CN109682134B - Gas-liquid separator and heat pump system - Google Patents
Gas-liquid separator and heat pump system Download PDFInfo
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- CN109682134B CN109682134B CN201811516993.2A CN201811516993A CN109682134B CN 109682134 B CN109682134 B CN 109682134B CN 201811516993 A CN201811516993 A CN 201811516993A CN 109682134 B CN109682134 B CN 109682134B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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Abstract
The invention discloses a gas-liquid separator and a heat pump system, relates to the technical field of air conditioning, and is used for improving the refrigerant circulation quantity of the heat pump system so as to improve the low-temperature heating capacity of the heat pump system. The gas-liquid separator includes: the air suction device comprises a shell, wherein an air inlet interface, an air suction interface and a liquid return interface are arranged on the shell; the balance pipe is sleeved in the liquid return interface, a liquid inlet of the balance pipe is positioned in the shell, and a liquid outlet of the balance pipe is positioned outside the shell; the ejector pipe comprises a first pipe section, a second pipe section and a third pipe section which are sequentially communicated, a connector connected with the liquid outlet of the balance pipe is arranged on the second pipe section, and the pipe diameter of the second pipe section is smaller than that of the first pipe section and that of the third pipe section. The gas-liquid separator provided by the invention can introduce the separated liquid refrigerant into the circulating pipeline of the heat pump system, so that the refrigerant circulating amount is increased, and the low-temperature heating capacity of the heat pump system is improved.
Description
Technical Field
The invention relates to the technical field of air conditioning, in particular to a gas-liquid separator and a heat pump system.
Background
When the air source heat pump system operates at high ambient temperature, the compressor can meet the requirements of users by operating at a lower frequency due to higher energy in the air, and the air source heat pump system has higher economical efficiency. However, when the compressor is operated at a low ambient temperature, the amount of heating is significantly reduced even if the compressor is operated at a high frequency because the energy in the air is low. And at the moment, the heating quantity required by a user is generally increased, the heating quantity is reduced while the demand is increased, and the dual contradiction causes the use of the air source heat pump at a lower environmental temperature to be greatly limited, so that the user demand is difficult to meet.
Disclosure of Invention
The invention aims to provide a gas-liquid separator and a heat pump system, which are used for improving the refrigerant circulation amount of the heat pump system and improving the low-temperature heating capacity of the heat pump system.
In order to achieve the above purpose, the invention provides the following technical scheme:
a first aspect of the present invention provides a gas-liquid separator comprising: the air suction device comprises a shell, wherein an air inlet interface, an air suction interface and a liquid return interface are arranged on the shell; the balance pipe is sleeved in the liquid return interface, a liquid inlet of the balance pipe is positioned in the shell, and a liquid outlet of the balance pipe is positioned outside the shell; the ejector pipe comprises a first pipe section, a second pipe section and a third pipe section which are sequentially communicated, a connector connected with the liquid outlet of the balance pipe is arranged on the second pipe section, and the pipe diameter of the second pipe section is smaller than that of the first pipe section and that of the third pipe section.
Optionally, the gas-liquid separator further comprises an air suction pipe sleeved in the air suction interface, the air suction port of the air suction pipe is positioned in the shell, and the air exhaust port of the air suction pipe is positioned outside the shell; the pipe section of the air suction pipe in the shell is of a U-shaped structure with an upward opening, the lowest point of the U-shaped structure is provided with an oil return hole, the liquid inlet of the balance pipe is lower than the air suction port of the air suction pipe, and the liquid inlet of the balance pipe is higher than the oil return hole.
Optionally, the height between the liquid inlet of the balance pipe and the bottom wall of the shell is h1The height between the air suction port of the air suction pipe and the bottom wall of the shell is h2The height between the oil return hole of the air suction pipe and the bottom wall of the shell is h3Wherein, 1.1h3≤h1≤0.6h2。
Optionally, the gas-liquid separator further comprises a solenoid valve disposed on a section of the balancing pipe located outside the housing, and the solenoid valve is used for controlling on-off of the balancing pipe and adjusting flow of the balancing pipe.
Optionally, the gas-liquid separator further comprises a first throttling element provided on a section of the balancing pipe located outside the housing.
Optionally, a first tapered transition pipe section is arranged between the second pipe section and the first pipe section, and the pipe diameter of the first tapered transition pipe section is gradually increased in a direction from the second pipe section to the first pipe section; and a second conical transition pipe section is arranged between the second pipe section and the third pipe section, and the pipe diameter of the second conical transition pipe section is gradually increased in the direction from the second pipe section to the third pipe section.
Optionally, the second pipe section has a pipe diameter d1The pipe diameters of the first pipe section and the third pipe section are d2Wherein, 0.6d2≤d1≤0.85d2。
Based on the above technical solution of the gas-liquid separator, the second aspect of the present invention provides a heat pump system, which includes a compressor, a gas cooler, an evaporator, and the gas-liquid separator in any one of the above technical solutions, which are connected in sequence from end to end through a pipeline; the heat pump system further includes: the high-pressure pipeline of the heat regenerator is connected in series with the pipeline between the gas cooler and the evaporator, and the low-pressure pipeline of the heat regenerator is connected in series with the pipeline between the evaporator and the gas inlet interface of the gas-liquid separator; the second throttling element is arranged on a pipeline between the high-pressure pipeline of the heat regenerator and the evaporator; the ejector pipe of the gas-liquid separator is connected in series with the pipeline between the low-pressure pipeline of the heat regenerator and the evaporator, or the ejector pipe of the gas-liquid separator is connected in series with the pipeline between the second throttling element and the evaporator.
