JPS59100392A - Fluid heat exchanger - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION More specifically, the annularly corrugated tube is
Parts of heat exchangers that may have straight, J-shaped, helical or similar profiles in the form of tube-to-tube, shell-to-tube, or coil-to-shell (with or without a centerbody) The present invention relates to a high performance, compact fluid heat exchanger used as a fluid heat exchanger.

Heat exchangers of the ridge type and profile are known and can also transfer heat from one fluid to another, heating, cooling,
Temperature metals are used to condense, evaporate, or otherwise transfer to change the level of thermal energy in a fluid. This heat transfer places the fluids in close enough proximity to each other that the cooler fluid
This is accomplished by placing it so that it absorbs all of the heat from the hotter fluid. Thermal theory, heat transfer must occur without allowing the fluids to mix. because,
For example, if the colder fluid is a refrigerant, brine solution, or the like and the hotter fluid is hot water, mixing will prevent the hot water from standing after heating. be. Similarly, hotter fluids become contaminated, and thus, to avoid contaminating them, hotter fluids must be kept out of contact with cooler fluids.

Having a similar profile of the prior art, however,
Heat exchangers constructed from smooth-walled tubes are inherently limited in their heat transfer performance.

At flow rates in the laminar range, the heat transfer of the heat exchanger is proportional to the surface area of the tubes. In this way (7), it has been observed that the performance of the heat exchanger is increased by replacing it with a helical twisted tube.Such a heat exchanger , U.S. Patent No. 3, g, 2
/1. , 30'I specification.

17 However, the construction of heat exchangers made from helically twisted tubes has several drawbacks. The first is that the increase in surface area compared to smooth-walled tubes is not very large. The second is
Spiral tubes are more flexible than smooth-walled tubes, but
It remains relatively difficult to form leak-free contours. Furthermore, in certain contours, the spiral shape is
One of the fluids in the heat exchanger is provided with a flow path that interferes with the flow of the second fluid.

For example, if the pipe is American bamboo, θ5? When twisted into a helical profile by a method such as that disclosed in . It appears along substantially the entire length of the tube. Such a profile makes it difficult to make some heat exchangers, for which a smooth section of the tube is recommended.

Other early attempts to change the surface area of internal organs were devices with raised fins or other contoured surfaces, which could help heat exchange take place. It helps to increase the surface area covered.

However, devices with finned tubes have other drawbacks such as increased thickness. Although finned tubes have a relatively large surface area, such tubes create a substantial increase in flow resistance within the area of the fins. In this case, the fluid flowing transversely to the plane of the fin will tend to precipitate some impurities or dirt near the base of the fin in the region having a lower flow velocity. Same'f! ! :Has. Such stagnation areas (bow 2, otherwise reduce the efficiency of tube-to-tube type heat exchangers of tube performance.

Another problem that arises from the use of finned tubes is the loss of heat exchange efficiency due to the high thermal resistance between the tube and the fins. When the fins are joined to a smooth tube by welding, brazing, or other fabrication techniques, does the seam between the pieces have a thermal resistance? Increases the efficiency of the heat exchanger.

Fins bonded to the outside of the tubes also tend to increase the stiffness of the assembly, which is a disadvantage in many heat exchanger profiles where flexibility of the tubes is required.

It is an object of the present invention to obtain an improved heat exchanger which overcomes these and other disadvantages of conventional heat exchangers formed from smooth-walled tubes or twisted spiral tubes, especially in the laminar flow range. It is an object of the present invention to obtain a heat exchanger exhibiting increased efficiency.

It is another object of the present invention to provide a heat exchanger incorporating a central annularly corrugated groove having an increased surface area compared to prior art heat exchangers of the same profile. .

It is yet another object of the present invention to obtain a heat exchanger that provides an increased surface area, overall integrated interior, and therefore a reduced overall light area.

For a given tube diameter, a heat exchanger that can be formed into tighter pends? It is yet another object of the present invention to obtain.

Fabrication of all smooth wall parts to improve? It is yet another object of the present invention to provide an improved heat exchanger having annular corrugated tubes containing annular corrugated tubes.

