Patent Application
20240327693
The present disclosure relates to a use as a refrigerant in a refrigeration cycle apparatus.
For refrigeration apparatuses, hydrofluoroolefin (HFO refrigerant) having lower global warming potential (hereinafter may be simply referred to as GWP) than a HFC refrigerant have been focused, and, for example, 1,2-difluoroethylene (HFO-1132) has been studied as a refrigerant having low GWP in PTL 1 (Japanese Unexamined Patent Application Publication No. 2019-196312).
A use as a refrigerant in a refrigeration cycle apparatus according to a first aspect is a use of at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin, as the refrigerant in the refrigeration cycle apparatus. The refrigeration cycle apparatus includes a refrigerant circuit including a compressor. The compressor includes a compression element that compresses the refrigerant, and an oil reservoir that stores a refrigerating machine oil. The pressure of air inside the refrigerant circuit is 667 Pa or less. The refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of an acid scavenger. The temperature of the refrigerating machine oil in the oil reservoir is maintained at 120° C. or lower.
A use as a refrigerant in a refrigeration cycle apparatus according to a second aspect is a use of at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin, as the refrigerant in the refrigeration cycle apparatus. The refrigeration cycle apparatus includes a refrigerant circuit including a compressor. The compressor includes a compression element that compresses the refrigerant, and an oil reservoir that stores a refrigerating machine oil. The pressure of air inside the refrigerant circuit is 1333 Pa or less. The refrigerating machine oil contains no acid scavenger or contains less than 3.0 wt % of an acid scavenger. The temperature of the refrigerating machine oil in the oil reservoir is maintained at 100° C. or lower.
A use as a refrigerant in a refrigeration cycle apparatus according to a third aspect is a use of at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin, as the refrigerant in the refrigerant. The refrigeration cycle apparatus includes a refrigerant circuit including a compressor. The compressor includes a compression element that compresses the refrigerant, and an oil reservoir that stores a refrigerating machine oil. The pressure of air inside the refrigerant circuit is 2000 Pa or less. The refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of an acid scavenger. The temperature of the refrigerating machine oil in the oil reservoir is maintained at 100° C. or lower.
A use as a refrigerant in a refrigeration cycle apparatus according to a fourth aspect is a use of at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin, as the refrigerant in the refrigeration cycle apparatus. The refrigeration cycle apparatus includes a refrigerant circuit including a compressor. The compressor includes a compression element that compresses the refrigerant, and an oil reservoir that stores a refrigerating machine oil. The pressure of air inside the refrigerant circuit is 2000 Pa or less. The refrigerating machine oil contains no acid scavenger or contains less than 3.0 wt % of an acid scavenger. The temperature of the refrigerating machine oil in the oil reservoir is maintained at 80° C. or lower.
A use as a refrigerant in a refrigeration according to a fifth aspect is a use of at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin, as the refrigerant in the refrigeration cycle apparatus. The refrigeration cycle apparatus includes a refrigerant circuit including a compressor. The compressor includes a compression element that compresses the refrigerant, and an oil reservoir that stores a refrigerating machine oil. The pressure of air inside the refrigerant circuit is 4000 Pa or less. The refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of an acid scavenger. The temperature of the refrigerating machine oil in the oil reservoir is maintained at 80° C. or lower.
Hereinafter, an air conditioning apparatus 1 as a refrigeration cycle apparatus according to the present embodiment will be described with reference to
The air conditioning apparatus 1 is an apparatus that conditions air in a target space by performing a vapor compression refrigeration cycle.
The air conditioning apparatus 1 includes, mainly, an outdoor unit 2, an indoor unit 3, a liquid-refrigerant connection pipe 6 and a gas-refrigerant connection pipe 5 that connect the outdoor unit 2 and the indoor unit 3 to each other, and a controller 7 that controls the operation of the air conditioning apparatus 1.
The air conditioning apparatus 1 performs a refrigeration cycle in which a refrigerant sealed in the refrigerant circuit 10 is compressed, condensed, radiates heat, is decompressed, evaporated, and then compressed again. In the present embodiment, the refrigerant circuit 10 is filled with a refrigerant for performing a vapor compression refrigeration cycle.
The refrigerant with which the refrigerant circuit 10 is filled is at least one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, and a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin. Since 1,2-difluoroethylene or other hydrofluoroolefin has low GWP, global warming is suppressed. In addition, 1,2-difluoroethylene and other hydrofluoroolefin are low in stability and easily decomposes due to a disproportionation reaction or the like, in particular, easily decomposes or deteriorates by being present with a refrigerating machine oil having a high temperature. However, deterioration and decomposition of a refrigerant are suppressed in the air conditioning apparatus 1 in the present embodiment, since the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, a refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of an acid scavenger, and the temperature of the refrigerating machine oil in an oil reservoir, which is described later, is maintained at 120° C. or lower.
The mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon is, for example, a mixed refrigerant that contains 1,2-difluoroethylene and R32, a mixed refrigerant that is made of only 1,2-difluoroethylene and R32, a mixed refrigerant that contains 1,2-difluoroethylene, R32, and R1234yf, or a mixed refrigerant that is made of only 1,2-difluoroethylene, R32, and R1234yf.
The mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin is, for example, a mixed refrigerant that contains 1,2-difluoroethylene and R1234yf, a mixed refrigerant that is made of only 1,2-difluoroethylene and R1234yf, a mixed refrigerant that contains 1,2-difluoroethylene, R32, and R1234yf, or a mixed refrigerant that is made of only 1,2-difluoroethylene, R32, and R1234yf.
The mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin is, for example, a mixed refrigerant that contains R1234yf, R1234ze, R1233zd, and a hydrofluorocarbon, a mixed refrigerant that is made of only R1234yf, R1234ze, R1233zd, and hydrofluorocarbon, a mixed refrigerant that contains 1,2-difluoroethylene, R32, and R1234yf, or a mixed refrigerant that is made of only 1,2-difluoroethylene, R32, and R1234yf.
Hydrofluorocarbon is, for example, R32, R134a, R410A, or the like, and R32 is preferable among them.
A refrigerating machine oil is enclosed together with the refrigerant in the refrigerant circuit 10. The refrigerating machine oil used together with the refrigerant is preferably an ether oil or an ester oil. The ether oil is, for example, a polyvinyl ether oil (PVE) or a polyoxyalkylene oil. The ester oil is, for example, a dibasic acid ester oil containing dibasic acid and monohydric alcohol, a polyol ester oil containing polyol and fatty acid, a complex ester oil containing polyol, polybasic acid, and monohydric alcohol (or fatty acid), a polyol carbonic acid ester oil, or the like. As the refrigerating machine oil, one type of a refrigerating machine oil may be solely used, or two or more types of refrigerating machine oils may be used in combination.
In the present embodiment, 3.0 wt % or more and 5.0 wt % or less of the acid scavenger is blended in the refrigerating machine oil. Consequently, corrosion of the refrigerant circuit 10 due to an acid that may be generated by decomposition of the refrigerant is suppressed. The blending amount of the acid scavenger can be, for example, a value obtained by measuring the refrigerating machine oil stored in an oil reservoir 37 of a compressor 11 in the refrigerant circuit 10 of the air conditioning apparatus 1 whose operation is stopped. As such an acid scavenger, phenyl glycidyl ether, alkyl glycidyl ether, alkylene glycol glycidyl ether, cyclohexene oxide, α-olefin oxide, an epoxy compound such as an epoxidized soybean oil, carbodiimide, or the like is usable. Among these, phenyl glycidyl ether, alkyl glycidyl ether, alkylene glycol glycidyl ether, cyclohexene oxide, or α-olefin oxide is preferable from the point of view of compatibility. The carbon number of each of these acid scavengers is preferably 3 or more and 30 or less and is more preferably 4 or more and 24 or less. The total carbon number of α-olefin oxide is 4 or more and 50 or less and is more preferably 4 or more and 24 or less. As the acid scavenger, only one type of acid scavengers may be used, or multiple types may be used in combination.
