JP2011099599A - Heat transport pipe - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inexpensive heat transport pipe with a simple configuration being a heat transport pipe transporting heat from a high temperature side heat exchange part to a low temperature side heat exchange part, capable of controlling heat transport, capable of deriving work, having little restraints of an installation attitude, and easy in connection with a heating object. <P>SOLUTION: The heat transport pipe includes a stack 4, a high temperature side heat exchanger 5 provided on a high temperature end 4c of the stack 4, a low temperature side heat exchanger 3 provided on a low temperature end 4d of the stack 4, and an expander 2 having an expansion chamber 2d communicated with the low temperature side heat exchanger 3. Pressure oscillation and a reciprocating flow are generated in a working fluid by the expander 2, heat Q1 transferred from the high temperature side heat exchanger 5 to the high temperature end 4c of the stack is transferred to the low temperature end 4d via a heat storage body 4b, part of the heat Q1 is discharged from the low temperature side heat exchanger 3, the rest is used as a work flow of the low temperature end 4d, and it is transferred to the expansion chamber 2d and output from the expander 2. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat transport pipe that transports heat from a heat input source to a location away from the heat input source.

  As a heat transport pipe of the prior art, as shown in FIG. 7, a wick 33 is lined in a pipe 31 closed at both ends, a working medium is enclosed, and heat is transported from a high temperature to a low temperature with a slight temperature difference. 30 is known. When the heat pipe 30 heats the high temperature part (evaporation part) 31a on one end side of the pipe 31, the liquid 32a of the working medium 32 in the wick 33 evaporates to become a vapor 32b, and the low temperature part (condensation part) on the other end side. ) Move to 31b. The steam 32 b that has moved to the low temperature portion 31 b is cooled there to become a liquid and returns to the high temperature portion 31 a by the capillary action of the wick 33. In this way, the working medium undergoes a phase change in the pipe 31 and transports heat from the high temperature part 31a to the low temperature part 31b.

  In addition, as shown in FIG. 8, a sealing device 41 penetrating a partition wall 46 that separates the high temperature side medium 44 and the low temperature side medium 45 is rotatably attached to the partition wall 46 with an axial point 43. A thermosiphon 40 enclosing a working medium 42 is disclosed. The thermosiphon 40 has no wick in the hermetic seal 41, and circulates the working medium 42 by gravity using the density difference between the liquid 42a and the vapor 42b of the working medium 42. That is, the liquid 42a having a high density in the hermetic seal 41 moves downward and the vapor 42b having a low density moves upward, so that the working medium 42 has a high-temperature part (evaporation part) 41a and a low-temperature part ( It circulates between (condensing part) 41b. Therefore, the high temperature part 41a of the sealing device 41 where the liquid 42a of the working medium 42 evaporates is located below the low temperature part 41b where the vapor 42b condenses. The thermosiphon 40 transports the heat of the high temperature side medium 44 to the low temperature side medium 45 when the high temperature side medium 44 and the low temperature side medium 45 are replaced with respect to the partition wall 46. As indicated by the alternate long and short dash line, the high temperature portion 41a is rotated so as to be positioned above the low temperature portion 41b (see, for example, Patent Document 1).

  Further, as shown in FIG. 9, an expansion chamber 52 formed by a piston 51a and a cylinder 51b provided in the expander 51, a normal temperature side heat exchanger 53, a pulse tube 54, a high temperature side heat exchanger 55, A thermoacoustic engine 50 is disclosed in which a regenerator (heat accumulator) 56 filled with a heat storage material 56a and a room temperature side heat exchanger 57 are connected in order (see, for example, FIG. 2 of Patent Document 2).

  Further, a thermoacoustic engine 60 shown in FIG. 10 is disclosed in order to cause the pressure vibration generated in the regenerator 56 to have a traveling wave significantly larger than a standing wave. That is, the thermoacoustic engine 60 includes an expansion chamber 62 formed by a piston 61a and a cylinder 61b included in the expander 61, a second normal temperature side heat exchanger 63, a pulse tube 64, and a high temperature side heat exchanger 65. The regenerator 66 filled with the heat storage material 66a, the first normal temperature side heat exchanger 67, and the compression chamber 69 formed by the piston 68a and the cylinder 68b of the compressor 68 are sequentially connected. Originally, in order to obtain work, the thermoacoustic engine 60 heats the high temperature side heat exchanger 65 to a high temperature (for example, approximately 600 ° C.), and the first normal temperature side heat exchanger 67 and the second normal temperature side heat exchanger 63. Is cooled to room temperature (for example, approximately 60 ° C.) (see, for example, FIG. 3 of Patent Document 2).

JP 58-182086 A JP 2006-112260 A

  However, the heat pipe 30 shown in FIG. 7 circulates the operating medium 32 by the capillary action of the wick 33 and transports heat, so that heat generated by the device attached to the high temperature part 31a of the heat pipe 30 is dissipated from the low temperature part 31b. The heat transport to be performed is always in an operating state. For this reason, there is a problem that the amount of heat release (heat transport amount) corresponding to the change in the state of the heat source of the device cannot be controlled. Further, for the same reason as described above, the heat pipe 30 can transport the heat even at a position where the position of the low temperature part 31b which is the condensing part is lower than the high temperature part 31a which is the evaporation part by tilting the pipe 31. There is a problem that the heat transport capability is lowered depending on the angle at which 31b is located on the lower side.

  Since the thermosiphon 40 of FIG. 8 circulates the working medium 42 using gravity, the installation posture of the thermosiphon 40 is lower in the position of the high temperature part 41a than the position of the low temperature part 41b, and there is a structural limitation. Moreover, the heat pipe 30 and the thermosiphon 40 utilize the phase change of the working fluid. In order to make the temperature difference between the evaporation part and the condensation part, it is necessary to make a pressure difference between the evaporation part and the condensation part according to it, but since the differential pressure is not positively applied by a pump etc., The pressure difference is small. Therefore, the prior art heat transport device is limited to heat transport in a state where the temperature difference between the evaporation temperature and the condensation temperature is small. Further, since the condensation temperature of the working fluid is a specific temperature determined by the type of the working fluid, the temperature range in which the heat transport device of the prior art is used is also limited.

