JP5113259B2 - Method for controlling transmission via one or more transmission elements - Google Patents

Description

  The present invention, inter alia, is a method for controlling the transfer of energy, radiation and / or mass through or through one or more transmission elements in a fluid treatment device, comprising: Relates to a method comprising the addition or reduction of energy, heat, radiation, substances, etc. to / from one or more fluids, preferably liquids.

BACKGROUND OF THE INVENTION Although the present invention is applicable in a broad sense, the background of the present invention is disclosed primarily with reference to a heat exchanger. Other applications of the invention include, for example, the transfer of substances and radiation to a fluid.

Today, many transfer devices, such as heat exchangers, are formed as plates or tubes, with different temperature fluids flowing on each side of the plate or tube, resulting in the transfer of heat between the fluids through the plate or tube. It is supposed to let you. Such heat exchangers have a flow rate where the local velocity inside the heat exchanger passes through the exchanger in a way that the local velocity cannot be changed without changing the flow rate through the heat exchanger (m ³ / h) is designed to correlate.

In particular, the heat exchanger in the heating system has been conventionally designed for a flow rate (m ³ / h) that satisfies the peak load condition. In partial load situations, it is necessary to maintain the peak load flow rate through the heat exchanger in order to keep the speed inside the heat exchanger high. Otherwise, the decrease in flow rate will cause a decrease in heat transfer, thereby failing to meet the cooling or heating requirements. Thus, if the flow through the heat exchanger can be reduced while maintaining heat transfer at a substantially constant or similar scale, a reduction in pressure loss can be achieved in a partial load situation during the heating system. it can.

  US patent application 2003/0209343 can be seen as such an example. This reference discloses a pump system for use in heat exchange applications having a pump chamber with a fluid inlet and a fluid outlet. A rotating device for moving the fluid over the surface to be cooled is included in the pump chamber. The face forms an integral part of the pump chamber in such a way that when the fluid passes through the rotating device, it also passes over the face and causes heat transfer between the face and the fluid. Another aspect of the invention includes that the surface to be cooled is integrally connected with the pump chamber and is separable from the surface to be cooled without disturbing the fluid circuit for heat exchange applications. . Also, the means for driving the rotating device can be configured to drive the means for cooling the fluid. In the embodiment of FIG. 3 of US Patent Application 2003/0209343, the cooling fluid is passed through the passage and into the impeller having vanes for guiding the fluid on the surface to be cooled. It is disclosed that it can be done. Optimum correlation or dependence between impeller rotational speed and flow rate (and in effect cooling available), considering that the objective is to design a compact and efficient pump for heat exchange applications Sex may be desirable. However, the fact that the rotation speed of the impeller can be made dependent on the flow rate is only briefly described, and there is no specific description of what this dependency can be.

  It has been found that conventional heat exchangers appear to have the disadvantage that heat transfer is strongly correlated with the flow rate of fluid passing through the heat exchanger. For example, a change in flow rate causes a change in heat transfer, which, on the other hand, compared to a situation where the flow rate through the heat exchanger can be changed without significantly changing the heat transfer. Results in limiting the operating life of the.

  Accordingly, an object of the present invention is to provide a method for an apparatus in which the strong correlation between flow rate and local velocity is at least relaxed, for example to obtain a more controllable transfer of heat, matter and / or radiation It is to be.

US patent application 2003/0209343

DISCLOSURE OF THE INVENTION Accordingly, in a first aspect, the present invention relates to a method for controlling the transfer of heat, material, radiation, etc., at least to or from a first fluid in the device, the device comprising: At least one stage including a transmission element and a rotatable impeller, the impeller being arranged such that a first fluid flowing out of the impeller flows along the plane of the transmission element; The first fluid flow along includes a spiral flow pattern that includes a radial velocity component (Vr) and a tangential velocity component (Vt), and the device is further configured to throttle the first fluid flow through the device. Including one or more throttle means, the rotational speed and throttle of the impeller
i) the transmission is a function of radial velocity component (Vr) and tangential velocity component (Vt), and
ii) The radial velocity component (Vr) and the tangential velocity component (Vt) are mutually controlled so as to be substantially independent.

By using the method of the present invention, the transmission amount AT is
AT = f ₁ (Vr) + f ₂ (Vt)
Can be represented as
In the equation, f ₁ and f ₂ are functions used to show the correlation between the tangential velocity Vt and the radial velocity Vr and the transmission amount AT, respectively.

  The amount of transmission can be varied by substantially changing the rotational speed of the impeller without substantially affecting the flow rate of the first fluid being processed through the device.

  The flow rate can be changed by changing the rotational speed of the impeller without substantially affecting the transmission amount of the first fluid in the apparatus.

  In this context, aperture is equal to suppression. Since the flow in the pipe is driven by a pressure difference, the restriction accordingly requires that a counter pressure is generated on the outlet side, i.e. the inlet pressure is reduced. Accordingly, the throttling means can include a throttling valve, one or more dedicated cavities for throttling, a diaphragm, a constriction of the first fluid pipe, a backflow or viscosity control means. Physical blockage or obstacle placement passively transfers the kinetic energy of the flow to back pressure. Thus, an active throttling method could provide back pressure with a dedicated pump, but consumes energy. As a special case, the squeezing effect can also be produced by changing the properties of the liquid, for example by electrorheology.

  The tangential speed can also be increased or decreased by increasing or decreasing the impeller rotation speed. An increase or decrease in impeller rotational speed can cause an increase or decrease in pressure, which can increase or decrease the radial velocity component and thus the flow rate through the device. In the present invention, the flow rate is correlated with the radial velocity component, but is considered to be slightly correlated with the tangential velocity component. Usually, the change in the tangential speed due to the change in the rotation speed of the impeller is so large that the change in the flow rate can be ignored.

