JP4565078B2 - Winding machine - Google Patents

Description

  The present invention relates to a winding machine. Note that this application claims priority based on Japanese Patent Application No. 2008-153488 filed on June 11, 2008, the entire contents of which are incorporated herein by reference. .

  The winding machine is used, for example, as a device that winds a coil around a teeth portion (magnetic teeth) of a stator core such as a motor or a generator. For example, as shown in FIG. 1, the stator core 20 of the motor 10 is an annular member, and a plurality of teeth portions 22 are evenly arranged in the circumferential direction across the slots 24, and the coil 26 includes each teeth portion. 22 is wound. A rotor 40 (rotor) is disposed inside the stator core 20.

  The coil 26 moves the nozzle of the winding machine along the outer periphery of the tooth portion 22, and winds the wire fed from the nozzle around the outer periphery of the tooth portion 22. As shown in FIG. 2, the stator core 20 has a structure in which a part of the slot 24 can be separated and a hinge 25 is provided in the slot 24 so that the slot 24 can be opened flat. In the stator core 20, the opening of the slot 24 is widened, so that the nozzle 50 of the winding machine 1 can be easily handled when the coil 26 is formed. And after forming the coil 26 in the teeth part 22, the stator core 20 is deform | transformed cyclically | annularly and an edge part is connected. By increasing the occupation ratio of the coil 26 to the slot 24 of the stator core 20, the amount of the coil 26 wound around the tooth portion 22 can be increased, and the performance of the motor 10 can be improved.

  For example, Japanese Patent Application Publication No. 2001-8418 (Patent Document 1) and Japanese Patent Application Publication No. 2004-72923 (Patent Document 2) are disclosed as winding devices for winding a wire around the stator core.

  Japanese Patent Application Publication No. 2001-8418 discloses an apparatus having a large crank mechanism and forming an elliptical orbit of a nozzle while swinging an arm.

  Japanese Patent Application Publication No. 2004-72923 discloses a device that forms square and rectangular trajectories, and discloses a winding device that moves a nozzle along the trajectories. In this publication, a nozzle is supported by a nozzle support plate in which a long hole-shaped Y-direction passive guide hole and an X-direction passive guide hole extending in the X direction and the Y direction orthogonal to each other are formed. The nozzle support plate is controlled by combining drive systems that drive in the X direction and the Y direction, respectively.

Japanese Patent Application Publication No. 2001-8418 Japanese Patent Application Publication No. 2004-72923

  In a winding device, we want to improve productivity by winding a wire around a stator core quickly. The device disclosed in Patent Document 1 includes a large crank mechanism and a swing slider mechanism, and moves the arm back and forth while swinging to form an elliptical orbit of the nozzle. With such a structure that swings the arm, the turning speed of the nozzle cannot be increased so much. Moreover, in patent document 2, the nozzle support plate is controlled combining the drive system which drives each to a X direction and a Y direction. For this reason, force acts on the nozzle support plate in a complicated manner in the X direction and the Y direction, and the turning speed of the nozzle cannot be increased so much.

  The winding machine according to the present invention includes a nozzle that feeds a wire, a nozzle support that supports the nozzle, and a drive mechanism that rotates the nozzle support. The drive mechanism includes a crankcase, an inner peripheral sun gear, a planetary gear member, and a crank member. The inner peripheral sun gear is fixedly disposed on the crankcase. The planetary gear member rotates and revolves while meshing the planetary gear with the inner peripheral sun gear. The crank member is disposed in the crankcase so as to rotate coaxially with the center line of the inner peripheral sun gear, and supports the planetary gear member so that it can rotate and revolve. Further, the planetary gear has a pitch circle diameter that is a half of the pitch circle diameter of the inner circumferential sun gear. The planetary gear member has an action portion that is driven by an elliptical orbit along with the rotation and revolution of the planetary gear at a position shifted from the pitch circle of the planetary gear. The nozzle support is connected to the action part.

  According to this winding machine, the drive mechanism rotates the planetary gear member while rotating the planetary gear supported by the crank member with the inner peripheral sun gear and revolves the planetary gear member, thereby driving the action portion in an elliptical orbit. By making the rotational movement of the crank member and the rotation and revolution of the planetary gear member faster, the turning speed of the nozzle support can be made much faster.

Diagram showing the structure of the motor The figure which shows the process of winding a wire around a stator core The front view which shows the winding machine which concerns on one Embodiment of this invention. 1 is a longitudinal side view showing a winding machine according to an embodiment of the present invention. The front view which shows the casing of the winding machine which concerns on one Embodiment of this invention. These are side views which show the planetary gear member of the winding machine which concerns on one Embodiment of this invention. These are front views which show the planetary gear member of the winding machine which concerns on one Embodiment of this invention. Mechanism diagram of drive mechanism These are side views which show the crank member of the winding machine which concerns on one Embodiment of this invention. These are front views which show the crank member of the winding machine which concerns on one Embodiment of this invention. Side view showing assembly of planetary gear member and crank member The figure which shows the turning state of a nozzle support body The figure which shows the turning state of a nozzle support body The figure which shows the turning state of a nozzle support body The figure which shows the balance of the planetary gear member Diagram showing the balance of the crank member The figure which shows the seal structure of the insertion space of a casing Front view showing a winding machine according to another embodiment of the present invention. A longitudinal side view showing a winding machine according to another embodiment of the present invention. The figure which shows the inner side of the 1st case body of the winding machine which concerns on other embodiment of this invention. The figure which shows the inner side of the 2nd case body of the winding machine which concerns on other embodiment of this invention. Sectional drawing which shows the structure of the seal structure of the winding machine which concerns on other embodiment of this invention, and a sliding support part. Sectional drawing which shows the sealing material of the winding machine which concerns on other embodiment of this invention. The figure which shows the guide which correct | amends the track | orbit of the nozzle support body of the winding machine which concerns on other embodiment of this invention. The figure which shows the modification of the drive mechanism of the winding machine which concerns on other embodiment of this invention.

  Hereinafter, a winding machine according to an embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the member and site | part which show | plays the same effect | action also in different embodiment.

  As shown in FIGS. 3 and 4, the winding machine 1000 includes a nozzle support 600 that supports the nozzles 501 to 503, a casing 700, and a drive mechanism 100. In FIG. 4, the code | symbol P has shown the winding part of the winding machine 1000 which winds the wire 510 supplied from the nozzles 501-503 around the teeth part of a stator core (illustration omitted).

≪Nozzle support 600≫
As shown in FIG. 3, the nozzle support 600 supports the nozzles 501 to 503. The nozzles 501 to 503 are wire supply units for feeding the wire. In this embodiment, the nozzle support body 600 is comprised by the substantially rhombus plate member. Then, the three nozzles 501 to 503 are placed at a predetermined interval in the substantially central portion of the nozzle support 600 so that the wire 510 can be wound around the three teeth portions 22 (see FIG. 2) of the stator core 20 at the same time. Installed side by side. The nozzle support 600 is accommodated in the casing 700, and is connected to the action part 105 of the drive mechanism 100 so as to turn on an elliptical orbit A.

