JPH05141801A - Heat pump type refrigerating plant - Google Patents
Heat pump type refrigerating plantInfo
- Publication number
- JPH05141801A JPH05141801A JP30163691A JP30163691A JPH05141801A JP H05141801 A JPH05141801 A JP H05141801A JP 30163691 A JP30163691 A JP 30163691A JP 30163691 A JP30163691 A JP 30163691A JP H05141801 A JPH05141801 A JP H05141801A
- Authority
- JP
- Japan
- Prior art keywords
- cooling
- pressure liquid
- heating
- cycle operation
- heat exchanger
- 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
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷暖房サイクル運転を
可能としたヒートポンプ式冷凍装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump type refrigerating apparatus capable of performing a heating / cooling cycle operation.
【０００２】[0002]
【従来の技術】従来、この種ヒートポンプ式冷凍装置
は、例えば実公平２−３６０５９号公報に記載され、か
つ、図３で示したように、圧縮機１０１に、冷暖房切換
機構１０２と、利用側熱交換器１０３、冷房用膨張機構
１０４、受液器１０５、暖房用膨張機構１０６、熱源側
熱交換器１０７及びアキュムレータ１０８をそれぞれ接
続して冷媒回路を形成している。また、前記冷房用膨張
機構１０４と暖房用膨張機構１０６には、これら各膨張
機構１０４，１０６を側路する逆止弁１０９，１１０を
並設している。更に、前記受液器１０５のガス域と前記
アキュムレータ１０８との間には、第１開閉弁１１１を
介装した第１均圧回路１１２を設け、また、前記受液器
１０５のガス域と前記暖房用膨張機構１０６及び熱源側
熱交換器１０７の中間部との間には、第２開閉弁１１３
を介装した第２均圧回路１１４を設けている。2. Description of the Related Art Heretofore, a heat pump type refrigerating apparatus of this kind has been described in, for example, Japanese Utility Model Publication No. 2-36059, and as shown in FIG. 3, a compressor 101, a cooling / heating switching mechanism 102, and a user side. The heat exchanger 103, the cooling expansion mechanism 104, the liquid receiver 105, the heating expansion mechanism 106, the heat source side heat exchanger 107, and the accumulator 108 are connected to each other to form a refrigerant circuit. Further, the cooling expansion mechanism 104 and the heating expansion mechanism 106 are provided with check valves 109 and 110, which bypass the expansion mechanisms 104 and 106, respectively. Further, a first pressure equalizing circuit 112 with a first opening / closing valve 111 interposed is provided between the gas region of the liquid receiver 105 and the accumulator 108, and the gas region of the liquid receiver 105 and the The second on-off valve 113 is provided between the heating expansion mechanism 106 and the intermediate portion of the heat source side heat exchanger 107.
The second pressure equalizing circuit 114 is provided.
【０００３】そして、暖房サイクル運転を行う場合は、
図３に点線矢印で示したように、前記冷暖房切換機構１
０２の切換操作により前記圧縮機１０１から吐出される
冷媒を、切換機構１０２、利用側熱交換器１０３、逆止
弁１０９、受液器１０５、暖房用膨張機構１０６、熱源
側熱交換器１０７、切換機構１０２、アキュムレータ１
０８、圧縮機１０１の経路で循環させ、前記利用側熱交
換器１０３での冷媒の凝縮熱を暖房に利用するのであっ
て、前記逆止弁１１０により受液器１０５の高圧液冷媒
が前記暖房用膨張機構１０６をバイパスして流れないよ
うにし、前記受液器１０５の高圧液冷媒を暖房用膨張機
構１０６で減圧して前記熱源側熱交換器１０７へ流して
いる。また、冷房サイクル運転を行う場合は、図３に実
線矢印で示したように、前記冷暖房切換機構１０２の切
換操作により前記圧縮機１０１から吐出される冷媒を、
切換機構１０２、熱源側熱交換器１０７、逆止弁１１
０、受液器１０５、冷房用膨張機構１０４、利用側熱交
換器１０３、切換機構１０２、アキュムレータ１０８、
圧縮機１０１の経路で循環させ、前記利用側熱交換器１
０３での蒸発熱を冷房に利用するのであって、前記逆止
弁１０９により受液器１０５の高圧液冷媒が前記冷房用
膨張機構１０４をバイパスして流れないようにし、前記
受液器１０５の高圧液冷媒を冷房用膨張機構１０４で減
圧して前記利用側熱交換器１０３へ流している。When performing a heating cycle operation,
As shown by a dotted arrow in FIG. 3, the cooling / heating switching mechanism 1
The refrigerant discharged from the compressor 101 by the switching operation of 02 is switched mechanism 102, utilization side heat exchanger 103, check valve 109, liquid receiver 105, heating expansion mechanism 106, heat source side heat exchanger 107, Switching mechanism 102, accumulator 1
08, the heat of condensation of the refrigerant in the use side heat exchanger 103 is circulated in the path of the compressor 101 for heating, and the high-pressure liquid refrigerant in the liquid receiver 105 is heated by the check valve 110. The high-pressure liquid refrigerant in the liquid receiver 105 is decompressed by the heating expansion mechanism 106 and is allowed to flow to the heat source side heat exchanger 107 so as not to flow. Further, when the cooling cycle operation is performed, the refrigerant discharged from the compressor 101 by the switching operation of the cooling / heating switching mechanism 102, as indicated by the solid arrow in FIG.
Switching mechanism 102, heat source side heat exchanger 107, check valve 11
0, liquid receiver 105, cooling expansion mechanism 104, utilization side heat exchanger 103, switching mechanism 102, accumulator 108,
It is circulated in the path of the compressor 101, and the use side heat exchanger 1
The heat of vaporization in 03 is used for cooling, and the check valve 109 prevents the high-pressure liquid refrigerant in the liquid receiver 105 from flowing by bypassing the cooling expansion mechanism 104. The high-pressure liquid refrigerant is decompressed by the cooling expansion mechanism 104 and is flown to the use side heat exchanger 103.
【０００４】[0004]
【発明が解決しようとする課題】所が、以上の如く構成
するヒートポンプ式冷凍装置において、逆止弁１０９，
１１０を介装するバイパス路は、冷房用膨張機構１０４
及び暖房用膨張機構１０６を介装した液管に、前記各膨
張機構を側路するように設けており、従って、前記バイ
パス路には、冷房及び暖房サイクルの何れの運転時で
も、高圧液冷媒が流入しているのであり、また、この高
圧液冷媒が逆止弁１０９，１１０で閉鎖されるようにな
っているのである。However, in the heat pump type refrigerating apparatus configured as described above, the check valve 109,
The bypass path provided with 110 is the cooling expansion mechanism 104.
Further, the expansion pipes for heating and the heating expansion mechanism 106 are provided in the liquid pipe so as to bypass each of the expansion mechanisms. Therefore, the bypass passage is provided with a high-pressure liquid refrigerant in both cooling and heating cycles. Is flowing in, and the high-pressure liquid refrigerant is closed by the check valves 109 and 110.
