JP3302782B2 - Transfer control method for solid-liquid mixed fluid - Google Patents
Transfer control method for solid-liquid mixed fluidInfo
- Publication number
- JP3302782B2 JP3302782B2 JP14842993A JP14842993A JP3302782B2 JP 3302782 B2 JP3302782 B2 JP 3302782B2 JP 14842993 A JP14842993 A JP 14842993A JP 14842993 A JP14842993 A JP 14842993A JP 3302782 B2 JP3302782 B2 JP 3302782B2
- Authority
- JP
- Japan
- Prior art keywords
- solid
- ipf
- mixed fluid
- liquid mixed
- ice
- 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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Description
【０００１】[0001]
【産業上の利用分野】本発明は、地域冷房等において、
熱源貯溜部に蓄積された冷熱を、氷等の潜熱物質と水等
の液体との固液混合流体により搬送する固液混合流体搬
送システムの冷熱量制御方法に関する。BACKGROUND OF THE INVENTION The present invention relates to
The present invention relates to a method for controlling the amount of cold energy of a solid-liquid mixed fluid transport system that transports cold stored in a heat source storage unit using a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water.
【０００２】[0002]
【従来の技術】地域冷房等において、熱源貯溜部に蓄積
されている冷熱を、負荷部に搬送する場合、単一の流体
を用いて顕熱を搬送する方法が提供されている。この場
合通常、流体の負荷側へ向かう流れの温度（往温度）は
５〜７℃、負荷側から熱源貯溜部へ向かう流れの温度
（復温度）は１０〜１３℃で以って顕熱を利用する方式
を採っており、この方式における冷熱の搬送量のコント
ロールは、流体の流量を増減することにより行ってい
る。2. Description of the Related Art In district cooling or the like, a method for transferring sensible heat using a single fluid when transferring cold stored in a heat source storage section to a load section has been provided. In this case, the temperature of the fluid flowing toward the load side (forward temperature) is usually 5 to 7 ° C., and the temperature of the flow from the load side to the heat source storage section (recovery temperature) is 10 to 13 ° C. In this method, the amount of cold heat transferred is controlled by increasing or decreasing the flow rate of the fluid.
【０００３】一方近年は、前記顕熱と併せて潜熱を利用
して冷熱を搬送する方式、即ち冷熱の移送を固液二相の
混合流体（例えば氷とブラインの固液混合流体）によっ
て行う方式が多く採用されるようになった。かかる冷暖
房システムにあっては、固液混合流体中の潜熱物質混合
充填率（以下“ＩＰＦ”と称する）を、負荷の変動又は
前記熱源貯溜部内のＩＰＦの変動に応じて調整して、固
液混合流体を前記負荷に供給する必要がある。On the other hand, in recent years, a system in which cold heat is conveyed using latent heat in combination with the sensible heat, that is, a system in which cold heat is transferred by a solid-liquid two-phase mixed fluid (for example, a solid-liquid mixed fluid of ice and brine). Became more widely adopted. In such a cooling and heating system, the solid-liquid mixed fluid filling rate (hereinafter, referred to as “IPF”) is adjusted according to a load fluctuation or a fluctuation of the IPF in the heat source storage section, and the solid-liquid A mixed fluid needs to be supplied to the load.
【０００４】図１５に、固液混合流体搬送システムの従
来例を示す。図において１は氷と水との固液混合流体が
収容される熱源貯溜部即ち氷槽であり、該貯氷槽１内の
固液混合流体は、搬送主管７に設けられた搬送ポンプ２
により加圧、吐出され、吐出側に設けられたＩＰＦ調整
器１４に導入され、ここで一部の水が抜き出され、水抜
き配管１６を経て貯氷槽１に戻される。貯氷槽１に戻さ
れる水の流量はＩＰＦ調整器１４の下流に設けられた質
量流量計６の密度値の検出により調節される。そしてＩ
ＰＦ制御の一例を数値により説明すると、所要の供給流
量をＱｍ3 ／ｍｉｎとし、所要のＩＰＦが３０％である
として、貯氷槽１内の固液混合流体即ち氷水のＩＰＦが
１０％であるときは、貯氷槽１の氷水流量３Ｑが搬送ポ
ンプ２により４ｋｇ／ｃｍ2 ・Ｇの圧力に加圧されて搬
送主管７に送り出され、ＩＰＦ調整器１４により２Ｑの
水流量が水抜き配管１６を経て貯氷槽１に戻され、これ
によりＩＰＦを３０％に調節された氷水流量Ｑが地域導
管８を経て負荷９に供給され冷熱を供給する。なお、８
ａは地域戻り導管、１５は水抜き流量を制御する自動調
整弁である。FIG. 15 shows a conventional example of a solid-liquid mixed fluid transfer system. In FIG. 1, reference numeral 1 denotes a heat source storage unit or an ice tank in which a solid-liquid mixed fluid of ice and water is stored, and a solid-liquid mixed fluid in the ice storage tank 1 is supplied by a transfer pump 2 provided in a transfer main pipe 7.
, And is introduced into the IPF adjuster 14 provided on the discharge side, where a part of the water is extracted and returned to the ice storage tank 1 via the drainage pipe 16. The flow rate of the water returned to the ice storage tank 1 is adjusted by detecting the density value of the mass flow meter 6 provided downstream of the IPF regulator 14. And I
An example of the PF control will be described by numerical values. When the required supply flow rate is Qm 3 / min, the required IPF is 30%, and the solid-liquid mixed fluid in the ice storage tank 1, that is, the IPF of the ice water is 10%. The ice water flow rate 3Q in the ice storage tank 1 is pressurized to a pressure of 4 kg / cm 2 · G by the transport pump 2 and sent out to the transport main pipe 7, and the IPQ regulator 14 reduces the 2Q water flow rate through the drain pipe 16. The ice water flow rate Q whose IPF is adjusted to 30% is returned to the ice storage tank 1, and is supplied to the load 9 via the regional conduit 8 to supply cold heat. In addition, 8
a is a regional return conduit, and 15 is an automatic regulating valve for controlling the drainage flow rate.
【０００５】そして前記ＩＰＦ調整器１４は例えば図１
６に示すように、ＩＰＦ調整器１４においては、貯氷槽
１からの固液混合流体が入口Ａから口径０．５ｍｍ程度
の孔１４ｂが穿設されたパンチングメタル製の管１４ａ
に導入され、該孔１４ｂから水のみが抜き取られて水出
口Ｃから水抜き配管１６を経て貯氷槽１に戻されること
により、ＩＰＦが調整される。[0005] The IPF adjuster 14 is, for example, shown in FIG.
As shown in FIG. 6, in the IPF adjuster 14, a solid-liquid mixed fluid from the ice storage tank 1 is filled with a hole 14b having a diameter of about 0.5 mm from the inlet A and made of a punched metal pipe 14a.
The IPF is adjusted by extracting only water from the hole 14b and returning the water from the water outlet C to the ice storage tank 1 via the drainage pipe 16.
【０００６】[0006]
【発明が解決しようとする課題】前記従来システムにお
いては、夜間等に負荷側が極少量の冷熱しか必要としな
い場合、冷熱量の減少操作を固液混合流体の流量を減少
させることにより行っている。しかしながら、この方式
によると、固液混合流体の流量に対する前記ＩＰＦの調
整の影響により、固液混合流体の搬送主管等の流体管路
の圧力損失は、液体（水）のみの場合に較べて大きくな
り、システム全体の効率が低下するとともに、流体管路
内に氷（潜熱物質）が詰り、配管の閉塞、破壊の発生を
誘起する。一方、かかる不具合を回避するために固液混
合流体の減少を抑制すると、必要以上の冷熱が負荷側へ
搬送され、潜熱の一部が利用されずに熱源貯溜部に戻っ
てくることとなり、搬送ポンプの動力が無駄に費される
こととなる。In the conventional system, when the load side needs only a small amount of cold heat at night or the like, the operation of reducing the amount of cold heat is performed by reducing the flow rate of the solid-liquid mixed fluid. . However, according to this method, due to the influence of the adjustment of the IPF on the flow rate of the solid-liquid mixed fluid, the pressure loss in the fluid conduit such as the main pipe for transporting the solid-liquid mixed fluid is larger than that in the case of only liquid (water). As a result, the efficiency of the entire system is reduced, and ice (latent heat substance) is clogged in the fluid pipeline, which causes blockage and breakage of the pipeline. On the other hand, if the reduction of the solid-liquid mixed fluid is suppressed in order to avoid such a problem, unnecessarily cold heat is transferred to the load side, and part of the latent heat returns to the heat source storage unit without being used, and the transfer is performed. The power of the pump is wasted.
【０００７】本発明はかかる従来技術の欠点に鑑み、負
荷の変動に応じて固液混合流体の流速及びＩＰＦを制御
することにより、負荷の変動による圧力損失を低減し、
搬送ポンプ動力の浪費を防止してシステムの効率を向上
せしめるとともに、配管系の閉塞の発生を防止する固液
混合流体搬送システムの冷熱量制御方法を提供する事を
目的とする。本発明の他の目的は、水抜き配管路への氷
の流出が多くなり、搬送固液混合流体の流量が多くなっ
ても、固液混合流体の搬送動力の増加の無い固液混合流
体の搬送制御方法を提供することにある。[0007] In view of the drawbacks of the prior art, the present invention controls the flow rate and IPF of the solid-liquid mixed fluid according to the load fluctuation, thereby reducing the pressure loss due to the load fluctuation,
It is an object of the present invention to provide a method for controlling the amount of cooling and heating of a solid-liquid mixed fluid transfer system, which prevents waste of power of a transfer pump, improves efficiency of the system, and prevents occurrence of blockage of a piping system. Another object of the present invention is to increase the flow of ice into the drainage pipe line and increase the flow rate of the solid-liquid mixed fluid even if the flow rate of the solid-liquid mixed fluid is large. An object of the present invention is to provide a transfer control method.