It is a further object of the present invention to provide an improved heat exchanger that is economical to manufacture and has increased performance.

Purpose and features of the present invention? According to one embodiment of the present invention shown, a first tube for transporting a first fluid in a first direction having a passageway therein and having first and second ends; a second tube for transporting a second fluid in a second direction, disposed inside said passageway and having a plurality of annular waves thereon; an inlet connected to the first end of the first tube for conducting into a first tube; and an inlet connected to the second end of the first tube for removing all of the fluid from the first tube. An improved heat exchanger is provided comprising an outlet connected to an end.

The applicant has discovered that the above objects can be realized by a heat exchanger of the type described above, by making use of an inner tube having an annular wave thereon. .

The use of annularly corrugated tubes in the heat exchanger of the present invention provides improved heat transfer throughout thickness resulting from the greatly increased effective surface area of the heat exchanger boundary. Experiments have shown that the use of annularly corrugated internal tubes provides a more useful heat transfer area (i.e., surface area) in the range of 1 lo-t, o-chi than a smooth-walled tube of the same length. It was shown that This is in contrast to the surface area of known twisted tubes, which have a total area thickness that is only 1.23 to 1.23 inches larger than that of a smooth walled tube. The further improvement in heat transfer provided by the present loading results from the absence of extraneous (thermal) conductive material on the surface of the tube, as in conventionally contoured tubes.

Only the thickness of the tube separates the two fluids.

Other advantages arise from the convenience of such an internal tube.

Annularly corrugated tubes are much more flexible than known tubes. This arrangement (simply, on the tube,
Introduction of non-deflectable external contours? Don't just avoid the tube? , making it more flexible than smooth tubing or even threaded tubing.

Furthermore, since the manufacture of annularly corrugated tubes is known, it is possible to make such tubes with flat land sections on them, which greatly reduces the overall utilization of this tube. It is more useful for increasing

It is believed that further advantages realized by heat exchangers made in accordance with the present invention will become apparent from the following description of exemplary embodiments of the present invention.

The improved heat exchanger according to the invention has particular utility in biomedical applications as part of a blood oxygenator or cardiac arrest unit. This heat exchanger is particularly suitable for such applications. Because an annularly corrugated tube has an increased surface area per unit length? This is because it has. When this heat exchanger is used in the field of such blood oxygenators or cardiac arrest units, the flow of blood through the heat exchanger is controlled to prevent undue foaming of the blood. , it is military police to stay within the laminar flow range. Since the amount of heat transfer is substantially proportional to the surface area, the improved heat exchanger according to the present invention provides substantially the same amount of heat transfer at lower flow rates by increasing the surface area per unit of tube thickness. Heat transfer? You can get it. Or does a heat exchanger (fabricated according to the present invention) still have comparable performance than a heat exchanger formed from twisted cone tubes of other prior art purchases?
While having a smaller total volume of gold H.

Thus, the improved performance of the heat exchanger according to the present invention means that a smaller volume of blood can be used in fewer people's bodies during use of a blood oxygenator or cardioplegia unit. so that it is necessary to be removed from.

A circular wave that can be mastered in such biomedical fields? An additional advantage resulting from the use of attached tubing (1, reduced filling volume for the blood flow path when all other dimensions are constant 11). Since it has a larger volume than a spiral twisted tube of comparable dimensions, there is necessarily less space for the blood to flow. The increased surface area of the cut tubes results in increased heat transfer, so even though a smaller volume of blood is in the biomedical unit, there is no corresponding reduction in heat exchange performance.

It is believed that the detailed description of the invention set forth above, as well as other objects, features and advantages, will become apparent from the following description, taken in conjunction with the accompanying drawings which illustrate presently preferred embodiments of the invention.

Reference is now made in particular to FIGS. 1 and 2, in which the basic outline of a tube-type heat exchanger according to the invention is shown.
It is generally designated by the symbol S. A first internal tube IO is placed inside the second external 'W, 2o with an internal passageway, 2/. Inner tube /θ(ri) A series of 7.2 annular waves are formed, and this wave 12 is
It has a valley /3 and a cooperating peak lll having a smaller diameter than the diameter of the passage, 2/. The first fluid /6 flows through V↓ in a first direction generally indicated by arrow /g.

