JPH04214154A - Multi-chamber type air-conditioning machine - Google Patents
Multi-chamber type air-conditioning machineInfo
- Publication number
- JPH04214154A JPH04214154A JP2400516A JP40051690A JPH04214154A JP H04214154 A JPH04214154 A JP H04214154A JP 2400516 A JP2400516 A JP 2400516A JP 40051690 A JP40051690 A JP 40051690A JP H04214154 A JPH04214154 A JP H04214154A
- Authority
- JP
- Japan
- Prior art keywords
- expansion valve
- pressure
- electric expansion
- outdoor unit
- controller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000004378 air conditioning Methods 0.000 title claims description 16
- 239000003507 refrigerant Substances 0.000 claims abstract description 10
- 238000010438 heat treatment Methods 0.000 abstract description 8
- 239000007788 liquid Substances 0.000 abstract description 7
- 238000000034 method Methods 0.000 abstract 2
- 230000006866 deterioration Effects 0.000 abstract 1
- 238000004781 supercooling Methods 0.000 description 6
- 230000001052 transient effect Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/005—Outdoor unit expansion valves
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/021—Inverters therefor
-
- 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
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
【0001】0001
【産業上の利用分野】本発明は、多室形空気調和機に関
し、特に、暖房運転時の個別制御が行われる多室形空気
調和機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-chamber air conditioner, and more particularly to a multi-chamber air conditioner in which individual control is performed during heating operation.
【0002】0002
【従来の技術】近年、ビルの空調には、個別分散空調が
多く採用されるようになり、特開平1−21287号公
報の発明のような多室形空気調和機の個別の制御化が進
められてきた。[Background Art] In recent years, individual distributed air conditioning has been increasingly used for air conditioning in buildings, and the individual control of multi-room air conditioners, such as the invention disclosed in Japanese Patent Application Laid-open No. 1-21287, has been progressing. I've been exposed to it.
【0003】この種の従来の多室形空気調和機について
図3ないし図5により説明する。A conventional multi-room air conditioner of this type will be explained with reference to FIGS. 3 to 5.
【0004】図3は、従来の多室形空気調和機の構成図
、図4は室外機側の制御フローチャート、図5は室内機
側の膨張弁の制御フローチャートである。FIG. 3 is a block diagram of a conventional multi-room air conditioner, FIG. 4 is a control flowchart for the outdoor unit, and FIG. 5 is a control flowchart for the expansion valve of the indoor unit.
【0005】図3において、多室形空気調和機の室外機
1は、能力可変圧縮機2,四方弁3,室外機側熱交換器
4,室外機側電動膨張弁5および室外機側ファン6から
、また、これに接続される複数の室内機7a,7b,7
cおよび7dは、それぞれ室内機側電動膨張弁8a,8
b,8cおよび8d、室内機側熱交換器9a,9b,9
cおよび9dならびに室内機側ファン10a,10b,
10cおよび10dから構成されている。また、上記の
室外機側電動膨張弁5と室内機側電動膨張弁8a,8b
,8cおよび8dは液管11で、室内機側熱交換器9a
,9b,9cおよび9dと四方弁3はガス管12でそれ
ぞれ接続されている。さらに、室外機1では、四方弁3
に接続するガス管12に設けられた圧力検知器13の検
出圧力に応じてインバータ制御器14で制御されるイン
バータ15が能力可変圧縮機2に、また、室外機側電動
膨張弁5に接続された液管11に設けられた冷媒温度検
知器16の検出温度に応じて開度を制御する膨張弁制御
器17が室外機側電動膨張弁5にそれぞれ接続されてい
る。また、室内機7a,7b,7cおよび7dでは、そ
れぞれ室内機側熱交換器9a,9b,9cおよび9dの
吸込口に配置された空気温度検知器18a,18b,1
8cおよび18dの検出空気温度とリモートコントロー
ラ(以下リモコンと称し図示せず)に設定された室内設
定温度との相異量から部屋の空調負荷算出器19a,1
9b,19cおよび19dが算出した空調負荷に応じて
開度を制御する膨張弁制御器20a,20b,20cお
よび20dが、それぞれ室内機側電動膨張弁8a,8b
,8cおよび8dに接続されている。In FIG. 3, an outdoor unit 1 of a multi-room air conditioner includes a variable capacity compressor 2, a four-way valve 3, an outdoor unit side heat exchanger 4, an outdoor unit side electric expansion valve 5, and an outdoor unit side fan 6. , and a plurality of indoor units 7a, 7b, 7 connected thereto.