  Although the spiral flow pattern can be generated by a stationary flow guide, the present invention has the unique advantage that the impeller generates a spiral flow pattern.

  However, if it is desired to increase or decrease the tangential velocity without affecting the radial velocity component, a throttle may be applied to correct the pressure increase or decrease due to the increase or decrease of the impeller rotation speed.

Thus, the present invention does not change the flow rate through the device, for example, changes the local velocity inside the device, which is a heat exchanger, for example, without changing the flow rate through the device. It is thought to provide a way to enable changes in transmission.
[Invention 101]
A method for controlling the transfer of heat, material, radiation, etc. in or to at least a first fluid in an apparatus comprising:
The apparatus includes at least one stage including a transmission element (2) and a rotatable impeller (3), wherein the impeller causes the first fluid flowing out of the impeller to face the transmission element (2). The first fluid flow along the face of the transfer element includes a spiral flow pattern having a radial velocity component (Vr) and a tangential velocity component (Vt). ,
The device further comprises one or more restricting means for restricting the flow of the first fluid through the device;
The rotational speed of the impeller and the aperture are
i) the amount of transmission is a function of the radial velocity component (Vr) and the tangential velocity component (Vt), and
ii) The radial velocity component (Vr) and the tangential velocity component (Vt) are substantially independent.
So that they are mutually controlled.
[Invention 102]
Transmission amount AT is
AT = f ₁ (Vr) + f ₂ (Vt)
Can be represented as
Where f ₁ and f ₂ are functions used to show the correlation between each of the tangential velocity Vt and the radial velocity Vr and the transmission amount AT,
The method of the invention 101.
[Invention 103]
101. The method of invention 101, wherein the amount of transmission can be changed by changing the rotational speed of the impeller without substantially affecting the flow rate of the first fluid being processed through the device.
[Invention 104]
101. The method of invention 101, wherein the flow rate can be varied by changing the rotational speed of the impeller without substantially affecting the transmission of the first fluid in the device.
[Invention 105]
The method of any of the invention 101-103, wherein the throttling means comprises a throttling valve, one or more dedicated cavities for throttling, a diaphragm, a constriction of the first fluid pipe, a countercurrent or viscosity control means .
[Invention 106]
101. The method of invention 101, wherein the impeller rotational speed is increased in response to increased transmission requirements and the impeller rotational speed is decreased in response to decreased transmission requirements.
[Invention 107]
101. The method of invention 101, wherein the impeller rotational speed is decreased in response to an increase in transmission demand and the impeller rotational speed is decreased in response to an increase in transmission demand.
[Invention 108]
The apparatus includes one or more channels through which the second fluid flows, the channels arranged such that transmission occurs between the first fluid and the second fluid via the transmission element. A method according to any one of the inventions 101 to 107.
[Invention 109]
109. The method of the present invention 108, wherein one or more channels through which the second fluid flows are provided in the transmission element.
[Invention 110]
An apparatus includes an impeller for a first fluid and an impeller for a second fluid, and a method is responsive to a given transmission request for the impeller for the first and second fluids. 108. The method of claim 108 or 109, comprising the step of controlling the rotational speed of
[Invention 111]
The method of the present invention 110, wherein the rotational speeds of the impellers for the first and second fluids are independently controllable.
[Invention 112]
The method of the present invention 110, wherein the rotational speeds of the impellers for the first and second fluids are rotated in common, such as disposed on a common drive shaft.
[Invention 113]
The present invention 108-112, wherein the device comprises one or more channels through which a third fluid flows, the channels being arranged such that communication between the fluids takes place via a transmission element Either way.
[Invention 114]
Any of the present inventions 108-113, wherein the apparatus includes an impeller for each fluid and the method includes controlling the rotational speed of the impeller for each fluid in response to a given transmission requirement. That way.
[Invention 115]
If the device further depends on one or more throttling means, for example a first fluid passing through the device and / or the present invention 108-112, the second fluid and / or the present invention 113-114 If subordinate, includes one or more throttle valves to throttle the third fluid flow, and the method further increases the flow restriction by the throttle means in response to an increase or decrease in transmission demand Or the method of any of claims 108-114, comprising the step of decreasing to thereby increase or decrease the pressure drop across the throttling means.
[Invention 116]
115. The method of claim 115, wherein the aperture is increased in response to an increase in impeller rotational speed.
[Invention 117]
The method of the present invention 116 for controlling the increase in throttle so that the flow rate of one or more of the fluid passing through the device does not substantially change, for example, changes less than 5%, as a result of an increase in impeller rotational speed. .
[Invention 118]
115. The method of claim 115, wherein the aperture is reduced in response to a decrease in impeller rotational speed.
[Invention 119]
The method of the present invention 118, wherein the reduction of the restriction is selected such that as a result of the reduction in impeller rotational speed, the flow rate of one or more of the fluids passing through the device does not change substantially, for example less than 5%. .
[Invention 120]
The method of any of the invention 1-119, wherein the transmission element comprises a filter element having pores that allow only particles smaller than a certain particle size to pass through the filter element.
[Invention 121]
120. The method of any of the present invention 101-119, wherein the transfer element comprises a heat transfer element.
[Invention 122]
The method of 121, wherein the heat transfer element comprises an internal channel through which the cooling / heating fluid can flow.
[Invention 123]
The method of any of the invention 101-119, wherein the transmission element comprises a radiation source or a radiation guide such that the radiation is emitted from the face of the transmission element into one or more fluids.
[Invention 124]
The method of any of the present invention 101-123, wherein the apparatus comprises a plurality of stages.
[Invention 125]
The method of the invention 124, wherein the transfer elements of the stages are similar to each other, for example identical to each other.
[Invention 126]
124. The method of claim 124, wherein the stage transfer elements are adapted for different transmissions.

