KR100433884B1 - Water jet device in water jet loom - Google Patents

Abstract

It provides a water jet that can further speed up the water jet room without causing a degradation in fabric quality. The cylinder 30 is screwed together to the pump housing 12 constituting the weft insertion pump 29. The piston 32 is slidably accommodated in the cylinder 30. The piston 32 is fixedly fixed to the plunger 14. A compression chamber 35 is formed between the inner circumferential surface of the cylinder 30 and the outer circumferential surface of the piston 32 and between the seals 33 and 34 attached to the cylinder 30 and the piston 32. An air pressure source 36 is connected to the compression chamber 35 via an air line 37.

Description

Water jet device in water jet room {WATER JET DEVICE IN WATER JET LOOM}

The present invention pumps water from the weft insertion nozzle by pumping water into a weft insertion nozzle by a weft insertion pump, and inserts the weft yarn by the water spray action of the weft insertion nozzle. A water jet device in a water jet loom.

FIG. 10 shows the water spray value of the conventional water jet room, and FIG. 11 shows the internal structure of the weft insertion pump 11 constituting the conventional water spray value. The storage chamber formation cylinder 13 is accommodated and fixed in the cylindrical pump housing 12 of the weft insertion pump 11. A plunger 14 is slidably housed in the cylinder of the reservoir chamber forming cylinder 13. The plunger 14 is equipped with a spring seat 15. A spring cap 16 is screwed to the inner circumferential surface of the cylindrical pump housing 12. The spring cap 16 is fixed to the pump housing 12 by tightening the locking nut 17. A coil spring 18 is sandwiched between the seat portion 151 of the spring seat 15 and the seat portion 161 of the spring cap 16.

The pump housing 12 is formed with a suction port 121 and a discharge port 122, and a water storage chamber 123 is formed between the suction port 121 and the discharge port 122. Check valves 19 and 20 are fitted between the reservoir 123 and the suction port 121 and between the reservoir 123 and the discharge port 122, respectively. As shown in FIG. 10, the suction pipe 24 connected to the suction port 121 is passed through a float box 25, and the discharge pipe 26 connected to the discharge port 122 is connected to the weft insert nozzle 27. Connected.

The plunger 14 is connected to the cam lever 22 via the joint 21. The cam lever 22 is connectable / disconnectable to the cam 23 via the cam follower 221. The cam lever 22 is reciprocated by the cooperation of the cam 23 and the coil spring 18 which rotate in the direction of the arrow Z of FIG. 10 at a constant angular speed in synchronization with the loom rotation. The plunger 14 and the spring seat 15 are integrally reciprocated by the reciprocating oscillation of the cam lever 22. In FIG. 10, when the cam lever 22 rotates left about the support shaft 222 according to the rotational force of the cam 23, the plunger 14 and the spring seat 15 are opposed to the spring force of the coil spring 18. To move (move from right to left in FIG. 11). The swinging operation of the spring seat 15 compresses the coil spring 18. The swinging operation of the plunger 14 sucks a certain amount of water from the float box 25 into the reservoir chamber 123 through the suction pipe 24. While the check valve 19 is opened and water is sucked into the water storage chamber 123, the check valve 20 is closed so that the water in the discharge pipe 26 does not flow back to the water storage chamber 123 side.

When the cam follower 221 exceeds the maximum diameter position Ma of the cam face 231 of the cam 23, the cam follower 221 is separated from the cam face 231 of the cam 23, and the coil spring 18 The plunger 14, which is subjected to the restoring force, pressurizes the water in the reservoir 123. When the water in the reservoir 123 is pressurized, the check valve 19 is closed and the check valve 20 is opened to pressurize the pressurized water in the reservoir 231 through the discharge pipe 26. Is sent to. Water pressurized by the weft insertion nozzle 27 is injected from the weft insertion nozzle 27, and the weft yarn Y is inserted into the inclined opening. The water spray of one cycle is complete | finished while the cam follower 221 separated from the cam surface 231 of the cam 23 contact | connects the cam surface 231 or the stopper 28 for injection quantity limitation provided separately.

The stopper 28 is composed of a floating-placed female screw 281, a male screw 282 screwed to the female screw 281 and a locking nut 283 screwed to the male screw 282. . The male screw 282 is fixed to the female screw 281 by tightening the locking nut 283. By changing the threaded insertion position of the male screw body 282 with respect to the female screw body 281, the final end position of the cam lever 22 in the double direction direction is changed.

Curve K in the graph of Fig. 13 shows the relationship between the loom rotation angle and the cam lift amount (that is, the displacement amount of the cam follower 221 in the radial direction at the minimum diameter position of the cam surface 231 of the cam 23). Indicates. The loom rotation angles θ1 to θ2 are water intake strokes in which the cam lift amount increases at substantially constant speed, and the loom rotation angles θ3 to θ4 are water injection strokes in which the cam lift amount is drastically reduced from the maximum value.

Since the inertia force of the water and the frictional resistance of the pipe are small, the neglected, the motion equation shown in the following equation (1) is established at the time of water injection from the weft insert nozzle 27.

m.dx ² / dt ² = (Fkx) + (Pa-Po) Ap ...

In equation (1),

m is the sum of the equivalent masses of the movable bodies of the power transmission system such as the cam lever 22, the plunger 14, the coil spring 18, the spring seat 15,

x is the displacement of the plunger 14,

dx ² / dt ² is the acceleration of the plunger 14,

k is the spring constant of the coil spring 18,

F is the compressive load of the coil spring 18 at the start of water spray,

Po is the pressure in the reservoir 123,

Pa is atmospheric pressure,

Ap is the cross-sectional area of the plunger 14.

The straight line f in the graph of FIG. 12 shows the relationship between the length of the coil spring 18 and the spring load. The range indicated by ho is an example of the displacement range of the coil spring 18 length used as the operating range of the plunger 14.

