The Solving of the Inverse Thermal Conductivity Problem for Study the Short Linear Heat Pipes ()

Arkady Vladimirovich Seryakov^{}

LLC “Rudetransservice”, Veliky Novgorod, Russia.

**DOI: **10.4236/eng.2022.146018
PDF
HTML XML
149
Downloads
733
Views
Citations

LLC “Rudetransservice”, Veliky Novgorod, Russia.

The results of studies by
solving the inverse thermal conductivity problem of the
heat capacity of evaporator of the short linear heat pipes (HP’s) with a Laval
nozzle-liked vapour channel and intended for cooling spacecraft and satellites
with strict take-off mass regulation are presented. Mathematical formulation of the inverse problem for the HP’s thermal conductivity in one-dimensional coordinate system is
accompanied by the measurement results using the monotonic heating method in a
vacuum adiabatic calorimeter the HP’s surface temperatures along the
longitudinal axis over the entire temperature load range, thermal resistance,
and arrays of thermal power data on the evaporator *Q _{ev}* and vortex flow calorimeter

Keywords

Short Linear HP’s, The Inverse Problem of Thermal Conductivity, The Monotonic Heating Method, Thermal Resistance and Heat Capacity

Share and Cite:

Seryakov, A. (2022) The Solving of the Inverse Thermal Conductivity Problem for Study the Short Linear Heat Pipes. *Engineering*, **14**, 185-216. doi: 10.4236/eng.2022.146018.

1. Introduction

The current development level of the computer technology and computing technologies allows us to significantly expand the class of applied problems to be solved. Those scientific and technical problems of the HP’s heat transfer that have traditionally been tried to be considered analytically are increasingly being analysed and solved with the help of numerical methods using specialized software for engineering calculations. We are talking about the application of computational programs for solving inverse problems of thermal conductivity of solids in one-dimensional formulation and the use of the obtained methods for analysing the operation of short HP’s with a Laval nozzle-liked vapour channel and a large amount of working fluid in the capillary-porous insert and evaporator. Numerical methods have received the greatest application due to a number of specific advantages, the main of which is their relatively simple implementation on computers [1] [2] [3].

Inverse problems are characterized by instability of their solutions, which manifests itself in the occurrence of large numerical changes in the solution with small changes in the initial data.

Tasks of this type are called incorrectly assigned tasks or ill-posed problems [4] [5] [6] [7] [8]. A large section of ill-posed problems consists of inverse problems that arise in cases where the necessary initial and boundary data for the formulation of a direct correct problem, for example, the direct heat conduction problem, are not available, but there is some additional information about the solution that allows us to formulate the inverse problem. Such problems include inverse problems of thermal conductivity (IPTC) [9] [10] [11].

The general nonlinear problem of non-stationary HP’s thermal conductivity can be considered as a set of three nonlinear problems: a problem in which the nonlinearity arises due to the temperature dependence of the coefficients of the main equation; a problem in which the boundary conditions are nonlinear, for example, due to evaporation or boiling of the working fluid in the evaporator; and a problem in which the nonlinearity arises due to the temperature dependence of internal heat sources (sinks). The boundaries between these problems are very conditional, since some transformations allow you to switch from one type of nonlinearity to another, which sometimes simplifies the use of certain methods for solving nonlinear problems.

The main difficulty in the approximate solution of ill-posed problems is the choice of regularization parameters to achieve the stability of the solution. To determine it, the following approaches are most widely used [12] [13] [14] [15]: the choice of the regularization parameter by the remainder in the different functional; the use of the variational method with the calculation of the Lagrange function (Lagrangian); an iterative method in which the regularization parameter is the number of iterations corresponding to the error of the input data [15]. This latter well-known methodology of solving inverse heat transfer problems is quite effective and is widely used in space technology, military science, aviation, but its implementation requires a large amount of computational work [12] [13].

When solving inverse problems for equations of mathematical physics, gradient iterative methods are widely used in the variational formulation of the inverse problem [13]. In this paper, we consider the simplest gradient iterative method for approximate solution of the retrospective (with inverse time) inverse problem of the evaporator heat capacity of short HP’s with a vapour channel similar to a Laval nozzle with a known value of thermal resistance *R** _{HP}* or thermal conductivity coefficient

In addition the heat source in the HP’s evaporator depends only on the time τ, and the temperature field *T*(*z*) in the entire geometric space of the HP inside the adiabatic calorimeter is experimentally determined using copper-constantan surface thermocouples. These measurements guarantee that the inverse problem has an unambiguous solution, but this solution is unstable; therefore, additional regularization and the use of the variational method [14] [15] with Lagrange multipliers to determine the optimal values of the parameters in the different functional are necessary to solve the problem. This method gives rapidly converging successive approximations of the exact solution.

A simple algorithm for the numerical solution of a one-dimensional inverse problem by the coefficient of thermal conductivity for calculating the heat capacity of a short HP’s evaporator with a boiling working fluid has been developed and implemented in the FORTRAN system for a PC. In this case, an important factor is the temperature of the external surface of the capillary-porous HP’s evaporator, which is close to a constant value. With further heating, the level of boiling working fluid in the HP’s evaporator slowly decreases, and the temperature of the external surface also slowly decreases. And this allows us to calculate the extreme behavior of the evaporator heat capacity and estimate the specific heat of working fluid boiling in them.

In addition, our simple algorithm is convenient for its implementation in the measuring scheme of an adiabatic vacuum calorimeter for the study of short HP’s. The capabilities of this algorithm are illustrated by solving several specific problems for calculating the heat capacity of short solids under monotonic heating at moderate temperatures, including a model problem with the evaporation of diethyl ether and, consequently, with variable initial conditions.

Thus, the main purpose of this work is to expand the research capabilities of HP heat pipes, solve inverse problems of thermal conductivity with their help and clarify the thermophysical characteristics of working fluids when boiling occurs in an HP capillary-porous evaporator. The proposed new application of the developed mathematical ideas makes it possible to significantly increase the scope of HP and raise the depth and vastness of the results obtained.

HP’s Thermophysical Analysis

When analyzing short HP’s, the thermophysical characteristics are represented by the so-called effective properties, and the process of heat transfer along the vertically oriented *z* coordinate is described by the thermal conductivity equation:

${\rho}_{HP}{\u0421}_{eff}\left(T\right){L}_{HP}{F}_{HP}\frac{\partial T}{\partial \tau}=\nabla \left({\lambda}_{eff}\left(T\right)\nabla T\right)$. (1)

The specific heat capacity of the HP’s is determined additively by the formula (2) when the components and materials are characterized by the absence of chemical interaction between them.

${\stackrel{\xaf}{C}}_{HP}\left(T\right)={\displaystyle {\sum}_{j}{\psi}_{j}{C}_{j}\left(T\right)}$. (2)

where *ψ** _{j}* is the mass fractions of the HP’s components,

During the phase transformation of the fluid component, for example, during the working fluid boiling process in the HP’s evaporator, Equation (1) must be supplemented with an additional source function:

$Y\left(T\right)={\rho}_{HP}{r}_{j}\left(T\right)\frac{\partial {\psi}_{j}}{\partial \tau}={\rho}_{HP}{r}_{j}\left(T\right)\frac{\partial {\psi}_{j}}{\partial T}\frac{\partial T}{\partial \tau}$. (3)

where *r** _{j}*(

Taking into account (2), Equation (1) can also be used in the presence of phase transformations in the HP with a new average heat capacity:

${\stackrel{\xaf}{C}}_{HP}\left(T\right)={\u0421}_{eff}\left(T\right)-{r}_{sp}\left(T\right)$.

The heat conduction equation in one-dimensional Cartesian coordinate system for calculating the heat propagation in a vertically oriented short linear HP’s with a cylindrical body along the longitudinal *z*-axis, during monotonic heating in an adiabatic calorimeter without heat losses through the side walls is written as follows:

$\begin{array}{l}{\rho}_{HP}{\u0421}_{v}\left(T\right){L}_{HP}{F}_{HP}\stackrel{\dot{}}{T}\left(z,\tau \right)={L}_{HP}{F}_{HP}\frac{1}{z}\frac{\partial}{\partial z}\frac{1}{{R}_{HP}\left(T\right)}\frac{\partial t\left(z,\tau \right)}{\partial z};\\ {R}_{HP}\left(T\right)=\frac{{L}_{HP}}{{\lambda}_{HP}\left(T\right){F}_{HP}}.\end{array}$ (4)

The process of heating and heat transfer using HP’s is endothermic process, parameter *Y*(*T*) has a negative value, *Y*(*T*) ≤ 0, which implies the principle of maximum and the uniqueness of the thermal conductivity equation solution [4] [5]. However, if the parameter *Y*(*T*) is positive, *Y*(*T*) > 0 in general case it may turn out that the heat capacity *c** _{v}*(

The measurement part of our method consists in a system for measuring the thermal power entering to the evaporator, the thermal power entering in the vortex flow calorimeter and the temperature distribution of the HP’s surface inside the adiabatic calorimeter. In the case of using a vacuum adiabatic calorimeter with slow monotonous heating, the temperature distribution along the HP’s body makes it possible to distinguish characteristic areas (zones) of the HP’s, for example, the zone of the evaporator, the temperature in which, under a high temperature load, is close to constant for a fairly long boiling time (several tens of minutes), the time when the level of the working fluid in the capillary-porous evaporator decreases from the initial value *h *= 3.5 mm to the final value *h* = 0.02 – 0.01 mm and even less than this value.

The monotonic heating mode is extremely informative for the study of the short HP’s with the phase transformation (boiling) of the working fluid in the evaporator [3] [6], since it maintains the temperature difference required by the monotonicity conditions between the evaporator and the condensation surface inside the HP and, in addition, contains the thermophysical characteristics of the HP in an implicit inverse form.

At the working fluid boiling beginning during a certain time interval, the temperature of the capillary-porous evaporator remains close to constant and with the continuation of heating and by solving the inverse problem of thermal conductivity, it becomes possible to calculate the heat capacity of the working evaporator and the heat of evaporation.

The mathematical description of the monotone heating mode contains and implies several simplifying assumptions, which as a result lead to analytical relations for the direct calculation of the IPTC.

