Two-stage jet flow reflection mixing diversion distributor, heat exchange device and air conditioner

Abstract

The utility model provides a two-stage jet flow reflection mixing flow guide distributor, a heat exchange device and refrigeration equipment. The two-stage jet flow reflection mixing flow guide distributor comprises a cavity, a liquid inlet pipe, a two-stage jet flow reflection mixing component and a plurality of branch pipes. The two-stage jet flow reflection mixing component comprises a first-stage reflection mixing plate, a second-stage jet flow hole plate and a second-stage reflection mixing plate which are sequentially distributed in the cavity at intervals in the flowing direction of the refrigerant. The first-stage reflecting and mixing plate is distributed opposite to the inflow end of the cavity so as to reflect and mix a refrigerant injected into the cavity from the liquid inlet pipe, and a plurality of overflowing holes are formed in the first-stage reflecting and mixing plate. The second-stage jet flow hole plate and the first-stage reflection mixing plate define a jet flow cavity, and a second-stage jet flow hole is formed in the jet flow cavity. The second-stage reflection mixing plate is opposite to the second-stage jet flow holes and is provided with a plurality of flow guide holes of which the number is the same as that of the shunting branch pipe holes; and each flow guide hole is basically coaxial with the corresponding shunting branch pipe hole. And the plurality of branch pipes are respectively welded and connected in the plurality of shunting branch pipe holes in the outflow end of the cavity.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigerant distribution, and particularly to a two-stage jet reflection mixing and diversion distributor, a heat exchange device and an air conditioner. Background Art

[0002] The multi-channel heat exchanger has the advantages of small pressure drop and large heat transfer coefficient, and is widely used in refrigeration systems to improve the refrigeration and heating performance of the refrigeration system. To ensure good heat exchange performance of the multi-channel heat exchanger, the two-phase refrigerant should be evenly distributed to each flow path of the heat exchanger. At present, distributors are mainly used in refrigeration systems to distribute the refrigerant. However, due to the limited installation space in the refrigeration equipment, the two-phase refrigerant after throttling by the expansion valve needs to be bent by the inlet connecting pipe and then enter the distributor. When the refrigerant passes through the bent section of the inlet connecting pipe, since the density and viscosity of the liquid-phase fluid are relatively large, the centrifugal force it receives is greater than that of the gas-phase refrigerant, so that the liquid-phase refrigerant accumulates on the outer side of the bent section, while the gas-phase refrigerant accumulates on the inner side of the bent section, resulting in the separation of the gas-liquid two phases. Furthermore, the asymmetric flow pattern of the two-phase refrigerant entering the distributor cavity will seriously affect the uniformity of the distributor.

[0003] To solve this problem, some people propose to perform continuous reverse bends on the inlet connecting pipe (as Figure 1 shown) or adjust the necessary straight section length after bending to improve the degree of gas-liquid two-phase separation. However, whether it is continuous reverse bending or the lengthening of the straight section length after bending, both will increase the installation space of the inlet connecting pipe, and the bending parameters or necessary straight section parameters need to be customized and verified according to the sizes of different models in actual applications. Obviously, such improvement schemes bring uncertainties and workloads in actual applications, which are uneconomical, and even cannot be applied to some models with small space, such as the indoor units of 1HP or 1.5HP household air conditioners. Further, continuous reverse bending will also bring other problems such as excessive pressure loss of the inlet refrigerant, excessive noise, and difficulty in ensuring the accuracy and consistency of batch processing.

[0004] In addition, some people also propose to process a throttling section with a reduced inner diameter in the middle area of the inlet pipe of the distributor, hoping to improve the inlet flow pattern of the refrigerant by increasing the refrigerant flow rate through the throttling section. However, simple pressure reduction and speed increase have extremely limited improvement on the inlet flow pattern of the refrigerant, especially when the input mass flow rate of the refrigerant is small, the improvement of the distribution performance by this optimization is minimal. Summary of the Utility Model

[0005] In order to overcome the deficiencies of the prior art, the utility model provides a two-stage jet reflection mixing and diversion distributor, a heat exchange device and an air conditioner.

[0006] To achieve the above object, the present utility model provides a two-stage jet reflection mixing and diversion distributor, which includes a cavity, a liquid inlet pipe, a two-stage jet reflection mixing component, and multiple branch pipes. The cavity has an inflow end and an outflow end, and a plurality of diversion branch pipe holes are distributed on the outflow end. The liquid inlet pipe is connected to the inflow end of the cavity to inject refrigerant into the cavity to form a primary jet. The two-stage jet reflection mixing component includes a primary reflection mixing plate, a secondary jet orifice plate, and a secondary reflection mixing plate that are sequentially and spaced apart along the refrigerant flow direction in the cavity. The primary reflection mixing plate is oppositely distributed relative to the inflow end of the cavity to reflect and mix the refrigerant injected into the cavity, and a plurality of flow holes are formed on the primary reflection mixing plate. The secondary jet orifice plate and the primary reflection mixing plate enclose a jet cavity, and a secondary jet hole is formed on the secondary jet orifice plate. The refrigerant reflected and mixed by the primary reflection mixing plate converges in the jet cavity through the flow holes and is jetted to the secondary reflection mixing plate through the secondary jet hole. The secondary reflection mixing plate is oppositely distributed relative to the secondary jet hole and has a plurality of diversion holes equal in number to the diversion branch pipe holes. Each diversion hole is substantially coaxial with the corresponding diversion branch pipe hole. The secondary reflection mixing plate reflects and mixes the refrigerant injected through the secondary jet hole and distributes it to the plurality of diversion branch pipe holes through the diversion holes. The multiple branch pipes are respectively welded and connected into the plurality of diversion branch pipe holes.

[0007] According to an embodiment of the present utility model, a primary reflection portion opposite to the liquid outlet end of the liquid inlet pipe is formed on the primary reflection mixing plate;

[0008] The primary reflection portion is a planar reflection portion with a reflection surface close to a plane;

[0009] Alternatively, the primary reflection portion is a primary reflection concave cavity with an opening facing the inflow end of the cavity, and the longitudinal section contour line of the primary reflection concave cavity is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

[0010] According to an embodiment of the present utility model, the primary reflection portion protrudes and extends toward the side where the secondary jet orifice plate is located to form a primary reflection concave cavity with an opening facing the inflow end of the cavity.

[0011] According to an embodiment of the present utility model, on the primary reflection mixing plate, a plurality of flow holes are evenly distributed in a ring on the plane of the primary reflection mixing plate outside the primary reflection portion.

[0012] According to an embodiment of the present utility model, the total flow area S1 of the plurality of flow holes on the primary reflection mixing plate and the cross-sectional area S0 of the cavity where the primary reflection mixing plate is located satisfy: 0.1 ≤ S1 / S0 ≤ 0.45.

[0013] According to an embodiment of the present utility model, the flow holes on the primary reflection mixing plate and the diversion holes on the secondary reflection mixing plate are all one or a combination of through holes, flanging holes, and arc bubble holes;

[0014] The secondary jet holes are through holes or flanging holes extending towards the side where the secondary reflection mixing plate is located.

[0015] According to an embodiment of the present invention, a secondary reflection part opposite to the secondary jet holes is formed on the secondary reflection mixing plate, and a plurality of diversion holes are annularly and equally spaced around the cavity axis on the plane of the secondary reflection mixing plate outside the periphery of the secondary reflection part.

[0016] The secondary reflection part is a planar reflection part with a reflection surface close to a plane.

