WO2016201623A1 - 制冷循环装置 - Google Patents
制冷循环装置 Download PDFInfo
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- WO2016201623A1 WO2016201623A1 PCT/CN2015/081564 CN2015081564W WO2016201623A1 WO 2016201623 A1 WO2016201623 A1 WO 2016201623A1 CN 2015081564 W CN2015081564 W CN 2015081564W WO 2016201623 A1 WO2016201623 A1 WO 2016201623A1
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- compressor
- refrigeration cycle
- oil
- compressors
- cycle apparatus
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
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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
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
- F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
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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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- 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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the invention relates to the field of refrigeration, and in particular to a refrigeration cycle device.
- the multi-connected air conditioner composed of a plurality of compressors and a plurality of evaporators provided in each room repeatedly starts or stops the compressor due to a change in the air-conditioning load. Therefore, the amount of oil retained by each compressor may increase or decrease, and a large amount of refrigerant condenses in the compressor that is cooled in the shutdown. A compressor with a reduced oil retention is prone to failure, and condensation of the refrigerant in the compressor not only causes a decrease in the performance of the refrigeration cycle, but also a large amount of oil is discharged when it is restarted.
- the present invention aims to solve at least one of the technical problems in the related art to some extent.
- the present invention proposes a refrigeration cycle apparatus in which the amount of oil discharged from the compressor to the refrigeration cycle is reduced, and the amount of refrigerant in the refrigeration cycle is stabilized.
- a refrigeration cycle apparatus comprising at least a condenser, an expansion valve, an evaporator, and a plurality of compressors, each of which has a rotary type of a low-pressure circuit that communicates with the evaporator
- the compression mechanism unit and the motor unit that drives the compression mechanism unit each include an oil reservoir, and at least one of the compressor exhaust circuits is connected to the sealed casing of the other compressor.
- the stopped compressor functions as an oil separator of the operating compressor, operating
- the amount of oil discharged from the compressor to the refrigeration cycle will decrease.
- each compressor can maintain a generally appropriate amount of oil.
- the stopped compressor is heated, and the refrigerant in the stopped compressor does not condense, so that the time during which the compressor in the stop of the preheating is turned on from the unstable operation to the stable operation is turned on.
- the start-up time of the refrigeration cycle apparatus can be shortened, and there is no liquid refrigerant in the stopped compressor, so the amount of refrigerant in the refrigeration cycle is stable.
- two compressors are arbitrarily selected from the plurality of compressors, and one of the compressors
- the exhaust circuit is connected to the sealed casing of the other compressor, and the exhaust pipe of the other compressor is connected to the condenser; or three compressors are arbitrarily selected from the plurality of compressors, and the first compressor is compressed.
- the exhaust circuit of the machine is connected to the sealed casing of the second compressor, and the exhaust circuit of the second compressor is connected to the sealed casing of the third compressor, and the exhaust pipe of the third compressor is connected.
- the condenser is arbitrarily selected from the plurality of compressors, and one of the compressors
- the exhaust circuit is connected to the sealed casing of the other compressor, and the exhaust pipe of the other compressor is connected to the condenser; or three compressors are arbitrarily selected from the plurality of compressors, and the first compressor is compressed.
- the exhaust circuit of the machine is connected to the sealed casing of the second compressor, and the exhaust circuit of the second compressor is connected to the sealed casing of the third compressor
- the sealed casing of the first compressor communicates with the oil reservoir of the second compressor or the third compressor.
- the oil separator provided in the refrigeration cycle apparatus is connected to a low pressure circuit or a sealed casing of the first compressor.
- an integrated reservoir is provided between the evaporator and the low pressure circuit.
- a low pressure circuit that connects the compression mechanism portion and the evaporator includes a check valve or a solenoid valve that prevents a refrigerant from flowing from the compression mechanism portion to the evaporator.
- the motor portion is composed of at least a stator core and a rotor core, and a motor coil provided in the stator core, and an open end of the exhaust circuit of the one compressor is
- the seal housing of the other compressor and the compression mechanism portion and the range in which the stator core is enclosed are open.
- the first compressor starts up first.
- At least one of the motor sections is a variable frequency type with a variable rotational speed.
- one of the two or three compressors arbitrarily selected from the plurality of compressors is a variable frequency variable frequency type, of which one or two
- the compression mechanism portion is a variable capacity type with a variable cooling capacity of two stages.