  The thermoacoustic engine 50 of FIG. 9 is not advantageous in terms of configuration when the high temperature side heat exchanger 55 (heat input part) is present in the center of the apparatus and the heat input part is connected to the object to be heated. That is, since both ends of the high temperature side heat exchanger 55 to which the thermoacoustic engine 50 receives heat are connected to the pulse tube 54 and the regenerator 56, the heat input to the high temperature side heat exchanger 55 is the high temperature side heat exchanger. 55 through the outer peripheral surface. For this reason, it is difficult to install a device that is a heat input source, the transfer area for heat input decreases, and the temperature difference increases during heat input performed through the outer peripheral surface. Further, since the thermoacoustic engine 50 includes the pulse tube 54 and the room temperature side heat exchanger 53, there is a problem that the configuration is complicated and the cost is increased.

  Also in the thermoacoustic engine 60 of FIG. 10, the high temperature side heat exchanger 65 (heat input part) exists in the center part of the apparatus, and it is not advantageous in terms of configuration when the heat input part is connected to the object to be heated. That is, since both ends of the high temperature side heat exchanger 65 that receives heat from the thermoacoustic engine 60 are connected to the pulse tube 64 and the regenerator 66, the heat input to the high temperature side heat exchanger 65 is the high temperature side heat exchanger. This is done via 65 outer peripheral surfaces. For this reason, it is difficult to install a device that is a heat input source, the transfer area for heat input decreases, and the temperature difference increases during heat input performed through the outer peripheral surface. In addition, the thermoacoustic engine 60 includes a pulse tube 64, a second room temperature side heat exchanger 63, and an expander 61, and requires a means for providing a phase difference between the expansion chamber 62 and the compression chamber 69. There is a problem that the configuration is complicated and the cost is high.

  The present invention has been made in view of the above problems, and is a heat transport pipe that transports heat from a high-temperature side heat exchange section to a low-temperature side heat exchange section, and can control heat transport and take out work. Another object of the present invention is to provide a heat transport pipe with less restrictions on the installation posture, easy connection to a heated object, a simple configuration, and low cost.

  In order to solve the above-mentioned problem, the invention described in claim 1 includes a stack having a heat storage body and having a temperature gradient from high temperature to low temperature, a high temperature side heat exchange section provided on the high temperature side of the stack, A heat transport pipe provided with a low temperature side heat exchange section provided on the low temperature side of the stack and an expander having an expansion chamber adjacent to and in communication with the low temperature side heat exchange section, Pressure oscillation and reciprocating flow are generated in the working fluid in the stack, and the stack is transmitted from the high temperature side heat exchange part to the high temperature side of the stack due to a temperature difference between the working fluid and the heat storage body. The generated heat is transported from the high temperature side of the stack to the low temperature side via the heat storage body, transferred from the low temperature side of the stack to the low temperature side heat exchange unit, and transferred to the low temperature side heat exchange unit. Part of the heat is from the low-temperature side heat exchanger Is heated, the rest is configured to be output from the expander is transmitted to the expansion chamber.

According to a second aspect of the present invention, the high temperature side heat exchanger is provided with a plurality of flow path holes provided at the high temperature end of the stack and having one end opened in the stack and the other end closed. And
The low temperature side heat exchanging section is a low temperature side heat exchanger provided with a plurality of flow path holes provided at a low temperature end of the stack, one end opening in the stack and the other end opening in the expansion chamber.

  The invention according to claim 3 is a configuration in which the expander has a function of a motor and a function of a generator.

  The invention according to claim 4 is characterized in that the working fluid is a mixture of gas and condensable fluid.

  The invention described in claim 5 is configured to include a bypass passage through which the working fluid bypasses between the high temperature side heat exchange section and the low temperature side heat exchange section or the expansion chamber.

In the first aspect of the present invention, due to the heat Q1 flowing into the high temperature side heat exchanging section and the reciprocating motion made by the expander, pressure vibration is generated in the working fluid (for example, gas such as helium or air) in the heat transport pipe, A reciprocating flow occurs. Then, the high temperature heat that has flowed into the high temperature side heat exchange section is transferred to the high temperature side of the stack. The transferred high-temperature heat is lowered in temperature by heat exchange between the reciprocating working fluid and the heat storage body, and is transported to the low temperature side as low-temperature heat of the stack. This low-temperature heat Q1 is transmitted from the low-temperature side of the stack to the low-temperature side heat exchange unit, and a part of the heat Q2 is radiated from the low-temperature side heat exchange unit. The remaining heat (Q1-Q2) = W _B is a work flow in the cold side of the stack (PV corresponding to work), the work flow and forward the working fluid during heat exchange with the regenerator and the working fluid This is due to the pressure difference caused by the temperature difference from the return. The remaining heat (Q1-Q2) = W _B passes through the low-temperature side heat exchanger section, is transmitted to a work flow W _B into the expansion chamber, the work flow W _B is output from the expander. As described above, the heat transport pipe of the present invention releases heat Q2 = (Q1−W _B ) from the low temperature side heat exchange section out of the heat Q1 input to the high temperature side heat exchange section, and from the expander. can output the work flow _{W B.}

  In addition, since the reciprocating flow does not occur in the working fluid when the expander is stopped, even when heat flows into the high temperature side heat exchange part, the high temperature side heat exchange part passes from the high temperature side heat exchange part via the stack. The heat transfer and work transfer to the expander are stopped. Therefore, by controlling the operation and stop of the expander according to the state change of the high temperature side heat exchange part or the state change of the low temperature side heat exchange part, the heat transport pipe of the present invention flows into the high temperature side heat exchange part. It is possible to appropriately control the transport of heat, the heat radiation from the low-temperature side heat exchanging section, and the work output from the expander.

