JP2002267285A - Cooler/refrigerator - Google Patents
Cooler/refrigeratorInfo
- Publication number
- JP2002267285A JP2002267285A JP2001069205A JP2001069205A JP2002267285A JP 2002267285 A JP2002267285 A JP 2002267285A JP 2001069205 A JP2001069205 A JP 2001069205A JP 2001069205 A JP2001069205 A JP 2001069205A JP 2002267285 A JP2002267285 A JP 2002267285A
- Authority
- JP
- Japan
- Prior art keywords
- evaporator
- refrigerant
- cooling
- expansion valve
- refrigeration
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、冷房および冷蔵機
能を備える冷房冷蔵装置に関するものであり、特に、簡
素な冷凍サイクルの構成に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling and refrigerating apparatus having a cooling and refrigerating function, and more particularly to a simple refrigerating cycle.
【０００２】[0002]
【従来の技術】乗用車などの車両用向けに車室内の冷房
を行なうとともに、飲料水などを冷蔵する冷蔵庫を備
え、この冷蔵庫を冷蔵する冷凍サイクルを有した冷房冷
蔵装置が知られている。この冷房冷蔵装置は、図２に示
すように、冷凍サイクル１００に組み込まれた受液器１
１０に接続された高圧配管に、第１蒸発器１２０ａと第
２蒸発器１２０ｂとを並列に接続したものである。所謂
一方の第１蒸発器１２０ａ側が車室内を冷房するための
蒸発器であって、上流側に電磁弁１３０および膨張弁１
４０ａが設けられ、他方の第２蒸発器１２０ｂ側が冷蔵
庫を冷蔵するための蒸発器であって、上流側に膨張弁１
４０ａが設けられている。そして、これらの膨張弁１４
０ａ、１４０ｂはそれぞれの蒸発器１２０ａ、１２０ｂ
の低圧配管側の出口温度を検知して冷媒流量を制御する
周知の温度式膨張弁である。2. Description of the Related Art There is known a cooling and refrigeration apparatus which cools a passenger compartment or the like for a vehicle, includes a refrigerator for chilling drinking water, and has a refrigeration cycle for chilling the refrigerator. As shown in FIG. 2, the cooling refrigeration apparatus includes a receiver 1 incorporated in a refrigeration cycle 100.
A first evaporator 120a and a second evaporator 120b are connected in parallel to a high-pressure pipe connected to 10. The so-called one first evaporator 120a side is an evaporator for cooling the vehicle interior, and the electromagnetic valve 130 and the expansion valve 1 are provided on the upstream side.
40a is provided, and the other second evaporator 120b side is an evaporator for refrigerating the refrigerator, and the expansion valve 1 is provided on the upstream side.
40a is provided. And these expansion valves 14
0a, 140b are the respective evaporators 120a, 120b
This is a well-known thermal expansion valve that controls the flow rate of refrigerant by detecting the outlet temperature on the low-pressure pipe side.
【０００３】なお、上記電磁弁１３０は、第１蒸発器１
２０ａ側に流れる冷媒流量を、例えば電磁弁１３０を１
分間開き、１５秒間閉じるなどの周期的に開閉遮断させ
ることで、冷房冷蔵機能のうち冷蔵機能の向上を優先し
たものである。なお、１５０は冷媒を圧縮する圧縮機
で、１６０は圧縮された冷媒を凝縮させる凝縮器であ
る。[0003] The solenoid valve 130 is connected to the first evaporator 1.
The flow rate of the refrigerant flowing to the side
By periodically opening and closing such as opening for minutes and closing for 15 seconds, priority is given to improving the refrigeration function among the cooling and refrigeration functions. In addition, 150 is a compressor for compressing the refrigerant, and 160 is a condenser for condensing the compressed refrigerant.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、乗用車
などの車両における冷蔵庫の冷蔵能力は、車室内を冷房
する冷房能力と比べて格段に小さく、かかる冷蔵庫のた
めに冷媒循環系の構成を冷房用の冷媒循環系と全く同じ
にすることは取り付けスペースおよび部品コストの両面
で無駄が多い。However, the refrigerating capacity of the refrigerator in a vehicle such as a passenger car is much smaller than the cooling capacity for cooling the passenger compartment. Making it exactly the same as the refrigerant circulation system is wasteful in terms of both mounting space and component costs.
