JP5295330B2 - Plate heat exchanger and refrigeration air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a plate type heat exchanger that is constituted by stacking a plurality of heat transfer plates to constitute a vertical plate type heat exchanger in which a function to separate oil is established. <P>SOLUTION: The plate type heat exchanger is configured so that: liquid flow passages where liquid flows and oil flow passages where oil mixed in the liquid flows are provided between the heat transfer plates 2, 3; and an liquid outlet hole from which the liquids flows out and an oil outlet hole from which the oil flows out are separately formed. In particular, the heat exchanger is constituted so that the liquid outlet hole is formed at the upstream side of the liquid inlet hole, and the oil outlet hole is formed at the downstream side of a liquid inlet hole from which the liquid flows in. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

  The present invention relates to, for example, a plate heat exchanger having a function of separating oil from a fluid, and a refrigeration air conditioner including the plate heat exchanger.

Patent Document 1 describes a plate heat exchanger provided with a function of separating oil inside. However, the plate-type heat exchanger described in Patent Document 1 is a horizontal plate-type heat exchanger in which the surface of the plate is installed horizontally. In general, plate-type heat exchangers are often installed with the plate surface vertically. Therefore, the range in which the plate heat exchanger described in Patent Document 1 can be used is limited.
Patent Document 2 describes a plate-type heat exchanger having a function of separating a gas and a liquid, and a vertical plate-type heat exchanger in which plates are installed vertically. However, the plate heat exchanger described in Patent Document 2 is not intended to separate oil from a fluid. Therefore, the plate heat exchanger described in Patent Document 2 cannot sufficiently separate oil from the fluid.

JP-A-1-230965 JP-A-11-287572

Conventional vertical plate heat exchangers cannot sufficiently separate the oil inside. Therefore, the conventional vertical plate type heat exchanger and the refrigeration air conditioner including the vertical plate type heat exchanger have the following problems (1) to (3).
(1) Refrigerating machine oil (hereinafter referred to as oil) in the heat exchanger becomes a thermal resistance. Therefore, if the fluid is subjected to heat exchange while oil is mixed in the fluid, the heat exchange performance cannot be sufficiently exhibited. Further, in the plate heat exchanger, the fluid often flows in a laminar flow, and stagnation is likely to occur. Therefore, oil with a high density tends to accumulate in the plate heat exchanger, and the effective heat transfer area decreases. That is, when heat is exchanged with a plate heat exchanger while oil is mixed in the fluid, the heat exchange performance deteriorates.
(2) When oil accumulates in the heat exchanger, the frictional resistance of the flow path increases. Therefore, sludge and dust are likely to accumulate, and the reliability of the heat exchanger decreases. Moreover, if oil accumulates in a heat exchanger, oil return to a compressor will not be performed. For this reason, the compressor may be damaged. As a result, there is a risk that the refrigeration air conditioner will break down.
(3) Providing equipment for separating oil in the refrigerant circuit of the refrigerating and air-conditioning apparatus leads to an increase in size and cost of the refrigerant circuit.

  For example, an object of the present invention is to provide a vertical plate type heat exchanger with a function of separating oil. Accordingly, an object is to provide a plate type heat exchanger and a refrigeration air conditioner with high performance and high reliability.

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,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates has an inflow hole through which a fluid flows in from the inflow pipe, an outflow hole through which the fluid flowing in from the inflow hole flows out, and an oil outflow hole through which oil mixed in the fluid flows out Is provided,
Each plate has a fluid flow path for flowing the fluid that has flowed in from the inflow hole to the outflow hole and a flow oil flow path for flowing the oil to the oil outlet hole between the plates stacked next to each other. It is formed.

  In the plate heat exchanger according to the present invention, a fluid flow path for flowing fluid and a flow oil flow path for flowing oil mixed in the fluid are formed, an outflow hole for flowing out the fluid, and an oil outlet hole for flowing out the oil And are formed. Thereby, oil can be separated and discharged from the fluid flowing into the plate heat exchanger.

The side view of the plate type heat exchanger 30. FIG. The front view of the plate type heat exchanger 30. FIG. The front view of the 2nd heat exchanger plate 2. FIG. The front view of the 1st heat-transfer plate 3. FIG. The front view of the 2nd reinforcement side plate 4. FIG. The disassembled perspective view of the plate-type heat exchanger 30. FIG. Sectional drawing of the plate-type heat exchanger 30 which concerns on Embodiment 1. FIG. Sectional drawing of the plate-type heat exchanger 30 which concerns on Embodiment 2. FIG. The figure which shows the heat-transfer plate 2 laminated | stacked next to the 1st reinforcement side plate 1 which concerns on Embodiment 2. FIG. The figure which shows heat-transfer plates 2 and 3 other than the heat-transfer plate 2 laminated | stacked next to the 1st reinforcement side plate 1 which concerns on Embodiment 2. FIG. Sectional drawing of the plate-type heat exchanger 30 which concerns on Embodiment 3. FIG. FIG. 6 is a diagram showing an oil separation pipe 13 according to Embodiment 3. Sectional drawing of the plate-type heat exchanger 30 which concerns on Embodiment 4. FIG. FIG. 6 shows an oil separation pipe 13 according to a fourth embodiment. The figure which shows the oil separation pipe | tube 13 which concerns on Embodiment 4 different from FIG. Sectional drawing of the plate-type heat exchanger 30 which concerns on Embodiment 5. FIG. FIG. 6 shows an oil separation pipe 13 according to a fifth embodiment. Sectional drawing of the plate type heat exchanger 30 which concerns on Embodiment 6. FIG. FIG. 10 shows heat transfer plates 2 and 3 according to the sixth embodiment. Explanatory drawing of the oil return method in the case of flowing oil into the 1st flow path of the 1st layer. Explanatory drawing of the oil return method in the case of flowing oil into the 1st flow path of the Nth layer. FIG. 10 shows heat transfer plates 2 and 3 according to the seventh embodiment. Sectional drawing of the plate type heat exchanger 30 which concerns on Embodiment 8. FIG. The figure which shows the heating hot-water supply system 39. FIG.

  1 to 6 are explanatory views of a basic configuration of a plate heat exchanger 30 according to the following embodiment. FIG. 1 is a side view of the plate heat exchanger 30. 2 is a front view of the plate heat exchanger 30 (viewed from the B side in FIG. 1). FIG. 3 is a front view of the second heat transfer plate 2. FIG. 4 is a front view of the first heat transfer plate 3. FIG. 5 is a front view of the second reinforcing side plate 4. FIG. 6 is an exploded perspective view of the plate heat exchanger 30.

