CN208901694U - Air conditioner circulation system and air conditioner - Google Patents

Abstract

The utility model relates to an air conditioner circulation system, including compressor, oil separator, first heat exchanger, throttling element, second heat exchanger and oil return branch road. The compressor, the oil separator, the first heat exchanger and the second heat exchanger form a loop, an oil return branch inlet of the oil return branch is communicated with an oil return hole of the oil separator, an oil return branch outlet of the oil return branch is communicated with an air inlet of the compressor, and a throttling device with adjustable opening degree is arranged on the oil return branch. According to different operation conditions, the opening degree of the throttling device is adjusted, normal oil return of the unit is guaranteed, energy loss of oil return bypass is reduced, reliability of unit operation is improved, and energy loss is reduced.

Description

Air conditioner circulation system and air conditioner

Technical Field

The utility model relates to an air conditioner technical field especially relates to an air conditioner circulation system and air conditioner.

Background

The existing air conditioning system includes an indoor heat exchanger, an outdoor heat exchanger, and a compressor, and a refrigerant circulates in a loop formed by the above components. One of the indoor heat exchanger and the outdoor heat exchanger serves as an evaporator, and the other serves as a condenser. The high-temperature and high-pressure refrigerant from the compressor enters the condenser to be condensed into liquid, then flows into the evaporator to be evaporated into low-temperature and low-pressure gas, and finally returns to the compressor. The compressor is used as a core component of the whole air conditioning system, and once the compressor is operated in an oil shortage state, the compressor is overheated or even burnt out, so that the whole system cannot operate normally, and the reliability of the operation of the system is reduced. Therefore, it is very important to control the oil return of the air conditioning system.

In the prior art, oil return of an air conditioning system is performed by arranging an oil return capillary tube for high-low pressure bypass between an oil separator and a compressor air inlet, and the oil return capillary tube has the following defects:

1) in the oil return process from the oil separator, an oil return bypass exists, and great energy loss is generated;

2) the throttling effect of the capillary tube is consistent all the time, and if the capillary tube is small, the unit cannot return oil normally; if the capillary is thick, the bypass capacity of the unit is large.

SUMMERY OF THE UTILITY MODEL

The utility model discloses exist when adopting the capillary oil return to current air conditioning system, the unable normal oil return of the thin unit of capillary, the great problem of the thick unit ability bypass of capillary provides an air conditioner circulation system, air conditioner and air conditioner.

An air conditioner circulation system comprises a compressor, an oil separator, a first heat exchanger, a throttling element, a second heat exchanger and an oil return branch, wherein the oil separator comprises a first oil separator, a second oil separator and a second oil separator, the first oil separator comprises a first oil separator, the second oil separator comprises a first heat exchanger, a second oil separator:

the compressor, the oil separator, the throttling element of the first heat exchanger, and the second heat exchanger form a loop;

an oil return branch inlet of the oil return branch is communicated with an oil return hole of the oil separator, an oil return branch outlet of the oil return branch is communicated with an air inlet of the compressor, and a throttling device with an adjustable opening degree is arranged on the oil return branch.

In one embodiment, the throttle device with adjustable opening degree is a first electronic expansion valve.

In one embodiment, a first filter is arranged between an oil return hole of the oil separator and the throttle device with the adjustable opening degree.

In one embodiment, the heat exchange gas-liquid separator further comprises a heat exchange gas-liquid separator, and the heat exchange gas-liquid separator comprises a heat exchange branch and a gas-liquid separation branch:

a first refrigerant port of the heat exchange branch is communicated with a second opening of the second heat exchanger, and a second refrigerant port of the heat exchange branch is communicated with a second opening of the first heat exchanger;

and a refrigerant inlet of the gas-liquid separation branch is selectively communicated with the first opening of the first heat exchanger or the first opening of the second heat exchanger, and a refrigerant outlet of the gas-liquid separation branch is communicated with the air inlet of the compressor.

