JP4169560B2 - Stirling cold supply system and operation method thereof - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a Stirling cold supply system that can supply cold heat generated by using a Stirling refrigerator unit to a cold utilization device and an operation method thereof.
[0002]
[Prior art]
The Stirling refrigerator unit can be reduced in size, has a high coefficient of performance and refrigeration efficiency, has a feature that the generated temperature range can be lowered, and can be easily replaced with Freon in recent global environmental problems (helium can be used). Has certain characteristics.
[0003]
For this reason, low-temperature liquid circulators, low-temperature thermostats, thermostats, heat shock test equipment, freeze dryers, temperature characteristic test equipment, including commercial and household cold-use equipment such as freezers, refrigerators, throw-in coolers, etc. Use as a cold heat source in blood / cell storage devices, cold coolers, various measuring devices, and the like is being studied.
[0004]
FIG. 11 is a circuit diagram showing a schematic configuration of such a Stirling cooler supply system 100. A Stirling refrigerator unit 110, a cooling water device 120 that processes waste heat of the Stirling refrigerator unit 110, a heat transfer device 130, and the like are shown. (See Patent Documents 1 and 2).
[0005]
In such a Stirling refrigerator unit 110, as shown in FIG. 12, the compression piston 111 reciprocates in the compression cylinder 112, so that the working gas (helium) in the compression space 113 formed between them is generated. The compression part 114 to be compressed and the expansion piston 115 reciprocate in the expansion cylinder 116 to expand the working gas in the expansion space 117 formed between them, the expansion part 118, the compression space 113 and the expansion space 117. The heat storage part 119 etc. which were provided in the gas flow path S which communicates are provided.
[0006]
Then, the motor 109 is driven and the crank mechanism 108 converts rotational power into reciprocating power, and the reciprocating power causes the compression piston 111 and the expansion piston 115 to reciprocate to compress / expand the working gas.
[0007]
The compressed working gas passes through the gas flow path S, accumulates heat in the heat accumulating unit 119, moves to the expansion space 117, and expands here, thereby generating cold (heat absorbing action).
[0008]
This cold heat cools the cold head 131 provided at the head of the expansion section 118. Since the secondary refrigerant circulates in the cold head 131, the secondary refrigerant is cooled to lower the temperature.
[0009]
The working gas expanded in the expansion unit 118 returns to the compression unit 114 through the heat storage unit 119, and one cycle is completed.
[0010]
The expansion piston 115 moves with a phase advance of approximately 90 degrees with respect to the compression piston 111.
[0011]
The heat transfer device 130 includes a secondary refrigerant pump 132 that pumps the secondary refrigerant so that the secondary refrigerant can circulate through a secondary refrigerant circuit formed so as to connect the cold head 131 and the cold energy utilization device 101.
[0012]
By the way, although the temperature rises when the working gas is compressed by the compression unit 114, the temperature of the working gas that moves to the expansion unit 118 via the heat storage unit 119 rises as it is, and the efficiency of generating cold heat decreases.
[0013]
In view of this, a cooling water device 120 (not shown in FIG. 12) is provided around the gas flow path S from the compression unit 114 to the heat storage unit 119 to cool the working gas flowing therethrough. It is like that.
[0014]
As shown in FIG. 11, the cooling water device 120 includes a working gas side heat exchanger (not shown) that exchanges heat between the working gas and the cooling water, a radiator 121 that exchanges heat between the cooling water and the atmosphere, and a working gas side heat exchanger. The cooling water pump 122 circulates the cooling water between the radiator 121 and the radiator 121.
[0015]
As a result, the working gas is cooled, and the heat is radiated to the atmosphere, so that the efficiency of generating cold heat is improved.
[0016]
[Patent Document 1]
Japanese Patent Laid-Open No. 200-186618
[Patent Document 2]
Japanese Patent Laid-Open No. 200-186619
[0017]
[Problems to be solved by the invention]
However, in the above configuration, there is a problem that it takes a considerable time to start the Stirling cold supply system 100 and lower the secondary refrigerant to a desired temperature (for example, −80 ° C.) (hereinafter referred to as pull-down). is there.
[0018]
That is, the Stirling refrigerator unit 110 is a cycle in which a working gas such as helium is compressed, released, expanded, and absorbed, unlike a refrigeration cycle that repeats normal compression, condensation, decompression, and evaporation. Although it has a generation capability, the temperature decrease rate of the cooling heat is not large in terms of unit time, and the time for the secondary refrigerant to reach the desired temperature becomes long depending on the cooling load of the secondary refrigerant.
[0019]
Accordingly, in order to pull down the Stirling refrigerator unit 110, the heat transfer device 130, and the cold energy utilization device 101 to a desired temperature range, a corresponding time is required.
[0020]
Of course, as shown in FIG. 13, it is possible to shorten the time required for pull-down by increasing the cooling power supply capacity by using a plurality of Stirling refrigerator units 110, but in this case, the cost increases. There is a problem that becomes a factor.
[0021]
Therefore, the present invention provides a Stirling cold heat supply system and an operation method thereof capable of reducing the pull-down time with a simple and inexpensive configuration and enhancing the cold heat generation capability of the Stirling refrigerator unit. For the purpose.
[0022]
[Means for Solving the Problems]
  In order to solve the above problems, the invention according to claim 1 is a Stirling refrigerator unit that compresses and expands a working gas to generate cold heat, cools the secondary refrigerant by the cold heat generated by the Stirling refrigerator unit, A heat transfer device for transferring the secondary refrigerant to the cold energy utilization device.WhileA compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, a decompressor that decompresses the refrigerant from the condenser, A refrigerant chiller unit provided with an evaporator for cooling the secondary refrigerant by the evaporation action of the refrigerant depressurized by the decompression device is provided.In the Stirling cold supply system, when starting the operation of the Stirling cold supply system, after operating the refrigerant chiller unit to cool the secondary refrigerant to a predetermined temperature, the Stirling refrigerator unit is operated, and the refrigerant chiller unit Stop drivingIt is characterized by that.
