JP6091601B2 - Plate heat exchanger and refrigeration cycle apparatus equipped with the same - Google Patents

Description

  The present invention relates to a plate heat exchanger and a refrigeration cycle apparatus including the plate heat exchanger.

  Conventionally, a plurality of heat transfer plates are stacked via inner fins, and different fluids are alternately passed through each flow path formed between the heat transfer plates to heat the heat transfer plates. There are stacked plate-type heat exchangers to be replaced (for example, see Patent Documents 1 and 2).

  This type of plate heat exchanger has a passage hole that serves as an inlet for fluid, and the fluid that has flowed from the passage hole passes through the inner fin, but the flow velocity of the inner fin on the side far from the passage hole is slow, The flow velocity closer to the passage hole becomes faster. For this reason, the flow velocity distribution is likely to occur in the flow path, and the region where the speed is low becomes a fluid retaining portion and does not function as a heat transfer surface, and the flow drift increases pressure loss. Therefore, in patent documents 1-3, the rectification | straightening part which makes uniform flow velocity distribution is provided.

Sho 59-229193 (6th page, Fig. 4) Sho 63-140295 (6th page, Fig. 1) JP 2001-41676 (2nd page, 3rd page, FIGS. 8 to 10)

  Both of the rectifying sections of Patent Documents 1 and 2 are configured by combining a plurality of plate-like members in a complicated manner, and there is a problem that the fabrication is difficult and the cost is high.

  The rectifying member of Patent Document 3 is formed by cutting and forming a single plate-like member or bending a plurality of plate-like members, and further simplification of the structure is required.

  The present invention has been made in view of these points, and an object thereof is to provide a low-cost plate heat exchanger capable of making the flow velocity distribution uniform with a simple structure and a refrigeration cycle apparatus including the same. And

In the plate heat exchanger according to the present invention, the first flow path and the second flow path are alternately formed between a plurality of heat transfer plates provided at predetermined intervals, and the first flow path and the second flow path are formed. A plate-type heat exchanger in which inner fins are respectively provided in a path, wherein each of the plurality of heat transfer plates includes a first fluid inlet to the first flow path or a second fluid inlet to the second flow path. An upstream passage hole and a downstream passage hole serving as an outlet for the first fluid from the first channel or an outlet for the second fluid from the second channel, the first channel and the second channel of each, is arranged upstream rectification plate partitioning the respective flow path into an upstream side passage hole side and the inner fin side, the upstream-side regulating plate has a plurality of openings serving as the first fluid or the second fluid flow path It has a section, so that towards the side farther from the side a short distance between the upstream passage hole the flow path resistance by the upstream-side regulating plate is reduced Is adjusted the opening area of the plurality of openings, also, in which towards the side farther from the side distance is close to the upstream side passage holes are disposed inclined so as to approach the inner fin side.

  The plate-type heat exchanger of the present invention can provide a low-cost plate-type heat exchanger that can make the flow velocity distribution uniform with a simple structure by arranging the rectifying plates.

It is a figure which shows the general inner fin type plate type heat exchanger in embodiment of this invention. It is a figure which shows an example of the inner fin 2 of FIG. It is a principal part expansion perspective view of FIG. It is explanatory drawing of the baffle plate 30 of FIG. It is explanatory drawing of the modification 1 of the baffle plate 30 of FIG. It is explanatory drawing of the modification 2 of the baffle plate 30 of FIG. It is explanatory drawing of the modification 3 of the baffle plate 30 of FIG. It is explanatory drawing of the modification 4 of the baffle plate 30 of FIG. It is explanatory drawing of the modification 5 of the baffle plate 30 of FIG. It is a principal part expansion perspective view of the plate type heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view of the plate type heat exchanger which concerns on Embodiment 3 of this invention. It is a perspective view of the modification of the plate type heat exchanger which concerns on Embodiment 3 of this invention. It is a figure which shows the refrigerant circuit of the refrigerating-cycle apparatus which concerns on Embodiment 4 of this invention.