[0017] Alternatively, the secondary reflection part is a secondary reflection concave cavity with an opening facing the secondary jet holes, and the longitudinal section contour line of the secondary reflection concave cavity is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

[0018] According to an embodiment of the present invention, the secondary reflection part protrudes and extends towards the outflow end of the cavity, forming a secondary reflection concave cavity on the side facing the secondary jet holes, and enclosing an annular diversion cavity with the inner wall of the cavity at the outflow end of the cavity.

[0019] According to an embodiment of the present invention, when the longitudinal section contour line of the secondary reflection concave cavity is a square or a trapezoid, the vertical distance H from the extended top end of the secondary reflection part to the inner bottom wall at the outflow end of the cavity satisfies: 0 ≤ H ≤ 3 mm.

[0020] According to an embodiment of the present invention, the downstream surface of the secondary reflection mixing plate is close to a plane. The two-stage jet reflection mixing and diversion distributor further includes an annular flow channel member disposed between the secondary reflection mixing plate and the outflow end of the cavity and inside the periphery of a plurality of diversion branch pipe holes. The annular flow channel member is a rotary member formed by protruding and extending from the inner bottom wall of the outflow end of the cavity towards the direction where the secondary reflection mixing plate is located and rotating around the cavity axis. An annular flow channel communicating with a plurality of diversion branch pipe holes is enclosed between the annular flow channel member and the inner wall of the cavity, and the cross-section of the annular flow channel member is basically unchanged or gradually decreases along the extension direction.

[0021] According to an embodiment of the present invention, the annular flow channel member is a cone or a frustum of a cone with a cross-section gradually decreasing along its extension direction, and the vertical distance H1 from the extended top end of the annular flow channel member to the secondary reflection mixing plate satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the vertical distance from the center of the inner bottom wall of the outflow end of the cavity to the downstream surface of the secondary reflection mixing plate.

[0022] According to an embodiment of the present invention, the annular flow channel member is an annular sleeve with a cross-section basically unchanged along its extension direction, and the extended top end of the annular sleeve abuts against the secondary reflection part on the secondary reflection mixing plate.

[0023] According to an embodiment of the present utility model, the chamber volume V1 enclosed by the first-stage reflection mixing plate and the inner wall of the chamber inlet end, the jet chamber volume V2 enclosed by the second-stage jet orifice plate and the first-stage reflection mixing plate, and the chamber volume V3 enclosed by the second-stage reflection mixing plate and the second-stage jet orifice plate satisfy: 0.6 ≤ V1 / V2 ≤ 1.5, 0.6 ≤ V3 / V2 ≤ 1.5.

[0024] According to an embodiment of the present utility model, the liquid inlet pipe includes a main body section with a substantially constant inner diameter and a jet section located downstream of the main body section and having a reduced inner diameter relative to the main body section.

[0025] According to an embodiment of the present utility model, the aperture diameter at the liquid outlet end of the second-stage jet orifice on the second-stage jet orifice plate is less than or equal to the minimum inner diameter of the jet section on the liquid inlet pipe.

[0026] According to an embodiment of the present utility model, a primary jet orifice plate is provided in the liquid inlet pipe. The primary jet orifice plate is formed with primary jet orifices having an aperture diameter smaller than the inner diameter of the main body section. The minimum aperture diameter of the primary jet orifices is the minimum inner diameter of the jet section, and the position where the primary jet orifice plate is located forms the jet section;

[0027] Alternatively, the jet section is a Venturi tube section, and the inner diameter of the throat of the Venturi tube section is the minimum inner diameter of the jet section;

[0028] Alternatively, the jet section is a straight section with a reduced inner diameter relative to the main body section.

[0029] According to an embodiment of the present utility model, each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1 mm ≤ △d ≤ 3.5 mm.

[0030] According to an embodiment of the present utility model, an attenuation section is formed on the first pipe section and extends bent toward one side of the center line of the shunt branch pipe orifice. An included angle θ is formed between the axis at the upstream end of the attenuation section and the axis at the downstream end of the attenuation section, and 90° ≤ θ ≤ 175°. Based on the attenuation section, the axis of the second pipe section intersects the center line of the shunt branch pipe orifice;

[0031] Alternatively, the first pipe section is a straight pipe.

[0032] According to an embodiment of the present utility model, each branch pipe further includes a branch section. The second pipe section is a tapered structure integrally formed with the first pipe section and having a gradually decreasing inner diameter. The branch section is welded to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed;

[0033] Alternatively, the branch section is socket-welded to the first pipe section, and the socket-welded portion of the two forms the second pipe section;

[0034] Alternatively, the branch section is socket-welded to the first pipe section, and the second pipe section is formed on the branch section.

[0035] On the other hand, the present utility model also provides a heat exchange device, which includes the above two-stage jet reflection mixing diversion distributor.

[0036] On the other hand, the present utility model also provides an air conditioner, which includes the above heat exchange device.

[0037] In summary, in the two-stage jet reflection mixing diversion distributor provided by the present utility model, the liquid inlet pipe injects the refrigerant with an asymmetric inlet flow pattern at a high speed into the cavity in the form of a primary jet; disturbing the inlet refrigerant flow pattern and increasing the kinetic energy of the refrigerant, providing a basis for arranging the refrigerant into a uniformly mixed dispersed flow pattern. After being reflected by the primary reflection mixing plate, the refrigerant injected at a high speed forms a turbulent flow with the incident flow beam in the preliminary arrangement chamber surrounded between the primary reflection mixing plate and the inner wall of the inlet end of the cavity, enhancing the degree of two-phase flow disorder so that the refrigerant gradually develops towards a dispersed flow pattern. The refrigerant after preliminary development enters the jet cavity, is fully mixed and developed in the jet cavity, and then converges at the secondary jet holes. The secondary jet holes reduce the pressure and increase the speed of the refrigerant, increasing the refrigerant flow rate so that it can always maintain the fully mixed refrigerant flow pattern in the reflection mixing cavity surrounded by the secondary reflection mixing plate and the secondary jet hole plate, thereby improving the distribution performance. Further, by precisely controlling the volume ratios of the preliminary arrangement chamber of the inlet refrigerant, the jet cavity, and the reflection mixing cavity in the subsequent distribution process, the refrigerant is fully developed into a stable dispersed flow pattern in the jet cavity and can always maintain this flow pattern in the subsequent distribution process, greatly improving the distribution performance of the distributor.

[0038] The two-stage jet reflection mixing diversion distributor provided by the present utility model integrates the arrangement of the inlet flow pattern of the refrigerant and the uniform distribution of the refrigerant after arrangement. The distributor with this structure eliminates the need for any adjustment and optimization on the liquid inlet pipe, which not only greatly facilitates the processing, installation, and welding of the liquid inlet pipe, but also significantly improves the applicability of the distributor so that it can be well compatible with various different specifications of refrigeration equipment.

[0039] To make the above and other objects, features, and advantages of the present utility model more obvious and understandable, the following specifically gives preferred embodiments and, in conjunction with the accompanying drawings, makes a detailed description as follows. Description of the Drawings

[0040] Figure 1 Shown is a schematic structural diagram of the liquid inlet pipe in the prior art with multiple bending parts provided on the liquid inlet pipe to improve the inlet refrigerant flow pattern of the distributor.

[0041] Figure 2 Shown is a schematic structural diagram of the two-stage jet reflection mixing diversion distributor provided in Embodiment 1 of the present utility model.

