KR100505543B1 - Water-spraying device of water jet loom - Google Patents

Abstract

When the electromagnetic open / close valve 49 is in an open state capable of supplying water, and the electromagnetic open / close valve 45 is in a closed state in which water cannot be supplied, the high-pressure water from the water supply source 29 is the weft insertion pump 64. The air pressure in the pressure chamber 321 in the tank is overcome and supplied to the weft insertion pump 64. When the electromagnetic open / close valve 49 is in a closed state in which water cannot be supplied, and the electronic open / close valve 45 is in an open state in which water can be supplied, water in the storage chamber 641 is discharged into the pressure chamber 321. It is supplied to the weft insertion nozzle 47 by air pressure. The electromagnetic opening and closing valve 45 is excited by a command from the control device 57.

Description

Water spray device in water jet room {WATER-SPRAYING DEVICE OF WATER JET LOOM}

The present invention relates to a water spraying device in a waterjet room for pumping water from a weft insertion nozzle by pressurizing water into a weft insertion nozzle by a weft insertion pump, and inserting a weft thread by a water injection action of the weft insertion nozzle.

Fig. 16 shows the water content value in the conventional waterjet room, and Fig. 17 shows the internal structure of the weft insertion pump 11 constituting the conventional water content value. In the cylindrical pump housing 12 of the weft insertion pump 11, a storage chamber formation cylinder 13 is accommodated and fixed, and a plunger 14 is slidably accommodated in the cylinder of the storage chamber formation cylinder 13. have. The spring seat 15 is attached to the plunger 14, and the 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 a lock nut 17. A coil spring 18 is interposed 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 interposed between the reservoir 123 and the suction port 121 and between the reservoir 123 and the discharge port 122. As shown in FIG. 16, the suction pipe 24 connected to the suction port 121 is connected to the float box 25, and the discharge pipe 26 connected to the discharge port 122 is the weft insertion nozzle 27. As shown in FIG. )

The plunger 14 is connected to the cam lever 22 via the joint 21. The cam lever 22 is foldable 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 in Fig. 16 at a constant angular speed in synchronization with the rotation of the loom. The plunger 14 and the spring seat 15 reciprocate integrally by the reciprocating oscillation of the cam lever 22. In FIG. 16, when the cam lever 22 rotates left about the support shaft 222 by the rotational force of the cam 23, the plunger 14 and the spring seat 15 resist the spring force of the coil spring 18. Dong (move from right to left in Figure 17). The swinging action of the spring seat 15 compresses the coil spring 18, and the swinging action of the plunger 14 sucks a certain amount of water from the float box 25 into the reservoir 123 through the suction pipe 24. . While the check valve 19 is opened and absorbed into the water storage chamber 123, the check valve 20 is closed so that 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 moves away from the cam face 231 of the cam 23 to restore the restoring force of the coil spring 18. The receiving plunger 14 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 opens, and the pressurized water in the reservoir 123 is discharged through the discharge pipe 26 to the weft insertion nozzle 27. Is sent to. Water pumped into the weft insertion nozzle 27 is ejected from the weft insertion nozzle 27 so that the weft yarn Y is inserted into the warp opening. The cam floor 221 away from the cam surface 231 of the cam 23 abuts against the cam surface 231, or one end of the cam lever 22 abuts against the injection quantity limiting stopper 28 formed separately. Water spray ends.

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

The curve K in the graph of FIG. 18 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 from the minimum diameter position of the cam surface 231 of the cam 23). 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 stroke strokes in which the cam lift amount decreases rapidly from the maximum value.

The weft insertion pump 11 obtains a driving force from the linearly driven motor through the cam 23 and the cam lever 22. Therefore, in the case where it is desired to change the injection timing of the weft insertion nozzle in accordance with the change of the foam type, the mounting of the cam 23 to the support shaft 232 of the cam 23 is adjusted, or the cam 23 is used. Or the screwing position of the lock nut 283 with respect to the female thread 281 in the stopper 28 needs to be changed. The necessity of such work hinders the automation of the waterjet room.

It is an object of the present invention to provide a water moisturizer suitable for the automation of a waterjet room.

Therefore, the present invention pressurizes water from the weft insertion nozzle by the weft insertion nozzle by a weft insertion pump using the spring means as the driving source for generating the water injection pressure, and sprays water from the weft insertion nozzle, and the weft yarn by the water injection action of the weft insertion nozzle. In the invention of claim 1, a water supply source capable of overcoming the spring force of the spring means to supply high-pressure water to the weft insertion pump, and the weft yarn from the water supply source. Between the first water supply state switching means which is switched between a state capable of supplying high pressure water with an insertion pump and a state in which it cannot be supplied, and a state in which water can be supplied from the weft insertion pump to the weft insertion nozzle and cannot be supplied. When supplying the high pressure water to the weft insertion pump from the water supply source; Group constituting the can having a third water supply state switching means to stop the injection device can be supplied to the weft insertion nozzle, direct a driving source of the second supply state switching means independent of the mechanism was mobilized.

When the first water supply state switching means is in a state capable of supplying, and the third water supply state switching means is in a state that cannot be supplied, the high pressure water of the water supply source overcomes the spring force of the spring means in the weft insertion pump to insert the weft thread. It is supplied by a pump. When the first water supply state switching means is in a state that cannot be supplied, and when the second and third water supply state switching means are in a state that can be supplied, the water in the weft insertion pump is applied to the spring force of the spring means in the weft insertion pump. To the weft insertion nozzle. The water supply switching state of the second water supply state switching means is switched independently from the direct drive. This independent conversion from the woven fabric mobilization facilitates water supply timing from the weft insertion pump to the weft insertion nozzle, i.e., changes in the water timing.

In the invention of claim 2, in the first embodiment, a water still value is provided with a water supply control means for electrically controlling the water supply switching state of the second water supply state switching means.

The water supply switching state of the second water supply state switching means is electrically switched by the water supply control means. Such electrical switching control facilitates the water supply timing from the weft insertion pump to the weft insertion nozzle, that is, the change in the water timing.

In the invention of claim 3, in claim 2, the drive source of the first water supply state switching means is independent from the direct drive source, and the water supply switching state of the first water supply state switching means is electrically controlled by the water supply control means. .

The water supply switching state of the first water supply state switching means is electrically switched by the water supply control means. Such electrical switching control facilitates changing the water supply timing from the water supply to the weft insertion pump.

