WO2013035459A1 - Pompe à chaleur - Google Patents

Pompe à chaleur Download PDF

Info

Publication number
WO2013035459A1
WO2013035459A1 PCT/JP2012/069334 JP2012069334W WO2013035459A1 WO 2013035459 A1 WO2013035459 A1 WO 2013035459A1 JP 2012069334 W JP2012069334 W JP 2012069334W WO 2013035459 A1 WO2013035459 A1 WO 2013035459A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat
heat medium
compressor
auxiliary
fluid
Prior art date
Application number
PCT/JP2012/069334
Other languages
English (en)
Japanese (ja)
Inventor
昇 壷井
Original Assignee
株式会社神戸製鋼所
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 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Publication of WO2013035459A1 publication Critical patent/WO2013035459A1/fr

Links

Images

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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B49/025—Motor control 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • 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
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • 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
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • 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]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a heat pump.
  • the heat medium receives the heat from the object to be cooled in the evaporator, cools the object to be cooled, releases the heat to the object to be heated in the condenser, and heats the object to be heated. That is, the heat pump performs cooling in the evaporator and heating in the condenser.
  • Patent Document 1 describes that the heat generated by the heat medium of the heat pump using a condenser is used for heating or process heating, and the heat generated by the heat medium using an evaporator is used for cooling or process cooling.
  • Non-Patent Document 1 describes a heat pump that can simultaneously produce 90 ° C. hot water and 7 ° C. cold water.
  • the load on the cooling side (demand) and the load on the heating side (demand) must be balanced. That is, even if the amount of heat required on the cooling side is large, if the amount of heat required on the heating side is small, sufficient cooling cannot be supplied to the cooling side. In practice, however, the heating-side load and the cooling-side load are almost unrelated to each other.
  • the condenser is a heat exchanger (main condenser) that cools the heat medium with the target fluid to be heated, and By separately configuring the heat exchanger (auxiliary condenser) that further cools the heat medium with another cold heat source, both the demand on the heating side and the demand on the cooling side can be satisfied simultaneously.
  • a heat medium for example, R134a
  • evaporator 101 that exchanges heat between the heat medium and a fluid to be cooled (cooling side load)
  • a heat medium for example, R134a
  • an auxiliary condenser 104 for exchanging heat with each other and a pressure reducing valve 105 for reducing the pressure of the heat medium.
  • FIG. 10 shows a thermal cycle in the heat pump of FIG. 9 on a pi diagram (Mollier diagram).
  • the condensation temperature of the heat medium in the main condenser 103 and the auxiliary condenser 104 is 70 ° C.
  • the evaporation temperature of the heat medium in the evaporator 101 is 0 ° C.
  • This heat pump heats the fluid to be heated to 63 ° C. at the outlet of the main condenser 103, and cools the fluid to be cooled to 7 ° C. at the outlet of the evaporator 101.
  • the amount of heat (heating load) required for the fluid to be heated is 108.2 kW and the amount of cooling heat (cooling load) required for the fluid to be cooled is 94.3 kW, 94.3 kW in the evaporator 101.
  • the number of rotations of the compressor 102 that is, the circulation flow rate of the heat medium is determined so that the cooling load can be achieved.
  • the power required for the compressor 102 to compress the heat medium at this flow rate to a pressure at which the saturated steam temperature becomes 70 ° C. is 41.0 kW.
  • the heat medium having this flow rate a total of 135.3 kW of heat is obtained in the main condenser 103 and the auxiliary condenser 104.
  • the flow rate of the auxiliary cooling fluid supplied to the auxiliary condenser 104 the ratio between the amount of heat received by the fluid to be heated in the main condenser 103 and the amount of heat received by the auxiliary cooling fluid in the auxiliary condenser 104 can be controlled.
  • the heating target fluid is heated by 108.2 kW in the main condenser 103, and the remaining 27.1 kW of heat is discarded in the auxiliary cooling fluid in the auxiliary condenser 104.
  • an object of the present invention is to provide a heat pump that can satisfy both the demand on the cooling side and the demand on the heating side at the same time and consumes less power in the compressor.
  • a first aspect of the heat pump according to the present invention includes a first evaporator in which a first heat medium is enclosed and heat exchange is performed between a fluid to be cooled and the first heat medium, A first compressor that compresses one heat medium, an intermediate heat exchanger that exchanges heat between the first heat medium and a second heat medium, and an auxiliary that exchanges heat between the first heat medium and an auxiliary cooling fluid A condenser, a first circulation passage provided with a first expansion valve for depressurizing the first heat medium, and the second heat medium are enclosed, and the intermediate heat exchanger and the second heat medium are enclosed.
