JP2011163736A - Heat exchanger, double cycle type refrigerator equipped with the same, and method for manufacturing heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact heat exchanger for a double cycle type refrigerator. <P>SOLUTION: The heat exchanger is used for a condenser 3 and an evaporator 4 of the double cycle type refrigerator combining two refrigerators. The condenser 3 and the evaporator 4 includes shells 5, 7 forming refrigerant spaces inside; partition plates 6, 8 partitioning the refrigerant spaces in the shells 5, 7; water chambers 10, 11, 33, 34 provided at the ends of the shells 5, 7 and partition plates 6, 8 to lead cold water or cooling water therein; and tube plates 20, 21, 30, 31 partitioning the water chambers 10, 11, 33, 34 from the refrigerant spaces in the shells 5, 7 and supporting a heat transfer tube through which the cold water or cooling water flows. The shells 5, 7 are divided by longitudinal division parts 5a, 7a extending in the longitudinal direction of the shells 5, 7, and the longitudinal division parts 5a, 7a are fixed to the partition plates 6, 8 by welding. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat exchanger for a double cycle refrigerator, a double cycle refrigerator equipped with the heat exchanger, and a method for manufacturing the heat exchanger.

In order to prevent global warming, a refrigerator having a high COP (coefficient of performance) is required, and a double cycle turbo refrigerator is proposed as one means.
The double cycle turbo chiller has a configuration in which water systems (a chilled water system and a chilled water system) of two turbo chillers are connected in series (see, for example, Patent Document 1 below). Thereby, compared with the case where a refrigerator is operated by one unit, the head difference per unit between a condenser and an evaporator can be made small, and performance improvement can be aimed at.
When such a double cycle turbo refrigerator is employed, in order to reduce the installation area, the inside of one shell of the evaporator and the evaporator (heat exchanger) is divided into two systems in which each refrigerant flows independently. There is a way to divide. In this case, a structure is employed in which a partition plate is installed inside the shell and the shell internal space is separated into two (see Patent Document 1).

JP-A-10-132400

  When the inside of the shell is divided using the partition plate as described above, if the shell is large, an operator can enter the inside and weld the partition plate to the inner peripheral surface of the shell. Since a worker cannot enter the inside if it is small, a conventional structure cannot be adopted.

  The present invention has been made in view of such circumstances, and has a structure in which the inside of the shell is divided by a partition plate even if the shell is small enough to prevent an operator from entering the shell. It is an object of the present invention to provide a heat exchanger, a double cycle refrigerator equipped with the heat exchanger, and a method for manufacturing the heat exchanger.

In order to solve the above problems, the heat exchanger of the present invention, the double cycle refrigerator equipped with the heat exchanger, and the method of manufacturing the heat exchanger employ the following means.
That is, the heat exchanger according to the present invention is a condensing of a double-cycle refrigerator that combines a first refrigerator that constitutes a refrigeration cycle with a first refrigerant and a second refrigerator that constitutes a refrigeration cycle with a second refrigerant. A shell that forms a refrigerant space therein, a partition plate that divides the refrigerant space in the shell into the first refrigerant and the second refrigerant, and the shell and the partition A heat exchange medium chamber that is provided at an end of the plate and into which the heat exchange medium is introduced; and a tube plate that partitions the refrigerant space in the shell and supports the heat transfer tubes through which the heat exchange medium flows. A heat exchanger provided, wherein the shell is divided by a longitudinal dividing portion extending in a longitudinal direction of the shell, and the longitudinal dividing portion is fixed to the partition plate. It is characterized by.

Since the shell is not an endless cylindrical body and is divided at the longitudinal division portion, the shell divided at the longitudinal division portion may be fixed to the partition plate. There is no need to enter the shell and perform the fixing work as in the case where the cylinder is a cylinder. Therefore, the shell can be fixed to the partition plate even for a shell that is so small that it cannot enter the cylindrical shell, so that the shell can be downsized and the entire heat exchanger can be made compact. Can be configured.
A typical method for fixing the shell to the partition plate is welding.
Examples of the heat exchange medium include cold water supplied to the evaporator and cooling water supplied to the condenser. In these cases, the heat exchange medium chamber is a water chamber.