Heating mode contains and implies several simplifying assumptions, which as a result lead to analytical relations for the direct calculation of the IPTC. However, it is necessary to introduce some specific adjustments to take into account several interfering factors. It is necessary to take into account the final longitudinal dimensions of the HP, which lead to a distortion of the HP’s temperature field due to the heat exchange of the condensation end surface and the nearby side section with the cooling running water in the calorimeter, while analytical expressions imply the one-dimensionality of the temperature field in the HP.

The relatively large noticeable temperature differences within the HP during the boiling of the working fluid in the evaporator also require certain adjustments to the calculations. The values of the corrections will (can) be estimated in a special way.

The direct problem of the HP thermal conductivity is to find the HP’s temperature (surface temperature for the thin HP’s in a one-dimensional model of heat propagation in an adiabatic calorimeter) that satisfies the differential equation of thermal conductivity and has the specified boundary and initial conditions of unambiguity [9] [10] [11].

The solution of the direct problem for the HP’s evaporator in the case of large temperature load and the boiling process beginning in the temperature region of the working fluid phase transition is accompanied by a nonlinear dependence of the intrinsic properties (heat capacity *C** _{HP}* and thermal resistance

At the same time, the average values of the obtained heat capacity results *C** _{HP}* are not of great interest and make it absolutely necessary to isolate the zone of the HP’s evaporator at the working fluid boiling beginning, thereby allocating the heat capacity

The inverse problem of thermal conductivity (IPTC) in this case is to determine the parameters of internal heat transfer also in a one-dimensional model of heat propagation in an adiabatic calorimeter, the thermal resistance *R** _{HP}* (or thermal conductivity

IPTC is an incorrect problem in the sense of Hadamard [3] [4] [5] [6] [7], *i.e.* one whose numerical solution is unstable. This instability manifests itself in a significant and abrupt change in the solution itself with a small change in the initial conditions. To solve such problems, regularization methods have been developed and sustainable solutions have been proposed [9] - [13].

Formulation and solution of coefficient inverse problems of heat conduction in a one-dimensional coordinate system with one-dimensional temperature field are the theoretical basis of the main experimental methods for the evaporator’s heat capacity study of short linear HP’s (HP’s evaporative fragment), using the results of thermal resistance measurement and the transferred heat power q_{ev} along the longitudinal axis to reflect a decrease in transmitted power due to losses on internal friction and heat transfer losses due to the nonabsolute adiabatic mode in the calorimeter [11] [12] [13] [14].

Thus, we have a coefficient inverse problem of thermal conductivity, when the known experimental data on the thermal resistance *R** _{HP}* and the side surface temperature

2. Method and Materials

To conduct the experimental studies of the linear HP’s thermal characteristics, we used previously developed and used in many previous studies short stainless steel HP’s with a Laval nozzle-shaped vapour channel, the detailed description of which was repeatedly given in previous publications [16] [17] [18]. A schematic diagram of the experimental test setup is shown in Figure 1. In the upper cover capacitive sensors are installed to measure the working fluid condensate film thickness and temperature [19] [20] [21].

The capillary-porous evaporator 7 together with insert 4 forming a unified hydraulic working fluid delivery system, are made of layers of a thin stainless steel mesh with 0.07 mm thick each layer, with a cell size of 0.04 mm. The diethyl ether C_{4}H_{10}O is used as the working fluid, which has the boiling temperature under the atmospheric pressure of T_{B} = 308.65 K (35.5˚C), freezing temperature T_{F} = 156.95 K (−116.2˚C) and critical parameters T_{C} = 466.55 K (193.4˚C), P_{C} = 3.61 MPa. The volume of the insertion pores is determined during manufacture, and in our case it is equal to 16.62 × 10^{−6} m^{3}, mass of diethyl ether with the density of 713.5 kg/m^{3} (20˚С) in the insert pores is equal to 11.858 × 10^{−3} kg. The restriction in the HP’s filling amount is made so that the evaporator is not flooded with ether at a high temperature load and the film boiling beginning on the lower cover surface of the HP (the evaporator surface).

The charging ratio of the HP with Laval-liked vapour channel (ratio of the diethyl ether volume to the total volume of the HP) is equal to 16.62 × 10^{−6} m^{3}/3.14 × 10^{−5} m^{3} = 0.529.

The length of our HP’s is *L _{HP}* = 0.1 m, diameter

Figure 1. HP’s diagram: 1: top cover; 2: cylinder body of the HP’s; 3: locking element; 4: multilayer mesh capillary-porous insert with uniform dense radial cross-linking; 5: bottom cover; 6: capillary injector channels with a diameter of 1 mm; 7: bottom flat multilayer mesh evaporator. There are capacitance sensors 8, 9, 10 installed inside the top cover [16] [17] [18], two of which are intended for a condensate film thickness measurement, while the third with a welded on its electrodes microthermistor CT3-19 to measure the film temperature.

The defining parameter of the entire capillary-porous insert and the evaporator is a small longitudinal interlayer gap (clearance) between layers of the metal mesh, which does not exceed 0.007 mm, and developed by a porous system the capillary pressure, which is sufficient for the HP’s work when the external inertial effects.

The last row of Table 1 shows the characteristics of a porous system, implemented in our HP’s with a diethyl ether as a working fluid and the interlayer gap thickness is used as the average pore diameter.

The orientation of the longitudinal pores (clearances) with the liquid diethyl ether coincides with the skeleton wires of the capillary-porous insert and the direction of the heat flux propagation, therefore, the effective value of the thermal conductivity coefficient of a diethyl ether-saturated evaporator and insert can be calculated as follows:

${\lambda}_{ev}=\Pi \cdot {\lambda}_{l}+\left(1-\Pi \right)\cdot {\lambda}_{sc}$. (5)

At the porosity value П = 0.72 and values *λ _{l} *= 0.136 W/m K,

The measuring calorimeter for the HP’s studies is shown in Figure 2. The external heat exchange surfaces of the HP’s condensation zone are provided with insulated thermocouples and installed at a depth of 1 diameter in a vortex flow calorimeter with a stable water flow. To ensure accurate measurement of heat power and increase the HP’s heat transfer coefficient, the jet stream of incoming water in the flow calorimeter is spun, the values of flow velocity and vorticity are recorded using air bubbles. The Reynolds number *Re _{cal}* in a calorimeter with water temperature

The HPs evaporators, also equipped with 0.1 mm diameter copper constantan wire thermocouples, is heated using a flat resistance heater, and the temperature is maintained at *δТ*, K higher than the diethyl ether boiling temperature of 308.65 K under atmospheric pressure. The heater temperature is stabilized and HP’s evaporators overheat value is set in the range of *δТ* = 0 ÷ 20 К, herewith heat power of single HP does not exceed 200 W.

Table 1. Characteristics of the mesh wick with diethyl ether as a working fluid.

Figure 2. Scheme for the pulsation, heat conductivity and thermal resistance measuring of the short HP’s in a vacuum adiabatic calorimeter, combined with a vortex flow calorimeter. 1: vortical continuous-flow calorimeter; 2: HP’s bolting flange; 3: glass cover; 4: cover fastening; 5: HP’s; 6: flat resistance heater; 7: outlet stub tube for water flow; 8: inlet stub tube swirler for water flow; 9: silicone sealant of the sensing wire; 10: capacitive sensors for measuring the thickness of the condensed layer of the working fluid; 11: the measuring and reference generators of the capacitive transducer; 12: external digital generator; 13: the amplifier; 14: digital oscilloscope; 15: computer; 16: commutation switch; 17: digital voltmeter; 18: container for constant water head; 19: source of air bubbles; 20: water flow meter; 21: vacuum-jacketed zero temperature container.

To reduce heat loss when working with HPs, they are placed in a stainless steel vacuum chamber 22 (10^{−3} torr), where they are further surrounded by thin-walled copper adiabatic screen 23, the inner surface of which is covered with a layer of nickel, and on the outer surface placed 4 sections guard heaters 24. The value of nonadiabaticity near the middle of the HP’s does not exceed ~2 × 10^{−2} K, in the field of the resistive heater H_{2} and HP’s evaporators nonadiabaticity is about ~10^{−1} K.

The main HP, called measuring, is filled with diethyl ether and the reference one, which is completely identical to the main HP, is filled with dehumidified air at a pressure of 1 bar with dew point temperature lower than 233.15 К (−40˚С). The heat transfer coefficient *K _{HP}*

Conducted measurements of the condensate film thickness on the internal surface of the HP upper cover, using capacitive sensors and developed high frequency generators [16] [17] [18], give interesting results. Increased film thickness (and HP’s high thermal resistance) at low temperature load and a sharp decrease in film thickness (and significantly reduced HP’s thermal resistance) with increasing temperature load can be associated with a toroidal vapour vortex rotation direction change [20] [21]. All the details of the indirect experimental confirmation of the vapour vortex rotation direction change near the flat condensation surface inside the HP’s vapour channel and the condensate film thickness as a function of the temperature load are given in [16] [17] [18]. The results of condensate film thickness measuring are shown in Figure 3.