If equation (1) is summarized with respect to the pressure Po of the storage chamber 123, ie, the water injection pressure, the following equation (2) can be obtained.

Po = Pa + (Fk, xm, dx ² / dt ² ) / Ap ... (2)

In equation (2), in the water spray initiation step, the mass m is first rapidly accelerated by the spring force F. Then, when the acceleration is completed, that is the inertial force (m and dx ² / dt ²⁾ is close to zero, the spring force (Fk and x) and the pressure (Po) to balance the water injection japhimyeonseo proceeds. The water spray pressure is high when the displacement (x) at the beginning of the water spray is small during the water spray process. On the other hand, as the water spray progresses and the coil spring 18 is restored, that is, as the displacement x increases, the water spray pressure Po gradually decreases. Immediately before the end of the water spray, the water spray pressure Po takes the lowest value during the water spray period. And when all the water sucked in the water storage chamber 123 is injected, the cam follower 221 collides with the stopper 28 or the cam 23, and the water injection pressure Po falls to atmospheric pressure. This decompression waveform of the water injection pressure Po is suitable for the insertion of the weft yarn Y.

That is, when water is injected from the weft insertion nozzle 27 according to the decompression waveform of the water injection pressure Po, the weft yarn Y is accelerated at the beginning of the weft insertion, and the water injection speed decreases with the weft insertion progress. Therefore, the weft speed is lowered. Therefore, loosening of the weft yarn can be prevented during the water spraying process, and stable weft insertion can be realized while keeping the weft (Y) posture straight.

The coil spring type water jet device having the characteristics as described above has been improved since the development of the water jet room. Therefore, the water spraying device of the coil spring method has been consistently adopted until now because of its reliability.

However, it is known that a resonance phenomena called surging occurs in the coil spring, and the surging vibration of the coil spring 18 adversely affects the insertion of the weft thread. That is, when the coil spring 18 generates surging vibration in the water spraying process, the surging vibration of the coil spring 18 is transmitted to the water in the water storage chamber 123 so that the waveform of the water spray pressure Po fluctuates. do. Waveform fluctuations in the water injection pressure Po resulting from the surging vibration of the coil spring 18 disrupt the weft Y insertion. Disruption of weft (Y) insertion reduces fabric quality.

The surging phenomenon of the coil spring 18 becomes remarkable as the temporal change of the water injection pressure Po increases, in other words, the higher the rotation speed of the loom. If the water spray cycle (= 60 sec / 1 loom revolutions per minute) coincides with the integral multiple of the surging vibration cycle, the surging is regularly excited and the vibration of the coil spring 18 becomes more severe.

In order to alleviate the surging vibration of the coil spring 18, a damping mechanism is added to the coil spring 18, or as a coil spring 18 as disclosed in Japanese Patent Laid-Open No. 10-299643, a non-linear spring (non- The use of a linear spring has been attempted. However, the countermeasure for adding the damping mechanism to the coil spring 18 has a problem that the structure is complicated and the cost is high. The countermeasure of using a nonlinear spring as the coil spring 18 has the problem that it is difficult to produce a preferable nonlinear spring which can effectively suppress generation of surging vibrations.

In order to speed up the loom, it is necessary to increase the weft (Y) insertion speed, that is, increase the water spray pressure (Po). In order to raise the water injection pressure Po, it can cope by increasing the compression amount of the coil spring 18. FIG. However, simply increasing the compression amount of the coil spring 18 and simply increasing the spring load causes the strength of the power transmission system such as the coil spring 18 and the cam lever 22 to be insufficient. Therefore, when the size of the power transmission system such as the coil spring 18 or the cam lever 22 is increased to increase the strength, the mass m of the formula (1) is increased and the ascending speed of the plunger 14 is lowered. Therefore, the rate of increase of the water injection pressure Po decreases. If the rate of increase of the water spray pressure (Po) is low, confusion of the spraying phenomenon of the jet tip is caused by the phenomenon that the slower water which is already released is overtaken by the faster water which is released later (hereinafter referred to as "overtaking phenomenon"). Done. As a result, high-speed droplets collide with the warp to scratch the warp, resulting in a draw streak in the textile product. This drawback degrades fabric quality.

It is an object of the present invention to provide a water jet which can further speed up a water jet room without causing a decrease in fabric quality.

1A is an overall view of a water spraying device immediately before the end of the water suction stroke of the first embodiment, and FIG. 1B is a side cross-sectional view of the weft insertion pump just before the end of the water suction stroke.

2A is an overall view of the water spraying device immediately before the end of the water spray stroke, and FIG. 2B is a side cross-sectional view of the weft insertion pump just before the water spraying stroke ends.

3 is a graph showing the relationship between the volume of the compression chamber and the pressure in the compression chamber.

4 is a graph showing the relationship between the axial length of the compression chamber and the thrust of the plunger at that time in terms of the air weight sealed in the compression chamber.

5A, 5C, and 5E are graphs showing measurement results of changes in water spray pressure in a water spray apparatus using a conventional coil spring, and FIGS. 5B, 5D, and 5F are water of the present embodiment using air spring means. It is a graph which shows the measurement result of the water injection pressure change in injector.

FIG. 6 is an overall view of a water spray device according to a second embodiment. FIG.

7 is a graph showing the relationship between the length of the diaphragm and the thrust of the plunger at that time.

Fig. 8 is a side sectional view of the weft insertion pump showing the third embodiment.

Fig. 9 is a side sectional view of the main portion of the water spraying device according to the fourth embodiment.

10 is a general view of a conventional water spraying device.

11 is a side cross-sectional view of the weft insertion pump 11.

12 is a graph showing the relationship between the length of the coil spring and the spring load.

13 is a graph showing the relationship between the loom rotation angle and the cam lift amount.

