Spherical flow valve and air conditioning system

Abstract

The invention discloses a spherical flow valve and an air conditioning system, and relates to the technical field of air conditioners. According to the spherical flow valve provided by the embodiment of the invention, the first auxiliary channel and the second auxiliary channel are additionally arranged in the valve element of the spherical flow valve, so that when the valve element is in the flow restraining state, fluid can enter from the first opening of the main channel and can also enter from the first auxiliary channel, and the fluid can flow out from the second opening of the main channel; and the water can flow out from the second auxiliary channel. And due to the change of the flow field, the fluid flows more smoothly, and the generated vortex can be eliminated or reduced, so that the noise is reduced. The air conditioning system provided by the embodiment of the invention comprises the spherical flow valve, so that the air conditioning system has the advantage of low noise.

Description

Technical Field

[0001] This application relates to the technical field of air conditioners, and more particularly, to a spherical flow valve and an air conditioning system. Background Art

[0002] The spherical flow valve is installed in a pipeline and can play a role in regulating the flow rate of the medium. In a traditional spherical flow valve, a channel is provided on the valve core, and the valve core can rotate relative to the valve seat. When the two openings of the channel on the valve core are respectively opposite to the inlet and outlet on the valve seat, the medium entering the valve seat from the inlet can pass through the channel and flow out from the outlet. By rotating the valve core, the valve seat can block a part of the opening of the channel, and the other part of the opening of the channel can still allow the medium to flow through, that is, the opening area allowing the medium to flow through becomes smaller, thereby suppressing the flow rate. However, when the traditional spherical flow valve suppresses the medium flow rate, it is prone to the problem of high noise. Summary of the Invention

[0003] The problem solved by this application is the problem of high noise in the existing spherical flow valve.

[0004] To solve the above problems, in a first aspect, this application provides a spherical flow valve, including a valve seat and a valve core disposed in the valve seat. Inlets and outlets are respectively provided on opposite sides of the valve seat. The valve core can rotate relative to the valve seat around a rotation axis. A main channel, a first auxiliary channel, and a second auxiliary channel are provided on the valve core. The main channel penetrates through the valve core and both ends form a first opening and a second opening. By rotating the valve core, the first opening and the second opening can be selectively communicated with the inlet and the outlet respectively, or the first opening and the second opening can be blocked by the inner wall surface of the valve seat; the first auxiliary channel and the second auxiliary channel are respectively located on opposite sides in the radial direction of the main channel, and one end extends to the inner side wall of the main channel, and the other end extends to the outer peripheral surface of the valve core; during the rotation stroke of the valve core relative to the valve seat, there is a flow rate suppression state. When the valve core is in the flow rate suppression state, a part of the first opening and the first auxiliary channel are communicated with the inlet, and a part of the second opening and the second auxiliary channel are communicated with the second opening.

[0005] In a traditional spherical flow valve, the reason for noise generation is that when the valve core suppresses the flow rate, the axis of the channel on the valve core forms an angle with the central axes of the inlet and outlet on the valve seat. The turbulent fluid is forced to flow through the channel. Due to the unreasonable flow field, vortices are likely to be generated inside the valve core or even outside the outlet, thereby generating noise. In the embodiments of this application, by adding the first auxiliary channel and the second auxiliary channel, when the valve core is in the flow rate suppression state, the fluid can enter from the first opening of the main channel or from the first auxiliary channel, and the fluid can flow out from the second opening of the main channel or from the second auxiliary channel. Due to the change in the flow field, the fluid flow becomes smoother, and the generated vortices can be eliminated or reduced, thereby reducing noise generation.

[0006] In an alternative embodiment, when the valve core is in the flow throttling state, the first opening and the first auxiliary channel are on opposite sides of the central axis of the inlet, and the second opening and the second auxiliary channel are on opposite sides of the central axis of the outlet. Since when the valve core is in the flow throttling state, the first opening / second opening has been deflected to one side of the central axis of the inlet / outlet and is partially blocked. At this time, if the first auxiliary channel / second auxiliary channel is on the same side as the first opening / second opening, it is not conducive to the smoothness of fluid flow. Therefore, setting the first auxiliary channel and the first opening on opposite sides of the central axis of the inlet, and setting the second auxiliary channel and the second opening on opposite sides of the central axis of the outlet can optimize the flow field, make the fluid flow more smoothly, and reduce the generation of vortices and noise.

[0007] In an alternative embodiment, the central axes of the first auxiliary channel, the second auxiliary channel, the inlet, and the outlet are all perpendicular to the rotation axis; when the valve core rotates until the first auxiliary channel is parallel to the central axis of the inlet or when the valve core rotates until the second auxiliary channel is parallel to the central axis of the outlet, the valve core is in the flow throttling state. It can be understood that when the channel is closer to being parallel to the central axes of the outlet and the inlet, the fluid is less likely to generate vortices due to the change in flow direction when passing through the channel. In this embodiment, since the valve core is in the flow throttling state when the first auxiliary channel is parallel to the central axis of the inlet or the second auxiliary channel is parallel to the central axis of the outlet, it means that the deflection angles of the first auxiliary channel and the second auxiliary channel relative to the central axes of the inlet and the outlet are relatively small (even parallel) in the flow throttling state of the valve core, and the fluid can pass through the first auxiliary channel and the second auxiliary channel more smoothly, reducing the generation of eddy currents and noise.

