Spherical flow valve and air conditioning system

Abstract

The utility model 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 utility model, 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] The present application relates to the technical field of air conditioning, and in particular to a spherical flow valve and an air conditioning system. Background Art

[0002] The ball flow valve is installed in the pipeline and can play a role in regulating the flow of the medium. The valve core of the traditional ball flow valve is provided with a channel, 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 part of the opening of the channel, while the other part of the opening of the channel can still allow the medium to flow, that is, the opening area allowing the medium to flow becomes smaller, thereby suppressing the flow. However, when suppressing the flow of the medium, the traditional ball flow valve is prone to high noise. Utility Model Content

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

[0004] To solve the above problems, in the first aspect, the present application provides a spherical flow valve, including a valve seat and a valve core arranged in the valve seat, an inlet and an outlet are respectively provided on opposite sides of the valve seat, the valve core can rotate around a rotation axis relative to the valve seat, a main channel, a first auxiliary channel and a second auxiliary channel are provided on the valve core, the main channel runs through the valve core and forms a first opening and a second opening at both ends, and by rotating the valve core, the first opening and the second opening can be selectively connected to 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 of the main channel in the radial direction, 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; the valve core has a flow suppression state during the rotation stroke relative to the valve seat, and when the valve core is in the flow suppression state, a part of the first opening and the first auxiliary channel are connected to the inlet, and a part of the second opening and the second auxiliary channel are connected to the second opening.

[0005] The reason why noise is generated in traditional spherical flow valves is that when the valve core suppresses the flow, the axis of the channel on the valve core forms an angle with the central axis of the inlet and outlet on the valve seat, and the turbulent fluid is forced to flow through the channel. Due to the unreasonable flow field, vortices are easily generated inside the valve core or even outside the outlet, thereby generating noise. In the embodiment of the present application, by adding a first auxiliary channel and a second auxiliary channel, when the valve core is in a flow 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 is smoother, and the generated vortices can be eliminated or reduced, thereby reducing the generation of noise.

[0006] In an optional embodiment, when the valve core is in a flow suppression 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 a flow suppression state, the first opening / second opening has been deflected to one side of the central axis of the inlet / outlet and is partially blocked, 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 the 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 smoother, and reduce the generation of vortices and noise.

[0007] In an optional embodiment, the central axes of the first auxiliary channel, the second auxiliary channel, and the inlet and outlet are all perpendicular to the rotation axis; when the valve core rotates to the point where the first auxiliary channel is parallel to the central axis of the inlet or when the valve core rotates to the point where the second auxiliary channel is parallel to the central axis of the outlet, the valve core is in a flow-repressed state. It can be understood that when the channel is closer to being parallel to the central axes of the inlet and the outlet, the fluid is less likely to generate vortices due to changes in flow direction when passing through the channel. In this embodiment, since 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, the valve core is in a flow-repressed state, which means that in the flow-repressed state, the first auxiliary channel and the second auxiliary channel of the valve core have a small deflection angle relative to the central axis of the inlet and the outlet (even parallel), and the fluid can pass through the first auxiliary channel and the second auxiliary channel more smoothly, reducing the generation of vortices and noise.

[0008] In an optional embodiment, a first point and a second point are provided on the edge of the entrance, and the first point and the second point are two end points of one diameter of the entrance, and a line connecting the first point and the second point is perpendicular to the rotation axis; when the valve core rotates to the point where the first auxiliary channel is parallel to the central axis of the entrance, the first point is opposite to the first opening, and the distance from the second point to the first auxiliary channel is α, satisfying [DR×sin(90°-θa-θb)] / 2<α≤D / 2, wherein D is the diameter of the entrance, 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 entrance.

[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. When α is too large, the flow field may be degraded and the effect of suppressing vortex may be poor. 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 effect of the first auxiliary channel on improving the smoothness of the flow field is relatively limited. When α is too small, the spherical flow valve may not be easy to close completely. For example, when α is less than [DR×sin(90°-θa-θb)], even if the main channel is rotated to be perpendicular to the central axis of the inlet, the first auxiliary channel cannot be completely blocked by the inner wall of the valve seat.

