CN108496009A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN108496009A CN108496009A CN201780007733.XA CN201780007733A CN108496009A CN 108496009 A CN108496009 A CN 108496009A CN 201780007733 A CN201780007733 A CN 201780007733A CN 108496009 A CN108496009 A CN 108496009A
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- China
- Prior art keywords
- flow path
- path portion
- rotary shaft
- muffler
- rotary
- Prior art date
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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
- 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
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/065—Noise dampening volumes, e.g. muffler chambers
-
- 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
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The rotary compressor (1) of the present invention has rotary shaft (3), rotary compression mechanism (4) and the muffler (10) configured around the axis of rotary shaft (3).Muffler (10) has：Compressed refrigerant is accommodated in inside by muffler body (11)；And flow path wall (12), between flow path wall (12) and rotary shaft (3) or bearing portion (6B), the discharge duct (100) of the specific length for the outside for making refrigerant flow out to muffler (10) along the axial direction of rotary shaft (3) is formed.Discharge duct (100) has：First flow path portion (101) is located at a part for the circumferential direction (D1) of rotary shaft (3)；And second flow path portion (102), it is adjacent with first flow path portion (101) in circumferential direction (D1), and the size ratio first flow path portion (101) radially of rotary shaft (3) is greatly, sectional area is bigger than first flow path portion (101).
Description
Technical field
The present invention relates to a kind of rotary compressors having rotary compression mechanism and exhaust silencer.
Background technology
Rotary compressor has：Rotary shaft, the rotary compression with piston rotary and cylinder set on rotary shaft
The muffler and shell (example of noise caused by the pulsation (pressure oscillation) of mechanism, inhibition by compressed refrigerant gas
Such as, patent document 1).
Outlet side of the refrigerant gas compressed by rotary compression mechanism from the component for being formed in the opening for blocking cylinder
Mouthful by by be expelled to the inside of muffler, from the gap between the diameter shrinkage part and rotary shaft of muffler by by be expelled to shell
Internal space.
In patent document 1, the gap (outlet of muffler) of the periphery of rotary shaft is formed in centered on rotary shaft, position
In with discharge port (entrance of muffler) symmetrical position in cylinder, the refrigeration being expelled to out of cylinder in muffler
The pulsation of agent gas is reduced by muffler.
Existing technical literature
Patent document
Patent document 1：Japanese Patent No. 3941809
Invention content
Problems to be solved by the invention
Even if can mainly reduce the pulsation of specific frequency content by muffler, it is also difficult to fully reduce other frequencies
The pulsation of ingredient.
When the pulsation that can not be fully reduced by muffler is expelled to the outside of muffler, the space in shell generates altogether
When ring, noise is generated.
Therefore, the object of the present invention is to provide a kind of arteries and veins that can also reduce and be unable to fully reduce on the inside of muffler
Dynamic rotary compressor.
Technical solution
The rotary compressor of the present invention is characterized in that having：The rotary shaft of rotation；Rotary compression mechanism has
Piston rotary set on rotary shaft and the cylinder configured with piston rotary；And muffler, the axis around rotary shaft configure, noise reduction
Device has：The fluid compressed by compression mechanism is accommodated in inside by muffler body；And flow path wall, in flow path wall and rotation
Axis or between the bearing portion that configures of axis of rotary shaft, being formed makes fluid flow out to the outside of muffler along the axial direction of rotary shaft
Specific length discharge duct, discharge duct has：First flow path portion is located at a circumferential part for rotary shaft；And the
Two flow path portions, in the circumferential with first flow path portion abut, and radially of the axis of rotation on size ratio first flow path portion it is big, sectional area
It is bigger than first flow path portion.
Since first flow path portion is different from the sectional area in second flow path portion, respectively in first flow path portion and second
The flow velocity of the fluid of road portion flowing is different.Therefore, the pressure for separately flowing into the fluid in first flow path portion and second flow path portion becomes
Dynamic phase-shifts, it is mutual from the pressure oscillation generation interference of first flow path portion and the fluid of second flow path portion outflow respectively
It offsets.
In the rotary compressor of the present invention, preferably discharge duct has multiple second flow path portions.
In the rotary compressor of the present invention, each sectional area in preferably multiple second flow path portions is mutually different.
In the rotary compressor of the present invention, preferably discharge duct is formed on the complete cycle around the axis of rotary shaft, and is had
Have in the multiple first flow path portions and multiple second flow path portions being circumferentially alternately arranged.
