CN115406023B - Fluorine pump double-circulation air conditioning system and control method thereof - Google Patents

Abstract

This invention discloses a refrigerant pump dual-cycle air conditioning system and its control method. The air conditioning system includes a compressor, condenser, receiver, pump, throttle, and evaporator connected in series via piping. It also includes a heat exchanger. The piping between the condenser and receiver is divided into a heat exchange section and two non-heat exchange sections connected to both ends of the heat exchange section. The heat exchanger absorbs heat from the heat exchange section through evaporation. The input end of the heat exchanger is connected to one of the non-heat exchange sections, and the output end of the heat exchanger is connected to the input end of the compressor. The control method uses the aforementioned air conditioning system. The air conditioning system and control method of this invention can increase the subcooling of the liquid in the receiver and control the superheat of the gas at the compressor inlet, thereby avoiding pump cavitation and compressor liquid slugging. The entire system has a simple structure, more reliable operation, simple piping installation, and is more convenient for engineering applications.

Description

Fluorine pump double-circulation air conditioning system and control method thereof

Technical Field

The invention relates to the field of air conditioners, in particular to a fluorine pump double-circulation air conditioning system and a control method thereof.

Background

The direct expansion air conditioner adopted by the traditional old data machine room adopts a refrigeration mode that a compressor is adopted to drive a refrigerant to finish cooling in winter, summer and transitional seasons, so that energy efficiency is low, energy waste is caused, and in northern areas, winter and transitional seasons, outdoor temperature is far lower than indoor temperature, so that outdoor air becomes a free natural cold source, and the pump can efficiently utilize the natural cold source. By utilizing the natural cold source, the working time of the compressor is reduced, so that the aim of saving energy is fulfilled.

A pump system (which may also be referred to as a refrigerant pump system because a refrigerant commonly used in an air conditioning refrigeration system is freon) is an air conditioning system in which a pump is used to drive the refrigerant instead of a compressor. In summer, the special air conditioner for the data center starts the refrigeration compressor to normally refrigerate, when the outdoor temperature is lower than the preset temperature of the controller, the controller is automatically switched to the refrigeration by the compressor, the freon liquid cooled by the outdoor air-cooled condensing part is conveyed into the evaporating part through the refrigerant pump, after the heat in the room is absorbed, the freon is converted from the liquid state into the gas state, enters the air-cooled condensing part and is cooled into the liquid again, and the cycle is repeated. Because the power of the refrigerant pump is far smaller than that of the refrigerating compressor, the energy efficiency ratio of the refrigerant pump is higher than that of the refrigerating compressor on the premise of the same refrigerating capacity, and therefore the energy-saving effect is achieved while the temperature is reduced.

If the fluid passing through the pump is liquid, cavitation will occur, and cavitation impact and erosion occur on the surface of the impeller of the pump (also called a fluorine pump), that is, cavitation occurs, and in addition, noise and vibration may occur in the pump, and the performance of the pump may be degraded, and when the performance of the pump is seriously degraded, the liquid in the pump may be interrupted, and the pump may not work normally. Thus, before the pump system is operated, it is necessary to ensure that no gas enters the pump. Likewise, the compressor also needs to avoid liquid suction during operation so as not to generate liquid impact.

Aiming at the current compound air conditioning system of the fluorine pump and the compressor, in order to prevent the problems of cavitation and liquid impact of the fluorine pump and the compressor respectively during the switching of the working modes, an additional electromagnetic valve is required to be arranged at the refrigerant inlet side of the fluorine pump and the compressor, and a gas-liquid separator is possibly required to be arranged at the inlet side of the compressor, so that the whole air conditioning system has a complex structure, and the control difficulty of the whole system is increased.

Disclosure of Invention

The invention aims to overcome the defects or problems in the background art, and provides a fluorine pump double-circulation air conditioning system and a control method thereof, which can increase the supercooling degree of liquid in a liquid reservoir and control the superheat degree of gas at an inlet of a compressor, so that cavitation of a pump and liquid impact of the compressor are avoided, an external cold source is not needed, the whole system is simple in structure, the system is more reliable in operation, a pipeline is simple to lay, and engineering application is more convenient.