In the plate heat exchanger 30, a plurality of heat transfer plates 2 and 3 are laminated. The plate heat exchanger 30 has a first reinforcement side plate 1 and a second reinforcement on one end side (B side and front side in FIG. 1) and the other end side (C side and rear side in FIG. 1), respectively. The side plate 4 for use is laminated.
As shown in FIGS. 3 and 4, each heat transfer plate 2, 3 is formed in a substantially rectangular plate shape. Each of the heat transfer plates 2 and 3 is provided with a first inflow hole 9 on one end side (upper side) of a substantially rectangular long side direction (longitudinal direction). Each heat transfer plate 2, 3 is provided with a first outflow hole 10 on the end side (lower side) in the longitudinal direction opposite to the first inflow hole 9. Each heat transfer plate 2, 3 is provided with a second inflow hole 11 on the same end side (lower side) in the longitudinal direction as the first outflow hole 10. Each heat transfer plate 2, 3 is provided with a second outflow hole 12 on the end side (upper side) in the same longitudinal direction as the first inflow hole 9. Here, each heat transfer plate 2, 3 is provided with a first inflow hole 9 and a first outflow hole 10 on the same end side (left side) in a substantially rectangular short side direction (short side direction). Each of the heat transfer plates 2 and 3 has a second inflow hole 11 and a second outflow hole 12 on the end side (right side) in the short direction opposite to the first inflow hole 9 and the first outflow hole 10. Is provided.
That is, each heat transfer plate 2, 3 is provided with a first inflow hole 9, a first outflow hole 10, a second inflow hole 11, and a second outflow hole 12 at four corners. In addition, the 1st inflow hole 9 and the 1st outflow hole 10 are called a primary side inflow / outflow hole. Similarly, the second inflow hole 11 and the second outflow hole 12 are referred to as 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 heat transfer plates 2 and 3. As shown in FIG. 2, the first reinforcing side plate 1 stacked on the forefront is provided with a first inflow pipe 5 at a position where the first inflow holes 9 are provided in the heat transfer plates 2 and 3. Similarly, the first outflow pipe 6 is provided at the position where the first outflow hole 10 is provided in the heat transfer plates 2 and 3, and the second inflow pipe 7 is provided at the position where the second inflow hole 11 is provided, A second outflow pipe 8 is provided at a position where the second outflow hole 12 is provided.
On the other hand, as shown in FIG. 5, the second reinforcing side plate 4 stacked on the backmost surface is not provided with the inflow / outflow tubes 5, 6, 7, 8 and the inflow / outflow holes 9, 10, 11, 12. In FIG. 5, the positions of the inflow / outflow pipes 5, 6, 7, 8 and the inflow / outlet holes 9, 10, 11, 12 are indicated by broken lines on the second reinforcement side plate 4. These are not provided in 4.
The plates 2 and 3 and the reinforcing side plates 1 and 4 have substantially the same substantially rectangular shape.

The heat transfer plates 2 and 3 are laminated so that the first inflow holes 9, the first outflow holes 10, the second inflow holes 11, and the second outflow holes 12 overlap each other. The heat transfer plate 2 and the heat transfer plate 3 are alternately stacked. The first reinforcing side plate 1 and the heat transfer plate 2 adjacent to the first reinforcing side plate 1 are a first inflow pipe 5 and a first inflow hole 9, a first outflow pipe 6 and a first outflow hole. 10, the second inflow pipe 7 and the second inflow hole 11, and the second outflow pipe 8 and the second outflow hole 12 are laminated so as to overlap each other.
Here, the first inflow passage for distributing the first fluid to the first flow paths by the first inflow pipe 5 of the first reinforcing side plate 1 and the first inflow holes 9 of the heat transfer plates 2 and 3. A hole is formed. Similarly, the second inflow passage for distributing the second fluid to the second flow paths by the second inflow pipe 7 of the first reinforcing side plate 1 and the second inflow holes 11 of the heat transfer plates 2 and 3. A hole is formed. Also, the first outflow passage hole through which the first fluid flows from each first flow path is formed by the first outflow pipe 6 of the first reinforcing side plate 1 and the first outflow holes 10 of the heat transfer plates 2 and 3. It is formed. Similarly, a second outflow passage hole through which the second fluid flows from each second flow path is formed by the second outflow pipe 8 of the first reinforcing side plate 1 and the second outflow holes 12 of the heat transfer plates 2 and 3. Is formed.

As shown in FIGS. 3 and 4, a plurality of irregularities are arranged in the longitudinal direction on the heat transfer plates 2 and 3. Concavities and convexities are formed in a V shape by having both ends on both ends in the short direction and turning points at positions shifted in the longitudinal direction from both ends. The pitch (width) of the unevenness is W shown in FIG. The V-shaped folding angle is 2θ.
The heat transfer plate 2 and the heat transfer plate 3 are arranged so that the direction of the unevenness is reversed. That is, the heat transfer plate 2 has irregularities formed in a V shape having a folding point below both ends, whereas the heat transfer plate 3 has a V shape having a folding point above both ends. Unevenness is formed on the mold (inverted V-shaped).
As described above, by alternately stacking the heat transfer plates 2 and 3 having the concave and convex shapes in the reverse V shape, a flow path with good heat transfer efficiency is formed between the heat transfer 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 9 flows to the first outflow hole 10 is between the front surface of the heat transfer plate 2 and the back surface of the heat transfer plate 3. It is formed. Similarly, a second flow path through which the second fluid flowing in from the second inflow hole 11 flows to the second outflow hole 12 is formed between the back surface of the heat transfer plate 2 and the front surface of the heat transfer plate 3. A first flow path is also formed between the back surface of the first reinforcing side plate 1 and the front surface of the adjacent heat transfer plate 2. Similarly, a first flow path is also formed between the front surface of the second reinforcing side plate 4 and the rear surface of the adjacent heat transfer plate 3.
The first fluid flowing in the first flow path and the second fluid flowing in the second flow path are heat-exchanged via the heat transfer plates 2 and 3.

Further, the first flow path formed closest to the first inflow pipe 5 is referred to as a first flow path in the first layer. The plates that form the first flow path of the first layer are called a first plate and a second plate. In particular, a plate laminated on the first inflow pipe 5 side is called a first plate, and a plate laminated on the side opposite to the first inflow pipe 5 is called a second plate. Here, since the first flow path of the first layer is formed between the first reinforcing side plate 1 and the heat transfer plate 2 adjacent thereto, the first reinforcing side plate 1 is the first plate, The heat transfer plate 2 stacked next to the reinforcing side plate 1 is the second plate.
In addition, the first channel formed on the side farthest from the first inflow pipe 5 is referred to as an Nth layer first channel. The plates forming the first flow path of the Nth layer are called the Nth plate and the (N + 1) th plate. In particular, a plate laminated on the first inflow pipe 5 side is called an Nth plate, and a plate laminated on the opposite side to the first inflow pipe 5 is called an N + 1th plate. Here, since the first flow path of the Nth layer is formed between the second reinforcing side plate 4 and the adjacent heat transfer plate 3, the second reinforcing side plate 4 is the N + 1th plate, The heat transfer plate 3 stacked next to the reinforcing side plate 4 is the Nth plate.

