JPH09236346A - Refrigerating device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To dissipate the heat of a gas flow passage quickly and improve refrigerating capacity by a method wherein operating fluid in a hollow section is evaporated by the absorption of heat through a gas flow passage while the fluid is moved to the side of a heat dissipating surface in a high speed to release the latent heat of evaporation on the heat dissipating surface and condense it. SOLUTION: When operating gas in a compression space is compressed by the movement of a compressing piston and the operating gas, whose temperature is raised to a high temperature by compression heat generated in this case, flows into a gas flow passage, the heat is transferred to the heat receiving surface 104 of a hollow section 102 and evaporates operating fluid in a wick 106. According to this evaporation, a pressure in the heat receiving surface 104 side of the hollow section 102 becomes higher than the heat dissipating surface 105 side of the hollow section 102 whereby a pressure difference is generated between both sides. In this case, the vapor of the operating fluid, evaporated by the pressure difference, is moved to the heat dissipating surface 105 side through the hollow section 102 in a high speed, then, releases the latent heat of evaporation on the heat dissipating surface 105 and is condensed. According to the heat dissipation, the heat of the gas flow passage is released to the outside.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas compression expansion refrigeration system such as a Stirling refrigeration system, and more particularly to a refrigeration system in which a high temperature working gas from a compression space is efficiently radiated to enhance the refrigeration capacity of the system. Regarding

[0002]

2. Description of the Related Art In recent years, there has been an urgent need to develop techniques for preserving various samples and various materials at extremely low temperatures in advanced technology fields such as the field of biotechnology and the field of electronic devices. In particular, Stirling refrigerating devices and the like have been attracting attention as means for achieving the above-mentioned extremely low temperatures, and are being widely used for various infrared sensors, freezers for cooling superconducting devices and the like, biomedical freezers, freezers and the like.

Here, the operation principle of the structure of a displacer type Stirling refrigerating machine will be described with reference to FIG. The expansion cylinder 2 and the compression cylinder 3 are attached to the main body housing 1 at an angle difference of 90 degrees, and the displacer 6 included in the expansion cylinder 2 and the compression piston 7 included in the compression cylinder 3 are common cranks. It is connected to the mechanism 5 and is reciprocally driven in a state in which the phases are 90 degrees out of phase with each other.

The displacer 6 is filled with a regenerator material 14 made of, for example, a sintered metal, and the working gas flowing from one opening of the displacer 6 is regenerator material 14.
In the process of passing through the inside of the
Heat exchange with the cold storage material 14 is performed.

This displacer 6 also has a function as a regenerative heat exchanger, and its heat exchange performance greatly influences the coefficient of performance of the refrigeration system. The expansion cylinder 2 and the compression cylinder 3 are separated from the crank chamber 12 by oil seals 8 and 9, respectively, and the base end portion of the expansion cylinder 2 and the compression space portion of the compression cylinder 3 are mutually separated by a gas flow path 4. It is in communication. As a result, the compression space 13 formed in the compression cylinder 3 and the expansion space 11 formed in the expansion cylinder 2 become
Through the gas flow path 4. On the other hand, the oil 10 is injected into the crank chamber 12.

Next, the operation of the Stirling refrigerating apparatus having the above-mentioned structure will be described with reference to FIG.
In FIG. 8, the horizontal axis represents time T and the vertical axis represents stroke S.

In the Stirling refrigerator, the displacer 6 reciprocates as shown by curves B and C in FIG. 8 and at the same time the compression piston 7 reciprocates as shown by curve D in FIG. Is shown in FIG.
The volume changes in the width region between the straight line A and the curve B, and the volume of the compression space 13 of the compression cylinder 3 changes in the width region between the curves C and D in FIG.

As a result, in the process of FIG. 8, the gas in the compression space 13 is compressed and flows into the expansion cylinder 2 through the gas flow path 4 (ideally isothermal compression). In the process of FIG. 8, this gas passes through the regenerator material 14 in the displacer 6 and exchanges heat with the regenerator material 14 to lower the temperature (cooling with constant volume). The gas that has passed through the regenerator material 14 flows into the expansion space 11 of the expansion cylinder 2 in the process of FIG. 8, and then expands as the displacer 6 descends (ideally, isothermal expansion). Next, in the process of FIG. 8, as the displacer 6 rises, the gas in the expansion space 11 passes through the regenerator material 14, exchanges heat with the regenerator material 14, and after the temperature rises, the gas passage It is again introduced into the compression space 13 via 4 (heating at constant volume).

