JP2010216754A - Plate type heat exchanger and refrigerating air-conditioning device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve strength of a plate-type heat exchanger while keeping heat exchanging performance of the plate-type heat exchanger. <P>SOLUTION: This plate-type heat exchanger 20 is formed by stacking a plurality of plates 2, 3. Each of the plates 2, 3 has a first inflow hole 5 as an inlet of a first fluid, a first outflow hole 6 as an outlet of the first fluid, a second inflow hole 7 as an inlet of a second fluid, and a second outflow hole 8 as an outlet of the second fluid at four corners. A first flow channel in which the first fluid flows and a second flow channel in which the second fluid flows, are formed between the stacked plates 2, 3 adjacent to each other to exchange heat between the first fluid and the second fluid. A longitudinal length L1 of each of the plates 2, 3 is four times or more of its lateral length L2. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to, for example, a plate heat exchanger in which a plurality of plates are stacked, and a refrigeration air conditioner including the plate heat exchanger.

Patent Document 1 describes a plate heat exchanger in which the shape of the fluid inflow hole and the shape of the outflow hole are elliptical. Patent Document 1 describes a plate heat exchanger in which the diameter of the fluid inflow hole and the diameter of the outflow hole are the same.
Patent Document 2 describes a plate heat exchanger in which the diameter of the fluid inflow hole and the diameter of the fluid outflow hole are different from each other. Patent Document 2 describes a plate heat exchanger in which a reinforcing member is provided at a fluid inflow hole and a fluid outflow hole to increase the strength.

JP-A-9-72685 Japanese translation of PCT publication No. 7-508581

The conventional plate heat exchanger has the following problems (1) to (3).
(1) Plate type heat exchangers generally have a low strength due to the thin plate thickness.
(2) In the plate heat exchanger in which the reinforcing member is provided in the inflow hole and the outflow hole, dust is easily clogged in the inflow hole and the outflow hole.
(3) When the flow rate of the fluid is large, the plate type heat exchanger has a limit in the flow velocity at the fluid inlet and outlet holes. Therefore, in order to process a large amount of fluid, it is necessary to widen the opening area between the inflow hole and the outflow hole. However, in order to increase the opening area between the inflow hole and the outflow hole, the width between the inflow hole and the outflow hole must be increased. If the width between the inflow hole and the outflow hole is increased, the strength is reduced and the heat transfer area is reduced. That is, the plate heat exchanger having a wide opening area between the inflow hole and the outflow hole has low strength and poor heat exchange performance.

  For example, an object of the present invention is to increase the strength of a plate heat exchanger while maintaining the heat exchange performance of the plate heat exchanger.

The plate heat exchanger according to the present invention is, for example,
It is a plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates includes
A first inflow hole serving as an inlet of the first fluid on either end side in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid on an end side in a longitudinal direction opposite to the first inflow hole;
A second inflow hole serving as an inlet for the second fluid on either end side in the longitudinal direction;
A second outflow hole serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow hole;
Each of the plates has a first flow path that spreads the first fluid flowing in from the first inflow hole in a short direction and flows to the first outflow hole between the plates stacked next to each other, and the first The first fluid flowing in the first flow path is formed by forming one flow path with a second flow path that spreads the second fluid flowing in from the inflow hole in the short direction and flows to the second outflow hole. Heat exchange between the fluid and the second fluid flowing through the second flow path;
Each of the plates is characterized in that the length in the longitudinal direction is at least four times the length in the lateral direction.

  In the plate heat exchanger according to the present invention, the length in the longitudinal direction is at least four times the length in the short direction. For this reason, the stress concerning the edge part of a plate can be suppressed. Therefore, the plate heat exchanger according to the present invention has high strength.

The side view of the plate type heat exchanger 20. FIG. The front view of the side plate 1 for reinforcement. The front view of the 2nd plate 2. FIG. The front view of the 1st plate 3. FIG. The front view of the side plate 4 for reinforcement. FIG. 3 is an exploded perspective view of the plate heat exchanger 20. The figure which shows the size of the plates 2 and 3 of the plate-type heat exchanger 20. FIG. The figure which shows the relationship between the ratio of the length of the longitudinal direction of a plate 2, 3, and a transversal direction, and stress. The figure which shows the relationship between the ratio of the length of the longitudinal direction of the plates 2, 3 and a transversal direction, and the weight of the plate-type heat exchanger 20. FIG. The figure which shows the plates 2 and 3 which made the diameter of the primary inflow / outlet hole smaller than the diameter of the secondary inflow / outlet hole. The figure which shows the plate-type heat exchanger 20 which made the diameter of the 1st inflow hole 5 smaller about the plates 2 and 3 by the side plate 1 side for reinforcement. The figure which shows the size of the plates 2 and 3 which brought the inflow / outlet hole to four corners. Explanatory drawing of the flow of the 1st fluid of the 1st plate 3 which brought the inflow / outlet hole to the four corners. Explanatory drawing of the unevenness | corrugation 9 of the 1st plate 3 which brought the inflow / outlet hole to the four corners. The figure which shows the unevenness | corrugation 9 of the 2nd plate 2 which brought the inflow / outlet hole to the four corners. The figure which shows the unevenness | corrugation 9 of the 1st plate 3 which brought the inflow / outlet hole to the four corners. The figure which shows the plates 2 and 3 which made the primary side inflow / outlet hole and the secondary side inflow / outlet hole different shapes. The figure which shows the plates 2 and 3 which made the primary side inflow / outlet hole and the secondary side inflow / outlet hole different shapes. The figure which shows the plates 2 and 3 which made the primary side inflow / outlet hole and the secondary side inflow / outlet hole different shapes. The comparison figure with the case where a primary side inflow / outflow hole is made into the same shape, and the case where a primary side inflow / outlet hole is made into a different shape. The figure which shows the plates 2 and 3 which made the primary side inflow / outlet hole and the secondary side inflow / outlet hole the same shape, and made shapes other than a circle | round | yen. The figure which shows the plates 2 and 3 which made the primary side inflow / outflow hole and the secondary side inflow / outlet hole the same shape, and made shapes other than a circle | round | yen. The figure which shows the plates 2 and 3 which made the primary side inflow / outflow hole and the secondary side inflow / outlet hole the same shape, and made shapes other than a circle | round | yen. The figure which shows the plates 2 and 3 which made the primary side inflow / outflow hole and the secondary side inflow / outlet hole the same shape, and made shapes other than a circle | round | yen. The figure which shows the heating hot-water supply system 29. FIG.

