CN218118820U - Valve seat assembly, compressor and refrigeration equipment - Google Patents

Abstract

The utility model discloses a valve seat assembly, and disclose the compressor with valve seat assembly, still disclose the refrigeration plant with compressor, valve seat assembly includes valve seat body and silk screen structure, valve seat body, set up the exhaust hole that is used for discharging refrigerant gas, the silk screen structure has seted up a plurality of meshes, the exhaust hole department is located to the silk screen structure, refrigerant gas can pass through the mesh earlier and then discharge to the outside of exhaust hole, refrigerant gas is behind the mesh, its flow field changes, can produce the influence to refrigerant gas pressure, the velocity of flow and the torrent yardstick that arouses the noise source, make refrigerant gas's pressure and velocity of flow all reduced, in order to reduce the noise of exhaust hole department, and pressure distribution and velocity of flow distribution are more even, make the gas pressure pulsation of exhaust hole position less; the pressure and the flow velocity of the high-pressure refrigerant gas are both reduced, so that the energy source generated by turbulence is reduced, the turbulence scale of the high-pressure refrigerant gas at the downstream position is reduced, and the impact force on the exhaust hole position is reduced.

Description

Valve seat assembly, compressor and refrigeration equipment

Technical Field

The utility model relates to a compressor technical field, in particular to disk seat subassembly, compressor and refrigeration plant.

Background

The compressor compresses low-pressure refrigerant gas into high-pressure refrigerant gas in the compression cavity, the high-pressure refrigerant gas is discharged from the exhaust hole of the valve seat, the pressure and the flow rate of the high-pressure refrigerant gas are high, certain impact force is achieved, and noise can be generated at the position of the exhaust hole. In the related art, sound insulation cotton is wrapped outside the compressor to achieve the noise reduction effect, but after the sound insulation cotton is wrapped, certain noise still exists in the compressor, and the frequency range of the noise is mainly below 2000 Hz.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a valve seat assembly can exert an influence to the gaseous flow field of the refrigerant of exhaust hole department, reaches noise reduction effect.

The utility model discloses still provide a compressor of having above-mentioned valve seat assembly.

The utility model discloses still provide a refrigeration plant who has above-mentioned compressor.

According to the utility model discloses a valve seat assembly of first aspect embodiment includes: the valve seat body is provided with an exhaust hole for exhausting refrigerant gas; the wire mesh structure is provided with a plurality of meshes and is arranged at the exhaust hole.

According to the utility model discloses the disk seat subassembly of first aspect embodiment has following beneficial effect at least: the screen structure is arranged at the exhaust hole, the refrigerant gas can pass through the mesh and then be discharged to the outside of the exhaust hole, the flow field of the refrigerant gas changes after passing through the mesh, the refrigerant gas passes through the mesh and then is discharged to the outside of the exhaust hole, the influence on the pressure, the flow speed and the turbulence scale of the refrigerant gas which excites a noise source can be generated, and the resistance is generated when the refrigerant gas passes through the mesh, so that the pressure and the flow speed of the refrigerant gas are reduced, the noise at the exhaust hole is reduced, the pressure distribution and the flow speed distribution are more uniform, and the gas pressure pulsation at the exhaust hole is smaller; the pressure and the flow velocity of the high-pressure refrigerant gas are both reduced, so that the energy source generated by turbulence is reduced, the turbulence scale of the high-pressure refrigerant gas at the downstream position is reduced, and the impact force on the exhaust hole position is reduced.

According to some embodiments of the invention, the wire mesh structure cover is located at the air inlet end of the exhaust hole.

According to the utility model discloses a some embodiments, the exhaust hole the inlet end department is equipped with the recess, the internal diameter of recess is greater than the internal diameter in exhaust hole, the silk screen structure is fixed in the recess.

According to some embodiments of the invention, the wire mesh structure is connected with the valve seat body laser welding, soldering or adhesive.