In the following Embodiments 1 to 5 and Embodiment 8, the plate heat exchanger 30 is placed vertically with the first inflow pipe 5 side in the longitudinal direction facing up and the first outflow pipe 6 side facing down. The Therefore, the first fluid that has flowed in from the first inflow pipe 5 flows downward through the first flow paths from the first inflow hole 9 to the first outflow hole 10, and flows out from the first outflow pipe 6. On the other hand, the second fluid that has flowed in from the second inflow pipe 7 flows upward from the second inflow hole 11 to the second outflow hole 12 through the second flow paths, and flows out from the second outflow pipe 8.
Also, in the following sixth and seventh embodiments, contrary to the first to fifth embodiments and the eighth embodiment, the plate heat exchanger 30 has the first outflow pipe 6 side in the longitudinal direction facing upward, The first inflow pipe 5 is placed vertically with the side facing down.
In the following embodiments, the first fluid is a refrigerant, and the second fluid is a fluid such as water heated or cooled by the refrigerant. Note that the refrigerant flows into the plate heat exchanger 30 from the first inflow pipe 5 in a state where oil is mixed.

Embodiment 1 FIG.
FIG. 7 is a cross-sectional view of the plate heat exchanger 30 according to the first embodiment. In particular, FIG. 7 is a cross-sectional view of the plate heat exchanger 30 in the AA ′ portion of FIG. In FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line.

  As shown in FIG. 7, the first flow path (the first flow path of the first layer) formed between the first reinforcing side plate 1 and the heat transfer plate 2 stacked adjacent thereto is arranged in the stacking direction. The width W1 is wider than the width W2 in the stacking direction of the other first flow paths. That is, the width W1 in the stacking direction of the first flow path of the first layer is wider than the width W2 in the stacking direction of the other first flow paths.

The flow of the refrigerant mixed with oil in the plate heat exchanger 30 will be described.
The refrigerant mixed with oil flows from the first inflow pipe 5. The refrigerant flowing in from the first inflow pipe 5 is distributed to each first flow path through the first inflow passage hole including the first inflow pipe 5 and the first inflow hole 9. The refrigerant distributed to each first flow path is heat-exchanged with the fluid flowing through the adjacent second flow path. Then, the heat-exchanged refrigerant flows out of the plate heat exchanger 30 through the first outflow passage hole including the first outflow pipe 6 and the first outflow hole 10.
Here, the oil has a higher density than the refrigerant. Therefore, oil is easier to fall than the refrigerant. For this reason, in the first inflow passage hole, the oil mixed in the refrigerant easily flows into the first flow path of the first layer. In particular, since the width W1 in the stacking direction of the first flow path of the first layer is wide, most of the oil mixed in the refrigerant flows into the first flow path of the first layer. On the other hand, since the density of the refrigerant is lower than that of oil, the refrigerant flows in a distributed manner into channels other than the first channel of the first layer (first channel after the second layer).
That is, most of the oil flows into the first flow path of the first layer, and most of the refrigerant flows into the first flow paths after the second layer. That is, the oil and the refrigerant are separated into the first channel in the first layer and the first channel in the second and subsequent layers. And in the 1st flow path after the 2nd layer, the refrigerant from which oil was separated is heat-exchanged via the adjacent second flow path and the heat transfer plates 2 and 3.

Oil has a high thermal resistance, and a heat-containing refrigerant cannot efficiently exchange heat. However, since the oil is separated from the refrigerant in the second and subsequent first flow paths, the thermal resistance is low. Therefore, heat exchange can be performed efficiently.
In addition, oil has higher density and viscosity and slower speed than refrigerant. Therefore, the oil tends to stay in the plate, causing the refrigerant to drift. However, since the oil is separated from the refrigerant in the first flow path after the second layer, the drift of the refrigerant is suppressed. Therefore, the heat transfer area can be increased, and heat can be exchanged more efficiently.
That is, the plate heat exchanger 30 according to Embodiment 1 has high heat exchange performance.

  The width W1 of the first flow path in the first layer is adjusted according to the amount of oil circulation. That is, if the oil circulation amount is large, the width W1 of the first flow path of the first layer may be widened, and if the oil circulation amount is small, the width W1 of the first flow path of the first layer may be narrowed.

  That is, the plate heat exchanger 30 according to the first embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30, the width dimension of the first layer is larger than the width dimension of the second and subsequent layers.

Embodiment 2. FIG.
FIG. 8 is a cross-sectional view of the plate heat exchanger 30 according to the second embodiment. FIG. 8 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 8, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line. FIG. 9 is a view showing the heat transfer plate 2 stacked next to the first reinforcing side plate 1. FIG. 10 is a view showing the heat transfer plates 2 and 3 other than the heat transfer plate 2 stacked next to the first reinforcing side plate 1.

In the plate heat exchanger 30 shown in FIG. 8, the opening area of the first inflow hole 9 of the heat transfer plate 2 stacked adjacent to the first reinforcing side plate 1 is the same as that of the other heat transfer plates 2 and 3. The opening area of one inflow hole 9 is smaller. Since the first inflow hole 9 is a circle, the diameter of the first inflow hole 9 of the heat transfer plate 2 stacked next to the first reinforcing side plate 1 is the first of the other heat transfer plates 2 and 3. It is smaller than the diameter of the inflow hole 9.
In particular, the first inflow hole 9 in the heat transfer plate 2 stacked next to the first reinforcing side plate 1 is provided from the longitudinal end (upper end) close to the first inflow hole 9. That is, the distance L1 from the upper end of the heat transfer plate 2 stacked next to the first reinforcing side plate 1 to the first inflow hole 9 is from the upper end of the other heat transfer plates 2 and 3 to the first inflow hole 9. Is substantially the same as the distance L2. That is, as shown in FIG. 8, the first inflow passage formed by the first inflow holes 9 of the heat transfer plates 2 and 3 by the heat transfer plate 2 stacked next to the first reinforcing side plate 1. A dam (wall, resistor) is formed on the first flow path side (lower side) of the hole.

As described in the first embodiment, since oil is more likely to fall than the refrigerant, it tends to flow into the first flow path of the first layer. In the plate heat exchanger 30 according to the second embodiment, a weir is formed below the first inflow passage hole by the heat transfer plate 2 stacked next to the first reinforcing side plate 1. By this weir, the oil which is going to flow into the first flow path after the second layer can be stopped and flowed into the first flow path of the first layer. As described above, since oil has a high density and easily falls, it easily flows under the first inflow passage hole. Therefore, oil can be prevented from flowing into the first flow path of the second and subsequent layers by the weir formed below the first inflow passage hole. That is, by providing the weir, oil can be separated from the refrigerant with high accuracy.
That is, the plate heat exchanger 30 according to the second embodiment has a high heat exchange performance, similar to the plate heat exchanger 30 according to the first embodiment.