- the increase or decrease gradient of the cooling capacity is a nearly linear shape.
- the expansion valve and the evaporator are respectively a plurality of.
- the compression mechanism portion is a rotary or a scroll type.
- Embodiment 1 is related to Embodiment 1 of the present invention, showing a refrigeration cycle device
- Figure 2 is a cross-sectional view showing the collective accumulator in relation to the first embodiment
- Figure 3 is related to the first embodiment, showing a refrigeration cycle device
- Figure 4 is a view showing a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
- Figure 5 is related to the second embodiment, showing a refrigeration cycle apparatus having an oil separator
- Figure 6 is a view showing a refrigeration cycle associated with a combination of a variable frequency compressor and a capacity control compressor in connection with Embodiment 3 of the present invention
- Figure 7 is a diagram showing a cooling capacity control diagram relating to two compressors in relation to the third embodiment
- Figure 8 is a view showing a cooling capacity control diagram relating to three compressors related to the third embodiment
- Fig. 9 is a view showing a refrigeration cycle apparatus of a scroll compressor according to a fourth embodiment of the present invention.
- Rotary compressor 10 (20, 30), housing 14 (24), compression mechanism portion 11 (21), motor portion 12 (22), oil reservoir 13 (23, 33), lubricating oil 13a,
- Oil separator plate 16 Oil drain pipe 24d, oil filler pipe 18 (28, 74), exhaust circuit 15, exhaust pipe 24b (34b), cylinder intake pipe 14a (24a), low pressure circuit 19 (29), discharge circuit 25 , connecting pipe 34c, oil sprinkling pipe 34d,
- first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
- features defining “first” or “second” may include at least one of the features, either explicitly or implicitly.
- the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
- the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one piece; it may be a mechanical connection, or it may be an electrical connection or a communication with each other; it may be directly connected or indirectly connected through an intermediate medium, and may be an internal connection of two elements or an interaction relationship between two elements. Unless otherwise expressly defined. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
- a refrigeration cycle apparatus is composed of at least a condenser, an expansion valve, an evaporator, and a plurality of compressors, each of which has a rotary compression mechanism portion that connects a low-pressure circuit of the evaporator and
- the motor unit that drives the compression mechanism unit also has an oil reservoir for each compressor. That is, each compressor includes a sealed casing (ie, a casing described below), a compression mechanism portion, and a motor portion, and the compression mechanism portion and the motor portion are respectively disposed in the sealed casing, and the bottom of the sealed casing has an oil reservoir.
- the cavity, the compression mechanism portion is connected to the evaporator through a low pressure circuit, and the motor portion is used to drive the compression mechanism portion.
- the compression mechanism portion may be a rotary or a scroll type.
- the expansion valve and the evaporator are respectively plural, that is, may include a plurality of expansion valves and a plurality of evaporators, and each room is correspondingly provided with one evaporator and one expansion valve, that is, the refrigeration cycle device may be multiple The room is temperature adjusted.
- At least one compressor exhaust circuit is coupled to the sealed housing of the other compressor.
- two compressors can be arbitrarily selected from a plurality of compressors, and an exhaust circuit of one compressor is connected to a sealed casing of the other compressor, and the other is connected.
- the exhaust pipe of the compressor is connected to the condenser.
- three compressors are arbitrarily selected from a plurality of compressors, and an exhaust circuit of the first compressor is connected to a sealed casing of the second compressor, and a second compressor is provided.
- the exhaust circuit is connected to the sealed casing of the third compressor, and the exhaust pipe of the third compressor is connected to the condenser.
- compressors selected from a plurality of compressors is not limited thereto, and may be four or more.
- N compressors can be selected from several compressors, the exhaust circuit of the first compressor is connected to the sealed housing of the second compressor, and so on, the row of the N-1 compressor
- the gas circuit is connected to the sealed casing of the Nth compressor, and the exhaust pipe of the Nth compressor is connected to the condenser, wherein N ⁇ 2. It can be understood that some of the N compressors may be operated, and the other part of the compressor is in a stopped state.
- the N-1th compressor when the N-1th compressor is operated and the Nth compressor is stopped, the high pressure refrigerant in the N-1th compressor flows into the Nth compressor for circulation, and the compressor in operation is stopped. It can be used as an oil separator for a running compressor, so the amount of oil discharged from the compressor in operation to the refrigeration cycle is reduced.
