Refrigerant uniform-flow distributor, heat exchanger assembly, and refrigeration device

Abstract

The present invention provides a refrigerant uniform-flow distributor, a heat exchanger assembly, and a refrigeration device, and the refrigerant uniform-flow distributor includes a body and a baffle. A liquid inlet pipe assembly hole is formed in a liquid inlet end of the body, and an inner wall of the liquid inlet end of the body extends obliquely towards a liquid outlet end of the body, with a generatrix being an arc or inclined straight line, and a plurality of branch pipe holes are formed in the liquid outlet end of the body. The baffle divides an accommodating chamber into a first chamber and a second chamber, and a plurality of baffle holes are formed in the baffle in a circular distribution around a centerline of the body, and the plurality of baffle holes are in a one-to-one correspondence with the plurality of branch pipe holes.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This Non-provisional application is based upon and claims priorities under 35 U.S.C. § 119 (a) on to Chinese Patent Application No. 2024220019461 filed on Aug. 16, 2024, Chinese Patent Application No. 2024221448642 filed on Sep. 2, 2024 and Chinese Patent Application No. 202422144852X filed on Sep. 2, 2024, the entire contents of which are hereby incorporated by reference.BACKGROUND OF THE INVENTIONField of the Invention

[0002] The present invention relates to the technical field of refrigerant distribution, and in particular to a refrigerant uniform-flow distributor, a heat exchanger assembly, and a refrigeration device.Description of the Related Art

[0003] A multi-flow-path heat exchanger has advantages of a low pressure drop and a great heat transfer coefficient, and is widely used in a refrigeration system to enhance both refrigeration and heating performance of the refrigeration system. To ensure that the multi-flow-path heat exchanger has good heat transfer performance, a two-phase refrigerant should be uniformly distributed to each flow path of the heat exchanger. Currently, the two-phase refrigerant is distributed in the refrigeration system mainly using a distributor. A most common problem with the distributor used in the refrigeration system is uneven refrigerant flow distribution, where some flow paths are provided with a lower flow rate of a liquid refrigerant and prematurely evaporating to dryness. A heat transfer coefficient in a region of evaporating to dryness is far less than a heat transfer coefficient in a two-phase region, which leads to a reduction in an effective heat transfer area and severely affects the heat transfer performance of the heat exchanger. Experimental evidence has shown that the reduction in heat transfer performance caused by uneven refrigerant distribution can be as great as 25%.

[0004] Currently, commonly used distributors in the refrigeration system include a Venturi-type distributor, a pressure-drop distributor, and an insert-type distributor. The Venturi-type distributor is difficult to machine due to a streamlined flow channel and with a high cost, making it difficult to ensure consistency after processing. The pressure-drop distributor is a simplified structure of the Venturi-type distributor, which shows some improvements in the processing difficulty and cost, but still faces issues such as great pressure loss, high noise, and significant impact of an installation angle on flow distribution performance. The impact of the installation angle on the flow distribution performance is most serious in the insert-type distributor.

[0005] To resolve a problem of uneven liquid distribution in an existing distributor, those skilled in the art have optimized and improved a structure of the existing distributor. Flow channels are mainly improved for the Venturi-type distributor and the pressure-drop distributor with complicated structures. An installation structure of each branch pipe on a liquid distribution side is mainly improved for the insert-type distributor (as shown in FIG. 1) with a simple structure and low cost. However, for the insert-type distributor, when the two-phase refrigerant enters an internal cavity of the distributor, and rapidly expands and diffuses, the two-phase refrigerant can easily undergo two-phase separation during diffusion due to gravity, leading to a large amount of a liquid-phase refrigerant sedimenting at the bottom of the distributor and failing to be distributed to the branch pipe, resulting in poor liquid distribution performance. This is also a main reason why the insert-type distributor is most severely affected by the installation angle.

[0006] To further improve the liquid distribution performance, it is also proposed that a screening plate or filter mesh is disposed inside a distributor cavity, with a plurality of small-diameter liquid passage holes in the screening plate or filter mesh. This type of structure is intended to create a specific pressure on the refrigerant on a liquid inlet pipe side through the screening plate or filter mesh, to achieve a uniform amount of refrigerant flowing through each liquid passage hole. However, some liquid passage holes are directly opposite to the liquid inlet pipe in the screening plate or filter mesh, the refrigerant entering the liquid inlet pipe preferentially passes through the liquid passage holes opposite to the liquid inlet pipe and into a liquid distribution side, making it difficult to implement uniform distribution of refrigerant flowing through all liquid passage holes. In addition, liquid passage holes with extremely small diameters inevitably hinder refrigerant passing, resulting in excessive refrigerant pressure loss. For the evaporator, excessive refrigerant pressure loss means a decrease in an evaporation temperature, a reduction in a refrigerating capacity per unit mass of refrigerant, and a decline in the refrigerating capacity per unit capacity of a compressor is detrimental to refrigeration cycle.BRIEF SUMMARY OF THE INVENTION

[0007] The present invention provides a refrigerant uniform-flow distributor, a heat exchanger assembly, and a refrigeration device to overcome at least one deficiency of the prior art.

[0008] To achieve the above purpose, the present invention provides a refrigerant uniform-flow distributor, including a body and a baffle. The body includes a liquid inlet end, a liquid outlet end, and an accommodating chamber communicating with the liquid inlet end and the liquid outlet end separately, where a liquid inlet pipe assembly hole is formed at the liquid inlet end of the body, an inner wall of the liquid inlet end extends obliquely towards the liquid outlet end of the body, with a generatrix of the inner wall being an arc or inclined straight line, and a plurality of branch pipe holes for liquid distribution are formed at the liquid outlet end of the body; The baffle is disposed inside the accommodating chamber of the body to divide the accommodating chamber into a first chamber and a second chamber, a plurality of baffle holes distributed in a circular shape around a centerline of the body and communicating with the first chamber and the second chamber are formed in the baffle, The plurality of baffle holes are used to be in a one-to-one correspondence with the plurality of branch pipe holes, and are located on an outer periphery of the liquid inlet pipe assembly hole when projected along an axial direction of the body. A line connecting a projection position A, on an inner wall of the liquid inlet end, of an outer edge of a downstream end of the baffle hole along the axial direction of the body and a center O of a downstream end of the liquid inlet pipe assembly hole forms an angle α with respect to a radial direction of the baffle, and 8°≤α≤170, an axial distance H1 from a surface of the baffle at which an upstream end of the baffle hole is located to the projection position A satisfies: 1 mm≤H1≤5 mm, and the outer edge of the downstream end of the baffle hole means an edge of the downstream end of the baffle hole farthest from a centerline of the body.

[0009] According to an embodiment of the present invention, the plurality of baffle holes are distributed at equal intervals in a circular shape in the baffle, a quantity of the baffle holes is the same as a quantity of the branch pipe holes, each baffle hole is basically coaxial with a corresponding branch pipe hole, and a ratio of a diameter D1 of the downstream end of the baffle hole to an outer diameter D2 of a branch pipe inserted into the branch pipe hole is set to 0.8-1.2.

[0010] According to an embodiment of the present invention, the refrigerant uniform-flow distributor further includes a plurality of branch pipes respectively connected to the plurality of branch pipe holes, each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and with an inner diameter reduced relative to an inner diameter of a downstream end of the first pipe section, and a difference Δd between the inner diameter d11 of the downstream end of the first pipe section and an inner diameter d12 of a downstream end of the second pipe section is: 0.1 mm≤Δd≤3.5 mm; and a reflective section, bending and extending to one side relative to a centerline of the branch pipe hole, is formed on the first pipe section, an axis at an upstream end of the reflective section intersects with an axis at a downstream end of the reflective section, to form an angle θ, where 90°≤θ≤175°, and based on the reflective section, an axis of the second pipe section intersects with the centerline of the branch pipe hole.

[0011] According to an embodiment of the present invention, the refrigerant uniform-flow distributor further includes a plurality of branch pipes respectively connected to the plurality of branch pipe holes, each branch pipe includes a connecting straight section, a jet part located downstream of the connecting straight section and with an inner diameter reduced relative to an inner diameter of a connecting straight section body, and a branch section located downstream of the jet part, the branch section is provided with an equal-diameter section with an inner diameter basically approximate to the inner diameter of the connecting straight section body, and a difference Δd′ between the inner diameter d11′ of the connecting straight section body and a minimum inner diameter d12′ of the jet part is: 0.1 mm≤Δd′≤3.5 mm.

[0012] According to an embodiment of the present invention, the baffle holes are through holes with basically the same diameters; or

[0013] diameters of the baffle holes are gradually decreased along a flowing direction of the refrigerant, and generatrices of inner walls of the baffle holes are straight lines or curved lines; or the baffle holes are arc-shaped bubble holes with hole walls protruding towards one or

[0014] both sides of the baffle.

[0015] According to an embodiment of the present invention, the baffle is a plate structure with two nearly flat side surfaces; or

[0016] a region on the baffle opposite to the liquid inlet pipe assembly hole is concave towards a direction in which the liquid outlet end of the body is located, to form a reflective mixed chamber with an opening facing the liquid inlet pipe assembly hole.

[0017] According to an embodiment of the present invention, the refrigerant uniform-flow distributor further includes a liquid inlet pipe welded to the liquid inlet pipe assembly hole, and an axial length L from a liquid outlet end surface of the liquid inlet pipe to a surface of the baffle at which the upstream ends of the baffle holes are located satisfies 3.5 mm≤L≤11.5 mm.

[0018] According to an embodiment of the present invention, a connecting section welded to the liquid inlet pipe assembly hole is formed on the liquid inlet pipe, and the connecting section is a straight section; or

[0019] the connecting section has a gradually expanding structure with a generatrix of an outer wall being an arch-shaped curve, the connecting section extends into the first chamber through the liquid inlet pipe assembly hole, and an outer wall of the connecting section is welded closely to the inner wall of the liquid inlet end of the body.