<< Drive mechanism 100 >>
Next, the drive mechanism 100 will be described. The drive mechanism 100 is a mechanism that rotates the nozzle support 600. In this embodiment, as shown in FIG. 3, both side portions 620 and 630 (in this embodiment, rhombus apex portions) of the nozzle support 600 are respectively connected to the action portion 105 of the drive mechanism 100.

  As shown in FIGS. 4 and 5, the drive mechanism 100 includes a crankcase 101, an inner peripheral sun gear 102, a planetary gear member 103, and a crank member 104. The action part 105 described above is provided on the planetary gear member 103.

≪Crankcase 101≫
As shown in FIG. 4, the crankcase 101 is a case that accommodates each member of the drive mechanism 100. In this embodiment, the crankcase 101 is a cylindrical member having a bottom. In FIG. 4, the crankcase 101 is disposed laterally with the bottom 111 facing the right side and the opening 112 facing the left side. The crankcase 101 has a structure in which a first member 101a on the opening 112 side and a second member 101b on the bottom 111 side are combined at an intermediate portion in the axial direction. In this embodiment, the crankcase 101 has an end of the opening 112 attached to the casing 700 described above.

  Inside the crankcase 101, spaces for accommodating the members of the drive mechanism 100 such as the crank member 104 and the inner peripheral sun gear 102 are formed. An insertion hole 113 through which the shaft portion 154 of the crank member 104 is inserted is formed in the bottom portion 111 of the crankcase 101 at the center of the bottom portion 111.

≪Inner sun gear 102≫
The inner peripheral sun gear 102 is an inner gear having teeth on the inner peripheral surface, and is fixed to a step 121 formed at an intermediate position on the inner peripheral surface of the crankcase 101.

≪Planetary gear member 103≫
As shown in FIG. 4, the planetary gear member 103 is a member that rotates and revolves while the planetary gear 131 is engaged with the inner circumferential sun gear 102. In this embodiment, the planetary gear member 103 includes a planetary gear 131 and a planetary shaft 132 as shown in FIGS. 6A and 6B. The planetary gear 131 is an external gear having teeth on the outer peripheral surface, and has a pitch circle diameter that is a half of the pitch circle diameter of the inner peripheral sun gear 102. That is, as shown in FIG. 7, the ratio between the radius r1 of the pitch circle 103c of the planetary gear 131 and the radius r2 of the pitch circle 102c of the inner peripheral sun gear 102 is r1: r2 = 1: 2. In this embodiment, as shown in FIGS. 4 and 9, a boss 141 is provided at the center of the planetary gear 131, and the boss 141 is attached to the end of the planetary shaft 132. The planetary gear member 103 is driven in the elliptical orbit A along with the rotation and revolution of the planetary gear 131 at a position shifted from the pitch circle 103c of the planetary gear 131 when viewed from the infinity point in the rotation axis direction of the planetary gear 131. An action part 105 is provided. In FIG. 7, c <b> 3 indicates the center of the action part 105.

<< Action part 105 >>
In this embodiment, as shown in FIG. 6A, the action portion 105 is provided at the end opposite to the planetary gear 131 mounted on the planetary shaft 132. The action part 105 is a pin-shaped part, and is provided at a position shifted in the radial direction from the central axis c2 of the planetary shaft 132, as shown in FIG. 6B. As shown in FIG. 7, the action portion 105 is disposed inside the pitch circle 103 c of the planetary gear 131.

≪Balancer attached to planetary gear member 103≫
In this embodiment, the planetary gear member 103 is provided with a first counterweight 145 at the end on the side where the action portion 105 is provided, and a first balancer 146 at the end on the opposite side. The first counterweight 145 and the first balancer 146 will be described in detail later.

≪Crank member 104≫
Next, the crank member in this crank apparatus will be described.
As shown in FIGS. 4 and 7, the crank member 104 is disposed in the crankcase 101 so as to rotate coaxially with the center line of the inner sun gear 102. The crank member 104 supports the planetary gear member 103 so that it can rotate and revolve.

  In this embodiment, as shown in FIG. 8A, the crank member 104 is a shaft member that is thick on one side and thin on the opposite side. As shown in FIG. 8A, FIG. 8B, and FIG. 9, a mounting hole 152 for mounting the above planetary gear member 103 is formed in the axial direction from the end surface of the one side. As shown in FIG. 7, the center line c <b> 2 of the mounting hole 152 is shifted from the rotation axis c <b> 1 of the crank member 104 by a distance of the radius r <b> 1 of the pitch circle 103 c of the planetary gear 131. It coincides with the center line c2. Further, as shown in FIGS. 8A and 9, the intermediate portion 153 of the crank member 104 is formed to be slightly thinner than the thick shaft portion 151. In the intermediate portion 153, the bottom portion of the mounting hole 152 formed in the thick shaft portion 151 is open to the side surface of the crank member 104 as indicated by reference numeral 152a in the drawing.

≪Power transmission, pulley 159≫
In this embodiment, a key groove 156 is cut in a shaft portion 154 extending from the intermediate portion 153 of the crank member 104, and a boss 158 is attached via a key 157. As shown in FIGS. 4 and 8, a pulley 159 around which a timing belt 201 is wound from a motor 200 as a power source is attached to the flange of the boss 158.

≪Balancer attached to crank member 104≫
In this embodiment, as shown in FIG. 8, the crank member 104 is provided with a second counterweight 161 at the end on one side and a second balancer 162 on the end on the opposite side. In this embodiment, the second balancer 162 is attached to the pulley 159 described above. The second counterweight 161 and the second balancer 162 will be described in detail later.

<< Attachment structure of planetary gear member 103 and crank member 104 >>
In this embodiment, as shown in FIGS. 4 and 9, the planetary gear member 103 is rotatably mounted in the mounting hole 152 of the crank member 104 with bearings 181 and 182 interposed therebetween. The planetary gear member 103 is mounted in the mounting hole 152 in a state in which the first counterweight 145 and the action portion 105 protrude from the mounting hole 152 of the crank member 104. Further, as shown in FIGS. 4 and 9, the planetary shaft 132 reaches an opening 152 a formed at the bottom of the mounting hole 152 of the crank member 104. The tooth surface of the planetary gear 131 attached to the end of the planetary shaft 132 is exposed to the outside of the crank member 104 through an opening 152 a formed at the bottom of the mounting hole 152 of the crank member 104.

≪Mounting structure to crankcase 101≫
The assembly of the planetary gear member 103 and the crank member 104 is mounted on the crankcase 101 as shown in FIG. The crank member 104 is rotatably mounted on the crankcase 101 with bearings 183 and 184 interposed therebetween. The crank member 104 is mounted so as to rotate coaxially with the center line c1 of the pitch circle 102c of the inner peripheral sun gear 102 fixed to the crankcase 101. The planetary gear 131 is exposed from an opening 152 a formed at the bottom of the mounting hole 152 of the crank member 104 and meshes with the inner peripheral sun gear 102. A spacer 185 and a seal 186 are mounted between the bearing 184 and the boss 158 to which the pulley 159 is attached in the insertion hole 113 through which the shaft portion 154 of the crank member 104 is inserted.

