evaporator
By setting first and second throttling plates in the evaporator inlet chamber and adjusting the opening size and arrangement, the problem of uneven refrigerant distribution during low-load operation was solved, achieving uniform temperature distribution and high superheat under both high and low loads, thus improving refrigeration efficiency.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- MAHLE INT GMBH
- Filing Date
- 2023-04-18
- Publication Date
- 2026-06-23
AI Technical Summary
In the prior art, the refrigerant circuit evaporator of motor vehicles has uneven refrigerant liquid phase distribution and overheating problems when operating at low load, resulting in uneven air outlet temperature, which is more pronounced in electric vehicles.
First and second throttling plates are installed in the inlet chamber of the evaporator. By adjusting the size and arrangement of the openings, the refrigerant is ensured to be evenly distributed into the tubes during low-load operation. The combined design of the first and second throttling plates prevents the formation of negative pressure and achieves a uniform temperature distribution.
It can achieve uniform temperature distribution in the evaporator under both high and low load operation, prevent negative pressure formation, and improve refrigeration efficiency and superheating.
Smart Images
Figure CN116907124B_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of evaporators, and more specifically to an evaporator for a refrigerant circuit in a motor vehicle. Background Technology
[0002] DE 10 2018 209 775 A1 discloses an evaporator for a refrigerant circuit in a motor vehicle, wherein the evaporator has a tube-fin assembly having a plurality of tubes and a plurality of fins, and the evaporator is designed to have a first manifold located on one side of the tube-fin assembly and a second manifold located on the other side of the tube-fin assembly, such that the first manifold has an input chamber and an output chamber, wherein the input chamber is provided with a refrigerant input interface and the output chamber is provided with a refrigerant output interface, wherein the first manifold optionally has an additional deflection chamber, and wherein the second manifold has a deflection chamber to deflect refrigerant from one set of tubes of the tube-fin assembly to another set of tubes.
[0003] In the evaporator according to this prior art, the first and second manifolds are generally horizontally arranged, with the first manifold located at the bottom of the evaporator and the second manifold located at the top, above the first manifold. Therefore, the inlet chamber with the refrigerant inlet and the outlet chamber with the refrigerant outlet are located below. While this arrangement offers structural space advantages in some configurations, the superheat is often too low and insufficient. If the evaporator is flipped so that the inlet chamber with the refrigerant inlet and the outlet chamber with the refrigerant outlet are located above, it results in very uneven liquid phase distribution of the refrigerant during low-load operation, leading to unacceptably large hot spots at the air outlet temperature on the tube fin assembly.
[0004] Furthermore, there is an increasing demand, particularly in electrically driven motor vehicles, for operation that can withstand significant overheating under low loads. Summary of the Invention
[0005] The purpose of this invention is to provide an evaporator that has a uniform temperature distribution throughout its operating range and can still achieve a high degree of superheating under low load operation.
[0006] This objective is achieved through the following technical solutions.
[0007] One embodiment of the present invention relates to an evaporator, particularly for a refrigerant circuit in a motor vehicle, comprising a tube-fin assembly, a first manifold located on one side of the tube-fin assembly, and a second manifold located on the other side of the tube-fin assembly. The tube-fin assembly has a plurality of tubes and a plurality of fins. The first manifold has an input chamber and an output chamber, wherein the input chamber is provided with a refrigerant input port and the output chamber is provided with a refrigerant output port. A first throttling plate and a second throttling plate are provided in the input chamber, the two throttling plates being spaced apart from each other. This achieves a sufficiently high refrigerant flow velocity and a sufficiently large refrigerant projection distance due to the presence of the first and second throttling plates, allowing the refrigerant to reach its end laterally in the input chamber even under low-load operation, thus uniformly distributing the refrigerant into the tubes fluidly connected to the input chamber. This also prevents the occurrence of negative pressure in the input chamber immediately after the first throttling plate, which would be disadvantageous as such negative pressure could reverse the flow velocity in the tubes of the tube-fin assembly. Therefore, a uniform temperature distribution can be achieved not only during high-load operation but also during low-load operation.
[0008] In one embodiment, it is also advantageous that the first throttling plate is formed by a first wall portion having at least one first opening, and / or the second throttling plate is formed by a second wall portion having at least one second opening. Therefore, the flow rate of the fluid, or refrigerant, can be appropriately adjusted by selecting the size and / or arrangement of the at least one first opening and the size and / or arrangement of the at least one second opening as needed.
