Secondary jet flow type liquid distribution head, heat exchanger assembly and air conditioner

Abstract

The utility model provides a secondary jet type liquid distribution head, a heat exchanger assembly and an air conditioner. The secondary jet type liquid distribution head comprises an input pipe, a first mixing cavity plate, a partition plate and a secondary jet plate, wherein the first mixing cavity plate, the partition plate and the secondary jet plate are sequentially arranged in an inner cavity of a liquid distribution body. Refrigerant is jetted into the liquid separation body through the input pipe, and the high-speed refrigerant is reflected by the first mixing cavity in the first mixing cavity plate and then gradually develops towards a dispersed flow pattern in a first cavity defined by the first mixing cavity plate and the inner wall of the input end of the liquid separation body. The partition plate is located between the first mixing cavity plate and the secondary jet flow plate, a second cavity is defined by the partition plate and the first mixing cavity plate, and a third cavity is defined by the partition plate and the secondary jet flow plate. By accurately controlling the volume ratio of the three cavities, the refrigerant subjected to preliminary arrangement is developed into a stable dispersed flow pattern in a step-by-step mixing mode, and then high-speed jet flow is formed through secondary jet flow holes in the secondary jet flow plate so as to improve the distribution uniformity.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigerant distribution, and particularly relates to a secondary jet type liquid distributor, a heat exchanger assembly and an air conditioner. Background Art

[0002] Multi-channel small-diameter heat exchangers have the advantages of strong heat exchange capacity, less material consumption, small refrigerant charge and small pressure drop. In order to evenly distribute the throttled gas-liquid two-phase refrigerant into each flow path of the heat exchanger, a refrigerant liquid distributor needs to be introduced in front of the heat exchanger. There is a problem of uneven flow distribution in the actual use of the liquid distributor, which reduces the performance of the refrigeration equipment. The factors causing the uneven flow distribution of the liquid distributor mainly include the body structure of the liquid distributor, the installation angle and the inlet flow pattern. The existing improvement of the performance of the liquid distributor mainly focuses on the body structure of the liquid distributor, while the research on the inlet flow pattern is relatively less.

[0003] However, due to the limitation of the installation space, the two-phase refrigerant after throttling by the expansion valve needs to be bent by the inlet connecting pipe and then enter the liquid distributor. When the refrigerant passes through the bent section of the inlet connecting pipe, since the density and viscosity of the liquid-phase refrigerant are relatively large, the centrifugal force it receives is greater than that of the gas-phase refrigerant, so that the liquid-phase refrigerant accumulates on the outer side of the bent section, while the gas-phase refrigerant accumulates on the inner side of the bent section. The gas-liquid two-phase separation occurs, which further leads to the asymmetry of the flow pattern of the two-phase refrigerant entering the liquid distributor body. This asymmetric flow pattern will seriously affect the uniformity of the liquid distributor. The inventor proposed a refrigerant liquid distributor structure in Chinese Patent CN216204506U. This structure uses the method of reflection mixing to enhance the collision intensity of the two-phase refrigerant to improve the liquid distribution uniformity. After the optimization of the input pipe and the mixing chamber structure parameters, this liquid distributor structure has excellent flow distribution performance when the input mass flow rate of the refrigerant is relatively large, but its improvement effect is relatively limited when the input mass flow rate of the refrigerant is relatively small (such as a 1HP or 1.5HP household air conditioner).

[0004] In order to solve the problem of uneven distribution of the inlet gas-liquid two-phase, some people also proposed to carry out continuous reverse bending on the inlet connecting pipe or adjust the necessary straight section length after bending to improve the degree of gas-liquid two-phase separation, as Figure 1 shown. However, whether it is continuous reverse bending or the lengthening of the straight section length after bending, it will increase the installation space of the inlet connecting pipe, making it difficult to be applied to models with a small installation space, such as 1HP or 1.5HP household air conditioners. In addition, in this solution, the bending parameters or the necessary straight section parameters need to be customized and designed according to the different model sizes in actual applications and verified; such an improvement solution is obviously uneconomical and difficult to repeat in actual applications; furthermore, continuous reverse bending will also bring a series of problems such as excessive pressure loss of the inlet refrigerant, excessive noise, and difficulty in ensuring the accuracy and consistency of batch processing. Summary of the Invention

[0005] The utility model aims to overcome the deficiencies of the prior art and provides a secondary jet type liquid distributor, a heat exchanger assembly and an air conditioner.

[0006] To achieve the above object, the utility model provides a secondary jet type liquid distributor, which comprises a liquid distribution body, an input pipe, a first mixing cavity plate, a partition plate and a secondary jet plate. Input pipe assembly holes and a plurality of liquid distribution holes are respectively formed at two axial ends of the liquid distribution body. The input pipe is connected to the input pipe assembly hole to inject refrigerant into the liquid distribution body. The first mixing cavity plate is arranged in the inner cavity of the liquid distribution body. A first mixing cavity with an opening facing the input pipe assembly hole is formed by the convex extension of the first mixing cavity plate at the position opposite to the input pipe assembly hole towards the side where the liquid distribution holes are located. A plurality of first diversion holes located on the outer periphery of the first mixing cavity when projected along the axial direction of the liquid distribution body are further formed on the first mixing cavity plate. A first chamber is defined by the plane of the upstream surface of the first mixing cavity plate near the first diversion holes and the inner wall of the input end of the liquid distribution body. The partition plate is located on the downstream side of the first mixing cavity plate. A second chamber surrounding the first mixing cavity and in a ring shape is defined between the partition plate and the first mixing cavity plate. A plurality of partition holes communicating with the second chamber are formed on the partition plate. The secondary jet plate is located on the downstream side of the partition plate and has a secondary jet hole. A third chamber is formed based on the secondary jet plate and the partition plate. The volumes V1 of the first chamber, V2 of the second chamber and V3 of the third chamber satisfy: 0.6 ≤ V1 / V2 ≤ 1.4,

[0007] 0.6 ≤ V2 / V3 ≤ 1.4.

[0008] According to an embodiment of the utility model, an avoidance hole is formed on the partition plate. The partition plate is sleeved outside the outer periphery of the first mixing cavity through the avoidance hole. A third chamber is defined by the downstream surface of the partition plate, the outer bottom wall of the first mixing cavity and the upstream surface of the secondary jet plate;

[0009] Alternatively, the position of the partition plate opposite to the first mixing cavity is in a closed structure, and the partition plate is basically attached to the outer bottom wall of the first mixing cavity.

[0010] According to an embodiment of the utility model, the plurality of partition holes and the plurality of first diversion holes on the first mixing cavity plate are distributed in a staggered manner. The sum of the flow-through areas S1 of the plurality of partition holes and the cross-sectional area S01 of the inner cavity of the liquid distribution body where the partition plate is located satisfy: 0.1 ≤ S1 / S01 ≤ 0.45.

[0011] According to an embodiment of the utility model, the first diversion holes and the partition holes are each one or a combination of through holes, flanging holes, arc bubble holes, etc.;

[0012] The secondary jet hole is a through hole or a flanging hole with a hole wall extending towards the output end of the liquid distribution body.

[0013] According to an embodiment of the present utility model, the secondary jet type liquid distributor further includes a second mixing chamber plate. The second mixing chamber plate is located on the downstream side of the secondary jet plate, and a re-mixing chamber is defined between the two. A liquid distribution chamber communicating with a plurality of liquid distribution holes is defined between the second mixing chamber plate and the inner wall of the output end of the main body. A reflection mixing area and a plurality of second diversion holes are formed on the second mixing chamber plate. The reflection mixing area is distributed opposite to the secondary jet holes. The plurality of second diversion holes correspond to the plurality of liquid distribution holes one by one and are annularly distributed on the plane of the second mixing chamber plate on the outer periphery of the reflection mixing area around the axis of the liquid distribution main body.

