WO2006095572A1 - Systeme de refrigeration a cycles - Google Patents

Systeme de refrigeration a cycles Download PDF

Info

Publication number
WO2006095572A1
WO2006095572A1 PCT/JP2006/303228 JP2006303228W WO2006095572A1 WO 2006095572 A1 WO2006095572 A1 WO 2006095572A1 JP 2006303228 W JP2006303228 W JP 2006303228W WO 2006095572 A1 WO2006095572 A1 WO 2006095572A1
Authority
WO
WIPO (PCT)
Prior art keywords
expander
compressor
refrigerant
oil
lubricating oil
Prior art date
Application number
PCT/JP2006/303228
Other languages
English (en)
Japanese (ja)
Inventor
Tomoichiro Tamura
Hiroshi Hasegawa
Masaru Matsui
Atsuo Okaichi
Takeshi Ogata
Original Assignee
Matsushita Electric Industrial Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2005065239A external-priority patent/JP2008133968A/ja
Priority claimed from JP2005065238A external-priority patent/JP2008133967A/ja
Application filed by Matsushita Electric Industrial Co., Ltd. filed Critical Matsushita Electric Industrial Co., Ltd.
Publication of WO2006095572A1 publication Critical patent/WO2006095572A1/fr

Links

Classifications

    • 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
    • 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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2102—Temperatures at the outlet of the gas cooler
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a compressor and an expander.
  • V a so-called vapor compression refrigeration cycle apparatus
  • An apparatus having an expander instead of an expansion valve is known.
  • the expansion energy in the process of expansion of the refrigerant can be recovered in the form of electric power or power, and the efficiency of the cycle can be improved by the amount of the recovered energy. it can.
  • a refrigeration cycle apparatus equipped with an expander, lubricating oil is also required for an expander that is not only a compressor. Therefore, a refrigeration cycle apparatus has been proposed in which an oil separator is provided on the refrigerant circuit and the lubricating oil separated by the oil separator is supplied to the expander.
  • Japanese Patent Application Laid-Open No. 2001-141315 discloses an oil separator provided between a compressor and a radiator, and an oil feed pipe connecting the oil separator and an inlet side pipe of the expander.
  • a refrigerating air conditioner provided is disclosed.
  • the refrigeration air conditioner disclosed in the above document aims to prevent a decrease in refrigeration capacity, and therefore there is a dedicated cooling source (for example, cooling water) for the cooler of the oil feed pipe. It was essential.
  • a dedicated cooling source for example, cooling water
  • the heat dissipation from the lubricating oil results in energy loss, which reduces the heating efficiency or heating efficiency of the entire cycle, in other words, the COP (coefficient of performa on the heating side of the cycle. nce).
  • the present invention has been made in view of the strong point, and an object of the present invention is to achieve both sufficient supply of lubricating oil to the expander and improvement of COP as a whole cycle. It is in.
  • the present invention provides a refrigerant circuit in which a compressor, a radiator, an expander, and an evaporator are connected in this order,
  • An oil supply passage provided separately from the refrigerant circuit for supplying the lubricating oil in the compressor or the lubricating oil discharged from the compressor between the radiator and the expander in the expander or the refrigerant circuit;
  • Expanding power in refrigerant circuit Provided is a refrigeration cycle apparatus comprising: a cooling device that cools lubricating oil by heat-exchanging refrigerant in a low-pressure portion that reaches the compressor through the evaporator and lubricating oil in the oil supply passage. To do.
  • the refrigeration cycle apparatus of the present invention since the lubricating oil can be transported from the compressor side to the expander side through the oil supply passage, a sufficient amount of lubricating oil can be supplied to the expander. . Further, since the lubricating oil in the oil supply passage is cooled by the refrigerant in the low-pressure part of the refrigerant circuit (hereinafter referred to as low-pressure refrigerant), no special cooling source is required. In addition, the heat release from the lubricant can be recovered, so the COP of the entire cycle can be improved. Therefore, it is possible to achieve both a sufficient supply of lubricating oil to the expander and an improvement in the COP of the entire cycle.
  • the oil supply passage may communicate the compressor and the expander.
  • the compressor and the expander each include a storage unit that stores lubricating oil
  • the storage unit of the compressor and the storage unit of the expander can be communicated with each other through the oil supply passage.
  • the compressor includes a compression mechanism that compresses the refrigerant, and a refrigerant that covers the compression mechanism and is compressed by the compression mechanism. It has a compressor shell that forms the space to be discharged, and the expander covers the expansion mechanism that expands the refrigerant and the expansion mechanism! And an expander shell that forms a space in which the refrigerant before being decompressed by the expansion mechanism is stored, and the compressor and the expander reservoir are provided inside the compressor shell and the expander shell, respectively.
