JP7200742B2 - Power transmission device, swing device for machine tool equipped with power transmission device, and method for adjusting power transmission device - Google Patents

Description

The present invention relates to a power transmission device, a turning device of a machine tool having the power transmission device, and a method for adjusting the power transmission device.

Conventionally, in a power transmission device configured with, for example, three or more gears for decelerating or accelerating, the magnitude of backlash between the gears was kept within a predetermined range in order to obtain operability and good performance. should be Various methods are conceivable to keep the magnitude of the backlash within a predetermined range. For example, it is conceivable to improve the positional accuracy of the three gear shafts and the dimensional accuracy of the gear teeth. In this case, only by assembling three gears, it is possible to obtain a backlash between the gears within a predetermined range. However, in this method, there is a problem that the cost for obtaining the necessary positional accuracy of the gear shaft and the dimensional accuracy of the gear teeth is very high.

However, as a technique for solving this problem, for example, there is a technique disclosed in Patent Document 1. In the technique of Patent Document 1, only the central gear of the three gears is movable, and the backlash between the gears is adjusted by moving the central gear. In this case, the positional accuracy of the gear shaft and the dimensional accuracy of the teeth of the gear can be manufactured with normal accuracy, so this point can be handled at low cost.

Japanese Patent No. 4655650

However, in the method of Patent Document 1, if the first backlash of the two backlashes between the gears is adjusted, the second backlash may change accordingly. In other words, it is very difficult to simultaneously adjust the backlash at two locations. As a result, a highly accurate backlash can be obtained, but there is a risk that the adjustment will take a long time and the cost will increase.

Therefore, the present invention provides a power transmission device that can adjust the backlash between gears at low cost and with high accuracy even if the power transmission device is composed of three or more gears, and a machine tool equipped with the power transmission device. It is an object of the present invention to provide a method for adjusting a swing device and a power transmission device.

(1. Power transmission device)
A power transmission device according to the present invention includes a housing, a first input/output gear to which a first input/output rotary shaft having a first input/output axis is connected, and an intermediate shaft offset by a predetermined distance from the first input/output axis. an intermediate gear arranged in line and meshing with the first input/output gear; and a second input/output gear, which is a gear group including at least one gear rotatably supported by the housing and meshing with the intermediate gear. Prepare. Further, the power transmission device includes a gear flange that rotatably supports the first input/output rotary shaft and is supported by the housing so as to be rotatable about the first input/output axis, and a gear flange that is coaxial with the intermediate axis. a first rotating body support member arranged to rotatably support the intermediate gear and supported by the gear flange so as to be movable within a predetermined range in the radial direction; and the first rotating body supporting member. a first mesh condition adjustment mechanism capable of being adjusted so that a first mesh condition having a predetermined first backlash between the first input/output gear and the intermediate gear is achieved by the radial movement of the By rotating the gear flange about the first input/output axis, the intermediate gear and the second input/output gear adjusted to the first meshing state between the first input/output gear and the second input/output gear are moved to a predetermined number. a second mesh adjustment mechanism that is adjustable to a second mesh condition having two backlashes.

With such a configuration, when the backlash between the gears from the first input/output gear to the second input/output gear is adjusted to a predetermined amount, the power transmission device first adjusts the , to adjust the first backlash between the first input/output gear and the intermediate gear. Then, after that, apart from the adjustment of the first backlash, the second backlash between the intermediate gear and the second input/output gear is adjusted.

For this reason, there is no possibility that the backlashes of the gears meshing with each other on both sides are simultaneously adjusted while moving one gear, and that the backlashes of the gears are interlocked with each other and changed each time the adjustment is performed. Therefore, the adjustment is easy, and the first backlash and the second backlash can be obtained with high precision in a short time. Since the first backlash and the second backlash can be obtained in a short time, it can be provided at low cost.

(2. Swivel device for machine tools)
In the turning device of a machine tool equipped with the power transmission device according to the present invention, the second input/output rotary shaft of the second input/output gear of the power transmission device is connected to the input shaft of the speed reducer provided in the turning device. In this way, since a low-cost power transmission device is applied to the turning device, the cost of the turning device can be reduced.

(3. Method of adjusting the power transmission device)
A method for adjusting a power transmission device according to the present invention moves the intermediate gear in the radial direction by means of a first meshing state adjusting mechanism, and adjusts the meshing state between the intermediate gear and the first input/output gear to the first meshing state. a second step of fixing to the gear flange the first rotating body support member that supports the intermediate gear while maintaining the first meshing state after the first step; By rotating the gear flange by a second meshing state adjusting mechanism, the first input/output gear and the intermediate gear meshing in the first meshing state on the gear flange are rotated around the first input/output axis, and a third step of setting the meshing state between the intermediate gear and the second input/output gear to the second meshing state. Such an adjustment method can provide the above-described high-precision, low-cost power transmission device.

It is a figure which shows the meshing state of the gear of the power transmission device which concerns on 1st embodiment. It is a II-II arrow directional cross-sectional view of FIG. FIG. 3 is a partially enlarged view of the periphery of a second bolt in FIG. 2; FIG. 3 is a partially enlarged view around a first bolt in FIG. 2; FIG. 5 is a diagram for explaining the state of radial movement of the intermediate gear when the first mesh state adjusting mechanism is operated; FIG. 10 is a diagram for explaining the state of rotation of the intermediate gear in the circumferential direction when the second mesh state adjusting mechanism is operated; FIG. 10 illustrates backlash between the first input/output gear and the intermediate gear, and between the intermediate gear and the second input/output gear; 4 is a flowchart of a backlash adjustment method; FIG. 3 is a cross-sectional view corresponding to FIG. 2 of a power transmission device according to a second embodiment; It is a figure which shows the backlash between the 1st input-output gear and 2nd input-output gear which concern on 2nd embodiment, and an intermediate gear. 1 is an overall view of a machine tool provided with a turning device to which a power transmission device is applied; FIG. FIG. 11 is an overall view of the turning device described in FIG. 10; 11. It is XII-XII arrow directional cross-sectional view of FIG.

