JPH043863A - Dry shell and tube type evaporator - Google Patents
Dry shell and tube type evaporatorInfo
- Publication number
- JPH043863A JPH043863A JP10374090A JP10374090A JPH043863A JP H043863 A JPH043863 A JP H043863A JP 10374090 A JP10374090 A JP 10374090A JP 10374090 A JP10374090 A JP 10374090A JP H043863 A JPH043863 A JP H043863A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchange
- space
- exchange section
- refrigerant outlet
- 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.)
- Granted
Links
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明はケーシング内に第１及び第２熱交換部を分割形
成して成る乾式シェルアンドチューブ形蒸発器に関する
。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a dry shell-and-tube evaporator in which first and second heat exchange sections are separately formed within a casing.
（従来の技術）
従来、此種蒸発器として、実開昭６２−２６７７６号公
報に見られ、また第７．８図に示すように、両端を閉鎖
した円筒状ケーシング（Ａ）内の一端側に冷媒入口空間
（Ｂ）を、また他端側に冷媒出口空間（Ｃ）をそれぞれ
設けて、これら各空間（Ｂ）（Ｃ）間に複数のパイプ群
（Ｄ）を設けると共に、前記冷媒入口空間（Ｂ）及び冷
媒出口空間（Ｃ）に、これら各空間（Ｂ）（Ｃ）をそれ
ぞれ左右に仕切る入口側及び出口側仕切板（Ｅ）ＣＦ）
をそれぞれ設けて、前記ケーシング（Ａ）内に第１及び
第２熱交換部（Ｇ）（Ｈ）を分割形成する一方、前記入
口側仕切板（Ｅ）の下端部に、前記第１熱交換部（Ｇ）
側の冷媒入口空間（Ｂ１）と第２熱交換部（Ｈ）側の冷
媒入口空間（Ｂ２）とを連通させ、停止側圧縮機に対応
する熱交換部（Ｇ）又は（Ｈ）に液冷媒が滞留し、再起
動時に液バツクが生ずるのを防ぐための小孔（１）を形
成したものが知られている。即ち、以上の如く構成され
る蒸発器は、第８図の如く前記各熱交換部（Ｇ）（Ｈ）
の各冷媒出口空間（Ｃ，）（Ｃ２）を、２台の第１及び
第２圧縮機（Ｊ）（Ｋ）の吸入側に連通させると共に、
前記各冷媒入口空間（Ｂ１）（Ｂ２）を、第１及び第２
電磁開閉弁（Ｌ）（Ｍ）を介して一つの受液器（Ｎ）に
連通させ、前記各圧縮器（Ｊ）（Ｋ）の吐出側に一つの
凝縮器（Ｐ）を連通させ、前記２台の圧縮機（Ｊ）（Ｋ
）のうち、１台の圧縮機のみを運転する部分容量運転時
には、停止側の圧縮機に対応する′Ｆｒｉ磁開閉弁開閉
弁、運転側圧縮機に対応する？１ｍ磁開閉弁のみを開い
て、一つの熱交換部にのみ冷媒を流通させ、かくして、
前記蒸発器における冷媒の流通面積を減少させて、この
部分容量運転に伴う冷媒循環量の減少に拘らず、前記蒸
発器の出口側においても、所望の冷媒流速が確保できる
ようにし、全容量運転時と同様に油戻しが行えるように
している。所が、前記した部分容量運転中、停止側圧縮
機に対応する電磁開閉弁に冷媒漏れが生じて、即ち、停
止側電磁開閉弁の入口側と出口側との圧力差により電磁
開閉弁から液冷媒が漏れて、この漏れた液冷媒が、停止
側熱交換部の冷媒入口空間に溜ることになるから、この
冷媒入口空間の残留液冷媒を、前記小孔（Ｉ）から運転
側熱交換部の冷媒入口空間に吸入させて、前記停止側熱
交換部に残留液冷媒が滞留することによる液パツクを防
止するようにしたのである。(Prior art) Conventionally, this type of evaporator is seen in Japanese Utility Model Application Laid-Open No. 62-26776, and as shown in Fig. 7.8, one end side in a cylindrical casing (A) with both ends closed. A refrigerant inlet space (B) is provided at one end, and a refrigerant outlet space (C) is provided at the other end, and a plurality of pipe groups (D) are provided between each of these spaces (B) and (C). In the space (B) and the refrigerant outlet space (C), there are inlet side and outlet side partition plates (E)CF) that partition these spaces (B) and (C) into left and right sides, respectively.
are provided respectively to form first and second heat exchange parts (G) and (H) separately in the casing (A), while the first heat exchange part is provided at the lower end of the inlet side partition plate (E). Department (G)
The refrigerant inlet space (B1) on the side is communicated with the refrigerant inlet space (B2) on the second heat exchange section (H) side, and liquid refrigerant is introduced into the heat exchange section (G) or (H) corresponding to the stopped compressor. It is known that a small hole (1) is formed in order to prevent liquid from accumulating and causing a liquid back-up at the time of restart. That is, the evaporator configured as described above has the heat exchange sections (G) (H) as shown in FIG.