【０００５】また、冷媒流量の分配を周期的に可変させ
るための電磁弁１３０を設けることにより、部品コスト
の増加、電磁弁１３０の作動音の騒音防止の施策の追加
および電磁弁１３０の開閉による車室内の吹出口からの
吹出空気温度の変動などの冷房機能への悪影響などの問
題がある。[0005] Further, by providing the solenoid valve 130 for periodically varying the distribution of the refrigerant flow rate, it is possible to increase the cost of parts, add measures to prevent noise from operating noise of the solenoid valve 130, and open and close the solenoid valve 130. There is a problem such as a bad influence on the cooling function such as a change in the temperature of the air blown from the air outlet in the vehicle cabin.
【０００６】そこで、本発明の目的は、上記点を鑑みた
ものであって、冷蔵側の冷媒循環系を簡素化することで
安価で、かつ快適性の良好な冷房冷蔵装置の提供をする
ことにある。SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a cooling and refrigeration apparatus which is inexpensive and has good comfort by simplifying the refrigerant circulation system on the refrigeration side. It is in.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するため
に、請求項１ないし請求項４に記載の技術的手段を採用
する。すなわち、請求項１に記載の発明では、冷凍サイ
クルに組み込まれた受液器（３）に接続された高圧配管
（７）に、二つの蒸発器（５ａ、５ｂ）を並列に接続さ
れた冷房冷蔵装置において、二つの蒸発器（５ａ、５
ｂ）のうち、一方の第１蒸発器（５ａ）が高圧配管
（７）の下流側に膨張弁（４）を介して配設され、他方
の第２蒸発器（５ｂ）が膨張弁（４）の下流側に減圧用
の固定絞り部材（６）を介して配設されるように構成す
ることを特徴としている。In order to achieve the above object, the technical means described in claims 1 to 4 is adopted. That is, according to the first aspect of the present invention, a cooling system in which two evaporators (5a, 5b) are connected in parallel to a high-pressure pipe (7) connected to a liquid receiver (3) incorporated in a refrigeration cycle. In the refrigerator, two evaporators (5a, 5a, 5a
b), one first evaporator (5a) is disposed downstream of the high-pressure pipe (7) via an expansion valve (4), and the other second evaporator (5b) is connected to the expansion valve (4). ) Is arranged via a fixed throttle member (6) for reducing pressure on the downstream side of (1).
【０００８】請求項１に記載の発明によれば、第２蒸発
器（５ｂ）を、例えば第１蒸発器（５ａ）を冷房用、第
２蒸発器（５ｂ）を冷蔵用とすると、第１蒸発器（５
ａ）は膨張弁（４）によって冷媒流量の調節が行なわ
れ、第２蒸発器（５ｂ）は膨張弁（４）および固定絞り
部材（６）によって冷媒流量の調節が行なわれる。According to the first aspect of the present invention, if the second evaporator (5b) is for cooling, for example, the first evaporator (5a) is for cooling, and the second evaporator (5b) is for refrigeration. Evaporator (5
In (a), the refrigerant flow rate is adjusted by the expansion valve (4), and in the second evaporator (5b), the refrigerant flow rate is adjusted by the expansion valve (4) and the fixed throttle member (6).
【０００９】従って、第２蒸発器（５ｂ）に蒸発温度の
低い冷媒を第２蒸発器（５ｂ）へ適切な流量に減圧しな
がら供給できるとともに、冷房用となる第１蒸発器（５
ａ）にも適切な流量に減圧しながら供給できる。これに
より、冷蔵側の冷媒循環系に、例えば固定絞り部材
（６）として、例えばオリフィスまたはキャピラリチュ
ーブなどを用いることで、従来と比べて、コストの安い
固定絞り部材（６）を追加することで良いため、冷蔵側
の冷媒循環系の簡素化が可能となり低コストが図れる。Therefore, a refrigerant having a low evaporation temperature can be supplied to the second evaporator (5b) while reducing the flow rate to an appropriate flow rate to the second evaporator (5b), and the first evaporator (5) for cooling is provided.
Also in a), it can be supplied while reducing the pressure to an appropriate flow rate. Thus, by using, for example, an orifice or a capillary tube as the fixed throttle member (6) in the refrigerant circulation system on the refrigeration side, by adding the fixed throttle member (6) which is lower in cost than the conventional one, As a result, the refrigerant circulation system on the refrigeration side can be simplified and cost can be reduced.
