JP4030219B2 - Plate heat exchanger and solution heat exchanger using the same - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a plate heat exchanger, and more particularly to a plate heat exchanger useful as a solution heat exchanger for an absorption refrigeration machine, in which a plurality of heat exchangers are integrated.
[0002]
[Prior art]
Conventionally, multi-tube (baffle) heat exchangers are mainly used as solution heat exchangers for absorption refrigerators. Depending on the absorption cycle, low-temperature solution heat exchangers, high-temperature solution heat exchangers, exhaust heat are used. A plurality of heat exchangers such as a recovery heat exchanger are attached as components.
Moreover, these solution heat exchangers are each arrange | positioned as an independent heat exchanger, these are connected by piping, and it is comprised so that a predetermined function can be exhibited.
Since these are multi-tube heat exchangers and are individually installed by pipe connection, they have the following drawbacks.
(1) The amount of solution in the heat exchanger and in the piping is large and the starting characteristics are poor.
(2) Because the size and weight of the solution heat exchanger is large, it is difficult to reduce the size and weight and is expensive.
(3) Piping is complicated and takes time to manufacture.
(4) The structure is difficult to mass-produce.
[0003]
Further, even if these solution heat exchangers are configured as a plate type, if they are installed alone, it is necessary to connect the pipes outside, so that the pipes are complicated and expensive, and the space cannot be reduced.
In particular, in the case of the plate type, since the pressure loss tends to be larger than the multi-tube type, in order to maximize the heat transfer effect within the allowable pressure loss range limited in the absorption refrigeration cycle, A structure that minimizes pressure loss due to external piping is required.
[0004]
[Problems to be solved by the invention]
The present invention solves the above-described problems, and can be mass-produced at low cost with a small size and light weight, can easily change the flow path configuration, and uses a plate-type heat exchanger in which pressure loss is minimized. It is an object to provide a solution heat exchanger for an absorption refrigerator.
[0005]
[Means for Solving the Problems]
In order to solve the above-described problems, in the present invention, in a plate heat exchanger having an integrated structure in which the inside is divided into two units U1 and U2 by a partition wall, the partition wall divided into the two units U1 and U2 includes , Having two different fluid flow paths for performing heat exchange between the divided units, and one of the flow paths for performing the heat exchange flows from one inlet of the unit U1. After passing through the heat exchanging part of the unit U1, the unit U2 enters the unit U2 through one communication flow path of the partition wall, and one branchs through the heat exchanging part of the unit U2, It flows out from one outlet of the unit U2, and the other is formed so as to flow out from another outlet without passing through the heat exchange part of the unit U2. The road is one of units U2 And then passes through the heat exchange section of the unit U2 and then enters the unit U1 through the other communication channel of the partition wall, where it merges with another fluid introduced from the other inlet of the unit U1. The plate heat exchanger is formed so as to flow out from one outlet of the unit U1 through the heat exchange part of the unit U1.
Further, in the present invention, in the plate heat exchanger having an integrated structure in which the inside is divided into two units U1 and U2 by the partition wall, the partition wall divided into the two units U1 and U2 includes a space between the divided units. The flow path of one of the flow paths for performing heat exchange flows from one inlet of the unit U1 and branches there. One passes through the heat exchange part of the unit U1 and flows out from one outlet of the unit U1, and the other passes through one communication channel of the partition without passing through the heat exchange part of the unit U1. The unit U2 enters the unit U2, passes through the heat exchange part of the unit U2, and flows out from one outlet of the unit U2. Another fluid channel of the channel for performing the heat exchange is the unit U1. U2 each different Another fluid that has flowed in through the mouth and passed through the heat exchange sections of the units U1 and U2 and passed through the heat exchange section of the unit U2 passes through the other communication flow path of the partition wall, The plate-type heat exchanger is characterized in that it is formed so as to merge with another fluid that has passed through the exchange section and to flow out from the other outlet of the unit U1.
[0006]
In the present invention, in the solution heat exchanger that performs heat exchange between the concentrated solution and the dilute solution of the absorption refrigerator, the plate-type heat exchanger described above is used as the heat exchanger. In the solution heat exchanger that performs heat exchange between the concentrated solution of the absorption refrigerator and the exhaust heat and the diluted solution, the plate heat exchanger described above is used as the heat exchanger.
The absorption refrigerator is a multi-effect absorption refrigerator, and a concentrated solution and / or a diluted solution can each form a plurality of flow paths.
[0007]
DETAILED DESCRIPTION OF THE INVENTION
Next, the present invention will be described in detail with reference to the drawings.
