CN221076808U - Refrigerating system and refrigerating equipment - Google Patents

Abstract

The utility model discloses a refrigerating system and refrigerating equipment, wherein the refrigerating system comprises a double-suction compressor, a first pipeline, a second pipeline, a third pipeline, a condenser and a heat regenerator. The double-suction compressor is provided with a first air suction port, a second air suction port and an air exhaust port, an inlet of a first pipeline is communicated with the air exhaust port, an inlet of a second pipeline is communicated with an outlet of the first pipeline, an outlet of the second pipeline is communicated with the first air suction port, an inlet of a third pipeline is communicated with an outlet of the first pipeline, an outlet of the third pipeline is communicated with the second air suction port, a condenser is arranged on the first pipeline, and a heat regenerator is used for enabling heat of refrigerant flowing out of the air exhaust port to be transferred to at least one of the first air suction port and the second air suction port, so that the energy efficiency of a refrigerating system is improved, and the cost is reduced.

Description

Refrigerating system and refrigerating equipment

Technical Field

The utility model relates to the technical field of refrigeration systems, in particular to a refrigeration system and refrigeration equipment.

Background

In the related art, a refrigerator mainly adopts a single-suction compressor with one inlet and one outlet, and at the same time, a rotor compressor only provides one compression ratio, and refrigeration and freezing of the refrigerator are controlled by switching a refrigerant flow path through an electric valve. In practice, the evaporation temperatures required for refrigeration and freezing are different, the refrigeration only requires a smaller compression ratio, while the refrigeration requires a larger compression ratio, the compressor efficiency is lower as the pressure ratio is larger, so that the refrigeration efficiency of the single suction compressor is limited, and in addition, the heat and the cold in the refrigeration system are not fully utilized, so that the refrigeration Coefficient (COP) of the refrigeration system is lower, and the energy efficiency is poorer.

Disclosure of utility model

The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides a refrigerating system, which can improve the energy efficiency of the refrigerating system, reasonably use the heat and the cold of the refrigerating system and reduce the cost.

The utility model also provides refrigeration equipment with the refrigeration system.

An embodiment of a refrigeration system according to a first aspect of the present utility model includes: the double-suction compressor is provided with a first air suction port, a second air suction port and an air discharge port; the inlet of the first pipeline is communicated with the exhaust port; the inlet of the second pipeline is communicated with the outlet of the first pipeline, and the outlet of the second pipeline is communicated with the first air suction port; a third pipeline, wherein an inlet of the third pipeline is communicated with an outlet of the first pipeline, and an outlet of the third pipeline is communicated with the second air suction port; the condenser is arranged on the first pipeline; and a regenerator for transferring heat of the refrigerant flowing out of the exhaust port to at least one of the first and second suction ports.

The refrigerating system according to the embodiment of the first aspect of the utility model has at least the following beneficial effects: by adopting the double-suction compressor, the refrigerant is split from the first pipeline to the second pipeline and the third pipeline, the first evaporator is arranged in the second pipeline, and the second evaporator is arranged in the third pipeline, so that double refrigeration is realized. Specifically, the first air suction port of the double-suction compressor maintains the compression ratio of the original compressor, and the compression ratio of the second air suction port of the double-suction compressor is reduced, so that the whole compression ratio of the double-suction compressor is reduced, the refrigeration Coefficient (COP) of the refrigeration system is improved, and the energy efficiency of the refrigeration system can be improved. In addition, the heat regenerator is arranged in the refrigerating system, the heat of the refrigerant flowing out of the exhaust port can be transferred to at least one of the first air suction port and the second air suction port by the heat regenerator, so that heat recovery is realized, the heat and the cold of the refrigerating system can be reasonably utilized, the refrigerating capacity of the refrigerating system is improved, the energy efficiency of the refrigerating system is further improved, and the cost is reduced.

