CN212362480U - Double-temperature air conditioning system - Google Patents
Double-temperature air conditioning system Download PDFInfo
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- CN212362480U CN212362480U CN202021689733.8U CN202021689733U CN212362480U CN 212362480 U CN212362480 U CN 212362480U CN 202021689733 U CN202021689733 U CN 202021689733U CN 212362480 U CN212362480 U CN 212362480U
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 51
- 239000003507 refrigerant Substances 0.000 claims description 61
- 238000001816 cooling Methods 0.000 claims description 35
- 238000010438 heat treatment Methods 0.000 claims description 31
- 230000001105 regulatory effect Effects 0.000 claims description 16
- 230000009977 dual effect Effects 0.000 claims description 10
- 239000003921 oil Substances 0.000 description 25
- 238000010521 absorption reaction Methods 0.000 description 10
- 238000007791 dehumidification Methods 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 10
- 230000008020 evaporation Effects 0.000 description 10
- 238000005057 refrigeration Methods 0.000 description 9
- 238000000034 method Methods 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000004781 supercooling Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 239000010687 lubricating oil Substances 0.000 description 6
- 230000005494 condensation Effects 0.000 description 5
- 238000009833 condensation Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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Abstract
The utility model provides a double-temperature air conditioning system, which comprises a compressor, wherein the compressor comprises two air suction ports and at least one air exhaust port; the outdoor heat exchanger is connected with an exhaust port of the compressor; the indoor heat exchange assembly comprises a first heat exchanger and a second heat exchanger, the first heat exchanger is connected with the outdoor heat exchanger through a first branch, a first throttling device is arranged on the first branch, and the first heat exchanger is connected with a first air suction port of the compressor; the second heat exchanger is connected with a second port of the outdoor heat exchanger, a second throttling device is arranged on a second branch, and the second heat exchanger is connected with a second air suction port of the compressor; the heat exchanger further comprises an intermediate heat exchanger, and the first branch and the second branch are connected with the intermediate heat exchanger simultaneously. The utility model discloses can improve the air conditioning system efficiency.
Description
Technical Field
The utility model relates to an air conditioning technology field especially relates to a two temperature air conditioning system.
Background
Two temperature air conditioning system set up two adjacent indoor heat exchangers at indoor, carry out step cooling dehumidification or intensification processing through to indoor return air for air conditioner system has realized that the heat transfer gradient is poor at indoor heat exchanger under refrigeration or the working condition of heating, has promoted the heat exchange efficiency of heat exchanger, and then promotes air conditioning system's whole efficiency.
However, the two supercooling degrees of the front and rear heat exchangers of the system under the heating condition are reduced compared with the supercooling degree under the heating condition of the conventional single-stage system, so that the inlet specific enthalpy of the evaporator is increased under the heating condition, the inlet-outlet specific enthalpy difference is reduced, the heat exchangers of the evaporator are reduced, and the energy efficiency of the system is reduced.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model provides a two temperature air conditioning system for solve the technical problem that the system energy efficiency that exists is low among the prior art at least, specifically:
in a first aspect, the present invention provides a dual temperature air conditioning system, including
A compressor comprising two suction ports and at least one discharge port;
the first port of the outdoor heat exchanger is connected with the exhaust port of the compressor;
an indoor heat exchange assembly comprises a first heat exchanger and a second heat exchanger,
a first port of the first heat exchanger is connected with a second port of the outdoor heat exchanger through a first branch, a first throttling device is arranged on the first branch, and a second port of the first heat exchanger is connected with a first air suction port of the compressor;
a first port of the second heat exchanger is connected with a second port of the outdoor heat exchanger through a second branch, a second throttling device is arranged on the second branch, and a second port of the second heat exchanger is connected with a second air suction port of the compressor;
the heat exchanger further comprises an intermediate heat exchanger, the first branch and the second branch are connected with the intermediate heat exchanger simultaneously, wherein,
on a refrigerant flow path, the first throttling device is positioned between the outdoor heat exchanger and the intermediate heat exchanger, and the second throttling device is positioned between the intermediate heat exchanger and the second heat exchanger; alternatively, the first and second electrodes may be,
on a refrigerant flow path, the first throttling device is positioned between the intermediate heat exchanger and the first heat exchanger, and the second throttling device is positioned between the second heat exchanger and the intermediate heat exchanger.