【０００８】[0008]
【課題を解決するための手段】本発明に至った経過を順
を追って説明する。図７は、氷等の潜熱物質と水等の液
体との固液混合流体を、図１に示すように冷熱源貯溜部
１から搬送主管７を介して負荷部９に搬送するシステム
において、固液混合流体の管７内の平均流速（以下、単
に流速）Ｖｍ〔ｍ／ｓ〕と内径５０ｍｍの配管における
圧力損失（ΔＰｍｍＡｑ／ｍ……配管１ｍ当りの圧力損
失を水柱ｍｍで表わしたもの）との関係を示すグラフで
あって、ＩＰＦを０％から２９％まで６段階に分け、流
速Ｖｍと圧力損失ΔＰとの関係をプロットしたものであ
る。このグラフによれば、ＩＰＦが小さくなる程、配管
における圧力損失ΔＰが減少することが分る。The process leading to the present invention will be described step by step. FIG. 7 shows a system for transferring a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water from the cold heat source storage unit 1 to the load unit 9 via the transfer main pipe 7 as shown in FIG. The average flow velocity (hereinafter simply referred to as flow velocity) Vm [m / s] of the liquid mixed fluid in the pipe 7 and the pressure loss in a pipe with an inner diameter of 50 mm (ΔPmmAq / m... 5 is a graph showing the relationship between the flow rate Vm and the pressure loss ΔP, in which the IPF is divided into six stages from 0% to 29%. According to this graph, the pressure loss ΔP in the pipe decreases as the IPF decreases.
【０００９】図８は図７の実験点を、横軸にＩＰＦ、縦
軸に圧力損失ΔＰをとって表わしたものであり、流速Ｖ
ｍを０．５３から２まで５段階に分けている。これによ
れば、高い流速Ｖｍ＝２．００ｍ／ｓよりも低い流速Ｖ
ｍ＝０．５３ｍ／ｓの方が、すなわち、流速Ｖｍが小さ
くなるほど、ＩＰＦを減少させたときの圧力損失ΔＰの
低下量が大きいことが分る。FIG. 8 shows the experimental points of FIG. 7 with IPF on the horizontal axis and pressure loss ΔP on the vertical axis.
m is divided into five stages from 0.53 to 2. According to this, the flow velocity Vm is lower than the high flow velocity Vm = 2.00 m / s.
It can be seen that m = 0.53 m / s, that is, the lower the flow velocity Vm, the greater the decrease in the pressure loss ΔP when the IPF is reduced.
【００１０】また図９は前記混合流体の流速Ｖｍ〔ｍ／
ｓ〕を一定とした場合において、ＩＰＦと「混合流体を
搬送する理論動力Ｗ当りの搬送冷熱量ｑ、すなわちｑ／
ｗ」との関係を示すグラフであって、流速Ｖｍ〔ｍ／
ｓ〕を０．５３から２．００までの５段階においてそれ
ぞれ一定にした場合において、ＩＰＦとｑ／ｗとの関係
をプロットしたものである。このグラフによれば、流速
Ｖｍ＝一定においてｑ／ｗが最大になるＩＰＦが存在す
ることが分る。このＩＰＦの最大値を適正ＩＰＦと呼称
し、この適正ＩＰＦと流速Ｖｍとの関係をとってプロッ
トしたのが図１０である。このグラフによれば、適正Ｉ
ＰＦとＶｍとは直線的な関係にあることが分る。FIG. 9 shows a flow rate Vm [m / m /
s] is constant, the IPF and “the amount of transport cooling heat q per theoretical power W for transporting the mixed fluid, ie, q /
w "and a flow rate Vm [m /
[s] is plotted in a case where the values are fixed at five levels from 0.53 to 2.00, respectively, between IPF and q / w. According to this graph, it is found that there is an IPF in which q / w becomes maximum when the flow velocity Vm is constant. The maximum value of the IPF is referred to as an appropriate IPF, and FIG. 10 is a graph plotting the relationship between the appropriate IPF and the flow velocity Vm. According to this graph, the proper I
It can be seen that PF and Vm have a linear relationship.
【００１１】本発明はかかる知見に着目して、氷等の潜
熱物質と水等の液体との固液混合流体を収容する熱源貯
溜部から搬送ポンプ及び搬送管を介して前記混合流体を
負荷部に搬送する固液混合流体の搬送制御方法におい
て、前記負荷側に供給される固液混合流体の搬送動力当
りの搬送熱量が最大となる、前記搬送管内における前記
混合流体のＩＰＦと管内流速との関係（アルゴリズム）
を例えば図１０及び図１２〜１４から予め求め、負荷側
の熱負荷変動に対応させて固液混合流体の搬送冷却量が
最大となるように前記アルゴリズムに基づいて、搬送管
内の流速又は／及びＩＰＦを制御することを第１の要旨
とする。The present invention pays attention to such knowledge, and loads the mixed fluid from a heat source storage section containing a solid-liquid mixed fluid of a latent heat substance such as ice and a liquid such as water via a transport pump and a transport pipe to a load section. In the method for controlling the transport of the solid-liquid mixed fluid to be transported to the load side, the amount of heat transferred per unit of transport power of the solid-liquid mixed fluid supplied to the load side is maximized. Relationships (algorithms)
10 and FIGS. 12 to 14 in advance, and based on the algorithm, the flow rate and / or the flow rate in the transfer pipe are determined based on the algorithm so that the transfer cooling amount of the solid-liquid mixed fluid is maximized in accordance with the heat load fluctuation on the load side. The first point is to control the IPF.
【００１２】この場合前記ＩＰＦの制御は、前記熱源貯
溜部内に設置された攪拌機の回転制御により行なっても
よく、又前記ＩＰＦを調整するＩＰＦ調整器から前記熱
源貯溜部への液体の抜き量を制御する事により行なって
もよく、更に、前記熱源貯溜部の固液混合流体出口近傍
に設けたメッシュの異なる金網または穴径の異なるパン
チングメタルを設けた場合において、前記メッシュ又は
パンチングメタルの穴径を切り換えて行なう事も出来
る。又前記熱源貯溜部内に、氷等の潜熱物質を攪拌し、
搬送管路側への氷寄せ若しくは取り出しを行なうための
一又は複数の攪拌機を設けた場合、前記攪拌機の運転間
隔および運転周波数を貯氷ＩＰＦ、搬送ＩＰＦに応じて
適宜に変化させることにより、攪拌動力を削減出来る。In this case, the control of the IPF may be performed by controlling the rotation of a stirrer installed in the heat source storage unit, and the amount of liquid drained from the IPF adjuster for adjusting the IPF to the heat source storage unit may be controlled. In the case where a wire mesh having a different mesh or a punching metal having a different hole diameter is provided near the solid-liquid mixed fluid outlet of the heat source storage section, the hole diameter of the mesh or the punching metal may be controlled. Can be switched. Also, in the heat source storage section, a latent heat substance such as ice is stirred,
When one or a plurality of stirrers are provided for bringing or removing ice to or from the transfer pipeline side, the stirrer power is changed by appropriately changing the operation interval and operation frequency of the stirrers according to the ice storage IPF and the transfer IPF. Can be reduced.
【００１３】そして本発明は、前記制御を容易にするた
めに、前記負荷側に供給される搬送熱量が、その最大値
からの割合に応じて、ＩＰＦを一定にして前記管内流速
を制御するか、若しくは管内流速を一定にしてＩＰＦを
制御するかを選択させるように制御することも要旨とす
る。そしてこの場合管内流速を一定にしてＩＰＦを制御
する場合において、前記ＩＰＦを段階的に制御すること
により一層の制御の簡略化と容易化が達成される。即ち
具体的には、負荷が部分負荷領域において変動した場
合、負荷がその最大値から所定の百分比の値の範囲にあ
るときは、固液混合流体のＩＰＦを一定に保持して固液
混合流体の流速を調節し、負荷が前記所定の百分比値よ
り小さい範囲にあるときは固液混合流体の流速を一定に
保持してＩＰＦを段階的に調節するのがよい。According to the present invention, in order to facilitate the control, the amount of heat transferred to the load side is controlled by controlling the flow rate in the pipe by keeping the IPF constant according to the ratio from the maximum value. In addition, it is also essential to control so as to select whether to control the IPF while keeping the flow velocity in the pipe constant .
You. In this case, in the case of controlling the IPF while keeping the pipe flow rate constant, further simplification and simplification of the control can be achieved by controlling the IPF stepwise. Specifically, when the load fluctuates in the partial load region, and when the load is within a range of a predetermined percentage value from the maximum value, the IPF of the solid-liquid mixed fluid is kept constant and the solid-liquid mixed fluid is maintained. When the load is in a range smaller than the predetermined percentage value, the flow rate of the solid-liquid mixed fluid is preferably kept constant to adjust the IPF stepwise.
【００１４】[0014]
【実施例】以下図面を参照して本発明の実施例について
詳細に説明する。但し、この実施例に記載されている構
成要素の形状、数値、仕様、相対配置等、特に特定的な
記載がない限りは、この発明の範囲をそれのみに限定す
る趣旨でなく、単なる説明例に過ぎないものである。Embodiments of the present invention will be described below in detail with reference to the drawings. However, unless otherwise specified, the shapes, numerical values, specifications, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention thereto, but are merely illustrative examples. It is nothing more than a thing.
