CN104755762A - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- CN104755762A CN104755762A CN201380056491.5A CN201380056491A CN104755762A CN 104755762 A CN104755762 A CN 104755762A CN 201380056491 A CN201380056491 A CN 201380056491A CN 104755762 A CN104755762 A CN 104755762A
- Authority
- CN
- China
- Prior art keywords
- oral area
- scroll compressor
- downstream
- upstream extremity
- end plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
-
- 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
- F04C18/0207—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 both members having co-operating elements in spiral form
- F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
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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
- F04C18/0207—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 both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0253—Details concerning the base
- F04C18/0261—Details of the ports, e.g. location, number, geometry
-
- 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
-
- 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
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
Abstract
Provided is a scroll compressor with which noise of a specific frequency range can be reduced when a mixed refrigerant is used. The scroll compressor (1) is equipped with: an orbiting scroll (30) rotatably linked to an eccentric pin (17A) of a main shaft (17); and a stationary scroll (20) which opposes the orbiting scroll (30) so as to form a compression chamber that compresses a refrigerant, and which has an end plate in which is formed a discharge port (23) that discharges the compressed refrigerant toward a high-pressure chamber (10B). The scroll compressor is characterized in that the discharge port (23) comprises: an upstream port section (23A) which is continuous with the compression chamber and has an aperture area of A1; and a downstream port section (33B) which is continuous with the upstream port section (23A) and has an aperture area of A2 which is larger than the aperture area A1 of the upstream port section (23A), with a node in the oscillation mode occurring at the boundary of the upstream port section (23A) and the downstream port section (23B).
Description
Technical field
The present invention relates to the scroll compressor of a kind of configuration example as indoor aircondition.
Background technique
The scroll compressor used in the refrigeration cycle such as aircondition, refrigerating plant possesses fixed eddy plate and coils with convolution whirlpool.Fixed eddy plate, convolution whirlpool dish are the component being integrally formed with gyrate roll bending wall respectively in the one side side of discoideus end plate.Make this fixed eddy plate coil opposed with convolution whirlpool with the state making roll bending wall engage, by motor etc., convolution whirlpool is coiled and carry out revolution circumnutation relative to fixed eddy plate.And, by make to be formed in pressing chamber between the roll bending wall of both sides from outer circumferential side to the movement of inner circumferential side while its volume is reduced, carry out the compression of the refrigerant gas in pressing chamber thus.
The refrigerant gas compressed by pressing chamber, by being formed in the ejection port on the end plate of fixed eddy plate, flowing into the hyperbaric chamber between discharge cap and housing, then sprays towards refrigerant circuit from the spraying pipe be arranged on housing.
The ejection port be formed on fixed eddy plate can impact the performance of scroll compressor or noise, therefore proposes various scheme.
Such as in patent documentation 1, improving mechanical efficiency to reduce the pressure loss, proposing the scheme forming diffuser at ejection port.In addition, in patent documentation 2, in order to realize the low noise of compressor steadily in the long term, propose the upper surface open at the end plate of fixed eddy plate and the anechoic room be communicated with the ejection port of fixed eddy plate.
[at first technical paper]
[patent documentation]
Patent documentation 1: Japanese Unexamined Patent Publication 6-66271 publication
Patent documentation 2: Japanese Unexamined Patent Publication 2012-122376 publication
Summary of the invention
[inventing the problem that will solve]
In order to suppress environmental pressure, use the mix refrigerant such as R410C (near azeotropic mixed refrigerant) or R407C (mixed non-azeotropic refrigerant) gradually.When using mix refrigerant, produce the composition in 1k ~ 2kHz region of the ejection pulsation of the ejection port of fixed eddy plate as noise.According to the research of the present inventor, patent documentation 1, patent documentation 2 do not propose solution to this noise.
The present invention completes based on this technical task, and its object is to provides a kind of scroll compressor that can reduce the noise of the specific frequency band produced when using mix refrigerant.
[for solving the scheme of problem]
The present inventor is studied to achieve these goals, and the velocity of sound drawing mix refrigerant and the relation of the distance comprising the refrigerant flow path spraying port can affect the conclusion that noise produces.