  The weir can be manufactured simply by reducing the diameter of the first inflow hole 9. Therefore, the weir can be manufactured at low cost.

  Similarly to the plate heat exchanger 30 according to the first embodiment, the width W1 in the stacking direction of the first flow path of the first layer is greater than the width W2 in the stacking direction of the first flow paths after the second layer. May be wide. In this case, the heat exchange performance can be further increased.

  That is, the plate heat exchanger 30 according to the second embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30 is characterized in that the refrigerant inflow pipe diameter (first inflow hole 9) is made smaller than the normal diameter to form a weir to enable separation of oil from the refrigerant.

Embodiment 3 FIG.
FIG. 11 is a cross-sectional view of the plate heat exchanger 30 according to the third embodiment. FIG. 11 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 11, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line. FIG. 12 is a diagram illustrating the oil separation pipe 13 according to the third embodiment.

In the plate heat exchanger 30 shown in FIG. 11, the oil separation pipe is disposed in the first inflow passage hole from the first inflow pipe 5 to the front of the heat transfer plate 2 stacked next to the first reinforcing side plate 1. 13 was provided. An oil outlet 14 (first hole) is formed in the oil separation pipe 13 between the first reinforcing side plate 1 and the heat transfer plate 2 stacked adjacent to the first reinforcing side plate 1 toward the first layer flow path. . In addition, a refrigerant outlet 15 (second hole) is formed in the oil separation pipe 13 toward the first inflow hole 9 of the heat transfer plate 2 stacked next to the first reinforcing side plate 1. The oil outlet 14 is a hole through which oil flows out, and the refrigerant outlet 15 is a hole through which refrigerant flows out.
The opening area of the oil outlet 14 is made smaller than the opening area of the inlet of the first layer flow path. In particular, the opening area of the oil outlet 14 is reduced while making the oil outlet 14 long in the stacking direction. The opening area of the oil outlet 14 is determined according to the density of oil, the amount (ratio) of oil contained in the refrigerant, and the like. For example, the opening area of the oil outlet 14 is set to an opening area where all the oil contained in the refrigerant flows out from the oil outlet 14.

As described in the first embodiment, since oil is more likely to fall than the refrigerant, it tends to flow into the first flow path of the first layer. In the plate heat exchanger 30 according to the second embodiment, an oil separation pipe 13 having an oil outlet 14 with a small opening area is provided. In particular, the opening area of the oil outlet 14 is the opening area through which all the oil contained in the refrigerant flows out from the oil outlet 14. Therefore, when oil flows out of the oil outlet 14 preferentially, the refrigerant does not flow out of the oil outlet 14. Therefore, the oil separation pipe 13 can prevent the refrigerant from flowing to the first flow path in the first layer. That is, by providing the oil separation pipe 13, oil can be separated from the refrigerant with high accuracy.
That is, the plate heat exchanger 30 according to the third embodiment has a high heat exchange performance, like the plate heat exchanger 30 according to the first embodiment.

Note that the opening area of the refrigerant outlet 15 may be a minute size like a fine nozzle. In this case, the flow rate of the refrigerant flowing out to the first inflow hole 9 of the first heat transfer plate can be increased. Since the flow rate is increased, the heat exchange performance is improved.
Further, by making the outer diameter of the oil separation pipe 13 substantially the same as the inner diameter of the first inflow pipe 5, the plate-type heat exchange shown in FIG. 11 can be performed simply by inserting the oil separation pipe 13 into the first inflow pipe 5. The vessel 30 can be manufactured. Thereby, the plate type heat exchanger 30 shown in FIG. 11 can be manufactured at low cost.
Further, the oil outlet 14 and the refrigerant outlet 15 formed in the oil separation pipe 13 are not limited to a circle but may be a polygon, an ellipse, or the like. In addition, the oil outlet 14 and the refrigerant outlet 15 may be configured with a plurality of holes instead of a single hole.

  Similarly to the plate heat exchanger 30 according to the first embodiment, the width W1 in the stacking direction of the first flow path of the first layer is greater than the width W2 in the stacking direction of the first flow paths after the second layer. May be wide. In this case, the heat exchange performance can be further increased.

  That is, the plate heat exchanger 30 according to Embodiment 3 has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30, an insertion type oil separation mechanism (oil separation pipe 13) is provided in the refrigerant inlet nozzle (first inflow pipe 5) to enable oil separation from the refrigerant.

Embodiment 4 FIG.
FIG. 13 is a cross-sectional view of the plate heat exchanger 30 according to the fourth embodiment. FIG. 13 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 13, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line. FIG. 14 is a diagram illustrating the oil separation pipe 13 according to the fourth embodiment.

In the plate heat exchanger 30 shown in FIG. 13, the oil separation pipe 13 is provided in the first inflow passage hole from the first inflow pipe 5 to the front of the second reinforcing side plate 4. The oil separation pipe 13 has an oil outlet 14 (first direction) in the direction of the first flow path (downward) between the second reinforcing side plate 4 and the heat transfer plate 3 stacked next to the second reinforcing side plate 4. 1 hole) is formed. Further, the oil separation pipe 13 includes a first reinforcing side plate 1 and a first reinforcing side plate 1 between the first reinforcing side plate 1 and the heat transfer plate 3 stacked next to the second reinforcing side plate 4. (2) A refrigerant outlet 15 (second hole) is formed in a direction different from the plurality of first flow paths formed between the heat transfer plates 3 stacked next to the reinforcing side plate 4. Here, the refrigerant outlet 15 is formed in the opposite direction (upward) to the first flow path.
That is, the oil outlet 14 is formed downward at the position of the first flow path (Nth first flow path) farthest from the first inflow pipe 5. The refrigerant outlet 15 is formed upward at the position of the other first flow path (the first flow path up to the (N-1) th layer).

The refrigerant mixed with oil flows from the first inlet pipe 5 through the oil separation pipe 13. Of the refrigerant mixed with oil, only the low density refrigerant flows out to the first flow path from the refrigerant outlet 15 to the N-1th layer. On the other hand, high-density oil does not flow out from the refrigerant outlet 15 but flows out from the oil outlet 14 to the first flow path of the Nth layer.
That is, the low-density refrigerant flows out from the refrigerant outlet 15 formed on the upper side. However, high-density oil does not flow out from the refrigerant outlet 15 formed on the upper side but flows out from the oil outlet 14 formed on the lower side. Most refrigerant flows out of the refrigerant outlet 15 before reaching the oil outlet 14. Therefore, almost only oil flows out from the oil outlet 14. That is, the oil and the refrigerant are separated into the first flow path of the Nth layer and the first flow path up to the (N-1) th layer. In the first flow path up to the (N-1) th layer, the refrigerant from which the oil has been separated is heat-exchanged via the adjacent second flow path and the heat transfer plates 2 and 3.

