JP2010058146A - Drawing apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drawing apparatus including a mechanism for controlling rotational phase difference of a spindle and a camshaft, which has a simple structure and causes few breakages and troubles. <P>SOLUTION: The drawing apparatus 1 includes: a drawing roller mount 15 movably supporting a drawing roller R in a radial direction at the tip of the spindle 10; and a cam plate 22 moving the drawing roller R in the radial direction by the relative rotational phase difference of the spindle 10 and the camshaft 24 at the tip of the camshaft 24 arranged to be coaxial with the spindle 10 in the spindle 10. In the drawing apparatus, at least one of the drive mechanisms of the spindle 10 and the camshaft 24 is configured of a numerically controlled motor SM, the rotation of the spindle 10 and the camshaft 24 is transmitted to a planetary gear mechanism 50, the rotational phase difference of the spindle 10 and the camshaft 24 is detected using a rotational phase difference detection means E arranged at the planetary gear mechanism 50, and drawing is carried out by controlling the numerically controlled motor SM based on a detected detection value. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a drawing apparatus, and more particularly to a drawing apparatus that performs drawing by moving a drawing roller attached to the tip of a rotating main shaft in a radial direction.

  Conventionally, as a drawing device for drawing, a drawing roller is supported on a drawing roller mounting base attached to the tip of a rotating spindle so that the drawing roller can be moved in the radial direction, and a cylindrical member such as a pipe to be processed by the drawing roller. There has been proposed a drawing apparatus in which a drawing process is performed (see, for example, Patent Document 1).

  As shown in FIGS. 4 to 7, the drawing device 1 ′ includes a main shaft mechanism 2 ′ and a support mechanism 3 that supports the pipe P to be processed so as to face the main shaft mechanism 2 ′. The spindle housing 11 of the mechanism 2 ′ is configured to be movable in the L direction shown in FIG. 4 by a drive motor 6 and a drive screw 7 on a guide rail 5 formed on the base 4.

  The main shaft mechanism 2 ′ is driven by a driving pulley 13 connected to a suitable driving motor (not shown), and is provided at a main shaft 10 supported by a main shaft housing 11 via a bearing 12 and at the tip of the main shaft 10. And a squeeze roller mounting base 15.

The squeezing roller mounting base 15 is attached to the tip of the main shaft 10 via a flange 16 and includes a main mounting base 20 having a guide groove 18 for guiding the support member 17 of the squeezing roller R in the radial direction, and the squeezing roller R. A cam plate 22 having a spiral groove 21 for moving in the radial direction is mainly used.
The support member 17 of the tool is provided with a guide pin 23 that enters into the spiral groove 21 to move the squeeze roller R in the radial direction.

  The main shaft 10 has a hollow structure, and a cam shaft 24 having a cam plate 22 attached to the tip thereof is disposed in the main shaft 10. The main shaft 10 and the cam shaft 24 are engaged via a speed change mechanism 30, and at an initial position. The squeezing roller R located at the position shown in FIG. 6 is moved in the radial direction to the position shown in FIG. A predetermined drawing process (for example, a diameter reduction process) is applied to the tip.

  The mandrel 40 inserted into the pipe P to be processed is disposed at the tip of a shaft 41 disposed in the cam shaft 24, and can be advanced and retracted in the axial direction of the main shaft 10 by an advancing / retreating cylinder (not shown). It is attached.

By the way, the conventional drawing apparatus 1 ′ uses a flexure-meshing type drive transmission device for the speed change mechanism 30.
As shown in FIGS. 5 and 8, the flexure mesh drive transmission device used in the speed change mechanism 30 includes a pair of outer rings 31, 32 engaged with the main shaft 10 and the cam shaft 24, respectively. A flexible tooth wheel 33 that meshes with a tooth groove formed on the inner surface of the outer ring (both have the same number of teeth) and has a tooth shape with a different number of teeth, the tooth wheel 33 in an elliptical shape, and It comprises a wave forming ring 34 that is rotatably supported and meshes at two locations facing the tooth gap.

