JP3345105B2 - Solid-liquid mixed fluid transfer device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to
The present invention relates to a solid-liquid mixed fluid transfer device that transfers cold heat accumulated in a heat source storage unit using a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water.

[0002]

2. Description of the Related Art In district cooling or the like, a method for transferring sensible heat using a single fluid when transferring cold stored in a heat source storage section to a load section has been provided. On the other hand, in recent years, a system in which cold heat is conveyed using latent heat in combination with the sensible heat, that is, a system in which cold heat is transferred by a solid-liquid two-phase mixed fluid (for example, a solid-liquid mixed fluid of ice and brine) is often used. It was started. In such a cooling and heating system, the latent heat substance mixed filling rate (hereinafter referred to as “IP
F ″) must be adjusted in accordance with the fluctuation of the load or the fluctuation of the IPF in the heat source reservoir, and the solid-liquid mixed fluid needs to be supplied to the load.

FIG. 4 shows a conventional example of the solid-liquid mixed fluid transfer system. In FIG. 1, reference numeral 1 denotes a heat source storage unit or an ice tank in which a solid-liquid mixed fluid of ice and water is stored. The solid-liquid mixed fluid in the ice storage tank 1 is pumped by a transfer pump 2 provided in a transfer main pipe 7. The water is discharged under pressure and introduced into the IPF regulator 14 provided on the discharge side, where a part of the water is extracted and returned to the ice storage tank 1 through the drainage pipe 16. The flow rate of the water returned to the ice storage tank 1 is adjusted by detecting the density value of the mass flow meter 6 provided downstream of the IPF regulator 14. An example of the IPF control will be described with numerical values. Assuming that the required supply flow rate is Qm ³ / min and the required IPF is 30%, the IPF of the solid-liquid mixed fluid in the ice storage tank 1, that is, the IPF
Is 10%, the ice water flow rate 3Q in the ice storage tank 1 is pressurized to a pressure of 4 kg / cm ² · G by the transport pump 2 and sent out to the transport main pipe 7, and the IPF adjuster 14 controls the 2Q.
Is returned to the ice storage tank 1 through the drainage pipe 16, whereby the ice water flow rate Q whose IPF is adjusted to 30% is supplied to the load 9 via the regional conduit 8 to supply cold heat. In addition,
8a is a return conduit, 15 is an automatic regulating valve for controlling the drainage flow rate.

The IPF adjuster 14 is, for example, shown in FIG.
As shown in FIG. 5, a pipe made of a punched metal surrounding an outer pipe 142 around an inner pipe 141 connected to the main transport pipe 7, and forming the inner pipe 141 with a hole 14b having a diameter of about 0.5 mm. 141, and both ends of the outer pipe 142 are closed, and a drain pipe 16 is provided therebetween.
It functions as a liquid drain for PF adjustment. With this configuration, the solid-liquid mixed fluid from the ice storage tank 1
4, only water is extracted from the holes 14 b of the punching metal, and is returned from the water outlet C of the outer pipe 142 to the ice storage tank 1 via the drain pipe 16, whereby the IPF is adjusted.

[0005]

However, in such a conventional system, an IPF is provided on the discharge side of the transport pump 2.
Since the regulator 14 is provided, the drainage flow rate returned to the ice storage tank 1 through the drainage pipe 16 is also increased to the supply pressure to the load 9 (3 to 4 kg / cm ² · G). That is, unnecessary power is applied to the transport pump 2.

For example, FIG. 6 shows that Q0 is a solid-liquid mixed fluid, that is, an ice water inlet flow rate, Q1 is a drainage flow rate, Q2 is a carrier ice water flow rate, and IPF0, IPF1 and IPF2 are Q0 and Q, respectively.
FIG. 9 is a graph showing the relationship between Q1 / Q0 and the amount of IPF increase in transport ice water when IPF0 = 13.4% as the IPF values of 1 and Q2, based on experimental results. (Note that IPF1 = 0% in the figure represents a curve when ice is not contained in the extracted water). As can be seen from the figure, when the value of Q1 / Q0 is 0.4 or more, the amount of ice flowing out to the drainage pipe 16 increases, so that the amount of water drainage is increased by an amount corresponding to the amount of ice flowing out. Must increase. For this reason, the capacity of the transport pump 2 must be increased by at least the increase in the amount of drainage, and the transport power of the solid-liquid mixed fluid increases.