According to some embodiments of the utility model, the silk screen structure with the valve seat body sets up to integrative piece, the silk screen structure is made by laser cutting forming process or stamping forming process.

According to some embodiments of the utility model, the silk screen structure set up in the exhaust hole, perhaps, the silk screen structure set up in the department of giving vent to anger in exhaust hole.

According to some embodiments of the utility model, the cross-sectional area in exhaust hole is S2, the distribution area of mesh is S3, S2 with S3 satisfies: s3 is more than or equal to S2.

According to some embodiments of the present invention, the porosity of the wire mesh structure is σ, σ satisfies: the sigma is more than or equal to 75 percent.

According to the utility model discloses a some embodiments, adjacent two interval between the mesh is d1, d1 satisfies: d1 is more than or equal to 0.05mm.

According to the utility model discloses a some embodiments, singly the cross-sectional area of mesh is S1, the cross-sectional area of exhaust hole is S2, S1 with S2 satisfies: S1/S2 is less than or equal to 0.1.

According to the utility model discloses a some embodiments, the thickness of silk screen structure is h1, h1 satisfies: h1 is more than or equal to 0.15mm and less than or equal to 1mm.

According to the utility model discloses a compressor of second aspect embodiment, including the valve seat assembly of first aspect embodiment.

According to the utility model discloses the compressor of second aspect embodiment, owing to including the valve seat component of first aspect embodiment, consequently have the beneficial effect of the valve seat component of first aspect embodiment at least, no longer describe herein.

According to the utility model discloses a refrigeration plant of third aspect embodiment, including the compressor of second aspect embodiment.

According to the utility model discloses refrigeration plant, following beneficial effect: the compressor of the embodiment of the second aspect is included, so that at least the beneficial effects of the compressor of the embodiment of the second aspect are achieved, and details are not repeated here.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

The invention is further described with reference to the following figures and examples, in which:

fig. 1 is a schematic structural view of a valve seat assembly according to an embodiment of the present invention;

FIG. 2 is an enlarged view at A shown in FIG. 1;

fig. 3 is a schematic structural diagram of a compressor according to an embodiment of the present invention;

FIG. 4 is an enlarged view at B shown in FIG. 3;

fig. 5 is a schematic structural view of a wire mesh structure according to some embodiments of the present invention;

fig. 6 is a top view of a wire mesh structure according to some embodiments of the present invention;

FIG. 7 is an enlarged view at C shown in FIG. 6;

fig. 8 is a cross-sectional view of a wire mesh structure according to some embodiments of the present invention;

figure 9 is a bar graph of experimental data for a compressor in accordance with an embodiment of the present invention;

figure 10 is a bar graph of experimental data for a compressor in accordance with an embodiment of the second aspect of the present invention.

Reference numerals:

a compressor 1000;

the valve seat comprises a valve seat body 100, an exhaust hole 110, a groove 111, a valve plate 120 and a limiter 130;

wire mesh structure 200, mesh 210;

pump body assembly 300, compression chamber 310;

a motor 400;

an upstream location 500;

a downstream location 600.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it should be understood that the orientation or positional relationship indicated with respect to the orientation description, such as up, down, front, rear, left, right, etc., is based on the orientation or positional relationship shown in the drawings, and is only for convenience of description and simplification of description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.

In the description of the present invention, a plurality of means are one or more, a plurality of means are two or more, and the terms greater than, less than, exceeding, etc. are understood as not including the number, and the terms greater than, less than, within, etc. are understood as including the number. If there is a description of first and second for the purpose of distinguishing technical features only, this is not to be understood as indicating or implying a relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of technical features indicated.

In the description of the present invention, unless there is an explicit limitation, the words such as setting, installation, connection, etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above words in combination with the specific contents of the technical solution.

