JP4539571B2 - Vapor compression cycle - Google Patents

Vapor compression cycle Download PDF

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JP4539571B2
JP4539571B2 JP2006018052A JP2006018052A JP4539571B2 JP 4539571 B2 JP4539571 B2 JP 4539571B2 JP 2006018052 A JP2006018052 A JP 2006018052A JP 2006018052 A JP2006018052 A JP 2006018052A JP 4539571 B2 JP4539571 B2 JP 4539571B2
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refrigerant
heat exchanger
indoor
indoor heat
outdoor
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JP2007198675A (en
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英明 石田
崇宏 中馬
正▲琢▼ 今津
裕嗣 武内
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Denso Corp
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Denso Corp
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Priority to CNB200610163030XA priority patent/CN100535546C/en
Priority to IT000029A priority patent/ITRM20070029A1/en
Priority to DE102007003870A priority patent/DE102007003870A1/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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02731—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2400/23—Separators

Description

本発明は、冷媒減圧手段の役割および冷媒循環手段の役割を果たすエジェクタを用いた蒸気圧縮式サイクルに関するもので、例えば、家庭用空調装置、車両用空調装置等に適用して有効である。   The present invention relates to a vapor compression cycle using an ejector that serves as a refrigerant decompression unit and a refrigerant circulation unit, and is effective when applied to, for example, a domestic air conditioner, a vehicle air conditioner, and the like.

従来、エジェクタを用いた蒸気圧縮式の冷凍サイクルとして、例えば特許文献１に示されるものが知られている。即ち、この冷凍サイクルは、冷媒圧縮機、室外熱交換器、エジェクタ、気液分離器が環状に接続されると共に、気液分離器とエジェクタの冷媒吸引口とを繋ぐ分岐流路に第１室内熱交換器が配設され、また、冷媒圧縮機と室外熱交換器との間に第２室内熱交換器および減圧器が配設されて形成されている。そして冷媒配管の所定部位にバイパス通路が介在されている。   Conventionally, as a vapor compression refrigeration cycle using an ejector, for example, one disclosed in Patent Document 1 is known. In other words, this refrigeration cycle includes a refrigerant compressor, an outdoor heat exchanger, an ejector, and a gas-liquid separator that are annularly connected, and a branch passage that connects the gas-liquid separator and the refrigerant suction port of the ejector to the first chamber. A heat exchanger is disposed, and a second indoor heat exchanger and a decompressor are disposed between the refrigerant compressor and the outdoor heat exchanger. A bypass passage is interposed at a predetermined portion of the refrigerant pipe.

この冷凍サイクルにおいては、バイパス通路を切替えて冷媒の流れを変えることで以下の３つの運転を可能としている。即ち、第１室内熱交換器で吸熱して、室外熱交換器で放熱することで冷房運転を可能とし、室外熱交換器で吸熱して、第２室内熱交換器で放熱することで暖房運転を可能とし、更に、室外熱交換器および第１室内熱交換器で吸熱して、第２室内熱交換器で放熱することで除湿暖房運転を可能としている。
特開２００４−２６００４号公報 In this refrigeration cycle, the following three operations are possible by changing the flow of the refrigerant by switching the bypass passage. That is, the cooling operation can be performed by absorbing heat with the first indoor heat exchanger and radiating heat with the outdoor heat exchanger, and the heating operation with absorbing heat with the outdoor heat exchanger and radiating heat with the second indoor heat exchanger. Furthermore, the dehumidifying and heating operation is enabled by absorbing heat with the outdoor heat exchanger and the first indoor heat exchanger and dissipating heat with the second indoor heat exchanger.
JP 200426004 A

しかしながら、上記冷凍サイクルにおいては、冷房運転時は第２室内熱交換器に装着されたエアミックスドアが閉じられて第２室内熱交換器による熱交換が成されないようにしており、また、暖房運転時はバイパス通路の切替えによって第１室内熱交換器が使用されない形となっている。よって、システム全体としてはすべての熱交換器が使用されないので、効率的でなく、コスト的には割高のものとなっている。   However, in the refrigeration cycle, during the cooling operation, the air mix door attached to the second indoor heat exchanger is closed so that heat exchange by the second indoor heat exchanger is not performed, and heating operation is performed. At times, the first indoor heat exchanger is not used by switching the bypass passage. Therefore, since not all heat exchangers are used in the entire system, the system is not efficient and is expensive.

本発明の目的は、上記問題に鑑み、配設される複数の熱交換器を常に有効に活用して、効率的に冷房、暖房、除湿暖房運転を可能とする蒸気圧縮式サイクルを提供することにある。   In view of the above problems, an object of the present invention is to provide a vapor compression cycle that can efficiently perform cooling, heating, and dehumidifying heating operations by effectively utilizing a plurality of arranged heat exchangers at all times. It is in.

本発明は上記目的を達成するために、以下の技術的手段を採用する。   In order to achieve the above object, the present invention employs the following technical means.

請求項１に記載の発明では、蒸気圧縮式サイクルにおいて、冷媒を吸入し圧縮する圧縮機（１１０）と、冷媒および室外空気の間で熱交換する室外熱交換器（１３０）と、室外熱交換器（１３０）から接続されて、開度調整可能とするノズル（１４１）によって高圧の冷媒を減圧膨張させると共に、冷媒吸引口（１４２）から冷媒を吸引した後に昇圧部（１４３）で昇圧させるエジェクタ（１４０）と、エジェクタ（１４０）から接続されて、冷媒と室内空気との間で熱交換する第１室内熱交換器（１５０）と、室外熱交換器（１３０）およびエジェクタ（１４０）の間から分岐して、冷媒吸引口（１４２）に接続される分岐流路（１６１）に配設されて、冷媒を減圧膨張させる減圧器（１６０）と、分岐流路（１６１）の減圧器（１６０）および冷媒吸引口（１４２）の間に配設されて、冷媒および室内空気の間で熱交換する第２室内熱交換器（１７０）と、圧縮機（１１０）が、第１室内熱交換（１５０）から冷媒を吸入して室外熱交換器（１３０）に吐出するように、あるいは室外熱交換器（１３０）から冷媒を吸入して第１室内熱交換器（１５０）に吐出するように冷媒の流路を切替える流路切替え手段（１２０）と、分岐流路（１６１）の第２室内熱交換器（１７０）および冷媒吸引口（１４２）の間に配設されて、分岐流路（１６１）の絞り度を可変する可変絞り（１８０）とを設けたことを特徴としている。   According to the first aspect of the present invention, in the vapor compression cycle, the compressor (110) that sucks and compresses the refrigerant, the outdoor heat exchanger (130) that exchanges heat between the refrigerant and the outdoor air, and the outdoor heat exchange. Ejector that is connected from the vessel (130) and decompresses and expands the high-pressure refrigerant by the nozzle (141) that allows the opening degree to be adjusted, and after the refrigerant is sucked from the refrigerant suction port (142), the pressure is increased by the pressure increasing unit (143) (140) and the first indoor heat exchanger (150) connected from the ejector (140) and exchanging heat between the refrigerant and the room air, and between the outdoor heat exchanger (130) and the ejector (140) And a decompressor (160) disposed in a branch channel (161) connected to the refrigerant suction port (142) to decompress and expand the refrigerant, and a decompressor (160) of the branch channel (161). ) And a second indoor heat exchanger (170) disposed between the refrigerant suction port (142) and exchanging heat between the refrigerant and room air, and a compressor (110) are connected to the first indoor heat exchanger (150). ) So that the refrigerant is sucked and discharged to the outdoor heat exchanger (130), or the refrigerant is sucked from the outdoor heat exchanger (130) and discharged to the first indoor heat exchanger (150). The branch channel (161) is disposed between the channel switching means (120) for switching the channel and the second indoor heat exchanger (170) and the refrigerant suction port (142) of the branch channel (161). And a variable diaphragm (180) that varies the degree of diaphragm.

これにより、室外熱交換器（１３０）、第１室内熱交換器（１５０）、第２室内熱交換器（１７０）の３つの熱交換器を常に活用した冷房運転、暖房運転、除湿暖房運転が可能となる。   As a result, the cooling operation, the heating operation, and the dehumidifying heating operation using the three heat exchangers of the outdoor heat exchanger (130), the first indoor heat exchanger (150), and the second indoor heat exchanger (170) are always performed. It becomes possible.

