WO2016017430A1 - 室外機および冷凍サイクル装置 - Google Patents
室外機および冷凍サイクル装置 Download PDFInfo
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- WO2016017430A1 WO2016017430A1 PCT/JP2015/070305 JP2015070305W WO2016017430A1 WO 2016017430 A1 WO2016017430 A1 WO 2016017430A1 JP 2015070305 W JP2015070305 W JP 2015070305W WO 2016017430 A1 WO2016017430 A1 WO 2016017430A1
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- gas
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- liquid separator
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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
- 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
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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
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/17—Speeds
- F25B2700/171—Speeds of the compressor
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2103—Temperatures near a heat exchanger
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
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- 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 an outdoor unit and the like.
- the present invention relates to the distribution of refrigerant to the heat transfer tubes of the outdoor heat exchanger.
- a refrigeration cycle apparatus using a refrigeration cycle basically includes a refrigerant circuit in which a compressor, a condenser, an expansion valve (decompression device), and an evaporator are connected by a refrigerant pipe to circulate the refrigerant.
- liquid refrigerant liquid refrigerant, refrigerant liquid
- a gas (gas) refrigerant gas refrigerant, refrigerant vapor
- liquid refrigerant coexist. It becomes a gas-liquid two-phase state and flows into the evaporator.
- the energy efficiency of the refrigeration cycle apparatus decreases due to, for example, deterioration of distribution characteristics in the heat exchanger.
- the distribution characteristics have been improved by adjusting the internal structure of the header, such as the amount of branch pipe protruding into the header that distributes the refrigerant to the heat transfer tubes, etc., the partition plate inside the header, and the installation of the ejection holes.
- the internal structure of the header such as the amount of branch pipe protruding into the header that distributes the refrigerant to the heat transfer tubes, etc., the partition plate inside the header, and the installation of the ejection holes.
- Patent Document 2 there is a method of improving distribution by attaching a mechanism for extracting a gas refrigerant to a gas-liquid separator, an upper part of the header, etc., and allowing a liquid single-phase refrigerant to flow into the header in the heat exchanger.
- This method is susceptible to the refrigerant flow rate. For example, when the refrigerant flow rate is large, the refrigerant can be evenly distributed, but when the refrigerant flow rate is small, the liquid refrigerant does not flow in the upper part of the header, and there is a possibility that the equal distribution cannot be performed.
- an object of the present invention is to provide an outdoor unit or the like that can improve distribution performance regardless of operating conditions.
- the outdoor unit according to the present invention passes through a compressor that compresses and discharges the sucked refrigerant, a condenser that dissipates heat to the refrigerant and condenses the refrigerant, a decompression device that decompresses the condensed refrigerant, and a decompression device.
- An evaporator having at least a gas-liquid separator that separates a gaseous refrigerant and a liquid refrigerant, a plurality of heat transfer tubes that absorb heat into the refrigerant to evaporate the refrigerant, and an inlet header that distributes the introduced refrigerant to the heat transfer tubes
- a header bypass pipe that is connected to the inlet and sucks the refrigerant flowing into the inlet header, a header flow adjustment device that adjusts the flow rate of the refrigerant
- the determination device determines the opening degrees of the gas-liquid separator-side flow rate adjustment device and the header-side flow rate adjustment device from the frequency of the compressor. Can be improved.
- FIG. 1 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
- the refrigeration cycle apparatus of Embodiment 1 configures a refrigerant circuit by connecting an outdoor unit (outdoor unit) 100 and a load unit (load side unit) 200 by a refrigerant pipe, and circulates the refrigerant.
- the outdoor unit 100 supplies capacity to the load machine 200 via a refrigerant.
- the load machine 200 supplies heat to the target load.
- the load machine 200 has a load heat exchanger 18.
- the load heat exchanger 18 functions as a condenser (heat radiator), condenses the refrigerant, and heats the load.
- the load heat exchanger 18 functions as a condenser.
- the load heat exchanger 18 also functions as an evaporator.
- the outdoor unit 100 includes a compressor 11, an outdoor heat exchanger 3, an expansion valve 16, a gas / liquid separator 1, a gas / liquid separator bypass pipe 5, a gas / liquid separator side flow rate adjustment valve 6, a header bypass pipe 8, and A header side flow rate adjusting valve 9 is provided.
- the compressor 11 compresses and discharges the sucked refrigerant.
- the capacity of the compressor 11 (the amount of refrigerant sent out per unit time) may be changed by arbitrarily changing the drive frequency of the compressor 11 using, for example, an inverter circuit.
- the expansion valve 16 serving as a decompression device (a throttling device) decompresses and expands the refrigerant.
- the gas-liquid separator 1 separates the flowing refrigerant into a gas refrigerant and a liquid refrigerant (including a gas-liquid two-phase refrigerant).
