JP2008224172A - Refrigerator - Google Patents
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Abstract
Description
本発明は冷凍システムの高効率化と省エネルギー化並びに可燃性冷媒の漏洩防止を図った冷蔵庫に関するものである。 The present invention relates to a refrigerator that achieves high efficiency and energy saving of a refrigeration system and prevents leakage of a flammable refrigerant.
近年、冷蔵庫は地球環境保護の観点から更なる省エネルギー化が求められている。 In recent years, refrigerators are required to further save energy from the viewpoint of protecting the global environment.
従来この種の冷蔵庫は、凝縮器出口部に切替弁を設け、この切替弁と圧縮機の吸込配管とを接続するバイパス回路を設け、適宜この切替弁により冷媒の流れを制御するという方法がとられていた(例えば、特許文献1参照)。 Conventionally, this type of refrigerator is provided with a switching valve at the outlet of the condenser, a bypass circuit that connects the switching valve and the suction pipe of the compressor, and the method of appropriately controlling the flow of the refrigerant with the switching valve. (For example, refer to Patent Document 1).
図5は、特許文献1に記載された従来の冷蔵庫の冷凍サイクルの構成図である。 FIG. 5 is a configuration diagram of a refrigeration cycle of a conventional refrigerator described in Patent Document 1.
図5に示すように、サイクル構成機器であるシェル内低圧型の圧縮機31と凝縮器32と冷凍室用減圧装置33aと冷凍室用蒸発器34aおよび逆止弁41を直列接続した第一回路35に対して、冷蔵室用減圧装置33bと冷蔵室用蒸発器34bを直列接続した第二回路36の入口側を凝縮器出口部に切替弁37を介して接続し、出口側を冷凍室用減圧装置33aの出口側に接続する。さらに切替弁37から圧縮機31の吸込配管38を連通するバイパス回路39を設けた。 As shown in FIG. 5, a first circuit in which a low-pressure compressor 31 in a shell, a condenser 32, a decompression device 33a for freezer compartment, an evaporator 34a for freezer compartment, and a check valve 41, which are cycle constituent devices, are connected in series. 35, the inlet side of the second circuit 36 in which the refrigerator for decompression chamber 33b and the evaporator 34b for refrigerator compartment are connected in series is connected to the outlet of the condenser via a switching valve 37, and the outlet side is for the freezer compartment. Connect to the outlet side of the decompression device 33a. Further, a bypass circuit 39 that communicates the switching valve 37 with the suction pipe 38 of the compressor 31 is provided.
さらに圧縮機31起動制御においては、圧縮機31停止後、第一回路35、第二回路36及びバイパス回路39すべてを閉鎖し、起動直前の所定時間だけバイパス回路39を開放し、圧縮機31の高低圧力差を低減した状態で、バイパス回路39を閉鎖、第一回路35を開放し、圧縮機31を起動させた。 Further, in the compressor 31 activation control, after the compressor 31 is stopped, the first circuit 35, the second circuit 36 and the bypass circuit 39 are all closed, and the bypass circuit 39 is opened for a predetermined time immediately before the activation. In a state in which the high-low pressure difference was reduced, the bypass circuit 39 was closed, the first circuit 35 was opened, and the compressor 31 was started.
これにより、起動時の圧縮機31内部における均圧化が図れ、圧縮機31の起動停止による庫内温度上昇が抑制される。 Thereby, the pressure equalization inside the compressor 31 at the time of starting can be achieved, and the rise in the internal temperature due to the stop of the starting of the compressor 31 is suppressed.
さらに、蒸発器34の除霜制御においては、通常、蒸発器34内部に貯留する冷媒のサーモサイフォン現象を利用して除霜効率を高めるべく、圧縮機31停止時に切替弁37を第一回路35もしくは第二回路36を開放して冷媒を蒸発器34へ環流させる。 Further, in the defrosting control of the evaporator 34, the switching valve 37 is usually connected to the first circuit 35 when the compressor 31 is stopped in order to increase the defrosting efficiency by utilizing the thermosiphon phenomenon of the refrigerant stored in the evaporator 34. Alternatively, the second circuit 36 is opened to circulate the refrigerant to the evaporator 34.
これにより、除霜時における蒸発器34における熱伝導が促進され、除霜時間が短縮され、熱負荷も減少し、冷却効率が改善される。
しかしながら、上記従来の構成では、バイパス回路39出口は、蒸発器34と圧縮機31の途中である吸入配管38であることから、バイパス回路39が開放されたときに高温液冷媒が圧縮機31へ流入すると同時に蒸発器34へも流入することから、蒸発器34での熱負荷が増大し、停止時の蒸発器34並びに庫内温度が上昇し、冷却効率が低下し消費電力量が増加する可能性があるといった課題があった。 However, in the above conventional configuration, the outlet of the bypass circuit 39 is the suction pipe 38 in the middle of the evaporator 34 and the compressor 31, so that the high-temperature liquid refrigerant is sent to the compressor 31 when the bypass circuit 39 is opened. Since it flows into the evaporator 34 at the same time as it flows in, the heat load in the evaporator 34 increases, the evaporator 34 and the internal temperature at the time of stop rise, the cooling efficiency decreases, and the power consumption can increase. There was a problem that there was sex.
