JP3390282B2 - Rolling oil supply device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling oil supply device for a rolling mill, and more particularly to a rolling oil supply device suitable for a hot rolling mill.

[0002]

2. Description of the Related Art Conventionally, when performing oil rolling in a hot rolling mill, a mixer for mixing hot water and rolling oil is provided in the vicinity of a spray nozzle arranged near a rolling roll. It is common to inject the mixed fluid mixed in (1) to the rolling roll through the spray nozzle (see, for example, JP-A-53-134755).

Rolling oil supply suitable for such a hot rolling mill
As a device, the present applicant has already disclosed in JP-A-3-128113.
I have a proposal. That is, its contents are shown in Figs.
As shown in, the mixer 14 for mixing the rolling oil and warm water, and
Rolling oil supply line 18 between mixer 14 and rolling oil tank 10
Located at the rolling oil supply pump 16
Return line 38 to oil mixer 14 or rolling oil tank 10
A three-way valve 20 selectively connected to the mixer 14 and a sprayer
Cheat N ₁~ N_TenMixed oil supply branch lines 22A to 22C between
Mixed oil shutoff valves 24A to 24C disposed in the hot water tank 12
Water supply with a hot water pump 26 connected between the mixer and the mixer 14
From the pipe 28, connect the mixer 14 and the mixed oil shutoff valves 24A-24C.
Bypass to the mixed oil supply branch pipelines 22A-22C
Pipe 30 and bypass branch pipes 30A to 30C and this bypass
Mixed oil shutoff valves 24A-24C provided on the branch pipes 30A-30C
Equipped with hot water shutoff valves 32A to 32C that are opened only when the
It is a thing.

Also, at the inlet side of the mixer 14, the rolling oil supply line 18
In addition, a rolling oil check valve that allows only flow in the direction of the mixer 14
34, the hot water supply pipe 28 at a position downstream of the bypass pipe 30, the hot water check valve 36 that allows only the flow in the direction of the mixer 14, and these rolling oil check valve 34, Hot water check valve 36, mixer 14, mixed oil shutoff valve 24A-24C, hot water shutoff valve 32A-32C, bypass pipe 30, bypass branch pipe 30A-
If the 30C is formed in the integral block 40, it can be made extremely compact.

When the rolling oil is injected, the rolling oil supply pump 16 and the hot water pump 26 are activated, and the hot water shutoff valve is activated.
In the closed state of the 32A to 32C, by opening the mixer 14 side to simultaneously mixed oil close valve 24A~24C the three-way valve 20, a spray nozzle N ₁ to N via the mixed oil supply branch pipe 22A~22C ₁₀ can be supplied with mixed oil. Specifically, the mixed oil supply conduit 22A is provided with spray nozzles N ₁ and N arranged at both ends of the material to be rolled (not shown) in the plate width direction.
_{In FIG. 10} , the mixed oil supply pipe 22B is provided at the four spray nozzles N _{4 to} N ₇ at the center of the material to be rolled in the plate width direction, and the mixed oil supply pipe 22C is provided at the central 4 spray nozzles N ₄ to N ₄ . The mixed oil is supplied to the spray nozzles N ₂ , N ₃ and N ₈ , N ₉ between N ₇ and the spray nozzles N ₁ , N _{10 at} both ends, respectively.

When the injection of rolling oil is stopped, the three-way valve 20 is switched to the return pipe 38 side, and at the same time, the mixed oil shutoff valves 24A to 24C are closed. On the other hand, hot water shutoff valve 32A ~
By supplying hot water to the spray nozzle N ₁ to N ₁₀ Open 32C, it is possible to prevent nozzle clogging.

[0007]

By the way, in the conventional rolling oil supply apparatus disclosed in the above-mentioned Japanese Patent Laid-Open No. 3-128113, the rolling oil injection from the spray nozzles N _{1 to} N _{10 is} started and stopped. It has an excellent effect that the delay of response can be greatly shortened, and the main components are the mixer 14, the mixed oil shutoff valves 24A to 24C, and the rolling oil check valve.
34, a bypass pipe 30, a bypass branch pipe 30A to 30C, a hot water shutoff valve 32A to 32C, and a hot water check valve 36 are integrated in a block 40.
Since it is formed inside, it has an effect that it can be installed in a rolling mill which has a narrow space and is in a bad environment of high temperature and high humidity, but has the following problems.

(1) When stopping the injection of rolling oil, the three-way valve 20 is switched to the return pipe 38 side, and at the same time, the mixed oil shutoff valves 24A to 24C are closed and the hot water shutoff valves 32A to 32C are opened. However, at this time, the hot water pressure has the same value as the pressure when the rolling oil is injected, so the injected hot water reaches the rolling rolls. Therefore, if the malfunction of the three-way valve 20 or internal leak and the malfunction or internal leak of the mixed oil shutoff valves 24A to 24C overlap, the rolling oil passes through the bypass pipe 30 and the bypass branch pipes 30A to 30C to generate hot water. At the same time, it adheres to the surface of the rolling roll. Therefore, when the rolling material bites into the material to be rolled at the start of the next rolling, slipping occurs, causing defective biting, or slipping between the rolling material and the material to be rolled, resulting in unstable rolling. May become.

(2) Since many stop valves such as the mixed oil stop valves 24A to 24C and the hot water stop valves 32A to 32C are arranged just before the spray nozzle header, the equipment including the control device becomes complicated and expensive. Moreover, since it is used in a bad environment of high temperature and high humidity near the hot rolling mill, there is a problem that the reliability and maintainability of the apparatus are poor. (3) In order to perform stable oil rolling, the mixing ratio of rolling oil to hot water is in a relatively low range of 0 to 5%, that is, the flow rate of rolling oil is low, and the material and thickness of the material to be rolled are large. It is necessary to control the mixing ratio, that is, the rolling oil flow rate, in a wide range and with high accuracy in accordance with changes in rolling conditions such as reduction ratio, rolling speed and rolling temperature. For this purpose, the feedback control method of measuring the flow rate of rolling oil with a flow meter and adjusting the opening degree of the flow rate control valve based on the measured value and the set value, as is commonly done in the past, is not possible. However, there are problems in terms of both measurement accuracy and control accuracy.

(4) In addition to the problem of (3), it is difficult to regularly measure and check the mixing ratio of hot water and rolling oil (that is, rolling oil concentration) for each spray nozzle header. is there. If you want to do so, stop the rolling mill and open the mixed oil shutoff valves 24A-24C one by one to collect the mixed oil jetted from each spray nozzle header into a container, or use the mixed oil shutoff valves 24A-24C. It is necessary to remove the connection in the middle of the pipeline from each to each spray nozzle header and collect the mixed oil in a container, which requires a lot of manpower and time, and there is a big problem in work safety. .

(5) In order to shorten the response delay at the time of starting and stopping the injection of rolling oil as much as possible, the mixed oil shutoff valves 24A to 24C
It is necessary to dispose the hot water shutoff valves 32A to 32C as close to the rolling rolls as possible, but the shutoff valves are opened and closed by an electromagnetic valve that uses electromagnetic force or an electric valve that uses an electric motor. If a limit switch or proximity switch is used to detect the opening and closing of valves, it is easy to cause deterioration of insulation and poor electrical connection under the adverse environment as described above, and reliability is improved. Therefore, the integrity will be significantly reduced.

If a gas pressure drive system such as air pressure is adopted for opening and closing the closing valve, some of the problems as described above can be solved, but the above-mentioned problems with respect to the detection of the opening and closing of the closing valve. No suitable solution has been proposed. Therefore, it is difficult to detect the opening / closing of the shutoff valve, and it is not possible to perform the open / close control of the shutoff valve with high reliability, or it is not possible to detect the open / close abnormality of the shutoff valve, and therefore unstable oil rolling operation,
There is a possibility that a large amount of defective products may be generated accordingly. In addition, it requires a lot of manpower and a long time to find an abnormal point, making it impossible to carry out oil rolling for a long time, and forcibly stopping the hot rolling mill for a long time, resulting in a decrease in operating rate. There is a fear of.

As a means for preventing the slip accident caused by the leakage of the rolling oil as described above, for example, an actual flat square 3
-81202 gazette, in the vicinity of the front surface of the spray nozzle, there is disclosed a technique of providing a retractable shield plate in a rolling oil injection passage through a drive mechanism such as a fluid cylinder, but according to this conventional technique, Even if rolling oil leaks, it can be blocked by the shielding plate, and the effect of reliably preventing rolling oil from reaching the rolling rolls is recognized, but the device itself becomes complicated and the shielding plate and its drive Since the mechanism is arranged in the vicinity of the rolling rolls, it is not only practically inferior in maintainability, but also difficult to install in a narrow space between stands of the continuous rolling mill, which is not practical.

The present invention has been made in order to solve the above-mentioned problems of the prior art. When the rolling oil is not injected, the three-way valve, the shut-off valve, or the like has a malfunction or internal leakage of the rolling oil. The first object of the present invention is to provide a rolling oil supply device for a rolling mill that can prevent rolling oil from adhering to rolling rolls and can be installed even in a narrow space. A second object of the present invention is to provide a rolling oil supply device for a rolling mill, which is low in cost, simple in equipment, inexpensive, and excellent in reliability and maintainability.

The present invention also provides a rolling condition in which the mixing ratio of the rolling oil to the diluting fluid is 0 to 5%, which is relatively low, and the material and thickness of the material to be rolled, the reduction ratio, the rolling speed and the rolling temperature. It is a third object of the present invention to provide a rolling oil supply device for a rolling mill capable of controlling the mixing ratio in a wide range with high accuracy according to the change of the above. A fourth object of the present invention is to provide a rolling oil supply device for a rolling mill, which can be arbitrarily operated even during the operation of, and is convenient for measuring and checking the mixing ratio.

