JPH03240809A - Constant flow rate device - Google Patents

Abstract

PURPOSE:To simplify the constitution of the constant flow rate device by forming two flow rate control parts while specifically connecting between a throttling mechanism having a variable throttling ratio and a pressure control valve. CONSTITUTION:A gas pressure feeding device 12 is provided between 1st and 2nd flow rate control parts 21 and 24 of a carbon dioxide constant flow rate device 50 which is set between the carbon dioxide sources 3 and 5 set at the upstream and downstreams sides respectively. The parts 21 and 24 are provided with the 1st and 2nd pressure control valves 22 and 26 and the 1st and 2nd needle valves 23 25. In such a constitution, the fluid supplied through the valve 22 is supplied to the valve 26 and the opening amount of the valve 22 is controlled in response to the differential pressure of the valve 26. So that the outlet pressure is not fluctuated despite the variance of the inlet pressure of the valve 22. Meanwhile the fluid supplied from the valve 25 is supplied to the valve 26 and the opening amount of the valve 26 is controlled in response to the differential pressure of the valve 25. So that the inlet voltage has no fluctuation despite the variace of the output pressure of the valve 26 respectively.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a constant flow device that pumps a predetermined instantaneous flow rate of fluid from an upstream fluid source in which the fluid pressure fluctuates to a F-stream fluid source. In particular, the present invention relates to a device that has a simple configuration and is therefore less likely to fail.

[Conventional technology]

@4 Figure is an explanatory diagram showing the configuration of a carbon dioxide gas constant flow device i11 as a conventional constant flow device.

In FIG. 4, 2 is a gas inlet of a constant flow device 1 connected to an upstream carbon dioxide gas source 3, and 4 is a gas outlet of a constant flow device 1 connected to a downstream carbon dioxide gas source 5.

6 is a pipe connecting the gas population 2 and the gas outlet 4.

7.8 is the gas population 2. All of them are pressure sensors that detect the pressure in the pipe line 6 near each gas outlet 4 and output pressure signals 7a*8a according to the detection results. 9 is an electric spade compressor with a fixed rotation speed provided in the pipe 6, and 10 is an RC pipe 6 so as to bypass the complexer 9.
11 is an fMit adjusting valve with a variable valve opening provided in the bypass flow path 10, and in this case, the complexer 9 controls the flow of carbon dioxide into the upstream carbon dioxide source 3 flowing from the gas population 2 into the pipe 6. It is provided to force-feed 3 m of carbon dioxide gas to the gas outlet 4, and also fiilf! ! 10 degree control valve 1
1 means that a part of the R amount Qb of the instantaneous f1ftiIkQ of 3 m of carbon dioxide gas discharged by the compressor 9 is recirculated through the tunnel 10, and by adjusting the opening degree of the valve 11, the recirculation 1M Rf Q b is It is provided so that the instantaneous Ri Qa = Q - Q b of the carbon dioxide gas 3!1 pumped to the gas outlet 4 becomes a predetermined value QaO.

Reference numeral 12 denotes a gas pressure feeding device consisting of a compressor 9, a flow path 10, and a valve 11. In FIG. 1, the pressure P! , the outlet side pressure P of the pressure feeding device 12 are each predetermined 1[P,. , P, · The opening degree of the valve 11 is adjusted and fixed so that the flow rate Q becomes QaO/c when the compressor 9 is operated.

13. 14 are pressure sensors that detect pressure P, , P, respectively, and output pressure signals 13al 141 according to the detection results, 15)! The fii sensor 16 detects the instantaneous flow rate Qt of the gas 3a flowing into the gas inlet 2 and outputs a flow rate signal 15ak according to the detection result, and adjusts the valve opening degree according to the input control signal 17a. 18 is a pipe resistance adjustment valve designed to change the pipe resistance R1 for 3 m of gas in the pipe line 6 between the flow rate sensor 15 and the gas pressure feeding device 12; Gas pressure feeding system fl1 by adjusting the valve opening degree
17 is a downstream pipe resistance control valve designed to change the pipe resistance R of the pipe line 6 between the gas outlet 4 and the gas outlet 4. Then, 17 is a pressure signal 7a*8ae
13as 14M and the flow rate signal 151 are input, the control signals 17a and 17b are output, and the signal 7a is output.
Even if the pressure P8 represented by the signal 8a and the pressure P represented by the signal 8a vary independently, the pressures p, , p, are each P
,. The above-mentioned constant flow device 1 is composed of the parts shown in the figure except for the gas sources 3 and 5.

