JP2009281610A - Refrigerating cycle - Google Patents

Refrigerating cycle Download PDF

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JP2009281610A
JP2009281610A JP2008131981A JP2008131981A JP2009281610A JP 2009281610 A JP2009281610 A JP 2009281610A JP 2008131981 A JP2008131981 A JP 2008131981A JP 2008131981 A JP2008131981 A JP 2008131981A JP 2009281610 A JP2009281610 A JP 2009281610A
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refrigerant
heat exchanger
refrigeration cycle
internal heat
capacity
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JP5180680B2 (en
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Satoshi Kaneko
智 金子
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Sanden Corp
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Sanden Corp
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Priority to JP2008131981A priority Critical patent/JP5180680B2/en
Priority to EP09750463.3A priority patent/EP2309208B1/en
Priority to PCT/JP2009/058336 priority patent/WO2009142101A1/en
Priority to US12/993,458 priority patent/US20110067435A1/en
Priority to CN2009801189126A priority patent/CN102037292A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/18—Refrigerant conversion

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating cycle capable of being operated with a refrigerating capacity which is the same as or higher than a refrigerating cycle using a conventional R134a, when a used refrigerant is changed to a new refrigerant R1234yf. <P>SOLUTION: In this refrigerating cycle comprising a compressor, a condenser, a pressure reducing/expanding means, an evaporator, and an internal heat exchanger exchanging heat between a condenser outlet-side refrigerant and an evaporator outlet-side refrigerant, R1234yf is used as the refrigerant, and a heat exchange amount by the internal heat exchanger reaches a prescribed value or larger determined in advance by simulation or test. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、冷凍サイクルに関し、とくに、新しい冷媒を用いる場合に高い冷凍能力をもって運転可能な冷凍サイクルに関する。   The present invention relates to a refrigeration cycle, and more particularly to a refrigeration cycle that can be operated with high refrigeration capacity when a new refrigerant is used.

例えば車両用空調装置等に用いられる蒸気圧縮式冷凍サイクルとして、図１に示すような基本構成を有するものが知られている。図１において、冷凍サイクル１は、冷媒を圧縮する圧縮機２と、圧縮した冷媒を凝縮する凝縮器３と、凝縮した冷媒を減圧・膨張させる減圧・膨張手段としての膨張弁４と、減圧・膨張した冷媒を蒸発させる蒸発器５と、凝縮器出口側冷媒と蒸発器出口側冷媒との間で熱交換を行う内部熱交換器６とを備えており、この冷凍サイクル１中を冷媒がその状態を変化させながら矢印の方向に循環される。このように冷凍サイクル１中に内部熱交換器６を設けると、一般的に冷凍能力を向上させることが可能であることが知られている。ところが、現状の代表的な冷媒であるＲ１３４ａを使用する場合には、内部熱交換器６による効果が比較的低いため、現実には殆ど用いられていないのが実情である。   For example, a vapor compression refrigeration cycle used for a vehicle air conditioner or the like has a basic structure as shown in FIG. In FIG. 1, a refrigeration cycle 1 includes a compressor 2 for compressing refrigerant, a condenser 3 for condensing the compressed refrigerant, an expansion valve 4 as decompression / expansion means for decompressing / expanding the condensed refrigerant, An evaporator 5 that evaporates the expanded refrigerant, and an internal heat exchanger 6 that performs heat exchange between the condenser outlet-side refrigerant and the evaporator outlet-side refrigerant are provided. It is circulated in the direction of the arrow while changing the state. Thus, it is known that providing the internal heat exchanger 6 in the refrigeration cycle 1 can generally improve the refrigeration capacity. However, when R134a, which is a typical refrigerant at present, is used, since the effect of the internal heat exchanger 6 is relatively low, it is actually not used in practice.