  Furthermore, according to the heat exchanger of the present invention, the tube sheet is divided by a divided portion provided at a predetermined position, and the divided portion is fixed to the partition plate. To do.

Since the tube sheet is divided, the tube sheet is smaller than an integrated tube sheet, and handling is easy. Thereby, storage, transportation work, and fixing work of the tube sheet are facilitated.
A typical method for fixing the tube plate to the partition plate is welding.

  Furthermore, according to the heat exchanger of the present invention, the partition plate is directed in a direction toward the first compressor of the first refrigerator or the second compressor of the second refrigerator. .

  Since the partition plate is directed in the direction toward the first compressor or the second compressor, the distance between the compressor and the first refrigerant space or the second refrigerant space located on both sides of the partition plate is made as much as possible. Can be shortened. Thereby, when using a heat exchanger as a condenser, the refrigerant | coolant discharge piping which connects between a compressor and a condenser can be shortened, and pressure loss can be reduced.

  Furthermore, according to the heat exchanger of the present invention, the partition plate is inclined at a predetermined angle with respect to the vertical direction.

  Since the partition plate is inclined at a predetermined angle (preferably 30 ° to 45 °) with respect to the vertical direction, the liquid refrigerant in the refrigerant space located on the upper side of the partition plate flows downward through the partition plate, and the refrigerant Liquid refrigerant is collected in a liquid reservoir at the bottom of the space. Thus, since the liquid refrigerant can be efficiently collected in the liquid reservoir at the bottom of the refrigerant space, the volume of the liquid reservoir can be reduced. On the other hand, when the heat transfer tube of the condenser is immersed in the liquid refrigerant, the function as the condensation heat transfer tube is significantly reduced. Since the volume of the liquid reservoir is reduced in the present invention, the space without the liquid refrigerant through which the heat transfer tube can be inserted becomes relatively wide, and a heat exchanger having high heat exchange efficiency is provided by arranging a large number of heat transfer tubes. can do.

  Moreover, the double cycle refrigerator of the present invention includes the heat exchanger described in any of the above.

By using the above heat exchanger, a compact double cycle refrigerator can be provided.
As the refrigerator, a turbo refrigerator is typically used.

  Moreover, the manufacturing method of the heat exchanger of this invention is a double cycle type refrigerator combined with the 1st refrigerator which comprises the refrigerating cycle by a 1st refrigerant | coolant, and the 2nd refrigerator which comprises the refrigerating cycle by a 2nd refrigerant | coolant. Used in the condenser and / or evaporator, a shell that forms a refrigerant space therein, a partition plate that divides the refrigerant space in the shell into the first refrigerant and the second refrigerant, the shell, and A heat exchange medium chamber that is provided at an end of the partition plate and into which the heat exchange medium is introduced, and a tube plate that partitions the refrigerant space in the heat exchange medium chamber and the shell and supports a heat transfer tube through which the heat exchange medium flows A method of manufacturing a heat exchanger, comprising: fixing a longitudinally divided portion of a shell divided by a longitudinally divided portion extending in a longitudinal direction to the partition plate. To do.

Since the shell is not an endless cylindrical body and is divided at the longitudinal division portion, the shell divided at the longitudinal division portion may be fixed to the partition plate. There is no need to enter the shell and perform the fixing work as in the case where the cylinder is a cylinder. Therefore, the shell can be fixed to the partition plate even for a shell that is so small that it cannot enter the cylindrical shell, so that the shell can be downsized and the entire heat exchanger can be made compact. Can be configured.
A typical method for fixing the shell to the partition plate is welding.

  According to the present invention, since the shell is divided in the longitudinal direction, the divided shell may be fixed to the partition plate. Therefore, the shell can be reduced in size, and the entire heat exchanger and thus the double cycle refrigerator can be configured compactly.

