JPH04190052A - Air conditioner and its operating method - Google Patents
Air conditioner and its operating methodInfo
- Publication number
- JPH04190052A JPH04190052A JP32187990A JP32187990A JPH04190052A JP H04190052 A JPH04190052 A JP H04190052A JP 32187990 A JP32187990 A JP 32187990A JP 32187990 A JP32187990 A JP 32187990A JP H04190052 A JPH04190052 A JP H04190052A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- side heat
- usage
- user
- throttling
- 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
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
本発明は、空気調和機等に使用されるヒートポンプサイ
クルに係り、快適性及び省エネルギを図るために異なる
温度レベルに制御できる複数の利用側熱交換器を設けた
ヒートポンプサイクルとその運転方法に関するものであ
る。The present invention relates to a heat pump cycle used in an air conditioner, etc., and relates to a heat pump cycle equipped with a plurality of heat exchangers on the user side that can control different temperature levels in order to improve comfort and save energy, and a method of operating the same. It is.
最近の冷凍サイクルを用いた空気調和装置としては、冷
房運転及び暖房運転が可能で年間空調機として使用でき
るヒートポンプ式が主流となっている。またこれまで冷
凍サイクルは空調や給湯等に使用されているが、これら
の利用側熱交換器の適切な温度レベルは空調方式（気流
方式、輻射方式等）や利用形態によって異なる。
ここで、比較的簡単な構成で、異なる温度レベルを作る
ことができる複数の利用側熱交換器を設けた従来の冷凍
サイクルとして以下のようなものが知られている。
■ 特開昭５２−１２４２５３号公報
この公報では、圧縮機、上流側熱交換器、下流側熱交換
器、絞り装置、蒸発器をこの順に接続したサイクル構成
とし、さらに上流側熱交換器と下流側熱交換器にそれぞ
れ独立した流体回路を設けて異なる温度レベルの被加熱
流体をとりだし、例えばそれぞれを給湯用と暖房用に使
うようにしている。
■ 特開昭６２−２７６３７１号公報
この公報では、圧縮機、四方弁、室外側熱交換器、減圧
装置、室内側熱交換器を順次冷媒配管で接続すると共に
、四方弁と室内側熱交換器の間に輻射パネルを設けたサ
イクル構成が開示されている。このサイクル構成におい
て、暖房運転時には、圧縮機を出た高温冷媒を輻射パネ
ルから室内側熱交換器に流して輻射パネルを室内側熱交
換器に比べてより高温にし、暖房時の快適性を向上する
ようにしている。
■ 特開平２−２０３１７０号公報
この公報では、圧縮機、四方弁、熱源側熱交換器、第１
減圧装置、輻射冷房用熱交換器、第２減圧装置、負荷側
熱交換器を順次配管接続すると共に、前記輻射冷房用熱
交換器をバイパスする配管に電磁弁を配置したものであ
る。その目的とする所は、冷媒を用いた輻射冷媒装置と
潜熱を除去するための空気式冷媒装置を有機的に結合す
るばかりでなく、合わせて暖房運転をも可能にした輻射
冷暖房装置を提供することにある。As recent air conditioners using a refrigeration cycle, the mainstream is a heat pump type that can perform cooling and heating operations and can be used as an air conditioner throughout the year. Furthermore, although refrigeration cycles have been used for air conditioning, hot water supply, etc., the appropriate temperature level of the user-side heat exchanger differs depending on the air conditioning method (airflow method, radiation method, etc.) and usage type. Here, the following is known as a conventional refrigeration cycle that has a relatively simple configuration and is provided with a plurality of user-side heat exchangers that can create different temperature levels. ■ JP-A-52-124253 This publication describes a cycle configuration in which a compressor, an upstream heat exchanger, a downstream heat exchanger, a throttling device, and an evaporator are connected in this order, and the upstream heat exchanger and downstream The side heat exchangers are each provided with independent fluid circuits to take out heated fluids at different temperature levels, and are used, for example, for hot water supply and space heating, respectively. ■ Unexamined Japanese Patent Publication No. 62-276371 In this publication, a compressor, a four-way valve, an outdoor heat exchanger, a pressure reducing device, and an indoor heat exchanger are sequentially connected by refrigerant piping, and the four-way valve and the indoor heat exchanger are connected in sequence. A cycle configuration is disclosed in which a radiant panel is provided in between. In this cycle configuration, during heating operation, the high-temperature refrigerant from the compressor flows from the radiant panel to the indoor heat exchanger, making the radiant panel higher temperature than the indoor heat exchanger, improving comfort during heating. I try to do that. ■ Unexamined Japanese Patent Publication No. 2-203170 This publication describes a compressor, a four-way valve, a heat source side heat exchanger, and a first
A pressure reducing device, a heat exchanger for radiant cooling, a second pressure reducing device, and a load-side heat exchanger are sequentially connected through piping, and a solenoid valve is arranged in the piping that bypasses the heat exchanger for radiant cooling. The objective is to provide a radiant air conditioning system that not only organically combines a radiant refrigerant system using refrigerant and an air refrigerant system for removing latent heat, but also enables heating operation. There is a particular thing.
ところで、最近の空気調和機では、快適性の向上に対す
る要求が非常に強くなっているが、これは省エネルギと
両立する形で満足させる必要が有る。
しかし上記した二つの温度レベルの得られる利用側熱交
換器を設けた従来の冷凍サイクルには、次のような問題
点が有る。
■の特許公報に開示されたれ冷凍サイクルは、廃熱サイ
ドを有嗜に利用するためのサイクル構成で、例えば冷房
運転と暖房運転の両方を行なう方式となっておらず年間
空気調和機としては使用できない。また二温度化におい
ても、上流側熱交換器は主に高温ガス域を利用し、凝縮
域を利用する下流側熱交換器よりも高温になるように設
定されているが、省エネルギについては特に考慮されて
いない。
■の特許公報に開示された冷凍サイクルは、冷房運転及
び暖房運転を行なうサイクル構成にしてあるが、四方弁
と室内側熱交換器の間に設けた輻射パネルは、■の特許
公報と同様に、暖房運転時には高温ガス域を利用して、
凝縮域を利用する室内側熱交換器より高温になるように
設定されている。
また冷房運転時、輻射パネルには、低温側冷媒が流れる
が、特に有効には利用されていない。
■の公報には、輻射冷房用熱交換器が二つの減圧装Incidentally, in recent air conditioners, there has been a very strong demand for improved comfort, and this needs to be met in a way that is compatible with energy saving. However, the conventional refrigeration cycle equipped with a user-side heat exchanger capable of obtaining the two temperature levels described above has the following problems. The refrigeration cycle disclosed in the patent publication No. 2 has a cycle configuration to utilize the waste heat side wisely.For example, it is not designed to perform both cooling and heating operations, so it is not used as an air conditioner throughout the year. Can not. In addition, even in dual temperature systems, the upstream heat exchanger mainly uses the high-temperature gas region and is set to have a higher temperature than the downstream heat exchanger that uses the condensation region. Not considered. The refrigeration cycle disclosed in the patent publication (■) has a cycle configuration that performs cooling operation and heating operation, but the radiant panel installed between the four-way valve and the indoor heat exchanger is similar to the patent publication (■). , Utilizing the high temperature gas area during heating operation,
It is set to have a higher temperature than the indoor heat exchanger that uses the condensation zone. Furthermore, during cooling operation, low-temperature refrigerant flows through the radiant panel, but it is not used particularly effectively. In the publication of ■, a heat exchanger for radiant cooling has two pressure reducing devices.
上記目的を達成するために、本発明にかかるヒートポン
プサイクルでは、圧縮機、四方弁、室外側熱交換器、第
一絞り装置、第一利用側熱交換器を順次冷媒配管で接続
した従来のヒートポンプサイクルにおいて、室外側熱交
換器と第一絞り装置との間にさらに第二絞り装置と第二
利用側熱交換器をこの順に設け、暖房運転時には第二利
用側熱交換器が第一利用側熱交換器の下流側になり冷房
及び除湿運転時には第二利用側熱交換器が第一利用側熱
交換器の上流側になるようなサイクル構成とする。また
さらには第一絞り装置と第二絞り装置の間に冷媒−第二
媒体（例えば水）とで熱交換器を行う中間熱交換器を設
けると共にこの第二媒体を第二利用側熱交換器に流すよ
うなサイクル構成にしたものである。
すなわち本発明は、縮機、利用側熱交換器、絞り装置、
室外側熱交換器及びこれらを流路切り換え弁を介して接
続する配管を備えたヒートポンプ式の空気調和機におい
て、主に室内側に設ける二系統の第一及び第二の利用側
熱交換器と、全開及び両方向流れの絞り制御をできる二
つの第一及び第二の絞り装置とを設け、これら第一利用
側熱交換器、第一絞り装置、第二利用側熱交換器、第二
絞り装置を順次接続して第二利用側熱交換器が二つの絞
り装置の間になるサイクル構成にしたことを特徴とする
空気調和機である。
また本発明は、前記空気調和機において、前記第二利用
側熱交換器と前記第二絞り装置との間に気液分離器を設
けると共に、該気液分離器と前記圧縮機の吸込側とをバ
ルブ及び絞り装置を介して接続したサイクル構成にした
ことを特徴とするものである。
また本発明は、前記空気調和機において、前記第一利用
側熱交換器と前記第一絞り装置との間に気液分離機を設
けると共に、該気液分離機と圧縮機の吸込側とをバルブ
及び絞り装置を介して接続したサイクル構成にしたこと
を特徴とするものである。
また本発明は、前記空気調和機において、前記第一絞り
装置と前記第二絞り装置の間に冷媒と第二媒体との熱交
換を行う中間熱交換器を設けると共に、前記第二利用側
熱交換器に該第二媒体を循環させるサイクル構成にした
ことを特徴とするものである。
また本発明は、圧縮機、利用側熱交換器、絞り装置、室
外側熱交換器及びこれらを流路切り換え弁を介して接続
する配管を備え、主に室内側に設ける二系統の第一及び
第二の利用側熱交換器と、全開及び両方向流れの絞り制
御をできる二つの第一及び第二の絞り装置とを設け、こ
れら第一利用側熱交換器、第一絞り装置、第二利用側熱
交換器、第二絞り装置を順次接続して第二利用側熱交換
器が二つの絞り装置の間になるサイクル構成にした空気
調和機の運転方法において、暖房運転の場合に、前記第
一絞り装置を全開、前記第二絞り装置を適当に絞ること
により、前記第一利用側熱交換器に比べて前記第二利用
側熱交換器の温度が低くなるように制御して運転するこ
とを特徴とする空気調和機の運転方法である。
また本発明は、圧縮機、利用側熱交換器、絞り装置、室
外側熱交換器及びこれらを流路切り換え弁を介して接続
する配管を備え、主に室内側に設ける二系統の第一及び
第二の利用側熱交換器と、全開及び両方向流れの絞り制
御をできる二つの第一及び第二の絞り装置とを設け、こ
れら第一利用側熱交換器、第一絞り装置、第二利用側熱
交換器、第二絞り装置を順次接続して第二利用側熱交換
器が二つの絞り装置の間になるサイクル構成にした空気
調和機の運転方法において、暖房運転の場合に、前記第
一絞り装置及び前記第二絞り装置をそれぞれ適当に絞る
ことにより、前記第一利用側熱交換器が高温側放熱器、
前記第二利用側熱交換器が低温側放熱器となるように制
御して運転することを特徴とする空気調和機の運転方法
である。
また本発明は、圧縮機、利用側熱交換器、絞り装置、室
外側熱交換器及びこれらを流路切り換え弁を介して接続
する配管を備え、主に室内側に設ける二系統の第一及び
第二の利用側熱交換器と、全開及び両方向流れの絞り制
御をできる二つの第一及び第二の絞り装置とを設け、こ
れら第一利用側熱交換器、第一絞り装置、第二利用側熱
交換器、第二絞り装置を順次接続して第二利用側熱交換
器が二つの絞り装置の間になるサイクル構成にした空気
調和機の運転方法において、冷房運転の場合に、前記第
二絞り装置及び前記第一絞り装置をそれぞれ適当に絞る
ことにより、前記第二利用側熱交換器が高温側吸熱器、
前記第一利用側熱交換器が低温側吸熱器となるように制
御して運転することを特徴とする空気調和機の運転方法
である。
また本発明は、圧縮機、利用側熱交換器、絞り装置、室
外側熱交換器及びこれらを流路切り換え弁を介して接続
する配管を備え、主に室内側に設ける二系統の第一及び
第二の利用側熱交換器と、全開及び両方向流れの絞り制
御をできる二つの第一及び第二の絞り装置とを設け、こ
れら第一利用側熱交換器、第一絞り装置、第二利用側熱
交換器、第二絞り装置を順次接続して第二利用側熱交換
器が二つの絞り装置の間になるサイクル構成にした空気
調和機の運転方法において、冷房運転の場合に、前記第
二絞り装置を全開、前記第一絞り装置を適当に絞ること
により、前記第二利用側熱交換器が放熱器、前記第一利
用側熱交換器が吸熱器となるように制御して運転するこ
とを特徴とする空気調和機の運転方法である。
また本発明は、圧縮機、利用側熱交換器、絞り装置、室
外側熱交換器及びこれらを流路切り換え弁を介して接続
する配管を備え、主に室内側に設ける二系統の第一及び
第二の利用側熱交換器と、全開及び両方向流れの絞り制
御をできる二つの第一及び第二の絞り装置とを設け、こ
れら第一利用側熱交換器、第一絞り装置、第二利用側熱
交換器、第二絞り装置を順次接続して第二利用側熱交換
器が二つの絞り装置の間になるサイクル構成にした空気
調和機の運転方法において、除湿運転の場合に、前記第
二絞り装置を全開、前記第一絞り装置を適当に絞ること
により、前記第二利用側熱交換器が放熱器、前記第一利
用側熱交換器が吸熱器となるように制御して運転するこ
とを特徴とする空気調和機の運転方法である。
また本発明は、前記空気調和機のいずれかにおいて、前
記第一利用側熱交換器を気流空調ユニット、前記第二利
用側熱交換器を輻射空調ユニットとしたことを特徴とす
る空気調和器である。
また本発明は、前記空気調和機のいずれかにおいて、前
記第一絞り装置及び第二絞り装置を、全開及び両方向流
れの絞り制御が可能な多機能膨張弁としたことを特徴と
する空気調和器である。
また本発明は、前記空気調和機のいずれかにおいて、前
記第一絞り装置及び前記第二絞り装置を、キャピラリチ
ューブとバルブを並列で対になるように設けた構成にし
たことを特徴とする空気調和器である。
また本発明は、前記空気調和機のいずれかにおいて、前
記第一絞り装置及び前記第二絞り装置を、膨張弁とバル
ブを並列で対になるように設けた構成にしたことを特徴
とする空気調和機である。
また本発明は、室内側に設けてそれぞれ異なる空調方式
に用いる二系統の第一及び第二の利用側熱交換器を、全
開及び両方向流れの絞り状態を切り換えて前記各熱交換
器の温度それぞれの空調方式に適した温度レベルに制御
できる二つの第一及び第二の絞り装置により、これら二
つの空調方式を複合使用することにより、暖房、冷房及
び除湿の各運転において、快適性と省エネルギを同時に
実現するようにしたことを特徴とする空気調和機の運転
方法である。In order to achieve the above object, the heat pump cycle according to the present invention is a conventional heat pump in which a compressor, a four-way valve, an outdoor heat exchanger, a first throttling device, and a first usage side heat exchanger are sequentially connected by refrigerant piping. In the cycle, a second expansion device and a second usage side heat exchanger are further installed in this order between the outdoor heat exchanger and the first expansion device, and during heating operation, the second usage side heat exchanger is connected to the first usage side. The cycle configuration is such that the second usage-side heat exchanger is on the downstream side of the heat exchanger and is on the upstream side of the first usage-side heat exchanger during cooling and dehumidification operations. Furthermore, an intermediate heat exchanger for performing a heat exchange between a refrigerant and a second medium (for example, water) is provided between the first expansion device and the second expansion device, and the second medium is transferred to a second usage-side heat exchanger. It has a cycle structure that allows it to flow. That is, the present invention includes a compressor, a utilization side heat exchanger, a throttling device,
