JP2008157524A - Piping for heat medium and testing apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To develop a piping for a heat medium usable in application of sending a heat medium in a low temperature state or a high temperature state to a constant-temperature apparatus side or the like while maintaining a predetermined temperature state, or usable in application of recovering cold or heat of a heat medium returning from the constant-temperature apparatus side or the like. <P>SOLUTION: In outgoing side crossover piping (the piping for a heat medium) 7, a periphery of a center pipe 50 is surrounded by an outline pipe 51, and an insertion pipe 52 is inserted into the center pipe 50. A gap between the center pipe 50 and the outline pipe 51 functions as an outgoing side passage 73. A gap between the insertion pipe 52 and the center pipe 50 functions as an outgoing side auxiliary passage 72. Return side crossover piping (the piping for a heat medium) is also composed of a center pipe and an outline pipe surrounding the center pipe. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a test apparatus used for a performance test of a semiconductor wafer. The present invention also relates to a heat medium pipe suitable for use in supplying a heat medium to the constant temperature device of the test apparatus described above or extracting the heat medium.

Electronic devices such as mobile phones and personal computers are widely used. These electronic devices are used in various applications and various environments in recent years. For this reason, it is necessary to test the influence of the electronic device itself and these components, such as integrated circuits, on the environment.
As a test apparatus that exposes these electronic components and the like to a high temperature environment and a low temperature environment, those having structures disclosed in Patent Document 1 and Patent Document 2 are known.
The test apparatus disclosed in Patent Documents 1 and 2 includes a thermostatic device called a thermal plate or a high and low temperature chuck, and performs a test by placing or fixing a semiconductor wafer on the thermostatic device.
A constant temperature device called a thermal plate or a high / low temperature chuck has an article placement surface on which a test object is placed or fixed. In many cases, an electric heater is attached to a part of the thermostatic device. A cavity is formed in the thermostatic device. A fluid (heat medium) having a predetermined temperature flows through the cavity.
And control of an electric heater and the operation | movement which flows a fluid into a cavity are used together, and the temperature of an article mounting surface is maintained at desired temperature. For example, when it is desired to lower the temperature of the article mounting surface, a low-temperature fluid is passed through the cavity.
JP-A-2005-45039 Japanese Patent Laid-Open No. 10-288646

By the way, in recent years, there is a demand for performing a test in a harsher situation and a demand for using a test apparatus having a larger surface for placing an article.
Therefore, the device for adjusting the temperature of the fluid flowing through the cavity tends to be larger. Therefore, the present inventors made a prototype of a test device in which the device for adjusting the temperature of the fluid flowing through the cavity is independent from the thermostatic device.
In other words, a heat medium supply device that includes a cooling device, cools and discharges the supplied air, and a test unit that includes a thermal plate are incorporated in separate cases, and a pipe connection such as a tube is connected between the two. . Specifically, the heat medium supply device and the test section were connected by a forward side pipe and a return side pipe.
Then, low-temperature air is produced by the heat medium supply device, low-temperature air is supplied to the constant temperature device in the test section via the forward piping (forward flow channel), and the air discharged from the constant temperature device is returned to the return piping. It was collected on the heat medium supply device side in the (return side flow path).

The prototype heat medium supply device has a large capacity cooling capacity compared to the conventional one, and the constant temperature equipment in the test section was able to cool down more than the old one.
However, the prototype test apparatus has a heat energy loss between the heat medium supply apparatus and the test section that cannot be ignored.
That is, in the test apparatus that was prototyped, the heat medium supply device is separate from the thermostatic device, and therefore, the cold air must be supplied to the thermostatic device by passing the outward piping. However, the cold air used for the test is an extremely low temperature of minus 90 ° C., and is likely to rise in temperature due to the influence of outside air.
Of course, a heat insulating material is attached to the outgoing side pipe, but the temperature of the cold air flowing through the outgoing side pipe is significantly different from the temperature of the outside air.
For this reason, the prototype test apparatus was dissatisfied with the temperature control range of the thermostatic device being restricted.
Furthermore, in order to compensate for the loss of thermal energy, it has been difficult to reduce the size of the refrigeration apparatus, and there has been a problem that power consumption increases.

