JPS5963382A - Pressurized-fluid supplying apparatus by means of diaphragm pump - Google Patents

Abstract

PURPOSE:To improve the total efficiency and suppress increase of the oil temperature by installing a pilot valve which is operated by the internal pressure in a main cylinder chamber, between the damper chamber of a subcylinder and an oil tank. CONSTITUTION:A damper plunger 47 is installed in a subcylinder chamber 46 which communicates to a main cylinder chamber 40, and a pilot valve which is operated by the compressed oil supplied from the rear chamber of a relief valve 43 connected to the main cylinder chamber 40 is installed between a damper chamber 58 and an oil tank 18. When the internal pressure in the main cylinder chamber 40 exceeds the set value in the relief valve 43, said relief valve 43 operates to allow the compressed oil in the main cylinder chamber 40 to act onto the pilot valve 71 through a conduit 66, and then the pilot valve 71 is switched. Therefore, a damper chamber 58 communicates to an oil tank, and the damper plunger 47 is tilted rightward, and the internal capacity of the subcylinder chamber 46 increases, and thus the total efficiency is increased, and rise of the oil temperature can be suppressed.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is suitable for use in, for example, pressure feeding of paint in a coating machine.
The present invention relates to a fluid pumping device using a suitable diaphragm pump.

For example, during painting operations using a paint sprayer, intermittent or interrupted spraying is essential, and pressure fluctuations during spraying lead to deterioration of atomization and must be avoided. On the other hand, an electric motor is generally used as the drive source for a diaphragm pump used to pump paint, but if the electric motor is started and stopped each time the spray is interrupted during painting, the switch will open and close. It may become too large and cause premature damage to the switch, or
Since the III current frequently flows through the B machine, it may overheat, and furthermore, the pumping pressure may fluctuate, resulting in practical problems. Therefore, it has been conventional practice to continuously operate the electric motor even when spraying is interrupted, in order to eliminate the above-mentioned problems.
For example, Japanese Patent Publication No. 51-15601 (U.S. Patent No. 368)
No. 0981) is publicly known. This thing is
Hydraulic oil is interposed between the diaphragm pump and the piston that is reciprocated by the shear motor, and when spraying is interrupted and the displacement of the diaphragm of the diaphragm pump is restricted, excess hydraulic oil is released from the relief nozzle.
This prevents the M machine from being overloaded and the oil pressure rises excessively, thereby enabling continuous operation of the electric motor even when spraying is interrupted. 'fkL is displaced in response to the 1X movement and outputs the work of sucking in and pumping paint.
Most of the input from the motor is consumed in pumping the coating 11, and the internal tA'! There is no unreasonableness in the ml, and no technical difficulties arise.

However, when the spray is interrupted and the diaphragm is locked, the volume change rate of the hydraulic chamber that stores hydraulic oil between the piston and the diaphragm becomes maximum, and when the volume of the hydraulic chamber decreases, the hydraulic oil in the hydraulic chamber decreases. It returns to the tank via the relief valve, and when the volume of the hydraulic chamber increases, hydraulic oil is sucked into the hydraulic chamber from the tank. In this case, the work of the piston is not output to the diaphragm pump, but rather the high-pressure hydraulic oil compressed to high pressure by the piston is discharged through the narrow gap between the relief pulp and the orifice, overcoming frictional resistance. Therefore, the input from the electric motor is converted into heat and appears as an increase in oil temperature.

However, it is common to use diaphragm 4 + υ fat, which is a desirable material due to its economic efficiency, durability, and strength, but it has the disadvantage of being weak against heat, and therefore,
If the oil temperature is too high, the durability of the diaphragm will be significantly reduced. Therefore, by generating air bubbles as described above and reducing the absolute amount of hydraulic fluid sucked into the hydraulic chamber,
This reduces the amount of oil that passes through the relief valve to prevent the temperature of the hydraulic oil from rising. However, during the suction stroke of the piston, negative pressure is created in the hydraulic oil, causing air leakage.
This is contrary to common sense in the use of hydraulic equipment and merely reduces the efficiency of the pump. Even if the load can be reduced by suppressing the amount of hydraulic oil, the work that the diaphragm pump can do during spraying is also reduced, and the overall efficiency is extremely low. In addition, the above-mentioned publication describes the effect of removing vaporization heat by generating air bubbles (cavitation) and cooling the hydraulic oil.
This first argument is a one-sided argument that only considers the effect during depressurization and ignores the heat generated when bubbles condense during the compression stroke.If you look at the entire suction and compression process, there is no cooling effect and it is simply a constant state caused by cavitation. In short, although it is possible to operate the electric motor continuously during spray interruption, it has the drawbacks of low efficiency and extremely short service life due to permanent installation due to cavitation.

