CN116576590A - Distributed compression refrigeration system - Google Patents

Abstract

The application relates to the technical field of refrigeration, and provides a distributed compression refrigeration system which comprises a cooling loop formed by a compressor, a condenser, a supercharging device, a cooler, a throttling device and an evaporator which are sequentially connected, wherein a refrigeration working medium circularly flows in the cooling loop, the supercharging device is suitable for carrying out secondary supercharging on the refrigeration working medium, the cooler is suitable for carrying out secondary cooling on the refrigeration working medium after the secondary supercharging, and the state of the refrigeration working medium flowing into the supercharging device is one of saturated liquid state, supercooled liquid state or supercritical state. The state of the refrigerating working medium before throttling is changed through the secondary pressurization and secondary cooling processes, the secondary heat release of the working medium is realized on the premise of unchanged original heat sink environment, the temperature-pressure characteristic relation of the refrigerating working medium is utilized, the process of throttling approximate isenthalpic under high pressure is utilized under the condition that the final cooling temperature is basically the same as the traditional system form, the lower dryness of the working medium after throttling is obtained, the refrigerating capacity of unit mass is improved, and the refrigerating energy efficiency of the system is improved.

Description

Distributed compression refrigeration system

Technical Field

The application relates to the technical field of refrigeration, in particular to a distributed compression refrigeration system.

Background

The vapor compression refrigeration cycle system consists of four basic processes: working medium compression, working medium cooling, working medium throttling and working medium heat absorption. In the process of cooling the working medium, the initial temperature and pressure conditions of throttling determine the dryness of the working medium after throttling, and in general, the lower the dryness of the working medium after throttling is, the larger the refrigerating capacity generated under the same compression power consumption is, and the higher the coefficient of performance of the system is. In order to improve the state of the refrigerant before throttling the working medium, the technical means adopted in general is to supercool the working medium, reduce the temperature difference between the working medium and the heat sink environment as much as possible or reduce the temperature below the heat sink environment, and release more heat in the cooling process. However, due to the physical characteristics of some working mediums, the throttling effect of the working mediums is difficult to improve under the conventional method of supercooling by utilizing natural heat sink, so that artificial auxiliary cooling equipment such as mechanical cooling, thermoelectric cooling and the like is attached to the original refrigerating system, and the complexity and the cost of the system are greatly increased. Currently, from the system principle and technical point of view, for example, CO ₂ And freon and other cooling problems, how to seek ways to improve the energy efficiency of the system in the process of cooling working media has been a bottleneck.

The application aims at the purposes of CO ₂ And the phenomenon of over-high dryness of vapor compression refrigeration cycle such as Freon after throttling effectively improves the working medium state of working medium before throttling, thereby greatly reducing the dryness of the working medium after throttling the working medium and improving the unit refrigerating capacity and refrigerating energy efficiency.

Disclosure of Invention

The present application is directed to solving at least one of the technical problems existing in the related art. Therefore, the application provides a distributed compression refrigeration system, which ensures that the refrigerant obtains lower dryness after throttling by performing secondary pressurization and secondary cooling on the refrigerant in a saturated liquid, supercooled liquid or supercritical state, and improves the refrigerating capacity of unit mass.

According to an embodiment of the application, a distributed compression refrigeration system includes:

the refrigerating system comprises a cooling loop formed by a compressor, a condenser, a supercharging device, a cooler, a throttling device and an evaporator which are sequentially connected, wherein a refrigerating working medium circularly flows in the cooling loop, the supercharging device is suitable for carrying out secondary supercharging on the refrigerating working medium flowing through the condenser, the cooler is suitable for carrying out secondary cooling on the refrigerating working medium flowing through the supercharging device, and the state of the refrigerating working medium flowing into the supercharging device is one of saturated liquid state, supercooled liquid state or supercritical state.