In one embodiment, the compressor further comprises a gas-liquid separator, a refrigerant inlet of the gas-liquid separator is communicated with a refrigerant outlet of the gas-liquid separation branch, and a refrigerant outlet of the gas-liquid separator is communicated with the gas inlet of the compressor.

In one embodiment, the air conditioner further comprises a four-way valve, a first port of the four-way valve is communicated with an exhaust port of the compressor, a second port of the four-way valve is communicated with a first opening of the first heat exchanger, a third port of the four-way valve is communicated with a refrigerant inlet of the gas-liquid separation branch, a fourth port of the four-way valve is communicated with a first opening of the second heat exchanger, wherein,

a first port of the four-way valve is communicated with a second port of the four-way valve, and a third port of the four-way valve is communicated with a fourth port of the four-way valve;

or,

and a first port of the four-way valve is communicated with a fourth port of the four-way valve, and a second port of the four-way valve is communicated with a third port of the four-way valve.

In one embodiment, the throttling element is a second electronic expansion valve, and the second electronic expansion valve is disposed between the second opening of the first heat exchanger and the second refrigerant port of the heat exchange branch.

In one embodiment, a second filter is further disposed between the second opening of the first heat exchanger and the second electronic expansion valve.

In one embodiment, a third filter is disposed between the second opening of the second heat exchanger and the first refrigerant port of the heat exchange branch.

An air conditioner includes the air conditioning cycle system as described above.

Based on the technical scheme, the embodiment of the utility model provides a can produce following technological effect at least:

the air conditioner circulating system comprises a compressor, an oil separator, a first heat exchanger, a throttling element, a second heat exchanger and an oil return branch. The compressor, the oil separator, the first heat exchanger and the second heat exchanger form a loop, an oil return branch inlet of the oil return branch is communicated with an oil return hole of the oil separator, an oil return branch outlet of the oil return branch is communicated with an air inlet of the compressor, and a throttling device with adjustable opening degree is arranged on the oil return branch. According to different operating conditions, the opening degree of the throttling device is adjusted, lubricating oil in the oil separator is guaranteed to return to the compressor quickly, damage caused by oil shortage of the compressor is avoided, and the reliability of the system is improved. Meanwhile, the high-temperature and high-pressure gaseous refrigerant coming out of the exhaust port of the compressor can be prevented from directly returning to the air inlet of the compressor through the throttling device, and energy loss caused by unnecessary oil return bypass is reduced.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification.

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

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

fig. 2 is a schematic diagram illustrating an air conditioning cycle system according to an embodiment of the present invention when operating in a heating mode;

fig. 3 is a schematic diagram illustrating an air conditioning cycle system according to an embodiment of the present invention when the air conditioning cycle system is in a cooling mode or a defrosting mode.

Description of reference numerals:

100-compressor

110-compressor discharge

Air inlet of 120-compressor

200-oil separator

210-oil separator air inlet

Air vent of 220-oil separator

300-first heat exchanger

310-first opening of first heat exchanger

320-second opening of the first Heat exchanger

400-second heat exchanger

410-first opening of second Heat exchanger

420-second opening of second heat exchanger

500-oil return branch

510-oil return branch inlet

520-oil return branch outlet

530-throttling device

540-first Filter

600-heat exchange gas-liquid separator

610-heat exchange branch

611-first refrigerant port of heat exchange branch

Second refrigerant port of 612-heat exchange branch

620-gas-liquid separation branch

621-refrigerant inlet of gas-liquid separation branch

622-refrigerant outlet of gas-liquid separation branch

700-gas-liquid separator

710-refrigerant inlet of gas-liquid separator

720-refrigerant outlet of gas-liquid separator

800-four-way valve

810-first port of four-way valve

820-second port of four-way valve

830-third Port of four-way valve

840-fourth port of four-way valve

900-second electronic expansion valve

910-second Filter

920-third Filter

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. The following description of the embodiments is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. In contrast, when an element is referred to as being "directly on" another element, there are no intervening elements present. In contrast, when an element is referred to as being "directly connected" to another element, there are no intervening elements present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only.