≪Track of action part 105≫
As described above, the planetary gear member 103 meshes with the inner peripheral sun gear 102 and rotates and revolves according to the rotation of the crank member 104. When viewed planarly from the axial direction of the crank member 104, the drive mechanism 100 has a radius r 1 of the pitch circle 103 c of the planetary gear member 103 and a radius of the pitch circle 102 c of the inner peripheral sun gear 102 as shown in FIG. The ratio with r2 is r1: r2 = 1: 2. Further, the action portion 105 is displaced from the rotation center axis c2 of the planetary gear member 103 in the radial direction by a distance r3 that is shorter than the radius r1 of the pitch circle 103c.

  According to the drive mechanism 100, the planetary gear member 103 is supported by the mounting hole 152 of the crank member 104 so as to be capable of rotating and revolving. When the crank member 104 rotates, the planetary gear member 103 rotates and revolves while meshing with the inner peripheral sun gear 102. The planetary gear member 103 rotates twice every revolution. At this time, the action unit 105 draws an elliptical orbit A. Note that the shape of the elliptical orbit A varies depending on the position where the action portion 105 is provided. The position of the action part 105 may be set so that a desired elliptical trajectory A is obtained.

<< Mounting structure of nozzle support 600 >>
In this embodiment, as shown in FIG. 5, there is a nozzle swirl space 710 in which the nozzles 501 to 503 swirl in the center of the casing 700, and the nozzles 715 and 716 formed on both sides of the nozzle swirl space 710 are respectively driven. A mechanism 100 is attached. In the winding machine 1000, the timing belt 201 is wound around the pulley 159 of the two drive mechanisms 100 and the pulley 210 of the motor 200, and the timing at which the action portion 105 of the drive mechanism 100 turns is adjusted. Thereby, the action part 105 of the two drive mechanisms 100 draws the vertically long elliptical orbit A in synchronization with each other as shown in FIG. As shown in FIG. 3, the nozzle support 600 formed of a substantially rhombus plate member has both side portions 620 and 630 (in this embodiment, apex portions on both sides of the rhombus) on the action portion 105 of the drive mechanism 100. Each is connected via a bearing 640 (see FIG. 4).

<< Track of nozzle support 600 and nozzles 501 to 503 >>
The nozzle support 600 is supported by the action part 105 of the drive mechanism 100 described above, and swivels along a vertically long elliptical orbit A in the vertical direction. In the winding machine 1000, the nozzles 501 to 503 for feeding out the wire are supported by the nozzle support 600 as shown in FIGS. 3 and 10 to 12, and as the nozzle support 600 turns, It rotates on an elliptical orbit A.

In this embodiment, the connection structure between the nozzle support 600 and the action part 105 of the drive mechanism 100 is such that the nozzle support 600 is attached to the action part 105 with a bearing 640 interposed therebetween. In this embodiment, two positions (both side portions 620 and 630) of the nozzle support body 600 that are separated from each other are connected to the action portion 105 of the drive mechanism 100.
The timing of the drive mechanism 100 is adjusted by the timing belt 201, and the action unit 105 of the drive mechanism 100 synchronizes with the same elliptical orbit A that is the same as shown in FIGS. 3 and 10 to 12, respectively. Draw. At this time, backlash generated in the inner sun gear 102 and the planetary gear 131 in the drive mechanism 100, backlash between the pulley 159 and the timing belt 201 of the drive mechanism 100, processing accuracy of each member, Depending on the assembling accuracy, the elliptical orbit A of the action portion 105 of the different drive mechanism 100 may be slightly shifted.

  In this embodiment, the position of the action part 105 of the drive mechanism 100 relative to the nozzle support 600 does not change at one place where the nozzle support 600 and the action part 105 of the drive mechanism 100 are connected. The position of the action part 105 of the drive mechanism 100 with respect to is provided. In other words, in this embodiment, a hole 721 (see FIG. 4) for attaching the bearing 640 to the nozzle support 600 is delicately provided at a portion where the action portion 105 of the right drive mechanism 100 shown in FIG. A long hole is provided so that the bearing 640 can move a little with respect to the nozzle support 600. Accordingly, the bearing 640 moves with respect to the nozzle support 600 in accordance with the relative subtle shift of the elliptical orbit A of the action portion 105 of the different drive mechanism 100, and absorbs the deviation. Thereby, the operation of the nozzle support 600 is made smooth.

  Note that, in this embodiment, the two distant positions of the nozzle support 600 are respectively connected to the action portion 105 of the drive mechanism 100 that rotates in the same elliptical orbit. Although illustration is omitted, in order to reduce the load applied to the action part 105 of the drive mechanism 100, the action part 105 of the drive mechanism 100 that rotates two or more positions of the nozzle support 600 synchronously on the same elliptical orbit is used. It is also possible to connect. In this case, the position of the action part 105 of the drive mechanism 100 with respect to the nozzle support 600 does not change in one position among the positions of the nozzle support body 600 connected to the action part 105 of the drive mechanism 100, and the other is the nozzle support body 600. The position of the action part 105 of the drive mechanism 100 with respect to the position may be configured to be displaceable. As a result, the elliptical orbit A of the action portion 105 of the different drive mechanism 100 can be allowed to be relatively delicately shifted, and the operation of the nozzle support 600 can be made smooth.

  The configuration that allows the position of the action part 105 of the drive mechanism 100 relative to the nozzle support 600 to be displaced is not limited to the above-described embodiment.

≪Operation of winding machine 1000≫
Patent Document 1 cited as the prior art involves a large arm swing, and Patent Document 2 has a structure in which guides in the X and Y directions are combined. Due to these structures, inertia force acts greatly, so that it is not suitable for rotating the nozzle support quickly, and therefore it is difficult to shorten the time required for the step of winding the wire around the stator core.
On the other hand, in the winding machine 1000 described above, as shown in FIGS. 4 and 7, the nozzle support 600 is connected to the action part 105 of the drive mechanism 100 and swivels on the elliptical orbit A. According to this winding machine 1000, the driving mechanism 100 rotates and revolves the planetary gear member 103 while meshing the planetary gear 131 supported by the crank member 104 with the inner peripheral sun gear 102, thereby causing the action portion 105. Can be smoothly driven on the elliptical orbit A. The rotational movement of the crank member 104 and the rotation and revolution of the planetary gear member 103 are a series of continuous movements, and less loss due to inertial force than the structures of Patent Document 1 and Patent Document 2 described above, and efficient. It can be driven. For this reason, the turning speed of the nozzle support 600 can be significantly increased as compared with Patent Documents 1 and 2 cited as the prior art.