  • the oil supply passage is at one end Is preferably connected to the compressor shell and the other end is connected to the expander shell.
  • an oil separator may be disposed between the compressor and the radiator in the refrigerant circuit.
  • the lubricating oil separated by the oil separator can be supplied between the radiator and the expander in the expander or refrigerant circuit through the oil supply passage.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a first embodiment.
  • FIG. 2 is a longitudinal sectional view of the compressor.
  • FIG. 3 is a longitudinal sectional view of the expander.
  • FIG. 4 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a second embodiment.
  • FIG. 5 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a third embodiment.
  • FIG. 6 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a fourth embodiment.
  • FIG. 7 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a fifth embodiment.
  • FIG. 8 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a sixth embodiment.
  • FIG. 9 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a seventh embodiment.
  • FIG. 10 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to an eighth embodiment.
  • FIG. 11 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a ninth embodiment.
  • the refrigeration cycle apparatus 10A includes a refrigerant circuit 11 in which a compressor radiator 2, an expander 3, and an evaporator 5 are connected in this order.
  • the refrigeration cycle apparatus 10A includes an oil supply pipe 7 (oil supply passage) that communicates the compressor 1 and the expander 3.
  • the oil supply pipe 7 also has a piping force provided separately from the refrigerant circuit 11, and this oil supply pipe 7 is provided with a cooler 6 (cooling device) and a valve 8 (flow rate adjusting device)! / ⁇
  • the valve 8 is a valve whose opening can be adjusted.
  • the refrigerant charged in the refrigerant circuit 11 is a refrigerant that is in a supercritical state in a high-pressure portion (portion from the compressor 1 through the radiator 2 to the expander 3) during operation.
  • Refrigerant of this embodiment The circuit 11 is filled with carbon dioxide (CO 2) as such a refrigerant.
  • CO 2 carbon dioxide
  • the type of the medium is not particularly limited.
  • the compressor 1 is a rotary compressor.
  • the compressor 1 is not limited to the rotary type, and may be another type of compressor (for example, a scroll compressor).
  • the compressor 1 includes a sealed container 21 constituting a compressor shell, an electric motor 24 and a compression mechanism 25 accommodated in the sealed container 21.
  • the compressor 1 is a so-called high-pressure dome type compressor, and a high-pressure side refrigerant (hereinafter simply referred to as a high-pressure refrigerant) of the refrigerant circuit 11 is stored in an internal space formed by the sealed container 21.
  • the sealed container 21 is a so-called vertically long container whose vertical length is longer than the horizontal length.
  • a terminal 43 to which a power cable or the like is connected is fixed to the upper wall of the sealed container 21.
  • a discharge pipe 31 is connected to the upper wall of the sealed container 21.
  • a suction pipe 32 is connected to the side wall of the sealed container 21, and an oil supply pipe 7 is connected to the bottom of the side wall of the sealed container 21.
  • the electric motor 24 includes a stator 22 fixed to the inner wall of the hermetic container 21 and a rotor 23 arranged inside the stator 22. On the outer peripheral side of the stator 22, a plurality of notches 41 serving as refrigerant flow paths are formed. A gap 42 is provided between the stator 22 and the rotor 23.
  • a shaft 26 is fixed to the center portion of the rotor 23.
  • the shaft 26 extends below the rotor 23.
  • an eccentric portion 26a in which the axial center L force of the shaft 26 is also offset is provided in the lower part of the shaft 26.
  • the upper part of the shaft 26 above the eccentric part 26 a is supported by the upper bearing member 27, and the lower part of the eccentric part 26 a is supported by the lower bearing member 28.
  • a cylinder 30 is disposed between the upper bearing member 27 and the lower bearing member 28.
  • An annular roller 29 is accommodated in the cylinder 30, and an eccentric portion 26 a is accommodated in the roller 29.
  • a vane 33 that contacts the roller 29 and a spring 34 that urges the vane 33 toward the roller 29 are provided.
  • the upper bearing member 27 includes a suction hole 35 for guiding the refrigerant from the suction pipe 32 into the cylinder 30, and A discharge hole 36 for discharging the refrigerant compressed in the cylinder 30 of the compression mechanism 25 into the internal space of the sealed container 21 is formed.
  • the bottom of the sealed container 21 forms an oil reservoir 37 (storage part) for storing lubricating oil.
  • the oil supply pipe 7 opens toward the oil reservoir 37. Force not shown
  • the oil pump 38 for pumping up the lubricating oil in the oil reservoir 37 is provided at the lower end of the shaft 26.
  • An oil supply hole (not shown) for supplying the lubricating oil pumped up by the oil pump 38 to the sliding portion is formed inside the shaft 26.
  • the expander 3 is a two-stage rotary expander that expands the refrigerant in two stages.