Embodiment 1 FIG.
1 to 6 are explanatory diagrams of the plate heat exchanger 20 according to the first embodiment. FIG. 1 is a side view of the plate heat exchanger 20. FIG. 2 is a front view of the reinforcing side plate 1. FIG. 3 is a front view of the second plate 2. FIG. 4 is a front view of the first plate 3. FIG. 5 is a front view of the reinforcing side plate 4. FIG. 6 is an exploded perspective view of the plate heat exchanger 20.

As shown in FIG. 1, the plate heat exchanger 20 is formed by laminating a plurality of plates 2 and 3. In the plate heat exchanger 20, reinforcing side plates 1 and 4 are laminated on the foremost surface (A side in FIG. 1) and the backmost surface (B side in FIG. 1), respectively.
As shown in FIGS. 3 and 4, each of the plates 2 and 3 is formed in a substantially rectangular plate shape. Each of the plates 2 and 3 is provided with a first inflow hole 5 on one end side (upper side) of the substantially rectangular long side direction (longitudinal direction). Each plate 2, 3 is provided with a first outflow hole 6 on the end side (lower side) in the longitudinal direction opposite to the first inflow hole 5. Each plate 2, 3 is provided with a second inflow hole 7 on the same end side (lower side) in the longitudinal direction as the first outflow hole 6. Each plate 2, 3 is provided with a second outflow hole 8 on the same end side (upper side) in the longitudinal direction as the first inflow hole 5. Here, each plate 2 and 3 is provided with a first inflow hole 5 and a first outflow hole 6 on the same end side (left side) in a substantially rectangular short side direction (short side direction). Each plate 2, 3 is provided with a second inflow hole 7 and a second outflow hole 8 on the end side (right side) in the short direction opposite to the first inflow hole 5 and the first outflow hole 6. .
That is, the plates 2 and 3 are provided with the first inflow hole 5, the first outflow hole 6, the second inflow hole 7, and the second outflow hole 8 at the four corners. In addition, the 1st inflow hole 5 and the 1st outflow hole 6 are called a primary side inflow / outlet hole. Similarly, the second inflow hole 7 and the second outflow hole 8 are called secondary inflow / outflow holes.

As shown in FIGS. 2 and 5, the reinforcing side plates 1 and 4 are also formed in a substantially rectangular plate shape like the plates 2 and 3. As shown in FIG. 2, the reinforcing side plate 1 stacked on the foremost surface has a first inflow hole 5 (first inflow pipe) and a first outflow hole 6 (first outflow) at the same positions as the plates 2 and 3. Tube), a second inflow hole 7 (second inflow pipe), and a second outflow hole 8 (second outflow pipe).
On the other hand, as shown in FIG. 5, the reinforcing side plate 4 stacked on the backmost surface is not provided with the first inflow hole 5, the first outflow hole 6, the second inflow hole 7, and the second outflow hole 8. In FIG. 5, the positions of the first inflow hole 5, the first outflow hole 6, the second inflow hole 7, and the second outflow hole 8 are indicated by broken lines on the reinforcing side plate 4. These are not provided.

The plates 2 and 3 and the reinforcing side plate 1 are laminated so that the first inflow holes 5, the first outflow holes 6, the second inflow holes 7, and the second outflow holes 8 overlap each other. The second plate 2 and the first plate 3 are alternately stacked.
The plates 2 and 3 and the reinforcing side plates 1 and 4 have substantially the same substantially rectangular shape.

As shown in FIGS. 3 and 4, a plurality of V-shaped concave portions and convex portions (uneven portions 9) are arranged in the longitudinal direction on the plates 2 and 3. The unevenness 9 is formed in a V shape having both end portions 13 at both ends in the short direction and having a turning point 12 at a position shifted from the both end portions 13 in the longitudinal direction. The pitch (width) of the unevenness 9 is W shown in FIG. In the second plate 2 and the first plate 3, the directions of the irregularities 9 are arranged in opposite directions. That is, in the second plate 2, the unevenness 9 is formed in a V shape having the folding point 12 below the both end portions 13, whereas in the first plate 3 the folding point is located above the both end portions 13. Irregularities 9 are formed in a V shape having 12 (inverted V shape).
As described above, by alternately laminating the plates 2 and 3 having the irregularities 9 formed in the reverse V-shape, a flow path with good heat transfer efficiency is formed between the plates 2 and 3. That is, as shown in FIG. 6, the first flow path through which the first fluid flowing in from the first inflow hole 5 flows to the first outflow hole 6 is between the back surface of the second plate 2 and the front surface of the first plate 3. It is formed. Similarly, a second flow path in which the second fluid flowing in from the second inflow hole 7 flows to the second outflow hole 8 is formed between the back surface of the first plate 3 and the front surface of the second plate 2.
The first fluid flowing through the first flow path and the second fluid flowing through the second flow path are heat-exchanged via the plates 2 and 3.

  FIG. 7 is a view showing the sizes of the plates 2 and 3 of the plate heat exchanger 20. In FIG. 7, the length L1 indicates the length of the plates 2 and 3 in the longitudinal direction. The length L2 indicates the length of the plates 2 and 3 in the short direction. The length L3 indicates the length from the first inflow hole 5 to the plate end in the short direction closer to the first inflow hole 5. The length L4 indicates the length from the first outflow hole 6 to the plate end in the short direction closer to the first outflow hole 6. The length L5 indicates the length from the second inflow hole 7 to the plate end in the short direction closer to the second inflow hole 7. The length L6 indicates the length from the second outflow hole 8 to the plate end in the short direction closer to the second outflow hole 8.