Additionally, the refrigerating machine oil can further contain at least one or more types of additives selected from the group consisting of an extreme pressure agent and an antioxidant. For example, 3 wt % or less of these additives are preferably blended in the refrigerating machine oil. By adjusting the blending amount of the antioxidant or the acid scavenger, the moisture content in a fluid including the refrigerant and the refrigerating machine oil is easily adjusted.
The extreme pressure agent includes, for example, an extreme pressure agent containing phosphoric acid esters; an extreme pressure agent based on an organosulfur compound such as monosulfides, polysulfides, sulfoxides, sulfones, thiosulfinates, sulfurized fats and oils, thiocarbonates, thiophenes, thiazoles, or methanesulfonic acid esters; an extreme pressure agent based on a thiophosphoric acid ester such as thiophosphoric acid triesters; an extreme pressure agent based on an ester such as a higher fatty acid, hydroxyaryl fatty acids, polyhydric alcohol esters, or acrylic acid esters; an extreme pressure agent based on an organochlorine such as chlorinated hydrocarbons, such as chlorinated paraffin, or a chlorinated carboxylic acid derivative; an extreme pressure agent based on a fluoroorganic compound such as fluorinated aliphatic carboxylic acids, fluorinated ethylene resins, fluorinated alkylpolysiloxanes, or fluorinated graphite; an extreme pressure agent based on alcohol such as higher alcohol; or an extreme pressure agent based on a metal compound such as naphthenic acid salts (lead naphthenate and the like), fatty acid salts (lead fatty acid and the like), thiophosphoric acid salts (zinc dialkyldithiophosphate and the like), thiocarbamic acid salts, an organomolybdenum compound, an organotin compound, an organogermanium compound, or a boric acid ester.
As the antioxidant, for example, a phenol-based antioxidant or an amine-based antioxidant is usable. The phenol-based antioxidant includes 2,6-di-tert-butyl-4-methylphenol (DBPC), 2,6-di-tert-butyl-4-ethylphenol, 2,2′-methylenebis (4-methyl-6-tert-butylphenol), 2,4-dimethyl-6-tert-butylphenol, 2,6-di-tert-buthylphenol, di-tert-butyl-p-cresol, bisphenol A, or the like. The amine-based antioxidant includes N,N′-diisopropyl-p-phenylenediamine, N,N′-di-sec-butyl-p-phenylenediamine, phenyl-α-naphthylamine, N.N′-di-phenyl-p-phenylenediamine, N,N-di (2-naphthyl)-p-phenylenediamine, or the like.
The moisture content inside the refrigerant circuit 10 is preferably 300 ppm or less from the point of view of suppression of decomposition of 1,2-difluoroethylene and other hydrofluoroolefin.
The pressure of air inside the refrigerant circuit 10 is 667 Pa (5 Torr) or less from the point of view of suppression of decomposition of the 1,2-difluoroethylene and other hydrofluoroolefin.
The moisture content and the pressure of air inside the refrigerant circuit 10 can be, for example, values of a fluid at an outlet of a heat exchanger (an indoor heat exchanger 18 or an outdoor heat exchanger 13) functioning as a condenser for the refrigerant or of a fluid at an outlet of a high-pressure receiver 8, which is described later, in the refrigerant circuit 10 of the air conditioning apparatus 1 in an operation stop state.
The outdoor unit 2 is connected to the indoor unit 3 through the liquid-refrigerant connection pipe 6 and the gas-refrigerant connection pipe 5 and constitutes part of the refrigerant circuit 10. The outdoor unit 2 includes, mainly, the compressor 11, a four-way switching valve 12, the outdoor heat exchanger 13, an expansion valve 9, the high-pressure receiver 8, a low-pressure receiver 14, an outdoor fan 15, a liquid-side shutoff valve 17, and a gas-side shutoff valve 16.
The compressor 11 is an apparatus that compresses the low-pressure refrigerant in the refrigeration cycle, until the refrigerant becomes to have a high pressure. As the compressor 11, for example, a compressor in which a compression element of a rotary type, a scroll type, or the like is rotationally driven by a compressor motor is usable. Details of the compressor 11 in the present embodiment will be described later. The compressor motor is used to change capacity, and the operation frequency of the compressor motor can be controlled by an inverter. For example, the number of revolutions of the compressor 11 is controlled with a predetermined target evaporation temperature as a target value during a cooling operation, and the number of rotations of the compressor 11 is controlled with a predetermined target condensation temperature as a target value during a heating operation.
By switching the connection states in the refrigerant circuit 10, the four-way switching valve 12 is switchable between a first connection state (refer to the solid lines in
The outdoor heat exchanger 13 is a heat exchanger that functions as a condenser or a radiator for the high-pressure refrigerant in the refrigeration cycle during a cooling operation and functions as an evaporator for the low-pressure refrigerant in the refrigeration cycle during a heating operation. The outdoor heat exchanger 13 includes a plurality of heat transfer tubes (not illustrated) in which the refrigerant flows, and a plurality of heat transfer fins (not illustrated) that are disposed with a gap therebetween, the gap allowing air to flow through the gap. The plurality of heat transfer tubes are arranged in the up-down direction, and the heat transfer tubes extend in the horizontal direction substantially. The plurality of heat transfer fins extending in the up-down direction are arranged in a direction in which the heat transfer tubes extend with a predetermined interval therebetween. The plurality of heat transfer fins and the plurality of heat transfer tubes are combined together such that the plurality of heat transfer tubes extend through the heat transfer fins.
The outdoor fan 15 generates an air flow for supplying outdoor air to the outdoor heat exchanger 13 inside the outdoor unit 2 and, after causing the outdoor air to exchange heat with the refrigerant in the outdoor heat exchanger 13, discharging the outdoor air to the outside of the outdoor unit 2. The outdoor fan 15 is rotationally driven by an outdoor fan motor.
The expansion valve 9 is provided between a liquid-side end portion of the outdoor heat exchanger 13 and the high-pressure receiver 8. The expansion valve 9 is, for example, an electronic expansion valve whose valve opening degree is adjustable by control. Details of the expansion valve 9 will be described later.
The high-pressure receiver 8 is provided between the expansion valve 9 and the liquid-side shutoff valve 17. The high-pressure receiver 8 is a refrigerant container capable of storing a surplus refrigerant as a liquid refrigerant.
The low-pressure receiver 14 is a refrigerant container that is provided between the suction side of the compressor 11 and one of connection ports of the four-way switching valve 12 and that is capable of storing, as a liquid refrigerant, a surplus refrigerant in the refrigerant circuit 10.
The liquid-side shutoff valve 17 is a manual valve that is disposed at a portion of the outdoor unit 2 connected to the liquid-refrigerant connection pipe 6.
The gas-side shutoff valve 16 is a manual valve that is disposed at a portion of the outdoor unit 2 connected to the gas-refrigerant connection pipe 5.