In addition, it was recognized that the prototype test equipment needed to be improved from the viewpoint of energy saving. That is, in the test apparatus that was prototyped, the air returning from the thermostatic apparatus was reheated by the heating apparatus and released into the atmosphere as it was. That is, the air returning from the thermostatic device was released without being reused even though the temperature was still very low. If the cold air returned from the thermostat can be recovered and reused, an excellent energy saving effect can be obtained. As a result, the cooling device can be downsized and the power consumption can be reduced.
Moreover, high temperature air etc. may be supplied to a thermostat, and in this case, the air which returns from a thermostat is high temperature. If the heat of the air returning from the thermostat can be recovered and reused, an excellent energy saving effect can be obtained.

  Therefore, the present invention has an object to solve the above-described problems, and is used for an application in which a heat medium in a low temperature state or a high temperature state is sent to a constant temperature device or the like while maintaining a predetermined temperature state. An object of the present invention is to develop a heat medium pipe that can be used for the purpose of recovering cold heat and heat from a heat medium returning from the device side or the like.

  The invention according to claim 1 for solving the above-mentioned problem is a multiple structure including a central tube and an outer tube surrounding part or all of the central tube, and has flexibility as a whole. This is a characteristic heat medium pipe.

The piping for the heat medium of the present invention can be used for heat insulation / cooling applications of the heat medium, or for recovering cold energy and heat.
When the heat medium pipe of the present invention is used for heat insulation / cold insulation of the heat medium, the heat medium to be transported flows through one of the central tube and the outer tube, and the other of the central tube and the outer tube. A heat medium for keeping the heat medium warm or cold is supplied (Claim 3).
According to the present invention, the heat medium to be transported is kept warm or cold by the heat medium for keeping warm or cold, and the temperature change in the transport process is small.

  The heat medium for keeping warm or keeping cold may be a refrigerant that realizes a refrigeration cycle (claim 4).

When the heat medium pipe of the present invention is used for heat recovery, the heat medium to be transported is flowed to one of the central tube and the outer tube, and the other of the central tube and the outer tube is separated from the heat medium. A heating medium for recovering heat or cold is passed (claim 5).
The heat medium pipe of the present invention is constituted by a multiple structure having a central tube and an outer tube surrounding the central tube. Therefore, the contact area between the central tube and the outer tube is large, and the heat exchange efficiency between them is high.
As a result, the heat medium pipe of the present invention can exhibit high efficiency even if it is used for heat insulation / cooling applications of the heat medium or used for recovering cold heat or heat.

  The invention according to claim 2 is the heat medium pipe according to claim 1, wherein the center tube further includes an insertion tube inside, and the insertion tube opens in a deep portion of the center tube. .

  In the heat medium pipe of the present invention, the central tube further includes an insertion tube for introducing or discharging the refrigerant or the heat medium therein. The insertion tube opens at the back of the center tube. Therefore, the heat medium introduced from the insertion tube passes through the insertion tube, reaches the inner portion of the central tube, is discharged at the inner portion, and reciprocates. As a result, the heat medium pipe of the present invention has a long residence time of the heat medium and high heat exchange efficiency between the heat media.

  The test apparatus using the above-described heat medium pipe is a constant temperature apparatus that introduces a heat medium into the cavity to bring the temperature of a specific temperature adjustment surface to a predetermined temperature, and a heat medium supply apparatus that supplies at least a low temperature heat medium And a return side crossover pipe for supplying the heat medium from the heat medium supply device to the constant temperature device and a return side crossover pipe for returning the heat medium from the constant temperature device to the heat medium supply device. At least one of these is a heat medium pipe according to any one of claims 1 to 5 (Claim 6).

If the heat medium pipe of the present invention is used for an application in which a heat medium in a low temperature state or a high temperature state is sent to the constant temperature device side or the like while maintaining a predetermined temperature state, a lower temperature heat medium or a higher temperature heat The medium can be supplied to the constant temperature device side or the like. Therefore, there is an effect that it is possible to improve the temperature control width of the thermostatic device or the like.
Furthermore, if the piping for the heat medium of the present invention is used for the purpose of recovering cold heat and heat from the heat medium, the cold heat and heat possessed by the heat medium returned from the constant temperature device and the like can be used effectively, and energy saving can be achieved. .

  Since the test apparatus of the present invention includes the heat medium pipe of the present invention, the temperature control range of the thermostatic device is large. Therefore, there is an effect that the test can be performed with higher accuracy. Furthermore, there is an effect that energy saving can be achieved.