Figure 1 is a general block diagram showing a reference example of Plate-type heat exchanger, (a) represents a front sectional view, (b) a plan view seen from the top, (c) is a plan view from below It is.
In FIG. 1, H ₁ and H ₂ are heat exchangers, P is a plate, B is a partition, and a ₁ to ₄ and b ₁ to ₄ are an inlet nozzle and an outlet nozzle for the fluid to be heated and the heating fluid, respectively. 1a, 2a and 1b, 2b indicate the flow of the fluid to be heated and the fluid for heating, respectively.
In FIG. 1, an upper unit 1U ₁ and a lower unit 2U ₂ are divided by a partition wall B. Independent heat exchangers H ₁ and H ₂ are integrally formed. As for the structure of the partition wall B, when the pressure difference between the unit 1U ₁ and the unit 2U ₂ is small, the basic shapes of the plates P constituting the plate heat exchangers H ₁ and H ₂ are exactly the same, and the fluid 1a and fluid 1b ( Alternatively, it is possible to employ a closed plate P without a flow path through which the fluid 2a and fluid 2b) flow. Further, when the pressure difference is large, the partition wall B may have a thickness necessary for strength.
[0008]
Further, the partition wall can be made into an airtight space in a vacuum state by using a plurality of plates, for example, to form a vacuum heat insulating layer, and heat loss between the heat exchangers H ₁ and H ₂ can be reduced. Furthermore, when using multiple passes, a vacuum heat insulating layer may be provided in the passes.
Unit 1U ₁ definitive fluid 1a (indicated by the solid line) leaves the nozzle a ₂ enters from the nozzle a _1. On the other hand (shown in phantom) fluid 1b exits from the nozzle b ₂ enters from the nozzle b _1. The fluid 1a and the fluid 1b flow alternately to exchange heat.
Similar to the flow even unit 1U ₁ unit 2U _2, fluid 2a (solid line) exits from the nozzle a ₄ enters the nozzle a _3, fluid 2b (dashed line) exits from the nozzle b ₄ enters the nozzle b _3, a fluid Heat exchange is performed between 2a and fluid 2b.
FIG. 1 shows an integration of two independent heat exchangers.
[0009]
Next, FIG. 2 shows the overall configuration diagram of an example of a plate heat exchanger of the present invention, (a) is a front sectional view, (b) is a plan view from above, from below (c) FIG.
In FIG. 2, the upper unit 1U ₁ and the lower unit 2U ₂ are divided by a partition wall B having flow paths c ₁ and d ₁ .
The unit 1U ₁ has three nozzles a ₁ , b ₁ , and b ₂ , and the unit 2U ₂ also has three nozzles a ₂ , b ₃ , and a ₄ . Further, the partition wall B is provided with flow paths that communicate between the units at two positions, a position c ₁ corresponding to the nozzle a ₂ and a position d ₁ corresponding to the nozzle b ₁ .
[0010]
When this is applied to the solution heat exchanger of the absorption refrigerator, the dilute solution 1a + 2a from the absorber enters from the nozzle a ₁ and flows between the plates in the unit 1U ₁ (low temperature solution heat exchanger), and the partition wall B Enters the unit 2U ₂ (high-temperature solution heat exchanger) from the communication channel c ₁ of the unit, part 2a flows between the plates in the unit 2U ₂ , exits from the nozzle a ₄ and flows to the high-temperature regenerator. . On the other hand, a part 1a of the dilute solution entering from the communication channel c ₁ flows out from the nozzle a _{2 as it is} and flows to the low temperature regenerator.
Return solution 2b from the high temperature regenerator, enters the nozzle b ₃ units 2U _2, and flows from the communication passage d ₁ of the partition wall B into the unit 1U ₁ flows between the plates in the unit 2U _2, the low-temperature regenerator return the solution 1b (coming from the nozzle b ₁ unit 1U ₁₎ and joined, it flows out of the nozzle b ₂ flows between the plates of the unit 1U ₁ go back again to the absorber.
[0011]
In this way, a compact heat absorption heat exchanger for absorption refrigerators that performs heat exchange between the low temperature dilute solution 1a + 2a and the high temperature concentrated solution (the return solution from the low temperature regenerator 1b or the high temperature regenerator 2b) is provided. It is materialized.
If it carries out like FIG. 2, a pipe joint will be six places, but when it arrange | positions independently like the past, a pipe joint will be eight places.
Here, in order to simplify the description of both the low-temperature solution heat exchanger and the high-temperature solution heat exchanger, the flow path configuration is one path, but of course, a plurality of paths may be used.
