CN216204442U

CN216204442U - Air conditioning system

Info

Publication number: CN216204442U
Application number: CN202122601942.3U
Authority: CN
Inventors: 于艳翠; 符渡; 黄建平; 刘茂龙; 陈云飞
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-10-27
Filing date: 2021-10-27
Publication date: 2022-04-05
Anticipated expiration: 2031-10-27

Abstract

The present application provides an air conditioning system. The air conditioning system comprises a compressor (A), a condenser (B), a first throttling device (V1B), an evaporator (D) and a turbocharger (E), wherein the turbocharger (E) comprises a compression end (Eb) and an expansion end (Ea), the compressor (A), the condenser (B), the first throttling device (V1B), the evaporator (D) and the compression end (Eb) are connected in series to form a refrigeration cycle loop, a bypass pipeline is arranged on the refrigeration cycle loop, one end of the bypass pipeline is connected to the outlet end of the condenser (B), the other end of the bypass pipeline is connected to an air suction port of the compressor (A) through the expansion end (Ea), and a second throttling device (V1a) is arranged on a bypass pipeline on the inlet side of the expansion end (Ea). According to the air conditioning system, the liquid impact at the turbine end of the turbocharger can be effectively avoided, and the working reliability of the air conditioning system is improved.

Description

Air conditioning system

Technical Field

The application relates to the technical field of refrigeration, in particular to an air conditioning system.

Background

At present, two compressors or one air-supplying enthalpy-increasing compressor is usually adopted by an air conditioning unit to meet the conditions of large load demand and large high-low pressure ratio. For example, the outdoor environment temperature is about-25 ℃, and the common means for realizing low-temperature refrigeration in the field of freezing and refrigeration adopts double-stage compression or cascade refrigeration circulation to meet the conditions of large load demand and large high-low pressure ratio. And a common means for realizing low-temperature heating in the field of air conditioners is a two-stage compression circulation system. If the refrigerating capacity and the refrigerating coefficient of the unit are further improved, a larger air displacement amount, a more efficient compressor or other ways for optimizing the refrigerating system are needed.

The related art discloses a heat pump system, which uses a turbocharger to increase the air inlet pressure of a compressor and increase the circulation flow, wherein a refrigerant (with a high probability of being liquid) flowing out of an outdoor unit condenser enters a turbine expansion end during refrigeration, the refrigerant (with a high probability of being in a gas-liquid two-phase state) flowing out of an indoor unit condenser enters a throttle valve firstly and then enters the turbine expansion end during heating, and the inlet of the general turbine expansion requires that a medium is in a gas state or a gas-liquid two-phase state, so that the turbine end of the turbocharger has a high risk of liquid impact during the refrigeration cycle of the heat pump system, and the working reliability of an air conditioning system is low.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem to be solved by the application is to provide an air conditioning system, which can effectively avoid the liquid impact at the turbine end of a turbocharger and improve the working reliability of the air conditioning system.

In order to solve the above problems, the present application provides an air conditioning system, including a compressor, a condenser, a first throttling device, an evaporator and a turbocharger, the turbocharger includes a compression end and an expansion end, the compressor, the condenser, the first throttling device, the evaporator and the compression end are connected in series to form a refrigeration cycle loop, a bypass pipeline is arranged on the refrigeration cycle loop, one end of the bypass pipeline is connected to an outlet end of the condenser, the other end is connected to an air suction port of the compressor through the expansion end, and a second throttling device is arranged on the bypass pipeline positioned at an inlet side of the expansion end.

Preferably, the air conditioning system further comprises a subcooler, a heat absorption part of the subcooler is connected to the bypass pipeline, a heat release part of the subcooler is connected to the refrigeration cycle loop, and the refrigerant in the bypass pipeline absorbs heat released by the refrigeration cycle loop through the heat absorption part to subcool the refrigeration cycle loop.

Preferably, a first end of the bypass line is connected to the refrigeration cycle at a first point, a second end of the bypass line is connected to the refrigeration cycle at a second point, the refrigeration cycle between the first point and the second point is a main path, and the main path is connected in parallel with the bypass line.

Preferably, the refrigerant of the bypass line and the refrigerant of the main line are merged at the second point and then flow to the suction port of the compressor.

Preferably, the compressor is any one of a scroll compressor, a rotor compressor, a screw compressor and a centrifugal compressor.

Preferably, the compression end is any one of a screw compressor, a piston compressor and a centrifugal compressor.

Preferably, the expansion end is a piston expander or a turbo expander.

Preferably, the first throttling means is an electronic expansion valve, a thermostatic expansion valve, a capillary tube or an orifice throttling means.