As a result, the cold head 15 provided on the head of the expansion cylinder 2 is cooled.

[0010]

When the gas flow passage 4 that connects the compression space 13 and the expansion space 11 is buried in the main body of the device for downsizing of the device, etc., this gas flow passage is used. 4 is provided with a radiation fin 16 outside the compression space 13
Displacer 6 while air cooling the hot working gas from
Supplies to the side.

However, since the gas flow path 4 is embedded in the main body of the apparatus, the heat radiation fins 16 cannot be attached so as to surround the gas flow path 4, and the high temperature working gas from the compression space 13 is sufficient. After passing through the regenerator material 14 in the displacer 6 without exchanging heat and exchanging heat with the regenerator material 14, it was flowing into the expansion space 11.

As a result, there is a problem in that the working gas in the expansion space 11 is prevented from lowering its temperature, and the refrigerating capacity of the refrigerating apparatus cannot be improved. In particular, in order to reduce the size of the device, the base end side of the compression cylinder 3 is placed in the compression space 1
3, when the base end portion of the expansion cylinder 2 and the base end portion of the compression cylinder 3 are communicated with each other by the gas flow passage 4, the heat radiation possible range is limited and this problem becomes serious.

The present invention has been made in view of the above circumstances, and after the high temperature working gas supplied from the compression space is sufficiently radiated while passing through the gas flow path embedded in the main body of the apparatus, it is transferred to the expansion space. By supplying the refrigerating device, a refrigerating device having improved refrigerating capacity is provided.

[0014]

SUMMARY OF THE INVENTION The present invention is directed to a compression space formed in a compression cylinder arranged inside a compressor body container and an expansion formed in an expansion cylinder arranged inside an expander body container. The space communicates with a gas flow path embedded in the main body of the apparatus, and the compression piston and the expansion piston or the expansion displacer reciprocate inside the compression cylinder and the expansion cylinder with a predetermined phase difference from each other. In a refrigerating apparatus that is provided with a driving unit that transmits a driving force so as to drive and that generates a low temperature by a heat cycle including an expansion process of a working gas that is guided from the compression space to the expansion space, is adjacent to the gas flow path. And an airtight pipe having a hollow portion inside,
A radiating means provided on the outside of the airtight pipe, and a wick having a capillary action, which is laid between the heat receiving surface on the gas flow path side of the hollow portion and the radiating surface on the radiating means side,
A heat receiving side pressing member that is provided inside the hollow portion and presses the wick against the heat receiving surface on the gas flow path side; And a working fluid that is enclosed in the hollow portion, evaporates on the heat receiving surface, and then releases and condenses evaporation latent heat on the heat radiating surface.

By using this structure, the working fluid in the hollow portion is evaporated by heat absorption from the gas flow path, moved to the heat radiating surface side at high speed, and latent heat of vaporization is released and condensed on the heat radiating surface. The heat of the gas flow path can be dissipated more quickly than

Further, preferably, the heat radiation side pressing member has a guide groove for guiding the condensed liquid phase working fluid to the heat receiving surface on the gas flow path side. By using this configuration, the working fluid liquefied by condensation on the heat dissipation surface is returned to the heat receiving surface side through the wick, and the liquid-phase working fluid deposited under the hollow portion by the guide groove is also received on the heat receiving surface. Be guided.

Further preferably, the heat radiating means is provided on the side opposite to the gas flow path side of the airtight pipe, and a plurality of the wicks are laid at predetermined intervals.

By using this structure, the working fluid evaporated on the heat receiving surface easily moves to the heat radiating surface side through the space between the wicks. More preferably, the gas flow passage communicates an expansion space formed on the base end side of the expansion cylinder with a compression space formed on the base end side of the compression cylinder.

By using this structure, it is possible to further reduce the size of the device.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a refrigerating apparatus of the present invention will be described below with reference to the drawings. The same configurations as those of the above-described conventional example are designated by the same reference numerals,
Detailed description of these parts will be omitted.