- the gas-liquid two-phase refrigerant flows through the two-phase refrigerant pipe 13.
- the gas-liquid separator bypass pipe 5 is a pipe connecting the gas outflow side of the gas-liquid separator 1 and the suction side pipe 14 of the compressor 11.
- the gas-liquid separator-side flow rate adjusting valve 6 serving as the gas-liquid separator-side flow rate adjusting device is a valve that adjusts the refrigerant flow rate passing through the gas-liquid separator bypass pipe 5 based on the control of the flow rate adjusting valve opening controller 17. is there.
- the header bypass pipe 8 is a pipe that connects the upper part of the inflow side header 2 (the terminal end side opposite to the refrigerant suction side) and the suction side pipe 14 of the compressor 11.
- the header-side flow rate adjustment valve 9 serving as the header-side flow rate adjustment device is a valve that adjusts the flow rate of the refrigerant passing through the header bypass pipe 8 based on the control of the flow rate adjustment valve opening controller 10.
- the refrigerant flow rate adjustment is performed by adjusting the valve opening by the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9, but the flow rate adjustment may be performed by another device.
- the control board 22 is a board that controls the refrigeration cycle apparatus.
- a signal including operation mode data such as cooling operation and heating operation is sent to the memory 19.
- a signal related to the frequency (driving frequency) sent from the compressor 11 is sent to the compressor frequency reader 20.
- the compressor frequency reader 20 reads the frequency of the compressor 11 and sends a signal including compressor frequency data to the memory 19.
- the memory 19 serving as a storage device is a device that temporarily or long-term stores data necessary for the determination device 21 to make a determination, for example.
- operation mode data sent from the control board 22 is stored.
- the compressor frequency data included in the signal sent from the compressor frequency reader 20 is stored.
- the determination device 21 is a device that performs determination processing in the refrigeration cycle apparatus.
- data stored in the memory 19 is read, and processing for controlling the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 is performed.
- FIG. 2 is a diagram relating to the control of the gas-liquid separator-side flow rate adjustment valve 6 and the header-side flow rate adjustment valve 9 according to Embodiment 1 of the present invention.
- the load of the refrigeration cycle apparatus is, for example, 67% to 100% (rated load), 34% to 66 It is classified into at least three, less than% (intermediate load) and 0% or more and less than 33% (1/4 load).
- the refrigerant flow rate flowing in the outdoor unit 100 increases.
- operating condition A the gas-liquid separator side flow rate adjustment valve 6 is opened and the header side flow rate adjustment valve 9 is closed.
- the refrigerant flow rate flowing through the outdoor unit 100 is smaller than that at the rated load.
- operation condition B control is performed to close the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9.
- FIG. 3 is a diagram showing a control flow of the gas-liquid separator-side flow rate adjustment valve 6 and the header-side flow rate adjustment valve 9 according to Embodiment 1 of the present invention. Based on FIG. 3, control of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 will be described.
- the relationship between the load and the frequency of the compressor 11 is obtained in advance by experiments, calculations, and the like.
- the compressor frequency at a load of 100% is f1.
- the driving compressor frequency is defined as f, for example, 0.67 ⁇ f1 ⁇ f ⁇ f1 is a rated load. Further, 0.34 ⁇ f ⁇ f1 ⁇ 0.67 is an intermediate load.
- 0 ⁇ f ⁇ 0.34 ⁇ f1 is set as a 1 ⁇ 4 load. Then, the relationship between the opening degree and the load of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 described in FIG. 2 is stored in the memory 19 as opening degree data.
- the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 are in a closed state (opening degree 0) (S1).
- the compressor 11 is driven (S2).
- a frequency signal is sent from the compressor 11 to the control board 22 (S3).
- the compressor frequency reader 20 determines the frequency of the compressor 11 being driven, and stores compressor frequency data in the memory 19 (S4).
- Determination device 21 reads compressor frequency data and opening degree data from memory 19 (S5). Then, the compressor frequency data is compared with the opening degree data (S6). It is determined whether the operating condition is an operating condition A (rated load), an operating condition B (intermediate load) or an operating condition C (1/4 load) (S7). Then, an opening degree signal based on the determined operating condition is transmitted to the flow rate adjustment valve opening degree controller 10 and the flow rate adjustment valve opening degree controller 17 (S8). Returning to S2, the determination of the operating condition based on the frequency of the compressor 11 is repeated.
- the flow adjustment valve opening controller 10 and the flow adjustment valve opening controller 17 control the gas-liquid separator side flow adjustment valve 6 and the header side flow adjustment valve 9 based on the received opening signal.
- a signal is sent to the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9.
- the refrigerant drift to the heat transfer tube 15 is suppressed according to a wide range of operating conditions. can do. Moreover, the dryness of the refrigerant flowing into the heat transfer tube 15 of the outdoor heat exchanger 3 can be adjusted.