Each refrigerant outlet space (C,) (C2) is communicated with the suction side of the two first and second compressors (J) (K),
Each of the refrigerant inlet spaces (B1) (B2) is divided into a first and a second refrigerant inlet space.
One liquid receiver (N) is connected to the discharge side of each of the compressors (J) and (K) through electromagnetic on-off valves (L) and (M), and one condenser (P) is connected to the discharge side of each of the compressors (J) and (K). Two compressors (J) (K
), during partial capacity operation in which only one compressor is operated, the 'Fri magnetic on-off valve corresponds to the compressor on the stop side, and the on-off valve corresponds to the compressor on the operating side. Only the 1m magnetic on-off valve was opened to allow the refrigerant to flow through only one heat exchange section, thus,
By reducing the refrigerant circulation area in the evaporator, a desired refrigerant flow rate can be ensured on the outlet side of the evaporator despite the reduction in the amount of refrigerant circulated due to partial capacity operation, and full capacity operation can be achieved. The oil can be returned in the same way as before. However, during the above-mentioned partial capacity operation, refrigerant leaked from the electromagnetic shut-off valve corresponding to the stop-side compressor. Since the refrigerant leaks and this leaked liquid refrigerant accumulates in the refrigerant inlet space of the stop side heat exchange section, the remaining liquid refrigerant in this refrigerant inlet space is transferred from the small hole (I) to the operation side heat exchange section. The refrigerant is sucked into the refrigerant inlet space of the refrigerant to prevent liquid puddles caused by residual liquid refrigerant remaining in the stop-side heat exchange section.
（発明が解決しようとする課題）
所が、以上の如く構成した蒸発器によると、例えば負荷
１００％のとき２台の圧縮機（Ａ）（Ａ）を、それぞれ
５０％の容量で運転している状態で、負荷が５０％に下
がった場合、１台の圧縮機を停止し、残り１台の圧縮機
を１００％の容量で運転するような場合、運転側圧縮機
に対応する運転側熱交換部における冷媒出口空間の冷媒
流速が急激に速くなって、停止側熱交換部における冷媒
入口空間内の液冷媒が、前記小孔（Ｉ）を通して運転側
熱交換部の冷媒入口空間に急激に引かれることになり、
このため、運転側熱交換部における冷媒入口空間内の冷
媒液量が一時的に多くなり、運転側圧縮機が湿り運転を
起こすことになる問題があった。(Problem to be Solved by the Invention) However, according to the evaporator configured as described above, for example, when the load is 100%, the two compressors (A) and (A) are each operated at 50% capacity. If the load drops to 50% while one compressor is stopped and the remaining compressor is operated at 100% capacity, the operating side heat corresponding to the operating compressor The refrigerant flow rate in the refrigerant outlet space in the exchange section suddenly increases, and the liquid refrigerant in the refrigerant inlet space in the stop-side heat exchange section suddenly flows through the small holes (I) into the refrigerant inlet space in the operation-side heat exchange section. I will be drawn away,
Therefore, there is a problem in that the amount of refrigerant liquid in the refrigerant inlet space in the driving-side heat exchange section temporarily increases, resulting in wet operation of the driving-side compressor.
本発明は以上の点に鑑み発明したもので、目的は、第１
熱交換部と第２熱交換部とがともに運転している状態で
、一方の運転に切換わったとき、停止した熱交換部側の
残留液冷媒を運転中の熱交換部側に吸込ませることがで
き、再起動時の液圧縮を防止できながら、運転側熱交換
部に、停止側熱交換部から大量に流入することによる液
圧縮を生ずることも解消できるようにする点にある。The present invention was invented in view of the above points, and the first purpose is to
When the heat exchange section and the second heat exchange section are both operating and the operation is switched to one of them, the residual liquid refrigerant from the stopped heat exchange section is sucked into the operating heat exchange section. The present invention is capable of preventing liquid compression at the time of restart, while also eliminating liquid compression caused by a large amount of liquid flowing into the operating side heat exchange section from the stopped side heat exchange section.
（課題を解決するための手段）
しかして、本発明はケーシング（１）内に、冷媒入口空
間（７）と冷媒出口空間（８）と、これら空間（７）（
８）を連通ずるパイプ群（３）とを設けると共に、前記
冷媒入口空間（７）及び冷媒出口空間（８）に、これら
各空間（７）（８）をそれぞれ左右に仕切る入口側及び
出口側仕切板（４）（５）をそれぞれ設けて、前記ケー
シング（１）内に第１及び第２熱交換部（Ｑ１）（Ｑ２
）を分割形成している乾式シェルアンドチューブ形蒸
発器において、前記第１熱交換部（Ｑ１）側の冷媒出口
空間（８ａ）と第２熱交換部（Ｑ２）側の冷媒出口空間
（８ｂ）とを連通する小径連通路（２１）を形成したも
のである。(Means for Solving the Problems) Accordingly, the present invention provides a refrigerant inlet space (7) and a refrigerant outlet space (8) within the casing (1), and these spaces (7) (
8), and the refrigerant inlet space (7) and refrigerant outlet space (8) are provided with an inlet side and an outlet side that partition these spaces (7) and (8) into left and right sides, respectively. Partition plates (4) and (5) are provided respectively, and first and second heat exchange parts (Q1) (Q2) are provided inside the casing (1).
