WO2007135957A1 - Mécanisme de réfrigération - Google Patents

Mécanisme de réfrigération Download PDF

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Publication number
WO2007135957A1
WO2007135957A1 PCT/JP2007/060151 JP2007060151W WO2007135957A1 WO 2007135957 A1 WO2007135957 A1 WO 2007135957A1 JP 2007060151 W JP2007060151 W JP 2007060151W WO 2007135957 A1 WO2007135957 A1 WO 2007135957A1
Authority
WO
WIPO (PCT)
Prior art keywords
pipe
temperature
heat
refrigerant
refrigeration
Prior art date
Application number
PCT/JP2007/060151
Other languages
English (en)
Japanese (ja)
Inventor
Satoru Sakae
Toshiaki Mukaidani
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP07743586A priority Critical patent/EP2019273A1/fr
Priority to US12/301,214 priority patent/US20090188276A1/en
Priority to AU2007252631A priority patent/AU2007252631A1/en
Publication of WO2007135957A1 publication Critical patent/WO2007135957A1/fr

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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D29/00—Arrangement or mounting of control or safety devices
    • F25D29/005—Mounting of control devices

Definitions

  • the present invention relates to a refrigeration apparatus including a refrigerant circuit that performs a vapor compression refrigeration cycle, and particularly relates to a suction pressure sensor mounting structure for measuring a suction pressure of a compression mechanism.
  • Patent Document 1 a refrigeration apparatus that includes a refrigerant circuit that performs a refrigeration cycle and that performs refrigeration or freezing in a warehouse is known (for example, Patent Document 1).
  • a refrigeration cooling heat exchanger In the refrigeration apparatus of Patent Document 1, a refrigeration cooling heat exchanger, a low-stage compressor, a high-stage compressor, an outdoor heat exchanger, and a refrigeration expansion valve are sequentially connected.
  • the refrigerant compressed in two stages by the low-stage compressor and the high-stage compressor dissipates heat in the outdoor heat exchanger to be condensed.
  • the liquefied refrigerant is expanded by the refrigeration expansion valve and flows through the refrigeration cooling heat exchanger, absorbs heat from the internal air, evaporates at ⁇ 30 ° C., and cools the internal temperature to ⁇ 20 ° C. . Then, the evaporated refrigerant is again sucked into the low-stage compressor, and thereafter this circulation is repeated.
  • Patent Document 1 Japanese Patent Laid-Open No. 2004-353996
  • suction pressure sensors for measuring the suction pressure of the compressors are provided in the suction pipes of the low-stage and high-stage compressors.
  • a narrow tube (c) is connected to the suction pipe (a) of the compressor, and a pressure sensor (b) is connected to the end of the thin pipe (c).
  • a male screw for connection is formed on the outer peripheral surface.
  • the pressure sensor (b) includes a connection portion (d) having a female screw formed on the inner peripheral surface, and the female screw of the connection portion (d) is screwed into the male screw of the thin tube (c). Connected to the suction pipe (a).
  • the present invention has been made in view of the strong point, and in a refrigeration apparatus having a suction pressure sensor for measuring the suction pressure of the compression mechanism, improves workability when the pressure sensor is attached and replaced. It is an object to improve the reliability of the pressure sensor.
  • a first invention includes a refrigerant circuit (10) in which an evaporator (16, 17), a compression mechanism (11), a condenser (13), and an expansion mechanism (15a, 15b) are sequentially connected.
  • the refrigeration apparatus includes a suction pressure sensor (25) for measuring the suction pressure of the compression mechanism (11), the suction pressure sensor (25) being a suction device of the compression mechanism (11).
  • the pipe (61) is connected via an endothermic pipe (90) for making the temperature of the connection part (25b) of the suction pressure sensor (25) higher than the temperature of the suction pipe (61).
  • the set temperature of the evaporator (16, 17) is low (0 ° C or lower), a low-temperature refrigerant of 0 ° C or lower also flows through the suction pipe (61) of the compressor mechanism (11). Therefore, according to the first aspect of the present invention, by attaching the pressure sensor (25) via the heat absorption pipe (90), the cold heat of the refrigerant flowing through the suction pipe (61) is converted to the connection part ( 25b) and the heat absorption pipe (90) absorbs heat from ambient air, etc.
  • the connection (25b) of the sensor (25) is set to a temperature higher than 0 ° C to prevent freezing of the connection (25b).
  • a second invention is the heat absorption pipe (90) according to the first invention, wherein the temperature of the connection part (25b) of the suction pressure sensor (25) depends on the ambient temperature. ) It is formed in a length that raises the temperature further.