また、上記従来の構成では、蒸発器34の除霜制御において、圧縮機31停止時に切替弁37を第一回路35もしくは第二回路36を開放して冷媒を蒸発器34へ環流させるが、蒸発器34は高温高圧液冷媒が流入するため、圧力が上昇し、蒸発器34の配管接続箇所から漏洩し、発火・火災の危険性が増大する可能性があるという課題があった。 In the conventional configuration, in the defrosting control of the evaporator 34, when the compressor 31 is stopped, the switching valve 37 opens the first circuit 35 or the second circuit 36 to circulate the refrigerant to the evaporator 34. Since the high-temperature and high-pressure liquid refrigerant flows into the vessel 34, there is a problem that the pressure rises and leaks from the pipe connection portion of the evaporator 34, which may increase the risk of ignition and fire.
また、吸入配管38内に冷凍機油(図示せず)が滞留することにより、圧縮機31起動時や液バック時等の過渡条件において、冷凍機油(図示せず)が圧縮機31内部に大量流入した場合、圧縮機31内部のバルブ(図示せず)が液圧縮により破壊する可能性があるといった課題があった。 In addition, since refrigeration oil (not shown) stays in the suction pipe 38, a large amount of refrigeration oil (not shown) flows into the compressor 31 under transient conditions such as when the compressor 31 is started or when the liquid is backed up. In such a case, there is a problem that a valve (not shown) inside the compressor 31 may be broken by liquid compression.
また、上記従来の構成では、圧縮機31起動制御において、起動直前の所定時間だけバイパス回路39を開放し、圧縮機31の高低圧力差を低減させたが、この所定時間が長すぎると、蒸発器34における熱負荷が増大し、冷蔵庫の増電につながる、また短すぎると圧力が十分均圧されずに、圧縮機31が始動するも、モータ(図示せず)のトルク不足により停止してしまう、あるいは、レシプロ圧縮機の場合、ピストン上死点端面に圧力荷重が発生し、ピストンが下死点まで移動し、コンロッド小端部とピストンを連結するピストンピンの摺動部に過度の荷重が発生する。その結果、摺動部の油膜が部分的に薄くなった状態で起動することから、摺動摩耗を引き起こし圧縮機31停止の可能性があるという課題があった。 Further, in the above-described conventional configuration, in the start-up control of the compressor 31, the bypass circuit 39 is opened only for a predetermined time immediately before the start-up to reduce the high-low pressure difference of the compressor 31. The heat load in the compressor 34 increases, leading to power increase in the refrigerator. If the pressure is too short, the pressure is not sufficiently equalized and the compressor 31 starts, but stops due to insufficient torque of the motor (not shown). In the case of a reciprocating compressor, a pressure load is generated at the top dead center of the piston, the piston moves to the bottom dead center, and an excessive load is applied to the sliding part of the piston pin that connects the small end of the connecting rod and the piston. Occurs. As a result, since it started in the state where the oil film of the sliding part became partially thin, there was a problem that there was a possibility of causing the sliding wear and stopping the compressor 31.
本発明は、上記従来の課題を解決するもので、凝縮器32からの高温冷媒を蒸発器34への流入を抑制することにより、蒸発器32の熱負荷を低減させ、消費電力量の低い冷蔵庫を提供することを目的とする。 The present invention solves the above-described conventional problems, and suppresses the flow of high-temperature refrigerant from the condenser 32 into the evaporator 34, thereby reducing the heat load on the evaporator 32 and reducing the power consumption of the refrigerator. The purpose is to provide.
本発明は、上記従来の課題を解決するもので、凝縮器32からの高温冷媒を蒸発器34への流入を抑制することにより、蒸発器34内部圧力上昇を低減させ、溶接箇所等のピンホールやクラックからの庫内冷媒漏洩を防止し、より安全性の高い冷蔵庫を提供することを目的とする。 The present invention solves the above-described conventional problems, and by suppressing the flow of high-temperature refrigerant from the condenser 32 into the evaporator 34, the internal pressure rise of the evaporator 34 is reduced, and pinholes such as welds are formed. The purpose is to provide a safer refrigerator that prevents refrigerant leakage from the cracks and cracks.
本発明は、上記従来の課題を解決するもので、吸入配管38内の冷凍機油(図示せず)の滞留を抑制し、冷凍機油(図示せず)が圧縮機31へ流入するときの圧縮機31破壊を防止し、信頼性の高い冷蔵庫を提供することを目的とする。 The present invention solves the above-described conventional problem, and suppresses the stay of refrigerating machine oil (not shown) in the suction pipe 38, and the compressor when the refrigerating machine oil (not shown) flows into the compressor 31. It aims at preventing destruction of 31 and providing a highly reliable refrigerator.
本発明は、上記従来の課題を解決するもので、凝縮器32からバイパス回路を通じ直接圧縮機へ高温冷媒を流入させることにより、圧縮機内部圧力を上昇、均圧バランスさせて、摺動部摩耗による圧縮機停止を回避した信頼性の高い冷蔵庫を提供することを目的とする。 The present invention solves the above-mentioned conventional problems. By flowing high-temperature refrigerant directly from the condenser 32 to the compressor through a bypass circuit, the internal pressure of the compressor is increased and the pressure is balanced, and the sliding portion wears. It aims at providing the reliable refrigerator which avoided the compressor stop by.
上記従来の課題を解決するために、圧縮機と、凝縮器と、減圧装置と、蒸発器を直列に接続した冷媒回路を備えた冷蔵庫において、凝縮器と減圧装置の間に切替弁を設け、切替弁から圧縮機までを連通するバイパス回路を設けたことを特徴とする。 In order to solve the above-described conventional problems, in a refrigerator including a compressor, a condenser, a decompression device, and a refrigerant circuit in which an evaporator is connected in series, a switching valve is provided between the condenser and the decompression device, A bypass circuit that communicates from the switching valve to the compressor is provided.
