JPH031056A - Heat pump type heat recovery apparatus - Google Patents
Heat pump type heat recovery apparatusInfo
- Publication number
- JPH031056A JPH031056A JP1132633A JP13263389A JPH031056A JP H031056 A JPH031056 A JP H031056A JP 1132633 A JP1132633 A JP 1132633A JP 13263389 A JP13263389 A JP 13263389A JP H031056 A JPH031056 A JP H031056A
- Authority
- JP
- Japan
- Prior art keywords
- heat
- heat recovery
- recovery device
- condenser
- supercooler
- 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
- 238000011084 recovery Methods 0.000 title claims abstract description 59
- 239000003507 refrigerant Substances 0.000 claims abstract description 26
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 18
- 239000007788 liquid Substances 0.000 claims description 12
- 239000006096 absorbing agent Substances 0.000 claims description 10
- 238000010521 absorption reaction Methods 0.000 claims description 7
- 239000007789 gas Substances 0.000 abstract description 11
- 230000000694 effects Effects 0.000 abstract description 6
- 239000002918 waste heat Substances 0.000 abstract description 6
- 238000001816 cooling Methods 0.000 abstract description 5
- 238000007865 diluting Methods 0.000 abstract description 3
- 238000005338 heat storage Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 abstract 1
- 238000005057 refrigeration Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000010797 grey water Substances 0.000 description 2
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Abstract
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明はヒートポンプ熱回収装置に関する。[Detailed description of the invention] [Industrial application field] The present invention relates to a heat pump heat recovery device.
圧縮機、凝縮器、蒸発器から成る冷凍サイクルにおいて
、凝縮器内の冷媒液を冷却液で飽和温度以下にすれば、
同じ所要動力において、冷凍能力を増加させる事は周知
である。In a refrigeration cycle consisting of a compressor, condenser, and evaporator, if the refrigerant liquid in the condenser is brought below the saturation temperature with cooling liquid,
It is well known that refrigeration capacity can be increased for the same power requirement.
従来の装置ではこの適冷を冷却水により行なっていた。In conventional equipment, this appropriate cooling was performed using cooling water.
なお、この値の装置として関連するものには例えば実開
昭４７−１６０５６号が挙げられる。A related device having this value is, for example, Utility Model Application No. 16056/1983.
上記従来技術は排熱の有効利用の点について配慮がされ
ていなかった。The above-mentioned conventional technology did not give consideration to the effective use of waste heat.
本発明の目的は冷凍機の排熱を有効に利用して、同じ所
要動力にて、冷凍能力を増加させ、省エネルギーを図る
ヒートポンプ熱回収装置を提供することにある。An object of the present invention is to provide a heat pump heat recovery device that effectively utilizes the exhaust heat of a refrigerator to increase the refrigeration capacity and save energy with the same required power.
上記目的を達成するために排熱を回収して利用するヒー
トポンプ熱回収装置において、圧縮機。A compressor in a heat pump heat recovery device that recovers and uses waste heat to achieve the above purpose.
凝縮器及び蒸発器からなる冷凍機の前記圧縮機の吐出ガ
ス配管に補助熱交換器を設け、前記凝縮器の冷媒液出口
配管に過冷却器を設け、前記補助熱交換器及び過冷却器
を水配管で接続したものである。An auxiliary heat exchanger is provided in the discharge gas piping of the compressor of the refrigerator consisting of a condenser and an evaporator, a supercooler is provided in the refrigerant liquid outlet pipe of the condenser, and the auxiliary heat exchanger and the supercooler are provided. It is connected by water piping.
また、本発明は上記日記を達成するために、吸収式冷凍
機の前記凝縮器の冷媒液出口配管に過冷却器を設け、前
記再生器の蒸気又はガスの排出口に補助熱交換器を設け
、過冷却器及び補助熱交換器を水配管で接続したもので
ある。Furthermore, in order to achieve the above-mentioned requirements, the present invention provides a supercooler in the refrigerant liquid outlet pipe of the condenser of the absorption chiller, and an auxiliary heat exchanger in the steam or gas outlet of the regenerator. , a supercooler and an auxiliary heat exchanger are connected by water piping.