Optionally, the compressor comprises a first-stage compression cavity and a second-stage compression cavity which are connected in series, and an external interface is arranged between the first-stage compression cavity and the second-stage compression cavity; the heat pump system further includes: the main flow path of the economizer is connected in series with a pipeline between the gas cooler and the high-pressure pipeline of the heat regenerator, and the secondary flow path of the economizer is connected in series with a pipeline between the gas cooler and the external interface of the compressor; a third throttling element provided on the conduit between the gas cooler and the secondary flowpath of the economizer; and the one-way valve is arranged on a pipeline between the auxiliary flow path of the economizer and the external interface of the compressor and is used for conducting the pipeline from the auxiliary flow path of the economizer to the external interface of the compressor in a one-way mode.
Based on the above technical solution of the gas-liquid separator, the third aspect of the present invention provides a heat pump system, which includes a compressor, a gas cooler, an evaporator, and the gas-liquid separator in any one of the above technical solutions, which are connected in sequence from end to end through a pipeline; the compressor comprises a first-stage compression cavity and a second-stage compression cavity which are connected in series, and an external interface is arranged between the first-stage compression cavity and the second-stage compression cavity; the heat pump system further includes: the main flow path of the economizer is connected in series with a pipeline between the gas cooler and the evaporator, and the auxiliary flow path of the economizer is connected in series with a pipeline between the gas cooler and an external interface of the compressor; a third throttling element provided on the conduit between the gas cooler and the secondary flowpath of the economizer; and the injection pipe of the gas-liquid separator is connected in series with a pipeline between the third throttling element and the secondary flow path of the economizer.
Compared with the prior art, the gas-liquid separator and the heat pump system provided by the invention have the following beneficial effects:
according to the gas-liquid separator provided by the invention, the shell is provided with the air inlet interface, the air suction interface and the liquid return interface, when the gaseous refrigerant enters the shell from the air inlet interface of the shell, gas-liquid separation can be realized so as to further reduce liquid phase components in the gaseous refrigerant, and the separated gaseous refrigerant can be discharged to the outside of the shell from the air suction interface of the shell so as to be compressed by the compressor, so that the phenomenon of air suction and liquid return of the compressor is reduced, and the compressor is not easy to damage. The liquid refrigerant separated from the shell can enter the balance pipe from the liquid inlet of the balance pipe, and the liquid refrigerant entering the balance pipe can be discharged to the outside of the shell from the liquid outlet of the balance pipe. The injection pipe comprises a first pipe section, a second pipe section and a third pipe section which are sequentially communicated, wherein a connecting port is arranged on the second pipe section and is connected with a liquid outlet of the balance pipe, and the pipe diameter of the second pipe section is smaller than that of the first pipe section and that of the third pipe section. When the ejector pipe is connected in series with the circulating pipeline of the heat pump system, the refrigerant in the circulating pipeline of the heat pump system can flow through the first pipe section, the second pipe section and the third pipe section of the ejector pipe, and the flow rate of the refrigerant in the circulating pipeline of the heat pump system is increased and the pressure of the refrigerant in the circulating pipeline of the heat pump system is reduced when the refrigerant flows through the second pipe section of the ejector pipe. Because the pressure of the second pipe section is less than the pressure in the shell, differential pressure can be established, the liquid refrigerant in the shell is sucked into the second pipe section of the injection pipe through the balance pipe, so that the liquid refrigerant in the shell can be mixed with the refrigerant in the circulating pipeline of the heat pump system to carry out secondary circulation, the liquid refrigerant is not easy to deposit in the shell, the refrigerant circulation quantity is improved, the heating capacity of the heat pump system at low ambient temperature can be improved, and the heat pump system has strong low-temperature heating capacity.
The beneficial effects that the heat pump system provided by the invention can achieve are the same as those that the gas-liquid separator provided by the technical scheme can achieve, and are not described herein again.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 shows a schematic configuration of a gas-liquid separator according to an embodiment of the present invention;
FIG. 2 shows a schematic structural view of a housing of one embodiment of the present invention;
FIG. 3 shows a schematic structural view of a balance tube of one embodiment of the present invention;
FIG. 4 shows a schematic of the gas-liquid separator of one embodiment of the present invention;
FIG. 5 shows a schematic diagram of an ejector tube according to an embodiment of the invention;
fig. 6 shows a schematic configuration diagram of a heat pump system according to an embodiment of the present invention.
Reference numerals:
10-gas-liquid separator, 102-shell, 104-air inlet interface,
106-an air suction interface, 108-a balance pipe, 110-a liquid inlet of the balance pipe,
112-ejector tube, 114-first tube section, 116-second tube section,
118-third pipe section, 120-solenoid valve, 122-first throttling element,
124-liquid return interface, 126-liquid discharge port of balance pipe, 128-air suction pipe,
130-suction inlet of suction pipe, 132-discharge outlet of suction pipe, 134-oil return hole,
136-an air inlet pipe, 138-a connecting port, 140-a first conical transition pipe section,
142-second conical transition piece, 202-compressor, 204-gas cooler,
206-evaporator, 208-drive, 210-regenerator,
212-the high pressure line of the regenerator, 214-the low pressure line of the regenerator, 216-the second throttling element,
218-first stage compression chamber, 220-second stage compression chamber, 222-economizer,
224-the main flow path of the economizer, 226-the secondary flow path of the economizer, 228-the third throttling element,
230-one-way valve.
Detailed Description
For the sake of understanding, the gas-liquid separator and the heat pump system according to the embodiments of the present invention will be described in detail with reference to the drawings attached to the specification.
Referring to fig. 1 to 5, a gas-liquid separator 10 according to an embodiment of the present invention includes: a shell 102, wherein the shell 102 is provided with an air inlet interface 104, an air suction interface 106 and a liquid return interface 124; the balance pipe 108 is sleeved in the liquid return interface 124, the liquid inlet 110 of the balance pipe 108 is positioned inside the shell 102, and the liquid outlet 126 of the balance pipe 108 is positioned outside the shell 102; the ejector pipe 112 comprises a first pipe section 114, a second pipe section 116 and a third pipe section 118 which are sequentially communicated, the second pipe section 116 is provided with a connecting port 138 connected with the liquid outlet 126 of the balance pipe 108, and the pipe diameter of the second pipe section 116 is smaller than that of the first pipe section 114 and the third pipe section 118.