The outdoor unit 2 includes an outdoor-unit control unit 71 that controls the operation of each portion that constitutes the outdoor unit 2. The outdoor-unit control unit 71 includes a microcomputer including a CPU, a memory, and the like. The outdoor-unit control unit 71 is connected to an indoor-unit control unit 72 of each indoor unit 3 through a communication line, and transmits and receives a control signal and the like.
The outdoor unit 2 is provided with a discharge temperature sensor 75, a suction temperature sensor 76, an outdoor heat-exchange temperature sensor 77, an outside-air temperature sensor 78, an oil-temperature detection sensor 79, and the like. Each of these sensors is electrically connected to the outdoor-unit control unit 71 and transmits a detection signal to the outdoor-unit control unit 71. The discharge temperature sensor 75 detects the temperature of the refrigerant flowing in a discharge pipe 4d that connects the discharge side of the compressor 11 to one of the connection ports of the four-way switching valve 12. The suction temperature sensor 76 detects the temperature of the refrigerant flowing in, among suction flow paths that connect the suction side of the compressor 11 to one of the connection ports of the four-way switching valve 12, a suction pipe 4e extending from the low-pressure receiver 14 to the suction side of the compressor 11. The outdoor heat-exchange temperature sensor 77 detects the temperature of the refrigerant flowing at an outlet of the liquid side of the outdoor heat exchanger 13, the liquid side being a side opposite to the side to which a third pipe 4c is connected. The outside-air temperature sensor 78 detects the temperature of outside air before passing through the outdoor heat exchanger 13. The oil-temperature detection sensor 79 detects the temperature of the refrigerating machine oil stored in the oil reservoir 37 of the compressor 11.
The indoor unit 3 is installed on a wall surface, a ceiling, or the like inside a room that is a target space. The indoor unit 3 is connected to the outdoor unit 2 through the liquid-refrigerant connection pipe 6 and the gas-refrigerant connection pipe 5 and constitutes a part of the refrigerant circuit 10.
The indoor unit 3 includes the indoor heat exchanger 18 and an indoor fan 19.
The indoor heat exchanger 18 is connected on the liquid side to the liquid-refrigerant connection pipe 6 and connected on the gas-side end to the gas-refrigerant connection pipe 5. The indoor heat exchanger 18 is a heat exchanger that functions as an evaporator for the low-pressure refrigerant in the refrigeration cycle during a cooling operation and functions as a condenser or a radiator for the high-pressure refrigerant in the refrigeration cycle during a heating operation.
The indoor fan 19 generates an air flow for suctioning air in a room that is an air-conditioning target space into the indoor unit 3 and, after causing the air to exchange heat with the refrigerant in the indoor heat exchanger 18, discharging the air to the outside of the indoor unit 3. The indoor fan 19 is driven to rotate by an indoor fan motor.
The indoor unit 3 includes the indoor-unit control unit 72 that controls the operation of each portion that constitutes the indoor unit 3. The indoor-unit control unit 72 includes a microcomputer including a CPU, a memory, and the like. The indoor-unit control unit 72 is connected to the outdoor-unit control unit 71 through a communication line, and transmits and receives a control signal and the like.
The indoor unit 3 is provided with an indoor liquid-side heat-exchange temperature sensor 73, an indoor-air temperature sensor 74, and the like. Each of these sensors is electrically connected to the indoor-unit control unit 72 and transmits a detection signal to the indoor-unit control unit 72. The indoor liquid-side heat-exchange temperature sensor 73 detects the temperature of the refrigerant flowing at an outlet of the liquid side of the indoor heat exchanger 18, the liquid side being a side opposite to the side to which the gas-refrigerant connection pipe 5 is connected. The indoor-air temperature sensor 74 detects the temperature of indoor air before passing through the indoor heat exchanger 18.
In the air conditioning apparatus 1, the outdoor-unit control unit 71 and the indoor-unit control unit 72 are connected to each other through a communication line and thereby constitute the controller 7 that controls the operation of the air conditioning apparatus 1.
The controller 7 includes, mainly, a processor, such as a CPU (central processing unit), and a memory, such as a ROM and a RAM. Various kinds of processing and control by the controller 7 are implemented by the portions included in the outdoor-unit control unit 71 and/or the indoor-unit control unit 72 that integrally function.
The controller 7 controls the components of the refrigerant circuit 10 such that the temperature of the refrigerating machine oil stored in the oil reservoir 37 in the refrigerant circuit 10 of the air conditioning apparatus 1 is maintained at 120° C. or lower. As such control, for example, the number of rotations of the compressor 11 is controlled such that the temperature of the refrigerating machine oil detected by the oil-temperature detection sensor 79 is maintained at 120° C. or lower.
A remote controller 70 is disposed in a room that is an air-conditioning target space or in a specific space in a building including an air-conditioning target space, and is used for an operation control instruction and monitoring of the operational state of the air conditioning apparatus 1 by a user or the like.
The remote controller 70 includes a reception portion 70a, such as an operation button or a touch panel, for receiving an input of information by being operated by a user or the like, and a display 70b capable of displaying various items of information. The remote controller 70 is connected to each of the outdoor-unit control unit 71 and the indoor-unit control unit 72 through a communication line and capable of supplying information received by the reception portion 70a from a user to the controller 7. Information received from the controller 7 can be output at the display 70b.
The information to be received by the reception portion 70a from a user or the like is not limited and includes various kinds of information such as an instruction to execute a cooling operating mode, an instruction to execute a heating operating mode, an instruction to stop an operation, and specification of a set temperature. The information to be displayed on the display 70b is not limited and includes a state (cooling or heating) of a current operating mode, a set temperature, information indicating occurrence of various abnormalities, and the like.
As the compressor 11, for example, a scroll compressor, such as that illustrated in
This compressor 11 includes a casing 20, a scroll compression mechanism 21, a drive motor 24, a crankshaft 25, a lower bearing 26, and a balance weight 30.
The casing 20 includes a substantially cylindrical cylinder member 20a that opens at the upper and lower ends thereof, and an upper cover 20b and a lower cover 20c that are provided at the upper end and the lower end of the cylinder member 20a, respectively. The cylinder member 20a is fixed to the upper cover 20b and the lower cover 20c by welding such that airtightness is kept. The casing 20 accommodates constituent devices of the compressor 11, including the scroll compression mechanism 21, the drive motor 24, the crankshaft 25, and the lower bearing 26. The oil reservoir 37 is formed between the lower end and a predetermined height inside the casing 20. The oil reservoir 37 has an oil reservoir space So for storing a refrigerating machine oil O for lubricating the scroll compression mechanism 21 and the like. The oil reservoir 37 is provided with the oil-temperature detection sensor 79 for detecting the temperature of the stored refrigerating machine oil. In the present embodiment, the oil-temperature detection sensor 79 is attached to the outer surface of the lower cover 20c to detect the temperature of the refrigerating machine oil stored in the oil reservoir 37. The suction pipe 4e through which the low-pressure gas refrigerant in the refrigeration cycle of the refrigerant circuit 10 is sucked and through which the gas refrigerant is supplied to the scroll compression mechanism 21 is provided at an upper portion of the casing 20 to extend through the upper cover 20b. The lower end of the suction pipe 4e is connected to a fixed scroll 22 of the scroll compression mechanism 21. The suction pipe 4e is in communication with a compression chamber Sc, which is described later, of the scroll compression mechanism 21. The discharge pipe 4d through which the refrigerant to be discharged to the outside of the casing 20 passes is provided at an intermediate portion of the cylinder member 20a of the casing 20. The discharge pipe 4d is disposed such that an end portion of the discharge pipe 4d inside the casing 20 projects in a high-pressure space Sh formed below a housing 27 of the scroll compression mechanism 21. The high-pressure refrigerant, which has been compressed by the scroll compression mechanism 21, in the refrigeration cycle flows through the discharge pipe 4d.