上記の如く、現状の代表的な冷媒としてＲ１３４ａを挙げることができるが、地球温暖化係数（ＧＷＰ）等のさらなる改善を目指して、新冷媒の研究、開発が行われている（例えば、非特許文献１）。このような改善を目指した新冷媒として、最近、Ｒ１２３４ｙｆが公表され、例えば、車両用空調装置等に用いられる冷凍サイクルへの適用についても、試験、研究を行うことが可能な状況となってきた。
冷凍２００８年３月号第８３巻第９６５号 As described above, R134a can be cited as a typical current refrigerant, but research and development of new refrigerants are being conducted with the aim of further improving the global warming potential (GWP) and the like (for example, non-patents). Reference 1). Recently, R1234yf has been announced as a new refrigerant aiming at such improvements, and it has become possible to conduct tests and research on application to refrigeration cycles used in, for example, vehicle air conditioners. .
Refrigeration March 2008 Issue 83 Volume 965

しかしながら、新冷媒Ｒ１２３４ｙｆを単に現行の冷凍サイクルにそのまま適用した場合、現行のＲ１３４ａを用いた冷凍サイクルに比べ、冷凍能力、成績係数（ＣＯＰ）ともに低くなる可能性が高い。また、その場合、冷凍能力を改善するためには、上述のような内部熱交換器６を用いることが有効であると考えられるものの、その効果の度合については明らかにされていない。   However, when the new refrigerant R1234yf is simply applied to the current refrigeration cycle as it is, both the refrigeration capacity and the coefficient of performance (COP) are likely to be lower than those of the current refrigeration cycle using R134a. In that case, in order to improve the refrigerating capacity, it is considered effective to use the internal heat exchanger 6 as described above, but the degree of the effect is not clarified.

そこで本発明の課題は、上記のような新冷媒の出現に着目し、とくに使用冷媒を特定の新冷媒Ｒ１２３４ｙｆに変更した場合に、従来のＲ１３４ａを用いた冷凍サイクルと同等以上の高い冷凍能力をもって運転可能な冷凍サイクルを提供することにある。   Accordingly, the object of the present invention is to focus on the emergence of the new refrigerant as described above, and has a high refrigeration capacity equivalent to or higher than that of the conventional refrigeration cycle using R134a, particularly when the refrigerant used is changed to the specific new refrigerant R1234yf. It is to provide an operable refrigeration cycle.

上記課題を解決するために、本発明に係る冷凍サイクルは、冷媒を圧縮する圧縮機と、圧縮した冷媒を凝縮する凝縮器と、凝縮した冷媒を減圧・膨張させる減圧・膨張手段と、減圧・膨張した冷媒を蒸発させる蒸発器と、凝縮器出口側冷媒と蒸発器出口側冷媒との間で熱交換を行う内部熱交換器とを備えた冷凍サイクルにおいて、冷媒としてＲ１２３４ｙｆを使用するとともに、前記内部熱交換器による熱交換量を、予めシミュレーションまたは試験により求めた所定値以上とすることを特徴とするものからなる。   In order to solve the above problems, a refrigeration cycle according to the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the compressed refrigerant, a decompression / expansion unit that decompresses / expands the condensed refrigerant, and a decompression / expansion unit. In a refrigeration cycle comprising an evaporator for evaporating the expanded refrigerant, and an internal heat exchanger for exchanging heat between the condenser outlet side refrigerant and the evaporator outlet side refrigerant, R1234yf is used as the refrigerant, The heat exchange amount by the internal heat exchanger is set to a predetermined value or more obtained in advance by simulation or test.