Furthermore, the present invention can detect the opening and closing of the shutoff valve with sufficient durability and reliability even under a bad environment of high temperature and high humidity, and can maintain stable oil rolling for a long time and detect abnormalities. A fifth object is to provide a rolling oil supply device for a rolling mill that is easy and can be performed in a short time.

[0017]

SUMMARY OF THE INVENTION The present invention is a rolling oil supply device for supplying a mixed fluid prepared by mixing a rolling oil with a diluent fluid to a rolling roll of a rolling mill through a spray nozzle, which is connected to a rolling oil source. A rolling oil supply pipe and a high-pressure dilution fluid supply pipe connected to a dilution fluid source are connected to each other to mix the rolling oil and the high-pressure dilution fluid to form a mixed fluid, and the rolling oil supply pipe A three-way valve that is attached to the passage and selectively flows the rolling oil whose pressure is increased by the rolling oil supply pump into the mixer or the return pipe; and the rolling oil supply pump and the three-way valve in the rolling oil supply pipe. A precision gear pump that is provided between the mixers and controls the flow rate of rolling oil by controlling the number of revolutions, a mixed fluid stop valve that is provided in each of the mixed fluid supply branch pipes that extend from the mixer to the spray nozzle, and the high-pressure dilution. Flow A high-pressure dilution fluid stop valve arranged in the supply line, a low-pressure dilution fluid supply main line branching from the upstream side of the high-pressure dilution fluid stop valve of the high-pressure dilution fluid supply line and attached with a throttle, A low pressure dilution fluid supply branch line connected to the dilution fluid supply main line and connected to each of the mixed fluid supply branch lines extending from the mixed fluid stop valve to the spray nozzle, and the low pressure dilution fluid supply branch line. And a low-pressure dilution fluid check valve provided in each of the rolling oil supply device and the rolling oil supply device.

Further, according to the present invention, the mixer, the mixed fluid stop valve, the low pressure dilution fluid check valve, a part of the rolling oil supply pipe line, a part of the mixed fluid supply branch pipe line, A rolling oil supply device characterized in that a part of the high pressure dilution fluid supply pipeline, a part of the low pressure dilution fluid supply main pipeline and a part of the low pressure dilution fluid supply branch pipeline are integrally formed in a block. Is.

A throttle is preferably provided downstream of the low-pressure dilution fluid check valve, and a main check valve is provided downstream of the throttle of the low-pressure dilution fluid supply main pipeline. It is advisable to provide pressure detection / warning means on the downstream side. Further, the from mixed fluid shut-off valve of providing branches the mixed fluid sample line to the mixed fluid supply branch conduit leading to the spray nozzle may further prior Symbol high dilution fluid supply conduit pressure diluent fluid shutoffs It is advisable to provide a pressure regulating valve on the upstream side of. Furthermore, a pressure regulating valve may be provided instead of the throttle of the low pressure dilution fluid main pipe line.

A gas pressure cylinder in which a poppet valve portion or a spool valve portion, a gas pressure cylinder portion, and a gas pressure signal type valve opening / closing detection means are integrally assembled in a cylindrical body in the mixed fluid shutoff valve. An actuated poppet valve or spool valve, or a gas cylinder actuated spool valve or poppet valve that integrally comprises a spool valve portion or poppet valve portion, a gas pressure cylinder portion, and gas pressure signal type valve opening / closing detection means. Good to use.

Further, the gas pressure signal type valve opening / closing detecting means is integrally provided so as to extend to the back surface of the gas pressure cylinder portion and has an inner diameter smaller than the outer diameter of the piston of the gas pressure cylinder portion. part is bored, and its almost a sensor sleeve which is provided a first through hole in the peripheral wall of the central portion, it is provided continuously to the sleeve for the sensor, the cylinder unit valve that have a larger inner diameter than the inner diameter of chamber is made forms and internal to the second and valve seat body sensor provided with through holes, the through holes provided in the gas pressure cylinder unit rear wall from the rear of the piston of the pneumatic cylinder unit to the peripheral wall Penetrating while touching,
When extended coaxially with the piston and fitted in the sensor sleeve, the central portion has a diameter smaller than the inner diameters of both ends of the sensor sleeve, and the length of the piston is in the retracted limit position, A sensor spool having a small diameter portion that extends from the first through hole to the valve chamber of the sensor valve seat body, and the sensor spool is provided at an end portion of the sensor spool on the side opposite to the pneumatic cylinder portion. The valve body portion having an outer diameter smaller than the inner diameter of the cylinder portion of the operating sleeve, and the end portion of the sensor valve seat body on the gas pressure cylinder portion side, within the stroke range of the valve body portion. A ring-shaped valve seat portion, which is slidably contactable with the outer peripheral surface of the valve body portion, and one of the first through hole or the second through hole are connected via a throttle, and are connected from a compressed gas source. A compressed gas line for supplying compressed gas, and the compressed gas line Good to constitute by the serial throttle upstream pressure detector attached to.

Alternatively, the gas pressure signal type valve opening / closing detection means includes a sensor sleeve integrally provided on the back surface of the gas pressure cylinder portion extending beyond the back wall and a piston of the gas pressure cylinder portion. It penetrates through the through hole provided in the back wall of the gas pressure cylinder portion from the back side, extends coaxially with the piston, is fitted in the sensor sleeve, and has both ends of the sensor sleeve in the central portion. Is provided at a position corresponding to the small diameter portion of the sensor spool of the sensor sleeve and a small diameter portion of which the outer diameter is smaller than the inner diameter of the portion, and communicates with each other when the piston is at the forward limit. However, when the piston is located at the backward limit, the contact is made between the outer peripheral wall of the sensor spool and the inner peripheral wall of the sensor sleeve at the end opposite to the gas pressure cylinder portion. And a pair of through holes provided in the inner peripheral wall of the sensor sleeve at a position where the mutual communication is cut off, and one of the pair of through holes is connected via a throttle, and a compressed gas source is provided. It may be constituted by a compressed gas pipeline for supplying the compressed gas from the above and a pressure detector mounted on the upstream side of the throttle of the compressed gas pipeline.

Further, the gas pressure signal type valve opening / closing detecting means is attached to the back surface of the gas pressure cylinder portion, and a first through hole is formed in a peripheral wall of an end portion on the gas pressure cylinder portion side, and a first through hole on the opposite side thereof. A sensor cylinder having a second through hole in the peripheral wall of the end portion, and a communication hole that is fitted to the sensor cylinder and that communicates with the front and rear space of the sensor piston in a part of the side wall of the sensor cylinder. A sensor piston whose gas pressure cylinder portion side is biased by a compression spring, and a sensor valve body portion which is fixed to the gas pressure cylinder portion side of the sensor piston and has an outer diameter smaller than the inner diameter of the sensor sleeve. A sensor piston rod fixed to the sensor valve body so that its tip can abut against the back surface of the piston of the gas pressure cylinder portion; and the front of the inner peripheral surface of the sensor sleeve. Mounting et is in a position corresponding to substantially the forward limit position of the piston, a ring-shaped valve seat body having a smaller inner diameter than the outer diameter of the valve body portion, the first or second
A compressed gas line connected to one of the through holes of the through a throttle to supply a compressed gas from a compressed gas source, and a pressure detector attached to the compressed gas line upstream of the throttle. You may comprise.

[0024] Incidentally, the second through hole of the sleeve for the sensor, the gas when the sensor piston rod is located at a position corresponding to substantially the forward limit position of the pressure cylinder of the piston, the gas of the sleeve for the sensor It may be provided on the pressure cylinder portion side and on the peripheral wall of the sensor sleeve between the sensor valve seat body.

[0025]

According to the present invention, a precision gear pump for controlling at least the flow rate of rolling oil by controlling the number of revolutions is provided between the rolling oil source of the rolling oil supply line and the three-way valve. , It is possible to control the mixing ratio of pure oil or other high-pressure dilution fluid and rolling oil in a wide range and with high precision in the range where the rolling oil flow rate is relatively low, and to obtain an appropriate rolling oil concentration corresponding to changes in rolling conditions. Controllable and stable oil rolling can be performed.

A mixed fluid shutoff valve is provided in the mixed fluid supply branch line from the mixer to one or a plurality of spray nozzle header groups, and a low-pressure dilution fluid supply branch line is connected to the downstream side thereof. , A low-pressure dilution fluid check valve that allows only a flow in the direction of the spray nozzle in each of these low-pressure dilution fluid supply branch pipelines, and a rolling oil supply pipeline between the rolling oil source and the three-way valve, A three-way valve that selectively connects a rolling oil source to the mixer or a return line to the rolling oil source, and a high-pressure dilution fluid stop valve to a high-pressure dilution fluid supply line that supplies a high-pressure dilution fluid to the mixer, respectively. Therefore, when the rolling oil is not injected, the three-way valve is switched to the rolling oil return side, and the high pressure dilution fluid stop valve and the mixed fluid stop valve are closed, so that the low pressure dilution fluid supply branch pipe line is closed. The pressure-diluting fluid check valve can be opened by the action of the differential pressure before and after it, and a low-pressure dilution fluid with a predetermined pressure can be supplied to the spray nozzle header group, preventing nozzle clogging without adhering to the rolling rolls. You can Further, when the rolling oil is injected, the low-pressure diluted fluid check valve is closed by the action of the differential pressure before and after the injection, so that the high-pressure mixed fluid does not flow back into the low-pressure diluted fluid supply pipeline.