The scroll compression mechanism 21 includes, mainly, the housing 27, the fixed scroll 22 disposed above the housing 27, and a movable scroll 23 that forms the compression chamber Sc by being combined with the fixed scroll 22.
The fixed scroll 22 includes a flat fixed-side end plate 22a, a spiral fixed-side wrap 22b projecting from the front surface of the fixed-side end plate 22a, and an outer edge portion 22c that surrounds the fixed-side wrap 22b. In a central portion of the fixed-side end plate 22a, a non-circular discharge port 22d in communication with the compression chamber Sc of the scroll compression mechanism 21 is formed to extend through the fixed-side end plate 22a in the thickness direction. The refrigerant compressed in the compression chamber Sc is discharged through the discharge port 22d, passes through a refrigerant passage, which is not illustrated, formed in the fixed scroll 22 and the housing 27, and flows into the high-pressure space Sh. This compressor 11 is a high-pressure dome-type compressor in which the high-pressure refrigerant is present in a region on the outer side of the scroll compression mechanism 21 in the casing 20.
The movable scroll 23 includes a flat movable-side end plate 23a, a spiral movable-side wrap 23b projecting from the front surface of the movable-side end plate 23a, and a cylindrical boss 23c projecting from the back surface of the movable-side end plate 23a. The fixed-side wrap 22b of the fixed scroll 22 and the movable-side wrap 23b of the movable scroll 23 are combined with each other in a state in which the lower surface of the fixed-side end plate 22a and the upper surface of the movable-side end plate 23a face each other. The compression chamber Sc is formed between the fixed-side wrap 22b and the movable-side wrap 23b that are adjacent to each other. In response to the movable scroll 23 revolving with respect to the fixed scroll 22 as described later, the volume of the compression chamber Sc periodically changes, and suction, compression, and discharge of the refrigerant are performed in the scroll compression mechanism 21. The boss 23c is a cylindrical portion whose upper end is closed. An eccentric portion 25b, which is described later, of the crankshaft 25 is inserted into a hollow portion of the boss 23c, and the movable scroll 23 and the crankshaft 25 are thereby coupled to each other. The boss 23c is disposed in an eccentric-portion space 28 formed between the movable scroll 23 and the housing 27. The eccentric-portion space 28 is in communication with the high-pressure space Sh through an oil supply path 39, which is described later, of the crankshaft 25 and the like, and the eccentric-portion space 28 is subjected to a high pressure. The lower surface of the movable-side end plate 23a inside the eccentric-portion space 28 is pressed upward by this pressure toward the fixed scroll 22. This force causes the movable scroll 23 to be in close contact with the fixed scroll 22. The movable scroll 23 is supported by the housing 27 via an Oldham ring 29 disposed in an “Oldham ring space Sr”. The Oldham ring 29 is a member that prevents the movable scroll 23 from rotating on its axis and causes the movable scroll 23 to revolve. With the use of the Oldham ring 29, when the crankshaft 25 rotates, the movable scroll 23 coupled at the boss 23c to the crankshaft 25 revolves with respect to the fixed scroll 22 without rotating on its axis, and the refrigerant inside the compression chamber Sc is compressed.
The housing 27 is press-fitted to the inner side of the cylinder member 20a and fixed at the entirety of the outer circumferential surface thereof in the circumferential direction to the cylinder member 20a. The housing 27 and the fixed scroll 22 are fixed to each other by a bolt or the like, which is not illustrated, such that the upper end surface of the housing 27 is in close contact with the lower surface of the outer edge portion 22c of the fixed scroll 22. The housing 27 has a concave portion 27a disposed to be recessed at a central portion of the upper surface, and an upper bearing portion 27b disposed below the concave portion 27a. The concave portion 27a surrounds the side surface of the eccentric-portion space 28 in which the boss 23c of the movable scroll 23 is disposed. An upper bearing 35 that is a cylindrical metal member pivotably supporting a main shaft 25a of the crankshaft 25 is disposed at the upper bearing portion 27b. The upper bearing 35 rotatably supports the main shaft 25a inserted into the upper bearing 35. The Oldham ring space Sr in which the Oldham ring 29 is disposed is formed in the housing 27.
The drive motor 24 includes an annular stator 33 fixed to the inner wall surface of the cylinder member 20a, and, on the inner side of the stator 33, a rotor 32 that is rotatably accommodated with a slight gap (air gap passage) provided between the rotor 32 and the stator 33. The stator 33 is configured to include a coil. The rotor 32 is coupled to the movable scroll 23 via the crankshaft 25 disposed to extend along the axis of the cylinder member 20a in the up-down direction. The rotor 32 rotates and thereby causes the movable scroll 23 to revolve with respect to the fixed scroll 22.
The crankshaft 25 transmits the driving force of the drive motor 24 to the movable scroll 23. The crankshaft 25 is disposed along the axis of the cylinder member 20a to extend in the up-down direction and couples the rotor 32 of the drive motor 24 and the movable scroll 23 of the scroll compression mechanism 21 to each other. The crankshaft 25 includes the main shaft 25a whose center axis is coincident with the axis of the cylinder member 20a, and the eccentric portion 25b that is displaced with respect to the axis of the cylinder member 20a. As described above, the eccentric portion 25b is inserted into the boss 23c of the movable scroll 23. A pin bearing 31 that is a cylindrical metal member pivotably supporting the eccentric portion 25b is provided on the outer side of the eccentric portion 25b in the radial direction. The main shaft 25a is rotatably supported by the pin bearing 31, the upper bearing 35 of the upper bearing portion 27b of the housing 27, and the lower bearing 26, which is described later. The main shaft 25a is coupled between the upper bearing 35 and the lower bearing 26 to the rotor 32 of the drive motor 24. The oil supply path 39 for supplying the refrigerating machine oil O to the scroll compression mechanism 21 and the like is formed inside the crankshaft 25. The lower end of the main shaft 25a is located inside the oil reservoir space So of the oil reservoir 37 formed in a lower portion of the casing 20, and the refrigerating machine oil O in the oil reservoir space So is supplied to the scroll compression mechanism 21 and the like through the oil supply path 39.
The balance weight 30 is an annular member separated from the crankshaft 25 and is fitted to the main shaft 25a. The balance weight 30 includes a cylindrical portion 30a and an eccentric portion 30b formed at a portion of the cylindrical portion 30a in the circumferential direction. The center of gravity of the cylindrical portion 30a is present on the axis of the crankshaft 25, and the cylindrical portion 30a has a circular shape as viewed in the axial direction. The center of gravity of the eccentric portion 30b is displaced from the axis of the crankshaft 25, specifically, is displaced from the axis of the crankshaft 25 in a predetermined direction. Consequently, the center of gravity of the entirety of the balance weight 30 is also displaced from the axis of the crankshaft 25 in a predetermined direction. As described above, the movable scroll 23 is slidably supported at a portion thereof in the vicinity of the center by the eccentric portion 25b of the crankshaft 25. Consequently, the movable scroll 23 is also displaced in the same direction as the eccentric portion 25b. With the above structure, it is possible to ensure balance with the movable scroll 23 by disposing the balance weight 30 at the main shaft 25a with the predetermined direction directed opposite to the displaced direction of the eccentric portion 25b. It is thus possible to prevent deviation of the crankshaft 25.
