JP2014119205A - Engine driven heat pump - Google Patents

Engine driven heat pump Download PDF

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JP2014119205A
JP2014119205A JP2012275682A JP2012275682A JP2014119205A JP 2014119205 A JP2014119205 A JP 2014119205A JP 2012275682 A JP2012275682 A JP 2012275682A JP 2012275682 A JP2012275682 A JP 2012275682A JP 2014119205 A JP2014119205 A JP 2014119205A
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refrigerant
engine
temperature
hot water
evaporator
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JP5841931B2 (en
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Hirotoshi Kihara
宏年 鬼原
Takanori Kubo
孝典 久保
Hirotaka Nakamura
広孝 中村
Keiji Sugimori
啓二 杉森
Sadanori Yasuda
定徳 保田
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Yanmar Co Ltd
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Yanmar Co Ltd
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    • 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

PROBLEM TO BE SOLVED: To provide an engine driven heat pump capable of preventing frosting on an evaporator when using engine cooling water as a hot-water supply heat source during heating operation.SOLUTION: The engine driven heat pump comprises: a refrigerant flow regulator (7) regulating a flow rate of a refrigerant flowing in an auxiliary evaporator (5); a pressure sensor (9) detecting a refrigerant low pressure which is the pressure of the refrigerant joining from a main evaporator (3) and the auxiliary evaporator (5) and returning to the compressor (1); and a controller (40) controlling the refrigerant flow regulator (7) so that, when supplying hot water during heat operation, a refrigerant evaporating temperature converted from the refrigerant low pressure becomes higher than a frosting start temperature at which frost is formed on the main evaporator.

Description

本発明は、圧縮機、凝縮器、主蒸発器、及びエンジン冷却水を熱源とする補助蒸発器を備えている冷媒回路と、圧縮機を駆動するエンジンの冷却水回路と、エンジン冷却水を給湯用熱源とする給湯熱交換器を備えている２次水の給湯回路と、を備えているエンジン駆動ヒートポンプに関する。   The present invention relates to a refrigerant circuit including a compressor, a condenser, a main evaporator, and an auxiliary evaporator that uses engine cooling water as a heat source, an engine cooling water circuit that drives the compressor, and hot water for supplying engine cooling water. The present invention relates to an engine-driven heat pump that includes a hot water supply circuit for secondary water that includes a hot water supply heat exchanger as a heat source.

特許文献１は、エンジン冷却水を熱源として空調能力の向上及び給湯を実行できるエンジン駆動ヒートポンプを開示している（００３６、００３７段落、図１、及び図２を参照）。エンジン駆動ヒートポンプは、冷媒回路３０及び冷却水回路８０を備えている。冷媒回路３０は、エンジン冷却水を熱源とする補助蒸発器（熱交換器９３）を備えている。冷却水回路８０は、エンジン冷却水を給湯用熱源とする給湯熱交換器（熱交換器９５）を備えている。このエンジン駆動ヒートポンプは、三方弁９１により、エンジン冷却水を給湯熱源（熱交換器９５）又は冷媒蒸発熱源（熱交換器９３）に分流する。   Patent Document 1 discloses an engine-driven heat pump that can improve air conditioning capability and perform hot water supply using engine cooling water as a heat source (see paragraphs 0036, 0037, FIG. 1 and FIG. 2). The engine-driven heat pump includes a refrigerant circuit 30 and a cooling water circuit 80. The refrigerant circuit 30 includes an auxiliary evaporator (heat exchanger 93) that uses engine coolant as a heat source. The coolant circuit 80 includes a hot water supply heat exchanger (heat exchanger 95) that uses engine coolant as a heat source for hot water supply. In this engine-driven heat pump, the engine cooling water is divided into a hot water supply heat source (heat exchanger 95) or a refrigerant evaporation heat source (heat exchanger 93) by a three-way valve 91.

特開平１０−１０３８１０号公報JP-A-10-103810

暖房運転が行われているとき、室外熱交換器は蒸発器として機能し、外気から熱を吸収して冷媒を加熱する。暖房運転が実行される時期は外気温度が低い時期であるため、暖房運転によって室外熱交換器に霜が発生する場合がある。室外熱交換器の着霜は、空調性能を低下させる。ところが、特許文献１は、暖房運転時にエンジン冷却水を給湯熱源として利用するときに、室外熱交換器の着霜を防止する構成を開示していない。   When the heating operation is performed, the outdoor heat exchanger functions as an evaporator and absorbs heat from the outside air to heat the refrigerant. Since the heating operation is performed at a time when the outside air temperature is low, frost may be generated in the outdoor heat exchanger by the heating operation. The frost formation of the outdoor heat exchanger reduces the air conditioning performance. However, Patent Document 1 does not disclose a configuration for preventing frost formation of the outdoor heat exchanger when engine cooling water is used as a hot water supply heat source during heating operation.

そこで、本発明は、暖房運転時にエンジン冷却水を給湯熱源として利用するときに、蒸発器の着霜を防止できるエンジン駆動ヒートポンプを提供する。   Therefore, the present invention provides an engine-driven heat pump that can prevent frosting of an evaporator when engine cooling water is used as a hot water supply heat source during heating operation.

本発明に係るエンジン駆動ヒートポンプは、冷媒回路であって、圧縮機、凝縮器、主蒸発器、及びエンジン冷却水を熱源とする補助蒸発器を備えており、主蒸発器及び補助蒸発器が並列に配置されている冷媒回路と、圧縮機を駆動するエンジンの冷却水回路であって、エンジン冷却水を給湯用熱源とする給湯熱交換器を備えている冷却水回路と、を備えているエンジン駆動ヒートポンプにおいて、補助蒸発器を流れる冷媒の流量を調整する冷媒流量調整器と、主蒸発器及び補助蒸発器から合流して圧縮機に戻る冷媒の圧力である冷媒低圧を検出する圧力センサと、暖房運転時に給湯を行う場合、冷媒低圧から換算される冷媒蒸発温度が主蒸発器に霜が発生する着霜開始温度よりも高くなるように冷媒流量調整器を制御する制御器と、を備えていることを特徴とする。   An engine-driven heat pump according to the present invention is a refrigerant circuit, and includes a compressor, a condenser, a main evaporator, and an auxiliary evaporator that uses engine cooling water as a heat source, and the main evaporator and the auxiliary evaporator are arranged in parallel. An engine comprising: a refrigerant circuit disposed in the engine; and a cooling water circuit for an engine that drives the compressor, the cooling water circuit including a hot water supply heat exchanger that uses the engine cooling water as a heat source for hot water supply. In the drive heat pump, a refrigerant flow rate regulator that adjusts the flow rate of the refrigerant flowing through the auxiliary evaporator, a pressure sensor that detects a refrigerant low pressure that is a pressure of the refrigerant that merges from the main evaporator and the auxiliary evaporator and returns to the compressor, A controller for controlling the refrigerant flow rate regulator so that the refrigerant evaporation temperature converted from the refrigerant low pressure is higher than the frosting start temperature at which frost is generated in the main evaporator when hot water is supplied during heating operation. And wherein the Rukoto.