Since the IPF adjuster 14 is formed of a punching metal in the inner pipe 141 through which the mixed fluid passes, ice water flowing into the perforated metal pipe (inner pipe) passes through the metal pipe 141. While the outer pipe 14
The IPF rises to the side 2 and flows out. Therefore, the IPF becomes higher as it is closer to the exit of the punching metal 141, so that the ice particles tend to stagnate at the exit of the adjuster 14,
When ice water is continuously passed through the regulator 14, the IPF
Blockage on the mixed fluid (ice water) side in the adjuster 14 also easily occurs. It is considered that this is because the pressure loss generated when the punched metal tube 141 passes through the ice water is about six times as large as that in the case of the straight pipe. In view of the drawbacks of the prior art, the present invention is to provide a mixed fluid transfer device which prevents waste of power of a transfer pump, improves the efficiency of the system, and prevents the clogging of the piping system of the IPF regulator. Aim.

[0008]

According to the present invention, a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water stored in a heat source storage section such as an ice storage tank is cooled or heated by the heat source storage section. A transfer pump is provided in the transfer line connecting other loads,
The solid-liquid mixed fluid transfer device configured to transfer the solid-liquid mixed fluid to the load side by the transfer pump and to return the mixed fluid to the heat source storage unit side after exchanging heat with the load. An IPF adjuster is interposed on a transfer pipe between the storage section outlet and the transfer pump suction port, and a pipe configuring the IPF adjuster is expanded to a larger diameter than the transfer pipe.
In addition, the large-diameter pipeline is separated into two upper and lower via a flat liquid separation plate, and the upper separation pipeline is connected to the transport pipeline so that the solid-liquid mixed water can be transported. A liquid drain port for closing both ends of the lower separation pipe side and draining a liquid such as water having a higher specific gravity than the latent heat substance such as ice on the lower separation pipe side; And the heat source storage section are connected via a liquid drain pipe. In this case, it is preferable to provide a pump in the liquid drain pipe so that the drain amount can be changed. In addition, the IPF adjuster may be configured such that both ends in the axial direction of a large-diameter pipe constituting the IPF adjuster are disposed.
It is connected to the transport pipeline via the funnel and the IPF
An adjuster, to a plurality arranged in series in the conveying conduit is not better good <br/>.

[0009]

According to the present invention, since the IPF regulator is provided on the suction side of the transport pump for transporting the mixed fluid, only the amount of the mixed fluid corresponding to the required amount of cold heat on the load side needs to be transported by the transport pump. In other words, an amount of pump power corresponding to the amount of liquid extracted into the liquid drain pipe is not required. Thus, a saving in pump power is achieved as compared to conventional devices. Again I
The pipeline constituting the PF adjuster is separated into upper and lower two via a flat liquid separation plate, and the upper separation pipeline is connected to the transport pipeline,
In addition, since the lower separation pipe side functions as a liquid drain section, pressure loss generated when ice water passes can be greatly reduced, and thereby the blockage of the piping system of the IPF regulator can be effectively prevented. That is, since the specific gravity of the ice is lower than that of the water, the ice is transported in the upper separation pipe in a state where the ice floats upward.
Since only the inner wall of the pipeline exists above the upper separation pipeline and the punch metal (liquid separation plate) exists only on the bottom side, the ice does not contact the punching metal, so that a pressure loss does not occur. Absent.

Further, both ends on the lower separation pipe side functioning as a liquid drain portion below the liquid separation plate are closed. In other words, since water is drained from the water retaining portion, the drainage is easy and accurate. Can be performed.

