JP3216560B2 - Heat source device - Google Patents
Heat source deviceInfo
- Publication number
- JP3216560B2 JP3216560B2 JP04184297A JP4184297A JP3216560B2 JP 3216560 B2 JP3216560 B2 JP 3216560B2 JP 04184297 A JP04184297 A JP 04184297A JP 4184297 A JP4184297 A JP 4184297A JP 3216560 B2 JP3216560 B2 JP 3216560B2
- Authority
- JP
- Japan
- Prior art keywords
- heat
- refrigerant
- heat storage
- air conditioner
- outdoor unit
- 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.)
- Expired - Fee Related
Links
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】冷凍サイクルを利用した空気
調和機の能力向上に関する。[0001] 1. Field of the Invention [0002] The present invention relates to improving the performance of an air conditioner using a refrigeration cycle.
【０００２】[0002]
【従来の技術】空気調和機の能力向上や夏期の電力ピー
クカットの方法として、液冷媒を冷却する方法がある。
例えば、特開平1−174866 号公報では空気調和機に蓄熱
槽を設け、蓄熱槽内の蓄熱媒体に冷熱を付与する冷凍サ
イクル回路と、液冷媒を冷却するための熱交換器を設
け、空調していない時に、蓄熱槽の蓄熱媒体に蓄冷して
おき、空調するときに液冷媒を蓄熱槽を通して冷却し、
能力向上や電力ピークカットしている。また、他の例
は、特開昭63−204076号公報では、ある室外機から冷却
回路を分岐し、その冷却回路を他の室外機の液冷媒側に
設けて熱交換器に導き、他の室外機の液冷媒を冷却でき
るようにし、最大能力以上の能力を要求されている室外
機の液冷媒を供給能力が余っている他の室外機で冷却
し、能力補償できるようにしている。2. Description of the Related Art As a method for improving the capacity of an air conditioner and for cutting off a power peak in summer, there is a method of cooling a liquid refrigerant.
For example, in JP-A-1-174866, an air conditioner is provided with a heat storage tank, a refrigeration cycle circuit for applying cold heat to a heat storage medium in the heat storage tank, and a heat exchanger for cooling the liquid refrigerant are provided. When not, cool the heat storage medium in the heat storage tank, cool the liquid refrigerant through the heat storage tank when air conditioning,
Capacities have been improved and power peaks have been cut. Another example is disclosed in JP-A-63-204076, in which a cooling circuit is branched from a certain outdoor unit, and the cooling circuit is provided on a liquid refrigerant side of another outdoor unit and guided to a heat exchanger. The liquid refrigerant of the outdoor unit can be cooled, and the liquid refrigerant of the outdoor unit, which is required to have a capacity equal to or greater than the maximum capacity, can be cooled by another outdoor unit having a surplus supply capacity so that the capacity can be compensated.
【０００３】[0003]
【発明が解決しようとする課題】上記のような、ある室
外機の能力を他の室外機で補償する場合、他の室外機の
供給能力が余っていないときは補償できない欠点があ
る。When the capacity of one outdoor unit is compensated for by another outdoor unit as described above, there is a disadvantage that the compensation cannot be made when the supply capacity of another outdoor unit is insufficient.
【０００４】本発明の目的は、複数の空調機の一部だけ
が最大能力以上の能力が要求されている場合でも、ま
た、全ての空調機が最大能力以上の能力が要求されてい
る場合でも能力補償できる冷熱源装置を提供することに
ある。[0004] The object of the present invention is to be applied to a case where only a part of a plurality of air conditioners is required to have a capacity greater than the maximum capacity, and a case where all the air conditioners are required to have a capacity greater than the maximum capacity. An object of the present invention is to provide a cold heat source device capable of compensating for the capacity.
【０００５】また、空調機に蓄熱槽を備えたものでは、
蓄熱を空調機が稼働していないときに行うため、その蓄
熱がなくなったとき能力向上の効果が得られなくなる。
さらに、室外機の数が多い場合、蓄熱槽の数も多くな
り、広いスペースが必要となる。 本発明の他の目的は
空調機稼働中でも蓄熱できる空気調和機を提供すること
と、蓄熱槽の数を減少し省スペースを図ることにある。In an air conditioner having a heat storage tank,
Since the heat storage is performed when the air conditioner is not operating, the effect of capacity improvement cannot be obtained when the heat storage is lost.
Furthermore, when the number of outdoor units is large, the number of heat storage tanks is also large, and a large space is required. It is another object of the present invention to provide an air conditioner that can store heat even while an air conditioner is operating, and to reduce the number of heat storage tanks to save space.