<1. First Embodiment>
(1-1. Overview of power transmission device 1)
First, the outline of the power transmission device will be described. In this embodiment, the power transmission device 1 shown in FIGS. 1 and 2 is configured by combining a plurality of (at least three) gears (corresponding to a first input/output gear, a second input/output gear and an intermediate gear). It is a power transmission device as well as a transmission device. An input shaft is integrally connected to one of the gears (first input/output gear, second input/output gear) arranged at both ends of the plurality of gears. An output shaft is integrally connected to the gear arranged on the other side. An output shaft of a power source such as a motor is connected to the input shaft of the power transmission device.

As a result, the gear connected to the input shaft of the power transmission device rotates around the input shaft, thereby actuating the gears that mesh adjacently, and transmitting the rotational torque to the output shaft via the actuated gear. Output. The output shaft of the power transmission device can be connected to, for example, the input shaft of another transmission device, the input shaft of a device that requires driving force, or the like. Note that each gear is not limited to a spur gear to be described later, and may be a helical gear.

The power transmission device 1 can be applied to various devices as a device that transmits power from a predetermined input shaft to a predetermined output shaft. For example, the power transmission device 1 can be applied to an engine balancer device provided in various vehicles. Further, the power transmission device 1 can be applied to a turning device (spindle turning device) of a 5-axis machining center (machine tool) described in this embodiment. In addition, the power transmission device 1 is not limited to the turning device of the above-described 5-axis machining center, and can also be used as a gear mechanism (for example, a reduction mechanism or a speed-up mechanism) of each part of other machine tools such as grinders, lathes, milling machines, etc. Applicable.

(1-2. Configuration of power transmission device 1)
A first embodiment of the power transmission device 1 will be described. Each figure used for explanation is a schematic diagram, and the shape of each part may not necessarily be exact. As shown in FIGS. 1 and 2, the power transmission device 1 mainly includes a housing 10 (see FIG. 2), a first input/output gear 20, a gear flange 30, a first rotor support member 40, and an intermediate gear. 50 , a first meshing condition adjusting mechanism 60 , a second input/output gear 70 , and a second meshing condition adjusting mechanism 80 .

(1-2-1. Housing 10)
As shown in FIG. 2, the housing 10 mainly includes a bottom plate 11 and side walls 12. As shown in FIG. Although not shown, the side walls 12 are erected along the entire outer circumference of the bottom plate 11 . The housing 10 accommodates the first input/output gear 20 , the gear flange 30 , etc., which constitute the power transmission device 1 , in a space surrounded by the bottom plate 11 and the side walls 12 . The bottom plate 11 has a stepped through hole 13 for fitting the gear flange 30 with a spigot, and a stepped surface 14 formed radially outwardly of the stepped through hole 13 on the first input/output gear 20 side. And prepare.

A plurality of (for example, 6 to 8) internal threads 15 are formed in alignment in the outer edge of the stepped surface 14 in the circumferential direction. The internal thread 15 fixes the gear flange 30 to the housing 10 by screwing a second bolt 16, which will be described in detail later, in a state in which the end surface 32a of the collar portion 32 of the gear flange 30 is in contact with the stepped surface 14. However, in FIG. 2, only one female thread 15 is shown. The fitting between the bottom plate 11 and the gear flange 30 will be described later. Moreover, as an example, a case in which the housing 10 does not have the side wall 12 may be assumed without being limited to the above aspect.

In this embodiment, as an example, the first input/output gear 20 is a spur gear. As shown in FIG. 1, the addendum diameter of the first input/output gear 20 is φD1. One end of the shaft-shaped first input/output rotary shaft 21 is integrally connected to the first input/output gear 20 as described above. At this time, one end of the first input/output rotating shaft 21 and the first input/output gear 20 may be integrally connected by any means.

For example, one end may be formed with a male thread, the other end may be formed with a female thread, and the male and female threads may be screwed together for connection. Alternatively, one end of the first input/output rotary shaft 21 and the first input/output gear 20 may be connected by welding. Alternatively, the first input/output rotating shaft 21 and the first input/output gear 20 may be connected by press fitting. Further, as in the present embodiment, the tooth portion of the first input/output gear 20 is formed by processing, for example, on the outer peripheral surface of the first input/output rotary shaft 21 on the one end side (the tip portion, the left side in FIG. 2). The one input/output rotating shaft 21 and the first input/output gear 20 may be integrated.

At this time, any processing such as cutting or forging may be used. In addition, the first input/output rotating shaft 21 and the first input/output gear 20 may be integrally formed by a method other than machining, such as casting or sintering. The same applies to a second input/output gear 70 and a second input/output rotary shaft 71, which will be described later.

Also, the other end (the right side in FIG. 2) of the first input/output rotary shaft 21 can be connected to an output shaft or an input shaft of various devices. For example, as an example, the other end of the first input/output rotary shaft 21 can be connected to the output shaft of the motor M described later in this embodiment. At this time, the first input/output rotating shaft 21 and the output shaft of the motor M may be connected by any means (method). For example, the first input/output rotary shaft 21 and the output shaft of the motor M may be integrally formed by the same shaft member as in this embodiment described later. As a result, the motor M is rotationally driven by the control device, and when the output shaft rotates, the first input/output gear 20 rotates integrally with the output shaft of the motor M via the first input/output rotating shaft 21 .

(1-2-2. Gear flange 30)
As shown in FIG. 2, the gear flange 30 includes a cylindrical portion 31 having an outer peripheral surface 31a, and the above-described collar portion 32 formed on the first input/output gear 20 side of the cylindrical portion 31. As shown in FIG. The flange portion 32 has an end surface 32a on the cylindrical portion 31 side in the axial direction. Further, the gear flange 30 has a through hole 30 a around the axial centers of the columnar portion 31 and the collar portion 32 .

The outer peripheral surface 31a of the columnar portion 31 is fitted to the inner peripheral surface 13a of the stepped through hole 13 of the housing 10 with a spigot. Then, as described above, the end surface 32a of the flange 32 abuts the stepped surface 14 of the opposing stepped through hole 13, and the gear flange 30 is positioned in the axial direction. Thus, the gear flange 30 is fitted in the stepped through hole 13 provided in the bottom plate 11 of the housing 10 with a spigot so that it can rotate around the first input/output axis C1 of the first input/output rotary shaft 21 .