【００１０】また、冷蔵側の冷媒循環系を膨張弁（４）
および固定絞り部材（６）によって冷媒流量の調節する
ことにより、例えば車室内の冷房能力に比べて冷蔵庫の
冷蔵能力が小さい冷房冷蔵装置であれば、上記固定絞り
部材（６）での減圧特性を予め径および長さを設定する
ことで、第１蒸発器（５ａ）側と第２蒸発器（５ｂ）側
とに冷媒量の分配が可能であるため、従来用いていた電
磁弁を不要とすることができ冷媒循環系をさらに簡素化
ができ安価な構成となる。The refrigerant circulation system on the refrigeration side is connected to an expansion valve (4).
By adjusting the flow rate of the refrigerant by the fixed throttle member (6), for example, in the case of a cooling refrigeration apparatus in which the refrigerator has a smaller refrigeration capacity than the cooling capacity in the vehicle cabin, the pressure reduction characteristic of the fixed throttle member (6) is reduced. By setting the diameter and length in advance, the amount of refrigerant can be distributed between the first evaporator (5a) side and the second evaporator (5b) side, so that the conventionally used solenoid valve is unnecessary. As a result, the refrigerant circulation system can be further simplified, resulting in an inexpensive configuration.
【００１１】また、電磁弁をなくすことで電磁弁の作動
音がなくなり快適性が向上するとともに、電磁弁の開閉
による車室内の吹出口からの吹出空気温度の変動などの
冷房機能への悪影響がなくなり、さらに快適性が向上す
る。In addition, the elimination of the solenoid valve eliminates the operating noise of the solenoid valve and improves the comfort. In addition, the opening and closing of the solenoid valve adversely affects the cooling function such as the fluctuation of the temperature of the air blown from the outlet in the passenger compartment. And comfort is further improved.
【００１２】請求項２に記載の発明では、膨張弁（４）
は、第１蒸発器（５ａ）および第２蒸発器（５ｂ）の低
圧配管（８）の合流点（Ｙ）の下流側の冷媒温度に基づ
いて冷媒流量を制御されることを特徴としている。According to the second aspect of the present invention, the expansion valve (4)
Is characterized in that the flow rate of the refrigerant is controlled based on the refrigerant temperature on the downstream side of the junction (Y) of the low-pressure pipe (8) of the first evaporator (5a) and the second evaporator (5b).
【００１３】請求項２に記載の発明によれば、膨張弁
（４）は、低圧配管（８）の合流点（Ｙ）の下流側の冷
媒温度を検出することにより、一方の第１蒸発器（５
ａ）への冷媒流量が制御され、他方の第２蒸発器（５
ｂ）の負荷を加味した全体的な冷房を行なえ、かつ両者
のスーパーヒートによる冷媒量の調整が行なわれるた
め、圧縮機への液圧縮もない。According to the second aspect of the present invention, the expansion valve (4) detects the temperature of the refrigerant downstream of the junction (Y) of the low-pressure pipe (8), so that one of the first evaporators. (5
The flow rate of the refrigerant to the second evaporator (5) is controlled.
Since the entire cooling in consideration of the load of b) can be performed and the amount of the refrigerant is adjusted by the superheat of both, there is no liquid compression to the compressor.
【００１４】請求項３に記載の発明では、膨張弁（４）
は、第１蒸発器（５ａ）よりも第２蒸発器（５ｂ）の方
が格段と小さい能力比のときには、第１蒸発器（５ａ）
の下流側の冷媒温度に基づいて冷媒流量を制御すること
を特徴としている。According to the third aspect of the present invention, the expansion valve (4)
When the second evaporator (5b) has a much smaller capacity ratio than the first evaporator (5a), the first evaporator (5a)
The flow rate of the refrigerant is controlled based on the temperature of the refrigerant on the downstream side of the refrigerant.
【００１５】請求項３に記載の発明によれば、例えば車
両の車室内を冷房する冷房能力と、５〜６本用の缶ジュ
ースを冷蔵する冷蔵能力とのような組み合わせのときに
は、膨張弁（４）が第１蒸発器（５ａ）の下流側の冷媒
温度に基づいて冷媒流量を制御することにより、第１蒸
発器（５ａ）側の冷媒が第２蒸発器（５ｂ）側の冷媒温
度を合流によって高めるために圧縮機に液冷媒を流出さ
せないため、車室内の冷房負荷に対応した冷媒流量の制
御ができ、第２蒸発器（５ｂ）側の影響を受けることが
ない。According to the third aspect of the present invention, for example, when the combination of the cooling capacity for cooling the cabin of the vehicle and the cooling capacity for cooling 5 to 6 canned juices, the expansion valve ( 4) controlling the refrigerant flow rate based on the refrigerant temperature on the downstream side of the first evaporator (5a), so that the refrigerant on the first evaporator (5a) side reduces the refrigerant temperature on the second evaporator (5b) side. Since the liquid refrigerant is not allowed to flow out to the compressor in order to increase by the merge, the refrigerant flow rate corresponding to the cooling load in the vehicle compartment can be controlled, and the second evaporator (5b) is not affected.