[0042] Figure 3 As shown Figure 2 is a schematic structural view after removing the liquid inlet pipe and the branch pipe in

[0043] Figure 4 As shown Figure 2 is a schematic structural view of the primary reflection mixing plate in

[0044] Figure 5A and Figure 5B and Figure 5C and Figure 5D and Figure 5E shown is a schematic structural view of the primary reflection mixing plate in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0045] Figure 6A and Figure 6B shown is a schematic structural view of the secondary jet orifice plate in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0046] Figure 7 As shown Figure 2 is a schematic structural view of the secondary reflection mixing plate in

[0047] Figure 8 shown is a schematic structural view after removing the liquid inlet pipe and the branch pipe in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0048] Figure 9A and Figure 9B shown is a schematic structural view of the liquid inlet pipe in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0049] Figure 9C shown is a schematic structural view of the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0050] Figure 10 As shown Figure 2 is a schematic structural view of the branch pipe in

[0051] Figure 11A and Figure 11B and Figure 11C and Figure 11D and Figure 11E and Figure 11F and Figure 11G is a schematic structural view of the branch pipe in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0052] Figure 12 shown is a schematic structural view of the two-stage jet reflection mixing and diversion distributor provided by Embodiment 2 of the present utility model.

[0053] Figure 13 As shown Figure 12 is a schematic structural view after removing the inlet pipe and the branch pipe.

[0054] Figure 14A 、 Figure 14B 、 Figure 14C and Figure 14D shown is a schematic structural view of the primary reflection mixing plate in the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model.

[0055] Figure 15 shown is a schematic structural view of the two-stage jet reflection mixing and diversion distributor provided by Embodiment III of the present utility model.

[0056] Figure 16 shown is a schematic structural view of the two-stage jet reflection mixing and diversion distributor provided by another embodiment of the present utility model. Detailed implementation manners

[0057] In the present application, the downstream or the upstream is divided based on the flow direction of the refrigerant. Generally, the refrigerant flows from the upstream to the downstream, and the area located downstream receives the refrigerant from the upstream. In a refrigeration device, the distributor is generally installed vertically or obliquely, and the inlet end of the distributor is located below the outlet end along the direction of gravity. The inertial force of the refrigerant in the distributor overcomes the gravity and flows in the direction opposite to the gravity; at this time, the upstream and the downstream are still divided according to the flow direction of the refrigerant.

[0058] Embodiment I

[0059] The distributor is connected between the expansion valve and the heat exchange device to evenly and equally distribute the throttled two-phase refrigerant to each branch of the heat exchange device. Such a connection manner makes the performance of the distributor affected not only by its own structure, but also by the upstream refrigerant flow state (i.e., the inlet flow pattern) and the factors of each downstream branch. Due to the limitation of the installation space in the refrigeration device, a bent inlet connecting pipe needs to be used to connect between the expansion valve and the inlet end of the distributor. Since the centrifugal forces received by the gas-liquid two-phase at the bent portion are different, the refrigerant undergoes phase separation at this place, resulting in an asymmetric inlet flow pattern of the distributor. This asymmetry is particularly obvious when the input mass flow rate of the refrigerant is small. For the congenital deficiency of the asymmetric refrigerant inlet flow pattern, it is extremely difficult for the existing distributors to improve it, which is also the main limiting factor for the existing distributors to further improve their performance. Therefore, some people have proposed a scheme to improve the inlet connecting pipe of the distributor to optimize the inlet flow pattern (such as Figure 1 shown), but this scheme increases the installation space of the inlet connecting pipe, making it difficult to be applicable to refrigeration devices with a small installation space; in addition, this optimization scheme also brings great difficulties to the processing and welding of the inlet connecting pipe.

[0060] In view of this, this embodiment provides a two-stage jet reflection mixing and diversion distributor that can organize and convert the inlet flow pattern before distribution. As Figure 2 shown, it includes a cavity 1, a liquid inlet pipe 2, a two-stage jet reflection mixing component 3, and multiple branch pipes 4. The cavity 1 has an inflow end 11 and an outflow end 12, and a plurality of diversion branch pipe holes 14 are distributed on the outflow end 12. The liquid inlet pipe 2 is connected to the inflow end 11 of the cavity to inject refrigerant into the cavity 1 to form a primary jet. The two-stage jet reflection mixing component 3 includes a primary reflection mixing plate 31, a secondary jet orifice plate 32, and a secondary reflection mixing plate 33 that are sequentially and spaced apart in the refrigerant flow direction within the cavity 1. Among them, the primary reflection mixing plate 31 is oppositely distributed to the inflow end 11 of the cavity to reflect and mix the refrigerant injected into the cavity 1, and a plurality of flow holes 311 are formed on the primary reflection mixing plate 31. The secondary jet orifice plate 32 and the primary reflection mixing plate 31 enclose a jet cavity 102, and a secondary jet hole 321 is formed on the secondary jet orifice plate 32. The refrigerant after being reflected and mixed by the primary reflection mixing plate 31 converges in the jet cavity 102 through the flow holes 311 and is jetted to the secondary reflection mixing plate 33 through the secondary jet hole 321. The secondary reflection mixing plate 33 is oppositely distributed to the secondary jet hole 321 and has a plurality of diversion holes 331 with the same number as the diversion branch pipe holes 14. Each diversion hole 331 is substantially coaxial with the corresponding diversion branch pipe hole 14. The secondary reflection mixing plate 33 reflects and mixes the refrigerant injected by the secondary jet hole 321, and then distributes it to the plurality of diversion branch pipe holes 14 through the diversion holes 331. The multiple branch pipes 4 are respectively welded and connected into the plurality of diversion branch pipe holes 14 on the outflow end 12 of the cavity.

[0061] In the two-stage jet reflection mixing and diversion distributor provided by this embodiment, the liquid inlet pipe 2 and the secondary jet hole 321 form a secondary jet. The liquid inlet pipe 2 injects the refrigerant into the cavity 1 once, disturbing the refrigerant flow pattern at the inlet of the cavity 1 and increasing the kinetic energy of the refrigerant so that the refrigerant can quickly develop into a dispersed flow pattern during the preliminary organization, providing a basis for the conversion of the refrigerant flow pattern from laminar at the inlet to a fully mixed dispersed flow pattern. The secondary jet hole 321 then increases the flow rate of the refrigerant after the flow pattern organization and conversion, so that the refrigerant can always maintain a uniformly mixed dispersed flow pattern during the distribution process, thereby improving the distribution uniformity. The following will combine Figures 2 to 10 to elaborate in detail on the structure and working principle of the two-stage jet reflection mixing and diversion distributor provided by this embodiment.

[0062] As Figure 2As shown in the figure, affected by the centrifugal force at the bending part of the liquid inlet pipe 2, the refrigerant input into the cavity 1 through the liquid inlet pipe 2 is in an asymmetric flow pattern of gas-liquid two-phase separation. The liquid inlet pipe 2 jets the refrigerant at a high speed into the cavity 1, and the high-speed refrigerant rebounds into the preliminary finishing cavity 101 enclosed by the first-stage reflection mixing plate 31 and the cavity inlet end 11 after being reflected by the first-stage reflection mixing plate 31. The reflection of the first-stage reflection mixing plate 31 promotes the collision of the gas-liquid two phases to preliminarily break up the liquid refrigerant into droplets; then, the refrigerant reflection beam and the incident beam moving in opposite directions form a turbulent flow in the preliminary finishing cavity 101, and the droplets are further broken up and scattered around, and the scattered droplets are distributed into the gas phase, causing the refrigerant to gradually develop into a uniformly mixed dispersed flow pattern. Then, the refrigerant enters the jet cavity 102 through multiple flow holes 311 on the first-stage reflection mixing plate 31. When the preliminarily sorted refrigerant flows through the flow holes 311, its flow rate increases, the liquid-phase mass flow rate increases with the increase of the liquid-phase flow rate, and the liquid film becomes thinner; the thinned liquid film breaks, causing the droplets to atomize into smaller shapes and disperse evenly into the gas phase, and the refrigerant gradually develops into a dispersed flow pattern in the jet cavity 102, thus realizing the sorting conversion from the inlet asymmetric flow pattern to the uniformly dispersed flow pattern.