【０００５】また、前記逆止弁１０９，１１０の一方側
は前記高圧液冷媒が作用しているのに対し、他方側は、
前記各膨張機構１０４，１０６で減圧された低圧液冷媒
が作用しているため、一方側と他方側との間には圧力差
があり、また、逆止弁１０９，１１０における塵芥等の
かみ込みにより前記高圧液冷媒が低圧側にリークするこ
とになるのである。The high-pressure liquid refrigerant acts on one side of the check valves 109 and 110, while the other side
Since the low-pressure liquid refrigerant decompressed by the expansion mechanisms 104 and 106 acts, there is a pressure difference between the one side and the other side, and dust such as dust is caught in the check valves 109 and 110. As a result, the high pressure liquid refrigerant leaks to the low pressure side.
【０００６】一方、冷暖房サイクル運転において、蒸発
器となる利用側又は熱源側熱交換器１０３，１０７の出
口側における過熱度は前記各膨張機構１０４，１０６の
絞り調整により制御されている。所が、前記したように
逆止弁１０９，１１０にリークがある場合、前記各膨張
機構１０４，１０４による絞り調節範囲内のリークであ
れば特に問題はないが、その調整範囲を越えてリークが
ある場合、前記リークが液冷媒であることから、湿り運
転となり圧縮機に液バックが生じ、この液バックにより
前記圧縮機１０１の破損事故を起こしたり、湿り運転に
よる油上がり及び潤滑不良を発生したりする問題があっ
た。On the other hand, in the cooling / heating cycle operation, the degree of superheat on the outlet side of the heat exchangers 103, 107 on the utilization side or the heat source side, which serves as an evaporator, is controlled by adjusting the throttles of the expansion mechanisms 104, 106. However, if there is a leak in the check valves 109 and 110 as described above, there is no particular problem as long as it is a leak within the throttle adjustment range by the expansion mechanisms 104 and 104, but there is a leak beyond the adjustment range. In some cases, since the leak is a liquid refrigerant, a wet operation is performed and a liquid back is generated in the compressor. This liquid back causes a damage accident of the compressor 101, and oil rise and poor lubrication due to the wet operation occur. There was a problem with.
【０００７】更に、以上のような冷暖房サイクル運転時
に、ポンプダウン運転を行う場合には、前記冷暖房用膨
張機構１０４，１０６を閉鎖し、かつ、前記第１，第２
開閉弁１１１，１１３を開放させて、前記受液器１０５
のガス域に貯溜されるガス冷媒を前記第１，第２均圧回
路１１２，１１４へと流すのであるが、このとき、前記
各逆止弁１０９，１１０を介して前記受液器１０５内の
高圧液冷媒がリークすると、ポンプダウン運転が行えな
くなる問題もあった。Further, when the pump-down operation is performed during the cooling / heating cycle operation as described above, the cooling / heating expansion mechanisms 104 and 106 are closed, and the first and second expansion mechanisms are closed.
The on-off valves 111 and 113 are opened and the liquid receiver 105 is opened.
The gas refrigerant stored in the gas region is flown to the first and second pressure equalizing circuits 112 and 114. At this time, the gas refrigerant in the liquid receiver 105 is passed through the check valves 109 and 110. If the high-pressure liquid refrigerant leaks, there is also a problem that the pump down operation cannot be performed.
【０００８】本発明は以上のような問題に鑑みてなした
もので、その目的は、冷暖房サイクル運転時圧縮機側へ
の液バックを阻止して、該圧縮機の破損事故や湿り運転
による油上がり及び潤滑不良を防止することができ、し
かも、ポンプダウン運転を確実に行うことができるヒー
トポンプ式冷凍装置を提供することにある。The present invention has been made in view of the above problems, and an object thereof is to prevent liquid back to the compressor side during the heating / cooling cycle operation, and to prevent oil from accidental damage or wet operation of the compressor. It is an object of the present invention to provide a heat pump type refrigerating apparatus which can prevent rising and poor lubrication and can reliably perform pump down operation.
【０００９】[0009]
【課題を解決するための手段】上記目的を達成するた
め、本発明では、圧縮機１、冷暖房切換機構２、利用側
熱交換器３、受液器５、冷房用膨張機構４、暖房用膨張
機構６及び熱源側熱交換器７を備え、冷暖房サイクル運
転を可能としたヒートポンプ式冷凍装置において、一端
側が暖房サイクル運転時高圧液冷媒が流れる高圧液域に
接続され、途中に暖房サイクル運転時の高圧液冷媒の流
れを許容する逆止弁１４をもち、かつ、前記冷房用膨張
機構４を側路する第１バイパス路１５と、一端側が冷房
サイクル運転時高圧液冷媒が流れる高圧液域に接続さ
れ、途中に冷房サイクル運転時の高圧液冷媒の流れを許
容する逆止弁１６をもち、かつ、前記暖房用膨張機構６
を側路する第２バイパス路１７との各他端側を、前記受
液器５のガス域に接続したものである。In order to achieve the above object, in the present invention, a compressor 1, a cooling / heating switching mechanism 2, a use side heat exchanger 3, a liquid receiver 5, a cooling expansion mechanism 4, a heating expansion are provided. In a heat pump type refrigerating apparatus including a mechanism 6 and a heat source side heat exchanger 7, which enables a heating / cooling cycle operation, one end side is connected to a high pressure liquid region in which a high pressure liquid refrigerant flows during a heating cycle operation, A first bypass passage 15 having a check valve 14 for allowing the flow of the high-pressure liquid refrigerant and shunting the cooling expansion mechanism 4, and one end side thereof connected to a high-pressure liquid region through which the high-pressure liquid refrigerant flows during a cooling cycle operation. The heating expansion mechanism 6 has a check valve 16 for allowing the flow of the high-pressure liquid refrigerant during the cooling cycle operation in the middle thereof.
The other end side of each of the second bypass passages 17 that bypasses is connected to the gas region of the liquid receiver 5.
【００１０】また、前記利用側熱交換器３は、冷房サイ
クル運転時低圧液室となり暖房サイクル運転時高圧液室
となる出入口室３６をもち、該出入口室３６に熱交換チ
ューブ３３を開口させると共に、前記出入口室３６に冷
房サイクル運転時低圧液管となる冷媒配管９１を、前記
出入口室３６の底面に対し上方に突出状で、かつ、突出
先端部が前記熱交換チューブ３３の開口側に向かって傾
斜状に開口させる一方、前記冷房用膨張機構４を側路す
る第１バイパス路１５の一端側を前記出入口室３６に、
該出入口室３６に開口する最下段の熱交換チューブ３３
より下方に開口させることが好ましい。Further, the utilization side heat exchanger 3 has an inlet / outlet chamber 36 which serves as a low pressure liquid chamber during the cooling cycle operation and serves as a high pressure liquid chamber during the heating cycle operation, and the heat exchange tube 33 is opened in the inlet / outlet chamber 36. A refrigerant pipe 91 serving as a low-pressure liquid pipe during the cooling cycle operation is provided in the inlet / outlet chamber 36 so as to project upward with respect to the bottom surface of the inlet / outlet chamber 36, and the protruding tip end faces the opening side of the heat exchange tube 33. While opening in a tilted manner, one end side of the first bypass passage 15 that bypasses the cooling expansion mechanism 4 is provided in the inlet / outlet chamber 36,
The lowermost heat exchange tube 33 opening to the entrance / exit chamber 36
It is preferable to open it further downward.