In the rotary compressor of the present invention, the part for being preferably formed as the flow path wall in second flow path portion is formed as section and is in
Substantially C fonts or section are in substantially V-shaped.
The rotary compressor of the present invention is characterized in that having：The rotary shaft of rotation；Rotary compression mechanism has
Piston rotary set on rotary shaft and the cylinder configured with piston rotary；And muffler, the axis around rotary shaft configure, noise reduction
Device has：The fluid compressed by compression mechanism is accommodated in inside by muffler body；And flow path wall, in flow path wall and rotation
Axis or between the bearing portion that configures of axis of rotary shaft, being formed makes fluid flow out to the outside of muffler along the axial direction of rotary shaft
Specific length discharge duct, discharge duct has：First flow path portion is located at a circumferential part for rotary shaft；And the
Two flow path portions, sectional area is bigger than first flow path portion, and first flow path portion is protruded from second flow path portion to radial outside.
In the rotary compressor of the present invention, preferably when the length of discharge duct is set as x0, will be in first flow path portion
The flow velocity of fluid be set as v1, by the flow velocity and v of the fluid in second flow path portion1Velocity ratio be set as α, defined frequency is set
For f when, n is natural number, α=n (v1/2fx0)+1 establishment.
Advantageous effect
Rotary compressor according to the present invention can also reduce the pulsation for being unable to fully reduce on the inside of muffler, because
This can inhibit the noise caused by pulsing.
Description of the drawings
Fig. 1 is the profilograph of the rotary compressor of first embodiment.
Fig. 2 (a) is the part for expanding rotary compressor shown in FIG. 1 and the figure shown.Fig. 2 (b) is to indicate muffler
Discharge duct figure.
Fig. 3 is the vertical view of muffler shown in Fig. 2 (a).
Fig. 4 (a) is the figure of the pulsation for the fluid for indicating to flow in the first flow path portion of the discharge duct of muffler, Fig. 4 (b)
It is the figure of the pulsation for the fluid for indicating to flow in the second flow path portion of the discharge duct of muffler.
Fig. 5 is the vertical view for the muffler that the rotary compressor of second embodiment has.
Fig. 6 is the vertical view for the muffler that the rotary compressor of the improvement of the present invention has.
Fig. 7 is the vertical view for the muffler that the rotary compressor of the other improvements example of the present invention has.
Fig. 8 is the vertical view for the muffler that the rotary compressor of the improvement of the present invention has.
Specific implementation mode
Hereinafter, being described with reference to embodiments of the present invention.
[first embodiment]
Compressor 1 shown in FIG. 1 keeps the gas refrigerant in accumulator (not shown) (gas-liquid separator) logical from piping 8,9
It crosses and sucks, compressed by compression mechanism 4.
Compressor 1 and accumulator constitute the refrigerating circulatory devices such as air regulator, refrigerator, and with for refrigerant circulation
Refrigerant circuit (not shown) connection.
Compressor 1 has：Motor 2 as power source；The rotary shaft rotated by the rotary driving force exported from motor 2
3 (bent axles)；By the rotary compression mechanism 4 for the rotary driving force driving transmitted via rotary shaft 3；Axis around rotary shaft 3 configures
Muffler 10,20；And shell 5.
Muffler 10,20 inhibits noise caused by the pulsation of the refrigerant compressed by compression mechanism 4.
Shell 5 accommodates motor 2, rotary shaft 3, compression mechanism 4 and muffler 10,20, and is formed as cylindric.
Motor 2 has：It is fixed on the stator 2A of the inner peripheral portion of shell 5；And it is configured at the rotor 2B of the inside of stator 2A.
Rotor 2B is rotated by being powered to the coil 2C set on stator 2A relative to stator 2A.
Rotary shaft 3 has：It is combined with rotor 2B and to the lower section of rotor 2B main shaft part 3A outstanding；Relative to main shaft part 3A
Axle center bias top crank-pin 3B；And the lower crank pin 3C of the axle center bias relative to main shaft part 3A.Lower part is bent
Axle center of the handle pin 3C relative to rotary shaft 3, (180 °) of the phase reversal towards top crank-pin 3B are eccentric.
Top crank-pin 3B is configured in the upper cylinder 412 of compression mechanism 4, and lower crank pin 3C is configured at compression mechanism
In 4 lower cylinder 422.
Illustrate compression mechanism 4 (Fig. 1).