[0009] Particularly advantageously, the at least one first opening has a first opening cross-sectional area and the at least one second opening has a second opening cross-sectional area, wherein the first opening cross-sectional area is smaller than the second opening cross-sectional area. This is also advantageously applicable to cases with multiple first openings, such as two, three, four, or more. The distribution of the first openings can also be advantageously chosen, for example, in the case of three first openings arranged in a triangular pattern.
[0010] In another embodiment, it is also suitable that the at least one first opening is or has an opening or multiple circular openings that are generally circular or other shapes, and / or the at least one second opening is or has at least one or more openings that are generally angular, such as, in particular, quadrilateral, rectangular, square or other shapes. Thus, for example, three first openings arranged in a triangular pattern and a second opening that can be designed as a quadrilateral may be provided.
[0011] It is also advantageous to have multiple first openings, which are the same size and / or different in terms of their cross-sectional area. Therefore, for example, three first openings can be arranged in a triangular pattern, wherein these three first openings can be the same size or different sizes, and two first openings can be the same size while one first opening can be larger or smaller than the other two. For example, a second opening can also be provided.
[0012] It is also particularly advantageous that one of the first openings and one of the second openings are aligned in a straight line. Therefore, a predetermined amount of refrigerant can flow from the first opening through the second opening.
[0013] Another advantage is that one of the first openings is at least partially not obscured by the projection of the second throttle plate onto the first throttle plate. Therefore, almost free flow can be achieved through the second throttle plate.
[0014] It is also advantageous that the two first openings are not aligned with the second opening. Therefore, the refrigerant flowing through them is preferably introduced into the pipe before the second expansion joint.
[0015] Advantageously, the two first openings are covered by the projection of the second throttling plate onto the first throttling plate. The refrigerant flowing through there is therefore preferably introduced into the pipe before the second throttling plate.
[0016] Advantageously, the first current collector protrudes laterally from the tube-fin assembly, and the first current collector can be divided into a protruding region and a core region, wherein the protruding region protrudes laterally from the tube-fin assembly, while the core region lies within the lateral length of the tube-fin assembly. Therefore, the protruding region can, for example, be used to house an interface, while the core region can be designed for turning within the tube-fin assembly area.
[0017] It is also suitable that the refrigerant inlet of the inlet chamber and / or the refrigerant outlet of the outlet chamber are located in a protruding area of the first manifold. This allows for a space-saving configuration.
[0018] In another embodiment, it is preferable that the first throttling plate is positioned in the input chamber at the transition between the protruding region and the core region. This allows for efficient distribution of fluid, such as refrigerant, into the tubes of the tube-finned assembly, thereby dispersing the fluid throughout all tubes connected to the input chamber. Consequently, a good fluid projection distance can be achieved for uniform distribution within the tubes.
[0019] Advantageously, the second throttling plate is located in the core region of the inlet chamber. This achieves a blocking throttling plate that balances the pressure rise caused by the first throttling plate and also blocks liquid media, such as refrigerant.
[0020] Particularly advantageous is that the input chamber has a lateral length X, wherein the ratio of the distance between the first and second throttle plates to the lateral length X is in the range of 0.15 to 0.36, particularly in the range of 0.21 to 0.33. This effectively achieves the relative effect between the second and first throttle plates.
[0021] It is also suitable that the input chamber and the tube fin assembly are designed and interconnected such that a portion of the tube fin assembly, i.e., N tube ends, extends into the input chamber, or the input chamber is fluidly connected to a portion of the tube fin assembly, i.e., N tube ends, wherein the ratio of the number of tube ends M to N between the first and second throttling plates is in the range of 0.15 to 0.36, particularly in the range of 0.21 to 0.33. This also effectively achieves the relative effect between the second and first throttling plates.
[0022] A particularly advantageous feature is that the first collector box is positioned above the second collector box. Attached Figure Description
[0023] The invention will now be described in detail with reference to the accompanying drawings and embodiments.
[0024] In the attached diagram:
[0025] Figure 1 A partial schematic diagram of a first embodiment of an evaporator according to the present invention is shown;
[0026] Figure 2 As shown Figure 1 Another partial schematic diagram of the evaporator shown;
[0027] Figure 3 A view of the first throttle plate with three first openings is shown;
[0028] Figure 4 A view of a second throttle plate with a second opening is shown; and
[0029] Figure 5 A view of an optional second throttle plate with an optional second opening is shown. Detailed Implementation
[0030] The present invention relates to an evaporator 1, particularly for a refrigerant circuit in a motor vehicle.