【００１１】[0011]
【作用】冷房サイクル運転時、熱源側熱交換器７で凝縮
した液冷媒は、前記第２バイパス路１７及び逆止弁１６
を介して暖房用膨張機構６を側路して受液器５に流れ、
該受液器５の液冷媒は冷房用膨張機構４を介して利用側
熱交換器３に流れるのであるが、このとき、前記冷房用
膨張機構４を側路する第１バイパス路１５は、前記受液
器５のガス域に接続されているから、前記第１バイパス
路１５には高圧ガス冷媒が導入され、この高圧ガス冷媒
の流れが前記第１バイパス路１５に介装する逆止弁１４
により閉鎖されることになるのであり、従って、この逆
止弁１４から高低差圧によりリークするとしても、ガス
冷媒がリークすることになるのである。In the cooling cycle operation, the liquid refrigerant condensed in the heat source side heat exchanger 7 is used as the second bypass passage 17 and the check valve 16.
Flow through the heating expansion mechanism 6 to the liquid receiver 5 via
The liquid refrigerant of the liquid receiver 5 flows to the utilization side heat exchanger 3 via the cooling expansion mechanism 4, and at this time, the first bypass passage 15 bypassing the cooling expansion mechanism 4 is Since it is connected to the gas region of the liquid receiver 5, high-pressure gas refrigerant is introduced into the first bypass passage 15, and the flow of this high-pressure gas refrigerant is inserted in the first bypass passage 15 to the check valve 14.
Therefore, even if the check valve 14 leaks due to the high and low differential pressure, the gas refrigerant will leak.
【００１２】また、暖房サイクル運転時も同様、前記暖
房用膨張機構６を側路する第２バイパス路１７には、高
圧ガス冷媒が導入され、この高圧ガス冷媒の流れが前記
第２バイパス路１７に介装する逆止弁１６により閉鎖さ
れることになるのであって、前記逆止弁１６からリーク
があっても、ガス冷媒がリークすることになる。つま
り、前記第１，第２バイパス路１５，１７は前記受液器
５のガス域に接続されているため、前記受液器５の高圧
液冷媒ではなくガス域に貯溜されたガス冷媒が、前記利
用側熱交換器３又は熱源側熱交換器７側へリークするこ
とになる。従って、能力は多少低下するとしてもリーク
による前記圧縮機１側への液バックが阻止され、この結
果、該圧縮機１側への液バックによる破損事故や湿り運
転による油上がり及び潤滑不良が防止される。Also during the heating cycle operation, similarly, the high-pressure gas refrigerant is introduced into the second bypass passage 17 that bypasses the heating expansion mechanism 6, and the flow of this high-pressure gas refrigerant is the second bypass passage 17. It is closed by the check valve 16 provided in the valve, and even if there is a leak from the check valve 16, the gas refrigerant will leak. That is, since the first and second bypass passages 15 and 17 are connected to the gas region of the liquid receiver 5, not the high-pressure liquid refrigerant of the liquid receiver 5, but the gas refrigerant stored in the gas region, It leaks to the use side heat exchanger 3 or the heat source side heat exchanger 7. Therefore, even if the capacity is slightly reduced, liquid back to the compressor 1 side due to leakage is prevented, and as a result, damage accidents due to liquid back to the compressor 1 side and oil rise and poor lubrication due to wet operation are prevented. To be done.
【００１３】更に、以上の如く行う冷暖房サイクル運転
時においてポンプダウン運転を行う場合、前記逆止弁１
４，１６を介して前記受液器５のガス域に貯溜されたガ
ス冷媒が前記利用側熱交換器３又は前記熱源側熱交換器
７側へリークしても、前記受液器５の高圧液冷媒は前記
逆止弁１４，１６を介してリークすることができないた
め、ポンプダウン運転を確実に行うことができる。Further, when the pump down operation is performed during the cooling / heating cycle operation performed as described above, the check valve 1 is used.
Even if the gas refrigerant stored in the gas region of the liquid receiver 5 leaks to the use-side heat exchanger 3 or the heat-source-side heat exchanger 7 via 4 and 16, the high pressure of the liquid receiver 5 Since the liquid refrigerant cannot leak through the check valves 14 and 16, the pump down operation can be reliably performed.
【００１４】また、前記利用側熱交換器３に、冷房サイ
クル運転時低圧液室となり暖房サイクル運転時高圧液室
となる出入口室３６を設け、該出入口室３６に熱交換チ
ューブ３３を開口させると共に、前記出入口室３６に冷
房サイクル運転時低圧液管となる冷媒配管９１を、前記
出入口室３６の底面に対し上方に突出させ、かつ、突出
先端部を前記熱交換チューブ３３の開口側に向かって傾
斜状に開口させる一方、前記冷房用膨張機構４を側路す
る前記第１バイパス路１５の一端側を前記出入口室３６
に、該出入口室３６に開口する最下段の熱交換チューブ
３３より下方に開口させるときには、冷房サイクル運転
時に、前記冷媒配管９１から前記出入口室３６に導入さ
れる低圧液冷媒を前記各熱交換チューブ３３に均一に分
配して、熱交換効率を高めることができ、また、暖房サ
イクル運転時には、前記出入口室３６から高圧液冷媒の
全量を前記第１バイパス路１５に速やかに流出させるこ
とができる。Further, the use side heat exchanger 3 is provided with an inlet / outlet chamber 36 which serves as a low pressure liquid chamber during a cooling cycle operation and serves as a high pressure liquid chamber during a heating cycle operation, and the heat exchange tube 33 is opened in the inlet / outlet chamber 36. A refrigerant pipe 91, which is a low-pressure liquid pipe during a cooling cycle operation, is projected in the inlet / outlet chamber 36 upward with respect to the bottom surface of the inlet / outlet chamber 36, and a protruding tip portion is directed toward the opening side of the heat exchange tube 33. While opening in an inclined shape, one end side of the first bypass passage 15 that bypasses the cooling expansion mechanism 4 is connected to the inlet / outlet chamber 36.