  In this embodiment, as shown in FIG. 3, at least two positions (in this embodiment, both side portions 620 and 630 (vertical apex portions on both sides of the rhombus nozzle support body 600)) of the nozzle support body 600 are located. These are connected to the action part 105 of the drive mechanism 100 that rotates in the same elliptical orbit synchronously. For this reason, the turning of the nozzle support 600 can be stabilized.

  Further, in this embodiment, as shown in FIG. 7, the action portion 105 is disposed so as to be shifted inside the pitch circle 103 c of the planetary gear 131. Therefore, the pitch circles 102 c and 103 c of the inner peripheral sun gear 102 and the planetary gear 131 can be increased with respect to the elliptical orbit A of the action portion 105, and a larger gear is adopted by the inner peripheral sun gear 102 and the planetary gear 131. can do. As a result, the reaction force that can be permitted when the inner peripheral sun gear 102 and the planetary gear 131 are driven is increased, and the nozzle support 600 (see FIG. 3) can be rotated more stably.

  The nozzles 501 to 503 supported by the nozzle support 600 are driven in an elliptical orbit A as shown in FIG. As shown in FIG. 4, the wire 510 supplied from the nozzles 501 to 503 driven in the elliptical orbit A is wound around a tooth portion of a stator core (not shown) at the winding portion P. Although illustration is omitted, the winding part P includes a mechanism capable of adjusting the position of the wire wound around the tooth part by moving the stator core back and forth according to the movement of the nozzles 501 to 503 driven by the elliptical orbit A. Thereby, the density of the wire wound around the tooth portion can be increased, and the performance of the motor can be improved.

  In this embodiment, as shown in FIGS. 4 and 6, the planetary gear member 103 is provided with a first counterweight 145 at the end on the side where the action portion 105 is provided, and at the end on the opposite side. A first balancer 146 is attached. As shown in FIGS. 4 and 8, the crank member 104 is provided with a second counterweight 161 at one end and a second balancer 162 at the opposite end.

≪Balancer≫
In this embodiment, the centrifugal force acting on the planetary gear member 103 is balanced by the first balancer 146, and the moment of the centrifugal force acting on the planetary gear member 103 at an arbitrary position on the rotation axis c2 of the planetary gear member 103. Are balanced. Further, the centrifugal force acting on the crank member 104 is balanced by the second balancer 162, and the moment of the centrifugal force acting on the crank member 104 is balanced at an arbitrary position on the rotation shaft c1 of the crank member 104. For this reason, this winding machine 1000 can reduce the vibration generated in the drive mechanism 100 and can further increase the turning speed of the nozzle support 600.
Hereinafter, the operation of the first balancer 146 and the second balancer 162 will be described.

≪Balance of planetary gear member 103≫
That is, in this embodiment, the planetary gear member 103 is composed of a planetary gear 131 and a planetary shaft 132 as shown in FIGS. 6A and 6B, and the action portion 105 provided at one end of the planetary shaft 132 has a nozzle. A support 600 is attached. This planetary gear member 103 can be modeled as shown in FIG. In FIG. 13, c2 is a rotation shaft of the planetary gear member 103, M1 is a mass body corresponding to the nozzle support 600 connected to the action portion 105, M2 is a mass body corresponding to the first counterweight 145, M3 Indicates mass bodies corresponding to the first balancer 146, respectively.

  In the model shown in FIG. 13, when the planetary gear member 103 rotates, the centrifugal force acting on the mass body M1 (operation member) is F1, and the centrifugal force acting on the mass body M2 (first counterweight 145) is F2. The centrifugal force acting on the mass body M3 (first balancer 146) is defined as F3. This planetary gear member 103 balances centrifugal force F1, centrifugal force F2, and centrifugal force F3 (F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities)).

In this case, F1, F2, and F3 can each be calculated by the formula “centrifugal force = mass × radius × (angular velocity) ² ”, and the directions of the centrifugal forces F1, F2, and F3 are radial with respect to the rotation axis c2. Acts outward. (Angular velocity) ² can be removed because it is common to each term, and the size of each term of F1, F2, and F3 can be replaced by mass × radius. Further, in this embodiment, as shown in FIGS. 6A and 6B, the action portion 105 to which the nozzle support 600 is attached and the first balancer 146 around the rotation axis c <b> 2 of the planetary gear member 103 are the first balancer 146. The counterweight 145 is disposed 180 ° shifted in the circumferential direction. Therefore, the centrifugal force F1 acting on the mass body M1 (operation member) and the centrifugal force F3 acting on the mass body M3 (first balancer 146) are the centrifugal force F2 acting on the mass body M2 (first counterweight 145). The direction is always opposite. Therefore, in this embodiment, the mass of the mass body M1 (operation member) is m1, the radial distance is A1, the mass of the mass body M2 (first counterweight 145) is m2, the radial distance is A2, and the mass body M3 ( When the mass of the first balancer 146) is m3 and the radial distance is A3, F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities) is (m1 × A1 + m3 × A3) − (m2 × A2) = 0 Become. As described above, when the planetary gear member 103 rotates with the nozzle support 600 attached to the action portion 105, the centrifugal force acting on the planetary gear member 103 is balanced.

  Furthermore, in this embodiment, the moment of the centrifugal force (F1, F2, F3) acting on the planetary gear member 103 is balanced at an arbitrary position on the rotation axis c2 of the planetary gear member 103.

  That is, as shown in FIG. 13, the axial distances from the arbitrary position O1 on the rotation axis c2 of the planetary gear member 103 to the positions where the centrifugal forces F1, F2, and F3 act are L1, L2, and L3, respectively. To do. The planetary gear member 103 has F1 × L1 + F2 × L2 + F3 × L3 = 0 (F1, F2, and F3 are vector quantities). Thereby, when the planetary gear member 103 rotates, the force acting to rotate the planetary gear member 103 around an axis orthogonal to the rotation axis c2 at an arbitrary position on the rotation axis c2 can be suppressed to a small value. it can.

  In this embodiment, the planetary gear member 103 adjusts the weight of the first balancer 146 so that F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities) and F1 × L1 + F2 × L2 + F3 × L3 = 0 ( F1, F2, and F3 are vector quantities). Actually, for each member, manufacturing tolerances occur in terms of weight and mounting position. When adjusting the weight of the first balancer 146, a dummy weight corresponding to the nozzle support 600 is disposed in the action portion 105, and the planetary gear member 103 is in the same state as that supported by the crank member 104. Is supported rotatably. Then, the planetary shaft 132 is rotated by a motor or the like, and the weight and the mounting position of the first balancer 146 may be finely adjusted so that the vibration generated in the planetary gear member 103 is reduced.

  Further, the first balancer 146 may be attached to the axial end portion of the planetary gear member 103. In this embodiment, the 1st balancer 146 is attached to the axial direction edge part of the planetary gear member 103 which left | separated from the position which attaches the action part 105 and the 1st counterweight 145 to an axial direction. In this case, the moment of centrifugal force acting on the planetary gear member 103 by the first balancer 146 is large in the vicinity of the action portion 105 and the first counterweight 145. Therefore, when the first balancer 146 is attached to the planetary gear member 103 at the same radial distance from the rotation axis c <b> 2 of the planetary gear member 103, the first balancer 146 can be made lighter than the other positions of the planetary gear member 103. As described above, the first balancer 146 can be lightened by attaching the first balancer 146 to the shaft end portion of the planetary gear member 103, so that the entire drive mechanism 100 can be lightened.