補助熱交換器により吐出ガスのスーパーヒート熱を取り
出し、この熱により熱回収装置内の蓄熱媒体を濃縮する
。次に熱回収装置内の濃縮された媒体を希釈することに
よって得られる冷却効果を利用して、過冷却器での熱を
熱回収装置に放熱する。この過冷却器と熱回収装置を使
用した運転の際に同し所要動力にて、冷凍能力の増加が
可能になる。The superheat heat of the discharged gas is extracted by the auxiliary heat exchanger, and the heat storage medium in the heat recovery device is condensed using this heat. Next, the heat in the supercooler is radiated to the heat recovery device using the cooling effect obtained by diluting the concentrated medium in the heat recovery device. When operating using this supercooler and heat recovery device, the refrigeration capacity can be increased with the same required power.
また、補助熱交換器により吸収式冷凍機の回収器の蒸気
又はガスの排熱を取り出し、この熱により熱回収装置内
の蓄熱媒体を濃縮する。次に熱回収装置内の濃縮された
媒体を希釈することによって得られる冷却効果を利用し
て、本体冷凍機から取り出した過冷却器での熱を熱回収
装置に放熱する。この過冷却器と熱回収装置を使用した
運転の際に同じ所要動力にて、冷凍能力の増加が可能に
なる。In addition, the auxiliary heat exchanger extracts waste heat of steam or gas from the recovery device of the absorption chiller, and uses this heat to condense the heat storage medium in the heat recovery device. Next, by utilizing the cooling effect obtained by diluting the concentrated medium in the heat recovery device, the heat taken out from the main refrigerator in the supercooler is radiated to the heat recovery device. When operating using this supercooler and heat recovery device, it is possible to increase the refrigeration capacity with the same required power.
以下、本発明の一実施例を第１図により説明する。 An embodiment of the present invention will be described below with reference to FIG.
最初に本装置の構成について説明する。本体の冷凍機は
圧縮機１と、その吐出配管に接続した補助熱交換器４と
、凝縮器２と、凝縮器２の冷媒液出口配管に接続した過
冷却器５と、膨張オリフィス６と、それに接続した蒸発
器３と、これと圧縮機１を接続した配管より成っている
。熱回収装置７は、再生器７ａ、７Ｑ縮器７ｂ、蒸発器
７ｃ、吸収器７ｄより成り、それらに接続配管と冷媒ポ
ンプ８、冷凍ポンプ１０．媒体ポンプ９．媒体ポンプ１
１と、切かえ用の弁１２．弁１３．弁１４゜弁１５．弁
１６を設けである。本体の冷凍機と熱回収装置７は配管
で接続してあり、これに水ポンプ１７、水ポンプ１８を
設けである。First, the configuration of this device will be explained. The main body refrigerator includes a compressor 1, an auxiliary heat exchanger 4 connected to its discharge pipe, a condenser 2, a subcooler 5 connected to the refrigerant liquid outlet pipe of the condenser 2, and an expansion orifice 6. It consists of an evaporator 3 connected to it, and piping connecting it to a compressor 1. The heat recovery device 7 consists of a regenerator 7a, a 7Q condenser 7b, an evaporator 7c, an absorber 7d, and connecting pipes, a refrigerant pump 8, a freezing pump 10. Media pump9. Media pump 1
1 and a switching valve 12. Valve 13. Valve 14° Valve 15. A valve 16 is provided. The refrigerator of the main body and the heat recovery device 7 are connected by piping, and a water pump 17 and a water pump 18 are provided to this.