The present invention was made in view of the above circumstances, and its purpose is to significantly improve overall efficiency, minimize the load when the diaphragm displacement is locked, and minimize the increase in oil profile. An object of the present invention is to provide a fluid pumping device using a diaphragm pump that can perform the following steps.

An embodiment of the present invention will be described below with reference to the drawings. 1 and 2 are upper and lower casings, which sandwich a diaphragm 3 between their opposing surfaces. Reference numeral 4 denotes a pump chamber recessed in the upper casing 1 so as to face the upper surface of the diaphragm 5, and the upper casing 1 is provided with a suction pipe 5 communicating with the pump chamber 4. Reference numeral 6 denotes a foot valve provided within the suction pipe 5, which is supported by a support member 7 fitted within the suction pipe 5 so as to be movable up and down.

Reference numeral 8 denotes an annular valve seat fixed to the lower surface side of the support member 7, and the two-way valve 6 is urged upward by the elastic force of the compression coil spring 90 and comes into contact with the valve seat 8, and is passed from the pump chamber 4 to the suction pipe 5. prevents backflow.

Ten discharge pipes are fitted into the upper casing 1 and communicate with the inside of the pump chamber 4 via a 111j passage 12 having a check pulp 11 in the middle. Reference numerals 13 and 14 indicate check balls and compression coil springs that hold the check pulp 11 in place, and one end of the compression coil spring 14 is supported by a plug 15 screwed into the upper casing 1. A diaphragm receiving member 17 having a plurality of communication holes 17a communicating vertically is housed in the recess formed in the lower casing 1 facing the lower surface of the lower casing.18 is the lower casing. In the oil tank section 2 provided in the oil tank section 2, this and the recessed section 16 are communicated with each other through a stepped circular communication hole 19. A cylindrical cylinder 2o is fitted into the communication hole 19, and a nut is inserted into the oil tank section 2. The diaphragm 5 is fixedly attached at the outer periphery of the shaft portion 22, which extends downwardly from the lower surface of the center of the diaphragm 5 into the cylinder 20 through the through hole 17b of the diaphragm receiving member 170. A compression coil spring 23 for urging is inserted, and the compression coil spring 2
The lower end of the compression coil spring 23 is in contact with a nut 24 screwed into the lower end of the shaft portion 25, and the upper end of the compression coil spring 23 is in contact with the lower surface of the diaphragm receiving portion 4-17.

