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WO2006126396A1 - Dispositif de cycle de refrigeration - Google Patents

Dispositif de cycle de refrigeration Download PDF

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Publication number
WO2006126396A1
WO2006126396A1 PCT/JP2006/309410 JP2006309410W WO2006126396A1 WO 2006126396 A1 WO2006126396 A1 WO 2006126396A1 JP 2006309410 W JP2006309410 W JP 2006309410W WO 2006126396 A1 WO2006126396 A1 WO 2006126396A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
lubricating oil
refrigeration cycle
oil
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2006/309410
Other languages
English (en)
Japanese (ja)
Inventor
Tomoichiro Tamura
Hiroshi Hasegawa
Masaru Matsui
Atsuo Okaichi
Takeshi Ogata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
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
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP2007517764A priority Critical patent/JP4065313B2/ja
Publication of WO2006126396A1 publication Critical patent/WO2006126396A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters

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 mechanical force, and the efficiency of the cycle is improved by the amount of the recovered energy. be able to.
  • lubricating oil is also required for an expander that is not only a compressor.
  • concentration of lubricating oil in the refrigerant increases, the heat transfer coefficient on the refrigerant side in the heat exchanger decreases and the refrigeration cycle performance decreases. Therefore, a refrigeration cycle apparatus in which an oil separator is provided on the refrigerant circuit has been proposed.
  • Japanese Patent Laid-Open No. 2003-240366 discloses a refrigeration provided with an oil separator provided between an expander and an evaporator, and an oil feed pipe connecting the oil separator and an inlet side pipe of a compressor.
  • An air conditioner is disclosed.
  • the refrigerant and the lubricating oil between the radiator and the expander are provided with heat exchange to exchange heat, and dissolved in the lubricating oil in the oil separator and the lubricating oil.
  • a configuration has been proposed in which the refrigeration capacity of the liquid refrigerant is recovered by the refrigerant between the radiator and the expander.
  • the temperature of the refrigerant between the radiator and the expander, and between the expander and the evaporator is small. Therefore, when the lubricant is heated by exchanging heat between the refrigerant between the radiator and the expander and the lubricant separated by the oil separator, the capacity of the heater increases. .
  • the present invention has been made in view of the points to be applied, and the object of the present invention is to appropriately control the temperature of the lubricating oil returned to the compressor and to control the temperature of the refrigerant discharged from the compressor.
  • heat exchange between the refrigerant and the lubricant between the compressor and the radiator increases the temperature difference between the refrigerant and the lubricant, thereby reducing the size of the heater.
  • the present invention provides:
  • a refrigerant circuit in which a compressor, a radiator, an expander, an oil separator and an evaporator are connected in this order;
  • An oil supply passage provided separately from the refrigerant circuit for supplying the lubricating oil separated by the oil separator between the evaporator and the compressor in the compressor or refrigerant circuit;
  • a flow rate adjusting means for adjusting the flow rate of the lubricating oil in the oil supply passage
  • a refrigeration cycle apparatus comprising:
  • the oil separator is provided in the refrigerant circuit, the amount of lubricating oil flowing into the evaporator can be reduced. Thereby, the heat transfer performance on the refrigerant side in the evaporator can be improved, and the efficiency of the refrigeration cycle can be improved.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 2 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 2.
  • FIG. 3 is a valve control flowchart in the second embodiment.
  • FIG. 4 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 3.
  • FIG. 5 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 4.
  • FIG. 6 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 5.
  • a refrigeration cycle apparatus 10A includes a refrigerant circuit 11 in which a compressor heat radiator 2, an expander 3, an oil separator 9, and an evaporator 5 are connected in this order. I have. Further, the refrigeration cycle apparatus 10A includes an oil supply pipe 7 as an oil supply passage for supplying the lubricating oil of the oil separator 9 to the compressor 1.
  • the oil supply pipe 7 is a pipe provided separately from the refrigerant pipe of the refrigerant circuit 11. One end of the oil supply pipe 7 is connected to the oil separator 9, and the other end is connected to the inlet side pipe 13 of the compressor 1 (that is, the refrigerant pipe between the evaporator 5 and the compressor 1). .