In the invention of claim 4, the spring means has a pressure chamber that accommodates a compressible gaseous fluid, and is a fluid spring means having spring pressure as the fluid pressure in the pressure chamber.

In the invention of claim 5, in the fourth aspect, the fluid spring means is an air spring means having air pressure as a spring force.

In Claim 4 and 5, since the surging vibration is small in the fluid spring means which made the compressible fluid pressure the spring force, the fluctuation | variation (pressure pulsation) of the water death pressure resulting from the surging vibration is small. Therefore, the state in which the insertion of the weft thread is disturbed by surging vibration is improved. In addition, since there is no conventional coil spring, it is possible to increase the rate of increase of the water injection pressure.

In the sixth aspect of the present invention, there is provided a spring force adjusting means for adjusting the fluid spring force in the fluid spring means, and an injection pressure control means for electrically controlling the spring force adjustment state in the spring force adjusting means. One mole was formed.

The spring force adjustment state in the spring force adjustment means is electrically controlled by the injection pressure control means. Such control of the spring force adjustment state makes it easy to change the water injection pressure in the weft insertion nozzle.

In the invention of claim 7, the spring force according to claim 6, comprising a fluid supply source for supplying a high pressure fluid to the pressure chamber of the fluid spring means, and a pressure regulating means for adjusting the fluid pressure supplied to the fluid spring means. An adjustment means was configured, and the pressure adjustment state in the pressure adjustment means was electrically controlled by the injection pressure control means.

The pressure regulation state in the pressure regulation means is electrically controlled by the injection pressure control means. Such control of the electric pressure adjustment state facilitates the change of the water injection pressure in the weft insertion nozzle.

In the invention of claim 8, the throttle flow passage communicates with the pressure chamber of the fluid spring means receiving the fluid from the fluid supply source, and the fluid flows slightly from the pressure chamber via the throttle flow passage.

The throttle channel lowers the pressure of the pressure chamber by releasing the fluid in the pressure chamber when the pressure of the water drops to the desired pressure.

In the invention of claim 9, the fluid spring means according to claim 4, comprising a fluid cylinder, a piston accommodated in the fluid cylinder, and the pressure chamber partitioned in the fluid cylinder by the piston, The movement from the point position to the bottom dead center position is caused by sending high pressure water to the weft insertion pump, and moves from the bottom dead center position to the top dead center position of the piston causing water supply from the weft insertion pump to the weft insertion nozzle. Was caused by the fluid pressure in the pressure chamber.

When the first water supply state switching means is in a state capable of supplying, and the third water supply state switching means is in a state that cannot be supplied, the high pressure water of the water supply source overcomes the pressure in the pressure chamber and lowers the piston from the top dead center position. Move to the point position. This is supplied to the weft insertion pump. When the first water supply state switching means is in a state that cannot be supplied and the second and third water supply state switching means are in a state that can be supplied, the piston moves from the bottom dead center position to the top dead center position by the pressure in the pressure chamber. Move. This supplies the water in the weft insertion pump to the weft insertion nozzle.

In the invention of claim 10, in the ninth aspect, a water jet having a position control means capable of changing the bottom dead center position of the piston is configured.

The injection pressure at the start of water injection can be changed by changing the bottom dead center position of the piston.

In the invention of claim 11, the water supply control means according to claim 9, wherein the holding means that is switched between a state capable of holding the piston at the bottom dead center position and a state that cannot be maintained is used as the second water supply state switching means. The holding means is electrically switched control between a maintainable state and a non-maintainable state.

When the piston is held at the bottom dead center position in the state where the holding means can hold, the water supply from the weft insertion pump to the weft insertion nozzle is blocked. When the piston is in the bottom dead center position and the third water supply state switching means is in a state capable of supplying, when the holding means is switched from the state in which it can hold, the piston moves from the bottom dead center position to the top dead center position. Start moving.

In the invention according to claim 12, in the water jet room, a plurality of weft yarns are inserted using a plurality of water treatment devices, and the first water supply state switching means in the plurality of water spraying apparatuses is connected to a single first water supply state switching means. Shared by.

The common use of the first water supply state switching means is advantageous for the compactization of the weft insertion device in the multicolor weft insertion.

Embodiment of the Invention

First embodiment:

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

As shown in FIG. 1A, a support cylinder 31 is vertically provided in the flow path block 30, and an air cylinder 32 as a fluid cylinder is fixed and coaxially supported on the support cylinder 31. The male cylinder 33 is accommodated in the support cylinder 31. The male cylinder 33 is fixed on the flow path block 30. An end wall plate 34 is fitted in the upper portion of the air cylinder 32. The plunger 35 is slidably fitted into the male cylinder 33. The upper end of the plunger 35 slidably penetrates through the end wall plate 34. The piston 37 is slidably accommodated in the air cylinder 32. The piston 37 is fixed to the plunger 35 and the piston 37 and the plunger 35 are integrally movable in the axial direction of the cylinders 32, 33.

In the through hole of the end wall plate 34 penetrating the upper end of the plunger 35, a seal ring 36 is mounted in sliding contact with the plunger 35. The sealing ring 38 is attached to the circumferential surface of the piston 37 so as to be in sliding contact with the inner circumferential surface of the air cylinder 32. The piston 37 partitions the pressure chamber 321 in the air cylinder 32.

On the lower surface of the piston 37, the position control part 371 is integrally formed. The position regulating portion 371 abuts against the upper end of the water cylinder 33 to define the lowest movement position of the piston 37, that is, the top dead center position of the piston 37.

The support cylinder 59 is vertically provided in the upper end of the air cylinder 32, and the support plate 60 is fastened and fastened to the upper end of the support cylinder 59 by the screw 61. As shown in FIG. Bolts 62 are screwed to the support plate 60. The bolt 62 is fixed to the support plate 60 by tightening the lock nut 63. The head 621 of the bolt 62 is above the axis of the plunger 35, and the upper end of the plunger 35 may abut the head 621 of the bolt 62. The bolt 62 defines the uppermost movement position of the plunger 35, that is, the bottom dead center position of the piston 37.

Euroblock 30, support cylinders 31 and 59, support plate 60, bolt 62, lock nut 63, air cylinder 32, water cylinder 33, plunger 35, piston (37) ) And the end wall plate 34 constitute a weft insertion pump 64. The air cylinder 32, the pressure chamber 321, the piston 37 and the seal rings 36, 38 constitute an air spring means.