Embodiments of the present invention will be further described below.
FIG. 1 is a perspective view showing an example of a test apparatus having a heat medium supply device and a thermostatic device. FIG. 2 is a piping system diagram of the test apparatus of FIG.

  The test apparatus 1 shown in FIG. 1 can place a semiconductor wafer in a high temperature environment or a low temperature environment.

As shown in FIG. 1, the test apparatus 1 is roughly divided into two apparatuses. That is, the test apparatus 1 is divided into a test section 3 having a built-in thermal plate (constant temperature device) 2 and a heat medium supply apparatus 5, and between them, a forward side crossover pipe (heat medium pipe) 7 and a return side The pipe is connected to a transition pipe (heat medium pipe) 8. The test unit 3 belongs to a wafer prober.
FIG. 2 is a piping system diagram of the test apparatus as described above. The inside of the frame A is a piping system in the test unit 3, and the inside of the frame B is a piping system in the heat medium supply device 5. In FIG. 2, two lines connecting the frame A and the frame B represent the forward side crossover piping 7 and the return side crossover piping 8.

The thermal plate (constant temperature device) 2 is a member also called a high / low temperature chuck, and the whole shape is a columnar shape. The top surface is an article placement surface 10 on which the object to be tested is placed, and the article placement surface 10 is adjusted to a desired temperature. That is, an electric heater (not shown) is attached to the thermal plate (constant temperature device) 2, and a cavity 11 is further provided inside. Then, the temperature of the article mounting surface 10 is adjusted by controlling the electric heater and circulating the cooled air in the cavity 11.
The thermal plate (constant temperature device) 2 is provided with a vacuum pipe (not shown) and has a function of holding the object to be tested on the article placement surface 10 by a vacuum force.

The thermal plate (constant temperature device) 2 is housed in a housing 12 independent of the heat medium supply device 5 as shown in FIG.
The thermal plate (constant temperature device) 2 is placed on an XY table 15 and can be moved to XY by a motor (not shown).
Pipes 16 and 17 are provided in the casing 12 of the test unit 3, and the cavity 11 and the outside of the casing 12 communicate with each other through the pipes 16 and 17.
A part of the air introduction path is provided in the housing 12 of the test unit 3. That is, as shown in the lower part of the frame A in FIG. 2, the housing 12 is provided with an air introduction port 18, the front end side of the air introduction port 18 is branched, one of which is connected via the electromagnetic valve 19. It is connected to an air inlet 78 of a return side crossover pipe 8 to be described later.
A portion branched to the other end side of the air inlet 18 is opened to the atmosphere via the electromagnetic valve 13.

  Note that dry air is supplied to the air inlet 18 of the casing 12 from a compressor (not shown). That is, a dry air source 29 is connected to the air inlet 18 via a pressure reducing valve.

The heat medium supply device 5 is a device that cools air, and has a cooling device built therein. The cooling device has two refrigeration cycles.
That is, the heat medium supply device 5 is configured by the primary side of the first stage side compressor 20, the first stage side condenser 21, the flow rate adjusting valve 22, the first stage side expansion valve 23, and the refrigerant cooling heat exchanger 25. First stage refrigeration cycle, second stage side compressor 30, second stage side condenser 31, secondary side of refrigerant cooling heat exchanger 25, second stage side expansion valve 33, and heat medium temperature adjustment heat exchange The second stage refrigeration cycle constituted by the vessel 35 is provided.

In the two refrigeration cycles, for example, a phase change such as alternative chlorofluorocarbon occurs, and a refrigerant that realizes the refrigeration cycle flows.
That is, in the first refrigeration cycle, the refrigerant is compressed by the first stage side compressor 20, and the refrigerant is condensed by being cooled by a fan (not shown) in the first stage side condenser 21. Then, the refrigerant passes through the first stage side expansion valve 23 and is vaporized in the primary side of the refrigerant cooling heat exchanger 25 to remove heat. The vaporized refrigerant returns to the first stage compressor 20.

  On the other hand, in the second refrigeration cycle, the refrigerant is compressed by the second-stage side compressor 30 and cooled by the fan in the second-stage side condenser 31 to lower the temperature of the refrigerant. The refrigerant enters the secondary side of the refrigerant cooling heat exchanger 25, and is rapidly cooled and liquefied by the action of the first refrigeration cycle. The refrigerant flowing through the second refrigeration cycle passes through the second stage side expansion valve 33 and is vaporized on the primary side of the heat exchanger 35 for adjusting the heat medium temperature to take heat away. The vaporized refrigerant returns to the second stage side compressor 30.

