JPS616558A - Heat pump device - Google Patents
Heat pump deviceInfo
- Publication number
- JPS616558A JPS616558A JP59126417A JP12641784A JPS616558A JP S616558 A JPS616558 A JP S616558A JP 59126417 A JP59126417 A JP 59126417A JP 12641784 A JP12641784 A JP 12641784A JP S616558 A JPS616558 A JP S616558A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat
- heat exchanger
- pump device
- compressor
- 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.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims description 39
- 239000007788 liquid Substances 0.000 claims description 19
- 238000010438 heat treatment Methods 0.000 description 13
- 239000002918 waste heat Substances 0.000 description 12
- 238000001816 cooling Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 6
- 239000007789 gas Substances 0.000 description 6
- 238000010257 thawing Methods 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005202 decontamination Methods 0.000 description 1
- 230000003588 decontaminative effect Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000002351 wastewater Substances 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
-
- 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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔妾業上の利用分野〕
本発明は主としてエンジンでコンプレッサを駆動してい
るヒートポンプ装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention mainly relates to a heat pump device in which a compressor is driven by an engine.
従来の、ヒートポンプの最大の欠点は、低温時の暖房能
力の低下及び除霜のためにたびたび運転を停止すること
であるが、エンジンでコンプレッサを駆動してエアコン
ディショニンクヲ行なうヒートポンプ装置では、そのエ
ンジン廃熱を暖房用出力に入力するだめの手段として、
（１）温水ラジェータを別に室内に設ける、（２）ヒー
トポンプの低圧側に廃熱を入力する、（３）中間ガス・
インジエクンヨンシステムを用いる。 （４）フロン再
循環システムを用いることが行、なわれている。The biggest drawbacks of conventional heat pumps are a reduction in heating capacity at low temperatures and frequent shutdowns for defrosting. As a means of inputting waste heat into heating output,
(1) Install a separate hot water radiator indoors, (2) Input waste heat to the low-pressure side of the heat pump, (3) Intermediate gas
The Injie Kunyong system is used. (4) Freon recirculation systems are being used.
しかしながら、上記（１）の場合には、温水ラジェータ
の追加により、室内ユニットえの配管が二重となり、冬
期における水の凍結、空気抜き及び水抜きの手間、更に
は室内ユニットの大型化などの問題があり、また、上記
（２）の場合には、低圧側への廃熱利用によシ、低圧が
上昇し、外気からの熱吸収効率が大幅に低下してしまう
という欠点がある。However, in the case of (1) above, the addition of a hot water radiator results in double piping for the indoor unit, which causes problems such as freezing of water in winter, the hassle of air and water removal, and furthermore, an increase in the size of the indoor unit. In addition, in the case of (2) above, there is a drawback that the low pressure increases due to the utilization of waste heat on the low pressure side, and the efficiency of heat absorption from the outside air decreases significantly.
一方、上記（３）の場合には、コンプレッサに追加工事
を要し、汎用コンプレッサを利用できず、一般的でなく
、上記（４）の場合には、冷媒ガスポンプが大型化する
という欠点があった。On the other hand, in the case of (3) above, additional work is required on the compressor and a general-purpose compressor cannot be used, which is not common, and in the case of (4) above, the refrigerant gas pump becomes larger. Ta.
そこで本発明は、前記従来の問題点を解消するだめにな
されたものであり、エンジンの廃熱を利用して暖房能力
の向上をはかると共に、除昂熱源にもエンジンの廃熱が
利用可能なヒートポンプ装置を提供することを目的とし
たものである。Therefore, the present invention has been made to solve the above-mentioned conventional problems, and aims to improve the heating capacity by using the waste heat of the engine, and also makes it possible to use the waste heat of the engine as a source of decontamination heat. The purpose is to provide a heat pump device.
即ち、本発明はヒートポンプ装置の利用側熱交換器と熱
源側熱交換器との間の冷媒液を冷媒液ポンプにより昇圧
した後、冷媒加熱器経由コンプレッサの吐出部側と利用
側熱交換器との間に圧送する冷媒系路を配設することに
より構成される。That is, the present invention increases the pressure of the refrigerant liquid between the user-side heat exchanger and the heat source-side heat exchanger of a heat pump device using a refrigerant liquid pump, and then increases the pressure between the refrigerant liquid and the compressor discharge section and the user-side heat exchanger via a refrigerant heater. It is constructed by arranging a refrigerant system line for pumping the refrigerant between the two.
以下図面を参照して本発明の詳細な説明するが、第１図
、第２図及び第３図は本発明の一実施例におけるエンジ
ン駆動式のヒートポンプ装置による冷暖房ンステムの系
統図であり、第１図はその冷房モードの、第２図はその
暖房モードの、そして第３図は除霜モードの各状態を示
している。The present invention will be described in detail below with reference to the drawings. FIGS. 1, 2, and 3 are system diagrams of a heating and cooling system using an engine-driven heat pump device according to an embodiment of the present invention. FIG. 1 shows the cooling mode, FIG. 2 shows the heating mode, and FIG. 3 shows the defrosting mode.