Explanation of symbols on the main parts of the drawings

12: pump housing 123: reservoir

13: reservoir forming cylinder 14: plunger

22: cam lever 23: cam

27: weft insertion nozzle 29, 47: weft insertion pump

30: cylinder 32: piston

33, 34: seal 35: compression chamber

36: air pressure source 37: air pipeline

38: pressure regulating valve 39: check valve

40: throttle passage 41: pressure gauge

43: diaphragm 431: pressure chamber

The present invention is directed to a water jet of a water jet room in which water is injected into the weft insert nozzle by a weft insert pump to inject water from the weft insert nozzle, and the weft insert is inserted by the water spray action of the weft insert nozzle. .

In addition, as a main aspect of the present invention, the water spraying device according to the present invention uses a fluid spring means having the pressure of the compressible gaseous fluid as a spring force as a driving source for generating the water spray pressure of the weft-inserting pump. do.

The fluid spring means is preferably an air spring means having air pressure as a spring force.

In the above configuration, since the surging vibration is small in the fluid spring means using the pressure of the compressible fluid as the spring force, there is little variation in the water injection pressure resulting from the surging vibration showing a wave shape. Therefore, the state in which the weft insertion is disturbed by the surging vibration is improved. In addition, since there is no conventional coil spring, the mass (m) can be reduced in the above formula (1) to increase the rate of increase of the water injection pressure.

In addition, the weft insertion pump is a pump housing, a plunger accommodated reciprocally in the pump housing, a cam mechanism for driving the plunger in the reciprocating direction, the fluid spring means for elastically supporting the plunger in the double direction, and the And a storage compartment partitioned within the pump housing so that the volume is changed by the reciprocating motion of the plunger, wherein water is sucked into the storage chamber by the pulsating operation of the plunger, and the water in the storage chamber by the double acting operation of the plunger. It is preferable to be pressurized by this weft insertion nozzle.

According to such a configuration, water is sucked into the reservoir chamber when the cam mechanism drives the plunger in the king direction. When the cam mechanism allows movement in the double acting direction of the plunger, the plunger is doubled by the fluid pressure of the fluid spring means. Conventional coil spring type weft insertion pumps can be retrofitted to the weft insertion pumps of the present invention by minor component changes and additions that replace the coil springs with fluid spring means.

The fluid spring means further includes a pressure chamber forming housing forming a volume changeable pressure chamber and pressure transfer means for transmitting a pressure in the pressure chamber to the plunger, the volume of the pressure chamber being a pulsating motion of the plunger. It can be reduced by the swinging operation of the cam mechanism that causes the.

When the volume of the pressure chamber is increased by the fluid pressure in this way, the plunger doubles and water in the reservoir is pumped to the weft insertion nozzle.

Preferably, the pressure transfer means is a piston coupled to the plunger, and the pressure chamber forming housing is a cylinder that reciprocally receives the piston in the pump housing.

In this configuration, when the piston defining the pressure chamber in the cylinder is moved by the fluid pressure, the plunger doubles and water in the reservoir is pumped to the weft insertion nozzle.

Moreover, it is preferable to make the said pressure chamber into the compression chamber which compresses a fluid according to the pulsation of the said plunger.

According to this configuration, the compression reaction of the fluid compressed in the compression chamber is used to double acting the plunger.

And a quasi-initial pressure setting means for setting a quasi-initial pressure of the fluid spring means, and the quasi-initial pressure can be the pressure in the compression chamber at the time of starting to compress the fluid in the compression chamber. have.

According to this configuration, the fluid in the compression chamber is started to be compressed in the quasi-initial pressure state set by the quasi-initial pressure setting means. The pressure in the compression chamber during the water spray process is above the quasi-initial pressure. Since the stroke of the plunger is constant for each weft insertion, the pressure at the maximum compression of the fluid in the compression chamber is constant, and the water spray is started under the pressure condition at the maximum compression of the fluid in the compression chamber.

Further, it is preferable to include initial pressure setting means for setting the initial pressure of the fluid spring means, and to set the initial pressure to the pressure in the pressure chamber at the start of water spraying.

According to this configuration, the fluid pressure in the pressure chamber is reset to the initial pressure for each weft insertion, and the water spray is started when the fluid pressure in the pressure chamber is in the initial pressure state. The pressure in the compression chamber during the water spray process is below the initial pressure.

In addition, the initial pressure setting means may be a fluid pressure source for supplying a fluid to the fluid spring means, a pressure setting means for setting the pressure of the fluid supplied to the fluid spring means, and a fluid of the pressure set by the pressure setting means And a supply switching means for switching to a state in which the fluid spring means can be supplied and to a state in which the fluid can not be supplied, wherein the supply switching means can be in a state capable of supplying before the water spray stroke and after the water suction stroke.

The period before the water spray stroke and after the water suction stroke is most suitable as the period for accurately resetting the fluid pressure in the pressure chamber to the initial pressure for each weft insertion.

Further, it is preferable that the pressure chamber forming housing is a diaphragm connected to the cam mechanism through a displacement carrier, and the pressure of the pressure chamber in the diaphragm is transmitted to the plunger through the displacement carrier and the cam mechanism. Simplified construction greatly improves the durability of the weft insertion pump.

Then, the piston is mounted on the cam mechanism side of the plunger in a axial direction to allow the plunger to be screwed, and the piston is relatively rotatable but the piston is prevented from moving in the axial direction. It is also preferable to change the initial volume of the pressure chamber in accordance with the change of the threaded mounting position of the positioning body.

According to this configuration, the gradient of the water injection pressure of the water injection device can be easily changed.

The initial volume of the pressure chamber in accordance with a change in the threaded mounting position of the male screw with respect to the female screw, wherein the male screw is mounted to the diaphragm and the displacement carrier is screwed to the female screw. You can also change

According to this configuration, the gradient of the water injection pressure of the water injection device can be easily changed.

Further, a coil spring may be accommodated in the pressure chamber formed in the pressure chamber forming housing.

According to this configuration, the suppressing effect of surging vibration is slightly less, but there is an advantage that the original pressure of the air pressure source can be reduced.

