Novel venturi type flow divider, heat exchange device and refrigeration equipment

Abstract

The utility model provides a novel venturi type flow divider, heat exchange device and refrigeration equipment, the venturi type flow divider comprises a body, a runner forming piece, a liquid inlet pipe and a plurality of branch pipes, the inner wall of the liquid inlet end of the body obliquely extends towards the liquid outlet end of the body, the runner forming piece is arranged in a flow dividing cavity of the body and protrudes towards the direction of a liquid inlet pipe assembling hole, and the branch pipes are arranged in the body. The cross section of the flow channel forming piece is gradually reduced in the protruding direction, and an annular flow channel is defined by the flow channel forming piece and the inner wall of the flow dividing cavity. The liquid inlet pipe is a circular pipe fitting with basically consistent wall thickness and comprises venturi pipe sections, and each venturi pipe section comprises a gradually-shrinking section with gradually-decreasing inner diameter, a throat straight section with basically consistent inner diameter and a gradually-expanding section with gradually-increasing inner diameter which are distributed in sequence. Each branch pipe comprises a first pipe section and a second pipe section, and the difference d between the inner diameter d11 of the downstream end of the first pipe section and the inner diameter d12 of the downstream end of the second pipe section is larger than or equal to 0.1 mm and smaller than or equal to 3.5 mm.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigerant distribution, and particularly relates to a novel Venturi shunt, a heat exchange device and a refrigeration equipment. Background Art

[0002] Existing air conditioner heat exchangers usually adopt a multi-flow path design. To improve the heat exchange efficiency, a shunt is needed to evenly distribute the two-phase refrigerant after throttling by an expansion valve to each branch of the heat exchanger. Traditional shunts are mostly made of copper materials. To reduce the cost of the shunt, some shunts made of stainless steel materials have emerged on the market. However, the existing stainless steel shunts generally have the problem of poor shunt uniformity. For this reason, Chinese Patent CN219494466U proposes a stainless steel liquid separation head assembly that shunts and guides the refrigerant based on a guide head. Compared with the existing stainless steel shunts, this structure can greatly improve the shunt uniformity, but there is still a certain gap compared with the traditional brass Venturi shunt with excellent performance. There are two main reasons for the uneven refrigerant shunt. One is the uneven shunt caused by the structure of the shunt itself, and the other is the influence of the connecting pipes of the shunt. The connecting pipes include an inlet connecting pipe and an outlet multi-branch pipe. The stainless steel liquid separation head assembly proposed in Chinese Patent CN219494466U mainly focuses on the improvement of the structure of the liquid separation head body, and does not deeply study the influence of the shunt pipe connection, especially the influence of the outlet branch on the shunt uniformity.

[0003] Limited by the installation space inside the air conditioner, the inlet connecting pipe of the shunt usually needs to be bent into an L-shaped structure. When the refrigerant passes through the bent part, due to the large density and viscosity of the liquid-phase fluid, the centrifugal force it receives is greater than that of the gas-phase refrigerant, so that the liquid-phase refrigerant accumulates on the outer side of the bent section, while the gas-phase refrigerant accumulates on the inner side of the bent section. The separation of the gas-liquid two phases leads to an asymmetric flow pattern at the inlet of the shunt, which seriously affects the performance of the shunt. To improve the refrigerant inlet flow pattern, some people also propose to process a jet section 100 with a reduced inner diameter at the inlet end of the brass shunt body, as shown in Figure 1A and Figure 1B shown. At present, the jet section 100 on the shunt body can only be formed by metal cutting. This forming method not only has high processing difficulty, high cost, but also is difficult to ensure the consistency after processing, thus greatly limiting the application of this type of shunt.

[0004] In the case of the outlet multi-branch pipes, considering problems such as welding blockage, welding deformation, and leakage, it is desired to use branch pipes with larger diameters. However, increasing the diameter of the branch pipes will reduce the flow velocity of the refrigerant in each flow path of the heat exchanger. The reduction of the refrigerant flow velocity in the branch pipes will in turn affect the flow state of the upstream refrigerant, reduce the refrigerant flow velocity in the flow divider (and even the inlet connecting pipe), exacerbate the gas-liquid two-phase separation, and deteriorate the flow dividing performance. In addition, since multiple branch pipes of the flow divider are connected to multiple branches of the heat exchanger, the reduction of the refrigerant flow velocity in the branch pipes will also affect the heat transfer temperature difference and irreversible loss of the heat exchanger, thereby leading to a decrease in the energy efficiency of the heat exchanger.

[0005] As described above, the performance of the flow divider is jointly affected by factors such as the refrigerant inlet flow pattern, the structure of the flow divider body, and the flow state of the refrigerant in each branch pipe after flow division. The negative impact of any one factor may offset the effects brought about by the improvement of other factors. Therefore, it is urgent to optimize the structure of the flow divider and its connecting pipelines as a whole to comprehensively improve the flow dividing performance. Utility Model Content

[0006] In order to overcome the deficiencies of the prior art, the present utility model provides a novel Venturi-type flow divider, a heat exchange device, and a refrigeration device with excellent flow dividing performance.

