WO2017081781A1 - Dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement - Google Patents

Dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement Download PDF

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Publication number
WO2017081781A1
WO2017081781A1 PCT/JP2015/081798 JP2015081798W WO2017081781A1 WO 2017081781 A1 WO2017081781 A1 WO 2017081781A1 JP 2015081798 W JP2015081798 W JP 2015081798W WO 2017081781 A1 WO2017081781 A1 WO 2017081781A1
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Prior art keywords
refrigerant
stage compression
control valve
temperature sensor
gas
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PCT/JP2015/081798
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English (en)
Japanese (ja)
Inventor
中村　淳
賢哲 安嶋
修平 柴田
宏幸 寺脇
Original Assignee
富士電機株式会社
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Application filed by 富士電機株式会社 filed Critical 富士電機株式会社
Priority to PCT/JP2015/081798 priority Critical patent/WO2017081781A1/fr
Priority to JP2017549926A priority patent/JP6680300B2/ja
Publication of WO2017081781A1 publication Critical patent/WO2017081781A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
    • Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply

Definitions

  • the present invention relates to an exhaust heat recovery heat pump device that can reliably avoid liquid compression of a side compressor.
  • Some heat pump devices use a two-stage compression type in which two compressors, a low-pressure compressor and a high-pressure compressor, are provided on the heat pump cycle.
  • the 1st decompression device which decompresses the refrigerant
  • a heat pump heating device including a passage and a control unit that controls a pressure reduction ratio of the refrigerant
  • the amount of pressure reduction by the low-pressure side (low-stage side) expansion valve (second decompression device) is controlled to control the high-pressure side (high-stage side) compressor. Liquid compression is prevented.
  • the low-stage side refrigerant flow is reduced by controlling the low-stage side expansion valve, and the low-stage compressor discharge temperature is increased to increase the suction of the high-stage compressor. This realizes an overheated state of the refrigerant. Therefore, the overheated state cannot always be maintained depending on the amount of liquid refrigerant mixed into the intermediate pipe (injection pipe line).
  • the condensed refrigerant is stored in the gas-liquid separator, and the liquid refrigerant may flow out from the intermediate pipe when the apparatus is activated. large.
  • the present invention has been made in view of the above, and the high-stage compressor of the two-stage compressor mixes the intermediate-pressure refrigerant from the gas-liquid separator and the intermediate-pressure refrigerant from the low-stage compressor.
  • An object of the present invention is to provide an exhaust heat recovery heat pump device that can reliably avoid liquid compression of a high-stage compressor when the refrigerant operates as an intake refrigerant.
  • an exhaust heat recovery heat pump device compresses an evaporator that evaporates the refrigerant with heat recovered from an external heat source, and the refrigerant evaporated in the evaporator
  • a low-stage compression mechanism a high-stage compression mechanism that compresses the refrigerant compressed by the low-stage compression mechanism, a condenser that condenses the refrigerant compressed by the high-stage compression mechanism and heats heated water, and A high-stage expansion mechanism that decompresses and expands the refrigerant condensed by the condenser, a gas-liquid separator that separates the refrigerant introduced from the high-stage expansion mechanism, and a liquid-side outlet of the gas-liquid separator.
  • a low-stage expansion mechanism that expands the refrigerant further under reduced pressure and introduces the refrigerant into the evaporator; and a refrigerant discharged from a gas-side outlet of the gas-liquid separator, and a discharge port of the low-stage compression mechanism and a high-stage compression mechanism
  • the present invention is characterized in that a refrigerant adjusting mechanism to be introduced into the suction port is provided.
  • the refrigerant adjustment mechanism is provided in the gas-liquid separator, and is provided in a level sensor for detecting a liquid level position and in the intermediate pipe.
  • the refrigerant adjustment mechanism includes a high-stage compression suction temperature sensor that detects a refrigerant temperature sucked into the high-stage compression mechanism, and the high-stage compression. Based on detection values of a high-stage compression suction pressure sensor that detects a refrigerant pressure sucked into the mechanism, a flow control valve provided in the intermediate pipe, the high-stage compression suction temperature sensor, and the high-stage compression suction pressure sensor And a controller for controlling the flow rate control valve.