[0020] According to an embodiment of the present invention, the liquid inlet pipe is a circular pipe with the basically same wall thickness, the liquid inlet pipe is connected to the liquid inlet pipe assembly hole and includes at least one Venturi pipe section, each Venturi pipe section includes a tapered section with a gradually decreased inner diameter, a throat-like straight section with the basically same inner diameter, and a gradually increased section with a gradually increased inner diameter that are distributed in sequence along a flowing direction of a refrigerant.

[0021] According to an embodiment of the present invention, two Venturi pipe sections connected in series are formed on the liquid inlet pipe, namely an upstream Venturi pipe section and a downstream Venturi pipe section, an inner diameter of a throat-like straight section of the downstream Venturi pipe section is less than or equal to an inner diameter of a throat-like straight section of the upstream Venturi pipe section.

[0022] According to an embodiment of the present invention, The liquid inlet pipe further includes a variable-diameter orifice plate disposed downstream of the Venturi pipe section, a variable-diameter orifice is provided in the variable-diameter orifice plate, and the variable-diameter orifice includes a tapered orifice section with a gradually decreased diameter along the flowing direction of the refrigerant and a throat-like orifice section located downstream of the tapered orifice section with a basically unchanged diameter.

[0023] According to an embodiment of the present invention, the branch pipe holes include drainage hole sections and connecting hole sections that are sequentially distributed along a flowing direction of a refrigerant, with diameters of the drainage hole sections gradually decreased along the flowing direction of the refrigerant and generatrices of inner walls of the drainage hole sections being straight lines or arcs.

[0024] According to an embodiment of the present invention, an angle β formed between a tangent at each of the generatrices of the inner walls of the drainage hole sections and a centerline of the branch pipe hole satisfies 10°≤β≤65°.

[0025] According to an embodiment of the present invention, a diameter of a downstream end of the drainage hole section is set to be smaller than a diameter of the connecting hole section, a limiting part which protrudes toward a center direction of the branch pipe hole is formed at a junction between the drainage hole section and the connecting hole section, the limiting part is configured to abut against an end surface of a branch pipe inserted into the branch pipe hole, and a diameter of the limiting part is basically approximate to an inner diameter of the inserted branch pipe.

[0026] According to an embodiment of the present invention, the refrigerant uniform-flow distributor includes a deflector welded closely to an inner end wall of the liquid outlet end of the body, and the deflector is provided with a plurality of deflector holes serving as drainage hole sections of the branch pipe holes; or

[0027] the drainage hole section and the connecting hole section are integrally formed on the end wall of the liquid outlet end of the body.

[0028] According to an embodiment of the present invention, the refrigerant uniform-flow distributor further includes a flow channel forming component disposed in the second chamber and located on inner peripheries of the plurality of branch pipe holes, the flow channel forming component is a rotating component formed by protruding and extending from an inner bottom wall of the liquid outlet end of the body towards a direction in which the baffle is located and rotating around an axis of the body, a circular flow channel communicating the baffle holes with the plurality of branch pipe holes is enclosed between the flow channel forming component and an inner peripheral wall of the second chamber, and a cross-section of the flow channel forming component remains basically unchanged or gradually decreased along an extension direction of the flow channel forming component.

[0029] According to an embodiment of the present invention, the flow channel forming component is a sleeve with a cross-section that remains basically unchanged along the extension direction, and an upper end of the sleeve abuts against a baffle region of inner peripheries of the plurality of baffle holes.

[0030] According to an embodiment of the present invention, the cross-section of the flow channel forming component is gradually decreased along the extension direction, and a vertical distance H2 from an extended top end of the flow channel forming component to a downstream surface of the baffle satisfies: 1 mm≤H2≤2H0 / 3, where H0 is a height of the second chamber.

[0031] According to an embodiment of the present invention, a radial distance L1 from a bottom outer periphery of the flow channel forming component to an inner peripheral wall of the second chamber satisfies: L1≤28 mm.

[0032] According to an embodiment of the present invention, the plurality of baffle holes are distributed at equal intervals in the baffle in an annular array, with a quantity of the baffle holes equal to a quantity of the branch pipe holes, and each baffle hole is basically coaxial with a corresponding branch pipe hole.

[0033] According to an embodiment of the present invention, the plurality of baffle holes are distributed in the baffle in a plurality of annular arrays, and a plurality of baffle holes with a same quantity are distributed at equal intervals in each annular array.

[0034] In another aspect, the present invention further provides a heat exchanger assembly, including the above refrigerant uniform-flow distributor.

[0035] In another aspect, the present invention further provides a refrigeration device, including the above heat exchanger assembly.

[0036] In summary, in the refrigerant uniform-flow distributor provided in the present invention, the accommodating chamber in the body is divided into the first chamber and the second chamber through the baffle, to reduce a capacity of each chamber in the body. The first chamber provides suitable expansion space for the refrigerant in gas-liquid two-phase state input through the liquid inlet pipe to fully mix the refrigerant in gas-liquid two-phase state into a high-speed dispersed flow pattern, effectively resolving a problem of gas-liquid two-phase segregation in the mixed refrigerant caused by an excessive inner chamber of the body in an existing distributor. In addition, the inner wall of the liquid inlet end is disposed to extend obliquely towards the liquid outlet end of the body, so that a secondary reflection surface is formed on the inner wall of the liquid inlet end, and the dispersed refrigerant reflected and mixed by the baffle is reflected into the plurality of baffle holes for the second time, implementing uniform flow guide and distribution of the refrigerant while further improving a mixing degree of the refrigerant in gas-liquid two-phase state through secondary reflection. The setting of the angle α related to the projection position A implements the control of the secondary reflection stroke from the baffle to the inner wall of the liquid inlet end, ensuring that the refrigerant reflected by the baffle can be incident on the inner wall of the liquid inlet end for secondary reflection. The axial distance H1 related to the projection position A determines the spatial positions of the baffle holes, so that the baffle holes are located on the emission path of the secondary reflection; and this setting also effectively prevents the obstruction of refrigerant flow by the inner wall of the body, so that the refrigerant can be evenly distributed into the plurality of baffle holes.

[0037] In addition, the plurality of baffle holes are located on the outer periphery of the projection region of the liquid inlet pipe assembly hole on the baffle, and the projection region of the liquid inlet pipe assembly hole on the baffle can block the input refrigerant and reflect the input refrigerant back into the first chamber to further promote the mixing of the refrigerant in gas-liquid two-phase state. What's more, the staggered distribution of the baffle holes and the liquid inlet holes effectively prevents the refrigerant from flowing directly into the second mixing chamber before being mixed, thereby greatly improving the mixing uniformity of the refrigerant in gas-liquid two-phase state.

[0038] To make the above and other objectives, features, and advantages of the present invention more obvious and understandable, the following preferred embodiments are presented in detail with reference to accompanying drawings.BRIEF DESCRIPTION OF THE DRAWINGS

[0039] FIG. 1 is a schematic structural diagram of an existing insert-type distributor;

[0040] FIG. 2 is a schematic structural diagram of a refrigerant uniform-flow distributor according to a first embodiment of the present invention;

[0041] FIG. 3 is a schematic sectional view of FIG. 2;

[0042] FIG. 4 is a schematic structural diagram of FIG. 3 after a liquid inlet pipe and a branch pipe is removed;

[0043] FIG. 5 is a schematic enlarged diagram of point B in FIG. 4;

[0044] FIG. 6 is a schematic structural diagram of a baffle in FIG. 2;

[0045] FIG. 7A, FIG. 7B, FIG. 7C, FIG. 7D, FIG. 7E, and FIG. 7F are schematic structural diagrams of the baffle according to another embodiment of the present invention;

[0046] FIG. 8 is a schematic structural diagram of an end cover in FIG. 2;

[0047] FIG. 9 is a schematic structural diagram of a body in the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0048] FIG. 10 is a schematic structural diagram of a deflector in FIG. 9;

[0049] FIG. 10A is a schematic structural diagram of the deflector according to another embodiment of the present invention;

[0050] FIG. 11 and FIG. 12 are schematic structural diagrams of the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0051] FIG. 13 is a schematic structural diagram of the refrigerant uniform-flow distributor according to a second embodiment of the present invention;

[0052] FIG. 14 is a schematic structural diagram of a baffle in FIG. 13;

[0053] FIG. 15A, FIG. 15B, FIG. 15C, and FIG. 15D are schematic structural diagrams of the baffle according to another embodiment of the present invention;

[0054] FIG. 16 is a schematic structural diagram of the refrigerant uniform-flow distributor according to a third embodiment of the present invention;

[0055] FIG. 16A is a partial schematic diagram of FIG. 16;

[0056] FIG. 17 is a schematic structural diagram of a branch pipe in the refrigerant uniform-flow distributor according to a fourth embodiment of the present invention;

[0057] FIG. 18A, FIG. 18B, and FIG. 18C are schematic structural diagrams of the branch pipe in the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0058] FIG. 19 is a schematic structural diagram of the refrigerant uniform-flow distributor according to a fifth embodiment of the present invention;

[0059] FIG. 20A, FIG. 20B, FIG. 20C, FIG. 20D, and FIG. 20E are schematic structural diagrams of the branch pipe in the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0060] FIG. 21 is a schematic structural diagram of the refrigerant uniform-flow distributor according to a sixth embodiment of the present invention;

[0061] FIG. 22 is a schematic structural diagram of the baffle in the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0062] FIG. 23 and FIG. 24 are schematic structural diagrams of the refrigerant uniform-flow distributor according to another embodiment of the present invention;

[0063] FIG. 25 is a schematic structural diagram of the refrigerant uniform-flow distributor according to a seventh embodiment of the present invention;

[0064] FIG. 26 is a schematic structural diagram of the refrigerant uniform-flow distributor according to an eighth embodiment of the present invention;

[0065] FIG. 27 and FIG. 28 are schematic structural diagrams of the liquid inlet pipe in the refrigerant uniform-flow distributor according to another embodiment of the present invention; and

[0066] FIG. 29 is a schematic structural view of a variable-diameter orifice plate in FIG. 28.DETAILED DESCRIPTION OF THE INVENTIONFirst Embodiment

[0067] As shown in FIG. 1, in a traditional insert-type distributor, when a refrigerant enters an inner cavity of the distributor to be diffused and mixed, a flow rate of the refrigerant slows down. A liquid-phase refrigerant is extremely easily separated from a gas-phase refrigerant under the action of gravity and deposits at the bottom of the distributor, which seriously affects the uniformity of liquid distribution. However, adding a filter-mesh-type distributor or screening-plate-type distributor also poses problems such as a refrigerant passing through branch pipe holes directly to a liquid distribution side after not fully mixed, as well as excessive pressure loss when the refrigerant passes through liquid passage holes. In view of this, this embodiment provides a refrigerant uniform-flow distributor with excellent flow uniformity and a low pressure loss.

