• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to both a system and a method for heat exchange with the airflow inside a wind tunnel. It is necessary to cool the airflow and control the temperature of said airflow inside a wind tunnel, for which purpose an optimally parameterized heat exchanger is used to obtain suitable cooling without an excessive increase in pressure loss. The present invention also relates to a design method for designing said heat exchanger. The present invention also relates to a wind tunnel comprising said system for heat exchange with the airflow circulating inside said wind tunnel.
    公开号:ES2652517A2
    申请号:ES201790043
    申请日:2016-04-29
    公开日:2018-02-02
    发明作者:José María Cancer Abóitiz；Isaac PRADA Y NOGUEIRA；Pablo José CANCILLO MARTÍNEZ；Enrique MARTÍN LÓPEZ；Ignacio SERRANO REMÓN
    申请人:Madrid Fly S L；Madrid Fly SL；
    IPC主号:
    专利说明:

    Wind tunnel exchanger
    5 Object of the invention
    The present invention relates to a system for the exchange of heat with the air flow inside a wind tunnel, as well as a method of regulating the air flow temperature inside a wind tunnel and design of said exchanger. At
    10 inside a wind tunnel it is necessary to cool the air flow and control the temperature of said air flow.
    Background of the invention
    15 Heat exchangers are used in wind tunnels, both horizontal and vertical, for cooling the air flow, which increases its temperature due to friction between said air flow and the internal walls of the wind tunnel duct .
    20 It is important in these wind tunnels to maintain a constant air temperature and density, so that the air flow temperature control is necessary. This implies achieving a uniform temperature profile in the test chamber or tunnel flight.
    For this, passive air exchange systems are known, which expel hot air
    25 inside the tunnel and replace it with new air, so that heat is dissipated from the inside of the tunnel. Said new air is introduced through a system of gates with various designs. This method does not allow an exhaustive control of the air flow temperature inside the tunnel.
    On the other hand, heat exchangers are known inside the duct, similar to the water radiators used in the cooling of the car engine, which cool the air flow. These devices introduce high pressure losses in the air flow as the heat transfer area increases.
    35 Aerodynamic profiles installed in the curvatures or corners of the wind tunnel are also used, which allow a better flow profile to be obtained with the corresponding


    Introduction of some pressure loss. This system requires, for proper cooling, the inclusion, within said profiles, of a system designed to act as a heat exchanger.
    5 Finally, there are also cooling options inside the wind tunnelby spraying water or low depth geothermal energy, which does notallows an optimal regulation of the air flow temperature profile and is not applicablein all types of systems, and may also have undesirable negative effects such asexcessive increase in relative humidity in the air inside the tunnel.
    Description of the invention
    The present invention proposes a solution to the above problems by means of a heat exchanger according to claim 1, a wind tunnel according to claim
    14, a method of regulating the temperature of an air flow inside a wind tunnel according to claim 15 and a design method for designing an exchanger according to claim 16. The dependent claims define preferred embodiments of the invention.
    A first inventive aspect provides a heat exchanger for wind tunnels, comprising:
    - at least a first wall and a second wall, each wall comprising at least a first edge, a second edge, a third edge and a fourth edge,
    25 -a total number (N) of tubes (Tijk) adapted to contain a working fluid, at least a plurality of said tubes (Tijk) forming at least one series (Sj), nS being the total number of series (Sj) ,
    30 -at least one inlet manifold of the working fluid connected to a first end of at least one tube (Tijk), and
    - at least one outlet manifold of the working fluid connected to a second end of at least one tube (Tijk),
    35 where the tubes (Tijk) of each series (Sj) form a plurality (nFj) of rows (Fj) and a


    plurality (ncjf) of columns (Cj) distributed according to rows (Fj), and where:
    - the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series (Sj),
    5 -the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different columns (Cj)from the same series (Sj),
    - the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column (Cj), said column (Cj) being the closest to either the third edge or the fourth edge, with respect to the tube ( Tijk) from the same series (Sj) closest to said third
    edge or fourth edge,
    - the distance (DGj),
    15 or between the nearest tubes (Tijk) of adjacent series (Sj), or
    or between the tube (Tijk) closest to the first edge or second edge and said first edge or second edge of the heat exchanger,
    20 are parameterized so that:
    - distance (DL2jf)> 0, and
    - distance (DGj)> distance (DTjf),
    so that:
    - the parameterization relative to the rows (Fj) mainly optimizes the pressure loss of the heat exchanger, and
    - The parameterization relative to the columns (Cj) mainly optimizes the total effective total transfer area of the heat exchanger.
    Throughout this document, it will be understood that the heat exchanger is comprised between at least two walls, including the total number (N) of tubes (Tijk) of the heat exchanger. Said exchanger is, by


    these walls, partially limited in volume, so that preferably the volume defined by said walls is also defined by the dimensions of the wind tunnel. In this way, the air flow completely affects the total number (N) of tubes (Tijk) of the heat exchanger.
    Advantageously, the section of the wind tunnel is completely occupied by tubes (Tijk) of the heat exchanger, so that there is an increased area of heat transfer with the air flow, without obstacles in the path of said air flow except the tubes themselves (Tijk).
    Said tubes (Tijk) of the heat exchanger contain a working fluid, preferably a refrigerant, which circulates through the tubes (Tijk) allowing the transfer of heat between said tubes (Tijk) and the flow of outside air to these tubes (Tijk)
    In a particular embodiment, the working fluid can be either gaseous or liquid or solid.
    Said working fluid allows, in a heat exchanger, both cooling and heating of the air flow, or any other fluid, to circulate outside the tubes
    20 (Tijk) of said heat exchanger.
    Throughout this document, it will be understood that a series (Sj) is a set of tubes (Tijk), which in turn form a number of rows (Fj) and columns (Cj), which can be both variable and constant between The different series.
    Advantageously, the distribution of the tubes (Tijk) in rows (Fj) and columns (Cj) in the heat exchanger, following a distribution established by the parameters DTjf, DL1jfl, DL2jf and DGj, allows an exchange of thermal power in the heat exchanger with minimal pressure loss.
    In a particular embodiment, the distances DTjf and DGj are considered as transverse distances, while DL1jfl and DL2jf are longitudinal distances.
    The determination of the parameters allows an optimal heat transfer in the
    35 heat exchanger, since an excessively low value of the DTjf parameter causes a high separation of the air flow that affects the tubes (Tijk), so that