FIG. 8 is a diagram showing the relationship between the ratio of the length between the longitudinal direction and the lateral direction of the plates 2 and 3 and the stress. The horizontal axis of FIG. 8 shows the ratio of the lengths of the plates 2 and 3 in the longitudinal direction to the length direction (length ratio). That is, the horizontal axis of FIG. 8 indicates the length L1 of the plates 2 and 3 in the longitudinal direction 1 / the length L2 of the plates 2 and 3 in the short direction. The vertical axis in FIG. 8 indicates the stress associated with the end portions (peripheral portions) of the plates 2 and 3. In FIG. 8, the stress is expressed as a stress ratio. The reference value of the stress ratio is a value indicated by the second point P from the right in FIG. Here, each point in FIG. 8 indicates a calculated value of the stress ratio with respect to the length ratio. The lines in FIG. 8 indicate values calculated from each point by the least square method.
As shown in FIG. 8, as the length L2 in the short direction of the plates 2 and 3 is shorter than the length L1 in the longitudinal direction of the plates 2 and 3, the stress on the peripheral edge of the plates 2 and 3 is smaller. Become. Therefore, it is desirable to make the length L2 as short as possible with respect to the length L1. In particular, it is desirable to shorten the length L2 so that the length L1 is four times as long as the length L2. However, due to the manufacturing limit of the plate heat exchanger 20, the length L2 cannot be significantly shortened. Therefore, it is desirable to shorten the length L2 so that the length L1 is about 4 to 6.5 times the length L2.
Moreover, the stress concerning the edge part of the plates 2 and 3 becomes small by shortening length L3, L4, L5, and L6. In particular, it is desirable to set the lengths L3, L4, L5, and L6 to 6% or less of the length L2 of the plates 2 and 3 in the short direction. Further, the lengths L3, L4, L5, and L6 may be set to 5.6 mm or less irrespective of the length L2 of the plates 2 and 3 in the short direction. However, the lengths L3, L4, L5, and L6 cannot be remarkably shortened due to the manufacturing limit of the plate heat exchanger 20. Therefore, it is desirable to set the lengths L3, L4, L5, and L6 to 3% or more and 6% or less of the length L2 of the plates 2 and 3 in the short direction. Similarly, it is desirable to set the lengths L3, L4, L5, and L6 to 3 mm or more and 5.6 mm or less.

FIG. 9 is a diagram illustrating the relationship between the ratio of the lengths of the plates 2 and 3 in the longitudinal direction and the short direction and the weight of the plate heat exchanger 20. In particular, in FIG. 9, how much the weight of the plate heat exchanger 20 is reduced when the length of the plates 2 and 3 is fixed and the length of the plates 2 and 3 is shortened. Show if you can.
The horizontal axis in FIG. 9 indicates the ratio (length ratio) between the length in the longitudinal direction and the length in the short direction of the plates 2 and 3, as in FIG. 8. The vertical axis in FIG. 9 indicates the weight reduction rate of the plate heat exchanger 20. The weight reduction rate of the plate heat exchanger 20 is the plate type heat produced by the length ratio (value indicated by the second point P from the right in FIG. 8) selected as the reference value of the stress ratio in FIG. This is a value calculated based on the weight of the exchanger 20.
By shortening the length L2, the plate heat exchanger 20 is reduced in size, so that the plate heat exchanger 20 can be reduced in weight. However, when the length L2 is shortened, not only the weight can be reduced by downsizing, but also the thickness of the plates 2 and 3 and the thickness of the reinforcing side plates 1 and 4 can be reduced, thereby further reducing the weight. That is, when the length L2 is shortened, the strength of the plate heat exchanger 20 is increased. Therefore, the plate thickness of the plates 2 and 3 and the thickness of the reinforcing side plates 1 and 4 can be reduced, and the plate heat exchanger 20 can be reduced in weight.
As a result, as shown in FIG. 9, by shortening the length L2 with respect to the length L1, the plate heat exchanger 20 is reduced in weight more than the weight reduction due to the miniaturization.

As described above, the plate-type heat exchanger 20 according to Embodiment 1 has a shorter length L2 in the short direction of the plates 2 and 3 than a length L1 in the longitudinal direction of the plates 2 and 3, The strength of the plate heat exchanger 20 is high.
Further, in the plate heat exchanger 20 according to the first embodiment, the length (length L3, L4, L5, L6) between the inflow / outlet holes 5, 6, 7, 8 and the plate end is shortened. The strength of the plate heat exchanger 20 is high.
Furthermore, since the strength of the plate heat exchanger 20 is increased, the weight of the plate heat exchanger 20 can be reduced.

  Further, by shortening the length L2 in the short direction, the fluid flowing in from the first inflow hole 5 and the second inflow hole 7 is likely to spread in the short direction. Therefore, there is no need to provide a distribution promoting member for promoting the spreading of the fluid around the first inflow hole 5 and the second inflow hole 7. Further, since the strength of the plate heat exchanger 20 is high, it is not necessary to provide a reinforcing member around the inflow holes (the first inflow hole 5 and the second inflow hole 7). Accordingly, since it is not necessary to provide a distribution promoting member or a reinforcing member, the pressing of the plates 2 and 3 is simplified. Therefore, the manufacturing cost of the plate heat exchanger 20 can be suppressed. Further, variation in the height of the unevenness 9 can be suppressed. That is, the plate type heat exchanger 20 with stable quality can be manufactured.

