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JP2009270496A - Compressor and refrigerating cycle using it - Google Patents

Compressor and refrigerating cycle using it Download PDF

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Publication number
JP2009270496A
JP2009270496A JP2008122043A JP2008122043A JP2009270496A JP 2009270496 A JP2009270496 A JP 2009270496A JP 2008122043 A JP2008122043 A JP 2008122043A JP 2008122043 A JP2008122043 A JP 2008122043A JP 2009270496 A JP2009270496 A JP 2009270496A
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Prior art keywords
refrigerant
compressor
hfo1234yf
pressure loss
sectional area
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Japanese (ja)
Inventor
Hiroshi Sato
博 佐藤
Toshiyuki Kawai
俊行 川井
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Sanden Corp
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Sanden Corp
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Priority to JP2008122043A priority Critical patent/JP2009270496A/en
Priority to PCT/JP2009/058291 priority patent/WO2009136565A1/en
Publication of JP2009270496A publication Critical patent/JP2009270496A/en
Pending legal-status Critical Current

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/263—HFO1234YF
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor reducing loss work and exhibiting high performance when a refrigerant in use is changed to R1234yf being a new refrigerant, and to provide a refrigerating cycle achieved in the high coefficient of performance (COP) by using the compressor. <P>SOLUTION: This compressor compresses the refrigerant, HFO1234yf is used as the refrigerant, and the channel cross-sectional area of a main pressure loss generating part is enlarged 1.05-1.40 times in comparison with the case that HFC134a is used as the refrigerant. The refrigerating cycle uses the compressor. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、特定の新しい冷媒を用いる場合にも高い性能が得られるようにした圧縮機と、その圧縮機を用いた冷凍サイクルに関する。   The present invention relates to a compressor capable of obtaining high performance even when a specific new refrigerant is used, and a refrigeration cycle using the compressor.

例えば車両用空調装置等に用いられる冷凍サイクルは、図１に示すような基本構成を有している。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循環される。このような冷凍サイクル１においては、動力の大半は圧縮機２で消費されるので、圧縮機２の性能が冷凍サイクル１の成績係数（ＣＯＰ）を大きく左右する。圧縮機２の性能向上の手法の一つに、圧縮機内でのある力損失を極力低減することが挙げられる。   For example, a refrigeration cycle used in a vehicle air conditioner or the like has a basic configuration 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 for evaporating the expanded refrigerant is provided, and the refrigerant is circulated through the refrigeration cycle 1 while changing its state. In such a refrigeration cycle 1, most of the power is consumed by the compressor 2, so the performance of the compressor 2 greatly affects the coefficient of performance (COP) of the refrigeration cycle 1. One technique for improving the performance of the compressor 2 is to reduce a certain force loss in the compressor as much as possible.

現状、代表的な冷媒としてＨＦＣ１３４ａが使用されており、その場合、圧縮機内の各部の形状やサイズは、冷媒としてＨＦＣ１３４ａを使用することを前提に最適な形状やサイズに設計されている。   At present, HFC134a is used as a typical refrigerant, and in this case, the shape and size of each part in the compressor are designed to the optimum shape and size on the assumption that HFC134a is used as the refrigerant.

この現状の代表的な冷媒ＨＦＣ１３４ａに対し、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、ＨＦＯ１２３４ｙｆ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 Research and development of new refrigerants have been conducted with the aim of further improving the global warming potential (GWP) and the like with respect to the present typical refrigerant HFC134a (for example, Non-Patent Document 1). Recently, HFO1234yf was announced as a new refrigerant aiming at such improvements, and it has become possible to test and study application to refrigeration cycles used in, for example, vehicle air conditioners. .
Refrigeration March 2008 Issue 83 Volume 965

ところが、現状の上記冷媒ＨＦＣ１３４ａに比べ、新冷媒ＨＦＯ１２３４ｙｆは密度が大きく冷媒流量が増加するため、冷媒ＨＦＣ１３４ａを使用していた場合のままの形態に新冷媒ＨＦＯ１２３４ｙｆを用いると、とくに圧縮機の吸入・吐出に伴う損失仕事が増大し、冷凍サイクルの成績係数（ＣＯＰ）が低下することとなる。   However, since the new refrigerant HFO1234yf has a higher density and the refrigerant flow rate increases compared to the current refrigerant HFC134a, if the new refrigerant HFO1234yf is used as it is when the refrigerant HFC134a is used, the intake / Lost work accompanying discharge increases, and the coefficient of performance (COP) of the refrigeration cycle decreases.