エンジン駆動ヒートポンプにおいて、制御器は、着霜開始温度よりも所定幅だけ高い上限温度を冷媒蒸発温度が超えないように冷媒流量調整器を制御する。   In the engine-driven heat pump, the controller controls the refrigerant flow rate regulator so that the refrigerant evaporation temperature does not exceed the upper limit temperature that is higher than the frosting start temperature by a predetermined width.

エンジン駆動ヒートポンプにおいて、制御器は、暖房運転時に外気温度が所定温度よりも低い場合に、冷媒蒸発温度が前記上限温度よりも高い温度範囲内に保たれる通常の暖房運転が行われるように、冷媒流量調整器を制御する。   In the engine-driven heat pump, the controller performs normal heating operation in which the refrigerant evaporation temperature is maintained within a temperature range higher than the upper limit temperature when the outside air temperature is lower than a predetermined temperature during heating operation. Control the refrigerant flow regulator.

このため、本発明に係るエンジン駆動ヒートポンプは、暖房運転時にエンジン冷却水を給湯熱源として利用するときに、蒸発器の着霜を防止できる。   For this reason, the engine-driven heat pump according to the present invention can prevent the evaporator from frosting when the engine coolant is used as a hot water supply heat source during heating operation.

本実施形態に係る冷媒回路の構成図である。It is a block diagram of the refrigerant circuit which concerns on this embodiment. 本実施形態に係る冷却水回路及び給湯回路の構成図である。It is a block diagram of the cooling water circuit and hot water supply circuit which concern on this embodiment. 着霜を防止するための制御機構の構成図である。It is a block diagram of the control mechanism for preventing frost formation. 冷媒蒸発温度及び給湯能力の関係を表す図である。It is a figure showing the relationship between refrigerant | coolant evaporation temperature and hot-water supply capability. 冷媒蒸発温度及び空調能力の関係を表す図である。It is a figure showing the relationship between refrigerant | coolant evaporation temperature and air-conditioning capability.

図面を参照して、本実施形態に係るエンジン駆動ヒートポンプを説明する。エンジン駆動ヒートポンプは、図１に示されるエンジン１０及び冷媒回路１００、及び図２に示される冷却水回路２００を備えている。   An engine-driven heat pump according to this embodiment will be described with reference to the drawings. The engine-driven heat pump includes the engine 10 and the refrigerant circuit 100 shown in FIG. 1, and the cooling water circuit 200 shown in FIG.

図１は、本実施形態に係る冷媒回路１００の構成図である。図１において、冷媒回路１００は、圧縮機１、四方弁２、室外熱交換器３、室内熱交換器４、エンジン排熱回収器５、第１膨張弁６、第２膨張弁７、及びブリッジ回路８を備えている。室外熱交換器３及び室内熱交換器４は、空気（室内空気又は室外空気）と冷媒との間で熱交換を行う装置である。室外熱交換器３及び室内熱交換器４はそれぞれ、冷房運転又は暖房運転の実行に応じて、凝縮器又は蒸発器として機能する。エンジン排熱回収器５は、冷却水回路２００を流れる冷却水からエンジン１０の排熱を回収し、冷媒回路１００の冷媒を加熱する。このため、エンジン排熱回収器５は、冷媒回路１００において蒸発器として機能する。エンジン１０は圧縮機１を駆動する。   FIG. 1 is a configuration diagram of a refrigerant circuit 100 according to the present embodiment. In FIG. 1, a refrigerant circuit 100 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an indoor heat exchanger 4, an engine exhaust heat recovery device 5, a first expansion valve 6, a second expansion valve 7, and a bridge. A circuit 8 is provided. The outdoor heat exchanger 3 and the indoor heat exchanger 4 are devices that exchange heat between air (indoor air or outdoor air) and a refrigerant. The outdoor heat exchanger 3 and the indoor heat exchanger 4 each function as a condenser or an evaporator according to the execution of the cooling operation or the heating operation. The engine exhaust heat recovery unit 5 recovers the exhaust heat of the engine 10 from the coolant flowing through the coolant circuit 200 and heats the refrigerant in the refrigerant circuit 100. For this reason, the engine exhaust heat recovery device 5 functions as an evaporator in the refrigerant circuit 100. The engine 10 drives the compressor 1.

冷媒回路１００は、吐出経路１１、吸入経路１２、ガス経路１３、第１液経路１４、第２経路１５、第３液経路１６、第４液経路１７、ガス経路１８、及びガス経路１９を備えている。吐出経路１１は、圧縮機１及び四方弁２を接続している。吸入経路１２は、四方弁２及び圧縮機１を接続している。ガス経路１３は、四方弁２及び室外熱交換器３を接続している。第１液経路１４は、室外熱交換器３及びブリッジ回路８を接続している。第１膨張弁６は、第１液経路１４上に配置されている。第２液経路１５は、ブリッジ回路８及びエンジン排熱回収器５を接続している。第２膨張弁７は、第２液経路１５上に配置されている。第３液経路１６は、室内熱交換器４及びブリッジ回路８を接続している。第４液経路１７は、ブリッジ回路８及び第２液経路１５を接続しており、接続点Ｐ１で第２液経路１５に合流している。接続点Ｐ１は、第２膨張弁７とブリッジ回路８との間に位置している。ガス経路１８は、室内熱交換器４及び四方弁２を接続している。ガス経路１９は、エンジン排熱回収器５及び吸入経路１２を接続しており、接続点Ｐ２で吸入経路１２に合流している。合流経路１２ａは、吸入経路１２の一部であり、吸入経路１２における接続点Ｐ２の下流側（圧縮機１側）部分を指している。   The refrigerant circuit 100 includes a discharge path 11, a suction path 12, a gas path 13, a first liquid path 14, a second path 15, a third liquid path 16, a fourth liquid path 17, a gas path 18, and a gas path 19. ing. The discharge path 11 connects the compressor 1 and the four-way valve 2. The suction path 12 connects the four-way valve 2 and the compressor 1. The gas path 13 connects the four-way valve 2 and the outdoor heat exchanger 3. The first liquid path 14 connects the outdoor heat exchanger 3 and the bridge circuit 8. The first expansion valve 6 is disposed on the first liquid path 14. The second liquid path 15 connects the bridge circuit 8 and the engine exhaust heat recovery device 5. The second expansion valve 7 is disposed on the second liquid path 15. The third liquid path 16 connects the indoor heat exchanger 4 and the bridge circuit 8. The fourth liquid path 17 connects the bridge circuit 8 and the second liquid path 15 and joins the second liquid path 15 at the connection point P1. The connection point P <b> 1 is located between the second expansion valve 7 and the bridge circuit 8. The gas path 18 connects the indoor heat exchanger 4 and the four-way valve 2. The gas path 19 connects the engine exhaust heat recovery device 5 and the suction path 12, and joins the suction path 12 at the connection point P2. The junction path 12a is a part of the suction path 12, and points to the downstream side (compressor 1 side) of the connection point P2 in the suction path 12.