【００１６】請求項４に記載の発明では、二つの蒸発器
（５ａ、５ｂ）のうち、第１蒸発器（５ａ）が車室内を
冷房するための熱交換器であり、第２蒸発器（５ｂ）が
冷蔵庫を冷蔵するための熱交換器であることを特徴とし
ている。According to the fourth aspect of the invention, of the two evaporators (5a, 5b), the first evaporator (5a) is a heat exchanger for cooling the interior of the vehicle, and the second evaporator (5a, 5b). 5b) is a heat exchanger for refrigerating a refrigerator.
【００１７】請求項４に記載の発明によれば、第２蒸発
器（５ｂ）を冷蔵するための熱交換器であることより、
具体的に冷房機能となる第１蒸発器（５ａ）に比べて、
蒸発温度の低い冷蔵機能を上述した膨張弁（４）および
固定絞り部材（６）によって冷媒流量の調節が可能とな
る。従って、別個に膨張弁（４）設ける必要はない。According to the fourth aspect of the present invention, since the heat exchanger is used to cool the second evaporator (5b),
Specifically, as compared with the first evaporator (5a) having a cooling function,
The refrigerant flow rate can be adjusted by the above-described expansion valve (4) and fixed throttle member (6) for a refrigeration function with a low evaporation temperature. Therefore, there is no need to provide a separate expansion valve (4).
【００１８】なお、上記各手段の括弧内の符号は、後述
する実施形態の具体的手段との対応関係を示すものであ
る。Note that the reference numerals in parentheses of the above means indicate the correspondence with specific means of the embodiment described later.
【００１９】[0019]
【発明の実施の形態】以下、本発明の一実施形態を図１
に基いて説明する。まず、図１は本実施形態に係る冷房
冷蔵装置の冷媒循環系統図であり、冷凍サイクルＡにお
いて、１は低圧のガス状冷媒を吸入および圧縮動作を行
なう圧縮機、２は高温高圧のガス状冷媒を凝縮するコン
デンサ、３は高温高圧の液状冷媒を貯える受熱器であ
る。DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIG.
It will be described based on FIG. First, FIG. 1 is a refrigerant circulation system diagram of a cooling and refrigeration apparatus according to the present embodiment. In a refrigeration cycle A, 1 is a compressor that sucks and compresses a low-pressure gaseous refrigerant, and 2 is a high-temperature and high-pressure gaseous refrigerant. A condenser 3 for condensing the refrigerant is a heat receiver for storing a high-temperature and high-pressure liquid refrigerant.
【００２０】そして、この受熱器３に接続された高圧配
管７は、後述する第１および第２蒸発器５ａに流通させ
る冷媒を減圧する膨張弁４に接続されている。この膨張
弁４の下流側は分岐点Ｘで第１蒸発器５ａ側と第２蒸発
器５ｂ側とに分岐される。The high pressure pipe 7 connected to the heat receiver 3 is connected to an expansion valve 4 for reducing the pressure of a refrigerant flowing through first and second evaporators 5a to be described later. The downstream side of the expansion valve 4 is branched at a branch point X into a first evaporator 5a side and a second evaporator 5b side.
【００２１】分岐点Ｘの一方には、車室内の冷房を行な
うための熱交換器としての第１蒸発器５ａが接続されて
いる。また、分岐点Ｘの他方には、冷蔵庫の冷蔵を行な
うための熱交換器としての第２蒸発器５ｂが減圧を行な
う固定絞り部材であるキャピラリチューブ６を介して接
続されている。そして、第１および第２蒸発器５ａ、５
ｂの下流側にそれぞれ接続された低圧配管８は、合流点
Ｙで合流され圧縮機１に接続されている。One of the branch points X is connected to a first evaporator 5a as a heat exchanger for cooling the passenger compartment. A second evaporator 5b as a heat exchanger for refrigeration of the refrigerator is connected to the other end of the branch point X via a capillary tube 6 as a fixed throttle member for reducing the pressure. And, the first and second evaporators 5a, 5
The low-pressure pipes 8 respectively connected to the downstream side of b are joined at a junction Y and connected to the compressor 1.