It is the schematic block diagram which showed the refrigerant circuit of the double cycle type turbo refrigerator concerning one Embodiment of this invention. It is sectional drawing which showed the evaporator of FIG. It is the perspective view which showed the external appearance of the double cycle type turbo refrigerator concerning one Embodiment of this invention. The fixed structure of the shell and partition plate of the condenser or evaporator concerning one Embodiment of this invention is shown, (a) is a top view, (b) is a front view, (c) is a longitudinal direction division | segmentation of the shell It is sectional drawing which showed the part. The fixed structure of the partition plate and tube plate of the evaporator concerning one Embodiment of this invention is shown, (a) is a longitudinal cross-sectional view, (b) is a front view, (c) is the case where complete penetration was performed It is the longitudinal cross-sectional view which showed. It is the perspective view which showed the fixation structure of the partition plate and tube plate of the evaporator concerning one Embodiment of this invention. The water chamber of the evaporator concerning one Embodiment of this invention is shown, (a) is a top view, (b) is a front view, (c) is a left view. It is the perspective view which showed the external appearance of the condenser concerning one Embodiment of this invention. It is a disassembled perspective view for demonstrating the manufacturing method of the evaporator of this invention. It is a disassembled perspective view for demonstrating the manufacturing method of the conventional evaporator. FIG. 4A is a front view before a flat plate is deformed, FIG. 4B is a plan view, and FIG. 4C is a front view after completion. FIG. 4 shows another modification of FIG. 4, (a) is a plan view, and (b) is a front view. FIG. 4 shows another modification of FIG. 4, (a) is a plan view, and (b) is a front view. The modification of FIG. 5 is shown, (a) is a top view, (b) is a front view. It is the schematic for demonstrating the effect | action of the condenser concerning one Embodiment of this invention, (a) shows this invention, (b) shows the comparative example 1, (c) shows the comparative example 2. FIG.

Embodiments according to the present invention will be described below with reference to the drawings.
Hereinafter, an embodiment of the present invention will be described with reference to FIG.
FIG. 1 shows a double cycle turbo chiller in which two refrigerators having two independent refrigerant systems are combined. The respective refrigerators are designated as a Unit A turbo refrigerator (first refrigerator, hereinafter referred to as “A Unit”) and a Unit B turbo refrigerator (second refrigerator, hereinafter referred to as “B Unit”), and are equivalent to each other. Capacity.
As shown in the figure, the double-cycle turbo refrigerator includes a condenser (heat exchanger) 3 in which a condenser 3a of Unit A and a condenser 3b of Unit B are integrated, and evaporation of Unit A. And an evaporator (heat exchanger) 4 in which the evaporator 4a and the evaporator 4b of Unit B are integrated.
The A-unit condenser 3a and the B-unit condenser 3b share a cooling water system with the communicating cooling water heat transfer tubes 9a, 9b. The Unit A evaporator 4a and the Unit B evaporator 4b share a chilled water system with the chilled water heat transfer tubes 10a and 10b communicated with each other.
The No. A condenser 3a is disposed upstream of the No. B condenser 3b in the cooling water flow direction. The cooling water flows into the Unit A condenser 3a at 32 ° C., for example, and flows out from the Unit B condenser 3b at 37 ° C., for example.
The A machine evaporator 4a is arrange | positioned with respect to the B machine evaporator 4b in the downstream of the flow direction of cold water. The cold water flows into the Unit B evaporator 4b at 12 ° C., for example, and flows out from the Unit A evaporator 4a at 7 ° C., for example.

  The A machine is driven by, for example, an A machine motor 2a whose rotation speed is variable by an inverter device, and a No. A turbo compressor 1a that compresses refrigerant, and a high-temperature and high-pressure gas refrigerant compressed by the A machine turbo compressor 1a. A machine A condenser 3a that condenses, a machine A expansion valve 12a that expands the liquid refrigerant condensed in the machine A condenser 3a, and a machine A evaporator that evaporates the liquid refrigerant expanded by the machine A expansion valve 12a 4a.

  Similarly to Unit A, Unit B is driven by a Unit B motor 2b whose rotational speed is variable by, for example, an inverter device, and is compressed by a Unit B turbo compressor 1b that compresses refrigerant and a high temperature compressed by the Unit B turbo compressor 1b. Unit B condenser 3b that condenses high-pressure gas refrigerant, Unit B expansion valve 12b that expands the liquid refrigerant condensed in Unit B condenser 3b, and liquid refrigerant expanded by Unit B expansion valve 12b evaporates And a No. B machine evaporator 4b.