According to some embodiments of the utility model, the refrigeration system comprises a first assembly and a second assembly, the first assembly is arranged on the second pipeline, the first assembly comprises a first throttling element and a first evaporator, the second assembly is arranged on the third pipeline, the second assembly comprises a second throttling element and a second evaporator, the second pipeline comprises a first section and a second section, the first section is connected with an inlet of the first throttling element, the second section is connected with an outlet of the first evaporator, the third pipeline comprises a third section and a fourth section, the third section is connected with an inlet of the second throttling element, and the fourth section is connected with an outlet of the second evaporator.

According to some embodiments of the utility model, at least one of the second and fourth sections exchanges heat with the first section through the regenerator.

According to some embodiments of the utility model, at least one of the second and fourth sections exchanges heat with the third section through the regenerator.

According to some embodiments of the utility model, at least one of the second and fourth sections exchanges heat with the first pipe through the regenerator.

According to some embodiments of the utility model, the first conduit comprises a fifth section connected to the outlet of the condenser, at least one of the second section and the fourth section exchanging heat with the fifth section through the regenerator.

According to some embodiments of the utility model, the first evaporator is a refrigerator evaporator and the second evaporator is a freezer evaporator.

According to some embodiments of the utility model, the first line is provided with a control valve connecting the second line and the third line to control the flow of refrigerant from the first line to the second line or the third line.

According to some embodiments of the utility model, the first throttling element and the second throttling element are each provided as a capillary tube.

A refrigeration appliance according to an embodiment of the second aspect of the utility model comprises a refrigeration system according to an embodiment of the first aspect.

The refrigeration apparatus according to the embodiment of the second aspect of the present utility model, due to the inclusion of the refrigeration system according to the embodiment of the first aspect, has at least the above-mentioned advantages, and will not be described in detail herein.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The utility model is further described with reference to the accompanying drawings and examples, in which:

FIG. 1 is a schematic diagram of a refrigeration system according to some embodiments of the present utility model;

FIG. 2 is a schematic diagram of a refrigeration system according to some embodiments of the utility model;

FIG. 3 is a schematic diagram of a refrigeration system according to some embodiments of the present utility model;

FIG. 4 is a schematic diagram of a refrigeration system according to some embodiments of the utility model;

FIG. 5 is a schematic diagram of a refrigeration system according to some embodiments of the present utility model;

FIG. 6 is a schematic diagram of a refrigeration system according to some embodiments of the utility model;

FIG. 7 is a schematic diagram of a refrigeration system according to some embodiments of the utility model;

Fig. 8 is a schematic diagram of a refrigeration system according to some embodiments of the utility model.

Reference numerals:

A refrigeration system 1000;

a double suction compressor 100, a first suction port 110, a second suction port 120, and a discharge port 130;

A first conduit 200, a fifth section 210;

a second conduit 300, a first section 310, a second section 320;

A third conduit 400, a third section 410, a fourth section 420;

A condenser 500;

a first throttling element 600, a first evaporator 610;

a second throttling element 700, a second evaporator 710;

Regenerator 800;

And a control valve 900.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.

Referring to fig. 1, a refrigeration system 1000 according to an embodiment of the present utility model is provided, wherein the refrigeration system 1000 includes a dual suction compressor 100, a first pipe 200, a second pipe 300, a third pipe 400, a condenser 500, a first component, a second component, and a regenerator 800. Since the refrigeration system 1000 of the present embodiment includes the double suction compressor 100, it should be noted that the double suction compressor 100 is additionally provided with the second suction port at the middle stroke of the conventional compressor, and therefore, the double suction compressor 100 has the first suction port 110 (primary suction) and the second suction port 120 (secondary suction), the primary suction maintains the compression ratio of the original compressor, and the compression ratio of the secondary suction is reduced. When the primary suction and the secondary suction are mixed, the whole compression ratio is reduced under the condition that the original compressor cylinder is unchanged, so that the refrigeration Coefficient (COP) of the refrigeration system 1000 is improved, and the system is more energy-saving. In addition, since the refrigeration system 1000 of the embodiment further includes the regenerator 800, the refrigeration system 1000 has a regenerative function, and the regenerator 800, in cooperation with the dual suction compressor 100, can fully utilize heat and cold in the system, thereby further improving the energy efficiency of the system.