Preferably, the second throttling means is an electronic expansion valve or a thermostatic expansion valve.

The application provides an air conditioning system, which comprises a compressor, a condenser, first throttling arrangement, evaporimeter and turbo charger, turbo charger includes compression end and expansion end, a compressor, a condenser, first throttling arrangement, evaporimeter and compression end series connection form the refrigeration cycle return circuit, be provided with the bypass pipeline on the refrigeration cycle return circuit, the one end of bypass pipeline is connected to the exit end of condenser, the other end is connected to the induction port of compressor through the expansion end, be located and be provided with second throttling arrangement on the bypass pipeline of the inlet side of expansion end. This air conditioning system has used turbo charger to carry out the pressure boost to the induction port of compressor, can promote the suction end pressure of compressor, increase circulation flow, in order to satisfy the high load, the high pressure ratio demand, reduce the requirement to the compressor, the compressor need not keep very high frequency operation promptly, improve the reliability of compressor, and simultaneously, through set up second throttling arrangement on the inlet side pipeline at turbo charger's expansion end, can carry out the throttle to the refrigerant that enters into the expansion end and step down, improve the refrigerant state that enters into the expansion end, reduce turbo charger's expansion end risk that the liquid hits takes place, improve turbo charger's operational reliability.

Drawings

Fig. 1 is a schematic structural diagram of an air conditioning system according to an embodiment of the present application;

FIG. 2 is a schematic diagram of a refrigeration cycle of an air conditioning system according to an embodiment of the present application;

fig. 3 is an enthalpy difference diagram of an air conditioning system according to an embodiment of the present application.

The reference numerals are represented as:

A. a compressor; B. a condenser; C. a subcooler; D. an evaporator; E. a turbocharger; ea. An expansion end; eb. A compression end; v1a, second throttling means; v1b, first throttling means.

Detailed Description

With combined reference to fig. 1 to 3, according to an embodiment of the present application, the air conditioning system includes a compressor a, a condenser B, a first throttling device V1B, an evaporator D, and a turbocharger E, the turbocharger E includes a compression end Eb and an expansion end Ea, the compressor a, the condenser B, the first throttling device V1B, the evaporator D, and the compression end Eb are connected in series to form a refrigeration cycle loop, a bypass line is disposed on the refrigeration cycle loop, one end of the bypass line is connected to an outlet end of the condenser B, the other end is connected to a suction port of the compressor a via the expansion end Ea, and a second throttling device V1a is disposed on the bypass line on an inlet side of the expansion end Ea.

This air conditioning system has applied turbo charger E to compressor A's induction port pressure boost, can promote compressor A's induction end pressure, increase circulation flow, in order to satisfy the high load, high pressure ratio demand, reduce the requirement to compressor A, compressor A need not keep very high frequency operation promptly, improve compressor A's reliability, and simultaneously, set up second throttling arrangement V1a on the import side pipeline through expansion end Ea at turbo charger E, can throttle the step-down to the refrigerant that enters into expansion end Ea, improve the refrigerant state that enters into expansion end Ea, reduce the risk that the expansion end Ea of turbo charger E takes place the liquid impact, improve turbo charger E's operational reliability.

In this embodiment, after the refrigerant is condensed by the condenser B to release heat, a part of the refrigerant enters the bypass pipeline, is throttled and depressurized by the second throttling device V1a, and then enters the expansion end Ea to perform expansion work to drive the turbocharger to work. The other part of the refrigerant flows along the refrigerant circulation loop, is throttled and depressurized by the first throttling device V1b, enters the evaporator D to evaporate and absorb heat, then enters the compression end Eb of the turbocharger E to be compressed, and the other compressed refrigerant is mixed with the gaseous refrigerant which does work through expansion and enters the air suction end of the compressor A.

Because the output end refrigerant pressure of the expansion end Ea and the output end refrigerant pressure of the compression end Eb are both greater than the outlet end refrigerant pressure of the evaporator D, the suction port refrigerant pressure of the compressor A can be greater than the suction port refrigerant pressure of the compressor A when the outlet of the evaporator D is directly connected with the suction port of the compressor A in the conventional structure, the suction end pressure of the compressor A can be improved by means of the turbocharger E, the circulation flow is increased, and the energy efficiency of the unit under the conditions of high air conditioner load demand and high unit high-low pressure ratio is improved.