In this way, since the gear flange 30 is supported by the housing 10 by the spigot, the gear flange 30 can be easily positioned and can be stably rotated around the first input/output axis C1 when the gear flange 30 rotates.

Gear flange through-holes 32b through which the plurality of second bolts 16 are inserted are formed at predetermined positions on the outer peripheral edge of the flange 32 of the gear flange 30 in the same number as the female threads 15 so as to correspond to the female threads 15 described above. be done. The gear flange 30 is fixed to the housing 10 by screwing a plurality of second bolts 16 inserted through the gear flange flange through-holes 32 b into the internal threads 15 . Specifically, the gear flange 30 is sandwiched and fixed between the housing 10 and the screwed second bolt 16 head.

The second bolt 16 and the gear flange flange through-hole 32b constitute a second engagement state adjusting mechanism 80, which will be described in detail later. As shown in FIG. 3, the hole diameter of the gear flange collar portion through hole 32b (gear flange hole diameter) is ΦDa2, and the shaft diameter of the second bolt 16 (second bolt shaft diameter) is Φda2 (<ΦDa2). shall be As a result, the gear flange 30 is in a state where the tightening by the second bolt 16 is released from the housing 10, that is, in a release state where the gear flange 30 is not fixed to the housing 10, the gear flange hole diameter ΦDa2 of the gear flange collar portion through-hole 32b and the second The bolt 16 can rotate in the circumferential direction by the diameter difference (ΦDa2−Φda2) from the second bolt shaft diameter Φda2. At this time, the diameter difference (ΦDa2−Φda2) forms an adjustment margin for adjusting backlash set between gears, which will be described later.

Also, the first input/output rotary shaft 21 (and the first input/output gear 20) is rotatably supported in the through hole 30a of the gear flange 30 via a ball bearing Br1. Note that the gear flange 30 may be the motor flange of the motor M when the first input/output rotary shaft 21 is connected to the output shaft of the motor M as well as being the input shaft. As a result, there is no need to provide a new gear flange in addition to the motor flange, so miniaturization and cost reduction can be achieved.

(1-2-3. First rotating body support member 40)
The first rotor support member 40 is a member that rotatably supports the intermediate gear 50 . As shown in FIG. 1, the first rotating body support member 40 is positioned at a position offset by a predetermined distance L1 from the first input/output axis C1 of the first input/output rotary shaft 21 supported by the gear flange 30 (intermediate axis C2). ) are arranged and supported by the gear flange 30 so as to be capable of moving within a predetermined range in the radial direction (see FIG. 5A), which will be described later. The intermediate axis C2 is the same as the intermediate gear 50 axis.

Mainly, as shown in FIG. 2, the first rotating body support member 40 includes a flange portion 41 that abuts on an end surface 30c of the gear flange 30 at an end surface 41a, and a protrusion projecting leftward from the center portion of the flange portion 41 in FIG. and a columnar intermediate gear support portion 42 formed as follows. A plurality of (for example, six) stepped holes 42 a are formed in the outer edge of the flange portion 41 so as to penetrate the flange portion 41 in the circumferential direction. As shown in FIG. 4, among the stepped holes 42a, a small-diameter through hole (flange through hole 43) formed on the side of the gear flange 30 accommodates a shaft of a first bolt 44 formed with a first bolt shaft diameter φda1. part is inserted. At this time, the diameter of the flange through-hole 43 is ΦDa1 (>Φda1).

At predetermined positions of the flange 32 and the cylindrical portion 31 of the gear flange 30 corresponding to the flange through-holes 43, female threads 17 for screwing the first bolts 44 are provided in the same number as the flange through-holes 43. It is formed. A plurality of first bolts 44 inserted through the flange through-holes 43 are screwed onto the internal threads 17 , whereby the first rotor support member 40 is fixed to the gear flange 30 . Specifically, the first rotating body support member 40 is sandwiched and fixed between the gear flange 30 and the head of the first bolt 44 to which it is screwed.

In addition, as shown in FIG. 4, the first bolt 44 and the flange through-hole 43 constitute a first engagement state adjusting mechanism 60, which will be described in detail later. Although the details will be described later, as described above, when the first rotating body support member 40 is in the unlocked state in which the first bolt 44 is loosened and is not fixed to the gear flange 30, the first engagement state adjustment is performed. Using the mechanism 60, the gear flange 30 can be moved within a predetermined radial range (see FIG. 5A).

As described above, the flange through-hole 43 has a diameter of ΦDa1, and the first bolt 44 has a first bolt shaft diameter of Φda1 (<ΦDa1). As a result, in the unfixed state, the first rotating body support member 40 has a diameter difference (ΦDa1-Φda1) between the flange hole diameter ΦDa1 of the flange through-hole 43 and the first bolt shaft diameter Φda1 of the first bolt 44. , relative to the gear flange 30 in the radial direction. In other words, the diameter difference (ΦDa1−Φda1) forms an adjustment margin (movement amount within a predetermined range) for adjusting backlash set between gears, which will be described later.

The intermediate gear support portion 42 rotatably supports the inner circumferential surface of the intermediate gear 50 through a ball bearing Br2, which is an angular ball bearing, in a state in which the annular intermediate gear 50 is meshed with the first input/output gear 20. . However, at this time, the magnitude of the backlash between the meshed intermediate gear 50 and the first input/output gear 20 is natural. The intermediate gear 50 is rotatably supported by the first rotating body support member 40 and coaxial with the intermediate axis C2 of the intermediate gear support portion 42 .

(1-2-4. Intermediate gear 50)
As described above, the first bolt 44 is inserted through the stepped hole 42a of the flange portion 41 of the first rotor support member 40, and the first rotor support member 40 and the gear flange 30 are fixed by screwing. A plurality of through holes 51 are formed in the intermediate gear 50 so as not to interfere with the first bolt 44 and the driver.

