JP2003287323A - Cold heat carrier - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent high pressure resistance from being required to each member even under a condition that a cold heat carrier 1 is stopped, and the temperature of a heat carrying medium reaches the room temperature. <P>SOLUTION: A buffer tank 6 to mitigate the pressure increase when the internal pressure in the pipe is increased is provided on a cold heat carrying pipe 5 between a carriage pump 4 and a cold heat source side heat exchanger 2 so that high pressure resistance is not required for each member even under a condition that the cold heat carrier 1 is stopped, and the temperature of the heat carrying medium reaches the room temperature. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cold heat transfer device for transferring cold heat from a cold heat source to equipment utilizing cold heat.

[0002]

2. Description of the Related Art Today, equipment utilizing cold heat (equipment utilizing cold heat) includes commercial or domestic equipment for cold heat use such as a freezer, a refrigerator, a throw-in cooler, a low temperature liquid circulator, a low temperature incubator, A wide variety of devices such as a constant temperature bath, a heat shock test device, a freeze dryer, a temperature characteristic test device, a blood / cell storage device, and a cold cooler are known.

In such a cold heat utilization device, cold heat may be generated by, for example, a Stirling refrigerator, and the cold heat may be conveyed and used by a cold heat conveying device.

FIG. 5 is a diagram showing a schematic configuration of such a cold heat transfer device 101. A cold heat source side heat exchanger 112 for exchanging heat between a heat transfer medium and a cold heat source, and a transfer pump 111 for pumping the heat transfer medium. A load side heat exchanger 113 for exchanging heat between the heat transfer medium and the cold heat utilization device is provided, and these are sequentially connected by a cool heat transfer pipe 115.

[0005]

However, when the cold heat transfer device 101 is stopped, the temperature of the heat transfer medium rises to room temperature, so that the internal pressure of the cold heat transfer pipe 115 increases.
For this reason, it is necessary to design each member to withstand pressure at room temperature at a minimum, which has been a factor in increasing costs.

That is, for example, when the heat carrier medium is sealed at 2 MPa at the temperature in order to convey the ultra-low temperature cold heat of −150 ° C. or less at a predetermined flow rate, the pressure resistance at room temperature is 2.5 to. 4 times (5 to 10 MPa) is required.

Cold heat transfer pipe 11 that withstands such high pressure
5, the heat exchanger 112 on the cold heat source side, the transfer pump 111, the cold heat utilization equipment, etc. are very expensive, and the cold heat transfer pipe 11
A high technology is also required for the welded portion for connecting the 5 and the like, which causes a significant cost increase.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a cold heat transfer apparatus which enables cost reduction by requiring a small withstand voltage value for each component even when the cold heat transfer apparatus is stopped. And

[0009]

In order to solve the above problems, the invention according to claim 1 provides a cold heat source side heat exchanger for exchanging heat between a heat carrying medium and a cold heat source, and pressure-feeding the heat carrying medium. In a cold heat transfer device in which a transfer pump and a load side heat exchanger for exchanging heat between the heat transfer medium and the cold heat utilization device are sequentially connected by a cold heat transfer pipe, between the transfer pump and the cold heat source side heat exchanger. To the cold heat transfer pipe, a buffer tank that suppresses an increase in internal pressure of the cold heat transfer pipe is connected and provided, so that even when the cold heat transfer device is stopped, the withstand pressure value required for each component can be small. It is characterized by enabling cost reduction.

The invention according to claim 2 is characterized in that a buffer tank is connected to a cold heat transfer pipe connecting the transfer pump and the heat exchanger on the cold heat source side via a capillary tube.

According to the third aspect of the present invention, when the buffer tank is connected to the cold heat transfer pipe connecting the transfer pump and the heat exchanger on the cold heat source side, the pressure inside the cold heat pipe by the buffer tank can be adjusted. It is characterized in that it is connected through a pressure regulator.

The invention according to claim 4 is characterized in that the buffer tank is provided with a relief valve for preventing the pressure in the buffer tank from exceeding a predetermined pressure.

According to the fifth aspect of the present invention, the space volume of the buffer tank is relative to the total volume of the heat transfer medium in the circulation path formed by the cold heat transfer pipe, the cold heat source side heat exchanger, the load side heat exchanger and the like. Is set to about 10 times.

