JP2004100071A - Air pressure regulating apparatus and air pressure regulating apparatus in jet loom - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve a flow rate characteristic in an air pressure regulating apparatus without making a cam drive means large. <P>SOLUTION: A valve body 29 is housed in a valve housing 28. A pressure chamber 34 is formed between a diaphragm 32 and a valve housing 28. The pressure chamber 34 is made to communicate with an output port 283. A reversely rotatable motor 35 is fixed in a casing 31. A cam 36 is fixed at the top of an output shaft 351 of the motor 35. A pressure regulating spring 37, a spring locus 38 and a rotator 39 are disposed between the diaphragm 32 and the cam 36. The rotator 39 is pressed to a cam surface 361 relatively rollably on the cam surface 361 of the cam 36 by spring force of the pressure-regulating spring 37. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an air pressure adjusting device and an air pressure adjusting device in a jet loom.
[0002]
[Prior art]
An apparatus for adjusting the pressure of air supplied to a weft insertion nozzle is disclosed in, for example, Patent Document 1. The air pressure adjusting device disclosed in Patent Literature 1 connects a diaphragm to a valve element that cuts off communication between an input port and an output port, and screwes a slider to a drive screw driven forward and reverse by a motor. The pressure adjusting spring is interposed between the slider and the diaphragm. When the drive screw is rotated by the operation of the motor, the position of the slider changes, and the urging force acting on the diaphragm from the pressure adjusting spring changes. Therefore, the air pressure on the output port side changes.
[0003]
[Patent Document 1]
Japanese Utility Model Publication No. 3-59380
[Problems to be solved by the invention]
When the air pressure adjusting device as described above is used, the air pressure on the output port side when the air is not supplied to the weft insertion nozzle is the output port side when the air is supplied to the weft insertion nozzle. Higher than the air pressure. It is said that the smaller the pressure difference, the better the flow characteristics in the air pressure regulator. Immediately after the start of operation of a loom using such an air pressure adjusting device, air having a pressure higher than usual is supplied to the weft insertion nozzle. If weft insertion is performed with air at a pressure higher than usual, the weft may not be inserted properly.
[0005]
In order to improve the flow characteristics in the air pressure adjusting device, the pressure receiving area of the diaphragm may be increased, but in this case, it is necessary to increase the spring force of the pressure adjusting spring. When the spring force of the pressure adjusting spring is increased, the sliding contact resistance (sliding resistance) between the slider and the drive screw increases. Therefore, it is necessary to increase the torque of the motor, and the motor becomes large. Increasing the size of the motor increases costs.
[0006]
SUMMARY OF THE INVENTION An object of the present invention is to improve the flow characteristics in an air pressure adjusting device without increasing the size of a cam driving means such as a motor.
[0007]
[Means for Solving the Problems]
Therefore, in the invention of claim 1, a valve body that opens and closes a passage between an input port and an output port, and a diaphragm that partitions a pressure chamber that communicates with the output port side so as to interlock with the valve body. A pressure adjusting spring for urging the diaphragm against the pressure in the pressure chamber, a cam, cam driving means for driving the cam, and a reverse of the diaphragm side by the urging force of the pressure adjusting spring. And a rotor which is urged toward the side of the cam and pressed against the cam surface of the cam.
[0008]
When the cam is driven, the rotor is displaced, and the urging force of the pressure adjusting spring acting on the diaphragm changes. Therefore, the air pressure on the output port side changes. The urging force of the pressure adjusting spring presses the rotor against the cam surface of the cam, but the rolling resistance of the rotor can be considerably smaller than the conventional sliding resistance between the slider and the drive screw. Therefore, even when the pressure receiving area of the diaphragm is increased to increase the spring force of the pressure adjusting spring, it is not necessary to increase the output of the cam driving means.
[0009]
According to a second aspect of the present invention, in the first aspect, the cam driving means is a motor capable of rotating forward and reverse.