(1-2-5. Second input/output gear 70)
As shown in FIG. 2, the second input/output gear 70 is supported by the bottom plate 11 of the housing 10 so as to be rotatable around the second input/output rotating shaft 71, and has at least one gear that meshes with the intermediate gear 50. group. In this embodiment, the second input/output gear 70 is composed of one gear. The second input/output gear 70 is connected to the second input/output rotary shaft 71 so as to be rotatable together. At this time, the second input/output rotary shaft 71 and the second input/output gear 70 may be connected by any means. Also, the addendum circle diameter ΦD2 of the second input/output gear 70 is larger than the addendum circle diameter ΦD1 of the first input/output gear 20 . The second input/output rotary shaft 71 is rotatably supported in a through hole 18 formed in the housing 10 via a ball bearing Br3.

The other end (the right side in FIG. 2) of the second input/output rotating shaft 71 can be connected to an output shaft or an input shaft of various devices. For example, when the output shaft of the motor M is connected to the other end of the first input/output rotary shaft 21, the rotational driving force (rotational torque) of the motor M is input to the first input/output gear 20, The power is transmitted from the input/output gear 20 to the second input/output gear 70 via the intermediate gear 50 . Therefore, the other end of the second input/output rotary shaft 71 is connected to an input shaft to which the transmitted rotational driving force (rotational torque) is input. On the other hand, when the input shaft of a predetermined device is connected to the other end of the first input/output rotary shaft 21, the output shaft of the predetermined device is connected to the other end of the second input/output rotary shaft 71. .

In the above, the second input/output rotary shaft 71 and the output shaft, or the second input/output rotary shaft 71 and the input shaft may be connected by any means (method). For example, the second input/output rotary shaft 71 and the output shaft or the input shaft may be integrally formed by the same shaft member.

(1-2-6. First engagement state adjusting mechanism 60)
The first meshing state adjusting mechanism 60 is mainly composed of the flange through hole 43 and the first bolt 44 as described above. The collar portion through-hole 43 is formed in the collar portion 41 of the first rotor support member 40 . The flange through-hole 43 is formed with a flange hole diameter ΦDa1. The first bolt 44 is inserted through the flange through-hole 43 and is formed with a first bolt shaft diameter Φda1 (<ΦDa1) smaller than the flange hole diameter ΦDa1 of the flange through-hole 43 screwed to the gear flange 30 .

Then, the first rotating body support member 40 can move by the diameter difference (ΦDa1-Φda1) between the flange hole diameter ΦDa1 of the flange through-hole 43 and the first bolt shaft diameter Φda1 (<ΦDa1) of the first bolt 44. As an adjustment margin within a predetermined range in the radial direction, adjustment is performed so that the first meshing state having a predetermined first backlash α1 (see FIG. 6) between the first input/output gear 20 and the intermediate gear 50 is achieved. (see FIG. 5A). A detailed adjustment method will be described later.

(1-2-7. Second engagement state adjusting mechanism 80)
The second meshing state adjusting mechanism 80 is configured by the gear flange collar portion through-hole 32b and the second bolt 16, as described above. The gear flange collar portion through-hole 32b is formed so as to penetrate the collar portion 32 of the gear flange 30 . The shaft portion of the second bolt 16 is formed with a second bolt shaft diameter Φda2 (<ΦDa2) smaller than the gear flange hole diameter ΦDa2 of the gear flange collar portion through-hole 32b.

Then, when the first rotating body support member 40 rotates, the diameter difference (ΦDa2−Φda2) between the gear flange hole diameter ΦDa2 of the gear flange flange through-hole 32b and the second bolt shaft diameter Φda2<ΦDa2) of the second bolt 16 is , as an adjustment allowance in the circumferential direction (rotational direction), a predetermined second backlash α2 (see FIG. 6) is adjusted to a second meshing condition (see FIG. 5B). A detailed adjustment method will be described later.

(1-3. Backlash adjustment method)
Next, a backlash adjustment method using the first mesh state adjusting mechanism 60 and the second mesh state adjusting mechanism 80 will be described. In addition, as a premise of the backlash adjustment method, only the first input/output gear 20 and the intermediate gear 50 are assembled at first, and the first input/output gear 20 and the intermediate gear 50 are meshed by chance, and the second The input/output gear 70 is preferably left unassembled.

Further, it is preferable that the first rotating body support member 40 and the gear flange 30 are not fixed and are in the unlocked state although the first bolt 44 and the second bolt 16 are inserted. In such a state, the method for adjusting the power transmission device 1 includes a first step S10, a second step S20, a third step S30, and a fourth step S40, as shown in the flowchart of FIG.

(1-3-1. First step S10)
In the first step S10 (first meshing state adjusting section), the first rotating body support member 40 (intermediate gear 50) is radially moved by the first meshing state adjusting mechanism 60, and the intermediate gear 50 and the first input/output gear are moved. 20 is adjusted to the first meshing state. Specifically, as shown in FIG. 5A, the operator moves the first rotating body support member 40 (intermediate gear 50) in the unlocked state in the radial direction, toward the first input/output gear 20, or in the first direction. It is moved away from the first input/output gear 20 . In this embodiment, the arrow A indicates the direction toward the first input/output gear 20 .

At this time, the first rotating body support member 40 (first input/output gear 20) is adjusted by the action of the above-described first mesh state adjusting mechanism 60 to change the flange hole diameter ΦDa1 of the flange through-hole 43 and the first bolt 44 to the diameter ΦDa1. It can be moved in the radial direction by a predetermined range corresponding to the diameter difference (ΦDa1−Φda1) from one bolt shaft diameter Φda1 (<ΦDa1). Then, the operator gradually moves the first rotating body support member 40 (and the first input/output gear 20) in the radial direction so that the backlash between the first input/output gear 20 and the intermediate gear 50 is set to a predetermined level. It is confirmed by, for example, a dial gauge whether or not the first backlash α1 of has been reached. After that, when the space between the first input/output gear 20 and the intermediate gear 50 reaches a predetermined first backlash α1, the radial movement of the first rotor support member 40 (and the intermediate gear 50) is stopped. Let

(1-3-2. Second step S20)
Next, in the second step S20 (first rotating body supporting member fixing portion), after the first step S10, the first rotating body supporting member 40 that supports the intermediate gear 50 while maintaining the first meshing state. is fixed to the gear flange 30. Specifically, the first rotating body support member 40 is fixed to the gear flange 30 by tightening the first bolt 44 .

