JP2001046828A - Heat exchanger and dehumidifying device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger and a dehumidifying device free from leakage of a refrigerant from a soldered part in the inside of the heat exchanger by eliminating the soldered part in a heat exchanger. SOLUTION: The heat exchanger is closed by a case 32 used as a pressure vessel. A refrigeration passage installed in an evaporation part in the inside of the case 32 is constituted of a plurality of branched pipes 63. But the respective branched pipes 63 are branched in the outside of the case 32 and assembled in the outside of the case 32. In other words, the soldered part 72 of a piece of refrigerant pipeline 71 and a plurality of branched pipes 63 are arranged in the outside of the case 32. Accordingly, this constitution differs from a conventional constitution, in which the solded part is provided in the inside of the case 32, and the soldered part can be repaired in the outside of the case 32.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a technical field including a heat exchanger and a dehumidifier using the heat exchanger.

[0002]

2. Description of the Related Art As an example of a dehumidifier, there is a refrigeration dehumidifier. The refrigeration dehumidifier includes a refrigeration circuit including a compressor, a condenser, and the like, and the refrigerant is cooled by the refrigeration circuit. On the other hand, the refrigeration type dehumidifier is provided with a heat exchanger, in which high-temperature humid air from the outside and the refrigerant cooled in the refrigeration circuit are introduced into the heat exchanger, and heat is generated between the high-temperature humid air and the refrigerant. Exchange is performed to dehumidify hot and humid air. The dry air after dehumidification is supplied to an external device such as a cylinder for use.

There are a plurality of heat exchangers,
In the dehumidifier, a shell and tube type is most commonly used for heat exchange between air and a refrigerant. In this conventional shell-and-tube heat exchanger, a refrigerant pipe (tube) through which a refrigerant flows is provided in a pressure vessel (shell). Here, in order to enhance heat exchange efficiency, the refrigerant pipe is configured to make a number of U-turns in the pressure vessel. Similarly, in order to increase the heat exchange efficiency, the air flow path is configured to be in contact with the refrigerant pipe while being circulated instead of being linear.

Further, the refrigerant pipe is branched into a relatively thin pipe in the pressure vessel in order to increase the contact area with air and improve the heat exchange efficiency. Then, the branch pipes are drawn out of the vessel after being connected again in the pressure vessel.

Here, since the refrigerant pipe is generally formed of a copper pipe, when the refrigerant pipe is repeatedly U-turned in the pressure vessel as described above, one copper pipe is required.
It is difficult to compose a book.

Therefore, conventionally, the refrigerant pipe is composed of a straight pipe and a U-shaped curved pipe, and the straight pipe and the curved pipe are brazed to make a number of U-turns in the pressure vessel. A refrigerant pipe was installed.

[0007]

However, the above-described conventional heat exchanger has various problems as described below.

(1) In a conventional heat exchanger, refrigerant pipes and the like are installed in a pressure vessel, and these are generally constituted by copper tubes. This was bypassed (U-turn) to increase the heat transfer area in the pressure vessel. In this case, the pressure vessel cannot be simply bypassed due to factors such as the size of the pressure vessel and the pipe diameter. That is, as described above,
The copper tube was composed of a straight portion and a curved portion, and these were brazed inside the pressure vessel. However, this brazed part has a lower reliability than other parts, and there is a problem that, as the brazing is continued, damage such as perforation due to corrosion or the like occurs, and refrigerant leakage easily occurs from that part. .

(2) When refrigerant leakage occurs due to breakage of the brazed portion described in (1) above, since the brazed portion is present in a sealed pressure vessel, the repair is practically carried out. Impossible. Therefore, in the past, when the above-mentioned refrigerant leakage was recognized, the entire heat exchanger had to be replaced instead of repairing the portion, which was uneconomical.

(3) The refrigerant pipe is actually branched into a plurality of relatively thin pipes in the pressure vessel. Further, the branch pipe is drawn out of the pressure vessel while being connected again in the pressure vessel. In such a conventional structure, for example, when the heat exchanger is controlled by a plurality of refrigeration circuits, the branch pipes must be drawn out of the container in advance for each refrigeration circuit system. Therefore, when it is desired to change the number of refrigeration circuits, the same heat exchanger cannot be used.

(4) In the conventional shell-and-tube type heat exchanger, the passage cross section of the air flow path cannot be made large and the air flow path makes many U-turns.
Resistance increases. Therefore, a relatively large pressure loss occurs in the air passage, which is not preferable from the viewpoint of energy saving.

(5) Refrigerant R22 conventionally used
Has a characteristic that the refrigerant temperature is constant unless there is a pressure loss in the heat exchanger, and it is relatively easy to set the refrigerant temperature to a desired temperature. On the other hand, a new refrigerant, for example, a refrigerant such as R407C, has a characteristic that the temperature is not constant even if the pressure is constant. In order to set the refrigerant temperature to a desired temperature corresponding to such refrigerants having different characteristics, it is necessary to intentionally create a predetermined pressure loss in a passage in the heat exchanger. However,
In the conventional heat exchanger, it is difficult to set the pressure loss to be large or small for each of the different kinds of refrigerants, so that there is a problem that it is not possible to easily cope with the different kinds of refrigerants.

The present invention has been made in view of the above circumstances, and has as its main object to provide a heat exchanger and a dehumidifier capable of solving the above problems (1) to (3). Things. It is another object of the present invention to provide a heat exchanger and a dehumidifier capable of solving the problems (4) and (5).

[0014]

Means for Solving the Problems and Effects of the Invention Characteristic means for achieving the above object will be described below. In addition, characteristic actions and effects of each means will be described as necessary.

Means 1. A passage through which the gas to be dehumidified is provided in the pressure vessel, a refrigerant passage through which a refrigerant for performing heat exchange with the gas to be dehumidified is provided, and the refrigerant passage is provided to the pressure vessel. A heat exchanger consisting of a tube with no joint from the introduction site to the exit site.

