WO2017094117A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2017094117A1 WO2017094117A1 PCT/JP2015/083754 JP2015083754W WO2017094117A1 WO 2017094117 A1 WO2017094117 A1 WO 2017094117A1 JP 2015083754 W JP2015083754 W JP 2015083754W WO 2017094117 A1 WO2017094117 A1 WO 2017094117A1
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- pipe
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- compressor
- refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/08—Compressors specially adapted for separate outdoor units
- F24F1/12—Vibration or noise prevention thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/04—Devices damping pulsations or vibrations in fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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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
- F25B41/00—Fluid-circulation arrangements
Definitions
- the present invention relates to an air conditioner that suppresses pressure pulsation caused by driving of a compressor.
- the air conditioner has a refrigerant circuit in which an outdoor unit having a compressor and an indoor unit are connected by a refrigerant pipe, and performs a cooling operation or a heating operation by driving the compressor.
- a compressor When the compressor is driven, pressure pulsation with a frequency corresponding to the operating frequency occurs.
- a specific resonance frequency exists in the pipe through which the refrigerant of the air conditioner flows, depending on the pressure state of the refrigerant and the length or volume of the pipe until the refrigerant flows into the indoor unit.
- Patent Document 1 discloses a flow channel device in which a plurality of small holes for blowing a jet flow are formed in an inner pipe through which a refrigerant flows, and the pressure pulsation is reduced by blowing the refrigerant from the small holes to the outer periphery from the inner pipe.
- the present invention has been made in order to solve the above-described problems, and an air conditioner capable of suppressing the occurrence of vibration due to pressure pulsation without incurring costs in accordance with the installation state of the air conditioner.
- the purpose is to provide.
- An air conditioner is an air conditioner in which an outdoor unit having a compressor and an indoor unit are connected via a gas pipe and a liquid pipe, and detects the discharge pressure of refrigerant discharged from the compressor.
- the suction pressure sensor for detecting the suction pressure of the refrigerant on the suction side of the compressor, the discharge pressure detected by the discharge pressure sensor, and the suction pressure detected by the suction pressure sensor, the compressor
- a control device that sets a range of the operating frequency, and the control device calculates a pipe volume of the entire pipe through which the refrigerant flows when the outdoor unit and the indoor unit are in a heating operation;
- a frequency table in which the discharge pressure, the differential pressure between the discharge pressure and the suction pressure, the pipe volume, the resonance frequency of the entire pipe through which the refrigerant flows, and the pipe volume calculated by the volume calculation unit ,Discharge pressure
- a frequency estimation unit that estimates the resonance frequency by referring to the frequency table based on the differential pressure between the discharge pressure and the suction pressure
- the resonance frequency is estimated from the pipe volume of the entire pipe through which the refrigerant flows, and the operation frequency of the compressor is set so as not to be operated by the estimated resonance frequency.
- Generation of noise due to pressure pulsation can be suppressed in accordance with the installation state of the air conditioner without separately installing a muffler for canceling the resonance frequency.
- FIG. 1 is a refrigerant circuit diagram illustrating an example of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
- the air-conditioning apparatus 1 will be described with reference to FIG.
- the air conditioner 1 performs a cooling operation or a heating operation using a refrigeration cycle (heat pump cycle) for circulating a refrigerant.
- a refrigeration cycle heat pump cycle
- one outdoor unit 10 and two indoor units 30 are connected by a gas pipe 2 a and a liquid pipe 2 b to constitute a refrigerant circuit.
- the case where two indoor units 30 are connected to the outdoor unit 10 is illustrated, but one or more indoor units 30 may be connected to the outdoor unit 10. That's fine.
- the outdoor unit 10 includes a compressor 11, a flow path switch 14, and an outdoor heat exchanger 15, and the compressor 11, the flow path switch 14, and the outdoor heat exchanger 15 are connected in series by a refrigerant pipe. .
- the compressor 11 compresses the sucked refrigerant into a high temperature / high pressure state.
- the compressor 11 is subjected to capacity control by controlling the operation frequency by, for example, power supply frequency conversion by an inverter circuit.
- the flow path switch 14 is composed of, for example, a four-way valve, and switches the refrigerant flow between the cooling operation and the heating operation.
- the outdoor heat exchanger 15 is composed of, for example, a fin-and-tube heat exchanger, and performs heat exchange between the refrigerant and the air.