[0014] According to an embodiment of the present utility model, the second mixing chamber plate at the reflection mixing area protrudes and extends towards the side where the liquid distribution holes are located, and the reflection mixing area becomes a second mixing chamber with an opening facing the secondary jet holes. Both the first mixing chamber and the second mixing chamber are in a shape where the longitudinal section profile line is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

[0015] According to an embodiment of the present utility model, the downstream surface of the second mixing chamber plate is close to a plane. The secondary jet type liquid distributor further includes an annular flow channel member disposed in the liquid distribution chamber and inside the circumference of the plurality of liquid distribution holes. The annular flow channel member is a rotary member formed by protruding and extending from the inner bottom wall of the output end of the main body towards the direction of the second mixing chamber plate and rotating around the axis of the liquid distribution main body. An annular flow channel communicating with the plurality of liquid distribution holes is defined between the annular flow channel member and the inner circumferential wall of the main body, and the cross-section of the annular flow channel member is basically unchanged or gradually decreases along the extension direction.

[0016] According to an embodiment of the present utility model, the annular flow channel member is a spacer sleeve with a cross-section that is basically unchanged along its extension direction. The extending top end of the spacer sleeve abuts against the reflection mixing area on the second mixing chamber plate.

[0017] According to an embodiment of the present utility model, the cross-section of the annular flow channel member gradually decreases along its extension direction. The vertical distance H1 from the extending top end of the annular flow channel member to the downstream surface of the second mixing chamber plate satisfies: 1mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the liquid distribution chamber.

[0018] According to an embodiment of the present utility model, the secondary jet type liquid distributor further includes a flow splitting and guiding member located on the downstream side of the secondary jet plate. The flow splitting and guiding member protrudes and extends from the inner bottom wall of the output end of the main body towards the direction of the secondary jet plate. The longitudinal section of the flow splitting and guiding member is triangular, and its extending top end is opposite to the secondary jet holes.

[0019] According to an embodiment of the present utility model, the minimum inner diameter of the primary jet part on the input pipe is greater than or equal to the minimum inner diameter of the secondary jet holes.

[0020] According to an embodiment of the present utility model, the input pipe includes a main body section and a jet section that are sequentially distributed along the refrigerant flow direction. The inner diameter of the main body section is basically unchanged, and a primary jet pipe hole with a reduced inner diameter compared to the main body section is formed on the jet section.

[0021] According to an embodiment of the present utility model, a jet plate is arranged in the input pipe, a primary jet pipe hole with an inner diameter smaller than that of the main body section is formed on the jet plate, and the input pipe section where the jet plate is located forms a jet section;

[0022] Alternatively, the jet section is a Venturi pipe section, and a primary jet pipe hole is formed at the throat of the Venturi pipe section;

[0023] Alternatively, the jet section is a straight pipe section with a reduced inner diameter relative to that of the main body section.

[0024] According to an embodiment of the present utility model, the secondary jet type liquid distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of liquid distribution holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1 mm ≤ △d ≤ 3.5 mm.

[0025] According to an embodiment of the present utility model, a reflection section is formed on the first pipe section and extends bent towards one side of the central axis of the liquid distribution hole. An included angle θ is formed between the axis at the upstream end of the reflection section and the axis at the downstream end of the reflection section, and 90° ≤ θ ≤ 175°. Based on the reflection section, the axis of the second pipe section intersects the central axis of the liquid distribution hole;

[0026] Alternatively, the first pipe section is a straight pipe.

[0027] According to an embodiment of the present utility model, each branch pipe further includes a branch section. The second pipe section is a tapered structure integrally formed with the first pipe section and having a gradually decreasing inner diameter. The branch section is welded and connected to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed;

[0028] Alternatively, the branch section is socket-welded to the first pipe section, and the socket-welding part of the two forms the second pipe section;

[0029] Alternatively, the branch section is socket-welded to the first pipe section, and the second pipe section is formed on the branch section.

[0030] On the other hand, the present utility model further provides a heat exchanger assembly, which includes the above-mentioned secondary jet type liquid distributor.

[0031] On the other hand, the present utility model further provides an air conditioner, which includes the above-mentioned heat exchanger assembly.

[0032] In summary, in the secondary jet type liquid distribution head provided by the present utility model, the input pipe injects the refrigerant with an asymmetric flow pattern into the inner cavity of the liquid distribution body at a high speed. After being reflected and mixed in the first mixing cavity, the high-speed refrigerant gradually develops into a dispersed flow pattern in the first cavity formed by the first mixing cavity plate and the inner wall of the input end of the liquid distribution body to achieve the preliminary arrangement of the refrigerant. A partition plate is provided to divide the space between the first mixing cavity plate and the secondary jet plate into a first cavity and a second cavity, and the volume ratio among the volume V1 of the first cavity, the volume V2 of the second cavity, and the volume V3 of the third cavity is controlled. This setting precisely controls the degree of volume expansion of the refrigerant when flowing between adjacent cavities to avoid excessive expansion of the refrigerant, and provides conditions for the refrigerant after preliminary arrangement to gradually develop into a stable dispersed flow pattern in the first cavity and the second cavity with smaller volumes. The refrigerant after stable development converges on the secondary jet holes on the secondary jet plate. The secondary jet holes reduce the pressure and increase the speed of the refrigerant, improving the flow rate of the refrigerant so that it can always maintain the arranged dispersed flow pattern during subsequent distribution, thereby greatly enhancing the liquid distribution performance of the liquid distribution head.

[0033] The secondary jet liquid distribution head provided by the present utility model realizes the arrangement of the refrigerant inlet flow pattern by arranging a first mixing cavity plate, a partition plate, and a secondary jet plate in the liquid distribution body, reducing the influence of the refrigerant inlet flow pattern on the liquid distribution performance. The liquid distribution head with this structure does not require any adjustment on the input pipe, which not only greatly facilitates the processing, installation, and welding of the input pipe, but also greatly improves the applicability of the liquid distribution head so that it can be well compatible with various different specifications of refrigeration equipment.

[0034] To make the above and other objects, features, and advantages of the present utility model more obvious and understandable, the following specifically enumerates preferred embodiments and, in conjunction with the accompanying drawings, makes a detailed description as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 The figure shows a schematic structural diagram of an input pipe in the prior art with multiple bending parts provided on the input pipe to improve the refrigerant flow pattern at the inlet of the liquid distribution head.

[0036] Figure 2 The figure shows a schematic structural diagram of the secondary jet type liquid distribution head provided by Embodiment 1 of the present utility model.

[0037] Figure 3 The figure shows Figure 2 a schematic distribution diagram of the first cavity, the second cavity, and the third cavity.

[0038] Figure 4 The figure shows Figure 2 a schematic structural diagram of the partition plate in.

[0039] Figure 5 The figure shows Figure 2 a schematic projection diagram of multiple first diversion holes on the first mixing cavity plate on the partition plate.

[0040] Figure 6A and Figure 6B The following figure shows a schematic structural diagram of the secondary jet type liquid distributor provided by another embodiment of the present utility model after removing the input pipe and the branch pipe.

[0041] Figure 7 The following figure shows Figure 2 a schematic structural diagram of the first mixing cavity plate in

[0042] Figure 8A , Figure 8B , Figure 8C , Figure 8D and Figure 8E The following figure shows a schematic structural diagram of the first mixing cavity plate in another embodiment of the present utility model.

[0043] Figure 9A and Figure 9B The following figure shows a schematic structural diagram of the secondary jet plate in another embodiment of the present utility model.

[0044] Figure 10A and Figure 10B The following figure shows a schematic structural diagram of the input pipe in another embodiment of the present utility model.

[0045] Figure 10C The following figure shows a schematic structural diagram of the secondary jet type liquid distributor provided by another embodiment of the present utility model.