Specifically, referring to fig. 1, the double suction compressor 100 further has an exhaust port 130, an inlet of the first pipe 200 communicates with the exhaust port 130, an inlet of the second pipe 300 communicates with an outlet of the first pipe 200, an outlet of the second pipe 300 communicates with the first suction port 110, an inlet of the third pipe 400 communicates with an outlet of the first pipe 200, and an outlet of the third pipe 400 communicates with the second suction port 120. Further, the condenser 500 is disposed in the first pipeline 200, the first component is disposed in the second pipeline 300, and the second component is disposed in the third pipeline 400. The first and second components may be understood as evaporation components. The first assembly includes a first throttling element 600 and a first evaporator 610, an outlet of the first throttling element 600 being in communication with an inlet of the first evaporator 610, and the second assembly includes a second throttling element 700 and a second evaporator 710, an outlet of the second throttling element 700 being in communication with an inlet of the second evaporator 710.

In the following, a description will be mainly given of the flow direction of the refrigerant and the temperature change thereof, and referring to the direction of the arrow in fig. 1, the refrigerant flows out of the double suction compressor 100 from the discharge port 130, and at this time, the refrigerant temperature is high. Then, the refrigerant enters the first line 200, and after heat dissipation from the condenser 500, the refrigerant may enter the second line 300 and the third line 400, and it may be understood that the second line 300 and the third line 400 split the refrigerant in the first line 200. In the second line 300, the refrigerant drops in temperature after passing through the first assembly; in the third line 400, the refrigerant drops in temperature after passing through the second assembly. Finally, the refrigerant enters the double suction compressor 100 through the first suction port 110 and the second suction port 120, and circulates. It is also understood that the refrigerant circulates in a counterclockwise direction, the first and second lines 200 and 300 form one refrigeration circuit, and the first and third lines 200 and 400 form another refrigeration circuit, thereby achieving dual refrigeration, and that the first, second and third lines 200, 300 and 400 are connected in parallel. Since the temperature of the refrigerant flowing out of the discharge port 130 is high and the temperature of the refrigerant passing through the first or second module is low, it is possible to consider the temperature difference using this part to make full use of the heat and cold of the system.

It will be appreciated that in some embodiments, the first evaporator 610 may be configured as a freezer evaporator for cooling the freezer compartment and the second evaporator 710 may be configured as a refrigerator evaporator for cooling the refrigerator compartment.

It should be noted that, the regenerator 800 is mainly used to transfer heat of the refrigerant flowing out from the exhaust port 130 to at least one of the first air intake port 110 and the second air intake port 120, specifically, a part of the first pipeline 200, the second pipeline 300 and the third pipeline 400 is connected to the regenerator 800, so as to realize heat exchange of each pipeline, realize heat transfer, recover heat of the refrigerant, fully utilize heat and cold in the refrigeration system 1000, and improve energy efficiency of the refrigeration system 1000 and reduce cost.

In addition, when the compressor sucks the refrigerant which is not sufficiently absorbed and evaporated, a liquid impact phenomenon is generated, and the liquid impact phenomenon mainly means that: insufficient endothermic evaporation of the refrigerant flowing out of the evaporator can lead to liquid refrigerant being doped therein, and the liquid refrigerant can generate a large impact force after entering the compressor to be compressed, damage internal parts of the compressor, and seriously cause structural fracture of the internal parts.

Based on this, in this embodiment, by providing the regenerator 800, the regenerator 800 transfers the heat of the refrigerant flowing out from the exhaust port 130 to at least one of the first air intake port 110 and the second air intake port 120, so that the temperature of the refrigerant before entering the first air intake port 110 or the second air intake port 120 is increased, wherein the liquid refrigerant is fully evaporated into a gaseous state, and the content of the liquid refrigerant can be reduced, thereby reducing the above-mentioned risk of liquid impact.

