CN113775527B - Compressor and air conditioner - Google Patents
Compressor and air conditioner Download PDFInfo
- Publication number
- CN113775527B CN113775527B CN202111236137.3A CN202111236137A CN113775527B CN 113775527 B CN113775527 B CN 113775527B CN 202111236137 A CN202111236137 A CN 202111236137A CN 113775527 B CN113775527 B CN 113775527B
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- compressor
- valve plate
- pump body
- exhaust port
- equal
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- 238000006073 displacement reaction Methods 0.000 claims abstract description 7
- 238000005096 rolling process Methods 0.000 claims description 8
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 2
- 238000007789 sealing Methods 0.000 claims 1
- 230000001133 acceleration Effects 0.000 description 8
- 238000005299 abrasion Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000010009 beating Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000001788 irregular 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
- F04C29/12—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
-
- 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
-
- 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
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
- F04C2250/102—Geometry of the inlet or outlet of the outlet
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The application provides a compressor and an air conditioner. The compressor comprises a pump body component, wherein the pump body component comprises a valve seat (1), at least two exhaust ports (2) are arranged on the valve seat (1), the areas of the exhaust ports (2) are S1, S2, … … and Sn in sequence, the unit is mm 2, the displacement of the compressor is V, the unit is mm 3, and V/[1000 (S1+S2+ … … +Sn) ]isless than or equal to 1.5. According to the compressor provided by the application, the impact force of slapping the valve seat when the valve plate is closed can be effectively reduced, the noise of the compressor is reduced, and the reliability of the compressor is improved.
Description
Technical Field
The application relates to the technical field of compressors, in particular to a compressor and an air conditioner.
Background
The existing traditional rotary vane compressor has serious abrasion of the sliding vane head and the inner wall of the cylinder, so that the compressor has large mechanical power consumption, poor overall energy efficiency and even causes the reliability problems of abnormal abrasion and the like when the abrasion is serious.
In the related art, a compressor structure is proposed, and by adopting a bearing cylinder structure, the relative sliding of the head part of the sliding vane and the inner wall of the inner ring is ensured to be converted into the rolling motion of the inner ring and the rolling body, so that the mechanical power consumption of the compressor is reduced, and the energy efficiency of the compressor is improved. Because the rolling bearing is used as the cylinder, the exhaust of the compressor cannot be arranged in the radial direction of the cylinder like a traditional sliding vane type compressor, and the exhaust port is arranged in the axial direction of the upper flange and the lower flange.
Because a plurality of exhaust ports are arranged on the flange end face at intervals and are positioned at the middle position in the exhaust process, according to calculation, when the sliding vane sweeps the exhaust ports, the exhaust speed is still higher, and the valve plate is positioned at the position with higher lift.
When the sliding vane sweeps the exhaust port, the pressure Pd of the exhaust cavity in the cavity of the exhaust port is changed into the pressure Pm of the compression cavity, the pressure Pd of the exhaust cavity (the inside of the compressor shell) is outside the cavity, the valve plate is closed under the action of the rigidity of the valve plate and the pressure difference between the inside and the outside of the cavity, and the valve plate is impacted at a larger speed, so that abnormal noise is caused, and even the valve plate is broken and other reliability problems are caused.
Disclosure of Invention
Therefore, the technical problem to be solved by the application is to provide the compressor and the air conditioner, which can effectively reduce the impact force of slapping the valve seat when the valve plate is closed, reduce the noise of the compressor and improve the reliability of the compressor.
In order to solve the problems, the application provides a compressor, which comprises a pump body assembly, wherein the pump body assembly comprises a valve seat, at least two exhaust ports are arranged on the valve seat, the areas of the exhaust ports are S1, S2, … … and Sn in sequence, the unit is mm 2, the displacement of the compressor is V, the unit is mm 3, and V/[1000 (S1+S2+ … … +Sn) ]isless than or equal to 1.5.
Preferably, V/[1000 (S1+S2+ … … +Sn) ]. Gtoreq.0.6.