ブリッジ回路８は、閉経路８０と、閉経路８０上に配置されている４つの逆止弁８１、８２、８３、８４とを備えている。ブリッジ回路８は、室外熱交換器３からの冷媒を室内熱交換器４及びエンジン排熱回収器５に流し、且つ室内熱交換器４からの冷媒を室外熱交換器３及びエンジン排熱回収器５に流すように、構成されている。   The bridge circuit 8 includes a closed path 80 and four check valves 81, 82, 83, 84 disposed on the closed path 80. The bridge circuit 8 allows the refrigerant from the outdoor heat exchanger 3 to flow to the indoor heat exchanger 4 and the engine exhaust heat recovery unit 5, and allows the refrigerant from the indoor heat exchanger 4 to flow to the outdoor heat exchanger 3 and the engine exhaust heat recovery unit. 5 is configured to flow.

冷媒回路１００は、合流経路１２ａ内の冷媒の圧力（冷媒低圧）を検出する圧力センサ９を備えている。   The refrigerant circuit 100 includes a pressure sensor 9 that detects the pressure (refrigerant low pressure) of the refrigerant in the merging path 12a.

冷房運転及び暖房運転を説明する。四方弁２は、冷房運転における冷房位置及び暖房運転における暖房位置のいずれか一方に切り替えられるように構成されている。図１において、四方弁２は暖房位置にある。四方弁２が冷房位置に切り替えられると、吐出経路１１がガス経路１３に接続され且つ吸入経路１２がガス経路１８に接続される。四方弁２が暖房位置に切り替えられると、吐出経路１１がガス経路１８に接続され且つ吸入経路１２がガス経路１３に接続される。   The cooling operation and heating operation will be described. The four-way valve 2 is configured to be switched to one of a cooling position in the cooling operation and a heating position in the heating operation. In FIG. 1, the four-way valve 2 is in the heating position. When the four-way valve 2 is switched to the cooling position, the discharge path 11 is connected to the gas path 13 and the suction path 12 is connected to the gas path 18. When the four-way valve 2 is switched to the heating position, the discharge path 11 is connected to the gas path 18 and the suction path 12 is connected to the gas path 13.

冷房運転において、冷媒は、圧縮機１から、吐出経路１１、ガス経路１３、室外熱交換器３、第１液経路１４、ブリッジ回路８、及び第４液経路１７（第１膨張弁６）を経由して、接続点Ｐ１に至る。第２膨張弁７が開かれている場合、冷媒は、接続点Ｐ１から、室内熱交換器４側だけでなくエンジン排熱回収器５側に流れる。第２膨張弁７が閉じられている場合、冷媒は、接続点Ｐ１から、室内熱交換器４側にのみ流れる。室内熱交換器４側に流れる冷媒は、接続点Ｐ１から、ブリッジ回路８、第３液経路１６、室内熱交換器４、ガス経路１８、及び吸入経路１２を経由して、圧縮機１に戻る。エンジン排熱回収器５側に流れる冷媒は、接続点Ｐ１から、第２膨張弁７、エンジン排熱回収器５、及びガス経路１９を経由して接続点Ｐ２に至り、接続点Ｐ２において室内熱交換器４側に流れる冷媒に合流する。なお、冷房運転では、第２膨張弁７は通常閉じられている。   In the cooling operation, the refrigerant flows from the compressor 1 through the discharge path 11, the gas path 13, the outdoor heat exchanger 3, the first liquid path 14, the bridge circuit 8, and the fourth liquid path 17 (first expansion valve 6). Via the connection point P1. When the second expansion valve 7 is opened, the refrigerant flows from the connection point P1 not only to the indoor heat exchanger 4 side but also to the engine exhaust heat recovery unit 5 side. When the second expansion valve 7 is closed, the refrigerant flows only from the connection point P1 to the indoor heat exchanger 4 side. The refrigerant flowing to the indoor heat exchanger 4 side returns to the compressor 1 from the connection point P1 via the bridge circuit 8, the third liquid path 16, the indoor heat exchanger 4, the gas path 18, and the suction path 12. . The refrigerant flowing to the engine exhaust heat recovery device 5 side reaches the connection point P2 from the connection point P1 via the second expansion valve 7, the engine exhaust heat recovery device 5, and the gas path 19, and the indoor heat at the connection point P2. The refrigerant flows into the exchanger 4 side. In the cooling operation, the second expansion valve 7 is normally closed.

冷房運転において、上述した冷媒の流れにより、室外熱交換器３は凝縮器として機能し、室内熱交換器４は蒸発器として機能する。また、第２膨張弁７が開かれている場合、エンジン排熱回収器５は補助的な蒸発器として機能する。   In the cooling operation, the outdoor heat exchanger 3 functions as a condenser and the indoor heat exchanger 4 functions as an evaporator due to the above-described refrigerant flow. When the second expansion valve 7 is opened, the engine exhaust heat recovery device 5 functions as an auxiliary evaporator.