  • the oil supply pipe 7 is provided with a heater 6A and a valve 8.
  • the valve 8 is a valve whose opening degree can be controlled, and is configured as a flow rate adjusting means for adjusting the flow rate of the lubricating oil flowing through the oil supply pipe 7 by the opening degree control.
  • the refrigerant charged in the refrigerant circuit 11 is a refrigerant that becomes a supercritical state in a high-pressure part (a part from the compressor 1 through the radiator 2 to the expander 3) during operation.
  • the refrigerant circuit 11 of Embodiment 1 is filled with carbon dioxide (CO 2) as such a refrigerant.
  • CO 2 carbon dioxide
  • the kind of refrigerant is not particularly limited.
  • the compressor 1 for example, a rotary compressor, a scroll compressor, or the like can be suitably used.
  • the format of the compressor 1 is not limited at all.
  • the type of the expander 3 is not limited at all.
  • an expander equipped with an expansion mechanism such as a rotary type or a scroll type can be suitably used.
  • a generator 4 is connected to the expander 3.
  • the generator 4 converts the expansion energy of the refrigerant recovered by the expander 3 into electric energy.
  • the generator 4 and the expander 3 are illustrated separately, but the generator 4 may be incorporated in the expander 3.
  • the motor drive shaft of the compressor 1 and the drive shaft of the expander 3 may be connected. sand That is, the compressor 1 and the expander 3 are placed in the same sealed container, and the compressor and the expander are integrated by connecting them with a drive shaft. Can do. At this time, the generator 4 is not required.
  • the configurations of the radiator 2 and the evaporator 5 are not limited at all.
  • an air-cooled or water-cooled heat exchanger may be used as the radiator 2 or the evaporator 5, for example.
  • the refrigerant discharged from the expander 3 is in a gas-liquid two-phase state. It is desirable to be able to separate well. Focusing on the fact that the specific gravity of the lubricating oil is larger than that of the liquid refrigerant, for example, an oil separator 9 having a structure as shown in FIG. 7 can be suitably employed.
  • the oil separator 9 shown in FIG. 7 is provided with a container 19 that receives the refrigerant discharged from the expander 3 and allows it to stand still.
  • An oil supply pipe 7 is connected to the bottom of the container 19, and a bifurcated pipe for sending liquid refrigerant 21 L and gaseous refrigerant 21 G stored on the lubricating oil 20 to the evaporator 5 on the side of the container 19.
  • the refrigerant pipe l ip is connected.
  • the heater 6A directly exchanges heat between the lubricating oil in the oil supply pipe 7 and the high-pressure refrigerant between the compressor 1 and the radiator 2.
  • the temperature difference between the high-temperature and high-pressure refrigerant between the compressor 1 and the radiator 2 and the lubricating oil passing through the oil supply pipe 7 is large. Therefore, as described in Japanese Patent Laid-Open No. 2003-240366, as compared with the case where heat is exchanged between the low-temperature and high-pressure refrigerant discharged from the radiator and the lubricating oil flowing through the oil supply pipe, heating is performed.
  • the vessel 6A is small.
  • the heater 6A for example, a double tube heat exchanger, a plate heat exchanger, a shell-and-tube heat exchanger, or the like can be suitably used. Further, without using a dedicated heat exchanger, for example, the oil supply pipe 7 and the refrigerant pipe of the refrigerant circuit 11 are arranged in parallel and brought into contact with each other. It is also possible to construct vessel 6A.
  • a refrigerant may flow through the inner flow path and lubricating oil may flow through the outer flow path. .
  • This can suppress an increase in pressure loss of the high-pressure refrigerant.
  • the heater 6A includes a refrigerant, a lubricating oil, It is preferable to use a so-called counterflow type heat exchange in which the refrigerant is circulated in an opposed state.
  • the evaporator 5 is provided with an evaporation temperature sensor 14 for detecting the evaporation temperature of the refrigerant.
