RU2001374C1 - Porous-compact heat exchanger - Google Patents

Description

The invention relates to heat engineering, a. more specifically to heat exchangers with heat transfer intensification, low mass, and small dimensions. The proposed porous-compact heat exchanger (PCTO) is a highly efficient and compact heat transfer device for heat engineering and energy systems using gases as heat carriers, this determines the possibility of its use in heat engineering, air conditioning systems, cryogenic technology, power engineering, engine building, etc.

The proposed porous compact heat exchanger can operate in a wide pressure range, the maximum operating temperature depends on the type of heat carrier and the material of the porous filler. So, for a copper filler we have: for inert gases Tmax 1000 K, for air Tmax 430 K.

A heat exchange device is known in which porous fillers are placed both in the inner and outer tubes. These fillers have the same thickness and are located in the same plane. Porous fillers are inserted into pipes with tension, which is ensured by their porous structure, and are thereby held in position.

However, this heat exchanger device has significant drawbacks, on the one hand, which do not allow the device to rationally use the entire heat transfer surface of porous fillers, which leads to an increase in the mass and dimensions of the structure, and on the other hand, leading to significant hydraulic losses in the device’s paths, which in turn leads to unacceptable power consumption for pumping coolants through them.

A heat exchange device is also known in which a porous filler fills the space between two shells. The longitudinal inlet and outlet coolant channels are evenly spaced around the circumference and are adjacent to the walls of the shells. The transverse flow of the coolant through the porous filler is carried out in the radial direction.

In this device, the heat transfer intensifier is most efficiently used in connection with pumping heat carrier through it in the direction of its smallest thickness. This leads to minimal power consumption for pumping the coolant through the porous filler. However, hydraulic losses through the pseudo device, apparently, will still be large due to losses in slotted longitudinal inlet and outlet coolant channels with a length comparable with the length of the device.

The aim of the invention is to reduce the weight and dimensions, reduce material consumption and increase the structural strength of the proposed porous compact heat exchanger, as well as providing minimal losses for pumping through the device of its coolants.

The goal is achieved due to the fact that its body, dividing impermeable

partitions (membranes), spacing pins between them and porous fillers are made as a single unit, i.e. monolithic, moreover, the spacing pins in the slotted channels are aligned with each other, forming a stitch between the membranes and the bottoms of the heat exchanger body, which are separated from the extreme porous fillers by a gap through the pin processes of the bottoms, and

the porosity of the fillers is selected in accordance with a ratio of 0, 0.85 when the structural relative thickness of the porous material changes from d 1 to d 10, while the heat exchanger body is cylindrical, round or oval in shape, to which the corresponding inlet and outlet hot and cold slit . input and output manifolds are connected to the windows on the housing

heat exchangers of the heat exchanger, forming hot and cold paths with its corresponding channels,

In the proposed PCTO, the principle of its operation is based on the intensification of heat transfer processes in the heat exchanger by introducing a porous filler from materials with high thermal conductivity into the ducts. In a structural sense, it is a monolithic body,

consisting of a shell with bottoms, divided internally by impermeable membranes (baffles) into slotted channels isolated from one another. Slotted channels are filled with porous material. TO

four collectors are welded to the monolithic body, forming heat exchanger paths together with the corresponding slotted channels. All odd slotted channels connected by openings to the corresponding collectors form a path, conditionally called cold. Similarly, even-numbered slotted channels and their corresponding collectors form a path, conditionally called hot. The number of slotted channels in a PCTO is always odd so that the cold path channels are extreme.

With the usual cubic layout of the heat exchanger, in particular PKTO. its main structural dimensions are characterized by a length L, a width B and a height h of a single slotted channel, moreover, at constant L and B, the channels of different heat exchanger paths can differ only in height h. The total height H of the heat exchanger is determined by the set of a number of its slotted channels, the value of which depends on the level of thermal power transmitted by the PCT Q.

The operation of a heat exchanger of any type, including the proposed PCTO, is described by a mathematical system of four equations:

- heat transfer equation;

- Equation of the balance of the transmitted heat power;

- two hydraulic Darcy equations for two heat exchange paths, by which the pressure losses in each of them are calculated when the corresponding coolants are pumped through them.

Solving the indicated system of equations together, one can obtain a number of relations necessary for calculating heat exchangers according to TK. In particular, for the proposed PCTO, one can obtain an expression for the ratio of the specific consumption of its coolants:

Gy g7t

CPI DTT n hi

Sr2 D T2 EZ G12

the implementation of which will ensure its structural tie, i.e. provides

execution of Li L. Here

 G

G b P P

where G is the mass flow rate of the coolant. Ј - porosity of the porous filler;

n is the number of slotted channels about the corresponding path of the heat exchanger.

