JP6233835B2 - Thermoacoustic engine and manufacturing method thereof - Google Patents

Description

  The present invention relates to a thermoacoustic engine for amplifying the acoustic power and acoustic power density of a working gas and a method for manufacturing the same.

  In recent years, global warming and energy problems have become serious. If huge waste heat generated in factories and vehicles and solar energy can be recovered with high efficiency, it will be a trump card for solving global warming and energy problems. Therefore, research on thermoacoustic engines has been actively conducted in order to recover these energies and drive them (for example, see Non-Patent Documents 1 and 2).

  Currently, thermoacoustic engines are being researched by many companies from the viewpoint of heat recovery and next-generation energy utilization. However, since this is a new field where full-fledged research has begun in the 21st century, there is a situation where basic technology has not yet been established.

  That is, if a plurality of heat accumulators can be connected while maintaining a high impedance at the heat accumulator position, a multistage thermoacoustic engine that can achieve both high efficiency and acoustic power amplification at a small temperature ratio can be realized. As this multistage thermoacoustic engine, the combination of the upstream side resonance tube, the room temperature heat exchanger, the heat accumulator, the high temperature heat exchanger and the downstream side resonance tube is considered as one unit, and the cross section of the heat accumulator with respect to the upstream side resonance tube A technique has been proposed in which a plurality of units are connected while expanding and increasing the cross-sectional area of the downstream resonance tube (see, for example, Non-Patent Document 3).

S. Backhaus, E. Tward and M. Petach, Appl. Phys. Lett., Vol. 85, No. 6, pp. 1085-1087 (2004) M. Miwa, T. Sumi, T. Biwa, Y. Ueda and T. Yazaki, Ultrasonics, 44, e1527-e1529 (2006) S. Hasegawa et al., TEION KOGAKU 47, 11-15 (2012)

  However, in the conventional multistage thermoacoustic engine, the acoustic power is amplified for each connected unit. However, since the cross-sectional area of the downstream resonance tube is enlarged, the acoustic power density cannot be increased. If the acoustic power density can be increased for each connected unit in a multistage thermoacoustic engine, a large acoustic power can be transmitted with traveling waves or sound waves close to traveling waves.

  Then, this invention makes it a subject to provide the thermoacoustic engine which increases the acoustic power density, and its manufacturing method while realizing the high impedance in a heat | energy storage position.

In view of the above-described problems, a thermoacoustic engine according to the present invention includes a regenerator that heats and cools working gas, a heater that is adjacent to one end of the regenerator, and heats one end of the regenerator, A cooler that is adjacent to the other end of the heat accumulator and discharges heat from the other end of the heat accumulator to the outside; and a resonance tube that is connected to the heater and the cooler respectively and is filled with the working gas. the provided, the prime mover to amplify the sound power and the acoustic power density of the working gas to form a temperature gradient between the ends of the heat accumulator is a multiple connected thermoacoustic engine in series, hereinafter formula (1 ) To Equation (7) to obtain the transfer matrix M _all of the thermoacoustic engine, and to obtain the acoustic power amplification factor G from the transfer matrix M _all using Equation (8) and Equation (9) to be described later. The length of the resonance tube is the calculated acoustic parameter. Over the amplification factor G is characterized in that it is set to be maximum.

According to such a configuration, the thermoacoustic engine increases the acoustic power density for each prime mover connected in series by setting the length of the resonance tube described above, and a large acoustic power is close to a traveling wave or traveling wave. Can be transmitted with sound waves.
Furthermore, the thermoacoustic engine can easily set the length of the resonance tube that maximizes the acoustic power amplification factor G using a calculation model in which the thermoacoustic differential equation derived by Rott is developed.

In the thermoacoustic engine according to the present invention, it is preferable that the plurality of connected prime movers have the same length and cross-sectional area of the resonance tube.
According to such a configuration, since all the resonance tubes are the same for each prime mover, the thermoacoustic engine can easily perform impedance matching at the connection point of the prime movers.

Further, the thermoacoustic engine according to the present invention is connected to one end of the plurality of prime movers, the input unit for inputting an input sound wave for amplifying the acoustic power and acoustic power density of the working gas, and the plurality of connected prime movers. It is preferable to further include an output unit that outputs amplified amplified sound waves from the other end of the prime mover.

In the thermoacoustic engine according to the present invention, it is preferable that the input unit is a motor loop that generates the input sound wave, and the output unit is a generator that generates power in response to the amplified sound wave.
According to this configuration, since the amplified acoustic power and acoustic power density of the working gas are converted into electric power by the generator, the thermoacoustic generator can be driven with higher efficiency.

  In the thermoacoustic engine according to the present invention, the input unit is a prime mover loop that generates the input sound wave, and the output unit is a cooling loop that performs cooling in response to the amplified sound wave or a temperature increase that performs temperature rise. Preferably either one of the warm loops.

  According to such a configuration, the amplified acoustic power and acoustic power density of the working gas are converted into heat flow in the cooling loop or the temperature raising loop. Therefore, the thermoacoustic engine can be driven with higher efficiency as a thermoacoustic cooler or a thermoacoustic heater.

Moreover, in view of the above-mentioned subject, the manufacturing method of the thermoacoustic engine which concerns on this invention uses the transfer matrix calculation process of calculating _| requiring the transfer matrix _Mall of the said thermoacoustic engine using Formula (1)-Formula (7), Using the equation (8), the eigenvalue calculation step for obtaining the eigenvalue λ of the transfer matrix M _{all and} the eigenvalue λ obtained in the eigenvalue calculation step are substituted into the equation (9), and the acoustic power gain G is calculated. A desired acoustic power gain calculation step, and a resonance tube length setting step for setting the length of the resonance tube so that the acoustic power gain G obtained in the acoustic power gain calculation step is maximized. It is characterized by.
According to this manufacturing method, the length of the resonance tube that maximizes the acoustic power gain G can be easily set using a calculation model in which the thermoacoustic differential equation derived by Rott is developed.