Embodiment 1 FIG.
FIG. 1 is a view showing a general inner fin type plate heat exchanger according to an embodiment of the present invention. FIG. 2 is a diagram illustrating an example of the inner fin 2 of FIG. 3 is an enlarged perspective view of a main part of FIG. In FIG. 1 to FIG. 3 and the drawings to be described later, the same reference numerals are the same or equivalent, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.

  The inner fin type plate heat exchanger (hereinafter simply referred to as “plate heat exchanger”) has a plurality of heat transfer plates 1 having flat heat transfer surfaces. The plurality of heat transfer plates 1 are provided at predetermined intervals, and a first flow path A through which the first fluid flows and a second flow path B through which the second fluid flows between the plurality of heat transfer plates 1. Are formed alternately. In FIG. 1, the flow direction of the first fluid is x, and the flow direction of the second fluid is y. And each of the 1st flow path A and the 2nd flow path B is provided with the inner fin 2 which accelerates | stimulates heat transfer. Moreover, the side plate 3 which plays the role of reinforcement is provided in the both ends of the lamination direction of the several heat exchanger plate 1, and the whole is integrally joined with the several heat exchanger plate 1 and the inner fin 2. As shown in FIG. Yes.

  Here, offset fins are used for the inner fins 2. The offset fin has a configuration in which the peaks and valleys in the plate width direction of the corrugated fins are shifted by half a mountain in the plate width direction every predetermined pitch in the longitudinal direction of the plate and are formed in a staggered pattern.

  The plurality of heat transfer plates 1 and the two side plates 3 are made of a substantially rectangular flat plate made of metal, and have a first fluid inflow pipe 4 and a first fluid at one of the four side plates 3. An outflow pipe 5 for one fluid, an inflow pipe 6 for the second fluid, and an outflow pipe 7 for the second fluid are provided.

  In addition, the heat transfer plate 1 has a first fluid inlet pipe 4, a first fluid outlet pipe 5, a second fluid inlet pipe 6, and a second fluid outlet pipe 7 at positions corresponding to the first fluid inlet pipe 4. An opening 11, a second opening 12, a third opening 13, and a fourth opening 14 are formed. The first opening 11, the second opening 12, the third opening 13, and the fourth opening 14 are an inlet of the first channel A, an outlet of the first channel A, and an inlet of the second channel B, respectively. The outlet of the second flow path B is formed.

  In the heat transfer plate 1, a closing portion 21 (see FIG. 3) is provided around the first opening 11 and the second opening 12 or the third opening 13 and the fourth opening 14. The blocking portion 21 has the third opening 13 and the fourth opening 14 sealed in the first flow path A through which the first fluid flows, and the first opening in the second flow path B through which the second fluid flows. 11 and the second opening 12 are sealed. In this way, the second fluid is prevented from flowing into the first flow path A, and the first fluid is prevented from flowing into the second flow path B.

Hereinafter, of the four openings formed in the heat transfer plate 1, the opening communicating with the inner fin 2 is referred to as a passage hole. Thus, the first flow path A, the first opening 1 1 and a second opening 1 2 is a passage hole, the second flow path B, the third opening 1 3 and the fourth opening 1 4 is a passage hole. Hereinafter, of the two passage holes provided in one heat transfer plate 1, a passage hole serving as a fluid inlet is referred to as an upstream passage hole 20 a and a passage hole serving as a fluid outlet is referred to as a downstream passage hole 20 b. In the following, when the first flow path A and the second flow path B are not distinguished, they are simply referred to as flow paths. Similarly, when the first fluid and the second fluid are not distinguished, they are simply referred to as fluids.

  The flow velocity of the fluid flowing into the flow path from the upstream side passage hole 20a is generally fast in the vicinity of the upstream side passage hole 20a, and slow in the distance. For this reason, the fluid hardly flows in the region M far from the upstream passage hole 20a, and the fluid stays. Therefore, since the flow rate of the fluid flowing downstream from the region M is reduced, the effective heat transfer area is reduced.