For the specified heat carriers and, therefore, their specific heat capacities Cm and Cp2, as well as the given temperature g-decays ATi and AT2, the first factor in the expression is given and then the value of the ratio Gy2 / Gyi can only be controlled due to the second factor, the parameters of which are usually set from 1 effective considerations.

From the above expression, barely / vO, that the proposed PKTO can have

The first non-trivial option occurs when the factor Cpi ДТ1 / (Ср2 ДТг) 1, which corresponds to the use of different and non-uniform heat transfer media with very different properties in heat transfer.

The second trivial option occurs when the factor Cpi ДТ1 / (Ср2Д Т2) - Cihi / fejta) - 1. i.e. here Gy2 Gyi, that for

0 Е Ј2 and hi - h2 corresponds to the use of the same type of heat carrier in both paths of the device.

For a general non-trivial version of the operation of the proposed PCTO from

heat transfer equations and determine the heat transfer coefficient, we obtain the equation

twenty

rdtl

2. .2. 1, b, b2h,) m

aiaiM 7p1 02E2b2 7p2 2 MY Ј2 fa

-f (Re).

where Q is the heat output transmitted by the PCTO;

0

0

5

0

D1l - average logarithmic pressure of its transmission;

F is the total heat transfer surface of all PCTO membranes;

K is the heat transfer coefficient;

Re- Reynolds criterion.

In addition, here in the denominator of the fraction, the first two terms are the thermal resistance of heat transfer from the heat carrier to the porous filler frame in the hot PCTO tract and the thermal resistance of heat transfer from the porous frame to the heat carrier in its cold path. These thermal resistances have analogs in classical terms for K, which are valid for smooth channel heat exchangers. The third term in the denominator of the fraction is the additional and specific thermal resistance of heat transfer in the PCTO, which occurs when heat is transmitted through the frames of their cirrus fillers. The fourth term in the denominator of the fraction is common and represents the heat transfer of heat when the heat flux passes through the separation heat transfer of the PCTO membrane.

The numbers 2 about the expression for the heat transfer coefficient are due to the adopted 6rqi design scheme, characterized by one dividing membrane and

melting channels (h / 2) of the corresponding heat exchanger paths.

In the written equation a, Nu А / dr are the corresponding heat transfer coefficients from the hot coolant to the porous filler frame and, conversely, from the filler frame to the cold coolant, where Nu is the Nusselt criterion: A is the thermal conductivity of the respective coolants;

dr „j - hydraulic di (1 U Е) + 2h

the meter of the corresponding slot channel, dn is the wire diameter of the MR structures of porous fillers; e - porosity of the respective fillers;

4 (1st) a -i-j dn

- specific surfaces of the corresponding porous fillers; 5m thermal conductivity of the frames of the corresponding porous fillers; h is the thickness of the separation heat transfer membrane; Am the thermal conductivity of its material; JJP th (m) / m are the so-called edge coefficients. forming a temperature profile in the porous fillers of the corresponding slotted channels of the PCTO; m Va h2 / (4 A dn) parameter of the corresponding edge coefficient.

For the trivial way of functioning of the proposed PCTO, the equations written above are simplified and take the form

Q

 TO

F atnaahrjp

for the Nusselt criterion Nu A Re Pr1 / 3, where the Pg criterion is Prandtl. The exponent 1/3 in the Prandtl criterion is generally accepted for porous systems.

In addition to the thermal characteristics of porous systems, experimental data on the purging of samples and PCTO also obtained data for calculating the hydraulic loss coefficient in these systems

Ј f (Re). using the Darcy equation to calculate it.

As a result of experimental studies of porous MR structures from copper with dn 0.1 and 0.2 mm were, in the first

approximation, the following empirical relationships are defined:

- to calculate coefficient A in criterion Nu

ODU0749-E4 29

in the range of e0 .97-6y 935 -0.6..D95;

-for calculating the coefficient n in the criterion Nu n - 1.59 (1- Ј l9) in the range of .6 ... 0.95;

- for calculating the thermal conductivity A of the frame of the porous filler based on copper

, 380 (1-e0 269)

Ј0.586

0.55 ... 0.95;

-to calculate the coefficient of hydraulic losses in a porous filler

t 1.88.1.8.82,

Ј (R§ +) in the range E

where the Reynolds criterion for porous systems (fillers) is calculated from the ratio Re Gy dr ///. Here p is the dynamic viscosity of the coolant.