  According to the present invention, by setting the length of the resonance tube described above, it is possible to realize high impedance at the heat accumulator position and increase the acoustic power density, and to generate a large acoustic power as a traveling wave or traveling wave. Can be transmitted with sound waves close to.

It is a schematic diagram which shows typically the structure of the thermoacoustic engine which concerns on 1st Embodiment of this invention. It is a schematic diagram which shows typically the structure which provided the buffer tank in the thermoacoustic engine of FIG. In 1st Embodiment, it is explanatory drawing explaining the setting of the resonance tube length. In 1st Embodiment, it is explanatory drawing explaining the setting of the resonance tube length. In 1st Embodiment, it is explanatory drawing explaining the amount of input heat. It is a flowchart which shows the manufacturing method of the thermoacoustic engine of FIG. It is a schematic diagram which shows typically the structure of the thermoacoustic engine which concerns on 2nd Embodiment of this invention. It is a schematic diagram which shows typically the structure of the thermoacoustic engine which concerns on 3rd Embodiment of this invention. In 4th Embodiment of this invention, it is a schematic diagram which shows typically the usage example of a thermoacoustic engine. In Example 1 of this invention, it is a table which shows the specification regarding a resonance tube, a thermal accumulator, a heater, and a cooler. In Example 1 of this invention, it is a graph which shows the relationship between an acoustic power gain, a resonance tube length, and unit efficiency. In Example 1 of this invention, it is a graph which shows normalized sound power distribution. In Example 1 of this invention, it is a graph which shows normalized sound power density distribution. In Example 2 of this invention, it is a table which shows the specification regarding a resonance tube, a thermal accumulator, a heater, and a cooler. In Example 2 of this invention, it is a graph which shows the relationship between an acoustic power gain, a resonance tube length, and unit efficiency. In Example 2 of this invention, it is a graph which shows normalized sound power distribution. In Example 2 of this invention, it is a graph which shows normalized sound power density distribution. In Example 3 of this invention, it is a table which shows the specification regarding a resonance tube, a thermal accumulator, a heater, and a cooler. In Example 3 of this invention, it is a graph which shows the relationship between acoustic power gain, resonance tube length, and unit efficiency. In Example 3 of this invention, it is a graph which shows normalized sound power distribution. In Example 3 of this invention, it is a graph which shows normalized sound power density distribution.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. In each embodiment, the same member is denoted by the same reference numeral, and the description thereof is omitted.

(First embodiment)
<Configuration of thermoacoustic engine>
With reference to FIG. 1, the structure of the thermoacoustic engine 1 which concerns on 1st Embodiment of this invention is demonstrated.
As shown in FIG. 1, the thermoacoustic engine 1 is a straight thermoacoustic engine in which two prime movers 10 (10 ₁ , 10 ₂ ) are connected in series.

[Motor]
The prime mover 10 amplifies the acoustic power and acoustic power density of the working gas by forming a temperature gradient between both ends of the regenerator 12, and the two resonance tubes 11 (11 a and 11 b) and the regenerator 12. And a heater 13 and a cooler 14. That is, the prime mover 10 handles the resonance tubes 11a and 11b, the heat accumulator 12, the heater 13, and the cooler 14 as one unit. Here, in the prime mover 10, the heater 13 is disposed on one end side of the regenerator 12 so that both ends of the regenerator 12 are sandwiched, and the cooler 14 is disposed on the opposite side, that is, the other end side of the regenerator 12. ing.
In Figure 1, illustrates the sound waves input from the outside to the motor 10 ₁ and wave input, thermoacoustic engine 1 is shown a sound wave and outputting the amplified sound waves output.

[Resonance tube]
The resonance tube 11 is a linear cylindrical tube filled with a working gas, and has a predetermined resonance tube length L and a cross-sectional area. Here, the resonance tube 11 a is connected to the cooler 14, and the resonance tube 11 b is connected to the heater 13. Moreover, resonance tube 11b of the engine 10 _1, the side that is not connected to the heater 13 is connected to the side that is not connected to the cooler 14 in the resonance tube 11a of the motor 10 _2. In addition, the resonance tube 11 has a resonance tube length L such that an acoustic power amplification factor described later is not less than a value obtained by multiplying the ratio of the heater temperature and the cooler temperature by a value of 0.7 or more and 1.0 or less. Is set. Details of the setting of the resonance tube length L will be described later.
As the working gas, nitrogen, helium, argon, a mixture of helium and argon, air, or the like is often used.
Here, the case of using atmospheric air as working gas, may open one end of the resonance tube 11a of the engine 10 _1. As shown in FIG. 2, a buffer tank 16 that encloses working gas may be provided at one end of the resonance tube 11a. That is, when the buffer tank 16 is provided, the working gas is filled and filled in the resonance tube 11, and when one end of the resonance tube 11a is opened, it is filled with atmospheric air.
In FIG. 2 and subsequent figures, part of the reference numerals is omitted for easy understanding of the drawings.

[Regenerator]
The heat accumulator 12 is provided in a pipe line of the resonance tube 11 and heats and cools the working gas. That is, the heat accumulator 12 forms a temperature gradient between both ends of the heat accumulator 12 by the heater 13 and the cooler 14, and amplifies the acoustic power and the acoustic power density of the working gas. The heat accumulator 12 is mainly a working gas by maintaining a temperature difference generated between one end thereof (hereinafter appropriately referred to as a high temperature portion 12b) and the other end portion (hereinafter appropriately referred to as a normal temperature portion 12a). Has a function of amplifying the sound power and sound power density. The heat accumulator 12 includes, for example, a ceramic honeycomb structure having a large number of parallel passages in the extending direction (pipeline direction) of the resonance tube 11 and a structure in which a large number of stainless steel mesh thin plates are laminated at a fine pitch. can do. Alternatively, a non-woven fabric made of metal fibers or the like can be used as the heat accumulator 12.