So-called dual rotation type compression mechanism 4 has：Top compression mechanism 41, lower part compression mechanism 42, demarcation strip 4A, with
And rotatably support the upper bearing 6 and lower bearing 7 of rotary shaft 3.
The inside of the cylinder 412 of demarcation strip 4A separation top compressions mechanism 41 and the cylinder 422 of lower part compression mechanism 42
It is internal.
Top compression mechanism 41 is configured to：Set on the upper piston rotor 411 of top crank-pin 3B, configured with top
The upper cylinder 412 of piston rotary 411 and around main shaft part 3A axis configure top muffler 10.
Upper piston rotor 411 is embedded in the peripheral part of top crank-pin 3B, with being rotated in for upper piston rotor 411
Revolution in upper cylinder 412.
Refrigerant from piping 8 by by be inhaled into upper cylinder 412.
Upper bearing 6 has：The abutting part 6A abutted with the upper surface of upper cylinder 412；And it is upward from abutting part 6A
Side is prominent, and around the cylindric bearing portion 6B of the axis of rotary shaft 3 (main shaft part 3A) configuration.
Abutting part 6A is fixed on the inner peripheral portion of shell 5.
In upper bearing 6 by bolt 11B integrally installed with upper cylinder 412, top muffler 10, lower cylinder
422 and lower silencer 20.
The refrigerant being inhaled into upper cylinder 412 is compressed into the outer of the upper piston rotor 411 than pressing on revolution
The blade (not shown) of circumference more leans on the space in front of direction of rotation.
Compressed refrigerant from the discharge port (not shown) of the abutting part 6A for being formed in upper bearing 6 by by be discharged
Discharge duct 100 to top muffler 10, and between top muffler 10 and bearing portion 6B by by into shell 5
Motor 2 lower section space discharge.
It is identical as top compression mechanism 41, lower part compression mechanism 42 be configured to include：Set on the lower part of lower crank pin 3C
The lower part of piston rotary 421, the lower cylinder 422 configured with lower piston rotor 421 and the axis configuration around main shaft part 3A disappears
Sound device 20.
Gas refrigerant from piping 9 by by be inhaled into lower cylinder 422.
Lower bearing 7 has：The abutting part 7A abutted with the lower face of lower cylinder 422；And it is downward from abutting part 7A
Side is prominent, and around the cylindric bearing portion 7B of the axis of rotary shaft 3 (main shaft part 3A) configuration.
The refrigerant being inhaled into lower cylinder 422 is compressed with the revolution of lower piston rotor 421, and from being formed in
The discharge port (not shown) of the abutting part 7A of lower bearing 7 by by be expelled in lower silencer 20.
It is expelled to discharge duct 200 of the refrigerant in lower silencer 20 between lower silencer 20 and bearing portion 7B
By by be expelled to the inner space of shell 5, and from the notch 61A for the abutting part 6A for being formed in upper bearing 6, (not shown)
Hole is gone through, and is expelled to the space of the lower section of the motor 2 in shell 5.
As described above, the refrigerant compressed respectively by top compression mechanism 41 and lower part compression mechanism 42 is expelled to shell
The space of the lower section of motor 2 in 5.This refrigerant from the notch set on stator 2A, rotor 2B by by the top of motor 2
Spatial flow, and from the discharge pipe 5A set on the top of shell 5 by by be expelled to refrigerant circuit.
Top compression mechanism 41 and lower part compression mechanism 42 respectively according to the gyration period of piston rotary 411,421, with
Pressure oscillation (pulsation) from discharge port discharging refrigerant.By top compression mechanism 41 and lower part compression mechanism 42 from row
Exit port by by the pulsation of compression refrigerant that is sprayed respectively to muffler 10,20 reduces respectively in muffler 10,20.
Here, when the pulsation for being unable to fully reduce by muffler 10,20 is expelled to the outside of muffler 10,20, in shell 5
When the space of the lower section of interior motor 2 is empathized, noise is generated.
Therefore, the compressor 1 of present embodiment is also reduced is unable to fully the pulsation reduced in the inside of muffler 10,20,
Therefore the discharge duct 100,200 for flowing out to the refrigerant of the outside of muffler 10,20 respectively out of muffler 10,20 has spy
Sign.
First, illustrate the composition of top muffler 10 (hereinafter referred to as muffler 10).
