CN219976794U

CN219976794U - Air conditioner

Info

Publication number: CN219976794U
Application number: CN202321046795.0U
Authority: CN
Inventors: 于小杰; 陈见兴
Original assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Current assignee: Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date: 2023-05-04
Filing date: 2023-05-04
Publication date: 2023-11-07
Anticipated expiration: 2033-05-04

Abstract

The utility model discloses an air conditioner, relates to the technical field of air conditioning, and aims to solve the problem that the volume and the separation effect of a gas-liquid separation device cannot be considered. The air conditioner includes a compressor having an air inlet end and a gas-liquid separator. The gas-liquid separator comprises a separating tank, an exhaust pipe, an air inlet pipe and a buffer tank, wherein the separating tank is provided with a separating cavity, one end of the exhaust pipe is inserted into the separating cavity, and the other end of the exhaust pipe is communicated with the air inlet end. One end of the air inlet pipe is inserted into the separation cavity, and the buffer tank is positioned in the separation cavity. One end of the air inlet pipe positioned in the separation cavity is inserted into the buffer tank, and the buffer tank is provided with a buffer outlet communicated with the separation cavity. The air conditioner provided by the utility model can reduce the volume of the gas-liquid separator and improve the gas-liquid separation effect.

Description

Air conditioner

Technical Field

The utility model belongs to the technical field of air conditioning, and particularly relates to an air conditioner.

Background

An air conditioner is a device which can regulate and control parameters such as temperature, humidity, flow rate and the like of ambient air in a building or a structure. Because of insufficient heat exchange at the user side, the refrigerant returned to the compressor by the evaporator is in a gas-liquid two-phase mixed state, and the air inlet end of the compressor can generate liquid impact due to the suction of liquid refrigerant and damage the compressor.

Based on this, it is necessary to install a gas-liquid separation device at the intake end of the compressor to avoid liquid refrigerant from directly entering the compressor. However, in the conventional gas-liquid separation apparatus, a gas-liquid two-phase refrigerant is separated. If the space of the separation cavity is increased, the space occupied by the gas-liquid separation device is greatly increased although the separation effect is better. If the space of the separation cavity is reduced, the occupied space of the gas-liquid separation device can be reduced, but the smaller separation cavity can not fully separate the mixed gas-liquid two-phase refrigerant, namely, the compressor still has the risk of sucking gas and carrying liquid, and the effect is poor.

Disclosure of Invention

The utility model provides an air conditioner, which aims to solve the problem that the volume and the separation effect of a gas-liquid separation device cannot be considered.

The embodiment of the utility model provides an air conditioner, which comprises a compressor with an air inlet end and a gas-liquid separator. The gas-liquid separator comprises a separating tank, an exhaust pipe, an air inlet pipe and a buffer tank, wherein the separating tank is provided with a separating cavity, one end of the exhaust pipe is inserted into the separating cavity, and the other end of the exhaust pipe is communicated with the air inlet end. One end of the air inlet pipe is inserted into the separation cavity, and the buffer tank is positioned in the separation cavity. One end of the air inlet pipe positioned in the separation cavity is inserted into the buffer tank, and the buffer tank is provided with a buffer outlet communicated with the separation cavity.

Because one end of the air inlet pipe is inserted into the buffer tank in the separation cavity, the refrigerant can firstly enter the buffer tank through the air inlet pipe. Therefore, the gas-liquid two-phase refrigerant can be initially separated in the buffer tank, and then the gas-liquid two-phase refrigerant entering the separation cavity can be further separated. Through the mode of second grade separation, can improve the separation effect of gas-liquid two-phase state refrigerant in the knockout drum by a wide margin to avoid liquid refrigerant to be inhaled the compressor by the inlet end of compressor, and lead to the problem emergence of compressor liquid to hit the damage.

On this basis, since the gas-liquid separator provided with the buffer tank has a better separation effect, the volume of the separation tank can be appropriately reduced, such as lowering the height of the vertical separation tank in the up-down direction, or reducing the inner diameter of the vertical separation tank. Although the lower end of the exhaust pipe is brought closer to the lower end of the intake pipe. However, due to the blocking of the buffer tank, the gas-liquid two-phase refrigerant still enters the separation cavity for continuous separation after preliminary separation in the buffer tank, so that a good separation effect of the gas-liquid two-phase refrigerant can be ensured. Therefore, the gas-liquid separator comprising the buffer tank provided by the embodiment of the application has the effect of reducing the volume of the buffer tank so as to reduce the occupied area of the gas-liquid separator while ensuring the gas-liquid separation effect. The space occupied by the gas-liquid separator in the outdoor unit can be reduced, and the gas-liquid separator can be flexibly arranged in the outdoor unit.

In some embodiments, the upper end of the separator tank is provided with an air inlet in the vertical direction, which communicates with the separation chamber. The lower end of the air inlet pipe is inserted into the separation cavity through the air inlet and is in sealing connection with the separation tank, and the lower end of the air inlet pipe is inserted into the buffer tank.

In some embodiments, the buffer tank has a buffer chamber, the upper end of the buffer tank is provided with a buffer inlet along the vertical direction, and the lower end of the air inlet pipe is inserted into the buffer chamber through the buffer inlet and is in contact connection with the buffer tank. Along a first straight line direction, the buffer outlet is arranged on the side wall of the buffer tank, and the first straight line direction is perpendicular to the vertical direction.

In some embodiments, the buffer outlet and the exhaust duct are located on opposite sides of the buffer chamber along a first linear direction.

In some embodiments, the lower end of the air inlet pipe is a slope structure along the vertical direction for increasing the opening area of the lower end of the air inlet end. In the buffer chamber, the ramp structure is disposed in a direction away from the buffer outlet.

In some embodiments, the upper end of the separator tank is further provided with an exhaust port in the vertical direction, and the exhaust port communicates with the separation chamber. The lower end of the exhaust pipe is inserted into the separation cavity through the exhaust port and is connected with the separation tank in a sealing way.

In some embodiments, the compressor is a supplemental air enthalpy compressor, the compressor further having an air outlet end and a supplemental air end, the air inlet end being in communication with the air outlet end, and the supplemental air end being in communication with the air outlet end. The air supplementing end is positioned between the air inlet end and the air outlet end along the flowing direction of the refrigerant. The air conditioner further comprises an air supplementing electric control valve, the separating tank is further provided with an air supplementing port, and the air supplementing port is communicated with the separating cavity. One end of the air supplementing electric control valve is connected with the separating tank and conducts the air supplementing port, and the other end of the air supplementing electric control valve is connected with the air supplementing end of the compressor. The air supplementing electric control valve is used for controlling the closing or the conduction of a refrigerant channel between the air supplementing port and the air inlet end of the compressor.

In some embodiments, the air conditioner further comprises a four-way valve, an outdoor heat exchanger, a first restrictor, and an indoor heat exchanger. The four-way valve has a first port, a second port, a third port, and a fourth port. The first port is connected with one end of the air inlet pipe far away from the separation cavity, and one end of the air outlet pipe far away from the separation cavity is connected with the air inlet end of the compressor. The compressor also has an air outlet end, and the air outlet end of the compressor is connected with the second port. One end of the outdoor heat exchanger is connected with the third port, and one end of the first throttle is connected with the other end of the outdoor heat exchanger. The other end of the first throttle is connected with one end of the indoor heat exchanger, and the other end of the indoor heat exchanger is connected with the fourth port. When the air conditioner is in a refrigerating working condition, the second port and the third port are conducted, and the first port is connected. The fourth port is conductive. When the air conditioner is in a heating working condition, the second port and the fourth port are conducted, and the first port and the third port are conducted.

In some embodiments, the separation tank is provided with a sensor interface, which communicates with the separation chamber. The air conditioner further comprises a controller and a liquid level sensor. The liquid level sensor is inserted into the separation cavity through the sensor interface. The liquid level sensor is used for detecting the liquid level height in the separation cavity and outputting a liquid level acquisition signal. The first throttle is an electronic expansion valve, and the controller is electrically connected with the first throttle and the liquid level sensor and receives a liquid level acquisition signal. When the liquid level acquisition signal is greater than or equal to a preset liquid level threshold value, the controller controls the opening degree of the first restrictor to be reduced.