), the refrigerant outlet space (8a) on the first heat exchange section (Q1) side and the refrigerant outlet space (8b) on the second heat exchange section (Q2) side. A small diameter communication path (21) is formed to communicate with the.
又、第１熱交換部（Ｑ１）側の冷媒出口空間（８ａ）に
連通ずる第１出口管（２２）と、第２熱交換部（Ｑ２）
側の冷媒出口空間（８ｂ）に連通ずる第２出口管（２３
）との間に小径連通路（２１）を介装するのが好ましい
。Also, a first outlet pipe (22) communicating with the refrigerant outlet space (8a) on the first heat exchange section (Q1) side, and a second heat exchange section (Q2).
A second outlet pipe (23) communicating with the side refrigerant outlet space (8b)
) is preferably provided with a small diameter communication passage (21).
又、小径連通路（２１）に、開度調整可能とした流量調
整弁（３６）を介装するのが好ましい。Further, it is preferable that a flow rate regulating valve (36) whose opening degree can be adjusted is interposed in the small diameter communication passage (21).
（作 用 ）
第１熱交換部（Ｑ１）と第２熱交換部（Ｑ２）とがとも
に運転している状態で、一つの運転に切換わったとき、
停止した熱交換部側に残留する液冷媒は、熱交換部でガ
ス化しつつ冷媒出口空間から小径連通路（２１）を通過
して、運転中熱交換部の冷媒出口空間に徐々に吸込まれ
るので、運転中熱交換部に、大量の液冷媒が流入するこ
とはなく、この結果、運転中の圧縮機が湿り運転になる
のを防止できるのである。(Function) When the first heat exchange section (Q1) and the second heat exchange section (Q2) are both operating and are switched to one operation,
The liquid refrigerant remaining on the stopped heat exchange section side is gasified in the heat exchange section, passes through the small diameter communication passage (21) from the refrigerant outlet space, and is gradually sucked into the refrigerant outlet space of the heat exchange section during operation. Therefore, a large amount of liquid refrigerant does not flow into the heat exchange section during operation, and as a result, it is possible to prevent the compressor from becoming wet during operation.
又、第１熱交換部（Ｑ１）側の冷媒出口空間（８ａ）に
連通ずる第１出口管（２２）と、第２熱交換部（Ｑ２）
側の冷媒出口空間（８ｂ）に連通ずる第２出口管（２３
）との間に小径連通路（２１）を介装することにより、
前記小径連通路（２１）からの液冷媒の流れを防止でき
るし、この小径連通路（２１）に流量調整弁（３６）を
簡単、容易に設けることができるのである。Also, a first outlet pipe (22) communicating with the refrigerant outlet space (8a) on the first heat exchange section (Q1) side, and a second heat exchange section (Q2).
A second outlet pipe (23) communicating with the side refrigerant outlet space (8b)
) by interposing a small diameter communication path (21) between the
The flow of liquid refrigerant from the small diameter communication passage (21) can be prevented, and the flow rate regulating valve (36) can be simply and easily provided in the small diameter communication passage (21).
又、小径連通路（２１）に、開度調整可能とした流量調
整弁（３６）を介装することにより、前記前記残留液冷
媒の小径連通路（２１）からの吸込み量を調整すること
ができるので、運転中圧縮機の湿り運転をより一層的確
に防止できるのである。Furthermore, by interposing a flow rate regulating valve (36) whose opening degree can be adjusted in the small diameter communication passage (21), the amount of the residual liquid refrigerant sucked from the small diameter communication passage (21) can be adjusted. Therefore, wet operation of the compressor during operation can be more accurately prevented.
