JP2003287321A - Plate type heat exchanger, and refrigerating machine having the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain the high heat exchange performance by unifying the vapor- liquid distribution between passes as much as possible in a plate type heat exchanger. <P>SOLUTION: In the plate type heat exchanger for forming a plurality of passes in the layer direction by laminating a plurality of heat transfer plates 3 with first flow passages 4 and second flow passages 5 in an alternately forming manner, and distributing a first medium R<SB>1</SB>to be phase-changed between the vapor and liquid phases in the rising direction in passes 12a-12l on the first flow passage 4 side, and a divider 21 is provided on the upstream side of an inlet side merging part 6 of the passes 12a-12l. In this configuration, even when the first medium R<SB>1</SB>flows into the plate type heat exchanger in the vapor-liquid phase state, the first medium R<SB>1</SB>is divided to keep similar vapor-liquid state before the first medium flows into the inlet side merging part 6, and flows in this divided state. The vapor-liquid distribution in each of the passes 12a-12l is unified as much as possible, and the heat exchange performance of the entire plate type heat exchanger is improved. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate heat exchanger and a refrigeration system equipped with the plate heat exchanger.

[0002]

28 and 29 show a conventional general plate heat exchanger Z. This heat exchanger Z is
For example, a plurality of heat transfer plates 3, 3, ... Forming the entire surface of a stainless plate material in a concavo-convex shape and forming openings of a predetermined size in the vicinity of the four corners thereof are adjacent to each other. Of the heat transfer plate 3 and the protrusions of the other heat transfer plate 3 are sequentially laminated so as to abut against each other, and the first flow path 4 and the second flow path 4 extending vertically between the heat transfer plates 3, 3 ,. The flow paths 5 are formed alternately, and the side plates 1, 3 are respectively provided at both ends of the heat transfer plates 3, 3 ,.
2 is attached and sandwiched, and these are integrated.

In this heat exchanger Z, the respective openings of the heat transfer plates 3, 3, ... Are respectively overlapped to form four collecting portions 6, 7, 19, 20 which are continuous in the stacking direction. At the same time, among the gathering portions 6, 7, 19, and 20, the gathering portion 6 (hereinafter, referred to as the inlet-side gathering portion 6) and the gathering portion 7 (hereinafter,
The outlet side collecting portion 7) means the heat transfer plates 3,
An inlet provided on the side plate 1 while communicating with each other through a plurality of paths 12, 12, ... Composed of the respective first flow paths 4, 4 ,. 8 and the outlet 9, respectively. Further, the inlet-side collecting portion 19 and the outlet-side collecting portion 20 which are vertically arranged on the other side in the left-right direction are provided with the second flow paths 5 formed between the heat transfer plates 3, 3 ,. , 5, ... Each of which communicates with each other through a plurality of paths (not shown) formed respectively, and faces the inflow port 19 and the outflow port 20 provided in the side plate 1.

Then, from the inlet 8 to the inlet side assembly
The first medium R flowing into the portion 6₁Of the inlet side collecting section 6
Pass through each of the above-mentioned paths 12, 12, ...
Rises and flows into the exit side gathering part 7, and then joins here.
Then, it flows out from the outlet 9. In addition, the inlet 1
The second medium R flowing from 0 into the inlet side collecting portion 19 ₂
Are the above-mentioned parts arranged in a row in the axial direction of the inlet side collecting portion 19.
After descending through the space and flowing into the outlet side collecting portion 11,
Here, they merge and flow out from the outlet 20. This
From the inlet side collecting part 6 to the outlet side collecting part 7
The first medium that ascends and flows through each of the paths 12, 12, ...
Body R₁And from the inlet side gathering portion 19 to the outlet side gathering portion
The second medium R that descends and flows through the above paths toward 20₂
Heat is exchanged between the and (see FIG. 29).

[0005]

By the way, when such a conventional plate heat exchanger is used as an evaporator of a refrigerating apparatus, the first medium R ₁ has a property that it does not cause a phase change. There is no problem as long as it is a single phase or gas single phase that flows into the inflow port 8 side, but the first medium R ₁ has a property of undergoing a phase change between a liquid phase and a gas phase, For example, in the case of a CFC refrigerant, the following problems will occur.

Namely, using the heat exchanger Z as an evaporator, and the case of adopting the chlorofluorocarbon refrigerant as a first medium R ₁ of the primary side, the first medium R _1, after exiting the condenser, the expansion valve Since it is introduced into the plate-type heat exchanger Z side while being decompressed in the above, as shown in FIG. 29, at the inflow port 8 of the heat exchanger Z, the first medium R ₁ is mixed with gas-liquid. It will flow in a two-phase state.

When the first medium R ₁ flows in the gas-liquid two-phase state from the inflow port 8 into the inlet side collecting portion 6 as described above, depending on conditions such as the flow rate of the first medium R ₁ , The liquid refrigerant may flow to the inner side of the inlet side collecting section 6 (that is, the inner side in the stacking direction of the heat exchanger Z), or conversely, the gas refrigerant may flow to the inner side of the inlet side collecting section 6. . Specifically, when the flow rate of the refrigerant is high, the liquid refrigerant is unevenly present on the inlet side of the inlet side collecting portion 6 and the gas refrigerant is biased on the inner side (the distribution state of this liquid refrigerant is shown in FIG. Curve L ₁
Is shown). On the other hand, when the flow rate of the refrigerant is small, the gas refrigerant is unevenly distributed on the inlet side of the inlet side collecting portion 6, and the liquid refrigerant is unevenly distributed on the inner side.

The uneven distribution of the liquid refrigerant and the gas refrigerant is caused in the stacking direction of the heat transfer plates 3, 3, ... In the heat exchanger Z, that is, in the direction in which the paths 12, 12 ,. This directly leads to non-uniform distribution of gas-liquid of the refrigerant, resulting in an extreme decrease in heat exchange performance. Therefore, the development of a technique for improving this is desired, but the actual situation is that an effective means has not been proposed yet.

Therefore, in the present invention, in the plate type heat exchanger in which a plurality of paths are formed in the stacking direction of the heat transfer plates, gas-liquid distribution between the paths is made as uniform as possible, and thus high heat exchange performance is achieved. The main purpose is to obtain.

[0010]

In the present invention, the following constitution is adopted as a concrete means for solving such a problem.

(A) First Invention of the Present Application In the first invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
The plate-type heat exchanger configured to perform heat exchange between and is characterized in that a flow divider 21 is provided on the upstream side of the inlet side collecting portion 6 of each of the paths 12a to 12l.

With such a structure, for example, the plate heat exchanger is used as an evaporator, and the first medium R ₁ flows into the plate heat exchanger side in a gas-liquid two-phase state. Even in the state, before the first medium R ₁ flows into the inlet side collecting portion 6 of the plate heat exchanger, the first medium R ₁ is divided in the flow divider 21 so as to have the same gas-liquid state, In this divided flow state, the gas flows into the inlet side collecting portion 6, so that, for example, compared to the case where the entire amount of the first medium R ₁ is directly flowed into the inlet side collecting portion 6 without being divided, The gas-liquid distribution of the first medium R ₁ in each of the paths 12a to 12l is made as uniform as possible, and as a result, the heat exchange performance of the plate-type heat exchanger as a whole is improved.

(B) Second Invention of the Present Invention In the second invention of the present application, in the plate heat exchanger according to the first invention, a plurality of branch pipes 22 to 25 are provided downstream of the flow divider 21. 31 to 42 are provided, and each branch pipe 2
It is characterized in that the outlet ends of 2 to 25 and 31 to 42 are located at predetermined intervals in the direction in which the paths 12a to 12l are arranged in the inlet side collecting portion 6.

According to this structure, the branch pipes 22-2 are provided.
Corresponding to the positions of the outlet ends of 5, 31 to 42, the paths 12a to 12l are virtually the branch pipes 22 to 25, 31.
To 42 are divided into path groups 13A to 13D each of which is formed by collecting a plurality of paths located in the vicinity of each exit end.

As a result, the first medium R ₁ in the gas-liquid two-phase state divided in the flow divider 21 is divided into the branch pipes 22.
25 to 31 to 42, these are intensively flown into each of the corresponding plurality of path groups 13A to 13D, and the first medium in the stacking direction when viewed as the whole plate heat exchanger. The gas-liquid distribution of R ₁ is made uniform by, for example, the branch pipes 22 to 25, 31
Compared with the case where the configuration does not include 42, it is more reliable, and accordingly, further improvement of the heat exchange performance of the plate heat exchanger as a whole can be expected.

(C) Third Invention of the Present Invention In the third invention of the present application, in the plate heat exchanger according to the second invention, each of the branch pipes 22 to 25, 31 is provided.
It is characterized in that the outlet ends of ~ 42 are directed upward or downward.

According to this structure, for example, when the outlet ends of the branch pipes 22 to 25, 31 to 42 are directed upward, the outlet ends of the branch pipes 22 to 25, 31 to 42 are Since the first medium R ₁ can be accurately flowed into each path belonging to the corresponding path group, the gas-liquid distribution of the first medium R ₁ in the stacking direction can be made uniform in the plate heat exchanger as a whole. Is further ensured, and further improvement in heat exchange performance of the plate-type heat exchanger as a whole can be expected.

Further, each of the branch pipes 22 to 25, 31 to 4
When the outlet ends of the two are directed downward, the first medium R ₁ in the gas-liquid two-phase state flowing out from each of the outlet ends of the first flow path 4 constituting each of the paths 12a to 12l. After colliding with the lower end and being gas-liquid mixed, it rises and the respective outlet ends flow into the respective paths belonging to the corresponding path groups 13A to 13D and ascend there, and the respective path groups 13A to 13D. It is possible to further promote the uniformization of gas-liquid distribution between the paths belonging to the above, and it is expected that the heat exchange performance of the entire plate heat exchanger will be further improved.