An air pressure source 39 as a fluid supply source is connected to the pressure chamber 321 via the air pipe passage 40. An electric pressure regulating valve 41 and a check valve 42 having a relief function are interposed on the air line 40. A throttle passage 43 is formed in parallel with the check valve 42 between the pressure regulating valve 41 and the pressure chamber 321. A pressure gauge 44 is connected to the air line 40 between the pressure regulating valve 41 and the check valve 42. The pressure gauge 44 is for checking the air pressure between the pressure regulating valve 41 and the check valve 42. The pressure regulating valve 41 always maintains the pressure in the air line 40 between the pressure regulating valve 41 and the check valve 42 at the pressure set by the pressure regulating valve 41. The pressure Pi (primary initial pressure) in the pressure chamber 321 set by the pressure regulating valve 41 is the pressure when the piston 37 in the pressure chamber 321 is in the top dead center position.

When the piston 37 moves from the top dead center position to the bottom dead center position, the air in the pressure chamber 321 of the air cylinder 32 is compressed by the presence of the check valve 42. Since the cross sectional area in the throttle passage 43 is weak, air leakage from the throttle passage 43 by a short time does not substantially occur. Thus, the pressure in the pressure chamber 321 increases as the piston 37 moves from the top dead center position toward the bottom dead center position. When the piston 37 reaches the bottom dead center position, that is, when the plunger 35 contacts the bolt 62, the pressure in the pressure chamber 321 becomes the maximum pressure Pm (> Pi).

On the flow path block 30, a top-closing electromagnetic opening and closing valve 45 is mounted. The flow paths 301 and 302 are formed in the flow path block 30. The cylinder 331 of the male cylinder 33 communicates with the flow path 301. The inlet port 451 of the electromagnetic open / close valve 45 communicates with the flow path 301, and the outlet port 452 of the electromagnetic open / close valve 45 communicates with the flow path 302. The flow path 302 communicates with the weft insertion nozzle 47 via the conduit 46.

The flow path block 48, which is different from the flow path block 30, is provided with a normally closed electromagnetic open / close valve 49. Flow paths 481 and 482 are formed in the flow path block 48. The inlet 491 of the electromagnetic opening and closing valve 49 communicates with the flow path 481, and the outlet 492 of the electromagnetic opening and closing valve 49 communicates with the flow path 482. The flow paths 482 and 301 are connected by a conduit 50. A part of the flow path 482,301, the pipe line 50, and the inside of the cylinder 331 of the water cylinder 33 becomes the water storage chamber 641. FIG.

The flow path 481 communicates with the float box 51 via the conduit 53, and a plunger pump 52 is interposed on the conduit 53. Water in the float box 51 is pumped by the plunger pump 52 toward the flow path 481 in the flow path block 48. The reflux conduit 54 is connected to the conduit 53 so as to be in parallel with the plunger pump 52. The pressure regulating valve 55 is interposed on the reflux conduit 54. A pulsation absorption device 56 is attached to the conduit 53 between the plunger pump 52 and the electromagnetic opening and closing valve 49. The plunger pump 52 is operated continuously, and the water of the float box 51 is continuously pumped toward the flow path 481 of the flow path block 48. When the electromagnetic open / close valve 49 is in the closed state, the water fed from the plunger pump 52 is returned to the float box 51 via the reflux conduit 54.

Float box (51), plunger pump (52), pulsation absorber (56), reflux conduit (54) and pressure regulating valve (55) are water supply sources (29) capable of supplying high pressure water to the weft insertion pump (64). Configure

The pressure regulating valve 55 is adjusted to cause a pressure Po that is considerably higher than the maximum pressure Pm in the pressure chamber 321 of the air cylinder 32. The pressure receiving area of the plunger 35 relative to the pressure of the water storage chamber 641 (ie, the cross-sectional area of the lower end of the plunger 35) is S1. And the hydraulic pressure area (ie, the area of the upper surface of the piston 37) of the piston 37 with respect to the air pressure in the pressure chamber 321 is set to S2 (> S1). The pressure Po is set to be higher than the pressure represented by Pm · S2 / S1. Therefore, the pressure in the conduit 43 between the plunger pump 52 and the solenoid valve 49 becomes a pressure Po higher than the pressure represented by Pm * S2 / S1. When the electromagnetic open / close valve 49 is in the open state and the electromagnetic open / close valve 45 is in the closed state, the pressure in the water storage chamber 641 also becomes the pressure Po. When the pressure in the water storage chamber 641 becomes the pressure Po, the total load by the pressure of the high pressure water applied to the plunger 35 exceeds the total load by the air pressure applied to the piston 37. Therefore, the piston 37 moves from the top dead center position to the bottom dead center position.

As shown in FIG. 1A, the electromagnetic shutoff valves 49 and 45 and the pressure regulating valve 41 are subjected to electric command control of a control device 57 incorporating a computer. The control data input device 58 is connected to the control device 57. The control data input device 58 includes the desired water timing in the weft insertion nozzle 47, that is, the excitation / element timing of the solenoid valve 45, the excitation / element timing of the solenoid valve 49, and the air cylinder. The desired quasi-initial pressure Pi in the pressure chamber 321 of the 32 is input to the control device 57, respectively, and stored. A rotary encoder 65 for loom rotation angle detection is connected to the control device 57. M shown in FIG. 1A is a linear motor which serves as a linear motor drive.

The control device 57 controls the excitation / element of the electromagnetic opening / closing valves 49 and 45 on the basis of the loom rotation angle detection information obtained from the rotary encoder 65 and the preset excitation / element timing. The controller 57 controls the pressure regulation state of the pressure regulating valve 41 so as to be the preset quasi-initial pressure Pi. The electromagnetic open / close valve 49 is a first water supply state switching means that is switched between a state capable of supplying high pressure water from the water supply source 29 to the weft insertion pump 64 and a state that cannot supply it. The electromagnetic open / close valve 45 is a second water supply state switching means that is switched between a state in which water can be supplied from the weft insertion pump 64 to the weft insertion nozzle 47 and a state in which it cannot be supplied. The solenoid opening and closing valve 45 is a third water supply state switching means for preventing water supply to the weft insertion nozzle 47 when supplying high pressure water from the water supply source 29 to the weft insertion pump 64. The pressure regulating valve 41 and the air pressure source 39 constitute spring force adjusting means for adjusting the fluid spring force in the fluid spring means. The control device 57 and the control data input device 58 are water supply control means for electrically controlling the water supply switching state of the second water supply state switching means (electromagnetic open / close valve 45), and spring force in the spring force adjusting means. An injection pressure control means for electrically controlling the adjustment state is configured.