In addition, when opening below the lowermost heat exchange tube 33 that opens into the inlet / outlet chamber 36, the low-pressure liquid refrigerant introduced from the refrigerant pipe 91 into the inlet / outlet chamber 36 during the cooling cycle operation is transferred to each of the heat exchange tubes. It is possible to evenly distribute the high-pressure liquid refrigerant to the first bypass passage 15 during the heating cycle operation.
【００１５】[0015]
【実施例】図１に示したヒートポンプ式冷凍装置は、圧
縮機１に、４路切換弁から成る冷暖房切換機構２と、水
熱交換器から成る利用側熱交換器３、冷房用膨張機構
４、受液器５、暖房用膨張機構６、空気熱交換器から成
る熱源側熱交換器７及びアキュムレータ８をそれぞれ冷
媒配管９で接続することにより、冷媒回路を形成してい
る。また、前記受液器５のガス域と前記アキュムレータ
８との間には、第１開閉弁１０を介装させた第１均圧回
路１１を接続すると共に、前記受液器５のガス域と、前
記暖房用膨張機構６及び熱源側熱交換器７を結ぶ冷媒配
管中間との間には、第２開閉弁１２を介装した第２均圧
回路１３を接続している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In the heat pump type refrigerating apparatus shown in FIG. 1, a compressor 1 is provided with a cooling / heating switching mechanism 2 consisting of a four-way switching valve, a utilization side heat exchanger 3 consisting of a water heat exchanger, and a cooling expansion mechanism 4. A refrigerant circuit is formed by connecting the liquid receiver 5, the heating expansion mechanism 6, the heat source side heat exchanger 7 including an air heat exchanger, and the accumulator 8 with a refrigerant pipe 9. Further, a first pressure equalizing circuit 11 having a first opening / closing valve 10 interposed is connected between the gas region of the liquid receiver 5 and the accumulator 8, and the gas region of the liquid receiver 5 is connected to the first pressure equalizing circuit 11. A second pressure equalizing circuit 13 having a second opening / closing valve 12 is connected between the heating expansion mechanism 6 and the refrigerant pipe intermediate connecting the heat source side heat exchanger 7.
【００１６】更に、前記冷房用膨張機構４は、弁開度を
電気的に制御する電動弁から成り、制御器４３からの出
力で電動弁の開度を調節できるようにしているのであっ
て、前記制御器４３は、前記利用側熱交換器３における
冷房サイクル運転時の出口側に介装した温度検出器４１
及び圧力検出器４２の検出結果に基づき動作するのであ
る。また、前記暖房用膨張機構６も、弁開度を電気的に
制御する電動弁から成り、制御器６３からの出力で電動
弁の開度を調節できるようにしているのであって、前記
制御器６３は、前記熱源側熱交換器７における暖房サイ
クル運転時の出口側に介装した温度検出器６１及び圧力
検出器６２の検出結果に基づき動作するのである。Further, the cooling expansion mechanism 4 is composed of an electric valve for electrically controlling the valve opening, and the opening of the electric valve can be adjusted by the output from the controller 43. The controller 43 is a temperature detector 41 provided on the outlet side of the utilization side heat exchanger 3 during the cooling cycle operation.
And, it operates based on the detection result of the pressure detector 42. Further, the heating expansion mechanism 6 is also composed of a motor-operated valve that electrically controls the valve opening, and the output of the controller 63 allows the opening of the motor-operated valve to be adjusted. 63 operates based on the detection results of the temperature detector 61 and the pressure detector 62 which are provided on the outlet side of the heat source side heat exchanger 7 during the heating cycle operation.
【００１７】また、前記利用側熱交換器３はシェルアン
ドチューブ式熱交換器を用い、その胴体には冷温水管
（図示せず）を接続しており、また、前記熱源側熱交換
器７は、ファンコイル熱交換器を用い、その一側にはモ
ータ７１を備えたファン７２を付設している。更に、前
記アキュムレータ８は、筒状の密閉容器８１を備え、該
容器８１の内方上部側に短寸の冷媒流入管８２と、油戻
し孔８３及びガス吸入孔８４をもつＵ字管から成る冷媒
流出管８５とを設けている。A shell-and-tube heat exchanger is used as the utilization side heat exchanger 3, a cold / hot water pipe (not shown) is connected to its body, and the heat source side heat exchanger 7 is A fan coil heat exchanger is used, and a fan 72 equipped with a motor 71 is attached to one side thereof. Further, the accumulator 8 is provided with a cylindrical hermetic container 81, and is composed of a U-shaped pipe having a short refrigerant inflow pipe 82, an oil return hole 83 and a gas suction hole 84 on the upper inner side of the container 81. A refrigerant outflow pipe 85 is provided.
【００１８】しかして以上のようなヒートポンプ式冷凍
装置において、暖房サイクル運転時に高圧液冷媒が流れ
る高圧液域と前記受液器５のガス域との間に、前記冷房
用膨張機構４を側路するように、途中に暖房サイクル運
転時の高圧液冷媒の流れを許容する逆止弁１４が介装さ
れた第１バイパス路１５を設けると共に、冷房サイクル
運転時に高圧液冷媒が流れる高圧液域と前記受液器５の
ガス域との間に、前記暖房用膨張機構６を側路するよう
に、途中に冷房サイクル運転時の高圧液冷媒の流れを許
容する逆止弁１６が介装された第２バイパス路１７を設
ける。In the heat pump type refrigerating apparatus as described above, the cooling expansion mechanism 4 is bypassed between the high pressure liquid region in which the high pressure liquid refrigerant flows and the gas region of the liquid receiver 5 during the heating cycle operation. As described above, the first bypass passage 15 in which the check valve 14 that allows the flow of the high-pressure liquid refrigerant during the heating cycle operation is interposed is provided in the middle, and a high-pressure liquid region in which the high-pressure liquid refrigerant flows during the cooling cycle operation is provided. A check valve 16 that allows the flow of the high-pressure liquid refrigerant during the cooling cycle operation is provided in the middle of the space between the gas region of the liquid receiver 5 and the expansion mechanism 6 for heating. A second bypass path 17 is provided.
【００１９】具体的には、前記第１バイパス路１５の長
さ方向一端を、後で詳述する前記利用側熱交換器３の出
入口室３１に、また、前記第２バイパス路１７の長さ方
向一端を、前記熱源側熱交換器７における冷房サイクル
運転時の冷媒出口側にそれぞれ接続して、これら第１及
び第２バイパス路１５，１７の長さ方向他端を前記受液
器５のガス域に接続させる。Specifically, one end in the length direction of the first bypass passage 15 is provided in the inlet / outlet chamber 31 of the utilization side heat exchanger 3 which will be described in detail later, and the length of the second bypass passage 17 is also provided. One end in the direction is connected to the refrigerant outlet side in the cooling cycle operation of the heat source side heat exchanger 7, and the other lengthwise ends of the first and second bypass passages 15 and 17 are connected to the receiver 5. Connect to gas area.