In some embodiments, the separation tank is provided with a viewing port communicated with the separation cavity, and the viewing port is positioned below the air supplementing port and the exhaust pipe along the vertical direction. The gas-liquid separator also comprises a first light-transmitting plate, the first light-transmitting plates are arranged in one-to-one correspondence with the liquid viewing holes, and the edges of one first light-transmitting plate and one liquid viewing hole are connected and seal the liquid viewing holes.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for 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 application, 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 a connection structure of an air conditioner according to an embodiment of the present application;

FIG. 2 is a schematic view of a structure in which a gas-liquid separator and an oil separator are installed between the compressor and the four-way valve shown in FIG. 1;

FIG. 3 is a schematic view of a connection structure of the compressor shown in FIG. 1 with an outdoor heat exchanger and an indoor heat exchanger;

fig. 4 is a schematic perspective view of an outdoor unit of an air conditioner according to an embodiment of the present application;

FIG. 5 is a front view of the gas-liquid separator shown in FIG. 4;

FIG. 6 is a front view of a gas-liquid separator according to the related art;

FIG. 7 is a cross-sectional view of the gas-liquid separator of FIG. 5;

FIG. 8 is a top view of the gas-liquid separator shown in FIG. 7;

FIG. 9 is a schematic perspective view of the surge tank shown in FIG. 7;

fig. 10 is a schematic view of a connection structure of an air conditioner according to the related art;

FIG. 11 is a side view of the gas-liquid separator of FIG. 5;

fig. 12 is a schematic diagram of a connection structure of an air conditioner including an air-supplementing enthalpy-increasing compressor according to an embodiment of the present application;

FIG. 13 is a schematic diagram of a circuit connection according to an embodiment of the present application;

fig. 14 is a schematic diagram of a variable frequency heat dissipation assembly for dissipating heat of a frequency converter according to an embodiment of the present application;

FIG. 15 is an exploded view of the water cooled heat exchanger shown in FIG. 14 mounted in contact with a frequency converter;

fig. 16 is a schematic diagram of a connection structure of a variable frequency heat dissipation assembly according to an embodiment of the present application for dissipating heat through refrigerant circulation of a compressor;

FIG. 17 is a schematic view of a connection structure of the variable frequency heat sink assembly shown in FIG. 16 further including a temperature sensor and a water flow switch;

FIG. 18 is a front view of a variable frequency heat sink assembly according to an embodiment of the present application further comprising a variable frequency heat exchanger box;

FIG. 19 is a front view of a water tank of the type shown in FIG. 18;

fig. 20 is a right side view of the water tank shown in fig. 19;

fig. 21 is a rear view of the water tank shown in fig. 19.

Detailed Description

The embodiment of the application provides an air conditioner, namely an air conditioner, which is equipment capable of adjusting and controlling parameters such as temperature, humidity, circulation flow rate and the like of ambient air in a building or a structure.

As shown in fig. 1, fig. 1 is a schematic diagram of a connection structure of an air conditioner 100 according to an embodiment of the present application. The air conditioner 100 may include a compressor 10, a four-way valve 20, an outdoor heat exchanger 30, a first throttle 40, and an indoor heat exchanger 50. Illustratively, the four-way valve 20 may have a first port a, a second port B, a third port C, and a fourth port D, and the compressor 10 may have an inlet end and an outlet end. The air inlet end of the compressor 10 may be connected to the first port a of the four-way valve, and the air outlet end of the compressor 10 may be connected to the second port B of the four-way valve. The third port C of the four-way valve may be connected to one end of the outdoor heat exchanger 30, the other end of the outdoor heat exchanger 30 may be connected to one end of the first restrictor 40, the other end of the first restrictor 40 may be connected to one end of the indoor heat exchanger 50, and the other end of the indoor heat exchanger 50 may be connected to the fourth port D of the four-way valve.

Based on this, the refrigerant can circulate between the outdoor heat exchanger 30 and the indoor heat exchanger 50, and a reversible phase change is generated, and the refrigerant can release or absorb heat while generating a phase change, so that heat can circulate between the outdoor heat exchanger 30 and the indoor heat exchanger 50. For example, the refrigerant may exchange heat with air at the outdoor heat exchanger 30, thereby releasing heat to heat ambient air (or absorbing heat to cool nearby air). And the refrigerant may also exchange heat at the indoor heat exchanger 50 to absorb heat to cool nearby media (or release heat to heat nearby media).

In the embodiment of the present application, the indoor heat exchanger 50 refers to a heat exchanger for cooling or heating air at the user side, and the indoor heat exchanger 50 may be installed in a room at the user side. Or may be located remotely from the user side, at which time the heat of the indoor heat exchanger 50 may be brought to the vicinity of the user side by a secondary circulation heat exchange branch for cooling or heating the air in the vicinity of the user side.

When the air conditioner 100 is in a cooling or dehumidifying condition, taking the solid arrow shown in fig. 1 as an example, the four-way valve 20 may be adjusted to make the second port B and the third port C conductive and to make the fourth port D and the first port a conductive. So that the refrigerant can circulate between the compressor 10, the second and third ports B and C of the four-way valve 20, the outdoor heat exchanger 30, the first throttle 40, the indoor heat exchanger 50, the fourth and first ports D and a of the four-way valve 20, and the compressor 10. In this process, the high-pressure gaseous refrigerant compressed by the compressor 10 may flow to the outdoor heat exchanger 30, so that the refrigerant may liquefy and release heat at the outdoor heat exchanger 30, and may heat other media near the outdoor heat exchanger 30. Then, the pressure of the liquid refrigerant flowing into the indoor heat exchanger 50 is reduced by the first throttle 40, so that the refrigerant can absorb heat and vaporize at the indoor heat exchanger 50, thereby cooling the medium near the indoor heat exchanger 50 and achieving heat exchange transfer between the outdoor heat exchanger 30 and the indoor heat exchanger 50.

When the air conditioner 100 is in a heating mode, taking the dashed arrow shown in fig. 1 as an example, the four-way valve 20 may be adjusted to make the second port B and the fourth port D conductive and to make the third port C and the first port a conductive. In this way, the refrigerant can circulate between the compressor 10, the second and fourth ports B and D of the four-way valve 20, the indoor heat exchanger 50, the first throttle 40, the outdoor heat exchanger 30, the third and first ports C and a of the four-way valve 20, and the compressor 10. In this process, the high-pressure gaseous refrigerant compressed by the compressor 10 may flow to the indoor heat exchanger 50 so that the refrigerant may liquefy at the indoor heat exchanger 50 and release heat for heating the medium near the indoor heat exchanger 50. Then, the pressure of the liquid refrigerant flowing into the outdoor heat exchanger 30 is reduced by the first throttle 40 so that the refrigerant can absorb heat at the outdoor heat exchanger 30 and be vaporized for cooling the medium around the outdoor heat exchanger 30 to achieve heat exchange transfer between the outdoor heat exchanger 30 and the indoor heat exchanger 50.

When the air conditioner 100 is in the cooling condition, the liquid refrigerant cannot be completely evaporated and vaporized at the indoor heat exchanger 50 due to insufficient heat exchange at the indoor heat exchanger 50 (i.e., at the user side). Thus, the refrigerant in the two phases of gas and liquid flows from the indoor heat exchanger 50 to the air inlet of the compressor 10, and if the refrigerant in the liquid state is sucked into the compressor 10 from the air inlet of the compressor 10, the compressor 10 generates liquid impact to damage the compressor 10. In addition, while the compressor 10 is continuously operated, lubrication oil is required to reduce the rotation resistance of the internal structure, but a portion of lubrication oil in the compressor 10 flows out from the air outlet end of the compressor 10 along with compressed refrigerant, and if lubrication oil flows into the indoor heat exchanger 50 and the outdoor heat exchanger 30, the lubrication oil attached to the inner wall of the heat exchanger reduces the heat exchange effect of the indoor heat exchanger 50 and the outdoor heat exchanger 30.

Based on this, as shown in fig. 2, the air conditioner 100 may further include a gas-liquid separator 60 and an oil separator 71. The gas-liquid separator 60 may be installed between the first port a of the four-way valve 20 and the intake end of the compressor 10 such that the first port a may be connected to and communicated with the intake end of the compressor 10 through the gas-liquid separator 60. In this way, when the gaseous refrigerant mixed with the liquid refrigerant or the lubricant oil flows to the air inlet end of the compressor 10 through the gas-liquid separator 60, the gas-liquid separator 60 can separate out non-gaseous impurities (such as the liquid refrigerant, the liquid lubricant oil or other impurities) so as to avoid that the impurities enter the compressor 10 to influence the stable operation of the compressor 10. The outlet end of the compressor 10 and the four-way valve 20 may be connected and connected by an oil separator 71. In this way, the oil separator 71 can separate the lubricating oil mixed in the high-pressure gaseous refrigerant flowing through, thereby avoiding the lubricating oil from adhering to the inner walls of the indoor heat exchanger 50 and the outdoor heat exchanger 30 when flowing through the two, so that the indoor heat exchanger 50 and the outdoor heat exchanger 30 have high heat exchange efficiency.

