JP5553828B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a plate heat exchanger having three separate fluid circuits. Such a plate heat exchanger will have two independent refrigerant circuits and one liquid circuit.

  A plate heat exchanger with one circuit for the liquid and two circuits for the refrigerant with three separate fluid circuits is advantageous over a heat exchanger with two fluid circuits. . Such a heat exchanger realizes a balanced cooling effect with little risk of freezing when used as an evaporator. It also operates effectively even under partial load conditions, thus reducing energy consumption. Installation is easy and quick, thereby reducing installation costs. Furthermore, the control device can be simpler and therefore cheaper.

  One common application of a three circuit heat exchanger is as an evaporator for the evaporation of refrigerant flowing in a cooling system. Such a cooling system typically includes a compressor, a condenser, an expansion valve, and an evaporator. Plate heat exchangers used as evaporators in these types of systems often have multiple heat exchange plates welded or brazed together, but a sealing gasket provides a seal between the heat transfer plates. Sometimes used.

  EP 0 765 461 B shows a plate heat exchanger with a plurality of flow channels for three different fluids between a plurality of plates. The three fluids can be supplied to the core of the plate such that a first fluid channel exists on each side of each of the remaining two fluids. These flow paths are created using two different types of plates. By providing an area around the port and defining a system with a circular flat plateau-like portion, it provides a good seal between adjacent plates at the open locations that make up the inlet and outlet channels for the three fluids be able to.

  EP-A-1062472B shows another example of a three-fluid circuit heat exchanger. This application is primarily concerned with hermetic joining of port holes.

  EP 0965025B describes a plate heat exchanger for three heat exchange fluids. The heat exchanger port holes are paired to allow each heat exchange fluid to pass through, and the straight line drawn between the center of the port holes divides the heat transfer portion into two similar portions. The holes are arranged symmetrically on both sides of the heat transfer part.

  These heat exchangers will work perfectly well for some applications. However, there is room for improvement in these current heat exchangers.

  Accordingly, it is an object of the present invention to provide an improved heat exchanger with improved flow distribution within each flow circuit. It is a further object of the present invention to provide a heat exchanger with improved heat transfer coefficient.

  The solution to this problem according to the invention is described in the characterizing part of claim 1. Claims 2 to 11 include advantageous embodiments of the heat exchange plate. Claims 12 to 21 include advantageous embodiments of the heat exchanger assembly. Claim 22 includes an advantageous heat exchanger.

  A first distribution area with three port holes, a heat distribution area, and a second distribution area with three port holes, used in a three-circuit heat exchanger assembly; In a heat exchange plate having a corrugated pattern with a ridge and a plurality of valleys, an object of the present invention is to provide a first distribution region when two plates are stacked such that a fluid channel is formed therebetween. Achieved by placing the central port hole vertically away from the short side end of the plate so that a fluid flow path is obtained between the central port hole of the plate and the short side end of the plate Is done.

  This first embodiment of the plate of the heat exchanger assembly provides a heat exchange plate that achieves improved flow distribution in the first distribution flow path for the refrigerant circuit. The advantage is that a larger part of the heat exchange plate, i.e. the peripheral area of the inactive inlet port, can also be used as an effective heat transfer surface. Another advantage is that the fluid flow distribution in the first or lower distribution channel is improved, which in turn improves the flow distribution in the heat transfer channel. Another advantage is that the flow in the liquid circuit and to the liquid outlet port is also improved. The efficiency of the heat exchanger will thus be improved.

  In an advantageous development of the plate according to the invention, when the two plates are stacked so that a fluid channel is formed between them, the central port hole of the second distribution area and the short side edge of the plate The central port hole is disposed vertically away from the short-side end of the plate so that a fluid flow path can be obtained therebetween. The advantage is that a larger part of the heat exchange plate, i.e. the peripheral area of the inactive outlet port, can also be used as an effective heat transfer surface. Another advantage is that the distribution of liquid flow from the inlet port is improved, which in turn improves the distribution of liquid flow in the heat transfer channel. Therefore, the efficiency of the heat exchanger will be further improved.

  In an advantageous development of the plate according to the invention, at least one corner of the plate has a refrigerant bypass around the port when the two plates are stacked such that a refrigerant fluid channel is formed between the plates. A flat, annular bypass portion adapted to form a flow path is provided. This will improve the distribution of fluid in the refrigerant channel of the heat exchanger.

  In an advantageous development of the plate according to the invention, when two plates are stacked such that a water channel is formed between the plates, a water flow path is obtained between two adjacent water bypass portions. As such, at least one water bypass portion is provided at the corner of the plate. This will improve the distribution of fluid in the water channel of the heat exchanger.

  In a further advantageous development of the plate according to the invention, a lower distribution groove is provided between the first distribution area and the heat exchange area, the lower distribution groove having at least one restriction area. The upper distribution groove is provided between the heat exchange region and the upper distribution region. All of these developments will allow improved fluid distribution within the heat exchanger.

  In an advantageous development of the plate according to the invention, the first distribution region has a chevron shape with a first layout, the second distribution region has a chevron shape with a second layout, and the heat exchange region has a first shape. The chevron shape of the first layout is oriented in the first angular direction, and the chevron shape of the second layout is oriented in the opposite angular direction. This will allow improved heat transfer of the heat exchanger.

  In a heat exchanger assembly having four heat exchange plates according to the present invention, the object of the present invention is to make the first plate, the second plate, the third plate, and the fourth plate different from each other. Is achieved.

  In an advantageous development of the assembly according to the invention, a first refrigerant channel is provided between the first plate and the second plate, and a water channel is provided between the second plate and the third plate. Provided, a second refrigerant channel is provided between the third plate and the fourth plate, and each fluid channel is a first provided between two first distribution regions adjacent to each other. A distribution flow path, a heat exchange flow path provided between two adjacent heat exchange areas, a second distribution flow path provided between two second distribution areas adjacent to each other, And a horizontal flow path is provided in the first distribution flow path between the central water port and the short side end of the assembly adjacent to the central water port. This is advantageous because the horizontal flow path improves the flow distribution in the first distribution flow path, which improves the flow distribution in the heat transfer flow path. This allows a larger portion of the heat exchange plate, i.e., the area surrounding the non-working inlet port, to function as an effective heat transfer surface. Another advantage is that fluid flow in the liquid circuit is improved because the entire liquid outlet port is open. Thus, the efficiency of the heat exchanger will be improved.

  In an advantageous development of the assembly according to the invention, a horizontal channel is provided in the second distribution channel between the central water port and the short side end of the assembly adjacent to the central water port. . The advantage is that a larger part of the heat exchange plate, i.e. the area surrounding the non-actuated outlet port, can also be used as an effective heat transfer surface. Another advantage is that the distribution of liquid flow from the inlet port is improved, which in turn improves the distribution of liquid flow in the heat transfer channel. Therefore, the efficiency of the heat exchanger will be further improved.

  In an advantageous development of the assembly according to the invention, a water bypass channel is provided in the water distribution channel located between the refrigerant port and the corner of the assembly. This is advantageous in that it provides a water bypass that significantly improves the distribution of water flow in the heat exchanger.

  In an advantageous development of the assembly according to the invention, a refrigerant bypass channel is provided around the refrigerant port in the refrigerant distribution channel. This is advantageous in that the distribution of the refrigerant flow is considerably improved.

  In an advantageous development of the assembly according to the invention, the working refrigerant inlet port comprises an inlet nozzle, the angle of the inlet nozzle being between 0 and 180 degrees with respect to the vertical axis, the inlet nozzle being the assembly. The vertical axis in the center of In this way, the inlet nozzle will face the center of the heat exchanger, which will improve the distribution of fluid within the heat exchanger.