When the cam is rotated, the rotor is displaced, and the urging force of the pressure adjusting spring acting on the diaphragm changes. Therefore, the air pressure on the output port side changes. The urging force of the pressure adjusting spring presses the rotor against the cam surface of the cam, but the rolling resistance of the rotor can be considerably smaller than the conventional sliding resistance between the slider and the drive screw. Therefore, even when the pressure receiving area of the diaphragm is increased to increase the spring force of the pressure adjusting spring, it is not necessary to increase the torque of the motor.
[0010]
According to a third aspect of the present invention, in the second aspect, the direction of the rotation axis of the cam is set in a direction perpendicular to the direction of displacement of the valve body, and the cam surface of the cam is formed on the peripheral surface of the cam. .
[0011]
Such a cam is suitable for easily forming a cam surface and obtaining a desired cam surface.
According to the fourth aspect of the present invention, the pressure of the air supplied to the weft insertion nozzle is targeted at a jet loom in which weft is inserted by the weft insertion nozzle. It was adjusted by an adjusting device.
[0012]
The air pressure adjusting device in which the flow characteristics are improved without increasing the size of the cam driving means contributes to avoiding a weft insertion defect immediately after the start of operation of the loom.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
[0014]
The weft yarn Y ejected by air injection from the weft insertion main nozzle 11 is inserted into the weft insertion auxiliary nozzle groups 12, 13, 14, 15 by relay injection of air. When the weft insertion is performed satisfactorily, the weft Y is detected by the weft detector 16 in a predetermined loom rotation angle range. The weft detection signal output from the weft detector 16 is sent to the control device 17. The rotary encoder 10 for detecting the rotation angle of the loom is signal-connected to the control device 17.
[0015]
Air injection in the weft insertion main nozzle 11 as the weft insertion nozzle is performed by exciting the electromagnetic on-off valve 18. When the solenoid on-off valve 18 is demagnetized, the air injection in the weft insertion main nozzle 11 stops. Air injection in the weft insertion auxiliary nozzle groups 12 to 15 as the weft insertion nozzles is performed by exciting the electromagnetic on-off valves 19, 20, 21 and 22. When the electromagnetic on / off valves 19 to 22 are demagnetized, the air injection in the weft insertion auxiliary nozzle groups 12 to 15 is stopped.
[0016]
The electromagnetic on-off valve 18 is connected to an air tank 23, and the electromagnetic on-off valves 19 to 22 are connected to an air tank 24. The air tanks 23 and 24 are connected to a pressure air supply source 27 via air pressure adjusting devices 25 and 26, respectively. The pressurized air from the pressurized air supply source 27 is sent to the weft insertion main nozzle 11 via the air pressure adjusting device 25, the air tank 23, and the electromagnetic on-off valve 18. The pressure air from the pressure air supply source 27 is sent to the weft insertion auxiliary nozzle groups 12 to 15 via the air pressure adjusting device 26, the air tank 24, and the electromagnetic switching valves 19 to 22.
[0017]
The internal structure of the air pressure adjusting device 25 will be described. The air pressure adjusting device 26 has the same structure as the air pressure adjusting device 25.
A valve body 29 is accommodated in the valve housing 28 so as to be able to reciprocate. The valve body 29 is urged toward the valve seat 281 by the spring force of the compression spring 30. A passage 284 formed in the valve housing 28 between the input port 282 and the output port 283 opens when the valve body 29 and the valve seat 281 are separated. When the valve body 29 and the valve seat 281 are joined, the passage 284 is closed.
[0018]
A cylindrical casing 31 is connected to the valve housing 28 via a diaphragm 32. A spring receiver 33 is attached to the center of the diaphragm 32. The valve rod 291 of the valve body 29 contacts the surface of the spring receiver 33 on the valve body 29 side.
[0019]
A pressure chamber 34 is formed between the diaphragm 32 and the valve housing 28. The pressure in the pressure chamber 34 urges the diaphragm 32 to the side opposite to the valve body 29. The pressure chamber 34 communicates with an output port 283 via a passage 285 formed in the valve housing 28. The pressure at the output port 283 spills through the passage 285 to the pressure chamber 34. Therefore, the pressure at the output port 283 acts on the diaphragm 32.