In the description of the present invention, it is to be understood that the terms "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are merely for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, are not to be construed as limiting the present invention.

The technical solution provided by the present invention is explained in more detail with reference to fig. 1 to 3.

Referring to fig. 1, an embodiment of the present invention provides an air conditioning cycle system, including a compressor 100, an oil separator 200, a first heat exchanger 300, a throttling element, a second heat exchanger 400, and an oil return branch 500. The compressor 100, the oil separator 200, the first heat exchanger 300, the throttling element, and the second heat exchanger 400 form a circuit. The air inlet 210 of the oil separator 200 is communicated with the air outlet 120 of the compressor 100, the oil return branch inlet 510 of the oil return branch 500 is communicated with the oil return hole of the oil separator 200, the oil return branch outlet 520 of the oil return branch 500 is communicated with the air inlet 120 of the compressor 100, the oil return branch 500 is provided with a throttling device 530 with adjustable opening degree, the opening degree of the throttling device 530 is adjustable, and the oil return amount in the oil separator 200 can be regulated and controlled in real time by adjusting the opening degree of the throttling device 530.

The first heat exchanger 300 may be a fin heat exchanger or a flooded shell and tube heat exchanger, and the second heat exchanger 400 may be a fin heat exchanger or a flooded shell and tube heat exchanger. The flooded shell and tube heat exchanger has the characteristics of high refrigerating capacity and high energy efficiency ratio, so the shell and tube heat exchanger is better when used as an indoor heat exchanger.

Referring to fig. 1, in one embodiment, the throttling device may be a first electronic expansion valve, and the electronic expansion valve has high sensitivity and fast adjustment response, and is suitable for an application with a wide operating condition range.

According to the technical scheme, the oil separator 200 is arranged between the air inlet 110 of the compressor 100, the oil return branch 500 is provided with the first electronic expansion valve, and the opening degree of the first electronic expansion valve is adjusted according to different operation conditions of the unit. When the outdoor environment temperature that compressor 100 is located is higher, the exhaust temperature of the gas vent 120 of compressor 100 is higher relatively, and the oil mass of gas vent 120 exhaust from compressor 100 is great, under the certain circumstances of the oil return rate of compressor 100, through the oil return branch 500 returns the oil mass that the air inlet 110 of compressor 100 just should be more, adjusts this moment the aperture increase of first electronic expansion valve makes the lubricating oil that oil separator 200 separated passes through oil return branch 500 in time returns to compressor 100 in, avoids the compressor to lack oil. When the outdoor environment temperature where the compressor 100 is located is low, the exhaust temperature of the exhaust port 120 of the compressor 100 is relatively low, the oil amount discharged from the exhaust port 120 of the compressor 100 is small, and under the condition that the oil return rate of the compressor 100 is constant, the oil amount returned to the air inlet 110 of the compressor 100 through the oil return branch 500 should be small, at this time, the opening degree of the first electronic expansion valve is adjusted to be reduced, so that the lubricating oil separated by the oil separator 200 is returned to the compressor 100 through the oil return branch 500 in time, and the oil shortage of the compressor is avoided. Meanwhile, the smaller opening degree of the first electronic expansion valve can avoid energy loss caused by the fact that the high-temperature and high-pressure gaseous refrigerant coming out of the exhaust port 120 of the compressor 100 directly returns to the compressor 100 through the oil return branch 500 without circulating in the system. According to different operation conditions of the unit, the opening degree of the first electronic expansion valve is adjusted, so that normal oil return of the unit can be ensured, the reliability of the operation of the unit is improved, and the energy loss of an oil return bypass can be reduced.