At this time, the first rotor support member 40 supporting the intermediate gear 50 is supported by the gear flange 30 . The first input/output gear 20 is also supported by the gear flange 30 . Since the first input/output gear 20 and the intermediate gear 50 are thus supported by the same member (the gear flange 30), the adjusted first backlash α1 is easily maintained.

(1-3-3. Third step S30)
In the third step (second mesh state adjusting section), first, the second input/output gear 70 is assembled. Then, as shown in FIG. 5B, the gear flange 30 is rotated around the first input/output axis C1 by the second mesh state adjusting mechanism 80. As shown in FIG. As a result, the first input/output gear 20 and the intermediate gear 50, which are meshed on the gear flange 30 while the first meshing state is maintained, are rotated around the first input/output axis C1, and the intermediate gear 50 and the second input/output gear are rotated. The meshing state with 70 is defined as a second meshing state.

Specifically, as shown in FIG. 5B , the operator rotates the unlocked gear flange 30 (intermediate gear 50 ) in the circumferential direction (see arrow E) to approach the second input/output gear 70 . At this time, the gear flange 30 (intermediate gear 50) has a gear flange hole diameter ΦDa2 of the gear flange brim portion through-hole 32b and a second bolt shaft diameter Φda2 (<ΦDa2 ) can be rotated in the circumferential direction by a predetermined range corresponding to the diameter difference (ΦDa2−Φda2).

Then, the operator gradually rotates the gear flange 30 (and the intermediate gear 50) in the circumferential direction so that the backlash between the intermediate gear 50 and the second input/output gear 70 becomes a predetermined second backlash α2. For example, a dial gauge is used to confirm whether or not the When the backlash between the intermediate gear 50 and the second input/output gear 70 reaches a predetermined second backlash α2, the circumferential movement of the gear flange 30 (intermediate gear 50) is stopped.

In the third step S30, when rotating the gear flange 30, the second meshing state adjusting mechanism 80 further inserts a rod-shaped member whose tip end is fitted into the hole 33 of the gear flange 30 and whose remaining portion protrudes from the gear flange 30. You may prepare. Then, by hitting the remaining portion of the rod-shaped member with a hammer or the like to apply (input) a force in the circumferential direction of the gear flange 30 to the rod-shaped member, the gear flange 30 is rotated around the first input/output axis C1, and the intermediate gear 50 and the intermediate gear 50 are rotated. The second input/output gear 70 may be adjusted to the second meshing state. Moreover, in the third step S30, the second input/output gear 70 is assembled afterward, but the present invention is not limited to this, and the second input/output gear 70 may be assembled from the beginning. Since the second input/output gear 70 is assembled from the beginning, the adjustment in the first step S10 becomes somewhat difficult, but the same effect can be obtained.

(1-3-4. Fourth step S40)
Next, in a fourth step S<b>40 (gear flange fixing portion), the gear flange 30 in which both the first meshed state and the second meshed state are held is fixed to the housing 10 . Specifically, the gear flange 30 is fixed to the housing 10 by tightening the plurality of second bolts 16 .

At this time, the meshing state between the first input/output gear 20 and the intermediate gear 50 is the first meshing state, and the backlash is adjusted to the predetermined first backlash α1. Further, the meshing state between the intermediate gear 50 and the second input/output gear 70 is the second meshing state, and the backlash is adjusted to a predetermined second backlash α2. Both the first backlash α1 and the second backlash α2 are adjusted while being directly measured by the operator using a dial gauge. Therefore, its accuracy is very high. As described above, since the method is very simple, it can be manufactured at a low cost, and the accuracy of the first backlash α1 and the second backlash α2 is good in both the first meshed state and the second meshed state.

(1-4. Effects of First Embodiment)
According to the above-described first embodiment, the power transmission device 1 produces a predetermined first backlash between the first input/output gear 20 and the intermediate gear 50 by moving the first rotor support member 40 in the radial direction. A first meshing state adjustment mechanism 60 that is adjustable to a first meshing state having α1 and rotation of the gear flange 30 about the first input/output axis C1 causes a first meshing with the first input/output gear 20. a second mesh state adjusting mechanism 80 that can be adjusted so that a second mesh state having a predetermined second backlash α2 between the intermediate gear 50 in the state and the second input/output gear 70 is achieved.

With such a configuration, when the power transmission device 1 adjusts the backlash between the gears 20, 50, 70 from the first input/output gear 20 to the second input/output gear 70 to predetermined amounts, the First, the first backlash α1 between the first input/output gear 20 and the intermediate gear 50 is adjusted using the one-mesh state adjusting mechanism 60 . After that, apart from the adjustment of the first backlash α1, the second backlash α2 between the intermediate gear 50 and the second input/output gear 70 is adjusted.

For this reason, there is no possibility that the backlashes of the gears meshing with each other on both sides are simultaneously adjusted while moving one gear, and that the backlashes of the gears are interlocked with each other and changed each time the adjustment is performed. Therefore, the adjustment is easy, and the predetermined first backlash α1 and the predetermined second backlash α2 can be obtained in a short time with high precision. Since the first backlash α1 and the second backlash α2 can be obtained in a short time, it can be provided at low cost.

The first meshing state adjusting mechanism 60 includes a flange through-hole 43 formed in the flange 41 provided at the radially outer end of the first rotor support member 40 on the side of attachment to the gear flange 30 . and a first bolt 44 having a first bolt shaft diameter Φda1 smaller than the flange hole diameter ΦDa1 of the flange through-hole 43 and screwed to the gear flange 30 through the flange through-hole 43 . Then, the first rotating body support member 40 (intermediate gear 50) can move by the diameter difference (ΦDa1-Φda1) between the flange hole diameter ΦDa1 of the flange through-hole 43 and the first bolt shaft diameter Φda1 of the first bolt 44. As an adjustment margin in a predetermined range in the radial direction, adjustment is performed to achieve the first meshing state.