【００２０】次に、以上の構成としたヒートポンプ式冷
凍装置の作用について説明する。先ず、暖房サイクル運
転を行う場合には、図１に点線矢印で示したように、前
記冷暖房切換機構２の切換操作により前記圧縮機１から
吐出される冷媒が、切換機構２、利用側熱交換器３、逆
止弁１４を介装した第１バイパス路１５、受液器５、暖
房用膨張機構６、熱源側熱交換器７、切換機構２、アキ
ュムレータ８及び圧縮機１の経路で循環するのであっ
て、前記受液器５の高圧液冷媒を前記暖房用膨張機構６
で減圧し、減圧した液冷媒を前記熱源側熱交換器７で蒸
発させ、この蒸発により熱を吸収し、この吸収熱を前記
利用側熱交換器３から凝縮熱として取り出し暖房に利用
される。また、冷房サイクル運転時には、前記冷暖房切
換機構２の切換操作により前記圧縮機１から吐出される
冷媒が、図１に実線矢印で示したように、切換機構２、
熱源側熱交換器７、逆止弁１６を介装した第２バイパス
路１７、受液器５、冷房用膨張機構４、利用側熱交換器
３、切換機構２、アキュムレータ８及び圧縮機１の経路
で循環するのであって、前記受液器５の高圧液冷媒を前
記冷房用膨張機構４で減圧し、減圧した液冷媒を前記利
用側熱交換器３で蒸発させ、この蒸発熱が冷房に利用さ
れる。Next, the operation of the heat pump type refrigerating apparatus having the above structure will be described. First, when the heating cycle operation is performed, the refrigerant discharged from the compressor 1 by the switching operation of the cooling / heating switching mechanism 2 is the switching mechanism 2 and the heat exchange on the use side, as shown by the dotted arrow in FIG. It circulates through the path of the device 3, the first bypass passage 15 with the check valve 14 interposed, the liquid receiver 5, the heating expansion mechanism 6, the heat source side heat exchanger 7, the switching mechanism 2, the accumulator 8 and the compressor 1. Therefore, the high pressure liquid refrigerant in the liquid receiver 5 is transferred to the heating expansion mechanism 6
The heat source-side heat exchanger 7 evaporates the depressurized liquid refrigerant, absorbs heat by this evaporation, and the absorbed heat is taken out from the use-side heat exchanger 3 as condensation heat and used for heating. Further, during the cooling cycle operation, the refrigerant discharged from the compressor 1 by the switching operation of the cooling / heating switching mechanism 2 is switched by the switching mechanism 2, as indicated by a solid arrow in FIG.
Of the heat source side heat exchanger 7, the second bypass passage 17 with the check valve 16 interposed, the liquid receiver 5, the cooling expansion mechanism 4, the utilization side heat exchanger 3, the switching mechanism 2, the accumulator 8 and the compressor 1. The high-pressure liquid refrigerant in the liquid receiver 5 is depressurized by the cooling expansion mechanism 4, and the depressurized liquid refrigerant is evaporated by the use side heat exchanger 3, and the heat of evaporation is cooled. Used.
【００２１】そして、以上の暖房サイクル運転時に、前
記受液器５から冷媒が前記第２バイパス路１７に介装し
た前記逆止弁１６を介して前記熱源側熱交換器７側へリ
ークしたり、また、冷房サイクル運転時に、前記受液器
５から冷媒が前記第１バイパス路１５に介装した前記逆
止弁１４を介して前記利用側熱交換器３側へリークした
りする場合、前記第１，第２バイパス路１５，１７は前
記受液器５のガス域に接続されているため、前記受液器
５の高圧液冷媒ではなくガス域に貯溜されたガス冷媒
が、前記利用側熱交換器３又は熱源側熱交換器７側へリ
ークすることになる。従って、冷暖房サイクル運転時リ
ークがあっても、能力が多少低下するだけであって前記
圧縮機１側への液バックが阻止され湿り運転も阻止され
る。この結果、前記圧縮機１側への液バックによる圧縮
機１の破損事故を防止することができるし、又湿り運転
も防止でき、例えば圧縮機１内における冷媒のフォーミ
ングをなくして油上がりや潤滑不良の発生を防止するこ
とができる。During the above heating cycle operation, the refrigerant leaks from the liquid receiver 5 to the heat source side heat exchanger 7 side through the check valve 16 provided in the second bypass passage 17. In the cooling cycle operation, when the refrigerant leaks from the liquid receiver 5 to the utilization side heat exchanger 3 side through the check valve 14 provided in the first bypass passage 15, Since the first and second bypass passages 15 and 17 are connected to the gas region of the liquid receiver 5, not the high-pressure liquid refrigerant of the liquid receiver 5 but the gas refrigerant stored in the gas region is the use side. It will leak to the heat exchanger 3 or the heat source side heat exchanger 7. Therefore, even if there is a leak during the heating / cooling cycle operation, the capacity is only slightly decreased, the liquid back to the compressor 1 side is blocked, and the wet operation is also blocked. As a result, it is possible to prevent the accident of damage to the compressor 1 due to the liquid back to the compressor 1 side, and also to prevent the wet operation. It is possible to prevent the occurrence of defects.
【００２２】また、各逆止弁１４，１６を介して前記受
液器５のガス域に貯溜されたガス冷媒が前記利用側熱交
換器３又は熱源側熱交換器７側へリークするときには、
そのリーク発生を前記圧縮機１側への液バックによる機
械故障ではなく、前記利用側熱交換器３又は熱源側熱交
換器７の能力ダウンで検出することができ、従って、前
記圧縮機１の破損事故が発生してから逆止弁１４，１６
を修理したり取り替えたりするようなことなく、能力ダ
ウンをもとに保守を行うことができる。Further, when the gas refrigerant stored in the gas region of the liquid receiver 5 leaks to the utilization side heat exchanger 3 or the heat source side heat exchanger 7 side via the check valves 14 and 16,
The occurrence of the leak can be detected not by a mechanical failure due to liquid back to the compressor 1 side but by a reduction in the capacity of the use side heat exchanger 3 or the heat source side heat exchanger 7, and therefore, the compressor 1 Check valves 14 and 16 after the damage accident
It is possible to perform maintenance based on a reduction in capacity without repairing or replacing.
【００２３】更に、前記各逆止弁１４，１６を介して前
記受液器５のガス域に貯溜されたガス冷媒が前記利用側
熱交換器３又は熱源側熱交換器７側へリークする場合、
高圧液冷媒がリークする場合に比較して前記アキュムレ
ータ８側への液戻り量を少なくでき、該アキュムレータ
８の小形化も可能となる。Further, when the gas refrigerant stored in the gas region of the liquid receiver 5 leaks to the use side heat exchanger 3 or the heat source side heat exchanger 7 side via the check valves 14 and 16 respectively. ,
The amount of liquid returned to the accumulator 8 side can be reduced as compared with the case where the high-pressure liquid refrigerant leaks, and the accumulator 8 can be downsized.