  In the present embodiment, an auxiliary refrigerant cooling heat exchanger 41 and a cold recovery heat exchanger 43 are provided in the heat medium supply device 5. The secondary flow path of the auxiliary refrigerant cooling heat exchanger 41 is connected in series with the intermediate portion of the flow path of the first stage condenser 21.

Next, the forward crossover pipe (heat medium pipe) 7 will be described.
FIG. 3 is a detailed view of the forward crossover piping portion of the piping system diagram of FIG. FIG. 4 is a cross-sectional view of a forward crossover pipe employed in the test apparatus of FIG.
The forward crossover pipe 7 has a multiple structure as shown in FIG. That is, the forward crossover pipe 7 is a triple structure including a center pipe 50, an outer pipe 51, and an insertion pipe 52.
The forward crossover pipe 7 is configured such that an outer tube 51 surrounds the center tube 50 and an insertion tube 52 is inserted into the center tube 50.

Most of the central tube 50 is buried in the outer tube 51 except for the rear end. A refrigerant discharge port 55 is provided in the protruding portion 53 that protrudes from the outer tube 51 of the central tube 50. The tip of the central tube 50 is closed.
The outer diameter of the center tube 50 is smaller than the inner diameter of the outer tube 51, and there is an annular gap between them. In the present embodiment, this gap functions as the outward flow path 73.

The insertion tube 52 is inserted into the central tube 50 from the protruding portion 53 described above, and the distal end thereof reaches the innermost part of the central tube 50 and opens. The outer diameter of the insertion tube 52 is smaller than the inner diameter of the central tube 50, and there is a gap between them. In the present embodiment, the air gap functions as the outward auxiliary flow path 72. That is, the forward auxiliary flow path 72 is adjacent to the forward flow path 73 and is in thermal contact therewith.
An air inlet 56 is opened at the proximal end of the outer tube 51 and an air outlet 57 is opened at the distal end.

  The actual structure of the forward crossover piping 7 is as shown in FIG. Has a thick shape and can be bent.

  The central tube 50 is formed by sequentially connecting a short tube 64, a tee 65, a short tube 66, and a resin tube 67 with a closed end, and the outer diameter thereof is smaller than the inner diameter of the central portion of the outer tube 51, An outward flow path 73 is formed by the gap between the two.

  The distal end side from the central portion of the short tube 66 of the central tube 50 is inserted into the outer tube 51. The central portion of the short tube 66 and the reducer 58 of the outer tube 51 are sealed.

The insertion tube 52 is formed by sequentially connecting a short tube 70 and a flexible thin tube 71. The portion of the short tube 70 of the insertion tube 52 reaches the portion of the short tube 66 of the center tube 50, and the narrow tube 71 reaches the vicinity of the tip of the center tube 50.
The outer diameter of the insertion tube 52 is smaller than the inner diameter of the central tube 50 in any part, and there is a gap between them, and this gap functions as the outward auxiliary flow path 72.
However, the insertion pipe 52 and the short pipe 64 which is the base end of the center pipe 50 are welded to maintain airtightness.
Note that a heat insulating material (not shown) is wound around the forward side crossover pipe 7.

Next, the return side crossover pipe (heat medium pipe) 8 will be described. FIG. 5 is a cross-sectional view of the return side crossover piping employed in the test apparatus of FIG.
As shown in FIG. 5, the return-side crossover pipe 8 has a double structure, and is constituted by a central tube 75 and an outer tube 76 that surrounds the central tube 75. The outer tube 76 is formed by sequentially connecting a tee 80, a flexible tube 81, and a tee 82. Both ends of the outer tube 76 are closed. On the other hand, the central tube 75 is formed by sequentially connecting a straight tube 83, a flexible tube 85, and a straight tube 86. Both the central tube 75 and the outer tube 76 are flexible.
The outer diameter of the central tube 75 is smaller than the inner diameter of the outer tube 76, and there is a gap between them. In the present embodiment, this gap functions as the return side auxiliary flow path 77. On the other hand, the central tube 75 functions as a return side flow path.
An air introduction port 78 and an air discharge port 79 are provided on the side surfaces in the vicinity of both ends of the outer tube 76.