  • the heat absorption pipe (90) absorbs heat from the surrounding air, and gradually rises from the suction pipe (61) to the connection portion (25b) of the suction pressure sensor (25). Warm the connection part (25b) of the suction pressure sensor (25) to a temperature higher than 0 ° C.
  • the minimum length of the endothermic pipe (90) is a predetermined set length that increases as the evaporation temperature of the evaporator (16, 17) decreases. Is set.
  • the temperature of the refrigerant flowing through the suction pipe (61) decreases. Therefore, by increasing the minimum length of the heat absorption pipe (90) as the evaporation temperature of the evaporator (16, 17) decreases, as the temperature of the refrigerant flowing through the suction pipe (61) decreases, This cold heat of the refrigerant is made difficult to be transmitted to the connection part (25b) of the suction pressure sensor (25). On the other hand, by increasing the area of the endothermic pipe (90), the endothermic amount of heat absorbed by the endothermic pipe (90) is increased.
  • the heat absorption pipe (90) is connected to the high pressure side pipe (64) of the refrigerant circuit (10) by a heat transfer member (91). ) Is attached through.
  • the heat of the high-pressure side pipe (64) is transferred through the heat transfer member (91), thereby increasing the heat absorption amount of the heat-absorbing pipe (90).
  • the connection (25b) of the pressure sensor (25) is higher than 0 ° C and the temperature.
  • the high-pressure side pipe (64) in the fourth aspect of the invention is a pipe through which the refrigerant flowing through the suction pipe (61) flows at a pressure higher than 0 ° C and flows through the refrigerant! Uh.
  • the high-pressure side pipe (64) is the discharge pipe (64) of the compression mechanism (11).
  • the heat absorption amount received by the heat absorption pipe (90) from the high pressure side pipe (64) via the heat transfer member (91) increases as the temperature of the high pressure side pipe (64) increases. Therefore, in the fifth aspect of the present invention, the heat absorption pipe (90) is disposed via the discharge pipe (64) and the heat transfer member (91) of the high-temperature compression mechanism (11). By connecting, the endothermic amount of the endothermic pipe (90) is surely increased.
  • the heat absorption pipe (90) makes it difficult for cold heat of the refrigerant flowing through the suction pipe (61) to be transmitted to the connection part (25b) of the suction pressure sensor (25).
  • the heat absorption pipe (90) can absorb heat from the surrounding air.
  • the connection part (25b) of the suction pressure sensor (25) is The temperature can be higher than 0 ° C.
  • freezing damage to the connection portion (25b) of the suction pressure sensor (25) can be prevented, and the reliability of the suction pressure sensor (25) is improved.
  • the endothermic pipe (90) is connected to the inlet pipe (61) from the inlet pipe (61) depending on the temperature of the connecting portion (25b) of the inlet pressure sensor (25).
  • the heat absorption pipe (90) absorbs the surrounding aerodynamic force because it is formed to rise in temperature, and the heat absorption pipe (90) is connected from the suction pipe (61) to the connection part of the suction pressure sensor (25) ( The temperature can be gradually raised over 25b).
  • the connection part (25b) of the suction pressure sensor (25) can be set to a temperature higher than 0 ° C.
  • the minimum length of the endothermic pipe (90) is set to the evaporator.
  • connection part (25b) of the suction pressure sensor (25) can be surely set to a temperature higher than 0 ° C.
  • the heat absorption pipe (90) absorbs the heat of the high pressure side pipe (64) of the refrigerant circuit (10) via the heat transfer member (91). Therefore, the endothermic amount of the endothermic pipe (90) can be increased. As a result, the suction pressure sensor (25) The connection (25b) can be brought to a temperature higher than 0 ° C.
  • the heat absorption pipe (90) can absorb the heat of the discharge pipe (64) of the compression mechanism (11) via the heat transfer member (91). Therefore, since the discharge pipe (64) of the compression mechanism (11) is at a high temperature, the heat absorption amount of the heat absorption pipe (90) can be reliably increased. As a result, the connection part (25b) of the suction pressure sensor (25) can be surely brought to a temperature higher than 0 ° C.
  • FIG. 1 is a piping system diagram showing a refrigerant circuit of a refrigeration apparatus according to an embodiment.
  • FIG. 2 is a schematic perspective view showing a suction pressure sensor mounting structure according to the embodiment.
  • FIG. 3 is a relationship diagram showing a relationship between the evaporation temperature of the refrigeration heat exchanger according to the embodiment and the length of the endothermic pipe.
