CN105604935A - Compressor and air conditioner provided with compressor - Google Patents

Compressor and air conditioner provided with compressor Download PDF

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Publication number
CN105604935A
CN105604935A CN201610071024.5A CN201610071024A CN105604935A CN 105604935 A CN105604935 A CN 105604935A CN 201610071024 A CN201610071024 A CN 201610071024A CN 105604935 A CN105604935 A CN 105604935A
Authority
CN
China
Prior art keywords
compressor
back pressure
quiet dish
noise elimination
pressure hole
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
Application number
CN201610071024.5A
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Chinese (zh)
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CN105604935B (en
Inventor
郭莉娟
谷欢欢
张荣婷
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Priority to CN201610071024.5A priority Critical patent/CN105604935B/en
Publication of CN105604935A publication Critical patent/CN105604935A/en
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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
    • 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
    • F04C18/0223—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 with symmetrical double wraps
    • 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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Abstract

The invention provides a compressor and an air conditioner provided with the compressor. The compressor comprises a static disc body and a noise elimination part, wherein the static disc body is provided with a static disc backpressure hole; the noise elimination part is arranged on the static disc body; and the noise elimination part is communicated with the static disc backpressure hole so that pressure pulse generated in the static disc backpressure hole is reduced. The noise elimination part is arranged on the static disc body so that the exhausting pressure pulse in the static disc backpressure hole is effectively reduced; and furthermore, exhausting noises of the compressor are reduced and the aim of lowering the noises of the whole compressor is realized, so that the quality of the compressor is effectively improved.