Since the constant flow device 1 is configured as described above, in this case, the respective pressures of the gas sources 3 and 5, and therefore the pressures P1 and P
It is clear that the gas flow f[Qa flowing out from the gas outlet 4 is maintained at QaoK even if 4 varies in the following manner.

[Problem to be solved by the invention]

Fixed! f! The I-1 is configured as described above.

In this case, there are five pressure sensors 7 and 8 as detection parts.
．． 13.14, a flow rate sensor 15, a pipe resistance adjustment valve 16.18 as an operating unit, and a control device 17, and a total of seven signals 7a+8a, 13ae are required.
It is clear that a signal transmission path for transmitting t4a, isa, 17me17b is required, and constant flow device [1] has a large number of components. There is a problem in that it is easy to occur.

For the purpose of the present invention, it is possible to create a device configuration that eliminates the need to use the sensors and control device 17 described above. Therefore, a malfunction occurred in the sheep! It is possible to obtain a constant flow device.

[Means to solve the problem]

To achieve the above object, according to the present invention, the first pressure regulating valve is arranged such that the fluid flowing out from the first pressure regulating valve flows into the first throttling mechanism having a variable throttling ratio;
It consists of an aperture mechanism and the +it! Even if the pressure regulating valve adjusts its valve opening according to the differential pressure of the first throttling mechanism and the pressure of the fluid at the inlet of the first pressure regulating valve fluctuates, the I! a 1st R amount control section that operates so that the pressure of the fluid at the outlet of the 1st pressure control valve does not fluctuate; a fluid pumping means for pumping the fluid flowing out from the first throttling mechanism; The second pressure regulating valve has a variable throttle ratio, into which the fluid flows in, and a second pressure regulating valve, into which the fluid flowing out from the second throttle mechanism flows. The pressure of the fluid at the outlet of the second pressure regulating valve fluctuates according to the differential pressure of the second throttle mechanism, and the pressure of the fluid at the inlet of the second pressure regulating valve does not fluctuate even in degrees Celsius. The constant flow device is configured to include a second flow rate control section.

[Effect]

With the above configuration, even if the fluid pressure (hereinafter, such pressure may simply be referred to as inlet pressure) Pt at the inlet of the first pressure regulating valve changes, the # regulating valve will operate. Since the flow rate of the fluid passing through the first throttle mechanism does not fluctuate, the inlet pressure of the R body pressure feeding means does not fluctuate, and the fluid pressure at the outlet of the second pressure regulating valve (hereinafter, such pressure It is sometimes simply referred to as outlet pressure.

) Even if P4 fluctuates, the flow rate of the fluid passing through the second throttle mechanism due to the operation of the second pressure regulating valve does not fluctuate.
The outlet pressure of the R body pumping means does not fluctuate, and therefore the upper R(if 11
Even if the above-mentioned pressure P1 as the pressure of the one-body source and the above-mentioned pressure P4 as the pressure of the single-flow fluid source vary independently, it is possible to force-feed the fluid at a constant flow rate QaO, and furthermore, in this case, , the first pressure regulating valve and the first throttle mechanism can be formed integrally, and the opening degree of the first pressure regulating valve can be set to 5Vc so as to be directly driven by the differential pressure of the first throttle mechanism; The two pressure regulating valves and the second throttling mechanism can be integrally formed and the valve opening of the second pressure regulating valve can be directly driven by the differential pressure of the second throttling mechanism. The number of components is much less than in the constant flow device I described above, so that a constant flow device is obtained in which the device configuration is less prone to failure.

〔Example〕

Figure 1 is part 1 of the present invention! This is an explanatory diagram showing the configuration of the embodiment. In this figure, the same thing as in Fig.
The same reference numerals as in the figure are given.

W, In Figure 1, 191 is a pressure indicator that monitors the internal pressure P of the pipe line 6 in the vicinity of the gas population 2, 192°19
3 is the input pressure P of the gas pressure feeding device 12, respectively.