Hereinafter, the present invention, particularly preferred embodiments thereof, will be disclosed in more detail with reference to the accompanying drawings.
FIG. 1a is a schematic cross-sectional view of a first embodiment of the device of the present invention. FIG. 1b schematically shows the spiral flow of the fluid leaving the impeller in FIG. 1b. FIG. 1c is a schematic graph of the head flow characteristics of a typical impeller, illustrating the working principle of the present invention. FIG. 1d is a graph showing the friction loss of the pump as a function of flow rate to illustrate the advantages of the present invention. 2 shows a heat transfer element of a heat exchange unit of an embodiment of the present invention. The heat transfer elements are shown from diagonally above (Figure 2a) and diagonally below (Figure 2b), respectively. 3 shows a flow path of a first fluid flowing in a channel of a heat treatment unit including three heat transfer elements shown in FIG. For clarity, the elements are shown spaced apart, but in practice they abut one another as shown in FIG. Furthermore, a part of the casing is cut away to show the heat transfer element. 3 shows a second fluid flow path flowing between the heat transfer elements shown in FIG. For clarity, the elements are shown spaced apart, but in practice they abut one another as shown in FIG. Furthermore, a part of the casing is cut away to show the heat transfer element. A part of preferable aspect of a heat exchange unit is shown roughly. 5a is a plan view, and FIG. 5b is a cross-sectional view taken along line AA in FIG. 5a. The side of the heat exchange unit of this invention is shown schematically. Fig. 2 schematically shows a cross-sectional view of a part of the heat exchange unit of the present invention with a pressure stage for pumping one of the fluids through the heat exchange unit. Both schematically illustrate a preferred embodiment of a heat exchanger for exchanging heat between two fluids provided with flow by an impeller. 1 schematically illustrates a preferred embodiment of a heat exchanger for exchanging heat between three fluids provided with flow by an impeller. 1 schematically illustrates a transmission element of the present invention for filtering particles, substances, etc. from a fluid. 1 schematically illustrates an embodiment of the present invention for emitting radiation into a fluid. FIG. 1a is a cross-sectional view and FIG. 11b is a three-dimensional view of some parts of the embodiment. Fig. 3 schematically shows an embodiment of the invention in which the transmission element is tube-shaped.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION FIG. 1 schematically shows a preferred embodiment of the device 1 of the present invention. The device 1 comprises one or more transmission elements 2 (two transmission elements are shown in FIG. 1), one or more impellers 3 (two are shown) and the rotation of the impeller 3 It includes a shaft 4 on which an impeller 3 is disposed to cause rotation. The apparatus disclosed in FIG. 2 has two stages each including a transmission element 2 and an impeller 3, and it is considered that the fluid to be treated is discharged from the impeller and flows through the surface of the transmission element 2. The device 1 is cylindrical and includes a cylindrical casing 5 containing an inlet element 6 and an outlet element 7. The transmission element 2 is circular. As shown in FIG. 1, a passage is left between the inner surface of the casing 5 and the edge of the transmission element 2, and a floor element 8 is disposed between the two transmission elements 2.

  The fluid to be treated flows into the device via the inlet element 6 and flows towards the rotating impeller 3. The fluid to be treated leaves the impeller and flows along one surface of the transmission element 2 toward the edge of the transmission element 2 and passes through a passage between the edge of the transmission element 2 and the inner surface of the casing 5. Instead of or in addition to the passage between the edge and the casing 5, one or more through-holes through which fluid can flow can be provided in the transmission element 2.

  Thanks to the presence of the floor element 8, the fluid 5 flows between the edge and the casing and then flows towards the second impeller. After passing through the second impeller 3, the fluid flows along the surface of the second transmission element 2 towards the edge, passes through the passage between the edge and the casing 8, and finally towards the outlet element 7. Leave the device 1 through it. The flow path is schematically indicated by arrows.

Transfer element 2 is a heat transfer element that passes when heat is transferred to or from the fluid to be processed, when mass is transferred to or from the fluid to be processed A mass transfer element that passes through, a radiation element that emits radiation into the fluid, or a radiation element that passes through when radiation is emitted into the fluid, or a combination thereof. The flow pattern of the fluid to be processed as it flows along the surface of the transfer element 2 is shown in FIG.1b as follows: radial radial velocity component Vr of transfer element 2 and tangential tangential velocity component of transfer element 2 It is a spiral flow pattern including Vt. Of course, there may be velocity components perpendicular to Vr and Vt. The flow pattern on the bottom surface (with respect to the orientation in the figure) also generally includes a spiral motion, but may differ from the spiral motion on the top surface. Vr correlates with the flow rate (m ³ / h) through the device and depends inter alia on the pressure loss through the device 1. Vt correlates with impeller rotation speed. It should be mentioned that pressure loss and impeller rotational speed may be correlated.

  For example, the transfer of energy and matter from the fluid to the transmission element 2 (or vice versa) includes, inter alia, the boundary flow of the surface of the transmission element 2 and the fluid to be processed when the fluid flows along the surface of the transmission element 2 It is governed by residence time, ie flow rate. Similarly, if radiation is emitted and flows from the transmission element 2 along the surface of the transmission element 2, inter alia boundary layer flow and residence time dominate the dose emitted to the fluid to be treated.

At least in relation to the vortex flow through the transmission element 2 (as explained in connection with FIG. 1), the general transfer equation for the transfer of energy, matter, etc. to the transmission element (or vice versa) is
Transmission amount = K * dwell time can be expressed as
In the formula, “transmission amount” is an amount transmitted from the fluid to be processed to the transmission element (or vice versa), and K is
K [ε / m ² s]
Represented as:

ε is, for example, Q (heat) or m (mass). ε correlates mainly with gradients such as temperature and concentration in the boundary layer close to the surface of the transfer element 2, and ε / m ^{2 of} K is considered to correlate only with Vt. Residence time / flow rate is considered to correlate with Vr only.