- the outdoor heat exchanger 15 functions as a condenser or a radiator that condenses the refrigerant discharged from the compressor 11 during the cooling operation, and functions as an evaporator that evaporates the refrigerant flowing from the indoor unit 30 during the heating operation.
- the outdoor unit 10 may be provided with an outdoor fan that blows air to the outdoor heat exchanger 15.
- An oil separator 12 and a check valve 13 are connected between the compressor 11 and the flow path switch 14.
- the oil separator 12 is provided on the discharge side of the compressor 11 and separates the refrigerating machine oil from the refrigerant gas discharged from the compressor 11 and mixed with the refrigerating machine oil.
- the oil separator 12 is connected to the flow path switch 14 and the accumulator 20, and the refrigerant that has turned into gas flows to the flow path switch 14 side, and the refrigeration oil passes through the oil return bypass circuit 24 and the suction side of the compressor 11. To flow.
- the oil return bypass circuit 24 is provided with an oil return bypass capillary 24a and an oil return bypass solenoid valve 24b.
- the oil return bypass capillary 24 a adjusts the flow rate of the refrigerating machine oil passing through the oil return bypass circuit 24.
- the oil return bypass solenoid valve 24b is connected in parallel to the oil return bypass capillary 24a, and adjusts the flow rate of the refrigerating machine oil flowing through the oil return bypass circuit 24 by opening / closing control.
- the check valve 13 is provided in the refrigerant pipe between the oil separator 12 and the flow path switch 14 and prevents the refrigerant from flowing backward to the discharge side of the compressor 11 when the compressor 11 is stopped.
- . 1 illustrates the case where the oil separator 12 and the check valve 13 are provided, but either the oil separator 12 or the check valve 13 may be provided,
- the flow path switch 14 may be directly connected.
- the air conditioner 1 has a sub outdoor heat exchanger 16 connected between the check valve 13 and the flow path switch 14.
- the sub outdoor heat exchanger 16 is composed of, for example, a fin-and-tube heat exchanger and, like the outdoor heat exchanger 15, performs heat exchange between the refrigerant flowing in via the flow path switch 14 and the air. It is.
- a sub flow path switch 22a composed of, for example, a four-way valve or a three-way valve.
- an on-off valve 22b is provided on the outdoor heat exchanger 15 side, and the refrigerant that flows to the outdoor heat exchanger 15 and the sub-outdoor heat exchanger 16 during operation by the sub-channel switch 22a and the on-off valve 22b.
- the capacity can be controlled.
- the refrigerant discharged from the compressor 11 flows into the sub outdoor heat exchanger 16.
- the sub flow switching device 22a connects the sub outdoor heat exchanger 16 and the accumulator 20 in the heating operation magnet, the refrigerant flowing out from the sub outdoor heat exchanger 16 is returned to the accumulator 20.
- the air conditioner 1 includes the inter-refrigerant heat exchanger 17 and the flow rate adjusting valve 18 provided between the outdoor heat exchanger 15 and the indoor unit 30.
- the inter-refrigerant heat exchanger 17 performs heat exchange between the refrigerant flowing through the liquid pipe 10 x and the refrigerant flowing through the bypass pipe 19.
- the bypass pipe 19 branches from the liquid pipe 10 x between the inter-refrigerant heat exchanger 17 and the flow rate adjustment valve 18 and flows into the inter-refrigerant heat exchanger 17.
- the bypass pipe 19 is provided with a bypass flow rate adjustment valve 19 a that adjusts the flow rate of the refrigerant flowing through the bypass pipe 19.
- the bypass flow rate adjusting valve 19a is constituted by a valve whose opening degree can be variably controlled, such as an electronic expansion valve, and functions as a pressure reducing valve or an expansion valve.
- the flow rate adjusting valve 18 is provided on the downstream side of the branch point of the bypass pipe 19 and is configured, for example, by an electronic expansion valve or the like that can be variably controlled, and functions as a pressure reducing valve or an expansion valve.
- an accumulator 20 that stores excess refrigerant circulating in the refrigerant circuit is provided on the suction side of the compressor 11. Further, between the outdoor unit 10 and the indoor unit 30, there are provided on-off valves 3a and 3b which are opened or closed manually by the control device 40 or installed to adjust the pressure fluctuation in the refrigeration cycle.
- the two indoor units 30 are connected in parallel to the outdoor unit 10 via the gas pipe 2a and the liquid pipe 2b, respectively, and expansion valves connected in series to the indoor heat exchanger 31 and the indoor heat exchanger 31, respectively. 32.