[Heater]
The heater (high temperature heat exchanger) 13 is provided adjacent to one end of the heat accumulator 12 in the pipe of the resonance tube 11 and heats one end of the heat accumulator 12 (high temperature portion 12b). That is, the heater 13 functions as a heat input unit that heats one end of the heat accumulator 12 using external heat. The heater 13 is composed of a heat exchanger for heating, for example. Specifically, the heater 13 has a configuration in which a large number of metal plates such as mesh plates are stacked at a fine pitch. A heating device (not shown) is connected to the heater 13 and is configured to be heated through an annular member 13a (FIG. 3) provided on the outer periphery thereof. In the drawing, for the sake of convenience, the left wall of the annular member 13a is shown between the regenerator 12 and the heater 13, but the heater 13 is adjacent to, in close contact with, one end side of the regenerator 12 through this left wall. ing.

[Cooler]
The cooler 14 is provided in the pipe line of the resonance tube 11 adjacent to the other end side of the heat accumulator 12, and discharges heat of the other end portion (normal temperature portion 12a) of the heat accumulator 12 to the outside. That is, the cooler 14 has a function of cooling by discharging heat from the other end of the heat accumulator 12 to the outside using cooling water, air, or the like. The cooler 14 is composed of a heat exchanger for cooling, for example. The cooler 14 basically has the same configuration as that of the heater 13. For example, a plurality of metal plates such as mesh plates are stacked at a minute pitch. The cooler 14 is provided with a cooling bracket 14a (FIG. 3) around it. A cooling water channel (not shown) is connected to the cooling bracket 14a, and the cooler 14 is configured to be able to maintain a constant cooling temperature via the cooling bracket 14a by the cooling water flowing through the cooling water channel. In the drawing, for convenience, the right wall of the cooling bracket 14a is shown between the regenerator 12 and the cooler 14, but the cooler 14 is adjacent to the other end of the regenerator 12 through this right wall, that is, in close contact. doing.

[Resonance tube length setting]
The setting of the resonance tube length L will be described in detail with reference to FIGS. 3 and 4 (see FIG. 1 as appropriate).
First, specifications other than the resonance tube length L are determined. Specifically, the diameter, the aperture ratio, and the flow path diameter are determined for the resonance tubes 11a and 11b included in each prime mover 10. Further, the length, diameter, opening ratio, and flow path diameter are determined for the regenerator 12, the heater 13, and the cooler 14 included in each prime mover 10. Moreover, about each motor | power_engine 10, a heater temperature and a cooler temperature are determined. Here, the heater temperature represents the temperature of the heater 13 included in each prime mover 10. The cooler temperature represents the temperature of the cooler 14 included in each prime mover 10. Also, the operating frequency, type and average pressure are determined for the working gas. Thereby, the elements of the transfer matrix other than the resonance tube length L are determined.

Subsequently, the transfer matrix M _all of the thermoacoustic engine 1 is obtained using the following calculation model. This calculation model is based on the thermoacoustic differential equation derived by Rott. The Rott thermoacoustic differential equation is described in detail in, for example, the document “N. Rott, Z. Angelw. Math. Phys. 20, pp. 230-243, 1969”. It is represented by (2).

Here, p is the pressure amplitude, U sectional average volumetric flow rate amplitude, j is the imaginary unit, omega is the angular frequency, A _C is the cross-sectional area of the resonance tube 11, the average pressure of p _m is the working gas, gamma is the specific heat ratio, ν is the kinematic viscosity coefficient, σ is the Prandtl number, T _m is the average temperature of the working gas inside the resonance tube 11, and α is the thermal diffusion coefficient.

Note that the temperature gradient dT _m / dx of the regenerator 12 is not constant. In the present embodiment, the temperature gradient dT _m / dx is set by performing iteration (repetitive calculation) on the condition that the enthalpy flow is constant in the regenerator 12.

Further, χ _α and χ _ν are complex functions depending on the temperature diffusion coefficient and the kinematic viscosity coefficient. χ _α and χ _ν can be expressed by the following equation (3) when the resonance tube 11 has a circular cross section.

Here, J ₀ and J ₁ are the 0th and 1st orders of the Bessel function, r is the radius of the resonance tube 11, and τ _α and τ _ν are the thermal relaxation time and the kinematic viscosity relaxation time. Also, using p (x), U (x) at point x, and p (0), U (0) at the point where x = 0, the solution of equation (1) is expressed by the following equation (4) ) And formula (5).

Here, e is the number of Napiers. By connecting Equation (4) with given elements, the entire sound field can be obtained. Here, as shown in FIG. 3, for each prime mover 10, the end of the resonance tube 11 a connected to the cooler 14 is a start point a, and the end of the resonance tube 11 b connected to the heater 13 is an end point b. The pressure amplitude at the start point a p _a, the cross-sectional average volumetric flow rate amplitude at the start a and U _a. Further, the pressure amplitude at the end point b is p _b , and the cross-sectional average volume flow velocity amplitude at the end point b is U _b . In this case, the relationship between the start point a and the end point b can be expressed by the following equation (6) using a transfer matrix.

Here, B _a is a transfer matrix of the resonance tube 11 a connected to the cooler 14, B _AHX is a transfer matrix of the cooler 14, B _reg is a transfer matrix of the regenerator 12, B _HHX is a transfer matrix of the heater 13, B _b is a transmission matrix of the resonance tube 11 b connected to the heater 13.

As shown in FIG. 4, impedance matching at the connection point is important for connecting the _two prime movers 10 ₁ and 10 ₂ . That, Z = a p / v, find specific acoustic impedance _{Z l} and specific acoustic impedance _{Z 2} and is equal condition of the prime mover 10 _{and second} prime mover 10 _1. Therefore, attention is paid to the eigenvalue λ of the transfer matrix M _all satisfying the following expressions (7) and (8).