（実 施 例 ）
第１〜６図に示した蒸発器は２バス構造の乾式シェルア
ンドチューブ形熱交換器であって、両端を椀形端板によ
り閉鎖した円筒状ケーシング（１）内の両端側に１対の
管板（２）（２）を設けて、第１及び第２端室（ｌａ）
（ｌｂ）と、熱交換室（１ｃ）とを画成し、この熱交換
室（ＩＣ）にブライン流入口（１１）とブライン流出口
（１２）とを設ける一方、前記各管板（２）（２）間に
、前記各端室（ｆａ）（ｆｂ）を連通する複数の第１〜
第４パイプ（３ａ）〜（３ｄ）から成るパイプ群（３）
を設けると共に、前記第１端室（ｌａ）に、該第１端室
（１ａ）を左右と上下とに仕切る入口側及び出口側仕切
板（４）（５）と兼用仕切板（６）とを設けて、前記第
１端室（１ａ）の上下方向下側に、二つの第１及び第２
冷媒入口空間（７ａ） （７ｂ）に区画した冷媒入口
空間（７）を設け、また、上側に二つの第１及び第２冷
媒出口空間（８ａ） （８ｂ）に区画した冷媒出口空
間（８）を設ける一方、前記第２端室（ｌｂ）に、該第
２端室（１ｂ）を左右に仕切る中間仕切板（９）を設け
て、前記第２端室（１ｂ）に、前記第１冷媒入口空間（
７ａ）及び第１冷媒出口空間（８ａ）に連通ずる第１連
絡空間（１０）と、前記第２冷媒入口空間（７ｂ）及び
第２冷媒出口空間（８ｂ）に連通ずる第２連絡空間（２
０）とを設け、前記第１冷媒入口空間（７ａ）と第１及
び第３パイプ（３ａ） （３ｃ）と、第１連絡空間（
１０）と第１冷媒出口空間（８ａ）とにより第１熱交換
部（Ｑ１）を形成し、また、前記第２冷媒入口空間（７
ｂ）と第２及び第４パイプ（３ｂ）（３ｄ）と、第２連
絡空間（２０）と第２冷媒出口空間（８ｂ）とにより第
２熱交換部（Ｑ２）を形成すると共に、前記出口側仕切
板（５）に、前記第１熱交換部（Ｑ１）側の第１冷媒出
口空間（８ａ）と第２熱交換部（Ｑ２）側の第２冷媒出
口空間（８ｂ）とを連通ずる小径連通路（２１）を形成
したのである。尚、前記ケーシング（１）の一端側端板
には、二つの冷媒入口（１３）（１３）を設け、また、
他端側端板には二つの冷媒出口（１４）（１４）を設け
ている。(Example) The evaporator shown in Figures 1 to 6 is a dry shell-and-tube heat exchanger with a two-bath structure. A pair of tube plates (2) (2) are provided on the sides of the first and second end chambers (la).
(lb) and a heat exchange chamber (1c), and the heat exchange chamber (IC) is provided with a brine inlet (11) and a brine outlet (12), while each tube plate (2) is provided with a brine inlet (11) and a brine outlet (12). (2) a plurality of first to third chambers communicating with each of the end chambers (fa) and (fb);
Pipe group (3) consisting of fourth pipes (3a) to (3d)
In addition, the first end chamber (la) is provided with inlet side and outlet side partition plates (4) and (5) and a dual-purpose partition plate (6) that partition the first end chamber (1a) into left and right and upper and lower parts. is provided, and two first and second chambers are provided below the first end chamber (1a) in the vertical direction.
A refrigerant inlet space (7) is provided which is divided into refrigerant inlet spaces (7a) and (7b), and a refrigerant outlet space (8) is divided into two first and second refrigerant outlet spaces (8a) and (8b) on the upper side. An intermediate partition plate (9) is provided in the second end chamber (lb) to partition the second end chamber (1b) into left and right sides, and the first refrigerant is provided in the second end chamber (1b). Entrance space (
7a) and the first refrigerant outlet space (8a), and a second communication space (2) that communicates with the second refrigerant inlet space (7b) and the second refrigerant outlet space (8b).
0), the first refrigerant inlet space (7a), the first and third pipes (3a) (3c), and the first communication space (
10) and the first refrigerant outlet space (8a) form a first heat exchange section (Q1), and the second refrigerant inlet space (7
b), the second and fourth pipes (3b) (3d), the second communication space (20), and the second refrigerant outlet space (8b) form a second heat exchange section (Q2), and the outlet A first refrigerant outlet space (8a) on the first heat exchange section (Q1) side and a second refrigerant outlet space (8b) on the second heat exchange section (Q2) side are communicated through the side partition plate (5). A small diameter communication path (21) was formed. In addition, two refrigerant inlets (13) (13) are provided on one end plate of the casing (1), and
Two refrigerant outlets (14) (14) are provided on the other end side end plate.
又、以上の如く構成される蒸発器は、第６図に示す如く
冷凍装置に適用するのであって、前記各冷媒出口（１４
）（１４）を、二つの出口管（２２）（２３）を介して
２台の第１及び第２圧縮機（２４）（２５）の吸入側に
連通させると共に、前記各冷媒入口（１３）（１３）を
、二つの流入管（２６）（２６）と、これら流入管（２
Ｂ）（２６）に連通ずる一つの流入管（２７）に連通さ
せるのであって、前記各流入管（２６）（２Ｂ）には、
第１及び第２電磁開閉弁（２８）（２９）と感温膨張弁
（３０）（３０）とを介装し、また、前記流入管（２７
）には、受液器（３１）と凝縮器（３２）とを接続して
いる。尚、（３３）（３３）は吸入逆止弁、（３４）（
３４）は吐出逆上弁、（３５）（３６）は感温筒である
。Furthermore, the evaporator configured as described above is applied to a refrigeration system as shown in FIG.
