Silent expansion valve

Abstract

The utility model provides a silent expansion valve, and belongs to the technical field of air conditioner parts. The self-balancing expansion valve solves the problem that a self-balancing expansion valve in the prior art is large in use noise. The mute type expansion valve comprises a tubular valve body, a male valve element and a female valve element are arranged in the valve body, a throttling channel is formed between the male valve element and the female valve element, a cylindrical noise reduction sleeve is further fixedly arranged in the valve body, the end, away from the male valve element, of the noise reduction sleeve is closed, and the other end of the noise reduction sleeve is communicated with the throttling channel. A first through hole is formed in the side wall of the noise reduction sleeve, and the center line of the first through hole intersects with the center axis of the valve body. The self-balancing expansion valve has the advantage that the self-balancing expansion valve has the sound reduction and noise reduction effects.

Description

Technical Field

[0001] The utility model belongs to the technical field of air-conditioning components and relates to a silent expansion valve. Background Art

[0002] The expansion valve is an important component of the refrigeration device, and its main function is to throttle and reduce pressure and adjust the air flow. For example, a Chinese patent document discloses an expansion valve (application number: 202111426601.5), which includes a main valve body and a defrost valve body. Both ends of the defrost valve body are connected to the main valve body. A valve core assembly is provided in the main valve body between the two ends of the defrost valve body. The defrost valve body has two limit parts, and both limit parts have flow holes that are arranged along the length of the defrost valve body. A defrost valve core that can slide and block the flow hole is provided between the two limit parts. Auxiliary springs are provided between the defrost valve core and the two limit parts, and the defrost valve core can be separated from the two limit parts under the action of the auxiliary spring. The starting elastic force of the main spring is greater than the elastic force value when the auxiliary spring is compressed to the defrost valve core to block the flow hole. The expansion valve has the following shortcomings during use: when cooling and heating, the gas flow rate in the valve body is fast, the use noise is large, and the customer experience is poor.

[0003] Summary of the Invention

[0004] The purpose of the utility model is to solve the above problems in the existing technology and propose a silent expansion valve. The technical problem to be solved by the utility model is how to make the self-balancing expansion valve have the effect of reducing noise.

[0005] The purpose of the utility model can be achieved through the following technical solutions:

[0006] A silent expansion valve comprises a tubular valve body, a male valve core and a female valve core are arranged in the valve body, a throttling channel is formed between the male valve core and the female valve core, and is characterized in that a cylindrical noise reduction sleeve is also fixed in the valve body, the end of the noise reduction sleeve away from the male valve core is closed and the other end is connected to the throttling channel, the side wall of the noise reduction sleeve has a through hole one, and the center line of the through hole one is arranged to intersect with the center axis of the valve body.

[0007] The silent expansion valve is provided with a noise reduction sleeve at the refrigeration inlet of the valve body, and the end of the noise reduction sleeve away from the male valve core is closed. In addition, the center line of the through hole 1 is arranged to intersect with the center axis of the valve body. When indoor cooling is performed, the refrigerant with a faster flow rate needs to collide with the closed end of the noise reduction sleeve and the wall of the valve body and the noise reduction sleeve before passing through the noise reduction sleeve through the through hole 1. This process consumes a certain amount of energy, thereby slowing down the flow rate of the refrigerant, thereby achieving the effect of reducing sound and noise.

[0008] In the above-mentioned silent expansion valve, an annular diverter groove 1 is formed between the outer peripheral wall of the closed end of the noise reduction sleeve and the inner wall of the valve body, and the through hole 1 is provided on the inner peripheral wall of the diverter groove 1 and connects the diverter groove 1 and the throttling channel. After the refrigerant airflow collides with the closed end of the noise reduction sleeve, it is diverted into the diverter groove 1, and then enters the interior of the noise reduction sleeve through the through hole 1. During this period, a certain amount of energy is consumed by colliding with the valve body and the wall of the noise reduction sleeve. Although the groove width of the diverter groove 1 is small, after the refrigerant airflow enters the interior of the noise reduction sleeve, the space inside the noise reduction sleeve is much larger than the space of the diverter groove 1, so it is beneficial to further slow down the flow rate of the refrigerant airflow as a whole, thereby further achieving the effect of reducing sound and noise.

