Partition plate type distributor, heat exchanger assembly and refrigeration equipment

Abstract

The utility model provides a partition plate type distributor, a heat exchanger assembly and refrigeration equipment. The partition plate type distributor comprises a body, partition plates and runner forming pieces. A liquid inlet pipe assembly hole, a plurality of liquid outlet holes and a containing cavity communicated with the liquid inlet pipe assembly hole and the liquid outlet holes are formed in the body. The partition plate is arranged in the containing cavity of the body to divide the containing cavity into a first cavity body and a second cavity body, a plurality of partition plate holes communicated with the first cavity body and the second cavity body are formed in the partition plate, and the multiple partition plate holes are annularly distributed around the axis of the body in the periphery of the projection area of the liquid inlet pipe assembly hole in the partition plate. The flow channel forming piece is arranged in the second cavity and located on the inner periphery of the multiple liquid outlet holes, the flow channel forming piece is a rotating piece which is formed by protruding and extending from the inner bottom wall of the liquid outlet end of the body to the direction where the partition plate is located and rotating around the axis of the body, and an annular flow channel communicating with the partition plate hole and the multiple liquid outlet holes is defined between the flow channel forming piece and the inner wall of the second cavity; and the cross section of the flow channel forming piece is basically unchanged or gradually reduced along the extension direction of the flow channel forming piece.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigerant distribution, and particularly to a partition type distributor, a heat exchanger assembly and a refrigeration device. Background Art

[0002] In a refrigeration system, a distributor is a device connected between the outlet end of a thermostatic expansion valve and a multi-branch evaporator, and is used to evenly distribute the refrigerant throttled by the thermostatic expansion valve into multiple branches of the evaporator. A distributor with excellent performance can effectively improve the performance of the evaporator, but the deterioration of its performance will also seriously affect the performance of the evaporator. Some literature shows that the negative impact brought by the deterioration of the distributor performance will far outweigh the positive impact brought by increasing the heat exchanger process.

[0003] The socket type distributor is widely used in existing refrigeration systems due to its simple structure and low cost. However, due to the enlarged mixing chamber of the socket type distributor, the velocity of the two-phase refrigerant decreases after entering the enlarged mixing chamber through the liquid inlet pipe. The inertial force of the liquid-phase refrigerant is not enough to overcome the gravity it receives, and the gas-liquid two-phase gradually separates. Part of the liquid refrigerant flows back along the inner wall of the distributor body to the bottom of the mixing chamber and is difficult to be distributed to the liquid outlet side, thus seriously affecting the refrigerant distribution uniformity. At the same time, this is also the main reason why the socket type distributor is most seriously affected by the installation angle.

[0004] To improve the distribution performance of the socket type distributor, someone proposed to add a screen type mixing partition or a separator with a nozzle in the mixing chamber, hoping that the refrigerant flowing in from the liquid inlet pipe can be mixed once in the cavity near the liquid inlet side under the barrier of the mixing partition, and the pressure on the liquid inlet side can be increased to enable the refrigerant to pass through the mixing partition evenly and quickly and enter the liquid outlet side cavity for secondary mixing. However, since some of the screen holes on the partition are directly opposite to the liquid inlet pipe (or the nozzle is directly opposite to the liquid inlet pipe), the refrigerant flowing in from the liquid inlet pipe passes directly through the opposite screen holes or nozzles and flows directly into the liquid outlet side cavity before being fully mixed; obviously, this optimization scheme is difficult to effectively improve the performance of the distributor. In this structure, when the refrigerant enters the larger cavity on the liquid outlet side through the screen type mixing partition or the separator with a nozzle, the gas-liquid two-phase separation caused by the volume expansion of the refrigerant will also occur, further deteriorating the distribution performance. In addition, the very small aperture screen holes and nozzles will inevitably hinder the passage of the refrigerant, resulting in too large a pressure loss of the refrigerant, and the too large pressure loss will cause the average evaporation temperature of the evaporator to be low, reducing the operating efficiency of the system. Summary of the Utility Model

[0005] The utility model aims to overcome the deficiencies of the prior art and provides a partition type distributor, a heat exchanger assembly and a refrigeration device.

[0006] To achieve the above object, the present utility model provides a partition type distributor, which includes a body, a partition board, and a flow channel forming member. Liquid inlet pipe assembly holes and a plurality of liquid outlet holes are respectively formed at two axial ends of the body, and a receiving cavity communicating the liquid inlet pipe assembly holes and the plurality of liquid outlet holes is formed inside the body. The partition board is disposed in the receiving cavity of the body to divide the receiving cavity into a first cavity and a second cavity. A plurality of partition holes communicating the first cavity and the second cavity are formed on the partition board, and the plurality of partition holes are annularly distributed around the axis of the body on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition board. The flow channel forming member is disposed in the second cavity and on the inner periphery of the plurality of liquid outlet holes. The flow channel forming member is a rotating member formed by protruding and extending from the inner bottom wall of the liquid outlet end of the body towards the direction of the partition board and rotating around the axis of the body. An annular flow channel communicating the partition holes and the plurality of liquid outlet holes is enclosed between the flow channel forming member and the inner wall of the second cavity, and the cross-section of the flow channel forming member is substantially unchanged or gradually decreases along its extending direction.

[0007] In an embodiment provided by the present utility model, the flow channel forming member is a spacer sleeve with a cross-section that is substantially unchanged along its extending direction, and the upper end of the spacer sleeve abuts against the partition area on the inner periphery of the plurality of partition holes.

[0008] In an embodiment provided by the present utility model, the radial distance L from the outer wall of the spacer sleeve to the inner edge of the liquid outlet hole satisfies: L ≤ 4 mm; the inner edge of the liquid outlet hole refers to: on the liquid outlet end of the body where the plurality of liquid outlet holes are located, the intersection of the connection line between the center of the liquid outlet hole and the center of the body and the edge of the liquid outlet hole.