Curve D in the graph of FIG. 4 represents the preset excitation / element timing of the electromagnetic open / close valve 45, and the curve E represents the preset excitation / element timing of the electromagnetic open / close valve 49. Curve F represents the change in injection pressure in the weft insertion nozzle 47 and curve G represents the change in pressure in the pressure chamber 321.

At the time when the excitation of the electromagnetic open / close valve 45 is switched to the element (the point at which the loom rotation angle θ is θ2 in FIG. 4), the piston 37 is in the top dead center position, and the electromagnetic open / close valve 49 is in the element state. Is in. The water spray in the weft insertion nozzle 47 is stopped. 1A and 1B show element states of the electromagnetic open and close valves 49 and 45. When the loom rotation angle θ becomes θ3, the control device 57 commands the excitation of the electromagnetic opening and closing valve 49. The electromagnetic open / close valve 49 is switched from the closed state to the open state based on the excitation command of the control device 57. As shown in FIG. 2B, when the electromagnetic opening and closing valve 49 is opened, the high pressure water pumped from the plunger pump 52 is sent to the water storage chamber 641 via the electromagnetic opening and closing valve 49. The high pressure water feeding to the water storage chamber 641 moves the piston 37 in the top dead center position shown in FIG. 1A to the bottom dead center position shown in FIG. 2A. When the loom rotation angle θ becomes θ4, the control device 57 commands the element of the electromagnetic opening and closing valve 49. The electromagnetic open / close valve 49 is switched from the open state to the closed state based on the element command of the control device 57. When the loom rotation angle θ becomes θ1, the control device 57 commands the excitation of the electromagnetic opening and closing valve 45. The solenoid valve 45 is switched from the closed state to the open state based on the excitation command of the control device 57. As shown in FIG. 3A and FIG. 3B, when the electromagnetic opening / closing valve 45 is opened, the piston 37 in the bottom dead center position moves toward the top dead center position by the air pressure in the pressure chamber 321. As shown in FIG. The movement of the piston 37 from the bottom dead center position to the top dead center position, that is, the movement of the plunger 35, pressurizes the water in the reservoir chamber 641 to the weft insertion nozzle 47 and water from the weft insertion nozzle 47. Is injected and the weft yarn Y is inserted.

When the piston 37 moves from the top dead center position to the bottom dead center position, the volume of the pressure chamber 321 decreases and the pressure in the pressure chamber 321 starts to rise from the quasi-initial pressure Pi. The start of the increase in pressure in the pressure chamber 321 closes the check valve 42. Thereafter, the pressure in the pressure chamber 321 rises as the piston 37 moves toward the bottom dead center position, and the pressure in the pressure chamber 321 reaches the maximum pressure when the piston 37 reaches the bottom dead center position. (Pm) is obtained. The pressure at the start of air compression in the pressure chamber 321 is defined as the quasi-initial pressure Pi set by the pressure regulating valve 41 due to the presence of the check valve 42. In other words, the pressure in the pressure chamber 321 is maintained at a level equal to or higher than the quasi-initial pressure Pi caused by the pressure regulating valve 41. Curve Pb in the graph of FIG. 5 shows the relationship between the volume of the pressure chamber 321 and the pressure in the pressure chamber 321.

The change in pressure represented by the curve Pb in Fig. 5 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 expressed by the following equation (1) as the polytropy change.

P · V ⁿ = constant… (One)

N in Formula (1) is a polytropy index, and n = 1.2 normally. When the volume of the pressure chamber 321 decreases from the initial volume Vo to (Vo-s.Aa), the following equation (2) is established.

P · (Vo-s · Aa) ⁿ = Pi · Vo ⁿ ... (2)

S in the formula (2) is the displacement amount of the piston 37 (set s = 0 at the start of compression), and Aa is the hydraulic pressure area of the piston 37 with respect to the pressure in the pressure chamber 321.

Therefore, when the volume of the pressure chamber 321 is (Vo-s.Aa), the pressure P in the pressure chamber 321 is represented by following formula (3).

P = Pi · Vo ⁿ / (Vo-s · Aa) ⁿ ... (3)

That is, curve Pb of FIG. 5 is represented by Formula (3). When the displacement amount s increases, that is, the volume of the pressure chamber 321 decreases, the pressure P in the pressure chamber 321 increases as follows along the curve Pb as indicated by arrow U1 in FIG. 5. The pressure Pm of FIG. 5 is the pressure when the volume Vo-s * Aa of the pressure chamber 321 is minimum. The maximum pressure Pm increases as the maximum value of the displacement amount s increases, that is, as the moving distance from the top dead center position to the bottom dead center position of the piston 37 increases. As the maximum value of the displacement amount s increases, the initial injection pressure in the weft insertion nozzle 47 increases and the decompression gradient of the injection pressure increases. The maximum value of the displacement amount s can be changed by changing the screwing position of the bolt 62 with respect to the support plate 60.

When the piston 37 moves from the bottom dead center position to the top dead center position, that is, when the displacement amount s decreases, the pressure P in the pressure chamber 321 follows the curve Pb as indicated by the arrow U2 in FIG. 5. It decreases as it goes down.

The curve Go in FIG. 6 represents the actual pressure change in the reservoir 641, and the curve Fo represents the actual water pressure change in the weft insertion nozzle 47. In this case, for example, between the hydraulic pressure area S1 of the plunger 35 with respect to the hydraulic pressure of the water storage chamber 641 and the hydraulic pressure area S2 (> S1) of the piston 37 with respect to the air pressure in the pressure chamber 321. The relationship of / S1 = 20 is set, and the quasi-initial pressure Pi is set to 0.2 MPa. When the flow path loss, friction in the seal rings 36 and 38, inertia force of the plunger 35 and inertia force of the piston 37 are ignored, the water injection pressure at the weft insertion nozzle 47 at the end of water injection is 0.2 S2 / S1 = 4 MPa.

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

(1-1) When the foam is changed, the water timing in the weft insertion nozzle 47 is often changed. Changing the water-time timing data stored in the control device 57 can be easily performed by the operation of the control data input device 58. The drive source of the electromagnetic open / close valve 45 is independent of the direct drive motor M as its solenoid portion. Switching control in the electromagnetic open / close valve 45 independent from the linear drive motor M makes it easy to change the water supply timing, that is, the water timing, from the weft insertion pump 64 to the weft insertion nozzle 47.