According to the distributed compression refrigeration system provided by the embodiment of the application, the compressors comprise the first compressor and the second compressor, the refrigeration working medium flows through the first compressor to enter the second compressor after being compressed, the throttling device comprises the first throttling device and the second throttling device, an intercooler is arranged between the cooler and the evaporator, and the first air inlet of the second compressor is communicated to the position above the liquid level of the intercooler.

According to the distributed compression refrigeration system provided by the embodiment of the application, the first outlet of the cooler is connected with the first restrictor, a part of refrigerant flows into the intercooler for cooling after being throttled by the first restrictor, a coil is arranged in the intercooler, the second outlet of the cooler is connected with the coil, and a part of refrigerant flows through the second restrictor through the coil and enters the evaporator;

the exhaust port of the first compressor is communicated below the liquid level of the intercooler, or the exhaust port of the first compressor is communicated with the second air inlet of the second compressor.

According to the distributed compression refrigeration system provided by the embodiment of the application, the intercooler is arranged between the first throttling device and the second throttling device, and the refrigeration working medium enters the intercooler for cooling through the first throttling device and flows into the evaporator through the second throttling device;

the exhaust port of the first compressor is communicated below the liquid level of the intercooler, or the exhaust port of the first compressor is communicated with the second air inlet of the second compressor.

According to the distributed compression refrigeration system provided by the embodiment of the application, the distributed compression refrigeration system further comprises a condensation evaporator, the cooling loop comprises a primary cooling loop and a secondary cooling loop, and the primary cooling loop and the secondary cooling loop realize heat exchange through the condensation evaporator;

the compressor comprises a first-stage compressor and a second-stage compressor, the throttling device comprises a first-stage throttling device and a second-stage throttling device, the cooler comprises a first-stage cooler and a second-stage cooler, and the supercharging device comprises a first-stage supercharging device and a second-stage supercharging device.

According to the distributed compression refrigeration system provided by the embodiment of the application, the primary cooling loop comprises the primary compressor, the condenser, the primary supercharging device, the primary cooler, the primary throttling device and the condensation evaporator which are connected in sequence;

the secondary cooling loop comprises a secondary compressor, the condensing evaporator, the secondary throttling device and the evaporator which are connected in sequence.

According to the distributed compression refrigeration system provided by the embodiment of the application, the secondary supercharging device and the secondary cooler are arranged between the condensation evaporator and the secondary throttling device, and the refrigeration working medium flows into the secondary throttling device after passing through the secondary supercharging device and the secondary cooler.

According to the distributed compression refrigeration system provided by the embodiment of the application, the secondary cooling loop comprises the secondary compressor, the condensation evaporator, the secondary supercharging device, the secondary cooler, the secondary throttling device and the evaporator which are connected in sequence;

the primary cooling loop comprises a primary compressor, a primary condenser, a primary throttling device and a condensation evaporator which are sequentially connected.

According to the distributed compression refrigeration system provided by the embodiment of the application, the distributed compression refrigeration system further comprises a heat regenerator, and the refrigerant at the outlet of the evaporator enters the compressor after being superheated by the heat regenerator;

the heat regenerator is arranged between the condenser and the supercharger, or the heat regenerator is arranged between the cooler and the throttling device.

According to the distributed compression refrigeration system provided by the embodiment of the application, the throttling device is at least one of a capillary tube, an expansion valve, an ejector and an expander.

The above technical solutions in the embodiments of the present application have at least one of the following technical effects:

the embodiment of the application provides a distributed compression refrigeration system, which comprises a cooling loop formed by a compressor, a condenser, a supercharging device, a cooler, a throttling device and an evaporator which are sequentially connected, wherein a refrigeration working medium circularly flows in the cooling loop, the supercharging device is suitable for carrying out secondary supercharging on the refrigeration working medium flowing through the condenser, the cooler is suitable for carrying out secondary cooling on the refrigeration working medium flowing through the supercharging device, and the state of the refrigeration working medium flowing into the supercharging device is one of saturated liquid state, supercooled liquid state or supercritical state. Therefore, the state of the refrigeration working medium before throttling is changed by adding the secondary pressurization and secondary cooling processes in the traditional vapor compression refrigeration cycle process, the secondary heat release of the working medium can be realized on the premise of unchanged original heat sink environment, the temperature-pressure characteristic relation of the refrigeration working medium is utilized, the process of throttling approximate isenthalpic under high pressure is utilized under the condition that the final cooling temperature is basically the same as the traditional system form, the lower dryness of the working medium after throttling is obtained, the refrigerating capacity of unit mass is improved, and the refrigerating energy efficiency of the system is improved.