c and 7d are indoor unit side electric expansion valves 8a and 8, respectively.
b, 8c and 8d, indoor unit side heat exchangers 9a, 9b, 9
c and 9d and indoor unit side fans 10a, 10b,
It is composed of 10c and 10d. In addition, the outdoor unit side electric expansion valve 5 and the indoor unit side electric expansion valves 8a and 8b are also provided.
, 8c and 8d are liquid pipes 11, which are connected to the indoor unit side heat exchanger 9a.
, 9b, 9c, and 9d and the four-way valve 3 are connected through gas pipes 12, respectively. Furthermore, in the outdoor unit 1, the four-way valve 3
An inverter 15 controlled by an inverter controller 14 in accordance with the detected pressure of a pressure detector 13 provided on a gas pipe 12 connected to the compressor 2 is connected to the variable capacity compressor 2 and to the electric expansion valve 5 on the outdoor unit side. Expansion valve controllers 17 that control the opening degree according to the temperature detected by a refrigerant temperature sensor 16 provided in the liquid pipe 11 are connected to the outdoor unit side motorized expansion valves 5, respectively. In addition, in the indoor units 7a, 7b, 7c and 7d, air temperature sensors 18a, 18b, 1 are arranged at the suction ports of the indoor unit side heat exchangers 9a, 9b, 9c and 9d, respectively.
Air conditioning load calculators 19a and 1 for the room are calculated from the amount of difference between the detected air temperatures 8c and 18d and the indoor temperature set on a remote controller (hereinafter referred to as remote controller, not shown).
Expansion valve controllers 20a, 20b, 20c and 20d which control the opening according to the air conditioning load calculated by 9b, 19c and 19d are the indoor unit side electric expansion valves 8a, 8b, respectively.
, 8c and 8d.
【0006】以上のように構成された多室形空気調和機
の動作について、暖房運転を例として説明する。[0006] The operation of the multi-room air conditioner configured as described above will be explained using heating operation as an example.
【0007】能力可変圧縮機2から吐出された高温高圧
の冷媒は、四方弁3およびガス管12を通り室内機側熱
交換器9a,9b,9cおよび9dに流入して凝縮液化
し、室内機側電動膨張弁8a,8b,8cおよび8dな
らびに液管11を介して室外機側電動膨張弁5で減圧さ
れ、室外機側熱交換器4で蒸発気化し、再び四方弁3を
通り能力可変圧縮機2にもどる。The high temperature and high pressure refrigerant discharged from the variable capacity compressor 2 passes through the four-way valve 3 and the gas pipe 12 and flows into the indoor unit side heat exchangers 9a, 9b, 9c and 9d, where it is condensed and liquefied. The pressure is reduced in the outdoor unit side electric expansion valve 5 via the side electric expansion valves 8a, 8b, 8c and 8d and the liquid pipe 11, evaporated in the outdoor unit side heat exchanger 4, and passed through the four-way valve 3 again for variable capacity compression. Return to machine 2.
【0008】この時、能力可変圧縮機2の能力は、その
時の空調負荷に応じて変化する圧力検知器11により検
知された(S41)検知圧力(暖房時は凝縮圧力)が、
予め決められた所定の圧力を読み取り(S42)、この
設定圧力と配管圧力比較し差圧を算出する(S43)。
そして、差圧に対応して能力可変圧縮機2の運転周波数
を決定し(S44)、インバータ制御器14によりイン
バータ15を制御して(S45)、検知圧力が所定の圧
力より高い時は低速方向、低い時は高速方向に制御され
る。At this time, the capacity of the variable capacity compressor 2 is determined by the detected pressure (condensing pressure during heating) detected by the pressure detector 11 (S41) which changes depending on the air conditioning load at that time.