In order to achieve the above purpose, the present invention adopts the following technical scheme:

the utility model provides a first, a fluorine pump dual cycle air conditioning system, including the compressor that loops through the pipeline and concatenates, condenser, reservoir, pump, choke ware and evaporimeter, still include the heat exchanger, the condenser with pipeline between the reservoir divide into the heat exchange section and with two non-heat exchange section that the both ends of heat exchange section link up, the heat exchanger absorbs through the evaporation the heat of heat exchange section, one of them non-heat exchange section of input intercommunication of heat exchanger, the output intercommunication of heat exchanger the input of compressor.

Based on the first technical scheme, still be equipped with technical scheme two, in the technical scheme two, the heat exchanger includes bypass expansion valve and heat transfer chamber, the heat transfer chamber export forms the output of heat exchanger, the pipeline between the entry of heat transfer chamber and the non-heat exchange section is first pipeline, bypass expansion valve concatenates on first pipeline.

Based on the second technical scheme, a third technical scheme is further provided, in the third technical scheme, the inlet of the heat exchange chamber is communicated with a non-heat exchange section close to the liquid storage device, and the flowing direction of gas in the heat exchange chamber is opposite to the flowing direction of liquid in the heat exchange section.

Based on the third technical scheme, a fourth technical scheme is further provided, wherein in the fourth technical scheme, the air conditioning system is divided into an indoor portion and an outdoor portion, the indoor portion comprises the throttle and the evaporator, and the outdoor portion comprises the compressor, the condenser, the liquid reservoir, the pump and the heat exchanger.

Based on the fourth technical scheme, a fifth technical scheme is further provided, in the fifth technical scheme, the inlet of the liquid reservoir is higher than the outlet of the liquid reservoir.

Based on the technical scheme five, still be equipped with technical scheme six, in technical scheme six, still include first control valve and second control valve, first control valve is parallelly connected between the input and the output of compressor through the pipeline, the second control valve is parallelly connected between the input of reservoir and the output of pump through the pipeline.

The invention also provides a control method of the fluorine pump double-circulation air conditioning system, which adopts the air conditioning system of the sixth technical scheme, and comprises the steps of obtaining outdoor temperature Tout, determining a running refrigerating mode according to the relation between Tout and a first set value T1 and a second set value T2, determining to run in the first refrigerating mode if Tout is greater than or equal to T1, determining to run in the second refrigerating mode if T2 is less than or equal to T1, determining to run in the third refrigerating mode if Tout is less than or equal to T2, adjusting the running refrigerating mode according to the relation between the outdoor temperature Tout and the first set value T1, the second set value T2 and the third set value Deltat and the current running refrigerating mode, switching to the second refrigerating mode if T2 is less than or equal to T1-Deltat, switching to the first refrigerating mode if Tout is greater than or equal to T1-, switching to the second refrigerating mode if Tout is less than or equal to T2-Deltat, switching to the third refrigerating mode if Tout is less than or equal to T2-DeltaT, switching to the third refrigerating mode and the third compressor is formed in the first refrigerating mode and the second refrigerating mode, and the third refrigerating mode is switched to the compressor mode, and the third refrigerating mode is switched to the refrigerating mode, and the second refrigerating mode is not smaller than or equal to the first refrigerating mode.

Based on the seventh technical scheme, a eighth technical scheme is further provided, in the eighth technical scheme, in the first refrigeration mode, the first control valve is closed, and the second control valve and the bypass expansion valve are both opened.

The control method of the fluorine pump double-circulation air conditioning system comprises the steps of obtaining outdoor temperature Tout, indoor temperature Tin and refrigeration requirement, obtaining a first set value T1, operating in a first refrigeration mode if Tin-Tout is smaller than T1 and the refrigeration requirement is larger than 100%, operating in a second refrigeration mode if Tin-Tout is larger than or equal to T1 and the refrigeration requirement is larger than or equal to 100%, operating in a third refrigeration mode if Tin-Tout is larger than or equal to T1 and the refrigeration requirement is larger than 30% and smaller than 100%, starting in the first refrigeration mode, forming refrigeration circulation with a condenser and an evaporator, closing in the second refrigeration mode, starting in the third refrigeration mode, and forming refrigeration circulation with the condenser and the evaporator.

Based on the technical scheme nine, a technical scheme ten is further provided, and in the technical scheme ten, the obtaining of the refrigeration requirement comprises the following steps of obtaining the indoor target temperature Tset and the second set value T2, and the refrigeration requirement is (Tin-Tset)/T2 which is 100%.