    it loses a large part of the effective thermal transfer area, while if the value of said parameter is excessively high, a high pressure loss occurs in the heat exchanger.
    5 In addition, the determination of parameter DL2jf allows to reduce airflow separation,allowing said air flow to flow between the different rows (Fj) of each series (Sj).
    Additionally, an excessively low value of parameter DL1jfl causes a reduction in the heat transfer area of the heat exchanger.
    10 Finally, the determination of parameter DGj allows optimum maintenance of the total number (N) of tubes (Tijk) of the heat exchanger.
    In a particular embodiment, the value of the parameter DGj between consecutive series (Sj) 15 allows access to each of the tubes (Tijk) of an operator or maintenance unit.
    Advantageously, the determination of each of the different parameters allows the improvement of the characteristics of the heat exchanger. Additionally, the design of these parameters combined in the heat exchanger allows a heat exchange
    20 optimal with air flow.
    The correct parameterization relative to the rows (Fj) allows additionally to optimize mainly the velocity profile of the air flow at the outlet of the heat exchanger, while the correct parameterization relative to the columns (Cj) allows
    In a further way, the temperature profile of said air flow is also optimized also at the heat exchanger outlet.
    In a particular embodiment, the heat exchanger comprises at least two tubes (Tijk) in fluidic communication forming at least one coil (Ri).
    30 Coil (Ri) is understood as a union of tubes (Tijk) through which the working fluid can circulate continuously.
    This allows the passage of working fluid continuously between different tubes (Tijk) of the
    35 heat exchanger, so that the pipe connections (Tijk) are reduced with both at least one inlet manifold and at least one outlet manifold.


    In a particular embodiment, the heat exchanger comprises a plurality (nl) of coils (Ri), where:
    5  each coil (Ri) comprises a plurality (g) of groups (Gj), and
     each group (Gj) comprises a plurality (ng) of tubes (Tijk),
    where each series (Sj) is formed by the same group (Gj) of each coil (Ri), and where:
     the number (nFj) of rows (Fj) of each series (Sj) is the number of tubes (Tijk) comprising each group (Gj), and
     the number (ncjf) of columns (Cj) of each series (Sj) is the number of coils (Ri).
    15 This distribution of tubes (Tijk) in the heat exchanger allows, advantageously, a union of tubes (Tijk), preferably correlatively, so that the temperature profile of the working fluid allows a homogeneous thermal transfer with the flow of air.
    In a particular embodiment, the number (ng) of tubes (Tijk) of each group (Gj) is two or three tubes (Tijk).
    This allows an optimal distribution of the total number (N) of tubes (Tijk) in the heat exchanger 25, as well as an optimal ratio of the parameters DTjf, DL1jfl, DL2jf and DGj.
    In a particular embodiment, at least one tube (Tijk) does not allow the circulation of working fluid.
    In a particular embodiment, at least one coil (Ri) does not allow the circulation of working fluid.
    This allows, advantageously, a modular heat exchanger, in which the number of coils (Ri) or tubes (Tijk) operative during operation can be modified
    35 of said heat exchanger according to the required specifications.


    In a particular embodiment, the total number (N) of tubes (Tijk) of the heat exchanger meets the following expression:
    �
    N = � � n� �
    5 In this way, the number of tubes (Tijk) is obtained according to an expression that depends on the number of rows (Fj), the number of columns (Cj) and the number of series (ns) of the heat exchanger, taking into account each of the series (Sj), thus allowing to obtain a heat exchanger with a velocity profile and a more uniform temperature profile at its output, with less pressure loss.
    In a particular embodiment, the total number (N) of tubes (Tijk) of the heat exchanger meets the following expression:
    N = g.n.n
    �
    In this way, the number of tubes (Tijk) is obtained according to an expression that depends so much
    15 of the number of rows (Fj) and the number of columns (Cj) of the heat exchanger, taking into account each of the series (Sj). Said number of tubes, arranged according to groups with the same number of tubes in equal coils, allows to obtain a velocity profile and a more uniform temperature profile at the exit of the heat exchanger, with a lower pressure loss.
    In a particular embodiment, the total number (N) of tubes (Tijk) of the heat exchanger is obtained from the following expression:
    A = ∑FA�,
    25 Being A the total effective heat transfer area of the heat exchanger, F� is a thermal transfer factor that allows to take into account that the tunnel air flow does not completely wet the total area of each tube, due to the actual separation of said flow, and A� the total thermal transfer area of a tube (Tijk).
    Advantageously, the total effective heat transfer area of the exchanger according to the number of tubes obtained thus has a value equal to or greater than the total effective transfer area value required for the design of said heat exchanger.


    In a particular embodiment, the heat exchanger comprises a distance DL3jn, which is the distance from the third or fourth edge to the nearest tube (Tijk) of each series (Sj), this distance being preferably the minimum distance established by construction of the heat exchanger.
    This minimum distance is established according to the heat exchanger's manufacturing criteria.
    Advantageously, the introduction of parameter DL3jn allows a correct manufacturing,
    10 transport and / or installation of the heat exchanger, so that the tubes (Tijk) cannot be damaged during the process and the space available for the installation of said tubes (Tijk) in the heat exchanger is the maximum.
    In a particular embodiment, the parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj of the
    15 heat exchanger meet the following expressions according to the width (B) and length (L) of the heat exchanger:
    � �
    o = ∑ + ∑ ∑
    � � � �
    � = � � � �
    20 or ∑ 1 + 2, ∀ = 1,…, ∀ = 1,… ,, where

    o =,…, + ∑3, ∀ = 1,…, �
    For maximum heat exchanger sizing, the maximum value of the
    25 values obtained in each case for the parameter Ljf, corresponding to each of the rows (Fj) of the same series (Sj), for each of the series (Sj). Said maximum value allows, advantageously, to consider the maximum value of the sum of the different values of the parameters DL1jfl and DL2jf among those obtained for all rows (Fj) of the same series (Sj), and for each of the series (Sj).
    Advantageously, these ratios allow obtaining a heat exchanger that has minimal pressure loss and maximum heat transfer.
    In a particular embodiment, at least one of the parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj of the heat exchanger maintains a constant value.


