JPH0894266A - Horizontal type condenser - Google Patents
Horizontal type condenserInfo
- Publication number
- JPH0894266A JPH0894266A JP23003894A JP23003894A JPH0894266A JP H0894266 A JPH0894266 A JP H0894266A JP 23003894 A JP23003894 A JP 23003894A JP 23003894 A JP23003894 A JP 23003894A JP H0894266 A JPH0894266 A JP H0894266A
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- Prior art keywords
- area
- flow rate
- subcool
- condensation
- fluid
- 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.)
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- Details Of Heat-Exchange And Heat-Transfer (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、横型コンデンサに係
り、特に、横置き状態の本体胴部の内部における熱交換
により、高温流体を凝縮状態に導く場合の熱効率の向上
を図るものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a horizontal condenser, and more particularly to improving the thermal efficiency in the case where a high temperature fluid is brought into a condensed state by heat exchange inside the main body in a horizontal state.
【０００２】[0002]
【従来の技術】図４は、実開平４−１２２９７４号公報
に記載されている蒸気の凝縮に使用される熱交換器の例
を示している。図４において、符号１は本体胴部、２は
管板、３は熱交換室、４は伝熱管、５はバッフルプレー
ト、６は切欠部、７は基部ケーシング、８は入り口プレ
ナム部、９は出口プレナム部、１０は管内流体用入り
口、１１は管内流体用出口、１２は胴内流体用入り口、
１３Ａは上部胴内流体用出口、１３Ｂは下部胴内流体用
出口である。2. Description of the Related Art FIG. 4 shows an example of a heat exchanger used for steam condensation disclosed in Japanese Utility Model Laid-Open No. 4-122974. In FIG. 4, reference numeral 1 is a main body portion, 2 is a tube plate, 3 is a heat exchange chamber, 4 is a heat transfer tube, 5 is a baffle plate, 6 is a notch portion, 7 is a base casing, 8 is an inlet plenum portion, and 9 is Outlet plenum portion, 10 is an inlet for fluid in the pipe, 11 is an outlet for fluid in the pipe, 12 is an inlet for fluid in the body,
13A is an upper body fluid outlet, and 13B is a lower body fluid outlet.
【０００３】このような熱交換器にあっては、管内流体
が上下の群に２分割された伝熱管４を実線の矢印で示す
ように往復するとともに、破線の矢印で示すように挿通
する胴内流体が蒸気である場合に、熱交換部３における
冷却に伴って一部が凝縮されて、蒸気分が上部胴内流体
用出口１３Ａから排出され、凝縮液分が下部胴内流体用
出口１３Ｂから排出される構造となっている。In such a heat exchanger, a body in which the fluid inside the tube reciprocates through the heat transfer tubes 4 divided into upper and lower groups as shown by solid arrows and is inserted as shown by broken arrows. When the inner fluid is steam, a part of it is condensed as it cools in the heat exchange unit 3, the vapor component is discharged from the upper in-body fluid outlet 13A, and the condensed liquid component is in the lower in-body fluid outlet 13B. The structure is such that it is discharged from.
【０００４】[0004]
【発明が解決しようとする課題】しかし、胴内流体を凝
縮させる場合であると、凝縮により胴内流体の体積が大
幅に減少する（常圧スチームでは約１０００分の１に減
少する）ために、伝熱性を維持しようとすると、胴内流
体の流速を著しく低下させる必要がある。胴内流体の流
速は、バッフルプレート５の間隔を変更することにより
調整可能であるものの、上述のように体積変動が大き過
ぎる場合には、実質的に不可能である。その対応案とし
ては、直列接続状態の蒸気凝縮用熱交換器と凝縮液用熱
交換器とを二つ使用して、個別に熱交換を行なうことが
考えられるが、その場合には、高温流体の方は二つの熱
交換器に直列的に送り込むことで対応できるものの、低
温流体は、二つの熱交換器に別々に流量の異なるものを
送り込む必要があり、非効率的なものとなるのに加え
て、種類の異なる熱交換器の準備や設置スペースの確保
等の面でも障害が大きくなる。However, in the case of condensing the in-body fluid, the volume of the in-body fluid is greatly reduced by the condensation (at atmospheric pressure steam, it is reduced to about 1/1000). In order to maintain heat conductivity, it is necessary to significantly reduce the flow velocity of the fluid in the body. The flow velocity of the in-body fluid can be adjusted by changing the interval between the baffle plates 5, but it is substantially impossible if the volume fluctuation is too large as described above. One possible solution is to use two steam condensing heat exchangers and a condensate heat exchanger that are connected in series, and perform heat exchange individually. Can be handled by feeding two heat exchangers in series, but the cryogenic fluid needs to be fed with different flow rates to the two heat exchangers, which is inefficient. In addition, obstacles become large in terms of preparing different types of heat exchangers and securing installation space.