A predetermined pressure is read (S42), and the set pressure is compared with the piping pressure to calculate the differential pressure (S43). Then, the operating frequency of the variable capacity compressor 2 is determined in accordance with the differential pressure (S44), and the inverter 15 is controlled by the inverter controller 14 (S45). , when it is low, it is controlled in a high speed direction.
【0009】また、室外機側電動膨張弁5は、その時の
運転状態に応じて変化する冷媒温度検知器16により検
出された(S46)室内機7a,7b,7cおよび7d
と室外機側電動膨張弁5の間の液管11の温度が、読み
込んだ設定温度(S47)と比較して温度差を算出する
(S48)。そして、この温度差に対応して室外機側電
動膨張弁5の開度を決定し(S49)、予め決められた
所定の温度になるように(所定の過冷却度になるように
)室外機側電動膨張弁制御器17により、検知温度が所
定の温度より高い時は閉方向、低い時は開方向に制御さ
れる(S50)。[0009] Also, the electric expansion valve 5 on the outdoor unit side is connected to the indoor units 7a, 7b, 7c and 7d, which is detected by the refrigerant temperature detector 16 (S46) which changes depending on the operating state at that time.
The temperature of the liquid pipe 11 between the and the outdoor unit side electric expansion valve 5 is compared with the read set temperature (S47) to calculate a temperature difference (S48). Then, the opening degree of the electric expansion valve 5 on the outdoor unit side is determined in accordance with this temperature difference (S49), and the outdoor unit is adjusted to a predetermined temperature (to a predetermined degree of supercooling). The side electric expansion valve controller 17 controls the valve to close when the detected temperature is higher than a predetermined temperature, and to open when the detected temperature is lower (S50).
【0010】さらに、室内機側電動膨張弁8a,8b,
8cおよび8dは、リモコンで設定された室温設定値と
空気温度検知機18a,18b,18cおよび18dで
検出される室内機7a,7b,7cおよび7dの吸込空
気の温度(S51)とリモコンで設定された室温設定値
(S52)とから空調負荷算出器19a,19b,19
cおよび19dにより部屋の空調負荷を算出し(S53
)、この算出された空調負荷に応じて室内機側電動膨張
弁8a,8b,8cおよび8dの開度を決定して(S5
4)、空調負荷が大きい時は開方向に、小さい時は閉方
向に制御される(S55)。Furthermore, indoor unit side electric expansion valves 8a, 8b,
8c and 8d are set using the room temperature set value set using the remote controller, the temperature of the intake air of the indoor units 7a, 7b, 7c, and 7d detected by the air temperature detectors 18a, 18b, 18c, and 18d (S51), and the remote controller. The air conditioning load calculators 19a, 19b, 19
The air conditioning load of the room is calculated from c and 19d (S53
), the opening degrees of the indoor unit-side electric expansion valves 8a, 8b, 8c, and 8d are determined according to the calculated air conditioning load (S5
4) When the air conditioning load is large, it is controlled in the open direction, and when it is small, it is controlled in the closed direction (S55).
【0011】そして、室外機1の能力可変圧縮機2の運
転周波数と室外機側電動膨張弁5の開度と、室内機側電
動膨張弁8a,8b,8cおよび8dの開度は、それぞ
れ独立して制御される。The operating frequency of the variable capacity compressor 2 of the outdoor unit 1, the opening degree of the electric expansion valve 5 on the outdoor unit side, and the opening degree of the electric expansion valves 8a, 8b, 8c and 8d on the indoor unit side are each independent. controlled by
【0012】0012
【発明が解決しようとする課題】しかしながら、上記の
構成では、能力可変圧縮機2の運転周波数と室外機側電
動膨張弁5の開度は、ともに室外機1側の制御要素であ
ることから同期した制御タイミングで制御される。However, in the above configuration, the operating frequency of the variable capacity compressor 2 and the opening degree of the electric expansion valve 5 on the outdoor unit side are both controlled elements on the outdoor unit 1 side, so they cannot be synchronized. It is controlled at the specified control timing.