This is a piston installed in a 25-piece cylinder 20 so as to be able to slide up and down.This piston has an upper piston 26 having a female threaded part 26a at the lower end, a lower piston 27 having a male threaded part 27n at the upper end, and a male threaded part 27a with a female threaded part. It is integrated by screwing into the lower piston 27.
An annular spring receiver 28 is attached to the outer periphery of the lower end of the sliding ring 2.
A compression coil spring 30 is installed between the spring receiver 28 and the nut 21 to heat the piston 25 downward. A concave portion 2 t is formed on the upper surface of the upper piston 26 so as to escape the shaft portion 22 .
A suction passage 31 is provided between the most disposed portion of the concave portion 26b and the lower outer periphery of the lower piston 27. The lower end of this suction passage 31 is located below the oil level in the oil tank portion 18 even when the piston 25 is raised to the maximum. 32 is a valve chamber formed in the middle part of the suction passage 31 so that the upper piston 26 and the lower piston 27 are connected to each other, and a ball '53 and a compression coil spring 34 are installed here.
A suction valve 35 consisting of the following is housed. 36 is an electric motor (not shown)] A drive rotatably driven by 1! 'l! i
It is rotatably supported by the lower casing 2 via a ball bearing 37, and a ball bearing 38 is attached to an eccentric shaft portion 36a at the tip, and is prevented from coming off by a stop ring 39. The lower end of the piston 25 mentioned above is always in contact with the outer ring 388 of the ball bearing 58 due to the elastic force of the compression coil generator 30. 40 is the cylinder 20. In the main cylinder chamber surrounded by the piston 25 and the diaphragm 3, a valve hole 42 is provided in the lower casing 2 and communicates with the main cylinder chamber 40 via a passage 41. 43 is a relief valve that opens and closes the end of the passage 41, and an adjustment knob 44 is provided in this 11 and the valve chamber 42 so that it can be screwed back and forth.
A compression coil genera 441m is arranged between the 4
Reference numeral 5 denotes a sub-casing fixed to the side of the lower casing 2, in which a sub-cylinder 46 as a sub-chamber is formed substantially horizontally, and a damper plunger 47 is movably housed in the sub-cylinder 46. . 48 is sub cylinder 4
This is an oil passage that communicates between one end of the cylinder 6 and the main cylinder chamber 40. 49 is a valve case fixed to the curved end of the sub-cylinder chamber 46 by screwing or the like, and this and the damper plunger 4
A damper spring 50 is disposed between the
A connector 51 is connected to the valve case 49. A suction valve 54 is housed in the valve case 49 and includes a ball 52 and a compression coil spring 53 that urges the ball 52 toward the passage 513 of the connector 51. Reference numeral 55 denotes an oil supply pipe that connects the oil tank portion 18 and the connector 51, and its both ends are fixed with connector nuts 56 and 57, respectively. 58 is the damper plunger 47 and the valve case 49
An air bleed valve 59 communicating with this chamber is screwed and fixed to the sag casing 45. 60 and the bow A/60 through the air vent hole 59
It has a compression coil spring 61 that biases toward B,
It is normally closed with a cap 62. 66 is a pilot cylinder provided parallel to the sub-cylinder 46 and 1113, one end of which is open to the oil tank section 18 through a passage 64, and the other end of the pilot cylinder 63 is screwed into the sag casing 45. It is communicated with the connector 65. A relief pipe 66 is connected to the connector 65 via a connector nut 67, and is connected to a relief passage 69 provided in the lower casing 2 via a connector nut 68. The relief passage 69 is bent at right angles within the lower casing 2 and communicates with the valve chamber 42. Incidentally, reference numeral 70 is a blind plug that closes an opening created due to processing when forming the relief passage 69 bent at a right angle. On the other hand, 71 is a pilot pulp serving as an operating groove provided horizontally in the pilot cylinder 63 so as to be movable horizontally, and an oil passage 72 consisting of four annular parts is formed on the outer periphery, and is biased toward the connector 65 by a pilot spring 75. ing. Reference numeral 74 denotes a return passage bored in the pilot pulp 71, one end of which communicates with the oil passage 72, and the other end open into the pilot cylinder 63 on the passage 64 side. Reference numeral 75 denotes a passage connecting the damper chamber 5 and the side wall of the pilot cylinder 63. This is a passageway in which the pilot pulp 71 is placed in the original position shown in FIG. 1 by the biasing force of the pilot spring 73. It opens into the pilot cylinder 63 on the left side of the passage 72 in the drawing. Reference numeral 76 denotes a return passage shaped to communicate between both ends of the pilot cylinder 630, and a cylinder portion 77 having a larger diameter than the return passage 76 communicates with the portion bent at a right angle near the connector 65. There is. This cylinder portion 77 is open to the side surface of the sub casing 45, and the open end is closed with a blind plug 79 having a seal 78. Reference numeral 80 denotes a pleaser comprising a piston 81 and needles 82 integrally arranged in a row, and a compression coil spring 83 is disposed between the piston 81 and the blind plug 79. and,
The needle /I/82 is set to have a diameter slightly smaller than the inner diameter of the return passage 76 so as to create a small gap on the inner surface of the return passage 76. As shown in FIG. 1, at the soft part where the piston 81 has moved to the maximum in the urging direction (leftward) of the compression coil spring 83, the needle 82 penetrates the right-angled portion of the return passage 76, The tip reaches 4 degrees to the left of the folded part.