According to the gas-liquid separator 10 provided by the invention, the shell 102 is provided with the air inlet interface 104, the air suction interface 106 and the liquid return interface 124, when the gaseous refrigerant enters the shell 102 from the air inlet interface 104 of the shell 102, gas-liquid separation can be realized, so that the liquid phase component in the gaseous refrigerant is further reduced, the separated gaseous refrigerant can be discharged to the outside of the shell 102 from the air suction interface 106 of the shell 102 for being compressed by the compressor, the phenomenon of air suction and liquid return of the compressor is reduced, and the compressor is not easily damaged. By enclosing the balance pipe 108 in the liquid return port 124 of the housing 102, the liquid inlet 110 of the balance pipe 108 is located inside the housing 102, and the liquid outlet 126 of the balance pipe 108 is located outside the housing 102, so that the liquid refrigerant separated from the inside of the housing 102 can enter the balance pipe 108 from the liquid inlet 110 of the balance pipe 108, and the liquid refrigerant entering the balance pipe 108 can be discharged to the outside of the housing 102 from the liquid outlet 126 of the balance pipe 108. The injection pipe 112 comprises a first pipe section 114, a second pipe section 116 and a third pipe section 118 which are sequentially communicated, a connecting port 138 is arranged on the second pipe section 116, the connecting port 138 is connected with the liquid outlet 126 of the balance pipe 108, and the pipe diameter of the second pipe section 116 is smaller than that of the first pipe section 114 and that of the third pipe section 118. When the ejector tube 112 is connected in series with the circulation line of the heat pump system, the refrigerant in the circulation line of the heat pump system flows through the first segment 114, the second segment 116, and the third segment 118 of the ejector tube 112, and the refrigerant in the circulation line of the heat pump system increases in flow rate and decreases in pressure when flowing through the second segment 116 of the ejector tube 112. Because the pressure at the second pipe section 116 is smaller than the pressure inside the shell 102, a pressure difference can be established, so that the liquid refrigerant inside the shell 102 is sucked into the second pipe section 116 of the ejector pipe 112 through the balance pipe 108, the liquid refrigerant inside the shell 102 can be mixed with the refrigerant in the circulating pipeline of the heat pump system to perform secondary circulation, the liquid refrigerant is not easy to deposit inside the shell 102, the refrigerant circulation amount is increased, the heating capacity of the heat pump system at low ambient temperature can be increased, and the heat pump system has strong low-temperature heating capacity.
For example, referring to fig. 6, the ejector tube 112 of the gas-liquid separator 10 may be connected in series to a pipe between the evaporator 206 and the heat regenerator 210 of the heat pump system, so that the liquid refrigerant inside the housing 102 can be mixed with the refrigerant in the circulating pipe of the heat pump system, and then the liquid refrigerant is gasified by an internal heat exchanger (e.g., the heat regenerator 210) and finally participates in the whole cycle. The problem of liquid refrigerant accumulation in the gas-liquid separator 10 is effectively solved, and the refrigerant circulation amount passing through the compressor 202 is increased, thereby realizing the improvement of the low-temperature heating capacity.
Illustratively, the balance tube 108 and the liquid return interface 124 are hermetically connected, and refrigerant inside the housing 102 is not easy to leak to the outside of the housing 102 from a connection part between the balance tube 108 and the liquid return interface 124.
It should be noted that the gas-liquid separator 10 according to the present invention improves the problem that a large amount of liquid refrigerant accumulates inside the casing 102 of the gas-liquid separator 10 and it is difficult to exhibit the heating capability, and also improves the problem that the heat pump system is degraded in the amount of heat generation at low ambient temperatures. The gas-liquid separator 10 has a simple structure, and can gasify the liquid refrigerant in the shell 102 and then participate in the circulation of the entire apparatus without additional power input, for example, without adding an additional electric heating device, thereby greatly increasing the refrigerant circulation amount.
It should be noted that a multi-split air conditioner capable of heating in winter and cooling in summer and having a four-way reversing valve also belongs to the technical field of air conditioning, and the present invention can also cover this field, and all air conditioning systems that adjust the refrigerant circulation amount by using the gas-liquid separator 10 can achieve improvement of low-temperature heating capability by the present invention.
Illustratively, referring to FIG. 4, the second pipe segment 116 has a pipe diameter d1The pipe diameters of the first pipe segment 114 and the third pipe segment 118 are d2Wherein, 0.6d2≤d1≤0.85d2. In this embodiment, the first pipe segment 114 and the third pipe segment 118 have pipe diameters d2The refrigerant in the circulating line of the heat pump system has equal flow rate and uniform pressure when flowing through the first segment 114 and the third segment 118 of the ejector tube 112. The second pipe section 116 has a pipe diameter d1，0.6d2≤d1≤0.85d2This allows the second section 116 of the eductor tube 112 to be of a smaller diameter, allowing the refrigerant to flow through the second section 116 of the eductor tube 112 at an increased flow rate and a reduced pressure, which allows the pressure at the second section to be less than the pressure inside the shell 102, thereby allowing a pressure differential to be established, and at the same time allowing the pressure differential to be established as much as possibleThe amount reduces the throttling effect caused by the necking. By the scheme, the liquid refrigerant in the shell 102 can be sucked into the second pipe section 116 of the injection pipe 112, so that the liquid refrigerant in the shell 102 can be mixed with the original refrigerant in the circulating pipeline of the heat pump system to perform secondary circulation, the liquid refrigerant is not easy to deposit in the shell 102, the refrigerant circulation quantity is increased, the heating capacity of the heat pump system at low ambient temperature can be increased, and the heat pump system has strong low-temperature heating capacity.