[0010] In an optional embodiment, a third point and a fourth point are provided on the edge of the outlet, and the third point and the fourth point are two end points of one diameter of the outlet, and a line connecting the third point and the fourth point is perpendicular to the rotation axis; when the valve core rotates to the point where 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 [DR×sin(90°-θa-θb)] / 2<α≤D / 2, wherein 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 optional 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; wherein Sa is the inlet area and Sb is the outlet area.

[0012] In an alternative embodiment, the inlet and outlet are of identical size and have coincident central axes.

[0013] In an optional embodiment, the first auxiliary channel and the second auxiliary channel are symmetrical relative to the rotation axis. When the first auxiliary channel and the second auxiliary channel are symmetrical relative 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 perform the same performance.

[0014] In an optional embodiment, a plurality of first auxiliary channels are provided 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 provided 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 opening a plurality of first auxiliary channels and a plurality of second auxiliary channels, the flow path of the fluid can be made more dispersed, thus preventing strong flow streams from generating vortices.

[0017] In an optional embodiment, the first auxiliary channel is a long hole, and the inner diameter of the first auxiliary channel 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 channel is a long hole, and the inner diameter of the second auxiliary channel in the circumferential direction of the valve core is smaller than the inner diameter of the second auxiliary channel in the axial direction of the valve core.

[0019] In a second aspect, the present application provides an air-conditioning system, comprising a pipeline for conveying a refrigerant, the pipeline being provided with a ball flow valve according to any one of the aforementioned embodiments.

[0020] In an optional embodiment, the air conditioning system includes a compressor, an outdoor heat exchanger and a plurality of indoor heat exchangers, and 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 flow divider, a high-pressure gas pipe flow divider and a low-pressure gas pipe flow divider. A plurality of indoor heat exchangers are mounted on a plurality of indoor branch lines in a one-to-one correspondence. A side of the outdoor heat exchanger away from the compressor is connected to one end of each indoor branch line through the liquid pipe flow divider. The other end of each indoor branch line is converged through the low-pressure gas pipe flow divider. The low-pressure gas pipe flow divider is connected to the suction side of the compressor. A first valve is provided on the indoor branch line between each indoor heat exchanger and the low-pressure gas pipe flow divider. The first valve is a spherical flow valve.

[0022] The air inlet end of the high-pressure gas pipe diverter is connected to the exhaust side of the compressor, and the multiple air outlet ends of the high-pressure gas pipe diverter are connected to the multiple indoor unit branches one by one through multiple high-pressure gas branch lines. The connection position of the high-pressure gas branch line and the indoor unit branch line is located between the first valve and the indoor heat exchanger, and a second valve is arranged on the high-pressure gas branch line.

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

[0024] Figure 1 It is a schematic diagram of the flow field of the existing spherical flow valve when suppressing flow;

[0025] Figure 2 This is a schematic diagram of a spherical flow valve in one embodiment of the present application; Figure 3 This is a schematic diagram of a spherical flow valve in a flow suppression state in one embodiment of the present application;

[0026] Figure 4 This is a schematic diagram of the flow field of a spherical flow valve when suppressing flow in one embodiment of the present application;

[0027] Figure 5This is a schematic diagram of a spherical flow valve fully closed in one embodiment of the present application;

[0028] Figure 6 This is a schematic diagram of the flow field when the first auxiliary channel is close to the first opening in one embodiment of the present application;

[0029] Figure 7 This is a schematic diagram of the flow field when the first auxiliary channel is far away from the first opening in one embodiment of the present application;

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

[0031] Fig. 9 This is a schematic diagram of a valve core in another embodiment of the present application;

[0032] Fig.10 This is a schematic diagram of an air conditioning system in an embodiment of the present application.