[0063] After the flow pattern conversion, the refrigerant needs to be evenly distributed to each branch pipe 4. Since the distributor is usually installed vertically, the refrigerant needs to be distributed from bottom to top in the direction opposite to gravity to multiple branch pipes 4, and the refrigerant will be affected by both inertial force and gravity during the distribution process. In the gas-liquid two-phase refrigerant, the flow of the liquid-phase refrigerant mainly depends on inertial force and gravity. Too low refrigerant flow rate will cause the inertial force of the liquid-phase refrigerant to be less than its gravity, and the liquid phase in the refrigerant after the flow pattern sorting is extremely susceptible to gravity and will be separated from the gas phase again, and even part of the liquid-phase refrigerant will deposit and cannot be distributed to the liquid outlet side, thus seriously affecting the distribution uniformity. In order to prevent the gas-liquid two-phase segregation from occurring again in the subsequent distribution process of the refrigerant after the flow pattern sorting, in this embodiment, a second-stage jet hole 321 is provided on the second-stage jet orifice plate 32, and the refrigerant mixed and developed in the jet cavity 102 gradually converges on the second-stage jet hole 321 and is sprayed into the reflection mixing cavity 103 enclosed by the second-stage reflection mixing plate 33 and the second-stage jet orifice plate 32 after the pressure is reduced and the speed is increased through the second-stage jet hole 321. The high-speed refrigerant increases the inertial force of the liquid-phase refrigerant so that it can overcome the influence of gravity and follow the gas phase flow, and makes the two-phase refrigerant maintain the flow pattern after uniform mixing as much as possible.

[0064] The high-speed refrigerant entering the reflection mixing chamber 103 will continue to flow forward under the action of inertia and impact the secondary reflection mixing plate 33. The secondary reflection mixing plate 33 reflects the refrigerant, enhancing the collision degree of the gas-liquid two-phase. At the same time, a convection occurs between the reflected beam and the jet beam to further promote the mixing of the gas-liquid two-phase. The mixed refrigerant is evenly distributed to a plurality of diversion holes 331. In this embodiment, the number of the plurality of diversion holes 331 is set to be the same as the number of the shunt branch holes 14, and each diversion hole 331 is substantially coaxial with its corresponding shunt branch hole 14. This setting forms the shortest axial transmission path between the diversion holes 331 and the corresponding shunt branch holes 14, and the high-speed refrigerant output from the diversion holes 331 can quickly enter the corresponding shunt branch holes 14, maintaining the flow pattern of the refrigerant after mixing as much as possible to ensure the distribution uniformity. In addition, in this embodiment, after the refrigerant accelerated by the secondary jet holes 321 enters the reflection mixing chamber 103, a high-pressure vortex will be formed on the downstream side of the secondary jet hole plate 32, and this high-pressure vortex will accelerate the refrigerant to enter the diversion holes 331.

[0065] This embodiment provides a two-stage jet reflection mixing diversion distributor. By optimizing the inner cavity structure of the distributor to replace the existing liquid inlet pipe bending scheme, the asymmetric flow pattern at the refrigerant inlet is sorted into a uniform dispersed flow pattern to reduce the influence of the refrigerant inlet flow pattern on the distribution performance. The conversion of the refrigerant inlet flow pattern realized based on the optimization of the distributor structure enables the two-stage jet reflection mixing diversion distributor provided in this embodiment to be highly compatible with various refrigerant inlet working conditions and refrigeration equipment in different installation spaces. Specifically, the sorting and conversion of the inlet flow pattern by the two-stage jet reflection mixing diversion distributor eliminates the influence of the refrigerant inlet flow pattern on the performance of the distributor, and the layout of the liquid inlet side pipeline no longer needs to consider the gas-liquid mixing situation of the refrigerant in the liquid inlet pipe, thus greatly facilitating the processing, installation and welding of the liquid inlet side pipeline. In addition, compared with the large installation space required for bending the liquid inlet pipe, the optimization of the structure inside the distributor cavity 1 only slightly increases the axial length of the distributor. Therefore, it can be well applied to refrigeration equipment in different installation spaces, including household air conditioner indoor units with a narrow space of 1HP or 1.5HP.

[0066] The condition for the refrigerant to develop into a stable dispersed flow pattern is that the Froude number, which represents the ratio of the inertial force of the liquid-phase refrigerant to the gravitational force, is greater than 7. The inertial force of the liquid-phase refrigerant is related to the refrigerant flow rate, and the flow rate of the refrigerant is in turn related to the volume of the chamber it is in. Therefore, it is set that 0.6 ≤ V1 / V2 ≤ 1.5 between the volume V1 of the preliminary sorting chamber and the jet chamber V2; this setting precisely controls the degree of expansion of the refrigerant entering the jet chamber 102, ensuring that the liquid phase of the refrigerant still has sufficient inertial force to overcome the influence of gravity after entering the jet chamber 102, providing conditions for the refrigerant to be fully mixed in the jet chamber 102 and develop into a stable dispersed flow pattern. Similarly, to prevent the refrigerant ejected from the secondary jet holes 321 from affecting the refrigerant flow rate due to excessive expansion after entering the reflection mixing chamber 103, it is also set that 0.6 ≤ V2 / V3 ≤ 1.5 between the volume V2 of the jet chamber and the volume V3 of the reflection mixing chamber. The ratio settings of the volume V1 of the preliminary sorting chamber, the volume V2 of the jet chamber, and the volume V3 of the reflection mixing chamber enable the refrigerant to maintain a uniform and stable dispersed flow pattern during both the flow pattern sorting stage and the redistribution stage after sorting, so as to further improve the distribution uniformity. Preferably, 0.8 ≤ V1 / V2 ≤ 1.2 and 0.8 ≤ V2 / V3 ≤ 1.2 are set. However, the present utility model does not make any limitations in this regard.

[0067] Specifically, as Figure 3 shown, the volume V1 of the preliminary sorting chamber refers to the volume of the chamber enclosed by the plane where the upstream surface of the first-stage reflection mixing plate 31 near the flow-through hole 311 is located and the inner wall of the chamber inlet end 11, such as Figure 3 the volume of the chamber 101 enclosed by the dashed line in Figure 3 The volume V2 of the jet chamber refers to the volume of the chamber enclosed by the plane where the upstream surface of the secondary jet hole plate 32 is located and the downstream surface of the first-stage reflection mixing plate 31, such as Figure 3 the volume of the chamber 102 enclosed by the dash-dotted line in

[0068] In this embodiment, as Figure 4 shown, a first-stage reflection portion 312 opposite to the liquid outlet end of the liquid inlet pipe 2 is formed on the first-stage reflection mixing plate 31, and the first-stage reflection portion 312 is a plane reflection portion with a reflection surface close to a plane. At this time, the first-stage reflection mixing plate 31 is a plate structure with both the upstream surface and the downstream surface close to a plane and a circular cross-section. However, the present utility model does not make any limitations in this regard. In other embodiments, the first-stage reflection portion 312 may also be a first-stage reflection concave cavity with an opening facing the chamber inlet end, such as Figure 5A shown; at this time, the downstream surface of the first-stage reflection mixing plate 31 is still close to a plane.