It is also possible to provide a flow rate adjusting mechanism (orifice OL or the like) at the nozzle a ₂ portion in order to adjust the flow distribution of the dilute solution (low temperature regenerator side and high temperature regenerator side) at the inlet portion of the unit 2U _2. .
In FIG. 2, the reference numerals a and c indicate the flow and nozzle of the dilute solution, and the reference numerals b and d indicate the flow and nozzle of the concentrated solution. The same applies to FIG.
[0012]
FIG. 3 shows an overall configuration diagram of another example of the plate heat exchanger of the present invention, where (a) is a front sectional view, (b) is a plan view seen from above, and (c) is seen from below. It is a top view.
In Figure 3, by a partition wall B having a flow path c _2, d _2, it is divided into an upper unit 1U ₁ and a lower unit 2U _2.
The unit 1U ₁ has four nozzles a ₁ , a ₂ , b ₁ , and b ₂ , and the unit 2U ₂ has two nozzles b ₃ and a ₄ . Further, the partition wall B is provided with flow paths that communicate between the units at two positions, a position c ₂ corresponding to the nozzle a ₁ and a position d ₂ corresponding to the nozzle b ₂ .
Explaining this by applying it to the solution heat exchanger of the absorption refrigerator, the dilute solution 1a + 2a from the absorber enters the unit 1U ₁ (low temperature solution heat exchanger) from the nozzle a ₁ , and part of it is a plate of the unit 1U ₁ It flows out from the nozzle a ₂ and flows to the low temperature regenerator.
[0013]
Part of the dilute solution 1a + 2a flowing into the unit 1U ₁ enters the unit 2U ₂ through the communication channel c ₂ of the partition wall B, flows between the plates, exits the nozzle a ₄ and flows to the high-temperature regenerator. .
Return solution 2b from the high temperature regenerator, enters the nozzle b ₃ units 2U _2, and flows between the plates of the unit 2U _2, and flows into the unit 1U ₁ through the communication passage d ₂ of the partition wall B, the low temperature joins the return solution 1b from vessel (coming from the nozzle b ₁ unit 1U _1), flows directly from the nozzle b _2, go back again to the absorber.
Further, by adding the nozzle a ₃ units 2U ₂ (shown in dashed line), it is also possible to introduce a solution 2c of other strains in the unit 2U _2.
[0014]
In this way, a heat exchanger for absorption refrigerators that is compact and has few pipes, performs heat exchange between the low temperature dilute solution 1a + 2a and the high temperature concentrated solution (return solution from the low temperature regenerator 1b or the high temperature regenerator 2b). Is materialized.
If it carries out like FIG. 3, a pipe joint will be six places, but when it arrange | positions independently like the past, a pipe joint will be eight places.
In FIG. 3, both the low-temperature solution heat exchanger and the high-temperature solution heat exchanger have a single flow path configuration for the sake of simplicity of explanation.
In order to adjust the flow rate distribution of the dilute solution 1a + 2a at the inlet portion of the unit 1U ₁ (the low-temperature regenerator side 1a and the high-temperature regenerator side 2a), the flow rate adjustment mechanism to the nozzle a ₂ parts similarly to FIG. 2 (orifice or the like ) Can also be made (not shown).
[0015]
In FIG. 4, the flow block diagram of the double effect absorption cold / hot water machine which applies this invention is shown.
In FIG. 4, A is an absorber, GL is a low temperature regenerator, GH is a high temperature regenerator, C is a condenser, E is an evaporator, HL is a low temperature heat exchanger, HH is a high temperature heat exchanger, SP is a solution pump, RP is a refrigerant pump, 1-7 are solution flow paths, 8-11 are refrigerant flow paths, and 12 is a cooling water flow path.
In the cooling operation of this apparatus, the dilute solution that has absorbed the refrigerant flows from the absorber A by the solution pump SP through the heated side of the low-temperature heat exchanger HL, and partly flows through the heated side of the high-temperature heat exchanger HH. It is introduced from the path 2 into the high temperature regenerator GH. In the high-temperature regenerator GH, the dilute solution is heated from the heating heat source 13 to evaporate the refrigerant and concentrated, and the concentrated solution passes through the flow path 3 and is heat-exchanged in the high-temperature heat exchanger HH. The solution is combined and introduced into the absorber A from the flow path 7 through the low-temperature heat exchanger HL.
