JP5571978B2 - Heat pump system - Google Patents

Heat pump system Download PDF

Info

Publication number
JP5571978B2
JP5571978B2 JP2010053430A JP2010053430A JP5571978B2 JP 5571978 B2 JP5571978 B2 JP 5571978B2 JP 2010053430 A JP2010053430 A JP 2010053430A JP 2010053430 A JP2010053430 A JP 2010053430A JP 5571978 B2 JP5571978 B2 JP 5571978B2
Authority
JP
Japan
Prior art keywords
refrigerant
compressor
temperature
heat exchanger
exhaust heat
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
Application number
JP2010053430A
Other languages
Japanese (ja)
Other versions
JP2011185571A (en
Inventor
喜徳 久角
義通 木内
秀樹 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Osaka Gas Co Ltd
Original Assignee
Osaka Gas Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Osaka Gas Co Ltd filed Critical Osaka Gas Co Ltd
Priority to JP2010053430A priority Critical patent/JP5571978B2/en
Publication of JP2011185571A publication Critical patent/JP2011185571A/en
Application granted granted Critical
Publication of JP5571978B2 publication Critical patent/JP5571978B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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

Landscapes

  • Heat-Pump Type And Storage Water Heaters (AREA)

Description

本発明は、燃焼機関により発生される駆動力により運転される圧縮機を冷媒循環路に備え、圧縮機により冷媒を圧縮して凝縮器に送り当該凝縮器で熱を放出するとともに、凝縮器から冷媒を膨張弁、蒸発器に送り、蒸発器で受熱して、圧縮機に戻るヒートポンプサイクルを備え、さらに、前記燃焼機関により発生する排熱を回収して、冷媒循環路を流れる冷媒に与える熱交換器を備えたヒートポンプシステムに関するとともに、その使用方法に関する。   The present invention includes a compressor that is operated by a driving force generated by a combustion engine in a refrigerant circulation path, compresses the refrigerant by the compressor, sends the refrigerant to a condenser, and releases heat from the condenser. A heat pump cycle that sends the refrigerant to an expansion valve and an evaporator, receives heat by the evaporator, and returns to the compressor, further recovers exhaust heat generated by the combustion engine, and gives heat to the refrigerant flowing through the refrigerant circuit It is related with the heat pump system provided with the exchanger, and its usage.

このようなヒートポンプシステムが、特許文献１、特許文献２に開示されている。
特許文献１は、エンジン駆動ヒートポンプ装置を関し、ヒートポンプ暖房における暖房能力の向上を図っている。
この特許文献１の図３には、暖房運転時の運転状態が示されている。
図３に示される暖房運転においては、圧縮機２から吐出される冷媒が、室内機８（３）、膨張弁４、室外熱交換器９（５）、冷媒加熱用熱交換器１６を経て、圧縮機２に戻る。エンジン冷却水は、エンジン１から排熱熱交換器１４を経た後、冷媒加熱用熱交換器１６に送られ、その後、エンジン１に戻る。ここで、部材番号は、特許文献１において付されている番号で記載している。 Such a heat pump system is disclosed in Patent Document 1 and Patent Document 2.
Patent Document 1 relates to an engine-driven heat pump device, and attempts to improve the heating capacity in heat pump heating.
FIG. 3 of Patent Document 1 shows an operation state during heating operation.
In the heating operation shown in FIG. 3, the refrigerant discharged from the compressor 2 passes through the indoor unit 8 (3), the expansion valve 4, the outdoor heat exchanger 9 (5), and the refrigerant heating heat exchanger 16, Return to the compressor 2. The engine coolant passes through the exhaust heat exchanger 14 from the engine 1, is then sent to the refrigerant heating heat exchanger 16, and then returns to the engine 1. Here, the member number is indicated by the number given in Patent Document 1.

特許文献２は、冷媒圧力の損失を低減させ、室外熱交換器とエンジン廃熱回収器に適正な冷媒量を供給することを可能としている。
特許文献２の図１に、このエンジン駆動式ヒートポンプの構成が示されている。段落〔００２８〕〜〔００３２〕を参照すると、このヒートポンプでも、暖房運転では、圧縮機２から吐出される冷媒が、室内熱交換器５、室外膨張弁６、室外熱交換器４、圧縮機２に戻る。さらに、このヒートポンプでは、室外熱交換器４とエンジン廃熱回収器１５を並列に配置し、エンジン廃熱回収器１５からの冷媒も圧縮機２に戻る。ここで、部材番号は、特許文献２において付されている番号で記載している。 Patent document 2 makes it possible to reduce the loss of refrigerant pressure and supply an appropriate amount of refrigerant to the outdoor heat exchanger and the engine waste heat recovery unit.
FIG. 1 of Patent Document 2 shows the configuration of this engine-driven heat pump. Referring to paragraphs [0028] to [0032], in this heat pump as well, in the heating operation, the refrigerant discharged from the compressor 2 is the indoor heat exchanger 5, the outdoor expansion valve 6, the outdoor heat exchanger 4, and the compressor 2. Return to. Further, in this heat pump, the outdoor heat exchanger 4 and the engine waste heat recovery unit 15 are arranged in parallel, and the refrigerant from the engine waste heat recovery unit 15 also returns to the compressor 2. Here, the member number is indicated by the number given in Patent Document 2.

これら特許文献１、２に開示のシステムにおけるヒートポンプとしての主要な差は、エンジン排熱をどのように利用するかの差であるが、基本的に、エンジン排熱熱交換器においてエンジン排熱を回収し、冷媒を過熱状態として圧縮機に導入する構成を採用している。   The main difference as a heat pump in the systems disclosed in these Patent Documents 1 and 2 is the difference in how the engine exhaust heat is used. Basically, the engine exhaust heat is exchanged in the engine exhaust heat exchanger. The structure which collect | recovers and introduce | transduces into a compressor by making a refrigerant into a superheated state is employ | adopted.

本願においては、エンジン排熱のヒートポンプサイクルにおける利用形態が問題となるため、上記の特許文献１に記載のヒートポンプを、従来技術の代表例として、以下説明する。
本明細書の図３に、特許文献１に開示のエンジン駆動式ヒートポンプ装置（ヒートポンプシステムの一例）の構成を簡略化して示した。図３において、同図左側に室内機５０を、同図右側に室外機６０を示している。室内機５０には、凝縮器として働く室内熱交換器５１が備えられており、室外機６０には、燃焼機関としてのガスエンジン６１、このガスエンジン６１により駆動される圧縮機６２、膨張弁６３、蒸発器としての室外熱交換器６４、燃焼機関から送り出される排熱により冷媒を過熱する排熱熱交換器として働く過熱器６５が備えられている。 In this application, since the utilization form in the heat pump cycle of engine exhaust heat becomes a problem, the heat pump described in Patent Literature 1 will be described below as a representative example of the prior art.
FIG. 3 of the present specification shows a simplified configuration of an engine-driven heat pump device (an example of a heat pump system) disclosed in Patent Document 1. 3, the indoor unit 50 is shown on the left side of the figure, and the outdoor unit 60 is shown on the right side of the figure. The indoor unit 50 includes an indoor heat exchanger 51 that functions as a condenser. The outdoor unit 60 includes a gas engine 61 as a combustion engine, a compressor 62 driven by the gas engine 61, and an expansion valve 63. An outdoor heat exchanger 64 serving as an evaporator and a superheater 65 serving as an exhaust heat exchanger that superheats the refrigerant by exhaust heat sent from the combustion engine are provided.