図２に、図１に示したのと同様の基本構成を備えた冷凍サイクルにおいて、同一の計算条件（凝縮温度、蒸発温度、過熱度、過冷却度など）における、内部熱交換器未使用の場合の現行冷媒Ｒ１３４ａを使用した場合と、内部熱交換器使用の場合の新冷媒Ｒ１２３４ｙｆを使用した場合の冷凍能力の計算結果を比較し、この新冷媒Ｒ１２３４ｙｆを使用した場合には内部熱交換器を使用することにより、どのように冷凍能力の向上をはかれるかを示している。図２の横軸は、内部熱交換器の熱交換量（内部熱交換器の能力）を示しており、縦軸は、冷凍サイクル全体としての冷凍能力を示している。内部熱交換器未使用の場合の現行冷媒Ｒ１３４ａの場合（内部熱交換器未使用であるので、内部熱交換器の熱交換量に対しては一定の冷凍能力として表示されている）に比べ、Ｒ１３４ａとは特性の異なるＲ１２３４ｙｆを使用する場合には、内部熱交換器設置により図２に示すように冷凍能力が変化する。つまり、内部熱交換器による熱交換量として、ある値以上、つまり、図２に示した比較特性図では０．７ｋＷ以上得られれば（０．７ｋＷ以上の領域に入れば）、この新冷媒Ｒ１２３４ｙｆ使用の場合において、内部熱交換器設置による冷凍能力向上効果が確実に得られることが分かる。しかし、内部熱交換器による熱交換量がある値よりも小さい場合には、図２に示した比較特性図では０．７ｋＷよりも小さい場合には、Ｒ１３４ａの場合よりもＲ１２３４ｙｆの場合の方が冷凍能力は低くなり、Ｒ１３４ａの場合に比べて内部熱交換器設置の効果が得られないことが分かる。したがって、内部熱交換器による熱交換量をある値（つまり、所定値）以上とすることによって初めて、Ｒ１２３４ｙｆを使用する場合においてＲ１３４ａの場合と同等以上の冷凍能力が得られ、実際に冷凍能力を向上できるようになることが分かる。本発明は、この技術思想に基づくものであり、冷媒としてＲ１２３４ｙｆを使用する場合に、内部熱交換器による熱交換量を、予めシミュレーションまたは試験により求めた所定値以上とすることを特徴とするものである。つまり、図２におけるＲ１３４ａの場合の特性線とＲ１２３４ｙｆの場合の特性線との交点の右側領域（ハッチングで示した領域）を用いる。換言すれば、上記内部熱交換器による熱交換量の所定値が、同一条件下で、冷媒にＲ１２３４ｙｆを使用した場合の冷凍サイクル全体としての冷凍能力が、冷媒にＲ１３４ａを使用した場合の冷凍サイクル全体としての冷凍能力以上となるように設定される。   FIG. 2 shows a refrigeration cycle having the same basic configuration as shown in FIG. The calculation results of the refrigeration capacity when using the new refrigerant R1234yf when using the current refrigerant R134a and when using the new refrigerant R1234yf when using the internal heat exchanger are compared, and when using this new refrigerant R1234yf, the internal heat exchanger It shows how to improve the refrigerating capacity by using The horizontal axis in FIG. 2 indicates the heat exchange amount of the internal heat exchanger (the capacity of the internal heat exchanger), and the vertical axis indicates the refrigeration capacity of the entire refrigeration cycle. Compared to the case of the current refrigerant R134a when the internal heat exchanger is not used (because the internal heat exchanger is not used, it is displayed as a constant refrigeration capacity with respect to the heat exchange amount of the internal heat exchanger) When R1234yf having different characteristics from R134a is used, the refrigeration capacity changes as shown in FIG. 2 due to the installation of the internal heat exchanger. That is, if the amount of heat exchange by the internal heat exchanger is greater than a certain value, that is, 0.7 kW or more in the comparative characteristic diagram shown in FIG. 2 (if entering the region of 0.7 kW or more), this new refrigerant R1234yf In the case of use, it turns out that the refrigerating capacity improvement effect by an internal heat exchanger installation is acquired reliably. However, when the amount of heat exchange by the internal heat exchanger is smaller than a certain value, in the comparative characteristic diagram shown in FIG. 2, when it is smaller than 0.7 kW, the case of R1234yf is better than the case of R134a. It turns out that a refrigerating capacity becomes low and the effect of an internal heat exchanger installation is not acquired compared with the case of R134a. Therefore, only when the amount of heat exchange by the internal heat exchanger is set to a certain value (that is, a predetermined value) or more, when using R1234yf, a refrigerating capacity equal to or higher than that of R134a is obtained, and the refrigerating capacity is actually It turns out that it can improve. The present invention is based on this technical idea, and when R1234yf is used as a refrigerant, the heat exchange amount by the internal heat exchanger is set to a predetermined value or more obtained in advance by simulation or test. It is. That is, the right side area (area shown by hatching) of the intersection of the characteristic line in the case of R134a and the characteristic line in the case of R1234yf in FIG. In other words, the refrigeration capacity of the entire refrigeration cycle when R1234yf is used as the refrigerant under the same conditions as the predetermined value of the heat exchange amount by the internal heat exchanger is the refrigeration cycle when R134a is used as the refrigerant. It is set to be more than the overall refrigeration capacity.