According to the above means 1, the gas to be dehumidified flows through the predetermined passage in the pressure vessel, and the refrigerant flows through the pipe passing therethrough. Heat exchange is performed, and the gas to be dehumidified is cooled to remove moisture.

Here, the pipe constituting the refrigerant passage does not have any joint such as a brazing portion in the pressure vessel, and when the pipe is joined to another pipe or the like, the joint is at a pressure. It will be provided outside the container. Since the possibility of breakage is extremely low at a portion of the pipe body where there is no joint, refrigerant leakage in the pressure vessel is prevented. Also, even if the joint of the tube is damaged outside the pressure vessel and refrigerant leakage occurs,
The damaged portion can be easily repaired without any modification in the pressure vessel. As a result, even if the joint is broken, it is not necessary to replace the entire heat exchanger.

Means 2. In the pressure vessel, an evaporator that performs heat exchange between the gas to be dehumidified and the refrigerant, and a pre-cooling / reheating unit that performs heat exchange between the gas to be dehumidified before the input to the evaporator and the gas to be dehumidified after the output of the evaporator. In the heat exchanger provided with, the evaporating section is provided with a passage through which the dehumidified gas is circulated in the pressure vessel, and a refrigerant passage through which the refrigerant is circulated in the passage.
A heat exchanger in which the refrigerant passage is constituted by a tube having no joint from the introduction part to the discharge part to the pressure vessel.

According to the means 2, the gas to be dehumidified flows through the passage formed in the evaporating section in the pressure vessel.
The refrigerant is circulated in the pipe passing through the evaporating section, whereby heat exchange is performed between the gas to be dehumidified and the refrigerant, and the gas to be dehumidified is cooled to remove water. Further, since the relatively high-temperature dehumidified gas before the input to the evaporator and the relatively low-temperature dehumidified gas after the output from the evaporator are heat-exchanged in the pre-cooling / reheating unit, the dehumidification in the evaporator is performed. The load is reduced,
Dew condensation due to the dehumidified gas after dehumidification is also prevented.

Here, the pipe constituting the refrigerant passage does not have any joint such as a brazed portion in the pressure vessel, and when the pipe is joined to another pipe or the like, the joint is at a pressure. It will be provided outside the container. Since the possibility of breakage is extremely low at a portion of the pipe body where there is no joint, refrigerant leakage in the pressure vessel is prevented. Also, even if the joint of the tube is damaged outside the pressure vessel and refrigerant leakage occurs,
The damaged portion can be easily repaired without any modification in the pressure vessel. As a result, even if the joint is broken, it is not necessary to replace the entire heat exchanger.

Means 3. In the pressure vessel, an evaporator that performs heat exchange between the gas to be dehumidified and the refrigerant, and a pre-cooling / reheating unit that performs heat exchange between the gas to be dehumidified before the input to the evaporator and the gas to be dehumidified after the output of the evaporator. In the heat exchanger provided with, the pre-cooling / reheating section is arranged near the center of the pressure vessel, and the evaporating section is arranged on the outer peripheral side of the pre-cooling / reheating section of the pressure vessel, In the pressure vessel, a passage through which the gas to be dehumidified is provided is provided, a refrigerant passage through which the refrigerant is provided is provided in the passage, and the refrigerant passage is provided from an introduction portion to the discharge portion to the pressure container. A heat exchanger consisting of a tube with no joints.

According to the means 3, the gas to be dehumidified flows through the passage formed in the evaporating section in the pressure vessel.
The refrigerant is circulated in the pipe passing through the evaporating section, whereby heat exchange is performed between the gas to be dehumidified and the refrigerant, and the gas to be dehumidified is cooled to remove water. Further, since the relatively high-temperature dehumidified gas before the input to the evaporator and the relatively low-temperature dehumidified gas after the output from the evaporator are heat-exchanged in the pre-cooling / reheating unit, the dehumidification in the evaporator is performed. The load is reduced,
Dew condensation due to the dehumidified gas after dehumidification is also prevented.

Here, the pipe constituting the refrigerant passage does not have any joint such as a brazing portion in the pressure vessel, and when the pipe is joined to another pipe or the like, the joint is at a pressure. It will be provided outside the container. Since the possibility of breakage is extremely low at a portion of the pipe body where there is no joint, refrigerant leakage in the pressure vessel is prevented. Also, even if the joint of the tube is damaged outside the pressure vessel and refrigerant leakage occurs,
The damaged portion can be easily repaired without any modification in the pressure vessel. As a result, even if the joint is broken, it is not necessary to replace the entire heat exchanger.

In addition, the pre-cooling / reheating section is disposed near the center of the pressure vessel, and the evaporating section is disposed by utilizing the space on the outer peripheral side of the pre-cooling / reheating section. Therefore, the tube constituting the refrigerant passage can be accommodated in the evaporating section only by having a relatively gentle curve without a fine U-turn, and without providing a joint portion of the tube in the pressure vessel. It can be easily stored in the evaporating section. In addition, since the evaporating section is arranged on the outer peripheral side of the pre-cooling / reheating section, the work of assembling the introduction part and the lead-out part of the pipe into the pressure vessel becomes easy.

Means 4. In the above means 3, the heat exchanger in which the pipe constituting the refrigerant passage is spirally wound around the outer peripheral side of the precooling / reheating unit.

According to the above-mentioned means 4, the tube may be arranged so as to continuously have a gentle curve so as to surround the pre-cooling / reheating portion from the outer periphery, which may cause damage to the tube. No load is applied, and the manufacture and assembly of the tube become easy. Further, since the cylindrical space portion is formed as the evaporating portion, the cross-sectional area of the flow path of the gas to be dehumidified can be made relatively large although the pressure vessel itself is compact. Moreover, the passage of the gas to be dehumidified in the evaporating section can be made linear, and pressure loss is almost eliminated. Further, since the total length of the tube in the evaporator can be easily changed by changing the number of turns of the tube, the change can easily cope with different refrigerants.