  In the speed change mechanism 30, when the wave forming wheel 34 is fixed and one outer ring 31 is driven, the tooth wheel 33 is rotated following the rotation, and the other outer ring 32 is also rotated via the tooth wheel 33. The At this time, the number of teeth of both the outer rings 31 and 32 is the same, and therefore, they are rotated at the same number of rotations.

On the other hand, the number of teeth of the tooth wheel 33 is usually smaller than that of the outer rings 31 and 32 (for example, two fewer).
Then, the outer ring 31 is fixed and the wave forming ring 34 is rotated. Reference numeral 35 denotes a drive reduction motor.
Accordingly, by rotating the wave forming ring 34 while rotating the outer ring 31, the relative rotational speed of the other outer ring 32 with respect to the outer ring 31 varies. The variable rotational speed is proportional to the rotational speed of the wave forming wheel 34.
In this way, differential rotation is performed by the flexibly meshing drive transmission device.

In FIG. 8, 36 is a support gear for the outer ring 31, 37 is a support gear for the outer ring 32, 38 is a drive gear that is attached to the main shaft 10 and meshes with the support gear 36, and 39 is a driven gear that meshes with the support gear 37.
As a result, a relative rotational speed difference between the outer ring 32 and the outer ring 31, more specifically, a rotational phase difference occurs between the main shaft 10 and the cam shaft 24, and the cam plate 22 is connected to the squeeze roller mounting base via the cam shaft 24. 15, the squeezing roller R can be moved in the radial direction, and the tip of the pipe P for processing fixed to the support mechanism 3 can be drawn.

Japanese Patent No. 3514730

  By the way, the transmission mechanism 30 has to form internal gears on both the outer rings 31 and 32 and to form an elliptical external gear on the toothed wheels 33, and the mechanism is complicated and power is transmitted via the transmission mechanism 30. Therefore, there is a problem that it is easy to cause damage or failure due to its structure.

  In view of the problems of the above-described conventional drawing device, the present invention is a mechanism for controlling the rotational phase difference between the main shaft and the camshaft, which has a simple structure and is less likely to cause damage or failure. It aims at providing the drawing processing apparatus which becomes.

  In order to achieve the above object, the drawing apparatus of the present invention is provided with a drawing roller mounting base that supports the drawing roller so as to be movable in the radial direction at the tip of the main shaft, and is arranged coaxially with respect to the main shaft. In a drawing apparatus equipped with a cam plate that moves the squeezing roller in the radial direction by the relative rotational phase difference between the main shaft and the cam shaft at the tip of the cam shaft provided, at least one of the drive mechanism of the main shaft and the cam shaft is a numerical value Consists of a controlled motor that transmits the rotation of the main shaft and cam shaft to the planetary gear mechanism, and detects and detects the rotational phase difference between the main shaft and the cam shaft using the rotational phase difference detection means provided in the planetary gear mechanism. It is characterized in that the numerical control type motor is controlled based on the detected value to perform the drawing process.

  In this case, the drive mechanism for the main shaft and the cam shaft can be constituted by a numerically controlled motor.

  Further, the rotational phase difference of the rotating shaft of the motor constituting the drive mechanism for the main shaft and the cam shaft can be detected by the rotational phase difference detecting means.

According to the drawing apparatus of the present invention, at least one of the drive mechanism of the main shaft and the cam shaft is constituted by a numerically controlled motor, the rotation of the main shaft and the cam shaft is transmitted to the planetary gear mechanism, and the rotation of the main shaft and the cam shaft is performed. By detecting the phase difference using the rotational phase difference detection means provided in the planetary gear mechanism and controlling the numerically controlled motor based on the detected value to perform the drawing process, the spindle and the camshaft Since the planetary gear mechanism used for controlling the rotational phase difference does not need to transmit power only by detecting the rotational phase difference, the planetary gear mechanism is unlikely to be damaged or broken down and can be a durable device.
In this case, when transmitting the rotation of the main shaft and the cam shaft to the two shafts of the planetary gear mechanism, the speed is changed so that the remaining one shaft of the planetary gear mechanism stops when the rotation speeds of the main shaft and the cam shaft are the same. Therefore, it is possible to provide a drawing device that can easily and easily detect the rotational phase difference.

