JPH0545703B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a pressure water supply device for weft insertion in a water jet loom. The present invention relates to a device for feeding pressurized water to a nozzle, which stores energy in an elastic body along with the suction stroke of a pump, and causes the stored elastic body to perform a discharge stroke.

(Prior art) As such a conventional device, for example,
There is one disclosed in Japanese Patent No. 136464, which will be explained with reference to FIG.

In the figure, 1 is a pump drive cam that rotates in the direction of arrow R in synchronization with the loom, and has a spiral cam surface 1.
a and a cam top 1b at its end. 2 is a rocker that can swing around a fixed shaft 3; 4 is a cam follower supported at one end of the rocker; 5 is a link rod connected to the other end of the rocker; 6 are connected to each other, and an elastic body, in this case a coil spring 8, is elastically loaded between the head 6a of the head rod 6 and a spring receiver 7 fixed to the frame of the loom. The cam follower 4 can be brought into elastic contact with the cam surface 1a.

10 is a plunger pump, 11 is its plunger, 12 is a suction valve, 13 is its valve ball, 14 is a valve spring that urges this valve ball in the valve closing direction, 15 is a discharge valve, 13' is its valve ball, Reference numeral 14' denotes a valve spring that biases the valve ball in the valve closing direction.

Reference numeral 16 denotes an L-shaped lever whose corner is supported on a fixed shaft 17. One end of the lever is connected to the end of the link rod 5, and the other end is connected to the plunger 11 via a connecting rod 18.

From the above configuration, when the cam 1 rotates in the direction of the arrow R, the rocker 2 rotates clockwise in the drawing (the same applies hereinafter), so the plunger 11 rotates between the link rods 5 and L.
The weft inserting water, which is pulled up through the shaped lever 16, the connecting rod 18, etc. and stored in the constant water level tank 19, is sucked into the pump 10 through the suction valve 12. At the same time, the coil spring 8 is elastically compressed by the head rod 6 to store energy. Next, come top 1
When the material b passes the cam follower 4, the locker 2 is released from the restraint from the cam surface 1a and becomes free, so the plunger 11 is driven by the stored coil spring 8 and descends, thereby removing the sucked weft insertion. Water is pressurized and fed to the weft insertion nozzle 21 via the discharge valve 15 and the water channel 20. The weft insertion nozzle 21 then starts to pull the weft W by injecting this water, and after a short period of time, the weft gripper 22 is opened and weft insertion is performed.

(Problem) By the way, for example, every minute
When weaving at high speeds of 1,000 revolutions or more, the water jet from the weft insertion nozzle scatters violently and collides with the warp threads, causing problems such as warp fuzz. The reason for this was found to be as follows.

Figure 4 shows the results of measuring the water supply pressure by installing the high-sensitivity pressure sensor 23 (Figure 3) just before the weft insertion nozzle. The axis is the water pressure p mentioned above.

In the figure, t ₀ is the beginning of the discharge stroke, that is, the time when the cam follower 4 comes off the cam top 1b, and the water pressure is p ₀ from this time until the stored coil spring starts to expand and reaches time t ₁ . Rise from p ₁ . After this water pressure reaches a peak p ₂ (t ₂ ), it gradually decreases until the coil spring ends its extension at time t ₃ .
_p3 , at which point the discharge stroke of the pump 10 ends. During this time, weft inserting water is injected from the weft inserting nozzle at a flow rate corresponding to the water pressure change. Note that between time points _t3 and _t4 , the water pressure drops rapidly because the discharge stroke of the pump is completed at the time of post-injection of weft insertion water based on inertia. Further, as shown in the figure, pulsation appears in the water pressure curve, but this is mainly due to the fluttering of the valve ball 13 or 13'. And again at time t ₀ −t ₁
The reason why the water pressure p does not rise so rapidly between
This is because the inertial force of the suction water acts during the transition period from the suction stroke to the discharge stroke.

From the above results, it can be seen that the splashing of the jetted water occurs at time t ₀
- As a result of the low-speed water jet between time _{t 1} colliding with the high-speed water jet between time points t ₁ and t ₃ and trying to push it away,
The former phenomenon can be interpreted as the explosive disintegration of low-speed water flow, and in high-speed looms, the effective water injection period t ₁ −
Because it is necessary to shorten t ₃ and insert the required length during that time, it is necessary to increase the water pressure p, which increases the difference in jet flow velocity at the weft insertion nozzle and causes the above-mentioned disintegration phenomenon to occur. That will happen.

Therefore, an object of the present invention is to prevent the above-mentioned explosive collapse phenomenon from occurring.

