JP2011169541A - Plate type heat exchanger and heat pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To uniformize a brazing area of an upper heat transfer plate and a lower heat transfer plate, in a plate type heat exchanger formed by stacking the plates having V-shaped corrugations so that the orientations of the V-shaped corrugations of the plates intersect with each other. <P>SOLUTION: In the plate type heat exchanger 100 formed by stacking the plurality of plates having V-shaped corrugations formed on heat transfer faces thereof so that the orientations of the V-shaped corrugations intersect with each other, the top 9 of the V-shaped corrugation of the upper heat transfer plate 2 and the top 10 of the V-shaped corrugation of the lower heat transfer plate 3 are jointed to each other so as to be shifted from each other only by a predetermined dimension a and intersect with each other, wherein preferably, the dimension a is 1 mm≤a≤7 mm, and more preferably, is 1 mm≤a≤4 mm. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a plate heat exchanger.

  There is a conventional plate heat exchanger in which the apexes of the V-shaped wave portions of the upper and lower plates are matched (for example, see Patent Document 1).

JP 2002-107074 A (page 6-8, FIG. 1)

Conventionally, in a plate heat exchanger, upper and lower plates are joined to each other by brazing each V-shaped wave contact. If the dimension in the longitudinal direction of the V-shaped apex of the upper and lower plates is large, the vicinity of the central part in the short direction is joined at two points, and if the V-shaped apex is matched, one point is joined. When the central part is joined at two points, the dimensions (intervals) in the short direction of these joining points are reduced, and the brazing material at the joining point is joined, so that the brazing area is uneven or unjoined parts are generated. . In such a case, since the bonding strength of the upper and lower plates is lowered, the pressure resistance strength of the heat exchanger is lowered. When the production amount is large, the temperature distribution of the heat exchange in the furnace and the plate is large at the time of brazing, and the brazing at the center of the plate which is difficult to be heated is slow to melt, so the brazing area tends to be uneven.
When the tops of the V-shaped waves are matched with the upper and lower plates and the central part is joined at one point as in Patent Document 1, when the plates are stacked by inverting the same plate in the heat exchanger, the plates are displaced at the time of stacking. There is a problem that the apexes are separated, the brazing area is non-uniform or unjoined, and the pressure resistance is reduced.

The plate heat exchanger of this invention is
In a plate heat exchanger in which a plurality of rectangular plates having a long side and a short side are laminated,
Each plate
When viewed from the laminating direction, the wave shape is displaced in the laminating direction, and the traveling direction is substantially symmetrical with respect to the virtual reference line with respect to the virtual reference line in the long side direction. A wave shape is formed that looks like a plurality of V-shaped irregularities with the virtual reference line on the V-shaped folded portion,
The upper and lower plates adjacent in the stacking direction are:
The layers are stacked so that the V-shaped directions are opposite to each other, and when viewed from the stacking direction, on the virtual reference line, the bottom that is the wave bottom of the upper plate and the wave peak of the lower plate are displayed. The top of the wave of the upper plate, the top of the wave of the upper plate, the bottom of the wave of the lower plate are repeatedly arranged in this order,
The distance a between the bottom of the adjacent upper plate on the virtual reference line and the top of the upper plate when viewed from the stacking direction is:
1mm ≦ a ≦ 7mm
It is characterized by being.

  According to the present invention, a plate heat exchanger with high pressure resistance can be provided.

1 is an external view of a plate heat exchanger 100 according to Embodiment 1. FIG. The front view (a) of the heat-transfer plate of Embodiment 1, AA sectional drawing (b), and the enlarged view (c) of AA cross section. The front view (a), BB sectional drawing (b) of the heat-transfer plate of Embodiment 2, and the enlarged view (c) of BB cross section. The front view (a) of the heat exchanger plate with a large R dimension of Embodiment 3, and the front view (b) of the heat exchanger plate with a small R dimension. The front view (a) of the 1st example of a heat exchanger plate of Embodiment 4, and the front view (b) of the 2nd example of a heat exchanger plate.