When the tube is spirally wound,
It is not limited to one layer, and it may be wound into a plurality of layers so that the required cross-sectional area of the gas to be dehumidified is obtained.

Means 5. In the above-mentioned means 4, the pressure vessel is formed in a long shape, and an introduction portion of the pipe constituting the refrigerant passage into the pressure vessel is provided at one longitudinal end of the pressure vessel, while an outlet portion is provided. Is a heat exchanger provided at the other longitudinal end of the pressure vessel.

According to the above means 5, the pipe wound spirally in the pressure vessel can be easily introduced and drawn out of the pressure vessel, so that the production and assembly work becomes easy, and Also useful for compactness.

Means 6. In any of the above means 2 to 5, the precooling / reheating unit is constituted by a plate heat exchanger configured by stacking a plurality of plates at predetermined intervals, and the plate heat exchanger is A heat exchanger in which pre-cooling passages through which the dehumidified gas before the input to the evaporating section flows and reheat passages through which the dehumidified gas after the output from the evaporating section flows are alternately arranged between the plates.

According to the above means 6, since the pre-cooling / reheating section is constituted by the plate type heat exchanger, the pre-cooling / reheating section can be formed into a compact and condensed shape. A heat exchanger having high dehumidification performance can be obtained while being compact as a whole.

Further, the precooling / reheating section constituted by the plate heat exchanger can be manufactured relatively compact even if a plurality of the plate heat exchangers are incorporated. When a plurality of plate heat exchangers are connected in series, the heat exchange efficiency is improved, and when they are connected in parallel, it is possible to cope with a large flow rate of the dehumidified gas. Moreover, the performance can be changed only by using a plurality of plate heat exchangers having the same configuration,
When preparing heat exchangers for various performances, it is advantageous in terms of manufacturing cost.

Means 7 In any one of the above means 1 to 6, a plurality of pipes constituting the refrigerant passage are provided, and each pipe is individually branched and uncoupled from an introduction site to a discharge site to the pressure vessel. Independently located heat exchanger.

According to the means 7, since the refrigerant passage is constituted by the plurality of pipes, the contact area with the gas to be dehumidified is increased, and the heat exchange efficiency is improved. Also in this case, each pipe body is independently introduced and led to the pressure vessel without branching and joining, and almost no refrigerant leakage occurs in the pressure vessel.

In addition, for the unnecessary pipes among the plurality of pipes for exhibiting the required heat exchange performance, the unnecessary portions of the unnecessary pipes are introduced after the outside of the pressure vessel. The lead-out part or both the lead-in and lead-out parts can be closed.

Means 8. In the means (7), the plurality of pipes constituting the refrigerant passage are joined to a refrigerant circulation pipe outside the pressure vessel outside the pressure vessel, so that the joint is exposed to the outside of the pressure vessel. Exchanger.

According to the above means 8, since the plurality of pipes constituting the refrigerant passage are joined to the refrigerant circulation pipe outside the pressure vessel, the joint portion, for example, the brazing portion is damaged and the refrigerant passage is damaged. Even if a leak occurs, it can be easily repaired. In addition, for the unnecessary pipes among the plurality of pipes to exhibit the required heat exchange performance, the unnecessary pipe introduction part, the lead-out part or the introduction after the outside of the pressure vessel. -Both outlet sites can be closed.

Further, since the pipe is joined to the refrigerant flow pipe outside the pressure vessel, not only can a plurality of pipes be combined into one pipe, but also a plurality of pipes can be connected to two pipes. Alternatively, it is also possible to combine a plurality of pipes with a number smaller than the number of pipes. As a result, for example, a plurality of refrigerant circulation systems can be provided without making any changes to the pressure vessel itself.

Means 9 In the above means 7 or 8,
A heat exchanger in which the plurality of pipes constituting the refrigerant passage have introduction parts to the pressure vessel arranged at positions close to each other and outlet parts from the pressure vessel arranged at positions close to each other.

According to the above-mentioned means 9, since the introduction parts and the lead-out parts of the plurality of pipes are gathered in the vicinity position, the plurality of pipes are gathered outside the pressure vessel, or the plurality of pipes are combined into a plurality of pipes. The workability at the time of branching is improved, and the possibility of breakage of the joint of each tube is reduced.

Means 10. The heat exchanger according to any one of the means 1 to 9, wherein the pressure vessel is configured by joining a plurality of divided vessels.

According to the means 10, the pressure vessel is composed of a plurality of divided vessels, so that, for example, an assembling operation for introducing or leading out the pipe constituting the refrigerant passage into or out of the pressure vessel can be smoothly performed. It can be carried out.

Means 11. In the above means 10, the plurality of divided containers are at least a divided container formed with an introduction portion of a tube constituting the refrigerant passage, a divided container formed with a discharge portion of the tube, And a divided vessel that supports the container from the outer peripheral side.

According to the means 11, the divided containers are
Assembling to include a divided container in which an introduction portion of a tube constituting a refrigerant passage is formed, a divided container in which a lead-out portion of the tube is formed, and a divided container which supports the tube from an outer peripheral side. Work becomes easier.

Means 12. The heat exchanger according to any one of the above means 1 to 11, wherein a plurality of projections are formed in the pipe body in the pressure vessel, or the pipe body itself is formed in a pleated shape.

According to the above means 12, the contact area between the pipe through which the refrigerant flows and the gas to be dehumidified is increased, and the heat exchange efficiency between the pipe and the pipe is simpler than when the pipe is simply cylindrical. Is improved.

Means 13. The heat exchanger according to any one of the above means 1 to 11, wherein a number of thin fins are formed in the tube in the pressure vessel.