Further, by changing the scavenging capacity of the vibration speed of the expander (rpm) or expansion chamber can be adjusted to work flow W _B at the low temperature side of the stack, heat transfer from the hot side heat exchanger to the cold-side heat exchanger work flow W _B outputted from the amount Q2 and the expander can be adjusted. A result, the heat transfer tube of the present invention, the work flow W _B output by the low-temperature heat transfer rate of the heat exchange section (heat radiation amount of the low-temperature side heat exchange portion) Q2 and the expander suitably can be controlled.

  Further, in the heat transport pipe of the present invention, the heat transport from the high temperature side heat exchange section to the low temperature side heat exchange section is performed by the reciprocating flow of the working fluid generated by the expander and the pressure vibration. The posture is not restricted by the direction of gravity and is free, and can also be used in a weightless environment.

  Furthermore, the heat transport pipe of the present invention transports heat by generating a reciprocating flow of the working fluid and pressure vibration using an expander without using the phase change of the working fluid. Is not limited to the phase change temperature (condensation temperature, evaporation temperature) of the working fluid.

  Further, as compared with the conventional thermoacoustic engine, the heat transport pipe of the present invention has two heat exchanging parts, a high temperature side and a low temperature side, so that the configuration is simple and the cost is low. Moreover, since the high temperature side heat exchange part is located at the end of the apparatus, it is easy to connect to the object to be heated and a large transfer area for heat input can be obtained.

  Furthermore, the heat transport pipe of the present invention does not need to be used at a high degree of vacuum like a conventional heat pipe, and can prevent performance degradation even when air flows in. In addition, when air is used as the working fluid, the average pressure is set to atmospheric pressure so that air does not flow in and out, and the average pressure of the working fluid in the heat transport pipe can be maintained at atmospheric pressure. As a result, the heat transport pipe of the present invention can maintain the heat transport capability to the low temperature side heat exchange section and the work capability by the expander.

  In the invention according to claim 2, since the end surface and the outer peripheral surface of the high temperature side heat exchanger can be made into a heat transfer surface by connecting the high temperature side heat exchanger to the high temperature end of the stack, the heat of the heat source The heat transfer area increases and the temperature difference that occurs during heat transfer decreases. Furthermore, the heat flowing from the heat source to the high temperature side heat exchanger can be evenly transferred to the working fluid flowing through the high temperature side heat exchanger.

  Further, by connecting the low temperature side heat exchanger to the low temperature end of the stack, the heat flowing out from the low temperature end of the stack can be evenly transferred to the working fluid flowing through the low temperature side heat exchanger.

  In the invention according to claim 3, since the expander has a generator and a motor function, when operating the heat transport pipe of the present invention, the expander functions as a motor and is used as a starter of the expander. Used as a generator for heat transport. As a result, the heat transport pipe of the present invention can be started reliably, is easy to use, and improves the heat transport to the low temperature heat exchange section and the controllability of work output from the expander.

  In the invention described in claim 4, the working fluid in the stack is a mixture of gas and condensable fluid. For this reason, heat transfer in each heat exchange part can be promoted by the phase change of the condensable fluid in the high temperature side heat exchange part and the low temperature side heat exchange part. This is because heat transfer by evaporation and condensation generally provides greater heat transfer performance than heat transfer by a gas monolayer. That is, the condensable fluid is vaporized in the high-temperature side heat exchange section and condensed in the low-temperature side heat exchange section, thereby causing a phase change and promoting heat transfer. As a result, the present invention, like the heat pump or thermosiphon of the prior art, can also perform limited heat transport in which the difference in heat transport temperature is small and the temperature range used is approximately equal to the phase change temperature of the condensable fluid. It becomes. In addition, the internal pressure does not become negative as in the conventional heat pump or thermosiphon.

  In the invention of claim 5, the working fluid is bypassed between the high temperature side heat exchange part and the low temperature side heat exchange part or the expansion chamber, so that the work flow generated at the high temperature end can be recovered at the expansion part, Output performance is improved.

It is explanatory drawing of the heat transport pipe which concerns on Example 1 of this invention. Is a diagram illustrating the average temperature of the heat storage body over the temperature and pressure and stack entire length to the displacement of the working fluid component of X ₀ of the stack of FIG. It is a figure which shows the work flow of the heat transport pipe and stack of FIG. It is sectional drawing of one Example of the high temperature side heat exchanger of FIG. It is sectional drawing of one Example of the low temperature side heat exchanger of FIG. It is explanatory drawing of the heat transport pipe which concerns on Example 2 of this invention. It is explanatory drawing of the prior art of the heat transport pipe | tube which concerns on this invention. It is explanatory drawing of the other prior art of the heat transport pipe | tube which concerns on this invention. It is explanatory drawing of the prior art relevant to the heat transport pipe | tube which concerns on this invention. It is explanatory drawing of the other prior art relevant to the heat transport pipe | tube which concerns on this invention.

  Embodiments of the present invention will be described below in detail with reference to the drawings.

  FIG. 1 is an explanatory diagram of a heat transport pipe according to a first embodiment of the present invention, and black arrows in the figure indicate a heat flow direction and a work direction. As shown in FIG. 1, the heat transport pipe 1 includes an expansion chamber 2d provided in the expander 2, a low temperature side heat exchanger (low temperature side heat exchange unit) 3, a stack 4, and a high temperature side heat exchanger (high temperature). Side heat exchange section) 5 is connected in this order.