This version of the operation of the PCTO and the equations describing it proved to be convenient for experimental studies of the processes of heat transfer and heat transfer in porous PCTO systems. Porous compact heat exchangers and two-channel heat transfer samples based on them, made in a trivial design (ei Ј 5 and hi - ha), blown in a gas-dynamic bench setup with hot and cold air, allowed us to obtain experimental data, the processing of which according to the above equations made it possible to first obtain the dependences cf (Re). h on them and empirical dependencies

Based on the performed systematic experimental studies of porous MR structures used in the proposed PCTO as intensifying the heat transfer process in heat exchangers of porous fillers, the empirical relations presented above represent the initial base of initial data for iterative optimization to optimize the design of the heat exchanger by weight and dimensions with allowable relative hydraulic losses in the device paths not exceeding -p- 1%. The latter requirement is a very strict requirement, which is extremely difficult to satisfy especially at low porosities of porous fillers, since the hydraulic loss coefficient is inversely proportional to the porosity F.

On the other hand, on the other hand, other equally important parameters of MR structures, which also depend on their porosity, with its increase, begin to sharply lose their intensifying heat transfer properties.

From the foregoing, there follows an essential distinguishing feature of the proposed PTO, 8 namely: the porosity of their porous fillers based on MR structures should be in the range from 0.75 to E 0.85, and the lower limit of porosity is less limited here, if possible p-1%.

Using the available source data base, the proposed PTOs were calculated in two versions of their functioning: in non-trivial and trivial, according to the exemplary TOR, presented here in the form of Table 1 with notes.

In the calculations, from structural and strength considerations, in order to satisfy the minimization requirements for the design of the PCTO by its weight, it is advisable to make its monolithic body cylindrical or oval-cylindrical, which will allow to have reliable radial strength of the structure with minimal live sections of its body in the order of 1 ... 3 mm, underneath the heat exchanger, which is also attached to the separation membranes.

And this is also an essential distinguishing feature of the proposed PCTO.

If the porous fillers do not completely fill the cylindrical or oval-cylindrical slot channels of the PCTO, with the formation of internal receiver collectors in each slot channel, then we can assume that the heat exchanger is assembled by approximately a cubic arrangement. But here a part (30%) of the heat transfer surface of the membranes will be lost, which, of course, is not desirable.

If the porous fillers completely fill the slotted channels of the cylindrical housing of the PCTO, then its arrangement will be cylindrical.

Both layout options of the proposed PTO are possible, the solutions to which, however, are made upon the requirements of specific TK.

As a result of the calculation of PCTO according to TK, the lengths of porous fillers LI and 1-2 are determined. as well as one of their thicknesses h (one of the heights of the slotted channels) for a given other According to technological considerations, a smaller height should not be less;;. -1 mm.

When calculating the PCT, they achieve its ties, i.e. compliance with the conditions

Next, the width of the slotted channels of the PCTO is determined by the layout ratio. For the cubic arrangement of the heat exchanger, the coefficient, Axial strength, of the PTO is usually ensured by the internal casing stitching with pins of all its membranes and bottoms, as well as by the liquid-phase 0 welding of external input and output collectors to its body.

The PCTO calculations performed here were performed at. the assumption that they have a cylindrical layout and complete filling of slotted channels with a porous filler. Moreover, it was assumed that, i.e. .

Some of the results of the calculations of the proposed PCTO using the 0-base data base for copper-based MR structures and approximate TK are presented in Table 2.

From the data in Table 2 it can be seen that in the non-trivial version of the PCTO, when it uses heat carriers with very different thermophysical properties, especially in their heat capacities (see table 1), with allowable losses in the DDR

0 heat exchanger max-p 1% implemented

not very large heat transfer coefficient W / (m2 K). Whereas in the trivial version of PCTO, which uses a coolant with medium thermophysical properties, this coefficient is three times higher and is equal to 1231 W / (m2K) with the same hydraulic losses in the tracts.

In accordance with this, the specific gravity of a nontrivial PCTO (at 2.7 kg / kW) is approximately 3 times higher than the specific gravity of the trivial PCTO (at 0.974 kg / kW).

The specific gravity of the proposed device is 2.7 kg / kW, although another 6 is permissible, but not desirable. Her desired level

5 upkg 1 kg / kW.