) (14) are communicated with the suction sides of the two first and second compressors (24) (25) via two outlet pipes (22) (23), and each of the refrigerant inlets (13) (13) with two inflow pipes (26) (26) and these inflow pipes (2
B) communicates with one inflow pipe (27) which communicates with (26), and each of said inflow pipes (26) (2B):
First and second electromagnetic on-off valves (28) (29) and temperature-sensitive expansion valves (30) (30) are interposed, and the inflow pipe (27)
) is connected to a liquid receiver (31) and a condenser (32). In addition, (33) (33) are suction check valves, (34) (
34) is a discharge reverse valve, and (35) and (36) are temperature-sensitive cylinders.
しかして、以上の如く構成した冷凍装置において、第１
及び第２圧縮機（２４）（２５）を駆動する場合、第１
及び第２Ｎ磁開閉弁（２８）（２９）を開とし、各圧縮
機（２４）（２５）から吐出される高圧ガス冷媒は凝縮
器（３２）で凝縮して液冷媒となった後、受液器（３１
）と各電磁開閉弁（２８）（２９）とを経て各感温膨張
弁（３０）（３０）に至り、該感温膨張弁（３０）（３
０）で減圧されて低圧となった液冷媒は、冷媒入口（１
３）（１３）から各冷媒入口空間（７ａ）（７ｂ）に流
入し、更に、第１及び第２パイプ（３ａ） （３ｂ）
内を流通し、各連絡空間（工０）（２０）を経て第３及
び第４パイプ（３ｃ）（３ｄ）内を流通し、これらパイ
プ（３ａ）〜（３ｄ）のパイプ群（３）内を流通する過
程で、熱交換室（１ｃ）に流入するブラインにより加熱
されて蒸発し、低圧ガス冷媒となって各冷媒出口空間（
８ａ）（８ｂ）に流出し、冷媒出口（１４）（１４）か
ら出口管（２２）（２３）を経て前記各圧縮機（２４）
（２５）に吸入されるのである。 そして、例えば負
荷１００％のとき第１及び第２圧縮機（２４）（２５）
を、それぞれ５０％の８皿で運転している状態で、負荷
が５０％になると、例えば第２圧縮機（２５）を停止し
、第１圧縮機（２４）を１００％の容量で運転するので
あるが、この場合、第１圧縮機（２４）に対応する運転
側の第１熱交換部（Ｑ１）における第１冷媒出口空間（
８ａ）の冷媒流速が急激に速くなり、停止した第２熱交
換部（Ｑ２）内の冷媒が、小径連通路（２１）から運転
側の第１熱交換部（Ｑ１）に急激に引かれることになる
が、前記小径連通路（２１）は、各熱交換部（Ｑ１）（
Ｑ２）の各冷媒出口空間（８ａ） （８ｂ）を連通し
ているため、停止した第２熱交換部（Ｑ２）の冷媒入口
空間（７ｂ）内に残留した液冷媒は、第２及び第４パイ
プ（３ｂ）（３ｄ）内でガス化しつつ徐々に第２冷媒出
口空間（８ｂ）内へ移動することになり、この第２冷媒
出口空間（８ｂ）内のガス冷媒が前記小径連通路（２１
）から第１冷媒出口空間（８ａ）内に引かれることにな
るので、第１熱交換部（Ｑ１）内に、大量の液冷媒量が
流入して、その液位が急激に増大することはないのであ
る。従って、停止した第２熱交換部（Ｑ２）側の第２電
磁開閉弁（２９）に漏れがあった場合でも前記小径連通
路（２１）から運転側の第１熱交換部（Ｑ１）に吸込ま
せることができるから、停止側第２熱交換部（Ｑ２）内
に過剰の液冷媒が残留するのを防止できながら、しかも
、前記第１熱交換部（Ｑ１）に大量の液冷媒が流入する
ことがないので、−時的でも運転中の第１圧縮機（２４
）が湿り運転になるのを防止できるのである。However, in the refrigeration system configured as described above, the first
and when driving the second compressor (24) (25), the first
Then, the second N magnetic on-off valves (28) and (29) are opened, and the high-pressure gas refrigerant discharged from each compressor (24) and (25) is condensed into liquid refrigerant in the condenser (32) and then sent to the receiver. Liquid container (31
) and each electromagnetic on-off valve (28) (29) to reach each temperature-sensitive expansion valve (30) (30).
The liquid refrigerant that has been depressurized and has a low pressure at the refrigerant inlet (1
3) From (13), the refrigerant flows into each refrigerant inlet space (7a) (7b), and further, the first and second pipes (3a) (3b)
It flows through the third and fourth pipes (3c) (3d) through each communication space (work 0) (20), and inside the pipe group (3) of these pipes (3a) to (3d). In the process of flowing, it is heated and evaporated by the brine flowing into the heat exchange chamber (1c), becoming a low-pressure gas refrigerant and filling each refrigerant outlet space (
8a) (8b), and flows from the refrigerant outlet (14) (14) through the outlet pipe (22) (23) to each of the compressors (24).