[0007] To achieve the above object, the present utility model provides a novel Venturi-type flow divider, which includes a body, a flow path forming member, a liquid inlet pipe, and multiple branch pipes. The body includes a liquid inlet end and a liquid outlet end. The inner wall of the liquid inlet end extends obliquely towards the liquid outlet end of the body, and the generatrix of its inner wall is an arc or an inclined straight line. A liquid inlet pipe assembly hole is formed on the liquid inlet end of the body, and a plurality of flow dividing holes are formed on its liquid outlet end. A flow dividing cavity communicating with the liquid inlet pipe assembly hole and the plurality of flow dividing holes is formed inside the body. The flow path forming member is arranged in the flow dividing cavity and is located inside the circumference of the plurality of flow dividing holes. The flow path forming member is a rotating member formed by protruding from the inner bottom wall of the liquid outlet end of the body towards the direction where the liquid inlet pipe assembly hole is located and rotating around the axis of the body. An annular flow path communicating with the plurality of flow dividing holes is enclosed between the flow path forming member and the inner wall of the flow dividing cavity, and the cross-section of the flow path forming member gradually decreases along the protruding direction. The liquid inlet pipe is a circular pipe fitting with a substantially uniform 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 gradually decreasing section with a gradually decreasing inner diameter, a throat straight section with a substantially uniform inner diameter, and a gradually increasing section with a gradually increasing inner diameter, which are distributed in sequence along the refrigerant flow direction. The plurality of branch pipes are respectively welded and connected to the plurality of flow dividing holes on the body. 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: 0.1mm ≤ △d ≤ 3.5mm.

[0008] According to an embodiment of the present utility model, two Venturi tube segments in series are formed on the liquid inlet pipe, namely an upstream Venturi tube segment and a downstream Venturi tube segment, and the inner diameter of the throat straight section of the downstream Venturi tube segment is less than or equal to the inner diameter of the throat straight section of the upstream Venturi tube segment.

[0009] According to an embodiment of the present utility model, the liquid inlet pipe further includes a reduced-diameter orifice plate disposed downstream of the Venturi tube segment. A reduced-diameter orifice is formed on the reduced-diameter orifice plate. The reduced-diameter orifice includes a tapered orifice section with a gradually decreasing aperture along the refrigerant flow direction and a throat orifice section located downstream of the tapered orifice section with a substantially constant aperture.

[0010] According to an embodiment of the present utility model, an attenuation section that bends and extends toward one side relative to the center line of the shunt hole is formed on the first pipe segment. 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 segment intersects the center line of the shunt hole;

[0011] Alternatively, the first pipe segment is a straight pipe.

[0012] According to an embodiment of the present utility model, each branch pipe further includes a branch section. The second pipe segment is a tapered structure integrally formed with the first pipe segment and having a gradually decreasing inner diameter. The branch section is welded to the second pipe segment, or the first pipe segment, the second pipe segment, and the branch section are integrally formed;

[0013] Alternatively, the branch section is socket-welded to the first pipe segment, and the socket-welded portion of the two forms the second pipe segment;

[0014] Alternatively, the branch section is socket-welded to the first pipe segment, and the second pipe segment is formed on the branch section.

[0015] According to an embodiment of the present utility model, the extended top end of the flow channel forming member is opposite to the assembly hole of the liquid inlet pipe, and the vertical distance H from the extended top end of the flow channel forming member to the end face of the liquid outlet end of the liquid inlet pipe satisfies: 1 mm ≤ H ≤ 2H0 / 3, where H0 is the height of the shunt cavity.

[0016] According to an embodiment of the present utility model, the radial distance L from the outer periphery of the bottom of the flow channel forming member to the inner edge of the shunt hole satisfies: L ≤ 4 mm; the inner edge of the shunt hole refers to: at the liquid outlet end of the body, the intersection of the connection line between the center of the shunt hole and the center of the body and the edge of the shunt hole.

[0017] According to an embodiment of the present utility model, the extended top end of the flow channel forming member is a plane; alternatively, the extended top end of the flow channel forming member is an arc-shaped curved surface, and the radius of curvature R of the arc-shaped curved surface satisfies: 0.5 mm ≤ R ≤ 5 mm.

[0018] According to an embodiment of the present utility model, on the longitudinal section of the flow channel forming member passing through the axis of the body, the included angle α formed by the extension lines of the two side generatrices of the flow channel forming member satisfies: 20° ≤ α ≤ 115°.

[0019] According to an embodiment of the present utility model, the body includes an end cover with an open liquid outlet end and at least one lining plate hermetically welded to the open end of the end cover, and a plurality of shunt holes are formed on the lining plate.

[0020] On the other hand, the present utility model also provides a heat exchange device, which includes the above-mentioned novel Venturi type shunt.

[0021] On the other hand, the present utility model also provides a refrigeration device, which includes the above-mentioned heat exchange device.