[0046] Figure 11 The following figure shows Figure 2 a schematic structural diagram of the branch pipe in

[0047] Figure 12A , Figure 12B , Figure 12C , Figure 12D , Figure 12E , Figure 12F and Figure 12G The following figure shows a schematic structural diagram of the branch pipe in another embodiment of the present utility model.

[0048] Figure 13 The following figure shows a schematic structural diagram of the secondary jet type liquid distributor provided by the second embodiment of the present utility model.

[0049] Figure 14 The following figure shows a schematic structural diagram of the secondary jet type liquid distributor provided by the third embodiment of the present utility model.

[0050] Figure 15 The following figure shows Figure 14 a schematic structural diagram after removing the liquid inlet pipe and the branch pipe in

[0051] Figure 16 The following figure shows a schematic structural diagram of the second mixing cavity plate in another embodiment of the present utility model.

[0052] Figure 17 The figure shows a structural schematic diagram of a secondary jet type liquid distributor after removing the inlet pipe and branch pipes provided by another embodiment of the present utility model.

[0053] Figure 18 The figure shows a structural schematic diagram of a secondary jet type liquid distributor provided by Embodiment 4 of the present utility model.

[0054] Figure 19 The figure shows a structural schematic diagram of a secondary jet type liquid distributor provided by another embodiment of the present utility model. Detailed implementation manners

[0055] In this application, the downstream or upstream is divided based on the flow direction of the refrigerant. Generally, the refrigerant flows from the upstream to the downstream, and the area located downstream receives the refrigerant from the upstream. In a refrigeration device, the liquid distributor is generally installed vertically or obliquely, and the inlet end of the liquid distributor is located below the outlet end along the direction of gravity. The inertial force of the refrigerant in the liquid distributor overcomes the gravity and flows in the direction opposite to the gravity; at this time, the upstream and downstream are still divided according to the flow direction of the refrigerant.

[0056] Embodiment 1

[0057] The liquid distributor is connected between the expansion valve and the heat exchanger assembly. Therefore, its liquid distribution performance is affected not only by its own structure, but also by the upstream refrigerant flow state (i.e., the inlet flow pattern) and the factors of each downstream branch. Due to the limitation of the installation space in the refrigeration device, the input pipe of the liquid distributor usually has a bending section. Since the centrifugal forces received by the gas-liquid two-phase at the bend are different, the refrigerant undergoes phase separation at this place, resulting in an asymmetric inlet flow pattern of the liquid distributor, and this asymmetry is particularly obvious when the mass flow rate of the refrigerant is small. For the asymmetric inlet flow pattern of the refrigerant with a small mass flow rate, it is extremely difficult for the existing liquid distributors to effectively improve it. In response to this, some people have proposed a solution to optimize the structure of the input pipe to improve the inlet flow pattern (as shown in Figure 1 ), but this optimization solution will bring problems such as a relatively large volume of the input pipe, which is difficult to be applicable to refrigeration devices with a narrow installation space, and difficulties in processing and welding the input pipe.

[0058] In view of this, this embodiment provides a secondary jet type liquid distributor that integrates inlet flow pattern rectification and uniform distribution of the refrigerant after rectification. As shown in Figure 2 and Figure 3As shown, the secondary jet type liquid distributor provided in this embodiment includes a liquid distribution body 1, an input pipe 5, a first mixing chamber plate 2, a partition plate 3, and a secondary jet plate 4. Input pipe assembly holes 13 and a plurality of liquid distribution holes 14 are respectively formed at both axial ends of the liquid distribution body 1. The input pipe 5 is connected to the input pipe assembly hole 13 to inject refrigerant into the liquid distribution body 1. The first mixing chamber plate 2 is disposed in the inner cavity of the liquid distribution body 1. A protrusion extends from a position on the first mixing chamber plate 2 opposite to the input pipe assembly hole 13 toward the side where the liquid distribution holes 14 are located to form a first mixing chamber 21 with an opening facing the input pipe assembly hole 13. A plurality of first diversion holes 22 are also formed on the first mixing chamber plate 2, which are located outside the first mixing chamber 21 when projected along the axial direction of the liquid distribution body 1. A first chamber 101 is defined between the plane of the upstream surface of the first mixing chamber plate 2 near the first diversion holes 22 and the inner wall of the input end of the liquid distribution body 1 (such as the chamber enclosed by the dotted line in Figure 3 ). The partition plate 3 is located on the downstream side of the first mixing chamber plate 2. A second chamber 102 that surrounds the first mixing chamber 21 and is annular is defined between the partition plate 3 and the first mixing chamber plate 2 (such as the chamber enclosed by the center dotted line in Figure 3 ). A plurality of partition holes 31 that communicate with the second chamber 102 are formed on the partition plate 3. The secondary jet plate 4 is located on the downstream side of the partition plate 3 and has a secondary jet hole 41. A third chamber 103 is formed based on the secondary jet plate 4 and the partition plate 3 (such as the chamber enclosed by the dotted line in Figure 3 ). The volumes V1 of the first chamber, V2 of the second chamber, and V3 of the third chamber satisfy: 0.6 ≤ V1 / V2 ≤ 1.4, 0.6 ≤ V2 / V3 ≤ 1.4.

[0059] In the secondary jet-type liquid distributor provided in this embodiment, the input pipe 5 and the secondary jet holes 41 form a secondary jet. The input pipe 5 injects the refrigerant into the liquid distribution body 1 in a primary jet, disturbing the refrigerant flow pattern at the inlet of the liquid distribution body 1 and increasing the kinetic energy of the refrigerant so that the refrigerant can quickly develop into a dispersed flow pattern during preliminary sorting, providing a basis for the conversion of the refrigerant flow pattern from a laminar flow at the inlet to a fully mixed dispersed flow pattern. The secondary jet holes 41 then increase the flow rate of the refrigerant after the flow pattern is sorted, so that the refrigerant can always maintain a uniformly mixed dispersed flow pattern during the redistribution process after sorting, thereby improving the liquid distribution uniformity. In particular, the secondary jet-type liquid distributor provided in this embodiment also provides a partition 3 between the first mixing chamber plate 2 and the secondary jet plate 4, forming a second chamber 102 and a third chamber 103 with relatively small volumes based on the partition 3, avoiding excessive expansion of the refrigerant due to the too large inner cavity volume of the liquid distribution body 1, and thus preventing the phenomenon of gas-liquid two-phase separation. On this basis, by controlling the volume ratio of adjacent chambers, the volume change rate of the refrigerant during flow is controlled to achieve precise control of the refrigerant flow rate, ensuring that the refrigerant after preliminary sorting is gradually mixed in the second chamber 102 and the third chamber 103 to develop into a stable dispersed flow pattern, and thus realizing the sorting of the refrigerant from the inlet asymmetric flow pattern to the uniformly mixed dispersed flow pattern.

[0060] The secondary jet-type liquid distributor provided in this embodiment optimizes the inner cavity structure of the liquid distribution body 1 to replace the existing input pipe bending scheme, sorting and stably developing the inlet asymmetric flow pattern into a uniformly mixed dispersed flow pattern, and reducing the influence of the refrigerant inlet flow pattern on the liquid distribution performance. Further, the refrigerant inlet flow pattern sorting achieved based on the optimization of the liquid distribution body also enables the secondary jet-type liquid distributor provided in this embodiment to be highly compatible with various refrigerant inlet conditions and refrigeration equipment with different installation spaces. Specifically, the inlet flow pattern sorting achieved based on the secondary jet-type liquid distributor makes it unnecessary to consider the gas-liquid mixing situation of the refrigerant in the input pipe when arranging the inlet side pipeline, thus greatly facilitating the processing, installation, and welding of the inlet side pipeline. In addition, compared with the large installation space required for input pipe bending, the optimization of the inner cavity structure of the liquid distribution body 1 only slightly increases the axial length of the liquid distributor. Therefore, it can be well applied to refrigeration equipment with different installation spaces, including household air conditioner indoor units with a narrow space of 1HP or 1.5HP.

