CN109899321A - It can be effectively reduced the compressor of blade harmonic noise - Google Patents
It can be effectively reduced the compressor of blade harmonic noise Download PDFInfo
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- CN109899321A CN109899321A CN201910297244.3A CN201910297244A CN109899321A CN 109899321 A CN109899321 A CN 109899321A CN 201910297244 A CN201910297244 A CN 201910297244A CN 109899321 A CN109899321 A CN 109899321A
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Abstract
The invention belongs to turbocharger apparatus technical fields, are related to a kind of compressor that can be effectively reduced blade harmonic noise, and the compressor includes a compressor casing, and the pressure impeller being rotatably dispose in the compressor casing；The interior surface of the compressor casing constitutes the axial admission road of compressor, and axial admission road includes at least one annular groove, and the axial admission road is formed on compressor casing, and it is axial axially parallel with pressure impeller；The annular groove is set to axial admission road inner wall, to reduce noise when work.Product of the present invention is simple and reasonable for structure, by processing annular groove in the axial admission road of compressor casing, when in use, operating noise can be effectively reduced.
Description
Technical field
The invention belongs to turbocharger apparatus technical fields, are related to a kind of pressure that can be effectively reduced blade harmonic noise
Mechanism of qi.
Background technique
As shown in Figure 1, compressor 10 includes a pressure impeller 12, pressure impeller 12 includes multiple blades 14, and pressure impeller 12 fills
It fits over for rotating in rotary shaft 16, while impeller 12 being pressed to be placed in compressor casing 18.There is an axis on compressor casing 18
To air intake duct 22.The axial admission road 22 of rotary shaft 16 and compressor casing 18 is concentric.Compressor casing 18 equally contains radial expansion
The diffuser 26 and runner 24 of exhibition, two feature distributions are on the endless belt centered on axial admission road 22.Diffuser 26
And runner 24 is distributed with one heart, while radially tangential.Runner 24 is connected with blower outlet.It, will by pressing the rotation of impeller 12
Air-flow is sucked from the axial admission road 22 of compressor casing 18, is then transported to compressed gas by diffuser 26 and runner 24
On the components being connected with compressor casing outlet.
One application of compressor is turbocharger.It is well known that turbocharger, which is one, provides pressure for internal combustion engine
Power is greater than the device of the compressed gas of atmospheric pressure (pressurization).Traditional turbocharger includes turbine wheel shaft, and turbine wheel shaft is by starting
The exhaust gas driven of machine, the downstream in enmgine exhaust, and link together with rotary shaft.Pressure impeller is connected to rotation
The other end of axis, bring is the result is that engine is rotated by the exhaust gas-driven turbine that exhaust manifold is discharged, due to turbine and pressure
Impeller is coaxially connected, and the rotation band dynamic pressure impeller of turbine is rotated around rotary shaft same direction.Compressor presses leaf under this application
Compressed gas is transported to motor intake manifold by wheel.
Such as Fig. 1, each blade 14 is connected to pressure impeller 12 from 36 radial outward expansion of root to vane tip 34
Wheel hub 38 on.Each blade 14 includes a leading edge 40 and trailing edge 42, and in practical applications, leading edge 40 is in axial admission
Rotation in road 22, trailing edge 42 are rotated in the inlet of diffuser.The curved distribution of vane tip 34 of each blade 14, simultaneously
Leading edge 40 is connected with trailing edge 42.In practical applications, the intermediary of the inswept compressor casing 18 of vane tip 34 of each blade 14
Curved surface 44, intermediary Surface 44 are defined on the centre in axial admission road 22 and diffuser 26.Intermediary Surface 44 and each blade 14
Vane tip 34 possess complementary curve form.
Axial admission road passes through nozzle portion 22a and conduit portion 22b.Conduit portion 22b is connected axially to spout portion
Divide 22a.Nozzle portion 22a and conduit portion 22b meet at a little 45.