Referring to fig. 1, in one embodiment, a first filter 540 is disposed between an oil return hole of the oil separator and the throttling device. The first filter 540 may be configured to filter impurities contained in the lubricating oil flowing out from the oil return port of the oil separator 200, so as to prevent the impurities from blocking the first electronic expansion valve and affecting the sensitivity of the first electronic expansion valve.

With reference to fig. 1, in one embodiment, the air conditioning cycle system further includes a heat exchange gas-liquid separator 600, and the heat exchange gas-liquid separator 600 includes a heat exchange branch 610 and a gas-liquid separation branch 620. The first refrigerant port 611 of the heat exchange branch 610 is communicated with the second opening 420 of the second heat exchanger 400, and the second refrigerant port 612 of the heat exchange branch 610 is communicated with the second opening 320 of the first heat exchanger 300. The refrigerant inlet 621 of the gas-liquid separation branch 620 may selectively communicate with the first opening 310 of the first heat exchanger 300 or the first opening 410 of the second heat exchanger 400, and the refrigerant outlet 622 of the gas-liquid separation branch 620 may communicate with the gas inlet 120 of the compressor 100.

According to the technical scheme, the heat exchange gas-liquid separator 600 with the heat exchange function is adopted, the high-temperature liquid refrigerant coming out of the condenser and the low-temperature gaseous refrigerant coming out of the evaporator can exchange heat in the heat exchange gas-liquid separator 600, so that the temperature of the high-temperature liquid refrigerant is reduced, the supercooling degree is increased, the temperature of the low-temperature gaseous refrigerant is increased, the superheat degree is improved, and the heat exchange capacity of the air conditioning system is improved.

The air conditioning system may be operated in a first operation mode and a second operation mode. The first operating mode includes a heating mode. When the air conditioning cycle system is in the heating mode, the refrigerant cycle diagram is shown in fig. 2. The second mode of operation includes a cooling mode and a defrost mode. When the air conditioning cycle system is in the cooling mode, a schematic diagram of the refrigerant cycle is shown in fig. 3. In the defrosting mode, the refrigerant cycle schematic diagram is basically the same as the refrigeration mode.

Referring to fig. 2, when the air conditioning cycle system is in the heating mode, the air conditioning cycle system is in the following communication state: the exhaust port 110 of the compressor 100 is communicated with the intake port 210 of the oil separator 200, the exhaust port 220 of the oil separator 200 is communicated with the first opening 310 of the first heat exchanger 300, and the second opening 320 of the first heat exchanger 300 is communicated with the second refrigerant port 612 of the heat exchange branch 610. The first refrigerant port 611 of the heat exchange branch 610 is communicated with the second opening 420 of the second heat exchanger 400, the first opening 410 of the second heat exchanger 400 is communicated with the refrigerant inlet 621 of the gas-liquid separation branch 620, and the refrigerant outlet 622 of the gas-liquid separation branch 620 is communicated with the air inlet 120 of the compressor 100. In the communication state, as shown by the solid arrows in fig. 2, the refrigerant flows through the following paths: the refrigerant flowing out of the compressor 100 flows to the oil separator 200, the first heat exchanger 300, the second refrigerant port 612 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the first refrigerant port 611 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the second heat exchanger 400, the refrigerant inlet 621 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, and the refrigerant outlet 622 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, and then returns to the compressor 100.

Referring to fig. 3, when the air conditioning cycle system is in the cooling mode or the defrosting mode, the air conditioning cycle system is in the following communication state: the air outlet 110 of the compressor 100 is communicated with the air inlet 210 of the oil separator 200, the air outlet 220 of the oil separator 200 is communicated with the first opening 410 of the second heat exchanger 400, the second opening 420 of the second heat exchanger 400 is communicated with the first refrigerant port 611 of the heat exchange branch 610, the second refrigerant port 612 of the heat exchange branch 610 is communicated with the second opening 320 of the first heat exchanger 300, the first opening 310 of the first heat exchanger 300 is communicated with the refrigerant inlet 621 of the gas-liquid separation branch 620, and the refrigerant outlet 622 of the gas-liquid separation branch 620 is communicated with the air inlet 120 of the compressor 100. In the above-described communication state, as indicated by the broken line arrows in fig. 3, the refrigerant flows through the following paths: the refrigerant flowing out of the compressor 100 flows to the gas-liquid separator 200, the second heat exchanger 400, the first refrigerant port 611 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the second refrigerant port 612 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the first heat exchanger 300, the refrigerant inlet 621 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, and the refrigerant outlet 622 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, and then returns to the compressor 100.

