CN111928548A - Gas-liquid separator, oil return system and air conditioning system - Google Patents
Gas-liquid separator, oil return system and air conditioning system Download PDFInfo
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- CN111928548A CN111928548A CN202010680760.7A CN202010680760A CN111928548A CN 111928548 A CN111928548 A CN 111928548A CN 202010680760 A CN202010680760 A CN 202010680760A CN 111928548 A CN111928548 A CN 111928548A
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- 239000007788 liquid Substances 0.000 title claims abstract description 166
- 238000004378 air conditioning Methods 0.000 title claims abstract description 25
- 239000003921 oil Substances 0.000 claims abstract description 300
- 239000010687 lubricating oil Substances 0.000 claims abstract description 87
- 238000005057 refrigeration Methods 0.000 claims description 63
- 239000003507 refrigerant Substances 0.000 claims description 55
- 230000006835 compression Effects 0.000 claims description 37
- 238000007906 compression Methods 0.000 claims description 37
- 238000002347 injection Methods 0.000 claims description 21
- 239000007924 injection Substances 0.000 claims description 21
- 239000000314 lubricant Substances 0.000 claims description 15
- 230000005484 gravity Effects 0.000 claims description 10
- 238000000034 method Methods 0.000 abstract description 13
- 238000010438 heat treatment Methods 0.000 description 7
- 238000001816 cooling Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 239000000243 solution Substances 0.000 description 3
- 239000000126 substance Substances 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000010726 refrigerant oil Substances 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 210000002445 nipple Anatomy 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000002000 scavenging effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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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
- F25B43/006—Accumulators
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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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
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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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- 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
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a gas-liquid separator, an oil return system and an air conditioning system. The gas-liquid separator includes: a barrel; an oil return port provided on the bottom of the cylinder and configured to communicate with an external oil return pipe; and the oil return straight pipe is arranged in the cylinder body and is vertically positioned on the oil return opening, and a plurality of open holes spaced from each other are formed in the pipe wall of the oil return straight pipe along the length direction of the oil return straight pipe. By providing an oil return straight pipe having a plurality of openings in the pipe wall in the gas-liquid separator and arranging it on the oil return opening at the bottom of the gas-liquid separator, the lubricating oil tumbling in the gas-liquid separator will enter the oil return straight pipe through the openings and flow down along its inner wall, with the result that the oil return straight pipe will be occupied by the liquid lubricating oil. Compared with the method that the gas-liquid mixed lubricating oil in the gas-liquid separator directly returns from the bottom oil return opening of the gas-liquid separator, the oil return speed of the full-liquid lubricating oil is much higher. The invention also discloses an oil return system comprising the gas-liquid separator and an air conditioning system.
Description
Technical Field
The invention relates to a refrigeration system, in particular to a gas-liquid separator, an oil return system and an air conditioning system.
Background
A vapor compression type refrigeration system generally includes four basic components of a compressor, a condenser, a throttle mechanism, and an evaporator, which form a circuit allowing a refrigerant to circulate therein, and compresses a low-temperature and low-pressure gas refrigerant into a high-temperature and high-pressure gas refrigerant using the compressor. Compressors, such as scroll compressors, centrifugal compressors, screw compressors, and the like, often require lubricating oil to provide lubrication and seal protection to the moving parts thereof during operation. Therefore, when the compressed high-temperature and high-pressure gas refrigerant is discharged from the compressor very quickly, the lubricant oil in the compressor is easily formed into oil vapor and oil droplet particles and discharged together with the gas refrigerant. When the lubricating oil enters the condenser and the evaporator together with the refrigerant, a layer of oil film is formed on the heat transfer wall surface, so that the thermal resistance is increased, the heat transfer effect of the condenser and the evaporator is reduced, and the refrigeration effect is reduced. Therefore, existing refrigeration systems, including but not limited to central air conditioning systems or multi-split systems, typically include an oil separator between the compressor and the condenser to separate the lubricant oil mixed in the refrigerant vapor. An oil separator is typically disposed on the discharge line connected to the discharge end of the compressor to separate the lubricant oil from the refrigerant before the lubricant oil-laden gaseous refrigerant enters the other major components of the refrigeration system. Vapor compression refrigeration systems are also typically provided with a gas-liquid separator to separate the refrigerant from the evaporator into a gaseous refrigerant and a liquid refrigerant before being drawn into the compressor and to allow only the gaseous refrigerant to return to the compressor, thereby avoiding liquid refrigerant from entering the compressor to break lubrication or otherwise damage the compressor. A certain amount of lubricating oil is also generally present in the gas-liquid separator. The oil separator and the gas-liquid separator return the lubricating oil to the return pipe of the compressor through respective return oil pipelines, so that the lubricating oil leaving the compressor can be returned to the compressor in time, otherwise the compressor can be damaged due to the lack of the lubricating oil.