  • the control unit is a saturated refrigerant calculated from a detection value of the high-stage compression suction temperature sensor and a detection value of the high-stage compression suction pressure sensor.
  • the opening degree of the flow control valve is adjusted so that the temperature difference from the temperature is greater than or equal to a predetermined value.
  • the refrigerant adjustment mechanism includes a high-stage compression suction temperature sensor that detects a refrigerant temperature sucked into the high-stage compression mechanism, and the high-stage expansion.
  • a high-stage expansion / discharge pressure sensor for detecting the pressure of refrigerant decompressed and expanded by the mechanism, a flow control valve provided in the intermediate pipe, detection values of the high-stage compression / intake temperature sensor and the high-stage expansion / discharge pressure sensor And a control unit for controlling the flow rate control valve based on the above.
  • the control unit is a saturated refrigerant calculated from a detection value of the high stage compression suction temperature sensor and a detection value of the high stage expansion discharge pressure sensor.
  • the opening degree of the flow control valve is adjusted so that the temperature difference from the temperature is greater than or equal to a predetermined value.
  • the refrigerant adjustment mechanism includes a high-stage compression suction temperature sensor that detects a refrigerant temperature sucked into the high-stage compression mechanism, and the high-stage expansion.
  • a high-stage expansion / discharge temperature sensor for detecting the temperature of the refrigerant decompressed and expanded by the mechanism, a flow control valve provided in the intermediate pipe, detection values of the high-stage compression / intake temperature sensor and the high-stage expansion / discharge temperature sensor And a control unit for controlling the flow rate control valve based on the above.
  • the control unit predetermines a temperature difference between a detection value of the high stage compression suction temperature sensor and a detection value of the high stage expansion discharge temperature sensor.
  • the opening degree of the flow control valve is adjusted so as to be equal to or greater than the value.
  • the exhaust heat recovery heat pump device is characterized in that, in the above invention, the intermediate pipe is provided with heating means for heating the refrigerant discharged from the gas side outlet of the gas-liquid separator.
  • the refrigerant adjustment mechanism is provided in the intermediate pipe, and heating means for heating the refrigerant derived from the gas-liquid separator; and the intermediate pipe
  • a heating refrigerant temperature sensor for detecting a refrigerant temperature at the outlet side of the heating means, a high stage compression suction pressure sensor for detecting a refrigerant pressure sucked into the high stage compression mechanism, and a flow control valve provided in the intermediate pipe
  • a control unit that controls the flow rate control valve based on detection values of the heating refrigerant temperature sensor and the high-stage compression suction pressure sensor.
  • the control unit includes a saturated refrigerant temperature calculated from a detection value of the heating refrigerant temperature sensor and a detection value of the high-stage compression suction pressure sensor.
  • the opening degree of the flow control valve is adjusted so that the temperature difference between the two is equal to or greater than a predetermined value.
  • the refrigerant adjustment mechanism is provided in the intermediate pipe, and heating means for heating the refrigerant derived from the gas-liquid separator; and the intermediate pipe
  • a heating refrigerant temperature sensor for detecting the refrigerant temperature at the outlet side of the heating means, a high stage expansion discharge pressure sensor for detecting the pressure of the refrigerant decompressed and expanded by the high stage expansion mechanism, and a flow rate provided in the intermediate pipe
  • a control unit that controls the flow rate control valve based on detection values of the high stage expansion discharge pressure sensor and the heating refrigerant temperature sensor.
  • the control unit includes a saturated refrigerant temperature calculated from a detection value of the heating refrigerant temperature sensor and a detection value of the high stage expansion discharge pressure sensor.
  • the opening degree of the flow control valve is adjusted so that the temperature difference between the two is equal to or greater than a predetermined value.
  • the refrigerant adjustment mechanism is provided in the intermediate pipe, and heating means for heating the refrigerant derived from the gas-liquid separator; and the intermediate pipe
  • a heating refrigerant temperature sensor for detecting the refrigerant temperature on the outlet side of the heating means, a high stage expansion discharge temperature sensor for detecting the temperature of the refrigerant decompressed and expanded by the high stage expansion mechanism, and a flow rate provided in the intermediate pipe
  • a control unit that controls the flow rate control valve based on detection values of the high stage expansion discharge temperature sensor and the heating refrigerant temperature sensor.