上記のような内部熱交換器による熱交換量の所定値以上への制御は、具体的には、例えば、上記減圧・膨張手段の開度を上記内部熱交換器の圧縮機側への出口側冷媒の過熱度に応じて制御することにより行うことが可能である。内部熱交換器の出口側冷媒の過熱度に応じて減圧・膨張手段（膨張弁）の開度を適切に制御することにより、上述の如く、冷凍サイクル全体の冷凍能力としてＲ１３４ａを使用した場合の冷凍能力以上の冷凍能力が得られるようになる。   Specifically, the control of the amount of heat exchange by the internal heat exchanger to a predetermined value or more is, for example, the opening of the decompression / expansion means on the outlet side to the compressor side of the internal heat exchanger This can be done by controlling according to the degree of superheat of the refrigerant. By appropriately controlling the opening of the decompression / expansion means (expansion valve) according to the degree of superheat of the refrigerant on the outlet side of the internal heat exchanger, as described above, when R134a is used as the refrigeration capacity of the entire refrigeration cycle A refrigeration capacity higher than the refrigeration capacity can be obtained.

このような本発明に係る冷凍サイクルは、基本的には新冷媒Ｒ１２３４ｙｆを使用しようとするあらゆる冷凍サイクルに適用可能であるが、とくに効率の良い運転が長期間にわたって安定して求められる車両用空調装置に用いられる冷凍サイクルに好適である。   Such a refrigeration cycle according to the present invention is basically applicable to any refrigeration cycle in which the new refrigerant R1234yf is to be used. However, a vehicle air conditioner in which efficient operation is required stably over a long period of time. Suitable for the refrigeration cycle used in the apparatus.

本発明に係る冷凍サイクルによれば、使用冷媒を新冷媒であるＲ１２３４ｙｆに変更した場合に、Ｒ１３４ａを使用した場合と同等以上の高い冷凍能力を実現でき、併せて新冷媒Ｒ１２３４ｙｆ自体が有する優れた地球温暖化係数（ＧＷＰ）等の改善特性を発揮させることができる。   According to the refrigeration cycle according to the present invention, when the refrigerant used is changed to R1234yf, which is a new refrigerant, a high refrigeration capacity equal to or higher than that when R134a is used can be realized, and the new refrigerant R1234yf itself has excellent Improvement characteristics such as global warming potential (GWP) can be exhibited.

以下に、本発明について、望ましい実施の形態とともに図面を参照しながら説明する。 本発明に係る冷凍サイクルの配設機器の基本構成としては、図１に示したものと同等のものでよい。図１においては、前述したように、冷凍サイクル１は、冷媒を圧縮する圧縮機２と、圧縮した冷媒を凝縮する凝縮器３と、凝縮した冷媒を減圧・膨張させる減圧・膨張手段としての膨張弁４と、減圧・膨張した冷媒を蒸発させる蒸発器５と、凝縮器出口側冷媒と蒸発器出口側冷媒との間で熱交換を行う内部熱交換器６とを備えている。   The present invention will be described below together with preferred embodiments with reference to the drawings. The basic configuration of the refrigeration cycle installation device according to the present invention may be the same as that shown in FIG. In FIG. 1, as described above, the refrigeration cycle 1 includes a compressor 2 that compresses refrigerant, a condenser 3 that condenses the compressed refrigerant, and expansion as decompression / expansion means that decompresses and expands the condensed refrigerant. A valve 4, an evaporator 5 that evaporates the decompressed and expanded refrigerant, and an internal heat exchanger 6 that performs heat exchange between the condenser outlet-side refrigerant and the evaporator outlet-side refrigerant are provided.

