CN110657097B - Damping device for exhaust valve in compressor, exhaust valve assembly and compressor - Google Patents
Damping device for exhaust valve in compressor, exhaust valve assembly and compressor Download PDFInfo
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- CN110657097B CN110657097B CN201810700723.0A CN201810700723A CN110657097B CN 110657097 B CN110657097 B CN 110657097B CN 201810700723 A CN201810700723 A CN 201810700723A CN 110657097 B CN110657097 B CN 110657097B
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- 238000013016 damping Methods 0.000 title claims abstract description 43
- 230000006835 compression Effects 0.000 claims abstract description 38
- 238000007906 compression Methods 0.000 claims abstract description 38
- 230000007246 mechanism Effects 0.000 claims description 14
- 239000012530 fluid Substances 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 4
- 230000007704 transition Effects 0.000 claims description 4
- 238000013461 design Methods 0.000 description 4
- 238000003754 machining Methods 0.000 description 4
- 230000002035 prolonged effect Effects 0.000 description 4
- 238000005266 casting Methods 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000000758 substrate Substances 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/065—Noise dampening volumes, e.g. muffler chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/13—Noise
- F04C2270/135—Controlled or regulated
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
The invention relates to a damping device for an exhaust valve in a compressor, the damping device comprising a stationary body (10), the stationary body (10) comprising an exhaust orifice fluidly connecting a compression chamber (C) and an exhaust chamber (D), the exhaust orifice comprising an inlet (13), an outlet (12) and an intermediate chamber (11) arranged between the inlet (13) and the outlet (12) fluidly connecting the inlet (13) and the outlet (12), the intermediate chamber (11) being configured to cause a backflow of gas from the exhaust chamber (D) into the intermediate chamber (11) creating a vortex flow (V). The invention also relates to a discharge valve assembly comprising the damping device and a compressor adopting the discharge valve assembly.
Description
Technical Field
The invention relates to the field of compressors, in particular to a damping device for an exhaust valve in a compressor. The invention also relates to a discharge valve assembly comprising the damping device and a compressor adopting the discharge valve assembly.
Background
This section provides background information related to the present disclosure, which does not necessarily constitute prior art to the present invention.
In general, the market requires a compressor to operate at high efficiency in a wide temperature range, and in order to cope with the requirement of the compressor for pressure ratio diversity, a dynamic exhaust valve (HVE), which is a one-way flow valve comprising a valve plate (moving part) and a valve plate (thrust part), is used, wherein the magnitude of impact force of fluid medium determines the opening degree of the valve in the forward direction, and the valve is closed to prohibit flow in the reverse direction. For example, in the description of the related art scroll compressor including the discharge valve, referring to fig. 1, fig. 1 is a longitudinal sectional view of the scroll compressor provided with the discharge valve. A scroll compressor (hereinafter simply referred to as a "compressor") 100 may include a housing 110. The housing 110 may include a housing body 112 having a substantially cylindrical shape, a top cover 114 mounted to a top of the housing body 112, and a bottom cover 116 mounted to a bottom of the housing body 112. The housing 110 defines an interior volume of the scroll compressor 100. Additionally, a partition 119 may be provided within the housing 110 such that the partition 119 defines a high pressure region HR with the top cover 114 (the high pressure region HR is adapted to temporarily store high pressure working fluid to be discharged to the outside of the compressor), and the partition 119 defines a low pressure region LR with the housing body 112 and the bottom cover 116.
The scroll compressor 100 also includes a compression mechanism CM disposed within the housing 110 and adapted to compress a working fluid, such as a refrigerant. The compression mechanism CM may include an orbiting scroll member 150 and a non-orbiting scroll member 160.
The orbiting scroll member 150 may include: a substrate 152; a spiral moving scroll 154 extending upward from an upper surface of the base plate 152; and a hub 156 extending downwardly from a lower surface of the base plate 152.
Non-orbiting scroll member 160 may include: a substrate 162; a spiral fixed scroll 164 extending downward from a lower surface of the base plate 162; a discharge hole 166 formed at a substantially center of the base plate 162 and adapted to communicate with a discharge chamber of the compression mechanism CM; and a recess 168 formed at a substantially center of the base plate 162, the recess 168 being located above the vent hole 166 and adapted to communicate with the high pressure region HR.