即ち、流路切替え手段（１２０）によって圧縮機（１１０）が第１室内熱交換器（１５０）から冷媒を吸入して、室外熱交換器（１３０）に吐出するように冷媒の流路を切替えると共に、可変絞り（１８０）を全開として絞り度を無くすことで、圧縮機（１１０）から吐出された冷媒は、室外熱交換器（１３０）からエジェクタ（１４０）および分岐流路（１６１）を流れる。そして、分岐流路（１６１）に流入した冷媒は、減圧器（１６０）で減圧されて第２室内熱交換器（１７０）に流入すると共に、全開となる可変絞り（１８０）を通過して、エジェクタ（１４０）の冷媒吸引口（１４２）に流入する。室外熱交換器（１３０）からエジェクタ（１４０）に流入した冷媒は、ノズル（１４１）によって減圧膨張され、また、冷媒吸引口（１４２）から吸引される冷媒と混合され、昇圧部（１４３）で昇圧されて第１室内熱交換器（１５０）に流入し、圧縮機（１１０）に戻る。よって、この場合の蒸気圧縮式サイクル（１００）では、第１、第２室内熱交換器（１５０、１７０）で室内空気から吸熱して、この熱を室外熱交換器（１３０）で放熱する形となり、第１、第２室内熱交換器（１５０、１７０）で室内空気を冷却する冷房運転が可能となる。   That is, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the first indoor heat exchanger (150) and discharges it to the outdoor heat exchanger (130). At the same time, the variable throttle (180) is fully opened to eliminate the throttle, so that the refrigerant discharged from the compressor (110) flows from the outdoor heat exchanger (130) through the ejector (140) and the branch flow path (161). . Then, the refrigerant flowing into the branch channel (161) is decompressed by the decompressor (160) and flows into the second indoor heat exchanger (170), and passes through the variable throttle (180) that is fully opened, It flows into the refrigerant suction port (142) of the ejector (140). The refrigerant flowing into the ejector (140) from the outdoor heat exchanger (130) is decompressed and expanded by the nozzle (141) and mixed with the refrigerant sucked from the refrigerant suction port (142). The pressure is increased and flows into the first indoor heat exchanger (150) and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the first and second indoor heat exchangers (150, 170) absorb heat from the indoor air, and the heat is radiated by the outdoor heat exchanger (130). Thus, the cooling operation in which the indoor air is cooled by the first and second indoor heat exchangers (150, 170) becomes possible.

また、流路切替え手段（１２０）によって圧縮機（１１０）が室外熱交換器（１３０）から冷媒を吸入して、第１室内熱交換器（１５０）に吐出するように冷媒の流路を切替えると共に、エジェクタ（１４０）のノズル（１４１）を全閉とし、更に、可変絞り（１８０）を全開として絞り度を無くすことで、圧縮機（１１０）から吐出された冷媒は、第１室内熱交換器（１５０）に流入する。そして、冷媒はエジェクタ（１４０）の昇圧部（１４３）から冷媒吸引部（１４２）を抜けて、全開となる可変絞り（１８０）を通過して、第２室内熱交換器（１７０）に流入する。第２室内熱交換器（１７０）から流出する冷媒は、減圧器（１６０）で減圧されて室外熱交換器（１３０）に流入し、圧縮機（１１０）に戻る。よって、この場合の蒸気圧縮式サイクル（１００）では、室外熱交換器（１３０）で室外空気から吸熱して、この熱を第１、第２室内熱交換器（１５０、１７０）で放熱する形となり、第１、第２室内熱交換器（１５０、１７０）で室内空気を加熱する暖房運転が可能となる。   Further, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the outdoor heat exchanger (130) and discharges it to the first indoor heat exchanger (150). At the same time, the nozzle (141) of the ejector (140) is fully closed, and further, the variable throttle (180) is fully opened to eliminate the throttle degree, so that the refrigerant discharged from the compressor (110) is subjected to the first indoor heat exchange. Into the vessel (150). Then, the refrigerant passes through the refrigerant suction part (142) from the pressure raising part (143) of the ejector (140), passes through the variable throttle (180) that is fully opened, and flows into the second indoor heat exchanger (170). . The refrigerant flowing out of the second indoor heat exchanger (170) is decompressed by the decompressor (160), flows into the outdoor heat exchanger (130), and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the outdoor heat exchanger (130) absorbs heat from the outdoor air, and the heat is radiated by the first and second indoor heat exchangers (150, 170). Thus, the heating operation for heating the indoor air with the first and second indoor heat exchangers (150, 170) becomes possible.

更に、流路切替え手段（１２０）によって圧縮機（１１０）が第１室内熱交換器（１５０）から冷媒を吸入して、室外熱交換器（１３０）に吐出するように冷媒の流路を切替えると共に、エジェクタ（１４０）のノズル（１４１）を全閉とし、更に、可変絞り（１８０）を絞って所定の絞り度することで、圧縮機（１１０）から吐出された冷媒は、室外熱交換器（１３０）から分岐流路（１６１）を流れる。そして、分岐流路（１６１）に流入した冷媒は、減圧器（１６０）で減圧されて第２室内熱交換器（１７０）に流入すると共に、可変絞り（１８０）で減圧されて、エジェクタ（１４０）の冷媒吸引口（１４２）に流入する。エジェクタ（１４０）の冷媒吸引口（１４２）に流入した冷媒は、昇圧部（１４３）を通り第１室内熱交換器（１５０）に流入し、圧縮機（１１０）に戻る。よって、この場合の蒸気圧縮式サイクル（１００）では、第１室内熱交換器（１５０）で室内空気から吸熱して、この熱を室外熱交換器（１３０）および第２室内熱交換器（１７０）で放熱する形となり、第１室内熱交換器（１５０）で室内空気を冷却すると共に、第２室内熱交換器（１７０）で室内空気を加熱する除湿暖房運転が可能となる。   Further, the flow path switching means (120) switches the refrigerant flow path so that the compressor (110) sucks the refrigerant from the first indoor heat exchanger (150) and discharges it to the outdoor heat exchanger (130). At the same time, the nozzle (141) of the ejector (140) is fully closed, and further, the variable throttle (180) is throttled to a predetermined throttle degree, so that the refrigerant discharged from the compressor (110) becomes the outdoor heat exchanger. (130) flows through the branch channel (161). Then, the refrigerant flowing into the branch flow path (161) is decompressed by the decompressor (160) and flows into the second indoor heat exchanger (170), and is decompressed by the variable restrictor (180) to be ejected by the ejector (140 ) Flows into the refrigerant suction port (142). The refrigerant that has flowed into the refrigerant suction port (142) of the ejector (140) flows into the first indoor heat exchanger (150) through the pressure increase unit (143) and returns to the compressor (110). Therefore, in the vapor compression cycle (100) in this case, the first indoor heat exchanger (150) absorbs heat from the indoor air, and this heat is absorbed by the outdoor heat exchanger (130) and the second indoor heat exchanger (170). ), The indoor air is cooled by the first indoor heat exchanger (150), and the dehumidifying and heating operation in which the indoor air is heated by the second indoor heat exchanger (170) becomes possible.

請求項２に記載の発明では、流路切替え手段（１２０）は、圧縮機（１１０）の吸入側、圧縮機（１１０）の吐出側、室外熱交換器（１３０）側、第１室内熱交換器（１５０）側の４点が接続されて、所定の２点同士を連通すると共に、その連通の組合せを切替え可能とする四方弁（１２０）としたことを特徴としており、これにより、容易に流路切替え手段（１２０）を構成することができる。   In the invention according to claim 2, the flow path switching means (120) includes the suction side of the compressor (110), the discharge side of the compressor (110), the outdoor heat exchanger (130) side, and the first indoor heat exchange. The four points on the side of the vessel (150) are connected to communicate with each other between two predetermined points, and the four-way valve (120) that enables switching of the combination of the communication is provided. A flow path switching means (120) can be configured.

請求項３に記載の発明では、室外熱交換器（１３０）から減圧器（１６０）へ流れる冷媒と、第１室内熱交換器（１５０）から圧縮機（１１０）へ流れる冷媒との間で熱交換する内部熱交換器（１９５）が設けられたことを特徴としている。   In the invention according to claim 3, heat is generated between the refrigerant flowing from the outdoor heat exchanger (130) to the decompressor (160) and the refrigerant flowing from the first indoor heat exchanger (150) to the compressor (110). An internal heat exchanger (195) for replacement is provided.

これにより、冷房運転時、あるいは除湿暖房運転時において、放熱後の冷媒を吸熱後の冷媒で冷却することができるので、放熱後の冷媒のエンタルピを小さくすることができ、吸熱側における入口側と出口側とのエンタルピ差を大きくして、吸熱能力を増大させることができる。また、吸熱後の冷媒は逆に加熱されることになり、所定の過熱度を持つ気相冷媒とすることができるので、圧縮機（１１０）における液圧縮を確実に防止することができる。   Thereby, during cooling operation or dehumidifying heating operation, the heat-radiated refrigerant can be cooled by the heat-absorbed refrigerant, so that the enthalpy of the heat-radiated refrigerant can be reduced, and the inlet side on the heat absorption side can be reduced. The enthalpy difference from the outlet side can be increased to increase the heat absorption capacity. Moreover, since the refrigerant | coolant after heat absorption will be heated conversely and it can be set as the gaseous-phase refrigerant | coolant with a predetermined superheat degree, the liquid compression in a compressor (110) can be prevented reliably.

尚、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

（第１実施形態）
本発明の第１実施形態を図１に示す。第１実施形態は、本発明に係る蒸気圧縮式サイクル１００を乗用車、バス、トラック等の車両に搭載される車両用冷凍サイクル装置に適用したものである。尚、図１は蒸気圧縮式サイクル１００の全体構成を示す模式図であり、図１中の細線矢印は冷房運転時の冷媒の流れ方向を示すものである。 (First embodiment)
A first embodiment of the present invention is shown in FIG. In the first embodiment, the vapor compression cycle 100 according to the present invention is applied to a vehicle refrigeration cycle apparatus mounted on a vehicle such as a passenger car, a bus, or a truck. FIG. 1 is a schematic diagram showing the overall configuration of the vapor compression cycle 100, and the thin line arrows in FIG. 1 indicate the flow direction of the refrigerant during the cooling operation.