Next, the piping over the test unit 3 and the heat medium supply device 5 will be described.
As described above, the test section 3 and the heat medium supply device 5 are pipe-coupled by the forward side crossover pipe 7 and the return side crossover pipe 8. That is, one end of each of the forward side crossover pipe 7 and the return side crossover pipe 8 is in the casing 12 of the test unit 3, and the other end is in the casing of the heat medium supply device 5.
The piping system extending over the test unit 3 and the heat medium supply device 5 will be described along the flow of air as follows.
That is, as described above, a part of the air introduction path is provided in the housing 12 of the test unit 3, and the distal end side of the air introduction port 18 is branched and the electromagnetic valve 19 is attached. The downstream side of the solenoid valve 19 is connected to the air introduction port 78 of the return side crossover piping 8. That is, the downstream side of the solenoid valve 19 is connected to the return side auxiliary flow path 77 of the return side crossover pipe 8.

Further, the air discharge port 79 of the return side crossover pipe 8 communicates with the secondary side inlet of the heat exchanger 43 for cold energy recovery. The secondary side outlet of the heat exchanger 43 for cold heat recovery enters the secondary side inlet of the heat exchanger 35 for heat medium temperature adjustment, and the secondary side outlet of the heat exchanger 35 for heat medium temperature adjustment crosses the outgoing side. It is connected to the air inlet 56 of the pipe 7. That is, the secondary side outlet of the heat exchanger 35 for adjusting the heat medium temperature is connected to the forward flow path 73.
The air discharge port 57 of the forward crossover pipe 7 is connected to the air introduction port of the cavity 11 of the thermal plate 2 by the pipe 16 in the housing 12 of the test unit 3.
The air discharge port of the thermal plate 2 is connected to one end of the center pipe 75 of the return side crossover pipe 8 via the pipe 17. That is, the air discharge port of the thermal plate 2 is connected to the return side flow path.
The other end of the central pipe 75 of the return side crossover pipe 8 communicates with the primary side inlet of the cold heat recovery heat exchanger 43. The primary outlet of the cold heat recovery heat exchanger 43 is further connected to the primary flow path inlet of the auxiliary refrigerant cooling heat exchanger 41. The primary channel outlet of the auxiliary refrigerant cooling heat exchanger 41 is open to the atmosphere.

Further, a part of the secondary side refrigeration cycle is branched and connected to the refrigerant inlet and the refrigerant outlet (refrigerant outlet 55) of the forward crossover pipe 7.
That is, the secondary refrigeration cycle is provided with a bypass flow path 36 that bypasses the heat exchanger 35 for adjusting the heat medium temperature, and the central pipe 50 of the forward crossover pipe 7 is connected to the bypass flow path 36.
More specifically, the secondary side expansion valve 33 in the secondary side refrigeration cycle and the heat exchanger 35 for adjusting the heat medium temperature are branched and connected to the refrigerant inlet of the forward crossover pipe 7. . The refrigerant outlet (refrigerant outlet 55) of the forward-side crossover pipe 7 is connected between the heat exchanger 35 for adjusting the heat medium temperature in the secondary-side refrigeration cycle and the second-stage compressor 30. Yes. Accordingly, the center pipe 50 of the forward side crossover pipe 7 is in parallel with the heat exchanger 35 for adjusting the heat medium temperature, and the central pipe 50 of the forward side crossover pipe 7 has the same temperature as the heat exchanger 35 for adjusting the heat medium temperature. Refrigerant passes through.