また、前述の如く、本発明では、基本的には図２に示したＲ１３４ａの場合の特性線とＲ１２３４ｙｆの場合の特性線との交点の右側領域（ハッチングで示した領域）を用いる。つまり、この領域では、Ｒ１２３４ｙｆを使用した場合に、内部熱交換器を備えることによって、Ｒ１３４ａの場合よりも冷凍能力を向上できる。そこで、上記図２における、Ｒ１３４ａの場合の特性線とＲ１２３４ｙｆの場合の特性線との交点の内部熱交換器熱交換量条件において、他の条件、例えば冷媒の凝縮温度を変化させた場合、冷凍サイクル全体の冷凍能力に対する内部熱交換器による能力向上効果（内部熱交換器の能力割合）がどのようになるかを表したのが、図３の特性Ａである。そして、この特性Ａに対し、内部熱交換器の効率を１００％と仮定した場合の、凝縮温度に対する冷凍サイクル全体の冷凍能力に対する内部熱交換器の能力割合の関係を示したのが、図３の特性Ｂである。すなわち、この特性曲線ＡとＢとの間に内部熱交換器の能力があれば、Ｒ１３４ａを使用した場合と同等以上の冷凍能力向上効果が得られることになり、実際には内部熱交換器の効率は１００％未満であるから、実際の設定、あるいは制御領域はこれら特性曲線ＡとＢとの間に位置することになる。   Further, as described above, in the present invention, basically, the right side area (the area indicated by hatching) of the intersection of the characteristic line in the case of R134a and the characteristic line in the case of R1234yf shown in FIG. That is, in this region, when R1234yf is used, the refrigeration capacity can be improved by providing an internal heat exchanger as compared with the case of R134a. Therefore, in the internal heat exchanger heat exchange amount condition at the intersection of the characteristic line in the case of R134a and the characteristic line in the case of R1234yf in FIG. 2 described above, for example, when the condensation temperature of the refrigerant is changed, A characteristic A in FIG. 3 shows how the capacity improvement effect (capacity ratio of the internal heat exchanger) by the internal heat exchanger with respect to the refrigeration capacity of the entire cycle becomes. FIG. 3 shows the relationship of the capacity ratio of the internal heat exchanger to the refrigeration capacity of the entire refrigeration cycle with respect to the condensation temperature, assuming that the efficiency of the internal heat exchanger is 100%. This is characteristic B. That is, if the capacity of the internal heat exchanger is between the characteristic curves A and B, the effect of improving the refrigerating capacity equal to or higher than that when the R134a is used can be obtained. Since the efficiency is less than 100%, the actual setting or control region is located between these characteristic curves A and B.

上記図３に示した計算結果における特性曲線ＡとＢとの交点は、冷凍能力に対する内部熱交換器の能力割合が６．６％の箇所に位置しているので、該能力割合が７％以上であれば、図３に示した関係特性からは、確実に、内部熱交換器により冷凍能力向上効果が得られることになる。能力割合の上限値はとくに限定しないが、図３に示した計算結果からは、３０％程度までは確実に冷凍能力向上効果が得られることを確認している。   The intersection of the characteristic curves A and B in the calculation result shown in FIG. 3 is located at a position where the capacity ratio of the internal heat exchanger to the refrigeration capacity is 6.6%, so that the capacity ratio is 7% or more. Then, from the relational characteristics shown in FIG. 3, the effect of improving the refrigerating capacity is surely obtained by the internal heat exchanger. Although the upper limit value of the capacity ratio is not particularly limited, the calculation result shown in FIG. 3 confirms that the effect of improving the refrigeration capacity is surely obtained up to about 30%.