蒸気圧縮式サイクル１００において、冷媒を吸入圧縮する圧縮機１１０は、電磁クラッチ１１１、ベルト等を介して図示しない車両走行用エンジンにより回転駆動される。電磁クラッチ１１１の断続は、図示しない制御装置によって制御されるようにしている。   In the vapor compression cycle 100, a compressor 110 that sucks and compresses refrigerant is rotationally driven by a vehicle travel engine (not shown) via an electromagnetic clutch 111, a belt, and the like. The on / off state of the electromagnetic clutch 111 is controlled by a control device (not shown).

尚、この圧縮機１１０としては、吐出容量の変化により冷媒吐出能力を調整できる可変容量型圧縮機、あるいは電磁クラッチ１１１の断続により圧縮機作動の稼働率を変化させて冷媒吐出能力を調整する固定容量型圧縮機のいずれを使用しても良い。また、圧縮機１１０として電動圧縮機を使用すれば、電動モータの回転数調整により冷媒吐出能力を調整できる。   The compressor 110 may be a variable displacement compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or a fixed compressor that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by switching the electromagnetic clutch 111. Any of the capacity type compressors may be used. If an electric compressor is used as the compressor 110, the refrigerant discharge capacity can be adjusted by adjusting the rotation speed of the electric motor.

この圧縮機１１０の冷媒吐出側には流路切替え手段としての四方弁１２０が配設されている。四方弁１２０は、４つの接続部を有し、内部に設けられた例えば電気アクチュエータ機構によって、所定の２つの接続部同士を連通すると共に、その連通の組合せを切替え可能とする弁である。   On the refrigerant discharge side of the compressor 110, a four-way valve 120 as a flow path switching unit is disposed. The four-way valve 120 is a valve that has four connection portions, and that allows two predetermined connection portions to communicate with each other and switch the combination of the communication by, for example, an electric actuator mechanism provided therein.

具体的には、四方弁１２０の４つの接続部には吸入配管１１２、吐出配管１１３、室外用配管１３１、室内用配管１５１が接続されている。そして、四方弁１２０は、図１中の四方弁１２０内の実線で示されるように、吐出配管１１３と室外用配管１３１とを連通状態とすると共に、室内用配管１５１と吸入配管１１２とを連通状態とする第１パターン、および図１中の四方弁１２０内の破線で示されるように、吐出配管１１３と室内用配管１５１とを連通状態とすると共に、室外用配管１３１と吸入配管１１２とを連通状態とする第２パターンの切替えを可能としている。四方弁１２０の上記第１、第２パターンの切替えは、図示しない制御装置によって制御されるようにしている。   Specifically, a suction pipe 112, a discharge pipe 113, an outdoor pipe 131, and an indoor pipe 151 are connected to the four connecting portions of the four-way valve 120. As shown by the solid line in the four-way valve 120 in FIG. 1, the four-way valve 120 brings the discharge pipe 113 and the outdoor pipe 131 into communication and also connects the indoor pipe 151 and the suction pipe 112 with each other. As shown by the first pattern and the broken line in the four-way valve 120 in FIG. 1, the discharge pipe 113 and the indoor pipe 151 are in communication, and the outdoor pipe 131 and the suction pipe 112 are connected. It is possible to switch the second pattern to be in the communication state. The switching of the first and second patterns of the four-way valve 120 is controlled by a control device (not shown).

室外用配管１３１の反四方弁側には、例えば車両のエンジンルームに配設される室外熱交換器１３０の一端側が接続されている。室外熱交換器１３０は、内部を流通する冷媒と室外空気との間で熱交換する熱交換器である。   For example, one end side of an outdoor heat exchanger 130 disposed in an engine room of the vehicle is connected to the anti-four-way valve side of the outdoor pipe 131. The outdoor heat exchanger 130 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the outdoor air.

本実施形態では、蒸気圧縮式サイクル１００の冷媒として、二酸化炭素（ＣＯ２）を使用しており、四方弁１２０によって流路が第１パターンに切替えられた時に、圧縮機１１０から吐出される高圧圧力は臨界圧力を超える超臨界サイクルとなるようにしている。この場合、室外熱交換器１３０は、超臨界状態の冷媒の熱を室外空気に放出して、この冷媒を冷却する放熱器（ガスクーラ）として作用する。また、四方弁１２０の流路切替えによって、室外熱交換器１３０に室外空気よりも低温となる低圧の冷媒が流れる場合は、室外熱交換器１３０は室外空気から吸熱する吸熱器として作用する。 In the present embodiment, carbon dioxide (CO 2 ) is used as the refrigerant of the vapor compression cycle 100, and the high pressure discharged from the compressor 110 when the flow path is switched to the first pattern by the four-way valve 120. The pressure is set to a supercritical cycle exceeding the critical pressure. In this case, the outdoor heat exchanger 130 functions as a radiator (gas cooler) that releases the heat of the supercritical refrigerant to the outdoor air and cools the refrigerant. In addition, when the low-pressure refrigerant having a temperature lower than that of the outdoor air flows through the outdoor heat exchanger 130 by switching the flow path of the four-way valve 120, the outdoor heat exchanger 130 acts as a heat absorber that absorbs heat from the outdoor air.

尚、冷媒としては、通常のフロン系冷媒を用いても良く、この場合は、四方弁１２０によって流路が第１パターンに切替えられた時に、圧縮機１１０から吐出される高圧圧力は臨界圧力を超えない亜臨界サイクルとなるので、室外熱交換器１３０は冷媒を凝縮する凝縮器として作用する。   As the refrigerant, a normal chlorofluorocarbon refrigerant may be used. In this case, when the flow path is switched to the first pattern by the four-way valve 120, the high-pressure pressure discharged from the compressor 110 is the critical pressure. Since the subcritical cycle is not exceeded, the outdoor heat exchanger 130 acts as a condenser that condenses the refrigerant.

室外熱交換器１３０の他端側には、後述するノズル部（ノズル）１４１の開度を調整可能とする可変式のエジェクタ１４０が接続されている。このエジェクタ１４０は、冷媒を減圧する減圧手段であると共に、高速で噴出する冷媒流の吸引作用（巻き込み作用）によって冷媒の循環（流体輸送）を行う冷媒循環手段（運動量輸送式ポンプ）でもある（ＪＩＳ Ｚ ８１２６ 番号２．１．２．３等参照）。   Connected to the other end of the outdoor heat exchanger 130 is a variable ejector 140 that can adjust the opening degree of a nozzle portion (nozzle) 141 described later. The ejector 140 is a decompression means for decompressing the refrigerant, and is also a refrigerant circulation means (momentum transport type pump) that circulates the refrigerant (fluid transport) by suction action (contraction action) of the refrigerant flow ejected at high speed ( JIS Z 8126 number 2.1.2.3 etc.).

エジェクタ１４０は、室外熱交換器１３０から流入する高圧冷媒の通路面積（開度）を小さく絞って、高圧冷媒を等エントロピ的に減圧膨張させるノズル部１４１を有している。ノズル部１４１は、絞りとなる所定のノズル開度に対して、ノズル開度ゼロとなる全閉状態への切替えを可能としている。このノズル部１４１のノズル開度は、図示しない制御装置によって制御されるようにしている。   The ejector 140 includes a nozzle portion 141 that reduces the passage area (opening degree) of the high-pressure refrigerant flowing from the outdoor heat exchanger 130 to an isentropic decompression expansion. The nozzle unit 141 is capable of switching to a fully closed state where the nozzle opening is zero with respect to a predetermined nozzle opening serving as a throttle. The nozzle opening degree of the nozzle portion 141 is controlled by a control device (not shown).

エジェクタ１４０の側壁には、ノズル部１４１の冷媒噴出口となる空間に連通して、後述する第２室内熱交換器１７０からの気相冷媒を吸引する冷媒吸引口１４２が設けられている。更に、ノズル部１４１および冷媒吸引口１４２の冷媒流れ下流側部位には、ノズル部１４１からの高速度の冷媒流と冷媒吸引口１４２からの吸引冷媒とを混合した後に、混合冷媒を昇圧させる昇圧部１４３が設けられている。   The side wall of the ejector 140 is provided with a refrigerant suction port 142 that communicates with a space serving as a refrigerant outlet of the nozzle portion 141 and sucks a gas phase refrigerant from a second indoor heat exchanger 170 described later. Further, in the downstream part of the refrigerant flow of the nozzle part 141 and the refrigerant suction port 142, after the high-speed refrigerant flow from the nozzle part 141 and the suction refrigerant from the refrigerant suction port 142 are mixed, the pressure is increased to boost the mixed refrigerant. A portion 143 is provided.