[0011]

Embodiments of the present invention will be described below in detail with reference to the drawings. However, unless otherwise specified, the shapes, numerical values, specifications, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention thereto, but are merely illustrative examples. It is nothing more than a thing. A solid-liquid mixed fluid transfer device according to an embodiment of the present invention will be described. FIG. 1 is a system diagram showing a first embodiment of the present invention,
In the figure, 1 is a heat source storage unit or ice storage tank in which a mixed fluid of ice and water (ice water) is stored, 7 is a transfer pipeline, 2 is a transfer pump, and an outlet of the heat source storage unit 1 and a suction port of the transfer pump 2. A plurality of first and second IPF adjusters 3A and 3B having the ice water drainage port are provided in series on a transfer conduit between the first and second IPF adjusters 3A and 3B. The drainage branch pipes 11 and 12 are drawn out, respectively, and join the drainage pipe 16 connected to the ice storage tank 1. Reference numeral 5 denotes a drainage pump provided in the drainage pipe passage 16, which is capable of arbitrarily controlling the amount of drainage. 6 is a mass flow meter, 8
Is a return conduit, and 9 is a cooling load.

The configuration of the IPF adjusters 3A and 3B (hereinafter collectively referred to as 3) will be described with reference to FIG.
It is configured to have a larger diameter, and both ends in the axial direction are continuously provided via a funnel portion 59. The pipe 50 is separated into two parts, upper and lower, via a flat plate-shaped punch metal 55, and a semicircular blind lid 5 having the same diameter as the pipe 50 is provided at both ends of the punch metal 55.
6 is attached. As a result, the separation pipe 50A on the upper side of the punch metal 55 is connected to the transfer pipe 7, and both ends of the separation pipe 50B on the lower side of the punch metal 55 are closed. A drain port 57 is provided on the bottom side of the separation pipe 50B, and the branch pipes 11 and 12 are connected to the drain port 57.

Next, to briefly explain the operation of this embodiment, the ice water in the ice storage tank 1 is supplied to the first IPF adjuster 3A and the second IPF adjuster 3B provided in the transfer pipe 7 by using the first IPF adjuster 3A and the second IPF adjuster 3B. Is sucked into the transfer pump 2 and the pump 2
It is pressurized to a pressure of g / cm 2 · G and conveyed to a regional conduit 8 via a mass flow meter 6. A number of cooling loads 9 are connected to the regional conduit 8. The ice water that has given the cold heat to the cold load 9 is returned to the ice storage tank 1 as water. The ice is supplied to the ice storage tank 1 by operating the ice maker 120 (not shown) using cheap electric power at night to make ice.
In this embodiment, two first and second IPF adjusters 3A and 3B are arranged in series in the transport line 7,
It is within the scope of the present invention to provide one PF adjuster 3A, 3B, or to provide three or more PF adjusters in series.

Next, an example of the method for adjusting the IPF according to the present invention and the reduction of the transport power thereby will be described with reference to FIG. Now, it is assumed that the IPF in the ice storage tank 1 is 10%, which is increased to 30%, and the supply flow rate Qm ³ / min needs to be supplied to the cooling load 9 at a supply pressure of 4 kg / cm ² · G. The general formula of the theoretical power of the pump is that the flow rate is Q0m ³
/ Min, and the differential pressure before and after the pump is ΔPkg / cm ² , it can be expressed as W = 1.63Q0ΔP (kW).

In order to satisfy the above requirements, 3Q amount of ice water is taken out from the ice storage tank 1, the rotation speed of the water removal pump 5 is controlled, and Q amount of water is drained by the IPF regulators 3A and 3B, respectively. Return the 2Q amount of water to the ice storage tank 1. The amount of drainage is calculated from the density value of the mass flow meter 6. On the other hand, the transport pump 2 pressurizes the Q amount of ice water to 4 kg / cm ² · G,
This is conveyed to the regional conduit 8. Pump theoretical power W1
W1 = 1.63 (2Q × 1 + Q × 4) = 9.78Q when the drain pump 5 and the transport pump 2 are summed.

On the other hand, the theoretical power W2 of the conventional pump shown in FIG. 4 is calculated as shown in FIG. 8 under the same conditions as above, and W2 = 1.63 × 3Q × 4 = 19.56Q. Comparing the theoretical pump power of the present invention with that of the conventional one, W1 / W2 = 1/2. That is, the present invention makes it possible to reduce the transportation power of the mixed water by half compared to the conventional one.

