JPH0360033B2 - - Google Patents
Info
- Publication number
- JPH0360033B2 JPH0360033B2 JP59231425A JP23142584A JPH0360033B2 JP H0360033 B2 JPH0360033 B2 JP H0360033B2 JP 59231425 A JP59231425 A JP 59231425A JP 23142584 A JP23142584 A JP 23142584A JP H0360033 B2 JPH0360033 B2 JP H0360033B2
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- steam
- evaporator
- heat medium
- expander
- 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 - Lifetime
Links
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Central Heating Systems (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、過給ヒートポンプの性能向上に関
し、更に詳しくは、動力回収用蒸気膨脹機により
駆動される速度型圧縮機により密度を上昇させた
流体を溶積型主圧縮機に供給することにより主圧
縮機を小型化すると共に、主圧縮機の駆動動力を
削減し、成績係数を向上した過給ヒートポンプに
関するものである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to improving the performance of supercharging heat pumps, and more particularly, the present invention relates to improving the performance of supercharging heat pumps, and more specifically, the present invention relates to improving the performance of supercharging heat pumps. The present invention relates to a supercharging heat pump that reduces the size of the main compressor by supplying fluid to the main compressor, reduces the driving power of the main compressor, and improves the coefficient of performance.
一般に、ヒートポンプシステムは、低温の熱源
から高温の熱源に熱エネルギーを移送させるシス
テムであつて、冷暖房装置として、更には、省エ
ネルギー化の要請から廃熱回収装置として各方面
において多用されている。そして、このようなヒ
ートポンプシステムとして広く知られているもの
に、圧縮機を用いた圧縮過程を有する圧縮式ヒー
トポンプシステムがある。
Generally, a heat pump system is a system that transfers thermal energy from a low-temperature heat source to a high-temperature heat source, and is widely used in various fields as an air-conditioning device and also as a waste heat recovery device due to the need for energy saving. One widely known type of heat pump system is a compression heat pump system that includes a compression process using a compressor.
従来の圧縮式ヒートポンプシステムは、低温熱
源から熱エネルギーを吸収する蒸発器と、この蒸
発器からの熱媒蒸発を断熱圧縮する圧縮機と、こ
の圧縮機によつて昇温・昇圧された熱媒体から熱
エネルギーを出力する凝縮器と、この凝縮器内に
おいて液化した熱媒体を断熱膨脹する膨脹弁など
の絞り機構とからなり、この絞り機構からの熱媒
体が前記蒸発器に戻され、循環供給されている。 A conventional compression heat pump system consists of an evaporator that absorbs thermal energy from a low-temperature heat source, a compressor that adiabatically compresses the evaporated heat medium from the evaporator, and a heat medium that is heated and pressurized by the compressor. It consists of a condenser that outputs thermal energy from the evaporator, and a throttling mechanism such as an expansion valve that adiabatically expands the liquefied heat medium in the condenser. has been done.
前記圧縮機としては、比較的小出力の場合（大
体500kw程度迄）往復動容積形、回転容積形（ス
クリユー式を含む）などの容積形圧縮機が使用さ
れ、比較的大出力の場合、速度形（遠心式、軸流
形）圧縮機が使用されている。これは、速度形圧
縮機が大量の蒸発を処理する特徴を持つためであ
る。溶積形圧縮機は、構造が簡単で、高圧が得ら
れるなど、優れているが、処理できる流体の容量
が小さいという欠点があり、ヒートポンプシステ
ムの高出力化を図る上で一つのネツクになつてい
た。 The compressor used is a positive displacement compressor such as a reciprocating displacement type or a rotating displacement type (including a screw type) when the output is relatively small (up to approximately 500kW), and when the output is relatively high, the Type (centrifugal, axial flow) compressors are used. This is because the speed type compressor has the characteristic of processing a large amount of evaporation. The volume compressor is superior in that it has a simple structure and can obtain high pressure, but it has the disadvantage that the capacity of the fluid that can be processed is small, which is one of the obstacles to increasing the output of the heat pump system. was.
