JPH11294908A - Steam drive steam exhaust type ice heat-storing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make ice at a low drive steam pressure, by installing the tip part of the nozzle of an ejector at a specific position in the mixing part of a diffuser according to a drive steam being introduced to a nozzle. SOLUTION: An ejector 15 includes an ejector body 19, a nozzle 17, and a diffuser 18, an ice heat-storing bath 12 is connected to the ejector body 19 via a valve 26, and the nozzle 17 is connected to a steam generator 14 and is installed in the ejector body 19 and the diffuser 18. A condenser 16 is connected to the diffuser 18, to the steam generator 14 via a pump 25, and to the ice heat-storing bath 12 via a valve 27. The mixing part of the diffuser 18 mixes drive steam that is injected from the nozzle 17 and steam that is generated from the ice heat-storing bath 12, a throat part compresses and accelerates the mixed steam, and an enlargement part decelerates the flow of steam and guides it into the condenser 16 while diffusing it. In this case, the tip part of the nozzle 17 is installed at a specific position in the mixing part of the diffuser 18.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steam-driven steam-exhaust type ice heat storage device using a jet pump as steam exhaust means.

[0002]

2. Description of the Related Art Freon substitutes such as hydrofluorocarbons and Freon-based refrigerants used in conventional ice heat storage devices are not desirable to be used because of their effects on the global environment such as depletion of the ozone layer and global warming. While the use of such chemical substances that harm the global environment is regulated, a non-fluorocarbon ice thermal storage cooling system using nighttime electric power using water as a working medium has been proposed in Japanese Patent Application Laid-Open No. 3-912623 filed by the present applicant. . Usually, such a steam-exhaust-type ice heat storage device such as the ice heat-storage cooling system includes an ice heat storage tank and a steam exhaust unit. In the ice storage cooling system, a water-absorbing polymer gel is used for storing water and / or ice in the ice storage tank, and a steam-driven jet pump is used as an example of the steam exhaust means.

FIG. 7 shows a schematic configuration diagram of a conventional steam-driven steam exhaust type ice heat storage device 1. The steam-driven steam exhaust type ice heat storage device 1 includes an ice heat storage tank 2 and a jet pump. The jet pump includes a steam generator 3, an ejector 4, and a condenser 5. The ejector 4 includes an ejector body 6, a nozzle 7 and a diffuser 8. The nozzle 7 is installed in the ejector body 6 located above the ice heat storage tank 2, and the tip 7 a of the nozzle 7 is connected to the ejector body 6.
Is located within.

[0004] The jet pump is driven by steam,
The operation is as follows. The driving steam generated from the steam generator 3 is expanded and accelerated in the nozzle 7 and has a Mach number of 1
And flows into the ejector main body 6.
The high-speed flow of the driving steam flowing into the ejector body 6 sucks the generated steam in the ice heat storage tank 2, is mixed with the steam generated from the ice heat storage tank 2 in the diffuser 8, and reaches the condenser 5 while diffusing. The water condensed in the condenser 5 is returned to the ice heat storage tank 2 via the steam generator 3 via the pump 9 and the valve 10.

On the other hand, in the ice heat storage tank 2, the pressure in the tank is reduced by a jet pump and the vacuum is maintained, so that a part of the water in the ice heat storage tank 2 evaporates at a normal temperature or less, and the latent water causes the remaining water. Is cooled. In this manner, the remaining water is stored in the ice heat storage tank 2 as cold water and / or ice.

[0006]

However, in such a conventional steam-driven steam exhaust type ice heat storage device,
The problem is that ice making is impossible with the suction capacity of conventional jet pumps because it is difficult to maintain the vacuum of the entire apparatus, and the lower the water temperature, the greater the amount of steam consumed and the lower the thermal efficiency. there were. Therefore, it was mainly used for cold water production. In the case of cold water production, the driving steam generally required a driving steam pressure of 0.294 MPa or more.