[0033] Description 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-exchanger Directional valve; 161-capillary tube; 180-external 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 channel; 3211-first opening; 3212-second opening; 322-first auxiliary channel; 323-second auxiliary channel. DETAILED DESCRIPTION

[0034] Figure 1 FIG. 1 is a schematic diagram of the flow field of an existing spherical flow valve when suppressing flow. Figure 1 As shown, when the existing spherical flow valve suppresses the flow, the two openings of the channel are partially blocked by the inner wall of the valve seat, and the fluid will flow into and out of the valve core from the unblocked opening. Since the fluid can only pass through the only channel of the valve core, when the valve core suppresses 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), and the fluid is forced to enter the valve core from one side of the central axis of the pipeline and flow out from the other side. The drastic change in flow direction of the fluid will produce violent turbulence, and then produce a large vortex, which will cause the spherical flow valve to generate noise. In the field of air conditioning, valves are used to adjust the flow of refrigerant. Traditional spherical flow valves 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, which provides auxiliary circulation in the valve core so that the fluid has a better flow field when passing through the valve core and after passing through the valve core, suppresses the generation of large vortices, and thus reduces noise. The embodiment of the present application also provides an air conditioning system, which uses the above-mentioned spherical flow valve to adjust the refrigerant flow, thereby suppressing the generation of noise and improving the user experience.

[0036] In order to make the above-mentioned objects, features and advantages of the present application more obvious and easy to understand, the specific embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0037] Figure 2 This is a schematic diagram of a spherical flow valve 300 in one embodiment of the present application; Figure 3 FIG. 3 is a schematic diagram of a spherical flow valve 300 in a flow suppression state in an embodiment of the present application. Figure 2 and Figure 3 As shown, the spherical flow valve 300 provided in the embodiment of the present application includes a valve seat 310 and a valve core 320 disposed in the valve seat 310. An inlet 311 and an outlet 312 are respectively provided on opposite sides of the valve seat 310. The inlet 311 is for fluid to enter the spherical flow valve 300, and the outlet 312 is for fluid to enter the spherical flow valve 300. In this embodiment, the flow of fluid from left to right is taken as an example for introduction, so the inlet 311 is arranged on the left side of the valve seat 310, and the outlet 312 is arranged on the right side of the valve seat 310. The inlet 311 and the outlet 312 can be connected to external pipelines, such as by welding or screwing. The valve core 320 can rotate around the rotation axis relative to the valve seat 310. The valve core 320 is provided with a main channel 321, a first auxiliary channel 322, and a second auxiliary channel 323. The main channel 321 runs through the valve core 320 and forms a first opening 3211 and a second opening 3212 at both ends. By rotating the valve core 320, the first opening 3211 and the second opening 3212 can be selectively connected to 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 channel 322 and the second auxiliary channel 323 are respectively located on opposite sides of the main channel 321 in the radial direction, and one end extends to the inner wall of the main channel 321, and the other end extends to the outer peripheral surface of the valve core 320; the valve core 320 has a flow suppression state during the rotation stroke relative to the valve seat 310. 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 connected to the inlet 311, and a part of the second opening 3212 and the second auxiliary channel 323 are connected to the second opening 3212.

[0038] In this embodiment, the inlet 311 and the outlet 312 on the valve seat 310 are of the same size and have the same central axis. Therefore, when the fluid flows in the reverse direction (i.e., the current inlet 311 flows in, and the current inlet 311 flows out), the ball flow valve 300 can still play the same regulating role.

[0039] The reason for the noise in the traditional spherical flow valve is that when the valve core suppresses the flow, the axis of the channel on the valve core forms an angle with the central axis of the inlet and outlet on the valve seat, and the turbulent fluid is forced to flow through the channel. Due to the unreasonable flow field, it is easy to generate vortices inside the valve core or even outside the outlet, thereby 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 a flow suppression 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 is smoother, and the generated vortices can be eliminated or reduced, thereby reducing the generation of noise. Figure 4 Schematic diagram of the flow field of the spherical flow valve 300 when the flow is suppressed in one embodiment of the present application. Figure 4 As 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 streams are dispersed, the fluid will not flow in and out from the two openings of the main channel 321, and the size of the vortex is smaller, so it is not easy to generate noise.