Here, a cross-sectional average velocity amplitude at A _a cross-sectional area at the starting point a, the cross-sectional area at A _b is the end point b, v _a cross-sectional average flow rate amplitude at the start point a, v _b end point b. In this case, the specific acoustic impedance of the start point a and an end point b is, assuming specific acoustic impedance _{Z = p a / v a =} p b / v b, it can be determined by the transfer matrix _{M all.}

The eigenvalues and eigenvectors depend on the matrix elements. When the specific acoustic impedance Z determined by the ratio of the elements of the eigenvector is close to ρ _m c (ρ _m is the average density of the working gas and c is the speed of sound), it means that it is close to traveling wave sound waves. Although there are two eigenvectors of the transfer matrix M _all , in this embodiment, it is assumed that the sound wave travels in the positive direction, and the specific acoustic impedance Z in which the real part is positive and the corresponding eigenvalue λ are used. The relationship between the eigenvalue λ and the sound power gain G can be expressed by the following equation (9). The sound power amplification factor G is the ratio of the sound power at the end point b to the sound power at the start point a.

Here, “˜” is a complex conjugate. Further, since the resonance tubes 11a and 11b have the same diameter, A _a = A _b is established, and therefore, the equation (9) can be expressed by the following equation (10).

Therefore, the acoustic power amplification factor G can be obtained by substituting the eigenvalue λ of the transfer matrix M _all into Equation (10). The resonance tube length L is set so that the acoustic power gain G is maximized.

With reference to FIG. 5, the relationship of the heat input to the prime movers 10 ₁ and 10 ₂ in the thermoacoustic engine 1 will be described. Here, the input amount of heat to the motor 10 ₁ and _{Q l,} the input amount of heat to the prime mover 10 ₂ and _{Q 2.} In addition, the acoustic power amplification factor of the prime mover 10 ₁ (resonance tube 11a to resonance tube 11b) is G _1, and the acoustic power amplification factor of the prime mover 10 ₂ (resonance tube 11a to resonance tube 11b) is G ₂ . If the prime movers 10 ₁ and 10 ₂ have the same configuration, the relationship between the input heat amounts Q ₁ and Q ₂ can be expressed by the following equation (11).

[Method of manufacturing thermoacoustic engine]
With reference to FIG. 6, as a manufacturing method of the thermoacoustic engine 1, a procedure for setting the resonance tube length L will be described (see FIG. 1 as appropriate).

First, in the manufacturing method of the thermoacoustic engine 1, specifications other than the resonance tube length L are determined (step S1).
Next, in the manufacturing method of the thermoacoustic engine 1, the transfer matrix M _all of the thermoacoustic engine 1 is obtained using the equations (1) to (7) (step S2: transfer matrix calculation step).

Next, in the manufacturing method of the thermoacoustic engine 1, the eigenvalue λ of the transfer matrix M _all is obtained using the equation (8) (step S3: eigenvalue calculation step).
Next, in the method for manufacturing the thermoacoustic engine 1, the eigenvalue λ obtained in the eigenvalue calculation step S3 is substituted into the equation (10) to obtain the acoustic power amplification factor G (step S4: acoustic power amplification factor calculation step).

  Next, in the manufacturing method of the thermoacoustic engine 1, the resonance tube length L is set so that the acoustic power amplification factor G obtained in the acoustic power amplification factor calculation step S4 is maximized (step S5: resonance tube length setting step). ).

[Action / Effect]
As described above, the thermoacoustic engine 1 uses the calculation model obtained by developing the thermoacoustic differential equation derived by Rott (Equation (1) to Equation (10)), and the resonance tube length at which the acoustic power amplification factor G is maximized. The length L can be easily set. As a result, the thermoacoustic engine 1 can achieve high impedance at the position of the regenerator 12 and increase the acoustic power density to transmit a large acoustic power with traveling waves or sound waves close to traveling waves. Furthermore, since the thermoacoustic engine 1 has the same configuration in which all the resonance tubes 11 included in each prime mover 10 have the same length and the same cross-sectional area, impedance matching at the connection point of each prime mover 10 can be easily performed.

(Second Embodiment)
<Configuration of thermoacoustic generator>
With reference to FIG. 7, differences from the first embodiment will be described regarding the configuration of the thermoacoustic engine 1 </ b> A according to the second embodiment of the present invention (see FIG. 1 as appropriate).
As shown in FIG. 7, the thermoacoustic engine 1 </ b> A is a thermoacoustic generator including the thermoacoustic engine 1 of FIG. 1, a motor loop (input unit) 20, and a generator (output unit) 30. Different from the first embodiment.

[Motor loop]
Motor loop 20 is provided is intended to enter the input waves for amplifying the acoustic power and acoustic power density motor 10 _1, the loop pipe 21, a regenerator 22, and heater 23, a cooler 24 .

The prime mover loop pipe 21 is an annular pipe filled with a working gas, and the pipe line is formed in a rounded quadrangular shape and includes straight pipe portions 21a to 21d that form straight portions corresponding to four sides. That is, the prime mover loop pipe 21 has two straight pipe portions 21a and 21b arranged substantially parallel to the vertical direction and two straight pipe portions 21c and 21d arranged substantially parallel to the horizontal direction. . The motor loop pipe 21 includes one end of the straight pipe portion 21a and one end of the straight pipe portion 21c, one end of the straight pipe portion 21b and the other end of the straight pipe portion 21c, and the other end of the straight pipe portion 21b and the straight pipe portion 21d. Are connected at one end and curved at this site. Moreover, the prime mover for the loop pipe 21, together with the other ends of the straight pipe portion 21d of the straight pipe portion 21a is connected, at the branch site connected to the resonance tube 11 of the motor 10 _1. The branched portion is curved on the upper side, but may be formed at a right angle.