- an outdoor heat exchanger 3 functions as an evaporator in the present embodiment, and exchanges heat with outdoor air (outside air) to evaporate and evaporate (vaporize and evaporate) the refrigerant.
- outdoor air outside air
- the outdoor heat exchanger 3 also functions as a condenser.
- the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 are controlled to be fully closed.
- FIG. 4 is a diagram showing a control flow of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 when the outdoor heat exchanger 3 according to Embodiment 1 of the present invention functions as a condenser.
- the outdoor heat exchanger 3 functions as a condenser or an evaporator.
- the gas-liquid separator-side flow rate adjustment valve 6 and the header-side flow rate adjustment valve 9 have arbitrary opening degrees (S11).
- the control board 22 sends a signal indicating the operation performed by the refrigeration cycle apparatus, and stores it in the memory 19 as operation mode data (S12).
- the determination device 21 reads the operation mode data (S13). Then, it is determined whether or not the refrigeration cycle apparatus performs a cooling operation (S14). If it determines with performing a cooling operation, the determination apparatus 21 will transmit the opening degree signal to the effect of closing a valve to the flow regulating valve opening controller 10 and the flow regulating valve opening controller 17 (S15).
- the flow rate adjustment valve opening controller 10 and the flow rate adjustment valve opening controller 17 perform control to close the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 based on the received opening degree signal.
- the outdoor heat exchanger 3 has a heat exchange section 3A and an outflow side header 4 composed of an inflow side header 2, a heat transfer tube 15, fins, and the like.
- the outflow side header 4 is a pipe that joins the gas refrigerant flowing out from the heat transfer pipe 15 and flows out to the suction side pipe of the compressor 11.
- FIG. 5 is a view showing the relationship between the inflow side header 2 and the heat transfer tube 15 according to Embodiment 1 of the present invention.
- the inflow side header 2 is a tube that distributes the inflowing refrigerant to the plurality of heat transfer tubes 15.
- the outdoor heat exchanger 3 in the present embodiment includes a plurality of heat transfer tubes 15 in which the gas-liquid two-phase refrigerant that has flowed into the inflow side header 2 is connected in a direction perpendicular to the refrigerant passage direction in the inflow side header 2. (Vertical header). And in the outdoor unit 100, the outdoor heat exchanger 3 is installed so that the pipe
- the gas-liquid two-phase refrigerant that has flowed through the two-phase refrigerant pipe 13 flows in from the header refrigerant inlet at the lower part of the inflow side header 2 and rises in the inflow side header 2 in the vertical upward direction. It flows in a flow and is divided into each heat transfer tube 15 and flows in the vertical direction (horizontal direction) in the heat transfer tube 15.
- coolant piping 13 and the inflow side header 2 are connected in the lowest end part of the inflow side header 2, and the refrigerant
- the gas-liquid separator bypass pipe 5 is positioned above the two-phase refrigerant pipe 13, the two-phase refrigerant pipe 13 and the inflow side header 2 may be connected on the lower side surface of the inflow side header 2. .
- This embodiment realizes distribution improvement in a wide range of operating conditions of the liquid refrigerant in the gas-liquid two-phase refrigerant in the inflow side header 2.
- the distribution of the liquid refrigerant in the inflow-side header 2 has a different tendency depending on the momentum of the refrigerant (gas-liquid two-phase refrigerant) at the header refrigerant inlet on the refrigerant inflow side.
- FIG. 6 is a diagram showing the distribution characteristics of the gas-liquid two-phase refrigerant in the inflow-side header 2 when the momentum at the header refrigerant inlet is large.
- FIG. 7 is a diagram showing the distribution characteristics of the gas-liquid two-phase refrigerant in the inflow-side header 2 when the momentum at the header refrigerant inflow port is small.
- the momentum increases as the refrigerant flow rate or the gas flow rate in the refrigerant increases, and decreases as the refrigerant flow rate or the gas flow rate in the refrigerant decreases.
- 6 and 7 both show a case where the gas refrigerant and the liquid refrigerant are 2: 8, FIG. 6 shows a case where the refrigerant flow rate is high, and FIG.
- the refrigerant flow rate is low.
- the refrigerant flow rate gas flow rate
- the momentum of the refrigerant in the header is strong, resulting in a distribution characteristic in which a large amount of liquid refrigerant is conveyed to the upper part of the header.
- the refrigerant flow rate gas flow rate
- the momentum of the refrigerant is small, the liquid refrigerant is not transported to the upper part of the header, and most of the liquid refrigerant is transported to the lower part of the header.
- FIG. 8 is a diagram showing distribution characteristics of the gas-liquid two-phase refrigerant in the inflow side header 2 according to Embodiment 1 of the present invention.