  • Second circulation in which a second compressor that compresses, a second condenser that exchanges heat between the second heat medium and the fluid to be heated, and a second expansion valve that depressurizes the second heat medium
  • a first flow control device for regulating the flow rate of the ⁇ body shall have a.
  • the 2nd aspect of the heat pump by this invention is a 1st evaporator with which a 1st heat medium is enclosed, and heat-exchanges between a cooling object fluid and the said 1st heat medium, and compresses the said 1st heat medium.
  • a first circulation flow in which a first compressor, an intermediate heat exchanger for exchanging heat between the first heat medium and the second heat medium, and a first expansion valve for depressurizing the first heat medium are interposed
  • a second condenser for exchanging heat between the second heat medium and a fluid to be heated; a second circulation passage having a second expansion valve for depressurizing the second heat medium; 2 Adjust the flow rate of the auxiliary heating fluid supplied to the auxiliary evaporator so that the suction pressure of the compressor becomes a predetermined set pressure.
  • a second flow control device that shall have the.
  • the 3rd aspect of the heat pump by this invention is a 1st evaporator with which a 1st heat medium is enclosed, heat-exchanges between a cooling object fluid and the said 1st heat medium, and compresses the said 1st heat medium.
  • a first circulation passage provided with a first expansion valve for depressurizing the first heat medium; and the second heat medium is sealed between the intermediate heat exchanger, the second heat medium and the auxiliary heating fluid.
  • An auxiliary evaporator for exchanging heat with the second compressor, a second compressor for compressing the second heat medium, a second condenser for exchanging heat between the second heat medium and the fluid to be heated, and the second heat medium.
  • the second circulation passage having a second expansion valve for reducing pressure, and the discharge pressure of the first compressor become a predetermined set pressure.
  • a first flow rate control device for adjusting the flow rate of the auxiliary cooling fluid supplied to the auxiliary condenser, and the suction pressure of the second compressor is supplied to the auxiliary evaporator so that the suction pressure becomes a predetermined set pressure.
  • a second flow rate control device for adjusting the flow rate of the auxiliary heating fluid.
  • the circulation flow rate of the heat medium in the first circulation channel with respect to the cooling load by optimizing the circulation flow rate of the heat medium in the first circulation channel with respect to the cooling load, and optimizing the circulation flow rate of the heat medium in the second circulation channel with respect to the heating load,
  • the amount of heat discarded outside the system can be made smaller than the circulation flow rate of the heat medium in accordance with the relatively large cooling load and heating load in one cycle, and the first compressor and the second compressor
  • the total power consumption is also smaller than the power consumption in one cycle.
  • the heat pump of the present invention includes a first rotation speed control device that controls the rotation speed of the first compressor so that the temperature of the fluid to be cooled at the outlet of the first evaporator becomes a predetermined set temperature. You may have. Furthermore, the heat pump of the present invention includes a second rotation speed control device that controls the rotation speed of the second compressor so that the temperature of the fluid to be heated at the outlet of the second condenser becomes a predetermined set temperature. You may have.
  • the operation of the first circulation channel and the second circulation channel can be stably performed, and a response similar to that of a normal heat pump can be obtained with respect to fluctuations in the cooling load and / or the heating load. It is done.
  • the heat pump is operated with the first circulation channel that operates at the optimum flow rate for the cooling load and the second circulation channel that operates at the optimum flow rate with respect to the heating load.
  • FIG. 10 is a Mollier diagram in the heat pump of FIG. 9.
  • FIG. 1 the structure of the heat pump which is 1st Embodiment of this invention is shown.
  • the heat pump of the present embodiment cools a cooling target fluid (circulated cold water) that is a cooling load source to a predetermined set temperature (for example, 7 ° C.), and simultaneously heats a heating target fluid (circulated hot water) that is a heating load source to a predetermined level. Used to heat to a set temperature (eg 63 ° C.).
  • the heat pump of the present embodiment has a first circulation channel 1 in which a first heat medium (for example, R134a) is enclosed and a second circulation channel 2 in which a second heat medium (for example, R134a) is enclosed.
  • first heat medium and the second heat medium are the same refrigerant, but may be different heat media.
  • the first circulation channel 1 includes a first evaporator 3 for exchanging heat between the fluid to be cooled and the first heat medium, a first compressor 4 for compressing the first heat medium, a first heat medium, and a first heat medium.