  • Fig. 4 is a piping system diagram showing a refrigerant circulation direction during the cooling operation of the refrigeration apparatus according to the embodiment.
  • FIG. 5 is a schematic configuration diagram showing a conventional suction pressure sensor mounting structure. Explanation of symbols
  • the embodiment of the present invention is a refrigeration apparatus (1) for cooling a cooling chamber, comprising an outdoor unit (2), a refrigeration unit (3), and a controller (100). ing.
  • the outdoor unit (2) is installed outdoors, while the refrigeration unit (3) is installed in a cooling room.
  • the refrigeration apparatus (1) is provided with an outdoor circuit (20) in the outdoor unit (2), and a refrigerator internal circuit (30) in the refrigeration unit (3). ing.
  • the gas end side of the outdoor circuit (20) and the gas end side of the refrigerator internal circuit (30) are connected by a gas side communication pipe (22), while the outdoor circuit ( The liquid end side of 20) and the liquid end side of the refrigerator internal circuit (30) are connected by a liquid side connecting pipe (21) to constitute a refrigerant circuit (10) of a vapor compression refrigeration cycle.
  • the outdoor circuit (20) of the outdoor unit (2) includes a compressor (11), an outdoor heat exchanger (13), a receiver (14), an outdoor expansion valve (45), a refrigerant heat exchanger ⁇ (50)
  • a branch expansion valve (46) is provided.
  • the outdoor circuit (20) is provided with a four-way switching valve (12), a liquid side closing valve (53), and a gas side closing valve (54).
  • one end of the liquid side connecting pipe (21) is connected to the liquid side closing valve (53), and one end of the gas side connecting pipe (22) is connected to the gas side closing valve (54).
  • One end is connected to each other!
  • the compressor (11) is a scroll compressor, and is configured such that the operation capacity is variable by inverter control.
  • One end of the suction pipe (61) is connected to the suction side of the compressor (11), and the other end of the suction pipe (61) is connected to the four-way switching valve (12).
  • One end of a discharge pipe (64) is connected to the discharge side of the compressor (11), and the other end of the discharge pipe (64) is connected to the four-way switching valve (12).
  • the outdoor heat exchange (13) is a cross fin type fin 'and' tube type heat exchange.
  • the first liquid pipe (81) is provided with a check valve (CV-1) that allows only the refrigerant to flow from the outdoor heat exchanger (13) to the receiver (14). At the bottom of the receiver (14) One end of the second liquid pipe (82) is connected.
  • the refrigerant heat exchanger (50) is a plate heat exchanger that exchanges heat between the refrigerant and the refrigerant.
  • the other end of the second liquid pipe (82) is connected to the inlet side of the first flow path (50a) of the refrigerant heat exchanger (50), and the outlet side of the first flow path (50a) is connected to the first flow path (50a).
  • One end of the three-liquid pipe (83) is connected.
  • the other end of the third liquid pipe (83) is connected to one end of the liquid side connecting pipe (21) via the liquid side closing valve (53).
  • the third liquid pipe (83) is provided with a check valve (CV-2) that allows only the flow of directional refrigerant to the first flow path (50a) force liquid side shut-off valve (53),
  • the third liquid pipe (83) is provided with a check valve (CV-2) that allows only the flow of directional refrigerant to the first flow path (50
  • branch liquid pipe (84) One end of the branch liquid pipe (84) is connected to the third liquid pipe (83) upstream of the check valve (CV-2), and the other end of the branch liquid pipe (84) is connected to the third liquid pipe (83).
  • the refrigerant heat exchanger (50) is connected to the inlet side of the second flow path (50b).
  • the branch liquid pipe (84) is provided with a branch expansion valve (46).
  • the branch expansion valve (46) is an electronic expansion valve whose opening degree is adjustable.
  • the outlet side of the second flow path (50b) of the refrigerant heat exchanger (50) is connected to one end of an injection pipe (85).
  • the other end of the injection pipe (85) is connected between the four-way switching valve (12) and the compressor (11) in the suction pipe (61).
  • a fourth liquid pipe (88) is connected between the check valve (CV-2) and the liquid side stop valve (53).
  • the other end of the fourth liquid pipe (88) is connected between the check valve (CV-1) and the receiver (14) in the first liquid pipe (81).
  • the fourth liquid pipe (88) is provided with a check valve (CV-3) that allows only the flow of the refrigerant directed from the third liquid pipe (83) to the receiver (14).
  • One end of a fifth liquid pipe (89) is connected to the branch liquid pipe (84) between the third liquid pipe (83) and the branch expansion valve (46).