- the refrigerant in the inflow side header 2 using the gas / liquid separator 1, the gas / liquid separator bypass pipe 5, the gas / liquid separator side flow rate adjustment valve 6, the header bypass pipe 8 and the header side flow rate adjustment valve 9 is used. Adjust the momentum.
- the header side flow rate adjustment valve 9 is fully closed, and the gas-liquid separator side flow rate adjustment valve 6 is opened to control the opening degree.
- coolant which flows into the inflow side header 2 inside can be reduced.
- the momentum is optimized by opening the gas-liquid separator-side flow rate adjustment valve 6 and adjusting the opening, and the liquid refrigerant can be distributed relatively evenly as shown in FIG.
- the header diameter is designed so that the momentum of the refrigerant flowing in the inflow-side header 2 is optimized when the refrigerant flow rate is smaller than the rated load and the momentum of the refrigerant is intermediate (intermediate load).
- the liquid refrigerant can be distributed relatively evenly as shown in FIG. 8 with the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 fully closed. it can.
- the gas-liquid separator side flow rate adjustment valve 6 When the momentum of the refrigerant is small (1/4 load), the gas-liquid separator side flow rate adjustment valve 6 is fully closed under the operating condition C so that the flow rate of the gas flowing through the inflow side header 2 is not reduced. . Further, the header-side flow rate adjusting valve 9 is opened so as to cause a suction flow in which the gas-liquid two-phase refrigerant flows in the upper part of the header. In addition, in the inflow side header 2, a liquid head difference is caused by gravity. For this reason, the gas refrigerant is likely to flow into the header bypass pipe 8 preferentially over the liquid refrigerant. Therefore, a decrease in the heat exchange amount due to the liquid refrigerant flowing through the header bypass pipe 8 is small. By controlling the opening degree of the header bypass pipe 8 and the header side flow rate adjusting valve 9 and the flow resistance of the header bypass pipe 8 and causing the optimum suction flow, the liquid refrigerant is distributed relatively evenly as shown in FIG. can do.
- the control target values of the valve opening degrees of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 controlled by the flow rate adjustment valve opening degree controller 17 and the flow rate adjustment valve opening degree controller 10 are previously introduced.
- the relationship between the refrigerant flow rate and the optimum gas flow rate for distribution is obtained based on the results of unit experiments, simulations, etc. in the side header 2, and the relationship between the compressor frequency and the opening degree is obtained from them,
- the gas-liquid separator-side flow rate adjustment valve 6 and the header-side flow rate adjustment valve 9 are controlled so as to be interlocked with the drive frequency of the compressor 11.
- the flow rate of the refrigerant flowing through the gas-liquid separator bypass pipe 5 and the header bypass pipe 8 is adjusted by the flow rate adjusting valve.
- the present invention is not limited to this.
- a combination of a capillary tube and a switching valve can be substituted. In this case, the cost can be reduced as compared with the use of the flow regulating valve.
- the refrigerant inlet is opened by opening the gas-liquid separator side flow rate adjustment valve 6.
- the flow rate of the gas refrigerant in the gas-liquid two-phase refrigerant is reduced and the momentum of the gas-liquid two-phase refrigerant is small, a suction flow is caused by the header-side flow rate adjusting valve 9, and the liquid refrigerant is sent to the header.
- the inflow side header 2 By raising the refrigerant to the header bypass pipe 8 connected to the terminal end of the inflow side header 2 up to the upper part, the inflow side header 2 can be operated under a wide range of conditions from a low refrigerant flow to a high operation condition. You can improve distribution.
- FIG. FIG. 9 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 2 of the present invention. 9, devices having the same reference numerals as those in FIG. 1 perform the same operations as those described in the first embodiment.
- the header bypass piping 8 is the outdoor heat exchanger 3. It passes through the heat exchange part 3A.
- the liquid refrigerant may pass through the header bypass pipe 8. The liquid refrigerant passing through the header bypass pipe 8 does not contribute to heat exchange.
- the outdoor unit 100 (refrigeration cycle apparatus) so that the header bypass pipe 8 passes through the heat exchange unit 3A, the liquid refrigerant of the gas-liquid two-phase refrigerant sucked at the upper part of the inflow side header 2 is also wasted. Heat can be exchanged by the outdoor heat exchanger 3. For this reason, the fall of the heat exchange amount in a heat exchanger by attracting
- the heat transfer pipe serving as the header bypass pipe 8 a pipe having an inner diameter (equivalent diameter) larger than that of the other heat transfer pipe 15 is used.
- a smooth pipe without a groove may be used as the heat transfer pipe to be the header bypass pipe 8.
- the type of pipe may be changed such that the heat transfer pipe serving as the header bypass pipe 8 is a circular pipe and the other heat transfer pipe 15 is a flat pipe.
- a flow resistor such as a capillary tube is installed in the suction side pipe 14 or the inner diameter of the outflow side header 4.