  In an advantageous development of the assembly according to the invention, a lower distribution channel is provided between the lower distribution channel and the heat exchange channel. This is advantageous in that the flow distribution in the lower distribution channel can be controlled in a more sophisticated manner so that the flow into the heat exchange channel is as uniform as possible.

  In an advantageous development of the assembly according to the invention, the lower distribution path has at least one restricting means so that a flow restriction is obtained in the lower distribution path. This is advantageous in that the flow distribution in the lower distribution channel can be controlled in a more sophisticated manner so that the flow into the heat exchange channel is as uniform as possible.

  In an advantageous development of the assembly according to the invention, an upper distribution channel is provided between the heat exchange channel and the upper distribution channel. This is advantageous in that the flow distribution into the upper distribution path can be made more uniform.

  An improved heat exchanger is obtained in a three-circuit heat exchanger having a plurality of heat exchanger assemblies of the present invention and further having at least a front plate and a rear plate.

  The invention will be described in more detail below with reference to embodiments shown in the accompanying drawings.

It is a figure which shows the heat exchange plate assembly of this invention. It is a figure which shows the 1st heat exchange plate used with the heat exchange plate assembly of this invention. It is a figure which shows the 2nd heat exchange plate used with the heat exchange plate assembly of this invention. It is a figure which shows the 3rd heat exchange plate used with the heat exchange plate assembly of this invention. It is a figure which shows the 4th heat exchange plate used with the heat exchange plate assembly of this invention.

  The embodiments of the invention with further refinements described below are to be regarded merely as examples and in no way limit the scope of protection provided by the claims.

  In the following example, water is used as an example of a fluid to be cooled or heated. The fluid to be cooled or heated is intended to be used in one phase, the complete liquid state. For this reason, the layout of the heat exchanger is adapted to single phase liquids for water circuits. Of course, other fluids can also be used, such as various mixtures of water and other fluids, eg, for freeze protection or corrosion prevention purposes. A refrigerant is used as an example of the fluid to be evaporated or condensed. The fluid is preferably used in two phases, a liquid state and a gas state, but the fluid may be used in only one of a liquid state, a gas state or a mixed state. The heat exchanger layout is therefore adapted to the two-phase fluid of the latter fluid circuit.

  The present invention relates to a plate heat exchanger having three distinct channel types that implements three different fluid circuits. One of the channels is configured to transport a single phase liquid that is heated or cooled. In this application, water will be used as an example of such a liquid. The other two channels are configured to transport a two-phase refrigerant adapted to evaporate and condense in the heat exchanger. The channels may be connected so that one refrigerant is commonly used in two circuits, or may be separated so that different refrigerants can be used in each circuit. In this application, a two-phase saturated fluid that is somewhat pressurized when entering the heat exchanger and will evaporate in the heat exchanger is used as an example of a refrigerant.

  Furthermore, the plate heat exchanger is of the permanent junction type in the example described, and the plates are brazed, glued, bonded, soldered or welded together to form a complete heat exchanger. . The plate heat exchanger has a plurality of heat exchanger assemblies, each assembly having four different heat exchange plates. However, it is also possible to use different sealing types such as inter-plate gaskets, weld plates, semi-welded plate units with every other gasket between the plates.

  The heat exchange plate is formed using two different press tools, whereby a first plate type having a layout in which the chevron is oriented in one direction and a second plate type having a layout in which the chevron is oriented in the opposite direction Two different plate types are obtained. This layout has a corrugated pattern consisting of a plurality of ridges and a plurality of troughs extending through the plate in a chevron layout, and the corrugated pattern is an angular direction change point along a vertical line that divides the plate into equal parts. It has. The corrugated pattern in the chevron layout is arranged to intersect at many points in the pattern when multiple plates are stacked together, thereby providing a strong and rigid heat exchanger for efficient heat transfer Is configured. This type of waveform pattern and layout is known to those skilled in the art. It is also possible to use a waveform pattern of the same angle over the entire surface, ie without any direction change points.

  Each plate type is a second step and undergoes one or more additional pressing / cutting operations, thereby creating four different plates. In a further operation, the porthole region of the plate is pressed and cut to a final shape, forming a nozzle well.

  The four plates including the first plate 101, the second plate 201, the third plate 301, and the fourth plate 401 obtained as a result of the above constitute a heat exchange plate assembly. Is laminated. The four plates are stacked so that every other plate has the same plate type unless the porthole region and the nozzle layout are considered. The porthole area is different between the plates, as will be explained below. The first and second plate types can also have different chevron layout angles. Therefore, the first plate type layout can be set to a slightly smaller angle and the second plate type layout can be set to a slightly larger angle so that the average angle value matches the desired angle value of the layout. .

  Each heat exchange plate includes a first distribution area or lower distribution area with three port holes, a central heat exchange area, and a second distribution area or upper distribution area with three port holes. Have. Each plate has a vertical or vertical axis and a horizontal or horizontal axis. The three port holes of the first distribution area are arranged symmetrically with respect to the longitudinal axis. The three port holes in the second distribution area are also arranged symmetrically with respect to the longitudinal axis. The port holes in the first region and the port holes in the second region may be arranged symmetrically with each other. However, in an advantageous embodiment, the six port holes of the first distribution area and the second distribution area are not arranged symmetrically with respect to one another. This is because the diameter of the porthole adapted to the vapor phase of the refrigerant is larger than the diameter of the porthole adapted to the incoming refrigerant liquid vapor mixture. The port holes are located approximately equidistant from the corners of the plate. In the present embodiment, the three port holes in the second distribution region are adapted to the refrigerant in the vapor state, and the three port holes in the first region are adapted to the liquid refrigerant.

  In one example, the heat exchanger is intended to use the refrigerant channel side for rising film evaporation and the water side opposite to it for cooling. In the following, the heat exchanger used for rising film evaporation is used to illustrate the present invention. Accordingly, the description in the description refers to the size and shape of the upright heat exchanger in such a vertical posture. For example, it is possible to change the angle around the horizontal axis and use the heat exchanger in other postures as required. The refrigerant two-phase fluid may be a mixture of liquid and vapor upon entry into the heat exchanger, may be completely evaporated upon exiting the heat exchanger, or may be superheated. The heat exchanger can also be used in a state where water and refrigerant flow in the same direction, that is, in a co-current state. The heat exchanger described is in a state where the refrigerant flows in a diagonal direction, that is, the refrigerant enters the heat exchanger through the lower corner port of the heat exchanger and passes through the upper corner port on the opposite side. It is adapted to exit the heat exchanger. Of course, the parallel flow through the heat exchanger, that is, the refrigerant enters the heat exchanger through the lower corner port of the heat exchanger and exits the heat exchanger through the upper corner port on the same side. Can be adapted, which is possible by adapting the inlet or outlet port in that way.

  The heat exchanger can also be used for downflow refrigerant film condensation, where the water side is heated in a counterflow or cocurrent configuration. The two-phase refrigerant fluid may be superheated or saturated when entering the heat exchanger through the upper distribution flow path, and may exit the heat exchanger through the lower refrigerant port. May be partially or fully condensed and may be supercooled. The heat exchanger can be used for a superheater or gas cooler in one-phase heat transfer, an evaporating economizer, and similar applications, depending on the installation requirements. Depending on the application, the plate layout may require minor modifications.