The condenser 3 is a shell-and-tube heat exchanger. The shell 5 forms an outer shell and forms a refrigerant space therein, and the inside of the shell 5 includes a refrigerant system of Unit A and a refrigerant system of Unit B. And a partition plate 6 for partitioning.
The evaporator 4 has the same configuration as the condenser 3 and is a shell-and-tube heat exchanger. The shell 7 forms an outer shell and forms a refrigerant space inside, and the inside of the shell 7. A partition plate 8 is provided for dividing and partitioning the refrigerant system of Unit A and the refrigerant system of Unit B.

FIG. 2 shows a longitudinal sectional view of the evaporator 4. As shown in the figure, the refrigerant space in the shell 7 is divided into two by a partition plate 8 at the center. Water chambers (heat exchange medium chambers) 10 and 11 are provided at both ends of the shell 7, respectively. The internal space of the shell 7 is closed by tube plates 20 and 21 from both ends, and the water chambers 10 and 11 are connected to the tube plates 20 and 21.
The water chamber 10 on one end side (right side in the figure) of the shell 7 is partitioned into an inlet water chamber 13 and an outlet water chamber 14 by a water chamber partition plate 15. The water chamber 11 on the other end side (the left side in the figure) of the shell 7 is formed as one space so that the cold water that has flowed in can be returned. Between the inlet water chamber 13 and the water chamber 11, there is provided a cold water heat transfer pipe 10 a through which cold water flows, and between the water chamber 11 and the outlet water chamber 14, the cold water transfer through which cold water flows. A heat pipe 10b is provided. The cold water heat transfer tubes 10a and 10b are supported by tube plates 20 and 21 disposed at both ends. The cold water heat transfer tubes 10a and 10b are shown in a simplified manner in the figure, one by one, but in reality, a plurality of heat transfer tubes 10a and 10b are provided in parallel.
The condenser 3 is different in that the cooling water flows instead of the cold water, but has substantially the same configuration as the evaporator 4.

FIG. 3 is a perspective view of the entire double cycle turbo chiller having the above-described configuration. As shown in the figure, the evaporator 4 is installed below, and two turbo compressors 1a, 1b are installed side by side in the axial direction. The condenser 3 is installed obliquely above the evaporator 4 and obliquely below the turbo compressors 1a and 1b. Further, as can be seen from the figure, the shells 5 and 7 of the condenser 3 and the evaporator 4 have a two-part structure having longitudinally divided parts 5a and 7a extending in the longitudinal direction. Partition plates 6 and 8 are fixed at portions 5a and 7a. Therefore, the figure shows a state in which the upper ends of the partition plates 6 and 8 protrude from the shells 5 and 7. The partition plate 6 of the evaporator 4 is provided in the vertical direction, whereas the partition plate 8 of the condenser 3 is provided in a direction inclined with respect to the vertical direction. This will be described later.
Further, as can be seen by referring to the tube plate 21 located on the water chamber 11 side of the evaporator 4, the tube plate 20 (the same applies to the tube plate 21) is divided into two parts, and the partition plate 6 is sandwiched from both sides. It has a structure that is fixed by. Moreover, the tube plates 30 and 31 of the condenser 3 are also divided into two vertically.
In the figure, reference numerals 33 and 34 denote cooling water chambers provided at both ends of the condenser 3.

  FIG. 4 shows a fixing structure between the shells 5 and 7 and the partition plates 6 and 8. As shown in the figure, the shells 5 and 7 are half cracks divided by the longitudinal dividing portions 5a and 7a. As shown in FIG.4 (c), the groove | channel is formed in the longitudinal direction division | segmentation part 5a, 7a. It fixes by performing welding continuously in a longitudinal direction in the state which contacted the outer surface of the partition plates 6 and 8 with this longitudinal direction division | segmentation part 5a, 7a. The welding is performed so as to be complete penetration welding from the outer peripheral side of the shells 5 and 7 (see the welding line W1 in FIG. 4B). Therefore, the welding line W1 is formed on the outer peripheral side of the shells 5 and 7, as shown in FIGS.