[0022] In summary, the novel Venturi type shunt provided by the present utility model is provided with at least one Venturi tube section on the liquid inlet pipe, and the throat straight section of the Venturi tube section is used to increase the speed of the refrigerant. A low pressure is formed near the high-speed refrigerant, and the adsorption effect generated by the low pressure will strengthen the fluid disturbance and promote the mixing of the two-phase flow to improve the inlet flow pattern of the shunt. By arranging a flow channel forming member in the shunt cavity, the top of the flow channel forming member reflects the high-speed refrigerant injected after being accelerated by the throat straight section, and the reflected refrigerant is incident on the inner wall of the inclined extending liquid inlet end of the body again. After being reflected twice by the inner wall of the liquid inlet end of the body, it is fully mixed into a uniform dispersed flow pattern in the annular flow channel, and then is uniformly distributed into a plurality of shunt holes along the annular flow channel. Further, the arrangement of the flow channel forming member effectively reduces the volume in the shunt cavity to control the flow rate of the refrigerant, ensuring that the liquid-phase refrigerant has sufficient inertia force in the shunt cavity to overcome the gravity it receives and avoiding the gas-liquid two-phase separation of the refrigerant during shunting again. On the outlet branch pipe, the first pipe section with a larger inner diameter increases the refrigerant flow rate distributed into each branch pipe and reduces the distribution resistance of the refrigerant; while the second pipe section increases the refrigerant flow rate by reducing the flow channel cross-section to meet the performance requirements of the subsequent heat exchange device. On this basis, by setting the inner diameter difference △d, the pressure reduction and speed increase degree of the refrigerant by the second pipe section are accurately controlled, avoiding excessive throttling resulting in excessive refrigerant pressure loss, and thus realizing the balanced control of the outlet refrigerant flow rate, flow velocity and pressure.

[0023] The present utility model takes into account the influencing factors such as the refrigerant inlet flow pattern, the uniformity of refrigerant mixing in the shunt cavity, and the flow state of the outlet refrigerant, and optimizes the liquid inlet pipe, the internal structure of the body and each outlet branch pipe of the shunt integrally to comprehensively improve its shunt performance.

[0024] In order to make the above and other objects, features and advantages of the present utility model more obvious and understandable, the following specifically enumerates preferred embodiments and, in conjunction with the accompanying drawings, makes a detailed description as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1A and Figure 1B The figure shows a schematic structural diagram of an existing brass diverter.

[0026] Figure 2 The figure shows a schematic structural diagram of the novel Venturi diverter provided in the first embodiment of the present invention.

[0027] Figure 3 The figure shows Figure 2 a schematic structural diagram after removing the liquid inlet pipe and the branch pipes.

[0028] Figure 4 The figure shows Figure 2 a schematic structural diagram of the liquid inlet pipe in

[0029] Figure 5A and Figure 5B The figure shows a schematic structural diagram of the novel Venturi diverter provided in another embodiment of the present invention.

[0030] Figure 6 The figure shows Figure 2 a schematic projection diagram of the flow channel forming member on the inner bottom wall of the liquid outlet end of the main body in

[0031] Figure 7 The figure shows Figure 2 a schematic structural diagram of the flow channel forming member in

[0032] Figure 8 The figure shows Figure 2 a schematic structural diagram of the branch pipe in

[0033] Figure 9A 、 Figure 9B 、 Figure 9C 、 Figure 9D 、 Figure 9E 、 Figure 9F and Figure 9G a schematic structural diagram of the branch pipe in the novel Venturi diverter provided in another embodiment of the present invention.

[0034] Figure 10 The figure shows a schematic structural diagram of the novel Venturi diverter provided in the second embodiment of the present invention.

[0035] Figure 11 The figure shows Figure 10 a schematic structural diagram of the liquid inlet pipe in

[0036] Figure 12 The figure shows a schematic structural diagram of the novel Venturi diverter provided in the third embodiment of the present invention.

[0037] Figure 13 The figure shows Figure 12 a schematic structural diagram of the liquid inlet pipe in

[0038] Figure 14 As shown Figure 12 in the structural schematic diagram of the reduced-diameter orifice plate.

[0039] Figure 15 As shown is the structural schematic diagram of the novel Venturi-type flow divider provided in the fourth embodiment of the present invention.

[0040] Figure 16 As shown Figure 15 a partial schematic diagram of Specific embodiments

[0041] In this application, the downstream or upstream is divided based on the flow direction of the refrigerant. Generally, the refrigerant flows from the upstream to the downstream, and the area located downstream receives the refrigerant from the upstream. In a refrigeration device, the flow divider is generally installed vertically or obliquely, and the liquid inlet end of the flow divider is located below the liquid outlet end along the direction of gravity. The inertial force of the refrigerant in the flow divider overcomes the gravity and flows in the direction opposite to the gravity; at this time, the upstream and downstream are still divided according to the flow direction of the refrigerant.

[0042] Embodiment 1

[0043] In a refrigeration system, the flow divider is a flow dividing element connected between an expansion valve and a heat exchange device. Such a connection method makes its performance affected not only by its own structure but also by the upstream inlet pipeline and the downstream outlet pipeline. The performance optimization of existing flow dividers mainly focuses on the body structure of the flow divider, while the optimization of the inlet and outlet connection pipelines is relatively less. In fact, the inlet refrigerant flow pattern and the outlet refrigerant flow state (including the pressure drop loss, flow velocity, and downstream pressure wave disturbance of the outlet refrigerant, etc.) will all have a great impact on the flow dividing performance. In view of this, this embodiment provides a novel Venturi-type flow divider with excellent flow dividing performance achieved through overall optimization.