  • Heat exchange is performed between the intermediate heat exchanger 5 that exchanges heat with the two heat mediums, an auxiliary cooling fluid (for example, cooling water produced in a cooling tower) for disposing heat outside the system, and the first heat medium.
  • An auxiliary condenser 6 and a first expansion valve 7 for depressurizing the first heat medium are interposed.
  • the second circulation channel 2 includes an intermediate heat exchanger 5, a second compressor 8 that compresses the second heat medium, and a second condenser 9 that exchanges heat between the second heat medium and the fluid to be heated.
  • the second expansion valve 10 that depressurizes the second heat medium is interposed.
  • the first circulation channel 1 includes a pressure detector 11 that detects the discharge pressure of the first compressor 4, and the flow rate of the auxiliary cooling fluid supplied to the auxiliary condenser 6 is controlled by the first flow rate control valve 12. It can be adjusted. And this heat pump is based on the detected value of the pressure detector 11, and the opening degree of the 1st flow control valve 12 is maintained so that the discharge pressure of the 1st compressor 4 may be kept at a predetermined setting pressure (for example, 0.7 MPa).
  • the first flow control device 13 that adjusts by PID control is provided.
  • the predetermined set pressure (for example, 0.7 MPa) is a pressure that is assumed when the compression ratio of the first compressor 4 and the compression ratio of the second compressor 8 are the same value or substantially the same value. It is good to be decided based on. By carrying out like this, the burden which concerns on each driving
  • the first compressor 4 and the second compressor 8 are driven by motors 16 and 17 whose frequencies are controlled by inverters 14 and 15, respectively.
  • the heat pump also has a cooling temperature detector 18 that detects the temperature of the fluid to be cooled at the outlet of the first condenser 3. The heat pump then passes through the inverter 14 so as to maintain the temperature of the cooling target fluid at the outlet of the first evaporator 3 at a predetermined set temperature (for example, 7 ° C.) based on the detection value of the cooling temperature detector 18.
  • the first rotation speed control device 19 that controls the rotation speed of the first compressor 4, that is, the circulation flow rate of the heat medium in the first circulation flow path 1, for example, by PID control.
  • this heat pump has a heating temperature detector 20 that detects the temperature of the fluid to be heated at the outlet of the second condenser 9. And this heat pump is based on the detection value of the heating temperature detector 20, and maintains the exit temperature of the fluid to be heated at a predetermined set value (for example, 63 ° C.) via the inverter 15 of the second compressor 8.
  • a second rotation speed control device 21 is provided that controls the rotation speed, that is, the circulation flow rate of the heat medium in the second circulation flow path 2 by, for example, PID control.
  • FIG. 2 shows on the pi diagram (Mollier diagram) the respective heat cycles of the first circulation channel 1 and the second circulation channel 2 of the heat pump of the present embodiment.
  • Point A is the state of the first heat medium at the outlet of the first evaporator 3
  • Point B is the state of the first heat medium at the inlet of the intermediate heat exchanger 5
  • Point C is the first state of the heat medium at the outlet of the auxiliary condenser 6.
  • the state of one heat medium, point D indicates the state of the first heat medium at the inlet of the first evaporator 3.
  • Point E is the state of the second heat medium at the outlet of the intermediate heat exchanger 5
  • Point F is the state of the second heat medium at the inlet of the second condenser 9
  • Point G is at the outlet of the second condenser 9.
  • the state of the second heat medium, point H indicates the state of the second heat medium at the inlet of the intermediate heat exchanger 5.
  • the amount of heat exchanged in the first evaporator 3, the intermediate heat exchanger 5, and the second condenser 9 is also shown.
  • the exchange heat amount is a value calculated by multiplying the amount of change in specific enthalpy on the Pi diagram by the flow rate of the heat medium.
  • the exchange heat amount (cooling load) in the first evaporator 3 is the rated value, that is, the load at which the rotation speed of the first compressor 4 is the maximum value, 94.3 kW
  • Point A is the evaporation pressure (for example, 0 ° C.) of the first heat medium in the first evaporator 3 and is a point on the saturated vapor line.
  • Point B is a predetermined polytropy change from point A to the discharge pressure (for example, 0.7 MPa) of the first compressor 4 determined according to the condensation temperature (for example, 25 ° C.) in the intermediate heat exchanger 5 and the auxiliary condenser 6. It is a point that did.
  • Point C is a point on the saturated liquid line at the condensation pressure in the intermediate heat exchanger 5 and the auxiliary condenser 6.
  • Point D is a point where adiabatic expansion (isoenthalpy change) is performed from point C to the evaporation pressure in the first evaporator 3.
