Throttling assembly

Abstract

The utility model provides a throttling assembly, which comprises a first valve pipe assembly and a second valve pipe assembly which are mutually connected in parallel through flow paths, the first valve pipe assembly comprises a first pipe and a first valve core assembly in the first pipe, and the second valve pipe assembly comprises a second pipe and a second valve core assembly and a third valve core assembly in the second pipe. The first valve element assembly is composed of a first valve seat and a first valve element, the second valve element assembly comprises a second valve seat, a second valve element and a first elastic piece, and the third valve element assembly comprises a third valve seat, a third valve element and a second elastic piece. When the refrigerant is in the first flow direction, the first valve element is in a complete circulation state, the second valve element and the third valve element are in a small hole throttling state, and when the refrigerant is in the second flow direction, the first valve element is in a closed state or a small hole throttling state, and the second valve element and the third valve element are in a flow adjusting state. The pneumatic noise of the valve pipe assembly in the using process is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of air conditioner pipeline throttle valve design, in particular to a throttling component. Background Art

[0002] As an air conditioning equipment widely used in life, the core components of heat pump air conditioner include a compressor, an outdoor heat exchanger, an indoor heat exchanger and a throttle valve (throttling element) on the pipeline connected between the outdoor heat exchanger and the indoor heat exchanger. The throttle valve is the core component of the air conditioner for cooling and heating. The applicant previously proposed a throttle valve with flow regulation function (patent application number is 202322234689.1), which includes two parallel valve pipe assemblies, each of which is provided with a valve core assembly. The valve core assemblies respectively assembled in the two valve pipe assemblies can form different throttling states for the reverse refrigerant fluid. However, the applicant found during use that the pressure difference between the front and back of one of the valve core assemblies (i.e., the fluid inlet and outlet) is large, and the flow fluctuation causes huge aerodynamic noise and valve core resonance noise. In order to solve the above-mentioned deficiencies in the prior art, the present utility model is proposed. Utility Model Content

[0003] The throttling assembly designed in the present invention can at least partially solve the above problems.

[0004] The utility model aims to provide a throttling component, comprising a first valve tube component and a second valve tube component connected in parallel with each other, wherein the first valve tube component comprises a first tube and a first valve core component assembled therein, and the second valve tube component comprises a second tube and a second valve core component and a third valve core component assembled therein in series, wherein the first valve core component consists of a first valve seat and a first valve core slidably connected to the first valve seat, the second valve core component comprises a second valve seat, a second valve core and a first elastic member, and the third valve core component comprises a third valve seat, a third valve core and a second elastic member. Under the action of the refrigerant pressure difference and the elastic force of the first elastic member and / or the second elastic member, when the refrigerant is in a first flow direction, the first valve core is in a full flow state, the second valve core and the third valve core are in a small hole throttling state, and when the refrigerant is in a second flow direction, the first valve core is in a closed state or a small hole throttling state, the second valve core and the third valve core are in a flow regulation state, and the first flow direction is opposite to the second flow direction.

[0005] In some embodiments, the second valve core and the third valve core have different resonance frequencies in the throttle assembly.

[0006] In some embodiments, a mass ratio of the second valve core to the third valve core is between 0.7 and 1.3, and the first elastic member and the second elastic member have different stiffnesses.

[0007] In some embodiments, a mass ratio of the second valve core to the third valve core is between 0.9 and 1.1, and the first elastic member and the second elastic member have different stiffnesses.

[0008] In some embodiments, a stiffness ratio of the first elastic member to the second elastic member is not less than 2 or not greater than 0.5.

[0009] In some embodiments, a diameter of the central flow hole on the second valve seat is greater than a diameter of the central flow hole on the third valve seat.

[0010] In some embodiments, a diameter of the central flow hole on the second valve core is greater than a diameter of the central flow hole on the third valve core.

[0011] In some embodiments, the diameter of the side flow hole of the second valve seat is not less than the diameter of the central flow hole thereof, and the diameter of the side flow hole of the third valve seat is not less than the diameter of the central flow hole thereof.