For a rolling rotor type compressor, the compressor is hereinafter referred to as a compressor, a gas suction pipe at the lower part of the compressor sucks low-pressure refrigerant gas in a liquid reservoir into a cylinder, the cylinder is connected with a crankshaft, the upper part of the crankshaft is fixed with a rotor of a motor, so that the motor can drive the crankshaft to rotate, and then the crankshaft can drive the cylinder to rotate so as to compress the low-pressure refrigerant gas, the low-pressure refrigerant gas is compressed and then changed into high-pressure refrigerant gas, and is discharged out of a pump body assembly, the high-pressure refrigerant gas enters a shell of the compressor, and finally is discharged out of the compressor from a gas outlet at the upper part of the compressor through a gap of the motor.

Specifically, the pump body assembly is provided with a valve seat, high-pressure refrigerant gas is discharged into a shell of the compressor from an exhaust hole of the valve seat, the pressure and the flow rate of the high-pressure refrigerant gas are high, certain impact force is achieved, and noise can be generated at the position of the exhaust hole. The exhaust noise mainly comprises: the high-speed high-pressure fluid is discharged from the valve port of the exhaust valve to generate monopole source noise; monopole source noise generated by valve plate fluttering; the high-speed high-pressure fluid drives the valve plate to slap the structure vibration noise generated by the limiter; the valve plate slaps the valve seat to generate structural vibration noise; dipole source noise generated under the influence of hard boundaries of a valve plate, a limiter, a valve seat and a silencer when high-speed high-pressure fluid is discharged; resonance noise generated by the compression cavity and the muffler cavity; the high-speed high-pressure fluid jet is involved in quadrupole source noise generated by the static fluid at the periphery of the high-speed high-pressure fluid jet.

In addition, the compressor intermittently sucks and exhausts air to ensure that the pressure of high-pressure refrigerant gas is non-uniformly changed in the position of the exhaust port, so that airflow pressure pulsation is caused, the pressure of the high-pressure refrigerant gas acting on a pipeline or a pump body assembly is not uniform, and a certain part has more concentrated or larger pressure, so that parts such as pipelines vibrate and fatigue damage is caused.

In the related art, soundproof cotton is usually wrapped outside the compressor to achieve the noise reduction effect, but after the soundproof cotton is wrapped, certain noise still exists in the compressor, the frequency range of the noise is mainly below 2000Hz, the noise in the frequency range occupies a significant proportion of the noise of the whole compressor, and the noise reduction effect of the soundproof cotton on the noise in the 1250Hz-2000Hz range is limited.

Based on this, referring to fig. 1 to 4, according to the utility model discloses a valve seat assembly of first aspect embodiment, valve seat assembly applies in compressor 1000, specifically, valve seat assembly includes valve seat body 100 and silk screen structure 200, valve seat body 100 is flange shape structure, valve seat body 100 is connected with compressor 1000's bent axle rotation, valve seat body 100 sets up to compressor 1000's bearing, valve seat body 100 is used for controlling the discharge of refrigerant gas, exhaust hole 110 has been seted up on valve seat body 100, exhaust hole 110 runs through valve seat body 100, exhaust hole 110 has the inlet end and the end of giving vent to anger, the end of giving vent to anger of exhaust hole 110 is provided with valve block 120 and stopper 130, valve block 120 is located between stopper 130 and valve seat body 100, the end of giving vent to anger of exhaust hole 110 and the inside cavity intercommunication of compressor 1000 casing, the inlet end of exhaust hole 110 and the compression chamber 310 intercommunication of pump body assembly 300 refrigerant, compressor 1000 compresses the low-pressure gas into high-pressure refrigerant gas in compression chamber 310, high-pressure gas strikes valve block 120 and opens it, high-pressure refrigerant gas discharges from exhaust hole 110, and flows to compressor 1000's casing.

