KR20130097867A - Flash tank, refrigeration apparatus including the same, and method for operating the refrigeration apparatus - Google Patents

Flash tank, refrigeration apparatus including the same, and method for operating the refrigeration apparatus Download PDF

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Publication number
KR20130097867A
KR20130097867A KR1020120019492A KR20120019492A KR20130097867A KR 20130097867 A KR20130097867 A KR 20130097867A KR 1020120019492 A KR1020120019492 A KR 1020120019492A KR 20120019492 A KR20120019492 A KR 20120019492A KR 20130097867 A KR20130097867 A KR 20130097867A
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South Korea
Prior art keywords
refrigerant
refrigerant liquid
closed space
flash tank
liquid level
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KR1020120019492A
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Korean (ko)
Inventor
히데요 아사노
마사토 타케다
신야 카토
이와오 테라시마
아키나 츠다
Original Assignee
마에카와 매뉴팩쳐링 캄파니 리미티드
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Priority to KR1020120019492A priority Critical patent/KR20130097867A/en
Publication of KR20130097867A publication Critical patent/KR20130097867A/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/04—Refrigerant level

Abstract

PURPOSE: A flash tank, a refrigeration device with the flash tank, and a driving method of the refrigeration device are provided to improve the safety of a refrigeration device by containing the maximum amount of a coolant liquid in a low pressure flooded evaporator when the refrigeration device is not operated. CONSTITUTION: A flash tank comprises an integral housing (34) in which a first closed space (S1) functioning as an intercooler and a second closed space (S2) functioning as an economizer cooler are adjacently arranged in a horizontal direction; a first variable diaphragm to adjust the tightening level of a first refrigerant liquid pipe which transmits a refrigerant liquid from the first closed space to the second closed space; a first refrigerant surface level adjusting device to adjust the surface level of the refrigerant in the first closed space by operating the first variable diaphragm; a second variable diaphragm to adjust the tightening level of a second refrigerant liquid pipe which transmits a refrigerant liquid from the second closed space to an evaporator; and a second refrigerant surface level adjusting device to adjust the surface level of the refrigerant in the second closed space by operating the second variable diaphragm. [Reference numerals] (14) Screw type two stage compressor; (24) Fluid flow device; (26) Flash tank; (28) CO_2 liquefier; (32) Variable throttle; (56) Liquid receiver; (64) Controller; (AA) CO_2 refrigerant gas; (BB) CO_2 refrigerant liquid

Description

FLASH TANK, REFRIGERATION APPARATUS INCLUDING THE SAME, AND METHOD FOR OPERATING THE REFRIGERATION APPARATUS}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is used in a refrigeration apparatus having a two-stage compressor, and relates to a flash tank having an intermediate cooling function and an economizer function, a refrigeration apparatus having the flash tank, and a method of operating the refrigeration apparatus.

In a refrigeration apparatus in which an evaporator, a compressor, a condenser, and an expansion mechanism are formed in a refrigerant circulation path to form a refrigeration cycle, generally, when the evaporation temperature of the refrigerant is low, or when the compression ratio is 10 or more, the low stage compressor and the high stage compressor It uses two stage compression method. By using two-stage compression, the discharged refrigerant gas temperature after compression can be lowered below the allowable temperature, and COP can be improved.

In the two-stage compression type refrigeration system, in order to further improve the COP, a part of the refrigerant liquid under high pressure at the outlet side of the condenser is branched from the main refrigerant circuit and decompressed, and the temperature of the remaining refrigerant liquid is reduced by vaporization and endotherm at the pressure reduction. On the other hand, the intermediate | middle cooler which supplies the vaporized refrigerant gas to the discharge gas path of a low pressure compressor, and lowers the refrigerant gas temperature of the discharge side of a low stage compressor is used. Moreover, on the same principle, the economizer cooler which supplies vaporized refrigerant gas to the refrigerant gas area | region during compression of a low pressure compressor, and lowers the temperature of the said refrigerant gas is used.

5 and 7 of Patent Document 1, two-stage compression NH 3 using a high-low stage two-stage economizer circuit, respectively A refrigeration apparatus is disclosed. Hereinafter, the outline of these two stage compression type refrigeration apparatus is demonstrated. FIG. 5 is a refrigeration apparatus disclosed in FIG. 5 of Patent Document 1. As shown in FIG. The refrigerating device 100A includes a screw type two-stage compressor 104, a condenser 112, and an expansion, which are composed of a low stage compressor 106 and a high stage compressor 108 in a main refrigerant circuit 102 in which NH 3 refrigerant circulates. The expansion mechanism 114 which consists of a valve etc., and the evaporator 116 are provided. The screw type two-stage compressor 104 has a single axis structure in which the low pressure compressor 106 and the high pressure compressor 108 are connected in series with one shaft, and are driven by the motor 110.

The high stage economizer circuit 120 and the low stage economizer circuit 130 are provided in the main refrigerant circuit 102 between the condenser 112 and the evaporator 116. The high stage economizer circuit 118 includes a branched high stage economizer cooler 122, a branch path 124 branched from the main refrigerant circuit 102, and an expansion valve 126, and a high stage economizer cooler 122. The high stage economizer passage 128 connected to the discharge passage 102a of the low stage compressor 106 is formed.

The low stage economizer circuit 130 includes a low stage economizer cooler 132 having a vessel shape, a branch passage 134 branched from the main refrigerant circuit 102 and an expansion valve 136 is formed, and a low stage economizer having a container shape ( 132 and the low stage economizer passage 138 connected to the low stage economizer port 106a arranged in the refrigerant gas region during compression of the low stage compressor 106.