Further, as described above, by simultaneously draining the water from the IPF regulators 3A and 3B, the outflow of ice to the drainage side flowing through the upper separation pipe 50 is reduced, and the regulators 3A and 3B are also removed. No blockage of the flow path on the ice water side occurs.

In the above-described embodiment, the case of district cooling using ice water has been described. However, a heat storage material which causes a change in state between water and solid due to a change in temperature is used as a latent heat substance in a capsule or the like. A case in which regional air conditioning is performed using a solid-liquid mixed fluid of water and water will be described with reference to the following embodiment. As a heat storage material that can be used for the IPF regulator,
A capsule (for example, a spherical capsule of 20 mm or less) that can be conveyed from a heat storage material that is solidified (including a slurry or a gel) at the time of heat storage for safety and corrosion resistance is used. Table 1 shows such a heat storage material, and Table 2 shows the state when the heat storage agent is used for cooling or heating.
Indicated by

FIG. 2 shows an embodiment of a regional air-conditioning system using the above-mentioned capsule as a solid-liquid mixed fluid conveying device according to an embodiment of the present invention. In the figure, 9 is a heating or cooling load (cold heat load), 21 is a heat source storage section, 22 and 23 are IPF adjusters, 24 is a transport pipeline, 25 is a transport pump, 26 is a drain pipe, and 27 is a drain pipe. Dedicated pump, 28 is an automatic regulating valve, 29 is a mass flow meter, 30 is a regional conduit, 31 is a circulating pump, 32 is an automatic regulating valve, 33 is a capsule collecting and regenerator, 34 is a punching of the capsule collecting and regenerator 33 Metal, 35 is a heat pump device, 36 to 40 and 46 are flow pipes, respectively.
Reference numerals 41 to 45 denote automatic adjustment valves. The heat pump device 35 is switched and used as a cooler during a cooling operation and as a heater during a heating operation.

First, when the heat pump device 35 is operated by using inexpensive nighttime electric power to perform the heat storage (cool storage) operation, the automatic adjustment valve 32 is closed, and the liquid temperature in the heat source storage section 21 is close to the heat storage temperature. Then, the automatic adjustment valves 41 and 45 are opened, the automatic adjustment valves 42, 43 and 44 are closed, and the circulation pump 31 is operated. The water in the heat source storage section 21 enters the capsule recovery and heat storage device 33 through the flow pipes 36 and 37, and then flows into the flow pipe 38.
After passing through the heat pump device 35 and heated here, it returns to the heat source storage section 21 through the flow pipes 39 and 40,
This cycle is repeated. By this circulation, heat (cold heat) is given to the heat storage material sealed in the capsule in the capsule recovery and storage unit 33.

When the temperature of the outlet of water or the temperature difference between the inlet and outlet of water in the capsule collecting and storing unit 33 is detected and the heat storage is completed, the automatic adjusting valves 42 and 43 are opened, and the automatic adjusting valves 41 and 43 are opened. The circulation pump 31 is operated with 44 and 45 closed. The water in the heat source reservoir 21 flows into the capsule collecting and storing device 33 through the automatic regulating valve 43 through the flow tube 36, and returns to the heat source storing portion 21 through the flow tube 46 with the capsule in the heat storage device. The capsule is stored in the reservoir.

The operation under the air-conditioning load is performed as follows. The automatic adjustment valve 32 is opened. By operating the transport pump 25, the solid-liquid mixed fluid of the capsule and water in the heat source storage section 21 is subjected to IP
The water is introduced into the F adjusters 22 and 23 and the exclusive draining pump 27 is operated, whereby an appropriate amount of water is extracted and returned to the heat source storage 21. The flow rate for draining water is mass flow meter 2
The number of rotations of the dedicated pump 27 is controlled by detecting the density value of No. 9 or by controlling the automatic adjustment valve 28 while keeping the number of rotations of the dedicated pump 27 constant.