Further, the mixed fluid shutoff valve corresponding to a specific spray nozzle header group is closed, and the other mixed fluid shutoff valve is opened to supply the mixed fluid to the corresponding spray nozzle header group, and the spray nozzle attached thereto is used. When injecting rolling oil, from the mixed fluid supply pipeline during the rolling oil injection, to the corresponding low pressure dilution fluid supply branch pipeline, low pressure dilution fluid supply main pipeline, and the mixed fluid shutoff valve being closed. The high-pressure mixed fluid is not back-flowed and injected into the spray nozzle header group in which the rolling oil injection is stopped via the corresponding low-pressure dilution fluid supply branch pipe.

Further, according to the present invention, the mixer, the mixed fluid stop valve, the low pressure dilution fluid check valve, a part of the rolling oil supply pipe line, a part of the mixed fluid supply branch pipe line, A part of the high pressure dilution fluid supply pipeline, a part of the low pressure dilution fluid supply main pipeline,
Since a part of the low-pressure dilution fluid supply branch pipe is integrally formed into a block, this block can be arranged close to the rolling rolls between rolling stands having a small space, and the rolling oil It is possible to minimize the response delay when starting and stopping the injection.

Further, according to the present invention, since the throttles are provided on the downstream side of the respective check valves of the low pressure dilution fluid supply branch pipe lines, the spray nozzle headers whose pressure loss values due to the throttles communicate with each other. If the spray resistance of the low-pressure dilution fluid is sprayed from any of the spray nozzles, the spray pressure will be almost equal if the preset value is set in consideration of the pipe resistance to the group, the number of spray nozzles and the spray nozzle diameter. Therefore, it is possible to surely prevent the clogging of all the spray nozzles and reliably prevent the low pressure dilution fluid injected from any of the spray nozzles from reaching the rolling roll. Further, the low-pressure dilution fluid source can be made common to a plurality of rolling stands, and compared with the case where the high-pressure dilution fluid source is reduced to a low pressure in one stage only by one stage of reduction,
The inner diameter of the diaphragm can be made relatively large, and the diaphragm can be prevented from being blocked.

Further, according to the present invention, a check valve is also provided in the low pressure dilution fluid supply main pipe line, and pressure detection /
Since the provided alarm means, each even internal leakage occurs in one of the check valves, high pressure mixing fluid or high-pressure diluent fluid before Symbol low <br/> pressure of the low pressure diluting fluid supply branch pipe It is possible to prevent backflow in the direction of the low-pressure dilution fluid source beyond the check valve in the dilution fluid supply main line, and to issue an alarm when the pressure detection means detects that the pressure has risen above a predetermined pressure setting value. Therefore, it is possible to quickly know that internal leakage has occurred in any one of the check valves of the low-pressure dilution fluid supply branch lines.

Further, according to the present invention, since the mixed fluid sampling pipe for sampling the mixed fluid is provided, the oil rolling is performed in the low flow rate region of the rolling oil in which it is difficult to measure the flow rate accurately and continuously. When performing rolling oil, by opening the stop valve at the end of the mixed fluid sampling pipeline branched from each of the mixed fluid supply pipeline from the mixed fluid shutoff valve to the spray nozzle during injection of rolling oil,
An appropriate amount of mixed fluid for analysis and measurement can be sampled optionally or periodically without disturbing the operation of the rolling mill.

Further, according to the present invention, since the mixed fluid shutoff valve is a gas cylinder actuation type poppet valve or a gas pressure cylinder actuation spool valve, and gas pressure signal type valve opening / closing detecting means is additionally provided, it is simple and compact. With a simple valve structure, the injection / stop control of rolling oil can be reliably performed with high reliability even in a bad environment of high temperature and high humidity. Also,
According to the present invention, as the gas pressure signal type valve opening / closing detecting means, a valve body provided for the sensor spool or the sensor piston synchronized / interlocked with the movement of the piston of the closing valve actuating gas cylinder, and the sensor Depending on the contact or separation with the valve seat provided on the sleeve or the inner wall of the sensor cylinder,
The internal pressure of the supply line for the compressed gas supplied into the sensor sleeve or the sensor cylinder is configured to be detected by a pressure detector at a remote position, and the valve open / close detection of the mixed fluid shutoff valve is performed. As described above, the valve opening / closing detection can be performed reliably and reliably even under an adverse environment of high temperature and high humidity as compared with the electrical detection means.

[0033]

Embodiments of the present invention will be described in detail below with reference to the drawings. [Embodiment 1] FIG. 1 is a pipeline diagram showing a configuration of a first embodiment of the present invention. In the figure, the same components as those of the conventional example shown in FIGS. 14 and 15 are designated by the same reference numerals, and in principle duplicate description will be omitted.

In this figure, 50 is a precision gear pump,
The rolling oil supply pipe 18 is mounted on the downstream side of the rolling oil supply pump 16 and controls the flow rate of the rolling oil supplied to the mixer 14 via the three-way valve 20. Reference numeral 52 is a rotation speed control device for controlling the rotation speed of the precision gear pump 50. 54 is a high-pressure hot water supply pipe branching from the hot-water supply pipe 28, and supplies high-pressure hot water to the mixer 14 via the high-pressure hot-water shutoff valve 56 and the high-pressure hot-water check valve 36. Reference numeral 58 is a low-pressure hot water supply main pipe branching from the hot-water supply pipe 28 and supplying low-pressure hot water whose pressure is reduced by a throttle 60 such as a restriction orifice.

Reference numerals 62A to 62C denote low pressure hot water supply branch pipes branched from the low pressure hot water supply main pipe 58, respectively, and mixed oil supply branch pipes 22A to 22 via low pressure hot water check valves 64A to 64C.
Spray nozzles N _{1 to} N attached to spray nozzle header groups arranged in the axial direction of rolling rolls (not shown) downstream of the C mixed fluid shutoff valves 24A to 24C, respectively.
It is connected in the middle of the mixed oil supply branch lines 22A to 22C up to ₁₀ .

FIG. 2 shows the mixer 14, the mixed fluid supply conduit 22, the mixed fluid supply branch conduits 22A to 22C, the mixed fluid shutoff valves 24A to 24C, the rolling oil check valve 34, and the high pressure hot water check valve. 36,
Low pressure hot water supply branch pipes 62A to 62C, low pressure hot water check valve 64A
~ 64C, part of the rolling oil supply line 18, high-pressure hot water supply line 54
Part of the low pressure hot water supply main pipe 58, and block 40A
It is a perspective view showing a state of being integrally formed with the.

The block 40A will be described in detail. First, as for the rolling oil check valve 34 and the high-pressure hot water check valve 36, as shown in FIG. 3, the rolling oil supply is arranged in parallel in the vertical direction with respect to the drawing. The end portion 18a of the pipe 18 and the end portion 54a of the high-pressure hot water supply pipe 54 are connected to each other. The rolling oil check valve 34 and the high-pressure hot water check valve 36 respectively have a valve seat 34
z, 36z, valve bodies 34t, 36t, and springs 34s, 36s for biasing the valve bodies 34t, 36t.

The mixer 14 is a high pressure hot water passage in the vertical direction.
14a and a rolling oil passage 14b which is formed orthogonally to the high-pressure hot water passage 14a and is connected to the end portion 18b of the rolling oil supply pipe 18, and rolling oil and high-pressure hot water are provided at the intersection of the two. They are merged and communicate with the outlet 14c. This exit 14c
Is approximately 1/2 in cross-sectional area with respect to the mixed fluid supply pipeline 22 connected to the three mixed fluid supply branch pipelines 22A to 22C, whereby the rolling oil and high pressure hot water flowing out from the outlet 14c are The mixed fluid is uniformly agitated and mixed by the vortex flow generated by the rapid expansion of the passage cross-sectional area.

The rolling oil check valve 34 and the high pressure hot water check valve
The springs 34s and 36s built into the 36 allow the valve bodies 34t and 36t
Are urged in the upward direction to contact the valve seats 34z and 36z, respectively, between the rolling oil check line 34 between the rolling oil check valve 34 and the front and rear end portions 18a and 18b, and the high pressure of the mixer 14. Hot water passage 14a
The space between the high pressure hot water supply line 54 and the end 54a of the high pressure hot water supply line 54 is cut off from each other, thereby preventing backflow from the downstream side to the upstream side. Further, at the time of rolling oil injection, the three-way valve 20 is switched to the mixer 14 side, and the high pressure hot water shutoff valve 56 and the mixed fluid shutoff valve 24.
When A to 24C are opened, the pressure of the rolling oil causes the valve element 34t of the rolling oil check valve 34 and the pressure of the high-pressure hot water causes the valve element 36t of the high-pressure hot water check valve 36 to turn into the force of the springs 34s and 36s, respectively. Overwhelmed and pushed down in the figure, rolling oil supply line
Between the front and rear end portions 18a and 18b of the rolling oil check valve 34 of 18, and
The high-pressure hot water passage 14a of the mixer 14 and the end portion 54a of the high-pressure hot water supply pipe 54 communicate with each other so that the rolling oil and the high-pressure hot water are supplied to the mixer 14.