(D) Fourth invention of the present application In the fourth invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
In the plate heat exchanger configured to perform heat exchange between the plurality of branch pipes 22, 23, 2 on the medium upstream side of the inlet side collecting portion 6 of each of the paths 12a to 12l.
4, 25 are provided in multiple stages in the vertical direction, and each of the branch pipes 22 to 2
The outlet ends of 5, 31 to 42 are located at predetermined intervals in the direction in which the paths 12a to 12l are arranged in the inlet side collecting portion 6.

According to this structure, for example, the first medium R ₁
Of the branch pipes 22 to 25, 31 to 42, when the flow rate of the branch pipes 22 to 25 and 31 to 42 is small and the liquid medium is normally used in a state where a large amount of liquid medium flows to the inner side of the inlet side collecting portion 6. The upper end side branch pipe is set such that the outlet end thereof is located on the inner side of the inlet side collecting portion 6, so that the gas medium is positively supplied from the upper side branch pipe to the inner side. It is possible to increase the amount of gas medium in the path located on the far side of the paths 12a to 12l. On the contrary, the first medium R ₁
Of the branch pipes 22 to 25, 31 to 42 when the gas flow rate is high and the gas medium normally flows in the inner side of the inlet side collecting portion 6 in a large amount. By setting the outlet end of the lower branch pipe toward the inner side of the inlet side collecting portion 6, the lower branch pipe positively supplies the liquid medium to the inner side. Pass 1
It is possible to increase the amount of the liquid medium in the path located on the far side of 2a to 12l.

As a result, in any of the above cases, the gas-liquid distribution of the first medium R ₁ in the stacking direction of the plate heat exchanger is made uniform, and the heat exchange performance of the plate heat exchanger is improved. Can be expected to improve.

(E) Fifth Invention of the Present Invention In the fifth invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
In a plate heat exchanger configured to perform heat exchange between the first medium R _{1 and} the paths 12 of the first medium R ₁ flowing into the inlet side collecting portion 6 in the plate side heat exchanger.
Flow rate adjusting member 16 for adjusting the inflow rate to the a to 12l side
It is characterized by the provision of.

According to this configuration, for example, the first medium R
_When the flow rate of ₁ is small and the liquid medium flows to the inner side of the inlet side collecting portion 6 in a large amount, the flow rate adjusting member 16 adjusts the flow rate of the liquid medium of the first medium R _1. In the case of use conditions in which the inflow of the liquid medium to the back side is suppressed, and conversely, the inflow flow rate of the first medium R ₁ is large and a large amount of the gas medium flows to the back side of the inlet side collecting portion 6. Is the first medium R ₁ by the flow rate adjusting member 16.
Of these, the flow rate of the gas medium is adjusted to suppress the inflow of the gas medium to the inner side, and as a result of these, the paths 12a to 1
The gas-liquid distribution of the first medium R ₁ flowing into the 2l is made as uniform as possible, and the heat exchange performance of the plate heat exchanger can be expected to be improved accordingly.

(F) Sixth Invention of the Present Application In the sixth invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
In a plate heat exchanger configured to perform heat exchange between the inlet side collecting portion 6 and the first medium R ₁ flowing from the inlet side to the back side of the inlet side collecting portion 6. After this, the flow direction control members 45 and 47 for controlling the flow direction so as to flow from the inner side to the inner side are further provided.

According to this structure, the inlet side collecting portion 6 is provided.
When the first medium R ₁ flows into the inside in a gas-liquid two-phase state,
A part of the first medium R ₁ is first of all the inlet side collecting portion 6
Each of the above paths 12 on the way from the entrance side to the back side of
a to 12l side, and a part of the other part is distributed to each of the paths 12 on the way from the back side to the entrance side.
Since it is distributed to each of a to 12 l, even under a use condition in which a large amount of liquid medium flows to the inner side of the inlet side collecting portion 6, conversely, a large amount of gas medium exists to the inner side of the inlet side collecting portion 6. Even under a flowing use condition, the medium distribution on the outward path and the medium distribution on the return path overlap each other, so that the entire area from the inlet side to the inner side of the inlet side collecting portion 6 (that is, each of the paths 12a to 12l). (In all cases), the gas-liquid distribution of the first medium R ₁ is made as uniform as possible, and the heat exchange performance of the plate heat exchanger can be expected to be improved accordingly.

(G) Seventh Invention of the Present Invention In the seventh invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
In the plate heat exchanger configured to perform heat exchange between the inlet side collecting portion 6 and the refrigerant inlet pipe 53, the outlet end of the refrigerant inlet pipe 53 is located deep inside the inlet side collecting portion 6. It is characterized in that it is inserted and arranged from the entrance side of.

According to this structure, the refrigerant inlet pipe 53 is formed.
When the first medium R ₁ is introduced into the inlet side collecting portion 6 through, because the outlet end of the refrigerant inlet pipe 53 is positioned in the back portion of the inlet-side collecting portion 6, the first medium R ₁ The gas medium is always positively introduced into the inner part regardless of the flow rate of the gas. Therefore, in the paths 12k and 12l corresponding to the inner part, the heat exchange performance deteriorates due to the concentrated inflow of the gas medium, but the other paths 12
In a to 12j, since the liquid medium flows in a state close to the liquid single phase, the gas-liquid distribution of the first medium R ₁ between the paths 12a to 12J is made as uniform as possible, and high heat exchange performance is realized. To be done. Moreover, the path 12 through which the gas medium flows in
The ratio of k and 12l in all the paths 12a to 12l is small, and this has a small effect on the heat exchange performance. As a result of these synergistic effects, higher heat exchange performance can be obtained for the plate heat exchanger as a whole.

(H) Eighth invention of the present application In the eighth invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
Comprising a plate heat exchanger Z _16, Z ₁₇ configured as to perform heat exchange between the, the plate type heat exchanger Z _16,
In the refrigerating apparatus in which Z ₁₇ is used as an evaporator, the plate type heat exchangers Z ₁₆ and Z _{17 are provided} on the upstream side,
It is characterized in that cooling means 64, 66 for cooling the first medium R ₁ before expansion by the expansion means 63 are provided.

According to this structure, the first medium R ₁ is decompressed in the expansion means 63 while being supercooled by the cooling means 64 and 66, so that the gas in the first medium R ₁ after decompression is reduced. The generation amount of the medium is reduced as much as possible, and the first medium R ₁ is provided on the heat exchanger Z ₁₆ and Z ₁₇ side.
Will flow in as close to the liquid single phase as possible. As a result, even if a special gas-liquid distribution promoting mechanism is not provided on the plate heat exchangers Z ₁₆ and Z ₁₇ side, the gas-liquid distribution to the paths 12a to 12l of the first medium R ₁ can be made uniform. It is realized that the heat exchange performance of the plate heat exchangers Z ₁₆ and Z ₁₇ is improved, and further, the performance improvement of the refrigerating apparatus including the plate heat exchangers Z ₁₆ and Z ₁₇ can be expected. It is a thing.

(I) Ninth Invention of the Present Application In the ninth invention of the present application, a plurality of heat transfer plates 3, 3,
.. are laminated so that the first flow paths 4 and the second flow paths 5 are alternately formed between the heat transfer plates 3, 3 ,. A plurality of paths are formed in the layer direction, and the first medium R ₁ that changes in phase between gas and liquid two phases is circulated in the ascending direction in each of the paths 12a to 12l on the first flow path 4 side, and the second flow path is formed. The second medium R ₂ flowing in the descending direction through each path on the fifth side
A plate type heat exchanger Z configured to perform heat exchange between the plate type heat exchanger Z ₁₈ and the plate type heat exchanger Z ₁₈ is used as an evaporator. A gas-liquid separator 67 for separating the first medium R ₁ into gas and liquid after the expansion by the expansion means 63 on the upstream side of _18.
And is configured to introduce only the liquid medium into the plate heat exchanger Z ₁₈ .

According to this structure, the first medium R ₁ is gas-liquid separated by the gas-liquid separator 67 and flows into the heat exchanger Z1 ₈ in the liquid single-phase state. Even if a special gas-liquid distribution promoting mechanism is not provided on the exchanger Z ₁₈ side, the gas-liquid distribution of the first medium R ₁ to the paths 12a to 12l can be made uniform, and the plate heat exchanger Z can be realized. _It can be expected that the heat exchange performance of ₁₈ will be improved, and that the performance of the refrigerating apparatus including the plate heat exchanger Z ₁₈ will be improved.

[0032]

As described above, in the plate heat exchanger according to the first to seventh inventions of the present application, the first path between the paths 12a to 12l arranged in the stacking direction of the heat transfer plates. High heat exchange performance is ensured by achieving uniform gas-liquid distribution of the medium R ₁ .
In the refrigeration apparatus according to the ninth aspect of the present invention, the first medium is allowed to flow into the plate heat exchanger in a liquid single-phase state as much as possible to promote gas-liquid distributability, thereby improving the plate heat exchanger. The heat exchange performance can be improved, and the refrigeration system performance can be expected to improve.

[0033]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention will be specifically described below based on preferred embodiments.

(A) Prerequisite Technology First, the prerequisite technology of each embodiment of the plate heat exchanger described below will be described.