[0009] In the above-mentioned silent expansion valve, the through hole 1 has a plurality of holes and is distributed along the circumference of the noise reduction sleeve, and each through hole 1 is arranged along the radial direction of the noise reduction sleeve. Each through hole 1 is arranged along the radial direction of the noise reduction sleeve, so that the extension direction of the through hole 1 is perpendicular to the flow direction of the refrigerant airflow, which is conducive to further slowing down the flow rate of the refrigerant airflow.

[0010] In the above-mentioned silent expansion valve, the through hole 1 is provided in a plurality and distributed along the circumference of the noise reduction sleeve, and each through hole 1 is inclined from the outside to the inside toward the open end of the noise reduction sleeve. Each through hole 1 is inclined from the outside to the inside toward the open end of the noise reduction sleeve, which is more conducive to the refrigerant airflow entering the noise reduction sleeve.

[0011] In the above-mentioned silent expansion valve, the inner peripheral wall surface of the first diverter groove has an inclined section inclined from the outside to the inside toward the closed end of the noise reduction sleeve, and the first through hole is located on the inclined section. The above structure enables the inlet of the first through hole to be arranged toward the notch of the diverter groove, which is further conducive to the refrigerant airflow entering the noise reduction sleeve.

[0012] In the above-mentioned silent expansion valve, the outer end surface of the closed end of the noise reduction sleeve has a guide surface 1 for slowing down the flow rate. By providing the guide surface 1, the refrigerant airflow can consume more energy when colliding with the closed end of the noise reduction sleeve, thereby slowing down the flow rate.

[0013] In the above-mentioned silent expansion valve, the guide surface is a plane. Setting the guide surface as a plane can increase the collision contact surface of the refrigerant airflow, thereby facilitating the slowing down of the flow rate of the refrigerant airflow.

[0014] In the above-mentioned silent expansion valve, the first guide surface is a guide convex surface that is convexly arranged in a direction away from the male valve core; or the first guide surface is a guide concave surface that is concavely arranged in a direction close to the male valve core. The guide convex surface increases the collision loss of the refrigerant airflow on the one hand, and is more conducive to diverting the refrigerant airflow to both sides on the other hand; while the guide concave surface increases the collision loss and resistance of the refrigerant airflow, which is conducive to further slowing down the flow rate of the refrigerant airflow.

[0015] In the above-mentioned silent expansion valve, the interior of the male valve core has a flow channel connecting the two sides of the male valve core, and a cylindrical positioning sleeve is fixedly provided at the end of the valve body away from the noise reduction sleeve. The end of the positioning sleeve away from the male valve core is closed and the other end is connected to the flow channel. The outer end surface of the closed end of the positioning sleeve has a guide surface 2 for slowing down the flow rate, and the side wall of the positioning sleeve has a through hole 2 arranged to intersect with the central axis of the valve body.

[0016] In the above-mentioned silent expansion valve, the interior of the male valve core has a flow passage connecting the two sides of the male valve core, and a cylindrical positioning sleeve is fixedly provided at the end of the valve body away from the noise reduction sleeve. The end of the positioning sleeve away from the male valve core is closed and the other end is connected to the flow passage. The outer end surface of the closed end of the positioning sleeve has a guide surface 2 for slowing down the flow rate, and the side wall of the positioning sleeve has a through hole 2, and the center line of the through hole 2 is arranged to intersect with the center axis of the valve body. By arranging the guide surface 2 at the end of the positioning sleeve located at the heating inlet, when heating the room, the refrigerant with a faster flow rate consumes a certain amount of energy after colliding with the guide surface 2 and the wall of the valve body and the positioning sleeve before passing through the positioning sleeve, thereby slowing down the flow rate of the refrigerant, thereby achieving the effect of reducing sound and noise.

[0017] In the above-mentioned silent expansion valve, an annular diverter groove 2 is formed between the outer peripheral wall of the closed end of the positioning sleeve and the inner wall of the valve body, and the through hole 2 is opened on the inner peripheral wall surface of the diverter groove 2. There are multiple through holes 2 and they are distributed along the circumference of the positioning sleeve, and each through hole 2 is inclined from the outside to the inside toward the open end of the positioning sleeve; or each through hole 2 is arranged along the radial direction of the positioning sleeve. Each through hole 2 is inclined from the outside to the inside toward the open end of the positioning sleeve, which is more conducive to the refrigerant airflow entering the positioning sleeve; and each through hole 2 is arranged along the radial direction of the positioning sleeve, so that the extension direction of the through hole 2 is perpendicular to the flow direction of the refrigerant airflow, which is conducive to further slowing down the flow rate of the refrigerant airflow.