  • the suction temperature sensor 12 and the evaporation temperature sensor 14 may be any sensor that substantially detects the refrigerant temperature. Therefore, the suction temperature sensor 12 and the evaporation temperature sensor 14 indirectly detect the refrigerant temperature by detecting the wall surface temperature of the pipe, even if the refrigerant temperature in the pipe is directly detected. May be.
  • the evaporation temperature sensor 14 may be provided between the expander 3 and the evaporator 5 as long as the evaporation temperature of the low-pressure side refrigerant can be detected.
  • a controller 15 is provided in the refrigeration cycle apparatus 10A.
  • the controller 15 receives the detection signals of the suction temperature sensor 12 and the evaporation temperature sensor 14 and identifies the detection values (detection temperatures) of the sensors 12 and 14. Based on the identified detection value, the opening degree of the valve 8 is controlled. Thereby, the difference between the temperature of the refrigerant sucked into the compressor 1 and the evaporation temperature of the refrigerant in the evaporator 5, that is, the so-called superheat degree can be appropriately controlled. Appropriate control of the degree of superheat can prevent overheating of the refrigerant discharged from the compressor.
  • the controller 15 need not be a dedicated controller provided for the control of the valve 8, and may control the compressor 1.
  • the suction temperature sensor 12 is arranged on the compressor 1 side in view of the confluence point of the inlet side pipe 13 and the oil supply pipe 7 of the compressor 1. If the suction temperature sensor 12 is arranged at such a position, the temperature of the refrigerant immediately before being sucked into the compressor 1 can be accurately measured.
  • the refrigerant discharged from the compressor 1 heats the lubricating oil by the heater 6A and at the same time releases heat. Furthermore, the refrigerant dissipates heat in the radiator 2, expands in the expander 3, and then is separated by lubricating oil power in the oil separator 9 mm. Next, the refrigerant absorbs heat in the evaporator 5 and is then sucked into the compressor 1.
  • the lubricating oil separated by the oil separator 9 flows through the oil supply pipe 7 and is heated by exchanging heat with the refrigerant in the heater 6A. Then, the heated lubricating oil flows into the inlet side pipe 13 of the compressor 1, merges with the refrigerant from the evaporator 5, and flows into the compressor 1. to this Thus, the lubricating oil is supplied to the compressor 1.
  • the lubricating oil flow rate is adjusted by valve 8.
  • the controller 15 controls the opening degree of the valve 8 based on the refrigerant temperature at the inlet of the compressor 1 and the refrigerant evaporation temperature in the evaporator 5. As described above, since the lubricating oil in the oil supply pipe 7 is heated by the heater 6A, the temperature of the refrigerant and the lubricating oil flowing into the compressor 1 increases as the amount of the lubricating oil flowing into the heater 6A increases. Become. Therefore, in the first embodiment, the controller 15 sets the degree of superheat, which is the difference between the refrigerant temperature at the inlet of the compressor 1 and the refrigerant evaporation temperature in the evaporator 5, to a predetermined value (target value). Control the opening of valve 8 so that it approaches. For example, the controller 15 decreases the opening degree of the valve 8 when the degree of superheat is equal to or greater than a predetermined value, and increases the opening degree of the valve 8 when the degree of superheat is less than a predetermined value.
  • the opening degree of the valve 8 may be controlled so that the degree of superheat falls within a predetermined range (target range). When the degree of superheat exceeds a predetermined range, the opening degree of the valve 8 is decreased. When the degree of superheat is less than the predetermined range, the opening degree of the valve 8 is increased. In this way, the valve 8 can be prevented from opening and closing constantly, and the possibility of failure of the valve 8 can be reduced. Change the superheat target value or target range according to the operating condition of the refrigeration cycle unit 10A.
  • the lubricating oil in the oil supply pipe 7 is heated with the high-pressure refrigerant between the compressor 1 and the radiator 2, so the heater 6A is Can be downsized.
  • the refrigeration capacity of the lubricating oil and the liquid refrigerant dissolved in the lubricating oil can be recovered in the refrigerant circuit, and the refrigeration efficiency of the entire cycle can be improved.
  • the opening degree of the valve 8 the degree of superheat can always be controlled within a predetermined value or within a predetermined range, so that the danger of the compressor 1 performing hydraulic compression can be avoided.