そこで本発明の課題は、上記のような問題点に着目し、とくに使用冷媒を新冷媒であるＨＦＯ１２３４ｙｆに変更した場合に、損失仕事を低減でき、高性能を発揮可能な圧縮機を提供するとともに、その圧縮機を用いることにより高い成績係数（ＣＯＰ）を実現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 provide a compressor capable of reducing lost work and exhibiting high performance, particularly when the refrigerant used is changed to HFO1234yf, which is a new refrigerant, focusing on the above problems. An object of the present invention is to provide a refrigeration cycle that can realize a high coefficient of performance (COP) by using the compressor.

上記課題を解決するために、本発明に係る圧縮機は、冷媒を圧縮する圧縮機であって、冷媒としてＨＦＯ１２３４ｙｆを使用するとともに、冷媒にＨＦＣ１３４ａを使用する場合に比べ、主圧力損失発生部の流路断面積を１．０５〜１．４０倍に拡大したことを特徴とするものからなる。   In order to solve the above-described problems, a compressor according to the present invention is a compressor that compresses a refrigerant, and uses HFO1234yf as a refrigerant and has a main pressure loss generation unit as compared with the case where HFC134a is used as a refrigerant. The channel cross-sectional area is increased by 1.05 to 1.40 times.

すなわち、圧縮機内において、冷媒ＨＦＣ１３４ａを使用する場合に主に圧力損失を発生させていた流路部分に関し、その流路断面積を、冷媒ＨＦＣ１３４ａを使用する場合の最適設計値に対して特定の範囲だけ拡大し、それによってその部分の圧力損失を効率よく大幅に低下させるようにしたものである。これにより、密度が高く冷媒流量が増加する傾向となる新冷媒ＨＦＯ１２３４ｙｆを使用する場合に、主圧力損失発生部における圧力損失を適切に低下させて、圧縮機の消費動力の増加を適切に抑え、ひいてはその圧縮機を使用する冷凍サイクルの成績係数（ＣＯＰ）を高めることが可能になる。   That is, in the compressor, regarding the flow path portion that has mainly generated pressure loss when the refrigerant HFC134a is used, the cross-sectional area of the flow path is a specific range with respect to the optimum design value when the refrigerant HFC134a is used. The pressure loss of the portion is effectively and greatly reduced by expanding only by that. Thereby, when using the new refrigerant HFO1234yf that tends to increase the refrigerant flow rate with high density, appropriately reduce the pressure loss in the main pressure loss generation unit, and appropriately suppress the increase in power consumption of the compressor, As a result, the coefficient of performance (COP) of the refrigeration cycle using the compressor can be increased.

圧縮機における吸入・吐出に伴う損失仕事は、つまり上記主圧力損失発生部における損失仕事は、とくに、シリンダへの冷媒吸入路および／またはシリンダからの冷媒吐出路の絞り部において発生する。換言すれば、圧縮機における損失仕事は、シリンダへの冷媒吸入路および／またはシリンダからの冷媒吐出路が絞られていることに起因する圧力損失が殆どである。後述の試験結果の範囲では、新冷媒ＨＦＯ１２３４ｙｆを使用する場合には、現行冷媒ＨＦＣ１３４ａを使用する場合に比べ、圧力損失は１．０１〜１．２７倍、つまり約１．０〜１．３倍になる。   The work lost due to suction / discharge in the compressor, that is, the work lost in the main pressure loss generating part, is generated particularly in the throttle part of the refrigerant suction path to the cylinder and / or the refrigerant discharge path from the cylinder. In other words, most of the lost work in the compressor is a pressure loss due to the restriction of the refrigerant suction path to the cylinder and / or the refrigerant discharge path from the cylinder. In the range of test results described later, when using the new refrigerant HFO1234yf, the pressure loss is 1.01 to 1.27 times, that is, about 1.0 to 1.3 times that when using the current refrigerant HFC134a. become.