The invention according to claim 6 is characterized in that the cold heat source is a Stirling refrigerator for compressing / expanding a heat carrier medium to generate cold heat.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a diagram showing a schematic configuration of a cold heat transfer apparatus 1 applied to the description of the embodiment of the present invention.

The cold heat transfer apparatus 1 includes a cold heat source side heat exchanger 2 for exchanging heat between a cold heat source such as a Stirling refrigerator and a heat transfer medium, a transfer pump 4 for pumping the heat transfer medium, and a heat transfer medium. It has a load side heat exchanger 3 and the like for exchanging heat with cold heat utilization equipment, and these are sequentially connected by a cold heat transfer pipe 5.

A buffer tank 6 is connected to a cold heat transfer pipe 5 connecting the transfer pump 4 and a cold heat source via a capillary tube 7.

The space volume of the buffer tank 6 is about 10 times as large as the total volume of the cold heat transfer pipe 5 and the space volume of the heat exchanger 2 on the cold heat source side, the heat exchanger 3 on the load side, etc. The internal pressure rise can be suppressed even when the cold heat transfer apparatus 1 is stopped.

As the heat carrier medium, nitrogen gas, helium gas or the like can be used.

When the heat carrier medium is condensed and stored in the buffer tank 6 as described above, the heat carrier medium amount necessary for the operation may be insufficient, so the cold heat carrier pipe 5
The buffer tank 6 and the buffer tank 6 are connected by a capillary tube 7 and are formed so that the internal temperature of the buffer tank 6 is always room temperature without heat insulating treatment.

As a result, only the gaseous heat carrier medium is stored in the buffer tank 6, which prevents a situation in which the amount of heat carrier medium required for the operation becomes insufficient.

Of course, the capillary tube 7 is designed to prevent the heat transfer medium during cold heat transfer from being mixed with the heat transfer medium in the buffer tank 6 so that the temperature of the heat transfer medium supplied to the cold heat utilization equipment does not drop. It also has an effect of suppressing mixing of the heat transfer medium inside and the heat transfer medium in the buffer tank 6.

By connecting the buffer tank 6 having a large capacity to the circulation path of the heat transfer medium in this way, for example, when the inner diameter of the cold heat transfer pipe 5 is 10 mm and the total length is 10 m (the heat exchanger 2 on the side of the cold heat source) The space volume of the load side heat exchanger 3 and the like is not considered for the time being), and the charging pressure at that temperature is 2 MPa in order to supply the heat carrier medium having a temperature of -173 ° C to the cold heat utilization equipment at a rate of 30 liters per minute. Consider the cold heat transfer device 1 filled with.

In this case, when the cold heat transfer device 1 is stopped and the heat transfer medium reaches room temperature (27 ° C.), the buffer tank 6 acts so as to mitigate the pressure increase, so that the internal pressure increase of the cold heat transfer pipe 5 is increased by 2. It will be about 0.6 MPa, and the rate of increase can be suppressed to only about 18%.

Therefore, the withstand pressure required for each member can be small, and the cost can be greatly reduced.

There is a concern that the buffer tank 6 may exceed the withstand pressure of each component due to an unexpected accident.

In order to deal with such a situation, it is preferable that the buffer tank 6 is provided with a relief valve 8 as shown in FIG.

The filling port 9 for filling the heat carrier medium
Is preferably provided in the buffer tank 6.

This is because if the cold heat transfer pipe 5 is provided with such a filling port 9, heat loss occurs due to heat intrusion from the filling port 9, but the buffer tank 6 is provided on the premise that it is installed at room temperature. This is because the heat invasion from the buffer tank 6 into the cold heat transfer pipe 5 is reduced by the capillary tube 7, so that heat loss can be suppressed.

Although the buffer tank 6 is connected by the capillary tube 7 in the above description, the present invention is not limited to this, and as shown in FIG. 3, the connection pipe 10 of the same type as the cold heat transfer pipe 5 is used. The same effect can be obtained by adjusting the amount of the operating heat transfer medium flowing through the cold heat transfer pipe 5 flowing into the buffer tank 6 by the flow rate adjusting valve 18 connected by the above.

As shown in FIG. 4, the Stirling refrigerator has a driving device 11 for generating a driving force by a motor 14.
And a cold heat generating device 33 that is driven by the driving device 11 to generate cold heat.