  • the control unit sets a temperature difference between a detection value of the heating refrigerant temperature sensor and a detection value of the high stage expansion discharge temperature sensor to a predetermined value or more.
  • the opening degree of the flow control valve is adjusted so that
  • the heating means is an internal heat exchanger that performs heat exchange between the refrigerant discharged from the condenser and the refrigerant flowing through the intermediate pipe. It is characterized by being.
  • the exhaust heat recovery heat pump device is the above invention, wherein the refrigerant has an intersection or contact of two or more saturated gas lines and isentropic lines in the superheated region on the Ph diagram. It has the characteristic which has.
  • the mixed refrigerant of the refrigerant discharged from the gas side outlet of the gas-liquid separator and the refrigerant compressed by the low-stage compression mechanism is used as a gas refrigerant having a superheat degree equal to or higher than a predetermined value. Since the refrigerant adjustment mechanism to be introduced into the suction port is provided, it is possible to reliably avoid liquid compression of the high stage compressor.
  • FIG. 1 is an overall configuration diagram of an exhaust heat recovery heat pump device according to Embodiment 1 of the present invention. It is a Ph diagram of R245fa including a saturated gas line and an isentropic line.
  • 2 is a configuration diagram of a refrigerant adjustment mechanism in a heat pump unit in Embodiment 1.
  • FIG. 3 is a schematic diagram showing an internal configuration of a gas-liquid separator 4.
  • FIG. 6 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism according to Embodiment 2.
  • FIG. 6 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism according to Embodiment 3.
  • FIG. FIG. 6 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism in a fourth embodiment.
  • FIG. 6 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism provided with heating means in Embodiment 2.
  • FIG. FIG. 10 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism in a fifth embodiment.
  • FIG. 10 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism in a sixth embodiment.
  • FIG. 10 is a configuration diagram of a heat pump unit including a refrigerant adjustment mechanism in a seventh embodiment. It is a block diagram of the heat pump part containing the refrigerant
  • FIG. 1 is an overall configuration diagram of an exhaust heat recovery heat pump apparatus 10 according to Embodiment 1 of the present invention.
  • the exhaust heat recovery heat pump device 10 is a system that recovers exhaust heat from warm water such as factory waste water and generates steam using the recovered exhaust heat.
  • the generated steam is external steam such as a drying device or a sterilizer. Sent to the use facility.
  • a high-stage compression mechanism 1b that compresses the refrigerant, a condenser 2 that condenses the refrigerant compressed by the high-stage compression mechanism and heats the water to be heated, and a high-stage expansion that decompresses and expands the refrigerant condensed by the condenser 2
  • a low-stage expansion mechanism 5 to be introduced an intermediate pipe L1 for introducing refrigerant discharged from the gas side outlet of the gas-liquid separator 4 between the discharge port of the low-stage compression mechanism and the suction port of the high-stage compression mechanism; And an open / close control valve 7 provided in the intermediate pipe L1.
  • the heater 2 a is connected between the outlet side of the condenser 2 and the high stage expansion mechanism 3.
  • the high stage expansion mechanism 3 and the low stage expansion mechanism 5 are, for example, electronic expansion valves.
  • the open / close control valve 7 is, for example, an electric valve.
  • the refrigerant flowing in the heat pump cycle of the heat pump unit 16 has an isentropic line L11 on the Ph diagram in the superheated region on the low pressure side and an isentropic line with the saturated gas line L12 on the high pressure side.
  • L11 is a refrigerant having the characteristic of having two or more intersections or contact points.
  • This refrigerant is, for example, 1,1,1,3,3-pentafluoropropane (structural formula: CHF 2 CH 2 CF 3 , R245fa).
  • FIG. 2 shows a Ph diagram of R245fa, where the saturated gas line L12 and the isentropic line L11 intersect at two points PP1 and PP2.
  • the refrigerant that has been compressed by the high-stage compression mechanism 1b to a high temperature and high pressure is cooled and condensed by exchanging heat with water circulating in the steam generation unit 12 in the condenser 2.