  In addition, when stagnation occurs in the fluid inside the plate heat exchanger, dust and scale easily accumulate in the stagnation portion. The plates 2 and 3 are easily corroded in the portion where dust and scale are accumulated. In addition, when a heat exchanger that may cause stagnation in the fluid is used in the evaporator, drift occurs and spots are generated in the temperature distribution. Therefore, there is a possibility that a part that freezes is formed. If the part which freezes is made, the intensity | strength of a heat exchanger will fall. However, in the plate heat exchanger 20 according to the first embodiment, the length in the short direction of the plates 2 and 3 is short, and it is difficult for the fluid to stagnate. Therefore, it is difficult for dust and scale to accumulate, and the strength does not decrease. Further, not only in the case where the fluid is water, but also in a fluid (for example, a hydrocarbon-based refrigerant or a low GWP refrigerant) that tends to cause a drift because of its low density and large pressure loss, the plate type according to the first embodiment. The heat exchanger 20 is effective. The chlorofluorocarbon refrigerant is also effective in suppressing the stagnation of refrigeration oil in the heat exchanger. For this reason, the power consumption of the apparatus using the plate-type heat exchanger 20 which concerns on Embodiment 1 can be reduced.

Embodiment 2. FIG.
In the second embodiment, a plate heat exchanger 20 in which the diameter of the primary inflow / outflow holes is smaller than the diameter of the secondary inflow / outflow holes will be described. That is, in the second embodiment, the plate heat exchanger 20 in which the opening area of the primary inflow / outflow holes is made smaller than the opening area of the secondary inflow / outflow holes will be described.

FIG. 10 is a view showing the plates 2 and 3 in which the diameter of the primary inflow / outflow hole is smaller than the diameter of the secondary inflow / outflow hole.
For example, when the plate heat exchanger 20 is used for exchanging heat between a liquid such as water and a refrigerant such as chlorofluorocarbon, the liquid inflow hole (herein referred to as the second inflow hole 7) wears the plate due to erosion. There is a risk of (thinning). Therefore, the diameters of the liquid inflow / outflow holes (second inflow hole 7 and second outflow hole 8) need to be set to a certain size. However, the diameters of the refrigerant inflow and outflow holes (first inflow hole 5 and first outflow hole 6) need to be increased in accordance with the diameters of the liquid inflow and outflow holes (second inflow hole 7 and second outflow hole 8). There is no. That is, the diameter of the first inflow hole 5 and the diameter of the first outflow hole 6 can be smaller than the diameter of the second inflow hole 7 and the diameter of the second outflow hole 8. Thus, when the diameter of the first inflow hole 5 and the diameter of the first outflow hole 6 are reduced, the diameters of the first inflow hole 5 and the diameter of the first outflow hole 6 are reduced. The length in the short direction can be shortened. Therefore, as described in Embodiment 1, the strength of the plate heat exchanger 20 is increased and the plate heat exchanger 20 can be reduced in weight.
The refrigerant is not limited to chlorofluorocarbon, but may be a hydrocarbon refrigerant or a low GWP refrigerant. Moreover, since the CO2 refrigerant has a high operating pressure, the strength of the plate heat exchanger 20 is required. In the case of using this CO2 refrigerant, a configuration in which the refrigerant inflow / outflow hole is smaller than the liquid outflow / inflow hole is particularly effective. Since the CO2 refrigerant has a higher density and a smaller pressure loss than the chlorofluorocarbon refrigerant, the diameters of the first inlet hole 5 and the first outlet hole 6 can be made smaller.

FIG. 11 is a view showing a plate heat exchanger 20 in which the diameters of the first inflow holes 5 are made smaller in the plates 2 and 3 on the reinforcing side plate 1 side.
The plate heat exchanger 20 shown in FIG. 11 is not only the diameter of the primary inflow / outflow hole is smaller than the diameter of the secondary inflow / outflow hole, but also a plate laminated on the reinforcing side plate 1 side. The diameter of the first inflow hole 5 is smaller by 2 or 3. That is, the diameter of the first inflow hole 5 is smaller in the plates 2 and 3 stacked on the reinforcing side plate 1 side than in the plates 2 and 3 stacked on the reinforcing side plate 4 side. In other words, the diameter of the first inflow hole 5 is as small as the plates 2 and 3 stacked on the side where the first fluid flows. In particular, the first inflow holes 5 of the plates 2 and 3 stacked on the reinforcing side plate 1 side are very small like a fine nozzle.
Since the first inflow holes 5 of the plates 2 and 3 stacked on the reinforcing side plate 1 side are extremely small, the flow rate of the first fluid can be increased even when the number of stacked plates 2 and 3 is large. Therefore, the first fluid is easily distributed to the plates 2 and 3 on the reinforcing side plate 4 side.
Moreover, since the diameter of the 1st inflow hole 5 is so large that the plates 2 and 3 laminated | stacked on the side plate 4 side for reinforcement, a 1st fluid distributes equally to the 1st flow path formed by each plate 2 and 3. It is easy to be done.

Embodiment 3 FIG.
In the third embodiment, a plate heat exchanger 20 is described in which the inflow / outlet holes are not only brought close to the plate end in the short direction but also placed near the plate end in the longitudinal direction. That is, in Embodiment 3, the plate heat exchanger 20 in which the inflow / outlet holes are brought close to the four corners (corners) of the plates 2 and 3 will be described.

FIG. 12 is a diagram showing the sizes of the plates 2 and 3 with the inflow and outflow holes brought to the four corners. In FIG. 12, the length L <b> 7 indicates the length from the first inflow hole 5 to the plate end in the longitudinal direction closer to the first inflow hole 5. The length L8 indicates the length from the first outflow hole 6 to the plate end in the longitudinal direction closer to the first outflow hole 6. The length L9 indicates the length from the second inflow hole 7 to the plate end in the longitudinal direction closer to the second inflow hole 7. The length L10 indicates the length from the second outflow hole 8 to the plate end in the longitudinal direction closer to the second outflow hole 8.
The lengths L7, L8, L9, and L10 are set to the same length as the lengths L3, L4, L5, and L6 shown in FIG. Thus, by reducing the lengths L7, L8, L9, and L10, it is possible to further reduce the stress related to the peripheral portion of the plate.

