WO2014175265A1 - 空気調和機 - Google Patents
空気調和機 Download PDFInfo
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- WO2014175265A1 WO2014175265A1 PCT/JP2014/061281 JP2014061281W WO2014175265A1 WO 2014175265 A1 WO2014175265 A1 WO 2014175265A1 JP 2014061281 W JP2014061281 W JP 2014061281W WO 2014175265 A1 WO2014175265 A1 WO 2014175265A1
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- refrigerant
- heat exchanger
- electronic expansion
- expansion valve
- thermistor
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- Embodiments of the present invention relate to an air conditioner.
- the amount of the encapsulated refrigerant in the refrigeration cycle differs depending on the refrigerant used.If an appropriate refrigerant is selected, the encapsulated amount can be reduced. Otherwise, there is a risk of causing condensation such as condensation or overheating of the air conditioner.
- the present embodiment provides an air conditioner that can reduce the amount of refrigerant enclosed and suppress the risk of causing a failure.
- An air conditioner includes a compressor whose rotational speed is variable by inverter control, an outdoor unit including an outdoor heat exchanger and an electronic expansion valve, an indoor unit including an indoor heat exchanger, and an indoor unit and an outdoor unit.
- an air conditioner having a refrigerant pipe connecting between them and a control device for controlling the operating frequency of the compressor and the opening of the electronic expansion valve, an HFC (Hydro Fluoro Carbon) single refrigerant is used as the refrigerant
- a main thermistor is provided at an intermediate position of the refrigerant pipe line of the indoor heat exchanger during cooling operation
- an auxiliary thermistor is provided at the inlet side pipe position of the refrigerant pipe member, and the temperature of each part is measured. If the temperature difference between the auxiliary thermistor and the main thermistor during cooling operation exceeds a predetermined reference value, the opening of the electronic expansion valve is adjusted to the characteristics of the HFC single refrigerant. To control the open side.
- an air conditioner 10 includes an outdoor unit 11, an indoor unit 12, a refrigerant pipe 13 that connects the outdoor unit 11 and the indoor unit 12, and through which refrigerant flows.
- the well-known refrigeration cycle is provided.
- the outdoor unit 11 and the indoor unit 12 are connected by electrical wiring (not shown), and when the air conditioner 10 is set by the user for the indoor unit 12 such as an operating state and an air temperature by a remote controller, for example, Air conditioning such as cooling operation, heating operation or dehumidifying operation is performed according to the setting.
- an HFC (Hydro Fluoro Carbon) single refrigerant (R32) is adopted as the refrigerant.
- This HFC single refrigerant has a larger latent heat than the conventional mixed refrigerant (R410A), and reduces the amount of refrigerant enclosed to obtain the same air conditioning capacity as when using the conventional mixed refrigerant. Can do. For example, in this embodiment, it can be reduced by about 10% compared to the mixed refrigerant.
- the outdoor unit 11 of the air conditioner 10 includes a compressor 14, an outdoor heat exchanger 15, an electronic expansion valve 16, a capillary tube 17, a four-way valve 18, and a control device 19 for controlling them.
- the outdoor unit 11 controls the four-way valve 18 to control the flow of the refrigerant during the cooling operation (in the direction indicated by the arrow A in FIG. 1) and the heating operation (FIG. 1).
- the air conditioning is performed by controlling the compressor 14, the electronic expansion valve 16, and the like. These controls are mainly performed by the control device 19.
- the control apparatus 19 is performing the valve control process (refer FIG. 6) mentioned later in relation to this embodiment.
- the refrigerant pipe 13 is provided with a strainer 20 for removing solids in the refrigerant
- the outdoor heat exchanger 15 is provided with an outdoor fan 21 for cooling.
- the indoor unit 12 includes an indoor heat exchanger 22, a dehumidifying two-way valve (hereinafter simply referred to as a dehumidifying valve 23), a main thermistor 24, an auxiliary thermistor 25, a cross flow fan 26, and the like.
- a dehumidifying valve 23 a dehumidifying two-way valve
- main thermistor 24 an auxiliary thermistor 25
- a cross flow fan 26 and the like.