  • the refrigerant exiting the condenser 2 is preheated with water heated in the water supply path 30 by the heater 2 a and further cooled, and then decompressed and expanded by the high stage expansion mechanism 3 and introduced into the gas-liquid separator 4.
  • the refrigerant discharged from the liquid-side outlet of the gas-liquid separator 4 is further decompressed and expanded by the low-stage expansion mechanism 5, and is evaporated by absorbing heat from the heat source hot water flowing through the hot water path 32 of the hot water supply unit 14 in the evaporator 6.
  • the refrigerant discharged from the gas side outlet of the gas-liquid separator 4 passes through the intermediate pipe L1 provided with the open / close control valve 7 and the discharge port of the low stage compression mechanism 1a and the suction port of the high stage compression mechanism 1b.
  • the refrigerant is mixed with the refrigerant discharged from the low-stage compression mechanism 1a and introduced into the suction port of the high-stage compression mechanism 1b.
  • the steam generating unit 12 uses the refrigerant circulating in the heat pump unit 16 as a heat source to evaporate water to generate steam, and the vapor-liquid two-phase flow including water and steam generated by the condenser 2 is converted into steam.
  • a water vapor separator 42 that separates into water
  • a steam supply path 44 that supplies the steam separated by the water vapor separator 42 to an external steam utilization facility, and water that is separated by the water vapor separator 42 is supplied from the water supply path 30.
  • a water circulation path 46 that joins the water to be led from the condenser 2 to the water vapor separator 42.
  • the water vapor separator 42 is formed of a cylindrical container along the vertical direction, and stores water inside the container by supplying water from the water supply path 30 connected to the water circulation path 46 connected to the lower end wall. .
  • water water supply
  • a water pipe or a water tank (not shown) is introduced to the water circulation path 46 through the heater 2 a by the water supply pump 48.
  • the feed water pump 48 is operated at its rotational speed via an inverter (INV) 52 based on a detection value (water level) of a water level sensor 50 that measures the water level of water stored in the water vapor separator 42. Is controlled.
  • a pressure relief valve 54 Connected to the water vapor separator 42 is a pressure relief valve 54 that is opened when the internal vapor pressure exceeds a predetermined pressure.
  • the water circulation path 46 includes a liquid pipe 46 a that communicates from the lower end wall of the steam separator 42 to the condenser 2, and a steam pipe 46 b that communicates from the condenser 2 to the upper side wall of the steam separator 42. Water flows through the liquid pipe 46a, and a gas-liquid two-phase flow containing water and steam flows through the steam pipe 46b.
  • a circulation pump 56 is provided in the liquid pipe 46a. The operation speed of the circulation pump 56 is controlled through an inverter (INV) 58 under the control of the control unit 20.
  • the steam supply path 44 is a path that is connected to the upper end wall of the water vapor separator 42 and is supplied into the water vapor separator 42 from the steam pipe 46b, where the steam after the water is separated is sent out to the outside.
  • the steam supply path 44 is provided with a pressure adjustment valve (steam pressure adjusting means) 60 for adjusting the pressure of the flowing steam.
  • the opening degree of the pressure regulating valve 60 is adjusted based on the steam pressure in the steam separator 42 measured by the pressure sensor 62 under the control of the control unit 20. By appropriately adjusting the opening degree of the pressure regulating valve 60, the flow rate and pressure of the steam sent out from the exhaust heat recovery heat pump device 10 can be controlled.
  • a steam compressor that compresses steam instead of or together with the pressure adjusting valve 60 may be used.
  • the control unit 20 controls the operating rotational speeds of the low-stage compression mechanism 1a and the high-stage compression mechanism 1b through inverters (INV).
  • the control unit 20 controls the heating output of the heat pump unit 16 based on detection values of a sensor (not shown) that detects the pressure and temperature on the heat pump cycle.
  • the low-stage compression mechanism 1a and the high-stage compression mechanism 1b may be, for example, a single two-stage scroll compressor that shares a rotating shaft.
  • the control unit 20 may further perform opening control of the high stage expansion mechanism 3 and the low stage expansion mechanism 5.