In the high stage economizer circuit 120, the refrigerant liquid branched from the main refrigerant circuit 102 in the branch path 124 is reduced in pressure through the expansion valve 126, and then flows into the high stage economizer cooler 122. A main refrigerant circuit 102 is disposed in the high stage economizer cooler 122, and the reduced pressure refrigerant absorbs heat from the high temperature and high pressure refrigerant liquid flowing through the main refrigerant circuit 102, and evaporates to form a low temperature low pressure refrigerant gas. . This refrigerant gas is sent to the intermediate port 102a via the high stage economizer passage 128 to cool the refrigerant gas discharged from the low stage compressor 106.

Similarly, the low stage economizer circuit 130 also branches from the main refrigerant circuit 102 in the branch path 134 and the refrigerant liquid depressurized by the expansion valve 136 passes through the main stage refrigerant circuit 102 in the low stage economizer cooler 132. The heat absorbed from the high temperature and high pressure refrigerant liquid flowing through the e), and evaporated to form a low temperature low pressure refrigerant gas. The refrigerant gas flows into the low stage economizer port 106a of the low stage compressor 106 via the low stage economizer passage 138 to cool the refrigerant gas during compression of the low stage compressor 106.

The refrigerant liquid flowing through the main refrigerant circuit 102 is cooled by these two stage economizer circuits 120 and 130 at the outlet side of the condenser 112, while the refrigerant gas under compression in the two stage compressor 104. In addition, it is cooled by the low temperature low pressure refrigerant gas supplied through the high stage economizer passage 128 and the low stage economizer passage 138. Thereby, while making the pressure of the refrigerant gas discharged | emitted from the two stage compressor 104 into below permissible pressure, COP can be improved.

FIG. 6 is a freezing apparatus disclosed in FIG. 7 of Patent Document 1. FIG. In the NH 3 refrigeration apparatus 100B, the configuration other than the high-low stage economizer circuits 140 and 150 is the same as that of the refrigeration apparatus 100A, and the same equipment or member is given the same reference numeral.

The high stage economizer cooler 142 of the high stage economizer circuit 140 and the low stage economizer cooler 152 of the low stage economizer circuit 150 are each comprised by the flash tank type | mold cooler which forms a container shape.

In the main refrigerant circuit 102 on the outlet side of the condenser 112, the total amount of the refrigerant liquid is reduced through the expansion valve 126, and then flows into the high stage economizer cooler 142. Under a reduced pressure atmosphere of the high stage economizer cooler 142, part of the refrigerant liquid is endothermed from the remaining refrigerant liquid, and evaporates to form a low temperature low pressure refrigerant gas. This refrigerant gas is supplied to the discharge passage 102a via the high stage economizer passage 128 to cool the refrigerant gas in the discharge passage 102a. The remaining refrigerant liquid is further depressurized by the expansion valve 136 through the conduit 102b, and then flows into the low stage economizer cooler 152.

Under the reduced pressure atmosphere of the low stage economizer cooler 152, some refrigerant liquids endotherm from the remaining refrigerant liquid, and evaporate to form a low temperature low pressure refrigerant gas. The refrigerant gas is supplied to the low stage economizer port 106a via the low stage economizer passage 138, and the low stage compressor 106 cools the refrigerant gas in the region during compression. In this way, the refrigerant liquid flowing through the main refrigerant circuit 102 is cooled by the two-stage economizer circuits 140 and 150 at the outlet side of the condenser 112, while being compressed in the two-stage compressor 104. The refrigerant gas is also cooled by the low temperature low pressure refrigerant gas supplied through the high stage economizer passage 128 and the low stage economizer passage 138. Thereby, while making the pressure of the refrigerant gas discharged | emitted from the two stage compressor 104 into below permissible pressure, COP can be improved.

Japanese Patent Laid-Open No. 2008-297996 (Figs. 5 and 7)

The NH 3 refrigeration apparatuses 100A and 100B disclosed in Patent Literature 1 are provided with two stages of high and low economizer circuits, and each of the economizer circuits requires a vessel-shaped cooler, a heat exchanger, or a piping or expansion mechanism. As a result, it is becoming a large and expensive construction.

In addition, NH 3 of the former In the refrigerating apparatus 100A, when a plate type heat exchanger is used for the economizer circuit, there are many welding points, which makes the production cumbersome and the refrigerant easily leaks. In addition, in the high stage economizer circuit 120 and the low stage economizer circuit 130, indirect heat exchange is carried out between the vaporized refrigerant gas and the refrigerant liquid flowing through the main refrigerant circuit 102. Therefore, in order to adjust the heat exchange amount, it is necessary to control the liquid supply amount of the refrigerant liquid, and the apparatus becomes large, and the operation is cumbersome.

When the low-end economizer cooler installed in the refrigerating unit is an indirect heat exchange system, the entire refrigerating unit includes a condenser and an evaporator, and four heat exchangers are required, thus requiring a large installation space and costing equipment. . In addition, since there are many pipes and many welding points, the construction period is prolonged.

This invention aims at simplifying the structure of the cooler and economizer circuit provided in the refrigeration apparatus provided with a two-stage compressor, and making manufacturing cost low in view of such a prior art subject.

Moreover, in the refrigeration apparatus provided with the two-stage compressor, it aims at improving the safety of the refrigeration apparatus after operation stop.

In order to achieve the above object, the flash tank of the present invention,

An intermediate cooler which is opened in a refrigerant circulation path between the condenser and the evaporator of the refrigerating device, vaporizes a portion of the refrigerant liquid under high pressure on the outlet side of the condenser by vaporizing it, and supplies the vaporized refrigerant gas to the intermediate port of the two stage compressor; In the flash tank used as an economizer cooler which accommodates and reduces the refrigerant liquid from an intermediate cooler, vaporizes a part thereof, and supplies the vaporized refrigerant gas to the refrigerant gas region during compression of the low stage compressor.