- the two indoor units 30 are illustrated as having the same components.
- the indoor heat exchanger 31 is composed of, for example, a fin tube heat exchanger, and performs heat exchange between the refrigerant and the air.
- the indoor heat exchanger 31 functions as an evaporator during cooling operation and as a condenser (or radiator) during heating operation.
- the expansion valve 32 functions as a pressure reducing valve or an expansion valve, and expands the refrigerant by reducing the pressure.
- the expansion valve 32 may be constituted by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve.
- the refrigerant flow path in the flow path switching unit 14 is switched so that the outdoor heat exchanger 15 becomes an evaporator and the indoor heat exchanger 31 becomes a condenser.
- the refrigerant discharged from the compressor 11 passes through the oil separator 12, the check valve 13, and the flow path switch 14, and flows into the indoor unit 30 through the gas pipe 2a.
- the indoor heat exchanger 31 heats the indoor air as the refrigerant dissipates heat to the indoor air.
- the refrigerant that has flowed out of the indoor heat exchanger 31 flows into the outdoor unit 10 through the expansion valve 32 and the liquid pipe 2b, and then flows into the outdoor heat exchanger 15 through the inter-refrigerant heat exchanger 17.
- the refrigerant exchanges heat with outdoor air, and then becomes a low-temperature / low-pressure refrigerant and is stored in the accumulator 20.
- the outdoor unit 10 includes a control device 40 that controls driving of each component such as the compressor 11 and the flow path switch 14.
- the indoor unit 30 is mounted with a control device 50 that controls driving of each actuator (for example, an expansion valve 32 or an indoor fan not shown) mounted on the indoor unit 30.
- FIG. 1 shows an example in which the control device 50 is mounted on each of the two indoor units 30. However, one control device controls both of the two indoor units 30. Also good.
- the control apparatus 50 is mounted in both the indoor units 30, the mutual control apparatus 50 is communicable by wire or radio
- the control device 50 mounted on the indoor unit 30 can communicate with the control device 40 mounted on the outdoor unit 10 in a wired or wireless manner.
- the control device 40 and the control device 50 are configured by, for example, a microcomputer that can control each actuator.
- the outdoor unit 10 includes a discharge pressure sensor 61a, a discharge temperature sensor 61b, a suction pressure sensor 62a, a suction temperature sensor 62b, a refrigerant temperature sensor 63, an intermediate temperature sensor 65, an outside air temperature sensor 64, and a supercooling temperature sensor 66. And a return temperature sensor 67.
- the discharge pressure sensor 61 a is provided between the oil separator 12 and the flow path switch 14 and detects the pressure (high pressure) of the refrigerant discharged from the compressor 11.
- the discharge temperature sensor 61b is provided between the compressor 11 and the oil separator 12, and detects the temperature of the refrigerant discharged from the compressor 11.
- the suction pressure sensor 62 a is provided on the upstream side of the accumulator 20 and detects the pressure (low pressure) of the refrigerant sucked into the compressor 11.
- the suction temperature sensor 62 b is provided between the accumulator 20 and the compressor 11 and detects the temperature of the refrigerant sucked into the compressor 11.
- the outdoor temperature sensor 64 detects the ambient temperature of the outdoor unit 10.
- the refrigerant temperature sensor 63 is provided between the outdoor heat exchanger 15 and the inter-refrigerant heat exchanger 17 and detects the temperature of the refrigerant passing between the outdoor heat exchanger 15 and the inter-refrigerant heat exchanger 17. is there.
- the intermediate temperature sensor 65 is provided between the branch point of the bypass pipe 19 and the flow rate adjusting valve 18, and detects the intermediate temperature of the refrigerant passing through the liquid pipe 10x.
- the supercooling temperature sensor 66 is provided in the bypass pipe 19 and detects the temperature of the refrigerant after passing through the inter-refrigerant heat exchanger 17.
- the return temperature sensor 67 is provided between the flow path switch 14 and the accumulator 20 and detects the return temperature of the refrigerant returning to the accumulator 20.
- the indoor unit 30 is provided with an indoor gas pipe temperature sensor 71 and an indoor liquid temperature sensor 72.
- the indoor gas pipe temperature sensor 71 is provided in the gas pipe 2 a connected to the indoor heat exchanger 31, and detects the refrigerant gas pipe temperature on the gas side of the indoor heat exchanger 31.
- the indoor liquid temperature sensor 72 is provided in the liquid pipe 2 b connected to the indoor heat exchanger 31 and detects the temperature of the refrigerant on the liquid side of the indoor heat exchanger 31.