In this manner, the solid-liquid mixed fluid adjusted to the required IPF is conveyed to the local conduit 30 and transfers heat to and from the load 9 to perform air conditioning. When the automatic adjustment valves 41, 42, 43 are closed and the automatic adjustment valves 44 or 45 are opened, the solid-liquid mixed fluid after heat transfer flows through the capsule collection and heat storage unit 33, and then flows through the flow pipe 40 to the heat source storage unit. Return to 21. For this reason, the latent heat used capsule in the solid-liquid mixed fluid is captured and accommodated in the capsule collecting and storing unit 33 by the punching metal 34 having an opening smaller than the diameter of the capsule.

There are two routes for returning the solid-liquid mixed fluid from the capsule recovery and regenerator 33 to the heat source storage section 21. That is, when the temperature of the solid-liquid mixed fluid is substantially equal to the heat storage temperature, the solid-liquid mixed fluid is returned to the heat source storage section 21 through the automatic adjustment valve 44, and the solid-liquid mixed fluid is used up to sensible heat. When there is a temperature difference from the heat storage temperature, the solid-liquid mixed fluid enters the heat pump device 35 via the automatic adjustment valve 45, where it is cooled or heated to approximately the heat storage temperature, and then returned to the heat source storage unit 21. You.

When the air conditioner operates at full load, it is a general method to use both the night operation method and the chasing operation method. Therefore, at the time of maximum load, the above-mentioned heat storage operation is also required, so that the capsule recovery and heat storage 3
Three units are installed in parallel, and the heat pump device 3
The cold water or hot water from 5 is flowed into the container where the capsules have been collected, a heat storage operation is performed, and then the capsules stored by the above-mentioned method are returned to the heat source storage unit 21.

Although the above embodiment is directed to district cooling, the present invention is not limited to this, and includes heating. Therefore, "load" includes "cooling load" and "heating load".
The “heat source storage section” includes an “ice storage tank” and a “high heat source”, respectively.

[0027]

As described above, according to the present invention, an IPF regulator is provided on the suction side of a transport pump for a solid-liquid mixed fluid,
Since an appropriate amount of water (water) is drained and returned to the heat source storage section in the adjuster, the transfer power is significantly reduced as compared with a conventional transfer pump having an IPF adjuster on the discharge side of the transfer pump. can do.

Also, since the IPF regulator can be installed near the heat source storage part, the flow resistance in the drainage pipe from the regulator to the storage part is extremely small as compared with the local conduit, and therefore, the IPF regulator is exclusively used for drainage. Even if a pump is used, the pressurization is about 1 kg / cm ² · G, and the increase in transport power due to this is extremely small.

In the conventional apparatus, when the value of the drainage flow rate / the solid-liquid mixed fluid inlet flow rate (the inlet means the inlet of the regulator) becomes 0.4 or more in the IPF regulator, the drainage is performed. Ice flow from the side increases, efficiency decreases,
In addition, although it is easy for the IPF regulator to be clogged on the mixed fluid side, if several IPF regulators are installed in series, the flow rate of water drained from one regulator can be reduced to a predetermined allowable value (40). %) Or less, so even when the rate at which the value of IPF must be increased is large,
There is no danger that the efficiency of each IPF regulator will be reduced, and a safe, reliable and efficient operation of the device can be achieved. Further, the flow rate of the solid-liquid mixed fluid conveyed to the cold load section is controlled by adjusting the operation of the transfer pump in accordance with the fluctuation of the cold load, and the operation of the stirrer in the heat source storage section is adjusted to control the heat source storage. Since the IPF of the solid-liquid mixed fluid flowing out of the section can be controlled,
This is suitable for the case where the control is performed in a stepless manner, and similarly to the above, a highly efficient district heating and cooling operation can be performed.

The present invention also relates to a line 5 constituting an IPF adjuster.
0 is separated into two upper and lower parts via a plate-like liquid separation plate, an upper separation line 50 is connected to a conveying line, and a lower separation line 50 is connected.
Since the side functions as a liquid drain portion, pressure loss generated when ice water passes can be greatly reduced, and thereby the blockage of the piping system of the IPF regulator can be effectively prevented. Further, both ends on the lower separation pipe 50 side functioning as a liquid drain portion below the liquid separation plate are closed, in other words, in order to drain water from the water retaining portion,
Drainage is easy and accurate. And so on.