【０００５】本発明は、これらの事情に鑑みてなされた
もので、一つの本体胴部で蒸気の凝縮と凝縮液の冷却と
を行ない、小型化を図るとともに、その際の熱交換効率
を向上させることを目的としている。The present invention has been made in view of these circumstances, and condenses vapor and cools the condensate in one main body to reduce the size and improve the heat exchange efficiency at that time. The purpose is to let.
【０００６】[0006]
【課題を解決するための手段】横置き状態の本体胴部の
内部に、熱交換室の高温流体と熱交換をする複数の伝熱
管が収納され、高温流体が熱交換によって凝縮状態に導
かれる横型コンデンサとして、熱交換室が、上下隔壁に
より大容積の凝縮域と小容積のサブクール域とに区画さ
れ、凝縮域及びサブクール域に、これらを接続する接続
口と、該接続口から離間した状態の高温流体入口及び凝
縮液出口とが配される構成が採用される。サブクール域
には、複数の伝熱管よりも口径の大きいバイパス管が並
列接続状態に配される。バイパス管には、その内部を挿
通する流体の流量を調整する流量調整手段が配される。
流量調整手段として、凝縮液の流量を検出する流量計
と、該流量計に接続され流量検出信号によりバイパス管
の流量を演算する演算部と、該演算部に接続状態にかつ
バイパス管に配され演算部の指令により開度を調整する
制御弁とを具備する構成が採用される。A plurality of heat transfer tubes for exchanging heat with a high temperature fluid in a heat exchange chamber are housed inside a main body body in a horizontal state, and the high temperature fluid is introduced into a condensed state by heat exchange. As a horizontal condenser, the heat exchange chamber is divided into a large-volume condensation area and a small-volume subcool area by upper and lower partition walls, and a state where the condensation area and the subcool area are connected to each other and are separated from the connection opening. The configuration in which the high temperature fluid inlet and the condensate outlet are arranged is adopted. In the subcool area, bypass pipes having a larger diameter than the heat transfer pipes are arranged in parallel. The bypass pipe is provided with flow rate adjusting means for adjusting the flow rate of the fluid passing through the inside thereof.
As a flow rate adjusting means, a flow meter that detects the flow rate of the condensate, a calculation unit that is connected to the flow meter and calculates the flow rate of the bypass pipe based on a flow rate detection signal, and a calculation unit that is connected to the calculation unit and is arranged in the bypass pipe. A configuration including a control valve that adjusts the opening degree according to a command from the calculation unit is adopted.
【０００７】[0007]
【作用】熱交換室の内部に送り込まれた高温流体は、大
容積の凝縮域において伝熱管に送り込まれた低温流体と
の間で熱交換を行ない、凝縮により凝縮液となる。凝縮
液は、小容積のサブクール域に送り込まれて、凝縮域に
達する前の低温流体との間で熱交換を行なう。低温流体
は、サブクール域において複数の伝熱管と口径の大きい
バイパス管とに分流し、流量調整手段によりバイパス管
の流量が調整されることにより、サブクール域における
熱交換量が制御される。凝縮液の流量は流量計により検
出されて、その検出データにより伝熱管の必要流量が演
算され、その演算結果に基づいて、制御弁を介してバイ
パス管の流量を調整することにより、サブクール域にお
ける伝熱管の流量が設定される。The high-temperature fluid sent into the heat exchange chamber exchanges heat with the low-temperature fluid sent to the heat transfer tube in the large-volume condensation area and becomes a condensed liquid by condensation. The condensate is fed into a small-volume subcooled region to exchange heat with the low temperature fluid before reaching the condensing region. The low-temperature fluid is divided into a plurality of heat transfer tubes and a bypass pipe having a large diameter in the subcool region, and the flow rate of the bypass pipe is adjusted by the flow rate adjusting means, so that the heat exchange amount in the subcool region is controlled. The flow rate of the condensate is detected by the flow meter, the required flow rate of the heat transfer tube is calculated from the detected data, and the flow rate of the bypass tube is adjusted via the control valve based on the calculation result. The flow rate of the heat transfer tube is set.
