JPS63260744A - Coolant fluid supply device - Google Patents

Abstract

PURPOSE:To surely clean a chip to be removed, by mounting a pressure increasing device, which generates a water hammer phenomenon by a blocking member intermittently opening and closing a return passage, to be interposed in a coolant fluid supply passage, in the case of a boring device. CONSTITUTION:Coolant fluid is allowed to flow into a high pressure chamber 18 of a pressure increasing unit 2 from a feed passage 4 by a volute pump and partly into a low pressure chamber 17 via a communication path 19 because a blocking member 22 is opened by a spring 26, and a supply device, filling a damper part 22c with the fluid through a groove 21c of a protruding member 21, returns the fluid to a storage tank from a passage 6. While the rest of the fluid is fed to a boring tool via a high pressure passage 5. If the predetermined time passes after the pump is operated, the supply device, increasing a flow speed of the coolant fluid to increase its dynamic pressure, moves the blocking member 22 to the right, till it closes the groove 21c, rapidly increasing pressure in the high pressure chamber 18 to generate water hammer, while if its reflective wave causes the pressure in the high pressure chamber 18 to decrease, the supply device moves the blocking member 22 to the left by a pressure in the damper part 22c, thus repeating the action in the above. In this way, the device well performs cooling of the boring tool, removal of a chip and washing.

Description

Detailed Description of the Invention [Industrial Application Field] The present invention provides a method for supplying coolant that cools the drilling tool and removes chips by jetting the coolant through the discharge passage of the drilling tool. It is related to the device.

[Problems that conventional techniques and inventions try to solve
When drilling a mortar hole etc. in a workpiece with a cutting tool, if the chips are not properly discharged from the hole, the cutting tool may be damaged or
Alternatively, if chips remain in this hole, there is a problem that it will have an adverse effect when the workpiece is assembled into a product. A jetting passage is provided in the tool, and this jetting passage is communicated via a supply passage with a storage tank in which a predetermined amount of coolant liquid is stored. - A coolant liquid supply device is generally used to eject a coolant liquid to remove the chips and cool the drilling tool.

However, when the blind hole becomes deep, the distance of the jetting passage increases, and the internal resistance of the coolant flowing down the jetting passage increases, and the pressure of the coolant jetting out from the jetting passage increases. As the coolant liquid decreases, the distance that the chips are transported from the blind hole by the coolant liquid increases, making it difficult to remove the chips.

This problem can be solved by changing the above feeding device to a larger one.
Alternatively, this can be avoided by, for example, replacing the supply device with a high-output one such as a plunger pump, but if the supply device is replaced with a larger one, the coolant fluid supply device itself becomes larger and there is less flexibility in the installation location. On the other hand, if the above-mentioned feeding device is changed to a plunger pump to obtain a high output, there is a problem that this plunger pump is not only relatively expensive but also requires complicated maintenance. . Further, due to the structure of the plunger pump, there is a limit to increasing the amount of coolant liquid ejected from the ejection passage, and it may be difficult to reliably remove the chips.

By the way, by blocking the fluid flowing through the pipe with, for example, an oscillating blocking member, the energy of the fluid flow is temporarily converted into high pressure energy on the upstream side of the valve body, resulting in the so-called water hammer phenomenon. Water hammer pumps are widely used to utilize this water hammer phenomenon to pump water to a higher location than the average water level.

The ratio P2/P+ of the pressure P2 which is upper bounded by this water hammer phenomenon and the pressure Pl of the fluid flowing through the pipe can be obtained up to about 20%. In this case, water ri in Pl
) is Q, and the water pressure at P2 is q, the efficiency of pressure increase is η = (q(P2-Pt))/((Q-q)Pt
), and the compression ratio P2/P1
The smaller the value, the better the efficiency, but there is little decrease in efficiency up to about P2/P1=10, and there is no problem in practical use.

Therefore, even if P2/P1=10 is adopted, P
At a pressure of 9/ci to 1=5, P due to the water hammer phenomenon described above.
It becomes possible to obtain a high pressure of 2=50Kg/aj.

However, in order to obtain this increased pressure, it is necessary for the blocking member to m19i the pipe line at a speed higher than a certain level, and the time T from when the blocking operation is started until it is completed is:
The length of the pipe line blocked by the above valve body is 1. If the sound speed of the fluid is a, it must be completed within the time determined by the formula T-241/a.

As a result, an impact sound is generated when this closing member is seated.

When the above-mentioned water hammer pump is used for pumping river water, etc., since the above-mentioned pipe g is long, it is possible to set the shutoff speed relatively slowly, and this! 7
It is possible to avoid the IJ sound becoming louder, and
Even if impact noise may be generated, it will not be a problem if it is used in an area with few people, but when this water hammer pump is installed in the coolant liquid supply device described above, the above pipe length 1 is naturally Since it is significantly shorter than the rivers in the area, it is necessary to shut off the pipeline as quickly as possible. Then, since the m-stroke that occurs when the valve body is seated cannot be ignored, it is difficult to use the water hammer pump as it is in the coolant liquid supply device.

[Object of the invention] The present invention has been made in view of the above circumstances, and is relatively inexpensive and easy to maintain, allows the water hammer phenomenon to be used with a simple configuration, and prevents the generation of impact noise. By generating high pressure in the coolant liquid, it is possible to cool the cutting tool and also to reliably remove and clean relatively heavy chips generated during machining with the cutting tool. The purpose is to provide a feeding device.

[Means for Solving the Problems] In the coolant supply device according to the present invention, a coolant liquid jetting passage is formed in the drilling tool, and this jetting passage and a storage tank storing the coolant liquid are configured to The supply Vt device is communicated through an interposed supply passage, and the supply passage is interposed with a pressure increase device that generates a water hammer phenomenon by means of a closing member that intermittently opens and closes the return passage. It is something.

[Function] With the above configuration, the pressure of the coolant liquid sent from the storage tank to the supply passage by the feeding device is increased by the pressure horn raising device interposed in the supply passage, and the coolant liquid is sent to the spout passage of the drilling tool. By spouting coolant liquid with increased pressure from the jetting passage, the drilling tool is cooled and chips are discharged from the machined hole during drilling.