[0009] In an embodiment provided by the present utility model, the cross-section of the flow channel forming member gradually decreases along its extending direction, and the vertical distance H1 from the extending top end of the flow channel forming member to the downstream surface of the partition board satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the second cavity.

[0010] In an embodiment provided by the present utility model, the extending top end of the flow channel forming member is a flat surface; or, the extending top end of the flow channel forming member is an arc-shaped curved surface and the radius of curvature R of the arc-shaped curved surface satisfies: 0.5 mm ≤ R ≤ 5 mm.

[0011] In an embodiment provided by the present utility model, on the longitudinal section of the flow channel forming member passing through the axis of the body, the included angle γ formed by the extended lines of the two side generatrices of the flow channel forming member satisfies: 20° ≤ γ ≤ 115°.

[0012] In an embodiment provided by the present utility model, the plurality of partition holes are equally spaced and distributed on the partition board in the form of an annular row. The number of partition holes is the same as the number of liquid outlet holes and each partition hole is substantially coaxial with the corresponding liquid outlet hole.

[0013] In an embodiment provided by the present utility model, a plurality of partition holes are distributed on the partition in the form of a plurality of annular columns, and the same number of partition holes are evenly spaced on each annular column.

[0014] In an embodiment provided by the present utility model, the partition holes are circular through holes or waist-shaped through holes;

[0015] Alternatively, the aperture of the partition hole gradually decreases in the direction pointing to the liquid outlet hole, and the generatrix of the inner wall of the partition hole is linear or arc-shaped;

[0016] Alternatively, the partition hole is an arc bubble hole with the hole wall convexly curved towards one or both sides of the partition.

[0017] In an embodiment provided by the present utility model, the partition is a flat plate structure with both side surfaces substantially close to a plane;

[0018] Alternatively, the projection area of the liquid inlet pipe assembly hole on the partition bulges towards the side where the liquid inlet pipe assembly hole is located, and the shape of the longitudinal section contour line of the bulge is one or a combination of a square, a trapezoid, a triangle, or a partial circle;

[0019] Alternatively, the projection area of the liquid inlet pipe assembly hole on the partition bulges towards the side where the liquid outlet hole is located to form a concave cavity with an opening facing the liquid inlet pipe assembly hole, and the longitudinal section contour line of the concave cavity is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

[0020] In an embodiment provided by the present utility model, the ratio of the aperture D1 of the downstream end of the partition hole to the outer diameter D2 of the branch pipe inserted into the liquid outlet hole is 0.8 - 1.2.

[0021] In an embodiment provided by the present utility model, the partition type distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of liquid outlet holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having an inner diameter reduced 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: 0.1mm ≤ △d ≤ 3.5mm.

[0022] In an embodiment provided by the present utility model, a reflection section is formed on the first pipe section and bends and extends towards one side relative to the center line of the liquid outlet 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 center line of the liquid outlet hole;

[0023] Alternatively, the first pipe section is a straight pipe.

[0024] In an embodiment provided by 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 to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed;

[0025] Alternatively, the branch section is socket-welded to the first pipe section, and the socket-welded portion of the two forms the second pipe section;

[0026] Alternatively, the branch section is socket-welded to the first pipe section, and the second pipe section is formed on the branch section.

[0027] On the other hand, the present utility model further provides a heat exchanger assembly, which includes any one of the above-mentioned partition distributors.

[0028] On the other hand, the present utility model further provides a refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0029] In summary, the partition distributor provided by the present utility model divides the internal accommodating cavity of the body into a first cavity and a second cavity through a partition to reduce the volume of each cavity in the body, providing a mixing space for the input refrigerant while avoiding excessive expansion of the refrigerant due to too large a cavity. By arranging a plurality of partition holes on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition, the projection area of the liquid inlet pipe assembly hole on the partition can block the input refrigerant and reflect it back into the first cavity, enhancing the mixing degree of the two-phase refrigerant to improve the distribution uniformity. At the same time, the staggered distribution of the partition holes and the liquid inlet pipe assembly holes also effectively prevents the refrigerant from directly passing through to the second cavity before being mixed, providing conditions for the refrigerant to be fully mixed in the first cavity. The flow channel forming member maintains the flow rate of the mixed refrigerant by reducing the volume of the second cavity, ensuring that the mixed refrigerant has sufficient inertial force in the second cavity to overcome the influence of gravity and avoiding gas-liquid two-phase segregation of the mixed refrigerant again. At the same time, the annular flow channel formed by the flow channel forming member and the inner wall of the second cavity also guides the fully mixed homogeneous refrigerant so that it can be evenly distributed into a plurality of liquid outlet holes.

[0030] 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

[0031] Figure 1 The structure diagram of the existing socket-type distributor is shown.

[0032] Figure 2 The structure diagram of the partition distributor provided in the first embodiment of the present utility model is shown.

[0033] Figure 2A Shown as Figure 2Schematic diagram of the structure after removing the liquid inlet pipe and the branch pipe.

[0034] Figure 3 As shown is Figure 2 Schematic diagram of the structure of the middle partition board.

[0035] Figure 4 Schematic diagram of the structure of the partition - type distributor provided by another embodiment of the present utility model.

[0036] Figures 5A to 5E Schematic diagram of the structure of the middle partition board in the partition - type distributor provided by another embodiment of the present utility model.

[0037] Figure 6 As shown is Figure 2 Schematic diagram of the structure of the flow - channel forming member.