- the stopped compressor functions as an oil separator of the operating compressor, operating
- the amount of oil discharged from the compressor to the refrigeration cycle will decrease.
- each compressor can maintain a generally appropriate amount of oil.
- the stopped compressor is heated, and the refrigerant in the stopped compressor does not condense, so that the time during which the compressor in the stop of the preheating is turned on from the unstable operation to the stable operation is turned on.
- the start-up time of the refrigeration cycle apparatus can be shortened, and there is no liquid refrigerant in the stopped compressor, so the amount of refrigerant in the refrigeration cycle is stable.
- the sealed casing of the first compressor is in communication with the oil reservoir of the second compressor or the third compressor. Therefore, the second compressor or the third compressor can be used to replenish the first compressor, and the oil supply is easy because the pressure difference is small.
- the oil separator 77 provided in the refrigeration cycle apparatus is connected to the low pressure circuit or the sealed casing of the first compressor.
- the oil stored in the oil separator 77 can be returned to the first compressor for recycling.
- an integrated reservoir 60 is provided between the evaporator and the low pressure circuit.
- the collective accumulator 60 By using the collective accumulator 60, excess refrigerant is ensured in the collective accumulator 60, which can be used the next time the compressor is started, and the collective accumulator 60 is compared to an individual accumulator that has been frequently stopped in the past.
- the volume can be reduced. That is, since there is no liquid refrigerant remaining in the accumulator at the time of stopping, the amount of refrigerant to be operated in the refrigerating cycle is generally appropriate, and the amount of refrigerant enclosed in the refrigerating cycle can be reduced.
- the shunting of the refrigerant and oil for the compressor in operation is averaged.
- the low pressure circuit that connects the compression mechanism portion and the evaporator includes a check valve or a solenoid valve that prevents the refrigerant from flowing from the compression mechanism portion to the evaporator.
- the motor portion is composed of at least a stator core and a rotor core, and a motor coil provided in the stator core, and an open end of the exhaust circuit of the one compressor is coupled to another compressor.
- the sealing housing and the compression mechanism portion and the range surrounded by the stator core are open. Thereby the oil separation effect can be improved.
- the first compressor starts up first.
- At least one of the motor sections is a variable frequency variable speed.
- one of the two or three compressors arbitrarily selected from a plurality of compressors is a variable frequency variable frequency type, and one or two compression mechanisms.
- the department is a variable capacity type with variable cooling capacity of 2 levels.
- the increase or decrease of the cooling capacity is nearly linear.
- the rotary compressor 10 houses the compression mechanism portion 11 and the motor portion 12 in the casing 14. At the same time, the compression mechanism portion 21 and the motor portion 22 are housed in the casing 24 of the rotary compressor 20. Further, each of the compressors is provided with an oil reservoir 13 and an oil reservoir 23 at the bottom of the casing, and a necessary lubricating oil 13a (hereinafter simply referred to as oil 13a) is stored therein.
- oil 13a a necessary lubricating oil 13a
- the oil reservoirs of the rotary compressor are respectively in a range from the height of the central portion of each compression mechanism portion to the bottom of each of the casings.
- the oil level in operation often fluctuates up and down. Especially when the compressor is started at low temperature, A large amount of oil is discharged into the condenser together with a large amount of condensed refrigerant, so the oil level and oil amount of the oil reservoir are greatly reduced.
- the oil separation plate 16 that rotates together with the rotor of the motor unit, and the spray oil that has been separated from the exhaust refrigerant of the compression mechanism unit 11 are dropped into the oil reservoir 13.
- the oil discharge pipe 24d opening to the oil reservoir chamber 23 of the rotary compressor 20 is connected to the rotary compressor 10 via the oil filler pipe 18.
- the oil filler pipe 18 is a means for returning the excess oil 13a in the oil reservoir 23 to the rotary compressor 10.
- the exhaust circuit 15 of the rotary compressor 10 is connected to the side surface of the casing 24 of the rotary compressor 20. Further, the exhaust pipe 24b of the rotary compressor 20 is connected to the inlet of the condenser 70 constituting the refrigeration cycle.