[0007] The conventional jet pump is useful in that it uses no substances other than water in its system and is highly safe for the environment. In addition, if ice making in the ice heat storage device is possible by driving a jet pump with a low vapor pressure, it is possible to use the steam that is currently generated at refuse treatment plants and wastefully disposed of in the environment, Save money.

[0008] It is an object of the present invention to provide a steam-driven steam-exhaust-type ice heat storage device capable of making ice at a low drive steam pressure.

[0009]

According to the first aspect of the present invention,
In order to solve the above problems, an ice heat storage tank that stores heat by storing water and / or ice and the like, and an exhaust unit that exhausts water vapor generated by reducing the pressure in the ice heat storage tank, A steam generator configured to generate steam,
An ejector for introducing, accelerating and injecting the steam, and a condenser for condensing driving steam ejected from the ejector, wherein the ejector is provided with an ejector main body, and a part thereof is provided in the ejector main body. A steam injection nozzle connected to the steam generator to inject drive steam,
A diffuser for mixing the driving steam injected from the nozzle and the steam generated from the ice heat storage tank and guiding the mixed steam to the condenser while diffusing the mixed steam, wherein the inner diameter of the diffuser is sequentially reduced in the axial direction. A first cylindrical portion (hereinafter simply referred to as a mixing portion) having an enlarged end portion at one end and a reduced end portion at the other end, the enlarged end portion being connected to the ejector body; A second cylindrical portion (hereinafter simply referred to as an enlarged portion) having a reduced end portion at one end and an enlarged end portion at the other end, the enlarged end portion being connected to the condenser; A third cylindrical portion (hereinafter simply referred to as a throat portion) having both ends connected to the reduced end portion of the mixing portion and the reduced end portion of the enlarged portion, and a tip portion of the nozzle is introduced into the nozzle. According to the pressure of the driving steam, the mixing section A steam-driven steam exhaust type ice thermal storage apparatus characterized by being installed at a predetermined position between the expanded end portion and reducing end.

[0010] According to the water vapor evacuation type ice heat storage tank configured as described above, the suction capacity of the evacuation means is improved, and ice can be produced because the ice heat storage tank is efficiently held in vacuum. According to a second aspect of the invention, in the steam-driven steam exhaust type ice heat storage device according to the first aspect, the driving steam introduced from the steam generator to the nozzle has a pressure of 0.294 MPa or less.

Further, in the steam heat storage type ice heat storage device according to claim 1 or 2, the ice heat storage tank may have a gel. Further, in the steam-driven steam exhaust type ice heat storage device according to claim 1 or 2, the ice heat storage tank may include a spray nozzle for spraying water into the ice heat storage tank in a spray form.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail with reference to the drawings, but the present invention is not limited to the following embodiments. In all the drawings, similar components are denoted by the same reference symbols and symbols. FIG. 1 and FIG. 2 are views showing one embodiment of a steam driven steam exhaust type ice heat storage device according to the present invention.

First, the configuration will be described. As shown in FIG. 1, the steam-driven steam exhaust type ice heat storage device 11 includes an ice heat storage tank 12 and a jet pump 13. The jet pump 13 includes a steam generator 14 and the ejector 1
5 and a condenser 16. Further, the ejector 15 includes an ejector body 19, a nozzle 17, and a diffuser 18. The ice heat storage tank 12 is connected to the ejector body 19 via a valve 26. The nozzle 17 is connected to the steam generator 14 and is installed in the ejector body 19 and the diffuser 18. The condenser 16 is connected to the diffuser 18, and further connected to the steam generator 14 via a pump 25 and to the ice heat storage tank 12 via a valve 27. Ejector body 19
Is equipped with a pressure gauge 24 for measuring the suction pressure by the jet pump 13.