When the compressor 10 is an oil-free compressor having a magnetic suspension structure, lubrication by using lubricating oil is not required in the cylinder of the compressor 10, that is, lubricating oil is not mixed when the high-pressure gaseous refrigerant flows out from the gas outlet end of the compressor 10. At this time, there is no need to install an oil separator at the air outlet end of the compressor 10, and the structure is simple.

In other embodiments, a four-way valve may not be required. As shown in fig. 3, the air outlet end of the compressor 10 of the air conditioner 100 may be communicated with the outdoor heat exchanger 30, and the air inlet end of the compressor 10 may be communicated with the indoor heat exchanger 50 through the gas-liquid separator 60, and the indoor heat exchanger 50 and the outdoor heat exchanger 30 may be communicated through the first choke 40. So that the refrigerant can circulate between the compressor 10, the outdoor heat exchanger 30, the first throttle 40, the indoor heat exchanger 50, the gas-liquid separator 60, and the compressor 10. At this time, the outdoor heat exchanger 30 may be used to heat a nearby medium, and the indoor heat exchanger 50 may be used to cool the nearby medium, so that the air conditioner 100 operates in a cooling or dehumidifying operation, i.e., a single cooling mode. In addition, the gas-liquid separator 60 installed between the indoor heat exchanger 50 and the compressor 10 can also prevent the liquid refrigerant of the user side from directly entering the compressor 10 from the air inlet end, so that the compressor 10 can continuously and stably operate.

In the air conditioner 100 of the single cooling mode, the air intake end of the compressor 10 may be directly connected to the indoor heat exchanger 50, and a gas-liquid separator may not be installed between the compressor 10 and the indoor heat exchanger 50. The selection may be made as needed, and is not limited thereto.

As shown in fig. 4, fig. 4 is a schematic perspective view of an outdoor unit of an air conditioner 100 according to an embodiment of the present application for the gas-liquid separator 60. The gas-liquid separator 60 may be installed in the outdoor unit and disposed near the compressor 10. With reference to fig. 5, fig. 5 is a schematic diagram of the gas-liquid separator 60 shown in fig. 4. The gas-liquid separator 60 may include a separation tank 61, an exhaust pipe 62, and an intake pipe 63, and the separation tank 61 has a separation chamber (not shown in the drawing) therein. With the gas-liquid separator 60 shown in fig. 4 being a vertical separator, the exhaust pipe 62 and the intake pipe 63 may extend in the up-down direction (i.e., the vertical direction), the lower end of the exhaust pipe 62 may be inserted into the separation tank 61, and the upper end of the exhaust pipe 62 may be connected to and conducted with the intake end of the compressor 10. The lower end of the intake pipe 63 may be inserted into the separation tank 61 as well, and the upper end of the intake pipe 63 may be connected to and communicated with the indoor heat exchanger 50 (shown in fig. 3) or the first end a (shown in fig. 2) of the four-way valve 20. So that the gas-liquid separator 60 can prevent liquid refrigerant (or impurities) from entering the compressor 10.

In the related art, as shown in fig. 6, fig. 6 is a front view of a gas-liquid separator 60 in the related art. In the up-down direction, the lower end of the exhaust pipe 62 and the lower end of the intake pipe 63 are inserted into the separation tank 61. In the separation tank 61, the lower end of the exhaust pipe 62 is disposed near the upper end of the separation tank 61, and the lower end of the intake pipe 63 extends downward and is disposed near the lower end of the separation tank 61. Based on this, the mixed refrigerant in the gas-liquid two-phase state flows along the gas inlet pipe 63 and is collected at the lower end of the separation tank 61 after entering the separation tank 61 through the gas inlet pipe 63. Then, the liquid refrigerant is accumulated at the lower end of the separation tank 61 by gravity, and the gaseous refrigerant may enter the compressor 10 (as shown in fig. 4) through the lower end of the discharge pipe 62, so that the compressor 10 operates smoothly and safely, and outputs the high-temperature and high-pressure gaseous refrigerant.

However, in the gas-liquid separator 60 shown in fig. 6, since the space size of the separation chamber in the separation tank 61 is a key index of the gas-liquid separation effect. Illustratively, the larger the space of the separation chamber, the better the separation effect of the gaseous refrigerant and the liquid refrigerant. In particular, the higher the separation chamber height in the up-down direction, i.e. in the up-down direction, the better the separation effect. But will greatly increase the volume of the separator tank 61, i.e. increase the space occupied by the gas-liquid separator 60. If the space of the separation chamber is reduced, the lower end of the intake pipe 63 is disposed near the lower end of the exhaust pipe 62, that is, the gas-liquid two-phase refrigerant cannot be sufficiently separated in the separation chamber, and is sucked into the compressor 10 (as shown in fig. 4), thereby causing damage to the compressor 10 due to liquid impact.

Based on this, as shown in fig. 7, fig. 7 is a sectional view of the gas-liquid separator 60 shown in fig. 5. As can be seen from the separating tank 61 cut in fig. 7, the gas-liquid separator 60 may further include a buffer tank 64, the buffer tank 64 may be installed in the separating chamber 65 of the separating tank 61, and the lower end of the gas inlet pipe 63 may be continuously inserted into the buffer tank 64 after being inserted into the separating chamber 65. The buffer tank 64 is provided with a buffer outlet 661, and the buffer outlet 661 is provided at an arbitrary position of the buffer tank 64 other than the bottom, that is, the buffer outlet 661 may be provided at a higher position of the buffer tank 64. So that the lower end of the air inlet pipe 63 may communicate with the separation chamber 65 through the buffer outlet 661. Based on this, when the gas-liquid two-phase refrigerant enters the separation tank 61 from the lower end of the gas inlet pipe 63, the gas-liquid two-phase refrigerant first accumulates in the buffer tank 64 and undergoes preliminary separation, the separated gas refrigerant can flow into the separation chamber 65 from the buffer outlet 661 at a higher position, and the liquid refrigerant accumulated in the buffer tank 64 also enters the separation chamber 65 when it passes through the lowest position of the buffer outlet 661. In the separation chamber 65, a portion of the mixed gas-liquid two-phase refrigerant may be further separated, so that the gaseous refrigerant may be sucked into the compressor 10 (shown in fig. 2) from the lower end of the discharge pipe 62, and the liquid refrigerant and other solid or liquid impurities may accumulate at the bottom of the separation chamber 65.

Thus, by the arrangement of the buffer tank 64, the gas-liquid two-phase refrigerant in the separation chamber 65 can be initially separated in the buffer tank 64, and then the gas-liquid two-phase refrigerant entering the separation chamber 65 can be further separated. In this way, by means of the secondary separation, the separation effect of the gas-liquid two-phase refrigerant in the separation tank 61 can be greatly improved, so that the problem that the liquid refrigerant enters the compressor 10 from the air inlet end of the compressor 10 and causes the liquid impact damage of the compressor 10 is avoided. On this basis, since the gas-liquid separator 60 provided with the buffer tank 64 has a better separation effect, it is possible to appropriately reduce the volume of the separation tank 61, such as lowering the height of the vertical separation tank 61 in the up-down direction, or reducing the inner diameter of the vertical separation tank 61. Although the lower end of the exhaust pipe 62 is brought closer to the lower end of the intake pipe 63. However, due to the blocking of the buffer tank 64, the gas-liquid two-phase refrigerant still enters the separation cavity 65 for continuous separation after preliminary separation in the buffer tank 64, so that a good separation effect of the gas-liquid two-phase refrigerant can be ensured.

Therefore, the gas-liquid separator 60 including the buffer tank 64 according to the embodiment of the present application has the effect of reducing the volume of the buffer tank 64 to reduce the occupied area of the gas-liquid separator 60 while ensuring the gas-liquid separation effect. The space occupied by the gas-liquid separator 60 in the outdoor unit can be reduced, and the gas-liquid separator 60 can be flexibly arranged in the outdoor unit.