[0016]
On the other hand, the remaining part of the dilute solution that has passed through the low temperature solution heat exchanger HL and branched to the high temperature regenerator GH is introduced into the low temperature regenerator GL. In the low-temperature regenerator, after being heated and concentrated by the refrigerant vapor from the high-temperature regenerator, it is combined with the concentrated solution from the high-temperature regenerator in the flow path 5, passes through the heating side of the low-temperature heat exchanger HL, and is absorbed from the flow path 7. Introduced into vessel A.
The refrigerant gas evaporated in the high temperature regenerator GH passes through the refrigerant flow path 8, is used as a heat source for the low temperature regenerator GL, and is then introduced into the condenser C. In the condenser C, it is cooled by the cooling water 12 and condensed together with the refrigerant gas from the low temperature regenerator GL. The condensed refrigerant liquid enters the evaporator E from the flow path 9. In the evaporator E, the refrigerant is circulated by the refrigerant pump RP and the flow paths 10 and 11 to evaporate. At that time, evaporative heat is taken from the cold water 14 on the load side, the cold water 14 is cooled, and is supplied to the cooling.
[0017]
The evaporated refrigerant is absorbed by the concentrated solution in the absorber A to become a dilute solution and circulates in the solution pump SP.
In Figure 4, the bypass pipe 15 and 16 is a pipe for use with this absorption chiller for heating, during heating operation, the open Hiyadansetsu valve V _1, V _2, the high-temperature regenerator steam To the A / E (absorber / evaporator) can body and heat the hot water 14 passing through the evaporator tube. Here, the refrigerant vapor condenses and becomes drain (refrigerant liquid), but can also be used for heating by returning the refrigerant liquid to the dilute solution circulation system through V ₂ .
In the absorption chiller / heater of FIG. 4, the plate heat exchanger of the present invention is used for the solution heat exchanger (low temperature HL, high temperature HH). The absorption chiller / heater of FIG. 4 is a branch flow in which the dilute solution 1 branches and flows into the low temperature regenerator GL and the high temperature solution heat exchanger HH after leaving the low temperature solution heat exchanger HL. A heat exchanger can be applied.
[0018]
In comparison to FIG. 2 and FIG. 4, the heat exchanger HL in FIG. 4, HH corresponds to H _1, H _2, respectively, in FIG 2, a ₁ in the Figure each flow path 1,2,4 of Figure 4 2, It corresponds to a ₄ and a ₂ , and the flow paths ₃ , ₅ , ₆ and 7 correspond to b ₃ , b ₁ , d ₁ and b ₂ in FIG.
FIG. 5 is an explanatory view showing various arrangements of the solution heat exchanger (low temperature, high temperature) and the exhaust heat recovery heat exchanger and the solution flow. In the present invention, the plate surrounded by the broken line is integrated. It is a type heat exchanger.
FIG. 5A shows that the low temperature solution heat exchanger HL and the high temperature solution heat exchanger HH are arranged in series, and after exiting the low temperature solution heat exchanger HL, the dilute solution is connected to the low temperature regenerator GL side and the high temperature solution heat. This is a case where the flow branches and flows to the exchanger HH, and is embodied in the plate heat exchanger of FIG.
[0019]
FIG. 5B shows a case where the low-temperature solution heat exchanger HL and the high-temperature solution heat exchanger HH are arranged in parallel and the dilute solution flows in parallel to each other, which is embodied in FIG. 3 in parallel flow.
FIG. 5 (c) shows a low temperature solution heat exchanger HL, an exhaust heat recovery heat exchanger HO, and a high temperature solution heat exchanger HH arranged in series, and the low temperature regeneration after the dilute solution exits the exhaust heat recovery heat exchanger HO. This is a case of branching flow to the vessel side GL and the high temperature solution heat exchanger HH side.
Here, the exhaust heat recovery heat exchanger HO is a drain heat exchanger that recovers heat from the steam drain when steam is used as a heating source, and heat from hot water recovered from the engine and various exhaust heat to the refrigeration cycle. Collectively refers to heat exchangers for recovery.
[0020]
FIG. 6 shows a general schematic diagram for explaining the flow of the plate heat exchanger.
A low-temperature fluid and a high-temperature fluid flow alternately between the stacked plates P to exchange heat between the plates. Each plate P has four flow holes for the entrance and exit of fluid 1a and fluid 1b.
FIG. 7 shows a general schematic diagram of a cross-sectional structure with respect to FIG.
The cross-sectional view is that of the inlet / outlet nozzle portion of the fluid a and flows through the flow path a.
