Shell and plate heat exchangers and heat exchange systems

Abstract

To provide a shell and plate type heat exchanger which enables reduction of a loading amount of a heat medium liquid in a shell, and to provide a heat exchange system.SOLUTION: A shell and plate type heat exchanger 30 includes a shell 35, a plate laminated body 40, and a discharge pipe 50. The shell 35 has a liquid reservoir part 37 of a first heat medium liquid T in a lower area. The plate laminated body 40 is disposed in the shell 35 so as to be partially immersed in the liquid reservoir part 37. The discharge pipe 50 is located above the plate laminated body 40 in the shell 35 and configured to discharge the first heat medium liquid T into the shell 35. The discharge pipe 50 is disposed at a position offset from a center 40C of the plate laminated body 40 in a lamination direction of the plate laminated body 40 and a width direction orthogonal to the lamination direction in a plan view.SELECTED DRAWING: Figure 3

Description

Technical Field

[0001] The present disclosure relates to a shell-and-plate heat exchanger and a heat exchange system.

Background Art

[0002] Conventionally, shell-and-plate heat exchangers are known. For example, Patent Document 1 discloses a shell-and-plate evaporator. In the hollow container of the evaporator, NH3 refrigerant liquid is discharged from the nozzle opening of the nozzle pipe onto the plate polymer. The NH3 refrigerant liquid exchanges heat with CO2 refrigerant flowing through the flow path formed in the plate polymer and vaporizes. The vaporized NH3 refrigerant gas is discharged from the hollow container.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, Patent Document 1 does not disclose a configuration for reducing the filling amount of NH3 refrigerant liquid in the evaporator.

[0005] An object of the present disclosure is to provide a shell-and-plate heat exchanger and a heat exchange system capable of reducing the filling amount of the heat transfer medium liquid.

Means for Solving the Problems

[0006] The shell-and-plate heat exchanger according to at least one embodiment of the present invention includes a shell having a liquid reservoir portion for the first heat transfer medium liquid, a plate laminate disposed in the shell so as to be partially immersed in the first heat transfer medium liquid, A discharge pipe located above the plate stack within the shell for discharging the first heat transfer liquid into the shell, Equipped with, In a plan view, the discharge pipe is positioned at a location offset from the center of the plate stack in both the stacking direction of the plate stack and the width direction perpendicular to the stacking direction.

[0007] The heat transfer fluid circulation system according to at least one embodiment of the present invention is The above shell-and-plate heat exchanger, A compressor for drawing in and compressing the first heat transfer gas, which is the vaporized first heat transfer liquid discharged from the shell, A condenser for the first heat transfer gas discharged from the compressor to exchange heat with a heat exchange medium and be converted into the first heat transfer liquid, A receiver connected to the condenser and the shell-and-plate heat exchanger, which stores the first heat transfer fluid discharged from the condenser, An expansion valve is provided in the supply path connecting the receiver and the shell-and-plate heat exchanger to reduce the pressure of the first heat transfer fluid. It is equipped with. [Effects of the Invention]

[0008] The present disclosure provides a shell-and-plate heat exchanger and a heat exchange system that can reduce the amount of heat transfer medium packed in the shell. [Brief explanation of the drawing]

[0009] [Figure 1] This is a diagram showing the configuration of a heat exchange system 1 according to one embodiment. [Figure 2] This is a cross-sectional view of a heat exchanger 30 according to one embodiment. [Figure 3] This is another cross-sectional view of the heat exchanger 30 according to one embodiment. [Figure 4A] This is a plan view from above of a discharge pipe 50 according to one embodiment. [Figure 4B]It is a plan view from above the discharge pipe 50 according to another embodiment. [Figure 4C] It is a plan view from above the discharge pipe 50 according to another embodiment. [Figure 4D] It is a plan view from above the discharge pipe 50 according to another embodiment. [Figure 5] It is a view in the width direction of the plate laminate 40 and the discharge pipe 50 according to one embodiment. [Figure 6] It is a view in the stacking direction of the plate 44A according to one embodiment. [Figure 7] It is a view in the stacking direction of the plate 44B according to one embodiment. [Figure 8] It is a view in the stacking direction of the plates 44A and 44B according to one embodiment. [Figure 9] It is a diagram showing the relationship between the temperature of the first heat medium liquid T and the temperature of the second heat medium R according to one embodiment.

Embodiments for Carrying Out the Invention

[0010] Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples. For example, expressions representing relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric", or "coaxial" not only strictly represent such arrangements, but also represent a state of relative displacement with tolerances or at an angle or distance such that the same function can be obtained. For example, expressions representing a state where things such as "identical", "equal", and "homogeneous" are equal not only strictly represent an equal state, but also represent a state where there are tolerances or differences such that the same function can be obtained. For example, expressions representing shapes such as a rectangular shape or a cylindrical shape not only represent the shapes such as a rectangular shape or a cylindrical shape in a geometrically strict sense, but also represent shapes including concave and convex portions, chamfered portions, etc. within a range where the same effect can be obtained. On the other hand, expressions such as "to possess," "to be equipped with," "to have," "to include," or "to have" a single component are not exclusive expressions that exclude the existence of other components.

[0011] Figure 1 is a diagram showing the configuration of a heat exchange system 1 according to one embodiment. The heat exchange system 1 includes a shell-and-plate heat exchanger 30. One embodiment of the shell-and-plate heat exchanger 30 (hereinafter also referred to as heat exchanger 30) is, for example, a full-liquid evaporator. In the heat exchanger 30 of one embodiment, the first heat transfer liquid T and the second heat transfer medium R exchange heat, causing the first heat transfer liquid T to vaporize and change into the first heat transfer gas Tv, and the second heat transfer medium R to cool and condense. One embodiment of the heat exchange system 1 includes a first heat transfer fluid circulation system 10 that constitutes a circulation cycle for a first heat transfer fluid T, and a second heat transfer fluid circulation system 20 that constitutes a circulation cycle for a second heat transfer fluid R.

