Heat exchanger

Abstract

To provide a heat exchanger capable of suppressing dry-out and increasing cooling efficiency of a heat generation component.SOLUTION: A heat exchanger 1 includes a casing 10 and a refrigerant flow path 20 in which a refrigerant flows. The casing 10 is configured to be integral with or separate from a heat generation component 2, and has an overheating outer wall surface 11 in a side in which the heat generation component 2 is provided, and a non-overheating outer wall surface 12 in a side opposite to the heat generation component 2. The refrigerant flow path 20 is formed between the heat generation component 2 and the overheating outer wall surface 11, and the non-overheating outer wall surface 12 inside the casing 10, and has an overheating flow path section 21 and a non-overheating flow path section 22. The overheating flow path section 21 is a flow path in which distance D1 between the heat generation component 2 and the refrigerant flow path 20 is closer than distance D2 between the non-overheating flow path section 12 and the refrigerant flow path 20. The non-overheating flow path section 22 is a flow path section in which distance D3 between the heat generation component 2 and the refrigerant flow path 20 is farther than distance D4 between the non-overheating outer wall surface 12 and the refrigerant flow path 20. The refrigerant flow path 20 is a zigzag flow path in which the overheating flow path section 21 and the non-overheating flow path section 22 are disposed alternately.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger that exchanges heat between a heat-generating component and a refrigerant. [Background technology]

[0002] The heat exchanger described in Patent Document 1 exchanges heat between a semiconductor element, which is a heat-generating component provided on the outer wall of a housing, and a refrigerant flowing through a refrigerant flow path formed inside the housing. The refrigerant flow path of this heat exchanger has a flow path that meanders in the in-plane direction of the outer wall surface of the housing on which the heat-generating component is provided, and a bypass flow path formed by cutting out a part of the wall of the meandering flow path. This makes the flow of the refrigerant turbulent, thereby increasing the heat transfer rate from the heat-generating component to the refrigerant. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] International Publication No. 2020 / 078647 Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the heat exchanger described in Patent Document 1, the distance between the outer wall surface of the housing on which the heat-generating components are mounted and the inner wall surface of the refrigerant flow path facing the heat-generating components is constant at all points. Therefore, when dry-out occurs, in which the inner wall surface of the refrigerant flow path facing the heat-generating components is covered with bubbles formed by boiling the refrigerant, the heat transfer coefficient between the inner wall surface and the refrigerant decreases, and the cooling efficiency of the heat-generating components may decrease.

[0005] To prevent dryout, it is possible to increase the flow rate of the refrigerant supplied to the heat exchanger. However, increasing the flow rate of the refrigerant increases the pressure loss of the refrigerant flowing through the refrigerant flow path. In addition, if the cross-sectional area of ​​the refrigerant flow path is increased to suppress the increase in pressure loss that accompanies an increase in the flow rate of the refrigerant, the size of the heat exchanger also increases.

[0006] In view of the above, an object of the present disclosure is to provide a heat exchanger capable of suppressing dry-out and improving the cooling efficiency of heat-generating components. [Means for solving the problem]

[0007] According to one aspect of the present disclosure, a heat exchanger for exchanging heat between a heat generating component (2) and a refrigerant comprises: A housing (10) which is formed integrally with a heat generating component or is formed as a separate member, and has a heated outer wall surface (11) on the side where the heat generating component is provided, and a non-heated outer wall surface (12) on the side opposite the heat generating component; a refrigerant flow path (20) formed inside the housing between the heat generating component and the overheated outer wall surface and the non-overheated outer wall surface, through which a refrigerant flows; The refrigerant flow path has a superheated flow path section (21) in which the distance (D1) between the heat-generating component and the refrigerant flow path is closer than the distance (D2) between the non-superheated outer wall surface and the refrigerant flow path, and a non-superheated flow path section (22) in which the distance (D3) between the heat-generating component and the refrigerant flow path is farther than the distance (D4) between the non-superheated outer wall surface and the refrigerant flow path, forming a serpentine flow path in which the superheated flow path sections and the non-superheated flow path sections are arranged alternately.

[0008] According to this, by making the refrigerant flow path a serpentine flow path, a swirling flow is formed in the flow of the refrigerant. Therefore, the bubbles generated by the boiling of the refrigerant in the superheated flow path are separated from the inner wall surface of the superheated flow path by the swirling flow, and flow toward the non-superheated flow path along with the flow of the refrigerant, so that the bubbles can be moved away from the superheated outer wall surface. Furthermore, in the flow from the superheated flow path to the non-superheated flow path and in the flow of the non-superheated flow path, the swirling flow can mix the liquid phase refrigerant and the bubbles, and promote the condensation of the bubbles. Therefore, this heat exchanger can prevent the occurrence of dry-out, in which the inner wall surface of the superheated flow path is covered with bubbles, and by supplying a liquid-rich refrigerant to the inner wall surface of the superheated flow path, the heat transfer coefficient from the inner wall surface to the refrigerant can be improved, and the cooling efficiency of the heat-generating components can be improved. Therefore, this heat exchanger can be used under high temperature and high heat flux conditions. In addition, "superheat flow path sections and non-superheat flow path sections are arranged alternately" includes not only direct connection between the superheat flow path sections and non-superheat flow path sections, but also connection between the superheat flow path sections and non-superheat flow path sections via other flow paths.