The existing gas-liquid separator has two different passive oil return modes. Fig. 1 shows one of the oil return methods. As shown in fig. 1, a conventional gas-liquid separator 31 has an inlet pipe 311 and an outlet pipe 312, and most of the inlet pipe 311 and the outlet pipe 312 are located in the gas-liquid separator 31. The intake pipe 311 is for receiving a low-temperature and low-pressure gas refrigerant (possibly mixed with a liquid refrigerant and a lubricating oil) from an evaporator (not shown in the figure). The outlet pipe 312 is formed in a substantially U-shape in the gas-liquid separator 31 and may be connected to the suction end of the compressor. Since the outlet of the intake pipe 311 in the gas-liquid separator 31 is open, the refrigerant can flow throughout the gas-liquid separator 31. Due to the action of gravity, the liquid refrigerant and possibly entrained lubricating oil will separate from the gas refrigerant and sink to the lower or bottom part of the gas-liquid separator 31, while the gas refrigerant flows in the upper part inside the gas-liquid separator 31. An inlet of the outlet pipe 312 in the gas-liquid separator 31 is positioned at an upper portion in the gas-liquid separator 31 and is offset from an outlet of the inlet pipe 311. With this arrangement, it is ensured that all of the refrigerant drawn from the outlet pipe 312 by the compressor is gaseous. In order to return the lubricating oil settled at the bottom of the gas-liquid separator 31 to the compressor, an oil suction hole 313 is formed at the lowest portion of the U-shaped outlet pipe 312. In order to prevent foreign substances from entering the outlet pipe 312, a screen 314 is disposed on the oil suction hole 313. The lubricating oil in the gas-liquid separator 31 is sucked into the outlet pipe 312 through the oil suction hole 313 and returned to the compressor with the gas refrigerant. By designing a proper oil suction aperture, the lubricating oil in the gas-liquid separator 31 can be completely sucked away, so that the oil return speed and the efficiency are high. However, since the outlet pipe 312 is long, both the pressure loss and the oil return resistance are large. In another gas-liquid separator, an oil suction port is not arranged on an air outlet pipe, but an oil return port is directly arranged at the bottom of the gas-liquid separator, and an independent oil return pipe for connecting the oil return port and an air return pipe of the compressor is arranged. The lubricating oil at the bottom of the gas-liquid separator returns to the return pipe of the compressor by means of gravity and a relatively small pressure difference. The oil return mode has low efficiency because the pressure difference between the oil return pipe at the bottom of the gas-liquid separator and the air return pipe of the compressor is too small. Moreover, the oil return amount of the gas-liquid separator with the oil return port arranged at the bottom is a fixed value. This may result in a higher amount of lubricating oil in the gas-liquid separator in case of high load of the refrigeration system. However, it is desirable that the amount of lubricant in the gas-liquid separator be low at high loads to ensure more oil lubrication in the compressor and refrigeration system. In addition, in a low-temperature environment, the fluidity of the lubricating oil is deteriorated, and oil cannot be returned in time, which eventually damages the compressor.
Accordingly, there is a need in the art for a new solution to the above problems.
Disclosure of Invention
In order to solve the above-mentioned problems in the prior art, i.e. to improve the oil return efficiency of the gas-liquid separator and reduce the pressure loss, the present invention provides a gas-liquid separator, comprising: a barrel; the oil return port is arranged on the bottom of the cylinder and is configured to be communicated with an external oil return pipe; and the oil return straight pipe is arranged in the cylinder and is vertically positioned on the oil return opening, and a plurality of open holes which are spaced from each other are formed in the pipe wall of the oil return straight pipe along the length direction of the oil return straight pipe.
In a preferred embodiment of the above gas-liquid separator, the diameters of the openings are the same.
In a preferred embodiment of the gas-liquid separator, a diameter of the oil return straight pipe is greater than or equal to a diameter of the oil return opening.
As will be appreciated by those skilled in the art, by providing a return oil straight pipe having a plurality of openings in the pipe wall within the gas-liquid separator and arranging it on the return oil port at the bottom of the gas-liquid separator, the tumbling oil within the gas-liquid separator will enter the return oil straight pipe through the openings and flow down along its inner wall, with the result that the return oil straight pipe will be occupied by liquid oil. Compared with the method that the gas-liquid mixed lubricating oil in the gas-liquid separator directly returns from the bottom oil return opening of the gas-liquid separator, the oil return speed of the full-liquid lubricating oil is much higher. Further, when the amount of the lubricating oil in the gas-liquid separator is large and the lower portion is liquid, the oil return is accelerated as the number of the holes submerged by the liquid lubricating oil increases due to the holes from top to bottom in the oil return straight pipe.
Preferably, the diameters of the openings in the oil return straight pipes are the same, so that oil is returned quickly when the amount of lubricating oil in the gas-liquid separator is large, and oil is returned slowly when the amount of lubricating oil in the gas-liquid separator is small.
In order to solve the above-mentioned problems in the prior art, i.e., to solve the technical problem that the oil return efficiency and the pressure loss cannot be considered at the same time, the present invention also provides an oil return system configured to be usable in a vapor compression type refrigeration system, and including: a vapor-liquid separator according to the above, said vapor-liquid separator being connected to a return pipe of a compressor of said vapor compression refrigeration system; the ejector is provided with an ejection end which can be connected to the high-pressure side of the vapor compression refrigeration system, an ejected end which can be connected to an external oil return pipe of the gas-liquid separator, and an outlet end which can be connected to an air return pipe of the compressor; the ejector is configured to introduce a jet of refrigerant or lubricant from the high pressure side into the ejector through the ejector end such that lubricant in the gas-liquid separator is drawn out by the jet and mixed with the jet to flow to a return pipe of the compressor via an outlet end of the ejector.
In a preferred technical scheme of the oil return system, the oil return system further comprises an oil separator, the oil separator is connected to an exhaust pipe of the compressor and is provided with an oil return port of the oil separator, and an injection end of the injector is connected to the oil return port of the oil separator through an oil return pipe of the oil separator; the ejector is configured to introduce the jet formed by the lubricating oil from the oil separator into the ejector through the ejector end so that the lubricating oil in the gas-liquid separator can be sucked out by means of the jet and flows to a gas return pipe of the compressor through an outlet end of the ejector after being mixed with the jet.
In a preferred embodiment of the oil return system, a first electromagnetic valve is disposed on a pipeline connecting the injection end and the high-pressure side or an oil return pipe of the oil separator, and the first electromagnetic valve is configured to be switchable between an open state and a closed state.
In a preferred embodiment of the oil return system, a first capillary is further disposed on a pipeline connecting the injection end and the high-pressure side or on an oil return pipe of the oil separator, and the first solenoid valve and the first capillary are positioned such that the refrigerant from the high-pressure side or the lubricating oil from the oil separator flows through the first solenoid valve and then flows through the first capillary.
In a preferred technical solution of the above oil return system, a second electromagnetic valve is provided on an oil return branch pipe connecting the outlet end of the ejector and the air return pipe of the compressor, and the second electromagnetic valve is configured to be switchable between an open state and a closed state.