  When the planetary gear member 103 is rotated, the centrifugal force acting on the planetary gear member 103 is balanced, and the moment of the centrifugal force acting on an arbitrary position on the rotation axis of the planetary gear member 103 is balanced. An example is shown in the model shown in FIG. For example, in the model shown in FIG. 13, the mass bodies M1, M2, and M3 have the same radial distance (A1, A2, A3) from the rotation axis c2 to the center of gravity. The mass body M1 is disposed on the left side from the position where the mass body M2 is attached to the rotation shaft c2, and the mass body M3 is disposed on the right side at a distance of 2S. In this case, when the mass body M1 is 2 g, the mass body M2 is 3 g, and the mass body M3 is 1 g, the centrifugal forces F1, F2, and F3 acting on the planetary gear member 103 are balanced, and the planetary gear member 103 rotates. The moments of centrifugal forces F1, F2, and F3 acting on an arbitrary position on the axis c2 are balanced. An example in which the centrifugal force acting on the planetary gear member 103 is balanced and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear member 103 is balanced is not limited to this example.

<< Balance of crank member 104 >>
The crank member 104 balances the centrifugal force acting on the crank member 104 and the moment of the centrifugal force acting on an arbitrary position on the rotation shaft c1 of the crank member 104. The drive mechanism 100 can be modeled as shown in FIG. In FIG. 14, c1 is the rotation shaft of the crank member 104, M11 is a mass body corresponding to the planetary gear member 103, M12 is a mass body corresponding to the second counterweight 161, and M13 is equivalent to the second balancer 162. Each mass is shown.

  In the model shown in FIG. 14, when the crank member 104 rotates, the centrifugal force acting on the mass body M11 (planetary gear 103) is F11, and the centrifugal force acting on the mass body M12 (second counterweight 161) is F12, The centrifugal force acting on the mass body M13 (second balancer 162) is defined as F13. This crank member 104 balances centrifugal force F11, centrifugal force F12, and centrifugal force F13 (F11 + F12 + F13 = 0 (F11, F12, and F13 are vector quantities)).

  Further, in this embodiment, the moment of the centrifugal force (F11, F12, F13) acting on the crank member 104 is balanced at an arbitrary position on the rotation axis c1 of the crank member 104.

  That is, as shown in FIG. 14, the axial distances from the arbitrary position O2 on the rotation axis c1 of the crank member 104 to the positions where the centrifugal forces F11, F12, and F13 act are L11, L12, and L13, respectively. . The crank member 104 has F11 × L11 + F12 × L12 + F13 × L13 = 0 (F11, F12, and F13 are vector quantities). As a result, when the crank member 104 rotates, the force acting to rotate the crank member 104 around an axis orthogonal to the rotation axis c1 at an arbitrary position on the rotation axis c1 can be kept small.

  In this embodiment, the crank member 104 adjusts the weight of the second balancer 162 so that F11 + F12 + F13 = 0 (F11, F12, and F13 are vector quantities) and F11 × L11 + F12 × L12 + F13 × L13 = 0 (F11). F12 and F13 are vector quantities). Actually, for each member, manufacturing tolerances occur in terms of weight and mounting position. When adjusting the weight of the second balancer 162, a dummy weight corresponding to the planetary gear member 103 is disposed on the crank member 104, and the crank member 104 is rotated in the same state as that supported by the crankcase 101. Support freely. Then, the weight and the mounting position of the second balancer 162 may be finely adjusted so that the crank member 104 is rotated by a motor or the like, and vibration generated in the crank member 104 is reduced.

  In this embodiment, the second balancer 162 is attached to the pulley 159. Since the pulley 159 is separated from the rotation axis c1 of the crank member 104, the centrifugal force that acts even when the weight of the second balancer 162 is reduced increases. For this reason, the lighter second balancer 162 can balance the centrifugal force acting on the crank member 104 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104.

  As described above, in the drive mechanism 100, when the crank member 104 rotates, the planetary gear member 103 rotates and revolves. With such a drive mechanism 100, it is extremely difficult to completely suppress vibration. However, in the drive mechanism 100, the centrifugal force acting on the planetary gear member 103 as described above and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear member 103 are balanced (balanced). Have been adjusted). Further, the centrifugal force acting on the crank member 104 and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104 are balanced (adjusted so as to be balanced). For this reason, it is possible to suppress a biased load from acting on the rotation shaft c2 of the planetary gear member 103 and the rotation shaft c1 of the crank member 104. Thereby, the vibration which arises in the drive mechanism 100 with rotation and revolution of the planetary gear member 103 can be made extremely small. Thereby, the turning speed of the nozzle support 600 can be remarkably increased.

  In addition, the 1st balancer 146 and the 2nd balancer 162 are good to be attached so that replacement | exchange is possible in the thing from which weight differs, respectively. Moreover, the 1st balancer 146 and the 2nd balancer 162 are good to be attached so that an attachment position can be changed. This makes it possible to finely adjust the weights and attachment positions of the first balancer 146 and the second balancer 162. For example, the mounting position of the first balancer 146 may be changed in the radial direction or the axial direction with respect to the rotation axis c <b> 2 of the planetary gear member 103. Accordingly, it is easy to balance the centrifugal force acting on the planetary gear member 103 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation axis c <b> 2 of the planetary gear member 103. Further, the second balancer 162 may be configured such that the attachment position can be changed in the radial direction or the axial direction with respect to the rotation axis c1 of the crank member 104. Accordingly, it is easy to balance the centrifugal force acting on the crank member 104 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation shaft of the crank member 104.

<< Case 700 >>
Next, the casing 700 will be described.
As shown in FIGS. 3 and 4, the casing 700 is a member that accommodates the nozzle support 600. In the winding machine 1000, the nozzle support 600 rotates as described above. However, since the nozzle support 600 is covered with the casing 700, safety can be ensured. In addition, foreign matter can be prevented from entering the drive mechanism 100 that supports the nozzle support 600 from the outside.

<< Structure of casing 700 >>
In this embodiment, as shown in FIG. 4, the casing 700 has a structure in which two case bodies 701 and 702 that are separable in the axial direction of the crank member 104 are fitted. A rectangular space 712 in which the nozzle support 600 turns is formed in the casing 700. FIG. 3 shows a state where the case body 701 (lid) is removed. FIG. 4 is a longitudinal side view of the winding machine, and is a sectional view taken along the line IV-IV in FIG. 3.

  In this embodiment, as shown in FIGS. 3 and 4, a nozzle turning space 710 in which the nozzles 501 to 503 supported by the nozzle support 600 are turned is provided at the center of the casing 700. In this embodiment, the casing 700 has the cylindrical partition 711 that forms the nozzle turning space 710. As shown in FIG. 4, the nozzle support 600 is attached to a slit-like gap 720 formed in the partition 711. A seal 730 is disposed in the slit-like gap 720.