- the cylinder intake pipe 14a of the rotary compressor 10 and the cylinder intake pipe 24a of the rotary compressor 20 are connected to the low-pressure exhaust pipe 62a of the collective accumulator 60 through the low-pressure circuit 19 and the low-pressure circuit 29, respectively. And a low pressure exhaust pipe 62b.
- the condenser 70 connected to the exhaust pipe 24b is connected in the order of the expansion valve 71 and the evaporator 72, and the low pressure outlet of the evaporator 72 is connected to the low pressure intake pipe 61 provided at the upper end of the collective accumulator 60.
- the low pressure circuit 19 and the low pressure circuit 29 are provided with the check valve 75a and the check valve 75b, respectively, and only the flow of the low pressure refrigerant from the collective accumulator 60 to the compression mechanism portion 11 and the compression mechanism portion 21 is possible.
- these check valves may also be solenoid valves. This completes the refrigeration cycle in which the refrigerant is enclosed.
- the number of expansion valves 71 and evaporators 72 in a multi-connected air conditioner that air-conditions a plurality of rooms or a plurality of rooms in a refrigerating apparatus increases. All of the low-pressure refrigerants which are evaporated in the evaporator 72 and have different superheat degrees are collected in the collective accumulator 60 and mixed.
- the refrigeration cycle diagram of FIG. 1 omits the four-way valve required for the air conditioner or the defrosting, which is used for both cold and heat, and simplifies the refrigeration cycle.
- the upper end low pressure suction pipe 61 is connected to the outlet of the evaporator 72.
- the intermediate partition 60c blocks the liquid refrigerant chamber 64 that stores the liquid refrigerant and the split chamber 63 that stores the gas refrigerant.
- the split chamber 63 is provided with the low pressure exhaust pipe 62a and the low pressure exhaust pipe 62b.
- the central pipe 60b fixed in the center of the intermediate partition 60c is provided with a plurality of oil holes 60d.
- the number of the above-mentioned low-pressure exhaust pipes is determined by the number of compressors.
- Fig. 1 the rotary compressor 10 is operating, and the rotary compressor 20 is being stopped. Therefore, the check valve 75a is opened and the check valve 75b is closed.
- the low-pressure refrigerant sucked from the cylinder intake pipe 14a is compressed into a high-pressure refrigerant in the compression mechanism portion 11, and is discharged between the compression mechanism portion 11 and the motor portion 12.
- the refrigerant discharged from the compression mechanism portion 11 usually contains a few percentages of oil during stable operation.
- the amount of oil that is mixed into the refrigerant in the refrigeration system is usually less than 1%.
- the rotary compressor 10 draws in a low-pressure refrigerant containing 1% of oil from the low-pressure circuit 19, 2 to 3% of oil is added to the compression chamber of the compression mechanism unit 11.
- the position of the connecting pipe 24c is preferably the upper portion of the exhaust hole provided in the vicinity of the upper end portion of the compression mechanism portion 21 and the lower side of the stator core constituting the motor portion 22.
- the rotating rotary compressor 20 can function as a highly efficient oil separator due to its housing volume effect and the separation effect of the motor portion 22. Therefore, the oil mixed by the high-pressure refrigerant can be separated and secured in the oil reservoir chamber 23 through the connecting pipe 24c.
- the oil which is mixed with the high-pressure refrigerant and discharged into the rotary compressor 20, for example, as low as 0.3%, and 0.5% of the oil is secured in the oil reservoir chamber 23.
- 0.3% of the oil is discharged from the exhaust pipe 24b together with the high-pressure refrigerant into the condenser 70 to become circulating oil circulating in the refrigeration apparatus. That is, the circulating refrigerant contains 0.3% oil.
- a high-pressure refrigerant containing 0.3% of oil is discharged to the condenser 70 through the exhaust pipe 24b. Thereafter, it is returned to the compression mechanism portion 11 through the expansion valve 71 and the evaporator 72 and further through the collective accumulator 60 and the low pressure circuit 19, thus reciprocatingly circulating. Due to this cycle, the stopped rotary compressor 20 is heated to approach the temperature of the rotary compressor 10.
- the effect of the check valve 75b disposed on the low pressure circuit 29 will be described.