Next, the operation of the test apparatus 1 in this embodiment will be described.
The test apparatus 1 in this embodiment can change the article mounting surface 10 of the thermal plate (constant temperature device) 2 from a low temperature of about minus 65 ° C. to a high temperature of 200 ° C. or higher. The test apparatus 1 exhibits a specific function when the temperature of the article placement surface 10 is adjusted to a low temperature.
That is, when the temperature of the article mounting surface 10 is controlled to a low temperature, the first stage side compressor 20 of the primary side refrigeration cycle and the second stage side compressor 30 of the secondary side refrigeration cycle are operated and dried. Dry air is introduced from the air source 29.
When the first stage side compressor 20 of the primary side refrigeration cycle and the second stage side compressor 30 of the secondary side refrigeration cycle are operated, each refrigeration cycle functions to adjust the heat medium temperature of the secondary side refrigeration cycle. The low-temperature refrigerant passes through the primary side of the heat exchanger for heat 35, and the secondary side of the heat exchanger 35 for adjusting the heat medium temperature is cooled.
Further, the refrigerant flows in the bypass flow path 36 that bypasses the heat exchanger 35 for adjusting the heat medium temperature, and the refrigerant flows in the forward auxiliary flow path 72 (between the central pipe 50 and the insertion pipe 52 of the forward crossover pipe 7). To do. More specifically, the refrigerant is introduced into the central tube 50 from the end of the insertion tube 52. Since the insertion tube 52 opens at the back side of the center tube 50, the refrigerant passes through the insertion tube 52 to reach the back side of the center tube 50 and is opened at a position on the back side.
Here, the distal end side of the central tube 50 is closed, and there is a gap (forward-side auxiliary channel 72) between the insertion tube 52 and the central tube 50, so that the refrigerant passes through the forward-side auxiliary channel 72. Flow and return to the proximal side. That is, the refrigerant reciprocates in the central tube 50 and returns to the proximal end side of the central tube 50, and is discharged from the refrigerant discharge port 55.

  The air flow is as described above, and the dry air introduced into the test unit 3 from the dry air source 29 enters the air introduction port 78 of the return side crossover piping 8 through the electromagnetic valve 19 and returns to the return side crossover piping. 8 flows through a gap (return side auxiliary flow channel 77) formed between the outer shell 76 and the central tube 75. Then, the air that has passed through the gap (return side auxiliary flow path 77) of the return side crossover pipe 8 passes through the secondary side of the cold heat recovery heat exchanger 43 and the secondary side of the heat exchanger 35 for adjusting the heat medium temperature. Flowing. Further, the air that has passed through the secondary side of the heat exchanger 35 for adjusting the heat medium temperature enters the air introduction port 56 of the forward crossover pipe 7 and is interposed between the outer pipe 51 and the central pipe 50 of the forward crossover pipe 7. It flows through the formed gap (forward-side flow path 73) and reaches the inside of the test section 3. The air that enters the cavity 11 of the thermal plate 2 through the pipe 16 and further exits the cavity 11 passes through the center pipe (return side flow path) 75 of the return side crossover pipe 8 through the pipe 17. The air that has passed through the central pipe (return side flow path) 75 of the return side crossover pipe 8 flows through the primary side of the cold heat recovery heat exchanger 43, and further flows through the primary side of the auxiliary refrigerant cooling heat exchanger 41, Open to the atmosphere.

Next, in the above-described series of air flows, the temperature of the air passing through each part is verified.
That is, the dry air supplied from the dry air source 29 is at room temperature. This air flows through a gap (return side auxiliary flow path 77) formed between the outer tube 76 and the center tube 75 of the return side crossover pipe 8 via the electromagnetic valve 19 (hereinafter referred to as “outward side air”). At this time, the air is cooled by the exhaust gas (hereinafter referred to as “return-side air”) flowing through the central pipe (return-side flow path) 75 of the return-side transition pipe 8.
That is, as described above, the return side air discharged from the cavity 11 of the thermal plate 2 flows through the center pipe 75 of the return side crossover pipe 8, but the temperature of the return side air is lower than the normal temperature, and the return side air Lower than air temperature.
Therefore, the forward air flowing between the outer tube 76 and the central tube 75 (return side auxiliary flow channel 77) is deprived of heat through the wall surface of the central tube 75, and the temperature is lowered.

Further, the forward air that has passed through the gap (return side auxiliary flow path 77) of the return side crossover pipe 8 passes through the secondary side of the heat exchanger 43 for cold energy recovery, but passes through the gap of the return side crossover pipe 8. The forward air is also cooled in the cold recovery heat exchanger 43 by exchanging heat with the return air.
In other words, the return side air flows on the primary side of the heat exchanger 43 for recovering cold heat, and the return side air is cooled because the return side air is at a lower temperature than the forward side air.

  The outgoing air that has passed through the cold heat recovery heat exchanger 43 enters the heat medium temperature adjusting heat exchanger 35 and is intensely cooled by the heat medium temperature adjusting heat exchanger 35. That is, the outgoing air flows through the secondary side of the heat exchanger 35 for adjusting the heat medium temperature, but the refrigerant cooled by the cooling device passes through the heat exchanger 35 for adjusting the heat medium temperature. Therefore, the outgoing air is extremely low in temperature when passing through the heat exchanger 35 for adjusting the heat medium temperature.