[0040] Figure 5 Schematic diagram of a fully closed spherical flow valve 300 in one embodiment of the present application. When the spherical flow valve 300 needs to be fully closed, 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. Figure 5 As 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 cutoff. 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 fully closed state. When the spherical flow valve 300 needs to be fully opened, it is only necessary to rotate the valve core 320 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 3In this embodiment, when the valve core 320 is in the flow suppression state, the first opening 3211 and the first auxiliary channel 322 are on the opposite sides of the central axis of the inlet 311, and the second opening 3212 and the second auxiliary channel 323 are on the opposite sides of the central axis of the outlet 312. When the valve core 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 channel 322 / the second auxiliary channel 323 is on the same side as the first opening 3211 / the second opening 3212, it is not conducive to the smoothness of the fluid flow. Therefore, setting the first auxiliary channel 322 and the first opening 3211 on the opposite sides of the central axis of the inlet 311, and setting the second auxiliary channel 323 and the second opening 3212 on the opposite sides of the central axis of the outlet 312 can optimize the flow field, make the fluid flow smoother, and reduce the generation of vortices and noise. For example, in Figure 3 In the embodiment, a portion 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 portion enters the first auxiliary channel 322 from a position below the central axis of the inlet 311; a portion of the fluid at the outlet 312 flows out of the second opening 3212 from a position below the central axis of the outlet 312, and another portion flows out of the second auxiliary channel 323 from a position above the central axis of the outlet 312.

[0042] In this embodiment, the central axes of the first auxiliary channel 322, the second auxiliary channel 323, the inlet 311, and the outlet 312 are all perpendicular to the rotation axis. Figure 3 and Figure 5 The rotation axis is perpendicular to Figure 3 , Figure 5 The display plane is located at the geometric center of the valve core 320. When the valve core 320 rotates to the central axis of the first auxiliary channel 322 parallel to the inlet 311 or when the valve core 320 rotates to the central axis of the second auxiliary channel 323 parallel to the outlet 312, the valve core 320 is in a flow-repressing state. It can be understood that when the channel approaches to being parallel to the central axis of the outlet 312 and the inlet 311, the fluid is less likely to generate vortices due to the change of flow direction when passing through the channel. In this embodiment, since the first auxiliary channel 322 is parallel to the central axis of the inlet 311 or the second auxiliary channel 323 is parallel to the central axis of the outlet 312, the valve core 320 is in a flow-repressing state, which means that the first auxiliary channel 322 and the second auxiliary channel 323 of the valve core 320 are relatively small (even parallel) relative to the central axis of the inlet 311 and the outlet 312 in the flow-repressing state, and the fluid can pass through the first auxiliary channel 322 and the second auxiliary channel 323 more smoothly, reducing the generation of vortices and noise.

[0043] In this embodiment, the first auxiliary channel 322 and the second auxiliary channel 323 are parallel to each other; further, the first auxiliary channel 322 and the second auxiliary channel 323 are symmetrical with respect to the center of the rotation axis. When the first auxiliary channel 322 and the second auxiliary channel 323 are symmetrical 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 exert the same performance. Since the first auxiliary channel 322 and the second auxiliary channel 323 are parallel to each other and symmetrical with respect to the center, when the first auxiliary channel 322 is parallel to the center axis of the inlet 311, the second auxiliary channel 323 is parallel to the center 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 end points 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 [DR×sin(90°-θa-θb)] / 2<α≤D / 2, wherein 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 channel 322 and the main channel 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 In the formula, [DR×sin(90°-θa-θb)] / 2 is represented by Rc.