The first closed space used as the intermediate cooler and the second closed space used as the economizer cooler are composed of a unitary housing arranged horizontally adjacent through the partition wall,

A first variable diaphragm capable of adjusting the degree of tightening of the first refrigerant liquid pipe that sends the refrigerant liquid from the first enclosed space to the second enclosed space, and a first liquid adjustable liquid level of the first enclosed space by operating the first variable diaphragm. 1 refrigerant level adjustment mechanism,

A second variable diaphragm capable of adjusting the degree of tightening of a second refrigerant liquid pipe sending refrigerant liquid from the second closed space to the evaporator, and a second refrigerant capable of adjusting the refrigerant liquid level in the second closed space by manipulating the second variable aperture; It is provided with the liquid level adjustment mechanism.

The flash tank of the present invention simplifies the configuration by forming the first closed space having the intermediate cooling function and the second closed space having the economizer function in the housing of the integral structure, as compared with the case where they are formed in the separate housing. can do. In addition, since the plate type heat exchanger is not used, the welding location can be reduced, the manufacturing cost can be reduced, and the problem of leakage of the refrigerant can be solved. Furthermore, since the first closed space and the second closed space are disposed adjacent to each other in the horizontal direction, the influence of gravity caused by the difference in height when exchanging the refrigerant liquid between these spaces can be eliminated. It is easy to send and receive liquids.

In the apparatus of the present invention, the first variable diaphragm or the second variable diaphragm is a variable throttle provided in the inlet passage of the first refrigerant liquid pipe or the second refrigerant liquid pipe, and the first refrigerant liquid level level adjusting mechanism or the second refrigerant liquid level level adjusting mechanism is provided. (A) floating on the refrigerant liquid surface and connected via the variable throttle and a mechanical link mechanism, and operating the variable throttle by changing the vertical position according to the refrigerant liquid level, thereby adjusting the tightening degree of the first refrigerant liquid pipe or the second refrigerant liquid pipe. What is necessary is just to float.

In this way, the liquid level of the refrigerant in the first closed space or the second closed space can be automatically adjusted by the float and the variable throttle connected by the mechanical link mechanism, so that the liquid supply control by the controller provided outside is unnecessary. In addition, since there is no need to use an expensive electronic control apparatus, and it is comprised only by mechanical components, installation cost can be reduced and generation | occurrence | production of a failure can also be reduced.

In the apparatus of the present invention, the first variable diaphragm or the second variable diaphragm is a flow rate adjusting valve provided in the first refrigerant liquid pipe or the second refrigerant liquid pipe, and the first refrigerant liquid level level adjusting mechanism or the second refrigerant liquid level level adjusting mechanism includes: What is necessary is just the electronic refrigerant liquid level detection apparatus which detects a refrigerant liquid level and adjusts the opening degree of the said flow regulating valve based on this detection value.

By using such an electronic refrigerant liquid level detector, it is possible to control the refrigerant liquid level of the intermediate cooling vessel and the economizer vessel to a good degree.

The refrigeration apparatus of the present invention is a refrigeration apparatus comprising a two-stage compressor, a condenser, a decompression mechanism, and an evaporator comprising a low stage compressor and a high stage compressor in a refrigerant circulation path, and constitutes a refrigeration cycle. It is.

Therefore, the refrigerating device of the present invention can obtain the above-mentioned effect obtained by the flash tank described above, and the manufacture of the refrigerating device can be facilitated, thereby reducing the manufacturing cost.

In the refrigeration apparatus of the present invention, if a liquid distributor is provided in the refrigerant liquid pipe between the condenser and the intermediate cooling vessel, and the variable throttle and float of the above configuration are provided in the liquid distributor, the first closed space and the second closed space. good.

In this way, when a variable throttle and a float interlocked with a mechanical link mechanism are used in all of the fluidizer, the first closed space, and the second closed space, automatic liquid supply control can be performed with these devices, and the controller provided outside Supply control is unnecessary. In addition, in the liquid supply control, it is not necessary to use an expensive electronic control apparatus, and the equipment cost can be reduced, and the occurrence of a failure can also be reduced.

In the refrigerating device of the present invention, the evaporator may be a fully liquid evaporator. When the full evaporator is used for the evaporator, since only the refrigerant gas in the saturated state is supplied to the compressor side, the liquid supply control for adjusting the superheat degree using an automatic expansion valve such as a thermal expansion valve is unnecessary. Therefore, the structure of the refrigerating device can be simplified and the cost can be reduced. Therefore, in the refrigerating device of the present invention, by providing the refrigerant liquid level adjusting mechanism and the full-sized evaporator composed of the variable throttle and float, the operation control of the refrigerating device is further facilitated, and the device configuration is further simplified. The cost can be reduced.

In addition, the operation method of the present invention using the refrigerating device of the present invention having a full evaporator,

The refrigerant gas pressure of the fully evaporator is set to be near atmospheric pressure, and the refrigerant liquid is transferred from the condenser or flash tank to the fully evaporator when the refrigeration unit is stopped, and the refrigerant liquid is stored as much as possible in the fully evaporator. It was made to be.

In the method of the present invention, when the refrigeration unit is stopped, the amount of refrigerant liquid stored in the condenser or flash tank, which becomes a high-pressure atmosphere, is reduced as much as possible, and the refrigerant liquid is stored as much as possible in the fully liquid evaporator in which the gaseous phase is maintained near atmospheric pressure. Let's do it. In this way, the refrigerant liquid can be kept as large as possible in the low pressure fully-packed evaporator at the time of stopping operation, thereby improving the safety of the refrigerating device.