  The first heat exchange plate 101 shown in FIG. 2 has a first distribution area, that is, a lower distribution area 102, a heat exchange area 103, and a second distribution area, that is, an upper distribution area 104. The plate has a vertical axis or vertical axis 105 and a horizontal axis or horizontal axis 106. The lower distribution region 102 includes a first refrigerant inlet port hole 107, a water outlet port hole 112, and a second refrigerant inlet port hole 109. A nozzle recess 114 is provided in the first inlet port hole 107.

  As will be appreciated, the entire surface of the heat exchange plate with the fluid flow path on the opposite side of the plate is the heat transfer area. Therefore, the heat exchange area 103 is called a heat exchange area. This is because although the fluid is distributed to some extent even in the heat exchange region, the main purpose is heat transfer. The lower and upper distribution areas have the dual purpose of both fluid distribution and heat transfer.

  The layout of the first distribution area 102 has one chevron shape, that is, a V shape, the direction change point is at the center of the plate, and divides the first distribution area into equal parts. The layout angle of the V-shaped layout is preferably between 50 degrees and 70 degrees with respect to the vertical axis of the heat exchanger. Therefore, the interior angle of the V shape is between 100 degrees and 140 degrees. While other angles are possible, the interior angle of the V-shape is advantageously obtuse. By making the chevron layout at a fairly small angle with respect to the horizontal axis, the horizontal coefficient of friction of the lower distribution channel is relatively low, facilitating refrigerant distribution across the width of the plate.

  The heat exchanging region 103 is provided with a chevron layout having three direction change points and dividing the heat exchanging region into four equal parts, that is, a waveform pattern exhibiting a W shape. The interior angle between the chevron is very important for the coefficient of friction of the channel. One advantage of using a W-shape rather than a V-shape at the same interior angle is that the average coefficient of friction in the heat transfer area is higher than when using a V-shape. Therefore, the heat transfer coefficient is higher than that of the conventional V-shape. By using the W shape, a layout whose direction changes three times is realized. It is also possible to use a chevron layout whose direction changes twice or more than four times. In the mountain-shaped transition region, that is, the direction change point, the flow velocity components in the horizontal direction and the vertical direction are reduced and may be close to zero. In the illustrated first plate, the layout resembles a W-shape arranged upside down.

  The corrugated W-shaped angle is preferably between 50 and 70 degrees with respect to the vertical axis of the heat exchanger. Therefore, the inner angle of the angle is between 100 degrees and 140 degrees. The interior angle of the chevron of the heat exchange region may be the same as the chevron of the first distribution region or may be somewhat smaller. Although other angles are possible, it is important that the interior angle of the chevron is an obtuse angle. The coefficient of friction of the heat exchange flow path depends on, for example, the angle inside the angle as well as the number of direction changes.

  The upper distribution area 104 of the plate includes a first refrigerant outlet port hole 108, a water inlet port hole 111, and a second refrigerant outlet port hole 110. The waveform pattern of the upper distribution area has a mountain-shaped layout similar to one V-shape arranged upside down. The interior corner of the V shape may be the same as the lower distribution area.

  The inner angles of the chevron of the lower distribution region, the heat exchange region, and the upper distribution region may be the same or different. In an advantageous embodiment, the lower distribution area and the chevron of the heat exchange area have the same interior angle. The chevron shape of the upper distribution area has a smaller angle with respect to the vertical axis in this embodiment. In a further advantageous embodiment, the lower distribution region chevron has a first angle, the heat exchange region chevron has a smaller second angle, and the upper distribution region chevron has a smaller angle. These angles are preferably between 50 and 70 degrees. The advantage of having different interior angles in different regions is that the volumetric flow rate is higher at the top of the heat exchanger when the refrigerant is evaporating. Thus, by varying the interior angle, the flow resistance will be lower when the volume flow rate increases with the direction of flow in the channel. The same is true when the flow is opposite and the heat exchanger is used to condense the steam. When the inner angle of the angle is small with respect to the vertical axis, the flow resistance in this flow direction is low.

  The second heat exchange plate 201 shown in FIG. 3 has a lower distribution area 202, a heat exchange area 203, and an upper distribution area 204. The plate has a vertical axis 205 and a horizontal axis 206. The lower distribution area 202 includes a first refrigerant inlet port hole 207, a water outlet port hole 212, and a second refrigerant inlet port hole 209. A nozzle recess 214 is provided in the first inlet port hole 207.

  The layout of the lower distribution area 202 has one chevron shape, that is, a V-shape, and the V-shape resembles a V-shape arranged upside down. The direction change point is in the center of the plate and divides the first distribution area into equal parts. Except for the direction of the chevron shape, the angle of the layout is the same as that of the first plate.

  The heat exchanging region 203 is provided with a chevron layout that has three direction change points and divides the heat exchanging region into four equal parts, that is, a waveform pattern that exhibits a W shape. In the second plate shown, the layout resembles a W shape. Except for the direction of the chevron shape, the angle of the layout is the same as that of the first plate.

  The upper distribution area 204 of the second plate includes a first refrigerant outlet port hole 208, a water inlet port hole 211, and a second refrigerant outlet port hole 210. The corrugated transverse pattern of the upper distribution region has a chevron layout similar to one V-shape. The interior angle of the V shape may be the same as the lower distribution area. Except for the direction of the chevron shape, the angle of the layout is the same as that of the first plate.

  The third heat exchange plate 301 shown in FIG. 4 has a lower distribution area 302, a heat exchange area 303, and an upper distribution area 304. The plate has a vertical axis 305 and a horizontal axis 306. The lower distribution region 302 includes a first refrigerant inlet port hole 307, a water outlet port hole 312, and a second refrigerant inlet port hole 309. The upper distribution area 304 of the plate includes a first refrigerant outlet port hole 308, a water inlet port hole 311, and a second refrigerant outlet port hole 310. Except for port holes and nozzle recesses, the third heat exchange plate is similar to the first heat exchange plate.

  The fourth heat exchange plate 401 shown in FIG. 5 has a lower distribution area 402, a heat exchange area 403, and an upper distribution area 404. The plate has a vertical axis 405 and a horizontal axis 406. The lower distribution region 402 includes a first refrigerant inlet port hole 407, a water outlet port hole 412, and a second refrigerant inlet port hole 409. The upper distribution area 404 of the plate includes a first refrigerant outlet port hole 408, a water inlet port hole 411, and a second refrigerant outlet port hole 410. Except for port holes and nozzle recesses, the fourth heat exchange plate is similar to the second heat exchange plate.

  In the description, the term working inlet port means that the inlet port is open so that refrigerant can flow into the refrigerant channel through the inlet port. A non-working inlet port means that the inlet port is sealed and refrigerant cannot enter the refrigerant channel through the non-working inlet port. The term working outlet port is similar, meaning that the outlet port is in contact with the refrigerant channel so that the refrigerant can flow out of the working outlet port. The non-working outlet port is sealed and refrigerant cannot flow out of the refrigerant channel through the non-working outlet port.

  FIG. 1 shows a heat exchange plate assembly 1 of the present invention including a first plate 101, a second plate 201, a third plate 301, and a fourth plate 401. Various plates are shown in FIGS. A plurality of plates are stacked on each other as many as necessary for a specific heat exchanger. In this way, a heat exchanger having a plurality of assemblies is configured. The number of assemblies can be selected depending on the required specifications of the heat exchanger. A complete heat exchanger also has specific front and rear plates (not shown) that are thicker than the individual heat exchange plates. The front plate and the rear plate will have connections and the like. In a complete heat exchanger, the liquid channel closest to the front and rear plates will be the water channel. Thus, a separate heat exchange plate that forms a water channel with the first plate may be included in the front plate, and a separate heat exchange plate that forms a water channel with the fourth plate is included in the rear plate. It may be. The front and rear plates increase the strength of the heat exchanger, making the heat exchanger more stable and stiff.