The other fj, 20 are generally cylindrical and have a prefix (1 outlet 217, respectively, a fitting, a 26th place, and a few phrases each, by !g). The second fluid passes in the direction indicated by the arrow 7a through the fitting roller at the supply pipe 22, and the second fluid passes through the fitting roller at the fitting 22.
Proceed through Otsu to joint 2gK, 8'li [corf], 41
From arrows, in general? Go out in the direction indicated by da.

As best illustrated by the second:' ,
The manufacture of annularly corrugated tubes is known and can be carried out, for example, by rolling or finger shaping. A method for the manufacture of such tubes is described in U.S. Pat. , q g g;

Those skilled in the art will appreciate that the first fluid 16 or the second fluid 30 may be a hotter fluid, and that the illustrated countercurrent flow of the fluid in question is merely exemplary. , that both fluids may flow in the same direction, that both fluids may be stationary at a point, and that the particular contours of the illustrated supply and outlet pipes may be varied. , it is understood.

FIG. 3 depicts another embodiment of the invention, but generally elements corresponding to those of FIGS. 1 and 2 are designated by like numerals with the addition of 3 ( For example, the first fluid is 3/6).

The profile of FIG. 3 is often utilized in refrigeration systems, where the second fluid 330 is the main fluid (e.g., green water, air) to be cooled by the refrigerant 3/l. This embodiment has been found to be particularly useful for condensers. This is because the annular groove allows the formation of drops within it.

A third embodiment of the invention is shown in Figures 1 and 5, in which elements similar to those shown in Figures 1 and 2 are designated by corresponding reference numbers. It is appended and identified (for example, like 1st fluid /I/B). This profile of the invention incorporates additional known elements (Spurger
') is particularly useful as a blood oxygenator or cardiac arrest unit. This example is
Although specifically described as such a device, it is clear that this profile also has other uses as a heat exchanger.

When this embodiment is used for such an end purpose, the second fluid a3o is blood and the third fluid 'J
/4 is the coolant, generally lukewarm water. This outline shows the coolant placed inside the shell (external tube) 172θ?
It has an inner tube 1110 for transporting, and also has a shell?
A second fluid, blood tlJ(1), flows through the gold. internal! <'/θ is spirally wound around the centrosome 'IIIQ, while the centrosome l111Q occupies the central volume ffk of the shell Q2091 and thus restricts the flow of blood. , blood q30 is cooled in the inner tube tIi.

Make sure to approach and pass through. The blood oxygenator is installed in a known manner in the bottom of the shell tt:to.
rger (not shown).

FIG. 5 shows the arrangement of the central body qtto, which may be solid or hollow. Centrosome/lq.

The outer surface of the shell and the inner surface of the shell form a flow path for the second flow. The second tube '110 is placed in the flow path so that the second fluid holder 30 is in the inner tube 1A.
Adjacent annular waves of soil on the surface of 10 and shell lI20
must flow parallel to the annular wave through a small area between the inner surface of the annular wave and the inner surface of the annular wave.

Such a restricted flow path results in much improved heat transfer throughout the thickness.

This allows the tube 1110 to wrap more completely around the central body ttqO'. This gives rise to several important advantages.

The first is to allow a larger number of inner tubes to be placed in a shell of the same volume. This dramatically increases the heat transfer performance of the device, given the increased surface area of a unit length of the inner tube (resulting from the annular wave profile, as discussed above). More importantly, the same amount of cooling can be accomplished with smaller equipment. Thus, when the present invention is used as a blood oxygenator or cardiac arrest unit, an absolute minimum volume of blood needs to be removed from the patient's body. When the person is a child, the need to drain a small volume of blood is increased.

Other essential features of the invention give rise to other advantages.

The same waves &7.2 are generated in the direction of flow of the blood 't30, for the direction of flow of the blood 't30, as it allows the tight wrapping of the internal tube 10 around the central body tiuo. The inner tubes yi face substantially parallel to each other.

