JPH0630863Y2 - Independent lifting device for bobbin rail in roving machine - Google Patents

Description

TECHNICAL FIELD The present invention relates to a single lifting device for bobbin rails in a roving frame.

Conventional technology Conventionally, in a roving machine that inputs a speed increment input from the bottom cone drum to the differential gear mechanism in order to make a speed difference between the rotation of the bobbin wheel and the rotation of the flyer, the rotation of the bottom cone drum is Further, it is transmitted to the lifter shaft via a bevel gear for switching up and down of the bobbin rail and a gear train. A differential gear mechanism is interposed in a gear train between the bevel gear and the lifter shaft, and a bobbin rail lifting motor is meshed with the differential gear mechanism (JP-A-60-9920).

According to the above, since the bobbin rail raising / lowering motor is installed only for raising / lowering the bobbin rail, the bobbin rail raising / lowering motor is not used in any other case and is used together with a large differential gear mechanism. Occupancy rate was not high.

Also, instead of the cone drum, a variable speed motor is provided separately from the main motor, and the rotation of this variable speed motor and the rotation of the main motor are combined and transmitted to the bobbin shaft. There is one that is connected to a lifter rack through an elevator switching gear device (Japanese Patent Laid-Open No. 63-264923).

According to Japanese Patent Laid-Open No. 63-264923, when the variable speed motor is driven, the lifter rack is moved up and down, and the differential gear mechanism is rotated to rotate the bobbin. That is, in order to raise / lower the bobbin rail independently, it is necessary to connect the dedicated motor for raising / lowering the bobbin rail via the differential gear mechanism as described above.

The subject of this invention is to solve such a problem.

Means for Solving the Problems In order to solve the above problems, the present invention combines a rotation of a main motor that drives a draft part and a rotation of a control motor that can independently change bobbin rotation, and transmits the combined rotation to a bobbin shaft. In a roving machine that includes a differential gear mechanism, and the control motor is linked to a lifter rack through an up-and-down switching gear device so as to drive a bobbin rail up and down, a transmission system from the control motor to the differential gear mechanism. Alternatively, the clutch is interposed in the middle of the transmission system from the differential gear mechanism to the bobbin rotating shaft.

Action According to the above, for example, when the roving bobbin is fully doffed, the clutch is disconnected and only the control motor is rotated to raise and lower only the lifter rack.

Embodiment FIG. 1 shows a main motor 1 to a belt transmission mechanism 2
The driving shaft 3 is rotationally driven via the drive shaft 3, and the front roller 8 of the draft part 7 is rotationally driven from the driving shaft 3 via the gear train 5 incorporating the twist change gear 4 and the belt transmission mechanism 6. . Further, the top shaft 10 is driven from the driving shaft 3 via the belt transmission mechanism 9, and the drive gear 11 integrated with the top shaft 10 is connected to the flyer 1.
The flyer 12 is driven to rotate at a constant speed by meshing with the upper driven gear 13.

On the other hand, a bobbin shaft 23 integrally fixed with a gear 22 that meshes with a bobbin wheel 21 rotatably supported on the bobbin rail 20 has a connecting shaft 2 via a universal joint 24.
It is connected with 5. Gear 26 integrated with this connecting shaft 25
Mesh with the output gear 31 of the differential gear mechanism 30. The external gear 32 of the differential gear mechanism 30 meshes with the gear 14 at the end of the driving shaft 3. One clutch plate of the electromagnetic clutch 34 is integrally connected to the input shaft 33 of the differential gear mechanism 30, and the other clutch plate is a servo motor that independently controls the rotation of the bobbin wheel 21 by the control device 100 described later. (Digital control motor) S
It is adapted to rotate with M via a belt transmission mechanism 35. Therefore, when the electromagnetic clutch 34 is connected, the constant speed rotation of the driving shaft 3 and the controlled rotation of the servo motor SM are combined by the differential gear mechanism 30, and the flyer rotation is speeded up by the controlled rotation of the servo motor SM. The bobbin wheel 21 to rotate the roving R to the bobbin 1
It is rolled up to 5.