この装置は、ガスエンジン６１により発生される駆動力により運転される圧縮機６２を冷媒循環路Ｌ１に備え、圧縮機６２により冷媒を圧縮して凝縮器５１に送り当該凝縮器５１で熱を放出するとともに、凝縮器５１から冷媒を膨張弁６３、蒸発器６４に送り、蒸発器６４で受熱して、圧縮機６２に戻るヒートポンプサイクルが備えられている。
一方、この装置には、ガスエンジンからの排熱は、蒸発器６４と圧縮機６２との間に設けられる過熱器６５に送られ、排熱を回収して、利用することができる。 This apparatus includes a compressor 62 operated by the driving force generated by the gas engine 61 in the refrigerant circuit L1, compresses the refrigerant by the compressor 62, sends the refrigerant to the condenser 51, and releases the heat from the condenser 51. In addition, a heat pump cycle is provided in which the refrigerant is sent from the condenser 51 to the expansion valve 63 and the evaporator 64, receives heat by the evaporator 64, and returns to the compressor 62.
On the other hand, in this apparatus, the exhaust heat from the gas engine is sent to a superheater 65 provided between the evaporator 64 and the compressor 62, and the exhaust heat can be recovered and used.

特開２００８−２８６４７６号公報JP 2008-286476 A 特開２００６−２５０４３６号公報JP 2006-250436 A

上記のようなヒートポンプシステムでは、一般に、冷媒にＲ４１０A（ディポン社の登録商標）が用いられており、投入一次エネルギー（HHV基準）の約３２％が燃焼機関としてのエンジンの軸端出力として圧縮機の駆動に使われ、また約５０％がエンジンの温水出力として冷媒蒸発の熱源の一部に利用される。ここで、エンジンの利用温水は、最高８５℃で約１０℃温度を下げてエンジンに戻される。即ち、排熱熱交換器において、温水が有する排熱を冷媒で回収する場合、温水温度は８５℃から７５℃程度まで温度低下を受ける。   In the heat pump system as described above, R410A (registered trademark of Dupont) is generally used as the refrigerant, and about 32% of the input primary energy (HHV standard) is used as a shaft end output of the engine as a combustion engine. About 50% is used as part of the heat source for refrigerant evaporation as engine warm water output. Here, the hot water of the engine is returned to the engine after the temperature is lowered by about 10 ° C. at a maximum of 85 ° C. That is, in the exhaust heat exchanger, when the exhaust heat of the hot water is recovered with the refrigerant, the hot water temperature is lowered from about 85 ° C. to about 75 ° C.

圧縮機の出口における吐出冷媒ガス温度は、外気温度、室内暖房設定温度、暖房熱負荷、熱交換器伝熱の性能などで決まる圧縮比と圧縮機の効率により左右されるが、圧縮機入口の冷媒の過熱度が５℃、室内吹き出し温風温度が３５℃なら、おおよそ６５℃である。
この圧縮機出口の冷媒ガスを、先の温水で加熱できれば、暖房時の成績係数は、（外気からの吸熱分）＋（圧縮機所要動力）＋（ガスエンジン温水出力）を投入一次エネルギーで割った値（１１８＋３２＋５０＝２００％）まで高めることができる。この計算値は、現在出願人らが製造しているヒートポンプシステムのカタログ値を参考にしたものであり、この例では、暖房出力９５kＷに対して、燃料であるのガス消費量の値が６４．８ｋＷであり、このクラスのガスエンジンの軸端効率を仮に３２％（ＨＨＶ）とすると、軸端出力に対するヒートポンプのＣＯＰは ９５/（６４．８×０．３２）＝４．６程度となる。ガス消費量を１００とすれば、外気からもらう熱：６８、冷媒の蒸発に役だつエンジン排熱：５０、エンジン軸出力：３２となり、５０＋６８＝１１８ が蒸発器がもらう熱となり、ヒートポンプの暖房ＣＯＰは 上述のように（１１８＋３２）/３２＝４．７となる。 The discharge refrigerant gas temperature at the compressor outlet depends on the compression ratio determined by the outside air temperature, the indoor heating set temperature, the heating heat load, the heat exchanger heat transfer performance, etc., and the efficiency of the compressor. If the degree of superheat of the refrigerant is 5 ° C. and the temperature of the indoor blowing hot air is 35 ° C., it is approximately 65 ° C.
If the refrigerant gas at the outlet of the compressor can be heated with the previous hot water, the coefficient of performance at the time of heating is calculated by dividing (heat absorption from the outside air) + (compressor power requirement) + (gas engine hot water output) by the input primary energy. The value can be increased to (118 + 32 + 50 = 200%). This calculated value is based on the catalog value of the heat pump system currently manufactured by the applicants. In this example, the value of gas consumption as fuel is 64.000 for a heating output of 95 kW. If the shaft end efficiency of this class of gas engine is 32% (HHV), the COP of the heat pump with respect to the shaft end output is about 95 / (64.8 × 0.32) = 4.6. If the gas consumption is 100, the heat received from the outside air is 68, the engine exhaust heat that is useful for the evaporation of the refrigerant is 50, the engine shaft output is 32, 50 + 68 = 118 is the heat that the evaporator receives, and the heating COP of the heat pump is As described above, (118 + 32) /32=4.7.

しかし、圧縮機の出口における吐出冷媒ガス温度が高いため、ガスエンジンの温水出力の一部しか冷媒の加熱に使えず、そのためシステムを簡略化するため、図３に示した特許文献１に開示の技術の如く、ガスエンジンの温水出力は、冷媒の蒸発熱源の一部として利用されている。
この場合、外気から得る冷媒蒸発熱は、投入一次エネルギーの約６８％であり、このシステムの成績係数は、（６８）＋（５０）＋（３２）の１５０％、また圧縮機の導入動力に対する成績係数は、１５０／３２＝４．７となる。 However, since the discharge refrigerant gas temperature at the outlet of the compressor is high, only a part of the hot water output of the gas engine can be used for heating the refrigerant. Therefore, in order to simplify the system, it is disclosed in Patent Document 1 shown in FIG. As in the art, the hot water output of a gas engine is used as part of the refrigerant evaporation heat source.
In this case, the refrigerant evaporative heat obtained from the outside air is about 68% of the input primary energy, and the coefficient of performance of this system is 150% of (68) + (50) + (32), and the introduction power of the compressor. The coefficient of performance is 150/32 = 4.7.

さらに外気から熱を得るには、通常外気温度より１０℃〜１５℃温度を下げた冷媒蒸発温度（外気５℃なら−１０℃前後）として、蒸発器の出口ではほぼ乾きガスにする必要がある。そのためこの冷媒蒸発温度は、電子膨張弁により圧縮機吸い込み圧力にリンクして制御されている。   Furthermore, in order to obtain heat from the outside air, it is necessary to make the gas almost dry at the outlet of the evaporator as the refrigerant evaporation temperature (about -10 ° C if the outside air is 5 ° C), which is usually 10 ° C to 15 ° C lower than the outside air temperature. . Therefore, the refrigerant evaporation temperature is controlled by being linked to the compressor suction pressure by an electronic expansion valve.