It will be appreciated that referring to fig. 1, in some embodiments, the second conduit 300 includes a first section 310 and a second section 320, with the first component being located between the first section 310 and the second section 320. The first section 310 may be understood as a first half of the second duct 300, and the second section 320 may be understood as a second half of the second duct 300, specifically, the first section 310 communicates with the inlet of the first throttling element 600 and the outlet of the first duct 200, and the second section 320 communicates with the first suction port 110 and the outlet of the first evaporator 610. The refrigerant passes through the first stage 310, the first throttling element 600 and the first evaporator 610 in this order, and then passes through the second stage 320, and the temperature of the refrigerant in the first stage 310 is greater than the temperature of the refrigerant in the second stage 320 due to the evaporation of the refrigerant in the first evaporator 610. The third conduit 400 includes a third section 410 and a fourth section 420, the second component being located between the third section 410 and the fourth section 420, the third section 410 being understood to be the first half of the third conduit 400 and the second section 320 being understood to be the second half of the third conduit 400. Specifically, the third section 410 communicates with the inlet of the second throttling element 700 and the outlet of the first conduit 200, and the fourth section 420 communicates with the second suction port 120 and the outlet of the second evaporator 710. The refrigerant sequentially passes through the third stage 410, the second throttling element 700 and the second evaporator 710, and then passes through the fourth stage 420, and the temperature of the refrigerant in the third stage 410 is higher than that of the refrigerant in the fourth stage 420 due to the evaporation of the refrigerant in the second evaporator 710.

Various ways of connecting regenerator 800 are described in detail below. It will be appreciated that the temperature of the refrigerant in the first section 310 is greater than the temperature of the refrigerant in the second section 320 and the fourth section 420, respectively, as the refrigerant in both the second section 320 and the fourth section 420 are vaporized by the evaporator. Based on this, it is contemplated that the temperature differential of this portion can be utilized and, in some embodiments, at least one of the second and fourth sections 320, 420 exchanges heat with the first section 310 through the regenerator 800, as shown with reference to fig. 1 and 8.

Specifically, referring to fig. 1, the fourth section 420 and the first section 310 are connected to the regenerator 800, and the fourth section 420 exchanges heat with the first section 310 through the regenerator 800, so that the temperature of the refrigerant before flowing into the first throttling element 600 can be reduced, the refrigerant can be fully evaporated and absorb heat, the evaporation temperature of the refrigerant is further reduced, the refrigerating capacity is improved, and a lower freezing temperature is realized. Also, the temperature of the refrigerant flowing out of the second evaporator 710 may be increased, and the risk of condensation or frost formation at the second suction port 120 may be reduced. In the test experiments of the present embodiment, the R600a refrigerant is used as the refrigerant, the refrigeration system 1000 is at the ambient temperature of 32 ℃, the refrigeration system 1000 receives the refrigeration and freezing refrigeration requests at the same time, and the test results: without the regenerator 800, the temperature of the refrigerating chamber is 4 ℃ and the temperature of the freezing chamber is-34 ℃; in the case where the above-described regenerator 800 is provided, the temperature of the refrigerating chamber is 4 c, the temperature of the freezing chamber is-41 c, and the temperature of the freezing chamber is reduced by 6 c and lower than in the case where the above-described regenerator 800 is not provided. In summary, after the regenerator 800 is added in this embodiment, the overall effect is better, the refrigerating capacity and energy efficiency of the refrigerating system 1000 are improved, the cost can be reduced, the temperature of the freezing chamber is lower, and the deep cooling effect can be achieved. Cryogenic cooling generally refers to a temperature range from 233K (about-40 ℃) to 77K (about-196 ℃).

Referring to fig. 1, in the present embodiment, by providing the regenerator 800 to exchange heat between the fourth stage 420 and the first stage 310, the temperature of the refrigerant in the fourth stage 420 can be increased, so that the refrigerant in the fourth stage 420 can absorb heat and evaporate sufficiently, and the humidity of the refrigerant sucked by the dual suction compressor 100 is reduced, thereby reducing the risk of liquid impact of the dual suction compressor 100.