次に、動作について説明する。まず熱回収運転について
説明する。本体の冷凍機の吐出冷媒ガスのスーパーヒー
ト熱により、補助熱交換器４にて、伝熱管内を流れる水
を加熱する。この水は熱間収装［７の再生器７ａの伝熱
管内に流入し、再生器７ａ内の媒体と熱交換し冷却され
、再び補助熱交換器４へ戻る。再生器７ａでは、熱出力
運転の時に希釈されて吸収器７ｄにたまった希媒体を媒
体ポンプ１１により、再生器７ａの伝熱管外へ散布する
。この希媒体は、伝熱管内を流れる水と熱交換し加熱さ
れて、媒体中の冷媒が蒸発して、媒体の濃度が上がる。Next, the operation will be explained. First, heat recovery operation will be explained. The superheat heat of the refrigerant gas discharged from the main body refrigerator heats the water flowing inside the heat transfer tube in the auxiliary heat exchanger 4. This water flows into the heat transfer tube of the regenerator 7a of the hot storage unit [7], exchanges heat with the medium in the regenerator 7a, is cooled, and returns to the auxiliary heat exchanger 4 again. In the regenerator 7a, the diluted rare medium accumulated in the absorber 7d during the thermal output operation is dispersed to the outside of the heat exchanger tubes of the regenerator 7a by the medium pump 11. This rare medium exchanges heat with the water flowing inside the heat transfer tube and is heated, the refrigerant in the medium evaporates, and the concentration of the medium increases.
これを再び媒体ポンプ９にて再生器７ａの伝熱管へ散布
して濃度を上げる。こうして希媒体が濃媒体になる。This is again sprayed onto the heat transfer tubes of the regenerator 7a using the medium pump 9 to increase the concentration. In this way, a dilute medium becomes a concentrated medium.
この蒸発した冷媒は、凝縮器７ｂで伝熱管内を流れる中
水等と熱交換して放熱し、凝縮して冷媒液になる。こう
して熱回収運転を行なう０次に熱出力運転について説明
する。本体の冷凍機の過冷却器５で凝縮器２の出口の冷
媒液を適冷した水は。The evaporated refrigerant exchanges heat with gray water or the like flowing in the heat transfer tube in the condenser 7b, radiates heat, and is condensed to become a refrigerant liquid. The zero-order heat output operation in which the heat recovery operation is performed in this manner will be explained. The water obtained by appropriately cooling the refrigerant liquid at the outlet of the condenser 2 in the supercooler 5 of the refrigerator of the main body.
加熱され、接続配管を通って、熱回収装置７の蒸発器７
Ｃの伝熱管内へ流入する。この水は蒸発器７ｃ内の冷媒
と熱交換し、冷却され再び過冷却器５へ戻る。蒸発器７
Ｃでは、熱回収運転の時に凝縮器７ｂにたまった冷媒液
を冷媒ポンプ８により。It is heated and passes through the connecting pipe to the evaporator 7 of the heat recovery device 7.
C flows into the heat exchanger tube. This water exchanges heat with the refrigerant in the evaporator 7c, is cooled, and returns to the supercooler 5 again. Evaporator 7
In C, the refrigerant liquid accumulated in the condenser 7b during the heat recovery operation is removed by the refrigerant pump 8.
蒸発器７ｃの伝熱管外へ散布する。冷媒液は伝熱管内を
流れる水と熱交換し、加熱されて蒸発する。Spread outside the heat transfer tube of the evaporator 7c. The refrigerant liquid exchanges heat with the water flowing inside the heat transfer tube, is heated, and evaporates.
蒸発しきれずに底に落下した冷媒液は、再び冷媒ポンプ
１０によ、り伝熱管へ散布する。この蒸発した冷媒は吸
収器７ｄへ流入する。吸収器７ｄでは、熱回収運転の時
に濃縮されて再生器７ａにたまった濃媒体を、媒体ポン
プ９により吸収器７ｄの伝熱管外に散布する。この濃媒
体に、蒸発器７Ｃに蒸発した冷媒が吸収されると共に、
吸収器７ｄの伝熱管内を流れる中水等と熱交換し放熱し
て、濃度が下がる。この媒体を、くり返し媒体ポンプ１
１により吸収器７ｄの伝熱管へ散布して、濃媒体を希媒
体にする。こうして熱出力運転を行なう。The refrigerant liquid that has not been completely evaporated and has fallen to the bottom is again sprayed onto the heat transfer tubes by the refrigerant pump 10. This evaporated refrigerant flows into the absorber 7d. In the absorber 7d, the medium pump 9 sprays the concentrated medium that is concentrated during the heat recovery operation and accumulated in the regenerator 7a outside the heat transfer tube of the absorber 7d. The refrigerant evaporated in the evaporator 7C is absorbed into this concentrated medium, and
It exchanges heat with gray water flowing in the heat exchanger tube of the absorber 7d, radiates heat, and the concentration decreases. This medium is repeatedly pumped into the medium pump 1.