Preferably, the pump body assembly includes a slide, and the slide projection is capable of completely covering the exhaust port in a projection plane in an axial direction of the pump body assembly when the slide is swept across the exhaust port.
Preferably, when the sliding vane sweeps the exhaust port, the width of the exhaust port along the thickness direction of the sliding vane is a, and the thickness of the sliding vane is L, wherein a is less than or equal to L-0.5mm.
Preferably, the pump body assembly further comprises a valve plate and a lift limiter, the valve plate can seal the exhaust port, the lift limiter and the valve plate are fixed on the valve seat, and the lift of the lift limiter is h which is less than or equal to 2mm.
Preferably, the pump body assembly further comprises a valve plate and a lift limiter, the valve plate can seal the exhaust port, the lift limiter and the valve plate are fixed on the valve seat, the lift of the lift limiter is h, the perimeter of the exhaust port is fi, the area of the exhaust port is Si, i=1, 2, … … and n, and the ratio of fi to h/Si is 1.15 or less.
Preferably, the shape of the exhaust port is circular, rectangular, diamond-shaped, trapezoidal or oval.
Preferably, the pump body assembly further comprises a plurality of sliding sheets and rollers, each sliding sheet can be slidably arranged on each roller, and the sliding sheets are uniformly distributed along the circumference of each roller.
Preferably, the pump body assembly further comprises a sliding vane and a bearing cylinder, wherein the bearing cylinder comprises an inner ring, rolling bodies and an outer ring, and the sliding vane is abutted on the inner peripheral wall of the inner ring.
Preferably, the rigidity of the valve plate is K, the unit is N/mm, and K is more than or equal to 3 and less than or equal to 10.
Preferably, K is 3.5.ltoreq.6.
According to another aspect of the present application, there is provided an air conditioner including a compressor, which is the above-mentioned compressor.
The application provides a compressor, which comprises a pump body component, wherein the pump body component comprises a valve seat, at least two exhaust ports are arranged on the valve seat, the areas of the exhaust ports are S1, S2, … … and Sn in sequence, the unit is mm 2, the displacement of the compressor is V, the unit is mm 3, and the V/[1000 (S1+S2+ … … +Sn) ] is less than or equal to 1.5. The compressor limits the overall exhaust speed of the compressor through the relation between the displacement and the exhaust port, thereby reducing the exhaust speed when the exhaust port is closed, reducing the opening height of the valve plate when the valve plate starts to be closed, reducing the impact force of the valve plate on the flange valve seat when the valve plate is closed, reducing the noise of the compressor and improving the reliability of the compressor.
Drawings
FIG. 1 is a schematic view showing a structure of a compressor according to an embodiment of the present application;
FIG. 2 is a schematic view showing a structure of a discharge port of a compressor according to an embodiment of the present application;
FIG. 3 is a schematic view illustrating a structure of a discharge port of a compressor according to an embodiment of the present application;
FIG. 4 is a schematic view showing a structure of a discharge port of a compressor according to an embodiment of the present application;
FIG. 5 is a schematic view showing the structure of a valve seat of a compressor according to an embodiment of the present application;
FIG. 6 is a structural dimension of a discharge valve plate of a compressor according to an embodiment of the present application;
FIG. 7 is a structural dimension of a discharge valve plate of a compressor according to an embodiment of the present application;
FIG. 8 is a time domain diagram of compressor shell vibration acceleration at different rigidities for a discharge valve plate of a compressor in accordance with one embodiment of the present application;
fig. 9 is a graph showing noise comparison between a related art compressor and a compressor according to an embodiment of the present application at different frequencies.
The reference numerals are expressed as:
1. a valve seat; 2. an exhaust port; 3. a sliding sheet; 4. a valve plate; 5. a lift limiter; 6. a roller; 7. and a bearing cylinder.
Detailed Description
Referring to fig. 1 to 9 in combination, according to an embodiment of the present application, a compressor includes a pump body assembly, the pump body assembly includes a valve seat 1, at least two exhaust ports 2 are provided on the valve seat 1, the areas of the exhaust ports 2 are S1, S2, … …, sn in sequence, the unit is mm 2, the displacement of the compressor is V, the unit is mm 3, wherein V/[1000 (s1+s2+ … … +sn) ] is less than or equal to 1.5.