FIG. 5 shows a structure for fixing the shell 7, the partition plate 8 and the tube plate 20 of the evaporator 4. As shown in the figure, the tube sheet 20 is divided into left and right parts by a dividing part 20c extending in the vertical direction, and is composed of a right tube sheet 20a and a left tube sheet 20b. The left and right tube plates 20a, 20b are fixed by welding in the vertical direction in a state where the divided portions 20c of the left and right tube plates 20a, 20b are in contact with the outer surface of the partition plate 8. Since welding is performed before fixing the shell 7 as will be described later, the welding is performed from both sides of the tube sheet 20. Therefore, as shown in the figure, the weld line W2 is formed on both the front and back sides of the tube sheet 20.
Further, the connection between the shell 7 and the tube sheet 20 is a complete penetration welding performed from the outside of the shell, as indicated by a weld line W3 in FIG.
Further, as shown in FIG. 5C, a groove is provided at the ends of the left and right tube sheets 20a and 20b, and the partition plate 8 and the tube sheet 20 are connected by complete penetration welding as indicated by a weld line W4. It is good to do.
The other tube plate 21 (see FIGS. 2 and 3) has a similar fixing structure.

  FIG. 6 is a perspective view showing a state in which the tube plate 20 is fixed as shown in FIG. Thus, the front end 8 a of the partition plate 8 protrudes from the tube plate 20. Thus, the water chamber 10 (refer FIG.2 and FIG.3) is fixed to the front side of the tube plate 20 from which the front-end | tip 8a of the partition plate 8 protruded as shown in FIG.

As shown in FIG. 7, a slit SL is formed on the mating surface of the water chamber 10 to be welded to the tube plate 20, and the slit SL has a shape corresponding to the front end portion 8 a of the partition plate 8. ing. The water chamber 10 is fixed to the tube plate 20 by welding the tube plate 20 and the partition plate 8 along the mating surface of the water chamber 10 including the slit SL.
The water chamber partition plate 15 that partitions the inside of the water chamber 10 is welded in a state of being in contact with the end face of the tip 8 a of the partition plate 8. Alternatively, instead of welding, a packing may be sandwiched between the water chamber partition plate 15 and the partition plate 8 to fix the watertight.
Reference numeral 22 shown in the figure denotes a cold water supply nozzle that supplies cold water to the inlet water chamber 13, and reference numeral 23 denotes a cold water discharge nozzle that discharges cold water from the outlet water chamber 14.

  FIG. 8 shows a perspective view of the condenser 3. As shown in the figure, the partition plate 6 is inclined at a predetermined angle with respect to the vertical direction. The tube plates 30 and 31 are divided into two vertically by dividing portions 30c and 31c extending obliquely with respect to the vertical direction so as to correspond to the inclined partition plate 6, and the upper tube plates 30a and 31a and the lower side are divided. It consists of tube plates 30b and 31b. The upper and lower tube sheets 30 a, 30 b, 31 a, 31 b are fixed by performing welding in the vertical direction in a state where the divided portions 30 c, 31 c are in contact with the outer surface of the partition plate 6. Since the welding is performed before fixing the shell 5 similarly to the evaporator 4 shown in FIG. 5, the welding is performed from both the front and back sides of the tube sheet 30.

Next, the manufacturing method of the evaporator 4 mentioned above is demonstrated using FIG. In addition, although the manufacturing method of the condenser 3 is also different in that the shapes of the tube plates 30 and 31 are different, the others are the same.
First, the tube plates 20a, 20b, 21a, and 21b divided into left and right are welded to both ends of the partition plate 8.
Next, internal components such as the heat transfer tube support plate 34 are welded to the partition plate 8.
And the shell 7 divided into right and left by the longitudinal direction division | segmentation part 7a is welded with respect to the partition plate 8. As shown in FIG.
Finally, the water chamber 10 is welded to the tube plates 20a and 20b, and the water chamber 11 is welded to the tube plates 21a and 21b.