- the opening control of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 is performed. By doing so, distribution can be improved over a wide range of operating conditions.
- FIG. FIG. 10 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
- FIG. 11 is a figure which shows the outline of the outdoor heat exchanger 3 which concerns on Embodiment 3 of this invention.
- the upper side temperature sensor 23 and the lower side temperature sensor 24 that are temperature detection means are attached at least to the upper part and the lower part of the outdoor heat exchanger 3.
- a thermocouple, a platinum resistance thermometer, or the like is used to detect the temperature.
- it is not limited to these. The position where the upper side temperature sensor 23 and the lower side temperature sensor 24 are attached will be described. As shown in FIG.
- the upper side temperature sensor 23 installed in the upper part side.
- the lower side temperature sensor 24 and the upper side temperature sensor 23 each detect the temperature of the refrigerant at the installation position.
- the temperature detected by the lower temperature sensor 24 is T1
- the temperature detected by the upper temperature sensor 23 is T2.
- the temperature reader 25 reads the temperatures detected by the upper temperature sensor 23 and the lower temperature sensor 24 and stores them in the memory 19 as data.
- the memory 19 stores at least the latest detected temperature T1 and detected temperature T2.
- the lower side temperature sensor 24 and the upper side temperature sensor 23 are respectively installed at different positions.
- the lower side temperature sensor 24 and the upper side temperature sensor 23 are arranged at the positions shown in the present embodiment to detect the temperature, so that the header side flow rate adjusting valve 9 of the header bypass pipe 8 is more suitable for distribution improvement. It becomes possible to control every time.
- the lower side temperature sensor 24 is arbitrarily selected as long as it is a lower heat transfer tube 15 (lower heat transfer tube 15B) than the heat transfer tube 15 (upper heat transfer tube 15A) provided with the upper side temperature sensor 23.
- the upper temperature sensor 23 is arranged in the uppermost heat transfer tube 15 and the lower temperature sensor 24 is arranged in the lowermost heat transfer tube 15. Therefore, the valve opening can be adjusted to a more optimal value.
- FIG. 12 is a diagram for explaining the relationship between the refrigerant and the temperature in the heat transfer tube 15 according to the third embodiment of the present invention.
- the temperature of the heat transfer tube 15 is a relatively short distance (about 1/2 when the total length is 1). Approaching air temperature.
- the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 can be controlled so that the liquid refrigerant reaches the upper part of the inflow side header 2.
- FIG. 13 is a diagram showing a control flow of the gas-liquid separator-side flow rate adjustment valve 6 and the header-side flow rate adjustment valve 9 according to Embodiment 3 of the present invention.
- the determination device 21 performs the processing shown in FIG. 13 when the operating condition is changed. The procedure until the determination device 21 determines the operating condition is the same as that described in the first embodiment.
- the gas-liquid separator side flow rate adjustment valve 6 is fully opened, and the header side flow rate adjustment valve 9 is fully closed. If it is determined that the operating condition B is satisfied, the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 are fully closed. If it is determined that the operating condition C is satisfied, the gas-liquid separator side flow rate adjustment valve 6 is fully closed and the header side flow rate adjustment valve 9 is fully opened.
- the determination apparatus 21 reads the data of the detected temperature T2 of the upper side temperature sensor 23 and the detected temperature T1 of the lower side temperature sensor 24 from the memory 19 (S21).
- the determination device 21 determines whether or not the operation condition B is satisfied (S22). If it determines with it being the driving
- the determination device 21 determines whether or not the detected temperature T1 and the detected temperature T2 satisfy the inequality T2-T1> 2 ° C. (S24).
- This inequality represents that the temperature of the upper heat transfer tube 15A in the outdoor heat exchanger 3 is more than 2 ° C. than the temperature of the lower heat transfer tube 15B.
- the high temperature of the upper heat transfer tube 15A indicates that the flow rate of the liquid refrigerant flowing through the upper heat transfer tube 15A is small. For this reason, it is necessary to supply a large amount of liquid refrigerant to the upper heat transfer tube 15A. Therefore, if the determination device 21 determines that the inequality is satisfied, the determination device 21 sends an opening signal for decreasing the opening of the gas-liquid separator-side flow rate adjustment valve 6 to the flow rate adjustment valve opening controller 17 (S25), and returns to S24.
- the determination device 21 determines whether or not the detected temperature T1 and the detected temperature T2 satisfy the inequality T2-T1> 2 ° C. (S28). As described above, this inequality indicates that the temperature of the upper heat transfer tube 15A in the outdoor heat exchanger 3 is more than 2 ° C. than the temperature of the lower heat transfer tube 15B. And it has shown that there is little flow volume of the liquid refrigerant which flows through 15 A of upper heat exchanger tubes. Therefore, when the determination device 21 determines that the inequality is satisfied, the determination device 21 sends an opening signal for increasing the opening of the header-side flow rate adjustment valve 9 to the flow rate adjustment valve opening controller 10 (S29), and returns to S28.