【００２４】また、以上のような冷暖房サイクル運転時
に、ポンプダウン運転を行う場合には、前記冷暖房用膨
張機構４，６を閉鎖し、かつ、前記第１及び第２均圧回
路１１，１３に介装させた各開閉弁１０，１２を開放さ
せて、前記受液器５のガス域に貯溜されるガス冷媒を前
記第１，第２均圧回路１１，１３へと流すことにより行
うのであるが、このとき、前記逆止弁１４，１６を介し
て前記受液器５のガス域に貯溜されたガス冷媒が前記利
用側熱交換器３又は前記熱源側熱交換器７側へリークし
ても、前記受液器５から高圧液冷媒が前記逆止弁１４，
１６を介してリークできないため、高圧液冷媒がリーク
する場合に比較してポンプダウン運転に大きく悪影響を
与えることがなく、このポンプダウン運転を確実に行う
ことができる。When the pump down operation is performed during the cooling / heating cycle operation as described above, the cooling / heating expansion mechanisms 4 and 6 are closed, and the first and second pressure equalizing circuits 11 and 13 are connected. This is done by opening the on-off valves 10 and 12 that have been interposed, and flowing the gas refrigerant stored in the gas region of the liquid receiver 5 to the first and second pressure equalizing circuits 11 and 13. However, at this time, the gas refrigerant stored in the gas region of the liquid receiver 5 leaks to the use side heat exchanger 3 or the heat source side heat exchanger 7 side via the check valves 14 and 16. Also, the high-pressure liquid refrigerant from the liquid receiver 5 is transferred to the check valve 14,
Since the leak cannot occur via 16, the pump down operation can be reliably performed without significantly affecting the pump down operation as compared with the case where the high pressure liquid refrigerant leaks.
【００２５】尚、図１に示した実施例では、前記第１バ
イパス路１５の長さ方向一端を、前記利用側熱交換器３
の前記出入口室３１に接続したが、暖房サイクル運転時
高圧液冷媒が流れる高圧液域となる前記利用側熱交換器
３と前記冷房用膨張機構４との中間部位に接続してもよ
い。In the embodiment shown in FIG. 1, one end in the lengthwise direction of the first bypass passage 15 is connected to the use side heat exchanger 3
Although it is connected to the inlet / outlet chamber 31 of the above, it may be connected to an intermediate portion between the use side heat exchanger 3 and the cooling expansion mechanism 4 which is a high pressure liquid region in which the high pressure liquid refrigerant flows during the heating cycle operation.
【００２６】更に、前記利用側熱交換器３は、図２に示
したように、両側が開放された中空筒部３１と、該筒部
３１の開放部に取付けられる蓋部３２とを備え、これら
筒部３１と蓋部３２との間に複数の熱交換チューブ３３
を支持する管板３４を介装させて、該管板３４で前記蓋
部３２を筒部３１に対し気密状に画成すると共に、前記
蓋部３２内に仕切板３５を設けて、この仕切板３５で前
記蓋部３２の内部を上下に画成し、その下部側に冷房サ
イクル運転時に低圧ガス室となり、かつ、暖房サイクル
運転時に高圧ガス室となる第１出入口室３６を形成する
一方、前記蓋部３２の内方上部側に、暖房サイクル運転
時に高圧ガス室となり、かつ、冷房サイクル運転時に低
圧ガス室となる第２出入口室３７を形成して、これら各
出入口室３６，３７に前記各熱交換チューブ３３の一端
を開口させている。Further, as shown in FIG. 2, the utilization side heat exchanger 3 is provided with a hollow cylindrical portion 31 whose both sides are open, and a lid portion 32 attached to the open portion of the cylindrical portion 31, A plurality of heat exchange tubes 33 are provided between the tubular portion 31 and the lid portion 32.
A tube plate 34 for supporting the above is interposed, the tube portion 34 defines the lid portion 32 in an airtight manner with respect to the tubular portion 31, and a partition plate 35 is provided in the lid portion 32 to form a partition plate. A plate 35 vertically defines the inside of the lid portion 32, and forms a first inlet / outlet chamber 36 on the lower side thereof, which serves as a low-pressure gas chamber during a cooling cycle operation and serves as a high-pressure gas chamber during a heating cycle operation. A second inlet / outlet chamber 37, which serves as a high-pressure gas chamber during the heating cycle operation and serves as a low-pressure gas chamber during the cooling cycle operation, is formed on the inner upper side of the lid portion 32, and the inlet / outlet chambers 36, 37 are provided with One end of each heat exchange tube 33 is opened.
【００２７】また、前記蓋部３２に形成する第１出入口
室３６には、前記冷房用膨張機構４から延び冷房サイク
ル運転時に低圧液管となる冷媒配管９１と、前記冷房用
膨張機構４を側路し前記逆止弁１４が介装された前記第
１バイパス路１５とのそれぞれ長さ方向一端側を接続さ
せると共に、前記蓋部３２の第２出入口室３７には、前
記冷暖房切換機構２側に至り冷房サイクル運転時に低圧
ガス管となる冷媒配管９２の長さ方向一端側を接続させ
ている。The first inlet / outlet chamber 36 formed in the lid 32 is provided with a refrigerant pipe 91 extending from the cooling expansion mechanism 4 and serving as a low pressure liquid pipe during a cooling cycle operation, and the cooling expansion mechanism 4 side. The first bypass passage 15 in which the check valve 14 is interposed is connected to one end side in the length direction, and the second inlet / outlet chamber 37 of the lid portion 32 is provided with the cooling / heating switching mechanism 2 side. Thus, one end side in the length direction of the refrigerant pipe 92 that serves as a low pressure gas pipe during the cooling cycle operation is connected.
【００２８】そして、前記第１出入口室３６に前記冷媒
配管９１と第１バイパス路１５とを接続するに際して、
前記冷媒配管９１を、前記出入口室３６の底壁面に対し
上方側に突出させ、かつ、突出先端部を前記熱交換チュ
ーブ３３の開口側に向かって傾斜状に開口させ、また、
前記第１バイパス路１５を、前記出入口室３６に開口さ
れる最下段の熱交換チューブ３３よりも下方位置に開口
させるのである。When connecting the refrigerant pipe 91 and the first bypass passage 15 to the first inlet / outlet chamber 36,
The refrigerant pipe 91 is projected upward with respect to the bottom wall surface of the inlet / outlet chamber 36, and the protruding tip portion is opened in an inclined shape toward the opening side of the heat exchange tube 33.
The first bypass passage 15 is opened at a position lower than the lowermost heat exchange tube 33 opened in the inlet / outlet chamber 36.