Description

Compressor and there is its air-conditioner
Technical field
The present invention relates to Compressor Technology field, in particular to a kind of compressor and there is its air-conditioner.
Background technology
As depicted in figs. 1 and 2, it is mainly made up of pump housing part and motor part screw compressor of the prior art. The pump housingPart is made up of quiet dish 1, Moving plate 2, cross slip-ring 3, upper bracket 4 and compressor housing 5 etc. Motor in screw compressorDriving crank rotates, and the eccentric part on bent axle drives Moving plate to rotate, and Moving plate can not occur under the effect of cross slip-ring 3Rotation, Moving plate 2 is taking the center of quiet dish 1 as pivot does the revolution translation without rotation. Moving plate 2 forms mutually and nibbles with quiet dish 1The periodic compression chamber of closing, thus realize suction, compression and the discharge of gas. Moving plate 2 in running always in floatState, this state is mainly to carry out balance by back pressure cavity 9. On Moving plate 2, offer back pressure hole 6 and back pressure hole 7, intermediate compressionGas in chamber is introduced air-flow in back pressure cavity 9 by the back pressure cavity intercommunicating pore 8 on back pressure hole 6, back pressure hole 7 and quiet dish successively,Make Moving plate 2 reach the state of longitudinal balance.
Because intermediate compression chamber is different with the pressure of back pressure cavity 9, in the time that intermediate compression chamber and back pressure cavity 9 are communicated with, can produce largerPressure fluctuation, this pressure fluctuation meeting causes screw compressor exhaust noise to increase, thereby affects the quality problem of compressor.
Summary of the invention
The air-conditioner that main purpose of the present invention is to provide a kind of compressor and has it, makes an uproar to solve compressor in prior artThe problem that sound is large.
To achieve these goals, according to an aspect of the present invention, provide a kind of compressor, having comprised: quiet dish body, toolThere is quiet dish back pressure hole; Noise elimination portion, is arranged on quiet dish body, and noise elimination portion is connected so that in quiet dish back pressure hole with quiet dish back pressure holeThe pressure fluctuation producing reduces.
Further, noise elimination portion comprises: resonant cavity; Interface channel, one end of interface channel is connected with resonant cavity, connects logicalThe other end in road is connected with quiet dish back pressure hole.
Further, the frequency of noise elimination of noise elimination portion is fr, and,
f r = c 2 π S ( t + 0.85 d ) V ,
Wherein, c is the velocity of sound in refrigerant; T is the length of interface channel; D is the diameter of the cross section of interface channel; V is for being total to
The volume in chamber shakes; S is the area of the cross section of interface channel.
Further, the sound deadening capacity of noise elimination portion is TL, and,
T L = 10 × lg [ 1 + ( S ( t + 0.85 d ) V 2 S 0 ( f f r - f r f ) ) 2 ] ,
Wherein, the length that t is interface channel; D is the diameter of the cross section of interface channel; V is the volume of resonant cavity; S isThe area of the cross section of interface channel; frFor the frequency of noise elimination of noise elimination portion; F is the frequency of quiet dish back pressure hole internal sound; S0ForThe area of the longitudinal section of quiet dish back pressure hole.
Further, resonant cavity is for being opened in the intrinsic airtight container cavity of quiet dish.
Further, interface channel is arranged in quiet dish body.
Further, interface channel is the connectivity slot being arranged on quiet dish body surface.
Further, resonant cavity is the groove being hollowly arranged on quiet dish body surface.
Further, compressor also comprises: Moving plate body, Moving plate body does the revolution translation without rotation, Moving plate in compressorBody has Moving plate back pressure hole, and in the time that Moving plate body does the revolution translation without rotation, Moving plate back pressure hole is away from noise elimination portion.
Further, when Moving plate body does the revolution translation without rotation, the movement locus of Moving plate back pressure hole is on quiet dish bodyBe projected as track, noise elimination portion is away from the arranged outside of track.
According to a further aspect in the invention, provide a kind of air-conditioner, comprised compressor, compressor is above-mentioned compressor.
Apply technical scheme of the present invention, a kind of compressor is provided, this compressor comprises quiet dish body and noise elimination portion. Wherein,On quiet dish body, have quiet dish back pressure hole, noise elimination portion is arranged on quiet dish body and with quiet dish back pressure hole and is connected so that described quiet dishThe pressure fluctuation producing in back pressure hole reduces. On quiet dish body, noise elimination portion is set, has effectively reduced the row in quiet dish back pressure holeAtmospheric pressure is pulsed, and then has reduced the exhaust noise of compressor, reaches the object of the noise that reduces compressor complete machine, thereby effectivelyLifting the quality of compressor.