これによって、凝縮器における高温高圧液冷媒は、バイパス回路を通じて圧縮機内部へ直接開放流入されるため、圧縮機内部圧力を短時間で上昇、均圧バランスさせることにより、圧縮機摺動部の油膜厚さを確保し、摩耗による圧縮機停止を回避することができる。 As a result, the high-temperature and high-pressure liquid refrigerant in the condenser is directly introduced into the compressor through the bypass circuit, so that the oil pressure of the compressor sliding portion is increased by increasing the pressure inside the compressor in a short time and balancing the pressure. Thickness can be secured and the compressor stop due to wear can be avoided.
また、圧縮機から蒸発器への環流は大幅に低減され、蒸発器での熱負荷は軽減されるため、消費電力量を大幅に低減することができる。同時に、蒸発器内部の圧力上昇は抑制されるため、溶接箇所等のピンホールやクラックからの庫内冷媒漏洩を防止し、冷蔵庫の安全性を確保できる。 Moreover, since the recirculation | reflux from a compressor to an evaporator is reduced significantly and the thermal load in an evaporator is eased, power consumption can be reduced significantly. At the same time, since the rise in pressure inside the evaporator is suppressed, leakage of refrigerant in the cabinet from pinholes and cracks such as welded portions can be prevented, and the safety of the refrigerator can be secured.
また、吸入配管内に貯留する冷凍機油量を抑制し、過渡運転条件等による冷凍機油が圧縮機31へ流入するときに発生する圧縮機破壊の危険性を低減し冷蔵庫の長期信頼性を確保できる。 In addition, the amount of refrigerating machine oil stored in the suction pipe is suppressed, the risk of compressor breakage that occurs when refrigerating machine oil flows into the compressor 31 due to transient operating conditions and the like can be reduced, and the long-term reliability of the refrigerator can be secured. .
本発明の冷蔵庫は、蒸発器の熱負荷を最小限に抑制し、消費電力量の低減を図り省エネ効果の極めて高い冷蔵庫を提供することができる。 The refrigerator of the present invention can provide a refrigerator with extremely high energy saving effect by minimizing the heat load of the evaporator and reducing the power consumption.
また、蒸発器内部圧力上昇を抑制することにより溶接箇所等のピンホールやクラックから冷媒の庫内漏洩を防止し、より安全性の高い冷蔵庫を提供することができる。 Further, by suppressing the rise in the internal pressure of the evaporator, it is possible to prevent the refrigerant from leaking from the pinholes and cracks at the welded portions, and to provide a safer refrigerator.
また、吸入配管内の冷凍機油の滞留量を低減し、冷凍機油が圧縮機へ流入するときに発生する圧縮機破壊を防止し、信頼性の高い冷蔵庫を提供することができる。 Further, the amount of refrigeration oil remaining in the suction pipe can be reduced, the compressor can be prevented from being destroyed when the refrigeration oil flows into the compressor, and a highly reliable refrigerator can be provided.
また、圧縮機内部圧力を短期間で上昇、均圧バランスさせることにより、摺動部摩耗による圧縮機停止を回避した信頼性の高い冷蔵庫を提供することができる。 Further, by increasing the internal pressure of the compressor in a short period of time and balancing the pressure, it is possible to provide a highly reliable refrigerator that avoids the stop of the compressor due to sliding portion wear.
請求項1に記載の発明は、圧縮機と、凝縮器と、減圧装置と、蒸発器を直列に接続した冷媒回路を設けた冷凍サイクルを備えた冷蔵庫において、前記凝縮器と前記減圧装置の間に切替弁を設け、前記切替弁から前記圧縮機までを連通するバイパス回路を設けた。 The invention according to claim 1 is a refrigerator including a compressor, a condenser, a decompression device, and a refrigeration cycle provided with a refrigerant circuit in which an evaporator is connected in series, and between the condenser and the decompression device. A switching valve is provided, and a bypass circuit communicating from the switching valve to the compressor is provided.
これによって、凝縮器からの高温高圧液冷媒は圧縮機内部へ直接開放流入されるため、蒸発器への環流は、一旦、内容積のある圧縮機に入り、その後断面積の小さい吸入配管へ流入するため、冷媒流入量は大幅に減少し、蒸発器における熱負荷は軽減され、また蒸発器内部の圧力上昇も減少する。これにより蒸発器における冷媒漏洩を防止し、高い安全性を確保することができる。さらに、蒸発器の熱負荷を低減させ、消費電力量を低減させることができる。また、吸入配管内に滞留する冷凍機油も減少するため、起動時や液バック時における圧縮機への油流入が減少することができる。 As a result, the high-temperature and high-pressure liquid refrigerant from the condenser is directly opened into the compressor, and the recirculation flow to the evaporator once enters the compressor having an internal volume and then flows into the suction pipe having a small cross-sectional area. Therefore, the refrigerant inflow amount is greatly reduced, the heat load in the evaporator is reduced, and the pressure rise inside the evaporator is also reduced. Thereby, the refrigerant | coolant leakage in an evaporator can be prevented and high safety | security can be ensured. Furthermore, the heat load of the evaporator can be reduced and the power consumption can be reduced. Further, since the refrigeration oil staying in the suction pipe is also reduced, the oil inflow to the compressor at the time of start-up or liquid back can be reduced.