  In this embodiment, as shown in FIG. 4, the case body 701 is formed with a circular hole forming the nozzle swirl space 710 at the center, and the first portion protruding into the casing 700 at the peripheral edge. A partition 711a is provided. The case body 702 is formed with a circular hole forming the nozzle swirl space 710 at the center, and a second partition 711b protruding into the casing 700 is provided at the peripheral edge thereof. The end surface of the first partition 711a on the case body 701 side and the end surface of the second partition 711b on the case body 702 side face each other, and the end surface of the first partition 711a and the end surface of the second partition 711b A slit-like gap 720 is formed between the two. The nozzle support 600 is a plate-like member and is attached to the slit-like gap 720.

  In this embodiment, as shown in FIG. 3, the drive mechanisms 100 are mounted on both sides of a partition 711 that partitions the cylindrical nozzle turning space 710. Specifically, openings 715 and 716 are formed on both sides of the case body 702 across the partition 711b. The drive mechanism 100 is attached to the openings 715 and 716. The drive mechanism 100 has the crankcase 101 mounted in the openings 715 and 716 with the action portion 105 facing the casing 700. The left and right drive mechanisms 100 are synchronized with a timing belt 201, and the action portions 105 of the left and right drive mechanisms 100 are rotated in the same elliptical orbit A in synchronization with each other. The nozzle support 600 is connected to the action part 105 of the drive mechanism 100.

  In this embodiment, the casing 700 ensures the airtightness of the support body turning space 712 in which the nozzle support body 600 turns, and the space 712 is supplied with lubricating oil. In this embodiment, a seal 730 is provided in the slit-shaped gap 720 so that the lubricating oil does not leak into the nozzle swirl space 710.

  That is, in this embodiment, the casing 700 has a nozzle turning space 710 in which the nozzles 501 to 503 supported by the nozzle support 600 are turned, and a support turning space 712 in which the nozzle support 600 is turned. . And the seal | sticker 730 which partitions off the nozzle turning space 710 and the support body turning space 712 is provided. Such a seal 730 can prevent the lubricating oil in the support turning space 712 from leaking into the nozzle turning space 710. Thereby, it can suppress that the wire which penetrates the nozzle turning space 710 gets dirty with oil.

<< Structure of seal 730 >>
Hereinafter, the structure of the seal 730 in this embodiment will be described.
In this embodiment, as shown in FIG. 15, the seal 730 is formed with a double seal inside and outside on the end face of the slit-like gap 720. The first seal 731 disposed outside is mounted in a mounting groove 722 formed on the end surface of the slit-shaped gap 720 and contacts the surface of the nozzle support 600. The second seal 732 disposed on the inside is forcibly pressed against the surface of the nozzle support 600 by the action of a spring 742 as an elastic body. In this embodiment, the second seal 732 has a tapered shape that gradually protrudes toward the surface of the nozzle support 600 from the inside toward the outside.

  Moreover, in this embodiment, it has a drain channel | path toward the outer side rather than a 2nd seal in the radial direction of a cylindrical insertion space. The drain passage may be formed by providing a groove in a part of the first seal 731, or a drain hole may be formed in a mounting groove for mounting the second seal 732.

  In this case, the seal is doubled, and the oil component in the support body swirling space 712 can be substantially blocked by the first seal 731 disposed outside. Furthermore, the oil component that has passed over the first seal 731 can also be blocked by the second seal 732 that is forcibly pressed against the surface of the nozzle support 600.

  Further, the second seal 732 has a tapered shape that gradually protrudes so as to approach the nozzle support 600 as the surface facing the nozzle support 600 moves from the inside to the outside. As for the 2nd seal | sticker 732, the outer top part presses against the surface of the nozzle support body 600 which turns. The oil component can be more reliably blocked by the second seal 732.

Next, a winding machine 1000A according to another embodiment is shown.
As shown in FIGS. 16 and 17, the winding machine 1000A is mainly different in the structure of a casing 700A. An example of a route for supplying the lubricating oil will also be described based on this embodiment.

  As shown in FIG. 17, the casing 700 </ b> A includes a first case body 701 </ b> A (lid) and a second case body 702 </ b> A. As shown in FIGS. 18 and 19, the first case body 701A and the second case body 702A are rectangular steel plates, each having a hole 771a that forms a nozzle swirl space 710 in which the nozzles 501 to 503 swirl at the center. 771b is formed.

  As shown in FIGS. 18 and 19, the first case body 701A and the second case body 702A are provided with seals 730 around the holes 771a and 771b, respectively. On the outside of the seal 730, a sliding support portion 780 for slidingly supporting the swiveling nozzle support body 600 is provided. Further, as shown in FIGS. 17 and 19, the second case body 702A has a recess 790 (see FIG. 19) so as to surround a support turning space 712 in which the nozzle support 600 turns and a region where the drive mechanism 100 is mounted. ) Is formed. A gasket 810 is attached around the recess 790. The drive mechanism 100 is disposed on both sides of the nozzle turning space 710. In this embodiment, openings 715 and 716 for mounting the drive mechanism 100 are formed on the outer side of the sliding support portion 780 in the second case body 702A. Further, in the first case body 701A, depressions 791 and 792 are formed in a region where the action portion 105 of the drive mechanism 100 turns.

  As shown in FIG. 16, the casing 700 </ b> A is provided with the driving mechanism 100 in the openings 715 and 716 formed in the second case body 702 </ b> A described above. As shown in FIG. 17, the drive mechanism 100 directs the action portion 105 from the openings 715 and 716 to a space formed between the first case body 701A and the second case body 702A and directs the crankcase 101 to the opening. 715 and 716. The timing belt 201 is mounted on the two drive mechanisms 100 so that the action portion 105 rotates synchronously on the same elliptical orbit A.

  The nozzle support body 600 is a substantially diamond-shaped plate-like member, and is mounted in a recess of the second case body 702A that forms the support body turning space 712. The action portions 105 of the two drive mechanisms 100 described above are connected to two positions away from the nozzle support 600.

  As shown in FIG. 16, the casing 700 </ b> A is attached with the first case body 701 </ b> A (lid) as shown in FIG. 17 in a state where the drive mechanism 100 and the nozzle support body 600 are attached to the second case body 702 </ b> A. . The gasket 810 attached to the second case body 702A is pressed against the first case body 701A as shown in FIG. The gasket 810 ensures the airtightness of the support swirl space 712.

  Next, the seal 730 constructed around the nozzle turning space 710 will be described.