暖房運転において、冷媒は、圧縮機１から、吐出経路１１、ガス経路１８、室内熱交換器４、第３液経路１６、ブリッジ回路８、及び第４液経路１７（第１膨張弁６）を経由して、接続点Ｐ１に至る。第２膨張弁７が開かれている場合、冷媒は、接続点Ｐ１から、室外熱交換器３側だけでなくエンジン排熱回収器５側に流れる。第２膨張弁７が閉じられている場合、冷媒は、接続点Ｐ１から、室外熱交換器３側にのみ流れる。室外熱交換器３側に流れる冷媒は、接続点Ｐ１から、ブリッジ回路８、第１液経路１４、室外熱交換器３、ガス経路１３、及び吸入経路１２を経由して、圧縮機１に戻る。エンジン排熱回収器５側に流れる冷媒は、接続点Ｐ１から、第２膨張弁７、エンジン排熱回収器５、及びガス経路１９を経由して接続点Ｐ２に至り、接続点Ｐ２において室外熱交換器３側に流れる冷媒に合流する。暖房運転では、エンジン排熱回収器５が補助的な蒸発器として機能するように、第２膨張弁７が必要に応じて開かれる。   In the heating operation, the refrigerant passes from the compressor 1 through the discharge path 11, the gas path 18, the indoor heat exchanger 4, the third liquid path 16, the bridge circuit 8, and the fourth liquid path 17 (first expansion valve 6). Via the connection point P1. When the second expansion valve 7 is opened, the refrigerant flows from the connection point P1 not only to the outdoor heat exchanger 3 side but also to the engine exhaust heat recovery unit 5 side. When the second expansion valve 7 is closed, the refrigerant flows only from the connection point P1 to the outdoor heat exchanger 3 side. The refrigerant flowing to the outdoor heat exchanger 3 side returns to the compressor 1 from the connection point P1 via the bridge circuit 8, the first liquid path 14, the outdoor heat exchanger 3, the gas path 13, and the suction path 12. . The refrigerant flowing to the engine exhaust heat recovery device 5 side reaches the connection point P2 from the connection point P1 via the second expansion valve 7, the engine exhaust heat recovery device 5, and the gas path 19, and the outdoor heat at the connection point P2. The refrigerant flows into the exchanger 3 side. In the heating operation, the second expansion valve 7 is opened as necessary so that the engine exhaust heat recovery device 5 functions as an auxiliary evaporator.

図２は、本実施形態に係る冷却水回路２００及び給湯回路３００の構成図である。図２において、冷却水回路２００は、エンジン１０、冷却水ポンプ２０、第１サーモスタットバルブ２１、第２サーモスタットバルブ２２、第３サーモスタットバルブ２３、給湯熱交換器２４、ラジエータ２５、及びエンジン排熱回収器５を備えている。給湯熱交換器２４は、冷却水回路２００を流れる冷却水からエンジン１０の排熱を回収し、給湯回路３００を流れる２次水を加熱する。   FIG. 2 is a configuration diagram of the cooling water circuit 200 and the hot water supply circuit 300 according to the present embodiment. In FIG. 2, the cooling water circuit 200 includes an engine 10, a cooling water pump 20, a first thermostat valve 21, a second thermostat valve 22, a third thermostat valve 23, a hot water supply heat exchanger 24, a radiator 25, and an engine exhaust heat recovery. A vessel 5 is provided. Hot water supply heat exchanger 24 recovers exhaust heat of engine 10 from the cooling water flowing through cooling water circuit 200 and heats secondary water flowing through hot water supply circuit 300.

また、冷却水回路２００は、実線で示される主経路２６、破線で示される第１バイパス経路２７、破線で示される第２バイパス経路２８、及び二点鎖線で示される第３バイパス経路２９を備えている。主経路２６は、エンジン１０から、第２サーモスタットバルブ２２、給湯熱交換器２４、第１サーモスタットバルブ２１、ラジエータ２５、及び冷却水ポンプ２０を経由して、エンジン１０に至っている。第１バイパス経路２７は、第１サーモスタットバルブ２１から、第３サーモスタットバルブ２３及びエンジン排熱回収器５を経由して、主経路２６上の合流点Ｐ３に至っている。合流点Ｐ３は、主経路２６においてラジエータ２５と冷却水ポンプ２０との間にある。第２バイパス経路２８は、主経路２６上の合流点Ｐ４に至っている。合流点Ｐ４は、主経路２６において給湯熱交換器２４と第１サーモスタットバルブ２１との間にある。第３バイパス経路２９は、第３サーモスタットバルブ２３から、第１バイパス経路２７上の合流点Ｐ５に至っている。合流点Ｐ５は、第１バイパス経路２７においてエンジン排熱回収器５と合流点Ｐ３との間にある。   The cooling water circuit 200 includes a main path 26 indicated by a solid line, a first bypass path 27 indicated by a broken line, a second bypass path 28 indicated by a broken line, and a third bypass path 29 indicated by a two-dot chain line. ing. The main path 26 reaches the engine 10 from the engine 10 via the second thermostat valve 22, the hot water supply heat exchanger 24, the first thermostat valve 21, the radiator 25, and the cooling water pump 20. The first bypass path 27 extends from the first thermostat valve 21 to the junction P3 on the main path 26 via the third thermostat valve 23 and the engine exhaust heat recovery device 5. The junction P3 is located between the radiator 25 and the cooling water pump 20 in the main path 26. The second bypass path 28 reaches a junction P4 on the main path 26. The junction P4 is between the hot water heat exchanger 24 and the first thermostat valve 21 in the main path 26. The third bypass path 29 extends from the third thermostat valve 23 to the junction P5 on the first bypass path 27. The junction P5 is located between the engine exhaust heat recovery device 5 and the junction P3 in the first bypass path 27.