According to the flash tank of the present invention, a refrigerant circulation path between the condenser and the evaporator of the refrigerating device is opened, and the refrigerant liquid under high pressure at the outlet side of the condenser is received and reduced in pressure to vaporize a portion of the vaporized refrigerant gas into the intermediate port of the two-stage compressor. An intermediate cooler for supplying and a flash tank used as an economizer cooler for receiving and reducing a refrigerant liquid from the intermediate cooler to vaporize a portion thereof, and supplying the vaporized refrigerant gas to the refrigerant gas region during compression of the low stage compressor. The first closed space used as a second chamber and the second closed space used as an economizer cooler consist of a housing having a unitary structure disposed adjacent to each other in a horizontal direction via a partition wall, and refrigerant liquid is supplied from the first closed space to the second closed space. A first variable aperture capable of adjusting the tightening degree of the first refrigerant liquid pipe to be sent; A second refrigerant liquid level adjustment mechanism capable of adjusting the refrigerant liquid level in the first enclosed space by operating the aperture; and a second adjustable adjustable tightening degree of the second refrigerant liquid pipe which sends the refrigerant liquid to the evaporator from the second enclosed space. A variable diaphragm and a second refrigerant liquid level adjustment mechanism capable of adjusting the refrigerant liquid level in the second closed space by operating the second variable aperture can simplify the configuration of the flash tank, thereby reducing the manufacturing cost. Can be.

In addition, since the plate type heat exchanger is not used, there are few welding points, the construction period can be shortened, and the problem of leakage of the refrigerant can be solved. In addition, since the first closed space having the intermediate cooling function and the second closed space having the economizer function are arranged adjacent to each other in the horizontal direction, it is possible to realize a flash tank that facilitates the exchange of refrigerant liquid between these spaces.

According to the refrigerating device of the present invention, a two-stage compressor, a condenser, a decompression mechanism, and an evaporator, each of which comprises a low stage compressor and a high stage compressor, are provided in a refrigerant circulation path. It is possible to realize a refrigerating device that can achieve the above-mentioned effects.

According to the operating method of the refrigerating device of the present invention, the refrigerating device is provided with a fully-packed evaporator, sets the refrigerant gas pressure of the fully-loaded evaporator to be near atmospheric pressure, and coolant liquid is condensed or flash tank when the refrigeration device is stopped. Since the liquid is transferred from the evaporator to the full evaporator and the refrigerant liquid is stored as much as possible within the allowed evaporator, the amount of refrigerant stored in the condenser or flash tank, which becomes a high pressure atmosphere, when the refrigeration unit is stopped, is reduced. In addition, since the refrigerant liquid can be stored as much as possible in the full-flow evaporator in which the gas phase station is maintained near atmospheric pressure, the safety of the refrigerating device at the time of stopping operation can be strengthened.

1 is an overall view according to a first embodiment of a refrigeration apparatus of the present invention.
2 is a partially enlarged view of a flash tank of the refrigerating device.
It is explanatory drawing of the refrigerant | coolant liquid level level adjusting mechanism which concerns on 2nd Embodiment of the refrigeration apparatus of this invention.
4: (A) is explanatory drawing which shows the heat balance of the refrigeration apparatus as a comparative example, (B) is explanatory drawing which shows the heat balance of the refrigeration apparatus which concerns on said 1st Embodiment.
5 is a general view of a conventional two-stage compression type refrigeration apparatus.
6 is an overall view showing another configuration example of a conventional two-stage compression type refrigeration apparatus.

EMBODIMENT OF THE INVENTION Hereinafter, this invention is demonstrated in detail using embodiment shown to drawing. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the scope of the present invention only thereto unless there is a specific description.

(Embodiment 1)

A first embodiment in which the method and apparatus of the present invention is applied to an NH 3 / CO 2 refrigeration apparatus will be described based on FIGS. 1 and 2. First, FIG. 1 shows NH 3 / CO 2 according to the present embodiment. It is an overall block diagram of the refrigerating device 10. In Figure 1, NH 3 refrigerant circulates primary coolant circuit 12, the low-stage compressor (16) and screw-type two-stage compressor (14) made of a high-stage compressor 18 and a condenser 22, a liquid ryugi to ( 24, a flash tank 26, and a CO 2 liquefier 28 are established. The two stage compressor 14 has a single axis structure in which the low pressure compressor 16 and the high pressure compressor 18 are connected in series to one shaft, and are driven by the motor 20.

The cooling water pipe 23 is provided in the condenser 22, and the NH 3 refrigerant gas is cooled by the cooling water c to condense. The condensed NH 3 refrigerant liquid r is once stored in the liquidator 24 and then sent to the flash tank 26 via the refrigerant liquid pipe 12b. Inside the housing 34 of the flash tank 26, the 1st closed space s1 used as an intermediate | middle cooler, and the 2nd closed space s2 used as an economizer cooler are formed. The coolant liquid pipe 12b is connected to the bottom face of the fluidizer 24 and the flash tank 26.

Inside the fluidizer 24, a variable throttle 32 is provided in the float 30 having the refrigerant liquid level level adjustment function and the inlet passage of the refrigerant liquid pipe 12b. By the variable throttle 32, the NH 3 refrigerant liquid r passing through the refrigerant liquid pipe 12b is depressurized and sent to the first closed space s1. In the flash tank 26, the first closed space s1 and the second closed space s2 are disposed adjacent to each other in the horizontal direction with the partition wall 38 interposed therebetween.