(1-2) The open / close state (ie, the water supply switching state of the first water supply switching means) of the electromagnetic open / close valve 49 is switched by electric command control of the control device 57. That is, the high pressure water supply timing from the plunger pump 52 to the weft insertion pump 64 is controlled by the electric command of the controller 57. The excitation / element timing data of the electromagnetic open / close valve 49 stored in the control device 57 can be easily changed by the operation of the control data input device 58. The drive source of the electromagnetic open / close valve 49 is independent of the direct drive motor M as its solenoid portion. Switching control in the electromagnetic open / close valve 49 independent of the linear drive motor M facilitates changing the high pressure water supply timing from the plunger pump 52 to the weft insertion pump 64.

(1-3) The air pressure in the pressure chamber 321 in the air cylinder 32 depends on the pressure adjustment state in the pressure regulating valve 41. The pressure adjusting state (ie, the pressure adjusting state in the pressure adjusting means) of the pressure adjusting valve 41 that influences the pressure in the pressure chamber 321 is controlled by the electric command of the control device 57. When the bubble type is changed, the water injection pressure in the weft insertion nozzle 47 is often changed. The data change of the quasi-initial pressure Pi stored in the control device 57 can be easily performed by the operation of the control data input device 58. The control of the pressure regulation state in the electric pressure regulating valve 41 facilitates the change of the water injection pressure in the weft insertion nozzle 47.

(1-4) The curves Ce, Cf, Cg, and Ch in the graphs of Figs. 7E, 7F, 7G, and 7H show measurement results of changes in water injection pressure in a water spray device using a conventional coil spring. Curves Ca, Cb, Cc, and Cd in the graphs of Figs. 7A, 7B, 7C, and 7D show measurement results of changes in water injection pressure in the water injection device of the present embodiment using air spring means. 7A and 7E show a case where the loom rotation speed is 700 rpm and the quasi-initial pressure Pi in the pressure chamber 321 is 0.25 MPa. 7B and 7F show a case where the loom rotation speed is 800 rpm and the quasi-initial pressure Pi in the pressure chamber 321 is 0.3 MPa. 7C and 7G show a case where the loom rotation speed is 900 rpm and the quasi-initial pressure Pi in the pressure chamber 321 is 0.4 MPa. 7D and 7H show a case where the loom rotation speed is 1000 rpm and the quasi-initial pressure Pi in the pressure chamber 321 is 0.5 MPa. In addition, said S2 / S1 is set to 11.2 and the ratio of the minimum volume with respect to the maximum volume in the pressure chamber 321 is 0.64.

In the water jetting apparatus of the present embodiment using the air spring means as the driving source for generating the water jetting pressure in the weft insertion pump, the fluctuations (pressure pulsations) of the water jetting pressure due to the surging vibration are all largely observed in the water jetting apparatus. Can not. However, in the case of using a conventional water still device using a coil spring as a driving source for generating water death pressure in the weft insertion pump, a large wave of fluctuation of water injection pressure due to surging vibration at a specific loom rotation speed (pressure pulsation) ) Becomes remarkable. This pressure pulsation increases the diffusion of water sand. Increased diffusion of water yarns tends to damage the warp yarns, and the weft posture becomes unstable in the second half of the weft insertion period, leading to poor weft insertion defects.

In the air spring means using spring pressure as the compressible fluid, the surging vibration is much smaller than that of the coil spring. As a result, there is little fluctuation (pressure pulsation) of the water death pressure due to surging vibration. The pressure pulsation occurrence in the case of using the coil spring becomes more remarkable as the loom rotation speed increases, but in the water spraying device of the present embodiment using the air spring means, the pressure pulsation caused by the surging vibration occurs even if the loom rotation speed becomes high speed such as 1000 rpm. Can't see. Therefore, there is little warp damage even in the high-speed rotation state of the loom such as 1000 rpm, and the weft yarn Y is stably inserted. Stable insertion of the weft yarn Y in the high speed operation of the loom enables high speed operation of the loom without impairing fabric quality.

(1-5) In the case of the conventional water jetting apparatus shown in Figs. 16 and 17, the inertial force of the water and the pipe frictional resistance are small and neglected, and when water is sprayed from the weft insert nozzle 27, the following formula (4) is used. The equation of motion is established.

m · d ² x / dt ² = (Hk · x) + (Pa-Po) · Ap... (4)

M in Equation (4) is the sum of the equivalent masses of the power train moving bodies such as the cam lever 22, the plunger 14, the coil spring 18, the spring seat 15, and the like, and x is the displacement of the plunger 14. , d ² x / dt ² is the acceleration of the plunger 14, k is the spring constant of the coil spring 18, H is the compressive load of the coil spring 18 at the start of water injection, Po is the pressure of the reservoir 123 , Pa is atmospheric pressure, Ap is the cross-sectional area of the plunger 14.

Equation (4) can be obtained by arranging equation (4) with respect to the pressure Po of the water storage chamber 123, that is, the water injection pressure.

Po = Pa + (Hk.xm.d ² x / dt ² ) / Ap... (5)

In the start of water sand in equation (5), first, the mass (m) is accelerated rapidly by the spring force (H). Subsequently, when the acceleration is completed, that is, when the inertia force (m · d ² x / dt ² ) approaches zero, the spring force (Hk · x) and the pressure (Po) are balanced and water spraying proceeds. Water displacement pressure is high when the displacement (x) at the beginning of water sand is small in the process of water photography, but water sand pressure (Po) is increased as the water spring proceeds to restore the coil spring (18), that is, the displacement (x) increases. Gradually decreases. Immediately before the end of the water injection, the water injection pressure Po takes the lowest value during the water injection period. When all the water sucked into the reservoir chamber 123 is sprayed, the cam follower 221 stops 28 or the cam 23. The water injection pressure (Po) drops to atmospheric pressure.

The mass m in the equation (4) is the sum of the equivalent masses of the power train moving body, and 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) in Formula (4) becomes small compared with the conventional water spraying apparatus which uses a coil spring. Reduction of the mass (m) due to the absence of the coil spring increases the rate of increase of the water death pressure, thereby suppressing the "catch-up phenomenon" of the jet. Therefore, the spray-shaped disturbance of the jet tip part resulting from the "catchup phenomenon" of a jet is suppressed. As a result, a situation in which high-speed droplets collide with the warp and damage the warp can be avoided, and the degradation of the fabric quality due to warp streak generation can be prevented.

(1-6) Although the pressure change obtained by the water spraying apparatus of this embodiment is shown in FIG. 5, the pressure gradient in the time change during water stroke is represented by following formula (6).