  The heat exchanger is a brazing type. A first refrigerant channel 2 is formed between the first and second plates. A water channel 3 is formed between the second and third plates. A second refrigerant channel 4 is formed between the third and fourth plates. A water channel is formed between the fourth plate and the first plate of another assembly. In this way, the heat exchanger has first and second refrigerant channels arranged every other side and surrounded on both sides by water channels.

  Both the refrigerant channel and the water channel have a lower distribution flow path, a heat exchange flow path, and an upper distribution flow path. The vertical length of the lower distribution channel is preferably less than half of the width of the heat exchanger, and the vertical length of the upper distribution channel is less than two-thirds of the width of the heat exchanger It is preferable that

  When the first plate 101 and the second plate 201 are disposed adjacent to each other, the first refrigerant channel 2 is configured. The refrigerant enters the first refrigerant channel through the first refrigerant inlet port 21 which is an operation inlet port constituted by the first refrigerant inlet port holes 107 and 207. The inlet port holes 107 and 207 are provided with concentric sealing parts 113 and 213 which are pressed against each other. The inlet to the first refrigerant channel is constituted by an inlet nozzle 25 in the sealed part. The inlet nozzle is realized by nozzle recesses 114, 214 in one or both sealed portions that are pressed by a second pressing step. The size, length and cross-section of the inlet nozzle, as well as the angular position of the inlet nozzle, are important for the distribution of refrigerant in the lower distribution flow path 10 formed between the lower distribution regions 102 and 202. is there. The size of the inlet nozzle depends in part on the inlet pressure of the refrigerant and is selected to achieve uniform flow distribution across all refrigerant channels throughout the heat exchanger. The angular position of the inlet nozzle is selected so that the refrigerant is evenly distributed across the entire width of the heat exchanger within each refrigerant channel.

  The inlet nozzle may be oriented at any selected angle, for example depending on the corrugated pattern layout of the bypass portion and the bypass portion around the inlet port. The angle of the inlet nozzle is preferably between 0 and 180 degrees with respect to the vertical axis, and is directed to the central vertical axis, more preferably between 90 and 150 degrees.

  In one embodiment, the inlet port is open. This may be advantageous when a heat exchanger is used such that, for example, in a gas cooler, the inlet port operates as a steam outlet port. In order to prevent the steam from blocking the outlet, the sealing part and the nozzle are cut off during the manufacturing stage. Instead, an open port similar to the exit port 22 is obtained. Such a port allows vapor or a mixture of vapor and liquid to exit through the port.

  To further improve refrigerant distribution, the working inlet port is provided with a working inlet port bypass channel 18 around the inlet port so that the refrigerant flows around the sides of the inlet port. Each plate has bypass portions 115, 215 extending around the entire circumference of the first inlet port hole. The bypass portion has the same press depth as the corrugated portion of the plate. Therefore, the bypass flow path 18 obtained as a result has a height twice as large as the press depth. This means that the friction pressure drop in the bypass channel is much smaller than when following the waveform pattern. Therefore, the bypass flow path 18 distributes a part of the refrigerant from the inlet nozzle to the distribution area around the operation inlet port.

  A portion of the refrigerant from the nozzle continues to flow in the direction from the nozzle to the corrugated pattern and further toward the second refrigerant inlet port 23, which is a non-working inlet port. Since the water outlet port holes 112 and 212 are arranged vertically away from the lower short side end of the plate, the lower horizontal flow path 13 is connected to the water outlet port and the lower short side of the heat exchanger. Formed in the lower distribution channel between the side ends. Therefore, the refrigerant can flow from below the water outlet port to the area around the non-operating inlet port. Since the flow of the refrigerant from the inlet nozzle has almost the same angle as the corrugation pattern of the first plate in this example, a part of the refrigerant has a relatively small coefficient of friction below the water outlet port and is therefore compared. Passes mainly in the horizontal direction at a high flow rate. When the refrigerant reaches the peripheral area of the non-working inlet port, the non-working inlet port bypass flow path 19 around the non-working inlet port will facilitate the distribution of the refrigerant to the peripheral area of the non-working inlet port. The bypass channel 19 around the non-working inlet port 23 is made in the same way as at the working inlet port. That is, the bypass channel 19 is made of each plate having bypass portions 117 and 217 extending around the entire periphery of the second inlet port hole. The bypass portion has the same press depth as the corrugated portion of the plate. Therefore, the resulting bypass flow path has a height twice the press depth. This means that the friction in the bypass channel is much less than the friction along the corrugated pattern. Thus, the bypass flow path distributes a portion of the refrigerant to the distribution area around the non-working inlet port. The second inlet port holes 109, 209 are provided with concentric sealing portions 116, 216 that are pressed against each other and thus seal the inactive inlet port.

  The flat circular portions around the water outlet port holes 112, 212 are pressed together so that the water outlet ports are sealed against the refrigerant channel. The water outlet port hole is arranged vertically away from the lower short side end of each plate. The water outlet port hole has a larger diameter than the refrigerant inlet port hole, and the center of the water outlet port hole is disposed closer to the horizontal axis of the plate than the center of the refrigerant inlet port hole. In this way, the lower horizontal flow path 13 is created in the refrigerant channel between the water outlet port and the short side end of the heat exchanger. Through this flow path, the refrigerant can pass under the water outlet port and reach the peripheral area of the non-operating inlet port. This greatly improves refrigerant distribution across the width of the channel and provides a more uniform flow across the width of the channel and thus through the heat exchange flow path. The flow path below the water outlet port will also increase the effective heat transfer area of the heat exchanger due to the area surrounding the non-working inlet port.

  In order to further improve the distribution of the refrigerant, the first refrigerant channel has a lower side located between the lower distribution flow path 10 and the heat exchange flow path 11 above the working inlet port and the non-working inlet port. Distribution paths 15 and 16 are provided. The lower distribution path is mainly constituted by flat distribution grooves 118, 119, 218, 219 pressed into the plate between the V shape of the distribution area and the W shape of the heat exchange area. , Extending from the long side of the plate to the water outlet port hole. The lower distribution path, on the one hand, promotes uniform distribution of the refrigerant into the heat exchange flow path 11, and on the other hand as a transition region between the V-shaped layout of the distribution region and the W-shaped layout of the heat exchange region. Will play a role. The height and shape of the lower distribution path can be selected to optimize flow distribution. The height of the pressed groove is about half the press depth of the plate in one example. In order to improve the mechanical strength of the heat exchanger, the lower distribution path may have one or more contact points. Since the corresponding distribution path is created in the water channel, the height of the lower distribution path in the refrigerant channel is preferably less than or equal to the sum of one press depth. The lower distribution path has a lower flow resistance in the horizontal direction of the channel compared to the flow resistance along the same length and width flow tube in the wave pattern of the heat transfer channel.

  If required, the lower distribution paths 15, 16 may have one or more restricted areas to control the distribution of flow across the width of the channels in the lower distribution flow path. The size and location of the restriction area is selected so that the flow through the distribution path 15 or 16 is distributed as uniformly as possible. The limiting portion is realized by changing the press depth at the location of the limiting area in the plate, ie by changing the height of the limiting area and / or by changing the width of the limiting area along the lower distribution path. be able to. In this way, various restricting portions can be placed at various positions within the lower distribution path 15, 16. The limiting portion provides an increase in local flow resistance that achieves flow distribution across the width of the lower distribution path. In one example, the restrictive portion spans most of the distribution path, thereby forming one or a few small openings between the distribution flow path and the heat exchange flow path. The size and position of the restriction portion can be determined by experimentation or calculation. Thus, the distribution of the refrigerant flowing into the heat exchange channel is improved.