[0012] In one embodiment of the second heat transfer medium circulation system 20, the gaseous second heat transfer medium R is cooled and liquefied by heat exchange in the heat exchanger 30. The liquefied second heat transfer medium R discharged from the heat exchanger 30 is sent to the receiver 28 via the circulation path 14. The liquid second heat transfer medium R stored in the receiver 28 is sent to the cooler 29 via the supply path 25 by the pump 17. The cooler 29 is, for example, a component of an air conditioner. In the cooler 29, the second heat transfer medium R exchanges heat with, for example, air. The air is cooled by the latent heat of vaporization of the second heat transfer medium R and sent to a designated space. Meanwhile, at least a portion of the second heat transfer medium R vaporizes through heat exchange with the air and is sent to the receiver 28 via the return path 19. The vaporized second heat transfer medium R in the receiver 28 is sent to the heat exchanger 30 via the circulation path 15 and liquefied again through heat exchange with the first heat transfer medium liquid T. In one embodiment of the second heat transfer medium circulation system 20, the second heat transfer medium R is a CO2 refrigerant. In one embodiment of the second heat transfer medium circulation system 20, a pressure is maintained at which the second heat transfer medium R can evaporate at room temperature. The second heat transfer medium R may be a heat transfer medium other than CO2. In other embodiments, the second heat transfer medium R may be cooling water or the like. Also, in the cooler 29, the second heat transfer medium R may exchange heat with a refrigerant other than air. The cooler 29 may be a component of a refrigerator or the like, instead of being a component of an air conditioner. Furthermore, in some embodiments, the heat exchanger 30 may be used as a condenser.

[0013] One embodiment of the first heat transfer medium circulation system 10 includes the heat exchanger 30 described above, a compressor 16 for compressing the first heat transfer medium gas Tv discharged from the heat exchanger 30, a condenser 11 for the first heat transfer medium gas Tv discharged from the compressor 16 to exchange heat with the heat exchange medium and be converted into a first heat transfer medium liquid T, a receiver 12 for storing the first heat transfer medium liquid T sent from the condenser 11, and an expansion valve 22 provided in a supply passage 13 connected to the receiver 12 and the heat exchanger 30, for reducing the pressure of the first heat transfer medium liquid T. Details of the heat exchanger 30 in one embodiment will be described later, but the heat exchanger 30 has a liquid reservoir 37 for the first heat transfer fluid T. The first heat transfer gas Tv discharged from the heat exchanger 30 is, for example, superheated steam. The degree of superheating of the first heat transfer gas Tv is maintained at a high level so that the compressor 16 that draws in the first heat transfer gas Tv can operate properly and liquid compression in the compressor 16 is suppressed. In one embodiment, the heat exchanger 30 is connected to an oil return passage 21 for returning the refrigerant oil E accumulated inside the heat exchanger 30 to the compressor 16. An on / off valve 24 is provided in the oil return passage 21. In one embodiment, since the specific gravity of the refrigerant oil E is greater than the specific gravity of the first heat transfer fluid T, the refrigerant oil E accumulates at the bottom of the liquid reservoir 37. In one embodiment, the condenser 11 is an evaporative condenser. In the condenser 11 of this embodiment, the first heat transfer medium gas Tv supplied from the compressor 16 is liquefied by heat exchange with cooling water. More specifically, the cooling water stored in the condenser 11 is pumped up by a water pump 11A and sprayed into the interior of the condenser 11 by heat transfer tubes 11B. The first heat transfer medium gas Tv flowing through the heat transfer tubes 23 inside the condenser 11 is cooled by the sprayed cooling water and changes into the first heat transfer medium liquid T. In other embodiments, the condenser 11 may be a water-cooled condenser or the like instead of an evaporative condenser. In one embodiment, the receiver 12 stores a first heat transfer fluid T, which is then sent to the heat exchanger 30 via a supply passage 13. The first heat transfer fluid T is depressurized by an expansion valve 22 during the process of being supplied to the heat exchanger 30. In one embodiment, refrigerant oil E is mixed into the first heat transfer medium gas Tv sent from the compressor 16 to the condenser 11. Consequently, refrigerant oil E is also mixed into the first heat transfer medium liquid T supplied to the heat exchanger 30. In one embodiment of the first heat transfer fluid circulation system 10, the first heat transfer fluid T is liquid ammonia, and the first heat transfer fluid Tv is ammonia gas. The first heat transfer fluid T and the first heat transfer fluid Tv may be heat transfer fluids other than ammonia. The heat exchange system 1 described above is a refrigeration cycle in which the first heat transfer fluid T is the primary refrigerant and the second heat transfer fluid R is the secondary refrigerant (brine). However, in other embodiments, the heat exchange system 1 may be applied to a binary refrigeration cycle. In this case, the first heat transfer fluid T is the primary refrigerant, the second heat transfer fluid R is the secondary refrigerant, and the heat exchanger 30 may be used as a cascade condenser.

[0014] Figure 2 is a cross-sectional view of a heat exchanger 30 according to one embodiment. Figure 3 is another cross-sectional view of the heat exchanger 30 according to one embodiment. Figure 2 is a cross-sectional view of the heat exchanger 30 along the width direction, which will be described later. Figure 3 is a cross-sectional view taken along line II in Figure 2.

[0015] In one embodiment, the heat exchanger 30 comprises a shell 35. The shell 35 in one embodiment has a liquid reservoir 37 for the first heat transfer fluid T. The shell 35 houses a plate stack 40, a discharge pipe 50, and a discharge duct 60. In one embodiment, the oil outlet 33, which is a component of the shell 35, is located below the plate stack 40 and is configured to discharge the refrigerant oil E that accumulates in the liquid reservoir 37. The oil outlet 33 is connected to the oil return passage 21 described above. In one embodiment, the shell 35 is cylindrical. For example, the shell wall portion 36 of the shell 35 is a peripheral wall portion.