[0069] In this embodiment, a plurality of flow holes 311 are annularly and equidistantly distributed around the axis of the cavity 1 on the plane of the first-stage reflection mixing plate 31 outside the first-stage reflection part 312. The sum of the flow areas S1 of the plurality of flow holes 311 on the first-stage reflection mixing plate 31 and the cross-sectional area S0 of the cavity where the first-stage reflection mixing plate 31 is located satisfy: 0.1 ≤ S1 / S0 ≤ 0.45. This area ratio limits the degree of pressure reduction and speed increase of the refrigerant by the flow holes 311, increases the flow rate of the refrigerant entering the jet cavity 102, so that the refrigerant develops into a stable dispersed flow pattern while avoiding the problem of excessive pressure loss of the refrigerant due to excessive pressure reduction. Specifically, the area ratio of S1 / S0 can be set to 0.15, 0.2, 0.25, 0.3, 0.35, 0.4, etc.

[0070] As Figure 4 shown, the flow holes 311 on the first-stage reflection mixing plate 31 in this embodiment are through holes with substantially the same inner diameter. However, the present invention does not make any limitation in this regard. In other embodiments, the flow holes 311 can also be inclined through holes with an inner diameter gradually decreasing along the refrigerant flow direction, as Figure 5B shown. Or, as Figure 5C shown, the flow holes 311 can be set as flanging holes with the inner wall generatrix in an arc shape and the hole diameter gradually decreasing along the refrigerant flow direction; or, a straight hole section with a substantially constant hole diameter can be added at the end of the flanging hole, that is, the inner wall generatrix of the flow hole is a combination of an arc shape and a straight line. In addition, in other embodiments, the flow holes 311 can also be set as arc bubble holes with the hole wall arcuately protruding towards one or both sides of the first-stage reflection mixing plate 31, as Figure 5D and Figure 5E shown.

[0071] As Figure 2 shown, the secondary jet holes 321 on the secondary jet orifice plate 32 are flanging holes with the hole wall extending towards the secondary reflection mixing plate 33. However, the present invention does not make any limitation in this regard. In other embodiments, the secondary jet holes can also be through holes with a substantially constant hole diameter, or through holes with a hole diameter gradually decreasing along the refrigerant flow direction (as Figure 6A shown). Or, a straight section can be added on the basis of the flanging hole, as Figure 6B shown.

[0072] In this embodiment, as Figure 2 and Figure 7As shown in the figure, a secondary reflection part 332 opposite to the secondary jet hole 321 is formed on the secondary reflection mixing plate 33. A plurality of diversion holes 331 are annularly distributed around the axis of the cavity 1 on the plane of the secondary reflection mixing plate 33 outside the secondary reflection part 332. The secondary reflection part 332 is a secondary reflection concave cavity with an opening facing the secondary jet hole 321. The bottom wall of the secondary reflection concave cavity reflects the refrigerant ejected from the secondary jet hole 321. After reflection, the refrigerant collides violently in the secondary reflection concave cavity, further enhancing the degree of two-phase flow disorder to promote the full mixing of the refrigerant. In this embodiment, the secondary reflection concave cavity formed by the secondary reflection part 332 is a cylindrical cavity with a square contour line in the longitudinal section. However, the present invention does not make any limitation in this regard. In other embodiments, the shape of the secondary reflection concave cavity may also be a prism with a square contour line in the longitudinal section, a frustum of a cone or a prism with a trapezoidal contour line in the longitudinal section, a cone or a pyramid with a triangular contour line in the longitudinal section, and one or more combinations of partial circles in the longitudinal section contour line; such as a combination of a cylinder and a partial sphere, a combination of a frustum of a cone and a partial sphere, a combination of a prism and a partial sphere, etc.

[0073] In this embodiment, the secondary reflection part 332 protrudes and extends towards the outflow end 12 of the cavity to form a secondary reflection concave cavity. This setting makes the downstream surface of the secondary reflection mixing plate 33 a curved surface structure with a convex middle part. An annular diversion cavity 104 is enclosed between the downstream surface of the secondary reflection part 332 and the inner peripheral wall of the cavity 1. This setting can reduce the volume of the diversion cavity 104 so that the refrigerant maintains a high-speed dispersed flow pattern and is quickly distributed into a plurality of diversion branch holes 14. Further, when the longitudinal section contour line of the secondary reflection concave cavity is square or trapezoidal, the vertical distance H between the extended top end of the secondary reflection part 332 and the inner bottom wall of the outflow end 12 of the cavity satisfies: 0 ≤ H ≤ 3 mm. Based on the determined height H0 of the diversion cavity 104 and the inner diameter of the cavity 1, the setting of the vertical distance H realizes the precise control of the volume in the diversion cavity 104, effectively avoiding the gas-liquid separation of the dispersed refrigerant due to the too large diversion cavity 104, and further improving the refrigerant distribution uniformity. Preferably, H is set to 0, that is, the extended top end of the secondary reflection concave cavity (secondary reflection part 332) abuts against the inner bottom wall of the outflow end 12 of the cavity, as Figure 2 shown. However, the present invention does not make any limitation in this regard. In other implementations, as Figure 8 shown, it is also possible to set that the extended top end of the secondary reflection concave cavity (secondary reflection part 332) does not abut against the inner bottom wall of the outflow end of the cavity, but at this time the vertical distance H is also less than or equal to 3 mm.

[0074] In the two-stage jet reflection mixing and diversion distributor provided in this embodiment, the liquid inlet pipe 2 forms a primary jet to increase the refrigerant flow rate at the inlet end 11 of the cavity, enhance the turbulence degree of the inlet refrigerant, and increase the refrigerant kinetic energy, so that the inlet refrigerant quickly develops into a dispersed flow pattern. To further increase the primary jet velocity of the refrigerant, this embodiment sets the liquid inlet pipe 2 to include a main body section 21 with a substantially constant inner diameter D0 and a jet section 22 located downstream of the main body section 21 and having a relatively reduced inner diameter compared to the main body section 21. The primary jet velocity of the refrigerant is increased based on the jet section 22 with a smaller inner diameter. However, the present utility model does not make any limitation in this regard. In other embodiments, when the primary jet velocity provided by the liquid inlet pipe 2 with a substantially consistent inner diameter is sufficient to meet the refrigerant distribution uniformity, the jet section may not need to be provided on the liquid inlet pipe 2, that is, the inner diameter of the entire liquid inlet pipe 2 is substantially consistent.

[0075] As Figure 2 shown, in this embodiment, the jet section 22 is a straight section integrally formed with the main body section 21, and the inner diameter D1 of the jet section is substantially constant within its length range and is smaller than the inner diameter D0 of the main body section. However, the present utility model does not make any limitation in this regard. In other embodiments, as Figure 9A shown, a primary jet orifice plate 23 may also be provided in the liquid inlet pipe 2. A primary jet orifice 230 with a diameter smaller than the inner diameter D0 of the main body section is formed on the primary jet orifice plate 23. The minimum inner diameter of the primary jet orifice 230 is the minimum inner diameter of the jet section 22, and the location where the primary jet orifice plate 23 is located forms the jet section 22. Specifically, the primary jet orifice 230 may be a flanged orifice, a straight orifice with a substantially constant inner diameter (as Figure 9B shown) or an inclined orifice, or any combination thereof. Or, as Figure 9C shown, the jet section 22 is set as a Venturi tube section, and the throat inner diameter of the Venturi tube section is the minimum inner diameter D1 of the jet section 22. In addition, in other embodiments, a plurality of Venturi tube sections may also be provided downstream of the main body section. In this structure, the throat inner diameter of the Venturi tube section closest to the inlet end 11 of the cavity is the minimum inner diameter of the jet section.