In particular, in the plates 2 and 3 shown in FIG. 12, the diameter of the primary inflow / outflow holes is smaller than the diameter of the secondary inflow / outflow holes. Therefore, the center of the primary inflow / outflow hole is arranged closer to the four corners of the plates 2 and 3 than the center of the secondary inflow / outflow hole.
Thus, by bringing the primary inflow / outflow holes (first inflow holes 5 and first outflow holes 6) having a small diameter toward the four corners of the plates 2 and 3, the first outflow holes 5 to the first outflow holes 6 are arranged. The distance to becomes longer. That is, the first flow path becomes longer. Therefore, the heat transfer area is increased, and the heat exchange performance of the plate heat exchanger 20 is improved.

FIG. 13 is an explanatory diagram of the flow of the first fluid in the first plate 3 with the inflow / outlet holes brought to the four corners. The plate is not limited to the plates 2 and 3 but the first plate 3. This is because the seal portion 11 is shown in FIG. That is, the seal portion 11 is provided at a different position between the second plate 2 and the first plate 3.
By bringing the first inflow hole 5 having a small diameter toward the corners of the plates 2 and 3, the running region 10 can be provided in the vicinity of the first inflow hole 5 in the first flow path. The running region 10 is a narrow region sandwiched between the plate end and the seal portion 11. That is, the width (length L11 from the plate end portion to the seal portion 11) of the running region 10 is narrower than the width (length L2) in the short direction of the first plate 3. The first fluid flowing in from the first inflow hole 5 passes through the narrow run-up region 10, spreads in the short direction of the plate heat exchanger 20, and flows into the first outflow hole 6.
The seal portion 11 is a wall that prevents the first fluid flowing in from the first inflow hole 5 from flowing into the second outflow hole 8. The seal portion 11 is formed so as to protrude in a convex shape in the stacking direction of the plates 2 and 3. Usually, the seal portion 11 is provided in a circular shape around the second outflow hole 8. However, here, the seal part 11 is provided with the first outflow hole 6 and the second inflow hole 7 from the longitudinal end side (upper side) where the first inflow hole 5 and the second outflow hole 8 are provided. It is provided so as to gradually approach the end portion (right side) on the second outflow hole 8 side in the lateral direction toward the end portion side (lower side) in the longitudinal direction. In particular, in FIG. 13, the seal portion 11 is provided in a curved shape that is gradually bent to the right side from the upper side to the lower side.
The seal portion 11 allows the first fluid that has flowed through the run-up region 10 to spread without difficulty to the end portion (right side) on the second outflow hole 8 side in the short direction. That is, the run-up region 10 and the seal portion 11 have a rectifying effect that guides the first fluid to the end (right side) on the second outflow hole 8 side in the short direction. By this rectifying effect, the first fluid can be prevented from stagnation around the seal portion 11 and in the vicinity of the outer periphery of the plates 2 and 3, and the heat exchange performance is improved. Moreover, the pressure loss of the first fluid can be reduced by this rectifying effect. That is, a high-performance plate heat exchanger 20 can be obtained.
Further, when the seal portion 11 is provided in a circle around the second outflow hole 8 as usual, a distribution promoting member is provided around the first inflow hole 5 to prevent the first fluid from drifting. There is a need. For example, the distribution promoting member is formed in a complicated shape such as a radial shape. Therefore, it is difficult to manufacture the plate heat exchanger 20 including the distribution promoting member. However, the plate-type heat exchanger 20 according to the third embodiment is only manufactured by curving the seal portion 11 and is easy to manufacture. Therefore, the plate heat exchanger 20 according to Embodiment 3 has high mass productivity.

FIG. 14 is an explanatory view of the unevenness 9 of the first plate 3 with the inflow / outlet holes brought to the four corners. FIG. 15 is a view showing the unevenness 9 of the second plate 2 with the inflow / outlet holes brought to the four corners. FIG. 16 is a view showing the unevenness 9 of the first plate 3 with the inflow / outlet holes brought to the four corners.
As described in the first embodiment, the plates 2 and 3 have both end portions 13 at both ends in the short direction, and the folding points 12 at positions shifted from the both end portions 13 in the longitudinal direction. A plurality of irregularities 9 formed in a letter shape are arranged in the longitudinal direction. In addition, the folding | turning point 12 of the unevenness | corrugation 9 of the plates 2 and 3 shown in FIG.3, 4 was provided in the center of the transversal direction. That is, the unevenness 9 was formed symmetrically.
Here, in the plates 2 and 3 shown in FIG. 14, the diameter of the primary inflow / outflow holes is smaller than the diameter of the secondary inflow / outflow holes. That is, in FIG. 14, the diameters of the first inflow hole 5 and the first outflow hole 6 are smaller than the diameters of the second inflow hole 7 and the second outflow hole 8. Therefore, as in the plates 2 and 3 shown in FIGS. 3 and 4, when the turning point 12 of the unevenness 9 is provided at the center in the short direction, the unevenness 9 is formed in the vicinity of the first inflow hole 5 and the first outflow hole 6. An area that will not be created. Therefore, in the vicinity of the first inflow hole 5 and the first outflow hole 6 having a small diameter, the turnover point 12 of the unevenness 9 is shifted toward the first inflow hole 5 and the first outflow hole 6 to form the unevenness 9. That is, as shown in FIG. 14, the line 15 connecting the turning points 12 of the unevenness 9 gradually shifts from the center line 14 in the short direction toward the first inflow hole 5 and the first outflow hole 6 in a curved shape. Formed.
Thereby, the unevenness | corrugation 9 can be formed also in the 1st inflow hole 5 and the 1st outflow hole 6 vicinity, and a heat-transfer area becomes long. Therefore, the heat exchange performance of the plate heat exchanger 20 is improved. The plates 2 and 3 are joined to the adjacent plates 2 and 3 at the portion where the unevenness 9 is formed. In general, the plates 2 and 3 are easily peeled in the vicinity of the inflow and outflow holes. However, by forming the unevenness 9 to the vicinity of the inflow and outflow holes, the junction points of the plates 2 and 3 are increased, and peeling of the plates 2 and 3 can be prevented. Further, the turning point 12 of the unevenness 9 gradually moves from the first inflow hole 5 to the center in the short direction and gradually moves from the center in the short direction to the first outflow hole 6. Therefore, the first fluid flowing in from the first inflow hole 5 can be smoothly moved to the center side in the short direction, and can be smoothly moved from the center side in the short direction to the first outflow hole 6. Therefore, the pressure loss of the first fluid can be reduced.
As shown in FIG. 16, also in the second plate 2, similar to the first plate 3, the folding points 12 of the unevenness 9 are set in the vicinity of the first inflow hole 5 and the first outflow hole 6 having a small diameter. The unevenness 9 is formed by shifting toward the inflow hole 5 and the first outflow hole 6.