From the above description of the present invention, compared with the prior art, the present invention has the following advantages:

1. In the first technical scheme, a pipeline between the condenser and the liquid storage device is divided into a heat exchange section and two non-heat exchange sections connected with two ends of the heat exchange section, namely, liquid refrigerant of the condenser sequentially passes through the non-heat exchange sections, the heat exchange sections and the non-heat exchange sections to reach the liquid storage device, a heat exchanger is arranged, the input end of the heat exchanger is communicated with one of the non-heat exchange sections, the output end of the heat exchanger is communicated with the input end of the compressor, the heat exchanger absorbs heat of the heat exchange sections through evaporation, namely, a liquid part of one of the non-heat exchange sections flows to the liquid storage device or the heat exchange section, and the liquid part flows to the heat exchanger, so that the heat of the heat exchange sections is taken away by evaporation, so that the temperature of the liquid refrigerant is reduced after the liquid refrigerant passes through the heat exchange sections, and then the temperature is greatly reduced after the liquid refrigerant flows to the liquid storage device, thereby increasing the supercooling degree of the liquid in the liquid storage device, ensuring that the pump is started or in the refrigeration mode switching process, preventing the pump from eroding, thereby protecting the pump, and the gas refrigerant evaporated by the heat exchanger flows to the inlet of the compressor through evaporation of the heat exchange section, namely, the liquid refrigerant can be better controlled to the heat exchanger or the heat exchanger, the whole system can be more conveniently controlled by the heat exchanger, and the heat exchanger can be more conveniently compressed by the air conditioner, and the air conditioner system can be more conveniently controlled by the heat exchanger.

2. In the second technical scheme, the condenser distributes the heat of the high-temperature high-pressure gas conveyed by the compressor into low-temperature high-pressure liquid, the heat exchanger comprises a bypass expansion valve and a heat exchange chamber, the bypass expansion valve is connected in series on the first pipeline, the low-temperature high-pressure liquid conveyed to the heat exchange section by the condenser is beneficial to being changed into low-temperature low-pressure wet steam through throttling, and the wet steam evaporates in the heat exchange chamber to take away the heat of the heat exchange section, so that the heat exchange device is simple in structure and easy to realize.

3. In the third technical scheme, the inlet of the heat exchange chamber is close to the liquid storage device, namely the inlet of the heat exchange chamber is communicated with the non-heat exchange section connected with the liquid storage device, and the temperature of liquid at the outlet of the heat exchange section is lower than that of liquid at the inlet of the heat exchange section because the non-heat exchange section is communicated with the outlet of the heat exchange section, so that the heat exchange efficiency is better after the liquid at the outlet of the heat exchange section enters the heat exchange chamber through the bypass expansion valve, the flowing direction of gas in the heat exchange chamber is opposite to that of the liquid in the heat exchange section, the heat exchange area is large, the heat exchange efficiency is higher, and in addition, the design is more convenient when a pipeline is connected, and the whole pipeline length is shorter.

4. In the fourth technical scheme, the outdoor part comprises a compressor, a condenser, a liquid storage device, a pump and a heat exchanger, so that the heat exchanger is conveniently connected with a non-heat exchange section and the pipeline at the input end of the compressor, the length of the whole pipeline is shorter, the pipeline is simple to lay, and the engineering application is more convenient.

5. In the fifth technical scheme, the inlet of the liquid storage pipe is higher than the outlet of the liquid storage pipe, so that gas is further prevented from entering the pump.

6. In the sixth technical scheme, the arrangement of the first control valve and the second control valve is beneficial to enabling the air conditioning system to operate in different refrigeration modes, and is more energy-saving and environment-friendly.

7. In the seventh technical scheme, the invention also provides a control method of the fluorine pump double-circulation air conditioning system, which adopts the air conditioning system in the sixth technical scheme, and has the same advantages as the above, in the scheme, when the first refrigeration mode is switched to the second refrigeration mode, the outdoor temperature is required to be less than or equal to T1-delta T, when the second refrigeration mode is switched to the first refrigeration mode, the outdoor temperature is required to be more than or equal to T1 < + > delta T, so that frequent switching of the first refrigeration mode and the second refrigeration mode is avoided, when the second refrigeration mode is switched to the third refrigeration mode, the outdoor temperature is required to be less than or equal to T2-delta T, and when the third refrigeration mode is switched to the second refrigeration mode, the outdoor temperature is required to be more than or equal to T2 < + > delta T, so that frequent switching of the second refrigeration mode and the third refrigeration mode is avoided, and frequent starting and stopping of a pump or a compressor are avoided, and unstable indoor working conditions are avoided.