1 to the heat exchanger tube of the absorber 7d to turn the concentrated medium into a diluted medium. In this way, thermal output operation is performed.
まず熱回収運転により、本体の冷凍機の排熱を利用し、
熱回収装置の媒体の濃縮を行なって熱出力運転の準備を
する０次に熱出力運転により、熱回収装置の媒体の希釈
を行なって、本体の冷凍機の過冷却を行なう。過冷却を
行なえば周知のように、同じ所要動力でも、冷凍容量は
増加する。First, the heat recovery operation utilizes the exhaust heat of the main unit's refrigerator,
The medium of the heat recovery device is diluted by the zero-order heat output operation in which the medium of the heat recovery device is concentrated to prepare for the heat output operation, and the main body refrigerator is supercooled. As is well known, if supercooling is performed, the refrigeration capacity will increase even with the same required power.
例えば夜間に熱回収運転を行ない、昼間のピーク負荷時
に熱出力運転を行なって、排熱を有効に利用できる。こ
れを図によって説明する。For example, exhaust heat can be used effectively by performing heat recovery operation at night and performing heat output operation during peak load during the day. This will be explained using a diagram.
例えば、第４図の様な負荷パターンのビルの冷房を行な
うとする。熱回収装置の冷凍機の場合はピーク負荷でも
オーバーロードせぬ様に、２１０（ＵＳＲＴ）の容量の
冷凍機を選定する。この所要動力は２６０（ＫＷ）であ
る、熱回収装置を付けた冷凍機の場合は、熱回収運転時
は１７０（ＵＳＲＴ）で２１２（ＫＷ）、熱出力運転時
は２００（ＵＳＲＴ）で２１２（ＫＷＩである。一方負
荷は第４図の様に、昼間は１７０ （ＵＳＲＴ）Ｘ４
（時間） ＋２００（ＵＳＲＴ）Ｘ６ ［時間）＝１８
８０ （ＵＳＲＴ・ｈ）、夜間は１．７０（ＵＳＲＴ］
Ｘ１４（時間〕＝２３８０（ＵＳＲＴ−ｈ）であり、１
日の合計は１８８０＋２３８０＝４２６０ ［ＵＳＲＴ
−ｈ／日］である。冷凍機を全負荷で運転したとすると
、ビルの負荷率を５５％として、熱回収装置なしの冷凍
機は年間で、（４２６０（ＵＳＲＴ−ｈ／日〕Ｘ３６５
（日）Ｘｏ、５５）／２１０ （ＵＳＲＴＩ＝４
０７２ Ｃ時間〕の運転時間になる。一方熱間収装百付
冷凍機は、１日にピーク負荷時の２００［ＵＳＲＴ］に
熱出力運転を６〔時間〕、通常負荷時の１７０ （ＵＳ
ＲＴ）に熱回収運転を１４＋４＝１８ ［時間１行なう
とすると１日平均では（１７０（ＵＳＲＴ）Ｘ１８ （
時間）＋２００（ＵＳＲＴ）Ｘ６ （時間））／２４［
時間］＝１７７．５（ＵＳＲＴ）になる。年間運転時間
は。For example, suppose that a building with a load pattern as shown in FIG. 4 is to be cooled. In the case of a refrigerator for the heat recovery device, a refrigerator with a capacity of 210 (USRT) is selected so as not to overload even at peak loads. The required power is 260 (KW), in the case of a refrigerator equipped with a heat recovery device, it is 170 (USRT) and 212 (KW) during heat recovery operation, and 200 (USRT) and 212 (KW) during heat output operation. KWI.On the other hand, as shown in Figure 4, the load is 170 (USRT) x 4 during the daytime.
(Time) +200 (USRT) x 6 [Time] = 18
80 (USRT/h), 1.70 (USRT) at night
X14 (time) = 2380 (USRT-h), 1
The total for the day is 1880+2380=4260 [USRT
-h/day]. Assuming that the chiller is operated at full load and the building load factor is 55%, the chiller without heat recovery device will produce (4260 (USRT-h/day) x 365
(Sun) Xo, 55)/210 (USRTI=4
The driving time will be 072 C hours]. On the other hand, a hot storage refrigerator has a heat output operation of 200 [USRT] at peak load for 6 [hours] per day, and 170 [USRT] at normal load.