Wherein when d1Equal to or close to 0.6d2At times, the pressure differential between the second pipe segment and the interior of the housing 102 is greater. When d is1Equal to or close to 0.85d2At times when the pressure differential between the second pipe segment and the interior of the housing 102 is small, the throttling effect created at the second pipe segment is correspondingly reduced.
It should be noted that the pipe diameter of the balance pipe 108 may be smaller than or equal to the pipe diameter of the second pipe section 116, or may be slightly larger than the pipe diameter of the second pipe section 116. At this time, the pressure of the refrigerant at the second section 116 of the ejector tube 112 is still lower than the pressure of the refrigerant inside the shell 102, and is not affected by the diameter of the balance tube 108.
In some embodiments, referring to fig. 5, the gas-liquid separator 10 further comprises a suction pipe 128 nested within the suction port 106, a suction port 130 of the suction pipe 128 being located inside the housing 102, and a discharge port 132 of the suction pipe 128 being located outside the housing 102; the section of the air suction pipe 128 located inside the housing 102 is in a U-shaped structure with an upward opening, an oil return hole 134 is formed at the lowest point of the U-shaped structure, the liquid inlet 110 of the balance pipe 108 is lower than the air inlet 130 of the air suction pipe 128, and the liquid inlet 110 of the balance pipe 108 is higher than the oil return hole 134.
In this embodiment, the pipe section of the suction pipe 128 located inside the casing 102 is in a U-shaped structure with an upward opening, so that the suction port 130 of the suction pipe 128 is located at a higher position inside the casing 102, the suction and liquid return phenomena are not easy to occur, and the compressor 202 is not easy to damage. Oil return of the compressor 202 can be realized by arranging the oil return hole 134 at the lowest point of the U-shaped structure (i.e. the pipe section of the air suction pipe 128 positioned in the shell 102), and the oil compression phenomenon is not easy to occur due to the small oil return hole 134, so that the compressor 202 is not easy to damage. The liquid inlet 110 of the balance pipe 108 is located between the air suction port 130 of the air suction pipe 128 and the oil return hole 134, so that the gaseous refrigerant and the lubricating oil inside the shell 102 are not easy to enter a circulation pipeline of the heat pump system through the balance pipe 108 and the injection pipe 112, and further the oil compression phenomenon is not easy to occur, and the gaseous refrigerant is not easy to be sucked away, thereby reducing the suction amount of the compressor 202.
Illustratively, the suction pipe 128 is hermetically connected with the suction port 106, and the refrigerant inside the casing 102 is not easily leaked to the outside of the casing 102 from the connection part between the suction pipe 128 and the suction port 106.
Illustratively, referring to FIG. 5, the inlet orifice 110 of the balance tube 108 has a height h from the bottom wall of the housing 1021The height h between the suction opening 130 of the suction pipe 128 and the bottom wall of the casing 1022The height h between the oil return hole 134 of the suction pipe 128 and the bottom wall of the housing 1023Wherein, 1.1h3≤h1≤0.6h2。
In this embodiment, when h1 is equal to or close to 1.1h3, it is ensured that the balance tube 108 is filled with as liquid refrigerant as possible, rather than lubricating oil. When h1 is equal to or close to 0.6h2, the liquid level in the shell 102 can not exceed h2, and the long-term safe operation of the system is ensured. When the liquid level is between 1.1h3 and 0.6h2, the liquid refrigerant can be led out of the shell 102 through the balance pipe 108 and the ejector pipe 112, so that the aim of adjusting the whole refrigerant circulation quantity is fulfilled.
Illustratively, referring to fig. 5, an air inlet pipe 136 is sleeved in the air inlet port 104 of the housing 102, and an end of the air inlet pipe 136 located inside the housing 102 is located at an upper portion of the inner space of the housing 102 and is spaced apart from the air inlet 130 of the air suction pipe 128.
Illustratively, the air inlet pipe 136 and the air inlet interface 104 are hermetically connected, and the refrigerant inside the housing 102 is not easy to leak to the outside of the housing 102 from the connection part between the air inlet pipe 136 and the air inlet interface 104.
Illustratively, as shown in fig. 1 and 5, the balance tube 108 extends through the bottom of the housing 102 and extends vertically upward into the interior of the housing 102 to a height h 1.
In some embodiments, referring to fig. 1, 3 and 5, the gas-liquid separator 10 further comprises a solenoid valve 120 disposed on a section of the balancing pipe 108 outside the housing 102, the solenoid valve 120 being configured to open and close the balancing pipe 108 and to regulate the flow rate of the balancing pipe 108.
In this embodiment, the solenoid valve 120 is provided to facilitate the control of the refrigerant in the balance pipe 108, so as to determine whether the liquid refrigerant flows out of the shell 102 from the inside of the shell 102 to the outside of the shell 102 through the balance pipe 108. Meanwhile, the flow can be adjusted, and the probability of the phenomenon of air suction and liquid return of the compressor 202 caused by overlarge flow speed of the liquid refrigerant is reduced.
In some embodiments, referring to fig. 1, 3, and 5, the gas-liquid separator 10 further includes a first throttling element 122 disposed on a section of the balancing pipe 108 that is external to the housing 102. Illustratively, the first throttling element 122 is an electronic expansion valve, a thermal expansion valve, or a capillary tube, etc.
In this embodiment, by providing the first throttling element 122 on the pipe section of the balance pipe 108 outside the shell 102, the refrigerant flowing through the balance pipe 108 can be throttled and depressurized, and the probability of occurrence of the suction-liquid return phenomenon of the compressor 202 due to an excessive flow rate of the liquid refrigerant can be further reduced.