[0009] The reference symbols in parentheses attached to each component indicate an example of the correspondence between the component and specific components described in the embodiments described below. [Brief description of the drawings]

[0010] [Figure 1] 1 is a schematic configuration diagram of a boil cooling system in which a heat exchanger according to a first embodiment is used. [Diagram 2] FIG. 1 is a cross-sectional view of a heat exchanger according to a first embodiment. [Diagram 3] FIG. 3 is an enlarged view of part III in FIG. 2. [Figure 4] FIG. 4 is an enlarged view of a portion IV in FIG. [Diagram 5] 5 is a cross-sectional view taken along line VV in FIG. 4. [Figure 6] 11 is a transparent plan view of a refrigerant flow path in a housing of a heat exchanger according to a second embodiment. FIG. [Figure 7] 7 is a see-through side view of a refrigerant flow path in the housing in a VII direction in FIG. 6. [Figure 8] FIG. 11 is a perspective view showing only a refrigerant flow path included in a heat exchanger according to a second embodiment. [Figure 9] FIG. 11 is a transparent plan view of a refrigerant flow path in a housing of a heat exchanger according to a third embodiment. [Figure 10] 10 is a perspective side view of a refrigerant flow path in the housing in the X direction of FIG. 9. FIG. [Figure 11] FIG. 11 is a transparent plan view of a refrigerant flow path in a housing of a heat exchanger according to a fourth embodiment. [Figure 12] 12 is a perspective side view of a refrigerant flow path in the housing in the XII direction of FIG. 11. [Figure 13] FIG. 11 is a perspective view showing only a refrigerant flow path included in a heat exchanger according to a fourth embodiment. [Figure 14] FIG. 13 is a transparent plan view of a refrigerant flow path in a housing of a heat exchanger according to a fifth embodiment. [Figure 15] 15 is a transparent side view of the refrigerant flow path in the housing in the XV direction of FIG. 14. [Figure 16] FIG. 13 is a transparent plan view of a refrigerant flow path in a housing of a heat exchanger according to a sixth embodiment. [Figure 17] 17 is a transparent side view of the refrigerant flow path in the housing in the XVII direction of FIG. 16. [Figure 18] FIG. 2 is a perspective view showing an example of a vortex shedder. [Figure 19] FIG. 11 is a perspective view showing another example of a vortex shedder. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0011] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals, and the description thereof will be omitted.

[0012] (First embodiment) The first embodiment will be described with reference to the drawings. As shown in Fig. 1, a heat exchanger 1 of the first embodiment is used in a boiling cooling system 3 that cools a heat-generating component 2. The heat-generating component 2 is, for example, a semiconductor element that generates heat when electricity is applied. The semiconductor element is, for example, a MOSFET or an IGBT.

[0013] The boiling cooling system 3 includes a heat exchanger 1, a radiator 4, a pump 5, and a refrigerant pipe 6. The refrigerant circulating through the boiling cooling system 3 may be, for example, water or an electrically insulating liquid such as LLC or Fluorinert. The pressure of the refrigerant is adjusted so that its boiling point is sufficiently lower than the average temperature of the heat-generating component 2 during operation.

[0014] The pump 5 sucks in a liquid-rich refrigerant and delivers the refrigerant toward the heat exchanger 1. Note that the liquid-rich refrigerant includes not only a single-phase liquid refrigerant but also a liquid-rich two-phase gas-liquid refrigerant (for example, a quality fraction of 0 to 0.2). The heat exchanger 1 exchanges heat between a refrigerant flowing through a refrigerant flow path 20 formed inside a housing 10 and a heat generating component 2. Heat generated by the heat generating component 2 is absorbed by the refrigerant. The refrigerant that flows out of the heat exchanger 1 flows into the radiator 4. The radiator 4 radiates heat of the refrigerant to the outside air or a predetermined heat medium.

[0015] Next, the heat exchanger 1 of the first embodiment will be described in detail.

[0016] As shown in FIG. 2 and FIG. 3, the heat exchanger 1 includes a refrigerant flow path 20 through which a refrigerant flows inside a housing 10. The housing 10 is formed of, for example, a metal or resin having excellent thermal conductivity. The housing 10 is configured integrally with a heat-generating component 2. The outer wall surface of the housing 10 on the side where the heat-generating component 2 is provided is called a superheated outer wall surface 11, and the outer wall surface opposite the heat-generating component 2 is called a non-superheated outer wall surface 12. The superheated outer wall surface 11 becomes hotter than the boiling point of the refrigerant due to heat generated by the heat-generating component 2. Although not shown in the drawings, the housing 10 and the heat-generating component 2 may be configured as separate members.