【０００６】[0006]
【０００７】[0007]
【０００８】[0008]
【課題を解決するための手段】上記目的を解決するたMeans for Solving the Problems To solve the above-mentioned object,
め、本発明は室外機と複数の室内機を有する空気調和機The present invention relates to an air conditioner having an outdoor unit and a plurality of indoor units.
に用いられ、蓄熱槽、蓄熱用熱交換器、蓄熱媒体、ポンHeat storage tank, heat exchanger for heat storage, heat storage medium, pump
プ及び室外機からの冷媒と熱交換するための熱交換器をAnd a heat exchanger for exchanging heat with refrigerant from the outdoor unit.
有した熱源装置であって、蓄熱媒体は、室外機で液となThe heat storage medium is converted into a liquid in the outdoor unit.
った冷媒が減圧され蓄熱用熱交換器へ入ることにより冷Refrigerant is decompressed and enters the heat exchanger for heat storage,
却され、冷却された蓄熱媒体はポンプより熱交換器へ送The cooled heat storage medium is sent from the pump to the heat exchanger.
り出され室外機からの液冷媒と熱交換されるものであAnd heat exchange with the liquid refrigerant from the outdoor unit.
る。You.
【０００９】これにより、室外機で液となった冷媒によ
り蓄熱媒体が冷却され、ポンプにより送り出されて室外
機からの液冷媒と熱交換されるので、能力向上が図られ
ると共に、熱源装置は冷凍サイクルを省略でき、コスト
を低減できる。 [0009] Thus, the refrigerant liquefied in the outdoor unit is
The heat storage medium is cooled and pumped out to
Heat exchange with liquid refrigerant from the machine,
In addition, the heat source device can omit the refrigeration cycle,
Can be reduced.
【００１０】[0010]
【００１１】空調機の液配管内の液冷媒と冷熱源装置か
らの冷熱源とを液配管に設置した熱交換器で熱交換する
ことにより、次のような働きをする。空調機が冷房運転
のとき、冷熱源装置から液冷媒を冷却するような冷熱源
を供給することにより、液冷媒の過冷却度が増え、冷媒
の膨張弁前の比エンタルピが小さくなり、冷媒の蒸発潜
熱が増え、空調機の冷房能力が増す。また、暖房運転の
ときは、冷熱源装置から液冷媒を加熱するような冷熱源
を供給することにより、液冷媒の過冷却度が減少、又
は、かわき度が増加し冷媒の膨張弁前の比エンタルピが
大きくなり、蒸発器出口の冷媒過熱度が増加する。ここ
で、膨張弁は蒸発器出口の冷媒過熱度が所定値となるよ
うに開くため蒸発圧力が増加する。これによって、圧縮
機吸入冷媒の比容積が小さくなり、冷媒循環量が増加す
る。さらに、吸入圧力が上昇することによって、吐出圧
力，凝縮圧力も上昇し、暖房能力が増加する。The following operation is performed by exchanging heat between the liquid refrigerant in the liquid pipe of the air conditioner and the cold heat source from the cold heat source device by the heat exchanger installed in the liquid pipe. When the air conditioner is in cooling operation, by supplying a cold heat source for cooling the liquid refrigerant from the cold heat source device, the degree of supercooling of the liquid refrigerant is increased, the specific enthalpy of the refrigerant before the expansion valve is reduced, and the refrigerant is cooled. The latent heat of evaporation increases, and the cooling capacity of the air conditioner increases. In the heating operation, by supplying a cold heat source for heating the liquid refrigerant from the cold heat source device, the degree of supercooling of the liquid refrigerant is reduced or the dryness is increased and the ratio of the refrigerant before the expansion valve is increased. The enthalpy increases, and the refrigerant superheat at the evaporator outlet increases. Here, since the expansion valve is opened so that the degree of superheat of the refrigerant at the evaporator outlet becomes a predetermined value, the evaporation pressure increases. As a result, the specific volume of the refrigerant drawn into the compressor is reduced, and the refrigerant circulation amount is increased. Further, as the suction pressure increases, the discharge pressure and the condensing pressure also increase, and the heating capacity increases.
【００１２】蓄熱槽を冷熱源装置に備え、蓄冷又は蓄熱
した蓄熱媒体を各空調機の液配管に設けた熱交換器に供
給することによって、上記に示した空調機の能力の向上
が実現できるとともに、各空調機に蓄熱槽を備えなくて
よいので、蓄熱槽の数が減り省スペースとなる。また、
蓄熱槽の蓄冷熱を冷熱源装置内の冷却加熱手段、又は、
空調機から分岐した冷凍サイクルによって行え、空調機
が稼働中でも蓄冷熱が可能となる。By providing a heat storage tank in a cold heat source device and supplying a heat storage medium having stored or cooled heat to a heat exchanger provided in a liquid pipe of each air conditioner, the above-described improvement in the performance of the air conditioner can be realized. In addition, since it is not necessary to provide a heat storage tank in each air conditioner, the number of heat storage tanks is reduced, and space is saved. Also,
Cooling and heating means in the cold heat source device, or,
It can be performed by the refrigeration cycle branched from the air conditioner, and it becomes possible to store cold heat even while the air conditioner is operating.