エジェクタ１４０の昇圧部１４３には、第１室内熱交換器１５０の一端側が接続され、第１室内熱交換器１５０の他端側は室内用配管１５１に接続されている。第１室内熱交換器１５０は、内部を流通する冷媒と室内空気との間で熱交換する熱交換器である。更に具体的には、四方弁１２０の流路切替えによって、第１室内熱交換器１５０に室内空気よりも低温となる低圧の冷媒が流れる場合は、第１室内熱交換器１５０は室内空気から吸熱する吸熱器として作用する。また、四方弁１２０の流路切替えによって、第１室内熱交換器１５０に室内空気よりも高温となる高圧の冷媒が流れる場合は、第１室内熱交換器１５０は冷媒の熱を室内空気に放出する放熱器として作用する。   One end side of the first indoor heat exchanger 150 is connected to the booster 143 of the ejector 140, and the other end side of the first indoor heat exchanger 150 is connected to the indoor pipe 151. The first indoor heat exchanger 150 is a heat exchanger that exchanges heat between the refrigerant circulating in the interior and the room air. More specifically, when the low-pressure refrigerant having a temperature lower than the room air flows through the first indoor heat exchanger 150 by switching the flow path of the four-way valve 120, the first indoor heat exchanger 150 absorbs heat from the room air. It acts as a heat sink. In addition, when the high-pressure refrigerant having a temperature higher than the indoor air flows through the first indoor heat exchanger 150 by switching the flow path of the four-way valve 120, the first indoor heat exchanger 150 releases the heat of the refrigerant to the indoor air. Acts as a radiator.

エジェクタ１４０のノズル部１４１側と冷媒吸引部１４２との間には分岐流路としての分岐配管１６１が接続されている。即ち、分岐配管１６１は、室外熱交換器１３０とエジェクタ１４０との間から分岐して、分岐した先端側が冷媒吸引口１４２に接続される配管である。尚、図１中のＺは、分岐配管１６１の分岐点を示す。   A branch pipe 161 as a branch flow path is connected between the nozzle part 141 side of the ejector 140 and the refrigerant suction part 142. That is, the branch pipe 161 is a pipe branched from between the outdoor heat exchanger 130 and the ejector 140, and the branched tip end side is connected to the refrigerant suction port 142. Note that Z in FIG. 1 indicates a branch point of the branch pipe 161.

上記分岐配管１６１には絞り機構１６０が配設されている。絞り機構１６０は、絞り開度を調整可能として分岐配管１６１を絞ることで、ここを流通する冷媒を減圧膨張させる減圧器である。絞り機構１６０の絞り開度は、図示しない制御装置によって制御されるようにしている。   A throttle mechanism 160 is disposed in the branch pipe 161. The throttle mechanism 160 is a decompressor that decompresses and expands the refrigerant flowing through the branch pipe 161 by allowing the throttle opening to be adjusted. The aperture opening degree of the aperture mechanism 160 is controlled by a control device (not shown).

分岐配管１６１の絞り機構１６０とエジェクタ１４０の冷媒吸引口１４２との間には、第２室内熱交換器１７０が配設されている。第２室内熱交換器１７０は、内部を流通する冷媒と室内空気との間で熱交換する熱交換器である。更に具体的には、上記第１室内熱交換器１５０と同様に、四方弁１２０の流路切替えによって、第２室内熱交換器１７０に室内空気よりも低温となる低圧の冷媒が流れる場合は、第２室内熱交換器１７０は室内空気から吸熱する吸熱器として作用する。また、四方弁１２０の流路切替えによって、第２室内熱交換器１７０に室内空気よりも高温となる高圧の冷媒が流れる場合は、第２室内熱交換器１７０は冷媒の熱を室内空気に放出する放熱器として作用する。   A second indoor heat exchanger 170 is disposed between the throttle mechanism 160 of the branch pipe 161 and the refrigerant suction port 142 of the ejector 140. The second indoor heat exchanger 170 is a heat exchanger that exchanges heat between the refrigerant circulating in the interior and the room air. More specifically, as in the case of the first indoor heat exchanger 150, when a low-pressure refrigerant having a temperature lower than the room air flows through the second indoor heat exchanger 170 by switching the flow path of the four-way valve 120, The second indoor heat exchanger 170 acts as a heat absorber that absorbs heat from room air. In addition, when a high-pressure refrigerant having a temperature higher than the room air flows through the second indoor heat exchanger 170 by switching the flow path of the four-way valve 120, the second indoor heat exchanger 170 releases the heat of the refrigerant into the room air. Acts as a radiator.

第２室内熱交換器１７０は、上記した第１室内熱交換器１５０と共に、空調ケース１５０Ｂ内に収容されて、空調ユニット１５０Ａを形成している。空調ユニット１５０Ａは、例えば車室内のインストルメントパネル内に配設されている。空調ユニット１５０Ａにおいては、図１中の太線矢印で示すように、図示しない送風機によって、第１室内熱交換器１５０側から第２室内熱交換器１７０側に室内空気（車室内に取り込んだ室外空気、あるいはもともとの室内空気）が供給されて、第１、第２室内熱交換器１５０、１７０によって、室内空気は熱交換されて、熱交換された室内空気は車室内に吹出される。   The second indoor heat exchanger 170 is housed in the air conditioning case 150B together with the first indoor heat exchanger 150 to form an air conditioning unit 150A. The air conditioning unit 150A is disposed, for example, in an instrument panel in the passenger compartment. In the air conditioning unit 150A, as indicated by a thick arrow in FIG. 1, indoor air (outdoor air taken into the vehicle interior) is transferred from the first indoor heat exchanger 150 side to the second indoor heat exchanger 170 side by a blower (not shown). Or the original indoor air) is supplied, and the first and second indoor heat exchangers 150 and 170 exchange the heat of the indoor air, and the heat-exchanged indoor air is blown into the vehicle interior.

更に、分岐配管１６１の第２室内熱交換器１７０と、エジェクタ１４０の冷媒吸引口１４２との間には、絞り機構１８０が配設されている。絞り機構１８０は、絞り開度を調整可能として分岐配管１６１を絞ることで、ここを流通する冷媒を減圧膨張させる可変絞りとしている。尚、絞り機構１８０の絞り開度は、分岐配管１６１と同等の流路面積を確保する全開状態まで調整可能となっている。そして、絞り機構１８０の絞り開度は、図示しない制御装置によって制御されるようにしている。   Further, a throttle mechanism 180 is disposed between the second indoor heat exchanger 170 of the branch pipe 161 and the refrigerant suction port 142 of the ejector 140. The throttle mechanism 180 is a variable throttle that decompresses and expands the refrigerant circulating through the branch pipe 161 by adjusting the throttle opening degree. The throttle opening of the throttle mechanism 180 can be adjusted to a fully open state that ensures a flow path area equivalent to that of the branch pipe 161. The throttle opening degree of the throttle mechanism 180 is controlled by a control device (not shown).

吸入配管１１２の途中には、ここを流れる冷媒を気液２相に分離するアキュムレータ（気液分離器）１９０が配設されている。アキュムレータ１９０は、分離した冷媒のうち液相冷媒を内部に溜めて、気相冷媒を流通させる。   An accumulator (gas-liquid separator) 190 that separates the refrigerant flowing therethrough into a gas-liquid two phase is disposed in the middle of the suction pipe 112. The accumulator 190 stores the liquid-phase refrigerant among the separated refrigerants, and distributes the gas-phase refrigerant.

そして、本蒸気圧縮式サイクル１００には、室外熱交換器１３０から絞り機構１６０へ流れる冷媒、更に具体的には室外熱交換器１３０から分岐点Ｚへ流れる冷媒と、四方弁１２０が第１パターンに切替えられた時の第１室内熱交換器１５０から圧縮機１１０へ流れる冷媒、更に具体的にはアキュムレータ１９０から圧縮機１１０へ流れる冷媒との間で熱交換する内部熱交換器１９５が設けられている。内部熱交換器１９５は、内部に２つの流路を有しており、両流路を流れる冷媒の間で熱交換する。   In the vapor compression cycle 100, the refrigerant flowing from the outdoor heat exchanger 130 to the expansion mechanism 160, more specifically, the refrigerant flowing from the outdoor heat exchanger 130 to the branch point Z, and the four-way valve 120 have a first pattern. An internal heat exchanger 195 for exchanging heat with the refrigerant flowing from the first indoor heat exchanger 150 to the compressor 110, more specifically with the refrigerant flowing from the accumulator 190 to the compressor 110, is provided. ing. The internal heat exchanger 195 has two flow paths inside and exchanges heat between the refrigerants flowing through both flow paths.

次に、上記構成に基づく第１実施形態の作動について、図２〜図６を加えて説明する。尚、図２は冷房運転時における冷媒状態を示すモリエル線図、図３は蒸気圧縮式サイクル１００の暖房運転時の冷媒流れを示す模式図、図４は暖房運転時における冷媒状態を示すモリエル線図、図５は蒸気圧縮式サイクル１００の除湿暖房運転時の冷媒流れを示す模式図、図６は除湿暖房運転時における冷媒状態を示すモリエル線図である。   Next, the operation of the first embodiment based on the above configuration will be described with reference to FIGS. 2 is a Mollier diagram showing the refrigerant state during the cooling operation, FIG. 3 is a schematic diagram showing the refrigerant flow during the heating operation of the vapor compression cycle 100, and FIG. 4 is a Mollier line showing the refrigerant state during the heating operation. FIG. 5 is a schematic diagram showing the refrigerant flow during the dehumidifying heating operation of the vapor compression cycle 100, and FIG. 6 is a Mollier diagram showing the refrigerant state during the dehumidifying heating operation.