In the preferable technical scheme of the oil return system, under the condition that the injection end of the injector is connected to the oil return port of the oil separator,
when the first electromagnetic valve and the second electromagnetic valve are both in an open state, lubricating oil from the oil separator and lubricating oil from the gas-liquid separator flow to an air return pipe of the compressor after being mixed by the ejector;
when the first solenoid valve is in a closed state and the second solenoid valve is in an open state, the oil separator is configured to stop oil return, and the gas-liquid separator is configured to return oil by means of gravity and a pressure difference;
when the first electromagnetic valve is in an open state and the second electromagnetic valve is in a closed state, lubricating oil from the oil separator can flow into the gas-liquid separator through the injected end of the injector to heat the lubricating oil in the gas-liquid separator; and is
The oil separator and the gas-liquid separator are configured to stop oil return when both the first solenoid valve and the second solenoid valve are in a closed state.
As will be appreciated by those skilled in the art, in order to improve the oil return efficiency of a vapor compression refrigeration system while ensuring that no significant pressure loss is generated, the oil return system of the present invention not only incorporates the vapor-liquid separator of the present invention, but also incorporates an eductor. The ejector has an ejection end, an ejected end, and an outlet end. The injection end is connected to the high-pressure side of the vapor compression refrigeration system. By connecting the ejector end to the high pressure side, a jet can be formed with refrigerant or lubricating oil from the high pressure side, which jet creates a negative pressure in the ejector. The jet may be formed by a configured restriction, such as a capillary tube, or by a jet nozzle disposed within the eductor, or by both a capillary tube and eductor nozzle. The end of the ejector, which is ejected, is communicated with the oil return port of the gas-liquid separator, and the outlet end of the ejector is communicated with the air return pipe of the compressor. Because the gas-liquid separator is positioned at the low-pressure side of the steam compression type refrigerating system, lubricating oil in the gas-liquid separator can be sucked out from the oil return port through the oil return straight pipe by means of negative pressure caused by jet flow, is mixed with the jet flow and then flows to the air return pipe of the compressor through the outlet end of the ejector. Through the configuration, the oil return system can efficiently return oil even under the condition of low temperature by utilizing high-pressure power, so that the oil return efficiency and the pressure loss can be considered, namely, the oil return efficiency is high, and the pressure loss is low. In addition, the injection oil return is utilized, the risk that the compressor sucks liquid refrigerant and/or lubricating oil can be avoided, and the refrigerant and the lubricating oil are changed into gaseous molecules after injection, so that the refrigerant can be gasified at the mixing port of the injector even if the refrigerant sucks the liquid refrigerant.
Preferably, the oil return system of the present invention further comprises an oil separator. The oil separator is connected to the discharge pipe of the compressor and is provided with an oil separator return. It can thus be seen that the oil separator is positioned on the high pressure side of the vapor compression refrigeration system. Therefore, the injection end of the injector can be connected to an oil return port of the oil separator through an oil return pipe of the oil separator. High pressure lubricating oil from an oil separator may be used to form the jet. The jet flow enters the ejector through the ejection end of the ejector and generates negative pressure in the ejector, so that the lubricating oil in the gas-liquid separator is sucked out under the action of the negative pressure, is mixed with the jet flow and then flows to the return air pipe of the compressor through the outlet end of the ejector. The configuration utilizes the high-pressure injection effect of the oil separator and the low-pressure state of the gas-liquid separator, and can realize the common oil return of the oil separator and the gas-liquid separator.
Preferably, a first electromagnetic valve is arranged on a pipeline connecting the ejector end and the high-pressure side or an oil return pipe of the oil separator, and a second electromagnetic valve is arranged on an oil return branch pipe connecting the outlet end of the ejector and an air return pipe of the compressor. Through different combination control of the first electromagnetic valve and the second electromagnetic valve, different requirements of the vapor compression refrigeration system on oil return in different operation modes can be met.
Preferably, the jet flow can be formed by the throttling action of a first capillary tube arranged on a pipeline connecting the ejection end and the high-pressure side or an oil return pipe of the oil separator, can also be formed by a jet flow nozzle in the ejector, or can be formed by the matching of the first capillary tube and the ejection nozzle.
The present invention also provides an air conditioning system, comprising: the gas-liquid separator as described above, wherein the gas-liquid separator is connected to a gas return pipe of a compressor of the air conditioning system, and an external oil return pipe of the gas-liquid separator is also connected to the gas return pipe; or an oil return system as described above. Through the gas-liquid separator or the oil return system, lubricating oil leaving the compressor can be effectively returned to the compressor of the air conditioning system in time, the compressor is prevented from being damaged, and the pressure loss of the air conditioning system can be effectively reduced.
Drawings
Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:
FIG. 1 is a schematic diagram of a prior art gas-liquid separator;
FIG. 2 is a schematic illustration of an embodiment of a gas-liquid separator of the present invention;
FIG. 3 is a schematic view of a first embodiment of the oil return system of the present invention;
FIG. 4 is a schematic cross-sectional view of an embodiment of an eductor in an oil return system of the present invention;
FIG. 5 is a schematic view of a second embodiment of the oil return system of the present invention;
FIG. 6 is a schematic view of a third embodiment of the oil return system of the present invention;
FIG. 7 is a schematic view of a fourth embodiment of the oil return system of the present invention;
fig. 8 is a flowchart of an embodiment of a control method of the oil return system of the present invention.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.
In order to solve the technical problem that the oil return efficiency and the pressure loss cannot be considered at the same time, the present invention provides a gas-liquid separator 12, including: a barrel 120; an oil return port 123, the oil return port 123 being provided on the bottom of the cylinder 120 and configured to communicate with the external oil return pipe 24; and a return straight pipe 124, the return straight pipe 124 is arranged in the cylinder 120 and is vertically positioned on the return port 123, and a plurality of open holes 125 spaced from each other are arranged on the pipe wall of the return straight pipe 124 along the length direction of the return straight pipe 124.