The lower bearing 26 is disposed below the drive motor 24. The lower bearing 26 is fixed on the inner side and below the cylinder member 20a. The lower bearing 26 is a cylindrical metal member that constitutes a bearing on the lower end side of the crankshaft 25 and that supports the main shaft 25a of the crankshaft 25 rotatably.
Next, an operation of the compressor 11 will be described.
When the drive motor 24 is started, the rotor 32 rotates with respect to the stator 33, and the crankshaft 25 fixed to the rotor 32 rotates. When the crankshaft 25 rotates, the movable scroll 23 coupled to the crankshaft 25 revolves with respect to the fixed scroll 22. Then, the low-pressure gas refrigerant in the refrigeration cycle is sucked into the compression chamber Sc from the peripheral side of the compression chamber Sc through the suction pipe 4e. In response to the movable scroll 23 revolving, the suction pipe 4e and the compression chamber Sc become not in communication with each other. Then, in response to a decrease in the capacity of the compression chamber Sc, the pressure in the compression chamber Sc starts to increase.
The refrigerant inside the compression chamber Sc is compressed in response to the capacity of the compression chamber Sc decreasing and eventually becomes the high-pressure gas refrigerant. The high-pressure gas refrigerant is discharged through the discharge port 22d located near the center of the fixed-side end plate 22a. Thereafter, the high-pressure gas refrigerant passes through a refrigerant passage, which is not illustrated, formed in the fixed scroll 22 and the housing 27 and flows into the high-pressure space Sh. The high-pressure gas refrigerant in the refrigeration cycle that has flewed into the high-pressure space Sh and been compressed by the scroll compression mechanism 21 is discharged from the discharge pipe 4d.
As the expansion valve 9, for example, an electronic expansion valve, such as that illustrated in
This expansion valve 9 includes, mainly, a coil 91, a rotor 92, the valve body 93, a casing 94, a valve seat member 95, and the like.
The coil 91 is provided in the circumferential direction with the longitudinal direction of the valve body 93 being considered as the axial direction.
The rotor 92 is driven to rotate by the coil 91. The rotor 92 moves in a screw axis direction by rotating.
The valve body 93 is constituted by a shaft 93a and the needle 93b. The shaft 93a has a cylindrical shape and extends vertically. One end of the shaft 93a is attached to the rotor 92 to be coaxial with the rotor 92. The shaft 93a moves together with the rotor 92 in the axial direction. The needle 93b is provided at the lower end of the shaft 93a to have a conical shape directed downward. The needle 93b projects into a valve-body-side space 96, which is described later.
The coil 91, the rotor 92, the shaft 93a of the valve body 93, and the like are accommodated in the inside of the casing 94.
The valve seat member 95 is provided below the casing 94. The valve seat member 95 includes a first coupling portion 97, a second coupling portion 98, the valve-body-side space 96 for causing the first coupling portion 97 and the second coupling portion 98 to be in communication with each other, and a valve seat 99 provided between the valve-body-side space 96 and the first coupling portion 97. The valve seat 99 has a funnel shape to face the needle 93b of the valve body 93 from below on the outer side in the radial direction.
Thus, the high-pressure liquid refrigerant that has flowed in from the first coupling portion 97 or the second coupling portion 98 is decompressed by passing through a gap between the needle 93b and the valve seat 99. The degree of decompression at this time is adjusted by changing the size of the gap between the needle 93b and the valve seat 99 by moving the valve body 93 forward or rearward by the rotation of the rotor 92.
The valve body 93 having the aforementioned needle 93b can be made of, for example, SUS or brass. The valve body 93 made of SUS is, for example, a valve body constituted by stainless steel that is steel in which, as with SUS304 and the like, a chromium content is 10.5 mass % or more and a carbon content is 1.2 mass % or less. The valve body 93 made of brass is, for example, a valve body constituted by a copper alloy containing 20 mass % or more of zinc. Even when the valve body 93 including the needle 93b is made of such a material, decomposition of the refrigerant is suppressed and corrosion of the valve body 93 due to a decomposition product is suppressed in the air conditioning apparatus 1 in the present embodiment since the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, the refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 120° C. or lower.
The 1,2-difluoroethylene and other hydrofluoroolefin used as refrigerants are unstable and easily decompose. In contrast, instead of using a single refrigerant of 1,2-difluoroethylene or other hydrofluoroolefin, the present embodiment uses one of a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluorocarbon, a mixed refrigerant containing 1,2-difluoroethylene and one or more types of hydrofluoroolefin, or a mixed refrigerant containing one or more types of hydrofluorocarbon and one or more types of hydrofluoroolefin. Consequently, a disproportionation reaction of 1,2-difluoroethylene and other hydrofluoroolefin can be suppressed.
In addition, it has been found that 1,2-difluoroethylene and other hydrofluoroolefin each decompose easily in a high-temperature environment and each decompose easily, in particular, in a location where 1,2-difluoroethylene or other hydrofluoroolefin is present together with a refrigerating machine oil having a high temperature in the refrigerant circuit. Such decomposition of the refrigerant due to heat may generate a refrigerant deterioration product that generates an acid such as a hydrofluoric acid and may cause corrosion of the components of the refrigerant circuit.
Meanwhile, in the air conditioning apparatus 1 in the present embodiment, not only the refrigerating machine oil containing 3.0 wt % or more and 5.0 wt % or less of the acid scavenger with the pressure of air inside the refrigerant circuit 10 being 667 Pa or less, but also the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 120° C. or lower. Consequently, decomposition of the refrigerant present together with the refrigerating machine oil is sufficiently suppressed, generation of an acid such as hydrofluoric acid from a decomposition product is also suppressed, and corrosion of the components of the refrigerant circuit 10 is suppressed. In particular, it is possible in the present embodiment to increase the temperature of the refrigerating machine oil in the oil reservoir 37 to 120° C. and thus possible to widen an operable condition range.
In the aforementioned embodiment, the air conditioning apparatus 1 in which the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, the refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 120° C. or lower has been described as an example.
However, the air conditioning apparatus 1 is not limited thereto and may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 1333 Pa or less, the refrigerating machine oil contains no acid scavenger or contains less than 3.0 wt % of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 100° C. or lower or at 900° C. or lower. In this case, the refrigerating machine oil may contain 1.0 wt % or more and 2.5 wt % or less of the acid scavenger or 2.0 wt % of the acid scavenger.
Also in this case, as grasped on the basis of the test results in
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 2000 Pa or less, the refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 100° C. or lower.
Also in this case, as grasped from the test results in
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 2000 Pa or less, the refrigerating machine oil contains no acid scavenger or contains less than 3.0 wt % of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 80° C. or lower. In this case, the refrigerating machine oil may contain 1.0 wt % or more and 2.5 wt % or less of the acid scavenger.
Also in this case, as grasped on the basis of the test results in
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 4000 Pa or less, the refrigerating machine oil contains 3.0 wt % or more and 5.0 wt % or less of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 80° C. or lower.
Also in this case, as grasped on the basis of the test results in
In each of the aforementioned embodiment and the other embodiments, an example in which the temperature of the refrigerating machine oil stored in the oil reservoir 37 is controlled to be a predetermined upper limit value or less has been described.