Since the first closed space s1 is depressurized, part of the NH 3 refrigerant liquid evaporates. At this time, as ppaeateum evaporation heat from the remaining refrigerant liquid NH 3 (r), to cool the refrigerant liquid remaining NH 3. The evaporated NH 3 refrigerant gas is sent to the intermediate port 12a of the two stage compressor 14 through the cooling passage 44.

The NH 3 refrigerant gas supplied from the cooling passage 44 to the intermediate port 12a cools the NH 3 refrigerant gas after the first stage compression discharged from the low stage compressor 16. In the first closed space s1, a float 40 having a refrigerant liquid level adjustment function and a variable throttle 42 disposed in the inlet opening of the refrigerant liquid pipe 12c are provided.

The coolant liquid pipe 12c is connected to the bottom face of the end plate 36a and the second closed space s2. When the NH 3 refrigerant liquid r in the first closed space s1 flows into the refrigerant liquid pipe 12c, it is depressurized by the variable throttle 42 and sent to the second closed space s2. Since the second closed space s2 is further depressurized than the first closed space s1, part of the NH 3 refrigerant liquid r evaporates. At this time, the evaporation heat is removed from the remaining NH 3 refrigerant liquid r, and the remaining refrigerant liquid is cooled. The evaporated NH 3 refrigerant gas is sent to the low stage economizer port 16a disposed in the region during the compression of the low stage compressor 16 through the economizer passage 50. The NH 3 refrigerant gas introduced into the low stage economizer port 16a cools the NH 3 refrigerant gas during compression in the low stage compressor 16.

The NH 3 refrigerant liquid r in the second closed space s2 is sent to the CO 2 liquefier 28 through the refrigerant liquid pipe 12d connected to the end plate 36b. In the CO 2 liquefier 28, the NH 3 refrigerant liquid exchanges heat with the CO 2 refrigerant liquid sent from the CO 2 circulation path 54 as the secondary refrigerant, endothermic and evaporates. CO 2 liquefier (28), forms a vessel shaped to NH 3 refrigerant (r) is stored therein, is composed of NH 3 refrigerant liquid flooded evaporator of the heat transfer tubes are arranged in the CO 2 refrigerant gas flows.

The NH 3 refrigerant gas evaporated in the CO 2 liquefier 28 is sent to the low stage compressor 16. On the other hand, a receiver 56 is provided in the CO 2 circulation path 54. In the CO 2 circulation path 54, a CO 2 refrigerant gas, which has been worked in an air cooler of another use, for example, an air conditioner, is sent from the pipe line 58.

The CO 2 refrigerant gas sent to the receiver 56 is sent to the CO 2 liquefier 28 via the CO 2 circulation path 54 and liquefied by exchanging heat with the NH 3 refrigerant liquid in the CO 2 liquefier 28. . The CO 2 refrigerant liquid r liquefied in the CO 2 liquefier 28 returns to the receiver 56 via the CO 2 circulation path 54, and also flows into the conduit 60 and pumps 62. By the air cooler or the like. In addition, a controller 64 for controlling the operation of the refrigerating device 10 is provided. The controller 64 controls the driving of the motor 20, the pump 62, and the like to control the operation of the entire apparatus. In addition, by inputting the detection value of the refrigerant liquid level gauge 52 provided in the CO 2 liquefier 28 to the controller 64, the controller 64 controls the operation of the refrigeration device 10 in accordance with this input value. , The refrigerant liquid level of the CO 2 liquefier 28 can be controlled.

Next, the structure of the refrigerant | coolant liquid level adjustment mechanism which consists of the float 40 and the variable throttle 42 provided in the 1st closed space s1 is demonstrated by FIG. In FIG. 2, the float 40 and the variable throttle 42 are connected by a link bar 66. A pair of guides 68 are provided on the inner side surface of the first closed space s1, and the variable throttle 42 is slidably mounted in the vertical direction along the guides 68. The float 40 moves up and down in accordance with the liquid level level L of the NH 3 refrigerant liquid r, and the variable throttle 42 moves up and down with the float 40, and the inlet of the refrigerant liquid pipe 12c is moved. It is possible to change the tightening degree of the opening.

Therefore, the float 40 and the variable throttle 42 are interlocked in the up and down direction in accordance with the liquid level L, whereby the liquid level L can be maintained at the set liquid level.

The float 30 and variable throttle 32 of the liquidizer 24, and the float 46 and variable throttle 48 of the economizer container 36 are also comprised in the same structure.

The volumes of the first closed space s1 and the second closed space s2 of the flash tank 26 are set to a volume inversely proportional to the NH 3 refrigerant gas pressure in these spaces. In addition, the cross-sectional areas of the cooling passage 44 and the economizer passage 50 are set such that the flow rate of the NH 3 refrigerant gas flowing through these passages is inversely proportional to the NH 3 refrigerant gas pressure in the space. As a result, the same mass of refrigerant gas can be supplied to the compressor side per unit time from both spaces.

In such a configuration, the NH 3 refrigerant liquid under compression in the low pressure compressor 16 is cooled by NH 3 refrigerant gas sent from the economizer passage 50, and after the first stage compression through the intermediate port 12a again. The NH 3 refrigerant gas is cooled by the NH 3 refrigerant gas sent from the cooling passage 44. Therefore, the NH 3 refrigerant gas temperature after the two-stage compression can be lowered below the allowable temperature. In addition, since the NH 3 refrigerant liquid leaving the condenser 22 is cooled in the first closed space s1 and the second closed space s2 of the flash tank 26, the COP of the refrigerating device 10 can be improved. have.