Further, as shown in FIG.
8 includes the driving steam injected from the nozzle 17 and the ice heat storage tank 1.
A mixing section 20 for mixing the steam generated from the mixing section 2, a throat section 21 for compressing and accelerating the mixed steam, and an expanding section 2 for reducing the flow of the steam and guiding it to the condenser 16 while diffusing the steam.
2 is included. The tip 17 a of the nozzle 17 is installed at a predetermined position in the mixing section 20 of the diffuser 18.

Next, the operation will be described. First, the driving steam generated from the steam generator 14 is introduced into the nozzle 17, expanded and accelerated in the nozzle 17, flows into the diffuser 18 at a supersonic speed exceeding Mach number 1, and the high-speed flow of the driving steam flows into the ice storage. The air in the tank 12 is sucked. For this reason, the inside of the ice heat storage tank 12 is kept in a vacuum, a part of the water in the tank is evaporated below normal temperature, and the steam from the ice heat storage tank 12 is diffused by the diffuser 1.
8 and is mixed with the driving steam in the mixing section 20 of the diffuser 18. The mixed steam is in the throat 2 of the diffuser 18.
1 at a supersonic speed, generates a quasi-shock wave at the throat portion 21 and causes a sudden rise in compression. And is condensed. The condensed water is returned to the ice heat storage tank 12 via the steam generator 14 via the pump 25 and the valve 27. On the other hand, in the ice heat storage tank 12, a part of the evaporated water cools the water itself by its latent heat, and the remaining water is made into ice.

[0016]

Embodiment 1 Hereinafter, a first embodiment of a steam-driven steam exhaust type ice heat storage device according to the present invention will be described. Here, in order to determine a predetermined position of the tip portion 17a of the nozzle 17 in the mixing section 20 of the diffuser 18, the nozzle 1
The suction pressure of the ejector main body 19 at each position was measured while changing the installation position of the tip portion 17a of the seventh.

Although the apparatus shown in FIG. 1 was used for the measurement, the purpose of this measurement is to measure the suction pressure in the ejector body 19, so that ice making is not performed, and the valve 26 communicating with the ice heat storage tank 12 is closed. The measurement was carried out in the state of being placed. The measurement was performed under the following three conditions. (1) Drive steam 120 ° C (0.06 MPa), nozzle 1
7 dimensions; throat diameter 34d is 2mm, outlet diameter 35d is 8m
m, length 17L is 57mm (2) Drive steam 130 ° C (0.12MPa), nozzle 1
Dimension of 7; throat diameter 34d is 2 mm, outlet diameter 35d is 10
mm, length 17L is 57mm (3) Drive steam 140 ° C (0.17MPa), nozzle 1
Dimension of 7; throat diameter 34d is 2 mm, outlet diameter 35d is 12
In all of (1) to (3), the nozzle 17 is made of stainless steel, and the shape of the nozzle 17 is narrowed to the throat 34 and the throttle angle of the pipe 33 is gentle, as shown in FIG. A tube in which a divergent pipe 35 extending from the throat portion 34 to the injection outlet linearly expands to the injection outlet was used.

In all of (1) to (3), the diffuser 18 is made of acrylic, and as shown in FIG. 2, the enlarged end diameter 20d of the mixing section is 44 mm and the throat diameter 21d is 18 mm.
mm, enlarged end diameter 22d of the enlarged portion is 46 mm, length 18
L is 498 mm in total length, 198 mm in the mixing section, and 100 in the throat section.
mm, and the enlarged portion was 200 mm. Under the conditions of (1) to (3), the measurement was performed as follows.

As shown in FIG. 4, the tip 1 of the nozzle 17
The position of 7a is shifted from the enlarged end face 20e of the mixing section 20 of the diffuser 18 toward the reduced end face by the enlarged end face 20e.
From the position of 20mm to the position of 180mm
Fix at each position moved by 0 mm, (1) to (3)
The jet pump 13 was driven by the driving steam under the following conditions, and the suction pressure was measured by the pressure gauge 24. The result is shown in FIG.