For the same reason, the radial dimension of a non-trivial PCTO is approximately 6 times larger than that of a trivial heat exchanger.

0 It should be noted that when calculating a nontrivial PCTO, its tie at given dni dn2 is 0.2 mm; Ei 0.8; 0,85 0.85, hi - 4 mm was realized only at h 18 mm and the hydraulic condition along its paths

5 DR

 S1%, as can be seen from Table 2, was performed.

R

Namely, the need to increase the height of the cold channel of the non-trivial PKTO to 18 mm in order to tie it and attach to the results that are shown in Table 2. Moreover, this need for dictation .... to fulfill the conditions - 1% for

P cold channel.

Attention is also drawn to the fact of low specific flow rates of coolants, at which the heat exchanger is connected with a non-trivial version of the PTO versus trivial.

At the same time, since the Reynolds criterion is directly proportional to the specific coolant flow rate, this means that the non-trivial PCTO connection was realized at low values of the parameters: Re, Nu, and at elevated Ј values, which led to a low value of the heat transfer coefficient K for this variant of the heat exchanger and difficulties in overcoming hydraulic losses in it along the slotted channels of its paths.

It is noteworthy that the fact that the diameter of the wire in their porous fillers from MP structures is equal to dn 0.2 mm is common to both calculated variants of PCTO.

In itself, this fact is compelled, since there is no database of initial data on MR structures formed from large-diameter wires. Of course, it needs to be created, but for this it is necessary to carry out additional experimental studies.

As can be seen from Table 2, this diameter of the wire of porous fillers perfectly satisfied the trivial version of PCTO and, apparently, poorly satisfies its non-trivial version.

The results of the analysis of the calculated data of the non-trivial version of PCTO show that, in fact, when using heat transfer agents with very different thermophysical properties in porous-component heat exchangers, in order to more conveniently tie it, it is necessary to use porous fillers based on MR structures with different wire diameters, including significantly exceeding dn 0.2 mm.

The analysis shows that in this case, a significant increase in the heat transfer coefficient K is possible when performing

requirements 1%, in particular due to por

the possibility of increasing the hydraulic diameters of the slotted channels in

both paths of the heat exchanger, even at their minimum heights.

The implementation of these features will allow for non-trivial options

PTTO receive characteristics not inferior to the characteristics obtained from trivial heat exchangers, and maybe improve the characteristics of the latter.

From the foregoing and reviewed

another significant distinguishing feature of the proposed PCTO follows. namely: structural thickness of the porous material of its porous fillers, for example, the diameter of the wire MP, should

is within the range of OTdn 0.1 to dn 1.0 mm. Moreover, the lower limit is limited by purely technological considerations of the possibility of manufacturing such MR structures, and the floating upper limit

first of all, it is limited only by considerations of expediency, as well as by the techno-yugic possibilities of their manufacture, taking into account that MR structures are formed from winded wire

spirals of various diameters.

If we take here the first lower limit of the restriction dn of 0.1 mm as the base one, since it is seriously limited by technology, then the essential distinguishing feature discussed above can be formulated in relative terms, namely: the structural relative thickness of the porous filler material should be in the range from 1 to

d 10.

It should be noted that the thermal and hydraulic characteristics of MR structures in an explicit form are determined by its parameters: porosity Ј. wire diameter dn and the ratio of the diameter of the winding (core diameter for winding spirals) to the diameter of the wire dK / dn, as well as not explicitly, it is possible the degree of shrinkage during their formation by pressing and their thickness

Thus, there are many degrees of freedom in MR structures, and to determine the nature of their influence on the thermal and hydraulic characteristics of these structures, very extensive experimental studies will be required, but this will automatically expand the initial source database for the calculated searches of the optimal design options for the proposed device for any cases of their functioning within the framework of the assigned TK.

It should also be noted that, upon completion of the indicated volumetric experimental studies and analysis of their results, circumstances may appear. which will allow us to write a separate taste for the MR structure as an object used in the PCTO proposed here.

The performed calculations of the proposed PCTO according to the scanty base of initial data, however, also showed that approximately 60 ... 70% of its mass falls on the mass of porous heat transfer fillers, although they have a high porosity of the order of 8.

In Fig.1 shows the proposed heat exchanger (longitudinal section bb in Fig.2 and 3); figure 2 is a section aa in figure 1; in Fig.Z - section bB in Fig.1; Fig. 4 is a graph of the operation of an experimental full-scale porous compact heat exchanger.