RT) and heat recovery operation is 14+4=18 [If it is performed once per hour, the daily average is (170 (USRT) x 18 (
time) + 200 (USRT) x 6 (hours))/24[
time] = 177.5 (USRT). Annual operating hours.
（４２６０（ＵＳＲＴ−ｈ／日３ ｘ３６５ （［Ｅ
Ｉ）Ｘｏ、５５／１７７．５［ＵＳＲＴ］＝４８１８［
時間〕である０年間の消費電力は、熱回収装置なしの場
合は、４０７２ （時間）Ｘ２６０ （ＫＷ）＝１０５
８７２０ （ＫＷ−ｈ） 、熱回収装置付の場合は４８
１８ （時間） Ｘ ２１２ （ＫＷＩ ＝１０２１４
１６（ＫＷ−ｈ）となる０両者の差は１０５８７２０−
１０２１４１６＝３７３０４（Ｋ Ｗ −ｈ ）となり
、熱回収装置を付けると年間で３７３０４ （Ｋｗ−ｈ
）の省エネルギーになる。(4260 (USRT-h/day 3 x 365 ([E
I) Xo, 55/177.5 [USRT] = 4818 [
If there is no heat recovery device, the power consumption for 0 years is 4072 (hours) x 260 (KW) = 105
8720 (KW-h), 48 if equipped with heat recovery device
18 (hours) x 212 (KWI =10214
The difference between 0 and 16 (KW-h) is 1058720-
1021416 = 37304 (Kw - h ), and if a heat recovery device is attached, the annual cost will be 37304 (Kw - h
) saves energy.
次に、他の実施例を第２図により説明する。Next, another embodiment will be explained with reference to FIG.
最初に本装置の構成について説明する０本体の冷凍機は
圧縮機１と、その吐出口管に接続した凝縮器２と、凝縮
器２の冷媒液出口配管に接続した過冷却器５と、膨張オ
リフィス６と、それに接続した蒸発器３と、これと圧縮
機１を接続した配管より成っている。熱回収装置７は、
再生器７ａ。First, we will explain the configuration of this device.The main body of the refrigerator consists of a compressor 1, a condenser 2 connected to its discharge outlet pipe, a supercooler 5 connected to the refrigerant liquid outlet pipe of the condenser 2, and an expansion It consists of an orifice 6, an evaporator 3 connected to it, and piping connecting this and a compressor 1. The heat recovery device 7 is
Regenerator 7a.
凝縮器７ｂ、蒸発器７ｃ、吸収器７ｄより成り、それら
に接続配管と冷媒ポンプ８．冷媒ポンプ１０、媒体ポン
プ９．媒体ポンプ１１と、切かえ用の弁１２．弁１３．
弁１４．弁１５．弁１６を設けである。本体の冷凍機と
熱回収装置７は水配管で接続してあり、これに水ポンプ
１８を設けである。It consists of a condenser 7b, an evaporator 7c, and an absorber 7d, with connecting pipes and a refrigerant pump 8. Refrigerant pump 10, medium pump 9. Medium pump 11 and switching valve 12. Valve 13.
Valve 14. Valve 15. A valve 16 is provided. The refrigerator of the main body and the heat recovery device 7 are connected by water piping, and a water pump 18 is provided to this.
次に動作について説明する。まず熱回収運転について説
明する。第１図の実施例では、補助熱交換器４により、
圧縮機１の吐出ガスのスーパーヒート熱を利用していた
が、本例では凝縮器２の排熱を利用して、この冷却水を
熱回収装置７の再生器７ａへ送り、熱回収運転を行なう
。その他は第１図の実施例と同じである。次に熱出力運
転については第１図の実施例と同じなので説明を省略す
る。Next, the operation will be explained. First, heat recovery operation will be explained. In the embodiment of FIG. 1, the auxiliary heat exchanger 4 provides
The superheat heat of the discharged gas of the compressor 1 was used, but in this example, the exhaust heat of the condenser 2 is used to send this cooling water to the regenerator 7a of the heat recovery device 7 to perform heat recovery operation. Let's do it. The rest is the same as the embodiment shown in FIG. Next, the thermal output operation is the same as that of the embodiment shown in FIG. 1, so the explanation will be omitted.