上記のようなＲ１３４ａの場合とＲ１２３４ｙｆの場合の、ある条件下における計算結果の一例を表１に示す。計算の前提条件は、以下の通りである。
・蒸発温度：０ｄｅｇ
・凝縮温度：５０ｄｅｇ
・蒸発器出口過熱度：５ｄｅｇ
・凝縮器出口過冷却度：５ｄｅｇ
・熱交換器・回路圧損：無しと仮定
・圧縮機効率：１００％と仮定 Table 1 shows an example of calculation results under a certain condition in the case of R134a and R1234yf as described above. The preconditions for the calculation are as follows.
Evaporation temperature: 0deg
・ Condensation temperature: 50deg
-Evaporator outlet superheat degree: 5deg
・ Condenser outlet supercooling degree: 5deg
・ Heat exchanger ・ Circuit pressure loss: None assumed ・ Compressor efficiency: 100% assumed

Figure 2009281610
Figure 2009281610

Ｒ１２３４ｙｆの場合、内部熱交換器の熱交換量を上げていくことで、表１におけるとくに太線で囲んだ部分に示すように、単位体積当たりの冷凍能力はＲ１３４ａと同等以上にできることが分かる。したがって、圧縮機の増速などが必要なくなる。また、圧縮機吸入冷媒密度が小さくなるため、冷媒循環量が減少し、圧力損失を低減できる。また、圧縮機吸入側冷媒過熱度が大きくなり、圧縮機吐出温度がＲ１３４ａよりも高くなり、効率の向上をはかることができる。さらに、圧縮機動力（消費動力）の増加は比較的小さいため、成績係数（ＣＯＰ）もＲ１３４ａと同等以上にできる。   In the case of R1234yf, it can be seen that by increasing the heat exchange amount of the internal heat exchanger, the refrigeration capacity per unit volume can be equal to or higher than that of R134a, as shown in the part surrounded by the bold line in Table 1. Therefore, it is not necessary to increase the speed of the compressor. Further, since the compressor suction refrigerant density is reduced, the refrigerant circulation amount is reduced, and the pressure loss can be reduced. Further, the degree of superheat of the compressor suction side refrigerant increases, the compressor discharge temperature becomes higher than R134a, and the efficiency can be improved. Furthermore, since the increase in compressor power (power consumption) is relatively small, the coefficient of performance (COP) can be equal to or higher than that of R134a.

また、モリエル線図上において、Ｒ１３４ａとＲ１２３４ｙｆを比較した結果の例を図４〜図６に示す。図４〜図６は、Ｒ１２３４ｙｆの場合の内部熱交換器の温度効率が異なる場合をそれぞれ示している。各図における条件は以下の通りである。   In addition, examples of the results of comparing R134a and R1234yf on the Mollier diagram are shown in FIGS. FIGS. 4-6 has each shown the case where the temperature efficiency of an internal heat exchanger in the case of R1234yf differs. The conditions in each figure are as follows.

図４に示したモリエル線図：
・蒸発温度：０ｄｅｇ
・凝縮温度：５０ｄｅｇ
・蒸発器出口過熱度：５ｄｅｇ
・凝縮器出口過冷却度：５ｄｅｇ
・Ｒ１３４ａについては内部熱交換器無しの特性
・Ｒ１２３４ｙｆについては、内部熱交換器有りでその温度効率が７５．３％ Mollier diagram shown in FIG.
Evaporation temperature: 0deg
・ Condensation temperature: 50deg
-Evaporator outlet superheat degree: 5deg
・ Condenser outlet supercooling degree: 5deg
・ R134a has no internal heat exchanger ・ R1234yf has an internal heat exchanger and its temperature efficiency is 75.3%