【0013】従って、通常の運転状態の場合は何等問題
はないが、過渡の運転状態の場合に吐出温度の過昇や吸
入圧力の低下により暖房能力が低下するという問題があ
った。[0013]Therefore, there is no problem in normal operating conditions, but in transient operating conditions, there is a problem in that the heating capacity is reduced due to an excessive rise in discharge temperature and a decrease in suction pressure.
【0014】即ち、過渡の運転状態である立上がり運転
時とか、例えば、室内機1の運転台数が、4台から急に
1台に変わる急激な運転状態の変化時には凝縮圧力の変
化に対し過冷却度の変化のスピードが遅いために、能力
可変圧縮機2の運転周波数と室外機側電動膨張弁5の開
度を同時に制御すると、凝縮圧力の変化中に過冷却度を
変化させることになり、室外機側電動膨張弁5の開度を
絞っても過冷却度が小さくなるといった逆応答を生じ、
設計した室外機側電動膨張弁5の開度より小さくなり過
ぎ、時間が経って過渡状態から通常状態になった時に室
外機側電動膨張弁5の開度が復帰せず室外機側電動膨張
弁5の絞り過ぎによる吐出温度の過昇や吸入圧力の低下
が生じ、信頼性が低く且つ快適性が劣るという問題があ
った。That is, during start-up operation, which is a transient operating state, or when there is a sudden change in the operating state, for example, when the number of indoor units 1 in operation suddenly changes from four to one, supercooling occurs due to changes in condensing pressure. Since the speed of change in temperature is slow, if the operating frequency of the variable capacity compressor 2 and the opening degree of the electric expansion valve 5 on the outdoor unit side are controlled simultaneously, the degree of supercooling will change while the condensing pressure is changing. Even if the opening degree of the electric expansion valve 5 on the outdoor unit side is reduced, a reverse response occurs in which the degree of supercooling decreases.
The opening degree of the electric expansion valve 5 on the outdoor unit side becomes too small than the designed opening degree, and when the transition state changes to the normal condition over time, the opening degree of the electric expansion valve 5 on the outdoor unit side does not return to normal. Excessive throttling of No. 5 causes an excessive rise in discharge temperature and a drop in suction pressure, resulting in problems of low reliability and poor comfort.
【0015】本発明は、上記の問題を解決するもので、
過渡の運転状態の場合でも吐出温度の過昇や吸入圧力の
低下による暖房能力の低下が生じない、信頼性が高い快
適性に優れた多室形空気調和機を提供するものである。[0015] The present invention solves the above problems.
The present invention provides a multi-room air conditioner that is highly reliable and provides excellent comfort, which does not cause a decrease in heating capacity due to an excessive rise in discharge temperature or a decrease in suction pressure even in a transient operating state.
【0016】[0016]
【課題を解決するための手段】上記の課題を解決するた
め、本発明は、上記インバータ制御器14と室外機1の
膨張弁制御器17との制御タイミングをずらすものであ
る。[Means for Solving the Problems] In order to solve the above problems, the present invention shifts the control timings of the inverter controller 14 and the expansion valve controller 17 of the outdoor unit 1.
【0017】[0017]
【作用】上記の構成により、立上がり時や急激な運転状
態の変化時などの過渡の運転状態で、変化スピードが遅
い過冷却度の制御、すなわち室外機側膨張弁5の開度制
御を、能力可変圧縮機2の運転周波数を制御して凝縮圧
力がほぼ安定した後に行うので、室外機側電動膨張弁5
の過度な絞り過ぎが防がれ、吐出温度の過昇や吸入圧力
の低下が生じない。[Function] With the above configuration, the ability to control the degree of supercooling that changes slowly, that is, the opening degree of the expansion valve 5 on the outdoor unit side, can be controlled in transient operating conditions such as startup or sudden changes in operating conditions. This is done after the operating frequency of the variable compressor 2 is controlled and the condensing pressure is almost stabilized, so the electric expansion valve 5 on the outdoor unit side
Excessive throttling is prevented, and an excessive rise in discharge temperature and a drop in suction pressure do not occur.
【0018】[0018]
【実施例】本発明の一実施例を図1および図2により説
明する。しかし、多室形空気調和機の構成は、従来と変
らないので、その説明は省略する。[Embodiment] An embodiment of the present invention will be explained with reference to FIGS. 1 and 2. However, since the configuration of the multi-room air conditioner is the same as the conventional one, a description thereof will be omitted.