  • this refrigeration cycle apparatus 10A by cooling the high-pressure refrigerant with lubricating oil, the pressure in the high-pressure portion of the refrigerant circuit 11 can be reduced, and the load on the compressor 1 can be reduced. . Therefore, the COP (coefficient of performance) of the refrigeration cycle, specifically, the COP when cooling an object such as air or water can be improved. Further, since the refrigerant is cooled in the heater 6A, the necessary heat release amount in the radiator 2 can be reduced. Therefore, it is possible to make the radiator 2 compact. is there.
  • the oil supply pipe 7 is provided with the valve 8 capable of controlling the opening degree, the supply amount of the lubricating oil to the heater 6A can be freely adjusted. it can. Further, the degree of superheat of the refrigerant sucked into the compressor 1 is controlled by controlling the opening degree of the valve 8 based on the refrigerant temperature at the inlet of the compressor 1 and the refrigerant evaporation temperature in the evaporator 5. Can. Therefore, the danger that the compressor 1 performs liquid compression can be avoided, and the reliability of the compressor 1 can be improved. Therefore, it is possible to achieve a high degree of compatibility between the refrigeration efficiency and the reliability of the compressor 1.
  • the refrigerant after having been separated from the lubricating oil by the oil separator 9 flows through the evaporator 5. Therefore, since it is possible to suppress the lubricating oil from flowing into the evaporator 5, the heat transfer coefficient on the refrigerant side of the evaporator 5 can be increased, and the performance of the evaporator 5 can be improved. Therefore, the refrigeration efficiency can be further improved.
  • the refrigeration cycle apparatus 10B includes a discharge temperature sensor 16 that detects the temperature of refrigerant discharged from the compressor 1 in addition to the refrigeration cycle apparatus 10A according to the first embodiment. And a heater 6B is used instead of the heater 6A.
  • the refrigeration cycle apparatus 10B is provided with a controller 15.
  • the controller 15 receives detection signals from the suction temperature sensor 12, the evaporation temperature sensor 14, and the discharge temperature sensor 16, and controls the opening degree of the valve 8.
  • the controller 15 may also be used as a controller for controlling the compressor 1 which is not necessarily a dedicated controller provided for controlling the valve 8.
  • the controller 15 includes a refrigerant temperature T1 sucked into the compressor 1 (referred to as a suction temperature T1), a refrigerant temperature T2 discharged from the compressor 1 (referred to as a discharge temperature T2), and an evaporator 5
  • the opening degree of the valve 8 is controlled based on the evaporation temperature ⁇ 3 of the refrigerant.
  • FIG. 3 is a flowchart for controlling the valve 8 by the controller 15. The control represented by this flowchart is repeatedly performed at regular intervals, for example.
  • step S1 the controller 15 determines that the discharge temperature ⁇ 2 is equal to or greater than a predetermined value Tb. It is determined whether it is. If it is determined that the discharge temperature T2 is equal to or higher than the predetermined value Tb, the opening degree of the valve 8 is decreased in step S4. When the opening degree of the valve 8 is reduced, the degree of superheat TSH represented by (T1 -T3) is lowered. Since the discharge temperature T2 decreases as the degree of superheat TSH decreases, damage to the seal member of the compressor 1 and deterioration of the lubricating oil due to the increase in the discharge temperature T2 can be avoided.
  • step S1 If it is determined in S1 that the discharge temperature T2 is lower than the predetermined value Tb, the process proceeds to step S2, and it is determined whether the degree of superheat TSH is equal to or higher than a predetermined value Ta. If it is determined that the degree of superheating TSH is equal to or greater than the predetermined value Ta, the opening degree of the valve 8 is reduced in step S4. As a result, the degree of superheat TSH decreases and the discharge temperature T2 decreases, so that damage to the seal member of the compressor 1 and deterioration of the lubricating oil due to excessive increase in the discharge temperature T2 can be avoided.
  • step S2 determines that the degree of superheat TSH is less than the predetermined value Ta, the opening degree of the valve 8 is increased in step S3. As a result, the degree of superheat TSH increases and approaches the predetermined value Ta, thereby increasing the efficiency of the refrigeration cycle.