2.1. The Heat Balance Equation of the Evaporator

The most general and informative non-stationary energy equation for the work description of the HP’s flat evaporator in the monotonous heating mode is the Fourier-Kirchhoff equation [5], which contains the isochoric heat capacity *C _{ev}*, J/kg∙K, and the average evaporator density
${\stackrel{\xaf}{\rho}}_{ev}$, kg/m

$\begin{array}{l}{C}_{ev}{\stackrel{\xaf}{\rho}}_{ev}{L}_{ev}F\left(\stackrel{\xaf}{z}\right)\left(\frac{\partial {\stackrel{\xaf}{T}}_{ev}}{\partial \tau}+v\cdot \nabla T\right)\\ ={L}_{ev}F\left(\stackrel{\xaf}{z}\right)\left(\frac{\partial}{\partial \tau}+div\left(v\right)\right){P}_{ev}+div\left({\lambda}_{HP}\nabla T\right)+{\displaystyle {\sum}_{i=1}^{i=2}{\mu}_{i}{\Phi}_{dfi}}\end{array}$. (6)

The dimensionless length
$\stackrel{\xaf}{z}$ and the average heat capacity *C _{ev}* of the HP’s evaporator calculate in the usual way:

${C}_{ev}={C}_{sc}+{x}_{ev}{C}_{vp}+\left(1-{x}_{ev}\right){C}_{fev}+{C}_{w};\text{\hspace{0.17em}}\text{\hspace{0.05em}}\stackrel{\xaf}{z}=\frac{z}{{L}_{HP}}$. (7)

Figure 3. The average values of the diethyl ether film thickness on the HP’s condensation surface, depending of the evaporator overheating *δT *= *T _{ev}* −

With an increase in the temperature load in the initial heating period of a capillary-porous HP’s mesh evaporator the wetting of the grid frame with diethyl ether deteriorates sharply, since the wetting angle increases with an increase in temperature. This effect is thermosensitive and already with a relatively small increase in temperature *δT* = *T _{ev}* –

The thickness of the diethyl ether layer decreases from ~3.5 mm at the heating beginning to the most intense boiling, while the vapour flow becomes stationary, and the thickness of the ether micro-layer does not exceed (1 - 2) × 10^{−2} mm. This fact greatly simplifies the conduct of assessments and the maximum achievable result in our conditions is as follows:

$\begin{array}{c}{Q}_{ev}=-{\lambda}_{H2}{\left(\frac{\partial {T}_{H2}}{\partial \stackrel{\xaf}{z}}\right)}_{\stackrel{\xaf}{z}=0}={E}_{H2}-{C}_{H2}{\stackrel{\dot{}}{T}}_{ev}\\ =\left({T}_{H2}-{\stackrel{\xaf}{T}}_{fev}\right){F}_{ev}\left(z\right)/\left(\frac{{\delta}_{c}}{{\lambda}_{c}}+\frac{{\delta}_{wev}}{{\lambda}_{w}}+\frac{{\delta}_{fev}}{{\lambda}_{fev}}+\frac{1}{{\alpha}_{ev}}\right)=118.4\text{\hspace{0.17em}}\text{W}\text{.}\end{array}$ (8)

$\begin{array}{l}\Delta {T}_{c}=\frac{{Q}_{ev}{\delta}_{c}}{{\lambda}_{c}{F}_{ev}}=5.4\text{\hspace{0.17em}}\text{K},\text{\hspace{0.17em}}\text{\hspace{0.17em}}\Delta {T}_{wev}=\frac{{Q}_{ev}{\delta}_{w}}{{\lambda}_{w}{F}_{ev}}=18.8\text{\hspace{0.17em}}\text{K},\\ \Delta {T}_{fev}=\frac{{Q}_{ev}{\delta}_{fev}}{{\lambda}_{fev}{F}_{ev}}=\left(35\dots 0.55\right)\text{K}.\end{array}$ (9)

The equation of the thermal energy of a working HP’s evaporator in a monotonic heating mode in the approximation of small heat losses ${k}_{HP}^{sh}\left({\stackrel{\xaf}{T}}_{HP}-{T}_{shel}\right)$ in the adiabatic calorimeter can be represented using enthalpy equation as follows:

${Q}_{ev}\left(\tau \right)={H}_{ev}\left(\tau \right)+{\displaystyle {\sum}_{i=1}^{i=2}{\mu}_{i}{\Phi}_{dfi}}+{k}_{HP}^{sh}\left({\stackrel{\xaf}{T}}_{HP}-{T}_{shel}\right)$. (10)

and the actual enthalpy equation of an evaporator in a monotonous heating mode also can be represented using this thermodynamic equation:

${H}_{ev}\left(\tau \right)={G}_{vp}\left(\tau \right)r\left({T}_{B}\right)+{G}_{vp}\left(\tau \right){\u0421}_{vp}\left({T}_{ev}-{T}_{sc}\right)+{G}_{l}\left(\tau \right){C}_{pl}\left({T}_{ev}-{\stackrel{\xaf}{T}}_{fev}\right)$. (11)

The expression for the thermal energy released in the HP’s condensation region is written similarly using the heat balance equation:

$\begin{array}{c}{Q}_{cond}={G}_{vp}r\left({T}_{B}\right)\frac{\text{d}{x}_{ev}}{\text{d}\stackrel{\xaf}{z}}+{G}_{vp}\left(1-{x}_{ev}\right){C}_{vp}\frac{\text{d}{T}_{fev}}{\text{d}\stackrel{\xaf}{z}}+{\lambda}_{sc}\left(1-\Pi \right)\frac{{\text{d}}^{2}{T}_{sc}}{\text{d}{\stackrel{\xaf}{z}}^{2}}{F}_{ev}\left(z\right){L}_{ev}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}-{\displaystyle {\sum}_{i=1}^{i=2}{\mu}_{i}{\Phi}_{dfi}}-{k}_{HP}^{sh}\left({\stackrel{\xaf}{T}}_{HP}-{T}_{shel}\right).\end{array}$ (12)

The performed measurements and calculations make it possible to estimate the heat transfer coefficient in the vortex flow calorimeter *α _{cal}* = 2.3 × 10

${Q}_{cond}=\left({\stackrel{\xaf}{T}}_{fcond}-{T}_{cal}\right){F}_{cond}/\left(\frac{{\delta}_{fcond}}{{\lambda}_{l}}+\frac{{\delta}_{w}}{{\lambda}_{w}}+\frac{1}{{\alpha}_{cal}}+\frac{1}{{\alpha}_{cond}}\right)=115.4\text{\hspace{0.17em}}\text{W}$.(13)

The thickness parameters in parentheses are equal to the following values:

$\begin{array}{l}{\delta}_{fcond}={10}^{-1}\text{\hspace{0.17em}}\text{-}\text{\hspace{0.17em}}{10}^{-3}\text{mm},\text{\hspace{0.17em}}\text{\hspace{0.17em}}{\delta}_{w}=1\text{\hspace{0.17em}}\text{mm},\\ {\alpha}_{cal}=2.4\times {10}^{3}\text{W}/{\text{m}}^{\text{2}}\cdot \text{K},\text{\hspace{0.17em}}\text{\hspace{0.17em}}{\alpha}_{cond}\ge \left(5\text{\hspace{0.17em}}\text{-}\text{\hspace{0.17em}}10\right)\times {10}^{3}\text{W}/{\text{m}}^{\text{2}}\cdot \text{K}.\end{array}$

To solve the complex Fourier-Kirchhoff Equation (6), it is necessary first to determine the velocity field of the liquid and vapour phases in a capillary-porous evaporator using the Navier-Stokes equations. The results of this study will be presented later in a separate report.

To simplify all subsequent calculations, the average cross-section HP’s temperature at any point at altitude ${\stackrel{\xaf}{z}}_{i}={z}_{i}/{L}_{HP}$ inside the vapour channel can be considered equal to the surface temperature of the HP, measured at this height $T{\left({\stackrel{\xaf}{z}}_{i},\tau \right)}_{sur}$ in the vacuum chamber of the adiabatic calorimeter:

$\frac{1}{F\left(\stackrel{\xaf}{z}\right)}{\displaystyle \int {T}_{HP}\left(\stackrel{\xaf}{z}\right)\text{d}{F}_{i}}={T}_{HP}{\left({\stackrel{\xaf}{z}}_{i}\right)}_{sur}={T}_{HP}\left(\stackrel{\xaf}{z}\right)$. (14)

The vapour flow can be estimated according to the interphase mass transfer gives in case of small departures from equilibrium by the Hertz-Knudsen equation [22] [23]:

${G}_{vp}=\frac{2\xi}{2-\xi}{\left(\frac{M}{2\pi R}\right)}^{1/2}\left(\frac{{P}_{ev}}{\sqrt{{\stackrel{\xaf}{T}}_{fev}}}-\frac{{P}_{fcond}}{\sqrt{{\stackrel{\xaf}{T}}_{fcond}}}\right)$. (15)

where the diethyl ether C_{4}H_{10}O, selected as the working fluid has a molar mass *M* = 74.1216 g/mol, *R* is the universal gas constant and *ξ* is the condensation coefficient, *ξ* ≤ 1, defined as the ratio of the number of vapour molecules condensing over the total number of molecules which strikes the liquid film surface.

There is a redistribution of the liquid mass of diethyl ether inside the HP, while the heat capacity of the evaporator increases due to the liquid film boiling. In this case, the temperature *T** _{fev}* of the diethyl ether layer and its dependence on time are determined using external thermocouples that control the temperature of the HP external surface inside the vacuum chamber. The results of the thermocouple measurements are shown in Figure 4 and Figure 5 in section 2.2.

2.2. Temperature Distribution Inside the Vapour Channel

Earlier calculations of the flow velocity and vapour density of diethyl ether using the Navier Stokes equation system in a short HP’s vapour channel similar to the Laval nozzle [16] [18], allow us to calculate the temperature distribution in this channel. The ratio between the pressure, density and temperature of the condensing vapor in the first approximation can be given by the equation of state of an ideal gas in the following form [19] [20] [21]:

$\begin{array}{l}{\rho}_{vp}^{mix}=\frac{P}{RT};\text{\hspace{0.17em}}\text{\hspace{0.17em}}\frac{{\rho}_{vp}^{mix}}{{\rho}_{v}}={\left(\frac{P}{{P}_{v}}\right)}^{1/k};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{P}_{v}~{P}_{fcond};\\ \frac{P}{{P}_{v}}={\left[1+\frac{k-1}{k}\frac{1}{R{T}_{v}}\left(\frac{{u}^{2}-{u}_{v}^{2}}{2}+\frac{{v}^{2}-{v}_{v}^{2}}{2m}\right)\right]}^{k/\left(k-1\right)}.\end{array}$ (16)

where *k* = 1.31 is the value of the adiabatic index of diethyl ether vapour.

Figure 4. Comparison of the experimental values of the HP’s surface temperature along the generatrix, and the calculated diethyl ether vapour temperature inside the Laval nozzle-liked formed vapour channel. A: is the upper part of the Figure 4. 1: black dots, the experimental values of the HP’s surface temperature *T _{sur}* with a vapour channel made in the Laval nozzle-liked form, K; 2: the solid curve, the calculated temperature values

Figure 5. The experimental values of the HP’s surface temperature of the evaporator with maximum filling by the diethyl ether at the boiling beginning on a large scale. It is clearly visible the weak evaporator temperature drop (<1 K) and a sharp drop of the vapour temperature inside the Laval nozzle-liked formed vapour channel above the evaporator, coinciding with the calculated vapour temperature values.