Illustratively, referring to fig. 1, 3 and 5, the balance pipe 108 has a solenoid valve 120 and a first throttling element 122 spaced apart on a pipe segment outside the housing 102, wherein the order of the first throttling element 122 and the solenoid valve 120 is adjustable.
In some embodiments, referring to fig. 4, a first tapered transition pipe segment 140 is disposed between the second pipe segment 116 and the first pipe segment 114, and the pipe diameter of the first tapered transition pipe segment 140 gradually increases in a direction from the second pipe segment 116 to the first pipe segment 114; a second conical transition pipe section 142 is arranged between the second pipe section 116 and the third pipe section 118, and the pipe diameter of the second conical transition pipe section 142 increases gradually in the direction from the second pipe section 116 to the third pipe section 118. In this embodiment, the first tapered transition pipe section 140 and the second tapered transition pipe section 142 can reduce the throttling effect caused by the necking as much as possible, so that the state of the refrigerant is relatively stable.
On the other hand, referring to fig. 6, based on the above-mentioned solution of the gas-liquid separator 10, an embodiment of the present invention provides a heat pump system, which includes a compressor 202, a gas cooler 204, an evaporator 206, and the gas-liquid separator 10 in any one of the above solutions, which are connected end to end by a pipeline in sequence. The heat pump system further includes: the regenerator 210 and the high-pressure line 212 of the regenerator 210 are connected in series to the pipeline between the gas cooler 204 and the evaporator 206, and the low-pressure line 214 of the regenerator 210 is connected in series to the pipeline between the evaporator 206 and the gas inlet interface 104 of the gas-liquid separator 10. And a second throttling element 216 disposed on the pipe between the high-pressure pipe 212 of the regenerator 210 and the evaporator 206. The ejector pipe 112 of the gas-liquid separator 10 is connected in series to the pipeline between the low-pressure pipeline 214 of the regenerator 210 and the evaporator 206, or the ejector pipe 112 of the gas-liquid separator 10 is connected in series to the pipeline between the second throttling element 216 and the evaporator 206. The second throttling element 216 may be, for example, an electronic expansion valve or a thermal expansion valve or a capillary tube, etc.
In the heat pump system provided by the present invention, the gas cooler 204 is a device for exchanging heat between a refrigerant and a cooling medium, the gas cooler 204 may be a double-pipe heat exchanger, a shell-and-tube heat exchanger, a plate heat exchanger, or other heat exchangers in various forms, the cooling medium may be water or air, and a corresponding driving device 208, such as a water pump or a blower, may be disposed on a cooling medium circuit.
The evaporator 206 is a device for exchanging heat between refrigerant and an ambient medium, the ambient medium may be air, and when the ambient medium is air, the ambient medium is called an air source heat pump, and the evaporator 206 may be a finned tube heat exchanger. The environmental medium may also be water, which is called a water source heat pump when the environmental medium is water, and the evaporator 206 may be a plate heat exchanger or a double pipe heat exchanger.
In the heating operation, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 202 exchanges heat with the cooling medium in the gas cooler 204 to form a liquid refrigerant. The liquid refrigerant flowing through the second throttling element 216 is throttled and depressurized, and then reduced in pressure, and then evaporated and absorbed heat in the evaporator 206, thereby forming a gaseous refrigerant. The gaseous refrigerant enters the gas-liquid separator 10 to undergo gas-liquid separation, and the separated gaseous refrigerant having a lower liquid-phase component is returned to the compressor 202 for compression.
The high-pressure pipeline 212 of the heat regenerator 210 is connected in series to the pipeline between the gas cooler 204 and the evaporator 206, the low-pressure pipeline 214 of the heat regenerator 210 is connected in series to the pipeline between the evaporator 206 and the gas inlet interface 104 of the gas-liquid separator 10, and the liquid refrigerant with higher temperature in the high-pressure pipeline 212 of the heat regenerator 210 exchanges heat with the gaseous refrigerant with lower temperature in the low-pressure pipeline 214 of the heat regenerator 210. By the above scheme, on one hand, the refrigerant can enter the low-pressure pipeline of the heat regenerator 210 to be heated to a superheated state, and the liquid-phase component in the gaseous refrigerant is reduced, so that the risk that the liquid refrigerant enters the compressor 202 for compression can be reduced. On the other hand, the dryness of the liquid refrigerant with higher temperature in the high-pressure pipeline 212 of the heat regenerator 210 is favorably reduced, that is, the gas phase component in the liquid refrigerant with higher temperature in the high-pressure pipeline 212 of the heat regenerator 210 is reduced, so that the operation energy efficiency of the heat pump system can be improved.
Illustratively, regenerator 210 may be a plate heat exchanger, a double tube heat exchanger, or other form of refrigerant-to-refrigerant heat exchanger.
When the ejector pipe 112 of the gas-liquid separator 10 is connected in series to the pipe between the low-pressure pipe 214 of the regenerator 210 and the evaporator 206, the gaseous refrigerant flowing out of the evaporator 206 flows to the ejector pipe 112, and when the gaseous refrigerant flows through the second pipe section 116 of the ejector pipe 112, the flow rate is increased and the pressure is reduced, and because the pressure is smaller than the pressure inside the casing 102 of the gas-liquid separator 10, a pressure difference can be established, so that the liquid refrigerant inside the casing 102 of the gas-liquid separator 10 is introduced into the second pipe section 116 of the ejector pipe 112, and the liquid refrigerant inside the casing 102 can be mixed with the original gaseous refrigerant in the circulating pipe. The mixed refrigerant enters the regenerator 210 for heat exchange to form a gaseous refrigerant. Through the scheme, the liquid refrigerant is not easy to deposit in the shell 102 of the gas-liquid separator 10, the refrigerant circulation quantity is increased, the heating capacity of the heat pump system at low ambient temperature can be increased, and the heat pump system has strong low-temperature heating capacity.