In addition, because the refrigerant entering the air suction end of the compressor A is mixed refrigerant, the mixed refrigerant comprises the refrigerant compressed by the compression end Eb and the refrigerant after expansion work is performed on the expansion end Ea, therefore, the refrigerant pressure of the air suction end of the compressor A is influenced by the refrigerant pressure compressed by the compression end Eb and the refrigerant pressure after expansion work is performed on the expansion end Ea, when the refrigerant pressure of the air suction end of the compressor A needs to be adjusted, the pressure of any one of the mixed refrigerants can be independently adjusted, the pressure of the two refrigerants can also be adjusted simultaneously, and the adjustment of the refrigerant pressure of the air suction end of the compressor A is more flexible. In addition, because the regulation of compressor A's the end pressure of breathing in can only realize through adjusting the refrigerant pressure after doing work to expansion end Ea inflation, consequently can realize compressor A's the end pressure regulation of breathing in under the invariable condition of refrigerating capacity of assurance evaporimeter D, can improve compressor A's the end pressure regulation of breathing in stability of temperature regulation in-process, reduce the temperature fluctuation of accommodation process, improve user's use and experience.

In the working process of the turbocharger, a part of expansion work can be recovered, so that power consumption is not needed, electric energy can be saved, the system reliability is further improved, and the unit energy efficiency is improved. For example, the compressor does work by 10kw at normal outdoor temperature of-20 ℃, the power consumption of the compressor is only 7kw, the compressor needs to be driven electrically, the power output by the turbine is supplied to the coaxial compression end, and the additional electrical input is not needed for pre-compression of the compression end.

In order to further improve the gasification effect of the refrigerant after entering the bypass pipeline and more effectively avoid the liquid impact phenomenon at the expansion end Ea, a flash evaporator can be further arranged on the refrigeration cycle loop, the bypass pipeline is connected to the gaseous refrigerant outlet end of the flash evaporator, and the first throttling device is connected to the liquid refrigerant outlet end of the flash evaporator, so that the phenomenon that the working performance of the turbocharger is influenced by the liquid refrigerant mixed in the bypass pipeline is more effectively avoided.

In one embodiment, the air conditioning system further comprises a subcooler C, a heat absorption part of the subcooler C is connected to the bypass pipeline, a heat release part of the subcooler C is connected to the refrigeration cycle loop, and the refrigerant in the bypass pipeline absorbs heat released by the refrigeration cycle loop through the heat absorption part to subcool the refrigeration cycle loop.

In this embodiment, the subcooler C mainly has two functions, and for the refrigerant circulation loop, the subcooler C mainly has the functions of subcooling the refrigerant entering the first throttling device V1b and the evaporator D, so that the subcooling degree of the system is improved, the refrigerating capacity per unit mass is improved, and the refrigerating performance of the evaporator D is improved; for the bypass pipeline, the main function is to heat the refrigerant in the bypass pipeline by utilizing the heat released by supercooling of the refrigerant circulation loop, so that the refrigerant in the bypass pipeline is gasified more fully, the refrigerant entering the expansion end Ea through the bypass pipeline is effectively ensured to be gaseous refrigerant, the phenomenon of liquid impact at the expansion end Ea is avoided, and the working reliability of the turbocharger is improved.

In one embodiment, a first end of the bypass line intersects the refrigeration cycle at a first point, a second end of the bypass line intersects the refrigeration cycle at a second point, and the refrigeration cycle between the first point and the second point is a main path that is in parallel with the bypass line.

In one embodiment, the refrigerant of the bypass line and the refrigerant of the main line are merged at the second point and then flow to the suction port of the compressor a.

In this embodiment, the pipeline that compression end Eb is located and the pipeline that expansion end Ea is located are parallelly connected for the gaseous state refrigerant of the gas vent of compressor can be after condenser B dispels the heat, through second throttling arrangement V1a throttle decompression back, absorb heat through subcooler C, then directly enter into expansion end Ea, can not pass through compression end Eb, can guarantee more effectively that the refrigerant that gets into expansion end Ea is gaseous state refrigerant, avoids the liquid hammer phenomenon more effectively.

In one embodiment, the compressor a is any one of a scroll compressor, a rotor compressor, a screw compressor, and a centrifugal compressor.

In one embodiment, the compression end Eb is any one of a screw compressor, a piston compressor, and a centrifugal compressor.

In one embodiment, the expansion end Ea is a piston expander or a turbo expander.

In one embodiment, the first restriction V1b is an electronic expansion valve, a thermal expansion valve, a capillary tube, or an orifice restriction.

In one embodiment, the second throttling device V1a is an electronic expansion valve or a thermal expansion valve.