まず、とのヒートポンプ装置は、エンジン１に軸継手２
４で連結されて駆動されるコンプレッサ８が設けられ、
このエンジン１には、排気ガス熱交換器２及び消音器３
が設けられ、更に、ラジェータ６に接続されたエンジノ
冷却水ライン７からエンジン冷却水ポンプ４を介して供
給された冷却水は、上記排気ガス熱交換器２から冷媒加
熱器１９を循環した後、サーモスタット５によりラジェ
ータ６側または直接エンジン冷却水ライン７に戻される
ようになっている。First, the heat pump device has an engine 1 and a shaft coupling 2.
A compressor 8 connected and driven by 4 is provided,
This engine 1 includes an exhaust gas heat exchanger 2 and a muffler 3.
Further, the cooling water supplied from the engine cooling water line 7 connected to the radiator 6 via the engine cooling water pump 4 is circulated from the exhaust gas heat exchanger 2 to the refrigerant heater 19, and then The thermostat 5 returns the water to the radiator 6 side or directly to the engine cooling water line 7.
一方、コンプレッサ８の吐出部側に設けられた四方弁１
７に接続された冷媒ライン２６には、室内ユニット９、
受液器１６、逆止弁１５付の暖房用膨張弁１４、室外側
熱交換器１６が設けられると共に、受液器１６とコンプ
レッサ８の吐出部側との間は、冷媒液ポンプ２０、逆止
弁２１、冷媒加熱器１９及び逆止弁２２を介して接続可
能になっている。On the other hand, a four-way valve 1 provided on the discharge part side of the compressor 8
The refrigerant line 26 connected to the indoor unit 9,
A liquid receiver 16, a heating expansion valve 14 with a check valve 15, and an outdoor heat exchanger 16 are provided, and a refrigerant liquid pump 20, a reverse Connection is possible via a stop valve 21, a refrigerant heater 19, and a check valve 22.
また、コンプレッサ８の流入部側にはアキュムレータ１
８が設けられると共に、上記室内ユニット９内には、逆
止弁１２付冷房用膨張弁１１及び室内側熱交換器１０が
設けられている。In addition, an accumulator 1 is provided on the inlet side of the compressor 8.
8 is provided, and in the indoor unit 9, an air conditioning expansion valve 11 with a check valve 12 and an indoor heat exchanger 10 are provided.
即ち、本発明のヒートポンプ装置では、利用側熱交換器
である室内側熱交換器１０と、熱源側熱交換器である室
外側熱交換器１６との間に設けられた受液器１６内の冷
媒液を冷媒液ポンプ２０により昇圧した後、冷媒加熱器
１９経由、コンプレッサ８の吐出部側と室内側熱交換器
比との間に圧送する冷媒系路を配設したものである。That is, in the heat pump device of the present invention, the liquid receiver 16 provided between the indoor heat exchanger 10, which is the utilization side heat exchanger, and the outdoor heat exchanger 16, which is the heat source side heat exchanger. A refrigerant system is provided in which the pressure of the refrigerant liquid is increased by the refrigerant pump 20 and then the refrigerant is pumped between the discharge section of the compressor 8 and the indoor heat exchanger ratio via the refrigerant heater 19.
上記の構成からなる本発明のヒートポンプ装置を冷房モ
ードで使用する際には、第１図の太線で示すごとく、冷
媒はコンプレッサ８の吐出部側から四方弁１７、室外側
熱交換器１６で放熱し、逆止弁１５、受液器１６から室
内ユニット９内の冷房用膨張弁１１から室内側熱交換器
１０で吸熱した後、冷媒ライン２６の四方弁１７、アキ
ュムレータ１８経由、コンプレッサ８の流入側に戻され
るが、この時の第１図の各点における圧力Ｐ及びエンタ
ルピー（１）を示したのが第４図のモリエル線図であり
、この冷房時においては、冷媒加熱器１９を通る冷媒系
路の冷媒液ポンプ２０はＯＦＦの状態にしている。When the heat pump device of the present invention having the above configuration is used in the cooling mode, as shown by the thick line in FIG. Then, after heat is absorbed by the indoor heat exchanger 10 from the check valve 15 and the liquid receiver 16 to the cooling expansion valve 11 in the indoor unit 9, the inflow of the compressor 8 is carried out via the four-way valve 17 of the refrigerant line 26 and the accumulator 18. The Mollier diagram in Figure 4 shows the pressure P and enthalpy (1) at each point in Figure 1 at this time. The refrigerant liquid pump 20 in the refrigerant system is turned off.