[Embodiments of the invention] Hereinafter, the present invention will be described in detail with reference to the drawings.

1 to 5 relate to the first embodiment of the present invention, in which FIG. 1 is an overall view of the coolant/liquid supply device, FIG. 2 is a cross-sectional side view of the pressure raising device, and FIG. Enlarged view of part A in Figure 1, No. 4
The figure is a side view of FIG. 3, and FIG. 5 is a characteristic diagram in which the vertical axis shows the pressure of the coolant liquid and the horizontal axis shows time.

In these figures, reference numeral 1 indicates that the coolant liquid S is at a predetermined level.
2 is a pressure increasing device, 3 is a drilling machine which is an example of a machine tool, and the above storage tank 1 and the pressure RW
The pressure increasing device 2 and the drilling machine 3 are connected to each other through a high pressure passage 5.
It is communicated with. Note that these feeding passages 4 and high pressure passages 5
A supply passage for coolant 1 to liquid S is constituted by these.

Further, a return passage 6 for coolant S is connected to the pressure increase device 2, and this return passage 6 communicates with the storage tank 1, while the coolant liquid S is supplied to the perforation 1ffi3 via the high pressure passage 5. A drain passage 7 is provided for returning the coolant liquid S to the storage tank 1.

The storage tank 1 is installed on the floor F, and a part of the storage tank 1 is extended obliquely upward, and the tip 1 of this extended part is
a is formed parallel to the above floor. Further, a conveyor device 1C is disposed inside the storage tank 1, and the conveyor device 1C is arranged to reciprocate between the bottom 1b of the storage tank 1 and the tip 1a.
Chips and the like accumulated in the tip 1a are conveyed to the tip 1a, and are dropped into the swarf box 8 through an opening 1d provided in the tip 1a.

The starting end of the feeding passage 4 is immersed in the coolant liquid S stored in the storage tank 1, and a strainer 4a is provided at the immersed starting end. is extended to the outside of the storage tank 1, and communicated with the pressure increase device 2 via a centrifugal pump 9, which is an example of a feeding device, arranged on the upper surface of the storage tank Ps1. An in-line filter 11 and a surge absorption tank 12 are disposed between the pressure increase device 2 and the pressure increase device 2, and a check valve 4b is further provided between the in-line filter 11 and the surge absorption tank 12. .

As shown in FIG. 2, the pressure increase device 2 is constructed by fitting flanges 14 and 16 into both open ends of a cylindrical casing 13, with a low pressure chamber 17 on one side of the flange 14 and a low pressure chamber 17 on the other side. A high pressure chamber 18 is formed on the flange 16 side, and both chambers 17 and 18 communicate with each other via a communication passage 19 which is an opening. Further, the feed passage 4 and the high pressure passage 5 are communicated with the high pressure chamber 18, while the return passage 6 is communicated with the low pressure chamber 17.

Furthermore, a proximal end 21a of a protruding member 21 extending in the direction of the communicating path 19 is fixed to a substantially central portion of the flange 14 on the low pressure chamber 17 side.
A cylindrical closing member 2 whose one end is closed is disposed at the distal end 21b of the
2 is crowned.

The area around the closed portion of this closing member 22 is formed to have a large diameter, and when this portion formed to have a large diameter is inserted into the communicating path 19, it becomes a closing portion 22a that closes this communicating path 19. ing. Further, the cylinder 22b formed in the closing part 22a is slidably fitted to the tip 21b of the protruding member 21, and the cylinder 22b and the tip 21b are slidably connected to each other.
The area surrounded by and becomes the damper part 22c when the closing part 011 slides.

A hole 21d is formed in the axial direction of the protruding member 21, and the shaft 23 is slidably inserted into the hole 21d. The tip end 23a of this shaft 23 is fixed to the closing part 22a of the closing member 22, while the base end 23b of this shaft 23 has a stopper 24 that restricts the sliding of the closing member 22 in the valve opening direction. is fixed so that it can be positioned.

The tip portion 21b of the protruding member 21 includes the low pressure chamber 17.
and the damper portion 22c of the closing member 22 attached to the tip portion 21b of the protruding member 21.
c is carved, and when the closing member 22 is slid in the direction of the volume valve, the low pressure chamber 17 and the inside of the damper portion 22c of the closing member 22 communicate with each other. When the communicating path 19 is closed, this closing member 2
By covering the entire length of the groove 21c with the second cylindrical body 22b, the low pressure chamber 17 and the inside of the damper portion 22c are cut off.

J3, the cross-sectional area of the groove 21c is constant up to a predetermined length m, but the low pressure chamber 17 side of the groove 21c is the protruding member 21.
The closure member 22 is formed loosely toward the outer peripheral surface of the closure member 22.
The frontage cross-sectional area of the groove 21c is gradually reduced just before the low pressure chamber 17 and the inside of the damper part 22C are shut off, and furthermore, the total length n of the groove 21c is
After the communicating path 19 is closed by the movement of 1. By doing so, the closing member 22 covers the entire length of the groove 210, and the inside of the damper portion 22C of the closing member 22 and the low pressure chamber 17 are set to be cut off.

Further, a spring retainer 22d is formed on the cylindrical body 22b of the closing member 22, and a compression coil spring 26 as an elastic member is installed between the spring retainer 22d and the seven flange 14, The member 22 is always biased in the releasing direction.

The high pressure passage 5 communicating with the high pressure chamber 18 has a check valve 5
It is connected to the high-pressure accumulator 27 via a, while it is branched in the middle and connected to the drilling machine 3.

This drilling machine 3 is installed on a bed 3a fixed to a floor F.
and a headstock 3C arranged on the bed 3a via a feed unit 3b.

Further, a work table 3q whose height and angle are freely adjustable is arranged on the bed 3a, and a work W is fixed onto this work table 3g.