  • control unit 20 may further control the water supply pump 48, the circulation pump 56, and the pressure regulating valve 60, but the steam generation unit 12 side may be controlled by another control unit (not shown). Good.
  • FIG. 3 is a configuration diagram of the refrigerant adjustment mechanism in the heat pump unit 16 according to the first embodiment.
  • FIG. 4 is a schematic diagram showing the internal configuration of the gas-liquid separator 4. Note that the condenser 2 shown in FIG. 3 may include a heater 2a, or may be configured without the heater 2a. As shown in FIG. 3, the gas-liquid separator 4 is provided with a level sensor 21 that detects the liquid level position.
  • the gas-liquid separator 4 includes a connection pipe 4a connected to the intermediate pipe L1 through the gas side communication port 4V, and a connection pipe 4b connected to the pipe to the low stage expansion mechanism 5 through the liquid side communication port 4L.
  • the control unit 20 opens and closes when the liquid level position detected by the level sensor 21 reaches a predetermined position between the liquid level position hb of the liquid side communication port 4L and the liquid level position ha of the gas side communication port 4V. Control to close the control valve 7 is performed. That is, the control unit 20 opens the opening / closing control valve 7 when the liquid level position detected by the level sensor 21 is less than the predetermined position, and closes the opening / closing control valve 7 when the level is equal to or greater than the predetermined position.
  • the predetermined position detected by the level sensor 21 may be at least less than the liquid level position ha.
  • the level sensor 21 may be a switch type that detects one point at a predetermined position, or may detect a liquid level position within a predetermined range including the predetermined position. Also, different values may be set for the predetermined value for opening and closing the open / close control valve 7 and the predetermined value for closing.
  • the liquid refrigerant in the gas-liquid separator 4 is connected to the discharge port of the low-stage compression mechanism 1a and the high-stage via the gas side communication port 4V and the intermediate pipe L1. It is possible to prevent introduction into the intermediate connection point PT between the compression mechanism 1b and the suction port. As a result, liquid refrigerant is not introduced into the suction port of the high-stage compression mechanism 1b, and liquid compression of the high-stage compression mechanism 1b can be prevented.
  • FIG. 5 is a configuration diagram of the heat pump unit 16 including the refrigerant adjustment mechanism in the second embodiment. As shown in FIG. 5, the refrigerant adjustment mechanism of the second embodiment is provided between the intermediate connection point PT and the high stage compression mechanism 1b, and detects the refrigerant temperature sucked into the high stage compression mechanism 1b.
  • the flow control valve 17 provided in L1 and the control part 20 which controls the flow control valve 17 based on the detected value of the high stage compression suction temperature sensor 22 and the high stage compression suction pressure sensor 23 are provided.
  • the control unit 20 determines that the temperature difference ⁇ T between the high stage compression suction temperature T1 detected by the high stage compression suction temperature sensor 22 and the saturation temperature Tsat1 at the high stage compression suction pressure P1 detected by the high stage compression suction pressure sensor 23 is
  • the opening degree of the flow control valve 17 is controlled so as to be equal to or greater than a predetermined value.
  • the control unit 20 sets the predetermined value of the temperature difference ⁇ T to 3K in order to reliably prevent liquid compression. Or about 5K to provide a margin for preventing liquid compression.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • FIG. 6 is a configuration diagram of the heat pump unit 16 including the refrigerant adjustment mechanism in the third embodiment.
  • the refrigerant adjustment mechanism of the third embodiment is provided between the intermediate connection point PT and the high stage compression mechanism 1b, and detects the refrigerant temperature sucked into the high stage compression mechanism 1b.
  • a high-stage expansion suction pressure sensor 24 provided between the high-stage expansion mechanism 3 and the gas-liquid separator 4 to detect the pressure of the refrigerant decompressed and expanded by the high-stage expansion mechanism 3;
  • the flow control valve 17 provided in the intermediate pipe L1 and the control unit 20 that controls the flow control valve 17 based on the detection values of the high stage compression suction temperature sensor 22 and the high stage expansion discharge pressure sensor 24 are provided.