[0061] The following will combine Figures 2 to 11 to make a detailed description of the structure and working principle of the secondary jet-type liquid distributor provided in this embodiment.

[0062] As Figure 2 and Figure 3As shown, affected by the centrifugal force at the bent part of the input pipe 5, the refrigerant input into the liquid separation body 1 through the input pipe 5 has an asymmetric flow pattern of gas-liquid two-phase separation. When the refrigerant flows through the primary jet pipe hole 50 on the input pipe 5, its flow velocity increases, and the streamline of the refrigerant pulsates to enhance its degree of disorder; at the same time, the increase in flow velocity also increases the kinetic energy of the refrigerant input into the liquid separation body 1. After entering the liquid separation body 1, the disturbed high-speed refrigerant is sprayed into the first mixing chamber 21, and after being reflected by the bottom wall of the first mixing chamber 21, it collides violently in the first mixing chamber 21 to break up the liquid-phase refrigerant into droplets. The first mixing chamber 21 provides a mixing space for the refrigerant during the stage of maximum kinetic energy after reflection, enhancing the degree of disorder to promote gas-liquid two-phase mixing. At the same time, when the mass flow rate of the input refrigerant is large and the flow velocity is fast, the setting of the first mixing chamber 21 can also effectively reduce the influence of the reflection force on the input refrigerant, avoiding the refrigerant reflux in the input pipe caused by excessive reflection force. The reflected flow beam and the incident flow beam of the refrigerant after being reflected and mixed in the first mixing chamber 21 form a turbulent flow in the first chamber 101, the droplets are further broken up and spread around, and the dispersed droplets are distributed into the gas phase, making the asymmetric refrigerant gradually develop into a uniformly mixed dispersed flow pattern, that is, the preliminary sorting of the refrigerant is realized.

[0063] Next, the preliminarily sorted refrigerant needs to be further developed into a stable dispersed flow pattern. The condition for the refrigerant to develop into a stable dispersed flow pattern is that the Froude number, which characterizes the ratio of the inertial force to the gravitational force of the liquid-phase refrigerant, is greater than 7. The inertial force of the liquid-phase refrigerant is related to the flow rate of the refrigerant, and the flow rate of the refrigerant is in turn related to the volume of the chamber it is in. Therefore, the area between the first mixing chamber plate 2 and the secondary jet plate 4 is divided into a second chamber 102 and a third chamber 103 with relatively small volumes by the partition plate 3, and the volume ratio of adjacent chambers is precisely controlled. The second chamber 102 and the third chamber 103 provide a mixing space for the refrigerant in a step-by-step mixing manner, effectively avoiding a sudden drop in the refrigerant flow rate caused by excessive expansion while promoting the full mixing of the two-phase flow, ensuring that the liquid-phase refrigerant in the second chamber 102 and the third chamber 103 has sufficient inertial force to overcome the influence of gravity, and providing conditions for the full mixing of the refrigerant and its development into a stable dispersed flow pattern. Specifically, the preliminarily sorted refrigerant enters the second chamber 102 through a plurality of first diversion holes 22 on the first mixing chamber plate 2. When the refrigerant flows through the plurality of first diversion holes 22, its flow rate increases, the liquid-phase mass flow rate increases with the increase of the liquid-phase flow rate, and the liquid film becomes thinner. The thinned liquid film breaks when colliding in the second chamber 102 to atomize into smaller-diameter liquid droplets and gradually disperse into the gas phase. The preliminarily atomized refrigerant enters the third chamber 103 through a plurality of partition holes 31 on the partition plate 3. Similarly, the acceleration of the refrigerant by the partition holes 31 makes the liquid film on the liquid droplets thinner, and the liquid droplets atomize into smaller forms in the third chamber 103 so that the refrigerant gradually develops into a stable dispersed flow pattern, thereby realizing the sorting conversion from the inlet asymmetric flow pattern to the uniform and stable dispersed flow pattern.

[0064] In this embodiment, it is set that the first chamber volume V1, the second chamber volume V2, and the third chamber volume V3 satisfy: 0.6 ≤ V1 / V2 ≤ 1.4, 0.6 ≤ V2 / V3 ≤ 1.4. Specifically, V1 / V2 and V2 / V3 can both be any volume ratio among 0.65, 0.7, 0.75, 0.8, 0.85, 0.9, 0.95, 1.0, 1.05, 1.1, 1.15, 1.2, 1.25, 1.3, 1.35. However, the present utility model does not make any limitation thereto. In other embodiments, V1 / V2 and V2 / V3 can both be any ratio within 0.6 to 1.4.

[0065] After the flow pattern is rectified (organized and stabilized), the refrigerant needs to be evenly distributed to each branch pipe 6. Since the liquid distributor is usually installed vertically, the refrigerant needs to be distributed from bottom to top in the direction opposite to gravity to multiple branch pipes 6. During the distribution process, the refrigerant will be affected by both inertial force and gravity. In the gas-liquid two-phase refrigerant, the flow of the liquid-phase refrigerant mainly depends on inertial force and gravity. Too low refrigerant flow rate will cause the inertial force of the liquid-phase refrigerant to be less than its gravity. After the flow pattern is rectified, the liquid phase in the refrigerant is extremely vulnerable to the influence of gravity and will be separated from the gas phase again, and even some refrigerant will deposit and cannot be distributed to the liquid outlet side, which will seriously affect the uniformity of the flow splitting. Therefore, in this embodiment, a secondary jet hole 41 is provided on the secondary jet plate 4. The refrigerant that develops into a dispersed flow pattern in the third chamber 103 gradually converges at the secondary jet hole 41 and is sprayed to the body output side 12 after the pressure is reduced and the speed is increased through the secondary jet hole 41. The high-speed refrigerant increases the inertial force of the liquid-phase refrigerant so that it can overcome the influence of gravity and follow the gas phase flow. The two-phase refrigerant maintains a dispersed flow pattern and is evenly distributed into multiple liquid distribution holes 14, thereby realizing uniform liquid distribution.

[0066] In the secondary jet type liquid distributor provided in this embodiment, the primary jet tube hole 50 and the secondary jet hole 41 form a two-stage jet, and both gradually increase the refrigerant flow rate to weaken the influence of gravity during the flow pattern rectification and uniform distribution process of the refrigerant, so that the refrigerant can always maintain a uniformly mixed dispersed flow pattern. Preferably, the minimum inner diameter D2 of the secondary jet hole 41 is less than or equal to the minimum inner diameter D1 of the primary jet tube hole 50. However, the present utility model does not make any limitation on this.

[0067] In this embodiment, as Figure 2 and Figure 4 shown, a relief hole 32 is formed on the partition plate 3 opposite to the first mixing chamber 21, and the partition plate 3 is sleeved outside the first mixing chamber 21 through the relief hole 32. At this time, the first chamber 101 refers to the chamber surrounded by the plane of the upstream surface of the first mixing chamber plate 2 near the first diversion hole 22 and the inner wall of the liquid distribution body input end 11, as Figure 3 the chamber surrounded by the dotted line in Figure 3 The second chamber 102 is an annular chamber surrounding the first mixing chamber 21 formed by the downstream surface of the first mixing chamber plate 2 and the upstream surface of the partition plate 3, as Figure 3 the area indicated by the center dotted line in Figure 3 The third chamber 103 is the chamber surrounded by the downstream surface of the first mixing chamber plate 2 at the first mixing chamber 21, the downstream surface of the partition plate 3, and the upstream surface of the secondary jet plate 4, as Figure 3 the area indicated by the dotted line in Figure 3 However, the present utility model does not make any limitation on this. In other embodiments, it is also possible to set the structure at the position of the partition plate opposite to the first mixing chamber to be a closed structure, and the partition plate is basically attached to the outer bottom surface of the first mixing chamber; at this time, the third chamber is the chamber surrounded by the downstream surface of the partition plate and the upstream surface of the secondary jet plate, asFigure 6A As shown. In other embodiments, such as Figure 6B shown, a partition plate 3 may also be provided downstream of the first mixing chamber 21, and the portion of the partition plate 3 opposite to the first mixing chamber 21 bulges and extends upstream to fit against the outer bottom surface of the first mixing chamber 21.