  The refrigerant enters the working inlet port 21 and is distributed in the lower distribution flow path 10, and then enters and passes through the heat exchange flow path 11 formed between the heat exchange regions 103 and 203. . The heat exchange flow path provides effective heat transfer between the refrigerant channel and the water channel by providing a large heat exchange area and relatively high frictional flow resistance due to all contact points between the corrugated patterns of the two plates. Secure. The W shape slightly increases the friction pressure drop in the heat exchange flow path and improves the total heat transfer of the heat exchanger compared to a single V shape.

  Flat horizontal distribution grooves 120, 220 are pressed on each plate between the heat exchange area and the upper distribution area of each plate, forming an upper distribution path 17 in the first refrigerant channel. . The upper distribution path distributes the refrigerant flow before the refrigerant enters the upper distribution flow path formed between the upper distribution areas 104 and 204 of the plate, and at the same time, the heat exchange flow path due to fluctuations in the evaporation of the refrigerant. To equalize the pressure difference that may occur within. Since the upper distribution path has a low flow resistance in the horizontal direction of the heat exchanger, distribution of the refrigerant is promoted before entering the upper distribution flow path 12. The evaporation of the refrigerant mainly ends in the upper distribution flow path, and the refrigerant vapor may be overheated. The height of each distribution groove is about half of the press depth of the plate because a corresponding horizontal distribution path is created in the water channel. For this reason, the upper distribution path has an overall height of one press depth.

  Mostly evaporated refrigerant enters the upper distribution flow path formed by the upper distribution areas 104 and 204 of the plate. The first refrigerant outlet port 22 which is an operation port is formed at the position of the first refrigerant outlet port holes 108 and 208 between the plates. A part of the refrigerant enters the upper distribution channel on the right side of the vertical axis 105, and a part of the refrigerant enters the upper distribution channel on the left side of the vertical axis 105. A part of the refrigerant reaches the bypass flow path 20 formed by the bypass portions 121 and 221 extending around the entire periphery of the second outlet port 24. The second refrigerant outlet port holes 110 and 210 are provided with concentric sealing portions 122 and 222 which are pressed against each other and seal the second outlet port which is a non-operating outlet port. The bypass portion has the same press depth as the corrugated portion of the plate. Therefore, the bypass channel 20 obtained as a result has a height twice the press depth. This means that the flow resistance in the bypass channel is much smaller than the flow resistance through the waveform pattern. Thus, the bypass channel allows a substantial portion of the refrigerant, which may be overheated, to pass through the horizontal channel above the water inlet port and primarily in the horizontal direction to the working outlet port.

  The flat circular portions around the water inlet port holes 111, 211 are pressed against each other and the water inlet is sealed from the refrigerant channel. The water inlet port hole is disposed below the upper short side end portion of each plate and separated in the vertical direction. The center of the water inlet port hole is located closer to the horizontal axis of the plate than the center of the refrigerant outlet port hole. Thus, the upper horizontal flow path 14 is disposed in the refrigerant channel between the water inlet port and the upper short side end of the heat exchanger. Through this horizontal flow path, the refrigerant is above the water inlet port, and the working outlet formed between the first refrigerant outlet port holes 108 and 208 from the bypass flow path 20 at the position of the non-working outlet port 24. It can flow to port 22. This reduces the flow resistance of the steam that may be overheated and significantly improves the flow distribution in the upper distribution flow path. Furthermore, this horizontal flow path prevents the steam from accumulating around the non-operating outlet port and becoming a blocking region where the steam stays in the peripheral area of the non-operating outlet port. The flow path also increases the total effective heat transfer area of the heat exchanger by providing an area around the non-working outlet port.

  When the second plate 201 and the third plate 301 are arranged adjacent to each other, the water channel 3 is configured. Water will enter the water channel through the water inlet port 42 constituted by the water inlet port holes 211, 311. Water will exit the water channel through the water outlet port 43 which is constituted by the outlet port holes 212, 312. All the refrigerant ports are sealed so that water and the refrigerant are not mixed. When the second and third plates are stacked, the bypass portions 215 and 315 are pressed together, thus sealing the first refrigerant inlet port. The bypass portions 217 and 317 and the bypass portions 221 and 321 are similarly pressed against each other so that the second refrigerant inlet port and the second refrigerant outlet port are sealed. The first refrigerant outlet port is sealed by flat portions 223 and 323 around the refrigerant outlet port holes 208 and 308 that are pressed against each other.

  The water inlet port holes 211 and 311 are arranged vertically away from the upper short side end of each plate edge of each plate. The center of the water inlet port hole is located closer to the horizontal axis of the plate than the center of the refrigerant outlet port hole. In this way, an upper horizontal flow path 34 is formed in the water channel between the water inlet port and the upper short side end of the heat exchanger. This increases the effective cross flow area of the water at the inlet, which in turn improves the water distribution in the upper distribution flow path and reduces the water channel pressure drop.

  To further improve water distribution and reduce water pressure drop, the water channel includes an upper water outlet between the second and first non-working refrigerant outlet ports and the upper corner of the heat exchanger. Bypass channels 40 and 41 are provided. The upper water bypass passages 40 and 41 are formed by water bypass portions 226, 227, 326, and 327 located outside the second and first refrigerant outlet port holes, respectively. These bypass parts are pressed against each other when the plates are arranged to form a refrigerant channel. This means that the water bypass channel has a height twice the press depth. Accordingly, these water bypass channels have a low frictional pressure drop and considerably facilitate the lateral distribution of water over the entire upper distribution channel.

  As water is distributed in the upper distribution flow path 32, the water is pressed into each plate and passes through flat horizontal distribution grooves 220, 320 that form a horizontal upper distribution path 37 in the water channel. This distribution path allows further distribution of water, and the water pressure along the entire upper distribution path is substantially equal. The upper distribution path also serves as a transition region between the V shape of the upper distribution flow path and the W shape of the heat exchange flow path. The height of each distribution groove is about half of the press depth of the plate. Therefore, the upper distribution path is 1 press deep in total.

  After passing through the upper distribution path 37, the water enters and passes through the heat exchange flow path 31 formed between the heat exchange regions 203 and 303. All contact points between the corrugated patterns of the two plates allow the heat exchange flow path to achieve a large heat exchange area and a relatively high coefficient of friction, thereby effective heat transfer between the water channel and the refrigerant channel. Is secured. Because of the W-shaped layout, the coefficient of friction in the heat exchange channel is somewhat increased compared to one V-shaped layout, thereby improving heat transfer.

  When water passes through the heat exchange flow path 31, the water passes through the two lower distribution paths 35 and 36 disposed between the heat exchange flow path and the lower distribution flow path, and then passes through the lower distribution flow path 30. Enter. These lower distribution paths are mainly constituted by flat distribution grooves 218, 219, 318, 319 pressed against the plate between the V shape of the distribution area and the W shape of the heat exchange area. It extends from the long side of the plate to the water outlet port hole. These distribution paths facilitate uniform distribution of water into the lower distribution flow path, and transition between the W-shaped layout of the heat exchange flow path and the V-shaped layout of the lower distribution flow path. It will serve as an area. The height and shape of the lower distribution path can be selected to optimize flow distribution. The height of the pressed groove may be about half of the press depth of the plate in one example. In order to improve the mechanical strength of the heat exchanger, the lower distribution path may have one or more contact points. The distribution path has a lower flow resistance in the horizontal direction of the heat exchanger compared to the flow resistance along the waveform pattern in the lower distribution flow path. This facilitates uniform flow distribution into the lower distribution path of the water.