Additional aspects and advantages of the application 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 application.

Drawings

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the related art, the drawings that are required to be used in the embodiments or the related technical descriptions will be briefly described, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other drawings may be obtained according to the drawings without inventive effort for those skilled in the art.

Fig. 1 is a schematic structural diagram of a distributed compression refrigeration system according to an embodiment of the present application;

FIG. 2 is a schematic diagram showing a connection of a regenerator according to an embodiment of the present application;

FIG. 3 is a second schematic diagram of a regenerator according to an embodiment of the present application;

FIG. 4 is a schematic diagram of a two-stage compression one-stage throttling intermediate full cooling architecture provided by an embodiment of the present application;

FIG. 5 is a schematic diagram of a two-stage compression one-stage throttling intermediate incomplete cooling structure provided by an embodiment of the application;

FIG. 6 is a schematic diagram I of a two-stage compression two-stage throttling intermediate complete cooling structure provided by an embodiment of the application;

FIG. 7 is a schematic diagram II of a two-stage compression two-stage throttling intermediate complete cooling structure provided by an embodiment of the application;

fig. 8 is a schematic structural diagram of a stacked refrigeration system according to the present application;

fig. 9 is a schematic diagram of a second structure of the stacked refrigeration system provided by the present application;

fig. 10 is a schematic diagram III of a stacked refrigeration system according to the present application;

FIG. 11 is a CO provided by the present application ₂ A pressure enthalpy diagram of the refrigerant;

fig. 12 is a pressure enthalpy diagram of the freon refrigerant provided by the application.

Reference numerals:

1. a compressor; 11. a first compressor; 12. a second compressor; 13. a first stage compressor; 14. a secondary compressor;

2. a condenser;

3. a supercharging device; 31. a first stage supercharging device; 32. a secondary supercharging device;

4. a cooler; 41. a primary cooler; 42. a secondary cooler;

5. a throttle device; 51. a first throttle; 52. a second restrictor; 53. a primary throttle device; 54. a secondary throttle device;

6. an evaporator;

7. a regenerator;

8. an intercooler; 81. a coiled pipe;

9. condensing the evaporator.

Detailed Description

Embodiments of the present application are described in further detail below with reference to the accompanying drawings and examples. The following examples are illustrative of the application but are not intended to limit the scope of the application.

In the description of the embodiments of the present application, it should be noted that the directions or positional relationships indicated by the terms "center", "longitudinal", "lateral", "upper", "lower", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience in describing the embodiments of the present application and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the embodiments of the present application. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In describing embodiments of the present application, it should be noted that, unless explicitly stated and limited otherwise, the terms "coupled," "coupled," and "connected" should be construed broadly, and may be either a fixed connection, a removable connection, or an integral connection, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in embodiments of the present application will be understood in detail by those of ordinary skill in the art.

In embodiments of the application, unless expressly specified and limited otherwise, a first feature "up" or "down" on a second feature may be that the first and second features are in direct contact, or that the first and second features are in indirect contact via an intervening medium. Moreover, a first feature "above," "over" and "on" a second feature may be a first feature directly above or obliquely above the second feature, or simply indicate that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the embodiments of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

In an embodiment of one aspect of the present application, as shown in fig. 1, an embodiment of the present application provides a distributed compression refrigeration system, where the distributed compression refrigeration system includes a cooling circuit formed by sequentially connecting a compressor 1, a condenser 2, a supercharging device 3, a cooler 4, a throttling device 5 and an evaporator 6, a refrigerant circulates in the cooling circuit, the supercharging device 3 is adapted to secondarily pressurize the refrigerant flowing through the condenser 2, the cooler 4 is adapted to secondarily cool the refrigerant flowing through the supercharging device 3, and a state of the refrigerant flowing into the supercharging device 3 is one of a saturated liquid state, a supercooled liquid state or a supercritical state.