More specifically, referring to fig. 5 and 8, a plurality of meshes 210 are formed on the screen structure 200, the inner diameters of the meshes 210 are smaller, the plurality of meshes 210 may be uniformly or non-uniformly arranged, the inner diameters of the meshes 210 are uniform along the length direction of the meshes 210, the extending direction of the meshes 210 is the same as the extending direction of the exhaust holes 110, and the meshes 210 penetrate through the screen structure 200. The wire mesh structure 200 is disposed in the exhaust hole 110, or the wire mesh structure 200 may also be disposed at an inlet end or an outlet end of the exhaust hole 110, such that the high-pressure refrigerant gas in the compression cavity 310 passes through the mesh 210 and then is exhausted out of the exhaust hole 110, the mesh 210 may conduct the exhaust hole 110, and the high-pressure refrigerant gas may pass through the mesh 210 and be exhausted from the exhaust hole 110. The silk screen structure 200 is fixed to be set up, and the silk screen structure 200 can with the pore wall butt of exhaust hole 110, and the silk screen structure 200 specifically is single-deck lamellar structure, and thickness is less, and the thickness of silk screen structure 200 is less than the length of exhaust hole 110. It should be noted that the shape of the screen structure 200 is adapted to the shape of the cross-sectional area of the exhaust hole 110, for example, when the cross-sectional area of the exhaust hole 110 is circular, the shape of the screen structure 200 is also circular, so that the screen structure 200 covers the exhaust hole 110 completely, and the high-pressure refrigerant gas can pass through the mesh 210, so as to achieve the noise reduction effect.

Referring to fig. 2 and 4, it should be noted that, with the screen structure 200 as a reference, positions on both sides of the air inlet side and the air outlet side of the screen structure 200 are respectively divided into an upstream position 500 and a downstream position 600, specifically, the upstream position 500 is located below the screen structure 200, the downstream position 600 is located above the screen structure 200, the high-pressure refrigerant gas in the compression chamber 310 firstly enters the screen structure 200 from the upstream position 500, then passes through the mesh 210 and flows out from the downstream position 600, and finally is discharged out of the exhaust hole 110, and the high-pressure refrigerant gas moves upward as a whole.

The mesh structure 200 has an effect on the flow rate, pressure and turbulence scale of the high pressure refrigerant gas at the discharge hole 110, as described below.

Regarding the influence on the flow velocity, the refrigerant gas generates a certain resistance when passing through the meshes 210 of the screen structure 200, the resistance increases with the increase of the flow velocity of the refrigerant gas, the meshes 210 can reduce the flow velocity of the refrigerant gas, and the screen structure 200 can make the flow velocity of the refrigerant gas at the downstream position 600 more uniform, in addition, after the flow velocity distribution of the refrigerant gas is made more uniform by the screen structure 200, the influence on two aspects can be generated, on the one hand, the harmonic component of the velocity profile of the high-pressure refrigerant gas is reduced, on the second hand, the conversion of the tangential velocity difference between the high-pressure refrigerant gas to the turbulent kinetic energy is reduced, and the two aspects cause that the wall pressure pulsation generated when the high-pressure refrigerant gas acts on the solid wall surface is reduced, and the change on the space distribution is reduced, so that the dipole source dipole noise is reduced.

Regarding the influence on the pressure, the screen structure 200 may influence the flow field of the refrigerant gas at the upstream position 500, so that the pressure of the flow field at the upstream position is redistributed, the existence of the solid wall surface may influence the flow rates of the high-pressure refrigerant gas at the upstream position 500 and the downstream position 600, thereby influencing the pressure generated by the inertia of the high-pressure refrigerant gas, and the solid wall surface may also reflect and scatter the pressure, thereby influencing the pressure in the high-pressure refrigerant gas.