【０００８】[0008]
【実施例】以下、本発明に係る横型コンデンサの一実施
例を図１ないし図３に基づいて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the horizontal capacitor according to the present invention will be described below with reference to FIGS.
【０００９】該一実施例における横型コンデンサには、
図１及び図２に示すように、横置き状態に設置される本
体胴部１と、該本体胴部１の内部に配され一対の管板２
で区画された状態の熱交換室３と、該熱交換室３に配さ
れ熱交換を行なうための伝熱管４及び流路を蛇行させる
ための複数のバッフルプレート５Ａ，５Ｂ及び切欠部６
と、基部ケーシング７に形成され伝熱管４により接続さ
れる入り口プレナム部８及び出口プレナム部９と、伝熱
管４への流体送り込み及び流出を行なうための管内流体
用入り口１０及び管内流体用出口１１と、上下の伝熱管
４を接続状態とするための中間ケーシング１４とが配さ
れる。The lateral capacitor in the one embodiment includes
As shown in FIGS. 1 and 2, a main body portion 1 installed horizontally and a pair of tube plates 2 arranged inside the main body portion 1.
A heat exchange chamber 3 in a state of being partitioned by, heat transfer tubes 4 arranged in the heat exchange chamber 3 for heat exchange, and a plurality of baffle plates 5A, 5B for meandering a flow path and notches 6
An inlet plenum portion 8 and an outlet plenum portion 9 formed in the base casing 7 and connected by the heat transfer tube 4, an in-pipe fluid inlet 10 and an in-pipe fluid outlet 11 for feeding and discharging the fluid to and from the heat transfer tube 4. And an intermediate casing 14 for connecting the upper and lower heat transfer tubes 4 to each other.
【００１０】これらの構造に加えて、熱交換室３には、
水平状態の上下隔壁２１により大容積の凝縮域２２と小
容積のサブクール域２３とが区画形成され、凝縮域２２
及びサブクール域２３には、その一部を中間ケーシング
１４の近傍で接続状態とする接続口２４と、該接続口２
４から離間した位置で凝縮域２２及びサブクール域２３
に対して接続状態の高温流体入口２５及び凝縮液出口２
６とが配される。In addition to these structures, the heat exchange chamber 3 has
The horizontal partition wall 21 divides and forms a large-volume condensation area 22 and a small-volume subcool area 23.
In the sub-cooling area 23, a connection port 24, a part of which is connected in the vicinity of the intermediate casing 14, and the connection port 2
4, the condensation area 22 and the subcool area 23
High temperature fluid inlet 25 and condensate outlet 2 connected to
6 and 6 are arranged.
【００１１】前記サブクール域２３には、複数の伝熱管
４よりも相対的に口径の大きいバイパス管２７が、伝熱
管４と並列接続状態に配される。In the subcool area 23, a bypass pipe 27 having a relatively larger diameter than the plurality of heat transfer tubes 4 is arranged in parallel with the heat transfer tubes 4.
【００１２】前記バイパス管２７には、その内部を挿通
する流体の流量を調整するための流量調整手段２８が配
され、該流量調整手段２８は、凝縮液排出ライン２９の
途中に配されて凝縮液の流量を検出する流量計３０と、
該流量計３０に接続され流量検出信号によりバイパス管
２７に流すべき流量を演算する演算部３１と、該演算部
３１に接続されるとともにバイパス管２７に配されて開
度を調整する機能を有する制御弁３２とを具備するもの
が採用される。The bypass pipe 27 is provided with flow rate adjusting means 28 for adjusting the flow rate of the fluid passing through the inside thereof, and the flow rate adjusting means 28 is provided in the middle of the condensate discharge line 29 to condense the fluid. A flow meter 30 for detecting the flow rate of the liquid,
It has a function of being connected to the flow meter 30 and calculating a flow rate to be flown to the bypass pipe 27 by a flow rate detection signal, and being connected to the calculation unit 31 and arranged in the bypass pipe 27 to adjust the opening degree. The one provided with the control valve 32 is adopted.