[0044] Such as Figure 2 and Figure 3As shown in the figure, the novel Venturi-type diverter provided in this embodiment includes a body 1, a flow channel forming member 2, a liquid inlet pipe 3, and multiple branch pipes 4. The body 1 includes a liquid inlet end 101 and a liquid outlet end 102. The inner wall of the liquid inlet end 101 extends obliquely towards the liquid outlet end 102 of the body, and the generatrix of its inner wall is an arc or an inclined straight line. A liquid inlet pipe assembly hole 11 is formed on the liquid inlet end 101 of the body, and multiple diversion holes 12 are formed on its liquid outlet end 102. A diversion cavity 13 communicating the liquid inlet pipe assembly hole 11 and the multiple diversion holes 12 is formed inside the body 1. The flow channel forming member 2 is arranged inside the diversion cavity 13 and is located on the inner circumference of the multiple diversion holes 12. The flow channel forming member 2 is a rotating member formed by protruding from the inner bottom wall of the liquid outlet end 102 of the body towards the direction where the liquid inlet pipe assembly hole 11 is located and rotating around the axis of the body 1. An annular flow channel 130 communicating the multiple diversion holes 12 is formed between the flow channel forming member 2 and the inner wall of the diversion cavity 13, and the cross-section of the flow channel forming member 2 gradually decreases along the protruding direction. The liquid inlet pipe 3 is a circular pipe fitting with a substantially uniform wall thickness. The liquid inlet pipe 3 is connected to the liquid inlet pipe assembly hole 11 and includes at least one Venturi tube section 31. Each Venturi tube section 31 includes a converging section 311 with a gradually decreasing inner diameter, a throat straight section 312 with a substantially uniform inner diameter, and a diverging section 313 with a gradually increasing inner diameter, which are distributed in sequence along the refrigerant flow direction. The multiple branch pipes 4 are respectively welded to the multiple diversion holes 12 on the body 1. Each branch pipe 4 includes a first pipe section 41 and a second pipe section 42 located downstream of the first pipe section 41 and having a reduced inner diameter relative to the inner diameter at the downstream end of the first pipe section 41. The difference △d between the inner diameter d11 at the downstream end of the first pipe section 41 and the inner diameter d12 at the downstream end of the second pipe section 42 is: 0.1mm ≤ △d ≤ 3.5mm.

[0045] The novel Venturi-type diverter provided in this embodiment optimizes the diverter as a whole from three aspects: the liquid inlet pipe 3, the structure of the body 1, and the branch pipes 4 to greatly improve its diversion performance. The following will combine Figures 2 to 8 to elaborate in detail on the structure and principle of the novel Venturi-type diverter provided in this embodiment.

[0046] As Figures 2 to 4As shown, when the asymmetric flow pattern refrigerant input upstream of the liquid inlet pipe 3 flows through the converging section 311 of the Venturi tube section 31, the flow rate of the refrigerant begins to increase and the pressure begins to decrease. The refrigerant reaches the maximum flow rate at the throat straight section 312 with the smallest cross-sectional area, and its pressure also drops to the lowest. A low-pressure area is formed near the high-speed refrigerant, and the adsorption effect generated by the low-pressure area will disturb the refrigerant flow pattern to promote the gas-liquid two-phase mixing. The two-phase flow gradually develops into a uniformly mixed dispersed flow pattern in the diverging section 313, thereby realizing the improvement of the refrigerant inlet flow pattern. In this embodiment, a Venturi tube section 31 is formed on the liquid inlet pipe 3, and a liquid inlet pipe assembly section 32 is further formed at the downstream end of the Venturi tube section 31. The liquid inlet pipe assembly section 32 is a straight pipe section and is welded and connected to the assembly hole straight section 111 on the liquid inlet pipe assembly hole 11. However, the present utility model does not make any limitation thereto.

[0047] In this embodiment, the liquid inlet pipe 3 is a circular pipe fitting with a substantially uniform wall thickness. The Venturi tube section 31 on the liquid inlet pipe 3 is formed by processing a circular pipe material through a process of expanding and contracting the orifice. This setting can accurately control the inner diameter change rate of the converging section 311 and the diverging section 313 and the transition structure between adjacent pipe sections, so as to form a smooth linear shape in the Venturi tube section 31, promote the gas-liquid two-phase mixing, and at the same time reduce the refrigerant pressure loss. Further, the Venturi structure formed based on the pipe fitting is a non-chip processing that does not require cutting. This processing method has the advantages of high processing accuracy, excellent product consistency, high processing efficiency, and less consumables.

[0048] In the novel Venturi type diverter provided in this embodiment, a flow channel forming member 2 is arranged in the main body 1, and the inner wall of the liquid inlet end 101 of the main body extends obliquely towards the liquid outlet end 102. This setting makes the outer peripheral wall near the top of the flow channel forming member 2 form a primary reflection surface to reflect the high-speed refrigerant injected into the Venturi tube section 31. The refrigerant after the primary reflection is incident on the inner wall of the obliquely extending liquid inlet end 101 of the main body again, and after being secondarily reflected by the inner wall of the liquid inlet end 101 of the main body, it is evenly distributed into a plurality of diversion holes 12 along the annular flow channel 130. The flow channel forming member 2 and the inner wall of the obliquely extending liquid inlet end 101 of the main body realize the secondary reflection of the incident refrigerant in the main body 1. During the reflection process, the liquid droplets are gradually atomized into smaller forms, and the refrigerant is fully mixed into a uniform dispersed flow pattern. Further, the setting of the flow channel forming member 2 also effectively reduces the volume of the diversion cavity 13, restricts the volume change rate of the refrigerant to control its flow rate, ensures that the liquid-phase refrigerant has sufficient inertial force to overcome the gravity it receives during the diversion process, and the refrigerant maintains a uniform mixed dispersed flow pattern to improve the diversion uniformity.