In the refrigerating device 10, during operation, the liquid level adjustment of the NH 3 refrigerant liquid r in the liquidator 24, the first closed space s1, and the second closed space s2 is performed as described above. Adjusted by the mechanism. In addition, the pressure of the gaseous-phase zone inside the CO 2 liquefier 28 is maintained at a low pressure near atmospheric pressure. When the operation is stopped, the NH 3 refrigerant liquid is transferred from the liquidator 24, the first closed space s1, and the second closed space s2 to the CO 2 liquefier 28, and the CO 2 liquefier ( While measuring the NH 3 refrigerant liquid level in 28) by the level meter 52, the controller 64 controls the NH 3 refrigerant liquid so that the NH 3 refrigerant liquid level becomes the maximum allowable liquid level.

Since the flash tank 26 integrally forms the 1st closed space s1 which has an intermediate cooling function, and the 2nd closed space s2 which has an economizer function, an intermediate | middle cooler and an economizer cooler separate as usual. Compared with the case where it is manufactured by, the structure can be simplified, and the manufacturing cost can be reduced. In addition, since the plate heat exchanger is not used, it is possible to reduce welding points and the like, making manufacturing easier, shortening the construction period, and solving the leakage problem of the refrigerant.

Further, since the first closed space s1 and the second closed space s2 are disposed in the horizontal direction to eliminate the vertical difference, the NH 3 refrigerant liquid is removed from the first closed space s1 in the refrigerant liquid pipe 12c. When sending to the second closed space s2, the influence of gravity caused by the vertical difference can be eliminated, so that the transfer of the NH 3 refrigerant liquid becomes easy.

Further, the coolant liquid level adjusting mechanism of the liquid flowr 24, the first closed space s1 and the second closed space s2 is composed of a float connected with a mechanical link mechanism and a variable throttle, and according to the liquid level L By interlocking in the up and down direction, the liquid level L can be automatically maintained at the set liquid level, and there is no need to provide an expensive electronic liquid level adjustment mechanism. Therefore, the occurrence of a failure can be reduced and the equipment cost can be reduced.

Further, as described above, the volumes of the first closed space s1 and the second closed space s2 are set to a volume inversely proportional to the NH 3 refrigerant gas pressure in these spaces, while the cooling passage 44 and the economizer passage are Since the flow rate of the NH 3 refrigerant gas flowing through the 50 is set to be a flow rate inversely proportional to the NH 3 refrigerant gas pressure in both spaces, the same mass of refrigerant gas per unit time can be supplied from both spaces to the compressor side. The heat balance of the refrigerating device 10 can be maintained satisfactorily.

In addition, in the refrigerating device 10, since the CO 2 liquefier 28 is constituted by a fully liquid evaporator, even if the approach temperature between the evaporation temperature of the NH 3 refrigerant and the condensation temperature of the CO 2 refrigerant is lowered, the heat exchange efficiency Can increase. In addition, the saturated refrigerant gas is always sent to the low pressure compressor 16. Therefore, since the liquid supply control for superheat degree adjustment using an automatic expansion valve, such as a thermal expansion valve, is unnecessary, the structure of the refrigerating device 10 can be simplified and cost can be reduced. Therefore, in the refrigerating device 10, the operation control mechanism can be greatly simplified by the combination of the refrigerant liquid level adjustment mechanism composed of the variable throttle and float and the CO 2 liquefier 28 constituted by a full evaporator. The cost can be reduced.

Further, in the refrigerating apparatus (10), at the time of operation stop, NH 3 refrigerant (r) in the CO 2 liquefier (28) so that the maximum permitted liquid level, since the control by the controller 64, a liquid ryugi (24 ), The amount of NH 3 refrigerant liquid held in the first closed space s1 and the second closed space s2 can be minimized. In this way, the amount of the refrigerant liquid held in the sealed space on the high pressure side is minimized, so that the maximum amount of the refrigerant liquid is held in the CO 2 liquefier 28 whose internal gas pressure is near atmospheric pressure, thereby increasing the safety of the refrigerant liquid pipe 12. Can be.

Further, at both ends of the flash tank 26 of the present embodiment, level sensors 70 and 71 for detecting the allowable upper limit level of the coolant liquid are provided, and at the cooling passage 44 and the economizer passage 50, The solenoid valves 72 and 73 are opened. When the coolant liquid level in the flash tank 26 reaches the allowable upper limit level, the level sensor 70 or 71 detects it and inputs a detection signal to the controller 64. The controller 64 receives this detection signal and closes the solenoid valves 72 and 73.

Thereby, when the coolant liquid is smooth in the flash tank 26 for some reason, it is possible to prevent the coolant liquid from flowing into the intermediate port 12a or the low stage economizer port 16a. When the refrigerant liquid level in the flash tank 26 is lower than the allowable upper limit level, the solenoid valves 72 and 73 are opened after a certain time.

(Embodiment 2)

Next, a second embodiment of the apparatus of the present invention will be described with reference to FIG. 3. This embodiment shows another example of the refrigerant | coolant liquid level level adjustment mechanism of the liquid flow machine 24, the 1st closed space s1, or the 2nd closed space s2. 3 shows a case where the refrigerant liquid level level adjusting mechanism of the present embodiment is provided in the second closed space s2. In FIG. 3, the electronic refrigerant liquid level sensor 76 is installed in the end plate 36b of the housing 34, while the refrigerant sends the refrigerant liquid to the CO 2 liquefier 28 from the second closed space s2. The flow regulating valve 78 is provided in the liquid pipe 12d. The electronic valve opening degree variable apparatus 78a is provided in the flow regulating valve 78.