The plate heat exchanger targeted by each of the following embodiments will be described with reference to, for example, the plate heat exchanger Z _{1 according} to the first embodiment shown in FIG.
The heat transfer plate 3 has the same basic structure as the conventional general heat exchanger Z (see FIGS. 28 and 29) described above, and includes, for example, a plurality of heat transfer plates 3 each formed by forming an uneven surface on a stainless plate material. , 3, ... are sequentially laminated so that the protrusions of the adjacent one heat transfer plate 3 and the protrusions of the other heat transfer plate 3 collide with each other, and each heat transfer plate 3, 3 ,. -Alternatively forming the first flow paths 4 and the second flow paths 5 extending in the up-and-down direction between the heat transfer plates 3, 3 ,.
The side plates 1 and 2 are attached to both ends in the stacking direction and sandwiched, and these are integrated.

The invention of the present application corresponds to the primary side refrigerant (“first medium R ₁ ” in the claims) on the side of the first flow path 4 of the first flow path 4 and the second flow path 5. ), Because it focuses on the flow state of
In FIG. 1, only the structure on the side of the first flow path 4 is shown, and on the side of the second flow path 5 only the structure of the passage in relation to the first flow path 4 is shown. Therefore, regarding the overall configuration of the plate heat exchanger Z ₁ , etc.,

2. Description of the Related Art The relevant description in the section "Prior Art" is incorporated herein by reference, and a duplicate description thereof will be omitted.

In the plate type heat exchanger Z ₁ ,
The heat transfer plate 3 is provided on the lower side and the upper side, respectively.
The inlet-side collecting portion 6 and the outlet-side collecting portion 7 extending in the stacking direction are provided, and one end of the inlet-side collecting portion 6 communicates with the inlet 8 and the other end communicates with the outlet 9. Then, between the heat transfer plates 3, 3, ...
The lower ends of the first flow paths 4, 4, ... That are formed alternately with the flow paths 5 and extend in the up-down direction have the lower ends of the first flow paths 5.
A plurality of upper ends (12 in this embodiment) arranged in the stacking direction of the heat transfer plate 3 by the first flow paths 4, 4 ,.
Individual) paths 12a to 12l are configured.

Therefore, basically, the primary-side refrigerant flowing from the inflow port 8 into the inlet-side collecting part 6 corresponds to each of the paths 12a to 12l from the inlet-side collecting part 6. .. flow into one of the flow paths 4, 4, ..., And flow upward through the respective first flow paths 4, 4 ,. Meeting part 7
After being collected in the above, the liquid is discharged from the outlet 9. Then, heat is exchanged with the secondary-side medium that descends and flows through the second flow paths 5, 5, ..., While the paths 12a to 12l are raised.

In this case, as the primary side refrigerant, for example, a Freon refrigerant having a property of undergoing a phase change between a gas phase and a liquid phase is adopted, and the plate heat exchanger Z ₁ is evaporated in a refrigeration system. When used as a container, the primary-side refrigerant is supplied to the inlet 8 side while being condensed in the condenser and decompressed by the expansion mechanism, so that the inlet 8 is in a gas-liquid two-phase state. It will flow in. In this way, the primary-side refrigerant flows into the plate heat exchanger Z ₁ in a gas-liquid two-phase state, whereby each of the paths 1
As described above, the gas-liquid distribution of the primary side refrigerant between 2a to 12l may be non-uniform, and the heat exchange performance of the plate heat exchanger Z ₁ may be deteriorated.

The present invention is a plate-type heat exchanger Z ₁ having a structure in which the paths 12a to 12l are arranged in a row in the flow direction of the inlet side collecting portion 6 as described above, and the inlet side collecting portion 6 is provided with the plate heat exchanger Z _1. Non-uniform gas-liquid distribution among the paths 12a to 12l due to the primary-side refrigerant flowing in a gas-liquid two-phase state,
And it is a technical subject to prevent the deterioration of heat exchange performance accompanying this as much as possible.

Then, as will be described later, in solving the above problems, in the plate heat exchangers Z _{1 to} Z _{15 according} to the first to fifteenth embodiments, the primary side refrigerant is taken by a countermeasure on the heat exchanger side. It is intended to enhance the gas-liquid distribution property of. In contrast, in the 16 to the 18th embodiment according plate heat exchanger Z ₁₆ to Z _18, considered as a refrigeration apparatus incorporating the plate heat exchanger, the primary side to the plate type heat exchanger The refrigerant is allowed to flow in a liquid single-phase state as much as possible to enhance the gas-liquid distribution of the primary side refrigerant.

Hereinafter, based on each embodiment, a peculiar structure of each will be described.

(B) Description of Embodiment (B-1) First Embodiment FIG. 1 shows a plate heat exchanger Z _{1 according} to the first embodiment of the present invention. In this plate-type heat exchanger Z ₁ , an inflow pipe 15 that is connected to the inflow port 8 and causes the primary-side refrigerant supplied from the condenser via an expansion mechanism (not shown) to flow into the inflow-side collecting part 6 is provided. A shunt 21 is provided near the inflow port 8 and the shunt 21 is provided.
Each of the four branch pipes 22 to 25 is connected to the downstream side of the branch pipes 22 to 25, and the primary side refrigerant divided by the flow divider 21 is connected to each of the branch pipes 22 to 25.
It is made to flow into the inside of the inlet side collecting portion 6 through 25. Furthermore, in this case, each of the branch pipes 22 to 25
The tube lengths are sequentially changed so as to correspond to the paths 12a to 12l.

Specifically, the twelve paths 12a to 12l arranged in a row in the flow direction of the inlet side collecting portion 6 are
Four path groups 13A, 13B, 13 are sequentially divided into three paths from the entrance side of the entrance side collecting section 6 toward the back side.
C, 13D, that is, the three paths 12a to 1 closest to the entrance
A first path group 13A composed of 2c, a second path group 13B composed of the next three paths 12d to 12f, and a third path group 13C composed of the next three paths 12g to 12i. , A fourth path group 13D composed of the three innermost paths 12j to 12l. Then, of the branch pipes 22 to 25, the outlet end of the first branch pipe 22 is the inlet end portion of the first pass group 13A (that is, pass 1).
2a, the second branch pipe 23 has its outlet end at the inlet end of the second pass group 13B (that is, the inlet end of pass 12d), and the third branch pipe 23 has its outlet. The end is at the inlet end of the third pass group 13C (that is, the inlet end of the pass 12g), and the outlet end of the fourth branch pipe 24 is at the inlet end of the fourth pass group 13D (that is, the pass). The pipe lengths are set so that they are located at the inlet ends of 12j).

By the pipe length setting, each of the branch pipes 2
2 to 25 and the respective path groups 13A to 13D in relation to each other, the primary side refrigerant flowing from the first branch pipe 22 mainly includes the three paths 12a to 12a belonging to the first path group 13A. The primary-side refrigerant flowing from the second branch pipe 23 into the second branch pipe 12c mainly passes through the three passes 12d to 12f belonging to the second pass group 13B to the third branch pipe 2 described above.
The primary side refrigerant flowing in from No. 4 is mainly the above third pass group 1
The primary-side refrigerant flowing into the three paths 12g to 12i belonging to 3C from the fourth branch pipe 25 is mainly the three paths 12j to 12l belonging to the fourth path group 13D.
, Respectively.

As described above, in the plate heat exchanger Z ₁ of this embodiment, the flow distributor 21 is provided on the upstream side of the inlet 8, and the branch pipes 22 to 22 extending from the flow distributor 21 to The exit end of 25 is connected to each of the above path groups 13A.
By corresponding to each of ~ 13D, the following unique effects can be obtained.

That is, when the gas-liquid two-phase primary side refrigerant is supplied to the plate type heat exchanger Z ₁ side through the inflow pipe 15, the primary side refrigerant is first branched by the flow divider 21 into each of the branches. It is divided into each of the tubes 22 to 25,
There is no variation in the gas-liquid state between the respective branch pipes 22 to 25, and they are made as uniform as possible. Then, the primary side refrigerant having no variation in the gas-liquid state in this way is branched from each of the branch pipes 22 to 25 whose pipe length is set so as to correspond to each of the path groups 13A to 13D.
By intensively flowing into each of the paths 13D, the gas-liquid distribution among the paths 12a to 12l is made uniform as much as possible.

As a result, even if the uneven distribution of the liquid refrigerant is likely to occur depending on the flow rate of the refrigerant,
The occurrence of such uneven distribution phenomenon is prevented as much as possible, and the heat exchange performance of the plate heat exchanger Z ₁ is improved. In other words, even when the plate heat exchanger Z ₁ is used as an evaporator into which the primary-side refrigerant flows in a gas-liquid two-phase state, the primary-side refrigerant flows in a liquid single phase or a gas single phase. This ensures high heat exchange performance equivalent to that in other cases.

(B-2) Second Embodiment FIG. 2 shows a plate heat exchanger Z _{2 according} to a second embodiment of the present invention. This plate-type heat exchanger Z ₂ is based on the structure of the plate-type heat exchanger Z ₁ of the above-described first embodiment, and a unique structure is added to the plate-type heat exchanger Z ₁ to obtain the effect of the plate-type heat exchanger Z ₁ . It is intended to further increase

That is, as shown in FIG. 2, in the plate heat exchanger Z _{2 of} this embodiment, each of the branch pipes 22 to 25 is
The exit ends of the respective paths are positioned substantially in the middle of the path row installation direction of the corresponding path groups, and the respective exit ends are moved upward (that is,
It is oriented in the circulation direction of the primary side refrigerant).

According to this structure, the above-described effects of the plate heat exchanger Z ₁ according to the first embodiment can be obtained, as well as the following unique effects. To be

That is, in the plate heat exchanger Z ₂ of this embodiment, each of the branch pipes 22, 23, 24, 25 described above is used.
The exit end of each of the path groups 13A to 13D, and the central path of each of the path groups 13A to 13D (that is, the second path 12b in the first path group 13A,
In the second pass group 13B, the fifth pass 12e and the third pass group 1
8C 12h in 3C, 1st in 4th pass group 13D
In the first pass 12k), since the respective outlets of the branch pipes 22, 23, 24 and 25 are directed upward, the primary side refrigerant is more accurately supplied to the respective passes belonging to the corresponding pass group. can be made to flow, which correspondingly uniform gas-liquid distribution of the primary refrigerant in between the respective paths 12a~12l is further promoted, further improvement in heat exchange performance of the plate heat exchanger Z ₂ can be expected Is.