- FIG. 1 in order to show the intermediate position of the indoor heat exchanger 22, the indoor heat exchanger 22 is schematically shown in a two-divided state, but the indoor heat exchanger 22 is shown in FIGS. ) And is integrally formed by a piping member.
- the indoor heat exchanger 22 is provided with a dehumidifying valve 23 at an intermediate position that is intermediate in the refrigerant flow.
- a main thermistor 24 is provided at a position downstream of the dehumidifying valve 23 during the cooling operation. Further, an auxiliary thermistor 25 is provided on the inlet side (corresponding to the inlet side piping position) where the refrigerant flows into the outdoor heat exchanger 15 during the cooling operation.
- the main thermistor 24 and the auxiliary thermistor 25 measure the temperature of each part.
- the axial fan functions as an indoor fan for forming an indoor air flow.
- the indoor blower is not limited to the axial flow fan, and may have other configurations.
- the indoor unit 12 is also provided with an indoor temperature sensor that detects the temperature of the room in which the indoor unit 12 is installed, a receiving unit that receives a signal from a remote controller, and the like.
- an indoor temperature sensor that detects the temperature of the room in which the indoor unit 12 is installed
- a receiving unit that receives a signal from a remote controller, and the like.
- the air conditioner 10 is operating under the standard cooling use conditions (outdoor temperature is 35 ° C./indoor temperature is 27 ° C.) defined by JIS (C9921-3, etc.), for example, the same Even under the standard cooling use conditions (that is, even when there is no change between the outdoor temperature and the indoor temperature), the temperature measured by the main thermistor 24 during the cooling operation (hereinafter, Tc and And the temperature measured by the auxiliary thermistor 25 (hereinafter referred to as Tj) may change.
- Tc and Tj are in a state where there is no temperature difference such that Tc is 24.0 ° C. and Tj is 24.0 ° C.
- the refrigerant circulation amount increases as the opening of the electronic expansion valve 16 (indicated by PMV (pls) in FIG. 3) increases. This is because the cooling capacity improves as the number increases, and the temperature of the indoor heat exchanger 22 decreases.
- the opening degree of the electronic expansion valve 16 when the opening degree of the electronic expansion valve 16 is controlled to the open side, the temperature difference between Tc and Tj increases as the refrigerant circulation amount increases, and the temperature difference between Tc and Tj increases.
- the machine 10 controls the opening degree of the electronic expansion valve 16 mainly in the range of the squeezed region (a state that is less than 3/5 with respect to the full opening as will be described later).
- the refrigerant circulation amount in the throttled region if the electronic expansion valve 16 is excessively throttled, the refrigerant circulation amount in the indoor heat exchanger 22 cannot be sufficiently obtained, and the refrigerant is superheated. Therefore, there is a risk that sufficient cooling capacity may not be obtained.
- the temperature rise of a refrigerating cycle is caused, there exists a possibility of causing the trouble of the damage and durability of the compressor 14.
- the refrigerant circulation amount of the refrigeration cycle increases.
- the refrigerant circulation amount sent to the indoor heat exchanger 22 is reduced from an appropriate value, so that cooling with respect to the load of the indoor intake air temperature is performed.
- the load is insufficient, and as a result, the refrigerant temperature in the middle part rises from the refrigerant temperature on the inlet side of the indoor heat exchanger 22.
- the main pipe thermistor 24 is in a reverse state where the temperature is higher than the temperature of the auxiliary thermistor 25 portion.
- the temperature difference in the reverse state becomes large, the temperature of the refrigerant returning to the compressor 14 becomes higher than a predetermined value, and the compressor 14 becomes a high temperature state.
- the opening degree of the electronic expansion valve 16 is always maintained at an optimal throttle state and is appropriately set. It is necessary to ensure the amount of refrigerant circulation.
- the refrigerant circulation amount changes not only by the opening degree of the electronic expansion valve 16 but also by the cooling capacity of the air conditioner 10. That is, if the cooling capacity is high, the refrigerant circulation amount increases even at the same opening degree. That is, in order to ensure an appropriate refrigerant circulation amount and prevent overheating in the indoor heat exchanger 22, control according to the cooling capacity is required.