[0012] In some embodiments, when the pressure difference between the inner cavities of the two end tubes of the second valve core assembly and the third valve core assembly opposite to each other is less than a first predetermined value, the second valve core and the third valve core are in a closed valve port state; when the pressure difference between the inner cavities of the two end tubes of the second valve core assembly and the third valve core assembly opposite to each other is greater than a second predetermined value, the second valve core and the third valve core are in a fully open valve port state.

[0013] In some embodiments, the first predetermined value is 0.6 MPa, and the second predetermined value is 2.6 MPa.

[0014] The throttling assembly of the utility model simultaneously arranges the second valve core assembly and the third valve core assembly in the second tube, so that the pressure difference between the inlet and outlet ends of the second tube can be jointly satisfied when the two valve cores are in the throttling state, thereby effectively reducing the pressure difference between the second valve core assembly and the third valve core assembly at each end, thereby reducing the pneumatic noise of the valve tube assembly during use. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a structural schematic diagram (partial cross-section) of the throttling assembly of the utility model.

[0016] In the figure:

[0017] 1. First valve tube assembly; 11. First tube; 121. First valve seat; 122. First valve core; 2. Second valve tube assembly; 20. Second tube; 21. Second valve core assembly; 211. Second valve seat; 212. Second valve core; 213. First elastic member; 214. First retaining ring; 22. Third valve core assembly; 221. Third valve seat; 222. Third valve core; 223. Second elastic member; 224. Second retaining ring; 31. First manifold; 32. Second manifold. DETAILED DESCRIPTION

[0018] Example embodiments will now be described more fully with reference to the accompanying drawings. However, example embodiments can be implemented in a variety of forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that the present invention will be comprehensive and complete and fully convey the concepts of the example embodiments to those skilled in the art. In the drawings, the thickness of regions and layers are exaggerated for clarity. The same reference numerals in the drawings represent the same or similar structures, and thus their detailed description will be omitted.

[0019] The described features, structures or characteristics may be combined in one or more embodiments in any suitable manner. In the following description, many specific details are provided to provide a full understanding of the embodiments of the present invention. However, those skilled in the art will appreciate that the technical solution of the present invention may be practiced without one or more of the specific details, or other methods, components, materials, etc. may be used. In other cases, known structures, materials or operations are not shown or described in detail to avoid blurring the various aspects of the present invention.

[0020] The following example is a throttling assembly of the utility model. This example is only a part of the embodiments of the utility model, but the protection scope of the utility model is not limited to this. All other embodiments obtained by ordinary technicians in this field without creative work should be included in the protection scope of the utility model.

[0021] Please refer to Figure 1As shown, according to an embodiment of the utility model, a throttling assembly is provided, comprising a first valve pipe assembly 1 and a second valve pipe assembly 2 connected in parallel with each other, wherein the first valve pipe assembly 1 comprises a first pipe 11 and a first valve core assembly (not labeled in the figure) assembled therein, the second valve pipe assembly 2 comprises a second pipe 20 and a second valve core assembly 21 and a third valve core assembly 22 assembled therein in series, wherein the first valve core assembly comprises a first valve seat 121 and a first valve core 122 slidably connected to the first valve seat 121, the second valve core assembly 21 comprises a second valve seat 211, a second valve core 212 and a first elastic member 213 (e.g., a spring), the third valve core assembly 22 comprises a third valve seat 221, a third valve core 2 22 and a second elastic member 223 (for example, a spring). Under the action of the refrigerant pressure difference and the elastic force of the first elastic member 213 and / or the second elastic member 223, when the refrigerant is in a first flow direction, the first valve core 122 is in a full flow state, the second valve core 212 and the third valve core 222 are in a small hole throttling state; when the refrigerant is in a second flow direction, the first valve core 122 is in a closed state or a small hole throttling state, the second valve core 212 and the third valve core 222 are in a flow regulation state. The first flow direction is opposite to the second flow direction. It can be understood that the corresponding two ends of the aforementioned first valve tube assembly 1 and the second valve tube assembly 2 are respectively connected in parallel through the first collecting head 31 and the second collecting head 32 to form the aforementioned flow path.