  Further, by configuring the drive mechanism of the main shaft and the cam shaft with a numerical control type motor, it is possible to accurately control the rotational speeds of both the main shaft and the cam shaft.

  Further, by detecting the rotational phase difference of the rotating shaft of the motor constituting the driving mechanism of the main shaft and the cam shaft by the rotational phase difference detecting means, as required between the rotating shaft of the motor and the main shaft and the cam shaft. Since the numerically controlled motor can be controlled using the rotational phase difference of the motor that drives the main shaft and the camshaft before being decelerated by the interposed reducer, the drawing can be performed with high accuracy.

  Embodiments of a drawing apparatus according to the present invention will be described below with reference to the drawings.

  1 to 3 show an embodiment of the drawing apparatus of the present invention.

  The drawing apparatus 1 includes a drawing roller mounting base 15 that supports the drawing roller R so as to be movable in the radial direction at the tip of the main shaft 10 as in the conventional example, and the main shaft 10 is coaxial with the main shaft 10. And a cam plate 22 for moving the squeezing roller R in the radial direction by the relative rotational phase difference between the main shaft 10 and the cam shaft 24. A rotational position in which at least one is constituted by a numerically controlled motor SM, the rotation of the main shaft 10 and the cam shaft 24 is transmitted to the planetary gear mechanism 50, and the rotational phase difference between the main shaft 10 and the cam shaft 24 is arranged in the planetary gear mechanism 50. By performing detection using the phase difference detection means E and controlling the numerically controlled motor SM based on the detected value, the rotational phase difference between the main shaft 10 and the camshaft 24 is set to a predetermined value to perform drawing processing. It is to Migihitsuji.

At least one of the drive mechanisms for the main shaft 10 and the cam shaft 24 may be a numerically controlled motor SM.
By the way, since the drive mechanism of the main shaft 10 is larger than the drive mechanism of the cam shaft 24, it is preferable in terms of cost that the drive mechanism of the cam shaft 24 is a numerically controlled motor SM.
In this case, the drive mechanism of the main shaft 10 is not particularly limited, and various motors such as an inverter motor can be used.

  The main shaft 10 and the cam shaft 24 are connected to the timing pulleys 8a and 8b of the motor IM and the numerically controlled motor SM via timing pulleys 9a and 9b, respectively.

 The numerically controlled motor SM is not particularly limited, but in the present embodiment, a servo motor is used.

  The servo motor is a motor whose rotation speed is proportional to the frequency of the command pulse transmitted from the control mechanism S and whose motor rotation angle is proportional to the number of output pulses of the command pulse. By defining the amount, it can be rotated to a position proportional to the number of pulses of the pulse train, and the pulse frequency becomes the number of rotations (rotational speed) of the motor, so that it can be easily determined for the other motor IM Thus, a predetermined rotational phase difference can be provided between the main shaft 10 and the camshaft 24.

  In addition, both the drive mechanism of the main shaft 10 and the cam shaft 24 can be configured by a numerically controlled motor SM, whereby the rotational speed control of both the main shaft 10 and the cam shaft 24 can be accurately performed.

In the drawing apparatus 1, the control mechanism S causes the main shaft 10 and the camshaft 24 to correspond to the feed speed and feed amount in the X-axis direction (see FIG. 2) of the drawing roller R preset in the control mechanism S. The cam shaft 24 has a rotational phase difference (in this specification, the “rotational phase difference” includes a rotational phase difference corresponding to the feed amount and a rotational phase difference speed corresponding to the feed rate). The rotational speed of the numerically controlled motor SM, which is the drive mechanism of the motor, is controlled, the detected value of the rotational phase difference between the main shaft 10 and the camshaft 24 detected by the rotational phase difference detecting means E is transmitted to the control mechanism S, and feedback control is performed. While performing, the rotational phase difference between the main shaft 10 and the cam shaft 24 is set to a predetermined set value.
In the present embodiment, the motor IM that is a drive mechanism of the main shaft 10 is controlled by the control mechanism S so as to be driven at a constant rotation.