[0017] The refrigerant flow path 20 is formed between the heat generating component 2 and the overheated outer wall surface 11 and the non-overheated outer wall surface 12 inside the housing 10. The refrigerant flow path 20 has a superheated flow path section 21, a non-overheated flow path section 22, and a communication path section 23. The overheated flow path section 21 is a flow path in which the distance D1 between the heat generating component 2 and the refrigerant flow path 20 is closer than the distance D2 between the non-overheated outer wall surface 12 and the refrigerant flow path 20. The non-overheated flow path section 22 is a flow path in which the distance D3 between the heat generating component 2 and the refrigerant flow path 20 is farther than the distance D4 between the non-overheated outer wall surface 12 and the refrigerant flow path 20. The communication path section 23 is a flow path that communicates the overheated flow path section 21 and the non-overheated flow path section 22. This refrigerant path is a serpentine flow path in which the overheated flow path section 21 and the non-overheated flow path section 22 are alternately connected via the communication path section 23. In the following description, the direction in which the overheat flow path sections 21 and the non-overheat flow path sections 22 are alternately arranged is referred to as the "extending direction of the housing."

[0018] As indicated by arrows F1 to F9 in Fig. 3, the refrigerant flows in a serpentine manner through the refrigerant flow passage 20. At this time, when the flow direction of the refrigerant flowing through the refrigerant flow passage 20 changes at a bent portion where the superheated flow passage section 21 and the communicating passage section 23 are connected and at a bent portion where the non-superheated flow passage section 22 and the communicating passage section 23 are connected, a secondary flow is generated by centrifugal force, and this secondary flow becomes a swirling flow. Note that the swirling flow refers to a refrigerant flow that flows downstream while swirling around the flow passage center line of the refrigerant flow passage 20.

[0019] In Fig. 4, the swirling flow generated in the refrigerant flow path 20 is indicated by arc-shaped arrows S3, S4, and S5 surrounding linear arrows F3, F4, and F5. In Fig. 5, the swirling flow is indicated by arc-shaped arrows S3, S31, and S32 surrounding symbol F3 pointing toward the depth of the page.

[0020] As shown in FIG. 4 and FIG. 5, the refrigerant flowing through the superheated flow path section 21 of the refrigerant flow path 20 absorbs heat from the superheated outer wall surface 11, and boils when its own temperature becomes higher than the boiling point. In FIG. 4 and FIG. 5, some of the bubbles generated by the boiling of the refrigerant are marked with the symbol B. The bubbles generated by the boiling of the refrigerant leave the inner wall surface 24 of the superheated flow path section 21 by the swirling flow, and flow toward the non-superheated flow path section 22 together with the flow of the refrigerant. Furthermore, the bubbles are mixed with the liquid-phase refrigerant by the swirling flow in the flow from the superheated flow path section 21 to the non-superheated flow path section 22 and in the flow of the non-superheated flow path section 22, and condensation is promoted. In FIG. 4, some of the bubbles mixed with the liquid-phase refrigerant are marked with the symbol L. This prevents dryout from occurring on the inner wall surface 24 of the superheated flow path section 21, and makes it possible to supply a liquid-rich refrigerant to the inner wall surface 24 of the superheated flow path section 21.

[0021] In the heat exchanger 1 of the first embodiment described above, the refrigerant flow path 20 is a serpentine flow path in which the superheated flow path portions 21 and the non-superheated flow path portions 22 are arranged alternately. According to this, a swirling flow is formed in the flow of the refrigerant in the refrigerant flow path 20. Therefore, the swirling flow causes the bubbles generated in the superheat flow path 21 to separate from the inner wall surface 24 of the superheat flow path 21 and flow toward the non-superheat flow path 22, so that the bubbles can be moved away from the superheated outer wall surface 11. Furthermore, in the flow from the superheat flow path 21 to the non-superheat flow path 22 and in the non-superheat flow path 22, the swirling flow can mix the liquid phase refrigerant and the bubbles, and promote the condensation of the bubbles. Therefore, this heat exchanger 1 can prevent the occurrence of dry-out on the inner wall surface 24 of the superheat flow path 21, and improve the heat transfer coefficient between the inner wall surface 24 of the superheat flow path 21 and the refrigerant by supplying a liquid-rich refrigerant to the inner wall surface 24 of the superheat flow path 21, thereby improving the cooling efficiency of the heat-generating component 2. Therefore, this heat exchanger 1 can be used under high temperature and high heat flux conditions.