[0038] Figure 7 As shown is Figure 2 Schematic diagram of the projection of the flow - channel forming member on the inner bottom wall of the liquid outlet end of the body.

[0039] Figure 8A and Figure 8B Schematic diagram of the structure of the middle partition board in the partition - type distributor provided by another embodiment of the present utility model.

[0040] Figure 9 As shown is Figure 2 Schematic diagram of the structure of the branch pipe.

[0041] Figure 10A 、 Figure 10B 、 Figure 10C 、 Figure 10D 、 Figure 10E 、 Figure 10F and Figure 10G Schematic diagram of the structure of the branch pipe in the partition - type distributor provided by another embodiment of the present utility model.

[0042] Figure 11 Schematic diagram of the structure of the partition - type distributor provided by Embodiment II of the present utility model.

[0043] Figure 12 Schematic diagram of the structure of the middle partition board in the partition - type distributor provided by another embodiment of the present utility model.

[0044] Figure 13 and Figure 14 Schematic diagram of the structure of the partition - type distributor provided by another embodiment of the present utility model.

[0045] Figure 15 Schematic diagram of the structure of the partition - type distributor provided by Embodiment III of the present utility model.

[0046] Figure 16The figure shows a schematic structural diagram of a partition in a partition-type distributor provided by another embodiment of the present utility model. Detailed implementation manners

[0047] 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 distributor is generally installed vertically or obliquely, and the liquid inlet end of the distributor is located below the liquid outlet end along the direction of gravity. The inertial force of the refrigerant in the distributor overcomes gravity and flows in the direction opposite to gravity; at this time, the upstream and downstream are still divided according to the flow direction of the refrigerant.

[0048] Embodiment 1

[0049] As Figure 1 shown, in a traditional jack-type distributor, when the refrigerant enters the inner cavity of the distributor for diffusion and mixing, the flow rate of the refrigerant drops suddenly. The liquid-phase refrigerant is easily separated from the gas-phase refrigerant under the action of gravity and deposited at the bottom of the mixing cavity, which seriously affects the distribution uniformity. In a distributor with a sieve-hole type (or nozzle type) partition, since the refrigerant directly passes through to the liquid outlet side without sufficient mixing, it is difficult to effectively improve the distribution performance. In addition, this structure will also bring other problems such as excessive refrigerant pressure loss and noise. In view of this, this embodiment provides a partition-type distributor with excellent shunt uniformity.

[0050] As Figure 1 shown, the partition-type distributor provided in this embodiment includes a body 1, a partition 2, and a flow channel forming member 3. At both axial ends of the body 1 (including the liquid inlet end 101 and the liquid outlet end 102), a liquid inlet pipe assembly hole 11 and a plurality of liquid outlet holes 12 are respectively formed. An accommodation cavity 103 communicating the liquid inlet pipe assembly hole 11 and the plurality of liquid outlet holes 12 is formed inside the body 1. The partition 3 is arranged in the accommodation cavity 103 of the body to divide the accommodation cavity 103 into a first cavity 1031 and a second cavity 1032. A plurality of partition holes 21 communicating the first cavity 1031 and the second cavity 1032 are formed on the partition 2, and the plurality of partition holes 21 are annularly distributed around the axis of the body 1 on the outer periphery of the projection area of the liquid inlet pipe assembly hole 11 on the partition 2. The flow channel forming member 3 is arranged in the second cavity 1032 and located inside the plurality of liquid outlet holes 12. The flow channel forming member 3 is a rotary member formed by protruding and extending from the inner bottom wall of the liquid outlet end 102 of the body towards the direction where the partition 2 is located and rotating around the axis of the body 1. An annular flow channel communicating the partition holes 21 and the plurality of liquid outlet holes 12 is enclosed between the flow channel forming member 3 and the inner wall of the second cavity 1032, and the cross-section of the flow channel forming member 3 is basically unchanged or gradually decreases along its extending direction.

[0051] In the baffle-type distributor provided in this embodiment, the baffle 2 divides the accommodation cavity 103 in the body 1 into a first cavity 1031 and a second cavity 1032, reducing the chamber volume after the refrigerant enters the body 1 to control the volume change rate of the refrigerant. While providing space for the full mixing of the two-phase flow, the refrigerant flow rate is maintained to ensure that the liquid-phase refrigerant has sufficient inertial force to overcome the gravity it receives, avoiding gas-liquid segregation after the refrigerant enters the body 1. On this basis, the baffle hole 21 is arranged on the outer periphery of the projection area of the liquid inlet pipe assembly hole 11 on the baffle 2, that is, the liquid inlet pipe assembly hole 11 and the baffle hole 21 are misaligned. This setting enables the high-speed refrigerant input into the body 1 not to directly pass through to the second cavity 1032 for direct distribution, but to be reflected back to the first cavity 1031 by the baffle reflection area 22 formed by the projection area of the liquid inlet pipe assembly hole 11 on the baffle 2. While the baffle reflection area 22 reflects the input refrigerant, it breaks up the liquid-phase refrigerant into droplets to promote gas-liquid mixing; at the same time, the reflected refrigerant flow beam and the incident flow beam form a turbulent flow in the first cavity 1031, enhancing the degree of disorder of the two-phase flow. The misaligned liquid inlet pipe assembly hole 11 and baffle hole 21 enable the input refrigerant to be fully mixed into a dispersed flow pattern in the first cavity 1031 and then distributed to the second cavity 1032, providing a basis for the uniform distribution of the refrigerant.