- the rotary compressor represented by the rotary compressor 20 has no intake valve, and the high-pressure refrigerant leaks into the cylinder intake pipe 24a through the compression chamber of the compression mechanism portion 21. Therefore, the pressure from the casing 24 to the check valve 75b is the high pressure side, and the check valve 75b closes to prevent the reverse flow of the collective accumulator 60.
- the rotary compressor 10 When the rotary compressor 10 is operated, when the motor unit 22 of the rotary compressor 20 is energized, when the rotary compressor 20 is started, the pressure difference acting on the slider in the compression mechanism portion of the rotary compressor 20 is zero. This is the same condition as the balanced pressure start after a long stop. However, the motor portion 22 may not be accelerated when the volume of the low pressure circuit 29 before the check valve 75b is too small. At this time, the muffler can be added before the cylinder intake pipe 24a and the check valve 75b.
- the check valve 75a and the check valve 75b are disposed in each connection circuit that connects the cylinder intake pipe 14a, the cylinder intake pipe 24a, and the evaporator 72.
- the check valve is disposed in the connection circuit connecting the accumulator and the evaporator 72.
- the invention is characterized by stopping
- the rotary compressor 20 shares the high pressure side pressure of the rotary compressor 10 in operation, and the rotary compressor 20 can be started and stopped at any time.
- the rotary compressor 10 recovers the above 0.3% oil from the refrigerant circulating in the refrigeration system. However, the rotary compressor 10 reduces the oil storage amount in proportion to the time operation, and on the other hand, the rotary compressor 20 that is stopped increases the oil storage amount.
- the oil filler pipe 18 is required as a solution thereto.
- the oil discharge pipe 24d provided on the side surface of the casing 24 of the rotary compressor 20 opens to the oil reservoir chamber 23. However, the opening position cannot be the lower side of the minimum oil level or the minimum oil amount required when the rotary compressor 20 is operated again.
- Patent Document 1 USP 2,988, 267
- Patent Document 2 JP-A-1999013664
- FIG. 3 is a state in which the rotary compressor 20 is started up during operation of the rotary compressor 10. As described above, the check valve 75b is opened due to the start, and the low pressure refrigerant flows from the collective accumulator 60 to the cylinder intake pipe 24a. Therefore, the amount of refrigerant circulation in the refrigeration cycle will increase.
- the high-pressure refrigerant discharged from the rotary compressor 10 and the high-pressure refrigerant discharged from the compression mechanism unit 21 are mixed by the motor unit 22. During this period, the oil contained in the mixed refrigerant is separated and secured in the oil reservoir 23.
- the high-pressure refrigerant having a reduced oil amount and reduced to 1% or less is discharged from the exhaust pipe 24b to the condenser 70.
- the low-pressure refrigerant having different degrees of superheat which is evaporated by the plurality of evaporators 72 is concentrated in the liquid refrigerant chamber 64 of the collective accumulator 60. Therefore, the superheat degree is averaged due to the mixing of the refrigerant. Further, the amount of oil discharged from the plurality of heat exchangers to the refrigeration cycle deteriorates the heat exchange efficiency of the heat exchanger. The amount of oil discharged from the refrigeration cycle at the time of stabilization is 1% or less in terms of the circulating refrigerant ratio.
- the averaged low-pressure refrigerant and the oil dissolved in the refrigerant do not interfere with each other, and are branched into the low-pressure exhaust pipe 62a and the low-pressure exhaust pipe 62b in the split chamber 63, and returned to the rotary compressor 10, respectively.
- the effect of the liquid refrigerant chamber 64 is to average the superheat of the low-pressure refrigerant, and the split chamber 63 can accurately distribute the split flow. Therefore, both rotary compressors can achieve optimum compression efficiency.
- the temperature of the refrigeration cycle is generally controlled by the rotary compressor 10 having a small displacement.
- the rotational efficiency of the rotary compressor 10 is also high from the viewpoints of room temperature control and APF (seasonal efficiency).
- the rotating rotary compressor 20 is heated. Therefore, the rotary compressor 10 is started first, and it is also desirable from the viewpoint of preventing condensation of the refrigerant of the rotary compressor 20.
- the rotary compressor 10 and the rotary compressor 20 are connected by the exhaust circuit 15, so that the rotary compressor 20 that is being stopped can be heated in advance.