The proposed porous compact heat exchanger has a monolithic body 1 with bottoms 2. The body is assembled from rings 3, between which are inserted impermeable dividing walls (membranes) 4, forming flow through slotted channels 5 of the heat exchanger. The slotted channels are partially or completely filled with porous-permeable fillers b, for example, from MR structures that intensify

heat transfer in the device, with spacer pins 7 evenly spaced in the fillers. In case of incomplete filling of the slotted channels 5 with porous fillers 6, internal receiver collectors 8 are formed in them, which are absent when the channels are completely filled with filler. In the rings 3 of the monolithic body 1, slotted windows 9 for the flow of hot coolant and slotted windows 10 for the flow of cold coolant are cut through. Outside the guns of the monolithic body 1, above the corresponding slotted windows 9 and 10, there are inlet and outlet external collectors 11 and 12, respectively, for hot and cold fluids with inlet fittings (nozzles) 13 and 14, respectively, for hot and cold fluids.

The proposed porous compact heat exchanger, for example, in the mode of counterflow of heat carriers works as follows.

Suppose, for example, that a coolant enters the heat exchanger through the lower inlet pipe 14 and the lower external collector 12, as well as through the lower slotted windows 10 of the housing 1 and enters the slotted channels 5 filled with the porous filler b partially or completely, respectively, through the internal receiver collectors 8 or, in their absence, n direct In this case, the cold coolant enters only the cold channel 5 of the heat exchanger. Further, the coolant flows through these slotted channels upward through the corresponding 5 porous fillers 6 in contact with the separation membranes 4, through which it receives the heat flux from the hot heat carrier flowing in countercurrent, from top to bottom, in the same order, but already through hot channels 5 of the heat exchanger through their hot porous fillers 6. Naturally, cold coolant is introduced into the heat exchanger and removed from it through 5 cold external collectors 12 and pipe 14, and the hot one corresponds to enno through the hot outer manifolds 11 and tubes 13.

It is understood that the proposed PCTO 0 may also work in a straight-through version, but, like any other type of heat exchanger, is less efficient.

The following 5 mechanism of its functioning follows from the above example of a description of the operation of the proposed PCTO. A hot heat carrier flowing through a hot porous filler gives off heat to its frame. This frame brings heat through the separation membrane to the 0 cold frame, from which this heat is removed by the coolant. With this operation, the effect of intensification of the heat transfer process due to the porous fillers 5 of the proposed heat exchanger is realized.

The indicated effect of the intensification of the heat transfer process was confirmed experimentally by the results of blowing both of experimental PCTs and their two-channel experimental models (samples) and is expressed by the fact that in this complex process of heat transfer, the heat transfer process between the frames of porous fillers and the heat transfer fluids described which is determined by criterial power dependences, has a degree under the Reynolds criterion.

In the process of conducting research on the proposed porous compact 0 heat exchanger, a small experimental series of 4 units was manufactured. These are mainly 15-channel PCTOs, in which 7 channels are hot and 8 channels are cold. These heat exchangers are made in a trivial design with a channel height of h-5 mm, porosity of porous fillers and MR structures on a copper base f - 0.8, with a wire diameter of dn 0.2 mm and an inner diameter of their body of 98.5 mm. Some of them were incomplete.

channels, i.e. approximately cubic layout g, mm Part of the design of these flKTOs was a housing with bottoms, spacers, membranes and manifolds with heat-supplying nozzles made of unalloyed structural steel St20, and part of stainless steel 12X18H10T. The spacing pins made of the corresponding steel had a diameter of 5 mm, and their number in the slotted channels was not fully filled with porous filler 17 and full - 19. The membranes were used in two thicknesses: from St-20 (5m 0.5 mm and from 12X18H9G (, 25mm.

The real heat transfer surface of the membrane, determined by the filler without the end surface of the pins, was respectively 55 cm for an incomplete half-fill, and 2 cm2 for a full fill, i.e. In the first case, the total .. heat transfer surface of the 14 membranes of the 15-channel PCTO will be 770 cm2 0.077 m2, and DO of the second 1008 cm2 - 0.1008 m2, i.e. these surfaces differ by 31%.

The weight of the design of the 15-channel PKTO together with external collectors and coolant supply pipes is 3.4 kg.

The dimensions of the cylindrical part of these heat exchangers are: outer diameter in the body 102 mm, height in the body 105 mm, pnsot without flanges (height of the heat transfer part of the device) 80 mm.

The top pinet of the casing is 1 75 mm, the call thickness is toro1.5 mm which should be recognized as overpriced here.