[0016] The plate stack 40 is placed within the shell 35 so as to be partially immersed in the first heat transfer fluid T located in the liquid reservoir 37. The plate stack 40 includes a plurality of stacked plates 44. In one embodiment, the plate stack 40 has a primary flow path A through which the first heat transfer liquid T and the first heat transfer gas flow, and a secondary flow path B through which the second heat transfer medium R flow. The primary flow path A communicates with the space inside the shell 35, and the secondary flow path B is blocked from this space. As an example, the primary flow path A and the secondary flow path B are arranged alternately along the stacking direction in which the multiple plates 44 are stacked. Both the primary flow path A and the secondary flow path B are spaces defined by the multiple plates 44. In one embodiment, at least the lower part of the primary flow path A is immersed in the first heat transfer fluid T in the liquid reservoir 37. The second heat transfer fluid R flowing down the secondary flow path B is supplied from the circulation path 15 (see Figure 1) via the inlet pipe 7 provided in the shell 35. In one embodiment, the second heat transfer fluid R flows downward within the secondary flow path B. In one embodiment, heat transfer from the second heat transfer medium R to the first heat transfer liquid T via the plate 44 causes the gaseous second heat transfer medium R to condense, and the first heat transfer liquid T vaporizes and changes into the first heat transfer gas Tv. In one embodiment, the condensed second heat transfer medium R is discharged into the circulation path 14 (see Figure 1) via the outlet pipe 6 provided in the shell 35. The first heat transfer gas Tv flows down the primary flow path A and escapes upward from the plate stack 40. In one embodiment, the first heat transfer gas Tv is heated until it becomes superheated steam. Further details of the configuration of the plate stack 40 will be described later. In the following explanation, the stacking direction of the plate stack 40 may be simply referred to as the stacking direction, and the direction perpendicular to the stacking direction and the vertical direction may be referred to as the width direction.

[0017] The discharge pipe 50 is located above the plate stack 40 within the shell 35 and is configured to discharge the first heat transfer fluid T into the shell 35. For example, the discharge pipe 50 is connected to a supply port 38 provided in the shell 35. In one embodiment, the discharge pipe 50 includes at least one discharge port 51 for discharging the first heat transfer fluid T supplied to the heat exchanger 30. In one embodiment, the discharge port 51 discharges the first heat transfer fluid T supplied from the supply passage 13 (see Figure 1) described above. In one embodiment, the discharged first heat transfer fluid T directly reaches at least one of the plate stack 40 or the shell wall portion 36. In another embodiment, the discharged first heat transfer fluid T may reach the liquid surface of the first heat transfer fluid T in the liquid reservoir portion 37 without directly contacting either the plate stack 40 or the shell wall portion 36. In this case, the discharge pipe 50 may be positioned in an upper or lower position close to the plate stack 40. In one embodiment, the discharge pipe 50 is positioned offset from the center 40C of the plate stack 40 in both the stacking direction and the width direction, in a plan view. By positioning the discharge pipe 50 offset from the center 40C, the areas to which the discharged first heat transfer fluid T directly reaches are concentrated. As an example, the discharge pipe 50 is positioned on one side of the center 40C in the stacking direction and on one side of the width direction (see Figures 2 and 3). The center 40C is perceived as a straight line extending vertically in the stacking direction or width direction (see Figures 2 and 3), and as a point in a plan view (Figures 4A to 4D). In one embodiment, the discharge port 51 is provided in the discharge pipe 50 in a region opposite in the width direction to the center 40C of the plate stack 40 with respect to the central axis 57 of the discharge pipe 50. In this case, the discharge port 51 is not provided in the region of the discharge pipe 50 on the other side in the width direction with respect to the central axis 57. In one embodiment, the discharge port 51 opens on one side in the width direction and on the lower side in the vertical direction. The direction of the opening of the discharge port 51 is the direction in which the axis of the discharge port 51 extends. In one embodiment, the discharge port 51 is positioned offset from the oil discharge port 33 in the stacking direction. This suppresses the mixing of the first heat transfer fluid T discharged from the discharge port 51 and the refrigerant oil E accumulated in the liquid reservoir 37, thereby suppressing the diffusion of the refrigerant oil E in the liquid reservoir 37. Note that the first heat transfer fluid T discharged from the discharge pipe 50 may contain refrigerant oil E.

[0018] The discharge duct 60 is located within the shell 35 and is configured to discharge the first heat transfer medium gas Tv from the shell 35. For example, the discharge duct 60 is located above the discharge pipe 50 and is joined to an outlet 32 ​​provided in the shell 35. For example, the discharge duct 60 is a hollow body extending in the stacking direction. In one embodiment, the shape of the discharge duct 60 in the stacking direction view is trapezoidal, but it may be other polygonal or circular shapes. In one embodiment, the discharge duct 60 includes at least one communication port 63 that communicates with the space within the shell 35. In one embodiment, the first heat transfer fluid Tv that has escaped from the plate stack 40 flows into the discharge duct 60 through the communication port 63 and is discharged from the discharge port 32. The discharged first heat transfer fluid is drawn into the compressor 16. In one embodiment, the communication port 63 is located offset from the discharge port 51 of the discharge pipe 50 in the stacking direction. In other words, the discharge port 51 is located offset from the communication port 63 in the stacking direction of the plate stack 40. This suppresses the mixing of the first heat transfer medium gas Tv rising towards the communication port 63 within the shell 35 and the discharged first heat transfer medium liquid T, thereby suppressing a decrease in the superheating degree of the first heat transfer medium gas Tv flowing into the discharge duct 60. Consequently, a decrease in the superheating degree of the first heat transfer medium gas drawn in by the compressor 16 is suppressed, and liquid compression by the compressor 16 is suppressed. In one embodiment, the discharge duct 60 is positioned offset in the width direction from the discharge port 51 of the discharge pipe 50. In other words, the discharge port 51 is positioned offset in the width direction from the discharge duct 60. This suppresses the mixing of the first heat transfer medium gas Tv rising towards the discharge duct 60 within the shell 35 and the discharged first heat transfer medium liquid T, thereby suppressing a decrease in the superheating degree of the first heat transfer medium gas Tv discharged from the discharge port 32.