- FIG. 14 is a diagram showing a refrigeration cycle apparatus according to Embodiment 4 of the present invention.
- the same reference numerals as in FIG. 1 perform the same operations as those described in the first embodiment.
- the outdoor heat exchanger 3 is installed so that the refrigerant outlet of the outflow header 4 is higher than the refrigerant inlet of the inflow header 2. Is. Since the refrigerant outlet of the outflow header 4 is positioned higher than the refrigerant inlet of the inflow header 2, the liquid refrigerant is likely to rise.
- FIG. 15 is a diagram showing an outline of the outdoor heat exchanger 3 according to Embodiment 4 of the present invention.
- FIG. 15 shows the inflow side header 2, the outflow side header 4, and the heat transfer tube 15 connected to both headers.
- the distance (height) from the lower end of the inflow side header 2 and the outflow side header 4 to the lowermost heat transfer tube 15 is defined as L1.
- the distance (height) from the lowermost heat transfer tube 15 to the uppermost heat transfer tube 15 is L2.
- the flow path length of the refrigerant is longer, and accordingly, the flow resistance is increased and the liquid refrigerant is less likely to flow. For this reason, a large amount is distributed to the upper heat transfer tube 15 side, and distribution can be improved.
- FIG. FIG. 16 is a diagram showing the relationship between the inflow side header 2 and the header bypass pipe 8 according to Embodiment 5 of the present invention.
- a space having a height longer than the pitch P between the heat transfer tubes 15 is provided at the end portion of the inflow side header 2 (a portion higher than the uppermost heat transfer tube 15 in the inflow side header 2). 2 is connected to the header bypass pipe 8 at the uppermost end.
- FIG. 17 is a diagram showing another example of the relationship between the inflow side header 2 and the header bypass pipe 8 according to Embodiment 5 of the present invention.
- the header bypass pipe 8 is inserted into the end portion of the inflow side header 2 so as to protrude into the internal space from the inner wall surface of the inflow side header 2.
- the liquid refrigerant utilizes the characteristic that it easily flows along the side wall of the pipe, and the opening portion of the header bypass pipe 8 is located at a position where the liquid refrigerant is difficult to flow.
- it protrudes to the inner diameter center part of the inflow side header 2 since it will open to the position where a liquid refrigerant hardly flows, it is still better.
- FIG. 18 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 6 of the present invention.
- the same reference numerals as those in FIG. 1 are used for operations similar to those described in the first embodiment.
- the refrigeration cycle apparatus of the present embodiment includes an internal heat exchanger 26.
- the internal heat exchanger 26 includes a refrigerant that flows in a pipe (loader downstream pipe 29) that connects between the load machine 200 (load heat exchanger 18) and the expansion valve 16, and a low-pressure refrigerant that flows in the header bypass pipe 8. Heat exchange.
- the heat exchange energy of the refrigerant can be recovered by the refrigerant flowing through the load machine downstream pipe 29. For this reason, the fall of the heat exchange amount in the outdoor unit 100 can be prevented. Further, the refrigerant flowing through the load machine downstream pipe 29 can be cooled by the internal heat exchanger 26. For this reason, the gas refrigerant of the refrigerant
- FIG. 19 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 7 of the present invention.
- the refrigeration cycle apparatus of the present embodiment includes an outdoor side heat sensor 3 and a lower side temperature sensor 24, which are temperature detection means, in the outdoor heat exchanger 3 of the sixth embodiment described above. At least the upper and lower portions of the heat exchanger 3 are attached. The positions where the upper side temperature sensor 23 and the lower side temperature sensor 24 are attached, the temperature sensor material, and the like are the same as those described in the third embodiment. Further, the control method of the gas-liquid separator side flow rate adjustment valve 6 and the header side flow rate adjustment valve 9 based on the temperatures detected by the upper side temperature sensor 23 and the lower side temperature sensor 24 is also described in the third embodiment. It is the same.
- the refrigeration cycle apparatus can be applied to, for example, a hot water supply apparatus, a refrigeration apparatus, and the like.