  The expander 2 includes a cylinder 2a, a piston 2b connected to one end of a rod 2c, and output recovery means 2e connected to the other end of the rod 2c, and an expansion chamber 2d is formed by the cylinder 2a and the piston 2b. The form of the output recovery means 2e may be either the same movement amount as the reciprocating motion of the piston 2b, a linear system that reciprocates, or a rotary system that converts the reciprocating motion of the piston 2b into a rotational motion by a crank mechanism or the like. More specifically, the output recovery means 2e is, for example, a generator or a fan. The generator takes the form of a linear generator in the case of a linear system and a rotary generator in the case of a rotary system.

  The stack 4 is provided for transporting heat from the high-temperature side heat exchanger 5 to the low-temperature side heat exchanger 3, and reciprocates with a large number of channels having a small channel cross-sectional area in which the working fluid flows. It has a heat storage function for exchanging regenerative heat with the working fluid. More specifically, in the stack 4, for example, a heat storage body 4b of a wire mesh of about 5 to 100 mesh is stacked in the pipe 4a. Alternatively, the tube 4a may be filled with a large number of elongated wires having a circular cross section. In this case, the gap between the wires forms a flow path, and the wires function as the heat storage body 4b. The flow resistance between both ends of the stack 4 is preferably small. In Example 1 and Examples 2 and 3 to be described later, both ends of the stack 4 under operating conditions (frequency of working fluid pressure, temperature, pressure). The pressure loss between them is very small.

  The high temperature side heat exchanger 5 is provided to transmit heat Q1 flowing from a heat source (not shown) such as equipment installed in the high temperature side heat exchanger 5 to the working fluid, and includes an outer peripheral surface 5a and an end surface 5b. Forms a heat transfer surface 5ab to which heat Q1 from a heat source (not shown) is transmitted. The end surface 5b is a flat surface for facilitating installation of a device that is a heat source.

  The low temperature side heat exchanger 3 is provided for releasing the heat Q2 of the working fluid flowing out from the low temperature end 4d of the stack 4 to the outside, and the outer peripheral surface 3a forms a heat transfer surface for releasing the heat Q2 to the outside. Moreover, it is preferable that the low-temperature side heat exchanger 3 and the high-temperature side heat exchanger 5 each have a small flow path resistance between both ends. In Example 1 and Examples 2 and 3 to be described later, The pressure loss between both ends of the exchangers 3 and 5 is very small.

  Air was used as the working fluid for filling the heat transport pipe 1. However, the working fluid may be a gas such as helium, hydrogen, nitrogen, or argon in addition to air, and a plurality of types of gases may be mixed. Although the amount of heat transport can be increased by increasing the sealing pressure of the working fluid, it may be less than atmospheric pressure. However, the atmospheric pressure or higher is preferable from the viewpoint of the amount of heat transport and the sealing property of the heat transport pipe 1. When air is used as the working fluid, the heat transport pipe 1 may not have a strictly sealed structure by setting the average pressure to atmospheric pressure.

Next, the operation and effect of the heat transport pipe 1 according to the embodiment of the present invention will be described. FIG. 2 is a diagram illustrating the pressure, temperature, and average temperature of the heat storage body with respect to the displacement of the working fluid element 6 at the position X ₀ (FIG. 1) of the stack 4 in FIG. In the figure, X _{0 to} X ₄ indicate the positions of the working fluid element 6 shown in FIG. 1, and A and B indicate the A position (high temperature end 4c) and B position (low temperature end 4d) of the stack 4 in FIG. . Hereinafter, the case where the output recovery means 2e of the expander 2 is the generator 2e1 will be described.

  The generator 2e1 has a generator function and a motor function. When the heat transport pipe 1 starts to operate, the generator 2e1 is used as a starter that causes the generator 2e1 to function as a motor and reciprocates the piston 2b. Thereby, pressure oscillation and reciprocating flow of the working fluid occur in the heat transport pipe 1. After the occurrence of pressure vibration, the generator 2e1 operates as a generator. Note that the expander 2 may be activated by generating minute vibrations in the working fluid and the piston 2b with a light impact force on the heat transport pipe 1 from the outside. In this case, the generator 2e1 functions only as a generator.

  Since each flow resistance of the high temperature side heat exchanger 5, the stack 4, the low temperature side heat exchanger 3, and the expansion chamber 2d is very small, the high temperature side heat exchanger 5, the stack 4, the low temperature side heat exchanger 3, The pressures in the expansion chamber 2d are almost equal. Moreover, the outer peripheral surface of the tube 4a of the stack 4 is covered with a heat insulating material (not shown), is insulated from the surroundings, and is formed of a material having low thermal conductivity of the tube 4a. The conduction heat of is very small. Furthermore, the heat of conduction of the heat accumulator 4b from the high temperature end 4c to the low temperature end 4d is very small. In the embodiment, the outer peripheral surface of the tube 4a of the stack 4 is covered with a heat insulating material. However, since strict heat insulation is not necessarily required, it can be used without being covered with a heat insulating material.

The high temperature heat flowing from the heat transfer surface 5ab of the high temperature side heat exchanger 5 is transmitted to the working fluid that reciprocates through the high temperature side heat exchanger 5, and is transmitted to the high temperature end 4c of the stack 4. The high temperature heat transferred to the high temperature end 4c of the stack 4 is transported to the low temperature end 4d of the stack 4 as low temperature heat while the temperature is lowered by heat exchange between the reciprocating working fluid and the heat storage body 4b. The The low temperature heat is transmitted from the low temperature end 4 d to the low temperature side heat exchanger 3, and a part of the low temperature heat (heat Q 2) is radiated from the low temperature side heat exchanger 3. The remaining heat (Q1-Q2) = _{W B} is transmitted to a work flow _{W B} into the expansion chamber 2d, work flow _{W B} is output from the expander 2.