また、請求項2に記載の発明は、請求項1に記載の発明の冷蔵庫において、前記圧縮機はレシプロ方式の低圧タイプで、かつ前記圧縮機メカ部の吸入経路とケーシングの吸入配管が連通または部分的に開放する。 Further, the invention according to claim 2 is the refrigerator according to claim 1, wherein the compressor is a reciprocating low-pressure type, and the suction passage of the compressor mechanical part and the suction pipe of the casing communicate with each other. Partially open.
これにより、吸入配管が連通の場合、高温のケーシング内部雰囲気ガスから吸入ガスへの吸熱現象を抑制し、圧縮機シリンダへ流入する吸入ガス温度を大幅に低減させる。その結果、圧縮機の体積効率並びにCOPが増大し、冷蔵庫の消費電力量低減を可能にする。一方、吸入配管が部分的に開放される場合、蒸発器における冷媒漏洩の可能性を低減するとともに、熱負荷量の低減が可能になる。 Thereby, when the suction pipe is in communication, the endothermic phenomenon from the high-temperature casing internal atmosphere gas to the suction gas is suppressed, and the temperature of the suction gas flowing into the compressor cylinder is greatly reduced. As a result, the volumetric efficiency and COP of the compressor increase, and the power consumption of the refrigerator can be reduced. On the other hand, when the suction pipe is partially opened, it is possible to reduce the possibility of refrigerant leakage in the evaporator and to reduce the heat load.
また、請求項3に記載の発明は、請求項1または請求項2に記載の発明の冷蔵庫において、前記制御装置は、前記圧縮機起動前の所定時間において、前記切替弁は、前記バイパス回路側を開放、前記減圧装置側を閉塞し、かつ前記圧縮機起動直後の所定時間経過後に前記切替弁のバイパス回路側を閉塞、前記減圧装置側を開放する。 The invention according to claim 3 is the refrigerator of the invention according to claim 1 or 2, wherein the control device is configured so that the switching valve is on the bypass circuit side during a predetermined time before starting the compressor. Is opened, the pressure reducing device side is closed, and the bypass circuit side of the switching valve is closed and the pressure reducing device side is opened after a lapse of a predetermined time immediately after starting the compressor.
これにより、圧縮機が起動し凝縮器内部に液冷媒が充満した状態で、切替弁を減圧装置側へ開放する制御をとる。その結果、通常断続運転直後もしくは除霜運転直後の起動時において、液冷媒は凝縮器から蒸発器へ短時間で到着することから、冷蔵庫運転開始時の冷却性能が向上し、消費電力量を著しく低減することができる。 Thus, control is performed to open the switching valve to the decompression device side in a state where the compressor is started and the liquid refrigerant is filled in the condenser. As a result, the liquid refrigerant arrives from the condenser to the evaporator in a short time at the start immediately after the intermittent operation or the defrosting operation, so that the cooling performance at the start of the refrigerator operation is improved and the power consumption is remarkably increased. Can be reduced.
また、請求項4に記載の発明は、請求項1から請求項3のいずれか一項に記載の発明の冷蔵庫において、前記制御装置の前記切替弁は、除霜運転時において、前記バイパス回路側及び前記減圧装置側を閉塞することを特徴とする。 The invention according to claim 4 is the refrigerator according to any one of claims 1 to 3, wherein the switching valve of the control device is on the bypass circuit side during the defrosting operation. And the pressure reducing device side is closed.
これにより、蒸発器に冷媒を極力滞留させない制御手段を講じ、さらに圧縮機に貯留する冷凍機油に蒸発器から環流してきた低温冷媒を溶解させることで、蒸発器内の冷媒量を削減することにより、除霜期間中、ヒータ等の熱源により蒸発器は加熱された際、蒸発器内に滞留する冷媒量が少量のためサーモサイフォン効果が得られず、蒸発器内部の圧力は上昇しない。その結果、蒸発器の配管継ぎ目・溶接箇所等のピンホールやクラックからの冷媒漏洩の可能性が低減でき、発火や火災の未然防止を図り、より高い安全性の確保が可能である。 As a result, control means for preventing the refrigerant from staying in the evaporator as much as possible is taken, and further, the amount of refrigerant in the evaporator is reduced by dissolving the low-temperature refrigerant circulating from the evaporator in the refrigerating machine oil stored in the compressor. During the defrosting period, when the evaporator is heated by a heat source such as a heater, the thermosiphon effect is not obtained because the amount of refrigerant staying in the evaporator is small, and the pressure inside the evaporator does not increase. As a result, it is possible to reduce the possibility of refrigerant leakage from pinholes and cracks in the pipe joints and welded portions of the evaporator, prevent ignition and fire, and ensure higher safety.
(実施の形態1)
図1は、本発明の実施の形態1における冷蔵庫の概略断面図を示すものであり、図2は同実施の形態の冷蔵庫の圧縮機の要部断面図を示すものであり、図3は同実施の形態の冷蔵庫の運転タイムチャートである。
(Embodiment 1)
FIG. 1 shows a schematic cross-sectional view of the refrigerator in Embodiment 1 of the present invention, FIG. 2 shows a cross-sectional view of the main part of the compressor of the refrigerator in the same embodiment, and FIG. It is an operation time chart of the refrigerator of an embodiment.
なお、背景技術と同一構成については同一符号を付す。 In addition, the same code | symbol is attached | subjected about the same structure as background art.