194 is a pressure indicator that monitors the internal pressure P4 of the pipe line 6 in the vicinity of the gas outlet 4, and 20 is a pressure indicator that monitors the outlet pressure P, and 20 is the flow rate Qa of the carbon dioxide gas 3a flowing out from the gas outlet 4. This is a flow rate indicator designed to monitor. Reference numeral 21 denotes a first flow control valve 21, which is composed of a first pressure regulating valve 22 and an AT needle valve 23 as a throttle mechanism with variable throttle ratio, and is attached to the pipe line 6 between the flow rate indicator 20 and the gas pressure feeding device 12. Part 24 is a conduit 6 between the gas pressure feeding device 12 and the gas outlet 4, and is composed of a @2 needle valve 25 and a second pressure regulating valve 26 as a throttle m structure with a variable throttle ratio.
A second flow control section attached to the flow control section 21.
24 are constructed as shown in FIG. 2 and FIG. 3, respectively. iE21ig1. The third WJ is a vertical sectional view of each of the flow rate control units 21 and 24.

In Figure 2, at 27:! ,! Figure 1 VC-Keru Pipeline 6
It is connected to the junction between the negative pipe section 6a of the flow rate indicator 20 and the first pipe section 6b of the gas pressure feeding device ff112 of the pipe line 6 in FIG. The columnar cavity 29, the through hole 30 with a circular cross section that communicates the cavity 29 and the recess 28, the communication passage 31 that communicates the cavity 29 and the conduit portion 6m, and the recess 28Vc are formed to communicate with each other. A constriction part 33 formed to constitute the above-mentioned needle valve 23 together with the valve body 32, a communication passage 34 that communicates the constriction part 33 and the conduit part 6b, and a constriction part 33 on the conduit part 6b side of the constriction part 33. The intangible part 36 provided with a pressure guide path 35 for guiding fluid pressure is provided with a truncated cone-shaped recess 37, and is shown so as to close the flange recess 28 on the -Ff' side. It is fixed to the main body part 27゛ by means that are not attached.
With a lid, this lid 36.

Further, a pressure guide path 38 is provided which communicates the pressure guide path 35 of the main body 27 with the recess 37 when the lid 36 is attached to the main body 27 as described above. 39 is a diaphragm sandwiched between the main body 27 and the lid 36; 40
is a spherical valve body arranged inside the cavity 29.

41 is a valve rod that penetrates through the through hole 30 so that the diaphragm 39 and the valve body 40 are fixedly KM-coupled; 42 is a coil spring provided in the recess 37 to press the diaphragm 39; This is a coil spring provided in the cavity 29 so as to press the valve body 40 upward. Then, @mentioned first flow rate control is 0! +121 is composed of the above-mentioned parts except for the conduit sections 6a and 6b. In the flow rate control section 21, the lower end of the through hole 30 serves as a valve seat for the valve element 4o, and a valve mechanism is formed by the F end of the first through hole 30 and the valve element 4o.

Since the flow rate control section 21 is configured as described above, the carbon dioxide gas 3a that has flowed into the main body section 27 from the pipe section 6!1 flows out to the pipe section 6b following the path of the arrow, but in this case, Pressure Pa in the connection between the pipe section 6b and the main body section 27
! As is clear from FIG. 1, if the diaphragm valve 39 and the valve are fixed, the diaphragm valve 39 and the valve Movable part 4 consisting of body 40 and valve stem 41
4 goes up and down. Therefore, in the second cause, if m Pam does not change, the differential pressure (PIiIn 'a) of the needle valve 23 will not change f even if Pa changes, so in this case, the pressure P□ and the needle valve 23 The carbon dioxide gas 3a with the instantaneous amount Q+ determined by the valve body setting position is transferred to the pipe section 6a or 6bf.
L' will flow.

T! Since each part of the ft-H control part 21 is constructed as described above, the valve opening degree is controlled by the main body part 27, the lid 36, the movable part 44, and the rings 42 and 44 of the needle valve 23. Pressure P1□ fluctuates depending on the differential pressure, and pressure P,
It can be said that the first pressure regulating valve 22 operates so that m does not fluctuate.