[0052] Furthermore, to achieve precise control of the volume in the first cavity 1031, the inner wall of the liquid inlet end 101 of the body can also be inclined and extended towards the liquid outlet end 102 of the body, and its inner wall generatrix is an arc or an inclined straight line. The connecting line between the projection position A of the outer edge of the downstream end of the baffle hole 21 on the inner wall of the liquid inlet end 101 along the axial direction of the body 1 and the center O of the downstream end of the liquid inlet pipe assembly hole 11 forms an angle α with the radial direction of the baffle 2, and 8° ≤ α ≤ 17°. The axial distance H from the baffle surface where the upstream end of the baffle hole 21 is located to the projection position A satisfies: 1 mm ≤ H ≤ 5 mm. The outer edge of the downstream end of the baffle hole 21 refers to the edge of the downstream end of the baffle hole 21 that is farthest from the center line of the body 1. The inner wall of the liquid inlet end 101 of the body is inclined and extended towards the liquid outlet end 102 of the body so that the inner wall of the liquid inlet end 101 forms a secondary reflection surface, reflecting the refrigerant after being reflected and mixed in the baffle reflection area 22 into multiple baffle holes 21 to improve the mixing degree of the two-phase refrigerant. The setting of the angle α related to the projection position A realizes the control of the secondary reflection stroke from the baffle 2 to the inner wall of the liquid inlet end 101 of the body, ensuring that the refrigerant reflected by the baffle reflection area 22 can be incident on the inner wall of the liquid inlet end 101 of the body again for secondary reflection. The axial distance H related to the projection position A determines the spatial position of the baffle hole 21 so that it is located on the outgoing path of the secondary reflection.

[0053] After sufficient mixing, the refrigerant enters the second cavity 1032 through multiple partition holes 21. When the refrigerant flows through the partition holes 21, its flow velocity increases. The liquid-phase mass flow rate increases with the increase of the liquid-phase flow velocity, and the liquid film becomes thinner, causing the liquid droplets to atomize into smaller forms to further promote the gas-liquid two-phase mixing. At the same time, the increase in the refrigerant flow velocity also gives the liquid refrigerant a greater inertial force to maintain the flow pattern of the uniformly mixed refrigerant. To avoid gas-liquid two-phase segregation of the refrigerant before distribution, the partition distributor provided in this embodiment further adds a flow channel forming member 3 in the second cavity 1032. Based on the flow channel forming member 3, an annular flow channel is constructed in the second cavity 1032 to achieve uniform distribution of the refrigerant. At the same time, the flow channel forming member 3 is used to reduce the volume of the second cavity 1032 to avoid the gas-liquid two-phase segregation problem caused by excessive expansion of the refrigerant.

[0054] In the partition distributor provided in this embodiment, the settings of the partition 2, the partition holes 21, and the flow channel forming member 3 enable the refrigeration energy input into the main body 1 to be fully mixed into a dispersed flow pattern in the first cavity 1031, and this flow pattern can be maintained all the time when entering the second cavity 1032 for distribution, thereby greatly improving the distribution performance of the distributor.

[0055] In this embodiment, as Figure 2 , Figure 2A and Figure 3 shown, the partition reflection area 22 opposite to the liquid inlet pipe assembly hole 11 protrudes and extends towards the liquid outlet end 102 of the main body to form a concave cavity 220 with an opening facing the liquid inlet pipe assembly hole 11. The concave cavity 220 provides a mixing space for the refrigerant during the maximum kinetic energy stage 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 concave cavity 220 can also effectively reduce the influence of the reflection force on the input refrigerant, avoiding the refrigerant in the liquid inlet pipe from flowing back due to excessive reflection force. In this embodiment, the concave cavity 220 is a cylindrical cavity with a square cross-sectional contour line, and the outer bottom surface of the concave cavity 220 abuts against the inner bottom wall of the liquid outlet end 102 of the main body. However, the present utility model makes no limitation thereto. In other embodiments, it is also possible to set that the outer bottom surface of the concave cavity 220 does not abut against the inner bottom wall of the liquid outlet end 102 of the main body, as Figure 4 shown.

[0056] In addition, regarding the shape of the concave cavity, in other embodiments, the concave cavity 220 can also be set as a prism with a square cross-sectional contour line, a frustum of a cone or a prism with a trapezoidal cross-sectional contour line (as Figure 5A shown), a cone or a pyramid with a triangular cross-sectional contour line (as Figure 5B shown), and a partial circular cross-sectional contour line (as Figure 5C shown), or a combination of one or more of them; such as a combination of a cylinder and a partial sphere (as Figure 5Das shown), a combination of a frustum of a cone and a partial sphere (such as Figure 5E ), a combination of a prism and a partial sphere, etc.

[0057] In this embodiment, as Figure 2 and Figure 6 shown, the flow channel forming member 3 is a hollow spacer sleeve with a substantially constant cross-section along its extending direction. The spacer sleeve is sleeved outside the cavity 220 formed by the protrusion of the partition reflection area 22, and its upper end abuts against the partition area on the inner circumference of the plurality of partition holes 21; that is, when projected along the axial direction of the body 1, the spacer sleeve serving as the flow channel forming member 3 is located between the cavity 220 and the plurality of partition holes 21. An annular flow channel communicating the plurality of partition holes 21 and the plurality of liquid outlet holes 12 is defined between the spacer sleeve and the inner peripheral wall of the second cavity 1032, reducing the cross-sectional area of the flow channel between the plurality of partition holes 21 and the plurality of liquid outlet holes 12 in the radial direction, controlling the volume change rate and the flow rate of the refrigerant in the second cavity 1032, and ensuring that the refrigerant can maintain a dispersed flow after mixing to be evenly distributed into the plurality of liquid outlet holes 12. Further, the radial distance L from the outer wall of the spacer sleeve to the inner edge of the liquid outlet hole 12 can be controlled to accurately control the volume ratio between the annular flow channel and the first cavity 1031, and further achieve accurate control of the refrigerant flow rate in the annular flow channel. As Figure 7 shown, the inner edge of the liquid outlet hole 12 refers to: at the liquid outlet end 102 of the body, the intersection of the connection line between the center of the liquid outlet hole 12 and the center of the body 1 (such as Figure 7 the dotted line in) and the edge of the liquid outlet hole 12, that is Figure 7 the position B in; Figure 7 in, the area formed by the dotted line is the projection of the flow channel forming member 3 on the liquid outlet end 102 of the body. Preferably, the radial distance L is set to satisfy: 0 ≤ L ≤ 4 mm, such as equidistant values of 0.5 mm, 1 mm, 1.5 mm, 2 mm, 2.5 mm, 3 mm, 3.5 mm, etc. When the radial distance L is 0, the outer wall of the spacer sleeve just tangentially contacts the inner edge of the liquid outlet hole 12. However, the present utility model does not make any limitation thereto.