[0068] In this embodiment, as Figure 5 shown, a plurality of partition holes 31 on the partition plate 3 are distributed in a staggered manner with a plurality of first diversion holes 22 on the first mixing chamber plate 2; Figure 5 The projection positions of the plurality of first diversion holes 22 on the partition plate 3 are indicated by dashed lines in. This setting enables the refrigerant preliminarily sorted in the first chamber 101 not to directly flow through to the third chamber 103, but to be preliminarily atomized in the second chamber 102 and then enter the third chamber 103 through a plurality of partition holes 31 for further atomization, and to be mixed and atomized step by step to ensure sufficient mixing of the two-phase flow. To avoid excessive pressure loss of the refrigerant caused by excessive acceleration of the first diversion holes 22 and the partition holes 31, the sum of the flow areas S1 of the plurality of partition holes 31 and the cross-sectional area S01 of the inner cavity of the body where the partition plate 3 is located satisfy: 0.1 ≤ S2 / S01 ≤ 0.45; the sum of the flow areas S2 of the plurality of first diversion holes 22 and the cross-sectional area S02 of the inner cavity of the body where the first mixing chamber plate 2 is located also satisfy: 0.1 ≤ S2 / S02 ≤ 0.45. Specifically, the area ratios S1 / S01 and S2 / S02 can be set to any of 0.15, 0.2, 0.25, 0.3, 0.35, etc.

[0069] In this embodiment, as Figure 7 shown, the first mixing chamber 21 is a cylindrical chamber with a square cross-sectional contour line in the longitudinal section, and the longitudinal section refers to the section along the depth direction of the first mixing chamber 21. However, the present invention makes no limitation thereto. In other embodiments, the shape of the first mixing chamber 21 may also be a prism with a square cross-sectional contour line in the longitudinal section, a frustum of a cone or a prism with a trapezoidal cross-sectional contour line in the longitudinal section (such as Figure 8A ), a cone or a pyramid with a triangular cross-sectional contour line in the longitudinal section (such as Figure 8B ), and a partial circle (i.e., a partial sphere, such as Figure 8C ) in the longitudinal section, or a combination of one or more of them. Such as a combination of a cylinder and a partial sphere (such as Figure 8D shown), a combination of a frustum of a cone and a partial sphere (such as Figure 8E shown), a combination of a prism and a partial sphere, etc.

[0070] In this embodiment, the first diversion holes 22 on the first mixing chamber plate 2 are through holes with substantially the same inner diameter. However, the present invention makes no limitation thereto. In other embodiments, the first diversion holes 22 may also be inclined through holes with an inner diameter gradually decreasing along the refrigerant flow direction, such as Figure 8C shown; in Figure 8CIn [the device], the first mixing cavity plate 2 includes a cavity plate body 2A and a lining plate 2B bonded and welded to the cavity plate body 2A. A plurality of body diversion holes are formed in the cavity plate body 2A, and a plurality of lining plate diversion holes that are basically coaxial are formed in the lining plate 2B. The body diversion holes and the corresponding lining plate diversion holes together form an inclined first diversion hole 22. Or, as Figure 8B shown, the first diversion hole 22 can be set as a flanging hole with an inner wall generatrix in an arc shape and a hole diameter gradually decreasing along the refrigerant flow direction; or, a straight hole section with a basically unchanged hole diameter can be added at the end of the flanging hole, that is, the inner wall generatrix of the first diversion hole is a combination of an arc shape and a straight line. In addition, in other embodiments, the first diversion hole 22 can also be set as an arc bubble hole with the hole wall arcuately protruding towards one side or both sides of the partition plate, as Figure 8A and Figure 8D shown.

[0071] In this embodiment, the partition hole 31 is a through hole with a basically consistent hole diameter. However, the present utility model does not make any limitation thereto. In other embodiments, the partition hole can also be one or a combination of an inclined through hole, a flanging hole, and an arc bubble hole with a gradually decreasing hole diameter. Specifically, reference can be made to Figures 8A to 8E the shape of the first diversion hole in Figure 2 shown. As Figure 2 shown, the secondary jet holes 41 on the secondary jet plate 4 are flanging holes with the hole wall extending towards the output end 12 of the liquid separation body. However, the present utility model does not make any limitation thereto. In other embodiments, the secondary jet holes 41 can also be through holes with a basically unchanged hole diameter, or through holes with a hole diameter gradually decreasing along the refrigerant flow direction (as Figure 9A shown). Or, a straight section can be added on the basis of the flanging hole, as Figure 9B shown.

[0072] In the secondary jet type liquid separator provided in this embodiment, the input pipe 5 forms a primary jet to increase the refrigerant flow rate at the inlet of the liquid separation body 1, enhance the turbulence degree of the inlet refrigerant, and increase the refrigerant kinetic energy, so that the inlet refrigerant quickly develops into a dispersed flow pattern. To further increase the primary jet speed of the refrigerant, this embodiment sets that the input pipe 5 includes a main body section 51 and a jet section 52 distributed in sequence along the refrigerant flow direction. The inner diameter D0 of the main body section 51 is basically unchanged, and a primary jet pipe hole 50 with a reduced inner diameter relative to the main body section 51 is formed on the jet section 52. Based on the smaller inner diameter primary jet pipe hole 50, the primary jet speed of the refrigerant is increased. However, the present utility model does not make any limitation thereto. In other embodiments, when the primary jet speed provided by the input pipe 5 with a basically consistent inner diameter is sufficient to meet the liquid separation uniformity requirement, the jet section may not need to be provided on the input pipe 5, that is, the inner diameter of the entire input pipe 5 is basically consistent.

[0073] As Figure 2As shown, in this embodiment, the jet section 52 is a straight section integrally formed with the main body section 51, and the inner diameter D1 of the jet section 52 is reduced relative to the inner diameter D0 of the main body section 51. A primary jet pipe hole 50 with a certain length is formed at the jet section 52. However, the present utility model does not make any limitation thereto. In other embodiments, such as Figure 10A shown, a jet orifice plate 53 may also be provided in the input pipe 5, and a primary jet pipe hole 50 is formed on the jet orifice plate 53. The jet section 52 of the input pipe is formed at the location where the jet orifice plate 53 is located; specifically, the primary jet pipe hole 50 may be a flanging hole, a straight hole with a substantially unchanged inner diameter (such as Figure 10B shown), or any one or combination of inclined holes. Or, as Figure 10C shown, the jet section 52 is provided as a Venturi tube section, and a primary jet pipe hole 50 is formed at the straight section of the throat of the Venturi tube section. The inner diameter at the straight section of the throat is the minimum inner diameter D1 of the primary jet pipe hole 50. In addition, in other embodiments, a plurality of Venturi tube sections may also be provided downstream of the main body section of the input pipe. In this structure, the straight section throat of the Venturi tube section closest to the input pipe assembly hole is used as the primary jet pipe hole.

[0074] In this embodiment, as Figure 2 and Figure 3 shown, the end of the jet section 52 is welded and connected to the inner part of the assembly straight section on the input pipe assembly hole 13. The end of the jet section 52 is the liquid outlet end of the input pipe 5. However, the present utility model does not make any limitation thereto. In other embodiments, the input pipe may also be integrally formed with the main body at the location where the input pipe assembly hole is located. Or, as Figure 10C shown, for the input pipe structure with the jet section 52 being a Venturi tube section, the input pipe assembly hole 13 may also be provided as a through hole without a welded assembly straight section. A gradually expanding section 54 with an outer wall generatrix in an arc curve is formed on the Venturi tube section downstream of the straight section of the throat. The gradually expanding section 54 extends into the first chamber 101 through the input pipe assembly hole 13, and the outer wall of the gradually expanding section 54 is welded in a surface-contact manner to the inner wall of the liquid distribution body input end 11.