[0020]
As shown in FIG. 2, a mounting wall 311 is projected from the casing 31, and a forward / reverse rotatable motor 35 is fixed to the mounting wall 311. The motor 35 as the cam driving means is a stepping motor. An output shaft 351 of the motor 35 penetrates the mounting wall 311, and a disc-shaped cam 36 is fixed to a tip of the output shaft 351. The center axis 352 of the output shaft 351 that is the rotation axis of the motor 35 passes through a position off the center of the circular shape of the disk-shaped cam 36. The disc-shaped cam 36 is an eccentric cam having a cam surface 361 on its peripheral surface.
[0021]
The diaphragm 32 and the cam 36 are opposed to each other via the inside of the cylinder of the casing 31, and a pressure adjusting spring 37, a spring seat 38, and a rotor 39 are interposed between the diaphragm 32 and the cam 36. The pressure adjusting spring 37 is located between a spring receiver 33 attached to the diaphragm 32 and a spring seat 38. The spring force of the pressure adjusting spring 37 urges the diaphragm 32 toward the valve body 29. This urging force opposes the spring force of the compression spring 30, and the opposing action always brings the valve rod 291 into contact with the spring receiver 33. Therefore, the valve element 29 and the diaphragm 32 are interlocked, and the valve element 29 and the diaphragm 32 can move integrally. The diaphragm 32 is displaced when the pressure in the pressure chamber 34 fluctuates. The spring receiver 33 and the valve rod 291 constitute an urging force transmitting means for transmitting the spring force (urging force) of the pressure adjusting spring 37 acting on the diaphragm 32 to the valve body 29.
[0022]
The spring force of the pressure adjusting spring 37 urges the spring seat 38 toward the cam 36. The rotor 39 is located between the spring seat 38 and the cam 36. The radial bearing type rotor 39 is supported by a support shaft 40 attached to a spring seat 38. The rotor 39 receives the spring force of the pressure adjustment spring 37 via the spring seat 38, and the outer ring 391 of the rotor 39 relatively moves on the cam surface 361 of the cam 36 by the spring force of the pressure adjustment spring 37. Rollably pressed against the cam surface 361.
[0023]
The center axis 352 of the output shaft 351 of the motor 35 is the rotation axis of the cam 36. The direction of the rotation axis (center axis 352) of the cam 36 is a direction orthogonal to the direction of displacement of the valve body 29. The direction of displacement of the valve body 29 is the direction of expansion and contraction of the pressure adjusting spring 37.
[0024]
Pressure detectors 41 and 42 are connected to the air tanks 23 and 24. The pressure detector 41 detects the pressure in the air tank 23, and the pressure detector 42 detects the pressure in the air tank 24. Information on the pressure detected by the pressure detectors 41 and 42 is sent to the control device 17.
[0025]
Next, the operation of the first embodiment will be described.
The control device 17 controls the rotation of the loom when the leading end of the weft reaches the detection area of the weft detector 16 based on the loom rotation angle information obtained from the rotary encoder 10 and the weft detection signal obtained from the weft detector 16. Know the angle. The control device 17 grasps the average value of the weft tip arrival times at a predetermined number of times based on the weft detection signal obtained from the weft detector 16 and the loom rotation angle detection information obtained from the rotary encoder 10. Then, the control device 17 controls the operation of the motor 35 so that the pressure in the air tank 23 becomes a pressure set in advance corresponding to the average value of the arrival time of the weft leading end. Similarly, the control device 17 controls the operation of a motor (not shown) in the air pressure adjusting device 26 so that the pressure in the air tank 24 becomes a pressure set in advance corresponding to the average value of the weft tip arrival timing. I do.
[0026]
When increasing the pressure in the air tank 23, the cam 36 is rotated so as to displace the rotor 39 toward the diaphragm 32. The rotor 39 is displaced toward the diaphragm 32 while relatively rolling on the cam surface 361. When the rotor 39 is displaced toward the diaphragm 32, the spring seat 38 is also displaced toward the diaphragm 32 integrally with the rotor 39, and the spring force of the pressure adjusting spring 37 is increased. Therefore, the valve body 29 is displaced so that the opposition between the pressure in the pressure chamber 34 and the spring force of the pressure adjusting spring 37 via the diaphragm 32 is balanced. As a result, the pressure at the output port 283 increases, and the pressure at the air tank 23 increases.