Generally, the smaller the exhaust speed of the exhaust port 2, the smaller the impact force of the air flow on the head of the valve plate 4, the smaller the force required to overcome the rigidity of the valve plate 4 itself, and the smaller the opening height of the valve plate 4 within the limit range of the lift limiter 5. Based on the characteristics, the compressor of the embodiment of the application limits the overall exhaust speed of the compressor through the relation between the displacement V and the area S of the exhaust port, thereby reducing the exhaust speed when the exhaust port 2 starts to be closed, and reducing the actual opening height of the valve plate 4 when the exhaust port 2 starts to be closed because the actual height of the valve plate 4 starts to be closed is related to the exhaust speed when the sliding vane 3 sweeps the exhaust port 2, reducing the impact force acting on the valve seat 1 when the valve plate 4 closes the exhaust port 2, reducing the noise of the compressor and improving the reliability of the compressor.
In one embodiment, V/[1000 (s1+s2+ … … +sn) ] ∈0.6, so that the number of exhaust ports 2 can be reduced, the clearance volume can be reduced, and the working energy efficiency of the compressor can be improved.
In one embodiment, the pump body assembly further comprises a sliding vane 3, when the sliding vane 3 sweeps the exhaust port 2, in the projection plane of the pump body assembly in the axial direction, the projection of the sliding vane 3 can completely cover the exhaust port 2, so that when the sliding vane 3 sweeps the exhaust port 2, the front cavity and the rear cavity of the cylinder of the pump body assembly of the compressor can be prevented from generating air leakage, and the compressor energy efficiency is effectively improved.
In one embodiment, when the sliding vane 3 sweeps the exhaust port 2, the width of the exhaust port 2 along the thickness direction of the sliding vane 3 is a, the thickness of the sliding vane 3 is L, a is less than or equal to L-0.5mm, and on the basis of considering processing and assembly errors, the cross air of the front cavity and the rear cavity of the air cylinder can be effectively avoided, and the operation reliability of the compressor is improved.
In one embodiment, the pump body assembly further comprises a valve plate 4 and a lift limiter 5, the valve plate 4 can seal the exhaust port 2, the lift limiter 5 and the valve plate 4 are fixed on the valve seat 1, the lift of the lift limiter 5 is h which is less than or equal to 2mm, so that the lifting height of the valve plate 4 can be limited, the acceleration distance when the valve plate 4 starts to be closed is reduced, the slapping acting force of the valve plate 4 on the valve seat 1 is reduced, the noise of the compressor is reduced, and the reliability of the compressor is improved.
In one embodiment, the pump body assembly further comprises a valve plate 4 and a lift limiter 5, the valve plate 4 can seal the exhaust port 2, the lift limiter 5 and the valve plate 4 are fixed on the valve seat 1, the lift of the lift limiter 5 is h, the perimeter of the exhaust port 2 is fi, the area of the exhaust port 2 is Si, i=1, 2, … … and n, wherein 1.15 is less than or equal to fi is h/Si is less than or equal to 1.5. In this embodiment, since the exhaust gas needs to be discharged through the axial space between the head of the valve plate 4 and the valve seat 1 after passing through the exhaust port 2, the area of the exhaust port 2 needs to be utilized as much as possible in order to reduce the exhaust loss, and therefore the exhaust area of the axial space between the head of the valve plate 4 and the valve seat 1 is larger than the area of the exhaust port 2, by the above definition, the condition can be effectively satisfied, so that the exhaust loss is effectively controlled. For the limitation that fi/Si is less than or equal to 1.15 and less than or equal to 1.5, the lower limit is to ensure that the flow area of the valve plate 4 is larger than the area of the exhaust port 2 after being opened, and the upper limit is mainly to limit the height h, so that the valve plate 4 is prevented from being too high in lift, the valve plate 4 is slapped from a higher position, the running acceleration path is increased, and the impact force for slapping the valve seat 1 is increased.