[0025]
  Claim2The invention according to the present invention is characterized in that a period for operating the Stirling refrigerator unit and the refrigerant chiller unit simultaneously is provided.
[0026]
  Claim3The invention according toA Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. A compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, and a decompression device that decompresses the refrigerant from the condenser In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by the evaporation action of the refrigerant decompressed by the decompression device,Stirling cold supply systemDrivingWhen starting, operate the refrigerant chiller unit to the specified temperature.2When the next refrigerant is cooled and the operation of the Stirling refrigerator unit is started from a temperature appropriately higher than the predetermined temperature, the refrigerant chiller unit and the Stirling refrigerator unit are simultaneously operated in this temperature range, and when the predetermined temperature is reached. Control is performed so that the operation of the refrigerant chiller unit is stopped and only the Stirling refrigerator unit is operated.
[0027]
  Claim4The invention according toA Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. A compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, and a decompression device that decompresses the refrigerant from the condenser In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by the evaporation action of the refrigerant decompressed by the decompression device,When starting the operation of the Stirling cold supply system, the refrigerant chiller unit and the Stirling refrigerator unit are simultaneously operated to a predetermined temperature to cool the secondary refrigerant, and when the predetermined temperature is reached, the operation of the refrigerant chiller unit is stopped. Control is performed so that only the Stirling refrigerator unit is operated.
[0028]
  Claim5According to the invention, the Stirling refrigerator unit that compresses and expands the working gas to generate cold heat, the secondary refrigerant is cooled by the cold heat generated in the Stirling refrigerator unit, and the secondary refrigerant is conveyed to the cold energy utilization device. In a Stirling cold supply system including a heat transfer device, a compressor that compresses a refrigerant, a condenser that condenses the refrigerant by exchanging heat between the refrigerant discharged from the compressor and outside air or water, and the condensation From the Stirling refrigerator unit by evaporating the refrigerant depressurized by the depressurizer, the evaporator for cooling the secondary refrigerant by the evaporating action of the refrigerant depressurized by the depressurizer, And a switching valve for switching whether the refrigerant from the condenser is effectively evaporated by the evaporator or by the second evaporator. And wherein the door.
[0029]
  Claim6The invention according to the present invention includes a decompressor for an evaporator, a decompressor for a second evaporator,TheIt is characterized by making it different.
[0030]
  Claim7The invention according to claim5Or claims6When starting operation of the described Stirling cold supply system, the refrigerant chiller unit is operated by switching the switching valve so that the refrigerant condensed in the condenser is effectively evaporated in the evaporator, and the secondary refrigerant is kept at a predetermined temperature. And switching the switching valve so that the refrigerant condensed in the condenser is effectively evaporated in the second evaporator.The
[0031]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a circuit diagram of a Stirling cold heat supply system 1 applied to the description of the first embodiment, and FIG. 2 is a diagram showing a configuration of the Stirling refrigerator unit.
[0032]
This Stirling cold supply system 1 includes a single Stirling refrigerator unit 4 that generates cold heat, a cooling water device 5 that exchanges heat with the working gas in the Stirling refrigerator unit 4 and radiates the heat, and a secondary refrigerant ( For example, HFE: any material that can sufficiently carry heat at a desired secondary refrigerant temperature, such as hydrofluoroether, is circulated between the Stirling refrigerator unit 4 and the cold energy utilization device 3 for Stirling refrigeration. A heat transfer device 6 that supplies the cold energy generated in the machine unit 4 to the cold energy utilization device 3; a control device 7 that controls the entire Stirling cold energy supply system 1 so that the amount of cold energy required from the cold energy utilization device 3 can be supplied; In order to shorten the time, the refrigerant chiller unit 8 or the like that cools the secondary refrigerant is a main component.
[0033]
As shown in FIG. 13, it is possible to increase the cooling power supply capacity by using a plurality of Stirling refrigerator units 4 and thereby shorten the pull-down time. In this case, however, the expensive Stirling refrigerator unit 4 Since it is necessary to provide more than one, it causes a cost increase.
[0034]
Further, in the case of a cold energy utilization device 3 such as a low-temperature prober used in a semiconductor facility, for example, a large amount of cold energy is not required at the time of use. If the refrigerator unit 4 is used to shorten the pull-down time, surplus capacity is generated and the economy is reduced.
[0035]
Therefore, in the present invention, as will be described later, a refrigerant chiller unit 8 having a compressor, a condenser, a decompression device, an evaporator, and the like is provided to shorten the pull-down time.
[0036]
As shown in FIG. 2, the Stirling refrigerator unit 4 is formed between a crank portion 12 that converts rotational power of the motor 11 into reciprocating power and a compression piston 14 that reciprocates within the compression cylinder 15. A compression portion 17 that compresses the working gas in the compression space 16, an expansion portion 21 that expands the working gas in the expansion space 20 formed by reciprocating the expansion piston 18 in the expansion cylinder 19, and compression It has a heat storage part 22 made of a metal mesh sheet or the like provided in a gas flow path S that communicates the space 16 and the expansion space 20.
[0037]
In the Stirling refrigerator unit 4, the crank portion 12 is housed in a crank housing 24 having a crank chamber 23 inside, a crank 26 connected to the motor shaft 25, a connecting rod 27 connected to the crank 26 at one end, and the connecting rod. 27, a cross guide head 28 connected to the other end of the head 27, a cross guide liner 29 for restricting the movement direction of the cross guide head 28 in one direction, and the like.
[0038]
Thereby, the rotational power of the motor 11 is converted into reciprocating power by the crank portion 12, and the compression piston 14 and the expansion piston 18 reciprocate.
[0039]
The expansion piston 18 moves with a phase advance of approximately 90 degrees with respect to the compression piston 14.