As shown in FIG. 4, the mixed fluid supply pipe 22 is arranged parallel to the drawing in the lateral direction, and is, for example, a gas cylinder actuated poppet valve. The spools 25A to 25C are communicated with each other. When the mixed fluid shutoff valves 24A to 24C are biased to the left by the springs 24s,
The valve bodies 42a to 42c are separated from the valve seats 44a to 44c, respectively, and the mixed fluid supply pipeline 22 is connected to the mixed fluid supply branch pipeline 22A to
22C, and from the left end of the figure, compressed air nozzle
When compressed air is introduced through 46A-46C, the pistons 37A-37C are pushed by this compressed air, overcome the bias of the spring 24s and move to the right side, and the valve elements 42a-42c are respectively moved to the valve seat 44a. .. to 44c, the mixed fluid supply pipeline 22 and the mixed fluid supply branch pipelines 22A to 22C are cut off from each other.

The end portion 58a of the low pressure hot water supply main line 58
As shown in FIG. 5, the low-pressure hot water check valves 64A to 64 are provided in the vertical direction with respect to the drawing and are arranged in parallel with the lateral direction.
It communicates with the entry side of C. Low pressure hot water check valve 64A ~ 64C
The outlet side of each is connected to the low pressure hot water supply branch pipelines 62A to 62C arranged in the direction perpendicular to the drawing. The configuration of the low pressure hot water check valves 64A to 64C is the same as the rolling oil check valve 34 described above.
The same as the high pressure hot water check valve 36, and when the mixed fluid shutoff valves 24A to 24C are opened during rolling oil injection, the high pressure acting through the force of the spring 64s and the low pressure hot water supply branch pipes 62A to 62C respectively built therein. Due to the pressure of the mixed fluid, the valve body 64t biased to the left with respect to the drawing comes into contact with the valve seat 64z, so that the communication between the front and rear pipe lines is blocked. In addition, the mixed fluid shutoff valves 24A to 24C are closed, and the low pressure hot water check valves 64A to 64C.
When the pressure on the downstream side of C decreases, the low pressure hot water supply main pipeline 58
The pressure of the low-pressure hot water filled in the end portion 58a of the valve overcomes the biasing force of the spring 64s to push the valve body 64t to the right in the figure, and the low-pressure hot-water check valves 64A to 64C are opened to open the low-pressure hot water. Is supplied to the spray nozzle group via the low pressure hot water supply branch pipes 62A to 62C.

The block 40A constructed in this manner has a very compact overall size of about 150 mm × 180 mm × 190 mm, so that the mixed fluid shutoff valves 24A to 24C to the nozzles N _{1 to} N _{10 are formed.} Is within 1.5 m, and the response delay at the start and stop of injection is within 1 second. Next, another configuration of the gas pressure cylinder actuated poppet valve used as the mixed fluid shutoff valves 24A to 24C shown in FIG. 4 will be described with reference to FIG.

This pneumatic cylinder operated poppet valve 100
Is formed by integrally forming a poppet valve portion 104, a gas pressure cylinder portion 106, and a valve opening / closing detection sensor portion 108, which is a gas pressure signal type valve closing detection means, provided inside a cylindrical body 102. It First, in the poppet valve section 104 and the pneumatic cylinder section 106, the valve seat body is attached to one end of the body 102.
112 is inserted, and the valve seat 112 has a body at the center.
A mixed fluid passage 112a provided in the longitudinal direction of 102 and a mixed fluid passage 112b intersecting with this at a right angle are formed. One end of the mixed fluid passage 112a is closed by a front lid 138 attached to the front end surface of the body 102, and the other end is opened to the taper portion 112t side provided in the valve chamber 110a provided inside the body 102. ing. Mixed fluid passage 112b
One end of the body 102 is closed by the inner wall surface 110b of the body 102,
The other end communicates with the mixed fluid outlet 144 of the peripheral wall of the body 102. Further, the valve chamber 110a communicates with a mixed fluid inflow port 142 provided through the peripheral wall of the body 102. An O-ring seat 110d sandwiching an O-ring 110c for sealing the valve body is provided on the right side of the valve chamber 110a in the drawing, and a piston chamber 118 is bored on the right side.

A poppet valve body 114 is inserted from the valve chamber 110a to the piston chamber 118 so as to be slidable left and right by a stroke L while the outer peripheral surface is sealed by an O-ring 110c. At the right end, a piston 116 with an O-ring 116b for sealing interposed is provided. To the left and right of this piston 116, penetrate the peripheral wall of the body 102,
Left piston chamber EXH holes that pass with the left piston chamber 118L of the piston chamber 118 is cut off to the left and right piston 116 146
And a right piston chamber supply / exhaust hole 148 for communicating compressed gas for piston operation, which communicates with the right piston chamber 118R, and a compression spring 136 is provided in the left piston chamber 118L.
It is installed so as to bias 16 to the right.

The valve opening / closing detection sensor unit 108 includes a sensor sleeve 120, a sensor valve seat 122, and a sensor spool 1.
It consists of 24 and. The sensor spool 124 has a diameter smaller than that of the piston 116, is coaxially coupled to the piston 116 on the right end surface thereof, and is slidably guided by the stroke L into the cylinder portion 120a of the sensor sleeve 120. On the further right side of the sensor sleeve 120, the left end circumscribes the outer peripheral surface of the valve body portion 128 of the sensor spool at the right end of the sensor spool 124, and a seal is provided between the sensor sleeve 120 and the right end side surface of the adjacent sensor sleeve 120. A sensor valve seat body 122 having a valve seat portion 130 so as to sandwich the O-ring 130a, and a valve chamber 134 having a diameter larger than the inner diameter thereof is formed on the right side of the valve seat portion 130, is inserted. A rear lid 140 is attached to the right end side surface of the body 102 so as to close the right end of the valve chamber 134.

A sensor spool small diameter portion 126 having an outer diameter smaller than the inner diameter of the sensor sleeve 120 is provided at the center of the sensor spool 124.
A space 132 is formed between the inner surface of the cylinder portion 120a of 120 and the inner surface of the cylinder portion 120a. A first through hole (exhaust hole) 150 penetrating the sensor sleeve 120 and the peripheral wall of the body 102 is formed so as to communicate with the space 132. Also, in order to communicate with the valve chamber 134 of the sensor valve seat 122,
A second through hole (air supply hole) 152 that penetrates the sensor valve seat 122 and the peripheral wall of the body 102 is formed.

In the figure, 160 is a compressed gas source,
Compressed air or compressed nitrogen gas is usually used as the compressed gas. Further, 162 is a compressed gas pipeline for supplying compressed gas from the compressed gas source 160 to the second through hole 152, 164 is a pressure switch attached to the compressed gas pipeline 162, and 166 is a throttle. The throttle 166 has a function of giving a back pressure to the compressed gas pipeline 164 so that the pressure switch 164 can reliably detect the pressure change when the compressed gas is discharged.

The operation of the gas pressure cylinder actuated poppet valve 100 thus constructed will be described below. As a normal state, the compressed gas is previously supplied from the compressed gas source 160 to the valve chamber 132 of the sensor valve seat 122 through the second through hole 152. Therefore, first, if you open the gas pressure cylinder operation dynamic poppet valve 100, by switching the solenoid valve, not shown, discharges the operating compressed air which has been supplied to the right piston chamber 118R from the right piston chamber supply and exhaust holes 148 . As a result, the urging force of the compression spring 136 causes the piston to move.
Stroke L until the 116 is pushed back to the right side of the figure and the rear surface of the piston 116 contacts the front surface of the sensor sleeve 120.
Just move to the right. At the same time, the tapered hole of the valve seat 112 is
The valve element 114, which was in contact with the taper portion 114t at the front end of the valve element 112t, moved to the right side, and the valve seat element 112 and the valve element 114 were separated from each other, and the valve chamber 110
a and the mixed fluid passage 112a in the valve seat 112 communicate with each other, and the mixed fluid is connected to the upstream side of the mixed fluid supply pipe (22 in FIG. 2) from the mixed fluid inlet 142 to the valve chamber 110a, the mixed fluid. After passing through the passage 112a and the mixed fluid passage 112b, the mixed fluid flows from the outflow port 144 toward the spray nozzle through the downstream side of the mixed fluid supply pipe.

In synchronization with the rightward movement of the piston 116 as described above, the sensor spool 124 moves rightward by the stroke L. As a result, the valve body portion 128 of the sensor spool at the right end of the sensor spool 124 leaves the contact with the valve seat portion 130 and enters the valve chamber 134, so that the valve chamber 134 and the space 132 in the sensor sleeve 120 are separated from each other. Come to communicate. At this time, as described above, the compressed gas normally supplied to the valve chamber 134 is discharged to the outside through the space 132 and the first through hole 150. For this reason, the internal pressure of the compressed gas pipeline 162 decreases, and by detecting this pressure change with the pressure switch 164, the gas cylinder actuated poppet valve 100 is detected.
Can be opened.

On the other hand, a pneumatic cylinder actuated poppet valve 1
When 00 is closed, a solenoid valve (not shown) is switched to supply the working compressed gas from the right piston chamber air supply / exhaust hole 148 to the right piston chamber 118R. As a result, the piston 116 is pushed to the left with respect to the drawing against the biasing force of the compression spring 136, and the stroke until the taper portion 114t at the front end of the valve body 114 contacts the taper hole portion 112t of the valve seat body 112. L
Just move to the left. Therefore, the valve chamber 110a and the valve seat body 1
The communication with the mixed fluid passage 112a in 12 is cut off, and the flow of the mixed fluid is stopped.

In synchronism with the above-described movement of the piston 116 to the left, the sensor spool 124 moves by the stroke L to the left in the figure. As a result, the sensor spool 124
The valve body portion 128 at the right end of the valve is inscribed in the valve seat portion 130, and the communication between the valve chamber 134 and the space 132 in the sensor sleeve 120 is cut off. Therefore, the discharge of the compressed gas from the valve chamber 134 stops, and the internal pressure of the compressed gas line 162 is reduced to the compressed gas source 1
Rise until pressure equals 60. By detecting this pressure change with the pressure switch 164, it can be detected that the gas cylinder actuated poppet valve 100 is closed.