- the pressure information detected by each pressure sensor and the temperature information detected by each temperature sensor are sent to the control device 40 and the control device 50 as signals.
- the control device 40 and the control device 50 control each actuator based on signals transmitted from each pressure sensor and each temperature sensor.
- the control device 40 has a function of setting the operating range of the operating frequency of the compressor 11 so as to prevent the piping of the air conditioner 1 from vibrating abnormally.
- FIG. 2 is a functional block diagram showing an example of the control device of FIG. 1, and the control device 40 will be described with reference to FIG. 1 and FIG. 2 includes a volume calculation unit 41, a frequency estimation unit 42, a condition setting unit 43, an operation control unit 44, and a data storage unit 45.
- the volume calculation unit 41 calculates the pipe volume VL of the entire pipe through which the refrigerant flows when the outdoor unit 10 and the indoor unit 30 are in operation.
- the pipe volume VL of the entire pipe is the sum of the pipe volumes inside the outdoor unit 10 and the indoor unit 30, and the pipe volumes of the gas pipe 2a and the liquid pipe 2b.
- the pipe volume (pipe length) inside the outdoor unit 10 and the indoor unit 30 is known from the time of manufacture and is stored in the data storage unit 45 in advance.
- the pipe volumes of the gas pipe 2a and the liquid pipe 2b differ depending on the length of the local pipe at the installation location. Therefore, the volume calculation unit 41 calculates the pipe volume VL in consideration of the gas pipe 2a and the liquid pipe 2b having different pipe volumes depending on the installation location.
- the volume calculation unit 41 uses the operating frequency f of the compressor 11, the discharge pressure, the differential pressure between the discharge pressure and the suction pressure, and the pipe diameter of the gas pipe 2a to determine the volume VL of the entire pipe through which the refrigerant flows. calculate.
- the volume calculation unit 41 includes a pipe diameter acquisition unit 41a, a circulation amount calculation unit 41b, and a volume estimation unit 41c.
- the pipe diameter acquisition unit 41a acquires the pipe diameter of the gas pipe 2a connected to the outdoor unit 10 and each indoor unit 30.
- the data storage unit 45 stores, for example, table information in which the capacity (horsepower) of the outdoor unit 10 and the indoor unit 30 is associated with the pipe diameter, and the pipe diameter acquisition unit 41a is stored in the data storage unit 45.
- the pipe diameter of the gas pipe 2a is acquired with reference to the table information stored in the above.
- the pipe diameter acquisition part 41a has illustrated about the case where the pipe length is acquired from the data storage part 45, you may acquire the pipe diameter input from an operator using input devices, such as a keyboard, for example. .
- the circulation amount calculation unit 41b uses the discharge pressure detected by the discharge pressure sensor 61a, the suction pressure detected by the suction pressure sensor 62a, and the saturated gas pressure corresponding to the return temperature detected by the return temperature sensor 67.
- the refrigerant circulation amount flowing in the refrigerant circuit during operation is calculated.
- Various known methods can be used as the refrigerant circulation amount calculation method.
- the volume estimation unit 41c is a pipe of the refrigerant circuit through which the refrigerant flows during operation based on the pipe diameter of the gas pipe 2a acquired by the pipe diameter acquisition unit 41a and the refrigerant circulation amount calculated by the circulation amount calculation unit 41b.
- the volume VL is calculated.
- the volume estimation unit 41c calculates the pressure loss in the gas pipe 2a by the discharge pressure detected by the discharge pressure sensor 61a and the saturated gas pressure corresponding to the gas pipe temperature detected by the indoor gas pipe temperature sensor 71. calculate. Thereafter, the volume estimation unit 41c calculates the pipe length of the gas pipe 2a from the refrigerant circulation amount, the pressure loss, and the pipe diameter.
- the volume estimation unit 41c determines that the gas pipe 2a and the liquid pipe 2b have substantially the same pipe length, and obtains the pipe volumes of the gas pipe 2a and the liquid pipe 2b.
- the pipe volume VL of the entire pipe is calculated by adding the pipe volume of the machine 30.
- the frequency estimation unit 42 estimates the resonance frequency fv with reference to the frequency table based on the pipe volume VL calculated by the volume calculation unit 41, the discharge pressure, and the differential pressure between the discharge pressure and the suction pressure. It is.
- the data storage unit 45 stores a frequency table used for estimating the resonance frequency fv.