  • the type of the expander 3 is not limited at all.
  • the expander 3 may be a single-stage rotary expander or another type of expander (for example, a scroll expander).
  • the expander 3 includes a sealed container 51 constituting an expander shell, a generator 52 accommodated in the sealed container 51, and an expansion mechanism 55. That is, the expander 3 is an expander with a built-in generator 52.
  • the expander 3 is a so-called high-pressure dome type expander, and high-pressure refrigerant is stored in the internal space formed by the sealed container 51.
  • the sealed container 51 is a vertically long container, similar to the sealed container 21 of the compressor 1. However, the shape and dimensions of the sealed container 51 are not limited at all.
  • a terminal 56 to which an electrical cable (not shown) is connected is fixed to the upper wall of the sealed container 51.
  • An inlet side pipe 57 is connected to the upper wall of the sealed container 51.
  • An outlet side pipe 58 is connected to the side wall of the sealed container 51, and an oil supply pipe 7 is connected to the bottom of the side wall of the sealed container 51.
  • the generator 52 includes a stator 53 that is fixed to the inner wall of the hermetic container 51, and a rotor 54 that is disposed inside the stator 53.
  • a shaft 59 is fixed to the center of the rotor 54. The shaft 59 extends upward and downward from the rotor 54, respectively.
  • a first eccentric portion 61 and a second eccentric portion 62 in which the axial force of the shaft 59 is also biased are provided on the upper side of the shaft 59.
  • the lower portion of the first eccentric portion 61 of the shaft 59 is supported by the lower bearing member 65 via the bearing 63.
  • a first cylinder 66 is provided on the lower bearing member 65.
  • a first roller 71 is accommodated in the first cylinder 66, and the inside of the first roller 71
  • the first eccentric portion 61 is arranged in the first.
  • An intermediate plate 67 is provided above the first cylinder 66, and a second cylinder 68 is disposed on the intermediate plate 67.
  • a second roller 72 is accommodated in the second cylinder 68, and a second eccentric portion 62 is disposed in the second roller 72.
  • An upper bearing member 69 is provided on the second roller 72.
  • the upper end portion of the shaft 59 is supported by the upper bearing member 69 via the bearing 64.
  • a block 70 is provided on the upper bearing member 69.
  • the lower bearing member 65 is formed with a suction hole 73 that communicates the internal space of the sealed container 51 with the inside of the first cylinder 66.
  • the intermediate plate 67 is formed with a communication hole 74 that communicates the inside of the first cylinder 66 and the inside of the second cylinder 68.
  • the upper bearing member 69 has a discharge hole 75 connected to the second cylinder 68.
  • the block 70 has a discharge hole 76 that communicates the discharge hole 75 and the outlet side pipe 58.
  • the bottom of the sealed container 51 forms an oil reservoir 77 for storing lubricating oil.
  • the oil supply pipe 7 opens toward the oil reservoir 77 by force.
  • an oil pump 78 for pumping up lubricating oil is also provided at the lower end of the shaft 59 of the expander 3.
  • an oil supply hole (not shown) for supplying the lubricating oil pumped up by the oil pump 78 to the sliding portion is formed inside the shaft 59! Speak.
  • the compressor 1 may have a configuration in which the electric motor 24 is externally attached by extending one end of the force shaft 26 configured to incorporate the electric motor 24 to the outside of the sealed container 21.
  • the expander 3 has a configuration in which the generator 52 is incorporated, but the configuration in which the generator 52 is externally attached by extending one end of the shaft 59 to the outside of the sealed container 51 may be used. Good
  • the configurations of the radiator 2 and the evaporator 5 are not limited at all.
  • the radiator 2 or the evaporator 5 for example, air-cooled or water-cooled heat exchange may be used.
  • the cooler 6 cools the lubricating oil in the oil supply pipe 7 with the low-pressure refrigerant in the refrigerant circuit 11.
  • the cooler 6 of the present embodiment is provided between the expander 3 and the evaporator 5.
  • the cooler 6 is configured by so-called liquid-liquid heat exchange that directly exchanges heat between the lubricating oil and the low-pressure refrigerant.
  • the specific form of the cooler 6 is not limited at all. A heavy tube heat exchanger, a plate heat exchanger, a shell and tube heat exchanger, and the like can be suitably used.
  • the oil supply pipe 7 and the pipe forming the refrigerant circuit 11 are arranged in parallel and brought into contact with each other, and further joined in that state (for example, brazed), thereby cooling. It is also possible to configure vessel 6.
  • the coolant may flow through the inner flow path and the lubricating oil may flow through the outer flow path. .
  • This can suppress an increase in pressure loss of the low-pressure refrigerant.
  • the cooler 6 is preferably a so-called counter-flow type heat exchanger that allows the refrigerant and the lubricating oil to flow in a facing state.
  • the overall refrigeration cycle apparatus 10 can reduce the number of parts and save energy.