[0068] As shown in FIG. 2 and FIG. 6, the refrigerant uniform-flow distributor provided in this embodiment includes a body 1 and a baffle 2. The body 1 includes a liquid inlet end 101, a liquid outlet end 102, and an accommodating chamber 103 that communicates the liquid inlet end 101 and the liquid outlet end 102 separately. A liquid inlet pipe assembly hole 104 is formed in the liquid inlet end 101 of the body, and an inner wall of the liquid inlet end 101 extends obliquely towards the liquid outlet end 102 of the body, with a generatrix of the inner wall being an arc or inclined straight line. A plurality of branch pipe holes 105 for liquid distribution are formed in the liquid outlet end 102 of the body. The baffle 2 is disposed inside the accommodating chamber 103 of the body 1 to divide the accommodating chamber 103 into a first chamber 1031 and a second chamber 1032. A plurality of baffle holes 21 distributed in a circular shape around a centerline of the body 1 and communicating with the first chamber 1031 and the second chamber 1032 are formed in the baffle 2. The plurality of baffle holes 21 are used to be in a one-to-one correspondence with the plurality of branch pipe holes 105, and are located on an outer periphery of the liquid inlet pipe assembly hole 104 when projected along an axial direction of the body 1.

[0069] A projection, on an inner wall of the liquid inlet end 101, of an outer edge of a downstream end of the baffle hole 21 along the axial direction of the body 1 is a projection position A. A line connecting the projection position A and a center O of a downstream end of the liquid inlet pipe assembly hole 104 forms an angle α with respect to a radial direction of the baffle 2, and 8°≤α≤17°. An axial distance H1 from a surface of the baffle 2 at which an upstream end of the baffle hole 21 is located to the projection position A satisfies: 1 mm≤H1≤5 mm. An outer edge of a downstream end of the baffle hole 21 means an edge of the downstream end of the baffle hole 21 farthest from a centerline of the body 1.

[0070] The downstream or upstream is divided based on a flowing direction of the refrigerant. Usually, the refrigerant flows from upstream to downstream, and a downstream region receives a refrigerant from upstream. In a refrigeration device, the distributor is usually installed vertically or obliquely, with the liquid inlet end of the distributor located below the liquid outlet end in a gravity direction. An inertia force of the refrigerant inside the distributor overcomes gravity and flows toward a direction opposite to the gravity direction. In this case, the upstream and downstream are still divided based on the flowing direction of the refrigerant. Based on the division of the upstream and downstream, the downstream end of the baffle hole 21 means an end of the baffle hole 21 facing the second chamber 1032, and the center O of the downstream end of the liquid inlet pipe assembly hole 104 means a cross-sectional center at an intersection of an inner wall of a straight section of the liquid inlet pipe assembly hole 104 and a curved inner wall of the liquid inlet end 101 of the body.

[0071] In an existing distributor, when the refrigerant enters a distributor cavity with an enlarged flow channel through the liquid inlet pipe, the refrigerant is subject to inertia, causing the refrigerant to diffuse, expand, and form vortices in the distributor cavity to promote mixing of the refrigerant in gas-liquid two-phase state. In addition, the enlarged distributor cavity also reduces a flow rate of the refrigerant. In the refrigerant in gas-liquid two-phase state, flowing of a liquid-phase refrigerant mainly relies on an inertia force and gravity. A decrease in a refrigerant flow rate inevitably weakens the inertia force of the liquid-phase refrigerant. After mixed, a liquid phase in the refrigerant is separated from a gas phase again under the action of gravity, thereby affecting the uniformity of refrigerant distribution.

[0072] In the refrigerant uniform-flow distributor provided in this embodiment, the baffle 2 divides the accommodating chamber 103 inside the body 1 into the first chamber 1031 and the second chamber 1032. While an internal capacity of the first chamber 1031 is reduced, the baffle 2 is used to reflect the input refrigerant, so that the refrigerant in gas-liquid two-phase state expands and is mixed into a high-speed dispersed state in the first chamber 1031. Based on this, the inner wall of the liquid inlet end 101 is disposed to extend obliquely towards the liquid outlet end 102 of the body, so that a secondary reflection surface is formed on the inner wall of the liquid inlet end 101, and the refrigerant reflected back to the first chamber 1031 through the baffle 2 is reflected back to a position of the baffle hole 21 through the inner wall of the liquid inlet end 101. This not only implements uniform flow guidance and distribution of the refrigerant to the plurality of baffle holes 21, but also further promotes collision and mixing of the refrigerant in gas-liquid two-phase state.

[0073] Among position parameters related to 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, the angle α determines an extension slope of the inner wall of the liquid inlet end 101 and a secondary reflection stroke from the baffle 2 to the inner wall of the liquid inlet end 101. Specifically, as the angle α is larger, a slope of a tangent at a position of the generatrix on the inner wall of the liquid inlet end 101 is greater, and the secondary reflection stroke from the baffle 2 to the inner wall of the liquid inlet end 101 is also greater. To enable the refrigerant to enter a secondary reflection surface formed on the inner wall of the liquid inlet end 101 at high speed, it is necessary to prevent the angle α from being extremely large. If the angle α is extremely small, a capacity inside the first chamber 1031 is compressed, causing insufficient mixing space for the refrigerant and increasing a resistance for the refrigerant to enter the baffle hole 21. Therefore, the angle α is set to satisfy a requirement of 8°≤α≤17°; and a preferred set angle α is between 10° and 15°. However, any limitation is not made thereto in the present invention. In other embodiments, the angle α may alternatively be any other angle value within a range of 8° to 17°.

[0074] For an axial distance H1 related to the projection position A, when a diameter of the accommodating chamber 103 of the body and the angle α are determined, a radial distance from the outer edge of the baffle hole 21 to the inner wall of the body 1 is also determined based on the axial distance H1. To be specific, a spatial position (including an axial distance and a radial distance from the baffle hole 21 to the inner wall of the body 1) of the baffle hole 21 within the body 1 is determined based on the axial distance H1. As the axial distance H1 is smaller, the baffle holes 21 are closer to the inner wall of the body 1, while the liquid inlet end 101 that extends obliquely hinders the refrigerant from entering the baffle holes 21, increasing a flow resistance. However, an excessively large axial distance H1 can cause the baffle holes 21 to be excessively close to the center of the body, resulting in the refrigerant not being fully mixed but entering the second chamber 1032 through the baffle holes 21, thereby seriously affecting the uniformity of liquid distribution. Therefore, the axial distance H1 is set to satisfy: 1 mm≤H1≤5 mm; and preferably, the axial distance H1 is set to 2 mm-4 mm. However, any limitation is not made thereto in the present invention. In other embodiments, the axial distance H1 may alternatively be set to other values within 1 mm-5 mm.

[0075] Further, as mentioned earlier, the inner wall of the liquid inlet end 101 of the body serves as the secondary reflection surface to distribute a fully mixed dispersed refrigerant into the baffle holes 21, thereby implementing uniform distribution of the refrigerant in the plurality of baffle holes 21. Therefore, it is necessary to comprehensively set the angle α of the projection position A and the axial distance H1, so that the baffle holes 21 are located on an emission path of the inner wall of the liquid inlet end 101 of the body.

[0076] Further, in the refrigerant uniform-flow distributor provided in this embodiment, the baffle holes 21 are located on an outer periphery of a projection region of the liquid inlet pipe assembly hole 104 on the baffle 2. As shown in FIG. 6, a region C enclosed by a dashed line is a projection region of the liquid inlet pipe assembly hole 104 on the baffle 2, and the region is a closed region to reflect the refrigerant input into the liquid inlet pipe assembly hole 104. The baffle holes 21 distributed in a staggered manner prevent the high-speed refrigerant input into the liquid inlet pipe assembly hole 104 from flowing into the second chamber 1032 for direct distribution. Instead, the high-speed refrigerant is reflected by an enclosed region on the baffle 2 and returns to the first chamber 1031 for further mixing. The refrigerant fully mixed into a dispersed state then evenly enters the second chamber 1032 through a plurality of the baffle holes 21 in a circular pattern to implement uniform distribution of the refrigerant, which effectively resolves a problem of uneven distribution of the refrigerant caused by the lack of time for the refrigerant to be mixed and directly flow to a liquid outlet side in an existing filter-mesh-type distributor or screening-plate-type distributor.

[0077] Related parameters of the baffle 2 and the projection position A of the outer edge of the downstream end of the baffle hole 21 and the staggered distribution of the plurality of baffle holes 21 and the liquid inlet pipe assembly hole 104 enable the refrigerant in gas-liquid two-phase state to be fully mixed into a high-speed dispersed flow pattern in the first chamber 1031. Afterwards, it is necessary to evenly distribute the fully mixed refrigerant into a plurality of the branch pipe holes 105. Therefore, in the refrigerant uniform-flow distributor provided in this embodiment, the plurality of baffle holes 21 are distributed at equal intervals in a circular shape in the baffle 2, and a quantity of the baffle holes 21 is the same as a quantity of the branch pipe holes 105. Each baffle hole 21 is basically coaxial with a corresponding branch pipe hole 105. Equidistant distribution of the plurality of baffle holes 21 ensures that the refrigerant fully mixed in the first chamber 1031 is evenly distributed within the plurality of baffle holes 21 in a circumferential direction. The basic coaxiality between the baffle holes 21 and the corresponding branch pipe holes 105 enables the shortest axial transmission path to be formed therebetween. The high-speed refrigerant output from the baffle holes 21 can quickly enter the corresponding branch pipe holes 105, maintaining a flow pattern of the refrigerant mixed as much as possible and further improving the uniformity of refrigerant distribution.