Therefore, since Vr and Vt are considered to be uncorrelated, the transmission amount is
Transmission amount = f ₁ (Vr) + f ₂ (Vt)
Can be expressed as

f ₁ and f ₂ are functions used to show the correlation between tangential and radial velocities and transmission. Therefore, according to the present invention, the transmission amount can be changed by changing the rotation speed of the impeller without affecting the flow rate of the processed fluid passing through the processing device.

  While the above discussion somehow reflects an ideal situation, for example, increasing impeller speed tends to increase the total pressure of the fluid as it passes through the impeller. If no other means are incorporated into the processing apparatus 1, this increase in total pressure can result in higher flow rates and give shorter residence times. To take this into account, a restriction of the flow of the fluid to be treated can be applied, for example by means of throttle valves 6a and 7a arranged in the inlet element 6 and / or the outlet element 7. In addition, one or more flow sensors are usually connected to the throttle valve to measure the actual flow rate through the processing device, for example increasing the rotational speed of the impeller is undesirable for the flow rate. If there is an increase, the device can be throttled to reduce the flow rate.

  If a diaphragm is applied, the control method can include increasing or decreasing the diaphragm while maintaining the rotational speed of the impeller.

  FIG. 1c is a schematic graph of typical impeller head flow characteristics w1 and w2 illustrating the working principle of the present invention. Curve P shows the pump curve. The horizontal scale shows the flow rate Q, and the vertical scale shows the head or the corresponding measure total pressure. If the impeller 3 is initially operating at the specified flow rate Q2 and it is desired to reduce the flow rate to the flow rate Q1, there are two ways to do so.

  First, as indicated by the solid arrow A, it is possible to reduce the flow rate Q passing through the impeller simply by reducing the rotational speed (of the impeller 3). However, this has the disadvantage that when following the operating curve w1, the corresponding head is somewhat reduced at a lower flow rate Q1.

  Second, as indicated by arrow B, it is possible to reduce the flow to the value Q1 using a restriction. This has the disadvantage of the relatively large pressure loss that is required to compensate for the additional head (and hence energy loss) from this process B.

  In the present invention, the flow rate Q and the throttle are mutually controlled so that the radial velocity component (Vr) and the contact velocity component (Vt) are substantially independent, and as a result, a relatively small change (increase / decrease) of the head. Makes it easy to change the flow rate Q (from Q2 to Q1). This is indicated by arrow C.

  In the present invention, the flow rate Q and the throttle are mutually controlled so that the radial velocity component (Vr) and the tangential velocity component (Vt) are substantially independent, so that the cross flow velocity, i.e. on the transmission surface, is controlled. It makes it easy to change the flow rate Q with a relatively small change (increase / decrease) in speed, and thus with a relatively small change in the transmission rate to or from the surface. Even more preferably, the change in crossflow rate and / or transmission rate may be substantially unchanged. For example, the flow rate can be changed at a rate of at least x10, at least x5, or at least x2.5 without substantially changing the resulting crossflow rate or transmission rate. Compared to previously known solutions, this is unprecedented to the best of the applicant's knowledge.

FIG. 1d is a graph showing friction loss of a typical pump as a function of flow rate (horizontal scale) to illustrate the advantages of the present invention. The two values shown on the curve, 2370 RPM and 1230 RPM, are the impeller rotational speeds noted as RPM per minute (RPM) in the two end point situations. The pump operates to generate a constant turbulence level. Turbulence is proportional to the velocity V of the fluid, and Reynolds number Re
Re = V / (d ・ ny)
Sought as
Where d is the typical distance between the working surfaces of the pump, ny is the viscosity, and V is
V = sqrt (Vr ² + Vt ² )
The speed required by

  From the graph in Figure 1d, the pump with the impeller at the specified ratio of tangential velocity component (Vt) and radial velocity component (Vr), Vt / Vr, is very optimal at the lowest power loss. It is clear that it works advantageously. With the present invention, this can be achieved more easily because the pump can be operated in such a way that the radial velocity component (Vr) and the tangential velocity component (Vt) are substantially independent. it can.

  It should also be noted from FIG. 1d that, according to the present invention, the impeller rotational speed can be changed at a rate of approximately x2 while maintaining a substantially unchanged crossflow speed or transmission rate. It is.

  The following are some of the aspects that have proven particularly useful when applying the control strategy disclosed above.

  The application of the present invention is for a heat exchanger where the fluid is cooled or heated by heat transfer from another fluid having a different temperature at least where heat transfer begins. FIGS. 2 a and 2 b show an embodiment of a transfer element in the form of a heat transfer element 2. The heat transfer element 2 is shown obliquely from above and obliquely below, respectively, and “upper” and “lower” relate to the orientation of the heat exchange unit in FIG. The heat transfer element 2 has a channel 14 for directing a first fluid along a first fluid contact surface that is the inner surface of the channel 14 and is therefore not directly visible in this view. As can be seen from the figure, the channel 14 extends while curving in one geometric plane. Each channel 14 includes a channel inlet 9 through which the first fluid enters the channel 14 and a channel outlet 12 through which the first fluid exits the channel 14. The channel outlet 12 and the channel inlet 9 include a fluid guide in the form of a connection stub 17 (see FIG. 3) that can be connected so that the heat transfer element 2 can be stacked, the first fluid being a single heat It can flow from the channel 14 of the transfer element 2 to the channel 14 of the heat transfer element 2 subsequently arranged. This will be described in more detail below. The heat transfer elements 2 preferably abut each other at the support bosses 10 and thereby support each other, but abutment only at the channel inlet 9 and the channel outlet 12 is also possible within the scope of the present invention. The heat transfer element 2 includes a central hole 11 (see FIG. 3) for placing the impeller 3, the function of which will be described below.