  • the sum of the exchange heat amount in the first evaporator 3 and the compression work of the compressor 4 (considering the efficiency of the compressor 4 as consumption power) is exchanged in the intermediate heat exchanger 5 and the auxiliary condenser 6. Equal to the amount of heat. Further, the ratio of the exchange heat quantity in the first evaporator 3 to the exchange heat quantity in the intermediate heat exchanger 5 and the auxiliary condenser 6 is the same as the evaporation pressure in the first evaporator 3 and the condensation in the intermediate heat exchanger 5 and the auxiliary condenser 6. Because it depends on the pressure, it is constant regardless of the rotational speed of the first compressor 4.
  • the amount of heat exchanged in the intermediate heat exchanger 5 (between point H and point E) of the second heat medium and the power consumed by the second compressor 8 (between point E and point F). Is equal to the amount of heat exchanged in the second condenser 9.
  • the ratio between the exchange heat quantity in the intermediate heat exchanger 5 and the exchange heat quantity in the second condenser 9 is such that the evaporation temperature (for example, 20 ° C.) of the second heat medium in the intermediate heat exchanger 5 and the second heat quantity in the second condenser 9. 2 Determined by the condensation temperature of the heat medium (for example, 70 ° C.).
  • the cooling load is 94.3 kW
  • the amount of exchange heat in the intermediate heat exchanger 5 and the auxiliary condenser 6 is 108.0 kW.
  • the heating load is 135.3 kW
  • the exchange heat amount in the intermediate heat exchanger 5 is 108.0 kW. That is, under this condition, the cooling load and the heating load are balanced in the intermediate heat exchanger 5.
  • the exchange heat quantity in the auxiliary condenser 6 must be zero, and the first flow control device 13 fully closes the first flow control valve 12.
  • the power consumption of the first compressor 4 is 13.7 kW
  • the power consumption of the second compressor 8 is 27.3 kW.
  • FIG. 3 shows a case where the heating load is reduced in the heat pump of the present embodiment.
  • the second rotation speed control device 21 decreases the circulation amount of the heat medium in the circulation flow path 2, The temperature rise at the outlet of the second condenser 9 of the fluid to be heated is prevented. As a result, the amount of heat that can be transferred from the first heat medium to the second heat medium in the intermediate heat exchanger 5 is reduced. Therefore, in order to maintain the condensation pressure, the first flow control device 13 performs the first flow rate control.
  • the control valve 12 is opened, and the auxiliary condenser 6 releases (discards) heat from the first heat medium to the auxiliary cooling fluid by a shortage of the exchange heat amount in the intermediate heat exchanger 5.
  • the state of the first heat medium between the intermediate heat exchanger 5 and the auxiliary condenser 6 is a point C ′ in FIG.
  • This point C ′ moves according to the circulation flow rate of the second heat medium in the second circulation flow path 2, that is, the heating load.
  • the heating load is zero, the point C ′ coincides with the point B, and all the heat amount difference between the point B and the point C is discarded outside the system through the auxiliary cooling fluid.
  • FIG. 3 shows a case where the heating load is 108.2 kW, which is 80% of the rated value.
  • the amount of heat that the second heat medium can receive from the first heat medium in the intermediate heat exchanger 5 is 85.6 kW.
  • the amount of heat to be released by the intermediate heat exchanger 5 and the auxiliary condenser 6 in the first circulation channel 1 is 108.0 kW as in FIG.
  • the first flow rate control device 13 adjusts the opening degree of the first flow rate control valve 12 so that the remaining heat amount 22.4 kW is discharged from the first heat medium to the auxiliary cooling fluid in the auxiliary condenser 6.
  • FIG. 4 shows a configuration of a heat pump according to the second embodiment of the present invention.
  • the same components as those of the above-described embodiments are denoted by the same reference numerals, and redundant description is omitted.
  • the positions of the intermediate heat exchanger 5 and the auxiliary condenser 6 in the first embodiment are exchanged.
  • the circulation flow rate of the first heat medium in the first circulation channel 1 is optimized according to the cooling load, and the second heat medium in the second circulation channel 2 is optimized.
  • the temperature is determined, and consequently the ratio of the power burden between the first compressor 4 and the second compressor 8 is determined. That is, the lower the discharge pressure of the first compressor 4, the smaller the power share of the first compressor 4.
  • the lower the condensation temperature in the intermediate heat exchanger 5 the lower the condensation temperature in the intermediate heat exchanger 5 with respect to the amount of heat (between point D and point A) received from the fluid to be cooled in the first evaporator 3.
  • the ratio of the amount of heat transferred to the second circulation channel 2 becomes small. Therefore, by setting the discharge pressure of the first compressor 4 to a pressure sufficiently lower than the condensation pressure in the second condenser 9, the power burden ratio of the second compressor 8 in the full load is increased to some extent, and the heating load is reduced. When it decreases, the reduction effect of the power consumption of the 2nd compressor 8 by reducing the circulating flow volume of the 2nd circulation flow path 2 comes to be acquired.
  • FIG. 5 shows a configuration of a heat pump according to a third embodiment of the present invention.
