JPH11173726A - Refrigerator for showcase - Google Patents

Abstract

PROBLEM TO BE SOLVED: To dissolve the cooling of customer's sheet in front of a showcase by simple means. SOLUTION: A refrigerator for a showcase, which performs the cooling o a showcase 4 by cold wind W cooled with an evaporator 12 or a secondary refrigerant, being equipped with a refrigeration cycle on high temperature side where primary refrigerant circulates and a freezing cycle b on low temperature side where a secondary refrigerant circulates, is so constituted as to blow out the hot wind W' heated by the air-cooled heat exchanger 15 frontward of the bottom of the showcase, arranging an air-cooled heat exchanger 15 connected in series to the upstream side of the condenser for a secondary refrigerant within the showcase 4, so as to dissolve the cooling of customer's feet in front of the showcase 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system for a showcase, and more particularly to a refrigeration system for a showcase in which the feet in front of the showcase are prevented from getting cold.

[0002]

2. Description of the Related Art As shown in FIG. 10, a general showcase is structured such that a product placed on a display shelf A is cooled by cold air W blown from above the display shelf A.

[0003]

However, in the case of the showcase having the above structure, since the front of the display shelf A is in an open state, most of the cool air W blown out from the upper part is in the display case A. The air leaks forward and stays, and a cool air zone C is formed at the feet in front of the showcase. The cold air zone C does not cause much problem in summer, but gives an unpleasant sensation that the feet of a person passing in front of the showcase cool down in seasons other than summer, especially in the middle period (for example, spring or autumn). The problem had arisen.

[0004] The present invention has been made in view of the above point, and an object of the present invention is to make it possible to eliminate cold at the front of the showcase by simple means.

[0005]

According to the first aspect of the present invention, as a means for solving the above problems, a primary refrigerant compressor 5 for compressing a primary refrigerant x, a primary refrigerant condensing liquid for condensing and liquefying the primary refrigerant x. A high-temperature side refrigeration cycle A in which a heat exchanger 6, a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x, and a primary refrigerant evaporator 8 for evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 13; A secondary refrigerant compressor 9 for compressing the refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and a secondary for decompressing the secondary refrigerant y The refrigerant pressure reducing mechanism 11 and the secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are connected to the refrigerant pipe 1.
And a low-temperature side refrigeration cycle B sequentially connected via the second cooling medium 4 and cooling the showcase 4 with the cool air W cooled by the secondary refrigerant evaporator 12. 4, an air-cooling heat exchanger 15 connected in series upstream of the secondary refrigerant condenser 10 is provided, and the hot air W 'heated by the air-cooling heat exchanger 15 is provided.
Is blown out toward the front of the bottom of the showcase 4.

With the above-described configuration, when the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15 during operation of the refrigeration system, the air-cooled heat The air passing through the exchanger 15 is heated and becomes hot air W ′, and the hot air W ′ is blown to the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '. In this case, the gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15 before being supplied to the secondary refrigerant condenser 10, so that the secondary refrigerant The cooling capacity required to condense and liquefy the secondary refrigerant y in the condenser 10 decreases, and the high-temperature side refrigeration cycle A
Capacity can be reduced.

According to the second aspect of the present invention, as a means for solving the above problems, a primary refrigerant compressor 5 for compressing the primary refrigerant x, a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, a primary refrigerant x A high-temperature side refrigeration cycle A in which a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 13. A secondary refrigerant compressor 9, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, a secondary refrigerant decompression mechanism 11 for decompressing the secondary refrigerant y, and A low-temperature side refrigeration cycle B in which a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y is sequentially connected via a refrigerant pipe 14; and the cold air W cooled by the secondary refrigerant evaporator 12 is provided. Showcase 4
In the showcase refrigeration system that cools the air, an air-cooled heat exchanger 15 connected in parallel with the secondary refrigerant condenser 10 is disposed in the showcase 4 and heated by the air-cooled heat exchanger 15. The blown hot air W ′ is blown out toward the front of the bottom of the showcase 4.

With the above-described structure, when the refrigeration apparatus is operated, a part of the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is condensed and liquefied in the air-cooled heat exchanger 15. Then, the air passing through the air-cooling heat exchanger 15 is heated to become hot air W ′, and the hot air W ′ is blown out toward the bottom front of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '. In this case, the gas refrigerant y discharged from the secondary refrigerant compressor 9 is partly condensed and liquefied in the air-cooled heat exchanger 15, and is condensed and liquefied in the secondary refrigerant condenser 10. The amount of refrigerant will decrease. Therefore, the cooling capacity required to condense and liquefy the secondary refrigerant y in the secondary refrigerant condenser 10 is reduced, and the capacity of the high-temperature side refrigeration cycle A can be reduced.

According to the third aspect of the present invention, as means for solving the above problems, a primary refrigerant compressor 5 for compressing the primary refrigerant x, a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, a primary refrigerant x A high-temperature side refrigeration cycle A in which a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 13. A secondary refrigerant compressor 9, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, a secondary refrigerant decompression mechanism 11 for decompressing the secondary refrigerant y, and A low-temperature side refrigeration cycle B in which a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y is sequentially connected via a refrigerant pipe 14; and the cold air W cooled by the secondary refrigerant evaporator 12 is provided. Showcase 4
In the showcase refrigeration system, an air-cooling heat exchanger 15 connected in series upstream of the primary refrigerant decompression mechanism 7 is disposed in the showcase 4. The hot air W ′ heated by the above is blown out to the front of the bottom of the showcase 4.