[0040]
Further, the compression piston 14 and the expansion piston 18 are connected to the cross guide head 28 via the piston rod 30, and one end thereof is closely attached and fixed to the piston rod 30, and the other end thereof is closely attached to the fixed plate 36. A fixed oil seal bellows 37 is provided.
[0041]
The oil seal bellows 37 is a metal bellows that expands and contracts as the piston rod 30 reciprocates, and airtightly partitions the space on the compression piston 14 or expansion piston 18 side and the space on the cross guide head 28 side.
[0042]
As a result, the oil 38 that lubricates the cross guide head 28 and the like adheres to the compression piston 14 and the expansion piston 18 and prevents the refrigerating efficiency from being lowered due to the oil 38 entering the compression space 16 and the expansion space 20.
[0043]
Further, the oil seal bellows 37 causes a space (hereinafter referred to as a back pressure chamber) 39 sandwiched between the oil seal bellows 37 and the compression piston 14 or the expansion piston 18 to be in an airtight state.
[0044]
For this reason, when the compression piston 14 or the expansion piston 18 reciprocates, the atmosphere of the back pressure chamber 39 is compressed and expanded, and the energy required for this compression and expansion becomes a motor load, which reduces the efficiency of generating heat.
[0045]
Therefore, a buffer tank 41 in which the back pressure chamber 39 and the crank chamber 23 are connected via a bellows 40 is provided.
[0046]
Further, the working gas side heat exchanger 35 is provided so as to cover the compression space 16 or to surround the gas flow path S that communicates the compression space 16 and the heat storage unit 22 so that the cooling water circulates. ing.
[0047]
In the Stirling refrigerator unit 4 having such a configuration, when the compression piston 14 moves from the bottom dead center to the top dead center, the working gas in the compression space 16 is compressed. During this time, the expansion piston 18 moves upward, reaches the top dead center, and then moves downward.
[0048]
The working gas compressed with the upward movement of the compression piston 14 flows through the gas flow path S and is sent to the expansion portion 21 side. When the expansion piston 18 moves downward, the working gas passes through the heat storage portion 22 and expands. 20 is sent.
[0049]
When the working gas passes through the heat storage unit 22, the heat is stored in the heat storage unit 22.
[0050]
As the expansion piston 18 reaches bottom dead center, the compression piston 14 moves from top dead center to bottom dead center, and the working gas expands.
[0051]
Since the expansion process at this time is an isothermal expansion process, the heat absorption accompanying the expansion is performed via the cold head 45 provided at the top of the expansion space 20, and as a result, the temperature of the cold head 45 is lowered and cold heat is generated. Since the secondary refrigerant circulates in contact with the cold head 45 in thermal contact as will be described later, the secondary refrigerant is cooled by the generated cold heat.
[0052]
As the compression piston 14 approaches the bottom dead center, the expansion piston 18 starts to move upward, and the working gas passes through the gas flow path S and exchanges heat in the heat storage unit 22 and returns to the compression space 16.
[0053]
By operating such a cycle as one cycle, the cold heat of the cold head 45 is used for the cold energy utilization device 3.
[0054]
The heat transfer device 6 includes a cold heat source side heat exchanger that exchanges heat between the cold heat and the secondary refrigerant, and the cold heat source side heat exchanger is formed by the cold head 45 described above. Hereinafter, the cold head 45 is referred to as a cold heat source side heat exchanger 45.
[0055]
The heat transfer device 6 has a secondary refrigerant pump 46 that circulates the secondary refrigerant to the cold energy utilization device 3 as a main component.
[0056]
When the working gas is compressed by the Stirling refrigerator unit 4, the temperature of the working gas rises. If the working gas is sent to the expansion unit 21 via the heat storage unit 22 in a state where the temperature has risen, the efficiency of generating cold heat decreases. For this reason, the cooling water device 5 is provided to dissipate the heat of the working gas to the atmosphere and transfer it to the expansion section 21.
[0057]
The cooling water device 5 is an operation in which a cooling water passage is formed so as to surround the gas flow path S between the compression space 16 and the heat storage unit 22 in the Stirling refrigerator unit 4 to exchange heat between the working gas and the cooling water. A gas-side heat exchanger 35, a radiator 65 that is an atmosphere-side heat exchanger that exchanges heat between the cooling water heat-exchanged in the working gas-side heat exchanger 35 and the atmosphere, and air is blown to the radiator 65 to supply the cooling water and the atmosphere. And a cooling water pump 67 for circulating cooling water between the working gas side heat exchanger 35 and the radiator 65, and the like.
[0058]
The refrigerant chiller unit 8 includes a compressor 71 that compresses a low-temperature refrigerant, such as R404A, a condenser 72 that condenses the refrigerant from the compressor 71 by exchanging heat with the outside air, and a decompression that depressurizes the refrigerant from the condenser 72. The apparatus 74, the evaporator 75 that cools the secondary refrigerant by exchanging heat between the refrigerant decompressed by the decompressor 74 and the secondary refrigerant, the receiver tank 73 that adjusts the circulating refrigerant amount, and the like are the main components. .
[0059]
The evaporator 75 is a double-pipe heat exchanger or a plate-type two-circuit heat exchanger. A refrigerant and a secondary refrigerant circulate, and the refrigerant absorbs heat from the secondary refrigerant and evaporates. As a result, the secondary refrigerant is cooled.
[0060]
The control device 7 includes a temperature detector 76 for detecting the secondary refrigerant, a register 77 for storing the detected temperature, and a setting for operating and stopping the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 when a preset temperature is reached. A memory 78 in which values are stored, a setting value is read from the memory 78, and a control unit 79 for operating and stopping the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 is compared with the contents of the register 77.
[0061]
The temperature of the secondary refrigerant is detected every predetermined time, and a plurality of measurement results are stored in the register 77.