[Brief description of the drawings]

FIG. 1 is a system diagram of a solid-liquid mixed fluid transfer device according to a first embodiment of the present invention.

FIG. 2 is a system diagram of a solid-liquid mixed fluid transfer device according to a second embodiment of the present invention.

3A and 3B show an example of an IPF adjuster applied to the embodiment, wherein FIG. 3A is an overall perspective view, and FIG. 3B is a perspective view of a main part of a punching metal.

FIG. 4 is a system diagram showing a conventional transport device.

FIG. 5 is a schematic sectional view showing an example of a conventional IPF adjuster.

FIG. 6 is a diagram showing functions of a conventional IPF adjuster.

FIG. 7 is a diagram illustrating the operation of the second device of the present invention.

FIG. 8 is an operation explanatory view of a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Ice storage tank as heat source storage part 2 Transport pump 3A, 3B Latent heat substance filling rate regulator (IPF regulator) 5 Drain pump 7 Transport pipeline 8 Regional conduit 9 Cold load 1a Solid-liquid mixed fluid outlet 1b Drain pipe 51 Wire mesh or punching metal 52 Stirrer

[Table 1]

[Table 2]

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Mitsuru Yamamoto 2-13-1, Botan, Koto-ku, Tokyo Co., Ltd. Inside Maekawa Manufacturing Co., Ltd. (72) Inventor Yasushi Ohno 2-13-1, Botan, Koto-ku, Tokyo Co., Ltd. Inside the Maekawa Works (72) Inventor Shunichi Aizawa 2-3-1 Botan, Koto-ku, Tokyo Co., Ltd. Inside the Maekawa Works Co., Ltd. (72) Inventor Takushi Yokoyama 2-3-1 Botan, Koto-ku, Tokyo Co., Ltd. (72) Inventor Yamato Morikawa 3-3-22 Nakanoshima, Kita-ku, Osaka City, Osaka Prefecture Inside Kansai Electric Power Company (72) Inventor Masahiro Miyawaki 3-2-2, Nakanoshima, Kita-ku, Osaka City, Osaka Kansai Electric Power Company (72) Inventor Ken Fujimoto 4-6-2 Komyobashi, Chuo-ku, Osaka-shi, Osaka Inside Nikken Sekkei Co., Ltd. (72) Inventor Tomohiro Kuriyama, Chuo-ku, Osaka-shi, Osaka 4-6-2 Hashi, Nikken Sekkei Co., Ltd. (56) References JP-A-3-236537 (JP, A) JP-A-3-129227 (JP, A) JP-A-3-34533 (JP, U ) Hikaru Hei 3-42932 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F24F 5/00 102 F25C 1/00

Claims (2)

(57) [Claims] 1. A conveyance for connecting a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water stored in a heat source storage section such as an ice storage tank to connect the heat source storage section to a cooling or heating or other load. A solid-liquid mixing unit configured to provide a transfer pump in a pipeline, transfer the solid-liquid mixed fluid to the load side by the transfer pump, and return the mixed fluid to the heat source storage unit side after exchanging heat with the load; In the fluid transfer device, an IPF adjuster is interposed on a transfer pipe between the heat source storage section outlet and the transfer pump suction port, and a pipe forming the IPF adjuster has a larger diameter than the transfer pipe. Forming by expanding
At the same time, the large-diameter pipe is separated into upper and lower two via a flat liquid separation plate, and an upper separation pipe is connected to the transfer pipe so as to be able to transfer the solid-liquid mixed water. Both ends of the lower separation pipe side are closed, and a liquid drain port for draining a liquid such as water having a higher specific gravity than the latent heat substance such as ice is provided on the lower separation pipe side, and a liquid drain port of the IPF regulator is provided. A solid-liquid mixed fluid transfer device, wherein the heat source storage section is connected via a liquid drain pipe. 2. A large-diameter pipeline constituting the IPF adjuster.
2. The solid-liquid mixed fluid according to claim 1, wherein both ends in the axial direction are connected to the conveying line via a funnel , and a plurality of the IPF adjusters are arranged in series on the conveying line. Transport device.