[0008] In an alternative embodiment, the edge of the inlet has a first point and a second point. The first point and the second point are the two endpoints of one of the diameters of the inlet, and the line connecting the first point and the second point is perpendicular to the rotation axis; when the valve core rotates until the first auxiliary channel is parallel to the central axis of the inlet, the first point is opposite to the first opening, and the distance from the second point to the first auxiliary channel is α, satisfying [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2, where D is the diameter of the inlet, R is the diameter of the valve core, θa is the angle between the first auxiliary channel and the main channel, and θb is the angle between the shortest path from the first point to the rotation axis and the central axis of the inlet.

[0009] It can be understood that the larger α is, the closer the first auxiliary channel is to the first opening; the smaller α is, the farther the first auxiliary channel is from the first opening. If α is too large, it may lead to deterioration of the flow field and a worse effect of suppressing vortices. For example, when α is greater than D / 2, the first opening and the first auxiliary channel are on the same side of the central axis of the inlet, and the improvement effect of the first auxiliary channel on the flow field smoothness is relatively limited. If α is too small, it may cause the spherical flow valve to be difficult to close completely. For example, when α is less than [D - R×sin(90° - θa - θb)], even after the main channel is rotated to be perpendicular to the central axis of the inlet, the first auxiliary channel still cannot be completely blocked by the inner wall surface of the valve seat.

[0010] In an alternative embodiment, there are a third point and a fourth point on the edge of the outlet. The third point and the fourth point are the two endpoints of one of the diameters of the outlet, and the line connecting the third point and the fourth point is perpendicular to the rotation axis; when the valve core rotates until the second auxiliary channel is parallel to the central axis of the outlet, the third point is opposite to the second opening, and the distance from the fourth point to the second auxiliary channel is α, satisfying [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2, where D is the diameter of the outlet, R is the diameter of the valve core, θa is the angle between the second auxiliary channel and the main channel, and θb is the angle between the shortest path from the third point to the rotation axis and the central axis of the outlet.

[0011] In an alternative embodiment, the cross-sectional area S1 of the first auxiliary channel satisfies: 0.03Sa ≤ S1 ≤ 0.35Sa; the cross-sectional area S2 of the second auxiliary channel satisfies: 0.03Sb ≤ S2 ≤ 0.35Sb; where Sa is the inlet area and Sb is the outlet area.

[0012] In an alternative embodiment, the inlet and the outlet have the same size and their central axes coincide.

[0013] In an alternative embodiment, the first auxiliary channel and the second auxiliary channel are centrosymmetric with respect to the rotation axis. In the case where the first auxiliary channel and the second auxiliary channel are centrosymmetric with respect to the rotation axis, the flow field is better, and when the fluid medium flows in the reverse direction, the spherical flow valve can still exhibit the same performance.

[0014] In an alternative embodiment, a plurality of first auxiliary channels are formed on the valve core, and the plurality of first auxiliary channels are arranged at intervals along the extension direction of the rotation axis;

[0015] And / or, a plurality of second auxiliary channels are formed on the valve core, and the plurality of second auxiliary channels are arranged at intervals along the extension direction of the rotation axis.

[0016] By providing a plurality of first auxiliary channels and a plurality of second auxiliary channels, the flow path of the fluid can be made more dispersed, avoiding the generation of vortices in strong fluid jets.

[0017] In an alternative embodiment, the first auxiliary passage is a long hole, and the inner diameter of the first auxiliary passage in the circumferential direction of the valve core is smaller than the inner diameter in the axial direction of the valve core;

[0018] and / or, the second auxiliary passage is a long hole, and the inner diameter of the second auxiliary passage in the circumferential direction of the valve core is smaller than the inner diameter in the axial direction of the valve core.

[0019] In a second aspect, the present application provides an air conditioning system, including a pipeline for transporting refrigerant, and a spherical flow valve according to any one of the foregoing embodiments is provided on the pipeline.

[0020] In an alternative embodiment, the air conditioning system includes a compressor, an outdoor heat exchanger, and a plurality of indoor heat exchangers. The outdoor heat exchanger can be selectively switched to communicate with the exhaust side or the suction side of the compressor through a reversing valve;

[0021] The air conditioning system further includes a liquid pipe diverter, a high-pressure gas pipe diverter, and a low-pressure gas pipe diverter. The plurality of indoor heat exchangers are respectively mounted on a plurality of indoor unit branch lines. One side of the outdoor heat exchanger away from the compressor is connected to one end of each indoor unit branch line through the liquid pipe diverter, and the other ends of each indoor unit branch line converge through the low-pressure gas pipe diverter, and the low-pressure gas pipe diverter is connected to the suction side of the compressor. A first valve is provided on the indoor unit branch line between each indoor heat exchanger and the low-pressure gas pipe diverter, and the first valve is a spherical flow valve;

[0022] The intake end of the high-pressure gas pipe diverter is connected to the exhaust side of the compressor, and the plurality of outlet ends of the high-pressure gas pipe diverter are respectively connected to a plurality of indoor unit branch lines through a plurality of high-pressure gas branch lines. The connection position of the high-pressure gas branch line and the indoor unit branch line is between the first valve and the indoor heat exchanger, and a second valve is provided on the high-pressure gas branch line.