FIG. 2 is a schematic view of an embodiment of a gas-liquid separator of the present invention. As shown in FIG. 2, in one or more embodiments, the gas-liquid separator 12 has a generally cylindrical barrel 120. An inlet pipe 121 and an outlet pipe 122 are arranged at the top of the cylinder 120 (based on the orientation shown in fig. 2). An oil return port 123 is formed at the bottom of the cylinder 120, and the oil return port 123 is communicated with the external oil return pipe 24 (see fig. 3) through an oil return port connecting pipe 126. A return straight pipe 124 is arranged in the cylinder 120, the return straight pipe 124 is positioned upright on the return port 123, and a plurality of mutually spaced openings 125 are provided in the pipe wall of the return straight pipe 124 along the length direction (or height direction) of the return straight pipe 124.
As shown in fig. 2, the inlet pipe 121 has a connection end (not shown) located outside the cylinder 120 and an open end 127 extending to the inside of the cylinder 120. The intake pipe 121 is connectable through a connecting end to a pipe communicating with an evaporator (not shown) of the vapor compression refrigeration system so as to receive a low-temperature low-pressure gas refrigerant (possibly mixed with a liquid refrigerant and a lubricating oil) from the evaporator. In one or more embodiments, the air inlet conduit 121 extends generally vertically downward within the barrel 120 and has its open end 127 positioned at an upper portion within the barrel 120. The open end 127 is open in the cylinder 120, so the refrigerant can flow into the gas-liquid separator 12 from the open end 127. Due to the effect of gravity, the liquid refrigerant and possibly entrained lubricating oil will separate from the gas refrigerant and sink to the lower or bottom part of the gas-liquid separator 12, while the gas refrigerant flows in the upper part inside the gas-liquid separator 12. As shown in FIG. 2, outlet tube 122 also has a connecting end (not shown) located outside of barrel 120 and an open end 128 extending into the interior of barrel 120. Outlet pipe 122 is connectable by its connecting end to the return pipe 21 of the compressor. Outlet duct 122 extends at an upper portion within gas-liquid separator 12 and forms a substantially 90 ° bend such that a portion of outlet duct 122 extends substantially horizontally within gas-liquid separator 12. The opening direction (horizontally) of the open end 128 of the outlet pipe 122 is thus staggered from the opening direction (vertically downward) of the open end 127 of the inlet pipe 121, and the open end 128 of the outlet pipe 122 and the open end 127 of the inlet pipe 121 are spaced apart from each other by a large distance. With this arrangement, it is ensured that all of the refrigerant drawn from outlet tube 122 by the compressor is gaseous.
As shown in fig. 2, in one or more embodiments, the oil return port 123 is centrally located in the bottom of the barrel 120. The center position generally belongs to the lowest position of the cylinder 120 in the vertical direction. Alternatively, the oil return port 123 may be provided near the center of the bottom of the cylinder 120, or may be disposed at another position in the bottom of the gas-liquid separator 12 as needed. A return nipple 126 extends below the bottom of the barrel 120 and may be secured to the return port 123. As shown in fig. 2, a return straight pipe 124 is fixed upright in the cylinder 120 above the return port 123. The length or vertical height of the return oil straight pipe 124 may reach or exceed the maximum level of the lubricating oil in the gas-liquid separator. The return straight pipe 124 has an upper end 124a and a lower end 124 b. In one or more embodiments, the upper end 124a is open. This increases the total opening area, and therefore, oil return can be accelerated in the case where the liquid level of the lubricating oil in the gas-liquid separator is high. Alternatively, the upper end 124a is closed. The upper end portion 124a and the open end 127 of the intake pipe 121 are arranged to be staggered from each other in the vertical direction, and are spaced from the open end 127 of the intake pipe 121 by a sufficient distance to avoid an interference phenomenon. The lower end 124b of the return straight pipe 124 covers the return port 123. In one or more embodiments, the return straight pipe 124 has a diameter d1 (pipe inner diameter) that is greater than a diameter of the return port 123 (not shown). Alternatively, the diameter d1 of the return straight pipe 124 is equal to the diameter of the return port 123. Accordingly, the diameter d1 of the return straight pipe 124 may be larger than the diameter d2 of the return nozzle 126. As shown in fig. 2, a plurality of holes 125 are distributed on the pipe wall of the oil return straight pipe 124 at intervals from top to bottom along the vertical direction (i.e., the length direction of the oil return straight pipe 124). The lowermost opening 125 is adjacent the oil return opening 123. Alternatively, the distance between adjacent apertures 125 is the same along the vertical direction. Alternatively, the distance between adjacent openings 125 may be different, depending on the actual requirements. As shown in FIG. 2, in one or more embodiments, the diameter d3 of all apertures 125 may be designed to be the same as each other. Alternatively, the diameter of the opening 125 can also be designed to be different.
The design that the oil return straight pipe with the hole is arranged on the oil return opening at the bottom of the gas-liquid separator can help the gas-liquid separator to return oil more quickly, and meanwhile, the pressure loss can be reduced. This is because the lubricating oil in the gas-liquid separator and the refrigerant are normally miscible in each other in the normal temperature range, and the ratio of the lubricating oil to the refrigerant is the same, so that the lubricating oil is often in a state of rolling up and down. The holes in the return straight tube 124 allow the tumbling oil to enter the return straight tube 124 and flow down the inner wall of the return straight tube 124. Therefore, the inside of the oil return straight pipe 124 is completely filled with the liquid lubricating oil, and the oil return of the completely filled liquid lubricating oil is obviously faster than that of the gas-liquid two-state lubricating oil. When the amount of lubricating oil is large and the lower portion thereof is liquid, the oil return of the gas-liquid separator is further accelerated as the number of the openings submerged by the liquid lubricating oil increases.
In order to solve the technical problem that the oil return efficiency and the pressure loss cannot be considered at the same time, the invention also provides an oil return system 1. The oil return system 1 is configured to be usable in a vapor compression refrigeration system (not shown in the drawings), and includes: the gas-liquid separator 12 as described above, the gas-liquid separator 12 being connected to the return pipe 21 of the compressor 11 of the vapor compression refrigeration system; and an ejector 14, the ejector 14 is provided with an ejector end 142 connectable to the high pressure side of the vapor compression refrigeration system, an ejector end 143 connectable to the external oil return pipe 24 of the gas-liquid separator 12, and an outlet end 144 connectable to the air return pipe 21 of the compressor 11; the eductor 14 is configured to introduce a jet (not shown) of refrigerant or lubricant from the high pressure side into the eductor 14 through the eductor end 142 such that lubricant within the gas-liquid separator 12 is drawn by the jet and mixed with the jet to flow through the outlet end 144 of the eductor 14 to the return air line 21 of the compressor 11.