[0018] Compared with the prior art, the advantages of the silent expansion valve are: 1. The silent expansion valve adds a noise reduction sleeve to the refrigeration inlet of the valve body, and the end of the noise reduction sleeve away from the male valve core is closed and the outer wall of the end has a guide surface 1 for slowing down the flow rate. When the indoor cooling is performed, the refrigerant with a faster flow rate consumes a certain amount of energy after colliding with the guide surface 1 and the wall of the valve body and the noise reduction sleeve before passing through the noise reduction sleeve, thereby slowing down the flow rate of the refrigerant and achieving the effect of reducing noise.

[0019] 2. This silent expansion valve further provides a guide surface 2 at the end of the positioning sleeve located at the heating inlet, so that when heating the room, the refrigerant with a faster flow rate consumes a certain amount of energy after colliding with the guide surface 2 and the wall of the valve body and the positioning sleeve before passing through the positioning sleeve, thereby slowing down the flow rate of the refrigerant and achieving the effect of reducing sound and noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a structural cross-sectional view of the initial state of the silent expansion valve in the first embodiment.

[0021] Figure 2 It is a partial structural cross-sectional view of the silent expansion valve in the first embodiment when heating.

[0022] Figure 3 It is a partial structural cross-sectional view of the silent expansion valve in the first embodiment during refrigeration.

[0023] Figure 4 It is a structural cross-sectional view of the initial state of the silent expansion valve in the second embodiment.

[0024] Figure 5 It is a structural cross-sectional view of the initial state of the silent expansion valve in the third embodiment.

[0025] Figure 6 It is a structural cross-sectional view of the initial state of the silent expansion valve in the fourth embodiment.

[0026] Figure 7 It is a structural cross-sectional view of the initial state of the silent expansion valve in the fifth embodiment.

[0027] In the figure, 1, valve body; 2, male valve core; 2a, plug connector; 2a1, throttling section; 2a11, throttling surface; 2a2, defrosting section; 2a3, give-way section; 2b, positioning step; 3, female valve core; 3a, throttling ring; 3a1, matching surface; 3b, steady flow ring; 4, elastic member; 4a, first spring; 4b, second spring; 5, throttling channel; 6, give-way channel; 7, defrosting channel; 8, positioning sleeve; 8a, guide surface two; 8b, through hole two; 9, spring seat; 9a, limit step; 10, flow passage; 11, noise reduction sleeve; 11a, guide surface one; 11b, through hole one; 12, diverter slot one; 12a, inclined section; 13, diverter slot two. DETAILED DESCRIPTION

[0028] The following are specific embodiments of the present invention and the accompanying drawings to further describe the technical solution of the present invention, but the present invention is not limited to these embodiments.

[0029] Embodiment 1

[0030] A silent expansion valve, refer to Figure 1-3, comprising a tubular valve body 1, a male valve core 2 and a female valve core 3 are arranged in the valve body 1, the end of the male valve core 2 has a columnar plug joint 2a, the female valve core 3 is cylindrical and is sleeved on the plug joint 2a of the male valve core 2, and the inner wall of the female valve core 3 has an annular throttling ring 3a, the valve body 1 is also provided with an elastic member 4 for driving the male valve core 2 to move relative to the female valve core 3, the plug joint 2a of the male valve core 2 is provided with a defrosting section 2a2 and a throttling section 2a1, and under the action of the elastic member 4, when When the side wall of the defrost section 2a2 is opposite to the inner wall of the throttling ring 3a, a defrost channel 7 is formed. When the male valve core 2 moves to the side wall of the throttling section 2a1 and is opposite to the inner wall of the throttling ring 3a, a throttling channel 5 is formed. A cylindrical noise reduction sleeve 11 is also fixed in the valve body 1. The end of the noise reduction sleeve 11 away from the plug connector 2a is closed and the other end is connected to the throttling channel 5. The side wall of the noise reduction sleeve 11 has a through hole 11b, and the center line of the through hole 11b is intersected with the center axis of the valve body 1.

[0031] Specifically, refer to Figure 1-3 An annular diverter groove 12 is formed between the outer peripheral wall of the closed end of the noise reduction sleeve 11 and the inner wall of the valve body 1. The through hole 11b is provided on the inner peripheral wall surface of the diverter groove 12 and connects the diverter groove 12 and the throttling channel 5. The guide surface 11a is a guide convex surface protruding in the direction away from the plug connector 2a.