[0023] In this embodiment, since the low-pressure gaseous refrigerant flows through the first valve, the first valve can use a spherical flow valve to adjust the flow rate, and can suppress the noise of the first valve, improving the user experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a schematic diagram of the flow field of an existing spherical flow valve during flow restriction;

[0025] Figure 2 It is a schematic diagram of a spherical flow valve according to an embodiment of the present application; Figure 3 It is a schematic diagram of a spherical flow valve according to an embodiment of the present application in a flow restriction state;

[0026] Figure 4 It is a schematic diagram of the flow field of a spherical flow valve according to an embodiment of the present application during flow restriction;

[0027] Figure 5Schematic diagram of a spherical flow valve in a fully closed state in an embodiment of the present application;

[0028] Figure 6 Schematic diagram of the flow field when the first auxiliary passage is relatively close to the first opening in an embodiment of the present application;

[0029] Figure 7 Schematic diagram of the flow field when the first auxiliary passage is relatively far from the first opening in an embodiment of the present application;

[0030] Figure 8 Schematic diagram of a valve core in another embodiment of the present application;

[0031] Figure 9 Schematic diagram of a valve core in still another embodiment of the present application;

[0032] Figure 10 Schematic diagram of an air conditioning system in an embodiment of the present application.

[0033] Explanation of reference numerals: 010 - air conditioning system; 100 - outdoor unit; 110 - compressor; 120 - outdoor heat exchanger; 122 - outdoor unit branch line; 123 - outdoor unit expansion valve; 130 - liquid pipe diverter; 140 - low - pressure gas pipe diverter; 141 - first valve; 142 - low - pressure gas main line; 150 - high - pressure gas pipe diverter; 151 - second valve; 152 - high - pressure gas branch line; 153 - high - pressure gas main line; 160 - reversing valve; 161 - capillary tube; 180 - outdoor fan; 200 - indoor unit; 210 - indoor heat exchanger; 220 - indoor fan; 230 - indoor unit branch line; 240 - indoor unit expansion valve; 300 - spherical flow valve; 310 - valve seat; 311 - inlet; 312 - outlet; 320 - valve core; 321 - main passage; 3211 - first opening; 3212 - second opening; 322 - first auxiliary passage; 323 - second auxiliary passage. Detailed implementation manners

[0034] Figure 1 Schematic diagram of the flow field of an existing spherical flow valve during flow restriction. As Figure 1 shown, when the existing spherical flow valve restricts the flow, both openings of the passage are partially blocked by the inner wall surface of the valve seat, and the fluid flows into and out of the valve core locally through the unblocked opening. Since the fluid can only pass through the sole passage of the valve core, when the valve core restricts the flow, the position where the fluid enters the valve core is completely deviated from the central axis of the pipeline (or the central axis of the valve seat inlet). The fluid is forced to concentrate and enter the valve core from one side of the central axis of the pipeline and flow out concentrated from the other side. And the fluid's drastic change in flow direction will generate intense turbulence, and then generate large vortices, thus causing noise in the spherical flow valve. In the air - conditioning field, the valve is used to regulate the refrigerant flow, and the traditional spherical flow valve will cause noise, affecting the user experience.

[0035] In order to improve the problem that the spherical flow valve in the prior art is prone to generate vortices and noise when suppressing the flow, the embodiment of the present application provides a spherical flow valve. By providing an auxiliary flow passage in the valve core, the fluid has a better flow field when passing through the valve core and after passing through the valve core, suppressing the generation of large vortices, thereby reducing noise. The embodiment of the present application also provides an air conditioning system, which uses the above spherical flow valve to adjust the refrigerant flow, so it can suppress the generation of noise and improve the user experience.

[0036] To make the above objects, features and advantages of the present application more obvious and understandable, the following will describe the specific embodiments of the present application in detail with reference to the accompanying drawings.

[0037] Figure 2 Schematic diagram of a spherical flow valve 300 in an embodiment of the present application; Figure 3 Schematic diagram of the spherical flow valve 300 in the flow suppression state in an embodiment of the present application. As Figure 2 and Figure 3 shown, the spherical flow valve 300 provided by the embodiment of the present application includes a valve seat 310 and a valve core 320 disposed in the valve seat 310. Inlet ports 311 and outlet ports 312 are respectively formed on opposite sides of the valve seat 310. Among them, the inlet port 311 allows fluid to enter the spherical flow valve 300, and the outlet port 312 allows fluid to enter the spherical flow valve 300. In this embodiment, the case where the fluid flows from left to right is taken as an example for introduction. Therefore, the inlet port 311 is disposed on the left side of the valve seat 310, and the outlet port 312 is disposed on the right side of the valve seat 310. The inlet port 311 and the outlet port 312 can be connected to external pipelines, for example, by welding or screwing. The valve core 320 can rotate relative to the valve seat 310 around the rotation axis. A main channel 321, a first auxiliary channel 322, and a second auxiliary channel 323 are formed in the valve core 320. The main channel 321 penetrates through the valve core 320 and both ends form a first opening 3211 and a second opening 3212. By rotating the valve core 320, the first opening 3211 and the second opening 3212 can be selectively communicated with the inlet port 311 and the outlet port 312 respectively, or the first opening 3211 and the second opening 3212 can be blocked by the inner wall surface of the valve seat 310; the first auxiliary channel 322 and the second auxiliary channel 323 are respectively located on opposite sides in the radial direction of the main channel 321, and one end extends to the inner side wall of the main channel 321, and the other end extends to the outer peripheral surface of the valve core 320; during the rotation stroke of the valve core 320 relative to the valve seat 310, there is a flow suppression state. When the valve core 320 is in the flow suppression state, a part of the first opening 3211 and the first auxiliary channel 322 are communicated with the inlet port 311, and a part of the second opening 3212 and the second auxiliary channel 323 are communicated with the second opening 3212.