In this way, the radially movable range of the first rotating body support member 40 (intermediate gear 50) can be set by the shaft diameter of the first bolt 44 and the diameter of the flange through-hole 43, so that cost reduction can be achieved. . Further, since the radial movement of the first rotating body support member 40 can only be performed within the range of the diameter difference (ΦDa1−Φda1), the first rotating body supporting member 40 moves too much, and the first input/output gear 20 and the intermediate gear 50 can be well suppressed.

Further, in the above-described first embodiment, the second meshing state adjusting mechanism 80 includes the gear flange flange through-hole 32b formed in the gear flange 30, and the gear flange flange through-hole 32b that is screwed to the gear flange 30. a second bolt 16 formed with a second bolt shaft diameter Φda2 smaller than the gear flange hole diameter ΦDa2 of the through hole 32b. Then, the diameter difference (ΦDa2-Φda2) between the gear flange hole diameter ΦDa2 of the gear flange flange through-hole 32b and the second bolt shaft diameter Φda2 of the second bolt 16 is used as an adjustment allowance in the circumferential direction in which the gear flange 30 can rotate. Adjustment is performed so that the intermediate gear 50 and the second input/output gear 70, which are in the first meshing state with the one input/output gear 20, are in the second meshing state with the predetermined second backlash α2.

Thus, when the intermediate gear 50 and the second input/output gear 70 are adjusted to the second meshing state, the rotatable range of the gear flange 30 in the circumferential direction is the shaft diameter Φda2 of the second bolt 16 and the gear flange collar portion. Since it can be set by the gear flange hole diameter ΦDa2 of the through hole 32b, the cost can be reduced. In addition, since the gear flange 30 can only rotate within the range of the diameter difference (ΦDa2−Φda2) in the circumferential direction, it is preferable to prevent the intermediate gear 50 from colliding with the second input/output gear 70 due to excessive rotation of the gear flange 30. can be suppressed to Further, in the first embodiment, the second input/output gear is composed of one gear (the second input/output gear 70 ), and the second input/output gear 70 is connected to the second input/output rotating shaft 71 . As a result, the power transmission device 1 can be manufactured with a simple configuration.

<2. Second Embodiment>
In the above-described first embodiment, the second input/output gear is one, but the configuration is not limited to this. As shown in FIG. 8, as the power transmission device 1A of the second embodiment, the second input/output gear, which is a gear group, may be composed of two gears 70A and 70B. The power transmission device 1A of the second embodiment differs from the power transmission device 1 of the first embodiment only in the second input/output gear. Therefore, only different parts will be described in detail, and descriptions of other similar parts will be omitted. Also, the same configurations may be described with the same reference numerals.

In the above, the two gears of the second input/output gear provided in the power transmission device 1A are one second input/output gear 70A that meshes with the intermediate gear in the second meshing state, and one second input/output gear 70A. is the other second input/output gear 70B meshing in the third meshing state having a third backlash α3 (see FIG. 9).

The housing 10A supports a second input/output rotary shaft 71 to which the other second input/output gear 70B is connected so as to be rotatable around the second input/output axis C3 via a ball bearing Br4. In addition, the housing 10A has a third input/output axis C4 arranged at a position offset by a predetermined distance L2 from the second input/output rotary shaft 71, and the second input/output rotation shaft 71 is movable within a predetermined range in the radial direction. It supports the rotating body support member 40A.

The second rotor support member 40A may be supported by the housing 10A with the same structure as the first rotor support member 40 of the first embodiment. One second input/output gear 70A is rotatably supported by the second rotor support member 40A via a ball bearing Br5. As a result, the second rotor support member 40A (and one 70A) can move radially within a predetermined range in the unlocked state.

In addition, the power transmission device 1A moves the second input/output gear 70A on one side and the second input/output gear 70A on the other side by moving in the radial direction of the second rotor support member 40A that supports the second input/output gear 70A on one side. A third mesh state adjusting mechanism 90 is provided so that the mesh state with the gear 70B can be adjusted to a third mesh state having a predetermined third backlash α3.

In such a configuration, before adjusting the meshing state between the intermediate gear 50 and the one second input/output gear 70A to the second meshing state, the one second input/output gear 70A is adjusted by the third meshing state adjusting mechanism 90. and the other second input/output gear 70B to the third meshing state. After that, the second meshing state adjusting mechanism 80 adjusts the meshing state between the intermediate gear 50 and one of the second input/output gears 70A to the second meshing state. Thus, as in the first embodiment, the backlashes between all the gears can be adjusted to the desired first backlash α1-third backlash α3, so that the same effect as in the first embodiment can be obtained. In addition, the gear group of the second input/output gear is not limited to the above aspect, and more than two gears may be provided.

(2-1. Modified example 1 of the second embodiment)
In addition, in the second embodiment, the two second input/output gears 70A and 70B are both supported by the housing 10A. However, not limited to this aspect, as Modification 1, both the two second input/output gears 70A and 70B are rotatable in the housing 10A in the same manner as the first input/output gear 20 and the intermediate gear 50 in the first embodiment. It may be a mode supported by a gear flange (not shown) supported by. That is, the second input/output gears (second input/output gears 70A and 70B) may be supported by the housing 10A via gear flanges. At this time, the gear flange shall have the same structure as the gear flange 30 in the first embodiment.

In the above case, after adjusting the meshing state between the second input/output gear 70A on one side and the second input/output gear 70B on the other side to the third meshing state using the third meshing state adjusting mechanism 90, the gear flange 30 and Both the gear flanges of Modification 1 may be rotated to adjust the meshing state between the intermediate gear 50 and one of the second input/output gears 70A to the second meshing state. Thereby, the magnitude of the backlash between the intermediate gear 50 and one of the second input/output gears 70A can be adjusted more accurately.

(3. Turning Device of Machine Tool Equipped with Power Transmission Device 1)
Next, a turning device of a machine tool will be described as an example of a device to which the power transmission device 1 described in the first embodiment is applied. As shown in FIG. 10, the machine tool 100 is a five-axis machining center and mainly includes a bed 110, a column 120, a saddle 130, a swivel device 200, a slide table 140 and a turntable 150. Bed 110 is generally rectangular and is placed on the floor. A column 120 is erected on the bed 110 .