When air-flow flows through compressor 10, acoustic pressure wave will be generated.The amplitude of acoustic pressure wave depends on blade 14 and passes through
Frequency, there are also the acoustic pressure wave of other different frequencies, but the acoustic pressure wave that passes through of blade occupy in compressor it is very big
Specific gravity.The generation of acoustic pressure wave is made derived from interaction of the air-flow between the pressure impeller 12 of rotation and static compressor casing 18
With.The frequency of acoustic pressure wave depends on the speed of pressure impeller 12 and the quantity of blade 14.Acoustic pressure wave can generate noise,
This noise is particularly evident near compressor 10.
Charge air flow is substantially equally distributed in each section in axial admission road 22, this, which is also resulted in, is calming the anger
Each acoustic pressure wave generated in machine 10 is same phase with remaining acoustic pressure wave, and the identical acoustic pressure wave of every kind of phase is mutual
Superposition causes the increase of acoustic pressure wave amplitude, and then leads to the intensity of blade Rotation Noise.
It is reported that the reduction measure for determining frequency noise is typically applied on compressor 10, as inlet port noise reduction, the ratio that is
Relatively effectively reduce the measure of blade Rotation Noise.Intake muffler (absorption or dissipation noise energy) can be mounted in air inlet
On 22, outside compressor 18, the intensity of rotating vane noise can be reduced.Intake muffler generally includes sound-absorbing material or more
Hole tubular structure and shell mechanism.This silencer is more expensive, and usually requires to occupy biggish space.
Summary of the invention
The present invention is in view of the above-mentioned problems, provide a kind of compressor that can be effectively reduced blade harmonic noise, the pressure shell knot
The noise of compressor can be effectively reduced in structure.
Technical solution according to the invention: a kind of compressor can be effectively reduced blade harmonic noise, the compressor
Comprising a compressor casing, and the pressure impeller being rotatably dispose in the compressor casing；It is characterized in that: the compressor casing
Interior surface constitutes the axial admission road of compressor, and axial admission road includes at least one annular groove, and the axial admission road is formed
In on compressor casing, and its it is axial with press impeller axially parallel；The annular groove is set to axial admission road inner wall, to reduce work
When noise.
As a further improvement of the present invention, the annular groove has the groove depth radially extended along axial admission road, groove depth
Radial inner end be axial admission road inner wall, the radial outer end of groove depth is placed in the outer wall radially inner side in axial admission road.
As a further improvement of the present invention, the annular groove is circumferentially having a fixed profile.
As a further improvement of the present invention, the annular groove is in the profile for circumferentially having a variation.
As a further improvement of the present invention, the depth of the annular groove is in the numerical value that radial direction is variation.
As a further improvement of the present invention, the annular groove includes import, and the inner surface radial direction of import and compressor casing
Alignment.
As a further improvement of the present invention, the longitudinal profile of the annular groove is rectangular-shaped.
As a further improvement of the present invention, what the outer apex angle and interior apex angle of the rectangular configuration of the annular groove were respectively formed turns
Angle is arc shape.
As a further improvement of the present invention, rectangular-shaped annular groove includes annular groove sealing surface and two axially opposing first
Side wall surface, second side wall surface, the import are formed by the space between the first side wall face, second side wall surface.
As a further improvement of the present invention, the size formula of the annular groove are as follows:
Sb is the area of annular groove import 50a, passes through formula: Sb=π diH is calculated, and wherein di is leading for axial admission road
The diameter of tube portion, h are the axial length of annular groove；
S is the sectional area in axial admission road, passes through formula:It is calculated；
L is the depth of annular groove, passes through formula:It obtains, wherein dg is the diameter of the closed surface of annular groove；
K is a coefficient, passes through formulaIt is calculated, wherein ω is the frequency of the sound wave in compressor, and c is pressure
The size of the velocity of sound in mechanism of qi.
As a further improvement of the present invention, 4 decibels of noise reduction when the compressor works.
As a further improvement of the present invention, the annular groove is set between the outer end face in axial admission road and pressure impeller.
As a further improvement of the present invention, the pressure impeller includes admission edge, and annular groove is set to axial admission road
Between outer end face and the end of admission edge.
As a further improvement of the present invention, the axial admission road includes conduit portion and is integrally connected to the conduit
The nozzle portion of portion of its outer, annular groove are set to conduit portion.