図５に示したモリエル線図：
・蒸発温度：０ｄｅｇ
・凝縮温度：５０ｄｅｇ
・蒸発器出口過熱度：５ｄｅｇ
・凝縮器出口過冷却度：５ｄｅｇ
・Ｒ１３４ａについては内部熱交換器無しの特性
・Ｒ１２３４ｙｆについては、内部熱交換器有りでその温度効率が９３．０％ Mollier diagram shown in FIG. 5:
Evaporation temperature: 0deg
・ Condensation temperature: 50deg
-Evaporator outlet superheat degree: 5deg
・ Condenser outlet supercooling degree: 5deg
・ R134a has no internal heat exchanger ・ R1234yf has an internal heat exchanger and its temperature efficiency is 93.0%

図６に示したモリエル線図：
・蒸発温度：０ｄｅｇ
・凝縮温度：５０ｄｅｇ
・蒸発器出口過熱度：５ｄｅｇ
・凝縮器出口過冷却度：５ｄｅｇ
・Ｒ１３４ａについては内部熱交換器無しの特性
・Ｒ１２３４ｙｆについては、内部熱交換器有りでその温度効率が９９．９％ Mollier diagram shown in FIG. 6:
Evaporation temperature: 0deg
・ Condensation temperature: 50deg
-Evaporator outlet superheat degree: 5deg
・ Condenser outlet supercooling degree: 5deg
・ R134a has no internal heat exchanger ・ R1234yf has an internal heat exchanger and its temperature efficiency is 99.9%

なお、上記における各例は、計算によるシミュレーション結果として示してあるが、これとは別に実際の試験によって求めて前述の所定値、あるいはシミュレーション結果と試験結果の両方を参照して定めた前述の所定値を用いることも可能である。   In addition, although each example in the above is shown as a simulation result by calculation, separately from this, the above-mentioned predetermined value obtained by an actual test and determined by referring to the above-mentioned predetermined value or both the simulation result and the test result. It is also possible to use a value.

本発明に係る冷凍サイクルは、Ｒ１２３４ｙｆの使用を予定しているあらゆる冷凍サイクルに適用可能であり、とくに車両用空調装置に用いられる冷凍サイクルとして好適なものである。   The refrigeration cycle according to the present invention can be applied to any refrigeration cycle in which R1234yf is scheduled to be used, and is particularly suitable as a refrigeration cycle used in a vehicle air conditioner.

本発明で対象としている冷凍サイクルの基本機器配置を示す概略構成図である。It is a schematic block diagram which shows basic equipment arrangement | positioning of the refrigerating cycle made into object by this invention. 冷媒Ｒ１２３４ｙｆとＲ１３４ａの特性を比較した内部熱交換器熱交換量と冷凍能力との関係図である。It is a related figure of the internal heat exchanger heat exchange amount and the refrigerating capacity which compared the characteristic of refrigerant | coolant R1234yf and R134a. 冷媒Ｒ１２３４ｙｆを使用する場合の凝縮温度と内部熱交換器能力割合との関係図である。It is a related figure of the condensation temperature in the case of using refrigerant | coolant R1234yf and an internal heat exchanger capability ratio. 冷媒Ｒ１２３４ｙｆとＲ１３４ａのある条件時の冷凍サイクルの運転状態の一例を示すモリエル線図である。It is a Mollier diagram which shows an example of the driving | running state of the refrigerating cycle at the time of condition with refrigerant | coolants R1234yf and R134a. 冷媒Ｒ１２３４ｙｆとＲ１３４ａの別の条件時の冷凍サイクルの運転状態の一例を示すモリエル線図である。It is a Mollier diagram which shows an example of the driving | running state of the refrigerating cycle at the time of another conditions of refrigerant | coolant R1234yf and R134a. 冷媒Ｒ１２３４ｙｆとＲ１３４ａのさらに別の条件時の冷凍サイクルの運転状態の一例を示すモリエル線図である。It is a Mollier diagram which shows an example of the driving | running state of the refrigerating cycle at the time of another condition of refrigerant | coolants R1234yf and R134a.

