WO2008131687A1 - Système de moteur thermoacoustique utilisant une source de chaleur à variation de température - Google Patents

Système de moteur thermoacoustique utilisant une source de chaleur à variation de température Download PDF

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Publication number
WO2008131687A1
WO2008131687A1 PCT/CN2008/070815 CN2008070815W WO2008131687A1 WO 2008131687 A1 WO2008131687 A1 WO 2008131687A1 CN 2008070815 W CN2008070815 W CN 2008070815W WO 2008131687 A1 WO2008131687 A1 WO 2008131687A1
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WIPO (PCT)
Prior art keywords
heat exchanger
traveling wave
temperature heat
high temperature
loop
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Application number
PCT/CN2008/070815
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English (en)
French (fr)
Inventor
Ercang Luo
Wei Dai
Zhanghua Wu
Jianying Hu
Original Assignee
Shenzhen Zhongke-Lihan Thermoacoustic Engineering Research Center Co., Ltd.
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Application filed by Shenzhen Zhongke-Lihan Thermoacoustic Engineering Research Center Co., Ltd. filed Critical Shenzhen Zhongke-Lihan Thermoacoustic Engineering Research Center Co., Ltd.
Publication of WO2008131687A1 publication Critical patent/WO2008131687A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/002—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using the energy of vibration of fluid columns
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
    • F02G2243/50—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes
    • F02G2243/54—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes thermo-acoustic

Definitions

  • thermoacoustic engines and more particularly to thermoacoustic engine systems that utilize variable temperature heat sources.
  • thermoacoustic engine is an energy conversion device that converts thermal energy into acoustic energy by using the thermoacoustic effect. It has the following advantages: There are no moving parts in the system, which fundamentally eliminates the wear and vibration that are common in conventional machinery, and the operation is stable and reliable. Long service life; using heat as an energy source, solar energy, waste heat, etc. can be used as a driving source, which is very meaningful for solving the problem of lack of power in remote areas; using inert gas as a working medium is conducive to environmental protection, so it has a very broad development. prospect. At present, the thermoacoustic conversion efficiency of the traveling wave thermoacoustic engine has reached 30%, which is close to the conversion efficiency of the internal combustion engine.
  • thermoacoustic engine systems are directed to fixed temperature heat transfer media.
  • 1 is a schematic view showing the structure of a conventional traveling wave thermoacoustic engine, which is mainly composed of a traveling wave loop 5 and a resonance tube 6.
  • the traveling wave loop high temperature heat exchanger 2 must be maintained at a certain temperature so that the regenerator 1 between it and the room temperature heat exchanger 3 can maintain a certain temperature gradient for the system to operate.
  • There are many ways to maintain the high temperature heat exchanger 2 at a constant high temperature such as using an electric heater or the like.
  • the high temperature heat exchanger cannot maintain a constant temperature, and the high temperature flue gas is formed by the fuel combustion to form a fluid heat source carrier, which enters from the inlet of the high temperature heat exchanger, and the high temperature flue gas is exchanged at a high temperature.
  • thermoacoustic engine supplies heat to the thermoacoustic engine, and the temperature of the heat transfer fluid medium after heat exchange is lowered and passes through the high temperature heat exchanger. The exit is discharged.
  • the current thermoacoustic engine system cannot efficiently utilize the heat of the heat transfer fluid medium.
  • the temperature of the high temperature flue gas is about 1000 °C
  • the design temperature of the high temperature heat exchanger is 950 °C.
  • the temperature of the flue gas flowing out of the high temperature heat exchanger is about 900 °C, then the flue gas heat is only used a small part, most of which will be discharged, not used, causing great energy loss. Therefore, it is desirable to have a thermoacoustic engine system that can fully utilize the heat of the heat transfer fluid and improve efficiency. Summary of the invention
  • the object of the present invention is to overcome the deficiencies of current thermoacoustic engines in the use of a variable temperature heat source, and to provide a thermoacoustic engine system utilizing a variable temperature heat source.
  • the present invention provides a thermoacoustic engine system utilizing a variable temperature heat source, including a resonance tube, further comprising at least two stages of traveling wave loops, all of which are shared by the traveling wave loop, each of said rows
  • the wave loop has a high temperature heat exchanger having an input port and an output port for inputting and outputting the heat transfer fluid medium, and the high temperature heat exchanger output port of the previous stage traveling wave loop and the latter
  • the high temperature heat exchanger input port of the directional traveling wave loop is connected, and the operating temperature of the high temperature heat exchanger of the at least two-stage traveling wave loop is from a previous first traveling wave loop to a subsequent first traveling wave loop The road is lowered in turn.
  • the invention installs two or more traveling wave loops on the resonance tube of the traveling wave thermoacoustic engine, and the design temperature of the high temperature heat exchanger on each traveling wave loop is different, and the design temperature is from the previous first loop to The latter stage is successively decremented; the heat carrier fluid flows into the high temperature heat exchanger of each stage loop in turn for heat exchange, and the engine can absorb the heat of the heat carrier fluid at different temperature ranges.
  • the traveling wave loop routing feedback tube, the first low temperature heat exchanger, the regenerator, the high temperature heat exchanger, the heat buffer tube and the second low temperature heat exchanger are sequentially connected to each other,
  • the traveling wave loops are in communication with the common resonant tube at respective second cryogenic heat exchangers and outside of the thermal buffer.
  • the traveling wave loop of each stage further includes a low temperature heat exchanger and a feedback tube, and a regenerator and a thermal buffer are disposed between the high temperature heat exchanger and the low temperature heat exchanger.
  • the heat recovery There is a partition between the heat exchanger and the heat buffer, the partition extending through the cryogenic heat exchanger and acting as a wall of the feedback tube on the outside of the low temperature heat exchanger.
  • the traveling wave loops of the stages share a low temperature heat exchanger and respectively include a regenerator and a heat buffer tube, and a high temperature heat exchanger, a regenerator and a high frequency heat exchanger in the first stage traveling wave loop.
  • the shared cryogenic heat exchanger sets a subsequent first-order traveling wave loop around the space.
  • the at least two stages of traveling wave loops are respectively connected to both ends of the resonance tube.
  • the heat buffer tubes of the traveling wave loops of the stages are coaxially located inside the regenerator.
  • all the traveling wave loops form a circumferentially symmetric multi-stage traveling wave loop nesting, and all of the regenerators, the heat buffer tubes and the feedback tubes are coaxially arranged.
  • the traveling wave loops of each stage further comprise a regenerator and a common low temperature heat exchanger, and all the high temperature heat exchangers of the traveling wave loop form an integral high temperature heat exchanger, and the whole high temperature heat exchanger A heater is disposed inside the regenerator.
  • the integral high temperature heat exchanger is formed by at least one fluid conduit disposed inside the regenerator.
  • the regenerator is bent into a shape of a cylinder having a hollow portion
  • the system further includes a heat buffer tube coaxially disposed in a hollow portion of the regenerator
  • the heat buffer tube is divided into at least two sections in the axial direction, and has a gap between the sections and the section for allowing a working gas to enter the heat buffer tube, the gap width being greater than or equal to the thermal buffer One percent of the length of the tube.
  • the present invention has the following technical effects:
  • the present invention employs at least two traveling wave loops of different operating temperatures, and the engine system can absorb heat of the heat carrier fluid at different temperature ranges, thereby improving heat conversion efficiency;
  • the present invention employs a coaxial or nested arrangement of at least two traveling wave loops such that the engine system has a compact construction while having high conversion efficiency.
  • Figure 1 is a typical prior art conventional structure of a traveling wave thermoacoustic engine
  • thermoacoustic engine system according to an embodiment of the present invention, which is a traveling wave thermoacoustic engine system equipped with a variable temperature heat source of three traveling wave loops;
  • FIG. 3 is a schematic diagram of a certain stage traveling wave loop of a thermoacoustic engine system according to an embodiment of the present invention; a schematic diagram of a machine system, wherein each stage traveling wave loop structure is as shown in FIG. 3;
  • FIG. 5 is a traveling wave thermoacoustic engine system of a symmetrically arranged variable temperature heat source according to an embodiment of the present invention
  • FIG. 6 is a traveling wave heat of a variable temperature heat source equipped with six traveling wave loops according to an embodiment of the present invention
  • Acoustic engine system ;
  • FIG. 7 is a traveling wave thermoacoustic engine system of a coaxial variable temperature heat source according to an embodiment of the present invention
  • FIG. 8(a)-(c) is a variation of four traveling wave loops according to an embodiment of the present invention
  • the traveling wave thermoacoustic engine system of the warm source wherein Fig. 8 (a) shows the traveling wave thermoacoustic engine system of the variable temperature heat source of the coaxial and high temperature heat exchanger disposed inside the regenerator; Fig. 8 (b) shows The thermoacoustic engine system of the present embodiment can be equivalently regarded as a thermoacoustic engine of four coaxial structures;
  • Fig. 8(c) is a cross-sectional view taken along line A-A of Fig. 8(b).
  • the invention proposes to install a multi-stage traveling wave loop operating at different temperatures on a resonance tube of a thermoacoustic engine to realize a thermal energy step to improve efficiency. The following will explain it theoretically.
  • thermoacoustic engine There is a heat carrier fluid of mass m, the temperature is 1000K, the specific heat capacity is C p , and the temperature of the room temperature heat exchanger is ⁇ . It is 300 baht. If only one traveling wave loop is designed on the thermoacoustic engine, the average design temperature of the hot end heat exchanger is 950 ⁇ , the temperature of the heat transfer fluid after flowing out of the heat exchanger is 900 ⁇ , and the thermal efficiency of the thermoacoustic engine is equal to the Carnot efficiency. , the total sound work that the thermoacoustic engine can convert can be expressed as:
  • the heat transfer fluid flowing out of the heat exchanger of the first stage loop flows into the heat exchanger of the second stage loop, and
  • the average design temperature of the high-temperature heat exchanger of the second-stage loop is 850K, and the temperature of the fluid flowing out is 800K.
  • the sound energy that can be converted by the second-stage loop is:
  • the hot end heat exchanger is designed for a temperature of 750K, and the fluid flows out at a temperature of 700K, the third stage loop can convert the sound power to:
  • thermoacoustic engine can be improved by stepwise utilization of thermal energy through a multi-stage traveling wave loop.
  • the invention will be further described below in conjunction with the examples.
  • each traveling wave loop is connected to the resonance tube of the thermoacoustic engine system.
  • the design structure of each traveling wave loop is as follows: Connect the feedback tube 5 from the resonance tube 6 in sequence, and change the temperature at low temperature.
  • Heater 3 (such as room temperature heat exchanger 3 with heat exchange with room temperature), regenerator 1, high temperature heat exchanger 2, heat buffer tube 4, the other end of the heat buffer tube 4, for example, through the same another low temperature change
  • the heat exchanger 3 is connected to the resonance tube 6.
  • Each stage of the high temperature heat exchanger has an input port 9 and an output port 10 for the input and output of the heat transfer fluid medium, and the high temperature heat exchanger output port 10 and the second stage traveling wave ring of the first stage traveling wave loop
  • the input port of the high temperature heat exchanger of the road is connected, and so on, the output port of the high temperature heat exchanger of the penultimate traveling wave loop is connected with the input port of the high temperature heat exchanger of the last stage traveling wave loop;
  • the operating temperature of the heat exchanger is sequentially reduced from the first-stage traveling wave loop to the last-stage traveling wave loop; since the optimum size of each component of the traveling wave loop is related to the design temperature of the high-temperature heat exchanger, each loop
  • the dimensions vary, and the design of the various loop sizes is well within the skill of the art.
  • the high temperature heat exchanger design of the first stage traveling wave loop has an average heat exchange temperature of about 600 ° C, the average heat exchange temperature of the second stage is about 500 ° C, and the average heat exchange temperature of the third stage is about 400 °. C.
  • the temperature of the heat transfer fluid flowing into the first stage high temperature heat exchanger is 650 ° C, the temperature at the time of the outflow is 550 ° C, and then enters the high temperature heat exchanger of the second stage loop, and flows out of the second stage high temperature heat exchanger.
  • the temperature is 450 ° C, and then the heat transfer fluid enters the high temperature heat exchanger of the third stage loop. After the heat exchange, the temperature of the heat transfer fluid is lowered to 350 ° C.
  • thermoacoustic engine system of the present embodiment the utilization of heat of a variable temperature heat source such as a heat transfer fluid can be greatly improved.
  • the single-stage traveling wave thermoacoustic engine of Figure 1 can also be designed as shown in Figure 3.
  • the regenerator 1, the heat buffer tube 4, the feedback tube 5, and the resonance tube 6 adopt a square structure, and a regenerator 1 and a heat buffer are disposed between the high temperature heat exchanger 2 and the low temperature heat exchanger 3.
  • the tube 4, the regenerator 1 and the heat buffer tube 4 are separated by a partition which extends through the low temperature heat exchanger 3 and serves as the inner side wall of the feedback tube 5 on the outside of the low temperature heat exchanger 3, feedback
  • the outer side wall of the tube 5 is formed by an integral outer casing constituting a traveling wave loop. As shown in Fig.
  • the partitions of the multi-level traveling wave loop are connected as a whole.
  • a single loop adopts the structure shown in FIG. 3
  • a plurality of traveling wave loops can be compactly mounted together, as shown in FIG. 4, and the room temperature heat exchanger 3 and the high temperature heat exchanger 2 of each loop can be directly Connected together to form a one-piece structure.
  • Each stage of the high temperature heat exchanger has an input port and an output port for the input and output of the heat transfer fluid medium, and the high temperature heat exchanger output port of the first stage traveling wave loop and the high temperature of the second stage traveling wave loop
  • the input ports of the heat exchanger are connected, and so on, the output port of the high temperature heat exchanger of the penultimate stage traveling wave loop is connected to the input port of the high temperature heat exchanger of the last stage traveling wave loop; in this embodiment
  • the connection structure for transporting the heat transfer fluid between the high temperature heat exchangers of each stage is very short.
  • the two-stage high temperature heat exchanger can be made close to each other. In the high temperature heat exchanger 2, the heat transfer is carried out. The fluid flows from the first-stage loop to the higher-order loop.
  • the temperature of the heat-carrying fluid will gradually decrease, so that the regenerators of the various stages are close to the high temperature.
  • the hot end temperature of the heater 2 will also gradually decrease, and a total five-stage traveling wave circuit is shown in FIG.
  • the temperature of the heat transfer fluid entering the high temperature heat exchanger 2 is 1 000 °C
  • the temperature of the high temperature heat exchanger flowing out of the last stage traveling circuit is 400 °C.
  • the design of this embodiment makes it possible to make the structure more compact and compact while making full use of heat.
  • the regenerator 1, the high temperature heat exchanger 2, the heat buffer tube 4, the feedback tube 5, and the common low temperature heat exchanger of each stage in this embodiment adopt a square structure, but are implemented.
  • the difference between the two examples is that the regenerator and the heat buffer tube of the previous stage are not close to each other but leave each other and form a space with the high temperature heat exchanger and the shared low temperature heat exchanger, and accommodate the latter stage in the space.
  • Each stage of the high temperature heat exchanger has an input port for the input and output of the heat transfer fluid medium (for example, it can be placed on the upper surface of the high temperature heat exchanger) and an output port (for example, it can be placed on the lower surface of the high temperature heat exchanger)
  • the high-temperature heat exchanger output port of the first-stage traveling wave loop and the high-temperature heat exchanger input port of the second-stage traveling wave loop are connected through the connecting pipe, and so on, the second-order traveling wave loop of the second-order
  • the high temperature heat exchanger output port and the high temperature heat exchanger input port of the last stage traveling wave loop are connected through a connecting pipe; the operating temperature of the high temperature heat exchanger starts from the first stage traveling wave loop to the last stage traveling wave ring
  • the circuit is sequentially lowered; each end of the resonance tube in the figure shows a four-stage traveling wave loop, and the average temperature of the high temperature heat exchanger designed for each stage, such as the loop from the first stage to the fourth stage, respectively 500 ° C
  • the design structure of the traveling wave loop of each coaxial structure is: connecting the feedback tube 5, the low temperature heat exchanger 3, and the heat return from the resonance tube 6 in this order.
  • the high temperature heat exchanger 2 the heat buffer tube 4 is disposed inside the regenerator 1 and coaxially mounted, and the two ends of the heat buffer tube 4 are respectively connected to the high temperature heat exchanger 2 and the low temperature heat exchanger 3.
  • Each stage of high temperature heat exchanger has an input port for the input and output of the heat transfer fluid medium (such as the left side in the figure of the high temperature heat exchanger) and an output port (such as can be placed in the high temperature heat exchanger) On the right side of the figure), and
  • the high-temperature heat exchanger output port of the first-order traveling wave loop and the high-temperature heat exchanger input port of the second-stage traveling wave loop are connected through the connecting pipe, and so on, the high-temperature heat exchange of the penultimate traveling wave loop
  • the high temperature heat exchanger input port of the output port of the last stage and the last stage traveling wave loop is connected through the connecting pipe; the operating temperature of the high temperature heat exchanger is sequentially decreased from the first stage traveling wave loop to the last stage traveling wave loop.
  • the operating temperature of the traveling wave loops at all levels is designed such that the average temperature of the high temperature heat exchangers from the first to sixth loops is 900 ° C, 800 ° C, 700 ° C, 600 ° C, respectively. 500 ° C, 400 ° C, the initial temperature of the heat carrier fluid is 950 ° C, the temperature drops 100 ° C per high temperature heat exchanger, the temperature of the last high temperature heat exchanger is 350 ° C, this kind of The thermoacoustic engine formed by the cascade of coaxial traveling wave loops not only greatly improves the utilization of the heat source, but also the multi-stage loop sharing the resonance tube makes the entire structure compact.
  • a plurality of traveling wave loops are coaxially arranged, that is, all the regenerators 1, the heat buffer tubes 4, and the feedback tubes 5 are coaxially arranged.
  • the regenerator 1 and the feedback tube 5 of the first-stage loop are located at the outermost layer of the entire coaxial structure, and the thermal buffer tube 4 of the first-stage loop is located at the center of the entire coaxial structure;
  • the heat exchanger and the feedback tube are located inside the previous stage loop, and the heat buffer tube of the latter stage loop is located at the outer layer of the previous stage loop, so that the multi-stage traveling wave loop forms a nested form.
  • This structure is obviously more compact than in Figures 5 and 6.
  • Each stage of the high temperature heat exchanger has an input port for the input and output of the heat transfer fluid medium (for example, it can be placed on the upper surface of the high temperature heat exchanger) and an output port (for example, it can be placed on the lower surface of the high temperature heat exchanger)
  • the high temperature heat exchanger output port of the first stage traveling wave loop and the high temperature heat exchanger input port of the second stage traveling wave loop are connected through a pipe (not shown), and so on, the second to last
  • the high temperature heat exchanger output port of the directional traveling wave loop is connected to the high temperature heat exchanger input port of the last stage traveling wave loop; the operating temperature of the high temperature heat exchanger starts from the first level traveling wave loop to the last stage The traveling wave loop is successively reduced.
  • the average temperature of the high temperature heat exchanger from the first to fourth loops is 900 ° C, 800 ° C, 700 °C, 600 ° C
  • the initial temperature of the heat carrier fluid is 950 ° C
  • the temperature drops by 100 ° C per high temperature heat exchanger is 550 ° C.
  • the connection between the regenerators of the various stages and the high temperature heat exchanger and the low temperature heat exchanger is obliquely mounted, The advantage is that the contact area between the regenerator and the high temperature heat exchanger and the low temperature heat exchanger is increased, which is more favorable for heat exchange.
  • the traveling wave loop is a coaxial structure, and the feedback tube 5, the shared low temperature heat exchanger 3, and the regenerator 1 are sequentially connected from the resonance tube 6, and the regenerator 1 is
  • the heat buffer tube 4 is coaxially disposed in the hollow portion of the regenerator 1 in a shape of a cylinder having a hollow portion;
  • the high temperature heat exchanger 2 takes the form of a fluid conduit for passing the fluid and performing with the regenerator 1
  • the fluid conduit enters the regenerator 1 from one end of the regenerator 1 and passes through the regenerator 1 and exits at the other end of the regenerator 1.
  • the heat exchange tube also extends to Come out from the low temperature heat exchanger 3.
  • the longitudinal length of the heat buffer tube 4 is 10 cm, which can be divided into four sections, and a gap 8 is left between the sections, and the gap width is not less than one percent of the length of the heat buffer tube 4.
  • the width of the gap 8 is 1 cm; the gap between the heat buffer tube 4 and the end surface 7 is 1 cm.
  • the structure actually combines the traveling wave loops of multiple coaxial structures together, as shown in Figure 8), because the temperature of the regenerator and the thermal buffer tube in each loop is linear, so The regenerators and the heat buffer tubes are combined according to the principle that the temperatures are equal, and the heat buffer tube is divided into several sections, and the design structure with gaps between the two sections is to maintain the flow characteristics of the original traveling wave loops.
  • Figure 8 (a) structure is equivalent to the cascade of four traveling wave loops in Figure 8 (b), the operating temperature is designed as 1000K, 900K, 800K, 700K, respectively, Figure 8)
  • the feedback tube 5 and the resonance tube 6 of the loop are also combined to form the structure of Fig. 8(b).
  • the heat exchange tube of the high temperature heat exchanger can be directly installed in the regenerator, so that the heat transfer fluid passes through After the regenerator, the temperature is directly reduced to a low temperature (such as room temperature), and the maximum use of heat.
  • Figure 8 (c) is a cross-sectional view taken along line A - A of Figure 8 (b), it can be seen that the heat exchange tube 2 of the high-temperature heat exchanger is substantially evenly distributed inside the regenerator 1, this embodiment
  • a plurality of linear heat exchange tubes are embedded in the regenerator, and of course, the heat exchange tubes can be embedded in the regenerator by other means, for example, at least one spiral heat exchange tube is embedded in the regenerator. .
  • thermoacoustic engine structure actually cascades an infinite number of traveling wave loops, which can heat from a high temperature heat source to a low temperature heat source. High utilization reaches its limit.

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Description

利用变温热源的热声发动机系统 技术领域
本发明涉及热声发动机， 特别涉及利用变温热源的热声发动机系统。 背景技术
热声发动机是一种利用热声效应将热能转换为声能的能量转换装置， 它 具有以下优点： 系统中没有运动部件， 从根本上消除了常规机械所普遍存在 的磨损与振动， 运行稳定可靠， 使用寿命长； 使用热作为能源， 可以利用太 阳能、废热等作为驱动源， 这对于解决偏远地区动力缺乏的问题非常有意义； 以惰性气体作为工质， 有利于环保， 所以具有非常广阔的发展前景。 目前， 行波热声发动机的热声转换效率已经达到了 30% , 已经接近内燃机的转换效 率。
在自然界和工程应用中， 目前主要存在两类热源载体： 一类热源载体是 固体介质， 另一类热源载体是流体介质。 对于固体热源载体， 其热量的利用 可以在固定的温度下进行， 例如， 利用太阳能或者同位素放射材料等给固体 加热并维持在一定的热平衡温度。 对于流体热源载体， 其热量的利用往往是 在变化的温度下体现出来的， 即热量的获得往往需要流体的降温来实现。 目 前的热声发动机系统是针对固定温度载热介质的。 图 1是现有的行波热声发 动机结构示意图， 它主要由一个行波环路 5和一个谐振管 6组成。 行波环路 高温换热器 2必须维持在一定的温度， 这样它与室温换热器 3之间的回热器 1 才能保持一定的温度梯度， 系统才能工作。 维持高温换热器 2处于恒定高 温的方法很多， 比如采用电加热器等等。 但在采用流体热源载体的情况下， 高温换热器不能够维持恒定的温度， 都是通过燃料燃烧获得高温烟气形成流 体热源载体， 从高温换热器的入口进入， 高温烟气在高温换热器内的换热为 热声发动机提供热量， 换热后的载热流体介质的温度降低并经过高温换热器 的出口排出。 在这种情况下， 目前的热声发动机系统就不能高效率地利用载 热流体介质的热量， 比如如果高温烟气的温度为 1000 °C左右， 高温换热器的 设计平均温度在 950 °C左右， 烟气流出高温换热器的温度为 900 °C左右， 那么 烟气热量仅仅被利用了很小的一部分， 绝大部分将被排放， 没有被利用， 造 成了极大的能量损失。 因此， 就希望有一种能够充分利用载热流体的热量、 提高效率的热声发动机系统。 发明内容
本发明的目的在于克服目前热声发动机在利用变温热源时存在不能完全 有效利用热量的不足， 提供一种利用变温热源的热声发动机系统。
为此， 本发明提供一种利用变温热源的热声发动机系统， 包括谐振管， 还包括至少两级行波环路， 所有的行波环路共用所述谐振管， 每个所述行波 环路有高温换热器， 所述高温换热器具有用于载热流体介质输入和输出的输 入口和输出口， 前一级行波环路的所述高温换热器输出口与后一级行波环路 的所述高温换热器输入口相连通， 所述至少两级行波环路的所述高温换热器 的工作温度从前一级行波环路到后一级行波环路依次降低。
本发明在行波热声发动机的谐振管上安装两个或两个以上的行波环路， 每个行波环路上的高温换热器的设计温度各不相同， 设计温度从前一级环路 向后一级依次递减； 载热流体依次流入各级环路的高温换热器进行换热， 发 动机可以在不同的温度段吸收利用载热流体的热量。
在上述技术方案中， 所述行波环路由反馈管、 第一低温换热器、 回热器、 所述高温换热器、 热緩沖管和第二低温换热器顺序连通构成， 各级所述行波 环路在各自的第二低温换热器处且在所述热緩沖器的外侧与共用的所述谐振 管相连通。
在上述技术方案中， 各级所述行波环路还包括低温换热器和反馈管， 在 所述高温换热器和所述低温换热器之间设置有回热器和热緩沖器， 所述回热 器和所述热緩沖器之间有一个隔板， 所述隔板延伸经过所述低温换热器并在 所述低温换热器的外侧作为所述反馈管的壁。
在上述技术方案中， 各级所述行波环路共用一个低温换热器并分别还包 括回热器和热緩沖管， 在前一级行波环路的高温换热器、 回热器和共用的低 温换热器围绕出的空间中设置后一级行波环路。
在上述技术方案中， 在所述谐振管的两端上， 分别连接有所述至少两级 行波环路。
在上述技术方案中， 各级所述行波环路的所述热緩沖管共轴地处于所述 回热器的内部。
在上述技术方案中，所有行波环路形成圓周对称形的多级行波环路嵌套， 所有的所述回热器、 所述热緩沖管和所述反馈管同轴布置。
在上述技术方案中， 各级行波环路还包括回热器和一个共用的低温换热 器， 所有的行波环路的高温换热器形成一个整体高温换热器， 所述整体高温 换热器设置在所述回热器的内部。
在上述技术方案中，所述整体高温换热器是由至少一根流体导管形成的， 设置在所述回热器的内部。
在上述技术方案中， 所述回热器被弯曲成具有中空部的圓筒的形状， 所 述系统还包括热緩沖管， 所述热緩沖管共轴地设置在所述回热器的中空部， 所述热緩沖管在轴向上分成至少两段， 在所述段与段之间具有用于使工作气 体进入到所述热緩沖管的间隙， 所述间隙宽度大于或等于所述热緩沖管长度 的百分之一。
与现有技术相比， 本发明具有如下技术效果：
1、本发明采用至少两个不同工作温度的行波环路，发动机系统可以在不 同的温度段吸收利用载热流体的热量， 提高了热量的转换效率；
2、本发明采用至少两个行波环路同轴或者嵌套布置，使得发动机系统在 具有高的转换效率的同时具有紧凑的结构。 附图说明
图 1为一典型的现有技术传统结构的行波热声发动机；
图 2为本发明一实施例中热声发动机系统示意图， 是装有三个行波环路 的变温热源的行波热声发动机系统；
图 3为本发明一实施例中热声发动机系统的某一级行波环路示意图； 机系统的示意图， 其中的每一级行波环路结构如图 3所示；
图 5为本发明一实施例中对称布置的变温热源的行波热声发动机系统； 图 6为本发明一实施例中装有六个行波环路的变温热源的行波热声发动 机系统；
图 7为本发明一实施例中同轴的变温热源的行波热声发动机系统； 图 8 (a) _ (c)为本发明一实施例中装有四个行波环路的变温热源的行 波热声发动机系统； 其中图 8 (a)表示同轴且高温换热器设置在回热器内部 的变温热源的行波热声发动机系统； 图 8 (b)表示本实施例的热声发动机系 统可以等效地看作是四个共轴结构的热声发动机； 图 8 (c)表示沿图 8 (b) 中 A— A线的剖面图。
附图标记一览表：
1——回热器， 2——高温换热器， 3——低温换热器， 4——热緩沖管， 5——反馈管， 6——谐振管，
7——端面， 8——间隙， 9——输入口，
10——输出口。 具体实施方式
下面结合附图和具体实施方式对本发明作进一步详细描述。
为了便于技术人员理解本发明， 在给出本发明的具体实施例之前， 对本 发明提出的在热声发动机的谐振管上安装在不同温度工作的多级行波环路， 实现热能阶梯， 以提高效率。 下面将从理论上对其进行解释。
殳设有质量为 m的载热流体， 其温度为 1000K, 比热容为 Cp, 室温换 热器温度 Γ。为 300Κ。 如果热声发动机上只设计有一个行波环路， 热端换热器 的平均设计温度为 950Κ, 载热流体在流出换热器之后的温度为 900Κ, 并且热 声发动机的热效率等于卡诺效率， 则该热声发动机可以转换出的总声功可以 表示为：
τ -Τ / 、 950-300
W, = mC AT, ^-^ = mC。 1000 - 900) = 68.4m：。
1 k ' 950 p 如果在行波热声发动机上安装两个行波环路， 让从第一级环路的换热器 流出的载热流体再流入第二级环路的换热器， 并且第二级环路的高温换热器 的平均设计温度为 850K, 流体流出的温度为 800K, 则第二级环路又可以转换 出的声功为：
W7 = mC AT7 ~~ °- = lOOmC ^ = 64.7mC
2 Tk p 850 p 所以在安装了两个不同设计温度的环路后， 同样的载热流体可以转换出 的总声功变为了 133.1mCp, 效率已经大为提高。
同样的， 如果安装第三个行波环路， 热端换热器设计温度为 750K, 流体 流出的温度为 700K, 则第三级环路又可以转换出的声功为：
W, = mC AT, ~~ °- = lOOmC = 60mC
p 3 Tk p 750 p 所以在安装了三个不同设计温度的环路后， 同样的载热流体可以转换出 的总声功变为了 193.1 , 效率又有所上升。
在极限情况下， 热声发动机上安装"个行波环路， 第一个行波环路的设 计温度为 1000K, 最后一个行波环路的设计温度为 400K (该温度应该高于发 动机的启振温度）， 每个环路的温差为 600/M, 则该热声发动能够转换出的总 声功量为： τ τ i .ηη1000-— -300 ;—„ η W, =∑mC ATi^ = YmC ^ =∑600mC 7"— 6'
Ρ η 誦— P10n2-6ni
η
当" 时， \¾. =325.11 , 此时系统的热能利用效率达到极限。
以上的计算说明通过多级行波环路阶梯式利用热能能够提高热声发动机 热能的利用效率。 下面将结合实施例进一步描述本发明。
实施例 1:
如图 2所示， 作为举例， 在热声发动机系统的谐振管上连接了三个行波 环路。 以图中所示的左侧第一个行波环路为第一级行波环路为例， 每个行波 环路的设计结构为： 从谐振管 6开始依次连接反馈管 5、 低温换热器 3 (比如 采用与室温进行热量交换的室温换热器 3) 、 回热器 1、 高温换热器 2、 热緩 沖管 4,热緩沖管 4的另一端比如通过同样的另一个低温换热器 3与谐振管 6 相连。 每一级高温换热器都具有用于载热流体介质输入和输出的输入口 9和 输出口 10, 且第一级行波环路的高温换热器输出口 10与第二级行波环路的 高温换热器输入口相连通， 依此类推， 倒数第二级行波环路的高温换热器输 出口与最后一级行波环路的高温换热器输入口相连通； 高温换热器的工作温 度从第一级行波环路开始到最后一级行波环路依次降低； 因为行波环路各部 件的最优化尺寸跟高温换热器的设计温度有关， 所以各个环路的尺寸有所不 同， 完成各个环路尺寸的设计是本领域技术人员能够胜任的。 第一级行波环 路的高温换热器设计的平均换热温度约为 600°C, 第二级的平均换热温度约 为 500°C, 第三级的平均换热温度约为 400°C。 载热流体流入第一级高温换热 器的温度为 650°C, 流出时的温度为 550°C, 随后进入第二级环路的高温换热 器， 流出第二级高温换热器时的温度为 450°C, 紧接着载热流体再进入第三 级环路的高温换热器， 经过换热后， 载热流体的温度降低到了 350°C, 此时 再排放载热流体， 损失的热量已经大为减少。 采用本实施例的热声发动机系 统就能够大大提高变温热源比如载热流体的热量的利用率。 实施例 2 :
图 1中的单级行波热声发动机也可以设计成图 3所示的结构。在图 3中， 回热器 1、 热緩沖管 4、 反馈管 5和谐振管 6采用了方形的结构， 在高温换热 器 2和低温换热器 3之间设置回热器 1和热緩沖管 4 ,回热器 1和热緩沖管 4 之间由一个隔板隔开， 该隔板延伸经过低温换热器 3 , 并在低温换热器 3的 外侧作为反馈管 5的内侧壁， 反馈管 5的外侧壁是由构成行波环路的整体外 壳形成。 如图 4所示， 为了使多个行波环路的结构更为紧凑， 多级行波环路 的隔板连成一个整体。 单个环路采用图 3所示的结构以后， 可以将多个行波 环路紧凑地安装在一起， 如图 4所示， 并且各个环路的室温换热器 3和高温 换热器 2可以直接连接在一起， 做成一体的结构。 每一级高温换热器都具有 用于载热流体介质输入和输出的输入口和输出口， 且第一级行波环路的高温 换热器输出口与第二级行波环路的高温换热器输入口相连通， 依此类推， 倒 数第二级行波环路的高温换热器输出口与最后一级行波环路的高温换热器输 入口相连通； 在本实施例中， 各级高温换热器之间的用于输送载热流体的连 接结构是很短的， 总体上可以做成两级高温换热器是紧靠的， 在高温换热器 2 内， 载热流体由第一级环路往更高级环路方向流动， 随着在高温换热器 2 内换热的进行， 载热流体的温度将会逐步下降， 这样各级回热器 1 的靠近高 温换热器 2的热端温度也将会逐步降低， 图 4中示出了共五级行波回路。 比 如载热流体进入高温换热器 2的温度为 1 000 °C , 流出最后一级行波回路高温 换热器的温度为 400 °C。 本实施例的设计在充分利用热量的同时还可以使结 构更加筒单紧凑。
实施例 3 :
如图 5所示， 本实施例中的每一级的回热器 1、 高温换热器 2、 热緩沖管 4、反馈管 5和共用的低温换热器采用了方形的结构， 但与实施例 2不同的是 前一级的回热器和热緩沖管不是靠近的而是彼此离开并与高温换热器以及共 用的低温换热器形成一定的空间， 在该空间中容纳后一级的高温换热器、 回 热器和热緩沖管， 各级的回热器和热緩沖管紧挨在一起， 并共用同一个低温 换热器 3 , 后一级的环路被包裹在前一级的环路内部， 每一级的回热器之间 由隔板隔开， 隔板延伸一部分到谐振腔 6内形成各级反馈管 5的壁， 这样的 结构也是比较紧凑的。 本实施例的另一个特点就是在谐振管的另一端也布置 了与上述相同的多级行波环路，这样的对称布置可以有效地减少系统的振动， 降低噪音。 每一级高温换热器都具有用于载热流体介质输入和输出的输入口 (比如可以设置位于高温换热器的上方表面）和输出口 （比如可以设置位于 高温换热器的下方表面） ， 且第一级行波环路的高温换热器输出口与第二级 行波环路的高温换热器输入口通过连接管相连通， 依此类推， 倒数第二级行 波环路的高温换热器输出口与最后一级行波环路的高温换热器输入口通过连 接管相连通； 高温换热器的工作温度从第一级行波环路开始到最后一级行波 环路依次降低； 图中谐振管的每端示出了四级行波环路， 设计每级的工作温 度比如为从第一级到第四级的环路的高温换热器的平均温度分别为 500 °C , 400 °C , 300 °C , 200 °C , 载热流体的初始温度为 550 °C , 每经过一个高温换热 器其温度下降 1 00 °C , 流出最后一个高温换热器时的温度为 150 °C , 这样就大 大提高了热源的利用率。 另外， 如图 5 中所示， 各级回热器与高温换热器和 低温换热器之间的连接是倾斜安装的， 这样做的好处就是增大了回热器与高 温换热器和低温换热器的接触面积， 更加有利于换热。
实施例 4 :
如图 6所示， 本实施例中， 在发动机的谐振管上连接了 6个同轴结构的 行波环路。 以图中左侧的第一级行波环路为例， 每个同轴结构的行波环路的 设计结构为： 从谐振管 6开始依次连接反馈管 5、 低温换热器 3、 回热器 1、 高温换热器 2 , 将热緩沖管 4设置在回热器 1内部与其同轴安装， 热緩沖管 4 的两端分别与高温换热器 2和低温换热器 3相连。 每一级高温换热器都具有 用于载热流体介质输入和输出的输入口 （比如可以设置位于高温换热器的图 中的左侧）和输出口 （比如可以设置位于高温换热器的图中的右侧） ， 且第 一级行波环路的高温换热器输出口与第二级行波环路的高温换热器输入口通 过连接管相连通， 依此类推， 倒数第二级行波环路的高温换热器输出口与最 后一级行波环路的高温换热器输入口通过连接管相连通； 高温换热器的工作 温度从第一级行波环路开始到最后一级行波环路依次降低， 各级行波环路的 工作温度设计为比如从第一级到第六级的环路的高温换热器的平均温度分别 为 900°C, 800°C, 700°C, 600°C, 500°C, 400°C, 载热流体的初始温度为 950 °C, 每经过一个高温换热器其温度下降 100°C, 流出最后一个高温换热器时 的温度为 350°C, 这种同轴的行波环路级联形成的热声发动机不仅大大提高 了热源的利用率， 并且多级环路共用谐振管使得整个结构紧凑。
实施例 5:
如图 7所示， 为多个行波环路同轴布置的形式， 即所有回热器 1、 热緩 沖管 4和反馈管 5同轴布置。 第一级环路的回热器 1和反馈管 5位于整个同 轴结构的最外层， 第一级环路的热緩沖管 4位于整个同轴结构的最中心； 后 一级环路的回热器和反馈管位于前一级环路的内部， 而后一级环路的热緩沖 管位于前一级环路的外层， 这样多级行波环路形成嵌套的形式。 相比图 5和 6 而言， 该结构显然更加紧凑。 每一级高温换热器都具有用于载热流体介质 输入和输出的输入口 （比如可以设置位于高温换热器的上方表面）和输出口 (比如可以设置位于高温换热器的下方表面） ， 且第一级行波环路的高温换 热器输出口与第二级行波环路的高温换热器输入口通过管道（图中未示出） 相连通， 依此类推， 倒数第二级行波环路的高温换热器输出口与最后一级行 波环路的高温换热器输入口相连通； 高温换热器的工作温度从第一级行波环 路开始到最后一级行波环路依次降低， 比如对于图 7 中的四级环路来说， 从 第一级到第四级的环路的高温换热器的平均温度分别为 900°C, 800°C, 700 °C, 600°C, 载热流体的初始温度为 950°C, 每经过一个高温换热器其温度下 降 100°C,流出最后一个低温换热器时的温度为 550°C。另夕卜，如图 7中所示， 各级回热器与高温换热器和低温换热器之间的连接是倾斜安装的， 这样做的 好处就是增大了回热器与高温换热器和低温换热器的接触面积， 更加有利于 换热。
实施例 6:
如图 8 (b)所示， 本实施例中行波环路为同轴结构， 从谐振管 6开始依 次连接反馈管 5、 共用的低温换热器 3、 回热器 1, 回热器 1是被弯曲成具有 中空部的圓筒的形状， 热緩沖管 4共轴地设置在回热器 1的中空部； 高温换 热器 2采用流体导管的形式来使流体通过并与回热器 1进行换热， 该流体导 管从回热器 1的一端进入回热器 1, 穿过回热器 1后， 在回热器 1的另一端 出来， 在本实施例中该换热管路还延伸到从低温换热器 3 出来。 在本实施例 中， 比如热緩沖管 4的纵向总长度为 10厘米， 可以被分成四段， 在段与段之 间留有间隙 8, 间隙宽度不小于热緩沖管 4长度的百分之一， 比如间隙 8的 宽度为 1cm; 热緩沖管 4与端面 7之间的间隙为 lcm。 该结构实际上是将多个 同轴结构的行波环路合并到了一起， 如图 8 )所示， 因为每个环路中回热 器和热緩沖管的温度都是线型分布， 因此可以把各个回热器和热緩沖管按照 温度对应相等的原则合并到一起， 把热緩沖管分成几段每两段之间留有间隙 的设计结构是为了保持原来各个行波环路的流动特征， 图 8 (a)结构就等效 为图 8(b)中四个行波环路的级联，其工作温度比如分别设计为 1000K, 900K, 800K, 700K, 图 8 ) 中的各级行波环路的反馈管 5和谐振管 6也进行了合 并形成图 8 (b) 的结构。 考虑到高温换热器内载热流体经过换热后温度是逐 步降低的， 只要换热充分就可以直接将高温换热器的换热管路安装在回热器 内， 这样载热流体在经过回热器后温度直接降低到低温温度（比如室温） ， 最大限度的利用了热能。 图 8 (c)表示图 8 (b) 中沿 A— A线的剖面图， 可 以看出高温换热器的换热管路 2基本上是均匀地分布在回热器 1的内部， 本 实施例中是采用多根直线形的换热管路嵌入在回热器中， 当然也可以其他手 段实现换热管路嵌入回热器，比如采用至少一根螺旋形换热管路嵌入回热器。
实际上本实施例 6中， 如果不考虑保持各级行波环路的流动特征， 就不 用在热緩沖管 4上留出间隙， 而是将热緩沖管 4的整个壁全部开放（或者说 就是在本实施例的结构中去掉了由其四周壁形成的热緩沖管 4 , 而是保留回 热器 1 围成的内部空间作为起热緩沖作用的构造） ， 这样的热声发动机构造 实际上将无限多个行波环路级联而成， 可以将从高温热源到低温热源的热量 的高利用率达到极限。
最后应说明的是： 以上实施例仅用以说明本发明的技术方案， 而非对其 限制； 尽管参照前述实施例对本发明进行了详细的说明， 本领域的普通技术 人员应当理解： 其依然可以对前述各实施例所记载的技术方案进行修改， 或 者对其中部分技术特征进行等同替换； 而这些修改或者替换， 并不使相应技 术方案的本质脱离本发明各实施例技术方案的精神和范围。

Claims

权 利 要 求 书
1、 一种利用变温热源的热声发动机系统， 包括谐振管， 其特征是， 还包 括至少两级行波环路， 所有的行波环路共用所述谐振管， 每个所述行波环路 有高温换热器， 所述高温换热器具有用于载热流体介质输入和输出的输入口 和输出口， 前一级行波环路的所述高温换热器输出口与后一级行波环路的所 述高温换热器输入口相连通， 所述至少两级行波环路的所述高温换热器的工 作温度从前一级行波环路到后一级行波环路依次降低。
2、根据权利要求 1所述的热声发动机系统， 其特征是， 所述行波环路由 反馈管、 第一低温换热器、 回热器、 所述高温换热器、 热緩沖管和第二低温 换热器顺序连通构成， 各级所述行波环路在各自的第二低温换热器处且在所 述热緩沖器的外侧与共用的所述谐振管相连通。
3、根据权利要求 1所述的热声发动机系统， 其特征是， 各级所述行波环 路还包括低温换热器和反馈管， 在所述高温换热器和所述低温换热器之间设 置有回热器和热緩沖器， 所述回热器和所述热緩沖器之间有一个隔板， 所述 隔板延伸经过所述低温换热器并在所述低温换热器的外侧作为所述反馈管的 壁。
4、根据权利要求 1所述的热声发动机系统， 其特征是， 各级所述行波环 路共用一个低温换热器并分别还包括回热器和热緩沖管， 在前一级行波环路 的高温换热器、 回热器和共用的低温换热器围绕出的空间中设置后一级行波 环路。
5、根据权利要求 1所述的热声发动机系统， 其特征是， 在所述谐振管的 两端上， 分别连接有所述至少两级行波环路。
6、根据权利要求 3所述的热声发动机系统， 其特征是， 各级所述行波环 路的所述热緩沖管共轴地处于所述回热器的内部。
7、根据权利要求 6所述的热声发动机系统， 其特征是， 所有行波环路形 成圓周对称形的多级行波环路嵌套， 所有的所述回热器、 所述热緩沖管和所 述反馈管同轴布置。
8、根据权利要求 1所述的热声发动机系统， 其特征是， 各级行波环路还 包括回热器和一个共用的低温换热器， 所有的行波环路的高温换热器形成一 个整体高温换热器， 所述整体高温换热器设置在所述回热器的内部。
9、根据权利要求 8所述的热声发动机系统， 其特征是， 所述整体高温换 热器是由至少一根流体导管形成的， 设置在所述回热器的内部。
1 0、 根据权利要求 8或 9所述的热声发动机系统， 其特征是， 所述回热 器具有中空部的圓筒的形状， 所述系统还包括热緩沖管， 所述热緩沖管共轴 地设置在所述回热器的中空部， 所述热緩沖管在轴向上分成至少两段， 在所 述段与段之间具有用于使工作气体进入到所述热緩沖管的间隙， 所述间隙宽 度大于或等于所述热緩沖管长度的百分之一。
PCT/CN2008/070815 2007-04-25 2008-04-25 Système de moteur thermoacoustique utilisant une source de chaleur à variation de température WO2008131687A1 (fr)

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