[0027]
When reducing the pressure in the air tank 23, the cam 36 is rotated so as to displace the rotor 39 to the side opposite to the diaphragm 32 side. The rotor 39 is displaced toward the side opposite to the diaphragm 32 while rolling relatively on the cam surface 361. When the rotor 39 is displaced toward the side opposite to the diaphragm 32, the spring seat 38 is also displaced integrally with the rotor 39 toward the side opposite to the diaphragm 32, and the spring force of the pressure adjusting spring 37 is reduced. Therefore, the valve body 29 is displaced so that the opposition between the pressure in the pressure chamber 34 and the spring force of the pressure adjusting spring 37 via the diaphragm 32 is balanced. As a result, the pressure at the output port 283 decreases, and the pressure at the air tank 23 decreases.
[0028]
The control device 17 performs feedback control of the motor 35 based on the pressure information obtained from the pressure detector 41. That is, the control device 17 controls the operation of the motor 35 so that the pressure detected by the pressure detector 41 becomes the preset pressure as described above. Similarly, the control device 17 performs feedback control of the motor in the air pressure adjusting device 26 based on the pressure information obtained from the pressure detector 42.
[0029]
In the first embodiment, the following effects can be obtained.
(1-1) The spring force (biasing force) of the pressure adjusting spring 37 presses the rotor 39 against the cam surface 361 of the cam 36. Therefore, when the cam 36 rotates, the rotor 39 relatively rolls on the cam surface 361. The magnitude of the rolling resistance of the radial bearing type rotor 39 when the rotor 39 relatively rolls on the cam surface 361 depends on the spring force of the pressure adjusting spring 37. That is, as the spring force of the pressure adjusting spring 37 increases, the rolling resistance of the rotor 39 increases.
[0030]
In order to improve the flow characteristics in the air pressure adjusting device 25, the pressure receiving area of the diaphragm 32 may be increased and the spring force of the pressure adjusting spring 37 may be increased. As the spring force of the pressure adjusting spring 37 increases, the rolling resistance of the rotor 39 increases. However, the rolling resistance of the rotor 39 when the radial bearing type rotor 39 relatively rolls on the cam surface 361 is considerably smaller than the sliding resistance between the conventional slider and the driving screw. Therefore, even when the pressure receiving area of the diaphragm 32 is increased to increase the spring force of the pressure adjusting spring 37, it is not necessary to increase the torque of the motor 35. As a result, the flow characteristics in the air pressure adjusting devices 25 and 26 can be improved without increasing the size of the motor 35.
[0031]
(1-2) When the operation of the loom (jet loom) is stopped, the electromagnetic on-off valves 18 to 22 are closed, and air is supplied to the weft insertion main nozzle 11 and the weft insertion auxiliary nozzle groups 12 to 15. There is no supply. When the loom is operating, the electromagnetic on-off valves 18 to 22 open and close at a high speed, and the supply of air to the weft insertion main nozzle 11 and the weft insertion auxiliary nozzle groups 12 to 15 is performed intermittently. When air is not supplied to the weft insertion main nozzle 11 and the weft insertion auxiliary nozzle groups 12 to 15 which are the weft insertion nozzles, the air pressure on the output port 283 side is equal to the weft insertion main nozzle 11 and the weft insertion nozzle. It is higher than the air pressure on the output port 283 side when air is intermittently supplied to the auxiliary nozzle groups 12 to 15. When the pressure difference is large, immediately after the start of the operation of the loom, air having a pressure higher than usual is supplied to the weft insertion main nozzle 11 and the weft insertion auxiliary nozzle groups 12 to 15. If weft insertion is performed with air at a pressure higher than usual, the weft may not be inserted properly.
[0032]
If the pressure difference is reduced, weft insertion failure immediately after the start of operation of the loom is avoided. The air pressure adjusting devices 25 and 26 whose flow characteristics are improved without increasing the size of the motor 35 contribute to avoiding a weft insertion failure immediately after the start of operation of the loom. That is, the air pressure adjusting devices 25 and 26 are particularly suitable as air pressure adjusting devices in a jet loom in which wefts are inserted by an air jet from a weft insertion nozzle.