Next, as shown in FIG. 2, the up-and-down switching gear device 40 of the bobbin rail 20 connects the two drive gears 42 and 43 with different numbers of teeth, which are connected to the transmission shaft 41 rotated by the servo motor SM, to the gear box. It is provided in 44. In the gear box 44, around the left and right support shafts 45, 46,
Driven gears 47, 47 facing the drive gears 42, 43, respectively
48 is rotatably supported. Large diameter drive gear 42
Is directly meshed with a large-diameter driven gear 47 facing this,
The small-diameter drive gear 43 is a small-diameter driven gear 4 which faces the small-diameter drive gear 43.
8 and the intermediate gear 49, and the number of teeth of each of these gears is set so that the two driven gears 47 and 48 rotate in the opposite directions at the same rotation speed. Two driven gears 4
A switching rod 50 slidably supported in the axial direction about the support shafts 45 and 46 is provided between 7 and 48, and
A switching wheel 51 is integrally fixed in the axial direction. Switching wheel 51 and the two driven gears 47, 4
8, a mountain-shaped meshing tooth 52 is provided on the entire circumference, and the switching wheel 51 drives the driven gears 47, 48.
By engaging with either one of the meshing teeth 52, the rotation direction of the switching wheel 51 is reversed. A transmission gear 53 having a wide tooth width is integrally fixed to the outer circumference of the switching wheel 51. From the transmission gear 53 through the gear train 54 to the shaft 5
5 is rotated (FIG. 1), and the pinion 58 of the lifter shaft 57 is rotated forward and backward via the gear train 56 to move the lifter rack 59 integrally fixed to the bobbin rail 20 up and down.

Next, the switching drive device 60 for moving the switching rod 50 back and forth in the axial direction will be described. As shown in FIG. 3, bearing bushes 62 are fixed to both sides of the box-shaped body 61 so as to face each other. The bearing bush 62 has a locking body 65, which will be described later.
A switching shaft 64 that constitutes the switching shaft body 63 is supported slidably in the axial direction. One end (the left side in FIG. 3) of the switching shaft 64 projects from the body 61 and is connected to a piston rod 67 of a pneumatic cylinder (biasing means) 66 of both rods fixed to the body 61. A flange member 68 is integrally screwed to the other end. This flange member 68
Has one end of the switching rod 50 integrally connected with another flange member 69 integrally connected in the axial direction. Switching shaft 6
A locking body 65 having locking portions 65a and 65b formed on both sides is integrally screwed in the central portion of 4. An engagement switching device 70 is arranged below the locking body 65. In this engagement switching device 70, a locking lever 72 is attached by a pin 71 to the upper portion of the L-shaped bracket 70A fixed to the body 61.
R and 72L face each other and are swingably supported. The locking levers 72R and 72L are L-shaped as a whole, and are provided with stoppers 72a and 72b like a beak of a bird which can be engaged with and disengaged from the locking portions 65a and 65b. Between the pins mounted in the middle of the lever portion 72c extending downward,
The tension spring 73 is interposed. Below the tension spring 73, guide wheels 74 that are rotatable forward from the bracket 70A (leftward in FIG. 4) are vertically provided at predetermined intervals. The switching operating rod 75 is guided between the guide wheels 74. The switching actuating rod 75 has a plane shape shown in FIG. 5, and push pins 76a and 76b capable of pressing the locking levers 72R and 72L on both sides are axially adjustable by a nut 77 on a front projection 75a. It is installed. Also,
The rear protruding portion 75b is integrally connected to a piston rod 79 of a pneumatic cylinder 78 mounted on the body 61. Further, on the lower surface of the body 61, a proximity as a bobbin rail up / down switching confirmation switch 80 is located at a lateral position of the lower end of the lever portion 72c when the stoppers 72a, 72b are engaged with the engaging portions 65a, 65b of the engaging body 65. The switch is attached. The cylinders 66 and 78 are connected to a compressed air source via switching valves 81 and 82, respectively. Therefore, FIG. 3 and FIG.
Assuming that the bobbin rail 20 is descending in the state shown in the figure,
When switching this to the rising, compressed air is accumulated in the cylinder chamber on the front side (right side) of the cylinder 66, and the locking lever 72L and the locking portion 6 are received by a switching command from the control device 100 described later.
5b is disengaged, the switching shaft 64 is moved leftward by utilizing the spring property of the pressure-accumulated air, the switching wheel 51 is engaged with the left driven gear 47 via the switching rod 50, and vice versa ( At this time, in the switching drive device 60, the stopper 72a is locked to the locking portion 65a, and in the up / down switching gear device 40, the switching wheel 51 is meshed with the left driven gear 47).
The compressed air is stored in the cylinder chamber on the rear side (left side) of the cylinder 66 and is urged to the right to release the engagement between the stopper 72a and the engagement portion 65a. In this embodiment, the up / down switching gear device 40 and the switching drive device 60 constitute an up / down switching means (bobbin forming device) for the bobbin rail 20. Reference numerals 83 and 84 are pressure sensors for confirming that the compressed air is accumulated in the cylinder chamber of the pneumatic cylinder 66.