Fixed scroll 164 may be engaged with orbiting scroll 154 to define a series of crescent-shaped working fluid pockets. These cavities may include: a closed compression chamber of increased pressure being compressed.
Therein, a discharge valve (such as an HVE valve) 190 may be provided in the recess 168 of the non-orbiting scroll member 160 to control the discharge of the compression mechanism CM. Specifically, referring to fig. 2 to 3, wherein fig. 2 is a partially exploded perspective view showing that an exhaust valve is provided at an exhaust hole of a compression mechanism of a related art compressor, wherein the exhaust valve 190 includes a valve plate 191, a valve plate 192, and a stopper 193. Fig. 3 is a partial perspective sectional view illustrating a discharge valve installed at a discharge hole of the compressor of fig. 2. At the beginning of the operation of the compression mechanism of the compressor, the pressure in the compression chamber defined between the movable scroll 150 and the fixed scroll 160 is lower than the pressure in the discharge chamber (i.e., the high-pressure region HR), the pressure difference between the chambers makes the discharge valve in a closed state (i.e., the valve plate 192 covers the valve hole of the closed valve plate), then the gas in the compression chamber will continue to be compressed until the pressure in the compression chamber reaches the sum of the pressure in the discharge chamber and the pressure loss, and the valve plate 192 can be opened to discharge the gas. As the compression mechanism continues to discharge, when the compression chamber pressure is less than the sum of the discharge chamber pressure and the pressure loss, a back flow of gas is generated, and the back flow of gas beats against the valve plate 192 of the discharge valve, so that the discharge valve is closed (i.e., the valve plate 192 again covers the valve hole of the closed valve plate 191). However, during the gas backflow, since there is no buffer zone, the valve plate 192 collides with the valve plate 191 at a great speed due to the rebound force of the gas backflow striking the valve plate and the valve plate 192 itself, which generates great striking noise and also reduces the life of the exhaust valve. Experiments have shown that the noise of a compressor with an exhaust valve is improved by at least 5 to 10 db compared to a compressor without an exhaust valve. And noise is continuously generated due to the fact that the exhaust gas, the backflow and the exhaust gas of the compressor are continuously circulated.
In order to suppress such noise, the related art provides a muffler M at the exhaust hole (as shown in fig. 4, wherein fig. 4 is a perspective view showing the muffler M according to the related art). However, in the case of employing the muffler M, only noise (e.g., high-frequency noise) in a partial frequency range in the entire frequency band can be suppressed in general. Moreover, due to the provision of the muffler, a pressure drop may also be caused to adversely affect the performance of the compressor and the entire refrigeration system. In addition, additionally providing the muffler may complicate a manufacturing process, increase manufacturing costs, and require additional installation space for the muffler due to an increased number of parts, and also deteriorate operational reliability of the compressor accordingly.
Disclosure of Invention
Technical problems to be solved by the invention
The damping device of the invention avoids the use of a silencer, in particular, in the undercompressed compressor of the exhaust valve, the exhaust performance of the compressor is maintained or improved, the noise of the exhaust valve can be obviously reduced, the service life of the exhaust valve is prolonged, and the running reliability of the compressor is improved.
Technical proposal
The present invention provides a damping device for a discharge valve in a compressor, the damping device comprising a stationary body comprising a discharge orifice fluidly connecting a compression chamber and a discharge chamber, the discharge orifice comprising an inlet, an outlet, and an intermediate chamber disposed between the inlet and the outlet fluidly connecting the inlet and the outlet, the intermediate chamber being configured to cause backflow of gas from the discharge chamber to generate a vortex within the intermediate chamber.
Preferably, a cross-sectional area of the intermediate chamber perpendicular to the gas flow direction is larger than a cross-sectional area of the outlet perpendicular to the gas flow direction and larger than a cross-sectional area of the inlet perpendicular to the gas flow direction.
More preferably, the cross-sectional area of the outlet perpendicular to the direction of flow of the air stream is larger than the cross-sectional area of the inlet perpendicular to the direction of flow of the air stream.
Preferably, the connection between the intermediate chamber and the outlet is arranged to allow a gradual transition of the intermediate chamber to the outlet.
Preferably, the maximum dimension of the intermediate chamber in a cross section substantially along the gas flow direction is equal to or greater than the equivalent diameter of the inlet.