84 is a relief passage that communicates between the cylinder portion 77 and the return passage 76, and 85 is a relief passage that communicates between the return passage 76 and the relief passage 84.
Plug body that closes the opening created when forming, 86.87
88 is an O-ring and backing that seal between the lower casing 2 and the sub-casing 45, and 88 is the drive shaft 3.
6 is an oil seal provided in the through hole 2a of the lower casing 2 through which the lower casing 2 passes. In addition, a paint tank 1 containing 90°C of paint which is fed under pressure through 5 suction pipes (not shown)
The discharge pipe 10 is connected to a spray gun via a high pressure hose (not shown). And 89
is the hydraulic oil as Sakumachi 1 liquid stored in the oil tank @7!18.

Next, the operation of the above configuration will be described. First, we will describe the state in which the trigger of the spray gun is pulled and paint is discharged from the discharge pipe 10. When the drive shaft 36 is rotated by an electric motor (not shown), the piston 25 is compressed to 1
It repeats the lowering in the direction of arrow B by the biasing force of the upper row and the compression coil spring 30 in the direction of arrow B against the upward movement of spring 30. When the piston 25 moves upward and the volume of the main cylinder gi40 decreases, the hydraulic oil 89 in the main cylinder chamber 40 flows into the lower surface of the diaphragm 3 through the communication hole 17n and compresses the diaphragm 3. The paint 90 in the pump chamber 4 pushes up and opens the check pole 13 of the check pulp 11 against the compression coil spring 14 and is forced to discharge toward the discharge pipe 10. be done.

Next, when the piston 25 descends, the volume inside the main cylinder chamber 40 increases, so the hydraulic oil 89 on the lower surface of the diaphragm 3 increases.
returns to the main cylinder chamber 40 via the communication hole 17B, and the diaphragm 3 is lowered by the biasing force of the compression coil M spring 23. Then, as the diaphragm 3 descends, the volume of the pump chamber 4 increases and the pressure of the paint 90 inside becomes negative, so the foot valve 6 descends against the compression coil spring 9 and separates from the valve seat 8. Then, the paint 90 from the suction pipe 5 is pumped into the pump chamber 4.
Inhale inside. In this way, as the piston 25 moves up and down, the diaphragm 3 moves up and down, and the internal volume of the pump chamber 4 increases and decreases.
0 is sucked in and forcefully fed toward the discharge pipe 10, whereby a mist of paint is sprayed from the spray gun. In this state, the damper plunger 47 is prevented from moving in the direction of arrow C by the hydraulic oil 89 in the damper chamber 5B, so it communicates with the main cylinder chamber 40 via the oil passage 48. The volume of the cylinder chamber 46 is minimal and does not change.

Further, in this case, even if the piston 25 reaches the top dead center, unless the pressure of the hydraulic oil 89 in the main cylinder chamber 40 becomes equal to or higher than the opening setting pressure of the relief valve 43, the relief valve 43 will not be opened, and the relief valve 43 will not be opened. Although the hydraulic oil 89 is not flowing from the passage 69, the hydraulic oil 89 in the main cylinder chamber 40 is not flowing into the piston 2.
Only a small amount of hydraulic oil 89 leaks from the gap between the sliding surface between the piston 25 and the cylinder 20, and the hydraulic oil 89 reduced due to such leakage flows into the suction passage 31 and the suction valve 55 near the end of the downward stroke of the piston 25. The oil is replenished from the oil tank section 18 via.

Next, the operation when the spraying of paint from the spray gun is interrupted will be described. That is, the piston 25 is in the direction of arrow A.
While the paint 90 in the pump chamber 4 is not discharged from the discharge pipe 1o, the diaphragm 3 rises in the direction of ! It is in a state where it is restrained by the paint 9° in the pump chamber 4.