[0058] In the partition type distributor provided in this embodiment, during the process that the refrigerant enters the second cavity 1032 through the plurality of partition holes 21 and is distributed to the plurality of liquid outlet holes 12, some of the refrigerant will inevitably impact on the inner bottom wall of the liquid outlet end 102 of the body and flow back along the inner wall of the second cavity 1032 and the outer wall of the flow channel forming member 3. The reflux of the refrigerant will generate an eddy current area near the liquid outlet hole 12, and the existence of the eddy current area will squeeze the refrigerant flow channel at the entrance of the liquid outlet hole 12, hindering the inflow of the refrigerant and affecting the performance of the distributor. In this embodiment, the setting of the radial distance L also reduces the reflection area of the inner bottom wall of the liquid outlet end 102 of the body on the refrigerant, thereby reducing the action range of the eddy current area and weakening its extrusion on the refrigerant distribution flow channel, improving the uniformity of refrigerant distribution while reducing the distribution resistance.

[0059] In this embodiment, a plurality of partition holes 21 are annularly distributed at equal intervals on the plane of the partition 2 outside the partition reflection area 22. The number of partition holes 21 is the same as the number of liquid outlet holes 12, and each partition hole 21 is substantially coaxial with the corresponding liquid outlet hole 12. This setting enables the formation of the shortest axial transmission path between the partition hole 21 and the corresponding liquid outlet hole 12, and the high-speed refrigerant output from the partition hole 21 can quickly enter the corresponding liquid outlet hole 12, and the flow pattern after the refrigerant is mixed is maintained as much as possible to achieve the uniform distribution of the refrigerant.

[0060] Although this embodiment is described by taking the number of partition holes 21 being the same as the number of liquid outlet holes 12 and the two being coaxially arranged as an example. However, the present invention does not make any limitation in this regard. In other embodiments, the number of partition holes may also be twice or three times the number of liquid outlet holes, and two or three partition holes form a group to correspond to the corresponding liquid outlet holes one by one. In the refrigerant uniform flow distributor provided in this embodiment, the number of partition holes 21 is limited and their aperture diameters are relatively large; preferably, the ratio of the aperture diameter D1 of the downstream end of the partition hole 21 to the outer diameter D2 of the branch pipe 4 inserted into the liquid outlet hole 12 is 0.8 to 1.2. The relatively large aperture diameter of the partition hole 21 is not only more conducive to the passage of the refrigerant but also can effectively reduce the pressure loss of the refrigerant during the distribution process. Specifically, the ratio of the aperture diameter D1 of the downstream end of the partition hole 21 to the outer diameter D2 of the branch pipe 3 inserted into the liquid outlet hole 12 can be set to ratios such as 0.85, 0.9, 0.95, 1.0, 1.05, 1.1, 1.15, etc. However, the present invention does not make any limitation in this regard. In other embodiments, D1 / D2 may also be other ratios within 0.8 to 1.2.

[0061] In this embodiment, as Figure 2 and Figure 3 shown, the partition hole 21 is a flanging hole with an arc-shaped inner wall generatrix and its aperture diameter gradually decreasing along the flow direction of the refrigerant. The gradual reduction of the inner diameter of the partition hole 21 can accelerate the refrigerant flowing through, increase the refrigerant flow rate so that it can quickly enter the corresponding liquid outlet hole 12; in addition, the acceleration of the partition hole 21 can also further promote the mixing of the gas-liquid two-phase refrigerant. However, the present invention does not make any limitation in this regard either. In other embodiments, the partition hole 21 can be set as an arc bubble hole with the hole wall arcuately protruding towards one side or both sides of the partition 2, as Figure 5A and Figure 5D shown.

[0062] Or, as Figure 5B and Figure 5C shown, the partition hole 21 is set as a converging hole with an inclined straight inner wall generatrix and its aperture diameter gradually decreasing along the flow direction of the refrigerant. In Figure 5CAmong them, the partition plate 2 includes a partition plate body 2A and a lining plate 2B stacked on the partition plate body 2A. A plurality of partition plate through holes are formed on the partition plate body 2A, and a plurality of lining plate holes corresponding to the plurality of partition plate through holes are formed on the lining plate 2B. The aperture of the lining plate holes gradually decreases along the flowing direction of the refrigerant. The lining plate holes and the corresponding partition plate through holes together form the partition plate holes 21. In Figure 5C Among them, the partition plate 2 includes a plurality of partition plate lining plates 2B stacked in the area near the partition plate through holes and having an area smaller than that of the partition plate body 2A. However, the present invention does not make any limitation thereto. In other embodiments, the lining plate may also be an integral piece.

[0063] Alternatively, the partition plate holes 21 are provided as through holes with substantially the same aperture along the flowing direction of the refrigerant, and the shape of the through holes is circular (as Figure 5E shown), oval (as Figure 8A shown) or waist-shaped (as Figure 8B shown), or any combination thereof.