8. In the eighth technical scheme, in the first refrigeration mode, the first control valve is closed, the second control valve and the bypass expansion valve are opened, at the moment, the refrigerant sequentially flows through the compressor and the condenser, after the refrigerant comes out of the condenser, the gas evaporated by the heat exchanger flows into the inlet of the compressor, so that the superheat degree of the inlet of the compressor is ensured, and the liquid impact of the compressor is avoided.

9. In the technical scheme, the refrigeration mode is adjusted according to the indoor and outdoor temperature difference and the refrigeration requirement, and the actual use condition is more met, so that the air conditioning system can always meet the refrigeration requirement, and the stable operation of indoor working conditions is ensured.

10. In the tenth technical scheme, the refrigeration requirement is determined by the target temperature and the indoor temperature, so that the refrigerator is more fit for the actual use condition.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the description of the embodiments below are briefly introduced, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic diagram of an air conditioning system according to embodiment 1 of the present invention;

fig. 2 is a schematic diagram of an air conditioning system according to embodiment 2 of the present invention.

The main reference numerals illustrate:

Compressor 10, condenser 20, accumulator 30, pump 40, throttle 50, evaporator 60, first control valve 70, second control valve 80, heat exchanger 90, heat exchange chamber 91, bypass expansion valve 92, first branch 01, second branch 02, heat exchange section 03, non-heat exchange section 04, first line 05, second line 06, indoor portion 100.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the described embodiments are preferred embodiments of the invention and should not be taken as excluding other embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without creative efforts, are within the protection scope of the present invention.

In the claims, specification and drawings hereof, unless explicitly defined otherwise, the terms "first," "second," or "third," etc. are used for distinguishing between different objects and not for describing a particular sequential order.

In the claims, specification and drawings of the present invention, unless explicitly defined otherwise, references to orientation or positional relationship such as the terms "center", "lateral", "longitudinal", "horizontal", "vertical", "top", "bottom", "inner", "outer", "upper", "lower", "front", "rear", "left", "right", "clockwise", "counterclockwise", etc. are based on the orientation and positional relationship shown in the drawings and are merely for convenience of description and to simplify the description, and do not indicate or imply that the apparatus or element referred to must have a particular orientation or be constructed and operated in a particular orientation, nor should it be construed as limiting the particular scope of the invention.

In the claims, specification and drawings of the present invention, unless explicitly defined otherwise, the term "fixedly connected" or "fixedly connected" should be construed broadly, i.e. any connection between them without a displacement relationship or a relative rotation relationship, that is to say includes non-detachably fixedly connected, integrally connected and fixedly connected by other means or elements.

In the claims, specification and drawings of the present invention, the terms "comprising," having, "and variations thereof as used herein, are intended to be" including but not limited to.

Example 1

Referring to fig. 1, fig. 1 shows a fluorine pump dual cycle air conditioning system including a compressor 10, a condenser 20, a reservoir 30, a pump 40, a restrictor 50, an evaporator 60, a first control valve 70, a second control valve 80, and a heat exchanger 90.

The compressor 10, the condenser 20, the reservoir 30, the pump 40, the restrictor 50 and the evaporator 60 are sequentially connected in series through a pipeline, the first control valve 70 is connected in parallel between an input end and an output end of the compressor 10 through a pipeline to form a first branch 01, and the second control valve 80 is connected in parallel between an input end of the reservoir 30 and an output end of the pump 40 through a pipeline to form a second branch 02. In this embodiment, the first control valve 70 and the second control valve 80 are both check valves, and the restrictor 50 is an electronic expansion valve.