According to the means 13, the contact area between the pipe through which the refrigerant flows and the gas to be dehumidified is greatly increased,
The heat exchange efficiency between the two is remarkably improved as compared with the case where the tube is simply cylindrical.

Means 14. In the above-mentioned means 13, in a region (evaporation section) where heat is exchanged between the gas to be dehumidified and the refrigerant,
A heat exchanger in which a flow direction of a gas to be dehumidified and a surface of a fin formed on the tube are generally parallel to each other.

According to the means 14, while the heat exchange efficiency between the gas to be dehumidified and the refrigerant is increased, the pressure loss during the flow of the gas to be dehumidified is almost eliminated by the myriad of fins.

Means 15. The heat exchanger according to any one of the above means 1 to 14 is provided in an apparatus main body, the apparatus main body is provided with a refrigeration circuit for cooling the refrigerant, and the dehumidification is performed using a refrigerant flow passage in the refrigeration circuit as the refrigerant passage. apparatus.

According to the means 15, it is possible to obtain a dehumidifier having the functions and effects described in the means 1 to 14. The refrigeration circuit is not limited to one system, and a plurality of systems can be provided.

[0053]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment will be described below with reference to FIGS. 1 is a sectional view of the heat exchanger, FIG. 2 is a front view of the heat exchanger, FIG. 3 is a circuit diagram of the dehumidifier, FIG. 4A is a schematic diagram of the heat exchanger, and FIG.
FIG. 5 is a perspective view of a precooling / reheater, and FIGS. 5A to 5D are views showing various examples of refrigerant pipes.

First, as an example, the outlines of the dehumidifier and the heat exchanger will be described with reference to FIG. 3 and FIG.

As shown in FIG. 3, the dehumidifier 1 has a substantially rectangular parallelepiped housing 2 in which various components of the dehumidifier 1 are integrated. The dehumidifier 1 in this embodiment is a so-called refrigeration dehumidifier. That is, a refrigerant such as chlorofluorocarbon is used to dehumidify the gas to be dehumidified, and a refrigeration circuit F for cooling the refrigerant is provided. In this embodiment, a case will be described in which air, particularly compressed air, is used as the gas to be dehumidified. However, it is needless to say that other gases such as nitrogen, helium, and the like, or a mixed gas thereof can be used. is there.

The structure of the refrigeration circuit F among the components of the dehumidifier 1 will be described. The compressor 3 as a compressor is connected to a compressor drive motor 4 as drive means, and the compressor drive motor 4 is driven. Then, the compressor 3 is operated to compress the refrigerant gas.

An accumulator 7 is mounted on the upstream side of the compressor 3. The accumulator 7 temporarily holds the liquid refrigerant, and does not supply the liquid refrigerant to the compressor 3 but supplies only the refrigerant gas.

A condenser 8 as a condenser is connected downstream of the compressor 3. In the vicinity of the condenser 8, a fan 9 is installed as a blower for blowing air to the condenser 8. A fan drive motor 10 as drive means is connected to the fan 9 so that the compressed refrigerant gas sent from the compressor 3 to the condenser 8 is cooled by the blowing action of the fan 9. The condenser 8 is greatly affected by the blowing action by detouring its flow path or by providing a large number of fins, thereby improving the cooling efficiency for the compressed refrigerant gas.

A filter dryer 11 is mounted downstream of the condenser 8. This filter dryer 1
1 comprises a filter and a desiccant (not shown),
Dust and moisture in the refrigeration circuit F are removed.

At the downstream side of the filter dryer 12, a capillary tube 12 which performs a pressure reducing action is mounted. This capillary tube 12 has a capillary structure,
The pressure of the liquid refrigerant passing therethrough is reduced.

The downstream side of the capillary tube 12 is introduced into the evaporator 13. The pipeline of the refrigeration circuit F introduced into the evaporator 13 is a refrigeration passage 14. In addition,
The specific structure of the freezing passage 14 will be described later. The accumulator 7 is connected to the downstream side of the freezing passage 14.

The accumulator 7, the compressor 3, the condenser 8, the filter dryer 11, the capillary tube 12, and the refrigerating passage 14 form a main flow path F1 of the refrigerating circuit F of the dehumidifier 1.

A bypass flow path F2 having a parallel relationship with the condenser 8, the filter dryer 11, and the capillary tube 12 is connected to the main flow path F1. A mechanical pressure capacity adjusting valve 15 is provided in the middle of the bypass flow path F2, and the communication of the bypass flow path F2 is switched or cut off by the pressure capacity adjusting valve 15. The pressure capacity adjusting valve 15 communicates or shuts off the bypass flow path F2 so that the pressure on the upstream side, that is, the pressure in the refrigeration passage 14 does not become lower than a set value. This adjustment prevents the refrigeration circuit F from freezing.

Next, high-temperature humid air as a dehumidified gas is supplied from an external air compressor (not shown), and the high-temperature humid air is cooled and dried in the evaporating section 13.
The configuration of the dehumidification target gas circuit S to be taken out again will be described.

An input passage 21 is connected to an external air compressor (not shown), and a pre-cooling / reheating device 22 is arranged downstream of the input passage 21. Pre-cooling / reheater 2
2, a precooling passage 23 downstream of the input passage 21 is provided.
Are formed. The specific structure of the precooling / reheater 22 will be described later.

The evaporating section 13 is disposed downstream of the pre-cooling passage 23. A cooling passage 24 downstream of the pre-cooling passage 23 is formed in the evaporating section 13. When the high-temperature humid air passing through the cooling passage 24 comes into contact with the refrigeration passage 14, heat exchange is performed in the evaporator 13.

A drain separation mechanism 25 is provided downstream of the evaporating section 13, and the drain separated here flows out to the drain passage 26 side. A drain discharge mechanism 27 is provided in the drain passage 26, and the drain is discharged to the outside of the housing 2 via the drain discharge mechanism 27.