Further optionally, the heat exchanger further comprises a bypass adjusting branch connected to the first branch or the second branch, two ends of the bypass adjusting branch are connected to two sides of the intermediate heat exchanger,
the adjusting branch is used for adjusting the flow of the refrigerant flowing through the intermediate heat exchanger in the first branch or the second branch.
Further optionally, a flow regulating valve is disposed on the bypass regulating branch,
the first throttling device is located between the outdoor heat exchanger and the intermediate heat exchanger, the second throttling device is located between the intermediate heat exchanger and the second heat exchanger, the first end of the bypass adjusting branch is connected between the first throttling device and the intermediate heat exchanger, and the second end of the bypass adjusting branch is connected between the intermediate heat exchanger and the first heat exchanger.
Further optionally, a flow regulating valve is disposed on the bypass regulating branch, the first throttling device is located between the intermediate heat exchanger and the first heat exchanger, the second throttling device is located between the second heat exchanger and the intermediate heat exchanger, a first end of the bypass regulating branch is connected between the second throttling device and the intermediate heat exchanger, and a second end of the bypass regulating branch is connected between the intermediate heat exchanger and the second heat exchanger.
Further optionally, the compressor is a double suction single row compressor comprising one said discharge port; alternatively, the first and second electrodes may be,
the compressor is a double-suction double-row compressor and comprises two exhaust ports.
Further optionally, the dual-temperature air conditioning system is a single-cooling air conditioning system, and the compressor is directly connected with the outdoor heat exchanger and the indoor heat exchange assembly; alternatively, the first and second electrodes may be,
the dual-temperature air conditioning system is a cooling and heating air conditioning system and further comprises a four-way reversing valve, and the compressor is connected with the outdoor heat exchanger and the indoor heat exchange assembly through the four-way reversing valve.
Further optionally, the first heat exchanger and the second heat exchanger are arranged side by side, wherein,
in the airflow direction, the first heat exchanger is positioned on the windward side, and the second heat exchanger is positioned on the leeward side.
By arranging the intermediate heat exchanger, the inlet specific enthalpy of the second heat exchanger of the system is reduced, the inlet-outlet specific enthalpy difference is increased, and the second heat exchange effect is improved to some extent under the refrigeration working condition; under the heating working condition, the supercooling degree of the first heat exchanger of the system is increased, the inlet specific enthalpy of the outdoor heat exchanger is reduced, the inlet-outlet specific enthalpy difference is increased, the heat exchange effect of the outdoor heat exchanger is improved to some extent, and the system energy efficiency is improved.
Drawings
The above and other objects, features and advantages of the present disclosure will become more apparent by describing in detail exemplary embodiments thereof with reference to the attached drawings. The drawings described below are merely some embodiments of the present disclosure, and other drawings may be derived from those drawings by those of ordinary skill in the art without inventive effort.
Fig. 1 is a schematic view of a double-suction double-row single-cooling double-temperature air conditioning system according to an embodiment of the present invention;
fig. 2 is a schematic view of a double-suction double-row cooling and heating dual-temperature air conditioning system according to an embodiment of the present invention;
fig. 3 shows a schematic diagram of a double-suction single-row single-cooling double-temperature air conditioning system according to an embodiment of the present invention;
fig. 4 is a schematic view of a double-suction single-row cooling and heating dual-temperature air conditioning system according to an embodiment of the present invention;
fig. 5 is a schematic view of a double-suction double-row cooling and heating dual-temperature air conditioning system according to another embodiment of the present invention;
fig. 6 is a schematic view of a dual-suction single-row cooling and heating dual-temperature air conditioning system according to another embodiment of the present invention.
In the figure:
1. a double suction double row single compressor; 21. a first four-way valve; 22. a second four-way valve; 3. an outdoor heat exchanger; 41. a first throttling device; 42. a second throttling device; 43. a flow regulating valve; 51. a first heat exchanger; 52. a second heat exchanger; 6. an oil separator; 61. an intermediate heat exchanger; 7. an oil return valve; 8. an indoor fan; 9. an outdoor fan.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, 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, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
The terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the embodiments of the present invention and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise, and "a plurality" typically includes at least two, but does not exclude the presence of at least one.