- FIG. 3 shows the relationship between the temperature difference (Tc ⁇ Tj) of each thermistor for each cooling capacity (cooling rated capacity) set in this embodiment and the rotational speed (operating frequency) of the compressor 14. As shown in FIG. 3, the appropriate temperature difference of Tc ⁇ Tj differs for each cooling capacity, and for each operating frequency of the compressor 14 even if the cooling capacity is the same rating.
- the throttle amount is throttled slightly larger than the optimum state, and in the state where the cooling load with respect to the indoor intake air temperature is insufficient, the intermediate portion is higher than the refrigerant temperature on the inlet side of the indoor heat exchanger 22.
- the temperature of the main pipe thermistor 24 becomes higher than the temperature of the room auxiliary thermistor 25, even if this temperature difference becomes larger than in the region where the operating frequency of the compressor 14 is relatively high. The problem that the compressor 14 is overheated due to the temperature rise of the refrigerant returning to the compressor 14 is unlikely to occur.
- the operating frequency of the compressor 14 is relatively within the range in which the opening degree of the electronic expansion valve 16 is controlled to the open side (the region in which the throttle amount is increased), that is, the reference value for controlling the throttle amount.
- a relatively large temperature difference is set for the low low load region, and a relatively small temperature difference is set for the high load region where the operation frequency is relatively high.
- the operating frequency of the compressor 14 for determining the temperature difference set as the reference value is set according to the cooling capacity.
- the control device 19 has a temperature difference that exceeds a design upper limit value (see graph G2) under the condition that the temperature difference decreases as the refrigerant circulation amount increases in the normal cycle (see graph G1).
- the opening degree of the electronic expansion valve 16 is controlled by executing the valve control process shown in FIG.
- the control device 19 first determines whether or not the cooling operation is being performed (S1). If the cooling operation is not being performed (S1: NO), the current operation state is maintained (S6). In contrast, if the cooling device is in the cooling operation (S1: YES), the control device 19 determines whether the rotational speed of the compressor 14 is equal to or higher than the reference frequency (S2). In the case of this embodiment, this reference frequency is set to about 1/5 of the maximum rotation speed (20 Hz in this embodiment).
- air conditioners installed in homes in Japan are adapted to the climate of Japan, and the indoor temperature range (for example, the air conditioner can be operated) based on the cooling standard use conditions defined by JIS. 20 ° C. to 32 ° C.) and an outdoor temperature range (for example, 18 ° C. to 43 ° C.) are set, and the air conditioner is designed to operate without any trouble under the conditions of each temperature range.
- the indoor / outdoor temperature ranges for example, when the indoor temperature (32 ° C.) is high and the outdoor temperature (18 ° C.) is low, and the indoor high temperature / outdoor low temperature conditions, the compressor 14 is shown in FIG.
- the opening degree of the electronic expansion valve 16 is 145 pls (145 pulses, which is 3/5 or more with respect to full open). Even if controlled to the open side, a reverse state is established in which Tc (27 ° C.) is larger than Tj (20 ° C.). In such an indoor high temperature / outdoor low temperature condition, since the opening degree of the electronic expansion valve 16 is already large (that is, the refrigerant circulation amount is already large), the electronic expansion valve 16 is opened more than that. Even if the degree is controlled to the open side, it is considered that the temperature difference cannot be reduced.
- control device 19 is the case where the rotational speed of the compressor 14 is lower than the reference frequency (S2: NO), and the opening degree of the electronic expansion valve 16 is 3/5 or more (S3: NO), the process proceeds to step S6 and the current operation state is maintained. That is, in this case, the opening degree of the electronic expansion valve 16 is not controlled in the valve control process. This is to prevent the cooling function of the indoor heat exchanger 22 from being impaired by suppressing the electronic expansion valve 16 from being excessively opened (for example, being fully opened).
- the process of controlling the electronic expansion valve 16 to the open side is performed when the electronic expansion valve 16 is opened when the operation frequency of the compressor 14 is a low speed rotation speed that is 1/5 or less of the maximum operation frequency. This is performed when the degree of opening is 3/5 or less with respect to full opening.