[0032] Further, refer to Figure 1-3 A yield section 2a3 is also provided on the plug connector 2a of the male valve core 2, and the yield section 2a3 and the throttling section 2a1 are respectively located on both sides of the defrost section 2a2, and the diameters of the defrost section 2a2, the throttling section 2a1 and the yield section 2a3 decrease successively, and a yield channel 6 with a certain flow rate can be formed between the side wall of the yield section 2a3 and the inner wall of the throttling ring 3a; the outer wall of the male valve core 2 has a positioning step portion 2b, and when the male valve core 2 moves to the position where the positioning step portion 2b abuts against the female valve core 3, the side wall of the yield section 2a3 is arranged opposite to the inner wall of the throttling ring 3a to form the yield channel 6.

[0033] More specifically, refer to Figure 1-3 A cylindrical positioning sleeve 8 is fixedly provided in the valve body 1, and a cylindrical spring seat 9 is movably provided between the positioning sleeve 8 and the male valve core 2, and the spring seat 9 is sleeved on the outer side of the male valve core 2. The elastic member 4 includes a first spring 4a abutting between the positioning sleeve 8 and the spring seat 9 and a second spring 4b abutting between the male valve core 2 and the female valve core 3. The spring coefficient of the first spring 4a is greater than the spring coefficient of the second spring 4b, and the inner wall of the spring seat 9 has a limiting step portion 9a for the male valve core 2 to abut.

[0034] Reference Figure 1-3The outer circumferential surface of the throttling section 2a1 has a plurality of annular throttling surfaces 2a11 with different outer diameters in the axial direction, and the inner circumferential surface of the throttling ring 3a is an annular mating surface 3a1. When the throttling ring 3a moves to a position opposite to the throttling section 2a1, a throttling channel 5 is formed between the mating surface 3a1 and the relative throttling surface 2a11; the inner wall of the female valve core 3 also has an annular flow stabilizing ring 3b in the circumferential direction, and the flow stabilizing ring 3b is arranged on a side away from the male valve core 2, and the flow stabilizing ring 3b and the throttling ring 3a are fitted together to form a whole, and the aperture of the flow stabilizing ring 3b is larger than the aperture of the throttling ring 3a.

[0035] The male valve core 2 has a flow passage 10 inside that connects the two sides of the male valve core 2. The flow passage 10 extends along the axial direction of the valve body 1. The end of the flow passage 10 close to the plug connector 2a passes through the side wall of the male valve core 2, and the end of the flow passage 10 away from the plug connector 2a passes through the end of the male valve core 2.

[0036] In this embodiment, it is preferred that the through hole 11b has a plurality of holes and is distributed along the circumference of the noise reduction sleeve 11, and each through hole 11b is arranged along the radial direction of the noise reduction sleeve 11; it is preferred that the noise reduction sleeve 11 is arranged adjacent to the female valve core 3. On the one hand, the structure of the valve body 1 is more compact, and on the other hand, the refrigerant can better push the male valve core 2 to move after passing through the noise reduction sleeve 11.

[0037] The following will explain the working principle of this silent expansion valve:

[0038] One end of the valve body 1 is a refrigeration inlet, and the other end is a heating inlet. The noise reduction sleeve 11 is arranged at the refrigeration inlet. In the shutdown state, the male valve core 2 and the female valve core 3 do not move under the action of the elastic member 4. In the initial state, the side wall of the defrosting section 2a2 of the male valve core 2 is opposite to the inner wall of the throttling ring 3a of the female valve core 3 and forms a defrosting channel 7, so that the refrigeration inlet can be connected to the heating inlet through the male valve core 2 and the female valve core 3. In addition, the diameters of the defrosting section 2a2, the throttling section 2a1 and the yielding section 2a3 are respectively The defrost passage 7 formed by the defrost section 2a2 and the throttling ring 3a is reduced, so that the passing area of ​​the defrost channel 7 formed by the defrost section 2a2 and the throttling ring 3a is smaller, and only a small amount of airflow can pass through, so that the power consumption in the defrost stage is less, which meets the development requirements of energy conservation and carbon reduction. Therefore, when the outdoor unit is defrosted before the air-conditioning equipment is started or the outdoor unit is defrosted during the indoor heating process, a smaller flow of refrigerant enters from the refrigeration inlet, and a smaller pressure difference does not need to push the male valve core 2 and the female valve core 3, so the refrigerant can pass through and flow out from the heating inlet to perform heating and defrosting of the outdoor unit.