[0022] In the first embodiment, the refrigerant flow path 20 has the superheated flow path sections 21 and the non-superheated flow path sections 22 arranged alternately with the communication path sections 23 interposed therebetween. This increases the number of points where the refrigerant flow direction changes in the refrigerant flow path 20, making it possible to strengthen the swirling flow. Therefore, the strong swirling flow can cause the air bubbles formed in the superheat flow path section 21 to detach from the inner wall surface 24 of the superheat flow path section 21. In addition, the strong swirling flow can mix the air bubbles detached from the inner wall surface 24 of the superheat flow path section 21 with the liquid-phase refrigerant, further promoting condensation of the air bubbles.

[0023] Second embodiment The second embodiment will be described. The second embodiment is different from the first embodiment in the configuration of the refrigerant flow path 20, and is otherwise similar to the first embodiment, so only the parts that differ from the first embodiment will be described. Note that in the figures referred to in the following description of each embodiment, hatching of the cross section of the housing 10 is omitted.

[0024] As shown in Figs. 6 to 8, the refrigerant flow path 20 of the heat exchanger 1 of the second embodiment is a spiral flow path. Here, the direction perpendicular to the housing extension direction among the in-plane directions of the superheated outer wall surface 11 is referred to as the "casing width direction". The superheat flow path section 21 is disposed obliquely with respect to the housing extension direction so that the upstream side is shifted to one side of the housing width direction and the downstream side is shifted to the other side of the housing width direction. The non-superheat flow path section 22 is disposed obliquely with respect to the housing extension direction so that the upstream side is shifted to the other side of the housing width direction and the downstream side is shifted to one side of the housing width direction. In this way, the refrigerant flow path 20 is a spiral flow path in which the flow path center line of the superheat flow path section 21 and the flow path center line of the non-superheat flow path section 22 are disposed obliquely with respect to the housing extension direction. Moreover, when viewed from the upstream side of the refrigerant flow in the housing extension direction, the refrigerant flow path 20 is formed in a counterclockwise spiral shape from the upstream side to the downstream side.

[0025] 6 and 7, the refrigerant flowing through the spiral channel repeatedly changes its flow direction in the same direction when viewed from the extension direction of the housing. Therefore, the spiral channel can strengthen the swirling flow.

[0026] In the heat exchanger 1 of the second embodiment described above, the refrigerant flow path 20 is a spiral flow path in which the flow path center line of the superheated flow path section 21 and the flow path center line of the non-superheated flow path section 22 are arranged obliquely with respect to the extension direction of the casing.

[0027] According to this, by forming the refrigerant flow path 20 into a spiral flow path, it is possible to strengthen the swirling flow. Therefore, the bubbles formed in the superheat flow path section 21 can be separated from the inner wall surface 24 of the superheat flow path section 21 by the strong swirling flow. In addition, the bubbles separated from the inner wall surface 24 of the superheat flow path section 21 are mixed with the liquid-phase refrigerant by the strong swirling flow in the flow from the superheat flow path section 21 to the non-superheat flow path section 22 and in the flow in the non-superheat flow path section 22, so that the condensation of the bubbles can be further promoted. Therefore, this heat exchanger 1 prevents the occurrence of dryout on the inner wall surface 24 of the superheat flow path section 21, and improves the heat transfer coefficient by supplying a liquid-rich refrigerant to the inner wall surface 24 of the superheat flow path section 21, thereby improving the cooling efficiency of the heat-generating component 2.

[0028] Third embodiment The third embodiment will be described. The third embodiment is different from the second embodiment in that a bypass flow path is added to the refrigerant flow path 20. Since the third embodiment is otherwise similar to the second embodiment, only the differences from the second embodiment will be described.

[0029] As shown in FIG. 9 and FIG. 10, the refrigerant flow path 20 of the heat exchanger 1 of the third embodiment is also a spiral flow path. Furthermore, in the third embodiment, the refrigerant flow path 20 has a bypass flow path 25. The bypass flow path 25 is a flow path that connects an arbitrary part of the refrigerant flow path 20 to another arbitrary part so as to provide a shortcut. Specifically, the bypass flow path 25 connects adjacent superheat flow path sections 21 to each other. Furthermore, the bypass flow path 25 is provided at a position in the direction in which the overheated outer wall surface 11 and the non-overheated outer wall surface 12 face each other with respect to the heat generating component 2. That is, the bypass flow path 25 is provided directly below the heat generating component 2. In the following description, the "direction in which the overheated outer wall surface 11 and the non-overheated outer wall surface 12 face each other" is referred to as the "thickness direction of the housing 10". Note that the number of bypass flow paths 25 connecting adjacent superheat flow path sections 21 is not limited to two as shown in FIG. 9, and may be one or three or more.

[0030] In the third embodiment, as shown by arrows F20 to F28 in Fig. 9 and Fig. 10, the refrigerant flowing through the spiral channel repeatedly changes its flow direction in the same direction when viewed from the housing extension direction. Therefore, the spiral channel can strengthen the swirling flow. Furthermore, the flow flowing out from the bypass channel 25 to the superheat channel section 21 can significantly disturb the swirling flow in the superheat channel section 21.