[0038] In this embodiment, the sizes of the inlet 311 and the outlet 312 on the valve seat 310 are the same and their central axes coincide. Therefore, when the fluid flows reversely (i.e., flows in through the current inlet 311 and flows out through the current inlet 311), the spherical flow valve 300 can still play the same regulating role.

[0039] In traditional spherical flow valves, the reason for noise generation is that when the valve core restricts the flow, the axis of the channel on the valve core forms an angle with the central axes of the inlet and the outlet on the valve seat. The turbulent fluid is forced to flow through the channel. Due to the unreasonable flow field, vortices are likely to be generated inside the valve core and even outside the outlet, thus generating noise. In the embodiment of the present application, by adding a first auxiliary channel 322 and a second auxiliary channel 323 to the valve core 320, when the valve core 320 is in the flow-restricting state, the fluid can enter from the first opening 3211 of the main channel 321 or from the first auxiliary channel 322, and the fluid can flow out from the second opening 3212 of the main channel 321 or from the second auxiliary channel 323. Due to the change in the flow field, the fluid flow becomes smoother, which can eliminate or reduce the generated vortices, thereby reducing noise generation. Figure 4 This is a schematic diagram of the flow field of the spherical flow valve 300 in the flow-restricting state in an embodiment of the present application. As Figure 4 shown, by adding a first auxiliary channel 322 and a second auxiliary channel 323 to the valve core 320, the flow field is optimized, the flow strands are dispersed, the fluid does not concentrate on flowing in and out through the two openings of the main channel 321, and the size of the vortices is smaller, so it is not easy to generate noise.

[0040] Figure 5 This is a schematic diagram of the spherical flow valve 300 being completely closed in an embodiment of the present application. When it is necessary to completely close the spherical flow valve 300, the valve core 320 can be rotated so that the first opening 3211, the second opening 3212 on the main channel 321, and the openings of the first auxiliary channel 322 and the second auxiliary channel 323 on the surface of the valve core 320 are all blocked by the valve seat 310. As Figure 5 shown, in this case, the fluid will be blocked by the valve core 320 and cannot flow from the inlet 311 of the valve seat 310 to the outlet 312, thereby achieving fluid cut-off. In the embodiment of the present application, when the main channel 321 of the valve core 320 is perpendicular to the central axis of the inlet 311 and / or the outlet 312, the spherical flow valve 300 can be in a completely closed state. When it is necessary to completely open the spherical flow valve 300, only the valve core 320 needs to be rotated so that the first opening 3211 of the main channel 321 faces the inlet 311 and the second opening 3212 faces the outlet 312.

[0041] Please continue to refer to Figure 3, in this embodiment, when the spool 320 is in the flow suppression state, the first opening 3211 and the first auxiliary passage 322 are on opposite sides of the central axis of the inlet 311, and the second opening 3212 and the second auxiliary passage 323 are on opposite sides of the central axis of the outlet 312. Since when the spool 320 is in the flow suppression state, the first opening 3211 / the second opening 3212 has been deflected to one side of the central axis of the inlet 311 / the outlet 312 and is partially blocked. At this time, if the first auxiliary passage 322 / the second auxiliary passage 323 is on the same side as the first opening 3211 / the second opening 3212, it is not conducive to the smoothness of fluid flow. Therefore, the first auxiliary passage 322 and the first opening 3211 are arranged on opposite sides of the central axis of the inlet 311, and the second auxiliary passage 323 and the second opening 3212 are arranged on opposite sides of the central axis of the outlet 312, which can optimize the flow field, make the fluid flow more smoothly, and reduce the generation of vortices and noise. For example, in Figure 3 In the embodiment, a part of the fluid at the inlet 311 enters the first opening 3211 from a position above the central axis of the inlet 311, and another part enters the first auxiliary passage 322 from a position below the central axis of the inlet 311; a part of the fluid at the outlet 312 flows out from the second opening 3212 from a position below the central axis of the outlet 312, and another part flows out from the second auxiliary passage 323 from a position above the central axis of the outlet 312.

[0042] In this embodiment, the central axes of the first auxiliary passage 322, the second auxiliary passage 323, the inlet 311, and the outlet 312 are all perpendicular to the rotation axis. In Figure 3 and Figure 5 In, the rotation axis is perpendicular to Figure 3 , Figure 5 's display plane and is located at the geometric center of the spool 320. When the spool 320 rotates until the first auxiliary passage 322 is parallel to the central axis of the inlet 311 or when the spool 320 rotates until the second auxiliary passage 323 is parallel to the central axis of the outlet 312, the spool 320 is in the flow suppression state. It can be understood that when the channel is closer to being parallel to the central axes of the outlet 312 and the inlet 311, the fluid is less likely to generate vortices due to the change in flow direction when passing through the channel. In this embodiment, since the spool 320 is in the flow suppression state when the first auxiliary passage 322 is parallel to the central axis of the inlet 311 or when the second auxiliary passage 323 is parallel to the central axis of the outlet 312, it means that the first auxiliary passage 322 and the second auxiliary passage 323 have a relatively small deflection angle (even parallel) with respect to the central axes of the inlet 311 and the outlet 312 in the flow suppression state of the spool 320, and the fluid can pass through the first auxiliary passage 322 and the second auxiliary passage 323 more smoothly, reducing the generation of eddy currents and noise.