In one embodiment, the shape of the exhaust port 2 is circular, rectangular, diamond-shaped, trapezoidal, or oval. The shape of the exhaust port 2 may be an irregular shape composed of a line segment and a curve.
In one embodiment, the pump body assembly further comprises a plurality of sliding sheets 3 and rollers 6, each sliding sheet 3 is slidably arranged on each roller 6, and the sliding sheets 3 are uniformly distributed along the circumference of each roller 6.
In one embodiment, the pump body assembly further comprises a sliding vane 3 and a bearing cylinder 7, wherein the bearing cylinder 7 comprises an inner ring, rolling bodies and an outer ring, and the sliding vane 3 is abutted on the inner peripheral wall of the inner ring. The bearing cylinder 7 is used as a cylinder, so that the relative sliding of the head part of the sliding vane 3 and the inner wall of the inner ring can be ensured to be changed into the rolling motion of the inner ring and the rolling body, thereby reducing the mechanical power consumption of the compressor and improving the energy efficiency of the compressor.
In one embodiment, the pump body assembly further comprises a valve plate 4, the valve plate 4 can seal the exhaust port 2, the rigidity of the valve plate 4 is K, the unit is N/mm, the elastic modulus of the material is E, the unit is N/mm 2, the waist width is b, the unit is mm, the thickness is t, the unit is mm, the effective length is l, the unit is mm, K=Eb×t≡3/(4×l≡3), and K is not more than 3 and not more than 10.
Preferably, K is 3.5.ltoreq.6.
The greater the rigidity K of the valve plate is, the greater the slapping force generated by the rigidity of the valve plate is; the smaller the rigidity is, the smaller the slapping force generated by the self rigidity is, but the higher the actual lift of the exhaust valve plate before closing at the same exhaust speed is, the longer the accelerating path before the valve plate impacts (slaps) the valve seat is, and the generated impact force is still larger. Therefore, the optimal range exists in K, the self-slapping force and the actual lift of the valve plate before closing can be considered, so that the slapping force of the valve plate 4 slapping from a high position can be reduced simultaneously under the condition of reducing the lift height of the valve plate 4, the impact force of the valve plate 4 on the valve seat 1 during closing is reduced more effectively, the noise of the compressor is reduced, and the reliability of the compressor is improved.
The rigidity of the valve plate can influence the actual lift (height) of the valve plate when the valve plate is closed, and meanwhile, the force generated by the rigidity of the valve plate can also be influenced, so that the force of the valve plate beating the valve seat is influenced. The greater the force of the slapping valve seat, the greater the vibration of the pump body will be, and the vibration transmitted to the outside of the compressor shell will be, resulting in the greater vibration of the compressor shell, and the greater the vibration acceleration and noise will be. Therefore, the stiffness of the valve plate affects the vibration acceleration and noise of the compressor housing.
Referring to FIG. 8, it can be seen that when K is 3.ltoreq.10, the slapping force generated by the stiffness of the valve plate and the slapping force caused by lift acceleration increase moderately, and the vibration acceleration finally reflected to the compressor shell is lower. Further, when K is more than or equal to 3.5 and less than or equal to 6, the vibration acceleration of the shell is minimum.
As can be seen from fig. 9, after the compressor according to the embodiment of the present application is adopted, compared with the compressor in the related art, the noise is reduced by 2dB at least when the compressor is operated at a frequency above 30Hz, and the noise reduction amplitude is more remarkable as the operating frequency is higher, so that the vibration noise of the compressor can be effectively reduced by adopting the compressor according to the embodiment of the present application.
According to an embodiment of the present application, an air conditioner includes a compressor, which is the compressor described above.
It will be readily appreciated by those skilled in the art that the above advantageous ways can be freely combined and superimposed without conflict.
The foregoing description of the preferred embodiments of the application is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the application. The foregoing is merely a preferred embodiment of the present application, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present application, and these modifications and variations should also be regarded as the scope of the application.