[0049] Specifically, as Figure 2 and Figure 3As shown, the body 1 includes an end cap 1A and a lining plate 1B hermetically welded to the open end of the end cap 1A. An inlet pipe assembly hole 11 is formed on the end cap 1A, and a plurality of shunt holes 12 are formed on the lining plate 1B. The inner wall of the end cap 1A extends obliquely towards the liquid outlet end 102 of the body and is a curved surface with an arc-shaped inner wall generatrix; preferably, the extending direction of the inner wall of the end cap 1A is substantially close to the inclined direction of the outer peripheral wall of the flow channel forming member 2. However, the present utility model does not make any limitation on the specific structure of the end cap. In other embodiments, such as Figure 5A As shown, the end cap 1A can also be set as a conical shape with an inclined straight inner wall generatrix; at this time, the inner wall generatrix of the end cap 1A can also be substantially parallel to the outer peripheral wall generatrix of the flow channel forming member 2.

[0050] Although this example is described with the body including an end cap and a lining plate. However, the present utility model does not make any limitation on this. In other embodiments, multiple stacked lining plates can also be provided on the liquid outlet end of the body, and the same number of lining plate holes are formed on each lining plate, and a plurality of coaxial lining plate holes together form a shunt hole. In other embodiments, such as Figure 5B As shown, the body 1 can also be set to include a single-end open cylinder 1C and an end cap 1A welded to the cylinder 1C. An inlet pipe assembly hole ( Figure 5B The inlet pipe 3 is assembled in it, so it is not marked) is formed on the end cap 1A, and a plurality of cylinder through holes are formed on the bottom of the cylinder 1C. Further, in this structure, a lining plate 1B can also be added to the bottom wall of the cylinder 1C, and a plurality of lining plate holes corresponding to the plurality of cylinder through holes are formed on the lining plate 1B, and the coaxial cylinder through holes and the lining plate holes together form a shunt hole 12.

[0051] In this embodiment, such as Figure 2 and Figure 3 As shown, the extending top end of the flow channel forming member 2 is opposite to the inlet pipe assembly hole 11, and the vertical distance H from the extending top end of the flow channel forming member 2 to the end face of the liquid outlet end of the inlet pipe 3 satisfies: 1mm ≤ H ≤ 2H0 / 3; H0 is the height of the shunt cavity, which refers to the vertical distance from the inner bottom wall of the liquid outlet end 102 of the body to the inner end face of the inlet pipe assembly hole 11. This setting enables the refrigerant entering the shunt cavity 13 to be quickly shunted into the annular flow channel 130; and on the premise of determining the body parameters, the volume in the shunt cavity 13 can be precisely controlled by adjusting the vertical distance H, thereby realizing the precise control of the refrigerant flow rate in the shunt cavity 13. In this embodiment, the end face of the liquid outlet end of the inlet pipe 3 is substantially flush with the inner end face of the inlet pipe assembly hole 11. However, the present utility model does not make any limitation on this. In other embodiments, the end face of the liquid outlet end of the inlet pipe 3 may not extend to the inner end face of the inlet pipe assembly hole 11; or, it may extend past the inner end face of the inlet pipe assembly hole and extend into the shunt cavity.

[0052] Further, the volume in the diversion cavity 13 can also be adjusted by controlling the radial distance L from the bottom outer periphery of the flow channel forming member 2 to the inner edge of the diversion hole 12. As shown in FIGS. 1 and Figure 6 As shown, the inner edge of the diversion hole 12 refers to: at the liquid outlet end 102 of the body, the intersection of the connection line (such as the dotted line in Figure 6 ) between the center of the diversion hole 12 and the center of the body 1 and the edge of the diversion hole 12, that is, Figure 6 at position B in Figure 6 ; in

[0053] , the area formed by the dotted line is the projection of the flow channel forming member 2 on the liquid outlet end 102 of the body. Preferably, the radial distance L is set to satisfy: 0≤L≤4mm, such as equally spaced distances of 0.5mm, 1mm, 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm, etc. When the radial distance L is 0, the bottom outer periphery of the flow channel forming member 2 just tangentially contacts the inner edge of the diversion hole 12. However, the present utility model does not make any limitation thereto.

[0054] In this embodiment, as shown in Figure 7 , the flow channel forming member 2 is approximately conical. In the longitudinal section of the flow channel forming member 2 passing through the axis of the body 1, the included angle α formed by the extension lines of the two side generatrices of the flow channel forming member 2 satisfies: 20°≤α≤115°. The included angle α limits the inclination slope of the peripheral wall of the flow channel forming member 2, that is, controls the cross-sectional change rate of the annular flow channel 130 so that the diverted refrigerant can be quickly distributed into multiple diversion holes 12. Preferably, the included angle α is set to 45°, 50° or 60°. However, the present utility model does not make any limitation thereto. In this embodiment, the extended top end of the flow channel forming member 2 is an arc surface and the radius of curvature R of the arc surface satisfies: 0.5mm≤R≤5mm. This setting enables the refrigerant to smoothly enter the annular flow channel 130 and also increases the reflection area of the top end of the flow channel forming member 2 for the incident refrigerant to further improve the diversion uniformity. However, the present utility model does not make any limitation thereto. In other embodiments, the flow channel forming member can also be set as a frustum-shaped structure with a flat top end.