It should be understood that the term "and/or" as used herein is merely one type of association that describes an associated object, meaning that three relationships may exist, e.g., a and/or B may mean: a exists alone, A and B exist simultaneously, and B exists alone. In addition, the character "/" herein generally indicates that the former and latter related objects are in an "or" relationship.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a good or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such good or system. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other like elements in a commodity or system that includes the element.
By arranging the intermediate heat exchanger, the inlet specific enthalpy of the second heat exchanger of the system is reduced, the inlet-outlet specific enthalpy difference is increased, and the second heat exchange effect is improved to some extent under the refrigeration working condition; under the heating working condition, the supercooling degree of the first heat exchanger of the system is increased, the inlet specific enthalpy of the outdoor heat exchanger is reduced, the inlet-outlet specific enthalpy difference is increased, the heat exchange effect of the outdoor heat exchanger is improved to some extent, and the system energy efficiency is improved. In addition, the load ratio of the front evaporator and the rear evaporator can be controlled by additionally arranging a bypass adjusting branch, and the proportion of the cooling load and the dehumidifying load in the actual refrigerating process can be adjusted. The present invention will be described in detail with reference to the following embodiments.
As shown in fig. 1, 2, 3 and 4, a dual temperature air conditioning system includes a compressor including two suction ports and at least one discharge port;
the first port of the outdoor heat exchanger 3 is connected with the exhaust port of the compressor, the outdoor heat exchanger further comprises an outdoor fan 9, the outdoor fan 9 blows air towards the outdoor heat exchanger 3 to generate airflow flowing through the outdoor heat exchanger 3, and the heat exchange efficiency of the outdoor heat exchanger 3 is improved;
an indoor heat exchange assembly, including a first heat exchanger 51 and a second heat exchanger 52,
a first port of the first heat exchanger 51 is connected with a second port of the outdoor heat exchanger 3 through a first branch, a first throttling device 41 is arranged on the first branch, and a second port of the first heat exchanger 51 is connected with a first air suction port of the compressor;
a first port of the second heat exchanger 52 is connected with a second port of the outdoor heat exchanger 3 through a second branch, a second throttling device 42 is arranged on the second branch, and a second port of the second heat exchanger 52 is connected with a second suction port of the compressor;
the indoor heat exchange assembly further comprises an indoor fan 8, the indoor fan 8 blows air towards the first heat exchanger 51 and the second heat exchanger 52 to generate air flow, and the first heat exchanger 51 and the second heat exchanger 52 are arranged side by side, wherein in the air flow direction, the first heat exchanger 51 is positioned on the windward side, and the second heat exchanger 52 is positioned on the leeward side.
And further comprises an intermediate heat exchanger 61, wherein the first branch and the second branch are simultaneously connected with the intermediate heat exchanger 61, wherein,
in the refrigerant flow path, the first throttling device 41 is located between the outdoor heat exchanger 3 and the intermediate heat exchanger 61, and the second throttling device 42 is located between the intermediate heat exchanger 61 and the second heat exchanger 52; alternatively, the first and second electrodes may be,
in the refrigerant flow path, the first throttle device 41 is located between the intermediate heat exchanger 61 and the first heat exchanger 51, and the second throttle device 42 is located between the second heat exchanger 52 and the intermediate heat exchanger 61.
Preferably, the heat exchanger further comprises a bypass adjusting branch connected to the first branch or the second branch, a flow adjusting valve 43 is arranged on the bypass adjusting branch, two ends of the bypass adjusting branch are connected to two sides of the intermediate heat exchanger 61, and the adjusting branch is used for adjusting the flow of the refrigerant flowing through the intermediate heat exchanger 61 in the first branch or the second branch.
As shown in fig. 1 to 4, the first throttling device 41 is located between the outdoor heat exchanger 3 and the intermediate heat exchanger 61, the second throttling device 42 is located between the intermediate heat exchanger 61 and the second heat exchanger 52, a first end of the bypass adjusting branch is connected between the first throttling device 41 and the intermediate heat exchanger 61, and a second end of the bypass adjusting branch is connected between the intermediate heat exchanger 61 and the first heat exchanger 51. The bypass adjusting branch is used for adjusting the flow rate of the refrigerant entering the intermediate heat exchanger 61 from the first branch.