In addition, for the horizontal separation tank 61, the buffer tank 64 may be installed in the separation chamber 65, and one end of the air inlet pipe 63 extending in the horizontal direction (or in the vertical direction) located in the separation chamber 65 may be inserted into the buffer tank 64, and the buffer outlet 661 may be opened at the side wall or the top wall of the buffer tank 64, so that the multistage separation effect of the gas-liquid two-phase refrigerant may be achieved, the separation effect of the gas-liquid two-phase refrigerant may be improved, and the volume of the separation tank 61 may be reduced.

In some embodiments, as shown in fig. 8, fig. 8 is a top view of the gas-liquid separator 60 shown in fig. 7. When the intake pipe 63 and the exhaust pipe 62 are installed, an exhaust port 662 and an intake port 663 may be opened at the upper end of the separation tank 61 in the up-down direction, and the exhaust port 662 and the intake port 663 may communicate with the separation chamber 65. The lower end of the exhaust pipe 62 may be inserted into the separation chamber 65 from the top down through the exhaust port 662, and after the lower end of the exhaust pipe 62 is inserted by a proper length, the outer wall of the exhaust pipe 62 and the separation tank 61 may be hermetically connected by welding. The outer wall of the exhaust pipe 62 and the separation tank 61 may be sealingly connected by the engagement of a nut and a packing, and the lower end of the exhaust pipe 62 may be inserted into the buffer tank 64. For the air inlet pipe 63, the lower end of the air inlet pipe 63 may be inserted into the separation chamber 65 from top to bottom through the air inlet 663, and after the lower end of the air inlet pipe 63 is inserted to a proper length, the outer wall of the air inlet pipe 63 and the separation tank 61 may be sealed and connected by welding or a nut-rubber ring or the like.

In this way, in the horizontal plane, the exhaust port 662 and the intake port 663 can be disposed close to each other so that the intake pipe 63 and the exhaust pipe 62 are disposed close to each other in the up-down direction, whereby the radial dimension of the separator tank 61 can be reduced to reduce the space occupied by the separator tank in the radial direction.

Based on this, when the buffer inlet 664 is opened on the side wall of the buffer tank 64 in the direction in which one of the radial lines of the buffer tank 64 is located (i.e., the first linear direction in the horizontal plane) with reference to fig. 7. If the buffer outlet 661 on the side wall of the buffer tank 64 is disposed in a direction in which the exhaust pipe 62 is located in a direction opposite to the first straight line direction, when the lower end of the exhaust pipe 62 is installed close to the buffer tank 64, the gas-liquid two-phase refrigerant or the liquid refrigerant flowing in from the buffer outlet 661 is sucked into the compressor 10 from the lower end of the exhaust pipe 62, and the compressor 10 is damaged (as shown in fig. 2).

To solve this problem, a buffer outlet 661 and an exhaust pipe 62 may be provided on opposite sides of the buffer tank 64 in the first straight direction. Taking the case where the first straight line direction is the left-right direction, the lower end of the exhaust pipe 62 may be located at the left side of the buffer tank 64, and the buffer outlet 661 may be opened at the right side wall of the buffer tank 64. Thus, the mixed refrigerant or the liquid refrigerant in the gas-liquid two-phase state flowing out of the buffer outlet 661 can flow from left to right into the separation chamber 65. The mixed refrigerant or the liquid refrigerant of the gas-liquid two-phase state flowing out to the right may be collected downward at the lower portion of the separation chamber 65, and secondary separation may occur. Since the exhaust pipe 62 is positioned at the left side of the buffer tank 64, the mixed refrigerant of gas-liquid two phases or the gaseous refrigerant is prevented from being directly sucked into the exhaust pipe 62.

The buffer outlet 661 may be formed in the front side wall and the rear side wall of the buffer tank 64, and the mixed refrigerant or the liquid refrigerant in the gas-liquid two-phase state flowing out of the buffer outlet 661 may be prevented from being directly sucked into the exhaust pipe 62 only by avoiding the buffer outlet 661 facing the exhaust pipe 62 in the first linear direction, which is not limited.

When the surge tank 64 is installed, as shown in fig. 9, fig. 9 is a schematic perspective view of the surge tank 64 shown in fig. 7. The buffer tank 64 may have a cylindrical structure, or may have a triangular prism, a rectangular parallelepiped, a pentagonal prism, or the like. Taking the example that the axis of the buffer tank 64 is parallel to the up-down direction, the buffer outlet 661 may be formed on a circumferential side wall of the buffer tank 64, and the buffer inlet 664 may be formed at an upper end (e.g., a top wall) of the buffer tank 64, so that the buffer inlet 664 may communicate with the buffer outlet 661 through a buffer chamber (not shown). In the separation chamber 65, the lower end of the air intake pipe 63 may be inserted into the buffer chamber through the buffer inlet 664 in the upward direction so that the buffer tank 64 may be in contact with the air intake pipe 63.

For example, since the air inlet pipe 63 may be fixedly connected to the separating tank 61 at the edge of the air inlet 663, after the lower end of the air inlet pipe 63 is inserted into the buffer chamber, the edge of the buffer tank 64 near the buffer inlet 664 may be connected to the air inlet pipe 63, for example, by fixedly connecting by welding, or by connecting by matching a nut and a sealing rubber ring, so that the positioning and mounting of the buffer tank 64 in the separating chamber 65 may be realized.

In addition, only the lower end of the intake pipe 63 may be inserted into the buffer chamber. In positioning the buffer tank 64, a plurality of brackets may be provided in the separation chamber 65, and the inner wall of the separation tank 61 may be connected to the outer wall of the buffer tank 64 through the plurality of brackets to position the buffer tank 64 at a predetermined position in the separation chamber 65. Wherein, a plurality of supports can be distributed on the circumference side of the buffer tank 64, and the supports, the buffer tank 64 and the separation tank 61 can be fixedly connected by welding. At this time, the air inlet pipe 63 and the buffer tank 64 may be connected hermetically near the edge of the buffer inlet 664, for example, by packing a gap between the air inlet pipe 63 and the edge of the buffer inlet 664. The lower end of the air inlet pipe 63 can be directly inserted into the buffer cavity, and only the air inlet pipe 63 is required to be partially contacted with the buffer tank 64 at the edge of the buffer inlet 664, namely, part of the primarily separated gaseous refrigerant can flow to the separation cavity 65 from the gap, so that the gas-liquid separation effect of the buffer tank 64 is not affected.

In the process of flowing the gas-liquid two-phase refrigerant into the buffer tank 64 through the gas inlet pipe 63, as shown in fig. 7, the gas-liquid two-phase refrigerant is prevented from directly entering the separation chamber 65 through the buffer outlet 661 after striking the inner wall of the buffer tank 64. The lower end of the intake pipe 63 may be provided with a slope structure, and the refrigerant from the intake pipe may be reduced by increasing the outlet area of the outlet end (i.e., lower end) of the intake pipe 63. Illustratively, the angle between the slope edge of the outlet at the lower end of the air inlet pipe 63 and the up-down direction may be 15 ° to 75 °, such as 15 °, 30 °, 45 °, 60 °, or 75 °. If the surge tank 64 has a large size in the up-down direction, the inclined edge of the lower end outlet of the intake pipe 63 may be set at an angle of 15 ° or 30 ° with respect to the up-down direction so that the lower end outlet of the intake pipe 63 has a large outlet area in the surge chamber. If the size of the surge tank 64 in the up-down direction is small, the lower end of the intake pipe 63 may be set to be 45 ° or 60 °, and the outlet area of the lower end of the intake pipe 63 may be increased as much as possible while ensuring that the lower ends of the intake pipe 63 are all located in the surge chamber.

In the case where the lower end of the air intake pipe 63 is provided with a slope structure, the buffer outlet 661 is provided in the side wall of the buffer tank 64 in the first linear direction as an example. Along the first straight line direction, the slope structure of the air inlet pipe 63 may be disposed towards a side far away from the buffer outlet 661, so as to avoid the refrigerant flowing out laterally from directly flowing into the separation chamber 65 from the buffer outlet 661, so as to reduce the primary gas-liquid separation effect.

In the case where the buffer outlet 661 is formed in the right side wall of the buffer tank 64, the lower end of the intake pipe 63 may be provided with a slope structure facing the front side wall or the rear side wall of the buffer tank 64. Alternatively, the slope structure may be flexibly set from the front side of the buffer tank 64 to the rear side wall of the buffer tank 64 in the clockwise direction from top to bottom, and only by avoiding the slope structure from facing the buffer inlet in the first linear direction.