In the formula (1) relevant to the velocity of sound, if consider boundary conditions, then λ=4L (L:L1 (fixed eddy plate end plate thickness)+L1 (whirlpool dish tooth depth)).
c＝f×λ …(1)
C: the velocity of sound (mm/s) f: frequency (kHz) λ: wavelength (4L)
The velocity of sound of the ejection port of the mix refrigerants such as R410A, 407C is about 160 ~ 180m/s.In addition, fixed eddy plate end plate thickness L1 is set to 10 ~ 20mm, tooth depth L2 is coiled in whirlpool and is set to 10 ~ 20mm.Here, L1 is equivalent to the length of the ejection port be formed on fixed eddy plate end plate, and L2 is equivalent to the length of being coiled the pressing chamber formed by fixed eddy plate and convolution whirlpool, and therefore L is the distance from pressing chamber to the refrigerant flow path of ejection port.And when the distance L of the velocity of sound (160m/s) of mix refrigerant, refrigerant passage is substituted into formula (1), acoustic feature value (f) becomes 1 ~ 2kHz.If ejection pulsation sympathetic response in this frequency band, then other structures (following, to be generically and collectively referred to as " structure ") constructing the surrounding of component and scroll compressor that are easy and scroll compressor resonate, and cause the noise from compressor to increase.
Therefore, the present inventor is conceived to regulate acoustic feature value to avoid the resonance with structure, and completes the present invention.
Namely the feature of scroll compressor of the present invention is to possess: convolution whirlpool dish, and it is linked to the eccentric axial portion of main shaft in rotatable mode; Fixed eddy plate, it coils opposed with convolution whirlpool thus forms the pressing chamber compressed refrigeration agent, and there is end plate, described end plate is formed with the ejection port that the refrigeration agent after by compression sprays towards hyperbaric chamber, ejection port comprises: be connected with pressing chamber and have opening area A1 upstream extremity oral area, to be connected with upstream extremity oral area and opening area A2 is greater than the downstream oral area of the opening area A1 of upstream extremity oral area, produce the joint of vibrational mode on the border of upstream extremity oral area and downstream oral area.
Scroll compressor of the present invention, by making the opening area of upstream extremity oral area and downstream oral area different from each other thus producing the joint of vibrational mode on the border of upstream extremity oral area and downstream oral area, only makes upstream extremity oral area be equivalent to the part of above-mentioned L1 thus.This structure shortens the distance L of above-mentioned refrigerant passage, thus can regulate higher to avoid the resonance with structure by the acoustic feature value obtained by formula (1).
Ejection port in the present invention comprises some modes.
About downstream oral area, can make opening area A2 on the flow direction of refrigeration agent equal or periodically or continuity expand.The port of the circle of equal diameters is preferably set in processability.
[invention effect]
According to the present invention, by making the opening area of upstream extremity oral area and downstream oral area different thus producing the joint of vibrational mode on the border of upstream extremity oral area and downstream oral area, thus shorten the distance L of refrigerant passage, thus acoustic feature value is regulated lower, the resonance with structure can be avoided.Therefore, scroll compressor of the present invention can reduce the noise of the specific frequency band produced when using mix refrigerant.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the scroll compressor represented in present embodiment.
The partial enlarged drawing that Fig. 2 (a) is Fig. 1, the IIb-IIb alignment that Fig. 2 (b) is Fig. 2 (a) looks sectional view.
Fig. 3 is the figure be described for the action effect of the ejection port of the fixed charge method end plate to present embodiment, Fig. 3 (a) schematically shows the ejection stream comprising the refrigeration agent of ejection port of present embodiment, and Fig. 3 (b) schematically shows the ejection stream of general refrigeration agent in the past.
Fig. 4 is that the figure of the variation of the ejection port representing present embodiment, Fig. 4 (a) show the example of periodically amplifying downstream oral area, and Fig. 4 (b) amplifies the example of downstream oral area with showing continuity.
Embodiment
Below, the present invention is described in detail for shown with reference to the accompanying drawings mode of execution.