【００１３】[0013]
【発明の実施の形態】本発明の一実施例を図１ないし図
３に示す。図１では、室外機１と室内機３とが液管７と
ガス管９で結合された空調機と、室外機２と三台の室内
機４，５，６とが液管８とガス管１０で結合された空調
機の二つの空調機が示されている。室外機１は圧縮機１
１，四方弁１２，室外熱交換器１３，制御弁１４，室外
ファン１５で構成されている。室内機３は制御弁１６，
室内熱交換器１７，室内ファン１８で構成されている。
室外機２及び室内機４，５，６は前記室外機１及び室内
機３と同様の構成である。二つの空調機のそれぞれの液
管には熱交換器２１，２２が取りつけられている。熱交
換器２１，２２には、液管７，９の他にそれぞれ制御弁
２３，２４を介した配管２６と配管２５が接続されてい
る。配管２５と配管２６は冷熱源装置２０に接続されて
いる。DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention is shown in FIGS. In FIG. 1, an air conditioner in which an outdoor unit 1 and an indoor unit 3 are connected by a liquid pipe 7 and a gas pipe 9, and an outdoor unit 2 and three indoor units 4, 5, and 6 are a liquid pipe 8 and a gas pipe. Two air conditioners of the air conditioner connected at 10 are shown. The outdoor unit 1 is a compressor 1
1, a four-way valve 12, an outdoor heat exchanger 13, a control valve 14, and an outdoor fan 15. The indoor unit 3 has a control valve 16,
It comprises an indoor heat exchanger 17 and an indoor fan 18.
The outdoor unit 2 and the indoor units 4, 5, and 6 have the same configuration as the outdoor unit 1 and the indoor unit 3. Heat exchangers 21 and 22 are attached to the respective liquid tubes of the two air conditioners. The heat exchangers 21 and 22 are connected to pipes 26 and 25 via control valves 23 and 24, respectively, in addition to the liquid pipes 7 and 9. The pipe 25 and the pipe 26 are connected to the cold heat source device 20.
【００１４】次に、動作について説明する。空調機の冷
房運転時、冷媒は実線矢印の向きに流れる。圧縮機１１
から吐出された高圧ガス冷媒は四方弁１２を通って室外
熱交換器１３へ流れ、室外ファン１５によって室外空気
と熱交換され凝縮し液冷媒となる。液冷媒は開度を大き
くした制御弁１４を通って液管７を流れ室内機３へ送ら
れる。室内機３では、液冷媒は開度を小さくした制御弁
１６で減圧され、室内熱交換器１７に入り、室内ファン
１８によって室内空気と熱交換される。このとき、室内
空気は冷却され、冷媒は蒸発し低圧ガス冷媒となってガ
ス管９を通って室外機１へ戻る。室外機１へ戻った低圧
ガス冷媒は四方弁１２を通って圧縮機１１へ吸入され
る。この冷媒状態をモリエル線図上に示すと図２の実線
のようになる。なお、室外機２と３台の室内機４，５，
６の空調機の冷房運転の動作も前記と同様である。この
ような冷房運転のとき、冷熱源装置２０から空調機の液
冷媒を冷却するような冷熱源を熱交換２１，２２へ供給
すると、冷熱源と液冷媒が熱交換し、液冷媒の過冷却度
が増加し、図２のモリエル線図上の破線のようになる。
すなわち、空調機の液冷媒の過冷却度が増加することに
よって、液冷媒の比エンタルピが小さくなり、冷媒蒸発
潜熱が増加し、冷房能力も増加する。暖房運転時、冷媒
は破線矢印のように流れる。圧縮機１１から吐出された
高圧ガス冷媒は四方弁１２を通ってガス管９へ流れ室内
機３へ入る。室内機３では室内熱交換器１７で室内ファ
ン１８によって室内空気と熱交換され、室内空気は暖め
られ、冷媒は凝縮して液冷媒となる。液冷媒は開度を大
きくした制御弁１６を通って、液管７へ流れ室外機１へ
送られる。室外機１では、液冷媒は開度を小さくした制
御弁１４で減圧され、室外熱交換器１３へ入り、室外フ
ァン１５によって、室外空気と熱交換され、冷媒は蒸発
して低圧ガス冷媒となって、四方弁１２を通って圧縮機
１１へ吸入される。室外機２と三台の室内機４，５，６
の空調機の暖房運転の動作も前述同様である。暖房運転
時の冷媒状態をモリエル線図上に示すと図３の実線のよ
うになる。このような暖房運転のとき、冷熱源装置２０
から空調機の液冷媒を加熱するような冷熱源を熱交換器
２１，２２へ供給すると、冷熱源と液冷媒が熱交換し、
液冷媒の過冷却度が減少、又は、かわき度が増加し、図
３のモリエル線図上の破線のようになる。すなわち、空
調機の液冷媒の過冷却度が減少、又は、かわき度が増加
することによって、液冷媒の比エンタルピが小さくな
り、冷媒蒸発潜熱が減少し、室外熱交換器１３出口の過
熱度、又は、圧縮機吐出ガス過熱度が大きくなるため、
制御弁１４の開度を大きくして過熱度が元の値になるよ
うにする。これによって、蒸発圧力が上昇し、圧縮機吸
入冷媒の比容積が小さくなり、冷媒循環量が増加する。
これに伴って、吐出圧力が上昇する。これによって、暖
房能力が増加する。Next, the operation will be described. During the cooling operation of the air conditioner, the refrigerant flows in the direction of the solid line arrow. Compressor 11
The high-pressure gas refrigerant discharged from the air flows through the four-way valve 12 to the outdoor heat exchanger 13, where it is heat-exchanged with outdoor air by the outdoor fan 15 and condensed to become a liquid refrigerant. The liquid refrigerant flows through the liquid pipe 7 through the control valve 14 whose opening degree is increased, and is sent to the indoor unit 3. In the indoor unit 3, the liquid refrigerant is depressurized by the control valve 16 whose opening degree is reduced, enters the indoor heat exchanger 17, and is exchanged with indoor air by the indoor fan 18. At this time, the indoor air is cooled, and the refrigerant evaporates to become a low-pressure gas refrigerant and returns to the outdoor unit 1 through the gas pipe 9. The low-pressure gas refrigerant returned to the outdoor unit 1 is sucked into the compressor 11 through the four-way valve 12. The state of the refrigerant on the Mollier diagram is as shown by the solid line in FIG. The outdoor unit 2 and the three indoor units 4, 5,