  Some water, particularly water from the center of the heat exchange channel 31, enters the water outlet port 43 formed by the water outlet port holes 212 and 312 directly from the upper heat exchange channel. The water outlet port is completely open because the corrugated pattern around the water outlet port allows water flow from all directions to the water outlet port. This allows a portion of the water distributed to the lower distribution area to enter the water outlet opening through the pattern between the water outlet port and the refrigerant inlet port and from the pattern below the water outlet port. Will be able to.

  To further improve water distribution, the lower distribution flow path 30 includes a lower water bypass flow between the inactive first and second refrigerant inlet ports and the lower corner of the heat exchanger. Paths 38 and 39 are provided. The lower water bypass flow path is constituted by water bypass portions 224, 225, 324, and 325 located at the first and second refrigerant inlet port holes, respectively. These bypass parts are pressed against each other when the plates are arranged to form the refrigerant flow path. This means that the lower water bypass channel has a height twice the press depth. Therefore, these lower water bypass channels have a low friction pressure drop and contribute significantly to directing the water flow to the water outlet port.

  To facilitate water distribution and increase the effective heat transfer area of the heat exchanger, the water outlet port holes are located vertically away from the lower short end of each plate. In this way, the lower horizontal flow path 33 is created in the water channel between the water outlet port and the lower short side end of the heat exchanger. Through this horizontal flow path, water can also flow into the water outlet port from below the port, improving the efficiency of the heat exchanger. The lower bypass flow path, combined with the water outlet port being offset upwards, significantly improves the distribution of water flow at the outlet and increases the effective cross-flow area of the water, Reduce the drop in outlet pressure all around the periphery of the port.

  The second refrigerant channel 4 is formed between the third plate 301 and the fourth plate 401 when they are disposed adjacent to each other, and is similar to the first refrigerant channel. The only difference between the first refrigerant channel and the second refrigerant channel is the inlet port, outlet port and inlet nozzle.

  The refrigerant enters the second refrigerant channel through the second inlet port 63 which is an operation inlet port constituted by the refrigerant inlet port holes 309 and 409. The inlet port holes 309, 409 include concentric sealing portions 316, 416 that will be pressed against each other. The inlet to the second refrigerant channel is formed by an inlet nozzle 65 through the sealing portion. The inlet nozzle is realized by nozzle recesses 314, 414 in one or both sealed portions. The size, length and cross-section of the inlet nozzle, as well as the angular position of the inlet nozzle, are important for refrigerant distribution in the lower distribution flow path 50 formed between the lower distribution regions 302 and 402. is there. The size of the inlet nozzle depends in part on the pressure drop in the refrigerant circuit and is selected to achieve uniform flow distribution across all refrigerant channels in the refrigerant circuit of the entire heat exchanger. The angular position of the inlet nozzle is selected so that the refrigerant is evenly distributed across the entire width of the heat exchanger within each refrigerant channel.

  The inlet nozzle may be oriented in any selected direction, depending on, for example, the lower distribution flow path and the corrugated pattern layout of the bypass portion around the inlet port. The angle of the inlet nozzle is preferably between 0 and 180 degrees with respect to the vertical axis, preferably facing the central vertical axis of the plate, more preferably between 90 and 150 degrees. .

  To further improve refrigerant distribution, the working inlet port is provided with a working inlet bypass channel 59 around the inlet port so that the refrigerant flows around the sides of the inlet port. Each plate has bypass portions 317, 417 extending around the entire perimeter of the inlet port hole. The bypass portion has the same press depth as the corrugated portion of the plate. Thus, the resulting working inlet bypass flow path has a height twice the press depth. This means that the friction in the bypass channel is much less than the friction along the corrugated pattern. Therefore, the bypass channel distributes a part of the refrigerant from the inlet nozzle to the distribution region around the operation inlet port.

  Some of the refrigerant from the nozzle also continues to flow in the direction from the nozzle to the corrugated pattern and further toward the first refrigerant inlet port 61, which is the non-working inlet port. Since the water outlet port holes 312 and 412 are arranged vertically away from the lower short side end of each plate, the lower horizontal flow path 53 is connected to the water outlet port and the lower short side of the heat exchanger. Formed in the lower distribution channel between the side ends. Therefore, the refrigerant can flow from below the water outlet port to the area around the non-operating inlet port. Since the flow from the inlet nozzle of the refrigerant has almost the same angle as the waveform pattern of the third plate in this example, a part of the refrigerant has a relatively small coefficient of friction below the water outlet port and is therefore compared. Passes mainly in the horizontal direction at a high flow rate. When the refrigerant reaches the peripheral area of the non-working inlet port 61, the bypass flow path 58 around the non-working inlet port will facilitate the distribution of the refrigerant to the peripheral area of the non-working inlet port. Bypass channel 58 is made in the same manner as at the working inlet port. That is, the bypass flow path 58 is made of each plate having bypass portions 315 and 415 extending around the entire periphery of the first refrigerant inlet port hole. The bypass portion has the same press depth as the corrugated portion of the plate. Therefore, the resulting bypass flow path has a height twice the press depth. This means that the friction in the bypass channel is much less than the friction along the corrugated pattern. Thus, the bypass flow path distributes a portion of the refrigerant to the distribution area around the non-working inlet port. The first inlet port holes 307, 407 are provided with concentric sealing portions 313, 413 which are pressed against each other and thus seal the inactive inlet port.

  The flat circular portions around the water outlet port holes 312 and 412 are pressed together so that the water outlet port is sealed against the refrigerant channel. The water outlet port hole is arranged vertically away from the lower short side end of each plate. The water outlet hole has a larger diameter than the refrigerant inlet port hole, and the center of the water outlet hole is arranged closer to the horizontal axis of the plate than the center of the refrigerant inlet port hole. In this way, the lower horizontal flow path 53 is formed in the refrigerant channel between the water outlet port and the lower short side end of the heat exchanger. Through this horizontal flow path, the refrigerant can pass under the water outlet port and reach the peripheral area of the non-operating inlet port. This significantly improves the distribution of the refrigerant across the plate width, thereby providing a more uniform flow through the heat exchange flow path and the total effective heat transfer of the heat exchanger by the peripheral area of the non-working inlet port. The area also becomes larger.

  In order to further improve the distribution of the refrigerant, the second refrigerant channel is located between the lower distribution flow path 50 and the heat exchange flow path 51 above the working inlet port and the non-working inlet port. Side distribution paths 55 and 56 are provided. The lower distribution path is mainly constituted by flat distribution grooves 318, 319, 418, 419 in both plates between the V shape of the distribution area and the W shape of the heat exchange area, and the length of the plate It extends from the side to the water outlet port hole. The lower distribution path, on the one hand, promotes uniform distribution of the refrigerant into the heat exchange channel 51, and on the other hand, the transition region between the V-shaped layout of the distribution region and the W-shaped layout of the heat exchange region. Will play a role. The height and shape of the lower distribution path can be selected to optimize flow distribution. The height of the groove may be about half of the press depth of the plate in one example. In order to improve the mechanical strength of the heat exchanger, the lower distribution path may have one or more contact points. Since the corresponding distribution path will be created in the water channel, the height of the lower distribution path in the refrigerant channel is preferably not more than one press depth in total. The lower distribution path has a lower flow resistance in the horizontal direction of the flow path compared to the flow resistance through the flow tube of the same length and width in the waveform pattern of the heat exchange flow path. The lower distribution paths 55, 56 may have one or more restricted areas to control flow distribution across the width of the channels in the lower distribution flow path. The restricted area may be one or more similar contact points that are fairly small, so that only one or a few small channels are configured between the distribution channel and the heat exchange channel. May be relatively large.