【００１５】図１乃至図３に本発明が適用される固液混
合流体搬送装置を示す。図において、１は氷と水との固
液混合流体が収容される熱源貯溜部、９は負荷部、７は
搬送主管、２は該搬送主管路に設けられた１又は複数の
搬送ポンプ、８は戻り導管、５２は前記貯溜部１内に設
置された１又は複数の攪拌機である。かかる装置におい
て、負荷部９の負荷即ち要求される搬送冷熱量が変化す
ると、それに応じて、搬送ポンプ２はその運転台数又は
／及び回転数を調節可能に、また熱源貯溜部１内の攪拌
機５２は、その運転台数又は／及び回転数を調節可能に
構成されている。前記攪拌機５２の機能について図２、
図３を参照して説明すると、図２においては攪拌機５２
の回転数が高いので熱源貯溜部１内の固液混合流体は
（イ）のように大まわりに循環する。したがって、搬送
主管７から流出する固液混合流体のＩＰＦは大きい。と
ころが攪拌機５２の回転数が低くなると、図３のよう
に、攪拌機５２による攪拌力が小さくなるため、固液混
合流体は（ロ）のように小まわりに循環することにな
り、氷（潜熱物質）は浮き上って上部に溜るようになる
ので、搬送主管７から流出する氷の量が減少し、固液混
合流体のＩＰＦが小さくなる。FIGS. 1 to 3 show a solid-liquid mixed fluid conveying apparatus to which the present invention is applied. In the drawing, reference numeral 1 denotes a heat source storage unit for storing a solid-liquid mixed fluid of ice and water, 9 denotes a load unit, 7 denotes a main transport pipe, 2 denotes one or a plurality of transport pumps provided in the main transport pipe, 8 Is a return conduit, and 52 is one or a plurality of stirrers installed in the storage unit 1. In such an apparatus, when the load of the load unit 9, that is, the required amount of transferred cooling heat, changes, the number of operating pumps and / or the number of rotations of the transfer pump 2 can be adjusted accordingly, and the stirrer 52 in the heat source storage unit 1 can be adjusted. Is configured such that its operating number and / or rotation speed can be adjusted. The function of the stirrer 52 is shown in FIG.
With reference to FIG. 3, in FIG.
Is high, the solid-liquid mixed fluid in the heat source storage section 1 circulates largely as shown in FIG. Therefore, the IPF of the solid-liquid mixed fluid flowing out of the transport main pipe 7 is large. However, when the rotation speed of the stirrer 52 decreases, the stirring force of the stirrer 52 decreases as shown in FIG. 3, so that the solid-liquid mixed fluid circulates around the small circle as shown in FIG. ) Rises and accumulates at the upper part, so that the amount of ice flowing out of the main transport pipe 7 decreases, and the IPF of the solid-liquid mixed fluid decreases.
【００１６】従ってかかる装置によれば前記負荷側に供
給される固液混合流体の搬送動力当りの搬送熱量が最大
となる、前記搬送管内における前記混合流体のＩＰＦと
管内流速との関係（アルゴリズム）を例えば図１０及び
図１２〜１４から予め求め、負荷側の熱負荷変動に対応
させて固液混合流体の搬送冷却量が最大となるように前
記アルゴリズムに基づいて、搬送ポンプ２の運転台数又
は／及び回転数と、熱源貯溜部１内の攪拌機５２の運転
台数又は／及び回転数とを夫々調節する事により負荷側
の熱負荷変動に対応させて固液混合流体の搬送冷却量が
最大となるように前記アルゴリズムに基づいて、搬送主
管の流速又は／及びＩＰＦを制御する事が出来る。Therefore, according to such an apparatus, the relation between the IPF of the mixed fluid in the transport pipe and the flow velocity in the pipe, which maximizes the amount of heat transferred per transport power of the solid-liquid mixed fluid supplied to the load side (algorithm) 10 and FIGS. 12 to 14 in advance, and based on the algorithm, the operating number of the transport pumps 2 or the number of operating the transport pumps 2 so that the transport cooling amount of the solid-liquid mixed fluid is maximized in accordance with the thermal load fluctuation on the load side. And / or the number of rotations and the operating number and / or the number of rotations of the stirrer 52 in the heat source storage unit 1 are adjusted to correspond to the heat load fluctuation on the load side, thereby maximizing the transfer cooling amount of the solid-liquid mixed fluid. Thus, the flow rate and / or the IPF of the main transport pipe can be controlled based on the algorithm.
【００１７】図４は本発明が適用される固液混合流体搬
送装置の第２実施例である。この実施例では搬送ポンプ
２の吐出側にＩＰＦ調整器１１を設けて、搬送ポンプ２
から吐出された固液混合流体から水を一部分離して水抜
き配管１６を経て熱源貯溜部１に戻すようにしている。
負荷部９の負荷（要求される搬送冷熱量）が変化したと
きは、それに応じて搬送ポンプ２の運転台数及び回転数
を調節して混合流体の流速を制御するとともに、水抜き
配管１６に設けた流量調節弁５３の弁開度を調節するこ
とによりＩＰＦ調整器１１から水抜き配管１６に流入す
る水の量を調節し、負荷部９に搬送する混合流体のＩＰ
Ｆを前記制御された流速における混合流体の搬送理論動
力当りの搬送冷熱量が適正ＩＰＦになるように制御す
る。例えば流量調節弁５３を適量閉じることにより分離
される水の量が減り、ＩＰＦを適正値まで小さくするこ
とができる。FIG. 4 shows a second embodiment of the solid-liquid mixed fluid transfer device to which the present invention is applied. In this embodiment, an IPF adjuster 11 is provided on the discharge side of the transport pump 2 so that the transport pump 2
Part of the water is separated from the solid-liquid mixed fluid discharged from the tank and returned to the heat source storage section 1 through the drain pipe 16.
When the load of the load section 9 (the required amount of cooling and transferring heat) changes, the number of operating pumps and the number of rotations of the transfer pump 2 are adjusted accordingly to control the flow rate of the mixed fluid, and provided in the drainage pipe 16. By adjusting the valve opening of the flow control valve 53, the amount of water flowing from the IPF regulator 11 to the drain pipe 16 is adjusted, and the IP of the mixed fluid conveyed to the load unit 9 is adjusted.
F is controlled such that the amount of cold transferred per theoretical transport power of the mixed fluid at the above-mentioned controlled flow rate becomes an appropriate IPF. For example, by closing the flow control valve 53 by an appropriate amount, the amount of separated water is reduced, and the IPF can be reduced to an appropriate value.
【００１８】図５及び図６は本発明の本発明が適用され
る固液混合流体搬送装置の第３実施例で熱源貯溜部１の
要部構成を示す。熱源貯溜部１の内壁には攪拌機５２及
び回転板５４が設けてあり、該回転板５４はステップモ
ーター等の駆動源５５に回転軸５６を介して直結され回
転駆動される。なお、該回転板５４は手動で回転させる
こともできる。FIGS. 5 and 6 show a main part of a heat source storage unit 1 in a third embodiment of a solid-liquid mixed fluid transporting apparatus to which the present invention is applied. A stirrer 52 and a rotary plate 54 are provided on the inner wall of the heat source storage unit 1, and the rotary plate 54 is directly connected to a drive source 55 such as a step motor via a rotary shaft 56 and is driven to rotate. The rotating plate 54 can be manually rotated.
【００１９】そして前記回転板５４にはメッシュの異な
る金網または穴径の異なるパンチングメタル５５ａ、５
５ｂ、５５ｃ、５５ｄが円周方向に取付けられている。
７ａは搬送主管７の固液混合流体取出口であり、前記回
転板５４を適宜回転させて、適正ＩＰＦに適合するメッ
シュの金網または穴径のパンチングメタルを混合流体取
出口７ａの位置に来るように設置して駆動源５５により
適宜角度回転させてパンチングメタル５５ａ、５５ｂ、
５５ｃ、５５ｄの穴径を切り換えて前記ＩＰＦを調整
し、これにより搬送される固液混合流体のＩＰＦを制御
することができる。The rotating plate 54 is provided with wire meshes having different meshes or punching metals 55a, 5a having different hole diameters.
5b, 55c and 55d are mounted in the circumferential direction.
Reference numeral 7a denotes a solid-liquid mixed fluid outlet of the transport main pipe 7, and the rotating plate 54 is appropriately rotated so that a mesh wire mesh or a punched metal having a hole diameter conforming to an appropriate IPF comes to the position of the mixed fluid outlet 7a. , And rotated by an appropriate angle by the drive source 55 to punch metal 55a, 55b,
The IPF is adjusted by switching the hole diameters of 55c and 55d, whereby the IPF of the conveyed solid-liquid mixed fluid can be controlled.
【００２０】以上、本発明の異なる３つの実施例につい
ては説明したが、負荷（要求される搬送冷熱量）の値は
次のようにして決めることができる。すなわち、図１１
において、負荷冷水の流量Ｑ２、負荷冷水の入口温度Ｔ
２、負荷冷水の出口温度Ｔ３を検出することにより求め
る方法と、固液混合流体の流量Ｑ１、固液混合流体のＩ
ＰＦ、固液混合流体の戻り水温度Ｔ１を検出することに
より求める方法がある。負荷９の値が決まれば、それに
見合う固液混合流体の流速、ＩＰＦは図１０に基づき図
１２のように決められるので図１２より搬送すべき冷熱
量に最適な流速とＩＰＦを求めて固液混合流体の制御を
することができる。Although the three different embodiments of the present invention have been described above, the value of the load (required amount of cooling and transporting heat) can be determined as follows. That is, FIG.