That is, the prime mover for the loop pipe 21, the operating gas in the resonance tube 11a of the engine 10 ₁ are connected by Tsudo state. The boundary between the resonance pipes 11a and motor loop pipe 21 of the engine 10 _1, the length of the resonance tube 11a may, if a position equal to or higher than the resonance tube length L. In Figure 7, the boundary between the resonance pipes 11a and motor loop pipe 21 of the engine 10 ₁ shown with reference numeral A1.

Since the heat accumulator 22, the heater 23, and the cooler 24 are the same as the heat accumulator 12, the heater 13, and the cooler 14 except that they are provided in the loop tube 21, detailed description thereof is omitted. The regenerator 22, the heater 23, and the cooler 24 can determine their sizes (length, diameter, opening ratio, flow path diameter) independently of the prime movers 10 ₁ and 10 ₂ .

[Generator]
Generator 30 is connected to the other end of the resonance tube 11b of the engine 10 _2, functions as a linear electric generator for generating electric power in response to amplified sound waves amplified by the prime mover 10. In other words, the generator 30 reciprocally vibrates the inner yoke 33 based on the acoustic power to convert the acoustic power into electric power.

Generator 30 is provided coupled to the other end of the resonance tube 11b of the engine 10 _2, the resonance tube 11 and the pressure vessel 39 for receiving internal pressure variation corresponding to the pressure fluctuation generated inside the loop pipe 21. Inside the pressure vessel 39, outer yokes (cylinders) 31, 31, coils 32 and 32 accommodated in the outer yokes 31 and 31, and an inner yoke (cylinder) 33 positioned between the outer yokes 31 and 31, respectively. Permanent magnets 34, 34 provided between the outer yokes 31, 31 and the inner yoke 33, respectively. The permanent magnets 34 and 34 are composed of S-pole and N-pole magnets, respectively.

  Such a structure in the generator 30 employs a power generation method based on the principle that a current is generated by a change in magnetic flux density that circulates around the coils 32 and 32 with time. That is, when the inner yoke 33 strokes based on the acoustic power, the magnetic flux density that circulates around the coils 32 and 32 greatly changes, and power generation is performed. Further, by attaching the projection 33a to the inner yoke 33, it is possible to suppress a decrease in magnetic flux density due to the magnetic flux passing through the air gap.

Note that the generator 30 is operating gas in the resonance tube 11b of the motor 10 ₂ are connected by Tsudo state. The boundary between the resonance tube 11b of the engine 10 ₂ and the generator 30, the length of the resonance tube 11b may be any position where the above resonance tube length L. In Figure 7, the boundary between the resonance tube 11b of the engine 10 ₂ and the generator 30 illustrated by reference numeral A2.

<Operation of thermoacoustic generator>
First, in the motor loop 20, the thermoacoustic engine 1 </ b> A heats the high temperature portion 22 b of the regenerator 22 by the heater 23 and cools the normal temperature portion 22 a of the regenerator 22 by the cooler 24. That is, a temperature difference is generated between the high temperature part 22b and the normal temperature part 22a. Due to this temperature difference, acoustic power of the working gas is mainly generated in the prime mover loop 20 (specifically, the heat accumulator 22). The acoustic power of the working gas generated in the prime mover loop 20 passes through the straight pipe portions 21a, 21c, 21b, and 21d of the loop pipe 21 in order as input sound waves and is transmitted to the prime movers 10 ₁ and 10 ₂ .

In the prime movers 10 ₁ and 10 ₂ , the acoustic power and the acoustic power density are amplified. At this time, since the resonance tube length L is set so that the acoustic power amplification factor G is maximized, the thermoacoustic engine 1A realizes a high impedance at the position of the heat accumulator 12 and increases the acoustic power density. be able to. As a result, the thermoacoustic engine 1A is transmitted with a large acoustic power to the generator 30, and the inner yoke 33 is reciprocally vibrated based on this acoustic power, whereby the acoustic power is converted into electric power and electric power is generated.

<Action and effect>
As described above, the thermoacoustic engine 1A has an advantage that there is no fundamental conversion loss or friction loss due to the conversion mechanism in addition to the same effects as those of the first embodiment, and expects miniaturization and high efficiency. be able to.

(Third embodiment)
<Configuration of thermoacoustic cooler>
With reference to FIG. 8, a different point from 2nd Embodiment is demonstrated about the structure of the thermoacoustic engine 1B which concerns on 3rd Embodiment of this invention (refer FIG. 7 suitably).
As shown in FIG. 8, the thermoacoustic engine 1B is different from the second embodiment in that the thermoacoustic engine 1B is a thermoacoustic cooler including a cooling loop (output unit) 40 instead of the generator 30 of FIG.

  The cooling loop 40 performs cooling in response to the acoustic power (amplified sound wave) amplified by the prime mover 10, and includes a refrigeration loop tube 41, a refrigeration regenerator 42, a refrigeration cooler 43, And an emitter 44.

[Freezing loop tube]
The refrigeration loop pipe 41 is an annular pipe in which working gas is enclosed, and the pipe path is formed of a rounded quadrangle and includes straight pipe portions 41a to 41d that form straight portions corresponding to the four sides. That is, the freezing loop pipe 41 includes two straight pipe parts 41a and 41b arranged substantially in parallel in the vertical direction to form straight parts corresponding to the four sides, and two straight pipe parts 41c arranged substantially in parallel in the horizontal direction. , 41d. The freezing loop pipe 41 includes one end of the straight pipe portion 41a and one end of the straight pipe portion 41c, one end of the straight pipe portion 41b and the other end of the straight pipe portion 41c, and the other end of the straight pipe portion 41b and the straight pipe portion 41d. Are connected at one end and curved at this site. Further, the refrigeration loop pipe 41, together with the other ends of the straight pipe portion 41d of the straight pipe portion 41a is connected, at the branch site connected to the resonance tube 11b of the engine 10 _2. The branched portion is curved on the upper side, but may be formed at a right angle.