【００１３】このような横型コンデンサにあっては、凝
縮されるべき高温流体が、図１の破線の矢印で示すよう
に、高温流体入口２５から、熱交換室３における凝縮域
２２、接続口２４、サブクール域２３を経由して凝縮液
出口２６から排出される挿通状態となり、高温流体を冷
却して凝縮状態とするための低温流体が、図１の実線の
矢印で示すように、管内流体用入り口１０から、入り口
プレナム部８、サブクール域２３の伝熱管４またはバイ
パス管２７、中間ケーシング１４の内部、凝縮域２２の
伝熱管４、出口プレナム部９を経由して管内流体用出口
１１から排出される挿通状態となる。In such a horizontal condenser, the high temperature fluid to be condensed is, as shown by the broken line arrow in FIG. 1, from the high temperature fluid inlet 25 to the condensation area 22 and the connection port 24 in the heat exchange chamber 3. , A low-temperature fluid for cooling the high-temperature fluid to a condensed state is discharged from the condensate outlet 26 via the sub-cooling area 23, as shown by a solid arrow in FIG. Discharge from the inlet 10 through the inlet plenum 8, the heat transfer pipe 4 or the bypass pipe 27 in the subcool region 23, the inside of the intermediate casing 14, the heat transfer pipe 4 in the condensation region 22, and the outlet plenum 9 from the in-pipe fluid outlet 11. The inserted state is reached.
【００１４】したがって、高温流体は、容積の大きい凝
縮域２２での冷却により凝縮されて凝縮液となり、この
凝縮により生成された凝縮液は、小容積のサブクール域
２３で凝縮域２２に達する前の低温流体との熱交換によ
り冷却される。Therefore, the high-temperature fluid is condensed by the cooling in the condensing zone 22 having a large volume to be a condensate, and the condensate produced by this condensing is before reaching the condensing zone 22 in the sub-cooling zone 23 having a small volume. It is cooled by heat exchange with the cryogenic fluid.
【００１５】そして、前述したように、高温流体は凝縮
されることによって著しく体積が減少するとともに、凝
縮液となることによって熱伝達性が高められるため、サ
ブクール域２３は、凝縮域２２と比較して、その横断面
積が著しく小さくなるように設定される。As described above, the volume of the high temperature fluid is remarkably reduced by being condensed, and the heat transfer property is enhanced by becoming the condensed liquid. Therefore, the subcool region 23 is compared with the condensing region 22. The cross-sectional area is set to be extremely small.
【００１６】しかし、本体胴部１の中を凝縮域２２及び
サブクール域２３に区画する場合には、サブクール域２
３と凝縮域２２との間で、低温流体を直列的に流す都合
上、サブクール域２３及び凝縮域２２における伝熱管４
の総断面積を概略一致させる必要が生じるため、サブク
ール域２３における総伝熱管４の断面積及びバイパス管
２７の断面積の和が、凝縮域２２における総伝熱管４の
断面積よりも若干大きくなるように、バイパス管２７の
口径を設定する。そして、バイパス管２７の流量を流量
調整手段２８により調整して、低温流体がサブクール域
２３から凝縮域２２に円滑に送り込まれるように設定す
る。However, when the main body 1 is divided into the condensation area 22 and the subcool area 23, the subcool area 2
3 and the condensing zone 22, the heat transfer tubes 4 in the subcool zone 23 and the condensing zone 22 for the purpose of flowing the low temperature fluid in series.