Referring to fig. 1 to 3, the air conditioning cycle system further includes a gas-liquid separator 700. The refrigerant inlet 710 of the gas-liquid separator 700 is communicated with the refrigerant outlet 622 of the gas-liquid separation bypass 620, and the refrigerant outlet 720 of the gas-liquid separator 700 is communicated with the gas inlet 120 of the compressor 100. Wherein:

when the air conditioning cycle system is in the heating mode, as shown by solid arrows in fig. 2, the refrigerant flows through the following paths: the refrigerant flowing out of the compressor 100 flows to the oil separator 200, the first heat exchanger 300, the second refrigerant port 612 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the first refrigerant port 611 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the second heat exchanger 400, the refrigerant inlet 621 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant outlet 622 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant inlet 710 of the gas-liquid separator 700, and the refrigerant outlet 720 of the gas-liquid separator 700, and then returns to the compressor 100.

When the air conditioning cycle is in the cooling mode or the defrosting mode, as indicated by the dotted arrows in fig. 3, the refrigerant flows through the following paths: the refrigerant flowing out of the compressor 100 flows to the oil separator 200, the second heat exchanger 400, the first refrigerant port 611 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the second refrigerant port 612 of the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the first heat exchanger 300, the refrigerant inlet 621 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant outlet 622 of the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant inlet 710 of the gas-liquid separator 700, and the refrigerant outlet 720 of the gas-liquid separator 700, and then returns to the compressor 100.

In the above technical solution, the gas-liquid separator 700 is provided, as shown by a solid arrow in fig. 2, when the air conditioning system is in the heating mode, the liquid refrigerant coming out of the first heat exchanger 300 continuously passes through the heat exchange branch 610 of the heat exchange gas-liquid separator 600 and the gas-liquid separator 700. Through two times of gas-liquid separation, the separation effect is improved, the liquid carrying amount of the refrigerant is greatly reduced, and the problem of liquid carrying of the refrigerant returning to the compressor 100 can be effectively solved.

When the air conditioning system is operated in the cooling mode and the defrosting mode, as shown by the dotted arrows in fig. 3, the liquid refrigerant coming out of the second heat exchanger 400 continuously passes through the heat exchange branch 610 of the heat exchange gas-liquid separator 600 and the gas-liquid separator 700. Through two times of gas-liquid separation, the separation effect is improved, the liquid carrying amount of the refrigerant is greatly reduced, and the problem of liquid carrying of the refrigerant returning to the compressor 100 can be effectively solved. By adopting the heat exchange gas-liquid separator 600 with the heat exchange function, the high-temperature liquid refrigerant coming out of the condenser and the low-temperature gaseous refrigerant coming out of the evaporator can exchange heat in the heat exchange gas-liquid separator 600, so that the temperature of the high-temperature liquid refrigerant is reduced, the supercooling degree is increased, the temperature of the low-temperature gaseous refrigerant is increased, the superheat degree is improved, and the heat exchange capacity of the air conditioning system is improved.

Referring to fig. 1, the air conditioning cycle system further includes a four-way valve 800. A first port 810 of the four-way valve 800 is communicated with the discharge port 110 of the compressor 100, a second port 820 of the four-way valve 800 is communicated with the first opening 310 of the first heat exchanger 300, a third port 830 of the four-way valve 800 is communicated with the refrigerant inlet 621 of the gas-liquid separation branch 620, and a fourth port 840 of the four-way valve 800 is communicated with the first opening 410 of the second heat exchanger 400. The four-way valve 800 serves as a reversing valve, and four ports can be in the following two communication states.