The headstock 3G is rotatably provided with a main shaft 3d that protrudes in the front-rear direction of the headstock 3C, and a coolant liquid S supply path (not shown) is formed in the main shaft 3d. A pulley 3f interlocked with a motor 3e is fixed to a portion of the main shaft 3d that projects rearward from the headstock 3C.

Further, an inducer 28 is disposed at the rear end of the main shaft 3d, and the high pressure passage 5 extending from the pressure increase device 2 is communicated with the inducer 28, and the flow flows down through the high pressure passage 5. The coolant liquid S is sent to the feed path of the main shaft 3d via the inducer 28.

Further, a gun drill 29, which is an example of a drilling tool, is attached to the tip of the main @3d that protrudes forward from the headstock 3C, and the gun drill 29 is used to drill the hole B1 in the workpiece W. It is composed of

As shown in FIGS. 3 and 4, this gun drill 29 is formed into a cylindrical shape with a cutout 29d, and a cutting blade 29b for drilling the hole B1 is fixed to the tip of the cutout. . Further, a jetting passage 29C is formed in the axial direction of the gun drill 29, and the jetting passage 29C communicates with the coolant feeding passage of the main shaft 3d. The liquid S is ejected, and the chips in the hole B1 are removed together with the coolant liquid S from the hole B1, and the gun drill 29 is cooled.

Furthermore, a drainage passage 7 is connected to the bed 3a, and this drainage passage 7 communicates with the storage tank 1, so that the coolant liquid S jetted out from the jetting passage 29c falls onto the bed 3a. From this bed 3a, liquid flows into the storage tank 1 via the drainage passage 7.

In addition, a return passage of the pressure increase device 2 is connected to the vicinity of a portion of the drain passage 7 that communicates with the storage tank 1, and these tuft passages 6 and the drain passage 7 are communicated with each other. A filter member 1e is disposed between this part and the starting end of the feeding passage 4 which is immersed in the coolant S of the storage tank 1, and a filter member 1e is disposed between the above-mentioned return passage 6 and the drain passage 7. Ripples in the coolant S in the storage tank 1 due to the coolant S flowing into the storage tank 1, chips, etc. are prevented as much as possible.

Next, the operation of the coolant liquid supply device having the above-described configuration will be explained.

When the centrifugal pump 9 is operated, the coolant liquid S in the storage tank 1 is sucked through the strainer 4a, and while flowing down the feeding passage 4, it is difficult for the coolant liquid S to be filtered by the strainer 4a at the in-line filter 11. While the fine foreign matter is filtered, some of it flows into the surge absorption tank 12, while the other coolant liquid S flows into the high pressure chamber 1 of the pressure upper limit device 2.
8.

Initially, the closing member 22 is biased by the spring spring 26 to open the valve, so that a portion of the coolant S flowing into the high pressure chamber 18 is absorbed. is connected to the low pressure chamber 1 via the communication path 19.
7 and the damper portion 22 of the closing member 22 from the low pressure chamber 17 through the groove 21c carved in the protruding member 21.
c and is filled with the damper portion 22c, and is returned from the low pressure chamber 17 to the storage tank 1 via the return passage 6. Further, the remainder of the coolant liquid S in the high pressure chamber 18 is branched to the high pressure passage 5 communicating with the high pressure chamber 18, and flows into the high pressure accumulator 27 via the check valve 5a, while flowing through the inductor I 28. The main shaft 3 of the drilling machine 3
Bed 3a of the drilling machine 3 from the jetting passage 29G of the gun drill 29 through a feed passage (not shown) formed at d.
be dropped upwards.

When the centrifugal pump 9 is operated for a predetermined period of time and the flow rate of the coolant liquid S flowing from the feed passage 4 into the high pressure chamber 18 of the pressure increase device 2 becomes high, the coolant 1
- The dynamic pressure due to the flow rate of the liquid S increases and the closing member 22 is pressed, so that the closing member 22 provided in one of the communication passages resists the biasing force of the compression coil spring 26 due to the coolant liquid S. It slides.

The sliding speed of the closing member 22 is gradually increased from a stationary state. When this shop O'' is started, the coolant liquid S filled in the damper part 22c of the closing part 4422 flows out to the low pressure chamber 17 through the groove 21c, so that the coolant in the damper part 22C The liquid S does not have any influence on the upper limit of the sliding speed of the closing member 22, and the communication path 19 of the pressure upper limit device 2 is rapidly blocked by the r'A closing portion 22a of the closing member 22. Ru.

This blocking member? After the communication path 19 is closed by the closing portion 22a of No. 2, the closing member 22 further slides to cover the entire length of the groove 210, and is moved until just before the damper portion 22c and the low pressure chamber 17 are shut off. and the cylindrical body 2 of this closing member 22
Groove 21c carved in the protrusion member 21 by 2b
By gradually reducing the opening cross-sectional area of
As the opening area of the groove 21c decreases, the pressure of the coolant liquid S in the damper portion 22C increases, so that the sliding movement of the closing member 22 is gently regulated. Ru.

Finally, the entire length of the groove 21c is covered by the falling movement of the closing member 22, and the pressure of the coolant liquid S in the damper portion 22C becomes maximum, and this closing member 22 moves as shown by the chain line in FIG. It is stopped at the end position. As described above, after the closing member 22 closes the communication passage 19, the valve speed is rapidly increased until the closing member 22 moves further and reaches the stroke end due to the above-mentioned damper action. This makes it possible to fully generate the water hammer phenomenon, and since the valve speed is reduced by the damper action until the stroke end is reached after the communication passage 19 is closed, the impact noise caused by the closing member 22 is reduced. This also prevents the closing member 22 from being worn out.

The communication path 19 is closed by the closing portion 22a of the closing member 22.
If the high pressure chamber 18 of the pressure increase device 2 is suddenly blocked, the flow of the coolant liquid S from the high pressure chamber 18 to the low pressure chamber 17 via the communication path 19 is abruptly stopped.
A so-called water hammer phenomenon occurs, and the pressure of the coolant liquid S in the high pressure chamber 18 rises instantaneously.