Therefore, the pressure of the hydraulic oil 89 in the main cylinder chamber 40 increases in inverse proportion to the decrease in the internal volume of the nuclear main cylinder chamber 4o due to the upward movement of the piston 25, and with a slight upward stroke, the pressure increases to the relief valve 43. set working pressure (e.g. 150
kg/ctl), the relief valve 43 moves in the direction of the arrow against the compression coil spring 44a and opens. Then, excess hydraulic oil 89 from the main cylinder chamber 40 flows into the valve chamber 42 through the passage 41 and flows into the relief passage 69.
While pressurizing the hydraulic oil 89 filling the relief pipe 66 and connector 65, the pressure is applied to the pilot valve 7.
1 and the left end surface of the piston 81, respectively. When the relief valve 43 is opened, high pressure is instantaneously applied to each end face of the pilot valve 71 and the piston 81, so the breather 80 instantaneously moves in the direction of arrow E, and the needle 82 temporarily moves the return passage 76. Open to! Rishi,
After that, the pleaser 8 is moved by the spring force of the compression coil spring 83.
When the needle 82 moves back in the opposite direction of the arrow E and the needle 82 enters the return passage 76, the amount of hydraulic oil 89 leaking from around the needle Iv 82 into the return passage 72 is significantly reduced. The pilot valve 71 is moved in the direction of the arrow F against the pilot spring 73 in substantially proportion to M of the hydraulic oil 89 passing through the valve 43, and eventually the oil passage 72 is communicated with the passage 75. (Second
(see figure). As a result, the operation in the damper nitrogen 58 is ffr! I oil 89 is 1eNK 75, oil passage 72 and return jm M&
74 and passage 64 into the oil tank section 18, the damper plunger 47 uses the pressure acting on the hydraulic oil 89 in the main cylinder chamber 40 to discharge the ETE.
&'? It begins to move in the direction of arrow C against the coil spring 50, and as the piston 25 moves up -L, Ii'i! in the main cylinder chamber 40! Secondary shilling chamber 4 according to the decrease in product
This results in an increase in the internal volume of 6. That is, once the internal pressure of the main cylinder chamber 40 has reached the set operating pressure of the relief valve t43, as the damper plunger 47 moves in the direction of arrow C, the internal pressure of the main cylinder chamber 40 rapidly decreases and becomes approximately equal to atmospheric pressure, and the relief valve 43 It is closed and the flow of hydraulic oil 89 into the dar chambers 42-- also stops. Then, the internal volume of the main cylinder chamber 40 is reduced and the internal gear of the sub cylinder chamber 46 is increased by I#-1 of #:'9.
．． This is performed at an equal rate of 1ii until the piston 25 reaches top dead center. Next, when the piston 25 exceeds the top dead center and begins to descend in the direction of arrow B, the damper plunger 47 is activated by the biasing force of the damper spring 50 as the internal volume of the main cylinder chamber 40 increases as the piston 25 descends. The cylinder 46 is moved in the opposite direction of arrow C, and the internal volume of the sub cylinder 46 is reduced.・Along with this, the internal volume of the damper chamber 58 increases at a rate approximately equal to the internal volume of the main cylinders Q', i 4 Q, but when the pressure of the 11 oil 890 inside the damper chamber 58 decreases, the suction The ball 52 of the valve 54 resists the compression coil spring 53.°C: IM path 5111
, and the inside of the damper chamber 58 (through the oil supply pipe 55 and the passage 51a in order) is connected from the oil tank part 18 to the damper hole 58 according to the increase in internal volume.
Inhale ilt 89. On the other hand, since the relief valve 43 is closed when the piston 25 descends from the top dead center to the bottom dead center, the hydraulic oil 89 does not flow into the pilot cylinder 65 on the right side of the pilot valve 71. However, since there is a slight gap between the needle/I/82 and the return passage 76, and the pilot valve 71 is biased in the opposite direction of the arrow F by the pilot spring 73, the pilot cylinder The hydraulic oil 89 in 63 is returned to the oil tank section through the gap around the needle 82, the return passage 76, and the passage 64, so that the pilot pulp 71 is returned to the oil tank part during the downward stroke of the piston 25 as shown in FIG. It is moved back to the original position shown.