(Means of the Invention) The means of the present invention for solving the above-mentioned problems is a device for feeding pressurized water from a pump that suctions and discharges water every revolution of a loom to a weft inserting nozzle. In a device that stores energy in an elastic body and performs a discharge stroke using the stored elastic body, a rest stroke is provided between the suction stroke and the discharge stroke, and the pump and the weft insertion nozzle are connected. An on-off valve is interposed in between, and a valve drive device is provided to drive the on-off valve in synchronization with the loom, and the operation timing of the valve drive device is set so as to open the on-off valve during the rest stroke of the pump. It is something.

(Function) The discharge operation of the pump is performed by the elastic body that stores energy and is virtually unrelated to the pump drive mechanism of the loom, so even if the crank angle of the loom advances, the discharge operation is restrained. You can leave it there.

According to the above configuration, even when the end of the suction stroke of the pump arrives, the on-off valve is still closed, so the suction water is trapped inside the pump and the inertial motion imparted during the suction stroke is suppressed. Then, the elastic body remains in a charged state and waits to pressurize the suction water. Therefore, the water pressure of the suction water increases as the hydrostatic pressure approaches the above-mentioned calming.

Here, when the valve drive device opens the on-off valve during the rest stroke, the suction water with the accumulated pressure is discharged in response to this, so this has a steep rise in water pressure and is sent to the weft insertion nozzle. Ru. Therefore, with the weft insertion nozzle, a high-speed jet can be obtained from the beginning, although there is a slight transient period, so that the collapse phenomenon of the preceding water flow can be made extremely small. Furthermore, according to the above configuration, the pump operates every revolution of the loom, and there is a rest stroke between the suction stroke and the discharge stroke, so the pump is not affected by the inertia of the drive system or the spring. In the rest stroke, even if the cam separates from the cam follower when moving from the suction stroke to the discharge stroke, the cam and the cam follower come into contact during the rest stroke, so there is no variation in operation.

(Example) In FIG. 1, 30 is a pump, 20 is the water channel leading from this pump to the weft insertion nozzle 21, and 6
0 is an on-off valve installed in this waterway, and 80 is a valve drive device that drives this on-off valve.

The operating principle of the pump 30 is the same as that of the conventional pump 10.
Although it is almost the same as the one shown in the figure, it has a more practical configuration. In this pump 30,
31 is a housing, 32 is a water passage passing through the housing, and 33 is a pump chamber communicating with the water passage. Most of the pump chamber 33 is formed inside a sleeve 34 screwed onto the housing 31.
35 has a cylindrical main body part 35a with one end closed by a plunger, a plunger head 35b protruding from this one end part, and an outer flange 35c formed at the other end. It is fitted externally. A spring case 36 is formed into a cylindrical shape with an annular bottom cover 36a at one end, and the outer periphery of the cylindrical portion is screwed into the housing 31 37 to enclose the main body 35a of the plunger. 38 is a lock nut for positioning this spring case. Reference numeral 39 denotes an elastic body, a coil spring in this example, which is elastically inserted between the annular bottom cover 36a of the spring case and the outer flange 35c of the plunger.

Reference numeral 40 denotes a suction valve constructed at one end of the water passage 32, which includes a nipple 41 attached to the mouth of the passage, a valve ball 42 arranged behind the nipple, and a valve spring that biases the valve ball toward the nipple 41. 43, etc., and the nipple is connected to the constant water level tank 19 (third
Figure). Reference numeral 44 denotes a discharge port formed at the other end of the water passage 32 to which the water passage 20 is connected.

50 is a pump drive cam that rotates clockwise (arrow R) in synchronization with the loom, and O is its rotation center. The cam 50 has a rotation center O in a counterclockwise direction.
A bottom cam surface 50a having the same distance from the top, a spiral cam surface 50b having the same distance gradually increasing, a top cam surface 50c having the same distance from the top cam surface 50c, and a top cam surface 50c having the same distance from the top cam surface 50c.
A straight cam surface 50d that connects the terminal end of the bottom cam surface 50a and the starting end of the bottom cam surface 50a in a substantially straight manner is connected, and θ _a ,
θ _b , θ _c and θ _d are these cam surfaces 50a, 50
These are the rotation angles corresponding to b, 50c, and 50d, respectively.

51 is an L-shaped rocker whose corner is supported on a fixed shaft 52; 53 is a cam follower supported on one end of this rocker and corresponds to the pump drive cam 50;
54 is the other end of the rocker 51 and the plunger head 3
a connecting rod connecting 5b with 5b;
Reference numeral 1a denotes an arm protruding from the other end of the rocker. Further, 55 is a stroke adjuster of the plunger 35, which has a stopper bolt 56 and its lock nut 57, and the stopper bolt 56 is opposed to the arm 51a to fix the adjuster.