Brief description of the drawings
The Figure of description that forms the application's a part is used to provide a further understanding of the present invention, schematic reality of the present inventionExecute example and explanation thereof for explaining the present invention, do not form inappropriate limitation of the present invention. In the accompanying drawings:
Fig. 1 shows the structural representation of compressor in prior art;
Fig. 2 shows the A place structure for amplifying schematic diagram in Fig. 1;
Fig. 3 shows according to the structural representation of the embodiment of the noise elimination portion on the quiet dish of compressor of the present invention;
Fig. 4 shows the B place structure for amplifying schematic diagram in Fig. 3;
Fig. 5 shows the cross-sectional view of the noise elimination portion on the quiet dish in Fig. 4; And
Fig. 6 shows according to the graph of a relation of the sound deadening capacity of compressor of the present invention and compressor internal sound frequency.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
1, quiet dish; 2, Moving plate; 3, cross slip-ring; 4, upper bracket; 5, housing; 6, back pressure hole; 7, back pressure hole; 8,Back pressure cavity intercommunicating pore; 9, back pressure cavity;
10, quiet dish body; 11, quiet dish back pressure hole; 20, noise elimination portion; 21, resonant cavity; 22, interface channel; 30, Moving plate originallyBody; 31, Moving plate back pressure hole; 32, track.
Detailed description of the invention
It should be noted that, in the situation that not conflicting, the feature in embodiment and embodiment in the application can combine mutually.Describe below with reference to the accompanying drawings and in conjunction with the embodiments the present invention in detail.
As shown in Figure 3 and Figure 4, according to one embodiment of present invention, provide a kind of compressor, comprised quiet dish body 10 HesNoise elimination portion 20. Quiet dish body 10 has quiet dish back pressure hole 11. Noise elimination portion 20 is arranged on quiet dish body 10, noise elimination portion 20 withQuiet dish back pressure hole 11 is connected so that the pressure fluctuation of quiet dish back pressure hole 11 interior generations reduces.
In the present embodiment, on quiet dish body 10, noise elimination portion 20 is set, has effectively reduced the exhaust in quiet dish back pressure hole 11Pressure fluctuation, and then reduced the exhaust noise of compressor, reach the object of the noise that reduces compressor complete machine. Thereby effectivelyPromote the quality of compressor. This noise elimination portion 20 simple in structure, cost is low and be easy to processing and implement.
Wherein, noise elimination portion 20 comprises resonant cavity 21 and interface channel 22. One end of interface channel 22 is connected with resonant cavity 21,The other end of interface channel 22 is connected with quiet dish back pressure hole 11. When the gas of quiet dish back pressure hole 11 exists ripple during by acoustic wave excitationMoving, the gas in interface channel 22 is towards the internal direction of resonant cavity 21 and the direction away from resonant cavity 21 of interface channel 22Flow, thereby cause the loss of quiet dish back pressure hole 11 interior acoustic energy, thereby reach the object that compressor is eliminated the noise.
Through experimental study repeatedly, in the time that back pressure cavity communicates with the intermediate compression chamber of compressor, pressure fluctuation at 500-1000Hz frequentlyDuan Zeng great, illustrates in quiet dish back pressure hole 11 and can produce this frequency range pulsation, these pressure fluctuation meetings increase the exhaust noise of compressorLarge and by compressor housing to external radiation, cause the problem that compressor total noise of centrifuge is large. Also can bring Moving plate running uneven simultaneouslySurely, increase compressor power consumption, affect the performance of compressor.
In the time that the gas in the intermediate compression chamber of compressor is introduced back pressure cavity, noise frequency composition and resonance in quiet dish back pressure hole 11When the intrinsic frequency in chamber 21 is consistent, it is maximum that the sound energy attenuation of quiet dish back pressure hole 11 reaches. Reduce exhaust pulsation and exhaust thereby reachThe object of noise.
In the present embodiment, the frequency of noise elimination of resonant cavity 21 is mainly by the length of interface channel 22, the cross section of interface channel 22Volume long-pending and resonant cavity 21 is determined. The frequency of noise elimination of note noise elimination portion 20 is fr, have:
f r = c 2 π S ( t + 0.85 d ) V ,
The sound deadening capacity of note noise elimination portion 20 is TL, has,
T L = 10 × lg [ 1 + ( S ( t + 0.85 d ) V 2 S 0 ( f f r - f r f ) ) 2 ] ,