Next, control of this roving frame will be described. For position control, which is a feature of the present invention, a pulse encoder PG1 is connected to a front roller shaft 8a that is integral with the front roller 8. The encoder PG1 outputs a pulse in proportion to the rotation angle of the front roller 8 and is a detection means for detecting the front roller rotation angle. Further, an absolute type pulse encoder PG3 for detecting the rotation angle of the lifter shaft 57 is provided at the end of the lifter shaft 57 of the drive mechanism that moves forward and backward for lifting the bobbin rail 20 from the lift switching gear device 40 to the lifter rack 59. The detection value of the encoder PG3 corresponds to the vertical position of the bobbin rail 20. Further, a non-contact type roving tension detecting device RT for detecting the tension of the roving R is disposed between the front roller 8 and the flyer top. This roving tension detecting device RT is disclosed in, for example, Japanese Patent No. 147.
As disclosed in No. 2674, the position of the roving is read by a large number of photoelectric sensors.

The control device 100 mainly includes a well-known microcomputer 101. The microcomputer 101 includes a central processing unit CPU 102, a read-only memory ROM 103 storing a program shown in FIG. 7, and a rewritable memory RAM 1 storing various data and calculation results.
04, the CPU 102 exchanges data and commands with the input / output interface I / O 105. The I / O 105 includes data required for calculating the bobbin winding diameter (bobbin diameter d ₀ at the time of initial winding, thickness of roving layer (constant increment) Δd, coefficient required for calculation by roving thread tension detecting device, etc.), And data showing the bobbin winding diameter shape (the angle θ ₁ of the upper shoulder B1 and the lower shoulder B2 in FIG. 8,
θ ₂ ), the initial value of the frequency division ratio kp set in the frequency divider 109 during the first winding, and the spinning conditions (count, twist number, fiber type, etc.)
Is connected to the input means (keyboard) 106, and the roving thread tension signal from the roving thread tension detecting device RT, the detection value corresponding to the bobbin rail position from the encoder PG3, and the bobbin rail via the sequencer 108. A switching confirmation signal from the up / down switching confirmation switch 80 is input. Further, a display means (display) 107 for displaying the content of the input data is connected, and the switching drive device 60 is connected via the sequencer 108.
A switching command for driving the cylinder 78 is output.

A frequency divider 1 in which a frequency division ratio kp is set in the control device 100.
09 is provided and is connected to the CPU 102. The frequency division ratio kp corresponds to the rotation angle ratio of the bobbin rotation angle to the rotation angle of the front roller 8 for proper winding with respect to the increase in the bobbin winding diameter D. An output pulse train obtained by multiplying the pulse train from the pulse encoder PG1 by a frequency division ratio kp (0.9999 or less, changed depending on the bobbin winding diameter D) is input to the servo amplifier 111 for driving the servo motor via the gate circuit 110. Is done.

The gate circuit 110 uses the pulse encoder P during normal operation.
It outputs forward and reverse pulses corresponding to the rotation direction of G1, and when there is no input from the pulse encoder PG1,
When the servo motor SM is desired to be driven, for example, when the bobbin rail 20 is lowered for doffing after the roving bobbin is full and the bobbin rail 20 is fully stopped, a built-in pulse is generated by a command from the sequencer 108. The servo motor SM is driven by the pulse from the device.

The servo motor SM is connected to a pulse encoder PG2 that detects the rotation angle of its rotation axis, and a position loop feedback control system 112 that sends a feedback pulse from the pulse encoder PG2 to the servo amplifier 111 is configured.