  FIG. 10 shows a manufacturing method of a conventional evaporator 4 'having a large size as a comparative example. In this manufacturing method, first, a partition plate 8 ′ is inserted into an endless cylindrical shell 7 ′, an operator enters the shell 7 ′, and the partition plate 8 ′ and the shell 7 ′ are welded. Next, internal parts such as the heat transfer tube support plate 34 ′ are brought into the shell 7 ′, and welding work is performed in the shell 7 ′. Then, the tube plates 20 ′ and 21 ′ are welded to both ends of the shell 7 ′. Finally, the water chambers 10 ′ and 11 ′ are welded to the tube plates 20 ′ and 21 ′.

As described above, according to the present embodiment, the following operational effects are obtained.
Since the shells 5 and 7 are not endless cylindrical bodies as in the comparative example of FIG. 10, but are divided by the longitudinal division parts 5a and 7a, the divided shells 5 and 7 are partitioned. What is necessary is just to fix each with respect to a board, and it is not necessary to enter into a shell and to perform fixing work like the case where the shell is made into the cylinder like the comparative example of FIG. Accordingly, the shells 5 and 7 that are so small that they cannot enter the cylindrical shell can be fixed to the partition plates 6 and 8, so that the shells 5 and 7 can be downsized. It becomes possible, and the condenser 3 and the evaporator 4 can be comprised compactly.
Further, since the tube sheets 20, 21, 30, 31 are divided, the size is smaller than that of the integrated tube sheet as in the comparative example of FIG. Thereby, storage, transportation work, and fixing work of the tube sheet are facilitated.

In this embodiment, as shown in FIG. 4, the shell divided into two parts is welded to the partition plate, but the shell may be divided into four parts as shown in FIG. 11. That is, as shown in FIG. 11A, four flat plates 7c, 7d, 7e, and 7f having grooves at both ends are welded to the partition plate 8, respectively. And as shown in FIG.11 (b), each flat plate 7c, 7d, 7e, 7f is bent in circular arc shape, and the free ends which are not welded are butt-welded.
In addition, as shown in FIG. 12, a gap is provided between the end portions of the longitudinally divided portions of the shells 7g and 7h divided into two, and overlay welding is performed on the end surface of the partition plate 8 so as to fill the gap. Good. Thereby, as shown to Fig.12 (a), comparatively wide welding line W1 'is formed.
As a modification of FIG. 12, as shown in FIG. 13, V-shaped grooves may be provided on both end faces of the partition plate 8.

  In FIG. 5, the left and right tube plates 20a and 20b are sandwiched and fixed to the partition plate 8. Instead, the shell 7 and the partition plate 8 are fixed as shown in FIG. 12 or FIG. In the case of welding, as shown in FIG. 14, the tube plate 20 may be divided into one piece without being divided, and the partition plate 8 and the shell 7 may be welded to the tube plate 20. With such a configuration, the workability of handling the tube sheet is reduced as compared with the case where it is divided into two, but the partition plate 8 does not protrude from the front side of the tube sheet 20 as shown in FIG. The water chambers 10 and 11 can be easily attached.

Next, the effect of the structure which has arrange | positioned the partition plate 6 of the condenser 3 inclining is demonstrated using FIG.
FIG. 4A shows the present embodiment, FIG. 4B shows Comparative Example 1, and FIG.
As shown in FIG. 15A, in the present embodiment, the partition plate 6 of the condenser 3 is inclined by a predetermined angle (for example, 30 ° to 45 °) with respect to the vertical direction. Thereby, the condensed liquid refrigerant L flows downward along the upper surface of the partition plate 6, and is stored in the liquid reservoir at the bottom of the refrigerant space of the No. A condenser 3a. The bottom of the refrigerant space of the No. A condenser 3a has a tapered cross-sectional shape because the partition plate 6 is inclined, whereby the liquid refrigerant is efficiently collected. Therefore, the liquid refrigerant can be easily taken out from the liquid refrigerant discharge pipe 3c. Further, since the volume of the liquid reservoir at the bottom can be reduced as a tapered cross-sectional shape, the space without the liquid refrigerant through which the heat transfer tube 9a (see FIG. 1) through which the cooling water flows can be made relatively large, and the heat transfer tube By arranging a large number of 9a, it is possible to provide the No. A condenser 3a having high heat exchange efficiency.
Moreover, since the inclination direction of the partition plate 6 is a direction toward the Unit A turbo compressor 1a, the refrigerant space of the Unit A condenser 3a located above the partition plate 6 approaches the Unit A turbo compressor 1a. It will be. Thereby, the discharge piping 1a-1 which connects the A machine compressor 1a and the refrigerant space of the A machine condenser 3a can be shortened, and pressure loss can be reduced. In the figure, reference numeral 1a-2 denotes a refrigerant suction pipe.