As mentioned above, the pressure increase in this case is such that the pressure hP1 of the coolant liquid S in the feeding passage 4 is, for example, 5 to 9/1f.
Even if it is fl, the pressure P2 of the coolant liquid S in the high pressure chamber 18 is raised to about 50.9/ci (If1-).

Then, the coolant liquid S in the high pressure chamber 18 flows into the high pressure passage 5 with this increased pressure, increasing the pressure of the coolant liquid S in the high pressure accumulator 27 via the check valve 5a, while increasing the pressure of the gun drill 29. Spout passage 2
Coolant liquid whose pressure has been increased is supplied to 9c, and this coolant liquid S whose pressure has been increased is jetted out from the jetting passage 29c.

Moreover, the pressure increased in the high pressure chamber 18 causes the coolant 1 to the liquid S in the feeding passage 4 to flow backward. However, since the feed passage 4 is provided with a check valve 4b, the coolant liquid S is prevented from reaching the centrifugal pump 9 and the in-line filter 11, and the coolant liquid S flowing backward through the feed passage 4 is prevented from reaching the centrifugal pump 9 and the in-line filter 11. It is absorbed into the surge absorption tank 12 interposed in the feed passage 4.

In addition, this surge absorption tank 12 absorbs the shock generated by the high pressure in the high pressure chamber 18 and transmitted to the feed passage 4, and has the effect of preventing the generation of noise in the piping system of the entire coolant liquid supply device. It also has

Immediately after high pressure is generated in the high pressure chamber 18, due to the nature of the water hammer phenomenon, a so-called reflected wave is generated in which negative pressure is generated in the high pressure chamber 18, and this reflected wave propagates to the feed passage 4 and the high pressure passage 5. be done.

The coolant S in the feeding passage 4 is sucked by this reflected wave, but there is a surge absorption tank 12 in the feeding passage 4.
Since the coolant S is stored in the surge absorbing tank 12, this reflected wave does not affect the centrifugal pump 9, and the surge absorption tank 12 in which the coolant S is stored increases the pressure increase device 2. The coolant liquid S is stably supplied to.

Further, the coolant liquid S in the high pressure passage 5 tends to be sucked into the high pressure chamber 18 by the reflected waves generated in the high pressure chamber 18, but the high pressure passage 5 is provided with a check valve 5a. Therefore, the propagation of the reflected wave is stopped by this check valve 5a.

Further, when a reflected wave is generated in the high pressure chamber 18, the pressurization of the coolant liquid S that has been jetted out from the jetting passage 29G of the gun drill 29 is stopped, but the pressure of the high pressure accumulator 27 is reduced to the high pressure passage 5. Therefore, the ejection pressure and ejection speed of the coolant liquid S ejected from the ejection passage 29C are gradually reduced as the pressure of the high pressure accumulator 27 is reduced.

When the pressure inside the high pressure chamber 18 is reduced, the closing member 2
Since the pressure of the coolant liquid S in the damper portion 22C of No. 2 is higher than that of the coolant liquid S in the high pressure chamber 18, the closing member 22 is slid toward the high pressure chamber 18 by the biasing force of the compression coil spring 26. The high pressure chamber 18 and the low pressure chamber 17 communicate with each other via the communication path 19, and the low pressure chamber 17 and the damper portion 22c of the closing member 22 communicate with each other via the groove 21C carved in the protruding member 21. communicated,
The pressure of the coolant liquid S in the damper part 22C is released, and the damper part 22C is filled with the coolant liquid S again. In this case, the closing member 22 is prevented from sliding in the valve opening direction by a stopper 24 fixed to the shaft 23.
However, since the closing member 22 is buffered by the coolant liquid S flowing into the high pressure chamber 18 from the feed passage 4 during the valve opening operation of the closing member 22, the valve opening by the closing member 22 is stopped. The impact of time is prevented from occurring.

Further, when the pressure in the high pressure chamber 18 is reduced, the pressure accumulated in the surge absorption tank 12 and the centrifugal pump 9 cause the coolant liquid S in the supply passage 4 and the surge absorption tank 12 to flow into the high pressure chamber 18. The closing member 22 is slid again to close one of the communication passages, thereby generating the next water hammer phenomenon in the high pressure chamber 18, and the same effect as described above is performed, and the above-mentioned ejection passage is closed. The coolant liquid S spouted from 29C is pressurized, and this coolant liquid S
The ejection speed and ejection pressure of are increased again.

That is, as shown by the solid line in FIG. 5, the pressure in the high pressure passage 5 is equal to the pressure P before the water hammer phenomenon occurs in the high pressure chamber 18.
1, the water hammer phenomenon causes the pressure to rise to P2, and then, due to the generation of reflected waves, the pressure decreases to below the pressure P1, and the next water hammer phenomenon causes the pressure to rise again to the pressure P2. Then, the pressure accumulated in the high pressure accumulator 27 is
As shown by the chain line in FIG. 5, the pressure in the high-pressure passage 5 is raised to P2, reaches the same pressure P2 after a predetermined time, and when the pressure in the high-pressure passage 5 decreases to below P1 due to the reflected wave, the above-mentioned The pressure inside the high pressure accumulator 27 is the coolant liquid S
As the coolant is ejected from the ejection passage 29C, it is lowered to P3, and then the pressure in the high pressure passage 5 is again raised by the water hammer, thereby raising the pressure to P2, and the coolant is ejected from the ejection passage 29c. The ejection pressure and ejection speed of the liquid S continue without interruption with constant fluctuations as shown by the chain line in FIG.

This cycle of variation can be varied by moving the stopper 24 of the shaft 23 that restricts the sliding movement of the closing member 22 in the valve opening direction. That is, when the position of the stopper 24 is moved in the direction away from the closing member 22, the closing member 22 is moved in the valve opening direction by the biasing force of the compression coil spring 26, and the communication passage 19 is closed. It takes more than a certain amount of time, and the number of opening/closing cycles decreases, and on the other hand, when the stopper 24 is moved toward one of the communicating paths, the number of cycles increases.