As a further improvement of the present invention, the nozzle portion is located at the axial outer end in the axial admission road of compressor casing
Place.
As a further improvement of the present invention, a plurality of annular groove is arranged in the inner wall in the axial admission road.
As a further improvement of the present invention, the axial length of the annular groove is between 5 millimeters to 45 millimeters.
As a further improvement of the present invention, the depth of the annular groove is between 5 millimeters to 10 millimeters.
As a further improvement of the present invention, the diameter in the axial admission road is between 30 millimeters to 50 millimeters.
As a further improvement of the present invention, the axial length of the annular groove and the ratio of depth are between 1:1 to 5:1.
As a further improvement of the present invention, the ratio of the axial length of the diameter and annular groove in the axial admission road is 1:
1 between 5:1.
As a further improvement of the present invention, the ratio of the depth of the diameter and annular groove in the axial admission road is arrived in 4:1
Between 25:1.
The invention also discloses a kind of turbocharger, including be connected to rotary shaft one end whirlpool end and above-mentioned compressor,
Pressure impeller is connected to the other end with the opposed rotary shaft of turbine.
The technical effects of the invention are that: product of the present invention is simple and reasonable for structure, passes through the axial admission in compressor casing
Annular groove is processed in road, when in use, operating noise can be effectively reduced.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of existing product.
Fig. 2 is structural schematic diagram of the invention.
Fig. 3 is the partial enlarged view in Fig. 2 at B.
Fig. 4 is sectional view along A-A in Fig. 2.
Specific embodiment
A specific embodiment of the invention is further described with reference to the accompanying drawing.
In Fig. 1~4, including compressor 10, pressure impeller 12, blade 14, rotary shaft 16, compressor casing 18, axial admission road
22, nozzle portion 22a, conduit portion 22b, runner 24, diffuser 26, compressor casing inner surface 28, pressure shell import 32, blade point
End 34, root 36, wheel hub 38, leading edge 40, trailing edge 42, intermediary Surface 44, annular groove 50 etc..
As shown in figs. 2 to 4, the present invention is a kind of compressor that can be effectively reduced blade harmonic noise, including compressor
Shell 18；Pressure shell import 32 is arranged in compressor casing 18, corresponds on compressor casing 18 and is coaxially disposed axial admission at pressure shell import 32
Road 22, axial admission road 22 is by compressor casing inner surface 28, in the internal stretch to compressor casing 18 in axial admission road 22
At chamber extension.The nozzle portion 22a and conduit portion 22b in axial admission road 22 including integrally connected, conduit portion 22b are from jet pipe
Part 22a is to 18 internal stretch of compressor casing.The radial diameter of the corresponding compressor casing inner surface 28 of nozzle portion 22a is with axis
Linearly reduce, table in the corresponding compressor casing of conduit portion 22b to the expansion of distance (internally being extended from pressure shell import 32)
The radial diameter in face 28 is remained unchanged with the expansion of axial distance (internally extending from pressure shell import 32).In other implementations
In example, axial admission road 22 only can include conduit portion 22b according to specifically used environment needs, in this case, it is axial into
The radial diameter of the corresponding compressor casing inner surface 28 of air flue 22 remains unchanged in entire axial length.
As shown in Fig. 2, annular groove 50 is arranged in 22 inner wall of axial admission road, annular groove 50 radially has a fixed profile or edge
Radial direction has the profile of a variation, and when annular groove 50 is radially fixed profile, the depth of annular groove 50 radially is fixed value,
When annular groove 50 is radially the profile of variation, the depth of annular groove 50 radially is the numerical value of variation.
In specific works, the function of annular groove 50 is similar to side resonator, for reducing the sound in compressor 10.Annular groove
50 effect is to upset the air-flow for passing through axial admission road 22, so that air-flow is divided into Liang Ge branch, what this two strands of air-flows generated
Sound wave difference phase.And then have the function that reduce magnitude of sound.The most ideal situation is that the phase of the sound wave generated by annular groove 50
The phase difference for the sound wave that position is generated with the air-flow by axial admission road 22 is 180 degree, can farthest be subtracted in this case
The amplitude of small superimposed sound wave.