With the above configuration, during operation of the refrigeration system, the relatively high-temperature liquid refrigerant x discharged from the primary refrigerant compressor 5 and condensed and liquefied by the primary refrigerant condenser 6 Is cooled by the air-cooled heat exchanger 15, the air passing through the air-cooled heat exchanger 15 is heated to generate hot air W ′.
And the warm air W 'is blown to the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '.
In this case, since the air-cooled heat exchanger 15 functions as a subcooler in the high-temperature side refrigeration cycle A, the capacity of the primary refrigerant condenser 6 can be reduced.

In order to solve the above-mentioned problems, the invention of claim 4 includes a primary refrigerant compressor 5 for compressing the primary refrigerant x, a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, a primary refrigerant x A high-temperature side refrigeration cycle A in which a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 13. A secondary refrigerant compressor 9, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, a secondary refrigerant decompression mechanism 11 for decompressing the secondary refrigerant y, and A low-temperature side refrigeration cycle B in which a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y is sequentially connected via a refrigerant pipe 14; and the cold air W cooled by the secondary refrigerant evaporator 12 is provided. Showcase 4
In the showcase refrigeration system, the inner tube 24 forming the primary refrigerant evaporator 8 and the outer tube 25 forming the secondary refrigerant condenser 10 are provided in the showcase 4.
And a cooling fan 26 for cooling the finned double-tube heat exchanger 3. The finned double-tube heat exchanger 3 The hot air W ′ heated by the above is blown out to the front of the bottom of the showcase 4.

With the above configuration, during operation of the refrigeration system, the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is supplied to the outer tube of the finned double-tube heat exchanger 3. When the condensed liquid is condensed and liquefied in the secondary refrigerant condenser 10, the air passing through the finned double-tube heat exchanger 3 is heated to become hot air W ', which is then turned into a showcase. 4 is blown out to the front of the bottom. Therefore, showcase 4
Is heated by the hot air W '. In this case, the gas refrigerant y supplied to the finned double tube heat exchanger 3 is cooled by the air passing through the inner tube 24 and the surface of the outer tube 25 constituting the primary refrigerant evaporator 8. Therefore, the cooling capacity of the high-temperature side refrigeration cycle A can be reduced.

In a fifth basic configuration of the present invention (invention of claim 5), as a means for solving the above-mentioned problems, a compressor 5, a condenser 6, a pressure reducing mechanism 7, and an evaporator 8 are connected to a refrigerant pipe 13. A refrigeration cycle A sequentially connected through
In the showcase refrigeration system for cooling the showcase 4 with the cool air W cooled by the evaporator 8, an air-cooled heat exchanger 15 connected to the high pressure side of the refrigeration cycle A is provided in the showcase 4. The hot air W ′ heated by the air-cooling heat exchanger 15 is blown out to the front of the bottom of the showcase 4.

With the above configuration, during operation of the refrigeration system, the high-temperature discharge gas refrigerant x discharged from the compressor 5 or the relatively high-temperature liquid refrigerant x condensed and liquefied by the condenser 6 When the air is cooled by the air-cooling heat exchanger 15, the air passing through the air-cooling heat exchanger 15 is heated to become hot air W ', and the hot air W' is blown out toward the bottom front of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '. In this case, the capacity of the condenser 6 can be reduced because the air-cooled heat exchanger 15 functions as a subcooler in the refrigeration cycle A.

In a sixth basic configuration of the present invention (invention of claim 6), as means for solving the above problems, the compressor 5, the air-cooled condenser 6, the pressure reducing mechanism 7, and the evaporator 8 are connected to the refrigerant pipe 13 And a refrigeration cycle A sequentially connected through the
The air-cooled condenser 6 is disposed in the showcase 4, and at least a part of the hot air W ′ heated by the air-cooled condenser 6 is disposed in the showcase 4. So that it blows out to the front of the bottom.

With the above arrangement, when the high-temperature discharge gas refrigerant x discharged from the compressor 5 is condensed and liquefied by the air-cooled condenser 6 during operation of the refrigeration system, the air-cooled condenser 6 Is heated to become warm air W ′, and at least a part of the warm air W ′ is blown out toward the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '. In this case, a part of the warm air W 'is blown out to the front of the bottom of the showcase 4 via a duct or the like.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

First Embodiment (corresponding to claim 1) FIGS. 1 and 2 show a refrigeration apparatus for a showcase according to a first embodiment of the present invention.