このような試験結果を反映させる場合、新冷媒ＨＦＯ１２３４ｙｆを使用する場合の圧力損失の増加を適切に抑制するためには、上記絞り部における最小流路断面積が、冷媒にＨＦＣ１３４ａを使用する場合の最小流路断面積の１．０５〜１．４０倍程度に拡大されていることが好ましい。このような流路断面積の拡大により、目標とする圧力損失の増加の抑制、圧縮機の消費動力の増加の抑制、ひいては目標とする冷凍サイクルの成績係数（ＣＯＰ）の実現が可能となる。   When reflecting such test results, in order to appropriately suppress an increase in pressure loss when using the new refrigerant HFO1234yf, the minimum flow path cross-sectional area in the throttle portion is the case where HFC134a is used as the refrigerant. It is preferably enlarged to about 1.05 to 1.40 times the minimum flow path cross-sectional area. By such an increase in the cross-sectional area of the flow path, it is possible to suppress the target increase in pressure loss, suppress the increase in power consumption of the compressor, and realize the target coefficient of performance (COP) of the refrigeration cycle.

上記主圧力損失発生部の目標とする流路断面積の拡大は、とくに、シリンダへの冷媒吸入孔、シリンダからの冷媒吐出孔、吸入弁の規制変位量、吐出弁の規制変位量の少なくとも一つの拡大により行うことが効果的である。   The enlargement of the target flow path cross-sectional area of the main pressure loss generating part is at least one of the refrigerant suction hole to the cylinder, the refrigerant discharge hole from the cylinder, the restriction displacement amount of the suction valve, and the restriction displacement amount of the discharge valve. It is effective to do so by expanding two.

このような本発明に係る圧縮機は、基本的には新冷媒ＨＦＯ１２３４ｙｆを使用しようとするあらゆる圧縮機に適用可能であるが、とくに効率の良い運転や、冷凍機油の劣化を防止して長期間にわたって高い耐久性が求められる車両用空調装置に用いられる圧縮機として好適なものである。   Such a compressor according to the present invention is basically applicable to any compressor that intends to use the new refrigerant HFO1234yf. However, the compressor is particularly efficient and prevents deterioration of the refrigeration oil for a long time. It is suitable as a compressor used in a vehicle air conditioner that requires high durability over a wide range.

本発明は、上記のような圧縮機を組み込んだ冷凍サイクル、すなわち、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を備えた冷凍サイクルであって、冷媒としてＨＦＯ１２３４ｙｆを使用するとともに、圧縮機として上記のような圧縮機を用いることを特徴とする冷凍サイクルについても提供する。   The present invention is a refrigeration cycle incorporating a compressor as described above, that is, a compressor that compresses a refrigerant, a condenser that condenses the compressed refrigerant, a decompression and expansion means that decompresses and expands the condensed refrigerant, There is also provided a refrigeration cycle comprising an evaporator for evaporating a decompressed / expanded refrigerant, wherein HFO1234yf is used as the refrigerant, and the above-described compressor is used as the compressor. .

このような冷凍サイクルにおいては、圧力損失の低い圧縮機を用いることにより、圧縮機の消費動力が低く抑えられ、高い冷凍サイクルの成績係数（ＣＯＰ）が達成される。   In such a refrigeration cycle, by using a compressor with a low pressure loss, the power consumption of the compressor is kept low, and a high coefficient of performance (COP) of the refrigeration cycle is achieved.

本発明に係る圧縮機によれば、新冷媒ＨＦＯ１２３４ｙｆを使用する場合に、圧力損失の低く抑えて消費動力を低く抑えることが可能になる。この圧縮機を用いた冷凍サイクルでは、新冷媒ＨＦＯ１２３４ｙｆを使用しても高い成績係数（ＣＯＰ）の実現が可能になる。   According to the compressor according to the present invention, when the new refrigerant HFO1234yf is used, it is possible to suppress the pressure loss to a low level and to reduce the power consumption. In the refrigeration cycle using this compressor, a high coefficient of performance (COP) can be realized even when the new refrigerant HFO1234yf is used.

以下に、本発明について、試験結果を主体に、図面を参照しながら説明する。
試験は、圧縮機単体に試験（圧縮機試験）と、その圧縮機冷凍サイクル中に組み込んだシステム試験とにおいて、現行冷媒ＨＦＣ１３４ａを使用した場合と新冷媒ＨＦＯ１２３４ｙｆを使用した場合とについて行った。冷凍サイクルにおける配設機器の基本構成としては、図１に示したものと同等とした。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とを備えており、冷凍能力を向上させるために、冷凍サイクル１における蒸発器５の出口側冷媒が過熱状態とされたり、凝縮器３出口側において過冷却状態とされたりしてもよい。 Hereinafter, the present invention will be described with reference to the drawings mainly based on test results.
The tests were performed for the case where the current refrigerant HFC134a was used and the case where the new refrigerant HFO1234yf was used in the test (compressor test) for the compressor alone and the system test incorporated in the compressor refrigeration cycle. The basic configuration of the arrangement equipment in the refrigeration cycle was 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 and an evaporator 5 for evaporating the decompressed / expanded refrigerant are provided. In order to improve the refrigeration capacity, the outlet side refrigerant of the evaporator 5 in the refrigeration cycle 1 is overheated, or the condenser 3 It may be in a supercooled state on the outlet side.