冷却水ポンプ２０は、主経路２６に冷却水を流す。サーモスタットバルブ２１−２３は、冷却水の温度に応じて、流路を切り替える。第１サーモスタットバルブ２１は、冷却水の温度が７１℃（第１温度）以上のときにラジエータ２５への流路を開き、８５°以上で第３サーモスタットバルブ２３への流路を閉じてラジエータ２５への流路だけを開く。一方で、第１サーモスタットバルブ２１は、冷却水の温度が７１℃未満のときにラジエータ２５への流路を閉じて第３サーモスタットバルブ２３への流路だけを開く。第２サーモスタットバルブ２２は、冷却水の温度が６８℃（第２温度）以上のときに給湯熱交換器２４への流路を開き、８０°以上でバイパス経路２８への流路を閉じて給湯熱交換器２４への流路だけを開く。一方で、第２サーモスタットバルブ２２は、冷却水の温度が６８℃未満のときに給湯熱交換器２４への流路を閉じて第２バイパス経路２８への流路だけを開く。第３サーモスタットバルブ２３は、冷却水の温度が６０℃（第３温度）以上のときにエンジン排熱回収器５へ流路を開き、７０°以上で第３バイパス経路２９への流路を閉じてエンジン排熱回収器５への流路だけを開く。一方で、第３サーモスタットバルブ２３は、冷却水の温度が６０℃未満のときにエンジン排熱回収器５への流路を閉じて第３バイパス経路２９への流路だけを開く。   The cooling water pump 20 flows cooling water through the main path 26. The thermostat valve 21-23 switches the flow path according to the temperature of the cooling water. The first thermostat valve 21 opens the flow path to the radiator 25 when the temperature of the cooling water is 71 ° C. (first temperature) or higher, and closes the flow path to the third thermostat valve 23 at 85 ° or higher to close the radiator 25. Open only the flow path to. On the other hand, the first thermostat valve 21 closes the flow path to the radiator 25 and opens only the flow path to the third thermostat valve 23 when the temperature of the cooling water is less than 71 ° C. The second thermostat valve 22 opens the flow path to the hot water supply heat exchanger 24 when the temperature of the cooling water is 68 ° C. (second temperature) or higher, and closes the flow path to the bypass path 28 at 80 ° C. or higher. Only the flow path to the heat exchanger 24 is opened. On the other hand, the second thermostat valve 22 closes the flow path to the hot water supply heat exchanger 24 and opens only the flow path to the second bypass path 28 when the temperature of the cooling water is less than 68 ° C. The third thermostat valve 23 opens the flow path to the engine exhaust heat recovery unit 5 when the temperature of the cooling water is 60 ° C. (third temperature) or higher, and closes the flow path to the third bypass path 29 at 70 ° C. or higher. Then, only the flow path to the engine exhaust heat recovery unit 5 is opened. On the other hand, the third thermostat valve 23 closes the flow path to the engine exhaust heat recovery device 5 and opens only the flow path to the third bypass path 29 when the temperature of the cooling water is less than 60 ° C.

なお、サーモスタットバルブ２２に替えて三方弁を使用すれば冷却水の温度に関わらず給湯熱交換器２４への流路を任意に開閉できるため、冷房運転時に給湯運転を禁止することも可能となる。   If a three-way valve is used instead of the thermostat valve 22, the flow path to the hot water supply heat exchanger 24 can be arbitrarily opened and closed regardless of the temperature of the cooling water, so that the hot water supply operation can be prohibited during the cooling operation. .

給湯回路３００は、２次水ポンプ３０、入水経路３１、出水経路３２、及び給湯熱交換器２４を備えている。入水経路３１は給湯熱交換器２４の入口に接続されており、出水経路３２は給湯熱交換器２４の出口に接続されている。２次水ポンプ３０は、入水経路３１から給湯熱交換器２４を経由して出水経路３２に２次水を流す。このため、給湯熱交換器２４で加熱された２次水が、出水経路３２から取り出される。   The hot water supply circuit 300 includes a secondary water pump 30, a water inlet path 31, a water outlet path 32, and a hot water supply heat exchanger 24. The incoming water path 31 is connected to the inlet of the hot water supply heat exchanger 24, and the outgoing water path 32 is connected to the outlet of the hot water supply heat exchanger 24. The secondary water pump 30 causes the secondary water to flow from the incoming water path 31 to the outgoing water path 32 via the hot water supply heat exchanger 24. For this reason, the secondary water heated by the hot water supply heat exchanger 24 is taken out from the water discharge path 32.

図３を参照して、着霜を防止するための制御機構を説明する。図３は、着霜を防止するための制御機構の構成図である。上述したように、エンジン駆動ヒートポンプは、冷却水を熱源として利用し、エンジン排熱回収器５において冷媒を補助的に加熱でき、且つ給湯熱交換器２４において２次水を加熱できる。冷媒を補助的に加熱することにより、空調能力が向上し、室外熱交換器３の着霜も防止される。また、２次水を加熱することにより、給湯が実現される。つまり、エンジン駆動ヒートポンプは、空調能力の向上（着霜防止）及び給湯が可能に構成されている。   A control mechanism for preventing frost formation will be described with reference to FIG. FIG. 3 is a configuration diagram of a control mechanism for preventing frost formation. As described above, the engine-driven heat pump can use cooling water as a heat source, can supplementally heat the refrigerant in the engine exhaust heat recovery unit 5, and can heat secondary water in the hot water supply heat exchanger 24. By supplementarily heating the refrigerant, the air conditioning capability is improved and frost formation on the outdoor heat exchanger 3 is also prevented. Moreover, hot water supply is implement | achieved by heating secondary water. That is, the engine-driven heat pump is configured to be capable of improving air conditioning capability (preventing frost formation) and supplying hot water.

図３において、エンジン駆動ヒートポンプは、制御器４０、気温センサ４１、圧力センサ９（図１）、第２膨張弁７（図１）、及び２次水ポンプ３０（図２）を備えている。気温センサ４１は、室外空気の温度（外気温度）を検出する。制御器４０は、室外熱交換器３に霜が発生しないように、気温センサ４１及び圧力センサ９の検出値（外気温度及び冷媒低圧）に基づいて、第２膨張弁７の開度及び２次水ポンプ３０の回転数を制御する。以下、この制御を詳しく説明する。   In FIG. 3, the engine-driven heat pump includes a controller 40, an air temperature sensor 41, a pressure sensor 9 (FIG. 1), a second expansion valve 7 (FIG. 1), and a secondary water pump 30 (FIG. 2). The air temperature sensor 41 detects the temperature of the outdoor air (outside air temperature). Based on the detected values of the air temperature sensor 41 and the pressure sensor 9 (outside air temperature and refrigerant low pressure), the controller 40 determines the degree of opening and the secondary expansion valve 7 so that frost is not generated in the outdoor heat exchanger 3. The number of rotations of the water pump 30 is controlled. Hereinafter, this control will be described in detail.