一方、省エネルギーの立場からヒートポンプの
成績係数の上昇が、また、経済性の観点からヒー
トポンプのコスト削減に対する必要性が近年益々
高まつてきており、このためには、膨脹弁でのエ
ネルギー回収が有効であると言われているが、実
現された例は少ない。 On the other hand, in recent years, the coefficient of performance of heat pumps has increased from the standpoint of energy conservation, and the need to reduce the cost of heat pumps from the standpoint of economic efficiency has increased, and energy recovery using expansion valves has become effective for this purpose. Although this is said to be the case, there are few examples of this being realized.
本発明の目的は、容積形圧縮機の前段に配置し
た速度形圧縮機により圧縮の一部を行い、容積形
圧縮機に供給する流体の圧力を上げて流体密度を
上昇させることによつて容積形圧縮機で処理でき
る流体の容量を大きくすることにより、また更に
速度形圧縮機の駆動動力に、凝縮器より排出され
る凝縮液からの回収熱エネルギーを利用すること
により、過給ヒートポンプの性能を向上させるこ
とにある。
An object of the present invention is to perform part of the compression by a velocity compressor placed before a positive displacement compressor, and to increase the pressure of the fluid supplied to the positive displacement compressor to increase the fluid density. The performance of the supercharging heat pump has been improved by increasing the capacity of the fluid that can be processed by the speed compressor, and by using the recovered thermal energy from the condensate discharged from the condenser to drive the speed compressor. The aim is to improve
すなわち、本発明の過給ヒートポンプは、蒸発
器、圧縮機、凝縮器及び膨脹弁からなり圧縮機を
２段に分け前段を速度形、後段を容積形とする過
給ヒートポンプにおいて、
凝縮器から膨脹弁を介して導入される熱媒体を
蒸気と液体とに分離させる気液分離器を設け、該
気液分離によつて分離された熱媒蒸気を膨脹機に
導き蒸発器の蒸発圧力以下まで膨脹させることに
より該蒸気膨脹機を駆動し、
該蒸気膨脹機と直結された前記前段圧縮機を該
蒸気膨脹機により駆動させると共に、前記膨脹機
で膨脹させた蒸気を復水器に導き冷却液化しこれ
をポンプにより昇圧して蒸発器に還流させ、
気液分離器によつて分離された熱媒液を前記蒸
発器に還流されることでサイクルをなすことを特
徴とするものである。
That is, the supercharging heat pump of the present invention consists of an evaporator, a compressor, a condenser, and an expansion valve, and the compressor is divided into two stages, the first stage being a velocity type and the second stage being a displacement type. A gas-liquid separator is provided to separate the heat medium introduced through the valve into vapor and liquid, and the heat medium vapor separated by the gas-liquid separation is guided to an expansion machine and expanded to below the evaporation pressure of the evaporator. The steam expander is driven by the steam expander, the pre-stage compressor directly connected to the steam expander is driven by the steam expander, and the steam expanded by the expander is guided to a condenser and cooled and liquefied. This is pressurized by a pump and refluxed to the evaporator, and the heat transfer liquid separated by the gas-liquid separator is refluxed to the evaporator to form a cycle.
以下、図面により本発明の実施例について説明
する。
Embodiments of the present invention will be described below with reference to the drawings.