When the ejector pipe 112 of the gas-liquid separator 10 is connected in series to the pipe between the second throttling element 216 and the evaporator 206, the liquid refrigerant throttled and depressurized by the second throttling element 216 flows to the ejector pipe 112, the flow rate is increased and the pressure is reduced when the liquid refrigerant flows through the second pipe section 116 of the ejector pipe 112, and because the pressure is lower than the pressure inside the shell 102 of the gas-liquid separator 10, a pressure difference can be established, so that the liquid refrigerant inside the shell 102 of the gas-liquid separator 10 is introduced into the second pipe section 116 of the ejector pipe 112 through the balance pipe 108, the liquid refrigerant inside the shell 102 can be mixed with the original liquid refrigerant in the circulating pipe, and the mixed refrigerant enters the evaporator 206 to absorb heat and be gasified, so as to form the gaseous refrigerant. Through the scheme, the liquid refrigerant is not easy to deposit in the shell 102 of the gas-liquid separator 10, the refrigerant circulation quantity is increased, the heating capacity of the heat pump system at low ambient temperature can be increased, and the heat pump system has strong low-temperature heating capacity.
For example, referring to fig. 6, the compressor 202 includes a first-stage compression chamber 218 and a second-stage compression chamber 220 connected in series, and an external interface is provided between the first-stage compression chamber 218 and the second-stage compression chamber 220; the heat pump system further includes: an economizer 222, a primary flow path 224 of the economizer 222 being connected in series with the conduit between the gas cooler 204 and the high pressure line 212 of the regenerator 210, and a secondary flow path 226 of the economizer 222 being connected in series with the conduit between the gas cooler 204 and the external interface of the compressor; a third throttling element 228 provided on the conduit between the gas cooler 204 and the secondary flowpath 226 of the economizer 222; and a check valve 230 provided in a pipe between the sub-flow passage 226 of the economizer 222 and the external port of the compressor 202, wherein the check valve 230 is configured to allow the pipe to be communicated in one direction from the sub-flow passage 226 of the economizer 222 to the external port of the compressor 202. Illustratively, the third throttling element 228 may be an electronic expansion valve or a thermal expansion valve or a capillary tube, etc.
In this embodiment, the compressor 202 may be a single-stage two-stage compression structure, and has a first-stage compression chamber 218 and a second-stage compression chamber 220 inside, the external suction end of the compressor 202 is connected to the suction port of the first-stage compression chamber 218, the discharge port of the first-stage compression chamber 218 is connected to the suction port of the second-stage compression chamber 220, and the discharge port of the second-stage compression chamber 220 is connected to the discharge end of the compressor 202. After the compression of the gaseous refrigerant in the first-stage compression cavity 218 is completed, the gaseous refrigerant enters the second-stage compression cavity 220 for compression, and finally the high-temperature and high-pressure gaseous refrigerant is discharged from the discharge end of the compressor 202. The pressure at the communication portion between the discharge port of the first-stage compression chamber 218 and the suction port of the second-stage compression chamber 220 is equal, and the external port is opened at the communication portion.
The primary 224 and secondary 226 flow paths of the economizer 222 each have two interfaces, one in and one out. A portion of the liquid refrigerant exiting the gas cooler 204 flows into the main flow path 224 of the economizer 222. The other part of the liquid refrigerant flowing out of the gas cooler 204 is throttled and depressurized by the third throttling element 228 to form a low-temperature and low-pressure liquid refrigerant, and then flows into the secondary flow path 226 to exchange heat with the higher-temperature liquid refrigerant in the main flow path 224. After the heat exchange is completed, the temperature of the liquid refrigerant in the main flow path 224 is reduced, and the refrigeration capacity of the whole system is improved. The refrigerant in the secondary flow path 226 absorbs heat and turns into a gaseous state, and then returns to the external interface of the compressor 202, so as to supplement air to the communication part between the exhaust port of the primary compression cavity 218 and the suction port of the secondary compression cavity 220, improve the air delivery capacity of the compressor 202, and improve the low-temperature heating capacity of the heat pump system. And a check valve 230 is provided in the supplementary air branch (i.e., a pipe between the sub-flow path 226 of the economizer 222 and an external port of the compressor 202) to prevent the supplementary air branch from leaking the refrigerant, and only supplementary air is allowed without leaking the refrigerant to the outside.
In summary, the economizer 222 performs the intermediate air make-up function, so that the attenuation of the heating capacity caused by the reduction of the overall refrigerant circulation amount is minimized, thereby improving the low-temperature heating capacity and greatly improving the usability of the heat pump system at low ambient temperature.
Illustratively, the heat pump system may be a carbon dioxide heat pump, which may utilize a carbon dioxide refrigerant, employing a transcritical cycle. The carbon dioxide refrigerant has excellent physical properties, low viscosity and large refrigerating capacity per unit volume, the refrigerating capacity per unit volume is three times that of the common refrigerant, and particularly, the low-ambient-temperature heating performance is greatly improved compared with that of the common refrigerant, and the low-temperature heating attenuation amplitude is small, so that the carbon dioxide refrigerant is very suitable for being used in cold regions. And because the low-temperature heating attenuation amplitude of the carbon dioxide refrigerant is small, the carbon dioxide refrigerant can stably heat the carbon dioxide heat pump at the temperature of-35 ℃ by matching with the economizer 222 and the gas-liquid separator 10, and the application range of the carbon dioxide heat pump is greatly expanded.
