Dual heat exchanger
By arranging the two plate heat exchangers directly adjacently through the separation plates, the problems of complex installation and large space occupancy in the prior art are solved, and a compact and efficient design and fluid flow stability are achieved.
Patent Information
- Application Number
- CN202380027681.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2023-06-05
- Filing Date
- 2023-11-03
- Publication Date
- 2025-02-14
AI Technical Summary
Existing dual heat exchangers require a lot of space and components when installed, resulting in complex layout and inefficient efficiency.
Two plate heat exchangers are arranged directly adjacently by the separation plates, avoiding the use of pipelines and connectors, ensuring fluid flow only through the parallel arrangement of the plates and the appropriate bypass design.
The compact design of dual heat exchangers is realized, reducing the need for installation space and components, and improving the installation efficiency of the system and the stability of fluid flow.
Smart Images
Figure CN119452219A_ABST
Abstract
Description
Technical Field
[0001] The invention relates to a double heat exchanger comprising two plate heat exchangers. Background Art
[0002] Air conditioning condensers in which the refrigerant condenses on a coolant, usually a water-glycol mixture, are known to be particularly suitable for air conditioning of electric vehicles. This is ensured by a first heat exchanger through which two different fluids thus flow. In addition, a second heat exchanger is provided for the refrigerant, which is usually present in both a high-pressure and a low-pressure state in the entire circuit and serves to transfer heat between the fluids in these two states.
[0003] Hitherto, the two heat exchangers have been connected by means of suitable lines and / or connecting pieces, which requires a relatively large amount of installation space and a large number of individual components. Summary of the invention
[0004] Technical issues
[0005] Against this background, it is an object of the present invention to create a double heat exchanger which requires a relatively small amount of installation space and / or a small number of individual components.
[0006] Technical solutions to the problem
[0007] This object is solved by the heat exchanger described in patent claim 1 .
[0008] According to this, the heat exchanger comprises a first plate heat exchanger in which heat is transferred between a first fluid and a second fluid, for example between a refrigerant on the one hand and a water-glycol mixture on the other hand, in particular in a ratio of about 50% for each fluid. A second plate heat exchanger is also provided in which heat is transferred between a first fluid in a first state and a first fluid in a second state. This is usually a refrigerant in a high-pressure state on the one hand and a refrigerant in a low-pressure state on the other hand. The double heat exchanger according to the invention is characterized in that the two plate heat exchangers are separated from each other only by means of a separating plate. However, any pipelines, connections, etc. between the two heat exchangers can advantageously be avoided. In addition, the amount of space required can be significantly reduced.
[0009] The present invention is essentially based on the following basic concept: allow two plate heat exchangers to directly adjoin each other, separated only by a separator plate, while ensuring the required fluid flow by means of appropriate measures, as will be described in more detail below. In other words, all plates of the two heat exchangers and the separator plate are arranged substantially parallel and preferably in unison with each other. This allows a particularly compact design to be achieved. The plates of the individual heat exchangers have an appropriate distance from each other so that an intermediate space in which the fluid can flow is defined. The separator plate is configured to be substantially the same distance from the correspondingly adjacent, so to speak, closest plates of the two heat exchangers. This results in a plate stack of multiple plates, each of which is substantially the same distance from each other, which, however, forms two fluid-separated heat exchangers. In addition, as will be described in more detail below, at least one additional separator plate can be provided to separate two or more regions of the heat exchanger from each other. The plates can, for example, be welded together to form a tight flow channel between the plates and possibly one or more bypasses extending through the multiple plates.
[0010] Preferred further developments are described in the further claims.
[0011] As already indicated, the heat exchanger according to the invention can advantageously be used to transfer heat between two fluids in different states if the states of these two fluids differ in terms of pressure.
[0012] This also applies to the preferred use of a refrigerant as the first fluid and, usually, a water-glycol mixture as the second fluid when a coolant is used.
[0013] In order to ensure the necessary fluid flow despite a compact design, it is advantageous if at least one plate heat exchanger comprises at least one bypass for conducting fluid to another plate heat exchanger.