It should be noted that the distributed compression refrigeration system may be adapted for use with CO ₂ And Freon gas or other steam and the like are directly throttled after being cooled to cause excessive dryness after throttling, the state of the refrigerant before throttling is changed by adding secondary pressurization and secondary cooling processes in the traditional vapor compression refrigeration cycle process, the secondary heat release of the refrigerant can be realized on the premise of unchanged original heat sink environment, and the temperature and pressure characteristics of the refrigerant are utilizedAnd under the condition that the final cooling temperature is basically the same as the traditional system form, the process of throttling approximate isenthalpic under high pressure is utilized, so that the working medium obtains lower dryness after throttling, the refrigerating capacity of the refrigerating working medium with unit mass is improved, and the refrigerating energy efficiency of the system is improved. Further, the heating amount may be increased under heating conditions.

As shown in fig. 11 and 12, the abscissa h is the specific enthalpy value, the ordinate P is the pressure value, a is the compression process of the compressor 1, B is the cooling process of the condenser 2, C is the secondary supercharging process of the supercharging device 3, D is the secondary cooling process of the cooler 4, E is the throttling process of the throttling device 5, F is the heat absorption process of the evaporator 6, T is the isotherm, K is the saturation curve, G ₁ The point represents the state point after secondary pressurization and secondary cooling of the refrigeration working medium, G ₂ The points represent the state points of the condenser 2 after cooling and direct throttling, and G is known by combining the characteristics of the pressure enthalpy diagram ₁ The dryness of the dots is lower than G ₂ The dryness of the point is improved, so that the dryness after throttling of the refrigerating working medium can be obviously reduced by using the distributed compression refrigerating system, the refrigerating capacity of the refrigerating working medium with unit mass is further improved, and the refrigerating energy efficiency of the system is improved.

In an alternative embodiment, the parts of the distributed compression refrigeration system are communicated through pipelines, and when the system works, the refrigeration working medium sequentially passes through the compressor 1, the condenser 2, the supercharging device 3, the cooler 4, the throttling device 5 and the evaporator 6 to complete a circulation process, the refrigeration working medium is subjected to heat release cooling twice in the condenser 2 and the cooler 4, and the compressor 1 and the supercharging device 3 are subjected to supercharging twice.

When the system is in operation, the refrigerant from the evaporator 6 is compressed by the compressor 1 and then enters a high-temperature and high-pressure state, then the refrigerant releases heat to the heat sink environment through the condenser 2 under the isobaric condition to realize condensation or cooling of the refrigerant, the refrigerant leaving the condenser 2 can be in a saturated liquid state, a supercooled liquid state or a supercritical state, then the pressure boosting device 3 carries out pressure boosting on the refrigerant at the outlet of the condenser 2, the temperature of the refrigerant is increased due to the pressure boosting process, the refrigerant after the secondary pressure boosting enters the cooler 4 to release heat to the heat sink environment again, then the refrigerant after heat release generates a cold effect through the throttling device 5, and the refrigerant at a low temperature enters the evaporator 6 to absorb heat and refrigerate.

It should be noted that the state of the refrigerant before entering the pressurizing device 3 should be one of a saturated liquid state, a supercooled liquid state, or a supercritical state, in order to distinguish from a multi-stage vapor compression cycle system that compresses saturated gas or superheated gas. After the primary condensation process of the vapor compression refrigeration cycle, the temperature and pressure of the refrigerant which is cooled originally are increased again by means of secondary pressurization of the refrigerant in a saturated liquid, supercooled liquid or supercritical state, the refrigerant with the temperature and pressure increased by the secondary pressurization is cooled secondarily to release heat, further heat release is achieved, and the throttling process of the refrigerant is carried out immediately.