    This allows for a more uniform distribution of the tubes (Tijk) in the heat exchanger the more constant the values of the different parameters.
    In a particular embodiment, all the parameterized distances DTjf are equal, all the parameterized distances DGj between tubes (Tijk) are equal and the number (nFj) of rows (Fj) of each series (Sj) is equal in the heat exchanger, and the expression is fulfilled:
    = (+ 1) + - 1�
    Advantageously, this allows a more uniform distribution of the tubes (Tijk) in the heat exchanger and a simpler manufacture thereof.
    In a particular embodiment, all the parameterized distances DL1jfl are equal, all the parameterized distances DL3jn are equal, the number (nFj) of rows (Fj) of each series (Sj) is the same and the number (ncjf) of columns (Cj) of each series (Sj) is the same, and the expression is fulfilled:
    = −11 + 2,…, + 23�
    Advantageously, this allows a more uniform distribution of the tubes (Tijk) in the heat exchanger and a simpler and less expensive manufacture thereof.
    In a particular embodiment, the heat exchanger comprises two input collectors and two output manifolds, in which each of the coils (Ri) is alternately connected to a different input manifold and a different output manifold, of so that the trajectory of the working fluid has a sense that alternates in each coil (Ri).
    In this way, each adjacent coil (Ri) alternates in the direction of circulation of the working fluid.
    This allows, in an advantageous way, a more homogeneous distribution of the workflow along the heat exchanger, by means of the different coils (Ri), which allows a heat exchange with the most homogeneous air flow, and therefore a profile of


    temperatures also more homogeneous.
    Additionally, this allows an increased modularity of the heat exchanger, allowing the closure of certain coils (Ri) by any means
    5 closing to operate only with certain coils (Ri) of the heat exchanger, in caseof leaks in any of them or in case of minor thermal transfer needsthan the maximum that can be achieved with the exchanger.
    In a particular embodiment, the closure means allows the closure of at least one tube
    10 (Tijk), allowing the closure of said tube for maintenance work or in case of thermal transfer needs less than the maximum that can be achieved with the exchanger.
    In a particular embodiment, in the heat exchanger each tube (Tijk) is a circular tube (Tijk) 15 with equal outside diameter (∅).
    The cross section of the tube (Tijk) is determined by the permissible range of working fluid velocities. The determination of the inner diameter of said tube (Tijk) is therefore also determined by the permissible range of fluid velocities of
    20 work when this tube (Tijk) is circular. Finally, the outer diameter of said tube (Tijk) is determined by criteria of maximum pressure that said tube (Tijk) must withstand or other structural or manufacturing criteria of the heat exchanger.
    Advantageously, the heat exchanger is manufactured with commercial elements, preferably circular tubes, which allows a reduction of the manufacturing cost.
    In a particular embodiment, the total effective heat transfer area of the heat exchanger, all the tubes (Tijk) being circular, is as follows:
    = ∅�
    F being an average thermal transfer factor for all tubes (Tijk).
    In a second inventive aspect, the invention provides a wind tunnel comprising at least one heat exchanger like that of the first inventive aspect.


    This allows the air flow that circulates along a wind tunnel to maintain a uniform temperature profile without distorting its profile of low velocities and pressure losses.
    In a third inventive aspect, the invention provides a method of regulatingtemperature of an air flow inside a wind tunnel comprising thefollowing stages:
     provide at least one heat exchanger according to the first inventive aspect,
     measure the temperature of the air flow inside the wind tunnel,
     regulate the temperature of the air flow by modifying either the number of tubes (Tijk) operating in the heat exchanger by means of closing means, or the 15 working fluid conditions, or the parameterized distances DTjf, DL1jfl,
    DL2jf, and DGj.
    Said modifiable working fluid conditions can be either the temperature, the composition or the physical state of said fluid.
    20 The regulation by modifying parameterized distances includes both the modification of the distances during the design of the system and the physical modification of the arrangement of at least one tube (Tijk) once all the tubes (Tijk) are installed.
    25 The temperature regulation of an air flow of a wind tunnel allows the control of both the temperature and the density of said air flow, so that both the test and flight conditions inside the wind tunnel are homogeneous and as close to the corresponding real situation.
    In a particular embodiment, the step of regulating the air flow temperature is performed by modifying the parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj.
    In a fourth inventive aspect, the invention provides a method of designing a heat exchanger according to the first inventive aspect for a wind tunnel that
    35 comprises the following stages:


    - define the dimensions of the heat exchanger, said dimensions being width (B), height (H) and length (L),
    - determine the total effective heat transfer area (A) of the necessary heat exchanger as well as the thermal transfer factor (Fm) and the total thermal transfer area (Atubo m) of each tube (Tijk),
    - determine the total number (N) of tubes (Tijk) of the heat exchanger by the following expression:
    ,
    = ∑ �
    - determine the number of total (nS) of series (Sj), the total number (nFj) of rows (Fj) of each series (Sj), and the total number (nCjf) of columns (Cj) of each series (Sj) , 15 -determine the following parameters:
    or the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series
    (Sj), 20
    or the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different columns (Cj) of the same series (Sj),
    or the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column
    25 (Cj), said column (Cj) being the closest to either the third edge or the fourth edge, with respect to the tube (Tijk) of the same series (Sj) closest to said third edge or fourth edge,
    or distance (DGj), 30
    • between the closest tubes (Tijk) of adjacent series (Sj), or
    • between the tube (Tijk) closest to the first edge or second edge and
    said first edge or second edge of the heat exchanger, 35
    or the distance (DL3jn) from the third edge or fourth edge to the nearest tube (Tijk)