As shown in Figure 1, the scroll compressor 1 of the present embodiment scroll compressor mechanism 2 that possesses electric motor 12 in housing 10, driven by electric motor 12.The refrigeration agents such as this scroll compressor 1 couple of R410C, R407C compress and supply to the such as refrigerant circuit such as air conditioner, refrigerating machine.
Housing 10 possesses the case top 102 of the housing body 101 of bottomed cylindrical of upper end opening, the opening of the upper end of covering shell main body 101.
The suction pipe 13 that never illustrated storage imports refrigeration agent in housing body 101 is provided with in the side of housing body 101.
In case top 102, be provided with the spraying pipe 14 spraying the refrigeration agent after being compressed by scroll compressor mechanism 2.The inside of housing 10 is separated into low pressure chamber 10A and hyperbaric chamber 10B by discharge cap 25.
Electric motor 12 possesses stator 15, rotor 16.
Stator 15 is provided with coil, this coil by by be arranged on housing body 101 side not shown power subsystem supply electric power thus produce magnetic field.Rotor 16 possesses permanent magnet and yoke as staple, and this external center is combined with main shaft 17 integratedly.
Be provided with the upper bearing 18 and lower bearing 19 that to be supported by main shaft 17 as rotating in the both end sides of main shaft 17 across electric motor 12.
In the containing space 190 being formed at upper bearing 18, the cam pin 17A being arranged on the upper end of main shaft 17 gives prominence to and is accommodated.
Scroll compressor mechanism 2 possesses fixed eddy plate 20, carries out the convolution whirlpool dish 30 of revolution circumnutation relative to fixed eddy plate 20.
Fixed eddy plate 20 possesses fixed charge method end plate 21, erects the gyrate roll bending 22 of setting from a face of fixed charge method end plate 21.Fixed eddy plate 20 also possesses ejection port 23 on fixed charge method end plate 21.Ejection port 23 runs through in the table of fixed charge method end plate 21, and one end (in the drawings for below) coil pressing chamber PR opening between 30 towards being formed in fixed eddy plate 20 and convolution whirlpool, the other end (being top in the drawings) is towards ejection port 27 opening of the discharge cap 25 of the top of covering fixed eddy plate 20.
In the present embodiment, ejection port 23, is made up of the upstream extremity oral area 23A being positioned at upstream side, the downstream oral area 23B that is positioned at downstream place compared with upstream extremity oral area 23A for benchmark with the flow direction F (Fig. 2 (a)) of refrigeration agent.Upstream extremity oral area 23A is connected with pressing chamber PR, and downstream oral area 23B is connected with upstream extremity oral area 23A.As shown in Fig. 2 (b), the opening shape of upstream extremity oral area 23A is rounded, and its opening area is set to A1.In addition, the opening shape of downstream oral area 23B is fan, and its opening area is set to A2.In the present embodiment, the opening area A2 of downstream oral area 23B is greater than the opening area A1 of upstream extremity oral area 23A.Further, according to the difference of this opening area, upstream extremity oral area 23A and downstream oral area 23B produces the joint of vibrational mode at its boundary part.For spraying port 23 like this, to form produced action effect by upstream extremity oral area 23A and downstream oral area 23B aftermentioned.
Convolution whirlpool dish 30 also possesses discoideus convolution end plate 31, erects the gyrate roll bending 32 of setting from a face of convolution end plate 31.
The back side of the convolution end plate 31 of convolution whirlpool dish 30 is provided with protruding 34, and in this projection 34, is assembled with driving lining 36 by bearing.Cam pin 17A is embedded with driving the inner side of lining 36.Thus, convolution whirlpool dish 30 combines with the axle center of main shaft 17 bias, therefore when main shaft 17 rotates, convolution whirlpool dish 30 with the eccentric distance in the axle center of distance main shaft 17 for radius of gyration and rotating (revolution).
It should be noted that, in order to not make convolution whirlpool coil 30 rotations while revolution, between convolution whirlpool dish 30 and main shaft 17, being provided with the not shown partition ring retraining rotation.