As shown in FIG. 1, the showcase refrigeration system comprises a primary refrigerant compressor 5 for compressing a primary refrigerant x.
Primary refrigerant condenser 6 for condensing and liquefying primary refrigerant x, primary refrigerant decompression mechanism 7 for decompressing primary refrigerant x, and primary refrigerant x
High-temperature side refrigeration cycle A in which a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant is sequentially connected through a refrigerant pipe 13, a secondary refrigerant compressor 9 for compressing a secondary refrigerant y, the primary refrigerant evaporator 8, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the secondary refrigerant y, a secondary refrigerant decompression mechanism 11 for decompressing the secondary refrigerant y, and a secondary refrigerant evaporation for evaporating the secondary refrigerant y. And a low-temperature side refrigeration cycle B in which units 12 are sequentially connected via a refrigerant pipe 14. The primary refrigerant evaporator 8 and the secondary refrigerant condenser 9 are disposed in the cascade heat exchanger 3 so that they can exchange heat with each other. An air-cooled heat exchanger 15 is arranged in series with the secondary refrigerant condenser 10 on the upstream side of the cascade heat exchanger 3 in the low-temperature side refrigeration cycle B. Reference numeral 16 denotes a fan for feeding air to the secondary refrigerant evaporator 12, and reference numeral 17 denotes a cooling fan for sending air to the air-cooling heat exchanger 15.

The primary refrigerant compressor 5 and the primary refrigerant condenser 6 are arranged in the outdoor unit 1, and the primary refrigerant decompression mechanism 7, the primary refrigerant evaporator 8, and the secondary refrigerant compressor 9 , An air-cooled heat exchanger 15, a secondary refrigerant condenser 10,
The secondary refrigerant pressure reducing mechanism 11 and the secondary refrigerant evaporator 12 are arranged in the showcase 4.

As shown in FIG. 2, the showcase 4 includes a display shelf 18 and a cool air circulation path 19, and a compressor 9 for the secondary refrigerant, a cascade heat exchanger 3
A machine room 20 for disposing the air-cooled heat exchanger 15 is formed. The cooling air circulation path 19 is provided with a cooling fan 16 and a secondary refrigerant evaporator 12. Then, the hot air W ′ heated by passing through the air-cooling heat exchanger 15 is blown out to a front foot of the showcase 4 from a hot air outlet 23 formed in the front of the machine room 20. ing. Reference numeral 21 denotes a cool air inlet, and reference numeral 22 denotes a cool air outlet.

The refrigeration system for a showcase constructed as described above operates as follows.

The primary refrigerant (high-temperature gas refrigerant) x fed from the primary refrigerant compressor 5 is supplied to a primary refrigerant condenser 6 as shown by a solid arrow in FIG. 1, where it is condensed and liquefied. The pressure is reduced by the primary refrigerant pressure reducing mechanism 7, evaporated and vaporized by the primary refrigerant evaporator 8, and returned to the primary refrigerant compressor 5.

On the other hand, the secondary refrigerant (high-temperature gas refrigerant) y pumped from the secondary refrigerant compressor 9 is pumped from the cooling fan 17 in the air-cooled heat exchanger 15 as shown by the solid arrows in FIG. After being condensed and liquefied by heat exchange with the primary refrigerant evaporator 8 in the secondary refrigerant condenser 10, the pressure is reduced by the secondary refrigerant decompression mechanism 11, and the secondary refrigerant evaporator is cooled. It is evaporated and vaporized in 12 and returned to the secondary refrigerant compressor 9. Therefore, the primary refrigerant evaporator 8
The secondary refrigerant y whose temperature has been lowered by heat exchange with the evaporator 12 evaporates and evaporates in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved.

By the way, as already described in the section of the prior art, most of the cool air W blown out from the cool air outlet 22 of the showcase 4 leaks to the front of the showcase 4 and the front feet of the showcase 4 In the present embodiment, when the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15, the air-cooled heat exchanger C is formed. The air passing through 15 is heated to become hot air W ′, and the hot air W ′ is blown out toward the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W ', and the cooling of the foot due to the cool air region C is eliminated.

In this case, the gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15 before being supplied to the secondary refrigerant condenser 10. The cooling capacity required to condense and liquefy the secondary refrigerant y in the secondary refrigerant condenser 10 is reduced, and the capacity of the high-temperature side refrigeration cycle A can be reduced.

The capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to a minimum value at which the temperature and the volume of the hot air W 'required to warm the front of the bottom of the showcase 4 can be secured. Further, the condenser 6 for the primary refrigerant includes:
An air-cooled type or a water-cooled type may be used. The air cooling fan 17
Is shut down in the summer, preferably in the middle (for example,
It is operated only during spring and autumn.

Second Embodiment (corresponding to claim 2) FIG. 3 shows a refrigeration system for a showcase according to a second embodiment of the present invention.

In this case, the machine room 2 at the bottom of the showcase 4
0 is provided with an air-cooled heat exchanger 15 connected in parallel with the secondary refrigerant condenser 10 in the low-temperature side refrigeration unit B. Other configurations are the same as those in the first embodiment, and a description thereof will be omitted.

The showcase refrigeration system configured as described above operates as follows.

The primary refrigerant (high-temperature gas refrigerant) x fed from the primary refrigerant compressor 5 is supplied to a primary refrigerant condenser 6 as shown by a solid line arrow in FIG. 3, where it is condensed and liquefied. The pressure is reduced by the primary refrigerant pressure reducing mechanism 7, evaporated and vaporized by the primary refrigerant evaporator 8, and returned to the primary refrigerant compressor 5.

On the other hand, a part of the secondary refrigerant (high-temperature gas refrigerant) y fed from the secondary refrigerant compressor 9 by a cooling fan in the air-cooled heat exchanger 15 as shown by a solid line arrow in FIG. At the same time as being condensed and liquefied by the air pumped from 17, the remaining gas refrigerant y is condensed and liquefied by heat exchange with the primary refrigerant evaporator 8 in the secondary refrigerant condenser 10, and then condensed and liquefied. The pressure is reduced by the pressure reducing mechanism 11, evaporated and vaporized by the secondary refrigerant evaporator 12, and returned to the secondary refrigerant compressor 9. Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be.