It will be appreciated that the secondary boost and secondary cooling process performed by the system between the condenser 2 and the throttle device 5 may be in a multi-compressor compression refrigeration system or in a cascade refrigeration system.

Further, after the refrigerant with the temperature and pressure increased by the supercharging device 3 is cooled for heat release, the temperature of the refrigerant at the outlet of the cooler 4 may be greater than, less than or equal to the temperature at the outlet of the condenser 2, and an operator may set and adjust the temperature according to the use requirement to achieve the optimal cooling effect.

It can be understood that the compressor 1 can be in the form of one-stage compression or multi-stage compression, and can be in the form of single-machine compression or multi-machine parallel compression; the supercharging device 3 may be a device such as a compressor 1 or a pump for raising the pressure of a liquid or supercritical refrigerant, and the supercharging device 3 may be electrically driven or hydraulically or other types of power driven, and the present application is not limited in particular.

The heat sink environments of the condenser 2 and the cooler 4 may be the same, or the heat sink temperature of the cooler 4 may be lower than the heat sink temperature of the condenser 2, or the heat sink temperature of the cooler 4 may be slightly higher than the heat sink temperature of the condenser 2, and the operator may set as needed, and the present application is not limited in particular.

According to one embodiment of the application, the distributed compression refrigeration system further comprises a storage means for storing the refrigerant, which may be arranged between the condenser 2 and the pressure increasing means 3, or between the cooler 4 and the throttling means 5, or between the throttling means 5 and the evaporator 6. Furthermore, a gas-liquid separator with a certain storage function can be added between the evaporator 6 and the compressor 1, so that the refrigerant entering the compressor 1 is ensured to be in a gaseous state.

According to one embodiment of the present application, as shown in fig. 2 and 3, the distributed compression refrigeration system further includes a regenerator 7, and the refrigerant at the outlet of the evaporator 6 enters the compressor 1 after being superheated by the regenerator 7; the regenerator 7 is arranged between the condenser 2 and the supercharging device 3, or the regenerator 7 is arranged between the cooler 4 and the throttling device 5.

Specifically, a heat recovery process is added on the basis of the embodiment of fig. 1, as shown in fig. 2, a heat recovery device 7 is arranged between the condenser 2 and the supercharging device 3, the refrigerant leaving the condenser 2 is subjected to wall-type heat exchange with the refrigerant leaving the evaporator 6 in the heat recovery device 7, and the temperature of the refrigerant before entering the supercharging device 3 is further reduced after the heat exchange, so that the cooling effect is improved.

Optionally, as shown in fig. 3, the regenerator 7 is disposed between the cooler 4 and the throttling device 5, and the refrigerant leaving the cooler 4 performs a wall-type heat exchange with the refrigerant leaving the evaporator 6 in the regenerator 7, so that the temperature of the refrigerant before entering the throttling device 5 is further reduced after the heat exchange, which is beneficial to improving the cooling effect.

According to an embodiment of the application, as shown in connection with fig. 4 to 7, the compressor 1 comprises a first compressor 11 and a second compressor 12, the refrigerant is compressed by the first compressor 11 and enters the second compressor 12, the throttling device 5 comprises a first throttling device 51 and a second throttling device 52, an intercooler 8 is arranged between the cooler 4 and the evaporator 6, and a first air inlet of the second compressor 12 is communicated to the position above the liquid level of the intercooler 8. By adjusting the connection relationship between the components, multi-stage throttling, intermediate complete cooling and intermediate incomplete cooling can be realized.