Calculations of moving vapour temperature in a short HP’s vapour channel, made in the form of Laval nozzle, were performed using the program code ANSYS\CFD Fluent 6.3.26 -20090623 [24] and using Equation (16) and other more complete calculation equations given in [19] [20] [21]. Taking into account the tabular values [25] [26] [27] of the diethyl ether vapour pressure at the humidity coefficient *γ _{dr}* = 0.2, the temperature distribution inside the vapour channel along the longitudinal

$T={T}_{v}{\left(\frac{P}{{P}_{v}}\right)}^{\left(k-1\right)/k}$. (17)

The calculated values of the vapour temperature along the longitudinal axis of the HP vapour channel at the temperature of lower layer of the diethyl ether in the evaporator ${\stackrel{\xaf}{T}}_{fev}=329.75\text{\hspace{0.17em}}\text{K}\left(56.6\u02da\text{C}\right)$. The calculation error is 0.3%, the measurement error of the HP’s surface temperature is less than 0.1 K. Heating and all calculations were carried out in the temperature range of the evaporator (298 - 348) K (25˚C - 75˚C).

The outer surface of the HP’s body in the region of a 3.5 mm high multilayer mesh evaporator, filled with boiling diethyl ether is characterized by a close to constant temperature under monotonous heating, which is clearly seen in Figure 4 and Figure 5. With further heating, the thickness of the diethyl ether layer in the evaporator and, accordingly, the width of the constant temperature region decreases.

Inside the vapour channel, the temperature decreases sharply, the temperature drop reaches *ΔT* = 35 K, due to the cooling in the condensation region and the influence of the Laval nozzle shape of the vapour channel. The results of the experimental analysis of the HP’s surface temperature distribution along the generatrix also confirmed the nonlinear nature of the temperature distribution as a function of the channel length in the Laval-liked vapour channel.

Experimental data shows a close to constant temperature of the evaporator when diethyl ether boils in it, a weak nonlinearity in the confuser part of the nozzle, and a strong nonlinearity in the behavior of the temperature near the HP’s condensation surface. With a further increase in the heat load, the length of the constant temperature region in the evaporator is reduced.

The results of numerical analysis of the vapour axial temperature distribution inside the Laval-liked HP’s vapour channel of compressible moist vapour at high heat loads confirm the nonlinear character of the temperature distribution as function of the channel length, which is due to the joint influence of the channel shape in the form of a Laval-liked nozzle and a sharp gradient vortex formation near the HP’s condensation surface, taking into account an additional temperature decrease inside the vortex ring of the condensing vapour [18] [21], which makes it extremely difficult to solve the heat equation for our HP’s.

2.3. Thermal Resistance Results

Experimental values in the stationary state of the thermal resistance *R** _{HP}* of a short HP’s are defined as the thermophysical characteristic of the heat transfer device as a whole [28], at a constant value of the temperature load (pressure) on the evaporator

The full temperature load on the evaporator *δ**t* = *T** _{ev}* –

Experimental values of thermal resistance *R** _{HP}* obtained during monotonic heating of the HP’s evaporator with a speed close to linear in time 3 × 10

${R}_{HP}\left(t\right)=\frac{{T}_{ev}-{T}_{cond}}{{Q}_{ev}}$. (18)

The small size and the low heating rates ensured that the measurements of the *R** _{HP}* were carried out under homogeneity conditions and local thermal equilibrium. The obtained values of the thermal resistance

The polynomial Equation (19) describing in dimensionless form the experimental values of the thermal resistance *R _{HPk}* for a time moment

$\begin{array}{l}{R}_{HPk}\left(\delta t\right)={\displaystyle {\sum}_{i=1}^{{n}_{R}}{R}_{HPki}{\left(\delta t\right)}^{i-1}}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.05em}}\text{\hspace{0.05em}}=-2.0795621\times {10}^{-8}{\left(\delta t\right)}^{7}+1.6029662\times {10}^{-6}{\left(\delta t\right)}^{6}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.05em}}\text{\hspace{0.05em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}-4.9921411\times {10}^{-5}{\left(\delta t\right)}^{5}+8.0489929\times {10}^{-4}{\left(\delta t\right)}^{4}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.05em}}\text{\hspace{0.05em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}-0.0071936{\left(\delta t\right)}^{3}+0.03633406{\left(\delta t\right)}^{2}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}\text{\hspace{0.05em}}\text{\hspace{0.05em}}\text{\hspace{0.17em}}\text{\hspace{0.17em}}-0.1113127\delta t+0.2702057,\text{\hspace{0.17em}}\text{\hspace{0.17em}}{n}_{R}\le 8\end{array}$ (19)

Standard deviation *σ* = 0. 0024929, Fisher criterion *R*^{2} = 0.9980243.

The obtained experimental results of thermal resistance at temperature load *δt* > 10 K allow us to estimate the characteristic total thickness of the diethyl ether film on the evaporator surface (boiling in the evaporator) and the condensation surface of short HP’s with a Laval nozzle-liked vapour channel and flat upper and lower covers as follows (without the thermal resistance of covers):

$\begin{array}{c}{\stackrel{\xaf}{\delta}}_{ev}+{\stackrel{\xaf}{\delta}}_{cond}~{R}_{HP}{\lambda}_{l}F\\ =4\times {10}^{-2}\text{K}/\text{W}\times 0.136\text{W}/{\text{m}}^{\text{2}}\cdot \text{K}\times 3.14\times {10}^{-4}\text{\hspace{0.05em}}\text{\hspace{0.05em}}{\text{m}}^{2}\\ \le 1.7\times {10}^{-6}\text{\hspace{0.05em}}\text{\hspace{0.05em}}\text{m}.\end{array}$

From the analysis of Figure(6), it follows that the film thickness on the evaporator is close to a constant value in the range of thermal loads *δT* = (10 - 20) K, and with a further increase in the temperature load *δT*, the evaporator begins to dry out and there is a sharp increase in the thermal resistance *R _{HP}*.

In addition, when the HP’s evaporator is monotonically heated, the diethyl ether layer thickness inside the evaporator *δ _{fev}*(

0 < *z* < *L _{ev}* = 0.035∙

$\frac{\partial {R}_{HP}}{\partial z}=\frac{\partial {R}_{HP}}{\partial t}\left(\frac{\partial t}{\partial z}\right)=\frac{\partial {R}_{HP}}{\partial t}{\left(\frac{\partial z}{\partial t}\right)}^{-1}>0;\text{\hspace{0.17em}}\text{\hspace{0.17em}}0\le z<{L}_{ev}=0.035\cdot {L}_{HP}$. (20)

The distributions of the experimental values of the HP’s surface temperature shown in Figure 4 and Figure 5 ((∂*t*/∂*z*) < 0) at the diethyl ether boiling beginning in a saturated evaporator under the monotonic heating, and the decreasing values of the thermal resistance on a global evaluation between evaporator and condenser ((∂*R _{HP}*/∂

3. Mathematical Model of the Inverse Thermal Conductivity Problem

Let’s formulate a mathematical statement of the inverse problem of restoring the heat capacity of working HP’s. Let there be a vertically oriented HP with the length *L** _{HP}* = 100 mm and diameter of 20 mm,

The classical equation of spatial thermal conductivity for the linear HP’s as a solid rod (solid body) is looks like this [4] [5] [6]:

${\rho}_{HP}{\u0441}_{v}\left(t\right){L}_{HP}F\left(\stackrel{\xaf}{z}\right)\frac{\partial T}{\partial \tau}=div\left({\lambda}_{HP}grad\text{\hspace{0.05em}}\text{\hspace{0.05em}}T\right)$. (21)

Figure 6. Thermal resistance *R** _{HP}*, depending on the evaporator overheating

In a working HP with monotonous heating the heat capacity *C** _{ev}* of the evaporator can be considered and analyzed only as the heat capacity of the HP’s lower fragment
${\u0421}_{ev}={\u0421}_{HP}\left(\stackrel{\xaf}{z}=0.035\right)$ with a thickness of

The distribution of the one-dimensional axisymmetric temperature field ${t}_{HP}{\left({\stackrel{\xaf}{z}}_{i}\right)}_{sur}$ and $\stackrel{\dot{}}{t}{\left(\stackrel{\xaf}{z},{\tau}_{k}\right)}_{sur}$ along the longitudinal dimensionless $\stackrel{\xaf}{z}$ -axis of a short linear HP’s is used to solve the heat conduction Equation (22) for the evaporator fragment without internal sources [4]:

$\frac{1}{\stackrel{\xaf}{z}}\frac{\partial}{\partial \stackrel{\xaf}{z}}\frac{1}{{R}_{ev}\left(t\right)}\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial \stackrel{\xaf}{z}}={\u0421}_{ev}\left(t\right)\stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},\tau \right);\text{\hspace{0.17em}}\text{\hspace{0.17em}}\stackrel{\xaf}{z}=\frac{z}{{L}_{HP}}\le 0.035$. (22)

The thermal resistance of the evaporator (evaporative HP fragment) is an integral part of the thermal resistance *R _{HP}* of the entire HP, and the value of the thermal resistance of the evaporator during the diethyl ether boiling at temperature load (pressure) > 11 K can be estimated using the experimental results presented in Figure 6. Given the close thicknesses of diethyl ether films in the evaporator and on the condensation surface of HP
${\stackrel{\xaf}{\delta}}_{ev}~{\stackrel{\xaf}{\delta}}_{cond}$ during film boiling, the thermal resistance of the evaporator (evaporative fragment) will be no more then

Energy losses due to friction in the vapour channel and non-absolute calorimeter adiabaticity lead to the fact that the thermal power of *Q _{ev}* and

$\left({Q}_{ev}-{Q}_{cond}\right)/{Q}_{ev}\le 2.6\%$.

And the heat power becomes a function of the dimensionless vertical coordinate $\stackrel{\xaf}{z}$ and time with monotonous heating:

${Q}_{ev}={Q}_{ev}\left(\stackrel{\xaf}{z},\tau \right)$. (23)

One of the possible formulations of the coefficient inverse problem (CIP) for Equation (23) consists in setting redefined boundary conditions, with the help of which the definition unicity of three functions – temperature ${t}_{sur}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$, heat capacity ${C}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ and thermal resistance ${R}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ (or thermal conductivity ${\lambda}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ ), moreover all functions must be analytical functions, for example, represented as polynomials or piecewise smooth spline functions. For experimentally determined boundary conditions, the inverse heat conduction problem for Equation (22) is usually incorrect in the classical sense [9] [10] [11]. To bring it to a conditionally correct formulation, we restrict the class of acceptable solutions to a set of piecewise regular approximating dependencies and apply the step – by step principle of natural regularization for IPTC solution [6] [9].