[0078] In this embodiment, for example, the quantity of the baffle holes 21 and the quantity of the branch pipe holes 105 are the same and both are coaxially arranged. However, any limitation is not made thereto in the present invention. In other embodiments, the quantity of the baffle holes can also be twice or three times the quantity of the branch pipe holes, and two or three baffle holes form a group to be in one-to-one correspondence with the corresponding branch pipe holes. In the refrigerant uniform-flow distributor provided in this embodiment, there is a limited quantity of the baffle holes with large diameters. Preferably, a ratio of a diameter D1 of the downstream end of the baffle hole 21 to an outer diameter D2 of a branch pipe 3 inserted into the branch pipe hole 105 is set to 0.8-1.2. The large baffle hole 21 not only better helps the passage of the refrigerant, but also effectively reduces pressure loss of the refrigerant during distribution. Specifically, the ratio of the diameter D1 of the downstream end of the baffle hole 21 to the outer diameter D2 of the branch pipe 3 inserted into the branch pipe hole 105 can be set to 0.85, 0.9, 0.95, 1.0, 1.05, 1.1, 1.15, or the like. However, any limitation is not made thereto in the present invention. In other embodiments, D1 / D2 may alternatively be other ratios within the range of 0.8-1.2.

[0079] In this embodiment, as shown in FIG. 3 and FIG. 4, the baffle holes 21 are through holes with diameters that are basically the same along a flowing direction of the refrigerant, and shapes that are circular. However, any limitation is not made thereto in the present invention. In other embodiments, the baffle holes may alternatively be set as oval or waist-shaped through holes.

[0080] In other embodiments, as shown in FIG. 7A and FIG. 7B, the baffle holes 21 may alternatively be set as collection holes with generatrices of inner walls being inclined straight lines and diameters gradually decreasing along a flowing direction of the refrigerant. Alternatively, as shown in FIG. 7C, the baffle 2 includes a baffle body 2a and a baffle liner 2b that is overlaid on the baffle body 2a. A plurality of through holes 2al are formed in the baffle body 2a, and a plurality of baffle liner holes 2b1, distributed corresponding to the plurality of through holes 2a1, are formed in the baffle liner 2b. Diameters of the baffle liner holes 2b1 are gradually decreased along the flowing direction of the refrigerant, and the baffle liner holes 2b1 and the corresponding through holes 2al form the baffle holes 21. In FIG. 7C, the baffle 2 includes the plurality of baffle liners 2b that are overlaid near the through holes 2al and have an area smaller than an area of the baffle body 2a. However, any limitation is not made thereto in the present invention. In other embodiments, an area of the baffle liner can be the same as the area of the baffle body. Gradual reduction of inner diameters of the baffle holes 21 can accelerate the refrigerant flowing through the baffle holes, increasing a flow rate of the refrigerant, so that the refrigerant can quickly enter the corresponding branch pipe holes 105. In addition, the acceleration caused by the baffle holes 21 can further facilitate mixing of the refrigerant in gas-liquid two-phase state. However, any limitation is also not made thereto in the present invention.

[0081] In other embodiments, as shown in FIG. 7D, the baffle holes 21 can also be set as flanged holes with arc-shaped generatrices of inner walls and gradually decreased diameters along a flowing direction of the refrigerant. Alternatively, straight hole sections with basically unchanged diameters can be added at ends of the flanged holes shown in FIG. 7D. To be specific, the generatrices of the inner walls of the baffle holes are combinations of arcs and straight lines. In addition, in other embodiments, the baffle holes 21 may alternatively be set to arc-shaped bubble holes with hole walls protruding towards one or both sides of the baffle, as shown in FIG. 7E and FIG. 7F.

[0082] In this embodiment, the baffle 2 is a plate structure with two nearly flat side surfaces and a circular cross-section. However, any limitation is not made thereto in the present invention. In other embodiments, a projection region of the liquid inlet pipe assembly hole on the baffle can alternatively be set to other shapes, such as a concave shape towards a direction in which the liquid outlet end of the body is located, to form a reflective mixed chamber with an opening facing the liquid inlet pipe assembly hole.

[0083] In this embodiment, as shown in FIG. 3 and FIG. 4, the refrigerant uniform-flow distributor further includes a liquid inlet pipe 4 welded to the liquid inlet pipe assembly hole 104, and an axial length L from a liquid outlet end surface of the liquid inlet pipe 4 to a surface of the baffle 2 at which the upstream ends of the baffle holes 21 are located satisfies 3.5 mm≤L≤11.5 mm. Specifically, the liquid inlet pipe assembly hole 104 is provided with an assembly hole straight section 106 extending outward from the body, and a connecting section 41 welded to the assembly hole straight section 106 is formed on the liquid inlet pipe 4. The connecting section 41 is a straight section, and an end surface of the connecting section 41 is a liquid outlet end surface of the liquid inlet pipe. Through such disposing, when an assembly strength of the liquid inlet pipe 4 satisfies requirements of the refrigeration system, the liquid outlet end of the liquid inlet pipe 4 is prevented from being excessively inserted into the first chamber 1031, which affects an effective mixed refrigerant capacity in the first chamber 1031 and a flow resistance of the refrigerant entering the baffle holes 21. In addition, as the refrigerant enters the first chamber 1031, the refrigerant inevitably faces volume expansion, resulting in a decrease in the flow rate of the refrigerant. An excessively long axial length L reduces kinetic energy that impacts the baffle 2, reducing a primary reflection mixing effect of the baffle 2 and a secondary reflection mixing effect of an inner wall of the liquid inlet end 101, thereby seriously affecting a mixed atomization degree of the refrigerant.

[0084] Preferably, the axial length L from the liquid outlet end surface of the liquid inlet pipe 4 to the surface of the baffle 2 at which the upstream ends of the baffle holes 21 are located is set to 4 mm, 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, or 10 mm. However, any limitation is not made thereto in the present invention. In other embodiments, the axial length L may alternatively be other values within 3.5 mm≤L≤11.5 mm.

[0085] In this embodiment, the liquid inlet pipe 4 is welded to the liquid inlet pipe assembly hole 104. The present invention does not impose any restrictions on a connection manner for the liquid inlet pipe. In other embodiments, the liquid inlet pipe may alternatively be integrally formed with the body at which the liquid inlet pipe assembly hole is located.

[0086] In the refrigerant uniform-flow distributor provided in this embodiment, a homogeneous dispersed flow output from the baffle holes 21 rushes towards the corresponding branch pipe holes 105 under the influence of an inertial force, and some refrigerant still inevitably collides with an inner bottom wall of the liquid outlet end 102 of the body and flows back along a peripheral wall of the body 1, thereby generating a vortex region near the branch pipe holes 105 and close to the peripheral wall of the body 1. The existence of the vortex region compresses a refrigerant flow channel at inlets of the branch pipe holes 105, reducing mass flow entering the branch pipe holes 105, which not only affects the uniformity of refrigerant distribution, but also impacts a flow resistance. To mitigate the adverse effect of the vortex region near the branch pipe holes 105 on the uniform flow distribution, in this embodiment, the branch pipe holes 105 are set to include drainage hole sections 1051 and connecting hole sections 1052 that are sequentially distributed along a flowing direction of the refrigerant, with diameters of the drainage hole sections 1051 gradually decreasing along the flowing direction of the refrigerant. When inner diameters of the connecting hole sections 1052 remain unchanged, gradual reduction of the diameters of the drainage hole sections 1051 inevitably increases diameters at inlets of the drainage hole sections (namely, enlarging refrigerant flow channels at the inlets), so that the refrigerant can better enter the drainage hole sections 1051. Further, the increase in the diameters at the inlets of the drainage hole sections 1051 also reduces a reflective area of the inner bottom wall of the liquid outlet end 102 of the body against the refrigerant, thereby reducing a range of the vortex region and weakening compression of the vortex region against the refrigerant flow channels, and further improving flow distribution uniformity and reducing a flow distribution resistance.

[0087] In this embodiment, the refrigerant uniform-flow distributor also includes a branch pipe 3 inserted into the connecting hole section 1052 of the branch pipe hole. Due to the influence of a wall thickness of the branch pipe 3, a step is formed on a front end surface of the branch pipe 3, and the refrigerant collides with a surface of this step to generate vortexes, thereby hindering flowing of the refrigerant. To resolve this problem, as shown in FIG. 4 and FIG. 5, in this embodiment, a diameter of a downstream end of the drainage hole section 1051 is set to be smaller than a diameter of the connecting hole section 1052. A limiting part 1053 which protrudes toward a center direction of the branch pipe hole 105 is formed at a junction between the drainage hole section 1051 and the connecting hole section 1052, and an inner diameter D3 at the limiting part 1053 is approximate to an inner diameter D4 of the inserted branch pipe 3. The limiting part 1053 is configured to abut against an insertion end surface of the branch pipe 4 to implement insertion assembly limitation of the branch pipe 3, while the inner diameter D3 of the limiting part 1053 is basically approximate to the inner diameter D4 of the branch pipe, so that there is no step at an insertion front end surface of the branch pipe 3. The refrigerant flowing into the drainage hole section 1051 can smoothly enter the branch pipe 3, further reducing the flow resistance of the refrigerant.