The drive device 11 has a motor housing having a motor chamber 13 inside, and the motor chamber 13 is composed of a stator 15 and a rotor 16 and is capable of normal and reverse rotation.
4 is installed, and the generated rotational power is output via the motor shaft 17.

The cold heat generator 33 includes a power converter 34 for converting the rotational power generated by the drive device 11 into reciprocating power, a compressor 64 for compressing the working gas, an expander 90 for expanding the working gas, and a compression chamber 66. A heat storage unit 174 that is provided in a gas flow path 175 that communicates with the expansion chamber 92 and that stores the heat of flowing working gas, and a heat radiating unit 193 that radiates the heat of the working gas that has been compressed by the compression unit 64 and has increased in temperature to the outside. , A cold head part 219 for supplying the cold heat generated by the expansion of the working gas in the expansion part 90 to the equipment utilizing cold heat, and an oil seal part for preventing the oil 248 of the crank chamber 36 from entering the compression chamber 66 and the expansion chamber 92. 148, back pressure chamber 15
4 and the crank chamber 36, and a pressure adjusting portion 125 that suppresses the generation of a differential pressure.

The power converter 34 has an internal crank chamber 36.
The crank housing is formed in contact with the motor housing through the motor housing top 19.

The motor shaft 17 and the crank shaft 37 are
It is rotatably supported by a bearing 21.

The motor housing and the crank housing are sealed with a lid, and the motor housing, the crank housing, and the motor housing top 1
9 is manufactured by casting.

By the way, a gas other than the atmosphere such as helium, hydrogen and nitrogen can be used as the working gas. In this case, the working gas is also enclosed in the crank chamber, the motor chamber and the buffer tank. It is preferable.

This is because the atmosphere in the crank chamber, the motor chamber, and the buffer tank slightly intrudes into the compression chamber and the expansion chamber due to long-time operation.

In the crank chamber 36, a crank shaft 37 connected to the motor shaft 17, a crank 38 composed of a compression crank 38a and an expansion crank 38b mounted on the crank shaft 37, and a compression connecting end connected to the crank 38. A connecting rod 41 including a rod 41a and an expanding connecting rod 41b, a cross guide head 44 including a compression cross guide head 44a and an expansion cross guide head 44b connected to the other end of the connecting rod 41, and the cross guide head 44.
There is provided a cross guide liner 47 and the like including a compression cross guide liner 47a and an expansion cross guide liner 47b for restricting the movement direction of 1 to one direction.

The compression crank 38a and the expansion crank 38b are provided eccentrically with respect to the axial center of the crankshaft 37, and when the motor 14 rotates in the normal direction, the expansion crank 38a.
b is provided so as to rotate in advance of the compression crank 38a by approximately 90 degrees in phase.

Here, the normal rotation of the motor 14 refers to the direction of rotation of the motor 14 when performing a cycle operation that produces cold heat.

At this time, the Stirling refrigerator 30 is provided with a balancer 51 in order to suppress the rotational imbalance caused by the phase difference between the expansion crank 38b and the compression crank 38a.

The cross guide liner 47 is a substantially cylindrical hole into which the cross guide head 44 is inserted, and is formed by punching the top of the crank housing.

As a result, the cross guide head 44 driven by the crank 38 is guided by the cross guide liner 47 to reciprocate.

The compression portion 64 includes a compression cylinder 68 and a compression cylinder 6 formed by making a hole in the cylinder housing 74.
8, a compression piston 67 which reciprocates in one end, one end of which is swingably attached to the compression cross guide head 44a and the other end of which is fixedly attached to the compression piston 67, which connects the compression piston 67 and the compression piston 67. It has a compression chamber 66 formed by the head side and a compression cylinder 68.

A piston ring is attached to the side cylindrical surface of the compression piston 67 to keep the compression chamber 66 airtight.

The expansion section 90 has an expansion cylinder 97, an expansion piston 93 that reciprocates in the expansion cylinder 97, one end swingably attached to the expansion cross guide head 44b, and the other end fixed to the expansion piston 93. An expansion piston rod 100 connecting these parts, an expansion chamber 92 formed by the head side of the expansion piston 93 and an expansion cylinder 97, and a cold head part 219 is formed on the outer peripheral part of the expansion chamber 92. ing.

A piston ring is attached to the expansion piston 93 to keep the expansion chamber 92 airtight.