In condition (1), the tip 17 of the nozzle 17
When the position of “a” is 20 mm from the enlarged end face 20 e of the mixing section 20 of the diffuser 18 and the inside diameter of the mixing section 20 at that position is about 41 mm, the suction pressure is about 1.3 kPa.
Further, the position of the tip 17a is shifted from the enlarged end face 20e by 20
When the mixing unit 20 is moved in the direction of the reduced end portion by mm, the suction pressure is reduced accordingly, the position of the tip portion 17a is 140 mm from the enlarged end surface 20e, and the inner diameter of the mixing portion 20 at that position is 140 mm. The suction pressure at about 26mm is about 0.30
kPa. Thereafter, when the position of the distal end portion 17a was further moved in the direction of the reduced end portion of the mixing section 20, the suction pressure increased.

From the above results, the tip 17 of the nozzle 17
It was shown that suction was performed most efficiently when the position a was 140 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18. Further, the position of the tip 17a of the nozzle 17 is set at 1 from the enlarged end face 20e of the mixing section 20 of the diffuser 18.
A suction pressure of 0.61 kPa or less was obtained between 20 mm and 180 mm, indicating that ice making was possible.

In condition (2), the tip 17 of the nozzle 17
When the position of “a” is 20 mm from the enlarged end face 20 e of the mixing section 20 of the diffuser 18 and the inner diameter of the mixing section 20 at that position is about 41 mm, the suction pressure is about 1.2 kPa.
Further, the position of the tip 17a is shifted from the enlarged end face 20e by 20
When the mixing unit 20 is moved in the direction of the reduced end by mm, the suction pressure decreases accordingly, the position of the tip 17a is 120 mm from the enlarged end surface 20e, and the inner diameter of the mixing unit 20 at that position is The suction pressure at about 28mm is about 0.30
kPa. Thereafter, when the position of the distal end portion 17a was further moved in the direction of the reduced end portion of the mixing section 20, the suction pressure increased.

From the above results, the tip 17 of the nozzle 17
It was shown that suction was performed most efficiently when the position a was 120 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18. Further, the position of the tip 17a of the nozzle 17 is 8 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18.
A suction pressure of 0.61 kPa or less was obtained between 0 mm and 180 mm, indicating that ice making was possible.

In condition (3), the tip 17 of the nozzle 17
When the position a was 20 mm from the enlarged end face 20 e of the mixing section 20 of the diffuser 18 and the inside diameter of the mixing section 20 at that position was 40 mm, the suction pressure was about 1.0 kPa. Further, the position of the distal end portion 17a is set at 20 m from the enlarged end surface 20e.
When the mixing unit 20 is moved in the direction of the reduced end by m, the suction pressure decreases accordingly, the position of the tip 17a is 100 mm from the enlarged end surface 20e, and the inside diameter of the mixing unit 20 at that position is The suction pressure at about 31 mm is about 0.27
kPa. Thereafter, when the position of the distal end portion 17a was further moved in the direction of the reduced end portion of the mixing section 20, the suction pressure increased.

From the above results, the tip 17 of the nozzle 17
It was shown that suction was performed most efficiently when the position a was 100 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18. Further, the position of the tip 17a of the nozzle 17 is 8 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18.
A suction pressure of 0.61 kPa or less was obtained between 0 mm and 180 mm, indicating that ice making was possible.

FIG. 5 shows that the position of the tip 17a of the nozzle in the mixing section of the diffuser depends on the position of the ejector main body 1a.
It was found that the suction pressure in 9 changed. In addition, the nozzle 17 that sucks the most efficiently depends on the difference in the driving steam pressure.
It is also shown that the installation location of the tip portion 17a is different. As described above, the tip portion 17a of the nozzle depends on the driving steam pressure.
Is fixed in the diffuser mixing section 20 at a position showing an efficient suction capacity, a suction pressure of 0.61 kPa or less can be obtained even when low-pressure steam of 0.17 MPa or less is used, and ice making can be performed. Indicated.