[0031] exist Figure 1 and 2 Partial views of evaporator 1 are schematically shown in the figures.
[0032] The evaporator has a tube-fin assembly 2, which has multiple tubes 3 and fins 4.
[0033] In addition, the evaporator also has a first manifold 5 located on one side of the tube fin assembly 2 and a second manifold 6 located on the other side of the tube fin assembly 2.
[0034] The first collector 5 can be located above the second collector 6, or alternatively below the second collector 6.
[0035] The first manifold 5 has an input chamber 7 and an output chamber 8. Furthermore, the input chamber 7 is equipped with a refrigerant input port 9. The output chamber 8 is equipped with a refrigerant output port 10. An input pipe is preferably connected to, for example, by brazing, the refrigerant input port 9, and an output pipe is preferably connected to, for example, by brazing, the refrigerant output port 10.
[0036] As in Figure 1 and 2 As shown, a first throttling plate 11 and a second throttling plate 12 are provided in the input chamber 7, and they are arranged separately from each other in the input chamber 7. Figure 3 and 4 These two throttle plates are also shown in Figure 5.
[0037] See here (see Figure 3 The first throttle plate 11 is formed by a first wall portion 13, in which at least one first opening 14, 15 is formed. In the illustrated embodiment, three first openings 14, 15 are provided. These three openings 14, 15 are arranged in a triangular pattern, wherein two smaller openings 15 are located at the bottom, and a larger opening 14 is located at the top and between the two smaller openings 15.
[0038] The second throttling plate 12 is formed by a second wall portion 16, in which at least one second opening 17 is formed. See Figure 4 Or 5.
[0039] Particularly suitable is that the at least one first opening 14, 15 has a first opening cross-sectional area and the at least one second opening 17 has a second opening cross-sectional area, wherein the first opening cross-sectional area is smaller than the second opening cross-sectional area. This also applies, exemplarily, to the sum of the first opening cross-sectional areas of the first openings 14, 15.
[0040] It can also be seen that the at least one first opening 14, 15 forms a generally circular opening or, alternatively, an opening of other shape, such as forming or having, as shown in the figure, a plurality of circular openings 14, 15.
[0041] The at least one second opening 17 forms or has at least one or more generally angular shapes, such as, in particular, quadrilateral, rectangular, square, or other shaped openings 17. In the illustrated embodiment, the second opening 17 is designed to be angular and has four corners, wherein the second opening 17 has three straight sides and one curved side. The curved side extends along the outer contour of the second wall portion 16, see [reference needed]. Figure 5 Here, the second opening 17 can also be designed to have four straight edges, such as... Figure 4 As shown in the image.
[0042] In principle, multiple first openings 14 and 15 can be provided, and these first openings can be the same size and / or different sizes in terms of their cross-sectional area. In the illustrated embodiment, the first opening 15 is smaller than the first opening 14.
[0043] from Figure 1 and Figure 2 It can also be seen that the first collector box 5 protrudes laterally from the tube fin assembly 2 with a protrusion U, and the first collector box 5 can be divided into a protruding region Ub and a core region Kb, wherein the protruding region Ub protrudes laterally from the tube fin assembly 2 and the core region Kb is located within the lateral length of the tube fin assembly 2.
[0044] The refrigerant input port 9 of the input chamber 7 and / or the refrigerant output port 10 of the output chamber 8 are located in the protruding area Ub of the first manifold 5.
[0045] The first throttling plate 11 is located in the input chamber 7 at the transition between the protruding region Ub and the core region Kb.
[0046] The second throttle plate 12 is disposed in the core region Kb within the input chamber 7.
[0047] In this configuration, the input chamber 7 has a lateral length X in Kb, wherein the ratio of the distance A between the first throttle plate 11 and the second throttle plate 12 to the lateral length X is in the range of 0.15 to 0.36, particularly in the range of 0.21 to 0.33. The length of the input chamber 7 in Ub and Kb is V.
[0048] Advantageously, the input chamber 7 and the tube fin assembly 2 can also be designed and interconnected such that a portion of the tube fin assembly 2, i.e., N tube ends, extends into the input chamber 7, or the input chamber 7 is fluidly connected to a portion of the tube fin assembly 2, i.e., N tube ends, wherein the ratio of the number M to N of tube ends between the first throttling plate 11 and the second throttling plate 12 is in the range of 0.15 to 0.36, particularly in the range of 0.21 to 0.33.