The temperature distribution of the cylindrical HP’s housing inside the vacuum chamber with an adiabatic shell near the flat resistive heater is symmetrical:

${\left[\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial x}\right]|}_{\stackrel{\xaf}{z}=0}={\left[\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial y}\right]|}_{\stackrel{\xaf}{z}=0}=0$. (24)

The initial boundary conditions [29] [30] [31]:

$t\left(0,\tau \right)\equiv {t}_{ev}={T}_{ev}\left(\tau \right)-\left({R}_{c}+{R}_{w}+{R}_{fev}\right){Q}_{ev}\left(\tau \right)$. (25)

$t\left(0,0\right)={t}_{0};\text{\hspace{0.17em}}\text{\hspace{0.17em}}t\left(0,{\tau}_{k}\right)={t}_{0}+{\tau}_{k}\times 3\times {10}^{-3}\text{K}/\text{s}$. (26)

$t\left({L}_{HP},{\tau}_{k}\right)\equiv {t}_{cond}={T}_{cond}\left({\tau}_{k}\right)+\left({R}_{cal}+{R}_{w}+{R}_{fcond}+{R}_{cond}\right){Q}_{cond}\left({\tau}_{k}\right)$. (27)

${Q}_{ev}\left(\stackrel{\xaf}{z}=0,{\tau}_{k}\right)={E}_{H2}-{C}_{H2}{\stackrel{\dot{}}{T}}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$. (28)

The *Q _{cond}* energy transmitted by HP to the vortex flow calorimeter during vapour condensation is determined using the experimental stand shown in Figure 2 and Equation (13).

We write down the dimensional equation of thermal conductivity to estimate the heat capacity of a capillary-porous evaporator with a finite height of 0.035∙*L _{HPi}* in the following standard form:

$z{\u0421}_{evk}\left(t\right)\stackrel{\dot{}}{t}\left(z,{\tau}_{k}\right)=\frac{\partial}{\partial z}\left[\frac{{L}_{HP}}{{R}_{HP}\left(t\right)F\left(z\right)}\frac{\partial t\left(z,{\tau}_{k}\right)}{\partial z}\right];\text{\hspace{0.17em}}\text{\hspace{0.17em}}\frac{z}{{L}_{HP}}\le 0.035$. (29)

And we introduce a general expression for the heat flow
$q\left(z,{\tau}_{k}\right)$ inside the short HP along the longitudinal *z* axis:

$q\left(z,{\tau}_{k}\right)=z{\lambda}_{HP}\frac{\partial {T}_{HP}\left(z,{\tau}_{k}\right)}{\partial z}=z\frac{{L}_{HP}}{{R}_{HP}{F}_{HP}}\frac{\partial {T}_{HP}\left(z,{\tau}_{k}\right)}{\partial z}={E}_{H2}-{C}_{H2}{\stackrel{\dot{}}{T}}_{ev}\left(z,{\tau}_{k}\right)$.(30)

In the first approximation, in which the heat flow is determined only by the HP’s capillary-porous evaporator without taking into account heat losses, the heat propagation equation in the vapour channel using the thermal resistance *R _{HP}* of a short HP’s as a whole can be written in the following form:

$\begin{array}{l}z\frac{{L}_{HP}}{{R}_{HP}\left(t\right){F}_{ev}}\frac{\partial {T}_{HP}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)}{\partial \stackrel{\xaf}{z}}\\ ={G}_{vp}r\left({T}_{B}\right)\frac{\text{d}{x}_{ev}}{\text{d}\stackrel{\xaf}{z}}+{G}_{vp}{C}_{vp}\frac{\text{d}{T}_{fev}}{\text{d}\stackrel{\xaf}{z}}+{\lambda}_{sc}\left(1-\Pi \right)\frac{{\text{d}}^{2}{T}_{sc}}{\text{d}{\stackrel{\xaf}{z}}^{2}}{F}_{ev}\left(z\right){L}_{ev}.\end{array}$ (31)

The solution of the Equations (29) and (31) is possible only with positive values of time *τ _{k} *and heat capacity
${\stackrel{\xaf}{C}}_{evk}\left(T\right)$ :

${\tau}_{k}>0;\text{\hspace{0.17em}}\text{\hspace{0.17em}}{\stackrel{\xaf}{C}}_{evk}\left(T\right)>0$

To simplify all subsequent calculations, it is possible to take the initial temperature value equal to zero:

$t\left(\stackrel{\xaf}{z},0\right)=0$

Equations (30) and (29) of the heat flow propagation
$q\left(z,{\tau}_{k}\right)$ can be rewritten in the dimensionless form
${q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ as the heat flow of the evaporator (without taking into account heat losses) along the *z*-axis at time moment *τ** _{k}* and presented as a system of two energy equations for calculating the heat capacity

$\stackrel{\xaf}{z}{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}+\frac{\partial {q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)}{\partial \stackrel{\xaf}{z}}=0$. (32)

$z\frac{{L}_{HP}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial \stackrel{\xaf}{z}}+{q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)=0$. (33)

The values of the variable thermal power ${q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ on the lower HP’s flat borders, on the upper boundary of the flat evaporator and on the upper flat borders are equal to:

${q}_{ev}\left(0,{\tau}_{k}\right)={Q}_{ev};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{q}_{ev}\left(0.035,{\tau}_{k}\right)={Q}_{0.035};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{q}_{ev}\left(1,{\tau}_{k}\right)={Q}_{cond}$. (34)

and Equation (33) for determination the transmitted thermal power by the HP’s capillary-porous evaporator at a height of *z* = 0.035∙*L _{HP}* is made using the HP’s surface temperature distribution in the adiabatic calorimeter:

$\begin{array}{c}{q}_{ev}\left(\stackrel{\xaf}{z}=0.035,{\tau}_{k}\right)=-z\frac{{L}_{HP}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}{\left[\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial \stackrel{\xaf}{z}}\right]|}_{\stackrel{\xaf}{z}=0.035}\\ =-0.035\frac{{L}_{HP}^{2}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}{\left[\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial \stackrel{\xaf}{z}}\right]|}_{\stackrel{\xaf}{z}=0.035}.\end{array}$ (35)

The heat capacity of the evaporator allows us to evaluate the work of the HP. To calculate the

HP’s evaporator heat capacity *C** _{evk}*, the heat output in the evaporator volume can be considered as reduced by the temperature reduce from the Equation (31) and (35), and an illustration of the experimental temperature distribution data from Figure 4 and Figure 5:

$0.035{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}=-{\left[\frac{\partial q\left(\stackrel{\xaf}{z},{\tau}_{k}\right)}{\partial \stackrel{\xaf}{z}}\right]|}_{\stackrel{\xaf}{z}=0.035}$. (36)

Figure 4 and Figure 5 show the close to the constant experimental temperature distribution inside the evaporator with boiling diethyl ether at a high heat load and further temperature drop in the HP’s Laval nozzle-liked vapour channel up to the condensation surface.

3.1. Performing Calculations of the Inverse Thermal Conductivity Problem

The inverse thermal conductivity problem (ITCP) solution for the HP’s evaporator is a method of stepwise continuation of the known solution, for example equal to zero at the initial moment, for the next time interval *Δτ _{k}* = (

The solution of the equations system (32) and (33) is carried out using experimentally determined surface temperature values
$t\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ in the range HP_{0.03} = (*τ _{k}*,

Crank-Nicholson calculation scheme, Figure 7 with temperature averaging on the previous calculation layer and taking into account the temperature dependence of the thermal conductivity coefficient can be used to improve the calculations accuracy. The equation for the Crank-Nicholson scheme calculation of the evaporator heat capacity is as follows:

${\rho}_{evi}{C}_{evi}\frac{{T}_{i}^{n+1}-{T}_{i}^{n}}{\Delta \tau}={\lambda}_{evi}\left(\frac{{T}_{i}^{n+1}+{T}_{i}^{n}}{2}\right)\left(\frac{{T}_{i-1}^{n+1}-2{T}_{i}^{n+1}+{T}_{i+1}^{n+1}}{2{h}^{2}}+\frac{{T}_{i-1}^{n}-2{T}_{i}^{n}+{T}_{i+1}^{n}}{2{h}^{2}}\right)$.(37)

Figure 7. A six-point difference scheme in which three points are taken from the next (new) time layer *n*+ 1, and three from the old (previous) time layer *n*.

The coefficient*λ _{evi}* of the evaporator thermal conductivity can be estimated by the Equation (5).