[0076] Furthermore, as Figure 2 shown, the aperture D2 at the liquid outlet end of the secondary jet orifice 321 is set to be less than or equal to the minimum inner diameter D1 of the jet section 22 on the liquid inlet pipe. A primary jet is formed at the jet section 22, and a secondary jet is formed at the secondary jet orifice 321. The two weaken the gravity influence of the refrigerant during the flow pattern sorting and uniform distribution process in a way of gradually increasing the refrigerant flow rate, so that the refrigerant can always maintain a uniformly mixed dispersed flow pattern.

[0077] In this embodiment, as Figure 3As shown, a liquid inlet pipe assembly hole 13 is formed on the cavity inlet end 11. The end of the jet section 22 is welded and connected to the inner part of the assembly straight section on the liquid inlet pipe assembly hole 13. The end of the jet section 22 is the liquid outlet end of the liquid inlet pipe 2. However, the present utility model does not make any limitation in this regard. In other embodiments, the input pipe may also be integrally formed with the cavity where the liquid inlet pipe assembly hole is located. Or, as Figure 9C shown, for the liquid inlet pipe structure where the jet section 22 is a Venturi tube section, a liquid inlet pipe assembly hole ( Figure 9C in which the liquid inlet pipe 2 is assembled, so it is not marked) can also be set as a through hole without a welded assembly straight section. A gradually expanding section 24 with an arc-shaped curve on the outer wall generatrix is formed on the Venturi tube section and is located downstream of the throat. The gradually expanding section 24 extends into the preliminary finishing cavity 101 through the liquid inlet pipe assembly hole, and the outer wall of the gradually expanding section 24 is welded to the inner wall of the cavity inlet end 11 in a surface contact manner.

[0078] As Figure 2 and Figure 10 shown, for multiple branch pipes 4 welded and connected in a plurality of shunt branch pipe holes 14, each branch pipe 4 includes a first pipe section 41 and a second pipe section 42 located downstream of the first pipe section 41 and with an inner diameter reduced relative to the inner diameter at the downstream end of the first pipe section 41. The difference △d between the inner diameter d11 at the downstream end of the first pipe section 41 and the inner diameter d12 at the downstream end of the second pipe section 42 is: 0.1 mm ≤ △d ≤ 3.5 mm. The first pipe section 41 with a larger inner diameter increases the refrigerant flow rate distributed into each branch pipe 4 and reduces the distribution resistance of the refrigerant, while the second pipe section 42 with a relatively smaller inner diameter can increase the refrigerant flow velocity to meet the performance requirements of the rear heat exchange device. On this basis, the inner diameter difference △d precisely controls the pressure reduction and speed increase degree of the refrigerant by the second pipe section 42, avoiding excessive pressure loss of the refrigerant due to excessive speed increase.

[0079] Furthermore, a damping section 411 extending bent towards one side relative to the center line of the shunt branch pipe hole 14 is formed on the first pipe section 41. An included angle θ is formed between the axis at the upstream end of the damping section 411 and the axis at the downstream end of the damping section 411, and 90° ≤ θ ≤ 175°. The setting of the damping section 411 makes the second pipe section 42 no longer coaxial with the center line of the shunt branch pipe hole 14. When there is a pressure wave downstream and it oscillates upstream, the damping section 411 reflects and absorbs part of the pressure wave and changes the propagation direction of the remaining pressure wave to make it decay rapidly, effectively avoiding the influence of the downstream pressure wave on the upstream shunt branch pipe hole 14 to further improve the distribution performance.

[0080] In this embodiment, the branch pipe 4 further includes a branch section 43 welded and connected to the first pipe section 41, and the second pipe section 42 is located on the branch section 43. Specifically, as Figure 10As shown, the upstream end of the branch section 43 is sleeved and connected to the downstream end of the first pipe section 41, and a second pipe section 42 with a gradually decreasing inner diameter is formed downstream of the socket connection of the branch section 43. However, the present utility model does not make any limitation in this regard. In other embodiments, the upstream end of the branch section 43 can also be internally sleeved and welded to the downstream end of the first pipe section 41; at this time, the second pipe section 42 is still a structure with a gradually decreasing inner diameter located downstream of the socket connection of the branch section 43, as Figure 11A shown.

[0081] Figure 11B , Figure 11C and Figure 11D are the schematic structural diagrams of the branch pipes provided by another embodiment of the present utility model. Figure 11B In this case, the first pipe section 41, the second pipe section 42, and the branch section 43 are integrally formed; Figure 11C In this case, the first pipe section 41 and the second pipe section 42 are integrally formed, and the branch section 43 is welded to the end of the second pipe section 42. Figure 11D In this case, based on the inner diameter difference between the downstream end of the first pipe section 41 and the upstream end of the branch section 43, the second pipe section 42 is directly formed at the socket connection of the first pipe section 41 and the branch section 43. In addition, multiple second pipe sections can also be provided at the downstream end of the first pipe section, and the branch section 43 can be set as a straight pipe or a bent pipe according to actual applications.

[0082] Although this embodiment is described by taking the attenuation section 411 formed on the first pipe section 41 as an example. However, the present utility model does not make any limitation in this regard. In other embodiments, the attenuation section may not be provided on the first pipe section 41. At this time, the first pipe section 41 is a straight pipe, as Figure 11E shown.

[0083] Furthermore, for the structure of the second pipe section 42, in other embodiments, the second pipe section 42 can also be provided to include a tapered section and a maintaining straight section located downstream of the tapered section and having a certain length L42. The inner diameter of the maintaining straight section is close to the inner diameter at the downstream end of the tapered section and is basically unchanged within the length L42, as Figure 11F shown. Or, an orifice plate 44 is added at the flared connection of the first pipe section 41 or the branch section 43, and the refrigerant is accelerated by the through holes 441 on the orifice plate 44; at this time, the pipe section where the orifice plate 44 is located is the second pipe section 42, as Figure 11G shown.

[0084] On the other hand, this embodiment also provides a heat exchange device including the above-mentioned secondary jet reflection mixing and diversion distributor. Specifically, the heat exchange device is a condenser or an evaporator.

[0085] On the other hand, this embodiment also provides a refrigeration device, which includes the above-mentioned heat exchanger assembly.

[0086] Embodiment Two

[0087] This embodiment is basically the same as Embodiment 1 and its variations, except that: the structure of the primary reflection mixing plate 31 is different.

[0088] As Figure 12 and Figure 13 shown, the primary reflection part 312 protrudes and extends toward the side where the secondary jet orifice plate 32 is located to form a primary reflection concave cavity with an opening facing the inflow end 11 of the cavity. This setting makes the downstream surface of the primary reflection mixing plate 31 a curved surface structure with a convex middle; in this structure, the jet cavity 102 refers to the cavity enclosed by the downstream surface of the curved primary reflection mixing plate 31 and the upstream surface of the secondary jet orifice plate 32, such as Figure 13 the cavity 102 enclosed by the center dash line.