First, as shown in fig. 2, a first port 810 of the four-way valve 800 communicates with a second port 820 of the four-way valve 800, and a third port 830 of the four-way valve 800 communicates with a fourth port 840 of the four-way valve 800. At the moment, the air-conditioning circulating system is in a heating mode to operate, and the flow direction of a refrigerant is as follows: the refrigerant from the compressor 100 flows to the oil separator 200, the four-way valve 800, the first heat exchanger 300, the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the second heat exchanger 400, the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant inlet 710 of the gas-liquid separator 700, and the refrigerant outlet 720 of the gas-liquid separator 700, and then returns to the compressor 100. The gaseous high-temperature and high-pressure refrigerant discharged from the discharge port 120 of the compressor 100 carries lubricating oil, which is separated in the oil separator 200 and returned to the compressor 100 through the oil return branch 500. The refrigerant condenses in the first heat exchanger 300 as a condenser to release heat to the outside to form a high-temperature liquid refrigerant, the high-temperature liquid refrigerant is subjected to impurity removal by the second filter 910, and then enters the heat exchange gas-liquid separator 600 through the second electronic expansion valve 900 to exchange heat with the low-temperature gaseous refrigerant flowing out of the first opening 410 of the second heat exchanger 400 as an evaporator, so that the temperature of the high-temperature liquid refrigerant is reduced, the supercooling degree is increased, meanwhile, the temperature of the low-temperature gaseous refrigerant is increased, and the superheat degree is increased. The high-temperature gaseous refrigerant after heat exchange comes out of the heat exchange gas-liquid separator 600, enters the gas-liquid separator 700, and finally returns to the compressor 100. In the heat exchange gas-liquid separator 600, the temperature of the liquid refrigerant is reduced, the supercooling degree is increased, the temperature of the gas refrigerant is increased, and the superheat degree is increased, so that the capacity of the air conditioning system is improved. Therefore, the two gas-liquid separators are adopted, and the problems of oil return and liquid carrying of the unit and the heat exchange efficiency are solved.

Second, as shown in fig. 3, the first port 810 of the four-way valve 800 communicates with the fourth port 840 of the four-way valve 800, and the second port 820 of the four-way valve 800 communicates with the third port 830 of the four-way valve 800. At the moment, the air-conditioning circulating system is in a refrigeration mode or a defrosting mode to operate, and the flow direction of a refrigerant is as follows: the refrigerant discharged from the compressor 100 flows to the oil separator 200, the four-way valve 800, the second heat exchanger 400, the heat exchange branch 610 of the heat exchange gas-liquid separator 600, the first heat exchanger 300, the gas-liquid separation branch 620 of the heat exchange gas-liquid separator 600, the refrigerant inlet 710 of the gas-liquid separator 700, and the refrigerant outlet 720 of the gas-liquid separator 700, and then returns to the compressor 100. The gaseous high-temperature and high-pressure refrigerant discharged from the discharge port 120 of the compressor 100 carries lubricating oil, which is separated in the oil separator 200 and returned to the compressor 100 through the oil return branch 500. The high-temperature high-pressure gaseous refrigerant condenses in the second heat exchanger 400 as a condenser and releases heat to the outside to be a high-temperature liquid refrigerant, and the high-temperature liquid refrigerant enters the heat exchange gas-liquid separator 600 and exchanges heat with the low-temperature gaseous refrigerant flowing out of the first opening 310 of the first heat exchanger 300 as an evaporator, so that the temperature of the high-temperature liquid refrigerant is reduced, the supercooling degree is increased, the temperature of the low-temperature gaseous refrigerant is increased, and the superheat degree is increased. The high-temperature gaseous refrigerant after heat exchange comes out of the heat exchange gas-liquid separator 600, enters the gas-liquid separator 700, and finally returns to the compressor 100. In the heat exchange gas-liquid separator 600, the temperature of the liquid refrigerant is reduced, the supercooling degree is increased, the temperature of the gas refrigerant is increased, and the superheat degree is increased, so that the capacity of the air conditioning system is improved. Therefore, the two gas-liquid separators are adopted, and the problems of oil return and liquid carrying of the unit and the heat exchange efficiency are solved.