図1において、例えば硬質発泡ウレタンなどの断熱材で周囲と断熱して構成されている冷蔵庫101は複数の断熱区画に区分されており、冷蔵室105、引出しタイプの冷凍室106、野菜室107、製氷室108、切替室109の構成となっている。 In FIG. 1, a refrigerator 101 configured to be insulated from the surroundings with a heat insulating material such as hard foam urethane is divided into a plurality of heat insulating compartments, and includes a refrigerator room 105, a drawer type freezer room 106, a vegetable room 107, The ice making chamber 108 and the switching chamber 109 are configured.
最上部に設けられて、最も使用頻度の高い冷蔵室105は、冷蔵保存のために凍らない温度を下限に通常1〜5℃でPCCセンサー113により設定されている。野菜室107は冷蔵室105と同等もしくは若干高い温度設定の2℃〜7℃とすることが多い。低温にすれば葉野菜の鮮度を長期間維持することが可能である。 The refrigerated room 105 provided at the top and most frequently used is set by the PCC sensor 113 at a temperature of 1 to 5 ° C., usually at a temperature that does not freeze for refrigerated storage. The vegetable room 107 is often set to a temperature setting of 2 ° C. to 7 ° C., which is the same as or slightly higher than that of the refrigerator room 105. If the temperature is lowered, the freshness of leafy vegetables can be maintained for a long time.
冷凍室106は冷凍保存のために通常−22から−18℃でFCCセンサー114により設定されているが、冷凍保存状態の向上のために、たとえば−30から−25℃の低温で設定されることもある。 The freezer compartment 106 is normally set by the FCC sensor 114 at −22 to −18 ° C. for frozen storage, but should be set at a low temperature of −30 to −25 ° C., for example, to improve the frozen storage state. There is also.
また、図1より、冷凍サイクル部品として、まず冷蔵庫上部背面に区画される機械室120に配置される圧縮機131、凝縮器132、機械室ファン(図示せず)、減圧装置133として本実施の形態においてはキャピラリーを用いる。さらに切替弁137、ドライヤ(図示せず)が配置される。また、切替弁137と圧縮機131の冷媒注入配管140を連通するバイパス配管139が構成される。 Further, as shown in FIG. 1, as the refrigeration cycle components, the compressor 131, the condenser 132, the machine room fan (not shown), and the decompression device 133 which are first arranged in the machine room 120 partitioned on the upper rear surface of the refrigerator In the form, a capillary is used. Further, a switching valve 137 and a dryer (not shown) are arranged. Further, a bypass pipe 139 that communicates the switching valve 137 and the refrigerant injection pipe 140 of the compressor 131 is configured.
凝縮器132は強制対流方式のものに加えて、冷蔵庫101の周囲鋼板を利用して自然放熱するための配管や、各室断熱扉体間の仕切りに配設して防滴防止を行うための配管を組み合わせてもよい。 In addition to the forced convection method, the condenser 132 is provided in a pipe for naturally dissipating heat using the surrounding steel plate of the refrigerator 101 and a partition between the heat insulating doors in each room to prevent drip-proofing. You may combine piping.
更に、図2より圧縮機131について説明すると、本実施の形態の圧縮機131は、低圧タイプで、かつケーシング163の吸入配管138とメカ部160の吸入経路161開口部162は、対向して連続的な流れを形成する位置関係にあるが部分的に圧縮機131内部に開放されている。さらに、バイパス回路139の出口部は、冷媒注入配管140のY型配管の片側に連結される、また吐出管はメカ部160からケーシング163に配設され、シリンダ(図示せず)からの加圧冷媒を凝縮器132へ流出させる。 Further, the compressor 131 will be described with reference to FIG. 2. The compressor 131 of the present embodiment is a low-pressure type, and the suction pipe 138 of the casing 163 and the suction path 161 opening 162 of the mechanical unit 160 are continuously opposed to each other. However, the compressor 131 is partially opened inside the compressor 131. Further, the outlet of the bypass circuit 139 is connected to one side of the Y-shaped pipe of the refrigerant injection pipe 140, and the discharge pipe is disposed from the mechanical section 160 to the casing 163 and pressurized from a cylinder (not shown). The refrigerant flows out to the condenser 132.
また、冷凍サイクルの構成機器である蒸発器134は庫内ファン151と共に、中段に位置する野菜室107の後方背面部に設けられている。これにより最下段の貯蔵室である冷凍室106の内容積と奥行きを最大限に大きくすることが可能である。 Moreover, the evaporator 134 which is a component apparatus of a refrigerating cycle is provided in the back back part of the vegetable compartment 107 located in a middle stage with the fan 151 in a store | warehouse | chamber. As a result, it is possible to maximize the internal volume and depth of the freezer compartment 106 which is the lowermost storage room.
なお、中段の野菜室107と最下段の冷凍室106は逆の構成となれば、野菜室の内容積と奥行きを最大限に大きくすることが可能となる。 If the middle vegetable room 107 and the lowermost freezer room 106 have the opposite configuration, it is possible to maximize the internal volume and depth of the vegetable room.
以上のように構成された冷蔵庫について、以下その動作、作用を説明する。 About the refrigerator comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.