In this state, the motor 3e of the drilling machine 3 is rotated, and this rotation is transmitted to the main motor 3 of the drilling machine 3 via the pulley 3f.
d, and the gun drill 2 is transmitted to the gun drill 2 by this main shaft 3d.
9 starts rotating. Next, the feeding unit 3b
J, the gun drill 29 is slid in the direction of the work W, and the cutting edge 29b of the gun drill 29 cuts the work W.
A hole B1 is drilled in the hole B1. Heat and chips are generated during this drilling.

As shown in FIG. 3, the ejection passages 29 of these two gun drills
From c, the coolant liquid S is ejected from the tip of the gun drill 29 at a predetermined cycle pressure, and the ejected coolant liquid S is discharged to the outside of the workpiece W through a notch 29d carved in the gun drill 29. Since the heat generated during drilling is cooled by the coolant S,
The chips resulting from this perforation fall together with the coolant liquid S through the notch 29d onto the bed 3a, and are returned to the storage tank 1 through the drain passage 7 connected to the bed 3a.

Further, when the drilling of the hole B1 is completed and the gun drill 29 is pulled out from the hole B1, the coolant S that has been discharged through the notch 29d of the gun drill 29 is directly discharged from the hole B1. It falls onto bed 3a. Further, the chips remaining in the holes 8+ are dropped together with the coolant liquid S onto the bed 3a, and are returned to the storage tank 1 via the drain passage 7.

The chips returned to this storage tank 1 sink in the coolant liquid S in the storage tank 1 at this temperature, are conveyed by a conveyor system E1C arranged in this storage tank 1, and are transferred to the tip 1a of the storage tank 1. The chips are dropped into the chip box 8 through the provided opening 1d.

In this embodiment, since the surge absorption tank 12 is interposed in the feed passage 4, it has the effect that the supply of the surcharge liquid S to the pressure increase device 2 is stabilized.

In addition, since the closing member 22 of the pressure device 2 is provided with a stopper 24 that can be positioned in one position, the ejection passage 29
This has the effect that the cycle pressure of the coolant liquid S spouted from G can be arbitrarily set.

In this embodiment, a gun drill 29 is used as an example of a drilling tool.
Although an example in which the gun drill 29 is used has been described, the drilling tool in the present invention is not limited to the gun drill 29 described above, and may be, for example, a drilling tool such as a hollow drill or a boring tool.

Furthermore, in this embodiment, the drilling machine 3 has been described as an example of a machine tool in which the above-mentioned drilling tool is held, but the machine tool is not limited to the drilling machine 3 alone, and may include, for example, an I&A, a polling machine, etc. There is no problem even if it is a machine tool.

Furthermore, in this embodiment, a case has been described in which a white hole is bored in the workpiece W by the drilling tool, but the object to be machined by the above-mentioned drilling tool is not limited to a blind hole, but also a through hole, a boring process, etc. Of course, it is possible to use it for processing the same area.

FIG. 6 is a cross-sectional side view of a pressure raising device according to a second embodiment of the present invention. Incidentally, the same members and members having the same function as those in the first embodiment described above are given the same reference numerals, and the explanation thereof will be omitted.

In this embodiment, a protruding member 21 is integrally provided on the flange 14 on the low pressure chamber 17 side, and the flange 14
A protrusion 14a is formed on the side opposite to the low pressure chamber 17, and a cylinder chamber 31 is formed inside the protrusion 14a.

A hole 21d is formed in the axial direction of the protruding member 21, and the shaft 23 is inserted through this hole 21. Both ends of this shaft 23 are exposed to the communication passage 19 of the pressure increase device 2 and the cylinder chamber 31, and the communication passage 19 is exposed to the cylinder chamber 31.
On the side exposed to this shaft 23 a compression coil spring 26 is fixed to the obsolete closure member 22 .
The portion exposed to the cylinder chamber 31 is screwed onto a piston 32 that is slidably disposed in the cylinder chamber 31.

Further, an annular tM 24 c communicating with the low pressure chamber is provided in the middle of the hole 21d, and the closing member 22
The coolant liquid S leaking from the damper portion 22G through the hole 21d is allowed to escape to the low pressure chamber 17, thereby preventing the coolant liquid S from reaching the cylinder chamber 31.

Front chamber 31a sandwiching the piston 32 of the cylinder chamber 31
The rear chamber 31b is provided with a protruding boat 31C and a retreating boat 31d, and the protruding boat 31G
After the reversing boat 31d is communicated via the air passage 33 with a 4-bot, 2-position directional control valve 34 equipped with, for example, a solenoid 34a, air is stored in one of the valves at a predetermined pressure. It is connected to an air source 36, and the other side is communicated with the atmosphere via a muffler 37.

Further, the solenoid 34a is connected to a power source 39 via a frequency switching device 38, and then electrically connected to a ground 41.

With this configuration, the coolant liquid S flows from the supply passage 4 into the high pressure chamber 18 and flows from the high pressure chamber 18 to the low pressure chamber 17 via the communication passage 19, while flowing down from the high pressure chamber 18 to the high pressure passage 5. Then, the current from the power source 39 is passed to the solenoid 34a via the frequency switching device 38, the directional control valve 34 is switched, and the air from the air source 36 is sent from the reverse boat 31d to the rear chamber 31b of the cylinder chamber 31. be provided.

Then, the piston 3 arranged in this cylinder chamber 31
2 is moved, the closing member 22 is slid through the shaft 23 screwed onto the piston 32, and the communicating passage 19 is closed by the closing member 22, thereby causing a water hammer phenomenon in the high pressure chamber 18. As a result, high pressure is generated in this high pressure chamber 18.

In the present embodiment, it is possible to expect the same effects as in the first embodiment described above, and since the closing member 22 is configured to be slid by the piston 32, there is no ejection from the drilling tool. This has the effect that it is possible to arbitrarily set the cycle in which the pressure of the coolant liquid S is increased.