【００２２】なお、膨張弁４の感温部４ａは、合流点Ｙ
の下流側の冷媒温度を検知するように設置されており、
第１蒸発器５ａ側の冷媒流量を制御するとともに、キャ
ピラリチューブ６を介してさらに減圧して第２蒸発器５
ｂ側にも冷媒流量を制御するものである。また、キャピ
ラリチューブ６は、第１蒸発器５ａ側または第２蒸発器
５ｂ側に流通させる冷媒の流量比と蒸発圧力を制御する
ものであって、冷媒負荷と冷蔵負荷との負荷比率によっ
て予め設定することができため、所定の径と長さに形成
されている。The temperature sensing portion 4a of the expansion valve 4 is connected to the junction Y
It is installed to detect the refrigerant temperature on the downstream side of
In addition to controlling the flow rate of the refrigerant on the first evaporator 5a side, the pressure in the second evaporator 5 is further reduced through the capillary tube 6.
The refrigerant flow is also controlled on the b side. The capillary tube 6 controls the flow ratio and the evaporation pressure of the refrigerant flowing through the first evaporator 5a or the second evaporator 5b, and is set in advance by the load ratio between the refrigerant load and the refrigeration load. Therefore, it is formed in a predetermined diameter and length.
【００２３】次に、以上の構成の冷房冷蔵装置の作動に
ついて説明する。図示しないエンジンの駆動力が伝達さ
れて、圧縮機１が回転すると冷媒が圧縮され、高温高圧
のガス状冷媒を吐出する。このガス状冷媒は、コンデン
サ２で凝縮されて高温高圧の液冷媒となり受液器３に貯
まる。Next, the operation of the cooling and refrigeration apparatus having the above configuration will be described. When a driving force of an engine (not shown) is transmitted and the compressor 1 rotates, the refrigerant is compressed and discharges a high-temperature and high-pressure gaseous refrigerant. This gaseous refrigerant is condensed by the condenser 2, becomes a high-temperature and high-pressure liquid refrigerant, and is stored in the receiver 3.
【００２４】そして、受液器３から高圧配管７を流れた
高温高圧の液冷媒は、膨張弁４より減圧されて低温低圧
の気液２相状態の霧状の冷媒となり、分岐点Ｘの一方の
第１蒸発器５ａ内で気化する。これにより、低温状態と
なった第１蒸発器５ａを通過する空気が冷却され車室内
を冷却、除湿するものである。そして、気化した冷媒は
第１蒸発器５ａから低圧配管８に流出される。The high-temperature and high-pressure liquid refrigerant flowing from the liquid receiver 3 through the high-pressure pipe 7 is reduced in pressure by the expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase mist-like refrigerant. Is vaporized in the first evaporator 5a. As a result, the air passing through the first evaporator 5a in a low temperature state is cooled to cool and dehumidify the vehicle interior. Then, the vaporized refrigerant flows out of the first evaporator 5a to the low-pressure pipe 8.
【００２５】また、分岐点Ｘの他方は、低温低圧の気液
２相状態の霧状の冷媒がさらにキャピラリチューブ６に
よつて減圧されて第２蒸発器５ｂ内で気化する。これに
より、低温状態となった第１蒸発器５ａが冷却されて冷
蔵庫内を冷蔵するものである。At the other end of the branch point X, the low-temperature and low-pressure gas-liquid two-phase mist refrigerant is further decompressed by the capillary tube 6 and vaporized in the second evaporator 5b. As a result, the first evaporator 5a in a low temperature state is cooled to refrigerate the refrigerator.
【００２６】そして、気化した冷媒は第２蒸発器５ａか
ら低圧配管８に流出され、それぞれ合流点Ｙで合流し圧
縮機１に吸入される。膨張弁４の感温部４ａは、合流点
よりも下流に設置されているため、合流する冷媒のスー
パーヒートを膨張弁４により、一定に制御でき、液冷媒
のまま圧縮機１に吸入されることはなく、この圧縮機１
を保護することができる。The vaporized refrigerant flows out of the second evaporator 5a to the low-pressure pipe 8, merges at the merging point Y, and is sucked into the compressor 1. Since the temperature sensing part 4a of the expansion valve 4 is located downstream of the junction, the superheat of the refrigerant to be joined can be controlled to a constant value by the expansion valve 4, and the refrigerant is sucked into the compressor 1 as a liquid refrigerant. This compressor 1
Can be protected.