Reference herein to a "vapor compression refrigeration system" includes, but is not limited to, a multiple refrigerant line system, or a central air conditioning system, or other refrigeration system having a compressor that compresses a vapor refrigerant. These vapor compression refrigeration systems not only have a refrigeration function, but also provide a heating function, a defrosting function, and the like.
By "high pressure side" as referred to herein is meant the portion of the vapor compression refrigeration system that extends from the discharge end of the compressor up to the condenser in which the refrigerant is typically in a high temperature, high pressure, gaseous or liquid state. Conversely, the portion of the circuit of the vapor compression refrigeration system that extends from the evaporator to the suction side of the compressor may be referred to as the "low pressure side". The gas-liquid separator is arranged between the suction end of the compressor and the evaporator. Therefore, when the vapor compression refrigeration system is operated, the gas-liquid separator is generally in a low-temperature and low-pressure state.
In one or more embodiments, the connection of the eductor end 142 of the eductor 14 to the high pressure side of the vapor compression refrigeration system includes: the bleed end 142 is connected by a line (not shown) directly to the discharge line 22 of the compressor or directly to a high pressure line upstream or downstream of the condenser to form a jet with a small portion of high pressure refrigerant separated from the high pressure side. In this case, the gas-liquid separator 12 is provided with a separate ejector 14. Alternatively, the ejector end 142 is connected to the oil separator oil return port 133 of the oil separator 13a or 13b through the oil separator oil return pipe 23 of the oil separator 13a or 13b to form a jet flow with high-pressure lubricating oil from the oil separator, so that the oil separator 13a or 13b and the gas-liquid separator 12 can be returned together through the ejector 14. Through this kind of oil return system, even under the low temperature condition (oil viscosity reduces), high-temperature high-pressure gas refrigerant or high-pressure lubricating oil also can draw and penetrate to be favorable to the oil return.
In one or more embodiments, a first solenoid valve 231 may be disposed on the above-described piping or oil separator return pipe 23 to control the oil return of the gas-liquid separator 12 and the oil separator 13a or 13b by controlling the first solenoid valve 23. In one or more embodiments, a first capillary tube 233 may also be provided on the above-described piping or oil separator return tube 23. The first capillary tube 233 is configured to throttle high pressure refrigerant from the line or high pressure lube oil from the oil separator return 23 into a desired jet.
Fig. 3 is a schematic view of a first embodiment of the oil return system of the present invention. As shown in fig. 3, the oil return system 1 includes a gas-liquid separator 12, a first oil separator 13a, and an ejector 14.
As shown in fig. 3, the inlet pipe 121 of the gas-liquid separator 12 may be connected to an evaporator (not shown), and the outlet pipe 122 is connected to one end of the return pipe 21. The other end of the muffler 21 is connected to the suction end 111 of the compressor 11. Therefore, the compressor 11 can directly suck the gas refrigerant from the gas-liquid separator 12 through the return pipe 21. The oil return port 123 of the gas-liquid separator 12 is communicated to the drawn end 143 of the ejector 14 via the external oil return pipe 24.
In one or more embodiments, the external return line 24 of the gas-liquid separator may also be connected to an auxiliary branch line 26 (see FIG. 4). The auxiliary branch 26 is connectable to an external device (not shown) via a shut-off valve 261. The external device may be, for example, a refrigerant storage tank, a lubricant storage tank, or an empty tank. When the shutoff valve 261 is opened, the refrigerant or the lubricating oil can be supplied to the refrigeration system through the auxiliary branch pipe 26 and can be discharged from the refrigeration system. Optionally, a second capillary tube 262 may be further provided on the auxiliary branch 26 to prevent foreign materials from entering the refrigeration system. Alternatively, a second filter 241 may be provided on the external oil return pipe 24 of the gas-liquid separator 12.
As shown in fig. 3, the first oil separator 13a has an inlet end 131, an outlet end 132, and an oil separator oil return opening 133. The inlet 131 is connected to the discharge tube 22 of the compressor 11 to receive high pressure gaseous refrigerant from the compressor. The discharge pipe 22 is connected to the discharge end 112 of the compressor 11. The inlet end 131 is typically disposed at an upper portion or top of the first oil separator 13 a. The high pressure gas refrigerant separates from the lubricating oil carried by it in the first oil separator 13a and then exits the first oil separator 13a in the flow direction a from the gas outlet end 132 at the top of the first oil separator 13 a. The lubricating oil separated from the high-pressure gas refrigerant sinks to the bottom of the first oil separator 13a by the action of gravity. The oil separator return port 133 is positioned at the bottom of the first oil separator 13a and is connected to the eductor end 142 of the eductor 14 by the oil separator return line 23.
In one or more embodiments, as shown in fig. 3, a first solenoid valve 231 is provided on the oil separator return pipe 23. The first solenoid valve 231 is configured to be switchable between an open and a closed state. When the vapor compression refrigeration system is operated for a long time (for example, for more than 8 hours), the first solenoid valve 231 may be in a normally open state. When the vapor compression refrigeration system is operated, the first solenoid valve 231 may also be controlled to be intermittently opened and closed, if necessary, for example, after the first predetermined period of time in the open state, the first solenoid valve 231 may be switched to the closed state for a second predetermined period of time, and then the first solenoid valve 231 may be opened again, and the above-described control steps may be repeatedly performed. In the intermittent opening and closing mode, the opening time of the first solenoid valve 231 is generally longer than the closing time. When the vapor compression refrigeration system stops operating, the first solenoid valve 231 is normally in a closed state.