In this embodiment, the heat exchanger 90 is mainly configured to avoid cavitation and liquid impact, the pipeline between the condenser 20 and the liquid reservoir 30 is divided into a heat exchange section 03 and two non-heat exchange sections 04 connected with two ends of the heat exchange section 03, that is, the liquid of the condenser 20 sequentially passes through the non-heat exchange sections 04, the heat exchange section 03 and the non-heat exchange sections 04 to reach the liquid reservoir 30, the heat exchanger 90 absorbs heat of the heat exchange sections 03 through evaporation, the input end of the heat exchanger 90 is communicated with one of the non-heat exchange sections 04, the output end of the heat exchanger 90 is communicated with the input end of the compressor 10, in this embodiment, the input end of the heat exchanger 90 is communicated with the non-heat exchange section close to the liquid reservoir 30, and the liquid of the non-heat exchange section 04 communicated with the input end of the heat exchanger 90 partially flows to the liquid reservoir 30, and the liquid flowing to the heat exchanger 90 is evaporated to heat the heat exchange sections 03, so that the temperature is reduced after the liquid passes through the heat exchange sections 03, the temperature is also greatly reduced after the liquid flows to the liquid reservoir 30, the liquid supercooling degree in the liquid reservoir 30 is increased, the liquid is guaranteed to be absorbed by the liquid reservoir 40 or the heat exchange section 04 is well, the liquid refrigerant 40 is prevented from being inhaled into the compressor 10, and the compressor 10 is prevented from being sucked into the liquid air-conditioner, and the compressor is prevented from being in the state.

Specifically, the heat exchanger 90 includes a bypass expansion valve 92 and a heat exchange chamber 91, the outlet of the heat exchange chamber 91 forms an output end of the heat exchanger 90, a pipeline between the outlet of the heat exchange chamber 91 and the input end of the compressor 10 is a second pipeline 06, a pipeline between the inlet of the heat exchange chamber 91 and the non-heat exchange section 04 is a first pipeline 05, and the bypass expansion valve 92 is connected in series on the first pipeline 05. In this embodiment, the inlet of the heat exchange chamber 91 is close to the liquid storage device 30, that is, the inlet of the heat exchange chamber 91 is communicated with the non-heat exchange section 04 connected with the liquid storage device 30, and since the non-heat exchange section 04 is communicated with the outlet of the heat exchange section 03, the temperature of the liquid at the outlet of the heat exchange section 03 is lower than that at the inlet of the heat exchange section 03, and after the liquid at the outlet of the heat exchange section 03 enters the heat exchange chamber 91 through the bypass expansion valve 92, the heat exchange efficiency is better, and the design is more convenient when the pipelines are connected, and the overall pipeline length is shorter. The bypass expansion valve 92 is an electronic bypass expansion valve 92 in this embodiment, and the electronic bypass expansion valve 92 has higher adjustment capability and adjustment accuracy, which is beneficial to making the low-temperature high-pressure liquid delivered to the first pipeline 05 by the non-heat exchange section 04 become low-temperature low-pressure wet steam through throttling, and the wet steam evaporates in the heat exchange chamber 91 to take away the heat of the heat exchange section 03, and has a simple structure and is easy to implement.

The heat exchange chamber 91 mainly adopts the structure of the plate heat exchanger 90 in this embodiment, the plate heat exchanger 90 belongs to the prior art, and this embodiment will not be described in detail, wherein the inlet and the outlet of the heat exchange chamber 90 are respectively located at two ends of the heat exchange chamber, so that the flow direction of the gas in the heat exchange chamber 91 is opposite to the flow direction of the liquid in the heat exchange section 03, the heat exchange area is large, and the heat exchange efficiency is higher.

The reservoir 30 is a reservoir with its inlet higher than its outlet, further avoiding gas from entering the pump 40.

In this embodiment, the air conditioning system is divided into an indoor portion 100 and an outdoor portion, the indoor portion 100 includes a restrictor 50 and an evaporator 60, and the outdoor portion includes a compressor 10, a condenser 20, a liquid reservoir 30, a pump 40 and a heat exchanger 90, so that the first branch 01, the second branch 02, the first pipeline 05 and the second pipeline 06 are all located in the outdoor portion, the overall pipeline length is shorter, the pipeline laying is simple, and the engineering application is more convenient.

In practice, the air conditioning system further includes a controller electrically connected to and controlling the first control valve 70, the second control valve 80, the compressor 10, the pump 40, the bypass expansion valve 92, the condenser 20, the restrictor 50, and the evaporator 60.

Based on the air conditioning system, the air conditioning system can operate three refrigeration modes, namely a first refrigeration mode, a second refrigeration mode and a third refrigeration mode.