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

The pressure gradient dP / dt in the conventional water spraying apparatus using the coil spring 18 shows a relatively linear change when disturbance such as surge is not involved. On the other hand, the pressure gradient dP / dt in the present embodiment using the air spring means is designed to design the pressure chamber 321, considering that dP / ds is a curve obtained by differentiating equation (5) by the displacement amount s. As a result, a large deviation from the straight line can be realized.

(1-7) The check valve 42 serves to block communication between the pressure regulating valve 41 and the pressure chamber 321 when compressing air in the pressure chamber 321, and the minimum pressure of the pressure chamber 321. (I.e., the quasi-initial pressure Pi set by the pressure regulating valve 41), and serves to supplement the air leakage when air leaks from the pressure chamber 321.

If the sealing function by the seal rings 36 and 38 is complete and there is no air leakage from the pressure chamber 321, the air by the check valve 42 during operation of the loom is operated unless the pressure adjusting valve 41 is operated. There is no entry and exit, and the check valve 42 merely serves as a stop valve.

When there is no air leak from the pressure chamber 321, even if the pressure in the pressure chamber 321 can be boosted by the operation of the pressure regulating valve 41, the pressure cannot be reduced by the action of the check valve 42. The throttle passage 43 actively leaks air in the pressure chamber 321 to the pressure regulating valve 41 side. The configuration in which the throttle passage 43 is formed in parallel with the check valve 42 makes it possible to depressurize the inside of the pressure chamber 321 when the sealing function by the seal rings 36 and 38 fully operates. This decompressable configuration enables the setting of the quasi-initial pressure Pi in the pressure chamber 321. The air pressure source 39, the pressure regulating valve 41, the check valve 42 and the throttle passage 43 constitute a quasi-initial pressure setting means for setting the quasi-initial pressure in the fluid spring means.

The air in the pressure chamber 321 starts compression in the quasi-initial pressure Pi set by the quasi-initial pressure setting means. The pressure in the pressure chamber 321 in the process of water injection is higher than the quasi-initial pressure Pi. Since the stroke of the piston 37 is constant for each weft insertion, the pressure when the air in the pressure chamber 321 is maximally compressed is always constant. Therefore, the water sand is started under the pressure Pm state when the air in the pressure chamber 321 is compressed to the maximum. The water injection pressure at the beginning of water injection always matches the pressure Pm higher than the quasi-initial pressure Pi set by the pressure regulating valve 41, and the water injection pressure in the water injection process is equal to or less than the pressure Pm and It becomes the above range. Therefore, it is possible to indirectly control the pressure at the beginning of water injection, which is an important factor in weft insertion, and to precisely adjust the water injection pressure.

(1-8) The bottom dead center position of the piston 37 can be changed by changing the screwing position of the bolt 62 with respect to the support plate 60. The bolt 62 and the lock nut 63 constitute a position regulating means capable of changing the bottom dead center position of the piston 37. The bottom dead center position change of the piston 37 changes the ratio of the minimum volume to the maximum volume of the pressure chamber 321. That is, the compression ratio of the air in the pressure chamber 321 can be easily changed by changing the screwing position of the bolt 62 with respect to the support plate 60. The pressure at the beginning of water injection, which is an important factor in weft insertion, can be easily changed by a simple operation of changing the screw fastening position of the bolt 62.

(1-9) In the conventional water spraying apparatus shown in FIG. 16, a vibration generating source having a large collision between the cam surface 231 of the cam 23 and the cam follower 221, and a collision between the cam lever 22 and the stopper 28 is large. Becomes In this embodiment, since there is no cam mechanism, the noise generated in the water jetting device is significantly reduced. This makes it possible to speed up the waterjet room without causing deterioration of the working environment in the factory.

Second embodiment:

Next, 2nd Embodiment of FIGS. 8-10 is demonstrated. The same code | symbol is used for the same structural part as 1st Embodiment.

The electromagnet 66 is attached to the bolt 62, and the magnetic body 67 is stopped at the upper end of the plunger 35. The electromagnet 66 receives an instruction of excitation / element control of the control device 57A having the same function as the control device 57 in the first embodiment. As shown in FIG. 9, when the magnetic body 67 is in contact with the electromagnet 66, that is, when the piston 37 is at the bottom dead center position, the magnetic body 67 is excited by the excitation of the electromagnet 66. ) Is held in contact with each other.

The solenoid valve 45 is excited after the solenoid valve 49 is demagnetized and before the water spray start timing. The electromagnet 66 is demagnetized at the water injection start timing after the excitation start of the electromagnetic open / close valve 45. Thereby, the magnetic body 67 is released by the adsorption | suction action of the electromagnet 66, and the piston 37 moves toward a top dead center position from a bottom dead center position as shown in FIG. Water in the reservoir 642 in the weft insertion pump 64A is pumped to the weft insertion nozzle 47 and moves in the weft insertion nozzle 47 as the piston 37 moves from the bottom dead center position to the top dead center position. Moisturizing begins.

The electromagnet 66 and the magnetic body 67 constitute holding means for switching the piston 37 to a state capable of holding the piston 37 at a bottom dead center position and to an unsustainable state. This holding means is a second water supply state switching means for switching from the weft insertion pump 64 to a state in which water can be supplied to the weft insertion nozzle 47 and a state in which it cannot be supplied. The solenoid valve 45 in the second embodiment prevents water supply to the weft insertion nozzle 47 when supplying high pressure water from the water supply source 29 to the weft insertion pump 64A with the weft insertion nozzle 47. The third water supply state switching means for. The control device 57A is a holding control means for electrically switching control of the holding means in a maintainable state and a non-maintainable state.

Moisture firing depends on the elements of the electromagnet 66. Therefore, the excitation start of the electromagnetic open / close valve 45 starts at the timing of switching the excitation of the electromagnetic open / close valve 49 to the element (that is, the timing at which the piston 37 reaches the bottom dead center position) to the water spray start timing (that is, And the timing at which the excitation of the electromagnet 66 is switched to the element). This gives room to the opening operation by the excitation of the electromagnetic open / close valve 45. Therefore, as the electromagnetic opening and closing valve 45, an electromagnetic opening and closing valve with a low response speed can be employed.

The higher the response speed of the electromagnetic open / close valve is, the more the impact force is increased when the valve body collides with the valve seat, and the valve body or the valve seat is prematurely worn, so that the sealing property is prematurely damaged. In addition, an electromagnetic open / close valve with a high response speed is expensive. The configuration in which the electromagnetic open / close valve as the electromagnetic open / close valve 45 is low in response speed contributes to cost reduction and improved reliability of the water spray device.