In one or more embodiments, as shown in fig. 3, a first capillary tube 233 is also provided on the oil separator return tube 23. The first capillary tube 233 can throttle the high-pressure lubrication oil from the first oil separator 13a into a jet flow by an appropriate configuration. The jet then enters the eductor 14 through the eductor end 142 of the eductor 14 and creates a negative pressure therein. Under the action of the negative pressure, the lubricating oil in the gas-liquid separator 12 is sucked into the ejector 14 through the ejection end 143, mixed with the jet flow, and then exits from the outlet end 144 of the ejector 14 to flow along the oil return branch pipe 25 to the return pipe 21 of the compressor 11. Alternatively, the first capillary 233 is eliminated, and an ejector nozzle 146 (see fig. 4) is provided in the ejector 14. A jet is formed through the injection nozzle 146. Alternatively, the first capillary 233 cooperates with the injection nozzle 146 to form a jet. Optionally, a first filter 232 may be further provided on the oil separator return pipe 23, the first filter 232 being positioned between the oil separator return opening 133 and the first solenoid valve 231 to prevent foreign substances or foreign substances from entering the first solenoid valve 231.
As shown in fig. 3, the injection end 142 of the injector 14 communicates with the oil separator return pipe 23, the injection end 143 thereof communicates with the external return pipe 24 of the gas-liquid separator 12, and the outlet end 144 thereof communicates with the return branch pipe 25. In one or more embodiments, as shown in FIG. 3, the return air line 21 of the compressor 11 is relatively short, while the return manifold 25 is relatively long.
Fig. 4 is a schematic cross-sectional view of an embodiment of an eductor in an oil return system of the present invention. As shown in fig. 4, the eductor 14 defines an eductor chamber 145 within its body 141. The injection cavity 145 is in communication with the injection end 142, the injected end 143, and the outlet end 144, respectively. In one or more embodiments, as shown in FIG. 4, the eductor chamber 145 has a tapered section of length L that tapers in inner diameter in a direction toward the outlet end 144. In order to provide a stable forward propulsion of the jet in the eductor 14, the length L of the tapered section may be set in the range of 2-5 times the internal diameter D of the tube at the outlet end 144 so that a negative pressure is created around the jet just as it enters the eductor chamber 145. By this negative pressure, the lubricating oil in the gas-liquid separator 12 can be actively sucked into the ejector 14 through the ejection end 143. In one or more embodiments, as shown in fig. 4, an injection nozzle 146 is disposed within the injection chamber 145, and the injection nozzle 146 is in direct communication with the injection end 142. Thus, the jet nozzle 146 can cooperate with the first capillary 233 to create a suitable jet within the jet chamber 145. Alternatively, the eductor 14 may eliminate the eductor nozzle 146 and the oil return system of the present invention may rely solely on the first capillary tube 233 to create the jet.
Fig. 5 is a schematic view of a second embodiment of the oil return system of the present invention. In one or more embodiments, the oil return system 1 includes a gas-liquid separator 12, a second oil separator 13b, and an ejector 14. As shown in fig. 5, a return straight pipe 134 is also provided in the second oil separator 13 b. A return straight pipe 134 is located within the housing of the second oil separator 13b and is arranged upright above the oil separator return opening 133. A plurality of openings 135 are formed in the wall of the return straight pipe 134 along the length of the return straight pipe 134. In one or more embodiments, the diameter of the apertures 135 may decrease in order in a top-to-bottom direction. When the lubricating oil is less, the oil is returned by the small hole and the oil return time is prolonged relatively, so that the high-pressure gas is prevented from directly returning to the low-pressure pipe, and the large pressure loss is caused. On the contrary, when the lubricating oil is much, the oil is returned by using the large hole and the small hole, so that the oil return amount can be increased. The portions not mentioned in this embodiment are the same as those in the above embodiment.
Fig. 6 is a schematic view of a third embodiment of the oil return system of the present invention. As shown in fig. 6, the oil return system includes a gas-liquid separator 12, a first oil separator 13a, and an ejector 14. In one or more embodiments, as shown in fig. 6, a second solenoid valve 251 is provided in the return manifold 25. The second solenoid valve 251 is configured to be switchable between an open and a closed state. As shown in FIG. 6, in one or more embodiments, the return air pipe 21 is configured to be substantially U-shaped and substantially longer than the return branch pipe 25. The return branch pipe 25 may extend horizontally to the U-shaped bottom of the return pipe 21 and be connected to the return pipe 21 at the bottom. This connection position is advantageous in the case of oil return by gravity. In one or more embodiments, as shown in FIG. 6, the external return line 24 of the gas-liquid separator 12 is connected to an auxiliary branch line 26. The auxiliary branch 26 is connectable to an external device (not shown) via a shut-off valve 261. The external device may be, for example, a refrigerant storage tank, a lubricant storage tank, or an empty tank. When the shutoff valve 261 is opened, the refrigerant or the lubricating oil can be supplied to the refrigeration system through the auxiliary branch pipe 26 and can be discharged from the refrigeration system. A second capillary tube 262 is also provided on the auxiliary branch 26 to prevent foreign materials from entering the refrigeration system. The gas-liquid separator return pipe 24 is provided with a second filter 241.
For the oil return system shown in fig. 6, different requirements of the vapor compression refrigeration system on oil return in different operation modes can be met by controlling different switch combinations of the first electromagnetic valve 231 and the second electromagnetic valve 251.