- the frequency estimation unit 42 refers to the frequency table based on the discharge pressure, the differential pressure, and the pipe volume VL. Thus, the resonance frequency fv is estimated.
- FIG. 3 is a schematic diagram illustrating an example of a frequency table.
- the frequency table is stored in a state in which the discharge pressure, the differential pressure between the discharge pressure and the suction pressure, the pipe volume, and the resonance frequency fv of the entire pipe through which the refrigerant flows are associated with each other.
- the discharge pressure is classified into, for example, a case where the discharge pressure is less than 30 kg / cm 2 and a case where the discharge pressure is 30 kg / cm 2 or more. 15K, 15-20K, 20K or more).
- the pipe volume VL is classified into three ranges (lower threshold ⁇ ⁇ VL, lower threshold ⁇ ⁇ VL ⁇ upper threshold ⁇ , VL> upper threshold ⁇ ) for each of the four classes of differential pressure ⁇ P, and resonance occurs for each class.
- the operation control unit 44 controls the operation frequency f within the range between the lower limit operation frequency fmin and the upper limit frequency fmax.
- the condition setting unit 43 sets the operation condition so as to avoid the resonance frequency fv being included in the range between the lower limit operation frequency fmin and the upper limit frequency fmax.
- the resonance frequency fv often occurs in a low frequency region of about 10 to 25 Hz.
- the correction value ⁇ f is set in advance in consideration of variations in local piping (variations in detection accuracy), but can be arbitrarily changed. Thus, by removing the resonance frequency fv from the operating range of the compressor 11, the abnormal vibration of the piping in the air conditioner 1 can be corrected and the generation of noise can be suppressed.
- the condition setting unit 43 does not change the operation condition, and the data storage unit 45 stores the lower limit operation frequency fmin as it is.
- the operation control unit 44 controls the compressor 11 based on the operation conditions stored in the data storage unit 45.
- the resonance frequency fv may change. For this reason, when the operating state changes, the resonance frequency fv is calculated and determined again.
- FIG. 4 is a flowchart showing the flow of control processing in the first embodiment, and an example of the operation of the control device will be described with reference to FIGS.
- the pipe diameter acquisition unit 41a refers to the data storage unit 45 based on the capacity (horsepower) of the outdoor unit 10 and the indoor unit 30, and the gas pipe 2a and the liquid pipe
- the pipe diameter 2b is acquired (step ST1).
- operation is instruct
- the control device 40 collects the detection information by the sensors installed in the outdoor unit 10 and the indoor unit 30 and the operating frequency f of the compressor 11. Thereafter, the pipe diameters of the gas pipe 2a and the liquid pipe 2b are acquired in the pipe diameter acquisition unit 41a. Further, the circulation amount calculation unit 41 b calculates the refrigerant circulation amount that flows through the entire air conditioner 1 from the discharge pressure, the suction pressure (return temperature), and the operating frequency of the compressor 11. In the volume estimation unit 41c, the pressure loss of the gas pipe 2a is calculated based on the saturated gas pressure corresponding to the discharge pressure and the indoor gas pipe temperature, and the refrigerant flows based on the pipe diameter, the refrigerant circulation amount, and the pressure loss. The pipe volume VL of the entire pipe is calculated (step ST3).
- the resonance frequency fv in the pipe volume is based on the resonance frequency table based on the high pressure detected by the pipe volume and discharge pressure sensor 61a, the low pressure detected by the suction pressure sensor 62a, and the differential pressure between the high pressure and the low pressure. (See step ST4, FIG. 7).
- the condition setting unit 43 determines whether or not the resonance frequency fv is included in the operation range of the compressor 11 (step ST5).
- the resonance frequency fv exists within the operation frequency range of the compressor 11.
- the piping of the air conditioner 1 may vibrate abnormally, and the operating frequency range of the compressor 11 is changed (step ST6).
- step ST5 when the lower limit operation frequency fmin is greater than the resonance frequency fv (NO in step ST5), it is determined that the entire pipe through which the refrigerant flows during operation does not resonate in the operation range of the compressor 11.
- the outdoor unit 10 and the indoor unit 30 in operation are changed as the timing for changing the lower limit operation frequency fmin, the pipe volume to which the refrigerant flows changes. Accordingly, since the resonance frequency fv may change, the calculation and determination of the resonance frequency fv is performed again (step ST3 to step ST6) at the timing when the operating state changes again (YES in step ST7).