  • the refrigerant discharged from the expander 3 is preliminarily heated before the evaporator 5. Therefore, the amount of heat exchange required for the evaporator 5 can be reduced, and the evaporator 5 can be made compact. Further, the low pressure side pressure that is the pressure in the low pressure portion of the refrigerant circuit 11 can be increased, and the load on the compressor 1 can be reduced. Therefore, COP can be improved.
  • the inlet side pipe 57 of the expander 3 is provided with a temperature sensor 81 for detecting the refrigerant temperature.
  • the temperature sensor 81 may be any sensor that substantially detects the refrigerant temperature. Therefore, the temperature sensor 81 detects the refrigerant temperature indirectly, for example, by detecting the wall surface temperature of the inlet side pipe 57, which may directly detect the refrigerant temperature in the inlet side pipe 57. There may be. Further, the temperature sensor 81 may be provided in the expander 3 itself (that is, in the sealed container 51) as long as it can detect the inlet refrigerant temperature that is the refrigerant temperature on the inlet side of the expander 3. .
  • the refrigeration cycle apparatus 10A is provided with a controller 80.
  • the controller 80 receives the detection signal from the temperature sensor 81 and controls the opening degree of the valve 8. It should be noted that the controller 80 is not necessarily a dedicated controller provided for the control of the valve 8. Of course, you can control it.
  • the temperature sensor 81 is arranged on the expander 3 side in view of the merging point force between the inlet side pipe 57 and the oil supply pipe 7 of the expander 3. In this way, it is possible to accurately measure the temperature of the refrigerant immediately before being sucked into the expander 3.
  • the refrigerant discharged from the compressor 1 dissipates heat in the radiator 2, expands in the expander 3, evaporates in the evaporator 5, and then sucked into the compressor 1.
  • the electric motor 24 is driven, and the roller 29 rotates in the cylinder 30 as the shaft 26 rotates.
  • the refrigerant is sucked into the cylinder 30 of the compression mechanism 25 from the suction pipe 32, and the refrigerant is compressed in the cylinder 30.
  • the compressed high-pressure refrigerant is discharged into the space in the sealed container 21 through the discharge hole 36 and then discharged from the discharge pipe 31.
  • the high-pressure refrigerant is sucked into the sealed container 51 through the inlet side pipe 57.
  • the high-pressure refrigerant flows into the first cylinder 66 through the suction hole 73 and expands in the first cylinder 66.
  • the first roller 71 is rotated by the expansion force of the refrigerant.
  • the refrigerant expanded in the first cylinder 66 flows into the second cylinder 68 through the communication hole 74 and further expands in the second cylinder 68.
  • the second roller 72 is rotated by the expansion force of the refrigerant.
  • the low-pressure refrigerant expanded in the second cylinder 68 is discharged from the outlet side pipe 58 through the discharge hole 75 and the discharge hole 76.
  • the internal pressure of the sealed container 21 of the compressor 1 is higher than the internal pressure of the sealed container 51 of the expander 3. Therefore, due to the internal pressure difference between the compressor 1 and the expander 3, the lubricating oil in the oil reservoir 37 of the compressor 1 flows into the oil reservoir 77 of the expander 3 through the oil supply pipe 7. At this time, the lubricating oil flowing through the oil supply pipe 7 is cooled in the cooler 6. In addition, by adjusting the opening of the valve 8 of the oil supply pipe 7, the oil supply pipe 7 The flow rate, that is, the amount of lubricating oil flowing into the expander 3 can be adjusted.
  • the controller 80 controls the opening degree of the valve 8 based on the inlet refrigerant temperature of the expander 3. For example, the controller 80 may adjust the inflow amount of the lubricating oil so that the internal temperature of the expander 3 does not increase or decrease too much. In the present embodiment, the controller 80 controls the opening degree of the valve 8 so that the inlet refrigerant temperature of the expander 3 becomes a predetermined value. For example, the controller 80 decreases the opening degree of the valve 8 when the inlet refrigerant temperature of the expander 3 is equal to or higher than a predetermined value, and increases the opening degree of the valve 8 when the inlet refrigerant temperature is lower than the predetermined value.
  • the oil supply pipe 7 that communicates the compressor 1 and the expander 3 is provided, and the lubricating oil in the compressor 1 is supplied to the expander 3 through the oil supply pipe 7. Since it is supplied, it is not necessary to install an oil separator in the refrigerant circuit 11 separately. Therefore, the number of parts can be reduced and the cost can be reduced as much as the oil separator is unnecessary. Further, since the cooler 6 is provided in the oil supply pipe 7, it is possible to prevent the high-temperature lubricating oil in the compressor 1 from flowing into the expander 3 as it is. For this reason, it is possible to avoid an excessive increase in the temperature of the refrigerant before expansion, and to suppress a decrease in evaporator capacity.