The configuration and operation and effect other than those described above are the same as those in the case of the first embodiment described above.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-3) Third Embodiment FIG. 3 shows a plate heat exchanger Z _{3 according} to a third embodiment of the present invention. The plate heat exchanger Z ₃ is positioned as a modified example of the plate heat exchanger Z ₂ of the second embodiment, and in the plate heat exchanger Z ₂ of the second embodiment, The path groups 13 corresponding to the outlet ends of the branch pipes 22 to 25, respectively.
It is directed downward in the central path of A to 13D.

With this structure, each branch pipe 2 is
The primary-side refrigerant in the gas-liquid two-phase state flowing into the inlet side collecting portion 6 side from the outlet ends of 2 to 25 collides with the lower wall portions of the paths 12b, 12e, 12h, 12k to which the respective outlet ends correspond. After the gas and liquid are mixed sufficiently,
Each of the paths 12a to 12 belonging to the 3A to 13D
Since l is increased, the homogenization of gas-liquid distribution among the paths belonging to the path groups 13A to 13D is further promoted, and the heat exchange performance of the plate heat exchanger Z ₃ is further improved. Can be expected.

Since the configuration and the effect other than the above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-4) Fourth Embodiment FIG. 4 shows a plate heat exchanger Z _{4 according} to a fourth embodiment of the present invention. In the plate heat exchanger Z _{1 to} Z _{3 according} to the first to third embodiments, the plate heat exchanger Z ₄ is provided with the outlet ends of the branch pipes 22 to 25 as they are at the inlet side collecting portion. 6 is open to the inside, the expansion mouth member 26, 26, which expands upward at each of the outlet ends of the branch pipes 22 to 25.
・ Attachment of each expansion mouth member 26, 26, ・
Is directed to each of the path groups 13A to 13D.

With this structure, each branch pipe 2 is
The primary side refrigerant flowing into the inlet side collecting portion 6 side from 2 to 25 is a path group 13A to 1A corresponding to each of them by the guide action of the expansion port members 26, 26 ,.
It will flow into the 3D more accurately, and as a result, the homogenization of gas-liquid distribution between the paths belonging to each of the path groups 13A to 13D will be further promoted,
Further improvement in heat exchange performance of the plate heat exchanger Z ₄ can be expected.

Since the configuration and the effect other than those described above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-5) Fifth Embodiment FIG. 5 shows a plate heat exchanger Z _{5 according} to a fifth embodiment of the present invention. The plate heat exchanger Z ₅ is the plate heat exchangers Z _{1 to} Z _{4 according} to the first to fourth embodiments, and the flow divider 21 and the branch pipes 2 are included in the plate heat exchanger Z _5.
2 to 25, that is, to further promote the improvement of the heat exchange performance by uniforming the gas-liquid distribution of the primary side refrigerant in each of the paths 12a to 12l.

That is, in the plate heat exchanger Z _{5 of} the fifth embodiment, as shown in FIG. 5, the flow distributor 21 is provided in the inflow pipe 15 and the plate heat exchanger Z ₅ is provided in the plate heat exchanger Z ₅ . The number of branch pipes 31 to 42 corresponding to the number of passes in the heat exchanger Z ₅ (12 in this embodiment) is connected. Then, the pipe lengths of the respective branch pipes 31 to 42 are sequentially changed stepwise so that the outlet ends of the respective branch pipes 31 to 42 correspond to the respective paths 12a to 12l and are directed upward.

With this structure, each path 12
The primary side refrigerant having a similar gas-liquid distribution can be accurately flowed into each of a to 12l, and each of the paths 12a to 1
The gas-liquid distribution in 2 liters became extremely good, and as a result,
It can be expected that the heat exchange performance of the plate heat exchanger Z ₅ will be significantly improved.

Since the configuration and the operation and effect other than the above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-6) Sixth Embodiment FIG. 6 shows a plate heat exchanger Z _{6 according} to a sixth embodiment of the present invention. This plate-type heat exchanger Z ₆ is based on the structure of the plate-type heat exchanger Z ₁ of the above-described first embodiment, and the plate-type heat exchanger Z ₁ is achieved by adding a unique structure thereto. This is aimed at further enhancing the effect.

That is, as shown in FIG. 6, in the plate heat exchanger Z _{6 of} this embodiment, each of the branch pipes 22 to 25 is
Of the path groups 13A to 13D corresponding to the exit ends of the
The respective path groups 13A-1D to partition 3A-13D from each other.
The partition plates 27 to 29 are arranged at the 3D boundary positions, respectively.

According to this structure, each of the branch pipes 22 ...
The primary side refrigerant flowing from 25 into the inlet side collecting portion 6 surely flows into the paths belonging to the respective path groups 13A to 13D corresponding to the respective branch pipes 22 to 25. As a result, for example, when the partition plates 27 to 29 are not provided, even if each of the branch pipes 22 to 25 corresponds to each of the path groups 13A to 13D, the target path due to the inflow inertia or the like is used. Not only the group but also a little more than this, it will flow into other adjacent path groups, but such cross-border inflow is surely prevented by the partitioning action of the partition plates 27 to 29, and each of the paths 12a. The gas-liquid distribution between ˜12 l is further homogenized, and the heat exchange performance of the plate heat exchanger Z ₆ can be expected to be further improved.

Since the configuration and the effect other than the above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-7) Seventh Embodiment FIG. 7 shows a plate heat exchanger Z _{7 according} to a seventh embodiment of the present invention. The plate heat exchanger Z ₇ has a slightly different structure from the plate heat exchangers Z _{1 to} Z _{6 according} to the first to sixth embodiments.

That is, in the plate heat exchanger Z _{7 according} to the seventh embodiment, the four branch pipes 22 to 25 are directly connected to the inflow pipe 15 without providing a flow divider. Is. Then, in this case, the branch pipes 22 to 25 are arranged vertically in multiple stages, and the relationship between the arrangement position and the pipe length is set as follows.

That is, the pipe length is the shortest at the bottom,
The first branch pipe 22 opening toward the entrance end of the path group 13A
The second path group 13 is provided above the first branch pipe 22.
The second branch pipe 23 opened toward the inlet end of B is
Above the second branch pipe 23, a third branch pipe 24 that opens toward the inlet end of the third pass group 13C is provided, and the uppermost stage has the longest pipe length and the inlet end of the fourth pass group 13D. The 4th branch pipe 25 which opens to the side is arrange | positioned, respectively.

With this structure, even if the flow divider is not provided, the gas-liquid distribution can be equalized to the same extent as when the flow divider is provided. That is, when the primary-side refrigerant flows in the gas-liquid two-phase state in the inflow pipe 15, the liquid refrigerant Rq flows along the bottom side of the inflow pipe 15 and the inflow pipe 15
The gas refrigerant Rg flows on the upper side of. Therefore, when the primary side refrigerant flows into the inlet side collecting portion 6 side through the branch pipes 22 to 25, a large amount of the liquid refrigerant Rq flows in the first branch pipe 22 located at the lowermost stage. On the contrary, a large amount of the gas refrigerant Rg flows through the fourth branch pipe 25 located at the uppermost stage. As a result, the path groups 13A to 13
In D, corresponding to the gas-liquid distribution of the primary side refrigerant flowing in from each of the branch pipes 22 to 25, the first pass group 13A side closer to the inlet side of the inlet side collecting portion 6 is the liquid occupied in the primary side refrigerant. The ratio of the refrigerant is high, and the ratio of the gas refrigerant occupying the primary side refrigerant is higher toward the inner side of the fourth pass group 13D.

Therefore, this plate heat exchanger Z ₇ is
This is suitable when used under conditions where the flow rate of the refrigerant is small. That is, under the condition that the flow rate of the refrigerant is small, a large amount of the gas refrigerant originally flows toward the inlet side of the inlet side collecting portion 6 and a large amount of the liquid refrigerant flows toward the back side. Therefore, under such an original refrigerant distribution form, as described above, the branch pipes 22 to 25 cause a large amount of liquid refrigerant to flow toward the inlet side of the inlet side collecting portion 6 and a large amount of gas refrigerant to the rear side. As a result, these two are complemented each other, and when viewed as the inlet side collecting section 6 as a whole, the gas-liquid distribution of the primary side refrigerant is made as uniform as possible in the entire range from the inlet side to the back side. Therefore, the heat exchange performance of the plate heat exchanger Z ₇ is improved.

The configuration and operation and effect other than the above are the same as those in the case of the first embodiment, so that FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-8) Eighth Embodiment FIG. 8 shows a plate heat exchanger Z _{8 according} to an eighth embodiment of the present invention. The plate heat exchanger Z ₈ is a one that is positioned as a modification of the plate heat exchanger Z ₇ according to the seventh embodiment, based on the same structure as the plate heat exchanger Z ₇ The difference from this is the arrangement of the branch pipes 22 to 25.

That is, in the plate heat exchanger Z ₇ of the _seventh embodiment, the first branch pipe 2 having the shortest pipe length is used.
2 was arranged in the lowermost stage and the fourth branch pipe 25 having the longest pipe length was arranged in the uppermost stage, respectively, on the contrary,
In the plate heat exchanger Z _{8 of} this embodiment, the first branch pipe 22 having the shortest pipe length at the uppermost stage and opening toward the inlet end of the first pass group 13A is connected to the first branch pipe 22. On the lower side, a second branch pipe 23 that opens toward the inlet end of the second pass group 13B is provided, and on the lower side of the second second branch pipe 23, near the inlet end of the third pass group 13C. The third branch pipe 24 that opens to the first branch pipe 2 that has the longest pipe length at the lowermost stage and that opens toward the inlet end of the fourth pass group 13D.
5 are arranged respectively.