, The flow rate of the load chilled water Q2 and the inlet temperature T of the load chilled water
2. The method of obtaining by detecting the outlet temperature T3 of the load cold water, the flow rate Q1 of the solid-liquid mixed fluid, and the I
There is a method of obtaining the temperature by detecting the return water temperature T1 of the PF and the solid-liquid mixed fluid. When the value of the load 9 is determined, the flow rate and IPF of the solid-liquid mixed fluid corresponding to the load 9 are determined as shown in FIG. 12 based on FIG. It is possible to control the mixed fluid.
【００２１】更に本発明は次のようにして実施すること
もできる。すなわち、図１２を用いる前記のような固液
混合流体の制御よりも簡単な、流速とＩＰＦの制御方法
の実施例（例えば内径１５０ｍｍの配管の場合）を図１
３及び図１４によって説明する。両図は、横軸に負荷
（要求される搬送冷熱量）、縦軸には配管内を流れてい
る固液混合流体のＩＰＦ〔％〕、流速Ｖ〔ｍ／ｓ〕をそ
れぞれ採っている。Further, the present invention can be carried out as follows. That is, an embodiment (for example, in the case of a pipe having an inner diameter of 150 mm) of a flow rate and IPF control method which is simpler than the control of the solid-liquid mixed fluid as described above using FIG.
3 and FIG. In both figures, the horizontal axis represents the load (required amount of transport cooling and heating), and the vertical axis represents the IPF [%] and the flow velocity V [m / s] of the solid-liquid mixed fluid flowing in the pipe.
【００２２】図１３は、負荷が部分負荷領域において変
動する場合を想定して４段階に分け、各段階におけるＩ
ＰＦはそれぞれ一定とするとともに各段階ごとのＩＰＦ
は互いに異なる値とし、混合流体の搬送主管７内の流速
は各段階において負荷の変動にしたがいそれぞれ連続的
に変化させている。これにより、検出された部分負荷の
大きさに応じて、同図からそれに対応する搬送冷熱量の
段階が選択され、該段階において検出された前記負荷に
対応するＩＰＦと流速とが選択されて固液混合流体の制
御を行なう。このような段階的制御は、図１２のように
ＩＰＦと流速とを共に連続的に制御する場合に比べて効
率は幾分低くなるが、なお従来技術に比べて大幅すぐれ
ており、制御方法は簡略化される。FIG. 13 shows a case in which the load fluctuates in the partial load region, and the load is divided into four stages.
PF is fixed and IPF for each stage
Are different from each other, and the flow velocity of the mixed fluid in the main transport pipe 7 is continuously changed at each stage in accordance with the fluctuation of the load. Thereby, the stage of the amount of transferred cooling heat corresponding to the detected partial load is selected from the figure, and the IPF and the flow velocity corresponding to the load detected in the stage are selected and fixed. The liquid mixture fluid is controlled. Such stepwise control has a somewhat lower efficiency than the case where both the IPF and the flow rate are continuously controlled as shown in FIG. 12, but is still significantly better than the conventional technique, and the control method is as follows. Simplified.
【００２３】図１４は、本発明の制御方法の他の実施例
であって、負荷が部分領域において変動する場合、或る
所定の部分負荷まですなわち全負荷から所定の部分負荷
までの比較的広い領域においては、ＩＰＦを一定にして
固液混合流体の流速を検出された負荷に応じて変化させ
る制御を行ない、前記所定の部分負荷よりも負荷が小さ
い領域においては、ＩＰＦを負荷すなわち要求される搬
送冷熱量に応じて低下させる。すなわち、地域冷房にお
いて最大負荷時での搬送主管７内の流速は２．０〜３．
０ｍ／ｓとなるよう配管サイズが選定される。この制御
方法においては、部分負荷時はＩＰＦを２０〜３０％の
範囲で一定に維持し、負荷が最大負荷の３０〜５０％ま
での領域では先ず流速（供給流量）を減少させ、それよ
りも負荷の小さい領域では流速（最低流速０．５ｍ／
ｓ）を下げずに一定とし、ＩＰＦを低くして負荷に応じ
た冷熱供給を行なう。なお、前記最低流速は搬送主管内
で潜熱物質（氷）が停滞しない流速とする。FIG. 14 shows another embodiment of the control method of the present invention. When the load fluctuates in a partial area, the control method is relatively wide from a predetermined partial load, that is, from a full load to a predetermined partial load. In the region, the IPF is controlled to be constant and the flow rate of the solid-liquid mixed fluid is changed in accordance with the detected load. In the region where the load is smaller than the predetermined partial load, the IPF is loaded, that is, required. Decrease in accordance with the amount of cold heat transported. That is, the flow rate in the main transport pipe 7 at the time of the maximum load in the district cooling is 2.0 to 3.0.
The pipe size is selected to be 0 m / s. In this control method, the IPF is kept constant in the range of 20 to 30% at the time of partial load, and the flow velocity (supply flow rate) is first reduced in the range where the load is 30 to 50% of the maximum load. In areas where the load is small, the flow velocity (minimum flow velocity 0.5 m /
s) is kept constant without lowering, and the IPF is lowered to supply cold heat according to the load. The minimum flow velocity is a flow velocity at which the latent heat substance (ice) does not stay in the main transport pipe.
【００２４】図１４によれば、負荷すなわち要求される
搬送冷熱量が１８００ｋＷ位まではＩＰＦを一定とし固
液混合流体の流速を変化させる制御を行ない、負荷が前
記値よりも小さい領域においては、検出された負荷に対
応するＩＰＦと流速とが選択されこれに適応した固液混
合流体の制御を行なう。このような制御は、図１２のよ
うなＩＰＦと流速とを共に連続的に制御する場合に比べ
ると効率は低くなるが、従来技術よりはまさっており、
制御方法は前記は第４実施例よりもさらに簡単になる。
尚、以上の実施例は地域冷房システムに適用されるの場
合であるが、本発明はこれに限定されることなく、暖房
の場合も含み、従って「負荷」には「冷却負荷」と「加
熱負荷」とを、「熱源貯溜部」には「貯氷槽」と「高熱
源」をそれぞれ含む。According to FIG. 14, control is performed to keep the IPF constant and change the flow velocity of the solid-liquid mixed fluid until the load, that is, the required amount of transferred cooling and heating is about 1800 kW, and in a region where the load is smaller than the above value, The IPF and the flow velocity corresponding to the detected load are selected, and the control of the solid-liquid mixed fluid is performed according to the selected IPF and flow velocity. Such control is less efficient than the case where both the IPF and the flow velocity are continuously controlled as shown in FIG. 12, but is superior to the prior art.
The control method is simpler than in the fourth embodiment.
Although the above embodiments are applied to the district cooling system, the present invention is not limited to this, and includes the case of heating, and accordingly, the “load” includes “cooling load” and “heating”. The "heat source storage part" includes an "ice storage tank" and a "high heat source".
【００２５】さて、例えば図１に記載したシステムにお
いて、貯氷槽１内に流動性を有する氷水を夜間に貯蔵
し、昼間にポンプ２により取り出して、その冷熱を空調
等に用いる空調システムを考える。その空調システムの
貯氷槽１においては、氷水を放置しておくと、氷水同士
が固着し、流動性が失われる、表面の空気に接する氷が
氷塊となる搬送管路７中に閉塞の原因となってしまうな
ど、システム運用上の障害となる為に、氷を貯蔵する夜
間に、氷水を攪拌する必要がある。また、又昼間時にお
いても取り出し口７ａからポンプ２で吸引するだけで氷
を取り出そうとしても水しか流出しない。For example, in the system shown in FIG. 1, an air conditioning system in which ice water having fluidity is stored in an ice storage tank 1 at night, taken out by a pump 2 in the daytime, and its cold heat is used for air conditioning or the like will be considered. In the ice storage tank 1 of the air conditioning system, if the ice water is left unattended, the ice water adheres to each other and loses fluidity. It is necessary to stir the ice water during the night of storing the ice in order to hinder the operation of the system, for example. In addition, even in the daytime, only water is flowed out when trying to extract ice only by suctioning the pump 2 from the outlet 7a.
【００２６】したがって、図１８（Ａ）に示すように、
氷水を取り出してその冷熱を利用する昼間には、取り出
し口７ａの前に、取り出し用の攪拌機５２（ＷＭ１）を
設置し、氷と水を攪拌して混合し、氷を取り出す必要が
ある。また、氷水を取り出しているうちに、取り出し口
７ａの前の氷が少なくなるので、氷寄せ用の攪拌機５２
（ＷＭ２）を運転するなどして、取り出し口１ａの前に
氷を寄せる必要がある。この場合夜間、攪拌機５２を運
転する際、常時運転しては消費電力量が大きくなってし
まうので、ＷＭ１、ＷＭ２を間欠的に運転する。その
時、運転間隔及び運転周波数を、最大貯氷ＩＰＦに合わ
せて一定にしていたので、貯氷ＩＰＦが小さいときは、
氷水の見かけの粘度が小さく水に近いため、氷水が波立
つほど攪拌してしまい無駄な攪拌動力を消費していた。
同様に昼間は、常時運転する取り出し用の攪拌機５２
（ＷＭ１）の運転周波数を、最大貯氷ＩＰＦに合わせて
一定にしていたので、貯氷ＩＰＦが小さいときは、氷水
の見かけの粘度が小さく水に近いため、氷水が波立つほ
ど攪拌してしまい無駄な攪拌動力を消費していた。さら
に、間欠的に運転する氷寄せ用の攪拌機５２（ＷＭ２）
の運転間隔および運転周波数を、貯氷ＩＰＦに合わせて
一定にしていたので、貯氷ＩＰＦが小さいときは、氷水
の見かけの粘土が小さく水に近いため、氷水が波立つほ
ど攪拌してしまい無駄な攪拌動力を消費していた。Therefore, as shown in FIG.