Embodiment 1 FIG.
The first embodiment will be described with reference to FIGS. FIG. 1 is a diagram illustrating an appearance of a plate heat exchanger 100 according to the first embodiment.
Fig.1 (a) is a side view (a), FIG.1 (b) is a front view (b).
The reinforcing side plate 1 shown in FIG. 1B is located on the outermost side and is provided with a fluid inlet / outlet pipe. FIG. 1B shows an inflow pipe 5 for the first fluid, an inflow pipe 6 for the second fluid, an outflow pipe 7 for the first fluid, and an outflow pipe 8 for the second fluid.
FIG.1 (c) is the upper side heat-transfer plate 2 which comprises the flow path of the 1st fluid and the 2nd fluid.
FIG. 1 (d) shows the lower heat transfer plate 3. The lower heat transfer plate 3 is placed so that the wave shape is opposed to the upper heat transfer plate 2 to form a flow path for the first fluid and the second fluid.
By alternately stacking the upper heat transfer plate 2 and the lower heat transfer plate 3 side by side, the flow paths of the first fluid and the second fluid are alternately and repeatedly formed. Hereinafter, when it is not necessary to distinguish the upper heat transfer plate 2 and the lower heat transfer plate 3, they may be simply referred to as plates.
FIG. 1E shows the reinforcing side plate 4. The reinforcing side plate 4 is located on the outermost side.
FIG. 1 (f) is a diagram showing a state in which the upper heat transfer plate 2 and the lower heat transfer plate 3 are overlapped.

(Basic structure of plate heat exchanger 100)
As shown in FIG. 1, the plate heat exchanger 100 has a V-shaped heat transfer surface provided with passage holes (inflow pipes 5, inflow pipes 6, outflow pipes 7, and outflow pipes 8) serving as fluid inlets and outlets at four corners. It is a plate type heat exchanger formed by laminating a plurality of plates having the following wave so that the V-shapes cross each other.
Each plate has a rectangular shape having a long side and a short side.

  Each of the plates serving as the upper heat transfer plate 2 and the lower heat transfer plate 3 has a wave shape that is displaced in the stacking direction (the X direction in FIG. 1A), and has a virtual reference line 101 in the long side direction as a boundary. Since the wave traveling direction 21 is formed substantially symmetrically with respect to the virtual reference line 101, a plurality of Vs having the virtual reference line 101 on the V-shaped folded portion when viewed from the stacking direction (X direction). A wave shape that looks like a letter-shaped irregularity is formed. Moreover, as shown in FIG.1 (f), the upper side heat-transfer plate 2 and the lower side heat-transfer plate 3 which adjoin in the lamination direction are laminated | stacked so that the direction of V character may mutually reverse.

  FIG. 2 is a diagram illustrating a stacked state of the upper and lower plates. FIG. 2A is a view corresponding to FIG. 1F and shows a state in which the upper heat transfer plate 2 and the lower heat transfer plate 3 are laminated. The wave shape of the upper heat transfer plate 2 is indicated by a solid line. The wave shape of the lower heat transfer plate 3 is indicated by a dotted line. FIG. 2B shows a cross section AA in FIG. FIG. 2C is an enlarged view of FIG.

As shown in FIG. 2 (a), the upper heat transfer plate 2 and the lower heat transfer plate 3 adjacent in the stacking direction are on the virtual reference line 101 when viewed from the stacking direction.
The bottom P (1) which is the wave bottom of the upper heat transfer plate 2,
The top P (2) which is the top of the wave of the lower heat transfer plate 3,
The top P (3) which is the top of the wave of the upper heat transfer plate 2,
Bottom P (4), which is the bottom of the wave of the lower heat transfer plate 3,
Are repeatedly arranged in this order.
In this state, the V-shaped apex 9 (corresponding to the bottom P (1)) of the adjacent upper heat transfer plate 2 on the virtual reference line 101 and the wave of the lower heat transfer plate 3 when viewed from the stacking direction. The V-shaped apex 10 (corresponding to the apex P (2)) is joined by being shifted by a “predetermined dimension a” so that the V-shape intersects in the plate longitudinal direction. Thereby, since these vertexes can be overlapped in the longitudinal direction, the brazing area can be made constant, so that the strength of the brazing portion is improved, and a heat exchanger having a stable strength even in mass production can be provided.

(Example of dimension a)
(1) Specifically, the dimension a is effectively 1 to 4 mm (1 mm ≦ a ≦ 4 mm). If the dimension a is shorter than 1 mm, there is a case where the distance between the V-shaped apex of the upper plate and the V-shaped apex of the lower plate is increased when the plates are stacked, and the V-shaped portions do not intersect with each other. When the thickness is in the range of 1 to 4 mm, the brazing area can be increased. The dimension a is adjusted in the range of 1 to 4 mm to adjust the brazing area according to the required strength. The dimension a is preferably in the range of 1 to 7 mm.
(2) When the dimension a is larger than 7 mm, the V-shaped apex is not joined at the V-shaped apex or the V-shaped apex of the upper plate is formed by the V-shaped apex adjacent to the target V-shaped apex of the lower plate Therefore, the brazing area cannot be kept constant.