【0019】図2は、室外機1の制御要素である能力可
変圧縮機2の運転周波数を制御するインバータ制御器1
4と室外機側電動膨張弁5の開度を制御する室外電動膨
張弁制御器17の制御タイミングを示しており、両者の
間に時間差ΔTを設けている。FIG. 2 shows an inverter controller 1 that controls the operating frequency of the variable capacity compressor 2, which is a control element of the outdoor unit 1.
4 and the control timing of the outdoor electric expansion valve controller 17 that controls the opening degree of the outdoor unit side electric expansion valve 5, and a time difference ΔT is provided between the two.
【0020】上記のように構成された多室形空気調和機
の動作について、暖房運転を例として説明する。なお、
冷媒の動作は従来例と変らないので、その説明は省略す
る。The operation of the multi-room air conditioner configured as described above will be explained by taking heating operation as an example. In addition,
Since the operation of the refrigerant is the same as in the conventional example, its explanation will be omitted.
【0021】多室形空気調和機を運転すると、まず、圧
力検知器13が、その時の圧力(暖房時は凝縮圧力)を
検出し(S1)、予め設定された所定の圧力と比較して
(S2,S3,S4)、検出圧力の方が高ければインバ
ータ制御器14がインバータ15を介して能力可変圧縮
機2に運転周波数を下げるように指示し、低ければ運転
周波数を上げるように指示する(S5)。その後ΔT時
間経過した時に(S6)、冷媒温度検知器16がその時
の室内機7a,7b,7cおよび7dの液管11の温度
を検出し(S7)、予め設定された所定の温度と比較し
て、検知温度の方が高ければ室外機1の膨張弁制御器1
7から室外機側電動膨張弁5に所定開度閉じるように指
示され、低ければ所定開度開けるように指示する(S8
,S9)。When the multi-room air conditioner is operated, the pressure detector 13 first detects the current pressure (condensing pressure during heating) (S1), compares it with a preset predetermined pressure ( S2, S3, S4), if the detected pressure is higher, the inverter controller 14 instructs the variable capacity compressor 2 to lower the operating frequency via the inverter 15, and if it is lower, instructs the variable capacity compressor 2 to increase the operating frequency ( S5). Thereafter, when a period of ΔT has elapsed (S6), the refrigerant temperature detector 16 detects the temperature of the liquid pipes 11 of the indoor units 7a, 7b, 7c, and 7d at that time (S7), and compares it with a predetermined temperature. If the detected temperature is higher, the expansion valve controller 1 of the outdoor unit 1
7 instructs the outdoor unit side electric expansion valve 5 to close to a predetermined opening, and if it is lower, instructs to open to a predetermined opening (S8
, S9).
【0022】また、室内機側電動膨張弁8a,8b,8
cおよび8dは、従来例と同様に室外機1の制御要素と
は独立して制御され、リモコンで設定された室温設定値
と空気温度検知器18a,18b,18cおよび18d
で検出される室内機7a,7b,7cおよび7dの吸込
空気の温度から空調負荷算出器19a,19b,19c
および19dが算出した空調負荷に応じて、室内機7a
,7b,7cおよび7dの膨張弁制御器20a,20b
,20cおよび20dにより室内機側電動膨張弁8a,
8b,8cおよび18dを、空調負荷が大きい時は開方
向に、小さい時には閉方向にそれぞれ制御する(S10
,S11)。[0022] Also, the indoor unit side electric expansion valves 8a, 8b, 8
c and 8d are controlled independently of the control elements of the outdoor unit 1 as in the conventional example, and are connected to the room temperature setting value set by the remote control and the air temperature detectors 18a, 18b, 18c and 18d.
Air conditioning load calculators 19a, 19b, 19c are calculated based on the temperature of the intake air of indoor units 7a, 7b, 7c and 7d detected by
and the indoor unit 7a according to the air conditioning load calculated by 19d.
, 7b, 7c and 7d expansion valve controllers 20a, 20b
, 20c and 20d, the indoor unit side electric expansion valve 8a,
8b, 8c, and 18d are controlled in the open direction when the air conditioning load is large, and in the closed direction when it is small (S10
, S11).