    of each series (Sj)
    according to the following expressions:
    � � �
    o = ∑ + ∑ ∑
    � � � �
    �
    or ∑ 1 + 2, ∀ = 1,…, ∀ = 1,…,
    = � � � �
    o =,…, + ∑3, ∀ = 1,…, �
    The total area (Atubo m) of thermal transfer of a tube (Tijk) is defined according to the section of each tube, as well as the total number (N) of tubes (Tijk).
    Additionally, once the step of determining the parameters specified according to the previous relationships has been carried out, the correct determination of the total number (N) of tubes (Tijk) is checked by the expression:
    �
    = � �
    � �
    Advantageously, the determination of the parameters DTjf, DL1jfl, DL2jf, DL3jn, DGj, nS, nFj and nCjf allows the design of a heat exchanger of optimum thermal transfer that has the air flow inside the wind tunnel and low loss of Pressure.
    In a particular embodiment, the design method further comprises the step of determining the total number (nl) of coils (Ri), the number (g) of groups (Gj) and the number (ng) of tubes (Tijk) in each group (Gj), prior to the stage of determining the different
    DTjf, DL1jfl, DL2jf, DL3jn and DGj parameters.
    This allows, advantageously, a more uniform distribution of the tubes (Tijk) in the heat exchanger and a simpler and less expensive manufacture thereof.
    All features and / or the method steps described herein (including the claims, description and drawings) may be combined in any combination, except for combinations of such mutually exclusive features.


    Description of the drawings
    The foregoing and other features and advantages of the invention will be made more clearly.
    5 from the following detailed description of a preferred embodiment, given only by way of illustrative and non-limiting example, with reference to the attached figures.
    Figure 1 shows a perspective view of an embodiment of the heat exchanger. 10 Figure 2A shows a front view of an embodiment of the heat exchanger.
    Figure 2B shows a plan view of section A-A of Figure 2A.
    15 Figure 2C shows a detailed view of Figure 2B.
    Figure 3 shows a front view of an embodiment of the heat exchanger.
    Figure 4 shows a diagram of the arrangement of an embodiment of the heat exchanger inside the wind tunnel.
    Figures 5A and 5B show the comparison of the contours of fluid temperature profiles in the heat exchangers tested.
    25 Figures 6A and 6B show the comparison of the contours of fluid velocity profiles in the heat exchangers under test.
    Detailed description of a preferred embodiment of the invention
    30 In the following detailed description the following nomenclature will be used:
    - Coil: Ri
    - Group: Gj 35 -Series: Sj


    - Tube: Tijk
    -Total number of coils: nl5-Total number of groups: g
    - Number of tubes per group: ng
    10-Rows: Fj
    - Columns: Cj
    - Total number of rows (Fj) in each series (Sj): nFj 15 - Total number of columns in each series (Sj) distributed according to rows (Fj): ncjf
    - Total number of series: nS
    Figure 1 shows a heat exchanger (1) according to a particular embodiment of the invention, intended for installation in a wind tunnel (2).
    Said heat exchanger (1) comprises a first wall (3) as a lower wall and a second wall (4) as an upper wall. The air flow to be cooled, coming from the
    25 wind tunnel (2), enters the heat exchanger (1) according to the direction shown in figure 1, that is, from the edge (9) of the heat exchanger (1) to the edge (10) of the heat exchanger heat (1).
    In this embodiment, the number (nl) of coils (Ri) is 55, each of 30 coils (Ri) comprising a total (g) of 6 groups (Gj), and each of these groups (Gj) comprising a number (ng) of 3 tubes (Tijk).
    Said tube arrangement (Tijk) forms a total of 6 series (Sj), each of said series (Sj) comprising a total (nFj) of 3 rows (Fj), the number of rows (Fj) being the number (ng ) 35 of tubes (Tijk) of each group (Gj), and also comprising a total (ncjf) of 55 columns (Cj), said number of columns (Cj) being the number (nl) of coils (Ri).


    The total number (N) of tubes (Tijk) in this particular example is 990 tubes, according to the arrangement described.
    5 The value of the parameters N, nFj, ng, ncjf, Fj, Sj, Gj, Cj, nl are always integer values.
    Said tubes (Tijk) all have cylindrical section, with an outer diameter of 28mm in this particular example.
    The heat exchanger (1) also comprises two input manifolds (5) and two output manifolds (6), which are alternately connected to each of the coils (Ri). In this way, the odd coils (Ri) are connected to the input manifold (5) to the left of Figure 1, and to the output manifold (6) located to the right of Figure 1, while the coils (Ri) pairs are connected to the
    15 remaining input (5) and output (6) collectors.
    The working fluid circulates inside the coils (Ri) and accesses said coil (Ri) through the inlet manifolds (5) and leaves the coil (Ri) through the outlet manifold (6).
    According to said arrangement of connections of the coils (Ri) to the input collectors
    (5) and outlet (6) an alternate route of the working fluid is obtained through the odd and even coils (Ri).
    Figure 2A shows a front view of an embodiment of a heat exchanger (1), limited by a first wall (3) as a bottom wall and a second wall (4) as a top wall, said walls (3, 4) defining the height (H) of the heat exchanger (1).
    In this particular embodiment, said height (H) has a value of 3 m.
    30 This figure shows the first coil (Ri) of the heat exchanger (1), formed by tubes (Tijk) joined together, by elbows. These elbows allow fluidic communication both between tubes (Tijk) of the same group (Gj) and between groups (Gj).
    35 These elbows are outside the air flow, being located outside the walls (3, 4) of the heat exchanger. This also happens with the input collectors (5) and the