[0019] Figures 4A to 4D are top views of discharge pipes 50A to 50D (50) according to one embodiment. As shown in Figures 4A to 4D, the discharge pipes 50A to 50D (50) are positioned offset from the center 40C of the plate stack 40 in a plan view. As shown in Figures 4A and 4B, the discharge pipes 50A and 50B (50) may be positioned on one side in the width direction relative to the center 40C. In this case, the direct contact of the discharged first heat transfer fluid T with more than half of the width direction area of ​​each plate 44 constituting the plate stack 40 is suppressed. Furthermore, as shown in Figure 4B, the discharge pipe 50B(50) may be positioned offset from the plate stack 40 in a plan view. In this case, it is possible to suppress the direct contact of the discharged first heat transfer fluid T with the entire plate stack 40. In the example of Figure 4B, the first heat transfer fluid T discharged from the discharge pipe 50B directly contacts the shell wall portion 36. Furthermore, as shown in Figures 4C and 4D, the discharge pipes 50C and 50D (50) may be positioned offset to one side with respect to the stacking direction relative to the center 40C of the plate stack 40. In this case, it is possible to suppress the direct contact of the discharged first heat transfer fluid T with more than half of the plates 44 constituting the plate stack 40. Furthermore, as shown in Figure 4D, the length of the discharge pipe 50D in the stacking direction (dimension Ld) may be 1 / 2 or less of the length of the plate stack 40 in the stacking direction (dimension Lp). In this case, the number of plates 44 that are directly exposed to the discharged first heat transfer fluid T is further reduced. Note that dimension Ld may be 1 / 3 or 1 / 4 or less of dimension Lp. Discharge pipes 50 whose length in the stacking direction is less than or equal to the specified value do not overlap with the plate stack 40 in a plan view.

[0020] Figure 5 is a view in the width direction of the plate stack 40 and discharge pipe 50 according to one embodiment. In Figure 5, the condensed second heat transfer medium R is not shown.

[0021] As described above, the plate laminate 40 according to one embodiment includes a plurality of stacked plates 44. In one embodiment, a predetermined uneven pattern is formed on each plate 44. For example, the uneven pattern is wave-shaped. In other embodiments, the uneven pattern may not be formed on each plate 44. In one embodiment, the multiple plates 44 include plates 44A and 44B arranged alternately in the stacking direction. Each of the plates 44A and 44B has an upper connecting passage 47 and a lower connecting passage 48. In one embodiment, the upper connecting passage 47 and the lower connecting passage 48 are formed in the center of the plate 44 in the width direction. For example, the upper connecting passage 47 and the lower connecting passage 48 are circular in shape when viewed in the stacking direction. In one embodiment, in at least one of the plates 44, the upper connecting passage 47 is connected to an inlet pipe 7 and the lower connecting passage 48 is connected to an outlet pipe 6. In one embodiment, adjacent plates 44A and 44B are joined by first joints 101 or second joints 102 that are alternately arranged in the stacking direction. In one embodiment, the first joint 101 joins two adjacent upper connecting passages 47 in the stacking direction and also joins two adjacent lower connecting passages 48 in the stacking direction. The space defined by the plates 44A and 44B joined by the first joint 101 is the primary flow path A described above. In one embodiment, the primary flow path A is immersed in the first heat transfer fluid T located in the liquid reservoir 37. The upper end of the primary flow path A is an opening at the upper end of the plate stack 40. For example, the first heat transfer fluid T can enter this opening located below the discharge port 51. In one embodiment, the second joint 102 joins the outer peripheral edges 49 of two adjacent plates 44 in the stacking direction. The space defined by the plates 44A and 44B joined by the second joint 102 is the secondary flow path B described above. In an embodiment in which a wave-shaped uneven pattern is formed on the plate 44, the primary channel A and the secondary channel B are wave-shaped.

[0022] In one embodiment, the gaseous second heat transfer medium R supplied from the inlet pipe 7 flows into the secondary flow path B via the upper connecting passage 47. As the gaseous second heat transfer medium R flows downward through the secondary flow path B, it imparts heat to the first heat transfer liquid T and condenses. The condensed second heat transfer medium R passes through each of the lower connecting passages 48 and is discharged from the outlet pipe 6. On the other hand, the first heat transfer liquid T in the liquid reservoir 37 is transformed into the first heat transfer gas Tv by the imparting of heat. The first heat transfer gas passes through the upper end of the primary flow path A and exits from the plate stack 40.

[0023] Figure 6 is a view of plate 44A in the stacking direction according to one embodiment. Figure 7 is a view of plate 44B in the stacking direction according to one embodiment. Figure 8 is a view of plates 44A and 44B in the stacking direction according to one embodiment. In Figure 8, plate 44B is shown by a dashed line.

[0024] As shown in Figures 6 and 7, plates 44A and 44B in one embodiment each exhibit a shape that is symmetrical in the width direction. Furthermore, in this example, plates 44A and 44B are symmetrical to each other in the width direction. In one embodiment, in each of plates 44A and 44B, the radius of curvature of the outer peripheral edge 49A, 49B(49) on one side in the width direction relative to the uppermost edge 46 is smaller than the radius of curvature of the uppermost edge 46. Therefore, plates 44A and 4B are non-circular in view in the stacking direction. In other embodiments, the plate 44 may be, for example, circular or elliptical in shape. Furthermore, each plate 44 may have an asymmetrical shape in the width direction.