  If the dimension a is in the range of 1 to 7 mm, more preferably in the range of 1 to 4 mm, the brazing area can be kept constant.

  As described above, in the plate heat exchanger 100 in which a plurality of plates having V-shaped waves on the heat transfer surface are stacked so that the V-shapes cross each other, the wave V of the upper heat transfer plate 2 is The character vertices 9 and the V-shaped vertices 10 of the lower heat transfer plate 3 were joined so as to cross each other with a predetermined dimension a. Here, the dimension a is preferably 1 mm ≦ a ≦ 7 mm, and more preferably 1 mm ≦ a ≦ 4 mm.

(1) If the plate heat exchanger 100 of the first embodiment, operating pressure of high CO ₂ can be used, hydrocarbons, it is possible the use of large fluid pressure drop and low GWP refrigerant.
(2) In the plate heat exchanger 100 according to the first embodiment, the vertexes of the V-shaped waves of the upper and lower plates are shifted to a predetermined dimension in the longitudinal direction, so that these vertices are not separated during plate lamination and brazing is performed. It can be done reliably.
(3) Further, the overlapping portion of the V-shape can be configured uniformly, and at the time of brazing, the overlapping portion can easily hold the brazing material by capillary force, and the brazing area of this portion can be made uniform. For this reason, variation in the brazing area in the plate can be suppressed, and the strength of the heat exchanger is improved. When the strength in the plate is improved, the plate thickness of the plate and the reinforcing side plate can be reduced, and the material cost can be reduced.
(4) Moreover, since the brazing area of the V-shaped portion can be made constant, the velocity distribution of the fluid inside the plate becomes uniform, the stagnation region is reduced, and the effective heat transfer area is increased.
(5) Further, since the speed difference between the region where the fluid flows and the stagnation region can be eliminated, the pressure loss can be reduced.
(6) Further, by improving the heat exchange performance, the necessary number of plates of the heat exchanger for the necessary capacity of the air conditioner can be minimized.
(7) It also becomes possible to provide plate heat exchange with high heat exchange efficiency. According to an air conditioner equipped with this heat exchanger, it is inexpensive and can reduce power consumption and CO2 emissions. .
(8) In addition, by reducing the stagnation region, refrigerating machine oil, sludge, clogging of dust, and the like remaining in the heat exchanger can be suppressed, and its reliability is improved.

Embodiment 2. FIG.
Next, a second embodiment will be described with reference to FIG. In the first embodiment described above, the wave V-shaped apex of the upper heat transfer plate 2 and the V-shaped apex of the lower heat transfer plate 3 are joined while being shifted by a predetermined dimension a in the plate longitudinal direction, and the brazing area is increased. It is intended to be adjusted. In the second embodiment, a case will be described in which both or one of the crest and bottom of the wave that is the V-shaped apex of the waves of the upper and lower plates are flattened and joined.

  FIG. 3 is a view showing the upper heat transfer plate 2 and the lower heat transfer plate 3 according to the second embodiment. FIG. 3 (a) shows the same state as FIG. 2 (a). Regions 31 to 34 that appear to be “ellipses” in FIG. 3A are joined to each other when flat portions are provided at both the peak and bottom of the wave that is the V-shaped apex of the waves of the upper and lower plates. A flat region is shown. The inside of each ellipse joins. FIG. 3B is a BB cross section of FIG. FIG. 3C is an enlarged view of FIG.

  As shown in FIG. 3, the plate heat exchanger 100 according to the second embodiment includes the bottom P (1) of the upper heat transfer plate 2 adjacent on the virtual reference line 101 and the top P of the lower heat transfer plate 3. At least one of (2) is characterized in that a flat flat portion is formed.

  When the bottom of the wave (upper heat transfer plate 2) or the top of the wave (lower heat transfer plate 3) at the top of the V-shape of the wave of the upper and lower plates is flattened and joined, Since they are joined, the area of the V-shaped apex portion where the brazing area tends to be non-uniform can be made constant.

Moreover, since the V-shaped parts of the upper and lower plates are joined by the surface, the strength is improved. By uniformizing the brazing area and surface bonding, it is possible to provide a heat exchanger with stable strength even in mass production. Further, when the area of the flat portion 11 at the V-shaped apex of the wave of the upper and lower plates is increased, the strength is improved, and when the area is reduced, the pressure loss is reduced. For the fluid having a large operating pressure such as CO ₂ and a small pressure loss, the former The latter is suitable for fluids with low operating pressure and large pressure loss, such as hydrocarbons and low GWP, and the area of the flat portion at the V-shaped apex may be adjusted according to the fluid used. Up to now, the case where both the V-shaped vertices of the wave of the upper and lower plates are flattened and joined has been described, but the same effect can be obtained when either one of the upper and lower plates is flattened.