[0043] In this embodiment, the first auxiliary passage 322 and the second auxiliary passage 323 are parallel to each other; further, the first auxiliary passage 322 and the second auxiliary passage 323 are centrosymmetric with respect to the center of the rotation axis. When the first auxiliary passage 322 and the second auxiliary passage 323 are centrosymmetric with respect to the center of the rotation axis, the flow field is better, and when the fluid medium flows in the reverse direction, the spherical flow valve 300 can still perform the same performance. Since the first auxiliary passage 322 and the second auxiliary passage 323 are parallel to each other and centrosymmetric, when the first auxiliary passage 322 is parallel to the central axis of the inlet 311, the second auxiliary passage 323 is parallel to the central axis of the outlet 312.

[0044] In this embodiment, the edge of the inlet 311 has a first point (point a in the figure) and a second point (point b in the figure). The first point and the second point are the two endpoints of one of the diameters of the inlet 311, and the line connecting the first point and the second point is perpendicular to the rotation axis. When the valve core 320 rotates until the first auxiliary passage 322 is parallel to the central axis of the inlet 311, the first point is opposite to the first opening 3211, and the distance from the second point to the first auxiliary passage 322 is α, satisfying [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2, where D is the diameter of the inlet 311, R is the diameter of the valve core 320, θa is the angle between the first auxiliary passage 322 and the main passage 321, and θb is the angle between the shortest path from the first point to the rotation axis and the central axis of the inlet 311. For the convenience of representation, in Figure 5 it, [D - R×sin(90° - θa - θb)] / 2 is represented by Rc.

[0045] It can be understood that the larger α is, the closer the first auxiliary passage 322 is to the first opening 3211; the smaller α is, the farther the first auxiliary passage 322 is from the first opening 3211. If α is too large, the optimization effect of the flow field may not be obvious, and the effect of suppressing vortices becomes worse. For example, when α is greater than D / 2, when the first auxiliary passage 322 is parallel to the central axis of the inlet 311, the first opening 3211 and the first auxiliary passage 322 will be on the same side of the central axis of the inlet 311, as Figure 6 shown, the improvement effect of the first auxiliary passage 322 on the smoothness of the flow field is relatively limited. If α is too small, it may cause the spherical flow valve 300 to be not easily completely closed. For example, when α is less than Rc, even if the main passage 321 is rotated to be perpendicular to the central axis of the inlet 311, the first auxiliary passage 322 still cannot be completely blocked by the inner wall surface of the valve seat 310, as Figure 7 shown, in Figure 7 the shown case, in order to completely close the spherical flow valve 300, it is necessary to further rotate the valve core 320 so that the main passage 321, the first auxiliary passage 322 and the second auxiliary passage 323 are completely blocked by the valve seat 310.

[0046] On the edge of the outlet 312, there are a third point (point c in the figure) and a fourth point (point d in the figure). The third point and the fourth point are the two endpoints of a diameter of the outlet 312, and the line connecting the third point and the fourth point is perpendicular to the rotation axis. Since the first auxiliary channel 322 and the second auxiliary channel 323 are centrosymmetric in this embodiment, the inlet 311 and the outlet 312 have the same size and their central axes coincide. Therefore, the angle between the second auxiliary channel 323 and the main channel 321 is also θa, and the angle between the shortest path from the third point to the rotation axis and the central axis of the outlet 312 is also θb. When the spool 320 rotates to make the second auxiliary channel 323 parallel to the central axis of the outlet 312, the third point is opposite to the second opening 3212, and it also satisfies [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2.

[0047] It can be understood that in other alternative embodiments, especially in embodiments where the first auxiliary channel 322 and the second auxiliary channel 323 are not centrosymmetric, one of the first auxiliary channel 322 or the second auxiliary channel 323 can be made to satisfy the above inequality, which can also play a role in improving the flow field.

[0048] Since the inner diameters of the first auxiliary channel 322 and the second auxiliary channel 323 will affect the flow field, too large an inner diameter will lead to a reduction in the flow inhibition effect, that is, a large amount of fluid flows through the auxiliary channels, and it is difficult to reduce the overall flow rate of the spherical flow valve 300. While too small an inner diameter will result in too little flow rate through the auxiliary channels in the flow inhibition state, and thus the improvement effect of the auxiliary channels on the flow field is limited. Therefore, in this embodiment, the cross-sectional area S1 of the first auxiliary channel 322 satisfies: 0.03Sa ≤ S1 ≤ 0.35Sa; the cross-sectional area S2 of the second auxiliary channel 323 satisfies: 0.03Sb ≤ S2 ≤ 0.35Sb; where Sa is the area of the inlet 311 and Sb is the area of the outlet 312.

[0049] In the embodiment of the present application, the angle θa between the first auxiliary channel 322 and the second auxiliary channel 323 and the main channel 321 will also affect the flow field. Optionally, θa has the following characteristics: when the first auxiliary channel 322 and the second auxiliary channel 323 are not provided, when the main channel 321 deflects by θa relative to the central axes of the inlet 311 and the outlet 312, the noise is the largest or the vortex is the most obvious. Specifically, the deflection angle of the spool 320 can be continuously adjusted through experiments or numerical simulation, and the angle by which the main channel 321 deflects relative to the central axes of the inlet 311 and the outlet 312 when the noise or the vortex is the largest is recorded as θa. It can be understood that in the embodiment of the present application, the first auxiliary channel 322 and the second auxiliary channel 323 parallel to the central axes of the inlet 311 and the outlet 312 are opened in the flow inhibition state where the main channel 321 has the largest noise or vortex, so as to improve the suppression effect on noise and vortex.