Since a part of the hydraulic oil 89 in the main cylinder chamber 40 passes through the relief valve 45 at the beginning of the upward stroke and is returned to the oil tank within one day, it becomes insufficient at the end of the downward stroke of the piston 25. However, since the pressure inside the main cylinder chamber 40 decreases at this time, the bow IV5 of the suction valve 35 decreases.
5 rises against the compression coil spring '55 and is opened, and the hydraulic oil 89 in the oil tank is transferred to the suction passage 3.
1 into the main cylinder chamber 40. In this case, the spring force of the compression coil spring 35 is set to a relatively small value, and the amount of oil to be sucked is also small.
Cavitation does not occur in the hydraulic oil 89 within the main cylinder chamber 40.

As described above, the relationship between the movement of the piston 25 and the pressure inside the main cylinder chamber 40 when the paint 90 is not discharged from the discharge pipe 10 is the relationship shown in FIGS. 3(a) and 3(C). That is, at the beginning of the upward stroke of the piston 25, the pressure in the main cylinder chamber 40 becomes the pressure of the relief valve 430 for a short time, but after that (at time t in FIG. 3) the pressure in the damper plunger 47 increases as described above. Since the movement in the direction of arrow C is falsified, the pressure within the main cylinder chamber 40 becomes approximately atmospheric pressure.

That is, when the spray is interrupted, the time when the main cylinder chamber 40 is at high pressure is short, and the load acting on the 'jtL drive shaft is only for a short time when the main cylinder chamber 40 is at high pressure. can be operated with extremely light loads.For example,
When the paint 90 is not discharged from the discharge pipe 10, the eaves attachment of the diaphragm 3 is locked, so the hydraulic oil 89 in the main cylinder chamber 40 must be discharged to the outside in response to the rise of the piston 25. That is, for example, assuming that the damper 47 does not move, the pressure inside the main cylinder 40 will be as shown in FIG. 3(b) throughout the entire upward stroke of the piston 25.
As shown in the figure, set pressure of relief ㅅf'43 (for example, 15
0 kg/clt). And M3 figure (b)
, (When comparing (1), the decrease in the volume of the main cylinder chamber 40 due to the rise of the piston 25 is the same in the case of this embodiment in which the damper plunger 47 moves, and in the case where it is assumed that the damper plunger 47 does not move. Similarly, approximately the same amount of hydraulic oil 89 is sent out from the main cylinder chamber 4°, and 71 (: the motive is that the same amount of hydraulic oil 89 is sent out from the main cylinder chamber 40.
In this embodiment, the work is to send out hydraulic oil 89 at approximately atmospheric pressure, whereas when the damper plunger 47 does not move, , the set pressure of the relief valve 43 (for example, 1
50 kg/ctJ), and the amount of work of the electric motor in this example is approximately 1/1.
It only costs 150. And in this way 'II mII
The work given to the hydraulic oil 89 by ttR is converted into 7g% energy, but in this embodiment, the amount of work is reduced, so the oil temperature can be suppressed by 10% lower.

In order to evaluate the performance of the apparatus used in this example, the inventor operated the apparatus in the normal position with no paint 90 being discharged from the discharge pipe 10 to pass through the relief valve 43. When the amount of hydraulic oil 89 is extremely low, the damper plunger 47 is mechanically fixed in the position shown in FIG. 1 to restrain the internal volume of the sub-cylinder 46 from increasing.
) Experiments were conducted under the operating conditions shown in Figure 4 (+1) and (+)), and the temperature rise of the hydraulic oil 89 within one day of the oil task section was measured.

That is, in the device of this embodiment, the time during which the internal pressure of the main cylinder chamber 40 becomes high is short, and the hydraulic oil 8 that passes through the relief *45 is
9, the temperature of the hydraulic oil 89 (l is clearly jJ IJ-) is proportional to the temperature of the hydraulic oil 89 passing through the valve 45, and is also proportional to the input of the 'Flf ml machine.・As mentioned above, when the relief valve 43 is open, the electric motor compresses the hydraulic oil 89 to high pressure and closes the narrow gap between the relief valve F/15 and the j11 path 41.
It performs the work of discharging water while resisting low resistance, and this work is converted into thermal energy to produce l1Il oil 89
However, in the device of this embodiment, the temperature of the hydraulic oil 89 passing through the relief valve 43 is significantly lowered. ■It has become possible to reduce the electric motor input and keep the temperature A of the hydraulic oil 89 low. In addition, the present inventor has developed the apparatus of this embodiment and the Japanese Patent Publication No. 51-15601 'ij
As a result of conducting an experiment with the device shown in the above publication under "C operation" with the same amount of paint discharged from the sprayer, it was found that the device of the above publication is electric (the efficiency of the paint discharge output with respect to the table input is about 40%). On the other hand, in the case of the device U of this embodiment, the above-mentioned efficiency reached approximately 80%, and the experimental results showed that the electric motor input could be halved. It does not perform any extra work that would cause cavitation in the hydraulic oil 89, and
Even in the upward stroke, no extra work is done to compress the crab bubbles created by cavitation, which reduces extra work and improves overall efficiency.