Regarding the effect on the scale of the turbulent flow, it should be noted that the turbulent flow is a flow state of the fluid, when the flow velocity of the fluid is increased greatly, the flow line is no longer clearly identifiable, many small eddies occur in the flow field, the laminar flow is destroyed, and not only sliding but also mixing between adjacent flow layers forms the turbulent flow. The turbulence scale refers to the distance swept by a turbulent air mass tumbling pulse for one cycle. The high-pressure refrigerant gas has a large flow velocity in the compression cavity 310 to form a plurality of turbulent flows and turbulent eddies with large turbulent scales, the impact force on the exhaust hole 110 is large, the cross sectional area of the single mesh 210 of the wire mesh structure 200 is small, the high-pressure refrigerant gas breaks the large vortex structure of the turbulent eddies to break the large vortex structure into small vortex structures with small turbulent scales after passing through the mesh 210, the small vortex structures with small turbulent scales are easy to dissipate under the action of viscosity, and then the turbulent scales of the high-pressure refrigerant gas at the downstream position 600 are reduced.

In summary, the silk screen structure 200 of the present embodiment changes the pressure, the flow rate and the turbulence scale of the high-pressure refrigerant gas by affecting the flow field of the high-pressure refrigerant gas, so that both the pressure and the flow rate of the refrigerant gas are reduced, and the pressure distribution and the flow rate distribution are more uniform, so as to reduce the noise at the exhaust hole 110, and make the gas pressure pulsation of the high-pressure refrigerant gas acting on the exhaust hole 110 smaller; the pressure and flow rate of the high-pressure refrigerant gas are both reduced, so that the energy source generated by turbulence is reduced, the turbulence scale of the high-pressure refrigerant gas at the downstream position 600 is reduced, the turbulence intensity is rapidly reduced, and the impact force can be reduced. It should be noted that, the wire mesh structure 200 of the present embodiment reduces noise from the source of the excitation noise, and before the high-pressure refrigerant gas generates noise, the characteristics of the flow field of the high-pressure refrigerant gas are changed to make the noise generated by the high-pressure refrigerant gas lower.

Note that, referring to the experimental data bar charts shown in fig. 9 and 10, the noise comparison effect charts of the comparative sample and the evaluation sample are shown, the ordinate on the vertical axis represents the noise value, the abscissa on the horizontal axis represents the frequency value of the corresponding noise, the bar chart on the far right side represents the integrated noise value, the black fill represents the increment of the evaluation sample on the basis of the comparative sample, the noise expressed as the evaluation sample is further deteriorated with respect to the comparative sample, the shadow fill represents the decrement of the evaluation sample on the basis of the comparative sample, and the noise expressed as the evaluation sample is improved with respect to the comparative sample.

Referring to fig. 9, when the compressor 1000 is in the operating condition of 90Hz, the effect of the wire mesh structure 200 is compared with that of the wire mesh structure 200, and the wire mesh structure 200 is disposed in the exhaust hole 110, so that it can be known that the wire mesh structure 200 has a better noise reduction effect on noise in the frequency range of 1250 to 2000 Hz. Referring to fig. 10, when the compressor 1000 is in the 60Hz operation condition, the effect of the wire mesh structure 200 is compared with that of the wire mesh structure 200, and the wire mesh structure 200 is disposed in the exhaust hole 110, so that it can be known that the wire mesh structure 200 has a better noise reduction effect on noise in the frequency range of 1250 to 2000Hz, and the wire mesh structure 200 can have a certain noise reduction effect when the compressor 1000 is in the 90Hz operation condition or the 60Hz operation condition.

It is understood that the wire mesh structure 200 and the valve seat body 100 are provided as a separate piece, which can be replaced, and the wire mesh structure 200 and the valve seat body 100 can also be provided as an integrated piece, the wire mesh structure 200 is manufactured by a laser cutting molding process or a punch forming process, and the wire mesh structure 200 can be located at the air inlet end position of the air outlet hole 110, so as to facilitate the above-mentioned processing.