  FIG. 3 shows a part of the heat exchange device according to the invention, in which the transfer element 2 is a heat transfer element as disclosed in connection with FIG. The apparatus shown in FIG. 3 is shown in a state where the heat transfer elements 2 are separated from each other, but actually, the heat transfer elements are in contact with each other as shown in FIG. Each heat transfer element 2 includes a channel 14 through which the first fluid flows. The heat transfer element 14 is a connection that connects the channels 14 of two adjacent heat transfer elements 2 together so that the first fluid flows out of the channel 14 of one heat transfer element and flows into the channels of the adjacent heat transfer element 2 Includes stub 17. This part is enclosed by a casing 22 which is shown only partially in FIG. 3 to show the interior of the part.

  The flow path of the first fluid passing through the heat exchange unit 1 is indicated by a broken line in FIG. Passes through the inlet in the form of an inlet pipe 15 and enters the heat exchange device 1, from which it flows through the throttle valve 15a and passes through one or more connecting stubs 17 of the upper heat transfer element 2 Reach channel 14. The first fluid flows through a continuous heat transfer element 2 as shown, and flows out of the last heat transfer element 2 from an outlet in the form of an outlet pipe 16 through a throttle valve 16a. The first fluid flow is usually caused by a pump (not shown) arranged external to the heat exchange unit 1, but the pump can also be used in the manner disclosed in FIG. ) May be integrated into the heat exchange unit 1 in the same manner. The first fluid exchanges heat / energy with the second fluid flowing between the heat transfer elements 2, i.e., along their second fluid contact surfaces.

  A second fluid flow path is schematically illustrated in FIG. The embodiment shown in FIG. 4 is the same as that shown in FIG. 3, but the viewing angle is different and the casing is completely removed from the drawing. The second fluid enters the central region of the first impeller 3 which can be rotated, for example by a motor drive shaft (not shown, see FIGS. 6 and 7). The central axis of the shaft coincides with the central axis of the impeller 3, and the second fluid preferably flows toward the impeller 3 along the entire circumference of the shaft. This is indicated by a single central arrow in the figure for illustrative purposes only. An edge 35 is sealed to the casing to define a channel between two adjacent heat transfer elements 2.

  The impeller 3 induces energy to the second fluid, which causes the second fluid to flow toward the edge 35 of the heat transfer element 2. From here, the second fluid flows into the space partially defined by the guide plate 36 (not shown in FIG. 2). This flow is mainly obtained by drawing from the impeller 3 arranged in the continuous heat transfer element 2, from which the flow pattern is repeated.

  The above figure shows that the first and second fluids generally flow in opposite directions, i.e. upward and downward with respect to the figure. However, it is also possible within the scope of the invention for the two fluids to flow in the same general direction.

  FIG. 5 shows a part of an embodiment of the heat exchange unit 1 of the present invention. FIG. 5a shows a portion of the heat exchange unit 1 from above, and FIG. 5b is a cross-sectional view taken along line AA of FIG. 5a. The channel 14 of the last heat transfer element 2 is slightly longer than the others because it is connected to the outlet pipe 16 as shown in FIG. 5b. The second fluid flow along the second fluid contact surface has a radial velocity component and a tangential velocity component. Furthermore, the second fluid flowing out of the impeller is in direct contact with the second fluid contact surface and the dynamic pressure is not converted to a static pressure before contact between the surface and the fluid occurs.

  Thus, by applying the control method outlined above, the heat transfer coefficient can be changed by changing the rotational speed of the impeller and thereby changing at least the tangential speed of the second fluid. . The flow rate through the device can further be controlled by throttling, for example by arranging throttling valves at the outlet and / or inlet of the heat exchange unit.

  FIG. 6 shows a preferred embodiment of the heat exchange unit of the present invention. The heat exchange unit 1 includes a casing having three casing elements: a first casing element 21, an intermediate casing element 22 and a second casing element 23. “Intermediate” is used to refer to the location of the element, ie, between the first casing element 21 and the second casing element 23.

  The heat transfer element 2 is arranged inside an intermediate casing element 22 which is formed as a cylinder open at both ends. An inlet pipe 15 that leads the first fluid to the heat transfer element 2 and an outlet pipe 16 that leads the first fluid from the heat transfer element 2 penetrate the wall of the first casing element 21 as shown in FIG. It extends. The first casing element 21 further includes an outlet 20 for a second fluid disposed on the first protrusion 24 of the first casing element 21. A fixture 25 for connecting the motor 26 to the unit is disposed on the first protrusion 24. The motor 26 is used to drive the impeller 3 disposed inside the heat exchange unit 1, and the impeller 3 passes through the wall of the protruding portion 24 from the motor 26 and normally becomes the second casing element 23. It is disposed on a shaft 27 that enters (does not penetrate).

  The second casing element 23 includes an inlet 19 for the second fluid, as shown in FIG. 6, and directs the second fluid to the heat transfer element 2 disposed in the intermediate casing element 22. A throttle valve for restricting the second fluid may be disposed in the second casing element 23.

  The heat exchange unit shown in FIG. 6 is assembled by inserting the intermediate casing element 22 into the first and second casing elements 21, 23, as shown in FIG. The seal between the intermediate casing element 22 and each of the first and second casing elements 21, 23 is in a groove (not shown) in the face where the seals (not shown) such as O-rings abut each other. It can be achieved by disposing in the above.

  In a preferred embodiment of the invention, the casing is a pressure-resistant casing adapted to resist the pressure difference between the pressure of the fluid in the heat exchange unit 1 and the ambient pressure, ie the pressure outside the heat exchange unit 1. .

  If desired, it is possible within the scope of the invention to ensure that the pressure of the second fluid increases in the heat exchange unit 1 before the second fluid passes through the heat transfer element 2. Such an increase in pressure can be established, for example, as shown in FIG. 7 which shows a detailed cross-sectional view of the heat exchange unit 1 of the present invention. The details shown include a part of the intermediate casing element 22, a second casing element 23 and a heat transfer element 2 with four impellers 3 stacked. The second casing element 23 has a second protrusion 28 comprising a pressure stage 29 having three shafts 3 and a shaft 27 on which all the impellers 3 are arranged. The shaft 27 is rotated by a motor 26 arranged as shown in FIG. The pressurization stage can preferably be used to pressurize the fluid more strongly than is necessary to overcome losses due to the flow through the heat exchange unit.