On the other hand, in the comparative example 1 shown in FIG. 15B, since the partition plate 6 is provided in the vertical direction, the refrigerant space of the Unit A condenser 3a is far from the Unit A turbo compressor 1a. Therefore, the discharge pipe 1a-1 becomes longer, and the pressure loss increases.
Moreover, in the comparative example 2 shown in FIG.15 (c), since the partition plate 6 is provided toward the horizontal direction, the length of the discharge piping 1a-1 is this embodiment shown to Fig.15 (a). However, the volume of the liquid pool at the bottom in the refrigerant space of the Unit A condenser 3a is increased. Therefore, the space through which the heat transfer tube for flowing the cooling water is inserted becomes relatively small, and the heat exchange efficiency cannot be increased as much as in the present embodiment.

In the above-described embodiment, the capacity of the two turbo refrigerators (No. A and No. B) has been described as being equivalent. However, the present invention is not limited to this and may have different capacities.
Moreover, although demonstrated using the turbo refrigerator as an example of a refrigerator, the refrigerator of another type may be sufficient if it is a refrigerator which comprises a double cycle.

3 Condenser (heat exchanger)
4 Evaporator (heat exchanger)
5, 7 Shells 5a, 7a Longitudinal dividing sections 6, 8 Partition plates 10, 11 Water chamber (heat exchange medium chamber)
20, 21, 30, 31 Tube sheet

Claims (6)

Used in a condenser and / or an evaporator of a double cycle refrigerator that combines a first refrigerator that constitutes a refrigeration cycle with a first refrigerant and a second refrigerator that constitutes a refrigeration cycle with a second refrigerant,
A shell that forms a refrigerant space inside;
A partition plate that partitions the refrigerant space in the shell into the first refrigerant and the second refrigerant;
A heat exchange medium chamber that is provided at an end of the shell and the partition plate and into which a heat exchange medium is introduced;
A tube plate for partitioning the heat exchange medium chamber and the refrigerant space in the shell and supporting a heat transfer tube through which the heat exchange medium flows;
A heat exchanger comprising:
The shell is divided by a longitudinal dividing portion extending in a longitudinal direction of the shell, and the longitudinal dividing portion is fixed to the partition plate.   The heat exchanger according to claim 1, wherein the tube sheet is divided by a dividing portion provided at a predetermined position, and the dividing portion is fixed to the partition plate.   The heat exchanger according to claim 1 or 2, wherein the partition plate is directed in a direction toward the first compressor of the first refrigerator or the second compressor of the second refrigerator.   The heat exchanger according to claim 3, wherein the partition plate is inclined at a predetermined angle with respect to a vertical direction.   A double-cycle refrigerator comprising the heat exchanger according to any one of claims 1 to 4. Used in a condenser and / or an evaporator of a double cycle refrigerator that combines a first refrigerator that constitutes a refrigeration cycle with a first refrigerant and a second refrigerator that constitutes a refrigeration cycle with a second refrigerant,
A shell that forms a refrigerant space inside;
A partition plate that partitions the refrigerant space in the shell into the first refrigerant and the second refrigerant;
A heat exchange medium chamber that is provided at an end of the shell and the partition plate and into which a heat exchange medium is introduced;
A tube plate for partitioning the heat exchange medium chamber and the refrigerant space in the shell and supporting a heat transfer tube through which the heat exchange medium flows;
A method of manufacturing a heat exchanger comprising:
A method for manufacturing a heat exchanger, characterized in that the longitudinally divided portion of the shell divided by the longitudinally divided portion extending in the longitudinal direction is fixed to the partition plate.

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