[0033]
(1-3) The cam 36 having a rotation axis (center axis 352) orthogonal to the displacement direction of the valve body 29 is suitable for easily forming the cam surface 361 and obtaining a desired cam surface 361. The cam surface 361 of the cam 36 (eccentric cam) in which the cam surface 361 is a circumferential surface is particularly easy to form.
[0034]
Next, a second embodiment of FIG. 3 will be described. The same components as those in the first embodiment are denoted by the same reference numerals.
In the cam 43 used in the air pressure adjusting device 25A of the second embodiment, the distance from the rotation axis (the center axis 352 of the output shaft 351) to the cam surface 431 monotonically increases. The angle range of the cam surface 431 about the rotation axis (center axis 352) can be set to exceed 180 °.
[0035]
The angle range of the cam surface 361 of the cam 36 in the first embodiment is less than 180 °. That is, if the maximum displacement of the rotor 39 due to the rotation of the cams 36 and 43 is the same, the displacement of the rotor 39 when the output shaft 351 rotates 1 ° Less than. This means that the air pressure adjusting device 25A using the cam 43 can perform finer adjustment of the air pressure than the air pressure adjusting device 25 using the cam 36.
[0036]
Next, a third embodiment of FIG. 4 will be described. The same components as those in the first embodiment are denoted by the same reference numerals.
A pair of support walls 312, 313 are formed on the casing 31 constituting the air pressure adjusting device 25 </ b> B, and a shaft 44 is rotatably supported on the support walls 312, 313 via a bearing 47. The cam 36 is fixed to the shaft 44 between the support walls 312 and 313. The shaft 44 passes through a position deviated from the center of the circle of the disc-shaped cam 36. A worm wheel 45 is fixed to one end of the shaft 44. A motor 35 is attached to the casing 31. The worm 46 is fixed to the output shaft 351 of the motor 35, and the worm 46 and the worm wheel 45 are engaged. The rotation of the output shaft 351 is transmitted to the shaft 44 via the engagement between the worm wheel 45 and the worm 46, and the cam 36 rotates integrally with the shaft 44.
[0037]
The spring force of the pressure adjusting spring 37 acting on the rotor 39 is received by the support walls 312 and 313 via the rotor 39, the cam 36, the shaft 44 and the bearing 47. That is, the spring force of the pressure adjusting spring 37 acting on the rotor 39 does not spread to the meshing portion between the worm wheel 45 and the worm 46. Therefore, the sliding resistance between the worm wheel 45 and the worm 46 is considerably smaller than the sliding resistance between the conventional slider and the drive screw. That is, the sliding resistance between the worm wheel 45 and the worm 46 does not cause a large load on the motor 35. As a result, in the second embodiment, the same effects as (1-1) to (1-3) in the first embodiment can be obtained.
[0038]
Further, in the third embodiment, the worm wheel 45 and the worm 46 constitute a speed reduction mechanism. Therefore, the amount of displacement of the rotor 39 when the output shaft 351 rotates 1 ° can be further reduced as compared with the case of the second embodiment. As a result, in the third embodiment, the air pressure can be adjusted more finely than in the second embodiment.
[0039]
Next, a fourth embodiment of FIG. 5 will be described. The same components as those of the third embodiment are denoted by the same reference numerals.
A linear motor 48 as a cam driving means is attached to the support walls 312 and 313 constituting the air pressure adjusting device 25C, and a movable member 481 of the linear motor 48 is attached with an inclined cam 49. The tilt cam 49 moves integrally with the mover 481. The rotor 39 is pressed against the cam surface 491 of the inclined cam 49 by the spring force of the pressure adjusting spring 37.
[0040]
The reciprocating direction of the mover 481 is a direction orthogonal to the displacement direction of the valve element 29, and the inclined cam 49 can reciprocate in a direction orthogonal to the displacement direction of the valve element 29. When the inclined cam 49 reciprocates, the rotor 39 is displaced in the direction of displacement of the valve body 29 while relatively rolling on the cam surface 491.