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Abstract
Description
図1は本発明の実施の形態1に係る冷凍サイクル装置の構成を示す図である。図1において、実施の形態1の冷凍サイクル装置は、室外機(室外ユニット)100と負荷機(負荷側ユニット)200とを冷媒配管により配管接続して冷媒回路を構成し、冷媒を循環させる。室外機100は、負荷機200に対して冷媒を介した能力供給を行う。また、負荷機200は、対象となる負荷に熱を供給する。
図9は本発明の実施の形態2に係る冷凍サイクル装置の構成を示す図である。図9において、図1と同じ符号を付している機器などについては、実施の形態1で説明したことと同様の動作を行う。
図10は本発明の実施の形態3に係る冷凍サイクル装置の構成を示す図である。また、図11は本発明の実施の形態3に係る室外熱交換器3の概略を示す図である。本実施の形態では、温度検出手段である上部側温度センサー23および下部側温度センサー24を、室外熱交換器3の上部および下部に少なくとも取り付けるようにしたものである。上部側温度センサー23および下部側温度センサー24において、温度を検出するために、熱電対、白金測温抵抗体などを用いる。ただし、これらに限るものではない。上部側温度センサー23および下部側温度センサー24を取り付ける位置について説明する。図11に示すように、本実施の形態では、室外熱交換器3の下部側に設置される下部側温度センサー24と上部側に設置される上部側温度センサー23とを有している。下部側温度センサー24および上部側温度センサー23は、それぞれ設置位置における冷媒の温度を検出する。ここで、下部側温度センサー24が検出する温度をT1とし、上部側温度センサー23が検出する温度をT2とする。また、温度読み取り器25は、上部側温度センサー23および下部側温度センサー24が検出した温度を読み取り、メモリー19にデータとして記憶させる。メモリー19には、少なくとも直近の検出温度T1および検出温度T2のデータが記憶される。
図14は本発明の実施の形態4に係る冷凍サイクル装置を示す図である。図14において、図1と同じ符号を付している機器などについては、実施の形態1において説明したことと同様の動作などを行う。図14に示すように、本実施の形態の冷凍サイクル装置は、流出側ヘッダー4の冷媒流出口が流入側ヘッダー2の冷媒流入口よりも高い位置となるように室外熱交換器3を設置したものである。流出側ヘッダー4の冷媒流出口が流入側ヘッダー2の冷媒流入口よりも高く位置することで、液冷媒が上昇しやすくなる。ここで、流出側ヘッダー4における冷媒流出口の鉛直方向(高さ方向)位置が、流入側ヘッダー2のヘッダー冷媒流入口よりも高いほど液冷媒が上昇しやすくなるので、なおよい。
図16は本発明の実施の形態5に係る流入側ヘッダー2とヘッダーバイパス配管8との関係を示す図である。図16では、伝熱管15間のピッチPよりも長い高さを有する空間を流入側ヘッダー2の終端部(流入側ヘッダー2において最上段の伝熱管15よりも高い部分)に設け、流入側ヘッダー2の最上端においてヘッダーバイパス配管8と接続している。伝熱管15間のピッチPよりも長い空間を設けることで、この空間で気液二相冷媒が気液分離し、ガス冷媒がヘッダーバイパス配管8を通過するようになるため、ヘッダーバイパス配管8への液冷媒の流入を防ぐことができる。
図18は本発明の実施の形態6に係る冷凍サイクル装置の構成を示す図である。図18において図1と同じ符号を付している機器などについては、実施の形態1において説明したことと同様の動作などを行う。図18に示すように、本実施の形態の冷凍サイクル装置は、内部熱交換器26を備えることを特徴とするものである。内部熱交換器26は、負荷機200(負荷熱交換器18)と膨張弁16との間を接続する配管(負荷機下流配管29)に流れる冷媒と、ヘッダーバイパス配管8に流れる低圧の冷媒とを熱交換させる。
図19は本発明の実施の形態7に係る冷凍サイクル装置の構成を示す図である。図19において図1と同じ符号を付している機器などについては、実施の形態1において説明したことと同様の動作などを行う。図19に示すように、本実施の形態の冷凍サイクル装置は、前述した実施の形態6の室外熱交換器3に、温度検出手段である上部側温度センサー23および下部側温度センサー24を、室外熱交換器3の上部および下部に少なくとも取り付けるようにしたものである。上部側温度センサー23および下部側温度センサー24を取り付ける位置、温度センサーの材料などについては、実施の形態3において説明したことと同様である。また、上部側温度センサー23および下部側温度センサー24の検出した温度に基づく気液分離器側流量調整弁6およびヘッダー側流量調整弁9の制御方法についても、実施の形態3において説明したことと同様である。
Claims (11)
- 吸入した冷媒を圧縮して吐出する圧縮機と、
前記冷媒に放熱させて前記冷媒を凝縮させる凝縮器と、
凝縮された前記冷媒を減圧させる減圧装置と、
減圧装置を通過した気体状の前記冷媒と液体状の前記冷媒に分離する気液分離器と、