In the above embodiment, the second through hole 1
Although the case where the compressed gas pipeline 162 is connected to 52 has been described, the compressed gas pipeline 162 may be connected to the first through hole 150 instead of the second through hole 152, and the action in that case is as described above. It is similar to the case of. Further, regarding the valve opening / closing detection sensor unit 108 of the above embodiment, the valve chamber 1 of the sensor valve seat 122 is
The inner diameter of 34 is made larger than the inner diameter of the sensor sleeve 120, and the second through hole 152 is formed so as to communicate with the valve chamber 134.
Although it has been described that the above is provided, it may be configured as shown in FIG. 7.

That is, the inner diameter of the valve chamber 134 is made equal to the inner diameter of the adjacent sensor sleeve 120, and the second through hole 1
52 is closed by the outer periphery of the valve body portion 128 of the sensor spool 124 when the piston 116 is at the forward limit position and the pneumatic cylinder actuated poppet valve 100 is closed, and the space 132 is When the communication cylinder is cut off, the piston 116 of the operating cylinder is in the retracted limit position, and the pneumatic cylinder operated poppet valve 100 is open, the through hole 1
52 is a space facing the small diameter portion 126 of the sensor spool 124.
The only difference is that it is provided in a position that communicates with 132. The operation of this structure is almost the same as that in the case of FIG.

Next, the operation of the first embodiment constructed as described above will be described. The rolling oil supply pump 16 sends the rolling oil in the rolling oil tank 10 to the rolling oil supply line 18, and at the same time, the hot water pump 26 sends the hot water in the hot water tank 12 to the hot water supply line 28. At this time, the three-way valve 20
Is switched to the mixer 14 side, the precision gear pump 50 is rotated at a predetermined rotation speed, and the high pressure hot water shutoff valve 56
Leave it open. The mixed fluid shutoff valves 24A-24C are
If the material to be rolled has a wide plate width, it is opened.
At this time, since the downstream side of the low pressure hot water check valves 64A to 64C has a high pressure and the upstream side has a low pressure, the low pressure hot water check valves 64A to 64C are closed due to the differential pressure, and the low pressure hot water supply main pipe for the high pressure mixed fluid is provided. Backflow in the direction of the path 58 is prevented.

The rolling oil supply pump 16 and the hot water pump
The rolling oil and the high-pressure hot water pumped by 26 push the rolling oil check valve 34 and the high-pressure hot water check valve 36, respectively, and reach the mixer 14, where they are merged and uniformly stirred, mixed and mixed. A fluid is formed. This mixed fluid reaches the mixed fluid shutoff valves 24A to 24C via the mixed fluid supply pipeline 22 connected to the downstream of the mixer 14, and the mixed fluid supply branch pipeline 22
It is ejected from each nozzle N _{1 to} N ₁₀ via A to 22C.

On the other hand, if the strip width of the rolled material is narrow,
Depending on the mixture fluid shutoff valve 24A only or 24A and 24C
Is closed. Then, the closed mixed fluid shutoff valve
Low-pressure hot water check valve 64 compatible with 24A or 24A and 24C
A or 64A and 64C are pushed open by low pressure hot water
And the corresponding nozzle N₁And N_TenOr N₁, N_TenAnd N
₂, N₃And N₈, N₉Only low pressure hot water is sprayed from
Will be done. Also, depending on changes in rolling conditions, rotation
The number of revolutions of the precision gear pump 50 is controlled by the number control device 52.
By controlling and adjusting the rolling oil supply flow rate,
Mixing ratio of rolling oil to pressurized water (that is, rolling oil concentration
The oil rolling is adjusted to the optimum oil rolling.

Depending on the strip width of the material to be rolled and other rolling conditions, any one or two systems of the mixed fluid shutoff valves 24A to 24C may be closed to adjust the rolling oil axial injection region. is there. In such a case, the mixed fluid shutoff valve 24A
Low pressure hot water check valves 64 of low pressure hot water supply branch lines 62A to 62C connected to the mixed fluid supply lines 22A to 22C which are open.
Since A to 64C are closed by the pressure difference between the front and rear, the mixed fluid supply pipes 22A to 22C having the mixed fluid shutoff valves 24A to 24C opened from the corresponding low pressure hot water supply branch pipes.
62A-62C, low-pressure hot water check valves 64A-64C, through the low-pressure hot water supply branch pipelines 62A-62C connected to the closed mixed fluid supply pipelines 22A-22C, the injection of rolling oil is stopped. Also, the high-pressure mixed fluid does not flow back to the inside of the spray nozzle header group to be ejected.

When the injection of rolling oil is stopped, the three-way valve 20
Is switched to the side of the return line 38 to the rolling oil tank 10, and at the same time, the high pressure hot water shutoff valve 36 and the mixed fluid shutoff valve 24A to
All 24C are closed. As a result, the supply of the rolling oil and the high-pressure hot water to the mixer 14 is stopped, and the supply of the mixed fluid to the spray nozzles N _{1 to} N ₁₀ is also stopped. At this time, the low pressure hot water check valve of the low pressure hot water supply branch lines 62A to 62C
64A~64C is pushed open by a low pressure hot water, low pressure hot water is supplied to the spray nozzle N ₁ to N _10. Therefore,
The spray nozzles N _{1 to} N ₁₀ are constantly supplied with low-pressure hot water in a state where rolling oil is not being sprayed to prevent nozzle clogging.

Further, if the low pressure hot water jetted from the spray nozzles N _{1 to} N ₁₀ is set in advance so that the jet pressure does not reach the rolling rolls, the hot water reaches the rolling rolls. Never. Therefore,
Malfunction of the three-way valve 20, internal leakage and mixed fluid shutoff valve 24A ~
Even if the rolling oil mixes in the low-pressure hot water due to the malfunction of 24C and internal leakage, the rolling oil does not reach the rolling rolls and a slip accident is prevented.

Here, the return pipe 38 side of the three-way valve 20
Switching, high pressure hot water shutoff valve 56 and mixed fluid shutoff valve 24A
Simultaneously with closing of ~ 24C, low pressure hot water check valves 64A ~ 64C are opened.
Closed the rolling oil check valve 34, high pressure hot water check valve 36 and mixed fluid.
Rolling oil, high-pressure hot water between the stop valves 24A to 24C, and
These mixed fluids are confined as they are. According to
Is supplied through the low pressure hot water supply branch pipes 62A to 64C.
The mixed fluid extruded by the low pressure hot water is
From stop valve 24A-24C to spray nozzle N₁~ N _TenFor up to
Only the amount remaining during this period is equivalent to the response delay
Becomes

In the above embodiment, the gas pressure cylinder operated poppet valve 1 is used as the mixed fluid shutoff valves 24A to 24C.
Although it has been described that 00 is used, a pneumatic cylinder actuated spool valve as shown in FIG. 8 may be used.
That is, the pneumatic cylinder actuated spool valve 200 is configured by forming the spool valve portion 202, the pneumatic cylinder portion 204, and the valve opening / closing detection sensor portion 206 as separate bodies, and integrally connecting these.

As shown in this figure, the spool valve portion 202 has a valve body 208 having a valve chamber 210 having a mixed fluid outlet 212 and a spool chamber 214 having an inlet 216. The inner diameter of the valve chamber 210 is formed larger than the inner diameter of the spool chamber 214. Front end of valve chamber 210 and spool chamber
An inner lid 21 having a through hole for spool guide is provided at the rear end of 214.
0a and an inner lid 214a are provided respectively, and outer lids 210b and 214b are attached to both end surfaces of the valve body 208 outside thereof.

A spool 218 is slidably inserted in the left-right direction with respect to the drawing through the spool guide through holes of these two inner lids 210a and 214a, and the spool chamber 214 is provided at the center of the spool 218. Valve body 2 so that it slides on the inner wall
20 are provided. The mounting position and the length of the spool 218 of the valve body 220 in the longitudinal direction are such that the valve body 220 is located completely inside the valve chamber 210 at the forward limit of the spool 218.
210 and spool chamber 214 are in communication with each other
In the backward limit of 218, the valve body 220 is slidably in contact with the inner peripheral wall of the spool chamber 214 so that the communication between the valve chamber 210 and the spool chamber 214 is cut off.

The gas pressure cylinder portion 204 attached to the right end of the valve body 208 is composed of a cylinder body 222, a piston 224 fitted therein, and a piston rod 226 attached to the front surface thereof. It is connected to the rear end of the spool 218. The piston 224
Is urged to the right by the compression spring 228 with respect to the drawing.
In addition, an air supply hole 232 for operating compressed gas is formed in the lid 230 at the right end of the cylinder body 222, and an exhaust hole 234 is formed through the peripheral wall of the cylinder body 222.

The valve opening / closing detection sensor unit 206 is connected to the right end of the gas pressure cylinder unit 204, and is fitted to the sensor cylinder 236 attached to the rear surface of the cylinder body 222, the lid 236a, and the sensor cylinder 236. The sensor piston 238, the valve body 240 having an outer diameter smaller than the inner diameter of the sensor cylinder 236 mounted on the sensor piston 238, mounted on the front surface of the valve body 240 and coupled to the rear surface of the piston 224. Sensor piston rod 242, and the tip 242a of the sensor piston rod 242 has a rear lid portion of the gas pressure cylinder portion 204.
It is inserted through the through hole 230a of 230 and can be brought into contact with the back surface of the piston 224 of the gas pressure cylinder portion 204.