[0055] In the novel Venturi-type flow divider provided in this embodiment, the refrigerant with an asymmetric flow pattern is input into the main body 1 after the flow pattern is improved through the Venturi tube section 31 on the liquid inlet pipe 3, and is further mixed in the flow dividing cavity 13 and then evenly distributed into multiple branch pipes 4 through the annular flow channel 130 and a plurality of flow dividing holes 12. As Figure 8 shown, each branch pipe 4 includes a first pipe section 41 and a second pipe section 42 located downstream of the first pipe section 41 and having an inner diameter smaller than the inner diameter d11 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 exchanger device. On this basis, the inner diameter difference △d precisely controls the degree of pressure reduction and speed increase of the refrigerant by the second pipe section 42, avoiding excessive pressure loss of the refrigerant due to excessive speed increase.

[0056] Further, a reflection section 411 is formed on the first pipe section 41 and extends bent towards one side of the center line of the flow dividing hole 12. An included angle θ is formed between the axis at the upstream end of the reflection section 411 and the axis at the downstream end of the reflection section 411, and 90° ≤ θ ≤ 175°. The setting of the reflection section 411 makes the second pipe section 42 no longer coaxial with the center line of the flow dividing hole. When there is a pressure wave downstream and it oscillates upstream, the reflection section 411 reflects and absorbs part of the pressure wave and changes the propagation direction of the remaining pressure wave to make it decay rapidly, effectively avoiding the influence of the downstream pressure wave on the upstream flow dividing hole 12 to further improve the distribution performance.

[0057] In this embodiment, the branch pipe 4 further includes a branch section 43 welded to the first pipe section 41, and the second pipe section 42 is located on the branch section 43. Specifically, as Figure 8 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 thereto. In other embodiments, it is also possible to set the upstream end of the branch section 43 to be welded inside 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 9A shown.

[0058] Figure 9B 、 Figure 9C and Figure 9D are schematic structural diagrams of the branch pipe provided in another embodiment of the present utility model. Figure 9B In it, the first pipe section 41, the second pipe section 42 and the branch section 43 are integrally formed; Figure 9CIn this case, the first pipe segment 41 and the second pipe segment 42 are integrally formed, and the branch segment 43 is welded to the end of the second pipe segment 42. Figure 9D In this case, based on the inner diameter difference between the downstream end of the first pipe segment 41 and the upstream end of the branch segment 43, the second pipe segment 42 is directly formed at the socket joint of the first pipe segment 41 and the branch segment 43. In addition, a plurality of second pipe segments can also be provided at the downstream end of the first pipe segment, and the branch segment 43 can be set as a straight pipe or a bent pipe according to actual applications.

[0059] Although this embodiment is described by taking the reflection segment 411 formed on the first pipe segment 41 as an example. However, the present utility model does not make any limitation thereto. In other embodiments, the first pipe segment 41 may not be provided with a reflection segment. At this time, the first pipe segment 41 is a straight pipe, as Figure 9E shown.

[0060] Furthermore, for the structure of the second pipe segment 42, in other embodiments, the second pipe segment 42 may further be provided to include a tapered segment and a maintaining straight segment located downstream of the tapered segment and having a certain length L42. The inner diameter of the maintaining straight segment is close to the inner diameter at the downstream end of the tapered segment and is basically unchanged within the length L42, as Figure 9F shown. Or, an orifice plate 44 is added at the flared joint of the first pipe segment 41 or the branch segment 43, and the refrigerant is accelerated by using the through holes 441 on the orifice plate 44; at this time, the pipe segment where the orifice plate 44 is located is the second pipe segment 42, as Figure 9G shown.

[0061] Correspondingly, this embodiment also provides a heat exchange device including the above-mentioned novel Venturi type diverter. Specifically, the heat exchange device is an evaporator or a condenser.

[0062] Furthermore, this embodiment also provides a refrigeration device including the above-mentioned heat exchange device.

[0063] Embodiment Two

[0064] This embodiment is basically the same as Embodiment One and its variations, except that: the structure of the liquid inlet pipe 3 is different.

[0065] In this embodiment, as Figure 10 and Figure 11 shown, two Venturi pipe segments in series are formed on the liquid inlet pipe 3, namely an upstream Venturi pipe segment 31' and a downstream Venturi pipe segment 31. The flow pattern of the inlet refrigerant is gradually improved through the two Venturi pipe segments in series, and the mixing uniformity of the inlet refrigerant is enhanced to improve the performance of the diverter.

[0066] Preferably, the inner diameter D1 of the throat straight section of the downstream Venturi tube section 31 is set to be smaller than the inner diameter D0 of the throat straight section of the upstream Venturi tube section 31'. This setting enables the refrigerant to be further accelerated at the throat straight section 312 of the downstream Venturi tube section 31, increasing the kinetic energy of the refrigerant incident into the main body 1, enhancing the gas-liquid two-phase mixing effect, and enabling the refrigerant to have a greater inertial force to maintain the mixed flow pattern. However, the present utility model does not make any limitation thereto. In other embodiments, the inner diameters of the throat straight sections of the two Venturi tube sections may also be set to be substantially the same.

[0067] Embodiment Three

[0068] This embodiment is basically the same as Embodiment Two and its variations, except that: the structure of the liquid inlet pipe 3 is different.