Embodiment 3 FIG.
Next, Embodiment 3 will be described with reference to FIG. In the second embodiment, the wave crest (the top of the lower heat transfer plate 3) and / or the bottom (the bottom of the upper heat transfer plate 2), which is the V-shaped apex of the waves of the upper and lower plates, are flattened. The case of joining was explained. In the third embodiment, a case will be described in which the V-shaped folded portion at the V-shaped apex of the wave of the upper and lower plates is formed by an arc of R1 to 4 mm.

  4A and 4B, the solid line indicates the center line 12 (corresponding to the ridge line) of the wave bottom of the upper heat transfer plate 2, and the broken line indicates the center line 13 of the wave peak of the lower heat transfer plate 3. (Corresponding to a ridgeline). In the plate heat exchanger 100 of the third embodiment, as shown in FIGS. 4A and 4B, the wave shape of each plate is the wave at the position of the virtual reference line 101 when viewed from the stacking direction. A V-shaped folded portion 102 corresponding to a V-shaped folded portion of the top portion P (2) and the bottom portion P (1) is formed by an arc having a radius R in a range of 1 mm ≦ R ≦ 4 mm. .

  4A shows a case where R is large (for example, R = 4 mm), and FIG. 4B shows a case where R is small (for example, R = 1 mm). The R dimension of the V-shaped folded portion 102 at the V-shaped apex of the wave of the upper and lower plates is 1 to 4 mm. Thereby, the brazing area at the V-shaped apex can be reduced.

When R exceeds 4 mm, the brazing area becomes excessive and pressure loss increases. When the upper and lower plates are joined at one V-shaped apex, if the wave pitch is reduced, the brazing portion at the apex and the brazing material adjacent to each other in the width direction are welded to fill the flow path. In order to prevent this, it is effective to form the R dimension of the V-shaped apex at 1 to 4 mm.
When the plate V-shaped angle θ (FIG. 4A) increases, the overlapping area of the V-shaped plates of the upper and lower plates increases in the width direction, causing the same problem as when the wave pitch is small. This problem can be prevented by making it smaller.

  In this way, the R dimension may be adjusted according to the specifications of the wave angle θ and the wave pitch. If the R dimension is small, the V-shaped overlapping area of the upper and lower plates is small, so that the capillary force can be increased, so that the brazing material can be easily aggregated and the variation in the brazing area can be suppressed. When combined with the first embodiment, it is effective in suppressing variations in the brazing area.

Embodiment 4 FIG.
A fourth embodiment will be described with reference to FIG. In the third embodiment, the case where the R dimension of the V-shaped apex of the wave of the upper and lower plates is 1 to 4 mm and the upper and lower plates are joined has been described. Embodiment 4 explains the case where the protrusion part made to protrude in the direction where a V character becomes thin at the V character vertex of an upper and lower plate is formed.

  5A and 5B, the solid line indicates the center line 12 (corresponding to a ridge line) of the wave bottom of the upper heat transfer plate 2, and the broken line indicates the center line 13 of the wave peak of the lower heat transfer plate 3. (Corresponding to a ridgeline). FIG. 5A shows a case where the protruding portion 103 is protruded in the direction in which the V shape becomes narrower at the V shape apex of the upper and lower plates. FIG.5 (b) shows the case where the protrusion part 103 is protruded in either one of the upper and lower plates.

  In the plate heat exchanger 100 of the fourth embodiment, the wave shape of each plate corresponds to a V-shaped folded portion between the top and bottom of the wave at the position of the virtual reference line 101 when viewed from the stacking direction. At least one of the V-shaped folded portion 102 (bottom portion) and the V-shaped folded portion 102 (top) has a protruding portion 103 that protrudes in the direction of the V-shaped folded portion (the direction in which the V-shape narrows). .

  As shown in FIG. 5 (a), the protruding portion 103 protrudes in the direction in which the V-shaped apex forms the bottom of the upper plate, and the V-shaped apex in the lower plate protrudes in the direction in which the V-shaped narrows. When the portion 103 is protruded, the V-shaped vertices of the upper and lower plates overlap at a predetermined distance when the plates are stacked. For this reason, the apex is not separated, the brazing area can be made constant, and the flow path width can be reduced due to the aggregation of the rows. As shown in FIG. 5B, the same effect as in FIG. 5A can be obtained even if the protrusion 103 is protruded in the direction in which the V-shaped apex is narrowed on only one of the upper and lower plates.