  In this embodiment, as shown in FIG. 20, the first case body 701A and the second case body 702A are formed with grooves 772 for mounting the sealing material 773 around the holes 771a and 771b forming the nozzle turning space 710. ing. The sealing material 773 is an annular sealing material, and an O-ring 775 is attached to the inner peripheral side surface. Further, in this embodiment, a spring 774 as an elastic member is disposed between the seal material 773 and the bottom of the groove 772 in a compressed state, and the seal material 773 is moved by the spring 774 to the nozzle support 600. Is pressed against the surface. Here, although the spring 774 as the elastic member is illustrated as a coil spring, the spring 774 is not limited to the coil spring as long as it has a function of reliably pressing the annular seal member 773 against the surface of the nozzle support 600. For example, various spring washers may be mounted.

  Further, the annular sealing material 773 has a tapered shape in which the surface 773a facing the nozzle support 600 gradually protrudes so as to approach the nozzle support 600 as it goes from the radially inner side to the outside of the annular seal material 773. Have.

  In this embodiment, the casing 700 </ b> A includes a sliding support portion 780 that supports the turning of the nozzle support 600. In this embodiment, vertically long grooves 781 are formed on both sides of the above-described slit-like gap 720, and a sliding material 782 is attached to the grooves 781.

  Thus, in this embodiment, the nozzle swirl space 710 and the support swirl space 712 are partitioned by the seal 730. The seal 730 prevents the lubricating oil from leaking into the nozzle turning space 710. In this embodiment, the seal 730 is disposed so as to surround the nozzle turning space 710, and includes an annular seal member 773 pressed against the surface of the nozzle support 600. As shown in FIG. 21, the annular sealing material 773 has a tapered shape that gradually protrudes toward the nozzle support 600 as the surface 773 a facing the nozzle support 600 moves from the inside to the outside. ing. For this reason, the taper-shaped top part of the sealing material 773 abuts on the surface of the swiveling nozzle support 600, and the lubricating oil adhering to the surface of the nozzle support 600 can be removed so as to be scraped off. Thereby, it can suppress that lubricating oil leaks into the nozzle turning space 710. Further, the casing 700 </ b> A includes a sliding support portion 780 that supports the turning of the nozzle support 600. For this reason, flapping of the nozzle support 600 can be suppressed.

  In particular, in this embodiment, the sliding support portion 780 is formed around the seal 730 that partitions the nozzle turning space 710. The plate-like nozzle support 600 is mounted in a slit-like gap 720 formed between the seals 730 that partition the nozzle turning space 710. The sliding support portion 780 is formed around the seal 730 and ensures the flatness of the nozzle support 600 around the seal 730. As a result, the nozzle support 600 can be properly mounted in the slit-shaped gap 720, and when the nozzle support 600 is turned, it can be turned smoothly without fluttering or being caught.

In this embodiment, a steel plate made of an aluminum alloy is used for the nozzle support 600, and the surface is subjected to hard alumite treatment. In addition, since the nozzle support body 600 turns, it is desirable that it is lightweight. In this embodiment, although the steel plate which consists of aluminum alloys is used, not only this but the various board | plate material provided with the required intensity | strength can be used, for example, the board | plate material made from carbon can be used.
In this embodiment, for example, a phosphor bronze alloy material is used for the sealing material 773 and the sliding material 782. Such an alloy is slippery with respect to the surface of the nozzle support 600 and has a desired hardness suitable for scraping off oil adhering to the surface of the nozzle support 600. Note that the material used for the sealing material 773 and the sliding material 782 is not limited to a phosphor bronze alloy material. For the sliding material 782, a material that is slippery with respect to the surface of the nozzle support 600 may be used. Further, the sealing material 773 has various materials having good hardness suitable for scraping off oil adhering to the surface of the nozzle support 600 and having good sliding with respect to the surface of the nozzle support 600. Can be used.

  For the sealing material 773 and the sliding material 782, for example, a cast iron material or a steel material can be used. Further, in order to reduce the use of lubricating oil, surface treatment may be performed on a base material such as cast iron or steel with a fluororesin-based material such as polytetrafluoroethylene. Further, a material obtained by kneading graphite or the like into a fluororesin material such as polytetrafluoroethylene may be used. The surface of the nozzle support 600 may also be subjected to a surface treatment with a fluororesin-based material such as polytetrafluoroethylene at least at a site where slip occurs between the sealing material 773 and the sliding material 782.

Next, a route for supplying lubricating oil will be described. In this embodiment, the lubricating oil is supplied from an oil supply hole 820 formed in the crankcase 101 of the drive mechanism 100 as shown in FIG. The supplied lubricating oil is supplied to the support body turning space 712 in the casing 700A through the gap 192 between the members in the drive mechanism 100 and the bearings 181 and 183. In this embodiment, the lubricating oil in the drive mechanism 100 is, for example, a gap 192 between the inner surface of the crankcase 101 and the outer surface of the crank member 104 or between the planetary gear member 103 and the crank member 104. It is also supplied to a portion where the inner peripheral sun gear 102 and the planetary gear 131 mesh with each other through a gap.
In this embodiment, as shown in FIG. 17, in the drive mechanism 100, a spacer 190 is mounted between a bearing 181 that mounts the planetary gear member 103 on the crank member 104 and the bearing 182. An oil path is also formed in the spacer 190.

  The lubricating oil supplied to the support body swirl space 712 in the casing 700 </ b> A forms an oil atmosphere in the support body swirl space 712 due to the rotation of the drive mechanism 100 and the swirl of the nozzle support body 600. With such an oil atmosphere, lubricating oil adheres to the surface of each member in the support body swirling space 712 of the casing 700A. Also, as shown in FIGS. 16 and 17, the lubricating oil supplied into the casing 700A is discharged from a discharge hole 830 formed in the lower portion of the support turning space 712 of the second case body 702A.

  Although illustration is omitted, a circulation device that collects the lubricating oil discharged from the discharge hole 830 and supplies it to the drive mechanism 100 again may be provided.

  As mentioned above, although the winding machine 1000 which concerns on one Embodiment of this invention was demonstrated, the winding machine 1000 which concerns on this invention is not limited to embodiment mentioned above.

  The specific shapes and structures of the inner sun gear 102, the planetary gear member 103, the crankcase 101, the crank member 104, and the like described above can be variously changed.

  For example, in the above-described embodiment, as shown in FIG. 3, the nozzle support 600 has both side portions 620 and 630 (vertical portions on both sides of the rhombus-shaped nozzle support 600) on the action portion 105 of the drive mechanism 100. Each is connected. The present invention is not necessarily limited to such a form. Although illustration is omitted, a guide for guiding the turning of the nozzle support 600 may be provided. Further, the position where the nozzle support 600 is connected to the action part 105 of the drive mechanism 100 may be three. Further, the position where the nozzle support 600 is connected to the action part 105 of the drive mechanism 100 may be one, and a guide may be provided at another position.