It should be noted that the specific position of the wire mesh structure 200 in the exhaust hole 110 does not affect the noise reduction effect of the wire mesh structure 200, and it is only required to ensure that the high-pressure refrigerant gas is firstly discharged out of the exhaust hole 110 through the mesh 210, but if the wire mesh structure 200 is located in the middle of the exhaust hole 110, when the wire mesh structure 200 is assembled, a tool needs to be inserted into the exhaust hole 110, so that the assembly operation is not convenient enough. Referring to fig. 2 and 4, it can be understood that the wire mesh structure 200 may be covered at the air inlet end of the exhaust hole 110, that is, the wire mesh structure 200 is located at one end of the exhaust hole 110 close to the compression chamber 310, the wire mesh structure 200 is located at the end of the exhaust hole 110, and more positions are left for assembling the wire mesh structure 200, which also facilitates performing processes such as gluing, welding, etc., and, when the wire mesh structure 200 and the valve seat body 100 are provided as a single piece, the wire mesh structure 200 is exposed outside the valve seat body 100, which may facilitate performing processes such as laser cutting, molding, or press molding.

Referring to fig. 2 and 4, it can be understood that the groove 111 is formed at the inlet end of the exhaust hole 110, the groove 111 is annular, it can be understood that the hole wall at the inlet end of the exhaust hole 110 is expanded radially outward to form the groove 111, and it can be specifically formed by a material removing process, the inner diameter of the groove 111 is larger than the inner diameter of the exhaust hole 110, when the groove 111 is understood as a part of the exhaust hole 110, the inner diameter of the groove 111 should be larger than the minimum inner diameter of the exhaust hole 110, and the inner diameter of the exhaust hole 110 is uniform in the length direction, so that the cross-sectional area of the groove 111 is larger than the cross-sectional area of the exhaust hole 110. The wire mesh structure 200 is fixed in the groove 111, for example, the wire mesh structure 200 is connected with the valve seat body 100 by laser welding, gluing or soldering, and it should be noted that, since the wire mesh structure 200 is fixed in the groove 111, the outer diameter of the wire mesh structure 200 is larger than the minimum inner diameter of the exhaust hole 110.

It can be understood that the mesh holes 210 may be any one of a square shape, a triangular shape or a circular shape, or may be other irregular shapes, as shown in fig. 5 to 7, the plurality of mesh holes 210 may be regularly and uniformly arranged, the cross-sectional areas of the plurality of mesh holes 210 are the same, and the plurality of mesh holes 210 are distributed at equal intervals in the longitudinal and transverse directions, so that the pressure and flow velocity distribution of the refrigerant gas passing through the mesh holes 210 is uniform, the distribution area of the mesh holes 210 is circular and adapted to the cross-sectional area of the exhaust holes 110, and the cross-sectional area of the mesh holes 210 at the circumferential edge of the circle is smaller due to the structure of the circular cut-off portion.

Referring to fig. 6, it can be understood that the distribution area of the mesh holes 210 is S3, the cross-sectional area of the exhaust holes 110 is S2, and the relationship: s3 is greater than or equal to S2, when the relation is met, the meshes 210 can be distributed in the exhaust holes 110 as much as possible, the number of the meshes 210 is large, high-pressure refrigerant gas can pass through the large number of the meshes 210, the influence on turbulent flow vortexes is enhanced, the turbulent flow scale of the turbulent flow vortexes is reduced, the noise reduction effect is further enhanced, the liquidity of the wire mesh structure 200 is good, and the exhaust resistance can be reduced. It should be noted that, the distribution area S3 of the mesh holes 210 is smaller than the total area of the screen structure 200, the cross-sectional area S2 of the exhaust holes 110 of the present embodiment is uniform along the length direction of the exhaust holes 110, and when the air inlet end of the exhaust holes 110 is provided with the groove 111 of the above-mentioned embodiment, since the cross-sectional area of the groove 111 is larger than the cross-sectional area of the exhaust holes 110, S2 of the present embodiment should be understood as the minimum cross-sectional area of the exhaust holes 110, the distribution area S3 of the mesh holes 210 of the present embodiment is circular, and the cross-sectional area S2 of the exhaust holes 110 is also circular.