また、この七−トポンプ装置を暖房モードとして使用す
る場合は、冷媒は第２図の太線で示すごとく、コンプレ
ッサ８の吐出部側から冷媒ライン２３経由、室内側熱交
換器１０で放熱した後、逆止弁１２、受液器１３、暖房
用膨張弁１４経由、室外側熱交換器１６で吸熱した後、
四方弁１７、アキュムレータ１８経由、コンプレッサ８
の流入部側に戻されるが、この時、冷媒加熱器１９を通
る冷媒系路の冷媒液ボ／プ２０をＯＮの状態にすること
により、受液器１３内の冷媒液は冷媒加熱器１９で加熱
された後、コンプレッサ８の吐出部側と利用側熱交換器
である室内側熱交換器１０との間に圧送されることにな
り、エンジン１の廃熱を暖房に有効に利用することにな
る。In addition, when this seven-tooth pump device is used in the heating mode, the refrigerant radiates heat from the discharge section of the compressor 8 via the refrigerant line 23 in the indoor heat exchanger 10, as shown by the thick line in FIG. After absorbing heat in the outdoor heat exchanger 16 via the check valve 12, liquid receiver 13, and heating expansion valve 14,
Four-way valve 17, via accumulator 18, compressor 8
However, at this time, by turning on the refrigerant liquid valve 20 of the refrigerant system path passing through the refrigerant heater 19, the refrigerant liquid in the receiver 13 flows into the refrigerant heater 19. After being heated, the waste heat from the engine 1 is sent under pressure between the discharge part side of the compressor 8 and the indoor heat exchanger 10, which is a user-side heat exchanger, so that the waste heat of the engine 1 can be effectively used for heating. become.
そこで、この場合の第２図の各点における圧力（Ｐ）及
びエンタルピー（１）を第５図のモリエル線図で示して
おり、冷媒液ポンプ２０の吐出量はＧ２で示され、冷媒
液ポンプ２０の昇圧幅はＰＨ−ｐＤで示され、暖房能力
＝（Ｇ、十Ｇ２Ｌ（ｉＢｉｃ）で示され、更にエンジン
１からの回収廃熱利用量はＧ２（Ｉ＋−菫Ｈ）で示され
る。Therefore, the pressure (P) and enthalpy (1) at each point in FIG. 2 in this case are shown in the Mollier diagram in FIG. The pressure increase width of 20 is indicated by PH-pD, the heating capacity = (G, 10 G2L (iBic)), and the amount of recovered waste heat utilization from the engine 1 is indicated by G2 (I + - Violet H).
更に、このヒートポンプ装置が除霜モードに使用される
場合は、第３図の太線で示すごと〈コンプレッサ８の吐
出部側からの冷媒液は、第１図の冷房モード時と同様に
循環するが、冷媒加熱器１９を通る冷媒系路の冷媒液ポ
ンプ２０はＯＮの状態としており、その結果、第３図の
各点における圧力（Ｐ）及びエンタルピーロ）を示すモ
リエル線図は第６図のごとく示される。Furthermore, when this heat pump device is used in the defrosting mode, as shown by the bold line in Fig. 3, the refrigerant liquid from the discharge section side of the compressor 8 is circulated in the same way as in the cooling mode in Fig. 1. , the refrigerant liquid pump 20 in the refrigerant line passing through the refrigerant heater 19 is in the ON state, and as a result, the Mollier diagram showing the pressure (P) and enthalpyro) at each point in FIG. 3 is as shown in FIG. It is shown as follows.
なお、上記実施例においては、冷媒加熱器°１９の熱源
をエンジン１の廃熱としているが、この熱源はガスバー
ナ、まだは排水、排ガス等、どのような熱源を使用して
も酷い。In the above embodiment, the heat source of the refrigerant heater 19 is the waste heat of the engine 1, but this heat source may be a gas burner, waste water, exhaust gas, or any other heat source that is terrible.
従って、本発明のヒートポンプ装置では、ヒートポンプ
の冷媒液の高圧側に廃熱を吸収させるため、熱源からの
吸熱効率の低下がないという利点があシ、また冷媒液ポ
ンプのＯＮ・ＯＦＦ制御により暖房能力の強弱切換が簡
単にできるので、操作が簡単である。Therefore, in the heat pump device of the present invention, waste heat is absorbed into the high-pressure side of the refrigerant liquid of the heat pump, so there is an advantage that there is no decrease in heat absorption efficiency from the heat source. It is easy to operate because you can easily switch between strong and weak abilities.
一方、本発明のヒートポンプ装置をエアコンに使用する
場合、廃熱を冷媒熱として搬送するので室内ユニットへ
の配管が従来と殆んど変らず、また汎用コンプレッサが
使用できるので、設備コストも安いという利点がある。On the other hand, when the heat pump device of the present invention is used in an air conditioner, the waste heat is transferred as refrigerant heat, so the piping to the indoor unit is almost the same as before, and a general-purpose compressor can be used, so the equipment cost is low. There are advantages.