まず、冷凍サイクルの動作について説明する。庫内の設定された各温度に応じて制御手段により冷凍サイクルが動作して冷却運転が行われる。まず圧縮機131の起動により吐出された高温高圧冷媒は、凝縮器132にて放熱して凝縮液化し、キャピラリーである減圧装置133に至る。その後、減圧装置133ではサクションライン138と熱交換しながら減圧されて低温低圧の液冷媒となって蒸発器134に至る。 First, the operation of the refrigeration cycle will be described. The refrigeration cycle is operated by the control means according to each set temperature in the refrigerator, and the cooling operation is performed. First, the high-temperature and high-pressure refrigerant discharged by starting the compressor 131 dissipates heat in the condenser 132 to be condensed and liquefied, and reaches a decompression device 133 that is a capillary. Thereafter, the decompression device 133 is decompressed while exchanging heat with the suction line 138, becomes a low-temperature and low-pressure liquid refrigerant, and reaches the evaporator 134.
庫内ファン151の動作により、庫内の空気と熱交換されて蒸発器134内の冷媒は蒸発気化する。低温の冷気をダンパ(図示なし)などで分配することで各室の冷却を行う。 By the operation of the internal fan 151, heat is exchanged with the air in the internal space, and the refrigerant in the evaporator 134 is evaporated. Each room is cooled by distributing low-temperature cold air with a damper (not shown).
尚、複数の蒸発器を用いる場合は流路制御手段により各蒸発器へ冷媒が供給される。 In addition, when using a some evaporator, a refrigerant | coolant is supplied to each evaporator by a flow-path control means.
次に、蒸発器134を出た冷媒はサクションライン138を経て圧縮機131へと吸い込まれる。以上の閉回路である第一回路135を冷媒が循環して冷蔵庫の冷却運転を可能にする。 Next, the refrigerant exiting the evaporator 134 is sucked into the compressor 131 through the suction line 138. The refrigerant circulates through the first circuit 135, which is the above-described closed circuit, to enable the cooling operation of the refrigerator.
図3について、各記号を説明すると、T1は、圧縮機運転開始時刻、T2は、冷凍運転(冷蔵室以外)開始時刻、T3は、圧縮機停止時刻を示す。また、T4は、圧縮機停止からバイパス回路を開放させるまでの時間、T5は、圧縮機起動からバイパス回路を封鎖するまでの時間である。さらに、TP1は、PCCセンサーの上限温度、TP2は、PCCセンサーの下限温度、TF1は、FCCセンサーの上限温度、TF2は、FCCセンサーの下限温度である。 Referring to FIG. 3, each symbol will be described. T1 represents a compressor operation start time, T2 represents a refrigeration operation (other than the refrigerator compartment) start time, and T3 represents a compressor stop time. T4 is the time from the compressor stop until the bypass circuit is opened, and T5 is the time from the start of the compressor until the bypass circuit is blocked. Further, TP1 is the upper limit temperature of the PCC sensor, TP2 is the lower limit temperature of the PCC sensor, TF1 is the upper limit temperature of the FCC sensor, and TF2 is the lower limit temperature of the FCC sensor.
以上をもとに、本実施の形態における冷蔵庫101の運転パターンにおいて冷凍室冷却開始T2から順次説明すると、圧縮機131運転が開始した後、PCCセンサー113温度がTP2以下となったため、冷蔵室ダンパー(図示せず)が閉じて、冷凍室106、切替室109、製氷室108、野菜室107の専用冷却運転となる。次に、T3では、FCCセンサー114温度がTF2以下となったら、圧縮機131の運転は停止され、同時に庫内ファン151停止、切替弁137は、第一回路135並びにバイパス回路139を閉鎖する。圧縮機停止期間中、庫内温度はほとんど上昇しない。一方、切替弁137は、圧縮機131停止後からT4時間経過後に、バイパス回路139を開放すると同時に第一回路135を閉鎖する。その結果、高圧液冷媒は冷媒注入配管140を介して圧縮機131へ直接流入開放される。したがって、圧縮機131内部圧力が上昇し、圧縮機131高圧側圧力とバランスし、圧力が数十秒から数分程度で均圧する。次に、T1では、FCCセンサー114温度がTF1以上となったため、圧縮機131運転を再開する。このとき、まだバイパス回路139のみを開放した状態のため、減圧装置(キャピラリー)133から蒸発器134への冷媒流入はなく、逆に蒸発器134から圧縮機131への冷媒吸入が行なわれる。この状態をT5時間、たとえば数秒から数十秒程度行なった後、切替弁137の第一回路135を開放し、かつバイパス回路139を閉鎖、同時に冷蔵室ダンパー(図示せず)を開放し、全室冷却運転とする。以上のT1からT3における一連の冷却パターンを順次繰り返すことにより、冷却運転を可能にする。 Based on the above, the operation pattern of the refrigerator 101 according to the present embodiment will be described in order from the freezer compartment cooling start T2. After the compressor 131 operation is started, the temperature of the PCC sensor 113 becomes TP2 or lower. (Not shown) is closed, and the freezing chamber 106, the switching chamber 109, the ice making chamber 108, and the vegetable chamber 107 are exclusively cooled. Next, at T3, when the temperature of the FCC sensor 114 becomes TF2 or less, the operation of the compressor 131 is stopped. At the same time, the internal fan 151 is stopped, and the switching valve 137 closes the first circuit 135 and the bypass circuit 139. During the compressor shutdown period, the internal temperature hardly rises. On the other hand, the switching valve 137 opens the bypass circuit 139 and closes the first circuit 135 at the same time after T4 time has elapsed since the compressor 131 stopped. As a result, the high-pressure liquid refrigerant flows directly into the compressor 131 through the refrigerant injection pipe 140 and is released. Therefore, the internal pressure of the compressor 131 rises and balances with the high pressure side pressure of the compressor 131, and the pressure is equalized in several tens of seconds to several minutes. Next, at T1, since the temperature of the FCC sensor 114 is equal to or higher than TF1, the operation of the compressor 131 is resumed. At this time, since only the bypass circuit 139 is still open, refrigerant does not flow from the decompression device (capillary) 133 to the evaporator 134, and conversely, refrigerant is sucked from the evaporator 134 to the compressor 131. After performing this state for T5 time, for example, several seconds to several tens of seconds, the first circuit 135 of the switching valve 137 is opened and the bypass circuit 139 is closed. At the same time, the refrigerator compartment damper (not shown) is opened. Room cooling operation. The cooling operation is enabled by sequentially repeating the series of cooling patterns from T1 to T3.