Embodiment of the invention

1st Embodiment

EMBODIMENT OF THE INVENTION Hereinafter, 1st Embodiment which actualized this invention is described based on FIG.

The same components as in the conventional apparatus of Figs. 10 and 11 are denoted by the same reference numerals and the detailed description thereof will be omitted.

As shown in FIG. 1B, the cylinder 30 is screwed to the pump housing 12 constituting the weft insertion pump 29. The cylinder 30 is fixed to the pump housing 12 by tightening the locking nut 31. The cylinder 30 is slidably accommodated so that the piston 32 surrounds the water storage chamber formation cylinder 13. The piston 32 is fixedly fixed to the plunger 14. The piston 32 and the plunger 14 are movable integrally in the axial direction of the cylinders 30 and 13.

The seal 30 is attached to the cylinder 30 so that sliding contact with the outer peripheral surface of the piston 32 is possible. The seal 34 is attached to the piston 32 so that sliding contact with the inner peripheral surface of the cylinder 30 is possible. A compression chamber 35 is formed between the inner circumferential surface of the cylinder 30 and the outer circumferential surface of the piston 32 and between the seals 33 and 34.

An air pressure source 36 is connected to the compression chamber 35 via an air line 37. On the air line 37, a pressure regulating valve 38 and a check valve 39 having a relief function are formed. The throttle passage 40 is formed in parallel with the check valve 39 between the pressure regulating valve 38 and the compression chamber 35. A pressure gauge 41 is connected to the air line 37 between the pressure regulating valve 38 and the check valve 39. The pressure gauge 41 is for measuring the air pressure between the pressure regulating valve 38 and the check valve 39. The air pressure between the pressure regulating valve 38 and the check valve 39 is set by operating the pressure regulating valve 38 while looking at the pressure gauge 41. The pressure regulating valve 38 having a relief function always maintains the pressure in the air line 37 between the pressure regulating valve 38 and the check valve 39 at the pressure set by the pressure regulating valve 38. The pressure Pi (semi-initial initial pressure) in the compression chamber 35 set by the pressure regulating valve 38 is the pressure when the piston 32 in the compression chamber 35 is located at the far right as shown in FIG. 2B. to be.

When the cam lever 22 rotates left about the support shaft 222, the plunger 14 and the piston 32 move in the moving direction shown by the arrow Q of FIGS. 1A and 1B. When the plunger 14 moves in the reciprocating direction indicated by the arrow Q, the volume of the storage chamber 123 increases, and water in the float box 25 is sucked into the storage chamber 123. When the piston 32 moves in the reciprocating direction indicated by the arrow Q, the volume of the compression chamber 35 decreases and the pressure in the compression chamber 35 starts to rise at the quasi-initial pressure Pi. The start of pressure rise in the compression chamber 35 causes the check valve 39 to close. Then, the pressure in the compression chamber 35 rises as the piston 32 moves, and the pressure in the compression chamber 35 becomes the maximum at the time when the movement of the piston 32 ends. The pressure at the start of air compression in the compression chamber 35 is defined as the quasi-initial pressure Pi set by the pressure regulating valve 38 in accordance with the presence of the check valve 39. That is, the pressure in the compression chamber 35 is maintained at a level equal to or higher than the quasi-initial pressure Pi set by the pressure regulating valve 38. Curve Pb in the graph of FIG. 3 shows the relationship between the volume of the compression chamber 35 and the pressure in the compression chamber 35.

The pressure change represented by the curve Pb of FIG. 3 is expressed as follows. In general, the change in the actual pressure P when the air is compressed and expanded in the air compressor is a polytropic change represented by the following equation (3).

P ・ V ⁿ = constant ‥‥ (3)

In formula (3), n is a polytropic index and n = 1.2 normally. When the volume of the compression chamber 35 is reduced from the initial volume Vo to (Vo-s.Aa), the following equation (4) is established.

P. (Vo-s.Aa) ⁿ = PiVo ⁿ ... (4)

In Formula (4), s is the displacement amount of piston 32 (s = 0 shall be set at the start of compression), and Aa is the cross-sectional area of the compression chamber 35. As shown in FIG.

Therefore, the pressure P in the compression chamber 35 when the volume of the compression chamber 35 is (Vo-s * Aa) is represented by following formula (5).

P = PiVo ⁿ / (Vo-sAa) ⁿ ... (5)

That is, curve Pb of FIG. 3 is represented by Formula (5). When the displacement amount s increases, that is, the volume of the compression chamber 35 decreases, the pressure P in the compression chamber 35 increases along the curve Pb as indicated by the arrow U1 in FIG. 3. The pressure Pm of FIG. 3 is the pressure when the volume Vo-s * Aa of the compression chamber 35 is minimum.

When the cam follower 221 passes the maximum diameter position Ma of the cam surface 231 of the cam 23, the cam lever 22 moves right about the support shaft 222, and the plunger 14 and The piston 32 moves in the double acting direction shown by the arrow R of FIGS. 2A and 2B by the pressure Pm of the compressed air in the compression chamber 35. When the plunger 14 moves in the double acting direction indicated by the arrow R, the water in the reservoir 123 is pressurized. The pressurized water in the reservoir 123 is pumped to the weft insertion nozzle 27. Water pressurized by the weft insertion nozzle 27 is sprayed from the weft insertion nozzle 27.

On the other hand, when the displacement amount s decreases, i.e., the volume of the compression chamber 35 increases, the pressure P in the compression chamber 35 decompresses along the curve Pb as indicated by the arrow U2 in FIG. do. As indicated by the arrow U2 in FIG. 3, the air pressure in the compression chamber 35 along the curve Pb is the water spray pressure of the weft insertion nozzle 27.

In the first embodiment, the following effects can be obtained.