The operation of the cooling operation of the air conditioner of No. 6 is the same as described above. In such a cooling operation, when a cold heat source for cooling the liquid refrigerant of the air conditioner is supplied from the cold heat source device 20 to the heat exchanges 21 and 22, the heat exchange between the cold heat source and the liquid refrigerant causes the liquid refrigerant to be supercooled. The degree increases, and becomes a broken line on the Mollier diagram in FIG.
That is, as the degree of subcooling of the liquid refrigerant of the air conditioner increases, the specific enthalpy of the liquid refrigerant decreases, the latent heat of refrigerant evaporation increases, and the cooling capacity also increases. During the heating operation, the refrigerant flows as indicated by the dashed arrows. The high-pressure gas refrigerant discharged from the compressor 11 flows through the four-way valve 12 to the gas pipe 9 and enters the indoor unit 3. In the indoor unit 3, heat is exchanged with the indoor air by the indoor fan 18 in the indoor heat exchanger 17, the indoor air is warmed, and the refrigerant is condensed into a liquid refrigerant. The liquid refrigerant flows to the liquid pipe 7 through the control valve 16 whose opening degree is increased, and is sent to the outdoor unit 1. In the outdoor unit 1, the liquid refrigerant is depressurized by the control valve 14 having a reduced opening, enters the outdoor heat exchanger 13, and is exchanged with outdoor air by the outdoor fan 15, and the refrigerant evaporates to a low-pressure gas refrigerant. Then, it is sucked into the compressor 11 through the four-way valve 12. Outdoor unit 2 and three indoor units 4, 5, 6
The operation of the heating operation of the air conditioner is the same as described above. The state of the refrigerant during the heating operation is shown on the Mollier diagram as a solid line in FIG. In such a heating operation, the cold heat source device 20
When a cold source that heats the liquid refrigerant of the air conditioner is supplied to the heat exchangers 21 and 22 from above, the cold heat source and the liquid refrigerant exchange heat,
The degree of supercooling of the liquid refrigerant decreases or the degree of dryness increases, as shown by a broken line on the Mollier diagram in FIG. That is, the degree of supercooling of the liquid refrigerant of the air conditioner is reduced, or, by increasing the degree of dryness, the specific enthalpy of the liquid refrigerant is reduced, the latent heat of refrigerant evaporation is reduced, and the degree of superheat at the outlet of the outdoor heat exchanger 13 is reduced. Or, because the degree of superheat of the compressor discharge gas increases,
The degree of opening of the control valve 14 is increased so that the degree of superheat becomes the original value. As a result, the evaporating pressure increases, the specific volume of the compressor suction refrigerant decreases, and the refrigerant circulation amount increases.