一方、ガスエンジンの最高８５℃の導入温水は、前述の−１０℃前後の冷媒の蒸発に用いられ、大きな温度差で熱交換ができ、伝熱面積を小さくできる反面、熱の有効活用の点では非常に無駄な利用形態となっている。   On the other hand, the hot water introduced at a maximum of 85 ° C in the gas engine is used for the evaporation of the above-mentioned refrigerant at around -10 ° C, and heat exchange can be performed with a large temperature difference and the heat transfer area can be reduced. Then, it is a very useless form of use.

従って、本願の目的は、燃焼機関の運転に従って発生する排熱を温水として回収し、当該温水が保有する熱を、当該燃焼機関から発生される動力により駆動される圧縮機を備えたヒートポンプサイクルにおいて充分利用でき、暖房運転において可能な限り高い成績係数を得ることができるヒートポンプシステムを得ることにある。   Therefore, an object of the present application is to recover exhaust heat generated in accordance with the operation of the combustion engine as hot water, and in a heat pump cycle including a compressor driven by power generated from the combustion engine. An object of the present invention is to obtain a heat pump system that can be used sufficiently and can obtain a coefficient of performance as high as possible in heating operation.

上記目的を達成するための、
燃焼機関により発生される駆動力により運転される圧縮機を冷媒循環路に備え、前記圧縮機により冷媒を圧縮して凝縮器に送り当該凝縮器で熱を放出するとともに、前記凝縮器から冷媒を膨張弁、蒸発器に送り、前記蒸発器で受熱して、前記圧縮機に戻るヒートポンプサイクルを備え、
前記燃焼機関により発生する排熱を温水として回収して、前記冷媒循環路を流れる冷媒に与える排熱熱交換器を備え、
前記圧縮機と前記凝縮器との間に前記排熱熱交換器を備え、
前記冷媒が前記圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環して前記圧縮機に戻るヒートポンプシステムであって、
前記排熱熱交換器から前記燃焼機関に戻る熱媒としての冷却水の温度を検出する戻り熱媒温度検出手段と、
前記膨張弁の開度を調整する開度調整手段とを備え、
前記戻り熱媒温度検出手段により検出される前記熱媒の温度に基づいて、前記開度調整手段を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段を備え、
前記排熱熱交換器への冷媒の温度を検出する冷媒温度検出手段と、
前記圧縮機であるスクロール式圧縮機の回転速度を調整する回転速度調整手段とを備え、
前記冷媒温度検出手段により検出される冷媒の温度に基づいて、前記回転速度調整手段を働かせて、前記排熱熱交換器に入る冷媒温度を目標温度に制御する第２制御手段を備え、
前記冷媒を、スクロール式圧縮機でのみ、当該圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環させる構成で、
前記第１制御手段による戻り熱媒温度制御、及び前記第２制御手段による冷媒温度制御により、前記蒸発器の出口及び前記圧縮機の出口における冷媒の状態を乾き度が１未満の気液混相状態とし、前記排熱熱交換器の出口における冷媒の状態を乾き度が１を超える過熱状態とすることを特徴とする。 To achieve the above purpose,
A compressor operated by a driving force generated by a combustion engine is provided in the refrigerant circulation path, the refrigerant is compressed by the compressor, sent to a condenser, heat is released from the condenser, and the refrigerant is discharged from the condenser. An expansion valve, a heat pump cycle that sends to the evaporator, receives heat at the evaporator, and returns to the compressor ;
An exhaust heat exchanger that recovers exhaust heat generated by the combustion engine as hot water and gives it to the refrigerant flowing through the refrigerant circulation path,
The exhaust heat exchanger is provided between the compressor and the condenser,
A heat pump system in which the refrigerant circulates in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator and returns to the compressor;
Return heat medium temperature detecting means for detecting the temperature of cooling water as a heat medium returning from the exhaust heat exchanger to the combustion engine;
Opening degree adjusting means for adjusting the opening degree of the expansion valve;
Based on the temperature of the heat medium detected by the return heat medium temperature detection means, the opening degree adjusting means is operated, and a first control means for controlling the return heat medium temperature to a target temperature is provided,
Refrigerant temperature detection means for detecting the temperature of the refrigerant to the exhaust heat exchanger;
A rotation speed adjusting means for adjusting the rotation speed of the scroll compressor as the compressor;
Based on the temperature of the refrigerant detected by the refrigerant temperature detection means, the second speed control means for controlling the refrigerant temperature entering the exhaust heat exchanger to a target temperature by operating the rotation speed adjustment means,
In the configuration in which the refrigerant is circulated in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator only in the scroll compressor.
By the return heat medium temperature control by the first control means and the refrigerant temperature control by the second control means, the state of the refrigerant at the outlet of the evaporator and the outlet of the compressor is a gas-liquid mixed phase state with a dryness of less than 1 And the state of the refrigerant at the outlet of the exhaust heat exchanger is an overheated state in which the dryness exceeds 1 .

このヒートポンプシステムでは、燃焼機関から回収した排熱を従来構成のように蒸発器から出た冷媒の蒸発・過熱に利用するのではなく、圧縮機による圧縮を終えた後の冷媒の蒸発・過熱に利用する。
即ち、蒸発器、圧縮機及び排熱熱交換器の入口まで気液混相状態で運転する。 In this heat pump system, the exhaust heat recovered from the combustion engine is not used for evaporation / overheating of the refrigerant discharged from the evaporator as in the conventional configuration, but for evaporation / overheating of the refrigerant after compression by the compressor. Use.
That is, it operates in a gas-liquid mixed phase state to the inlets of the evaporator, the compressor and the exhaust heat exchanger.

例えば、安定運転時の蒸発器出口冷媒のクオリティー（乾き度）を０．８５前後とする。この使用状態では、蒸発器管内を流れる冷媒は、常に二相流の状態であり、これまでの蒸発器出口を常に乾きガスまで昇温する運転に比べて、循環量を増やす効果も相まって、伝熱性能が高められ、圧縮機の吸い込み圧力を高めることができる。さらに、付加的効果として、これにより冬季の着霜を防止することが可能となる。   For example, the quality (dryness) of the evaporator outlet refrigerant during stable operation is set to about 0.85. In this state of use, the refrigerant flowing in the evaporator pipe is always in a two-phase flow state, which is combined with the effect of increasing the circulation rate compared to the operation in which the evaporator outlet is always heated to dry gas. Thermal performance is increased and the suction pressure of the compressor can be increased. Furthermore, as an additional effect, this makes it possible to prevent winter frosting.