Therefore, the sum of the cross-sectional area of the total heat transfer tube 4 in the subcool area 23 and the cross-sectional area of the bypass tube 27 is slightly larger than the cross-sectional area of the total heat transfer tube 4 in the condensation area 22. The diameter of the bypass pipe 27 is set so that Then, the flow rate of the bypass pipe 27 is adjusted by the flow rate adjusting means 28 so that the low temperature fluid is smoothly fed from the subcool area 23 to the condensation area 22.
【００１７】また、図１例では、流量調整手段２８にお
いて、流量計３０による凝縮液排出ライン２９の凝縮液
量の検出が行なわれ、流量の検出データにより、サブク
ール域２３の伝熱管４に流すべき低温流体の必要流量が
演算される。これらの低温流体の必要流量に基づいて、
制御弁３２の開度調整を行なって、バイパス管２７を流
す低温流体の流量を調整することにより、サブクール域
２３における伝熱管４の流量が設定され、言い換える
と、サブクール域２３における熱交換量が制御される。Further, in the example of FIG. 1, the flow rate adjusting means 28 detects the amount of condensate in the condensate discharge line 29 by the flow meter 30, and the flow rate detection data causes it to flow to the heat transfer tube 4 in the subcool area 23. The required flow rate of the low temperature fluid to be calculated is calculated. Based on the required flow rate of these cryogenic fluids,
By adjusting the opening degree of the control valve 32 and adjusting the flow rate of the low temperature fluid flowing through the bypass pipe 27, the flow rate of the heat transfer tube 4 in the subcool region 23 is set, in other words, the heat exchange amount in the subcool region 23 is changed. Controlled.
【００１８】図３は、高温流体の凝縮及び凝縮液の冷却
と、低温流体の温度上昇との関係モデルを示している。
高温流体入口２５の高温流体の温度がＴ1 である場合、
凝縮域２２における凝縮時には、潜熱の放出により高温
流体がほぼ一定の温度Ｔc となり、サブクール域２３に
おける凝縮液の冷却によって凝縮液出口２６の凝縮液の
温度がＴ2 まで低下するものとし、この際に、低温流体
が入り口プレナム部８で温度ｔ1 ，出口プレナム部９で
温度ｔ2 となり、温度ｔ1 から温度ｔ2 まで円滑に変化
して、温度ｔ2 が温度Ｔ2 と同程度以上であれば、両者
の熱交換が理想的に行なわれたことを意味する。つま
り、前述の図４例の従来技術のように、サブクール域に
おける熱交換が不十分であると、温度Ｔc と温度Ｔ2 と
の差が少なくなり、熱交換効率が低下するが、図１及び
図２例では、温度Ｔc と温度Ｔ2 との差が大きく、サブ
クール域２３の熱交換効率の向上を図ることができる。FIG. 3 shows a model of the relationship between the condensation of the hot fluid and the cooling of the condensate and the temperature rise of the cold fluid.
When the temperature of the hot fluid at the hot fluid inlet 25 is T 1 ,
At the time of condensation in the condensing zone 22, the temperature of the high temperature fluid becomes almost constant Tc due to the release of latent heat, and the cooling of the condensate in the subcool zone 23 lowers the temperature of the condensate at the condensate outlet 26 to T 2. when the temperature t 1 cryogen in the inlet plenum section 8, next the temperature t 2 in the outlet plenum section 9, changes smoothly from the temperature t 1 to a temperature t 2, the temperature t 2 is temperature T 2 and more comparable If so, it means that the heat exchange between them was ideally performed. That is, if the heat exchange in the subcool region is insufficient as in the prior art of the example of FIG. 4 described above, the difference between the temperature T c and the temperature T 2 is reduced, and the heat exchange efficiency is reduced. Further, in the example of FIG. 2, the difference between the temperature T c and the temperature T 2 is large, and the heat exchange efficiency in the subcool region 23 can be improved.
