JPH046355A - Multiple-room type air-conditioner - Google Patents
Multiple-room type air-conditionerInfo
- Publication number
- JPH046355A JPH046355A JP2107917A JP10791790A JPH046355A JP H046355 A JPH046355 A JP H046355A JP 2107917 A JP2107917 A JP 2107917A JP 10791790 A JP10791790 A JP 10791790A JP H046355 A JPH046355 A JP H046355A
- Authority
- JP
- Japan
- Prior art keywords
- outdoor
- heat exchanger
- outdoor heat
- valve
- pressure pipe
- 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
- 239000003507 refrigerant Substances 0.000 claims description 26
- 238000001704 evaporation Methods 0.000 claims description 8
- 230000008020 evaporation Effects 0.000 claims description 6
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 230000005494 condensation Effects 0.000 claims description 5
- 238000009833 condensation Methods 0.000 claims description 5
- 238000000034 method Methods 0.000 abstract description 2
- 101100491857 Columba livia ASL gene Proteins 0.000 abstract 2
- 238000001816 cooling Methods 0.000 description 9
- 238000010438 heat treatment Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000087 stabilizing effect 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
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、室外機と複数の室内機との間を２本の冷媒
配管で接続し、各室内機の運転モードを冷房と暖房の混
在を可能とする冷暖同時マ）Ｌナーてアコンの自律分散
協調副部に関するものである。[Detailed Description of the Invention] [Field of Industrial Application] This invention connects an outdoor unit and a plurality of indoor units with two refrigerant pipes, and sets the operation mode of each indoor unit to a mixture of cooling and heating. This article relates to an autonomous decentralized cooperative subsection of an air conditioner that enables simultaneous cooling and heating.
第５図は例えば特開平１−３０２０７４号公報に示され
た従来の多室式空気調和機を示す構成図であり、図にお
いて、（１）は室外機、（２）は容量可変圧縮機、（３
）は四方弁、＋４１ ＋、ｆ室外側熱交換器、（５）は
室外側膨張弁、（６ａｌ 、 （６ｂ） 、 （６ｃ）
は室内機、（８ａ） 。FIG. 5 is a configuration diagram showing a conventional multi-room air conditioner disclosed in, for example, Japanese Patent Application Laid-Open No. 1-302074. In the figure, (1) is an outdoor unit, (2) is a variable capacity compressor, (3
) is a four-way valve, +41 +, f outdoor heat exchanger, (5) is outdoor expansion valve, (6al, (6b), (6c)
is an indoor unit, (8a).
（８ｂｌ 、 （８ｃ）は室内側熱交換器、（９）は室
外側送風機、（１０ａ） 、 （１０ｂ） 、 （１０
ｃ）は室内側送風機、（１））はヘッダー （１２ａ）
、 （１２ｂ） 、 （１２ｃ）は室内側第に方弁、
（１３ａ） 、 （１３ｂ） 、 （１３ｃｌは室内側
第２二方弁、（１４ａ） 、 （１４ｂ） 、 （１４
ｃ）は室内側第１膨張弁、（１５ａ）。(8bl, (8c) is the indoor heat exchanger, (9) is the outdoor blower, (10a), (10b), (10
c) is the indoor blower, (1)) is the header (12a)
, (12b), (12c) are the indoor side valves,
(13a), (13b), (13cl is the second two-way valve on the indoor side, (14a), (14b), (14
c) is a first indoor expansion valve (15a);
（１５ｂ） （１５ｃ）は室内側第２膨張弁、（１
６）は二方弁である。次に動作ｔζついて説明する。圧
縮機（２）によって圧縮された高温高圧ガス冷媒は、四
方弁（３）を通り室外側熱交換Ｍ（４）で一部凝縮液化
し、中圧の二相冷媒として室外側膨張弁（５）を経由し
て室内に送られる。室内機（６ａ）が暖房モードで室内
機（６ｂ） 、 （６ｃ）が冷房モードの時、室内に
送られた中圧の二相冷媒は室内側第に方弁（１２ａ）を
経由して室内側熱交換器（８ａ）で凝縮液化し、室内側
第２膨張弁（１５ａ）を経てヘッダー（１））に液とし
て溜まる。この中圧液冷媒が室内機（６ｂ）、 （６ｃ
）の室内第１膨張弁（１４ｂ） 、 （１４ｃ）を通っ
て各々室内熱交換器（８ｂｌ 、 （８ｃ）に入り、
こごて低圧蒸発してガス化した冷媒は室内側第２二方弁
（１３ｂＪ 、 ＜１３ｃ）を経て室外機（１）に帰る
。そして四方弁（３）を経て再び圧縮機（２）に帰り、
冷媒サイクルが形成される。(15b) (15c) is the second indoor expansion valve, (1
6) is a two-way valve. Next, the operation tζ will be explained. The high-temperature, high-pressure gas refrigerant compressed by the compressor (2) passes through the four-way valve (3) and is partially condensed and liquefied in the outdoor heat exchanger M (4). ) into the room. When the indoor unit (6a) is in the heating mode and the indoor units (6b) and (6c) are in the cooling mode, the medium-pressure two-phase refrigerant sent indoors passes through the indoor side valve (12a) and returns to the room. It is condensed and liquefied in the inner heat exchanger (8a), passes through the second indoor expansion valve (15a), and accumulates as a liquid in the header (1)). This medium pressure liquid refrigerant is supplied to the indoor unit (6b), (6c
) into the indoor heat exchangers (8bl, (8c)) through the indoor first expansion valves (14b), (14c), respectively;
The refrigerant evaporated at low pressure and gasified by the iron returns to the outdoor unit (1) via the second indoor two-way valve (13bJ, <13c). Then, it returns to the compressor (2) via the four-way valve (3), and then returns to the compressor (2) again.