With this structure, even if the flow divider is not provided, the gas-liquid distribution can be equalized to the same extent as in the case where the flow divider is provided. That is, when the primary-side refrigerant flows in the gas-liquid two-phase state in the inflow pipe 15, the liquid refrigerant Rq flows along the bottom side of the inflow pipe 15 and the inflow pipe 15
The gas refrigerant Rg flows on the upper side of. Therefore, when the primary-side refrigerant flows into the inlet-side collecting portion 6 side through the branch pipes 22 to 25, a large amount of the liquid refrigerant Rq flows in the fourth branch pipe 25 located at the lowermost stage. On the contrary, a large amount of the gas refrigerant Rg flows through the first branch pipe 22 located at the uppermost stage. As a result, the path groups 13A to 13
In D, the gas that occupies the primary side refrigerant closer to the first pass group 13A closer to the inlet side of the inlet side collecting portion 6 in correspondence with the gas-liquid distribution of the primary side refrigerant flowing from each of the branch pipes 22 to 25. The ratio of the refrigerant is high, and the ratio of the liquid refrigerant in the primary-side refrigerant is higher toward the inner side of the fourth pass group 13D.

Therefore, this plate heat exchanger Z₈Is
This is suitable for use under conditions where the refrigerant flow rate is high.
It is suitable. That is, under the condition that the refrigerant flow rate is high
Is essentially liquid-cooled toward the inlet side of the inlet side collecting section 6
A large amount of the medium flows, and a large amount of the gas refrigerant flows to the back side. Therefore,
Under such an original form of refrigerant distribution, as described above,
The inlet of the inlet side collecting portion 6 by each branch pipe 22 to 25
A large amount of gas refrigerant flows to the side, and a large amount of liquid refrigerant flows to the back side.
By doing so, these two are complemented each other, and
When viewed as part 6 as a whole, all from the entrance side to the back side
In the range, gas-liquid distribution of the primary side refrigerant is made as uniform as possible.
As a result, the above plate type heat exchanger Z ₇Heat exchange performance
Will be improved.

Since the configuration and the operation and effect other than those described above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-9) Ninth Embodiment FIG. 9 shows a plate heat exchanger Z _{9 according} to a ninth embodiment of the present invention. This plate type heat exchanger Z ₉ has a plate-shaped flow rate adjusting member 1 in the inlet side collecting portion 6.
By arranging 6 to adjust the flow rate of the primary-side refrigerant in the gas-liquid two-phase state flowing from the inlet 8 into the inlet-side collecting portion 6 from the inlet side toward the inner side, 1
It is intended to make the gas-liquid distribution of the primary side refrigerant in 2a to 12l uniform.

Specifically, in this embodiment, as shown in FIGS. 9 to 11, the width dimension close to the diameter dimension of the inlet 8 and about 1 / l of the axial length of the inlet side collecting portion 6 are obtained. A plate material having a length of about 2 is used as the flow rate adjusting member 16, and this is provided in the inlet side collecting portion 6 at the lower end position of the boundary portion between the first path 12a and the second path 12b and the sixth path. Pass 12f
And the upper end position of the boundary between the seventh pass 12g and the seventh pass 12g (that is, between the first pass group 13A and the second pass group 13B).

According to this structure, the primary side refrigerant flowing from the inflow port 8 into the inlet side collecting portion 6 is
First, it collides with the flow rate adjusting member 16, and a part Ra thereof is guided by the upper surface of the flow rate adjusting member 16 and deflected upward, and the flow rate adjusting member 16 flows into the corresponding paths 12a to 12f and the other one. The portion Rb deviates laterally from the flow rate adjusting member 16 and flows out to the back surface side (that is, the third pass group 13C and the fourth pass group 13D side), and thereafter, each of these pass groups 1
It flows into the paths 12g to 12l belonging to 3C and 13D.

Therefore, for example, when the flow rate of the primary side refrigerant is small and the liquid refrigerant flows to the inner side of the inlet side collecting portion 6 under a large amount, the liquid refrigerant is mainly adjusted by the flow rate adjusting member 16. As a result, the inflow of the liquid refrigerant into the back side is suppressed. On the contrary, in the case of the use condition that the flow rate of the primary-side refrigerant is large and the gas refrigerant flows to the inner side of the inlet side collecting portion 6, the gas refrigerant is mainly subjected to the adjusting action by the flow rate adjusting member 16, The inflow of the gas refrigerant to the inner side is suppressed.

As a result of these, each of the paths 12a to 12l
The gas-liquid distribution of the primary side refrigerant in the is as uniform as possible,
The heat exchange performance of the plate heat exchanger Z ₉ can be expected to be improved.

Since the configuration and the operation and effect other than those described above are the same as those in the case of the first embodiment, the configuration shown in FIG.
The same reference numerals are given to the respective members corresponding to the respective members in FIG. 1, and the corresponding description is cited, and the description will be omitted.

(B-10) Tenth Embodiment FIG. 12 shows a plate heat exchanger Z _{10 according} to a tenth embodiment of the present invention. Similar to the plate heat exchanger Z _{9 of} the ninth embodiment, this plate heat exchanger Z ₁₀ adjusts the flow rate of the primary side refrigerant by the flow rate adjusting member 16 arranged in the inlet side collecting portion 6. The purpose is to make the gas-liquid distribution of each of the paths 12a to 12l uniform as much as possible, and the difference from this is in the configuration of the flow rate adjusting member 16.

That is, in the plate heat exchanger Z _{10 of} the tenth embodiment, as shown in FIGS. 13 and 14, the flow rate adjusting member 16 has a width dimension close to the diameter dimension of the inflow port 8. The first pass group 13A to the third pass group 13
Three vertical wall members 17A, 17B, and 17C having different heights are sequentially arranged on the base material 18 made of a plate material having a length extending over C at predetermined intervals in order of height (specifically, in three paths). It is configured by standing and fixing it at intervals such that it straddles. Then, the flow rate adjusting member 16 is oriented in a direction such that the vertical wall member 17A having the lowest height is located on the inlet side of the inlet side collecting portion 6, and the vertical wall member 17A is disposed on the fourth pass 12d. , Wall material 17
B to the 7th pass 12g, and vertical wall material 17C to the 10th
Are arranged in the entrance side collecting portion 6 so as to be respectively located on the paths 12j.

According to this structure, the primary side refrigerant flowing from the inflow port 8 into the inlet side collecting portion 6 is
First, in the first pass group 13A, the vertical wall member 17A is guided, and a portion Ra ₁ thereof is deflected upward and flows into each of the passes 12a to 12c belonging to the first pass group 13A.
The other part Ra ₂ bypasses the lateral side of the vertical wall member 17A and flows to the second pass group 13B side.

In the second pass group 13B, the primary-side refrigerant that has flown in from the first pass group 13A side is guided by the vertical wall member 17B, and a part Rb ₁ thereof is deflected upward. Each path 12d belonging to the second path group 13B
12f side, the other part Rb ₂ is the vertical wall material 17B
To the side of the third pass group 13C, bypassing the side of

Furthermore, in the third pass group 13C, the primary-side refrigerant that has flown in from the second pass group 13B side is bypassed.
In response to the guiding action of the vertical wall member 17C, a part Rc ₁ thereof is deflected upward and each pass 12g belonging to the third pass group 13C.
~ 12i side, the other part Rc ₂ is the vertical wall material 17
It bypasses the side of C and flows to the side of the fourth pass group 13D.

Then, in the fourth pass group 13D, the primary side refrigerant Rd bypassed from the third pass group 13C side.
Is deflected upward and each path 12 belonging to the fourth path group 13D
It flows into the j to 12l side.

Note that, for example, in the case of a use condition in which the inflow rate of the primary side refrigerant is small and the liquid refrigerant flows a lot toward the inner side of the inlet side collecting portion 6, the liquid refrigerant is mainly adjusted by the flow rate adjusting member 16. As a result, the inflow of the liquid refrigerant into the back side is suppressed. On the contrary, in the case of the use condition that the flow rate of the primary-side refrigerant is large and the gas refrigerant flows to the inner side of the inlet side collecting portion 6, the gas refrigerant is mainly subjected to the adjusting action by the flow rate adjusting member 16, The inflow of the gas refrigerant to the inner side is suppressed.

As described above, the primary side refrigerant flowing in the gas-liquid two-phase state from the inflow port 8 to the inlet side collecting portion 6 side has the vertical wall members 17A, 17B, 17C of the flow rate adjusting member 16.
By sequentially adjusting the flow rate by
The gas-liquid distribution of ~ 12 l is made as uniform as possible, and the heat exchange performance of the plate heat exchanger Z ₁₀ is improved.

FIG. 14 shows another structural example of the flow rate adjusting member 16 in which the vertical wall members 17A, 17B and 17C are alternately staggered in the left-right direction and arranged in a staggered manner. The same effect as described above can also be obtained by the flow rate adjusting member 16.

Since the configuration and the effect other than the above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members of No. 2 corresponding to the respective members of FIG. 1, and the corresponding description is cited to omit the description.