  • the other end of the pipe (89) is connected between the other end of the outdoor heat exchanger (13) in the first liquid pipe (81) and the check valve (CV-1).
  • the fifth liquid pipe (89) is provided with an outdoor expansion valve (45).
  • the first port is at the discharge pipe (64), the second port is at the suction pipe (61), and the third port is at one end of the outdoor heat exchange (13),
  • the 4th port is connected to each gas side shutoff valve (54).
  • the four-way selector valve (12) is in a first state (actually shown in FIG. 1) in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other. Switch between the first port and the fourth port and the second port and the third port (shown in broken lines in Fig. 1). It is configured to be possible.
  • the outdoor circuit (20) includes an oil separator (70) and an oil return pipe (71).
  • the oil separator (70) is provided in the discharge pipe (64) and separates the discharge gas power refrigerating machine oil of the compressor (11).
  • One end of the first oil return pipe (71) is connected to the oil separator (70), and the other end of the first oil return pipe (71) is connected to the injection pipe (85) of the suction pipe (61). It is connected between the connection part and the compressor (11).
  • the oil return pipe (71) is provided with a capillary tube (72) for adjusting the flow rate of the refrigerating machine oil.
  • the suction pipe (61) of the compressor (11) has a suction temperature sensor (24) and a connection between the connection of the injection pipe (85) and the connection of the oil return pipe (71).
  • a suction pressure sensor (25) is provided in order.
  • the suction pressure sensor (25) is connected to the suction pipe (61) via a heat absorption pipe (90) as a feature of the present invention.
  • a discharge pressure sensor (23) and a discharge temperature sensor (19) are provided on the discharge side of the compressor (11).
  • a temperature sensor (51) is provided on the outlet side of the first flow path (50a) of the refrigerant heat exchanger (50).
  • the outdoor unit (2) is provided with an outdoor air temperature sensor (13a) and an outdoor fan (13f). Outdoor air is sent to the outdoor heat exchanger (13) by this outdoor fan (13f).
  • the refrigerator internal circuit (30) of the refrigeration unit (3) is provided with two refrigeration heat exchangers (16, 17) and two drain pan heaters (26, 27).
  • Each of the refrigerated heat exchanges ⁇ (16, 17) is the same cross fin type fin 'and' tube type heat exchange ⁇ , and heat exchange is performed between the refrigerant and the air in the cooling chamber. It is configured in the evaporator.
  • One end of each refrigeration heat exchanger (16, 17) is connected to each refrigeration expansion valve (15a, 15b) via a pipe.
  • one end of each gas side branch pipe (22a, 22b) is connected to the other end of each of the refrigeration heat exchangers (16, 17).
  • the other ends of (22a, 22b) join together and are connected to the other end of the gas side connecting pipe (22).
  • Each of the refrigeration expansion valves (15a, 15b) is an electronic expansion valve configured to be adjustable in opening, and is configured as an expansion mechanism.
  • Each refrigeration heat exchanger (16, 17) is provided with a first refrigerant temperature sensor (16b, 17b), and the other refrigeration heat exchanger (16, 17) has a second refrigerant at the other end.
  • Temperature sensors (18a, 18b) are respectively provided.
  • the first refrigerant temperature sensors (16b, 17b) measure the evaporation temperature of the refrigerant in the refrigeration heat exchanger (16, 17).
  • the refrigeration expansion valve (15a, 15b) has a refrigerant evaporating temperature at which the measured temperature of the second refrigerant temperature sensor (18a, 18b) is measured by the first refrigerant temperature sensor (16b, 17b).
  • the opening degree is adjusted so as to be higher than a predetermined temperature (for example, 5 ° C.).
  • the drain pan heaters (26, 27) are not shown in the figure, and are disposed in the drain pan, and prevent the drain pan from forming frost and generating ice by flowing a high-temperature and high-pressure refrigerant and heating the drain pan. It is.
  • One end of each drain pan heater (26, 27) is connected to one end of each liquid side branch pipe (21a, 21b), and the other end of each liquid side branch pipe (21a, 21b) joins each other. It is connected to the other end of the liquid side communication pipe (21).
  • the other end of the drain pan heater (26, 27) is connected to one end of the refrigeration expansion valve (15a, 15b).
  • the refrigeration unit (3) is provided with cooling room temperature sensors (16a, 16b) and cooling room fans (16f, 17f). Air in the cooling chamber is sent to the refrigeration heat exchangers (16, 17) by the fans (16f, 17f) in the cooling chamber.
  • the controller (100) performs switching and opening adjustment of various valves provided in the refrigerant circuit (10) to control a cooling operation operation for maintaining the cooling chamber at a set temperature, and for controlling the cooling chamber.