- the exhaust circuit 15 of the rotary compressor 10 is connected to the rotary compressor 20, and the high-pressure refrigerant of the rotary compressor 10 is circulated in the rotary compressor 20. Due to this arrangement,
- the rotating rotary compressor 20 functions as a high-efficiency oil separator of the rotary compressor 10 in operation. Therefore, the amount of oil discharged from the rotary compressor 10 to the refrigeration cycle is reduced as compared with the conventional design of the rotary compressor 20 that does not pass through. At the same time, each rotary compressor can maintain a generally appropriate amount of oil.
- the volume of the collective reservoir can be reduced compared to the conventional reservoir that has been frequently stopped. That is, since there is no liquid refrigerant remaining in the accumulator at the time of stopping, the amount of refrigerant to be operated in the refrigerating cycle is generally appropriate, and the amount of refrigerant enclosed in the refrigerating cycle can be reduced.
- the control of the refrigerant and lubricating oil in the refrigeration cycle is easy, and the refrigeration cycle efficiency and reliability are superior.
- a rotary compressor (30) and a total of three compressors are added to the first embodiment to constitute a refrigeration cycle apparatus.
- the discharge circuit 25 of the rotary compressor 20 is connected to the connection pipe 34c of the rotary compressor 30.
- the oil filler pipe 28 is connected to the oil discharge pipe 34d of the rotary compressor 30 and the rotary compressor 10. The above three rotary compressors are all in operation.
- the high-pressure refrigerant discharged from the rotary compressor 10 and the exhaust refrigerant of the rotary compressor 20 are collected and flowed into the rotary compressor 30. Further, the discharge refrigerant collection from the rotary compressor (30) is discharged from the exhaust pipe (34b) to the condenser (70). On the other hand, the excess oil 13a of the oil reservoir 33 is returned from the oil filler pipe 28 to the rotary compressor 10.
- a part of the discharge amount of the rotary compressor 10 by the flow of the high-pressure refrigerant described above can be secured in the rotary compressor 20, and a part of the discharge amount of the rotary compressor 20 is secured in the rotary compressor 30. Therefore, the amount of discharge from each rotary compressor is smaller than the conventional design in which the refrigerant flows directly to the condenser 70.
- the excess oil secured in the rotary compressor 30 is automatically supplied with oil from the oil reservoir 33 to the rotary compressor 10 in operation. That is, since the amount of oil can be controlled between the three rotary compressors, the respective rotary compressors can maintain an appropriate amount of oil. At the same time, the amount of oil discharged to the refrigeration cycle can be reduced. That is, in the second embodiment, the same effects as those in the first embodiment can be obtained.
- the oil filler pipe 28 is omitted, and an oil separator 77 is provided between the exhaust pipe 34b and the condenser 70, and the oil secured in the oil separator 77 is returned to the rotary compressor 10. Since the excess oil 13a secured in the oil reservoir 33 of the rotary compressor 30 does not return to the rotary compressor 10, the amount of oil discharged from the exhaust pipe 34b increases, and can be secured in the oil separator 77.
- the oil secured in the oil separator 77 is returned to the low pressure circuit 19 through the oil filler pipe 74 (dashed line) or directly back to the rotary compressor 10.
- the method such as the fuel injection described in the first embodiment is used.
- the oil separator 77 can be used as an alternative to the method disclosed in Fig. 4 of the embodiment 1 or the embodiment 2.
- Embodiment 3 is a specific application case of Embodiment 1 or Embodiment 2.
- the motor unit 12 of the rotary compressor 10 employs a variable frequency motor having a variable rotational speed
- the rotary compressor 20 employs a cooling capacity of two stages.
- the variable capacity control type compression mechanism unit 21 is a specific application case of Embodiment 1 or Embodiment 2.
- mode A is a cooling amount that is variable according to the rotational speed.
- the capacity control type compression mechanism portion 21 can be realized by a prior art, such as the disclosure of Patent Document 3 (CN201410046931.5), the rotary compressor of Patent Document 3 including a pressure switcher, one of the compression mechanism portions 21.
- the vane chamber is in a sealed state, and the pressure switch can switch the pressure of the sealed vane chamber between two different pressures to stop or cancel the compression of the cylinder corresponding to the sealed vane chamber.
- the compression mechanism unit 21 is composed of two parts of the first compression material 26a and the second compression material 26b, and is disposed with a three-way valve (not shown) disposed outside the compressor.