A refrigerant cycle is formed.
従来の多室式空気調和機は以上のように構成されている
ので、圧縮機（２）の容量制御、室外側送風機（９）の
風量制御、室外側膨張弁（５）の制御、暖房モードの室
内機（６ａ）の出口の膨張弁（１５ａ）や冷房モードの
室内機（６ｂ） ｐ （６ｅ）の入口の膨張弁（１４ｂ
ｌ。Since the conventional multi-room air conditioner is configured as described above, the capacity control of the compressor (2), the air volume control of the outdoor fan (9), the control of the outdoor expansion valve (5), and the heating mode are performed. The expansion valve (15a) at the outlet of the indoor unit (6a) in the cooling mode and the expansion valve (14b) at the inlet of the indoor unit (6b) in cooling mode (6e)
l.
（１４ｅｌの制御が必要であり、その制御のための信号
が室内−室外間を行き来して制御が複雑になり、従って
信頼性、運転性能の安定性に欠けろという問題があった
。(It is necessary to control the 14el, and signals for the control go back and forth between indoors and outdoors, making the control complicated. Therefore, there is a problem that reliability and stability of driving performance are lacking.
この発明は上記のような問題点を解消するためになされ
たもので、室外機におし）で自律的に能力制御が行え、
イ＝頼性運転性能の安定性のよい自律分散型冷暖同時空
気調和ができろ装置を得ることを目的とする。This invention was made to solve the above-mentioned problems, and allows the outdoor unit to autonomously control its capacity.
A. The purpose of the present invention is to obtain an autonomous decentralized system capable of simultaneous cooling and heating air conditioning with good reliability and stable operation performance.
乙の発明に掛かる多室式空気調和機は、室外機側に高圧
圧力検知器Ｐｄと低圧圧力検知器Ｐｓを設け、目標高圧
圧力Ｐｄｒと目標低圧圧力Ｐｓゞとの各偏差ΔＰｄ＝Ｐ
ｄ’−Ｐｄ、△Ｐｓ＝Ｐｓ”−Ｐｓに応じて圧縮機能力
変更量ΔＱｃｏｍｐと室外熱交換器の熱交換能力変更量
△Ａｋ、をにて決定し、特に室外熱交換器を凝縮器とし
て使用する時、ＡＫｃの大きさに応して、複数に分割し
た熱交換器とガスバイパス管を選択的選ぶことができる
ようにしたものである。The multi-room air conditioner according to the invention of B is provided with a high pressure detector Pd and a low pressure detector Ps on the outdoor unit side, and each deviation ΔPd=P between the target high pressure Pdr and the target low pressure Ps.
The compression function power change amount ΔQcomp and the heat exchange capacity change amount ΔAk of the outdoor heat exchanger are determined according to d'-Pd, △Ps=Ps''-Ps, and in particular, the outdoor heat exchanger is used as a condenser. When used, a plurality of divided heat exchangers and gas bypass pipes can be selectively selected according to the magnitude of AKc.
この発明における多室式空気調和機は、冷凍サイクルの
高圧圧力の目標値Ｐｄ’と低圧圧力の目標値Ｐｓ’に対
し、実時間計測の高圧圧力Ｐｄと低圧圧力Ｐｓを圧力セ
ンサーにて集録し、その偏差ΔＰｄと△Ｐｓを演算し、
定数マ）・リックス熱交換器の熱交換能力が制御される
。The multi-chamber air conditioner according to the present invention uses a pressure sensor to collect real-time measured high pressure Pd and low pressure Ps with respect to the high pressure target value Pd' and the low pressure target value Ps' of the refrigeration cycle. , calculate the deviations ΔPd and ΔPs,
The heat exchange capacity of the constant matrix heat exchanger is controlled.
以下、この発明の一実施例を図について説明する。第１
図において、（１）１，を室外機、（２）はこの室外機
（１）内の容量可変圧縮機、（３）は四方弁、（４ａｌ
、 （４ｂ）は並列に接続された室外熱交換器、（６
＆）〜（６Ｃ）は室内機、（７）Ｌよアキュムレータ、
（８ａ）〜（８Ｃ）は室内熱交換器、（１２ａ）〜（１
２ｃ）はこの室内熱交換器（８ａ）〜（８ｃ）の一端に
接続された電子膨張弁、（１７）。An embodiment of the present invention will be described below with reference to the drawings. 1st
In the figure, (1) 1 is an outdoor unit, (2) is a variable capacity compressor in this outdoor unit (1), (3) is a four-way valve, (4al
, (4b) is an outdoor heat exchanger connected in parallel, (6
&) ~ (6C) is the indoor unit, (7) L is the accumulator,
(8a) to (8C) are indoor heat exchangers, (12a) to (1
2c) is an electronic expansion valve (17) connected to one end of the indoor heat exchangers (8a) to (8c).