(1-1) In the graphs of Figs. 5A, 5C and 5E, the curves C1, C2 and C3 show the measurement results of the water jet pressure change of the water jet device using the conventional coil spring. The curves E1, E2, E3 in the graphs of FIGS. 5B, 5D and 5F are patterns using air spring means consisting of a cylinder 30, a piston 32, a seal 33, 34 and a compression chamber 35. The measurement result of the water injection pressure change of the water injection device of embodiment is shown. 5A and 5B show a case where the loom rotation speed is 700 rpm, FIGS. 5C and 5D show a case where the loom rotation speed is 800 rpm, and FIGS. 5E and 5F show a case where the loom rotation speed is 1000 rpm.

When the loom rotation speed is 700 rpm, the water of the present embodiment using the air spring means as a drive source for generating the water injection pressure of the conventional water jet device using the coil spring as the drive source for the water injection pressure generation of the weft insertion pump and the weft insertion pump. Even in the injector, the water jet pressure due to surging vibration does not appear to fluctuate greatly.

When the rotation speed of the loom reaches 800 rpm, as shown in FIG. 5D, the water spraying pressure of the present embodiment does not appear to fluctuate greatly due to surging vibration, but as shown in FIG. 5C, the conventional water spraying apparatus is shown. In this case, the fluctuation of water injection pressure due to surging vibration is remarkable.

When the loom rotation speed reaches 1000 rpm, as shown in Fig. 5E, in the conventional water spraying device, the fluctuation of the water spraying pressure caused by surging vibration is greatly increased. However, as shown in FIG. 5F, even if the rotation speed of the loom reaches 1000 rpm, the water injection pressure resulting from the surging vibration does not appear to fluctuate greatly.

In the air spring means which uses the pressure of the air which is a compressible fluid as the spring force, the surging vibration is very small compared with the coil spring. Therefore, the fluctuation | variation which seems to wave largely the water injection pressure resulting from surging vibration is small. In the case of using the coil spring, the occurrence of surging vibration becomes remarkable as the loom rotation speed increases, but in the water spraying device of the present embodiment using the air spring means, no surging vibration occurs even when the loom rotation speed is 1000 rpm. Therefore, the weft yarn Y is stably inserted even in a high speed rotation state of the loom 1000 rpm. Stable insertion of the weft yarn Y in the high speed operation of the loom enables high speed operation of the loom without compromising fabric quality.

(1-2) In said Formula (1), mass (m) is a sum of the equivalent mass of the movable body of a power transmission system. Therefore, the smaller the mass m, the higher the initial velocity at the time of double acting of the plunger 14, that is, the rate of increase of the water injection pressure. In the water spraying apparatus of this embodiment which does not use a coil spring, the mass (m) of said Formula (1) becomes small compared with the conventional water spraying apparatus which uses a coil spring. The reduction of the mass m due to the absence of the coil spring speeds up the rate of increase of the water jet pressure and suppresses the occurrence of "overtaking" of the jet. Therefore, the confusion of the spray shape of the jet tip caused by the "overtaking phenomenon" of the jet is suppressed. As a result, a situation in which high-speed water droplets collide with the warp and damage the warp is avoided, and the degradation of the fabric quality due to the generation of the tangle is avoided.

(1-3) The weft insertion pump 29 includes a pump housing 12 having a reservoir 123, a plunger 14, a reservoir forming cylinder 13, an air spring means, a locking nut 17, a joint ( 21, a cam mechanism composed of a cam 23 and a cam lever 22. The conventional weft insertion pump 11 of FIGS. 10 and 11 includes a pump housing 12 having a reservoir 123, a plunger 14, a reservoir forming cylinder 13, a spring seat 15, a spring cap ( 16), a cam mechanism composed of a locking nut 17, a joint 21, a cam 23, and a cam lever 22.

The air spring means of the weft insertion pump 29 consists of a cylinder 30, a piston 32 and seals 33, 34. The spring seat 15 constituting the weft insertion pump 11 can be operated by the piston 32 constituting the weft insertion pump 29. In addition, the pump housing 12, the plunger 14, the reservoir chamber forming cylinder 13, the locking nut 17, and the cam mechanism which comprise the conventional weft insertion pump 11 are comprised of the weft insertion pump 29 as it is. Can be used as a part.

That is, the conventional coil spring type weft insertion pump 11 is a weft insertion pump of the present invention by changing and adding a small part that changes the spring cap 16 to the cylinder 30 and adds the seals 33 and 34. Can be converted to (29).

(1-4) The change in the water jet pressure obtained by the water jetting apparatus of this embodiment is as shown in Fig. 3, but the pressure gradient of the time change during the water jet stroke is expressed by the following equation (6).

dP / dt = (dP / ds) (ds / dt) ... (6)

In the conventional water spraying device using the coil spring 18, the pressure gradient dP / dt shows a relatively linear change when no external inaccuracy such as surging is involved. On the other hand, the pressure gradient dP / dt of the present embodiment using the air spring means is as designed by the compression chamber 35, considering that dP / ds is a curve obtained by differentiating equation (5) by the displacement amount s. It is also possible to realize changes that deviate significantly from the straight line.

As a result, by changing the air pressure or the volume of the air chamber in the air spring pump, it is a non-linear characteristic of the air spring and can change the spring force or the gradient of the spring force, thereby allowing various weaving conditions (eg fabric width) , Water inclination type, loom rotation speed, etc.) can realize the water injection pressure of a wide range of conditions.

(1-5) Curves Pb1, Pb2, Pb3, Pb4, and Pb5 in the graph of Fig. 4 indicate the air weight sealed in the compression chamber 35 in terms of the axial length H of the compression chamber 35. The relationship between the load of the piston 32 (that is, the thrust of the plunger 14) at that time is shown. The air weights in the curves Pb1, Pb2, Pb3, Pb4, Pb5 decrease in this order. That is, in the compression chamber 35, the initial air sealing pressure (the quasi-initial pressure Pi set by the pressure regulating valve 38) decreases the curves Pb1, Pb2, Pb3, Pb4, and Pb5 in this order.