  Therefore, the plate heat exchanger 30 according to the fourth embodiment has high heat exchange performance, similar to the plate heat exchanger 30 according to the first embodiment.

FIG. 15 is a view showing an oil separation pipe 13 according to Embodiment 4 different from FIG. 13 and 14, one refrigerant outlet 15 is formed between the first reinforcing side plate 1 and the heat transfer plate 3 stacked next to the second reinforcing side plate 4. However, as shown in FIG. 15, the coolant outlet 15 may be divided into a plurality of parts. In particular, the refrigerant outlet 15 may be formed for each first flow path formed between the first reinforcing side plate 1 and the heat transfer plate 3 stacked next to the second reinforcing side plate 4. .
The oil outlet 14 may also be configured with a plurality of holes instead of being configured with one hole.
Further, the oil outlet 14 and the refrigerant outlet 15 formed in the oil separation pipe 13 are not limited to a circle but may be a polygon, an ellipse, or the like.
The oil separation pipe 13 has a diameter smaller than the inner diameter of the first inflow passage hole.

  Note that the width in the stacking direction of the first flow path in the Nth layer may be wider than the width in the stacking direction of the first flow path and the second flow path up to the Nth layer.

  That is, the plate heat exchanger 30 according to the fourth embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30, the oil separation path is provided in the refrigerant path that is the longest distance from the refrigerant inlet nozzle (first inflow pipe 5).

Embodiment 5 FIG.
FIG. 16 is a cross-sectional view of the plate heat exchanger 30 according to the fifth embodiment. FIG. 16 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 16, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line. FIG. 17 is a diagram illustrating the oil separation pipe 13 according to the fifth embodiment.

  In the plate heat exchanger 30 shown in FIG. 16, the oil separation pipe 13 is provided in the first inflow passage hole from the first inflow pipe 5 to the front of the second reinforcing side plate 4. In the oil separation pipe 13, a mixture outlet 16 is formed in front of the second reinforcing side plate 4 toward the second reinforcing side plate 4. That is, unlike the oil separation pipe 13 described in the third and fourth embodiments, the two types of holes of the oil outlet 14 and the refrigerant outlet 15 are not formed, but one type of hole (mixture outlet 16). ) Is formed. From the mixture outlet 16, the refrigerant mixed with oil flows out.

  The refrigerant mixed with the oil flowing out from the mixture outlet 16 collides with the wall surface of the second reinforcing side plate 4. By colliding with the wall surface, high density oil and low density refrigerant are separated. When the oil and the refrigerant are separated, the high-density oil falls as it is and flows into the first flow path of the Nth layer. On the other hand, most of the low-density refrigerant flows into the first flow path up to the (N-1) th layer. That is, the oil and the refrigerant are separated into the first flow path of the Nth layer and the first flow path up to the (N-1) th layer. In the first flow path up to the (N-1) th layer, the refrigerant from which the oil has been separated is heat-exchanged via the adjacent second flow path and the heat transfer plates 2 and 3.

Therefore, the plate heat exchanger 30 according to the fifth embodiment has high heat exchange performance, similar to the plate heat exchanger 30 according to the first embodiment.
The insertion distance of the oil separation pipe 13 (distance from the mixture outlet 16 to the second reinforcing side plate 4) and the opening area of the mixture outlet 16 are determined according to the amount (ratio) of oil mixed into the refrigerant. To do.

Embodiment 6 FIG.
FIG. 18 is a cross-sectional view of a plate heat exchanger 30 according to the sixth embodiment. FIG. 18 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 18, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line. FIG. 19 is a diagram showing the heat transfer plates 2 and 3 according to the sixth embodiment.
In the first to fifth embodiments, the plate heat exchanger 30 is vertically placed with the first inflow pipe 5 side in the longitudinal direction facing up and the first outflow pipe 6 side facing down. However, it is assumed that the plate heat exchanger 30 shown in FIG. 18 is vertically placed with the first outflow pipe 6 side in the longitudinal direction facing up and the first inflow pipe 5 side facing down. Therefore, the first fluid that has flowed in from the first inflow pipe 5 flows upward from the first inflow hole 9 to the first outflow hole 10 through the first flow paths and out of the first outflow pipe 6. On the other hand, the second fluid that has flowed in from the second inflow pipe 7 flows downward through the second flow paths from the second inflow hole 11 to the second outflow hole 12, and flows out from the second outflow pipe 8.

In the plate heat exchanger 30 shown in FIG. 18, the oil outlet pipe 17 is provided on the first reinforcing side plate 1. In addition, oil outlet holes 18 were formed in the heat transfer plates 2 and 3.
The oil outlet pipe 17 was provided at a position opposite to the first outlet pipe 6 with respect to the first inlet pipe 5. That is, since the first outflow pipe 6 is provided at one end (upper side) in the longitudinal direction of the first reinforcing side plate 1, the oil outlet pipe 17 is the other end in the longitudinal direction of the first reinforcing side plate 1. (Lower side). Similarly, the oil outlet hole 18 was provided at a position opposite to the first outlet hole 10 with respect to the first inlet hole 9. That is, since the first outflow hole 10 is formed at one end (upper side) in the longitudinal direction of the heat transfer plates 2 and 3, the oil outlet hole 18 is at the other end in the longitudinal direction of the heat transfer plates 2 and 3 ( (Lower side).
Further, in the plate heat exchanger 30 shown in FIG. 18, the flowing oil flow path through which oil contained in the refrigerant flowing in from the first inflow pipe 5 flows to the oil outlet hole 18 is the front surface of the heat transfer plate 2 and the heat transfer plate 3. It is formed between the back surface. Similarly, a fluid flow path is formed between the back surface of the first reinforcing side plate 1 and the front surface of the adjacent heat transfer plate 2, and the front surface of the second reinforcing side plate 4 and the adjacent heat transfer plate 2. A fluid flow path is also formed between the back surface of the heat plate 3. The opening area of the inlet of the fluid flow path is adjusted according to the amount of oil circulation. That is, the opening area of the inlet of the fluid flow path is set to an opening area through which all the oil contained in the refrigerant flows out.
The oil outlet pipe 17 of the first reinforcing side plate 1 and the oil outlet holes 18 of the heat transfer plates 2 and 3 form a fluid passage passage hole through which oil flows from each fluid passage.