Preferably, the fixed body comprises a first half body and a second half body which are separated, the first half body comprises the outlet and a first middle cavity, the second half body comprises the inlet and a second middle cavity, and the first middle cavity and the second middle cavity are matched to form the middle cavity when the first half body is connected with the second half body.
Preferably, the contour of the intermediate chamber is configured as a contour formed by a curve, by a line segment or by a connection of a curve and a line segment, as seen in a section of the stationary body in the direction of gas flow.
Preferably, the intermediate chamber is a swivel chamber having a longitudinal central axis of the vent hole as a swivel axis.
Preferably, the lowest point of the intermediate chamber along the longitudinal central axis of the vent hole in the direction from the vent chamber towards the compression chamber extends beyond or is flush with the following plane: the plane is a plane perpendicular to the flow direction of the air flow at the intersection of the contour of the intermediate cavity and the contour of the inlet.
The invention also provides an exhaust valve assembly, which comprises an exhaust valve and the damping device, and further comprises a valve plate, a valve plate and a limiter, wherein the valve plate, the valve plate and the limiter are arranged at the outlet of the exhaust hole of the damping device.
The invention also provides a compressor comprising the exhaust valve assembly.
Preferably, the compressor is a scroll compressor, and the compression mechanism of the scroll compressor includes a fixed scroll member and an movable scroll member defining a compression chamber therebetween, a base plate of the fixed scroll member forming the fixed body of the damping device of the discharge valve assembly, wherein a discharge hole of the damping device is provided at a substantially radial center of the base plate of the fixed scroll member.
Technical effects
The damping device for the exhaust valve has the beneficial effects that: the gas flows back in the exhaust hole to form vortex so as to generate resistance, reduce the pressure difference between the pressure of the exhaust cavity and the pressure of the compression cavity, prolong the closing time of the valve and weaken the impact between the valve plate of the exhaust valve and the valve plate, thereby achieving the aim of reducing noise; the impact force and the frequency of the valve plate are reduced, the service life of the valve plate can be obviously prolonged, and the reliability of the compressor is further improved; avoiding the use of prior art silencers M, reducing the weight of the casting and reducing the cost
Drawings
The features and advantages of the present invention will be more readily understood from the detailed description provided below, taken in conjunction with the accompanying drawings, in which:
fig. 1 is a longitudinal sectional view showing a related art compressor provided with a discharge valve.
Fig. 2 is a partially exploded perspective view illustrating the disposition of an exhaust valve at an exhaust hole of a non-orbiting scroll part of the compressor of fig. 1, wherein the exhaust valve includes a valve plate, and a stopper.
Fig. 3 is a partial perspective cross-sectional view illustrating a related art after a discharge valve is installed at a discharge hole of a non-orbiting scroll part of a compressor.
Fig. 4 is a perspective view showing a related art muffler for an exhaust valve.
Fig. 5 is a sectional view illustrating a damping device for an exhaust valve according to one embodiment of the present invention, wherein the damping device includes an exhaust hole having an inlet, an outlet, and an intermediate chamber.
Fig. 6 is a perspective cross-sectional view illustrating a damping device for an exhaust valve according to one embodiment of the present invention, wherein the damping device includes an exhaust hole having an inlet, an outlet, and an intermediate chamber.
Fig. 7 is a schematic view showing sectional areas of respective outlines of an inlet, an outlet, and an intermediate chamber of the exhaust hole in fig. 5, seen from a gas backflow direction from the exhaust chamber, wherein the sectional area outline of the intermediate chamber is indicated by a broken line.
Fig. 8 is a perspective cross-sectional view illustrating an exhaust valve assembly including the damping device of fig. 5 according to the present invention.
Fig. 9 is a sectional view showing a damping device for an exhaust valve according to another embodiment of the present invention, wherein the damping device is of a split type structure.
Fig. 10 is a flow chart showing formation of a vortex in the exhaust hole using the damping device according to the present invention.
Fig. 11 is a flow diagram showing the flow of air in a prior art vent.
Detailed Description
The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses.
Next, a damping device for an exhaust valve according to an embodiment of the present invention will be described with reference to fig. 5 to 9.
The compressor referred to in the embodiments in the drawings is a scroll compressor, however, it should be understood that the present invention is not limited to scroll compressors, but may be applied to any suitable type of compressor. The compression mechanism of the scroll compressor includes a non-orbiting scroll member and an orbiting scroll member (not shown) defining a compression chamber C therebetween, the compression chamber C being in fluid communication with a discharge chamber D through a discharge hole, wherein gas is compressed in the compression chamber C and then discharged into the discharge chamber D through the discharge hole.