[0045] It can be understood that the larger the α is, the closer the first auxiliary channel 322 is to the first opening 3211; the smaller the α is, the farther the first auxiliary channel 322 is from the first opening 3211. Too large a α may result in an unclear flow field optimization effect and a poor vortex suppression effect. For example, when α is greater than D / 2, when the first auxiliary channel 322 is parallel to the central axis of the inlet 311, the first opening 3211 and the first auxiliary channel 322 will be on the same side of the central axis of the inlet 311, such as Figure 6 As shown in FIG. 1 , the first auxiliary channel 322 has a relatively limited effect on improving the smoothness of the flow field. If α is too small, the spherical flow valve 300 may not be completely closed. For example, when α is less than Rc, even if the main channel 321 is rotated to be perpendicular to the central axis of the inlet 311, the first auxiliary channel 322 cannot be completely blocked by the inner wall surface of the valve seat 310. Figure 7 As shown, in Figure 7 In the illustrated case, in order to completely close the spherical flow valve 300 , the valve core 320 needs to be further rotated so that the main channel 321 , the first auxiliary channel 322 and the second auxiliary channel 323 are completely blocked by the valve seat 310 .

[0046] The edge of the outlet 312 has 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 two end points of one 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 centrally symmetrical in this embodiment, the inlet 311 and the outlet 312 are of the same size and the central axis coincides, 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 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 [DR×sin(90°-θa-θb)] / 2<α≤D / 2 is also satisfied.

[0047] It can be understood that in other optional embodiments, especially in embodiments where the first auxiliary channel 322 and the second auxiliary channel 323 are not centrally symmetrical, one of the first auxiliary channel 322 or the second auxiliary channel 323 can 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, an inner diameter that is too large will reduce the flow suppression effect, that is, a large amount of fluid flows through the auxiliary channel, and the overall flow of the spherical flow valve 300 is difficult to reduce. If the inner diameter is too small, the flow through the auxiliary channel will be too small in the flow suppression state, which will lead to limited improvement of the flow field by the auxiliary channel. 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, the noise is maximum or the vortex is most obvious when the main channel 321 is deflected θa relative to the central axis of the inlet 311 and the outlet 312. Specifically, the deflection angle of the valve core 320 can be continuously adjusted by experiment or numerical simulation, and the angle of deflection of the main channel 321 relative to the central axis of the inlet 311 and the outlet 312 is recorded as θa when the noise or vortex is maximum. It can be understood that the embodiment of the present application is to open the first auxiliary channel 322 and the second auxiliary channel 323 parallel to the central axis of the inlet 311 and the outlet 312 when the main channel 321 is in a flow suppression state with the maximum noise or vortex, so as to improve the suppression effect of noise and vortex.

[0050] Figure 8 Schematic diagram of a 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. Figure 8 As shown, three first auxiliary channels 322 are provided on the valve core 320. Similarly, multiple second auxiliary channels 323 may be provided on the valve core 320, and the multiple second auxiliary channels 323 are arranged at intervals along the extension direction of the rotation axis. By providing multiple first auxiliary channels 322 and multiple second auxiliary channels 323, the flow path of the fluid can be more dispersed, avoiding the generation of vortices by strong streams.

[0051] Fig. 9 Schematic diagram of the valve core 320 in 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. Fig. 9 As 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 extension 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. In this way, the flow can be more dispersed in the auxiliary channel, the flow rate can be slowed down, and vortex is not easy to generate.

[0052] In a second aspect, the present application provides an air conditioning system 010, including a pipeline for conveying a refrigerant, on which a ball flow valve 300 according to any one of the aforementioned embodiments is disposed.

[0053] Fig.10 FIG. 1 is a schematic diagram of an air conditioning system 010 in an embodiment of the present application. Fig.10 As shown, the air conditioning system 010 provided in the embodiment of the present application includes an indoor unit 200 and multiple outdoor units 100. The outdoor unit 100 includes a compressor 110, an outdoor heat exchanger 120, a liquid pipe splitter 130, a high-pressure gas pipe splitter 150, a low-pressure gas pipe splitter 140 and an outdoor fan 180. The indoor unit 200 includes an indoor heat exchanger 210 and a corresponding indoor fan 220.