[0062]
Next, operation | movement of the Stirling cold-heat supply system 1 of such a structure and its control method are demonstrated.
[0063]
FIG. 3 is a diagram schematically showing a pull-down characteristic (solid line) (hereinafter referred to as pull-down characteristic) in the Stirling refrigerator unit 4 and a pull-down characteristic (one-dot chain line) in the refrigerant chiller unit 8. As can be seen from the figure, the Stirling refrigerator unit 4 can be gradually lowered in temperature from the refrigerant chiller unit 8 at the time of start-up, and can be lowered to a temperature of −80 ° C. or lower.
[0064]
On the other hand, in the refrigerant chiller unit 8 using R404A as the refrigerant, the temperature drops faster than the Stirling refrigerator unit 4 at the time of activation, but it is difficult to lower the temperature to below -40 ° C.
[0065]
Therefore, in the present invention, as shown in FIG. 4, the refrigerant chiller unit 8 is operated at the time of start-up (a dashed-dotted region), and reaches a temperature range where the temperature drop rate of the refrigerant chiller unit 8 is slow (for example, −40 ° C.). Then, by switching to the operation of the Stirling refrigerator unit 4, the pull-down time is shortened while maintaining the ability to supply cold heat to extremely low temperatures.
[0066]
Such operation control will be described with reference to the flowchart shown in FIG. It should be noted that the flow of large control is as follows: (1) T ≧ −35 ° C., (2) −35 ° C.> T ≧ −40 ° C., (3) −40 In the case of ° C> T ≧ −76 ° C., (4) in the case of −76 ° C.> T ≧ −80 ° C., in the case of (5) T <−80 ° C.
[0067]
In the following description, a case where control is performed based on temperatures such as −35 ° C., −40 ° C., −76 ° C., and −80 ° C. will be described. I will add.
[0068]
That is, −40 ° C. is an example of the reached temperature of the secondary refrigerant by the refrigerant chiller unit 8, and −80 ° C. is an example of the temperature required in the cold energy utilization device 3. Depending on the configuration of the refrigerant chiller unit 8 including the type of refrigerant and the scale of the chiller 8, the temperature reached by the refrigerant chiller unit 8 may differ, and the temperature required for the cold energy utilization device 3 is other than -80 ° C. There are times.
[0069]
Further, −35 ° C. is an example of a temperature at which the pull-down characteristic becomes dull as the refrigerant chiller unit 8 approaches the ultimate temperature (the temperature decrease rate becomes small), and the dullness of the pull-down characteristic starts to become noticeable. Similar to the case of temperature, the temperature varies depending on the refrigerant and the configuration of the refrigerant chiller unit 8.
[0070]
Further, at -76 ° C., since the Stirling refrigerator unit 4 supplies cold heat in a certain temperature range by repeating operation and stop, the Stirling refrigerator unit 4 is operated and stopped as conditions for supplying cold heat in this temperature range. This is a setting parameter determined by the temperature required by the cold energy utilization device 3 as a matter of course.
[0071]
When the system is activated, that is, when the operation is started, first, it is determined whether or not the temperature of the secondary refrigerant is in the temperature range of T ≧ −35 ° C. of (1). Only the unit 8 is operated (processing of step SA1 → SA2).
[0072]
As a result, the secondary refrigerant is cooled by exchanging heat with the refrigerant in the evaporator 75 and the temperature is lowered. As shown in FIGS. 3 and 4, the temperature drop of the secondary refrigerant caused by the operation of the refrigerant chiller unit 8 is faster than the temperature drop of the secondary refrigerant caused by the Stirling refrigerator unit 4, so that the pull-down time can be shortened. become.
[0073]
Next, it is determined whether or not the temperature of the secondary refrigerant is in the temperature range of −35 ° C.> T ≧ −40 ° C. of (2). In this temperature range, the Stirling refrigerator unit 4 is also operated. Then, simultaneous operation with the refrigerant chiller unit 8 is performed (processing of step SA1 → SA3 → SA4).
[0074]
As described above, since the temperature decrease rate decreases as the refrigerant chiller unit 8 approaches the ultimate temperature, waiting until the refrigerant chiller unit 8 reaches the ultimate temperature of −40 ° C. may lead to a longer pull-down time. There is.
[0075]
Therefore, when the dullness of the pull-down characteristic starts to become noticeable, the simultaneous operation with the Stirling refrigerator unit 4 is performed, so that the pull-down time can be further shortened.
[0076]
In this way, when the secondary refrigerant falls below −40 ° C. and enters the temperature range of −40 ° C.> T ≧ −76 ° C. of (3), the operation of the refrigerant chiller unit 8 is stopped, and the Stirling refrigerator The operation is switched to the unit 4 only (steps SA1 → SA3 → SA5 → SA6).
[0077]
Since the reached temperature of the refrigerant chiller unit 8 is −40 ° C., even if the refrigerant chiller unit 8 is operated further, the secondary refrigerant cannot be cooled. On the contrary, the refrigerant of the refrigerant chiller unit 8 is cooled by the secondary refrigerant. Occurs. Therefore, the operation of the refrigerant chiller unit 8 is stopped and only the operation of the Stirling refrigerator unit 4 is performed.
[0078]
When the Stirling refrigerator unit 4 starts operation and the temperature of the secondary refrigerant enters −76 ° C.> T ≧ −80 ° C. in (4), it is determined whether or not the temperature of the secondary refrigerant continues to drop. .
[0079]
As a result, when the temperature of the secondary refrigerant continues to drop, the current state where only the Stirling refrigerator unit 4 is operated is maintained (processing of steps SA1 → SA3 → SA5 → SA8 → SA9 → SA6).
[0080]
On the other hand, when the temperature drop of the secondary refrigerant has stopped, it is determined that the secondary refrigerant has reached the desired temperature, and the operation of the Stirling refrigerator unit 4 is also stopped (steps SA1 → SA3 → SA5 → SA8 → SA9 → SA10 processing).