[0039] The silent expansion valve adds a defrost section 2a2 to the plug connector of the male valve core, so that in the initial state, the side wall of the defrost section 2a2 is opposite to the inner wall of the throttling ring 3a to form a defrost channel 7. In addition, the diameter of the defrost section 2a2 is relatively large, so the passing area of ​​the defrost channel 7 formed by the defrost section 2a2 and the throttling ring 3a is relatively small, and only a small amount of airflow can pass through, thereby reducing the power consumption in the defrost stage, thereby meeting the development requirements of energy conservation and carbon reduction. At the same time, the silent expansion valve does not need to add an additional defrost valve body, and the structure is more compact.

[0040] After the outdoor unit defrosts, the indoor unit heats normally. At this time, the pressure difference at both ends of the valve body 1 is large, and the refrigerant flows in from the heating inlet. The gap between the plug connector 2a of the male valve core 2 and the throttling ring 3a of the female valve core 3 is not enough to meet the refrigerant passing requirements. Under the action of the large pressure difference, the refrigerant will push the male valve core 2 near the refrigeration inlet to compress the second spring 4b to slide toward the refrigeration inlet and quickly move to a position where the yielding section 2a3 is opposite to the throttling ring 3a, and a yielding channel 6 is formed between the yielding section 2a3 and the throttling ring 3a. At this time, the positioning step 2b of the male valve core 2 abuts against the end of the female valve core 3, so that the male valve core 2 cannot slide further toward the refrigeration inlet, so that the passing area of ​​the yielding channel 6 reaches the maximum and is maintained. In addition, the preferred heating state of this embodiment is controlled by the solenoid valve set at the refrigeration inlet of the valve body 1. So far, in the heating stage, the silent expansion valve does not adjust the flow through the valve body 1, and the work of adjusting the flow is completed by the solenoid valve. In this way, the volume of the silent expansion valve can be smaller and the structure is more compact.

[0041] When the room is cooled, the refrigerant flows in from the cooling inlet, and the refrigerant with a faster flow rate first contacts the guide surface 11a of the noise reduction sleeve 11. Since the guide surface 11a is a guide convex surface that is convexly arranged in the direction away from the plug connector 2a, the refrigerant with a faster flow rate will consume a part of the energy after contacting the guide surface 11a, thereby slowing down the flow rate of the refrigerant. At the same time, the guide surface 11a will guide the refrigerant to flow to the diversion groove 12 on both sides, and then enter the interior of the noise reduction sleeve 11 through the through hole 11b. During this period, the refrigerant will collide with the valve body 1 and the wall of the noise reduction sleeve 11. The surface consumes a certain amount of energy. Although the width of the diverter groove 12 is small, after the refrigerant airflow enters the noise reduction sleeve 11, the space inside the noise reduction sleeve 11 is much larger than the space of the diverter groove 12, so it is beneficial to further slow down the flow rate of the refrigerant airflow as a whole. The refrigerant will collide with the inner wall of the valve body 1 and the side wall of the noise reduction sleeve 11, and finally enter from the through hole 11b on the side wall of the noise reduction sleeve 11. In this process, the refrigerant will further consume energy and reduce the flow rate, so that the refrigerant flows to the channel formed by the plug connector 2a and the throttling ring 3a at a slower flow rate, from The noise reduction sleeve 11 of the above structure can achieve the effect of reducing noise during indoor cooling. At this time, the gap between the plug connector 2a of the male valve core 2 and the throttling ring 3a of the female valve core 3 is not enough to meet the passage demand of the refrigerant. Under the action of a large pressure difference, the refrigerant will accelerate the male valve core 2 to move in the reverse direction, compress the first spring 4a and slide toward the heating inlet, so that the throttling section 2a1 on the plug connector 2a quickly moves to a position opposite to the throttling ring 3a, and the throttling surfaces 2a11 of the throttling section 2a1 on the plug connector 2a will gradually move away from the throttling surface 2a1 on the female valve core 3. The throttling ring 3a is formed by the plurality of throttling surfaces 2a11 of the throttling section 2a1 of the plug connector 2a and the inner circumferential surface of the throttling ring 3a on the female valve core 3 in sequence to form a throttling channel 5. In different refrigeration states, such as low-temperature, medium-low refrigeration, intermediate refrigeration, low-frequency refrigeration, rated refrigeration or maximum refrigeration, the pressure difference at both ends of the valve body is different, thereby pushing the male valve core 2 to compress the first spring 4a to different degrees, so that the plurality of throttling surfaces 2a11 of the throttling section 2a1 of the plug connector 2a and the throttling ring 3a respectively form throttling channels 5 with different passing areas to adjust the flow rate.