- the resonance frequency fv is estimated from the pipe volume VL of the entire pipe through which the refrigerant flows, and the operation frequency of the compressor 11 is set so as not to be operated at the estimated resonance frequency fv. Accordingly, it is possible to suppress the generation of noise due to pressure pulsation corresponding to the installation state of the air conditioner 1 without separately installing a muffler for canceling the resonance frequency fv.
- the resonance frequency fv varies depending on the local piping or the like, it is necessary to set a lower limit operating frequency for each air conditioner 1 individually. Therefore, there is a possibility that the lower limit operating frequency of all the air conditioners can be increased in order to obtain an operating frequency that can include all the air conditioners 1. Then, in the operation with a low load such as the operation of only a small capacity indoor unit, there remains a problem that the frequency of starting and stopping increases.
- the resonance frequency fv is estimated from the piping volume VL of the entire piping through which the refrigerant flows in order to consider the installation state of the air conditioner 1 such as the local piping.
- the operation frequency of the compressor 11 is set so as not to be operated at the estimated resonance frequency fv. Then, the generation of noise due to pressure pulsation can be suppressed in accordance with the installation state of the air conditioner 1 without using a muffler or the like.
- condition setting unit 43 compares the resonance frequency fv with the lower limit operation frequency fmin in the range of the operation frequency f, and sets the resonance frequency fv as the lower limit operation frequency fmin when the resonance frequency fv is greater than the lower limit operation frequency fmin. When it is, it is possible to reliably prevent pressure pulsation from occurring during operation at a low operating frequency based on an empirical rule that the resonance frequency fv tends to exist in the low frequency region.
- the volume calculation unit 41 acquires a pipe diameter of the gas pipe 2a, a pipe diameter acquisition unit 41a, a circulation amount calculation unit 41b that calculates a circulation amount of refrigerant flowing through the outdoor unit 10 and the indoor unit 30 that are in operation,
- the gas pipe 2a has a volume estimation unit 41c that estimates the pipe volume of the gas pipe 2a based on the pipe diameter and the refrigerant circulation amount and calculates the pipe volume VL of the entire pipe through which the refrigerant flows
- the gas pipe 2a is installed at In consideration of the fact that the pipe length varies depending on, etc., the pipe volume of the gas pipe 2a can be accurately estimated, and the resonance frequency fv can be accurately derived.
- FIG. FIG. 5 is a refrigerant circuit diagram illustrating an example of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- the air-conditioning apparatus 100 will be described with reference to FIG.
- the air conditioner 100 of FIG. 5 differs from the air conditioner of FIG. 1 in that two outdoor units 110A and 110B are connected to the indoor unit 30 in parallel.
- the outdoor units 110A and 110B are connected in parallel to each other via gas branch pipes 102a and 102b and a distributor 103a, and the distributor 103a is connected to each indoor unit via a gas pipe 102c. 30.
- the outdoor units 110A and 110B are connected to each other in parallel via liquid branch pipes 102p and 102q and a distributor 103p, and the distributor 103p is connected to each indoor unit 30 via a liquid pipe 102r.
- 1 illustrates the case where the distributor 103a and the distributor 103p are mounted on the air conditioner 100, the connection may be made using a T-shaped tube or the like.
- FIG. 6 is a flowchart showing an operation example of the air conditioner of FIG. 5, and an operation example of the air conditioner 100 will be described with reference to FIGS. 5 and 6.
- the same steps as those in the flowchart of FIG. 4 are denoted by the same reference numerals, and the description thereof is omitted.
- the condition setting unit 43 in FIG. 2 compares the lower limit operating frequencies fmina and fminb with the resonance frequency fv for each of the outdoor units 110A and 110B (steps ST15a and ST15b).
- step ST15a If the lower limit operating frequency fmina is higher than the resonance frequency fv (NO in step ST15a), it is determined that there is no point in the operating range of the compressor 11 on the outdoor unit 110A side where the piping of the present system resonates. Similarly, when the lower limit operation frequency fminb is higher than the resonance frequency fv (NO in step ST15b), it is determined that there is no point in the operation range of the compressor 11 on the outdoor unit 110B side where the piping of the present system resonates.
- the lower limit operating frequency fmina is set to the value of the resonance frequency fv + ⁇ f (step ST16a).
- the lower limit operating frequency fminb is set to the value of the resonance frequency fv + ⁇ f (step ST16b).