Experimental temperature *t _{k}* at time

${t}_{k}=t\left(\stackrel{\xaf}{z},{\tau}_{k}\right)=\delta t\left(\stackrel{\xaf}{z},{\tau}_{k}\right)+{t}_{B};\text{\hspace{0.17em}}\text{\hspace{0.17em}}\delta {t}_{k}=\delta t\left(\stackrel{\xaf}{z},{\tau}_{k}\right)={t}_{k}-{t}_{B}$. (38)

At the initial time moment *τ _{k}* and at the initial temperature value

${C}_{evk}\left(t\right)=\varphi \left(\xi \right)\cdot {\displaystyle {\sum}_{i=1}^{{n}_{c}}{C}_{evki}{\left(\delta t\right)}^{i-1}};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{n}_{C}\le 10.$ (39)

Approximation function *Φ*(*ξ*) is a mandatory regularizing parameter in the form of monotone increasing function, *Φ*(*ξ*) = *ξ*, or maybe exp(*ξ*). The value of numerical parameter *Φ*(*ξ*) determines the stability and the range of acceptable heat capacity properties, and smoothes out non-linearity’s in a blurred thermal transformation in the HP’s evaporator. With the change from linear to an exponential dependence, the error in calculating the heat capacity decreases markedly, especially when the polynomial heat capacity function leaves the peak, see Figure 8. This is due to the fact that exp(*ξ*) provides a limit on the range of HP’s permissible properties in a positive value with *C** _{evk}* and

The temperature time derivative is a constant value for time values *τ* > *τ _{k}* and is a coordinating (synchronizing) parameter of all measurements in a time interval

$\begin{array}{l}{\stackrel{\dot{}}{t}}_{i}>0,\text{\hspace{0.17em}}\text{\hspace{0.05em}}i=0,\cdots ,2,\text{\hspace{0.17em}}\text{\hspace{0.17em}}\tau >{\tau}_{k};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{t}_{k}={t}_{0}+{\tau}_{k}\times 3\times {10}^{-3}\text{K}/\text{s};\\ \Delta {t}_{k}=\Delta {\tau}_{k}\times 3\times {10}^{-3}\text{K}/\text{s}.\end{array}$ (40)

The experimental distribution of the HP’s surface temperature *t _{k}* at time

$\begin{array}{l}{t}_{ev}\left({\tau}_{k}\right)={t}_{k0}\left(\stackrel{\xaf}{z}=0\right)>0;\text{\hspace{0.17em}}\text{\hspace{0.17em}}{t}_{0.035}\left({\tau}_{k}\right)={t}_{k0}\left(\stackrel{\xaf}{z}=0.035\right)>0;\\ {t}_{1}\left({\tau}_{k}\right)={t}_{k0}\left(\stackrel{\xaf}{z}=1\right)>0.\end{array}$ (41)

The accounting and synchronization of the thermal resistance *R _{HPk}* equilibrium values (33) in a linear slow heating process to the moments of time measurements

$\tau >{\tau}_{k}:{Q}_{\stackrel{\xaf}{z}=0}\left({\tau}_{k}\right)={Q}_{ev};\text{\hspace{0.17em}}{Q}_{\stackrel{\xaf}{z}=0.035}\left({\tau}_{k}\right)={q}_{\stackrel{\xaf}{z}=0.035};\text{\hspace{0.17em}}{q}_{\stackrel{\xaf}{z}=1}\left({\tau}_{k}\right)={Q}_{cond}$. (42)

Figure 8. The calculated values of the HP’s evaporator heat capacity *C** _{ev}*/

When the ITCP problem at time *τ _{k}* is solved and the temperature at time

To reduce the number of *C*_{k}_{+1} parameters, defined at each time interval *Δτ _{k}*

The total number of equations for crosslinking *N _{c} *= 2 (heat capacity and temperature derivative of heat capacity), and the maximum degree of the polynomial

In addition, the method of numerical solution of ITCP for short linear HP’s using a polynomial expansion of the heat capacity, the size of each time *Δτ _{k}* step is an important regularizing parameter [12] [13] [14] [15] [32] [33]. The optimal time step size

The program that controls the operation of the measuring stand, Figure 2, has two operating modes: “control” and “measurement”. In the “control” mode, all sensors are cycled, including thermocouples, thermistors, capacitive sensors, controls the power of the main resistive heater and protective heaters of the adiabatic calorimeter system, the regime of “zero heating” mode of the HP’s evaporator is specified, the measurement results are processed and output on the display screen.

In this mode, the parameters of the control program are specified such as the duration of the sensors readings measurement, the measurement times of digital voltmeters, oscilloscopes, frequency meters, etc. After the HP evaporator and the vortex flow calorimeter reach stationary isothermal states, the program switches to the “measurement” mode.

The main resistive heater H_{2} and control system are switched on, and the linear time heating of the HP’s evaporators begins, the adiabatic system and all measuring sensors start working. In this mode, the temperatures distribution on the outer surface of the measuring HP, the evaporator heat power, the condensation surface temperature, the heat output of the adiabatic system and all other thermal characteristics, including the heat transfer characteristics of the HP, are measured. The obtained experimental data arrays are saved and a measurement library is formed.

3.2. Performing Calculations of the Evaporator Heat Capacity

We analyze the case when the thermal resistance *R _{HP}*, Equation (19) of the entire HP as a whole is known, have a positive value and it is necessary to calculate the heat capacity of a capillary-porous evaporator with a height of 3.5 mm and saturated with diethyl ether. We integrate Equation (22) with respect to
$\stackrel{\xaf}{z}$ and, taking into account the experimental boundary conditions (25), (26), (27) and (28) we obtain a nonlinear integral equation for calculating the evaporator heat capacity at the time moment

${\int}_{0}^{0.035}\stackrel{\xaf}{z}{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)\text{d}\stackrel{\xaf}{z}}=0.035{q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$. (43)

To solve such integral equations, the finite difference method is used, based on replacing the derivatives with their approximate values expressed in terms of the functions differences at individual discrete points (nodes) of the finite-difference grid, Equation (37).

We will solve the functional Equation (43) by the iterative method, for which it is necessary to proceed to the variational formulation of this task. We define the target functional as the discrepancy, corresponding to the difference between the left and right sides of Equation (43), and the calculation problem for each time interval *Δτ _{k}* will look like the task of minimizing the discrepancy functional:

$\begin{array}{c}{\displaystyle {\sum}_{k}\delta {C}_{evk}\left(t\right)}=\frac{1}{2}{\displaystyle {\sum}_{k}{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}{\left[{\displaystyle {\int}_{0}^{0.035}\stackrel{\xaf}{z}{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)\text{d}\stackrel{\xaf}{z}}-0.035{q}_{ev}\left({\tau}_{k}\right)\right]}^{2}\text{d}\tau}}\\ =\mathrm{inf}{\u0421}_{evk}^{i}\left(t\right).\end{array}$ (44)

The most suitable way to minimize the functional is the conjugate gradient method [34] [35] [36]. To calculate the gradient components of the functional (44) (Frechet derivatives) at the points of minimizing sequence, the method of the optimal process control theory [35] [36] is used, described by partial differential equations [35]. In this method, an important role is played by the so-called conjugate boundary value problems corresponding to the original optimal control problem.

The Lagrange functional L for minimization the problem (44) with additional conditions (22), (25), (26) and with the values of the heat flow at the boundaries of the evaporator (32), (36) is as follows:

$\begin{array}{c}L=\left[\frac{\partial {\displaystyle {\sum}_{k}\delta {C}_{evk}\left(t\right)}}{\partial {c}_{i}}\right]+{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\eta}\left(\stackrel{\xaf}{z}{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}+\frac{\partial q\left(\stackrel{\xaf}{z},{\tau}_{k}\right)}{\partial \stackrel{\xaf}{z}}\right)\right]\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}+{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\chi}\left({q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)+z\frac{{L}_{HP}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}\frac{\partial t\left(\stackrel{\xaf}{z},\tau \right)}{\partial \stackrel{\xaf}{z}}\right)\right]\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}.\end{array}$ (45)

where the domain of variables *τ _{k}* and
${q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ is kept the same as HP

To obtain the gradient expression of the functional L [35], Lagrange multipliers and formulate the conjugate task of calculating the heat capacity, we present a variation of the Lagrange function with respect to the variables *τ _{k}* and
${q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)$ and the heat capacity parameters
${\u0421}_{evk}^{i}\left(t\right)$, and taking into account the boundary conditions (25) and (26) and the initial conditions (32), (33), (40) and expressions for the heat flow (30), (35):

$\begin{array}{c}\delta L={\displaystyle {\sum}_{i}{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\chi {\u0421}_{evk}^{i}\left(t\right){g}_{i}\delta \left(\stackrel{\xaf}{z}\frac{{L}_{HP}^{2}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}\right)}\right]\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}-{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\left(\stackrel{\xaf}{z}{\u0421}_{evk}^{i}\left(t\right)\stackrel{\dot{}}{\eta}+\stackrel{\xaf}{z}\frac{{L}_{HP}^{2}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}\frac{\partial b}{\partial \stackrel{\xaf}{z}}\right)}\right]\delta t\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}-{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\left(\frac{\partial \eta}{\partial \stackrel{\xaf}{z}}-\stackrel{\xaf}{z}\chi \right)}\right]\delta {q}_{ev}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}+{\displaystyle {\int}_{0}^{0.035}\stackrel{\xaf}{z}\eta {\u0421}_{evk}^{i}\left(t\right)\delta t\text{d}\stackrel{\xaf}{z}}\\ \text{\hspace{0.17em}}\text{\hspace{0.17em}}+{\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[\stackrel{\xaf}{z}\frac{{L}_{HP}^{2}}{{R}_{HP}F\left(\stackrel{\xaf}{z}\right)}-{\displaystyle {\int}_{0}^{0.035}\stackrel{\xaf}{z}\eta {\u0421}_{evk}^{i}\left(t\right)\stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)\text{d}\stackrel{\xaf}{z}}-0.03{q}_{ev}\left({\tau}_{k}\right)\right]\delta t\text{d}{\tau}_{k}}.\end{array}$ (46)

where the value *g _{k}* denotes the derivative of the heat capacity components in the following form:

${g}_{i}=\frac{\partial {C}_{evk}\left(t,{\tau}_{k}\right)}{\partial {\u0421}_{evk}^{i}\left(t,{\tau}_{k}\right)};\text{\hspace{0.17em}}\text{\hspace{0.17em}}\frac{\partial {\displaystyle {\sum}_{k}\delta {C}_{evk}\left(t\right)}}{\partial {\u0421}^{i}\left(t,{\tau}_{k}\right)}={\displaystyle {\int}_{{\tau}_{k}}^{{\tau}_{k+1}}\left[{\displaystyle {\int}_{0}^{0.035}\eta \stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},{\tau}_{k}\right){g}_{i}}\right]\text{d}\stackrel{\xaf}{z}\text{d}{\tau}_{k}}$. (47)

where *η*, is the solution of the conjugate problem completely corresponding to the original problem (22), (25) and (27). In the reverse time, *τ* = *τ _{k}*

$\stackrel{\xaf}{z}{\eta}_{k}={a}^{k}\frac{\partial \left(\stackrel{\xaf}{z}\partial {\eta}_{k}/\partial \stackrel{\xaf}{z}\right)}{\partial \stackrel{\xaf}{z}};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{a}^{k}=\frac{{\lambda}_{k}}{{C}_{evk}\left(t,{\tau}_{k}\right)}=\frac{1}{{C}_{evk}\left(t,{\tau}_{k}\right)}\frac{{L}_{HP}}{{R}_{HPk}F\left(\stackrel{\xaf}{z}\right)}$. (48)

Both the initial and boundary conditions of the conjugate task are written in the usual way, and at the upper boundary of the evaporator, the conjugate value is equal to the caloric residual from the square brackets in the Equation (44):

$\eta \left(\stackrel{\xaf}{z},0\right)=0;\text{\hspace{0.17em}}\text{\hspace{0.17em}}\eta \left(0,{\tau}_{k}\right)=0$.