As shown in fig. 5 and 6, the first throttling device 41 is located between the intermediate heat exchanger 61 and the first heat exchanger 51, the second throttling device 42 is located between the second heat exchanger 52 and the intermediate heat exchanger 61, the first end of the bypass adjusting branch is connected between the second throttling device 42 and the intermediate heat exchanger 61, and the second end of the bypass adjusting branch is connected between the intermediate heat exchanger 61 and the second heat exchanger 52. The bypass adjusting branch is used for adjusting the flow rate of the refrigerant entering the intermediate heat exchanger 61 through the second branch.
Preferably, as shown in fig. 1, 3 and 6, the compressor is a double-suction single-row compressor 1, and includes one exhaust port, the dual-temperature air conditioning system is a single-cooling air conditioning system, the compressor is directly connected to the outdoor heat exchanger 3 and the indoor heat exchange assembly, or the dual-temperature air conditioning system is a cooling and heating air conditioning system, and further includes a four-way reversing valve, and the compressor is connected to the outdoor heat exchanger 3 and the indoor heat exchange assembly through the four-way reversing valve.
Or, as shown in fig. 2, 4, and 5, the compressor is a double-suction double-row compressor 11, and includes two exhaust ports, and further includes an oil separator 6, one of the exhaust ports is connected to the oil separator 6, the lubricating oil carried in the refrigerant is separated by the oil separator 6, the oil separator 6 is further connected to an oil sump of the compressor by an oil return valve 7, and the separated lubricating oil flows back to the oil sump of the compressor by the oil return valve 7. The refrigerant discharged through the oil separator 6 and the refrigerant directly discharged from the discharge port are merged and flow into the outdoor heat exchanger 3.
Preferably, the dual-temperature air conditioning system is a single-cooling air conditioning system, the compressor is directly connected with the outdoor heat exchanger 3 and the indoor heat exchange assembly, or the dual-temperature air conditioning system is a cooling and heating air conditioning system and further comprises a four-way reversing valve, and the compressor is connected with the outdoor heat exchanger 3 and the indoor heat exchange assembly through the four-way reversing valve.
As shown in fig. 2, a double-suction double-row cooling and heating air conditioning system is taken as an example for detailed description:
the compressor is a double-suction double-row single compressor, one exhaust port of the compressor is connected with the oil separator 6, and meanwhile, an oil return port of the oil separator 6 is connected with an oil pool of the compressor through an oil return valve 7 and used for returning oil. The oil separator 6 is connected to the port D of the second four-way valve 22, and the other discharge port of the compressor is connected to the port D of the first four-way valve 21. A port C of the first four-way valve 21 and a port C of the second four-way valve 22 are connected to a first port of the outdoor heat exchanger 3; the port S of the first four-way valve 21 and the port S of the second four-way valve 22 are respectively one suction port of the compressor: a second port of the first heat exchanger 51 is connected to the port E of the first four-way valve 21, and a second port of the second heat exchanger 52 is connected to the port E of the second four-way valve 22.
The second port of the outdoor heat exchanger 3 is connected to the first port of the first heat exchanger 51 through a first branch and to the second heat exchanger 52 through a second branch, and the first branch is provided with the first throttling device 41 and the second branch is provided with the second throttling device 42.
The intermediate heat exchanger 61 is connected to the first branch and the second branch at the same time, the first throttling device 41 and the second throttling device 42 are respectively positioned at two sides of the intermediate heat exchanger 61, the first throttling device 41 is positioned at one side close to the outdoor heat exchanger 3, and the second throttling device 42 is positioned at one side close to the second heat exchanger 52.
The bypass adjusting branch is connected to the first branch, two ends of the bypass adjusting branch are respectively connected between the first throttling device 41 and the intermediate heat exchanger 61, and between the intermediate heat exchanger 61 and the first heat exchanger 51, and the bypass adjusting branch is provided with a flow adjusting valve 43.
The principle of the double-suction double-row single-cooling air conditioning system, the double-suction single-row single-cooling air conditioning system and the double-suction single-row cooling and heating air conditioning system is the same as that of the above systems, and the detailed description thereof is omitted.