[0081]
Whether or not the temperature drop continues is determined from a temperature change obtained from the temperatures of the plurality of secondary refrigerants stored in the register 77.
[0082]
Finally, when the temperature of the secondary refrigerant reaches T <−80 ° C. of (5), since the secondary refrigerant has reached the desired temperature, the operation of the Stirling refrigerator unit 4 is also stopped (Step SA1 → SA3 → SA5 → SA8 → SA10).
[0083]
Thus, when the operation of the Stirling cold energy supply system 1 is started to perform pull-down, only the refrigerant chiller unit 8 is operated so as to shorten the pull-down time. It becomes possible to improve convenience.
[0084]
Next, a second embodiment of the present invention will be described with reference to the drawings. Note that description of the same configuration as that of the first embodiment is omitted as appropriate.
[0085]
In the first embodiment, in order to shorten the pull-down time, when the operation of the Stirling cold heat supply system 1 is started, only the refrigerant chiller unit 8 is operated, and when the temperature reached the refrigerant chiller unit 8 is Stirling. Control to switch to operation of only the refrigerator unit 4 was performed.
[0086]
On the other hand, in the present embodiment, as shown in FIG. 6, the pull-down time is further shortened by simultaneously operating the refrigerant chiller unit 8 and the Stirling refrigerator unit 4 at the time of startup. .
[0087]
In FIG. 6, the two-dot chain line indicates the time when the refrigerant chiller unit 8 and the Stirling refrigerator unit 4 are operated simultaneously, and the solid line indicates the pull-down characteristic when only the Stirling refrigerator unit 4 is operated. Yes. In order to show the difference from the pull-down characteristic in the configuration according to the first embodiment, the pull-down characteristic in the first embodiment is indicated by a dotted line.
[0088]
FIG. 7 is a flowchart showing an operation control procedure in such a case. As a large control flow, (1) T ≧ −40 ° C., (2) T <−40 ° C., (3) -40 In the case of ° C> T> −76 ° C., (4) the process is divided into cases where T ≦ −80 ° C.
[0089]
First, when the Stirling cold supply system 1 is activated, it is determined whether or not the temperature of the secondary refrigerant is in the temperature range of T ≧ −40 ° C. of (1). The temperature of the secondary refrigerant immediately after startup is often room temperature. In such a case, the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 are operated (processing of step SB1 → SB2 → SB3).
[0090]
In the case of this control, the determination process at −35 ° C. is not provided as in the first embodiment. As is clear from the above description, since the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 are operated simultaneously immediately after startup, it is necessary to make the pull-down characteristic of the refrigerant chiller unit 8 slow. Because there is no.
[0091]
When the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 are operated at the same time and the temperature of the secondary refrigerant falls and falls within the temperature range of T <−40 ° C. of (2), the refrigerant chiller unit 8 is further operated. However, since the refrigerant chiller unit 8 becomes a heat load, the operation of the refrigerant chiller unit 8 is stopped (processing of step SB1 → SB2 → SB4).
[0092]
Thereafter, when the temperature of the secondary refrigerant is in the temperature range of −40 ° C.> T> −76 ° C. of (3), only the Stirling refrigerator unit 4 is operated, and the temperature change of the secondary refrigerant is determined.
[0093]
As a result, when the temperature drop of the secondary refrigerant continues, the current state where only the Stirling refrigerator unit 4 is operated is maintained (processing of steps SB1 → SB5 → SB6 → SB4).
[0094]
On the other hand, when the temperature drop of the secondary refrigerant has stopped, it is determined that the secondary refrigerant has reached the desired temperature, and the operation of the Stirling refrigerator unit 4 is also stopped (from step SB1 → SB5 → SB6 → SB7). processing).
[0095]
Finally, when the temperature of the secondary refrigerant reaches T <−80 ° C. in (4), since the secondary refrigerant has reached the desired temperature, the operation of the Stirling refrigerator unit 4 is also stopped (step SB1 → SB5 → SB7).
[0096]
In this way, immediately after the start-up, the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 are operated simultaneously, so that the pull-down time can be greatly shortened, and the cold energy utilization device 3 can be used quickly. Convenience is improved.
[0097]
Next, a third embodiment of the present invention will be described with reference to the drawings. In addition, description is abbreviate | omitted suitably about the same structure as the structure demonstrated so far.
[0098]
In the first and second embodiments, the pull-down time is obtained by operating the refrigerant chiller unit 8 only when the temperature of the secondary refrigerant is −40 ° C. or higher as when the Stirling cold supply system 1 is started. Was shortened.
[0099]
In such a configuration, the refrigerant chiller unit 8 was not used at all when it was used (when the temperature required by the cold energy utilization device 3 reached and the utilization of the cold energy utilization device 3 was started).
[0100]
This is because the temperature required by the cold energy utilization device 3 is -80 ° C. and extremely low temperature, and the reached temperature of the refrigerant chiller unit 8 is −40 ° C. Therefore, the secondary refrigerant is cooled using the refrigerant chiller unit 8. The cause was the inability to do so.
[0101]
Therefore, in the present embodiment, when the temperature of the secondary refrigerant is −40 ° C. or higher, the secondary refrigerant is cooled by the refrigerant chiller unit 8 and the temperature of the secondary refrigerant becomes −40 ° C. or lower. The cooling water of the Stirling refrigerator unit 4 is cooled by the refrigerant chiller unit 8.
[0102]
As described above, in the Stirling refrigerator unit 4, the working gas and the cooling water which are compressed by the compression unit and become high temperature in the working gas side heat exchanger 35 in the cooling water device 5 in order to increase the heat generation efficiency. Heat exchange.
[0103]
At this time, the heat of the working gas is absorbed by the cooling water by heat exchange, and the cooling water circulates in the radiator 65 and dissipates heat to the atmosphere.