また、圧縮後の冷媒の飽和温度を３０℃前後と設定しても、凝縮器に導入される冷媒温度は約７５℃まで昇温でき、その吹き出し温風温度を高めることができ、従来システムで得られる同じ温風温度を低い圧縮比で実現でき、圧縮機の効率向上にも寄与して導入動力に対する成績係数を高めることができる。すなわち圧縮比を下げることで前記の成績係数を４．７から５．５に上げることができ、（５．５×３２＝１７６）＋（５０）となり、投入一次エネルギー比２２６％と現行の約１．５１１８倍の暖房能力を得ることができる。   Even if the saturation temperature of the compressed refrigerant is set to around 30 ° C., the temperature of the refrigerant introduced into the condenser can be raised to about 75 ° C., and the temperature of the blown hot air can be increased. The same hot air temperature obtained can be realized at a low compression ratio, contributing to an improvement in the efficiency of the compressor and increasing the coefficient of performance for the introduction power. In other words, by reducing the compression ratio, the coefficient of performance can be increased from 4.7 to 5.5, which is (5.5 × 32 = 176) + (50), and the input primary energy ratio is 226%, which is about the current level. A heating capacity of 1.5118 times can be obtained.

ここで、圧縮機はスクロール式圧縮機とする。
気液混相状態の冷媒を良好に圧縮できるためである。 Here, the compressor is a scroll compressor.
This is because the gas-liquid mixed phase refrigerant can be compressed well.

このような構成のヒートポンプシステムにおいて、その運転制御に関して、以下の構成を有することとする。
１ 燃焼機関に戻る熱媒温度の制御
燃焼機関に戻る熱媒温度の制御は、下記の構成を採用することで実現できる。
即ち、排熱熱交換器から燃焼機関に戻る熱媒としての冷却水の温度を検出する戻り熱媒温度検出手段と、膨張弁の開度を調整する開度調整手段とを備え、
戻り熱媒温度検出手段により検出される熱媒の温度に基づいて、開度調整手段を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段を備える。
この構成にあっては、燃焼機関に戻る熱媒の温度を、ヒートポンプサイクルに備えられる膨張弁の開度調整で、容易に行うことができる。ここで、膨張弁を開側に操作することで、熱媒戻り温度を低下させることができ、膨張弁を閉側に操作することで、熱媒戻り温度を上昇させることができる。 In such a configuration of a heat pump system, for its operation control, and have the following configuration.
1 Control of heat medium temperature returning to the combustion engine Control of the heat medium temperature returning to the combustion engine can be realized by adopting the following configuration.
That is, a return heat medium temperature detection means for detecting the temperature of cooling water as a heat medium returning from the exhaust heat exchanger to the combustion engine, and an opening degree adjustment means for adjusting the opening degree of the expansion valve,
Based on the temperature of the heat medium detected by the return heat medium temperature detection means, a first control means for controlling the return heat medium temperature to the target temperature by operating the opening degree adjustment means.
With this configuration, the temperature of the heat medium that returns to the combustion engine can be easily adjusted by adjusting the opening of the expansion valve provided in the heat pump cycle. Here, by operating the expansion valve to the open side, the heat medium return temperature can be lowered, and by operating the expansion valve to the close side, the heat medium return temperature can be raised.

２ 燃焼機関に戻る熱媒温度の制御
排熱熱交換器へ導入される冷媒温度の制御は、下記の構成を採用することで実現できる。
即ち、排熱熱交換器への冷媒の温度を検出する冷媒温度検出手段と、
圧縮機であるスクロール式圧縮機の回転速度を調整する回転速度調整手段とを備え、
冷媒温度検出手段により検出される冷媒の温度に基づいて、回転速度調整手段を働かせて、排熱熱交換器に入る冷媒温度を目標温度に制御する第２制御手段を備える。
この構成にあっては、ヒートポンプサイクルに備えられる圧縮機の回転速度制御で、排熱熱交換器への冷媒の温度を容易に制御できる。ここで、回転速度を上昇させることで、冷媒の温度を上昇させることができ、回転速度を低下させることで、冷媒の温度を下降させることができる。 2 Control of the temperature of the heating medium returning to the combustion engine Control of the temperature of the refrigerant introduced into the exhaust heat exchanger can be realized by adopting the following configuration.
That is, a refrigerant temperature detecting means for detecting the temperature of the refrigerant to the exhaust heat exchanger,
A rotation speed adjusting means for adjusting the rotation speed of a scroll compressor that is a compressor;
Based on the temperature of the refrigerant detected by the refrigerant temperature detecting means, a second control means is provided for controlling the refrigerant temperature entering the exhaust heat exchanger to a target temperature by operating the rotation speed adjusting means.
In this configuration, the temperature of the refrigerant to the exhaust heat exchanger can be easily controlled by controlling the rotational speed of the compressor provided in the heat pump cycle. Here, the temperature of the refrigerant can be increased by increasing the rotation speed, and the temperature of the refrigerant can be decreased by decreasing the rotation speed.

本願に係る、これまで説明してきたヒートポンプシステムでは、蒸発器の出口及び前記圧縮機の出口における冷媒の状態を乾き度が１未満の気液混相状態とし、前記排熱熱交換器の出口における冷媒の状態を乾き度が１以上の気相状態とする。
またその運転方法としては、燃焼機関により発生される駆動力により運転される圧縮機を冷媒循環路に備え、前記圧縮機により冷媒を圧縮して凝縮器に送り当該凝縮器で熱を放出するとともに、前記凝縮器から冷媒を膨張弁、蒸発器に送り、前記蒸発器で受熱して、前記圧縮機に戻るヒートポンプサイクルを備え、
前記燃焼機関により発生する排熱を温水として回収して、前記冷媒循環路を流れる冷媒に与える排熱熱交換器を備え、
前記圧縮機と前記凝縮器との間に前記排熱熱交換器を備え、
前記冷媒が前記圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環して前記圧縮機に戻るヒートポンプシステムの運転方法であって、
前記排熱熱交換器から前記燃焼機関に戻る熱媒としての冷却水の温度を検出する戻り熱媒温度検出手段と、前記膨張弁の開度を調整する開度調整手段とを備え、
前記戻り熱媒温度検出手段により検出される前記熱媒の温度に基づいて、前記開度調整手段を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段を備え、
前記排熱熱交換器への冷媒の温度を検出する冷媒温度検出手段と、
前記圧縮機であるスクロール式圧縮機の回転速度を調整する回転速度調整手段とを備え、前記冷媒温度検出手段により検出される冷媒の温度に基づいて、前記回転速度調整手段を働かせて、前記排熱熱交換器に入る冷媒温度を目標温度に制御する第２制御手段を備え、前記冷媒を、スクロール式圧縮機でのみ、当該圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環させる構成に前記ヒートポンプシステムを構成し、
前記第１制御手段による戻り熱媒温度制御、及び前記第２制御手段による冷媒温度制御により、前記蒸発器の出口及び前記圧縮機の出口における冷媒の状態を乾き度を１未満の気液混相状態とし、前記排熱熱交換器の出口における冷媒の状態を乾き度が１を超える過熱状態として当該ヒートポンプシステムを運転することとなる。
結果、前記排熱熱交換器の出口における冷媒の状態を乾き度が１以上の気相状態とすることで、成績係数の高い運転を実現できる。 In the heat pump system described so far according to the present application, the state of the refrigerant at the outlet of the evaporator and the outlet of the compressor is changed to a gas-liquid mixed phase with a dryness of less than 1, and the refrigerant at the outlet of the exhaust heat exchanger Is a gas phase state having a dryness of 1 or more.
In addition, as a method of operation, a compressor operated by a driving force generated by a combustion engine is provided in a refrigerant circulation path, the refrigerant is compressed by the compressor, sent to a condenser, and heat is released by the condenser. A heat pump cycle that sends refrigerant from the condenser to an expansion valve and an evaporator, receives heat by the evaporator, and returns to the compressor;
An exhaust heat exchanger that recovers exhaust heat generated by the combustion engine as hot water and gives it to the refrigerant flowing through the refrigerant circulation path,
The exhaust heat exchanger is provided between the compressor and the condenser,
The operation method of the heat pump system in which the refrigerant circulates in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator and returns to the compressor,
A return heat medium temperature detecting means for detecting the temperature of cooling water as a heat medium returning to the combustion engine from the exhaust heat exchanger, and an opening degree adjusting means for adjusting the opening degree of the expansion valve,
Based on the temperature of the heat medium detected by the return heat medium temperature detection means, the opening degree adjusting means is operated, and a first control means for controlling the return heat medium temperature to a target temperature is provided,
Refrigerant temperature detection means for detecting the temperature of the refrigerant to the exhaust heat exchanger;
A rotation speed adjusting means for adjusting the rotation speed of the scroll compressor as the compressor, and based on the refrigerant temperature detected by the refrigerant temperature detecting means, the rotation speed adjusting means is operated to 2nd control means which controls the refrigerant | coolant temperature which enters into a heat-heat exchanger to target temperature, The said refrigerant | coolant is only a scroll type compressor, the said compressor, the said exhaust heat heat exchanger, the said condenser, the said expansion valve The heat pump system is configured to circulate in the order of the evaporator,
By the return heat medium temperature control by the first control means and the refrigerant temperature control by the second control means, the state of the refrigerant at the outlet of the evaporator and the outlet of the compressor is a gas-liquid mixed phase state with a dryness of less than 1 Then, the heat pump system is operated with the state of the refrigerant at the outlet of the exhaust heat exchanger as an overheated state where the dryness exceeds 1.
As a result, an operation with a high coefficient of performance can be realized by setting the state of the refrigerant at the outlet of the exhaust heat exchanger to a gas phase state with a dryness of 1 or more.