Along with this, the discharge pressure increases. This increases the heating capacity.
【００１５】次に、冷熱源装置２０の一実施例を図４に
示す。図４において、冷熱源装置２０は圧縮機３０，四
方弁３１，熱交換器３２，制御弁３３，ファン３４で構
成されている。空調機の液冷媒を冷却する場合は、四方
弁３１を実線のようにしておく。圧縮機３０から吐出さ
れた高圧ガス冷媒は四方弁３１を通って、熱交換器３２
へ入り、ファン３４によって室外空気と熱交換され、冷
媒は凝縮して液冷媒となり、開度を大きくした制御弁３
３を通って配管２６へ流れる。液冷媒は配管２６から開
度を小さくした制御弁２３，２４を通って減圧され、熱
交換器２１，２２へ入り、空調機の液冷媒と熱交換され
る。このとき、空調機の液冷媒は冷却され過冷却度が大
きくなる。冷熱源装置２０から送られた冷媒は蒸発して
低圧ガス冷媒となり、配管２５を通って冷熱源装置２０
へ戻り、四方弁３１を通って圧縮機３０へ吸入される。
空調機の液冷媒を過熱する場合は四方弁３１を破線のよ
うに切換えておく。圧縮機３０から吐出された高圧ガス
冷媒は四方弁３１を通って配管２５へ流れ、熱交換器２
１，２２へ入り空調機の液冷媒と熱交換される。このと
き空調機の液冷媒は加熱され過冷却度が小さくなる。又
は、かわき度が大きくなる。冷熱源装置２０から送られ
た冷媒は凝縮し液冷媒となる。液冷媒は開度を大きくし
た制御弁２３，２４を通って配管２６へ流れ冷熱源装置
２０へ戻る。冷熱源装置２０へ入った液冷媒は開度を小
さくした制御弁３３で減圧されて、熱交換器３２へ入
り、ファン３４によって室外空気と熱交換され、蒸発し
て低圧ガス冷媒となり四方弁３１を通って圧縮機３０へ
吸入される。ここで、制御弁２３，２４の開度を調整す
ることによって、熱交換器２１，２２へ流れる冷熱源の
流量を調整することができる。Next, one embodiment of the cold heat source device 20 is shown in FIG. 4, the cold heat source device 20 includes a compressor 30, a four-way valve 31, a heat exchanger 32, a control valve 33, and a fan 34. When cooling the liquid refrigerant of the air conditioner, the four-way valve 31 is set as shown by the solid line. The high-pressure gas refrigerant discharged from the compressor 30 passes through the four-way valve 31 and passes through the heat exchanger 32.
The heat is exchanged with the outdoor air by the fan 34, and the refrigerant is condensed into a liquid refrigerant, and the control valve 3 having a large opening degree is formed.
3 to the pipe 26. The liquid refrigerant is depressurized from the pipe 26 through control valves 23 and 24 whose opening degrees are reduced, enters the heat exchangers 21 and 22, and exchanges heat with the liquid refrigerant of the air conditioner. At this time, the liquid refrigerant of the air conditioner is cooled, and the degree of supercooling increases. The refrigerant sent from the cold heat source device 20 evaporates into a low-pressure gas refrigerant, and passes through the pipe 25 to be cooled.
Then, it is sucked into the compressor 30 through the four-way valve 31.
When the liquid refrigerant of the air conditioner is overheated, the four-way valve 31 is switched as shown by a broken line. The high-pressure gas refrigerant discharged from the compressor 30 flows through the four-way valve 31 to the pipe 25, and the heat exchanger 2
Steps 1 and 22 are performed to exchange heat with the liquid refrigerant of the air conditioner. At this time, the liquid refrigerant of the air conditioner is heated and the degree of supercooling is reduced. Or, the degree of dryness increases. The refrigerant sent from the cold heat source device 20 condenses into liquid refrigerant. The liquid refrigerant flows to the pipe 26 through the control valves 23 and 24 whose openings are increased, and returns to the cold heat source device 20. The liquid refrigerant that has entered the cold heat source device 20 is decompressed by the control valve 33 having a reduced opening, enters the heat exchanger 32, is heat-exchanged with outdoor air by the fan 34, evaporates to a low-pressure gas refrigerant, and becomes the four-way valve 31. Through the compressor 30. Here, by adjusting the opening of the control valves 23 and 24, the flow rate of the cold heat source flowing to the heat exchangers 21 and 22 can be adjusted.