  • the control unit 20 determines that the temperature difference ⁇ T between the high stage compression suction temperature T1 detected by the high stage compression suction temperature sensor 22 and the saturation temperature Tsat2 at the high stage expansion discharge pressure P2 detected by the high stage expansion discharge pressure sensor 24 is
  • the opening degree of the flow control valve 17 is controlled so as to be equal to or greater than a predetermined value.
  • the control unit 20 sets the predetermined value of the temperature difference ⁇ T to 3K in order to reliably prevent liquid compression. Or about 5K to provide a margin for preventing liquid compression.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • the high-stage expansion / discharge pressure sensor 24 may be a high-stage expansion / discharge pressure sensor 24 a that detects the pressure in the gas state in the gas-liquid separator 4, or between the gas-liquid separator 4 and the flow control valve 17. It is good also as the high stage expansion discharge pressure sensor 24b which detects the pressure in the intermediate pipe L1. In the third embodiment, it is preferable to apply when the pressure loss of the flow control valve 17 is small.
  • FIG. 7 is a configuration diagram of the heat pump unit 16 including the refrigerant adjustment mechanism in the fourth embodiment.
  • the refrigerant adjustment mechanism of the fourth embodiment is provided between the intermediate connection point PT and the high-stage compression mechanism 1b, and detects the refrigerant temperature sucked into the high-stage compression mechanism 1b.
  • the flow control valve 17 provided in the intermediate pipe L1 and the control unit 20 that controls the flow control valve 17 based on the detection values of the high stage compression suction temperature sensor 22 and the high stage expansion / discharge temperature sensor 25 are provided.
  • the temperature difference ⁇ T between the high-stage compression suction temperature T1 detected by the high-stage compression suction temperature sensor 22 and the saturation temperature Tsat3 (T2) detected by the high-stage expansion / discharge temperature sensor 25 becomes a predetermined value or more.
  • the opening degree of the flow control valve 17 is controlled.
  • the temperature detected by the high stage expansion discharge temperature sensor 25 is regarded as the saturation temperature Tsat3.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • the high-stage expansion / discharge temperature sensor 25 may be a high-stage expansion / discharge temperature sensor 25 a that detects the temperature of the gas state in the gas-liquid separator 4 or between the gas-liquid separator 4 and the flow control valve 17. It is good also as the high stage expansion discharge temperature sensor 25b which detects the temperature in the intermediate pipe L1. Moreover, in this Embodiment 4, it is preferable to apply when the pressure loss of the flow control valve 17 is small.
  • an internal heat exchanger 8 is provided between the gas-liquid separator 4 and the flow rate control valve 17 as a heating means.
  • the internal heat exchanger 8 is connected to the condenser 2 and the high stage expansion mechanism 3 and uses the heat of the refrigerant derived from the condenser 2 to derive the refrigerant derived from the gas side outlet of the gas-liquid separator 4. Heat.
  • the heating means may heat the refrigerant led out from the gas side outlet of the gas-liquid separator 4 using an external heat source such as a heater in addition to the internal heat exchanger 8 described above.
  • FIG. 9 is a configuration diagram of the heat pump unit 16 including the refrigerant adjustment mechanism in the fifth embodiment.
  • the refrigerant adjustment mechanism of the fifth embodiment is provided between the flow rate control valve 17 and the intermediate connection point PT, and is on the outlet side of the internal heat exchanger 8 (heating means) of the intermediate pipe L1.
  • the flow control valve 17 is controlled based on the detected values of the heating refrigerant temperature sensor 26 that detects the refrigerant temperature, the flow control valve 17 provided in the intermediate pipe L1, the heating refrigerant temperature sensor 26, and the high-stage compression suction pressure sensor 23.
  • a control unit 20 is controlled based on the detected values of the heating refrigerant temperature sensor 26 that detects the refrigerant temperature, the flow control valve 17 provided in the intermediate pipe L1, the heating refrigerant temperature sensor 26, and the high-stage compression suction pressure sensor 23.
  • the control unit 20 determines that the temperature difference ⁇ T between the heating refrigerant temperature T3 detected by the heating refrigerant temperature sensor 26 and the saturation temperature Tsat1 at the high stage compression suction pressure P1 detected by the high stage compression suction pressure sensor 23 is a predetermined value or more. Thus, the opening degree of the flow control valve 17 is controlled. By controlling the opening degree of the flow control valve 17 by the controller 20, the liquid refrigerant is prevented from being introduced into the high-stage compression mechanism 1b.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • the sixth embodiment prevents liquid compression of the high-stage compression mechanism 1b when the heating means shown in the modifications of the second to fourth embodiments is provided in the configuration of the heat pump unit 16 of the third embodiment. It is.