[0069] In Embodiment Two, the liquid inlet pipe 3 passes through two serially connected Venturi tube sections 31 to perform secondary mixing on the input refrigerant to improve the improvement effect of the inlet refrigerant flow pattern. However, the series connection of the two Venturi tube sections 31, 31' will make the length of the liquid inlet pipe 3 longer and difficult to be applied to refrigeration equipment with strict installation space. Therefore, this embodiment provides a liquid inlet pipe structure that can achieve secondary mixing and has a shorter length.

[0070] In this embodiment, the liquid inlet pipe 3 includes a Venturi tube section 31 and a variable-diameter orifice plate 33 located downstream of the Venturi tube section 31. Specifically, as Figures 12 to 14 shown, a liquid inlet pipe assembly section 32 in the form of a straight pipe section is formed downstream of the Venturi tube section 31, and the variable-diameter orifice plate 33 is arranged in the liquid inlet pipe assembly section 32. The variable-diameter orifice plate 33 has a variable-diameter orifice 330, and the variable-diameter orifice 330 includes a gradually reducing orifice section 331 with a gradually decreasing aperture along the refrigerant flow direction and a throat orifice section 332 located downstream of the gradually reducing orifice section 331 with a substantially constant aperture. In this embodiment, the variable-diameter orifice plate 33 with a thinner thickness is used to replace the downstream Venturi tube section with a longer length in Embodiment Two, shortening the length of the liquid inlet pipe 3 while achieving secondary mixing to be compatible with refrigeration equipment with different installation spaces, including refrigeration equipment with a narrow installation space (such as a 1HP or 1.5HP household air conditioner indoor unit).

[0071] Embodiment Four

[0072] This embodiment is basically the same as Embodiment One and its variations, except that: the assembly method of the liquid inlet pipe 3 and the main body 1 is different.

[0073] As Figure 15As shown, in this embodiment, the liquid inlet pipe assembly hole 11 is a through hole without an assembly hole straight section. The liquid inlet pipe assembly section 32 on the liquid inlet pipe 3 is a gradually expanding structure with an arc-shaped curve for the outer wall generatrix. The liquid inlet pipe assembly section 32 extends into the main body 1 through the liquid inlet pipe assembly hole 11, and the outer wall of the liquid inlet pipe assembly section 32 is welded in contact with the inner wall of the liquid inlet end 101 of the main body. In this embodiment, it is defined that: the extension line of the inner wall generatrix of the throat straight section 312 on the Venturi tube section 31 intersects the virtual extension plane of the inner wall of the liquid inlet end 101 of the main body at the liquid inlet pipe assembly hole 11 at position K, and the cross-section of the liquid inlet pipe 3 passing through position K is the end face of the liquid outlet end of the liquid inlet pipe 3; the vertical distance H is the distance from the extended top end of the flow channel forming member 2 to the end face of the liquid outlet end of the liquid inlet pipe 3.

[0074] In addition, affected by the connection method of the liquid inlet pipe 3, as Figure 16 shown, it is also defined that: the extension line of the outer wall generatrix of the throat straight section 312 on the Venturi tube section intersects the virtual extension plane of the inner wall of the liquid inlet end 101 of the main body at the liquid inlet pipe assembly hole 11 at position K', and the cross-section of the liquid inlet pipe 3 passing through position K' is the inner end face of the liquid inlet pipe assembly hole 11. Based on this, the height H0 of the diversion cavity is determined.

[0075] However, the utility model does not make any limitation on the specific structure of the liquid inlet pipe assembly hole. In other embodiments, when there is an assembly hole welding straight section on the liquid inlet pipe assembly hole, the liquid inlet pipe assembly section 32 can also be set to include a straight section and a gradually expanding pipe section located downstream of the straight section and welded in contact with the inner wall of the liquid inlet end of the main body.

[0076] In summary, the novel Venturi-type flow divider provided by the present utility model increases the speed of the refrigerant by arranging at least one Venturi tube section on the liquid inlet pipe and utilizing the straight section of the throat of the Venturi tube section. A low pressure is formed near the high-speed refrigerant, and the adsorption effect generated by the low pressure will strengthen the fluid disturbance, promote the mixing of the two-phase flow, and improve the inlet flow pattern of the flow divider. By arranging a flow path forming member in the flow dividing cavity, the top of the flow path forming member reflects the high-speed refrigerant flowing in after being accelerated by the straight section of the throat. The reflected refrigerant is incident again on the inner wall of the liquid inlet end of the body extending obliquely, and after being reflected twice by the inner wall of the liquid inlet end of the body, it is fully mixed into a uniform dispersed flow pattern in the annular flow path, and then is evenly distributed into a plurality of flow dividing holes along the annular flow path. Further, the arrangement of the flow path forming member effectively reduces the volume in the flow dividing cavity to control the flow rate of the refrigerant, ensuring that the liquid-phase refrigerant has sufficient inertial force in the flow dividing cavity to overcome the gravity it receives, and avoiding the occurrence of gas-liquid two-phase separation again during flow division. On the outlet branch pipe, the first pipe section with a larger inner diameter increases the refrigerant flow rate distributed into each branch pipe and reduces the distribution resistance of the refrigerant; while the second pipe section increases the refrigerant flow rate by reducing the flow path cross-section to meet the performance requirements of the subsequent heat exchange device. On this basis, by setting the inner diameter difference △d, the pressure reduction and speed increase degree of the second pipe section on the refrigerant are accurately controlled, avoiding excessive throttling resulting in excessive refrigerant pressure loss, and thus realizing the balanced control of the outlet refrigerant flow rate, flow velocity, and pressure.