When the air weight sealed in the compression chamber 35 is constant (curve Pb4 in the illustrated example), the axial length H of the compression chamber 35 is shortened, so that the operating range of the piston 32, namely When the operating range of the plunger 14 ('h1' in the illustrated example) is selected, the gradient of the plunger 14's thrust and its change is increased. On the contrary, when the length H in the axial direction of the compression chamber 35 is extended, and the operating range of the plunger 14 ('h2' in the illustrated example) is selected, the gradient of the thrust of the plunger 14 and its change is obtained. Becomes smaller. Increasing the air weight sealed in the compression chamber 35 increases the thrust level of the plunger 14 as a whole. Moreover, when the air weight sealed in the compression chamber 35 is increased, the gradient with respect to the change of thrust of the plunger 14 becomes large. It can be seen, for example, by comparing the gradient of each curve Pb1, Pb2, Pb3, Pb4, Pb5 in the illustrated operating range 'h2'.

The selection of the thrust magnitude or thrust gradient of this plunger 14 is made possible by the nonlinear nature of the air spring of the air spring means. That is, the water spraying device of the present embodiment using the air spring means makes it possible to realize water spray pressure under a wide range of conditions that can cope with various weaving conditions (e.g., fabric width, warp type, loom rotation speed, etc.). .

(1-6) In the conventional water spray apparatus using the coil spring 18, as shown in FIG. 12, the spring load of the coil spring 18, that is, the water spray pressure, can be changed. Therefore, it is necessary to adjust the initial compression amount by adjusting the threaded insertion position of the spring cap 16 with respect to the pump housing 12. In this adjustment, it is necessary to repeat the operation of observing the weft insertion situation with, for example, a stroboscope and adjusting the screw insertion position of the spring cap 16 in accordance with the observation situation. Adjusting the threaded insertion position of the spring cap 16 is an annoying task that the coil spring 18 must perform while receiving a strong spring load.

In the water injection device of the present embodiment, in order to change the water injection pressure, the pressure adjusting valve 38 may be operated to adjust the quasi-initial pressure Pi in the compression chamber 35, and this pressure adjustment operation is easy.

(1-7) The check valve 39 serves to block the passage between the pressure regulating valve 38 and the pressure chamber 35 when compressing air in the compression chamber 35, and the minimum pressure of the compression chamber 35. (I.e., the quasi-initial pressure Pi set by the pressure regulating valve 38), and serves to supplement the air leakage when air leaks from the compression chamber 35.

When the sealing function by the seals 33 and 34 is complete and there is no air leakage from the compression chamber 35, air in and out of the check valve 39 during loom operation is operated unless the pressure regulating valve 38 is operated. And the check valve 39 only acts as a stop valve.

When there is no air leakage from the compression chamber 35, the pressure in the compression chamber 35 can be increased by the operation of the pressure regulating valve 38, but the pressure reduction by the action of the check valve 39 is possible. Not. The throttle passage 40 actively leaks air in the compression chamber 35 to the pressure regulating valve 38 side. The configuration in which the throttle passage 40 is formed in parallel with the check valve 39 makes it possible to depressurize the inside of the compression chamber 35 when the seal function by the seals 33 and 34 is fully operated. This decompressable configuration enables setting of the quasi-initial pressure Pi of the compression chamber 35. The air pressure source 36, the pressure regulating valve 38, the check valve 39 and the throttle passage 40 constitute semi-initial pressure setting means for setting the quasi-initial pressure in the fluid spring means.

The air in the compression chamber 35 starts to be compressed in the quasi-initial pressure Pi set by the quasi-initial pressure setting means. The pressure in the compression chamber 35 of the water spray process is equal to or higher than the quasi-initial pressure Pi. Since the stroke of the plunger 14 is constant for each weft insertion, the pressure when the air in the compression chamber 35 is maximally compressed is always constant. Therefore, the water spray is started under the pressure Pm state when the air in the compression chamber 35 is compressed to the maximum. The water spraying pressure at the beginning of the water spraying always corresponds to the pressure Pm higher than the quasi-initial pressure Pi set by the pressure regulating valve 38. In the water spraying process, the water spraying pressure is equal to or less than the pressure Pm and is' Pi. 'Is in the range above. Therefore, in the weft insertion, the pressure at the beginning of water spraying start, which is an important factor, can be indirectly controlled, so that the water spray pressure with good precision can be adjusted.

(1-8) In the air jet room, which is similar in principle to the water jet room, the automation of the weft insertion is controlled well by applying feedback control to the air pressure for weft insertion according to the weft insertion situation. This automation frees the operator from cumbersome pressure adjustments, greatly improving work efficiency. This is because in the air jet room, a method of directly adjusting the injection pressure of the weft inserting air by a pressure regulating valve is adopted, and it is relatively easy to control the pressure regulating valve electrically. In this embodiment as well, the pressure regulating valve 38 is electrically controlled, so that feedback control can be applied to the water jet pressure in accordance with the weft insertion situation.

2nd Embodiment

Next, 2nd Embodiment of FIG. 6 and FIG. 7 is described. The same code | symbol is used for the same component part as 1st Embodiment, and the detailed description is abbreviate | omitted.

As shown in FIG. 6, a rubber diaphragm 43 is attached to the air spring adjustment base 42. The diaphragms 43 and the cam levers 22 are equipped with displacement carriers 45 and 46. The displacement carriers 45 and 46 are in contact with each other and the pressure of the pressure chamber 431 in the diaphragm 43 is transmitted to the plunger 14 through the displacement carriers 45 and 46, the cam lever 22 and the joint 21. do. In the weft insertion pump 47 of 2nd Embodiment, the cylinder 30 and piston 32 which comprise the weft insertion pump 29 of 1st Embodiment are excluded.