In the daytime when ice water is taken out and the cold heat is used, it is necessary to install a stirrer 52 (WM1) for taking out in front of the take-out port 7a, stir and mix the ice and water, and take out the ice. Also, while the ice water is being taken out, the amount of ice in front of the take-out port 7a is reduced.
It is necessary to drive the (WM2) to bring ice in front of the outlet 1a. In this case, when the stirrer 52 is operated at night, the power consumption becomes large if the stirrer 52 is always operated. Therefore, the WM1 and WM2 are operated intermittently. At that time, since the operation interval and the operation frequency were kept constant in accordance with the maximum ice storage IPF, when the ice storage IPF was small,
Since the apparent viscosity of the ice water was small and close to that of the water, the ice water was agitated so as to undulate, consuming unnecessary stirring power.
Similarly, in the daytime, a stirrer 52 for taking out which is constantly operated.
Since the operating frequency of (WM1) was kept constant in accordance with the maximum ice storage IPF, when the ice storage IPF was small, the apparent viscosity of the ice water was small and close to water, so that the ice water was agitated so that it became wavy and wasted. The stirring power was consumed. Furthermore, an intermittently operating ice stirrer 52 (WM2)
Since the operating interval and operating frequency of the ice storage were constant in accordance with the ice storage IPF, when the ice storage IPF was small, the apparent clay of the ice water was small and close to the water. Was consuming power.
【００２７】従ってこの様な場合、攪拌機５２の運転間
隔および運転周波数を貯氷ＩＰＦ、搬送ＩＰＦに応じて
適切に変化させることにより、攪拌動力を削減出来る。
尚、貯氷ＩＰＦは、氷水の温度で検知ることが出来、又
搬送ＩＰＦは、搬送する氷水の密度で検知することがで
きる。そして運転間隔はシーケンサを用いて変化させる
ことができ、運転周波数は、攪拌機５２の駆動モ−タの
インバータで変化させることができる。Therefore, in such a case, the stirring power can be reduced by appropriately changing the operation interval and operation frequency of the stirrer 52 according to the ice storage IPF and the transport IPF.
The ice storage IPF can be detected by the temperature of the ice water, and the transport IPF can be detected by the density of the ice water to be transported. The operation interval can be changed by using a sequencer, and the operation frequency can be changed by an inverter of a drive motor of the stirrer 52.
【００２８】次に前記攪拌機５２の運転間隔及び運転周
波数の好ましい実施例を表１、表２、表３に基づいて説
明する。先ず夜間には、攪拌機５２ＷＭ１とＷＭ２を同
時に１分間、貯氷ＩＰＦに応じて表１に示す運転方法で
運転する。昼間には、氷取り出し用の攪拌機５２（ＷＭ
１）を常時、貯氷ＩＰＦに応じて表２に示す運転方法で
運転する。また、昼間には、氷寄せ用の攪拌機５２（Ｗ
Ｍ２）を１分間、搬送ＩＰＦが貯氷ＩＰＦより１５％以
上小さくなったときに、表３に示す運転方法で運転す
る。Next, preferred embodiments of the operation interval and operation frequency of the stirrer 52 will be described with reference to Tables 1, 2 and 3. First, at night, the stirrers 52WM1 and WM2 are simultaneously operated for one minute by the operation method shown in Table 1 according to the ice storage IPF. In the daytime, a stirrer 52 for removing ice (WM
1) is always operated by the operation method shown in Table 2 according to the ice storage IPF. In the daytime, the ice stirrer 52 (W
M2) is operated by the operation method shown in Table 3 when the transport IPF is smaller than the ice storage IPF by 15% or more for one minute.
【００２９】[0029]
【表１】 [Table 1]
【表２】 [Table 2]
【表３】 [Table 3]
【００３０】さて前記したように貯氷槽１内に高いＩＰ
Ｆで氷が貯溜されている場合、その付着性から１つの大
きな塊となってしまう。この為図１８（Ａ）に示すよう
に、負荷と熱交換後の温度が上がった戻り水を戻り配管
５９により貯氷槽１の全表面に散布していたが、これの
みでは足りずこれを攪拌するには大きな攪拌機５２と動
力が必要のみならず、しばしば攪拌に必要な動力が大き
過ぎ、過負荷で攪拌機５２が停止してしまう場合があっ
た。このような、大きな氷塊が攪拌機５２入口部の羽根
に引っかかり、攪拌機５２が過負荷になる場合、攪拌機
５２を一旦停止して、正逆回転を数回繰り返すことによ
り、氷塊が細断され、過負荷を防止できる。又戻り水
も、貯氷槽１内の氷水に表面から、その熱で大きな氷の
塊を細断するように戻すよにするのがよい。即ち大きな
塊が小さくなると、攪拌機５２の大きさ、攪拌動力が小
さくて済む。そしてこの様な構成は図１９（Ａ）に示す
ように、氷を細断したい大きさに合わせて、貯氷槽１上
部に開閉制御バルブ５８を介して戻り水の戻り配管５９
を配置し、戻り配管５９の下の穴から、戻り水を氷表面
に流出させる。戻り水に接触した氷は、戻り水の熱で解
けるため、大きな氷の塊は、図の例では４つに小さく細
断される。氷塊を細断する順序としては、まず、氷水取
り出し口７ａの近辺から、適宜バルブ５８を開閉して行
う。なぜなら、戻り水を全体の戻り配管５９から戻す
と、各配管から流出する流量が十分でなく、氷を細断で
きにくいから、また、取り出し口７ａに近い氷から流出
させる方が氷の移動に要する動力が少なく効率的だから
である。As described above, high IP is stored in the ice storage tank 1.
When ice is stored in F, it becomes one large lump due to its adhesion. For this reason, as shown in FIG. 18 (A), the return water whose temperature has increased after the heat exchange with the load was sprayed on the entire surface of the ice storage tank 1 by the return pipe 59, but this alone was not sufficient and this was stirred. This requires not only a large stirrer 52 and power, but also the power required for stirring is often too large, and the stirrer 52 may stop due to overload. When such a large ice block is caught on the blades at the inlet of the stirrer 52 and the overload of the stirrer 52 occurs, the stirrer 52 is temporarily stopped, and the ice block is shredded by repeating the forward and reverse rotations several times. Load can be prevented. Also, it is preferable that the return water is returned to the ice water in the ice storage tank 1 from the surface so that a large lump of ice is shredded by the heat. That is, when the large lump becomes small, the size of the stirrer 52 and the stirring power are small. 19A, the return pipe 59 is provided above the ice storage tank 1 via the open / close control valve 58 in accordance with the size of the ice to be shredded.
And return water flows out to the ice surface from the hole below the return pipe 59. Since the ice that has come into contact with the return water is melted by the heat of the return water, a large lump of ice is cut into four small pieces in the example shown in the figure. The order of shredding the ice block is to open and close the valve 58 appropriately near the ice water outlet 7a. This is because when the return water is returned from the entire return pipe 59, the flow rate flowing out of each pipe is not sufficient, and it is difficult to shred the ice. This is because it requires less power and is more efficient.
【００３１】さて、図１８（Ｂ）に示すように、貯氷槽
１の氷水の取出し口７ａ側には金網またはパンチングメ
タル５１を設け、搬送主管側に搬送される氷粒子径の制
限を行なっている。この場合、前記金網のメッシュ
（目）またはパンチングメタル５１の孔５２ａは、配管
途中に設けられる流量調整バルブ５７や氷水受入設備で
の熱交換器の通過隙間より小さい寸法からなるととも
に、前記メッシュまたは孔の氷水流通総面積は取出し口
７ａの断面積より十分に大きく構成されている。更に前
記金網またはパンチングメタル５１と貯氷槽１の内壁と
の間には５０ｍｍ以上の間隙を設けている。As shown in FIG. 18 (B), a wire mesh or a punching metal 51 is provided on the ice water outlet 7a side of the ice storage tank 1 to limit the diameter of ice particles to be conveyed to the main conveying pipe side. I have. In this case, the mesh (mesh) of the wire mesh or the hole 52a of the punching metal 51 has a size smaller than a passage of a heat exchanger in a flow control valve 57 or an ice water receiving facility provided in the middle of the pipe, and the mesh or the mesh The total ice water flow area of the hole is configured to be sufficiently larger than the cross-sectional area of the outlet 7a. Further, a gap of 50 mm or more is provided between the wire mesh or the punching metal 51 and the inner wall of the ice storage tank 1.