  • the valve 8 based on the refrigerant temperature T1 at the inlet of the compressor 1 and the refrigerant evaporation temperature T3 in the evaporator 5, the superheat degree TSH of the refrigerant sucked by the compressor 1 is controlled. Can be controlled to approach the predetermined value Ta. Further, in the second embodiment, the discharge temperature T2 of the compressor 1 is detected, and when the discharge temperature T2 becomes equal to or higher than the predetermined value Tb, the opening degree of the valve 8 is reduced and the degree of superheat TSH is reduced. .
  • the temperature T2 of the refrigerant discharged from the compressor 1 is reduced, and the discharge temperature T2 is excessively increased, so that damage to the seal member of the compressor 1 and deterioration of the lubricating oil can be avoided.
  • the effect becomes remarkable under high load conditions where the difference between the high and low pressures of the refrigeration cycle is large, and the applications and installation conditions to which this refrigeration cycle apparatus can be applied are expanded.
  • the heater 6B according to the second embodiment also uses the high-pressure refrigerant in the refrigerant circuit 11 to cool the lubricating oil in the oil supply pipe 7, but differs in configuration from the first embodiment. .
  • the heater 6B according to the second embodiment is configured to indirectly exchange heat between the lubricating oil and the high-pressure refrigerant.
  • the radiator 2 according to the second embodiment exchanges heat between air and the refrigerant.
  • the heater 6B is configured by air heat exchange in which air (outside air) heated by the radiator 2 and the lubricating oil are subjected to heat exchange. The air after passing through the air heat exchanger constituting the heater 6B flows into the air heat exchanger constituting the radiator 2.
  • the refrigeration cycle apparatus 10B according to the second embodiment is provided with a blower 17 that is common to Sarakuko, the radiator 2 and the heater 6B. Thereby, heat exchange efficiency increases. However, it goes without saying that a blower is provided in each of the radiator 2 and the heater 6B.
  • the refrigeration cycle apparatus 10C of the third embodiment employs a heater 6C in place of the heater 6A of the refrigeration cycle apparatus 10A of the first embodiment.
  • the heater 6C is integrated with the radiator 2, that is, the heater 6C is also used as the radiator 2.
  • the oil supply pipe 7 passes through the radiator 2, and the refrigerant flowing into the radiator 2 (or air before being heated by the refrigerant or air after being heated) exchanges heat with the lubricating oil. .
  • Other configurations are the same as those in the first embodiment.
  • illustration of the intake temperature sensor 12, the evaporation temperature sensor 14, and the controller 15 is omitted.
  • Embodiment 3 Therefore, in Embodiment 3, the same effect as in Embodiment 1 can be obtained.
  • the oil supply pipe 7 is provided with the valve 8.
  • the refrigeration cycle apparatus 10D of the fifth embodiment is provided with an oil pump 8a instead of the valve 8 (or together with the valve 8).
  • the controller 15 controls the oil pump 8 a based on the refrigerant temperature at the inlet of the compressor 1 and the refrigerant evaporation temperature in the evaporator 5.
  • the refrigeration cycle apparatus 10E has an oil supply pipe separated into oil. It is branched between the vessel 9 and the heater 6A. That is, the oil supply pipes 17 and 27 as the oil supply passage are separated from the main supply pipe 17 as the main passage where the heater 6A is disposed and the oil separator 9 by branching from the main supply pipe 17.
  • the sub-supply pipe 27 as a sub-passage that can be supplied between the evaporator 5 and the compressor 1 in the refrigerant circuit 11 without heating the lubricant oil by the heater 6A.
  • the sub supply pipe 27 branched from the main supply pipe 17 between the oil separator 9 and the heater 6A is joined again with the main supply pipe 17 on the downstream side of the heater 6A, and the main supply pipe 17 is compressed. It is connected to the inlet side pipe 13 of machine 1. However, the auxiliary supply pipe 27 may be directly connected to the inlet side pipe 13 without joining the main supply pipe 17! / ⁇ .