The pressure chamber 431 in the diaphragm 43 is connected to the air pressure source 36 via the air line 37. On the air line 37, a pressure regulating valve 38 and an electromagnetic opening and closing valve 44 are formed. A pressure gauge 41 is connected to the air line 37 between the pressure regulating valve 38 and the solenoid valve 44. The diaphragm 43 is composed of a pressure chamber forming housing constituting the air spring means.

The solenoid valve 44 is opened by excitation in a certain period immediately before the start of water injection (period indicated by 'T' in Fig. 13), and the initial pressure Pk set by the pressure regulating valve 38 is The pressure chamber 431 in the diaphragm 43 is supplied. The electromagnetic opening and closing valve 44 is composed of supply switching means for switching the pressure air set by the pressure regulating valve 38, which is a pressure setting means, to a state capable of supplying the fluid spring means and a non-supply state. The electromagnetic switching valve 44, which is a supply switching means, becomes a state capable of being supplied by the excitation in the period T before the water injection stroke and after the water intake stroke.

In the second embodiment, the following effects can be obtained.

(2-1) The water spraying pressure at the beginning of water spraying always matches the initial pressure Pk set by the pressure regulating valve 38, and the water spraying pressure in the water spraying process is in the range of the initial pressure Pk or less. . Therefore, it is possible to directly control the pressure at the beginning of water spraying start, which is an important factor in weft insertion, so that the water jet pressure can be adjusted with high precision. Moreover, the air pressure source 36 which is a fluid pressure source, the pressure regulating valve 38 with a relief function, and the solenoid opening / closing valve 44 set the initial pressure of the fluid spring means at the time of the injection start of every water spray. Configure the initial pressure setting means.

(2-2) Since the seals 33 and 34 in the first embodiment become unnecessary, the durability of the weft insertion pump 47 is significantly improved compared to the weft insertion pump 29 of the first embodiment.

(2-3) In the graph of Fig. 7, the curves Pc1, Pc2, Pc3, Pc4 are in the state where the load on the plunger 14 is zero (i.e., the cam follower 221 has the maximum diameter position of the cam surface 231). The air pressure sealed to the diaphragm 43 in the state of (Ma) is the parameter of the length (L: shown in FIG. 6) of the diaphragm 43 and the load of the piston 32 at that time (that is, The thrust of the plunger 14). The pressure level of air in the curves Pc1, Pc2, Pc3, Pc4 is decreasing in this order. That is, the initial air sealing pressure (initial pressure Pk set by the pressure regulating valve 38) in the diaphragm 43 is lowered in the order of curves Pc1, Pc2, Pc3, Pc4.

If the air pressure sealed in the diaphragm 43 is constant (curve Pc3 in the illustrated example), the length L of the diaphragm 43 is shortened so that the operating range of the plunger 14 ('h3' in the illustrated example) ), The thrust of the plunger 14 increases and at the same time the gradient for the change decreases. On the contrary, if the length L of the diaphragm 43 is made longer and the operating range of the plunger 14 ('h4' in the illustrated example) is selected, the thrust of the plunger 14 is small and the gradient for the change is Gets bigger Increasing the initial pressure Pk supplied to the pressure chamber 431 in the diaphragm 43 increases the thrust level of the plunger 14 as a whole. Moreover, when the initial pressure Pk supplied to the diaphragm 43 is increased, the gradient with respect to the thrust change of the plunger 14 becomes large. This can be seen, for example, by comparing the gradients of the respective curves Pc1, Pc2, Pc3, Pc4 in the illustrated operating range 'h4'.

This selection of the thrust size or thrust gradient of the plunger 14 is made possible by the nonlinear nature of the air spring supplied to the compression chamber 431 in the diaphragm 43 constituting the air spring means. That is, even in the water spray apparatus of 2nd Embodiment, the water spray pressure of very wide conditions which can respond to various weaving conditions are realizable.

(2-4) Some time period (T) immediately before the start of the water spray is a period before the water spray stroke and after the water suction stroke. This period T is when the volume of the pressure chamber 431 is minimum, and the air pressure in the pressure chamber 431 when the volume of the pressure chamber 431 is minimum is reset to the initial pressure Pk for each weft insertion. . Therefore, the period before the water spray stroke and after the water suction stroke is most suitable as a period for accurately resetting the air pressure in the pressure chamber 431 to the initial pressure Pk at the start of the water spray.

(2-5) The same effect as (1-8) of 1st Embodiment can be acquired.

Third embodiment

Next, 3rd Embodiment of FIG. 8 is described. The same code | symbol is used for the same component part as 1st Embodiment, and the detailed description is abbreviate | omitted.

As for the plunger 14, the nut type positioning body 48 is screwed together. The piston 32 is supported by the positioning body 48 so that relative rotational movement is possible. Movement of the piston 32 in the axial direction with respect to the positioning body 48 is prevented by a pair of snap rings 49 and 50. The position adjusting body 48 is fixed to the plunger 14 by tightening the locking nut 51 screwed to the plunger 14.

In the case of changing the operating range of the plunger 14 in the graph of FIG. 4 from 'h2' to 'h1', the screw-mounted position of the position adjusting body 48 is closer to the joint 21 side as indicated by the broken line. Just do it. As the threaded mounting position changes, the seal 34 comes close to the seal 33. As a result, the length H of the compression chamber 35 when the piston 32 is in the double-acting end position becomes shorter than in the case of the solid line position in FIG. 8.

The water spray pressure and its gradient (corresponding to the spring constant) have the most suitable values according to the weaving conditions described above. In the conventional water spraying apparatus, when the weaving condition is changed, it is necessary to select the coil spring to meet the changed weaving condition. However, coil springs have manufacturing constraints and their lengths and spring constants in themselves, which makes it difficult to always select the most suitable coil spring. In addition, to cope with various weaving conditions, a variety of coil springs should be prepared, which is uneconomical in terms of cost and management.