(B-11) Eleventh Embodiment FIG. 15 shows a plate heat exchanger Z _{11 according} to an eleventh embodiment of the present invention. This plate heat exchanger Z ₁₁
In the same manner as the plate heat exchangers Z ₉ and Z _{10 of} the ninth and tenth embodiments, the flow rate of the primary side refrigerant is adjusted by the flow rate adjusting member 16 arranged in the inlet side collecting portion 6. The present invention aims to make the gas-liquid distribution of each of the paths 12a to 12l as uniform as possible, and is different from this in the structure of the flow rate adjusting member 16.

That is, in the plate heat exchanger Z _{11 of} the eleventh embodiment, as shown in FIG. 16, a triangular plate material is curved in an arc shape to form a triangular gutter shape, which is used for the above flow rate adjustment. The member 16 is used. And this flow rate adjusting member 1
6 on top of the inlet-side gathering portion 6, its top 16a side facing the inlet-side of the inlet-side gathering portion 6, the wide bottom facing toward the back side, and straddling the entire length of the inlet-side gathering portion 6. It is attached like this.

According to this structure, the primary side refrigerant flowing from the inflow port 8 into the inlet side collecting portion 6 is
From the inlet side collecting portion 6, the flow is branched into each of the paths 12a to 12l and flows in. However, since the flow rate adjusting member 16 is located above the inlet side collecting portion 6, the primary side refrigerant is It flows upward by bypassing the side edge of the flow rate adjusting member 16. In this case, the width dimension of the flow rate adjusting member 16 increases from the inlet side of the inlet side collecting portion 6 toward the back side, in other words, the inlet side from the inlet side toward the back side. The flow passage area formed between the side collecting portion 6 and the flow rate adjusting member 16 is reduced.

Therefore, the primary side refrigerant is the inlet side collecting portion 6
When flowing from the inlet side to the back side in the inside, the amount flowing to the pass side by bypassing the side edge of the flow rate adjusting member 16 decreases as going from the first pass group 13A side to the fourth pass group 13D side. The flow rate is adjusted as follows. For example, when the flow rate of the primary-side refrigerant is small and the liquid refrigerant flows to the inner side of the inlet side collecting portion 6 under a large amount, the liquid refrigerant mainly receives the adjusting action of the flow rate adjusting member 16, The inflow of the liquid refrigerant to the inner side (that is, the inflow to the inner path) is suppressed. On the contrary, in the case of the use condition that the flow rate of the primary-side refrigerant is large and the gas refrigerant flows to the inner side of the inlet side collecting portion 6, the gas refrigerant is mainly subjected to the adjusting action by the flow rate adjusting member 16, The inflow of the gas refrigerant to the inner side is suppressed.

In this way, from the inlet 8 to the inlet side
The primary side refrigerant flowing into the collecting portion 6 side in the gas-liquid two-phase state is
By sequentially adjusting the flow rate by the flow rate adjusting member 16,
Gas-liquid distribution of each path 12a-12l is made as uniform as possible
Plate heat exchanger Z _TenImproves heat exchange performance of
It is what is done.

Since the configuration and operational effects other than the above are the same as those in the case of the first embodiment, FIG.
The same reference numerals are given to the respective members of 5 corresponding to the respective members of FIG. 1, and the corresponding description is cited to omit the description.

(B-12) Twelfth Embodiment FIG. 17 shows a plate heat exchanger Z _{12 according} to a twelfth embodiment of the present invention. In this plate heat exchanger Z ₁₂ , the pipe body is bent in a U shape in the inlet side collecting portion 6 to form a first pipe portion 45A and a second pipe portion 45B, and the pipe portions 45A, Predetermined spacing on the outer wall surface of 45B (specifically, the spacing between the paths 12a to 12l)
The inflow pipe 45 formed by the through holes 46, 46, ...
The bent portion is inserted and arranged with the bent portion facing toward the back side, and
The primary side refrigerant is made to flow in from the end side of the pipe portion 45A and is made to flow in a folded shape toward the end side of the second pipe portion 45B. While passing through the inflow pipe 45, the passages 46, 46, ...
The primary side refrigerant flows out to each of the 2a to 12l sides. The inflow pipe 45 corresponds to the "flow direction control member" in the claims.

The above structure is based on the following idea. That is, for example, the primary side refrigerant is passed through each of the paths 12a to 1
When the configuration is such that the 2 l is flown in the row direction, as shown in FIG. 23, the amount of the liquid refrigerant is greatly inclined from the inlet side to the inner side of the inlet side collecting portion 6, and the uneven distribution phenomenon of gas-liquid distribution occurs. (This point is also mentioned in the section of the prior art (see the liquid level line L in FIG. 29)), and the heat exchange performance of the plate heat exchanger is deteriorated. This phenomenon is largely due to the fact that the primary side refrigerant is linearly distributed from the inlet side of the inlet side collecting portion 6 toward the inner side. Therefore,
For example, once the primary-side refrigerant is made to flow from the inlet side of the inlet-side collecting portion 6 to the back side, it is reversed, and this time it is made to flow toward the inlet side to the back side, so that the air flow in the forward path as a whole is reduced. The liquid distribution and the gas-liquid distribution in the return path overlap each other, and FIG.
As shown in, the gas-liquid distribution in each of the paths 12a to 12l is made as uniform as possible.

Based on such knowledge, the inflow pipe 45 is formed into a folded tubular shape as described above.

Therefore, the inflow pipe 45 is arranged in the inlet side collecting portion 6, and the primary side refrigerant is caused to flow from one end side of the first pipe portion 45A to flow to the back side, and then further reversed. , The second pipe portion 45B side is made to flow from the inner side toward the inlet side, and in the course of this flow, the through holes 46, 46, ...
From By flowing the primary side refrigerant into the respective path 12a~12l side, as a result, the gas-liquid distribution is made uniform refrigerant distribution state is achieved, the more plate heat exchanger Z ₁₂
The heat exchange performance of is improved.

The configuration and the operation and effects other than those described above are the same as those in the case of the first embodiment described above.
The description of the members 7 will be omitted by assigning the same reference numerals to the members of FIG. 1 corresponding to the members of FIG.

(B-13) Thirteenth Embodiment FIGS. 18 and 19 show a plate heat exchanger Z _{13 according} to a thirteenth embodiment of the present invention. Similar to the plate heat exchanger Z _{12 of the twelfth} embodiment, the plate heat exchanger Z ₁₃ folds the primary side refrigerant from the inlet side of the inlet side collecting portion 6 to the inner side and then turns back. , Each of the above paths 12a to 12l by flowing from the back side toward the entrance side
The aim is to achieve uniform gas-liquid distribution. And, in particular, the plate heat exchanger Z of this embodiment
_{In 13} , the outer pipe 47 having a closed tip is used as an inflow pipe 47 (“corresponding to a circulation direction control member” in the claims) for realizing the return circulation of the primary side refrigerant.
A double tube composed of A and an inner tube 47B arranged substantially concentrically inside the outer tube 47A is provided, and the inflow tube 47 is fitted and arranged in the inlet side collecting portion 6. Also, FIG.
As shown in FIG. 9, the outer pipe 47A and the inner pipe 47B are provided with through holes 48, 48, ..., And 4 at the intervals corresponding to the intervals at which the paths 12a to 12l are formed in the outer peripheral walls.
, 49, ... Are formed.

Then, the primary-side refrigerant is introduced from one end of the inner pipe 47B attached to the inflow port 8 to flow out from the tip thereof to a portion near the tip of the outer pipe 47A, and further inverted. The outer tube 47A
Through the outer flow path 50 between the second pipe portion 45B and the second pipe portion 45B. In this way, when the primary-side refrigerant flows back through the inner pipe 47B and the outer flow path 50 in sequence, first, while the primary-side refrigerant flows through the inner pipe 47B toward the tip side thereof, A part of the through holes 49, 49, ... Then, the primary-side refrigerant flowing out to the outer flow path 50 flows out from the tip of the inner pipe 47B into the outer flow path 50 and flows into the outer flow path 50 to the inlet side. , And while flowing out through the through holes 48, 48, ... Provided in the outer pipe 47A,
It flows into each of the paths 12a to 12l.

According to the circulation of the primary side refrigerant, when the primary side refrigerant flows out from the through holes 49, 49, ... Of the inner pipe 47B to the outer flow passage 50 side, the gas-liquid distribution of the outflowing refrigerant is biased. In addition, in the primary-side refrigerant that flows back inside the outer flow path 50 and flows back, there is a bias in gas-liquid distribution, which is the reverse tendency of the one flowing out from the inner pipe 47B side. However, by mixing and overlapping these two, .. from the through holes 48, 48, ... Of the outer tube 47A.
In the primary side refrigerant flowing into the 12l side, the deviation of the gas-liquid distribution is absorbed and is made as uniform as possible, and as a result, high heat exchange performance is ensured in the plate heat exchanger Z ₁₃ . is there.

Since the configuration and the operation and effect other than those described above are the same as those in the case of the first embodiment, the configuration shown in FIG.
The description of the members 8 will be omitted by assigning the same reference numerals to the members 8 of FIG. 1 and quoting the corresponding description.

(B-14) Fourteenth Embodiment FIGS. 20 and 21 show a plate heat exchanger Z _{14 according} to a fourteenth embodiment of the present invention. The plate heat exchanger Z ₁₄ is positioned as a modification of the plate heat exchanger Z ₁₃ of the thirteenth embodiment, and is a plate heat exchanger Z _{13 according} to the thirteenth embodiment. In contrast, the inflow pipe 47 is configured by a concentric double pipe, whereas the outer pipe 47A and the inner pipe 47B are
It is composed of an eccentric double tube with eccentricity. That is, as shown in FIG. 21, one side of the outer tube 47A and one side of the inner tube 47B are joined and integrated. Further, through holes 51, 51, ... Are provided at the joint portion between the outer pipe 47A and the inner pipe 47B at intervals corresponding to the arrangement intervals of the paths 12a to 12l, and the joint portion of the outer pipe 47A is Through hole 5 on the opposite wall
The through holes 52, 52, ... Are provided corresponding to 1, 51 ,.