【００２７】また、第２蒸発器５ｂ側の負荷が大きくな
ったときには、第２蒸発器５ｂ側に流れる冷媒のスーパ
ーヒートが大きくなり、これに伴ない合流点Ｙで合流し
た冷媒のスーパーヒートも大きくなる。膨張弁４はスー
パーヒートの増大に応じて冷媒流量を増大するように調
節するため第１蒸発器５ａの能力が高まり、第２蒸発器
５ｂの能力を補うように車室内の冷房を行なう。When the load on the second evaporator 5b side increases, the superheat of the refrigerant flowing to the second evaporator 5b increases, and the superheat of the refrigerant joined at the junction Y also increases. growing. The expansion valve 4 adjusts the flow rate of the refrigerant in accordance with the increase of the superheat, so that the capacity of the first evaporator 5a is increased, and the interior of the vehicle is cooled so as to supplement the capacity of the second evaporator 5b.
【００２８】また、逆に第２蒸発器５ｂの負荷が小さく
なったときには、第２蒸発器５ｂの出口のスーパーヒー
トが小さくなり、これに伴ない合流した冷媒のスーパー
ヒートも小さくなる。このため膨張弁４が自動的に絞ら
れて、第１蒸発器５ａの能力が下がり、全体的な冷房を
行なわれるものである。Conversely, when the load on the second evaporator 5b is reduced, the superheat at the outlet of the second evaporator 5b is reduced, and the superheat of the joined refrigerant is also reduced accordingly. For this reason, the expansion valve 4 is automatically throttled, the capacity of the first evaporator 5a is reduced, and overall cooling is performed.
【００２９】以上の一実施形態の冷房冷蔵装置によれ
ば、第１、第２蒸発器５ａ、５ｂからの低圧配管８の合
流点Ｙの下流に設置された感温部が検知する冷媒温度に
基づいて膨張弁４が調節されることと、膨張弁４の下流
側にキャピラリチューブ６を介して第２蒸発器５ｂ側に
冷媒循環系とを構成することにより、従来二つの膨張弁
４を設けたものと比較し、格安なキャピラリチューブ６
でできるため、冷蔵側の冷媒循環系の簡素化が可能とな
り低コストが図れる。According to the cooling and refrigerating apparatus of one embodiment described above, the temperature of the refrigerant detected by the temperature-sensing section installed downstream of the junction Y of the low-pressure pipe 8 from the first and second evaporators 5a and 5b is reduced. Conventionally, two expansion valves 4 are provided by adjusting the expansion valve 4 on the basis of the above and by forming a refrigerant circulation system on the second evaporator 5b side via the capillary tube 6 downstream of the expansion valve 4. Capillary tube 6 cheaper than
Therefore, the refrigerant circulation system on the refrigeration side can be simplified, and the cost can be reduced.
【００３０】また、第２蒸発器５ｂ側の冷媒循環系を膨
張弁４およびキャピラリチューブ６によって冷媒流量を
調節することにより、例えば車室の冷房能力に比べて冷
蔵庫の冷蔵能力が小さい冷房冷蔵装置であれば、上記キ
ャピラリチューブ６での減圧特性を予め径および長さを
設定することで、第１蒸発器５ａ側と第２蒸発器５ｂ側
とに冷媒量の分配が可能であるため、従来用いていた電
磁弁を不要とすることができ冷媒循環系をさらに簡素化
ができ安価な構成となる。Further, by controlling the refrigerant flow rate of the refrigerant circulation system on the side of the second evaporator 5b by the expansion valve 4 and the capillary tube 6, for example, a cooling and refrigerating apparatus having a refrigerator with a smaller refrigerating capacity than the cooling capacity of a passenger compartment. Then, by setting the diameter and length of the decompression characteristic in the capillary tube 6 in advance, the amount of refrigerant can be distributed to the first evaporator 5a side and the second evaporator 5b side. The solenoid valve used can be dispensed with, and the refrigerant circulation system can be further simplified, resulting in an inexpensive configuration.
【００３１】また、電磁弁をなくすことで電磁弁の作動
音がなくなり快適性が向上するとともに、電磁弁の開閉
による車室内の吹出口からの吹出空気温度の変動などの
冷房機能への悪影響がなくなり、さらに快適性が向上す
る。In addition, the elimination of the solenoid valve eliminates the operating noise of the solenoid valve and improves comfort, and the opening and closing of the solenoid valve adversely affects the cooling function such as the fluctuation of the temperature of the air blown from the air outlet in the passenger compartment. Disappears and the comfort is further improved.