  • the lubricating oil can be sufficiently supplied to the expander 3 and the refrigeration cycle apparatus 10A can be reduced in size or weight.
  • the lubricating oil in the oil supply pipe 7 is cooled by the low-pressure refrigerant in the refrigerant circuit 11, there is no need to provide a dedicated cooling source for cooling the lubricating oil. Further, the heat radiation from the lubricating oil can be recovered in the refrigerant circuit 11, and the COP of the entire cycle can be improved. Therefore, it is possible to achieve both the sufficient supply of the lubricating oil to the expander 3 and the improvement of the COP of the entire cycle.
  • this refrigeration cycle apparatus 10A by heating the low-pressure refrigerant with lubricating oil, the low-pressure side pressure of the refrigerant circuit 11 can be increased, and the load on the compressor 1 can be reduced. Therefore, the COP of the refrigeration cycle can be improved. Further, since the refrigerant is heated in the cooler 6, the required heating amount in the evaporator 5 can be reduced. Therefore, it is possible to make the evaporator 5 compact.
  • the oil reservoir 37 is provided in the compressor 1, the oil reservoir 77 is provided in the expander 3, and the oil supply pipe 7 is interposed. Since the oil reservoirs 37 and 77 are communicated with each other, the lubricating oil can be supplied from the compressor 1 to the expander 3 with a simple configuration.
  • the compressor 1 and the expander 3 are both high-pressure dome type, and the pressure applied to the lubricating oil in the compressor 1 and the expander 3 is the compression mechanism 25 and the expansion mechanism 55.
  • the sliding part is at a pressure higher than the pressure applied to the lubricating oil during lubrication. Accordingly, the lubricating oil is satisfactorily supplied from the oil reservoirs 37 and 77 to the sliding portions of the compression mechanism 25 and the expansion mechanism 55.
  • the valve 8 capable of adjusting the opening degree is provided in the oil supply pipe 7, the supply amount of the lubricating oil to the expander 3 can be freely adjusted. That is, an appropriate amount of lubricating oil can always be supplied to the expander 3. Further, the refrigerant temperature before expansion can be controlled by adjusting the opening degree of the valve 8 based on the inlet refrigerant temperature of the expander 3. Therefore, a decrease in evaporator capacity can be suppressed, and an increase in load on the compressor 1 can be suppressed. Therefore, the COP of the refrigeration cycle apparatus 10 can be improved regardless of fluctuations in the operating state.
  • a lance between the internal pressure of the compressor 1 and the internal pressure of the expander 3 can be obtained by appropriately adjusting the opening degree of the valve 8.
  • the difference between the internal pressure of the compressor 1 and the internal pressure of the expander 3 can be maintained at a predetermined value by adjusting the opening of the valve 8. Therefore, a refrigerant pipe (equal pressure line) for connecting the compressor 1 and the expander 3 is not particularly necessary.
  • the amount of oil in the compressor 1 and the amount of oil in the expander 3 can be balanced by controlling the opening degree of the valve 8.
  • the lubricating oil supplied to the expander 3 is returned to the compressor 1 again through the evaporator 5.
  • the amount of lubricating oil discharged from the expander 3 exceeds the amount of lubricating oil discharged from the compressor 1. Therefore, the line for supplying the lubricating oil from the expander 3 side to the compressor 1 side need not be considered.
  • the oil supply pipe 7 communicates with the oil reservoir 37 of the compressor 1 and the oil reservoir 77 of the expander 3, but the arrangement of the oil supply pipe 7 is It is not limited to this. That is, one end of the oil supply pipe 7 of the refrigeration cycle apparatus 10B shown in FIG. The other end of the refrigerant circuit 11 is connected to a pipe 57 (an inlet side pipe 57 of the expander 3) between the radiator 2 and the expander 3.
  • the controller 80 controls the opening degree of the valve 8 based on the inlet refrigerant temperature of the expander 3.
  • the control executed by the controller 80 is not limited to the above control.
  • a rotation speed detection sensor 82 for detecting the rotation speed of the expander 3 is provided, and the opening degree of the valve 8 is controlled based on the rotation speed of the expander 3. It may be.
  • the controller 80 increases the opening degree of the valve 8 when the rotational speed of the expander 3 is greater than or equal to a predetermined value, and decreases the opening degree of the valve 8 when the rotational speed is less than a predetermined value. As a result, a sufficient amount of lubricating oil can always be supplied in accordance with the rotational speed, and cycle efficiency can be improved.
  • controlling the rotational speed of the expander 3 means controlling the operating capacity of the expander 3.
  • the method of controlling the operating capacity of the expander 3 is not limited to the method of controlling the rotational speed.
  • the expander 3 may be a plurality of expander cables connected in parallel to each other. In this case as well, the overall operating capacity of the expander 3 can be controlled by adjusting the number of expander units.