  • the controller 20 determines that the temperature difference ⁇ T between the heating refrigerant temperature T3 detected by the heating refrigerant temperature sensor 26 and the saturation temperature Tsat2 at the high stage expansion discharge pressure P2 detected by the high stage expansion discharge pressure sensor 24 is equal to or greater than a predetermined value.
  • the opening degree of the flow control valve 17 is controlled.
  • the liquid refrigerant is prevented from being introduced into the high-stage compression mechanism 1b.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • the seventh embodiment prevents liquid compression of the high-stage compression mechanism 1b when the heating means shown in the modification examples of the second to fourth embodiments is provided in the configuration of the heat pump unit 16 of the fourth embodiment. It is.
  • FIG. 11 is a configuration diagram of the heat pump unit 16 including the refrigerant adjustment mechanism in the seventh embodiment.
  • the refrigerant adjustment mechanism of the seventh embodiment is provided between the flow rate control valve 17 and the intermediate connection point PT, and is on the outlet side of the internal heat exchanger 8 (heating means) of the intermediate pipe L1.
  • a heating refrigerant temperature sensor 26 that detects the refrigerant temperature, and a high stage expansion discharge that is provided between the high stage expansion mechanism 3 and the gas-liquid separator 4 and detects the temperature of the refrigerant decompressed and expanded by the high stage expansion mechanism 3. It has a temperature sensor 25, a flow rate control valve 17 provided in the intermediate pipe L1, and a control unit 20 that controls the flow rate control valve 17 based on detected values of the heating refrigerant temperature sensor 26 and the high stage expansion discharge temperature sensor 25.
  • the control unit 20 controls the flow rate so that the temperature difference ⁇ T between the heating refrigerant temperature T3 detected by the heating refrigerant temperature sensor 26 and the saturation temperature Tsat3 (T2) detected by the high stage expansion discharge temperature sensor 25 becomes a predetermined value or more.
  • the opening degree of the valve 17 is controlled. By controlling the opening degree of the flow control valve 17 by the controller 20, the liquid refrigerant is prevented from being introduced into the high-stage compression mechanism 1b.
  • the temperature difference ⁇ T is positive, it can be seen that the refrigerant joined from the intermediate pipe L1 is in an overheated state, so the liquid of the high-stage compression mechanism 1b can be obtained without providing a margin for the temperature difference ⁇ T. Compression can be prevented.
  • control unit 20 increases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is equal to or greater than the upper limit value, and decreases the opening degree of the flow control valve 17 when the temperature difference ⁇ T is less than the lower limit value.
  • the control unit 20 may perform linear opening degree control based on the absolute value of the temperature difference ⁇ T. Further, the control unit 20 may perform opening degree control by PID control that brings the temperature difference ⁇ T closer to a predetermined value.
  • the high-stage expansion / discharge temperature sensor 25 may be a high-stage expansion / discharge temperature sensor 25 a that detects the temperature of the gas state in the gas-liquid separator 4, or the gas-liquid separator 4 and the internal heat exchanger 8.
  • a high-stage expansion / discharge temperature sensor 25b that detects the temperature in the intermediate pipe L1 may be used.
  • the heating refrigerant temperature sensor 26 may be a heating refrigerant temperature sensor 26 a provided between the outlet of the internal heat exchanger 8 and the flow rate control valve 17. In addition, in this Embodiment 7, it is preferable to apply when the pressure loss of the flow control valve 17 and the internal heat exchanger 8 is small.
  • the flow control valve 17 is provided on the upstream side (gas-liquid separator 4 side) of the internal heat exchanger 8.