[0054] In this embodiment, a plurality of indoor heat exchangers 210 are mounted on a plurality of indoor branch lines 230 in a one-to-one correspondence, and the outdoor heat exchanger 120 is connected to the compressor 110 through the reversing valve 160. Through the reversing valve 160, the outdoor heat exchanger 120 can selectively switch to be connected to the exhaust side or the suction side of the compressor 110, so that it can be determined whether the outdoor heat exchanger 120 performs the function of condensation or evaporation. The side of the outdoor heat exchanger 120 away from the compressor 110 is connected to one end of each indoor branch line 230 through the liquid pipe diverter 130, and the other end of each indoor branch line 230 is converged through the 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 a plurality of inlet ends and an outlet end, and the plurality of inlet ends are connected to the plurality of indoor 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 an air inlet end and multiple air outlet ends. The air inlet end of the high-pressure gas pipe diverter 150 is connected to the exhaust side of the compressor 110. The multiple air outlet ends of the high-pressure gas pipe diverter 150 are connected to the multiple indoor branch lines 230 one by one through multiple high-pressure gas branch lines 152. The connection position between the high-pressure gas branch line 152 and the indoor branch line 230 is located between the first valve 141 and the indoor heat exchanger 210. A second valve 151 is provided on the high-pressure gas branch line 152.

[0056] The cooling and heating free function can be realized by controlling the first valve 141 and the second valve 151. For example, in the cooling condition, the outdoor heat exchanger 120 releases heat as a condenser, and each indoor heat exchanger 210 absorbs heat as an evaporator. At this time, the first valve 141 on each indoor unit branch line 230 is opened, and the second valve 151 on each high-pressure gas branch line 152 is closed. The refrigerant passes through the exhaust side of the compressor 110, the outdoor heat exchanger 120, the liquid pipe splitter 130, the indoor heat exchanger 210, and the low-pressure gas pipe splitter 140 in sequence, and finally merges into the suction side of the compressor 110 to complete a cycle. When one or more (should be less than the total number of indoor units 200 currently in cooling operation) indoor units 200 need to be changed to 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, the refrigerant for the heating indoor unit 200 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 cooling indoor heat exchanger 210, the low-pressure gas pipe diverter 140 in sequence, and finally merges into the suction side of the compressor 110 to complete a cycle.

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

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

[0059] In this embodiment, the capillary tube 161 has a smaller diameter than other pipelines, and its flow rate is very small and its resistance is very large, so it does not cause a short circuit in the refrigerant circulation. In other words, even if the E port is connected to the D port, a large amount of refrigerant will not 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 from other pipelines (in this embodiment, it enters the indoor heat exchanger 210 through the high-pressure gas main line 153). In the discussion of refrigerant circulation heating and cooling, the capillary tube 161 can be regarded as a short circuit.

[0060] In this embodiment, the air inlet end of the high-pressure gas pipe diverter 150 is connected to 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 air inlet end of the high-pressure gas pipe diverter 150, and the other end is connected to the pipeline between the reversing valve 160 and the compressor 110. The low-pressure gas pipe diverter 140 is connected to the suction side of the compressor 110 through the low-pressure gas main line 142.