However, for example, the predetermined upper limit temperature of the refrigerating machine oil stored in the oil reservoir 37 may be determined on the basis of the pressure of air inside the refrigerant circuit 10. Specifically, a temperature of the refrigerating machine oil grasped by substituting a value of the pressure of air inside the refrigerant circuit 10 into the following equation may be used as the upper limit temperature. The following equation is obtained on the basis of an experimental result showing a state of decomposition of the refrigerant in response to the temperature of the refrigerating machine oil and the pressure of air inside the refrigerant circuit 10.
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, the refrigerating machine oil contains 2.0 wt % or more of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 120° C. or lower.
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, the refrigerating machine oil contains 0.3 wt % or more of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 100° C. or lower.
The air conditioning apparatus 1 may be, for example, an air conditioning apparatus in which the pressure of air inside the refrigerant circuit 10 is 1333 Pa or less, the refrigerating machine oil contains 0.3 wt % or more of the acid scavenger, and the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at 80° C. or lower.
In the aforementioned embodiment, an example in which the components, such as the compressor 11, of the refrigerant circuit 10 are controlled on the basis of a temperature of the refrigerating machine oil detected by the oil-temperature detection sensor 79 has been described.
However, for example, a correlation between the number of rotations of the compressor 11 and the temperature of the refrigerating machine oil in the oil reservoir 37 is stored as data in a memory, and the number of the rotations may be controlled on the basis of the data such that the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at a predetermined value or lower.
Alternatively, for example, a correlation between a discharge temperature, which is the temperature of the refrigerant discharged from the compressor 11, and the temperature of the refrigerating machine oil in the oil reservoir 37 is stored as data in a memory, and the discharge temperature may be controlled on the basis of the data such that the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at a predetermined value or lower.
Further, for example, a correlation between a discharge pressure, which is the pressure of the refrigerant discharged from the compressor 11, and the temperature of the refrigerating machine oil in the oil reservoir 37 is stored as data in a memory, and the discharge pressure may be controlled on the basis of the data such that the temperature of the refrigerating machine oil in the oil reservoir 37 is maintained at a predetermined value or lower.
In the aforementioned embodiment, an example in which the air conditioning apparatus 1 including the refrigerant circuit 10 in which the compressor 11 of a high-pressure dome type is used has been described.
However, for example, the air conditioning apparatus 1 may include the refrigerant circuit 10 in which a compressor 11a of a low-pressure dome type is used. The refrigerant and the refrigerating machine oil to be used are the same as those in the aforementioned embodiment.
The air conditioning apparatus 1 according to the other embodiment J includes the refrigerant circuit 10 illustrated in
The refrigerant circuit 10 includes a first expansion valve 9a and a second expansion valve 9b, instead of the expansion valve 9 in the aforementioned embodiment, and is provided with an injection pipe 4f. The first expansion valve 9a is provided between the high-pressure receiver 8 and the outdoor heat exchanger 13. The second expansion valve 9b is provided between the high-pressure receiver 8 and the liquid-side shutoff valve 17. The injection pipe 4f connects the high-pressure receiver 8 and the compressor 11a to each other. Hereinafter, the compressor 11a will be described in detail.
The compressor 11a is a so-called low-pressure dome-type scroll compressor. As illustrated in
The casing 54 includes a substantially cylindrical cylinder member 54a, an upper cover 54b attached to the upper end of the cylinder member 54a, and a lower cover 54c attached to the lower end of the cylinder member 54a. The cylinder member 54a is fixed to the upper cover 54b and the lower cover 54c by welding such that airtightness is kept. The casing 54 accommodates components of the compressor 11a, including the compression mechanism 40, the floating member 47, the housing 52, the seal member 55, the motor 58, the crankshaft 59, and the lower bearing housing 62.
The compression mechanism 40 is installed in an upper portion of the casing 54. The floating member 47 and the housing 52 are installed below the compression mechanism 40. The motor 58 is installed below the housing 52. The lower bearing housing 62 is installed below the motor 58.
An oil reservoir 37a is formed in a bottom portion of the casing 54. The oil reservoir 37a has the oil reservoir space So that stores the refrigerating machine oil for lubricating the compression mechanism 40 and the like. The oil reservoir 37a is a portion of the casing 54 and corresponds to a portion below the lower bearing housing 62. For example, as illustrated in
The internal space of the casing 54 is partitioned into a first space S1 and a second space S2 by a first flow path 56. The first space S1 is a space on the lower side with respect to the first flow path 56. The second space S2 is a space on the upper side with respect to the first flow path 56. The first flow path 56 is fixed to the compression mechanism 40 and the casing 54 by welding such that airtightness is kept between the first space S1 and the second space S2.
The first flow path 56 is a plate-shaped member having an annular shape in plan view. The inner circumferential side of the first flow path 56 is fixed at the entire circumference to an upper portion of a fixed scroll 41 of the compression mechanism 40. The outer circumferential side of the first flow path 56 is fixed at the entire circumference to the inner surface of the casing 54.
The first space S1 is a space in which the motor 58 is installed. The first space S1 is a space into which the refrigerant before being compressed by the compressor 11a flows from the refrigerant circuit 10 including the compressor 11a. The first space S1 is a space into which the low-pressure refrigerant in the refrigeration cycle flows.
The second space S2 is a space into which the refrigerant discharged from the compression mechanism 40 (the refrigerant compressed by the compression mechanism 40) flows. The second space S2 is a space into which the high-pressure refrigerant in the refrigeration cycle flows.
The suction pipe 4e, the discharge pipe 4d, and the injection pipe 4f are attached to the casing 54 such that the inside and the outside of the casing 54 are in communication with each other.
The suction pipe 4e is attached to a portion near the center of the casing 54 in the up-down direction (vertical direction). Specifically, as illustrated in
The discharge pipe 4d is attached at a height position above the first flow path 56 to an upper portion of the casing 54. Specifically, as illustrated in
The refrigerant (the high-pressure refrigerant in the refrigeration cycle) that has been compressed by the compression mechanism 40 and has flowed into the second space S2 flows out to the outside of the compressor 11a through the discharge pipe 4d.
The injection pipe 4f is attached at a height position below the first flow path 56 to an upper portion of the casing 54. Specifically, as illustrated in
The compression mechanism 40 includes, mainly, the fixed scroll 41 and a movable scroll 42. The fixed scroll 41 and the movable scroll 42 are combined with each other and form the compression chamber Sc. The compression mechanism 40 compresses the refrigerant in the compression chamber Sc and discharges the compressed refrigerant.
As illustrated in
The fixed scroll 41 includes a disk-shaped fixed-side end plate 41a, a spiral-shaped fixed-side wrap 41b, and a peripheral portion 41c. The fixed-side wrap 41b and the peripheral portion 41c extend from the front surface (lower surface) of the fixed-side end plate 41a toward the movable scroll 42 (downward). In a bottom view of the fixed scroll 41, the fixed-side wrap 41b is formed in a spiral shape (involute shape) extending from a portion near the center of the fixed-side end plate 41a toward the outer circumferential side. The peripheral portion 41c has a cylindrical shape. The peripheral portion 41c is located on the outer circumferential side of the fixed-side end plate 41a so as to surround the fixed-side wrap 41b.