試験は、システム試験においては、圧縮機回転数、蒸発器入口温度、蒸発器前面風量、凝縮器入口温度、凝縮器前面風量の条件を各種変更し、圧縮機試験においては、圧縮機回転数、吐出圧力、吸入圧力、圧縮機入口過熱度等のの条件を各種変更して行った。試験結果のデータは、図２に示すように、主として現行冷媒ＨＦＣ１３４ａとを使用した場合に対する新冷媒ＨＦＯ１２３４ｙｆを使用した場合の比として採取した。具体的には、図２の各プロットに示すように、システム試験における圧縮機吸入側と吐出側、圧縮機試験における圧縮機吸入側と吐出側とについて、冷媒流量比（ＨＦＯ１２３４ｙｆ／ＨＦＣ１３４ａ）と、圧縮機の圧力損失比（ＨＦＯ１２３４ｙｆ／ＨＦＣ１３４ａ）との関係として求めた。図２における多数のプロットは、実際の圧縮機、システムの運転範囲を考慮した試験結果として得られたものであり、新冷媒ＨＦＯ１２３４ｙｆを使用する場合の最適設計条件を求めるための試験結果として使用可能なものである。   In the system test, various conditions were changed for the compressor rotation speed, the evaporator inlet temperature, the evaporator front airflow, the condenser inlet temperature, and the condenser front airflow. In the compressor test, the compressor rotation speed, Various conditions such as discharge pressure, suction pressure, and compressor inlet superheat were changed. As shown in FIG. 2, the test result data was collected as a ratio when the new refrigerant HFO1234yf was used with respect to the case where the current refrigerant HFC134a was mainly used. Specifically, as shown in each plot of FIG. 2, the refrigerant flow rate ratio (HFO1234yf / HFC134a) for the compressor suction side and discharge side in the system test, and the compressor suction side and discharge side in the compressor test, It calculated | required as a relationship with the pressure loss ratio (HFO1234yf / HFC134a) of a compressor. A large number of plots in FIG. 2 are obtained as test results in consideration of the operation range of the actual compressor and system, and can be used as test results for obtaining optimum design conditions when using the new refrigerant HFO1234yf. It is a thing.

上記試験結果からは、図２に示すように、圧縮機における圧力損失比（ＨＦＯ１２３４ｙｆ／ＨＦＣ１３４ａ）は１．０１〜１．２７倍の範囲となった。この結果を反映させて新冷媒ＨＦＯ１２３４ｙｆを使用する場合の圧力損失の増加を適切に抑制するためには、計算上、主圧力損失発生部、とくに吸入側および／または吐出側流路の絞り部における最小流路断面積を、冷媒にＨＦＣ１３４ａを使用する場合の最小流路断面積の１．０５〜１．４０倍程度に拡大すればよいことが分かった。このような適切な流路断面積の拡大により、前述したように、新冷媒ＨＦＯ１２３４ｙｆを使用する場合の目標性能、つまり、圧力損失の増加の抑制、圧縮機の消費動力の増加の抑制、ひいては目標とする冷凍サイクルの成績係数（ＣＯＰ）の実現が可能となる。   From the above test results, as shown in FIG. 2, the pressure loss ratio (HFO1234yf / HFC134a) in the compressor was in the range of 1.01 to 1.27 times. In order to appropriately suppress the increase in pressure loss when the new refrigerant HFO1234yf is used by reflecting this result, the calculation is performed in the main pressure loss generation part, particularly in the throttle part of the suction side and / or discharge side flow path. It has been found that the minimum channel cross-sectional area may be increased to about 1.05 to 1.40 times the minimum channel cross-sectional area when using HFC134a as the refrigerant. As described above, by appropriately expanding the flow path cross-sectional area, the target performance when using the new refrigerant HFO1234yf, that is, suppression of increase in pressure loss, suppression of increase in power consumption of the compressor, and target The coefficient of performance (COP) of the refrigeration cycle can be realized.