  That is, the high-temperature heat flowing from the heat transfer surface 5ab of the high-temperature side heat exchanger 5 is transferred to the working fluid reciprocatingly flowing through the high-temperature side heat exchanger 5, and heat Q1 is generated in one cycle at the high-temperature end 4c of the stack 4. The total enthalpy H (= Q1) in a high temperature state equal to This total enthalpy H passes through the stack 4 and flows out from the low temperature end 4d of the stack 4 at a low temperature. The total enthalpy passing through each cross section of the stack 4 and the total enthalpy flowing out from the low temperature end 4 d are equal to the total enthalpy H flowing into the high temperature end 4. That is, the low-temperature heat having the same heat quantity as the high-temperature heat is transmitted to the low temperature end 4d.

  By the way, since the heat capacity of the heat storage body 4b of the stack 4 and the heat transfer coefficient between the heat storage body 4b and the working fluid are finite, heat exchange between the heat storage body 4b and the working fluid is insufficient, and the heat storage body 4b Creates a temperature difference between the working fluid and the working fluid. For this reason, a difference occurs between the return and return temperatures of the reciprocating working fluid. Since the heat capacity of the heat accumulator 4b is finite but relatively large, the temperature fluctuation of the heat accumulator 4b in one cycle is relatively small, and the average temperature of the heat accumulator 4b at each position over the entire length of the stack 4 is shown in FIG. As shown in FIG.

Here, attention is paid to the working fluid element 6 that reciprocates around the position X ₀ of the stack 4. The temperature of one cycle of the working fluid element 6 intersects with a substantially straight line (FIG. 2) of the average temperature of the heat accumulator 4b, and the major axis is tilted downward to the right and indicated by a substantially ellipse (thick broken line in FIG. 2). That is, when the working fluid element 6 is moved to the position X ₂ through the position X _0, X ₁ from the position X _3, the temperature of the working fluid element 6 is lower than the average temperature of the heat storage body 4b, and a position X When moving from position ₂ via position X ₀ , position X ₄ to position X ₃ , the temperature becomes higher than the average temperature of the heat storage body 4 b, resulting in a clockwise irreversible change indicated by the arrow.

The temperature of the clockwise working fluid element 6 in one cycle, 1 cycle pressure of the working fluid component 6 is when the pressure in moving from the position X ₁ to position X ₄ is moved from the position X ₄ to the position X ₁ The major axis in FIG. 2 is indicated by a substantially elliptical shape in the clockwise direction (in the direction of the arrow) inclined substantially downward to the right. This substantially ellipse shows a PX diagram (pressure / displacement diagram) of the working fluid element 6, and when the displacement X of the working fluid element 6 is multiplied by the cross-sectional area of the stack 4, It becomes a virtual PV diagram. This virtual PV diagram is work flow W _M in the cross section MM, the area value of the virtual PV diagram shows the value of the work flow W _M of the cross-section MM.

FIG. 3 is a diagram illustrating the work flow W in each cross section orthogonal to the flow direction of the working fluid in the heat transport pipe 1 and the stack 4. As shown in FIG. 3, the work flow W increases substantially linearly to the right by 0 at a position C in the vicinity of the high temperature end 4 c of the stack 4 and a slight negative value at the high temperature end 4 c of the stack 4. a plus maximum value W _B at the cold end 4d of the stack 4. Work flow W _B of the maximum value is transmitted to the expansion chamber 2d through the low-temperature heat exchanger 3, forms expansion work piston 2b is equal to reciprocate to work flow W _B in the expansion chamber 2d. From this expansion work, the generator 2e1 outputs electric power. Note that the work flow is displayed with plus or minus in the direction of the direction, and the plus region represents the work flow toward the low temperature side, and the minus region represents the work flow toward the high temperature side.

On the other hand, the heat quantity Q1 of the high-temperature heat flowing into the high-temperature side heat exchanger 5 from the heat source flows into the high temperature end 4c of the stack 4 in the form of total enthalpy H (= Q1), and a part of the total enthalpy H is The work flow W becomes, and the remaining heat (H-W), that is, heat (Q1-W) passes through the stack 4 while decreasing the temperature and heat quantity, and becomes low-temperature heat (H-W _B ). To. This low-temperature heat (H-W _B ) is equal to (Q 1 -W _B ), flows into the low-temperature side heat exchanger 3, and is released from the outer peripheral surface 3 a to the outside as the heat Q 2 released from the low-temperature side heat exchanger. The Here, the released heat Q2 is represented by Q2 = (Q1-W _B ).

  FIG. 4 is a cross-sectional view of the high temperature side heat exchanger 5 of FIG. As shown in FIG. 4, the high temperature side heat exchanger 5 is configured to evenly form channel holes 5d having one end opened and the other end closed in a cylindrical block 5c made of a material having high thermal conductivity (for example, copper). As described above, the outer peripheral surface 5a and the flat end surface 5b of the high temperature side heat exchanger 5 form a heat transfer surface 5ab on which heat Q1 from the heat source is input. And the end surface of the high temperature side heat exchanger 5 on the side where the flow path hole 5d opens is connected to the high temperature end 4c of the stack 4 (FIG. 1). The heat Q1 that has flowed into the heat transfer surface 5ab of the high temperature side heat exchanger 5 passes through the block 5c by heat conduction, is transferred to the working fluid from the inner peripheral surface of the flow path hole 5d, and flows into the high temperature end 4c of the stack 4 To do. More specifically, the heat Q1 flowing into the high temperature end 4c is the total enthalpy H of one cycle of the working fluid flowing into and out of the high temperature end 4c of the stack 4 as described above.