[0064] In the partition type distributor provided in this embodiment, the refrigerant input into the body 1 is fully mixed in the first cavity 1031 and then enters the second cavity 1032 through a plurality of partition plate holes 21. Then it is evenly distributed to a plurality of liquid outlet holes 12 through the annular flow channel and then enters a plurality of branch pipes 4. As Figure 9 shown, each branch pipe 4 includes a first pipe section 41 and a second pipe section 42 located downstream of the first pipe section 41 and having an inner diameter reduced relative to the inner diameter at the downstream end of the first pipe section 41. The difference △d between the inner diameter d11 at the downstream end of the first pipe section 41 and the inner diameter d12 at the downstream end of the second pipe section 42 is: 0.1mm ≤ △d ≤ 3.5mm. The first pipe section 41 with a larger inner diameter increases the refrigerant flow rate distributed into each branch pipe 4 and reduces the distribution resistance of the refrigerant, while the second pipe section 42 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 pressure reduction and speed increase degree of the second pipe section 42 on the refrigerant, avoiding excessive pressure loss of the refrigerant due to excessive speed increase.

[0065] Furthermore, a reflection section 411 that bends and extends towards one side of the center line of the liquid outlet hole 12 is formed on the first pipe section 41. An included angle θ is formed between the axis at the upstream end of the reflection section 411 and the axis at the downstream end of the reflection section 411, and 90° ≤ θ ≤ 175°. The setting of the reflection section 411 makes the second pipe section 42 no longer coaxial with the center line of the liquid outlet hole. When there is a pressure wave downstream and it oscillates upstream, the reflection section 411 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 outlet hole 12 to further improve the distribution performance.

[0066] In this embodiment, the branch pipe 4 further includes a branch section 43 welded to the first pipe section 41, and the second pipe section 42 is located on the branch section 43. Specifically, as Figure 9 shown, the upstream end of the branch section 43 is sleeved and connected to the downstream end of the first pipe section 41, and a second pipe section 42 with a gradually decreasing inner diameter is formed downstream of the socket joint of the branch section 43. However, the present utility model does not make any limitation thereto. In other embodiments, the upstream end of the branch section 43 can also be internally sleeved and welded to the downstream end of the first pipe section 41; at this time, the second pipe section 42 is still a structure with a gradually decreasing inner diameter located downstream of the socket joint of the branch section 43, as Figure 10A shown.

[0067] Figure 10B 、 Figure 10C and Figure 10D are schematic structural diagrams of the branch pipe provided in another embodiment of the present utility model. Figure 10B In it, the first pipe section 41, the second pipe section 42 and the branch section 43 are integrally formed; Figure 10C In it, the first pipe section 41 and the second pipe section 42 are integrally formed, and the branch section 43 is welded to the end of the second pipe section 42. Figure 10D In it, based on the inner diameter difference between the downstream end of the first pipe section 41 and the upstream end of the branch section 43, the second pipe section 42 is directly formed at the socket joint of the first pipe section 41 and the branch section 43. In addition, multiple second pipe sections can also be provided at the downstream end of the first pipe section, and the branch section 43 can be set as a straight pipe or a bent pipe according to actual applications.

[0068] Although this embodiment is described by taking the reflection section 411 formed on the first pipe section 41 as an example. However, the present utility model does not make any limitation thereto. In other embodiments, the reflection section may not be provided on the first pipe section 41. At this time, the first pipe section 41 is a straight pipe, as Figure 10E shown.

[0069] Furthermore, for the structure of the second pipe section 42, in other embodiments, the second pipe section 42 can also be set to include a tapered section and a maintaining straight section located downstream of the tapered section and having a certain length L42. 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 L42, as Figure 10F shown. Or, an orifice plate 44 is added at the flared joint of the first pipe section 41 or the branch section 43, and the refrigerant is accelerated by using the through holes 441 on the orifice plate 44; at this time, the pipe section where the orifice plate 44 is located is the second pipe section 42, as Figure 10G shown.

[0070] In this embodiment, the partition distributor further includes a liquid inlet pipe 5 welded and connected to the liquid inlet pipe assembly hole 11. However, the present utility model does not make any limitation on the structure of the liquid inlet pipe 5 and its connection manner with the liquid inlet pipe assembly hole 11. In other embodiments, the liquid inlet pipe may also be integrally formed with the body at the liquid inlet pipe assembly hole.

[0071] On the other hand, this embodiment also provides a heat exchanger assembly including the above-mentioned partition distributor.

[0072] On the other hand, this embodiment also provides a refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0073] Embodiment Two

[0074] This embodiment is basically the same as Embodiment One and its variations, the difference being: the structures of the partition 2 and the flow channel forming member are different.

[0075] As Figure 11 shown, in this embodiment, the partition 2 is a flat plate structure with both side surfaces (i.e., the upstream surface and the downstream surface) being close to a plane. In this structure, the partition reflection area 22 formed by the projection area of the liquid inlet pipe assembly hole 11 on the partition 2 is also a plane structure. In this embodiment, the partition holes 21 are circular through holes with basically the same aperture. However, the present utility model does not make any limitation on this. In other embodiments, the partition holes may also be converging holes with the aperture gradually decreasing in the direction pointing to the liquid outlet hole 12 and the inner wall generatrix being linear, or flanging holes with the inner wall generatrix being arc-shaped; or, they may be arc bubble holes with the hole wall being arc-shaped convex to one side or both sides of the partition.