[0027]

Embodiment 2 Hereinafter, a second embodiment of the steam-driven steam exhaust type ice heat storage device according to the present invention will be described. Ice making was actually performed in an ice heat storage tank using the apparatus shown in FIG. One unit of columnar water-absorbing polymer gel (not shown) (manufactured by Nippon Shokubai Co., Ltd .: Aquaric CA-H3) was placed in a 40-liter ice heat storage tank 12 with a diameter of 30 mm and a length of 35 m.
m was placed horizontally at 5 mm intervals and filled up to 20 liters (filling rate 52%). Further, a thermocouple (not shown) was inserted into the gel layer in order to confirm that the water-absorbing polymer gel was made into ice.

The water-absorbing polymer gel in this embodiment uses a crosslinked product of sodium polyacrylate. In addition, starch-based, cellulose-based, and synthetic polymer-based (for example, other polyacrylate-based, polyvinyl alcohol-based) ,
Polyacrylamide-based, polyoxyethylene-based, etc.) can be appropriately selected and used from known materials of water-absorbing polymer gels, such as powder, sheet or fiber. There may be.

An ice heat storage tank 1 using a water-absorbing polymer gel
2 may be the ice heat storage tank 37 shown in FIG. The ice heat storage tank 37 is provided with a spray nozzle 3 for spraying water in a spray form.
8 is provided in the ice heat storage tank 37, and water 39 is sprayed in a spray form to increase the evaporation area of water. Therefore, the water 40 accumulated in the ice heat storage tank 37 is cooled by the latent heat of the evaporated water, and is stored as ice in the tank.

Similarly, various methods for increasing the water evaporation area can be used. nozzle,
A diffuser having the same shape as that of Example 1 was used.
The nozzle 17 is a stainless steel nozzle. As shown in FIG. 3, the throat diameter 34d is 2 mm, and the outlet diameter 35d is 12 m.
m and length 17L were 57 mm. The shape of the nozzle can be variously changed as needed.

The diffuser 18 is made of acrylic and has an enlarged end diameter 20d of the mixing section 20 of 44 mm as shown in FIG.
Throat diameter 21d is 18mm, enlarged end diameter 2 of enlarged part 22
2d was 46 mm and length 18L was 498 mm. The tip 17a of the nozzle 17 is fixed to a position where the air in the ice heat storage tank in the mixing unit 20 of the diffuser 18 obtained in advance by measurement is sucked most efficiently. Here is about 140
5C obtained from the measurement of Example 1, the tip position of the nozzle was 100 mm from the enlarged end face 20e of the mixing section 20 of the diffuser 18 because the driving steam of 0 ° C. (0.17 MPa) was used. In the position, it was installed at a point where the inside diameter of the diffuser 18 at that point was about 31 mm.

The tip of the nozzle can be installed at a position where the ice heat storage tank is efficiently sucked according to the pressure of each driving steam. Next, from the steam generator 14 at about 140 ° C., 0.1
A driving steam of 7 MPa was generated. With the pressure gauge 24,
As a result of measuring the suction pressure of the ejector main body 19, the suction pressure capable of making ice was maintained at about 0.6 kPa or less, and the temperature of the thermocouple inserted into the gel layer became -3 ° C. It was confirmed that ice making was completed in 185 minutes.

It is also possible to connect the ejector with steam that is generated in a refuse treatment plant or the like as driving steam and is wasted in the environment, and introduces the steam into a nozzle.

[0034]

According to the first aspect of the present invention, the tip of the steam injection nozzle of the ejector is disposed at an appropriate position in the mixing section of the diffuser in accordance with the driving steam pressure introduced into the nozzle. Since the suction capacity of the jet pump is improved and the ice heat storage tank is efficiently held in vacuum, ice can be produced.