  • the defrosting operation is controlled.
  • the suction pressure sensor (25) is connected to the suction pipe (61) of the compressor (11) via the heat absorption pipe (90) as shown in FIGS. Furthermore, the heat absorption pipe (90) is connected to the discharge pipe (64) of the compressor (11) by a heat transfer member (91).
  • the heat absorption pipe (90) is for making the temperature of the connection part (25b) of the suction pressure sensor (25) higher than the temperature of the suction pipe (61).
  • one end of the endothermic pipe (90) is connected to the middle of the suction pipe (61) of the compressor (11).
  • the heat-absorbing pipe (90) is formed with a pipe diameter thinner than that of the suction pipe (61) and a length of 20 cm, and is bent four times to be compact. Further, a male screw (not shown) is formed on the outer periphery of the other end of the heat absorption pipe (90).
  • the suction pressure sensor (25) includes a sensor body (25a) and a connection portion (25b), and a female screw (not shown) is formed on the inner peripheral surface of the connection portion (25b).
  • the suction pressure sensor (25) is attached to the heat absorbing pipe (90) by screwing the female screw of the connecting portion (25b) with the male screw at the other end of the heat absorbing pipe (90). ing.
  • an L-shaped port tube (90a) having a gauge port (26) is connected to the other end of the heat absorption pipe (90).
  • the heat transfer member (91) is formed in a plate shape having an L-shaped cross section.
  • the heat transfer member (91) in the lateral direction is fixed to the downstream side of the oil separator (70) in the discharge pipe (64), while the other end is on the other end side of the heat absorption pipe (90) ( It is fixed to the connection part (25b) of the suction pressure sensor (25).
  • the lower end side of the heat transfer member (91) is fixed to the port thin tube (90a).
  • the heat transfer member (91) also has a function as a support member that supports the heat absorption pipe (90).
  • Fig. 3 shows the evaporating temperature of the refrigerated heat exchanger (16, 17) and the length of the endothermic pipe (90) at which the connection part (25b) of the suction pressure sensor (25) is 10 ° C. It is a figure which shows a relationship.
  • pipe structure A is a structure in which the heat absorption pipe (90) is not connected by the discharge pipe (64) of the compressor (11) and the heat transfer member (91).
  • Heat transfer pipe (90) and discharge pipe (64) Show the structure connected by member (91)!
  • the length of the endothermic pipe (90) at which the temperature of the connection part (25b) of the suction pressure sensor (25) is 10 ° C is the evaporation of the refrigeration heat exchange (16, 17).
  • the temperature was 20cm at -10 ° C, 48cm at -30 ° C, and 57cm at -40 ° C. This is because the temperature of the refrigerant flowing through the suction pipe (61) decreases as the evaporation temperature of the refrigerated heat exchanger (16, 17) decreases, so the cold heat is used to connect the connection part (25b) of the suction pressure sensor (25). This is because it is necessary to increase the area of the heat absorption pipe (90) and increase the amount of heat absorbed by the heat absorption pipe (90) from the surrounding air.
  • the length of the endothermic pipe (90) at which the temperature of the connection part (25b) of the suction pressure sensor (25) is 10 ° C is refrigerated heat exchange (16, 17 ) Is 10cm at 10 ° C, 25cm at 30 ° C, and 32cm at 40 ° C.
  • the length needs to be increased as the evaporation temperature decreases.
  • the length can be shortened compared to A. This is because the heat absorption pipe (90) can absorb heat from the discharge pipe (64) of the high-temperature compressor (11) via the heat transfer member (91), and therefore absorbs heat only from the surrounding air. This is because the endothermic amount of the endothermic pipe (90) can be increased with certainty.
  • the temperature of the connection part (25b) of the suction pressure sensor (25) may be higher than at least 0 degrees so as not to freeze the connection part (25b).
  • the length to be considered was examined. This is because if the length of the endothermic pipe (90) is set to a length where the temperature of the connection (25b) is higher than 0 ° C, the evaporation temperature of the refrigeration heat exchanger (16, 17) will be This is because the temperature of the connecting part (25b) can be surely raised above 0 ° C even if it temporarily falls due to fluctuations in the cooling load.
  • the minimum length of the heat absorption pipe (90) was set to the length shown in FIG.
  • the evaporation temperature of the refrigeration heat exchanger (16, 17) is
  • the endothermic pipe (90) needs to be 10cm or more in piping structure B. Therefore, the endothermic pipe (90) is formed to a length of 20 cm, which is an arbitrary length of 10 cm or more.