The air that has passed through the secondary side of the heat exchanger 35 for adjusting the heat medium temperature enters the air introduction port 56 of the forward crossover pipe 7 and is formed between the outer pipe 51 and the central pipe 50 of the forward crossover pipe 7. The air passing through the forward gap 73 (outward flow path 73) reaches the inside of the test section 3, and during this time, the air passing through the forward flow path 73 in the forward crossover pipe 7 is cooled by the refrigerant.
That is, the outward air flows through a gap (outward flow path 73) formed between the outer tube 51 of the forward transfer pipe 7 and the central pipe 50, but is adjacent to the forward flow path 73 and the central pipe 50. There is a flow path (forward-side auxiliary flow path 72), and the refrigerant flows in the forward-side auxiliary flow path 72. The forward side auxiliary flow path 72 is adjacent to the forward side flow path 73 and is in thermal contact therewith. Therefore, the outward air continues to be cooled by the refrigerant even when passing through the outward crossover pipe 7, and the temperature rise is suppressed.
In addition, since the temperature of the refrigerant flowing through the center tube 50 is the same as the temperature of the refrigerant passing through the heat exchanger 35 for adjusting the heat medium temperature as described above, the temperature change of the outgoing air is small.

  The forward air enters the cavity 11 of the thermal plate 2, cools the surface of the thermal plate 2, and raises its own temperature. However, the air discharged from the cavity 11 is still lower than room temperature.

Further, the air leaving the cavity passes through the central pipe (return side flow path) 75 of the return side crossover pipe 8 through the pipe 17, and as described above, gives cold heat to the forward side air and raises its temperature.
Further, the air that has passed through the central pipe (return-side flow path) 75 of the return-side crossover pipe 8 flows through the primary side of the cold-heat recovery heat exchanger 43, gives cold heat to the forward-side air, and rises in temperature.
Further, the return side air flows on the primary side of the auxiliary refrigerant cooling heat exchanger 41 and contributes to the condensation of the refrigerant in the primary side refrigeration cycle.
In this way, in the present embodiment, the cold energy is recovered three times, so that the thermal efficiency is high. Moreover, since the exhaust gas finally discharged has a temperature close to room temperature, it is difficult to change the indoor environment. In other words, in the case of the conventional test apparatus, since the air discharged from the cavity of the thermal plate was opened to the atmosphere as it was, there was a case where condensation occurred at the exhaust port. Since it is close to room temperature, no condensation occurs.

In the embodiment described above, the refrigerant is caused to flow through the central pipe 50 of the forward crossover pipe 7, and the forward air is passed through the surrounding gap (the forward flow path 73).
This is because the temperature of the refrigerant is lower than that of the outgoing air, and has an effect of suppressing the diffusion of cold heat to the atmosphere. Further, since the refrigerant reciprocates in the center tube 50, the residence time of the refrigerant is long, and the heat exchange efficiency with the outgoing air is high.
Furthermore, since the flow path reciprocates inside the center tube 50 as described above, the internal pressure loss is large. On the other hand, the air gap (outward flow path 73) formed around the central tube 50 is a linear flow path, so that the pressure loss is small. Therefore, in this embodiment, in order to reduce the pressure loss of the forward air, the forward air is passed through the surrounding gap.
However, the present invention is not limited to this configuration, and the forward air may be flowed through the central tube 50 and the refrigerant may be flowed through a flow path formed around the air.

The same applies to the return side pipe, and in this embodiment, the return side air is circulated through the center pipe 75 and the forward side air is allowed to pass therethrough, but conversely, the forward side air is allowed to pass through the center pipe 75, Return air may be passed around it.
In the return side crossover piping 8, the reason that the return side air is passed to the central tube 75 side and the forward side air is allowed to pass therearound is the same as that of the forward side crossover piping 7. This is because the temperature is higher than the return side.

  Further, in the present embodiment, a structure having a reciprocating flow path as shown in FIGS. 3 and 4 is adopted for the forward side crossover pipe 7, and a structure having only the straight flow path shown in FIG. However, both of them may adopt the structure shown in FIG. 3, 4 or 5, and adopt the structure shown in FIG. 5 for the forward side crossover piping 7 and the return side crossover piping 8. The structure shown in FIGS. 3 and 4 may be adopted. In the case of adopting the structure shown in FIGS. 3 and 4 as the return side crossover piping 8, for example, it is constituted by a multiple structure having a cavity portion and an outer tube surrounding a part or all of the cavity portion. And it is set as the structure which equips the inside of the said cavity part with the insertion pipe which introduce | transduces or discharges a refrigerant | coolant or gas, and the said insertion pipe opens in the back part of a cavity part.