Wherein, c is the velocity of sound in refrigerant, and t is the length of interface channel 22, and d is the diameter of the cross section of interface channel 22, VFor the volume of resonant cavity 21, S is the area of the cross section of interface channel 22, frFor the frequency of noise elimination of noise elimination portion 20, f is quietThe frequency of dish back pressure hole 11 internal sounds, S0For the area of the longitudinal section of quiet dish back pressure hole 11. The sound deadening capacity song of this noise elimination structureLine is as Fig. 6, and it is more obvious that this structure can reduce the exhaust noise, the especially 800Hz that when back pressure hole is communicated with, produce well.
Preferably, resonant cavity 21 can be the airtight container cavity being opened in quiet dish body 10. Make like this resonant cavity 21 to quietThe noise that dish back pressure hole 11 produces while being connected with the back pressure hole on Moving plate body 30 has good noise elimination effect. Certainly resonance,Chamber 21 can be to be also hollowly arranged at the lip-deep groove of quiet dish body 10, the open side of groove now must with Moving plate thisBody 30 seals, thereby reaches effective soundproof effect. Resonant cavity 21 can also be the cylinder being arranged in quiet dish body 10Shape cavity or spherical hollow space.
Further, interface channel 22 also can be arranged in quiet dish body 10. Can increase like this interface channel 22 withSealing between resonant cavity 21. Certainly, interface channel 22 can be to be also opened between quiet dish back pressure hole 11 and resonant cavity 21Connectivity slot, or be arranged in quiet dish body 10 and be positioned at a certain height on quiet dish body 10 with resonant cavity 21 and the quiet dish back of the bodyThe through hole of pressing hole 11 to be connected. Need only in the situation that meeting frequency of noise elimination, sound deadening capacity and not collaborating resonant cavity 21Can be opened in any position being connected with quiet dish back pressure hole 11. Certainly, interface channel 22 can also be to be arranged at quiet dish body10 lip-deep connectivity slots. Similarly, the open side of connectivity slot should seal with Moving plate body 30 so that resonant cavity 21It is optimum that soundproof effect reaches.
Wherein, Moving plate body 30 does the revolution translation without rotation in compressor, and Moving plate body 30 has Moving plate back pressure hole 31,In the time that Moving plate body 30 does the revolution translation without rotation, Moving plate back pressure hole 31 is away from noise elimination portion 20. Arrange effectively and avoid like thisMoving plate back pressure hole 31 cause compressor to collaborate while being connected with noise elimination portion 20, thereby affected the noise elimination effect of noise elimination portion 20Really. As shown in Figure 4 and Figure 5, in the time that Moving plate body 30 does the revolution translation without rotation, the movement locus of Moving plate back pressure hole 31On quiet dish body 10, be projected as track 32, noise elimination portion 20 is away from the arranged outside of track 32.
Because Moving plate body 30 is done the revolution translation without rotation at the circle around certain radius. So any point all on Moving plate body 30To make revolution translation, the movement locus 32 of the Moving plate back pressure hole 31 of Moving plate body 30 around this circle. If resonant cavity 21 knot of eliminating the noiseStructure designs in the movement locus of Moving plate back pressure hole 31, and Moving plate back pressure hole 31 can be connected with resonant cavity 21, will cause compression chamberIn Moving plate back pressure hole 31, resonant cavity 21 and interface channel 22 to gas leakage in the back pressure cavity of compressor, make compressorPerformance reduces, so the noise elimination portion 20 of compressor can only be opened in Moving plate back pressure hole 31 movement locus region in addition.
The exhaust gas pressure pulse producing when the intermediate compression chamber that can effectively reduce like this compressor is connected with back pressure cavity, therebyReduce the noise that this exhaust gas pressure pulse produces, the noise of compressor complete machine is reduced greatly. Exhaust gas pressure pulseAfter reducing, Moving plate body 30 even running better under the support force of axial gas and the balanced action of back pressure, reducesThe power consumption of compressor, compressor performance is effectively promoted.
Compressor in above-described embodiment can also be used in air-conditioner technical field, according to a further aspect in the invention, providesA kind of air-conditioner. This air-conditioner comprises compressor, and compressor is the compressor in above-described embodiment.
From the foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for the technology people of this areaMember, the present invention can have various modifications and variations. Within the spirit and principles in the present invention all, any amendment of doing,Protection scope of the present invention is equal to replacement, improvement etc., within all should be included in.