（１８）は上記室外機（１）と分流コントローラ（１９
）とを結ぶ連絡配管、（２０）は上記分流コントローラ
（１９）内の高圧管部、（２１）は低圧管部、（２２）
は中圧管部、（２３）は電子膨張弁、（２４ａ）〜（２
４ｃ） 、 （２５λ）〜（２５ｅ）は電磁開閉弁であ
る。分流コントローラ（１９）から各室内機（６ａ）〜
（６Ｃ）へはそれぞれ２本の配管で接続されており、各
室内機（６ｍ）〜（６Ｃ）へはそれぞれ２本の配管で接
続されており、各室内機（６ａ）〜（６Ｃ）ノ一端はそ
れぞれ電子膨張弁（１２ａ） 〜（１２ｃｌを介して分
流コントローラ（１９）の中圧管部（２２）に接続され
、また他端はそれぞれ分流コントローラ（１９）の電磁
開閉弁（２４ａ） 〜（２４ｃ）および（２５ａ）〜（
２５ｃ）を介して高圧管部（２０）および低圧管部（２
１）につながっている。(18) is the outdoor unit (1) and the shunt controller (19).
), (20) is the high-pressure pipe section in the branch controller (19), (21) is the low-pressure pipe section, (22)
is a medium pressure pipe section, (23) is an electronic expansion valve, (24a) to (2
4c), (25λ) to (25e) are electromagnetic on-off valves. From the shunt controller (19) to each indoor unit (6a)
(6C) is connected with two pipes each, and each indoor unit (6m) to (6C) is connected with two pipes each, and each indoor unit (6a) to (6C) is connected with two pipes. One end is connected to the medium pressure pipe section (22) of the branch controller (19) via the electronic expansion valve (12a) to (12cl), and the other end is connected to the electromagnetic on-off valve (24a) to (24a) of the branch controller (19), respectively. 24c) and (25a) to (
25c) to the high pressure pipe section (20) and the low pressure pipe section (2
It is connected to 1).
（２６ｍ） 、 （２６ｂ） 、 （２７ａ） 、 （
２７ｂ）は各室外熱交換器（４ａ） 、 （４ｂ）の両
側にそれぞれ接続された開閉弁、（２８）は室外熱交換
器（４ａ） 、 （４ｂ）に並列に設けられたバイパス
路、（２９）はこのバイパス＃ （２８）に設けられた
バイパス開閉弁である。(26m), (26b), (27a), (
27b) is an on-off valve connected to both sides of each outdoor heat exchanger (4a), (4b), (28) is a bypass path provided in parallel to the outdoor heat exchanger (4a), (4b), ( 29) is a bypass opening/closing valve provided in this bypass # (28).
また、（３０）は容量可変圧縮機（２）の冷媒吐出側に
設けられその圧力Ｐｄを検知する高圧検知器、（３１）
はアキュムレータ（７）の冷媒入口側に設けられその圧
力Ｐｓと検知する低圧検知器、（３２）は上記高圧検知
！ （３０） 、低圧検知器（３１）の検知出力に基づ
いて四方弁（３）、室外側送風機（９）、開閉弁（２６
＆） 。Further, (30) is a high pressure detector provided on the refrigerant discharge side of the variable capacity compressor (2) to detect the pressure Pd; (31)
is a low pressure detector installed on the refrigerant inlet side of the accumulator (7) to detect its pressure Ps, and (32) is the high pressure detector! (30), four-way valve (3), outdoor blower (9), on-off valve (26) based on the detection output of the low pressure detector (31).
&).
（２６ｂ） 、 （２７ａｌ 、 （２７ｂ） 、バイ
パス開閉弁（２９）を制御する制御装置である。また（
３３）は四方弁である。(26b), (27al, (27b), a control device that controls the bypass on-off valve (29).
33) is a four-way valve.
このような構成の空気調和機において、室内機（６ａ）
が暖房運転モード、室内機（６ｂ） 、 （６ｃ）が冷
房運転モードである場合の動作を説明する。In an air conditioner with such a configuration, the indoor unit (6a)
The operation when is in the heating operation mode and the indoor units (6b) and (6c) are in the cooling operation mode will be explained.
室外機（１）内の圧縮機（２）で圧縮された高１高圧の
ガス冷媒は四方弁（３）を経て、室外熱交換器（４ｍ）
。The high-pressure gas refrigerant compressed by the compressor (2) in the outdoor unit (1) passes through the four-way valve (3) and is transferred to the outdoor heat exchanger (4 m).
.
（４ｂ）で一部凝縮し、二相冷媒となって高圧連絡配管
（１７）を経由して室内の分流コンＩ・ローラ（１９）
に入る。ここで気液分離器（３０）で分離された高圧ガ
ス冷媒は高圧ガス管部（２０）を経て電磁開閉弁（２５
ａ）より室内機（６ａ）に流入し、その室内熱交換式（
８＆）で暖房に供される。その後、冷媒は電子膨張弁（
１２ａ）を経て中圧管部（２２）に流入する。この冷媒
は、気液分離器（３０）の液層部から電子膨張弁（２３
）を経由して中圧管部（２２）に流入する冷媒と合流し
て室内機（６ｂ） 、 （６ｃ）に流入する。そして、
各々電子膨張弁（１２ｂ） 、 （１２ｅ）で低圧にな
り室内熱交換器（８ｂ） 、 （８ｃ）で冷房に供され
てガス化し、その後電磁開閉弁（２４ｂ） 、 （２４
ｅ）を経て低圧管部（２１）に合流し分流コノトローラ
（１９）を出て室外への連絡配管（１８）に入る。そし
て、室外１）ｉ！（１）の四方弁（３）、アキュムレー
タ（７）を通り再び圧縮部（２）に循環して冷暖同時冷
媒回路が構成されている。(4b), becomes a two-phase refrigerant, and passes through the high-pressure connecting pipe (17) to the indoor distribution controller I/roller (19).