[0050] Figure 8 This is a schematic diagram of the valve core 320 in another embodiment of the present application. Optionally, a plurality of first auxiliary channels 322 are provided on the valve core 320, and the plurality of first auxiliary channels 322 are arranged at intervals along the extending direction of the rotation axis. As Figure 8 shown, 3 first auxiliary channels 322 are provided on the valve core 320. Similarly, a plurality of second auxiliary channels 323 can be provided on the valve core 320, and the plurality of second auxiliary channels 323 are arranged at intervals along the extending direction of the rotation axis. By providing a plurality of first auxiliary channels 322 and a plurality of second auxiliary channels 323, the flow path of the fluid can be made more dispersed, avoiding the generation of vortices by strong fluid jets.

[0051] Figure 9 This is a schematic diagram of the valve core 320 in still another embodiment of the present application. Optionally, the first auxiliary channel 322 is a long hole, and the inner diameter of the first auxiliary channel 322 in the circumferential direction of the valve core 320 is smaller than the inner diameter in the axial direction of the valve core 320. As Figure 9 shown, the first auxiliary channel 322 is a long hole, so its inner cavity is a flat cavity, the width direction of the flat cavity is consistent with the extending direction of the rotation axis of the valve core 320 (i.e., the axial direction of the valve core 320), and the thickness direction of the flat cavity is consistent with the circumferential direction of the valve core 320. Similarly, the second auxiliary channel 323 can also be a long hole, and the inner diameter of the second auxiliary channel 323 in the circumferential direction of the valve core 320 is smaller than the inner diameter in the axial direction of the valve core 320. This makes the fluid jet more dispersed in the auxiliary channel, the flow rate can be slowed down, and vortices are not easily generated.

[0052] In a second aspect, the present application provides an air conditioning system 010, including a pipeline for conveying refrigerant, and the pipeline is provided with the spherical flow valve 300 in any one of the foregoing embodiments.

[0053] Figure 10 This is a schematic diagram of the air conditioning system 010 in an embodiment of the present application. As Figure 10 shown, the air conditioning system 010 provided by the embodiment of the present application includes an indoor unit 200 and a plurality of outdoor units 100. The outdoor unit 100 includes a compressor 110, an outdoor heat exchanger 120, a liquid pipe diverter 130, a high-pressure gas pipe diverter 150, a low-pressure gas pipe diverter 140, and an external fan 180. The indoor unit 200 includes an indoor heat exchanger 210 and a corresponding internal fan 220.

[0054] In this embodiment, multiple indoor heat exchangers 210 are mounted on multiple indoor unit branch lines 230 in a one-to-one correspondence. The outdoor heat exchanger 120 is connected to the compressor 110 through a reversing valve 160. Through the reversing valve 160, the outdoor heat exchanger 120 can be selectively switched to communicate with the exhaust side or the suction side of the compressor 110. Therefore, it can be determined whether the outdoor heat exchanger 120 functions as a condenser or an evaporator. One side of the outdoor heat exchanger 120 away from the compressor 110 is connected to one end of each indoor unit branch line 230 through a liquid pipe diverter 130. The other ends of the indoor unit branch lines 230 converge through a low-pressure gas pipe diverter 140, and the low-pressure gas pipe diverter 140 is connected to the suction side of the compressor 110. It can be understood that the low-pressure gas pipe diverter 140 has multiple intake ends and one outlet end. The multiple intake ends are connected to the multiple indoor unit branch lines 230 in a one-to-one correspondence, and the outlet end is connected to the suction side of the compressor 110. A first valve 141 is provided on the indoor unit branch line 230 between each indoor heat exchanger 210 and the low-pressure gas pipe diverter 140, and an indoor unit expansion valve 240 is provided on the indoor unit branch line 230 between each indoor heat exchanger 210 and the liquid pipe diverter 130.

[0055] The high-pressure gas pipe diverter 150 has one intake end and multiple outlet ends. The intake end of the high-pressure gas pipe diverter 150 is connected to the exhaust side of the compressor 110. The multiple outlet ends of the high-pressure gas pipe diverter 150 are connected to the multiple indoor unit branch lines 230 through multiple high-pressure gas branch lines 152 in a one-to-one correspondence. The connection position of the high-pressure gas branch line 152 and the indoor unit branch line 230 is between the first valve 141 and the indoor heat exchanger 210, and a second valve 151 is provided on the high-pressure gas branch line 152.