  In order to improve the non-uniformity in the flow rate distribution accompanying the uneven flow velocity distribution in the short direction (XY direction in FIG. 3) of the heat transfer plate 1, the following configuration is adopted. That is, in each of the first flow path A and the second flow path B, a plate-like rectifying plate 30 for equalizing the flow velocity is disposed between the upstream passage hole 20a and the inner fin 2. The rectifying plate 30 is disposed on the heat transfer plate 1 so as to partition the upstream side passage hole 20a and the inner fin 2 from each other.

4A and 4B are explanatory views of the current plate 30 in FIG. 3, in which FIG. 4A is a front view, FIG. 4B is a cross-sectional view taken along the line A-A in FIG. 4 is an explanatory diagram for explaining the characteristics of the current plate 30 in FIG. 3, and the number, scale, and the like of the openings 31 do not correspond exactly to those in FIG. 3. This is the same in the explanatory view of the current plate 30 described later.
In the rectifying plate 30, a plurality of openings 31 are formed at intervals in the partition direction of the rectifying plate 30 (longitudinal direction of the rectifying plate 30). In the rectifying plate 30, the opening areas of the plurality of openings 31 are adjusted so that the flow path resistance of the rectifying plate 30 decreases as the distance from the side closer to the upstream passage hole 20a in the rectifying plate 30 increases. ing. Specifically, the opening areas of the plurality of openings 31 are formed larger in the order in which the rectifying plate 30 is located on the side farther from the side closer to the upstream passage hole 20a.

  In FIG. 4, a plurality of openings 31 (31a, 31b) are formed in a circular shape here, and the diameter of the opening 31a on the region A1 side far from the upstream passage hole 20a is close to the upstream passage hole 20a. It is formed larger than the diameter of the opening 31b on the A2 side. Here, the opening area is adjusted in two stages, but the opening area is not limited to two stages, and a plurality of stages may be used.

  With this configuration, the opening area of each opening 31a located on the region A1 side far from the upstream passage hole 20a is larger than each opening 31b located on the region A2 side near the upstream passage hole 20a. Therefore, the flow resistance on the region A1 side where the flow velocity is slow in the rectifying plate 30 is smaller than that on the region A2 side where the flow velocity is fast, and the fluid easily flows into the region M. Thereby, the flow velocity in the XY direction can be made uniform, and the retention of fluid in the region M can be improved. As a result, the downstream portion of the region M in the heat transfer plate 1 can function as a heat transfer surface, and the effective heat transfer area can be expanded.

  Here, the length L1 in the XY direction of the region A1 in which the opening 31 is formed large may be shorter than the length L2 in the same direction of the closing portion 21. The flow path formed by the blocking portion 21 and the rectifying plate 30 is narrower than the flow path between the upstream passage hole 20a and the rectifying plate 30 and hardly flows into the region M. For this reason, a region of L1 having a low resistance is provided in the rectifying plate 30, but if L1 is made larger than L2, the fluid flows out from the opening 31 in L1 on the near side before flowing into the region M, and the speed is increased. It is difficult to make uniform. By making L1 smaller than L2, the speed can be made more uniform than when L1> L2.

  The blocking portion 21 becomes a resistance of the fluid flowing into the region M. In the present invention, the opening area of the rectifying plate 30 is adjusted, so that the increase in pressure loss due to the resistance can be reduced. For this reason, it is effective in improving the deviation of the flow velocity distribution. The shape of each opening 31 is not limited to a circle, and may be a square, a rectangle, or the like. In FIG. 4, the diameters of the openings 31a in the region A1 are all the same, and the diameters of the openings 31b are also the same in the region A2, but the diameter gradually increases as the distance from the upstream passage hole 20a increases. You may comprise so that it may become large.

  Here, if the rectifying plate 30 is not provided, an increase in the flow velocity due to the drift causes an increase in pressure loss. However, since the flow velocity increase due to the drift can be suppressed by arranging the current plate 30, pressure loss can be reduced.