According to one embodiment of the present application, as shown in fig. 4 and 5, the first restrictor 51 and the second restrictor 52 are connected in parallel, the first outlet of the cooler 4 is connected with the first restrictor 51, a part of refrigerant is throttled by the first restrictor 51 and flows into the intercooler 8 to be cooled, a coil 81 is arranged in the intercooler 8, the second outlet of the cooler 4 is connected with the coil 81, and a part of refrigerant flows through the second restrictor 52 to enter the evaporator 6 via the coil 81; the discharge port of the first compressor 11 communicates below the level of the intercooler 8, or the discharge port of the first compressor 11 communicates with the second inlet port of the second compressor 12.

It can be understood that the pressure of the refrigerant compressed by the second compressor 12 is higher than the pressure of the refrigerant compressed by the first compressor 11, so as to implement two-stage compression of the refrigerant. A space capable of storing a certain refrigerant is formed between the coil 81 and the side wall of the intercooler 8, and the coil 81 is disposed below the liquid surface of the intercooler 8.

Alternatively, as shown in fig. 4, the discharge port of the first compressor 11 is connected below the liquid level of the intercooler 8, and the first intake port of the second compressor 12 is connected above the liquid level of the intercooler 8. Part of the refrigerant at the outlet of the cooler 4 enters the intercooler 8 to generate a certain cooling effect after being throttled by the first throttle 51, and the other part enters the coil 81 under the liquid level of the intercooler 8 to further realize supercooling. The refrigerant exiting coil 81 below the liquid level in intermediate cooler 8 is throttled by second throttle 52 and enters evaporator 6. The refrigerant at the outlet of the first compressor 11 is cooled by the intercooler 8 and then enters the second compressor 12 for compression.

Alternatively, as shown in fig. 5, the exhaust port of the first compressor 11 may also be in communication with the second inlet port of the second compressor 12, and the refrigerant at the outlet of the first compressor 11 does not need to enter the intercooler 8, but is directly introduced into the second compressor 12 for compression.

According to one embodiment of the present application, as shown in fig. 6 and 7, the first restrictor 51 and the second restrictor 52 are connected in series, the intercooler 8 is disposed between the first restrictor 51 and the second restrictor 52, and the refrigerant enters the intercooler 8 through the first restrictor 51 and flows into the evaporator 6 through the second restrictor 52, thereby realizing two-stage throttling; the discharge port of the first compressor 11 communicates below the level of the intercooler 8, or the discharge port of the first compressor 11 communicates with the second inlet port of the second compressor 12.

Alternatively, as shown in fig. 6, the exhaust port of the first compressor 11 is communicated below the liquid level of the intercooler 8, the refrigerant at the outlet of the cooler 4 directly throttles and enters the intercooler 8 through the first throttle 51, and the refrigerant at the outlet of the first compressor 11 is cooled by the intercooler 8 and then enters the second compressor 12 for compression.

Alternatively, as shown in fig. 7, the exhaust port of the first compressor 11 is communicated with the second air inlet of the second compressor 12, and the refrigerant at the outlet of the cooler 4 directly enters the intercooler 8 through the throttling of the first throttle device 51, and the refrigerant at the outlet of the first compressor 11 directly enters the second compressor 12 for compression.

According to one embodiment of the present application, as shown in connection with fig. 8-10, the distributed compression refrigeration system may be a cascade-based refrigeration system, the system further comprising a condensation evaporator 9, the cooling circuit comprising a primary cooling circuit and a secondary cooling circuit, the primary cooling circuit and the secondary cooling circuit effecting heat exchange through the condensation evaporator 9; the compressor 1 includes a first stage compressor 13 and a second stage compressor 14, the throttle device 5 includes a first stage throttle device 53 and a second stage throttle device 54, the cooler 4 includes a first stage cooler 41 and a second stage cooler 42, and the supercharging device 3 includes a first stage supercharging device 31 and a second stage supercharging device 32.

It is understood that the primary cooling circuit is a high temperature stage cooling circuit and the secondary cooling circuit is a low temperature stage cooling circuit, i.e. the temperature of the primary cooling circuit is higher than the temperature of the secondary cooling circuit.