As shown in fig. 5 and 6, the non-orbiting scroll part of the compression mechanism of the scroll compressor includes: a base plate forming the fixed body 10, and a spiral fixed wrap extending downward from a lower surface of the base plate. Wherein the fixed body 10 of the base plate is substantially disc-shaped, and an exhaust hole adapted to communicate with the exhaust chamber of the compression mechanism is provided at substantially the center of the fixed body 10. The vent comprises an inlet 13, an outlet 12 and an intermediate chamber 11 disposed between the inlet 13 and the outlet 12 in fluid communication with the inlet 13 and the outlet 12. In the case where the discharge valve is installed at the discharge hole of the base plate of the non-orbiting scroll member to control the discharge of the compression mechanism, and when the gas backflow is generated as the compression mechanism is discharged such that the compression chamber C pressure is smaller than the sum of the discharge chamber D pressure and the pressure loss, the gas backflow from the discharge chamber D generates a substantially vortex V in the intermediate chamber 11 (as shown in fig. 10). Because the gas flows back to form strong vortex in the middle cavity of the exhaust hole, a large amount of energy is additionally consumed, the pressure difference between the pressure of the exhaust cavity and the pressure of the compression cavity is reduced, the closing time of the valve is prolonged, the impact between the valve plate of the exhaust valve and the valve plate is weakened, and the purpose of noise reduction is achieved; the impact force and the frequency of the valve plate are reduced, the service life of the valve plate can be obviously prolonged, and the reliability of the compressor is further improved; while avoiding the use of prior art silencers M (shown in fig. 3), reducing the weight of the casting and reducing costs.
That is, the non-orbiting scroll member may act as a damping device for an exhaust valve of a scroll compressor, wherein a base plate of the non-orbiting scroll member forms a fixed body of the damping device. It will be appreciated by those skilled in the art that the vent hole configuration of the fixed body of the damping device (non-orbiting scroll member) may be applied to a fixed compression member of a compression structure of any type of compressor provided with a discharge valve.
Specifically, as shown in fig. 7, the cross-sectional area A1 of the intermediate chamber 11 perpendicular to the gas flow direction F (shown in the drawing as being substantially in the longitudinal direction of the exhaust hole) is larger than the cross-sectional area A2 of the outlet 12 perpendicular to the gas flow direction F and larger than the cross-sectional area A3 of the inlet 13 perpendicular to the gas flow direction F, and wherein the contour of the intermediate chamber 11 may be configured as a contour formed by a curve, a line segment, or a connection of a curve and a line segment as viewed from the cross-section of the fixing body 10 in the gas flow direction F. Those skilled in the art will appreciate that in other aspects of the embodiments, the cross-sectional area A1 of the intermediate chamber 11 may also be smaller than the cross-sectional area A2 of the outlet 12. Furthermore, the contour of the intermediate chamber 11 may be any shape suitable for generating a vortex of the gas backflow, such as a funnel shape, a conical groove, etc.
Referring to fig. 10 and 11, the p region represents a middle pressure region in the discharge hole, and the configuration of the discharge hole (particularly, the middle chamber) of the damping device (i.e., the base plate of the non-orbiting scroll member) according to the present invention can significantly increase the area of the middle pressure region to improve gas flow distribution, thereby reducing the pressure difference between the upper and lower sides of the valve plate and thus reducing noise caused by slapping the valve plate. As shown in fig. 10, a vortex V is generated in the intermediate chamber (radially outer portion). Furthermore, according to related experiments, it was demonstrated that the pressure drop of the discharge chamber and the compression chamber can be reduced by about 35% during the gas backflow of the compressor according to the embodiment of the present invention as compared with the related art. Meanwhile, the pressure drop of the new design according to the embodiment of the present invention is increased by only 5% compared to the conventional design during the normal discharge of the compressor. That is, the damping device of the present invention can significantly reduce the pressure difference between the discharge chamber pressure and the compression chamber pressure while maintaining the discharge performance of the discharge valve, thereby reducing noise caused by the impact of the valve plate.