to go into. Here, the high-pressure gas refrigerant separated by the gas-liquid separator (30) passes through the high-pressure gas pipe section (20) and then passes through the electromagnetic on-off valve (25).
a) flows into the indoor unit (6a), and its indoor heat exchange type (
8&) is used for heating. Then, the refrigerant is transferred to the electronic expansion valve (
12a) and flows into the medium pressure pipe section (22). This refrigerant is transferred from the liquid layer part of the gas-liquid separator (30) to the electronic expansion valve (23).
), the refrigerant flows into the indoor units (6b) and (6c). and,
The pressure is reduced to low by the electronic expansion valves (12b) and (12e), respectively, and then cooled and gasified by the indoor heat exchangers (8b) and (8c), after which the electromagnetic on-off valves (24b) and (24
e), joins the low-pressure pipe section (21), exits the branch controller (19), and enters the connecting pipe (18) to the outside. And outdoor 1) i! The refrigerant is circulated through the four-way valve (3) of (1) and the accumulator (7) and back to the compression section (2) to form a simultaneous cooling and heating refrigerant circuit.
以上の冷媒回路において、室内機（６ａ）の熱交換＠Ｉ
（８ａ）ば凝縮器として作用し、室内機（６ｂ） 、
ｆ６ｅ）の熱交換器（ｇｂ）、 （８ｃ）は蒸発器と
して作用している。In the above refrigerant circuit, the indoor unit (6a) heat exchange @I
(8a) acts as a condenser, and indoor unit (6b),
The heat exchanger (gb), (8c) of f6e) is acting as an evaporator.
上記のような動作においては、各室内機（１２ａ）〜（
１２ｂ）の能力の変化あるいは暖房モードと冷房モード
の切り換えにより室外機（１）側に要求される熱交換能
力も変わるが、これに対応して室外機（１）の液交換能
力を制御する必要がある。この実施例においては、高圧
検知Ｗ （３０）が検知した高圧Ｐｄを示す信号と低圧
検知器（３１）が検知した低圧Ｐｓを示す信号とが制御
装置（３２）に伝えられるが、般に圧縮機能力をアップ
すると高圧Ｐｄは上昇し、低圧Ｐｓは下降する。又蒸発
器能力をアップすると高圧Ｐｄも低圧Ｐｓも上昇し、逆
に凝１）ａ＠ＩＦ能力をアップすると高圧Ｐｄも低圧Ｐ
ｓも下降する。In the above operation, each indoor unit (12a) to (
12b) or switching between heating mode and cooling mode, the heat exchange capacity required of the outdoor unit (1) also changes, and it is necessary to control the liquid exchange capacity of the outdoor unit (1) accordingly. There is. In this embodiment, a signal indicating the high pressure Pd detected by the high pressure detector W (30) and a signal indicating the low pressure Ps detected by the low pressure detector (31) are transmitted to the control device (32). When the functional power is increased, the high pressure Pd increases and the low pressure Ps decreases. Also, when the evaporator capacity is increased, both the high pressure Pd and the low pressure Ps increase, and conversely, when the condensation capacity is increased, the high pressure Pd and the low pressure Ps are increased.
s also decreases.
この高圧Ｐｄおよび低圧が一定値を維持した定常状態で
あれば、室内側と室外側の熱交換能力が平衡していると
いうことであるから、これら高圧Ｐｄおよび低圧Ｐｓを
、所定の目標高圧圧力Ｐｄｘおよび目標低圧圧力Ｐｓ’
になるように室外機１））の熱交換能力を制御すれば室
外機（１）内で閉じた自律的制御ができる。圧縮機能力
Ｑ ｃｏｍｐの変更量を△Ｑ ｅｏｍｐ、室外熱交換器
の熱交換能力Ａｋ、の変更量をΔＡ ｋ ｏとした場合
、上述のＰｄ、Ｐｓとの関係は次の（１）式になる。If this high pressure Pd and low pressure are in a steady state where they maintain constant values, it means that the heat exchange capacity between the indoor side and the outdoor side is balanced, so these high pressure Pd and low pressure Ps are set to a predetermined target high pressure Pdx and target low pressure Ps'
If the heat exchange capacity of the outdoor unit 1) is controlled so that If the amount of change in the compression function Q comp is ΔQ eomp, and the amount of change in the heat exchange capacity Ak of the outdoor heat exchanger is ΔA k o, then the relationship with Pd and Ps described above is expressed by the following equation (1). Become.
ａ、 ｂ、 ｃ、 ｄ＞０ （１また
だし、ａ、ｂ、ｃ、ｄは予しめ決められる定数であり、
またΔＰｄ、ΔＰｓはそれぞれ目標値との偏差すなわち
ΔＰｄ＝Ｐｄ’−Ｐｄ、△Ｐｓ＝Ｐｓ”−Ｐｓである。a, b, c, d>0 (1, but a, b, c, d are predetermined constants,
Further, ΔPd and ΔPs are deviations from the target values, that is, ΔPd=Pd′−Pd and ΔPs=Ps″−Ps, respectively.