The configuration of the pump 30 is as described above, and
The following adjustments will be made. That is, since the compressed coil spring 39 pulls up the plunger 35, urges the rocker 51 clockwise, and presses the cam follower 53 against the pump drive cam 50, the stopper bolt 56 is first screwed in and the arm 51a is moved. While pressing the rocker 51 counterclockwise through the cam follower 53, adjust so that the cam follower 53 just contacts the bottom cam surface 50a or faces the bottom cam surface 50a with a slight gap,
This position is fixed using a lock nut 57.
Next, the spring case 36 is moved back and forth by its threaded portion 37 to apply a required set load to the coil spring 39, and this state is rotated by the lock nut 38. The above set load is the water pressure _P3 at the end of the discharge stroke.
(Figure 4).

A diagram P shown in FIG. 2 illustrates the lifting height of the plunger 35. In the figure, the horizontal axis represents the crank angle α of the loom with reference to the beating time, and the weft insertion period of the loom, that is, the gripper 2
As shown by G in the same figure, the open period of 2 is α=
(110° to 250°).

Now, as the pump drive cam 50 rotates, the cam follower 53 transfers from the bottom cam surface 50a to the spiral cam surface 50b, at this time (α=240°).
The suction operation is performed in the range of rotation angle θ _b (α=240° to 80°). That is, since the rocker 51 is pushed from the spiral cam surface 50b via the cam follower 53 and rotates counterclockwise while pulling down the plunger 35, the weft insertion water in the constant water level tank flows into the suction valve 40.
is pushed open and sucked into the pump chamber 33, and at the same time, the coil spring 39 is compressed and stored. At the end of the suction stroke S (α=80°), the cam follower 53 transfers to the top cam surface 50c, and from there, in the range of rotation angle _θc (α=80° to 100°), the rocker 51
stops, thereby causing the plunger 35 to rest. In this rest stroke _R1 , the valve ball 4
2 becomes stable and the suction valve 40 is completely closed. Next, the top cam surface 50c is the cam follower 5.
3, the locker 51 is released, and the stored coil spring 39 rapidly pushes the plunger 35 to discharge the suction water from the pump chamber 33. This discharge stroke E occurs when the arm 51a abuts against the stopper bolt 56 (α=
200°), and the rotation angle between them is approximately θ _d . After that, the bottom cam surface 50a becomes the cam follower 5.
Since Rotsuka 51 is brought to rest by contacting or confronting 3, it becomes the second resting stroke _R2 , and this resting stroke
The next suction stroke S starts from the final stage of R ₂ (α=240°).

Next, in the on-off valve 60, 61 is a valve case that has a through hole 62, and 63 is a sleeve that is fitted near the front end of the through hole 62 (the right end in the drawing) and is brought into contact with the stepped portion 62a of the through hole. After positioning, it is fixed with a presser nut 64. Reference numeral 65 indicates an inlet for water discharged from the pump 30, 66 indicates a water inlet passage communicating with the inlet and surrounding the sleeve 63, and 67 indicates a water passage connecting the inlet water passage and the inside of the sleeve 63. The hole 68 is a delivery port connected to the weft insertion nozzle 21, and 69 is a delivery port connected to the weft insertion nozzle 21.
A delivery water passage 70 surrounding the sleeve 3 is a plurality of valve holes that communicate the delivery water passage with the inside of the sleeve 63. A spool valve 71 is fitted into the sleeve 63 by means of two lands 71a and 71b formed on the spool valve, and has a valve shaft 71c protruding forward and its front end surface serving as a valve head 71d. 72 is a valve spring that presses the spool valve forward; 73 is a receiving washer for the valve spring;
In the illustrated forward position, the valve hole 70 is closed by the land 71a, and in the retracted position, the lands 71a and 71b are closed so that the valve hole communicates with the water supply passage 67 from between the lands 71a and 71b. The position is determined.

In the valve drive device 80, 81 is a valve drive cam that rotates clockwise (arrow R) in synchronization with the loom;
O′ is its center of rotation. Reference numeral 82 denotes a V-shaped lever whose corner is supported on a fixed shaft 83, which is disposed between the valve drive cam 81 and the spool valve 71, supports the cam follower 84 at the free end of the cam 81, and The free end of the spool valve 71 has a valve head 7.
A protrusion 85 is fixed opposite to 1d. 8
Reference numeral 6 denotes a spring that urges this lever to rotate toward the valve driving cam 81. This spring causes the cam follower 84 to come into elastic contact with the cam, and the protrusion 85 receives the valve head 71d of the spool valve. .

In the valve drive cam 81, 81a and 81b
are a small radius cam surface and a large radius cam surface formed in the range of rotation angles θ ₁ and θ ₂ , respectively, and their centers are the rotation center O′. 81c and 81d are a valve opening cam surface and a valve closing cam surface connecting the small radius cam surface 81a and the large radius cam surface 81b, respectively, θ ₃
and θ ₄ are rotation angles of these valve train cam surfaces 81c and 81d, respectively.