Referring to fig. 1 to 3, two paths of gas refrigerant 2 (with a pressure of P2) with a lower pressure from the turbocharger E are compressed by the compressor a for one time to form a high-pressure gas refrigerant 3 (with a pressure of P3), and then condensed by the condenser B to release heat to form a high-pressure liquid refrigerant 4 (with a pressure of P3), wherein a portion of the high-pressure liquid refrigerant 4 is throttled and depressurized by the branch electronic expansion valve V1a to form a refrigerant 7 (with a pressure of P7) and then flows into the subcooler C to exchange heat with another portion of the high-pressure liquid refrigerant 4 of the main path, the main-path high-pressure liquid refrigerant is subcooled, the branch refrigerant 7 absorbs heat to form a branch gas refrigerant 8 with superheat, and the branch gas refrigerant 8 with an intermediate pressure (with a pressure of P7) enters the turbine end Ea of the turbocharger E and is expanded to form a branch gas refrigerant 2 'with a lower pressure (with a pressure of P2').

The high-pressure liquid refrigerant 5 with the sub-cooled main path is throttled and decompressed into a two-phase refrigerant 6 (with a pressure of P6) by an electronic expansion valve V1b, and then flows into an evaporator D to absorb an external low-temperature heat source to become a low-pressure gaseous refrigerant 1 (with a pressure of P6). The refrigerant 1 enters the compression end Eb of the turbocharger E and is compressed into superheated gaseous refrigerant 2 ″ of lower pressure (pressure P2'). Then, the two paths of gas refrigerants 2' and 2 ″ flowing out of the turbocharger E are mixed to form the gas refrigerant 2.

Turbocharger function in this application: expansion end Ea is the turbine, and compression end Eb is the compressor, and turbine and expander are coaxial structure, and high-pressure gas promotes the turbine and outwards exports the merit, turns into the kinetic energy of turbine with high-pressure gas internal energy, and the compressor that drives turbocharger through the pivot rotates, and turbocharger's compressor compresses the refrigerant.

The above pressure magnitude relationship is as follows: p3> P7> P2> P6 ═ P1.

The air conditioning system of this application embodiment can be used to the operating mode of big pressure ratio, for example freezing cold storage, ultra-low temperature refrigeration, ultra-low temperature heating etc. have the advantage that the efficiency is high.

It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.

The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed. The foregoing is only a preferred embodiment of the present application, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present application, and these modifications and variations should also be considered as the protection scope of the present application.

Claims

1. The air conditioning system is characterized by comprising a compressor (A), a condenser (B), a first throttling device (V1B), an evaporator (D) and a turbocharger (E), wherein the turbocharger (E) comprises a compression end (Eb) and an expansion end (Ea), the compressor (A), the condenser (B), the first throttling device (V1B), the evaporator (D) and the compression end (Eb) are connected in series to form a refrigeration cycle loop, a bypass pipeline is arranged on the refrigeration cycle loop, one end of the bypass pipeline is connected to the outlet end of the condenser (B), the other end of the bypass pipeline is connected to an air suction port of the compressor (A) through the expansion end (Ea), and a second throttling device (V1a) is arranged on the bypass pipeline on the inlet side of the expansion end (Ea).

2. The air conditioning system according to claim 1, further comprising a subcooler (C), wherein a heat absorption portion of the subcooler (C) is connected to the bypass line, a heat release portion of the subcooler (C) is connected to the refrigeration cycle line, and a refrigerant in the bypass line absorbs heat released from the refrigeration cycle line through the heat release portion via the heat absorption portion to subcool the refrigeration cycle line.

3. The air conditioning system of claim 1, wherein a first end of the bypass line intersects the refrigeration cycle at a first point, a second end of the bypass line intersects the refrigeration cycle at a second point, and the refrigeration cycle between the first point and the second point is a main path that is in parallel with the bypass line.

4. The air conditioning system according to claim 3, wherein the refrigerant of the bypass line and the refrigerant of the main path are merged at a second point and then flow to a suction port of the compressor (A).

5. Air conditioning system according to claim 1, wherein the compressor (a) is any one of a scroll compressor, a rotor compressor, a screw compressor and a centrifugal compressor.

6. Air conditioning system according to claim 1, wherein the compression end (Eb) is any one of a screw compressor, a piston compressor and a centrifugal compressor.

7. Air conditioning system according to claim 1, characterized in that said expansion end (Ea) is a piston expander or a turbo expander.

8. Air conditioning system according to claim 1, wherein the first throttle device (V1b) is an electronic expansion valve, a thermostatic expansion valve, a capillary tube or an orifice throttle device.

9. Air conditioning system according to claim 1, wherein said second throttling means (V1a) is an electronic or thermal expansion valve.