- the three valve ports of the three-way valve are respectively connected to the sliding chamber of the second compression member 26b, a low pressure environment (such as a return air port or a low pressure circuit), and a high pressure environment (such as a space inside the housing).
- the second compression member 26b is subjected to the cylinder stop operation or the cylinder release operation by the control of the three-way valve, and the cooling capacity is level 2 by the combination with the first compression member 26a in the normal operation. Switch.
- the capacity of the rotary compressor 20 can be switched between 50% and 100%.
- This mode of operation is called mode B and mode C, respectively.
- the capability ratio is not only 50:100, but can be designed to be 20:100.
- the refrigeration capacity of the rotary compressor 10 at 120 rps is 6 kW
- only the minimum value (10 rps) of the refrigeration capacity during operation of the rotary compressor 10 is 0.5 kW, and the maximum value (120 rps) is 6 kW.
- the mode B of the rotary compressor 20 has a cooling capacity of 6 kW and a mode C of 12 kW.
- the minimum value and the maximum value of the cooling capacity are 0.5 KW to 6 KW in the range of the mode A. Further, when the rotary compressor 20 is started in the mode B, the minimum value and the maximum value are 0.5 KW to 12 kW in the range of A + B. Further, when the rotary compressor 20 is switched to the mode C, the minimum value and the maximum value are in the range of 12 kW to 18 kW in the A+C range. In other words, it is possible to continuously perform linear cooling amount control between 0.5 KW and 18 KW by the operation of the rotary compressor 10 and the rotary compressor 20.
- linear cooling capacity control can be performed between 0.5 KW and 30 KW.
- the air conditioner can improve the air conditioning quality of each room, and the overall efficiency of the system can be maximized, while ensuring the system's reliability.
- the refrigeration cycle devices disclosed in Embodiments 1 and 2, and the variable capacity variable device using the same are not only rotary pressure
- the scroll compressor and the internal pressure of the sealed casing can also be applied to a scroll compressor of a high pressure side.
- the scroll compressor 110 houses the compression mechanism portion 111 and the motor portion 12 in the casing 14
- the scroll compressor 120 houses the compression mechanism portion 121 and the motor portion 22 in the casing 24.
- each of the compressors may store the oil 13a in the oil reservoir chamber 13 and the oil reservoir chamber 23 at the bottom of the casing.
- the scroll compressor 110 and the scroll compressor 120 are generally lower than the rotary compressor 10 and the rotary compressor 20, and the compression mechanism portion is on the upper side of the casing and the motor portion is on the lower side. As in Embodiment 1, the exhaust circuit 15 is disposed between them.
- the cylinder intake pipe 14a and the cylinder intake pipe 24a are connected to the compression mechanism portion 111 and the compression mechanism portion 121, respectively.
- the newly added connecting pipe 24c opens between the compression mechanism portion 121 and the stator core of the motor portion 22.
- the techniques disclosed in the first embodiment, the second embodiment, and the third embodiment can be applied.
- the oil return to the scroll compressor 110 by the oil filler pipe 18 can be borrowed by a method of fuel injection or air jet disclosed by the scroll compressor.
- the present invention can be applied to an air conditioner or the like as a refrigeration apparatus equipped with a plurality of rotary compressors.
- the control of the cooling capacity can be continuously performed by the application of the variable frequency compressor or the variable displacement compressor.
- the problem to be solved by the present invention is as follows: a plurality of compressors and a multi-connected air conditioner comprising a plurality of evaporators provided in each room, the compressor is repeatedly started and stopped due to a change in the air-conditioning load. Therefore, the amount of oil retained by each compressor is increased or decreased, and a large amount of refrigerant is condensed in the compressor that is cooled in the shutdown. Compressors with reduced oil retention are prone to failure, and refrigerant condensation in the compressor not only causes a decrease in the performance of the refrigeration cycle, but also discharges a large amount of oil when restarted.
- the high-temperature oil mixed refrigerant discharged from the first compressor in operation passes through the second compressor that is stopped or in operation. At this time, the oil separated by the second compressor is automatically returned to the first compressor in the oil reservoir of the compressor.
- the No. 2 compressor in the shutdown will heat up, so it can avoid condensation of the refrigerant.