The downstream side of the cooling passage 24 is
A reheat passage 28 formed in the reheater 22 is connected. The reheating passage 28 is formed so as to be in contact with the pre-cooling passage 23. Further, an output passage 29 extending outside is connected to the downstream side of the reheat passage 28.

The input passage 21, the pre-cooling passage 23, the cooling passage 24, the reheating passage 28 and the output passage 29 form a dehumidifying gas circuit S of the dehumidifier 1.

Now, the schematic structure of the evaporator 13 and the pre-cooler / reheater 22 will be further described with reference to FIG. 4. In this embodiment, the evaporator 13 and the pre-cooler / reheater 22 are simply The heat exchanger 31 is unitized as one heat exchanger 31, and the heat exchanger 31 is housed in the housing 2.

That is, the heat exchanger 31 has a case 32 as a sealed pressure vessel, in which the rectangular parallelepiped precooling / reheating device 22 is housed. The precooling / reheater 22 is configured as a plate-type heat exchanger, as shown in FIG. That is, the precooling / reheater 22 includes a rectangular cylindrical frame 33 having both ends in the longitudinal direction open, and a plurality of corrugated plates 34 are fixed on the inner peripheral side thereof in a state of being stacked. These are made of aluminum.

At one end in the longitudinal direction of each of the plates 34, an intermediate portion of each of the plates 34 is partitioned by a partition piece 35. In addition, on one side of the partition piece 35, every other gap between the plates 34 is a closed piece 36.
The portion not closed by the closing piece 36 is open. On the other hand, the partition piece 35
On the other side across which is closed, the portion which is open on the one side is closed by a closing piece 36, and the portion closed on the one side is open. Further, at the other end in the longitudinal direction of each of the plates 34, a closing piece 36 is attached exactly opposite to the above.

As described above, in the pre-cooling / reheater 22, the air introduced from the position of the outline arrow A is derived from the position of the outline arrow B, and the air introduced from the position of the outline arrow C. Is derived from the position of the white arrow D. The flow path from the white arrow A to the white arrow B is the pre-cooling passage 23, and the white arrow C
The flow path extending from D to D is the reheat passage 28, and heat exchange is performed between the air flowing through the precooling passage 23 and the reheat passage 28. Therefore, here, the entrance corresponding to the outline arrow A is the pre-cooling entrance 37, and the outline arrow B
The outlet corresponding to the white arrow C is the pre-cooling outlet 38, the inlet corresponding to the white arrow C is the reheat inlet 39, and the outlet corresponding to the white arrow D is the reheat outlet 40.

As shown in FIG. 4A, the input passage 21 is connected to the pre-cooling inlet 37, and the output passage 29 is connected to the reheating outlet 40. A guide passage 41 is formed on the outer peripheral side of the precooling / reheater 22 to guide the fluid led out from the precooling outlet 38 to the opposite end (here, the upper part) of the precooling / reheater 22.

The evaporator 13 is provided between the outer peripheral side of the guide passage 41 and the inner peripheral surface of the case 32, and the refrigerating passage 14 is disposed in the evaporator 13. The refrigerating passage 14 is constituted by a fin tube in which a number of fins are formed around a pipe spirally wound around the pre-cooling / reheating device 22, while the cooling passage 24 is formed of a case 32.
The refrigeration passage 1 between the inner periphery and the outer periphery of the guide passage 41
4 formed by the surrounding gap. This cooling passage 1
4 is led to the lower part of the case 32, but since the lower part of the reheat inlet 39 is open, the air is guided to the reheat passage 28 from here, and is output to the output passage 2 through the reheat outlet 40.
9 will be led.

Next, the dehumidifier 1 constructed as described above
When the high-temperature humid air is supplied from the external air compressor to the input passage 21 in a compressed state (pressurized state), the pre-cooled passage 23, the cooling passage 24, and the reheat passage 28 Air is supplied to the output passage 29.

On the other hand, the compressor 3 and the fan 9 are driven by the compressor drive motor 4 and the fan drive motor 10. Then, the refrigerant circulates in the refrigeration circuit F. That is, the low-pressure refrigerant gas is compressed by the compressor 3 to become a compressed refrigerant gas, and is cooled in the condenser 8 to become a compressed liquid refrigerant. Then, after dust and moisture are removed by the filter dryer 11, the pressure is reduced by the capillary tube 12 to become a low-pressure liquid refrigerant.

When the liquid refrigerant passes through the refrigerating passage 14, heat exchange is performed between the liquid refrigerant and the high-temperature humid air passing through the cooling passage 24. As a result, the liquid refrigerant in the refrigeration passage 14 becomes a low-pressure high-temperature refrigerant and is supplied to the accumulator 7.

On the other hand, the high-temperature humid air is cooled and dehumidified by heat exchange to become cooled dry air,
Sent to 8. Since the reheating passage 28 is in contact with the pre-cooling passage 23, heat exchange is also performed at the contacted portion. That is, the cooling and drying air in the reheating passage 28 and the pre-cooling passage 2
Heat exchange is performed between the high-temperature humid air and the high-temperature humid air, and the cooled dry air is heated to be dried air and sent to the output passage 29, and the high-temperature humid air is pre-cooled. Then, the dry air taken out from the output passage 29 is supplied to an external fluid pressure device such as an electromagnetic valve, an air cylinder, or the like for use.

The outline of the dehumidifier 1 is as described above. In this embodiment, since the specific configuration of the heat exchanger 31 is as shown in FIGS. The specific configuration will be further described. FIG.
The same reference numerals are given to the same or corresponding components as those described above, and the description is omitted.