The utility model also provides a control method of two temperature air conditioning system, include:
in the cooling mode, the air conditioner is operated,
the refrigerant passing through the indoor heat exchange assembly enters the compressor for compression, the compressed high-temperature and high-pressure exhaust gas enters the outdoor heat exchanger 3 for condensation, and the low-temperature and high-pressure refrigerant flowing through the outdoor heat exchanger 3 is throttled and depressurized in two ways, wherein a part of the refrigerant enters the first branch, flows through the first throttling device 41 and the intermediate heat exchanger 61, and enters the first heat exchanger 51 for evaporation and heat absorption;
the other part of the refrigerant enters the second branch, flows through the intermediate heat exchanger 61 and the second throttling device 42, and enters the second heat exchanger 52 for evaporation and heat absorption.
Preferably, the dual temperature air conditioning system comprises a bypass adjusting branch, and the control method comprises the following steps:
setting the threshold value of the air humidity parameter as B, the actual indoor air humidity parameter value as A,
in the cooling mode, the air conditioner is operated,
when A is less than or equal to B,
the flow regulating valve 43 is in a fully open state, the refrigerant passing through the first heat exchanger 51 and the indoor heat exchanger respectively enters the compressor for compression, the compressed high-temperature and high-pressure exhaust gas enters the outdoor heat exchanger 3 for condensation, the low-temperature and high-pressure refrigerant passing through the outdoor heat exchanger 3 is divided into two paths for throttling and pressure reduction, wherein,
a part of refrigerant enters the first branch, flows through the first throttling device 41 and the bypass adjusting branch, and enters the first heat exchanger 51 for evaporation and heat absorption;
the other part of the refrigerant enters the second branch, flows through the second throttling device 42, enters the second heat exchanger 52 for evaporation and heat absorption, and completes the circulation; alternatively, the first and second electrodes may be,
when A is larger than B, the flow regulating valve 43 is regulated to increase the dehumidification load of the indoor heat exchange assembly, the refrigerant passing through the first heat exchanger 51 and the second heat exchanger 52 respectively enters the compressor for compression, the compressed high-temperature high-pressure exhaust gas enters the outdoor heat exchanger 3 for condensation, the low-temperature high-pressure refrigerant flowing through the outdoor heat exchanger 3 is subjected to throttling depressurization in two paths, wherein,
a part of refrigerant enters the first branch path, flows through the first throttling device 41 for throttling, a part of throttled refrigerant enters the intermediate heat exchanger 61 for heat exchange, and the other part of throttled refrigerant enters the first heat exchanger 51 for evaporation and heat absorption after being merged with the refrigerant after heat exchange through the flow regulating valve 43;
and the other part of the refrigerant enters the second branch, flows through the intermediate heat exchanger 61 and the second throttling device 42, enters the second heat exchanger 52, evaporates and absorbs heat, and completes the circulation.
Preferably, in the present embodiment, the air humidity parameter is a parameter capable of reflecting air humidity, such as air relative humidity, air moisture content, and the like.
Further comprising:
and a heating mode in which the flow rate adjustment valve 43 is closed.
As shown in particular in figure 5 of the drawings,
the refrigeration system and the control method thereof are described below by taking a double-suction double-discharge cooling and heating type air conditioning system as an example. Assume that the indoor air relative humidity is a and the target relative humidity is B.
(1) In the refrigeration mode, when A is less than or equal to B, the flow bypass valve 43 is in a full open state, and at the moment, the refrigerant does not pass through the heat exchange of the intermediate heat exchanger 61, and the indoor cooling and dehumidification can be realized only by adjusting the first throttling devices 41 and 42; the specific process is as follows:
the refrigerant passing through the first heat exchanger 51 and the indoor heat exchanger 52 respectively enters the compressor 1 through the first four-way valve 21 and the four-way reversing valve 22 for compression, the compressed high-temperature and high-pressure exhaust gas is divided into two paths, one path is directly discharged out of the compressor, the other path separates out the lubricating oil carried by the refrigerant through the oil separator 6, the lubricating oil returns to an oil pool through an oil return valve 7, the two paths of high-temperature and high-pressure refrigerant are converged and then enter the outdoor heat exchanger 3 for condensation, the low-temperature and high-pressure refrigerant passing through the outdoor heat exchanger 3 is divided into two paths for throttling and pressure reduction, and the other path passes through the first throttling device 41 and the bypass flow valve 43 and; the other path flows through the second throttling device 42 and enters the indoor rear heat exchanger 52 for evaporation and heat absorption, and the cycle is completed.