Still referring to fig. 5, the intermediate cavity 11 may advantageously be a rotating cavity (fictive rotating forming cavity) with respect to the general longitudinal central axis L of the vent hole for ease of machining.
Further, in the present application, for convenience of description, the expression referring to the terms "high", "low" or "height" is defined as a height direction along the longitudinal axis of the discharge hole, wherein the direction from the discharge chamber toward the compression chamber along the longitudinal axis is a high-to-low direction. As shown in fig. 5, the lowest point of the intermediate chamber 11 in the direction of the discharge hole longitudinal center axis L from the discharge chamber D toward the compression chamber C extends beyond or is flush with the following plane: the plane is the plane Y perpendicular to the flow direction F of the air flow where the contour of the intermediate chamber 11 intersects the contour of the inlet 13. This makes it easier to create vortex resistance at the lowest point of the intermediate chamber to attenuate the impact of the valve plate and further reduce noise. Meanwhile, the phenomenon that the exhaust performance is reduced due to the fact that the profile of the central cavity is tilted in the exhaust direction and the exhaust resistance is increased during exhaust can be avoided, and therefore the exhaust performance is not affected.
Also, the largest dimension T of the cross section of the intermediate chamber 11 in the gas flow direction F may be larger than the equivalent diameter d of the inlet 13 to ensure that the intermediate chamber 11 has sufficient space to generate a vortex.
According to an aspect of one embodiment of the present invention, referring to fig. 7, the cross-sectional area A2 of the outlet 12 of the exhaust hole perpendicular to the airflow direction F is larger than the cross-sectional area A3 of the inlet 13 perpendicular to the airflow direction F, such that exhaust gas passing through the central chamber 11 from the inlet 13 to the outlet 12 is facilitated, thereby improving exhaust performance. Advantageously, the connection 14 between the intermediate chamber 11 and the outlet 12 may be arranged to allow a gradual transition of the intermediate chamber 11 to the outlet 12, for example, the profile of the cross section of the connection in the gas flow direction F is free of sharp transitions, which may be arcuate or stepped, to further improve the exhaust performance.
According to another aspect of one embodiment of the present invention, referring to fig. 9, the fixed body 10 of the non-orbiting scroll member includes separate first and second body halves 10a and 10b, and the first and second body halves 10a and 10b may be coupled in a threaded connection, for example. The first half body 10a comprises an outlet 12 and a first intermediate cavity 11a, and the second half body 10b comprises an inlet 13 and a second intermediate cavity 11b, wherein the first intermediate cavity 11a and the second intermediate cavity 11b cooperate to form the intermediate cavity 11 when the first half body 10a is connected with the second half body 10 b. Compared with the integral design with high technological requirements on casting parting and machining, the split design of the fixed vortex part is convenient for parting and machining, for example, a numerical control machine tool and other middle cavities are adopted for machining.
According to another embodiment of the present invention, there is provided a discharge valve assembly, see fig. 8, including the above-described damping device, i.e., a non-orbiting scroll, and a discharge valve. The exhaust valve further comprises a valve plate 15, a valve plate 16 and a limiter 17 which are arranged at the outlet 12 of the exhaust hole of the damping device.
Although various aspects of embodiments of the present invention have been described in detail herein, it is to be understood that the invention is not limited to those precise embodiments described and shown herein, and that other modifications and variations may be effected by one skilled in the art without departing from the spirit or scope of the invention. All such modifications and variations are intended to be within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent elements.
Claims (11)
1. Damping device for an exhaust valve in a compressor, characterized in that it comprises a stationary body (10), said stationary body (10) comprising an exhaust orifice in fluid communication with a compression chamber (C) and an exhaust chamber (D), said exhaust orifice comprising an inlet (13), an outlet (12) and an intermediate chamber (11) arranged between said inlet (13) and said outlet (12) in fluid communication with said inlet (13) and said outlet (12), said intermediate chamber (11) being configured to cause a backflow of gas from said exhaust chamber (D) creating a vortex (V) within said intermediate chamber (11),
Wherein the lowest point of the intermediate chamber along the longitudinal centre axis (L) of the discharge orifice, in the direction from the discharge chamber towards the compression chamber, extends beyond the following plane: the plane is a plane (Y) perpendicular to the airflow direction (F) where the contour of the intermediate chamber (11) intersects the contour of the inlet (13).