In a heat pump type air conditioner equipped with an outdoor heat exchanger and piping that connects these via a flow path switching valve, two systems of first and second user side heat exchangers are mainly provided indoors. , two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first usage-side heat exchanger, first throttling device, second usage-side heat exchanger, and second throttling device are provided. This air conditioner is characterized in that it has a cycle configuration in which the heat exchanger on the second usage side is located between the two expansion devices by connecting the heat exchangers in sequence. Further, in the air conditioner, the present invention provides a gas-liquid separator between the second usage-side heat exchanger and the second expansion device, and a gas-liquid separator and the suction side of the compressor. It is characterized by a cycle configuration in which the two are connected via a valve and a throttle device. Further, in the air conditioner, the present invention provides a gas-liquid separator between the first usage-side heat exchanger and the first expansion device, and a gas-liquid separator and the suction side of the compressor. It is characterized by a cycle configuration connected via a valve and a throttle device. Further, in the air conditioner, the present invention provides an intermediate heat exchanger for exchanging heat between the refrigerant and the second medium between the first expansion device and the second expansion device; It is characterized by having a cycle configuration in which the second medium is circulated through an exchanger. Further, the present invention includes a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve, and has two systems, a first and a first system provided mainly on the indoor side. A second user-side heat exchanger and two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first user-side heat exchanger, first throttling device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which a side heat exchanger and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices, in the case of heating operation, The operation is controlled so that the temperature of the second usage-side heat exchanger is lower than that of the first usage-side heat exchanger by fully opening the first expansion device and appropriately restricting the second expansion device. This is a method of operating an air conditioner characterized by the following. Further, the present invention includes a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve, and has two systems, a first and a first system provided mainly on the indoor side. A second user-side heat exchanger and two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first user-side heat exchanger, first throttling device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which a side heat exchanger and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices, in the case of heating operation, By appropriately throttling the first throttling device and the second throttling device, the first usage side heat exchanger becomes a high temperature side radiator,
This is a method of operating an air conditioner, characterized in that the second usage side heat exchanger is controlled and operated so as to function as a low temperature side radiator. Further, the present invention includes a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve, and has two systems, a first and a first system provided mainly on the indoor side. A second user-side heat exchanger and two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first user-side heat exchanger, first throttling device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which a side heat exchanger and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices, in the case of cooling operation, the above-mentioned first By appropriately throttling the second throttling device and the first throttling device, the second usage side heat exchanger becomes a high temperature side heat absorber,
This is a method of operating an air conditioner, characterized in that the air conditioner is controlled and operated so that the first usage side heat exchanger becomes a low temperature side heat absorber. Further, the present invention includes a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve, and has two systems, a first and a first system provided mainly on the indoor side. A second user-side heat exchanger and two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first user-side heat exchanger, first throttling device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which a side heat exchanger and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices, in the case of cooling operation, the above-mentioned first By fully opening the second throttling device and appropriately throttling the first throttling device, the second usage-side heat exchanger is controlled and operated as a heat radiator and the first usage-side heat exchanger is a heat absorber. This is a method of operating an air conditioner characterized by the following. Further, the present invention includes a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve, and has two systems, a first and a first system provided mainly on the indoor side. A second user-side heat exchanger and two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first user-side heat exchanger, first throttling device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which a side heat exchanger and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices, in the case of dehumidifying operation, By fully opening the second throttling device and appropriately throttling the first throttling device, the second usage-side heat exchanger is controlled and operated as a heat radiator and the first usage-side heat exchanger is a heat absorber. This is a method of operating an air conditioner characterized by the following. The present invention also provides an air conditioner, characterized in that, in any of the air conditioners, the first usage-side heat exchanger is an airflow air conditioning unit, and the second usage-side heat exchanger is a radiant air conditioning unit. be. The present invention also provides an air conditioner characterized in that, in any of the air conditioners, the first throttle device and the second throttle device are multifunctional expansion valves capable of throttle control for full opening and bidirectional flow. It is. The present invention also provides an air conditioner, characterized in that, in any of the air conditioners, the first throttle device and the second throttle device are configured such that a capillary tube and a valve are provided in parallel in pairs. It is a harmonizer. The present invention also provides an air conditioner, characterized in that, in any of the air conditioners, the first throttle device and the second throttle device are configured such that an expansion valve and a valve are provided in parallel as a pair. It is a harmonizing machine. Further, the present invention provides two systems of first and second user-side heat exchangers provided indoors and used for different air conditioning systems, respectively, by switching between a fully open state and a bidirectional flow throttling state to adjust the temperature of each heat exchanger. The two first and second diaphragm devices can control the temperature at a temperature level suitable for the air conditioning system, and by using these two air conditioning systems in combination, comfort and energy savings can be achieved in each operation of heating, cooling, and dehumidification. A method of operating an air conditioner is characterized in that the following are simultaneously realized.
以上述べた二つの絞り装置と二つの利用側熱交換器を用
いたヒートポンプサイクルにおいて、第一絞り装置と第
二絞り装置を協調して適切に絞ることにより、第一利用
側熱交換器と第二利用側熱交換器を、快適性及び省エネ
ルギの点から、それぞれに対して採用する空調方式に適
した温度レベルに制御する。 ここで例えば第一利用側
熱交換器を気流空調ユニット、第二利用側熱交換器を輻
射空調ユニットとして使用する場合を考える。暖房運転
時には、第一絞り装置を全開にし第二絞り装置を適当に
絞ることにより、輻射空調ユニットは主に過冷却域を有
効に利用することになると同時に気流空調ユニットに比
べて温度が低くなる。
また冷房運転時には、第二絞り装置を絞るか全開にし第
一絞り装置を適当に絞ることにより、輻射空調ユニット
は高温側蒸発器あるいは過冷却器となり、気流空調ユニ
ットに比べて温度が高くなる。
さらに除湿運転時には、第二絞り装置全開とし第一絞り
装置を十分絞ると共に気流空調ユニットの風量を減らす
ことにより、気流空調ユニットで湿気をとり輻射空調ユ
ニットで気温低下を防止する。
この結果、本サイクル構成及び本制御方法により快適性
及び省エネルギが同時に達成される。In the heat pump cycle using the two expansion devices and the two user-side heat exchangers described above, by coordinating the first expansion device and the second expansion device to appropriately throttle the first and second usage-side heat exchangers, it is possible to The heat exchangers on the dual-use side are controlled to a temperature level suitable for the air conditioning system adopted for each from the viewpoint of comfort and energy saving. Here, for example, consider a case where the first usage side heat exchanger is used as an airflow air conditioning unit and the second usage side heat exchanger is used as a radiant air conditioning unit. During heating operation, the first throttle device is fully opened and the second throttle device is appropriately throttled, so that the radiant air conditioning unit makes effective use of the supercooled region and at the same time lowers the temperature compared to the airflow air conditioning unit. . Furthermore, during cooling operation, by throttling or fully opening the second throttling device and appropriately throttling the first throttling device, the radiation air conditioning unit becomes a high-temperature side evaporator or supercooler, and the temperature becomes higher than that of the airflow air conditioning unit. Furthermore, during dehumidification operation, the second diaphragm device is fully opened, the first diaphragm device is fully throttled, and the air volume of the airflow air conditioning unit is reduced, so that the airflow air conditioning unit removes moisture and the radiation air conditioning unit prevents a drop in temperature. As a result, comfort and energy savings are simultaneously achieved with this cycle configuration and this control method.