圧力センサ９は、上述したように、冷媒低圧（合流経路１２ａ内の冷媒の圧力）を検出する。冷媒の飽和蒸気線に基づいて、冷媒低圧に対応する冷媒蒸発温度（飽和蒸気温度）が特定される。冷媒蒸発温度が着霜開始温度よりも低下すると、室外熱交換器３に霜が発生する。本発明者らの試験によれば、着霜開始温度は−３．０℃である。   As described above, the pressure sensor 9 detects the refrigerant low pressure (the pressure of the refrigerant in the merging path 12a). Based on the saturated vapor line of the refrigerant, the refrigerant evaporation temperature (saturated vapor temperature) corresponding to the refrigerant low pressure is specified. When the refrigerant evaporation temperature falls below the frosting start temperature, frost is generated in the outdoor heat exchanger 3. According to the tests of the present inventors, the frosting start temperature is -3.0 ° C.

給湯に供給される冷却水の熱量は、エンジン排熱回収器５を流れる冷媒の流量及び／又はエンジン冷却水の流量を変更することによって、変更される。第２膨張弁７は、エンジン排熱回収器５を流れる冷媒の流量を調整する。このため、第２膨張弁７による冷媒の流量の調整により、給湯に供給される冷却水の熱量が変更される。   The amount of heat of the cooling water supplied to the hot water supply is changed by changing the flow rate of the refrigerant flowing through the engine exhaust heat recovery device 5 and / or the flow rate of the engine cooling water. The second expansion valve 7 adjusts the flow rate of the refrigerant flowing through the engine exhaust heat recovery unit 5. For this reason, the amount of heat of the cooling water supplied to the hot water supply is changed by adjusting the flow rate of the refrigerant by the second expansion valve 7.

室外熱交換器３の着霜防止を実現するために、次の制御が行われている。制御器４０は、暖房運転時に給湯を行う場合、室外熱交換器３に霜が発生する着霜開始温度よりも冷媒蒸発温度が高くなるように、第２膨張弁７を制御する。   In order to prevent frost formation of the outdoor heat exchanger 3, the following control is performed. When supplying hot water during the heating operation, the controller 40 controls the second expansion valve 7 so that the refrigerant evaporation temperature becomes higher than the frosting start temperature at which frost is generated in the outdoor heat exchanger 3.

第２膨張弁７の開度が小さくなると、空調能力の向上（着霜防止）に供給される熱量が増大し、且つ給湯に供給される熱量が減少する。給湯に供給される熱量を増大するためには、第２膨張弁７の開度が増大することは好ましくない。   When the opening degree of the second expansion valve 7 is reduced, the amount of heat supplied for improving the air conditioning capability (preventing frost formation) increases and the amount of heat supplied to the hot water supply decreases. In order to increase the amount of heat supplied to the hot water supply, it is not preferable that the opening degree of the second expansion valve 7 increases.

給湯に供給される熱量を確保するために、次の制御が行われている。制御器４０は、着霜開始温度よりも所定幅だけ高い上限温度を冷媒蒸発温度が超えないように、第２膨張弁７を制御する。所定幅は例えば１．５℃であり、この場合、上限温度は−１．５℃である。つまり、冷媒蒸発温度が−１．５℃から−３．０℃の範囲内に保たれるように、第２膨張弁７が制御される。   In order to secure the amount of heat supplied to the hot water supply, the following control is performed. The controller 40 controls the second expansion valve 7 so that the refrigerant evaporation temperature does not exceed the upper limit temperature that is higher than the frosting start temperature by a predetermined width. The predetermined width is, for example, 1.5 ° C., and in this case, the upper limit temperature is −1.5 ° C. That is, the second expansion valve 7 is controlled so that the refrigerant evaporation temperature is maintained within the range of −1.5 ° C. to −3.0 ° C.

給湯の可否を決定するために、次の制御が行われている。制御器４０は、暖房運転時に外気温度が所定温度よりも低い場合に、通常の暖房運転が行われるように、第２膨張弁７を制御する。外気温度が所定温度よりも低い場合に給湯に排熱が利用されると、室外熱交換器３に着霜が発生する。本実施形態では、所定温度は２℃である。通常の暖房運転では、冷媒蒸発温度が前記上限温度（−１．５℃）よりも高い温度範囲内に保たれている。本実施形態では、次のようにして、冷媒蒸発温度の低下に応じて給湯への排熱の供給が停止され、冷媒蒸発温度が上述の温度範囲に保たれる。通常の暖房運転では、第２膨張弁７が開かれており、冷媒がエンジン排熱回収器５を流れる。エンジン排熱回収器５では冷却水から冷媒に排熱が供給されるので、冷却水の温度が低下する。冷却水の温度が６８℃より低下すると、第２サーモスタットバルブ２２が給湯熱交換器２４への流路を閉じる。この結果、給湯に排熱が供給されず、排熱がすべて冷媒に供給され、冷媒蒸発温度の低下が抑制される。なお、制御器４０は、給湯をできなくするために、第２膨張弁７を開くだけでなく、更に２次水ポンプ３０の駆動を停止してもよい。また、冷房運転においても、室内熱交換器４への着霜を防止するために、第２膨張弁７を制御する上述の制御が行われてもよい。   The following control is performed to determine whether hot water supply is possible. The controller 40 controls the second expansion valve 7 so that the normal heating operation is performed when the outside air temperature is lower than a predetermined temperature during the heating operation. If exhaust heat is used for hot water supply when the outside air temperature is lower than a predetermined temperature, frost formation occurs in the outdoor heat exchanger 3. In the present embodiment, the predetermined temperature is 2 ° C. In normal heating operation, the refrigerant evaporation temperature is maintained within a temperature range higher than the upper limit temperature (−1.5 ° C.). In the present embodiment, the supply of exhaust heat to the hot water supply is stopped in accordance with a decrease in the refrigerant evaporation temperature as described below, and the refrigerant evaporation temperature is maintained in the above temperature range. In normal heating operation, the second expansion valve 7 is opened, and the refrigerant flows through the engine exhaust heat recovery device 5. Since the exhaust heat is supplied from the cooling water to the refrigerant in the engine exhaust heat recovery device 5, the temperature of the cooling water decreases. When the temperature of the cooling water falls below 68 ° C., the second thermostat valve 22 closes the flow path to the hot water supply heat exchanger 24. As a result, no exhaust heat is supplied to the hot water supply, and all the exhaust heat is supplied to the refrigerant, and a decrease in the refrigerant evaporation temperature is suppressed. The controller 40 may not only open the second expansion valve 7 but also stop driving the secondary water pump 30 in order to disable hot water supply. In the cooling operation, the above-described control for controlling the second expansion valve 7 may be performed in order to prevent frost formation on the indoor heat exchanger 4.