この（１）式を変形すれば、となる。If we transform this equation (1), we get the following.
このようにして求められた△Ｑ ｅｏｍｐＬこ基づし）
で圧縮機（２）の容量側部を行う。また求められた基づ
き室外熱交換器（４ａ） 、 （４ｂ）を凝ｍ器にして
放熱源として使うか蒸発器にして吸熱源として使うかを
判断して四方弁（３１，（３３）を制御する。例えば、
上記の動作状態てあれば、前の熱交換能力と求められた
熱交換能力とにより得られる熱交換能力が、正であると
きはそのまま室外熱交換器（４ａ） 、 （４ｂ）を凝
縮器とするサイクルとし、負となったときは室外熱交換
器（４ｍ） 、 （４ｂ）を蒸発器とするサイクルにす
る。そして、サイクルにおける熱交換能力（正のときＡ
Ｋｅ、負のときＡＫ ｃ）の可変制御は、室外側送風機
（９）の回転数制御および開閉弁（２６ａ） （２６
ｂ） 、 （２７ａ） 、 （２７ｂ） 、バイパス弁
（２９）の開閉制御によりなされる。すなわち、求めら
れる熱交換能力に応じて動作させる室外熱交換器の選択
およびバイパス路（２８）による冷媒のバイパス要否の
決定を行うとともに、そのときの室外送風機（９）の回
転数を可変することにより熱交換能力を連続的に制御す
るものである。第２図にこのようなｆｆ１Ｊ御における
ｆｔｌＮｍブロック図を示す。△Q eompL obtained in this way)
Perform the capacity side of the compressor (2). Also, based on the obtained results, it is determined whether the outdoor heat exchangers (4a) and (4b) are used as condensers as heat radiation sources or evaporators as heat absorption sources, and the four-way valves (31, (33) are controlled. For example,
Under the above operating conditions, if the heat exchange capacity obtained from the previous heat exchange capacity and the determined heat exchange capacity is positive, the outdoor heat exchangers (4a) and (4b) are converted into condensers. When the value becomes negative, the cycle uses the outdoor heat exchanger (4m) and (4b) as the evaporator. Then, the heat exchange capacity in the cycle (when positive, A
Ke, AK when negative c) Variable control is the rotation speed control of the outdoor fan (9) and the on-off valve (26a) (26
b) , (27a) , (27b) This is done by controlling the opening and closing of the bypass valve (29). That is, it selects the outdoor heat exchanger to be operated according to the required heat exchange capacity and determines whether or not it is necessary to bypass the refrigerant using the bypass path (28), and at the same time, varies the rotational speed of the outdoor blower (9) at that time. This allows continuous control of heat exchange capacity. FIG. 2 shows a block diagram of ftlNm in such ff1J control.
例えば室外熱交換器（４ａ） 、 （４ｂｌ凝縮器とし
て用いる場合、必要な熱交換能力に応じて室外熱交換器
（４ｍ）、 （４ｂ）両方を用いるか、室外熱交換式（
４ｂ）のみを用いるか、小るいはバイパス路（２８）に
より冷媒を一部バイパスさせながら室外熱交換器を用い
るかが選択されて各開閉弁（２６ａ） 、 （２６ｂｌ
、 （２７ａ）（２７ｂ）、バイパス弁（２９）の開
閉がなされ、さらに室外送風機（９）の回転数が制御さ
れる。第３図にそれぞれの場合における室外送風機の回
転数と凝縮器の熱交換能力の関係を示し、室外熱交換器
（４ａ） 、 （４ｂ）両方を用いた場合、室外熱交換
器（４ｂ）のみを用いた場合、バイパス路（２８）によ
りバイパスする場合の順にＡＫｃも低くなり、かつそれ
ぞれにおいて室外送風機（９）の回転数に対してＡＫｃ
が連続的に変化している。For example, when using an outdoor heat exchanger (4a), (4bl condenser), depending on the required heat exchange capacity, both the outdoor heat exchanger (4m) and (4b) may be used, or the outdoor heat exchanger (4b) may be used.
4b) or use an outdoor heat exchanger while partially bypassing the refrigerant through the bypass passage (28).
, (27a) (27b), the bypass valve (29) is opened and closed, and the rotation speed of the outdoor blower (9) is further controlled. Figure 3 shows the relationship between the rotational speed of the outdoor fan and the heat exchange capacity of the condenser in each case. When both outdoor heat exchangers (4a) and (4b) are used, only the outdoor heat exchanger (4b) is used. When using the bypass path (28), AKc also decreases in the order of bypass, and in each case, AKc decreases with respect to the rotation speed of the outdoor blower (9).
is changing continuously.
このようにすれば室外機（１）内で自律的な能力制御が
行える。In this way, autonomous capacity control can be performed within the outdoor unit (1).