In the first refrigeration mode, the first control valve 70 is closed, the second control valve 80 is opened, the bypass expansion valve 92 and the restrictor 50 are opened, the pump 40 is closed, the compressor 10 is opened and forms a refrigeration cycle with the condenser 20 and the evaporator 60, specifically, the compressor 10 compresses the refrigerant circulated from the evaporator 60 to a high-temperature and high-pressure state, the gaseous refrigerant is compressed to be sent to the condenser 20 to be condensed into low-temperature and high-pressure refrigerant liquid, the refrigerant liquid is split at the outlet of the heat exchange section 03 through the heat exchange section 03, one part flows to the evaporator 60 through the non-heat exchange section 04, the second branch 02 and the restrictor 50, the other part flows to the heat exchange chamber 91 through the first pipeline 05 and the bypass expansion valve 92, and flows to the inlet of the compressor 10 through the second pipeline 06, and the liquid refrigerant absorbs heat and evaporates to enter the compressor 10 through the evaporator 60, thus completing a refrigeration cycle.

In the second refrigeration mode, the first control valve 70 and the second control valve 80 are closed, the bypass expansion valve 92 and the restrictor 50 are opened, the compressor 10 and the pump 40 are both opened and form a refrigeration cycle with the condenser 20 and the evaporator 60, specifically, after the refrigerant comes out of the compressor 10, the refrigerant enters the condenser 20 to be condensed into refrigerant liquid, the refrigerant liquid is split at the outlet of the heat exchange section 03, one part flows to the evaporator 60 through the non-heat exchange section 04, the liquid storage 40, the pump 40 and the restrictor 50, the other part flows to the heat exchange chamber 91 through the first pipeline 05 and the bypass expansion valve 92, flows to the inlet of the compressor 10 through the second pipeline 06, and the liquid refrigerant enters the compressor 10 through the heat absorption evaporation of the evaporator 60, thus completing a refrigeration cycle.

In the third refrigeration mode, the first control valve 70, the bypass expansion valve 92 and the restrictor 50 are all opened, the second control valve 80 is closed, the compressor 10 is closed, the pump 40, the condenser 20 and the evaporator 60 form a refrigeration cycle, specifically, the refrigerant enters the condenser 20 through the first branch 01 to be condensed into refrigerant liquid after exiting from the evaporator 60, the refrigerant liquid is split at the outlet of the heat exchange section 03, one part flows to the evaporator 60 through the non-heat exchange section 04, the pump 40 and the restrictor 50, the other part flows to the heat exchange chamber 91 through the first pipeline 05 and the bypass expansion valve 92, then flows to the condenser 20 through the second pipeline 06 and the first branch 01, and the liquid refrigerant absorbs heat and evaporates through the evaporator 60 to enter the first branch 01, so that one refrigeration cycle is completed.

In this embodiment, the heat exchanger 90 is provided to increase the supercooling degree of the liquid in the liquid storage device 30 and control the superheat degree of the inlet gas of the compressor 10, so that an external cold source is not needed, the whole system is simple in structure, the system is more reliable in operation, the pipeline is simple to lay, and the engineering application is more convenient.

Example 2

Embodiment 2 is substantially the same as embodiment 1 except that, referring to fig. 2, the inlet of the heat exchange chamber 91 is communicated with the non-heat exchange section 04 near the condenser 20, so that the liquid refrigerant condensed by the condenser 20 flows partially to the heat exchange chamber 91 through the first pipeline 05 and partially to the heat exchange section 03, the electronic expansion valve 92 throttles the low-temperature high-pressure liquid into low-temperature low-pressure wet steam to take away the heat of the heat exchange section 03, and the flow direction of the gas in the heat exchange chamber 91 is substantially the same as the flow direction of the liquid in the heat exchange section 03, so that the liquid in the heat exchange section 03 exchanges heat synchronously, and the heat exchange efficiency is high.

Example 3

The present invention provides a control method of a control system, which adopts the air conditioning system of embodiment 1 or 2, the control method comprising;

acquiring an outdoor temperature Tout, determining a refrigeration mode of operation according to the relation between Tout and a first set value T1 and a second set value T2, if Tout is greater than T1, determining to operate in the first refrigeration mode, if T2 is less than or equal to T1, determining to operate in the second refrigeration mode, and if Tout is less than or equal to T2, determining to operate in the third refrigeration mode;

Adjusting the refrigeration mode of operation according to the relation between the outdoor temperature Tout and the first set value T1, the second set value T2 and the third set value Deltat and the refrigeration mode of current operation;

if the current refrigerating mode is the first refrigerating mode, if T2 is less than or equal to Tout and less than or equal to T1-Deltat, switching to the second refrigerating mode;

If the current refrigerating mode is the second refrigerating mode, if Tout is more than or equal to T1+ [ delta ] T, switching to the first refrigerating mode, and if Tout is less than or equal to T2- [ delta ] T, switching to the third refrigerating mode;

If the current cooling mode is the third cooling mode, if T2+ [ delta ] T is less than or equal to Tout and less than or equal to T1, switching to the second cooling mode.