  • the refrigeration cycle apparatus 10D of the fourth embodiment is a modification of the cooler 6 of the oil supply pipe 7 in the refrigeration cycle apparatus 10A of the first embodiment.
  • the cooler 6 is configured to indirectly exchange heat between the lubricating oil and the low-pressure refrigerant.
  • the evaporator 5 of the present embodiment also has a so-called air heat exchange force that exchanges heat between the air and the refrigerant, and the cooler 6 is the air before being cooled by the evaporator 5 or after being cooled. Air heat exchange ⁇ for heat exchange between oil and lubricating oil Therefore, it is comprised.
  • a blower 9 common to the evaporator 5 and the cooler 6 is provided. However, it goes without saying that a fan is provided in each of the evaporator 5 and the cooler 6.
  • the oil supply pipe 7 is provided with the valve 8.
  • the oil supply pipe 7 may be provided with an oil pump 8a instead of the valve 8 (or together with the valve 8).
  • the oil pump 8a plays a role of a conveying device that conveys the lubricating oil in the oil supply pipe 7.
  • the controller 80 may control the oil pump 8a based on the inlet refrigerant temperature or the operating capacity of the expander 3.
  • the flow rate of the lubricating oil in the oil supply pipe 7 can be increased even when the pressure difference between the compressor 1 and the expander 3 is small. it can. Therefore, a sufficient amount of lubricating oil can always be supplied to the expander 3. Moreover, it becomes possible to control the flow rate of the lubricating oil widely.
  • each embodiment described below employs a configuration in which an oil separator is disposed on the outlet side of the compressor 1 in the refrigerant circuit 11 and the lubricating oil recovered by the oil separator is supplied to the expander 3 side. To do.
  • the refrigeration cycle apparatus 10F includes a refrigerant circuit 11 in which a compressor radiator 2, an expander 3, and an evaporator 5 are connected in this order.
  • An oil separator 9 is disposed between the compressor 1 and the radiator 2 in the refrigerant circuit 11.
  • the refrigeration cycle apparatus 10F includes an oil supply pipe 7 that supplies the lubricating oil of the oil separator 9 to the expander 3.
  • the oil supply pipe 7 has one end connected to the oil separator 9 and the other end connected to the inlet side pipe 57 of the expander 3.
  • the oil supply pipe 7 is provided with a cooler 6 and a valve 8.
  • the valve 8 is a valve whose opening can be adjusted.
  • the refrigerant discharged from the compressor 1 is separated from the lubricating oil in the oil separator 9, then radiates heat in the heat radiator 2, expands in the expander 3, and becomes a low-temperature and low-pressure refrigerant.
  • the low-temperature and low-pressure refrigerant is heated by the cooler 6 at the same time as the lubricating oil is cooled. At this time, a part of the cooling medium may or may not evaporate. Then, the refrigerant heated by the cooler 6 evaporates by the evaporator 5 and then is sucked into the compressor 1.
  • the lubricating oil separated by the oil separator 9 flows through the oil supply pipe 7 and is cooled by exchanging heat with the refrigerant in the cooler 6.
  • the cooled lubricating oil flows into the inlet side pipe 57 of the expander 3, merges with the refrigerant from the radiator 2, and flows into the expander 3.
  • the flow rate of lubricating oil is adjusted by valve 8.
  • the opening degree of the valve 8 may be controlled based on the inlet refrigerant temperature of the expander 3, and the opening degree of the valve 8 may be controlled based on the rotation speed of the expander 3. Even so,
  • the refrigerant and the lubricating oil are separated by the oil separator 9, and the lubricating oil is supplied to the expander 3 through the oil supply pipe 7.
  • a sufficient amount of lubricating oil can be supplied for 3. Since the lubricating oil in the oil supply pipe 7 is cooled by the low-pressure refrigerant in the refrigerant circuit 11, it is not necessary to newly provide a cooling source. Further, the heat radiation from the lubricating oil can be recovered in the refrigerant circuit 11, and the COP of the entire cycle can be improved. Accordingly, it is possible to achieve both sufficient supply of lubricating oil to the expander 3 and improvement of COP of the entire site.
  • this refrigeration cycle apparatus 10F by heating the low-pressure refrigerant with lubricating oil, the low-pressure side pressure of the refrigerant circuit 11 can be increased, and the load on the compressor 1 can be reduced. Therefore, the COP of the refrigeration cycle can be improved. Further, since the refrigerant is heated in the cooler 6, the required heating amount in the evaporator 5 can be reduced. Therefore, it is possible to make the evaporator 5 compact. [0070] Further, according to the present embodiment, since the valve 8 capable of adjusting the opening degree is provided in the oil supply pipe 7, the supply amount of the lubricating oil to the expander 3 can be freely adjusted.
  • the refrigerant temperature before expansion can be controlled. Therefore, it is possible to suppress a decrease in the viscosity of the lubricating oil due to a decrease in the refrigerant temperature before expansion and a decrease in the evaporator capacity due to an increase in the refrigerant temperature before expansion.