A ring-shaped sensor valve seat 244 is attached to the inner peripheral surface of the sensor cylinder 236 at a position substantially corresponding to the forward limit position of the piston 224 of the gas pressure cylinder portion 204. An annular compressed body flow passage is formed between the compressed body and the outer peripheral surface of the. Also, pistons for sensors
238 includes a sensor cylinder in the sensor cylinder 236
A communication hole 250 is provided to allow spaces 246 and 248 in front of and behind 238 to communicate with each other to allow compressed gas to flow therethrough. The sensor piston 238 is biased to the left with respect to the drawing by the compression spring 252. In addition, the peripheral wall of the sensor cylinder 236 has a first through hole (air supply hole) 254 capable of communicating with the rear space 248 and a second through hole located in front of the sensor valve seat body 244. Holes (exhaust holes) 256 are drilled.

The operation of the gas pressure cylinder actuated spool valve 200 thus constructed will be described below. As a normal state, the compressed gas is supplied from the compressed gas source 160 to the space 248 behind the sensor piston 238 through the through hole 254. Therefore, first, if you open the gas pressure cylinder operation dynamic type spool valve 200 is supplied with compressed gas from the supply hole 232 of the actuating compressed gas to the back of the piston 224 by switching the solenoid valve (not shown). As a result, the piston 224 is pushed to the left side in the drawing against the biasing force of the compression spring 228, and moves leftward in the drawing until the front surface of the valve body 220 contacts the inner wall of the inner lid 210a. Then, the valve chamber 210 communicates with the spool chamber 214 so that the mixed fluid flows into the spool chamber 214 from the inflow port 216, passes through the valve chamber 210, and flows out from the outflow port 212 (22A to 22C in FIG. 2). ) Is supplied to the nozzle.

Following the leftward movement (advancement) of the piston 224 as described above, the sensor piston 238 is a compression spring.
Energized at 252 and pushed from right to left. As a result, the sensor valve body 240 comes into contact with the sensor valve seat 244 to close the passage of the compressed gas. Therefore, the compressed gas in the compressed gas line 162 rises until it becomes equal to the pressure of the compressed gas source 160. By detecting this pressure change with the pressure switch 164, the gas cylinder operated spool valve
It can be seen that the 200 has moved to the open side.

On the other hand, the pneumatic cylinder actuated spool valve 2
When 00 is opened, the compressed gas supplied to the rear piston chamber 222a is removed from the working compressed gas supply hole 232 by switching the solenoid valve. As a result, the compression spring 2
The urging force of 28 pushes the piston 224 to the right in the figure, and moves it to the right with respect to the figure until the circumferential surface of the valve body 220 contacts the inner circumferential surface of the spool chamber 214. This allows the valve chamber
The communication between 210 and the spool chamber 214 is cut off, and the flow of the mixed fluid is stopped.

As the piston 222 moves to the right (retracts) as described above, the sensor piston rod 242 is pushed from the left to the right against the biasing force of the compression spring 252. A gap is created between the valve body 240 and the sensor valve seat 244. As a result, the compressed gas is compressed by the pressure switch 164, the throttle 166, and the first through hole (air supply hole) 254.
Through the communication hole 250 of the sensor piston 238 into the front space 246, and through the gap between the sensor valve body 240 and the sensor valve seat body 244 to the second through hole ( Exhaust hole) 256 to be released to the outside. For this reason, the internal pressure of the compressed gas pipeline 162 decreases, and by detecting this pressure change with the pressure switch 164, it can be seen that the gas pressure cylinder actuated spool valve 200 has operated to the closing side.

In the embodiment shown in FIG. 8, the first through hole (air supply hole) 254 is provided behind the sensor piston 238.
However, as shown in FIG. 9, when the sensor piston 238 is located at a position substantially corresponding to the forward limit position of the gas cylinder portion 204, the gas pressure cylinder portion is more than the sensor piston 238. No. 1 on the peripheral wall of the sensor cylinder 236 between the sensor valve seat body 244 and the 204 side.
A through hole (air supply hole) 254 may be provided. In this case, the communication hole 250 of the sensor piston 238 makes the inner pressure of the space 248 behind the sensor piston 238 equal to the inner pressure of the front space 246 so that when the sensor piston 238 moves left and right, It acts so as not to interfere. Therefore, instead of the communication hole 250, the sensor cylinder 236
A ventilation hole (not shown) may be provided in the peripheral wall or the rear lid portion 236a for communicating the space 248 behind the sensor piston 238 with the outside.

In the embodiment shown in FIGS. 8 and 9, the sensor piston 238 among the first and second two through holes 254, 256 of the peripheral wall of the sensor cylinder 236 is used.
First through hole 254 (in the case of FIG. 8) that communicates with the space 248 behind the sensor or the gas cylinder portion 204 side of the sensor piston 238 and between the sensor valve seat body 244 and the first through hole 254. The compressed gas line 162 is used as the air supply hole (in the case of FIG. 9).
Although the present invention is not limited to this,
The second through hole 256 at the front end of the sensor cylinder 236 is used as an air supply hole, and the compressed gas pipeline 162 is connected to the first through hole.
254 may be an exhaust hole, and the operation in this case is no different from that of the above-mentioned embodiment. Second Embodiment Next, a second embodiment of the present invention will be described with reference to FIG.

In this embodiment, the pressure adjusting valve 70 and the pressure adjuster 72 are provided in the high pressure hot water supply pipe 54 branched from the hot water supply pipe 28.
The low pressure hot water supply main line 58 to the pressure regulating valve 74 and the pressure regulator.
76 is provided so that high pressure hot water and low pressure hot water controlled to a predetermined pressure can be supplied, and low pressure hot water check valves 64A to 64C of the low pressure hot water supply branch pipelines 62A to 62C of the block 40B. Low-pressure hot water throttle 66A on each downstream side
The point that 66C is attached is different from the first embodiment shown in FIG.

The operation and effect of this second embodiment are as follows. That is, since the supply pressure of the high-pressure and low-pressure hot water can be arbitrarily adjusted within the range of the boosting capacity of the hot water pump 26, the hot water tank 12 and the hot water pump 26 can be shared by a plurality of rolling stands that require different pressures, Equipment costs,
Maintenance costs can be reduced. Also, by installing the low-pressure hot water restrictors 66A to 66C, the difference in piping resistance to the target spray nozzle header, the number of connected spray nozzles,
The pressure loss values of the low pressure hot water restrictors 66A to 66C can be set according to the size (caliber) of the spray nozzles, and the low pressure hot water is jetted from the spray nozzles at substantially the same jet pressure. It is possible to prevent clogging of all spray nozzles and prevent the injection low-pressure hot water from reaching the rolling rolls. Example 3 Next, a third example of the present invention will be described with reference to FIG.

In the third embodiment, a main check valve 78 is connected to the low pressure hot water supply pipe main pipe 58 shown in the second embodiment downstream of the pressure regulator 74, and the main check valve 78 is connected. A pressure detection / alarm device 80 is attached downstream of the valve 78, and the other structure is the same as that of the second embodiment shown in FIG. According to this embodiment, any of the mixed fluid shutoff valves 24A-24C is open and the corresponding low pressure hot water supply branch lines 62A-62.
In the state where the pressure of the high-pressure mixed fluid acts on the upstream side of any one of the low pressure hot water check valves 64A to 64C of C, if there is an internal leak in any of the low pressure hot water check valves, high pressure mixing is performed. The fluid flows backward in the low-pressure hot water supply main pipe 58 to the hot water tank 12 side, but the reverse flow is blocked by the main check valve 78, and the equipment upstream from it is contaminated by rolling oil or damaged by the action of high pressure. It can be prevented.

Further, the pressure in the low pressure hot water supply main pipeline 58 downstream of the main check valve 78 is constantly monitored by a pressure detection / alarm device 80 provided downstream of the main check valve 78. When a backflow of the high-pressure mixed fluid occurs due to internal leakage of any one of the low-pressure hot water check valves 64A to 64C, and the pressure in the low-pressure hot water supply main conduit 58 exceeds a preset upper limit value, an abnormal alarm is issued. Therefore, it is possible to promptly know the abnormality and take prompt action. Fourth Embodiment Next, a fourth embodiment of the present invention will be described with reference to FIG.

In the fourth embodiment, the mixed fluid supply branch pipelines 22A to 22C of the third embodiment shown in FIG. 11 are branched from the middle to provide mixed fluid sampling pipelines 82A to 82C. It is led to the collecting tank 86, and the stop valves 84A to
84C is provided. According to this fourth embodiment,
Any one or more of the mixed fluid shutoff valves 24A to 24C are in an open state during a rolling operation, etc., and any one of the shutoff valves 84A to 84C is opened when rolling oil is injected from the corresponding nozzle, Corresponding mixed fluid sampling conduits 82A-82
Through C, the mixed fluid being jetted can be easily sampled. By analyzing and measuring the mixing ratio (concentration) of the rolling oil of the sampled mixed fluid, failure or failure of the precision gear pump 50 or rotation speed control device 52, blockage or leakage of each pipeline, malfunction of three-way valve, etc. It is very easy to check and identify whether the concentration of rolling oil does not deviate from the specified value, or whether the flow control performance characteristics of the precision gear pump 50 are exerted as designed, making it extremely stable and stable. Helps maintain the desired oil rolling. [Fifth Embodiment] Next, a fifth embodiment of the present invention will be described with reference to FIG.