Referring to fig. 1 to 3, in one embodiment, the throttling element is a second electronic expansion valve 900, and the second electronic expansion valve 900 is disposed between the second opening 320 of the first heat exchanger 300 and the second refrigerant port 612 of the heat exchange branch 610. A second electronic expansion valve 900 is disposed between the second opening 320 of the first heat exchanger 300 and the second refrigerant port 612 of the heat exchange branch 610, and the second electronic expansion valve 900 is arranged to achieve throttling and pressure reducing effects. Further, a second filter 910 is further disposed between the second opening 320 of the first heat exchanger 300 and the second electronic expansion valve 900, and the second filter 910 can be used for removing impurities.

Referring to fig. 1 to 3, in one embodiment, a third filter 920 is disposed between the second opening 420 of the second heat exchanger 400 and the first refrigerant port 611 of the heat exchange branch 610. The third filter 920 can remove impurities in the refrigerant.

The air conditioner circulating system comprises a compressor, an oil separator, a first heat exchanger, a throttling element, a second heat exchanger and an oil return branch. The compressor, the oil separator, the first heat exchanger and the second heat exchanger form a loop, an oil return branch inlet of the oil return branch is communicated with an oil return hole of the oil separator, an oil return branch outlet of the oil return branch is communicated with an air inlet of the compressor, and a throttling device with adjustable opening degree is arranged on the oil return branch. According to different operation conditions, the opening degree of the throttling device is adjusted, normal oil return of the unit is guaranteed, energy loss of oil return bypass is reduced, reliability of unit operation is improved, and energy loss is reduced.

An air conditioner, its characterized in that includes the utility model discloses the air conditioner circulation system that arbitrary technical scheme provided.

The utility model provides an air conditioner oil return control method adopts the utility model discloses air conditioner circulation system that arbitrary technical scheme provided, oil return control method includes:

the preset ambient temperature values T1, T2 and T3 … … Tx are set, x is larger than or equal to 4, and the preset ambient temperature values refer to the outdoor atmospheric ambient temperature where the compressor is located.

The actual temperature Ty of the environment where the compressor is located is detected for the y time, y is more than or equal to 1, and specifically, the actual atmospheric environment temperature where the compressor is located can be detected by adopting an environment temperature sensing bulb;

and comparing the actual temperature Ty with preset ambient temperature values T1, T2 and T3 … … Tx, and controlling the opening of the regulating valve according to the comparison result. And the opening degree of the regulating valve is different under different atmospheric environment temperatures. The opening of the regulating valve may be different for different types of compressors under the same atmospheric environment temperature.

In one embodiment, the oil return control method further includes:

when Ty is more than or equal to Tx and less than T (x +1), x is more than or equal to 1, y is more than or equal to 1, and the opening of the regulating valve is controlled to be Ky. For example, when the ambient temperature T1 of the compressor is detected to be not less than Ty1 and not more than T2, the controller controls the opening of the regulating valve to be Ky1, the opening of the regulating valve is Ky1, so that lubricating oil in the oil separator can be ensured to return to the compressor quickly, meanwhile, high-temperature and high-pressure gaseous refrigerant from the exhaust port of the compressor can be prevented from directly returning to the air inlet of the compressor through the regulating valve, and energy loss caused by unnecessary oil return bypass is reduced.