本発明に係る圧縮機および冷凍サイクルは、基本的に新冷媒ＨＦＯ１２３４ｙｆを使用するあらゆる圧縮機および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圧縮機および冷凍サイクルとして好適なものである。   The compressor and the refrigeration cycle according to the present invention are basically applicable to any compressor and refrigeration cycle using the new refrigerant HFO1234yf, and particularly suitable as a compressor and a refrigeration cycle used in a vehicle air conditioner. is there.

本発明で対象としている圧縮機を用いた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 using the compressor made into object by this invention. 新冷媒ＨＦＯ１２３４ｙｆを使用する場合の最適設計条件を求めるための試験結果を示す、冷媒流量比（ＨＦＯ１２３４ｙｆ／ＨＦＣ１３４ａ）と圧縮機の圧力損失比（ＨＦＯ１２３４ｙｆ／ＨＦＣ１３４ａ）との関係図である。It is a relationship figure of the refrigerant | coolant flow rate ratio (HFO1234yf / HFC134a) and the pressure loss ratio (HFO1234yf / HFC134a) which shows the test result for calculating | requiring the optimal design conditions in the case of using new refrigerant | coolant HFO1234yf.

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 DESCRIPTION OF SYMBOLS 1 Refrigeration cycle 2 Compressor 3 Condenser 4 Expansion valve 5 as decompression / expansion means Evaporator

Claims (6)

冷媒を圧縮する圧縮機であって、冷媒としてＨＦＯ１２３４ｙｆを使用するとともに、冷媒にＨＦＣ１３４ａを使用する場合に比べ、主圧力損失発生部の流路断面積を１．０５〜１．４０倍に拡大したことを特徴とする圧縮機。   The compressor compresses the refrigerant, and HFO1234yf is used as the refrigerant, and the flow passage cross-sectional area of the main pressure loss generating part is expanded by 1.05-1.40 times compared to the case where HFC134a is used as the refrigerant. A compressor characterized by that. 前記主圧力損失発生部が、シリンダへの冷媒吸入路および／またはシリンダからの冷媒吐出路の絞り部からなる、請求項１に記載の圧縮機。   The compressor according to claim 1, wherein the main pressure loss generation unit includes a refrigerant suction path to the cylinder and / or a throttle section of a refrigerant discharge path from the cylinder. 前記絞り部における最小流路断面積が、冷媒にＨＦＣ１３４ａを使用する場合の最小流路断面積の１．０５〜１．４０倍に拡大されている、請求項２に記載の圧縮機。   The compressor according to claim 2, wherein the minimum flow path cross-sectional area in the throttle portion is expanded to 1.05 to 1.40 times the minimum flow path cross-sectional area when HFC134a is used as the refrigerant. 前記主圧力損失発生部の流路断面積の拡大が、シリンダへの冷媒吸入孔、シリンダからの冷媒吐出孔、吸入弁の規制変位量、吐出弁の規制変位量の少なくとも一つの拡大により行われている、請求項１〜３のいずれかに記載の圧縮機。   The flow passage cross-sectional area of the main pressure loss generator is enlarged by at least one of the refrigerant suction hole to the cylinder, the refrigerant discharge hole from the cylinder, the restriction displacement amount of the suction valve, and the restriction displacement amount of the discharge valve. The compressor according to any one of claims 1 to 3. 車両用空調装置に用いられる、請求項１〜４のいずれかに記載の圧縮機。   The compressor in any one of Claims 1-4 used for a vehicle air conditioner. 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を備えた冷凍サイクルにおいて、冷媒としてＨＦＯ１２３４ｙｆを使用するとともに、前記圧縮機として請求項１〜５のいずれかに記載の圧縮機を用いることを特徴とする冷凍サイクル。   In a refrigeration cycle comprising a compressor for compressing refrigerant, a condenser for condensing the compressed refrigerant, a decompression / expansion means for decompressing / expanding the condensed refrigerant, and an evaporator for evaporating the decompressed / expanded refrigerant, While using HFO1234yf as a refrigerant | coolant, the compressor in any one of Claims 1-5 is used as the said compressor, The refrigerating cycle characterized by the above-mentioned.
JP2008122043A 2008-05-08 2008-05-08 Compressor and refrigerating cycle using it Pending JP2009270496A (en)

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JP2014145366A (en) * 2014-05-20 2014-08-14 Mitsubishi Electric Corp Refrigerant compressor

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JP2014145366A (en) * 2014-05-20 2014-08-14 Mitsubishi Electric Corp Refrigerant compressor

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