【実施例】
以下、本発明の実施例を図面により詳細に説明する。
第１図乃至第３図は本発明の第１の実施例を示すもので
、このうち第１図は二つの利用側熱交換器を設けたヒー
トポンプサイクルの構成図、第２図は、第１図のサイク
ル構成における、暖房運転時のモリエル線図、第３図は
冷房運転時のモリエル線図、第４図は除湿運転時のモリ
エル線図である。
第１図において、１は圧縮機、２は冷房と暖房の運転状
態を切り替える四方弁、３は第一利用側熱交換器、４は
両方向流九の絞り制御及び全開状態が可能な多機能の第
一絞り装置、５は第二利用側熱交換器、６は両方向流れ
の絞り制御及び全開状態が可能な多機能の第二絞り装置
、７は室外側熱交換器、８は圧縮機への液戻りを防止す
るためのアキュムレータであり、これらが順次冷媒配管
によって接続されると共に第二利用側熱交換器５が第一
絞り装置４と第二絞り装置Ｉ６との間に設けられたサイ
クル構成になっている。
以上のサイクル構成により、四方弁２の切り換え及び第
一絞り装ｗ４と第二絞り装Ｍ６の絞り制御により、各熱
交換器の温度レベルを適当に切り換えて、暖房、冷房、
除湿の各運転を行なうことができる。以下、第２図〜第
４図の各モリエル線図を参照しながら各運転状態を説明
する。
まず暖房運転時には、第１図において四方弁の切り換え
により、冷媒を、圧縮機１→四方弁２→第一利用側熱交
換器３→第一絞り装置４→第二利用側熱交換器５→第二
絞り装置６→室外側熱交換器７→四方弁２→アキユムレ
一タ８→圧縮機１の順に循環させるにの場合、第一絞り
装ｆｆｉ！４を全開、第二絞り装置６を適当に絞ること
により、第一利用側熱交換器３が凝縮器、第二利用側熱
交換器５が過冷却器、室外側熱交換器７が蒸発器となる
ように運転する。すなわち第２図のモリエル線図におい
て、冷媒は、圧縮器１によりＡ点→Ｂ点のように高温高
圧ガスに圧縮されたあと、四方弁２を経て第一利用側熱
交換器３に入り、Ｃ点→Ｄ□点のように過熱域から飽和
域にかけて放熱して凝縮し、第二利用側熱交換器５に入
る。第二利用側熱交換器５では、Ｄ１点→ＥＩ点→Ｆ１
点のように状態変化して、飽和域から過冷却域にかけて
放熱する。この場合、過冷却域は温度一定の飽和域から
徐々に温度が下がる領域であるため、第二利用側熱交換
器５の平均温度は第一利用側熱交換器３の温度より低く
なる。次に第二利用側熱交換器５をでた冷媒は、第二絞
り装ｗ６でＦ工点→Ｇ点のように減圧・膨張した後、蒸
発器となる室外側熱交換器７に入ってＧ点→Ｈ点のよう
に吸熱蒸発し、さらに四方弁２、アキュムレータ８を通
ってＡ点の状態になって圧縮機１に吸い込まれる。以上
より、第一利用側熱交換器３を高温側の暖房源、第二利
用側熱交換器５を低温側の暖房源として利用することが
できる。
ところで、代表的な暖房方式としては温風暖房と輻射暖
房が有り、さらに輻射暖房の代表例として床暖房が有る
。ここで快適な温度レベルを考えると、温風暖房では約
４０℃以上の吹き出し温度、床暖房では約２０℃〜３０
℃の床面温度が必要であり、それぞれ異なった温度レベ
ルとなる。また温風暖房は通常の暖房時以外で、例えば
寒い室外から帰って急速に暖房したいような場合にも有
効であり、床暖房は頭寒足熱のような快適な暖房状態を
作るのに有効である。
従って本実施例では、第１図のサイクル構成と上述の制
御方法により、第一利用側熱交換器３を温風暖房方式、
第二利用側熱交換器５を床暖房方式として使用し、さら
には両者を複合使用することにより快適性を向上できる
空気調和機を実現できる。
また第２図において、暖房運転におけるサイクルのエネ
ルギ効率を表わす暖房成績係数は次の式％式％
この場合、Ｅ□−Ｆ２点間の過冷却域を長くして、例え
ば床暖房等の比較的低温レベルの暖房に有効に使うこと
により、成績係数を向上し省エネルギを実現することが
できる。
なお以上の説明において輻射暖房として床暖房を考えた
が、これに限らず、輻射面として壁、天井、パネル等積
々の面を考えることができ、床の場合と同様に、それぞ
れに適した温度レベルに設定することにより快適性や省
エネルギを実現することが可能になる。
従って以上述べた本実施例においては、暖房運転時に快
適性の向上と省エネルギを同時に実現することができる
。この場合、第一絞り装置４を多少絞って第２図のモリ
エル線図上でＤ１点→Ｄ２点に減圧・膨張した後、第二
利用側熱交換器５でＤ２→Ｅ２→Ｆ、のように放熱させ
てやると、二相域のり、→Ｅ２点間が長くなり液域のＥ
−Ｆ点間が短くなるため、冷媒封入量を減らすことがで
きる従って以上述べた第１図及び第２図の実施例におい
ては、暖房運転時に快適性の向上と省エネルギを同時に
実現することが可能となる。
次に冷房運転時には、第１図において四方弁２を切り換
えて、冷媒を、圧縮機１→四方弁２→室外側熱交換器７
→第２絞り装置６→第二利用側熱交換器５→第一絞り装
置４→第一利用側熱交換器３→四方弁２→アキユムレ一
タ８→圧縮機ｌの順に循環させる。この場合、第二絞り
装置６及び第一絞り装置４を適当に絞って、室外側熱交
換器７が凝縮器、第二利用側熱交換器５が高温側蒸発機
、第一利用側熱交換器３が低温側蒸発機となるように運
転する。すなわち第３図のモリエル線図において、冷媒
は、圧縮機１により工点→Ｊ点のように高温高圧ガスに
圧縮された後、四方弁２を経て室外側熱交換器７に入っ
てに点→Ｍ１点のように飽和域から過冷却域まで冷却さ
れる。次に第二絞り装置６によりＭ工点→Ｎ点のように
多少減圧・膨張されたのち高温側蒸発器となる第二利用
側熱交換器５に入りＮ点→Ｏ点まで蒸発する。この後、
第一絞り装置４に入って０点→Ｐ８点のようにさらに減
圧されてから低温側蒸発器となる第一利用側熱交換器３
に入って、Ｐ工点→Ｑ点のように蒸発し、更に四方弁２
、アキュムレータ８を通り、１点の状態となって圧縮器
１に吸い込まれる。なおこの場合の冷房運転におけるサ
イクルのエネルギ効率を表わす冷房成績係数は次式とな
る。
ところで代表的な冷房方式としては冷風冷房及び天井冷
却・壁面冷却・輻射パネル等の輻射冷房があるが、それ
らの適切な冷媒の蒸発温度レベルは、それぞれ５〜１５
℃位の間、１５〜３０℃位の間であり、異なっている。
また輻射冷房では、水処理の点から冷却面に結露しない
ようにする必要がある。
したがって、第１図において、第一利用側熱交換器３を
冷風方式の低温側蒸発器、第二利用側熱交換器５を輻射
方式の高温側蒸発器として利用することにより、上述の
各方式に適した温度レベルを実現することができる。ま
た冷風方式の第一利用側熱交換器３で除湿して湿度を下
げることができ、さらに第二利用側熱交換器の温度は第
一利用側熱交換器の温度より高いため、輻射方式の第二
利用側熱交換器表面への結露を防止することができる。
以上より、第１図および第３図の実施例では冷房運転に
おいても冷風と輻射の複合により不快な冷風を体に当て
ずに冷房・除湿を行なって快適な冷房状態を作ることが
できる。またさらには暑い室外から帰って急速に涼みた
い場合等では冷風を体に当てて涼むことができることか
ら、通常時及び過渡時を含めて快適冷房を実現できる空
気調和機とすることができる。
さらにまた冷房運転において、第二絞り装置６を全一と
し、第一絞り装置４を十分絞ることにより、室外側熱交
換器７を凝縮器、第二利用側熱交換器５を過冷却器、第
一利用側熱交換器３を蒸発器となるようにする。すなわ
ち第３図のモリエル線図上の各熱交換器において、冷媒
は、室外側熱交換器７でに点→Ｌ点まで冷却されたあと
第二利用側熱交換器５に入ってＬ点→Ｍ３点まで冷却さ
れて十分過冷却された状態になる。次に第一絞り装置４
に入ってＭ２点→Ｐ２点まで減圧・膨張されたあと第一
利用側熱交換器３に入りＰ２点→Ｑ点まで吸熱・蒸発す
る。
この場合の冷房成績係数は、次式で表わされる。
ここで（３）式の冷房成績係数を上述の（２）式と比べ
ると、（３）式のほうが、第３図のモリエル線図におい
てＭｌ−Ｍ、点間のエンタルピー差に相当する分だけ冷
房成績係数が増大し省エネルギーとなる。
この第二利用側熱交換器５を過冷却器とする絞り制御方
法は、例えば第二利用側熱交換器５を床面に組み込んで
使用する場合等では、冷廊快適性の向上にも効果がある
。
すなわち冷房状態において、立っている人や椅子に座っ
ている人にとっての適切な床面温度は、１９〜２８℃位
であるが、座ったり寝転んだ場合には適切な温度は更に
高くなる。このうち低い温度範囲は例えば前述の第二絞
り装置６を絞る制御方法によって実現でき、温度の高い
方は、第１図において、第二絞り装置６を全開にして第
二利用側熱交換器５を過冷却器として使うことにより実
現できる。この場合には、第二利用側熱交換器５での冷
媒は、温度一定の飽和域から温度が徐々に低下する過冷
却域まで変化し、その平均温度は温度一定の飽和域にあ
る室外側熱交換器７より低く３０℃前後にでき、さらに
第二利用側熱交換器５からの熱は室内と床下に放熱され
る（各放熱割合は床の構造によって調整できる）。
ここで気流空調だけの場合には一般に冷気が下方に移動
して床付近が冷えすぎるという問題がある。これに対し
、本実施例のように蒸発器とした第一利用側熱交換器３
を室内上方に取り付けて冷風ユニットとして使用し、過
冷却器とした第二利用側熱交換器５を床暖房ユニットと
して使うことにより、床付近の冷えすぎの無い快適な冷
房状態に実現でき、ひいては昼寝をするときなどにも床
面を快適な（温度）状態にできる。またさらには第二絞
り装置６を適当に絞ったりあるいは全開にして第二利用
側熱交換器５を蒸発器としたり過冷却器とすることによ
り床面付近を人間の活動状態にあわせて快適な（温度）
状態にできる。
従って、以上述べたように、冷房運転の場合にも気流ユ
ニットと輻射ユニットを複合して使用することにより真
に快適な状態を実現できる空気調和機とすることができ
る。
さらに除湿運転の場合には、四方弁により冷媒の流れ方
向を冷房運転と同じにした状態で、第二絞り装置６を全
開とし、第一絞り装置４を十分に絞ることにより、第一
利用側熱交換器３を除湿するのに十分低温の蒸発器、第
二利用側熱交換器５を過冷却器として作用させる。また
第一利用側熱交換器３は、一般的に気流ユニットとして
使用しその風量を大幅に絞る。
この場合のモリエル線図は第４図のようになり、冷媒は
、圧縮器１によりＳ点→Ｔ点のように高温高圧ガスに圧
縮された後、四方弁２をへて室外側熱交換器７に入り、
Ｕ点→Ｖ点のように凝縮する。
つづいて全開の第二絞り装Ｍ６を経て第二利用側熱交換
器５に入り、Ｖ点→Ｗ点のように冷却されると同時にこ
の時の放熱量は室内の加熱に使われる０次に第一絞り装
置４でＷ点→Ｘ点のように十分減圧・膨張した後、第一
利用側熱交換器３でＸ点→Ｙ点のように十分低温で蒸発
し、室内の除湿シ行う。
以上の結果、第一利用側熱交換器３により十分な除湿を
行うと同時に冷えすぎを第二利用側熱交換器５で温める
ことにより、冷えすぎの無い快適な除湿運転を行うこと
ができる。
次に第５図は、本発明の第２の実施例を示すサイクル構
成図であり、第１図の実施例においてさらに第二利用側
熱交換器５と第二絞り装置６の間に気液分離器９を設け
ると共に、バルブ１０、キャピラリチューブ等よりなる
微少絞り装！１１を介して気液分離器９とアキュムレー
タ８を接続したサイクル構成にしたものである。また第
１図と同一番号をつけたものは同一部分を示す。
第５図における暖房、冷房、除湿の各運転において、四
方弁２や第一絞り装置４、第二絞り装置６の制御方法は
第一図の実施例と同一であり、また冷媒の凝縮域や蒸発
域の使用状態や温度レベルも基本的には第１図と同等で
ある。
以下、各運転での動作や効果について説明する。
まず暖房運転では、バルブ１０を閉じる。この結果、サ
イクル状態さらには効果が、第一図の実施例と同様にな
る。
冷房運転で、第二絞り装置６及び第一絞り装置４を適当
に絞って、第二利用側熱交換器５を高温側蒸発器、第一
利用側熱交換器３を低温側蒸発器として使用する場合に
は、バルブ１０を開いて運転する。この場合、絞られて
二相状態になった冷媒が気液分離器９に入ると、ここで
冷凍能力に寄与しないガス冷媒と冷凍能力に寄与する液
冷媒とに分離される。このうちガス冷媒は、さらにバル
ブ１０から絞り装置１１を通って圧縮器吸込圧力まで絞
られた後、アキュムレータ８で第一利用側熱交換器３か
ら四方弁２を通ってきたメインのガス冷媒と混合して圧
縮器１に吸い込まれる。また液冷媒は、第二利用側熱交
換器５に入って吸熱・蒸発し、さらに第一絞り装！！４
に入り減圧・膨張した後、第１図の実施例と同様に、第
一利用側熱交換器３、四方弁２を通り、アキュムレータ
８で微少絞り装置１１を通ってきたガス冷媒と混合して
圧縮器１に吸い込まれる。この結果、第１図の実施例に
比べて、第二利用側熱交換器５や第一利用側熱交換器を
通る側の冷媒流量が気液分離！Ｉ９で分離された冷凍能
力に寄与しないガス冷媒の分だけ減少し、気液分Ｉ器９
以降での圧力損失が減り、省エネルギ（省電力）となる
。
また冷房運転で第二絞り装Ｗ６を全開、第一絞り装置を
４適当に絞って、第二利用側熱交換器５を過冷却器、第
一利用側熱交換器を蒸発器として使う場合には、バルブ
１０を閉じて運転する。この場合には、サイクル状態さ
らには効果が第１図の場合と同様になる。
さらに除湿運転時には、バルブ１０を閉じる。
この結果、サイクル状態やさらには効果が、第１図の実
施例と同様になる。冷媒の流れ状態やモリエル線図上で
の状態変化さらには効果が、第１図の実施例と同様にな
る。
第６図は本発明の第３の実施例を示すサイクル欅成図で
あり、第５図に比べて気液分離器１２の位置をを第一利
用側熱交換器３と第一絞り装［４との間に変えた場合で
あり、その他の構成は第５図と同一である。
第６図において、暖房運転時には、バルブ１０を閉じる
。この結果、動作や効果は第５図あるいは第１図の実施
例と同一になる。
冷房運転時には、バルブ１０を開いて運転する。
この場合には、第５図のように第二絞り装置６を絞った
場合だけでなく、第二絞り装置を全開とした場合にも効
果がある。前者の第二絞り装置６を絞った場合、第二絞
り装置６、第二利用側熱交換器５及び第一絞り装置４で
発生した冷凍能力に寄与しないガス冷媒の合計が気液分
離器１２で分離されて、バルブ１０、絞り装置１１等を
通って圧縮機１に吸い込まれ、液成分のみが第一利用側
熱交換器３へ流れる。この結果、第一利用側熱交換器３
以降での圧力損失が減り、その相当分だけ省エネルギと
なる。また後者の第二絞り装置６を全開とした場合、第
一絞り装置４を通過した後の冷媒は減圧・膨張して二相
状態となっており、ガス成分は気液分離器１２によって
分離されてた後、バルブ１０、絞り装置１１等を通って
圧縮器１に吸い込まれ、液成分のみが第一利用側熱交換
器３の方へ流れる。この結果、第一利用側熱交換器３以
降での圧力損失が減り、その分だけ省エネルギとなる。
さらに除湿運転時には、バルブ１０を閉しても開いても
よい。バルブ１０を閉じた場合には、第５図あるいは第
１図と同様の動作及び効果となる。
バルブ１ｏを開いた場合には、冷房運転の場合と同様に
、第一絞り装置４で絞られて二相状態になった冷媒のガ
ス成分は気液分離器１２で分離されて液成分のみが第一
利用側熱交換器３の方へ流れ。
圧力損失の低減により、省エネルギとなる。
次に第７図は本発明の第４の実施例であるサイクル構成
の一部分を示す図で、第１図、第５図、第６図における
二点鎖線で囲まれた部分の他の実施例を示す部分図であ
り、他の部分はこれらの図と同一である。第７図におい
て、１３は冷媒側熱交換部１４と水等の第二媒体側熱交
換部１５からなる中間熱交換器、１６は第二媒体を循環
させるためのポンプ、１７は第二媒体を循環させて熱交
換を行う構造の第二利用側熱交換器であり、さらに第一
図と同一番号を付けたものは同一部分を示す、また破線
で示した気液分離器９は第６図の実施例に対応する場合
であり、第１図及び第６図の実施例に対応する場合では
気液分離器９は無い。
以上の構成により、第７図の実施例では、暖房・冷房・
除湿の各運転において、冷媒サイクル側では四方弁２、
第一絞り装置４、第二絞り装置６、バルブ１０（以上図
示省略）を第１図の実施例さらには第５図、第６図の実
施例と同様に制御する。
この結果、暖房・冷房・除湿の各運転において、第７図
における第一利用側熱交換器３、室外側熱交換器７（以
上図示省略）のサイクル状態は、第１図あるいは第５図
、第６図の実施例と同様になり、さらに中間熱交換器１
３の冷媒側熱交換部１４のサイクル状態は第１図あるい
は第５図、第６図の第二利用側熱交換器５と同様になる
。こうした運転状態において、ポンプ１６を運転して第
二媒体を第二利用側熱交換器１７に循環させることによ
り、第７図の第二利用側熱交換器１７に第１図あるいは
第５図、第６図の第二利用側熱交換器５と同様の作用を
行わせることができる。
以上の結果、第７図の実施例も快適性や省エネルギの点
で第１図、第５図、第６図と同等の効果を得ることがで
きる。
さらに第７図の実施例において、中間熱交換器１３を室
外に置いてポンプ１６の運転を止める場合を考える。こ
の状態は利用側熱交換器が一個の場合に相当し、暖房運
転時には、第二絞り装置６を全開にし第一絞り装置４を
適当に絞ることにより、中間熱交換器１３の冷媒側熱交
換部１４を室外蒸発器として利用でき、外気からの吸熱
性能の向上により暖房能力の増大あるいは省エネルギを
図ることができる。また冷房運転時にも第二絞り装置６
を全開にし第一絞り装Ｎ４を適当に絞ることにより、冷
媒側熱交換部１４を室外側凝縮器として利用でき、外気
への放熱性能の向上により冷房能力の増大あるいは省エ
ネルギを図ることができる。
さらに第８図は、本発明の第５の実施例であるサイクル
構成の一部分を示す図で、第７図における一点鎖線で囲
まれた部分において第二利用側熱交換器を複数にした場
合に対応する、本発明による第５の実施例の部分図であ
り、他の部分は第７図あるいは第１図、第５図、第６図
と同一である。
第８図において、１８は冷媒側熱交換部分１９、第二媒
体熱交換部分２０．２３からなる中間熱交換器である。
２１．２４は第二媒体循環用のポンプ、２２．２５はそ
れぞれ１番目、２番目の第二利用側熱交換器であり、２
０．２１．２２と２３．２４．２５の各組でそれぞれ独
立した１番目、２番目の第二利用側空調ユニットを形成
している。
以上の構成においては、１番目、２番目の各第二利用側
空調ユニットを、それぞれを独立して第７図における第
二媒体側熱交換部１５、ポンプ１６、第二利用側熱交換
器１７からなる一組の空調ユニットと同様に動作させる
ことができる。
また、第８図（あるいは第７図）のように、中間熱交換
器を設は第二媒体を介して第二利用側熱交換器を接続す
る方式にすることにより、第二利用側熱交換器２２．２
５の数を増やしても冷媒側熱交換部１９の大きさはそれ
ほど大きくする必要が無いため必要冷媒量もそれ程増え
ない。従って第８図（あるいは第７図）の実施例は、第
一利用側熱交換器及び第二利用側熱交換器の使用を含め
て、複数の利用側空調ユニットを設けたいわゆる多温度
のマルチタイプ空気調和機を比較的に容易に構築するこ
とができる。さらに第８図の実施例でも、快適性や省エ
ネルギの点で、第１図、第５図、第６図及び第７図と同
様の効果が得られることはいうまでもない。
なお第８図においては、第二利用側熱交換器を２個設け
る構成としたが、これに限らず３個以上設けることも可
能で、この場合にも同様の効果が得られることは勿論で
ある。
ところで、これまでに述べた第１図、第５図、第６図、
第７図、第８図の実施例では、第一絞り装置及び第二絞
り装置として全開状態及び両方向流れの絞り制御が可能
な多機能膨張弁を想定して説明してきたが、これに限ら
ず構造の簡単なキャピラリチューブを用いても同様の効
果を得ることができる。
第９図は、第１図において絞り装置に構造の簡単なキャ
ピラリチューブを用いた場合に相当する本発明の第６の
実施例を示すサイクル構成図である。この図において、
２６は第一キャピラリチューブ、２７は第一バルブ、２
８は第二キャピラリチューブ、２９は第二バルブであり
、また第１図と同一番号を付したものは同一部分を示す
。
以上の構成により、第一キャピラリチューブ２６と第一
バルブ２７、第二キャピラリチューブ２８と第二バルブ
２９がそれぞれ対になって絞り装置を構成しており、キ
ャピラリチューブに絞り作用を行なわせる時には対で並
列に設けたバルブを閉じ、また全開状態にするにはバル
ブを開くことにより、キャピラリチューブとバルブから
なる各対に、（第１図の場合はど微調整はきかないが）
それぞれ第１図の第一絞り装置、第二絞り装置とほぼ同
等の作用を行なわせることができる。この結果、暖房、
冷房、除湿の各運転において、第１図とほぼ同等の効果
を得ることができ、比較的簡単な絞り構造及び絞り制御
により、快適性や省エネルギを実現することができる。
さらに第９図の実施例は、第５図、第６図、第７図、第
８図の実施例にも適用でき、これらの図において絞り装
置４．６として多機能膨張弁の代わりにキャピラリチュ
ーブとバルブを並列で対にした絞り装置を設けることに
より、第９図の場合と同様に比較的簡単な絞り構造及び
絞り制御により快適性の向上や省エネルギを図ることが
できることは明らかである。
なお第９図の実施例では、絞り装置としてそれぞれバル
ブ２７．２９と対にしたキャピラリチューブ２６．２８
を用いたが、これに限らず通常の膨張弁をバルブと対に
して用いることも可能で、この場合には、キャピラリチ
ューブの場合に比べて１、構造は多少複軸になるが微調
整の絞り制御ができ、これまでの実施例と同様に快適性
や省エネルギを実現することができる。また通常の膨張