圧縮機131起動前、高温高圧液冷媒は凝縮器132から圧縮機131内部へ直接開放流入される。このとき、圧縮機131から蒸発器134への冷媒流入量に関して、一端、冷却システムの中で突出した体積、例えば1.5Lを有する圧縮機131に入り、次に管内径の小さい、例えば内径φ5.3mmの吸入配管138へ流入しようとした場合、流路抵抗が大きく作用し、冷媒流入量は大幅に減少し、蒸発器134における熱負荷は軽減されるとともに、蒸発器134内部の圧力上昇も減少する。これにより蒸発器134における冷媒漏洩を防止し、高い安全性を確保することができる。さらに、蒸発器134の熱負荷を低減させることにより、圧縮機起動時における蒸発器134の冷却性能が増加し、消費電力量の低減を図り省エネ効果の極めて高い冷蔵庫を提供することができる。 Before the compressor 131 is started, the high-temperature high-pressure liquid refrigerant is directly opened from the condenser 132 into the compressor 131. At this time, regarding the refrigerant inflow from the compressor 131 to the evaporator 134, the refrigerant 131 enters the compressor 131 having a volume protruding in the cooling system, for example, 1.5L, and then has a small pipe inner diameter, for example, an inner diameter φ5. When trying to flow into the 3 mm suction pipe 138, the flow resistance is greatly affected, the refrigerant flow rate is greatly reduced, the heat load on the evaporator 134 is reduced, and the pressure inside the evaporator 134 is also increased. Decrease. Thereby, the refrigerant | coolant leak in the evaporator 134 can be prevented and high safety | security can be ensured. Furthermore, by reducing the heat load of the evaporator 134, the cooling performance of the evaporator 134 at the time of starting the compressor is increased, so that the power consumption can be reduced and a refrigerator with an extremely high energy saving effect can be provided.
また、吸入配管138内に滞留する冷凍機油(図示せず)も減少するため、起動時や液バック時における圧縮機131への油流入が減少することができ、圧縮機131バルブの破損を防止し、信頼性の高い冷蔵庫101を実現することができる。 Also, since the refrigeration oil (not shown) staying in the suction pipe 138 is reduced, the oil inflow to the compressor 131 at the time of start-up and liquid back can be reduced, and the compressor 131 valve is prevented from being damaged. In addition, a highly reliable refrigerator 101 can be realized.
更に、圧縮機131起動制御に関して、圧縮機131が起動し凝縮器132内部に液冷媒が充満した状態で、切替弁137を減圧装置133側へ開放することから、断続運転直後もしくは除霜運転直後の起動時において、蒸発器134に液冷媒が短時間で充満することから、蒸発器134の冷え出し遅れを防止し、冷蔵庫101運転開始時の冷却性能が向上し、消費電力量を著しく低減することができる。 Furthermore, regarding the compressor 131 activation control, the switching valve 137 is opened to the decompression device 133 side in the state where the compressor 131 is activated and the condenser 132 is filled with liquid refrigerant, so immediately after the intermittent operation or immediately after the defrosting operation. Since the liquid refrigerant is filled in the evaporator 134 in a short time at the start-up time, the cooling of the evaporator 134 is prevented from being delayed, the cooling performance at the start of the operation of the refrigerator 101 is improved, and the power consumption is remarkably reduced. be able to.
また、従来例の蒸発器2基に対して、本実施の形態は1基としたことから、蒸発器134及び周辺部品が不要となる分、収納容量をおおよそ5L程度増大させることができる。また、コストの観点から、従来例の中における蒸発器及び周辺部品、さらには逆止弁を省くことができることから、大幅な合理化が可能になる。 In addition, since the present embodiment uses only one evaporator compared to the two conventional evaporators, the storage capacity can be increased by about 5 L, because the evaporator 134 and peripheral components are unnecessary. In addition, from the viewpoint of cost, the evaporator, peripheral components, and check valve in the conventional example can be omitted, so that significant rationalization is possible.
尚、本実施の形態の機械室は、冷蔵庫背面上部に設置したが、冷蔵庫背面下部においても、切替弁を含めた構成が同じになることより、同様の効果が得られる。 In addition, although the machine room of this Embodiment was installed in the refrigerator back upper part, since the structure including a switching valve becomes the same also in a refrigerator back lower part, the same effect is acquired.
(実施の形態2)
図4は、本発明の実施の形態2における冷蔵庫の圧縮機の要部断面図を示すものである。なお、背景技術と同一構成については同一符号を付す。
(Embodiment 2)
FIG. 4 shows a cross-sectional view of a main part of the refrigerator compressor according to Embodiment 2 of the present invention. In addition, the same code | symbol is attached | subjected about the same structure as background art.