[0075] As Figure 2 and Figure 11As shown in the figure, on the liquid separation side of the secondary jet liquid separator, each branch pipe 6 includes a first pipe section 61 and a second pipe section 62 located downstream of the first pipe section 61 and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section 61. The difference △d between the inner diameter d11 at the downstream end of the first pipe section 61 and the inner diameter d12 at the downstream end of the second pipe section 62 is: 0.1mm ≤ △d ≤ 3.5mm. The first pipe section 61 with a larger inner diameter increases the refrigerant flow rate distributed into each branch pipe 6 and reduces the distribution resistance of the refrigerant, while the second pipe section 62 with a relatively smaller inner diameter can increase the refrigerant flow velocity to meet the performance requirements of the rear heat exchanger assembly. On this basis, the inner diameter difference △d precisely controls the degree of pressure reduction and speed increase of the refrigerant in the second pipe section 62, avoiding excessive pressure loss of the refrigerant due to excessive speed increase.

[0076] Furthermore, a reflection section 611 is formed on the first pipe section 61 and extends bendedly to one side relative to the center line of the liquid separation hole 14. An included angle θ is formed between the axis at the upstream end of the reflection section 611 and the axis at the downstream end of the reflection section 611, and 90° ≤ θ ≤ 175°. The setting of the reflection section 611 makes the second pipe section 62 no longer coaxial with the center line of the liquid separation hole. When there is a pressure wave downstream and it oscillates upstream, the reflection section 611 reflects and absorbs part of the pressure wave and changes the propagation direction of the remaining pressure wave to make it decay rapidly, effectively avoiding the influence of the downstream pressure wave on the upstream liquid separation hole 14 to further improve the distribution performance.

[0077] In this embodiment, the branch pipe 6 further includes a branch section 63 welded to the first pipe section 61, and the second pipe section 62 is located on the branch section 63. Specifically, as Figure 11 shown, the upstream end of the branch section 63 is sleeved and connected to the downstream end of the first pipe section 61, and a second pipe section 62 with a gradually decreasing inner diameter is formed downstream of the socket joint of the branch section 63. However, the present invention makes no limitation in this regard. In other embodiments, it is also possible to set the upstream end of the branch section 63 to be internally sleeved and welded to the downstream end of the first pipe section 61; at this time, the second pipe section 62 is still a structure with a gradually decreasing inner diameter located downstream of the socket joint of the branch section 63, as Figure 12A shown.

[0078] Figure 12B 、 Figure 12C and Figure 12D are the structural schematic diagrams of the branch pipes provided by another embodiment of the present invention. Figure 12B In it, the first pipe section 61, the second pipe section 62 and the branch section 63 are integrally formed; Figure 12C In it, the first pipe section 61 and the second pipe section 62 are integrally formed, and the branch section 63 is welded to the end of the second pipe section 62. Figure 12DIn this case, based on the inner diameter difference between the downstream end of the first pipe section 61 and the upstream end of the branch section 63, the second pipe section 62 is directly formed at the socket connection between the first pipe section 61 and the branch section 63. In addition, multiple second pipe sections can also be provided at the downstream end of the first pipe section, and the branch section 63 can be set as a straight pipe or a bent pipe according to actual applications.

[0079] Although this embodiment is described by taking the example that the first pipe section 61 is formed with a reflection section 611. However, the present utility model does not make any limitation thereto. In other embodiments, the first pipe section 61 may not be provided with a reflection section. At this time, the first pipe section 61 is a straight pipe, such as Figure 12E shown.

[0080] Furthermore, for the structure of the second pipe section 62, in other embodiments, the second pipe section 62 can also be provided to include a tapered section and a maintaining straight section located downstream of the tapered section and having a certain length L62. The inner diameter of the maintaining straight section is close to the inner diameter at the downstream end of the tapered section and is basically unchanged within the length L62, such as Figure 12F shown. Alternatively, an orifice plate 66 is added at the flared connection of the first pipe section 61 or the branch section 63, and the refrigerant is accelerated by the through holes 661 on the orifice plate 66; at this time, the pipe section where the orifice plate 66 is located is the second pipe section 62, such as Figure 12G shown.

[0081] On the other hand, this embodiment also provides a heat exchanger assembly including the above-mentioned secondary jet type liquid distributor.

[0082] On the other hand, this embodiment also provides a refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0083] Embodiment Two

[0084] This embodiment is basically the same as Embodiment One and its variations, the difference being that: the secondary jet type liquid distributor further includes a flow splitting and guiding member 7 located on the downstream side of the secondary jet plate 4. As Figure 13 shown, the flow splitting and guiding member 7 is located inside the circumference of a plurality of liquid distribution holes 14. The flow splitting and guiding member 7 protrudes and extends from the inner bottom wall of the output end 12 of the main body towards the direction where the secondary jet plate 4 is located. The flow splitting and guiding member 7 is a flow splitting and guiding cone with a triangular longitudinal section, and the extending top end of the flow splitting and guiding member 7 is opposite to the secondary jet hole 41.

[0085] The refrigerant with a dispersed flow pattern after flow pattern rectification is jet to the flow splitting and guiding member 7 after pressure reduction and acceleration through the secondary jet hole 41, and is evenly distributed into a plurality of liquid distribution holes 14 along the inclined circumferential wall of the flow splitting and guiding member 7. Further, the setting of the flow splitting and guiding member 7 can also reduce the volume of the liquid distribution cavity 105 surrounded by the secondary jet plate 4 and the inner wall of the output end 12 of the liquid distribution main body, avoiding the excessive expansion of the evenly mixed refrigerant in the liquid distribution cavity 105 and affecting the liquid distribution performance.

[0086] Although the flow splitting and guiding member 7 in this embodiment is taken as an example of a conical shape for illustration. However, the present utility model does not make any limitation thereto. In other examples, the flow splitting and guiding member may also be a pyramid with a triangular longitudinal section. Preferably, the number of conical surfaces of the pyramid is set to be the same as the number of liquid distribution holes; for example, when the number of liquid distribution holes is four, the flow splitting and guiding member can be set as a quadrangular pyramid, and the four inclined side surfaces of the quadrangular pyramid are distributed opposite to the four liquid distribution holes.

[0087] Embodiment III

[0088] This embodiment is basically the same as Embodiment I and its variations, the difference being that the secondary jet type liquid distributor further includes a second mixing cavity plate 8.

[0089] As Figure 14 and Figure 15 shown, the second mixing cavity plate 8 is located on the downstream side of the secondary jet plate 4, and a re-mixing cavity 104 is formed between the two. A liquid distribution cavity 105 communicating with a plurality of liquid distribution holes 14 is formed between the second mixing cavity plate 8 and the inner wall of the main body output end 12. A reflection mixing area 81 and a plurality of second guiding holes 82 are formed on the second mixing cavity plate 8. The reflection mixing area 81 is distributed opposite to the secondary jet holes 41. The plurality of second guiding holes 82 correspond to the plurality of liquid distribution holes 14 one by one and are annularly distributed around the axis of the liquid distribution body 1 on the plane of the second mixing cavity plate 8 outside the reflection mixing area 81. The uniformly distributed refrigerant after flow pattern rectification is ejected into the re-mixing cavity 104 through the secondary jet holes 41 after pressure reduction and speed increase. Under the action of inertia force, the high-speed refrigerant will continue to flow forward and impact the second mixing cavity plate 8. The second mixing cavity plate 8 reflects the refrigerant, enhancing the collision degree of the gas-liquid two-phase while the reflected flow beam also undergoes convection with the jet flow beam to promote the mixing of the gas-liquid two-phase.