弁を用いたこの構成の絞り装置は、第５図、第６図、第
７図、第８図の実施例にも適用でき、同様の効果が得ら
れることは明らかである。Embodiments Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. 1 to 3 show a first embodiment of the present invention, of which FIG. 1 is a block diagram of a heat pump cycle provided with two heat exchangers on the user side, and FIG. In the cycle configuration shown in the figure, FIG. 3 is a Mollier diagram during heating operation, FIG. 3 is a Mollier diagram during cooling operation, and FIG. 4 is a Mollier diagram during dehumidification operation. In Fig. 1, 1 is a compressor, 2 is a four-way valve that switches between cooling and heating operating states, 3 is a first user side heat exchanger, and 4 is a multi-function device that can control flow in both directions and can be fully opened. 1 is a first throttling device, 5 is a second usage-side heat exchanger, 6 is a multi-functional second throttling device that is capable of bidirectional flow throttling control and fully open state, 7 is an outdoor heat exchanger, and 8 is a heat exchanger for the compressor. This is an accumulator for preventing liquid return, and a cycle configuration in which these are sequentially connected by refrigerant piping and a second usage-side heat exchanger 5 is provided between the first expansion device 4 and the second expansion device I6. It has become. With the above cycle configuration, the temperature level of each heat exchanger can be appropriately switched by switching the four-way valve 2 and controlling the first restrictor W4 and the second restrictor M6 to provide heating, cooling,
Each dehumidification operation can be performed. Hereinafter, each operating state will be explained with reference to the Mollier diagrams shown in FIGS. 2 to 4. First, during heating operation, the refrigerant is transferred by switching the four-way valve in FIG. When circulating in the order of second throttling device 6 → outdoor heat exchanger 7 → four-way valve 2 → storage unit 8 → compressor 1, first throttling device ffi! 4 is fully opened and the second throttle device 6 is appropriately throttled, the first usage-side heat exchanger 3 becomes a condenser, the second usage-side heat exchanger 5 becomes a subcooler, and the outdoor heat exchanger 7 becomes an evaporator. Drive so that That is, in the Mollier diagram of FIG. 2, the refrigerant is compressed into high temperature and high pressure gas by the compressor 1 from point A to point B, and then enters the first user side heat exchanger 3 via the four-way valve 2. The heat is radiated and condensed from the superheat region to the saturation region from point C to point D□, and then enters the second usage-side heat exchanger 5. In the second usage side heat exchanger 5, D1 point → EI point → F1
It changes state like a dot and radiates heat from the saturated region to the supercooled region. In this case, since the supercooling region is a region where the temperature gradually decreases from the saturated region where the temperature is constant, the average temperature of the second usage-side heat exchanger 5 is lower than the temperature of the first usage-side heat exchanger 3. Next, the refrigerant that exits the second user-side heat exchanger 5 is decompressed and expanded in the second restrictor w6 from point F to point G, and then enters the outdoor heat exchanger 7, which serves as an evaporator. It evaporates endothermically from point G to point H, passes through the four-way valve 2 and accumulator 8, reaches point A, and is sucked into the compressor 1. As described above, the first usage-side heat exchanger 3 can be used as a high-temperature side heating source, and the second usage-side heat exchanger 5 can be used as a low-temperature side heating source. By the way, typical heating methods include hot air heating and radiant heating, and a typical example of radiant heating is floor heating. Considering the comfortable temperature level here, the outlet temperature for warm air heating is about 40℃ or higher, and for floor heating it is about 20℃ to 30℃.
A floor temperature of °C is required, each resulting in a different temperature level. Hot-air heating is also effective for situations other than normal heating, such as when you want to quickly heat your home after returning from a cold day outdoors, and floor heating is effective for creating comfortable heating conditions when your head is cold and your feet are warm. Therefore, in this embodiment, by using the cycle configuration shown in FIG.
By using the second user-side heat exchanger 5 as a floor heating system and by using both in combination, an air conditioner that can improve comfort can be realized. In addition, in Fig. 2, the heating coefficient of performance, which represents the energy efficiency of the cycle in heating operation, is calculated using the following formula (% formula %). By effectively using it for heating at low temperature levels, it is possible to improve the coefficient of performance and realize energy savings. In the above explanation, we considered floor heating as radiant heating, but it is not limited to this; walls, ceilings, panels, and other stacked surfaces can also be considered as radiant surfaces, and as with floors, By setting the temperature level, it becomes possible to achieve comfort and energy savings. Therefore, in the present embodiment described above, it is possible to simultaneously improve comfort and save energy during heating operation. In this case, after the first throttle device 4 is throttled to some extent to reduce and expand the pressure from point D1 to point D2 on the Mollier diagram in FIG. If heat is dissipated to
- Since the distance between points F becomes shorter, the amount of refrigerant charged can be reduced.Therefore, in the embodiments shown in Figures 1 and 2 described above, it is possible to simultaneously improve comfort and save energy during heating operation. It becomes possible. Next, during cooling operation, the four-way valve 2 is switched in FIG. 1 to transfer the refrigerant from the compressor 1 to the four-way valve 2 to the outdoor heat exchanger
→ second expansion device 6 → second usage-side heat exchanger 5 → first expansion device 4 → first usage-side heat exchanger 3 → four-way valve 2 → storage unit 8 → compressor 1. In this case, the second throttle device 6 and the first throttle device 4 are appropriately throttled so that the outdoor heat exchanger 7 becomes a condenser, the second usage-side heat exchanger 5 becomes a high-temperature side evaporator, and the first usage-side heat exchanger Operate so that the evaporator 3 functions as a low-temperature side evaporator. In other words, in the Mollier diagram shown in Fig. 3, the refrigerant is compressed into high-temperature, high-pressure gas by the compressor 1 from the work point to the J point, and then passes through the four-way valve 2, enters the outdoor heat exchanger 7, and returns to the point. → It is cooled from the saturated region to the supercooled region as shown at M1 point. Next, after being somewhat depressurized and expanded from the M work point to the N point by the second expansion device 6, it enters the second usage side heat exchanger 5, which serves as a high temperature side evaporator, and evaporates from the N point to the O point. After this,
The first use-side heat exchanger 3 enters the first expansion device 4 and becomes further depressurized from point 0 to point P8, and then becomes a low-temperature side evaporator.
It evaporates from point P to point Q, and then the four-way valve 2
, passes through the accumulator 8, becomes a single point state, and is sucked into the compressor 1. In this case, the cooling coefficient of performance representing the energy efficiency of the cycle in cooling operation is expressed by the following formula. By the way, typical cooling methods include cold air cooling, ceiling cooling, wall cooling, and radiant cooling such as radiant panels, but the appropriate evaporation temperature level of the refrigerant for each of these is 5 to 15.
℃, and between 15 and 30℃, which are different. In addition, in radiant cooling, it is necessary to prevent condensation from forming on the cooling surface from the viewpoint of water treatment. Therefore, in FIG. 1, by using the first usage-side heat exchanger 3 as a cold-air type low-temperature side evaporator and the second usage-side heat exchanger 5 as a radiation-type high-temperature side evaporator, each of the above-mentioned systems can be used. It is possible to achieve a temperature level suitable for In addition, the first user-side heat exchanger 3 of the cold air method can dehumidify and lower the humidity, and since the temperature of the second user-side heat exchanger is higher than the temperature of the first user-side heat exchanger, the radiation method Condensation on the surface of the second usage side heat exchanger can be prevented. As described above, in the embodiments shown in FIGS. 1 and 3, even during cooling operation, a comfortable cooling state can be created by performing cooling and dehumidification by combining cold air and radiation without exposing the body to unpleasant cold air. Furthermore, when you return from a hot day outdoors and want to cool down quickly, you can blow cold air onto your body to cool yourself down, so the air conditioner can provide comfortable cooling both during normal times and during transient times. Furthermore, in the cooling operation, by setting the second throttle device 6 to full capacity and sufficiently throttling the first throttle device 4, the outdoor heat exchanger 7 can be used as a condenser, and the second usage side heat exchanger 5 can be used as a supercooler. The first usage side heat exchanger 3 is made to function as an evaporator. In other words, in each heat exchanger on the Mollier diagram in FIG. 3, the refrigerant is cooled in the outdoor heat exchanger 7 from a point to a point L, and then enters the second user heat exchanger 5 and cools from a point L to a point L. It is cooled to the M3 point and becomes sufficiently supercooled. Next, the first squeezing device 4