第１図実施例と同じ様に、まず熱回収運転を行ない、次
に熱力運転を行なう。As in the embodiment shown in FIG. 1, first a heat recovery operation is performed, and then a thermal power operation is performed.
また更に他の実施例を第３図により説明する。Still another embodiment will be explained with reference to FIG.
最初に本装置′の構成について説明する。第１５図の実
施例の補助熱交換器４を、吸収式冷凍機１９の再生器の
蒸気又はガスの排出口に取り付けた。First, the configuration of this device' will be explained. The auxiliary heat exchanger 4 of the embodiment shown in FIG. 15 was attached to the steam or gas outlet of the regenerator of the absorption refrigerator 19.
これ以外は第１図の実施例と同じである。Other than this, the embodiment is the same as the embodiment shown in FIG.
次に動作について説明する。まず熱回収運転について説
明する。第１図の実施例では、補助熱交換器４により、
圧縮８！１の吐呂ガスのスーピーヒート熱を利用してい
たが、本例では、吸収式冷凍機１９の再生器の蒸気又は
ガスの排熱を利用して、補助熱交換器４にて、この排熱
により水を加熱して、熱回収装置７の再生器７ａへ送り
、熱回収運転を行なう。その他は第１図の実施例と同じ
である０次に熱出力運転については第１図の実施例と同
じなので、説明を省略する。Next, the operation will be explained. First, heat recovery operation will be explained. In the embodiment of FIG. 1, the auxiliary heat exchanger 4 provides
The heat from the compressed 8!1 steam gas was used, but in this example, the waste heat of the steam or gas from the regenerator of the absorption chiller 19 is used to generate heat in the auxiliary heat exchanger 4. This waste heat heats water and sends it to the regenerator 7a of the heat recovery device 7 to perform heat recovery operation. The rest is the same as the embodiment shown in FIG. 1. Since the zero-order heat output operation is the same as the embodiment shown in FIG. 1, the explanation thereof will be omitted.
第１図の実施例と同じ様に、まず熱回収運転を行ない５
次に熱出力運転を行なう。As in the example shown in Fig. 1, heat recovery operation is first performed.
Next, perform thermal output operation.
以上の３つの実施例で述べた本体の冷凍機としては、遠
心圧縮機式冷凍機、スクリュー圧縮機式冷凍機、往復動
圧縮機式冷凍機、スクロール圧縮機式冷凍機等がある。The main body refrigerators described in the above three embodiments include centrifugal compressor refrigerators, screw compressor refrigerators, reciprocating compressor refrigerators, scroll compressor refrigerators, and the like.
本発明によれば、熱回収装置のない冷凍機と比べると、
同じ所要動力でも大きい冷凍容量を得ることができるの
で、省エネルギーの効果がある。According to the present invention, compared to a refrigerator without a heat recovery device,
Since a large refrigeration capacity can be obtained with the same required power, there is an energy saving effect.
第１図は、冷凍機に補助熱交換器、過冷却器を設けて、
熱回収装置を組合わせた実施例の系統図、第２図は冷凍
機に過冷却器を設けて、熱回収装置を組合わせた他の実
施例の系統図、第３図は冷凍機に過冷却器を設け、吸収
式冷凍機に補助熱交換器を設けて、熱回収装置を組合わ
せた更に他の実施例の系統図、第４図は負荷パターンの
一例を示す図である。
１・・・圧縮機、２・・・凝縮器、３・・・蒸発器、４
・・・補助熱交換器、５・・・過冷却器、６・・膨張オ
リフィス、７・・・熱回収装置、７ａ・・・再生器、７
ｂ・・・凝縮器、７ｃ・・・蒸発器、７ｄ・・・吸収器
、８・・・冷媒ポンプ。
９・・・媒体ポンプ、１０・・・冷媒ポンプ、１１・・
・媒体ポンプ、１２・・・弁、１３・・・弁、１４・・
・弁、１５・・・弁、１６・・・弁、１７・・・水ポン
プ、１８・・・水ポンプ、１９・・・吸収式冷凍機。Figure 1 shows a refrigerator equipped with an auxiliary heat exchanger and a subcooler,
A system diagram of an embodiment in which a heat recovery device is combined; Figure 2 is a system diagram of another embodiment in which a refrigerator is equipped with a supercooler and a heat recovery device is combined; FIG. 4 is a system diagram of still another embodiment in which a cooler is provided, an auxiliary heat exchanger is provided in the absorption refrigerator, and a heat recovery device is combined. FIG. 4 is a diagram showing an example of a load pattern. 1... Compressor, 2... Condenser, 3... Evaporator, 4
... Auxiliary heat exchanger, 5... Supercooler, 6... Expansion orifice, 7... Heat recovery device, 7a... Regenerator, 7
b... Condenser, 7c... Evaporator, 7d... Absorber, 8... Refrigerant pump. 9... Medium pump, 10... Refrigerant pump, 11...