The electronic refrigerant liquid level sensor 76 detects the liquid level L of the NH 3 refrigerant liquid r stored in the second closed space s2, and operates the electronic valve opening degree variable device 78a according to the detected value. do. As a result, the liquid level L can be maintained at the set value. By using the electronic refrigerant liquid level sensor 76, the liquid level L can be controlled to a high degree.

[Example]

Next, the result of having calculated | required COP of the refrigeration apparatus 80 as a comparative example and the refrigeration apparatus 10 of the said 1st embodiment through a test is demonstrated by FIG. First, FIG. 4A shows the heat balance when the structure of the refrigeration apparatus 80 of the comparative example and the refrigerating apparatus 80 were operated. In FIG. 4A, the intermediate cooling vessel 82 and the economizer vessel 84 are provided in the outlet side main refrigerant circuit 12 of the condenser 22 from the upstream side. The intermediate cooler 82 and the economizer cooler 84 employ an indirect heat exchange method using a plate heat exchanger.

On the outlet side of the condenser 22, branch passages 86 and 88 are taken from the main refrigerant circuit 12, a variable throttle 90 is formed in the branch passage 86, and a variable throttle in the branch passage 88. (92) is established. In addition, on the downstream side of the economizer cooler 84, a variable throttle 94 is provided in the main refrigerant circuit 12. The NH 3 refrigerant liquid branched from the branch path 86 is reduced in pressure via the variable throttle 90, and is evaporated by heat exchange with the NH 3 refrigerant liquid flowing through the main refrigerant circuit 12 in the intermediate cooler 82. The vaporized NH 3 refrigerant gas is cooled to + 7 ° C and sent to the intermediate port 12a.

On the other hand, the NH 3 refrigerant liquid of the main refrigerant circuit 12 is cooled to 10 ° C in the intermediate cooler 82 to reach the economizer cooler 84. The NH 3 refrigerant liquid branched from the branch path 88 is reduced in pressure via the variable throttle 92, and is evaporated by heat exchange with the NH 3 refrigerant liquid flowing through the main refrigerant circuit 12 in the economizer cooler 84. The vaporized NH 3 refrigerant gas is cooled to -26 ° C and sent to the low stage economizer port 16a. The NH 3 refrigerant liquid of the main refrigerant circuit 12 is cooled to −22.6 ° C., further reduced in pressure through the throttle 94, and brought into the CO 2 liquefier 28 at a temperature of −35 ° C.

FIG. 4B shows a heat balance when the refrigerating device 10 of the first embodiment is operated. In the refrigeration apparatus 80, since the intercooler (82) is an indirect heat exchange method using an plate type heat exchanger, sent to the intermediate port (12a) does not go down to the temperature of the NH 3 gas refrigerant. Similarly, since the economizer cooler 84 is an indirect heat exchange method using a plate heat exchanger, the temperature of the NH 3 refrigerant gas sent to the low stage economizer port 16a is not lowered. Therefore, compared with the refrigeration apparatus 10, COP falls.

In addition, in the refrigerating device 80, since the plate type heat exchanger is used, the variable throttle 94 is used as the temperature expansion valve, and by this temperature expansion valve, the outlet side refrigerant of the CO 2 liquefier 28 is used. It is necessary to adjust the degree of superheat of the gas. At this time, as described above, since the temperature of the refrigerant liquid may not fall to the set value at the outlet side of the economizer cooler 84, there is a problem that adjustment of the thermostatic expansion valve is difficult. In addition, there is a fear of refrigerant leakage in the plate heat exchanger.

In the refrigerating device 10, as shown in the drawing, the temperature of the refrigerant liquid drops to the set value on the outlet side of the first closed space s1 and the outlet side of the second closed space s2, thereby improving COP. You can. Moreover, in this test, the COP of the refrigerating device 10 was 5.9% higher than that of the refrigerating device 80. In addition, since the refrigeration apparatus 10 does not use a plate type heat exchanger, the possibility of refrigerant leakage is low, and when the flash tank 26 is manufactured, the first closed space s1 and the second closed space s2 are used. Since this is manufactured integrally, the number of welding processes can be reduced and manufacture becomes easy. In addition, since the thermal efficiency to the flash tank 26 is better than that of the refrigerating device 80, the size of the flash tank 26 can be reduced, and thus the cost can be reduced.

[Industrial applicability]

According to the present invention, a flash tank which is used in a refrigeration apparatus having a two-stage compressor and has the functions of an intermediate cooler and an economizer cooler and has an integrated structure, can be easily manufactured and can reduce manufacturing costs.

10, 80: NH 3 / CO 2 Refrigeration unit
12, 102: main refrigerant circuit (coolant circulation path)
12a, 102a: middle port
12b, 12c, 12d: refrigerant liquid pipe
14, 104: screw-type two stage compressor
16, 106: low pressure compressor
16a, 106a: Low-end economizer port
18, 108: high pressure compressor
20, 110: motor
22, 112: condenser
23: coolant pipe
24: liquidator
26: flash tank
28: CO 2 Liquefier
30, 40, 46: float
32, 42, 48, 90, 92, 94: variable throttle
34: Housing
36a, 36b: end plates
38: partition wall
44: cooling passage
50: economizer passage
52: refrigerant level gauge
54: CO 2 circuit
56: receiver
58, 60, 102b: pipeline
62: pump
64: controller
66: Link Bar
68: guide
70, 71: level sensor
72, 73: solenoid valve
76: electronic liquid level sensor (electronic refrigerant liquid level detection device)
78: flow adjustment valve
78a: electronic valve opening variable
82: medium cooler
84: economizer circuit
86, 88, 124, 134: branch road
100A, 100B: NH 3 refrigeration unit
116: evaporator
120, 140: high-stage economizer circuit
122, 142: high stage economizer cooler
126, 136: expansion valve
128: Godan Economizer Pathway
130, 150: low stage economizer circuit
132, 152: low stage economizer cooler
138: low stage economizer passage
L: refrigerant liquid level
c: coolant
r: NH 3 refrigerant
s1: first closed space
s2: second closed space