  • the four-way selector valve (12) of the outdoor circuit (20) is set to the first state by the control of the controller (100).
  • the outdoor expansion valve (45) is fully closed.
  • the compressor (11) is operated, the refrigeration expansion valves (15a, 15b) and the branch expansion valve (46) are appropriately controlled in opening degree, and the refrigerant circulates in the direction indicated by the solid line arrow in FIG. .
  • the set temperature of the cooling chamber in this cooling operation is, for example, 2 ° C.
  • the refrigerant discharged from the compressor (11) is sent from the discharge pipe (64) to the outdoor heat exchanger (13) through the four-way switching valve (12).
  • the outdoor heat exchanger (13) the refrigerant dissipates heat to the outdoor air and condenses.
  • the refrigerant condensed in the outdoor heat exchanger (13) flows through the first liquid pipe (81), passes through the receiver (14), flows into the second liquid pipe (82), and enters the refrigerant heat exchanger (50 ) In the first flow path (50a). .
  • the liquid refrigerant that has flowed through the first flow path (50a) flows through the third liquid pipe (83), and a part of the refrigerant is used as a branching refrigerant as shown by the broken line arrow in FIG. , Is decompressed by the branch expansion valve (46), and flows into the second flow path (50b) of the refrigerant heat exchanger (50).
  • the liquid refrigerant flowing through the first flow path (50a) exchanges heat with the branched refrigerant flowing through the second flow path (50b) .
  • the third liquid pipe ( 83) flows through the liquid side connecting pipe (21) via the liquid side shut-off valve (53) and flows into the refrigerator circuit (30).
  • the branched liquid refrigerant in the second flow path (50b) evaporates and is indicated to the suction pipe (61) of the compressor (11) through the instruction pipe (85).
  • the liquid refrigerant power at 15 ° C is diverted to the liquid side branch pipes (21a, 21b), flows through the drain pan heaters (26, 27), and the drain pans (56, 57) Prevent frost formation.
  • the liquid refrigerant that has also drained the drain pan heater (26, 27) is decompressed and expanded when passing through each refrigeration expansion valve (15a, 15b) and introduced into each refrigeration heat exchanger (16, 17). Is done.
  • the refrigerant absorbs heat from the air in the cooling chamber and evaporates at an evaporation temperature of, for example, 10 ° C.
  • the air cooled by the refrigeration heat exchanger (16, 17) is supplied into the cooling chamber, and the temperature in the cooling chamber is maintained at the set temperature of 2 ° C.
  • each of the refrigeration heat exchangers (16, 17) flows through the gas side branch pipes (22a, 22b), and then joins in the gas side communication pipe (22). Thereafter, the gas refrigerant flows through the gas side connecting pipe (22), flows through the suction pipe (61) through the four-way switching valve (12), and is sucked into the compressor (11) and compressed.
  • the suction pressure sensor (25) is endothermic. It is connected to the suction pipe (61) via the pipe for piping (90), and further connected to the heat absorption pipe (90), the discharge pipe (64) of the compressor (11) and the heat transfer member (91). Therefore, the connection part (25b) of the suction pressure sensor (25) is not frozen and damaged. Furthermore, as shown in Fig. 3, if the evaporation temperature of the refrigerated heat exchanger (16, 17) is 23 ° C or higher, the temperature of the connection part (25b) of the suction pressure sensor (25) is reliably 10 ° C. As described above, even when the cooling load fluctuates during the cooling operation, the connecting portion (25b) can be surely brought to a temperature higher than 0 ° C.
  • the refrigeration apparatus (1) is configured to perform the defrosting operation by temporarily stopping the cooling operation.
  • the operation during the defrosting operation is not shown, but the four-way selector valve (12) is set to the second state, the refrigeration expansion valves (15a, 15b) are fully open, and the branch expansion valve (46) is fully closed.
  • the outdoor expansion valve (45) is appropriately controlled, and reverse cycle defrost is performed in which the refrigerant circulates in the reverse direction to that during the cooling operation.
  • the discharged gas refrigerant of the compressor (11) flows through each refrigeration heat exchanger (16, 17) and each drain pan heater (26, 27), and each refrigeration heat exchange (16, 17)
  • the frost adhering to the drain pan dissipates heat and condensates and flows through the fourth liquid pipe (88) of the outdoor circuit (20).
  • the refrigerant flows through the liquid side communication pipe (21) and is introduced into the outdoor circuit (20), and then flows through the fourth liquid pipe (88), and the refrigerant heat exchange (50) between the receiver (14) and the refrigerant (50). It flows through one channel (50a).