Embodiment 4 FIG.
In the fourth embodiment, a plate heat exchanger 20 in which the shapes of the primary inflow hole and the secondary inflow hole are deformed will be described.

FIGS. 17 to 19 are views showing the plates 2 and 3 in which the primary inflow / outflow holes and the secondary inflow / outflow holes have different shapes while maintaining a necessary opening area.
In FIG. 17, it was made into the substantially ellipse different from a primary side inflow / outflow hole and a secondary side inflow / outflow hole. In FIG. 18, one circle is divided into two, and one is a primary inflow / outflow hole and the other is a secondary inflow / outflow hole. In FIG. 19, the substantially rectangular shape is divided into two, and one is a primary inflow / outflow hole and the other is a secondary inflow / outflow hole.
In addition, the diameter of the primary inflow / outflow hole shown in FIGS. 17 to 19 is smaller than the diameter of the secondary inflow / outflow hole.

FIG. 20 shows a comparison between the case where the primary inflow / outlet holes and the secondary side inflow / outlet holes have the same shape and the case where the primary side inflow / outlet holes and the secondary side inflow / outlet holes have different shapes. It is. FIG. 20 shows the first outflow hole 6 and the second inflow hole 7 side in the longitudinal direction of the plates 2 and 3. FIG. 20A shows the plates 2 and 3 in which the first outflow hole 6 and the second inflow hole 7 are both circular. On the other hand, FIG. 20 (b) is similar to FIG. 18 except that one circle is divided into two, and one is a primary side inflow / outlet hole and the other is a secondary side inflow / outlet hole. Indicates. Moreover, the diameter of the primary inflow / outflow hole shown in FIGS. 20A and 20B is smaller than the diameter of the secondary inflow / outflow hole.
The first outflow hole 6 shown in FIG. 20A is a circle having a diameter “12 mm”, and the second inflow hole 7 is a circle having a diameter “28 mm”. The first outflow hole 6 and the second inflow hole 7 are separated by “3 mm”. Therefore, the opening area of the first outflow hole 6 is “36πm ² ”, and the opening area of the second inflow hole 7 is “196πm ² ”. The length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “43 mm”.
On the other hand, the first outflow hole 6 shown in FIG. 20B is a ¼ portion of a circle having a diameter of “24 mm”, and the second inflow hole 7 is a ¾ portion of a circle of “31 mm”. The first outflow hole 6 and the second inflow hole 7 are separated by “3 mm”. Therefore, the opening area of the first outflow hole 6 is “36πm ² ”, and the opening area of the second inflow hole 7 is “192πm ² ”. The length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “31 mm”.
That is, the first outflow hole 6 shown in FIG. 20A and the first outflow hole 6 shown in FIG. 20B have the same opening area of “36πm ² ”. Further, the second inflow hole 7 shown in FIG. 20A and the second inflow hole 7 shown in FIG. 20B have substantially the same opening area of “196πm ² ” and “192πm ² ”. However, the length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is “43 mm” in the plates 2 and 3 shown in FIG. In the plates 2 and 3 shown in b), it is “31 mm”. That is, the length from the end of the first outflow hole 6 to the end of the second inflow hole 7 is longer for the plates 2 and 3 shown in FIG. 20B than for the plates 2 and 2 shown in FIG. Much shorter than 3. That is, by forming the first outflow hole 6 and the second inflow hole 7 as shown in FIG. 20 (b), the plate 2, The length in the lateral direction of 3 can be greatly shortened.

FIG. 21 to FIG. 24 are diagrams showing the plates 2 and 3 in which the primary inflow and outflow holes and the secondary inflow and outflow holes have the same shape and a shape other than a circle while maintaining a necessary opening area. is there.
In FIG. 21, the primary inflow / outlet holes and the secondary inflow / outlet holes have the same substantially oval shape. 22 and 23, the primary side inflow and outflow holes and the secondary side inflow and outflow holes have the same fan shape. In FIG. 24, the primary inflow hole and the secondary inflow hole have the same star shape.

  Thus, the length of the plates 2 and 3 in the short direction can be shortened by combining the shapes of the primary inflow and outflow holes and the secondary inflow and outflow holes in various shapes. Therefore, the effect described in the first embodiment can be obtained. In addition, when the secondary inflow / outlet hole and the secondary inflow / outlet hole have the same shape, the plate heat exchanger 20 can be configured by one type of plates 2 and 3.

Embodiment 5 FIG.
Embodiment 5 demonstrates the heating hot-water supply system 29 which is the usage example of the plate-type heat exchanger 20 demonstrated in the above embodiment.