本発明に係るヒートポンプシステムの概略構成を示す構成図。The block diagram which shows schematic structure of the heat pump system which concerns on this invention. 本発明及び従来に係るヒートポンプシステムのエンタルピー−圧力線図及び温度線図。The enthalpy-pressure diagram and temperature diagram of the heat pump system according to the present invention and the related art. 従来技術に係るヒートポンプシステムの概略構成を示す構成図。The block diagram which shows schematic structure of the heat pump system which concerns on a prior art.

以下、図面に基づいて、本願に係るヒートポンプシステムの構成を説明する。
図１に示すように、燃焼機関であるガスエンジン１により発生される駆動力により運転される圧縮機２を冷媒循環路Ｌ１に備え、圧縮機２により冷媒を圧縮して凝縮器である室内熱交換器１１に送り当該室内熱交換器１１で熱を放出するとともに、室内熱交換器１１から冷媒を膨張弁である電子膨張弁３、蒸発器である室外熱交換器４に送り、この室外熱交換器４で受熱して、圧縮機２に戻るヒートポンプサイクルを備えて構成されている。
さらに、ガスエンジン１は、排熱熱交換器５との間で冷却水が循環される構成が採用されており、熱媒であるエンジン冷却水をガスエンジンの冷却ジャケット１５と排熱熱交換器５との間で循環させる冷却水循環路Ｌ２を備えており、当該エンジン冷却水によりガスエンジン１により発生する排熱を回収して、冷媒循環路Ｌ１を流れる冷媒に与えることが可能となっている。 Hereinafter, the configuration of the heat pump system according to the present application will be described based on the drawings.
As shown in FIG. 1, a compressor 2 that is operated by a driving force generated by a gas engine 1 that is a combustion engine is provided in the refrigerant circulation path L1, and the refrigerant is compressed by the compressor 2 so that the indoor heat that is a condenser. The heat is sent to the exchanger 11 to release the heat from the indoor heat exchanger 11, and the refrigerant is sent from the indoor heat exchanger 11 to the electronic expansion valve 3 as an expansion valve and the outdoor heat exchanger 4 as an evaporator. A heat pump cycle that receives heat by the exchanger 4 and returns to the compressor 2 is provided.
Further, the gas engine 1 adopts a configuration in which cooling water is circulated between the exhaust heat exchanger 5 and the engine coolant that is a heat medium is used as the gas engine cooling jacket 15 and the exhaust heat exchanger. The cooling water circulation path L2 circulated between the engine 5 and the exhaust gas generated by the gas engine 1 is recovered by the engine cooling water and can be given to the refrigerant flowing through the refrigerant circulation path L1. .

本発明に係るヒートポンプシステムでは、図１に示すように、圧縮機２と室内熱交換器１１との間に排熱熱交換器５を備え、冷媒循環路Ｌ１において、冷媒が圧縮機２、排熱熱交換器５、室内熱交換器１１、電子膨張弁３、室外熱交換器４の順に循環して圧縮機２に戻る構成が採用されている。   In the heat pump system according to the present invention, as shown in FIG. 1, an exhaust heat exchanger 5 is provided between the compressor 2 and the indoor heat exchanger 11, and in the refrigerant circuit L 1, the refrigerant is discharged from the compressor 2 and the exhaust heat exchanger 5. A configuration is adopted in which the heat heat exchanger 5, the indoor heat exchanger 11, the electronic expansion valve 3, and the outdoor heat exchanger 4 are circulated in order and returned to the compressor 2.

ここで、本願においては、圧縮機２としてスクロール式圧縮機を採用している。このようにスクロール式圧縮機を採用している理由は、冷媒が気液混相状態にあっても、その良好な圧縮駆動が可能となるためである。   Here, in the present application, a scroll compressor is employed as the compressor 2. The reason why the scroll compressor is employed in this way is that good compression driving is possible even when the refrigerant is in a gas-liquid mixed phase state.

さらに、このヒートポンプシステムには制御装置７が備えられており、この制御装置７によりヒートポンプサイクルの運転状態および冷却水サイクルの運転状態を制御できるように構成されている。具体的には、ヒートポンプサイクルに関しては、このサイクルに備えられる圧縮機２の回転速度、電子膨張弁３の開度を制御可能とされており、冷却水サイクルに関しては、このサイクルに備えられる循環ポンプ６の回転速度を制御可能とされている。
前記圧縮機２の回転速度は、制御装置７に備えられる回転速度調整手段７１により調整される。一方、電子膨張弁３の開度は、制御装置７に備えられる開度調整手段７２により調整される。これらは、これまでのヒートポンプシステムにおける制御構成と変わることはない。 Further, the heat pump system is provided with a control device 7, which is configured to be able to control the operation state of the heat pump cycle and the operation state of the cooling water cycle. Specifically, with respect to the heat pump cycle, the rotational speed of the compressor 2 provided in this cycle and the opening degree of the electronic expansion valve 3 can be controlled. With respect to the cooling water cycle, the circulation pump provided in this cycle. 6 can be controlled.
The rotation speed of the compressor 2 is adjusted by a rotation speed adjusting means 71 provided in the control device 7. On the other hand, the opening degree of the electronic expansion valve 3 is adjusted by an opening degree adjusting means 72 provided in the control device 7. These are the same as the control configuration in the conventional heat pump system.