As shown in fig. 10, fig. 10 is a schematic diagram of a connection structure of an air conditioner 100 according to the related art. The air conditioner 100 may further include a liquid storage tank 72, an economizer 73, and a make-up air electric control valve 74, and, for example, a cooling operation, a refrigerant may circulate between the compressor 10, the outdoor heat exchanger 30, the liquid storage tank 72, the economizer 73, the first throttle 40, the indoor heat exchanger 50, the gas-liquid separator 60, and the compressor 10. Because the refrigerant flowing from the air outlet end 12 of the compressor 10 to the outdoor heat exchanger 30 for liquefying and releasing heat has a higher temperature, the heat exchange efficiency of the refrigerant is affected. Based on this, the compressor 10 may be provided as a gas-supplementing enthalpy-increasing compressor, and the compressor 10 is provided with a gas-supplementing end 13 communicating with the gas-outlet end 12 in addition to the gas-inlet end 11 and the gas-outlet end 12. After entering the compressor 10 from the air inlet end 11, the gaseous refrigerant is primarily compressed under the work of the compressor 10. The air-supplementing end 13 of the compressor 10 may be located between the air-intake end 11 and the air-outlet end 12 along the flow direction of the refrigerant, so that the primarily compressed gaseous refrigerant may be mixed with the gaseous refrigerant sucked by the air-supplementing end 13, and further compressed in the compressor 10, and then flows from the air-outlet end 12 to the outdoor heat exchanger 30. At this time, the compressed refrigerant may have a higher pressure and a lower temperature, and the refrigerating capacity of the compressor 10 may be increased, which is advantageous for improving the energy efficiency ratio of the air conditioner 100.

With continued reference to fig. 10, the economizer 73 has two heat exchange passages therein which can exchange heat, one end of the first heat exchange passage can be connected to the accumulator 72, and the other end of the heat exchange passage can be connected to the first throttle 40. One end of the second heat exchange passage may be connected to the liquid reservoir 72 through the air make-up electronically controlled valve 74, and the other end of the heat exchange passage may be connected to the air make-up end 13 of the compressor 10. In this way, when the air-supplementing electric control valve 74 is opened during the process of flowing the liquid refrigerant from the liquid storage tank 72 to the first restrictor 40, part of the liquid refrigerant can flow into the second heat exchange channel due to the function of the restrictor, and the part of the liquid refrigerant can absorb the heat of the liquid refrigerant in the first heat exchange channel due to the pressure reduction in the second heat exchange channel, and is vaporized in the second heat exchange channel, and the temperature of the refrigerant in the first heat exchange channel is lower. The vaporized refrigerant in the second heat exchange path may then be drawn into the air-make-up end 13 of the compressor 10 along the conduit to increase the energy efficiency ratio of the air conditioner 100.

However, the arrangement of the economizer in the above embodiment makes the structure of the air conditioner 100 more complicated. In order to simplify the structure of the air conditioner 100, as shown in fig. 11, fig. 11 is a side view of the gas-liquid separator 60 shown in fig. 5. The gas-liquid separator 60 may further be provided with a gas-compensating port 665, the gas-compensating port 665 may be provided at a position above a top wall or a side wall of the separation tank 61, and the gas-compensating port 665 may communicate with the separation chamber 65 (shown in fig. 7) for outputting the separated gaseous refrigerant. When the gas-liquid separator 60 with the gas-supplementing port 665 is used, as shown in fig. 12, fig. 12 is a schematic diagram of a connection structure of the air conditioner including the gas-supplementing enthalpy-increasing compressor 10 according to the embodiment of the application. One end of the make-up electric control valve 74 may be connected to the separator tank 61 and communicate with the make-up port 665, and the other end of the make-up electric control valve 74 may be connected to the make-up end 13 of the compressor 10, so that the make-up electric control valve 74 may be used to control the closing or communication of the refrigerant passage from the make-up port 665 to the intake end 11. Thus, when the air conditioner 100 is in the refrigeration condition, a part of the gaseous refrigerant can be sucked into the compressor 10 through the air inlet end 11 of the compressor 10 by the air outlet pipe 62 and is primarily compressed, then another part of the gaseous refrigerant can be sucked into the compressor 10 through the air supplementing end 13 by the air supplementing opening 665 via the opened air supplementing electric control valve 74, after being mixed with the primarily compressed first part of the refrigerant, the mixed refrigerant can be further compressed by the compressor 10, the temperature of the gaseous refrigerant flowing out from the air outlet end 12 of the compressor 10 can be reduced, and the refrigerating capacity of the compressor 10 can be increased, so that the energy efficiency ratio of the air conditioner 100 can be increased.

The embodiment of the application can realize the supplement of the gaseous refrigerant to the air supplementing end 13 by additionally arranging the air supplementing port 665 on the separating tank 61, and can improve the energy efficiency ratio of the air conditioner 100 by increasing the refrigerating capacity of the compressor 10 and reducing the exhaust temperature. Compared with the technical proposal that the gas refrigerant is supplemented to the gas supplementing end 13 through the additionally arranged economizer 73 in the prior art. This solution is simple and effective without adding additional components in the air conditioner 100.

In some embodiments, as shown in fig. 11, a bypass port 666 may be provided in the separation tank 61, the bypass port 666 may be in communication with the separation chamber 65 shown in fig. 7, and the bypass port 666 may be provided in an upper position of the separation tank 61. When the gas-liquid separator 60 is installed, in connection with fig. 12, the air conditioner 100 may further include a bypass electric control valve 75, and the bypass opening 666 may communicate with the gas outlet end 12 of the compressor 10 or the gas inlet side of the indoor heat exchanger 30 through the bypass electric control valve 75, and the bypass electric control valve 75 may be in a normally closed state. Thus, when the air conditioner 100 is turned off, the bypass electric control valve 75 can be controlled to be opened, so that the separation tank 61 can be communicated with the air outlet end 12 and the indoor heat exchanger 30, and the overall pressure of the refrigerant circulation inside the air conditioner 100 is balanced.

With continued reference to fig. 11, the separator tank 61 may also be provided with a drain 667, with the drain 667 opening at the lower end of the separator tank 61. Can be directly arranged at the drain outlet 667 and used for controlling the opening and closing of the drain outlet 667, and the drain valve can be set to be in a normally closed state. When the drain valve is opened, solid or liquid impurities accumulated at the lower end of the separation tank 61 may be discharged through the drain port 667.

Since the liquid refrigerant is accumulated in the gas-liquid separation tank 61, when the liquid refrigerant accumulated in the separation tank 61 is excessive, the liquid refrigerant is mixed with the gaseous refrigerant discharged from the exhaust pipe 62 and the gas-compensating port 665. As shown in fig. 5, the separation tank 61 may further be provided with a viewing port 668, and the viewing port 668 may be in communication with the separation chamber 65 (as shown in fig. 7), and in conjunction with fig. 11, the viewing port 668 on the separation tank 61 may be disposed below the air supply port 665 and the air discharge pipe 62. The number of the viewing holes 668 may be one or plural, and the plurality of viewing holes 668 may be distributed at intervals in the vertical direction on the separation tank 61. Correspondingly, the gas-liquid separator 60 may further include first light-transmitting plates 67, and the number of the first light-transmitting plates 67 may be the same as that of the viewing holes 668 and one-to-one corresponding to the number of the viewing holes. For example, a first light-transmitting plate 67 may be attached to the edge of a viewing aperture 668 and seal the viewing aperture 668.

At a viewing port 668, the separation tank 61 and a first light-transmitting plate 67 may be adhesively connected for sealing the viewing port 668. The first light-transmitting plate 67 can be fixedly clamped at the liquid viewing hole 668 in a clamping limiting mode, and a gap at the edge of the liquid viewing hole 668 can be filled with the first light-transmitting plate 67 in a matched mode, so that the first light-transmitting plate 67 is in sealing connection with the liquid viewing hole 668. In this way, the first light-transmitting plate 67 and the viewing aperture 668 facilitate the inspection of the liquid level of the liquid refrigerant in the separation chamber 65, and the more the viewing aperture 668, the higher the detection accuracy.

Further, with continued reference to fig. 11, the separator tank 61 is provided with a sensor interface 669 that communicates with the separator chamber 65 (shown in fig. 7). Based on this, as shown in fig. 13, fig. 13 is a schematic circuit connection diagram according to an embodiment of the present application. The air conditioner 100 may further include a controller 81 and a liquid level sensor 76. The liquid level sensor 76 may be inserted into the separation chamber 65 through the sensor interface 669, and is configured to detect a liquid level of the liquid refrigerant in the separation chamber 65, and may output a liquid level acquisition signal. Correspondingly, the first throttle 40 may be an electronic expansion valve, the controller 81 may be electrically connected to the liquid level sensor 76 and the first throttle 40, and the controller 81 may receive a liquid level acquisition signal output from the liquid level sensor 76.