前記冷媒に吸熱させて前記冷媒を蒸発させる複数の伝熱管および流入した前記冷媒を該伝熱管に分配する流入側ヘッダーとを少なくとも有する蒸発器と
を配管接続して構成する冷媒回路の前記圧縮機、前記気液分離器および前記蒸発器となる室外熱交換器を少なくとも備え、
前記気液分離器が分離した前記気体状の冷媒を前記蒸発器をバイパスさせる気液分離器バイパス配管と、
該気液分離器バイパス配管を通過する前記冷媒の流量を調整する気液分離器側流量調整装置と、
前記流入側ヘッダーの冷媒流入側と反対側のヘッダー終端側において一端が前記流入側ヘッダーと接続され、前記流入側ヘッダーに流入した前記冷媒を吸引するヘッダーバイパス配管と、
該ヘッダーバイパス配管を通過する前記冷媒の流量を調整するヘッダー側流量調整装置と、
前記圧縮機の周波数から前記気液分離器側流量調整装置と前記ヘッダー側流量調整装置との開度を判定する判定装置と
をさらに備える室外機。 - 周波数帯f1>周波数帯f2>周波数帯f3を満足するように少なくとも3つの範囲に前記圧縮機の周波数帯を分けた場合に、
前記判定装置は、
前記圧縮機の周波数が、前記周波数帯f1の範囲内にあるときは、前記気液分離器側流量調整装置を開き、前記ヘッダー側流量調整装置を閉じると判定し、
前記圧縮機の周波数が、前記周波数帯f2の範囲内にあるときは、前記気液分離器側流量調整装置および前記ヘッダー側流量調整装置を閉じると判定し、
前記圧縮機の周波数が、前記周波数帯f3の範囲内にあるときは、前記気液分離器側流量調整装置を閉じ、前記ヘッダー側流量調整装置を開くと判定する請求項1に記載の室外機。 - 前記複数の伝熱管のうち、一部の前記伝熱管を、前記ヘッダーバイパス配管の一部とする請求項1または請求項2に記載の室外機。
- 前記流入側ヘッダーの前記冷媒流入側の前記伝熱管と前記ヘッダー終端側の前記伝熱管とに少なくとも取り付けられ、それぞれ取り付けられた位置の温度を検出する温度検出手段をさらに備え、
前記冷媒流入側の前記伝熱管の検出温度をT1とし、前記ヘッダー終端側の前記伝熱管の検出温度をT2とした場合に、
前記判定装置は、
前記圧縮機の周波数が、前記周波数帯f1の範囲内にあるとき、T2-T1>2℃である場合には、前記気液分離器側流量調整装置の開度を減少させると判定し、T2-T1<-2℃である場合には、前記気液分離器側流量調整装置の開度を増加させると判定し、
前記圧縮機の周波数が、前記周波数帯f3の範囲内にあるとき、T2-T1>2℃である場合には、前記ヘッダー側流量調整装置の開度を増加させると判定し、T2-T1<-2℃である場合には、前記気液分離器側流量調整装置の開度を増加させると判定する請求項2または請求項3に記載の室外機。 - 前記複数の伝熱管を通過した前記冷媒を合流させて流出させる流出側ヘッダーの冷媒流出口が、前記流入側ヘッダーの冷媒流入口の位置よりも高い位置にあることを特徴とする請求項1~請求項4のいずれか一項に記載の室外機。
- 前記ヘッダーバイパス配管を前記液体状の冷媒が通過しない構造とすることを特徴とする請求項1~請求項5のいずれか一項に記載の室外機。
- 前記冷媒流入側から最も遠い位置にある前記伝熱管と前記流入側ヘッダーの最終端部分の間の距離が、前記伝熱管間の距離よりも長い構造とすることを特徴とする請求項6に記載の室外機。
- 前記ヘッダーバイパス配管の前記一端を前記流入側ヘッダーに突出させて、前記流入側ヘッダーと接続される構造とすることを特徴とする請求項6に記載の室外機。
- 請求項1~8のいずれか一項に記載の室外機と、
冷媒に放熱させて前記冷媒を凝縮させる凝縮器となる負荷熱交換器を有する負荷機と
を配管接続して冷媒回路を構成することを特徴とする冷凍サイクル装置。 - 前記負荷熱交換器と減圧装置とを接続する配管と、前記ヘッダーバイパス配管との間に内部熱交換器を備え、
該内部熱交換器は、前記負荷熱交換器側から前記減圧装置側に流れる前記冷媒と前記ヘッダーバイパス配管を流れる前記冷媒とを熱交換する請求項9に記載の冷凍サイクル装置。 - 空気調和装置または冷凍装置である請求項9または請求項10に記載の冷凍サイクル装置。
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Also Published As
Publication number | Publication date |
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CN106574812A (zh) | 2017-04-19 |
JPWO2016017430A1 (ja) | 2017-04-27 |
EP3176521A1 (en) | 2017-06-07 |
EP3176521B1 (en) | 2021-06-30 |
JP6359102B2 (ja) | 2018-07-18 |
US20170205128A1 (en) | 2017-07-20 |
US10240837B2 (en) | 2019-03-26 |
EP3176521A4 (en) | 2018-02-28 |
CN106574812B (zh) | 2019-07-19 |
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