１．冷房運転（図１、図２）
図示しない制御装置は、四方弁１２０を第１パターンに切替え、絞り機構１８０の絞り開度を全開状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。圧縮機１１０で圧縮され吐出された高温高圧冷媒は、吐出配管１１３、四方弁１２０、室外用配管１３１を通り室外熱交換器１３０に流入する。室外熱交換器１３０では高温の冷媒の熱が室外空気に放出されて、冷却される（図２中の室外ＨＥ）。 1. Cooling operation (Figs. 1 and 2)
A control device (not shown) switches the four-way valve 120 to the first pattern, fully opens the throttle opening of the throttle mechanism 180, connects the electromagnetic clutch 111, and drives the compressor 110 by the vehicle running engine. . The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the outdoor heat exchanger 130 through the discharge pipe 113, the four-way valve 120, and the outdoor pipe 131. In the outdoor heat exchanger 130, the heat of the high-temperature refrigerant is released to the outdoor air and cooled (outdoor HE in FIG. 2).

室外熱交換器１３０を流出した冷媒は、内部熱交換器１９５の一方の流路を流通し、後述するアキュムレータ１９０から流出されて内部熱交換器１９５の他方の流路を流通する低温低圧冷媒によって更に冷却される（図２中の上側の波状部）。   The refrigerant that has flowed out of the outdoor heat exchanger 130 flows through one flow path of the internal heat exchanger 195, flows out of an accumulator 190 described later, and flows through the other flow path of the internal heat exchanger 195 by low-temperature and low-pressure refrigerant. Further cooling is performed (the upper wavy portion in FIG. 2).

内部熱交換器１９５の一方の流路から流出した冷媒は、分岐点Ｚにてエジェクタ１４０に向かう冷媒流れと、分岐配管１６１に向かう冷媒流れとに分流する。   The refrigerant flowing out from one flow path of the internal heat exchanger 195 is divided into a refrigerant flow toward the ejector 140 and a refrigerant flow toward the branch pipe 161 at the branch point Z.

エジェクタ１４０に流入した冷媒は、ノズル部１４１で減圧膨張され、低温低圧冷媒となる（図２中のエジェクタ）。従って、ノズル部１４１で冷媒の圧力エネルギーが速度エネルギーに変換され、このノズル部１４１の噴出口から冷媒は高速度となって噴出する。この際の冷媒圧力低下により、冷媒吸引口１４２から分岐配管１６１の第２室内熱交換器１７０通過後の冷媒（気相冷媒）を吸引する。ノズル部１４１から噴出した冷媒と冷媒吸引口１４２に吸引された冷媒は、ノズル部１４１下流側の昇圧部１４３で混合されると共に、速度（膨張）エネルギーが圧力エネルギーに変換されて、昇圧される。   The refrigerant that has flowed into the ejector 140 is decompressed and expanded by the nozzle portion 141 to become a low-temperature and low-pressure refrigerant (ejector in FIG. 2). Accordingly, the pressure energy of the refrigerant is converted into velocity energy at the nozzle portion 141, and the refrigerant is ejected from the nozzle outlet of the nozzle portion 141 at a high speed. Due to the refrigerant pressure drop at this time, the refrigerant (gas phase refrigerant) after passing through the second indoor heat exchanger 170 of the branch pipe 161 is drawn from the refrigerant suction port 142. The refrigerant ejected from the nozzle part 141 and the refrigerant sucked into the refrigerant suction port 142 are mixed in the pressure-increasing part 143 on the downstream side of the nozzle part 141, and the speed (expansion) energy is converted into pressure energy to be pressurized. .

そして、エジェクタ１４０（昇圧部１４３）から流出した冷媒は第１室内熱交換器１５０に流入する。第１室内熱交換器１５０では、冷媒は図１中の太線矢印方向の室内空気から吸熱して蒸発する（図２中の室内ＨＥ１）。室内空気は、冷媒蒸発時の蒸発潜熱により冷却される。   Then, the refrigerant that has flowed out of the ejector 140 (the pressure increasing unit 143) flows into the first indoor heat exchanger 150. In the first indoor heat exchanger 150, the refrigerant absorbs heat from the indoor air in the direction of the thick arrow in FIG. 1 and evaporates (indoor HE1 in FIG. 2). The indoor air is cooled by the latent heat of vaporization when the refrigerant evaporates.

一方、分岐配管１６１に流入した冷媒は、絞り機構１６０で減圧膨張されて低温低圧冷媒となり（図２中の絞り１６０）、この低温低圧冷媒が第２室内熱交換器１７０に流入する。第２室内熱交換器１７０では、上記第１室内熱交換器１５０を通過した室内空気から吸熱して蒸発する（図２中の室内ＨＥ２）。室内空気は、第２室内熱交換器１７０での冷媒蒸発時の蒸発潜熱により更に冷却される。蒸発後の冷媒は、全開状態に制御された絞り機構１８０を通過して、冷媒吸引口１４２からエジェクタ１４０内に吸引される。   On the other hand, the refrigerant flowing into the branch pipe 161 is decompressed and expanded by the throttle mechanism 160 to become a low-temperature and low-pressure refrigerant (throttle 160 in FIG. 2), and this low-temperature and low-pressure refrigerant flows into the second indoor heat exchanger 170. The second indoor heat exchanger 170 absorbs heat from the indoor air that has passed through the first indoor heat exchanger 150 and evaporates (room HE2 in FIG. 2). The indoor air is further cooled by the latent heat of evaporation when the refrigerant evaporates in the second indoor heat exchanger 170. The evaporated refrigerant passes through the throttle mechanism 180 controlled to be fully open, and is sucked into the ejector 140 from the refrigerant suction port 142.

そして、第１室内熱交換器１５０から流出された蒸発後の冷媒は、室内配管１５１、四方弁１２０、吸入配管１１２を経て、アキュムレータ１９０に吸入される。アキュムレータ１９０では、冷媒は気液分離され、液相冷媒は内部に溜められると共に、気相冷媒は内部熱交換器１９５の他方の流路を流通する。この時、内部熱交換器１９５の一方の流路を流通する高温高圧の冷媒によって加熱されて、所定の過熱度を持った気相冷媒となって（図２中の下側の波状部）、圧縮機１１１に吸入され、再び圧縮される。   The evaporated refrigerant that has flowed out of the first indoor heat exchanger 150 is sucked into the accumulator 190 through the indoor pipe 151, the four-way valve 120, and the suction pipe 112. In the accumulator 190, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant flows through the other flow path of the internal heat exchanger 195. At this time, it is heated by the high-temperature and high-pressure refrigerant flowing through one flow path of the internal heat exchanger 195 to become a gas-phase refrigerant having a predetermined superheat degree (lower wavy portion in FIG. 2). It is sucked into the compressor 111 and compressed again.

尚、図示しない制御装置は、第２室内熱交換器１７０を通過した室内空気の温度が、車両乗員の設定する設定空気温度となるように、絞り機構１６０の絞り開度を制御する。   A control device (not shown) controls the throttle opening of the throttle mechanism 160 so that the temperature of the indoor air that has passed through the second indoor heat exchanger 170 becomes the set air temperature set by the vehicle occupant.

２．暖房運転（図３、図４）
図示しない制御装置は、四方弁１２０を第２パターンに切替え、エジェクタ１４０のノズル部１４１を全閉状態にし、絞り機構１８０の絞り開度を全開状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。圧縮機１１０で圧縮され吐出された高温高圧冷媒は、吐出配管１１３、四方弁１２０、室内用配管１５１を通り第１室内熱交換器１５０に流入する。 2. Heating operation (Figs. 3 and 4)
A control device (not shown) switches the four-way valve 120 to the second pattern, fully closes the nozzle portion 141 of the ejector 140, fully opens the throttle opening of the throttle mechanism 180, and puts the electromagnetic clutch 111 into a connected state. The compressor 110 is driven by a vehicle travel engine. The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the first indoor heat exchanger 150 through the discharge pipe 113, the four-way valve 120, and the indoor pipe 151.

第１室内熱交換器１５０では、冷媒は図１中の太線矢印方向の室内空気に放熱して冷却される（図４中の室内ＨＥ１）。つまり、室内空気は冷媒からの放熱により加熱される。   In first indoor heat exchanger 150, the refrigerant dissipates heat to indoor air in the direction of the thick arrow in FIG. 1 and is cooled (indoor HE1 in FIG. 4). That is, the room air is heated by heat dissipation from the refrigerant.

第１室内熱交換器１５０で冷却された冷媒は、エジェクタ１４０の昇圧部１４３側から流入する。ここではエジェクタ１４０のノズル部１４１が全閉状態に制御されているため、昇圧部１４３に流入した冷媒はエジェクタ１４０内を通過し冷媒吸引口１４２から流出する。更に冷媒は全開状態に制御された絞り機構１８０を通過して第２室内熱交換器１７０に流入する。   The refrigerant cooled by the first indoor heat exchanger 150 flows from the booster 143 side of the ejector 140. Here, since the nozzle portion 141 of the ejector 140 is controlled to be fully closed, the refrigerant flowing into the pressure increasing portion 143 passes through the ejector 140 and flows out from the refrigerant suction port 142. Further, the refrigerant passes through the throttle mechanism 180 controlled to be fully opened and flows into the second indoor heat exchanger 170.

第２室内熱交換器１７０では、冷媒は上記第１室内熱交換器１５０を通過した室内空気に放熱して冷却される（図４中の室内ＨＥ２）。つまり、室内空気は第２室内熱交換器１７０での冷媒からの放熱により更に加熱される。   In the second indoor heat exchanger 170, the refrigerant dissipates heat to the indoor air that has passed through the first indoor heat exchanger 150 and is cooled (indoor HE2 in FIG. 4). That is, the indoor air is further heated by the heat radiation from the refrigerant in the second indoor heat exchanger 170.