  • the high stage expansion discharge temperature sensor 25 is provided between the internal heat exchanger 8 and the intermediate connection point PT, so that the fifth embodiment It is possible to obtain the same effects as those of .about.7.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention concerne un dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement conçu de sorte que la compression de liquide du compresseur d'étage supérieur d'un compresseur à deux étages peut être évitée de manière fiable lorsque le compresseur d'étage supérieur fonctionne à l'aide, en tant que fluide frigorigène d'aspiration, d'un fluide frigorigène mélangé comprenant un fluide frigorigène à pression intermédiaire provenant d'un séparateur gaz-liquide et un fluide frigorigène à pression intermédiaire provenant du compresseur d'étage inférieur. Ce dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement est équipé d'un mécanisme d'ajustement de fluide frigorigène qui introduit un fluide frigorigène mélangé, comprenant un fluide frigorigène évacué depuis la sortie côté gaz d'un séparateur gaz-liquide (4) et un fluide frigorigène comprimé par un mécanisme de compression d'étage inférieur (1a), dans l'ouverture d'aspiration d'un mécanisme de compression d'étage supérieur (1b), le fluide frigorigène mélangé faisant office de fluide frigorigène gazeux présentant un degré de surchauffe qui est une valeur prédéfinie, ou un degré supérieur. Le mécanisme d'ajustement de fluide frigorigène est équipé : d'un capteur de niveau (21) qui est disposé sur le séparateur gaz-liquide (4) de manière à détecter le niveau de liquide ; d'une soupape de commande d'ouverture et de fermeture (7) qui est placée sur un tuyau intermédiaire (L1) ; et d'une unité de commande (20) qui commande la soupape de commande d'ouverture et de fermeture (7) vers une position fermée si le niveau de liquide détecté par le capteur de niveau (21) atteint une position prédéfinie sur la base d'un orifice de communication côté gaz sur le tuyau intermédiaire (L1).
PCT/JP2015/081798 2015-11-11 2015-11-11 Dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement WO2017081781A1 (fr)

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PCT/JP2015/081798 WO2017081781A1 (fr) 2015-11-11 2015-11-11 Dispositif de type pompe à chaleur à récupération de chaleur de gaz d'échappement
JP2017549926A JP6680300B2 (ja) 2015-11-11 2015-11-11 排熱回収ヒートポンプ装置

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CN109579347A (zh) * 2018-12-04 2019-04-05 南京天加环境科技有限公司 一种能够避免压缩机回液的多联机系统及其控制方法
JP2020024046A (ja) * 2018-08-06 2020-02-13 富士電機株式会社 ヒートポンプ装置
CN111023508A (zh) * 2019-12-20 2020-04-17 Tcl空调器(中山)有限公司 一种空调器控制方法、存储介质及空调器
EP4145061A1 (fr) 2021-09-06 2023-03-08 Mitsubishi Heavy Industries Thermal Systems, Ltd. Appareil de réfrigération

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JP2014016079A (ja) * 2012-07-06 2014-01-30 Daikin Ind Ltd ヒートポンプ
JP2014119157A (ja) * 2012-12-14 2014-06-30 Sharp Corp ヒートポンプ式加熱装置

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JPH11142001A (ja) * 1997-11-06 1999-05-28 Daikin Ind Ltd 空気調和機
JP2006177597A (ja) * 2004-12-22 2006-07-06 Hitachi Home & Life Solutions Inc 冷凍装置及びこれを用いた空気調和機
JP2010216687A (ja) * 2009-03-13 2010-09-30 Daikin Ind Ltd ヒートポンプシステム
JP2014016079A (ja) * 2012-07-06 2014-01-30 Daikin Ind Ltd ヒートポンプ
JP2014119157A (ja) * 2012-12-14 2014-06-30 Sharp Corp ヒートポンプ式加熱装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020024046A (ja) * 2018-08-06 2020-02-13 富士電機株式会社 ヒートポンプ装置
CN109579347A (zh) * 2018-12-04 2019-04-05 南京天加环境科技有限公司 一种能够避免压缩机回液的多联机系统及其控制方法
CN111023508A (zh) * 2019-12-20 2020-04-17 Tcl空调器(中山)有限公司 一种空调器控制方法、存储介质及空调器
EP4145061A1 (fr) 2021-09-06 2023-03-08 Mitsubishi Heavy Industries Thermal Systems, Ltd. Appareil de réfrigération

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