更に、除霜モード用の熱源に工／ジン廃熱がそのま１利
用できるという効果もある。Furthermore, there is also the effect that industrial/engine waste heat can be used directly as a heat source for the defrosting mode.
第１図、第２図及び第３図は本発明の一実施例における
エンジン駆動式のヒートポンプ装置による冷暖房システ
ムの系統図であり、第１図はその冷房モードの、第２図
はその暖房モードの、そして第３図は除霜モードの各状
態を示し、第４図、第５図及び第６図は本実施例のヒー
トポンプ装置におけるモリエル線図を示しているが、第
４図は冷房モードの、第５図は暖房モードの、そして第
６図は除霜モードの状態を示している。
１・・エンジン、８・・・コンプレソ？、９・・・室内
ユニット、１０・・室内側熱交換器、１３・・・受液器
、１６・・・室外側熱交換器、１９・・・冷媒加熱器、
２ｏ・・・冷媒液ポンプ。FIGS. 1, 2, and 3 are system diagrams of a heating and cooling system using an engine-driven heat pump device according to an embodiment of the present invention. FIG. 1 shows the cooling mode, and FIG. 2 shows the heating mode. , and Fig. 3 show each state of the defrosting mode, and Figs. 4, 5, and 6 show Mollier diagrams of the heat pump device of this embodiment, and Fig. 4 shows the state of the cooling mode. 5 shows the heating mode, and FIG. 6 shows the defrosting mode. 1...engine, 8...compresso? , 9... Indoor unit, 10... Indoor heat exchanger, 13... Liquid receiver, 16... Outdoor heat exchanger, 19... Refrigerant heater,
2o... Refrigerant liquid pump.
Claims (1)
の間の冷媒液を冷媒液ポンプにより昇圧した後、冷媒加
熱器経由コンプレッサの吐出部側と利用側熱交換器との
間に圧送する冷媒系路を配設したことを特徴とするヒー
トポンプ装置。After the refrigerant liquid between the user-side heat exchanger and the heat source-side heat exchanger of the heat pump device is boosted in pressure by a refrigerant liquid pump, it is sent under pressure between the discharge part side of the compressor and the user-side heat exchanger via a refrigerant heater. A heat pump device characterized in that a refrigerant system path is provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59126417A JPS616558A (en) | 1984-06-21 | 1984-06-21 | Heat pump device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59126417A JPS616558A (en) | 1984-06-21 | 1984-06-21 | Heat pump device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS616558A true JPS616558A (en) | 1986-01-13 |
Family
ID=14934652
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59126417A Pending JPS616558A (en) | 1984-06-21 | 1984-06-21 | Heat pump device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS616558A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS632055U (en) * | 1986-06-20 | 1988-01-08 | ||
| JPH02161269A (en) * | 1988-12-13 | 1990-06-21 | Yanmar Diesel Engine Co Ltd | Defrosting device |
| JPH03105174A (en) * | 1989-09-20 | 1991-05-01 | Sanyo Electric Co Ltd | Gas heat pump type refrigerating device |
| JPH05215435A (en) * | 1991-12-11 | 1993-08-24 | Sanden Corp | Engine-driven heat pump device |
| JP2007040638A (en) * | 2005-08-04 | 2007-02-15 | Denso Corp | Ejector type cycle |
| JP2012088021A (en) * | 2010-10-22 | 2012-05-10 | Daikin Industries Ltd | Refrigerating apparatus |
| US11780133B2 (en) | 2020-12-16 | 2023-10-10 | Canon Kabushiki Kaisha | Method for manufacturing article and injection molding system |
-
1984
- 1984-06-21 JP JP59126417A patent/JPS616558A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS632055U (en) * | 1986-06-20 | 1988-01-08 | ||
| JPH02161269A (en) * | 1988-12-13 | 1990-06-21 | Yanmar Diesel Engine Co Ltd | Defrosting device |
| JPH03105174A (en) * | 1989-09-20 | 1991-05-01 | Sanyo Electric Co Ltd | Gas heat pump type refrigerating device |
| JPH05215435A (en) * | 1991-12-11 | 1993-08-24 | Sanden Corp | Engine-driven heat pump device |
| JP2007040638A (en) * | 2005-08-04 | 2007-02-15 | Denso Corp | Ejector type cycle |
| JP2012088021A (en) * | 2010-10-22 | 2012-05-10 | Daikin Industries Ltd | Refrigerating apparatus |
| US11780133B2 (en) | 2020-12-16 | 2023-10-10 | Canon Kabushiki Kaisha | Method for manufacturing article and injection molding system |
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