On the other hand, in the apparatus of this embodiment, the paint 9 is
Since the main cylinder chamber 40 becomes high pressure for a short time when there is no discharge of 0, this high pressure acts on the diaphragm 5 each time,
During the downward stroke of the piston 25, an action is performed to forcefully feed the legally applied paint from the check pulp 11 to the pump main body 4 side to the discharge pipe 10 side again, and the pressure of the paint 90 in the g path from the discharge pipe 10 to the spray is reduced. It acts to keep the temperature constant. Hit, paint 9
0 contains a certain amount of solid matter, so check pulp 1
1's check ball 11 and foot valve 6 are completely turned into 4th hand parts! Although it is difficult to block the pipes in parallel, as a result of the nine actions described above, the pressure of the paint 90 after the discharge pipe 10 can be made constant.

The paint 9 is still connected from the discharge pipe 10 during the above (1゜) process.
Immediately after the relief valve 45 opens when there is no discharge of 0, the pleaser 80 once flJs in the direction of arrow E and returns to its original position, and then the pilot pulp 71 starts moving in the direction of arrow F. However, such movement is caused by a sudden increase in the dynamic pressure acting on the piston 81 immediately after the relief valve 43 is opened, and as a result of this action, fluid in the hydraulic oil 89 is generated between the needle 82 and the relief passage 76. Even if some garbage or the like gets caught, it will be automatically dropped. Therefore, when the piston 25 descends, the hydraulic oil 89 flows well between the needle 82 and the relief passage 76, and the pilot pulp 71
This has the effect of ensuring that the is returned in the opposite direction of arrow F.

The air bleed valve 59 is for discharging the air in the damper chamber 58 to the outside after manufacturing or maintenance to allow the device to operate normally. After filling the relief passage 69 and relief pipe 66 with hydraulic oil 89 from the main cylinder chamber 40, the set pressure of the relief valve 43 was increased, the cap 62 was removed, and the oil was passed through the air bleed valve 59. If you install a pipe etc. that returns the hydraulic oil 89 to the oil tank part 18 and similarly rotate the drive shaft 36 and set it in a state where the damper plunger 47 reciprocates in accordance with the vertical movement of the piston 25, the damper When the plunger 47 moves in the opposite direction of arrow C, the oil 89 is sucked into the damper chamber 58 from the oil tank section 18 through the oil supply pipe 55, and when the damper plunger 47 moves in the direction of arrow C, the damper chamber 58 The air in the damper chamber 58 is vented while the hydraulic oil 89 circulates along the path where the hydraulic oil 89 returns to the oil tank section 18 with the air inside the damper chamber 58 through the air vent valve 59. It is then closed with a cap 62 as shown in FIG.

If the air bleed valves 59i and 59t, the sub cylinder 46, and the pilot cylinder 63 are installed below the oil level of the oil tank portion 18, they can be made unnecessary.

In the above embodiment, the internal volume of the sub-cylinder 46 is changed according to the movement of the damper plunger 47, but the point is that the internal volume of the sub-cylinder 46 may be changed as long as it can be increased or decreased. Although the movement of the damper plunger 47 is restrained by the hydraulic oil 89 filled in the damper chamber 58, a general mechanical locking means may also be used. 171?, a pressure switch that detects the pressure inside the main cylinder chamber 40, and a coil, a magnet r, etc. that respond to this.
It is also possible to do so.