It is worth noting that the flow of the carbon dioxide transcritical refrigeration cycle is slightly different from the conventional vapor compression refrigeration cycle. At this time, the suction pressure of the compressor 202 is lower than the critical pressure, the evaporation temperature is also lower than the critical temperature, the heat absorption process of the cycle is still performed under the subcritical condition, and the heat exchange process is mainly completed by latent heat. However, the discharge pressure of the compressor 202 is higher than the critical pressure, the condensing process of the refrigerant is completely different from that in the subcritical state, and the heat exchange process is performed by means of sensible heat, and at this time, the high-pressure heat exchanger is not called as a condenser any more, but is called as a gas cooler 204.
In another aspect, referring to fig. 6, based on the above-mentioned technical solution of the gas-liquid separator 10, an embodiment of the present invention provides a heat pump system, which includes a compressor 202, a gas cooler 204, an evaporator 206, and the gas-liquid separator 10 in any one of the above-mentioned technical solutions, which are connected end to end by a pipeline; the compressor 202 comprises a first-stage compression cavity 218 and a second-stage compression cavity 220 which are connected in series, and an external interface is arranged between the first-stage compression cavity 218 and the second-stage compression cavity 220; the heat pump system further includes: an economizer 222, a main flow path 224 of the economizer 222 being connected in series with the piping between the gas cooler 204 and the evaporator 206, and a secondary flow path 226 of the economizer 222 being connected in series with the piping between the gas cooler 204 and the external interface of the compressor; a third throttling element 228 provided on the conduit between the gas cooler 204 and the secondary flowpath 226 of the economizer 222; wherein the ejector tube 112 of the gas-liquid separator 10 is connected in series to the conduit between the third throttling element 228 and the secondary flowpath 226 of the economizer 222.
In the heat pump system provided by the invention, the injection pipe 112 of the gas-liquid separator 10 is connected in series with the pipeline between the third throttling element 228 and the secondary flow path 226 of the economizer 222, the liquid refrigerant after being throttled and decompressed by the third throttling element 228 flows to the injection pipe 112, the flow rate is increased and the pressure is reduced when the liquid refrigerant flows through the second pipe section 116 of the injection pipe 112, since the pressure is lower than the pressure inside the casing 102 of the gas-liquid separator 10, a pressure difference can be established, the introduction of the liquid refrigerant inside the casing 102 of the gas-liquid separator 10 into the second pipe section 116 of the ejector pipe 112 through the equalizing pipe 108 is achieved, so that the liquid refrigerant inside the shell 102 can be mixed with the liquid refrigerant existing in the circulation pipe, the mixed refrigerant enters the economizer 222 to exchange heat, to form gaseous refrigerant, and finally the gaseous refrigerant is returned to the external interface of the compressor 202 to increase the amount of return air to the compressor 202. Through the scheme, the liquid refrigerant is not easy to deposit in the shell 102 of the gas-liquid separator 10, the refrigerant circulation quantity is increased, the heating capacity of the heat pump system at low ambient temperature can be increased, and the heat pump system has strong low-temperature heating capacity.
In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.
Claims (15)
1. A heat pump system is characterized by comprising a compressor, a gas cooler, an evaporator and a gas-liquid separator which are sequentially connected end to end through pipelines;
the heat pump system further includes:
the high-pressure pipeline of the heat regenerator is connected in series with the pipeline between the gas cooler and the evaporator, and the low-pressure pipeline of the heat regenerator is connected in series with the pipeline between the evaporator and the gas inlet interface of the gas-liquid separator;
the second throttling element is arranged on a pipeline between a high-pressure pipeline of the heat regenerator and the evaporator;
the ejector pipe of the gas-liquid separator is connected in series with a pipeline between a low-pressure pipeline of the heat regenerator and the evaporator, or the ejector pipe of the gas-liquid separator is connected in series with a pipeline between the second throttling element and the evaporator;
the gas-liquid separator includes:
the air suction device comprises a shell, wherein an air inlet interface, an air suction interface and a liquid return interface are arranged on the shell;
the balance pipe is sleeved in the liquid return interface, a liquid inlet of the balance pipe is positioned in the shell, and a liquid outlet of the balance pipe is positioned outside the shell;
the injection pipe comprises a first pipe section, a second pipe section and a third pipe section which are sequentially communicated, a connector connected with a liquid outlet of the balance pipe is arranged on the second pipe section, and the pipe diameter of the second pipe section is smaller than that of the first pipe section and that of the third pipe section.
2. The heat pump system of claim 1, wherein the gas-liquid separator further comprises a suction pipe nested within the suction interface, a suction port of the suction pipe being located inside the housing, a discharge port of the suction pipe being located outside the housing;
the pipe section of the air suction pipe located in the shell is of a U-shaped structure with an upward opening, an oil return hole is formed in the lowest point of the U-shaped structure, a liquid inlet of the balance pipe is lower than an air suction port of the air suction pipe, and a liquid inlet of the balance pipe is higher than the oil return hole.
3. The heat pump system of claim 2, wherein the liquid inlet of the balance pipe has a height h from the bottom wall of the housing1The air suction port of the air suction pipe is far away from the shellThe height between the bottom walls of the body is h2The height between the oil return hole of the air suction pipe and the bottom wall of the shell is h3Wherein, 1.1h3≤h1≤0.6h2。
4. The heat pump system according to claim 1, wherein the gas-liquid separator further comprises a solenoid valve disposed on a section of the balancing pipe located outside the housing, the solenoid valve being configured to control on/off of the balancing pipe and to adjust a flow rate of the balancing pipe.
5. The heat pump system of claim 1, wherein the gas-liquid separator further comprises a throttling element disposed on a section of the balancing pipe external to the housing.
6. The heat pump system according to any one of claims 1 to 5, wherein a first tapered transition pipe section is arranged between the second pipe section and the first pipe section, and the pipe diameter of the first tapered transition pipe section gradually increases in a direction from the second pipe section to the first pipe section;
and a second conical transition pipe section is arranged between the second pipe section and the third pipe section, and the pipe diameter of the second conical transition pipe section is gradually increased in the direction from the second pipe section to the third pipe section.