The frequency division ratio kp is a function of the bobbin winding diameter D,
It is known from the following calculation. That is, θr: Front roller rotation angle (rad) qr: Number of pulses per rotation of encoder PG1 (constant value) θs: Servo motor rotation angle (rad) qs: Front roller rotation angle θr per rotation of encoder PG2 As the number of pulses (constant value) of the product of the number of pulses output by the rotation of the front roller 8 and the frequency division ratio kp is equal to the number of feedback pulses output by the rotation of the servo motor SM, kp = (Θs / θr) × (qs / qr) ... On the other hand, θF: Front roller rotation angle θr, flyer rotation angle (rad) r: Front roller radius (constant value depending on machine base) θB: Front roller rotation angle θr , Bobbin rotation angle (rad), from the relationship between the spinning length and the winding, (θB−θF) × D / 2 = θr × r ... , The differential gear mechanism 40 sets the constant A so as to satisfy the relationship of θB = θF + A × θs ..., and then θr × r / (D / 2) = A × θs ..., and kp = r × (Qs / qr) / (A × D / 2) = f (D).

Further, the relationship between the front roller rotation angle θr and the movement amount 1 of the bobbin rail 20 is: S = width of one roving roll (a constant changed by the lifter change wheel 16), l = θr × r × S / (2 × π × D / 2) ... From the following, it can be seen that l = A × S × θs / (2 × π) = f (θs) ..., which is a function of the rotation angle θs of the servo motor SM.

Next, a control program for bobbin rotation and up / down switching of the bobbin rail 20 written in the ROM 103 will be described with reference to the flowchart of FIG. Each functional step is realized by each step of the flowchart.
That is, step 1 is a means for calculating the bobbin rail up / down switching position for the next time (see FIG. 8), and the bobbin rail 2 for forming the lower shoulder portion B2 of the following formula is used.
0 switching position l ₂ = L− (D−d ₀ ) / (2 × tan θ ₂ ) ... Bobbin rail 2 for forming the upper shoulder portion B1 of the roving bobbin.
0 of Shitagiri changeover position _{l 1 = (D-d 0} ) / (2 × tanθ 1) ... ( the origin of the bobbin rail 20, and corresponds with the uppermost end of the coarse wound) and below the elevator switching position _l 1 by, ₁₂ is calculated, and the rotation angle of the lifter shaft 57 corresponding to these values is calculated. Normally, the roving R is started to be wound from the upper and lower intermediate portions of the empty bobbin, so that the roving R once descends to the lowest point and is switched to move to the uppermost end of the bobbin rail 20.
Is controlled, and then the above equation is followed.

Step 2 is a means for reading the roving tension detection signal, which is read several times during one ascending or descending stroke of winding the body winding portion B3 excluding the upper and lower shoulder portions B1 and B2. Step 3 is a means for discriminating whether or not the reading point is the last, and step 4 is means for calculating a correction value for the roving layer thickness based on the tension signal. Based on the roving tension, the roving further layer thickness (constant increment Δd Is calculated by multiplying the deviation between the preset target tension value and the detected detection value by a constant coefficient.
Next, step 5 is a means for calculating the next bobbin winding diameter D,
The following equation, D (next bobbin winding diameter) = D (this bobbin winding diameter) + 2
It is calculated by × (Δd−ε). In step 6, the next bobbin winding diameter D calculated in step 5 is substituted into the above equation to calculate the pulse division ratio kp for the next bobbin winding diameter D. Step 7 is a comparing means for comparing the detected value from the encoder PG3 with the calculated values corresponding to the vertical switching positions l ₁ and l ₂ of the bobbin rail 20 calculated in the above step 1, and step 8 is the step in step 7 above. , Or the lower switching position l ₁ ,
When it becomes l ₂ , an output means for outputting a lifting / lowering switching command to the sequencer 108, a step 9 is a judging means for judging whether or not there is a switching confirmation signal from the bobbin rail lifting / lowering switching confirmation switch 80 of the switching drive device 60, and a step 10 is a minute. It is a pulse division ratio updating means for outputting and updating the pulse division ratio kp calculated in step 6 to the frequency divider 109. Among these functional means, the next pulse division ratio calculation means (step 6) and pulse division ratio update means (step 10) are the frequency divider 109, the gate circuit 110, and the servo amplifier 1 described above.
11, together with the position loop feedback system 112, constitutes the digital control means 120.