  • the refrigerant flows through the fifth liquid pipe (89)
  • the refrigerant is expanded by the outdoor expansion valve (45), condensed by the outdoor heat exchanger (13), and sucked into the compressor (11).
  • the heat absorption pipe (90) can make it difficult to transmit the cold heat of the refrigerant flowing through the suction pipe (61) to the connection part (25b) of the suction pressure sensor (25).
  • the heat absorption pipe (90) can absorb the surrounding air and discharge pipe (64) force. This
  • the connection part (25b) of the suction pressure sensor (25) is higher than 0 ° C. Temperature.
  • freezing damage to the connection portion (25b) of the suction pressure sensor (25) can be prevented, and the reliability of the suction pressure sensor (25) is improved.
  • damage can be prevented without filling with silicon or brazing, workability at the time of installing and replacing the suction pressure sensor (25) is improved as compared with the conventional damage prevention measures.
  • the heat absorption pipe (90) absorbs heat from the discharge pipe (64) of the refrigerant circuit (10) via the heat transfer member (91), the heat absorption pipe (90) absorbs heat. The amount of heat can be increased. Thereby, the connection part (25b) of the suction pressure sensor (25) can be set to a temperature higher than 0 ° C.
  • the heat absorption pipe (90) can absorb the heat of the discharge pipe (64) of the compression mechanism (11) via the heat transfer member (91), the compression mechanism (11) Since the discharge pipe (64) has a high temperature, the heat absorption amount of the heat absorption pipe (90) can be reliably increased. As a result, the connection part (25b) of the suction pressure sensor (25) can be surely brought to a temperature higher than 0 ° C.
  • the heat absorption pipe (90) is formed to a length of 20 cm and is further connected by the discharge pipe (64) and the heat transfer member (91). 91) It is possible to prevent freezing only by forming the endothermic pipe (90) to a predetermined length. That is, as shown in Fig. 3, even in the piping structure A where the endothermic pipe (90) is not connected to the discharge pipe (64), the length of the endothermic pipe (90) is If the set length is set to be longer as the evaporation temperature is lower, such as 20 cm or more and 48 cm or more at -30 ° C, the connection part (25b) of the suction pressure sensor (25) should be 10 ° C or more. can do . Therefore, if the length of the endothermic pipe (90) is set to be longer than this length, the connecting part (25b) that connects the endothermic pipe (90) to the discharge pipe (64) can be reliably Freezing damage can be prevented by raising the temperature.
  • the endothermic pipe (90) is connected to the temperature of the connection (25b) of the suction pressure sensor (25).
  • the degree may be such that the temperature rises from the suction pipe (61) according to the ambient temperature.
  • the minimum length of the endothermic pipe (90) may be set to a predetermined set length that becomes longer as the evaporation temperature of the evaporator (16, 17) becomes lower.
  • the endothermic pipe (90) may be installed at any position! /,
  • the endothermic pipe (90) is located near the discharge pipe (64). If installed in this manner, the heat of the high-temperature discharge pipe (64) is transmitted through the air, and the amount of heat absorption can be further increased.
  • the length of the endothermic pipe (90) shown in Fig. 3 is merely an example, and the length of the endothermic pipe (90) is the same as that of the endothermic pipe (90). It is preferable to set the temperature appropriately depending on the ambient temperature conditions, the heat conductivity of the heat transfer member (91), the temperature of the discharge pipe (64) of the compressor (11), and the like. If the evaporation temperature of the evaporator (16, 17), where the cooling load fluctuation of the refrigeration system (1) is small, the length of the heat absorption pipe (90) is connected to the suction pressure sensor (25). The temperature of the part (25b) may be set to a length that becomes, for example, 1 ° C.
  • the refrigeration apparatus (1) of the above embodiment has performed a refrigeration cycle in which the refrigerant is compressed by one stage. It is also possible to perform a refrigeration cycle that compresses the two stages. In that case, since the temperature of the refrigerant flowing through the suction pipe of the low-stage compressor becomes very low, even if a pressure sensor for measuring the pressure of this low-temperature refrigerant is attached to the suction pipe via the heat absorption pipe. Good. Further, the heat absorption pipe may be connected to the high pressure side pipe of the refrigerant circuit or the discharge pipe through which the refrigerant discharged from the low stage compressor flows through a heat transfer member.
  • the endothermic pipe (90) is connected to the discharge pipe (64) of the compressor, but is connected to the other high-pressure side pipe of the refrigerant circuit (10). May be.
  • the first to third liquid pipes (81, 82, 83) are exemplified.