Third embodiment:

Next, the third embodiment of FIGS. 11 and 12 will be described. The same code | symbol is used for the same structural part as 2nd Embodiment.

The difference from the second embodiment is that the electromagnetic three-way valve 68 is used instead of the electromagnetic opening and closing valves 49 and 45 in the second embodiment. The electromagnetic three-way valve 68 receives a command of excitation / element control of the control device 57B having the same function as the control device 57A in the second embodiment. 11 shows an excited state of the electromagnetic three-way valve 68. The excited state of the electromagnetic three-way valve 68 can supply the high pressure water pumped from the plunger pump 52 to the water storage chamber 643 in the weft insertion pump 64B, and further, the water in the water storage chamber 643 is inserted into the weft chamber. It is a state which cannot be supplied to the nozzle 47. The piston 37 is in the bottom dead center position. 12 shows the device state of the electromagnetic three-way valve 68. As shown in FIG. The element state of the electromagnetic three-way valve 68 cannot supply the high pressure water pumped from the plunger pump 52 to the water storage chamber 643, and can supply the water of the water storage chamber 643 to the weft insertion nozzle 47. It is a state. The piston 37 is on the way from the top dead center position to the bottom dead center position.

The electromagnetic three-way valve 68 serves as a first water supply state switching means and a third water supply state switching means.

In the third embodiment, the number of the solenoid valves can be reduced in comparison with the first and second embodiments, which makes it possible to further compact the water spray device and reduce the cost.

Fourth Embodiment:

Next, the fourth embodiment of FIGS. 13 and 14 will be described. The same code | symbol is used for the same structural part as 3rd Embodiment.

The difference from the third embodiment is that the electromagnetic rotary valve 69 is used instead of the electromagnetic three-way valve 68 in the third embodiment. The electromagnetic three-way valve 68 receives an instruction of excitation / element control of the control device 57C having the same function as the control device 57A in the second embodiment. 13 shows the excited state of the electromagnetic rotating valve 69. The excited state of the electromagnetic rotary valve 69 can supply the high pressure water pumped from the plunger pump 52 to the reservoir 642, and cannot supply the water of the reservoir 642 to the weft insertion nozzle 47. It is a state. The piston 37 is in the bottom dead center position. 14 shows an element state of the electromagnetic rotary valve 69. The element state of the electromagnetic rotary valve 69 cannot supply the high pressure water pumped from the plunger pump 52 to the reservoir 642, and can supply the water of the reservoir 642 to the weft insertion nozzle 47. It is a state. The piston 37 is on the way from the top dead center position to the bottom dead center position.

The electromagnetic rotary valve 69 also serves as a first water supply state switching means and a third water supply state switching means.

In 4th Embodiment, the same effect as 3rd Embodiment can be acquired.

Fifth Embodiment:

Next, 5th Embodiment of FIG. 15 is described. The same code | symbol is used for the same structural part as 1st Embodiment.

Weft insertion pump 64, solenoid opening and closing valve 45, flow path block 30 and pressure regulating valve for ejecting the wefts Y1, Y2 and Y3 from the plurality of weft insertion nozzles 47 in the casing bodies 701, 702 and 703, respectively. 41 is housed. The casing bodies 701, 702, 703 and these housing parts each constitute a water jet unit. The single solenoid valve 49 communicates with the flow path 301 in the flow path block 30 in each casing body 701, 702, 703 via the common pipe 71 and the branch pipes 711, 712, 713. The single solenoid valve 49 is a shared component of each of the above water spray devices. Check valves 72, 73, and 74 are interposed on branch lines 711, 712, 713. When the solenoid valve 45 is in the closed state, the water being sent to the reservoir chamber 641 of each of the weft insertion pumps 64 is maintained at a high pressure due to the presence of the check valves 72, 73, and 74. Waiting for jet

In the control device 57D having the same function as the control device 57 in the first embodiment, weft selection pattern data is input and stored by an input operation of the control data input device 58D. The control device 57D selects and excites / elements of at least one of the electromagnetic opening / closing valves 45 for each weft insertion based on the preset weft selection pattern data. For this reason, only one of the weft yarns Y1, Y2, and Y3 is selected, is ejected from the weft insertion nozzle 47, and weft insertion.

In the conventional water spraying apparatus shown in Fig. 16, the insertion of two-color wefts is limited due to the constraints of the size and mounting conditions of the apparatus. Since the water retaining device having the air spring means as the driving source for generating water injection pressure becomes very compact compared with the conventional water injection device, weft insertion of more than two colors can be inserted as in the fifth embodiment. In the fifth embodiment, the single solenoid valve 49 is shared as the first water supply state switching means for controlling the high pressure water supply to the plurality of weft insertion pumps 64. Therefore, the whole water spraying device for inserting a multi-color weft becomes more compact, and the effect of reducing the apparatus cost is also remarkable. In the fifth embodiment, since the weft insertion pump 64 and the electromagnetic switching valve 45 serving as the noise source are accommodated in the casing bodies 701, 702, 703, the noise is further reduced than in the case of the first embodiment. As a result of the present inventors measuring and comparing the noise of the starter of the present embodiment with the conventional apparatus, the result was that the noise of the starter of the present embodiment is 10 dB or more smaller than that of the conventional apparatus.

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

(1) In the first embodiment, the electromagnetic opening and closing valve is interposed on the throttle passage 43, and the opening and closing control of the electromagnetic opening and closing valve is performed only when the quasi-initial pressure Pi is changed in accordance with the change of the foam type.

(2) Instead of the solenoid valve 49 in the first and second embodiments, a mechanical on / off valve for opening and closing in synchronism with loom rotation is to be used. The use of the mechanical open / close valve is possible because there is room in the switching operation of the second water supply state switching means.

(3) Use fluid spring means for springing the pressure of compressible gaseous fluids other than air, such as inert gases (nitrogen gas, carbon dioxide, etc.).

(4) A weft insertion pump using the coil spring shown in Fig. 17 as the spring means shall be employed in the present invention.

(5) Connect a management computer managing multiple waterjet rooms with a computer built into the loom by communication, and remotely operate multiple waterjet rooms through the management computer.

(6) Feedback control of water timing or water injection pressure based on the operation data of the waterjet room.