In this embodiment, when a part of the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is condensed in the air-cooled heat exchanger 15, the air-cooled heat exchanger 15
Is heated to become warm air W ′, and the warm air W ′ is blown out toward the bottom front of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W ', and the cooling of the foot due to the cool air region C is eliminated.

In this case, a part of the gas refrigerant y discharged from the secondary refrigerant compressor 9 is condensed and liquefied in the air-cooled heat exchanger 15, and condensed and liquefied in the secondary refrigerant condenser 10. As a result, the cooling capacity of the high-temperature side refrigeration cycle A can be reduced.

Incidentally, the capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to the minimum which can ensure the temperature and the volume of the hot air W 'required for warming the front front of the bottom of the showcase 4. Further, the condenser 6 for the primary refrigerant includes:
An air-cooled type or a water-cooled type may be used. The air cooling fan 17
Is shut down in the summer, preferably in the middle (for example,
It is operated only during spring and autumn.

Third Embodiment (corresponding to claim 3) FIG. 4 shows a refrigeration apparatus for a showcase according to a third embodiment of the present invention.

In this case, the machine room 2 at the bottom of the showcase 4
At 0, an air-cooling heat exchanger 15 connected in series upstream of the primary refrigerant pressure reducing mechanism 7 is provided. Other configurations are the same as those in the first embodiment, and a description thereof will be omitted.

The refrigeration system for a showcase constructed as described above operates as follows.

The primary refrigerant (high-temperature gas refrigerant) x fed from the primary refrigerant compressor 5 is supplied to the primary refrigerant condenser 6, where it is condensed and liquefied, as shown by the solid line arrow in FIG. After being further cooled by the cold / heat exchanger 15, the pressure is reduced by the primary refrigerant pressure reducing mechanism 7, evaporated and vaporized by the primary refrigerant evaporator 8, and returned to the primary refrigerant compressor 5.

On the other hand, the secondary refrigerant (high-temperature gas refrigerant) y fed from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant condenser 10 in the secondary refrigerant condenser 10 as shown by a solid line arrow in FIG. After being condensed and liquefied by heat exchange with the evaporator 8, the pressure is reduced by the secondary refrigerant decompression mechanism 11, then evaporated and vaporized by the secondary refrigerant evaporator 12, and returned to the secondary refrigerant compressor 9. Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be.

In the present embodiment, when the relatively high-temperature liquid refrigerant x condensed and liquefied in the primary refrigerant condenser 6 is cooled by the air-cooled heat exchanger 15, the air-cooled heat exchanger 15 The passing air is heated and becomes hot air W ′, and the hot air W ′ is blown out toward the bottom front of the showcase 4. Therefore, the cold air region C formed at the bottom front of the showcase 4
Is heated by the warm air W ′. In this case, since the air-cooled heat exchanger 15 acts as a supercooler in the high-temperature side refrigeration cycle A, the primary refrigerant condenser 6
Capacity can be reduced.

Incidentally, the capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to the minimum which can secure the temperature and the volume of the hot air W 'required for warming the front of the bottom of the showcase 4. Further, the condenser 6 for the primary refrigerant includes:
An air-cooled type or a water-cooled type may be used. The air cooling fan 17
Is shut down in the summer, preferably in the middle (for example,
It is operated only during spring and autumn.

Fourth Embodiment (corresponding to claim 4) FIG. 5 shows a refrigeration apparatus for a showcase according to a fourth embodiment of the present invention.

In this case, the inner tube 24 constituting the primary refrigerant evaporator 8 and the outer tube 25 constituting the secondary refrigerant condenser 10
The cascade heat exchanger 3 is constituted by a finned double-tube heat exchanger consisting of: a cascade heat exchanger 3 and a cooling device for cooling the cascade heat exchanger 3 at the bottom of the showcase 4. A fan 26 is provided. Reference numeral 27 denotes a fin formed on the outer periphery of the outer tube 25. Then, the hot air W ′ heated when passing through the cascade heat exchanger 3 is heated by a hot air outlet 23 (see FIG. 2) formed in the front of the machine room 20 at the bottom of the showcase 4.
From the front. Other configurations are the same as those in the first embodiment, and a description thereof will be omitted.

The refrigeration system for a showcase constructed as described above operates as follows.

The primary refrigerant (high-temperature gas refrigerant) x fed from the primary refrigerant compressor 5 is supplied to a primary refrigerant condenser 6 as shown by a solid line arrow in FIG. 5, where it is condensed and liquefied. The pressure is reduced by the primary refrigerant pressure reducing mechanism 7, evaporated and vaporized by the primary refrigerant evaporator 8, and returned to the primary refrigerant compressor 5.

On the other hand, the secondary refrigerant (high-temperature gas refrigerant) y fed from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant condenser 10 in the secondary refrigerant condenser 10 as shown by a solid line arrow in FIG. After being condensed and liquefied by heat exchange with the evaporator 8, the pressure is reduced by the secondary refrigerant decompression mechanism 11, then evaporated and vaporized by the secondary refrigerant evaporator 12, and returned to the secondary refrigerant compressor 9. Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be.