    outlet manifolds (6). This allows the air flow to find no obstacles in its path, with the exception of the tubes (Tijk), so that the pressure loss is minimized.
    Figure 2B shows a plan view of the A-A cut made on the front view of the5 figure 2A.
    Said plan view shows the remaining dimensions of the heat exchanger (1), that is, its width (B) and its length (L). In this particular embodiment, the width (B) has a value of 6 m and the length (L) has a value of 3.5 m.
    10 Figure 2B also shows the arrangement of the 55 coils (Ri) and the 6 series (Sj) that they form. In each series (Sj) the different groups (Gj) are also observed, which make up said series (Sj). As can be seen, a series (Sj) is the grouping of the same group (Gj) of each coil (Ri). For example, the series (S1) is the set of groups (G1) of
    15 the 55 coils that make up the heat exchanger (1).
    The arrangement of each tube (Tijk) as a function of the row (Fj) and column (Cj) to which it belongs is also represented in Figure 2B, where both the arrangement between different series (Sj) and the displaced distribution of rows (Fj) and columns (Cj), according to a
    20 parameterization detailed below.
    Figure 2C shows a detail (C), taken from the plan view of the section of Figure 2B.
    This particular embodiment shows the different parameters that define the distribution of the 25 tubes (Tijk) in the heat exchanger.
    First, this detail partially shows two series (Sj), the S5 and S6 series in this embodiment, and the different groups (Gj) in each of them. Each series (Sj) consists of 3 rows (Fj) and in which a maximum of 10 columns (Cj) are shown.
    The parameters dimensioned in this particular embodiment are DTjf, DL1jfl, DL2jf and DGj, all of which are constant between different series (Sj), with the exception of the DL2jf values in each series (Sj), which takes a zero value for the odd rows of each series (F1 and F3) and a constant value for even rows (F2).
    First, DTjf defines the distance between two rows (Fj) of the same series (Sj).


    In this particular example, said distance has a value of 112 mm, so that it allows the access of an operator or machine for maintenance work of each of the tubes (Tijk) of the even rows (F2) of each series (Sj ). This distance also allows the formation of a longitudinal duct, that is, in the direction of passage of the air flow, for the passage of said air flow.
    The distance DL1jfl defines the distance between two tubes (Tijk) of the same row (Fj), said two tubes (Tijk) of the same row (Fj) always being perfectly aligned. The value of the distance DL1jfl is 59 mm in this particular embodiment.
    This distance allows the incident air flow in both tubes (Tijk) to follow a path suitable for a better use of the thermal transfer area of the tube (Tijk) located behind the previous one.
    The distance DL2jf defines the distance between two tubes (Tijk) of two different rows (Fj) and the same column (Cj), said column (Cj) being the closest to the third edge (9), with respect to the tube (Tijk ) of the same series (Sj) closest to said third edge (9). Although in columns 2C the columns (Cj) are offset, they correspond one by one. Figure 2B shows the arrangement of a column, that is, a coil (Ri). The distance value DL2jf is 0 mm for odd rows (F1 and F3) and 84 mm for even rows (F2) in this particular embodiment.
    This distance allows the air flow to influence a larger tube surface (Tijk), reducing the separation of the flow, so that the heat transfer increases and the pressure loss of the exchanger (1) decreases.
    The DGj distance defines the distance between the two closest tubes (Tijk) of two consecutive series (Sj). The distance DGj also defines the distance between the tubes (Tijk) of the rows (Fj) located at the ends of the distribution of the total number (N) of tubes (Tijk) and the edges (7, 8) of the exchanger (1 ), located to the left and right of Figures 2B and 2C. The value of the distance DGj is 665 mm in this particular embodiment.
    This distance allows both the access of an operator or machine and their free movement for maintenance work on each of the tubes (Tijk) of the odd rows (F1 and F3) of each series (Sj). This distance also allows the formation of a longitudinal duct, that is, in the direction of passage of the air flow, for the passage of said flow of


    air.
    In a particular embodiment, parameter DL3jn is also sized.
    5 Said distance DL3jn defines the distance between the edges (9, 10) of the heat exchanger
    (1) and the nearest tube (Tijk) in each case.
    This distance is taken during the parameterization, as usual, as the minimum distance necessary for the correct construction and manufacture of the heat exchanger 10 (1). In this particular embodiment the DL3jn takes a value of 115 mm.
    Figure 3 shows a front view of the particular embodiment of heat exchanger
    (1) described in the previous figures.
    15 This situation shows the situation of the lower and upper walls (3, 4) as well as one of the coils (Ri), connected to the inlet manifold (5) and to the outlet manifold (6).
    The figure also shows the connection between the different tubes (Tijk) that make up the coil, by means of elbows, and the parameterization related to the ducts that allow the passage of air flow as well as the maintenance of each tube (Tijk) both by a Operator as per a machine adapted for this purpose.
    Finally, Figure 4 shows a diagram of a wind tunnel (2) through which an air flow circulates. A heat exchanger (1) in said wind tunnel (2) is already shown.
    It can be seen how, in the operative position, the heat exchanger (1) has fluid connections between the pipes (Tijk) and the inlet manifolds (5) and the outlet manifolds (6) located outside the actual wind tunnel duct (2) through which the flow of
    30 air
    Tests and simulations
    In order to demonstrate the importance of the parameterization of the mentioned variables 35 (DTjf, DL1jfl, DL2jf, DL3jn, DGj, nS, nFj and nCjf), especially the influence of the parameters DTjf, DL2jf, and DGj on the performance of the exchanger of heat, several have been carried out


    tests and simulations to compare the performance results of different heat exchangers by varying the values of these parameters.
    These tests and simulations have been carried out with fluid dynamics software
    5 computational (CFD), and consist of comparing the pressure losses and temperature drops of the heat exchangers studied, in order to establish the differences in performance and behavior of said heat exchangers depending on the values given to the different parameters already mentioned; that is the parameters DTjf, DGj and DL2jf.
    10 Two different heat exchangers with different values of such parameters have been studied.
    The first heat exchanger (IC1) is the one disclosed in the preferred embodiment already
    15 described, with the given parameter values, while the second heat exchanger (IC2) corresponds to a known heat exchanger with a classic tube distribution, in which said tubes are arranged as a bundle of aligned tubes, which has equal longitudinal distances and equal transverse distances between tubes. The parameter values of both heat exchangers are as follows:
    IC2 IC1
    DL2 = 0 mm (for each tube) DL2 = 84 mm> 0
    DT = DG = 315.8 mm DT = 112 mm <DG = 665 mm
    Two different comparisons have been tested and are shown in Figures 5a, 5b, 6a and 6b. For both cases, the air flow enters the heat exchanger from the top of the figures and exits said heat exchanger from the bottom
    25 of said figures.
    Figures 5A and 5B show the contours of the fluid temperature profile in the heat exchangers under test. Results of the fluid temperature evolution of IC1 can be observed in Figure 5A, in which there is a wake of cooled fluid at the heat exchanger outlet, more intense than that observed for IC2 in Figure 5B, decreasing the temperature of average output. Accordingly, the thermal transfer is higher for IC1, which demonstrates that the parameter conditions given in the preferred embodiment improve the performance of the heat exchanger.