$\eta \left(\stackrel{\xaf}{z}=0.035,{\tau}_{k}\right)={\left[{\displaystyle {\int}_{0}^{0.035}\stackrel{\xaf}{z}{C}_{evk}\left(t\right)\stackrel{\dot{}}{t}\left(\stackrel{\xaf}{z},{\tau}_{k}\right)\text{d}\stackrel{\xaf}{z}}-0.035{q}_{ev}\left({\tau}_{k}\right)\right]}^{2}\left({\tau}_{k+1}-\tau \right)$. (49)

the inverse problem for the heat capacity
${C}_{evk}\left(t,{\tau}_{k}\right)$ at each *k*-th interval is reduced to finding the minimum of the functional by the method of conjugate gradients.

The solution of the HP’ evaporator thermal conductivity inverse problem (32), (37) and (46) and the solution of the integral Equation (44) for determining the evaporator heat capacity was carried out using the developed program in Fortran [3] [4] [5].

In the conjugate gradient method, one-dimensional minimization in the permissible direction was carried out using the interpolation-extrapolation method [35]. The described algorithm for determining the piecewise function *C _{evk}*(

For a measuring sample with conductive heat transfer, all details are from Equation (22). For a model sample, the boundary conditions are given below in Equations (50) and (51):

$\stackrel{\xaf}{z}={L}_{ev}:\lambda \frac{\partial T}{\partial \stackrel{\xaf}{z}}={Q}_{cond}$. (50)

Table 2. Calculated values of the relative heat capacity when heating two samples with different heat transfer parameters and the influence assessment of the various mathematical processing.

$\stackrel{\xaf}{z}=0:\lambda \frac{\partial T}{\partial \stackrel{\xaf}{z}}={Q}_{ev}-{G}_{ev}\cdot {Q}_{vp}$. (51)

where the evaporation rate and the saturated vapor pressure are estimated as follows:

${G}_{ev}=const\frac{{P}_{vp}-\stackrel{\xaf}{P}}{\sqrt{2\pi RT/M}};\text{\hspace{0.17em}}\text{\hspace{0.17em}}{P}_{vp}=\stackrel{\xaf}{P}\mathrm{exp}\left(-\frac{{Q}_{vp}}{RT}\right)$

To calculate the heat capacity of the evaporator, a rather complex program was developed in FORTRAN, using computational equations based on the Simpson method [37] [38] [39] and Equation (37), which represents the most complete numerical iterative Crank-Nicholson scheme [37] [38] and for brevity is shown in Figure 7. All calculation details are given in [29] [30] [31], the iterative process is completed when the result *δC _{ev}*/

$\frac{\delta {C}_{ev}}{{C}_{ev}}=\sqrt{{\left(\frac{\delta \stackrel{\dot{}}{t}}{\stackrel{\dot{}}{t}}\right)}^{2}+{\left(\frac{\delta {q}_{ev}}{{q}_{ev}}\right)}^{2}}\le 0.3\text{\hspace{0.17em}}\text{J}/\text{K}$. (52)

The results of the calculated solution of equation (44) in the range of temperature load on the HP’s evaporator *δt* = *T _{ev}* −

The evaporation enthalpy of the working evaporator with boiling diethyl ether was estimated earlier in Equation (11), therefore we can substitute the known table values for diethyl ether [25] [26] [27] and can get an expression for the effective heat capacity of a linearly heated capillary-porous HP’s evaporator at the ether boiling beginning:

$\begin{array}{c}{\u0421}_{ev}=\frac{{H}_{ev}}{\stackrel{\dot{}}{t}}\\ =\frac{\left(345\text{\hspace{0.17em}}\text{kJ}/\text{kg}+1.75\text{\hspace{0.17em}}\text{kJ}/\text{kg}\cdot \text{K}\times 11\text{\hspace{0.17em}}\text{K}+2.34\text{\hspace{0.17em}}\text{kJ}/\text{kg}\cdot \text{K}\times 16\text{\hspace{0.17em}}\text{K}\right)\times 1.57\times {10}^{-4}\text{kg}/\text{s}}{3\times {10}^{-3}\text{K}/\text{s}}\\ =21.02\text{\hspace{0.17em}}\text{kJ}/\text{K}.\end{array}$ (53)

The ratio of the heat capacity of the evaporator with diethyl ether to the dry evaporator *C** _{ev}*/

$\frac{{\u0421}_{ev}}{{\u0421}_{ev0}}=\frac{{\u0421}_{ev0}+{H}_{ev}/\stackrel{\dot{}}{t}}{{\u0421}_{ev0}}=1+\frac{{H}_{ev}/\stackrel{\dot{}}{t}}{{\u0421}_{ev0}}=\frac{21.02+1.2}{1.2}=18.5$. (54)

which is very close to the maximum numerical value of the heat capacity of the HP’s evaporator.

Equations (53) and (54) confirm the correspondence of the experimental and calculated thermophysical characteristics of diethyl ether located in the evaporator at a high temperature load.

4. Conclusions

1) The measurements of the surface temperature of short linear HP’s with linear heating of the evaporator in time make it possible to unambiguously record an uneven drop in surface temperature. The HP’s surface temperature values around the evaporator, which are close to constant, allow us to estimate a small drop in the transmitted thermal power in the HP’s vapour channel. The constancy of the surface temperature around the evaporator also allows us to apply the method of solving the inverse problem of thermal conductivity (IPTC), and numerically obtain the extreme value of the heat capacity of the area (fragment) of the HP’s evaporator. This calculated result was obtained for the first time.

2) The HP’s external surface temperature of the capillary-porous evaporator, which is close to a constant value with monotonous heating, confirms the boiling process beginning and allows us to estimate the complex thermophysical parameters of diethyl ether in the evaporator.

3) With step-by-step regularization of the inverse problem solution of the HP’s thermal conductivity and piecewise smooth polynomial approximation of unknown coefficients, it is possible to minimize the error in restoring the evaporator heat capacity using a polynomial-exponential approximation function that restricts the range of acceptable heat capacity values by only positive values.

Acknowledgements

The author expresses gratitude to Tsvetkov Oleg Borisovich, Professor of ITMO, St. Petersburg, for his active participation in the discussion of this article at the Institute’s conferences. The author expresses special gratitude to the management of “RUDETRANSSERVICE”, Veliky Novgorod, for providing instruments and equipment for conducting experimental determination of thermal characteristics of heat pipes with heating close to linear in time.

Nomenclature

*a* = *λ*/*C** _{P}*∙

*a** ^{k}* =

*C** _{eff}*: effective heat capacity of the HP, J/K;

*C** _{HP}*(

*c** _{v}*(

*c** _{v}*(

*C*_{ev}_{0}—heat capacity of the dry evaporator, J/K;

*C** _{ev}*—heat capacity of the evaporator with diethyl ether, J/K;

*C** _{ev}*—calculated heat capacity of the evaporator, J/K;

*C** _{l}*—diethyl ether heat capacity, J/kg∙K;

*C** _{vp}*—heat capacity of diethyl ether moist vapour, J/kg∙K;

*C** _{fev}*—heat capacity of diethyl ether on the evaporator surface, J/kg∙K;

*E*_{H}_{2}—thermal power of the resistive heater, W;

*F** _{HP}*(s

*G _{l}*—mass flow rate of diethyl ether liquid phase in the evaporator, kg/s;

*G** _{mix}*—mass flow of the moist saturated vapour over the evaporator, kg/s;

*G** _{vp}*—mass flow rate of dry saturated vapour over the evaporator, kg/s;

(1 – *x** _{ev}*) =

*g _{k}*—the derivative of the heat capacity components;

*H _{ev}*—enthalpy of the HP’s evaporator, W;

*L** _{HP}*—HP’s length, m;

*L _{ev}*—the thickness of the capillary porous evaporator, m;

$\stackrel{\xaf}{P}$ —the average pressure in the vapour channel, Pa;

*P** _{ev}*—pressure above the evaporator, Pa;

*P** _{fcond}*—pressure on the condensation surface, Pa;

*P** _{v}*—the vapour pressure inside the toroidal vortex, close to the condensation pressure

*Pr*—the Prandtl number of the diethyl ether vapour;

*Q** _{ev}*—heat input to the evaporator, W;

*Q** _{cond}*—heat of condensation, W;

*R** _{c}*—thermal resistance of the lubricant layer, K/W;

*R** _{ev}*—thermal resistance of the evaporator, K/W;

*R** _{w}*—thermal resistance of the metal cover, K/W;

*R** _{HP}*(

*r*(*T** _{B}*) —specific heat of evaporation of diethyl ether, kJ/kg;

*T** _{B}*—boiling point of the diethyl ether, K;

*T** _{cal}*—the temperature of the flowing water in the vortex calorimeter;

*T** _{cond}*—condensation surface temperature

${\stackrel{\xaf}{T}}_{fcond}$ —the average temperature of the diethyl ether film on the HP’s condensation surface, K;

${\stackrel{\xaf}{T}}_{fev}$ —the average temperature of diethyl ether boiling microlayer on the HP’s lower cover surface, K;

${T}_{HP}\left(\stackrel{\xaf}{z}\right)$ —the temperature inside the HP’s vapour channel at a height of $\stackrel{\xaf}{z}$ above the evaporator, K;

*T** _{ev}*—stationary temperature of the grid evaporator saturated with the diethyl ether, K;

*T** _{sc}*—stationary temperature of the evaporator metal mesh, K;

*T** _{v}*—he vapour temperature inside the toroidal vapour vortex, K;

$\stackrel{\dot{}}{t}$ —temperature growth rate, K/s;

*v*—vapour (and liquid) phases flow velocity inside the capillary-porous evaporator, m/s;

*x _{ev}*—the degree of vapour moisture in the evaporator;

*Y*—parameter of the additional source function, J;

$\stackrel{\xaf}{z}=z/{L}_{HP}$ —dimensionless longitudinal coordinate;