図４、５を参照して、暖房運転時に給湯に熱量が供給される場合における、冷媒蒸発温度、給湯能力、空調能力の変化を説明する。図４は、冷媒蒸発温度及び給湯能力の関係を表す図である。図５は、冷媒蒸発温度及び空調能力の関係を表す図である。   With reference to FIGS. 4 and 5, changes in the refrigerant evaporation temperature, the hot water supply capacity, and the air conditioning capacity when heat is supplied to the hot water supply during the heating operation will be described. FIG. 4 is a diagram illustrating the relationship between the refrigerant evaporation temperature and the hot water supply capacity. FIG. 5 is a diagram illustrating the relationship between the refrigerant evaporation temperature and the air conditioning capability.

図４、５において、実線のグラフＧ１は、標準の暖房運転における関係を示しており、破線のグラフＧ２は、外気温度が高い状態での暖房運転（以下、過負荷の暖房運転）における関係を示している。横軸は冷媒蒸発温度を示しており、図４の縦軸は給湯能力を示しており、図５の縦軸は空調能力を示している。着霜範囲Ａは、室外熱交換器３に霜が発生する冷媒蒸発温度の範囲を示しており、制御範囲Ｂは、給湯に熱量を供給しながら着霜防止を実現する場合の冷媒蒸発温度の範囲を示している。   4 and 5, the solid line graph G1 indicates the relationship in the standard heating operation, and the broken line graph G2 indicates the relationship in the heating operation (hereinafter referred to as overload heating operation) in a state where the outside air temperature is high. Show. The horizontal axis indicates the refrigerant evaporation temperature, the vertical axis in FIG. 4 indicates the hot water supply capacity, and the vertical axis in FIG. 5 indicates the air conditioning capacity. The frosting range A indicates the range of the refrigerant evaporation temperature at which frost is generated in the outdoor heat exchanger 3, and the control range B is the refrigerant evaporation temperature in the case of realizing frosting prevention while supplying heat to the hot water supply. The range is shown.

標準の暖房運転及び過負荷の暖房運転において、室外熱交換器３／室内熱交換器４の容量比は、１００％である。   In the standard heating operation and the overload heating operation, the capacity ratio of the outdoor heat exchanger 3 / the indoor heat exchanger 4 is 100%.

図４、５において、グラフの隣にある矢印は、通常運転から給湯を行う運転への制御の方向を示している。図４を参照すると、双方のグラフＧ１、Ｇ２において、給湯能力が増大するように制御されており、これに応じて冷媒蒸発温度が低下している。図５を参照すると、双方のグラフＧ１、Ｇ２において、冷媒蒸発温度が低下するにつれて、空調能力が低下している。つまり、空調能力の低下に合わせて、給湯能力が増大している。   4 and 5, the arrow next to the graph indicates the direction of control from the normal operation to the operation of supplying hot water. Referring to FIG. 4, in both graphs G1 and G2, the hot water supply capacity is controlled to increase, and the refrigerant evaporation temperature decreases accordingly. Referring to FIG. 5, in both graphs G1 and G2, the air conditioning capacity decreases as the refrigerant evaporation temperature decreases. That is, the hot water supply capacity is increasing as the air conditioning capacity decreases.

図４、５に示されるように、通常の暖房運転では、グラフＧ１の終端が制御範囲Ｂ内に留まるように、第２膨張弁７の制御量が制限されている。一方、過負荷の暖房運転では、冷媒低圧が十分高く、冷媒蒸発温度が着霜開始温度よりも十分高いため、着霜を防止するために第２膨張弁７の制御量を制限する必要がない。制御量が制限されていないため、図４、５において、給湯能力及び空調能力に関して、グラフＧ２の変化幅は、グラフＧ１の変化幅よりも大きい。   As shown in FIGS. 4 and 5, in the normal heating operation, the control amount of the second expansion valve 7 is limited so that the end of the graph G <b> 1 remains within the control range B. On the other hand, in the overload heating operation, the refrigerant low pressure is sufficiently high and the refrigerant evaporation temperature is sufficiently higher than the frosting start temperature, so that it is not necessary to limit the control amount of the second expansion valve 7 in order to prevent frosting. . Since the control amount is not limited, in FIGS. 4 and 5, the change width of the graph G2 is larger than the change width of the graph G1 with respect to the hot water supply capacity and the air conditioning capacity.

本実施形態に係るエンジン駆動ヒートポンプは、上述の構成を有することにより、次の作用、効果を有している。   The engine-driven heat pump according to the present embodiment has the following operations and effects by having the above-described configuration.

（１）本実施形態に係るエンジン駆動ヒートポンプは、冷媒回路１００と、冷却水回路２００とを備えている。冷媒回路１００は、圧縮機１、室内熱交換器４（凝縮器）、室外熱交換器３（主蒸発器）、及びエンジン冷却水を熱源とするエンジン排熱回収器５（補助蒸発器）を備えており、室外熱交換器３及びエンジン排熱回収器５が並列に配置されている。冷却水回路２００は、圧縮機を駆動し、エンジン冷却水を給湯用熱源とする給湯熱交換器２４を備えている。エンジン駆動ヒートポンプは、第２膨張弁７（冷媒流量調整器）と、圧力センサ９と、制御器４０とを備えている。第２膨張弁７は、エンジン排熱回収器５を流れる冷媒の流量を調整する。圧力センサ９は、室外熱交換器３及びエンジン排熱回収器５から合流して圧縮機１に戻る冷媒の圧力を検出する。制御器４０は、暖房運転時に給湯を行う場合、室外熱交換器３に霜が発生する着霜開始温度よりも冷媒蒸発温度が高くなるように第２膨張弁７を制御する。 (1) The engine-driven heat pump according to this embodiment includes a refrigerant circuit 100 and a cooling water circuit 200. The refrigerant circuit 100 includes a compressor 1, an indoor heat exchanger 4 (condenser), an outdoor heat exchanger 3 (main evaporator), and an engine exhaust heat recovery unit 5 (auxiliary evaporator) that uses engine cooling water as a heat source. The outdoor heat exchanger 3 and the engine exhaust heat recovery unit 5 are arranged in parallel. The cooling water circuit 200 includes a hot water supply heat exchanger 24 that drives a compressor and uses engine cooling water as a heat source for hot water supply. The engine-driven heat pump includes a second expansion valve 7 (refrigerant flow regulator), a pressure sensor 9, and a controller 40. The second expansion valve 7 adjusts the flow rate of the refrigerant flowing through the engine exhaust heat recovery unit 5. The pressure sensor 9 detects the pressure of the refrigerant that merges from the outdoor heat exchanger 3 and the engine exhaust heat recovery unit 5 and returns to the compressor 1. When supplying hot water during the heating operation, the controller 40 controls the second expansion valve 7 so that the refrigerant evaporation temperature is higher than the frosting start temperature at which frost is generated in the outdoor heat exchanger 3.