【００３２】前記のように構造、寸法等の条件を設定す
ることにより多少の氷塊が金網またはパンチングメタル
５１の前に停滞しても、金網またはパンチングメタル５
１の通路面積が大きいので、氷水通過面積の減少する割
合が小さくなり、前記氷塊の停滞によって他の氷の停滞
を生起することはない。したがって配管中に流出し搬送
される氷粒の大きさが限定され、配管中の通過隙間縮小
部においても氷塊が停滞せず、混合水通路の閉塞を防止
することができる。また、金網またはパンチングメタル
５１を通過する氷水の速度は氷水の流通断面積の関係で
取出し口７ａを通過する速度よりも十分に小さく、地域
冷房システムの負荷が最大の場合においても例えば０．
１ｍ／ｓ以下にすることができるので、金網またはパン
チングメタル５１の一部分において氷塊が溜って閉塞を
起すのを防止することができる。By setting conditions such as the structure and dimensions as described above, even if some ice blocks stagnate in front of the wire mesh or punched metal 51,
Since the passage area of 1 is large, the decreasing rate of the ice water passage area is small, and the stagnation of the ice block does not cause the stagnation of other ice. Therefore, the size of the ice particles flowing out and conveyed into the pipe is limited, and the ice block does not stay in the passage gap reduction portion in the pipe, and the blockage of the mixed water passage can be prevented. Further, the speed of the ice water passing through the wire mesh or the punching metal 51 is sufficiently smaller than the speed of passing through the outlet 7a due to the cross-sectional area of the flow of the ice water.
Since the speed can be set to 1 m / s or less, it is possible to prevent ice blocks from accumulating in a part of the wire mesh or the punching metal 51 and causing blockage.
【００３３】また前記のような、氷塊及び氷粒付着によ
る閉塞防止は次のようにしても行なわれる。すなわち、
図１８に示すように貯氷槽１中の金網またはパンチング
メタル５１の近傍に設置される氷水の攪拌機５２はその
噴流方向が金網またはパンチングメタル５１を通過する
氷水流に直角に、すなわち金網またはパンチングメタル
５１の表面に平行となるように構成される。この噴流の
力により金網またはパンチングメタル５１の前方で氷塊
の停滞するのを防止でき、かつ攪拌機５２の台数及び回
転数制御により、所定のＩＰＦで氷水の取り出しができ
る。その結果、従来の冷水のみの冷熱搬送に比べ搬送動
力を削減できることになる。The prevention of blockage due to the adhesion of ice blocks and ice particles as described above can also be performed as follows. That is,
As shown in FIG. 18, the ice water agitator 52 installed near the wire mesh or the punching metal 51 in the ice storage tank 1 has a jet direction perpendicular to the ice water flow passing through the wire mesh or the punching metal 51, that is, the wire mesh or the punching metal. 51 so as to be parallel to the surface. The stagnation of the ice block in front of the wire mesh or the punching metal 51 can be prevented by the force of the jet, and the ice water can be taken out with a predetermined IPF by controlling the number and the rotation speed of the stirrers 52. As a result, the transport power can be reduced as compared with the conventional cold transport using only cold water.
【００３４】次に図２０に前記金網またはパンチングメ
タル５１の詳細を示す。この例では、金網またはパンチ
ングメタル５１はハニカム形状に構成されており、例え
ば、これの孔５１ａの径を５ｍｍとし、ピッチを６ｍｍ
とすれば、地域冷房システムが全負荷の場合でも氷水の
通過速度を０．１ｍ／ｓ位とすることができる。更に金
網またはパンチングメタル５１の大きさを変えることに
より、任意の流路隙間において閉塞を起すことなく氷水
を搬送することが可能となる。Next, FIG. 20 shows the details of the wire mesh or punched metal 51. In this example, the wire mesh or the punching metal 51 is formed in a honeycomb shape. For example, the diameter of the hole 51a is 5 mm, and the pitch is 6 mm.
Then, even when the district cooling system has a full load, the passage speed of the ice water can be about 0.1 m / s. Further, by changing the size of the wire netting or the punching metal 51, it is possible to convey ice water without blocking in any flow path gap.
【００３５】しかしながら前記パンチングメタル５１の
穴径を、配管径によらず一定にしているため、大きな配
管径の時は、配管径に対するパンチングメタル５１の穴
径が小さくなり、取り出し部での圧力損失が大きいとい
う問題点があった。例えば氷水を搬送する際の流量制御
を搬送主管７に設けた開閉弁５７のバルブ開度でする場
合、同じ流量削減割合の時のバルブ開口高さｈは、配管
径により異なる。たとえば、設計流量の１／１０に流量
を削減するときのバルブ開口高さｈは、配管径５０ｍｍ
の時５ｍｍで、配管径１５０ｍｍの時１５ｍｍになると
いうことである。ただし、この流量削減率とバルブ開口
高さｈの関係は、バルブの種類、圧力などにより異なる
ので、示した数字は参考例の意味しかない。したがっ
て、最小の流量時のバルブ開口高さｈに合わせて、パン
チングメタル５１の穴径を決めれば、配管径が大きくな
ったときでも取り出し部における圧力損失が大きくなる
ことを防ぐことができる。尚バルブ開口高さｈと種々の
バルブとの関係は図１７に示す。However, since the hole diameter of the punching metal 51 is constant irrespective of the pipe diameter, when the pipe diameter is large, the hole diameter of the punching metal 51 with respect to the pipe diameter becomes small, and the pressure loss at the take-out portion is reduced. There was a problem that was large. For example, when the flow rate of ice water is conveyed by controlling the opening degree of the on-off valve 57 provided in the main conveyance pipe 7, the valve opening height h at the same flow rate reduction ratio differs depending on the pipe diameter. For example, when the flow rate is reduced to 1/10 of the designed flow rate, the valve opening height h is 50 mm in pipe diameter.
5 mm at that time, and 15 mm at a pipe diameter of 150 mm. However, since the relationship between the flow rate reduction rate and the valve opening height h differs depending on the type of the valve, the pressure, and the like, the numbers shown are only for reference. Therefore, if the hole diameter of the punching metal 51 is determined according to the valve opening height h at the time of the minimum flow rate, it is possible to prevent an increase in pressure loss at the take-out portion even when the pipe diameter increases. FIG. 17 shows the relationship between the valve opening height h and various valves.
【００３６】[0036]
【発明の効果】以上記載した如く本発明によれば、負荷
の変動に応じて負荷部に搬送される固液混合流体の搬送
動力当りの搬送冷熱量が最大となるように制御した為、
圧力損失が少なく、搬送動力の消費が少ない高効率の地
域冷暖房運転ができる。又負荷の変動に応じて負荷部に
搬送される固液混合流体の流速を搬送ポンプの運転を調
節することによって制御するとともに、熱源貯溜部内の
攪拌機の運転を調節することにより、熱源貯溜部から流
出する固液混合流体のＩＰＦを制御することができるの
で、前記制御を無段階に行なう場合に適しており、前記
と同様、効率の高い地域冷暖房運転ができる。更に固液
混合流体の流速を搬送ポンプの運転を調節することによ
って制御するとともに、搬送ポンプの吐出側において固
液混合流体から水（液体）を一部分離して熱源貯溜部に
戻すとともに、その戻し量を調節することにより、負荷
部に搬送される固液混合流体のＩＰＦを制御することが
できるので、特に熱源貯溜部内のＩＰＦが小さいときに
高効率の運転ができる。更に又、負荷部に搬送する固液
混合流体の流速を搬送ポンプの運転を調節することによ
って制御するとともに、熱源貯溜部内の固液混合流体流
出口近傍にメッシュの異なる金網または穴径の異なるパ
ンチングメタルを切換え設置することにより、熱源貯溜
部から流出する固液混合流体のＩＰＦを制御することが
できるので、段階的ではあるが制御を簡単に行なうこと
ができ、かつ高効率運転も維持できる。As described above, according to the present invention, since the amount of cooling / transporting the solid-liquid mixed fluid conveyed to the load portion per conveyance power according to the fluctuation of the load is controlled to be maximum,
High-efficiency district heating and cooling operation with low pressure loss and low power consumption. In addition, the flow rate of the solid-liquid mixed fluid conveyed to the load section is controlled by adjusting the operation of the transfer pump in accordance with the change in load, and the operation of the stirrer in the heat source storage section is controlled by adjusting the operation of the stirrer in the heat source storage section. Since the IPF of the solid-liquid mixed fluid flowing out can be controlled, it is suitable for the case where the control is performed in a stepless manner, and similarly to the above, a highly efficient district heating and cooling operation can be performed. Further, the flow rate of the solid-liquid mixed fluid is controlled by adjusting the operation of the transfer pump, and water (liquid) is partially separated from the solid-liquid mixed fluid at the discharge side of the transfer pump and returned to the heat source storage portion. By adjusting the pressure, the IPF of the solid-liquid mixed fluid conveyed to the load can be controlled, so that high-efficiency operation can be performed particularly when the IPF in the heat source storage is small. Further, the flow rate of the solid-liquid mixed fluid conveyed to the load portion is controlled by adjusting the operation of the transfer pump, and a wire mesh having a different mesh or a punch having a different hole diameter is provided near the solid-liquid mixed fluid outlet in the heat source storage portion. By switching and installing the metal, it is possible to control the IPF of the solid-liquid mixed fluid flowing out of the heat source storage part, so that the control can be performed stepwise but easily, and high efficiency operation can be maintained.