In FIG. 1, reference numeral 101 denotes an airtight pipe which is provided adjacent to the gas flow path 4 on its upper surface and has a hollow portion 102 inside, and a heat radiation fin on the outside of the gas flow path 4 side. 103 is provided.

As shown in FIG. 2, the airtight pipe 101 has a heat receiving surface 1 on the gas flow path 4 side in the hollow portion 102.
A wick 106 having a capillary action is continuously laid between 04 and the heat radiating surface 105 on the heat radiating fin 103 side. The wick 106 is composed of a wire mesh having a large number of openings, and a plurality of wicks are laid in the hollow portion 102 at predetermined intervals.

Reference numeral 107 denotes a heat receiving side pressing member which is provided in the hollow portion 102 and presses the wick 106 against the heat receiving surface 104 on the gas flow path 4 side, and the wick 106 is brought into contact with the heat receiving surface 104 by the contact of the projection 107a. Pressed.

Reference numeral 108 denotes a heat radiating side pressing member which is provided in the hollow portion 102 and presses the wick 106 against the heat radiating surface 105 on the heat radiating fin 103 side, and has a convex portion 108a and a groove portion 108b in a direction orthogonal to the gas flow path 4. A plurality of the wicks 10 are alternately provided.
6 is pressed against the heat dissipation surface 105. Further, the groove portion 108b is configured such that the groove becomes deeper toward the gas flow path 4 side, and as will be described later, the groove portion 108b is condensed in the heat dissipation portion,
It serves as a guide groove for guiding the accumulated liquid-phase working fluid 109 to the heat receiving surface 104. And the working fluid 109
Is a working fluid that is enclosed in the hollow portion 102, evaporates on the heat receiving surface 104, and then releases latent heat of vaporization on the heat radiating surface 105 to condense, and is made of water, methanol, ethanol, or the like. As described above, the airtight pipe 101 constitutes a so-called heat pipe.

Next, the heat radiation operation of the gas flow path 4 by the airtight pipe 101 will be described with reference to FIGS. 3 to 6. First, the compression space 1 is moved by the movement of the compression piston 7.
When the working gas in 3 is compressed and the working gas that has become hot due to the compression heat generated at this time flows into the gas flow path 4, this heat is transmitted to the heat receiving surface 104 of the hollow portion 102, and the heat receiving surface 104 wicks the heat. The working fluid 109 in 106 is evaporated (see FIG. 3).

Due to this evaporation, the heat receiving surface 10 of the hollow portion 102
The air pressure on the four side becomes higher than that on the heat radiating surface 105 side of the hollow portion 102, and a pressure difference occurs on both sides. The vapor of the working fluid 109 evaporated due to this pressure difference is
The inside of 2 is moved to the heat radiating surface 105 side at high speed (see FIG. 4), and latent heat of vaporization is released and condensed on the heat radiating surface 105 (see FIG. 5). Due to this heat dissipation, the heat of the gas flow path 4 is released to the outside.

The working fluid 10 liquefied by condensation
9 returns to the heat receiving surface 104 side through the inside of the wick 106 by the capillary action (see FIG. 6), and thereafter, the same movement is repeated. In the description of the present embodiment, the guide groove 108b guides the liquid-phase working fluid 109 condensed and accumulated on the heat radiating surface 105 to the heat receiving surface 104.

In this way, when the working fluid 109 is circulated, the pressure difference between the heat receiving surface 104 side and the heat radiating surface 105 side in the airtight pipe 101 and the capillary action of the wick 106 are used. Since no special external power source is required, the structure is simple and the reliability of heat dissipation performance can be improved.

Further, as shown in FIG. 2, a plurality of wicks 106 are arranged in the hollow portion 102 in the same direction as the gas flow path 4 at a predetermined interval. This is each wick 10
This is because the working fluid 109 evaporated on the heat receiving surface 104 easily moves to the heat radiating surface 105 side through the space between the six.

As described above, the working fluid 109 is evaporated by the heat absorption from the gas flow path 4 and moved to the heat radiating surface 105 side at a high speed to release the latent heat of vaporization on the heat radiating surface 105 to condense it. Compared with this, the heat of the gas flow path 4 can be radiated quickly.