In an alternative embodiment, as shown in fig. 9, the primary cooling circuit comprises a primary compressor 13, a condenser 2, a primary booster 31, a primary cooler 41, a primary throttle 53 and a condensing evaporator 9, which are connected in sequence; the secondary cooling circuit comprises a secondary compressor 14, a condensing evaporator 9, a secondary throttling device 54 and an evaporator 6, which are connected in sequence.

According to an embodiment of the present application, as shown in fig. 8, based on the embodiment corresponding to fig. 9, a secondary supercharging device 32 and a secondary cooler 42 are provided between the condensation evaporator 9 and the secondary throttling device 54, and the refrigerant of the secondary cooling circuit flows into the secondary throttling device 54 after passing through the secondary supercharging device 32 and the secondary cooler 42.

In the secondary cooling loop, the refrigerant is compressed by the secondary compressor 14 and enters the condensing evaporator 9 to cool and release heat, then the pressure and temperature are raised again by the secondary supercharging device 32, further cooling and release heat are carried out in the secondary cooler 42, and the refrigerant at the outlet of the secondary cooler 42 enters the evaporator 6 to absorb heat and refrigerate after being throttled by the secondary throttling device 54. In the primary cooling loop, the refrigerant is compressed by the primary compressor 13 and enters the condenser 2 to cool and release heat, then the pressure and temperature are raised again by the primary supercharging device 31, further cooling and release heat are carried out in the primary cooler 41, and the refrigerant at the outlet of the primary cooler 41 enters the condensing evaporator 9 to absorb heat from the refrigerant in the secondary cooling loop after being throttled by the primary throttling device 53.

According to one embodiment of the application, as shown in fig. 10, the secondary cooling circuit comprises a secondary compressor 14, a condensation evaporator 9, a secondary supercharging device 32, a secondary cooler 42, a secondary throttling device 54 and an evaporator 6, which are connected in sequence; the primary cooling circuit comprises a primary compressor 13, a primary condenser 2, a primary throttling device 53 and a condensation evaporator 9 which are connected in sequence. The primary supercharging device 31 and the primary cooler 41 are reduced in the primary cooling circuit in comparison with the corresponding embodiment of fig. 8.

According to one embodiment of the application, the throttling means 5 is at least one of a capillary tube, an expansion valve, an ejector, an expander.

It is understood that the throttling device 5 in the distributed compression refrigeration system is not limited to various capillaries and expansion valves, and may be an ejector, an expander or other devices with the effect of generating throttling of the refrigerant.

The embodiment of the application provides a distributed compression refrigeration system, which comprises a cooling loop formed by sequentially connecting a compressor 1, a condenser 2, a supercharging device 3, a cooler 4, a throttling device 5 and an evaporator 6, wherein a refrigerating medium circularly flows in the cooling loop, the supercharging device 3 is suitable for carrying out secondary supercharging on the refrigerating medium flowing through the condenser 2, the cooler 4 is suitable for carrying out secondary cooling on the refrigerating medium flowing through the supercharging device 3, and the state of the refrigerating medium flowing into the supercharging device 3 is one of saturated liquid state, supercooled liquid state or supercritical state. By adding the secondary pressurization and secondary cooling processes in the traditional vapor compression refrigeration cycle process, the state of the refrigeration working medium before throttling is changed, the secondary heat release of the working medium can be realized on the premise of unchanged original heat sink environment, the temperature-pressure characteristic relation of the refrigeration working medium is utilized, the process of throttling approximate isenthalpic under high pressure is utilized under the condition that the final cooling temperature is basically the same as the traditional system form, the lower dryness of the working medium after throttling is obtained, the refrigerating capacity of unit mass is improved, and the refrigerating energy efficiency of the system is improved. Further, the heating amount may be increased under heating conditions.

Finally, it should be noted that: the above embodiments are only for illustrating the technical aspects of the present application, and are not limiting. Although the application has been described in detail with reference to the embodiments, it will be understood by those skilled in the art that the technical solutions described in the foregoing embodiments may be modified or some of the technical features may be replaced with equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present application, and are intended to be included in the scope of the present application.