- the control device 19 determines that the temperature difference (Tc ⁇ Tj) between the main thermistor 24 and the auxiliary thermistor 25 is the reference value. If it is above (refer to FIG. 4) (S4: YES), the electronic expansion valve 16 is promptly controlled to open by a predetermined pulse (S5).
- the predetermined pulse may be appropriately set according to the characteristics of the HFC single refrigerant.
- the control device 19 determines that the opening degree of the electronic expansion valve 16 is less than 3/5 (S3: YES). ),
- the electronic expansion valve 16 is controlled to open by a predetermined pulse (S5). That is, unlike the case of the indoor high temperature / outdoor low temperature conditions shown in FIG. 3, it rotates like the leftmost term in the indoor temperature (27 ° C.) and outdoor temperature (35 ° C.), which are the standard cooling use conditions in FIG. Even if the number is low (7.8 Hz), if the opening degree of the electronic expansion valve 16 is about 49 pls (if it is less than 3/5 with respect to full opening), the electronic expansion valve 16 is opened.
- the refrigerant circulation amount is increased.
- the opening of the electronic expansion valve 16 is opened. Even if it is controlled to the side (even if it is open), depending on the temperature conditions between the room and the room (conditions where the outdoor temperature is low and the indoor temperature is high), the temperature difference exceeds the set value. For example, the compressor 14 is not overloaded (abnormal operation), and the refrigeration cycle is not abnormal. Therefore, the electronic expansion valve 16 is controlled to open.
- the routine proceeds to step S6.
- the current operating state will be maintained.
- the air conditioner 10 controls the opening degree of the electronic expansion valve 16 according to the temperature difference (Tc ⁇ Tj) between the main thermistor 24 and the auxiliary thermistor 25, the rotational frequency of the compressor 14, and the cooling capacity. is doing.
- the air conditioner 10 of this embodiment demonstrated above there exist the following effects. Since the HFC single refrigerant (R32) is adopted, the latent heat can be increased with respect to the conventional mixed refrigerant (R410A), and the amount of refrigerant enclosed to obtain the same ability as the conventional one is reduced. be able to. Thereby, the manufacturing cost can be reduced, and for example, the refrigerant pipe 13 can be reduced in size and weight.
- the opening degree of the electronic expansion valve 16 is controlled based on the difference between the refrigerant temperature of the suction side piping of the compressor 14 and the measured temperature of the main pipe thermistor 24 of the indoor heat exchanger 22 during the cooling operation.
- the opening degree of the electronic expansion valve 16 is controlled based on the temperature difference of the auxiliary thermistor 25 with respect to the main pipe thermistor 24 as in the embodiment, it is possible to suppress excessive throttling of the electronic expansion valve 16. For this reason, when the electronic expansion valve 16 is excessively throttled during the cooling operation, about half of the indoor heat exchanger 22 is dried, and the intake air passing therethrough cannot be dehumidified and dew condensation inside the indoor unit 12 is reduced. can do. Moreover, an excessive refrigeration cycle temperature rise due to a shortage of the refrigerant circulation amount can be suppressed.
- the reference value for controlling the opening degree of the electronic expansion valve 16 is set in accordance with the operating frequency of the compressor 14 and in accordance with the size of the cooling capacity, a model having a relatively large cooling capacity.
- the reference operating frequency can be set low to protect the compressor 14, and the optimum throttle amount and control can be performed respectively.
- the process of controlling the electronic expansion valve 16 to the open side is performed, whereas when it exceeds 1/5, the process is performed according to the current opening degree of the electronic expansion valve 16.
- the air conditioner 10 includes an indoor unit 12 having an indoor heat exchanger 22, an outdoor unit 11 having an outdoor heat exchanger 15, and between the outdoor heat exchanger 15 and the indoor heat exchanger 22.
- a heat transfer pipe (refrigerant pipe 13) through which refrigerant flows is connected.
- an HFC single refrigerant is used as the refrigerant.