[0089] Compared with Embodiment 1, this embodiment sets a primary reflection concave cavity at the primary reflection part 312 to enhance the preliminary sorting effect of the refrigerant flow pattern. Specifically, the refrigerant with an asymmetric flow pattern enters the primary reflection concave cavity formed by the primary reflection part 312, and after being reflected by the bottom wall of the primary reflection concave cavity, it collides violently in the primary reflection concave cavity to break up the liquid-phase refrigerant into droplets. The primary reflection concave cavity provides a mixing space for the refrigerant during the maximum kinetic energy stage after reflection, enhances the degree of disorder to promote the gas-liquid two-phase mixing. At the same time, when the input refrigerant mass flow rate is large and the flow velocity is fast, the setting of the primary reflection concave cavity can also effectively reduce the influence of the reflection force on the input refrigerant, and avoid the refrigerant reflux in the inlet pipe caused by too large reflection force.

[0090] In this embodiment, the primary reflection concave cavity formed by the protrusion and extension of the primary reflection part 312 is a cylindrical cavity with a square contour line in the longitudinal section, and the longitudinal section refers to the section along the depth direction of the primary reflection concave cavity. However, the present invention makes no limitation in this regard. In other embodiments, the shape of the primary reflection concave cavity can also be a prism with a square contour line in the longitudinal section, a frustum of a cone or a prism with a trapezoidal contour line in the longitudinal section (such as Figure 14A ), a cone or a pyramid with a triangular contour line in the longitudinal section (such as Figure 14B ), and a part of a circular contour line in the longitudinal section (i.e., a part of a spherical shape, such as Figure 14C ) or a combination of one or more of them. Such as a combination of a cylindrical shape and a part of a spherical shape (such as Figure 14D shown), a combination of a frustum of a cone and a part of a spherical shape, a combination of a prism and a part of a spherical shape, etc.

[0091] Embodiment 3

[0092] This embodiment is basically the same as Embodiment 1 and its variations, except that: the structure of the secondary reflection mixing plate 33 is different.

[0093] As Figure 15As shown, in this embodiment, the downstream surface of the secondary reflection mixing plate 33 (i.e., the surface close to the cavity outflow end 12 side) is close to a plane. The two-stage jet reflection mixing and diversion distributor further includes an annular flow channel member 5 disposed between the secondary reflection mixing plate 33 and the cavity outflow end 12 and located on the inner periphery of the plurality of shunt branch holes 14. The annular flow channel member 5 is a rotating member formed by protruding and extending from the inner bottom wall of the cavity outflow end 12 towards the direction of the secondary reflection mixing plate 33 and rotating around the axis of the cavity 1. An annular flow channel communicating with the plurality of shunt branch holes 14 is defined between the annular flow channel member 5 and the inner wall of the cavity 1. The cross-section of the annular flow channel member 5 is substantially unchanged or gradually decreases along the extension direction.

[0094] Similar to the secondary reflection part 332 in Embodiment 1 protruding and extending towards the cavity outflow end 12 to form a secondary reflection cavity, in this embodiment, the setting of the annular flow channel member 5 can reduce the volume of the shunt cavity 104 to prevent gas-liquid separation of the mixed homogeneous refrigerant in the shunt cavity 104. At the same time, the annular flow channel defined by the annular flow channel member 5 and the inner peripheral wall of the cavity 1 can also guide the homogeneous refrigerant so that it can be evenly distributed into the plurality of shunt branch holes 14 distributed in a ring shape, thereby realizing the symmetrical diversion of the refrigerant.

[0095] As Figure 15 shown, the annular flow channel member 5 is a cone with a cross-section gradually decreasing along its extension direction. The vertical distance H1 from the extension top end of the annular flow channel member 5 to the downstream surface of the secondary reflection mixing plate 33 satisfies: 1mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the shunt cavity, that is, the vertical distance from the center of the inner bottom wall of the cavity outflow end 12 to the downstream surface of the secondary reflection mixing plate 33. However, the present utility model does not make any limitation in this regard. In other embodiments, the annular flow channel member may also be a frustum of a cone. Or, as Figure 16 shown, the annular flow channel member 5 is an annular sleeve with a cross-section substantially unchanged along its extension direction. The extension top end of the annular sleeve abuts against the secondary reflection part 332 on the secondary reflection mixing plate 33. In other embodiments, the annular flow channel member can also be set as a combination of a cone and a spacer sleeve.

[0096] In summary, in the two-stage jet reflection mixing and diversion distributor provided by the present utility model, the liquid inlet pipe injects the refrigerant with an asymmetric inlet flow pattern at a high speed into the cavity in the form of a primary jet; disturbing the inlet refrigerant flow pattern and increasing the kinetic energy of the refrigerant, providing a basis for organizing the refrigerant into a uniformly mixed dispersed flow pattern. After being reflected by the primary reflection mixing plate, the refrigerant injected at a high speed forms a turbulent flow with the incident jet beam in the preliminary organization chamber surrounded between the primary reflection mixing plate and the inner wall of the inflow end of the cavity, enhancing the degree of two-phase flow disorder so that the refrigerant gradually develops into a dispersed flow pattern. The refrigerant after preliminary development enters the jet cavity, and after being fully mixed and developed in the jet cavity, it converges at the secondary jet holes. The secondary jet holes reduce the pressure and increase the speed of the refrigerant, increasing the refrigerant flow rate so that it can always maintain the fully mixed refrigerant flow pattern in the reflection mixing cavity surrounded by the secondary reflection mixing plate and the secondary jet hole plate, thereby improving the distribution performance. Further, by precisely controlling the volume ratios of the preliminary organization chamber, the jet cavity and the reflection mixing cavity in the subsequent distribution process of the inlet refrigerant, the refrigerant is fully developed into a stable dispersed flow pattern in the jet cavity and can always maintain this flow pattern in the subsequent distribution process, greatly improving the distribution performance of the distributor.

[0097] The two-stage jet reflection mixing and diversion distributor provided by the present utility model integrates the organization of the refrigerant inlet flow pattern and the uniform distribution of the refrigerant after organization. The distributor with this structure eliminates the need for any adjustment and optimization on the liquid inlet pipe, which not only greatly facilitates the processing, installation and welding of the liquid inlet pipe, but also significantly improves the applicability of the distributor so that it can be well compatible with various different specifications of refrigeration equipment.

[0098] Although the present utility model has been disclosed above with the preferred embodiments, it is not intended to limit the present utility model. Any person skilled in this art can make some modifications and refinements without departing from the spirit and scope of the present utility model. Therefore, the protection scope of the present utility model shall be subject to the scope claimed in the claims.

Claims

1. A two-stage jet reflection mixing and diversion distributor, characterized in that Comprising: A cavity having an inflow end and an outflow end, and a plurality of shunt branch pipe holes are distributed on the outflow end; An inlet pipe connected to the inflow end of the cavity to inject refrigerant into the cavity to form a primary jet; A two-stage jet reflection and mixing component including a primary reflection and mixing plate, a secondary jet orifice plate, and a secondary reflection and mixing plate that are sequentially and spaced apart along the refrigerant flow direction in the cavity; The primary reflection and mixing plate is oppositely distributed relative to the inflow end of the cavity to reflect and mix the refrigerant injected into the cavity, and a plurality of flow holes are formed on the primary reflection and mixing plate; The secondary jet orifice plate and the primary reflection and mixing plate enclose a jet cavity, and a secondary jet hole is formed on the secondary jet orifice plate. The refrigerant reflected and mixed by the primary reflection and mixing plate is collected in the jet cavity through the flow holes and jets to the secondary reflection and mixing plate through the secondary jet hole; The secondary reflection and mixing plate is oppositely distributed relative to the secondary jet hole and has a plurality of diversion holes equal in number to the shunt branch pipe holes. Each diversion hole is substantially coaxial with the corresponding shunt branch pipe hole. The secondary reflection and mixing plate reflects and mixes the refrigerant injected through the secondary jet hole and distributes it to the plurality of shunt branch pipe holes through the diversion holes; A plurality of branch pipes are respectively welded and connected into the plurality of shunt branch pipe holes.