[0056] By controlling the first valve 141 and the second valve 151, the free cooling and heating function can be realized. For example, in the refrigeration working condition, the outdoor heat exchanger 120 functions as a condenser to release heat, and each indoor heat exchanger 210 functions as an evaporator to absorb heat. At this time, the first valves 141 on the indoor unit branch lines 230 are opened, and the second valves 151 on the high-pressure gas branch lines 152 are closed. The refrigerant sequentially passes through the exhaust side of the compressor 110, the outdoor heat exchanger 120, the liquid pipe diverter 130, the indoor heat exchanger 210, and the low-pressure gas pipe diverter 140, and finally converges into the suction side of the compressor 110 to complete a cycle. When one or more (should be less than the total number of the current refrigeration-running indoor units 200) indoor units 200 need to be changed to the heating mode, the first valve 141 on the corresponding indoor unit branch line 230 is closed, and the second valve 151 on the corresponding high-pressure gas branch line 152 is opened. At this time, for the refrigerant of the heating indoor unit 200, it sequentially passes through the exhaust side of the compressor 110, the high-pressure gas pipe diverter 150, the heating indoor heat exchanger 210, the liquid diverter, the refrigeration indoor heat exchanger 210, and the low-pressure gas pipe diverter 140, and finally converges into the suction side of the compressor 110 to complete a cycle.

[0057] In Figure 10 Figure 10 In the embodiment, the air conditioning system 010 includes a reversing valve 160. The outdoor unit branch line 122 is communicated with the compressor 110 through the reversing valve 160, and an outdoor unit expansion valve 123 is arranged on the outdoor unit branch line 122. The function of the reversing valve 160 is to control whether the outdoor heat exchanger 120 is used for condensation or evaporation.

[0058]

[0058] Further, in the embodiment, the reversing valve 160 is a four-way reversing valve. The reversing valve 160 includes a C port, a D port, an S port and an E port. The C port of the reversing valve 160 is communicated with the outdoor unit branch line 122, the D port of the reversing valve 160 is communicated with the exhaust side of the compressor 110, the S port of the reversing valve 160 is communicated with the suction side of the compressor 110, and the E port of the reversing valve 160 is communicated with the suction side of the compressor 110 through a capillary tube 161. The C port of the reversing valve 160 can be selectively communicated with the D port or the S port. When the C port is communicated with the D port, the E port is communicated with the S port, and the outdoor unit 100 is used as a condenser; when the C port is communicated with the S port, the E port is communicated with the D port, and the outdoor unit 100 is used as an evaporator.

[0059]

[0059] In this embodiment, the capillary tube 161 has a smaller pipe diameter compared with other pipelines, its flow rate is very small and the resistance is very large. Therefore, it does not cause a short circuit in the refrigerant cycle. In other words, even if the E port is communicated with the D port, it will not cause a large amount of refrigerant to directly enter the suction side from the exhaust side of the compressor 110 through the capillary tube 161. The refrigerant still mainly enters the heat exchanger through other pipelines (in this embodiment, it enters the indoor heat exchanger 210 through the high-pressure gas main line 153). During the discussion of the heating and cooling processes of the refrigerant cycle, the capillary tube 161 can be regarded as an open circuit.

[0060]

[0060] In this embodiment, the inlet end of the high-pressure gas splitter 150 is communicated with the exhaust side of the compressor 110 through the high-pressure gas main line 153. Specifically, one end of the high-pressure gas main line 153 is connected to the inlet end of the high-pressure gas splitter 150, and the other end is connected to the pipeline between the reversing valve 160 and the compressor 110. The low-pressure gas splitter 140 is communicated with the suction side of the compressor 110 through the low-pressure gas main line 142.

[0061]

[0061] In this embodiment, the first valve 141 selects the spherical flow valve 300 provided in the above embodiment of the present application. Since the low-pressure gaseous refrigerant flows through the first valve 141, the first valve 141 can use the spherical flow valve 300 to adjust the flow rate, and can suppress the noise of the first valve 141, improving the user experience. In other alternative embodiments, the second valve 151 or the indoor unit expansion valve 240 can also select the spherical flow valve 300.

[0062] Although the present application is disclosed as above, the present application is not limited thereto. Any person skilled in the art can make various changes and modifications without departing from the spirit and scope of the present application. Therefore, the protection scope of the present application shall be subject to the scope defined by the claims.

Claims

1. A spherical flow valve, characterized in that, It includes a valve seat (310) and a valve core (320) disposed within the valve seat (310). Opposite sides of the valve seat (310) are respectively provided with an inlet (311) and an outlet (312). The valve core (320) can rotate relative to the valve seat (310) about a rotation axis. A main passage (321), a first auxiliary passage (322), and a second auxiliary passage (323) are provided on the valve core (320). The main passage (321) penetrates through the valve core (320) and both ends form a first opening (3211) and a second opening (3212). By rotating the valve core (320), the first opening (3211) and the second opening (3212) can be selectively communicated with the inlet (311) and the outlet (312) respectively, or the first opening (3211) and the second opening (3212) can be blocked by the inner wall surface of the valve seat (310). The first auxiliary passage (322) and the second auxiliary passage (323) are respectively located on opposite sides in the radial direction of the main passage (321), and one end extends to the inner side wall of the main passage (321), and the other end extends to the outer peripheral surface of the valve core (320). During the rotation stroke of the valve core (320) relative to the valve seat (310), there is a flow inhibition state. When the valve core (320) is in the flow inhibition state, a part of the first opening (3211) and the first auxiliary passage (322) are communicated with the inlet (311), and a part of the second opening (3212) and the second auxiliary passage (323) are communicated with the second opening (3212).

2. The spherical flow valve according to claim 1, wherein When the valve core (320) is in the flow inhibition state, the first opening (3211) and the first auxiliary passage (322) are on opposite sides of the central axis of the inlet (311), and the second opening (3212) and the second auxiliary passage (323) are on opposite sides of the central axis of the outlet (312).