(2) In the cooling mode, when A is larger than B, the bypass flow valve 43 is gradually adjusted, the dehumidification load of the indoor heat exchanger is increased, and the indoor air relative humidity A is controlled to be smaller than or equal to the target relative humidity B. At this time, a part of the refrigerant throttled by the first throttle device 41 exchanges heat with the refrigerant before being throttled by the second throttle device 42 in the intermediate heat exchanger 61, so that specific enthalpy of the refrigerant entering the indoor heat exchanger 52 is reduced, thereby increasing a dehumidification load of the indoor heat exchanger 52. The specific process is as follows:
the refrigerant passing through the first heat exchanger 51 and the indoor heat exchanger 52 respectively enters the compressor 1 through the first four-way valve 21 and the four-way reversing valve 22 for compression, the compressed high-temperature and high-pressure exhaust gas is divided into two paths, one path is directly discharged out of the compressor, the other path separates out the lubricating oil carried by the refrigerant through the oil separator 6, the lubricating oil returns to an oil pool through the oil return valve 7, the two paths of high-temperature and high-pressure refrigerant are converged and then enter the outdoor heat exchanger 3 for condensation, the low-temperature and high-pressure refrigerant passing through the outdoor heat exchanger 3 is divided into two paths for throttling and depressurization, one path passes through the first throttling device 41 for throttling, one part of the throttled refrigerant enters the intermediate heat exchanger 61 for heat exchange, and the other part passes through the bypass flow valve 43 and is converged with the; the other path of the heat flows through the intermediate heat exchanger 61 and the second throttling device 42 and enters the second heat exchanger 52 for evaporation and heat absorption, and the cycle is completed.
(3) In the heating mode, no dehumidification is needed in the room, so the bypass throttle valve is in the fully closed state, the electronic expansion valves 41 and 42 can be adjusted according to the system state, and the flow state of the system at this time is: the refrigerant flowing through the indoor heat exchanger 52 and the second throttle device 42 exchanges heat with the refrigerant flowing through the first heat exchanger 51 in the intermediate heat exchanger 61.
The system of the double-suction double-row single-cooling type air conditioner, the double-suction single-row single-cooling type air conditioner and the double-suction single-row cooling and heating type air conditioner also adopts the improved mode.
Alternatively, the first and second electrodes may be,
as shown in fig. 6, the control method of the dual-temperature air conditioning system includes:
in the cooling mode, the air conditioner is operated,
the refrigerant passing through the first heat exchanger 51 and the second heat exchanger 52 is compressed by the compressor 1, the compressed high-temperature and high-pressure exhaust gas enters the outdoor heat exchanger 3, the high-temperature and high-pressure refrigerant is condensed in the outdoor heat exchanger 3, the low-temperature and high-pressure refrigerant passing through the outdoor heat exchanger 3 is throttled and depressurized in two paths, wherein,
a part of refrigerant enters the first branch path, flows through the intermediate heat exchanger 61 and the first throttling device 41, enters the first heat exchanger 51, and is evaporated and absorbs heat;
the other part of the refrigerant enters the second branch, flows through the second throttling device 42, then enters the intermediate heat exchanger 61 and the flow regulating valve 43 respectively in two paths, and finally enters the second heat exchanger 52 for evaporation and heat absorption, so as to complete the circulation.
Further comprising:
and a heating mode in which the flow rate adjustment valve 43 is closed.