Such a profile creates a lower flow resistance than prior art devices.

Furthermore, flow paths parallel to the annular waves create much less turbulence inside the shell. In blood oxygenators, this turbulence can cause undesirable agitation and foaming of the blood. Thus, when the present invention is conveniently used as a blood oxygenator or cardioplegia unit, the present invention provides the ability to maintain the same degree of heat transfer throughout the device. Make it possible to achieve and pass.

As another example, the device depicted in FIG. -'i indicates.

Elements that are common to those shown in Figures 1 and 2 have subscripts (such as the first fluid A/A).

In this embodiment, a number of internal tubes bi.

are placed inside the shell (external '74) b, 2o. To ensure flow around the shell &20 of the first fluid 6/2, a series of alternating baffles bso are arranged along its length.

These baffles 1-50 cause the flow of the second fluid 430 to be in an "up and down" flow fashion, thereby causing the flow to be generally parallel to the annular wave 4/-1. . In this way, the performance of the heat exchanger is optimized.

As mentioned above, flat lands may be arranged at predetermined locations along the length of the inner tube 610, such that the baffle plate 650 is secured to the inner tube, 4/0. It is also worth noting that all the places where it can be used can serve advantageous purposes.

As will be readily apparent to those skilled in the art, the foregoing description, while highly recommended, does not nevertheless reflect the exemplary present invention V.
However, the present invention may be embodied in other specific forms or forms without departing from the spirit or essential characteristics thereof. be.

[Brief explanation of the drawing]

Figure 3 is a partially cutaway front view of a positive tube type heat exchanger according to the present invention; Part I, IIJ cross-sectional view of the second embodiment of the heat exchanger in the form of a single tube, Figures 1 and 2 are:
A partially cut-away front view of a coil and shell type heat exchanger as another embodiment of the present invention, Figure g5 is &-3 in Figure 4.
FIG. 6 is a partially cut-away front view of a tube type heat exchanger according to another embodiment of the present invention. 41

Claims (1)

[Scope of Claims] l A first tube for transporting a first fluid in a first direction, the tube having a passage therein and a first end and a second end; a second tube for transporting a second fluid in a second direction, having a plurality of annular waves thereon; and a second tube for transporting a second fluid in a second direction; an inlet means connected to one end and said second fluid? and outlet means connected to the second end of the first tube for discharging from the first tube. - the surface area of the part of the second tube having an annular wave thereon is smaller than that of a smooth-walled tube of equal length by qθ~100
% of the fluid heat exchanger of claim 1. 3. The fluid heat exchanger according to claim 1, wherein the outer diameter of the annular wave is smaller than the inner diameter of the first tube. q. A fluid heat exchanger according to claim 1, wherein the plurality of annular waves comprises the entire length of the second tube. S. Claim 1, wherein the second pipe further has at least one flat land portion thereon.
A mounted fluid heat exchanger. 4111 A second tube is connected to the first end of the second tube for introducing the second fluid into the second tube and the second end thereof. and second outlet means connected to the front second end of the second tube for discharging all of the second fluid from the second tube. Fluid heat exchanger as described in Section. 7. The fluid heat exchanger according to claim 1, wherein each of said first to second hundredth tubes has a full length, and said axes of said first to second tubes are coaxial. g. The fluid heat exchanger according to claim 1, wherein the first direction is opposite to the second direction. 9. The fluid heat exchanger according to claim 1, wherein the first direction and the second direction are the same. 10. The fluid heat exchanger according to claim 7, wherein the first and second tubes are coiled. // The fluid heat exchanger according to claim 1, wherein said second plurality of second tubes are arranged inside said first tube. 2. The fluid heat exchanger according to claim 1, wherein a third number of baffle plates are arranged inside the first tube. /3 Each of the second plurality of second tubes has at least one flattened portion, and each of the baffle plates has a portion of the second plurality of second tubes, 13. The fluid heat exchanger according to claim 12, wherein the fluid heat exchanger is fixed at its flat land portion.