After being depressurized and expanded from point M2 to point P2, it enters the first user heat exchanger 3 and absorbs heat and evaporates from point P2 to point Q. The cooling coefficient of performance in this case is expressed by the following formula. Here, when comparing the cooling performance coefficient of equation (3) with equation (2) above, equation (3) is better by an amount corresponding to Ml-M, the enthalpy difference between points in the Mollier diagram of Figure 3. The cooling coefficient of performance increases, resulting in energy savings. This throttling control method using the second user-side heat exchanger 5 as a supercooler is also effective in improving the comfort of the cooling corridor, for example, when the second user-side heat exchanger 5 is installed and used on the floor. There is. That is, in an air-conditioned state, the appropriate floor surface temperature for a person standing or sitting on a chair is about 19 to 28 degrees Celsius, but when sitting or lying down, the appropriate temperature is even higher. The lower temperature range can be realized, for example, by the aforementioned control method of throttling the second throttling device 6, and the higher temperature range can be achieved by fully opening the second throttling device 6 in FIG. This can be achieved by using it as a supercooler. In this case, the refrigerant in the second user side heat exchanger 5 changes from a saturated region where the temperature is constant to a supercooled region where the temperature gradually decreases, and the average temperature is on the outdoor side where the temperature is in the saturated region where the temperature is constant. The temperature can be lowered to around 30° C. than that of the heat exchanger 7, and the heat from the second user-side heat exchanger 5 is radiated into the room and under the floor (each heat radiation ratio can be adjusted depending on the structure of the floor). If only airflow air conditioning is used, there is generally a problem that cold air moves downward, making the area near the floor too cold. On the other hand, the first use side heat exchanger 3 which is an evaporator as in this embodiment
By attaching it to the upper part of the room and using it as a cold air unit, and using the second user side heat exchanger 5, which is a supercooler, as a floor heating unit, it is possible to achieve a comfortable cooling condition without excessively cooling the area near the floor. The floor surface can be kept in a comfortable (temperature) state even when taking a nap. Furthermore, by appropriately throttling the second diaphragm device 6 or opening it fully, the second user-side heat exchanger 5 can be used as an evaporator or supercooler to make the area near the floor surface comfortable according to the state of human activity. (temperature)
state. Therefore, as described above, by using the air flow unit and the radiation unit in combination even in the case of cooling operation, it is possible to provide an air conditioner that can realize a truly comfortable state. Furthermore, in the case of dehumidifying operation, the second throttle device 6 is fully opened and the first throttle device 4 is sufficiently throttled, with the refrigerant flow direction set in the same direction as the cooling operation using the four-way valve. The evaporator, which is low enough to dehumidify the heat exchanger 3, and the second usage-side heat exchanger 5 act as a supercooler. Further, the first user-side heat exchanger 3 is generally used as an airflow unit, and its air volume is greatly reduced. The Mollier diagram in this case is as shown in Figure 4, and the refrigerant is compressed into high-temperature, high-pressure gas by the compressor 1 from point S to point T, and then passes through the four-way valve 2 to the outdoor heat exchanger. Entering 7,
Condenses from point U to point V. Next, it passes through the fully opened second diaphragm M6 and enters the second user-side heat exchanger 5, where it is cooled from point V to point W. At the same time, the amount of heat released at this time is 0-order, which is used for indoor heating. After being sufficiently depressurized and expanded from point W to point X in the first expansion device 4, it is evaporated at a sufficiently low temperature from point X to point Y in the first user-side heat exchanger 3, thereby dehumidifying the room. As a result of the above, by performing sufficient dehumidification by the first usage-side heat exchanger 3 and at the same time warming the excessively cold temperature by the second usage-side heat exchanger 5, a comfortable dehumidification operation without excessive cooling can be performed. Next, FIG. 5 is a cycle configuration diagram showing a second embodiment of the present invention. In the embodiment of FIG. In addition to the separator 9, a micro-diaphragm device consisting of a valve 10, capillary tube, etc. is installed! This has a cycle configuration in which a gas-liquid separator 9 and an accumulator 8 are connected via a gas-liquid separator 9 and an accumulator 8. Also, the same numbers as in FIG. 1 indicate the same parts. In each of the heating, cooling, and dehumidifying operations shown in FIG. The usage conditions and temperature levels of the evaporation zone are basically the same as in Figure 1. The operations and effects of each operation will be explained below. First, in heating operation, the valve 10 is closed. As a result, the cycle state and effect become similar to the embodiment shown in FIG. During cooling operation, the second expansion device 6 and the first expansion device 4 are appropriately throttled to use the second usage-side heat exchanger 5 as a high-temperature side evaporator and the first usage-side heat exchanger 3 as a low-temperature side evaporator. If so, open the valve 10 and operate. In this case, when the refrigerant that has been throttled into a two-phase state enters the gas-liquid separator 9, it is separated into a gas refrigerant that does not contribute to the refrigeration capacity and a liquid refrigerant that contributes to the refrigeration capacity. Of these, the gas refrigerant is further throttled from the valve 10 through the throttle device 11 to the compressor suction pressure, and then combined with the main gas refrigerant that has passed from the first user heat exchanger 3 through the four-way valve 2 in the accumulator 8. The mixture is sucked into the compressor 1. In addition, the liquid refrigerant enters the second user-side heat exchanger 5, absorbs heat and evaporates, and is further transferred to the first restrictor! ! 4
After being depressurized and expanded, it passes through the first user-side heat exchanger 3 and four-way valve 2, and is mixed with the gas refrigerant that has passed through the micro-throttle device 11 in the accumulator 8, as in the embodiment shown in FIG. It is sucked into the compressor 1. As a result, compared to the embodiment shown in FIG. 1, the refrigerant flow rate through the second usage-side heat exchanger 5 and the first usage-side heat exchanger is separated into gas and liquid! The amount of gas refrigerant that does not contribute to the refrigeration capacity separated in I9 is reduced, and the gas-liquid separator I9
Subsequent pressure loss is reduced, resulting in energy savings (power savings). In addition, when the second throttle device W6 is fully opened during cooling operation, the first throttle device is appropriately throttled, and the second user-side heat exchanger 5 is used as a supercooler and the first user-side heat exchanger 5 is used as an evaporator. is operated with valve 10 closed. In this case, the cycle state and effect will be the same as in the case of FIG. Further, during dehumidification operation, the valve 10 is closed. As a result, the cycle conditions and even the effects become similar to those of the embodiment shown in FIG. The flow state of the refrigerant, the state change on the Mollier diagram, and the effects are the same as in the embodiment shown in FIG. FIG. 6 is a cycle diagram showing a third embodiment of the present invention, and compared to FIG. 4, and the other configurations are the same as in FIG. 5. In FIG. 6, the valve 10 is closed during heating operation. As a result, the operation and effects are the same as those of the embodiment shown in FIG. 5 or 1. During cooling operation, the valve 10 is opened. In this case, there is an effect not only when the second diaphragm device 6 is throttled as shown in FIG. 5, but also when the second diaphragm device is fully opened. When the former second throttle device 6 is throttled, the total amount of gas refrigerant that does not contribute to the refrigerating capacity generated in the second throttle device 6, second usage-side heat exchanger 5, and first throttle device 4 is reduced to the gas-liquid separator 12. The liquid component is separated and sucked into the compressor 1 through the valve 10, throttle device 11, etc., and only the liquid component flows to the first usage side heat exchanger 3. As a result, the first user side heat exchanger 3