    known heat IC2.
    Figures 6A and 6B show the fluid velocity profile contours in the same heat exchangers tested. Results of the fluid velocity distribution of IC1 can be seen in Figure 6A, in which the wake of the flow for each of the two sets of tubes is slightly wider than that shown for each of the six sets of tubes of IC2, which can be seen in Figure 6B, which indicates a higher pressure loss for this area in the distribution with two sets of tubes (IC1). These two sets of tubes can potentially result in 10 higher local pressure losses than the tubes equally spaced in the distribution of IC2. However, due to the parameterization performed in IC1, related to the values of DG, DT and DL2, the local pressure losses in the ducts in which DG is measured will be considerably lower for IC1. Therefore, a distribution of pipes of this type such as that provided in IC1 can lead to losses
    Higher local pressure in the regions affected by the flow wake, but at a lower overall pressure loss, demonstrating that the parameter conditions given in this example (i.e. in the present invention) improve the performance of a heat exchanger
    20 The following table also presents the results obtained from the CFD simulations in the system per unit:
    Pressure losses
    Heat exchanger Temperature drop [.u.] [.u.]
    IC1 0.93 1.09 IC2 11
    As shown in the table, IC1, that is, the heat exchanger of the preferred embodiment 25, has lower pressure losses while improving its temperature drop, thereby improving the performance of the heat exchanger.
    Accordingly, the parameterization of a heat exchanger according to the first inventive aspect provides a heat exchanger in which the heat exchange with the fluid is higher, while resulting in lower pressure losses.
    Additional remarks


    The present invention is also directed to:
    [1] Heat exchanger (1) for wind tunnels (2), comprising:5
    - at least a first wall (3) and a second wall (4), each wall (3, 4) comprising at least a first edge (7), a second edge (8), a third edge (9) and a fourth edge (10),
    10 -a total number (N) of tubes (Tijk) adapted to contain a working fluid, at least a plurality of said tubes (Tijk) forming at least one series (Sj), the total number (nS) of series ( Sj),
    - at least one inlet manifold (5) of the working fluid connected to a first end of at least one tube (Tijk), and
    - at least one outlet manifold (6) of the working fluid connected to a second end of at least one tube (Tijk),
    20 wherein the tubes (Tijk) of each series (Sj) form a plurality (nFj) of rows (Fj) and a plurality (ncjf) of columns (Cj) distributed according to the rows (Fj), and where:
    - the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series (Sj),
    25 -the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different columns (Cj) of the same series (Sj),
    - the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column (Cj), said column (Cj) being the closest to either the third edge (9) or the fourth edge (10) , with respect to the tube (Tijk) of the same series (Sj) closest to said
    third edge (9) or fourth edge (10),
    - the distance (DGj),
    35 or between the nearest tubes (Tijk) of adjacent series (Sj), or


    or between the tube (Tijk) closest to the first edge or the second edge (7, 8) and said first edge or second edge (7, 8) of the heat exchanger (1),
    They are parameterized so that:
    - the parameterization relative to the rows (Fj) mainly optimizes the pressure loss of the heat exchanger (1), and
    - The parameterization relative to the columns (Cj) mainly optimizes the total total effective transfer area of the heat exchanger (1).
    [2] Heat exchanger (1) according to [1], where at least two tubes (Tijk) are in fluidic communication, forming at least one coil (Ri).
    [3] Heat exchanger (1) according to [2], comprising a plurality (nl) of coils (Ri), where:
     each coil (Ri) comprises a plurality (g) of groups (Gj), and
     each group (Gj) comprises a plurality (ng) of tubes (Tijk),
    where each series (Sj) is formed by the same group (Gj) of each coil (Ri), and where:
     the number (nFj) of rows (Fj) of each series (Sj) is the number of tubes (Tijk) comprising each group (Gj), and
     the number (ncjf) of columns (Cj) of each series (Sj) is the number of coils (Ri).
    [4] Heat exchanger (1) according to any of [1-3], where the total number of tubes
    (N) meets the expression:
    �
    = � � � �
    [5] Heat exchanger (1) according to [3], where the total number of tubes (N) meets the


    expression:
    = .. �
    [6] Heat exchanger (1) according to any of [1-5], where the total number (N) of5 tubes (Tijk) of the heat exchanger (1) is obtained from the following relation:
    = ∑ �,
    being A the total effective heat transfer area of the heat exchanger (1), � a 10 thermal transfer factor and � the total thermal transfer area of a tube
    (Tijk)
    [7] Heat exchanger (1) according to any of [1-6], where the distance (DL3jn) is the distance from the third edge or the fourth edge (9, 10) to the nearest tube (Tijk) of each series
    15 (Sj), this distance being preferably the minimum distance established by construction of the heat exchanger (1).
    [8] Heat exchanger (1) according to claim 7, wherein the parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj of said heat exchanger (1) meet
    20 the following expressions according to the width (B) and length (L) of the heat exchanger (1):
    � � �
    o = ∑ + ∑ ∑
    � � � �
    � = � � � �
    25 or ∑ 1 + 2, ∀ = 1,…, ∀ = 1,… ,, where
    o =,…, + ∑3, ∀ = 1,…, �
    [9] Heat exchanger (1) according to [8], where at least one of the parameterized distances 30 DTjf, DL1jfl, DL2jf, DL3jn and DGj maintains a constant value.
    [10] Heat exchanger (1) according to [8] or [9], where all DTjf parameterized distances are equal, all DGj parameterized distances between tubes (Tijk) are equal and the number (nFj) of rows (Fj) of each series (Sj) is the same, and the following is true