In the present embodiment, the high temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is supplied to the outer tube 25 of the finned double tube heat exchanger 3 serving as a cascade heat exchanger. When condensed and liquefied in the constituent secondary refrigerant condenser 10, the air passing through the cascade heat exchanger 3 is heated to become hot air W ′, and the hot air W ′ is blown out toward the bottom front of the showcase 4. You. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W '. In this case, the gas refrigerant y supplied to the cascade heat exchanger 3 is cooled by the inner pipe 24 constituting the primary refrigerant evaporator 8 and the air passing through the surface of the outer pipe 25. The cooling capacity of the side refrigeration cycle A can be reduced.

The primary refrigerant condenser 6 may be air-cooled or water-cooled. In addition, the air-cooling fan 26 is shut down in summer, and preferably in an intermediate period (for example, in spring,
Driving only in autumn).

Fifth Embodiment (Corresponding to Claim 5) FIG. 6 shows a refrigerator for a showcase according to a fifth embodiment of the present invention.

In this case, the refrigeration system for a showcase is a unitary refrigeration system having a refrigeration cycle A in which a compressor 5, a condenser 6, a pressure reducing mechanism 7, and an evaporator 8 are sequentially connected via a refrigerant pipe 13. It is configured. The showcase 4 is provided with a cool air circulation path 19, and at the bottom thereof, a machine room 20 for disposing an air cooling heat exchanger 15 connected in series with the condenser 6 upstream of the pressure reducing mechanism 7. Are formed. The cooling air circulation path 19 is provided with a cooling fan 16 and an evaporator 8. Then, the hot air W ′ heated by passing through the air-cooled heat exchanger 15 is supplied to the machine room 2.
0 is blown out to the front foot of the showcase 4. The compressor 5 and the condenser 6 are arranged in the outdoor unit 1. Reference numeral 17 denotes a cooling fan that sends air to the air-cooled heat exchanger 15 under pressure.

The showcase refrigeration system configured as described above operates as follows.

The refrigerant (high-temperature gas refrigerant) x fed from the compressor 5 is supplied to the condenser 6 where it is condensed and liquefied, as shown by the solid line arrow in FIG. 6, and further cooled by the air-cooled heat exchanger 15. After that, the pressure is reduced by the pressure reducing mechanism 7, evaporated and vaporized by the evaporator 8, and then returned to the compressor 5. The showcase 4 is cooled by the cool air W cooled by the evaporator 8.

In this embodiment, when the relatively high-temperature liquid refrigerant x condensed and liquefied in the condenser 6 is cooled in the air-cooled heat exchanger 15, the air passing through the air-cooled heat exchanger 15 Is heated to become hot air W ′, and the hot air W ′ is blown out toward the front of the bottom of the showcase 4. Therefore, the cool air region C formed in front of the bottom of the showcase 4 is the warm air W '.
Will be warmed up. In this case, the capacity of the condenser 6 can be reduced because the air-cooled heat exchanger 15 functions as a subcooler in the refrigeration cycle A.

Incidentally, the capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to a minimum that can secure the temperature and the volume of the hot air W 'required for warming the front of the bottom of the showcase 4. Further, the condenser 6 may be an air-cooled type or a water-cooled type. The operation of the air-cooling fan 17 is stopped in the summer season, and is desirably operated only in the middle period (for example, in the spring and autumn).

In the present embodiment, the showcase refrigeration system is of a separate type having an outdoor unit, but may be of an integral type in which the entire refrigeration system is arranged in a showcase.

Sixth Embodiment (corresponding to claim 5) FIG. 7 shows a showcase refrigeration apparatus according to a sixth embodiment of the present invention.

In this case, the refrigeration system for a showcase is a unitary refrigeration system having a refrigeration cycle A in which a compressor 5, a condenser 6, a decompression mechanism 7, and an evaporator 8 are sequentially connected via a refrigerant pipe 13. It is configured. The showcase 4 is provided with a cool air circulation path 19, and at the bottom thereof, the compressor 5, an air-cooled heat exchanger 15 connected in series with the condenser 6 on the discharge side of the compressor 5, and a pressure reducing mechanism 7. A machine room 20 for arranging is provided. The cooling air circulation path 19 is provided with a cooling fan 16 and an evaporator 8. The hot air W ′ heated by passing through the air-cooled heat exchanger 15 is blown out from the front of the machine room 20 to the front foot of the showcase 4. Reference numeral 17 denotes a cooling fan that sends air to the air-cooled heat exchanger 15 under pressure.

The refrigeration system for a showcase constructed as described above operates as follows.

The high-temperature discharge gas refrigerant x sent from the compressor 5 is supplied to the air-cooled heat exchanger 1 as shown by the solid arrows in FIG.
In 5, the air is cooled by the air fed from the cooling fan 17, then condensed and liquefied in the condenser 6, then depressurized by the decompression mechanism 7, vaporized by the evaporator 8, and returned to the compressor 5. The showcase 4 is cooled by the cool air W cooled by the evaporator 8.