In the water spraying apparatus of the third embodiment, the water spraying pressure is changed as described in the first embodiment, and the screw of the position adjusting body 48 with respect to the plunger 14 is used to change the gradient of the water spraying pressure. This can be done by changing the expression mounting position. The change of the screw mounting position of the positioning body 48 can be easily performed by reducing the pressure in the compression chamber 35 to atmospheric pressure.

Fourth embodiment

Next, 4th Embodiment of FIG. 9 is described. The same code | symbol is used for the same component part as 2nd Embodiment, and the detailed description is abbreviate | omitted.

The female screw body 52 is attached to the diaphragm 43, and the male screw body 53 is screwed together to the female screw body 52. As shown in FIG. The male screw body 53 is fixed to the female screw body 52 by tightening a locking nut 54 screwed to the male screw body 53. The male screw body 53 abuts against the displacement carrier 46 on the cam lever 22 side.

When the operating range of the plunger 14 is changed from 'h4' to 'h3' in the graph of FIG. 7, the female thread body 52 is brought closer to the air spring adjusting base 42 side as indicated by the broken line. 52, the screw mounting position of the male screw body 53 may be changed. In accordance with the change of the threaded mounting position, the length L of the diaphragm 43 when the plunger 14 is in the double-acting end position becomes shorter than in the case of the solid line position in FIG. 9.

In the water spraying device of the fourth embodiment, in order to change the gradient of the water spraying pressure, the threaded mounting position of the male screw body 53 with respect to the female screw body 52 may be changed. The change of the threaded mounting position of the male screw body 53 can be easily performed by reducing the pressure in the diaphragm 43 to about atmospheric pressure.

In the present invention, the following embodiments are also possible. for example,

(1) using the initial pressure setting means consisting of the pressure regulating valve 38 and the electromagnetic open / close valve 44 in the second embodiment in the first embodiment,

(2) accommodating the coil spring in the compression chamber 35 in the first embodiment and the third embodiment, and generating the thrust of the plunger 14 by the air spring and the coil spring,

(3) The coil spring is accommodated in the pressure chamber 431 in the second and fourth embodiments, and the thrust of the plunger 14 is shared between the air spring and the coil spring to generate the coil spring. In (2) and (3), the suppressing effect of surging vibration is slightly less, but there is an advantage that the original pressure of the air pressure source 36 can be reduced.

(4) using a mechanical on / off valve to open and close in synchronization with the loom rotation in place of the solenoid valve 44; and

(5) The use of a fluid spring means which makes the pressure of a compressible gaseous fluid other than air, such as an inert gas (nitrogen gas, carbon dioxide, etc.) a spring force.

According to the present invention, there is provided a water spray apparatus capable of further speeding up a water jet room without causing a decrease in fabric quality.

Claims (13)

In the water jet device of the water jet room to pump water into the weft insertion nozzle by the weft insertion pump to inject water from the weft insertion nozzle, and insert the weft by the water spray action of the weft insertion nozzle, A water jet device in a water jet room using a fluid spring means using the pressure of a compressible gaseous fluid as a spring force as a drive source for generating a water jet pressure of the weft insertion pump. The method of claim 1, And the fluid spring means is an air spring means having air pressure as a spring force. The method according to claim 1 or 2, The weft insertion pump, Pump housing, A plunger accommodated reciprocally in the pump housing, A cam mechanism for driving the plunger in the king direction; The fluid spring means for elastically supporting the plunger in a double acting direction, and And a reservoir compartment defined in the pump housing such that the volume is changed by the reciprocating motion of the plunger, The pulsing operation of the plunger sucks water into the water storage chamber, and the double acting operation of the plunger pumps water in the water storage chamber into the weft insert nozzle. The method of claim 3, wherein The fluid spring means, A pressure chamber forming housing forming a volume changeable pressure chamber, and And a pressure transmitting means for transmitting the pressure in the pressure chamber to the plunger, And the volume of the pressure chamber is reduced by the actuation of the cam mechanism resulting in the actuation of the plunger. The method of claim 4, wherein The pressure transmitting means is a piston coupled to the plunger, And the pressure chamber forming housing is a cylinder that reciprocally receives the piston in the pump housing. The method of claim 5, wherein And the pressure chamber is a compression chamber that compresses a fluid in response to the pulsation of the plunger. The method of claim 6, A quasi-initial pressure setting means for setting a quasi-initial pressure of the fluid spring means, And said quasi-initial pressure is the pressure in said compression chamber at the time of starting to compress the fluid in said compression chamber. The method of claim 4, wherein An initial pressure setting means for setting an initial pressure of the fluid spring means, And said initial pressure is the pressure in said pressure chamber at the start of water injection. The method of claim 8, The initial pressure setting means, A fluid pressure source for supplying fluid to the fluid spring means, Pressure setting means for setting a pressure of the fluid supplied to the fluid spring means, and And a supply switching means for switching the fluid of the pressure set by the pressure setting means into a state capable of supplying the fluid spring means and a state in which the fluid cannot be supplied. And the supply switching means is capable of being supplied in a period before the water spray stroke and after the water suction stroke. The method of claim 4, wherein The pressure chamber forming housing is a diaphragm connected to the cam mechanism via a displacement carrier; The pressure of the pressure chamber in the diaphragm is transmitted to the plunger through the displacement carrier and the cam mechanism, the water jet device in the water jet room. The method of claim 5, wherein On the cam mechanism side of the plunger, a position adjusting member capable of reciprocating in the axial direction of the plunger is screwed. The position adjusting body is equipped with the piston which can rotate relatively but is prevented from moving in the axial direction. And an initial volume of the pressure chamber can be changed in accordance with a change in the screw mounting position of the position adjusting body. The method of claim 10, The diaphragm is equipped with a female thread, The displacement carrier is a male screw threaded to the female screw body, And the initial volume of the pressure chamber can be changed in accordance with a change in the threaded mounting position of the male threaded body relative to the female threaded body. The method of claim 4, wherein And a coil spring in the pressure chamber formed in the pressure chamber forming housing.