As shown in particular in figure 5 of the drawings,
is a double-suction double-row cooling and heating type air conditioner system. In a refrigeration mode, refrigerants passing through a first heat exchanger 51 and an indoor heat exchanger 52 respectively enter two cylinders of a compressor 1 through a first four-way valve 21 and a four-way reversing valve 22 to be compressed, high-temperature and high-pressure exhaust after compression is divided into two paths, one path of the high-temperature and high-pressure exhaust is converged with the refrigerant passing through an oil separator 6, a port D and a port C of the four-way reversing valve 22 and the other path of the high-temperature and high-pressure exhaust and then enters a condenser 3, the high-temperature and high-pressure refrigerant is condensed in an outdoor heat exchanger 3, the low-temperature and high-pressure refrigerant passing through the outdoor heat exchanger 3 is divided into two paths to be throttled and depressurized, and the other path of the high-temperature and high-pressure refrigerant passes through an; the other path firstly flows through the second throttling device 42, then enters the intermediate heat exchanger 61 and the bypass flow valve 43 respectively in two paths, and finally enters the second heat exchanger 52 for evaporation and heat absorption to complete the circulation. Wherein, the proportion of indoor heat exchanger cooling load and dehumidification load can be realized through the flow of adjusting bypass flow valve.
In the heating mode, the refrigerant flowing through the first heat exchanger 51 and throttled by the first throttling device 41 exchanges heat with the refrigerant flowing through the indoor heat exchanger 52 in the intermediate heat exchanger 61, so that the cold-out supercooling degree of the indoor heat exchanger 52 is increased, and the heating capacity of the indoor heat exchanger 52 is improved.
As shown in fig. 6, a double suction single discharge cooling and heating type air conditioner system is provided. In a refrigeration mode, refrigerants of a first heat exchanger 51 and an indoor heat exchanger 52 respectively enter two cylinders of a compressor 1 through a port E and a port S of a first four-way valve 21 and a port E and a port S of a four-way reversing valve 22 to be compressed, high-temperature and high-pressure exhaust gas after compression is divided into two paths, one path of high-temperature and high-pressure exhaust gas passes through the port D and the port C of the first four-way valve 21 and the other path of high-temperature and high-pressure exhaust gas passes through the port D and the port C of the four-way reversing valve 22 to be converged and then enters an outdoor heat exchanger 3, the high-temperature and high-pressure refrigerant is condensed in the outdoor heat exchanger 3, the low-temperature and high-pressure refrigerant after flowing through the outdoor heat exchanger 3 is divided into two paths to; the other path firstly flows through the second throttling device 42, then enters the intermediate heat exchanger 61 and the bypass flow valve 43 respectively in two paths, and finally enters the second heat exchanger 52 for evaporation and heat absorption to complete the circulation. Wherein, the proportion of indoor heat exchanger cooling load and dehumidification load can be realized through the flow of adjusting bypass flow valve.
In the heating mode, the refrigerant flowing through the first heat exchanger 51 and throttled by the first throttling device 41 exchanges heat with the refrigerant flowing through the indoor heat exchanger 52 in the intermediate heat exchanger 61, so that the cold-out supercooling degree of the indoor heat exchanger 52 is increased, and the heating capacity of the indoor heat exchanger 52 is improved.
The dual-temperature air conditioning brother system provided by the utility model can realize the step cooling and dehumidification of the indoor air under the refrigeration working condition, and the dehumidification capability and the air conditioning energy efficiency have better effect compared with the conventional air conditioning; under the heating condition, the system can realize the cascade heating of the indoor air and effectively improve the heat exchange efficiency of the system. The system improves the heat exchange effect of the heat exchanger under heating working conditions and refrigeration working conditions after the subcooler is added due to the fact that the supercooling degree of the indoor heat exchanger is smaller under the heating working conditions of the indoor dual-temperature system, and therefore the upgrading of the system energy efficiency is achieved. In addition, the load ratio of the front evaporator and the rear evaporator can be changed by adding the flow regulating valve, and the proportion of the cooling load and the dehumidifying load in the actual refrigerating process is regulated.