With mutual eccentric gauge quantitatively and the angle of rotation that the mode staggering 180 degree of phase places roll bending 22,32 engaged and whirlpool of circling round coil 30 contact with each other in multiple position accordingly.So, be formed with pressing chamber PR relative to the central part (most inner peripheral portion) of the vortex of roll bending 22,32, and along with the convolution of convolution whirlpool dish 30, pressing chamber moves to inner circumferential side while making its volume reduce gradually point symmetry.And, farthest compressed at the central part refrigeration agent of vortex.The pressing chamber PR of Fig. 1 shows this part.
In this scroll compressor mechanism 2, the volume of the pressing chamber PR be formed between the whirlpool dish 20,30 of both sides is also reduced in the short transverse of roll bending in the midway of vortex.For this reason, coil 30 both sides at fixed eddy plate 20 and convolution whirlpool, reduce the height of roll bending in inner circumferential side compared with outer circumferential side, and the end plate of the other side side making in inner circumferential side roll bending stair-stepping with this opposed compared with outer circumferential side is outstanding to end plate inner face side.
In order to the scroll compressor 1 of above this structure is started, excitation is carried out to electric motor 12, and in housing 10, imports refrigeration agent by suction pipe 13.
When electric motor 12 is excited, main shaft 17 rotates, and is accompanied by this, and convolution whirlpool dish 30 carries out revolution circumnutation relative to fixed eddy plate 20.So, compressed in the pressing chamber PR of refrigeration agent between convolution whirlpool dish 30 and fixed eddy plate 20, and the refrigeration agent of the low pressure chamber 10A be directed in housing 10 from suction pipe 13 is inhaled between convolution whirlpool dish 30 and fixed eddy plate 20.Further, in pressing chamber PR by the refrigeration agent after compressing successively by the ejection port 23 of fixed charge method end plate 21, the ejection port 27 of discharge cap 25 and spraying to hyperbaric chamber 10B, more externally to spray from spraying pipe 14.Like this, the suction of refrigeration agent, compression and ejection is carried out continuously.
In the present embodiment, the ejection port 23 of fixed eddy plate 20 is made up of above-mentioned upstream extremity oral area 23A and downstream oral area 23B, the opening area A2 of downstream oral area 23B is larger compared with the opening area A1 of upstream extremity oral area 23A, and upstream extremity oral area 23A and downstream oral area 23B produces the joint of vibrational mode on its border.With reference to Fig. 3, the action effect so arranged is described.
First, the ejection port one 23 in the past that the opening area shown in Fig. 3 (b) is constant is described.This opening area is set to the A1 identical with the upstream extremity oral area 23A of present embodiment.In other words, spray port one 23 to be equal to the structure that the upstream extremity oral area 23A of present embodiment is connected to the end in downstream side.
In Fig. 3 (b), the wavelength X in following formula (1) is determined by the aggregate value of L1 ' following by definition, L2 ', L3 '.When applying ejection port one 23 in the past, stream C1 ' is continuous with the vibrational mode of stream C2 ', and stream C3 ' and in contrast by the joint of the stream C1 at upstream side place and stream C2 in its boundary generation vibrational mode.And, with regard to the length L ' (L1 '+L2 ') of the total of stream C1 ' and stream C2 ', when considering boundary conditions, λ=4L '.As described above, the velocity of sound in the refrigerant flow path of the mix refrigerants such as R410A, 407C is about 160 ~ 180m/s, the thickness of fixed charge method end plate (L2 ') is being set to 10 ~ 20mm, whirlpool is coiled tooth depth (L1 ') when being set to 10 ~ 20mm, acoustic feature value (f) is 1 ~ 2kHz (being set to the situation of c=160m/s).But this may produce the resonance with structure.