[0025] As shown in Figure 6, in one embodiment, the plate 44A includes inclined protrusions 81-84. Multiple of each of these four types of protrusions are provided. In one embodiment, the inclined protrusions 81-84 are convex in the same direction in the stacking direction. In one embodiment, the inclined protrusions 81-84 are formed by press working, and both sides of the plate 44 are corrugated by the inclined protrusions 81-84. In one embodiment, the inclined protrusions 81 to 84 all extend vertically downward toward one side in the width direction. As an example, the inclined protrusions 81 to 84 all extend in a straight line. In one embodiment, of the inclined protrusions 81 to 84, inclined protrusion 81 is located below the discharge pipe 50. The multiple inclined protrusions 81 include multiple first protrusions 111. Each first protrusion 111 starts from an outer peripheral edge 49A (49) located on one side in the width direction from the center 40C and extends vertically downward toward the other side in the width direction. The upper end of each vertically adjacent first protrusion 111 defines an opening into which the discharged first heat transfer fluid T can enter. The discharged first heat transfer fluid T can enter the primary flow path A (see Figure 5) described above through this opening. In one embodiment, the first protrusion 111 extends in a direction at an angle of 45 degrees or less with respect to the horizontal plane. In this case, even if the first heat transfer fluid T enters the primary flow path A from the outer peripheral edge 49A of the plate 44A, the first heat transfer fluid T flows down along the first protrusion 111 to one side in the width direction and downward in the vertical direction. The angle of the extension direction of the first protrusion 111 with respect to the horizontal plane corresponds to angle θ in Figure 6. In other embodiments, the plate 44A may not have inclined protrusions 82-84, nor may it have inclined protrusions 81 other than the first protrusion 111. The acute angle between the extending direction of the first protrusion 111 and the horizontal plane may be greater than 45 degrees.

[0026] As shown in Figure 7, the plate 44B of one embodiment includes inclined protrusions 91 to 94. As described above, the plate 44B of one embodiment has a shape symmetrical to the plate 44A in the width direction. The inclined protrusion 91 has a shape symmetrical to the inclined protrusion 81 of the plate 44A. Similarly, the inclined protrusion 92 has a shape symmetrical to the inclined protrusion 82, the inclined protrusion 93 has a shape symmetrical to the inclined protrusion 83, and the inclined protrusion 94 has a shape symmetrical to the inclined protrusion 84. In one embodiment, a plurality of inclined protrusions 93 are located below the discharge pipe 50. The plurality of inclined protrusions 93 include a plurality of second protrusions 112. Each second protrusion 112 starts from an outer peripheral edge 49B (49) on one side in the width direction from the center 40C and extends vertically downward toward the other side in the width direction. The upper end of each of vertically adjacent second protrusions 112 defines an opening into which the discharged first heat transfer fluid T can enter. The discharged first heat transfer fluid T can enter the primary flow path A described above through this opening. In one embodiment, as previously described, in the stacking direction view, the radius of curvature of the outer peripheral edge 49B located on one side of the width direction relative to the uppermost end 46 is smaller than the radius of curvature of the uppermost end 46. As a result, the plate 44B in the stacking direction view becomes non-circular. Therefore, the number of openings into which the first heat transfer fluid T can enter, formed by the upper ends of adjacent second protrusions 112 in the vertical direction, is reduced. The reduction in the number of such openings is obvious when comparing the non-circular plate 44B with the circular plate 44B shown by the dashed line. By reducing the number of such openings, it is possible to suppress the entry of the first heat transfer fluid T into the primary flow path A. In other embodiments, as previously described, the plate 44 may be circular in shape.

[0027] As shown in Figure 8, in one embodiment, the multiple inclined protrusions 81 of plate 44A overlap with the multiple inclined protrusions 93 and 94 of plate 44B in the stacking direction. Also, the multiple inclined protrusions 82 overlap with the multiple inclined protrusions 92 in the stacking direction, and the multiple inclined protrusions 83 and 84 overlap with the multiple inclined protrusions 91 in the stacking direction. In one embodiment, since plates 44A and 44B are symmetrical with respect to each other in the width direction, the extension direction of the inclined protrusions 81-84 is opposite to that of the inclined protrusions 91-94. As a result, the number of intersections between any of the inclined protrusions 81-84 and any of the inclined protrusions 91-94 increases when viewed in the stacking direction. In the region where intersections occur, any of the inclined protrusions 81-84 and any of the inclined protrusions 91-94 face each other. In this region, the spacing between plates 44A and 44B in the stacking direction is narrow, making it difficult for the first heat transfer fluid T to flow down through the primary flow path A. Therefore, the increase in the number of intersections increases the space in which it is difficult for the first heat transfer fluid T to flow down. In other embodiments, plates 44A and 44B may be asymmetrical with respect to each other in the width direction.

[0028] Figure 9 shows the relationship between the temperature of the first heat transfer fluid T and the temperature of the second heat transfer fluid R according to one embodiment. The height of point S1 indicates the temperature immediately after the first heat transfer fluid T flows into the heat exchanger 30 (inlet temperature). For example, this supply temperature is the evaporation temperature of the first heat transfer fluid T. The height of point S2 indicates the temperature immediately after the first heat transfer gas Tv is discharged from the heat exchanger 30 (outlet temperature). Furthermore, the height of point S3 indicates the temperature immediately after the second heat transfer medium R flows into the heat exchanger 30 (inlet temperature), and the height of point S4 indicates the temperature immediately after the second heat transfer medium R is discharged from the heat exchanger 30 (outlet temperature). In one embodiment, the inlet and outlet temperatures of the second heat transfer medium R are the same. In other embodiments, these temperatures may be different. For example, in embodiments where a different brine is used as the second heat transfer medium R, the outlet temperature of the second heat transfer medium R is lower than the inlet temperature. In one embodiment, Δt in Figure 9 SH This indicates the superheating temperature of the first heat transfer gas Tv.