  • the auxiliary condenser 6 is not provided in the first circulation channel 1, but the auxiliary evaporator is interposed between the intermediate heat exchanger 5 and the second compressor 8 in the second circulation channel 2. 22 is interposed.
  • the auxiliary evaporator 22 exchanges heat between the auxiliary heating fluid for supplying heat from outside the system and the second heat medium.
  • the flow rate of the auxiliary heating fluid supplied to the auxiliary evaporator 22 can be adjusted by the second flow rate adjustment valve 23.
  • the heat pump of the present embodiment is provided with a suction pressure detector 24 for detecting the suction pressure of the second compressor 8 in the second circulation flow path 2, and based on the detection value of the suction pressure detector 24.
  • a second flow rate control device 25 that adjusts the opening of the second flow rate adjustment valve 23 by, for example, PID control so as to keep the suction pressure of the two compressors 8 at a predetermined set pressure (for example, 2.1 MPa).
  • FIG. 6 shows respective thermal cycles of the first circulation channel 1 and the second circulation channel 2 of the heat pump of the present embodiment.
  • the cooling load is 80% (75.4 kW) of the rated value (94.3 kW)
  • the heating load is the rated value (135.3 kW). Since it is obvious to those skilled in the art, although not described in detail, the heat cycle when the heat pump of this embodiment is full load (both cooling load and heating load are rated values) is the same as that of the first embodiment. It becomes equal to FIG. 2 shown.
  • the second heat medium having a flow rate capable of releasing 135.3 kW of heat in the second condenser 9 is an intermediate heat exchanger. 5 and auxiliary evaporator 22 need to receive a total of 108 kW of heat.
  • the first heat medium having a flow rate capable of absorbing 94.3 kW in the first evaporator 3 is changed to the second heat medium in the intermediate heat exchanger 5. Only 86.4 kW can be supplied. Therefore, the second heat medium at the outlet of the intermediate heat exchanger 5 is on the point E ′ and is in the state of wet steam.
  • the point E ′ varies according to the circulation flow rate of the first heat medium, that is, the cooling load, and coincides with the point H when the cooling load is zero.
  • the second heat medium flowing out from the intermediate heat exchanger 5 is further heated by the auxiliary heating fluid in the auxiliary evaporator 22 by 21.6 kW, which is the difference in heat amount between the point E and the point E ′.
  • the second flow rate control device 25 adjusts the opening of the second flow rate control valve 23 so as to maintain the detection value of the suction pressure detector 24 at the set pressure. Since the suction amount of the second compressor 8 is equal to the circulation flow rate according to the heating load, maintaining the suction pressure of the second compressor 8 at a predetermined set pressure depends on the heating load in the auxiliary evaporator 22. It means that the second heat medium is heated to the state of saturated steam at point E by the circulation flow rate.
  • FIG. 7 shows the configuration of a heat pump according to the fourth embodiment of the present invention.
  • the positions of the intermediate heat exchanger 5 and the auxiliary evaporator 22 in the third embodiment of FIG. 5 are exchanged.
  • the circulation flow rate of the first heat medium in the first circulation channel 1 is optimized according to the cooling load, and the second heat in the second circulation channel 2 is obtained.
  • the amount of cold heat discarded from the second heat medium to the outside of the system can be reduced, a high coefficient of performance can be realized, and the consumption of the auxiliary heating fluid can be reduced.
  • FIG. 8 shows a configuration of a heat pump according to the fifth embodiment of the present invention.
  • the present embodiment has an auxiliary condenser 6 in the first circulation channel 1 and an auxiliary evaporator 22 in the second circulation channel 2.
  • the second flow rate control valve 23 is fully closed to perform the same operation as the heat pump of the first embodiment shown in FIG. Is small
  • the first flow rate control valve 12 is fully closed to perform the same operation as the heat pump of the third embodiment shown in FIG.
  • the auxiliary evaporator 22 can be omitted from the present embodiment, and the same configuration as that of the first embodiment can be obtained, and the heating load is cooled.
  • the auxiliary condenser 6 can be omitted from the present embodiment, and the same configuration as that of the third embodiment can be obtained.
  • the auxiliary condenser 6 is arranged in the first circulation channel 1 upstream of the intermediate heat exchanger 5.
  • the auxiliary evaporator 22 may be disposed in the second circulation passage 2 on the upstream side of the intermediate heat exchanger 5.
  • the rotation speed of the first compressor 4 is controlled by the first rotation speed control device 19, and the rotation speed of the second compressor 8 is controlled by the second rotation speed control device 21.
  • the first rotation speed controller 19 and the inverter 14 may be omitted and the rotation speed of the first compressor 4 may be fixed.
  • the second rotation speed control device 21 and the inverter 15 may be omitted and the rotation speed of the second compressor 8 may be fixed.