[0042] The cooling modes of multiple flow levels are as follows:

[0043] Low-medium-low refrigeration mode: the male valve core 2 moves toward the heating inlet direction, and the third spring 4c is partially compressed.

[0044] Intermediate cooling mode: the male valve core 2 continues to compress the third spring 4 c until the male valve core 2 abuts against the spring seat 9 .

[0045] Low-frequency refrigeration mode: the male valve core 2 pushes the spring seat 9, and the first spring 4a is partially compressed.

[0046] Rated refrigeration mode: the male valve core 2 continues to push the spring seat 9, and the first spring 4a is further compressed.

[0047] Maximum cooling mode: the male valve core 2 further pushes the spring seat 9 until the spring seat 9 abuts against the positioning sleeve 8 and is difficult to move further.

[0048] Embodiment 2

[0049] The structure and principle of this embodiment are basically the same as those of the first embodiment, except that: Figure 4 , the guide surface 11a is a plane.

[0050] Embodiment 3

[0051] The structure and principle of this embodiment are basically the same as those of the first embodiment, except that: Figure 5 The guide surface 11a is a guide concave surface that is recessed toward the direction close to the plug connector 2a. When the refrigerant with a faster flow rate contacts the guide surface 11a that is recessed toward the direction close to the plug connector 2a, it will also consume part of the energy, thereby slowing down the flow rate of the refrigerant.

[0052] Embodiment 4

[0053] The structure and principle of this embodiment are basically the same as those of the first embodiment, the second embodiment, or the third embodiment. The difference is that: Figure 6 The interior of the male valve core 2 has a flow passage 10 connecting the two sides of the male valve core 2. A cylindrical positioning sleeve 8 is fixedly provided at the end of the valve body 1 away from the noise reduction sleeve 11. The end of the positioning sleeve 8 away from the plug connector 2a is closed and the other end is connected to the flow passage 10. The outer end surface of the closed end of the positioning sleeve 8 has a guide surface 8a for slowing down the flow rate. The side wall of the positioning sleeve 8 has a through hole 8b, and the center line of the through hole 8b is intersected with the center axis of the valve body 1.

[0054] In the present embodiment, an annular diverter groove 13 is preferably formed between the outer peripheral wall of the closed end of the positioning sleeve 8 and the inner wall of the valve body 1, and the through hole 8b is provided on the inner peripheral wall of the diverter groove 13. There are multiple through holes 8b distributed along the circumference of the positioning sleeve 8, and each through hole 8b is inclined from the outside to the inside toward the open end of the positioning sleeve 8; or each through hole 8b is arranged along the radial direction of the positioning sleeve 8.

[0055] By setting the guide surface 8a at the end of the positioning sleeve 8, when the indoor heating is on, the refrigerant flows in from the heating inlet, and the refrigerant with a faster flow rate first contacts the guide surface 8a of the positioning sleeve 8. Since the guide surface 8a is a convex guide surface that is convexly arranged in the direction away from the plug connector 2a, or a concave guide surface that is concavely arranged in the direction close to the plug connector 2a, the refrigerant with a faster flow rate will consume a part of the energy after contacting the guide surface 8a, thereby slowing down the flow rate of the refrigerant. At the same time, the guide surface 8a will guide the refrigerant to flow to the two sides to the diversion groove 2 13, and then enters the interior of the positioning sleeve 8 through the through hole 8b. During this period, a certain amount of energy is consumed by colliding with the valve body 1 and the wall of the positioning sleeve 8. Although the width of the diverter groove 13 is relatively small, after the refrigerant airflow enters the interior of the positioning sleeve 8, the space inside the positioning sleeve 8 is much larger than the space of the diverter groove 13, so it is beneficial to further slow down the flow velocity of the refrigerant airflow as a whole, so that the refrigerant flows to the flow channel 10 at a slower flow rate, so that the structure of setting the guide surface 8a at the end of the positioning sleeve 8 can also play a role in reducing noise when heating the room.