Referring to fig. 6, it should be noted that the distribution area of the mesh holes 210 specifically means that all the mesh holes 210 are regarded as a whole, the outer periphery of the whole is closed to form a reference pattern, the reference pattern is circular, and the area of the reference pattern is the area S3 of the distribution area of the mesh holes 210.

It should be noted that the porosity is a percentage of a pore volume in the material to a total volume of the material in a natural state, and the porosity directly reflects a degree of compaction of the material, and for this embodiment, the porosity is a percentage of a volume of the mesh holes 210 of the screen structure 200 to a volume of the screen structure 200 when the screen structure 200 is a solid body. When the porosity is too large, the influence on the flow field of the refrigerant gas is weak, the noise reduction effect is not good enough, and when the porosity is too small, the fluidity of the silk screen structure 200 is poor, the exhaust resistance is large, and the exhaust efficiency is influenced. Based on this, the present embodiment defines that the porosity of the screen structure 200 is σ, and σ satisfies the relation: sigma is more than or equal to 75 percent, and when the relational expression is satisfied, the noise reduction effect and the exhaust efficiency of the screen structure 200 can be simultaneously considered.

It can be understood that when the distance between two adjacent mesh holes 210 in the screen structure 200 is too small and the two mesh holes 210 are too close, the structural strength of the screen structure 200 is low, the screen structure 200 needs to bear the impact force of the high-pressure refrigerant gas, and the screen structure is easily damaged when the structural strength is too low. Based on this, the present embodiment defines that the distance between two adjacent meshes 210 is d1, and d1 satisfies the relation: d1 is not less than 0.05mm, and when the relational expression is satisfied, the distance between two adjacent meshes 210 is large, and the wall thickness is large, so that the structural strength of the whole silk screen structure 200 is large, and the durability can be improved.

It can be understood that the ratio of the cross-sectional area of the single mesh 210 in the cross-sectional area of the exhaust hole 110 has a certain relation with the influence on the flow field of the high-pressure refrigerant gas, and when the ratio is larger, it indicates that the volume ratio of the single mesh 210 relative to the exhaust hole 110 is larger, and the cross-sectional area of the mesh 210 is not small enough to have a weak influence on the flow field of the refrigerant gas, for example, the large vortex structure of the turbulent vortex is not small enough to form a small vortex structure after passing through the mesh 210, and the viscous effect on the turbulent vortex is also weak, and the energy of the turbulent vortex cannot be well lost. Based on this, the present embodiment defines that the cross-sectional area of the single mesh 210 is S1, the cross-sectional area of the exhaust holes 110 is S2, and S1 and S2 satisfy the relationship: S1/S2 is less than or equal to 0.1, and when the relation is satisfied, the turbulence scale of the turbulence vortex can be further weakened, the impact force generated by the turbulence vortex can be reduced, and the noise reduction effect is good.

It can be understood that the flow field of the high-pressure refrigerant gas is influenced by the screen structure 200 of the present embodiment, so as to change the distribution of the flow velocity and the pressure of the high-pressure refrigerant gas, thereby achieving the noise reduction effect, the thickness of the screen structure 200 has little influence on the noise reduction effect, and the requirement of the screen structure 200 on the thickness is low based on the noise reduction effect. However, when the thickness of the screen structure 200 is too large, the mesh 210 penetrates through the screen structure 200, and the length of the mesh 210 is too large, so that when refrigerant gas passes through the screen structure 200, the generated resistance is large, and the exhaust efficiency is affected; when the thickness of the screen structure 200 is too small, the structural strength of the screen structure 200 is small, and the screen structure is easily damaged when bearing the impact force of the high-pressure refrigerant gas. Based on this, referring to fig. 8, the present embodiment defines that the thickness of the screen structure 200 is h1, and the thickness h1 satisfies the relation: h1 is more than or equal to 0.15mm and less than or equal to 1mm, and when the relational expression is satisfied, the exhaust resistance is small and the structural strength is large.