Claims (11)

1. a compressor, is characterized in that, comprising:
Quiet dish body (10), has quiet dish back pressure hole (11);
Noise elimination portion (20), is arranged at described quiet dish body (10) upper, described noise elimination portion (20) and described quiet dish back pressure hole(11) be connected so that the pressure fluctuation producing in described quiet dish back pressure hole (11) reduces.
2. compressor according to claim 1, is characterized in that, described noise elimination portion (20) comprising:
Resonant cavity (21);
Interface channel (22), one end of described interface channel (22) is connected with described resonant cavity (21), described connectionThe other end of passage (22) is connected with described quiet dish back pressure hole (11).
3. compressor according to claim 2, is characterized in that, the frequency of noise elimination of described noise elimination portion (20) is fr, and,
f r = c 2 π S ( t + 0.85 d ) V ,
Wherein,
C is the velocity of sound in refrigerant;
T is the length of described interface channel (22);
D is the diameter of the cross section of described interface channel (22);
V is the volume of described resonant cavity (21);
S is the area of the cross section of described interface channel (22).
4. compressor according to claim 2, is characterized in that, the sound deadening capacity of described noise elimination portion (20) is TL, and,
T L = 10 × lg [ 1 + ( S ( t + 0.85 d ) V 2 S 0 ( f f r - f r f ) ) 2 ] ,
Wherein,
T is the length of described interface channel (22);
D is the diameter of the cross section of described interface channel (22);
V is the volume of described resonant cavity (21);
S is the area of the cross section of described interface channel (22);
frFor the frequency of noise elimination of described noise elimination portion (20);
F is the frequency of described quiet dish back pressure hole (11) internal sound;
S0For the area of the longitudinal section of described quiet dish back pressure hole (11).
5. compressor according to claim 2, is characterized in that, described resonant cavity (21) is for being opened in described quiet dish body(10) the airtight container cavity in.
6. compressor according to claim 2, is characterized in that, described interface channel (22) is arranged at described quiet dish body(10) in.
7. compressor according to claim 2, is characterized in that, described interface channel (22) is for being arranged at described quiet dish originallyThe lip-deep connectivity slot of body (10).
8. compressor according to claim 2, is characterized in that, described resonant cavity (21) is described quiet for being hollowly arranged atThe lip-deep groove of dish body (10).
9. compressor according to claim 1, is characterized in that, described compressor also comprises:
Moving plate body (30), described Moving plate body (30) does the revolution translation without rotation in described compressor, described movingDish body (30) has Moving plate back pressure hole (31), in the time that described Moving plate body (30) does the revolution translation without rotation, and instituteState Moving plate back pressure hole (31) away from described noise elimination portion (20).
10. compressor according to claim 9, is characterized in that, when described Moving plate body (30) does without the revolution of rotation flatWhen moving, the movement locus of described Moving plate back pressure hole (31) is projected as track (32) on described quiet dish body (10),Described noise elimination portion (20) is away from the arranged outside of described track (32).
11. 1 kinds of air-conditioners, comprise compressor, it is characterized in that, described compressor is described in claim 1 to 10 any oneCompressor.
CN201610071024.5A 2016-02-01 2016-02-01 Compressor and air conditioner with it Active CN105604935B (en)

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Application Number Priority Date Filing Date Title
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CN105604935B CN105604935B (en) 2018-10-26

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106015010A (en) * 2016-07-04 2016-10-12 珠海凌达压缩机有限公司 Compressor stator and compressor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996035056A1 (en) * 1995-05-02 1996-11-07 Lg Electronics Inc. Axial sealing apparatus for scroll type compressor
CN1510272A (en) * 2002-12-25 2004-07-07 乐金电子(天津)电器有限公司 Static vortex pan of vortex compressor
CN1828189A (en) * 2006-03-23 2006-09-06 杭州钱江水泥厂 Oil-free vortex air conditioner compressor
CN202091197U (en) * 2011-06-13 2011-12-28 珠海格力节能环保制冷技术研究中心有限公司 Vertex compressor and static vertex disc
CN103384769A (en) * 2011-03-29 2013-11-06 日立空调·家用电器株式会社 Scroll compressor
CN205533205U (en) * 2016-02-01 2016-08-31 珠海格力节能环保制冷技术研究中心有限公司 Compressor and air conditioner with same

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996035056A1 (en) * 1995-05-02 1996-11-07 Lg Electronics Inc. Axial sealing apparatus for scroll type compressor
CN1510272A (en) * 2002-12-25 2004-07-07 乐金电子(天津)电器有限公司 Static vortex pan of vortex compressor
CN1828189A (en) * 2006-03-23 2006-09-06 杭州钱江水泥厂 Oil-free vortex air conditioner compressor
CN103384769A (en) * 2011-03-29 2013-11-06 日立空调·家用电器株式会社 Scroll compressor
CN202091197U (en) * 2011-06-13 2011-12-28 珠海格力节能环保制冷技术研究中心有限公司 Vertex compressor and static vertex disc
CN205533205U (en) * 2016-02-01 2016-08-31 珠海格力节能环保制冷技术研究中心有限公司 Compressor and air conditioner with same

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106015010A (en) * 2016-07-04 2016-10-12 珠海凌达压缩机有限公司 Compressor stator and compressor
CN106015010B (en) * 2016-07-04 2019-02-26 珠海凌达压缩机有限公司 Compressor stator and compressor

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