As shown in FIGS. 1 and 2, the case 32
Is actually a cylindrical body 32a and a pair of bowl-shaped end plates 32 formed so as to close both ends thereof.
b. Further, the trunk 32a is divided into three in the longitudinal direction. These body part 32a and end plate 3
Since 2b is made of stainless steel, it has high corrosion resistance.

Each of the input passage 21 and the output passage 29 is formed of a tubular body, and is fixed by welding to one of the end plates 32b. Further, the precooling / reheater 22 and the respective tubes of the input passage 21 and the output passage 29 are merely sealed by an O-ring 59 (only the output passage 29 side is shown). And pre-cooling / reheating unit 2
2 is supported by the support member 60 from below. Therefore, the positioning of each tube of the input passage 21 and the output passage 29 is performed by fixing to the end plate 32b, and the precooling / reheater 22 can be installed so as to match the fixed position of each tube. .

Further, a guide passage 41 for guiding the gas led out from the pre-cooling outlet 38 to the opposite end of the pre-cooling / reheating device 22.
Is configured as follows. That is, a metal cylindrical body 61 such as stainless steel is disposed at a predetermined interval on the outer peripheral side of the pre-cooling / reheating unit 22. An aluminum plate 62 is fixed below the precooling / reheater 22. The outer peripheral portion of the aluminum plate 62 is in close contact with the lower inner peripheral side of the cylindrical body 61, and the space therebetween is sealed. Accordingly, the gas led out from the pre-cooling outlet 38 flows to the outer peripheral side on the upper surface side of the aluminum plate 62, and thereafter, the outer peripheral side of the pre-cooling / reheater 22 and the cylindrical body 6
1 flows upward in the gap with the inner peripheral side. A guide passage 41 is formed by a gap between the outer peripheral side of the precooling / reheater 22 and the inner peripheral side of the cylindrical body 61. The cylinder 61
Since the upper end is open, the gas that has passed through the guide passage 41 reaches the upper space in the case 32, where it is U-turned to the outer peripheral side and guided to the evaporating section 13.

The evaporating section 13 is formed in a cylindrical space between the inner peripheral side of the case 32 and the outer peripheral side of the cylindrical body 61. In the schematic configuration shown in FIG. 4A, the refrigerating passage 14 is described as a single winding, but a specific configuration is, for example, a triple winding. The refrigeration passage 14 is specifically composed of a plurality of (here, six) branch pipes 63. An infinite number of thin fins 64 are formed in each of the branch pipes 63. The specific configuration of the branch pipe 63 is as shown in FIG. 5 (a). However, as shown in FIG. 5 (b), an infinite number of disks 65 are formed in place of the fins 64, and FIG. In order to improve the heat transfer effect, there are a number of protrusions 66 formed as shown in FIG. 5 and a shape in which the branch pipe 63 itself has a helical curved surface 67 as shown in FIG. The various branch pipes 63 thus obtained can be appropriately used. However, the branch pipe 63 having the thin plate-shaped fins 64 on the outer periphery is
It is most excellent in that the pressure loss is small and the heat transfer effect is high.

In order to fix each branch pipe 63 to the outer peripheral side of the cylindrical body 61, a number of projections (not shown) are formed on the outer peripheral surface of the cylindrical body 61, and a wire passes through each of the projections. Through holes are formed. Each branch pipe 63 is wound around the outer periphery of the cylindrical body 61 so as to be caught by the projection, and is connected to the outer periphery of each branch pipe 63 by a wire passed through the through-hole. 61 is fixed to the outer peripheral position.

Instead of such a structure for positioning the branch pipes 63, a heat radiating plate having holes formed in a size that can be passed by the respective branch pipes 63 is radially arranged in the evaporating section 13 and is provided in the holes. Each branch pipe 63 may be positioned by passing through each branch pipe 63. Further, a heat insulating sheet made of rubber or the like may be arranged on the outer peripheral side of the cylindrical body 61 to enhance the gas cooling effect in the evaporating section 13.

Each of the branch pipes 63 is arranged such that, from the outer peripheral side thereof, the trunk part 32a at the middle of the three trunk parts 32a
Supported by

As shown in FIG. 1 and FIG.
The case 3 is aligned in the lower part of the case 32
2 are introduced individually. This introduction part is provided in the trunk part 32a arranged below the three trunk parts 32a. After being wound around the inside of the case 32, it is individually led out of the case 32 in a state of being aligned at the upper part of the case 32. This derivation site is based on
It is provided on the trunk portion 32a that is disposed above the two trunk portions 32a.

Each of the branch pipes 63 does not have a joint such as a brazing portion when viewed individually, and leakage of the refrigerant from the joint in the case 32 is prevented. And each branch pipe 6
3 are collectively brazed to one refrigerant pipe 71 outside the case 32. Therefore, the brazing portion 72 which is a joining portion between the refrigerant pipe 71 and each branch pipe 63 is provided in the case 32.
It is in a state of being exposed to the outside (the state where the brazing portion 72 has been applied is shown only in FIG. 2).

Incidentally, as shown in FIG.
4, 75 are provided as a pair. One drain outlet 7
5 is provided on the bottom surface of the lower end plate 32b, and the other drain outlet 74 is provided on a part of the peripheral surface of the body 32a. In particular, the drain outlet 75 provided on the end plate 32b is used when the heat exchanger 31 is used in a vertical position as shown in the figure, and the drain outlet 74 provided on the body 32a is connected to the heat exchanger 31. Used when placed horizontally. And the drain outlet 7 on the unused side
4 or 75 is closed. The drain outlet 74 required for use in the horizontal position is provided in the case 32 of the branch pipe 63.
It is preferable to provide the branch pipe 63 on the side opposite to the outlet from the viewpoint of protecting the branch pipe 63 from corrosion.