A saddle 130 is provided on the side surface of the column 120 so as to be movable in the X-axis direction. A swivel device 200 to which a spindle device 300 is attached is provided on a side surface of the saddle 130 so as to be movable in the Y-axis direction that coincides with the vertical direction. A slide table 140 is provided on the bed 110 so as to be movable in the Z-axis direction. A turntable 150 is provided on the slide table 140 so as to be rotatable around the Y axis (B axis). A workpiece (not shown) is fixed to the turntable 150 via a jig.

As shown in FIG. 11, the turning device 200 includes a turning shaft portion 210 (see FIG. 12) that constitutes a turning portion, a turning body portion 220, a fixed body portion 230, and a reduction mechanism portion 240. The speed reduction mechanism 240 internally includes the power transmission device 1 according to the first embodiment. The turning device 200 rotates the turning shaft portion 210 together with the turning body portion 220 with respect to the fixed body portion 230 . As a result, the turning device 200 can change the attitude (orientation of the rotation axis R) of the spindle device 300 from the horizontal direction (0 degrees) through the vertical direction (180 degrees) to a predetermined angle θ (for example, 210 degrees). Then, the spindle device 300 is rotated and indexed (not shown). The rotation angle of the swivel main body 220 (swivel shaft 210) is detected using, for example, a detector such as a rotary encoder having an encoder head and an encoder scale (not shown).

The swivel shaft portion 210 shown in FIG. 12 has a hollow cylindrical shape, and its upper end side is arranged inside the fixed main body portion 230 so that the swivel axis D is inclined at approximately 45 degrees with respect to the Z axis. A ring gear 210a is provided at the upper end of the turning shaft portion 210, as shown in FIG. and is rotatably supported.

The swivel body portion 220 is fixed to the lower end of the swivel shaft portion 210 so as not to be relatively rotatable, and is rotatable around the swivel axis D. As shown in FIG. As shown in FIG. 11, the main shaft device 300 rotates around the turning axis D of the turning shaft portion 210 in a state in which the rotation axis R of the main shaft 310 is inclined 45 degrees with respect to the turning axis D of the turning shaft portion 210 . provided as possible. Here, a rotary tool 320 is detachably attached to the tip side of the main shaft 310 , and a motor (not shown) for rotating the main shaft 310 is connected to the rear end side of the main shaft 310 .

The fixed body portion 230 is provided movably in the Y-axis direction with respect to the side surface of the saddle 130 . As shown in FIGS. 11 and 12, a motor as a driving source for generating a rotational driving force for rotating the turning shaft portion 210 and the turning body portion 220 around the turning axis D is installed inside the fixed body portion 230 . M is housed. The output shaft of the motor M is connected to the first input/output rotary shaft 21 of the first input/output gear 20 of the power transmission device 1 forming part of the speed reduction mechanism 240 . As shown in FIG. 11 , the first input/output gear 20 is provided so as to protrude from the side surface of the fixed body portion 230 and is housed inside the housing 10 .

The reduction mechanism portion 240 includes a rotating shaft portion 241 and the power transmission device 1 as an intermediate transmission portion. In the power transmission device 1, the first input/output rotary shaft 21 of the first input/output gear 20 is integrally connected to the output shaft of the motor M as described above. Also, the second input/output rotary shaft 71 of the second input/output gear 70 is integrally connected to the input shaft of the rotary shaft portion 241 included in the turning device 200 . At this time, the rotating shaft portion 241 is a rotating shaft portion such as a worm gear or a roller gear cam mechanism (see JP-A-2017-89663).

As shown in FIG. 12, the rotating shaft portion 241 is arranged so as to form a so-called offset shaft with respect to the ring gear 210a of the turning shaft portion 210. As shown in FIG. The rotating shaft portion 241 reduces the rotational speed of the second input/output gear 70 and transmits the rotational driving force to the ring gear 210 a of the turning shaft portion 210 .

As described in the first embodiment, the second input/output gear 70 meshes with the first input/output gear 20 connected to the output shaft of the motor M via the intermediate gear 50 . The second input/output gear 70 has a larger diameter than the first input/output gear 20, and reduces the rotation speed of the motor M (first input/output gear 20) via the second input/output rotating shaft 71. A rotational driving force is transmitted to the connected rotating shaft portion 241 . The second input/output rotary shaft 71 is integrally connected to the input shaft of the rotary shaft portion 241 so as to be coaxial with the rotary shaft portion 241 .

(3-1. Operation of machine tool 100)
Next, the machining operation of the machine tool 100 on the workpiece will be described. In this embodiment, a machining operation for drilling a hole in one side surface of a workpiece when the posture of the spindle device 300 (orientation of the rotation axis R) is in the horizontal direction (0 degrees) will be described.

The control device of the machine tool 100 rotates the turntable 150 to position the machining side of the workpiece on the rotating tool 320 side, and drives the motor for rotating the spindle 310 to rotate the rotating tool 320 . Then, the control device drives the motor M as a drive source to rotate the turning shaft portion 210 and the turning main body portion 220 to turn the spindle device 300, and determines the rotational phase of the rotary tool 320 to be 0 degrees. Subsequently, the control device moves the saddle 130, the swivel device 200 and the slide table 140 in the X, Y, and Z axial directions, respectively, and starts machining to drill a hole in one side of the workpiece.

In this case, when the revolving device 200 rotates the attitude (orientation of the rotation axis R) of the spindle device 300, the rotational driving force generated by the motor M is transmitted to the revolving shaft portion 210 via the reduction mechanism portion 240. be. That is, in the reduction mechanism portion 240, the second input/output gear 70 of the power transmission device 1 reduces the rotational speed of the first input/output gear 20 via the intermediate gear 50 (first stage reduction). The second input/output gear 70 is coaxially connected to the input shaft of the rotating shaft portion 241 via the second input/output rotating shaft 71 . As a result, the rotary shaft portion 241 rotates at the same rotational speed as the second input/output gear 70 .