[0041]
In the fourth embodiment, the same effects as in the items (1-1) and (1-2) in the first embodiment can be obtained.
In the present invention, the following embodiments are also possible.
[0042]
(1) In the first and second embodiments, a geared motor is used as the motor 35. The geared motor uses a reduction gear mechanism to reduce the rotation of a rotor in the motor and output the reduced rotation. If a geared motor is used as the motor 35 for driving the cam 43, the displacement of the rotor 39 when the output shaft 351 rotates by 1 ° is smaller than in the second embodiment. As a result, fine adjustment of the air pressure can be performed as in the third embodiment.
[0043]
(2) The direction of the rotation axis of the motor is set as the direction of displacement of the valve body 29, and an end face cam is used as a cam driven by the motor. The cam surface of the end face cam fixed to the output shaft of the motor faces the diaphragm 32, and the rotor 39 in contact with the cam surface is displaced in the direction of the rotation axis of the motor.
[0044]
(3) In the first embodiment, the mounting wall 311 is formed separately from the casing 31.
(4) In the third embodiment, the support walls 312 and 313 are formed separately from the casing 31.
[0045]
The invention that can be grasped from the above-described embodiment will be described below.
[1] In any one of claims 1 to 3, an urging force of the pressure adjusting spring for urging the rotor is transmitted to the rotor via a spring seat of the pressure adjusting spring, The air pressure adjusting device, wherein the rotor is a radial bearing supported on a support shaft attached to the spring seat.
[0046]
[2] The air pressure adjusting device according to any one of [1] to [3] and [1], wherein the cam is a disc-shaped eccentric cam.
[3] The air pressure adjusting device according to any one of [1] to [3] and [1], wherein the cam has a cam surface whose distance from a rotation axis thereof to a cam surface monotonically increases.
[0047]
【The invention's effect】
As described in detail above, according to the present invention, the rotor is urged to the side opposite to the diaphragm side by the urging force of the pressure adjusting spring and pressed against the cam surface of the cam. There is an excellent effect that the flow characteristics in the air pressure adjusting device can be improved without increasing the size of the driving means.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an air pressure adjusting device according to a first embodiment and a combination diagram of air piping.
FIG. 2 is a sectional view of a main part.
FIG. 3 is an essential part cross-sectional view showing a second embodiment.
FIG. 4 is an essential part cross-sectional view showing a third embodiment.
FIG. 5 is a sectional view of a main part showing a fourth embodiment.
[Explanation of symbols]
11 ... weft insertion main nozzle as weft insertion nozzle. 12 to 15: a group of auxiliary nozzles for weft insertion as nozzles for weft insertion. 25, 25A, 25B, 25C, 26: Air pressure adjusting device. 282 input port. 283 output port. 284 ... passage. 29 ... valve body. 32 ... diaphragm. 34 ... Pressure chamber. 35 ... Motor as cam driving means. 352: A central axis as a rotation axis of the cam. 36, 43 ... Cam. 361, 431: Cam surface. 37 ... Pressure adjusting spring. 39 ... Rotor. 48 Linear motor as cam driving means. 49 ... inclined cam. 491 ... Cam surface.

Claims (4)

A valve element for opening and closing the passage between the input port and the output port;
A diaphragm that partitions a pressure chamber communicating with the output port side so as to interlock with the valve body;
A pressure adjusting spring that biases the diaphragm against the pressure of the pressure chamber;
Cam and
Cam driving means for driving the cam;
An air pressure adjusting device comprising: a rotor which is urged by a biasing force of the pressure adjusting spring toward a side opposite to the diaphragm side and pressed against a cam surface of the cam. The air pressure adjusting device according to claim 1, wherein the cam driving unit is a motor that can rotate forward and backward. The air pressure according to claim 2, wherein the direction of the rotation axis of the cam is set in a direction orthogonal to the direction of displacement of the valve body, and the cam surface of the cam is formed on the peripheral surface of the cam. Adjustment device. An air pressure adjusting device in a jet loom, wherein the pressure of air supplied to the weft insertion nozzle is adjusted by the air pressure adjusting device according to any one of claims 1 to 3.

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