[0088] In this embodiment, a generatrix of an inner wall of the drainage hole section 1051 is an inclined straight line, and there is an angle β between the generatrix of the inner wall of the drainage hole section 1051 (the generatrix of the inner wall of the drainage hole section coincides with a tangent at the generatrix of the inner wall) and a centerline of the branch pipe hole 105, where 10°≤β≤65°. Preferably, the angle β may be set to 45°, as shown in FIG. 5. However, any limitation is not made thereto in the present invention. In other embodiments, the angle β may be other values within 10°-65°, such as 15°, 20°, 25°, 30°, 40°, 45°, 50°, 55°, 60°, or the like. Although the generatrix of the inner wall of the drainage hole section is, for example, the inclined straight line in this embodiment, any limitation is not made thereto in the present invention. In other embodiments, the drainage hole section may alternatively be a flanged hole with an arc-shaped generatrix of the inner wall, where the angle β formed between the tangent at the generatrix of the inner wall of the drainage hole section and the centerline of the branch pipe hole satisfies 10°≤β≤65°. As shown in FIG. 2 and FIG. 8, in this embodiment, the body 1 includes a cylindrical body 11, an end cover 12, and a liner 13. The cylindrical body 11 is integrally formed and has an open end at one side, with a plurality of flow distribution holes 111 formed at a bottom of the cylindrical body 11. The liner 13 is welded to an inner bottom surface of the cylindrical body 11, forming a liquid outlet end wall of the body 1 with the cylindrical body 11. A plurality of liner holes 131 that are coaxial with the plurality of flow distribution holes 111 are formed in the liner 13, and the liner holes 131 and the corresponding flow distribution holes 111 form the branch pipe holes 105. Specifically, a section of the liner hole 131 close to the second chamber 1032 forms the drainage hole section 1051, while a section close to a bottom of the cylindrical body 11 and the flow distribution hole 111 form the connecting hole section 1052. The end cover 12 has a curved surface shape, one end is welded to an open end of the cylindrical body 11, and the other end is provided with the liquid inlet pipe assembly hole 104.

[0089] The drainage hole section and the connecting hole section are, for example, integrally formed on the end wall of the liquid outlet end of the body in this embodiment. However, any limitation is not made thereto in the present invention. In other embodiments, as shown in FIG. 9 and FIG. 10, the refrigerant uniform-flow distributor may also include a deflector 5 welded to an inner end wall of the liquid outlet end 102 of the body. The deflector 5 is provided with a plurality of deflector holes serving as the drainage hole sections 1051 of the branch pipe holes. FIG. 10A is a schematic structural diagram of the deflector according to another embodiment of the present invention. In this structure, a depth of the deflector hole is based on a thickness of the deflector.

[0090] In this embodiment, an inner wall of the end cover 12 extends at an incline toward the liquid outlet end 102 of the body, and a generatrix of an inner wall presents a curved arc surface. However, any limitation is not made thereto in the present invention. In other embodiments, as shown in FIG. 11, a generatrix of an inner wall of a liquid inlet end 101 of the body may also be set to be an inclined straight line, and an inner wall contour of the end cover 12 presents a frustum shape.

[0091] FIG. 12 is a schematic structural diagram of the refrigerant uniform-flow distributor according to another embodiment of the present invention. In this structure, a body 1′ includes an end cover 12′ and a liner 13′. A liquid inlet pipe assembly hole 104 with a curved surface shape is formed at one end of the end cover 12′, while the liner 13′ is embedded at the other end of the end cover 12′, and a plurality of liner holes, serving as branch pipe holes 105, are formed in the liner 13′. Similarly, in other embodiments, a generatrix of an inner wall of the end cover 12′ in FIG. 12 is alternatively an inclined straight line. In addition, there is only one liner in each of FIG. 1, FIG. 9, FIG. 11, and FIG. 12. However, any limitation is not made thereto in the present invention. In other embodiments, there are alternatively a plurality of liners, and the plurality of liners are stacked and welded to an inner wall and outer wall of the cylindrical body, or embedded in an open end of the end cover after stacked.

[0092] Correspondingly, this embodiment further provides a heat exchanger assembly, and the heat exchanger assembly includes the refrigerant uniform-flow distributor provided in this embodiment. Specifically, the heat exchanger assembly is a condenser or an evaporator. In addition, this embodiment further provides a refrigeration device that includes the condenser or evaporator.Second Embodiment

[0093] This embodiment is basically the same as the first embodiment with basically the same variations, with a difference as follows: as shown in FIG. 13 and FIG. 14, a cavity 201 with an opening facing the liquid inlet pipe assembly hole 104 (not labeled in FIG. 13 and FIG. 14 due to the assembly of the liquid inlet pipe 4) is formed in a region of the baffle 2 that is corresponding to the liquid inlet pipe assembly hole 104, and the baffle 2 at the cavity 201 extends towards the liquid outlet end 102 of the body.

[0094] Compared with the first embodiment, this embodiment provides ample mixing space for the refrigerant that is reflected after high-speed impact by setting up the cavity 201 on the baffle 2 to facilitate full mixing of the refrigerant in gas-liquid two-phase state. In addition, when a mass flow rate of the input refrigerant input is large, disposing of the cavity 201 can also effectively reduce the impact of a reflective force on the input refrigerant at the liquid inlet pipe assembly hole 104, preventing refrigerant backflow in the liquid inlet pipe caused by an excessively great reflective force. The baffle 2 at the cavity 201 extends towards a side of the liquid outlet end 102 of the body. Through such disposing, a capacity in the second chamber 1032 is reduced, preventing a homogeneous phase refrigerant output from the baffle holes 21 from experiencing gas-liquid phase segregation in the second chamber 1032 due to re-expansion and deceleration; and an annular flow distribution groove is enclosed between an outer wall of the cavity 201 and the second chamber 1032, and the homogeneous phase refrigerant output from the baffle holes 21 is evenly distributed along the annular flow distribution groove into the plurality of branch pipe holes 105 distributed circularly at a bottom of the body 1, implementing symmetrical flow distribution of the refrigerant.

[0095] In this embodiment, an inner cavity shape of the cavity 201 is cylindrical, and an outer bottom wall of the cavity 201 abuts against an inner bottom wall of the liquid outlet end 102 of the body. However, any limitation is not made thereto in the present invention. In other embodiments, the inner cavity shape of the cavity may alternatively be one or more combinations of a cone (as shown in FIG. 15A), a frustum of a cone (as shown in FIG. 15B), a prism, a frustum of a prism, a pyramid, or a part of a spherical shape (as shown in FIG. 15C), such as a combination (as shown in FIG. 15D) of a cylindrical shape and the part of the spherical shape, a combination of the frustum of a cone and the part of the spherical shape, a combination of the prism and the part of the spherical shape, or the like.Third Embodiment

[0096] This embodiment is basically the same as the first embodiment with basically the same variations, with a difference as follows: a structure of the liquid inlet pipe assembly hole 104 is different from a structure of the liquid inlet pipe 4.

[0097] As shown in FIG. 16 and FIG. 16A, in this embodiment, the liquid inlet pipe assembly hole 104 is a through hole without an assembly hole straight section. In this embodiment, the liquid inlet pipe 4 has a Venturi pipe structure, and a connecting section 41′ has a gradually expanding structure with a generatrix of an outer wall being an arch-shaped curve. The connecting section 41′ extends into the first chamber 1031 through the liquid inlet pipe assembly hole 104, and an outer wall of the connecting section 41′ is welded closely to the inner wall of the liquid inlet end 102 of the body.

[0098] It is defined that an extension line of a generatrix of an inner wall of a throat-like straight section 40′ on a Venturi pipe section intersects with a virtual extension plane, at the liquid inlet pipe assembly hole 104, of the inner wall of the liquid inlet end 101 at a position K, and a cross-section of the liquid inlet pipe 4 passing through the position K is an end surface of the liquid outlet end of the liquid inlet pipe 4. In addition, due to a connection manner for the liquid inlet pipe 4, in this embodiment, the liquid inlet pipe 4 is welded to the inner wall of the liquid inlet end 101 of the body through the gradually expanding connecting section 41′. Therefore, it is defined that an extension line of a generatrix of an outer wall of the throat-like straight section 40′ on the Venturi pipe section intersects with the virtual extension plane, at the liquid inlet pipe assembly hole 104, of the inner wall of the liquid inlet end 101 at a position K′, and a cross-section center of the liquid inlet pipe 4 passing through the position K′ is a downstream end center O of the liquid inlet pipe assembly hole, as shown in FIG. 16A.

[0099] In this embodiment, the axial length L from the liquid outlet end surface of the liquid inlet pipe 4 to the surface of the baffle 2 at which the upstream end of the baffle holes 21 are located still satisfies 3.5 mm≤L≤11.5 mm. Similarly, the angle α between 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 102 along an axial direction of the body and a center O of the downstream end of the liquid inlet pipe assembly hole and a radial direction of the baffle 2 still satisfies: 8°≤α≤17°.

[0100] However, a specific structure of the liquid inlet pipe assembly hole is not limited in any manner in the present invention. In other embodiments, when the liquid inlet pipe assembly hole has an assembly hole straight section, the connecting section on the liquid inlet pipe can also be disposed to include a straight section and a gradually increased section that is downstream of the straight section and closely welded the inner wall of the liquid inlet end of the body.

[0101] In this embodiment, there are ten branch pipes 3. However, any limitation is not made thereto in the present invention.Fourth Embodiment

[0102] This embodiment is basically the same as the first embodiment with basically the same variations, with a difference as follows: a structure of the branch pipe 3 is different.

[0103] In this embodiment, as shown in FIG. 17, each branch pipe 3 includes a first pipe section 31 and a second pipe section 32 located downstream of the first pipe section 31 and with an inner diameter reduced relative to an inner diameter of a downstream end of the first pipe section 31. A difference Δd between the inner diameter d11 of the downstream end of the first pipe section 31 and an inner diameter d12 of a downstream end of the second pipe section 32 is: 0.1 mm≤Δd≤ 3.5 mm. A reflective section 311, bending and extending to one side relative to a centerline of the branch pipe hole 105, is the first pipe section 31. An axis at an upstream end of the reflective section 311 intersects with an axis at a downstream end of the reflective section to form an angle θ, where 90°≤θ≤175°. Based on the reflective section 311, an axis of the second pipe section 32 intersects with the centerline of the branch pipe hole 105.