【００１９】[0019]
【発明の効果】以上説明したように、本発明に係る横型
コンデンサによれば、以下のような効果を奏する。 （１） 熱交換室が、上下隔壁により大容積の凝縮域と
小容積のサブクール域とに区画される構成の採用によ
り、一つの本体胴部の内部で蒸気の凝縮と凝縮液の冷却
とを行なって、小型化と省スペース化とを図り、低コス
ト化を達成することができる。 （２） サブクール域に、複数の伝熱管よりも口径の大
きいバイパス管を並列接続状態に配して冷却流体と分流
させることにより、全量の冷却流体を直列的に挿通させ
て、熱交換効率を向上させることができる。 （３） バイパス管に、その内部を挿通する流体の流量
を調整する流量調整手段を配することにより、凝縮域の
大容積化とサブクール域の小容積化とを容易にして、一
層の熱効率の向上を図ることができる。 （４） 流量調整手段として、流量計、演算部及び制御
弁を付加することにより、凝縮液量に対応してサブクー
ル域の低温流体の流量を設定し、精度の高い熱交換を実
施することができる。As described above, the horizontal capacitor according to the present invention has the following effects. (1) By adopting a configuration in which the heat exchange chamber is divided into a large-volume condensing region and a small-volume subcooling region by upper and lower partition walls, vapor condensation and condensate cooling can be performed inside one main body. Therefore, it is possible to achieve miniaturization, space saving, and cost reduction. (2) By arranging bypass pipes having a larger diameter than a plurality of heat transfer pipes in a parallel connection in the subcool region and dividing the flow with the cooling fluid, the entire amount of cooling fluid is inserted in series to improve heat exchange efficiency. Can be improved. (3) By arranging a flow rate adjusting means for adjusting the flow rate of the fluid inserted through the bypass pipe, it is easy to increase the volume of the condensation region and decrease the volume of the subcool region, and to further improve the thermal efficiency. It is possible to improve. (4) By adding a flow meter, an arithmetic unit and a control valve as the flow rate adjusting means, the flow rate of the low temperature fluid in the subcool region can be set in accordance with the amount of condensed liquid, and highly accurate heat exchange can be performed. it can.
【図１】本発明に係る横型コンデンサの一実施例を示す
正断面図である。FIG. 1 is a front sectional view showing an embodiment of a horizontal capacitor according to the present invention.
【図２】本発明に係る横型コンデンサの一実施例を示す
横断面図である。FIG. 2 is a cross-sectional view showing an example of a horizontal capacitor according to the present invention.
【図３】本発明に係る横型コンデンサの熱交換時におけ
る温度変化のモデル図である。FIG. 3 is a model diagram of a temperature change during heat exchange of the horizontal capacitor according to the present invention.
【図４】蒸気凝縮に使用される熱交換器の従来例を示す
一部を切欠した正面図である。FIG. 4 is a partially cutaway front view showing a conventional example of a heat exchanger used for vapor condensation.
１ 本体胴部 ２ 管板 ３ 熱交換室 ４ 伝熱管 ５Ａ，５Ｂ バッフルプレート ６ 切欠部 ７ 基部ケーシング ８ 入り口プレナム部 ９ 出口プレナム部 １０ 管内流体用入り口 １１ 管内流体用出口 １４ 中間ケーシング ２１ 上下隔壁 ２２ 凝縮域 ２３ サブクール域 ２４ 接続口 ２５ 高温流体入口 ２６ 凝縮液出口 ２７ バイパス管 ２８ 流量調整手段 ２９ 凝縮液排出ライン ３０ 流量計 ３１ 演算部 ３２ 制御弁 1 Main Body 2 Tube Plate 3 Heat Exchange Chamber 4 Heat Transfer Tube 5A, 5B Baffle Plate 6 Notch 7 Base Casing 8 Inlet Plenum 9 Outlet Plenum 10 Inlet Fluid Inlet 11 Inlet Fluid Outlet 14 Intermediate Casing 21 Upper and Lower Partition 22 Condensation area 23 Subcool area 24 Connection port 25 High temperature fluid inlet 26 Condensate outlet 27 Bypass pipe 28 Flow rate adjusting means 29 Condensate discharge line 30 Flow meter 31 Computing section 32 Control valve
Claims (4)
熱交換室（３）の高温流体と熱交換をする複数の伝熱管
（４）が収納され、高温流体が熱交換によって凝縮状態
に導かれる横型コンデンサであって、熱交換室が、上下
隔壁（２１）により大容積の凝縮域（２２）と小容積の
サブクール域（２３）とに区画され、凝縮域及びサブク
ール域に、これらを接続する接続口（２４）と、該接続
口から離間した状態の高温流体入口（２５）及び凝縮液
出口（２６）とが配されることを特徴とする横型コンデ
ンサ。1. Inside the main body (1) in a horizontal state,
A horizontal condenser in which a plurality of heat transfer tubes (4) for exchanging heat with the high temperature fluid in the heat exchange chamber (3) are housed, and the high temperature fluid is introduced into a condensed state by heat exchange, and the heat exchange chamber includes upper and lower partition walls ( 21) is divided into a large-volume condensation area (22) and a small-volume subcool area (23), and the condensation area and the subcool area are connected to the connection port (24) and separated from the connection opening. A horizontal condenser having a hot fluid inlet (25) and a condensate outlet (26) of
（４）よりも口径の大きいバイパス管（２７）が並列接
続状態に配されることを特徴とする請求項１記載の横型
コンデンサ。2. The horizontal capacitor according to claim 1, wherein a bypass pipe (27) having a larger diameter than the plurality of heat transfer pipes (4) is arranged in parallel in the subcool region (23).