第１図は、本発明にかかる過給ヒートポンプの
系統図であつて、低温熱源から熱媒エネルギーを
吸収する蒸発器１に配管２から供給された熱媒体
は、蒸発器１において、吸熱・蒸発して蒸気Ｓと
なり、配管４を経由して溶積形圧縮機５に供給さ
れるが、前記配管４には、溶積形圧縮機５の上流
側に速度形圧縮機であるターボ圧縮機２２が配置
され、蒸気Ｓを密度の高い状態として容積形圧縮
機５に供給する。なお、往復動圧縮機は蒸気の流
れが断続的であるため、前後に蓄圧器２３，２４
を配置する。 FIG. 1 is a system diagram of a supercharging heat pump according to the present invention, in which the heat medium supplied from a pipe 2 to an evaporator 1 that absorbs heat medium energy from a low-temperature heat source is absorbed and evaporated in the evaporator 1. This becomes steam S, which is supplied to the molten type compressor 5 via the piping 4, but the piping 4 includes a turbo compressor 22, which is a velocity type compressor, on the upstream side of the molten type compressor 5. is arranged to supply steam S in a high-density state to the positive displacement compressor 5. In addition, since the flow of steam in a reciprocating compressor is intermittent, there are pressure accumulators 23 and 24 at the front and rear.
Place.
容積形圧縮機５に吸収された蒸気は、圧縮され
て高温・高圧蒸気Ｓとなり、配管６を経由して凝
縮器７に供給される。そして、この凝縮器７にお
いて、高温の熱エネルギーを出力すると共に、蒸
気Ｓは凝縮する。前記凝縮器７において凝縮され
た熱媒体Ｌは、配管１０を経由して膨脹弁１１に
て膨脹し、気液分離器１２において液体l1と蒸気
S1とに分離される。気液分離器１２で分離された
蒸気S1は、配管１３をか経由して蒸発膨脹機１４
に供給され、蒸発器１１における蒸発圧力以下ま
で膨脹し、低圧蒸気S2となつて配管１７を経由し
て復水器１８に送られ、ここで、凝縮して低温液
体l2となり、配管１９を経由してポンプ２０によ
り昇圧され、蒸発器１に還流する。膨脹機１４の
出口圧力は低い程、メリツトが大きく真空が望ま
しいが、通常は、冷却水で冷却するので、常温凝
縮圧力となる。一方、気液分離器１２において分
離された液体l1は、配管１５を経由して蒸発器１
に循環供給される。 The steam absorbed by the positive displacement compressor 5 is compressed into high-temperature, high-pressure steam S, which is supplied to the condenser 7 via a pipe 6. The condenser 7 outputs high-temperature thermal energy and condenses the steam S. The heat medium L condensed in the condenser 7 is expanded in an expansion valve 11 via a pipe 10, and is separated into liquid l1 and steam in a gas-liquid separator 12.
Separated into S 1 and The steam S 1 separated by the gas-liquid separator 12 passes through the pipe 13 to the evaporative expander 14
It expands to below the evaporation pressure in the evaporator 11, becomes low-pressure steam S2 , and is sent to the condenser 18 via the pipe 17, where it is condensed to become a low-temperature liquid L2 , which is sent to the pipe 19. It is pressurized by a pump 20 and refluxed to the evaporator 1. The lower the outlet pressure of the expander 14, the greater the advantage, and a vacuum is desirable; however, since cooling is normally performed with cooling water, the pressure is condensed at room temperature. On the other hand, the liquid l 1 separated in the gas-liquid separator 12 passes through the pipe 15 to the evaporator 1
is supplied in circulation.
前記のように、蒸気膨脹機１４の出力をターボ
圧縮機２２（速度形圧縮機）の駆動力として利用
すると共に、蒸発器１からの熱媒蒸気Ｓを、その
ターボ圧縮機２２を経由して、容積形圧縮機５に
供給するようにしたことにより、熱媒蒸気Ｓを密
度の高い状態として容積形圧縮機５に供給できる
ため、容積形圧縮機５の小型化が可能で、コスト
低減を図ることができる。しかも、ターボ圧縮機
２２は、蒸気膨脹機１４の出力を駆動力として利
用しているため、自立的に作動し、熱媒蒸発圧縮
のための動力の一部をカバーできる。 As mentioned above, the output of the steam expander 14 is used as the driving force for the turbo compressor 22 (speed type compressor), and the heat medium vapor S from the evaporator 1 is passed through the turbo compressor 22. By supplying the heat medium vapor S to the positive displacement compressor 5, the heat medium vapor S can be supplied to the positive displacement compressor 5 in a high-density state, so the positive displacement compressor 5 can be downsized and costs can be reduced. can be achieved. Moreover, since the turbo compressor 22 uses the output of the steam expander 14 as the driving force, it operates independently and can cover part of the power for evaporating and compressing the heat medium.