[0031] In the heat exchanger 1 of the third embodiment described above, the refrigerant flow path 20 has the bypass flow path 25. This makes it possible to significantly disturb the flow of refrigerant in the main flow path by collision between the refrigerant flowing in the main flow path of the refrigerant flow path 20 excluding the bypass flow path 25 (i.e., the superheated flow path section 21, the non-superheated flow path section 22, and the communicating path section 23) and the refrigerant flowing out from the downstream side of the bypass flow path 25 into the main flow path. Therefore, the bubbles formed in the superheated flow path section 21 can be detached from the inner wall surface 24 of the superheated flow path section 21 by the more turbulent refrigerant flow. In addition, the bubbles detached from the inner wall surface 24 of the superheated flow path section 21 are mixed with the liquid phase refrigerant by the more turbulent refrigerant flow, further promoting condensation of the bubbles. Furthermore, the bypass flow path 25 can suppress an increase in pressure loss of the refrigerant flowing through the refrigerant flow path 20, thereby improving the flow rate of the refrigerant flowing through the refrigerant flow path 20. Therefore, this heat exchanger 1 can improve the heat transfer coefficient from the heat-generating component 2 to the refrigerant, and improve the cooling efficiency of the heat-generating component 2.

[0032] In the third embodiment, the bypass flow path 25 connects adjacent superheat flow path sections 21 to each other. This increases the flow rate of the refrigerant flowing through the bypass flow path 25 and the superheat flow path section 21. This makes it possible to more effectively prevent dryout from occurring in the bypass flow path 25 and the superheat flow path section 21. Therefore, the heat exchanger 1 can further improve the cooling efficiency of the heat-generating component 2.

[0033] Furthermore, in the third embodiment, the bypass flow path 25 is provided at a position on the heat-generating component 2 in the thickness direction of the housing 10. According to this, by providing the bypass flow path 25 in the coolant flow path 20 at a position directly below the heat generating component 2, the portion of the overheated outer wall surface 11 that becomes hot can be effectively cooled.

[0034] (Fourth embodiment) The fourth embodiment will be described. The fourth embodiment differs from the third embodiment in that the refrigerant flow path 20 is configured with a plurality of spiral flow paths, and is otherwise similar to the third embodiment, so only the differences from the third embodiment will be described.

[0035] 11 to 13, the refrigerant flow path 20 of the heat exchanger 1 of the fourth embodiment has a plurality of spiral flow paths. Specifically, the refrigerant flow path 20 has two spiral flow paths. One of the two spiral flow paths is called a first spiral flow path 210, and the other is called a second spiral flow path 220.

[0036] The first spiral flow path 210 has a first overheat flow path section 211, a first non-superheat flow path section 212, and a first communication path section 213. The second spiral flow path 220 has a second overheat flow path section 221, a second non-superheat flow path section 222, and a second communication path section 223. The configurations of the first overheat flow path section 211 and the second overheat flow path section 221 are the same as the configuration of the overheat flow path section 21 described in the second embodiment. The configurations of the first non-superheat flow path section 212 and the second non-superheat flow path section 222 are the same as the configuration of the non-superheat flow path section 22 described in the second embodiment. The configurations of the first communication path section 213 and the second communication path section 223 are the same as the configuration of the communication path section 23 described in the first and second embodiments.

[0037] The first spiral channel 210 and the second spiral channel 220 are provided such that the first overheat channel sections 211 and the second overheat channel sections 221 are alternately arranged in the extension direction of the casing, and the first non-overheat channel sections 212 and the second non-overheat channel sections 222 are alternately arranged. That is, the second spiral channel 220 is provided in the space left by forming the first spiral channel 210 in the casing 10.

[0038] When the refrigerant flow path 20 is configured with two spiral flow paths as in the fourth embodiment, the number of the multiple superheat flow path portions 211, 221 in one of the two spiral flow paths can be reduced when the pitch and length of the superheat flow path portions 21, 211, 221 are the same, compared to when the refrigerant flow path 20 is configured with one spiral flow path. For example, in FIG. 13, four superheat flow path portions 211, 221 are shown, but the first spiral flow path 210 has two first superheat flow path portions 211. The second spiral flow path 220 also has two second superheat flow path portions 221. Therefore, when the refrigerant flow path 20 is configured with multiple spiral flow paths, the temperature of the refrigerant flowing through the downstream superheat flow path portion of the multiple superheat flow path portions 21 can be reduced compared to when the refrigerant flow path 20 is configured with one spiral flow path. Therefore, in the heat exchanger 1 of the fourth embodiment, by configuring the refrigerant flow path 20 with multiple spiral flow paths 210, 220, the heat transfer coefficient between the heat-generating component 2 and the refrigerant can be improved from the upstream side to the downstream side, and the cooling efficiency of the heat-generating component 2 can be improved.