An annular groove 108 is formed so as to surround the lower end of the expansion piston 93, and the gas passage 175 is connected to the annular groove 108 and communicates with the compression chamber 66.

The heat storage section 174 has a cylindrical heat storage material 176 made of a mesh-shaped metal sheet made of brass or stainless steel, and a large number of heat storage materials 176 are stacked and mounted.

Then, when the working gas expanded in the expansion chamber 92 and lowered in temperature flows toward the compression chamber 66,
The cold heat of the working gas is stored and used to cool the working gas flowing from the compression chamber 66 to the expansion chamber 92.

When the working gas that has been compressed in the compression chamber 66 and has increased in temperature flows from the compression chamber 66 toward the expansion chamber 92, the heat of the working gas is stored, and the heat is stored in the expansion chamber 92. Used to heat the working gas flowing from the compression chamber 66 to the compression chamber 66.

The heat radiating portion 193 is provided mainly for the purpose of quickly releasing the heat of the working gas, which has been compressed by the compression portion 64 and has increased in temperature, to the outside, and is provided with the radiator 195 having fins.

The cooling water circulating through the heat radiating portion 193 circulates in the cooling water circuit 202 by the circulation pump 198.

Then, the heat radiation exchanger 196 provided in the cooling water circuit 202 exchanges heat with the outside air blown by the blower fan 197 to cool it.

In the Stirling refrigerator 30 according to the present invention, when the crank 38 rotates, the oil 248 stored in the bottom portion of the crank chamber 36 is scraped up to the crank 3
8 and the connecting rod 41, the cross guide head 44 and the cross guide liner 47, and the like are attached to the sliding parts to lubricate these sliding parts.

At this time, the reciprocating movement of the cross guide head 44 causes the oil 248 in the sliding portion between the cross guide head 44 and the cross guide liner 47 to move into the compression piston 67.
And the expansion piston 93 side, the head side of the cross guide head 44 (the compression piston 67 and the expansion piston 93
Side).

Since the cross guide head 44 reciprocates at a very fast cycle, the oil 2 accumulated in this way is
48 is bounced off and adheres to the compression piston 67 and the expansion piston 93, and this is sent to the compression chamber 66 and the expansion chamber 92 by the reciprocating motion of the compression piston 67 and the expansion piston 93, thereby lowering the refrigeration efficiency.

The amount of oil 248 accumulated on the head side of the cross guide head 44 depends on the pressure difference between the head and the bottom of the cross guide head 44, and when a large pressure difference occurs, the amount of oil 248 accumulated is large. And the compression chamber 66
A large amount of oil 248 enters the expansion chamber 92.

The temperature of the crank chamber 36 rises due to the long-term operation of the Stirling refrigerator 30, but the pressure in the crank chamber 36 rises as the temperature rises.

That is, the oil 2 is stored in the compression chamber 66 and the expansion chamber 92.
The main reason for the intrusion of 48 is mainly the reciprocating movement of the cross guide head 44 and the like, and the differential pressure between the back pressure chamber 154 and the crank chamber 36.

Therefore, in order to prevent the oil 248 fed by the cross guide head 44 from adhering to the compression piston 67 and the expansion piston 93, an oil seal portion 148 having an oil seal bellows as a main component is provided.

Such an oil seal portion 148 has an oil seal bellows 149 provided between the cross guide head 44 and the expansion piston 93 and the compression piston 67.
And has an airtight partition between the cross guide head 44 and the expansion piston 93 and the compression piston 67. Hereinafter, the space on the expansion piston 93 and compression piston 67 side is referred to as the back pressure chamber 154.

As the oil seal bellows 149, a metal forming bellows integrally formed by pressing a metal material or a metal welding bellows assembled by welding is used.

As a result, the back pressure chamber 154 becomes airtight, and the inconvenience of the oil 248 entering the compression chamber 66 and the expansion chamber 92 from the crank chamber 36 can be completely prevented.

The back pressure chamber 154 is formed on each of the back pressure side of the compression piston 67 and the back pressure side of the expansion piston 93, and the back pressure chamber communication hole 155 is formed so that they communicate with each other.
Are formed.

By the way, the space volume on the crank chamber 36 side is sufficiently larger than the space volume of the back pressure chamber 154.

The space volume on the crank chamber 36 side is the sum of the crank chamber 36 and the motor chamber 13 because they communicate with each other.