  The plate heat exchangers described in the first to fourth embodiments can be used for many industrial and household devices equipped with a plate heat exchanger, such as air conditioning, power generation, and food sterilization treatment equipment. . For example, the present invention can be used for the radiator, the evaporator, or any of the heat pump device in which a compressor, a radiator, an expansion mechanism, and an evaporator are connected by piping.

  1 reinforcing side plate, 2 upper heat transfer plate, 3 lower heat transfer plate, 4 reinforcing side plate, 5 first fluid inflow pipe, 6 second fluid inflow pipe, 7 first fluid outflow pipe, 8 Second fluid outflow pipe, 9 V-shaped apex of wave bottom of upper heat transfer plate, 10 V-shaped apex of wave peak of lower heat transfer plate, 11 Flat portion of V-shaped apex of wave of upper and lower plates, 12 Center line of wave bottom of upper heat transfer plate, 13 Center line of wave peak of lower heat transfer plate, 21 Wave traveling direction, 100 Plate heat exchanger, 101 Virtual reference line, 102 V-shaped folding Part, 103 protrusion part.

Claims (6)

In a plate heat exchanger in which a plurality of rectangular plates having a long side and a short side are laminated,
Each plate
When viewed from the laminating direction, the wave shape is displaced in the laminating direction, and the traveling direction is substantially symmetrical with respect to the virtual reference line with respect to the virtual reference line in the long side direction. A wave shape is formed that looks like a plurality of V-shaped irregularities with the virtual reference line on the V-shaped folded portion,
The upper and lower plates adjacent in the stacking direction are:
The layers are stacked so that the V-shaped directions are opposite to each other, and when viewed from the stacking direction, on the virtual reference line, the bottom that is the wave bottom of the upper plate and the wave peak of the lower plate are displayed. The top of the wave of the upper plate, the top of the wave of the upper plate, the bottom of the wave of the lower plate are repeatedly arranged in this order,
The distance a between the bottom of the adjacent upper plate on the virtual reference line and the top of the upper plate when viewed from the stacking direction is:
1mm ≦ a ≦ 7mm
A plate type heat exchanger characterized by the above. The distance a is
1mm ≦ a ≦ 4mm
The plate heat exchanger according to claim 1, wherein   The flat part is formed in at least one of the bottom part of the upper plate and the top part of the lower plate that are adjacent to each other on the virtual reference line. Plate heat exchanger. The wave shape of each plate is
When viewed from the stacking direction, the V-shaped folded portion corresponding to the V-shaped folded portion of the top and bottom of the wave at the position of the virtual reference line has a radius R in the range of 1 mm ≦ R ≦ 4 mm. The plate heat exchanger according to any one of claims 1 to 3, wherein the plate heat exchanger is formed in an arc. The wave shape of each plate is
When viewed from the stacking direction, at least one of the V-shaped folded portions corresponding to the V-shaped folded portions of the top and bottom of the wave at the position of the virtual reference line is in a direction in which the V-shape is narrowed. It has a protrusion part which protrudes, The plate type heat exchanger in any one of Claims 1-4 characterized by the above-mentioned. In the heat pump device in which the compressor, the first heat exchanger, the expansion mechanism, and the second heat exchanger are connected by piping,
As at least one of the first heat exchanger and the second heat exchanger,
A plurality of rectangular plates having a long side and a short side are laminated,
Each plate
When viewed from the laminating direction, the wave shape is displaced in the laminating direction, and the traveling direction is substantially symmetrical with respect to the virtual reference line with respect to the virtual reference line in the long side direction. A wave shape is formed, which appears as a plurality of V-shaped irregularities in one direction of the virtual reference line, with the virtual reference line on the V-shaped folded portion,
The upper and lower plates adjacent in the stacking direction are:
The layers are stacked so that the V-shaped directions are opposite to each other, and when viewed from the stacking direction, on the virtual reference line, the bottom that is the wave bottom of the upper plate and the wave peak of the lower plate are displayed. The top of the wave of the upper plate, the top of the wave of the upper plate, the bottom of the wave of the lower plate are repeatedly arranged in this order,
The distance H between the bottom of the adjacent upper plate and the top of the upper plate on the virtual reference line when viewed from the stacking direction is:
1mm ≦ H ≦ 7mm
A heat pump device comprising a plate heat exchanger.

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