The inner surface of the end plate 32b at the lower part of the case 32 is a space for drain reservoir. A siphon tube 76 is provided at the drain discharge port 75 so as to protrude into this space. This siphon tube 76
Is connected to the drain discharge mechanism 27 outside the case 32. As a result, only the supernatant of the drain can be discharged, and the clogging of the drain discharge mechanism 27 can be prevented. Further, since the siphon tube 76 has a shape in which the tip is obliquely cut, drain is prevented from flowing down along the side surface of the siphon tube 76, and a large amount of drain is prevented from flowing into the siphon tube 76 at once. can do.

In addition, the end plate 32 at the bottom of the case 32
Another drain outlet 73 is provided on the inner surface side b. By providing a dedicated drain discharge mechanism at the drain discharge port 73, there is an advantage that sludge or the like accumulated in the drain reservoir can be discharged manually or automatically.

According to the heat exchanger 31 configured as described above, the refrigerating passage 14 is wound around the precooling / reheating device 22 so as to be circulated as a plurality of branch pipes 63.
In this way, the branch pipe 6 is circulated around the precooling / reheater 22.
By arranging 3, it is not necessary to make the branch pipe 63 make a U-turn with a small radius of curvature. As a result, it is not necessary to provide a brazing portion for each branch pipe 63 in the case 32,
It can be configured as a single tube. A brazing portion 72 for connecting the branch pipes 63 to one refrigerant pipe 71 collectively can be provided outside the case 32.

As a result, even if the brazing portion 72 is damaged and refrigerant leakage occurs, repair work can be easily performed outside the case 32. Therefore, it is not necessary to replace the entire heat exchanger 31 in accordance with the breakage of the brazed portion 72.
Repair costs in case of breakage are reduced.

Further, since a plurality of branch pipes 63 individually enter the case 32 and are individually taken out of the case 32, even when a plurality of refrigeration circuits F are used, the structure of the heat exchanger 31 is not changed. An appropriate number of branch pipes 63 are not changed.
Can be connected collectively for each refrigeration circuit F. Therefore, when it is desired to control the dehumidification capacity by controlling the number of operating refrigeration circuits F, it is very advantageous to use the heat exchanger 31 of this embodiment.

Further, since a plurality of branch pipes 63 individually enter the case 32 and are individually taken out of the case 32, for example, all the branch pipes 63 are not necessary in terms of heat exchange performance, and some branch pipes 63 are not necessary. When the branch pipe 63 is used, the heat exchanger 3
1 can be easily handled after the assembly.
That is, by closing the entrance, exit, or entrance / exit of each branch pipe 63 to the case 32 outside the case 32, unnecessary flow of the refrigerant in the branch pipe 63 can be eliminated. Therefore, in recent years, the specification of a wide variety of heat exchangers,
It is possible to cope with fewer heat exchangers, and there are advantages such as reduction of stock types and cost.

In the evaporating section 13, the flow path of the air to be dehumidified gas extends linearly, and almost no pressure loss occurs. As a result, it is preferable from the viewpoint of energy saving.
In the case of the type in which the thin fins 64 are provided on the outer circumference of the branch pipe 63 as described above, the flow direction of the air is substantially parallel to the surface of the fins 64, so that almost no pressure loss occurs. .

Further, the branch pipe 6 arranged in the evaporating section 13
Assuming that the diameter of the pipe 3 is constant, the pressure loss in the evaporator 13 can be adjusted only by changing the number and length (number of turns) of the branch pipe 63, and the adjustment of the pressure loss becomes easy. As a result, it is easy to set optimal temperature conditions for different types of refrigerants, and when adopting different types of refrigerants, it is possible to easily cope with them simply by setting the number and length (number of turns) of the branch pipe 63.

Further, since each branch pipe 63 is inserted and removed from the side of the case 32 of the heat exchanger 31, it is possible to prevent the whole from becoming long, and to save the heat exchanger 31 and the dehumidifier 1. This can contribute to space.

The body 32a of the case 32 is divided into three parts so that the branch pipes 63 can be inserted into and taken out of the body 32a at both ends. Is configured to support the outer peripheral side. Thereby, workability at the time of assembling each branch pipe 63 is improved.

Note that, in addition to the embodiment described above,
The following various embodiments are conceivable.

That is, the pre-cooling / reheating unit 22 is connected to the heat exchanger 31.
Instead of the type incorporating one, the present invention may be implemented as a type incorporating a plurality of types. For example, the pre-cooling / reheater 22 may be connected in series in the longitudinal direction, or may be connected in parallel. Also in this case, the design of the evaporating section 13 may be changed by changing the number of turns of the branch pipe 63. And, as described above,
When the reheaters 22 are connected in series, the heat exchange efficiency is improved, and when they are connected in parallel, it is possible to cope with an increased air flow rate. Of course, a combination of the series connection and the parallel connection may be used to increase the air flow rate and improve the heat exchange efficiency. Further, even in this case, since the same pre-cooling / reheating device 22 is used, the dehumidifying ability can be changed without increasing the types of components.

The introduction part and the lead-out part of each branch pipe 63 into the case 32 are provided on the side surface of the case 32.
May be provided on the upper surface side and the lower surface side. In addition, although the introduction section and the lead-out section are vertically separated from each other, they need not always be vertically separated.

The precooling / reheater 22 is not limited to the plate type as in the above embodiment, but may be another type such as a cross fin coil type.
A type in which only reheating is performed without performing precooling may be employed.

Further, as shown in FIG. 6, a cylindrical skirt portion 81 may be provided at or near the extended position below the body portion 32a. Due to the skirt portion 81, the air that has passed through the evaporating portion 13 can enter the pre-cooling / reheating device 22 only after wrapping around from the tip side of the skirt portion 81. When the air flows around the tip of the skirt portion 81, the moisture mixed with the air is appropriately separated from the air by the skirt portion 81, and there is no possibility that the moisture enters the precooling / reheating device 22. Then, the water attached to the skirt portion 81 accumulates in a drain reservoir formed in the lower end plate 32b.