- the control device 19 of the present embodiment operates the dehumidifying valve 23 based on the reheat dehumidifying operation command, while the temperature difference of the auxiliary thermistor 25 with respect to the main thermistor 24 is preset after the dehumidifying valve 23 is operated.
- the reheat dehumidification operation can be normally performed by re-operation at the time of malfunction. Further, if it is determined that the dehumidification valve 23 is malfunctioning even if it is re-activated, it can be determined that the failure has occurred.
- the present invention is not limited to those exemplified in the above-described embodiment, and can be modified or expanded as follows. You may apply both control of the electronic expansion valve 16 of 1st Embodiment, and control of the dehumidification valve 23 of 2nd Embodiment.
- the electronic expansion valve 16 is controlled to open, and when the temperature difference is still greater than or equal to the predetermined value, the subsequent electronic expansion valve 16 is opened.
- the control for changing the operation may not be performed. Thereby, it can prevent that the electronic expansion valve 16 opens fully and the cooling function of the indoor heat exchanger 22 is impaired.
- 10 is an air conditioner
- 11 is an outdoor unit
- 12 is an indoor unit
- 13 is a refrigerant pipe
- 14 is a compressor
- 15 is an outdoor heat exchanger
- 16 is an electronic expansion valve
- 19 is a control device
- 22 is an indoor unit.
- a heat exchanger, 23 is a dehumidifying valve
- 24 is a main thermistor
- 25 is an auxiliary thermistor.
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Abstract
Description
本実施形態は、冷媒の封入量を削減することができるとともに、障害を引き起こすおそれを抑制できる空気調和機を提供する。
(第1実施形態)
以下、第1実施形態について、図1から図6を参照しながら説明する。図1に示すように、本実施形態の空気調和機10は、室外機11、室内機12、および室外機11と室内機12とを接続してその内部を冷媒が流れる冷媒配管13等により構成される周知の冷凍サイクルを備えている。これら室外機11および室内機12は図示しない電気配線により接続されており、空気調和機10は、室内機12に対して例えばリモコン等により運転状態や空温等の設定がユーザにより行われると、その設定に従って冷房運転、暖房運転あるいは除湿運転等の空調を行う。
次に、上記構成の空気調和機10の作用について説明する。
圧縮機14の運転周波数は、室内温度と設定温度の差に基づく室内の空調負荷状態で制御されることが行われている。この場合、空気調和機10が例えばJIS(C9921-3など)で定められている冷房標準使用条件(室外温度が35℃/室内温度が27℃の状態)で運転していると想定すると、同じ冷房標準使用条件であっても(つまり、室外温度と室内温度とに変化がない状態であっても)、冷房運転を行っている最中に、主管サーミスタ24により測定した温度(以下、Tcと称する)と、補助サーミスタ25により測定した温度(以下、Tjと称する)とが変化する場合がある。
このため、空気調和機10においては、TcとTjとの温度差を考慮しつつも必要な冷房能力を得るために、電子膨張弁16の開度を常に最適の絞り状態に維持して適切な冷媒循環量を確保することが必要とされている。