[0104]
Accordingly, by causing the refrigerant and the cooling water in the evaporator 75 of the refrigerant chiller unit 8 having a temperature lower than that of the atmosphere to be heat exchangers, the cooling water becomes lower in temperature, and as a result, the temperature of the working gas can be lowered. become.
[0105]
By reducing the temperature of the working gas, the cycle efficiency in the Stirling refrigerator unit 4 is increased, the efficiency of generating cold heat is improved, the temperature drop of the secondary refrigerant can be accelerated, and the temperature reached by the Stirling refrigerator is also increased. It will be improved.
[0106]
With such an effect, as shown in FIG. 13, cold heat corresponding to the case where a plurality of Stirling refrigerator units 4 are used can be generated, and the refrigerant chiller unit 8 can be operated at all times. Economic efficiency improves compared to the case.
[0107]
FIG. 8 is a circuit diagram showing a configuration of the Stirling cooling / heating supply system 1 that performs such an operation. The configurations of the refrigerant chiller unit 8 and the cooling water device 5 are different from the configuration shown in FIG.
[0108]
That is, the refrigerant chiller unit 8 is additionally provided with a second evaporator 80 and a second decompression device 81, and the refrigerant circulation path is switched by a three-way valve (switching valve) 82. The second evaporator 80 is a substitute for the radiator 65 of the cooling water device 5.
[0109]
With such a configuration, when the secondary refrigerant is cooled by the refrigerant chiller unit 8, the three-way valve 82 is switched so that the refrigerant circulates in the flow path indicated by the solid line arrow.
[0110]
Thus, the refrigerant from the compressor 71 is condensed by exchanging heat with the outside air in the condenser 72, and an appropriate amount of this refrigerant is supplied to the decompression device 74 via the receiver tank 73. Thereafter, the refrigerant is decompressed by the decompression device 74 and exchanges heat with the secondary refrigerant in the evaporator 75.
[0111]
The secondary refrigerant is cooled by this heat exchange, and the refrigerant evaporates and returns to the compressor 71 through the evaporator 75.
[0112]
On the other hand, when cooling water is cooled by the refrigerant chiller unit 8, the three-way valve 82 is switched so that the refrigerant circulates in the flow path indicated by the dotted arrow. At this time, the cooling water pump 67 is operated.
[0113]
Thereby, the refrigerant from the compressor 71 is condensed by exchanging heat with the outside air in the condenser 72, and an appropriate amount of this refrigerant is supplied to the second decompression device 81 via the receiver tank 73 and is decompressed. Thereafter, the refrigerant is supplied to the second evaporator 80, where the refrigerant exchanges heat with the cooling water to evaporate and return to the compressor 71. The cooling water is cooled.
[0114]
FIG. 9 is a diagram showing the pull-down characteristic in such a configuration, where the alternate long and short dash line is the pull-down characteristic when the secondary refrigerant is cooled by the refrigerant chiller unit 8, and the solid line is the cooling water cooled by the refrigerant chiller unit 8. The pull-down characteristic is shown. The dotted line in the figure shows the pull-down characteristic in the case of the first embodiment for comparison.
[0115]
As is clear from this figure, it can be understood that when the cooling water is cooled by the refrigerant chiller unit 8, the cooling power generation capability of the Stirling refrigerator unit 4 is improved, so that the pull-down characteristic is also improved. In addition, the improvement in the heat generation capacity of the Stirling refrigerator unit 4 appears as a change in the slope of the pull-down characteristic.
[0116]
FIG. 10 is a flowchart showing an operation method of the Stirling cold heat supply system 1 having such a configuration. When the temperature T of the secondary refrigerant is (1) T ≧ −35 ° C., (2) −35 ° C.> T ≧ In the case of −40 ° C., (3) T <−40 ° C., (4) −76 ° C.> T ≧ −80 ° C., and (5) T <−80 ° C.
[0117]
In FIG. 10, the chiller (secondary refrigerant) means that the refrigerant chiller unit 8 operates to cool the secondary refrigerant, and the chiller (cooling water) means that the refrigerant chiller unit 8 cools the cooling water. That means it is working.
[0118]
First, when the Stirling cold energy supply system 1 is started, it is determined whether or not the temperature of the secondary refrigerant is in the range of T ≧ −35 ° C. of (1). The refrigerator unit 4 is not operated and only the refrigerant chiller unit 8 is operated, and at that time, the three-way valve 82 is switched so as to cool the secondary refrigerant (processing of steps SC1 → SC2 → SC3).
[0119]
In this case, simultaneous operation of the Stirling refrigerator unit 4 is also conceivable, but in the present invention, the Stirling refrigerator unit 4 is stopped. This is because the cooling water is not cooled because the refrigerant chiller unit 8 is used for cooling the secondary refrigerant, and in this state, the Stirling refrigerator unit 4 cannot exhibit a predetermined cold heat generation capability.
[0120]
Of course, the temperature of the refrigerant that has exchanged heat with the secondary refrigerant in the evaporator 75 may be lower than the temperature of the cooling water. In this case, although the cooling water can be cooled, the Stirling refrigerator unit can be cooled. 4 can generate a little amount of cold energy while it cannot exhibit its predetermined cold energy generation capability.
[0121]
Therefore, simultaneous operation of the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 can be performed.
[0122]
When the cooling of the secondary refrigerant proceeds and enters the temperature range of −35 ° C.> T ≧ −40 ° C. in (2), the temperature change of the secondary refrigerant is determined.
[0123]
As a result, when the temperature of the secondary refrigerant is decreasing, it is determined that the secondary refrigerant has not yet been pulled down to the temperature reached by the refrigerant chiller unit 8, and the current state is maintained (steps SC1 → SC2 → SC4). → Process of SC5 → SC6).