The inflow pipe 47 having such a structure is inserted into the inlet side collecting portion 6 of the plate heat exchanger Z _{14 with} the through holes 51, 51, ... Side upward. The inner pipe 47 arranged and extending outward from the inflow port 8
The primary side refrigerant is introduced from one end side of B, and this is introduced into the inner pipe 4
After passing through the inside of 7B to the tip side, it is further turned back toward the inlet side through the outer flow path 50 between the outer tube 47A and the inner tube 47B.

As described above, the primary side refrigerant is the inner pipe 47B.
When flowing back by sequentially passing through and the outer flow path 50, first, a part of the primary-side refrigerant flows through the inside holes 47, 5 of the inner tube 47B while flowing toward the tip side thereof.
.. are sequentially flowed out, and flow into the paths 12a to 12l. Further, the other part of the primary side refrigerant flowing from the tip of the inner pipe 47B into the outer flow passage 50 sequentially flows out through the through holes 52, 52, ... While flowing in the outer flow passage 50. Then, it flows into each of the paths 12a to 12l.

According to the circulation of the primary side refrigerant, the primary side refrigerant is
When the side refrigerant is in the forward path, the through holes 51, 51, ...
When these flow into each of the paths 12a to 12l,
The gas-liquid distribution is biased between the
On the return path, from the through holes 52, 52, ...
Even when flowing into 12a to 12l, gas-liquid components are
Although the distribution is biased, in each of the paths 12a to 12l
Means that the refrigerant on the outward path and the refrigerant on the return path are mixed and overlap.
With, the bias of gas-liquid distribution among the paths 12a to 12l is possible.
It is absorbed as much as possible and its uniformity is achieved.
G heat exchanger Z ₁₄High heat exchange performance is secured in
It is something.

The structure and operation and effect other than those described above are the same as those in the case of the first embodiment described above.
The same reference numerals are given to the respective members of 0 corresponding to the respective members of FIG. 1, and the corresponding description is cited to omit the description.

(B-15) Fifteenth Embodiment FIG. 24 shows a plate heat exchanger Z _{15 according} to a fifteenth embodiment of the present invention. In this plate heat exchanger Z ₁₅ , a straight refrigerant inlet pipe 53 having an outer diameter smaller than the inner diameter of the inlet side collecting portion 6 by a predetermined dimension is provided in the inlet side collecting portion 6 from the inlet 8 side. Insert the outlet end 5
3a on the inner side of the inlet side collecting portion 6, specifically, on the 10th side.
It is located near the boundary between the path 12j and the eleventh path 12k.

According to this structure, the refrigerant inlet pipe 53 is
When the primary side refrigerant is introduced into the inlet side collecting portion 6 through the outlet side of the inlet side collecting portion 6 because the outlet end of the refrigerant inlet pipe 53 is located at the back of the inlet side collecting portion 6, Regardless of this, the gas refrigerant is always positively introduced into the inner part. Therefore, the path 12 corresponding to the inner part
In k and 12l, the heat exchange performance deteriorates due to the concentrated inflow of the gas refrigerant, but other paths 12a to
In 12j, since the liquid refrigerant flows in a state close to a liquid single phase, gas-liquid distribution of the primary side refrigerant among the paths 12a to 12J is made as uniform as possible, and high heat exchange performance is realized. Moreover, the paths 12k, 12 through which the gas refrigerant flows in
The ratio of 1 in all the paths 12a to 12l is small (that is, about 2/12), and the influence of this on the heat exchange performance is also small. As a synergistic effect of these, higher heat exchange performance is obtained when the plate heat exchanger Z ₁₅ is viewed as a whole.

The structure and operation and effect other than the above are the same as those of the first embodiment, and therefore, FIG.
The same reference numerals are given to the respective members of No. 4 corresponding to the members of FIG. 1, and the corresponding description is cited to omit the description.

(B-16) Sixteenth Embodiment FIG. 25 shows a refrigerant circuit diagram of a refrigerating apparatus X _{1 according} to the sixteenth embodiment of the present invention. This freezer X
₁ is a compressor 61 and a heat exchanger 62 that functions as a condenser.
The expansion valve 63 and the plate heat exchanger Z ₁₆ functioning as an evaporator are operatively connected to each other through the flow passages 71 and 72. A refrigerant having a property of phase change between phases, for example, a chlorofluorocarbon refrigerant is used, and the purpose thereof is to enhance the heat exchange performance of the plate heat exchanger Z ₁₆ so that the entire refrigerant circuit X ₁ is The point is to improve performance.

A problem in solving such a problem is that the primary side refrigerant flows into the plate heat exchanger Z ₁₆ in a gas-liquid two-phase state, and the gas-liquid distribution becomes non-uniform between the respective paths, resulting in heat exchange performance. Is to decrease.

Therefore, in this embodiment, the inflow of the primary-side refrigerant into the plate heat exchanger Z ₁₆ is performed in a state close to the liquid single phase as much as possible, not in the gas-liquid two-phase state. It was made possible.

That is, in this embodiment, a heat exchanger 64 for self-cooling (“cooling means” in the claims) is provided in the passage 71 between the heat exchanger 62 and the expansion valve 63.
The refrigerant inlet 64a of the heat exchanger 64 is branched from the downstream side of the heat exchanger 64, and an expansion valve 65 (“expansion means” in claims) is provided in the middle of the branch.
Corresponding to the bypass passage 73, and the refrigerant outlet 64b of the heat exchanger 64 is connected to the bypass passage 7
4 to the flow path 72.

In the heat exchanger 64, the refrigerant inlet 64a is on the downstream side of the flow passage 71, and the refrigerant outlet 6 is provided.
4b is set so that it is on the upstream side of the flow path,
In the heat exchanger 64, the primary-side refrigerant flowing through the flow passage 71 side and the bypass refrigerant introduced from the bypass passage 73 side are in counterflow.

According to this structure, when the liquid refrigerant condensed in the heat exchanger 62 flows through the flow passage 71 to the expansion valve 63, a part of the primary side refrigerant flows from the bypass passage 73. After being branched and decompressed in the expansion valve 65, it is introduced to the refrigerant inlet 64a side of the heat exchanger 64, while flowing through the heat exchanger 64 from the refrigerant inlet 64a side toward the refrigerant outlet 64b side, It exchanges heat with the liquid refrigerant flowing through the flow path 71 and supercools it.

Therefore, the primary-side refrigerant supercooled in the heat exchanger 64 is decompressed in the expansion valve 63, so that the generation of gas refrigerant in the depressurized primary-side refrigerant is reduced as much as possible. The primary side refrigerant is introduced into the plate heat exchanger Z ₁₆ side in a state close to the liquid single phase as much as possible. As a result, even if a special gas-liquid distribution promoting mechanism is not provided on the plate-type heat exchanger Z ₁₆ side, the gas-liquid distribution can be made uniform among the paths of the plate-type heat exchanger Z _16. the plate-type improved heat exchange performance of the heat exchanger Z ₁₆ is, and by extension in which attained the performance improvement of the refrigeration apparatus X ₁ configured with the plate heat exchanger Z _16.

(B-17) Seventeenth Embodiment FIG. 26 shows a refrigerant circuit diagram of a refrigerating machine X _{2 according to} a seventeenth embodiment of the present invention. This freezer X
₂ is a compressor 61 and a heat exchanger 62 that functions as a condenser.
The expansion valve 63 and the plate heat exchanger Z ₁₇ functioning as an evaporator are operatively connected to each other through the flow passages 71 and 72. A refrigerant having a property of phase change between phases, for example, a Freon refrigerant is used, and its aim is to make the plate heat exchanger similar to the refrigerant circuit X _{1 according} to the 16th embodiment. The point is to improve the performance of the entire system by improving the heat exchange performance of Z ₁₇ .

In the refrigerant circuit X ₁ of the sixteenth embodiment, the flow passage 71 is provided with the heat exchanger 64, and the heat exchanger 64 self-cools the primary refrigerant to While the refrigerant is supercooled, in the refrigerant circuit X ₂ of this embodiment, a heat exchanger using an external heat source between the heat exchanger 62 and the expansion valve 63 in the flow path 71. It is equipped with 66.

Therefore, the refrigerant circuit X of this embodiment is₂To
The liquid refrigerant condensed in the heat exchanger 62
On the way to the expansion valve 63 through the flow path 71
Is supercooled by the heat exchanger 66, and
The primary side refrigerant is decompressed in the expansion valve 63.
With, it is possible to generate gas refrigerant in the primary side refrigerant after depressurization.
As much as possible, the primary side refrigerant is as close to a liquid single phase as possible
In the state, the plate type heat exchanger Z₁₇Be introduced on the side
become. As a result, the plate heat exchanger Z₁₇Special on the side
Even without providing another gas-liquid distribution promoting mechanism, the plate-type heat exchange
Exchanger Z₁₇Achieves uniform gas-liquid distribution between each pass
The plate type heat exchanger Z mentioned above ₁₇Heat exchange
Performance is improved, and by extension, the plate heat exchanger Z₁₇Equipped with
Refrigerating device X₂The performance of
It

(B-18) Eighteenth Embodiment FIG. 27 shows a refrigerant circuit diagram of a refrigerating machine X _{3 according to} an eighteenth embodiment of the present invention. This freezer X
₃ is a compressor 61 and a heat exchanger 62 that functions as a condenser.
The expansion valve 63 and the plate heat exchanger Z ₁₈ functioning as an evaporator are operatively connected to each other through the flow passages 71 and 72. A refrigerant having a property of phase change between phases, for example, a chlorofluorocarbon refrigerant is used, and the purpose thereof is the refrigerant circuits X ₁ and X _{2 according to} the sixteenth and seventeenth embodiments.
Similarly, the point is to improve the performance of the entire system by increasing the heat exchange performance of the plate heat exchanger Z ₁₈ .