According to the utility model discloses compressor 1000 of second aspect embodiment, including the valve seat assembly of above-mentioned embodiment, compressor 1000 specifically can be rotary compressor or rolling rotor compressor, because the compressor 1000 of this embodiment includes the valve seat assembly of above-mentioned embodiment, consequently has foretell beneficial effect, no longer explains here.

According to the utility model discloses refrigeration plant of third aspect embodiment, including the compressor 1000 of above-mentioned embodiment, this refrigeration plant can be domestic appliance such as air conditioner, refrigerator, because the refrigeration plant of this embodiment includes the compressor 1000 of above-mentioned embodiment, consequently has foretell beneficial effect, no longer explains here.

The harm of noise to the human body is systemic, and can cause changes in the auditory system and also affect the non-auditory system. The influence of noise on the auditory organs is a process from physiological migration to pathological, and pathological hearing impairment must reach a certain intensity and contact time. The changes in damage to the auditory organs caused by prolonged exposure to more intense noise typically progress from temporary to permanent hearing threshold shifts. In addition, repeated long-term stimulation of noise, which exceeds the physiological tolerance, can cause damage to the central nervous system, excite the cerebral cortex and inhibit imbalance, cause abnormal conditioned reflex, cause cerebrovascular dysfunction and change of brain position, thereby producing neurasthenia syndrome, which can cause symptoms such as headache, dizziness, tinnitus, easy fatigue, poor sleep and the like, and can also cause neurobehavioral effects such as memory, thinking ability, learning ability, reading ability reduction and the like of an exposer.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made without departing from the spirit of the present invention within the knowledge of those skilled in the art.

Claims (13)

1. A valve seat assembly, comprising:

the valve seat body is provided with an exhaust hole for exhausting refrigerant gas;

the wire mesh structure is provided with a plurality of meshes and is arranged at the exhaust hole.

2. The valve seat assembly of claim 1, wherein the wire mesh structure is disposed over an air inlet end of the exhaust vent.

3. The valve seat assembly of claim 2, wherein the inlet end of the exhaust vent has a recess with an inner diameter greater than an inner diameter of the exhaust vent, the wire mesh structure being secured within the recess.

4. The valve seat assembly of claim 1, wherein the wire mesh structure is laser welded, soldered, or adhesively attached to the valve seat body.

5. The valve seat assembly of claim 1, wherein the wire mesh structure is provided as a unitary piece with the valve seat body, the wire mesh structure being made by a laser cutting forming process or a stamping forming process.

6. The valve seat assembly of claim 1, wherein the wire mesh structure is disposed within the exhaust bore or is disposed at an outlet end of the exhaust bore.

7. The valve seat assembly according to claim 1, wherein the cross-sectional area of the exhaust hole is S2, the area of the distribution area of the mesh hole is S3, and S2 and S3 satisfy: s3 is more than or equal to S2.

8. The valve seat assembly of claim 1, wherein the wire mesh structure has a porosity σ, the σ satisfying: the sigma is more than or equal to 75 percent.

9. The valve seat assembly as claimed in claim 1, wherein the spacing between two adjacent mesh openings is d1, and d1 satisfies: d1 is more than or equal to 0.05mm.

10. The seat assembly of claim 1, wherein the cross-sectional area of the individual mesh openings is S1, the cross-sectional area of the exhaust holes is S2, and S1 and S2 satisfy: S1/S2 is less than or equal to 0.1.

11. The valve seat assembly of claim 1, wherein the wire mesh structure has a thickness h1, wherein h1 satisfies: h1 is more than or equal to 0.15mm and less than or equal to 1mm.

12. A compressor, comprising a valve seat assembly as claimed in any one of claims 1 to 11.

13. Refrigeration appliance, characterized in that it comprises a compressor as claimed in claim 12.

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