When the back pressure chamber 154 is in an airtight state under such a volume relationship, the expansion piston 93 and the compression piston 6 are
Due to the reciprocating operation of No. 7, a large pressure fluctuation is generated in the back pressure chamber 154, and a large pressure difference is generated between the back pressure chamber 154 and the crank chamber 36.

When the pressure in the back pressure chamber 154 becomes higher than the pressure in the crank chamber 36, the oil seal bellows 149.
When the pressure in the back pressure chamber 154 becomes lower than the pressure in the crank chamber 36, on the contrary, the oil seal bellows 149 expands like a beader.

Such a deformation is repeatedly caused in the oil seal bellows 149, and is easily damaged.

Further, since the pressure fluctuation in the back pressure chamber 154 acts as a brake for the reciprocating motion of the expansion piston 93 and the compression piston 67, the load on the motor 14 increases correspondingly, and the refrigeration efficiency decreases.

Therefore, a back pressure chamber communication hole 155 is provided to communicate the back pressure chambers 154 formed on the back pressure side of the compression piston 67 and the back pressure side of the expansion piston 93, respectively.

Since the compression piston 67 and the expansion piston 93 reciprocate while maintaining a predetermined phase difference, their back pressure side pressure also fluctuates while maintaining a predetermined phase difference.

Therefore, by connecting the back pressure side of the compression piston 67 and the back pressure side of the expansion piston 93 through the back pressure chamber communication hole 155, the pressure fluctuations are mutually absorbed.

However, even with such a structure, the pressure is completely reduced due to the difference in space volume between the back pressure side of the compression piston 67 and the back pressure side of the expansion piston 93, the flow resistance of the atmosphere filling the back pressure chamber 154, and the like. Unable to absorb fluctuations.

Therefore, a pressure adjusting portion 125 having a buffer tank 126 is provided so that more complete pressure fluctuation can be performed.

The buffer tank 1 of the pressure adjusting unit 125
26 includes a pressure adjusting bellows 127 that airtightly divides the space in the tank into two spaces. One space communicates with the back pressure chamber 154 by the back pressure side communication pipe 128, and the other space communicates with the crank side communication pipe 130. Communicates with the crank chamber 36 and the motor chamber 13.

A space communicating with the back pressure chamber 154 is referred to as a back pressure side buffer chamber 129, and a space communicating with the crank chamber 36 is referred to as a crank side buffer chamber 131.

At least the back pressure side buffer chamber 12
The space volume of 9 is sufficiently larger than the space volume of the back pressure chamber 154.

As the pressure adjusting bellows 127, a metal forming bellows or a metal welded bellows can be used similarly to the oil seal bellows 149, but the expansion and contraction amount is not so large as that of the oil seal bellows 149. It is also possible to use a rubber bellows.

As a result, the pressure fluctuation in the back pressure chamber 154 is automatically alleviated by the pressure fluctuation in the back pressure side buffer chamber 129, and is absorbed by the expansion and contraction of the pressure adjusting bellows 127, so that the back pressure chamber 154 and the crank chamber 36 are separated. Between the oil seal bellows 14
9 can be prevented from being deteriorated or destroyed, and the Stirling refrigerator 30 can be improved in operation performance and durability.

Since the motor chamber 13 communicates with the crank chamber 36, the same effect can be obtained even if the crank side buffer chamber 131 communicates with the motor chamber 13.

The cold head portion 219 has the cooling fins 2
20 and a jacket (not shown) provided so as to enclose the tip portion of the cooling fin 220, and a flow path for the heat transfer medium is formed between the cooling fin 220 and the jacket.

As the heat carrier medium, ethyl alcohol, HFE, PFC, PFG, nitrogen, helium, argon or the like can be used.

As a result, the heat transfer medium is cooled through the cooling fins 220 by the cold heat generated in the expansion chamber 92, and the cold heat is supplied to the cold heat utilizing equipment.

Next, the operation of the Stirling refrigerator 30 having such a configuration will be described.

When the motor 14 is driven, its rotational power is transmitted to the crankshaft 37 via the motor shaft 17.

A crank 38 is eccentrically attached to the crank shaft 37, and a cross guide head 44 is connected to the crank 38 via a connecting rod 41. Therefore, the rotational power is the reciprocating power of the cross guide head 44. To be converted.