【００３２】（他の実施形態）以上の一実施形態では、
冷蔵用の第２蒸発器５ａ側にキャピラリチューブ６を固
定絞り部材として用いたがオリフィスなどの固定絞りを
用いても良い。(Other Embodiments) In the above embodiment,
Although the capillary tube 6 is used as a fixed throttle member on the side of the second evaporator 5a for refrigeration, a fixed throttle such as an orifice may be used.
【００３３】また、膨張弁４の感温部４ａを低圧配管８
の合流点Ｙの下流側に設置させた温度式膨張弁を用いた
が、これに限らず、合流点Ｙの下流側の冷媒温度に基づ
いて弁の開度をコンピータで演算し、アクチュエータを
介して調節する電子式膨張弁でも良い。The temperature sensing part 4a of the expansion valve 4 is connected to the low pressure pipe 8
Although the temperature type expansion valve installed downstream of the junction Y was used, the present invention is not limited to this, and the degree of opening of the valve is calculated by a computer based on the refrigerant temperature downstream of the junction Y, and is calculated via an actuator. An electronic expansion valve that adjusts the pressure may be used.
【００３４】また、以上の実施形態では、膨張弁４の感
温部４ａを低圧配管８の合流点Ｙの下流側に設置させ
て、第１蒸発器５ａと第２蒸発器５ｂとの両者のスーパ
ーヒートに基づいて冷媒流量の制御を行なったが、例え
ば冷房用空調ユニット内に併設される缶ジュースなどを
５〜６本ぐらいを収納する小型の冷蔵庫などにおいて
は、言換えれば冷蔵用の第２蒸発器５ｂの冷房能力が第
１蒸発器５ａの冷蔵能力と比べて格段と小さいときに
は、第１蒸発器５ａ側の冷媒が第２蒸発器５ｂ側の冷媒
温度を合流によって高めるために圧縮機に液冷媒を流出
させないため、膨張弁４の感温部４ａを第１蒸発器５ａ
側の下流側に配設しても良い。これにより、上記実施形
態と比べて車室内の冷房負荷に対応した冷媒流量の制御
ができ、第２蒸発器５ｂ側の影響を受けることがない。In the above embodiment, the temperature sensing portion 4a of the expansion valve 4 is installed downstream of the junction Y of the low-pressure pipe 8, so that both the first evaporator 5a and the second evaporator 5b are provided. Although the flow rate of the refrigerant was controlled based on the superheat, for example, in a small refrigerator or the like that stores about 5 to 6 bottles of canned juice or the like provided in the air conditioning unit for cooling, in other words, When the cooling capacity of the second evaporator 5b is significantly smaller than the cooling capacity of the first evaporator 5a, the compressor on the first evaporator 5a side increases the refrigerant temperature on the second evaporator 5b side by merging. In order to prevent the liquid refrigerant from flowing out, the temperature sensing portion 4a of the expansion valve 4 is connected to the first evaporator 5a.
May be arranged on the downstream side. Thus, the flow rate of the refrigerant corresponding to the cooling load in the vehicle compartment can be controlled as compared with the above-described embodiment, and there is no influence on the second evaporator 5b side.
【図１】本発明の一実施形態における冷房冷蔵装置の冷
凍サイクルＡを示す冷媒循環系統図である。FIG. 1 is a refrigerant circulation system diagram showing a refrigeration cycle A of a cooling refrigerator according to an embodiment of the present invention.
【図２】従来技術における冷房冷蔵装置の冷凍サイクル
１００を示す冷媒循環系統図である。FIG. 2 is a refrigerant circulation system diagram showing a refrigeration cycle 100 of a cooling and refrigeration apparatus according to the related art.