  As described above, in the first embodiment, the plate-like rectifying plate 30 is arranged between the upstream passage hole 20a provided in the heat transfer plate 1 and the inner fin 2 so as to partition the both. The current plate 30 was provided with a plurality of openings 31 at intervals in the partition direction. Furthermore, the opening area of the plurality of openings 31 was adjusted so that the flow resistance when the fluid passed through the rectifying plate 30 was smaller on the side farther than the side closer to the upstream passage hole 20a. Thereby, the flow velocity distribution can be made uniform, the uneven flow rate on the inlet side of the inner fin 2 can be improved, the effective heat transfer area can be increased, and the pressure loss can be reduced.

  In addition, since the current plate 30 has a simple structure in which a hole is formed in the plate-like member, it is easy to manufacture, and the effect of expanding the effective heat transfer area and reducing pressure loss can be realized at a low cost. It is possible to reduce the weight.

  Moreover, since the rectifying plate 30 has a simple structure in which holes are formed in the plate-like member, the size of each opening 31 for making the flow velocity distribution uniform can be easily adjusted. Further, although it is inexpensive even if the rectifying plate 30 is made of a single component, if it is molded integrally with the inner fin 2, the number of components is reduced, and therefore the cost is further reduced. Further, the rectifying plate 30 can be joined to the heat transfer plate 1 by brazing, and the plate heat exchanger can be manufactured at low cost by integral brazing.

  Moreover, in the current plate 30, the partition which is a part between the opening parts 31 has the effect | action which mixes the fluid which passed the opening part 31, and acts on equalization of the flow rate suitably.

  Further, since the rectifying plate 30 is arranged upright so as to partition between the upstream side passage hole 20a and the inner fin 2, the installation of the rectifying plate 30 functioning as a distribution improving mechanism does not require a wide space, It can be installed in a small space.

  Further, the region M in which retention is likely to occur is a portion where the flow rate of the fluid is slow when the rectifying plate 30 is not provided. For this reason, when the fluid is water and the plate heat exchanger is used as an evaporator, the temperature is locally lowered and becomes a starting point of freezing. However, in the first embodiment, since the flow velocity of the fluid in the region M can be increased, freezing can be suppressed and quality can be improved.

Thus, since the plate heat exchanger of the first embodiment has effects such as high heat transfer, low pressure loss, and high reliability, a CO ₂ refrigerant having a small evaporation capacity, a hydrocarbon having a large pressure loss, A combustible refrigerant such as a low GWP refrigerant can also be used.

  Moreover, since the offset fin was used for the inner fin 2, the following effects are acquired. The offset fin is a heat transfer promoting body having a low pressure loss and has a small resistance, so that the fluid easily flows linearly. For this reason, if the current plate 30 is not provided and the fluid does not flow into the region M, the fluid hardly flows into the region downstream from the region M. In this case, the effective heat transfer area is reduced as described above. However, it is possible to reduce pressure loss and expand the effective heat transfer area by using offset fins with low pressure loss as the heat transfer surface and further combining with the rectifying plate 30.

  Moreover, the rise of pressure loss can be suppressed by improving the heat transfer by the leading edge effect of the offset fin. The leading edge effect refers to an effect that can be realized by actively using the leading edge portion of the flat plate as a heat transfer portion by utilizing the property that the heat transfer coefficient is good at the leading edge portion of the flat plate. That is, when a flat plate is placed in the flow, the boundary layer is thin at the leading edge of the flat plate and becomes thicker toward the downstream. For this reason, heat transfer becomes favorable in the front edge part of a flat plate where the thickness of a boundary layer is thin.

  Further, the current plate 30, the offset fins, and the heat transfer plate 1 having a flat heat transfer surface can be manufactured by pressing, and a plate heat exchanger having high heat transfer performance with low pressure loss can be manufactured at low cost. If the plate heat exchanger has a low pressure loss, less power is required to operate the fluid. For this reason, the capacity | capacitance of the pump and compressor used as the motive power source which flows a fluid into a plate type heat exchanger can be made small.