During the operation of the compressor 11a, the movable scroll 42 turns with respect to the fixed scroll 41, thereby causing the refrigerant (the low-pressure refrigerant in the refrigeration cycle) that has flowed from the first space S1 into the compression chamber Sc on the peripheral side to be compressed as the refrigerant moves toward the compression chamber Sc on the innermost side (center side). A discharge port 41d through which the refrigerant compressed in the compression chamber Sc is to be discharged is formed near the center of the fixed-side end plate 41a to extend through the fixed-side end plate 41a in the thickness direction (up-down direction) of the fixed-side end plate 41a. The discharge port 41d is in communication with the compression chamber Sc on the innermost side. A discharge valve 43 that opens and closes the discharge port 41d is mounted above the fixed-side end plate 41a. When the pressure in the compression chamber Sc that is on the innermost side and that is in communication with the discharge port 41d increases to be higher than the pressure in the space (second space S2) above the discharge valve 43 by a predetermined value or more, the discharge valve 43 opens to allow the refrigerant to flow into the second spaces S2 through the discharge port 41d.
On the outer circumferential side of the discharge port 41d of the fixed-side end plate 41a, a relief hole 41e is formed to extend through the fixed-side end plate 41a in the thickness direction of the fixed-side end plate 41a. The relief hole 41e is in communication with the compression chamber Sc formed on the outer circumferential side with respect to the compression chamber Sc that is on the innermost side and that is in communication with the discharge port 41d. The relief hole 41e is in communication with the compression chamber Sc in the middle of compression of the compression mechanism 40. A plurality of the relief holes 41e may be formed in the fixed-side end plate 41a. A relief valve 44 that opens and closes the relief hole 41e is mounted above the fixed-side end plate 41a. When the pressure in the compression chamber Sc in communication with the relief hole 41e increases to be higher than the pressure in the space (second space S2) above the relief valve 44 by a predetermined value or more, the relief valve 44, which is a safety valve, opens to allow the refrigerant to flow into the second space S2 through the relief hole 41e.
The movable scroll 42 includes a disk-shaped movable-side end plate 42a, a spiral-shaped movable-side wrap 42b, and a cylindrical boss portion 42c. The movable-side wrap 42b extends from the front surface (upper surface) of the movable-side end plate 42a toward the fixed scroll 41 (upward). The boss portion 42c extends from the back surface (lower surface) of the movable-side end plate 42a toward the motor 58 (downward). In a top view of the movable scroll 42, the movable-side wrap 42b is formed in a spiral shape (involute shape) extending from a portion near the center of the movable-side end plate 42a toward the outer circumferential side.
The fixed-side wrap 41b of the fixed scroll 41 and the movable-side wrap 42b of the movable scroll 42 are combined with each other and form the compression chamber Sc. The fixed scroll 41 and the movable scroll 42 are combined with each other such that the front surface (lower surface) of the fixed-side end plate 41a and the front surface (upper surface) of the movable-side end plate 42a face each other. Consequently, the compression chamber Sc surrounded by the fixed-side end plate 41a, the fixed-side wrap 41b, the movable-side wrap 42b, and the movable-side end plate 42a is formed.
The compression mechanism 40 has a symmetrical wrap structure or an asymmetrical wrap structure. In the compression mechanism 40 having the symmetrical wrap structure, a first compression chamber surrounded by the outer circumferential surface of the movable-side wrap 42b and the inner circumferential surface of the fixed-side wrap 41b, and a second compression chamber surrounded by the inner circumferential surface of the movable-side wrap 42b and the outer circumferential surface of the fixed-side wrap 41b are formed to be point-symmetrical when viewed in the vertical direction. In the compression mechanism 40 having the asymmetrical wrap structure, the first compression chamber and the second compression chamber are not formed to be point-symmetrical when viewed in the vertical direction.
The movable-side end plate 42a is disposed above the floating member 47. During the operation of the compressor 11a, the floating member 47 is pressed toward the movable scroll 42 by the pressure of a back pressure space Sb formed below the floating member 47. Consequently, when a pressing portion 50 at an upper portion of the floating member 47 comes into contact with the back surface (lower surface) of the movable-side end plate 42a, the floating member 47 presses the movable scroll 42 toward the fixed scroll 41. The movable scroll 42 is brought into close contact with the fixed scroll 41 by the force of the floating member 47 pressing the movable scroll 42 toward the fixed scroll 41. Consequently, leakage of the refrigerant through a gap between the tip (distal end surface) of the fixed-side wrap 41b and the bottom surface (the main surface in contact with the tip) of the movable-side end plate 42a and a gap between the tip of the movable-side wrap 42b and the bottom surface of the fixed-side end plate 41a is suppressed.
The back pressure space Sb is a space formed between the floating member 47 and the housing 52. As illustrated in
An Oldham coupling 45 is disposed between the movable scroll 42 and the floating member 47. The Oldham coupling 45 is slidably engaged with both the movable scroll 42 and the floating member 47. The Oldham coupling 45 causes the movable scroll 42 to turn with respect to the fixed scroll 41 while suppressing rotation of the movable scroll 42 on its axis.
The boss portion 42c is disposed in an eccentric-portion space 51 surrounded by the inner surface of the floating member 47. A first bearing metal 46 is disposed inside the boss portion 42c. The first bearing metal 46 is, for example, press-fitted to the inside of the boss portion 42c and fixed. An eccentric portion 60 of the crankshaft 59 is inserted into the first bearing metal 46. As a result of the eccentric portion 60 being inserted into the first bearing metal 46, the movable scroll 42 and the crankshaft 59 are coupled to each other.
The floating member 47 is disposed on the back surface side (the side opposite to the side where the fixed scroll 41 is disposed) of the movable scroll 42. The floating member 47 is pressed toward the movable scroll 42 by the pressure of the back pressure space Sb and thereby presses the movable scroll 42 toward the fixed scroll 41. A portion of the floating member 47 also functions as a bearing that supports the crankshaft 59.
The floating member 47 includes, mainly, a cylindrical body portion 47a, the pressing portion 50, and an upper bearing housing 48.
The body portion 47a forms the eccentric-portion space 51 surrounded by the inner surface of the body portion 47a. The boss portion 42c of the movable scroll 42 is disposed in the eccentric-portion space 51.
The pressing portion 50 is a cylindrical member extending from the upper end of the body portion 47a toward the movable scroll 42. As illustrated in
The upper bearing housing 48 is a cylindrical member disposed below (below the eccentric-portion space 51) the body portion 47a. A second bearing metal 49 is disposed inside the upper bearing housing 48. The second bearing metal 49 is, for example, press-fitted to the inside of the upper bearing housing 48 and fixed. The second bearing metal 49 rotatably supports a main shaft 61 of the crankshaft 59.
The housing 52 is a substantially cylindrical member disposed below the fixed scroll 41 and the floating member 47. The housing 52 supports the floating member 47. The back pressure space Sb is formed between the housing 52 and the floating member 47. The housing 52 is, for example, attached to the inner surface of the casing 54 by press fitting.
The seal member 55 is a member for forming the back pressure space Sb between the floating member 47 and the housing 52. The seal member 55 is, for example, a gasket, such as an O-ring. As illustrated in
The first chamber B1 is in communication through the first flow path 56 with the compression chamber Sc in the middle of compression. The first flow path 56 is a flow path that guides the refrigerant (the intermediate-pressure refrigerant) in the middle of compression in the compression mechanism 40 to the first chamber B1. The first flow path 56 is formed in the fixed scroll 41 and the housing 52.