さて、本願に係るヒートポンプシステムには、本願独特の構成が採用されている。
図１に示すように、排熱熱交換器５からガスエンジン１に戻る冷却水の温度を検出する戻り熱媒温度検出手段Ｔ１が備えられている。そして、この戻り熱媒温度検出手段Ｔ１により検出される熱媒の温度に基づいて、開度調整手段７２を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段７３が備えられている。
ここで第１制御手段７３は、戻り熱媒温度が目標温度に対して低い場合に、電子膨張弁３を閉側に制御し、戻り熱媒温度が目標温度に対して高い場合に、電子膨張弁３を開側に制御する。 Now, the structure peculiar to this application is employ | adopted for the heat pump system which concerns on this application.
As shown in FIG. 1, return heat medium temperature detecting means T <b> 1 for detecting the temperature of the cooling water returning from the exhaust heat exchanger 5 to the gas engine 1 is provided. Then, based on the temperature of the heat medium detected by the return heat medium temperature detection means T1, first opening control means 73 is provided to control the return heat medium temperature to the target temperature by operating the opening degree adjustment means 72. Yes.
Here, the first control means 73 controls the electronic expansion valve 3 to be closed when the return heat medium temperature is lower than the target temperature, and when the return heat medium temperature is higher than the target temperature, the electronic expansion valve 3 The valve 3 is controlled to open.

図１に示すように、排熱熱交換器５への冷媒の温度を検出する冷媒温度検出手段Ｔ２が備えられている。そして、この冷媒温度検出手段Ｔ２により検出される冷媒の温度に基づいて、前記回転速度調整手段７１を働かせて、前記排熱熱交換器５に入る冷媒温度を目標温度に制御する第２制御手段７４が備えられている。
ここで第２制御手段７４は、冷媒温度が目標温度に対して低い場合に、圧縮機２の回転速度を増加側に制御し、冷媒温度が目標温度に対して高い場合に、圧縮機２の回転速度を低下側に制御する。 As shown in FIG. 1, a refrigerant temperature detecting means T <b> 2 for detecting the temperature of the refrigerant to the exhaust heat exchanger 5 is provided. Then, based on the refrigerant temperature detected by the refrigerant temperature detecting means T2, the rotation speed adjusting means 71 is operated to control the refrigerant temperature entering the exhaust heat exchanger 5 to a target temperature. 74 is provided.
Here, the second control means 74 controls the rotational speed of the compressor 2 to increase when the refrigerant temperature is lower than the target temperature, and when the refrigerant temperature is higher than the target temperature, Control the rotation speed to the lower side.

以下、図２に基づいて、本願に係るヒートポンプシステムと、従来構造に係るヒートポンプシステムとを比較して、その運転状態を説明する。
図２において、（ａ）がヒートポンプシステムのエンタルピー−圧力線図であり、（ｂ）が温度線図である。
これらの図において、実線で本願に係るヒートポンプシステムの状態を示し、一点鎖線で、従来のヒートポンプシステムの状態を示した。
本願に係るヒートポンプシステムに関して、圧縮機２における圧縮をＳ１−Ｓ２で、排熱熱交換器５における冷媒の加熱をＳ２−Ｓ３で、室内熱交換器１１における凝縮をＳ３−Ｓ４で、電子器膨張弁３における膨張をＳ４−Ｓ５で、室外熱交換器４における蒸発をＳ５−Ｓ１で示した。 Hereinafter, based on FIG. 2, the heat pump system which concerns on this application and the heat pump system which concerns on a conventional structure are compared, and the driving | running state is demonstrated.
In FIG. 2, (a) is an enthalpy-pressure diagram of a heat pump system, and (b) is a temperature diagram.
In these drawings, the state of the heat pump system according to the present application is indicated by a solid line, and the state of a conventional heat pump system is indicated by a one-dot chain line.
Regarding the heat pump system according to the present application, compression in the compressor 2 is S1-S2, heating of the refrigerant in the exhaust heat exchanger 5 is S2-S3, condensation in the indoor heat exchanger 11 is S3-S4, and electronic expansion The expansion in the valve 3 is denoted by S4-S5, and the evaporation in the outdoor heat exchanger 4 is denoted by S5-S1.

従来技術に係るヒートポンプシステムに関して、圧縮機６２における圧縮をｓ２−ｓ３で、室内熱交換器５１における凝縮をｓ３−ｓ４で、電子器膨張弁６３における膨張をｓ４−ｓ５で、室外熱交換器６４における蒸発をｓ５−ｓ１で、さらに、過熱器６５における蒸発後の過熱をｓ１−ｓ２で示した。   Regarding the heat pump system according to the prior art, compression in the compressor 62 is s2-s3, condensation in the indoor heat exchanger 51 is s3-s4, expansion in the electronic expansion valve 63 is s4-s5, outdoor heat exchanger 64 Evaporation in is indicated by s5-s1, and superheat after evaporation in the superheater 65 is indicated by s1-s2.

さらに、図２（ｂ）には、本願に係る排熱熱交換器５における熱媒であるエンジン冷却水の温度変化をＣ１−Ｃ２で、従来技術に係る排熱熱交換器６５における熱媒であるエンジン冷却水の温度変換をｃ１−ｃ２で示している。また、本願に係る室内熱交換器１１における室内気の温度変化をＲ１−Ｒ２で、従来技術に係る室内熱交換器５１における室内気の温度変換をｒ１−ｒ２で示している。   Further, FIG. 2 (b) shows the temperature change of engine cooling water, which is a heat medium in the exhaust heat exchanger 5 according to the present application, as C1-C2 and the heat medium in the exhaust heat exchanger 65 according to the prior art. The temperature conversion of a certain engine cooling water is indicated by c1-c2. Moreover, the temperature change of the indoor air in the indoor heat exchanger 11 which concerns on this application is shown by R1-R2, and the temperature conversion of the indoor air in the indoor heat exchanger 51 which concerns on a prior art is shown by r1-r2.

図２（ａ）から判明するように、本願に係るヒートポンプシステムでは、安定運転時の室外熱交換器（蒸発器）４の出口の冷媒のクオリティー（乾き度）を０．８５前後とする。結果、当該室外熱交換器４内の蒸発器管を流れる冷媒は、常に二相流の状態とできる。   As can be seen from FIG. 2A, in the heat pump system according to the present application, the quality (dryness) of the refrigerant at the outlet of the outdoor heat exchanger (evaporator) 4 during stable operation is set to about 0.85. As a result, the refrigerant flowing through the evaporator pipe in the outdoor heat exchanger 4 can always be in a two-phase flow state.