Further, as shown in FIG. 7, a cylindrical porous plate 85 protruding toward the drain reservoir side may be provided at or near the extended position below the body 32a. This perforated plate 8
Due to 5, air that has passed through the evaporator 13 can enter the precooling / reheater 22 only from the hole of the perforated plate 85. Then, when the air flows around the hole of the perforated plate 85, the moisture mixed with the air is appropriately separated by the periphery of the hole, and there is no possibility that the water enters the precooling / reheating device 22. The water adhering to the perforated plate 85 is removed from the lower end plate 3
It will collect in the drain reservoir formed in 2b. When the perforated plate 85 having a large number of holes is provided, the effect of separating air and moisture is further enhanced as compared with the case where the skirt 81 is provided as described above.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a heat exchanger according to one embodiment.

FIG. 2 is a front view of the heat exchanger.

FIG. 3 is a circuit diagram of a dehumidifier.

4A is a schematic view of a heat exchanger, and FIG. 4B is a perspective view of a pre-cooling / reheating device.

FIGS. 5A to 5D are diagrams showing various examples of a refrigerant pipe.

FIG. 6 is a cross-sectional view of a heat exchanger according to another embodiment.

FIG. 7 is a cross-sectional view of a heat exchanger according to still another embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Dehumidifier, 2 ... Housing as an apparatus main body, 13
... Evaporation unit, 14 ... Refrigeration passage as a refrigerant passage, 21 ... Input passage, 22 ... Precooling / reheating unit as a precooling / reheating unit, 2
3 ... pre-cooling passage, 24 ... cooling passage, 28 ... reheating passage, 31
... a heat exchanger, 32 ... a case as a pressure vessel, 63 ... a branch pipe as a tube constituting a refrigerant passage, 71 ... a refrigerant pipe, 72 ... a brazing part as a joint, F ... a refrigeration circuit, S
... Dehumidified gas circuit.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Isao Ito Komaki City, Aichi Pref. FA03 FA04 GA01 GA03 GB02 GB04 GB06

Claims (12)

[Claims] 1. A pressure vessel is provided with a passage through which a gas to be dehumidified is circulated, and a refrigerant passage through which a refrigerant for performing heat exchange with the gas to be dehumidified is provided. A heat exchanger constituted by a tube having no joint from an introduction part to an outlet part to the pressure vessel. 2. An evaporator for exchanging heat between a gas to be dehumidified and a refrigerant in a pressure vessel, and a precooler for exchanging heat between the gas to be dehumidified before input to the evaporator and the gas to be dehumidified after output from the evaporator. In a heat exchanger provided with a reheating unit, the evaporating unit is provided with a passage through which the gas to be dehumidified is circulated in the pressure vessel, and a refrigerant passage through which the refrigerant is circulated in the passage. A heat exchanger in which the refrigerant passage is constituted by a tube having no joint from the introduction part to the discharge part to the pressure vessel. 3. An evaporator for exchanging heat between a dehumidified gas and a refrigerant in a pressure vessel, and a precooler for exchanging heat between the dehumidified gas before the input of the evaporator and the dehumidified gas after the output of the evaporator. In a heat exchanger provided with a reheating unit, the precooling / reheating unit is arranged near the center of the pressure vessel, and the evaporating unit is arranged on the outer peripheral side of the precooling / reheating unit of the pressure vessel. The evaporating section is provided with a passage through which the gas to be dehumidified is circulated in the pressure vessel, and a refrigerant passage through which the refrigerant is circulated is provided in the passage, and the refrigerant passage is introduced into the pressure vessel. A heat exchanger consisting of a tube with no joints from the part to the outlet part. 4. A tube constituting the refrigerant passage is spirally wound around an outer peripheral side of the pre-cooling / re-heating section.
The heat exchanger as described. 5. The pressure vessel is formed in an elongated shape, and an introduction portion of the pipe constituting the refrigerant passage into the pressure vessel is provided at one longitudinal end of the pressure vessel, and an outlet portion. The heat exchanger according to claim 4, wherein the heat exchanger is provided at the other end in the longitudinal direction of the pressure vessel. 6. The pre-cooling / re-heating unit is configured by a plate heat exchanger configured by stacking a plurality of plates at a predetermined interval, and the plate heat exchanger is provided between each plate. The pre-cooling passage through which the gas to be dehumidified flows before the input to the evaporating section and the reheating passage through which the gas to be dehumidified flows after the output from the evaporating section are alternately arranged. A heat exchanger according to item 1. 7. A plurality of tubes constituting the refrigerant passage are provided, and each of the tubes is independently arranged without branching and joining from a site for introduction to the pressure vessel to a site for discharge. The heat exchanger according to claim 1. 8. A plurality of pipes constituting the refrigerant passage,
The heat exchanger according to claim 7, wherein the heat exchanger is joined to a refrigerant circulation pipe outside the pressure vessel outside the pressure vessel, thereby exposing the joint to the outside of the pressure vessel. 9. A plurality of pipes constituting the refrigerant passage,
9. The heat exchanger according to claim 7, wherein the introduction portions to the pressure vessel are arranged at positions close to each other, and the extraction portions from the pressure container are arranged at positions close to each other. 10. 10. The heat exchanger according to claim 1, wherein the pressure vessel is configured by joining a plurality of divided vessels. 11. The container according to claim 11, wherein:
A divided container in which an introduction portion of a tube constituting the refrigerant passage is formed, a divided container in which a lead-out portion of the tube is formed, and a divided container which supports the tube from an outer peripheral side. 11. The heat exchanger according to 10. 12. A heat exchanger according to claim 1, wherein said heat exchanger is provided in an apparatus main body, said apparatus main body is provided with a refrigeration circuit for cooling said refrigerant, and refrigerant circulation in said refrigeration circuit is performed. A dehumidifier that uses a passage as the refrigerant passage.