The diagram EV shown in FIG. 2 illustrates the operation timing of the valve drive device 80.

While the small radius cam surface 81a is in contact with the cam follower 84 (rotation angle θ ₁ ), the spool valve 71 is at its forward limit and the on-off valve 60 is closed as described above. The start of this valve closing period θ ₁ is α = 230°, and the end thereof is α = 90°.
It is said that Here, when the cam follower 84 moves onto the valve opening cam surface 81c, the lever 82 rotates counterclockwise to drive the spool valve 71 to its backward limit, and fully open the on-off valve 60. The end of this valve opening period θ ₃ is set to α=105°. From this final stage, the cam follower 84 moves onto the large radius cam surface 81b and maintains the fully open state of the valve. The end of this valve opening period θ ₂ is α = 220°
From here, the cam follower reaches the valve closing cam surface 81.
When the lever 82 is moved clockwise from the valve spring 72 via the spool valve 71, the lever 82 reaches the starting point of the small radius cam surface 81a after the valve closing period θ ₄ has elapsed, and the spool valve 71 moves forward. At the end, the on-off valve 60 is fully opened.

That is, in this embodiment, as described above, the pump 3
After the suction stroke S of 0, the discharge operation of the plunger 35 is mechanically restrained and a rest stroke R ₁ (α=80
100°), and most of the valve opening period θ ₃ (α = 90° to 100°) is set in this rest stroke, so the latter half of the period θ ₃ (α = 100°) is set in the rest stroke. ~
105°) and the on-off valve 60 is almost fully opened, at which point the discharge operation is performed. Therefore, the water pressure p can rise more steeply. In addition, even if the cam separates from the cam follower due to the influence of inertia or spring at the end of the suction process in the drive system, the operation of the cam and cam follower will be stabilized during this rest stroke _R1 , and there will be no fluctuation in operation. .

Further, in this embodiment, a second rest stroke R ₂ (α=200° to 240°) is provided following the discharge stroke E, and the above-mentioned valve closing operation period is extended during this rest stroke R ₂ (α=220°).
230°), it is possible to provide a margin for the period θ ₄ , thereby making it possible to form the valve-closing cam surface 81d smoothly. This not only improves the followability of the spool valve 71 and improves the reproducibility of the valve closing timing, especially in high-speed looms, but also suppresses surging, particularly at the weft insertion nozzle 21, caused by the valve closing operation. This can limit the pulsating after-injection of the fuel.

In this embodiment, an automatic ball valve similar to the conventional one is used as the suction valve 40, but instead of this suction valve, a forced opening/closing type valve device similar to the discharge side opening/closing valve 60 and its valve driving device 80 is used. be able to.

The diagram SV shown in Fig. 2 shows an example of the operation timing in this case, where θ ₅ is the closing (fully closed) period of the suction side on-off valve, and θ ₆ and θ ₇ are the closing period of the valve. In the valve operation period and the valve opening operation period, the behavior of the intake water can be controlled by setting these operation periods θ ₆ and θ ₇ in the rest stroke R ₁ and the second rest stroke R ₂ , respectively, as shown in the diagram. We are trying to stabilize the situation.

Furthermore, as the valve driving device, an electromagnetic actuator or the like which operates in synchronization with the loom can be used.

(Effects) As explained above, according to the present invention, when supplying high-pressure water to the weft insertion nozzle, the pump can operate stably, and the water supplied from the pump is initially stabilized. Since the jet water is discharged at high speed and the scattering of the jet water stream can be suppressed, the above-mentioned problem particularly in high-speed looms can be solved.

[Brief explanation of the drawing]

FIG. 1 is an overall sectional view of essential parts showing one embodiment of the present invention, FIG. 2 is an explanatory diagram illustrating the operation timing of the present invention, FIG. 3 is an overall sectional view of essential parts illustrating a conventional device, and FIG. FIG. 4 is an explanatory diagram of the operation of the conventional device. 1... Pump drive cam, 8... Elastic body (coil spring), 10... Pump, 21... Weft insertion nozzle,
30...Pump, 35...Plunger, 39...
Elastic body, 50...Pump drive cam, 60...Opening/closing valve, 80...Valve drive device, 81...Valve drive cam.

Claims (1)

[Scope of Claims] 1. A device for feeding pressurized water from a pump that suctions and discharges water every revolution of a loom to a weft inserting nozzle, which stores energy in an elastic body along with the suction stroke of the pump, In a device that performs a discharge stroke using the stored elastic body, a rest stroke is provided between the suction stroke and the discharge stroke, an on-off valve is interposed between the pump and the weft insertion nozzle, and the loom is A pressurized water supply device for a water-injection type loom, comprising a valve drive device that synchronously drives the on-off valve, and the operation timing of the valve drive device is set so as to open the on-off valve during the rest stroke of the pump. .