3. The spherical flow valve according to claim 2, wherein, The central axes of the first auxiliary passage (322), the second auxiliary passage (323), the inlet (311), and the outlet (312) are all perpendicular to the rotation axis. When the valve core (320) rotates until the first auxiliary passage (322) is parallel to the central axis of the inlet (311) or when the valve core (320) rotates until the second auxiliary passage (323) is parallel to the central axis of the outlet (312), the valve core (320) is in the flow inhibition state.

4. The spherical flow valve according to claim 3, characterized in that, The edge of the inlet (311) has a first point and a second point, where the first point and the second point are the two endpoints of one of the diameters of the inlet (311), and the line connecting the first point and the second point is perpendicular to the rotation axis; when the valve core (320) rotates until the first auxiliary channel (322) is parallel to the central axis of the inlet (311), the first point is opposite to the first opening (3211), and the distance from the second point to the first auxiliary channel (322) is α, satisfying [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2, where D is the diameter of the inlet (311), R is the diameter of the valve core (320), θa is the included angle between the first auxiliary channel (322) and the main channel (321), and θb is the included angle between the shortest path from the first point to the rotation axis and the central axis of the inlet (311).

5. The spherical flow valve according to claim 3, characterized in that The edge of the outlet (312) has a third point and a fourth point, where the third point and the fourth point are the two endpoints of one of the diameters of the outlet (312), and the line connecting the third point and the fourth point is perpendicular to the rotation axis; when the valve core (320) rotates until the second auxiliary channel (323) is parallel to the central axis of the outlet (312), the third point is opposite to the second opening (3212), and the distance from the fourth point to the second auxiliary channel (323) is α, satisfying [D - R×sin(90° - θa - θb)] / 2 < α ≤ D / 2, where D is the diameter of the outlet (312), R is the diameter of the valve core (320), θa is the included angle between the second auxiliary channel (323) and the main channel (321), and θb is the included angle between the shortest path from the third point to the rotation axis and the central axis of the outlet (312).

6. The spherical flow valve according to claim 1, wherein The cross-sectional area S1 of the first auxiliary channel (322) satisfies: 0.03Sa ≤ S1 ≤ 0.35Sa; the cross-sectional area S2 of the second auxiliary channel (323) satisfies: 0.03Sb ≤ S2 ≤ 0.35Sb; where Sa is the area of the inlet (311) and Sb is the area of the outlet (312).

7. The spherical flow valve according to claim 1, characterized in that, The inlet (311) and the outlet (312) have the same size and their central axes coincide.

8. The spherical flow valve according to claim 1, characterized in that, The first auxiliary channel (322) and the second auxiliary channel (323) are centrosymmetric with respect to the rotation axis.

9. The spherical flow valve according to claim 1, wherein, A plurality of the first auxiliary channels (322) are provided on the valve core (320), and the plurality of the first auxiliary channels (322) are arranged at intervals along the extension direction of the rotation axis; and / or, a plurality of the second auxiliary channels (323) are provided on the valve core (320), and the plurality of the second auxiliary channels (323) are arranged at intervals along the extension direction of the rotation axis.

10. The spherical flow valve according to claim 1, wherein, The first auxiliary passage (322) is an elongated hole, and the inner diameter of the first auxiliary passage (322) in the circumferential direction of the valve core (320) is smaller than the inner diameter in the axial direction of the valve core (320); and / or, the second auxiliary passage (323) is an elongated hole, and the inner diameter of the second auxiliary passage (323) in the circumferential direction of the valve core (320) is smaller than the inner diameter in the axial direction of the valve core (320).

11. An air conditioning system, characterized in that, It includes a pipeline for conveying refrigerant, and the spherical flow valve (300) described in any one of claims 1-10 is provided on the pipeline.

12. The air-conditioning system according to claim 11, characterized in that, The air conditioning system (010) includes a compressor (110), an outdoor heat exchanger (120) and a plurality of indoor heat exchangers (210), and the outdoor heat exchanger (120) can be selectively switched to communicate with the exhaust side or the suction side of the compressor (110) through a reversing valve (160); The air conditioning system (010) further includes a liquid pipe splitter (130), a high-pressure gas pipe splitter (150) and a low-pressure gas pipe splitter (140). A plurality of the indoor heat exchangers (210) are respectively mounted on a plurality of indoor unit branch lines (230). One side of the outdoor heat exchanger (120) away from the compressor (110) is connected to one end of each of the indoor unit branch lines (230) through the liquid pipe splitter (130). The other ends of each of the indoor unit branch lines (230) converge through the low-pressure gas pipe splitter (140), and the low-pressure gas pipe splitter (140) is connected to the suction side of the compressor (110). A first valve (141) is provided on the indoor unit branch line (230) between each indoor heat exchanger (210) and the low-pressure gas pipe splitter (140), and the first valve (141) is the spherical flow valve (300); The inlet end of the high-pressure gas pipe splitter (150) is connected to the exhaust side of the compressor (110), and a plurality of outlet ends of the high-pressure gas pipe splitter (150) are respectively connected to a plurality of the indoor unit branch lines (230) through a plurality of high-pressure gas branch lines (152). The connection position of the high-pressure gas branch line (152) and the indoor unit branch line (230) is located between the first valve (141) and the indoor heat exchanger (210), and a second valve (151) is provided on the high-pressure gas branch line (152).

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