そして、第２室内熱交換器１７０を流出した冷媒は、絞り機構１６０で減圧膨張されて低温低圧冷媒となり（図２中の絞り１６０）、この低温低圧冷媒は、分岐点Ｚ、内部熱交換器１９５の一方の流路を通過して、室外熱交換器１３０に流入する。尚、ここでは、内部熱交換器１９５の両流路を流通する冷媒は、共に低温低圧冷媒となるため、内部熱交換器１９５における上記冷房運転時のような熱交換は成されない。   The refrigerant that has flowed out of the second indoor heat exchanger 170 is decompressed and expanded by the throttle mechanism 160 to become a low-temperature and low-pressure refrigerant (throttle 160 in FIG. 2), and this low-temperature and low-pressure refrigerant is divided into the branch point Z, the internal heat exchanger. It passes through one flow path 195 and flows into the outdoor heat exchanger 130. Here, since the refrigerant flowing through both flow paths of the internal heat exchanger 195 is both a low-temperature and low-pressure refrigerant, heat exchange in the internal heat exchanger 195 during the cooling operation is not performed.

室外熱交換器１３０では、冷媒は室外空気から吸熱して蒸発する（図４中の室外ＨＥ）。そして、室外熱交換器１３０から流出された蒸発後の冷媒は、室外用配管１３１、四方弁１２０、吸入配管１１２を経て、アキュムレータ１９０に吸入される。アキュムレータ１９０では、上記冷房運転時と同様に、冷媒は気液分離され、液相冷媒は内部に溜められると共に、気相冷媒は内部熱交換器１９５の他方の流路を通過し、圧縮機１１１に吸入され、再び圧縮される。   In the outdoor heat exchanger 130, the refrigerant absorbs heat from the outdoor air and evaporates (outdoor HE in FIG. 4). The evaporated refrigerant that has flowed out of the outdoor heat exchanger 130 is sucked into the accumulator 190 through the outdoor pipe 131, the four-way valve 120, and the suction pipe 112. In the accumulator 190, as in the cooling operation, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant passes through the other flow path of the internal heat exchanger 195. Inhaled and compressed again.

尚、図示しない制御装置は、第２室内熱交換器１７０を通過した室内空気の温度が、車両乗員の設定する設定空気温度となるように、絞り機構１６０の絞り開度を制御する。   A control device (not shown) controls the throttle opening of the throttle mechanism 160 so that the temperature of the indoor air that has passed through the second indoor heat exchanger 170 becomes the set air temperature set by the vehicle occupant.

３．除湿暖房運転（図５、図６）
図示しない制御装置は、四方弁１２０を第１パターンに切替え、エジェクタ１４０のノズル部１４１を全閉状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。圧縮機１１０で圧縮され吐出された高温高圧冷媒は、吐出配管１１３、四方弁１２０、室外用配管１３１を通り室外熱交換器１３０に流入する。室外熱交換器１３０では高温の冷媒の熱が室外空気に放出されて、冷却される（図６中の室外ＨＥ）。 3. Dehumidification heating operation (Figs. 5 and 6)
A control device (not shown) switches the four-way valve 120 to the first pattern, fully closes the nozzle portion 141 of the ejector 140, and connects the electromagnetic clutch 111 to drive the compressor 110 by the vehicle travel engine. . The high-temperature and high-pressure refrigerant compressed and discharged by the compressor 110 flows into the outdoor heat exchanger 130 through the discharge pipe 113, the four-way valve 120, and the outdoor pipe 131. In the outdoor heat exchanger 130, the heat of the high-temperature refrigerant is released to the outdoor air and cooled (outdoor HE in FIG. 6).

室外熱交換器１３０を流出した冷媒は、内部熱交換器１９５の一方の流路を流通し、後述するアキュムレータ１９０から流出されて内部熱交換器１９５の他方の流路を流通する低温低圧冷媒によって更に冷却される（図６中の上側の波状部）。   The refrigerant that has flowed out of the outdoor heat exchanger 130 flows through one flow path of the internal heat exchanger 195, flows out of an accumulator 190 described later, and flows through the other flow path of the internal heat exchanger 195 by low-temperature and low-pressure refrigerant. Further cooling is performed (the upper wavy portion in FIG. 6).

内部熱交換器１９５の一方の流路から流出した冷媒は、エジェクタ１４０のノズル部１４１が全閉状態に制御されていることから、分岐点Ｚを通過して分岐配管１６１に流入する。   The refrigerant flowing out from one flow path of the internal heat exchanger 195 passes through the branch point Z and flows into the branch pipe 161 because the nozzle portion 141 of the ejector 140 is controlled to be fully closed.

分岐配管１６１に流入した冷媒は、絞り機構１６０で所定量減圧されて（図６中の絞り１６０）、この冷媒が第２室内熱交換器１７０に流入する。第２室内熱交換器１７０では、冷媒の放熱によって、後述する第１室内熱交換器１５０を通過して冷却（除湿）された室内空気を加熱する（図６中の室内ＨＥ２）。室内熱交換器１７０から流出した冷媒は、絞り機構１８０によって減圧膨張されて、冷媒吸引口１４２からエジェクタ１４０内に流入する。   The refrigerant flowing into the branch pipe 161 is decompressed by a predetermined amount by the throttle mechanism 160 (throttle 160 in FIG. 6), and this refrigerant flows into the second indoor heat exchanger 170. In the second indoor heat exchanger 170, the indoor air cooled (dehumidified) through the first indoor heat exchanger 150 described later is heated by the heat radiation of the refrigerant (indoor HE2 in FIG. 6). The refrigerant that has flowed out of the indoor heat exchanger 170 is decompressed and expanded by the throttle mechanism 180 and flows into the ejector 140 from the refrigerant suction port 142.

エジェクタ１４０に流入した冷媒は、昇圧部１４３を通過して、第１室内熱交換器１５０に流入する。第１室内熱交換器１５０では、冷媒は図１中の太線矢印方向の室内空気から吸熱して蒸発する（図６中の室内ＨＥ１）。室内空気は、冷媒蒸発時の蒸発潜熱により冷却（除湿）される。ここでは、室内空気は第１室内熱交換器１５０によって冷却（除湿）されて、更に第２室内熱交換器１７０によって加熱される。   The refrigerant that has flowed into the ejector 140 passes through the pressure increasing unit 143 and flows into the first indoor heat exchanger 150. In the first indoor heat exchanger 150, the refrigerant absorbs heat from the indoor air in the direction of the thick arrow in FIG. 1 and evaporates (indoor HE1 in FIG. 6). The indoor air is cooled (dehumidified) by the latent heat of vaporization when the refrigerant evaporates. Here, the indoor air is cooled (dehumidified) by the first indoor heat exchanger 150 and further heated by the second indoor heat exchanger 170.

そして、第１室内熱交換器１５０から流出された蒸発後の冷媒は、室内配管１５１、四方弁１２０、吸入配管１１２を経て、アキュムレータ１９０に吸入される。アキュムレータ１９０では、上記冷房運転時と同様に、冷媒は気液分離され、液相冷媒は内部に溜められると共に、気相冷媒は内部熱交換器１９５の他方の流路を流通する。この時、内部熱交換器１９５の一方の流路を流通する高温高圧の冷媒によって加熱されて、所定の過熱度を持った気相冷媒となって（図６中の下側の波状部）、圧縮機１１１に吸入され、再び圧縮される。   The evaporated refrigerant that has flowed out of the first indoor heat exchanger 150 is sucked into the accumulator 190 through the indoor pipe 151, the four-way valve 120, and the suction pipe 112. In the accumulator 190, as in the cooling operation, the refrigerant is separated into gas and liquid, the liquid phase refrigerant is stored inside, and the gas phase refrigerant flows through the other flow path of the internal heat exchanger 195. At this time, it is heated by the high-temperature and high-pressure refrigerant flowing through one flow path of the internal heat exchanger 195 to become a gas-phase refrigerant having a predetermined superheat degree (lower wavy portion in FIG. 6). It is sucked into the compressor 111 and compressed again.

尚、図示しない制御装置は、第２室内熱交換器１７０を通過した室内空気の湿度、温度が、車両乗員の設定する設定空気湿度、温度となるように、絞り機構１６０、１８０の絞り開度を制御する。   The control device (not shown) restricts the opening degree of the throttle mechanisms 160 and 180 so that the humidity and temperature of the indoor air that has passed through the second indoor heat exchanger 170 become the set air humidity and temperature set by the vehicle occupant. To control.

以上のように、本実施形態の蒸気圧縮式サイクル１００では、室外熱交換器１３０、可変式のエジェクタ１４０、第１、第２室内熱交換器１５０、１７０、流路切替え手段１２０、および可変絞りとしての絞り機構１８０を設けるようにしているので、流路の切替えおよび所定部位での冷媒減圧が可能となり、室外熱交換器１３０、第１室内熱交換器１５０、第２室内熱交換器１７０の３つの熱交換器を常に活用した冷房運転、暖房運転、除湿暖房運転が可能となる。   As described above, in the vapor compression cycle 100 of the present embodiment, the outdoor heat exchanger 130, the variable ejector 140, the first and second indoor heat exchangers 150 and 170, the flow path switching unit 120, and the variable throttle Therefore, the flow path can be switched and the refrigerant can be depressurized at a predetermined location, and the outdoor heat exchanger 130, the first indoor heat exchanger 150, and the second indoor heat exchanger 170 can be switched. The cooling operation, the heating operation, and the dehumidifying heating operation using the three heat exchangers at all times are possible.