【0023】この時、室外機1は、室外機側電動膨張弁
5は能力可変圧縮機2の運転周波数が変化してΔT時間
後制御されるため、冷媒システムの凝縮圧力がほぼ安定
した状態で、過冷却度を制御することになり、これは凝
縮圧力に応じた過冷却度を制御することになり、通常運
転および過渡の運転状態において共に適正な制御が行わ
れる。At this time, the outdoor unit side electric expansion valve 5 of the outdoor unit 1 is controlled after a period of ΔT as the operating frequency of the variable capacity compressor 2 changes, so the condensation pressure of the refrigerant system remains almost stable. , the degree of supercooling is controlled in accordance with the condensing pressure, and proper control is performed both in normal operation and in transient operating conditions.
【0024】[0024]
【発明の効果】以上説明したように、本発明によれば、
通常運転はもちろんのこと過渡の運転状態の場合でも室
外機側電動膨張弁を絞り過ぎる現象が生ぜず、吐出温度
の過昇による機器の信頼性の低下や吸入圧力の低下によ
る能力低下によって快適性が低下することのない信頼性
の高い多室形空気調和機が得られる。[Effects of the Invention] As explained above, according to the present invention,
Not only during normal operation but also during transient operating conditions, the phenomenon of over-throttling the electric expansion valve on the outdoor unit side does not occur, and comfort is improved by reducing equipment reliability due to excessive rise in discharge temperature and reduced capacity due to decrease in suction pressure. A highly reliable multi-room air conditioner that does not deteriorate in performance can be obtained.
【0025】なお、本発明は多室形空気調和機だけでな
く、室内機1台、室外機1台の通常の空気調和機におい
ても同様の効果を有することは言うまでもない。It goes without saying that the present invention has similar effects not only on multi-room air conditioners, but also on ordinary air conditioners with one indoor unit and one outdoor unit.
【図1】本発明による多室形空気調和機の室外機側制御
要素の制御フローチャートである。FIG. 1 is a control flowchart of an outdoor unit side control element of a multi-room air conditioner according to the present invention.
【図2】本発明による多室形空気調和機の室外機側制御
要素の制御タイミングチャートである。FIG. 2 is a control timing chart of the outdoor unit side control elements of the multi-room air conditioner according to the present invention.
【図3】従来の多室形空気調和機の構成図である。FIG. 3 is a configuration diagram of a conventional multi-room air conditioner.
【図4】従来の室外機側制御要素の制御フローチャート
である。FIG. 4 is a control flowchart of a conventional outdoor unit side control element.
【図5】従来の室内機側制御要素の制御フローチャート
である。FIG. 5 is a control flowchart of a conventional indoor unit side control element.
1…室外機、 2…能力可変圧縮機、 3…四方弁
、 4…室外機側熱交換器、5…室外機側電動膨張弁
、 6…室外機側ファン、 7a,7b,7c,7
d…室内機、 8a,8b,8c,8d…室内機側電
動膨張弁、 9a,9b,9c,9d…室内機側熱交
換器、 10a,10b,10c,10d…室内機側
ファン、 11…液管、 12…ガス管、 13
…圧力検知器、 14…インバータ制御器、 15
…インバータ、 16…冷媒温度検知器、 17,
20a,20b,20c,20d…膨張弁制御器、
18a,18b,18c,18d…空気温度検知器、
19a,19b,19c,19d…空調負荷算出器。1...Outdoor unit, 2...Variable capacity compressor, 3...Four-way valve, 4...Outdoor unit side heat exchanger, 5...Outdoor unit side electric expansion valve, 6...Outdoor unit side fan, 7a, 7b, 7c, 7
d...Indoor unit, 8a, 8b, 8c, 8d...Indoor unit side electric expansion valve, 9a, 9b, 9c, 9d...Indoor unit side heat exchanger, 10a, 10b, 10c, 10d...Indoor unit side fan, 11... Liquid pipe, 12...Gas pipe, 13
...Pressure detector, 14...Inverter controller, 15
...Inverter, 16...Refrigerant temperature detector, 17,
20a, 20b, 20c, 20d...expansion valve controller,
18a, 18b, 18c, 18d...air temperature sensor,
19a, 19b, 19c, 19d...Air conditioning load calculator.