[0104] The first pipe section 31 with a large inner diameter increases a refrigerant flow distributed into each branch pipe 3 and reduces a refrigerant distribution resistance, while the second pipe section 32 with a relatively small inner diameter can enhance a refrigerant flow rate within the branch pipe, to satisfy performance requirements of the heat exchanger assembly at a rear end. Based on this, the difference Δd between the inner diameters precisely controls a pressure drop acceleration degree of the refrigerant in the second pipe section 32, preventing excessive acceleration that could lead to a significant refrigerant pressure loss. Disposing of the reflective section 311 causes the second pipe section 32 to be no longer coaxial with the centerline of the branch pipe hole 105. When pressure waves exist downstream and oscillate upstream, the reflective section 311 reflects and absorbs some of the pressure waves and changes a propagation direction of remaining pressure waves, causing the remaining pressure waves to decay rapidly, effectively preventing the influence of downstream pressure waves on branch pipe holes 105 upstream, to further improve distribution performance.

[0105] In this embodiment, the branch pipe 3 also includes a third pipe section 33 welded to the first pipe section 31, and the second pipe section 32 is located on the third pipe section 33. Specifically, as shown in FIG. 17, the third pipe section 33 is provided with a sleeving connection part 331 that is sleeved at an end of the first pipe section 31 and has a flared structure, and the second pipe section 32 with an internal diameter gradually decreasing is formed downstream of the sleeving connection part 331. However, any limitation is not made thereto in the present invention. In other embodiments, an outer sleeve of an end of the first pipe section 31 may be welded to the sleeving connection part 331 on the third pipe section 33. In this case, the second pipe section still has a structure, with an inner diameter gradually decreasing, located downstream of the sleeving connection part 331, as shown in FIG. 18A.

[0106] FIG. 18B and FIG. 18C are schematic structural diagrams of the branch pipe according to another embodiment of the present invention. In FIG. 18B, the first pipe section 31, the second pipe section 32, and the third pipe section 33 are integrally formed. In FIG. 18C, the first pipe section 31 and the second pipe section 32 are integrally formed, while the third pipe section 33 is welded to an end of the second pipe section. In other embodiments, the second pipe section can alternatively be formed directly at a sleeving connection position between the first pipe section and the second pipe section. In addition, a plurality of second pipe sections can be disposed at a downstream end of the first pipe section. The third pipe section 33 can be disposed as either a straight pipe or a bent pipe according to actual applications.Fifth Embodiment

[0107] This embodiment is basically the same as the first embodiment with basically the same variations, with a difference as follows: the branch pipe 3 has another structure.

[0108] As shown in FIG. 19, in this embodiment, each branch pipe 3 includes a connecting straight section 31′, a jet part 32′, located downstream of the connecting straight section 31′, with an inner diameter decreasing relative to an inner diameter d11′ of a connecting straight section body 311′, and a branch section 33′ located downstream of the jet part 32′. The branch section 33′ is provided with an equal-diameter section 331′ with an inner diameter basically approximate to the inner diameter d11′ of the connecting straight section body. A difference Δd′ between the inner diameter d11′ of the connecting straight section body and a minimum inner diameter d12′ of the jet part 32′ is: 0.1 mm≤Δd′<3.5 mm. The connecting straight section body 311′ means a pipe section of the connecting straight section 31′ where both an inner diameter and outer diameter remain basically unchanged.

[0109] The refrigerant uniform-flow distributor provided in this embodiment improves a flow velocity of the refrigerant in the branch pipe 3 by adding the jet part 32′ to each branch pipe 3 to satisfy performance requirements of the heat exchanger assembly at a rear end. Based on this, the inner diameter difference Δd′ precisely controls a pressure drop acceleration degree that the jet part 32′ exerts on the refrigerant, preventing excessive acceleration that could lead to a significant refrigerant pressure loss. Further, an inner diameter d13′ of the equal-diameter section 331′ disposed on the branch section 33′ is basically approximate to the inner diameter d11′ of the connecting straight section body, to reduce a flow resistance of the refrigerant in the branch pipe 3, implementing balanced control of a refrigerant flow rate and pressure loss.

[0110] In this embodiment, the jet part 32′ is integrally formed as a converging section upstream of the branch section 33′, and the two are welded after being integrally formed and connected to the connecting straight section 31′. However, any limitation is not made thereto in the present invention. In other embodiments, as shown in FIG. 20A, the jet part 32′ can alternatively be integrally formed downstream of the connecting straight section 31′, and then welded to the branch section 33′. Alternatively, as shown in FIG. 20B, the connecting straight section 31′, the jet part 32′, and the branch section 33′ can be integrally formed.

[0111] Alternatively, the jet part 32′ is a jet orifice plate placed at a sleeving connection position between the connecting straight section 31′ and the branch section 33′. Specifically, as shown in FIG. 20C, an upstream end of the branch section 33′ is sleeved on a downstream end of the connecting straight section 31′ after flared, and the jet part 32′ is placed at a flared part of the branch section 33′. Similarly, when a flared part of the downstream end of the connecting straight section 31′ is sleeved on the upstream end of the branch section 33′, the jet part 32′ can alternatively be placed at the flared part of the downstream end of the connecting straight section 31′, as shown in FIG. 20D.

[0112] Alternatively, the jet part 32′ can be set to a straight pipe section, with two ends respectively sleeved on the connecting straight section 31′ and the branch section 33′, as shown in FIG. 20E. In FIG. 19, FIGS. 20A, and 20E, the jet part 32′ has a length L32 with an inner diameter that remains basically unchanged. However, any limitation is not made thereto in the present invention.

[0113] The present invention does not impose any restrictions on a formation manner for the jet part. Any other jet part structures that can implement a reduction in an inner diameter relative to the inner diameter of the connecting straight section of the body are within the protection scope of the present invention.Sixth Embodiment

[0114] This embodiment is basically the same as the second embodiment with basically the same variations, with a difference as follows: as shown in FIG. 21, the refrigerant uniform-flow distributor provided in this embodiment further includes a flow channel forming component 6 disposed within the second chamber 1032 and located around inner perimeters of the plurality of branch pipe holes 105. The flow channel forming component 6 extends from an inner bottom wall of the liquid outlet end 102 of the body towards a direction in which the baffle 2 is located, and a cross-section thereof remains basically unchanged or gradually decreased along the extension direction, forming an annular flow distribution groove between the flow channel forming component 6 and an inner wall of the second chamber 1032.

[0115] Similar to the second embodiment, in this embodiment, an annular flow channel is constructed based on the flow channel forming component 6 in the second chamber 1032 to implement uniform distribution of the refrigerant, while the flow channel forming component 6 is used to reduce a capacity of the second chamber 1032 to prevent gas-liquid two-phase segregation caused by excessive expansion of the refrigerant. Specifically, as shown in FIG. 21, the flow channel forming component 6 is a hollow sleeve with a cross-section that remains usually unchanged during extension. The sleeve is sleeved on the cavity 201 with an upper end abutting against a baffle region in inner peripheries of the plurality of baffle holes 21. To be specific, when axial projection is performed along the body 1, the sleeve that serves as the flow channel forming component 6 is located between the cavity 201 and the plurality of baffle holes 21. An annular flow channel communicating with the plurality of baffle holes 21 and the plurality of branch pipe holes 105 is formed between the sleeve and an inner peripheral wall of the second chamber 1032. The cross-sections of the flow channels between the plurality of baffle holes 21 and the plurality of branch pipe holes 105 are reduced radially, to control a volume change rate and flow rate of the refrigerant in the second chamber 1032, ensuring that the refrigerant can maintain a dispersed flow after mixed, to be evenly distributed into the plurality of branch pipe holes 105. Further, a radial spacing L1 from a bottom periphery of the flow channel forming component 6 to the inner peripheral wall of the second chamber 1032 can be controlled to precisely control a capacity ratio of the annular flow channel and the first chamber 1031, thus implementing precise control of a refrigerant flow rate within the annular flow channel. Preferably, L1 is set to satisfy: L1≤28 mm, for example, L1 is 11 mm, 15 mm, 18 mm, 20 mm, 23 mm, or 25 mm.

[0116] In the refrigerant uniform-flow distributor provided in this embodiment, when the refrigerant enters the second chamber 1032 through the plurality of baffle holes 21 and is distributed into the plurality of branch pipe holes 105, some refrigerant inevitably collides with the inner bottom wall of the liquid outlet end 102 of the body and flows back along the inner peripheral wall of the second chamber 1032 and an outer wall of the flow channel forming component 6. Backflow of the refrigerant generates a vortex region near the branch pipe holes 105, and the presence of the vortex region compresses a refrigerant flow channel at an inlet of the branch pipe hole 105, hindering the flow of refrigerant and affecting the performance of the distributor. In this embodiment, setting of the radial spacing L1 also reduces a reflective area of the inner bottom wall of the liquid outlet end 102 of the body to the refrigerant, thereby reducing an effective range of the vortex region and weakening compression of the vortex region on a refrigerant distribution flow channel, improving the uniformity of refrigerant distribution while reducing the distribution resistance.

[0117] Similar to the first embodiment, in this embodiment, the plurality of baffle holes 21 are distributed in the baffle 2 at equal intervals in an annular array, with a quantity of the baffle holes 21 equal to a quantity of the branch pipe holes 105, and each baffle hole 21 is basically coaxial with a corresponding branch pipe hole 105. However, any limitation is not made thereto in the present invention. In other embodiments, as shown in FIG. 22, eight baffle holes 21 are distributed on the baffle 2 in two annular arrays, and four baffle holes 21 are distributed at equal intervals in each annular array. In this case, four branch pipe holes 105 are also provided in the liquid outlet end 102 of the body.