    expression:
    = (+ 1) + - 1�
    [11] Heat exchanger (1) according to any of [8-10], where all distances
    5 parameterized DL1jfl are equal, all parameterized distances DL3jn are equal, the number (nFj) of rows (Fj) of each series (Sj) is equal and the number (ncjf) of columns (Cj) of each series (Sj) is same, and where the following expression is fulfilled:
    = −11 + 2,…, + 23�
    10 [12] Heat exchanger (1) according to any of [2-11], wherein said heat exchanger (1) comprises:
    - two input collectors (5), and
    15-two outlet manifolds (6)
    where each of the coils (Ri) is alternately connected to a different inlet manifold (5) and a different outlet manifold (6), so that the working fluid path has a direction that alternates in each coil (Ri).
    [13] Heat exchanger (1) according to any of [1-12], where each tube (Tijk) is a circular tube with the same outside diameter ().
    [14] Wind tunnel (2) comprising at least one heat exchanger (1) according to any one of [1-13].
    [15] Method of regulating the temperature of an air flow inside a wind tunnel (2) comprising the following stages:
    30  provide at least one heat exchanger (1) according to any of [1-13],
     measure the temperature of the air flow inside the wind tunnel (2),


     regulate the temperature of the air flow by modifying the number of tubes (Tijk) of the heat exchanger (1) by means of closing means, or the working fluid conditions, or the parameterized distances DTjf, DL1jfl, DL2jf and DGj.
    [16] Design method to design a heat exchanger (1) for a wind tunnel
    (2) according to any of [7-13], which comprises the following stages:
    - define the dimensions of the heat exchanger (1), said dimensions being the width (B), the height (H) and the length (L),
    - determine the total effective heat transfer area (A) of the heat exchanger (1) required as well as the thermal transfer factor (Fm) and the total thermal transfer area (Atubo m) of each tube (Tijk),
    15 -determine the total number (N) of tubes (Tijk) of the heat exchanger (1) by the following expression:
    = ∑ �, 20 -determine the number of total (nS) of series (Sj), the total number (nFj) of rows (Fj) of each series (Sj), and the total number (nCjf) of columns (Cj) of each series (Sj),
    - determine the following parameters: 25
    or the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series (Sj),
    or the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different 30 columns (Cj) of the same series (Sj),
    or the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column (Cj), said column (Cj) being the closest to either the third edge (9) or the fourth edge (10) , with respect to the tube (Tijk) of the same series (Sj) more
    35 next to said third edge (9) or fourth edge (10),


    or distance (DGj),
    • between the closest tubes (Tijk) of adjacent series (Sj), or
    5 • between the tube (Tijk) closest to the first edge or the second edge (7,8) and said first edge or second edge (7, 8) of the heat exchangerheat (1),
    or the distance (DL3jn) from the third edge or fourth edge (9, 10) to the tube (Tijk) plus 10 next of each series (Sj)
    according to the following expressions:
    � � �
    o = ∑ + ∑ ∑
    � � � � �
    o = ∑1 + 2, ∀ = 1,…, ∀ = 1,…,
    �
    o =,…, + ∑3, ∀ = 1,…, �
    20 [17] Design method for designing a heat exchanger (1) according to [16], further comprising the step of determining the total number (nl) of coils (Ri), the number (g) of groups (Gj) and the number (ng) of tubes (Tijk) in each group (Gj), prior to the stage of determining the different parameters DTjf, DL1jfl, DL2jf, DL3jn and DGj.

    权利要求:
    Claims (15)
    [1]
    1. Heat exchanger (1) for wind tunnels (2), comprising:
    5-at least a first wall (3) and a second wall (4), each wall (3, 4) comprising at least a first edge (7), a second edge (8), a third edge (9) and a fourth edge (10),
    - a total number (N) of tubes (Tijk) adapted to contain a working fluid, 10 forming at least a plurality of said tubes (Tijk) at least one series (Sj), the total number (nS) of series (Sj) being ),
    - at least one inlet manifold (5) of the working fluid connected to a first end of at least one tube (Tijk), and 15 - at least one outlet manifold (6) of the working fluid connected to a second end of the minus a tube (Tijk),
    wherein the tubes (Tijk) of each series (Sj) form a plurality (nFj) of rows (Fj) and a plurality (ncjf) of columns (Cj) distributed according to the rows (Fj), and where:
    - the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series (Sj),
    - the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different columns (Cj) 25 of the same series (Sj),
    - the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column (Cj), said column (Cj) being the closest to either the third edge (9) or the fourth edge (10), with respect to the tube (Tijk) of the same series (Sj) closest to said
    30 third edge (9) or fourth edge (10),
    - the distance (DGj),
    or between the nearest tubes (Tijk) of adjacent series (Sj), or 35
    or between the tube (Tijk) closest to the first edge or the second edge (7, 8) and said first edge or second edge (7, 8) of the heat exchanger (1),
    They are parameterized so that: 40

    - distance (DL2jf)> 0, and
    - distance (DGj)> distance (DTjf),
    5 so that:
    - the parameterization relative to the rows (Fj) mainly optimizes the pressure loss of the heat exchanger (1), and
    10 -the parameterization related to the columns (Cj) mainly optimizes the total total effective transfer area of the heat exchanger (1).
    [2]
    2. Heat exchanger (1) according to claim 1, wherein at least two tubes (Tijk) are in fluidic communication, forming at least one coil (Ri).
    [3]
    3. Heat exchanger (1) according to claim 2, comprising a plurality (nl) of coils (Ri), wherein:
     each coil (Ri) comprises a plurality (g) of groups (Gj), and 20  each group (Gj) comprises a plurality (ng) of tubes (Tijk),
    where each series (Sj) is formed by the same group (Gj) of each coil (Ri), and where:
    25  the number (nFj) of rows (Fj) of each series (Sj) is the number of tubes (Tijk) comprising each group (Gj), and
     the number (ncjf) of columns (Cj) of each series (Sj) is the number of coils (Ri).
    [4]
    4. Heat exchanger (1) according to any of the preceding claims, wherein the total number of tubes (N) meets the expression:
    �
    = � �
    � �
    35. Heat exchanger (1) according to claim 3, wherein the total number of tubes
    (N) meets the expression:
    = .. �

    [6]
    6. Heat exchanger (1) according to any of the preceding claims, wherein the total number (N) of tubes (Tijk) of the heat exchanger (1) is obtained from the following relationship:
    5= ∑ �,
    where A is the total effective heat transfer area of the heat exchanger (1), � a thermal transfer factor and � the total thermal transfer area of a tube
    10 (Tijk).
    [7]
    7. Heat exchanger (1) according to any of the preceding claims, wherein the distance (DL3jn) is the distance from the third edge or the fourth edge (9, 10) to the nearest tube (Tijk) of each series (Sj), this distance being preferably the
    15 minimum distance established by construction of the heat exchanger (1).
    [8]
    8. Heat exchanger (1) according to claim 7, wherein the parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj of said heat exchanger (1) meet the following expressions according to width (B) and length (L) of the
    20 heat exchanger (1):
    � �
    o = ∑ + ∑ ∑
    � � � �
    �
    or ∑ 1 + 2, ∀ = 1,…, ∀ = 1,… ,, where
    = � � �
    o =,…, + ∑ 3, ∀ = 1,…,
    � �
    [9]
    9. Heat exchanger (1) according to claim 8, wherein at least one of the 30 parameterized distances DTjf, DL1jfl, DL2jf, DL3jn and DGj maintains a constant value.
    [10]
    10. Heat exchanger (1) according to claim 8 or 9, wherein all DTjf parameterized distances are equal, all DGj parameterized distances between tubes (Tijk) are equal and the number (nFj) of rows (Fj) of each series (Sj) is the same, and it is fulfilled
    35 the following expression:

    = (+ 1) + - 1�
    [11]
    11. Heat exchanger (1) according to any of claims 8 to 10, wherein all the parameterized distances DL1jfl are equal, all distances
    5 parameterized DL3jn are equal, the number (nFj) of rows (Fj) of each series (Sj) is equal and the number (ncjf) of columns (Cj) of each series (Sj) is the same, and where the following is true expression:
    = −11 + 2,…, + 23�
    12. Heat exchanger (1) according to any of claims 2 to 11, wherein said heat exchanger (1) comprises:
    - two input collectors (5), and
    15-two outlet manifolds (6)
    where each of the coils (Ri) is alternately connected to a different inlet manifold (5) and a different outlet manifold (6), so that the working fluid path has a direction that alternates in each coil (Ri).
    [13]
    13. Heat exchanger (1) according to any of the preceding claims, wherein each tube (Tijk) is a circular tube with the same outer diameter ().
    [14]
    14. Wind tunnel (2) comprising at least one heat exchanger (1) according to any one of the preceding claims.
    [15]
    15. Method of temperature regulation of an air flow inside a wind tunnel (2) comprising the following stages:
    30  providing at least one heat exchanger (1) according to any one of claims 1 to 13,
     measure the temperature of the air flow inside the wind tunnel (2),
    35  regulate the temperature of the air flow by changing the number of tubes (Tijk) of the heat exchanger (1) by means of closing means, or

    working fluid conditions, or the parameterized distances DTjf, DL1jfl, DL2jf and DGj.
    [16]
    16. Design method to design a heat exchanger (1) for a wind tunnel
    5 (2) according to any of claims 7 to 13, comprising the followingstages:
    - define the dimensions of the heat exchanger (1), said dimensions being the width (B), the height (H) and the length (L), 10
    - determine the total effective heat transfer area (A) of the heat exchanger (1) required as well as the thermal transfer factor (Fm) and the total thermal transfer area (Atubo m) of each tube (Tijk),
    15 -determine the total number (N) of tubes (Tijk) of the heat exchanger (1) by the following expression:
    ,
    = ∑ �
    20 -determine the number of total (nS) of series (Sj), the total number (nFj) of rows (Fj) of each series (Sj), and the total number (nCjf) of columns (Cj) of each series ( Sj),
    - determine the following parameters:
    25 or the distance (DTjf) between tubes (Tijk) of different rows (Fj) of the same series (Sj),
    or the distance (DL1jfl) between tubes (Tijk) of the same row (Fj) and of different
    columns (Cj) of the same series (Sj), 30
    or the distance (DL2jf) between tubes (Tijk) of different rows (Fj) and the same column (Cj), said column (Cj) being the closest to either the third edge (9) or the fourth edge (10) , with respect to the tube (Tijk) of the same series (Sj) closest to said third edge (9) or fourth edge (10),
    or distance (DGj),

    • between the closest tubes (Tijk) of adjacent series (Sj), or
    • between the tube (Tijk) closest to the first edge or the second edge (7,
    8) and said first edge or second edge (7, 8) of the heat exchanger (1),
    or the distance (DL3jn) from the third or fourth edge (9, 10) to the nearest tube (Tijk) of each series (Sj)
    10 according to the following expressions:
    � � �
    o = ∑ + ∑ ∑
    � � � �
    �
    o = ∑ 1 + 2, ∀ = 1,…, y∀j = 1,…, n
    � � �
    or L = maxL, ..., + ∑DL3, ∀j = 1,…, n�
    [17]
    17. Design method for designing a heat exchanger (1) according to claim 16, further comprising the step of determining the total number (nl) of
    20 coils (Ri), the number (g) of groups (Gj) and the number (ng) of tubes (Tijk) in each group (Gj), prior to the stage of determining the different parameters DTjf, DL1jfl, DL2jf, DL3jn and DGj.

    DRAWINGS







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    引用文献:
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    SE423151B|1977-11-16|1982-04-13|Stal Laval Apparat Ab|HEAD EXCHANGER WITH ROADLINGER BETWEEN BERWEGGAR|
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    WO2012051525A2|2010-10-14|2012-04-19|William Robert Martindale|High efficiency cascade-style heat exchanger|
    FI126014B|2014-03-04|2016-05-31|Uponor Infra Oy|Heat exchanger for low temperatures|
    EP2995898A3|2014-09-12|2016-05-11|Solex Thermal Science Inc.|Heat exchanger for heating bulk solids|
    DE202014105709U1|2014-11-26|2016-02-29|Akg Thermotechnik International Gmbh & Co. Kg|heat exchangers|CN109945716B|2019-03-25|2019-11-12|中国空气动力研究与发展中心超高速空气动力研究所|A kind of high-temperature cooler supporting device for heat exchange tube bundle|
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    PCT/EP2016/059622|WO2016174209A1|2015-04-30|2016-04-29|Exchanger for a wind tunnel|
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