  In addition, when an offset fin is used for the inner fin 2, the above effect can be obtained, but the inner fin of the present invention is not limited to the offset fin. In addition, the inner fin 2 of the present invention includes not only fins formed separately from the heat transfer plate 1 but also fins formed by corrugating the surface of the heat transfer plate 1.

  In addition, the uniform distribution of the flow rate is necessary on the inlet side of the flow path and not on the outlet side. Therefore, it is possible to reduce the cost by providing the rectifying plate 30 only on the inlet side, not on both the inlet side and the outlet side.

  Note that the number, shape, and arrangement of the openings 31 of the rectifying plate 30 are not limited to the structure shown in FIG. 1, and various modifications can be made, for example, as in Modifications 1 to 4 below. Each of the modifications has a configuration in which a plurality or one opening 31 is formed so that the flow resistance when passing through the rectifying plate 30 is smaller on the side farther than the side near the upstream passage hole 20a. . In any modification, there is an effect of equalizing the flow velocity.

(Modification 1)
FIGS. 5A and 5B are explanatory views of a first modification of the rectifying plate 30 in FIG. 3, where FIG. 5A is a front view, FIG. 5B is a cross-sectional view taken along line AA in FIG.
In FIG. 4 , the plurality of openings 31 are provided in each of the region A1 and the region A2, but one opening 31 (31a, 31b) may be provided in each of the region A1 and the region A2. FIG. 5 shows an example in which the shape of the opening 31 is rectangular. Also in this configuration, as in FIG. 4, the opening area 31a on the region A1 side far from the upstream passage hole 20a is made larger than the opening portion 31b on the region A2 side near the upstream passage hole 20a. ing.

(Modification 2)
6A and 6B are explanatory diagrams of a second modification of the current plate 30 in FIG. 3, in which FIG. 6A is a front view, FIG. 6B is a cross-sectional view taken along the line AA in FIG.
In FIG. 4, the diameter of the opening 31 is different in each of the region A1 and the region A2, but in FIG. 6, all the openings have the same diameter, and the number of the openings 31 is increased as the distance from the upstream passage hole 20a increases. I try to increase it. In the above description, the opening area of the opening 31 is increased in two steps from the side closer to the upstream passage hole 20a to the side farther from the side closer to the upstream side passage hole 20a. However, the number of steps is not limited to two. Shows an example of three stages.

(Modification 3)
7A and 7B are explanatory views of Modification 3 of the rectifying plate 30 in FIG. 3, in which FIG. 7A is a front view, FIG. 7B is a cross-sectional view taken along line AA in FIG.
In FIG. 7, the number of openings 31 is one, and the opening area of the rectifying plate 30 increases as the distance from the upstream passage hole 20a increases from the shorter side.

(Modification 4)
In the fourth modification, the flow path resistance when passing through the rectifying plate 30 is smaller on the side farther from the upstream passage hole 20a due to the outer shape of the rectifying plate 30.

8A and 8B are explanatory views of a fourth modification of the current plate 30 in FIG. 3, in which FIG. 8A is a front view, FIG. 8B is a plan view, and FIG. 8C is a side view.
The rectifying plate 30 in FIG. 8 is such that the height of the rectifying plate 30 in the stacking direction (left and right direction in FIG. 1) decreases as the distance from the side closer to the upstream passage hole 20a in the rectifying plate 30 increases. Is formed.

  Although the rectifying plate 30 shown in FIGS. 3 to 8 is a simple plate, the rectifying plate 30 may be configured as in Modification 5 shown in FIG.