Claims
1. An evaporator (1) for a refrigerant circuit in a motor vehicle, the evaporator having a tube-fin assembly (2), a first manifold (5) located on one side of the tube-fin assembly (2) and a second manifold (6) located on the other side of the tube-fin assembly (2), the tube-fin assembly having a plurality of tubes (3) and a plurality of fins (4), the first manifold (5) having an input chamber (7) and an output chamber (8), wherein, The input chamber (7) is equipped with a refrigerant input interface (9) and the output chamber (8) is equipped with a refrigerant output interface (10). The characteristic is that a first throttling plate (11) and a second throttling plate (12) are provided in the input chamber (7), and the first throttling plate and the second throttling plate are located in the input chamber (7) separately from each other. The first collector box (5) protrudes laterally from the tube fin assembly (2) and the first collector box (5) can be divided into a protruding region and a core region, wherein the protruding region protrudes laterally from the tube fin assembly (2) and the core region is located within the lateral length of the tube fin assembly (2). The first throttle plate (11) is disposed in the input chamber (7) at the transition between the protruding area and the core area; The second throttle plate (12) is disposed in the core region of the input chamber (7); The input chamber (7) has a lateral length X, wherein the ratio of the distance A between the first throttle plate (11) and the second throttle plate (12) to the lateral length X is in the range of 0.15 to 0.
36.
2. The evaporator (1) as claimed in claim 1, characterized in that, The first throttle plate (11) is formed by a first wall portion (13) in which at least one first opening (14, 15) is formed, and / or the second throttle plate (12) is formed by a second wall portion (16) in which at least one second opening (17) is formed.
3. The evaporator (1) as described in claim 2, characterized in that, The at least one first opening (14, 15) has a first opening cross-sectional area and the at least one second opening (17) has a second opening cross-sectional area, wherein the first opening cross-sectional area is smaller than the second opening cross-sectional area.
4. The evaporator (1) as described in claim 2 or 3, characterized in that, The at least one first opening (14, 15) is or has a generally circular opening (14, 15) or a plurality of circular openings (14, 15), and / or the at least one second opening (17) is or has at least one or a plurality of generally angular openings (17).
5. The evaporator (1) as described in claim 4, characterized in that, A plurality of first openings (14, 15) are provided, and the first openings are the same size and / or different sizes in terms of their cross-sectional area.
6. The evaporator as described in claim 2, characterized in that, One of the first openings (14) and one of the second openings (17) are in a straight line.
7. The evaporator as claimed in claim 2, characterized in that, One of the first openings (14) is at least partially not covered by the projection of the second throttle plate (12) onto the first throttle plate (11).
8. The evaporator as claimed in claim 2, characterized in that, The two first openings (15) and the second opening (17) are not on the same straight line.
9. The evaporator as claimed in claim 2, characterized in that, Two of the first openings (15) are covered by the projection of the second throttle plate (12) onto the first throttle plate (11).
10. The evaporator (1) as claimed in claim 1, characterized in that, The refrigerant input port (9) of the input chamber (7) and / or the refrigerant output port (10) of the output chamber (8) are located in the protruding area of the first manifold (5).
11. The evaporator (1) as claimed in claim 1, characterized in that, The ratio of the distance A between the first throttle plate (11) and the second throttle plate (12) to the lateral length X is in the range of 0.21 to 0.
33.
12. The evaporator (1) as claimed in claim 1, characterized in that, The input chamber (7) and the tube fin assembly (2) are designed and interconnected such that a portion of the tube fin assembly (2), i.e., N tube ends, extends into the input chamber (7) or the input chamber (7) is fluidly connected to a portion of the tube fin assembly (2), i.e. N tube ends, wherein the ratio of the number M to N of tube ends between the first throttling plate (11) and the second throttling plate (12) is in the range of 0.15 to 0.
36.
13. The evaporator (1) as claimed in claim 12, characterized in that, The ratio of the number of pipe ends M to N between the first throttling plate (11) and the second throttling plate (12) is in the range of 0.21 to 0.
33.
14. The evaporator (1) as claimed in claim 1, characterized in that, The first collector box (5) is positioned above the second collector box (6).