The flow of the refrigerant mixed with oil in the plate heat exchanger 30 will be described.
The refrigerant mixed with oil flows from the first inflow pipe 5.
Then, the high-density oil is distributed to the lower flow oil flow paths through the first inflow passage holes (the first inflow pipe 5 and the first inflow hole 9). Then, the oil flows out of the plate heat exchanger 30 through the flowing oil passage hole (the oil outlet pipe 17 and the oil outlet hole 18).
On the other hand, the low-density refrigerant is distributed to the upper first flow paths through the first inflow passage holes (the first inflow pipe 5 and the first inflow hole 9). The refrigerant distributed to each first flow path is heat-exchanged with the fluid flowing through the adjacent second flow path. The heat-exchanged refrigerant flows out of the plate heat exchanger 30 through the first outflow passage hole (the first outflow pipe 6 and the first outflow hole 10). In addition, it is difficult for the low-density refrigerant to flow into the lower fluid flow paths. This is because high-density oil flows into each of the lower fluid passages and the inlet of the fluid passage is blocked.
That is, most of the oil flows into the flowing oil flow path, and most of the refrigerant flows into the first flow path. That is, the oil and the refrigerant are separated into the flowing oil passage and the first passage. In the first flow path, the refrigerant from which the oil has been separated is heat-exchanged via the adjacent second flow path and the heat transfer plates 2 and 3.
That is, the plate heat exchanger 30 according to the sixth embodiment has higher heat exchange performance than the plate heat exchanger 30 according to the first embodiment.

In addition, the plate heat exchanger 30 according to the sixth embodiment allows the oil and the refrigerant to flow out of the plate heat exchanger 30 in a state where the oil and the refrigerant are separated. Therefore, the oil flowing out from the oil outlet pipe 17 to the outside of the plate heat exchanger 30 may be returned to the compressor. That is, by returning oil to the compressor, the reliability of a heat source device such as an air conditioner is improved.
When the plate heat exchanger 30 is used in an evaporator, liquid refrigerant generally flows from the lower side of the plate heat exchanger 30 into the plate heat exchanger 30. Here, when refrigerant leakage occurs, the amount of vapor refrigerant increases inside the plate heat exchanger 30. Therefore, the speed difference between the oil and the refrigerant becomes large, and the oil and the refrigerant are easily separated. At this time, oil does not return to the compressor in the plate heat exchanger 30 having no path for oil to return to the compressor. For this reason, there exists a possibility that a compressor may be damaged and a refrigeration air conditioner may break down.

In addition, as described in the first to third embodiments, when oil flows through the first flow path (first flow path of the first layer) from the first inflow pipe 5 most often, As described above, even when oil is allowed to flow through the first flow path (Nth first flow path) farthest from the first inflow pipe 5, the oil can be returned.
FIG. 20 is an explanatory diagram of an oil return method in the case of flowing oil through the first flow path of the first layer. FIG. 21 is an explanatory diagram of an oil return method in the case of flowing oil into the first flow path of the Nth layer.
As shown in FIGS. 20 and 21, an oil outlet pipe 17 is provided below the first outlet pipe 6 of the first reinforcing side plate 1, and below the first outlet holes 10 of the heat transfer plates 2 and 3. An oil outlet 18 is provided. In addition, each heat transfer plate 2, 3 forms a fluid flow passage and a fluid flow passage that continues from the first inlet 9 to the oil outlet 18 between the adjacent heat transfer plates 2, 3. And the V-shaped unevenness | corrugation of each heat-transfer plate 2 and 3 is formed toward a flowing oil flow path. That is, the unevenness is not formed around the first outflow hole 10, and the unevenness is formed only on the oil outlet hole 18 side. Then, most of the oil having high density and high viscosity flows along the unevenness, and therefore flows into the oil outlet hole 18. On the other hand, most of the low-density and low-viscosity refrigerant flows to the first outflow hole 10 regardless of the unevenness. As a result, the oil flows out from the oil outlet pipe 17 to the outside of the plate heat exchanger 30, and the refrigerant flows out of the first outlet pipe 6 to the outside of the plate heat exchanger 30. That is, the oil and the refrigerant flow out of the plate heat exchanger 30 in a state where the oil and the refrigerant are separated. Therefore, oil can be returned to the compressor.
In the above description, the heat transfer plates 2 and 3 are provided with irregularities so that oil flows into the oil outlet holes 18. However, unevenness may be formed so that the oil flows into the oil outlet hole 18 only in the heat transfer plates 2 and 3 that form the first flow path through which the oil flows. That is, in FIG. 20, the unevenness may be formed so that oil flows only to the oil outlet hole 18 only in the heat transfer plate 2 closest to the first inflow pipe 5. If it is FIG. 21, you may form an unevenness | corrugation so that oil may flow into the oil outlet hole 18 only to the heat-transfer plate 3 most distant from the 1st inflow tube 5. FIG.

  That is, the plate heat exchanger 30 according to the sixth embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30, the oil return path (oil outlet pipe 17) is configured at a position shifted from the center of the refrigerant inlet nozzle (first inlet pipe 5).

Embodiment 7 FIG.
FIG. 22 is a diagram showing the heat transfer plates 2 and 3 according to the seventh embodiment. FIG. 22 shows the heat transfer plates 2 and 3 of the plate heat exchanger 30 shown in FIG.

In the heat transfer plates 2 and 3 shown in FIG. 22, a groove 19 is formed on the oil outlet hole 18 side of the first inlet hole 9.
Oil with high density and high viscosity flows through the groove 19. That is, it flows below the first inflow passage hole. Therefore, oil is easy to flow into the flowing oil flow path. On the other hand, since the refrigerant has low density and low viscosity, if oil flows through the groove 19, it is difficult for the refrigerant to flow through the groove 19. That is, it flows above the first inflow passage hole. Therefore, the refrigerant easily flows into the first flow path.
That is, in the plate heat exchanger 30 according to the seventh embodiment, oil and refrigerant are more easily separated than in the plate heat exchanger 30 according to the sixth embodiment. Therefore, the plate heat exchanger 30 according to the seventh embodiment has higher heat exchange performance than the plate heat exchanger 30 according to the sixth embodiment.

  The reinforcing side plates 1 and 4 and the heat transfer plates 2 and 3 are made by a press. Therefore, the number and interval of the grooves 19 can be easily adjusted depending on the shape of the mold. Therefore, the precision which isolate | separates oil easily can be improved.

  Instead of providing the groove 19 in the first inflow hole 9, the shape of the first inflow hole 9 may be a triangle or a star. In this case, the first inflow hole 9 is formed so that a triangular or star-shaped sharpened portion is on the oil outlet 18 side. Similarly, the first inflow hole 9 may be elliptical. In this case, the elliptical long side is formed in the longitudinal direction (vertical direction) of the heat transfer plates 2 and 3. By doing in this way, it becomes easy to isolate | separate oil similarly to the case where the groove | channel 19 is provided in the 1st inflow hole 9. FIG.

  In the plate heat exchanger 30 according to the first and second embodiments, the groove 19 may be provided on the first flow path side (lower side) of the first inflow pipe 5. In the plate heat exchanger 30 according to the third to fifth embodiments, the groove 19 may be provided on the first flow path side (lower side) of the oil separation pipe 13. Thereby, oil and a refrigerant | coolant become easy to isolate | separate.