  FIG. 8 shows a further embodiment in which both fluids are pumped through the unit 1 by the use of an impeller 3 arranged therein. This figure shows this embodiment in an exploded view with the heat transfer elements 2 spaced apart and the casing (except for the end casing parts 34a, 34b) removed to allow the interior of the heat exchange unit to be seen. The heat exchange unit 1 includes a number of heat transfer elements 2 formed as disks stacked to provide a channel 31 between adjacent elements 2 as shown. With this configuration, the surface of the heat transfer element 2 facing the channel constitutes a fluid contact surface for each of the first and second fluids.

  A connecting stub 32 is provided that directs fluid from one channel 31 to another channel 31 located upstream of the adjacent channel. These may be disposed on some of the elements, as shown, or they may be separate parts that fit into a mating connection provided on the element 2. Each heat transfer element 2 abuts the casing at the edge 33. The edge 33 is preferably sealed against the casing.

  Two fluid flow paths are shown in FIG. 8, in which the first fluid enters the heat exchange unit 13 from below (with respect to the orientation of FIG. 8) via the inlet stub and passes through the connection stub 32 to the channel. Flow into 31. The channel 31 is connected to the impeller 3 via a connection stub 32. After the total pressure in the first fluid is increased by the impeller 3, the fluid flows as a vortex towards the connection stub 32 and passes through it (the flow can be linear when passing through the connection stub 32) Into the next channel 31. In this next channel, the fluid flows towards and through the next connection stub 32 leading to the impeller. After this pattern has been repeated many times by stacking more heat transfer elements 2, the first fluid can flow out of the unit via the outlet stub.

  The second fluid flows into the heat exchange unit from above via the inlet stub and reaches the impeller 3 via the connection stub 32. After the impeller 3, the second fluid flows into the channel 31 while swirling and flows toward the connecting stub that guides the fluid to the next channel 31. The fluid passes through the next channel 31 and flows towards and through the connecting stub 32 that directs the fluid to the impeller 3. After this pattern has been repeated many times by stacking more heat transfer elements, the second fluid can flow out of the unit through the outlet stub.

  As can be seen from FIG. 8, the channel through which the first fluid flows is disposed between the channels 31 through which the second fluid flows (or from either fluid). Depending on whether the situation is viewed or vice versa), both fluids have different temperatures, so that heat exchange takes place between the fluids via the heat transfer element 2.

  The embodiment shown in FIG. 8 is shown having an octagonal cross section when viewed from above. However, the cross section may be given other shapes, for example square or circular. The outer casing is preferably made as a tube and end casing parts in the form of plates as shown as 34a and 34b in FIG. 8 are arranged at both ends of the tube. The end casing part includes a connecting stub that acts as an inlet / outlet through which the first and second fluids are pumped into and out of the unit, and can be shaped as shown, for example, in FIG. The end casing part 34a also includes a through hole through which the shaft 27 on which the impeller is disposed extends. Suspension of the shaft 27 can be provided by a bearing (not shown) disposed in the end casing, between the shaft 27 and the end casing through which the shaft 27 extends from the unit. A seal is provided to avoid fluid leakage.

  FIG. 9 shows an embodiment in which three fluids are pumped through the unit 1 by use of an impeller 3 arranged therein. This figure shows this embodiment in an exploded view with the heat transfer elements 2 spaced apart and the casing (except for the end casing parts 34a, 34b) removed to allow the inside of the heat transfer unit to be seen. The end casing parts 34a, 34b can be shaped as shown in FIG. 6, for example. The heat exchange unit 1 includes a number of heat transfer elements 2 formed as disks with edges 33, stacked to provide a channel 31 between adjacent elements 2, as shown. The edge 33 of the heat transfer element 2 is sealed with respect to the casing. With this configuration, the surface of the heat transfer element 2 facing the channel constitutes a fluid contact surface for the fluid.

  Also in this embodiment, the heat transfer unit includes inlet and outlet stubs through which fluid flows into and out of unit 1. In this figure, three fluid flow paths are shown. Similar to FIG. 8, the unit includes shafts 27 connected to a motor for rotating the impeller, these shafts being arranged in the unit by bearings.

  If the impeller 3 is arranged on more than one shaft 27, these shafts 27 can be driven by the same or different motors 26.

  In another embodiment, the present invention relates to a filtration device. In this embodiment, the transmission element 2 is a disk-shaped mass transmission element as shown in FIG. FIG. 10a shows the mass transfer element 2 seen from above, and FIG. 10b shows a cross section seen from the line AA in FIG. 10a. The mass transfer element 2 is made of a porous material that allows particles of less than a given particle size to flow into the internal channel 37. Inner channel 37 is connected to a suction device, such as a pump, to provide a pressure differential between the fluid flowing along the outer surface and the fluid flowing along channel 37. As indicated by the arrows in the figure, this provides a flow of fluid having particles less than a given particle size into channel 37 and out of the channel towards the pump. The fluid is pressurized by the impeller 3 and flows out of the impeller in a spiral flow pattern toward the edge of the transmission element 2.

  Such a transfer element 2 can replace the heat transfer element shown in the previous figure, in which case the opening 38 of the channel 37 is connected to a flow channel that directs the fluid containing the particles to the pump. . For example, as disclosed in connection with the heat transfer device shown in FIG. 3, by disposing the impeller 3 in the central through hole 38, the fluid to be filtered is pumped through the filtration device. Furthermore, as disclosed in connection with FIG. 1, a passage can be left between the casing and the edge of the mass transfer element 2.