In a specific implementation, the temperature sensor may be configured to collect the outdoor temperature, the first set point is typically 15 ℃, and the second set point is typically 5 ℃. The third setting Δt can be set according to the measured temperature profile, in this embodiment Δt is 2-3 ℃.

The control method of the embodiment adopts the air conditioning system of embodiment 1 or 2, and has the same advantages as described above, in this scheme, when the first refrigeration mode is switched to the second refrigeration mode, the outdoor temperature needs to be less than or equal to T1- Δt, when the second refrigeration mode is switched to the first refrigeration mode, the outdoor temperature needs to be greater than or equal to t1+ [ Δt, so as to avoid frequent switching between the first refrigeration mode and the second refrigeration mode, when the second refrigeration mode is switched to the third refrigeration mode, the outdoor temperature needs to be less than or equal to T2- Δt, and when the third refrigeration mode is switched to the second refrigeration mode, the outdoor temperature needs to be greater than or equal to t2+ [ Δt, so as to avoid frequent switching between the second refrigeration mode and the third refrigeration mode, thereby avoiding frequent starting and stopping of the pump 40 or the compressor 10, and avoiding unstable indoor working conditions.

Example 3

The present invention provides a control method of a control system, which adopts the air conditioning system of embodiment 1 or 2, the control method comprising:

The method comprises the steps of obtaining an outdoor temperature Tout, an indoor temperature Tin, a first set value T1 and a refrigeration requirement, wherein the step of obtaining the refrigeration requirement comprises the step of obtaining an indoor target temperature Tset and a second set value T2, and the refrigeration requirement is (Tin-Tset)/T2 which is 100%.

If Tin-Tout is less than T1 and the refrigeration requirement is greater than 100%, operating in a first refrigeration mode;

if Tin-Tout is more than or equal to T1 and the refrigeration requirement is more than or equal to 100%, operating in a second refrigeration mode;

If Tin-Tout is more than or equal to T1 and the refrigeration requirement is more than 30% and less than 100%, the operation is performed in a third refrigeration mode.

In a specific implementation, the temperature sensor may be configured to collect the outdoor temperature and the indoor temperature, which belongs to the prior art, and this embodiment does not seem to be vermilion any more, in practical application, T1 is typically 20 ℃, and T2 is typically 3 ℃.

In the technical scheme, the refrigeration mode is adjusted according to the indoor and outdoor temperature difference and the refrigeration requirement, and the actual use condition is more met, so that the air conditioning system can always meet the refrigeration requirement, and the stable operation of indoor working conditions is ensured.

The foregoing description of the embodiments and description is presented to illustrate the scope of the invention, but is not to be construed as limiting the scope of the invention. Modifications, equivalents, and other improvements to the embodiments of the invention or portions of the features disclosed herein, as may occur to persons skilled in the art upon use of the invention or the teachings of the embodiments, are intended to be included within the scope of the invention, as may be desired by persons skilled in the art from a logical analysis, reasoning, or limited testing, in combination with the common general knowledge and/or knowledge of the prior art.

Claims (9)

1. The utility model provides a fluorine pump dual cycle air conditioning system, includes compressor (10), condenser (20), reservoir (30), pump (40), choke (50) and evaporimeter (60) that pass through the pipeline in series in proper order, characterized by still includes heat exchanger (90), the pipeline between condenser (20) and reservoir (30) divide into heat exchange section (03) and two non-heat exchange section (04) that link up with the both ends of heat exchange section (03), heat exchanger (90) absorb through the evaporation heat of heat exchange section (03), one of them non-heat exchange section (04) of input intercommunication of heat exchanger (90), the output intercommunication of heat exchanger (90) the input of compressor (10);

the heat exchanger (90) comprises a bypass expansion valve (92) and a heat exchange chamber (91), an outlet of the heat exchange chamber (91) forms an output end of the heat exchanger (90), a pipeline between an inlet of the heat exchange chamber (91) and a non-heat exchange section (04) is a first pipeline (05), and the bypass expansion valve (92) is connected in series on the first pipeline (05).