As shown in Fig. 2 (a), muffler 10 has：Muffler body 11, in supporting for muffler body 11 and upper bearing 6
Space is formed between socket part 6A；And flow path wall 12, it is formed for refrigeration between flow path wall 12 and the bearing portion 6B of upper bearing 6
Agent flows out to the discharge duct 100 of the outside of muffler 10.Flow path wall 12 is formed at opening for the plane central portion of muffler 10
The peripheral part of mouth 10A.The bearing portion 6B of upper bearing 6 passes to this opening 10A.
Muffler body 11 and flow path wall 12 are integrally formed by metal materials such as aluminium alloys, such as by deep-draw deep processing.
Muffler body 11 freezes the compression compressed in upper cylinder 412 and sprayed from discharge port (not shown)
Agent is accommodated in inside, reduces the pulsation of compression refrigerant.
The space of the inside of muffler body 11 is for the refrigerant being ejected in muffler body 11, as corresponding
In the resistance of spatial volume carry out work, therefore refrigerant is pulsed through muffler 10 and decays.
Muffler body 11 is extended with the radial outside of defined straight radial flow path wall 12, is overlooked under visual angle and is formed as round
Shape.The end of the radial outside of muffler body 11 is anchored on upper bearing 6 at circumferential multiple positions by bolt 11B.
Bolt 11B is omitted in Fig. 3.
The inner circumferential end 111 of muffler body 11 is located at the top of abutting part 6A, and continuously to flow path wall 12.Here, noise reduction
The inner circumferential end 111 of device main body 11 via bending section 112 continuously to flow path wall 12, but inner circumferential end 111 can also directly it is continuous extremely
Flow path wall 12.Bending section 112 is bent by the top towards inner circumferential end 111 in a manner of convex.
It is fitted in a manner of the main frequency content of pulsation of the size, volume of muffler body 11 to be suitble to compression refrigerant
Locality determines.Main frequency content is for example positioned at the midband for the 500Hz~1kHz for being easy to generate noise.
The space of the inside of muffler body 11, which can also be divided into, once stores the refrigerant sprayed from discharge port
The region of inside and from this region it is secondary storage refrigerant outside region.Even such two-stage muffler, can also lead to
Cross the discharge duct 100 for constituting the outside for flowing out to muffler from the region in outside for refrigerant in such a way, obtain with
The 10 identical effect of muffler of present embodiment.
Flow path wall 12 is connected via bending section 112 with muffler body 11.
Axial direction of the flow path wall 12 from identical height along bearing portion 6B on complete cycle erects.The height of the upper end of flow path wall 12
It is fixed on complete cycle.
As shown in Fig. 2 (b), between the inner peripheral portion and the peripheral part of bearing portion 6B of flow path wall 12, it is equivalent to flow path wall 12
Height length being axially formed along rotary shaft 3 of discharge duct 100.
There may come a time when the height according to entire muffler 10, flow path wall 12 it is opposed with the peripheral part of rotary shaft 3 without with axis
Bearing portion 6B is opposed.In the case, it is formed with discharge duct between the inner peripheral portion of flow path wall 12 and the peripheral part of rotary shaft 3
100。
Lower silencer 20 (Fig. 1) be configured to 10 same shape of top muffler, in above-below direction with it is upper
The opposite direction of portion's muffler 10, the axis around lower bearing 7 configure.
Lower silencer 20 has flow path wall 22 between muffler body 21 and the bearing portion 7B of lower bearing 7, described
Flow path wall 22 forms the discharge duct 200 for the outside that muffler 20 is flowed out to for refrigerant.
Hereinafter, illustrating the composition of discharge duct 100,200.
Fig. 3 shows the flow path wall 12 of the bearing portion 6B and top muffler 10 for the upper bearing 6 that the axis around rotary shaft 3 configures
Between with defined flow path length x0The discharge duct 100 of formation.
The size of the discharge duct 100 radially of rotary shaft 3 changes on the circumferential D1 of rotary shaft 3.
The flow path length x of discharge duct 1000(Fig. 2 (b)) is identical on complete cycle.
The sectional area of entire discharge duct 100, that is, consider the axial area of the projection of discharge duct 100 to rotary shaft 3
Both the performance of compressor 1 and the pulsation reducing effect realized by muffler 10 determine.
About lower silencer 20, the vertical view of discharge duct 200 is omitted, but discharge duct 200 can also be with discharge
Flow path 100 is similarly constituted.
Hereinafter, the composition of discharge duct 100 is described in detail.