FIG. 5 is a cross-sectional view of the low temperature side heat exchanger 3 of FIG. The low temperature side heat exchanger 3 includes a plurality of flow path holes 3c that penetrates through a cylindrical block 3b made of a material having high thermal conductivity (for example, copper). Both ends of the low temperature side heat exchanger 3 are respectively connected to the low temperature end 4d of the stack 4 and the expansion chamber 2d of the expander 2 (FIG. 1). As described above, the outer peripheral surface 3a of the low temperature side heat exchanger 3 forms a heat transfer surface for releasing the heat Q2 to the outside. And out of the total enthalpy H (= Q1) flowing from the low temperature end 4d of the stack 4 to the low temperature side heat exchanger 3, heat Q2 (= Q1-W _B ) flows from the inner peripheral surface of the flow path hole 3c, The heat passes through the block 3b and is radiated from the outer peripheral surface 3a. Work flow W _B of the total enthalpy H that flows into the low-temperature side heat exchanger 3 is transmitted via the channel hole 3c to the expansion chamber 2d.

As described above, the heat transport pipe 1 of the first embodiment transports the heat Q1 flowing into the high temperature side heat exchanger 5 to the low temperature side heat exchanger 3, and heat Q2 = (Q1) from the low temperature side heat exchanger 3 to the outside. -W _B) with releasing the work flow W _B is output from the expander 2 that can be used as a new effective energy.

Furthermore, the mesh number of the heat storage body 4b in which for example a wire mesh, by changing the material of the filling amount or regenerator 4b, can be adjusted to work flow W _B outputted from the expander 2.

  Moreover, since the heat transport pipe 1 transports heat by pressure vibration and reciprocating flow generated in the working fluid, the heat transport is stopped when the expander 2 is stopped. Therefore, when the high-temperature side heat exchanger 5 is installed in the equipment that is the heat source, and it is desirable to warm up the equipment at the time of startup, for example, in order to shorten the startup time of the equipment, the expander 2 is stopped until the warm-up is finished. The transportation is stopped and the warming of the equipment is promoted. After the warming of the equipment is finished, the expander 2 is operated to dissipate heat from the equipment from the low-temperature side heat exchanger 3 to control the heat transportation. That is, by controlling the operation and stop of the expander 2 in accordance with the state change of the high temperature side heat exchanger 5 or the state change of the low temperature side heat exchanger 3, the heat transport pipe 1 of the first embodiment is The transport of heat flowing into the heat exchanger 5 (heat radiation from the low temperature side heat exchanger 3) and the work output from the expander 2 can be controlled as appropriate.

Further, by controlling the operation state of the expander 2, for example, the vibration frequency (the number of rotations) or the stroke of the piston 2b (corresponding to the scavenging volume of the expansion chamber 2d) in response to the change in the operation state of the device, the stack 4 can adjust the value of the work flow W _B at the cold end 4d, heat transfer rate from the hot-side heat exchanger 5 to the low-temperature heat exchanger 3 (heat radiation amount) Q2 (= Q1-W B ) values also coordinates it can. Result, heat transport pipe 1 of the first embodiment, appropriate work flow W _B outputted from the low-temperature heat transfer rate to the heat exchanger 3 (the heat radiation amount of the low-temperature heat exchanger 3) Q2 and the expander 2 Can control.

  Further, in the expander 2, since the output recovery means 2e has the function of the generator 2e1 and the function of the motor, when the heat transport pipe 1 is operated, the generator 2e1 functions as a motor. It is used for a starter, and the generator 2e1 is used as an original generator for heat transport. As a result, the heat transport pipe 1 can be reliably started, is easy to use, and improves the heat transport to the low temperature heat exchanger 3 and the controllability of work output from the expander 2.

  Further, since one end of the high temperature side heat exchanger 5 is connected to the high temperature end 4c of the stack 4, the other end face 5b and the outer peripheral surface 5a of the high temperature side heat exchanger 5 are connected to the heat input from the heat source. Is used as a heat transfer surface 5ab. Thereby, the area which transfers the heat of a heat source increases, and the temperature difference produced in the case of heat transfer reduces. Moreover, since the high temperature side heat exchanger 5 is provided at one end of the heat transport pipe, it can be easily connected to the heated object and can be used in a wide range of applications. Since the end surface 5b, which is a heat transfer surface through which heat flows into the high temperature side heat exchanger 5, is a flat heat transfer surface, an apparatus (not shown) that is a heat source that inputs heat to the high temperature side heat exchanger 5 is easily provided. Can be installed. In the first embodiment, the end surface 5b is a flat surface, but various structures can be selected as appropriate for the end surface 5b and the outer peripheral surface 5a. For example, the outer peripheral surface 5a and the end surface 5b may have a radiating fin structure so that heat can be easily transferred between the fluid to be heated. Further, the end surface 5b may be structured so as to have a concavo-convex structure so as to be fitted to the concavo-convex structure of the object to be heated. If it carries out like this, the heat-transfer area between to-be-heated bodies can be enlarged.

  Furthermore, since the high temperature side heat exchanger 5 is uniformly provided with a plurality of flow path holes 5d through which the working fluid flows, a wide heat transfer surface for transferring the heat Q1 to the working fluid can be secured. Moreover, since heat can be transmitted also to the working fluid flowing through the flow path hole 5d in the central portion of the high temperature side heat exchanger 5, heat is evenly transferred to the working fluid flowing through the plurality of flow path holes 5d. As a result, the temperature difference between the heat transfer surface 5ab of the high temperature side heat exchanger 5 into which the heat of the heat source flows and the working fluid can be reduced, and the operation flows through the cross section of the high temperature side heat exchanger 5 orthogonal to the flow of the working fluid. The temperature of the fluid becomes uniform.

  Moreover, since the low temperature side heat exchanger 3 is uniformly provided with a plurality of flow passage holes 3c through which the working fluid flows, a wide heat transfer surface for transferring the heat Q2 from the working fluid to the block 3b can be secured. Moreover, since heat can be transmitted also to the working fluid flowing through the flow path hole 3c in the central portion of the low temperature side heat exchanger 3, heat is evenly transferred to the working fluid flowing through the plurality of flow path holes 3c. As a result, the temperature difference between the working fluid flowing in the flow path hole 3c and the block 3b can be reduced, and the temperature of the working fluid flowing in the cross section of the low temperature side heat exchanger 3 orthogonal to the flow of the working fluid becomes uniform. .