For example, the controller 81 may include a comparison circuit of a relay structure to facilitate setting a preset liquid level threshold value, such that the controller 81 may compare the received liquid level acquisition signal with the preset liquid level threshold value, and when the liquid level acquisition signal is greater than or equal to the preset liquid level threshold value (i.e., a liquid refrigerant having a higher liquid level is accumulated in the separation chamber 65), the controller 81 may control the opening degree of the first throttle 40 to be reduced. At this time, taking the example that the air conditioner 100 is under the cooling condition, the flow rate of the liquid refrigerant flowing into the indoor heat exchanger 50 through the first throttle 40 is reduced, and less liquid refrigerant can be fully evaporated and vaporized at the indoor heat exchanger 50, i.e. the liquid refrigerant in the separation tank 61 can be quickly vaporized and flows into the compressor 10, so as to reduce the amount of liquid refrigerant flowing into the separation tank 61.

It should be noted that, as shown in fig. 13, the controller 81 may be further electrically connected to the bypass electric control valve 75, for example, the controller 81 may include a bypass relay electrically connected to the bypass electric control valve 75, for controlling the opening or closing of the bypass electric control valve 75. The controller 81 may also be electrically connected to the electrically controlled valve 74, e.g., the controller 81 may include an electrically controlled valve relay electrically connected to the electrically controlled valve 74 for controlling the opening or closing of the electrically controlled valve 74.

In other embodiments, the controller 81 may also be an integrated circuit board, etc. and may be configured to control the air-make-up electric control valve 74, the bypass electric control valve 75 and the first throttle 40 by a preset program and different preset parameters, which are not limited thereto.

Because the air conditioner 100 generally adopts the compressor 10 with a variable frequency structure, the rotation speed of the compressor 10 is convenient to control, so that the compressor 10 can be operated in an optimal rotation speed state according to different user working conditions, and the energy efficiency ratio of the air conditioner 100 is improved. When driving the compressor 10 of the inverter type structure, as shown in fig. 4, the air conditioner 100 may further include an inverter 82, and the inverter 82 may be electrically connected with the compressor 10 and control the rotation speed of the compressor 10. In this way, the frequency converter 82 can control and regulate the rotation speed of the compressor 10, so that the compressor 10 can operate in an optimal rotation speed state according to different user working conditions, and the energy efficiency ratio of the air conditioner 100 is improved.

When the load of the working condition of the user is large, the frequency converter 82 needs to output large power to control the frequency-converted compressor 10 to operate at high speed, which results in a large heating value of the frequency converter 82. To solve the heat dissipation problem of the inverter 82.

As shown in fig. 14, the air conditioner 100 may further include a variable frequency heat radiating assembly 90, and the variable frequency heat radiating assembly 90 may include a water tank 91, a water-cooled heat exchanger 92, a circulation pump 93, and a variable frequency heat exchanger 94.

In connection with fig. 15, the water-cooled heat exchanger 92 may be installed in contact with the inverter 82 shown in fig. 4, or the water-cooled heat exchanger 92 may be installed in contact with the inverter 82 through other heat conducting structures for absorbing heat generated from the inverter 82. Wherein, the water-cooled heat exchanger 92 can be split type component, namely, the water-cooled heat exchanger 92 can include two heating panels 921 and water-cooled radiating pipe 922, be water-cooled heat transfer passageway (not shown in the figure) in the water-cooled radiating pipe 922, the water-cooled radiating pipe 922 can be extruded between two heating panels 921 to with two heating panels 921 laminating contact, the heating panel 921 can be connected with converter 82 contact, so that the heat that converter 82 produced can be taken away to the coolant liquid that water-cooled heat transfer passageway (i.e. in the water-cooled radiating pipe 922) flowed through for quick cooling down converter 82, guarantee that converter 82 can last the low temperature operation, have better stability.

In addition, the water-cooled heat exchanger 92 may be an integral member, a sidewall of the water-cooled heat exchanger 92 may contact the inverter 82, and a water-cooled heat exchanging channel (not shown) may be formed inside the water-cooled heat exchanger 92 for flowing a cooling liquid and taking away heat generated from the inverter 82. To rapidly cool the inverter, with continued reference to fig. 14, one end of the water-cooled heat exchanger 92 may be in communication with the water tank 91, and the other end of the water-cooled heat exchanger 92 may be in communication with one end of the inverter heat exchanger 94. And the variable frequency heat exchanger 94 may be communicated with the water tank 91 through a circulation pump 93. Based on this, an appropriate amount of cooling liquid (such as cooling water or a mixed solution of water and an antifreezing agent) may be added into the water tank 91, and the cooling liquid may circulate in the water tank 91, the circulation pump 93, the variable frequency heat exchanger 94, the water-cooled heat exchanger 92, and the water tank 91 by being driven by the circulation pump 93. Thus, in conjunction with fig. 15, the heat generated by the frequency converter 82 during high-load operation can be quickly absorbed by the cooling liquid flowing through the water-cooled heat exchanger 92, and the heat can be quickly emitted along with the cooling liquid flowing through the frequency-converted heat exchanger 94, so as to realize a continuous and stable cooling effect on the frequency converter 82, and avoid damage to the frequency converter 82 caused by continuous high-temperature overload.

The circulation pump 93 may be installed between the water tank 91 and the inverter heat exchanger 94 as shown in fig. 14. The circulation pump 93 may be installed between the water-cooled heat exchanger 92 and the variable frequency heat exchanger 94. The cooling liquid can be driven to circulate in the water tank 91, the circulation pump 93, the variable frequency heat exchanger 94, the water-cooled heat exchanger 92 and the water tank 91, which is not limited.

For the variable frequency heat exchanger 94, a heat exchanger of a gas-liquid structure such as a coil heat exchanger, a fin heat exchanger or a flat tube heat exchanger may be provided as the variable frequency heat exchanger 94 for heat exchange between gas and liquid. At this time, the variable frequency heat exchanger 94 is provided with a first heat exchange channel corresponding to the water-cooling heat exchange channel, one end of the first heat exchange channel may be communicated with one end of the water-cooling heat exchange channel, the other end of the water-cooling heat exchange channel may be communicated with the liquid inlet side of the water tank 91, and the other end of the first heat exchange channel may be communicated with the liquid outlet side of the water tank 91 through the circulation pump 93. So that the cooling fluid absorbs heat from the inverter 82 at the water-cooled heat exchange passage and then radiates heat to the nearby air through the inverter heat exchanger 94 at the first heat exchange passage. At this time, in order to improve the heat dissipation efficiency of the variable frequency heat exchanger 94, the variable frequency heat dissipation assembly 90 may further include a heat dissipation fan, which may be installed near the variable frequency heat exchanger 94, for driving air to rapidly flow through the variable frequency heat exchanger 94, so as to improve the heat exchange efficiency of the cooling liquid and the air in the first heat exchange channel, and satisfy the requirement of rapid heat dissipation.

In addition, the variable frequency heat exchanger 94 may be a liquid-liquid type heat exchanger such as a plate heat exchanger or a shell-and-tube heat exchanger, and may be used for heat exchange between liquids. Taking the variable frequency heat exchanger 94 as an example, as shown in fig. 16, fig. 16 is a schematic diagram of a connection structure of the variable frequency heat dissipating assembly 90 according to the embodiment of the present application for dissipating heat by circulating the refrigerant of the compressor 10. The variable frequency heat exchanger 94 may include a first heat exchange channel 941 and a second heat exchange channel 942. Along the flow direction of the refrigerant, the downstream port of the first heat exchange passage 941 may communicate with the water-cooled heat exchanger 92, and the upstream port of the first heat exchange passage 941 may communicate with the water tank 91 through the circulation pump 93.

Correspondingly, with continued reference to fig. 16, the variable frequency heat sink assembly 90 may further include a second restrictor 95, and one end of the second heat exchange channel 942 may be in communication with the first restrictor 40 through the second restrictor 95. For example, an end of the second throttle 95 remote from the variable frequency heat exchanger 94 may be connected to any refrigerant line between the first throttle 40 and the outdoor heat exchanger 30 in the flow direction of the refrigerant. Alternatively, the end of the second throttle 95 remote from the variable frequency heat exchanger 94 may be connected to any refrigerant line between the first throttle 40 and the indoor heat exchanger 50. It is only necessary to enable the liquid refrigerant to flow through the second restrictor 95 into the second heat exchange channel 942 for vaporization in the variable frequency heat exchanger 94 and to absorb heat in the first heat exchange channel 941, thereby rapidly removing heat generated by the variable frequency heat exchanger 82 (shown in fig. 15).