【００３７】又、検出された負荷変動値に応じて負荷部
に搬送される混合流体の流速とＩＰＦを段階的に調節す
ることにより、ＩＰＦと流速とを連続的に変化させて制
御する場合に比べて効率は幾分低くなるものの従来技術
よりも高効率が得られ、しかも制御が簡単になる。この
場合負荷が部分負荷領域において変動した場合、負荷が
その最大値から所定の百分比の値の範囲にあるときは、
固液混合流体のＩＰＦを一定に保って固液混合流体の流
速を調節し、負荷が前記所定の百分比値より小さい範囲
にあるときは固液混合流体の流速を一定に保って固液混
合流体のＩＰＦを検出された負荷に対応して段階的に調
節することができるので、従来技術に較べ高効率を維持
しつつ、簡単に制御ができる。等の種々の著効を有す。Also, by controlling the flow rate of the mixed fluid conveyed to the load section and the IPF stepwise in accordance with the detected load fluctuation value, the IPF and the flow rate are continuously changed to control. Although the efficiency is somewhat lower, higher efficiency is obtained than in the prior art, and the control is simpler. In this case, when the load fluctuates in the partial load region, when the load is in a range of a predetermined percentage value from its maximum value,
The flow rate of the solid-liquid mixed fluid is adjusted by keeping the IPF of the solid-liquid mixed fluid constant, and when the load is in a range smaller than the predetermined percentage value, the flow rate of the solid-liquid mixed fluid is kept constant to maintain the IPF of the solid-liquid mixed fluid constant. Can be adjusted stepwise according to the detected load, so that the control can be easily performed while maintaining high efficiency as compared with the related art. And so on.
【図１】本発明に適用される固液混合流体搬送装置の概
略図。FIG. 1 is a schematic diagram of a solid-liquid mixed fluid transfer device applied to the present invention.
【図２】図１の装置において、攪拌機の回転数が高いと
きの氷水貯溜部の説明図。FIG. 2 is an explanatory view of an ice water storage unit when the rotation speed of a stirrer is high in the apparatus of FIG.
【図３】図１の装置において、攪拌機の回転数が低いと
きの氷水貯溜部の説明図。FIG. 3 is an explanatory view of an ice water storage unit when the rotation speed of the stirrer is low in the apparatus of FIG. 1;
【図４】本発明に適用される固液混合流体搬送装置の他
の概略図。FIG. 4 is another schematic diagram of the solid-liquid mixed fluid transfer device applied to the present invention.
【図５】本発明の他の実施例に係る氷水貯溜部の断面概
略図。FIG. 5 is a schematic sectional view of an ice water storage section according to another embodiment of the present invention.
【図６】図５の実施例の回転板の正面図。FIG. 6 is a front view of the rotating plate of the embodiment shown in FIG. 5;
【図７】固液混合流体搬送時における搬送管内の圧力勾
配と流速の関係を示す線図。FIG. 7 is a diagram showing a relationship between a pressure gradient and a flow velocity in a transfer pipe during transfer of a solid-liquid mixed fluid.
【図８】固液混合流体搬送時における搬送管内の圧力勾
配とＩＰＦの関係を示す線図。FIG. 8 is a diagram showing a relationship between a pressure gradient in a transfer pipe and an IPF during transfer of a solid-liquid mixed fluid.
【図９】固液混合流体搬送時における搬送管内の搬送理
論動力当りの搬送冷熱量とＩＰＦの関係を示す線図。FIG. 9 is a diagram showing the relationship between the amount of cold transport and the IPF per theoretical transport power in the transport pipe during the transport of the solid-liquid mixed fluid.
【図１０】固液混合流体搬送時における搬送管内の適正
ＩＰＦと流速の関係を示す線図。FIG. 10 is a diagram showing a relationship between an appropriate IPF in a transfer pipe and a flow rate during transfer of a solid-liquid mixed fluid.
【図１１】固液混合流体搬送時における負荷部における
冷熱受授流体の状態説明図。FIG. 11 is an explanatory diagram of a state of a cold heat receiving and receiving fluid in a load unit when a solid-liquid mixed fluid is transferred.
【図１２】固液混合流体搬送時における搬送冷熱量と固
液混合流体の適正ＩＰＦ、流速の関係を示す線図。FIG. 12 is a graph showing the relationship between the amount of cold heat transported during solid-liquid mixed fluid conveyance, the appropriate IPF of the solid-liquid mixed fluid, and the flow velocity.
【図１３】搬送冷熱量と固液混合流体のＩＰＦ、流速及
び搬送動力比の関係を示す線図であり、特に本発明の他
の実施例の説明図である。FIG. 13 is a diagram showing the relationship between the amount of cold energy transferred and the IPF of the solid-liquid mixed fluid, the flow rate, and the transfer power ratio, and is an explanatory view particularly illustrating another embodiment of the present invention.
【図１４】搬送冷熱量と固液混合流体のＩＰＦ、流速及
び搬送動力比の関係を示す線図であり、特に本発明の他
の実施例の説明図である。FIG. 14 is a diagram showing the relationship between the amount of cold energy transferred, the IPF of the solid-liquid mixed fluid, the flow rate, and the transfer power ratio, and is an explanatory view particularly illustrating another embodiment of the present invention.
【図１５】従来の搬送装置を示す系統図。FIG. 15 is a system diagram showing a conventional transport device.
【図１６】ＩＰＦ調整器の一例を示す断面略図。FIG. 16 is a schematic sectional view showing an example of an IPF adjuster.
【図１７】搬送主管に設けた開閉制御弁のバルブ開口高
さｈと種々のバルブとの関係を示す説明図。FIG. 17 is an explanatory diagram showing a relationship between a valve opening height h of an open / close control valve provided on a main transport pipe and various valves.
【図１８】本発明が適用される氷水貯溜部を示し、
（Ａ）が平面概略図、（Ｂ）が平面図である。FIG. 18 shows an ice water reservoir to which the present invention is applied;
(A) is a schematic plan view and (B) is a plan view.
【図１９】本発明の実施例に係る氷水貯溜部を示し、
（Ａ）が平面概略図、（Ｂ）が正面図である。FIG. 19 shows an ice water storage section according to an embodiment of the present invention;
(A) is a schematic plan view, and (B) is a front view.
【図２０】氷水貯溜部の取り出し口に取付けられるパン
チングメタルの部分図。FIG. 20 is a partial view of a punching metal attached to an outlet of the ice water storage unit.
１ 熱源貯溜部としての貯氷槽 ２ 搬送ポンプ ３、４ ＩＰＦ調整器 ７ 搬送主管 ８ 戻り導管 ９ 負荷 ７ａ 固液混合流体取出口 １６ 水抜き配管 ５１ 金網またはパンチングメタル ５２ 攪拌機 DESCRIPTION OF SYMBOLS 1 Ice storage tank as heat source storage part 2 Transport pump 3, 4 IPF adjuster 7 Transport main pipe 8 Return conduit 9 Load 7a Solid-liquid mixed fluid outlet 16 Drainage pipe 51 Wire mesh or punching metal 52 Stirrer
───────────────────────────────────────────────────── フロントページの続き (72)発明者 浜岡 幸夫 東京都江東区牡丹２丁目13番１号 株式 会社前川製作所内 (72)発明者 相沢 旬一 東京都江東区牡丹２丁目13番１号 株式 会社前川製作所内 (72)発明者 大野 泰司 東京都江東区牡丹２丁目13番１号 株式 会社前川製作所内 (72)発明者 横山 卓史 東京都江東区牡丹２丁目13番１号 株式 会社前川製作所内 (72)発明者 森川 大和 大阪府大阪市北区中之島３丁目３番22号 関西電力株式会社内 (72)発明者 宮脇 正博 大阪府大阪市北区中之島３丁目３番22号 関西電力株式会社内 (72)発明者 藤本 健 大阪府大阪市中央区高麗橋４丁目６番２ 号 株式会社日建設計内 (72)発明者 栗山 知広 大阪府大阪市中央区高麗橋４丁目６番２ 号 株式会社日建設計内 審査官 近藤 裕之 (56)参考文献 特開 平３−129228（ＪＰ，Ａ) 特開 平６−147561（ＪＰ，Ａ) 実開 平３−42932（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F24F 5/00 F25C 1/00 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Yukio Hamaoka 2-13-1, Botan, Koto-ku, Tokyo Stock inside Maekawa Works (72) Inventor Shunichi 2-1-1, Botan, Koto-ku, Tokyo Stock Inside the Maekawa Works Co., Ltd. (72) Inventor Yamato Morikawa 3-3-22 Nakanoshima, Kita-ku, Osaka-shi, Osaka Kansai Electric Power Co., Inc. (72) Inventor Masahiro Miyawaki 3-2-2, Nakanoshima, Kita-ku, Osaka-shi, Osaka Kansai Electric Power Co., Inc. (72) Inventor Ken Fujimoto 4-6-2 Komyo Bridge, Chuo-ku, Osaka-shi, Osaka Inside Nikken Sekkei Co., Ltd. (72) Inventor Tomohiro Kuriyama Chuo-ku, Osaka-shi, Osaka 4-6-2 Rehashi Examiner, Nikken Sekkei Co., Ltd. Hiroyuki Kondo (56) References JP-A-3-129228 (JP, A) JP-A-6-147561 (JP, A) 42932 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F24F 5/00 F25C 1/00
Claims (7)
合流体を収容する熱源貯溜部から搬送ポンプ及び搬送管
を介して前記混合流体を負荷部に搬送する固液混合流体
の搬送制御方法において、 前記負荷側に供給される固液混合流体の搬送動力当りの
搬送熱量が最大となる、前記搬送管内における前記混合
流体の潜熱物質混合充填率（ＩＰＦ）と管内流速との関
係（アルゴリズム）を予め求め、 負荷側の熱負荷変動に対応させて固液混合流体の搬送冷
却量が最大となるように前記アルゴリズムに基づいて、
搬送管内の流速又は／及びＩＰＦを制御するとともに、 前記ＩＰＦを制御する際に、前記熱源貯溜部の固液混合
流体出口近傍に設けたメッシュの異なる金網または穴径
の異なるパンチングメタルを設けた場合において、前記
メッシュ又は穴径を切り換えて前記ＩＰＦを制御する こ
とを特徴とする固液混合流体の搬送制御方法。1. A solid-liquid mixture of a latent heat substance such as ice and a liquid such as water.