The second chamber B2 is in communication through a second flow path 57 with the discharge port 41d of the fixed scroll 41. The second flow path 57 is a flow path that guides the refrigerant (the high-pressure refrigerant) discharged from the compression mechanism 40 to the second chamber B2. The second flow path 57 is formed in the fixed scroll 41 and the housing 52.
During the operation of the compressor 11a, the pressure in the second chamber B2 is higher than the pressure in the first chamber B1. However, the force with which the movable scroll 42 is pressed toward the fixed scroll 41 by the pressure of the back pressure space Sb is not easily increased to be excessive, since the area of the first chamber B1 is larger than the area of the second chamber B2 in plan view. With the second chamber B2 being disposed on the inner side with respect to the first chamber B1, the force with which the movable scroll 42 is pressed downward by the pressure of the compression chamber Sc and the force with which the movable scroll 42 is pressed upward by the floating member 47 are easily balanced.
The motor 58 drives the movable scroll 42. The motor 58 includes a stator 58a and a rotor 58b. The stator 58a is an annular member fixed to the inner surface of the casing 54. The rotor 58b is a cylindrical member disposed on the inner side of the stator 58a. A slight gap (air gap) is formed between the inner circumferential surface of the stator 58a and the outer circumferential surface of the rotor 58b.
The crankshaft 59 extends through the rotor 58b in the axial direction of the rotor 58b. The rotor 58b is coupled to the movable scroll 42 via the crankshaft 59. The motor 58 drives the movable scroll 42 by rotation of the rotor 58b and turns the movable scroll 42 with respect to the fixed scroll 41.
The crankshaft 59 couples the rotor 58b of the motor 58 and the movable scroll 42 of the compression mechanism 40 to each other. The crankshaft 59 extends in the up-down direction. The crankshaft 59 transmits the driving force of the motor 58 to the movable scroll 42.
The crankshaft 59 includes, mainly, the eccentric portion 60 and the main shaft 61.
The eccentric portion 60 is disposed above the main shaft 61. The center axis of the eccentric portion 60 is displaced with respect to the center axis of the main shaft 61. The eccentric portion 60 is coupled to the first bearing metal 46 disposed inside the boss portion 42c of the movable scroll 42.
The main shaft 61 is rotatably supported by the second bearing metal 49 disposed in the upper bearing housing 48 of the floating member 47 and by a third bearing metal 63 disposed in the lower bearing housing 62. The main shaft 61 is coupled, between the upper bearing housing 48 and the lower bearing housing 62, to the rotor 58b of the motor 58. The main shaft 61 extends in the up-down direction.
An oil passage (not illustrated) is formed inside the crankshaft 59. The oil passage has a main path and a branch path. The main path extends from the lower end to the upper end of the crankshaft 59 in the axial direction of the crankshaft 59. The branch path extends from the main path in the radial direction of the crankshaft 59. The refrigerating machine oil in the oil reservoir 37a is pumped up by a pump (not illustrated) provided at the lower end of the crankshaft 59 and is supplied through the oil path to sliding portions between the crankshaft 59 and each of the first bearing metal 46, the second bearing metal 49, and the third bearing metal 63 and sliding portions and the like of the compression mechanism 40.
The lower bearing housing 62 is fixed to the inner surface of the casing 54. The lower bearing housing 62 is disposed below the motor 58. The third bearing metal 63 is disposed inside the lower bearing housing 62. The third bearing metal 63 is, for example, press-fitted to the inside of the lower bearing housing 62 and fixed. The main shaft 61 of the crankshaft 59 passes through the third bearing metal 63. The third bearing metal 63 rotatably supports a lower portion side of the main shaft 61 of the crankshaft 59.
Hereinafter, an operation of the compressor 11a in a normal state will be described. The normal state is a state in which the pressure of the refrigerant discharged through the discharge port 41d of the compression mechanism 40 is higher than the pressure in the compression chamber Sc in the middle of compression.
When the motor 58 is driven, the rotor 58b rotates, and the crankshaft 59 coupled to the rotor 58b also rotates. When the crankshaft 59 rotates, the Oldham coupling 45 causes the movable scroll 42 to turn, without rotating on its axis, with respect to the fixed scroll 41. The low-pressure refrigerant that has flowed into the first space S1 from the suction pipe 4e passes through a refrigerant passage (not illustrated) formed in the housing 52 and is sucked into the compression chamber Sc on the peripheral side of the compression mechanism 40. When the movable scroll 42 turns, the first space S1 and the compression chamber Sc are caused to be not in communication with each other, the capacity of the compression chamber Sc decreases, and the pressure in the compression chamber Sc increases. The intermediate-pressure refrigerant is injected from the injection pipe 4f into the compression chamber Sc in the middle of compression. The pressure of the refrigerant increases as the refrigerant moves from the compression chamber Sc on the peripheral side (outer side) toward the compression chamber Sc on the center side (inner side), and the pressure of the refrigerant becomes a high pressure in the refrigeration cycle eventually. The refrigerant compressed by the compression mechanism 40 is discharged through the discharge port 41d of the fixed-side end plate 41a into the second space S2. The high-pressure refrigerant in the second space S2 is discharged from the discharge pipe 4d.
In the compressor 11a described above, the refrigerating machine oil stored in the oil reservoir 37a is positioned on the low-pressure side with respect to the compression mechanism 40 and is subjected to a low pressure. Therefore, it is easy to suppress an increase in the temperature of the refrigerating machine oil, compared with a case where the refrigerating machine oil is subjected to the high-pressure refrigerant as in the high-pressure dome-type compressor 11 in the aforementioned embodiment.
As shown in
For example, the air conditioning apparatus 1 using the low-pressure dome-type compressor 11a may be configured such that the pressure of air inside the refrigerant circuit 10 is 667 Pa or less, 3.0 wt % or more and 5.0 wt % or less of the acid scavenger is blended in the refrigerating machine oil, and the temperature of the refrigerating machine oil in the oil reservoir 37a is maintained at 140° C. or lower. Furthermore the air conditioning apparatus 1 using the low-pressure dome-type compressor 11a may be configured such that the pressure of air inside the refrigerant circuit 10 is 1333 Pa or less, 3.0 wt % or more and 5.0 wt % or less of the acid scavenger is blended in the refrigerating machine oil, and the temperature of the refrigerating machine oil in the oil reservoir 37a is maintained at 140° C. or lower. Furthermore, the air conditioning apparatus 1 using the low-pressure dome-type compressor 11a may be configured such that the pressure of air inside the refrigerant circuit 10 is 2000 Pa or less, 3.0 wt % or more and 5.0 wt % or less of the acid scavenger is blended in the refrigerating machine oil, and the temperature of the refrigerating machine oil in the oil reservoir 37a is maintained at 135° C. or lower.
The content ratio of the acid scavenger in the refrigerating machine oil is a ratio when the refrigerating machine oil is considered 100 parts by weight.
The refrigeration cycle apparatus may include a control unit including a processor or the like that grasps a result of detection by the temperature detection unit and controls the number of rotations of the compressor on the basis of the result of the detection.
While embodiments of the present disclosure have been described above, it should be understood that various changes in the forms and details are possible without departing from the gist and the scope of the present disclosure described in the claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2021-202400 | Dec 2021 | JP | national |
The present application claims priority to PCT/JP2022/045214 filed Dec. 8, 2022, and JP 2021-202400 filed Dec. 14, 2021, both of which are incorporated herein by reference.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/JP2022/045214 | Dec 2022 | WO |
| Child | 18741836 | US |