  Further, since the heat Q1 flowing into the high temperature side heat exchanger 5 is transported through the stack 4 by the reciprocating flow of the working fluid generated by the expander and the pressure vibration, the installation posture of the heat transport pipe 1 is in the direction of gravity. Unconstrained and free. Further, the heat transport pipe 1 can be used for heat transport even in a weightless environment.

  Further, heat transport devices such as heat pipes and thermosiphons in the prior art utilize the phase change of the working fluid. For this reason, when the heat transport device of the prior art transports heat from the high temperature side to the low temperature side, the temperature difference in heat transport from the high temperature side to the low temperature side is limited to be small. The temperature range in which the heat transport device is used is limited to the phase change temperature (condensation temperature, evaporation temperature) determined by the type of working fluid. However, since the heat transport pipe 1 of the first embodiment uses gas as the working fluid, the temperature difference between the high temperature side heat exchanger 5 and the low temperature side heat exchanger 3 varies from a small temperature difference to a large temperature difference. It can cover a wide range. Furthermore, the heat transport pipe 1 of the first embodiment transports the working fluid by reciprocating flow of the working fluid and pressure vibration without using the phase change of the working fluid. As a result, the temperature range in which the heat transport pipe 1 is used is not limited to the phase change temperature of the working fluid.

  Further, the heat transport tube 1 of the first embodiment does not require the pulse tube 54 of the conventional thermoacoustic engine 50 (FIG. 9) and the room temperature side heat exchanger 53. Also. A pulse tube 64 of a conventional thermoacoustic engine 60 (FIG. 10), a second room temperature side heat exchanger 63, an expander 61, and means for providing a phase difference between the expansion chamber 62 and the compression chamber 69; Is unnecessary. Therefore, the heat transport pipe 1 of the first embodiment has a simple configuration and is low in cost.

  The heat transport pipe 1 does not need to be used at a high degree of vacuum unlike a conventional heat pipe, and can prevent performance degradation even when air flows in. In addition, when air is used as the working fluid and the average pressure is set to atmospheric pressure, some inflow and outflow of air does not cause a problem in operation. As a result, the heat transport pipe 1 can maintain the heat transport capability to the low temperature side heat exchange section 3 and the work capability of the expander 2.

  FIG. 6 is an explanatory diagram of the heat transport pipe according to the second embodiment of the present invention. In FIG. 6, the same reference numerals as those in FIG. 1 are assigned to the same names, parts having the same shapes, and the same names and parts having the same shapes. As shown in FIG. 6, in the heat transport pipe 10, the low temperature side heat exchanger 3 and the high temperature side heat exchanger 5 of the heat transport pipe 1 of FIG. That is, in the heat transport pipe 10, the expansion chamber 2d of the expander 2 and the stack 14 are sequentially connected. A low temperature side heat exchanging portion 13 (a portion surrounded by a thick solid line in FIG. 6) is formed on the low temperature end 14d side of the stack 14, and a high temperature side heat exchanging portion 15 (the thick side in FIG. 6) on the high temperature end 14c side of the stack 14. A portion surrounded by a solid line) is formed. The low temperature side heat exchange unit 13 and the high temperature side heat exchange unit 15 are part of the stack 14 and have a stack function and a heat exchanger function. And the high temperature side heat exchange part 15 and the low temperature side heat exchange part 13 laminate | stack a plurality of wire meshes which are the heat storage bodies 14b, for example in the axial direction of the pipe 14a, and pipe | tube the outer periphery (both ends of the wire which forms a wire mesh) The inner peripheral surface of 14a is brought into thermal contact with, for example, diffusion bonding. As a result, the wire mesh has a function as a heat transfer and heat transfer medium for heat input or heat dissipation and a function as a heat storage body for regenerating heat exchange of the working fluid. Other configurations of the heat transport pipe 10 are the same as those of the heat transport pipe 1.

  The high temperature end outer surface 15b (the outer surface of the high temperature end 14c of the stack 14) of the high temperature side heat exchange unit 15 is a flat surface for installing a heat source device (not shown) and the like, and the high temperature side heat exchange unit 15 functions as a heat transfer surface for heat input. Moreover, the outer peripheral surface 15a of the high temperature side heat exchange part 15 also functions as a heat transfer surface for heat input, and the heat transfer surface 15ab of heat flowing into the high temperature side heat exchange part 15 is formed by the high temperature end outer surface 15b and the outer peripheral surface 15a. It is formed. The heat that has flowed into the outer peripheral surface 15a of the high temperature side heat exchanging portion 15 flows from both ends of the wire rod to the center in the longitudinal direction of the wire by heat conduction and is transmitted from the outer peripheral surface of the wire to the working fluid. Further, the heat from the heat source is transmitted from the inner surface of the high temperature end 14c of the stack 14 and the inner peripheral surface of the high temperature side heat exchanging portion 15 to the working fluid reciprocally flowing in the vicinity of each surface. As described above, the temperature of the working fluid that is transmitted to the working fluid that reciprocates in the central portion of the high temperature side heat exchange section 15 and flows through the cross section of the high temperature side heat exchange section 15 that is orthogonal to the flow of the working fluid becomes substantially uniform. .

  Heat is transferred from the working fluid reciprocatingly flowing through the central portion of the low temperature side heat exchanging portion 13 to the wire of the wire mesh, and the temperature of the working fluid flowing through the cross section of the low temperature side heat exchanging portion 13 orthogonal to the flow of the working fluid is approximately. It becomes uniform. Then, the wire mesh wire which is also the heat storage body 14 b and the heat Q 2 transmitted to the inner peripheral surface of the low temperature side heat exchange unit 13 are radiated from the outer peripheral surface 13 a of the low temperature side heat exchange unit 13.