  • the first valve 18 is disposed on the main supply pipe 17 between the branch point where the sub supply pipe 27 branches from the main supply pipe 17 and the heater 6A, and the second A valve 28 is arranged on the secondary supply pipe 27.
  • the first valve 18 and the second valve 28 are both valves whose opening degree can be controlled, and the flow rate of the lubricating oil flowing through the main supply pipe 17 and the lubricating oil flowing through the sub supply pipe 27 are controlled by the opening degree.
  • the oil flow rate can be adjusted.
  • the controller 15 controls the opening and closing of the first valve 18 and the second valve 28 to interlock the flow rate of the lubricating oil in the main supply pipe 17 and the flow rate of the lubricating oil in the sub supply pipe 27. adjust.
  • the opening degree of the valve 8 is reduced under conditions where the degree of superheat TSH is equal to or greater than the predetermined value Ta (for example, at high outside air temperature). Then, the flow resistance value of the oil supply pipe 7 facing the heater 6A increases, so that the lubricating oil flows through the evaporator 5 that does not pass through the oil supply pipe 7 and returns to the compressor 1.
  • the heat transfer coefficient on the refrigerant side in the evaporator 5 decreases, and the problem that the heat transfer performance deteriorates again comes to the surface.
  • the auxiliary supply pipe 27 is provided, and if the lubricating oil that cannot flow through the main supply pipe 17 is returned to the compressor 1 using the auxiliary supply pipe 27, the evaporator 5 Therefore, it is possible to appropriately control the superheat degree TSH without causing a decrease in heat transfer coefficient on the refrigerant side.
  • a specific control procedure is as follows. First, as described in FIG. 3, the opening degree of the first valve 18 is controlled according to the degree of superheat TSH. On the other hand, the opening of the second valve 28 is the entire oil supply pipe. All flow path resistance values are controlled to be always constant. In other words, control is performed to reduce the opening of the other in conjunction with increasing the opening of one of the valves. However, the opening of the first valve 18 and the
  • downstream ends of the oil supply pipes 7, 17, and 27 are the inlet side pipes 1 of the compressor 1.
  • a throttle mechanism such as a capillary tube is used instead of the valves 8, 18, and 28 that are adjustable in opening. May be provided.
  • the types of the oil supply pipes 7, 17, and 27 are not limited at all.
  • the oil supply pipes 7, 17, and 27 may be formed of flexible pipes so that they are not easily damaged by the vibration of the compressor 1 or the expander 3.
  • the length and shape of the oil supply pipes 7, 17, and 27 are not limited at all.
  • the oil supply pipes 7, 17, and 27 are short in length, and are preferably straight pipes.
  • the refrigerant charged in the refrigerant circuit is not limited to the refrigerant that is in the supercritical state in the high-pressure portion of the refrigerant circuit, and may be a refrigerant that does not enter the supercritical state in the high-pressure portion.
  • the present invention is useful for a refrigeration cycle apparatus including a compressor and an expander.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L’invention concerne un dispositif de cycle de réfrigération (10A) comprenant un circuit frigorifique (11) dans lequel un compresseur (1), un radiateur (2), un expanseur (3), un séparateur d’huile (9) et un évaporateur (5) sont connectés dans cet ordre, ainsi qu’un conduit de lubrification (7) qui relie le séparateur d’huile (9) et la canalisation (13) à l’entrée du compresseur (1). Le conduit de lubrification (7) comprend une vanne (8) dont le degré d’ouverture est réglable et un générateur de chaleur (6A) qui chauffe l’huile de lubrification par échange thermique entre un frigorigène haute pression et l’huile. Des capteurs de température (12, 14) sont disposés respectivement au niveau du conduit d’entrée (13) et de l’évaporateur (5). Un régulateur (15) règle le degré d’ouverture de la vanne (8) selon des valeurs de détection des capteurs de température (12, 14).