The flow control part 21 is composed of a pressure control valve 22 and a needle valve 23 arranged so that the carbon dioxide gas 31 flowing out from the pressure control valve 22 is absorbed by a needle valve 23rcfI, and the valves 22 and 23 are integrated. It can be said that it was formed by

Next, the configuration and operation of the second flow control section 24 will be explained with reference to FIG. In fig.

The difference from FIG. 2 is that the main body portion 45 corresponding to the main body portion 27 in FIG.
The above-mentioned cavity 29 is connected to the pipe section 6C of the helmet 12 and the pipe section 6d on the side of the gas outlet 4 of the pipe 6 in FIG. Not provided and #! A truncated conical valve body 47 is provided directly on the lower surface of the plumb 90, and a coil spring 48 is provided between the bottom surface of the recess 28 and the diaphragm 39 instead of the springs 42 and 43 shown in FIG. Then,
The flow rate side section 24 is composed of the illustrated sections except for the pipe sections 6C and 6d. In addition, in Fig. 3, the second
A second needle valve 25 is provided corresponding to the needle valve 23 in the figure, and since the knee wave control section 24 is configured as described above, the flow from the pipe section 6C to the main body section 45 is A large carbon dioxide gas of 3 m follows the route of the arrow to pipe section 6.
d, but in this case, the pipe portion 6C and the main body portion 45
If the pressure Pbt in the RNJ is fixed, as is clear from Figure 1, the a
Even if the pressure Pbz in the R section fluctuates, the pressure Pb in the recess 28
The movable part 49, which consists of the diaphragm 39 and the valve body 47, moves up and down so as not to vibrate. Therefore, in FIG.
If s does not fluctuate, -Pbm fluctuates and the differential pressure (PbIPbm) of the needle valve 25 does not fluctuate either. The carbon dioxide gas 3a is connected to the pipe section 6C or 6
It will flow through d.

In the flow rate control unit 24, each part is configured as described above, so the valve opening degree is adjusted by the main body part 45, the lid 36, the movable part 49, and the spring 48 according to the differential pressure of the needle valve 25. It can be said that the second pressure regulating valve 26 is configured to operate so that the pressure Pbm does not fluctuate even if the pressure Pbm fluctuates, and the R amount control sieve part 24 is connected to the gas pressure feeding device fl1.
The valves 25 and 2 are composed of a second needle valve 25 into which the carbon dioxide gas 3a flowing out from the needle valve 25 flows, and a second pressure regulating valve 26 into which the carbon dioxide gas 3a flowing out from the needle valve 25 flows.
6 can be said to be integrally formed.

Now, in FIG. 1, each part is constructed as described above. Therefore, as mentioned above, the pressure P8 is P.

and the pressure P is P. Adjust the opening degree of the valve 11 so that when the compressor 9 is operated with the button closed, the flow rate flowing out from the gas pressure feeding device 12 becomes Qao. Flow rate Q flowing through the flow rate control part 21.

When the pressure P1. P.

Even if they vary independently, the carbon dioxide gas 3a at a predetermined constant flow rate Q8° can be pumped from the gas source 3 to the gas source 5. Therefore, in @1 figure, each part shown except gas sources 3 and 5.

Constant flow rate Qa even if the pressures of gas sources 3 and 5 vary independently
A carbon dioxide gas constant flow device f50 that can force-feed O carbon dioxide scum 31 from the gas source 3 to the gas source 5 is configured.

Since constant flow device 50 operates as described above.

- After adjusting the flow rate adjusting valve 11 and needle valve 23.25 to determine the opening degree of each valve, the pressure indicator 191~
It is clear that 194 and flow indicator 20 may be omitted. ℃, the constant flow device 50 has the first and second f
It is possible to configure the system with only the quantity control section 21, 24 and the gas pressure feeding device 12.

Constant f! configured in this way! The tt device 50 has the above-mentioned constant flow f.
Since it is clear that the number of components is very small compared to the device IK, the constant flow device #L50 has a simple device configuration and is therefore a constant flow device that is less likely to malfunction.

Although the above-mentioned embodiment was a constant flow device for pumping carbon dioxide gas, one aspect of the present invention is a constant flow lid device for pumping fluids other than carbon dioxide gas.
It is obvious that #d is also applicable without any explanation.