  • a decrease in the viscosity of the lubricating oil due to a decrease in the refrigerant temperature before expansion
  • a decrease in the evaporator capacity due to an increase in the refrigerant temperature before expansion By suppressing the decrease in the lubricating oil viscosity, an increase in sliding loss in the expander 3 can be suppressed, and as a result, the reliability and performance of the expander 3 can be improved.
  • the refrigeration cycle apparatus 10F of the present embodiment it is possible to improve the COP of the refrigeration cycle while ensuring the reliability of the expander 3 regardless of fluctuations in the operating state.
  • the refrigerant after being separated from the lubricating oil by the oil separator 9 flows through the radiator 2. Therefore, it is possible to prevent or suppress the lubricating oil from flowing into the radiator 2, so that the heat transfer coefficient on the refrigerant side of the radiator 2 can be increased, and the performance of the radiator 2 can be improved. . Therefore, COP can be further improved.
  • the seventh embodiment is obtained by changing the cooler 6 of the oil supply pipe 7 in the refrigeration cycle apparatus 10F of the sixth embodiment.
  • the cooler 6 is configured to indirectly exchange heat between the lubricating oil and the low-pressure refrigerant, similarly to the refrigeration cycle apparatus 10D of the fourth embodiment (see FIG. 6). It is configured.
  • a common blower 17 is provided for the evaporator 5 and the cooler 6.
  • the eighth embodiment is also a modification of the cooler 6 of the oil supply pipe 7 in the refrigeration cycle apparatus 10F of the sixth embodiment.
  • the cooler 6 is integrated with the evaporator 5.
  • the oil supply pipe 7 is steamed It passes through the generator 5, and in the evaporator 5, the lubricating oil and the refrigerant (or air before being cooled by the refrigerant or air after being cooled) exchange heat.
  • Other configurations are the same as those in the sixth embodiment.
  • the valve 8 is provided in the oil supply pipe 7.
  • the oil supply pipe 7 may be provided with an oil pump 8a instead of the valve 8 (or together with the valve 8).
  • the controller 80 may control the oil pump 8a based on the inlet refrigerant temperature or the operating capacity of the expander 3. The effect of oil pump 8a is as explained in Fig. 7.
  • the downstream end of the oil supply pipe 7 is connected to the inlet side pipe 5 7 of the expander 3.
  • the oil supply pipe 7 supplies lubricating oil to the expander 3
  • the downstream end of the oil supply pipe 7 is connected to the expander 3 itself, specifically, to the oil reservoir 77 of the expander 3. You can be ⁇ .
  • a throttle mechanism such as a capillary tube may be provided instead of the valve 8 whose opening degree can be adjusted.
  • the valve 8 can be omitted.
  • the type of the oil supply pipe 7 is not limited at all.
  • the oil supply pipe 7 may be formed of a flexible pipe so that the oil supply pipe 7 is not easily damaged by vibration of the compressor 1 or the expander 3.
  • the length and shape of the oil supply pipe 7 are not limited at all. However, from the viewpoint of reducing the pressure loss of the oil supply pipe 7, it is preferable that the length of the oil supply pipe 7 is short, and it is preferable that the oil supply pipe 7 is a straight pipe.
  • the compressor 1 and the expander 3 are high-pressure dome types. However, as long as the performance of the lubricating oil is not deteriorated, the compressor 1 and the expander 3 may be a low-pressure dome type in which low-pressure refrigerant is stored inside.
  • the refrigerant charged in the refrigerant circuit 11 is not limited to a refrigerant that is in a supercritical state in the high pressure portion of the refrigerant circuit 11, and may be a refrigerant that does not enter a supercritical state in the high pressure portion.
  • the present invention is useful for a refrigeration cycle apparatus including a compressor and an expander.
  • the present invention can be suitably applied to a water heater, a heating device, and a dryer that heat an object such as water or air with a radiator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L’invention concerne un système de réfrigération à cycles (10A) comprenant un circuit réfrigérant (11) où un compresseur (1), un radiateur (2), un dispositif d’expansion (3) et un évaporateur (5) sont connectés dans cet ordre et une conduite d'alimentation en huile (7) pour permettre une communication de la cuvette du compresseur (1) avec la cuvette du dispositif d’expansion (3). La conduite d’alimentation (7) est fournie avec un refroidisseur (6) pour accueillir un lubrifiant de refroidissement et une valve (8) pour la régulation du flux de lubrifiant. Le tuyautage du côté entrée (57) du dispositif d’expansion (3) est fourni avec un capteur de température (81). Un contrôleur (80) contrôle l’ouverture d’une valve (8) en rapport avec la température du réfrigérant du dispositif d’expansion (3).
PCT/JP2006/303228 2005-03-09 2006-02-23 Systeme de refrigeration a cycles WO2006095572A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2005-065238 2005-03-09
JP2005065239A JP2008133968A (ja) 2005-03-09 2005-03-09 冷凍サイクル装置
JP2005-065239 2005-03-09
JP2005065238A JP2008133967A (ja) 2005-03-09 2005-03-09 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2006095572A1 true WO2006095572A1 (fr) 2006-09-14