- the low pressure refrigerant and oil passing through several evaporators are concentrated in one collective reservoir. Here, the low pressure refrigerant after the superheat is averaged can be correctly split into the operating compressor. Therefore, both the running and stopping compressors must maintain the necessary amount of refrigerant and oil to avoid over or under.
- the first feature "on” or “under” the second feature may be a direct contact of the first and second features, or the first and second features may be indirectly through an intermediate medium, unless otherwise explicitly stated and defined. contact.
- the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above the second feature or It is obliquely above, or merely indicates that the first feature level is higher than the second feature.
- the first feature "below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.
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Abstract
Description
Claims (13)
- 一种制冷循环装置,其特征在于,至少由冷凝器、膨胀阀、蒸发器和数台压缩机组成,每台所述压缩机的密封壳体中具备连通所述蒸发器的低压回路的回转式压缩机构部以及驱动所述压缩机构部的电机部,每台所述压缩机还具备储油腔,至少有一个压缩机的排气回路与另一个压缩机的密封壳体连接。
- 根据权利要求1所述的制冷循环装置,其特征在于,从所述数台压缩机中任意选择两台压缩机,一方压缩机的排气回路与另一方压缩机的密封壳体连接,所述另一方压缩机的排气管连接所述冷凝器;或者从所述数台压缩机中任意选择3台压缩机,第1台压缩机的排气回路连接第2台压缩机的密封壳体,所述第2台压缩机的排气回路连接第3台压缩机的密封壳体,所述第3台压缩机的排气管连接所述冷凝器。
- 根据权利要求2所述的制冷循环装置,其特征在于,所述第1台压缩机的密封壳体与所述第2台压缩机或者所述第3台压缩机的储油腔连通。
- 根据权利要求2所述的制冷循环装置,其特征在于,所述制冷循环装置中具备的油分离器与所述第1台压缩机的低压回路或者密封壳体连接。
- 根据权利要求1所述的制冷循环装置,其特征在于,所述蒸发器和所述低压回路之间具备集合式储液器。
- 根据权利要求1所述的制冷循环装置,其特征在于,连接所述压缩机构部和所述蒸发器的低压回路中,具备防止从所述压缩机构部向所述蒸发器进行冷媒流动的单向阀或者电磁阀。
- 根据权利要求1所述的制冷循环装置,其特征在于,所述电机部至少由定子铁芯和转子铁芯以及所述定子铁芯中具备的电机线圈组成,所述一个压缩机的所述排气回路的开口端对被所述另一个压缩机的密封壳体和压缩机构部以及定子铁芯围住的范围开口。
- 根据权利要求2所述的制冷循环装置,其特征在于,所述第1台压缩机最先开始启动。
- 根据权利要求1所述的制冷循环装置,其特征在于,所述电机部中至少一个是旋转速度可变的变频式。
- 根据权利要求1所述的制冷循环装置,其特征在于,从所述数台压缩机中任意选择的2台或者3台压缩机中,其中1台的电机部为旋转速度可变的变频式,其中1台或者2台的压缩机构部为制冷能力2级可变的变容式。
- 根据权利要求10所述的制冷循环装置,其特征在于,所述2台或者3台的压缩机组合中得到的最小制冷量和最大制冷量的范围中,所述制冷量的增减坡度为近直线状。
- 根据权利要求1所述的制冷循环装置,其特征在于,所述膨胀阀和所述蒸发器分别为多个。
- 根据权利要求1所述的制冷循环装置,其特征在于,所述压缩机构部为旋转式或者涡旋式。
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PCT/CN2015/081564 WO2016201623A1 (zh) | 2015-06-16 | 2015-06-16 | 制冷循环装置 |
EP15895196.2A EP3312526A4 (en) | 2015-06-16 | 2015-06-16 | REFRIGERATION CIRCUIT DEVICE |
JP2017533673A JP2017531156A (ja) | 2015-06-16 | 2015-06-16 | 冷凍サイクル装置 |
US15/511,544 US10605492B2 (en) | 2015-06-16 | 2015-06-16 | Refrigeration cycle device |
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Also Published As
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US10605492B2 (en) | 2020-03-31 |
EP3312526A1 (en) | 2018-04-25 |
EP3312526A4 (en) | 2019-01-23 |
US20170284706A1 (en) | 2017-10-05 |
JP2017531156A (ja) | 2017-10-19 |
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