Subsequent pressure loss is reduced, resulting in energy savings corresponding to that amount. Furthermore, when the latter second throttle device 6 is fully opened, the refrigerant after passing through the first throttle device 4 is decompressed and expanded and becomes a two-phase state, and the gas component is separated by the gas-liquid separator 12. After that, the liquid component is sucked into the compressor 1 through the valve 10, the throttle device 11, etc., and only the liquid component flows toward the first usage-side heat exchanger 3. As a result, the pressure loss after the first use-side heat exchanger 3 is reduced, resulting in energy savings correspondingly. Furthermore, during dehumidification operation, the valve 10 may be closed or opened. When the valve 10 is closed, the operation and effect are similar to those shown in FIG. 5 or FIG. 1. When the valve 1o is opened, the gas component of the refrigerant that has been throttled into a two-phase state by the first throttling device 4 is separated by the gas-liquid separator 12, and only the liquid component is left, as in the case of cooling operation. Flows toward the first usage side heat exchanger 3. Reduced pressure loss results in energy savings. Next, FIG. 7 is a diagram showing a part of the cycle configuration which is the fourth embodiment of the present invention, and is another embodiment of the part surrounded by the two-dot chain line in FIGS. 1, 5, and 6. This is a partial diagram showing the other parts of the figure. In FIG. 7, 13 is an intermediate heat exchanger consisting of a refrigerant side heat exchange part 14 and a second medium side heat exchange part 15 such as water, 16 is a pump for circulating the second medium, and 17 is a pump for circulating the second medium. This is a second usage-side heat exchanger with a structure that exchanges heat by circulating it. Furthermore, the same numbers as in Figure 1 indicate the same parts, and the gas-liquid separator 9 shown with a broken line is the same as in Figure 6. In the case corresponding to the embodiment shown in FIGS. 1 and 6, the gas-liquid separator 9 is not provided. With the above configuration, in the embodiment shown in FIG.
In each dehumidification operation, on the refrigerant cycle side, four-way valve 2,
The first throttle device 4, the second throttle device 6, and the valve 10 (not shown above) are controlled in the same manner as in the embodiment shown in FIG. 1, as well as in the embodiments shown in FIGS. 5 and 6. As a result, in each operation of heating, cooling, and dehumidification, the cycle states of the first usage-side heat exchanger 3 and the outdoor heat exchanger 7 (not shown) in FIG. 7 are as shown in FIG. 1 or 5. The structure is similar to the embodiment shown in FIG. 6, and the intermediate heat exchanger 1
The cycle state of the refrigerant-side heat exchange section 14 of No. 3 is the same as that of the second usage-side heat exchanger 5 of FIG. 1, FIG. 5, or FIG. 6. In such an operating state, by operating the pump 16 to circulate the second medium to the second usage-side heat exchanger 17, the second usage-side heat exchanger 17 shown in FIG. It can perform the same function as the second usage-side heat exchanger 5 in FIG. 6. As a result of the above, the embodiment shown in FIG. 7 can also achieve the same effects as those shown in FIGS. 1, 5, and 6 in terms of comfort and energy saving. Furthermore, in the embodiment shown in FIG. 7, consider a case where the intermediate heat exchanger 13 is placed outdoors and the operation of the pump 16 is stopped. This state corresponds to the case where there is only one heat exchanger on the user side, and during heating operation, the second throttle device 6 is fully opened and the first throttle device 4 is appropriately throttled to exchange heat on the refrigerant side of the intermediate heat exchanger 13. The section 14 can be used as an outdoor evaporator, and heating capacity can be increased or energy can be saved by improving heat absorption performance from outside air. Also, during cooling operation, the second throttle device 6
By fully opening the first restrictor N4 and appropriately restricting the first restrictor N4, the refrigerant side heat exchange section 14 can be used as an outdoor condenser, and cooling capacity can be increased or energy can be saved by improving heat dissipation performance to the outside air. . Further, FIG. 8 is a diagram showing a part of the cycle configuration according to the fifth embodiment of the present invention, in which a plurality of second use-side heat exchangers are provided in the part surrounded by the dashed line in FIG. 7 is a corresponding partial view of a fifth embodiment according to the present invention, other parts being the same as FIG. 7 or FIG. 1, FIG. 5, and FIG. 6; In FIG. 8, 18 is an intermediate heat exchanger consisting of a refrigerant side heat exchange section 19 and a second medium heat exchange section 20.23. 21.24 is a pump for second medium circulation, 22.25 is the first and second second use side heat exchangers, respectively;
Each set of 0.21.22 and 23.24.25 forms an independent first and second user-side air conditioning unit. In the above configuration, each of the first and second second usage-side air conditioning units is independently connected to the second medium-side heat exchanger 15, pump 16, and second usage-side heat exchanger 17 in FIG. It can be operated in the same way as a set of air conditioning units. In addition, as shown in Figure 8 (or Figure 7), by connecting the intermediate heat exchanger to the second user side heat exchanger via the second medium, the second user side heat exchanger can be Vessel 22.2
Even if the number 5 is increased, the size of the refrigerant-side heat exchange section 19 does not need to be increased so much, and the required amount of refrigerant will not increase that much. Therefore, the embodiment shown in FIG. 8 (or FIG. 7) is a so-called multi-temperature multi-unit system in which a plurality of user-side air conditioning units are provided, including the use of a first user-side heat exchanger and a second user-side heat exchanger. type air conditioner can be constructed relatively easily. Furthermore, it goes without saying that the embodiment shown in FIG. 8 also provides the same effects as those shown in FIGS. 1, 5, 6, and 7 in terms of comfort and energy saving. In addition, in FIG. 8, the configuration is shown in which two second heat exchangers are provided, but the configuration is not limited to this, and it is also possible to provide three or more, and it goes without saying that the same effect can be obtained in this case as well. be. By the way, Figures 1, 5, 6, and
In the embodiments shown in FIGS. 7 and 8, explanations have been made assuming that the first throttle device and the second throttle device are multifunctional expansion valves capable of throttle control in a fully open state and bidirectional flow, but the invention is not limited to this. A similar effect can be obtained by using a capillary tube with a simple structure. FIG. 9 is a cycle configuration diagram showing a sixth embodiment of the present invention, which corresponds to the case where a capillary tube with a simple structure is used as the expansion device in FIG. 1. In this diagram,
26 is the first capillary tube, 27 is the first valve, 2
8 is a second capillary tube, 29 is a second valve, and the same numbers as in FIG. 1 indicate the same parts. With the above configuration, the first capillary tube 26 and the first valve 27, and the second capillary tube 28 and the second valve 29 are each paired to form a throttling device, and when the capillary tube is to perform a throttling action, the By closing the valves installed in parallel with each other, and opening the valves to fully open each pair of capillary tubes and valves, (although fine adjustment is not possible in the case of Figure 1)
It is possible to perform substantially the same functions as the first diaphragm device and the second diaphragm device shown in FIG. 1, respectively. As a result, heating
In each operation of air conditioning and dehumidification, substantially the same effects as those shown in FIG. 1 can be obtained, and comfort and energy savings can be achieved by a relatively simple throttle structure and throttle control. Furthermore, the embodiment of FIG. 9 can also be applied to the embodiments of FIGS. 5, 6, 7 and 8, in which a capillary is used as the throttle device 4.6 instead of the multifunctional expansion valve. It is clear that by providing a throttling device in which a tube and a valve are paired in parallel, it is possible to improve comfort and save energy through a relatively simple throttling structure and throttling control, as in the case of Fig. 9. . In the embodiment shown in FIG. 9, capillary tubes 26 and 28 each are paired with a valve 27 and 29 as a restricting device.