  The control mechanism S controls the rotational phase difference between the main shaft 10 and the cam shaft 24 and also controls the drive motor 6 for moving the main shaft mechanism 2 in the L direction shown in FIG. Yes.

As shown in FIG. 3, the planetary gear mechanism 50 has a known structure including a sun gear 51, an outer ring gear 52, and a planetary gear 53, and includes a sun shaft 51 a that rotatably supports the sun gear 51 and an outer ring gear 52. The rotation of the main shaft 10 and the camshaft 24 is transmitted to two of the three shafts of the outer shaft 52a that is rotatably supported and the carrier shaft 54a that rotatably supports the carrier 54 in which the planetary gear 53 is rotatably disposed. Then, when the rotational speeds of the main shaft 10 and the camshaft 24 are the same, the remaining one shaft is shifted and transmitted.
As a result, the rotational phase difference can be detected easily and simply.
The rotation of the main shaft 10 and the cam shaft 24 is transmitted to the two shafts of the planetary gear mechanism 50 without changing the speed so that the remaining one shaft rotates when the rotation speed of the main shaft 10 and the cam shaft 24 is the same. This rotational speed can also be used as a detection value.

In addition, it is not particularly limited to which axis of the planetary gear mechanism 50 the rotation of the main shaft 10 and the cam shaft 24 is transmitted. In this embodiment, the numerical control that is the drive mechanism of the cam shaft 24 is performed on the carrier shaft 54a. In addition to transmitting the rotation directly from the drive shaft of the motor SM, the timing pulley 52b formed on the outer ring shaft 52a and the timing pulley 8c fitted to the drive shaft of the motor IM which is the drive mechanism of the main shaft 10 are connected by a timing belt. I have to.
In this case, for example, when the number of teeth of the sun gear 51, the outer ring gear 52, and the planetary gear 53 is a, b, and c, respectively, the rotation number of the carrier shaft 54a / the rotation number of the outer ring shaft 52a = b / (a + b). Since the sun shaft 51a is stopped, the ratio of the timing pulley 52b and the timing pulley 8c is set to b: (a + b) to transmit the rotation of the drive shaft of the motor IM.
The connection between the outer ring shaft 52a and the drive shaft of the motor IM can be performed through a gear mechanism, for example, in addition to using a timing pulley and a timing belt.

The rotation phase difference detection means E has a function of detecting the rotation angle of the remaining one shaft (the sun gear 51 in this embodiment) that does not transmit the rotation of the main shaft 10 and the cam shaft 24 of the planetary gear mechanism 50. However, in this embodiment, a rotary encoder capable of measuring the rotation angle and rotation position of the shaft is used.
As described above, in this embodiment, the rotation of the cam shaft 24 is transmitted to the carrier shaft 54a, the rotation of the main shaft 10 is transmitted to the outer ring shaft 52a, and the rotation angle of the sun gear 51 is detected by the rotation phase difference detection means E. However, the shaft of the planetary gear mechanism 50 that transmits the rotation of the main shaft 10 and the camshaft 24 can be arbitrarily selected by appropriately selecting the gear ratio and the rotation direction when transmitting the rotation. Then, the rotational phase difference detecting means E is arranged on the remaining one shaft that does not transmit the rotation of the main shaft 10 and the cam shaft 24 of the planetary gear mechanism 50.

A description will be given of a method of drawing the tip of the workpiece pipe P supported by the support mechanism 3 in the above configuration.
First, in the initial state where the main shaft 10 and the cam shaft 24 are rotated without moving the squeezing roller R in the radial direction of the squeezing roller mounting base 15, the main shaft 10 and the cam shaft 24 are synchronously rotated at the same rotational speed, for example, 500 to 700 rpm. In addition, the control mechanism S controls the motor IM that is the drive mechanism of the main shaft 10 and the numerically controlled motor SM that is the drive mechanism of the cam shaft 24, while rotating the drive motor 6 via the drive screw 7. Is moved in the L direction (right direction) shown in FIG.