[0022] In this technical solution, by simultaneously arranging the second valve core assembly 21 and the third valve core assembly 22 in the second tube 20, the pressure difference between the inlet and outlet ends of the second tube 20 can be jointly satisfied when the two valve cores are in the throttling state, thereby effectively reducing the pressure difference between the second valve core assembly 21 and the third valve core assembly 22 at their respective ends, thereby reducing the pneumatic noise of the valve tube assembly during use.

[0023] See also Figure 1 As shown, a first retaining ring 214 is provided in the opening end of the aforementioned second valve seat 211, so that the first elastic member 213 is clamped between the second valve core 212 and the first retaining ring 214. Similarly, a second retaining ring 224 is provided in the opening end of the aforementioned third valve seat 221, so that the second elastic member 223 is clamped between the third valve core 222 and the second retaining ring 224.

[0024] In some embodiments, the second valve core 212 and the third valve core 222 have different resonance frequencies in the throttling assembly, thereby preventing the two valve cores from resonating and being damaged in the assembly while effectively avoiding the generation of valve core resonance noise. That is, using different resonance frequencies can effectively suppress resonance in the system.

[0025] According to the spring oscillator resonance frequency calculation formula f=2π(k / m)1 / 2, in the formula, m is the mass of the spring oscillator, k is the spring coefficient of the spring oscillator, avoiding the resonance of the second valve core assembly 21 and the third valve core assembly 22 can be achieved by limiting the mass of the second valve core 212 and the third valve core 222 and the stiffness (i.e., stiffness coefficient) of the corresponding first elastic member 213 and the second elastic member 223. Specifically, the mass ratio of the second valve core 212 to the third valve core 222 is between 0.7 and 1.3, and the stiffness of the first elastic member 213 and the second elastic member 223 is different. Preferably, the mass ratio of the second valve core 212 to the third valve core 222 is between 0.9 and 1.1, and the stiffness of the first elastic member 213 and the second elastic member 223 is different. In a specific embodiment, the masses of the second valve core 212 and the third valve core 222 are both approximately 20 g. It should be noted that the second valve core 212 and the third valve core 222 should also meet the relevant requirements of the aforementioned mass ratio on the premise of meeting the aforementioned mass. Generally speaking, the second valve core 212 and the third valve core 222 can be formed by machining a cylinder with the same outer contour, and the difference in mass can be adjusted by the diameter of the flow hole thereon, so that the selection of raw materials tends to be consistent, which is convenient for production.

[0026] In some embodiments, the stiffness ratio of the first elastic member 213 to the second elastic member 223 is not less than 2 or not greater than 0.5, so as to ensure that the stiffness coefficients of the elastic members are relatively different, thereby effectively avoiding the occurrence of resonance when the valve core mass is relatively small. In a specific embodiment, the spring stiffness of the first elastic member 213 and the second elastic member 223 are 3N / mm and 1.5N / mm respectively.

[0027] In a specific embodiment, the diameter of the central flow hole (not marked in the figure) on the second valve seat 211 is larger than the diameter of the central flow hole (not marked in the figure) on the third valve seat 221; the diameter of the central flow hole on the second valve core 212 is larger than the diameter of the central flow hole on the third valve core 222, thereby forming gradient throttling when the refrigerant is in the second flow direction.

[0028] In another preferred embodiment, the diameter of the side flow hole (not marked in the figure) of the second valve seat 211 is not less than the diameter of the central flow hole thereof, and the diameter of the side flow hole of the third valve seat 221 is not less than the diameter of the central flow hole thereof.