(25). For example, when the load is 100%, the first and second compressors (24) (25)
When the load reaches 50%, for example, the second compressor (25) is stopped and the first compressor (24) is operated at 100% capacity. However, in this case, the first refrigerant outlet space (
8a) The refrigerant flow rate suddenly increases, and the refrigerant in the stopped second heat exchange section (Q2) is suddenly drawn from the small diameter communication passage (21) to the first heat exchange section (Q1) on the operating side. However, the small diameter communication path (21) is connected to each heat exchange section (Q1) (
Since the refrigerant outlet spaces (8a) and (8b) of Q2) are communicated with each other, the liquid refrigerant remaining in the refrigerant inlet space (7b) of the stopped second heat exchange section (Q2) is transferred to the second and fourth refrigerant. The gas refrigerant in the second refrigerant outlet space (8b) gradually moves into the second refrigerant outlet space (8b) while being gasified in the pipes (3b) (3d), and the gas refrigerant in the second refrigerant outlet space (8b) flows into the small diameter communication path (21).
) into the first heat exchanger outlet space (8a), a large amount of liquid refrigerant will flow into the first heat exchanger (Q1) and the liquid level will not increase rapidly. There isn't. Therefore, even if there is a leak in the second electromagnetic on-off valve (29) on the stopped second heat exchange section (Q2), suction will be sucked from the small diameter communication passage (21) into the first heat exchange section (Q1) on the operating side. Since it is possible to prevent excessive liquid refrigerant from remaining in the second heat exchange section (Q2) on the stop side, a large amount of liquid refrigerant can flow into the first heat exchange section (Q1). Therefore, even if it is temporary, the first compressor (24
) can prevent wet operation.
尚、以上説明した実施例では、ケーシング（１）内の出
口側仕切板（５）に小径連通路（２１）を設けたが、そ
の他、第５図の如く各冷媒出口空間（８ａ） （８ｂ
）の冷媒出口（１４）（１４）に接続する前記各出口管
（２２）（２３）の間に小径連通路（２１）を設けても
よい。又、この第５図の場合、破線に示した如く小径連
通路（２１）に、開度調整可能とした流量調整弁（３６
）を介装するのが好ましい。又、この流量調整弁（３６
）は、手動操作で調整するようにする他、例えば前記各
圧縮機（２４）（２５）の吐出側冷媒の湿り度を検出し
て、この湿り度に基づいて自動的に調整するようにして
もよいのである。以上のように流量調整弁（３６）を設
けることにより、前記小径連通路（２１）からの吸込み
量を調整することができるので、運転中圧縮機の湿り運
転をより一層的確に防止できるのである。In the embodiment described above, the small diameter communication passage (21) was provided in the outlet side partition plate (5) in the casing (1), but in addition, each refrigerant outlet space (8a) (8b) was provided as shown in FIG.
) A small diameter communication passage (21) may be provided between each of the outlet pipes (22) (23) connected to the refrigerant outlet (14) (14) of the refrigerant outlet (14). In addition, in the case of this Fig. 5, a flow rate regulating valve (36) whose opening degree can be adjusted is installed in the small diameter communication passage (21) as shown by the broken line.
) is preferably used. In addition, this flow rate adjustment valve (36
) may be adjusted manually or, for example, by detecting the humidity of the refrigerant on the discharge side of each of the compressors (24) and (25) and automatically adjusting based on this humidity. It is also good. By providing the flow rate adjustment valve (36) as described above, the amount of suction from the small-diameter communication passage (21) can be adjusted, so that wet operation of the compressor can be more accurately prevented during operation. .
又、以上説明した蒸発器は、ケーシング（１）の一端側
に冷媒入口空間（７）と冷媒出口空間（８）とを設けて
、ケーシング（１）の一端側に吸入した冷媒を、ケーシ
ング（１）の他端側で反転させて前記一端側の冷媒出口
空間（８）から排出するようにした２バス構造のもので
あるが、その他、本発明の蒸発器は、ケーシング（１）
の一端側に設ける冷媒入口空間に吸入した冷媒を、ケー
シングの他端側に設ける冷媒出口空間から排出するよう
にした１バス構造であってもよい。Furthermore, the evaporator described above is provided with a refrigerant inlet space (7) and a refrigerant outlet space (8) at one end of the casing (1), so that the refrigerant sucked into the one end of the casing (1) is transferred to the casing (1). 1) The evaporator of the present invention has a two-bath structure in which the refrigerant is inverted at the other end and discharged from the refrigerant outlet space (8) at the one end.
A one-bath structure may be used in which the refrigerant sucked into a refrigerant inlet space provided at one end of the casing is discharged from a refrigerant outlet space provided at the other end of the casing.