[0056] Embodiment 5

[0057] The structure and principle of this embodiment are basically the same as those of the first embodiment, the second embodiment, the third embodiment, or the fourth embodiment. The difference is that: Figure 7 Each through hole 11b is inclined from the outside to the inside toward the open end of the noise reduction sleeve 11.

[0058] In this embodiment, the inner wall surface of the diverter groove 12 preferably has an inclined section 12a which is inclined from the outside to the inside toward the closed end of the noise reduction sleeve 11, and the through hole 11b is located on the inclined section 12a.

[0059] The specific embodiments described herein are merely examples of the spirit of the present invention. Those skilled in the art may make various modifications or additions to the specific embodiments described or replace them in similar ways, but they will not deviate from the spirit of the present invention or exceed the scope defined by the appended claims.

Claims

1. A silent expansion valve, comprising a tubular valve body (1), wherein a male valve core (2) and a female valve core (3) are arranged in the valve body (1), and a throttling channel (5) is formed between the male valve core (2) and the female valve core (3), characterized in that: A cylindrical noise reduction sleeve (11) is also fixedly disposed in the valve body (1), the end of the noise reduction sleeve (11) away from the male valve core (2) is in a closed state and the other end is connected to the throttling channel (5), the side wall of the noise reduction sleeve (11) has a through hole 1 (11b), and the center line of the through hole 1 (11b) is arranged to intersect with the center axis of the valve body (1).

2. A silent expansion valve according to claim 1, characterized in that: An annular flow dividing groove (12) is formed between the outer peripheral wall of the closed end of the noise reduction sleeve (11) and the inner wall of the valve body (1), and the through hole (11b) is provided on the inner peripheral wall surface of the flow dividing groove (12) and connects the flow dividing groove (12) and the throttling channel (5).

3. A silent expansion valve according to claim 2, characterized in that: The through hole one (11b) has a plurality of holes and is distributed along the circumference of the noise reduction sleeve (11), and each through hole one (11b) is arranged along the radial direction of the noise reduction sleeve (11).

4. A silent expansion valve according to claim 2, characterized in that: The through hole one (11b) has a plurality of holes and is distributed along the circumference of the noise reduction sleeve (11), and each through hole one (11b) is arranged obliquely from the outside to the inside toward the open end of the noise reduction sleeve (11).

5. A silent expansion valve according to claim 4, characterized in that: The inner peripheral wall surface of the diverter groove (12) has an inclined section (12a) which is arranged from the outside to the inside towards the closed end of the noise reduction sleeve (11), and the through hole (11b) is located on the inclined section (12a).

6. A silent expansion valve according to any one of claims 1 to 5, characterized in that: The outer end surface of the closed end of the noise reduction sleeve (11) has a flow guide surface 1 (11a) for slowing down the flow velocity.

7. A silent expansion valve according to claim 6, characterized in that: The guide surface 1 (11a) is a plane.

8. A silent expansion valve according to claim 6, characterized in that: The guide surface one (11a) is a guide convex surface that is convexly arranged in a direction away from the male valve core (2); or the guide surface one (11a) is a guide concave surface that is concavely arranged in a direction close to the male valve core (2).

9. A silent expansion valve according to claim 6, characterized in that: The male valve core (2) has a flow passage (10) inside that communicates with both sides of the male valve core (2); a cylindrical positioning sleeve (8) is fixedly provided at the end of the valve body (1) away from the noise reduction sleeve (11); the end of the positioning sleeve (8) away from the male valve core (2) is in a closed state and the other end is connected to the flow passage (10); the outer end surface of the closed end of the positioning sleeve (8) has a guide surface 2 (8a) for slowing down the flow rate; the side wall of the positioning sleeve (8) has a through hole 2 (8b), and the center line of the through hole 2 (8b) is arranged to intersect with the center axis of the valve body (1).

10. A silent expansion valve according to claim 9, characterized in that: An annular flow diversion groove 2 (13) is formed between the outer peripheral wall of the closed end of the positioning sleeve (8) and the inner wall of the valve body (1); the through hole 2 (8b) is provided on the inner peripheral wall of the flow diversion groove 2 (13); there are a plurality of through holes 2 (8b) distributed along the circumference of the positioning sleeve (8), and each through hole 2 (8b) is arranged obliquely from the outside to the inside toward the open end of the positioning sleeve (8); or each through hole 2 (8b) is arranged along the radial direction of the positioning sleeve (8).

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