  As described above, the heat transport pipe 10 according to the second embodiment can easily install a heat source device (object to be heated) and the like, and the heat transfer area of heat input from the heat source is increased, and further, the high temperature side heat exchange section 15 In addition, heat transfer with the working fluid is favorably performed in the low temperature side heat exchanging portion 13.

  Moreover, since the high temperature side heat exchange part 15 and the low temperature side heat exchange part 13 serve as the stack 14, compared with the heat transport pipe 1 of FIG. 1, the structure of the heat transport pipe 10 is further simple and low. It becomes cost. In particular, the heat transport pipe 10 is suitable for a small size and a small amount of heat transport. Other operations and effects of the heat transport pipe 10 are the same as those of the heat transport pipe 1.

  The third embodiment uses a mixture of air (gas) and water (condensable fluid) as the working fluid instead of the air of the first embodiment, and FIG. 1 is applied mutatis mutandis. The temperature of the high temperature side heat exchanger 5 is about 100 ° C., and the temperature of the low temperature side heat exchanger 3 is about 30 ° C. When the heat transport pipe 1 is in operation, water evaporates in the high temperature side heat exchanger 5 and changes in phase from liquid to gas, and condenses in the low temperature side heat exchanger 3 and changes in phase from gas to liquid. Since heat transfer by evaporation and condensation has a heat transfer performance larger than that by gas single layer, heat transfer in the high temperature side heat exchanger 5 and the low temperature side heat exchanger 3 can be promoted. As a result, like the heat pump or thermosiphon of the prior art, limited heat transport is also possible in which the difference in heat transport temperature is small and the temperature range used is approximately equal to the phase change temperature of the condensable fluid. In addition, the internal pressure does not become negative as in the conventional heat pump or thermosiphon.

  In Example 3, air is used as the gas. However, any gas can be used as long as it is in the gas phase at a temperature higher than the temperature of the low-temperature side heat exchange section. For example, the gas illustrated in Example 1 can be used. In Example 3, although water was used as the condensable fluid, any fluid that condenses in the low temperature side heat exchange section and evaporates in the high temperature side heat exchange section can be used. Although the condensable fluid to be used varies depending on the temperature of each heat exchange section when using the heat transport pipe, examples thereof include chlorofluorocarbon fluids and hydrocarbon fluids.

  In the fourth embodiment, a bypass passage is provided in the second embodiment shown in FIG. Specifically, the high temperature side heat exchange unit 15 and the expansion chamber 2d are connected by a bypass pipe (bypass passage) through which a working fluid can flow. The bypass pipe is provided outside the stack 14. As apparent from the graph of the work flow W in FIG. 3, the work flow W is negative (that is, there is a work flow toward the high temperature side) without the stack 4 on the high temperature side heat exchanger 5 side than the position C of the stack 4. It has become. As a result, a work flow can be obtained even at a slightly high temperature end portion (difference from 0 to minus portion). FIG. 3 illustrates the first embodiment, but the same applies to the sixth embodiment. By connecting the high temperature side heat exchanging section 15 and the expansion chamber 2d with a bypass passage, the work flow generated at the high temperature end (difference between 0 and the minus section) can be recovered by the expansion section, and the output performance can be improved. .

  In the fourth embodiment, a bypass passage is provided between the high temperature side heat exchange unit 15 and the expansion chamber 2d, but a bypass passage may be provided between the high temperature side heat exchange unit 15 and the low temperature side heat exchange unit 13. Similar effects can be obtained. In the fourth embodiment, the bypass passage is provided outside the stack 14, but may be provided inside the stack. In that case, the working fluid does not flow between the bypass passage and the heat storage body 14b.

1, 10, 20 Heat transport pipe 2 Expander 2d Expansion chamber 2e1 Generator 3 Low temperature side heat exchanger (low temperature side heat exchange section)
4, 14, 24 Stack 4b, 14b, 24b Heat storage body 5 High temperature side heat exchanger (high temperature side heat exchange part)
13, 23 Low temperature side heat exchange section 15, 25 High temperature side heat exchange section 24e Steam flow path (flow path)

Claims (5)

A stack with a thermal gradient from high temperature to low temperature with heat storage,
A high temperature side heat exchange section provided on the high temperature side of the stack;
A low temperature side heat exchange section provided on the low temperature side of the stack;
An expander having an expansion chamber adjacent to and communicating with the low temperature side heat exchange section,
The expander generates pressure vibration and reciprocating flow in the working fluid in the stack,
In the stack, heat transferred from the high temperature side heat exchanging unit to the high temperature side of the stack due to a temperature difference between the working fluid and the heat storage body is directed from the high temperature side to the low temperature side of the stack. Transported through the heat storage body, transferred from the low temperature side of the stack to the low temperature side heat exchange unit,
A part of the heat transferred to the low temperature side heat exchange part is radiated from the low temperature side heat exchange part, and the rest is transferred to the expansion chamber and output from the expander. . The high temperature side heat exchange part is provided at the high temperature end of the stack, and is a high temperature side heat exchanger provided with a plurality of channel holes having one end opened in the stack and the other end closed,
The low temperature side heat exchanging unit is a low temperature side heat exchanger provided with a plurality of flow path holes provided at a low temperature end of the stack, one end opened in the stack and the other end opened in the expansion chamber. The heat transport pipe according to claim 1. The heat transport pipe according to claim 1, wherein the expander has a function of a motor and a function of a generator. The heat transport pipe according to any one of claims 1 to 3, wherein the working fluid is a mixture of a gas and a condensable fluid. 5. The apparatus according to claim 1, further comprising: a bypass passage that bypasses the working fluid between the high temperature side heat exchange unit and the low temperature side heat exchange unit or the expansion chamber. Heat transport pipe.

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