３…受液器 ４…膨張弁 ５ａ…第１蒸発器（蒸発器） ５ｂ…第１蒸発器（蒸発器） ６…キャピラリチューブ（固定絞り部材） ７…高圧配管 ８…低圧配管 Ｙ…合流点 DESCRIPTION OF SYMBOLS 3 ... Liquid receiver 4 ... Expansion valve 5a ... 1st evaporator (evaporator) 5b ... 1st evaporator (evaporator) 6 ... Capillary tube (fixed throttle member) 7 ... High pressure piping 8 ... Low pressure piping Y ... Confluence point
Claims (4)
（３）に接続された高圧配管（７）に、二つの蒸発器
（５ａ、５ｂ）を並列に接続された冷房冷蔵装置におい
て、 前記二つの蒸発器（５ａ、５ｂ）のうち、一方の第１蒸
発器（５ａ）が前記高圧配管（７）の下流側に膨張弁
（４）を介して配設され、他方の第２蒸発器（５ｂ）が
前記膨張弁（４）の下流側に減圧用の固定絞り部材
（６）を介して配設されるように構成することを特徴と
する冷房冷蔵装置。1. A cooling and refrigerating apparatus in which two evaporators (5a, 5b) are connected in parallel to a high-pressure pipe (7) connected to a liquid receiver (3) incorporated in a refrigeration cycle. Of the two evaporators (5a, 5b), one first evaporator (5a) is disposed downstream of the high-pressure pipe (7) via an expansion valve (4), and the other second evaporator (5a, 5b). 5b) is arranged downstream of the expansion valve (4) via a fixed pressure reducing member (6) for reducing pressure.
（５ａ）および前記第２蒸発器（５ｂ）の低圧配管
（８）の合流点（Ｙ）の下流側の冷媒温度に基づいて冷
媒流量を制御することを特徴とする請求項１に記載の冷
房冷蔵装置。2. The expansion valve (4) is based on a refrigerant temperature downstream of a junction (Y) of a low-pressure pipe (8) of the first evaporator (5a) and the second evaporator (5b). The cooling and refrigeration apparatus according to claim 1, wherein the flow rate of the refrigerant is controlled by controlling the flow rate of the refrigerant.
（５ａ）よりも前記第２蒸発器（５ｂ）の方が格段と小
さい能力比のときには、前記第１蒸発器（５ａ）の下流
側の冷媒温度に基づいて冷媒流量を制御することを特徴
とする請求項１に記載の冷房冷蔵装置。3. The expansion valve (4), when the second evaporator (5b) has a much smaller capacity ratio than the first evaporator (5a), the first evaporator (5a). The cooling refrigerating apparatus according to claim 1, wherein the flow rate of the refrigerant is controlled based on the temperature of the refrigerant on the downstream side of the cooling medium.
ち、前記第１蒸発器（５ａ）が車室内を冷房するための
熱交換器であり、前記第２蒸発器（５ｂ）が冷蔵庫を冷
蔵するための熱交換器であることを特徴とする請求項１
ないし請求項３のいずれか一項に記載の冷房冷蔵装置。4. The first evaporator (5a) of the two evaporators (5a, 5b) is a heat exchanger for cooling a vehicle interior, and the second evaporator (5b) is a refrigerator. 2. A heat exchanger for refrigeration of the food.
The cooling and refrigeration apparatus according to claim 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001069205A JP2002267285A (en) | 2001-03-12 | 2001-03-12 | Cooler/refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001069205A JP2002267285A (en) | 2001-03-12 | 2001-03-12 | Cooler/refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002267285A true JP2002267285A (en) | 2002-09-18 |
Family
ID=18927270
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001069205A Pending JP2002267285A (en) | 2001-03-12 | 2001-03-12 | Cooler/refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002267285A (en) |
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-
2001
- 2001-03-12 JP JP2001069205A patent/JP2002267285A/en active Pending
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| KR100753522B1 (en) * | 2001-05-15 | 2007-08-30 | 한라공조주식회사 | Air Conditioning System to be able to adjusted Amount of Refrigerants for itself |
| EP2014678A2 (en) | 2002-09-12 | 2009-01-14 | Oncotherapy Science, Inc. | KDR peptides and vaccines comprising the same |
| EP2014679A1 (en) | 2002-09-12 | 2009-01-14 | Oncotherapy Science, Inc. | KDR peptides and vaccines comprising the same |
| EP2261247A2 (en) | 2002-09-12 | 2010-12-15 | Oncotherapy Science, Inc. | KDR peptides and vaccines comprising the same |
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| US8252174B2 (en) | 2008-08-01 | 2012-08-28 | GM Global Technology Operations LLC | Vehicle-integrated water harvesting system |
| CN102954615A (en) * | 2011-08-31 | 2013-03-06 | 杭州三花研究院有限公司 | Electric automobile and heat management system thereof |
| CN102954615B (en) * | 2011-08-31 | 2015-12-09 | 杭州三花研究院有限公司 | Thermal management system of electric automobile and electric automobile |
| CN111609592A (en) * | 2020-04-24 | 2020-09-01 | 珠海格力电器股份有限公司 | Dual-temperature air conditioning system, control method and air conditioner |
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