これに対して、制御装置19は、圧縮機14の回転数が基準周波数以上である場合には(S2:YES)、主管サーミスタ24と補助サーミスタ25との温度差(Tc-Tj)が基準値(図4参照)以上であれば(S4:YES)、速やかに電子膨張弁16を所定パルス分だけ開側に制御する(S5)。これにより、冷媒循環量が増加して冷房能力が増加し、室内熱交換器22の過熱が防止される。なお、ステップS4にて参照する基準値は、圧縮機14の現在の回転数に応じて図4のいずれかを選択すればよい。また、所定パルスは、HFC単一冷媒の特性に応じて適宜設定すればよい。
このように、空気調和機10は、主管サーミスタ24と補助サーミスタ25との温度差(Tc-Tj)、圧縮機14の回転周波数、および冷房能力に応じて、電子膨張弁16の開度を制御している。
HFC単一冷媒(R32)を採用しているので、従来採用されていた混合冷媒(R410A)に対して潜熱を大きくすることができ、従来と同等の能力を得るための冷媒封入量を減少させることができる。これにより、製造コストを削減できるとともに、例えば冷媒配管13の小型化・軽量化等を図ることも可能となる。
以下、第2実施形態について説明する。第2実施形態の構成は第1実施形態と共通するので、図1等を参照しながら説明する。
空気調和機10は、図1に示すように、室内熱交換器22を有する室内機12、室外熱交換器15を有する室外機11、室外熱交換器15と室内熱交換器22との間を接続して冷媒の流れる伝熱管(冷媒配管13)を備えている。また、本実施形態でも、冷媒としてHFC単一冷媒を使用している。
これにより、再熱除湿運転時の除湿弁23の動作不良を検知することができる。また、動作不良時には再作動させることで、再熱除湿運転を正常に行うことができる。さらに、仮に再作動させたとしても除湿弁23が動作不良を起こしていると判定した場合には、故障と判断することもできる。
本発明は、上記した実施形態にて例示したものに限定されることなく、次のように変形又は拡張することができる。
第1実施形態の電子膨張弁16の制御と第2実施形態の除湿弁23の制御との双方を適用してもよい。
主管サーミスタ24に対する補助サーミスタ25の温度差が所定値以上の場合に電子膨張弁16を開側に制御した後、その温度差が未だ所定値以上の場合は、その後の電子膨張弁16を開側に変更動作させる制御を実施しないようにしてもよい。これにより、電子膨張弁16が全開となって室内熱交換器22の冷却機能が損なわれることを防止することができる。
Claims (4)
- インバータ制御により回転数が可変の圧縮機、室外熱交換器および電子膨張弁を備える室外機と、室内熱交換器を備える室内機と、前記室外機および前記室内機の間を接続する冷媒配管と、前記圧縮機の運転周波数および前記電子膨張弁の開度を制御する制御装置と、を備えた空気調和装置において、
前記冷媒としてHFC(Hydro Fluoro Carbon)単一冷媒を使用し、
冷房運転時における前記室内熱交換器の前記冷媒配管の中間位置に主管サーミスタを設けるとともに、当該冷媒配管の入口側配管位置に補助サーミスタを設けてそれぞれの部位の温度を測定し、
前記制御装置は、冷房運転時における前記主管サーミスタに対する前記補助サーミスタの温度差が予め定められている基準値以上になると、前記電子膨張弁の開度を前記HFC単一冷媒の特性に合わせて開側に制御することを特徴とする空気調和機。 - 前記基準値は、前記圧縮機の運転周波数に応じて、運転周波数が相対的に高い状態では相対的に小さい温度差が設定され、運転周波数が相対的に低い状態では相対的に大きい温度差が設定され、
前記基準値に設定する温度差を決定するための前記圧縮機の運転周波数は、冷房能力に応じて設定されることを特徴とする請求項1記載の空気調和機。 - 前記制御装置は、前記圧縮機の運転周波数が1/5未満の低回転領域であるとき、および、前記圧縮機の運転周波数が1/5を超える状態であって且つ前記電子膨張弁の開度が全開に対して3/5未満の状態のとき、前記電子膨張弁の開度を開側に制御する一方、前記電子膨張弁を開側に変更動作を行った後における前記主管サーミスタに対する前記補助サーミスタの温度差が所定値以上であるとき、その後は前記電子膨張弁を開側に制御することを規制することを特徴とする請求項1または2記載の空気調和機。
- 室内熱交換器を有する室内機、室外熱交換器を有する室外機、前記室外熱交換器と前記室内熱交換器との間を接続して冷媒の流れる伝熱管を備えた空気調和装置において、
前記冷媒としてHFC単一冷媒を使用し、
前記室内機は、再熱除湿運転用の除湿弁が室内熱交換器に設けられており、
室内熱交換器の除湿弁の冷房運転時における下流側の位置に主管サーミスタを設け、冷房基準の入口側に補助サーミスタを設けてそれぞれの部位の温度を測定し、再熱除湿運転指令に基づいて除湿弁を作動させる一方、当該除湿弁の作動後において前記主管サーミスタに対する前記補助サーミスタの温度差が予め設定されている基準値以上となった場合、前記除湿弁の作動不良と判断して除湿弁を再度作動させることを特徴とする空気調和機。
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JP2018091586A (ja) * | 2016-12-07 | 2018-06-14 | パナソニックIpマネジメント株式会社 | 空気調和機 |
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CN107144057B (zh) * | 2017-05-26 | 2019-08-30 | 广东美的制冷设备有限公司 | 空调系统及其控制装置、方法 |