する流体の流量を調整する流量調整手段（２８）が配さ
れることを特徴とする請求項２記載の横型コンデンサ。3. The horizontal capacitor according to claim 2, wherein the bypass pipe (27) is provided with flow rate adjusting means (28) for adjusting the flow rate of the fluid passing through the inside thereof.
を検出する流量計（３０）と、該流量計に接続され流量
検出信号によりバイパス管（２７）の流量を演算する演
算部（３１）と、該演算部に接続状態にかつバイパス管
に配され演算部の指令により開度を調整する制御弁（３
２）とを具備することを特徴とする請求項３記載の横型
コンデンサ。4. A flow rate adjusting means (28), a flow meter (30) for detecting the flow rate of the condensate, and a calculation section (for calculating the flow rate of the bypass pipe (27) connected to the flow meter according to the flow rate detection signal. 31) and a control valve (3) which is connected to the arithmetic unit and is arranged in the bypass pipe to adjust the opening degree according to a command from the arithmetic unit.
2. The horizontal capacitor according to claim 3, comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23003894A JP3641840B2 (en) | 1994-09-26 | 1994-09-26 | Horizontal capacitor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23003894A JP3641840B2 (en) | 1994-09-26 | 1994-09-26 | Horizontal capacitor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0894266A true JPH0894266A (en) | 1996-04-12 |
| JP3641840B2 JP3641840B2 (en) | 2005-04-27 |
Family
ID=16901597
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23003894A Expired - Fee Related JP3641840B2 (en) | 1994-09-26 | 1994-09-26 | Horizontal capacitor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3641840B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101014535B1 (en) * | 2008-10-24 | 2011-02-14 | 기아자동차주식회사 | Heat exchanger with cap having fuel cooling pipe |
| CN106017122A (en) * | 2016-05-23 | 2016-10-12 | 中国能源建设集团广东省电力设计研究院有限公司 | Automatic adjusting system and method for water inflow flow speed of condenser cooling pipes |
| KR20180001347U (en) * | 2016-10-29 | 2018-05-10 | 김만철 | Fluid cooling device and dehumidification system including the same |
| KR20190010941A (en) * | 2017-07-24 | 2019-02-01 | 두산인프라코어 주식회사 | Heat exchanger for engine |
-
1994
- 1994-09-26 JP JP23003894A patent/JP3641840B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101014535B1 (en) * | 2008-10-24 | 2011-02-14 | 기아자동차주식회사 | Heat exchanger with cap having fuel cooling pipe |
| CN106017122A (en) * | 2016-05-23 | 2016-10-12 | 中国能源建设集团广东省电力设计研究院有限公司 | Automatic adjusting system and method for water inflow flow speed of condenser cooling pipes |
| KR20180001347U (en) * | 2016-10-29 | 2018-05-10 | 김만철 | Fluid cooling device and dehumidification system including the same |
| KR20190010941A (en) * | 2017-07-24 | 2019-02-01 | 두산인프라코어 주식회사 | Heat exchanger for engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3641840B2 (en) | 2005-04-27 |
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