As shown in fig. 16, the refrigerant in the second heat exchange channel 942 can flow out from the other end of the second heat exchange channel 942 after evaporating and vaporizing by absorbing heat. Based on this, the end of the second heat exchanging channel 942 may be provided to communicate with the inlet end of the compressor 10, thereby achieving the circulating flow of the refrigerant at the second heat exchanging channel 942. For example, if the air inlet end of the compressor 10 is connected to the gas-liquid separator 60, the air inlet end of the second heat exchange channel 942 may be connected to the air inlet side of the gas-liquid separator 60, and after being separated by the gas-liquid separator 60, the gaseous refrigerant may be sucked into the compressor 10 to be compressed and circulated.

It should be noted that, if the air conditioner 100 has only a single cooling mode, the end of the second heat exchange channel 942 away from the second restrictor 95 may be disposed to communicate with the end of the indoor heat exchanger 50 away from the first restrictor 40.

In addition, if the gas-liquid separator 60 is not connected at the intake end of the compressor 10, the end of the second heat exchange passage 942 remote from the second restrictor 95 may be directly communicated with the intake end of the compressor 10. Alternatively, if the air conditioner 100 includes the four-way valve 20, the end of the second heat exchanging channel 942 remote from the second restrictor 95 may be in communication with the first port a of the four-way valve 20. The expanded gaseous refrigerant may be fed into the compressor 10.

To facilitate controlling the heat dissipation capacity of the variable frequency heat sink assembly 90 so that the frequency converter 92 (shown in fig. 15) may be operated in a suitable temperature range, supercooling or overheating of the frequency converter 82 is avoided. As shown in fig. 17, the variable frequency heat sink assembly 90 may further include at least one of a temperature sensor 96 and a flow switch 97. For example, a temperature sensor 96 may be installed between the water-cooled heat exchanger 92 and the inverter heat exchanger 94 in the flow direction of the cooling liquid for detecting the temperature of the cooling liquid flowing from the inverter heat exchanger 94 to the water-cooled heat exchanger 92, and the temperature sensor 96 may output a temperature acquisition signal. The temperature sensor 96 may be installed near the variable frequency heat exchanger 94 or near the water-cooled heat exchanger 92, but is not limited thereto.

With continued reference to fig. 17, when the flow switch 97 is installed, the circulation pump 93 may communicate with the first heat exchange channel 941 through the flow switch 97, and the flow switch 97 may be used to monitor the flow rate of the coolant flowing through the circulation pump 93 and output a flow rate acquisition signal. The flow switch 97 may be installed between the water tank 91 and the circulation pump 93, and the flow collection signal may be output, which is not limited thereto.

Based on this, in connection with fig. 13, the controller 81 may be electrically connected to the temperature sensor 96, the flow switch 97, the circulation pump 93, and the inverter 82. And the controller 81 can control the circulating pump 93 and the frequency converter 82 to start synchronously, so that the frequency conversion heat dissipation component can dissipate heat of the frequency converter 82 in time. When the frequency converter 82 is turned off, the circulating pump 93 may be turned off in a delayed manner to cool the waste heat of the frequency converter 82, and the delayed turn-off function of the circulating pump 93 may be satisfied by a delay relay. Correspondingly, the second restrictor 95 may also be provided as an electronic expansion valve, and the controller 81 may also be electrically connected to the second restrictor 95.

For example, the controller 81 may include a comparison circuit having a temperature controller or a relay, etc. to facilitate the preset temperature threshold value to be set in advance. In this way, the controller 81 may receive the temperature acquisition signal output from the temperature sensor and compare the temperature acquisition signal with a first preset temperature threshold. When the temperature acquisition signal is greater than or equal to the first preset temperature threshold, it indicates that the temperature of the cooling liquid flowing out of the variable frequency heat exchanger 94 is higher, at this time, the controller 81 may control the second restrictor 95 to open or increase the opening degree to increase the flow rate of the cooling medium in the second heat exchange channel 942, so that the temperature of the cooling liquid flowing out of the first heat exchange channel 941 is lower, thereby rapidly cooling the variable frequency heat exchanger 82 and operating in a suitable temperature interval.

In addition, the first temperature threshold may be set to be greater than the second temperature threshold, and if the temperature acquisition signal received by the controller 81 is less than the second preset temperature threshold, it indicates that the temperature of the cooling liquid flowing out of the variable frequency heat exchanger 94 is lower, so that the frequency converter 82 is rapidly cooled and is operated in a lower temperature environment. At this time, the controller 81 may control the second restrictor 95 to decrease the opening degree or close. To reduce the flow rate of the refrigerant in the second heat exchange channel 942 and even stop the circulating flow of the refrigerant in the second heat exchange channel 942. So that the higher temperature coolant flowing out of the first heat exchange channel 941 avoids operating the inverter 82 in a lower temperature environment.

After receiving the temperature acquisition signal, the controller 81 may also adjust the operating temperature environment of the inverter 82 by controlling the rotational speed of the circulation pump 93. If the temperature acquisition signal is greater than or equal to the first preset temperature threshold, the controller 81 may increase the rotation speed of the circulation pump 93 to take away more heat from the frequency converter 82 through the rapid circulation flow of the cooling liquid. If the temperature acquisition signal is less than the second preset temperature threshold, the controller 81 may decrease the rotation speed of the circulation pump 93 to decrease the flow rate of the cooling liquid, thereby reducing the heat exchange with the frequency converter 82 at the water-cooled heat exchanger 92.

In some embodiments, as shown in fig. 18, the variable frequency heat sink assembly 90 may further include a variable frequency heat exchanger tank 98, and the water tank 91, the circulation pump 93, and the variable frequency heat exchanger 94 are mounted within the variable frequency heat exchanger tank 98. In the case where the variable frequency heat sink assembly 90 further includes the second restrictor 95, the temperature sensor 96 and the flow switch 97, the second restrictor 95, the temperature sensor 96 and the flow switch 97 are installed in the variable frequency heat sink box 98. Thus, when the variable frequency heat sink assembly 90 is disposed, the variable frequency heat exchange box 98 having the above-mentioned components mounted thereon may be disposed close to the outdoor unit of the air conditioner 100 or may be directly mounted in the outdoor unit, and then the water-cooled heat exchanger 92 (shown in fig. 15) may be mounted in contact with the frequency converter 82, and then the water-cooled heat exchanger may be passed through the variable frequency heat exchange box 98 through a pipe so that one end of the water-cooled heat exchange passage communicates with the water tank 91 and the other end of the water-cooled heat exchange passage communicates with the outlet side of the first heat exchange passage. In the process, components such as the water tank 91, the circulating pump 93, the second restrictor 95 of the variable frequency heat exchanger 94, the temperature sensor 96, the flow switch 97 and the like are not required to be additionally installed and arranged, and the installation process is convenient and quick.

In the variable frequency heat sink assembly 90, the water tank 91 is a main structure for storing the cooling liquid. As shown in fig. 19, fig. 19 is a front view of a water tank 91 shown in fig. 18. The water tank 91 may be a split structure, including a tank main body 911 and a tank top cover 912, the tank main body 911 may enclose a solution chamber 913 having an opening at one side, the solution chamber 913 is used for containing a cooling liquid, and the tank top cover 912 may be disposed close to the opening of the solution chamber 913 and connected to an upper edge of the tank main body 911, taking an example that the opening of the solution chamber 913 is located at an upper side of the tank main body 911. The case main body 911 and the case top 912 may be connected to each other by rivets or welding, or the case main body 911 and the case top 912 may be detachably connected to each other by screws or a clip structure.

With continued reference to fig. 19, one or more vent holes 9141 may be provided in the tank top cover 912 to equalize the air pressure inside and outside the solution chamber 913. Correspondingly, a liquid inlet 9142, a liquid outlet 9143 and a liquid outlet 9144 which are communicated with the solution cavity 913 can be formed on the tank main body 911. The liquid inlet 9142 and the liquid outlet 9143 may be formed on a side wall of the main tank body 911, for example, the liquid inlet 9142 and the liquid outlet 9143 may be formed on a front side wall of the main tank body 911 and distributed at intervals along a left-right direction. The drain hole 9144 may be formed near the bottom of the tank body 911, for example, the drain hole 9144 may be formed in the bottom wall of the tank body 911.