The position of annular groove 50 is a cyclic structure on axial admission road 22, and can extend to axial admission road
22 whole circumference.The diameter of annular groove 50 is bigger than the diameter of compressor casing inner surface 28, and is less than compressor casing inner surface 28
The diameter of corresponding compressor casing outer surface 29.Therefore, the depth L of annular groove 50 is smaller than the import wall thickness of compressor casing 18, pressure
The import wall thickness of mechanism of qi shell 18 refers to the distance between compressor casing inner surface 28 and compressor casing outer surface 29.The axis of annular groove 50
It is less than the length in axial admission road 22 to length L, is specifically the leading edge from pressure shell import 32 to the blade 14 of pressure impeller 12
40.In other embodiments, the length of annular groove 50 may arrive pressure impeller with the interface point 45 of nozzle portion 22a and conduit portion 22b
The leading edge 40 of 12 blade 14 is equidistant, and specifically, 50 axial length of annular groove can achieve 140 millimeters.It is specific again
It says, the axial length of annular groove 50 is usually 5 millimeters to 45 millimeters, it is also desirable to 5 millimeters to 15 millimeters, such as 10 millimeters.
It is of course also possible to be 30 millimeters to 45 millimeters, at 42 millimeters or so, such as 41.65 millimeters.
As shown in figure 3, the section of annular groove 50 is rectangle.Annular groove 50 includes import 50a, closed surface 50b and the first side
Wall surface 50c and second side wall surface 50d.The turning 52 of annular groove 50 is a curved surface features, be by compressor casing inner surface 28 and
The first side wall face 50c and second side wall surface 50d are formed, and are also possible to the first side wall face 50c and second side wall surface 50d and closing is bent
Face 50b composition.The size at turning 52 is usually related with the size of annular groove 50, in order to provide the effect of optimal reduction noise.?
In the example illustrated, annular groove 50 is a uniform cyclic structure.Alternatively, in other instances, the section of annular groove 50
It can not be uniform cyclic structure.The shape of the depth L of annular groove 50, axial length h or an entire circle, can become
Change.
As shown in Fig. 2, having an annular groove 50 on axial admission road 22.In other instances, on axial admission road 22
The quantity of annular groove 50 is unlimited, can be for 2,3,4 or more.Each annular groove 50 can have identical profile, can also
With different.
The method is mainly characterized in that the annular groove 50 on compressor 10, main function is the leaf reduced in compressor 10
Piece harmonic noise, this reduction amount are also referred to as insertion loss.The calculation method application of insertion loss is quarter-wave original
Reason.In general, a quarter silencer includes a side slot, this slot is connected on main air flow passage, and a T-type is formed
Shape.It is by quarter-wave formula in the calculating of the insertion loss of quarter-wave silencer:
The annular groove 50 that the application of quarter-wave formula can permit on axial admission road 22 has unused shape, without
It is that a side slot is connected on main air flow passage.In figs. 3 and 4, some variables can be found:
The size formula of the annular groove 50 are as follows:
Sb is the area of annular groove import 50a, passes through formula: Sb=π diH is calculated, and wherein di is axial admission road 22
The diameter of conduit portion 22b, h are the axial length of annular groove 50；
S is the sectional area in axial admission road 22, passes through formula:It is calculated；
L is the depth of annular groove 50, passes through formula:It obtains, wherein dg is the closed surface 50b of annular groove 50
Diameter；
K is a coefficient, passes through formulaIt is calculated, wherein ω is the frequency of the sound wave in compressor 10, and c is
The size of the velocity of sound in compressor；
IL is insertion loss.