[0124]
On the other hand, when the temperature drop of the secondary refrigerant has stopped, it is determined that the secondary refrigerant has reached the temperature reached by the refrigerant chiller unit 8, and the three-way valve 82 is switched (step SC → SC2 → Process of SC4 → SC5 → SC7).
[0125]
The switching of the three-way valve 82 causes the refrigerant to flow through the circulation path indicated by the dotted line arrow shown in FIG. 8 to cool the cooling water, and the cold heat generation capacity of the Stirling refrigerator unit 4 is enhanced. The pull-down time can be shortened.
[0126]
Of course, when the pull-down is completed and the state of use is reached, there is a margin for load fluctuations in the heat-utilizing equipment by the amount of increased heat generation capacity, so that the performance of the system can be improved.
[0127]
The temperature of the secondary refrigerant falls within the temperature range of T <−40 ° C. of (3). This state is normally maintained because the flow is switched by the three-way valve 82 since the state (2) is normally passed, but if not, the process described in (2) is performed. (Steps SC1-> SC1-> SC2-> SC4-> SC7).
[0128]
Next, when the temperature of the secondary refrigerant enters the temperature range of −76 ° C.> T ≧ −80 ° C. of (4), it is determined whether or not the temperature of the secondary refrigerant continues to drop.
[0129]
As a result, when the temperature of the secondary refrigerant is decreasing, the current state is maintained (processing of steps SC1 → SC8 → SC10 → SC7).
[0130]
On the other hand, when the temperature of the secondary refrigerant has stopped decreasing, it is determined that the secondary refrigerant has reached the desired temperature, and the operation of the Stirling refrigerator unit 4 is stopped. At this time, the cooling water is not required to be cooled, so the refrigerant chiller unit 8 also stops operating (step SC1 → SC8 → SC10 → SC9).
[0131]
Finally, when the temperature of the secondary refrigerant reaches T <−80 ° C. of (5), the secondary refrigerant has reached the desired temperature, and the operation of the Stirling refrigerator unit 4 and the refrigerant chiller unit 8 is stopped. (Step SC1 → SC8 → SC9).
[0132]
Thus, since the refrigerant chiller unit 8 is used for cooling the secondary refrigerant and the cooling water in accordance with the temperature of the secondary refrigerant, the pull-down time can be shortened and the cooling of the Stirling refrigerator unit 4 is generated. The capacity can be improved, and the performance of the Stirling cold supply system 1 is improved.
[0133]
【The invention's effect】
  As described above, according to the first aspect of the present invention, the Stirling refrigerator unit that compresses and expands the working gas to generate cold heat, the secondary refrigerant is cooled by the cold heat generated by the Stirling refrigerator unit, A heat transfer device for transferring the secondary refrigerant to the cold energy utilization device.WhileA compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, a decompressor that decompresses the refrigerant from the condenser, A refrigerant chiller unit provided with an evaporator for cooling the secondary refrigerant by the evaporation action of the refrigerant depressurized by the decompression device is provided.In the Stirling cold supply system, when starting the operation of the Stirling cold supply system, after operating the refrigerant chiller unit to cool the secondary refrigerant to a predetermined temperature, the Stirling refrigerator unit is operated, and the refrigerant chiller unit Stop drivingTherefore, the pull-down time can be shortened with a simple and inexpensive configuration.
[0136]
  Claim2According to the invention, the period for operating the Stirling refrigerator unit and the refrigerant chiller unit at the same time is provided.TheTherefore, the pull-down time can be shortened.
[0137]
  Claim3According to the invention concerningA Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. A compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, and a decompression device that decompresses the refrigerant from the condenser In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by the evaporation action of the refrigerant decompressed by the decompression device,Stirling cold supply systemDrivingWhen starting, operate the refrigerant chiller unit to the specified temperature.2When the next refrigerant is cooled and the operation of the Stirling refrigerator unit is started from a temperature appropriately higher than the predetermined temperature, the refrigerant chiller unit and the Stirling refrigerator unit are simultaneously operated in this temperature range, and when the predetermined temperature is reached. Since the operation of the refrigerant chiller unit is stopped and only the Stirling refrigerator unit is operated, the pull-down time can be shortened.
[0138]
  Claim4According to the invention concerningA Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. A compressor that compresses the refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant, and a decompression device that decompresses the refrigerant from the condenser In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by the evaporation action of the refrigerant decompressed by the decompression device,When starting the operation of the Stirling cold supply system, the refrigerant chiller unit and the Stirling refrigerator unit are simultaneously operated to a predetermined temperature to cool the secondary refrigerant, and when the predetermined temperature is reached, the operation of the refrigerant chiller unit is stopped. Since only the Stirling refrigerator unit is operated, the pull-down time can be shortened.
[0139]
  Claim5According to the invention, the Stirling refrigerator unit that compresses and expands the working gas to generate cold, the secondary refrigerant is cooled by the cold generated by the Stirling refrigerator unit, and the secondary refrigerant is used as the cold utilization device. In a Stirling cold supply system comprising a heat transfer device for transferring, a compressor that compresses a refrigerant, a condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant; A decompressor for decompressing the refrigerant from the condenser, an evaporator for cooling the secondary refrigerant by the evaporating action of the refrigerant decompressed by the decompressor, and a Stirling refrigerator by evaporating the refrigerant decompressed by the decompressor A second evaporator that absorbs heat radiation from the unit, and a switching valve that switches whether the refrigerant from the condenser is effectively evaporated by the evaporator or by the second evaporator. Because it was example, simple and inexpensive construction, with shortened pull-down time, it is possible to enhance the cold generating capacity of the Stirling refrigerator unit.
[0140]
  Claim6According to the invention, the decompressor for the evaporator and the decompressor for the second evaporatorTheSince they are different, the circuit configuration becomes simple and control becomes easy.