2. A fluorine pump dual cycle air conditioning system according to claim 1 wherein the inlet of the heat exchange chamber (91) communicates with a non-heat exchange section (04) adjacent the reservoir (30), the direction of flow of gas in the heat exchange chamber (91) being opposite to the direction of flow of liquid in the heat exchange section (03).

3. A fluorine pump dual cycle air conditioning system according to claim 2, characterized in that the air conditioning system is divided into an indoor section (100) and an outdoor section, the indoor section (100) comprising the restrictor (50) and the evaporator (60), the outdoor section comprising the compressor (10), the condenser (20), the reservoir (30), the pump (40) and the heat exchanger (90).

4. A fluorine pump dual cycle air conditioning system as claimed in claim 3 wherein said reservoir (30) has an inlet higher than an outlet thereof.

5. The fluorine pump dual cycle air conditioning system of claim 4, further comprising a first control valve (70) and a second control valve (80), said first control valve (70) being connected in parallel between the input and output of the compressor (10) via a conduit, said second control valve (80) being connected in parallel between the input of the reservoir (30) and the output of the pump (40) via a conduit.

6. A control method of a fluorine pump double-circulation air conditioning system, characterized in that it adopts the fluorine pump double-circulation air conditioning system according to claim 5, the control method comprising;

Acquiring an outdoor temperature Tout, determining a refrigeration mode of operation according to the relation between Tout and a first set value T1 and a second set value T2, if Tout is greater than T1, determining to operate in the first refrigeration mode, if T2 is less than or equal to T1, determining to operate in the second refrigeration mode, and if Tout is less than or equal to T2, determining to operate in the third refrigeration mode;

Adjusting the refrigeration mode of operation according to the relation between the outdoor temperature Tout and the first set value T1, the second set value T2 and the third set value Deltat and the refrigeration mode of current operation;

if the current refrigerating mode is the first refrigerating mode, if T2 is less than or equal to Tout and less than or equal to T1-Deltat, switching to the second refrigerating mode;

If the current refrigerating mode is the second refrigerating mode, if Tout is more than or equal to T1+ [ delta ] T, switching to the first refrigerating mode, and if Tout is less than or equal to T2- [ delta ] T, switching to the third refrigerating mode;

if the current cooling mode is the third cooling mode, if T2+ [ delta ] T is less than or equal to Tout and less than or equal to T1, switching to the second cooling mode;

In the first refrigeration mode, the compressor (10) is on and forms a refrigeration cycle with the condenser (20) and the evaporator (60), the pump (40) being off;

in the second refrigeration mode, both the compressor (10) and the pump (40) are on and form a refrigeration cycle with the condenser (20) and the evaporator (60);

In the third refrigeration mode, the compressor (10) is off, the pump (40) is on and forms a refrigeration cycle with the condenser (20) and the evaporator (60).

7. A control method of a fluorine pump dual cycle air conditioning system as set forth in claim 6 wherein in said first cooling mode said first control valve (70) is closed and said second control valve (80) and bypass expansion valve (92) are both open.

8. A control method of a fluorine pump dual cycle air conditioning system, characterized in that it adopts the fluorine pump dual cycle air conditioning system of claim 5, the control method comprising:

Acquiring an outdoor temperature Tout, an indoor temperature Tin and a refrigeration requirement, and acquiring a first set value T1;

If Tin-Tout is less than T1 and the refrigeration requirement is greater than 100%, operating in a first refrigeration mode;

if Tin-Tout is more than or equal to T1 and the refrigeration requirement is more than or equal to 100%, operating in a second refrigeration mode;

If Tin-Tout is more than or equal to T1 and the refrigeration requirement is more than 30% and less than 100%, operating in a third refrigeration mode;

In the first refrigeration mode, the compressor (10) is on and forms a refrigeration cycle with the condenser (20) and the evaporator (60), the pump (40) being off;

in the second refrigeration mode, both the compressor (10) and the pump (40) are on and form a refrigeration cycle with the condenser (20) and the evaporator (60);

In the third refrigeration mode, the compressor (10) is off, the pump (40) is on and forms a refrigeration cycle with the condenser (20) and the evaporator (60).

9. The method of claim 8, wherein obtaining the cooling requirement comprises obtaining an indoor target temperature Tset and a second set value T2, wherein the cooling requirement is (Tin-Tset)/T2 x 100%.