また、第４図は上記高圧Ｐｄ、低圧Ｐｓのかわりにこの
空気調和装置全体における冷媒の凝縮温度ＣＴ、蒸発温
度ＥＴを検出して室外機（１）の制御を行う場合の構成
図を示す。（３４）は各室内機（６ａｌ〜（６ｃ）に設
けられた冷媒温度センサー （３５）はこの冷媒温度セ
ンサー（３４）の検知温度に基づき電子膨張弁（１２ａ
）〜（１２ｃ）を制御し、各室内機（６ａ）〜（６ｃ）
の自律制御を行うためのマイコノ、（３６）は室外熱交
換器（４ｂ）に設けられた温度センサーである。Moreover, FIG. 4 shows a configuration diagram when the outdoor unit (1) is controlled by detecting the condensation temperature CT and evaporation temperature ET of the refrigerant in the entire air conditioner instead of the above-mentioned high pressure Pd and low pressure Ps. (34) is a refrigerant temperature sensor (35) provided in each indoor unit (6al to (6c)). Based on the detected temperature of this refrigerant temperature sensor (34), an electronic expansion valve (12a) is installed.
) to (12c), and each indoor unit (6a) to (6c)
The microcontroller (36) for autonomous control is a temperature sensor installed in the outdoor heat exchanger (4b).
このような場合、冷媒温度センサー（３４）、温度セン
サー（３６）の検知温度中、最大のものを凝縮温度ＣＴ
、最小のものを蒸発温度ＥＴとし、それぞれ目標凝縮温
度ＣＴ’、目標蒸発温度ＥＴ”との偏差ΔＣＴ、△ＥＴ
を求め、上記高圧Ｐｄ、低圧ＰＳの場合と同様にして次
式から△Ｑ ｅｏｍｐ、△ＡＫＯを求め、
同様に熱交換能力を制御してもよい。この場合、例えば
室内側において最大と最小の温度をマイコン（３５）等
で選択し、これを室外側に伝送し、室外側の検知温度と
比較するなどの方法があるが、少なくとも室内−室外間
に（＝号の伝送路がひとつは必要となる。しかしながら
圧力検知器に比べ温度センサーの方がコスト面で有利で
ある。In such a case, the maximum temperature detected by the refrigerant temperature sensor (34) and temperature sensor (36) is determined as the condensing temperature CT.
, the smallest one is taken as the evaporation temperature ET, and the deviations from the target condensation temperature CT' and the target evaporation temperature ET' are ΔCT and ΔET, respectively.
Then, ΔQ eomp and ΔAKO are determined from the following equations in the same manner as in the case of the high pressure Pd and low pressure PS, and the heat exchange capacity may be controlled in the same manner. In this case, for example, there is a method in which the maximum and minimum temperatures on the indoor side are selected by a microcomputer (35), etc., and these are transmitted to the outdoor side and compared with the detected temperature on the outdoor side. At least one transmission line is required. However, a temperature sensor is more cost-effective than a pressure sensor.
以上のように、この発明によれば、室外機内の圧縮機と
室外熱交換器と四方弁の制御を、室外機内の高圧圧力と
低圧圧力のみの検知で制御するようにしたので、室内機
と室外機との自律分散制御が可能となす、イ＝頼性の向
上、運転性能の安定化がＬまかられる効果がある。As described above, according to the present invention, the compressor, outdoor heat exchanger, and four-way valve in the outdoor unit are controlled by detecting only the high pressure and low pressure in the outdoor unit. Autonomous decentralized control with the outdoor unit is possible, which has the effect of improving reliability and stabilizing driving performance.
また高圧圧力、低圧圧力のかわりに冷媒サイクル中の凝
縮温度、蒸発温度を検知して同様に制御することにより
、室外機運転の安定化がはかられる。Furthermore, by detecting the condensation temperature and evaporation temperature in the refrigerant cycle instead of the high pressure and low pressure and controlling them in the same way, the operation of the outdoor unit can be stabilized.
第１図はこの発明の一実施例による多室式空気調和機を
示す構成図、第２図は制御ブロック図、第３図はその動
作制御を説明する説明図、第４図は別の発明の実施例に
よる多室式空気調和機の構成図、第５図は多室式空気調
和機を示す構成図である。
図において、（１）は室外機、（６ａ）〜（６Ｃ）は室
内機、（８ａ） 〜（８ｃ）は室内熱交換器、（１２ａ
） 〜（１２ｃ）は電子膨張弁、（１７）、 （１８）
は連絡配管、（１９）は分流コンＩ、ローラ、（２０）
は高圧管部、（２１）は低圧管部、（２２）は中圧管部
、（２４ａ） 〜（２４ｃ） 、 （２５ａ） 〜（２
５ｃ）は電磁開閉弁、（２６ａ） 、 （２６ｂ） 、
（２７ａ） 、 （２７ｂ）は開閉弁、（２８）はバ
イパス路、（２９）はバイパス弁、（３０）は高圧検知
器、（３１）は低圧検知器、（３２）は制御装置、（３
４）は冷媒温度センサー （３６）は温度センサーであ
る。
なお、各図中同一符号は同一または相当部分を示す。Fig. 1 is a configuration diagram showing a multi-room air conditioner according to an embodiment of the present invention, Fig. 2 is a control block diagram, Fig. 3 is an explanatory diagram explaining its operation control, and Fig. 4 is another invention. Fig. 5 is a block diagram showing a multi-room air conditioner according to an embodiment of the present invention. In the figure, (1) is an outdoor unit, (6a) to (6C) are indoor units, (8a) to (8c) are indoor heat exchangers, and (12a) are indoor units.