In the present embodiment, the high-temperature gas refrigerant x discharged from the compressor 5 is supplied to the air-cooled heat exchanger 15.
The air passing through the air-cooled heat exchanger 15 is heated when it is cooled by the cooling air, and becomes hot air W ′, and the hot air W ′ is blown out toward the bottom front of the showcase 4. Therefore, showcase 4
Is warmed by the warm air W 'formed at the front of the bottom of the airbag, and the cooling of the foot due to the cold air region C is eliminated.

In this case, the gas refrigerant x discharged from the compressor 5 is cooled by the air-cooled heat exchanger 15 before being supplied to the condenser 6, so that the refrigerant x is condensed and liquefied in the condenser 6. Cooling capacity required for
The condenser 6 can be downsized.

Incidentally, the capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to the minimum which can secure the temperature and the volume of the hot air W 'required to warm the front of the bottom of the showcase 4. Further, the condenser 6 may be an air-cooled type or a water-cooled type. The operation of the air-cooling fan 17 is stopped in the summer season, and is desirably operated only in the middle period (for example, in the spring and autumn).

Seventh Embodiment (Corresponding to Claim 5) FIG. 8 shows a refrigeration apparatus for a showcase according to a seventh embodiment of the present invention.

In this case, only the point that the air-cooled heat exchanger 15 is connected in parallel with the condenser 6 is different from the sixth embodiment, and the other configuration is the same as that of the sixth embodiment. Description is omitted.

The refrigeration system for a showcase constructed as described above operates as follows.

As shown by the solid arrows in FIG. 8, a part of the high-temperature discharged gas refrigerant x fed from the compressor 5 is condensed and liquefied by the air fed from the cooling fan 17 in the air-cooled heat exchanger 15. After the residue is condensed and liquefied in the condenser 6, the pressure is reduced by the pressure reducing mechanism 7, vaporized and vaporized in the evaporator 8, and returned to the compressor 5. The showcase 4 is cooled by the cool air W cooled by the evaporator 8.

In the present embodiment, when a part of the high-temperature gas refrigerant x discharged from the compressor 5 is condensed and liquefied in the air-cooled heat exchanger 15, the air passing through the air-cooled heat exchanger 15 The hot air W 'is heated, and the hot air W' is blown toward the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W ', and the cooling of the foot due to the cool air region C is eliminated.

In this case, since a part of the gas refrigerant x discharged from the compressor 5 is cooled by the air-cooled heat exchanger 15, the cooling capacity required to condense and liquefy the refrigerant x in the condenser 6 is reduced. As a result, the size of the condenser 6 can be reduced.

Note that the capacity of the air-cooling heat exchanger 15 and the air volume of the cooling fan 17 are set to a minimum value at which the temperature and the volume of the hot air W 'required to warm the front of the bottom of the showcase 4 can be secured. Further, the condenser 6 may be an air-cooled type or a water-cooled type. The operation of the air-cooling fan 17 is stopped in the summer season, and is desirably operated only in the middle period (for example, in the spring and autumn).

Eighth Embodiment (corresponding to claim 6) FIG. 9 shows a refrigerator for a showcase according to an eighth embodiment of the present invention.

In this case, an air-cooled condenser is used as the condenser 6 in the showcase refrigerating apparatus, and when the refrigerant x is condensed and liquefied in the air-cooled condenser 6, the refrigerant x is fed to the air-cooled condenser 6 by the cooling fan 27. The heated air is heated to become hot air W ′, and a part of the hot air W ′ is blown toward the front of the bottom of the showcase 4. In addition,
The air-cooled heat exchanger 15 is omitted. The other configuration is the same as that of the sixth embodiment, and the description is omitted.

The refrigeration system for a showcase constructed as described above operates as follows.

The high-temperature discharge gas refrigerant x fed from the compressor 5 is condensed and liquefied in the air-cooled condenser 6 as shown by solid arrows in FIG. It is vaporized and returned to the compressor 5. The showcase 4 is cooled by the cool air W cooled by the evaporator 8.

In the present embodiment, when the high-temperature gas refrigerant x discharged from the compressor 5 is condensed and liquefied by the air-cooled condenser 6, the air passing through the air-cooled condenser 6 is heated and heated. The wind W ′ is blown, and the warm wind W ′ is blown toward the front of the bottom of the showcase 4. Therefore, the cool air region C formed at the front of the bottom of the showcase 4 is heated by the warm air W ', and the cooling of the foot due to the cool air region C is eliminated.

In the case of this embodiment, the air-cooled condenser 6
Is required to condense and liquefy an amount of refrigerant sufficient to secure the refrigeration capacity, so that the entire amount of hot air W ′ heated through the air-cooled condenser 6 is supplied to the showcase 4. If the air blows out to the front of the bottom, there is a possibility that a problem that the air becomes too warm may occur. Therefore, most of the warm air W 'is blown to the rear side of the showcase 4 and a part of the warm air W' is ducted (not shown). The front part of the bottom of the showcase 4 is guided to the front.

[0077]

According to the first aspect of the present invention, when the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15, it passes through the air-cooled heat exchanger 15. The air to be heated is heated and becomes hot air W 'and blows out to the front front of the bottom of the showcase 4, so that the cool air region C formed at the front front of the bottom of the showcase 4 is heated by the hot air W'. Thus, there is an excellent effect that the cooling of the foot due to the cold air region C can be eliminated by a simple means of providing the air-cooling heat exchanger 15.