[0061] In this embodiment, the first valve 141 uses the ball 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 ball flow valve 300 to adjust the flow, and can suppress the noise of the first valve 141, thereby improving the user experience. In other optional embodiments, the second valve 151 or the indoor expansion valve 240 can also use the ball 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: The invention comprises a valve seat (310) and a valve core (320) arranged in the valve seat (310), wherein the valve seat (310) is provided with an inlet (311) and an outlet (312) on opposite sides thereof, respectively; the valve core (320) can rotate relative to the valve seat (310) around a rotation axis; the valve core (320) is provided with a main channel (321), a first auxiliary channel (322) and a second auxiliary channel (323); the main channel (321) runs through the valve core (320) and forms a first opening (3211) and a second opening (3212) at both ends thereof; by rotating the valve core (320), the first opening (3211) and the second opening (3212) can be selectively connected to the inlet (311) and the outlet (312) respectively, or the first opening (3211) and the second opening (3212) can be selectively connected to the inlet (311) and the outlet (312) respectively, or the first opening (3212) can be selectively connected to the inlet (311) and the outlet (312) respectively. The first opening (3211) and the second opening (3212) are 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 of the main channel (321) in the radial direction, and one end extends to the inner wall of the main channel (321), and the other end extends to the outer peripheral surface of the valve core (320); the valve core (320) has a flow suppression state during the rotation stroke relative to the valve seat (310), and 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 connected to the inlet (311), and a part of the second opening (3212) and the second auxiliary channel (323) are connected to the second opening (3212).

2. The spherical flow valve according to claim 1, characterized in that: When the valve core (320) is in the flow suppression state, the first opening (3211) and the first auxiliary channel (322) are located on different sides of the central axis of the inlet (311), and the second opening (3212) and the second auxiliary channel (323) are located on different sides of the central axis of the outlet (312).

3. The spherical flow valve according to claim 2, characterized in that: The central axes of the first auxiliary channel (322), the second auxiliary channel (323), the inlet (311), and the outlet (312) are all perpendicular to the rotation axis; when the valve core (320) rotates to the point where the first auxiliary channel (322) is parallel to the central axis of the inlet (311) or when the valve core (320) rotates to the point where the second auxiliary channel (323) is parallel to the central axis of the outlet (312), the valve core (320) is in a flow suppression 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, the first point and the second point are two end points of one diameter 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, which satisfies [DR×sin(90°-θa-θb)] / 2<α≤D / 2, wherein 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 channel (322) and the main channel (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).

5. The spherical flow valve according to claim 3, characterized in that: A third point and a fourth point are provided on the edge of the outlet (312), the third point and the fourth point are two end points of one diameter of the outlet (312), and a 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 [DR×sin(90°-θa-θb)] / 2<α≤D / 2, wherein D is the diameter of the outlet (312), R is the diameter of the valve core (320), θa is the angle between the second auxiliary channel (323) and the main channel (321), and θb is the 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, characterized in that: 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; wherein 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 with each other.

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

9. The spherical flow valve according to claim 1, characterized in that: The valve core (320) is provided with a plurality of the first auxiliary channels (322), 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, characterized in that: 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 of the valve core (320) in the axial direction; And / or, the second auxiliary channel (323) is 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 of the valve core (320) in the axial direction.

11. An air conditioning system, characterized in that: It comprises a pipeline for conveying refrigerant, on which a spherical flow valve (300) according to any one of claims 1 to 10 is arranged.

12. The air conditioning system according to claim 11, characterized in that: The air conditioning system (010) comprises a compressor (110), an outdoor heat exchanger (120) and a plurality of indoor heat exchangers (210); the outdoor heat exchanger (120) can be selectively switched to communicate with the exhaust side or the intake side of the compressor (110) via a reversing valve (160); The air conditioning system (010) further comprises a liquid pipe diverter (130), a high-pressure gas pipe diverter (150) and a low-pressure gas pipe diverter (140); the plurality of indoor heat exchangers (210) are mounted on the plurality of indoor unit branches (230) in a one-to-one correspondence; the 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 the liquid pipe diverter (130); the other end of each indoor unit branch line (230) is converged through the low-pressure gas pipe diverter (140); and the low-pressure gas pipe diverter (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 diverter (140); the first valve (141) is the spherical flow valve (300); The air inlet end of the high-pressure gas pipe diverter (150) is connected to the exhaust side of the compressor (110), and the multiple air outlet ends of the high-pressure gas pipe diverter (150) are connected to the multiple indoor unit branches (230) through multiple high-pressure gas branch lines (152) in a one-to-one correspondence. The connection position between 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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