  Further, in relation to the mass transfer element 2 and the impeller, the flow along the surface of the mass transfer element 2 is a spiral motion including a tangential velocity component and a radial velocity component. Mass transfer through the mass transfer element 2 is the difference between the pressure of the fluid flow along the outer surface of the mass transfer element 2 and the pressure in the channel 37 and the radial and tangential velocities of the fluid along the outer surface of the mass transfer element 2 Correlate with components. Therefore, mass transfer can be controlled by using a control method that controls the tangential and radial velocities according to the speed of the impeller and possibly a restriction.

  Or, if the material defining the channel 14 (see FIG. 2) is made of a porous material that allows particles of less than a given particle size to flow into the channel 14, for example, the heat transfer element shown in FIG. Can also be used as the mass transfer element 2. Therefore, in this configuration, for example, the heat exchange unit shown in FIG. 5 can be used as the filtration unit.

  In a further aspect, the control method relates to emitting radiation, particularly ultraviolet light, into the fluid. Such an embodiment is shown schematically in FIG. FIG. 11a shows a cross-sectional view of a processing portion that can be arranged as the unit shown in FIGS. 1 and 6. FIG. For example, the structure shown in FIG. 11 may be used instead of the stack of transfer elements shown in FIGS. FIG. 11b is a three-dimensional view of the fluid flow path being processed in the processing portion around the four floor elements and the radiation source.

  The processing portion is cylindrical along its longitudinal axis (perpendicular to the orientation of FIG. 11) and includes a tubular and cylindrical outer casing 18 with a number of elements disposed therein. Three impellers 3 are disposed on the shaft 23 inside the processing portion. Also, floor elements 39, 40 are disposed in the processing portion, and these floor elements 39, 40, for example in combination with the impeller 3, define a flow passage through the processing portion. The flow path through the flow passage is indicated by a dotted line in FIG. 11a.

  A radiation source 41 is disposed inside the radiation source shield 42. The radiation source 41 is preferably a UV radiation source that emits UV radiation, and the radiation source shield 42 is preferably a tubular member that is transparent to UV radiation. Preferably it is made of quartz. Although the radiation source 41 and the radiation source shield 42 are disposed tangent to the floor element, as shown in FIG. 11, many other configurations of the radiation source and shield are contemplated within the scope of the present invention.

  The floor elements 39, 40 are two different shapes. The floor element 39 leaves a passage between its edge and the outer casing 18, and the floor element 40 has its edge sealed to the casing 18 to allow fluid to flow towards the impeller 3 and into the impeller. Includes a central through hole. Therefore, this structure is similar to the structure shown in FIG. Therefore, when the shaft 23 rotates, the impeller 3 pumps the fluid, and the fluid flows from the inlet and is processed in a flow pattern that enters the first impeller 3, which is the impeller located most upstream toward the inlet in the processing portion. Pass through the part. The fluid leaves the first impeller 3, flows toward the edge of the first floor element 39, passes the edge, and then flows toward the second impeller 3 located downstream of the first impeller 3. This pattern is repeated until the fluid leaves the processing portion.

  While the fluid passes through the processing portion, the fluid flows in the immediate vicinity of the UV radiation source located in the radiation source shield 42. Furthermore, the floor elements 39, 40 are preferably made of a material that is transparent to UV radiation, for example quartz, and the radiation is located close to the radiation source shield 42, depending on the attenuation characteristics of the fluid. It penetrates to the area of the processing part that does not. The treatment portion is designed such that a number of connected channels are defined by the floor elements 39, 40, of which channel 44 is a direct exposure channel through which the radiation source emits radiation directly into it, Channel 43 is an indirect exposure channel through which the radiation source indirectly emits radiation as it passes through one or more floor elements 39,40. In this regard, the radiation source is believed to emit directly into the channel 44, but the radiation source is shielded by the radiation source shield 42.

  It should be noted that whether the indirect exposure channel receives radiation depends inter alia on the damping characteristics of the fluid. For example, if the fluid highly attenuates radiation, the radiation will not penetrate the fluid and cannot enter the indirect exposure channel. However, the treatment portion is designed so that the radiation from the UV source enters the indirect exposure channel 43 when the attenuation from the fluid is negligible.

The fluid leaving the impeller 3 flows in a spiral pattern disclosed in connection with the above embodiment. In this aspect, the radiation shield, along with the radiation source, is considered the transmission element of the present invention. Furthermore, if one or more floor elements 39, 40 are transparent to the radiation emitted from the radiation source, these elements are considered to transmit radiation to the fluid, so these elements Is also considered a transfer element of the present invention. Thus, the fluid passing through the radiation shield and thus the radiation source and the transmission element (if made of a radiolucent material) also flows in a spiral flow pattern comprising a radial velocity component V _r and a tangential velocity component V _t . The control method of the present invention can be applied to control the radial and tangential velocities.

  The above control method has the advantage that the magnitude of the radial and tangential velocity components can be controlled independently of each other. By using this control method, the flow rate passing through the apparatus can be increased or decreased, for example, while maintaining the magnitude of the tangential velocity component. Alternatively, the magnitude of the tangential velocity component can be increased without changing the flow rate. By using this control method, contamination to the radiation source can be eliminated, and the advantage that the tailing effect (particles block each other) can be reduced by increasing the tangential velocity component.

  The control method can include the use of information regarding the relationship between impeller rotational speed and, for example, heat, material or radiation transfer. This information can include quantitative or qualitative information regarding the correlation with the tangential velocity of the fluid, and the correlation can depend on the physical properties of the fluid. Information can be obtained, for example, from experiments or computer simulations. Typically stored in a database or other computer readable medium from which it can be retrieved by a control system used in the application of the control method of the present invention. Alternatively, it may be stored in a way that requires manual interaction as part of the control method. The control method can include controlling the speed of the impeller associated with one fluid or two or more fluids. The control method can additionally or alternatively include control of one or more throttle means, eg throttle valves.