[0141]
  Claim7According to the invention according to claim5Or claims6When starting operation of the described Stirling cold supply system, the refrigerant chiller unit is operated by switching the switching valve so that the refrigerant condensed in the condenser is effectively evaporated in the evaporator, and the secondary refrigerant is kept at a predetermined temperature. Since the switching valve is switched so that the refrigerant condensed in the condenser is effectively evaporated in the second evaporator after cooling down to the above, the pull-down time can be shortened.
[Brief description of the drawings]
FIG. 1 is a circuit diagram of a Stirling cold heat supply system according to first and second embodiments.
FIG. 2 is a configuration diagram of a Stirling refrigerator unit applied to the description of each embodiment.
FIG. 3 is a schematic diagram of pull-down characteristics of a refrigerant chiller unit and a Stirling refrigerator unit.
FIG. 4 is a schematic diagram of pull-down characteristics in the Stirling cold heat supply system according to the first embodiment.
FIG. 5 is a flowchart showing an operation procedure in the Stirling cold energy supply system according to the first embodiment.
FIG. 6 is a schematic diagram of pull-down characteristics in the Stirling cold heat supply system according to the second embodiment.
FIG. 7 is a flowchart showing an operation procedure in the Stirling cold energy supply system according to the second embodiment.
FIG. 8 is a circuit diagram of a Stirling cold heat supply system according to a third embodiment.
FIG. 9 is a schematic diagram of pull-down characteristics in the Stirling cold heat supply system according to the third embodiment.
FIG. 10 is a flowchart showing an operation procedure in the Stirling cold heat supply system according to the third embodiment.
FIG. 11 is a circuit diagram of a Stirling cold heat supply system applied to the description of the prior art.
FIG. 12 is a circuit diagram of a Stirling cold heat supply system applied to the description of the prior art.
FIG. 13 is a configuration diagram of a Stirling refrigerator unit applied to the description of the prior art.
[Explanation of symbols]
1 Stirling cold supply system
3 Cold energy equipment
4 Stirling refrigerator unit
5 Cooling water device
6 Heat transfer device
7 Control device
8 Refrigerant chiller unit
35 Working gas side heat exchanger
45 cold head
71 Compressor
72 Condenser
74 Pressure reducing device
75 Evaporator
76 Temperature detector
77 registers
78 memory
79 Control unit
80 Second evaporator
81 Second decompressor

Claims (7)

A Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. while Ru equipped,
A compressor for compressing the refrigerant;
A condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant;
A decompression device for decompressing the refrigerant from the condenser;
In a star-ring cold supply system provided with a refrigerant chiller unit comprising an evaporator for cooling the secondary refrigerant evaporating action of reduced pressure refrigerant in the decompression device,
When starting the operation of the Stirling cold supply system, after operating the refrigerant chiller unit to cool the secondary refrigerant to a predetermined temperature, the Stirling refrigerator unit is operated, and the refrigerant chiller unit is operated. The operation method of the Stirling cold supply system characterized by stopping . The method of operating the Stirling cold supply system according to claim 1, characterized in that a period in which driving with the Stirling refrigerator unit and the refrigerant chiller unit simultaneously. A Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. While preparing
A compressor for compressing the refrigerant;
A condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant;
A decompression device for decompressing the refrigerant from the condenser;
In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by an evaporation action of the refrigerant decompressed by the decompression device,
Wherein when starting Stirling cold operating the supply system, to operate the coolant chiller unit cools the predetermined temperature until in front Symbol secondary refrigerant, and, from the predetermined temperature than the appropriate high temperature of the Stirling refrigerator unit In operation, the refrigerant chiller unit and the Stirling refrigerator unit are simultaneously operated in this temperature range, and when the predetermined temperature is reached, the operation of the refrigerant chiller unit is stopped and only the Stirling refrigerator unit is operated. The operation method of the Stirling cold supply system characterized by controlling as follows. A Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. While preparing
A compressor for compressing the refrigerant;
A condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant;
A decompression device for decompressing the refrigerant from the condenser;
In a Stirling cold supply system provided with a refrigerant chiller unit including an evaporator that cools the secondary refrigerant by an evaporation action of the refrigerant decompressed by the decompression device,
Wherein when starting driving the Stirling cold supply system, the refrigerant chiller unit and the Stirling refrigerator unit and simultaneous operation to a predetermined temperature to cool the secondary refrigerant of the refrigerant chiller unit to reach the predetermined temperature An operation method of a Stirling cold supply system, characterized in that the operation is stopped and only the Stirling refrigerator unit is operated. A Stirling refrigerator unit that compresses and expands the working gas to generate cold, and a heat transfer device that cools the secondary refrigerant by the cold generated in the Stirling refrigerator unit and conveys the secondary refrigerant to a cold energy utilization device. In the provided Stirling cold supply system,
A compressor for compressing the refrigerant;
A condenser that causes the refrigerant discharged from the compressor to exchange heat with outside air or water, and condenses the refrigerant;
A decompression device for decompressing the refrigerant from the condenser;
An evaporator that cools the secondary refrigerant by the evaporating action of the refrigerant decompressed by the decompressor;
A second evaporator that evaporates the refrigerant decompressed by the decompression device and absorbs heat radiation from the Stirling refrigerator unit;
A Stirling cold supply system, comprising: a switching valve for switching whether the refrigerant from the condenser is effectively evaporated by the evaporator or by the second evaporator. Stirling cold supply system of claim 5 wherein varying the pressure reducing device of the pressure reducing device and a second evaporator in the evaporator. 7. The refrigerant chiller unit by switching the switching valve so that the refrigerant condensed in the condenser is effectively evaporated in the evaporator when starting the operation of the Stirling cold supply system according to claim 5 or 6. The Stirling is characterized by switching the switching valve so that the refrigerant condensed in the condenser is effectively evaporated in the second evaporator after the secondary refrigerant is cooled to a predetermined temperature. How to operate the cold supply system.

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