【００２９】以上の配管構成とすることにより、冷房サ
イクル運転時には、前記冷媒配管９１から前記出入口室
３６に導入される低圧液冷媒が、図２で示したように、
該出入口室３６に開口される前記各熱交換チューブ３３
の上部側から下部側にかけ均一に分配されて、熱交換効
率が高められ、また、暖房サイクル運転時には、前記出
入口室３６から高圧液冷媒の全量が前記第１バイパス路
１５側に速やかに流出することができる。With the above piping configuration, the low-pressure liquid refrigerant introduced from the refrigerant piping 91 into the inlet / outlet chamber 36 during the cooling cycle operation is as shown in FIG.
Each heat exchange tube 33 opened to the inlet / outlet chamber 36
Is evenly distributed from the upper side to the lower side, the heat exchange efficiency is enhanced, and during the heating cycle operation, the entire amount of the high-pressure liquid refrigerant quickly flows out to the first bypass passage 15 side from the inlet / outlet chamber 36. be able to.
【００３０】[0030]
【発明の効果】以上説明したように、本発明のヒートポ
ンプ式冷凍装置では、一端側が暖房サイクル運転時に高
圧液冷媒が流れる高圧液域に接続され、途中に暖房サイ
クル運転時の高圧液冷媒の流れを許容する逆止弁１４を
もち、かつ、冷房用膨張機構４を側路する第１バイパス
路１５と、一端側が冷房サイクル運転時に高圧液冷媒が
流れる高圧液域に接続され、途中に冷房サイクル運転時
の高圧液冷媒の流れを許容する逆止弁１６をもち、か
つ、暖房用膨張機構６を側路する第２バイパス路１７と
の各他端側を、受液器５のガス域に接続させたから、暖
房サイクル運転時に、前記第２バイパス路１７に介装し
た前記逆止弁１６を介して前記熱源側熱交換器７側へリ
ークしたり、また、冷房サイクル運転時に、前記受液器
５から冷媒が前記第１バイパス路１５に介装した前記逆
止弁１４を介して前記利用側熱交換器３側へリークした
りする場合、前記第１，第２バイパス路１５，１７は何
れも前記受液器５のガス域に接続されているため、前記
受液器５の高圧液冷媒ではなくガス域に貯溜されたガス
冷媒が、前記利用側熱交換器３又は熱源側熱交換器７側
へリークすることになる。従って、冷暖房サイクル運転
時たとえリークがあっても圧縮機１側への液バックを阻
止できて、該圧縮機１の破損事故や湿り運転による油上
がり及び潤滑不良を防止することができ、しかも、ポン
プダウン運転も確実に行うことができる。As described above, in the heat pump type refrigerating apparatus of the present invention, one end side is connected to the high pressure liquid region through which the high pressure liquid refrigerant flows during the heating cycle operation, and the flow of the high pressure liquid refrigerant during the heating cycle operation is midway. And a first bypass passage 15 that has a check valve 14 that allows the high-pressure liquid refrigerant flowing during the cooling cycle operation, and a first bypass passage 15 that bypasses the expansion mechanism 4 for cooling. The check valve 16 that allows the flow of the high-pressure liquid refrigerant during operation is provided on the other end side of the second bypass passage 17 that bypasses the heating expansion mechanism 6 to the gas region of the liquid receiver 5. Since they are connected to each other, during the heating cycle operation, they leak to the heat source side heat exchanger 7 side through the check valve 16 provided in the second bypass passage 17, or during the cooling cycle operation, the received liquid. Refrigerant from the container 5 When leaking to the utilization side heat exchanger 3 side through the check valve 14 provided in the bypass passage 15, both the first and second bypass passages 15 and 17 are provided in the liquid receiver 5. Since it is connected to the gas area, not the high-pressure liquid refrigerant of the receiver 5 but the gas refrigerant stored in the gas area leaks to the use side heat exchanger 3 or the heat source side heat exchanger 7 side. Become. Therefore, during the heating / cooling cycle operation, even if there is a leak, liquid back to the compressor 1 side can be prevented, and it is possible to prevent a damage accident of the compressor 1 and oil rising and lubrication failure due to wet operation, and The pump down operation can be performed reliably.
【００３１】また、前記利用側熱交換器３に、冷房サイ
クル運転時低圧液室となり暖房サイクル運転時高圧液室
となる出入口室３６を設け、該出入口室３６に熱交換チ
ューブ３３を開口すると共に、前記出入口室３６に冷房
サイクル運転時低圧液管となる冷媒配管９１を、前記出
入口室３６の底面に対し上方に突出させ、かつ、突出先
端部を前記熱交換チューブ３３の開口側に向かって傾斜
状に開口させる一方、前記冷房用膨張機構４を側路する
前記第１バイパス路１５の一端側を前記出入口室３６
に、該出入口室３６に開口する最下段の熱交換チューブ
３３よりも下方に開口させることにより、冷房サイクル
運転時に、前記冷媒配管９１から前記出入口室３６に導
入される低圧液冷媒を前記各熱交換チューブ３３に均一
に分配できて、前記利用側熱交換器３の熱交換効率を高
めることができ、また、暖房サイクル運転時には、前記
出入口室３６から高圧液冷媒の全量を前記第１バイパス
路１５に速やかに流出させることができる。Further, the utilization side heat exchanger 3 is provided with an inlet / outlet chamber 36 which serves as a low pressure liquid chamber during the cooling cycle operation and serves as a high pressure liquid chamber during the heating cycle operation, and the heat exchange tube 33 is opened in the inlet / outlet chamber 36. A refrigerant pipe 91, which is a low-pressure liquid pipe during a cooling cycle operation, is projected in the inlet / outlet chamber 36 upward with respect to the bottom surface of the inlet / outlet chamber 36, and a protruding tip portion is directed toward the opening side of the heat exchange tube 33. While opening in an inclined shape, one end side of the first bypass passage 15 that bypasses the cooling expansion mechanism 4 is connected to the inlet / outlet chamber 36.
The low-pressure liquid refrigerant introduced from the refrigerant pipe 91 into the inlet / outlet chamber 36 during the cooling cycle operation is opened below the lowermost heat exchange tube 33 opening in the inlet / outlet chamber 36. It can be uniformly distributed to the exchange tubes 33, and the heat exchange efficiency of the use side heat exchanger 3 can be improved. Further, during the heating cycle operation, the entire amount of the high pressure liquid refrigerant is discharged from the inlet / outlet chamber 36 to the first bypass passage. It can be quickly drained to 15.
【図１】本発明にかかるヒートポンプ式冷凍装置の冷媒
回路図である。FIG. 1 is a refrigerant circuit diagram of a heat pump type refrigerating apparatus according to the present invention.
【図２】利用側熱交換器を拡大して示す一部省略断面図
である。FIG. 2 is a partially omitted cross-sectional view showing an enlarged use side heat exchanger.
【図３】従来例を示す冷媒回路図である。FIG. 3 is a refrigerant circuit diagram showing a conventional example.