In the refrigerant circuits X ₁ and X ₂ of the sixteenth and seventeenth embodiments, the primary side refrigerant (liquid refrigerant) from the heat exchanger 62 is overheated before flowing into the expansion valve 63. By cooling, the primary side refrigerant after expansion in the expansion valve 63 is brought into a state close to a liquid single phase as much as possible, so that gas-liquid distribution in the plate heat exchangers Z ₁₆ and Z ₁₇ is made uniform. In the refrigerant circuit X ₃ of this embodiment, the gas-liquid separator 67 is provided between the expansion valve 63 and the plate heat exchanger Z _{18 in} order to improve the heat exchange performance. The gas refrigerant separated here is returned to the flow path 72 side through the bypass 70, so that the primary-side refrigerant is in a liquid single-phase state with respect to the plate heat exchanger Z ₁₈ side. It was designed to be introduced.

[0130] Thus, in the refrigerant circuit X ₃ in this embodiment, the plate heat exchanger Z _{1 8} to the primary side refrigerant liquid the plate from being introduced in a single phase state heat exchanger Z
_Even if a special gas-liquid distribution promoting mechanism is not provided on the ₁₈ side, uniform distribution of gas-liquid between the paths of the plate heat exchanger Z ₁₈ is realized, and the heat of the plate heat exchanger Z ₁₈ is correspondingly increased. Exchange performance is improved, and by extension, the plate heat exchanger Z
_It is possible to improve the performance of the refrigerating apparatus X _{3 including} the ₁₈ .

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a plate heat exchanger according to a first embodiment of the present invention.

FIG. 2 is a cross-sectional view of a plate heat exchanger according to a second embodiment of the present invention.

FIG. 3 is a cross-sectional view of a plate heat exchanger according to a third embodiment of the present invention.

FIG. 4 is a sectional view of a plate heat exchanger according to a fourth embodiment of the present invention.

FIG. 5 is a cross-sectional view of a plate heat exchanger according to a fifth embodiment of the present invention.

FIG. 6 is a cross-sectional view of a plate heat exchanger according to a sixth embodiment of the present invention.

FIG. 7 is a cross-sectional view of a plate heat exchanger according to a seventh embodiment of the present invention.

FIG. 8 is a cross-sectional view of a plate heat exchanger according to an eighth embodiment of the present invention.

FIG. 9 is a sectional view of an essential part of a plate heat exchanger according to a ninth embodiment of the present invention.

FIG. 10 is a perspective view of the flow rate adjusting member shown in FIG.

11 is a view taken in the direction of arrows XI-XI in FIG.

FIG. 12 is a sectional view of an essential part of a plate heat exchanger according to a tenth embodiment of the present invention.

13 is a perspective view of the flow rate adjusting member shown in FIG.

FIG. 14 is a perspective view showing another structural example of the flow rate adjusting member.

FIG. 15 is a cross-sectional view of essential parts of a plate heat exchanger according to an eleventh embodiment of the present invention.

16 is a perspective view of the flow rate adjusting member shown in FIG.

FIG. 17 is a cross-sectional view of essential parts of a plate heat exchanger according to a twelfth embodiment of the present invention.

FIG. 18 is a cross-sectional view of essential parts of a plate heat exchanger according to a thirteenth embodiment of the present invention.

19 is a cross-sectional view of main parts of XIX-XIX in FIG.

FIG. 20 is a cross-sectional view of essential parts of a plate heat exchanger according to a fourteenth embodiment of the present invention.

21 is a cross-sectional view of the main part XXI-XXI of FIG. 20. FIG.

FIG. 22 is a distribution diagram of the liquid refrigerant in the plate heat exchanger.

FIG. 23 is a distribution diagram of the liquid refrigerant in the plate heat exchanger.

FIG. 24 is a cross-sectional view of essential parts of a plate heat exchanger according to a fifteenth embodiment of the present invention.

FIG. 25 is a refrigerant circuit diagram of a refrigeration system including a plate heat exchanger according to a sixteenth embodiment of the present invention.

FIG. 26 is a refrigerant circuit diagram of a refrigeration system including a plate heat exchanger according to a seventeenth embodiment of the present invention.

FIG. 27 is a refrigerant circuit diagram of a refrigeration system including a plate heat exchanger according to an eighteenth embodiment of the present invention.

FIG. 28 is an external perspective view of a conventional general plate heat exchanger.

FIG. 29 is a cross-sectional view of a conventional general plate heat exchanger.

[Explanation of symbols]

1 and 2 are side plates, 3 is a heat transfer plate, 4 is a first flow path, 5
Is the second flow path, 6 is the inlet side collecting portion, 7 is the outlet side collecting portion, 8
Is an inflow port, 9 is an outflow port, 10 is an inflow port, 11 is an outflow port 1, 12a to 12l are paths, 13 is a path group, 15 is an inflow pipe, 16 is a flow rate adjusting member, 17 is a vertical wall member, 18 is Base material,
21 is a flow divider, 22-25 is a branch pipe, 26 is an expansion member, 27-29 are partition plates, 31-42 are branch pipes, 45 is an inflow pipe, 46 is a through hole, 47 is an inflow pipe, 48 and 49. the through hole 50 is the outer flow path, 51 and 52 through hole, 53 a refrigerant inlet pipe, X ₁ to X ₃ is a refrigerant circuit diagram, Z ₁ to Z ₁₈ is a plate heat exchanger.

Claims (9)

[Claims] 1. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. A plate type heat exchanger configured as described above, characterized in that a shunt (21) is provided on the upstream side of the inlet side collecting portion (6) of each of the paths (12a) to (12l). Heat exchanger. 2. The plurality of branch pipes (22) to the downstream side of the flow distributor (21) according to claim 1.
(25), (31) to (42) are provided, and each branch pipe (2
2) to (25) and (31) to (42) are connected to the outlet ends of the paths (12a) to (12a) in the inlet side collecting portion (6).
A plate heat exchanger characterized in that the plate heat exchangers are arranged at a predetermined interval in a row direction of (12 l). 3. The branch pipes (22) to (25), (31) to (42) according to claim 2.
The plate-type heat exchanger having the outlet end thereof directed upward or downward. 4. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. The plate heat exchanger configured as described above, wherein a plurality of branch pipes (22) to (2) are provided on the upstream side of the medium with respect to the inlet side collecting portion (6) of each of the paths (12a) to (12l).
5), (31) to (42) are provided in a vertical direction in multiple stages, and the outlet ends of the respective branch pipes (22) to (25) and (31) to (42) are inside the inlet side collecting section (6). In the plate heat exchanger, the plates (12a) to (12l) in (1) are arranged at predetermined intervals in the direction in which they are arranged. 5. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. The plate heat exchanger configured as described above, wherein each of the paths (12) of the first medium (R ₁ ) flowing into the inlet side collecting portion (6) flows into the inlet side collecting portion (6).
A plate heat exchanger characterized in that a flow rate adjusting member (16) for adjusting the inflow rate to the sides (a) to (12l) is provided. 6. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. The plate-type heat exchanger configured as described above, wherein the first medium (R ₁ ) is circulated from the inlet side of the inlet side gathering portion (6) to the back side in the inlet side gathering portion (6). After that, a plate heat exchanger is provided with a flow direction control member (45, 47) for controlling the flow direction so as to further flow from the back side to the inlet side. 7. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. A plate heat exchanger configured as described above, wherein the refrigerant inlet pipe (53) has its outlet end located at the back of the inlet side collecting part (6).
The plate heat exchanger is characterized in that it is inserted and arranged from the inlet side of the. 8. A plurality of heat transfer plates (3), (3),
.. between the heat transfer plates (3), (3), ...
First channel (4) and second channel (5) are alternately formed in
So that the flow paths (4) and (5) are laminated in the layer direction.
Forming a plurality of paths, each path on the side of the first flow path (4)
In (12a) to (12l), the first phase change between gas-liquid two phases
1 medium (R₁) In the ascending direction, and the second flow path
The second medium flowing in the descending direction through each path on the (5) side
(R₂) With a pre-configured heat exchanger.
Heat exchanger (Z₁₆, Z₁₇), The plate type heat
Exchanger (Z ₁₆, Z₁₇) Is used as an evaporator
In refrigeration equipment, Plate heat exchanger (Z₁₆, Z₁₇) Upstream,
The first medium (R₁) Is expanded by the expansion means (63)
A cooling means (64, 66) for cooling in front
And a refrigerating device. 9. A plurality of heat transfer plates (3), (3),
.. are laminated so that the first flow paths (4) and the second flow paths (5) are alternately formed between the heat transfer plates (3), (3) ,. A plurality of paths are formed in the layer direction for each of the flow paths (4) and (5), and the paths (12a) to (12l) on the first flow path (4) side have a phase change between gas-liquid two phases. So that the first medium (R ₁ ) flowing in the rising direction is made to flow, and heat is exchanged with the second medium (R ₂ ) flowing in the descending direction in each path on the second flow path (5) side. A plate type heat exchanger (Z ₁₈ ) configured as described above, wherein the plate type heat exchanger (Z ₁₈ ) is used as an evaporator, the upstream side of the plate type heat exchanger (Z ₁₈ ). On the side, a gas-liquid separator (67) that separates the first medium (R ₁ ) into gas and liquid after expansion by the expansion means (63) is provided, and only the liquid medium is plate-type heat exchange A refrigerating apparatus, which is configured to be introduced into a container (Z ₁₈ ).