上記のように、本発明の過給ヒートポンプは、
膨脹弁から導出される気液混合熱媒体を蒸気と液
体とに分離させる気液分離器に導き、該気液分離
器によつて分離された熱媒蒸気を膨脹機に導き蒸
発器の蒸気圧力以下まで膨脹させるので、蒸気膨
脹機による回収動力が増加する。この回収動力の
増加は新たに必要となるポンプ２０の駆動動力よ
り遥かに大きく、従つて、全体として動力回収量
は大幅に増加する。また、該蒸気膨脹機によつて
前記前段圧縮機を駆動させ熱媒蒸気の圧縮のため
の動力の一部をカバーできるので、主圧縮機の駆
動動力が減縮し、ヒートポンプの成績係数が上昇
すると共に、前記前段圧縮機は自立的に作動す
る。
As mentioned above, the supercharging heat pump of the present invention
The gas-liquid mixed heat medium drawn out from the expansion valve is guided to a gas-liquid separator that separates it into vapor and liquid, and the heat medium vapor separated by the gas-liquid separator is guided to the expansion machine to reduce the vapor pressure of the evaporator. Since it is expanded to below, the power recovered by the steam expander increases. This increase in recovered power is much larger than the newly required drive power for the pump 20, and therefore, the amount of recovered power increases significantly as a whole. In addition, since the steam expander can drive the pre-stage compressor and cover a part of the power for compressing the heat medium vapor, the driving power of the main compressor is reduced and the coefficient of performance of the heat pump is increased. At the same time, the pre-stage compressor operates independently.
更に、動力回収用蒸気膨脹機により駆動される
前記前段圧縮機により密度を上昇させた流体を容
積形圧縮機に供給（過給）することにより主圧縮
機を小型化することができる。前述のように、蒸
気膨脹機と前段圧縮機は軸で直結され自立的に作
動し、所謂過給機を構成する。また、前段圧縮機
を速度形とすることにより極めて小型の過給機と
することができる。小型の速度形圧縮機（ターボ
圧縮機）は極めて高速回転を要し、通常の電動機
で駆動することは一般に難しいが、本発明では、
フラツシユ蒸気を生成して膨脹機において蒸気を
低圧まで充分膨脹させて駆動できるので、容易に
高速駆動が実現できる。 Furthermore, the main compressor can be downsized by supplying (supercharging) the fluid whose density has been increased by the pre-stage compressor driven by the power recovery steam expander to the positive displacement compressor. As mentioned above, the steam expander and the pre-compressor are directly connected by a shaft and operate independently, forming a so-called supercharger. Furthermore, by making the front stage compressor a speed type, it is possible to make the supercharger extremely compact. A small speed compressor (turbo compressor) requires extremely high speed rotation and is generally difficult to drive with a normal electric motor, but in the present invention,
Since it is possible to generate flash steam and sufficiently expand the steam to a low pressure in an expander for driving, high-speed driving can be easily realized.
以上の如く、膨脹弁から導出される気液混合熱
媒体を蒸気と液体とに分離させる気液分離器に導
き、該気液分離器によつて分離された熱媒蒸気を
膨脹機に導き蒸発器の蒸発圧力以下まで膨脹させ
該膨脹機を駆動し、該膨脹機により軸で直結され
た速度形前段圧縮機を駆動し主圧縮機を過給する
ので、ヒートポンプ全体として小型化が達成さ
れ、製造コストが低下し、しかも成績係数の高い
ヒートポンプが実現される。 As described above, the gas-liquid mixed heat medium drawn out from the expansion valve is led to the gas-liquid separator that separates it into vapor and liquid, and the heat medium vapor separated by the gas-liquid separator is led to the expansion machine and evaporated. The heat pump is expanded to below the evaporation pressure of the heat pump and the expander is driven, and the expander drives the speed-type pre-stage compressor directly connected to the shaft to supercharge the main compressor, so the overall size of the heat pump can be reduced. A heat pump with reduced manufacturing costs and a high coefficient of performance can be realized.