１ 圧縮機 ２ 冷暖房切換機構 ３ 利用側熱交換器 ３３ 熱交換チューブ ３６ 出入口室 ４ 冷房用膨張機構 ５ 受液器 ６ 暖房用膨張機構 ７ 熱源側熱交換器 １４ 逆止弁 １５ 第１バイパス路 １６ 逆止弁 １７ 第２バイパス路 ９１ 冷媒配管 DESCRIPTION OF SYMBOLS 1 Compressor 2 Air conditioning switching mechanism 3 Utilization side heat exchanger 33 Heat exchange tube 36 Entrance / exit chamber 4 Cooling expansion mechanism 5 Liquid receiver 6 Heating expansion mechanism 7 Heat source side heat exchanger 14 Check valve 15 First bypass passage 16 Check valve 17 Second bypass passage 91 Refrigerant piping
Claims (2)
交換器３、受液器５、冷房用膨張機構４、暖房用膨張機
構６及び熱源側熱交換器７を備え、冷暖房サイクル運転
を可能としたヒートポンプ式冷凍装置において、一端側
が暖房サイクル運転時高圧液冷媒が流れる高圧液域に接
続され、途中に暖房サイクル運転時の高圧液冷媒の流れ
を許容する逆止弁１４をもち、かつ、前記冷房用膨張機
構４を側路する第１バイパス路１５と、一端側が冷房サ
イクル運転時高圧液冷媒が流れる高圧液域に接続され、
途中に冷房サイクル運転時の高圧液冷媒の流れを許容す
る逆止弁１６をもち、かつ、前記暖房用膨張機構６を側
路する第２バイパス路１７との各他端側を、前記受液器
５のガス域に接続していることを特徴とするヒートポン
プ式冷凍装置。1. A cooling / heating cycle operation, comprising a compressor 1, a cooling / heating switching mechanism 2, a use side heat exchanger 3, a liquid receiver 5, a cooling expansion mechanism 4, a heating expansion mechanism 6 and a heat source side heat exchanger 7. In the heat pump type refrigerating device capable of, one end side is connected to a high-pressure liquid region in which the high-pressure liquid refrigerant flows during the heating cycle operation, and has a check valve 14 that allows the flow of the high-pressure liquid refrigerant during the heating cycle operation, Further, the first bypass passage 15 for bypassing the cooling expansion mechanism 4 and one end side thereof are connected to the high pressure liquid region in which the high pressure liquid refrigerant flows during the cooling cycle operation,
The check valve 16 that allows the flow of the high-pressure liquid refrigerant during the cooling cycle operation is provided on the way, and each of the other end sides of the second bypass passage 17 that bypasses the heating expansion mechanism 6 is connected to the liquid receiving portion. A heat pump type refrigerating apparatus, which is connected to the gas region of the container 5.
時低圧液室となり暖房サイクル運転時高圧液室となる出
入口室３６をもち、該出入口室３６に熱交換チューブ３
３を開口させると共に、前記出入口室３６に冷房サイク
ル運転時低圧液管となる冷媒配管９１を、前記出入口室
３６の底面に対し上方に突出状で、かつ、突出先端部が
前記熱交換チューブ３３の開口側に向かって傾斜状に開
口させる一方、冷房用膨張機構４を側路する第１バイパ
ス路１５の一端側を前記出入口室３６に、該出入口室３
６に開口する最下段の熱交換チューブ３３より下方に開
口させていることを特徴とする請求項１記載のヒートポ
ンプ式冷凍装置。2. The heat exchanger 3 on the use side has an inlet / outlet chamber 36 which serves as a low pressure liquid chamber during a cooling cycle operation and serves as a high pressure liquid chamber during a heating cycle operation, and the heat exchange tube 3 is provided in the inlet / outlet chamber 36.
3 is opened, and a refrigerant pipe 91 that serves as a low-pressure liquid pipe during the cooling cycle operation is provided in the inlet / outlet chamber 36 so as to project upward with respect to the bottom surface of the inlet / outlet chamber 36, and the protruding tip portion is the heat exchange tube 33. Of the first bypass passage 15 which bypasses the expansion mechanism 4 for cooling, is provided in the inlet / outlet chamber 36, and the inlet / outlet chamber 3 is opened.
The heat pump type refrigerating apparatus according to claim 1, wherein the heat exchange tube 33 is opened below the lowermost heat exchange tube 33 that opens at 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30163691A JPH05141801A (en) | 1991-11-18 | 1991-11-18 | Heat pump type refrigerating plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30163691A JPH05141801A (en) | 1991-11-18 | 1991-11-18 | Heat pump type refrigerating plant |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05141801A true JPH05141801A (en) | 1993-06-08 |
Family
ID=17899330
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30163691A Pending JPH05141801A (en) | 1991-11-18 | 1991-11-18 | Heat pump type refrigerating plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05141801A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112628115A (en) * | 2020-12-31 | 2021-04-09 | 中盐华能储能科技有限公司 | Multi-section series compressor system capable of emergently stopping under pipe explosion working condition and stopping method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5195712A (en) * | 1975-02-05 | 1976-08-21 | ||
| JPS51111177A (en) * | 1975-03-20 | 1976-10-01 | Tokyo Electric Co Ltd | Absorbing device |
| JPS5480687A (en) * | 1977-12-09 | 1979-06-27 | Toyo Electric Mfg Co Ltd | Semiconductor controlled rectifier |
| JPS62125264A (en) * | 1985-11-26 | 1987-06-06 | 株式会社デンソー | Refrigeration cycle device |
| JPS62210362A (en) * | 1986-03-11 | 1987-09-16 | 株式会社デンソー | Heat pump type air conditioner for car |
| JPS63306364A (en) * | 1987-06-05 | 1988-12-14 | 株式会社デンソー | Air-conditioning changeover type air conditioner |
-
1991
- 1991-11-18 JP JP30163691A patent/JPH05141801A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5195712A (en) * | 1975-02-05 | 1976-08-21 | ||
| JPS51111177A (en) * | 1975-03-20 | 1976-10-01 | Tokyo Electric Co Ltd | Absorbing device |
| JPS5480687A (en) * | 1977-12-09 | 1979-06-27 | Toyo Electric Mfg Co Ltd | Semiconductor controlled rectifier |
| JPS62125264A (en) * | 1985-11-26 | 1987-06-06 | 株式会社デンソー | Refrigeration cycle device |
| JPS62210362A (en) * | 1986-03-11 | 1987-09-16 | 株式会社デンソー | Heat pump type air conditioner for car |
| JPS63306364A (en) * | 1987-06-05 | 1988-12-14 | 株式会社デンソー | Air-conditioning changeover type air conditioner |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112628115A (en) * | 2020-12-31 | 2021-04-09 | 中盐华能储能科技有限公司 | Multi-section series compressor system capable of emergently stopping under pipe explosion working condition and stopping method |
| CN112628115B (en) * | 2020-12-31 | 2023-02-24 | 中盐华能储能科技有限公司 | Multi-section series compressor system capable of emergently stopping under pipe explosion working condition and stopping method |
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