(Modification 5)
9A and 9B are explanatory views of Modification 5 of the rectifying plate 30 in FIG. 3, where FIG. 9A is a front view, FIG. 9B is an end view of the AA cut portion of FIG. .
The rectifying plate 30 has a configuration in which a pair of leg portions 32 extending in parallel to each other in a direction orthogonal to the rectifying plate 30 is provided from both ends of the rectifying plate 30 in a short direction (a direction orthogonal to the partition direction). .
By making each of the pair of leg portions 32 a joint surface with the heat transfer plate 1, the rectifying plate 30 becomes a support column. And by adjusting the length of a pair of leg part 32, the area of a pair of leg part 32, the heat-transfer plate 1, and a joining surface can be adjusted according to required intensity | strength. For this reason, by adjusting the length of the pair of leg portions 32 according to the strength required around the passage hole having a low peel strength, and using the adjusted pair of leg portions 32 as the joint surface, the periphery of the upstream passage hole 20a Can be improved to the required strength.

  Further, when the rectifying plate 30 is formed into the shape shown in FIG. 9, it can be manufactured at a low cost because it can be manufactured by a single press if it is manufactured by a press.

Embodiment 2. FIG.
The second embodiment is different from the first embodiment with respect to the arrangement of the current plate 30. Other points are the same as in the first embodiment. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the second embodiment.

FIG. 10 is an enlarged perspective view of a main part of the plate heat exchanger according to Embodiment 2 of the present invention.
In the second embodiment, the rectifying plate 30 is inclined and provided on the heat transfer plate 1 so that the distance between the rectifying plate 30 and the inner fin 2 decreases from the side closer to the upstream passage hole 20a toward the far side. .

  With this configuration, the same effect as in the first embodiment can be obtained, and the fluid that has flowed into the flow path from the upstream side passage hole 20a can be guided to the region M. This makes it easier for the fluid to flow to the region M than when the rectifying plate 30 is disposed orthogonal to the flow direction as in the first embodiment. For this reason, in addition to the adjustment of the opening area of the opening 31 in the first embodiment, the flow velocity distribution can be adjusted more finely by adjusting the inclination angle of the rectifying plate 30 in the second embodiment.

Embodiment 3 FIG.
In the first and second embodiments, the rectifying plate 30 is disposed between the upstream passage hole 20 a and the inner fin 2 in each of the first flow path A and the second flow path B. In the third embodiment, the rectifying plate 30 is also disposed between the downstream passage hole 20b and the inner fin 2. Other points are the same as in the first and second embodiments. Note that the modification applied to the same components as those in the first embodiment is similarly applied to the third embodiment.

FIG. 11 is a perspective view of a plate heat exchanger according to Embodiment 3 of the present invention.
As shown in FIG. 11, the rectifying plate 30 is also arranged between the downstream passage hole 20 b and the inner fin 2.

  According to the third embodiment, the same effects as those of the first and second embodiments can be obtained, and the rectifying plates 30 are arranged on both the upstream side and the downstream side. Side distribution is improved. Thereby, compared with the case where the baffle plate 30 is arrange | positioned only at the inlet_port | entrance of a fluid, a higher effect is acquired about expansion of an effective heat-transfer area, reduction of a pressure loss, and suppression of freezing.

  Further, since the rectifying plate 30 is located at the entrance / exit of the flow path, the flow of the heat exchanger for fluid such as an air conditioner capable of switching between cooling and heating or an air conditioner capable of simultaneous cooling and heating is changed. It is effective when applied to a device whose direction is switched in the opposite direction.

Further, when the fluid undergoes a phase change in the plate heat exchanger and the density of the fluid changes between the inlet side and the outlet side, the inlet side rectifying plate 30 and the outlet side rectifying plate 30 are matched to the density change. The total opening area of the openings 31 (the sum of the opening areas of all the openings 31) may be made different. For example, when the inlet side is liquid and the outlet side is steam (that is, the density is lower than that of the liquid and the pressure loss when passing through the opening 31 tends to increase), as shown in FIG. the total opening area of the rectifying plate 30 on the left side) of 12, may be larger than the total opening area of the rectifying plate 30 on the inlet side (right side in FIG. 12). Thereby, the pressure loss can be reduced.

Embodiment 4 FIG.
The fourth embodiment relates to a refrigeration cycle apparatus to which any of the plate heat exchangers of the first to third embodiments is applied.