[0029] According to the inventors' findings, the relationship between the amount of heat exchanged Q between the first heat transfer fluid T and the second heat transfer fluid R in the heat exchanger 30 and the overall heat transfer coefficient K of the heat exchanger 30 is defined by the following equation (1). Q=K×A h ×Δt m ...Equation (1) A in equation (1) h Δt is the heat transfer area in the heat exchanger 30. m This is the arithmetic mean temperature difference in the heat exchanger 30. Also, the arithmetic mean temperature difference (Δt m The ratio is defined by Δt1, which is the difference between the inlet temperature of the second heat transfer medium R and the inlet temperature of the first heat transfer medium T, and Δt2, which is the difference between the outlet temperature of the second heat transfer medium R and the evaporation temperature of the first heat transfer medium T, as shown in equation (2). Δt m =(Δt1+Δt2) / 2 ...Equation (2) According to the inventors' findings, in some embodiments of the present disclosure, the heat exchange amount Q and the arithmetic mean temperature difference Δt are compared with the comparative embodiments described later. mIt was found that there was no significant difference. Therefore, it was found that there was no significant difference in the overall heat transfer coefficient K between the embodiment of this disclosure and the comparative embodiment. This means that when the heat exchange system 1 including the heat exchanger 30 is installed in a specified location, the amount of first heat transfer fluid T to be filled into the heat exchanger 30 can be reduced, and the heat exchange system 1 can be made less expensive. The comparative embodiment, as an example, is one in which the discharge pipe 50 extending in the stacking direction is positioned so as to overlap with the center 40C of the plate stack 40 in a plan view. More specifically, it is an embodiment in which the length of the discharge pipe 50 in the stacking direction is 1 / 2 or more of the stacking direction length of the plate stack 40.

[0030] Furthermore, in several embodiments of this disclosure, it has been confirmed that the liquid level of the first heat transfer fluid T in the liquid reservoir 37 of the heat exchanger 30 is lower compared to the comparative embodiments described above. This means that the amount of the first heat transfer fluid T accumulating in the liquid reservoir 37 of the shell 35 is reduced, and the space within the shell 35 that acts on the superheating of the first heat transfer fluid Tv is increased. In other words, in embodiments of this disclosure, the degree of superheating of the first heat transfer fluid Tv discharged from the heat exchanger 30 can be increased compared to the comparative embodiments. This makes it possible to suppress liquid compression in the compressor 16 that sucks in the first heat transfer fluid Tv discharged from the heat exchanger 30.

[0031] Below, several embodiments of a shell-and-plate heat exchanger 30 and a heat exchange system 1 will be described.

[0032] (1) A shell-and-plate heat exchanger 30 according to at least one embodiment of the present invention is A shell 35 having a liquid reservoir 37 for the first heat transfer fluid T, A plate stack 40 is placed inside the shell 35 so as to be partially immersed in the first heat transfer fluid T, Within the shell 35, a discharge pipe 50 is located above the plate stack 40 and discharges the first heat transfer fluid T into the shell 35, Equipped with, The discharge pipe 50 is positioned in a plan view at a location offset from the center 40C of the plate stack 40 in the stacking direction of the plate stack 40 and in the width direction perpendicular to the stacking direction.

[0033] According to the configuration described in (1) above, the discharge pipe 50 is positioned offset from the center 40C of the plate stack 40 in a plan view, so that the area where the discharged first heat transfer fluid T directly hits is concentrated. As a result, the area of ​​the plate stack 40 that is directly hit by the discharged first heat transfer fluid T can be reduced. Consequently, the area of ​​the plate stack 40 in which the first heat transfer fluid T inhibits the rise of the first heat transfer gas Tv is reduced. Therefore, the first heat transfer gas Tv can escape from the plate stack 40 more easily than before, and the amount of first heat transfer fluid T in the liquid reservoir 37 is reduced. Thus, a shell-and-plate type heat exchanger 30 that can reduce the amount of first heat transfer fluid T filled in the shell 35 is realized. For example, in the primary flow path A located below the discharge port 51, when the discharged first heat transfer fluid T moves toward the liquid reservoir 37, the space within the primary flow path A for the first heat transfer fluid gas to rise becomes smaller. Also, when the discharged first heat transfer fluid T remains near the upper end of the primary flow path A, at least a portion of the upper end of the primary flow path A is blocked by the first heat transfer fluid T. Therefore, when the first heat transfer fluid T from the discharge pipe 50 enters the primary flow path A, which includes a function as an upward path for the first heat transfer fluid gas, the escape of the first heat transfer fluid gas Tv from the plate stack 40 may be inhibited. In this respect, by adopting the above configuration, the direct inhibition of the rise of the first heat transfer fluid T by the first heat transfer fluid T is suppressed, and thus the vaporization of the first heat transfer fluid T in the liquid reservoir 37 can be promoted.

[0034] (2) In some embodiments, in the configuration of (1) above, The discharge pipe 50 is positioned offset to one side in the stacking direction relative to the center 40C of the plate stack 40.

[0035] According to the configuration described in (2) above, in more than half of the plates 44 that make up the plate stack 40, the first heat transfer gas Tv can avoid direct obstruction from the first heat transfer liquid T. Therefore, the first heat transfer gas Tv can escape more easily from the plate stack 40, and the amount of the first heat transfer liquid T in the liquid reservoir 37 can be reduced.

[0036] (3) In some embodiments, in the configuration of (2) above, The length of the discharge pipe 50 in the stacking direction is 1 / 2 or less of the length of the plate stack 40 in the stacking direction.

[0037] According to the configuration described in (3) above, the number of plates 44 that are directly covered by the discharged first heat transfer fluid T among the multiple plates 44 constituting the plate stack 40 is further reduced. Therefore, the first heat transfer gas Tv can escape more easily from the plate stack 40, and the amount of the first heat transfer fluid T in the liquid reservoir 37 can be reduced.

[0038] (4) In some embodiments, in any of the configurations (1) to (3) above, The discharge pipe 50 is positioned at a location offset to one side in the width direction from the center 40C of the plate stack 40.

[0039] According to the configuration described in (4) above, the first heat transfer gas Tv can easily escape from the plate stack 40 in more than half of the area in the width direction of each plate 44, and the amount of the first heat transfer liquid T in the liquid reservoir 37 can be reduced.

[0040] (5) In some embodiments, in the configuration described in (4) above, The discharge pipe 50 is provided in a region of the discharge pipe 50 that is on the opposite side in the width direction from the center 40C of the plate stack 40 with respect to the central axis 57 of the discharge pipe 50, and includes a discharge port 51 for discharging the first heat transfer fluid T.