) ~ (12c) are electronic expansion valves, (17), (18)
is the connecting pipe, (19) is the diverter controller I, roller, (20)
is a high pressure pipe section, (21) is a low pressure pipe section, (22) is a medium pressure pipe section, (24a) to (24c), (25a) to (2
5c) are electromagnetic on-off valves, (26a), (26b),
(27a), (27b) are on-off valves, (28) are bypass paths, (29) are bypass valves, (30) are high pressure detectors, (31) are low pressure detectors, (32) are control devices, (3
4) is a refrigerant temperature sensor. (36) is a temperature sensor. Note that the same reference numerals in each figure indicate the same or corresponding parts.
Claims (2)
と室外側送風機とを備え、室外から室内への連絡配管を
高圧管と低圧管との２本で構成し、上記２本の連絡配管
を分流コントローラに接続し、この分流コントローラ内
で高圧管部と低圧管部と中圧管部に三分割し、複数の室
内機を各々個別の電子膨張弁を介して上記中圧管部に接
続し、各室内機の他端は上記高圧管部もしくは上記低圧
管部に選択的に接続できるごとく構成された多室式空気
調和機において、上記室外熱交換器を複数並列に設け、
この室外熱交換器のひとつに開閉弁を接続し、室外熱交
換器と並列にバイパス開閉弁を有するバイパス路を接続
するとともに、上記室外機内にその高圧圧力Ｐｄを検知
する高圧検知器と低圧圧力Ｐｓを検知する低圧検知器と
を設け、これら高圧検知器、低圧検知器の検知圧力と設
定された目標高圧圧力Ｐｄ＾＊、目標低圧圧力Ｐｓ＾＊
との各偏差ΔＰｄ＝Ｐｄ＾＊−Ｐｄ、ΔＰｓ＝Ｐｓ＾＊
−Ｐｓに基づいて圧縮機能力変更量ΔＱｃｏｍｐと室外
熱交換器の熱交換能力変更量ΔＡｋ＿０を求め、その求
められたΔＱｃｏｍｐに基づいて上記容量可変圧縮機の
能力制御を行うとともに、ΔＡｋ＿０に基づいて上記室
外熱交換器の開閉弁、バイパス開閉弁、室外側送風機を
制御して室外側熱交換器の熱交換能力制御を行う制御手
段を設けたことを特徴とする多室式空気調和機。(1) The outdoor unit is equipped with a variable capacity compressor, a four-way valve, an outdoor heat exchanger, and an outdoor fan. Connect the connecting piping to a branch controller, divide it into three parts: a high-pressure pipe, a low-pressure pipe, and a medium-pressure pipe, and connect multiple indoor units to the medium-pressure pipe through individual electronic expansion valves. In a multi-room air conditioner configured such that the other end of each indoor unit can be selectively connected to the high-pressure pipe section or the low-pressure pipe section, a plurality of the outdoor heat exchangers are provided in parallel,
An on-off valve is connected to one of the outdoor heat exchangers, a bypass passage having a bypass on-off valve is connected in parallel with the outdoor heat exchanger, and a high pressure detector and a low pressure detector are installed in the outdoor unit to detect the high pressure Pd. A low pressure detector is provided to detect Ps, and the detected pressures of these high pressure detectors and low pressure detectors and the set target high pressure Pd^* and target low pressure Ps^* are installed.
Each deviation ΔPd=Pd^*-Pd, ΔPs=Ps^*
Based on -Ps, the compression function force change amount ΔQcomp and the heat exchange capacity change amount ΔAk_0 of the outdoor heat exchanger are determined, and the capacity of the variable capacity compressor is controlled based on the determined ΔQcomp. A multi-room air conditioner comprising a control means for controlling the heat exchange capacity of the outdoor heat exchanger by controlling the on-off valve, the bypass on-off valve, and the outdoor fan of the outdoor heat exchanger.