図4より圧縮機231について説明すると、本実施の形態の圧縮機231は、低圧タイプで、かつ圧縮機231の吸入配管238とメカ部260の吸込経路261開口部262は、連結され連続的に冷媒をシリンダ(図示せず)へ供給する。さらに、バイパス回路239の出口部は、冷媒注入配管240のY型配管の片側に連結される。 The compressor 231 will be described with reference to FIG. 4. The compressor 231 of the present embodiment is a low-pressure type, and the suction pipe 238 of the compressor 231 and the suction passage 261 opening 262 of the mechanical unit 260 are connected and continuously. A refrigerant is supplied to a cylinder (not shown). Further, the outlet portion of the bypass circuit 239 is connected to one side of the Y-type piping of the refrigerant injection piping 240.
以上より、高温の圧縮機231内部雰囲気ガスから吸入ガスへの吸熱現象を抑制し、圧縮機231シリンダ(図示せず)へ流入する吸入ガス温度を大幅に低減させる。その結果、圧縮機231の体積効率並びにCOPが増大し、冷蔵庫101の消費電力量低減を可能にする。 As described above, the endothermic phenomenon from the high-temperature compressor 231 internal atmosphere gas to the intake gas is suppressed, and the intake gas temperature flowing into the compressor 231 cylinder (not shown) is greatly reduced. As a result, the volumetric efficiency and COP of the compressor 231 increase, and the power consumption of the refrigerator 101 can be reduced.
また、除霜運転時において、本実施の形態の制御装置である切替弁137は、バイパス回路239側及び減圧装置133側を閉塞する制御とした。 Further, during the defrosting operation, the switching valve 137 which is the control device of the present embodiment is configured to close the bypass circuit 239 side and the decompression device 133 side.
これにより、蒸発器134に冷媒を極力滞留させない制御手段を講じ、さらに圧縮機231に貯留する冷凍機油(図示せず)に蒸発器134から環流してきた低温冷媒を溶解させることで、更に蒸発器134内の冷媒量を削減することにより、除霜期間中、ヒータ等の熱源により蒸発器134は加熱された際、蒸発器134内に滞留する冷媒量が少量よりサーモサイフォン効果が得られず、蒸発器134内部の圧力は上昇しない。その結果、蒸発器134の配管継ぎ目等からの冷媒漏洩がなくなり、冷蔵庫101に関して高い安全性が確保できる。 Thus, a control means for preventing the refrigerant from staying in the evaporator 134 as much as possible is provided, and further by dissolving the low-temperature refrigerant circulating from the evaporator 134 in the refrigerating machine oil (not shown) stored in the compressor 231, the evaporator By reducing the amount of refrigerant in 134, when the evaporator 134 is heated by a heat source such as a heater during the defrost period, the amount of refrigerant staying in the evaporator 134 is less than a small amount, and the thermosiphon effect cannot be obtained. The pressure inside the evaporator 134 does not increase. As a result, there is no refrigerant leakage from the pipe joint or the like of the evaporator 134, and high safety can be secured for the refrigerator 101.
尚、特に低温(−30℃〜−80℃)冷凍サイクルを実現する場合、通常冷凍運転(−30℃〜−40℃)に対して、蒸発器234の圧力が著しく低下することから、本実施の形態の効果が大きい。 In particular, when a low temperature (-30 ° C to -80 ° C) refrigeration cycle is realized, the pressure of the evaporator 234 is significantly reduced with respect to the normal refrigeration operation (-30 ° C to -40 ° C). The effect of the form is great.
尚、本実施の形態に関して、凝縮器を高元サイクルで冷却する二元冷凍の低元サイクルに利用しても同様の効果が得られる。 In addition, regarding this Embodiment, the same effect is acquired even if it utilizes for the low element cycle of the two-stage freezing which cools a condenser by a high element cycle.
以上のように、本発明にかかる冷蔵庫は、冷凍システムの高効率化と省エネルギー化ならびに可燃性冷媒の漏洩防止を図ることが可能となるので、冷蔵庫や自動販売機を含む冷凍機器全般に適用できる。 As described above, since the refrigerator according to the present invention can improve the efficiency and energy saving of the refrigeration system and prevent leakage of the flammable refrigerant, it can be applied to all refrigeration equipment including refrigerators and vending machines. .
101 冷蔵庫
131,231 圧縮機
132 凝縮器
133 減圧装置
134 蒸発器
137 切替弁
138,238 吸入配管
139,239 バイパス回路
160,260 メカ部
161,261 吸入経路
163,263 ケーシング
DESCRIPTION OF SYMBOLS 101 Refrigerator 131,231 Compressor 132 Condenser 133 Pressure reducing device 134 Evaporator 137 Switching valve 138,238 Suction piping 139,239 Bypass circuit 160,260 Mechanical part 161,261 Suction path 163,263 Casing
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JP2005180738A (en) * | 2003-12-17 | 2005-07-07 | Toshiba Corp | Refrigerator |
JP2006329142A (en) * | 2005-05-30 | 2006-12-07 | Matsushita Electric Ind Co Ltd | Sealed compressor |
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JP2003035462A (en) * | 2001-07-23 | 2003-02-07 | Hitachi Ltd | Refrigerator |
JP2003287333A (en) * | 2002-03-29 | 2003-10-10 | Toshiba Corp | Refrigerator |
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JP2010169353A (en) * | 2009-01-26 | 2010-08-05 | Panasonic Corp | Refrigerator |
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