このため、本実施形態に係るエンジン駆動ヒートポンプは、暖房運転時にエンジン冷却水を給湯熱源として利用するときに、蒸発器の着霜を防止できる。   For this reason, the engine drive heat pump which concerns on this embodiment can prevent frost formation of an evaporator, when using engine cooling water as a hot water supply heat source at the time of heating operation.

（２）本実施形態に係るエンジン駆動ヒートポンプにおいて、制御器４０は、着霜開始温度よりも所定幅だけ高い上限温度を冷媒蒸発温度が超えないように冷媒流量調整器を制御する。 (2) In the engine-driven heat pump according to the present embodiment, the controller 40 controls the refrigerant flow rate regulator so that the refrigerant evaporation temperature does not exceed the upper limit temperature that is higher than the frosting start temperature by a predetermined width.

このため、本実施形態に係るエンジン駆動ヒートポンプは、蒸発器の着霜を防止しながら、給湯に供給される熱量を確保できる。   For this reason, the engine drive heat pump which concerns on this embodiment can ensure the calorie | heat amount supplied to hot water supply, preventing the frost formation of an evaporator.

（３）本実施形態に係るエンジン駆動ヒートポンプにおいて、制御器４０は、暖房運転時に外気温度が所定温度よりも低い場合に、冷媒蒸発温度が前記上限温度よりも高い温度範囲内に保たれる通常の暖房運転が行われるように、冷媒流量調整器を制御する。 (3) In the engine-driven heat pump according to the present embodiment, the controller 40 normally maintains the refrigerant evaporation temperature within a temperature range higher than the upper limit temperature when the outside air temperature is lower than a predetermined temperature during heating operation. The refrigerant flow rate regulator is controlled so that the heating operation is performed.

このため、本実施形態に係るエンジン駆動ヒートポンプは、室外熱交換器に着霜が発生する状況では、エンジン冷却水を給湯用熱源として利用することを禁止できる。   For this reason, the engine drive heat pump which concerns on this embodiment can prohibit using engine cooling water as a heat source for hot water supply in the condition where frosting generate | occur | produces in an outdoor heat exchanger.

１ 圧縮機
３ 室外熱交換器（暖房運転における主蒸発器）
４ 室内熱交換器（暖房運転における凝縮器）
５ エンジン排熱回収器（補助蒸発器）
７ 第２膨張弁（冷媒流量調整器）
９ 圧力センサ
１０ エンジン
２４ 給湯熱交換器
３０ ２次水ポンプ
４０ 制御器
１００ 冷媒回路
２００ 冷却水回路 1 Compressor 3 Outdoor heat exchanger (main evaporator in heating operation)
4 Indoor heat exchanger (condenser in heating operation)
5 Engine exhaust heat recovery unit (auxiliary evaporator)
7 Second expansion valve (refrigerant flow controller)
9 Pressure sensor 10 Engine 24 Hot water supply heat exchanger 30 Secondary water pump 40 Controller 100 Refrigerant circuit 200 Cooling water circuit

Claims (3)

冷媒回路であって、圧縮機、凝縮器、主蒸発器、及びエンジン冷却水を熱源とする補助蒸発器を備えており、主蒸発器及び補助蒸発器が並列に配置されている冷媒回路と、
圧縮機を駆動するエンジンの冷却水回路であって、エンジン冷却水を給湯用熱源とする給湯熱交換器を備えている冷却水回路と、を備えているエンジン駆動ヒートポンプにおいて、
補助蒸発器を流れる冷媒の流量を調整する冷媒流量調整器と、
主蒸発器及び補助蒸発器から合流して圧縮機に戻る冷媒の圧力である冷媒低圧を検出する圧力センサと、
暖房運転時に給湯を行う場合、冷媒低圧から換算される冷媒蒸発温度が主蒸発器に霜が発生する着霜開始温度よりも高くなるように冷媒流量調整器を制御する制御器と、を備えていることを特徴とするエンジン駆動ヒートポンプ。 A refrigerant circuit comprising a compressor, a condenser, a main evaporator, and an auxiliary evaporator that uses engine coolant as a heat source, and the refrigerant circuit in which the main evaporator and the auxiliary evaporator are arranged in parallel;
In an engine-driven heat pump comprising: an engine cooling water circuit that drives a compressor, and a cooling water circuit that includes a hot water supply heat exchanger that uses engine cooling water as a heat source for hot water supply,
A refrigerant flow controller for adjusting the flow rate of the refrigerant flowing through the auxiliary evaporator;
A pressure sensor that detects a refrigerant low pressure that is a pressure of the refrigerant that merges from the main evaporator and the auxiliary evaporator and returns to the compressor;
A controller for controlling the refrigerant flow rate regulator so that the refrigerant evaporation temperature converted from the refrigerant low pressure is higher than the frosting start temperature at which frost is generated in the main evaporator when hot water is supplied during heating operation. An engine-driven heat pump. 制御器は、着霜開始温度よりも所定幅だけ高い上限温度を冷媒蒸発温度が超えないように冷媒流量調整器を制御する、請求項１に記載のエンジン駆動ヒートポンプ。   The engine-driven heat pump according to claim 1, wherein the controller controls the refrigerant flow rate regulator so that the refrigerant evaporation temperature does not exceed an upper limit temperature that is higher than the frosting start temperature by a predetermined width. 制御器は、暖房運転時に外気温度が所定温度よりも低い場合に、冷媒蒸発温度が前記上限温度よりも高い温度範囲内に保たれる通常の暖房運転が行われるように、冷媒流量調整器を制御する、請求項２に記載のエンジン駆動ヒートポンプ。   When the outside air temperature is lower than a predetermined temperature during the heating operation, the controller controls the refrigerant flow regulator so that the normal heating operation is performed in which the refrigerant evaporation temperature is maintained within a temperature range higher than the upper limit temperature. The engine-driven heat pump according to claim 2, which is controlled.
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