Although this embodiment is configured to use air having a predetermined pressure to slide the closing member 22, the material for sliding the closing member 22 is not limited to air. For example, hydraulics.

It is also possible to configure it to slide by using an electromagnetic actuator or other communication configuration.

Further, in this embodiment, a directional control valve 34 equipped with a solenoid 34a is used to switch the air from the air source 36, but the means for switching the air is limited to this directional υ control valve 34. Instead, it may be switched by a rotary valve or the like, for example.

Further, the means for sliding the closing member 22 is not limited to the cylinder chamber 31 and the piston 32, but can also be slid by, for example, a motor.

7 to 9 relate to a third embodiment of the present invention, in which FIG. 7 is a cross-sectional side view of the pressure increasing device, and FIG. 8 is a cross-sectional side view of the pressure increasing device, and FIG.
9 is a view taken along the line IX-IX in FIG. 7.

In this embodiment, a shaft chamber 42 is disposed on the bottom surface of a cylindrical low pressure chamber 17, and seven flange 1 is provided on the top surface of this low pressure chamber 17.
4 is fitted, and the return passage 6 is communicated with the low pressure chamber 17 via this flange 14. In addition, the above-mentioned low pressure chamber 1
As shown in FIG. 9, a long hole-shaped communication passage 19 is formed in the wall surface 17a of the side part 7, and the low pressure chamber 17 is connected to the supply passage 4 and the high pressure passage 5 through this communication passage 19. It communicates with a connected high pressure chamber 18.

In addition, the low pressure chamber 17 includes a closing portion 2 having a certain width.
2εl and a base end portion 22e formed at a substantially right angle to the closing portion 22a.
is placed in the shift compartment 42, while the shifter 1? A foot 43 is rotatably installed inside with a bearing 43a,
The tip 43b of the shaft 43 is exposed to the low pressure chamber 17, and the rotary valve 22 is attached to the tip 43b.
The base end portion 22e of is fixed.

This rotary valve 22 is connected to the tip 4 of the shaft 43.
The rotary valve 22 is configured to be rotatable within the low pressure chamber 17 centering on the closed portion 22a of the rotary valve 22.
rotates with a minute gap with respect to the wall surface 17a of the low pressure chamber, and with this rotation, the closed portion 22a
Accordingly, the communication path 19 is configured to be 1 mlff+.゛Also, the above-mentioned low pressure chamber 17 and the seat? A sealing member 44 is interposed between the shaft chamber 42 and the shaft chamber 42 to prevent the coolant S in the low pressure chamber 17 from penetrating into the shaft chamber 42 .

Further, a hydraulic motor 46, for example, is disposed on the V end portion 43c side of the shaft 43, and the hydraulic motor 46 is arranged on the V end portion 43c side of the shaft 43. W NI
43c and the output shaft 46a of this hydraulic motor 46 are connected and fixed.

The feeding boat 46b of the hydraulic motor 46 also has a two-bot, two-position directional control valve 47. Flow M control valve 48. Variable hydraulic pump 49
The return boat 46c of the hydraulic motor 46 is also communicated with the oil tank 51.

With this configuration, when the solenoid 47a is excited with the coolant S flowing into the high pressure chamber 18 through the supply passage 4, the oil from the oil tank 51 supplied by the variable hydraulic pump 49 will It is fed to the feeding boat 46b of the hydraulic motor 46 while being regulated by the flow rate control valve 48. Then, the rotation of the hydraulic motor 46 is started, and this rotation is transmitted to the shaft 43 and the rotary shaft in the low pressure chamber 17 When the valve 22 is rotated, this rotary valve 22
The communication path 19 is periodically closed by the closing portion 22a.

When this communication passage 19 is closed, high pressure is generated in the high pressure chamber 18, and the coolant liquid S generated in this pressure chamber 18 flows into the high pressure passage 5 connected to this high pressure chamber 18.

In this embodiment, the hydraulic motor 46 is controlled by a flow rate control valve 48 and a directional control valve 47, but the control means for the hydraulic motor 46 is not limited to this configuration. For example, a variable hydraulic pump It is also possible to configure it so that it is directly controlled by 49.

In addition, in this embodiment, the rotary valve 2 as a closing member
Although the rotary valve 22 is configured to be rotated by a hydraulic motor 46, the means for rotating the rotary valve 22 is not limited to this hydraulic motor 46, and may be, for example, a pneumatic or electric motor.

FIG. 10 is an overall view of a coolant liquid supply device according to a fourth embodiment of the present invention.

In this embodiment, the storage tank 1 for the coolant liquid S is configured as a concentrated coolant treatment tank. This storage tank 1 is divided into a sedimentation tank 52 in which a conveyor device 1C is arranged and a supernatant tank 53, and these sedimentation tank 52 and supernatant tank 53 are communicated with each other by a passage 57.

A plurality of pumps 54 connected to motors 54a are arranged in the sedimentation tank 52, and the upstream side of the passage 57 is branched and connected to these pumps 54, while the downstream side of the passage 57 is connected to the pumps 54. A filter system 56 is interposed.

Further, a trough 52aIfi is connected to the sedimentation tank 52, and a pressure is applied to this trough 52a. A return passage 6 for the coolant liquid S connected to the device 2 is communicated with the device 2 .

Furthermore, a plurality of pumps 9 each having a motor 9a are arranged in this supernatant tank 53 as well, and the upstream side of the feed passage 4 is branched and connected to these pumps 9.

The midway of this feeding passage 4 is branched into many parts, and among the branched feeding passages 4, the feeding passage to the machine tool that requires high-pressure coolant fluid is communicated with the pressure increase device 2, and the feeding passage 4 is connected to the pressure increasing device 2. An in-line filter 11, a spiral cylinder 158 used as a booster pump, a check valve 4b, and a surge absorption tank 12 are interposed between the branched portion of the feed passage 4 and the pressure increase device 2. ing.