[0090] In this embodiment, the second mixing cavity plate 8 at the reflection mixing area 81 bulges and extends towards the side where the liquid distribution holes 14 are located, and the reflection mixing area 81 becomes a second mixing cavity with an opening facing the secondary jet holes 41. The inner bottom wall of the second mixing cavity (reflection mixing area 81) reflects the high-speed refrigerant ejected from the secondary jet holes 41, and the reflected refrigerant is fully mixed in the second mixing cavity with the maximum kinetic energy. In addition, the convex extension of the reflection mixing area 81 also forms an annular liquid distribution cavity 105 between the second mixing cavity plate 8 and the inner wall of the liquid distribution body 1. This setting can reduce the volume of the liquid distribution cavity 105 to maintain a high-speed dispersed flow pattern of the refrigerant and quickly distribute it into a plurality of liquid distribution holes 14. However, the present utility model does not make any limitation thereto. In other implementations, a concave cavity can also be formed at the reflection mixing area 81 based on the thickness of the second mixing cavity plate 8 itself. At this time, the downstream surface of the second mixing cavity plate 8 is still basically close to a plane, as Figure 16 shown. Or, the second mixing cavity plate is set as a flat plate structure with both side surfaces close to a plane.

[0091] Further, the vertical distance H between the extended top end of the second mixing chamber (reflection mixing area 81) and the inner bottom wall of the body output end 12 satisfies: 0 ≤ H ≤ 3 mm. Based on the determined height H0 of the liquid separation chamber 105 and the inner diameter of the liquid separation body 1, the setting of the vertical distance H realizes the precise control of the volume inside the liquid separation chamber 105, effectively avoiding the re-occurrence of gas-liquid separation of the dispersed refrigerant due to the over-large liquid separation chamber 105, and further improving the uniformity of refrigerant distribution. Preferably, H is set to 0, that is, the extended top end at the second mixing chamber (reflection mixing area 81) abuts against the inner bottom wall of the body output end 12, as Figure 2 shown. However, the present utility model makes no limitation thereto. In other embodiments, as Figure 17 shown, it is also possible to set the extended top end at the second mixing chamber (reflection mixing area 81) not to abut against the inner bottom wall of the body output end 12, but at this time the vertical distance H is also less than or equal to 3 mm.

[0092] In this embodiment, the second mixing chamber (reflection mixing area 81) is a cylindrical chamber with a square cross-sectional contour line. However, the present utility model makes no limitation thereto. In other embodiments, the shape of the second mixing chamber can also be a prism with a square cross-sectional contour line, a frustum of a cone or a prism with a trapezoidal cross-sectional contour line, a cone or a pyramid with a triangular cross-sectional contour line, and one or more combinations of a partially circular cross-sectional contour line; such as a combination of a cylinder and a partial sphere, a combination of a frustum of a cone and a partial sphere, a combination of a prism and a partial sphere, etc.

[0093] In this embodiment, the number of the second diversion holes 82 is the same as the number of the liquid separation holes 14, and each second diversion hole 82 is substantially coaxial with the corresponding liquid separation hole 14. This setting forms the shortest axial transmission path between the second diversion hole 82 and the corresponding liquid separation hole 14, and the high-speed refrigerant output from the second diversion hole 82 can quickly enter the corresponding liquid separation hole 14, and as much as possible maintain the flow pattern after refrigerant mixing to ensure the distribution uniformity. In addition, in this embodiment, after the refrigerant accelerated by the secondary jet holes 41 enters the re-mixing chamber 104, a high-pressure vortex will be formed on the downstream side of the secondary jet plate 4, and this high-pressure vortex will accelerate the refrigerant to enter the second diversion hole 82.

[0094] Embodiment 4

[0095] This embodiment is basically the same as Embodiment 3 and its variations, the difference being: the structure of the second mixing chamber plate 8 is different, and the secondary jet type liquid separation head further includes an annular flow channel member 9.

[0096] As Figure 18As shown, in this embodiment, the downstream surface of the second mixing chamber plate 8 is close to a plane. The secondary jet type liquid distributor further includes an annular flow channel member 9 disposed in the liquid distribution chamber 105 and located inside the circumference of a plurality of liquid distribution holes 14. The annular flow channel member 9 is a rotating member formed by protruding and extending from the inner bottom wall of the output end 12 of the main body towards the direction of the second mixing chamber plate 8 and rotating around the axis of the liquid distribution main body 1. An annular flow channel communicating with the plurality of liquid distribution holes 14 is defined between the annular flow channel member 9 and the inner peripheral wall of the liquid distribution main body 1, and the cross-section of the annular flow channel member 9 is substantially unchanged or gradually decreases along the extending direction.

[0097] Similar to the second mixing chamber plate 8 at the reflection mixing zone 81 in the third embodiment protruding and extending towards the side where the liquid distribution holes 14 are located, the setting of the annular flow channel member 9 in this embodiment can reduce the volume of the liquid distribution chamber 105 to prevent gas-liquid separation of the mixed homogeneous refrigerant in the liquid distribution chamber 105. At the same time, the annular flow channel defined by the annular flow channel member 9 and the inner peripheral wall of the liquid distribution main body 1 can also guide the homogeneous refrigerant so that it can be evenly distributed into the plurality of liquid distribution holes 14 distributed in a circular symmetry to achieve symmetrical flow splitting of the refrigerant.

[0098] As Figure 18 shown, the annular flow channel member 9 is a cone with a cross-section gradually decreasing along its extending direction. The vertical distance H1 from the extending top end of the annular flow channel member 9 to the downstream surface of the second mixing chamber plate 8 satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the liquid distribution chamber. However, the present utility model makes no limitation thereto. In other embodiments, as Figure 19 shown, the annular flow channel member 9 may also be a cylindrical spacer sleeve with a cross-section substantially unchanged along its extending direction, and the extending top end of the spacer sleeve abuts against the area of the second mixing chamber plate 8 inside the circumference of a plurality of second diversion holes 82. In other embodiments, the annular flow channel member may also be set as a combination of a cone and a spacer sleeve.

[0099] In summary, in the secondary jet type liquid distributor provided by the present utility model, the input pipe injects the refrigerant with an asymmetric flow pattern into the inner cavity of the liquid distributor at a high speed. The high-speed refrigerant is reflected and mixed in the first mixing cavity and gradually develops into a dispersed flow pattern in the first cavity surrounded by the first mixing cavity plate and the inner wall of the input end of the liquid distributor body to achieve the preliminary arrangement of the refrigerant. A partition plate is provided to divide the space between the first mixing cavity plate and the secondary jet plate into a first cavity and a second cavity and control the volume ratio among the volume V1 of the first cavity, the volume V2 of the second cavity, and the volume V3 of the third cavity. This setting precisely controls the degree of volume expansion of the refrigerant when flowing in adjacent cavities to avoid excessive expansion of the refrigerant, providing conditions for the refrigerant after preliminary arrangement to gradually develop into a stable dispersed flow pattern in the first cavity and the second cavity with smaller volumes. The refrigerant after stable development converges at the secondary jet holes on the secondary jet plate, and the secondary jet holes reduce the pressure and increase the speed of the refrigerant, increasing the flow rate of the refrigerant so that it can always maintain the arranged dispersed flow pattern during subsequent distribution, greatly improving the liquid distribution performance of the liquid distributor.

[0100] The secondary jet liquid distributor provided by the present utility model realizes the arrangement of the refrigerant inlet flow pattern by providing a first mixing cavity plate, a partition plate, and a secondary jet plate in the liquid distributor body, reducing the influence of the refrigerant inlet flow pattern on the liquid distribution performance. The liquid distributor with this structure does not require any adjustment on the input pipe, which not only greatly facilitates the processing, installation, and welding of the input pipe, but also greatly improves the applicability of the liquid distributor so that it can be well compatible with various refrigeration devices of different specifications.