Claims (10)

1. A distributed compression refrigeration system, comprising:

the refrigerating system comprises a cooling loop formed by a compressor, a condenser, a supercharging device, a cooler, a throttling device and an evaporator which are sequentially connected, wherein a refrigerating working medium circularly flows in the cooling loop, the supercharging device is suitable for carrying out secondary supercharging on the refrigerating working medium flowing through the condenser, the cooler is suitable for carrying out secondary cooling on the refrigerating working medium flowing through the supercharging device, and the state of the refrigerating working medium flowing into the supercharging device is one of saturated liquid state, supercooled liquid state or supercritical state.

2. The distributed compression refrigeration system of claim 1 wherein said compressors include a first compressor and a second compressor, refrigerant flowing through said first compressor for compression into said second compressor, said throttling means including a first throttle and a second throttle, an intercooler being disposed between said cooler and said evaporator, a first inlet of said second compressor being in communication with a liquid level above said intercooler.

3. The distributed compression refrigeration system of claim 2 wherein a first outlet of said chiller is connected to said first restrictor and a portion of refrigerant is throttled by said first restrictor and flows into said intercooler for cooling, a coil is disposed in said intercooler and a second outlet of said chiller is connected to said coil and a portion of refrigerant flows through said second restrictor via said coil and into said evaporator;

the exhaust port of the first compressor is communicated below the liquid level of the intercooler, or the exhaust port of the first compressor is communicated with the second air inlet of the second compressor.

4. The distributed compression refrigeration system of claim 2 wherein said intercooler is disposed between said first and second throttles, refrigerant entering said intercooler through said first throttles for cooling and flowing into said evaporator through said second throttles;

the exhaust port of the first compressor is communicated below the liquid level of the intercooler, or the exhaust port of the first compressor is communicated with the second air inlet of the second compressor.

5. The distributed compression refrigeration system of claim 1 further comprising a condensing evaporator, the cooling circuit comprising a primary cooling circuit and a secondary cooling circuit, the primary cooling circuit and the secondary cooling circuit effecting heat exchange through the condensing evaporator;

the compressor comprises a first-stage compressor and a second-stage compressor, the throttling device comprises a first-stage throttling device and a second-stage throttling device, the cooler comprises a first-stage cooler and a second-stage cooler, and the supercharging device comprises a first-stage supercharging device and a second-stage supercharging device.

6. The distributed compression refrigeration system of claim 5 wherein said primary cooling circuit comprises said primary compressor, said condenser, said primary booster means, said primary cooler, said primary throttle means, and said condensing evaporator connected in sequence;

the secondary cooling loop comprises a secondary compressor, the condensing evaporator, the secondary throttling device and the evaporator which are connected in sequence.

7. A distributed compression refrigeration system as set forth in claim 6 wherein said secondary supercharging device and said secondary cooler are disposed between said condensing evaporator and said secondary throttling device, refrigerant flowing into said secondary throttling device after passing through said secondary supercharging device and said secondary cooler.

8. The distributed compression refrigeration system of claim 5 wherein said secondary cooling circuit comprises said secondary compressor, said condensing evaporator, said secondary supercharging device, said secondary cooler, said secondary throttling device, and said evaporator connected in sequence;

the primary cooling loop comprises a primary compressor, a primary condenser, a primary throttling device and a condensation evaporator which are sequentially connected.

9. The distributed compression refrigeration system according to any one of claims 1 to 8 further comprising a regenerator through which refrigerant exiting said evaporator is superheated and enters said compressor;

the heat regenerator is arranged between the condenser and the supercharger, or the heat regenerator is arranged between the cooler and the throttling device.

10. A distributed compression refrigeration system as claimed in any one of claims 1 to 8 wherein said throttling means is at least one of a capillary tube, an expansion valve, an ejector, an expander.