[0041] According to the configuration described in (5) above, the discharge port 51 is not located on the other side in the width direction relative to the central axis 57, but is located only on one side in the width direction relative to the central axis 57. Therefore, on the other side in the width direction relative to the center 40C of the plate stack 40, the first heat transfer medium gas Tv can easily escape from the plate stack 40.

[0042] (6) In some embodiments, in the configuration of (4) or (5) above, The plate stack 40 includes a plurality of stacked plates 44, At least one of the plates 44 has a plurality of first protrusions 111 that start from an outer peripheral edge 49 located on one side in the width direction of the plate stack 40 relative to the center 40C, and extend vertically downward toward the one side in the width direction.

[0043] According to the configuration of (6) above, when the first heat transfer fluid T that has reached the outer peripheral edge 49 flows down along the outer peripheral edge 49, the first protrusion 111 can prevent the first heat transfer fluid T from entering the space formed between the plates 44. Therefore, the first heat transfer gas Tv can be prevented from being obstructed by the first heat transfer fluid T between the plates 44, and the first heat transfer gas Tv can be promoted to escape from the plate stack 40.

[0044] (7) In some embodiments, in the configuration of (6) above, The plurality of first protrusions 111 extend in a direction that is 45 degrees or less with respect to the horizontal plane.

[0045] According to the configuration of (7) above, even when the first heat transfer fluid T enters the space formed between the plates 44 from the outer peripheral edge 49 of the plate 44, the first protrusion 111 extends in a direction at an angle of 45 degrees or less with respect to the horizontal plane, so the first heat transfer fluid T flows down along the first protrusion 111 to one side in the width direction and downward in the vertical direction. This shortens the path that the first heat transfer fluid T travels between the plates 44. Therefore, the upward movement of the first heat transfer gas Tv is suppressed by the first heat transfer fluid T, and thus the first heat transfer gas Tv can escape from the plate stack 40.

[0046] (8) In some embodiments, in the configuration of (7) above, The plate stack 40 includes a plurality of stacked plates 44, At least one of the plates 44 has a plurality of second protrusions 112 that extend vertically downward toward the other side in the width direction, starting from the outer peripheral edge 49.

[0047] According to the configuration of (8) above, the extension direction of the multiple second protrusions 112 is opposite to the extension direction of the multiple first protrusions 111, so the number of intersections between the second protrusions 112 and the first protrusions 111 increases when viewed in the stacking direction. In other words, the space formed between the opposing first protrusions 111 and second protrusions 112, into which the discharged first heat transfer fluid T cannot easily enter, increases. Therefore, the discharged first heat transfer fluid T can be prevented from entering the space formed between the two plates 44, and thus the rise of the first heat transfer gas Tv is prevented from being hindered by the first heat transfer fluid T.

[0048] (9) In some embodiments, in any of the configurations (6) to (8) above, The outer peripheral edge 49 of the plate 44 has a shape in which the radius of curvature of the outer peripheral edge 49 on one side of the width direction relative to the uppermost end 46 is smaller than the radius of curvature of the uppermost end 46.

[0049] According to the configuration described in (9) above, the number of openings that can enter between the plates 44 below the discharge port 51 is reduced compared to the case where the plates 44 are circular in shape. Therefore, the entry of the first heat transfer fluid T into the space formed between the two plates 44 is suppressed.

[0050] (10) In some embodiments, in any of the configurations (1) to (9) above, The system includes a discharge duct 60 which includes a communication port 63 that communicates with the space inside the shell 35, and is configured to discharge the vaporized first heat transfer liquid T, which is the first heat transfer gas Tv, from the shell 35. The discharge pipe 50 includes a discharge port 51 for discharging the first heat transfer fluid T. The discharge port 51 is provided at a position offset from the communication port 63 in the stacking direction.

[0051] According to the configuration of (10) above, the first heat transfer medium gas Tv generated in the plate stack 40 flows into the discharge duct 60 via the communication port 63 and is discharged from the shell 35. Since the discharge port 51 is positioned offset from the communication port 63 in the stacking direction, mixing of the first heat transfer medium gas Tv rising toward the communication port 63 and the discharged first heat transfer medium liquid T is suppressed. Therefore, a reduction in the degree of superheating of the first heat transfer medium gas Tv discharged from the discharge duct 60 can be suppressed. For example, in an embodiment in which the first heat transfer medium gas Tv discharged from the discharge duct 60 is drawn into the compressor 16, it is preferable to increase the degree of superheating of the first heat transfer medium gas Tv from the viewpoint of avoiding liquid compression in the compressor 16. In this respect, by employing the shell-and-plate type heat exchanger 30 having the above configuration, a decrease in the degree of superheating of the first heat transfer medium gas Tv discharged from the shell 35 is suppressed, and the compressor 16 can operate properly.

[0052] (11) In some embodiments, in any of the configurations (1) to (10) above, The shell 35 is provided with a discharge duct 60 configured to discharge the vaporized first heat transfer liquid T, which is the first heat transfer gas Tv, from the shell 35. The discharge pipe 50 includes a discharge port 51 for discharging the first heat transfer fluid T. The discharge port 51 is provided at a position offset from the discharge duct 60 in the width direction.

[0053] According to the configuration described in (11) above, mixing of the first heat transfer gas Tv rising toward the discharge duct 60 and the discharged first heat transfer liquid T is suppressed, thereby suppressing a decrease in the degree of superheating of the first heat transfer gas Tv discharged from the heat exchanger 30.

[0054] (12) In some embodiments, in any of the configurations (1) to (11) above, The shell 35 is located below the plate stack 40 and includes an oil outlet 33 for discharging the refrigerant oil E that accumulates in the liquid reservoir 37. The discharge pipe 50 includes a discharge port 51 for discharging the first heat transfer fluid T. The discharge port 51 is provided at a position offset from the oil discharge port 33 in the stacking direction.