〔Effect of the invention〕

As described above, in the present invention, from the first pressure regulating valve and the Ll throttling mechanism arranged so that the fluid flowing out from the first pressure regulating valve flows into the first throttling mechanism having a throttle ratio. and the ml pressure applying valve is the first
A first valve that operates so that the pressure of the fluid at the outlet of the first pressure reducing valve does not fluctuate even if the pressure of the fluid at the inlet of the third pressure reducing valve changes according to the differential pressure of the throttling mechanism.
ffi quantity control leg, a fluid pumping means for pumping the fluid flowing out from the first throttle mechanism, a variable throttle ratio w into which the fluid flowing out from the fluid pumping means flows, a two-throttle mechanism, and two throttle mechanisms on the side. and a second pressure regulating valve into which the outflowing fluid flows, and the @2 pressure regulating valve adjusts its opening degree according to the differential pressure of the wg2 throttling mechanism to control the flow of fluid at the outlet of the second pressure regulating valve. The constant flow device is configured to include a second flow rate control section that operates so that the pressure of the fluid at the inlet of the second pressure regulating valve does not vary even if the pressure fluctuates.

Therefore, with the above configuration, even if the fluid pressure (hereinafter, such pressure may simply be referred to as inlet pressure) Pt at the inlet of the fJIt1 pressure regulator valve changes, the operation of the regulator valve will not change. Therefore, the flow rate of the fluid passing through the first throttle mechanism does not change, so the inlet pressure of the fluid pressure feeding means does not change, and the pressure of the fluid at the outlet of the second pressure regulating valve (hereinafter, such pressure is sometimes simply called the outlet pressure.) Even if Pa fluctuates, the #! Since the flow rate of the fluid passing through the second throttling mechanism does not change due to the operation of the two-pressure regulating valve, the outlet pressure of the fM body pumping means does not fluctuate. The above pressure P1 as the pressure of the fluid source and downstream @
Even if the pressure P4 as the pressure of the fluid source fluctuates independently, a constant flow rate Q1° of fluid can be pumped; The valve opening degree of the first pressure regulating valve can be directly driven by the differential pressure of the first throttling mechanism, and the second pressure regulating valve and the second throttling mechanism can be integrally formed. second
Since the valve opening degree of the pressure regulating valve can be directly driven by the differential pressure of the @2 throttling mechanism, the present invention has a constant Rfk.
The device components are therefore much fewer than in the constant flow device 1 described above.

This has the effect of providing a constant flow device that has a simple device configuration and is less likely to malfunction.

[Brief explanation of drawings]

FIG. 1 is an explanatory diagram illustrating the configuration of an embodiment of the present invention. FIG. 2 and FIG. 3 are configuration explanatory diagrams of the main parts that are different from each other in FIG. 1. FIG. 4 is an explanatory diagram illustrating the configuration of a conventional foot R lid device. 12... Gas pressure feeding device (fluid pressure feeding means), 21
...First flow rate control section, 22...First pressure regulating valve, 23...First dollar valve (first throttling mechanism), 24... ...@25ft quantity system part, 25...
...Second needle valve (second throttle mechanism). 26... Second pressure regulating valve, 50... Carbon dioxide constant flow wave '++-no 23'2' Figure 1 + I' Figure

Claims (1)

[Claims] 1) The first pressure regulating valve includes the first pressure regulating valve and the first throttling mechanism arranged so that the fluid flowing out from the first pressure regulating valve flows into the first throttling mechanism having a variable throttling ratio. adjusts the opening degree of the valve according to the differential pressure of the first throttle mechanism, so that even if the pressure of the fluid at the inlet of the first pressure regulating valve changes, the fluid at the outlet of the first pressure regulating valve changes. a first flow control section that operates so that the pressure does not fluctuate;
A fluid pumping means for pumping the fluid flowing out from the first throttle mechanism; a second throttle mechanism having a variable throttling ratio into which the fluid flowing out from the fluid pumping means flows; and a second pressure regulating valve that adjusts the valve opening according to the differential pressure of the second throttling mechanism to adjust the pressure of the fluid at the outlet of the second pressure regulating valve. a second flow rate control section that operates so that the pressure of the fluid at the inlet of the second pressure regulating valve does not fluctuate even if the pressure of the fluid fluctuates.