That is, the refrigeration loop pipe 41, the operating gas in the resonance tube 11b of the motor 10 ₂ are connected by Tsudo state. The boundary between the resonance tube 11b of the engine 10 ₂ and the freezing loop pipe 41, the length of the resonance tube 11b may be any position where the above resonance tube length L. In Figure 8, the boundary between the resonance tube 11b of the engine 10 ₂ and the freezing loop pipe 41 shown as a code A3.

[Refrigerator for refrigerating]
The refrigerating regenerator 42 is provided in the pipe line of the freezing loop pipe 41 and cools the working gas. In other words, refrigerating heat accumulator 42, the motor 10 _2, resonance pipes 11b, the straight tube portion 41d of the refrigeration loop pipe 41, 41b, 41c, one end portion of the refrigeration for the heat accumulator 42 through the tubes in the order of 41a (hereinafter The acoustic power transmitted to the room temperature unit 42a is appropriately referred to as one end portion (room temperature portion 42a) of the refrigerating regenerator 42 and the other end portion of the refrigerating heat accumulator 42 (hereinafter appropriately referred to as the low temperature portion 42b). It has a function of converting to a temperature difference between. Since the normal temperature part 42a of the refrigerating regenerator 42 is cooled by the refrigerating cooler 43, the low temperature part 42b of the refrigerating regenerator 42 is cooled to a temperature lower than the normal temperature part 42a by the transmitted acoustic power. Cold air is generated. This cold air is taken out by the cold air discharger 44. The refrigerating regenerator 42 is made of a regenerator material having a large heat capacity. As the regenerator material, for example, stainless steel, copper, lead or the like can be used, and various shapes can be applied to the refrigerating regenerator 42.

[Refrigerator for refrigeration]
The refrigeration cooler 43 is provided in the pipe line of the refrigeration loop pipe 41 adjacent to one end side of the refrigeration heat accumulator 42, and releases heat from one end (normal temperature part 42a) of the refrigeration heat accumulator 42 to the outside. To do. In other words, the refrigeration cooler 43 has a function of releasing and cooling the heat at one end of the refrigeration regenerator 42 using cooling water, air, or the like. The refrigeration cooler 43 is composed of, for example, a cooling heat exchanger. Specifically, the refrigeration cooler 43 has a configuration in which a large number of metal plates such as mesh plates are laminated at a minute pitch. The refrigeration cooler 43 is provided with a cooling bracket 43a around it. A cooling water channel (not shown) is connected to the cooling bracket 43a, and the refrigeration cooler 43 can maintain a constant cooling temperature via the cooling bracket 43a by the cooling water flowing through the cooling water channel. In the drawing, for convenience, the lower wall of the cooling bracket 43a is shown between the refrigerating regenerator 42 and the refrigerating cooler 43. However, the refrigerating cooler 43 is connected to the refrigerating regenerator 42 through the lower wall. Adjacent to one end side, that is, in close contact.

[Cold air discharger]
The cool air discharger 44 is provided adjacent to the other end of the refrigerating regenerator 42 in the pipe line of the refrigerating loop pipe 41, and generates cool air generated at the other end (low temperature part 42b) of the refrigerating regenerator 42. It will be released to the outside. That is, the cold air discharger 44 functions as a cold air output unit that extracts the cold air generated at the other end of the refrigerating regenerator 42 to the outside. The cool air discharger 44 is constituted by a heat exchanger for freezing, for example. The cool air discharger 44 basically has the same configuration as the refrigeration cooler 43. For example, a large number of metal plates such as mesh plates are stacked at a minute pitch. An annular member 44 a made of a high thermal conductivity material (for example, copper) for extracting cold air (cold heat) is disposed at the outer peripheral position of the cold air discharger 44. In the drawing, for convenience, the upper wall of the annular member 44a is shown between the refrigerating regenerator 42 and the cold air discharger 44. The cold air discharger 44 is connected to the other end of the freezing regenerator 42 through this upper wall. Adjacent to, ie in close contact with, the side.

<Operation of thermoacoustic cooler>
In the thermoacoustic engine 1B, like the thermoacoustic engine 1A, the acoustic power of the working gas is mainly generated in the prime mover loop 20 (specifically, the heat accumulator 22). The acoustic power of the working gas generated in the prime mover loop 20 passes through the straight pipe portions 21a, 21c, 21b, and 21d of the loop pipe 21 in order as input sound waves and is transmitted to the prime movers 10 ₁ and 10 ₂ .

In the prime movers 10 ₁ and 10 ₂ , the acoustic power and the acoustic power density are amplified. At this time, since the resonance tube length L is set so that the acoustic power amplification factor G is maximized, the thermoacoustic engine 1B realizes a high impedance at the position of the heat accumulator 12 and increases the acoustic power density. be able to. As a result, the thermoacoustic engine 1 </ b> B can transmit a large acoustic power to the cooling loop 40.

  Next, the acoustic power transmitted to the refrigerating regenerator 42 is cooled by releasing the heat to the outside by the refrigerating cooler 43 and the low temperature of the freezing regenerator 42 and the freezing regenerator 42. It is converted into a temperature difference with the part 42b. Then, the cold air (cold heat) generated in the low temperature portion 42b of the refrigerating regenerator 42 due to the temperature difference between both ends of the refrigerating regenerator 42 is taken out by the cold air discharger 44, whereby the refrigerating capacity is obtained.

<Action and effect>
As described above, as in the second embodiment, the thermoacoustic engine 1B has an advantage that there is basically no conversion loss or friction loss due to the conversion mechanism, and can be expected to be downsized and highly efficient.
The thermoacoustic engine 1B has been described as including a cooling loop. However, instead of the cooling loop 40, a temperature increasing loop (not shown) for increasing the temperature may be provided. Since this temperature raising loop is the same as the prime mover loop 20 of FIG. 7, detailed description thereof is omitted.