と室外側送風機とを備え、室外から室内への連絡配管を
高圧管と低圧管との２本で構成し、正気２本の連絡配管
を分流コントローラに接続し、この分流コントローラ内
で高圧管部と低圧管部と中圧管部に三分割し、複数の室
内機を各々個別の電子膨張弁を介して上記中圧管部に接
続し、各室内機の他端は上記高圧管部もしくは上記低圧
管部に選択的に接続できるごとく構成された多室式空気
調和機において、上記室外熱交換器を複数並列に設けこ
の室外熱交換器のひとつに開閉弁を接続し、室外熱交換
器と並列にバイパス開閉弁を有するバイパス路を接続す
るとともに、上記室外機および室内機における冷媒の凝
縮温度ＣＴと蒸発温度ＥＴとを検知する凝縮温度検知器
、蒸発温度検知器を設け、これら凝縮温度検知器、蒸発
温度検知器の検知温度と設定された目標凝縮温度ＣＴ＾
＊、目標蒸発温度ＥＴ＾＊との各偏差ΔＣＴ＝ＣＴ＾＊
−ＣＴ、ΔＥＴ＝ＥＴ＾＊−ＥＴに基づいて圧縮機能力
変更量ΔＱｃｏｍｐと室外熱交換器の熱交換能力変更量
ΔＡｋ＿０を求め、その求められたΔＱｃｏｍｐに基づ
いて上記容量可変圧縮機の能力制御を行うとともに、Δ
Ａｋ＿０に基づいて上記室外熱交換器の開閉弁、バイパ
ス開閉弁、室外側送風機を制御して室外側熱交換器の熱
交換能力制御を行う制御手段を設けたことを特徴とする
多室式空気調和機。(2) The outdoor unit is equipped with a variable capacity compressor, a four-way valve, an outdoor heat exchanger, and an outdoor fan. Connect the connecting piping to a branch controller, divide it into three parts: a high-pressure pipe, a low-pressure pipe, and a medium-pressure pipe, and connect multiple indoor units to the medium-pressure pipe through individual electronic expansion valves. In a multi-room air conditioner configured such that the other end of each indoor unit can be selectively connected to the high-pressure pipe section or the low-pressure pipe section, a plurality of the above outdoor heat exchangers are installed in parallel to transfer this outdoor heat. An on-off valve is connected to one of the exchangers, a bypass path having a bypass on-off valve is connected in parallel with the outdoor heat exchanger, and the condensation temperature CT and evaporation temperature ET of the refrigerant in the outdoor unit and indoor unit are detected. A condensing temperature detector and an evaporating temperature detector are provided, and the detected temperatures of these condensing temperature detectors and evaporating temperature detector and the set target condensing temperature CT^
*, each deviation ΔCT from the target evaporation temperature ET^* = CT^*
Based on -CT, ΔET=ET^*-ET, the compression function force change amount ΔQcomp and the heat exchange capacity change amount ΔAk_0 of the outdoor heat exchanger are determined, and the capacity control of the variable capacity compressor is controlled based on the determined ΔQcomp. At the same time, Δ
A multi-room air system characterized by comprising a control means for controlling the heat exchange capacity of the outdoor heat exchanger by controlling the on-off valve, the bypass on-off valve, and the outdoor blower of the outdoor heat exchanger based on Ak_0. harmonizer.
Priority Applications (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2107917A JP2893844B2 (en) | 1990-04-23 | 1990-04-23 | Air conditioner |
| AU72991/91A AU636726B2 (en) | 1990-03-19 | 1991-03-18 | Air conditioning system |
| DE69100574T DE69100574T2 (en) | 1990-03-19 | 1991-03-19 | Air conditioner. |
| EP91302356A EP0448345B1 (en) | 1990-03-19 | 1991-03-19 | Air conditioning system |
| ES91302356T ES2047984T3 (en) | 1990-03-19 | 1991-03-19 | AIR CONDITIONING SYSTEM. |
| EP92202252A EP0509619B1 (en) | 1990-03-19 | 1991-03-19 | Air conditioning system |
| DE69116855T DE69116855T2 (en) | 1990-03-19 | 1991-03-19 | air conditioner |
| ES92202252T ES2085552T3 (en) | 1990-03-19 | 1991-03-19 | AIR CONDITIONING SYSTEM. |
| US07/672,071 US5142879A (en) | 1990-03-19 | 1991-03-19 | Air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2107917A JP2893844B2 (en) | 1990-04-23 | 1990-04-23 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH046355A true JPH046355A (en) | 1992-01-10 |
| JP2893844B2 JP2893844B2 (en) | 1999-05-24 |
Family
ID=14471328
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2107917A Expired - Lifetime JP2893844B2 (en) | 1990-03-19 | 1990-04-23 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2893844B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US5540555A (en) * | 1994-10-04 | 1996-07-30 | Unosource Controls, Inc. | Real time remote sensing pressure control system using periodically sampled remote sensors |
| WO2014192139A1 (en) | 2013-05-31 | 2014-12-04 | 三菱電機株式会社 | Heat-medium conversion device, and air conditioner provided with heat-medium conversion device |
| WO2018003096A1 (en) * | 2016-06-30 | 2018-01-04 | 三菱電機株式会社 | Air-conditioning device |
| JPWO2020217379A1 (en) * | 2019-04-25 | 2021-10-21 | 三菱電機株式会社 | Refrigeration cycle equipment |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11060771B2 (en) | 2016-10-25 | 2021-07-13 | Samsung Electronics Co., Ltd. | Air conditioner with a refrigerant ratio adjustor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5540555A (en) * | 1994-10-04 | 1996-07-30 | Unosource Controls, Inc. | Real time remote sensing pressure control system using periodically sampled remote sensors |
| WO2014192139A1 (en) | 2013-05-31 | 2014-12-04 | 三菱電機株式会社 | Heat-medium conversion device, and air conditioner provided with heat-medium conversion device |
| US10001304B2 (en) | 2013-05-31 | 2018-06-19 | Mitsubishi Electric Corporation | Heat medium relay unit and air-conditioning apparatus including the heat medium relay unit |
| WO2018003096A1 (en) * | 2016-06-30 | 2018-01-04 | 三菱電機株式会社 | Air-conditioning device |
| GB2564995A (en) * | 2016-06-30 | 2019-01-30 | Mitsubishi Electric Corp | Air-conditioning device |
| JPWO2018003096A1 (en) * | 2016-06-30 | 2019-02-14 | 三菱電機株式会社 | Air conditioner |
| GB2564995B (en) * | 2016-06-30 | 2021-04-28 | Mitsubishi Electric Corp | Air-conditioning apparatus |
| JPWO2020217379A1 (en) * | 2019-04-25 | 2021-10-21 | 三菱電機株式会社 | Refrigeration cycle equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2893844B2 (en) | 1999-05-24 |
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