Next, the operation will be described. The description is made during one stroke in which the bobbin rail 20 descends from the upper switching position l ₂ to the lower switching position l ₁ (the roving R is wound around the bobbin 15 from the lower shoulder portion B2 to the upper shoulder portion B1). To do. At this point in time, the CPU 102 has set the pulse division ratio kp calculated corresponding to the newly wound bobbin winding diameter D on the frequency divider 109, and the pulse corresponding to a certain rotation angle of the front roller 8 is set. The output pulse obtained by multiplying the frequency division ratio kp is the gate circuit 1
It is input to the servo amplifier 111 via 10. The servo amplifier 111 rotates the servo motor SM by a predetermined angle so as to follow the input pulse, and the servo motor SM is rotated.
Rotation of the differential gear mechanism 30 rotates the input shaft 33,
According to the bobbin winding diameter D, the front roller rotation angle θ is combined with the constant rotation of the main motor 1 according to the bobbin winding diameter D.
The rotation angle θ is rotated by an appropriate rotation angle corresponding to r.
Rough yarn R spun from the front roller 8 rotated by r
Take up properly. At this time, the servo motor SM is output by the output pulse of the encoder PG1 connected to the front roller 8.
Since the rotation is controlled, the response is extremely fast. The bobbin rail 20 descends from the upper switching position l ₂ and winds the roving R around the bobbin from the bottom to the top. However, as shown in FIG. The elevation switching position (lower switching position l _{1 in} this case) is calculated, and the rotation angle of the lifter shaft 57 corresponding to this is calculated and stored in the RAM 104. Then, in Steps 2 and 3, the tension of the roving R across the front roller 8 and the flyer top is read from the roving tension detector RT. Then, in step 4, the correction value ε for the further thickness (constant increment) Δd is calculated by this tension signal. Next, from the correction value ε calculated in step 4, the bobbin winding diameter D that is currently wound, and the constant increment Δd, the bobbin for the next time (after switching the up and down movement of the bobbin rail 20 to the up position at the lower switching position l ₁ ). Calculate the winding diameter D with an equation,
Predict. Next, at step 6, the next pulse division ratio kp is calculated based on the next bobbin winding diameter D, and the RAM 10
Store in 4. After step 6 is executed, when the detected value corresponding to the vertical position of the bobbin rail 20 from the encoder PG3 input in step 7 matches the calculated value corresponding to the lower switching position l ₁ stored in step 1,
A switching command is immediately output (steps 7 and 8). When the bobbin rail 20 is lowered, the up-and-down switching gear device 40 is in the state shown in FIG. 2 and the switching drive device 60 is in the state shown in FIG.
Before the switching signal is output, compressed air is supplied to the front cylinder chamber of the cylinder 66 to accumulate pressure and urge it in the switching direction (left in FIG. 3). Then, the switching signal is transmitted to the piston rod 79 via the sequencer 108 by the switching signal.
To the left. Then, the switching operation rod 7
5, the push pin 76b comes into contact with the locking lever 72L, and the stopper 72b and the locking portion 65b are disengaged. Then, the compressed air that has accumulated pressure acts as if it were a spring, causing the piston rod 67 to instantly move to the left and cause the switching rod 50 to move.
The switching wheel 51 in the state shown in FIG. 2 is engaged with the left driven gear 47 to switch the rotation direction of the output shaft 55 to raise the bobbin rail 20. Locking lever 72L
When the switch shaft 64 is disengaged and the switching shaft 64 moves to the left, the stopper 72a of the locking lever 72R is rotated clockwise by the force of the spring 73 to engage with the locking portion 65a. In this way, the stopper 72a (7
In the state in which 2b) is engaged with the corresponding locking portion 65a (65b), the switching shaft 64 cannot move in the axial direction, so even if there is an accident such that the supply of compressed air to the cylinder 66 is lost due to a power failure or the like, the switching wheel The 51 does not move away from the driven gear 47 (48) that has been meshed until then, and the bobbin rail 20 does not drop.

When the right locking lever 72R engages with the locking step portion 65a in this manner, the right-side up / down switching confirmation switch (proximity switch) 80 confirms it and sends a confirmation signal to the sequencer 108.
To the I / O 105 via. CPU10 that received this
In step 2, after step 9, the pulse frequency division ratio kp of the frequency divider 109 is updated in step 10 with the value calculated in step 6.

Hereinafter, steps 1 to 10 are repeated to wind up the roving. However, since either one of the upper and lower switching positions l ₁ and l ₂ is calculated according to the above-described formula for each up / down switching, the bobbin winding diameter D
The ascending / descending stroke of the bobbin rail 20 is sequentially shortened with an increase in. As a result, the upper and lower shoulders B1 and B2 are formed according to the input data. Changing the shape of the bobbin requires only inputting the input data from the input device 106, and therefore does not require any trouble.