[0039] In the fourth embodiment, the bypass passage 25 also connects adjacent superheat flow path sections 21. That is, the bypass passage connects the first superheat flow path section 211 and the second superheat flow path section 221 which are adjacent to each other.

[0040] In the fourth embodiment, as shown by arrows F30 to F36 in Fig. 11 and Fig. 12, the refrigerant flowing through the first spiral passage 210 and the second spiral passage 220 repeatedly changes its flow direction in the same direction when viewed from the housing extension direction. Therefore, the first spiral passage 210 and the second spiral passage 220 can strengthen the swirling flow. Furthermore, in the fourth embodiment, the bypass passage 25 can also significantly disturb the swirling flow.

[0041] In the heat exchanger 1 of the fourth embodiment described above, the refrigerant flow path 20 has a plurality of spiral flow paths. The first superheat flow path sections 211 and the second superheat flow path sections 221 are alternately arranged in the housing extension direction, and the first non-superheat flow path sections 212 and the second non-superheat flow path sections 222 are also alternately arranged. According to this, by forming the refrigerant flow path 20 with multiple spiral flow paths, when the pitch and length of the superheat flow path portions are the same, the number of multiple superheat flow path portions in one of the multiple spiral flow paths can be reduced compared to when the refrigerant flow path 20 is formed with a single spiral flow path. Therefore, the temperature of the refrigerant flowing through the downstream superheat flow path portion among the multiple superheat flow path portions each of the multiple spiral flow paths can be reduced. Therefore, by forming the refrigerant flow path 20 with multiple spiral flow paths 210, 220, this heat exchanger 1 can improve the heat transfer coefficient between the heat-generating component 2 and the refrigerant from the upstream side to the downstream side, and improve the cooling efficiency of the heat-generating component 2.

[0042] Fifth embodiment The fifth embodiment will be described. The fifth embodiment is similar to the second embodiment except that the flow path cross-sectional area of ​​the refrigerant flow path 20 is changed, and therefore only the differences from the second embodiment will be described.

[0043] As shown in Figures 14 and 15, the refrigerant flow path 20 of the heat exchanger 1 of the fifth embodiment is also a spiral flow path having a superheated flow path section 21, a non-superheated flow path section 22, and a communication path section 23. As shown by arrows F40 to F48 in Figures 14 and 15, the refrigerant flowing through the spiral flow path repeatedly changes its flow direction in the same direction when viewed from the extension direction of the housing. Therefore, the spiral flow path can strengthen the swirling flow.

[0044] 15, in the fifth embodiment, the flow path cross-sectional area α of the superheated flow path section 21 is smaller than the flow path cross-sectional area β of the non-superheated flow path section 22. This makes the flow velocity of the refrigerant flowing through the superheated flow path section 21 faster than the flow velocity of the refrigerant flowing through the non-superheated flow path section 22. This improves the heat transfer coefficient from the superheated outer wall surface 11 to the refrigerant flowing through the superheated flow path section 21. On the other hand, by forming the flow path cross-sectional area β of the non-superheated flow path section 22 larger than the flow path cross-sectional area α of the superheated flow path section 21, the flow velocity of the refrigerant flowing through the non-superheated flow path section 22 becomes slower than the flow velocity of the refrigerant flowing through the superheated flow path section 21. This increases the time during which the swirling flow mixes the air bubbles and the liquid-phase refrigerant in the non-superheated flow path section 22 to condense the air bubbles. This promotes condensation of the air bubbles in the non-superheated flow path section 22, and allows a liquid-rich refrigerant to be supplied to the superheated flow path section 21.

[0045] Sixth embodiment The sixth embodiment will be described. The sixth embodiment is different from the second embodiment in that a vortex generator is provided in the coolant flow path 20, and is otherwise similar to the second embodiment, so only the differences from the second embodiment will be described.

[0046] As shown in Fig. 16 and Fig. 17, the refrigerant flow path 20 of the heat exchanger 1 of the sixth embodiment is also a spiral flow path having a superheated flow path section 21, a non-superheated flow path section 22, and a communication path section 23. As shown by arrows F50 to F58 in Fig. 16 and Fig. 17, the refrigerant flowing through the spiral flow path repeatedly changes its flow direction in the same direction when viewed from the extension direction of the housing. Therefore, the spiral flow path can strengthen the swirling flow.

[0047] In the sixth embodiment, a vortex generator 26 is provided in the refrigerant flow passage 20. The vortex generator 26 is a member that generates vortices in the refrigerant flow. Examples of the vortex generator 26 include a wing-shaped fin shown in FIG. 18 and a triangular fin shown in FIG. 19. The surfaces of the triangular fin are provided at an angle to the flow passage center line. The arrows F60 to F63 in FIG. 18 and FIG. 19 indicate the flow direction of the refrigerant. The vortex generator 26 is disposed to suppress an increase in pressure loss of the refrigerant flowing through the refrigerant flow passage 20 and to generate vortices in the refrigerant flow downstream of the vortex generator 26.