[0076] The same as in Embodiment One, in this embodiment, a plurality of partition holes 21 are equally spaced and distributed on the partition 2 in the form of an annular row, the number of partition holes 21 is the same as the number of liquid outlet holes 12, and each partition hole 21 is basically coaxial with the corresponding liquid outlet hole 12. However, the present utility model does not make any limitation on this. In other embodiments, as Figure 12 shown, eight partition holes 21 are distributed on the partition 2 in the form of two annular rows, and four partition holes 21 are equally spaced and distributed on each annular row; at this time, the body liquid outlet end 102 also has four liquid outlet holes 12.

[0077] Although this embodiment is described by taking the plate structure with both side surfaces of the partition 2 being close to a plane as an example. However, the present utility model does not make any limitation on this. In other embodiments, a concave cavity type partition reflection area 22 may also be formed on the surface of the partition 2 facing the liquid inlet pipe assembly hole side (i.e., the upstream surface), while the downstream surface is still close to a plane, as Figure 13 shown.

[0078] In this embodiment, the flow channel forming member 3 is a cone with a cross-section gradually decreasing along its extending direction. An annular flow channel with a gradually decreasing cross-section is formed between the conical flow channel forming member 3 and the inner peripheral wall of the second cavity 1032. The inclined peripheral wall of the flow channel forming member 3 forms the inner wall of the annular flow channel, so as to evenly distribute the high-speed refrigerant injected into the second cavity 1032 to a plurality of liquid outlet holes 12. On this basis, the gradual reduction of the flow channel cross-section will also increase the flow rate of the refrigerant and enable it to quickly enter the liquid outlet holes 12, avoiding gas-liquid two-phase separation during the distribution process after mixing of the refrigerant.

[0079] Specifically, as Figure 11 shown, the vertical distance H1 from the extending top end of the flow channel forming member 3 to the downstream surface of the partition 2 satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the second cavity. Based on the determined inner diameter of the main body 1 and the height H0 of the second cavity, the setting of the vertical distance H1 realizes the precise control of the volume inside the second cavity 1032. In this embodiment, the flow channel forming member 3 is close to a conical shape. In the longitudinal section of the flow channel forming member 3 passing through the axis of the main body 1, the included angle γ formed by the extended lines of the two generatrices on both sides of the flow channel forming member 3 satisfies: 20° ≤ γ ≤ 115°. The included angle γ limits the inclination slope of the peripheral wall of the flow channel forming member 3, that is, realizes the precise control of the change rate of the annular flow channel cross-section, so that the refrigerant after shunting can be quickly distributed to the liquid outlet holes 12. Preferably, the included angle γ is set to 45°, 50° or 60°. However, the present utility model does not make any limitation thereto. Further, to enable the refrigerant to smoothly enter the annular flow channel, the extending top end of the flow channel forming member 3 is provided with an arc-shaped curved surface, and the curvature radius R of the arc-shaped curved surface satisfies: 0.5 mm ≤ R ≤ 5 mm. However, the present utility model does not make any limitation thereto. In other embodiments, the flow channel forming member 3 may also be provided as a frustum-shaped structure with a flat top end. Or, as Figure 14 shown, the flow channel forming member 3 is a spacer sleeve with a cross-section that is basically unchanged along its extending direction.

[0080] Although this embodiment is described by taking the partition 2 as a plate-type structure with both side surfaces being close to planes and the flow channel forming member 3 as a cone with a cross-section gradually decreasing along the extending direction as an example. However, the present utility model does not make any limitation thereto. In other embodiments, when the partition 2 protrudes towards the side where the liquid outlet holes 12 are located (i.e., the partition structure in Embodiment 1) or protrudes towards the side where the liquid inlet pipe assembly hole 11 is located (i.e., the partition structure in Embodiment 3) in the projection area of the liquid inlet pipe assembly hole on the partition, the flow channel forming member 3 may also be provided as a conical or frustum-shaped structure. At this time, the vertical distance H1 is the vertical distance from the extending top end of the flow channel forming member 3 to the downstream surface of the protrusion on the partition; and the height H0 of the second cavity is the vertical distance from the inner bottom wall of the liquid outlet end 102 of the main body to the downstream surface of the protrusion on the partition.

[0081] Embodiment 3

[0082] This embodiment is basically the same as Embodiment 1 and its variations, except that: the structure of the partition plate 3 is different.

[0083] As Figure 15 shown, in the partition distributor provided in this embodiment, the projection area of the liquid inlet pipe assembly hole 11 on the partition plate 2 bulges toward the side where the liquid inlet pipe assembly hole 11 is located, and the bulge is a bulb with a partial circular cross-sectional contour line. However, the present invention makes no limitation thereto. In other embodiments, the bulge may also be a pyramid with a square cross-sectional contour line, a frustum of a cone with a trapezoidal cross-sectional contour line (as Figure 16 shown) or a frustum, or a combination of one or more of a cone or a frustum with a triangular cross-sectional contour line.

[0084] In summary, the partition distributor provided by the present invention divides the internal accommodation cavity of the body into a first cavity and a second cavity through the partition plate to reduce the volume of each cavity in the body, providing a mixing space for the input refrigerant while avoiding excessive expansion of the refrigerant due to too large a cavity. By providing a plurality of partition holes on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition plate, the projection area of the liquid inlet pipe assembly hole on the partition plate can block the input refrigerant and reflect it back into the first cavity, enhancing the mixing degree of the two-phase refrigerant to improve the distribution uniformity. At the same time, the staggered distribution of the partition holes and the liquid inlet pipe assembly holes also effectively prevents the refrigerant from directly passing through to the second cavity without being mixed in time, providing conditions for the refrigerant to be fully mixed in the first cavity. The flow channel forming member maintains the flow rate of the mixed refrigerant by reducing the volume of the second cavity, ensuring that the refrigerant has sufficient inertia force in the second cavity to overcome the influence of gravity and preventing the mixed refrigerant from undergoing gas-liquid two-phase segregation again. At the same time, the annular flow channel formed by the flow channel forming member and the inner wall of the second cavity also guides the homogeneous refrigerant after sufficient mixing so that it can be evenly distributed into a plurality of liquid outlet holes.