  • the compression mechanism (11) is composed of one compressor (11).
  • the compression mechanism (11) may be composed of a plurality of compressors connected in parallel.
  • the present invention is useful for a refrigeration apparatus including a suction pressure sensor that measures the suction pressure of a compression mechanism.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un mécanisme de réfrigération dans lequel une soupape de dilatation de réfrigération, un échangeur de chaleur de réfrigération, un compresseur (11) et un échangeur de chaleur d'extérieur sont interconnectés séquentiellement, ledit mécanisme comprenant un circuit de réfrigérant permettant de réaliser un cycle de réfrigération par compression de vapeur. Un capteur de pression d'aspiration (25) est attaché à un tube d'aspiration (61) du compresseur (11) par un tube d'absorption de chaleur (90). Le tube d'absorption de chaleur (90) est connecté à un tube d'évacuation (64) du compresseur (11) par un élément de transmission de chaleur (91). La longueur du tube d'absorption de chaleur (90) est supérieure ou égale à une longueur minimum prédéterminée, qui est plus grande lorsque la température de la vapeur dans l'échangeur de chaleur de réfrigération est plus faible.
PCT/JP2007/060151 2006-05-18 2007-05-17 Mécanisme de réfrigération WO2007135957A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07743586A EP2019273A1 (fr) 2006-05-18 2007-05-17 Mécanisme de réfrigération
US12/301,214 US20090188276A1 (en) 2006-05-18 2007-05-17 Refrigeration system
AU2007252631A AU2007252631A1 (en) 2006-05-18 2007-05-17 Refrigeration system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006139040A JP4082434B2 (ja) 2006-05-18 2006-05-18 冷凍装置
JP2006-139040 2006-05-18

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WO2007135957A1 true WO2007135957A1 (fr) 2007-11-29

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EP (1) EP2019273A1 (fr)
JP (1) JP4082434B2 (fr)
KR (1) KR20090013222A (fr)
CN (1) CN101449118A (fr)
AU (1) AU2007252631A1 (fr)
WO (1) WO2007135957A1 (fr)

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JP5585189B2 (ja) * 2010-04-30 2014-09-10 ダイキン工業株式会社 空気調和装置
JP5821384B2 (ja) * 2011-08-08 2015-11-24 ダイキン工業株式会社 センサの取付構造
JP2014163548A (ja) * 2013-02-22 2014-09-08 Fujitsu General Ltd 空気調和装置
CN103759477B (zh) * 2014-01-07 2016-06-29 广东美芝制冷设备有限公司 制冷循环装置
JP6431776B2 (ja) * 2015-01-19 2018-11-28 出光興産株式会社 潤滑油組成物
CN111855735B (zh) * 2020-08-06 2021-06-22 兰州理工大学 一种盐溶液盐胀及冻胀高效、精准测量装置

Citations (5)

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JPS50148Y1 (fr) * 1970-08-12 1975-01-06
JPS5116317Y1 (fr) * 1970-08-13 1976-04-28
JPH09329517A (ja) * 1996-06-10 1997-12-22 Fuji Koki:Kk 圧力検出装置
JP2002048665A (ja) * 2000-07-31 2002-02-15 Yamatake Corp 圧力測定装置のスチームジャケット構造
JP2004353996A (ja) 2003-05-30 2004-12-16 Daikin Ind Ltd 冷凍装置

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Publication number Priority date Publication date Assignee Title
JPH0431689A (ja) * 1990-05-24 1992-02-03 Hitachi Ltd スクロール圧縮機およびそれを用いた冷凍サイクル
JP2004301456A (ja) * 2003-03-31 2004-10-28 Toyota Industries Corp 冷凍サイクル装置及び冷凍サイクル装置用機器

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
JPS50148Y1 (fr) * 1970-08-12 1975-01-06
JPS5116317Y1 (fr) * 1970-08-13 1976-04-28
JPH09329517A (ja) * 1996-06-10 1997-12-22 Fuji Koki:Kk 圧力検出装置
JP2002048665A (ja) * 2000-07-31 2002-02-15 Yamatake Corp 圧力測定装置のスチームジャケット構造
JP2004353996A (ja) 2003-05-30 2004-12-16 Daikin Ind Ltd 冷凍装置

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US20090188276A1 (en) 2009-07-30
JP4082434B2 (ja) 2008-04-30
AU2007252631A1 (en) 2007-11-29
EP2019273A1 (fr) 2009-01-28
JP2007309586A (ja) 2007-11-29
KR20090013222A (ko) 2009-02-04
CN101449118A (zh) 2009-06-03

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