FIG. 25 is a diagram showing a heating and hot water supply system 29.
The heating and hot water supply system 29 includes a compressor 21, a plate heat exchanger 20, an expansion valve 22, a heat exchanger 23, a hot water heater 24, a heater 25, a refrigerant path 26, and a water path 27. Here, the plate-type heat exchanger 20 is the plate-type heat exchanger 20 described in the above embodiment. The compressor 21, the plate heat exchanger 20, the expansion valve 22, the heat exchanger 23, and the refrigerant path 26 are a heat exchange system 28.
The refrigerant repeatedly flows through the refrigerant path 26 in the order of the compressor 21, the plate heat exchanger 20, the expansion valve 22, and the heat exchanger 23. As described above, the compressor 21 compresses the refrigerant. The plate heat exchanger 20 exchanges heat between the refrigerant compressed by the compressor 21 and the liquid (here, water) flowing through the water channel 27. Here, the refrigerant is cooled and the water is warmed by heat exchange in the plate heat exchanger 20. The expansion valve 22 controls expansion of the refrigerant heat-exchanged by the plate heat exchanger 20. The heat exchanger 23 performs heat exchange between the expanded refrigerant and air in accordance with the control of the expansion valve 22. Here, the heat is exchanged in the heat exchanger 23 to warm the refrigerant and cool the air. Then, the warmed refrigerant enters the compressor 21.
On the other hand, water flows through the water channel 27 between the plate heat exchanger 20, the hot water heater 24 and the heater 25. As described above, the water is warmed by heat exchange in the plate heat exchanger 20. Then, the warmed water flows to the water heater 24 and the heater 25. The hot water supply water does not have to be heat exchanged by the plate heat exchanger 20. That is, the water flowing through the water channel 27 and the water for hot water supply may be further heat-exchanged by the water heater 24 or the like.

The plate heat exchanger 20 described in the above embodiment has high strength, is small and light, and is efficient. Therefore, the heat exchange system 28 using the plate heat exchanger 20 described in the above embodiment is also efficient. Moreover, the heating hot water supply system 29 using the heat exchange system 28 is also efficient.
Here, the heat exchange system (ATW (Air To Water) system) that heats water with the refrigerant compressed by the plate heat exchanger 20 described in the above embodiment has been described. However, the present invention is not limited to this, and it is also possible to form a refrigeration cycle (refrigeration air conditioner) that heats or cools a fluid such as air by performing heat exchange using the plate heat exchanger 20 described in the above embodiment. .

That is, the above embodiment can be summarized as follows.
The plate heat exchanger 20 has passage holes serving as fluid inlets and outlets at four corners, and is a plate heat exchanger formed by laminating a plurality of plates provided with fluid inflow and outflow tubes. The ratio of the height (H) to W) is 4 to 6.5.

  The plate heat exchanger 20 is a plate heat exchanger having a passage hole serving as a fluid inlet / outlet at four corners, and a plurality of plates provided with fluid inflow pipes and outflow pipes. The length in the width direction of the inlet / outlet of the side and secondary fluid and the outer peripheral edge of the plate is 3 to 6% with respect to the width (W) of the plate.

  The plate heat exchanger 20 is a plate heat exchanger having a passage hole serving as a fluid inlet / outlet at four corners, and a plurality of plates provided with fluid inflow pipes and outflow pipes. The length in the width direction between the inlet / outlet of the side and secondary fluid and the outer peripheral edge of the plate is 3 to 5.6 mm.

  The plate heat exchanger 20 is a plate heat exchanger having a passage hole serving as a fluid inlet / outlet at four corners, and a plurality of plates provided with fluid inflow pipes and outflow pipes. The inlet and outlet diameters of the side fluid and the secondary fluid are different dimensions.

  The plate heat exchanger 20 is a plate heat exchanger having a passage hole serving as a fluid inlet / outlet at four corners, and a plurality of plates provided with fluid inflow pipes and outflow pipes. The center of the inlet / outlet diameter of the side fluid is shifted from the center of the inlet / outlet diameter of the secondary fluid, and the inlet / outlet of the fluid is brought closer to the outer peripheral edge of the plate.

  The plate-type heat exchanger 20 has passage holes serving as fluid inlets and outlets at four corners, and is a plate-type heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. The crests formed by folding are gradually shifted from the center of the plate, and the end points of the waves are brought close to the inflow / outlet.

  The plate heat exchanger 20 is a plate heat exchanger having a passage hole serving as a fluid inlet / outlet at four corners, and a plurality of plates provided with fluid inflow pipes and outflow pipes. The center of the inlet / outlet diameter of the side fluid is shifted from the center of the inlet / outlet diameter of the secondary fluid, and the combination of irregular shapes such as circles and polygons is maintained while maintaining the required opening area according to the processing flow rate of the secondary fluid. To do.

  Further, the plate heat exchanger 20 is a plate heat exchanger in which a plurality of plates having a passage hole serving as a fluid inlet / outlet at four corners and provided with an inflow pipe and an outflow pipe for fluid are stacked. It is characterized by the combination of the same shape such as a circle or a polygon while maintaining the necessary opening area depending on the processing flow rate of the side fluid.

  1, 4 Reinforcing side plate, 2nd plate, 3rd plate, 5th first inflow hole, 6th first outflow hole, 7th second inflowhole, 8th outflow hole, 9 unevenness, 10 run-up area, 11 Sealing part, 12 Folding point, 13 Both ends, 14 Center line in short direction, 15 Line connecting folding point 12, 20 Plate heat exchanger, 21 Compressor, 22 Expansion valve, 23 Heat exchanger, 24 Hot water supply 25, heater, 26 refrigerant path, 27 water path, 28 heat exchange system.