Claims (1)
機,四方弁,熱交換器および電動膨張弁を備えた室外機
と、電動膨張弁および熱交換器とをそれぞれ備えた複数
の室内機とを並列的に接続し、上記室内機と四方弁間の
配管に設けた圧力検知器の検出圧力に応じて、インバー
タの周波数を制御するインバータ制御器と、上記室内機
と室外機の電動膨張弁間の配管に設けた冷媒温度検知器
の検出温度に応じて室外機の電動膨張弁開度を制御する
膨張弁制御器と、室内機に設けた空気温度検知器の検出
する吸込空気温度と室温度設定値から空調負荷算出器が
算出する空調負荷に応じて室内機の電動膨張弁開度を制
御する膨張弁制御器とを設けた多室形空気調和機におい
て、上記のインバータ制御器と室外機の膨張弁制御器と
の制御タイミングをずらしたことを特徴とする多室形空
気調和機。Claim 1: An outdoor unit equipped with a compressor whose capacity is variable by an inverter, a four-way valve, a heat exchanger, and an electric expansion valve, and a plurality of indoor units each equipped with an electric expansion valve and a heat exchanger are connected in parallel. an inverter controller that controls the frequency of the inverter according to the detected pressure of a pressure detector installed in the piping between the indoor unit and the four-way valve, and an electric expansion valve between the indoor unit and the outdoor unit. An expansion valve controller that controls the electric expansion valve opening degree of the outdoor unit according to the temperature detected by the refrigerant temperature sensor installed in the piping, and the intake air temperature and room temperature settings detected by the air temperature sensor installed in the indoor unit. In a multi-room air conditioner equipped with an expansion valve controller that controls the electric expansion valve opening degree of the indoor unit according to the air conditioning load calculated by the air conditioning load calculator from the value, the inverter controller and the outdoor unit A multi-room air conditioner characterized by staggered control timing with an expansion valve controller.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2400516A JP2689025B2 (en) | 1990-12-05 | 1990-12-05 | Multi-room air conditioner |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2400516A JP2689025B2 (en) | 1990-12-05 | 1990-12-05 | Multi-room air conditioner |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH04214154A true JPH04214154A (en) | 1992-08-05 |
JP2689025B2 JP2689025B2 (en) | 1997-12-10 |
Family
ID=18510413
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2400516A Expired - Fee Related JP2689025B2 (en) | 1990-12-05 | 1990-12-05 | Multi-room air conditioner |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2689025B2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002156146A (en) * | 2000-11-17 | 2002-05-31 | Mitsubishi Heavy Ind Ltd | Air conditioning apparatus |
KR100444971B1 (en) * | 2002-08-06 | 2004-08-18 | 삼성전자주식회사 | Multi-chamber type air conditioner and method for controlling electric expansion valve thereof |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59104051A (en) * | 1982-12-03 | 1984-06-15 | 株式会社東芝 | Air conditioner |
JPH01212870A (en) * | 1988-02-19 | 1989-08-25 | Matsushita Refrig Co Ltd | Multichamber type air conditioner |
-
1990
- 1990-12-05 JP JP2400516A patent/JP2689025B2/en not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59104051A (en) * | 1982-12-03 | 1984-06-15 | 株式会社東芝 | Air conditioner |
JPH01212870A (en) * | 1988-02-19 | 1989-08-25 | Matsushita Refrig Co Ltd | Multichamber type air conditioner |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002156146A (en) * | 2000-11-17 | 2002-05-31 | Mitsubishi Heavy Ind Ltd | Air conditioning apparatus |
JP4616461B2 (en) * | 2000-11-17 | 2011-01-19 | 三菱重工業株式会社 | Air conditioner |
KR100444971B1 (en) * | 2002-08-06 | 2004-08-18 | 삼성전자주식회사 | Multi-chamber type air conditioner and method for controlling electric expansion valve thereof |
Also Published As
Publication number | Publication date |
---|---|
JP2689025B2 (en) | 1997-12-10 |
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