c＝f×λ …(1)
C: the velocity of sound (mm/s) f: frequency (kHz) λ: wavelength (4L)
λ＝L1’+L2’+L3’
L1 ': the length of the stream C1 ' of the refrigeration agent in pressing chamber PR
L2 ': the length of the stream C2 ' of the refrigeration agent in fixed charge method end plate 21
L3 ': the length of the stream C3 ' of the refrigeration agent at downstream place compared with fixed charge method end plate 21
Therefore, as shown in Fig. 3 (a) of present embodiment, the opening of ejection port 23 is significantly expanded from midway, the stream (C1, C2) and the stream (C3) from downstream oral area 23B to the refrigeration agent in downstream side of the refrigeration agent to upstream extremity oral area 23A, produces the joint of vibrational mode.Like this, because the L being equivalent to L ' in the past shortens, therefore, it is possible to improve acoustic feature value (f), therefore, it is possible to avoid the resonance with structure.Such as, the thickness from fixed charge method end plate 21 1/4 position formed downstream oral area 23B time, acoustic feature value (f) becomes 1.6 ~ 3.2kHz.
But, can easily infer, in order to shorten L, as long as thinning fixed charge method end plate 21.But, in order to make fixed eddy plate 20 guarantee required intensity, sometimes cannot thinning fixed charge method end plate 21.Particularly, High Rotation Speed and lightweight are required for scroll compressor 1, be therefore in the fixed charge method end plate 21 being difficult to thinning fixed eddy plate 20 in current scope of allowing, be difficult to carry out the state of further slimming.Therefore, the structure of the ejection port 23 of present embodiment becomes and can avoid the important mechanism with the resonance of structure when not thinning fixed charge method end plate 21.
In addition, as ejection port 23, by increasing the opening area of downstream oral area 23B, can reduce the pressure loss of the refrigeration agent at this part place, the performance that therefore can also contribute to scroll compressor 1 improves.
In the present embodiment, set the opening area A2 of downstream oral area 23B in the mode of the joint producing vibrational mode by the relation of the opening area A1 with upstream extremity oral area 23A.In addition, consider the vibration with the structure of surrounding, so that the length L2 that can avoid setting upstream port 23A with the mode of acoustic feature value (f) of the resonance of structure can be obtained.As long as the vibration test carrying out simulating just can obtain either party in the opening area A2 of above-mentioned downstream oral area 23B and the length L2 of upstream port 23A.
It should be noted that, in the above-described embodiment, show opening area example constant on the flow direction of refrigeration agent as downstream oral area 23B, but the present invention is not limited to this.Such as, as long as effect of the present invention can be obtained, also can as Fig. 4 (a) Suo Shi periodically expand downstream oral area 23B, can also as Fig. 4 (b) Suo Shi continuity ground expansion downstream oral area 23B.In addition, about upstream extremity oral area 23A, although the diagram of eliminating, however also can make opening area periodically or continuity change.
In addition, the opening shape of downstream oral area 23B is fan-shaped, but the present invention is not limited to this, also can be other opening shape, such as circular.
Further, the situation based on the composition producing 1k ~ 2kHz region that ejection is pulsed as noise describes the present invention, but this is only an example, can certainly apply the present invention to reduce the noise of the composition beyond this scope.
In addition, the opening shape of downstream oral area 23B is arbitrary, and is not limited to fan.
In addition, only otherwise depart from purport of the present invention, then can accept or reject and select structure cited in above-mentioned mode of execution or suitably change to other structures.
[description of reference numerals]
1 scroll compressor
2 scroll compressor mechanisms
10 housings
10A low pressure chamber
10B hyperbaric chamber
12 electric motors
13 suction pipes
14 spraying pipes
15 stators
16 rotors
17 main shafts
17A cam pin
18 upper bearings
19 lower bearings
20 fixed eddy plates
22,32 roll bendings
23 ejection ports
23A upstream extremity oral area
23B downstream oral area
25 discharge caps
27 ejection ports
30 convolution whirlpool dishes
34 is protruding
36 drive lining
101 housing body
102 case top
21 fixed charge method end plates
31 convolution end plates
Claims (2)
1. a scroll compressor, is characterized in that, possesses:
Convolution whirlpool dish, it is linked to the eccentric axial portion of main shaft in rotatable mode;
Fixed eddy plate, it coils opposed with described convolution whirlpool thus forms the pressing chamber compressed refrigeration agent, and has end plate, described end plate is formed with the ejection port that the described refrigeration agent after by compression sprays towards hyperbaric chamber,
Described ejection port comprises: be connected with described pressing chamber and have opening area A1 upstream extremity oral area, to be connected with described upstream extremity oral area and opening area A2 is greater than the downstream oral area of the opening area A1 of described upstream extremity oral area, produce the joint of vibrational mode on the border of described upstream extremity oral area and described downstream oral area.