FIG. 13 is a diagram showing a refrigerant circuit of the refrigeration cycle apparatus 40 according to Embodiment 4 of the present invention.
The refrigeration cycle apparatus 40 is a general refrigeration cycle apparatus including a compressor 41, a condenser (including a gas cooler) 42, a throttle device 43, and an evaporator 44. The plate heat exchanger according to any one of the first to third embodiments is applied as one or both of the condenser 42 and the evaporator 44 of the refrigeration cycle apparatus 40.

  According to the fourth embodiment, by providing the plate heat exchanger according to the first to third embodiments, the refrigeration cycle apparatus 40 with high energy saving and reliability and low cost can be obtained. The refrigerant circuit shown in FIG. 13 is an example, and the refrigerant circuit to which the plate heat exchanger of the present invention is applied is not limited to the configuration shown in FIG. For example, a refrigerant circuit that can be switched between cooling and heating by providing a four-way valve may be used, or a refrigerant circuit that can be operated simultaneously with cooling and heating.

  As an application example of the present invention, the present invention can be used in many industrial and household equipment equipped with a plate heat exchanger, such as air conditioning, power generation, and food sterilization equipment.

  DESCRIPTION OF SYMBOLS 1 Heat transfer plate, 2 Inner fin, 3 Side plate, 4 Inflow pipe, 5 Outflow pipe, 6 Inflow pipe, 7 Outflow pipe, 11 1st opening, 12 2nd opening, 13 3rd opening, 14 4th opening, 20a Upstream passage hole, 20b Downstream passage hole, 21 Blocking portion, 30 Rectifier plate, 31 Opening portion, 31a Opening portion, 31b Opening portion, 32 Leg portion, 40 Refrigeration cycle device, 41 Compressor, 42 Condenser, 43 Restriction Apparatus, 44 Evaporator, A 1st flow path, A1 area | region, A2 area | region, B 2nd flow path, M area | region.

Claims (13)