ここでは、四方弁１２０を用いることで、容易に流路切替え手段（１２０）を構成することができる。   Here, the flow path switching means (120) can be easily configured by using the four-way valve 120.

また、蒸気圧縮式サイクル１００内に、内部熱交換器１９５を設けるようにしているので、冷房運転時、あるいは除湿暖房運転時において、室外熱交換器１３０での放熱後の冷媒を、第１室内熱交換器１５０での吸熱後の冷媒で冷却することができ、放熱後の冷媒のエンタルピを小さくすることができ、室内熱交換器（１５０および１７０、あるいは１５０）における入口側と出口側とのエンタルピ差を大きくして、吸熱能力を増大させることができる。また、第１室内熱交換器１５０での吸熱後の冷媒は逆に加熱されることになり、所定の過熱度を持つ気相冷媒とすることができるので、圧縮機１１０における液圧縮を確実に防止することができる。   Further, since the internal heat exchanger 195 is provided in the vapor compression cycle 100, the refrigerant after the heat release in the outdoor heat exchanger 130 is supplied to the first indoor chamber during the cooling operation or the dehumidifying heating operation. It is possible to cool with the refrigerant after absorbing heat in the heat exchanger 150, to reduce the enthalpy of the refrigerant after heat dissipation, and to reduce the enthalpy between the inlet side and the outlet side in the indoor heat exchanger (150 and 170 or 150). The enthalpy difference can be increased to increase the endothermic capacity. In addition, the refrigerant after the heat absorption in the first indoor heat exchanger 150 is heated in reverse, so that it can be a gas phase refrigerant having a predetermined superheat degree, so that the liquid compression in the compressor 110 is ensured. Can be prevented.

（第２実施形態）
本発明の第２実施形態を図７に示す。第２実施形態は、上記第１実施形態に対して、流路切替え手段を変更したものである。第２実施形態における流路切替え手段は、四方弁１２０に代えて三方弁１２０Ａを用いて、電磁弁１２０Ｂ、１２０Ｃ、連通配管１２０Ｄを追加して形成されるようにしている。 (Second Embodiment)
A second embodiment of the present invention is shown in FIG. In the second embodiment, the flow path switching means is changed with respect to the first embodiment. The flow path switching means in the second embodiment is formed by using a three-way valve 120A instead of the four-way valve 120 and adding electromagnetic valves 120B and 120C and a communication pipe 120D.

三方弁１２０Ａは、３つの接続部を有し、各接続部には吐出配管１１３、室外用配管１３１、室内用配管１５１が接続されている。そして、三方弁１２０Ａの内部に設けられた例えば電気アクチュエータ機構によって、吐出配管１１３と室外用配管１３１とが連通状態とされる第１パターン、および吐出配管１１３と室内用配管１５１とが連通状態とされる第２パターンの切替えを可能としている。三方弁１２０Ａの上記第１、第２パターンの切替えは、図示しない制御装置によって制御されるようにしている。   The three-way valve 120A has three connecting portions, and a discharge pipe 113, an outdoor pipe 131, and an indoor pipe 151 are connected to each connecting section. The first pattern in which the discharge pipe 113 and the outdoor pipe 131 are in communication with each other, for example, by an electric actuator mechanism provided inside the three-way valve 120A, and the discharge pipe 113 and the indoor pipe 151 in communication with each other. The second pattern can be switched. The switching of the first and second patterns of the three-way valve 120A is controlled by a control device (not shown).

吸入配管１１２の圧縮機１１０側端部は、室外用配管１３１に接続されており、この接続部近傍に吸入配管１１２を開閉する電磁弁１２０Ｂを配設している。電磁弁１２０Ｂの開閉は、図示しない制御装置によって制御されるようにしている。   An end portion of the suction pipe 112 on the compressor 110 side is connected to the outdoor pipe 131, and an electromagnetic valve 120B for opening and closing the suction pipe 112 is disposed in the vicinity of the connection portion. The opening and closing of the electromagnetic valve 120B is controlled by a control device (not shown).

また、室内用配管１５１の第１室内熱交換器１５０近傍と、吸入配管１１２の電磁弁１２０Ｂおよびアキュムレータ１９０間のアキュムレータ１９０近傍とを連通させる連通配管１２０Ｄを設け、この連通配管１２０Ｄには、連通配管１２０Ｄを開閉する電磁弁１２０Ｃを配設している。電磁弁１２０Ｃの開閉は、上記電磁弁１２０Ｂと同様に、図示しない制御装置によって制御されるようにしている。   In addition, a communication pipe 120D is provided for connecting the vicinity of the first indoor heat exchanger 150 of the indoor pipe 151 and the vicinity of the accumulator 190 between the electromagnetic valve 120B and the accumulator 190 of the suction pipe 112, and the communication pipe 120D is connected to the communication pipe 120D. An electromagnetic valve 120C that opens and closes the pipe 120D is provided. The opening and closing of the solenoid valve 120C is controlled by a control device (not shown), similar to the solenoid valve 120B.

上記構成において、冷房運転時は、図示しない制御装置によって、三方弁１２０Ａを第１パターンに切替え、電磁弁１２０Ｂを閉じ、電磁弁１２０Ｃを開く。そして、絞り機構１８０の絞り開度を全開状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。すると、図７中の実線矢印のように冷媒は循環し、第１実施形態と同様に、第１、第２室内熱交換器１５０、１７０で吸熱して、室外熱交換器１３０で放熱するサイクルとなり、第１、第２室内熱交換器１５０、１７０による室内空気の冷却が可能となる。   In the above configuration, during the cooling operation, the control device (not shown) switches the three-way valve 120A to the first pattern, closes the solenoid valve 120B, and opens the solenoid valve 120C. Then, the throttle opening of the throttle mechanism 180 is fully opened, and the electromagnetic clutch 111 is connected, and the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by solid line arrows in FIG. 7, and a cycle in which heat is absorbed by the first and second indoor heat exchangers 150 and 170 and is radiated by the outdoor heat exchanger 130 as in the first embodiment. Thus, the indoor air can be cooled by the first and second indoor heat exchangers 150 and 170.

また、暖房運転時は、図示しない制御装置によって、三方弁１２０Ａを第２パターンに切替え、電磁弁１２０Ｂを開き、電磁弁１２０Ｃを閉じる。そして、エジェクタ１４０のノズル部１４１を全閉状態にし、絞り機構１８０の絞り開度を全開状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。すると、図７中の破線矢印のように冷媒は循環し、第１実施形態と同様に、室外熱交換器１３０で吸熱して、第１、第２室内熱交換器１５０、１７０で放熱するサイクルとなり、第１、第２室内熱交換器１５０、１７０による室内空気の加熱が可能となる。   During heating operation, the control device (not shown) switches the three-way valve 120A to the second pattern, opens the electromagnetic valve 120B, and closes the electromagnetic valve 120C. Then, the nozzle part 141 of the ejector 140 is fully closed, the throttle opening of the throttle mechanism 180 is fully opened, and the electromagnetic clutch 111 is connected, so that the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by broken line arrows in FIG. 7, and similarly to the first embodiment, the heat is absorbed by the outdoor heat exchanger 130 and is radiated by the first and second indoor heat exchangers 150 and 170. Thus, the indoor air can be heated by the first and second indoor heat exchangers 150 and 170.

更に、除湿暖房運転時は、図示しない制御装置によって、三方弁１２０Ａを第１パターンに切替え、電磁弁１２０Ｂを閉じ、電磁弁１２０Ｃを開く。そして、エジェクタ１４０のノズル部１４１を全閉状態にすると共に、電磁クラッチ１１１を接続状態にして、圧縮機１１０を車両走行用エンジンにより駆動する。すると、図７中の一点鎖線矢印のように冷媒は循環し、第１実施形態と同様に、第１室内熱交換器１５０で吸熱して、室外熱交換器１３０、第２室内熱交換器１７０で放熱するサイクルとなり、第１室内熱交換器１５０による室内空気の冷却、および第２室内熱交換器１７０による室内空気の加熱が可能となる。   Further, during the dehumidifying heating operation, the three-way valve 120A is switched to the first pattern by a control device (not shown), the electromagnetic valve 120B is closed, and the electromagnetic valve 120C is opened. Then, the nozzle portion 141 of the ejector 140 is fully closed, and the electromagnetic clutch 111 is connected, and the compressor 110 is driven by the vehicle running engine. Then, the refrigerant circulates as indicated by a one-dot chain line arrow in FIG. 7, and similarly to the first embodiment, the refrigerant absorbs heat by the first indoor heat exchanger 150, and the outdoor heat exchanger 130 and the second indoor heat exchanger 170. Thus, the indoor air can be cooled by the first indoor heat exchanger 150 and the indoor air can be heated by the second indoor heat exchanger 170.