Claims (10)
1. The compressor is characterized by comprising a pump body assembly, wherein the pump body assembly comprises a valve seat (1), at least two exhaust ports (2) are arranged on the valve seat (1), the areas of the exhaust ports (2) are S1, S2, … … and Sn in sequence, the unit is mm, the displacement of the compressor is V, the unit is mm, and V/[1000 (S1+S2+ … … +Sn) ] is more than or equal to 0.6 and less than or equal to 1.5;
The pump body assembly further comprises a valve plate (4) and a lift limiter (5), the valve plate (4) can be used for sealing the exhaust port (2), the lift limiter (5) and the valve plate (4) are fixed on the valve seat (1), the lift of the lift limiter (5) is h, the perimeter of the exhaust port (2) is fi, the area of the exhaust port (2) is Si, i=1, 2, … … and n, and 1.15 is less than or equal to fi h/Si is less than or equal to 1.5.
2. The compressor according to claim 1, characterized in that the pump body assembly further comprises a slide (3), the slide (3) being projected to cover the exhaust port (2) completely in a projection plane of the pump body assembly in an axial direction when the slide (3) sweeps across the exhaust port (2).
3. The compressor according to claim 2, wherein the width of the exhaust port (2) in the thickness direction of the slide sheet (3) is a, and the thickness of the slide sheet (3) is L, a is less than or equal to L-0.5mm.
4. Compressor according to claim 1, characterized in that the lift h of the lift limiter (5) satisfies: h is less than or equal to 2mm.
5. The compressor according to claim 1, characterized in that the shape of the discharge port (2) is circular, rectangular, diamond-shaped, trapezoidal or oval.
6. The compressor of claim 1, wherein the pump body assembly further comprises a plurality of vanes (3) and rollers (6), each vane (3) being slidably disposed on a roller (6), the plurality of vanes (3) being uniformly distributed along a circumferential direction of the roller (6).
7. The compressor of claim 1, wherein the pump body assembly further comprises a slide (3) and a bearing cylinder (7), the bearing cylinder (7) comprising an inner ring, rolling bodies and an outer ring, the slide (3) abutting on an inner peripheral wall of the inner ring.
8. The compressor according to claim 1, characterized in that the stiffness of the valve plate (4) is K, in N/mm, 3.ltoreq.k.ltoreq.10.
9. The compressor according to claim 8, it is characterized in that the method comprises the steps of, K is more than or equal to 3.5 and less than or equal to 6.
10. An air conditioner comprising a compressor, wherein the compressor is the compressor of any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111236137.3A CN113775527B (en) | 2021-10-22 | 2021-10-22 | Compressor and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111236137.3A CN113775527B (en) | 2021-10-22 | 2021-10-22 | Compressor and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113775527A CN113775527A (en) | 2021-12-10 |
| CN113775527B true CN113775527B (en) | 2024-08-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111236137.3A Active CN113775527B (en) | 2021-10-22 | 2021-10-22 | Compressor and air conditioner |
Country Status (1)
| Country | Link |
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| CN (1) | CN113775527B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107542658A (en) * | 2017-09-29 | 2018-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and there is its air conditioner |
| CN110953152A (en) * | 2019-11-25 | 2020-04-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressors and Air Conditioners |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4778772B2 (en) * | 2005-10-26 | 2011-09-21 | 日立アプライアンス株式会社 | Rotary compressor |
| CN109026696B (en) * | 2018-09-25 | 2023-07-28 | 珠海格力电器股份有限公司 | Compressor pump body, compressor and air conditioner |
| CN112324660B (en) * | 2020-10-09 | 2021-10-15 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
| CN214036129U (en) * | 2020-12-03 | 2021-08-24 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotor compressor and air conditioner with same |
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2021
- 2021-10-22 CN CN202111236137.3A patent/CN113775527B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107542658A (en) * | 2017-09-29 | 2018-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and there is its air conditioner |
| CN110953152A (en) * | 2019-11-25 | 2020-04-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressors and Air Conditioners |
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| CN113775527A (en) | 2021-12-10 |
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