As shown in the first table, four different oil return modes can be realized by the combined control of the switches of the first solenoid valve 231 and the second solenoid valve 251. When both the first electromagnetic valve 231 and the second electromagnetic valve 251 are opened, the lubricating oil in the gas-liquid separator 12 is drawn into the ejector 14 by forming a jet flow of the high-pressure lubricating oil from the first oil separator 13a with the aid of the jet flow. The lubricating oil from the first oil separator 13a and the lubricating oil from the gas-liquid separator 12 are mixed in the ejector 14, and then flow together along the oil return branch pipe 25 to the air return pipe 21, and then return to the compressor 11 through the suction end 111 of the compressor 11. When the first solenoid valve 231 is closed and the second solenoid valve 251 is opened, the first oil separator 13a stops oil return, and thus no jet is formed in the ejector 14. The lubricating oil in the gas-liquid separator 12 flows into the ejector 14 by gravity and pressure difference, and then flows to the gas return pipe 21 through the oil return branch pipe 25. When the first electromagnetic valve 231 is opened and the second electromagnetic valve 251 is closed, the high-pressure lubricating oil from the first oil separator 13a can enter the gas-liquid separator 12 after passing through the injecting end 142 and the injected end 143 of the injector 14 in sequence, and the lubricating oil in the gas-liquid separator 12 can be heated. When both the first solenoid valve 231 and the second solenoid valve 251 are closed, the oil return of the first oil separator 13a and the gas-liquid separator 12 is stopped.
Watch two
Table two above lists that different switch combination controls of the first solenoid valve 231 and the second solenoid valve 251 can correspond to different operation conditions of the vapor compression refrigeration system. As shown in table two, when the first solenoid valve 231 and the second solenoid valve 251 are both opened, the first oil separator 13a and the gas-liquid separator 12 return oil together, and thus, the basic operation conditions of the vapor compression refrigeration system, that is, the normal operation conditions, such as the cooling condition and the heating condition, can be applied. When the vapor compression refrigeration system is operated at an ultra-low temperature, since the fluidity of the lubricating oil in the gas-liquid separator 12 becomes poor, it is necessary to perform the intermittent heating. For this demand, the first solenoid valve 231 is opened, and the second solenoid valve 251 is intermittently closed. This allows the high-pressure lubricating oil in the first oil separator 13a to be introduced into the gas-liquid separator 12 and heats the lubricating oil therein. For example, the first solenoid valve 231 is opened and the second solenoid valve 251 is closed for, for example, 10 minutes or other suitable period of time. After 10 minutes, the second solenoid valve 251 is then opened, and the first solenoid valve 231 remains open for, for example, 1 hour or other suitable period of time. After 1 hour, the step of closing the second solenoid valve 251 is repeated, if necessary. When the vapor compression refrigeration system is operating in the defrosting mode or the oil return mode, the first oil separator 13a needs to stop oil return, and therefore, the first solenoid valve 231 is closed, and the second solenoid valve 251 is opened, so that the gas-liquid separator 12 can still return oil by means of gravity and a pressure difference. When the vapor compression refrigeration system is stopped, both the first solenoid valve 231 and the second solenoid valve 251 are in the closed state.
Watch III
As shown in the third table, by controlling the opening and closing of the first solenoid valve 231 and the second solenoid valve 251, it is also possible to control the manner of discharging the lubricating oil from the vapor compression refrigeration system and adding the lubricating oil to the refrigeration system. For example, when it is necessary to discharge the lubricating oil from the gas-liquid separator 12, the refrigeration system is stopped and left for, for example, 24 hours or other suitable time while both the first electromagnetic valve 231 and the second electromagnetic valve 251 are in the closed state. In this case, the lubricating oil of the gas-liquid separator 12 may be slowly discharged and then may be discharged to an external storage device via the auxiliary branch 26. In order to discharge the lubricating oil in the first oil separator 13a, the refrigeration system can be operated at low frequency, with the first solenoid valve 231 open and the second solenoid valve 251 closed, so that the lubricating oil in the first oil separator 13a can be slowly drained off and can then be discharged via the auxiliary branch 26 into an external storage device. When the refrigeration system needs to be lubricated, both the first solenoid valve 231 and the second solenoid valve 251 may be closed and the refrigeration system is in operation. In this case, a small amount of high-pressure refrigerant may be mixed into the lubricant tank, and then the lubricant may be added by inverting the tank.
Fig. 7 is a schematic view of a fourth embodiment of the oil return system of the present invention. As shown in fig. 7, the oil return system includes the gas-liquid separator 12, the second oil separator 13b, and the ejector 14. As described above, the return straight pipe 134 is provided in the second oil separator 13 b. A return straight pipe 134 is located within the housing of the second oil separator 13b and is arranged upright above the oil separator return opening 133. A plurality of openings 135 are formed in the wall of the return straight pipe 134 along the length of the return straight pipe 134. In one or more embodiments, as shown in fig. 7, a second solenoid valve 251 is provided in the return manifold 25. The second solenoid valve 251 is configured to be switchable between an open and a closed state. Similar to the oil return system shown in fig. 6, different requirements of the vapor compression refrigeration system on oil return in different operation modes can be met by controlling different switch combinations of the first electromagnetic valve 231 and the second electromagnetic valve 251. The portions not mentioned in this embodiment are the same as those in the above embodiment.
The oil return systems shown in fig. 6 and 7 can be controlled based on different operating conditions of the vapor compression refrigeration system. The control method determines an operation mode in which the vapor compression refrigeration system is located, and controls opening or closing of the first solenoid valve 231 and the second solenoid valve 251 based on the operation mode. The operating modes include, but are not limited to, a shutdown mode, a cooling mode, a heating mode, a defrost mode, and an oil return mode. In the heating mode, the control method further determines whether the ambient temperature is lower than a predetermined temperature value. When the ambient temperature is lower than the predetermined temperature value, the first electromagnetic valve 231 is opened, and the second electromagnetic valve 251 is intermittently closed to intermittently heat the gas-liquid separator 12.