【００１６】冷熱源装置２０の他の実施例を図５に示
す。図５において、冷熱源装置２０は圧縮機３０，四方
弁３１，熱交換器３２，制御弁３３，ファン３４，蓄熱
用熱交換器３５,蓄熱槽４０,ポンプ４１で構成されてい
る。空調機の液冷媒を冷却、又は、過熱する場合は、蓄
熱槽４０内の蓄熱媒体を冷却、又は、過熱しておく。蓄
熱媒体はポンプ４１で配管２６へ送り出され、制御弁２
３を通って熱交換器２１で空調機の液冷媒と熱交換され
てから、配管２５を通って蓄熱槽へ戻る。次に、蓄熱媒
体の冷却過熱手段について説明する。蓄熱媒体を冷却す
る場合は四方弁３１を実線のように切換えておく。圧縮
機３０から吐出された高圧ガス冷媒は四方弁３１を通っ
て熱交換器３２で室外空気と熱交換され凝縮して液冷媒
となる。液冷媒は開度を小さくした制御弁３３で減圧さ
れて、蓄熱用熱交換器３５へ入り、蓄熱媒体と熱交換さ
れる。このとき、蓄熱媒体は冷却され、冷媒は蒸発して
低圧ガス冷媒となり、四方弁３１を通って圧縮機３０へ
吸入される。蓄熱媒体を過熱する場合は四方弁３１を破
線のように切換えておく。圧縮機３０から吐出された高
圧ガス冷媒は四方弁３１を通って、蓄熱用熱交換器３５
へ入り、蓄熱媒体を熱交換される。このとき、蓄熱媒体
は加熱され、冷媒は凝縮して液冷媒となる。液冷媒は開
度を小さくした制御弁３３で減圧されて熱交換器３２へ
入り、室外空気と熱交換され低圧ガス冷媒となって、四
方弁３１を通って圧縮機３０へ吸入される。本実施例に
よれば、空調負荷が最大容量以下の場合、空調機の能力
向上分だけ空調機の圧縮機の容量を減少することができ
るので、蓄熱媒体への蓄冷熱を夜間などの空調機が稼働
していないときに行うことにより、夏期の電力ピークカ
ットの効果が得られる。Another embodiment of the cold heat source device 20 is shown in FIG. In FIG. 5, the cold heat source device 20 includes a compressor 30, a four-way valve 31, a heat exchanger 32, a control valve 33, a fan 34, a heat storage heat exchanger 35, a heat storage tank 40, and a pump 41. When the liquid refrigerant of the air conditioner is cooled or overheated, the heat storage medium in the heat storage tank 40 is cooled or overheated. The heat storage medium is sent out to the pipe 26 by the pump 41 and the control valve 2
After passing through 3, the heat exchanger 21 exchanges heat with the liquid refrigerant of the air conditioner, and then returns to the heat storage tank through the pipe 25. Next, the cooling / heating means of the heat storage medium will be described. When cooling the heat storage medium, the four-way valve 31 is switched as shown by the solid line. The high-pressure gas refrigerant discharged from the compressor 30 passes through the four-way valve 31 and exchanges heat with outdoor air in the heat exchanger 32 to condense into a liquid refrigerant. The liquid refrigerant is depressurized by the control valve 33 whose opening degree is reduced, enters the heat storage heat exchanger 35, and exchanges heat with the heat storage medium. At this time, the heat storage medium is cooled, the refrigerant evaporates and becomes a low-pressure gas refrigerant, and is sucked into the compressor 30 through the four-way valve 31. When the heat storage medium is overheated, the four-way valve 31 is switched as shown by a broken line. The high-pressure gas refrigerant discharged from the compressor 30 passes through the four-way valve 31 and passes through the heat storage heat exchanger 35.
And the heat storage medium is exchanged heat. At this time, the heat storage medium is heated, and the refrigerant condenses into a liquid refrigerant. The liquid refrigerant is decompressed by the control valve 33 whose opening degree is reduced, enters the heat exchanger 32, exchanges heat with outdoor air, becomes a low-pressure gas refrigerant, and is sucked into the compressor 30 through the four-way valve 31. According to the present embodiment, when the air-conditioning load is equal to or less than the maximum capacity, the capacity of the compressor of the air conditioner can be reduced by an amount corresponding to the improvement in the capacity of the air conditioner. By performing this operation when the power supply is not operating, the effect of peak power cut in summer can be obtained.