[0048] The heat exchanger 1 of the sixth embodiment described above includes the vortex generator 26 inside the refrigerant flow path 20. This makes it possible to control the position at which the vortex is generated by the vortex generator 26 in the coolant flow path 20, and to generate the vortex at the intended position. Therefore, the heat transfer coefficient at a location with high heat generation density in the coolant flow path 20 can be increased, and the location can be cooled effectively.

[0049] (Other embodiments) (1) In each of the above embodiments, the refrigerant flow path 20 is configured such that the superheated flow path section 21 and the non-superheated flow path section 22 are connected via the communicating path section 23. However, the present invention is not limited to this. For example, the refrigerant flow path 20 may be configured such that the communicating path section 23 is eliminated and the superheated flow path section 21 and the non-superheated flow path section 22 are directly connected alternately.

[0050] (2) In the above second embodiment, the refrigerant flow path is formed in a counterclockwise spiral shape from the upstream side to the downstream side when viewed from the upstream side of the refrigerant flow in the housing extension direction, but this is not limited to the above. For example, the refrigerant flow path may be formed in a clockwise spiral shape from the upstream side to the downstream side when viewed from the upstream side of the refrigerant flow in the housing extension direction.

[0051] (3) In the fourth embodiment, the refrigerant flow path 20 has been described as having two spiral flow paths, but this is not limited thereto. For example, the refrigerant flow path 20 may have three or more spiral flow paths. That is, the refrigerant flow path 20 may have, for example, a third spiral flow path and a fourth spiral flow path in addition to the first and second spiral flow paths 210 and 220.

[0052] (4) In the above embodiments, the bypass flow path 25 has been described as connecting adjacent superheat flow path sections 21 to each other, but this is not limited thereto. The bypass flow path 25 may connect any part of the refrigerant flow path 20 to another any part. For example, the bypass flow path 25 may connect adjacent non-superheat flow path sections 22 to each other, may connect a superheat flow path section 21 to a non-superheat flow path section 22, may connect a superheat flow path section 21 to a communicating path section 23, may connect a non-superheat flow path section 22 to a communicating path section 23, or may connect communicating path sections 23 to each other.

[0053] The present disclosure is not limited to the above-mentioned embodiments, and can be appropriately modified within the scope of the claims. In addition, the above-mentioned embodiments and parts thereof are not unrelated to each other, and can be appropriately combined except when the combination is clearly impossible. In addition, in each of the above-mentioned embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential, except when it is specifically stated that they are essential or when it is clearly considered to be essential in principle. In addition, in each of the above-mentioned embodiments, when the numbers, values, amounts, ranges, etc. of the components of the embodiment are mentioned, they are not limited to the specific numbers, except when it is specifically stated that they are essential or when it is clearly limited to a specific number in principle. In addition, in each of the above-mentioned embodiments, when the shape, positional relationship, etc. of the components are mentioned, they are not limited to the shape, positional relationship, etc., except when it is specifically stated that they are essential or when it is clearly limited to a specific shape, positional relationship, etc. in principle.