Alternatively, referring to fig. 8, the second stage 320 and the first stage 310 may be connected to the regenerator 800, and the second stage 320 exchanges heat with the first stage 310 through the regenerator 800, so that the temperature of the refrigerant before flowing into the first throttling element 600 may be reduced, and the refrigerant may absorb heat sufficiently to evaporate, so as to further reduce the evaporation temperature of the refrigerant, increase the refrigerating capacity, and realize a lower freezing temperature. Also, the temperature of the refrigerant flowing out of the first evaporator 610 may be increased, and the risk of condensation or frosting of the return air at the first suction port 110 may be reduced.

In some embodiments, referring to fig. 8, the second section 320 may exchange heat with the first section 310 through the regenerator 800, so that heat of the refrigerant in the first section 310 may be transferred to the refrigerant in the second section 320, so that the temperature of the refrigerant in the first section 310 may be reduced, a lower evaporation temperature may be achieved, the refrigerating capacity of the freezing chamber may be improved, and the deep cooling effect may be better. The temperature of the refrigerant in the second section 320 may also be increased to reduce the risk of condensation or frost back at the first suction port 110. Alternatively, both the first section 310 and the second section 320 may exchange heat with the fourth section 420 via the regenerator 800.

It will be appreciated that since the refrigerant is compressed by the double suction compressor 100, the refrigerant flowing out of the discharge port 130 has a relatively high pressure and a relatively high temperature, and the first line 200 is connected to the discharge port 130, the temperature of the refrigerant in the first line 200 is generally relatively high and the heat quantity is relatively high. The refrigerant flowing out of the first evaporator 610 is generally at a lower temperature than the refrigerant flowing out of the second evaporator 710. Thus, the temperature of the refrigerant in the first circuit 200 is greater than the temperature of the refrigerant in both the second and fourth sections 320, 420, and a temperature differential utilizing this portion can be considered.

Based thereon, referring to fig. 2, 3, and 4, in some embodiments, at least one of the second section 320 and the fourth section 420 exchanges heat with the first pipe 200 through the regenerator 800. Specifically, referring to fig. 2, both the second section 320 and the fourth section 420 exchange heat with the first pipe 200 through the regenerator 800. Or referring to fig. 3, the fourth section 420 exchanges heat with the first pipeline 200 through the regenerator 800, so that heat of the refrigerant in the first pipeline 200 can be transferred to the refrigerant in the fourth section 420, so as to raise the temperature of the refrigerant in the fourth section 420, and reduce the risk of condensation or frosting of the return air of the fourth section 420. Or referring to fig. 4, the second section 320 exchanges heat with the first pipeline 200 through the regenerator 800, so that heat of the refrigerant in the first pipeline 200 can be transferred to the refrigerant in the second section 320, so as to raise the temperature of the refrigerant in the second section 320, and reduce the risk of condensation or frosting of the return air of the second section 320. Or referring to fig. 6, the first section 310 and the fourth section 420 exchange heat with the first pipeline 200 through the regenerator 800, and are mainly used for heating the refrigerant in the fourth section 420, so as to further reduce the risk of condensation or frosting of the return air of the fourth section 420.

Specifically, referring to FIG. 2, in some embodiments, the first conduit 200 includes a fifth section 210, the fifth section 210 being connected to an outlet of the condenser 500. It should be noted that, because the heat is dissipated through the condenser 500, the refrigerant in the fifth section 210 is in a liquid state, and the heat exchange effect of the liquid refrigerant is better. In addition, the refrigerant in the second and fourth sections 320 and 420 is in a gaseous state due to evaporation through the evaporator. At least one of the second section 320 and the fourth section 420 exchanges heat with the fifth section 210 through the heat regenerator 800, and the heat regenerator 800 in a liquid-gas heat exchange mode can be adopted, so that the heat exchange effect is good, and the connection is convenient.