Fluid a enters through nozzle a ₁ and exits through the flow path of the plate heat exchanger to the opposite nozzle a ₂ . Further, the outlet of the fluid a can be the nozzle b ₁ .
On the other hand, the fluid 1b enters from the nozzle b _1, it passes through the flow path b of the plate heat exchanger enters the nozzle b ₂ on the opposite side. Further, the outlet of the fluid b ₂ can be the nozzle a ₁ .
[0021]
【The invention's effect】
According to the present invention, the following effects can be achieved.
(1) By using a plate heat exchanger, the amount of solution can be reduced and mass production can be achieved at low cost.
(2) By integrating a plurality of solution heat exchangers via the partition walls, higher functionality can be achieved, piping can be facilitated, and a significant reduction in size and weight can be achieved.
(3) A free flow path configuration (absorption cycle) is possible by changing the structure of the partition wall according to the function and purpose of the heat exchanger. In other words, the flow path configuration of the partition wall can freely cope with solution flows such as a branch flow, a parallel flow, and a series flow.
(4) The partition wall has the same structure as the plate constituting the plate heat exchanger, and can be dealt with by changing only the configuration of the flow path, so that mass production is possible at low cost.
[Brief description of the drawings]
[1] a whole configuration diagram showing a reference example of Plate-type heat exchanger, (a) represents a front sectional view, (b) a plan view seen from the top, (c) is a plan view from below.
FIG. 2 is an overall configuration diagram showing an example of a plate heat exchanger according to the present invention, where (a) is a front sectional view, (b) is a plan view seen from above, and (c) is a plan view seen from below. Figure.
FIG. 3 is an overall configuration diagram showing another example of the plate heat exchanger of the present invention, where (a) is a front sectional view, (b) is a plan view seen from above, and (c) is seen from below. Plan view.
FIG. 4 is a flow configuration diagram of a double-effect absorption chiller / heater to which the present invention is applied.
FIG. 5 is an explanatory diagram of various systems of a heat exchanger to which the present invention is applied and a solution flow.
FIG. 6 is a schematic diagram for explaining the flow of a plate heat exchanger.
7 is a schematic diagram illustrating a cross-sectional structure of FIG.

Claims (3)

  In the plate heat exchanger having an integrated structure in which the inside is divided into two units U1 and U2 by a partition wall, the partition wall divided into the two units U1 and U2 performs heat exchange to communicate between the divided units. There are two different fluid flow paths to be performed, and one of the flow paths to perform the heat exchange flows from one inlet of the unit U1 and passes through the heat exchange section of the unit U1. After that, the unit U2 enters the unit U2 through one communication channel of the partition wall, branches there, one flows through the heat exchange part of the unit U2, flows out from one outlet of the unit U2, and the other Is formed so as to flow out from another outlet without passing through the heat exchanging portion of the unit U2, and another fluid flow path for the heat exchange flows from one inlet of the unit U2. Heat exchange of the unit U2 And then enters the unit U1 through the other communication channel of the partition wall, where it merges with another fluid introduced from the other inlet of the unit U1 and passes through the heat exchange part of the unit U1. It forms so that it may flow out from one exit of U1, The plate type heat exchanger characterized by the above-mentioned.   In the plate heat exchanger having an integrated structure in which the inside is divided into two units U1 and U2 by a partition wall, the partition wall divided into the two units U1 and U2 performs heat exchange to communicate between the divided units. One of the flow paths for performing the heat exchange has two different fluid flow paths to perform, and flows from one inlet of the unit U1 and branches there. Through the heat exchanging part of the unit U1 and out of one outlet of the unit U1, and the other enters the unit U2 through one communication channel of the partition without passing through the heat exchanging part of the unit U1. It is formed so that it passes through the heat exchange part of the unit U2 and flows out from one outlet of the unit U2, and another fluid channel of the channel for performing the heat exchange is provided for each of the units U1 and U2. Flowing in from the inlet The other fluid that has passed through the respective heat exchange portions of the knits U1 and U2 and passed through the heat exchange portion of the unit U2 passes through the other communication flow path of the partition wall and passes through the heat exchange portion of the unit U1. The plate-type heat exchanger is formed so as to flow out from the other outlet of the unit U1 by joining with another fluid.   A solution heat exchanger for performing heat exchange between a concentrated solution and a dilute solution in an absorption refrigerator, wherein the heat exchanger is the plate heat exchanger according to claim 1 or 2, wherein the heat exchanger is 1 A solution heat exchanger for an absorption refrigerator, wherein one fluid channel is a dilute solution channel and another fluid channel is a concentrated solution channel.

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