In this way, when the roving R is wound and becomes full, a full pipe stop command is output from the sequencer 108, and the main motor 1,
Both the servo motor SM is stopped. Next, for doffing, first, the sequencer 108 outputs a clutch disengagement command to the clutch 34 to disengage the clutch 34, and the switching wheel 51 of the up-and-down switching gear device 40.
However, when the bobbin rail 20 meshes with the driven gear 47 on the ascending side by the normal rotation of the servomotor SM (this is determined by the signal from the up / down switching confirmation switch 80 of the bobbin rail 20), the switching drive device 60 is used. The switching wheel 51 meshes with the driven gear 48. In this state, the servo motor S is transferred from the sequencer 108 to the gate circuit 110.
Issue M forward rotation command. The gate circuit 110 inputs a normal rotation pulse train from the internal pulse generator to the servo amplifier 111. The servomotor SM normally rotates so as to follow this pulse, lowers the bobbin rail 20 to a predetermined doffing position, performs doffing with a doffing device (not shown), and supplies a new empty bobbin. Then, the switching wheel 51 is set to the driven gear 4 on the rising side of the bobbin rail 20.
After engaging with 7, the servo motor SM is normally rotated to raise the bobbin rail 20 to a predetermined winding start position, and then the main motor 1 is activated to perform winding again.

The clutch may be interposed in the transmission system from the differential gear mechanism to the bobbin shaft, for example, in the connection shaft 25. In this embodiment, a digitally controlled motor is used, but an analogly controlled motor may be used.

As described above, according to the bobbin rail single lifting device in the roving machine of the present invention, the rotation of the main motor that drives the draft part and the rotation of the control motor that can independently change the bobbin rotation are combined. In the roving machine which is provided with a differential gear mechanism for transmitting the bobbin shaft to the bobbin shaft, and the control motor is linked to the lifter rack via an up-and-down switching gear device so as to drive the bobbin rail up and down. Since a clutch is interposed in the middle of the transmission system to the mechanism or the transmission system from the differential gear mechanism to the bobbin shaft, for example, at the time of doffing a full roving bobbin, the clutch is disconnected and the control motor is turned on. By driving,
Only the bobbin rail can be raised and lowered, and the motor dedicated to raising and lowering the bobbin rail can be eliminated.

[Brief description of drawings]

1 is a schematic perspective view of a drive mechanism, FIG. 2 is a sectional view of an up-and-down switching gear device, FIG. 3 is a side view of a switching drive device, and FIG. 4 is a sectional view taken along line IV-IV of FIG. FIG. 6 is a plan view of the switching operation rod, FIG. 6 is a view showing a control device, FIG. 7 is a flow chart showing a control program, and FIG. 8 is a view showing a roving bobbin. 1 ... Main motor, 7 ... Draft part, 8 ... Front roller, 15 ... Bobbin, 23 ... Bobbin shaft, 34 ... Electromagnetic clutch, 40 ... Elevating switching gear device, 59 ... Lifter rack, 60 ... ... Switching drive device, 1
00 ... Control device, SM ... Servo motor (digital control motor), PG1 ... Encoder (front roller rotation angle detection device)

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Hideki Hashimoto 1-2 Ishiodai, Kasugai City, Aichi Prefecture 130-1 Town Ishiodai 130-1 (72) Creator Makoto Omori 6-24 Minamihonmachi, Tsushima City, Aichi Prefecture (72) Creator Kenji Sasaki 82, Brahma, Fujishima-cho, Komaki-shi, Aichi Examiner Hiroyuki Sugino (56) References JP-A-51-102128 (JP, A) JP-A-62-132183 (JP, U)

Claims (1)

[Scope of utility model registration request] 1. A differential gear mechanism that combines the rotation of a main motor that drives a draft part and the rotation of a control motor that can independently change bobbin rotation to transmit the rotation to a bobbin shaft, and the control motor includes: In a roving machine linked to a lifter rack through an up / down switching gear device so as to drive a bobbin rail up and down, a transmission system from the control motor to a differential gear mechanism or a transmission system from a differential gear mechanism to a bobbin shaft. An independent lifting device for bobbin rails in a roving machine, characterized in that a clutch is interposed in the middle of the process.