また、圧縮機２による圧縮後の冷媒の飽和温度を３０℃前後と設定しても、室内熱交換器（凝縮器１１）に導入される冷媒温度は約７５℃まで昇温できるので、室内熱交換器１１の吹き出し温風温度を高めることができ、従来システムで得られる同じ温風温度を低い圧縮比で実現でき、圧縮機の効率向上にも寄与して導入動力に対する成績係数を高めることができることとなった。   Even if the saturation temperature of the refrigerant compressed by the compressor 2 is set to around 30 ° C., the refrigerant temperature introduced into the indoor heat exchanger (condenser 11) can be raised to about 75 ° C. The temperature of the hot air blown from the exchanger 11 can be increased, the same hot air temperature obtained in the conventional system can be realized at a low compression ratio, and the coefficient of performance for the introduction power can be increased by contributing to the improvement of the efficiency of the compressor. I was able to do it.

燃焼機関の運転に従って発生する排熱を温水として回収し、当該温水が保有する熱を、当該燃焼機関から発生される動力により駆動される圧縮機を備えたヒートポンプサイクルにおいて充分利用でき、暖房運転において可能な限り高い成績係数を得ることができるヒートポンプシステムを得ることができた。   The exhaust heat generated according to the operation of the combustion engine is recovered as warm water, and the heat held by the warm water can be sufficiently utilized in a heat pump cycle including a compressor driven by power generated from the combustion engine. A heat pump system capable of obtaining the highest possible coefficient of performance could be obtained.

１ ガスエンジン
２ 圧縮器
３ 電子膨張弁
４ 室外熱交換器
５ 排熱熱交換器
１１ 室内熱交換器
７ 制御装置
７１ 回転速度調整手段
７２ 開度調整手段
７３ 第１制御手段
７４ 第２制御手段
Ｔ１ 熱媒温度検出手段
Ｔ２ 冷媒温度検出手段 DESCRIPTION OF SYMBOLS 1 Gas engine 2 Compressor 3 Electronic expansion valve 4 Outdoor heat exchanger 5 Exhaust heat exchanger 11 Indoor heat exchanger 7 Controller 71 Rotational speed adjusting means 72 Opening adjusting means 73 First control means 74 Second control means T1 Heat medium temperature detection means T2 Refrigerant temperature detection means

Claims (2)

燃焼機関により発生される駆動力により運転される圧縮機を冷媒循環路に備え、前記圧縮機により冷媒を圧縮して凝縮器に送り当該凝縮器で熱を放出するとともに、前記凝縮器から冷媒を膨張弁、蒸発器に送り、前記蒸発器で受熱して、前記圧縮機に戻るヒートポンプサイクルを備え、
前記燃焼機関により発生する排熱を温水として回収して、前記冷媒循環路を流れる冷媒に与える排熱熱交換器を備え、
前記圧縮機と前記凝縮器との間に前記排熱熱交換器を備え、
前記冷媒が前記圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環して前記圧縮機に戻るヒートポンプシステムであって、
前記排熱熱交換器から前記燃焼機関に戻る熱媒としての冷却水の温度を検出する戻り熱媒温度検出手段と、
前記膨張弁の開度を調整する開度調整手段とを備え、
前記戻り熱媒温度検出手段により検出される前記熱媒の温度に基づいて、前記開度調整手段を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段を備え、
前記排熱熱交換器への冷媒の温度を検出する冷媒温度検出手段と、
前記圧縮機であるスクロール式圧縮機の回転速度を調整する回転速度調整手段とを備え、
前記冷媒温度検出手段により検出される冷媒の温度に基づいて、前記回転速度調整手段を働かせて、前記排熱熱交換器に入る冷媒温度を目標温度に制御する第２制御手段を備え、
前記冷媒を、スクロール式圧縮機でのみ、当該圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環させる構成で、
前記第１制御手段による戻り熱媒温度制御、及び前記第２制御手段による冷媒温度制御により、前記蒸発器の出口及び前記圧縮機の出口における冷媒の状態を乾き度が１未満の気液混相状態とし、前記排熱熱交換器の出口における冷媒の状態を乾き度が１を超える過熱状態とするヒートポンプシステム。 A compressor operated by a driving force generated by a combustion engine is provided in the refrigerant circulation path, the refrigerant is compressed by the compressor, sent to a condenser, heat is released from the condenser, and the refrigerant is discharged from the condenser. An expansion valve, a heat pump cycle that sends to the evaporator, receives heat at the evaporator, and returns to the compressor;
An exhaust heat exchanger that recovers exhaust heat generated by the combustion engine as hot water and gives it to the refrigerant flowing through the refrigerant circulation path,
The exhaust heat exchanger is provided between the compressor and the condenser,
A heat pump system in which the refrigerant circulates in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator and returns to the compressor;
Return heat medium temperature detecting means for detecting the temperature of cooling water as a heat medium returning from the exhaust heat exchanger to the combustion engine;
Opening degree adjusting means for adjusting the opening degree of the expansion valve;
Based on the temperature of the heat medium detected by the return heat medium temperature detection means, the opening degree adjusting means is operated, and a first control means for controlling the return heat medium temperature to a target temperature is provided,
Refrigerant temperature detection means for detecting the temperature of the refrigerant to the exhaust heat exchanger;
A rotation speed adjusting means for adjusting the rotation speed of the scroll compressor as the compressor;
Based on the temperature of the refrigerant detected by the refrigerant temperature detection means, the second speed control means for controlling the refrigerant temperature entering the exhaust heat exchanger to a target temperature by operating the rotation speed adjustment means,
In the configuration in which the refrigerant is circulated in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator only in the scroll compressor.
By the return heat medium temperature control by the first control means and the refrigerant temperature control by the second control means, the state of the refrigerant at the outlet of the evaporator and the outlet of the compressor is a gas-liquid mixed phase state with a dryness of less than 1 And a heat pump system in which the state of the refrigerant at the outlet of the exhaust heat exchanger is set to an overheated state in which the dryness exceeds 1 . 燃焼機関により発生される駆動力により運転される圧縮機を冷媒循環路に備え、前記圧縮機により冷媒を圧縮して凝縮器に送り当該凝縮器で熱を放出するとともに、前記凝縮器から冷媒を膨張弁、蒸発器に送り、前記蒸発器で受熱して、前記圧縮機に戻るヒートポンプサイクルを備え、A compressor operated by a driving force generated by a combustion engine is provided in the refrigerant circulation path, the refrigerant is compressed by the compressor, sent to a condenser, heat is released from the condenser, and the refrigerant is discharged from the condenser. An expansion valve, a heat pump cycle that sends to the evaporator, receives heat at the evaporator, and returns to the compressor;
前記燃焼機関により発生する排熱を温水として回収して、前記冷媒循環路を流れる冷媒に与える排熱熱交換器を備え、  An exhaust heat exchanger that recovers exhaust heat generated by the combustion engine as hot water and gives it to the refrigerant flowing through the refrigerant circulation path,
前記圧縮機と前記凝縮器との間に前記排熱熱交換器を備え、  The exhaust heat exchanger is provided between the compressor and the condenser,
前記冷媒が前記圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環して前記圧縮機に戻るヒートポンプシステムの運転方法であって、  The operation method of the heat pump system in which the refrigerant circulates in the order of the compressor, the exhaust heat exchanger, the condenser, the expansion valve, and the evaporator and returns to the compressor,
前記排熱熱交換器から前記燃焼機関に戻る熱媒としての冷却水の温度を検出する戻り熱媒温度検出手段と、前記膨張弁の開度を調整する開度調整手段とを備え、  A return heat medium temperature detecting means for detecting the temperature of cooling water as a heat medium returning to the combustion engine from the exhaust heat exchanger, and an opening degree adjusting means for adjusting the opening degree of the expansion valve,
前記戻り熱媒温度検出手段により検出される前記熱媒の温度に基づいて、前記開度調整手段を働かせて、戻り熱媒温度を目標温度に制御する第１制御手段を備え、  Based on the temperature of the heat medium detected by the return heat medium temperature detection means, the opening degree adjusting means is operated, and a first control means for controlling the return heat medium temperature to a target temperature is provided,
前記排熱熱交換器への冷媒の温度を検出する冷媒温度検出手段と、  Refrigerant temperature detection means for detecting the temperature of the refrigerant to the exhaust heat exchanger;
前記圧縮機であるスクロール式圧縮機の回転速度を調整する回転速度調整手段とを備え、前記冷媒温度検出手段により検出される冷媒の温度に基づいて、前記回転速度調整手段を働かせて、前記排熱熱交換器に入る冷媒温度を目標温度に制御する第２制御手段を備え、前記冷媒を、スクロール式圧縮機でのみ、当該圧縮機、前記排熱熱交換器、前記凝縮器、前記膨張弁、前記蒸発器の順に循環させる構成に前記ヒートポンプシステムを構成し、  A rotation speed adjusting means for adjusting the rotation speed of the scroll compressor as the compressor, and based on the refrigerant temperature detected by the refrigerant temperature detecting means, the rotation speed adjusting means is operated to 2nd control means which controls the refrigerant | coolant temperature which enters into a heat-heat exchanger to target temperature, The said refrigerant | coolant is only a scroll type compressor, the said compressor, the said exhaust heat heat exchanger, the said condenser, the said expansion valve The heat pump system is configured to circulate in the order of the evaporator,
前記第１制御手段による戻り熱媒温度制御、及び前記第２制御手段による冷媒温度制御により、前記蒸発器の出口及び前記圧縮機の出口における冷媒の状態を乾き度を１未満の気液混相状態とし、前記排熱熱交換器の出口における冷媒の状態を乾き度が１を超える過熱状態として当該ヒートポンプシステムを運転するヒートポンプシステムの運転方法。By the return heat medium temperature control by the first control means and the refrigerant temperature control by the second control means, the state of the refrigerant at the outlet of the evaporator and the outlet of the compressor is a gas-liquid mixed phase state with a dryness of less than 1 And a method of operating the heat pump system in which the state of the refrigerant at the outlet of the exhaust heat exchanger is overheated with a dryness exceeding 1.
JP2010053430A 2010-03-10 2010-03-10 Heat pump system Expired - Fee Related JP5571978B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2010053430A JP5571978B2 (en) 2010-03-10 2010-03-10 Heat pump system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2010053430A JP5571978B2 (en) 2010-03-10 2010-03-10 Heat pump system