Further, in this case, the gas refrigerant y discharged from the secondary refrigerant compressor 9 is cooled by the air-cooled heat exchanger 15 before being supplied to the secondary refrigerant condenser 10. In addition, the amount of the refrigerant condensed and liquefied in the secondary refrigerant condenser 10 is reduced, and there is also an effect that the cooling capacity of the high-temperature side refrigeration cycle A can be reduced.

According to the second aspect of the present invention, when a part of the high-temperature gas refrigerant y discharged from the secondary refrigerant compressor 9 is condensed in the air-cooled heat exchanger 15, the air-cooled heat exchanger 15 The passing air is heated and becomes warm air W 'and blows out to the front of the bottom of the showcase 4, so that the cool air region C formed at the front of the bottom of the showcase 4 is warmed by the warm air W'. Thus, there is an excellent effect that the cooling of the foot due to the cold air region C can be eliminated by a simple means of providing the air-cooled heat exchanger 15.

Further, in this case, a part of the gas refrigerant y discharged from the secondary refrigerant compressor 9 is condensed and liquefied in the air-cooled heat exchanger 15, so that the secondary refrigerant condenser 10
As a result, the amount of refrigerant condensed and liquefied is reduced, and the cooling capacity of the high-temperature side refrigeration cycle A can be reduced.

According to the third aspect of the present invention, when the relatively high-temperature liquid refrigerant x condensed and liquefied in the primary refrigerant condenser 6 is cooled by the air-cooled heat exchanger 15, the air-cooled heat exchanger 15 The passing air is heated and becomes warm air W 'and blows out to the front of the bottom of the showcase 4, so that the cool air region C formed at the front of the bottom of the showcase 4 is warmed by the warm air W'. Thus, there is an excellent effect that the cooling of the foot due to the cold air region C can be eliminated by a simple means of providing the air-cooled heat exchanger 15.

Further, in this case, since the air-cooled heat exchanger 15 functions as a supercooler in the high-temperature side refrigeration cycle A, the capacity of the primary refrigerant condenser 6 can be reduced.

According to the fourth aspect of the present invention, the high-temperature gas refrigerant y discharged from the secondary-refrigerant compressor 9 constitutes the outer tube 25 of the finned double-tube heat exchanger 3 for the secondary refrigerant. When condensed and liquefied in the condenser 10, the air passing through the finned double-tube heat exchanger 3 is heated to become hot air W ′ and blown out toward the bottom front of the showcase 4.
The cool air region C formed at the front of the bottom of the showcase 4 is warmed by the warm air W ', and the cooling of the foot due to the cool air region C is performed by the primary refrigerant evaporator 8 and the secondary refrigerant condenser 1.
There is an excellent effect that 0 can be eliminated by a simple means of comprising the finned double tube heat exchanger 3.

In this case, the gas refrigerant y supplied to the finned double-tube heat exchanger 3 is supplied to the primary refrigerant evaporator 8.
Is cooled by the inner tube 24 side and the air passing through the surface of the outer tube 25, so that the cooling capacity of the high-temperature side refrigeration cycle A can be reduced.

According to the fifth aspect of the present invention, the high-temperature discharged gas refrigerant x discharged from the compressor 5 or the relatively high-temperature liquid refrigerant x condensed and liquefied in the condenser 6 is supplied to the air-cooled heat exchanger 15. When cooled, the air passing through the air-cooled heat exchanger 15 is heated to become hot air W ′ and is blown out to the front of the bottom of the showcase 4.
The cold air region C formed at the front of the bottom is warmed by the warm air W ', and the cooling of the feet by the cold air region C
There is an excellent effect that the problem can be solved by a simple means of providing the air-cooling heat exchanger 15.

Further, since the air-cooled heat exchanger 15 functions as a precooler, a condenser or a supercooler in the refrigeration cycle A, the capacity of the condenser 6 can be reduced.

According to the sixth aspect of the present invention, when the high-temperature discharge gas refrigerant x discharged from the compressor 5 is condensed and liquefied in the air-cooled condenser 6, the air passing through the air-cooled condenser 6 is heated. At least partly showcase 4
, The cold air region C formed in the front front of the bottom of the showcase 4 is warmed by the warm air W ', and the cooling of the foot due to the cold air region C is used as a condenser. There is an excellent effect that the problem can be solved by a simple means of using the air-cooled condenser 6.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a first embodiment of the present invention.

FIG. 2 is a longitudinal sectional view of the showcase refrigeration apparatus according to the first embodiment of the present invention.

FIG. 3 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a second embodiment of the present invention.

FIG. 4 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a third embodiment of the present invention.

FIG. 5 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a fourth embodiment of the present invention.

FIG. 6 is a longitudinal sectional view of a showcase refrigeration apparatus according to a fifth embodiment of the present invention.

FIG. 7 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a sixth embodiment of the present invention.

FIG. 8 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to a seventh embodiment of the present invention.

FIG. 9 is a refrigerant circuit diagram of a showcase refrigeration apparatus according to an eighth embodiment of the present invention.

FIG. 10 is a perspective view of a general showcase.