[0029] In some embodiments, when the pressure difference between the two end tubes of the second valve core assembly 21 and the third valve core assembly 22 opposite to each other is less than a first predetermined value, the second valve core 212 and the third valve core 222 are in a closed valve state ( Figure 1 In the state shown), at this time, the second valve core assembly 21 and the third valve core assembly 22 both rely on the central flow hole for throttling. In a specific embodiment, the first predetermined value is 0.6Mpa. Experiments have verified that under the pressure difference in this state, the valve core fits the valve seat and no resonance occurs; when the pressure difference in the inner cavities of the two ends of the tubes opposite to each other of the second valve core assembly 21 and the third valve core assembly 22 is greater than the second predetermined value, the second valve core 212 and the third valve core 222 are in a fully open valve port state. In a specific embodiment, the second predetermined value is 2.6Mpa. Experiments have verified that under the pressure difference in this state, the valve core fits the retaining ring (that is, the first retaining ring) on ​​the valve seat and no resonance occurs.

[0030] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may be subject to various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A throttling assembly, characterized in that: The invention comprises a first valve tube assembly (1) and a second valve tube assembly (2) which are connected in parallel with each other in flow paths, wherein the first valve tube assembly (1) comprises a first tube (11) and a first valve core assembly assembled therein, and the second valve tube assembly (2) comprises a second tube (20) and a second valve core assembly (21) and a third valve core assembly (22) assembled therein in series, wherein the first valve core assembly comprises a first valve seat (121) and a first valve core (122) slidably connected to the first valve seat (121), the second valve core assembly (21) comprises a second valve seat (211), a second valve core (212) and a first elastic member (213), and the third valve core assembly ( 22) includes a third valve seat (221), a third valve core (222) and a second elastic member (223). Under the action of the refrigerant pressure difference and the elastic force of the first elastic member (213) and / or the second elastic member (223), when the refrigerant is in a first flow direction, the first valve core (122) is in a full flow state, the second valve core (212) and the third valve core (222) are in a small hole throttling state; when the refrigerant is in a second flow direction, the first valve core (122) is in a closed state or a small hole throttling state, the second valve core (212) and the third valve core (222) are in a flow regulating state; the first flow direction is opposite to the second flow direction.

2. The throttle assembly according to claim 1, characterized in that: The second valve core (212) and the third valve core (222) have different resonance frequencies in the throttling assembly.

3. The throttle assembly according to claim 1, characterized in that: The mass ratio of the second valve core (212) to the third valve core (222) is between 0.7 and 1.3, and the first elastic member (213) and the second elastic member (223) have different rigidities.

4. The throttle assembly according to claim 3, characterized in that: The mass ratio of the second valve core (212) to the third valve core (222) is between 0.9 and 1.1, and the first elastic member (213) and the second elastic member (223) have different rigidities.

5. The throttle assembly according to any one of claims 1 to 4, characterized in that: The stiffness ratio of the first elastic member (213) to the second elastic member (223) is not less than 2 or not greater than 0.

5.

6. The throttle assembly according to claim 1, characterized in that: The diameter of the central flow hole on the second valve seat (211) is greater than the diameter of the central flow hole on the third valve seat (221).

7. The throttle assembly according to claim 1, characterized in that: The diameter of the central flow hole on the second valve core (212) is greater than the diameter of the central flow hole on the third valve core (222).

8. The throttle assembly according to claim 1, characterized in that: The diameter of the side flow hole of the second valve seat (211) is not less than the diameter of the central flow hole thereof, and the diameter of the side flow hole of the third valve seat (221) is not less than the diameter of the central flow hole thereof.

9. The throttle assembly according to claim 1, characterized in that: When the pressure difference between the inner cavities of the two ends of the tube of the second valve core assembly (21) and the third valve core assembly (22) opposite to each other is less than a first predetermined value, the second valve core (212) and the third valve core (222) are in a closed valve port state; when the pressure difference between the inner cavities of the two ends of the tube of the second valve core assembly (21) and the third valve core assembly (22) opposite to each other is greater than a second predetermined value, the second valve core (212) and the third valve core (222) are in a fully open valve port state.

10. The throttle assembly according to claim 9, characterized in that The first predetermined value is 0.6 MPa, and the second predetermined value is 2.6 MPa.

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