[0014] Undesired heat transfer can thereby advantageously be minimized, since the at least one bypass comprises a pipe, for example made of plastic.
[0015] A bypass in the form of a tube may advantageously lead to the dryer and may be attached and fluidically connected to a holder to which the dryer is also attached and fluidically connected.
[0016] Furthermore, the tubes can be arranged at a distance from the opening edges of the plate, so that a further bypass is formed between the tubes and the opening edges, which bypass can be connected in a suitable manner.
[0017] Thus, a bypass can be formed in an advantageous manner by means of opening edges that are connected to one another, for example welded together.
[0018] If the second heat exchanger comprises two inlets for the fluid in the first state, in particular the low-pressure state, the heat exchanger according to the invention can advantageously be used for two separate refrigerant circuits. It is advantageous with respect to the surrounding components if the two inlets are located on opposite sides. It should be noted that the two refrigerant circuits can be used, for example, for air conditioning the front area of the vehicle interior on the one hand and the rear area of the vehicle interior on the other hand.
[0019] Advantages in terms of heat transfer are also to be expected if at least one heat exchanger can be traversed by a countercurrent flow.
[0020] With regard to the first heat exchanger, it may be further advantageous from an energy point of view if the first heat exchanger comprises a subcooling section for the refrigerant. This section can advantageously be separated by means of a separating plate, so that a compact design can be maintained despite the additional subcooling section.
[0021] Furthermore, it is presently preferred that the first heat exchanger additionally comprises a dryer.
[0022] Furthermore, it can be advantageous in terms of flow if at least one intermediate space between the plates is blocked, such that at least one heat exchanger comprises at least one blocking member, in particular a ring, between at least two plates.
[0023] A particularly efficient design of the heat exchanger is achieved if a plurality of plates, preferably all plates and also the separator plates of at least one, preferably both, heat exchangers are arranged substantially parallel and preferably aligned with one another.
[0024] At least one rib may advantageously be arranged in at least one plate in an effective manner to separate different areas of the heat exchanger and / or parallel to each other, for example in a straight or zigzag manner, to form fluid channels.
[0025] Due to the preferably provision of a plurality of protrusions, in particular circular protrusions, favorable flow conditions arise in the distribution region.
[0026] The heat exchanger according to the invention preferably comprises brackets for fastening to surrounding components.
[0027] The bracket preferably comprises at least one plate portion, in particular parallel to the plates of the heat exchanger, and preferably at least one bent portion for fastening to surrounding components, for example by means of a screw connection. BRIEF DESCRIPTION OF THE DRAWINGS
[0028] Embodiments of the present invention will be explained in more detail below with reference to the accompanying drawings. These drawings show:
[0029] Figure 1a , Figure 1b: A first cross-sectional view of a heat exchanger according to the invention, Figure 1b yes Figure 1a An enlarged view of the lower part of
[0030] Figure 2a , Figure 2b : A second cross-sectional view of a heat exchanger according to the present invention, Figure 2b yes Figure 2a An enlarged view of the lower part of
[0031] Figure 3 : Dryer;
[0032] Figures 4 to 6 : Figure 3 Different views of the supply line and holder of the dryer;
[0033] Figures 7 to 10 : Different views of the holder of the heat exchanger according to the present invention;
[0034] Fig.11 : A side view of the heat exchanger of Figures 1 and 2;
[0035] Fig.12 : Fig.11 A perspective view of the basic parts of a heat exchanger;
[0036] Fig.13 and Fig.14 : Side and perspective views of alternative embodiments of the basic parts;
[0037] Fig.15 : Fig.11 A cross-sectional top view of a heat exchanger,
[0038] Fig.16 and Fig.17 : its details;
[0039] Fig.18 : A top view of the plate with the blocking member; and
[0040] Fig.19 : Fig.18 Cross-sectional view of the design. DETAILED DESCRIPTION
[0041] With regard to the double heat exchanger 10 shown in FIG. 1 , it should first be explained that the heat exchanger comprises a dryer 20 situated on the left side of the figure, and a first heat exchanger 12 comprising a condensation section 22 and a subcooling section 24 is connected to the dryer 20 in the region of identifiable plates. The dryer 20 is substantially cylindrical, and may also be referred to as a “bottle”, and the longitudinal axis of the dryer 20 is substantially parallel to the plane of the plates of the heat exchanger and to the longer edges of the generally rectangular plates. The second heat exchanger 14 is situated on the far right side of the figure, and it is obvious that the two heat exchangers 12, 14 are separated from each other only by means of suitable separation plates, and that the two sections 22, 24 of the first heat exchanger 12 are also separated from each other only by means of another separation plate. As mentioned above, the plates may, for example, be welded together to form a tight flow channel between the plates, and possibly to form a bypass extending through a plurality of plates, such as Fig.16 and Fig.17 For a particularly efficient design of the heat exchanger, preferably all plates and also the separation plates are of the same size and are arranged substantially parallel and preferably in line with one another.