【００１７】なお、図４及び図５の実施例の冷熱源装置
２０の冷媒は空調機の冷媒と同一のものであっても、異
なる種類のものでも良い。The refrigerant of the cold heat source device 20 in the embodiment of FIGS. 4 and 5 may be the same as the refrigerant of the air conditioner or may be of a different type.
【００１８】次に、本発明のさらに他の実施例を図６に
示す。図６では、蓄熱媒体の冷却過熱手段を空調機の冷
媒回路を分岐し、利用している。すなわち、空調機のガ
ス管９，液管７は分岐され、開閉弁５２，５３を介して
ガス管９′，液管７′へ接続され、また、空調機のガス
管１０，液管８も分岐され、開閉弁５４，５５を介して
ガス管９′，液管７′へ接続される。液管７′の他端は
制御弁５１を介して蓄熱用熱交換器３５へ接続される。
ガス管９′の他端は蓄熱用熱交換器３５の他端に接続さ
れる。室外機１を利用して蓄熱媒体を冷却、又は、加熱
する場合、開閉弁５２，５３を開き、開閉弁５４，５５
を閉じておく。蓄熱媒体を冷却する場合は、室外機１を
冷房運転状態にすることによって、液冷媒が液管７，開
閉弁５３，液管７′を通って制御弁５１へ送られる。制
御弁５１の開度は小さくなっており、液冷媒は減圧さ
れ、蓄熱用熱交換器３５へ入り、蓄熱媒体と熱交換され
る。このとき、蓄熱媒体は冷却され、冷媒は低圧ガス冷
媒となって、ガス管９′、開閉弁５２を通ってガス管９
へ入り室外機１へ戻る。蓄熱媒体を加熱する場合は、室
外機２を暖房運転状態にすることによって、高圧ガス冷
媒がガス管９，開閉弁５２，ガス管９′を通って蓄熱用
熱交換器３５へ入り、蓄熱媒体と熱交換される。このと
き、蓄熱媒体は加熱され、冷媒は凝縮し液冷媒となる。
液冷媒は開度を大きくした制御弁５１を通り、さらに、
液管７′，開閉弁５３，液配管７を通って室外機１へ戻
る。室外機２を利用して、蓄熱媒体を冷却、又は、加熱
する場合は、開閉弁５２，５３を閉じ、開閉弁５４，５
５を開き、室外機１と同様の動作をすれば良い。Next, still another embodiment of the present invention is shown in FIG. In FIG. 6, the cooling / heating means of the heat storage medium is used by branching the refrigerant circuit of the air conditioner. That is, the gas pipe 9 and the liquid pipe 7 of the air conditioner are branched and connected to the gas pipe 9 'and the liquid pipe 7' via the on-off valves 52 and 53, and the gas pipe 10 and the liquid pipe 8 of the air conditioner are also formed. It is branched and connected to the gas pipe 9 'and the liquid pipe 7' via the on-off valves 54 and 55. The other end of the liquid pipe 7 ′ is connected to a heat storage heat exchanger 35 via a control valve 51.
The other end of the gas pipe 9 ′ is connected to the other end of the heat storage heat exchanger 35. When cooling or heating the heat storage medium using the outdoor unit 1, the on-off valves 52 and 53 are opened, and the on-off valves 54 and 55 are opened.
Is closed. When cooling the heat storage medium, the outdoor unit 1 is set to the cooling operation state, whereby the liquid refrigerant is sent to the control valve 51 through the liquid pipe 7, the on-off valve 53, and the liquid pipe 7 '. The opening of the control valve 51 is small, and the liquid refrigerant is depressurized, enters the heat storage heat exchanger 35, and exchanges heat with the heat storage medium. At this time, the heat storage medium is cooled, and the refrigerant becomes a low-pressure gas refrigerant.
And return to the outdoor unit 1. When heating the heat storage medium, the outdoor unit 2 is set to the heating operation state, whereby the high-pressure gas refrigerant enters the heat storage heat exchanger 35 through the gas pipe 9, the on-off valve 52, and the gas pipe 9 ', and Heat exchange with. At this time, the heat storage medium is heated, and the refrigerant condenses to become a liquid refrigerant.
The liquid refrigerant passes through the control valve 51 whose opening degree is increased, and further,
The liquid returns to the outdoor unit 1 through the liquid pipe 7 ′, the on-off valve 53, and the liquid pipe 7. When cooling or heating the heat storage medium using the outdoor unit 2, the on-off valves 52 and 53 are closed, and the on-off valves 54 and 5 are closed.
5, the same operation as the outdoor unit 1 may be performed.