Specifically, referring to fig. 2, both the second section 320 and the fourth section 420 exchange heat with the fifth section 210 through the regenerator 800, and mainly, heat of the refrigerant in the fifth section 210 is transferred to the refrigerant in the second section 320 and the fourth section 420, so as to reduce the temperature of the refrigerant in the second section 320 and the fourth section 420 and reduce the risk of condensation or frost formation of the return air. It should be noted that, in the test experiment of this embodiment, the R600a refrigerant is used as the refrigerant, the refrigeration system 1000 is in an environment with a temperature of 32 ℃ and a relative humidity of the environment is 85%, and the refrigeration system 1000 receives the refrigeration and freezing refrigeration requests at the same time, and the test results: under the condition that the heat regenerator 800 is not arranged, the temperature of the refrigerating chamber is 4 ℃, the temperature of the freezing chamber is-18 ℃, after the refrigerating system 1000 stably operates, the pipeline at the second air suction port 120 has a condensation phenomenon, namely, the surface of the pipeline has liquid drop-shaped water drops, and the pipeline at the first air suction port 110 has a frosting phenomenon, namely, the surface of the pipeline is frozen; in the case of the regenerator 800, the temperature of the refrigerating chamber is 4 ℃, the temperature of the freezing chamber is-18 ℃, after the refrigerating system 1000 stably operates, the pipelines at the first air suction port 110 and the second air suction port 120 are free from frosting and condensation, and the refrigerating system 1000 consumes less energy and improves the energy efficiency by 3%. In this embodiment, after the regenerator 800 is added, the risk of condensation and frosting of the return air can be reduced, and the energy efficiency of the refrigeration system 1000 is improved, so that the cost is reduced.

It should be noted that, the connection mode of the regenerator 800 may be selected according to actual requirements, for example, when the deep cooling effect needs to be improved, the connection mode of fig. 1 may be adopted, and when the risk of condensation or frosting of the return air needs to be reduced, the connection mode of fig. 2 may be adopted.

It will be appreciated that the temperature of the refrigerant in the third section 410 is greater than the temperature of the refrigerant in the second section 320 and the fourth section 420, since the refrigerant in the third section 410 has not been vaporized by the second evaporator 710 and the refrigerant in both the second section 320 and the fourth section 420 have been vaporized by the evaporators. Based on this, in some embodiments, at least one of the second section 320 and the fourth section 420 exchanges heat with the third section 410 through the regenerator 800. Specifically, referring to fig. 7, the fourth section 420 and the third section 410 are connected to the regenerator 800, and the fourth section 420 exchanges heat with the third section 410 through the regenerator 800, so that the risk of condensation or frosting of the return air of the fourth section 420 can be reduced. Referring to fig. 5, the second section 320 and the third section 410 are connected to the regenerator 800, and the second section 320 exchanges heat with the third section 410 through the regenerator 800, so that the risk of condensation or frosting of the return air of the second section 320 can be reduced. Or it may be that the second section 320, the third section 410 and the fourth section 420 all connect into the regenerator 800.

It will be appreciated that with reference to fig. 1, in some embodiments, the connection between the first line 200, the second line 300 and the third line 400 is provided with a control valve 900, and it will be appreciated that the first line 200 is provided with a control valve 900, and the control valve 900 connects the second line 300 and the third line 400. The control valve 900 is used to control the flow rate of the refrigerant flowing from the first line 200 to the second line 300 or the third line 400, and may flexibly adjust the flow rate of the refrigerant, for example, the flow rate of the refrigerant flowing from the first line 200 to the second line 300 may be made greater than the flow rate of the refrigerant flowing from the first line 200 to the third line 400, and more refrigerant may flow into the first evaporator 610 to provide more refrigerating capacity, and the deep cooling effect of the freezing chamber may be improved. The control valve 900 may also be used to control the on-off of the lines, for example, when the refrigerator compartment is not in need of refrigeration, the control valve 900 may be controlled to disconnect the first line 200 from the third line 400. Or when the freezing compartment has no cooling demand, the control valve 900 may be controlled to disconnect the first and second lines 200 and 300. The control valve 900 may specifically be an electrically operated valve.