(Fourth embodiment)
With reference to FIG. 9, the specific usage method is illustrated as thermoacoustic engine 1C which concerns on 4th Embodiment of this invention (refer FIG. 1 suitably).

As shown in FIG. 9, the thermoacoustic engine 1C is different from the first embodiment in that the thermoacoustic engine 1C further includes a prime mover 10 ₃ connected in series to the prime movers 10 ₁ and 10 ₂ in FIG. The prime mover 10 _3, the same as in the prime mover ₁₀ 1, 10 _2, the description thereof is omitted.

Here, the thermoacoustic engine 1 </ b> C uses exhaust heat generated in the factory 60. That is, the thermoacoustic engine 1C cools the coolers 14 of the prime movers 10 ₁ to 10 ₃ with the cooling water cooled by the cooling device 50. At this time, the thermoacoustic engine 1 may perform cooling by air cooling instead of cooling by cooling water. The thermoacoustic engine 1 </ b> C heats the heaters 13 of the prime movers 10 ₁ to 10 ₃ by the exhaust heat generated at the factory 60. Thus, in the thermoacoustic engine 1C, a temperature gradient is formed at both ends of the regenerator 12 of the prime movers 10 ₁ to 10 ₃ .

The thermoacoustic engine 1C can also be used as a thermoacoustic engine that is heated by exhaust heat generated in an automobile engine and that is cooled by water cooling or air cooling.
Furthermore, the thermoacoustic engine 1C can be used as a thermoacoustic engine that is heated by exhaust heat generated by the engine of the ship and that is cooled by water cooling or air cooling using seawater for engine cooling.

<Action and effect>
As described above, since the thermoacoustic engine 1C can use the exhaust heat generated around the thermoacoustic engine 1C, it can improve the energy recovery efficiency and contribute to solving global warming and energy problems. Can do.

(Modification)
The thermoacoustic engine according to the present invention is not limited to the above-described embodiment, and can be modified without departing from the gist thereof.
In each of the above-described embodiments, the thermoacoustic engine has been described as connecting two or three prime movers in series, but four or more prime movers may be connected in series.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. In each Example, it was set as the same structure as the thermoacoustic engine 1 of FIG. Here, parameters relating to the resonance tubes 11a and 11b, the regenerator 12, the heater 13 and the cooler 14, and parameters relating to the cooler temperature, the heater temperature and the working gas are set as parameters, and the resonance tube length L is set as a parameter. Asked. Hereinafter, Examples 1 to 3 will be described.

Example 1
In Example 1, the specifications regarding the resonance tubes 11a and 11b, the heat accumulator 12, the heater 13 and the cooler 14 are shown in FIG. The cooler temperature is 300 (K), the heater temperature is 600 (K), the operating frequency is 40 (Hz), and the working gas is atmospheric pressure air.
In FIG. 10, the resonance tube 11a is illustrated as the resonance tube 1, and the resonance tube 11b is illustrated as the resonance tube 2 (the same applies to FIGS. 14 and 18).

That is, in Example 1, the heaters 13 of the prime movers 10 ₁ and 10 ₂ are heated at 600 (K), and the cooler 14 of the prime movers 10 ₁ and 10 ₂ is cooled at 300 (K). In the first embodiment, the heater temperature and the cooler temperature are the same for each prime mover 10, but the heater temperature and the cooler temperature may be different for each prime mover 10.

  And the acoustic power gain G was computed using the above-mentioned calculation model. FIG. 11 shows the relationship among the acoustic power amplification factor G, the resonance tube length L, and the unit efficiency η. In FIG. 11, the relationship between the acoustic power amplification factor G and the resonance tube length L is illustrated by a solid line, the portion where the acoustic power amplification factor G is maximum is illustrated by a dot, and the relationship between the resonance tube length L and the efficiency η is illustrated. This is illustrated by a broken line (the same applies to FIGS. 15 and 19).

The unit efficiency η represents the thermal efficiency of each prime mover 10, and is represented by the following equation (12) as input acoustic power Win _in the prime mover 10, and the difference in output acoustic power W _out from the prime mover 10 is defined as the input heat quantity Q. It can be defined as the value divided by.

  From FIG. 11, when the resonance tube length L is 0.43 [m], the acoustic power gain G of each prime mover 10 is a maximum of 1.55, so this resonance tube length L is set.

FIG. 12 shows a normalized sound power distribution when the resonance tube length L is set, and FIG. 13 shows a normalized sound power density distribution. 12, the horizontal axis x [m] is shown in FIG. 13, the left end of the resonance tube 11a of the engine 10 ₁ (i.e., wave thermoacoustic engine 1 position input) is the distance relative to the. Further, in FIG. 12, the sound power W ₀ at the position of x = 0 is normalized, and in FIG. 13, the sound power density I ₀ at the position of x = 0 is normalized.

12 and 13, it can be seen that the acoustic power and the acoustic power density increase every time the prime movers 10 ₁ and 10 ₂ are connected. In addition, it is thought that the acoustic power density decreased in the vicinity of the regenerator 12 because the cross-sectional area of the regenerator 12 is larger than that of the resonance tube 11.

(Example 2)
In Example 2, the specifications regarding the resonance tubes 11a and 11b, the heat accumulator 12, the heater 13, and the cooler 14 are shown in FIG. The cooler temperature is 300 (K), the heater temperature is 600 (K), the operating frequency is 40 (Hz), and the working gas is helium at 10 atm. Then, the sound power gain G was calculated using the same calculation model as in Example 1.

  The relationship among the acoustic power gain G, the resonance tube length L, and the unit efficiency η is shown in FIG. From FIG. 15, when the resonance tube length L is 2.61 [m], the acoustic power amplification factor G of each prime mover 10 is 1.70, which is the maximum, so this resonance tube length L is set.