（発明の効果）
以上の如く本発明は、ケーシング（１）内に、冷媒入口
空間（７）と冷媒出口空間（８）と、これら空間（７）
（８）を連通ずる複数のバイブ群（３）とを設けると共
に、前記冷媒入口空間（７）及び冷媒出口空間（８）に
、これら各空間（７）（８）をそれぞれ左右に仕切る入
口側及び出口側仕切板（４）（５）をそれぞれ設けて、
前記ケーシング（１）内に第１及び第２熱交換部（Ｑ１
）（Ｑ２）を分割形成している乾式シェルアンドチュー
ブ形蒸発器において、前記第１熱交換部（Ｑ１）側の冷
媒出口空間（８ａ）と第２熱交換部（Ｑ２）側の冷媒出
口空間（８ｂ）とを連通ずる小径連通路（２１）を形成
したから、第１熱交換部（Ｑ１）と第２熱交換部（Ｑ２
）とがともに運転している状態で、一つの運転に切換わ
ったとき、停止した熱交換部側の残留液冷媒を運転側に
吸込ませることができながら、しかも、この残留液冷媒
は、停止側熱交換部でガス化しつつ冷媒出口空間から小
径連通路（２１）を通過して、運転側熱交換部の冷媒出
口空間に徐々に吸込ませることができるので、運転側熱
交換部に大量の液冷媒が流入することはなくなり、この
結果、運転中の圧縮機が湿り運転になるのを防止できる
のである。(Effects of the Invention) As described above, the present invention provides a refrigerant inlet space (7), a refrigerant outlet space (8), and a refrigerant outlet space (7) in the casing (1).
(8) and a plurality of vibrator groups (3) that communicate with each other, and the refrigerant inlet space (7) and the refrigerant outlet space (8) are provided with an inlet side that partitions these spaces (7) and (8) into left and right sides, respectively. and exit side partition plates (4) and (5) respectively,
First and second heat exchange parts (Q1) are provided in the casing (1).
) (Q2), the refrigerant outlet space (8a) on the first heat exchange section (Q1) side and the refrigerant outlet space on the second heat exchange section (Q2) side. (8b), the first heat exchange section (Q1) and the second heat exchange section (Q2) are formed.
) are operating together, and when switching to one operation, the residual liquid refrigerant on the stopped heat exchanger side can be sucked into the operating side; While being gasified in the side heat exchange section, the refrigerant can pass through the small diameter communication passage (21) from the refrigerant outlet space and be gradually sucked into the refrigerant outlet space of the operation side heat exchange section. Liquid refrigerant no longer flows in, and as a result, it is possible to prevent the compressor from becoming wet during operation.
又、第１Ｍ交換部（Ｑ１）側の冷媒出口空間（８ａ）に
連通ずる第１出口管（２２）と、第２熱交換部（Ｑ２）
側の冷媒出口空間（８ｂ）に連通ずる第２出口管（２３
）との間に小径連通路（２１）を介装することにより、
この小径連通路（２１）を介して液冷媒が流れるのを確
実に防止できるし、また、前記小径連通路（２１）に流
量調整弁（３６）を簡単、容易に設けることができるの
である。Also, a first outlet pipe (22) communicating with the refrigerant outlet space (8a) on the first M exchange section (Q1) side, and a second heat exchange section (Q2).
A second outlet pipe (23) communicating with the side refrigerant outlet space (8b)
) by interposing a small diameter communication path (21) between the
It is possible to reliably prevent the liquid refrigerant from flowing through the small diameter communication passage (21), and the flow rate regulating valve (36) can be simply and easily provided in the small diameter communication passage (21).
又、小径連通路（２１）に、開度調整可能とした流量調
整弁（３６）を介装することにより、前記前記残留液冷
媒の小径連通路（２１）からの吸込み量を調整すること
ができるので、運転中圧縮機の湿り運転をより一層的確
に防止できるのである。Furthermore, by interposing a flow rate regulating valve (36) whose opening degree can be adjusted in the small diameter communication passage (21), the amount of the residual liquid refrigerant sucked from the small diameter communication passage (21) can be adjusted. Therefore, wet operation of the compressor during operation can be more accurately prevented.