2. Damping device for an exhaust valve in a compressor according to claim 1, wherein the cross-sectional area (A1) of the intermediate chamber (11) perpendicular to the gas flow direction (F) is larger than the cross-sectional area (A2) of the outlet (12) perpendicular to the gas flow direction (F) and larger than the cross-sectional area (A3) of the inlet (13) perpendicular to the gas flow direction (F).
3. Damping device for an exhaust valve in a compressor according to claim 2, wherein the cross-sectional area (A2) of the outlet (12) is larger than the cross-sectional area (A3) of the inlet (13).
4. A damping device for a discharge valve in a compressor according to any one of claims 1 to 3, wherein the connection (14) between the intermediate chamber (11) and the outlet (12) is arranged to allow a gradual transition of the intermediate chamber (11) to the outlet (12).
5. A damping device for an exhaust valve in a compressor according to any one of claims 1 to 3, wherein the largest dimension (T) of the intermediate chamber (11) in a cross section substantially in the gas flow direction (F) is equal to or larger than the equivalent diameter (d) of the inlet (13).
6. A damping device for an exhaust valve in a compressor according to any one of claims 1 to 3, wherein the fixed body (10) comprises a first half-body (10 a) and a second half-body (10 b) separated, the first half-body (10 a) comprising the outlet (12) and a first intermediate cavity (11 a), the second half-body (10 b) comprising the inlet (13) and a second intermediate cavity (11 b), wherein the first intermediate cavity (11 a) and the second intermediate cavity (11 b) cooperate to form the intermediate cavity (11) when the first half-body (10 a) is connected with the second half-body (10 b).
7. A damping device for a discharge valve in a compressor according to any one of claims 1 to 3, wherein the contour of the intermediate chamber (11) is configured as a contour formed by a curve, by a line segment or by a connection of a curve and a line segment, as seen in a section of the stationary body (10) in the gas flow direction (F).
8. A damping device for a discharge valve in a compressor according to any one of claims 1 to 3, wherein the intermediate chamber (11) is a swivel chamber with the longitudinal centre axis (L) of the discharge orifice as swivel axis.
9. A vent valve assembly, characterized in that it comprises a vent valve and a damping device according to any one of claims 1 to 8, the vent valve comprising a valve plate (15), a valve plate (16) and a stopper (17) arranged at the outlet (12) of a vent hole of the damping device.
10. A compressor is characterized in that, the compressor comprising the discharge valve assembly of claim 9.
11. The compressor of claim 10, being a scroll compressor having a compression mechanism comprising a non-orbiting scroll member and an orbiting scroll member defining the compression chamber therebetween, a base plate of the non-orbiting scroll member forming the fixed body of the damping device of the discharge valve assembly, wherein a discharge orifice of the damping device is disposed at a substantially radial center of the base plate of the non-orbiting scroll member.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810700723.0A CN110657097B (en) | 2018-06-29 | 2018-06-29 | Damping device for exhaust valve in compressor, exhaust valve assembly and compressor |
| US17/256,905 US11493040B2 (en) | 2018-06-29 | 2019-06-21 | Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor |
| PCT/CN2019/092246 WO2020001379A1 (en) | 2018-06-29 | 2019-06-21 | Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor |
| EP19826326.1A EP3816450B8 (en) | 2018-06-29 | 2019-06-21 | Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810700723.0A CN110657097B (en) | 2018-06-29 | 2018-06-29 | Damping device for exhaust valve in compressor, exhaust valve assembly and compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110657097A CN110657097A (en) | 2020-01-07 |
| CN110657097B true CN110657097B (en) | 2024-08-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810700723.0A Active CN110657097B (en) | 2018-06-29 | 2018-06-29 | Damping device for exhaust valve in compressor, exhaust valve assembly and compressor |
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| CN111852873B (en) * | 2020-07-27 | 2022-08-09 | 重庆长安汽车股份有限公司 | Mechanical vacuum pump |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101983288A (en) * | 2008-04-04 | 2011-03-02 | Lg电子株式会社 | Scroll compressor |
| CN105190041A (en) * | 2013-06-27 | 2015-12-23 | 三菱重工业株式会社 | Scroll-type compressor |
| CN208416954U (en) * | 2018-06-29 | 2019-01-22 | 艾默生环境优化技术(苏州)有限公司 | Damping device for exhaust valve in compressor, exhaust valve assembly and compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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