[0054] (In view of the present disclosure) The present disclosure described above can be understood from the following viewpoints, for example. [First viewpoint] A heat exchanger for exchanging heat between a heat generating component (2) and a refrigerant, a housing (10) which is formed integrally with the heat generating component or is formed as a separate member, and which has a heated outer wall surface (11) on the side where the heat generating component is provided, and a non-heated outer wall surface (12) on the side opposite the heat generating component; a refrigerant flow path (20) formed inside the housing between the heat generating component and the overheated outer wall surface and the non-overheated outer wall surface, through which a refrigerant flows; The refrigerant flow path has a superheated flow path section (21) in which the distance (D1) between the heat-generating component and the refrigerant flow path is closer than the distance (D2) between the non-superheated outer wall surface and the refrigerant flow path, and a non-superheated flow path section (22) in which the distance (D3) between the heat-generating component and the refrigerant flow path is farther than the distance (D4) between the non-superheated outer wall surface and the refrigerant flow path, and the superheated flow path section and the non-superheated flow path section are arranged alternately to form a serpentine flow path. [Second viewpoint] The heat exchanger according to a first aspect, wherein the refrigerant flow path has a communication passage portion (23) that communicates the heat flow path portion and the non-superheat flow path portion, and the superheat flow path portion and the non-superheat flow path portion are alternately arranged via the communication passage portion. [Third Perspective] The heat exchanger according to the first or second aspect, wherein the refrigerant flow path is a spiral flow path in which a flow path center line of the superheat flow path section and a flow path center line of the non-superheat flow path section are obliquely disposed with respect to a direction in which the superheat flow path sections and the non-superheat flow path sections are alternately arranged. [Fourth viewpoint] The refrigerant flow path has a plurality of the spiral flow paths, A first spiral flow path (210) of the plurality of spiral flow paths includes a first superheat flow path portion (211) and a first non-superheat flow path portion (212), a second spiral flow path (220) of the plurality of spiral flow paths includes a second superheat flow path portion (221) and a second non-superheat flow path portion (222); The heat exchanger according to a third aspect, wherein the first spiral flow path and the second spiral flow path are arranged such that the first superheat flow path sections and the second superheat flow path sections are alternately arranged, and the first non-superheat flow path sections and the second non-superheat flow path sections are alternately arranged. [Fifth viewpoint] The heat exchanger according to any one of the first to fourth aspects, wherein the refrigerant flow path has a bypass flow path (25) that connects an arbitrary portion of the refrigerant flow path to another arbitrary portion so as to provide a shortcut. [Sixth viewpoint] The heat exchanger according to a fifth aspect, wherein the bypass flow path connects adjacent superheat flow path portions to each other. [Seventh viewpoint] The heat exchanger according to a fifth or sixth aspect, wherein the bypass passage is provided at a position relative to the heat-generating component in a direction in which the overheated outer wall surface and the non-overheated outer wall surface face each other. [Eighth viewpoint] 13. The heat exchanger according to claim 12, wherein a cross-sectional area (α) of the superheat channel section is smaller than a cross-sectional area (β) of the non-superheat channel section. [Ninth viewpoint] The heat exchanger according to any one of the first to eighth aspects, further comprising a vortex generator (26) provided inside the refrigerant flow path to generate vortices in the flow of the refrigerant. [Explanation of symbols]

[0055] 1 heat exchanger 2 Heat generating parts 10. Chassis 11. Overheated exterior wall 12 Non-heated exterior wall 20 Coolant flow path 21 Superheat flow path section 22 Non-superheated flow path section

Claims

1. A heat exchanger for exchanging heat between a heat-generating component (2) and a refrigerant, A housing (10) that is formed integrally with the heat generating component or is formed as a separate member, and has a heated outer wall surface (11) on the side where the heat generating component is provided, and a non-heated outer wall surface (12) on the opposite side to the heat generating component; a refrigerant flow path (20) formed inside the housing between the heat generating component and the overheated outer wall surface and the non-overheated outer wall surface, through which a refrigerant flows; The refrigerant flow path has a superheated flow path section (21) in which the distance (D1) between the heat-generating component and the refrigerant flow path is closer than the distance (D2) between the non-superheated outer wall surface and the refrigerant flow path, and a non-superheated flow path section (22) in which the distance (D3) between the heat-generating component and the refrigerant flow path is farther than the distance (D4) between the non-superheated outer wall surface and the refrigerant flow path, and the superheated flow path section and the non-superheated flow path section are arranged alternately to form a serpentine flow path.

2. 2. The heat exchanger according to claim 1, wherein the refrigerant flow path has a communication passage portion (23) that connects the heat flow path portion and the non-superheat flow path portion, and the superheat flow path portion and the non-superheat flow path portion are alternately arranged via the communication passage portion.

3. 3. The heat exchanger according to claim 1, wherein the refrigerant flow path is a spiral flow path in which a flow path center line of the superheat flow path section and a flow path center line of the non-superheat flow path section are obliquely arranged with respect to a direction in which the superheat flow path section and the non-superheat flow path section are alternately arranged.

4. The refrigerant flow path has a plurality of the spiral flow paths, A first spiral flow path (210) of the plurality of spiral flow paths has a first superheated flow path portion (211) and a first non-superheated flow path portion (212), A second spiral flow path (220) among the plurality of spiral flow paths has a second superheated flow path portion (221) and a second non-superheated flow path portion (222), 4. The heat exchanger according to claim 3, wherein the first spiral flow path and the second spiral flow path are arranged such that the first superheat flow path sections and the second superheat flow path sections are alternately arranged, and the first non-superheat flow path sections and the second non-superheat flow path sections are alternately arranged.

5. 3. The heat exchanger according to claim 1, wherein the refrigerant flow path has a bypass flow path (25) that connects an arbitrary portion of the refrigerant flow path to another arbitrary portion so as to take a shortcut.

6. The heat exchanger according to claim 5 , wherein the bypass flow path connects adjacent superheat flow path portions to each other.

7. The heat exchanger according to claim 5 , wherein the bypass passage is provided at a position relative to the heat generating component such that the overheated outer wall surface and the non-overheated outer wall surface face each other.

8. 3. The heat exchanger according to claim 1, wherein a cross-sectional area (α) of the superheat flow path section is smaller than a cross-sectional area (β) of the non-superheat flow path section.

9. The heat exchanger according to claim 1 or 2, further comprising a vortex generator (26) provided inside the refrigerant flow path to generate vortices in the flow of the refrigerant.

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