  The refrigerant enters the working inlet port 63 and is distributed in the lower distribution flow path 50, and then enters and passes through the heat exchange flow path 51 in the same manner as described for the first refrigerant channel. Become.

  Flat horizontal distribution grooves 320 and 420 are pressed on each plate between the heat exchange area and the upper distribution area of each plate to form an upper distribution path 57 in the second refrigerant channel. The upper distribution path can occur in the heat exchange flow path due to fluctuations in refrigerant evaporation before the refrigerant enters the upper distribution flow path 52 formed between the upper distribution areas 304, 404 of the plate. Even pressure difference is made uniform. The refrigerant may be partially or completely evaporated at this stage and may be further superheated. In the upper distribution path, since the flow resistance is low in the horizontal direction of the heat exchanger, distribution of the refrigerant is promoted before entering the upper distribution flow path. The height of each distribution path is about half of the press depth of the plate because a corresponding horizontal distribution path is created in the water channel. As a result, the total distribution path is one press deep.

  The refrigerant that is mostly evaporated at the crossing portion enters the upper distribution flow path 52 formed by the upper distribution regions 304 and 404 of the plate. The second refrigerant outlet port 64 which is an operation port is formed at the position of the second refrigerant outlet port holes 310 and 410 between the plates. A part of the refrigerant enters the upper distribution channel on the left side of the vertical axis 305, and a part of the refrigerant enters the upper distribution channel on the right side of the vertical axis 305. A part of the refrigerant reaches the non-operational outlet port bypass flow path 60 constituted by the bypass portions 323 and 423 extending around the entire periphery of the first refrigerant outlet port 62 that is the non-operational outlet port. The first refrigerant outlet port holes 308 and 408 are provided with concentric sealing portions 328 and 428 that are pressed against each other to seal the first outlet port. The bypass portion has the same press depth as the corrugated portion of the plate. Therefore, the resulting bypass flow path has a height twice the press depth. This means that the friction in the bypass channel is much less than the friction along the corrugated pattern. Thus, the bypass channel allows a substantial portion of the refrigerant that may be overheated to pass through the transverse corrugated pattern channel above the water inlet port to the working outlet port.

  The flat circular portions around the water inlet port holes 311 and 411 are pressed against each other, and the water inlet is sealed from the refrigerant channel. The water inlet port hole is arranged vertically away from the upper short side end of each plate. The center of the water inlet port hole is located closer to the horizontal axis of the plate than the center of the refrigerant outlet port hole. In this way, the upper horizontal flow path 54 is disposed in the refrigerant channel between the water inlet port and the upper short side end of the heat exchanger. Through this horizontal flow path, the refrigerant flows above the water inlet port, and is an operating outlet port configured between the bypass flow path 60 at the position of the non-operating outlet port 62 and the second refrigerant outlet port holes 310 and 410. It can flow up to 64. This considerably improves the distribution of the refrigerant flow in the upper distribution flow path and prevents heat concentration around the non-working outlet port. Furthermore, the total effective heat transfer area of the heat exchanger is increased by the peripheral area of the non-working outlet port.

  The present invention can provide an improved three circuit plate heat exchanger with a substantial improvement in the overall thermal performance of the heat exchanger. This is due to improved flow distribution in the heat exchanger. The invention should not be regarded as limited by the embodiments described above, but numerous further variations and modifications are possible in the claims that follow.

DESCRIPTION OF SYMBOLS 1 Plate assembly 2 1st refrigerant | coolant channel 3 Water channel 4 2nd refrigerant | coolant channel 10 Lower distribution flow path 11 Heat exchange flow path 12 Upper distribution flow path 13 Lower horizontal flow path 14 Upper horizontal flow path 15 Lower distribution Path 16 Lower distribution path 17 Upper distribution path 18 First refrigerant inlet port bypass flow path 19 Second refrigerant inlet port bypass flow path 20 Second refrigerant outlet port bypass flow path 21 Operation inlet port 22 Operation outlet port 23 Non-passage Operating inlet port 24 Non-operating outlet port 25 Inlet nozzle 30 Lower distribution flow path 31 Heat exchange flow path 32 Upper distribution flow path 33 Lower horizontal flow path 34 Upper horizontal flow path 35 Lower distribution path 36 Lower distribution path 37 Upper side Distribution path 38 Water bypass channel 39 Water bypass channel 40 Water bypass channel 41 Water bypass channel 42 Water inlet port 43 Water outlet port 50 Lower distribution flow path 51 Heat exchange flow path 52 Upper distribution flow path 53 Lower horizontal flow path 54 Upper horizontal flow path 55 Lower distribution path 56 Lower distribution path 57 Upper distribution path 58 First refrigerant inlet port bypass flow Path 59 Second refrigerant inlet port bypass flow path 60 First refrigerant outlet port bypass flow path 61 Non-working inlet port 62 Non-working outlet port 63 Working inlet port 64 Working outlet port 65 Inlet nozzle 101 First heat exchange plate 102 Lower distribution area 103 Heat exchange area 104 Upper distribution area 105 Vertical axis 106 Horizontal axis 107 First refrigerant inlet port hole 108 First refrigerant outlet port hole 109 Second refrigerant inlet port hole 110 Second refrigerant outlet Porthole 111 Water inlet porthole 112 Water outlet porthole 113 Sealed part 114 Nozzle recess 115 Bypass portion 116 Sealed portion 117 Bypass portion 118 Lower distribution groove 119 Lower distribution groove 120 Upper distribution groove 121 Bypass portion 122 Sealed portion 123 Flat portion 124 Lower water bypass portion 125 Lower water bypass portion 126 Upper water Bypass portion 127 Upper water bypass portion 201 Second heat exchange plate 202 Lower distribution region 203 Heat exchange region 204 Upper distribution region 205 Vertical axis 206 Horizontal axis 207 First refrigerant inlet port hole 208 First refrigerant outlet port Hole 209 Second refrigerant inlet port hole 210 Second refrigerant outlet port hole 211 Water inlet port hole 212 Water outlet port hole 213 Sealed portion 214 Nozzle recess 215 Bypass portion 216 Sealed portion 217 Viper Portion 218 Lower distribution groove 219 Lower distribution groove 220 Upper distribution groove 221 Bypass portion 222 Sealing portion 223 Flat portion 224 Lower water bypass portion 225 Lower water bypass portion 226 Upper water bypass portion 227 Upper water bypass portion 301 Third Heat exchange plate 302 Lower distribution area 303 Heat exchange area 304 Upper distribution area 305 Vertical axis 306 Horizontal axis 307 First refrigerant inlet port hole 308 First refrigerant outlet port hole 309 Second refrigerant inlet port hole 310 Second 2 Refrigerant outlet port hole 311 Water inlet port hole 312 Water outlet port hole 313 Sealed portion 314 Nozzle recess 315 Bypass portion 316 Sealed portion 317 Bypass portion 318 Lower distribution groove 319 Lower distribution groove 320 Upper distribution groove 321 Flat Minute 323 Bypass portion 324 Lower water bypass portion 325 Lower water bypass portion 326 Upper water bypass portion 327 Upper water bypass portion 328 Sealed portion 401 Fourth heat exchange plate 402 Lower distribution region 403 Heat exchange region 404 Upper distribution region 405 Vertical axis 406 Horizontal axis 407 First refrigerant inlet port hole 408 First refrigerant outlet port hole 409 Second refrigerant inlet port hole 410 Second refrigerant outlet port hole 411 Water inlet port hole 412 Water outlet port hole 413 Sealed portion 414 Nozzle recess 415 Bypass portion 416 Sealed portion 417 Bypass portion 418 Lower distribution groove 419 Lower distribution groove 420 Upper distribution groove 421 Flat portion 423 Bypass portion 424 Lower water bypass portion 425 Lower water bypass Portion 426 the upper water bypass section 427 upper water bypass portion 428 sealing portion