When the cross guide head 44 reciprocates, the expansion piston 9 connected through the piston rod.
3 and the compression piston 67 reciprocate to compress the working gas,
Expands.

At this time, the oil 24 is applied by the crank 38.
8 adheres to the cross guide head 44 and the like, but the crank chamber 36 and the back pressure chamber 15 are prevented by the oil seal bellows 149.
4 and 4 are completely partitioned.

The pressure difference between the back pressure chamber 154 and the expansion chamber 92 is adjusted by the buffer tank 126 to suppress the generation of the pressure difference between them. At this time, the pressure adjusting bellows 127 is used. Since the buffer tank 126 is partitioned by the buffer tank 126, the oil 248 does not flow from the crank chamber 36 or the like into the back pressure chamber 154 via the buffer tank 126.

Therefore, the oil 248 does not enter the back pressure chamber 154 and the compression chamber 66 and the expansion chamber 92,
It is possible to prevent the reduction of refrigeration efficiency.

Since the buffer tank 126 suppresses the differential pressure between the back pressure chamber 154 and the expansion chamber 92, the load on the motor 14 is reduced, and the reduction in refrigeration efficiency can be suppressed.

In this way, when the expansion piston 93 and the compression piston 67 reciprocate and the expansion piston 93 approaches the top dead center and becomes slow in movement, the compression piston 67 rapidly moves near the middle toward the top dead center. As a result, the working gas is substantially adiabatically compressed and its temperature rises.

The compressed working gas flows through the gas passage 175 and flows into the heat radiating portion 193, where it radiates heat to the cooling water via the radiator 195 to lower the temperature.

The cooling water is circulated in the cooling water circuit 202 in the circulation pump 198 and is cooled by exchanging heat with the outside air in the heat radiation exchanger 196.

The working gas radiated to the cooling water is stored in the heat storage unit 17
4 flows into the heat storage material 4 and passes through the heat storage material 176.
The heat is stored in 76 and flows into the expansion chamber 92.

Then, the compression piston 67 approaches the top dead center, and its speed also slows down.

Then, the expansion piston 93 rapidly moves toward the bottom dead center, whereby the expansion chamber 92 rapidly expands, and the working gas in the expansion chamber 92 adiabatically expands and cools.

As a result, the temperature of the cold head portion 219 is lowered, the heat transfer medium is cooled through the cooling fins 220, and cold heat is supplied to the cold heat utilization equipment.

When the expansion piston 93 moves from the bottom dead center to the top dead center, the compression piston 67 moves from the intermediate position toward the bottom dead center, whereby the working gas is expanded.
To the compression chamber 66 through the gas flow path 175.

At this time, the working gas that has expanded and decreased in temperature stores cold heat in the heat storage material 176 and flows into the compression chamber 66 via the heat radiating portion 193 to complete one cycle.

[0104]

As described above, according to the present invention,
Since the cold heat transfer pipe between the transfer pump and the heat exchanger on the cold heat source side is provided with a buffer tank for suppressing an increase in the internal pressure of the cold heat transfer pipe, the cold heat transfer device is stopped so that the heat transfer medium becomes room temperature. Even under such a circumstance, the high withstand voltage is not required for each member, and the cost can be reduced.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a cold heat transfer apparatus applied to an explanation of an embodiment of the present invention.

FIG. 2 is a configuration diagram of a cold heat transfer device when a relief valve or the like is provided.

FIG. 3 is a configuration diagram of a cold heat transfer device when a flow rate adjusting valve or the like is provided.

FIG. 4 is a schematic configuration of a Stirling refrigerator.

FIG. 5 is a configuration diagram of a cold heat transfer device applied to a description of a conventional technique.