*u** _{v}*,

Greek

*α** _{cal}*—heat transfer coefficient in the vortex flow calorimeter, W/m

*α** _{cond}*—heat transfer coefficient in the HP’s condensation region, W/m

*δ _{fcond}*—the average thickness of the diethyl ether film on the condensation surface, m;

*δ _{w}*—the thickness of the flat metal bottom cover, m;

*η*—Lagrange multiplier;

*λ** _{eff}*—effective thermal conductivity, W/m·K;

${\stackrel{\xaf}{\lambda}}_{HP}$ —effective thermal conductivity of the HP, W/m∙K;

*λ** _{l}*—thermal conductivity of diethyl ether, W/m∙K;

*λ*(*t*)—HP thermal conductivity coefficient, W/m∙K;

*λ _{sc}*—thermal conductivity coefficient of metal mesh evaporator frame, W/m∙K;

*λ _{w}*—thermal conductivity coefficient of metal top and bottom covers, W/m∙K;

*μ** _{i}*—friction coefficients;

*ξ*—condensation coefficient defined as the ratio of the number of vapour molecules condensing over the total number of molecules which strikes the surface;

Π—the porosity of the evaporator and insert (wick) in the HP’s vapour channel;

*ρ** _{HP}*—HP’s density, kg/m

${\rho}_{vp}^{mix}$ —the density of moist vapour inside the vapour channel, kg/m^{3};

*ρ** _{v}*—the vapour density inside the toroidal vortex, kg/m

${\stackrel{\xaf}{\rho}}_{ev}$, kg/m^{3}—average evaporator density, kg/m^{3};

*τ*—time, s;

*Δ**τ** _{k}*—time step for calculations and measurements, s;

*Φ _{df}*—dissipative functions;

*χ*—Lagrange multiplier;

*ψ*—the mass fractions of the HP’s components;

Conflicts of Interest

The author declares no conflicts of interest regarding the publication of this paper.

[1] | Brebbia, C.A. and Dominguez, J. (1998) Boundary Elements: An Introductory Course. WIT Press & Computational Mechanics Publication, Boston & Southampton, 325 p. |

[2] | Nakayama, A. and Kuwanara, F. (2008) A General Bioheat Transfer Model Based on the Theory of Porous Media. International Journal of Heat and Mass Transfer, 51, 3190-3199. https://doi.org/10.1016/j.ijheatmasstransfer.2007.05.030 |

[3] | Beck, J., Blackwell, B. and Clair, C. (1985) Inverse Heat Conduction Ill Posed Problems. Wiley & Sons, New York, 308 p. |

[4] | Carslaw, H.S. and Jaeger, J.C. (1986) Conduction of Heat in Solids. Oxford University Press, Oxford, 510 p. |

[5] | Lykov, A.V. (1967) Theory of Thermal Conductivity. Higher School, Moscow, 600 p. |

[6] | Platunov, E. (1973) Thermophysical Measurements in a Monotonic Mode. Energy, Moscow, 144 p. (In Russian) |

[7] | Isachenko, V.P., Osipova, V.A. and Sukomel, A.S. (1981) Heat Transfer. Energoizdat, Moscow, 416 p. (In Russian) |

[8] | Kutateladze, S.S. (1979) Fundamentals of the Heat Transfer Theory. 5th Edition, Atomizdat, Moscow, 416 p. (In Russian) |

[9] | Denisov, A.M. (1994) Introduction to the Theory of Inverse Problems. MU, Moscow, 208 p. (In Russian) |

[10] | Tikhonov, A.M. (1963) On the Solution of Incorrectly Set Tasks and the Method of Regularization. DAN USSR, 151, 501-504. |

[11] | Tikhonov, A.N. and Arsenin, V.Ya. (1979) Methods for Solving Incorrect Problems. Science, Moscow, 284 p. (In Russian) |

[12] | He, J.-H. (1999) Variational Iteration Method—A Kind of Non-Linear Analytical Technique: Some Examples. International Journal of Non-Linear Mechanics, 34, 699-708. https://doi.org/10.1016/S0020-7462(98)00048-1 |

[13] |
He, J.-H. (2006) Some Asymptotic Methods for Strongly Nonlinear Equations. International Journal of Modern Physics B, 20, 1141-1199. https://doi.org/10.1142/S0217979206033796 |

[14] |
Lu, J. (2007) Variational Iteration Method for Solving Two-Point Boundary Value Problems. Journal of Computational and Applied Mathematics, 207, 92-95. https://doi.org/10.1016/j.cam.2006.07.014 |

[15] | Yan, L., Fu, C.-L. and Yang, F.L. (2008) The Method of Fundamental Solutions for the Inverse Heat Source Problem. Engineering Analysis with Boundary Elements, 32, 216-222. https://doi.org/10.1016/j.enganabound.2007.08.002 |

[16] |
Seryakov, A.V. (2018) Intensification of Heat Transfer Processes in the Low Temperature Short Heat Pipes with Laval Nozzle Formed Vapour Channel. American Journal of Modern Physics, 7, 48-61. https://doi.org/10.11648/j.ajmp.20180701.16 |

[17] |
Seryakov, A.V., Shakshin, S.L. and Alekseev, P. (2017) The Droplets Condensate Centering in the Vapour Channel of Short Low Temperature Heat Pipes at High Heat Loads. Journal of Physics: Conference Series, 891, Article ID: 012123. https://doi.org/10.1088/1742-6596/891/1/012123 |

[18] |
Seryakov, A.V. (2019) Computer Modeling of the Vapour Vortex Orientation Changes in the Short Low Temperature Heat Pipes. International Journal of Heat and Mass Transfer, 140, 243-259. https://doi.org/10.1016/j.ijheatmasstransfer.2019.04.123 |

[19] | Seryakov, A.V. (2016) Characteristics of Low Temperature Short Heat Pipes with a Nozzle-Shaped Vapour Channel. Journal of Applied Mechanics and Technical Physics, 57, 69-81. https://doi.org/10.1134/S0021894416010089 |

[20] |
Seryakov, A.V. (2017) The Study of Condensation Processes in the Low-Temperature Short Heat Pipes with a Nozzle-Shaped Vapour Channel. Engineering, 9, 190-240. https://doi.org/10.4236/eng.2017.92010 |

[21] |
Seryakov, A.V. (2019) Numerical Modeling of the Vapour Vortex. Journal of High Energy Physics, Gravitation and Cosmology, 5, 218-234. https://doi.org/10.4236/jhepgc.2019.51013 |

[22] | Fowler, R.H. (1936) Statistical Mechanics. 2nd Edition, Cambridge University Press, London. |

[23] | Chapman, S. and Cowling, T.G. (1953) The Mathematical Theory of Non-Uniform Gases. Cambridge University Press, London, 447 p. |

[24] | CFdesign 10.0 2009. Version 10.0-20090623. User’s Guide. |

[25] | Mackay, D., Shiu, W., Ma, K. and Lee, S. (2006) Handbook of Physical-Chemical Properties and Environmental Fate for Organic Chemicals. Vol. III. Oxygen Containing Compounds. Taylor and Francis, Abingdon-on-Thames. |

[26] | (1976) Tables of Physical Values. Guide under the ed. of Kikoin I.K. Atomizdat, Moscow. 1008 p. |

[27] | Vargaftic, N.B. (1972) Handbook of Thermophysical Properties of Gases and Liquids. Publishing House of Physics and Mathematical Literature, Moscow, 721 p. |

[28] | Faghri, A. (1995) Heat Pipe Science and Technology. Taylor and Francis, Washington DC. |

[29] | Seryakov, A.V. and Alekseev, A.P. (2020) A Study of the Short Heat Pipes by the Monotonic Heating Method. Journal of Physics: Conference Series, 1683, Article ID: 022051. https://doi.org/10.1088/1742-6596/1683/2/022051 |

[30] | Seryakov, A.V. and Alekseev, A.P. (2020) Investigation of Short Heat Pipes by the Method of Monotonous Heating. III International Conference “Modern Problems of Thermophysics and Energy”, Moscow, 19-23 October 2020, 270-272. |

[31] | Seryakov, A.V. and Alekseev, A.P. (2020) Investigation of Short Linear Heat Pipes by Solving the Inverse Problem of Thermal Conductivity. Reshetnev Readings. Materials of the XXIV International Scientific and Practical Conference Dedicated to the Memory of the General Designer of Rocket and Space Systems, Krasnoyarsk, 10-13 November 2020, Part 1, 144-146. |

[32] |
Odibat, Z.M. and Momani, S. (2006) Application of Variational Iteration Method to Nonlinear Differential Equations of Fractional Order. International Journal of Nonlinear Sciences and Numerical Simulation, 7, 27-34. https://doi.org/10.1515/IJNSNS.2006.7.1.27 |

[33] |
Farcas, A. and Lesnic, D. (2006) The Boundary-Element Method for the Determination of a Heat Source Dependent on One Variable. Journal of Engineering Mathematics, 54, 375-388. https://doi.org/10.1007/s10665-005-9023-0 |

[34] | Elsholts, L.E. (2008) Calculus of Variations: A Textbook for Physical and Physical-Mathematical Faculties of Universities. Moscow Publishing House, Moscow, 205 p. (In Russian) |

[35] | Elsholts, L.E. (1969) Differential Equations and Calculus of Variations. Nauka, Moscow. (In Russian) |

[36] | Tslaf, L.Y. (2005) Calculus of Variations and Integral Equations: A Reference Guide. 3rd Edition, St. Petersburg Publishing House, St. Petersburg, 192 p. (In Russian) |

[37] | Marchuk, G.I. (1980) Methods of Computational Mathematics. Nauka, Moscow, 536 p. (In Russian) |

[38] | Tikhonov, A.N. and Samarsky, A.A. (1966) Equations of Mathematical Physics. Nauka, Moscow, 724 p. (In Russian) |

[39] | Kalitkin, N.N. (1978) Numerical Methods. Nauka, Moscow, 512 p. (In Russian) |

Journals Menu

Contact us

+1 323-425-8868 | |

customer@scirp.org | |

+86 18163351462(WhatsApp) | |

1655362766 | |

Paper Publishing WeChat |

Copyright © 2024 by authors and Scientific Research Publishing Inc.

This work and the related PDF file are licensed under a Creative Commons Attribution 4.0 International License.