Publications (2)

Publication Number Publication Date
JP2011185571A JP2011185571A (en) 2011-09-22
JP5571978B2 true JP5571978B2 (en) 2014-08-13

Family

ID=44792077

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2010053430A Expired - Fee Related JP5571978B2 (en) 2010-03-10 2010-03-10 Heat pump system

Country Status (1)

Country Link
JP (1) JP5571978B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013068405A (en) * 2011-09-09 2013-04-18 Osaka Gas Co Ltd Heat pump system and method of operating the same

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1021700B1 (en) * 2013-07-09 2016-01-11 P.T.I. DEVICE FOR ENERGY SAVING
CN111306834B (en) * 2020-03-30 2024-07-12 天津商业大学 Multifunctional heat pump module and air source heat pump system formed by same
CN114061125B (en) * 2020-07-30 2024-03-19 广东美的暖通设备有限公司 Control method and control device of air conditioning system, controller and air conditioning system

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5021763U (en) * 1973-06-20 1975-03-12
JPS5655571Y2 (en) * 1974-07-13 1981-12-25
JPS616557A (en) * 1984-06-21 1986-01-13 ヤンマーディーゼル株式会社 Engine heat pump device
JPS63105372A (en) * 1986-10-22 1988-05-10 株式会社日立製作所 Air conditioner
JPH10185349A (en) * 1996-12-18 1998-07-14 Matsushita Seiko Co Ltd Air conditioner
JP2001116392A (en) * 1999-10-12 2001-04-27 Aisin Seiki Co Ltd Air conditioner
JP4296741B2 (en) * 2002-01-28 2009-07-15 パナソニック電工株式会社 Cogeneration system
JP4288361B2 (en) * 2003-03-19 2009-07-01 ヤンマー株式会社 Control device for system with maintenance time notification function
JP4565923B2 (en) * 2004-08-03 2010-10-20 三洋電機株式会社 Air conditioner
JP2006250436A (en) * 2005-03-10 2006-09-21 Yanmar Co Ltd Engine-driven heat pump
JP2007225141A (en) * 2006-02-21 2007-09-06 Mitsubishi Heavy Ind Ltd Gas heat pump type air conditioner and its starting method
JP2007255771A (en) * 2006-03-22 2007-10-04 Denso Corp Ejector type cycle
JP4990677B2 (en) * 2007-05-17 2012-08-01 大阪瓦斯株式会社 Engine-driven heat pump device
JP5200593B2 (en) * 2008-03-13 2013-06-05 アイシン精機株式会社 Air conditioner

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013068405A (en) * 2011-09-09 2013-04-18 Osaka Gas Co Ltd Heat pump system and method of operating the same

Also Published As

Publication number Publication date
JP2011185571A (en) 2011-09-22

Similar Documents

Publication Publication Date Title
EP1884648B1 (en) Co-generation unit and control method of the same
US20080022707A1 (en) Co-generation
JP6852642B2 (en) Heat pump cycle
KR101270616B1 (en) Co-generation
US9175889B2 (en) Heat source system and control method thereof
JP2006170537A (en) Heat exchange system
JP5375919B2 (en) heat pump
JP2013148331A (en) Heat pump system
JP5571978B2 (en) Heat pump system
JP2007303806A (en) Refrigerating cycle device and its operation method
JP2007212024A (en) Refrigerating cycle device and its control method
CN107328002A (en) The air conditioner heat pump system and its working method of a kind of temperature control throttling
WO2013002018A1 (en) Rankine cycle
KR200412598Y1 (en) Heat pump system for having function of hot water supply
JP5907812B2 (en) Heat pump system and operation method thereof
KR20100005736U (en) Heat pump system
JP2006234321A (en) Outdoor unit and air conditioner
JP3933076B2 (en) Air conditioner
JP4857903B2 (en) Water heater
JP2013044239A (en) Exhaust heat recovery system for vehicle
JP5959327B2 (en) heat pump
KR101170712B1 (en) Using a gas engine heat pump geothermal heating and cooling systems
JP3871207B2 (en) Refrigeration system combining absorption and compression
JP2003336929A (en) Absorbing and compression type refrigerator and method of operating the refrigerator
KR100712858B1 (en) Control Method of Electric generation air condition system

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20121204

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20130919

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20131003

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20131202

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20140529

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20140627

R150 Certificate of patent or registration of utility model

Ref document number: 5571978

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

LAPS Cancellation because of no payment of annual fees