With this configuration, when the motor 9a is operated, the pump 9 is operated by the motor 9a Ui19! and supernatant tank 5
The coolant liquid S of No. 3 is flowed down to the feeding passage 4. The coolant liquid S is then flowed down in the direction of the perforation t13 through the plurality of branched oil supply passages 4, respectively.

After this coolant liquid S is filtered by an in-line filter 11, the pressure is further increased by a centrifugal pump 58,
It flows into the surge absorption tank 12 and the pressure raising device 2 via the check valve 4b, becomes high pressure by the water hammer phenomenon of the pressure raising device 2, and is ejected from the gun drill 29 of the drilling machine 3.

Further, the coolant liquid S returned from the return passage 6 is
The sediment flows into WJ 52 1 to rough 52a and is sucked into the pump 9 again.

The coolant S supplied to the drilling hole 13 is ejected from the gun drill 29 to the processing hole B1 of the workpiece W, and then falls onto the bed 3a together with chips, and the liquid drain passage 7 connected to the bed 3a of the drilling machine 3 , and are sent to the sedimentation tank 52 of the storage tank 1 together with the chips via the trough 52a. The above-mentioned 1. separated in this settling tank 52. lJ powder is this powder 52
It is conveyed and discharged by a conveyor device 1C arranged at. Further, the coolant liquid S from which the chips have been separated in the sedimentation tank 52 is pumped to a pump 5 connected to a motor 54a.
4 and through passage 57 to filter system 5.
6 and sent to the above-mentioned supernatant tank 53, and then supplied to each punching machine 3 again.

In this embodiment, a centrifugal pump 58 as a booster pump is installed in each of the branched feeding passages 4, but this centrifugal pump 58 is installed at the most upstream side of the feeding passage 4. It is also possible to omit this by increasing the pressure of the pump 9 to some extent.

In this embodiment, since the reservoir W11 is configured as a concentrated coolant treatment tank, it is not necessary to provide this reservoir 11 for each drilling type 3, which has the effect of reducing the installation area.

Moreover, in this embodiment, the storage tank 1 sinks! 2 tanks 5
2 and a supernatant tank 53, and the structure is such that only the coolant liquid S from which chips have been separated in the settling tank 52 is sent to the supernatant tank 53, so that it flows down to the feeding passage 4. This has the effect of preventing foreign matter such as the chips from being mixed into the coolant liquid S.

11 to 15 relate to a fifth embodiment of the present invention, in which FIG. 11 is an overall view of a coolant liquid supply device, FIG. 12 is a sectional side view of a pressure raising device, and FIG. 13 is a twelfth xm- xm
FIG. 14 is an enlarged view of section B in FIG. 12, and FIG. 15 is a view taken along the twelfth Xv arrow.

In this embodiment, the high pressure passage 5 used in the first embodiment and the high pressure accumulator 2 interposed in this high pressure passage 5 are used.
7. While the check valve 5a and the inducer 28 are eliminated, a pressure increasing device 2 is disposed at the rear end of the drilling machine 3 where the inducer 28 was placed, and this pressure increasing device 2 is installed in the drilling machine 3. It is fixed to the headstock 3C of No. 3.

This pressure increase device 2 has the same configuration as that used in the third embodiment described above, but the pressure increase device 2 of this third embodiment has a low pressure chamber 17 and a high pressure chamber 18. The rotary valve 22, which is an open base member, has been swapped in position.
The feeding passage 4 communicates with a high pressure chamber 18 in which the pressure chamber 18 is rotatably arranged.

The rotary valve 2 is also provided on the wall of this high pressure chamber 18.
A communication passage 19 in the form of a long hole, which is closed at 2, is formed, and the high pressure chamber 18 is communicated with the low pressure chamber 17 via this communication passage 19. Furthermore, a return passage 6 is provided in this low pressure chamber 17.
The high pressure passage 5 that was connected in the previous embodiment is eliminated from this part.

The rotary valve 22 disposed in the high pressure chamber 18 has a balance weight 22f on the side of the rotary valve 22 facing the closed portion 22a. Further, the base end 22e of the rotary valve 22 is fixed to the tip 43b of the shaft 43 through which the high pressure passage 5 is formed in the axial direction, by a key 43d and a stop bolt 43e.

As shown in FIG. 14, the high pressure chamber 18 and the shaft 4
A labyrinth packing 59 is provided between the sealing member 44 of the shaft chamber 42 through which the shaft chamber 3 is inserted, and the pressure of the coolant liquid S flowing into the high pressure chamber 18 is applied to the sealing portion of the shaft chamber 42 and the sealing member 44 of the shaft chamber 42. The coolant liquid is prevented from leaking from the seal member 44 by not acting directly on the seal member 44. Further, a drain passage 42a is provided between the labyrinth packing 59 of the shaft chamber 42 and the sealing member 44, and the coolant liquid S leaking to the sealing member 44 side via the labyrinth packing 59 is drained to the bed 3a. Configured to be dropped.

The base end 43c of the shaft 43 protrudes from the shaft chamber 42, and this protruding portion is fixed to the rear end 3h of the main shaft 3d of the drilling machine 3 via a coupling 60. .

This coupling 60 is connected to the seat 11 as shown in FIG.
A square pin 60b is formed protruding from a portion of the foot 43 that projects from the shift chamber 42 at right angles to the axial center of the shaft 43, and this square pin 60b is formed at the rear end 3h of the main shaft 3d. A hole 60a is formed in the rear end portion 3h, and the hole 60a is engaged with the engaging portion 60C.
The base end portion 43c of the shaft 43 is inserted into.

An O-ring 61 is attached to the lζ portion of the shaft 43 that is inserted into the hole 60a, and the coolant liquid S flows into the hole 60a through the high-pressure passage 5 formed in the axial direction of the shaft 43. Leakage is prevented.

Further, a feed passage 62 communicating with the hole 60a is formed in the axial direction of the main shaft 3d, and this feed passage 62 communicates with the ejection passage 29c of the gun drill 29.

With this configuration, the rotation of the centrifugal pump 9 is started, and the main shaft 3d is rotated by the motor 3e while the coolant S in the storage tank 1 is flowing into the high pressure chamber 18 of the pressure increase device 2 through the supply passage 4. start.