The rotating shaft portion 241 meshes with the ring gear 210 a of the turning shaft portion 210 . Therefore, the rotation speed of the rotating shaft portion 241 is reduced and transmitted to the ring gear 210a (second stage reduction). In this way, the rotational speed of the motor M (first input/output gear 20) is reduced through the first stage reduction by the power transmission device 1 and the second stage reduction by the rotary shaft portion 241, and the ring gear 210a of the turning shaft portion 210 rotates. transmitted. As a result, the speed reduction mechanism portion 240 can transmit a rotational driving force (torque) that is inversely proportional to the speed reduction to the turning shaft portion 210 . By applying the low-cost power transmission device 1 to the turning device 200 in this manner, the machine tool 100 can also be manufactured at low cost.

It should be noted that the power transmission device 1 of the first embodiment is applied to the turning device 200 in the description. However, the power transmission device 1A of the second embodiment or the power transmission device according to Modification 1 of the power transmission device 1A may be applied to the turning device 200 . Also by this, the same effect as the power transmission device 1 of the first embodiment can be obtained.

Power transmission device 10.10A Housing 16 Second bolt 20 First input/output gear 21 First input/output rotary shaft 30 Gear flange 32b Gear flange through hole 40 first rotating body supporting member 40A; second rotating body supporting member 42; intermediate gear support portion 43; flange through hole 44; first bolt 50; Second input/output gear 70A One second input/output gear 70B The other second input/output gear 71 Second input/output rotary shaft 80 Second mesh adjustment mechanism 90 Three-engage state adjusting mechanism 100; machine tool 200; turning device M; motor S10; first step S20; second step S30; third step S40; fourth step α1; first backlash , α2: second backlash, α3: third backlash, ΦDa1: flange hole diameter, Φda1: first bolt shaft diameter, ΦDa2: gear flange hole diameter, Φda2: second bolt shaft diameter.

Claims (9)

a housing;
a first input/output gear coupled to a first input/output rotary shaft having a first input/output axis;
an intermediate gear arranged on an intermediate axis offset by a predetermined distance from the first input/output axis and meshing with the first input/output gear;
a second input/output gear, which is a gear group comprising at least one gear rotatably supported by the housing and meshing with the intermediate gear;
a gear flange that rotatably supports the first input/output rotary shaft and is supported by the housing so as to be rotatable about the first input/output axis;
a first rotating body support member arranged coaxially with the intermediate axis to rotatably support the intermediate gear and supported by the gear flange so as to allow movement within a predetermined range in the radial direction;
A first meshing state having a predetermined first backlash between the first input/output gear and the intermediate gear can be achieved by moving the first rotating body support member in the radial direction. a meshing state adjustment mechanism;
By rotating the gear flange about the first input/output axis, a predetermined gap between the intermediate gear and the second input/output gear adjusted to the first meshing state with the first input/output gear a second mesh adjustment mechanism that is adjustable to a second mesh condition having a second backlash;
A power transmission device. 2. The power transmission device according to claim 1, wherein said gear flange is fitted to said housing with a spigot. The first mesh state adjusting mechanism is
a brim portion through hole formed in a brim portion provided at an end portion of the first rotating body support member on a mounting side to the gear flange;
a first bolt inserted through the flange through-hole and screwed to the gear flange and formed with a first bolt shaft diameter smaller than the flange hole diameter of the flange through-hole;
The difference in diameter between the flange hole diameter of the flange through-hole and the first bolt shaft diameter of the first bolt is adjusted within the predetermined range in the radial direction in which the first rotating body support member can move. 3. The power transmission device according to claim 1 or 2, wherein the adjustment is performed to bring the first meshing state as described above. The second mesh state adjustment mechanism is
a gear flange through-hole formed in the gear flange;
a second bolt that is inserted through the gear flange brim through-hole and screwed onto the gear flange, and is formed with a second bolt shaft diameter that is smaller than the gear flange hole diameter of the gear flange brim through-hole;
The difference in diameter between the gear flange hole diameter of the gear flange flange through-hole and the second bolt shaft diameter of the second bolt is used as an adjustment margin in the circumferential direction in which the gear flange can rotate, and is adjusted to achieve the second meshing state. 4. The power transmission device according to any one of claims 1 to 3, wherein: the first input/output rotary shaft is both an input shaft and an output shaft of a motor;
wherein the gear flange is a motor flange of the motor;
The power transmission device according to any one of claims 1-4. 6. The power transmission device according to claim 1, wherein said second input/output gear is composed of one gear, and said second input/output gear is connected to a second input/output rotary shaft. The second input/output gear is composed of two gears,
The two gears are
One second input/output gear that meshes with the intermediate gear in the second meshing state, and the other second input gear that meshes with the one second input/output gear in a third meshing state having a predetermined third backlash. is the output gear,
The housing is
The second input/output rotary shaft to which the other second input/output gear is connected is rotatably supported around the second input/output axis, and the third input/output rotary shaft is offset from the second input/output rotary shaft by a predetermined distance. supporting a second rotating body support member on which an output axis is arranged and capable of moving within a predetermined range in the radial direction;
The power transmission device
The one second input/output gear is supported in a state before the second meshing state adjusting mechanism adjusts the meshing state between the intermediate gear and the second input/output gear to the second meshing state. A third meshing state in which the predetermined third backlash exists between the one second input/output gear and the other second input/output gear due to the radial movement of the second rotor support member. 6. The power transmission device according to any one of claims 1 to 5, further comprising a third mesh state adjusting mechanism that can be adjusted so that A turning device for a machine tool comprising the power transmission device according to claim 6 or 7,
The power transmission device
A turning device for a machine tool, wherein the second input/output rotary shaft of the second input/output gear is connected to an input shaft of a speed reducer included in the turning device. A method for adjusting a power transmission device according to any one of claims 1 to 7,
a first step of moving the intermediate gear in the radial direction by the first mesh state adjusting mechanism to adjust the mesh state between the intermediate gear and the first input/output gear to the first mesh state;
a second step of fixing, to the gear flange, the first rotating body support member supporting the intermediate gear while maintaining the first meshing state after the first step;
By rotating the gear flange by the second meshing condition adjusting mechanism, the first input/output gear and the intermediate gear meshing in the first meshing condition on the gear flange are rotated around the first input/output axis, and a third step of setting the meshing state between the intermediate gear and the second input/output gear to the second meshing state.

Images