2. scroll compressor according to claim 1, wherein,
The described opening area A2 of described downstream oral area is equal or periodically or continuously expand on the flow direction of described refrigeration agent.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012257840A JP5951456B2 (en) | 2012-11-26 | 2012-11-26 | Scroll compressor |
| JP2012-257840 | 2012-11-26 | ||
| PCT/JP2013/005482 WO2014080553A1 (en) | 2012-11-26 | 2013-09-17 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104755762A true CN104755762A (en) | 2015-07-01 |
| CN104755762B CN104755762B (en) | 2016-10-26 |
Family
ID=50775751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380056491.5A Active CN104755762B (en) | 2012-11-26 | 2013-09-17 | Scroll compressor |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2918841A4 (en) |
| JP (1) | JP5951456B2 (en) |
| CN (1) | CN104755762B (en) |
| WO (1) | WO2014080553A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4043729A4 (en) * | 2019-10-11 | 2023-01-25 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Electric compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5853288A (en) * | 1995-03-22 | 1998-12-29 | Mitsubishi Denki Kabushiki Kaisha | Scroll compressor having a counterboring part communicating with an intermediate pressure chamber |
| JP2009167983A (en) * | 2008-01-18 | 2009-07-30 | Daikin Ind Ltd | Scroll compressor |
| CN102016319A (en) * | 2008-04-22 | 2011-04-13 | 松下电器产业株式会社 | Scroll compressor |
| JP2012122376A (en) * | 2010-12-07 | 2012-06-28 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| CN102753829A (en) * | 2010-02-15 | 2012-10-24 | 大金工业株式会社 | Scroll compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5342183A (en) | 1992-07-13 | 1994-08-30 | Copeland Corporation | Scroll compressor with discharge diffuser |
| JPH07269485A (en) * | 1994-03-31 | 1995-10-17 | Mitsubishi Heavy Ind Ltd | Compressor |
| JP2010065560A (en) * | 2008-09-09 | 2010-03-25 | Daikin Ind Ltd | Scroll compressor |
-
2012
- 2012-11-26 JP JP2012257840A patent/JP5951456B2/en active Active
-
2013
- 2013-09-17 WO PCT/JP2013/005482 patent/WO2014080553A1/en active Application Filing
- 2013-09-17 CN CN201380056491.5A patent/CN104755762B/en active Active
- 2013-09-17 EP EP13856394.5A patent/EP2918841A4/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5853288A (en) * | 1995-03-22 | 1998-12-29 | Mitsubishi Denki Kabushiki Kaisha | Scroll compressor having a counterboring part communicating with an intermediate pressure chamber |
| JP2009167983A (en) * | 2008-01-18 | 2009-07-30 | Daikin Ind Ltd | Scroll compressor |
| CN102016319A (en) * | 2008-04-22 | 2011-04-13 | 松下电器产业株式会社 | Scroll compressor |
| CN102753829A (en) * | 2010-02-15 | 2012-10-24 | 大金工业株式会社 | Scroll compressor |
| JP2012122376A (en) * | 2010-12-07 | 2012-06-28 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014105606A (en) | 2014-06-09 |
| EP2918841A4 (en) | 2015-12-16 |
| JP5951456B2 (en) | 2016-07-13 |
| WO2014080553A1 (en) | 2014-05-30 |
| EP2918841A1 (en) | 2015-09-16 |
| CN104755762B (en) | 2016-10-26 |
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Effective date of registration: 20170907 Address after: Tokyo, Japan, Japan Patentee after: MITSUBISHI heavy industry refrigeration air conditioning system Co Ltd Address before: Tokyo, Japan Patentee before: Mit-subishi Heavy Industries Ltd. |