第１図は本発明蒸発器の一実施例を示す縦断面図、第２
図は第１図横断面図、第３図は第２図ＩＩＩ−ＩＩＩ線
断面図、第４図は第２図ｒＶ−ＩＶ線断面図、第５図は
別の実施例を示す縦断面図、第６図は冷凍装置に適用し
た例の説明図、第７図は従来例の縦断面図、第８図は同
冷凍装置に適用した例の説明図である。
（１）・・・・ケーシング
（３）・・・・パイプ群
（４）・・・・入口側仕切板
（５）・・・・出口側仕切板
（７）・・・・冷媒入口空間
（８）・・・・冷媒出口空間
（８ａ）・・・・第１冷媒出口空間
（８ｂ）・・・・第２冷媒出口空間
（２１）・・・・小径連通路
（２２）（２３）・・・・出口管
（３６）・・・・流量調整弁
（Ｑ１）・・・・第１熱交換部
（Ｑ２）・・・・第２熱交換部Fig. 1 is a vertical cross-sectional view showing one embodiment of the evaporator of the present invention;
The figures are a cross-sectional view of FIG. 1, a cross-sectional view taken along the line III--III of FIG. 2, a sectional view taken along the line rV-IV of FIG. , FIG. 6 is an explanatory diagram of an example applied to a refrigeration device, FIG. 7 is a longitudinal sectional view of a conventional example, and FIG. 8 is an explanatory diagram of an example applied to the same refrigeration device. (1)...Casing (3)...Pipe group (4)...Inlet side partition plate (5)...Outlet side partition plate (7)...Refrigerant inlet space ( 8)...Refrigerant outlet space (8a)...First refrigerant outlet space (8b)...Second refrigerant outlet space (21)...Small diameter communication passage (22) (23)... ... Outlet pipe (36) ... Flow rate adjustment valve (Q1) ... First heat exchange section (Q2) ... Second heat exchange section
Claims (1)
出口空間（８）と、これら空間（７）（８）を連通する
パイプ群（３）とを設けると共に、前記冷媒入口空間（
７）及び冷媒出口空間（８）に、これら各空間（７）（
８）をそれぞれ左右に仕切る入口側及び出口側仕切板（
４）（５）をそれぞれ設けて、前記ケーシング（１）内
に第１及び第２熱交換部（Ｑ＿１）（Ｑ＿２）を分割形
成している乾式シェルアンドチューブ形蒸発器において
、前記第１熱交換部（Ｑ＿１）側の冷媒出口空間（８ａ
）と第２熱交換部（Ｑ＿２）側の冷媒出口空間（８ｂ）
とを連通する小径連通路（２１）を形成したことを特徴
とすると乾式シェルアンドチューブ形蒸発器。 ２）第１熱交換部（Ｑ＿１）側の冷媒出口空間（８ａ）
に連通する第１出口管（２２）と、第２熱交換部（Ｑ＿
２）側の冷媒出口空間（８ｂ）に連通する第２出口管（
２３）との間に小径連通路（２１）を介装した請求項１
記載の乾式シェルアンドチューブ形蒸発器。 ３）小径連通路（２１）に、開度調整可能とした流量調
整弁（３６）を介装した請求項１記載の乾式シェルアン
ドチューブ形蒸発器。[Claims] 1) A refrigerant inlet space (7), a refrigerant outlet space (8), and a pipe group (3) communicating these spaces (7) and (8) are provided in the casing (1), and , the refrigerant inlet space (
7) and the refrigerant outlet space (8), each of these spaces (7) (
8) Inlet side and outlet side partition plates (
4) In a dry shell-and-tube evaporator in which first and second heat exchange parts (Q_1) (Q_2) are separately formed in the casing (1) by providing (5), the first heat exchanger Refrigerant outlet space (8a) on the exchange part (Q_1) side
) and the refrigerant outlet space (8b) on the second heat exchange section (Q_2) side
A dry shell-and-tube type evaporator characterized by forming a small-diameter communication path (21) that communicates with the evaporator. 2) Refrigerant outlet space (8a) on the first heat exchange section (Q_1) side
The first outlet pipe (22) communicates with the second heat exchange section (Q_
2) side refrigerant outlet space (8b).
Claim 1 wherein a small diameter communication passage (21) is interposed between the
The dry shell-and-tube evaporator described. 3) The dry shell-and-tube evaporator according to claim 1, wherein the small-diameter communication passage (21) is provided with a flow rate regulating valve (36) whose opening degree can be adjusted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2103740A JP2591248B2 (en) | 1990-04-19 | 1990-04-19 | Dry shell and tube evaporator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2103740A JP2591248B2 (en) | 1990-04-19 | 1990-04-19 | Dry shell and tube evaporator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH043863A true JPH043863A (en) | 1992-01-08 |
| JP2591248B2 JP2591248B2 (en) | 1997-03-19 |
Family
ID=14362015
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2103740A Expired - Fee Related JP2591248B2 (en) | 1990-04-19 | 1990-04-19 | Dry shell and tube evaporator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2591248B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103277944A (en) * | 2013-05-08 | 2013-09-04 | 杭州赛富特设备有限公司 | Dry-type evaporator |
| JP2013231591A (en) * | 2009-06-29 | 2013-11-14 | Johnson Controls Technology Co | System for limiting pressure difference in dual compressor chiller |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6225776U (en) * | 1985-07-31 | 1987-02-17 |
-
1990
- 1990-04-19 JP JP2103740A patent/JP2591248B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6225776U (en) * | 1985-07-31 | 1987-02-17 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013231591A (en) * | 2009-06-29 | 2013-11-14 | Johnson Controls Technology Co | System for limiting pressure difference in dual compressor chiller |
| CN103277944A (en) * | 2013-05-08 | 2013-09-04 | 杭州赛富特设备有限公司 | Dry-type evaporator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2591248B2 (en) | 1997-03-19 |
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