In the fifth embodiment, as shown in FIG.
The branch pipes of the three systems of the fourth embodiment shown in FIG.
There are 5 systems of mixed fluid supply branch pipes 22A to 22E, low pressure hot water supply branch pipes 62A to 62E, and mixed fluid sampling pipes 82A to 82E, and a gas pressure cylinder actuated poppet valve 100A to a mixed fluid stop valve. The block 40D is integrally formed by using 100E. A filter 88 is attached to the low pressure hot water supply main pipeline 58.

In the block 40D, a part of the working compressed gas supply pipe lines 90A to 90E for supplying the compressed gas to the gas pressure cylinder portions 106A to 106E of the gas pressure cylinder actuation type poppet valves 100A to 100E are provided. , Valve opening / closing sensor
108A to 108E supplies compressed gas for detecting valve opening and closing, a part of the compressed gas supply pipelines 92A to 92E for detecting valve opening and closing, and compressed gas for detecting valve opening and closing discharged from the sensor units for valve opening and closing detection 108A to 108E. Compressed gas discharge branch pipes 94A to 94E for discharging air to the outside of the block 40D and the compressed gas discharge main pipe line
94 are installed internally.

Reference numeral 96 in the figure is a quick joint for connecting the mixed fluid sampling conduits 82A to 82E in the block 40D to an external hose (not shown), and a stop valve 84 is provided at the end of the hose. (See Figure 12). Reference numeral 98 denotes the compressed gas supply pipelines 90A to 90E for operation, the compressed gas supply pipelines 92A to 92E for valve opening / closing detection, and the compressed gas discharge main pipeline 94 in the block 40D, which correspond to the outside of the block 40D. It is a multi-connector for connecting with the conduit of.

The dimensions of the block 40D itself constructed in this way are 194 mm × 275 mm × 140 mm, and this block 40D
When the above-mentioned components are assembled on the outer surface of, the maximum external dimensions are 328 mm × 350 mm × 183 mm. This block
If 40D is placed in the mill, the gas cylinder actuated poppet valve 100A built into the block 40D
The pipe length from the outlet side of 100E (mixed fluid shutoff valves 24A to 24E) to the nozzle is within 1.7 m, which is slightly longer than that of the other embodiments described above, and the time of injection start and injection stop The response delay was within 1 second, which is almost the same as in the above-mentioned embodiment. This effect is the same when the gas pressure cylinder actuated spool valve 200 is used as the mixed fluid shutoff valves 24A to 24C.

In the above embodiments, an example in which hot water is used as a fluid for diluting rolling oil has been described.
The present invention is not limited to this, and hot water, soft water, pure water, or the like may be used instead of hot water. Further, it is needless to say that the present invention is not limited to the above-described embodiments and includes various modifications without departing from the gist of the configuration of the present invention.

[0083]

Since the present invention has the above-mentioned structure, it has the following effects. Since the precision gear pump is used to supply the rolling oil, the mixing ratio of the high-pressure dilution fluid and the rolling oil can be controlled in a wide range and with high precision in the range where the flow rate of the rolling oil is relatively low. It is possible to control the appropriate rolling oil concentration according to changes, and to perform stable oil rolling. In addition, since a throttle is provided in the low pressure dilution fluid supply main pipeline,
When the rolling oil is not injected, a low-pressure dilution fluid of a specified pressure is supplied to the spray nozzle, constantly spraying from the spray nozzle to prevent clogging of the spray nozzle, and the dilution fluid spraying from the spray nozzle is at a low pressure Therefore, even if the rolling oil mixes with the low-pressure dilution fluid being jetted due to valve malfunctions or internal leaks, it will not adhere to the rolling rolls and will be rolled next time. It is possible to prevent troubles due to defective biting of the material to be rolled, slips, and defective rolled products.

Since the main constituent parts and a part of the pipeline connecting them are integrally formed with the block, it is possible to arrange the block close to the rolling rolls between rolling stands having a small space. It is possible to minimize the response delay at the time of starting and stopping the injection of rolling oil, and it is possible to perform appropriate and stable oil rolling corresponding to changes in various rolling conditions. Also, when replacing or overhauling component parts, by replacing each block with a spare part, it is possible to minimize the manpower and time for parts replacement in the rolling mill, and enhance the safety of replacement work. be able to.

A throttle is provided on the downstream side of each check valve of the low-pressure dilution fluid supply branch pipeline, and the pressure loss value due to this throttle is pipe resistance to each spray nozzle header group communicating with each other, the number of spray nozzles, and the spray nozzle diameter. In consideration of the above, it is set to a predetermined value in advance, so it is possible to make the injection pressures of the low-pressure dilution fluids injected from any of the spray nozzles almost equal, and to block all spray nozzles. It is possible to surely prevent the low-pressure dilution fluid injected from any of the spray nozzles from reaching the rolling roll.

Since the main check valve is also attached to the low-pressure dilution fluid supply main pipeline and the pressure detection / alarm means is provided on the upstream side thereof, it is internally provided in any one of the check valves of the low-pressure dilution fluid supply branch pipeline. Even if a leak occurs, it is possible to prevent the high-pressure mixed fluid or the high-pressure diluted fluid from flowing back over the main check valve of the low-pressure diluted fluid supply main line in the direction of the low-pressure diluted fluid source, and at the prescribed pressure setting. When the value exceeds the value, an alarm is issued, so that it is possible to quickly know that an internal leak has occurred in any one of the check valves of the low pressure dilution fluid supply branch lines.

Since the mixed-fluid sampling pipes branched from the mixed-fluid supply branch pipes from the mixed-fluid shutoff valve to the spray nozzle header group are provided, it is difficult to measure the flow rate accurately and continuously. Even when oil rolling is performed in the low flow rate range of rolling oil, by opening the stop valve at the end of the rolling oil during injection, a mixed fluid of an amount suitable for analysis and measurement can be voluntarily or periodically added. Sampling can be performed without hindering the operation of the rolling mill, and the concentration of rolling oil can be adjusted to a specified value due to malfunctions / deficiencies of precision gear pumps, blockages / leakage of various pipelines, malfunctions of valves, etc. Check whether it is not out of alignment,
It is extremely easy to check and identify whether or not the flow control performance of the precision gear pump is exerting according to the design characteristics, and it is possible to carry out and maintain stable oil rolling as intended.

Since the gas pressure cylinder operated poppet valve or the gas pressure cylinder operated spool valve in which the gas pressure signal type valve opening / closing detection means is attached to the mixed fluid stop valve is used, the valve structure is simple and compact, and Reliable rolling oil injection / stop control even under adverse conditions of high temperature and high humidity.
It can be operated with high reliability.

[Brief description of drawings]

FIG. 1 is a pipeline diagram showing the configuration of a first embodiment of a rolling oil supply system of the present invention.

FIG. 2 is a perspective view showing a block used in the first embodiment in a perspective manner.

3 is a cross-sectional view taken along the line I-I of FIG.

FIG. 4 is a sectional view taken along the line II-II of FIG.

5 is a sectional view taken along the line III-III of FIG.

FIG. 6 is a cross-sectional view showing an example of the structure of a gas cylinder actuated poppet valve used in the first embodiment.

7 is a cross-sectional view showing a modified example of FIG.

FIG. 8 is a sectional view showing an example of the structure of a gas pressure cylinder actuated spool valve used in the first embodiment.

9 is a cross-sectional view showing a modified example of FIG.

FIG. 10 is a pipe diagram showing a configuration of a second embodiment of the rolling oil supply system of the present invention.

FIG. 11 is a pipeline diagram showing a configuration of a third embodiment of the rolling oil supply system of the present invention.

FIG. 12 is a pipeline diagram showing the configuration of a fourth embodiment of the rolling oil supply system of the present invention.

FIG. 13 is a pipe diagram showing a configuration of a main part of a fifth embodiment of the rolling oil supply system of the present invention.

FIG. 14 is a pipeline diagram showing a configuration of a conventional rolling oil supply device.

FIG. 15 is a perspective view showing a block used in a conventional rolling oil supply device in a perspective manner.

[Explanation of symbols]