  That is, the plate heat exchanger 30 according to the seventh embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30 is characterized in that a groove 19 is provided in the shape of the refrigerant inlet path.

Embodiment 8 FIG.
FIG. 23 is a cross-sectional view of the plate heat exchanger 30 according to the eighth embodiment. FIG. 23 is a cross-sectional view of the plate heat exchanger 30 taken along the line AA ′ of FIG. In FIG. 23, similarly to FIG. 7, the refrigerant flow is indicated by a solid line, and the oil flow is indicated by a broken line.

The plate heat exchanger 30 shown in FIG. 23 includes an oil return pipe 20 that connects the first inflow pipe 5 and the first outflow pipe 6. The oil return pipe 20 connects the first outflow pipe 6 side (lower side) of the first inflow pipe 5 to the first inflow pipe 5 side (upper side) of the first outflow pipe 6. High-density oil flowing through the first inflow pipe 5 easily flows into the oil return pipe 20 provided on the lower side. On the other hand, the low-density refrigerant hardly flows into the oil return pipe 20. Therefore, oil and refrigerant are separated.
In the plate heat exchanger 30 according to the eighth embodiment, since oil flows from the first inflow pipe 5 to the first outflow pipe 6, the oil flows into the heat exchange portion constituted by the heat transfer plates 2 and 3. Can be prevented. Therefore, the plate heat exchanger 30 according to Embodiment 8 has high heat exchange performance.

Note that, similarly to the opening area of the oil outlet 14 described in the third embodiment, the opening area of the inlet portion from the first inflow pipe 5 to the oil return pipe 20 is the oil density or the amount of oil contained in the refrigerant. You may decide according to (ratio) etc.
Further, as described in the sixth embodiment, the oil discharge pipe 17 may be provided separately from the first outflow pipe 6. Then, the first inlet pipe 5 and the oil outlet pipe 17 may be connected by the oil return pipe 20.
Further, as described in the seventh embodiment, the groove 19 may be formed on the lower side of the first inflow pipe 5.

  In the plate heat exchanger 30 according to the eighth embodiment, the oil return pipe 20 is disposed in an unused space between the first inflow pipe 5 and the first outflow pipe 6. Therefore, oil and refrigerant can be separated without increasing the size of the plate heat exchanger 30.

  That is, the plate heat exchanger 30 according to the eighth embodiment has a passage hole serving as a fluid inlet / outlet, and is a plate heat exchanger formed by laminating a plurality of plates provided with a fluid inflow pipe and an outflow pipe. 30 is characterized in that an oil return path is provided by connecting the refrigerant inlet and outlet nozzles.

  The plate heat exchanger 30 according to the above embodiment is effective not only for a chlorofluorocarbon refrigerant such as R410a but also for an air conditioner using a natural refrigerant such as HC or CO2. It is effective for an air conditioner using oil that is weakly compatible with oil such as CO2 or incompatible with refrigerant.

  When the plate heat exchanger 30 is used in a condenser, the refrigerant enters the plate heat exchanger 30 in a vapor state. Therefore, the refrigerant is easy to separate from oil. Therefore, in this case, the plate heat exchanger 30 according to the above embodiment is particularly effective.

  In addition, when stagnation occurs in the plate heat exchanger, dust and scale easily accumulate in the stagnation part. This induces corrosion of the heat exchanger. However, in the plate heat exchanger 30 according to the above-described embodiment, oil that is a cause of fluid stagnation is separated before entering the heat transfer surface. Therefore, a highly reliable plate heat exchanger 30 can be provided.

  Moreover, when a plate-type heat exchanger is used as an evaporator, temperature distribution occurs due to drift and a frozen part is formed, so that the strength of the heat exchanger is reduced. However, in the plate heat exchanger 30, in order to prevent a drift, it can prevent that the intensity | strength of a heat exchanger falls.

Further, by providing an oil return path for the separated oil separately from the fluid circuit, it is possible to return the oil to the compressor. Thereby, the reliability of a compressor improves and the quality of the air-conditioning equipment carrying this improves. In particular, the refrigerant used for the fluid of the air conditioner is high-pressure, and it is possible to suppress damage to the device due to an increase in the refrigerant circuit pressure due to oil clogging.
If an oil separator is provided in the fluid circuit to return oil, the number of parts constituting the circuit increases. For this reason, the size and cost of the device equipped with the fluid circuit is increased. However, the plate heat exchanger 30 incorporates an oil return mechanism therein, and the number of parts can be reduced. In particular, in an outdoor unit of an air conditioner, securing the installation space is an issue, so the plate heat exchanger 30 is effective. That is, since the outdoor unit on which the plate heat exchanger 30 is mounted is small, the installation space is reduced, and an inexpensive outdoor unit can be provided.

  In the above embodiment, a first flow path (first flow path in the first layer) is formed between the first reinforcing side plate 1 and the heat transfer plate 2 adjacent thereto, so that the second reinforcing side plate is used. The first flow path (first flow path of the first layer) is formed between the side plate 4 and the adjacent heat transfer plate 3. That is, a flow path is also formed between the reinforcing side plates 1 and 4 and the heat transfer plates 2 and 3. However, a flow path may not be formed between the reinforcing side plates 1 and 4 and the heat transfer plates 2 and 3.

Embodiment 9 FIG.
In the ninth embodiment, a heating and hot water supply system 39 that is an example of use of the plate heat exchanger 30 described in the above embodiment will be described.

FIG. 24 is a diagram showing a heating and hot water supply system 39.
The heating and hot water supply system 39 includes a compressor 31, a plate heat exchanger 30, an expansion valve 32, a heat exchanger 33, a hot water heater 34, a heater 35, a refrigerant path 36, and a water path 37. The compressor 31, the plate heat exchanger 30, the expansion valve 32, the heat exchanger 33, and the refrigerant path 36 are a heat exchange system 38.
The refrigerant repeatedly flows in the order of the compressor 31, the plate heat exchanger 30, the expansion valve 32, and the heat exchanger 33 through the refrigerant path 36. As described above, the compressor 31 compresses the refrigerant. The plate heat exchanger 30 exchanges heat between the refrigerant compressed by the compressor 31 and the liquid (here, water) flowing through the water channel 37. Here, the refrigerant is cooled and the water is warmed by heat exchange in the plate heat exchanger 30. The expansion valve 32 controls expansion of the refrigerant heat exchanged by the plate heat exchanger 30. The heat exchanger 33 performs heat exchange between the expanded refrigerant and air in accordance with the control of the expansion valve 32. Here, the heat is exchanged in the heat exchanger 33, whereby the refrigerant is warmed and the air is cooled. Then, the warmed refrigerant enters the compressor 31.
On the other hand, water flows through the water channel 37 between the plate heat exchanger 30, the water heater 34 and the heater 35. As described above, the water is warmed by the heat exchange in the plate heat exchanger 30. Then, the warmed water flows to the water heater 34 and the heater 35. Note that the hot water supply water does not have to be heat exchanged by the plate heat exchanger 30. That is, the water flowing through the water channel 37 and the water for hot water supply may be further heat-exchanged by the water heater 34 or the like.