- the resonance frequency fv in consideration of the pipe lengths of the gas branch pipes 102a and 102b and the liquid branch pipes 102p and 102q. Calculation will be performed. Therefore, similarly to the first embodiment, the operation frequency of the compressor 11 is set not to be operated at the estimated resonance frequency fv, so that the air conditioner 100 can be installed without using a muffler or the like. In addition, generation of noise due to pressure pulsation can be suppressed.
- FIG. 7 is a refrigerant circuit diagram illustrating an example of the air-conditioning apparatus according to Embodiment 3 of the present invention.
- the air-conditioning apparatus 200 will be described with reference to FIG.
- the air conditioner 100 of FIG. 7 is different from the air conditioner of FIG. 1 in that three outdoor units 210A, 210B, and 210C are connected to the indoor unit 30 in parallel.
- the outdoor units 210A and 210B are connected in parallel to each other via gas branch pipes 202a and 202b and a distributor 205a, and the distributor 205a is connected to the gas branch pipes 203a and 203b and the distributor 205b.
- the distributor 205b is connected to the indoor unit 30 via the gas pipe 204a, and the outdoor units 210A, 210B, and 210C are connected in parallel to each other.
- the outdoor units 210B and 210C are connected in parallel to each other via the liquid branch pipes 202p and 202q and the distributor 205p, and the distributor 205p is connected to the outdoor unit 210A via the liquid branch pipes 202r and 202s and the distributor 205r. It is connected.
- the distributor 205r is connected to the indoor unit 30 via the liquid pipe 202t, and the outdoor units 210A, 210B, and 210C are connected in parallel to each other.
- FIG. 8 is a flowchart showing an operation example of the control device of FIG. 7, and an operation example of the air conditioner 100 will be described with reference to FIGS.
- the same steps as those in the flowchart of FIG. 4 are denoted by the same reference numerals and description thereof is omitted.
- the condition setting unit 43 in FIG. 2 compares the lower limit operating frequencies fmina, fminb, fminc and the resonance frequency fv for each of the outdoor units 210A to 210C (steps ST25a to ST25c).
- the resonance frequency fv exists within the operation range of the compressor 11 on the outdoor unit 110A side.
- the lower limit operating frequency fmina is set to the value of the resonance frequency fv + ⁇ f (step ST26a).
- the resonance frequency fv exists within the operation range of the compressor 11 on the outdoor unit 210B side.
- the lower limit operating frequency fminb is set to the value of the resonance frequency fv + ⁇ f (step ST26b).
- the resonance frequency fv exists within the operation range of the compressor 11 on the outdoor unit 210C side.
- the lower limit operating frequency fminc is set to the value of the resonance frequency fv + ⁇ f (step ST26c).
- the resonance frequency fv is calculated in consideration of the pipe lengths of the gas branch pipe and the liquid branch pipe. It will be. Therefore, as in the first embodiment, the operation frequency of the compressor 11 is set not to be operated at the estimated resonance frequency fv, so that the air conditioner 200 is installed without using a muffler or the like. In addition, generation of noise due to pressure pulsation can be suppressed.
- the embodiment of the present invention is not limited to the above embodiment, and various changes can be made.
- the condition setting unit 43 in FIG. 2 compares the lower limit operation frequency fmin and the resonance frequency fv, the case where the operation condition is set so that the lower limit operation frequency fmin is greater than the resonance frequency fv is illustrated. If the resonance frequency fv is not included in the range of the operating frequency, the present invention is not limited to this. For example, when the resonance frequency fv is included between the lower limit operation frequency fmin and the upper limit frequency fmax, the condition setting unit 43 may set the operation condition so as to exclude only the resonance frequency fv from the operation range. Good.
- the case where the range of the operating frequency f for each of the outdoor units 110A, 110B, 210A to 210C is compared with the resonance frequency fv is exemplified, but the lower limit operating frequency during operation is illustrated.
- the lowest lower limit operating frequency fmin among fmin may be selected and compared with the resonance frequency fv.