10 Rolling oil tank (rolling oil source) 12 Hot water tank (diluting fluid source) 14 Mixer 16 Rolling oil supply pump 18 Rolling oil supply line 20 Three-way valve 22 Mixed oil supply line (mixed fluid supply line) 22A-22E Mixed oil supply branch pipe (mixed fluid supply branch pipe) 24A to 24E Mixed oil stop valve (mixed fluid stop valve) 26 Hot water pump (diluting fluid pump) 28 Hot water supply pipe (diluting fluid supply pipe) 32A to 32C Hot water stop valve (dilution fluid stop valve) 34 Rolling oil check valve 36 High pressure hot water check valve (high pressure dilution fluid check valve) 38 Return line 40, 40A, 40B, 40C, 40D Block 50 Precision gear pump 52 Speed control Equipment 54 High-pressure hot water supply line (high-pressure dilution fluid supply line) 56 High-pressure hot water stop valve (high-pressure dilution fluid stop valve) 58 Low-pressure hot water supply main line (low-pressure dilution fluid supply main line) 60 Throttle 62A to 62E Low-pressure hot water supply branch Pipe line (low pressure dilution fluid supply branch line) 64A to 64E Pressure hot water check valve (low pressure dilution fluid check valve) 66A to 66E Low pressure hot water throttle (dilution fluid throttle) 70, 74 Pressure adjustment valve 72, 76 Pressure regulator 78 Main check valve 80 Pressure detection / alarm (pressure detection)・ Alarm means) 82A to 82E Mixed fluid sampling pipes 84A to 84C Stop valve 86 Collecting tank 88 Filter 90A to 90E Operating compressed gas supply pipe 92A to 92E Valve open / closed detection compressed gas supply pipe 94 Compressed gas discharge main pipe 94A to 94E Compressed gas discharge branch line 96 Quick joint 98 Multi-connector 100A to 100E Gas pressure cylinder actuated poppet valve 102 Body 104 Poppet valve part 106 Gas pressure cylinder part 108 Sensor for detecting valve opening / closing (gas pressure signal type valve opening / closing) 112) Valve seat body 114 Poppet valve body 116 Piston 118L Left piston chamber 118R Right piston chamber 120 Sensor sleeve 120a Cylinder part 122 Sensor valve seat body 124 Sensor spool 128 Valve body part 130 Valve seat part 1 34 Valve chamber 136 Compression spring 142 Inlet 144 Outlet 146 Left piston chamber air supply / exhaust hole 148 Right piston chamber air supply / exhaust hole 150 First through hole (exhaust hole) 152 Second through hole (air supply hole) 160 Compressed gas source 162 Compressed gas pipeline 164 Pressure switch 166 Throttle 200 Gas pressure cylinder actuated spool valve 202 Spool valve section 204 Gas pressure cylinder section 206 Valve opening / closing detection sensor section (gas pressure signal type valve opening / closing detection means) 208 Valve body 210 Valve chamber 212 Outlet port 214 Spool chamber 216 Inlet port 218 Spool 220 Valve body 222 Cylinder body 224 Piston 226 Piston rod 228 Compression spring 230 Lid 232 Air supply hole 234 Exhaust hole 236 Sensor cylinder 238 Sensor piston 240 Valve body 242 Sensor piston Rod 244 Sensor valve seat 250 Communication hole 252 Compression spring 254 First through hole (air supply hole) 256 Second through hole (exhaust hole) N _{1 to} N ₁₀ Spray nozzle

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) B21B 45/02 310 B21B 27/10

Claims (13)

(57) [Claims] 1. A rolling oil supply device for supplying a mixed fluid prepared by mixing rolling oil with a diluting fluid to a rolling roll of a rolling mill through a spray nozzle, wherein a diluting fluid and a rolling oil supply line connected to a rolling oil source. A high pressure dilution fluid supply line connected to the source, a mixer for mixing the rolling oil and the high pressure dilution fluid to form a mixed fluid, and a rolling oil attached to the rolling oil supply line A three-way valve for selectively injecting the rolling oil whose pressure is increased by a supply pump into the mixer or the return line, and the number of rotations provided between the rolling oil supply pump and the three-way valve in the rolling oil supply line. A precision gear pump that controls the flow rate of rolling oil by control, a mixed fluid shutoff valve provided in each of the mixed fluid supply branch pipes from the mixer to the spray nozzle, and a high pressure dilution fluid supply pipe High A dilution fluid shutoff valve, a low pressure dilution fluid supply main line branching from the upstream side of the high pressure dilution fluid shutoff valve of the high pressure dilution fluid supply line and attached with a throttle, and connected to the low pressure dilution fluid supply main line. At the same time, a low pressure dilution fluid supply branch line connected to each of the mixed fluid supply branch lines from the mixed fluid stop valve to the spray nozzle, and a low pressure dilution fluid reverse branch provided in each of the low pressure dilution fluid supply branch lines. A rolling oil supply device comprising a stop valve. 2. A mixer as described above, a mixed fluid shutoff valve,
Low pressure dilution fluid check valve, part of rolling oil supply pipeline, part of mixed fluid supply branch pipeline, part of high pressure dilution fluid supply pipeline, part of low pressure dilution fluid supply main pipeline The rolling oil supply apparatus according to claim 1, wherein a part of the low-pressure dilution fluid supply branch line is integrally formed in a block. 3. The rolling oil supply device according to claim 1, wherein a throttle is provided on the downstream side of the low-pressure dilution fluid check valve. 4. The main check valve is provided on the downstream side of the throttle of the low-pressure dilution fluid supply main pipe line, and the pressure detection / warning means is provided on the downstream side of the main check valve. rolling oil supply device or the <br/> described. 5. The rolling oil supply device according to any one of the mixing to the fluid shutoff valve claims 1 formed by providing the mixed fluid supply branch pipe branches the mixed fluid sample line leading to the spray nozzle 4 . 6. rolling oil supply device according to any one of the high pressure diluent fluid on the upstream side of the high pressure diluent fluid shut-off valve of the supply pipe formed by providing a pressure regulating valve according to claim 1 to 5. 7. A pressure adjusting valve is provided in place of the throttle of the low pressure dilution fluid main pipe line.
Rolling oil supply device according to. 8. A gas pressure cylinder in which a poppet valve portion or a spool valve portion, a gas pressure cylinder portion, and a gas pressure signal type valve opening / closing detection means are integrally assembled in a cylindrical body in the mixed fluid shutoff valve. The rolling oil supply device according to any one of claims 1 to 7, wherein an operating poppet valve or a spool valve is used. 9. A gas pressure cylinder actuated spool valve or poppet in which a spool valve portion or a poppet valve portion, a gas pressure cylinder portion, and a gas pressure signal type valve opening / closing detection means are integrally formed with the mixed fluid shutoff valve. The rolling oil supply device according to any one of claims 1 to 7, wherein a valve is used. 10. The gas pressure signal type valve opening / closing detection means,
A cylinder portion is provided integrally with the rear surface of the gas pressure cylinder portion so as to extend to the back surface thereof and has an inner diameter smaller than the outer diameter of the piston of the gas pressure cylinder portion. A sensor sleeve provided with a through hole of
Is continuously provided in the sleeve for the sensor, the valve chamber to have a larger inner diameter than the inner diameter of the cylinder portion is made form, and a second through-hole of the sensor valve seat body provided at its peripheral wall, the gas The piston of the pressure cylinder portion penetrates through the through hole provided in the back wall of the gas pressure cylinder portion while inscribing, extends coaxially with the piston, is fitted in the sensor sleeve, and has a central portion. A small diameter portion having a diameter smaller than the inner diameters of both ends of the sensor sleeve and extending from the first through hole to the valve chamber of the sensor valve seat when the length of the piston is at the retracted limit position. And a valve body portion having an outer diameter smaller than the inner diameter of the cylinder portion of the sensor sleeve, which is provided at an end portion of the sensor spool on the side opposite to the pneumatic cylinder portion. Gas cylinder side of valve seat A ring-shaped valve seat portion that is provided at an end portion and is slidably contactable with the outer peripheral surface of the valve body portion within the range of the stroke of the valve body portion, and the first through hole or the second through hole. And a pressure detector attached to an upstream side of the throttle of the compressed gas pipeline, the compressed gas pipeline being connected to one of the two via a throttle to supply the compressed gas from the compressed gas source. The rolling oil supply device according to claim 8, wherein the rolling oil supply device is provided. 11. The gas pressure signal type valve opening / closing detection means includes a sensor sleeve integrally provided on a back surface of the gas pressure cylinder section and extending beyond a back wall, and a piston of the gas pressure cylinder section. Penetrating while penetrating from a back surface to a through hole provided in the back wall of the gas pressure cylinder portion, extending coaxially with the piston, and fitted in the sensor sleeve,
The center of the sensor sleeve has a small-diameter portion having an outer diameter smaller than the inner diameter of both ends of the sensor sleeve, and the sensor sleeve is provided at a position corresponding to the small-diameter portion of the sensor spool. Are in the forward limit, they communicate with each other, and when the piston is in the backward limit, they are mutually connected by the contact portion between the sensor spool outer peripheral wall and the sensor sleeve inner peripheral wall at the end opposite to the gas pressure cylinder portion. A pair of through holes provided in the inner peripheral wall of the sensor sleeve at a position where the communication between the two is cut off, and one of the pair of through holes is connected via a throttle to compress the compressed gas source. 9. A compressed gas pipeline for supplying gas and a pressure detector mounted upstream of the throttle in the compressed gas pipeline. Rolling oil supply system. 12. The gas pressure signal type valve opening / closing detection means is attached to the back surface of the gas pressure cylinder portion, and has a first through hole in a peripheral wall of an end portion on the gas pressure cylinder portion side, and a first through hole on the opposite side. A sensor cylinder having a second through hole in the peripheral wall of the end portion, and a communication hole that is fitted to the sensor cylinder and that communicates with the front and rear space of the sensor piston in a part of the side wall of the sensor cylinder. A sensor piston whose gas pressure cylinder portion side is biased by a compression spring, and a sensor valve body portion which is fixed to the gas pressure cylinder portion side of the sensor piston and has an outer diameter smaller than the inner diameter of the sensor sleeve. A sensor piston rod fixed to the sensor valve body so that its tip can abut against the back surface of the piston of the gas pressure cylinder portion; and the piston on the inner peripheral surface of the sensor sleeve. A ring-shaped valve seat body having an inner diameter smaller than the outer diameter of the valve body portion, which is attached to a position substantially corresponding to the forward limit position of the valve body, and a throttle in one of the first or second through hole. A compressed gas pipeline connected to supply a compressed gas from a compressed gas source, and a pressure detector mounted upstream of the throttle of the compressed gas pipeline. 9. The rolling oil supply device according to item 9. 13. The gas of the sensor sleeve when the sensor piston rod is positioned in the second through hole of the sensor sleeve at a position corresponding to substantially the forward limit position of the piston of the gas pressure cylinder portion. 12. Symbol mounting of the rolling oil supply system is characterized in that provided in the sleeve wall sensor between the pressure cylinder side a and the sensor valve seat body.