以上のように、三方弁１２０Ａ、電磁弁１２０Ｂ、１２０Ｃ、連通配管１２０Ｄ等を用いた流路切替え手段においても、室外熱交換器１３０、第１室内熱交換器１５０、第２室内熱交換器１７０の３つの熱交換器を常に活用した冷房運転、暖房運転、除湿暖房運転が可能となる。   As described above, also in the flow path switching means using the three-way valve 120A, the electromagnetic valves 120B and 120C, the communication pipe 120D, etc., the outdoor heat exchanger 130, the first indoor heat exchanger 150, and the second indoor heat exchanger 170 are used. The cooling operation, the heating operation, and the dehumidifying heating operation that always use these three heat exchangers are possible.

（第３実施形態）
本発明の第３実施形態を図８に示す。第３実施形態は、上記第１実施形態に対して、内部熱交換器１９５の配設位置を変更したものである。 (Third embodiment)
A third embodiment of the present invention is shown in FIG. 3rd Embodiment changes the arrangement | positioning position of the internal heat exchanger 195 with respect to the said 1st Embodiment.

ここでは、冷房運転時、あるいは除湿暖房運転時に内部熱交換器１９５内で高温高圧冷媒が流通する一方の流路を、分岐配管１６１に配設しており、これにより上記第１実施形態と同様の効果を得ることができる。   Here, one flow path through which the high-temperature and high-pressure refrigerant circulates in the internal heat exchanger 195 during the cooling operation or the dehumidifying heating operation is disposed in the branch pipe 161, thereby the same as in the first embodiment. The effect of can be obtained.

（その他の実施形態）
上記各実施形態では、蒸気圧縮式サイクル１００を車両用冷凍サイクル装置に適用したものとして説明したが、家庭用空調装置の冷凍サイクルに適用しても良い。 (Other embodiments)
In each of the above embodiments, the vapor compression cycle 100 has been described as being applied to a vehicle refrigeration cycle apparatus. However, the vapor compression cycle 100 may be applied to a refrigeration cycle of a home air conditioner.

第１実施形態における蒸気圧縮式サイクルを示す模式図である（冷房運転時）。It is a schematic diagram which shows the vapor | steam compression-type cycle in 1st Embodiment (at the time of air_conditionaing | cooling operation). 冷房運転時における冷媒状態を示すモリエル線図である。It is a Mollier diagram which shows the refrigerant | coolant state at the time of air_conditionaing | cooling operation. 第１実施形態における蒸気圧縮式サイクルを示す模式図である（暖房運転時）。It is a schematic diagram which shows the vapor compression cycle in 1st Embodiment (at the time of heating operation). 暖房運転時における冷媒状態を示すモリエル線図である。It is a Mollier diagram which shows the refrigerant | coolant state at the time of heating operation. 第１実施形態における蒸気圧縮式サイクルを示す模式図である（除湿暖房運転時）。It is a schematic diagram which shows the vapor | steam compression-type cycle in 1st Embodiment (at the time of dehumidification heating operation). 除湿暖房運転時における冷媒状態を示すモリエル線図である。It is a Mollier diagram which shows the refrigerant | coolant state at the time of a dehumidification heating operation. 第２実施形態における蒸気圧縮式サイクルを示す模式図である。It is a schematic diagram which shows the vapor compression type cycle in 2nd Embodiment. 第３実施形態における蒸気圧縮式サイクルを示す模式図である。It is a schematic diagram which shows the vapor | steam compression-type cycle in 3rd Embodiment.

符号の説明Explanation of symbols

１００ 蒸気圧縮式サイクル
１１０ 圧縮機
１２０ 四方弁（流路切替え手段）
１３０ 室外熱交換器
１４０ エジェクタ
１４１ ノズル部
１４２ 冷媒吸引口
１４３ 昇圧部
１５０ 第１室内熱交換器
１６０ 絞り機構（減圧器）
１６１ 分岐配管（分岐流路）
１７０ 第２室内熱交換器
１８０ 絞り機構（可変絞り）
１９５ 内部熱交換器 100 Vapor compression cycle 110 Compressor 120 Four-way valve (flow path switching means)
130 Outdoor Heat Exchanger 140 Ejector 141 Nozzle Part 142 Refrigerant Suction Port 143 Booster Part 150 First Indoor Heat Exchanger 160 Throttle Mechanism (Decompressor)
161 Branch piping (branch flow path)
170 Second indoor heat exchanger 180 Throttle mechanism (variable throttle)
195 Internal heat exchanger

Claims (3)

冷媒を吸入し圧縮する圧縮機（１１０）と、
前記冷媒および室外空気の間で熱交換する室外熱交換器（１３０）と、
前記室外熱交換器（１３０）から接続されて、開度調整可能とするノズル（１４１）によって高圧の前記冷媒を減圧膨張させると共に、冷媒吸引口（１４２）から前記冷媒を吸引した後に昇圧部（１４３）で昇圧させるエジェクタ（１４０）と、
前記エジェクタ（１４０）から接続されて、前記冷媒と室内空気との間で熱交換する第１室内熱交換器（１５０）と、
前記室外熱交換器（１３０）および前記エジェクタ（１４０）の間から分岐して、前記冷媒吸引口（１４２）に接続される分岐流路（１６１）に配設されて、前記冷媒を減圧膨張させる減圧器（１６０）と、
前記分岐流路（１６１）の前記減圧器（１６０）および前記冷媒吸引口（１４２）の間に配設されて、前記冷媒および前記室内空気の間で熱交換する第２室内熱交換器（１７０）と、
前記圧縮機（１１０）が、前記第１室内熱交換（１５０）から前記冷媒を吸入して前記室外熱交換器（１３０）に吐出するように、あるいは前記室外熱交換器（１３０）から前記冷媒を吸入して前記第１室内熱交換器（１５０）に吐出するように前記冷媒の流路を切替える流路切替え手段（１２０）と、
前記分岐流路（１６１）の前記第２室内熱交換器（１７０）および前記冷媒吸引口（１４２）の間に配設されて、前記分岐流路（１６１）の絞り度を可変する可変絞り（１８０）とを設けたことを特徴とする蒸気圧縮式サイクル。 A compressor (110) for sucking and compressing refrigerant;
An outdoor heat exchanger (130) for exchanging heat between the refrigerant and outdoor air;
The high-pressure refrigerant is decompressed and expanded by a nozzle (141) connected from the outdoor heat exchanger (130) and adjustable in opening, and after the refrigerant is sucked from the refrigerant suction port (142), 143) an ejector (140) to be boosted;
A first indoor heat exchanger (150) connected from the ejector (140) to exchange heat between the refrigerant and room air;
The refrigerant branches from between the outdoor heat exchanger (130) and the ejector (140), and is disposed in a branch flow path (161) connected to the refrigerant suction port (142) to decompress and expand the refrigerant. A decompressor (160);
A second indoor heat exchanger (170) disposed between the decompressor (160) and the refrigerant suction port (142) of the branch channel (161) and exchanging heat between the refrigerant and the indoor air. )When,
The compressor (110) sucks the refrigerant from the first indoor heat exchange (150) and discharges it to the outdoor heat exchanger (130), or from the outdoor heat exchanger (130). A flow path switching means (120) for switching the flow path of the refrigerant so as to inhale and discharge to the first indoor heat exchanger (150),
A variable throttle (not shown) disposed between the second indoor heat exchanger (170) and the refrigerant suction port (142) of the branch channel (161) to vary the throttle degree of the branch channel (161). 180). 前記流路切替え手段（１２０）は、前記圧縮機（１１０）の吸入側、前記圧縮機（１１０）の吐出側、前記室外熱交換器（１３０）側、前記第１室内熱交換器（１５０）側の４点が接続されて、所定の２点同士を連通すると共に、その連通の組合せを切替え可能とする四方弁（１２０）としたことを特徴とする請求項１に記載の蒸気圧縮式サイクル。   The flow path switching means (120) includes a suction side of the compressor (110), a discharge side of the compressor (110), the outdoor heat exchanger (130) side, and the first indoor heat exchanger (150). The vapor compression cycle according to claim 1, wherein the four points on the side are connected to communicate with each other between two predetermined points, and the four-way valve (120) is configured to switch the combination of the communication. . 前記室外熱交換器（１３０）から前記減圧器（１６０）へ流れる前記冷媒と、
前記第１室内熱交換器（１５０）から前記圧縮機（１１０）へ流れる前記冷媒との間で熱交換する内部熱交換器（１９５）が設けられたことを特徴とする請求項１または請求項２に記載の蒸気圧縮式サイクル。 The refrigerant flowing from the outdoor heat exchanger (130) to the decompressor (160);
The internal heat exchanger (195) for exchanging heat with the refrigerant flowing from the first indoor heat exchanger (150) to the compressor (110) is provided. 2. A vapor compression cycle according to 2.
JP2006018052A 2006-01-26 2006-01-26 Vapor compression cycle Expired - Fee Related JP4539571B2 (en)

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JP2006018052A JP4539571B2 (en) 2006-01-26 2006-01-26 Vapor compression cycle
CNB200610163030XA CN100535546C (en) 2006-01-26 2006-11-27 Vapour compression cooling circulation device
IT000029A ITRM20070029A1 (en) 2006-01-26 2007-01-22 STEAM REFRIGERANT CYCLE COMPRESSION DEVICE
DE102007003870A DE102007003870A1 (en) 2006-01-26 2007-01-25 Vapour compression cooling circuit comprises a compressor for sucking and compressing a coolant, an outer heat exchanger and two inner heat exchangers

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