[0118] In this embodiment, for example, the cavity 201 is formed on the baffle 2. However, any limitation is not made thereto in the present invention. In other embodiments, the baffle 2 may alternatively be a flat-plate structure with surfaces on both sides approximate to being planar, as shown in FIG. 23. Alternatively, a cavity is formed on a surface (namely, an upstream surface) of the baffle 2 facing a side of the liquid inlet pipe assembly hole, while the other side surface (namely, a downstream surface) remains approximate to being planar, as shown in FIG. 24.Seventh Embodiment

[0119] This embodiment is basically the same as the sixth embodiment with basically the same variations, with a difference as follows: a structure of the baffle 2 is different from a structure of the flow channel forming component 6.

[0120] As shown in FIG. 25, in this embodiment, the baffle 2 is a plate structure with two nearly flat side surfaces. The flow channel forming component 6 is a conical shape whose cross-section is gradually decreased in an extension direction. An annular flow channel with a gradually decreased cross-section is enclosed between the conical flow channel forming component 6 and the inner peripheral wall of the second chamber 1032. An inclined peripheral wall of the flow channel forming component 6 forms an inner wall of the annular flow channel, so that a high-speed refrigerator injected into the second chamber 1032 is uniformly distributed into the plurality of branch pipe holes 105. Based on this, gradual reduction of a flow channel cross-section also increases the flow rate of the refrigerant, so that the refrigerant quickly enters the branch pipe holes 105, preventing the separation of a gas phase from a liquid phase during the distribution of the refrigerant after mixed.

[0121] Specifically, as shown in FIG. 25, a vertical distance H2 from an extended top end of the flow channel forming component 6 to a downstream surface of the baffle 2 satisfies: 1 mm≤H2≤2H0 / 3, where H0 is a height of the second chamber 1032. Based on the determined inner diameter of the body 1 and the height H0 of the second chamber, setting of the vertical distance H2 implements precise control of a capacity in the second chamber 1032. In this embodiment, the flow channel forming component 6 is approximate to a conical shape, and on a longitudinal cross-section of the flow channel forming component 6 passing through an axis of the body 1, an angle γ formed by extension lines of generatrices on both sides of the flow channel forming component 6 satisfies: 200≤γ≤115°. The angle γ limits an inclination slope of a peripheral wall of the flow channel forming component 6, so that a change rate of a cross-section of the annular flow channel is precisely controlled, and the refrigerant after distributed can be quickly distributed into the branch pipe holes 105. Preferably, the angle γ is set to 45°, 50°, or 60°. However, any limitation is not made thereto in the present invention.

[0122] Further, to enable the refrigerant to smoothly enter the annular flow channel, the extended top end of the flow channel forming component 6 is set to have an arc-shaped curved surface, and a radius of curvature R of the arc-shaped curve surface satisfies: 0.5 mm≤R≤5 mm. However, any limitation is not made thereto in the present invention. In other embodiments, the flow channel forming component 6 may alternatively be configured as a circular truncated cone structure with a flat surface extending at the top.

[0123] In this embodiment, for example, the baffle 2 is a plate-like structure with both side surfaces approximate flat, and the flow channel forming component 6 is a conical shape whose cross-section is gradually decreased in an extension direction. However, any limitation is not made thereto in the present invention. In other embodiments, when the baffle 2 has a projection region of the liquid inlet pipe assembly hole on the baffle that protrudes towards a side where the branch pipe holes 105 are located to form a cavity (such as baffle structures in the second embodiment and the six embodiment) or protrudes towards a side where the liquid inlet pipe assembly hole 104 is located (namely a baffle structure in the third embodiment), the flow channel forming component 6 may alternatively be set to have a conical or circular truncated cone-shaped structure. In this case, the vertical distance H2 is a vertical distance from an extended top of the flow channel forming component 6 to a downstream surface at a protrusion on the baffle. The height H0 of the second chamber is a vertical distance from an inner bottom wall of the liquid outlet end 102 of the body to the downstream surface at the protrusion on the baffle.Eighth Embodiment

[0124] This embodiment is basically the same as the first embodiment with basically the same variations, with a difference as follows: a structure of the liquid inlet pipe 4 is different.

[0125] As shown in FIG. 26, in this embodiment, a Venturi pipe section 42 is formed on the liquid inlet pipe 4, and a connecting section 41 is formed at a downstream end of the Venturi pipe section 42. The connecting section 41 is a straight pipe section that is welded to an assembly hole straight section 106 on the liquid inlet pipe assembly hole. However, any limitation is not made thereto in the present invention.

[0126] In this embodiment, the liquid inlet pipe 4 is a circular pipe fitting with a basically uniform wall thickness, and the Venturi pipe section 42 on the liquid inlet pipe 4 is formed by processing a circular pipe material through a tapering technique. This disposing allows for precise control of inner diameter change rates of a gradually tapered section 421 and a gradually increased section 423, as well as a transitional structure between adjacent pipe sections, so that a smooth linear flow is formed within the Venturi pipe section 42, facilitating mixing of the refrigerant in gas-liquid two-phase state while reducing a refrigerant pressure loss. Further, the Venturi structure formed based on the pipe fittings is a structure formed in a chipless processing manner that does not require cutting. This processing manner has advantages such as high processing accuracy, excellent product consistency, high processing efficiency, and minimal material consumption.

[0127] FIG. 27 is a schematic structural diagram of the refrigerant uniform-flow distributor according to another embodiment of the present invention. In this structure, there are two Venturi pipe sections, connected in series, formed on the liquid inlet pipe 4, namely an upstream Venturi pipe section 42′ and a downstream Venturi pipe section 42. A flow pattern of the refrigerant at the inlet is gradually improved through the two Venturi pipe sections connected in series, enhancing the mixing uniformity of the refrigerant at the inlet to improve the performance of the distributor. Preferably, an inner diameter D42 of a throat-like straight section of the downstream Venturi pipe section 42 is smaller than an inner diameter D42′ of a throat-like straight section of the upstream Venturi pipe section 42′. This disposing further accelerates the refrigerant at the throat-like straight section 422 of the downstream Venturi pipe section 42, increasing kinetic energy of the refrigerant injected into the body 1, enhancing a gas-liquid two-phase mixing effect, and allowing the refrigerant to have a greater inertial force to maintain a flow pattern after mixed.

[0128] However, the series connection of the two Venturi pipe sections 42 and 42′ enables a length of the liquid inlet pipe 4 to be long, making it difficult to be applied to a refrigeration device with strict installation space. To address this, a liquid inlet pipe structure capable of implementing secondary mixing while having a short length is provided in the refrigerant uniform-flow distributor shown in FIG. 28. In this structure, the liquid inlet pipe 4 includes a Venturi pipe section 42 and a variable-diameter orifice plate 43 located downstream of the Venturi pipe section 42. Specifically, a connecting section 41 presenting a straight pipe section is formed downstream of the Venturi pipe section 42, and the variable-diameter orifice plate 43 is disposed within the connecting section 41. As shown in FIG. 29, a variable-diameter orifice 430 is provided in the variable-diameter orifice plate 43, and the variable-diameter orifice 430 includes a tapered orifice section 431 with a gradually decreased diameter along a flowing direction of the refrigerant, and a throat-like orifice section 432 located downstream of the tapered orifice section 431 with a basically unchanged diameter. In the refrigerant uniform-flow distributor in FIG. 28, a long downstream Venturi pipe section in FIG. 27 is replaced with the variable-diameter orifice plate 43 that is thin, which shortens a length of the liquid inlet pipe 4 while implementing secondary mixing, to accommodate refrigeration devices in different pieces of installation space, including a refrigeration device in narrow installation space (such as 1HP or 1.5HP household air conditioning indoor units).

[0129] In summary, in the refrigerant uniform-flow distributor provided in the present invention, the accommodating chamber in the body is divided into the first chamber and the second chamber through the baffle, to reduce a capacity of each chamber in the body. The first chamber provides suitable expansion space for the refrigerant in gas-liquid two-phase state input through the liquid inlet pipe to fully mix the refrigerant in gas-liquid two-phase state into a high-speed dispersed flow pattern, effectively resolving a problem of gas-liquid two-phase segregation in the mixed refrigerant caused by an excessive inner chamber of the body in an existing distributor. In addition, the inner wall of the liquid inlet end is disposed to extend obliquely towards the liquid outlet end of the body, so that a secondary reflection surface is formed on the inner wall of the liquid inlet end, and the dispersed refrigerant reflected and mixed by the baffle is reflected into the plurality of baffle holes for the second time, implementing uniform flow guide and distribution of the refrigerant while further improving a mixing degree of the refrigerant in gas-liquid two-phase state through secondary reflection. The setting of the angle α related to the projection position A implements the control of the secondary reflection stroke from the baffle to the inner wall of the liquid inlet end, ensuring that the refrigerant reflected by the baffle can be incident on the inner wall of the liquid inlet end for secondary reflection. The axial distance H1 related to the projection position A determines the spatial positions of the baffle holes, so that the baffle holes are located on the emission path of the secondary reflection; and this setting also effectively prevents the obstruction of refrigerant flow by the inner wall of the body, so that the refrigerant can be evenly distributed into the plurality of baffle holes.

[0130] In addition, the plurality of baffle holes are located on the outer periphery of the projection region of the liquid inlet pipe assembly hole on the baffle, and the projection region of the liquid inlet pipe assembly hole on the baffle can block the input refrigerant and reflect the input refrigerant back into the first chamber to further promote the mixing of the refrigerant in gas-liquid two-phase state. What's more, the staggered distribution of the baffle holes and the liquid inlet holes effectively prevents the refrigerant from flowing directly into the second mixing chamber before being mixed, thereby greatly improving the mixing uniformity of the refrigerant in gas-liquid two-phase state.

[0131] The present invention has been disclosed in the preferred embodiments as described above, which is not intended to limit the present invention. Any person skilled in the art may make slight changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be deemed to be the scope of protection in the claims.