[0042] The fluid flow is basically as follows. According to the orientation in the figure, the gaseous refrigerant at high pressure enters the condensing section 22 of the first heat exchanger 12 via port 26 in the direction of arrow A and flows downward in all the intermediate spaces between the plates of this section according to the figure, and flows approximately diagonally when viewed from the side to the port shown at the bottom of Figure 2, which is located behind the drawing plane of Figure 1.
[0043] According to FIG. 1 , the coolant is supplied countercurrently from the lower right according to arrow B, the coolant first flows through a suitable bypass 28, through the second heat exchanger 14, and then disperses in all the intermediate spaces between the plates of the two sections 22, 24 of the first heat exchanger 12, thence again seen from the left side of FIG. 1 , towards the upper left to the outlet 30 for the coolant shown on the right side in FIG. 2 , see arrow K. The bypass 32 is again provided by the second heat exchanger 14. The above-mentioned ports 26 and outlets 30, as well as similar components cited below, can be welded to one or more plates, in particular to the outermost plates.
[0044] In the lower region of FIG. 2 , the separation plate 34 between the heat exchanger 12 and the heat exchanger 14 and the separation disc 36 between the sections 22 and 24 of the first heat exchanger 12 are clearly visible. Although the separation plates 34, 36 are only clearly visible in the lower region, it is obvious that the separation plates 34, 36 and all other plates extend to the upper ends of the heat exchangers 12, 14, so that the heat exchangers and / or sections are separated from each other. With regard to the separation plate 36, its effect is that in the lower region, the refrigerant entering from the upper left according to FIG. 1 flows to the left in the annular cavity around the inner tube 38 according to the arrow F into the dryer 20, and flows upwards in the dryer according to the arrow G, then flows downwards according to the arrow H, and from there flows through the tube 38 according to the arrow I into the subcooling section 24. Here, the tube 38 can be said to bypass the condensation section 22. In the adjacent subcooling section 24, the heat transfer with the coolant takes place here in the form of a parallel flow, which enters the section 24 at the bottom according to the arrow B according to FIG. 1, then flows, so to speak, in the intermediate space between the plates in the drawing plane, and leaves the section at the upper right according to the arrow K according to the cross-section shown behind it in FIG. 2.
[0045] The coolant thus flows from the front (FIG. 1, arrow B) to the rear (FIG. 2, arrow K) with respect to the drawing plane, and the refrigerant in the subcooling section 24 flows from the rear (FIG. 2, arrow I) to the front (FIG. 1), however, the upward flow in the figure does not extend to the upper end of the subcooling section 24, but only to the channel 40 leading to the second heat exchanger 14, in which heat transfer with the refrigerant in the low-pressure state takes place. As is evident in the lower area of FIG. 1, the refrigerant is supplied through two ports 42, 44 arranged on opposite sides according to arrows C, D in the shown example and is guided through the entire first heat exchanger 12 via a bypass 46 in the shown case. The refrigerant is discharged through a port 54 in the upper area according to arrow E, and an outlet 48 for high-pressure refrigerant is evident in FIG. 2 at the bottom right according to arrow J. Heat is transferred in particular usually from the low-pressure refrigerant to the high-pressure refrigerant via the already subcooled refrigerant. At least one, preferably all, of the inlet, outlet, channel and bypass preferably extend perpendicular to the plane of the plate. The plate stack of the second heat exchanger 14 is about as thick as the subcooling section 24, and the plate stack of the first heat exchanger 12 is about twice as thick as the subcooling section 24.