Claims (13)

It is a plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates includes
A first inflow hole serving as an inlet of the first fluid on either end side in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid on an end side in a longitudinal direction opposite to the first inflow hole;
A second inflow hole serving as an inlet for the second fluid on either end side in the longitudinal direction;
A second outflow hole serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow hole;
Each of the plates has a first flow path that spreads the first fluid flowing in from the first inflow hole in a short direction and flows to the first outflow hole between the plates stacked next to each other, and the first The first fluid flowing in the first flow path is formed by forming one flow path with a second flow path that spreads the second fluid flowing in from the inflow hole in the short direction and flows to the second outflow hole. Heat exchange between the fluid and the second fluid flowing through the second flow path;
Each plate has a length in the longitudinal direction that is at least four times the length in the lateral direction. The length from the first inflow hole to the plate end in the short direction closer to the first inflow hole, and the plate end in the short direction closer to the first outflow hole from the first outflow hole A length from the second inflow hole to the plate end in the short direction closer to the second inflow hole, and a length from the second outflow hole to the second outflow hole. The plate-type heat exchanger according to claim 1, wherein the length to the plate end in the short direction is 6% or less of the length in the short direction. The length from the first inflow hole to the plate end in the short direction closer to the first inflow hole, and the plate end in the short direction closer to the first outflow hole from the first outflow hole A length from the second inflow hole to the plate end in the short direction closer to the second inflow hole, and a length from the second outflow hole to the second outflow hole. The plate-type heat exchanger according to claim 1 or 2, wherein the length to the plate end portion in the short direction is 5.6 mm or less. The opening area of the first inflow hole and the opening area of the first outflow hole are both smaller than both the opening area of the second inflow hole and the opening area of the second outflow hole. The plate heat exchanger according to any one of claims 1 to 3. The center of the first inflow hole and the center of the first outflow hole are provided closer to the end of the plate than the center of the second inflow hole and the center of the second outflow hole. Item 5. The plate heat exchanger according to Item 4. In the plate heat exchanger, the first plate and the second plate are alternately laminated,
The first inflow hole and the second outflow hole are provided on the same end side in the longitudinal direction,
The first plate is a seal portion that prevents fluid flowing in from the first inflow hole from flowing into the second outflow hole, and is a convex seal portion protruding in the stacking direction in which the plurality of plates are stacked. The second outflow gradually in the short direction from the end in the longitudinal direction where the first inflow hole and the second outflow hole are provided toward the end in the longitudinal direction on the opposite side. The plate heat exchanger according to claim 4 or 5, wherein the plate heat exchanger is provided so as to approach an end portion on a hole side. Each plate includes
A plurality of concave and convex portions formed in a V shape by having both end portions at both ends in the short direction and having a turning point at a position shifted from the both end portions in the longitudinal direction are arranged in the longitudinal direction. And
In the vicinity of at least one of the first inflow hole and the first outflow hole, the return point becomes closer to the hole from the center in the short direction as the hole is closer to the hole. The plate-type heat exchanger according to any one of claims 4 to 6, wherein a portion is formed. The plurality of plates are stacked such that the first inflow holes overlap with each other, and sequentially from the first inflow holes of the plates stacked on one side in the stacking direction to the first inflow holes of the plates stacked on the other side. The first fluid flows in;
The plate type heat exchanger according to any one of claims 4 to 7, wherein the first inflow hole has a smaller diameter as the plate stacked on the one side into which the first fluid flows. The first inflow hole and the second outflow hole are provided on the same end side in the longitudinal direction, and the second inflow hole and the first outflow hole are the same end in the longitudinal direction. Provided on the side,
The shape of the first inflow hole is different from the shape of the second outflow hole, and the shape of the second inflow hole is different from the shape of the first outflow hole. The plate type heat exchanger in any one of 1-8. The first inflow hole and the second outflow hole are formed by dividing one circle or one oval or one polygonal hole into two,
10. The second inflow hole and the first outflow hole are formed by dividing one circle, one ellipse, or one polygonal hole into two. Plate heat exchanger. A refrigeration air conditioner comprising the plate heat exchanger according to any one of claims 1 to 10. It is a plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates includes
A first inflow hole serving as an inlet of the first fluid on an end side in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid on an end side in the longitudinal direction opposite to the first inflow hole;
A second inflow hole serving as an inlet for the second fluid on the end in the longitudinal direction;
A second outflow hole serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow hole,
Each of the plates has a first flow path that spreads the first fluid flowing in from the first inflow hole in a short direction and flows to the first outflow hole between the plates stacked next to each other, and the first 2 The first fluid that flows through the first flow path by forming one flow path of the second flow path that flows into the second outflow hole by spreading the second fluid that has flowed into the inflow hole in the short direction. Heat exchange with the second fluid flowing through the second flow path,
The length from the first inflow hole to the plate end in the short direction closer to the first inflow hole, and the plate end in the short direction closer to the first outflow hole from the first outflow hole A length from the second inflow hole to the plate end in the short direction closer to the second inflow hole, and a length from the second outflow hole to the second outflow hole. The plate-type heat exchanger is characterized in that the length to the plate end in the short direction is 6% or less of the length in the short direction. It is a plate heat exchanger formed by laminating a plurality of plates,
Each plate of the plurality of plates includes
A first inflow hole serving as an inlet of the first fluid on an end side in the longitudinal direction;
A first outflow hole serving as an outlet of the first fluid on an end side in the longitudinal direction opposite to the first inflow hole;
A second inflow hole serving as an inlet for the second fluid on the end in the longitudinal direction;
A second outflow hole serving as an outlet of the second fluid is provided on the end side in the longitudinal direction opposite to the second inflow hole,
Each of the plates has a first flow path that spreads the first fluid flowing in from the first inflow hole in a short direction and flows to the first outflow hole between the plates stacked next to each other, and the first 2 The first fluid that flows through the first flow path by forming one flow path of the second flow path that flows into the second outflow hole by spreading the second fluid that has flowed into the inflow hole in the short direction. Heat exchange with the second fluid flowing through the second flow path,
The length from the first inflow hole to the plate end in the short direction closer to the first inflow hole, and the plate end in the short direction closer to the first outflow hole from the first outflow hole A length from the second inflow hole to the plate end in the short direction closer to the second inflow hole, and a length from the second outflow hole to the second outflow hole. A plate type heat exchanger characterized in that the length to the plate end in the short direction is 5.6 mm or less.

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