[Explanation of symbols]

3 is a finned double-tube heat exchanger (cascade heat exchanger), 5 is a compressor for the primary refrigerant (compressor), 6 is a condenser for the primary refrigerant (condenser, air-cooled condenser), and 7 is a primary refrigerant. 8 is a primary refrigerant evaporator (evaporator),
9 is a compressor for secondary refrigerant, 10 is a condenser for secondary refrigerant, 11
Is a secondary refrigerant pressure reducing mechanism, 12 is a secondary refrigerant evaporator, 1
3, 14 are refrigerant pipes, 15 is an air-cooled heat exchanger, 16, 17
Is a cooling fan, 20 is a machine room, 23 is a hot air outlet, 24
Is an inner tube, 25 is an outer tube, 26 is a cooling fan, 27 is a fin, A is a high-temperature refrigeration cycle (refrigeration cycle), B is a low-temperature refrigeration cycle, C is a cold air region, W is cold air, and W 'is hot air. , X is the primary refrigerant (refrigerant), and y is the secondary refrigerant.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Yuji Fujimoto 1304 Kanaokacho, Sakai City, Osaka Prefecture Daikin Industries, Ltd. Inside the Kanaoka Plant of Sakai Seisakusho Co., Ltd. (72) Katsuhiro Nishioka 2-4 Nakazaki Nishi Kita-ku, Osaka No. 12 Umeda Center Building Daikin Industries, Ltd.

Claims (6)

[Claims] 1. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (13); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle in which a decompression mechanism (11) for a secondary refrigerant for decompressing air and an evaporator (12) for a secondary refrigerant for evaporating and evaporating the secondary refrigerant (y) are sequentially connected via a refrigerant pipe (14). (B), wherein the secondary refrigerant evaporator (12)
A refrigeration system for a showcase that cools the showcase (4) with the cool air (W) cooled at the upstream side of the condenser (10) for the secondary refrigerant in the showcase (4). An air-cooled heat exchanger (15) connected in series to
Hot air (W ') heated by the air-cooled heat exchanger (15)
Is blown out toward the front of the bottom of the showcase (4). 2. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (13); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle in which a decompression mechanism (11) for a secondary refrigerant for decompressing air and an evaporator (12) for a secondary refrigerant for evaporating and evaporating the secondary refrigerant (y) are sequentially connected via a refrigerant pipe (14). (B), wherein the secondary refrigerant evaporator (12)
A refrigeration system for a showcase that cools the showcase (4) with the cool air (W) cooled in (1), wherein the showcase (4) is provided in parallel with the secondary refrigerant condenser (10). A connected air-cooled heat exchanger (15) is provided, and the hot air (W ′) heated by the air-cooled heat exchanger (15) is blown to the bottom front of the showcase (4). A refrigeration system for a showcase, comprising: 3. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (13); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle in which a decompression mechanism (11) for a secondary refrigerant for decompressing air and an evaporator (12) for a secondary refrigerant for evaporating and evaporating the secondary refrigerant (y) are sequentially connected via a refrigerant pipe (14). (B), wherein the secondary refrigerant evaporator (12)
A showcase refrigeration system for cooling the showcase (4) with the cool air (W) cooled in the above, wherein the showcase (4) is provided upstream of the primary refrigerant pressure reducing mechanism (7). An air-cooled heat exchanger (15) connected in series,
Hot air (W ') heated by the air-cooled heat exchanger (15)
Is blown out toward the front of the bottom of the showcase (4). 4. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (13); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle in which a decompression mechanism (11) for a secondary refrigerant for decompressing air and an evaporator (12) for a secondary refrigerant for evaporating and evaporating the secondary refrigerant (y) are sequentially connected via a refrigerant pipe (14). (B), wherein the secondary refrigerant evaporator (12)
The showcase refrigeration system cools the showcase (4) with the cool air (W) cooled in the above, wherein the showcase (4) includes the evaporator (8) for the primary refrigerant. A finned double-pipe heat exchanger (3) comprising a pipe (24) and an outer pipe (25) constituting the secondary refrigerant condenser (10); and a finned double-pipe heat exchanger ( And a cooling fan (26) for cooling the hot air (W ') heated by the finned double-tube heat exchanger (3). A refrigeration apparatus for a showcase, characterized in that the refrigeration apparatus is configured to blow out the air to the refrigerator. 5. A refrigeration cycle (A) comprising a compressor (5), a condenser (6), a pressure reducing mechanism (7), and an evaporator (8) sequentially connected via a refrigerant pipe (13), Showcase (4) with cold air (W) cooled by the evaporator (8)
A refrigeration system for a showcase that cools the refrigeration cycle, wherein an air-cooled heat exchanger (15) connected to the high-pressure side of the refrigeration cycle (A) is provided in the showcase (4). A refrigeration system for a showcase, wherein the hot air (W ') heated by the cold / heat exchanger (15) is blown to the front of the bottom of the showcase (4). 6. A refrigeration cycle (A) comprising a compressor (5), an air-cooled condenser (6), a pressure reducing mechanism (7), and an evaporator (8) sequentially connected via a refrigerant pipe (13). A showcase refrigeration system for cooling a showcase (4) with cold air (W) cooled by the evaporator (8),
The air-cooled condenser (6) is disposed in the showcase (4), and at least a part of the hot air (W ′) heated by the air-cooled condenser (6) is supplied to the showcase (4). A refrigeration system for a showcase, wherein the refrigeration unit is configured to blow out to the front of the bottom.