Claims (22)

First distribution with three port holes (107, 109, 112; 207, 209, 212; 307, 309, 312; 407, 409, 412) used in a three-circuit heat exchanger assembly (1) Region (102; 202; 302; 402), heat exchange region (103; 203; 303; 403) and three port holes (108, 110, 111; 208, 210, 211; 308, 310, 311; 408) , 410, 411) and a second distribution area (104; 204; 304; 404), and the central port hole (111, 112; 211, 212; 311, 312; 411, 412) Is a port hole for water, and the other port holes (107, 108, 109, 110; 207, 208, 209, 210; 307, 308, 3 9,310; 407,408,409,410) is a porthole for refrigerant, a heat exchanger plate having a wave pattern having a plurality of ridges and a plurality of troughs (101; in 401); 201; 301
When the two plates are stacked such that a refrigerant channel is formed therebetween, the central port hole (112; 212, 312; sealed with respect to the refrigerant channel in the first distribution region; between the short end of the plate 412) such that said fluid flow path only part of the refrigerant flows is obtained, the central port flowing from the porthole other than the center of the porthole The heat exchange plate according to claim 1, wherein the holes are arranged vertically away from the end portions on the short side of the plate with respect to the port holes other than the central port hole. When the two plates are stacked so that a refrigerant channel is formed between them, in the second distribution region, the central port hole (111; 211, 311; 411) and the short side of the plate The center port hole is disposed vertically away from the short-side end of the plate so that a fluid flow path can be obtained between the plate and the end. Plate as described in.   The port holes (107, 109, 110; 207, 209, 210; 307, 308, 309; 407, 408, 409) located at the corners of the plate form a refrigerant fluid channel between the plates. A flat and annular bypass portion (115, 117, 121; 215, 217, 221; 315, 317) is formed so as to form a refrigerant bypass passage around the port when two plates are stacked together. , 323; 415, 417, 423).   When two plates are stacked such that a water channel is formed between the plates, two adjacent water bypass portions (124, 125, 126, 127; 224, 225, 226, 227; 324) , 325, 326, 327; 424, 425, 426, 427), the water bypass portion is provided at a corner of the plate so as to obtain a water flow path. 4. The plate according to 3.   The first distribution region (102; 202; 302; 402) has a chevron shape having a first layout, and the second distribution region (104; 204; 304; 404) has a chevron shape having a second layout. The heat exchange region (103; 203; 303; 403) has a chevron shape having a third layout, and the chevron shape of the first layout faces a first angular direction. The plate according to any one of claims 1 to 4, wherein the chevron shape of the second layout is oriented in an opposite angular direction.   The plate according to claim 5, wherein the chevron shape having the third layout faces the same angular direction as the chevron shape having the first layout.   The plate according to claim 5, wherein the chevron shape having the third layout has more direction change points than the chevron shape having the first and second layouts.   8. The chevron shape having the first and second layouts is similar to a V shape, and the chevron shape having the third layout is similar to a W shape. 2. The plate according to item 1.   Two lower distribution grooves (118, 119; 218, 219; 318, 319; 418, 419) adjacent to each other when the two plates are stacked so that a fluid channel is formed between the plates. 9. The lower distribution groove is provided between the first distribution area and the heat exchange area so that a lower distribution path can be obtained between the first distribution area and the heat exchange area. The plate according to any one of the above.   The lower distribution groove (118, 119; 218, 219; 318, 319; 418, 419) has at least one restriction region so that flow restriction is obtained in the lower distribution path. The plate according to claim 9, wherein:   When two plates are stacked so that a fluid channel is formed between the plates, an upper distribution path is obtained between two upper distribution grooves (120; 220; 320; 420) adjacent to each other. 11. The plate according to claim 1, wherein the upper distribution groove is provided between the heat exchange region and the second distribution region.   Four plates according to any one of claims 1 to 11, wherein the first plate (101), the second plate (201), the third plate (301), A heat exchanger assembly, characterized in that it is different from the fourth plate (401).   A first refrigerant channel (2) is provided between the first plate (101) and the second plate (201), and a water channel (3) is formed between the second plate (201) and the second plate (201). Each of the three plates (301) and the second refrigerant channel (4) is provided between the third plate (301) and the fourth plate (401). The channel (2, 3, 4) includes a first distribution channel (10; 30; 50) provided between two first distribution regions (102, 202, 302, 402) adjacent to each other. A heat exchange flow path (11; 31; 51) provided between two heat exchange regions (103, 203, 303, 403) adjacent to each other, and two second distribution regions (104, 204) adjacent to each other. , 304, 404) in the second distribution Wherein the horizontal flow path (13; 33; 53) is adjacent to the central water port (43) and the central water port (43). The heat exchanger assembly according to claim 12, wherein the heat exchanger assembly is provided in the first distribution flow path between the three-dimensional short side end portion.   A horizontal flow path (14; 34; 54) is the second distribution flow path (between the central water port (42) and the short side end of the assembly adjacent to the central water port (42). The heat exchanger assembly according to claim 12 or 13, wherein the heat exchanger assembly is provided at 12; 32; 52).   Water distribution flow in which water bypass channels (38, 39, 40, 41) are located between the refrigerant ports (21, 22, 23, 24; 61, 62, 63, 64) and the corners of the assembly. 15. A heat exchanger assembly according to any one of claims 12 to 14, characterized in that it is provided in the path (30, 32).   Refrigerant bypass channels (18, 19, 20; 58, 59, 60) are connected to the refrigerant ports (21, 23, 24; 61, 62, 63) in the refrigerant distribution channels (10, 12; 50, 52). The heat exchanger assembly according to any one of claims 12 to 15, wherein the heat exchanger assembly is provided around the periphery.   The working inlet port (21) comprises an inlet nozzle (25), the working inlet port (63) comprises an inlet nozzle (65), the angle of both said inlet nozzles being from 0 ° to 180 ° with respect to the vertical axis. 17. A heat exchanger assembly according to any one of claims 12 to 16, characterized in that the inlet nozzle is in degrees and faces the vertical axis in the center of the assembly.   The heat exchanger assembly of claim 17, wherein the angle of the inlet nozzle is between 90 degrees and 150 degrees.   Lower distribution paths (15, 16; 35, 36; 55, 56) are provided between the lower distribution flow paths (10, 30, 50) and the heat exchange flow paths (11, 31, 51). 19. A heat exchanger assembly according to any one of claims 12 to 18, characterized in that   The upper distribution path (17, 37, 57) is provided between the heat exchange flow path (11, 31, 51) and the upper distribution flow path (12, 32, 52). The heat exchanger assembly according to any one of 12 to 19.   21. The heat exchange plate (101; 201; 301; 401) is joined by gluing, soldering, brazing, bonding, or welding. Heat exchanger assembly.   A three-circuit heat exchanger comprising a plurality of heat exchanger assemblies according to any one of claims 12 to 21 and further comprising a front plate and a rear plate.

Images