Then, the rotation of this main shaft 3d is transmitted to the shaft 43 via the coupling 60, and the tip end 4 of this shaft 43
A rotary valve 22 as a closing member fixed to 3b is rotated within the high pressure chamber 18.

If the communication passage 19 is not blocked by the closure part 22a of the rotary valve 22, the fluid resistance in the high pressure passage 5 is greater than the fluid resistance in the communication passage 19, so that the fluid flows into the high pressure chamber 18. Most of the coolant liquid S flows into the low pressure chamber 17 via the communication passage 19, returns from the low pressure chamber 17 to the storage tank 1 via the return passage 6, and a portion flows through the high pressure passage 5 to the gun drill 29. is dropped onto the bed 3a of the drilling machine 3 from the jetting passage 29c.

Next, when the communication passage 19 is closed by the closure part 22a, the flow of the coolant liquid S flowing into the low pressure chamber 17 through the communication passage 19 is rapidly blocked, and water is not allowed to flow into the high pressure chamber 18. An impact phenomenon occurs, and the pressure of the coolant liquid S in the high pressure chamber 18 is rapidly increased.

Then, the coolant liquid S in the high pressure chamber 18 flows into the high pressure passage 5.
It flows into the feed passage 62 of the main @3d and is ejected from the ejection passage 29C of the gun drill 29.

Further, when the pressure in the high pressure chamber 18 is increased due to the water hammer phenomenon, this pressure tends to leak to the shirts 1 to 42 connected to the high pressure chamber 18, but the high pressure chamber 18 and the A labyrinth packing 59 is provided between the shaft chamber 42 and the shaft chamber 42.
Since this labyrinth packing 59 is interposed, leakage of the pressure in the high pressure chamber 18 is prevented. In this case, the high pressure chamber 1 is
Although the coolant liquid S of No. 8 enters into the shaft chamber 42 side, the seal member 44 disposed in this shaft chamber 42 prevents the coolant liquid S from entering into the innermost part of this shaft chamber 42. At the same time, the coolant liquid S that has entered between the labyrinth rose 4:n 59 and the seal member 44 is drained out through the drain passage 42a.

In this embodiment, the high pressure accumulator 27 is connected to the high pressure passage 5.
is removed and the pressure raised by the pressure increase device 2 is directly transmitted to the jetting passage 29G, so that the jetting pressure and speed of the coolant liquid S jetted from these two jetting passages are lower than the pressure raised by the pressure raising device 2. It fluctuates periodically according to the operation of
This has the effect that chips in the hole B1 of the workpiece W can be more easily removed.

Further, in this embodiment, since the rotary valve 22 is provided with a balance weight 22r, the rotary valve 22 has the effect of smoother rotation.

FIG. 16 is an overall view of a coolant supply device according to a sixth embodiment of the present invention.

In this embodiment, the storage tank 1 for the coolant liquid S of the fifth embodiment described above is configured as a centralized coolant treatment tank, and has the same effect as the fifth embodiment, and the storage tank This embodiment has the same effect as the fourth embodiment described above, in which Embodiment 1 is configured as a central processing tank.

In these embodiments, an in-line filter 11 is interposed in the supply passage, and the in-line filter 11 is configured to filter the coolant S in the supply passage. It is also possible to dispose of the waste water, and to arrange a filter device in the drainage passage so that the chips can be filtered by the filter device.

[Effects of the Invention] As explained above, according to the coolant liquid supply device of the present invention, a pressure increase device is installed in which a water hammer phenomenon is generated by a closing member that intermittently opens and closes a return passage. Even if a centrifugal pump set to low pressure is used in the delivery device, the pressure of the coolant liquid will increase.
This has the effect that it is easy to increase the ejection pressure and ejection m of the coolant liquid ejected from the ejection passage of the drilling tool.

In addition, since the water hammer phenomenon is generated in the pressure increase device by the closing member that intermittently opens and closes the return passage, it is possible to reliably prevent the occurrence of a third impact sound, and the coolant equipped with this pressure increase device can This has the effect of preventing the entire liquid supply device from increasing in size, thereby increasing the freedom of installation location.

[Brief explanation of the drawing]

1 to 5 relate to the first embodiment of the present invention, in which FIG. 1 is an overall view of the coolant liquid supply device, FIG. 2 is a cross-sectional side view of the pressure increase device, and FIG. 3 is the same as that of FIG. An enlarged view of part A, FIG. 4 is a side view of FIG. 3, FIG. 5 is a characteristic diagram in which the vertical axis shows the pressure of the coolant and the horizontal axis shows time, and FIG. 6 shows the second embodiment of the present invention. Cross-sectional side views of such pressure raising device, FIGS. 7 to 9
The figures relate to a third embodiment of the present invention, and FIG. 7 is a cross-sectional side view of the pressure increase device, FIG. 8 is a view taken along the line ■-■ in FIG. 7, and FIG.
The figure is a view taken along the line IX-IX in FIG. 7, FIG.
Figures 1 to 15 are the fifth part of the present invention; Figure 13 is the xm-xm line arrow diagram in Figure 12; Figure 14 is an enlarged view of section B in Figure 12; Figure 15 is the Xv diagram in Figure 12. The arrow view, FIG. 16 is an overall view of a coolant liquid supply device according to a sixth embodiment of the present invention. 1...Storage tank 9...Feeding device 4.5...Supply passage 6...Return passage 19... ...Opening portion 22...Closing member 29...Drilling tool 29C...Ejection passage Fig. 7 Fig. 8 Fig. 9 Q-2f

Claims (1)

[Claims] A coolant discharge passage is formed in the drilling tool,
This discharge passage and a storage tank storing the coolant liquid are communicated via a supply passage in which a feeding device is interposed,
A coolant liquid supply device characterized in that a pressure increase device is installed in the supply passage and generates a water hammer phenomenon by a closing member that intermittently opens and closes the return passage.