[0046] Figure 3 The dryer 20 is shown in detail and includes a holder 50 and a tube 38 extending therefrom. Figure 6 The cross-sectional view corresponds to the bottom cross-sectional view of FIG. 2 , and the required openings for fluid flow into and out of the dryer 20 are in Figure 4 and Figure 5The central opening is particularly connected to the hollow space surrounding the tube 38 and is used for inflow into the dryer 20. The left opening is used for outflow and is particularly as Figure 6 2 and extends around the tube 38 according to the arrow F, in the direction of the dryer 20, upwards in the dryer 20 according to the arrow G, from there downwards into the retainer 50 according to the arrow H, and further through the tube 38 according to the arrow I. Figure 4 The two upper and lower openings that are particularly evident in the figure are used to fasten the dryer 20 to the holder 50.
[0047] Figures 7 to 10 The bracket 52 is shown with a plate portion 64. Fig.11 and Fig.12 66 and serves for fastening to surrounding components. In particular, the recognizable bent portion 66 serves for fastening to surrounding components, while the plate portion 64 of the bracket 52 abuts against the plate of the heat exchanger. Fastening to the heat exchanger or surrounding components occurs via the visible opening 68 in the bent portion 66 by means of welding or screw connections.
[0048] Fig.11 1 shows a side view of a dual heat exchanger 10 comprising a dryer 20, a first heat exchanger 12, a second heat exchanger 14 and sections 22 and 24 of the first heat exchanger 12, and separation plates 36 and 34 arranged between the sections or heat exchangers, respectively.
[0049] Fig.12 Shown is a plate of a second plate heat exchanger 14. In this figure, the bypass 32 for the coolant, as already shown in FIG. 2 , is located at the upper right, the port 54 for discharging the refrigerant at low pressure is located at the upper left, the channel 40 for the refrigerant from the subcooling section 24 to the second heat exchanger 14 is located below it on the right, the bypass 28 for the coolant to the first heat exchanger 12 is located at the lower left, the supply line 44 for the low-pressure refrigerant is located above it, and the outlet 48 for the high-pressure refrigerant is located at the lower right. Ribs 56 located in the upper region ensure separation between low-pressure refrigerant and high-pressure refrigerant in the shown plate, wherein the ribs 56 extend parallel to the shorter edge of the plate and can be seen between the outlet 30 and the port 54 on the one hand and between the outlet 30 and the channel 40 on the other hand. In the plate below it, corresponding ribs are formed below the ports 44 and the heat transfer area 58 formed between the ports. In the case shown, the heat transfer area 58 is formed by a plurality of channels parallel to the longer edges of the plate, these channels being formed by ribs.
[0050] It should be noted that, according to the orientation on the left side in the figures, the passage 40 from the subcooling section to the second heat exchanger can also be located on the other side. In addition, the ribs of the heat transfer area 58 can be configured to be narrower than in the figures and do not extend into the area adjacent to the passage 40 or the port 44.
[0051] Distribution areas are located between the heat transfer area 58 and the ports and between the ports, and these distribution areas may be provided with more protrusions in the form of rounded protrusions (dimples) than the number shown, especially in the case of shorter ribs.
[0052] exist Fig.13 As shown in FIG. 1 , the distribution area can also include sawtooth ribs, and the individual ports, such as the channels 40 in the case shown, can also be Fig.13 1 and 2 or in the rear region at different positions. Fig.14 Shows Fig.13 1 and 2 .