According to the second aspect of the present invention, the driving steam introduced from the steam generator to the nozzle is 0.294.
Since it has a pressure of MPa or less, energy can be saved by using steam that is generated at a refuse treatment plant or the like as driving steam and is wasted in the environment. According to the third and fourth aspects of the present invention, since the evaporation area of the water introduced into the ice heat storage tank can be increased, the ice making can be performed more efficiently.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram showing one embodiment of a steam driven steam exhaust type ice heat storage device according to the present invention.

FIG. 2 is a schematic configuration diagram showing one embodiment of an ejector constituting a part of the steam driven steam exhaust type ice heat storage device shown in FIG.

FIG. 3 is an enlarged sectional view of the nozzle shown in FIG. 2;

FIG. 4 is an enlarged cross-sectional view showing the positions of the tips of the diffuser and the nozzle in the embodiment of the present invention.

FIG. 5 is a graph showing a change in suction pressure depending on the position of the tip of the nozzle according to one embodiment.

FIG. 6 is a schematic diagram showing another embodiment of the ice heat storage tank constituting a part of the steam-driven steam exhaust type ice heat storage device shown in FIG. 1, which is different from the first embodiment.

FIG. 7 is a schematic configuration diagram of a conventional steam-driven steam exhaust type ice heat storage device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 Steam drive steam exhaust type ice heat storage device 12 Ice heat storage tank 13 Jet pump (exhaust means) 14 Steam generator 15 Ejector 16 Condenser 17 Nozzle 18 Diffuser 19 Ejector main body 20 Diffuser mixing part (first cylindrical part) 21 Diffuser Throat part (third cylindrical part) 22 Enlarged part of diffuser (second cylindrical part)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Ian Uriam Ames United Kingdom England Chesterfield Barborough Crof Cressoo Fireburn 25 (72) Inventor Ken Satoshi 1-35-8 Nihonbashi Kakigashi-cho, Chuo-ku, Tokyo Sanken Equipment Equipment Co., Ltd. (72) Inventor Kyouko Yamamoto 2-31-25 Higashicho, Koganei City, Tokyo (72) Inventor Hideo Kameyama 2-13-28 Inokashira, Mitaka City, Tokyo

Claims (4)

[Claims] 1. An ice heat storage tank for storing water and / or ice and storing heat, and an exhaust means for exhausting water vapor generated by reducing the pressure in the ice heat storage tank. Includes a steam generator that generates steam, an ejector that introduces and accelerates and injects the steam, and a condenser that condenses steam injected from the ejector, wherein the ejector is an ejector body, A steam injection nozzle partially provided in an ejector body and connected to the steam generator for injecting drive steam, and mixing the drive steam injected from the nozzle with steam generated from the ice heat storage tank; A diffuser that guides the vapor to the condenser while diffusing the vapor, wherein the diffuser is formed with an inner diameter sequentially reduced in the axial direction, and has an enlarged end at one end and a reduced end at the other end. A first cylindrical portion having the enlarged end portion connected to the ejector body, an inner diameter formed to be sequentially enlarged in the axial direction, a reduced end portion at one end, and an enlarged end portion at the other end; A second cylindrical portion having the enlarged end portion connected to the condenser; a third cylindrical portion having both ends connected to a reduced end portion of the first cylindrical portion and a reduced end portion of the second cylindrical portion; Wherein the tip of the nozzle is installed at a predetermined position between an enlarged end and a reduced end of the first cylindrical portion in accordance with the pressure of the driving steam introduced into the nozzle. Features a steam-driven steam-exhaust ice heat storage device. 2. A steam-driven steam-exhaust type ice heat storage device according to claim 1, wherein the driving steam introduced from said steam generator to said nozzle has a pressure of 0.294 MPa or less. Exhaust ice heat storage device. 3. The steam-driven steam-exhaust ice heat storage device according to claim 1, wherein the ice heat storage tank has a gel. 4. An ice heat storage device according to claim 1, wherein said ice heat storage tank includes a spray nozzle for spraying water into said ice heat storage tank. Steam driven steam exhaust type ice heat storage device.