・Medium pump, 12...valve, 13...valve, 14...
・Valve, 15...Valve, 16...Valve, 17...Water pump, 18...Water pump, 19...Absorption refrigerator.
Claims (1)
おいて、圧縮機、凝縮器及び蒸発器からなる冷凍機の前
記圧縮機の吐出ガス配管に補助熱交換器を設け、前記凝
縮器の冷媒液出口配管に過冷却器を設け、前記補助熱交
換器及び過冷却器を水配管で接続したことを特徴とする
ヒート熱回収装置。 ２、凝縮器の熱によつて媒体を濃縮することを特徴とす
る請求項１記載のヒートポンプ熱回収装置。 ３、排熱を回収して利用するヒートポンプ熱回収装置に
おいて、蒸気器、吸収器、再生器及び凝縮器から吸収式
冷凍機の前記凝縮器の冷媒液出口配管に過冷却器を設け
、前記再生器の蒸気又はガスの排出口に補助熱交換器を
設け、過冷却器及び補助熱交換器を水配管で接続したこ
とを特徴とするヒートポンプ熱回収装置。[Scope of Claims] 1. In a heat pump heat recovery device that recovers and utilizes exhaust heat, an auxiliary heat exchanger is provided in the discharge gas piping of the compressor of a refrigerator consisting of a compressor, a condenser, and an evaporator, A heat recovery device characterized in that a supercooler is provided in the refrigerant liquid outlet pipe of the condenser, and the auxiliary heat exchanger and the supercooler are connected by a water pipe. 2. The heat pump heat recovery device according to claim 1, wherein the medium is concentrated by the heat of the condenser. 3. In a heat pump heat recovery device that recovers and utilizes exhaust heat, a supercooler is provided from the steamer, absorber, regenerator, and condenser to the refrigerant liquid outlet piping of the condenser of the absorption chiller, 1. A heat pump heat recovery device, characterized in that an auxiliary heat exchanger is provided at the steam or gas outlet of the device, and the supercooler and the auxiliary heat exchanger are connected by water piping.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1132633A JP2685583B2 (en) | 1989-05-29 | 1989-05-29 | Heat pump heat recovery device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1132633A JP2685583B2 (en) | 1989-05-29 | 1989-05-29 | Heat pump heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH031056A true JPH031056A (en) | 1991-01-07 |
| JP2685583B2 JP2685583B2 (en) | 1997-12-03 |
Family
ID=15085893
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1132633A Expired - Lifetime JP2685583B2 (en) | 1989-05-29 | 1989-05-29 | Heat pump heat recovery device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2685583B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100809023B1 (en) * | 2007-01-04 | 2008-03-03 | 박상술 | A heat exchanger for a public bath |
| US9500395B2 (en) | 2011-07-05 | 2016-11-22 | Carrier Corporation | Refrigeration circuit, gas-liquid separator and heating and cooling system |
-
1989
- 1989-05-29 JP JP1132633A patent/JP2685583B2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100809023B1 (en) * | 2007-01-04 | 2008-03-03 | 박상술 | A heat exchanger for a public bath |
| US9500395B2 (en) | 2011-07-05 | 2016-11-22 | Carrier Corporation | Refrigeration circuit, gas-liquid separator and heating and cooling system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2685583B2 (en) | 1997-12-03 |
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