[0077] The present utility model takes into account influencing factors such as the refrigerant inlet flow pattern, the uniformity of refrigerant mixing in the flow dividing cavity, and the flow state of the outlet refrigerant, and comprehensively optimizes the liquid inlet pipe, the internal structure of the body, and each outlet branch pipe of the flow divider to comprehensively improve its flow dividing performance.

[0078] Although the present utility model has been disclosed above with 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 novel Venturi type diverter, characterized in that, Comprising: A body, including a liquid inlet end and a liquid outlet end. The inner wall of the liquid inlet end extends obliquely towards the liquid outlet end, and the generatrix of its inner wall is an arc or an inclined straight line. A liquid inlet pipe assembly hole is formed on the liquid inlet end of the body, and a plurality of shunt holes are formed on its liquid outlet end. A shunt cavity communicating the liquid inlet pipe assembly hole and the plurality of shunt holes is formed inside the body; A flow channel forming member, arranged inside the shunt cavity and located on the inner periphery of the plurality of shunt holes. The flow channel forming member is a rotating member formed by protruding from the inner bottom wall of the liquid outlet end of the body towards the direction where the liquid inlet pipe assembly hole is located and rotating around the axis of the body. An annular flow channel communicating the plurality of shunt holes is enclosed between the flow channel forming member and the inner wall of the shunt cavity, and the cross-section of the flow channel forming member gradually decreases along the protruding direction; A liquid inlet pipe, which is a circular pipe fitting with a substantially uniform wall thickness. The liquid inlet pipe is connected to the liquid inlet pipe assembly hole and includes at least one Venturi tube section. Each Venturi tube section includes a converging section with a gradually decreasing inner diameter, a throat straight section with a substantially uniform inner diameter, and a diverging section with a gradually increasing inner diameter, which are distributed in sequence along the refrigerant flow direction; A plurality of branch pipes, which are respectively welded and connected to the plurality of shunt holes on the body. 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: 0.1mm ≤ △d ≤ 3.5mm.

2. The novel Venturi type flow divider according to claim 1, wherein Two series-connected Venturi tube sections are formed on the liquid inlet pipe, namely an upstream Venturi tube section and a downstream Venturi tube section. The inner diameter of the throat straight section of the downstream Venturi tube section is less than or equal to the inner diameter of the throat straight section of the upstream Venturi tube section.

3. The novel Venturi shunt according to claim 1, characterized in that, The liquid inlet pipe further includes a variable diameter orifice plate arranged downstream of the Venturi tube section. A variable diameter orifice is formed on the variable diameter orifice plate. The variable diameter orifice includes a converging orifice section with a gradually decreasing aperture along the refrigerant flow direction and a throat orifice section located downstream of the converging orifice section and having a substantially constant aperture.

4. The novel Venturi shunt according to claim 1, characterized in that, An attenuation section is formed on the first pipe section, which extends bent towards one side relative to the center line of the shunt 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 hole; Alternatively, the first pipe section is a straight pipe.

5. The novel Venturi shunt according to claim 1, wherein, Each branch pipe also includes a branch section. The second pipe section is a tapered structure integrally formed with the first pipe section and having a gradually decreasing inner diameter. The branch section is welded and connected to the second pipe section, or the first pipe section, the second pipe section, and the branch section are integrally formed; Alternatively, the branch section is socket-welded to the first pipe section, and the socket-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.

6. The novel Venturi shunt according to claim 1, characterized in that, The extended top end of the flow channel forming member is opposite to the liquid inlet pipe assembly hole, and the vertical distance H from the extended top end of the flow channel forming member to the end face of the liquid outlet of the liquid inlet pipe satisfies: 1mm ≤ H ≤ 2H0 / 3, where H0 is the height of the shunt cavity.

7. The novel Venturi type diverter according to claim 1, characterized in that, The radial distance L from the outer periphery of the bottom of the flow channel forming member to the inner edge of the shunt hole satisfies: L ≤ 4 mm; the inner edge of the shunt hole refers to: at the liquid outlet end of the body, the intersection of the line connecting the center of the shunt hole and the center of the body with the edge of the shunt hole.

8. The novel Venturi type flow divider according to claim 1, characterized in that, The extended top end of the flow channel forming member is a plane; or, the extended top end of the flow channel forming member is an arc-shaped curved surface and the radius of curvature R of the arc-shaped curved surface satisfies: 0.5 mm ≤ R ≤ 5 mm.

9. The novel Venturi shunt according to claim 1, characterized in that, On the longitudinal section of the flow channel forming member passing through the axis of the body, the included angle α formed by the extended lines of the two side generatrices of the flow channel forming member satisfies: 20° ≤ α ≤ 115°.

10. The novel Venturi type diverter according to claim 1, characterized in that, The body includes an end cover with an open liquid outlet end and at least one lining plate hermetically welded to the open end of the end cover, and a plurality of shunt holes are provided on the lining plate.

11. A heat exchange device, characterized in that, It includes the novel Venturi type shunt device according to any one of claims 1 to 10.

12. A refrigeration device, characterized in that, It includes the heat exchange device according to claim 11.

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