PCT/JP2006/309410 2005-05-24 2006-05-10 Dispositif de cycle de refrigeration Ceased WO2006126396A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007517764A JP4065313B2 (ja) 2005-05-24 2006-05-10 冷凍サイクル装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-150376 2005-05-24
JP2005150376 2005-05-24

Publications (1)

Publication Number Publication Date
WO2006126396A1 true WO2006126396A1 (fr) 2006-11-30

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PCT/JP2006/309410 Ceased WO2006126396A1 (fr) 2005-05-24 2006-05-10 Dispositif de cycle de refrigeration

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JP (1) JP4065313B2 (fr)
WO (1) WO2006126396A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008108055A1 (fr) * 2007-03-08 2008-09-12 Daikin Industries, Ltd. Dispositif frigorifique
JP2008267787A (ja) * 2007-03-27 2008-11-06 Daikin Ind Ltd 冷凍装置
JP2012211763A (ja) * 2007-03-27 2012-11-01 Daikin Industries Ltd 冷凍装置
JP2012247134A (ja) * 2011-05-27 2012-12-13 Sanyo Electric Co Ltd 超低温冷凍装置
EP2431685A4 (fr) * 2009-05-11 2014-06-25 Lg Electronics Inc Climatiseur
JP2014181878A (ja) * 2013-03-21 2014-09-29 Aisin Seiki Co Ltd 空調装置
CN104654665A (zh) * 2013-11-25 2015-05-27 珠海格力电器股份有限公司 多联机系统的室外机模块及具有其的多联机系统
JP2016020783A (ja) * 2014-07-15 2016-02-04 三菱重工業株式会社 ターボ冷凍機の油回収装置
CN113551447A (zh) * 2020-04-14 2021-10-26 青岛海尔空调器有限总公司 制热模式下空调系统的压缩机回油控制方法和控制系统
IT202200016839A1 (it) * 2022-08-05 2024-02-05 Carel Ind Spa Impianto frigorifero e metodo di azionamento dello stesso

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Cited By (18)

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JP2008224053A (ja) * 2007-03-08 2008-09-25 Daikin Ind Ltd 冷凍装置
US20100101268A1 (en) * 2007-03-08 2010-04-29 Katsumi Sakitani Refrigeration system
CN101627265B (zh) * 2007-03-08 2013-04-17 大金工业株式会社 制冷装置
WO2008108055A1 (fr) * 2007-03-08 2008-09-12 Daikin Industries, Ltd. Dispositif frigorifique
EP2136158A4 (fr) * 2007-03-27 2015-06-03 Daikin Ind Ltd Dispositif réfrigérant
JP2008267787A (ja) * 2007-03-27 2008-11-06 Daikin Ind Ltd 冷凍装置
JP2012211763A (ja) * 2007-03-27 2012-11-01 Daikin Industries Ltd 冷凍装置
EP2136158B1 (fr) 2007-03-27 2018-11-14 Daikin Industries, Ltd. Dispositif réfrigérant
US8353180B2 (en) 2007-03-27 2013-01-15 Daikin Industries, Ltd. Refrigerating apparatus
EP2431685A4 (fr) * 2009-05-11 2014-06-25 Lg Electronics Inc Climatiseur
JP2012247134A (ja) * 2011-05-27 2012-12-13 Sanyo Electric Co Ltd 超低温冷凍装置
JP2014181878A (ja) * 2013-03-21 2014-09-29 Aisin Seiki Co Ltd 空調装置
CN104654665A (zh) * 2013-11-25 2015-05-27 珠海格力电器股份有限公司 多联机系统的室外机模块及具有其的多联机系统
CN104654665B (zh) * 2013-11-25 2017-02-01 珠海格力电器股份有限公司 多联机系统的室外机模块及具有其的多联机系统
JP2016020783A (ja) * 2014-07-15 2016-02-04 三菱重工業株式会社 ターボ冷凍機の油回収装置
CN113551447A (zh) * 2020-04-14 2021-10-26 青岛海尔空调器有限总公司 制热模式下空调系统的压缩机回油控制方法和控制系统
IT202200016839A1 (it) * 2022-08-05 2024-02-05 Carel Ind Spa Impianto frigorifero e metodo di azionamento dello stesso
EP4317865A1 (fr) * 2022-08-05 2024-02-07 Carel Industries S.p.A. Installation frigorifique et son procédé de fonctionnement

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