As is clear from the above description, the present invention has excellent advantages in that it can significantly improve the overall efficiency, minimize the load when the diaphragm is displaced, and suppress the rise in oil temperature. An effective iZG body pumping device using a diaphragm pump can be provided.

[Brief explanation of the drawing]

The drawings show an example of -'3'J/ill (Fig. 1 is a diagram of the entire tfie, and Fig. 2 is a longitudinal If of the main part of the working state of Jiλ1m and Akane. Figure 3 is a diagram showing the relationship between piston stroke and main cylinder chamber pressure, and Figure 4 is a diagram showing the relationship between piston stroke and main cylinder chamber pressure.
It is. In the drawing, 3 is a diaphragm, 4 is an eye chamber, 18 is an oil tank, 25 is a piston, 36 is a drive shaft, 40 is a main cylinder chamber, 43 is a relief valve, and 46 is an auxiliary cylinder chamber (
47 is a damper plunger, 58 is a damper chamber, 63 is a pilot cylinder, 71 is a pilot pulp (actuator 4ff), 80 is a pleaser'-, 811 is a piston, 811 is a needle, 89 is a hydraulic oil, 90 is a paint Applicant: Asahi Osumi Sangyo Co., Ltd. Tsurisha No. 4 M (a) → Temperature (°C) (b) → Product No. 1 Director-General of the Agency, Patent Application No. 175775 No. 1, Showa 57-175775, Invention,
ov name Fluid pressure feeding device 3 using diaphragm pump
, person making the amendment 4, agent〒4g. Voluntary 6 Specification subject to amendment. 7. The entire text of page 28 of the specification of amendments is corrected as shown in the attached sheet. 8. Reason for the amendment There is an error in the name of the title to be issued on page 28 r of the specification. is the breather, 181 is the piston, 82 is the knee) -/L/
, 89 is hydraulic oil, 90 t:j: paint, applicant
Asahi Inukuma Sanshiba (Above Corporate Procedures Amendment Form 1982 IN41, January lG11 Commissioner of the Patent Office ■, Indication of Width Matters η Temple Request 11? I 57-173773 No. 2,
SM Akira (D name $J< Fluid pumping device using diaphragm bong 3, relationship with the case of the person making the amendment Patent Kawaishi 1 person 4 / Agent 〒460 Address 116-151 Sakae 4-chome, Naka-ku, Nashiyoshi City 6 Nissan Life Insurance Company Itll of the detailed description of the invention of the specification subject to amendment V and C. 7. Contents of the amendment (1) Page 9 of the specification, 11th column, section 12 of the same page. Respectively stated in the 16th line of the same page. "Sub-cylinder 46" of [ε
11] Cylinder chamber 46,” corrects NJ. (2) Press "sub cylinder 46" described in lines 12 to 16 of the 10th shell as "sub cylinder chamber 46". (3) "Sub-cylinder" described in page 18, line 6 of the same
Correct n1 as "sub-cylinder chamber". (4) Same No. 24. j= is corrected from "Checkbo/l/11J" written on the 7th line to "Checkbo/L/13J." ``1 escape passage 76'' is corrected to ``1 return passage 76''. (6) "Sub-cylinder 46" written in item 11 of page 26 and line 12 of section on the same page is corrected to "sub-cylinder chamber 46." (7) "Negagadori" stated in the first line of page 25 of the same
I am corrected by saying, ``Return.''

Claims (1)

[Claims] 1. A pump chamber that has a diaphragm on one side and sucks and discharges a pressurized liquid according to the displacement of the diaphragm, and a piston that communicates with the other side of the diaphragm and is reciprocated by a drive source, and is actuated inside. A main cylinder chamber filled with liquid, an auxiliary chamber that communicates with the main cylinder chamber and whose internal volume can be increased or decreased, and an increase in the content of the auxiliary chamber when the internal pressure of the main cylinder chamber is below a predetermined value. A fluid produced by a diaphragm pump, which is configured to restrict the internal pressure of the cylinder and increase the internal volume of the auxiliary chamber in accordance with the decrease in the internal volume of the main cylinder chamber when the internal pressure of the cylinder exceeds the predetermined value. Pumping device.