Claims (7)

An intermediate cooler which is opened in a refrigerant circulation path between the condenser and the evaporator of the refrigerating device, vaporizes a portion of the refrigerant liquid under high pressure on the outlet side of the condenser by vaporizing it, and supplies the vaporized refrigerant gas to the intermediate port of the two stage compressor; In the flash tank used as an economizer cooler which accommodates and reduces the refrigerant liquid from an intermediate cooler, vaporizes a part thereof, and supplies the vaporized refrigerant gas to the refrigerant gas region during compression of the low stage compressor.
The first closed space used as the intermediate cooler and the second closed space used as the economizer cooler are composed of a unitary housing arranged horizontally adjacent through the partition wall,
A first variable diaphragm capable of adjusting the degree of tightening of the first refrigerant liquid pipe that sends the refrigerant liquid from the first enclosed space to the second enclosed space, and a first liquid adjustable liquid level of the first enclosed space by operating the first variable diaphragm. 1 refrigerant level adjustment mechanism,
A second variable diaphragm capable of adjusting the degree of tightening of a second refrigerant liquid pipe sending refrigerant liquid from the second closed space to the evaporator, and a second refrigerant capable of adjusting the refrigerant liquid level in the second closed space by manipulating the second variable aperture; A liquid level adjusting mechanism is provided.
Flash tank.
The method of claim 1,
The first variable aperture or the second variable aperture is a variable throttle provided in the inlet passage of the first refrigerant liquid pipe or the second refrigerant liquid pipe,
The first refrigerant liquid level adjusting mechanism or the second refrigerant liquid level adjusting mechanism floats on the refrigerant liquid level and is connected via the variable throttle and a mechanical link mechanism, and operates a variable throttle by changing the vertical position in accordance with the refrigerant liquid level. To adjust the tightness of the first refrigerant liquid pipe or the second refrigerant liquid pipe.
Flash tank.
The method of claim 1,
The first variable diaphragm or the second variable diaphragm is a flow rate adjustment valve provided in the first refrigerant liquid pipe or the second refrigerant liquid pipe,
The first refrigerant liquid level level adjusting mechanism or the second refrigerant liquid level level adjusting mechanism is an electronic refrigerant liquid level level detecting device that detects the refrigerant liquid level and adjusts the opening degree of the flow rate adjusting valve based on the detected value. doing
Flash tank.
A refrigeration apparatus comprising a two-stage compressor, a condenser, a decompression mechanism, and an evaporator comprising a low stage compressor and a high stage compressor in a refrigerant circulation path, and comprising a refrigeration cycle, wherein the flash tank according to claim 1 is provided.
Freezer.
5. The method of claim 4,
A liquidator is provided in the refrigerant liquid pipe between the condenser and the intermediate cooling vessel, and the variable throttle and float having the configuration of claim 2 are provided in the liquidator, the first closed space and the second closed space. By
Freezer.
5. The method of claim 4,
The evaporator is characterized in that the full evaporator
Freezer.
In the operating method of the refrigeration apparatus according to claim 6,
The refrigerant gas pressure of the full evaporator is set to be near atmospheric pressure, and the refrigerant liquid is transferred from the condenser or flash tank to the full evaporator when the refrigeration unit is stopped, and the refrigerant liquid is allowed to the full evaporator within the allowable limit. Characterized in that to be stored as much as possible
How to operate a refrigeration unit.
KR1020120019492A 2012-02-27 2012-02-27 Flash tank, refrigeration apparatus including the same, and method for operating the refrigeration apparatus KR20130097867A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020120019492A KR20130097867A (en) 2012-02-27 2012-02-27 Flash tank, refrigeration apparatus including the same, and method for operating the refrigeration apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020120019492A KR20130097867A (en) 2012-02-27 2012-02-27 Flash tank, refrigeration apparatus including the same, and method for operating the refrigeration apparatus

Publications (1)

Publication Number Publication Date
KR20130097867A true KR20130097867A (en) 2013-09-04

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105004106A (en) * 2014-04-25 2015-10-28 重庆美的通用制冷设备有限公司 Shell and tube heat exchanger and cold water unit with same
US10337778B2 (en) 2015-07-13 2019-07-02 Carrier Corporation Economizer component and refrigeration system thereof
CN113063234A (en) * 2019-12-31 2021-07-02 Lg电子株式会社 Multistage compression type refrigerating device
CN113063235A (en) * 2019-12-31 2021-07-02 Lg电子株式会社 Multistage compression type refrigerating device

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105004106A (en) * 2014-04-25 2015-10-28 重庆美的通用制冷设备有限公司 Shell and tube heat exchanger and cold water unit with same
US10337778B2 (en) 2015-07-13 2019-07-02 Carrier Corporation Economizer component and refrigeration system thereof
CN113063234A (en) * 2019-12-31 2021-07-02 Lg电子株式会社 Multistage compression type refrigerating device
CN113063235A (en) * 2019-12-31 2021-07-02 Lg电子株式会社 Multistage compression type refrigerating device
KR20210085935A (en) * 2019-12-31 2021-07-08 엘지전자 주식회사 Multistage compression type frozen apparatus
KR20210085936A (en) * 2019-12-31 2021-07-08 엘지전자 주식회사 Multistage compression type frozen apparatus
CN113063235B (en) * 2019-12-31 2023-04-14 Lg电子株式会社 Multi-stage compression type refrigerating device

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