Typically, the rotation speed of compressor is 80000 revolutions per minute to 190000 revolutions per minute.The axial length h of annular groove
It can be up to 140 millimeters, such as 5 millimeters to 45 millimeters or 10 millimeters to 35 millimeters.In other instances, axial annular groove
Axial length can be 5 millimeters to 15 millimeters, such as 10 millimeters；Or 30 millimeters to 45 millimeters, it is acted at 42 millimeters, such as
41.65 millimeters.The depth L of annular groove can be 30 millimeters maximum.It further illustrates, the depth L of annular groove L can be 5 millimeters to 10 millis
Rice, for example, 7 millimeters；Or 7 millimeters to 9 millimeters, for example, 8.85 millimeters.The diameter d of conduit portioniIt can be arbitrary value, most
It is 180 millimeters big.It further illustrates, the diameter d of conduit portioniCan be between 30 millimeters to 50 millimeters, such as 41.8 millimeters.Ring
Ratio (h:L) between the axial length h of slot and the depth L coefficient of annular groove is between 1:1 to 5:1.It further illustrates, this ratio
Value can be between 2:1 to 4:1, for example, 1.43:1 or 4.71:1.The diameter d of conduit portioniWith annular groove axial length h's
Ratio (di: h) between 1:1 to 5:1.Further illustrate, this coefficient can between 1:1 to 2:1, for example, 1.27:1. or
Person is between 3:1 to 4.5:1, for example, 4.18:1.The diameter d of conduit portioniRatio (d between the depth L coefficient of annular groovei:
L) between 4:1 to 25:1.It further illustrates, this coefficient can be 5:1 to 10:1, such as 5.97:1；Or it is arrived in 10:1
15:1, then 15:1 to 20:1, for example, 19.67:1.
Using the compressor of this patent structure, 85% blade harmonic noise can be lowered, and averagely reduction amplitude is 4 points
Shellfish.31% blade harmonic noise can be lowered 6 decibels.In the operating condition of 140000 revolutions per minute of revolving speed, maximum amplitude can
To reduce by 11 decibels.
Claims (23)
1. a kind of compressor that can be effectively reduced blade harmonic noise, the compressor includes a compressor casing, Yi Jizhuan
The dynamic pressure impeller (12) being set in the compressor casing (18)；It is characterized by: the interior surface of the compressor casing is constituted
The axial admission road of compressor, axial admission road include at least one annular groove, and the axial admission road (22) is formed in compressor
On shell (18), and it is axial axial parallel with pressure impeller (12)；The annular groove (50) is set to axial admission road (22) inner wall, with
Reduce noise when work.
2. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) there is the groove depth radially extended along axial admission road (22), the radial inner end of groove depth is the interior of axial admission road (22)
Wall, the radial outer end of groove depth are placed in the outer wall radially inner side in axial admission road (22).
3. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 1 or 2, it is characterised in that: the ring
Slot (50) is circumferentially having a fixed profile.
4. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 1 or 2, it is characterised in that: the ring
Slot (50) is in the profile for circumferentially having a variation.
5. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 4, it is characterised in that: the annular groove
(50) depth is in the numerical value that radial direction is variation.
6. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
It (50) include import (50a), and import (50a) is aligned with the inner surface radial direction of compressor casing (18).
7. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 6, it is characterised in that: the annular groove
(50) longitudinal profile is rectangular-shaped.
8. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 7, it is characterised in that: the annular groove
(50) turning (52) that the outer apex angle and interior apex angle of rectangular configuration are respectively formed is arc shape.
9. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 7, it is characterised in that: rectangular-shaped ring
Slot (50) includes annular groove sealing surface (50b) and two axially opposing the first side wall faces (50c), second side wall surfaces (50d), described
Import (50a) is formed by the space between the first side wall face (50c), second side wall surface (50d).
10. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) size formula are as follows:
Sb is the area of annular groove import (50a), passes through formula: Sb=π diH is calculated, and wherein di is axial admission road (22)
The diameter of conduit portion 22b, h are the axial length of annular groove (50)；
S is the sectional area of axial admission road (22), passes through formula:It is calculated；
L is the depth of annular groove (50), passes through formula:It obtains, wherein dg is the closed surface of annular groove (50)
The diameter of (50b)；
K is a coefficient, passes through formulaIt is calculated, wherein ω is the frequency of the sound wave in compressor 10, and c is to calm the anger
The size of the velocity of sound in machine.
11. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: described to calm the anger
4 decibels of noise reduction when machine works.
12. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) it is set between the outer end face in axial admission road (22) and pressure impeller (12).
13. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 12, it is characterised in that: the pressure leaf
Taking turns (12) includes admission edge (40), and annular groove (50) is set to the outer end face in axial admission road (22) and the end of admission edge (40)
Between end.
14. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the axial direction
Air intake duct (22) includes conduit portion (22b) and the nozzle portion (22a) for being integrally connected to the outer end the conduit portion (22b),
Annular groove (50) is set to conduit portion (22b).
15. can be effectively reduced the compressor of blade harmonic noise as claimed in claim 14, it is characterised in that: the jet pipe
Partially (22a) is located at the axial outer end in axial admission road (22) of compressor casing (18).
16. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the axial direction
A plurality of annular groove (50) is arranged in the inner wall of air intake duct (22).
17. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) axial length is between 5 millimeters to 45 millimeters.
18. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) depth is between 5 millimeters to 10 millimeters.
19. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the axial direction
Diameter (the d of air intake duct (22)i) between 30 millimeters to 50 millimeters.
20. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the annular groove
(50) ratio (h:L) of axial length (h) and depth (L) is between 1:1 to 5:1.
21. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the axial direction
Diameter (the d of air intake duct (22)i) ratio (d with the axial length (h) of annular groovei: h) between 1:1 to 5:1.
22. can be effectively reduced the compressor of blade harmonic noise as described in claim 1, it is characterised in that: the axial direction
Diameter (the d of air intake duct (22)i) and annular groove depth (L) ratio between 4:1 to 25:1.
23. a kind of turbocharger, it is characterised in that: including being connected to the whirlpool end of rotary shaft (16) one end and such as claim 1
The compressor, pressure impeller (12) are connected to the other end with the opposed rotary shaft of turbine (16).
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910297244.3A CN109899321A (en) | 2019-04-15 | 2019-04-15 | It can be effectively reduced the compressor of blade harmonic noise |
| GB2116009.8A GB2597185B (en) | 2019-04-15 | 2020-04-15 | Compressor |
| US17/604,193 US12031552B2 (en) | 2019-04-15 | 2020-04-15 | Compressor |
| PCT/CN2020/084985 WO2020211788A1 (en) | 2019-04-15 | 2020-04-15 | Compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910297244.3A CN109899321A (en) | 2019-04-15 | 2019-04-15 | It can be effectively reduced the compressor of blade harmonic noise |
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| Publication Number | Publication Date |
|---|---|
| CN109899321A true CN109899321A (en) | 2019-06-18 |
Family
ID=66954826
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910297244.3A Pending CN109899321A (en) | 2019-04-15 | 2019-04-15 | It can be effectively reduced the compressor of blade harmonic noise |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020211788A1 (en) * | 2019-04-15 | 2020-10-22 | Wuxi Cummins Turbo Technologies Company Ltd. | Compressor |
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| CN101776091A (en) * | 2009-01-09 | 2010-07-14 | 陈晶 | Compressor casing of pressurizer |
| CN103511337A (en) * | 2012-06-20 | 2014-01-15 | 福特环球技术公司 | Turbocharger compressor noise reduction system and method |
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| CN206801619U (en) * | 2017-06-08 | 2017-12-26 | 安徽江淮汽车集团股份有限公司 | A kind of turbocharger |
| CN208221189U (en) * | 2017-12-29 | 2018-12-11 | 宁波丰沃涡轮增压系统有限公司 | A kind of turbocharger pressure shell structure of low induction noise |
| CN210152976U (en) * | 2019-04-15 | 2020-03-17 | 无锡康明斯涡轮增压技术有限公司 | Compressor capable of effectively reducing harmonic noise of blades and turbocharger |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020211788A1 (en) * | 2019-04-15 | 2020-10-22 | Wuxi Cummins Turbo Technologies Company Ltd. | Compressor |
| GB2597185A (en) * | 2019-04-15 | 2022-01-19 | Wuxi Cummins Turbo Tech Company Ltd | Compressor |
| GB2597185B (en) * | 2019-04-15 | 2023-05-17 | Wuxi Cummins Turbo Tech Company Ltd | Compressor |
| US12031552B2 (en) | 2019-04-15 | 2024-07-09 | Wuxi Cummins Turbo Technologies Company Ltd. | Compressor |
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