According to the oil return control method, the optimal opening degree of the oil return electronic expansion valve is determined according to different environmental temperatures, normal oil return of the unit is guaranteed, damage caused by oil shortage of the compressor is avoided, and the reliability of the system is improved. Meanwhile, energy loss caused by unnecessary oil return bypass is reduced, and the capacity and the operation reliability of the unit are improved.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not to be construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.

Claims (10)

1. An air conditioning cycle system, characterized by comprising a compressor (100), an oil separator (200), a first heat exchanger (300), a throttling element, a second heat exchanger (400) and an oil return branch (500):

the compressor (100), the oil separator (200), the throttling element of the first heat exchanger (300) and the second heat exchanger (400) form a circuit;

an oil return branch inlet (510) of the oil return branch (500) is communicated with an oil return hole of the oil separator (200), an oil return branch outlet (520) of the oil return branch (500) is communicated with an air inlet (120) of the compressor (100), and a throttling device (530) with an adjustable opening degree is arranged on the oil return branch (500).

2. The air conditioning cycle system of claim 1, wherein the opening-adjustable throttling device (530) is a first electronic expansion valve.

3. The air conditioning cycle system of claim 1, wherein a first filter (540) is disposed between an oil return hole of the oil separator and the throttle device (530) with adjustable opening degree.

4. The air conditioning cycle system of claim 1, further comprising a heat exchange gas-liquid separator (600), the heat exchange gas-liquid separator (600) comprising a heat exchange branch (610) and a gas-liquid separation branch (620):

a first refrigerant port (611) of the heat exchange branch (610) is communicated with a second opening (420) of the second heat exchanger (400), and a second refrigerant port (612) of the heat exchange branch (610) is communicated with a second opening (320) of the first heat exchanger (300);

a refrigerant inlet (621) of the gas-liquid separation branch (620) is selectively communicated with the first opening (310) of the first heat exchanger (300) or the first opening (410) of the second heat exchanger (400), and a refrigerant outlet (622) of the gas-liquid separation branch (620) is communicated with the air inlet (120) of the compressor (100).

5. The air conditioning cycle system of claim 4, further comprising a gas-liquid separator (700), wherein a refrigerant inlet (710) of the gas-liquid separator (700) is communicated with a refrigerant outlet (622) of the gas-liquid separation branch (620), and a refrigerant outlet (720) of the gas-liquid separator (700) is communicated with the air inlet (120) of the compressor (100).

6. The air conditioning cycle system of claim 4, further comprising a four-way valve (800), wherein a first port (810) of the four-way valve (800) communicates with the discharge port (110) of the compressor (100), a second port (820) of the four-way valve (800) communicates with the first opening (310) of the first heat exchanger (300), a third port (830) of the four-way valve (800) communicates with the refrigerant inlet (621) of the gas-liquid separating branch (620), and a fourth port (840) of the four-way valve (800) communicates with the first opening (410) of the second heat exchanger (400), wherein,

a first port (810) of the four-way valve (800) is in communication with a second port (820) of the four-way valve (800), and a third port (830) of the four-way valve (800) is in communication with a fourth port (840) of the four-way valve (800);

or,

the first port (810) of the four-way valve (800) is communicated with the fourth port (840) of the four-way valve (800), and the second port (820) of the four-way valve (800) is communicated with the third port (830) of the four-way valve (800).

7. The air conditioning cycle system of claim 1, wherein the throttling element is a second electronic expansion valve (900), and the second electronic expansion valve (900) is disposed between the second opening (320) of the first heat exchanger (300) and the second refrigerant port (612) of the heat exchange branch (610).

8. The air conditioning cycle system as set forth in claim 7, wherein a second filter (910) is further provided between said second opening (320) of said first heat exchanger (300) and said second electronic expansion valve (900).

9. The air conditioning cycle system of claim 4, wherein a third filter (920) is disposed between the second opening (420) of the second heat exchanger (400) and the first refrigerant port (611) of the heat exchange branch (610).

10. An air conditioner characterized by comprising the air conditioning cycle system as recited in any one of claims 1 to 9.