However, it is not limited to this, and it is also possible to use a normal expansion valve as a pair with the valve. Aperture control is possible, and comfort and energy savings can be achieved in the same way as in the previous embodiments. It is clear that the throttle device having this configuration using a normal expansion valve can also be applied to the embodiments shown in FIGS. 5, 6, 7, and 8, and similar effects can be obtained.
以上詳細に説明したように、本発明によれば、主に空調
時の暖房運転、冷房運転さらには除湿運転を行うヒート
ポンプサイクルにおいて、室内側に第一及び第二の二つ
の利用側熱交換器を設けると共にこのうちの第二利用側
熱交換器の両側に第一及び第二の二つの絞り装置を設け
たサイクル構成とし、二つの絞り装置を協調して適切に
制御することにより、暖房、冷房、除湿の各運転におい
て、二つの利用側熱交換器を例えば気流方式や輻射方式
等の空調方式に対して適切な異なる温度レベルに制御す
る事ができる。この結果、人の種々の活動状態に応じて
快適状態を実現できると共に省エネルギを図る事ができ
る。
また第二利用側熱交換器に対しては、二つの絞り装置の
間に冷媒−第二媒体中間熱交換器を設け、第二媒体を第
二利用側熱交換器に循環させるサイクル構成にすること
により、冷媒封入量を増やすことなく複数の第二利用側
熱交換器を設けることが可能で、多温度マルチヒートポ
ンプ等のシステムを構築する上で優れたサイクル構成を
提供できる。As described above in detail, according to the present invention, in a heat pump cycle that mainly performs heating operation, cooling operation, and dehumidification operation during air conditioning, two user-side heat exchangers are installed on the indoor side. A cycle configuration is adopted in which two throttle devices, the first and second, are installed on both sides of the second heat exchanger on the user side, and by controlling the two throttle devices in coordination and appropriately, heating, In each cooling and dehumidifying operation, the two user-side heat exchangers can be controlled to different temperature levels appropriate for the air conditioning method, such as the airflow method or the radiation method. As a result, it is possible to realize a comfortable state depending on the various activity states of the person and to save energy. In addition, for the second usage side heat exchanger, a refrigerant-second medium intermediate heat exchanger is installed between the two expansion devices, and a cycle configuration is adopted in which the second medium is circulated to the second usage side heat exchanger. By doing so, it is possible to provide a plurality of second use-side heat exchangers without increasing the amount of refrigerant sealed, and it is possible to provide an excellent cycle configuration in constructing a system such as a multi-temperature multi-heat pump.
第１図は本発明による二つの利用側熱交換器を設けこれ
らの温度レベルを二つの膨張弁により適切に制御する二
温度ヒートポンプサイクルの第１の実施例を示す構成図
である。
第２図、第３図及び第４図はそれぞれ第１図の二温度ヒ
ートポンプサイクルにおける暖房運転、冷房運転及び除
湿運転に相当するモリエル線図である。
第５図及び第６図はそれぞれ第１図の実施例をさらに改
善した本発明による第２及び第３の実施例を示す構成図
である。
第７図は第二媒体を介して第二利用側熱交換器を接続し
た構成の本発明による第４の実施例を示す構成図で第１
図、第５図および第６図における第二利用側熱交換器に
関係する所の部分図である。
第８図は第７図において第二利用側熱交換器を複数にし
た場合の本発明による第５の実施例を示す部分図である
。
第９図は絞り装置にキャピラリチューブを用いた場合の
本発明による第６の実施例を示す図である。
１・・・圧縮機 ２・・・四方弁
３・・・第一利用側熱交換器 ４・・・第一絞り装置５
．１７，２２，２５・・・第二利用側熱交換器６・・・
第二絞り装置 ７・・・室外側熱交換器９．１２・・
・気液分離機
１０．２７，２９・・・バルブ １１・・・絞り装置
１３．１８・・・中間熱交換器
１４．１９・・・冷媒側熱交換部
１５．２０．２３・・・第二媒体側熱交換部１６．２１
，２４・・・ポンプ
２６．２８・・・キャピラリチューブ。FIG. 1 is a block diagram showing a first embodiment of a two-temperature heat pump cycle according to the present invention, which is provided with two heat exchangers on the utilization side and whose temperature levels are appropriately controlled by two expansion valves. 2, 3, and 4 are Mollier diagrams corresponding to heating operation, cooling operation, and dehumidification operation in the two-temperature heat pump cycle of FIG. 1, respectively. FIGS. 5 and 6 are block diagrams showing second and third embodiments of the present invention, respectively, which are further improvements over the embodiment shown in FIG. FIG. 7 is a configuration diagram showing a fourth embodiment of the present invention in which a second usage-side heat exchanger is connected via a second medium.
FIG. 7 is a partial view of a portion related to the second usage-side heat exchanger in FIGS. 5 and 6; FIG. FIG. 8 is a partial view showing a fifth embodiment of the present invention in which a plurality of second heat exchangers are provided in FIG. 7. FIG. 9 is a diagram showing a sixth embodiment of the present invention in which a capillary tube is used as the aperture device. 1... Compressor 2... Four-way valve 3... First usage side heat exchanger 4... First throttle device 5
．． 17, 22, 25...Second usage side heat exchanger 6...
Second throttle device 7...Outdoor heat exchanger 9.12...
- Gas-liquid separator 10.27, 29... Valve 11... Throttle device 13.18... Intermediate heat exchanger 14.19... Refrigerant side heat exchange section 15.20.23... No. Two medium side heat exchange section 16.21
, 24...Pump 26.28...Capillary tube.
Claims (1)
器及びこれらを流路切り換え弁を介して接続する配管を
備えたヒートポンプ式の空気調和機において、主に室内
側に設ける二系統の第一及び第二の利用側熱交換器と、
全開及び両方向流れの絞り制御をできる二つの第一及び
第二の絞り装置とを設け、これら第一利用側熱交換器、
第一絞り装置、第二利用側熱交換器、第二絞り装置を順
次接続して第二利用側熱交換器が二つの絞り装置の間に
なるサイクル構成にしたことを特徴とする空気調和機。 ２、請求項１において、前記第二利用側熱交換器と前記
第二絞り装置との間に気液分離器を設けると共に、該気
液分離器と前記圧縮機の吸込側とをバルブ及び絞り装置
を介して接続したサイクル構成にしたことを特徴とする
空気調和機。 ３、請求項１において、前記第一利用側熱交換器と前記
第一絞り装置との間に気液分離機を設けると共に、該気
液分離機と圧縮機の吸込側とをバルブ及び絞り装置を介
して接続したサイクル構成にしたことを特徴とする空気
調和機。 ４、請求項１〜３のいずれかにおいて、前記第一絞り装
置と前記第二絞り装置の間に冷媒と第二媒体との熱交換
を行う中間熱交換器を設けると共に、前記第二利用側熱
交換器に該第二媒体を循環させるサイクル構成にしたこ
とを特徴とする空気調和機。 ５、圧縮機、利用側熱交換器、絞り装置、室外側熱交換
器及びこれらを流路切り換え弁を介して接続する配管を
備え、主に室内側に設ける二系統の第一及び第二の利用
側熱交換器と、全開及び両方向流れの絞り制御をできる
二つの第一及び第二の絞り装置とを設け、これら第一利
用側熱交換器、第一絞り装置、第二利用側熱交換器、第
二絞り装置を順次接続して第二利用側熱交換器が二つの
絞り装置の間になるサイクル構成にした空気調和機の運
転方法において、暖房運転の場合に、前記第一絞り装置
を全開、前記第二絞り装置を適当に絞ることにより、前
記第一利用側熱交換器に比べて前記第二利用側熱交換器
の温度が低くなるように制御して運転することを特徴と
する空気調和機の運転方法。 ６、圧縮機、利用側熱交換器、絞り装置、室外側熱交換
器及びこれらを流路切り換え弁を介して接続する配管を
備え、主に室内側に設ける二系統の第一及び第二の利用
側熱交換器と、全開及び両方向流れの絞り制御をできる
二つの第一及び第二の絞り装置とを設け、これら第一利
用側熱交換器、第一絞り装置、第二利用側熱交換器、第
二絞り装置を順次接続して第二利用側熱交換器が二つの
絞り装置の間になるサイクル構成にした空気調和機の運
転方法において、暖房運転の場合に、前記第一絞り装置
及び前記第二絞り装置をそれぞれ適当に絞ることにより
、前記第一利用側熱交換器が高温側放熱器、前記第二利
用側熱交換器が低温側放熱器となるように制御して運転
することを特徴とする空気調和機の運転方法。 ７、圧縮機、利用側熱交換器、絞り装置、室外側熱交換
器及びこれらを流路切り換え弁を介して接続する配管を
備え、主に室内側に設ける二系統の第一及び第二の利用
側熱交換器と、全開及び両方向流れの絞り制御をできる
二つの第一及び第二の絞り装置とを設け、これら第一利
用側熱交換器、第一絞り装置、第二利用側熱交換器、第
二絞り装置を順次接続して第二利用側熱交換器が二つの
絞り装置の間になるサイクル構成にした空気調和機の運
転方法において、冷房運転の場合に、前記第二絞り装置
及び前記第一絞り装置をそれぞれ適当に絞ることにより
、前記第二利用側熱交換器が高温側吸熱器、前記第一利
用側熱交換器が低温側吸熱器となるように制御して運転
することを特徴とする空気調和機の運転方法。 ８、圧縮機、利用側熱交換器、絞り装置、室外側熱交換
器及びこれらを流路切り換え弁を介して接続する配管を
備え、主に室内側に設ける二系統の第一及び第二の利用
側熱交換器と、全開及び両方向流れの絞り制御をできる
二つの第一及び第二の絞り装置とを設け、これら第一利
用側熱交換器、第一絞り装置、第二利用側熱交換器、第
二絞り装置を順次接続して第二利用側熱交換器が二つの
絞り装置の間になるサイクル構成にした空気調和機の運
転方法において、冷房運転の場合に、前記第二絞り装置
を全開、前記第一絞り装置を適当に絞ることにより、前
記第二利用側熱交換器が放熱器、前記第一利用側熱交換
器が吸熱器となるように制御して運転することを特徴と
する空気調和機の運転方法。 ９、圧縮機、利用側熱交換器、絞り装置、室外側熱交換
器及びこれらを流路切り換え弁を介して接続する配管を
備え、主に室内側に設ける二系統の第一及び第二の利用
側熱交換器と、全開及び両方向流れの絞り制御をできる
二つの第一及び第二の絞り装置とを設け、これら第一利
用側熱交換器、第一絞り装置、第二利用側熱交換器、第
二絞り装置を順次接続して第二利用側熱交換器が二つの
絞り装置の間になるサイクル構成にした空気調和機の運
転方法において、除湿運転の場合に、前記第二絞り装置
を全開、前記第一絞り装置を適当に絞ることにより、前
記第二利用側熱交換器が放熱器、前記第一利用側熱交換
器が吸熱器となるように制御して運転することを特徴と
する空気調和機の運転方法。 １０、請求項１〜４のいずれかにおいて、前記第一利用
側熱交換器を気流空調ユニット、前記第二利用側熱交換
器を輻射空調ユニットとしたことを特徴とする空気調和
器。 １１、請求項１〜４のいずれかにおいて、前記第一絞り
装置及び第二絞り装置を、全開及び両方向流れの絞り制
御が可能な多機能膨張弁としたことを特徴とする空気調
和器。 １２、請求項１〜４のいずれかにおいて、前記第一絞り
装置及び前記第二絞り装置を、キャピラリチューブとバ
ルブを並列で対になるように設けた構成にしたことを特
徴とする空気調和器。 １３、請求項１〜４のいずれかにおいて、前記第一絞り
装置及び前記第二絞り装置を、膨張弁とバルブを並列で
対になるように設けた構成にしたことを特徴とする空気
調和機。 １４、室内側に設けてそれぞれ異なる空調方式に用いる
二系統の第一及び第二の利用側熱交換器を、全開及び両
方向流れの絞り状態を切り換えて前記各熱交換器の温度
それぞれの空調方式に適した温度レベルに制御できる二
つの第一及び第二の絞り装置により、これら二つの空調
方式を複合使用することにより、暖房、冷房及び除湿の
各運転において、快適性と省エネルギを同時に実現する
ようにしたことを特徴とする空気調和機の運転方法。[Claims] 1. A heat pump type air conditioner equipped with a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping connecting these via a flow path switching valve. a first and second user-side heat exchanger of two systems installed on the indoor side;
Two first and second throttling devices capable of fully open and bidirectional flow throttling control are provided, and these first use side heat exchangers,
An air conditioner characterized in that a first throttling device, a second usage-side heat exchanger, and a second throttling device are sequentially connected to form a cycle configuration in which the second usage-side heat exchanger is located between the two throttling devices. . 2. In claim 1, a gas-liquid separator is provided between the second usage-side heat exchanger and the second throttle device, and the gas-liquid separator and the suction side of the compressor are connected by a valve and a throttle. An air conditioner characterized by having a cycle configuration connected through a device. 3. In claim 1, a gas-liquid separator is provided between the first usage-side heat exchanger and the first throttle device, and a valve and a throttle device are provided between the gas-liquid separator and the suction side of the compressor. An air conditioner characterized by having a cycle configuration connected through. 4. In any one of claims 1 to 3, an intermediate heat exchanger for exchanging heat between the refrigerant and the second medium is provided between the first expansion device and the second expansion device, and the second usage side An air conditioner characterized by having a cycle configuration in which the second medium is circulated through a heat exchanger. 