In the embodiment described above, the bypass flow path 36 that bypasses the heat exchanger 35 for adjusting the heat medium temperature is provided, and the central pipe 50 of the forward crossover pipe 7 is connected to the bypass flow path 36. However, the present invention is not limited to this configuration. For example, the configuration shown in FIG. 6 may be used.
FIG. 6 is a piping system diagram of the test apparatus according to the second embodiment of the present invention. In the piping system of FIG. 6, the center pipe 50 of the forward crossover pipe 7 and the heat exchanger 35 for adjusting the heat medium temperature are connected in series.
In the configuration of FIG. 6, the center pipe of the forward crossover pipe 7 is connected to the downstream side of the second stage side expansion valve 33, and the heat exchanger 35 for adjusting the heat medium temperature is connected to the downstream side thereof. The temperature adjusting heat exchanger 35 may be connected first.
Further, the second stage side condenser 31 and the second stage side expansion valve 33 may be branched and connected to the central pipe 50 of the forward side crossover pipe 7. When this configuration is adopted, the insertion tube 52 in the center tube 50 functions as an expansion means (capillary tube).
Further, in this embodiment, the cooling device constitutes a two-line refrigeration cycle, and the low-temperature refrigerant produced by the second-stage refrigeration cycle is introduced into the forward crossover pipe 7, but the first-stage refrigeration cycle The produced low-temperature refrigerant may be introduced into the forward crossover pipe 7. However, in this case, since the temperature of the refrigerant is higher than in the case of the first embodiment, it is desirable to flow the refrigerant through the outer flow path.

  In each of the embodiments described above, temperature-controlled air is introduced into the cavity 11 of the thermal plate 2. That is, in each of the above-described embodiments, air is used as the heat medium. However, a gas such as nitrogen may be used as the heat medium instead of air. Furthermore, a liquid heat medium can also be employed.

It is a perspective view which shows an example of the test apparatus which has a heat carrier supply apparatus and a thermostat. It is a piping system diagram of the test apparatus of FIG. FIG. 3 is a detailed view of a forward crossover piping portion of the piping system diagram of FIG. 2. FIG. 2 is a cross-sectional view of a forward crossover pipe employed in the test apparatus of FIG. 1. It is sectional drawing of the return side crossover piping employ | adopted with the testing apparatus of FIG. It is a piping system diagram of a testing device concerning a second embodiment of the present invention.

Explanation of symbols

1 Test equipment 2 Thermal plate (constant temperature equipment)
5 Heat medium supply device 7 Outward crossover piping (heat medium piping)
8 Return-side crossover piping (heat medium piping)
11 Cavity 50 Center tube 51 Outer tube 52 Insertion tube 75 Center tube 76 Outer tube

Claims (6)

  A heat medium pipe characterized in that it is a multiple structure having a central tube and an outer tube surrounding part or all of the central tube, and has flexibility as a whole.   The heat transfer pipe according to claim 1, wherein the center pipe further includes an insertion pipe therein, and the insertion pipe opens in a deep portion of the center pipe.   The heat medium to be transported flows through one of the central tube and the outer tube, and the heat medium for keeping the heat medium warm or cold flows through the other of the central tube or the outer tube. The heat medium piping according to 1 or 2.   The heat medium pipe according to claim 3, wherein the heat medium for keeping heat or cold is a refrigerant that realizes a refrigeration cycle.   A heat medium to be transported flows through one of the central tube and the outer tube, and a heat medium for recovering heat or cold from the heat medium flows through the other of the central tube and the outer tube. The heat medium piping according to claim 1 or 2.   A constant temperature device that introduces a heat medium into the cavity to bring the temperature of a specific temperature control surface to a predetermined temperature, a heat medium supply device that supplies at least a low temperature heat medium, and heat from the heat medium supply device to the constant temperature device. 6. A forward crossover pipe for supplying a medium and a return crossover pipe for returning the heat medium from the constant temperature device to the heat medium supply device, wherein at least one of the forward side pipe and the return side pipe is any one of claims 1 to 5. A test apparatus, which is the heat medium pipe according to item 1.

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