[0053] Fig.15 A cross-sectional top view in the area of ports 42 and 44 for low pressure refrigerant is shown. Fig.16 and Fig.17 Obviously, all the plates in this region, in particular the plates at the edges of the openings, can be bent and welded together so that the intermediate spaces between the plates are sealed, thereby forming the bypass 46 as described.
[0054] In certain cases of use, it may also be advantageous to block the individual intermediate spaces between the plates in order to reduce the heat transfer. By blocking the individual intermediate spaces between the plates in this way, the pressure losses can be kept low in an advantageous manner. Fig.18 and Fig.19 In the case shown, a blocking member in the form of a ring 62 is provided for the high pressure region, for example. Thus, as described above, the heat transfer can be optimized without increasing the number of channels for the low-pressure refrigerant, which would lead to an undesirable increase in pressure losses. The blocking member can be connected to the plate by means of welding.
[0055] Industrial Applicability
[0056] The invention relates to a double heat exchanger comprising two plate heat exchangers.
Claims
1. A dual heat exchanger (10), comprising a first plate heat exchanger (12) and a second plate heat exchanger (14), wherein heat is transferred between a first fluid and a second fluid in the first plate heat exchanger (12), and heat is transferred between the first fluid in a first state and the first fluid in a second state in the second plate heat exchanger (14), characterized in that: The two heat exchangers are separated from one another only by means of a separating plate (34).
2. The dual heat exchanger (10) according to claim 1, characterized in that: The two states of the first fluid differ in pressure.
3. The dual heat exchanger (10) according to claim 1 or 2, characterized in that: The first fluid is a refrigerant and / or the second fluid is a coolant, the second fluid being in particular a water-glycol mixture.
4. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that At least one plate heat exchanger (12, 14) includes at least one bypass (28, 32, 38, 46) for directing fluid to another plate heat exchanger.
5. The dual heat exchanger (10) according to claim 4, characterized in that: At least one bypass (28, 32, 38, 46) comprises a tube (38), for example made of plastic.
6. The dual heat exchanger (10) according to claim 5, characterized in that: The tube (38) is attached and fluidly connected to a holder (50) to which the dryer (20) is also attached and fluidly connected.
7. The double heat exchanger (10) according to claim 5 or 6, characterized in that: The tubes (38) are arranged at a distance from a plurality of opening edges of the plates of the plate heat exchanger (12).
8. The double heat exchanger (10) according to any one of claims 4 to 7, characterized in that: The bypass (46) is formed by means of opening edges of the plates of the plate heat exchanger (12) which are connected to one another, for example welded together.
9. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that The second heat exchanger (40) comprises two inlets (42, 44) for the first fluid in a first state, in particular a low-pressure state, the two inlets (42, 44) being preferably arranged on opposite sides.
10. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that At least one heat exchanger (12, 14) is capable of being traversed by countercurrent flow.
11. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that The first heat exchanger (12) comprises a subcooling section (24) which is separated by means of a separation plate (36).
12. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that The first heat exchanger (12) includes a dryer (20).
13. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that At least one heat exchanger (12, 14) comprises between at least two plates at least one blocking member (62), in particular a ring, for blocking an intermediate space between the two plates.
14. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that A plurality of plates, preferably all plates, of at least one heat exchanger (12, 14) and the separation plate (34) are arranged substantially parallel and preferably in line with one another.
15. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that At least one plate comprises at least one rib (56) for separating different areas of the heat exchanger (12, 14) and / or parallel to each other, for example in a straight line or zigzag manner, to form fluid channels.
16. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that At least one plate comprises, in at least one distribution area, a plurality of protrusions, in particular circular protrusions.
17. Double heat exchanger (10) according to at least one of the preceding claims, characterized in that The dual heat exchanger (10) comprises at least one bracket (52) for fastening to surrounding components.
18. The dual heat exchanger (10) according to claim 17, characterized in that: The bracket comprises at least one plate portion (64) which is preferably parallel to the plate of the heat exchanger and at least one bent portion (66) which is preferably used for fastening to surrounding components.