5.Equipped with a compressor, a user side heat exchanger, a throttle device, an outdoor heat exchanger, and piping that connects these via a flow path switching valve. A user-side heat exchanger and two first and second throttle devices capable of full-open and bidirectional flow throttle control are provided, and these first user-side heat exchanger, first throttle device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which the cycle configuration is such that a heat exchanger and a second throttling device are sequentially connected so that the second usage-side heat exchanger is located between the two throttling devices, in the case of heating operation, the first throttling device is fully opened and the second throttling device is appropriately throttled, thereby controlling and operating the second usage-side heat exchanger so that the temperature of the second usage-side heat exchanger is lower than that of the first usage-side heat exchanger. How to operate an air conditioner. 6.Equipped with a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping that connects these via a flow path switching valve. A user-side heat exchanger and two first and second throttle devices capable of full-open and bidirectional flow throttle control are provided, and these first user-side heat exchanger, first throttle device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which the cycle configuration is such that a heat exchanger and a second throttling device are sequentially connected so that the second usage-side heat exchanger is located between the two throttling devices, in the case of heating operation, the first throttling device By appropriately throttling the second throttling device, the first usage-side heat exchanger is controlled and operated so as to function as a high-temperature side radiator, and the second usage-side heat exchanger functions as a low-temperature side radiator. A method of operating an air conditioner characterized by the following. 7.Equipped with a compressor, a user side heat exchanger, a throttle device, an outdoor heat exchanger, and piping that connects these via a flow path switching valve. A user-side heat exchanger and two first and second throttle devices capable of full-open and bidirectional flow throttle control are provided, and these first user-side heat exchanger, first throttle device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which the cycle configuration is such that the second use side heat exchanger is connected between the two expansion devices and the second expansion device in sequence, in the case of cooling operation, the second expansion device By appropriately throttling the first throttling device, the second usage-side heat exchanger is controlled and operated so as to become a high-temperature side heat absorber, and the first usage-side heat exchanger becomes a low-temperature side heat absorber. A method of operating an air conditioner characterized by the following. 8.Equipped with a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping that connects these via a flow path switching valve. A user-side heat exchanger and two first and second throttle devices capable of full-open and bidirectional flow throttle control are provided, and these first user-side heat exchanger, first throttle device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which the cycle configuration is such that the second use side heat exchanger is connected between the two expansion devices and the second expansion device in sequence, in the case of cooling operation, the second expansion device is fully opened and the first throttling device is appropriately throttled, thereby controlling and operating the second usage-side heat exchanger as a radiator and the first usage-side heat exchanger as a heat absorber. How to operate an air conditioner. 9.Equipped with a compressor, a user-side heat exchanger, a throttle device, an outdoor-side heat exchanger, and piping that connects these via a flow path switching valve. A user-side heat exchanger and two first and second throttle devices capable of full-open and bidirectional flow throttle control are provided, and these first user-side heat exchanger, first throttle device, and second user-side heat exchanger are provided. In the method of operating an air conditioner in which the cycle configuration is such that a heat exchanger and a second throttling device are sequentially connected so that the second usage-side heat exchanger is located between the two throttling devices, in the case of dehumidification operation, the second throttling device is fully opened and the first throttling device is appropriately throttled, thereby controlling and operating the second usage-side heat exchanger as a radiator and the first usage-side heat exchanger as a heat absorber. How to operate an air conditioner. 10. The air conditioner according to claim 1, wherein the first usage-side heat exchanger is an airflow air conditioning unit, and the second usage-side heat exchanger is a radiant air conditioning unit. 11. The air conditioner according to any one of claims 1 to 4, wherein the first throttle device and the second throttle device are multifunctional expansion valves capable of throttle control of full opening and bidirectional flow. 12. The air conditioner according to any one of claims 1 to 4, wherein the first throttle device and the second throttle device have a configuration in which a capillary tube and a valve are provided in parallel as a pair. . 13. The air conditioner according to any one of claims 1 to 4, wherein the first throttle device and the second throttle device include an expansion valve and a valve arranged in parallel as a pair. . 14. Two systems of first and second user-side heat exchangers installed on the indoor side and used for different air conditioning methods are switched between fully open and bidirectional flow throttling states to create an air conditioning method for each temperature of each heat exchanger. By using two first and second diaphragm devices that can control the temperature at an appropriate temperature level, combined use of these two air conditioning systems achieves comfort and energy savings in heating, cooling, and dehumidification operations at the same time. A method of operating an air conditioner, characterized in that:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32187990A JP2926268B2 (en) | 1990-11-26 | 1990-11-26 | Air conditioner and method of operating the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32187990A JP2926268B2 (en) | 1990-11-26 | 1990-11-26 | Air conditioner and method of operating the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04190052A true JPH04190052A (en) | 1992-07-08 |
| JP2926268B2 JP2926268B2 (en) | 1999-07-28 |
Family
ID=18137426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32187990A Expired - Lifetime JP2926268B2 (en) | 1990-11-26 | 1990-11-26 | Air conditioner and method of operating the same |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2926268B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003050060A (en) * | 2001-08-03 | 2003-02-21 | Mitsubishi Electric Corp | Air conditioner refrigerant circuit |
| JP2006349270A (en) * | 2005-06-16 | 2006-12-28 | Ishimoto Kenchiku Jimusho:Kk | Water heat source heat pump type radiation panel air conditioner |
| JPWO2006051617A1 (en) * | 2004-11-12 | 2008-05-29 | 株式会社前川製作所 | Heat pump using CO2 as a refrigerant and operating method thereof |
| JP2010032105A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
| JP2010032104A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
-
1990
- 1990-11-26 JP JP32187990A patent/JP2926268B2/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003050060A (en) * | 2001-08-03 | 2003-02-21 | Mitsubishi Electric Corp | Air conditioner refrigerant circuit |
| JPWO2006051617A1 (en) * | 2004-11-12 | 2008-05-29 | 株式会社前川製作所 | Heat pump using CO2 as a refrigerant and operating method thereof |
| JP4827191B2 (en) * | 2004-11-12 | 2011-11-30 | 株式会社前川製作所 | Operation method of heat pump using CO2 as refrigerant |
| JP2006349270A (en) * | 2005-06-16 | 2006-12-28 | Ishimoto Kenchiku Jimusho:Kk | Water heat source heat pump type radiation panel air conditioner |
| JP2010032105A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
| JP2010032104A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2926268B2 (en) | 1999-07-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2012000323A1 (en) | Multi-split air conditioner capable of refrigerating and heating simultaneously | |
| JP4556453B2 (en) | Heat pump hot water supply air conditioner | |
| JP6120943B2 (en) | Air conditioner | |
| JP3884591B2 (en) | Air conditioner | |
| JP3283706B2 (en) | Air conditioner | |
| JP2006029598A (en) | Air conditioning apparatus and control method thereof | |
| JP3969381B2 (en) | Multi-room air conditioner | |
| JPH04332350A (en) | Air conditioner and its operating method | |
| JP2001317831A (en) | Air conditioner | |
| JPH04190052A (en) | Air conditioner and its operating method | |
| JPH01247966A (en) | Air conditioner | |
| JP2022052743A (en) | Multi-air conditioner for heating, cooling and ventilation | |
| JP2006194525A (en) | Multi-room air conditioner | |
| JP2005283058A (en) | Reheat dehumidification type air conditioner | |
| JPS6211263B2 (en) | ||
| CN112797516B (en) | air conditioning system | |
| JP3885063B2 (en) | Air conditioner | |
| JP3677887B2 (en) | Air conditioner | |
| JPH0942706A (en) | Air conditioner | |
| JP3598520B2 (en) | Air conditioner | |
| JPH0451319Y2 (en) | ||
| KR100974179B1 (en) | Dehumidification Air Conditioner and Dehumidification Method | |
| JPS6349669A (en) | Air conditioner | |
| JP2822769B2 (en) | Heat pump system | |
| JPH0894207A (en) | Air conditioner |