7. The heat pump system according to any one of claims 1-5, wherein the second tube segment has a tube diameter d1The pipe diameters of the first pipe section and the third pipe section are d2Wherein, 0.6d2≤d1≤0.85d2。
8. The heat pump system of claim 1, wherein the compressor comprises a first stage compression chamber and a second stage compression chamber connected in series, and an external interface is arranged between the first stage compression chamber and the second stage compression chamber;
the heat pump system further includes:
the main flow path of the economizer is connected in series with a pipeline between the gas cooler and a high-pressure pipeline of the regenerator, and the secondary flow path of the economizer is connected in series with a pipeline between the gas cooler and an external interface of the compressor;
a third throttling element provided on a conduit between the gas cooler and a secondary flowpath of the economizer;
and the check valve is arranged on a pipeline between the auxiliary flow path of the economizer and the external interface of the compressor, and the check valve is used for conducting the pipeline from the auxiliary flow path of the economizer to the external interface of the compressor in a one-way mode.
9. A heat pump system is characterized in that the heat pump system comprises a compressor, a gas cooler, an evaporator and a gas-liquid separator which are sequentially connected through pipelines; the compressor comprises a first-stage compression cavity and a second-stage compression cavity which are connected in series, and an external interface is arranged between the first-stage compression cavity and the second-stage compression cavity;
the heat pump system further includes:
an economizer, a main flow path of which is connected in series to a pipe between the gas cooler and the evaporator, and a sub-flow path of which is connected in series to a pipe between the gas cooler and an external port of the compressor;
a third throttling element provided on a conduit between the gas cooler and a secondary flowpath of the economizer;
the injection pipe of the gas-liquid separator is connected in series with a pipeline between the third throttling element and the secondary flow path of the economizer;
the gas-liquid separator includes:
the air suction device comprises a shell, wherein an air inlet interface, an air suction interface and a liquid return interface are arranged on the shell;
the balance pipe is sleeved in the liquid return interface, a liquid inlet of the balance pipe is positioned in the shell, and a liquid outlet of the balance pipe is positioned outside the shell;
the injection pipe comprises a first pipe section, a second pipe section and a third pipe section which are sequentially communicated, a connector connected with a liquid outlet of the balance pipe is arranged on the second pipe section, and the pipe diameter of the second pipe section is smaller than that of the first pipe section and that of the third pipe section.
10. The heat pump system of claim 9, wherein the gas-liquid separator further comprises a suction pipe nested within the suction interface, a suction port of the suction pipe being located inside the housing, a discharge port of the suction pipe being located outside the housing;
the pipe section of the air suction pipe located in the shell is of a U-shaped structure with an upward opening, an oil return hole is formed in the lowest point of the U-shaped structure, a liquid inlet of the balance pipe is lower than an air suction port of the air suction pipe, and a liquid inlet of the balance pipe is higher than the oil return hole.
11. The heat pump system of claim 10, wherein the liquid inlet of the balancing pipe has a height h from the bottom wall of the housing1The height between the air suction port of the air suction pipe and the bottom wall of the shell is h2The height between the oil return hole of the air suction pipe and the bottom wall of the shell is h3Wherein, 1.1h3≤h1≤0.6h2。
12. The heat pump system according to claim 9, wherein said gas-liquid separator further comprises a solenoid valve disposed on a section of said balance pipe outside said housing, said solenoid valve being configured to control opening and closing of said balance pipe and to regulate a flow rate of said balance pipe.
13. The heat pump system of claim 9, wherein the gas-liquid separator further comprises a throttling element disposed on a section of the balancing pipe external to the housing.
14. The heat pump system according to any one of claims 9-13, wherein a first tapered transition pipe section is provided between said second pipe section and said first pipe section, and the pipe diameter of said first tapered transition pipe section gradually increases in a direction from said second pipe section to said first pipe section;
and a second conical transition pipe section is arranged between the second pipe section and the third pipe section, and the pipe diameter of the second conical transition pipe section is gradually increased in the direction from the second pipe section to the third pipe section.
15. The heat pump system according to any one of claims 9-13, wherein a tube diameter of said second tube segment is d1The pipe diameters of the first pipe section and the third pipe section are d2Wherein, 0.6d2≤d1≤0.85d2。
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| CN112413954B (en) * | 2020-11-23 | 2021-11-16 | 珠海格力电器股份有限公司 | Air source heat pump hot water chilling unit control method and device and air conditioning system |
| CN114322380A (en) * | 2022-01-10 | 2022-04-12 | 台州龙江化工机械科技有限公司 | Gas-liquid separator and gas-liquid separator |
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| JP2000320918A (en) * | 1999-05-13 | 2000-11-24 | Osaka Gas Co Ltd | Ammonia absorption refrigerator |
| JP4333556B2 (en) * | 2004-10-28 | 2009-09-16 | 株式会社デンソー | Gas-liquid separator for ejector cycle |
| CN202304149U (en) * | 2011-10-26 | 2012-07-04 | 广东芬尼克兹节能设备有限公司 | Gas-liquid separator with double filter screens |
| CN103111213B (en) * | 2013-02-04 | 2015-10-21 | 西安交通大学 | A kind of venturi mixer containing special Inserting Tube |
| CN105444450A (en) * | 2014-07-04 | 2016-03-30 | 约克广州空调冷冻设备有限公司 | Refrigeration device |
| CN104501483B (en) * | 2014-12-30 | 2017-03-29 | 珠海格力电器股份有限公司 | Refrigerant migration system, refrigerating system and air conditioner |
| CN204555458U (en) * | 2015-03-27 | 2015-08-12 | 广东美的制冷设备有限公司 | Gas-liquid separator and air-conditioner |
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