[0101] Although the present utility model has been disclosed above with the preferred embodiments, it is not intended to limit the present utility model. Any person skilled in this art can make some modifications and refinements without departing from the spirit and scope of the present utility model. Therefore, the protection scope of the present utility model shall be subject to the scope claimed in the claims.

Claims

1. A secondary jet type liquid distributor, characterized in that, Comprising: A liquid separation body, with an input pipe assembly hole and a plurality of liquid separation holes formed at both axial ends thereof; An input pipe, connected to the input pipe assembly hole to inject refrigerant into the liquid separation body; A first mixing cavity plate, disposed in the inner cavity of the liquid separation body. At a position on the first mixing cavity plate opposite to the input pipe assembly hole, it protrudes and extends towards the side where the liquid separation holes are located to form a first mixing cavity with an opening facing the input pipe assembly hole. On the first mixing cavity plate, there are also formed a plurality of first diversion holes that are located on the outer periphery of the first mixing cavity when projected along the axial direction of the liquid separation body. The plane where the upstream surface of the first mixing cavity plate near the first diversion holes is located and the inner wall of the input end of the liquid separation body enclose a first chamber; A partition plate, located on the downstream side of the first mixing cavity plate. The partition plate and the first mixing cavity plate enclose a second chamber that surrounds the first mixing cavity and is annular. A plurality of partition holes communicating with the second chamber are formed on the partition plate; A secondary jet plate, located on the downstream side of the partition plate and having a secondary jet hole. A third chamber is formed based on the secondary jet plate and the partition plate. The volumes V1 of the first chamber, V2 of the second chamber, and V3 of the third chamber satisfy: 0.6 ≤ V1 / V2 ≤ 1.4, 0.6 ≤ V2 / V3 ≤ 1.

4.

2. The secondary jet type liquid distributor according to claim 1, characterized in that A relief hole is formed on the partition plate. The partition plate is sleeved on the outer periphery of the first mixing cavity through the relief hole. The third chamber is enclosed by the downstream surface of the partition plate, the outer bottom wall of the first mixing cavity, and the upstream surface of the secondary jet plate; Alternatively, the position on the partition plate opposite to the first mixing cavity is of a closed structure, and the partition plate is basically attached to the outer bottom wall of the first mixing cavity.

3. The secondary jet type liquid distributor according to claim 1, characterized in that, The plurality of partition holes and the plurality of first diversion holes on the first mixing cavity plate are staggeredly distributed. The sum of the flow - through areas S1 of the plurality of partition holes and the cross - sectional area S01 of the inner cavity of the liquid separation body where the partition plate is located satisfy: 0.1 ≤ S1 / S01 ≤ 0.

45.

4. The secondary jet type liquid distributor according to claim 1, characterized in that, Both the first diversion holes and the partition holes are one or a combination of through - holes, flanged holes, and arc - bubble holes; The secondary jet hole is a through - hole or a flanged hole with a hole wall extending towards the output end of the liquid separation body.

5. The secondary jet type liquid distributor according to claim 1, characterized in that, The secondary jet type liquid separation head further includes a second mixing cavity plate. The second mixing cavity plate is located on the downstream side of the secondary jet plate and encloses a re - mixing cavity therebetween. The second mixing cavity plate and the inner wall of the output end of the body enclose a liquid separation cavity communicating with the plurality of liquid separation holes. The second mixing cavity plate is formed with a reflection mixing area and a plurality of second diversion holes. The reflection mixing area is distributed opposite to the secondary jet hole. The plurality of second diversion holes correspond to the plurality of liquid separation holes one by one and are annularly distributed around the axis of the liquid separation body on the plane of the second mixing cavity plate on the outer periphery of the reflection mixing area.

6. The secondary jet-type liquid distributor according to claim 5, characterized in that, The second mixing cavity plate at the reflection mixing area protrudes and extends towards the side where the liquid separation holes are located. The reflection mixing area becomes a second mixing cavity with an opening facing the secondary jet hole. Both the first mixing cavity and the second mixing cavity are of a combination of one or more of a square, trapezoid, triangle, or partial circle in the longitudinal section profile.

7. The secondary jet type liquid distributor according to claim 5, characterized in that, The downstream surface of the second mixing cavity plate is close to a plane. The secondary jet type liquid distributor further includes an annular flow channel member disposed in the liquid distribution cavity and located on the inner periphery of a plurality of liquid distribution holes. The annular flow channel member is a rotary member formed by protruding and extending from the inner bottom wall of the output end of the body towards the direction of the second mixing cavity plate and rotating around the axis of the liquid distribution body. An annular flow channel communicating with a plurality of liquid distribution holes is defined between the annular flow channel member and the inner peripheral wall of the body, and the cross-section of the annular flow channel member is substantially unchanged or gradually decreases along the extending direction.

8. The secondary jet type liquid distributor according to claim 7, wherein, The annular flow channel member is a spacer sleeve with a cross-section that is substantially unchanged along its extending direction, and the extending top end of the spacer sleeve abuts against the reflection mixing area on the second mixing cavity plate.

9. The secondary jet type liquid distributor according to claim 7, wherein The cross-section of the annular flow channel member gradually decreases along its extending direction, and the vertical distance H1 from the extending top end of the annular flow channel member to the downstream surface of the second mixing cavity plate satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the liquid distribution cavity.

10. The secondary jet type liquid distributor according to claim 1, characterized in that, The secondary jet type liquid distributor further includes a flow splitting and guiding member located on the downstream side of the secondary jet plate. The flow splitting and guiding member protrudes and extends from the inner bottom wall of the output end of the body towards the direction of the secondary jet plate. The longitudinal section of the flow splitting and guiding member is triangular in shape and its extending top end is opposite to the secondary jet hole.

11. The secondary jet type liquid distributor according to claim 1, wherein, The minimum inner diameter of the primary jet portion on the input pipe is greater than or equal to the minimum inner diameter of the secondary jet hole.

12. The secondary jet type liquid distributor according to claim 1, wherein, The input pipe includes a main body section and a jet section sequentially distributed along the refrigerant flow direction. The inner diameter of the main body section is substantially unchanged, and a primary jet pipe hole with a reduced inner diameter relative to the main body section is formed on the jet section.

13. The secondary jet type liquid distributor according to claim 12, wherein, A jet plate is disposed in the input pipe, and a primary jet pipe hole with an inner diameter smaller than the inner diameter of the main body section is formed on the jet plate. The input pipe section where the jet plate is located forms the jet section; Alternatively, the jet section is a Venturi pipe section, and the throat of the Venturi pipe section forms the primary jet pipe hole; Alternatively, the jet section is a straight pipe section with a reduced inner diameter relative to the main body section.

14. The secondary jet type liquid distributor according to claim 1, characterized in that, The secondary jet type liquid distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of liquid distribution holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1 mm ≤ △d ≤ 3.5 mm.

15. The secondary jet type liquid distributor according to claim 14, characterized in that, A reflection section that bends and extends towards one side of the central line of the liquid distribution hole is formed on the first pipe section. An included angle θ is formed between the axis at the upstream end of the reflection section and the axis at the downstream end of the reflection section, and 90° ≤ θ ≤ 175°. Based on the reflection section, the axis of the second pipe section intersects the central line of the liquid distribution hole; Alternatively, the first pipe section is a straight pipe.

16. The secondary jet type liquid distributor according to claim 14, characterized in that, Each branch pipe also includes a branch section. The second pipe section is a tapered structure integrally formed with the first pipe section and having a gradually decreasing inner diameter. The branch section is welded and connected to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed; Alternatively, the branch section is socket-welded to the first pipe section, and the socket-welding portion of the two forms the second pipe section; Alternatively, the branch section is socket-welded to the first pipe section, and the second pipe section is formed on the branch section.

17. A heat exchanger assembly, characterized in that, Including the secondary jet type liquid distributor according to any one of claims 1 to 16.

18. An air conditioner, characterized in that, Comprising the heat exchanger assembly according to claim 17.

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