[0055] According to the configuration described in (12) above, the diffusion of the refrigerant oil E in the liquid reservoir 37 can be suppressed, thereby preventing the refrigerant oil E from obstructing heat transfer from the second heat transfer medium R to the first heat transfer medium T. Furthermore, by suppressing the diffusion of the refrigerant oil E, the discharge of the refrigerant oil E from the oil outlet 33 is promoted, thereby preventing a shortage of refrigerant oil E in the compressor 16.

[0056] (13) A heat exchange system 1 according to at least one embodiment of the present invention is A shell-and-plate heat exchanger 30 as described in any of (1) to (12) above, A compressor 16 for drawing in and compressing the first heat transfer gas Tv, which is the vaporized first heat transfer liquid T discharged from the shell 35, A condenser 11 is provided for the first heat transfer medium gas Tv discharged from the compressor 16 to exchange heat with a heat exchange medium and be converted into the first heat transfer medium liquid. A receiver 12 is connected to the condenser 11 and the shell-and-plate heat exchanger 30, and stores the first heat transfer fluid T discharged from the condenser 11, An expansion valve 22 is provided in the supply passage 13 connected to the receiver 12 and the shell-and-plate type heat exchanger 30, for reducing the pressure of the first heat transfer fluid. It is equipped with.

[0057] According to the configuration of (13) above, the amount of the first heat transfer fluid T in the shell 35 can be reduced for the same reasons as in (1) above. [Explanation of Symbols]

[0058] 1: Heat exchange system 11: Condenser 12: Receiver 13: Supply route 16: Compressor 22: Expansion valve 30: Shell-and-plate heat exchanger (heat exchanger) 33:Oil drain port 35: Shell 37: Liquid reservoir 40: Plate stack 40C: Center 44: Plate 47 :Top end 49: Peripheral edge 50:Discharge pipe 57: Central axis 51:Discharge port 63: Connecting port 111: First protrusion 112: Second convex part E: Refrigerating machine oil T: 1st heat transfer liquid Tv: First heat transfer gas

Claims

1. a shell having a liquid reservoir for the first heat transfer liquid; a plate stack disposed within the shell so as to be partially immersed in the first heat transfer liquid; a discharge pipe located within the shell above the plate stack for discharging the first heat transfer liquid into the shell; Equipped with The discharge pipe is disposed at a position offset from the center of the plate stack in both the stacking direction of the plate stack and the width direction perpendicular to the stacking direction in a plan view. Shell and plate heat exchanger.

2. 2. The shell-and-plate heat exchanger according to claim 1, wherein the discharge pipe is disposed at a position offset to one side in the stacking direction with respect to the center of the plate stack.

3. 3. The shell-and-plate heat exchanger according to claim 2, wherein the length of the discharge pipe in the stacking direction is equal to or less than half the length of the plate stack in the stacking direction.

4. 4. The plate-and-shell heat exchanger according to claim 1, wherein the discharge pipe is disposed at a position shifted to one side in the width direction from the center of the plate stack.

5. 5. The plate-and-shell heat exchanger according to claim 4, wherein the discharge pipe is provided in a region of the discharge pipe that is opposite in the width direction from the center of the plate stack with respect to a central axis of the discharge pipe, and includes a discharge port for discharging the first heat transfer medium liquid.

6. The plate stack includes a plurality of stacked plates, At least one of the plates has a plurality of first protrusions that extend downward in the vertical direction from an outer peripheral edge located on the one side in the width direction relative to the center of the plate stack as a starting point toward the one side in the width direction.

6. The shell-and-plate heat exchanger according to claim 4 or 5.

7. The shell-and-plate heat exchanger according to claim 6 , wherein the plurality of first protrusions extend in a direction that forms an angle of 45 degrees or less with respect to a horizontal plane.

8. The plate stack includes a plurality of stacked plates, 8. The plate-and-shell heat exchanger according to claim 7, wherein at least one of the plates has a plurality of second convex portions extending from the outer peripheral edge toward the other side in the width direction and downward in the vertical direction.

9. 9. The plate-and-shell heat exchanger according to claim 6, wherein the plate has a shape such that, when viewed in the stacking direction, the radius of curvature of the outer peripheral edge located on the one side in the width direction of the uppermost end is smaller than the radius of curvature of the uppermost end.

10. an exhaust duct including a communication port communicating with a space within the shell and configured to exhaust a first heat medium gas, which is the vaporized first heat medium liquid, from the shell; the discharge pipe includes a discharge port for discharging the first heat transfer medium liquid, 10. The shell-and-plate heat exchanger according to claim 1, wherein the discharge port is provided at a position shifted from the communication port in the stacking direction.

11. an exhaust duct disposed within the shell and configured to exhaust a first heat transfer gas, which is the vaporized first heat transfer liquid, from the shell; the discharge pipe includes a discharge port for discharging the first heat transfer medium liquid, 11. The shell-and-plate heat exchanger according to claim 1, wherein the discharge port is provided at a position offset from the exhaust duct in the width direction.

12. the shell is located below the plate stack and includes an oil discharge port for discharging refrigeration oil accumulated in the liquid reservoir, the discharge pipe includes a discharge port for discharging the first heat transfer medium liquid, 12. The shell-and-plate heat exchanger according to claim 1, wherein the discharge port is provided at a position shifted from the oil discharge port in the stacking direction.

13. A shell-and-plate heat exchanger according to any one of claims 1 to 12; a compressor for drawing in and compressing a first heat transfer gas, which is the vaporized first heat transfer liquid discharged from the shell; a condenser for converting the first heat medium gas discharged from the compressor into the first heat medium liquid by heat exchange with a heat exchange medium; a receiver connected to the condenser and the shell-and-plate heat exchanger, for storing the first heat transfer liquid discharged from the condenser; an expansion valve provided in a supply passage connected to the receiver and the shell-and-plate heat exchanger, for reducing the pressure of the first heat transfer liquid; A heat exchange system comprising:

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