[0085] Although the present invention has been disclosed above with the preferred embodiments, it is not intended to limit the present invention. Any person skilled in this art can make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the scope claimed in the claims.

Claims

1. A baffle type dispenser, characterized in that, Comprising: A body, with a liquid inlet pipe assembly hole and a plurality of liquid outlet holes formed at its two axial ends respectively. A receiving cavity communicating the liquid inlet pipe assembly hole and the plurality of liquid outlet holes is formed inside the body; A partition plate, arranged in the receiving cavity of the body to divide the receiving cavity into a first cavity and a second cavity. A plurality of partition plate holes communicating the first cavity and the second cavity are formed on the partition plate, and the plurality of partition plate holes are annularly distributed around the axis of the body on the outer periphery of the projection area of the liquid inlet pipe assembly hole on the partition plate; A flow channel forming member, arranged inside the second cavity and on the inner periphery of the plurality of liquid outlet holes. The flow channel forming member is a rotary member formed by protruding and extending from the inner bottom wall of the liquid outlet end of the body towards the direction where the partition plate is located and rotating around the axis of the body. An annular flow channel communicating the partition plate holes and the plurality of liquid outlet holes is enclosed between the flow channel forming member and the inner wall of the second cavity, and the cross-section of the flow channel forming member is basically unchanged or gradually decreases along its extending direction.

2. The partition distributor according to claim 1, characterized in that, The flow channel forming member is a spacer sleeve with a cross-section basically unchanged along its extending direction, and the upper end of the spacer sleeve abuts against the partition plate area on the inner periphery of the plurality of partition plate holes.

3. The baffle distributor according to claim 2, characterized in that, The radial distance L from the outer wall of the spacer sleeve to the inner edge of the liquid outlet hole satisfies: L≤4mm; the inner edge of the liquid outlet hole refers to: at the liquid outlet end of the body where the plurality of liquid outlet holes are located, the intersection of the connection line between the center of the liquid outlet hole and the center of the body and the edge of the liquid outlet hole.

4. The partition type dispenser according to claim 1, characterized in that, The cross-section of the flow channel forming member gradually decreases along its extending direction, and the vertical distance H1 from the extending top end of the flow channel forming member to the downstream surface of the partition plate satisfies: 1mm≤H1≤2H0 / 3, where H0 is the height of the second cavity.

5. The baffle type dispenser according to claim 4, characterized in that, The extending top end of the flow channel forming member is a flat surface; or, the extending top end of the flow channel forming member is an arc-shaped curved surface and the curvature radius R of the arc-shaped curved surface satisfies: 0.5mm≤R≤5mm.

6. The partition distributor according to claim 4, characterized in that, On the longitudinal section of the flow channel forming member passing through the axis of the body, the included angle γ formed by the extended lines of the two side generatrices of the flow channel forming member satisfies: 20°≤γ≤115°.

7. The baffle type dispenser according to claim 1, wherein The plurality of partition plate holes are equally spaced and distributed on the partition plate in the form of an annular row. The number of partition plate holes is the same as the number of liquid outlet holes and each partition plate hole is basically coaxial with the corresponding liquid outlet hole.

8. The baffle type dispenser according to claim 1, wherein The plurality of partition plate holes are distributed on the partition plate in the form of a plurality of annular rows, and the same number of partition plate holes are equally spaced and distributed on each annular row.

9. The baffle distributor according to claim 1, characterized in that, The partition plate holes are circular through holes or waist-shaped through holes; Or, the aperture of the partition plate hole gradually decreases in the direction pointing to the location of the liquid outlet hole and the inner wall generatrix of the partition plate hole is linear or arc-shaped; Or, the partition plate hole is an arc bubble hole with the hole wall arc-shaped convex towards one or both sides of the partition plate; 10. The partition type dispenser according to claim 1, characterized in that, The partition plate is a flat plate structure with both side surfaces basically close to a plane; Or, the projection area of the liquid inlet pipe assembly hole on the partition plate protrudes towards the side where the liquid inlet pipe assembly hole is located, and the shape of the longitudinal section contour line of the protrusion is one or a combination of a square, a trapezoid, a triangle or a partial circle; Or, the projection area of the liquid inlet pipe assembly hole on the partition plate protrudes towards the side where the liquid outlet hole is located to form a concave cavity with an opening facing the liquid inlet pipe assembly hole, and the longitudinal section contour line of the concave cavity is one or a combination of a square, a trapezoid, a triangle or a partial circle; 11. The partition distributor according to claim 1, wherein The ratio of the downstream end aperture D1 of the partition plate hole to the outer diameter D2 of the branch pipe inserted into the liquid outlet hole is 0.8 - 1.

2.

12. The partition type dispenser according to claim 1, characterized in that, The baffle distributor further includes a plurality of branch pipes respectively welded and connected in a plurality of liquid outlet 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.

13. The partition distributor according to claim 12, wherein, A reflection section is formed on the first pipe section and extends curvedly to one side with respect to the central axis of the liquid outlet 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 outlet hole; Alternatively, the first pipe section is a straight pipe.

14. The baffle type dispenser according to claim 12, characterized in that, 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; Alternatively, the branch section is socket-welded to the first pipe section, and the socket-welded 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.

15. A heat exchanger assembly, characterized in that, It includes the baffle distributor according to any one of claims 1 to 14.

16. A refrigeration device, characterized in that, It includes the heat exchanger assembly according to claim 15.

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