Using the existing source dhmnnh base (gm qfcinjp), for the portable compact heat exchangers described here were at HcntMui on the PCM dependencies proposed in Fig. 4, assuming incomplete filling of their gap channels with porous fillers from copper-based MP structures for various their porosity h using a wire with d - 0.2 im. In the calculations, in addition, the following is typical: the average heat pressure t drink along the PKTO paths is 2 MPa (20 atm), their average temperature for inert gases is Ha and for air is 00 K. Relative

path pressure losses were assumed to be 1%.

From the data of FIG. 4, for the considered PCTO with fixed porosity of their porous fillers g O we will have the results presented in Table 3.

If the average logarithmic temperature head of heat transfer in the considered PCTO is reduced by 2 times, i.e. If it takes Atn 10 K, then the specific mass characteristics of these heat exchangers will deteriorate when they are physically unchanged in mass and dimensions, i.e. will increase by 2 times. But then

blows notice that D 1p 10 K is extremely

small, although for some operating conditions the proposed PTO may be required, but even with such

Under conditions, these heat exchangers will function efficiently.

 The main advantage of the proposed porous compact heat exchanger when working with gas heat transfer fluids

at least in its trivial design, as can be seen from the data in Table 3, it consists in low mass and overall characteristics (0.5 ... 1.5 kg / kW with an average logarithmic temperature head of 10 ... 20

degrees for coolants of the hydrogen, xenon series, respectively, with an average pressure in the paths of 2 MPa and at very low relative pressure losses in their paths of 1%).

With experimental expansion

source data bases, for design searches of more and more optimal design options offered by PTTOs, the ability to find designs and

For their non-trivial execution, when using non-uniform heat carriers with strongly differing thermophysical properties in them, providing such heat exchangers with mass

characteristics that are not inferior to the characteristics of heat exchangers with tririal design.

(56) U.S. Patent No. 3,433,299.Cl, published. 1969.

USSR copyright certificate No. 486205. class 3/02. OPERPICK: Q73.

Note. 1. A counterflow circuit for supplying heat carriers to the heat exchanger is contemplated.

2. The thermophysical properties of the heat carriers are taken from the reference literature at their average temperature along the heat exchanger paths T and at their average pressure in them P - 10 -105 Pa (10 atm).

AR

3. The relative allowable pressure loss along the heat exchanger paths is 1%.

P i.e. , 1 -105Pa (0.1 atm).

Table 1

Continuation of table 1

cTable 2

Note. 1. The material of the case, membranes, pins, bottoms and collectors is stainless steel 12X18H9T.

2 The accepted PCTO arrangement is cylindrical when the slotted channels are completely filled with a porous filler.

3. The non-trivial version of the PCTO was calculated according to the ToR of Table 1,

4. The trivial version of PCTO was calculated according to the TK of Table 1, but with the adjustment of its initial data. So in these calculations it was accepted: TI T2 600 K; Tg Tg 214 K and in accordance with the underestimation of the average temperature of the coolant by 97 K, its thermophysical properties were accordingly adjusted here.

5 In the table. 2 pcto - the specific gravity of the proposed device.

k

 Oil refinery - incomplete filling of slotted channels

PKTO porous filler; PZ - their complete filling.

Claims (1)

The claims PORO-COMPACT HEAT EXCHANGER, Containing housed in a housing including a shell with bottoms, impermeable separation membranes forming slotted flow channels for pumping coolants and porous fillers located in them with spacer pins, and collectors, characterized in that, for the purpose of reducing weight and dimensions reducing material consumption and increasing the structural strength, as well as ensuring minimal losses for pumping heat transfer fluids, housing with spacer membranes, spacing Pins and nopnctbie fillers made zaodProdolzhenie t bl 2 Table3 but, moreover, the spacing pins in the slotted channels are arranged coaxially with each other with the formation of stitches between the membranes and the bottoms of the housing, separated from the extreme porous fillers by gaps, in which the pins are also placed, the porosity of the fillers is selected in accordance with the ratio of 0.75 e 0.85 , when the structural relative thickness of the porous material changes from 6 1 to b 10, and the casing is cylindrical, round or oval in cross section and its surface is provided with slotted inlet and outlet windows for coolants protected with appropriate collectors FIG. 2 j-j /4 ik AT 6 b Fig.Z QS o, sr 0.6 0, tS e QiS 0.8 0.8f Q9 Ot9f C) Dianometer of filler wire - o, 2.mm 4 - hydrogen 2 helium 3 - toadyx -xenon FIG. B