Based on this, during the process of installing the variable frequency heat dissipation assembly 90, along the flow direction of the cooling liquid, one end of the water-cooling heat exchange channel, which is close to the water tank 91, may be communicated with the liquid inlet 9142 for injecting the cooling liquid after absorbing heat into the solution cavity 913. And the liquid outlet 9143 may be communicated with one end of the first heat exchange channel 941 near the water tank 91 through the circulation pump 93, for extracting the cooling liquid (after absorbing heat) in the solution cavity 913 and cooling in the first heat exchange channel 941.

As shown in fig. 20, fig. 20 is a right side view of the water tank shown in fig. 19. The case body 911 may be provided with a bar-shaped hole 9145, and the bar-shaped hole 9145 may be provided on a side wall (e.g., a right side wall) of the case body 911 and extend in the up-down direction. The water tank 91 may further include a second light-transmitting plate 915, and the second light-transmitting plate 915 may be connected to an edge of the strip-shaped hole 9145 and seal the strip-shaped hole 9145, thereby preventing leakage of cooling liquid from the strip-shaped hole 9145 in the solution chamber 913. Since the second light-transmitting plate 915 has better light transmittance, the liquid level of the cooling liquid in the tank main body 911 can be clearly observed through the second light-transmitting plate 915 and the strip-shaped holes 9145.

Illustratively, as shown in fig. 21, fig. 21 is a rear view of the tank shown in fig. 19. The side wall of the tank main body 911 may be provided with a liquid replenishing hole 9146 for replenishing the cooling liquid into the solution chamber 913. Referring to fig. 13, the tank 91 may further include a drain valve 916 and a make-up valve 917. Wherein, one end of the fluid-filling valve 917 may be in communication with the fluid-filling hole 9146, and the other end of the fluid-filling valve 917 may be used to connect a water supply pipe, and the fluid-filling valve 917 may be in a normally closed state.

Illustratively, one end of the drain valve 916 may be in communication with the drain hole 9144, and the drain valve 916 is also normally closed. The make-up valve 917 and the drain valve 916 may be electrically controlled valves, and the controller 81 may be electrically connected to the make-up valve 917 and the drain valve 916. The controller 81 may receive the flow rate acquisition signal of the flow rate switch 97, compare the flow rate acquisition signal with a preset flow rate threshold, and if the flow rate acquisition signal is less than or equal to the preset flow rate threshold, it indicates that the cooling liquid in the water tank 91 is less, and at this time, may control the valve of the liquid replenishment valve 917 to be opened so as to add replenishment cooling into the solution cavity 913.

The controller 81 can control the opening state of the liquid replenishing valve 917 through a time delay relay, and after a preset time, the time delay relay can automatically close the liquid replenishing valve 917, so that the overflow of the replenished cooling liquid from the solution cavity 913 is avoided. In the case where the drain valve 916 is not activated for a long time, the drain valve 916 may be controlled to be opened by the controller 81 to drain the coolant in the solution chamber 913. The drain valve 916 may be a manual valve, that is, the drain valve 916 may be opened or closed manually, which is not limited thereto.

In other embodiments, the water tank 91 may be a unitary structure surrounded by the tank main body 911, which has better sealing performance. In this case, it is necessary to provide an air vent 9141 in the tank main body 911 to balance the air pressure inside and outside the solution chamber 913.

In the description of the present specification, a particular feature, structure, material, or characteristic may be combined in any suitable manner in one or more embodiments or examples.

The present application is not limited to the above embodiments, and any changes or substitutions that can be easily understood by those skilled in the art within the technical scope of the present application are intended to be included in the scope of the present application. Therefore, the protection scope of the application is subject to the protection scope of the claims.

Claims

1. An air conditioner, comprising:

a compressor having an intake end;

and a gas-liquid separator comprising:

a separation tank having a separation chamber;

one end of the exhaust pipe is inserted into the separation cavity, and the other end of the exhaust pipe is communicated with the air inlet end;

the air inlet pipe is inserted into the separation cavity at one end;

and a buffer tank located within the separation chamber; the air inlet pipe is positioned at one end of the separation cavity and is inserted into the buffer tank, and the buffer tank is provided with a buffer outlet communicated with the separation cavity.

2. The air conditioner according to claim 1, wherein an air inlet is provided at an upper end of the separation tank in a vertical direction, the air inlet being in communication with the separation chamber;

The lower end of the air inlet pipe is inserted into the separation cavity through the air inlet and is in sealing connection with the separation tank, and the lower end of the air inlet pipe is inserted into the buffer tank.

3. The air conditioner of claim 2, wherein the buffer tank has a buffer chamber;

along the vertical direction, the upper end of the buffer tank is provided with a buffer inlet, and the lower end of the air inlet pipe is inserted into the buffer cavity through the buffer inlet and is in contact connection with the buffer tank;

along a first straight line direction, the buffer outlet is arranged on the side wall of the buffer tank, and the first straight line direction is perpendicular to the vertical direction.

4. An air conditioner according to claim 3 wherein the buffer outlet and the bleed duct are located on opposite sides of the buffer chamber in the first linear direction.

5. The air conditioner of claim 3, wherein a lower end of the air inlet pipe is of a slope structure in the vertical direction for increasing an opening area of a lower end of the air inlet end;

in the buffer chamber, the ramp structure is disposed in a direction away from the buffer outlet.

6. The air conditioner according to claim 2, wherein an air outlet is further provided at an upper end of the separation tank in the vertical direction, and the air outlet communicates with the separation chamber;

The lower end of the exhaust pipe is inserted into the separation cavity through the exhaust port and is in sealing connection with the separation tank.

7. The air conditioner according to any one of claims 1 to 6, wherein the compressor is a make-up enthalpy compressor, the compressor further having an air outlet end and an air inlet end, the air inlet end being in communication with the air outlet end, and the air inlet end being in communication with the air outlet end; the air supplementing end is positioned between the air inlet end and the air outlet end along the flowing direction of the refrigerant;

the air conditioner further comprises an air supplementing electric control valve, the separating tank is further provided with an air supplementing port, and the air supplementing port is communicated with the separating cavity; one end of the air supplementing electric control valve is connected with the separating tank and conducts the air supplementing port, and the other end of the air supplementing electric control valve is connected with the air supplementing end of the compressor; the air supplementing electric control valve is used for controlling the closing or the conduction of a refrigerant channel between the air supplementing port and the air inlet end of the compressor.

8. The air conditioner according to any one of claims 1 to 6, further comprising:

the four-way valve is provided with a first port, a second port, a third port and a fourth port; the first port is connected with one end, far away from the separation cavity, of the air inlet pipe, and one end, far away from the separation cavity, of the air outlet pipe is connected with the air inlet end of the compressor; the compressor is further provided with an air outlet end, and the air outlet end of the compressor is connected with the second port;

An outdoor heat exchanger, one end of which is connected with the third port;

a first throttle; one end of the first throttle is connected with the other end of the outdoor heat exchanger;

the indoor heat exchanger is connected with the other end of the first throttle at one end and the other end of the indoor heat exchanger is connected with the fourth port;

when the air conditioner is in a refrigerating working condition, the second port and the third port are communicated, and the first port and the fourth port are communicated; when the air conditioner is in a heating working condition, the second port and the fourth port are conducted, and the first port and the third port are conducted.

9. The air conditioner according to claim 8, wherein the separation tank is provided with a sensor interface, the sensor interface being in communication with the separation chamber;

the air conditioner further comprises a controller and a liquid level sensor; the liquid level sensor is inserted into the separation cavity through the sensor interface; the liquid level sensor is used for detecting the liquid level height in the separation cavity and outputting a liquid level acquisition signal; the first throttle is an electronic expansion valve, and the controller is electrically connected with the first throttle and the liquid level sensor and receives the liquid level acquisition signal;

When the liquid level acquisition signal is greater than or equal to a preset liquid level threshold value, the controller controls the opening degree of the first restrictor to be reduced.

10. The air conditioner according to claim 7, wherein the separation tank is provided with a liquid viewing hole communicated with the separation chamber, and the liquid viewing hole is positioned below the air supply port and the exhaust pipe in the vertical direction;

the gas-liquid separator also comprises a first light-transmitting plate, wherein the first light-transmitting plate is arranged in one-to-one correspondence with the liquid viewing holes, and one first light-transmitting plate is connected with one edge of the liquid viewing hole and seals the liquid viewing hole.