KR102354891B1 (ko) * | 2017-05-31 | 2022-01-25 | 삼성전자주식회사 | 공기 조화기 및 그 제어 방법 |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03194361A (ja) * | 1989-12-25 | 1991-08-26 | Toshiba Corp | 膨張弁の制御方法 |
JPH08261576A (ja) * | 1995-03-27 | 1996-10-11 | Mitsubishi Electric Corp | 非共沸混合冷媒搭載の冷凍装置 |
JPH10325622A (ja) * | 1997-03-26 | 1998-12-08 | Mitsubishi Electric Corp | 冷凍サイクル装置 |
JP2000266388A (ja) * | 1999-03-17 | 2000-09-29 | Mitsubishi Electric Corp | マルチ形冷凍サイクル装置の制御方法および制御装置 |
JP2001221526A (ja) * | 2000-02-04 | 2001-08-17 | Mitsubishi Electric Corp | 冷凍空調装置 |
JP2003262429A (ja) * | 2002-03-06 | 2003-09-19 | Mitsubishi Electric Corp | 空気調和機および空気調和機の運転方法 |
JP2007078348A (ja) * | 2006-12-20 | 2007-03-29 | Mitsubishi Electric Corp | 空気調和機 |
JP2013072621A (ja) * | 2011-09-29 | 2013-04-22 | Panasonic Corp | 空気調和機 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08254363A (ja) * | 1995-03-15 | 1996-10-01 | Toshiba Corp | 空調制御装置 |
JPH10220881A (ja) * | 1997-02-05 | 1998-08-21 | Toshiba Corp | 空気調和機の制御方法 |
JP3999608B2 (ja) * | 2002-09-03 | 2007-10-31 | 東芝キヤリア株式会社 | 空気調和機 |
JP4668769B2 (ja) * | 2005-11-09 | 2011-04-13 | 東芝キヤリア株式会社 | 空気調和機 |
-
2013
- 2013-04-25 JP JP2013092479A patent/JP6151079B2/ja not_active Expired - Fee Related
-
2014
- 2014-04-22 WO PCT/JP2014/061281 patent/WO2014175265A1/ja active Application Filing
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Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03194361A (ja) * | 1989-12-25 | 1991-08-26 | Toshiba Corp | 膨張弁の制御方法 |
JPH08261576A (ja) * | 1995-03-27 | 1996-10-11 | Mitsubishi Electric Corp | 非共沸混合冷媒搭載の冷凍装置 |
JPH10325622A (ja) * | 1997-03-26 | 1998-12-08 | Mitsubishi Electric Corp | 冷凍サイクル装置 |
JP2000266388A (ja) * | 1999-03-17 | 2000-09-29 | Mitsubishi Electric Corp | マルチ形冷凍サイクル装置の制御方法および制御装置 |
JP2001221526A (ja) * | 2000-02-04 | 2001-08-17 | Mitsubishi Electric Corp | 冷凍空調装置 |
JP2003262429A (ja) * | 2002-03-06 | 2003-09-19 | Mitsubishi Electric Corp | 空気調和機および空気調和機の運転方法 |
JP2007078348A (ja) * | 2006-12-20 | 2007-03-29 | Mitsubishi Electric Corp | 空気調和機 |
JP2013072621A (ja) * | 2011-09-29 | 2013-04-22 | Panasonic Corp | 空気調和機 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2018091586A (ja) * | 2016-12-07 | 2018-06-14 | パナソニックIpマネジメント株式会社 | 空気調和機 |
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CN105190195A (zh) | 2015-12-23 |
CN105190195B (zh) | 2017-09-08 |
JP2014214964A (ja) | 2014-11-17 |
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