【００１９】[0019]
【００２０】[0020]
【発明の効果】 本発明によれば、 冷熱源装置に蓄熱槽を
備え、蓄冷熱を冷熱源装置で行うため、空調機が稼働中
でも蓄冷熱ができ、蓄冷熱量が減少して、能力向上効果
が低下することがない。 According to the present invention, a heat storage tank to the cold heat source device
Since the cold storage heat is provided by the cold heat source device, the cold storage heat is generated even while the air conditioner is operating, and the amount of the cold storage heat is reduced, so that the effect of improving the capacity is not reduced .
【００２１】さらに、蓄熱槽の蓄冷熱を空調機の冷媒回
路を利用することによって、冷熱源装置内の冷凍サイク
ルを省略できコストの効果がある。Further, the use of the refrigerant circuit of the air conditioner by utilizing the regenerative heat of the heat storage tank can omit the refrigeration cycle in the cold heat source device, which is cost effective.
【図１】本発明の一実施例を示すエアコンシステムの系
統図。FIG. 1 is a system diagram of an air conditioner system showing one embodiment of the present invention.
【図２】冷房運転時の効果を示すモリエル線図。FIG. 2 is a Mollier chart showing the effect during cooling operation.
【図３】暖房運転時の効果を示すモリエル線図。FIG. 3 is a Mollier chart showing an effect during a heating operation.
【図４】冷熱源装置の一実施例を示す系統図。FIG. 4 is a system diagram showing one embodiment of a cold heat source device.
【図５】冷熱源装置の他の実施例を示す系統図。FIG. 5 is a system diagram showing another embodiment of the cold heat source device.
【図６】本発明の他の実施例を示すエアコンシステムの
系統図。FIG. 6 is a system diagram of an air conditioner system showing another embodiment of the present invention.
１，２…室外機、３，４，５…室内機、７，８…液管、
１１，３０…圧縮機、１４，１６，２３，２４，３３，
５１…制御弁、２０…冷熱源装置、２１，２２…熱交換
器、３５…蓄熱用熱交換器、４０…蓄熱槽、４１…ポン
プ。1, 2, ... outdoor unit, 3, 4, 5 ... indoor unit, 7, 8 ... liquid pipe,
11, 30 ... compressor, 14, 16, 23, 24, 33,
51: control valve, 20: cold heat source device, 21, 22, heat exchanger, 35: heat exchanger for heat storage, 40: heat storage tank, 41: pump.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭63−279061（ＪＰ，Ａ) 特開 昭64−10062（ＪＰ，Ａ) 特開 昭57−19560（ＪＰ，Ａ) 実開 平３−93333（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 1/00 F25B 5/00 F25B 13/00 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-279061 (JP, A) JP-A-64-10062 (JP, A) JP-A-57-19560 (JP, A) 93333 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F25B 1/00 F25B 5/00 F25B 13/00
Claims (1)
機に用いられ、蓄熱槽、蓄熱用熱交換器、蓄熱媒体、ポ
ンプ及び前記室外機からの冷媒と熱交換するための熱交
換器を有した熱源装置であって、 前記蓄熱媒体は、前記室外機で液となった冷媒が減圧さ
れ前記蓄熱用熱交換器へ入ることにより冷却され、冷却
された蓄熱媒体は前記ポンプより前記熱交換器へ送り出
され前記室外機からの液冷媒と熱交換されることを特徴
とする熱源装置。1. A heat exchanger for use in an air conditioner having an outdoor unit and a plurality of indoor units, for exchanging heat with a heat storage tank, a heat storage heat exchanger, a heat storage medium, a pump, and a refrigerant from the outdoor unit. In the heat source device, the heat storage medium is cooled by cooling the refrigerant that has become a liquid in the outdoor unit and enters the heat storage heat exchanger, and the cooled heat storage medium is supplied from the pump to the heat storage medium. A heat source device, wherein the heat source device is sent to an exchanger and exchanges heat with liquid refrigerant from the outdoor unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04184297A JP3216560B2 (en) | 1997-02-26 | 1997-02-26 | Heat source device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04184297A JP3216560B2 (en) | 1997-02-26 | 1997-02-26 | Heat source device |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28754691A Division JP3213992B2 (en) | 1991-11-01 | 1991-11-01 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09250824A JPH09250824A (en) | 1997-09-22 |
| JP3216560B2 true JP3216560B2 (en) | 2001-10-09 |
Family
ID=12619521
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04184297A Expired - Fee Related JP3216560B2 (en) | 1997-02-26 | 1997-02-26 | Heat source device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3216560B2 (en) |
-
1997
- 1997-02-26 JP JP04184297A patent/JP3216560B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH09250824A (en) | 1997-09-22 |
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