Family

ID=36953173

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/303228 WO2006095572A1 (fr) 2005-03-09 2006-02-23 Systeme de refrigeration a cycles

Country Status (1)

Country Link
WO (1) WO2006095572A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008075531A (ja) * 2006-09-21 2008-04-03 Fujitsu General Ltd 膨張機を備えた冷媒回路
WO2008108055A1 (fr) * 2007-03-08 2008-09-12 Daikin Industries, Ltd. Dispositif frigorifique
JP2008223651A (ja) * 2007-03-14 2008-09-25 Daikin Ind Ltd 流体機械
JP2009174476A (ja) * 2008-01-25 2009-08-06 Daikin Ind Ltd 膨張機
JP2009228927A (ja) * 2008-03-19 2009-10-08 Daikin Ind Ltd 冷凍装置
JP2011510258A (ja) * 2008-01-17 2011-03-31 キャリア コーポレイション 潤滑剤冷却器を備える冷媒蒸気圧縮システム
JP2012167926A (ja) * 2012-06-12 2012-09-06 Daikin Industries Ltd 冷凍装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5696259U (fr) * 1979-12-24 1981-07-30
JP2001141315A (ja) * 1999-11-10 2001-05-25 Aisin Seiki Co Ltd 冷凍空調機
JP2002005021A (ja) * 2000-06-16 2002-01-09 Mitsubishi Heavy Ind Ltd オイルセパレータ内蔵圧縮機
JP2003148814A (ja) * 2001-11-15 2003-05-21 Matsushita Electric Ind Co Ltd 冷凍装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5696259U (fr) * 1979-12-24 1981-07-30
JP2001141315A (ja) * 1999-11-10 2001-05-25 Aisin Seiki Co Ltd 冷凍空調機
JP2002005021A (ja) * 2000-06-16 2002-01-09 Mitsubishi Heavy Ind Ltd オイルセパレータ内蔵圧縮機
JP2003148814A (ja) * 2001-11-15 2003-05-21 Matsushita Electric Ind Co Ltd 冷凍装置

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008075531A (ja) * 2006-09-21 2008-04-03 Fujitsu General Ltd 膨張機を備えた冷媒回路
US20100101268A1 (en) * 2007-03-08 2010-04-29 Katsumi Sakitani Refrigeration system
JP2008224053A (ja) * 2007-03-08 2008-09-25 Daikin Ind Ltd 冷凍装置
WO2008108055A1 (fr) * 2007-03-08 2008-09-12 Daikin Industries, Ltd. Dispositif frigorifique
AU2008222268B2 (en) * 2007-03-08 2011-05-26 Daikin Industries, Ltd. Refrigeration system
AU2008222268C1 (en) * 2007-03-08 2012-03-29 Daikin Industries, Ltd. Refrigeration system
CN101627265B (zh) * 2007-03-08 2013-04-17 大金工业株式会社 制冷装置
JP2008223651A (ja) * 2007-03-14 2008-09-25 Daikin Ind Ltd 流体機械
JP2011510258A (ja) * 2008-01-17 2011-03-31 キャリア コーポレイション 潤滑剤冷却器を備える冷媒蒸気圧縮システム
US8424337B2 (en) 2008-01-17 2013-04-23 Carrier Corporation Refrigerant vapor compression system with lubricant cooler
JP2009174476A (ja) * 2008-01-25 2009-08-06 Daikin Ind Ltd 膨張機
JP2009228927A (ja) * 2008-03-19 2009-10-08 Daikin Ind Ltd 冷凍装置
JP2012167926A (ja) * 2012-06-12 2012-09-06 Daikin Industries Ltd 冷凍装置

Similar Documents

Publication Publication Date Title
US9897360B2 (en) Refrigeration apparatus
JP4949768B2 (ja) スクリュー圧縮機
JP2009127902A (ja) 冷凍装置及び圧縮機
JP4816220B2 (ja) 冷凍装置
WO2007123088A1 (fr) Appareil de réfrigération
WO2006095572A1 (fr) Systeme de refrigeration a cycles
JP4065313B2 (ja) 冷凍サイクル装置
KR101020916B1 (ko) 냉매 사이클 장치
KR20030095240A (ko) 초임계 냉매 사이클 장치
JP2007271211A (ja) 冷凍装置
JP2010107181A (ja) 冷凍装置
JP2008133968A (ja) 冷凍サイクル装置
JP2007212024A (ja) 冷凍サイクル装置および冷凍サイクル装置の制御方法
JP2007154726A (ja) 密閉型圧縮機及び冷凍サイクル装置
JP2021021509A (ja) 空気調和装置
JP2003065618A (ja) 熱搬送装置
JP4278402B2 (ja) 冷媒サイクル装置
US11885548B2 (en) Refrigeration cycle apparatus that injects refrigerant into compressor during low load operation
WO2009098900A1 (fr) Système de réfrigération
WO2009098863A1 (fr) Dispositif de réfrigération
JP2013096602A (ja) 冷凍サイクル装置
JP2004286322A (ja) 冷媒サイクル装置
WO2015104822A1 (fr) Dispositif à cycle de réfrigération
JP2004028485A (ja) Ｃｏ２冷媒サイクル装置
JP2007010257A (ja) ヒートポンプ装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU

122 Ep: pct application non-entry in european phase

Ref document number: 06714368

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP