JP2013117325A - Thermoacoustic refrigeration device - Google Patents
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本発明は、熱音響冷凍装置に関し、特に、気柱管内に封入された気体に熱音響効果により自励振動を発生させ、この自励振動を利用して冷凍処理を行う熱音響冷凍装置に関する。 The present invention relates to a thermoacoustic refrigeration apparatus, and more particularly to a thermoacoustic refrigeration apparatus that generates self-excited vibration by a thermoacoustic effect in a gas sealed in an air column tube and performs refrigeration using the self-excited vibration.
図１０に示すように、一般的な熱音響冷凍装置５０は、気体が封入されたループ状の気柱管５１に原動機５２と冷凍機５３とを配設して構成されている。熱音響冷凍装置５０では、原動機５２に外部からの熱が加えられると音波が発生し、この音波の音響パワーが気柱管５１を介して冷凍機５３に流れ込むと、冷凍機５３の温度を低下させることで、対象物の冷凍（冷却）に寄与するようになっている。 As shown in FIG. 10, a general thermoacoustic refrigeration apparatus 50 is configured by disposing a prime mover 52 and a refrigerator 53 in a loop-shaped air column tube 51 in which a gas is enclosed. In the thermoacoustic refrigeration apparatus 50, when external heat is applied to the prime mover 52, sound waves are generated, and when the acoustic power of the sound waves flows into the refrigerator 53 through the air column tube 51, the temperature of the refrigerator 53 decreases. By doing so, it contributes to the freezing (cooling) of the object.
原動機５２は、気柱管５１の軸方向に、常温よりも高温状態の熱源と熱交換を行う加熱部熱交換器５４と、常温の熱源と熱交換を行う常温部熱交換器５５と、これら加熱部・常温部の熱交換器５４，５５間で温度勾配を保持する再生器５６とを配置して構成されている。この原動機５２では、気柱管５１内の気体が加熱部熱交換器５４で常温よりも高温となり、常温部熱交換器５５で常温となることで、再生器５６に温度勾配が形成される。そして、この時に発生する熱エネルギの一部が力学的エネルギである音響エネルギに変換されて、気柱管５１内の気体が自励振動を起こすことで、気柱管５１内に音響振動、すなわち音波を発生させる。 The prime mover 52 includes, in the axial direction of the air column tube 51, a heating part heat exchanger 54 that exchanges heat with a heat source in a state higher than normal temperature, a normal temperature part heat exchanger 55 that exchanges heat with a normal temperature heat source, A regenerator 56 that maintains a temperature gradient between the heat exchangers 54 and 55 of the heating unit / normal temperature unit is arranged. In the prime mover 52, the gas in the air column pipe 51 becomes higher than the normal temperature in the heating part heat exchanger 54 and becomes normal temperature in the normal temperature part heat exchanger 55, thereby forming a temperature gradient in the regenerator 56. A part of the heat energy generated at this time is converted into acoustic energy, which is mechanical energy, and the gas in the air column tube 51 causes self-excited vibration, so that acoustic vibration in the air column tube 51, that is, Generate sound waves.
冷凍機５３は、気柱管５１の軸方向に、常温よりも低温の熱が取り出されるクーラ部熱交換器５７と、常温の熱源と熱交換を行う常温部熱交換器５８と、これらクーラ部・常温部の熱交換器５７，５８間で温度勾配を保持する再生器５９とを配置して構成されている。この冷凍機５３では、逆スターリングサイクルと同様のサイクルが行われ、クーラ部熱交換器５７の気体は常温よりも低温となる。そして、この低温と外部の媒体との間で熱交換が行われることで、対象物は冷凍（冷却）される。 The refrigerator 53 includes a cooler section heat exchanger 57 that extracts heat lower than room temperature in the axial direction of the air column tube 51, a room temperature section heat exchanger 58 that performs heat exchange with a room temperature heat source, and these cooler sections. A regenerator 59 that maintains a temperature gradient between the heat exchangers 57 and 58 in the normal temperature section is arranged. In this refrigerator 53, a cycle similar to the reverse Stirling cycle is performed, and the gas in the cooler part heat exchanger 57 is cooler than room temperature. And an object is frozen (cooled) by heat exchange between this low temperature and an external medium.
原動機５２及び、冷凍機５３の常温部熱交換器５５，５８では、図示しない外部から供給される冷却水等の熱媒体との熱交換により、気体の温度は常温に保たれている。 In the normal temperature part heat exchangers 55 and 58 of the prime mover 52 and the refrigerator 53, the temperature of the gas is maintained at normal temperature by heat exchange with a heat medium such as cooling water supplied from the outside (not shown).
ところで、上述した従来の熱音響冷凍装置では、封入されている気体は気柱管内を移動して循環することができる。そのため、クーラ部熱交換器５７で低温となった気体（冷気）が拡散すると、この気体がクーラ部熱交換器５７から離間することで、クーラ部熱交換器５７の冷却効率は低下する。 By the way, in the conventional thermoacoustic refrigeration apparatus mentioned above, the enclosed gas can move and circulate within the air column tube. Therefore, when the gas (cold air) having a low temperature is diffused in the cooler part heat exchanger 57, the gas is separated from the cooler part heat exchanger 57, so that the cooling efficiency of the cooler part heat exchanger 57 is lowered.
例えば、図１０に示す気柱管５１においては、気柱管５１内に封入された気体は、冷凍機５３のクーラ部熱交換器５７から再生器５９、常温部熱交換器５８を通り、ループを通って原動機５２へと移動する。さらに、気体は原動機５２の加熱部熱交換器５４から再生器５６、常温部熱交換器５５を通り、ループを通って冷凍機５３へと移動する。その結果、気柱管５１内には、図１０中に矢印で示すようなループに沿った循環流が発生する。 For example, in the air column tube 51 shown in FIG. 10, the gas sealed in the air column tube 51 passes from the cooler part heat exchanger 57 of the refrigerator 53 through the regenerator 59 and the room temperature part heat exchanger 58, and loops. And move to the prime mover 52. Further, the gas moves from the heating section heat exchanger 54 of the prime mover 52 through the regenerator 56 and the normal temperature section heat exchanger 55 to the refrigerator 53 through the loop. As a result, a circulation flow along a loop as shown by an arrow in FIG.
このような循環流を抑制すべく、例えば図１１に示すように、気柱管５１内のクーラ部熱交換器５７と隣接する位置に、気体の流れを遮断する遮断壁６０を配設することが考えられる。遮断壁６０を設けることで、クーラ部熱交換器５７から気柱管５１を通って常温部熱交換器５８側に流れるエネルギが遮断され、冷凍機出力の向上を図ることができる。 In order to suppress such a circulating flow, for example, as shown in FIG. 11, a blocking wall 60 for blocking the gas flow is provided at a position adjacent to the cooler heat exchanger 57 in the air column pipe 51. Can be considered. By providing the blocking wall 60, the energy flowing from the cooler section heat exchanger 57 through the air column tube 51 to the normal temperature section heat exchanger 58 side is blocked, and the output of the refrigerator can be improved.
しかしながら、原動機５２側の出力が大きくなると、気体の振動振幅が増大されて再生器５９よりも長くなり（図１１中の矢印Ｘ参照）、クーラ部熱交換器５７の冷凍エネルギが再生器５９を介して常温部熱交換器５８に運ばれる所謂ドリームパイプ効果により、出力の低下を引き起こす可能性がある。 However, when the output on the prime mover 52 side is increased, the vibration amplitude of the gas is increased and becomes longer than that of the regenerator 59 (see arrow X in FIG. 11), and the refrigeration energy of the cooler section heat exchanger 57 The so-called dream pipe effect that is conveyed to the room temperature heat exchanger 58 through the air may cause a decrease in output.
また、冷凍機５３や遮断壁６０の外径を大きくして、気柱管５１にこれら冷凍機５３と遮断壁６０とを収容する二つの拡径部を形成する構造も考えられる。しかしながら、二つの拡径部を形成する構造では、クーラ部熱交換器５８と遮断壁６０との間の管路径の変化による損失を増大させる虞がある。 Further, a structure in which the outside diameters of the refrigerator 53 and the blocking wall 60 are increased to form two enlarged diameter portions for accommodating the refrigerator 53 and the blocking wall 60 in the air column pipe 51 is also conceivable. However, in the structure in which the two enlarged diameter portions are formed, there is a risk of increasing loss due to a change in the pipe diameter between the cooler heat exchanger 58 and the blocking wall 60.
本発明は、このような点に鑑みてなされたもので、その目的は、クーラ部熱交換器の冷凍エネルギが再生器を介して常温部熱交換器に運ばれるドリームパイプ効果及び、管路径の変化による損失を低減して、冷凍機の出力を効果的に向上させることにある。 The present invention has been made in view of the above points, and its purpose is to achieve a dream pipe effect in which the refrigeration energy of the cooler section heat exchanger is conveyed to the normal temperature section heat exchanger via the regenerator, and the pipe diameter. It is to reduce the loss due to the change and to effectively improve the output of the refrigerator.
上記目的を達成するため、本発明の熱音響冷凍装置は、気体が封入される気柱管と、前記気柱管の軸方向に、常温よりも高温の熱源と熱交換を行う第１の熱交換器、温度勾配を保持する第１の再生器、及び、常温の熱源と熱交換を行う第２の熱交換器を配置した原動機と、前記気柱管の軸方向に、常温よりも低温の熱が取り出される第３の熱交換器、温度勾配を保持する第２の再生器、及び、常温の熱源と熱交換を行う第４の熱交換器を配置した冷凍機と、前記第３の熱交換器と隣接する前記気柱管に配置されて該気柱管に封入された気体の循環流を抑止する遮断壁とを備える熱音響冷凍装置であって、前記冷凍機及び前記遮断壁を配置した前記気柱管に、該気柱管よりも内径が長く、かつ、その軸方向に沿って同一径で延在する拡径部を形成すると共に、前記冷凍機及び前記遮断壁の外径を前記拡径部の内径と同一径に形成して該拡径部内に収容したことを特徴とする。 In order to achieve the above object, the thermoacoustic refrigeration apparatus of the present invention includes an air column tube in which a gas is sealed, and a first heat that exchanges heat with a heat source higher than room temperature in the axial direction of the air column tube. A motor having a exchanger, a first regenerator for maintaining a temperature gradient, and a second heat exchanger for exchanging heat with a normal temperature heat source, and in the axial direction of the air column tube, A third heat exchanger from which heat is extracted, a second regenerator for maintaining a temperature gradient, a refrigerator having a fourth heat exchanger for exchanging heat with a normal temperature heat source, and the third heat A thermoacoustic refrigeration apparatus comprising an exchanger and a blocking wall disposed in the air column tube adjacent to the air column tube to suppress a circulation flow of gas sealed in the air column tube, wherein the refrigerator and the blocking wall are disposed In the air column tube, an enlarged diameter portion having an inner diameter longer than that of the air column tube and extending with the same diameter along the axial direction is formed. While, characterized by being accommodated in the refrigerator and the enlarged inside diameter portion of the outer diameter of the blocking wall formed on the inner diameter and the same diameter of the enlarged diameter portion.
また、前記拡径部内の前記遮断壁が配置される位置を、前記第３の熱交換器の側面と前記遮断壁との距離が該遮断壁の最大振幅の５倍よりも短く、かつ、最大振幅の半分の値よりも長くなる位置に設定してもよい。 Further, the position where the blocking wall is disposed in the enlarged diameter portion is set such that the distance between the side surface of the third heat exchanger and the blocking wall is shorter than five times the maximum amplitude of the blocking wall, and the maximum You may set to the position which becomes longer than the half value of an amplitude.
本発明の熱音響冷凍装置によれば、クーラ部熱交換器の冷凍エネルギが再生器を介して常温部熱交換器に運ばれるドリームパイプ効果及び、管路径の変化による損失を低減して、冷凍機の出力を効果的に向上することができる。 According to the thermoacoustic refrigeration apparatus of the present invention, the refrigeration energy of the cooler section heat exchanger is transferred to the room temperature section heat exchanger via the regenerator, and the loss due to the change in the pipe diameter is reduced, and the refrigeration The output of the machine can be improved effectively.
以下、図１〜４に基づいて、本発明の一実施形態に係る熱音響冷凍装置を説明する。同一の部品には同一の符号を付してあり、それらの名称および機能も同じである。したがって、それらについての詳細な説明は繰返さない。 Hereinafter, based on FIGS. 1-4, the thermoacoustic refrigerating apparatus which concerns on one Embodiment of this invention is demonstrated. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.
図１に示すように、本実施形態の熱音響冷凍装置１は、気体が封入されるループ状の気柱管２と、気柱管２よりも内径を長く形成された拡径部１１と、気柱管２に配置された原動機３と、拡径部１１内に配置された冷凍機４と、拡径部１１内に配置されて気体の循環流を抑止する遮断壁１２とを有する。 As shown in FIG. 1, the thermoacoustic refrigeration apparatus 1 of the present embodiment includes a loop-shaped air column tube 2 in which a gas is enclosed, a diameter-enlarged portion 11 having an inner diameter longer than the air column tube 2, It has a prime mover 3 arranged in the air column tube 2, a refrigerator 4 arranged in the enlarged diameter portion 11, and a blocking wall 12 arranged in the enlarged diameter portion 11 to suppress a gas circulation flow.
原動機３は、気柱管２の長手方向（以下、軸方向という）に、常温よりも高温状態の熱源と熱交換を行う加熱部熱交換器（第１の熱交換器）５と、常温の熱源と熱交換を行う常温部熱交換器（第２の熱交換器）６と、これら加熱部・常温部の熱交換器５，６間で温度勾配を保持する再生器（第１の再生器）７とを配置して構成されている。 The prime mover 3 includes a heating section heat exchanger (first heat exchanger) 5 that performs heat exchange with a heat source in a longitudinal direction of the air column tube 2 (hereinafter referred to as an axial direction) with a heat source in a higher temperature than normal temperature, A normal temperature section heat exchanger (second heat exchanger) 6 that performs heat exchange with the heat source, and a regenerator (first regenerator) that maintains a temperature gradient between the heat exchangers 5 and 6 of the heating section and the normal temperature section ) 7 is arranged.
冷凍機４は、拡径部１１の軸方向に、常温よりも低温の熱が取り出されるクーラ部熱交換器（第３の熱交換器）８と、常温の熱源と熱交換を行う常温部熱交換器（第４の熱交換器）９と、これらクーラ部・常温部の熱交換器８，９間で温度勾配を保持する再生器（第２の再生器）１０とを配置して構成されている。なお、冷凍機４を構成するクーラ部熱交換器８、常温部熱交換器９及び、再生器１０の外径は、拡径部１１の内径と同一径に形成されている。 The refrigerator 4 includes a cooler part heat exchanger (third heat exchanger) 8 that extracts heat lower than room temperature in the axial direction of the enlarged diameter part 11, and a room temperature partial heat that performs heat exchange with a room temperature heat source. An exchanger (fourth heat exchanger) 9 and a regenerator (second regenerator) 10 that maintains a temperature gradient between the heat exchangers 8 and 9 in the cooler portion and the normal temperature portion are arranged. ing. The outer diameters of the cooler part heat exchanger 8, the room temperature part heat exchanger 9, and the regenerator 10 constituting the refrigerator 4 are formed to be the same diameter as the inner diameter of the enlarged diameter part 11.
拡径部１１は、図２に示すように、その内径を拡径部１１の内径よりも長く（本実施形態では約２倍）形成されており、気柱管２の軸方向に沿って同一径で延在して設けられている。この拡径部１１の内部には、冷凍機４及び遮断壁１２が適切な間隔を隔てて収容されている。 As shown in FIG. 2, the enlarged diameter portion 11 has an inner diameter longer than the inner diameter of the enlarged diameter portion 11 (about twice in this embodiment), and is the same along the axial direction of the air column tube 2. It is provided extending in diameter. Inside the enlarged diameter portion 11, the refrigerator 4 and the blocking wall 12 are accommodated at an appropriate interval.
遮断壁１２は、拡径部１１内に位置して気柱管２内の気体の振動に随伴して振動するように、その周縁部の全周を拡径部１１の内周面に固定されている。すなわち、遮断壁１２は、気柱管２内の気体の振動により、その中央部が気柱管２の軸方向に振動して破線及び二点鎖線の状態に変形するように構成されている。この遮断壁１２は、気柱管２内の気体が反対側に漏れない程度の気密性を有し、かつ、その中央部が振動できる程度の柔軟性（弾性）を有することが好ましい。このような遮断壁１２としては、例えば比較的厚さが薄く形成された金属、ガラス、セラミックス、樹脂、ゴム、繊維などがある。 The blocking wall 12 is fixed to the inner peripheral surface of the enlarged diameter portion 11 so that the entire circumference of the peripheral wall is located in the enlarged diameter portion 11 and vibrates accompanying the vibration of the gas in the air column tube 2. ing. That is, the blocking wall 12 is configured such that the central portion thereof vibrates in the axial direction of the air column tube 2 due to the vibration of the gas in the air column tube 2 and deforms into a broken line and a two-dot chain line state. The blocking wall 12 is preferably airtight enough to prevent the gas in the air column tube 2 from leaking to the opposite side, and has flexibility (elasticity) such that the central portion can vibrate. Examples of such a blocking wall 12 include metal, glass, ceramics, resin, rubber, fiber, and the like that are formed to be relatively thin.
なお、本実施形態において、遮断壁１２が拡径部１１の内周面に固定される位置は、クーラ部熱交換器８の側面からの距離が遮断壁１２の最大振幅の５倍よりも短くなる位置に設定されている。これは、遮断壁１２を設けたことにより循環流は抑止されるが、遮断壁１２がクーラ部熱交換器８から遠くなると冷気の拡散が大きくなり、期待した効果を得られなくなるためである。遮断壁１２の位置は、クーラ部熱交換器８の側面から遮断壁１２の最大振幅の５倍よりも近い位置が望ましく、最大振幅の２倍、１倍と近づくほど好適となる。最適位置は、冷気の拡散が最も小さくなり、かつ、クーラ部熱交換器８の側面と遮断壁１２との接触（干渉）を回避できる最大振幅の半分よりも若干長くなる位置である。 In the present embodiment, the position where the blocking wall 12 is fixed to the inner peripheral surface of the enlarged diameter portion 11 is such that the distance from the side surface of the cooler portion heat exchanger 8 is shorter than five times the maximum amplitude of the blocking wall 12. Is set to a position. This is because the circulation flow is suppressed by providing the blocking wall 12, but if the blocking wall 12 is far from the cooler heat exchanger 8, the diffusion of cold air increases, and the expected effect cannot be obtained. The position of the blocking wall 12 is desirably a position closer to 5 times the maximum amplitude of the blocking wall 12 from the side surface of the cooler heat exchanger 8, and the closer to 2 times or 1 time the maximum amplitude, the more suitable. The optimum position is a position where the diffusion of the cold air is minimized and slightly longer than half of the maximum amplitude at which contact (interference) between the side surface of the cooler section heat exchanger 8 and the blocking wall 12 can be avoided.
次に、本実施形態に係る熱音響冷凍装置１による作用効果について説明する。 Next, the effect by the thermoacoustic refrigeration apparatus 1 which concerns on this embodiment is demonstrated.
本実施形態の熱音響冷凍装置１では、気柱管２の拡径部１１内に収容された再生器１０は、その外径を気柱管２の内径よりも長く形成されている。すなわち、再生器１０の外径を長く（再生器１０を太く）形成したことで、図１０に示すような再生器５９を気柱管５１と同一径に形成した従来構造に比べて内部気体の振幅は短く抑制される（図２の矢印Ｙ参照）。結果として、内部気体の振幅は再生器１０内に収められ、クーラ部熱交換器８の冷凍エネルギが再生器１０を介して常温部熱交換器９に運ばれる所謂ドリームパイプ効果を効果的に抑制することができる。 In the thermoacoustic refrigeration apparatus 1 of the present embodiment, the regenerator 10 accommodated in the enlarged diameter portion 11 of the air column tube 2 has an outer diameter longer than the inner diameter of the air column tube 2. That is, by forming the regenerator 10 to have a long outer diameter (thickening the regenerator 10), the regenerator 59 as shown in FIG. The amplitude is suppressed short (see arrow Y in FIG. 2). As a result, the amplitude of the internal gas is accommodated in the regenerator 10, and the so-called dream pipe effect in which the refrigeration energy of the cooler heat exchanger 8 is conveyed to the normal temperature heat exchanger 9 via the regenerator 10 is effectively suppressed. can do.
したがって、本実施形態の熱音響冷凍装置１によれば、ドリームパイプ効果を低減することが可能になると共に、原動機３の出力が大きくなった場合においても冷凍機４の出力を効果的に向上することができる。 Therefore, according to the thermoacoustic refrigeration apparatus 1 of the present embodiment, the dream pipe effect can be reduced, and the output of the refrigerator 4 can be effectively improved even when the output of the prime mover 3 is increased. be able to.
また、本実施形態の熱音響冷凍装置１では、冷凍機４及び遮断壁１２が収容される拡径部１１は、気柱管２の軸方向に沿って同一径で延在して形成されている。すなわち、図３に示すように、冷凍機４が収容される拡径部１１ａと遮断壁１２が収容される拡径部１１ｂとを別体に形成した場合は、クーラ部熱交換器８と遮断壁１２との間の管路径の変化による損失を増大させる虞がある。これに対し、本実施形態の熱音響冷凍装置１によれば、クーラ部熱交換器８と遮断壁１２との間の管路径は同一に形成されているので、管路径の変化による損失を効果的に低減することができる。 Further, in the thermoacoustic refrigeration apparatus 1 of the present embodiment, the enlarged diameter portion 11 in which the refrigerator 4 and the blocking wall 12 are accommodated is formed to extend with the same diameter along the axial direction of the air column tube 2. Yes. That is, as shown in FIG. 3, when the enlarged diameter portion 11 a in which the refrigerator 4 is accommodated and the enlarged diameter portion 11 b in which the blocking wall 12 is accommodated are formed separately, the cooler portion heat exchanger 8 and the cutoff are formed. There is a risk of increasing the loss due to the change in the diameter of the pipe line with the wall 12. On the other hand, according to the thermoacoustic refrigeration apparatus 1 of the present embodiment, since the pipe diameter between the cooler part heat exchanger 8 and the blocking wall 12 is formed to be the same, the loss due to the change in the pipe diameter is effective. Can be reduced.
また、本実施形態の熱音響冷凍装置１では、気柱管２内の気体の循環流を抑止する遮断壁１２の外径は、気柱管２の内径よりも長く形成されている。すなわち、本実施形態の熱音響冷凍装置１では、図４（ａ）に示す気柱管５１内に遮断壁６０を直接的に設けた従来構造と比べて、遮断壁１２の表面積は拡径部１１の分だけ拡張して形成されている。その結果、遮断壁１２の振幅は、従来構造の遮断壁６０の振幅に比べて小さく抑制されるようになっている（図４（ｂ）参照）。 Further, in the thermoacoustic refrigeration apparatus 1 of the present embodiment, the outer diameter of the blocking wall 12 that suppresses the circulation flow of the gas in the air column tube 2 is formed longer than the inner diameter of the air column tube 2. That is, in the thermoacoustic refrigeration apparatus 1 of the present embodiment, the surface area of the blocking wall 12 is larger than that of the conventional structure in which the blocking wall 60 is directly provided in the air column tube 51 shown in FIG. It is formed by expanding by 11 parts. As a result, the amplitude of the blocking wall 12 is suppressed to be smaller than the amplitude of the blocking wall 60 having the conventional structure (see FIG. 4B).
したがって、遮断壁１２が気柱管２内の気体の振動と随伴して大きく振動することを効果的に抑制できると共に、遮断壁１２がクーラ部熱交換器８の側面に接触（干渉）して破損することを確実に防止することができる。 Therefore, it is possible to effectively suppress the shielding wall 12 from vibrating greatly accompanying the vibration of the gas in the air column tube 2, and the shielding wall 12 comes into contact (interference) with the side surface of the cooler section heat exchanger 8. It is possible to reliably prevent breakage.
また、本実施形態の熱音響冷凍装置１では、遮断壁１２の拡径部１１内に固定される位置は、クーラ部熱交換器８の側面からの距離が遮断壁１２の最大振幅の５倍よりも短くなる位置に設定されている。 Moreover, in the thermoacoustic refrigeration apparatus 1 of this embodiment, the position fixed in the diameter-expanded portion 11 of the barrier wall 12 is such that the distance from the side surface of the cooler heat exchanger 8 is five times the maximum amplitude of the barrier wall 12. The position is set to be shorter.
したがって、遮断壁１２がクーラ部熱交換器８から離間することで引き起こされる冷気の拡散を防止することができると共に、熱音響冷凍装置１の冷凍性能を効果的に向上することができる。 Therefore, the diffusion of the cold air caused by the separation of the blocking wall 12 from the cooler heat exchanger 8 can be prevented, and the refrigeration performance of the thermoacoustic refrigeration apparatus 1 can be effectively improved.
なお、本発明は、上述の実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で、適宜変形して実施することが可能である。 In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.
例えば、図５に示すように、気柱管２を冷凍機４が配設された冷凍機ループ管２ａと、原動機３が配設された原動機ループ管２ｂと、これら二つのループ管２ａ，２ｂを相互に接続する直線状の接続管２ｃとを備え構成してもよい。 For example, as shown in FIG. 5, the air column tube 2 includes a refrigerator loop tube 2a in which the refrigerator 4 is disposed, a motor loop tube 2b in which the prime mover 3 is disposed, and these two loop tubes 2a and 2b. And a straight connection pipe 2c that connects the two to each other.
また、図６に示すように、気柱管２を冷凍機４が配設された冷凍機ループ管２ａと、冷凍機ループ管２ａに接続されると共に原動機３が配設された直線状の接続管２ｃとを備えて構成してもよく、図７に示すように、気柱管２を原動機３が配設された原動機ループ管２ｂと、原動機ループ管２ｂに接続されると共に冷凍機４が配設された直線状の接続管２ｃとを備えて構成してもよい。さらに、図８に示すように気柱管２を直線状の配管のみで構成してもよい。 Further, as shown in FIG. 6, the air column tube 2 is connected to the refrigerator loop tube 2a in which the refrigerator 4 is disposed, and the linear connection in which the prime mover 3 is disposed while being connected to the refrigerator loop tube 2a. As shown in FIG. 7, the air column tube 2 is connected to the motor loop tube 2b in which the motor 3 is disposed, and the motor loop tube 2b and the refrigerator 4 is You may comprise and comprise the linear connection pipe | tube 2c arrange | positioned. Furthermore, as shown in FIG. 8, the air column tube 2 may be composed of only a straight line.
また、図９に示すように、遮断壁１２をピストン２１と一対のバネ部材２２とを備え構成してもよい。ピストン２１は、気柱管２の長手方向に間隔を隔てて対向配置された一対のピストンヘッド２３と、これら一対のピストンヘッド２３を連結するピストンロッド２４とを有する。ピストンロッド２４は一対のバネ部材２２により気柱管２の長手方向に移動可能に支持されている。気柱管２内の気体が振動すると、ピストン２１は破線及び、二点鎖線で示すように気柱管２内を長手方向に摺動移動して振動するように構成されている。係る構造により、遮断壁１２の全体は、図１〜８に示すものに比べて気柱管２の長手方向の幅は長くなるが、厚みのない剛体の遮断壁に仮想的に置き換えることが可能となる。 As shown in FIG. 9, the blocking wall 12 may include a piston 21 and a pair of spring members 22. The piston 21 includes a pair of piston heads 23 that are opposed to each other with a space in the longitudinal direction of the air column tube 2, and a piston rod 24 that couples the pair of piston heads 23. The piston rod 24 is supported by a pair of spring members 22 so as to be movable in the longitudinal direction of the air column tube 2. When the gas in the air column tube 2 vibrates, the piston 21 is configured to vibrate by sliding in the air column tube 2 in the longitudinal direction as indicated by a broken line and a two-dot chain line. With this structure, the entire barrier wall 12 has a longer width in the longitudinal direction of the air column tube 2 than that shown in FIGS. 1 to 8, but can be virtually replaced with a rigid barrier wall having no thickness. It becomes.
１ 熱音響冷凍装置
２ 気柱管
３ 原動機
４ 冷凍機
５ 加熱部熱交換器（第１の熱交換器）
６ 常温部熱交換器（第２の熱交換器）
７ 再生器（第１の再生器）
８ クーラ部熱交換器（第３の熱交換器）
９ 常温部熱交換器（第４の熱交換器）
１０ 再生器（第２の再生器）
１１ 拡径部
１２ 遮断壁
DESCRIPTION OF SYMBOLS 1 Thermoacoustic refrigeration apparatus 2 Air column pipe 3 Prime mover 4 Refrigerator 5 Heating part heat exchanger (1st heat exchanger)
6 Room temperature heat exchanger (second heat exchanger)
7 Regenerator (first regenerator)
8 Cooler heat exchanger (third heat exchanger)
9 Room temperature heat exchanger (fourth heat exchanger)
10 Regenerator (second regenerator)
11 Expanded portion 12 Blocking wall
Claims (2)
前記気柱管の軸方向に、常温よりも高温の熱源と熱交換を行う第１の熱交換器、温度勾配を保持する第１の再生器、及び、常温の熱源と熱交換を行う第２の熱交換器を配置した原動機と、
前記気柱管の軸方向に、常温よりも低温の熱が取り出される第３の熱交換器、温度勾配を保持する第２の再生器、及び、常温の熱源と熱交換を行う第４の熱交換器を配置した冷凍機と、
前記第３の熱交換器と隣接する前記気柱管に配置されて該気柱管に封入された気体の循環流を抑止する遮断壁と、を備える熱音響冷凍装置であって、
前記冷凍機及び前記遮断壁を配置した前記気柱管に、該気柱管よりも内径が長く、かつ、その軸方向に沿って同一径で延在する拡径部を形成すると共に、前記冷凍機及び前記遮断壁の外径を前記拡径部の内径と同一径に形成して該拡径部内に収容したことを特徴とする熱音響冷凍装置。 An air column tube filled with gas,
In the axial direction of the air column tube, a first heat exchanger that exchanges heat with a heat source having a temperature higher than normal temperature, a first regenerator that maintains a temperature gradient, and a second heat exchanger that performs heat exchange with a heat source at normal temperature A prime mover with a heat exchanger of
A third heat exchanger that extracts heat lower than normal temperature in the axial direction of the air column tube, a second regenerator that maintains a temperature gradient, and fourth heat that exchanges heat with a normal temperature heat source. A refrigerator with an exchanger,
A thermoacoustic refrigeration apparatus comprising: a blocking wall disposed in the air column pipe adjacent to the third heat exchanger and suppressing a circulation flow of gas sealed in the air column pipe,
The air column tube in which the refrigerator and the blocking wall are arranged has an inner diameter longer than that of the air column tube and has an enlarged diameter portion extending with the same diameter along the axial direction, and the refrigeration unit The thermoacoustic refrigeration apparatus is characterized in that the outer diameter of the machine and the blocking wall is formed to be the same as the inner diameter of the enlarged diameter portion and is accommodated in the enlarged diameter portion.
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