It is understood that the first throttling element 600 and the second throttling element 700 of the above embodiment may be configured as a thermal expansion valve, an electronic expansion valve, a capillary tube, or the like, and the regenerator 800 may be a patch type heat exchanger, a shell and tube type heat exchanger, a double pipe type heat exchanger, or the like.

It should be understood that a plurality of regenerators 800 may be provided in the above embodiment, so that the above connection modes of the plurality of regenerators 800 are implemented simultaneously, which is not limited herein.

It can be appreciated that the embodiment of the present utility model further provides a refrigeration device, where the refrigeration device includes the refrigeration system 1000 of the foregoing embodiment, and specifically, the refrigeration device may be a refrigerator, a freezer, a refrigerated container, or the like, and since the refrigeration device includes the refrigeration system 1000 of the foregoing embodiment, the foregoing technical effects are provided, and will not be repeated herein.

In the description of the present utility model, it should be understood that references to orientation descriptions such as upper, lower, front, rear, inner, outer, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the utility model.

In the description of the present utility model, the description of the first and second embodiments is only for the purpose of distinguishing technical features, and should not be construed as indicating or implying relative importance or implying the number of technical features indicated or the precedence of technical features indicated.

In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, installation, connection, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical scheme.

The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, and finally, it should be described that: the above embodiments are only for illustrating the technical solution of the present utility model, and not for limiting the same; although the utility model has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present utility model.

Claims (10)

1. A refrigeration system, comprising:

the double-suction compressor is provided with a first air suction port, a second air suction port and an air discharge port;

The inlet of the first pipeline is communicated with the exhaust port;

The inlet of the second pipeline is communicated with the outlet of the first pipeline, and the outlet of the second pipeline is communicated with the first air suction port;

A third pipeline, wherein an inlet of the third pipeline is communicated with an outlet of the first pipeline, and an outlet of the third pipeline is communicated with the second air suction port;

the condenser is arranged on the first pipeline;

And a regenerator for transferring heat of the refrigerant flowing out of the exhaust port to at least one of the first and second suction ports.

2. The refrigeration system of claim 1, wherein the refrigeration system comprises a first assembly and a second assembly, the first assembly is disposed in the second conduit, the first assembly comprises a first throttling element and a first evaporator, the second assembly is disposed in the third conduit, the second assembly comprises a second throttling element and a second evaporator, the second conduit comprises a first section and a second section, the first section is connected with an inlet of the first throttling element, the second section is connected with an outlet of the first evaporator, the third conduit comprises a third section and a fourth section, the third section is connected with an inlet of the second throttling element, and the fourth section is connected with an outlet of the second evaporator.

3. The refrigerant system as set forth in claim 2, wherein at least one of said second and fourth sections exchanges heat with said first section through said regenerator.

4. The refrigerant system as set forth in claim 2, wherein at least one of said second and fourth sections exchanges heat with said third section through said regenerator.

5. The refrigerant system as set forth in claim 2, wherein at least one of said second and fourth sections exchanges heat with said first circuit through said regenerator.

6. The refrigerant system as set forth in claim 5, wherein said first circuit includes a fifth section connected to an outlet of said condenser, at least one of said second section and said fourth section exchanging heat with said fifth section through said regenerator.

7. The refrigeration system of claim 2, wherein the first evaporator is a refrigerator compartment evaporator and the second evaporator is a freezer compartment evaporator.

8. The refrigeration system of claim 2 wherein said first line is provided with a control valve connecting said second line and said third line to control the flow of refrigerant from said first line to said second line or said third line.

9. The refrigeration system of claim 1, wherein the first throttling element and the second throttling element are each provided as capillary tubes.

10. Refrigeration device, characterized by comprising a refrigeration system according to any of claims 1 to 9.