Exemplary embodiments of the present disclosure are specifically illustrated and described above. It is to be understood that the present disclosure is not limited to the precise arrangements, instrumentalities, or instrumentalities described herein; on the contrary, the disclosure is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
Claims (7)
1. A dual temperature air conditioning system characterized in that: comprises that
A compressor comprising two suction ports and at least one discharge port;
the first port of the outdoor heat exchanger (3) is connected with the exhaust port of the compressor;
an indoor heat exchange assembly comprising a first heat exchanger (51) and a second heat exchanger (52),
a first port of the first heat exchanger (51) is connected with a second port of the outdoor heat exchanger (3) through a first branch, a first throttling device (41) is arranged on the first branch, and a second port of the first heat exchanger (51) is connected with a first air suction port of the compressor;
a first port of the second heat exchanger (52) is connected with a second port of the outdoor heat exchanger (3) through a second branch, a second throttling device (42) is arranged on the second branch, and a second port of the second heat exchanger (52) is connected with a second suction port of the compressor;
further comprising an intermediate heat exchanger (61), the first branch and the second branch being connected to the intermediate heat exchanger (61) simultaneously, wherein,
on a refrigerant flow path, the first throttling device (41) is positioned between the outdoor heat exchanger (3) and the intermediate heat exchanger (61), and the second throttling device (42) is positioned between the intermediate heat exchanger (61) and the second heat exchanger (52); alternatively, the first and second electrodes may be,
in the refrigerant flow path, the first throttling device (41) is positioned between the intermediate heat exchanger (61) and the first heat exchanger (51), and the second throttling device (42) is positioned between the second heat exchanger (52) and the intermediate heat exchanger (61).
2. A dual temperature air conditioning system as set forth in claim 1, wherein: the heat exchanger also comprises a bypass adjusting branch which is connected to the first branch or the second branch, two ends of the bypass adjusting branch are connected to two sides of the intermediate heat exchanger (61),
the adjusting branch is used for adjusting the flow of the refrigerant flowing through the intermediate heat exchanger (61) in the first branch or the second branch.
3. A dual temperature air conditioning system as set forth in claim 2, wherein: a flow regulating valve (43) is arranged on the bypass regulating branch,
the first throttling device (41) is located between the outdoor heat exchanger (3) and the intermediate heat exchanger (61), the second throttling device (42) is located between the intermediate heat exchanger (61) and the second heat exchanger (52), a first end of the bypass adjusting branch is connected between the first throttling device (41) and the intermediate heat exchanger (61), and a second end of the bypass adjusting branch is connected between the intermediate heat exchanger (61) and the first heat exchanger (51).
4. A dual temperature air conditioning system as set forth in claim 2, wherein: the bypass adjusting branch is provided with a flow adjusting valve (43), the first throttling device (41) is located between the intermediate heat exchanger (61) and the first heat exchanger (51), the second throttling device (42) is located between the second heat exchanger (52) and the intermediate heat exchanger (61), the first end of the bypass adjusting branch is connected between the second throttling device (42) and the intermediate heat exchanger (61), and the second end of the bypass adjusting branch is connected between the intermediate heat exchanger (61) and the second heat exchanger (52).
5. A dual temperature air conditioning system as claimed in claim 3 or 4, wherein: the compressor is a double-suction single-row compressor and comprises one exhaust port; alternatively, the first and second electrodes may be,
the compressor is a double-suction double-row compressor and comprises two exhaust ports.
6. A dual temperature air conditioning system as set forth in claim 5, wherein: the dual-temperature air conditioning system is a single-cooling air conditioning system, and the compressor is directly connected with the outdoor heat exchanger (3) and the indoor heat exchange assembly; alternatively, the first and second electrodes may be,
the dual-temperature air conditioning system is a cooling and heating air conditioning system and further comprises a four-way reversing valve, and the compressor is connected with the outdoor heat exchanger (3) and the indoor heat exchange assembly through the four-way reversing valve.
7. A dual temperature air conditioning system as set forth in claim 6, wherein: the first heat exchanger (51) and the second heat exchanger (52) being arranged side by side, wherein,
in the airflow direction, the first heat exchanger (51) is positioned on the windward side, and the second heat exchanger (52) is positioned on the leeward side.
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| CN202021689733.8U CN212362480U (en) | 2020-08-13 | 2020-08-13 | Double-temperature air conditioning system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202021689733.8U CN212362480U (en) | 2020-08-13 | 2020-08-13 | Double-temperature air conditioning system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111998565A (en) * | 2020-08-13 | 2020-11-27 | 珠海格力电器股份有限公司 | Dual-temperature air conditioning system and control method thereof |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111998565A (en) * | 2020-08-13 | 2020-11-27 | 珠海格力电器股份有限公司 | Dual-temperature air conditioning system and control method thereof |
| CN111998565B (en) * | 2020-08-13 | 2024-02-27 | 珠海格力电器股份有限公司 | Double-temperature air conditioning system and control method thereof |
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