Fig. 8 is a flowchart of an embodiment of a control method of the oil return system of the present invention. As shown in fig. 8, in step S1, it is determined whether or not the vapor compression refrigeration system is in a shutdown state. When the refrigeration system is in a shutdown state, the control method proceeds to step S2 to close both the first solenoid valve 231 and the second solenoid valve 251. When the refrigeration system is in operation, control determines whether the refrigeration system is defrosting or scavenging in step S3. If so, the control method proceeds to step S4, where the first solenoid valve 231 is closed and the second solenoid valve 251 is opened. If the refrigeration system is not performing defrost or oil return, control may proceed to step S5 to determine if the refrigeration system is operating in a heating mode. If so, control proceeds to step S6 to determine whether the ambient temperature Ta0 is less than a predetermined temperature value, such as 10℃ or other suitable temperature value. If the ambient temperature Ta0 is less than the predetermined temperature value, the control method proceeds to step S7, opening the first solenoid valve 231 and interstitially closing the second solenoid valve 251 to heat the lubricating oil in the gas-liquid separator 12 with the lubricating oil in the oil separator 13a or 13 b. For example, the first solenoid valve 231 is kept open all the time, the second solenoid valve 251 is closed for 10 minutes, and then the second solenoid valve 251 is opened for 1 hour; the step of closing the second solenoid valve 251 is then repeated. When the ambient temperature Ta0 is not less than the predetermined temperature value, control may proceed to step S9 with both the first solenoid valve 231 and the second solenoid valve 251 open. If the refrigeration system is not operating in the heating mode, control proceeds to step S8 to determine if the refrigeration system is operating in the cooling mode. If so, the control method proceeds to step S9 where both the first solenoid valve 231 and the second solenoid valve 251 are opened. If the refrigeration system is not operating in the cooling mode, the control process ends.
The present invention also relates to an air conditioning system comprising any of the gas-liquid separators 12 described above or any of the oil return systems 1 described above. The air conditioning system includes, but is not limited to, a multi-split air conditioning system or other suitable air conditioning system. In one or more embodiments, the air conditioning system includes the gas-liquid separator 12 of the present invention. The gas-liquid separator 12 is connected to the return pipe 21 of the compressor 11 of the air conditioning system through its inlet pipe 121 and outlet pipe 122, respectively. An external return pipe 24 of the gas-liquid separator 12 is connected to the return pipe 21 directly or through a return branch pipe 25. In this case, without an eductor, the gas-liquid separator 12 relies on gravity and pressure differential for oil return. By virtue of the above-described configuration of the return straight pipe 124, the gas-liquid separator 12 can also help the air conditioning system achieve oil return with high efficiency and without large pressure loss. Instead, the air conditioning system comprises the oil return system 1 described above. By combining the gas-liquid separator 12 of the present invention with an ejector, the air conditioning system of the present invention not only has a high oil return efficiency of the lubricating oil, but also has a low pressure loss. Further, the air conditioning system can control the oil return system of the air conditioning system based on the control method.
So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (10)
1. A gas-liquid separator, comprising:
a barrel;
the oil return port is arranged on the bottom of the cylinder and is configured to be communicated with an external oil return pipe; and
the oil return straight pipe is arranged in the cylinder and is vertically positioned on the oil return opening, and a plurality of open holes spaced from each other are formed in the pipe wall of the oil return straight pipe along the length direction of the oil return straight pipe.
2. The gas-liquid separator of claim 1, wherein the apertures are all the same diameter.
3. The gas-liquid separator according to claim 1 or 2, wherein a diameter of said oil return straight pipe is equal to or larger than a diameter of said oil return port.
4. An oil return system configured to be usable with a vapor compression refrigeration system, comprising:
the vapor-liquid separator of any of claims 1-3 connected to a return pipe of a compressor of the vapor compression refrigeration system; and
the ejector is provided with an ejection end which can be connected to the high-pressure side of the vapor compression refrigeration system, an ejected end which can be connected to an external oil return pipe of the gas-liquid separator, and an outlet end which can be connected to an air return pipe of the compressor; the ejector is configured to introduce a jet of refrigerant or lubricant from the high pressure side into the ejector through the ejector end such that lubricant in the gas-liquid separator is drawn out by the jet and mixed with the jet to flow to a return pipe of the compressor via an outlet end of the ejector.
5. The oil return system of claim 4, further comprising an oil separator connected to the compressor discharge line and provided with an oil separator oil return, the eductor end of the eductor being connected to the oil separator oil return through an oil separator oil return line; the ejector is configured to introduce the jet formed by the lubricating oil from the oil separator into the ejector through the ejector end so that the lubricating oil in the gas-liquid separator can be sucked out by means of the jet and flows to a gas return pipe of the compressor through an outlet end of the ejector after being mixed with the jet.
6. The oil return system according to claim 4 or 5, wherein a first solenoid valve is provided on a pipe connecting the injection end and the high pressure side or on the oil separator oil return pipe, the first solenoid valve being configured to be switchable between an open state and a closed state.
7. The oil return system of claim 6, wherein a first capillary tube is further provided on a line connecting the injection end and the high pressure side or on the oil separator oil return pipe, and the first solenoid valve and the first capillary tube are positioned such that refrigerant from the high pressure side or lubricating oil from the oil separator flows through the first solenoid valve before flowing through the first capillary tube.
8. The oil return system according to claim 4 or 5, wherein a second solenoid valve is provided on an oil return branch pipe connecting the outlet end of the ejector and the return pipe of the compressor, the second solenoid valve being configured to be switchable between an open state and a closed state.
9. The oil return system of claim 8 wherein, with the eductor end of the eductor connected to the oil separator oil return,
when the first electromagnetic valve and the second electromagnetic valve are both in an open state, lubricating oil from the oil separator and lubricating oil from the gas-liquid separator flow to an air return pipe of the compressor after being mixed by the ejector;
when the first solenoid valve is in a closed state and the second solenoid valve is in an open state, the oil separator is configured to stop oil return, and the gas-liquid separator is configured to return oil by means of gravity and a pressure difference;
when the first electromagnetic valve is in an open state and the second electromagnetic valve is in a closed state, lubricating oil from the oil separator can flow into the gas-liquid separator through the injected end of the injector to heat the lubricating oil in the gas-liquid separator; and is
The oil separator and the gas-liquid separator are configured to stop oil return when both the first solenoid valve and the second solenoid valve are in a closed state.
10. An air conditioning system, characterized in that the air conditioning system comprises:
the gas-liquid separator according to any one of claims 1 to 3 wherein said gas-liquid separator is connected to a gas return pipe of a compressor of said air conditioning system and an external oil return pipe of said gas-liquid separator is also connected to said gas return pipe; or
The oil return system of any one of claims 4-9.
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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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