FIG. 16 shows the normalized sound power distribution when the resonance tube length L is set, and FIG. 17 shows the normalized sound power density distribution. 16 and 17, it can be seen that the sound power and the sound power density increase every time the prime movers 10 ₁ and 10 ₂ are connected as in the first embodiment.

(Example 3)
In Example 3, the specifications regarding the resonance tubes 11a and 11b, the heat accumulator 12, the heater 13, and the cooler 14 are shown in FIG. The cooler temperature is 300 (K), the heater temperature is 600 (K), the operating frequency is 25 (Hz), and the working gas is helium at 30 atm. Then, the sound power gain G was calculated using the same calculation model as in Example 1.

  The relationship among the acoustic power amplification factor G, the resonance tube length L, and the unit efficiency η is shown in FIG. From FIG. 19, when the resonance tube length L is 5.49 [m], the acoustic power amplification factor G of each prime mover 10 is maximum at 1.62, so this resonance tube length L is set.

FIG. 20 shows the normalized sound power distribution when the resonance tube length L is set, and FIG. 21 shows the normalized sound power density distribution. 20 and 21, it can be seen that the sound power and the sound power density increase each time the prime movers 10 ₁ and 10 ₂ are connected, as in the first embodiment.

  Here, the results of FIGS. 11, 15, and 19 are organized. From these graphs, if the resonance tube length L is set so that the acoustic power gain G is 70% or more of the ratio between the heater temperature and the cooler temperature, the unit efficiency η is also increased, and the thermoacoustic engine 1 is large. It is considered that the acoustic power can be transmitted by traveling waves or sound waves close to traveling waves. That is, the resonance tube length L may be set so that the acoustic power gain G is not less than a value obtained by multiplying the ratio between the heater temperature and the cooler temperature by a value not less than 0.7 and not more than 1.0. Recognize.

1, 1A, 1B, 1C Thermoacoustic engine 10, 10 ₁ , 10 ₂ , 10 ₃ Motor 11, 11, 11a, 11b Resonant tube 12 Heat storage 13 Heater 14 Cooler 20 Motor loop (input unit)
30 Generator (Output unit)
40 Cooling loop (output part)

Claims (6)

A regenerator that heats and cools the working gas, a heater that is adjacent to one end of the regenerator, heats one end of the regenerator, is adjacent to the other end of the regenerator, and other than the regenerator A cooler that discharges heat of the end to the outside, and a resonance tube that is connected to the heater and the cooler, respectively, and is filled with the working gas, and forms a temperature gradient between both ends of the regenerator. A thermoacoustic engine in which a plurality of prime movers that amplify the acoustic power and acoustic power density of the working gas are connected in series,
p is the pressure amplitude, U sectional average volumetric flow rate amplitude, j is the imaginary unit, omega is the angular frequency, the cross-sectional area of A _C is the resonance tube, p _m is the average pressure of the working gas, gamma is the specific heat ratio, [nu is Kinematic viscosity coefficient, σ is Prandtl number, T _m is the average temperature of the working gas inside the resonance tube, χ _α , χ _ν are complex functions depending on the temperature diffusion coefficient and kinematic viscosity coefficient, α is the thermal diffusion coefficient, J _0, 0-th and 1-th order of J ₁ is a Bessel function, r is the radius of the resonance tube, tau _alpha, tau _[nu thermal relaxation time and kinematic viscosity relaxation time, the resonance tube B _a is the cooler side B _AHX is the transfer matrix of the cooler, B _reg is the transfer matrix of the regenerator, B _HHX is the transfer matrix of the heater , B _b is the transfer matrix of the resonance tube on the heater side, and e is Napier _{number, p a, v a, U} a co of the cooler side Pressure amplitude at the end of the tube, cross-sectional average flow rate amplitude and cross-sectional average volumetric flow rate amplitude, p _{b, v b,} the pressure amplitude at the end of the resonance tube of U _b is the heater side, cross-sectional average flow rate amplitude and cross the mean volume Using equations (1) to (7), the flow velocity amplitude, A _a is the cross-sectional area at the end of the resonance tube on the cooler side, and A _b is the cross-sectional area at the end of the resonance tube on the heater side. And obtaining a transfer matrix M _all of the thermoacoustic engine ,

Using Equations (8) and (9) in which λ represents an eigenvalue, an acoustic power amplification factor G is obtained from the transfer matrix M _all .

The thermoacoustic engine is characterized in that the length of the resonance tube is set so that the obtained acoustic power gain G is maximized .   The thermoacoustic engine according to claim 1, wherein the plurality of prime movers have the same length and cross-sectional area of the resonance tube. An input unit for inputting an input sound wave for amplifying the acoustic power and acoustic power density of the working gas to one end of the plurality of connected prime movers;
From the other end of the plurality of connected prime movers, an output unit that outputs amplified amplified sound waves;
Thermoacoustic engine according to claim 1 or claim 2, further comprising a. The input unit is a motor loop that generates the input sound wave,
The thermoacoustic engine according to claim 3 , wherein the output unit is a generator that generates power in response to the amplified sound wave. The input unit is a motor loop that generates the input sound wave,
The thermoacoustic engine according to claim 3 , wherein the output unit is one of a cooling loop that performs cooling in response to the amplified sound wave and a temperature rising loop that performs temperature increase. A method for manufacturing a thermoacoustic engine according to claim 1 ,
A transfer matrix calculation step for _obtaining a transfer matrix M _all of the thermoacoustic engine using the equations (1) to (7);
Using the equation (8), an eigenvalue calculating step for obtaining an eigenvalue λ of the transfer matrix M _all ;
Substituting the eigenvalue λ obtained in the eigenvalue calculation step into the equation (9) to obtain the acoustic power amplification factor G,
A resonance tube length setting step for setting the length of the resonance tube so that the acoustic power amplification factor G obtained in the acoustic power amplification factor calculation step is maximized;
The manufacturing method of the thermoacoustic engine characterized by including.

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