When the squeezing roller R reaches an appropriate position with respect to the peripheral surface of the pipe P to be processed, the cam plate 22 is moved to the main mounting base 20 in order to move the squeezing roller R in the radial direction of the squeezing roller mounting base 15. The rotation speed of the numerically controlled motor SM, which is the drive mechanism of the camshaft 24, is determined by a command pulse transmitted from the control mechanism S so as to rotate at a predetermined angle (for example, in a range of −90 degrees to +90 degrees). The squeezing roller R is moved to a predetermined position in the radial direction of the squeezing roller mounting base 15.
At this time, the rotational phase difference detecting means E detects the rotational phase difference between the main shaft 10 and the camshaft 24 and feeds back the detected value to the control mechanism S, whereby the squeezing roller R is moved in the radial direction of the squeezing roller mounting base 15. It can be accurately positioned at a predetermined position.
Then, the main shaft mechanism 2 is moved in the L direction (left direction) shown in FIG. 1 while the squeezing roller R is moved in the radial direction of the squeezing roller mounting base 15 and brought into contact with the peripheral surface of the pipe P to be processed. Thus, a predetermined drawing process (for example, a diameter reduction process) is applied to the tip of the pipe P to be processed.

  The drawing apparatus of the present invention has been described based on the embodiments thereof. However, the present invention is not limited to the configurations described in the above embodiments, and the configuration is appropriately changed without departing from the spirit of the present invention. Is something that can be done.

  In the drawing apparatus of the present invention, the mechanism for controlling the rotational phase difference between the main shaft and the camshaft and the power mechanism are separate mechanisms, the structure is simple, and there is little damage or failure. For this reason, it can be suitably used for high-load drawing devices or drawing devices that require continuous operation.

1 is an overall view showing an embodiment of a drawing apparatus of the present invention. It is a partial cross section figure which shows the spindle mechanism used for the drawing apparatus. It is explanatory drawing of the planetary gear mechanism used for the drawing apparatus, (a) is a side sectional view of a partly cutout, and (b) is an XX sectional view in (a). It is a general view which shows the conventional drawing apparatus. It is a partial cross section figure which shows the spindle mechanism used for the conventional drawing apparatus. It is a top view which shows the initial state of the tool mounting base for drawing. It is a top view which shows the movement state of the tool mounting base for drawing. It is explanatory drawing of the transmission mechanism used for the conventional drawing processing apparatus, (a) is a front view (X1-X1 sectional drawing in (b)) of a transmission mechanism, (b) is YY sectional drawing in (a), (C) is explanatory drawing of a speed change effect | action.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Drawing apparatus 2 Main shaft mechanism 10 Main shaft 15 Diaphragm roller mounting base 20 Main mounting base 22 Cam plate 24 Cam shaft 50 Planetary gear mechanism E Rotational phase difference detection means IM motor S control mechanism SM Numerical control type motor

Claims (3)

  A squeezing roller mounting base is provided at the tip of the main shaft so as to support the squeezing roller so as to be movable in the radial direction. In a drawing apparatus provided with a cam plate that moves the squeezing roller in the radial direction by a rotational phase difference, at least one of the drive mechanism of the main shaft and the cam shaft is constituted by a numerically controlled motor, and the rotation of the main shaft and the cam shaft is performed. Transmission to the planetary gear mechanism, the rotational phase difference between the main shaft and the camshaft is detected using the rotational phase difference detection means provided in the planetary gear mechanism, and the numerically controlled motor is controlled based on the detected value to perform drawing. Drawing apparatus characterized by performing the above.   2. The drawing apparatus according to claim 1, wherein the drive mechanism for the main shaft and the cam shaft is constituted by a numerically controlled motor. 3. The drawing apparatus according to claim 1, wherein a rotation phase difference between rotation shafts of motors constituting a drive mechanism for the main shaft and the cam shaft is detected by a rotation phase difference detection means.

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