The plate heat exchanger 30 described in the above embodiment has good heat exchange efficiency. Therefore, the heat exchange system 38 using the plate heat exchanger 30 described in the above embodiment is also efficient. Moreover, the heating hot-water supply system 39 using the heat exchange system 38 is also efficient.
Here, the heat exchange system (ATW (Air To Water) system) for heating water with the refrigerant compressed by the plate heat exchanger 30 described in the above embodiment has been described. However, the present invention is not limited to this, and it is 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 30 described in the above embodiment. .

The above is summarized as follows.
The plate heat exchanger according to the above embodiment is
It is a plate heat exchanger formed by laminating a plurality of plates,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates is provided with an inflow hole through which a fluid flows from the inflow pipe and an outflow hole through which the fluid that flows in from the inflow hole flows out,
Each of the plates forms a flow path for flowing the fluid flowing in from the inflow hole to the outflow hole between the plates stacked next to each other,
The first-layer flow path, which is the flow path formed on the one end side in the stacking direction, is wider in the stacking direction than the other flow paths.

Of the first plate and the second plate forming the first layer flow path, the inflow hole provided in the second plate stacked on the other end side in the stacking direction is provided in another plate. The opening area is smaller than the inflow hole formed.

By the inflow pipe and the inflow hole provided in each plate, a passage hole for distributing the fluid to each flow path of the plurality of flow paths formed by each plate is formed,
A pipe through which the fluid flows, and a first hole is formed in the direction of the first layer flow path between the first plate and the second plate forming the first layer flow path; A pipe having a second hole formed in the second plate, which is provided on the second plate stacked on the other end side in the stacking direction of the first plate and the second plate, is formed in the passage hole. It is characterized by being provided in.

The plate heat exchanger according to the above embodiment is
It is a plate heat exchanger formed by laminating a plurality of plates,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates is provided with an inflow hole through which a fluid flows from the inflow pipe and an outflow hole through which the fluid that flows in from the inflow hole flows out,
Each of the plates forms a flow path for flowing the fluid flowing in from the inflow hole to the outflow hole between the plates stacked next to each other,
By the inflow pipe and the inflow hole provided in each plate, a passage hole for distributing the fluid to each flow path of the plurality of flow paths formed by each plate is formed,
A tube through which the fluid flows, and the Nth layer flow path between an Nth plate and an N + 1th plate forming an Nth layer flow path formed on the other end side in the stacking direction. The first hole is formed in the direction, and the one end of the Nth plate is formed on the one end of the Nth plate stacked on the one end of the Nth and N + 1th plates. A pipe having a second hole formed in a direction different from the flow path is provided in the passage hole.

The plate heat exchanger according to the above embodiment is
It is a plate heat exchanger formed by laminating a plurality of plates,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates is provided with an inflow hole through which a fluid flows from the inflow pipe and an outflow hole through which the fluid that flows in from the inflow hole flows out,
Each of the plates forms a flow path for flowing the fluid flowing in from the inflow hole to the outflow hole between the plates stacked next to each other,
By the inflow pipe and the inflow hole provided in each plate, a passage hole for distributing the fluid to each flow path of the plurality of flow paths formed by each plate is formed,
The pipe in which the fluid flows inside, and is stacked on the other end side among the Nth plate and the N + 1th plate forming the Nth layer flow path formed on the other end side in the stacking direction. A tube having a hole in the direction of the (N + 1) th plate before the (N + 1) th plate is provided in the passage hole.

The plate heat exchanger according to the above embodiment is
It is a plate heat exchanger formed by laminating a plurality of plates,
On one end side in the stacking direction in which the plurality of plates are stacked, an inflow pipe serving as a fluid inlet and an outflow pipe serving as a fluid outlet are provided,
Each plate of the plurality of plates is provided with an inflow hole through which a fluid flows from the inflow pipe, and an outflow hole through which the fluid that flows in from the inflow hole flows out to the outflow pipe,
Each of the plates forms a flow path for flowing the fluid flowing in from the inflow hole to the outflow hole between the plates stacked next to each other,
An oil return pipe through which oil mixed in the fluid flows is provided between the inflow pipe and the outflow pipe.

  DESCRIPTION OF SYMBOLS 1 1st reinforcement side plate, 2, 3 Heat transfer plate, 4 2nd reinforcement side plate, 5 1st inflow pipe, 6 1st outflow pipe, 7 2nd inflow pipe, 8 2nd outflow pipe, 9 1st Inflow hole, 10 1st outflow hole, 11 2nd inflow hole, 12 2nd outflow hole, 13 Oil separation pipe, 14 Oil outlet, 15 Refrigerant outlet, 16 Mixer outlet, 17 Oil outlet pipe, 18 Oil outlet hole, 19 Groove, 20 Oil return pipe, 30 Plate heat exchanger, 31 Compressor, 32 Expansion valve, 33 Heat exchanger, 34 Water heater, 35 Heating machine, 36 Refrigerant path, 37 Water path, 38 Heat exchange system, 39 Heating hot water system.

Claims (2)

It is a plate heat exchanger formed by laminating a plurality of plates,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates has an inflow hole through which a fluid flows in from the inflow pipe, an outflow hole through which the fluid flowing in from the inflow hole flows out, and an oil outflow hole through which oil mixed in the fluid flows out Is provided,
Each plate has a fluid flow path for flowing the fluid that has flowed in from the inflow hole to the outflow hole and a flow oil flow path for flowing the oil to the oil outlet hole between the plates stacked next to each other. Forming ,
The outflow hole is formed above the inflow hole,
The oil outlet hole is formed below the inlet hole,
A plate heat exchanger, wherein the inflow hole is formed with a predetermined groove on the oil outlet hole side . A refrigerant path in which a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger are sequentially connected;
The first heat exchanger is
It is a plate heat exchanger formed by laminating a plurality of plates,
An inflow pipe serving as a fluid inlet is provided on one end side in the stacking direction in which the plurality of plates are stacked,
Each plate of the plurality of plates has an inflow hole through which a fluid flows in from the inflow pipe, an outflow hole through which the fluid flowing in from the inflow hole flows out, and an oil outflow hole through which oil mixed in the fluid flows out Is provided,
Each plate has a fluid flow path for flowing the fluid that has flowed in from the inflow hole to the outflow hole and a flow oil flow path for flowing the oil to the oil outlet hole between the plates stacked next to each other. Forming ,
The outflow hole is formed above the inflow hole,
The oil outlet hole is formed below the inlet hole,
A refrigerating and air-conditioning apparatus , wherein a predetermined groove is formed in the inflow hole on the oil outflow side .

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