As described above, the present invention overcomes the spring force of the spring means to supply high-pressure water from the water supply source to the weft insertion pump, and to supply water from the weft insertion pump to the weft insertion nozzle. Since the drive source of the second water supply state switching means that is switched to the state is independent from the linear drive source, it has an excellent effect of providing a water jet value suitable for automation of the waterjet room.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 shows a first embodiment, Fig. 1A is an overall view of a water spray device, and Fig. 1B is a simplified diagram showing an excitation / element state of an electromagnetic open / close valve 49,45.

Fig. 2 shows the first embodiment, Fig. 2A is a sectional view showing the main parts showing the state where the piston 37 is in the bottom dead center position, and Fig. 2B is a simplified diagram showing the excitation / element states of the electromagnetic opening and closing valves 49 and 45;

Fig. 3 shows the first embodiment, Fig. 3A is a sectional view showing the main parts showing the state where the piston 37 moves from the bottom dead center position to the top dead center position, and Fig. 3B shows the excitation / element of the electromagnetic opening and closing valves 49 and 45. Simplified representation of the status.

Fig. 4 is a graph showing excitation / element timing, injection pressure change in the weft insertion nozzle 47, and pressure change in the pressure chamber 321 of the solenoid valves 45 and 49 of the first embodiment.

5 is a graph showing the relationship between the volume of the pressure chamber 321 of the first embodiment and the pressure in the pressure chamber 321.

Fig. 6 is a graph showing the change in injection pressure in the weft insertion nozzle 47 and the change in pressure in the pressure chamber 321 of the first embodiment.

7A to 7D are graphs showing measurement results of changes in water injection pressure in the water spraying device of the first embodiment using air spring means, and FIGS. 7E to 7H are numbers of water spraying devices using the conventional coil spring. A graph showing the measurement result of the change in injection pressure.

Fig. 8 is an overall view of a water spraying device showing a second embodiment.

Fig. 9 is a sectional view showing the main parts of a state in which the piston 37 is in the bottom dead center position in the second embodiment.

FIG. 10 is a sectional view showing the principal parts of a state in which the piston 37 moves from a bottom dead center position to a top dead center position in the second embodiment. FIG.

Fig. 11 is an overall view of a water spraying device showing a third embodiment.

Fig. 12 is an overall view of the water spraying device, showing a state in which the piston 37 moves from the bottom dead center position to the top dead center position in the third embodiment.

Fig. 13 is an overall view of a water spraying device showing a fourth embodiment.

FIG. 14 is an overall view of a water spraying device showing a state where the piston 37 moves from the bottom dead center position to the top dead center position in the fourth embodiment.

Fig. 15 is an overall view of a water spraying device showing a fifth embodiment.

16 is an overall view of a conventional water spraying device.

17 is a side sectional view of the weft insertion pump 11;

18 is a graph showing the relationship between the loom rotation angle and the cam lift amount;

* Explanation of symbols for the main parts of the drawings *

29: water supply source 45: solenoid valve

47: weft insertion nozzle 49: electromagnetic opening and closing valve

57 control device 64 weft insertion pump

321: pressure chamber

Claims (12)

In a waterjet room in which water is injected from the weft insertion nozzle by pressurizing the water into the weft insertion nozzle by a weft insertion pump using a spring means as a driving source for generating the water injection pressure, and inserting the weft by the water injection action of the weft insertion nozzle. As a water spray device of A water supply source capable of overcoming the spring force of the spring means to supply high pressure water to the weft insertion pump; First water supply state switching means for switching between a state capable of supplying high pressure water from the water supply source to the weft insertion pump and a state in which it cannot supply; Second water supply state switching means for switching between a state in which water can be supplied from the weft insertion pump to the weft insertion nozzle and a state in which it cannot be supplied; A third water supply state switching means for preventing water supply to the weft insertion nozzle when supplying high pressure water from the water supply source to the weft insertion pump, And a water jetting device in the waterjet room, wherein the driving source of the second water supply state switching means is independent from the linear driving source. The water spraying device in a waterjet room according to claim 1, further comprising a water supply control means for electrically controlling a water supply switching state of the second water supply state switching means. 3. The water jet room according to claim 2, wherein the driving source of the first water supply state switching means is independent from the linear driving source, and the water supply switching state of the first water supply state switching means is electrically controlled by the water supply control means. Water spray device. 4. The water jet room according to any one of claims 1 to 3, wherein the spring means has a pressure chamber for receiving a compressible gaseous fluid and is a fluid spring means having a spring force of the fluid pressure in the pressure chamber. Injector. 5. The water spray apparatus according to claim 4, wherein the fluid spring means is air spring means using a spring force of air. The water jet room according to claim 4, further comprising: a spring force adjusting means for adjusting the spring force in the fluid spring means; and an injection pressure control means for electrically controlling the spring force adjusting state in the spring force adjusting means. Water spray device. 7. The pressure adjusting means according to claim 6, wherein the spring force adjusting means includes a fluid supply source for supplying a high pressure fluid to the pressure chamber of the fluid spring means, and a pressure adjusting means for adjusting the fluid pressure supplied to the fluid spring means. And the pressure adjusting state in the pressure adjusting means is electrically controlled by the injection pressure controlling means. The water jet in the waterjet room according to claim 6, wherein the throttle flow passage communicates with the pressure chamber of the fluid spring means receiving the fluid from the fluid supply source, and the fluid flows slightly from the pressure chamber via the throttle flow passage. Device. 5. The fluid spring means according to claim 4, wherein the fluid spring means has a fluid cylinder, a piston accommodated in the fluid cylinder, and the pressure chamber partitioned in the fluid cylinder by the piston, and the bottom dead center position at the top dead center position of the piston. The movement of the furnace is caused by sending high pressure water to the weft insertion pump, and the movement from the bottom dead center position to the top dead center position of the piston causing water supply from the weft insertion pump to the weft insertion nozzle is caused by the fluid in the pressure chamber. Water spraying device in waterjet room caused by pressure. 10. The water jetting device according to claim 9, further comprising a position control means capable of changing the bottom dead center position of the piston. 10. The water supply control means according to claim 9, wherein the second water supply state switching means is a holding means that is switched between a state capable of maintaining the piston at the bottom dead center position and an unmaintainable state, wherein the water supply control means And a water jetting device in the waterjet room for electrically switching and controlling said holding means between non-maintenable states. The waterjet room according to claim 1, wherein the waterjet room inserts a plurality of weft yarns by using a plurality of water jets, and the waterjet room sharing the first water supply state switching means in the multiple water spray devices by a single first water supply state switching means. Water spray device in