Landscapes

  • 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)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Abstract

L'invention concerne une pompe à chaleur, en mesure de satisfaire simultanément la demande côté refroidissement et la demande côté chauffage, et grâce à laquelle la quantité d'énergie consommée par les compresseurs est faible, pompe à chaleur comportant : un premier chemin d'écoulement de circulation (1), qui est rempli d'un premier milieu chauffant et dans lequel sont intercalés un premier évaporateur (3) qui échange de la chaleur entre un fluide devant être refroidi et le premier milieu chauffant, un premier compresseur (4) qui comprime le premier milieu chauffant, un échangeur de chaleur intermédiaire (5) qui échange de la chaleur entre le premier milieu chauffant et un second milieu chauffant, un condenseur auxiliaire (6) qui échange de la chaleur entre le premier milieu chauffant et un fluide refroidissant auxiliaire, et un premier détendeur (7) qui réduit la pression du premier milieu chauffant ; un second chemin d'écoulement de circulation (2), qui est rempli du second milieu chauffant et dans lequel sont intercalés l'échangeur de chaleur intermédiaire (5), un second compresseur (8) qui comprime le second milieu chauffant, un second condenseur (9) qui échange de la chaleur entre le second milieu chauffant et un fluide devant être chauffé, et un second détendeur (10) qui réduit la pression du second milieu chauffant ; et un premier dispositif de régulation du volume d'écoulement (13) qui règle le volume d'écoulement du fluide refroidissant auxiliaire fourni au condenseur auxiliaire (6) de sorte que la pression de décharge du premier compresseur (4) réalise une pression réglée prescrite.
PCT/JP2012/069334 2011-09-08 2012-07-30 Pompe à chaleur WO2013035459A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-196181 2011-09-08
JP2011196181 2011-09-08

Publications (1)

Publication Number Publication Date
WO2013035459A1 true WO2013035459A1 (fr) 2013-03-14

Family

ID=47831911

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/069334 WO2013035459A1 (fr) 2011-09-08 2012-07-30 Pompe à chaleur

Country Status (2)

Country Link
JP (1) JP2013068409A (fr)
WO (1) WO2013035459A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112254366A (zh) * 2020-11-10 2021-01-22 云南道精制冷科技有限责任公司 一种冷热联供双效板换机组