Transfer pump and transfer pipe from the heat source storage unit that contains the combined fluid
Solid-liquid mixed fluid that conveys the mixed fluid to the load via
In the transfer control method, the solid-liquid mixed fluid supplied to the load side per transfer power
The mixing in the transfer pipe, in which the transfer heat amount is maximized
The relation between the latent heat substance mixed filling rate (IPF) of the fluid and the flow velocity in the pipe
The algorithm (algorithm) is determined in advance, and the transfer cooling of the solid-liquid mixed fluid is performed in accordance with the thermal load fluctuation on the load side.
Based on the algorithm so that the reject amount is maximized,
Control the flow rate or / and IPF in the transport tubeWith When controlling the IPF, solid-liquid mixing of the heat source storage section
Wire mesh of different mesh or hole diameter provided near the fluid outlet
When punching metal of different
Switch the mesh or hole diameter to control the IPF This
And a method for controlling the transport of a solid-liquid mixed fluid.
回転制御により前記ＩＰＦを制御することを特徴とする
請求項１記載の固液混合流体の搬送制御方法。2. The method according to claim 1, wherein the IPF is controlled by controlling the rotation of a stirrer installed in the heat source storage unit.
前記熱源貯溜部への液体の抜き量を制御する事により前
記ＩＰＦを制御することを特徴とする請求項１記載の固
液混合流体の搬送制御方法。3. The transport of a solid-liquid mixed fluid according to claim 1, wherein the IPF is controlled by controlling an amount of liquid withdrawn from the IPF adjuster for adjusting the IPF to the heat source reservoir. Control method.
合流体を収容する熱源貯溜部から搬送ポンプ及び搬送管
を介して前記混合流体を負荷部に搬送する固液混合流体
の搬送制御方法において、 前記負荷側に供給される固液混合流体の搬送動力当りの
搬送熱量が最大となる、前記搬送管内における前記混合
流体の潜熱物質混合充填率（ＩＰＦ）と管内流速との関
係（アルゴリズム）を予め求め、 負荷側の熱負荷変動に対応させて固液混合流体の搬送冷
却量が最大となるように前記アルゴリズムに基づいて、
搬送管内の流速又はＩＰＦを制御する際に、 前記負荷側に供給される搬送熱量が、その最大値からの
割合に応じて、ＩＰＦ を一定にして前記管内流速を制御
するか、若しくは管内流速を一定にしてＩＰＦを制御す
るかを選択させることを特徴とする 固液混合流体の搬送
制御方法。(4)Solid-liquid mixing of latent heat substance such as ice and liquid such as water
Transfer pump and transfer pipe from the heat source storage unit that contains the combined fluid
Solid-liquid mixed fluid that conveys the mixed fluid to the load via
In the transfer control method of Per unit power of the solid-liquid mixed fluid supplied to the load side
The mixing in the transfer pipe, in which the transfer heat amount is maximized
The relation between the latent heat substance mixed filling rate (IPF) of fluid and the flow velocity in the pipe
Find the engagement (algorithm) in advance, Conveyance cooling of solid-liquid mixed fluid in response to thermal load fluctuation on the load side
Based on the algorithm so that the reject amount is maximized,
When controlling the flow rate or IPF in the transfer pipe, The amount of heat transferred to the load side is calculated from the maximum value.
IPF according to percentage To control the flow velocity in the pipe
Or control the IPF by keeping the flow velocity in the pipe constant.
Or select Conveying solid-liquid mixed fluid
Control method.
する場合において、前記ＩＰＦを段階的に制御すること
を特徴とする請求項４記載の固液混合流体の搬送制御方
法。 5. The IPF is controlled by keeping the flow velocity in the pipe constant.
5. The method according to claim 4 , wherein the step of controlling the IPF is performed stepwise .
合流体を収容する熱源貯溜部から搬送ポンプ及び搬送管
を介して前記混合流体を負荷部に搬送する固液混合流体
の搬送制御方法において、 前記負荷側に供給される固液混合流体の搬送動力当りの
搬送熱量が最大となる、前記搬送管内における前記混合
流体の潜熱物質混合充填率（ＩＰＦ）と管内流速との関
係（アルゴリズム）を予め求め、 負荷側の熱負荷変動に対応させて固液混合流体の搬送冷
却量が最大となるように前記アルゴリズムに基づいて、
搬送管内の流速又は／及びＩＰＦを制御するとともに、 前記熱源貯溜部内に、氷等の潜熱物質を撹拌し、搬送管
路側への氷寄せ若しくは取り出しを行なうための一又は
複数の撹拌機を設け、 前記撹拌機の運転間隔および運転周波数を貯氷ＩＰＦ、
搬送ＩＰＦに応じて適宜に変化させることを特徴とする
固液混合流体の搬送制御方法。6.Solid-liquid mixing of latent heat substance such as ice and liquid such as water
Transfer pump and transfer pipe from the heat source storage unit that contains the combined fluid
Solid-liquid mixed fluid that conveys the mixed fluid to the load via
In the transfer control method of Per unit power of the solid-liquid mixed fluid supplied to the load side
The mixing in the transfer pipe, in which the transfer heat amount is maximized
The relation between the latent heat substance mixed filling rate (IPF) of fluid and the flow velocity in the pipe
Find the engagement (algorithm) in advance, Conveyance cooling of solid-liquid mixed fluid in response to thermal load fluctuation on the load side
Based on the algorithm so that the reject amount is maximized,
Controls the flow rate or / and IPF in the transport tube, In the heat source storage section, a latent heat substance such as ice is stirred,
One or other way to pull or remove ice on the roadside
Provide multiple stirrers, The operation interval and operation frequency of the stirrer are stored in an ice storage IPF,
It is characterized in that it is appropriately changed according to the transport IPF.
A transport control method for a solid-liquid mixed fluid.
合流体を収容する熱源貯溜部から搬送ポンプ及び搬送管
を介して前記混合流体を負荷部に搬送する固液混合流体
の搬送制御方法において、 前記負荷側に供給される固液混合流体の搬送動力当りの
搬送熱量が最大となる、前記搬送管内における前記混合
流体の潜熱物質混合充填率（ＩＰＦ）と管内流速との関
係（アルゴリズム）を予め求め、 負荷側の熱負荷変動に対応させて固液混合流体の搬送冷
却量が最大となるように前記アルゴリズムに基づいて、
搬送管内の流速又は／及びＩＰＦを制御するとともに、 負荷部で熱交換後の戻り水を貯氷槽上より貯氷槽表面に
散布可能に構成した熱源貯溜部を設け、 前記貯氷槽上部に截断すべき氷形状に合わせ戻り水の戻
り配管を配置し、戻り配管の下穴から、戻り水を流出さ
せる ことを特徴とする固液混合流体の搬送制御方法。7.Solid-liquid mixing of latent heat substance such as ice and liquid such as water
Transfer pump and transfer pipe from the heat source storage unit that contains the combined fluid
Solid-liquid mixed fluid that conveys the mixed fluid to the load via
In the transfer control method of Per unit power of the solid-liquid mixed fluid supplied to the load side
The mixing in the transfer pipe, in which the transfer heat amount is maximized
The relation between the latent heat substance mixed filling rate (IPF) of fluid and the flow velocity in the pipe
Find the engagement (algorithm) in advance, Conveyance cooling of solid-liquid mixed fluid in response to thermal load fluctuation on the load side
Based on the algorithm so that the reject amount is maximized,
Controls the flow rate or / and IPF in the transport tube, Return water after heat exchange at the load from the ice storage tank to the surface of the ice storage tank
Provide a heat source storage unit configured to be sprayable, Return the water to the top of the ice storage tank according to the ice shape to be cut
And return water from the pilot hole in the return line.
Let A method for controlling the transport of a solid-liquid mixed fluid, comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14842993A JP3302782B2 (en) | 1992-05-29 | 1993-05-28 | Transfer control method for solid-liquid mixed fluid |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13877292 | 1992-05-29 | ||
| JP4-138772 | 1992-05-29 | ||
| JP14842993A JP3302782B2 (en) | 1992-05-29 | 1993-05-28 | Transfer control method for solid-liquid mixed fluid |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06265183A JPH06265183A (en) | 1994-09-20 |
| JP3302782B2 true JP3302782B2 (en) | 2002-07-15 |
Family
ID=26471736
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14842993A Expired - Fee Related JP3302782B2 (en) | 1992-05-29 | 1993-05-28 | Transfer control method for solid-liquid mixed fluid |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3302782B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011190983A (en) * | 2010-03-15 | 2011-09-29 | Shinryo Corp | Dynamic type ice storage system suitable for great depth water tank |
| JP6339441B2 (en) * | 2014-07-31 | 2018-06-06 | 高砂熱学工業株式会社 | Sherbet ice making system and sherbet ice making method |
| JP6612904B2 (en) * | 2018-01-15 | 2019-11-27 | 高砂熱学工業株式会社 | Sherbet ice making system and sherbet ice making method |
-
1993
- 1993-05-28 JP JP14842993A patent/JP3302782B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06265183A (en) | 1994-09-20 |
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