第１図は本発明にかかる過給ヒートポンプの系
統図である。
１……蒸発器、５……容積形圧縮機、７……凝
縮器、１１……膨脹弁、１２……気液分離器、１
４……蒸気膨脹機、１８……復水器、２０……ポ
ンプ、２２……ターボ圧縮機。
FIG. 1 is a system diagram of a supercharging heat pump according to the present invention. 1... Evaporator, 5... Positive displacement compressor, 7... Condenser, 11... Expansion valve, 12... Gas-liquid separator, 1
4... Steam expander, 18... Condenser, 20... Pump, 22... Turbo compressor.
Claims (1)
圧縮機を２段に分け前段を速度形、後段を容積形
とする過給ヒートポンプにおいて、 凝縮器から膨脹弁を介して導入される熱媒体を
蒸気と液体とに分離させる気液分離器を設け、該
気液分離器によつて分離された熱媒蒸気を膨脹機
に導き蒸発器の蒸発圧力以下まで膨脹させること
により該蒸気膨脹機を駆動し、 該蒸気膨脹機と直結された前記前段圧縮機を該
蒸気膨脹機により駆動させると共に、前記膨脹機
で膨脹させた蒸気を復水器に導き冷却液化しこれ
をポンプにより昇圧して蒸発器に還流させ、 気液分離器によつて分離された熱媒液を前記蒸
発器に還流させることでサイクルをなすことを特
徴とする過給ヒートポンプ。[Scope of Claims] 1. In a supercharging heat pump that consists of an evaporator, a compressor, a condenser, and an expansion valve, and the compressor is divided into two stages, the first stage being a velocity type and the second stage being a displacement type, A gas-liquid separator is provided to separate the heat medium introduced into vapor and liquid, and the heat medium vapor separated by the gas-liquid separator is guided to an expansion machine and expanded to below the evaporation pressure of the evaporator. The steam expander is driven by the steam expander, and the pre-stage compressor, which is directly connected to the steam expander, is driven by the steam expander, and the steam expanded by the expander is guided to a condenser where it is cooled and liquefied. A supercharging heat pump characterized in that a cycle is formed by increasing the pressure with a pump and causing the heat medium to flow back to the evaporator, and then flowing the heat medium liquid separated by a gas-liquid separator back to the evaporator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23142584A JPS61110849A (en) | 1984-11-05 | 1984-11-05 | Heat pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23142584A JPS61110849A (en) | 1984-11-05 | 1984-11-05 | Heat pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61110849A JPS61110849A (en) | 1986-05-29 |
| JPH0360033B2 true JPH0360033B2 (en) | 1991-09-12 |
Family
ID=16923373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23142584A Granted JPS61110849A (en) | 1984-11-05 | 1984-11-05 | Heat pump system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61110849A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4622193B2 (en) * | 2001-08-31 | 2011-02-02 | ダイキン工業株式会社 | Refrigeration equipment |
| US8181481B2 (en) * | 2005-11-24 | 2012-05-22 | Shell Oil Company | Method and apparatus for cooling a stream, in particular a hydrocarbon stream such as natural gas |
| JP7038300B2 (en) * | 2017-07-27 | 2022-03-18 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5033369U (en) * | 1973-07-20 | 1975-04-10 | ||
| JPS5824634A (en) * | 1981-08-05 | 1983-02-14 | Nissan Motor Co Ltd | Shock absorber |
-
1984
- 1984-11-05 JP JP23142584A patent/JPS61110849A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61110849A (en) | 1986-05-29 |
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