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6211439B2 (ja) * 2014-03-05 2017-10-11 本田技研工業株式会社 二元ヒートポンプの制御方法
JP6603394B2 (ja) 2016-02-17 2019-11-06 Ｐｈｃホールディングス株式会社 冷凍装置
DE102017216361A1 (de) * 2017-09-14 2019-03-14 Weiss Umwelttechnik Gmbh Verfahren zur Konditionierung von Luft
JP2023087517A (ja) * 2021-12-13 2023-06-23 伸和コントロールズ株式会社 冷凍装置及び温調システム
EP4414629A1 (fr) * 2022-11-25 2024-08-14 Daikin Industries, Ltd. Système à cycle de réfrigération

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6249160A (ja) * 1985-08-28 1987-03-03 シャープ株式会社 ヒ−トポンプ給湯装置
JPS62261865A (ja) * 1986-05-09 1987-11-14 三菱重工業株式会社 ヒ−トポンプ装置
JPH07234026A (ja) * 1994-02-24 1995-09-05 Mitsubishi Heavy Ind Ltd 冷凍装置及びその運転方法
JP2007232245A (ja) * 2006-02-28 2007-09-13 Mitsubishi Electric Corp 冷凍システムおよび冷凍システムの運転方法
JP2008298406A (ja) * 2007-06-04 2008-12-11 Toyo Eng Works Ltd 多元ヒートポンプ式蒸気・温水発生装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6249160A (ja) * 1985-08-28 1987-03-03 シャープ株式会社 ヒ−トポンプ給湯装置
JPS62261865A (ja) * 1986-05-09 1987-11-14 三菱重工業株式会社 ヒ−トポンプ装置
JPH07234026A (ja) * 1994-02-24 1995-09-05 Mitsubishi Heavy Ind Ltd 冷凍装置及びその運転方法
JP2007232245A (ja) * 2006-02-28 2007-09-13 Mitsubishi Electric Corp 冷凍システムおよび冷凍システムの運転方法
JP2008298406A (ja) * 2007-06-04 2008-12-11 Toyo Eng Works Ltd 多元ヒートポンプ式蒸気・温水発生装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112254366A (zh) * 2020-11-10 2021-01-22 云南道精制冷科技有限责任公司 一种冷热联供双效板换机组

Also Published As

Publication number Publication date
JP2013068409A (ja) 2013-04-18

Similar Documents

Publication Publication Date Title
WO2013035459A1 (fr) Pompe à chaleur
JP5492346B2 (ja) 空調給湯システム
US9175889B2 (en) Heat source system and control method thereof
JP5121747B2 (ja) 地中熱ヒートポンプ装置
JP2007187386A (ja) 除湿空調システム
WO2015133107A1 (fr) Générateur d'eau chaude à pompe à chaleur
JP2017190925A (ja) 燃料電池用廃熱回収システム
WO2012102197A1 (fr) Système de cogénération
WO2009142004A1 (fr) Système de chauffage
KR20120045248A (ko) 복합 냉난방 온수 장치
KR101169706B1 (ko) 급탕용 히트펌프 시스템
WO2020064014A1 (fr) Système de gestion de température de véhicule
WO2012090579A1 (fr) Système de source de chaleur et procédé de commande pour celui-ci
JP5788526B2 (ja) 空調給湯システム
JP2013127332A (ja) 温水暖房装置
JP2006118820A (ja) ヒートポンプ式給湯装置
KR20080073996A (ko) 수열원 공기 조화 시스템 및 그 제어방법
JP5150300B2 (ja) ヒートポンプ式給湯装置
JP2015124911A (ja) 給湯空調システム
JP4277836B2 (ja) ヒートポンプ給湯機
JP6814071B2 (ja) 廃熱利用吸収式冷凍システム及び吸収式冷凍機
JP2006017377A (ja) ヒートポンプ給湯機
WO2014108997A1 (fr) Dispositif de climatisation
JP5280835B2 (ja) 潜熱蓄熱装置を具備した圧縮式ヒ−トポンプ
JP2014005961A (ja) 冷凍サイクル装置及びそれを備えた温水生成装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12830395

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12830395

Country of ref document: EP

Kind code of ref document: A1