Claims

1. A refrigerant uniform-flow distributor, comprising:a body, comprising a liquid inlet end, a liquid outlet end, and an accommodating chamber communicating with the liquid inlet end and the liquid outlet end separately, wherein a liquid inlet pipe assembly hole is formed at the liquid inlet end of the body, an inner wall of the liquid inlet end extends obliquely towards the liquid outlet end of the body, with a generatrix of the inner wall being an arc or inclined straight line, and a plurality of branch pipe holes for liquid distribution are formed at the liquid outlet end of the body;a baffle, disposed inside the accommodating chamber of the body to divide the accommodating chamber into a first chamber and a second chamber, a plurality of baffle holes distributed in a circular shape around a centerline of the body and communicating with the first chamber and the second chamber are formed in the baffle, the plurality of baffle holes are used to be in a one-to-one correspondence with the plurality of branch pipe holes, and are located on an outer periphery of the liquid inlet pipe assembly hole when projected along an axial direction of the body; anda line connecting a projection position A, on an inner wall of the liquid inlet end, of an outer edge of a downstream end of the baffle hole along the axial direction of the body and a center O of a downstream end of the liquid inlet pipe assembly hole forms an angle α with respect to a radial direction of the baffle, and 8°≤α≤17°, an axial distance H1 from a surface of the baffle at which an upstream end of the baffle hole is located to the projection position A satisfies: 1 mm≤H1≤5 mm, and the outer edge of the downstream end of the baffle hole means an edge of the downstream end of the baffle hole farthest from a centerline of the body.

2. The refrigerant uniform-flow distributor according to claim 1, wherein the plurality of baffle holes are distributed at equal intervals in a circular shape in the baffle, a quantity of the baffle holes is the same as a quantity of the branch pipe holes, each baffle hole is basically coaxial with a corresponding branch pipe hole, and a ratio of a diameter D1 of the downstream end of the baffle hole to an outer diameter D2 of a branch pipe inserted into the branch pipe hole is set to 0.8-1.2.

3. The refrigerant uniform-flow distributor according to claim 1, wherein the refrigerant uniform-flow distributor further comprises a plurality of branch pipes respectively connected to the plurality of branch pipe holes, each branch pipe comprises a first pipe section and a second pipe section located downstream of the first pipe section and with an inner diameter reduced relative to an inner diameter of a downstream end of the first pipe section, and a difference Δd between the inner diameter d11 of the downstream end of the first pipe section and an inner diameter d12 of a downstream end of the second pipe section is: 0.1 mm≤Δd≤3.5 mm; and a reflective section, bending and extending to one side relative to a centerline of the branch pipe hole, is formed on the first pipe section, an axis at an upstream end of the reflective section intersects with an axis at a downstream end of the reflective section to form an angle θ, wherein 90°≤θ≤175°, and based on the reflective section, an axis of the second pipe section intersects with the centerline of the branch pipe hole.

4. The refrigerant uniform-flow distributor according to claim 1, wherein the refrigerant uniform-flow distributor further comprises a plurality of branch pipes respectively connected to the plurality of branch pipe holes, each branch pipe comprises a connecting straight section, a jet part located downstream of the connecting straight section and with an inner diameter reduced relative to an inner diameter of a connecting straight section body, and a branch section located downstream of the jet part, the branch section is provided with an equal-diameter section with an inner diameter basically approximate to the inner diameter of the connecting straight section body, and a difference Δd′ between the inner diameter d1l′ of the connecting straight section body and a minimum inner diameter d12′ of the jet part is: 0.1 mm≤Δd′≤3.5 mm.

5. The refrigerant uniform-flow distributor according to claim 1, wherein the baffle holes are through holes with basically the same diameters;diameters of the baffle holes are gradually decreased along a flowing direction of the refrigerant, and generatrices of inner walls of the baffle holes are straight lines or curved lines; orthe baffle holes are arc-shaped bubble holes with hole walls protruding towards one or both sides of the baffle.

6. The refrigerant uniform-flow distributor according to claim 1, wherein the baffle is a plate structure with two nearly flat side surfaces; ora region on the baffle opposite to the liquid inlet pipe assembly hole is concave towards a direction in which the liquid outlet end of the body is located, to form a reflective mixed chamber with an opening facing the liquid inlet pipe assembly hole.

7. The refrigerant uniform-flow distributor according to claim 1, wherein the refrigerant uniform-flow distributor further comprises a liquid inlet pipe welded to the liquid inlet pipe assembly hole, and an axial length L from a liquid outlet end surface of the liquid inlet pipe to a surface of the baffle at which the upstream ends of the baffle holes are located satisfies 3.5 mm≤L≤11.5 mm.

8. The refrigerant uniform-flow distributor according to claim 7, wherein a connecting section welded to the liquid inlet pipe assembly hole is formed on the liquid inlet pipe, and the connecting section is a straight section; orthe connecting section has a gradually expanding structure with a generatrix of an outer wall being an arch-shaped curve, the connecting section extends into the first chamber through the liquid inlet pipe assembly hole, and an outer wall of the connecting section is welded closely to the inner wall of the liquid inlet end of the body.

9. The refrigerant uniform-flow distributor according to claim 7, wherein the liquid inlet pipe is a circular pipe with the basically same wall thickness, the liquid inlet pipe is connected to the liquid inlet pipe assembly hole and comprises at least one Venturi pipe section, each Venturi pipe section comprises a tapered section with a gradually decreased inner diameter, a throat-like straight section with the basically same inner diameter, and a gradually increased section with a gradually increased inner diameter that are distributed in sequence along a flowing direction of a refrigerant.

10. The refrigerant uniform-flow distributor according to claim 9, wherein two Venturi pipe sections connected in series are formed on the liquid inlet pipe, namely an upstream Venturi pipe section and a downstream Venturi pipe section, an inner diameter of a throat-like straight section of the downstream Venturi pipe section is less than or equal to an inner diameter of a throat-like straight section of the upstream Venturi pipe section.

11. The refrigerant uniform-flow distributor according to claim 9, wherein the liquid inlet pipe further comprises a variable-diameter orifice plate disposed downstream of the Venturi pipe section, a variable-diameter orifice is provided in the variable-diameter orifice plate, and the variable-diameter orifice comprises a tapered orifice section with a gradually decreased diameter along the flowing direction of the refrigerant and a throat-like orifice section located downstream of the tapered orifice section with a basically unchanged diameter.

12. The refrigerant uniform-flow distributor according to claim 1, wherein the branch pipe holes comprise drainage hole sections and connecting hole sections that are sequentially distributed along a flowing direction of a refrigerant, with diameters of the drainage hole sections gradually decreased along the flowing direction of the refrigerant and generatrices of inner walls of the drainage hole sections being straight lines or arcs.

13. The refrigerant uniform-flow distributor according to claim 12, wherein an angle β formed between a tangent at each of the generatrices of the inner walls of the drainage hole sections and a centerline of the branch pipe hole satisfies 10°≤β≤65°.

14. The refrigerant uniform-flow distributor according to claim 12, wherein a diameter of a downstream end of the drainage hole section is set to be smaller than a diameter of the connecting hole section, a limiting part which protrudes toward a center direction of the branch pipe hole is formed at a junction between the drainage hole section and the connecting hole section, the limiting part is configured to abut against an end surface of a branch pipe inserted into the branch pipe hole, and a diameter of the limiting part is basically approximate to an inner diameter of the inserted branch pipe.

15. The refrigerant uniform-flow distributor according to claim 12, wherein the refrigerant uniform-flow distributor comprises a deflector welded closely to an inner end wall of the liquid outlet end of the body, and the deflector is provided with a plurality of deflector holes serving as drainage hole sections of the branch pipe holes; orthe drainage hole section and the connecting hole section are integrally formed on the end wall of the liquid outlet end of the body.

16. The refrigerant uniform-flow distributor according to claim 1, wherein the refrigerant uniform-flow distributor further comprises a flow channel forming component disposed in the second chamber and located on inner peripheries of the plurality of branch pipe holes, the flow channel forming component is a rotating component formed by protruding and extending from an inner bottom wall of the liquid outlet end of the body towards a direction in which the baffle is located and rotating around an axis of the body, a circular flow channel communicating the baffle holes with the plurality of branch pipe holes is enclosed between the flow channel forming component and an inner peripheral wall of the second chamber, and a cross-section of the flow channel forming component remains basically unchanged or gradually decreased along an extension direction of the flow channel forming component.

17. The refrigerant uniform-flow distributor according to claim 16, wherein the flow channel forming component is a sleeve with a cross-section that remains basically unchanged along the extension direction, and an upper end of the sleeve abuts against a baffle region of inner peripheries of the plurality of baffle holes.

18. The refrigerant uniform-flow distributor according to claim 16, wherein the cross-section of the flow channel forming component is gradually decreased along the extension direction, and a vertical distance H2 from an extended top end of the flow channel forming component to a downstream surface of the baffle satisfies: 1 mm≤H2≤2H0 / 3, wherein H0 is a height of the second chamber.

19. The refrigerant uniform-flow distributor according to claim 16, wherein a radial distance L1 from a bottom outer periphery of the flow channel forming component to an inner peripheral wall of the second chamber satisfies: L1≤28 mm.

20. The refrigerant uniform-flow distributor according to claim 16, wherein the plurality of baffle holes are distributed at equal intervals in the baffle in an annular array, with a quantity of the baffle holes equal to a quantity of the branch pipe holes, and each baffle hole is basically coaxial with a corresponding branch pipe hole.

21. The refrigerant uniform-flow distributor according to claim 16, wherein the plurality of baffle holes are distributed in the baffle in a plurality of annular arrays, and a plurality of baffle holes with a same quantity are distributed at equal intervals in each annular array.

22. A heat exchanger assembly, comprising the refrigerant uniform-flow distributor as claimed in claim 1.

23. A refrigeration device, comprising the heat exchanger assembly as claimed in claim 22.

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