In the above aspect, the radial and tangential velocities can be considered to be in a plane parallel to the plane of the transmission element. FIG. 12 shows an embodiment in which the transmission element 2 has a tube shape. The first fluid flows inside the transmission element 2, and the second fluid flows outside the transmission element 2 and inside the casing 18. Both fluids are shown to flow in a spiral flow pattern, and as shown, the tangential velocity component V _t is considered to be the rotating portion of the flow, and the radial velocity component V _r is the longitudinal velocity component ( This is considered to be indicated by an arrow labeled r in the figure. Since the radial component can be regarded as a component that correlates with the flow rate, and the tangential velocity component can be regarded as a component that does not correlate with the flow rate, this configuration matches the above.

  In accordance with a preferred embodiment of the present invention, recirculation may be applied to one or more of the fluids flowing through the device. Such recirculation can be implemented by directing all or part of the fluid flowing from the outlet of the device to the inlet of the device.

Claims (26)

A method for controlling the transfer of heat, material, radiation, etc. in or to at least a first fluid in an apparatus comprising:
The apparatus includes at least one stage including a transmission element (2) and a rotatable impeller (3), wherein the impeller causes the first fluid flowing out of the impeller to face the transmission element (2). The first fluid flow along the face of the transfer element includes a spiral flow pattern having a radial velocity component (Vr) and a tangential velocity component (Vt). ,
The device further comprises one or more restricting means for restricting the flow of the first fluid through the device;
The rotational speed of the impeller and the aperture are
i) the amount of transmission is a function of the radial velocity component (Vr) and the tangential velocity component (Vt), and
ii) A method in which the radial velocity component (Vr) and the tangential velocity component (Vt) are mutually controlled to be substantially independent. Transmission amount AT is
AT = f ₁ (Vr) + f ₂ (Vt)
Can be represented as
Where f ₁ and f ₂ are functions used to show the correlation between each of the tangential velocity Vt and the radial velocity Vr and the transmission amount AT,
The method of claim 1.   The method of claim 1, wherein the amount of transmission can be changed by changing the rotational speed of the impeller without substantially affecting the flow rate of the first fluid being processed through the device.   2. The method according to claim 1, wherein the flow rate can be changed by changing the rotational speed of the impeller without substantially affecting the amount of transmission of the first fluid in the apparatus.   The throttle means comprises a throttle valve, one or more dedicated cavities for throttling, a diaphragm, a constriction of a first fluid pipe, a counterflow or viscosity control means. The method described.   2. The method of claim 1, wherein the impeller rotational speed is increased in response to an increase in transmission demand and the impeller rotational speed is decreased in response to a decrease in transmission demand.   The method of claim 1, wherein the impeller rotational speed is decreased in response to an increase in transmission demand and the impeller rotational speed is decreased in response to an increase in transmission demand. The apparatus includes one or more channels through which the second fluid flows, the channels arranged such that transmission occurs between the first fluid and the second fluid via the transmission element. is, any one process according 請 Motomeko 1-7.   9. The method of claim 8, wherein one or more channels through which the second fluid flows are provided in the transmission element.   An apparatus includes an impeller for a first fluid and an impeller for a second fluid, and a method is responsive to a given transmission request for the impeller for the first and second fluids. 10. The method according to claim 8 or 9, further comprising the step of controlling the rotational speed of.   11. The method of claim 10, wherein the rotational speeds of the impellers for the first and second fluids are independently controllable.   11. The method of claim 10, wherein the rotational speeds of the impellers for the first and second fluids are rotated in common, such as disposed on a common drive shaft.   13. The device of claims 8-12, wherein the device comprises one or more channels through which a third fluid flows, the channels being arranged such that communication between the fluids occurs via the transmission element. The method according to any one of the above.   The apparatus of any of claims 8-13, wherein the apparatus includes an impeller for each fluid and the method includes controlling the rotational speed of the impeller for each fluid in response to a given transmission requirement. The method according to claim 1. If the device is further dependent on one or more throttling means, for example a first fluid passing through the device and / or claims 8-12, a second fluid and / or claims 13-14 If subordinate, includes one or more throttle valves to throttle the third fluid flow, and the method further increases the flow restriction by the throttle means in response to an increase or decrease in transmission demand or by reducing small, thereby comprising the step of increasing or decreasing small the pressure drop according to the restrictor means, the method of any one claim of 請 Motomeko 8-14.   16. The method of claim 15, wherein the aperture is increased in response to an increase in impeller rotational speed.   17. The restriction increase is controlled such that as a result of an increase in impeller rotational speed, the flow rate of one or more fluids passing through the device does not substantially change, for example, changes less than 5%. Method.   16. The method of claim 15, wherein the aperture is reduced in response to a decrease in impeller rotational speed.   19. The throttle reduction is selected such that, as a result of the reduction in impeller rotational speed, the flow rate of one or more of the fluids passing through the device does not change substantially, e.g., changes less than 5%. Method. Transmission element, said containing filter elements, any one process according 請 Motomeko 1 to 19 having a hole to pass only particles smaller than a certain particle size in the filter element.   20. A method according to any one of the preceding claims, wherein the transfer element comprises a heat transfer element.   23. The method of claim 21, wherein the heat transfer element includes an internal channel through which cooling / heating fluid can flow.   20. A method according to any one of the preceding claims, wherein the transmission element comprises a radiation source, or a radiation guide such that the radiation is emitted from the face of the transmission element into one or more fluids. Device comprises a plurality of stages, any one process according 請 Motomeko 1-23.   25. A method according to claim 24, wherein the transfer elements of the stage are similar to each other, for example identical to each other.   25. The method of claim 24, wherein the stage transfer elements are adapted for different transmissions.

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