The first flow path and the second flow path are alternately formed between a plurality of heat transfer plates provided at a predetermined interval, and inner fins are provided in the first flow path and the second flow path, respectively. A plate heat exchanger,
Each of the plurality of heat transfer plates includes an upstream passage hole serving as an inlet of the first fluid to the first flow path or an inlet of the second fluid to the second flow path, and an opening from the first flow path. A downstream passage hole serving as an outlet of the first fluid or an outlet of the second fluid from the second flow path,
In each of the first flow path and the second flow path, an upstream rectifying plate that divides each flow path into the upstream passage hole side and the inner fin side is disposed,
Said upstream-side regulating plate, the first fluid or a plurality of openings serving as the passage of the second fluid, it is the upstream side of the distance is on the side farther from the near side to the upstream side passage hole The opening areas of the plurality of openings are adjusted so that the flow resistance by the rectifying plate is reduced , and the side farther from the side closer to the upstream passage hole is closer to the inner fin side. A plate-type heat exchanger that is inclined to approach . Wherein an upstream-side regulating plate and the same downstream straightening plate, further plate heat exchanger according to claim 1, further comprising between the inner fin and the downstream passage hole. The upstream-side regulating plate and said plurality of shaped openings have different downstream straightening plate is the same total open area, the more claim 1, further comprising between the inner fin and the downstream passage hole Plate heat exchanger. Of the two rectifying plates of the upstream rectifying plate and the downstream rectifying plate, the total opening area of the rectifying plate having the lower fluid density when passing through the rectifying plate is the one having the higher fluid density. The plate heat exchanger according to claim 3 , wherein the plurality of openings of each of the two rectifying plates are formed so as to be larger than a total opening area of the rectifying plates. The first flow path and the second flow path are alternately formed between a plurality of heat transfer plates provided at a predetermined interval, and inner fins are provided in the first flow path and the second flow path, respectively. A plate heat exchanger,
Each of the plurality of heat transfer plates includes an upstream passage hole serving as an inlet of the first fluid to the first flow path or an inlet of the second fluid to the second flow path, and an opening from the first flow path. A downstream passage hole serving as an outlet of the first fluid or an outlet of the second fluid from the second flow path,
In each of the first flow path and the second flow path, an upstream rectifying plate that divides each flow path into the upstream passage hole side and the inner fin side is disposed,
Said upstream-side regulating plate, the first fluid or a plurality of openings serving as the passage of the second fluid, it is the upstream side of the distance is on the side farther from the near side to the upstream side passage hole The opening areas of the plurality of openings are adjusted so that the flow path resistance due to the rectifying plate is reduced ,
A plate further comprising a downstream rectifying plate between the downstream passage hole and the inner fin, wherein the upstream rectifying plate and the plurality of openings have the same shape but different total opening areas. Type heat exchanger. Of the two rectifying plates of the upstream rectifying plate and the downstream rectifying plate, the total opening area of the rectifying plate having the lower fluid density when passing through the rectifying plate is the one having the higher fluid density. The plate heat exchanger according to claim 5 , wherein the plurality of openings of each of the two rectifying plates are formed so as to be larger than a total opening area of the rectifying plates. The plurality of openings of the upstream rectifying plate have a larger opening area on the side farther from the side closer to the upstream passage hole than the plurality of openings of the upstream rectifying plate. The plate heat exchanger according to any one of claims 1 to 6 . The plurality of openings of the upstream rectifying plate are configured to have the same size,
Distribution置個number of said plurality of openings of the upstream straightening vane, before Symbol often claim towards the upstream-side regulating plate and a long distance side than the near side of the upstream-side passage holes 1 to claim 6 The plate type heat exchanger as described in any one of . The plate type heat exchanger according to any one of claims 1 to 8 , wherein the inner fin is an offset fin. The upstream straightening plate further comprises a pair of legs extending parallel to each other in a direction perpendicular from both ends in the direction perpendicular to the partition direction of the upstream-side regulating plate on the upstream rectification plate, the pair of legs The plate-type heat exchanger according to any one of claims 1 to 9 , wherein the plate-type heat exchanger is a joint surface with the heat transfer plate. A plate heat exchanger in which first flow paths and second flow paths are alternately formed between a plurality of stacked heat transfer plates, and inner fins are provided in the first flow path and the second flow path, respectively. Because
Each of the plurality of heat transfer plates includes an upstream passage hole serving as an inlet of the first fluid to the first flow path or an inlet of the second fluid to the second flow path, and an opening from the first flow path. A downstream passage hole serving as an outlet of the first fluid or an outlet of the second fluid from the second flow path,
Each of the first flow path and the second flow path is provided with a rectifying plate that divides each flow path into the upstream passage hole side and the inner fin side,
The rectifying plate has one opening extending in the partition direction of the rectifying plate, and is inclined so that the side farther from the side closer to the upstream passage hole is closer to the inner fin side. Are arranged,
In the plate heat exchanger, the opening area of the opening is adjusted so that the flow resistance by the rectifying plate is smaller on the side farther than the side closer to the upstream passage hole. A plate heat exchanger in which first flow paths and second flow paths are alternately formed between a plurality of stacked heat transfer plates, and inner fins are provided in the first flow path and the second flow path, respectively. Because
Each of the plurality of heat transfer plates includes an upstream passage hole serving as an inlet of the first fluid to the first flow path or an inlet of the second fluid to the second flow path, and an opening from the first flow path. A downstream passage hole serving as an outlet of the first fluid or an outlet of the second fluid from the second flow path,
Each of the first flow path and the second flow path is provided with a rectifying plate that divides each flow path into the upstream passage hole side and the inner fin side,
The rectifying plate is formed to have a lower height on the side of the rectifying plate that is farther away from the side closer to the upstream passage hole, and from the side closer to the upstream side passage hole. The plate type heat exchanger is arranged so as to be inclined so that the far side is closer to the inner fin side . A refrigeration cycle apparatus comprising the plate heat exchanger according to any one of claims 1 to 12 .

Images