Further, as shown in FIG. 22, the nozzle support 600 that supports the nozzles 501 to 503 does not have to be diamond-shaped.
Further, the elliptical orbit A may be corrected as shown in FIG. That is, the winding machine 1000A according to the present invention includes, for example, a guide 750 that corrects the elliptical orbit A for rotating the nozzle support 600 in an application where the rotation speed of the nozzle support 600 is decreased. You may prepare. For example, a guide groove 751 is formed so that the nozzle support 600 moves linearly at an arc portion connecting the major axes of the ellipses, and a pin 752 provided on the nozzle support 600 is engaged with the guide groove 751. In addition, the trajectory B around which the nozzle support 600 turns is corrected. In this embodiment, a slider 753 may be provided for the connection structure of the nozzle support 600 and the action portion 105 of the drive mechanism 100 so as to allow correction of the turning trajectory of the nozzle support 600. In the form shown in FIG. 22, a corrected trajectory B in which the nozzle support 600 moves linearly is formed at an arc portion connecting the major axes of the ellipse A. The drive mechanism 100 further forms a vertically long ellipse A, the arc portion connecting the long axes of the ellipse A is brought close to a straight line, both ends are corrected, and the nozzle support 600 does not move in the vertical direction more than necessary. In addition, a guide may be provided.

  Further, in the above-described embodiment, the action portion 105 is disposed so as to be shifted to the inside of the pitch circle 103 c of the planetary gear 131. As a result, the action part 105 is swung on the elliptical orbit A. However, as shown in FIG. 23, the action part 105 may be shifted to the outside of the pitch circle 103c of the planetary gear 131 to form an elliptical orbit. Thus, when the action part 105 has shifted | deviated outside the pitch circle 103c of the planetary gear 131, when forming the elliptical orbit of the same shape, the planetary gear 131 and the inner peripheral sun gear 102 can be made small. Further, each member of the drive mechanism 100, for example, the crank member 104 can be reduced. For this reason, the inertia force which acts on the drive mechanism 100 can be suppressed small.

  In addition, it is desirable to reduce the weight of each member of the drive mechanism 100, in particular, a member such as the crank member 104 that generates an inertial force associated with rotation during driving. For example, a light material such as an aluminum alloy may be used, or the wall thickness may be reduced while ensuring a required strength.

  As mentioned above, although the various modifications are illustrated about the winding machine concerning one embodiment of the present invention, the winding machine concerning the present invention is not limited to the modification mentioned above.

DESCRIPTION OF SYMBOLS 100 Drive mechanism 101 Crank case 102 Inner periphery sun gear 103 Planetary gear member 104 Crank member 105 Action part 131 Planetary gear 132 Planetary shaft 145 1st counterweight 146 1st balancer 161 2nd counterweight 162 2nd balancer 181-184 Bearing 186 Seal 200 Motor 201 Timing belt 210 Pulley 501-503 Nozzle 510 Wire rod 600 Nozzle support 610 Central portion 620, 630 Nozzle support both sides 700, 700A Casing 710 Nozzle swirl space 712 Support swirl space 720 Slit-shaped gap 722 Mounted Groove 730 Seal 731 First seal 732 Second seal 750 Guide 751 Guide groove 752 Pin 753 Slider 772 Groove 773 for attaching a seal material Seal material 775 O-ring 7 80 Sliding support portion 810 Gasket 820 Oil supply hole 830 Discharge hole 1000, 1000A Winding machine A Elliptical track

Claims (12)

A nozzle support for supporting a nozzle for feeding out the wire,
A drive mechanism connected to at least two positions away from the nozzle support and having an action part that rotates in the same elliptical orbit synchronously;
A winding machine comprising:
The drive mechanism is
A crankcase,
An inner sun gear fixedly disposed on the crankcase;
A planetary gear member that rotates and revolves while meshing a planetary gear with the inner circumferential sun gear;
A crank member disposed in the crankcase so as to rotate coaxially with the center line of the inner sun gear, and supporting the planetary gear member so as to be capable of rotating and revolving,
The planetary gear has a pitch circle diameter that is a half of the pitch circle diameter of the inner circumferential sun gear;
The planetary gear member has an action portion that is driven by an elliptical orbit along with the rotation and revolution of the planetary gear at a position shifted from the pitch circle of the planetary gear ,
The crank member is a shaft member, and a mounting hole for mounting the planetary gear member is formed in an axial direction on one end face of the crank member,
The center axis of the mounting hole is formed at a position shifted from the rotation axis of the crank member by the distance of the radius of the pitch circle of the planetary gear,
A winding machine in which the planetary gear member is rotatably supported in the mounting hole with a bearing interposed therebetween . In the connection structure between the nozzle support and the action portion of the drive mechanism, the position of the action portion of the drive mechanism with respect to the nozzle support is changed in one of at least two positions away from the nozzle support. In the other, the winding machine according to claim 1 , wherein the position of the operating portion of the drive mechanism relative to the nozzle support is displaceable. Wherein the nozzle support with a guide for correcting the elliptical orbit to rotate, the winding machine according to claim 1 or 2. The winding machine according to any one of claims 1 to 3 , wherein the action portion is displaced inward of a pitch circle of the planetary gear. The winding machine according to any one of claims 1 to 3 , wherein the action portion is shifted to an outside of a pitch circle of the planetary gear. The planetary gear member balances the centrifugal force acting on the planetary gear member, and balances the moment of centrifugal force acting on the planetary gear member at an arbitrary position on the rotational axis of the planetary gear member,
The crank member, the centrifugal force balance acting on the crank member and the moment of the centrifugal force acting on the crank member at an arbitrary position on the rotation axis of the crank member is balanced, claims 1-5 Winding machine described in any of the above. The planetary gear member is
The first counterweight provided at the end on the side where the action portion is provided;
A first balancer provided at an axial end of the planetary gear member that is axially separated from a position where the action portion is provided;
Have
The centrifugal force acting on the planetary gear member is balanced by the first counterweight and the first balancer, and the centrifugal force acting on the planetary gear member at an arbitrary position on the rotation axis of the planetary gear member. The winding machine according to claim 6 , wherein the moments are balanced. The crank member is a shaft member, and a mounting hole for mounting the planetary gear member is formed in an axial direction on one end face of the crank member,
A second counterweight provided on the end face of the crank member in which the mounting hole is formed;
A second balancer provided at a position separated in the axial direction from a position at which the second counterweight is provided;
Have
The second counterweight and the second balancer balance the centrifugal force acting on the crank member, and the moment of the centrifugal force acting on the crank member at an arbitrary position on the rotation shaft of the crank member. The winding machine according to claim 7 . The winding machine according to any one of claims 1 to 8 , further comprising a casing for housing the nozzle support. The casing has a nozzle swirl space in which a nozzle supported by the nozzle support swirls, and
A support turning space in which the nozzle support turns; and
The winding machine according to claim 9 , comprising a seal that partitions the nozzle swirl space and the support swirl space. The seal includes an annular seal material,
The annular sealing material is disposed so as to surround the nozzle swirling space, and is pressed against the surface of the nozzle support,
11. The winding according to claim 10 , wherein a surface of the annular seal material facing the nozzle support has a tapered shape that gradually protrudes so as to approach the nozzle support gradually from the inside toward the outside. Machine. The winding machine according to any one of claims 9 to 11 , wherein the casing includes a sliding support portion that supports turning of the nozzle support.

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