[Explanation of symbols]

1 Cold heat transfer device 2 Cold heat source side heat exchanger 3 Load side heat exchanger 4 Conveyor pump 5 Cold heat transfer piping 6 buffer tanks 7 Capillary tube 8 relief valve 9 Filling port 10 connection piping 18 Flow control valve

─────────────────────────────────────────────────── ───

[Procedure amendment]

[Submission date] July 9, 2002 (2002.7.9)

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0008

[Correction method] Change

[Correction content]

Therefore, an object of the present invention is to provide a cold / heat transfer device which enables cost reduction by requiring a small withstand voltage value for each component even when the cold / heat transfer device is stopped. And

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0009

[Correction method] Change

[Correction content]

[0009]

In order to solve the above problems, the invention according to claim 1 provides a cold heat source side heat exchanger for exchanging heat between a heat carrying medium and a cold heat source, and pressure-feeding the heat carrying medium. In a cold heat transfer device in which a transfer pump and a load side heat exchanger for exchanging heat between the heat transfer medium and the cold heat utilization device are sequentially connected by a cold heat transfer pipe, between the transfer pump and the cold heat source side heat exchanger. The cold heat transfer pipe is provided with a buffer tank that suppresses an increase in the internal pressure of the cold heat transfer pipe, so that even if the cold heat transfer device stops, the withstand pressure value required for each component can be small. It is characterized by enabling cost reduction.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0047

[Correction method] Change

[Correction content]

The expansion section 90 has an expansion cylinder 97, an expansion piston 93 that reciprocates in the expansion cylinder 97, one end swingably attached to the expansion cross guide head 44b, and the other end fixed to the expansion piston 93. , An expansion piston rod 100 connecting them, an expansion chamber 92 formed by the head side of the expansion piston 93 and an expansion cylinder 97, and a cold head portion 219 formed on the outer peripheral portion of the expansion chamber 92. There is.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0050

[Correction method] Change

[Correction content]

The heat storage section 174 has a cylindrical heat storage material 176 made of a mesh-shaped metal sheet made of brass or stainless steel, and a large number of the heat storage materials 176 are stacked and mounted.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0092

[Correction method] Change

[Correction content]

The pressure difference between the back pressure chamber 154 and the crank chamber 36 is adjusted by the buffer tank 126 to suppress the generation of the pressure difference between them. At this time, the pressure adjusting bellows 127 is used. Since the buffer tank 126 is partitioned by the buffer tank 126, the oil 248 does not flow from the crank chamber 36 or the like into the back pressure chamber 154 via the buffer tank 126.

[Procedure correction 6]

[Document name to be amended] Statement

[Correction target item name] 0094

[Correction method] Change

[Correction content]

Since the buffer tank 126 suppresses the pressure fluctuation in the back pressure chamber 154, the load on the motor 14 is reduced and the reduction in refrigeration efficiency can be suppressed.

[Procedure Amendment 7]

[Document name to be corrected] Drawing

[Name of item to be corrected] Fig. 4

[Correction method] Change

[Correction content]

[Figure 4]

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hiroshi Sekiya             2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture             Within Yo Denki Co., Ltd. F-term (reference) 3L044 BA02 DB02 DD06 FA02 KA02

Claims (6)

[Claims] 1. A cold heat source side heat exchanger for exchanging heat between a heat carrier medium and a cold heat source, a carrier pump for pumping the heat carrier medium, and a load side for heat exchange between the heat carrier medium and the cold heat utilization device. In a cold heat transfer device in which a heat exchanger is sequentially connected by a cold heat transfer pipe, in a cold heat transfer pipe between the transfer pump and the cold heat source side heat exchanger, a buffer for suppressing an increase in internal pressure of the cold heat transfer pipe A cold heat transfer device, which is provided by connecting a tank. 2. The cold heat transfer apparatus according to claim 1, wherein the buffer tank is connected to a cold heat transfer pipe connecting the transfer pump and the cold heat source side heat exchanger via a capillary tube. 3. When the buffer tank is connected to the cold heat transfer pipe connecting the transfer pump and the cold heat source side heat exchanger, a pressure adjustment is performed so that the internal pressure of the cold heat pipe by the buffer tank can be adjusted. The cold heat transfer apparatus according to claim 1 or 2, wherein the cold heat transfer apparatus is connected via a heater. 4. The cold heat transfer apparatus according to claim 3, wherein the buffer tank is provided with a relief valve for preventing the pressure in the buffer tank from exceeding a predetermined pressure. 5. The space volume of the buffer tank is approximately 10 times the total volume in the circulation path of the heat carrier medium formed by the cold heat carrier pipe, the cold heat source side heat exchanger, the load side heat exchanger, and the like. It is set to 1.
4. The cold heat transfer device according to any one of 4 to 4. 6. The cold heat transfer apparatus according to claim 1, wherein the cold heat source is a Stirling refrigerator that compresses / expands a heat transfer medium to generate cold heat.