side sectional view showing a main part of still another embodiment of the planetary selvedge device of the present invention.

1. . . Planetary selvedge device (planetary gear weaving device)

2. . . Rotary axis

3. . . Planetary bracket

4. . . Sun gear forming part

5. . . Planetary gear

6. . . Intermediate gear

7. . . Gear cover

11. . . Support bracket

12. . . Drive shaft

13. . . Driven pulley

13a. . . groove

14. . . Drive pulley

14a. . . Pulley support

15. . . Bearing housing

15a. . . Cylinder

16. . . Timing belt

19. . . Gear train

91. . . Oil seal

BH. . . Spool bracket

MO. . . lubricating oil

Claims (3)

A planetary gear type selvedge device for a loom, comprising: a planetary support rotatably disposed around an axis of a central axis, the planetary support being symmetrically arranged to an axis of the central axis and rotatably supporting a pair of support shafts a disk-shaped support disk; a sun gear disposed coaxially with the planet carrier and non-rotatably disposed; a pair of intermediate gears rotatably supported on the support disk and meshing with the sun gear; a pair of planet gears, Mounting on each of the other ends of the pair of support shafts that fix the wired shaft bracket at one end, and the pair of planetary gears respectively mesh with the intermediate gear; the cover member is surrounded by the sun gear, the planetary gears, and At least an outer peripheral portion of the gear train formed by the intermediate gear, the cover member is non-rotatably disposed, and as a non-rotating member, the cover member has a radius along the entire circumference of the circumferential surface of the planetary carrier in a radial direction of the central axis a facing surface opposite to each other; and a receiving space for the gear train, wherein the receiving space is defined by the planetary bracket and the cover member, and The inclusion includes: a space-tight oil seal is provided between the oppositely facing surfaces of the planetary support that is rotationally driven and the radial direction of the cover member to maintain liquid tightness, and Internally stored as a lubricant. The planetary gear type selvedge device of the loom according to claim 1, wherein the oil seal is disposed such that an inner circumferential surface thereof and an outer circumferential surface of the support disc or an outer diameter having an outer diameter of the support disc The outer peripheral surface of a portion of the planet carrier is crimped. The planetary gear type selvedge device of the loom according to claim 2, wherein the oil seal is disposed closer to the bobbin bracket than the gear train in the axial direction of the center shaft.