符号の説明Explanation of symbols

１ 冷凍サイクル
２ 圧縮機
３ 凝縮器
４ 減圧・膨張手段としての膨張弁
５ 蒸発器
６ 内部熱交換器 DESCRIPTION OF SYMBOLS 1 Refrigeration cycle 2 Compressor 3 Condenser 4 Expansion valve 5 as decompression / expansion means Evaporator 6 Internal heat exchanger

Claims (6)

冷媒を圧縮する圧縮機と、圧縮した冷媒を凝縮する凝縮器と、凝縮した冷媒を減圧・膨張させる減圧・膨張手段と、減圧・膨張した冷媒を蒸発させる蒸発器と、凝縮器出口側冷媒と蒸発器出口側冷媒との間で熱交換を行う内部熱交換器とを備えた冷凍サイクルにおいて、冷媒としてＲ１２３４ｙｆを使用するとともに、前記内部熱交換器による熱交換量を、予めシミュレーションまたは試験により求めた所定値以上とすることを特徴とする冷凍サイクル。   A compressor that compresses the refrigerant; a condenser that condenses the compressed refrigerant; a decompression / expansion means that decompresses / expands the condensed refrigerant; an evaporator that evaporates the decompressed / expanded refrigerant; and a condenser outlet-side refrigerant; In a refrigeration cycle including an internal heat exchanger that exchanges heat with the evaporator outlet side refrigerant, R1234yf is used as the refrigerant, and the amount of heat exchange by the internal heat exchanger is obtained in advance by simulation or test. A refrigeration cycle characterized by having a predetermined value or more. 前記内部熱交換器による熱交換量の所定値が、同一条件下で、冷媒にＲ１２３４ｙｆを使用した場合の冷凍サイクル全体としての冷凍能力が、冷媒にＲ１３４ａを使用した場合の冷凍サイクル全体としての冷凍能力以上となるように設定されている、請求項１に記載の冷凍サイクル。   When the predetermined value of the heat exchange amount by the internal heat exchanger is the same, the refrigerating capacity as the whole refrigerating cycle when R1234yf is used as the refrigerant is the refrigerating capacity as the whole refrigerating cycle when R134a is used as the refrigerant. The refrigeration cycle according to claim 1, wherein the refrigeration cycle is set to be equal to or greater than the capacity. 前記内部熱交換器による熱交換量の所定値が、冷凍サイクル全体としての冷凍能力に対する能力割合として設定されている、請求項１または２に記載の冷凍サイクル。   The refrigeration cycle according to claim 1 or 2, wherein the predetermined value of the heat exchange amount by the internal heat exchanger is set as a capacity ratio with respect to the refrigeration capacity of the entire refrigeration cycle. 前記内部熱交換器による熱交換量の所定値の前記冷凍サイクル全体としての冷凍能力に対する能力割合が７％以上に設定されている、請求項３に記載の冷凍サイクル。   The refrigeration cycle according to claim 3, wherein a capacity ratio of a predetermined value of a heat exchange amount by the internal heat exchanger to a refrigeration capacity of the entire refrigeration cycle is set to 7% or more. 前記内部熱交換器による熱交換量の所定値以上への制御が、前記減圧・膨張手段の開度を前記内部熱交換器の圧縮機側への出口側冷媒の過熱度に応じて制御することにより行われる、請求項１〜４のいずれかに記載の冷凍サイクル。   Controlling the amount of heat exchange by the internal heat exchanger to a predetermined value or more controls the opening of the decompression / expansion means according to the degree of superheat of the outlet side refrigerant to the compressor side of the internal heat exchanger. The refrigeration cycle according to claim 1, wherein the refrigeration cycle is performed. 車両用空調装置に用いられる、請求項１〜５のいずれかに記載の冷凍サイクル。   The refrigeration cycle according to any one of claims 1 to 5, which is used in a vehicle air conditioner.
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