2. The two-stage jet reflection mixing and diversion distributor according to claim 1, wherein A primary reflection portion opposite to the liquid outlet end of the inlet pipe is formed on the primary reflection and mixing plate; The primary reflection portion is a planar reflection portion with a reflection surface close to a plane; Alternatively, the primary reflection portion is a primary reflection concave cavity with an opening facing the inflow end of the cavity, and the longitudinal cross-sectional contour line of the primary reflection concave cavity is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

3. The two-stage jet reflection mixing and diversion distributor according to claim 2, characterized in that, The primary reflection portion protrudes and extends towards the side where the secondary jet orifice plate is located to form a primary reflection concave cavity with an opening facing the inflow end of the cavity.

4. The two-stage jet reflection mixing and diversion distributor according to claim 2, characterized in that, On the primary reflection and mixing plate, a plurality of flow holes are evenly distributed in a ring on the plane of the primary reflection and mixing plate outside the primary reflection portion.

5. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, The total flow area S1 of the plurality of flow holes on the primary reflection and mixing plate and the inner cross-sectional area S0 of the cavity where the primary reflection and mixing plate is located satisfy: 0.1 ≤ S1 / S0 ≤ 0.

45.

6. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, The flow holes on the primary reflection and mixing plate and the diversion holes on the secondary reflection and mixing plate are each one or a combination of a through hole, a flanged hole, and an arc bubble hole; The secondary jet hole is a through hole or a flanged hole extending towards the side where the secondary reflection and mixing plate is located.

7. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, A secondary reflection portion opposite to the secondary jet hole is formed on the secondary reflection and mixing plate, and a plurality of diversion holes are annularly and equally spaced around the cavity axis on the plane of the secondary reflection and mixing plate outside the secondary reflection portion; The secondary reflection portion is a planar reflection portion with a reflection surface close to a plane; Alternatively, the secondary reflection portion is a secondary reflection concave cavity with an opening facing the secondary jet hole, and the longitudinal cross-sectional contour line of the secondary reflection concave cavity is one or a combination of a square, a trapezoid, a triangle, or a partial circle.

8. The two-stage jet reflection mixing and diversion distributor according to claim 7, characterized in that, The secondary reflection portion protrudes and extends towards the outflow end of the cavity, forms a secondary reflection concave cavity on the side facing the secondary jet hole, and encloses an annular shunt cavity with the inner wall of the cavity at the outflow end of the cavity.

9. The two-stage jet reflection mixing and diversion distributor according to claim 8, characterized in that When the longitudinal cross-sectional contour line of the secondary reflection concave cavity is a square or a trapezoid, the vertical distance H from the extended top end of the secondary reflection portion to the inner bottom wall of the outflow end of the cavity satisfies: 0 ≤ H ≤ 3 mm.

10. The two-stage jet reflection mixing and diversion distributor according to claim 1, wherein, The downstream surface of the secondary reflection mixing plate is close to a plane. The two-stage jet reflection mixing and diversion distributor further includes an annular flow channel member disposed between the secondary reflection mixing plate and the outlet end of the cavity and on the inner periphery of a plurality of shunt branch pipe holes. The annular flow channel member is a rotary member formed by protruding and extending from the inner bottom wall of the cavity outlet end towards the direction of the secondary reflection mixing plate and rotating around the cavity axis. An annular flow channel communicating with a plurality of shunt branch pipe holes is enclosed between the annular flow channel member and the inner wall of the cavity, and the cross-section of the annular flow channel member is substantially unchanged or gradually decreases along the extension direction.

11. The two-stage jet reflection mixing and diversion distributor according to claim 10, characterized in that, The annular flow channel member is a cone or a frustum of a cone with a cross-section gradually decreasing along its extension direction. The vertical distance H1 from the extended top end of the annular flow channel member to the secondary reflection mixing plate satisfies: 1 mm ≤ H1 ≤ 2H0 / 3, where H0 is the vertical distance from the center of the inner bottom wall of the cavity outlet end to the downstream surface of the secondary reflection mixing plate.

12. The two-stage jet reflection mixing and diversion distributor according to claim 10, characterized in that, The annular flow channel member is an annular sleeve with a cross-section substantially unchanged along its extension direction. The extended top end of the annular sleeve abuts against the secondary reflection portion on the secondary reflection mixing plate.

13. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, The chamber volume V1 enclosed by the primary reflection mixing plate and the inner wall of the cavity inlet end, the jet chamber volume V2 enclosed by the secondary jet orifice plate and the primary reflection mixing plate, and the chamber volume V3 enclosed by the secondary reflection mixing plate and the secondary jet orifice plate satisfy: 0.6 ≤ V1 / V2 ≤ 1.5, 0.6 ≤ V3 / V2 ≤ 1.

5.

14. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, The liquid inlet pipe includes a main body section with a substantially unchanged inner diameter and a jet section located downstream of the main body section and with an inner diameter reduced relative to the main body section.

15. The two-stage jet reflection mixing and diversion distributor according to claim 14, characterized in that, The aperture diameter at the liquid outlet end of the secondary jet holes on the secondary jet orifice plate is less than or equal to the minimum inner diameter of the jet section on the liquid inlet pipe.

16. The two-stage jet reflection mixing and diversion distributor according to claim 14, characterized in that, A primary jet orifice plate is disposed in the liquid inlet pipe. Primary jet holes with aperture diameters smaller than the inner diameter of the main body section are formed on the primary jet orifice plate. The minimum aperture diameter of the primary jet holes is the minimum inner diameter of the jet section, and the location where the primary jet orifice plate is located forms the jet section; Alternatively, the jet section is a Venturi tube section, and the inner diameter of the throat of the Venturi tube section is the minimum inner diameter of the jet section; Alternatively, the jet section is a straight section with an inner diameter reduced relative to the main body section.

17. The two-stage jet reflection mixing and diversion distributor according to claim 1, characterized in that, 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 the inner diameter at the downstream end of the first pipe section. The difference △d between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1 mm ≤ △d ≤ 3.5 mm.

18. The two-stage jet reflection mixing and diversion distributor according to claim 17, characterized in that, An attenuation section is formed on the first pipe section and bends and extends towards one side relative to the center line of the shunt branch pipe hole. An included angle θ is formed between the axis at the upstream end of the attenuation section and the axis at the downstream end of the attenuation section, and 90° ≤ θ ≤ 175°. Based on the attenuation section, the axis of the second pipe section intersects the center line of the shunt branch pipe hole; Alternatively, the first pipe section is a straight pipe.

19. The two-stage jet reflection mixing and diversion distributor according to claim 17, characterized in that, Each branch pipe further includes a branch section. The second pipe section is a tapered structure integrally formed with the first pipe section and with a gradually decreasing inner diameter. The branch section is welded to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed; Alternatively, the branch section is sleeved and welded to the first pipe section, and the sleeved and welded part forms the second pipe section; Alternatively, the branch section is socket-welded to the first pipe section, and the second pipe section is formed on the branch section.

20. A heat exchange device, characterized in that, Comprising the two-stage jet reflection mixing and diversion distributor according to any one of claims 1 to 19.

21. An air conditioner, characterized in that, Comprising the heat exchange device according to claim 20.

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