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Abstract
Description
図1は、本発明の実施の形態1に係る空気調和装置1の一例を示す冷媒回路図であり、図1に基づいて空気調和装置1について説明する。空気調和装置1は、冷媒を循環させる冷凍サイクル(ヒートポンプサイクル)を利用して、冷房運転または暖房運転を行なうものである。図1の空気調和装置1は、1台の室外機10と2台の室内機30とがガス配管2a及び液配管2bにより接続され、冷媒回路を構成している。なお、図1の空気調和装置1において、2台の室内機30が室外機10に接続されている場合について例示しているが、1台以上の室内機30が室外機10に接続されていればよい。
図5は、本発明の実施の形態2に係る空気調和装置の一例を示す冷媒回路図であり、図5を参照して空気調和装置100について説明する。なお、図5の空気調和装置100において図1の空気調和装置1と同一の構成を有する部位には同一の符号を付してその説明を省略する。図5の空気調和装置100が図1の空気調和装置と異なる点は、2台の室外機110A、110Bが室内機30に対し並列に接続されている点である。
図7は、本発明の実施の形態3に係る空気調和装置の一例を示す冷媒回路図であり、図7を参照して空気調和装置200について説明する。なお、図7の空気調和装置100において図1の空気調和装置1と同一の構成を有する部位には同一の符号を付してその説明を省略する。図7の空気調和装置100が図1の空気調和装置と異なる点は、3台の室外機210A、210B、210Cが室内機30に対し並列に接続されている点である。
Claims (4)
- 圧縮機を有する室外機と室内機とをガス配管及び液配管を介して接続した空気調和装置であって、
前記圧縮機から吐出される冷媒の吐出圧力を検知する吐出圧力センサと、
前記圧縮機の吸入側の冷媒の吸入圧力を検知する吸入圧力センサと、
前記吐出圧力センサにより検知された前記吐出圧力と、前記吸入圧力センサにより検知された吸入圧力とに基づいて、前記圧縮機の運転周波数の範囲を設定する制御装置と
を有し、
前記制御装置は、
前記室外機及び前記室内機が暖房運転している際に、冷媒が流れている配管全体の配管容積を算出する容積算出部と、
前記吐出圧力と、前記吐出圧力と吸入圧力との差圧と、前記配管容積と、冷媒が流れている配管全体の共振周波数とが対応づけされた周波数テーブルと、
前記容積算出部において算出された前記配管容積と、前記吐出圧力と、前記吐出圧力と前記吸入圧力との差圧とに基づいて、前記周波数テーブルを参照して共振周波数を推定する周波数推定部と、
前記圧縮機の運転周波数が前記周波数推定部において推定された共振周波数になることを規制するように、前記圧縮機の運転周波数の範囲を設定する条件設定部と
を備える空気調和装置。 - 前記条件設定部は、共振周波数と運転周波数の範囲の下限運転周波数とを比較し、共振周波数が下限運転周波数より大きい場合、共振周波数を下限運転周波数として設定するものである請求項1に記載の空気調和装置。
- 前記ガス配管から前記室内機に流れる冷媒のガス配管温度を検知する室内ガス配管温度センサをさらに備え、
前記容積算出部は、
前記ガス配管の配管径を取得する配管径取得部と、
前記吐出圧力と、前記吸入圧力と、前記室内ガス配管温度センサにより検知されたガス配管温度と、前記圧縮機の運転周波数とに基づいて、運転している前記室外機及び前記室内機に流れる冷媒循環量を算出する循環量算出部と、
前記配管径取得部において取得された配管径と、前記循環量算出部において算出された冷媒循環量とに基づいて、前記ガス配管の配管容積を推定するとともに、冷媒が流れている配管全体の前記配管容積を算出する容積推定部と
を有するものである請求項1または2に記載の空気調和装置。 - 前記室外機は、前記室内機に並列に複数接続されており、
前記条件設定部は、複数の前記室外機毎にそれぞれ前記圧縮機の運転周波数の範囲を設定するものである請求項1~3のいずれか1項に記載の空気調和装置。
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WO2019193946A1 (ja) * | 2018-04-03 | 2019-10-10 | 株式会社デンソー | 空調装置 |
JP2021124227A (ja) * | 2020-02-03 | 2021-08-30 | 東芝ライフスタイル株式会社 | 空気調和機の室外機および空気調和機 |
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JPH11248226A (ja) * | 1998-02-26 | 1999-09-14 | Matsushita Electric Ind Co Ltd | 多室形空気調和装置 |
JP2012110070A (ja) * | 2010-11-15 | 2012-06-07 | Panasonic Corp | 空気調和機 |
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JP2008002372A (ja) * | 2006-06-23 | 2008-01-10 | Matsushita Electric Ind Co Ltd | 圧縮機の制御装置 |
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JP2012110070A (ja) * | 2010-11-15 | 2012-06-07 | Panasonic Corp | 空気調和機 |
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JP2021124227A (ja) * | 2020-02-03 | 2021-08-30 | 東芝ライフスタイル株式会社 | 空気調和機の室外機および空気調和機 |
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