In the description of the above embodiment, the present invention is described as
Although the case where the present invention is applied to the piston 1 displacer type Stirling refrigerating apparatus has been described, the present invention is also applicable to other gas compression expansion refrigerating apparatuses.

[0032]

As described above, according to the present invention, the working fluid in the hollow portion is evaporated by the heat absorption from the gas passage,
Since it moves to the heat radiating surface at high speed and releases the latent heat of vaporization on the heat radiating surface to condense, the heat in the gas flow path can be radiated faster than before, and the hot working gas from the compression space radiates heat sufficiently. Without it, it does not flow into the expansion space. Therefore, it is possible to provide a refrigerating apparatus with improved refrigerating capacity.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a schematic configuration of a Stirling refrigerating apparatus according to an embodiment of the present invention.

FIG. 2 is a schematic configuration diagram for explaining a configuration of an airtight pipe 101 of the present invention.

FIG. 3 is a gas flow path 4 using the airtight pipe 101 of the present invention.
FIG. 6 is a schematic cross-sectional view for explaining the heat radiation operation of FIG.

FIG. 4 is a gas flow path 4 using the airtight pipe 101 of the present invention.
FIG. 6 is a schematic cross-sectional view for explaining the heat radiation operation of FIG.

FIG. 5 is a gas flow path 4 using the airtight pipe 101 of the present invention.
FIG. 6 is a schematic cross-sectional view for explaining the heat radiation operation of FIG.

FIG. 6 is a gas flow path 4 using the airtight pipe 101 of the present invention.
FIG. 6 is a schematic cross-sectional view for explaining the heat radiation operation of FIG.

FIG. 7 is a cross-sectional view of a conventional Stirling refrigeration system.

FIG. 8 is a diagram illustrating a process of a Stirling refrigeration cycle.

[Explanation of symbols]

 1 Body Housing 2 Expansion Cylinder 3 Compression Cylinder 4 Gas Flow Path 5 Crank Mechanism 6 Displacer 7 Compression Piston 8, 9 Oil Seal 10 Oil 11 Expansion Space 12 Crank Chamber 13 Compression Space 14 Cold Storage Material 15 Cold Head 16 Radiating Fin 101 Airtight Pipe 102 hollow part 103 heat dissipation fin 104 heat receiving surface 105 heat dissipation surface 106 wick 107 heat receiving side pressing member 108 heat dissipation side pressing member 109 working fluid

Claims (4)

[Claims] 1. A compression space formed in a compression cylinder arranged inside a compressor body container and an expansion space formed in an expansion cylinder arranged inside an expander body container are provided in an apparatus body. A driving force is transmitted so that the compression piston and the expansion piston or the expansion displacer reciprocally drive the inside of the compression cylinder and the inside of the expansion cylinder, respectively, with a predetermined phase difference, while being communicated with each other by an embedded gas flow path. A refrigerating apparatus for generating a low temperature by a heat cycle including an expansion process of a working gas guided from the compression space to the expansion space, the refrigeration device being provided adjacent to the gas flow path, and having a hollow portion inside thereof. An airtight pipe having: a heat radiating means provided outside the airtight pipe; a heat receiving surface on the gas flow path side of the hollow portion; Side radiating surface, a wick having a capillary action, and a heat receiving side pressing member that is provided in the hollow portion and presses the wick against the heat receiving surface on the gas flow path side, and is provided in the hollow portion. A heat-radiating-side pressing member that presses the wick against the heat-dissipating surface on the heat-dissipating means side; and a working fluid that is enclosed in the hollow portion and that evaporates on the heat-receiving surface and then releases and condenses evaporation latent heat on the heat-dissipating surface. A refrigerating apparatus comprising: 2. The refrigerating apparatus according to claim 1, wherein the heat radiation side pressing member has a guide groove for guiding the condensed liquid phase working fluid to the heat receiving surface on the gas flow path side. 3. The heat radiating means is provided on the side opposite to the gas flow path side of the airtight pipe, and a plurality of the wicks are laid at predetermined intervals. 2. The refrigerating apparatus according to 2. 4. The gas flow passage communicates with an expansion space formed on the base end side of the expansion cylinder and a compression space formed on the base end side of the compression cylinder. The refrigerating apparatus according to claim 1.