Discharge duct 100 has：Positioned at the first flow path portion 101 of a part of the circumferential D1 of rotary shaft 3 and in circumferential direction
The upper second flow path portions 102 abutted with first flow path portion 101 D1.The two in first flow path portion 101 and second flow path portion 102 it
Between, the sectional area in second flow path portion 102 is relatively large.
It compresses and is expelled to the compression refrigerant in muffler 10 on one side with pulsation, on one side respectively in first flow path portion
101 and second flow path portion 102 flow and flow out to the outside of muffler 10.The refrigerant flowed out from first flow path portion 101
Pressure oscillation and the pressure oscillation of the refrigerant flowed out from second flow path portion 102 are interfered with each other and are reduced.
Discharge duct 100 preferably has multiple first flow path portions 101 and multiple second flow path portions 102.Present embodiment
There are three first flow path portion 101 and three second flow path portions 102 for the tool of discharge duct 100.
Discharge duct 100 is preferably formed on the complete cycle around the axis of rotary shaft 3, first flow path portion 101 and second flow path portion
102 alternately configure on the circumferential D1 of rotary shaft 3 every one.
Second flow path portion 102 preferably substantially uniformly configures on circumferential D1.
Flow path wall 12 has：First wall portion 121 forms first between the first wall portion 121 and the peripheral part of bearing portion 6B
Flow path portion 101；And second wall portion 122, second flow path portion is formed between the second wall portion 122 and the peripheral part of bearing portion 6B
102.There is quantity identical with first flow path portion 101 in the first wall portion 121, the second wall portion 122 exists and 102 phase of second flow path portion
Same quantity.
First flow path portion 101 is formed as the section arc-shaped with rotary shaft 3 and bearing portion 6B concentric circles.First wall portion
121 is also identical.
First wall portion 121 separates defined compartment of terrain along the peripheral surface (barrel surface) of bearing portion 6B and is configured at the peripheral surface.
Interval between first wall portion 121 and the peripheral surface of bearing portion 6B, that is, the width in first flow path portion 101 is, for example, less than
1mm。
Second flow path portion 102 is in the shape swelled towards radial outside relative to the peripheral surface of bearing portion 6B.Second wall portion
122 is also identical.
The size ratio first flow path portion 101 radially of the rotary shaft 3 in second flow path portion 102 is big.
The section shape of second wall portion 122 corresponding with second flow path portion 102 can for example suitably determine for C fonts (or
Person's U-shaped), V-shaped etc..It is preferred that passing through the top most swelled from one end 122A for the second wall portion 122 being connected with the first wall portion 121
The other end 122C of portion 122B to the second wall portion 122 is formed as smooth shape, so as to from second flow path portion 102 by fluid
Flow path loss become smaller.
As an example, the second wall portion 122 of present embodiment be respectively relative to from circumferential D1 centrally through
It is substantially C-shaped that center line CL is symmetrically formed as section.Side from top 122B to the both sides of circumferential D1 that can also be to be extended from
Formula forms the second wall portion 122 in substantially V-shaped.
The section shape in first flow path portion 101 and second flow path portion 102 is in the rotary shaft 3 orthogonal with the paper of Fig. 3
It is fixed in axial direction, but it is not limited to this.
Discharge duct 100 is divided into the width of narrow first flow path portion 101 and flow path relative on circumferential D1
One flow path portion, 101 widened second flow path portion 102.Along rotary shaft 3 between these first flow path portions 101 and second flow path portion 102
Radial draw boundary line (for example, L1, L2) can assume first flow path portion 101 and second flow path using this boundary line as boundary
Each sectional area in portion 102.
The sectional area in first flow path portion 101 is smaller than the sectional area in second flow path portion 102.Therefore, it is flowed in first flow path portion 101
The velocity ratio of dynamic refrigerant is fast in the flow velocity for the refrigerant that second flow path portion 102 is flowed.
Fig. 4 indicate respectively from the inside of muffler body 11 flow into first flow path portion 101 refrigerant pulsation (a) and from
The inside of muffler body 11 flows into the pulsation (b) of the refrigerant in second flow path portion 102.Here, horizontal axis indicates the length of flow path
The distance x in direction.
In the relatively small first flow path portion 101 of sectional area, flow velocity is fast, therefore first flow path portion 101 shown in Fig. 4 (a)
Pressure oscillation p1Waveform and Fig. 4 (b) shown in second flow path portion 102 pressure oscillation p2Waveform compare, horizontal axis (x) side
To being stretched.
Injection separately flows into the first, second flow path portion 101,102 to the refrigerant in muffler body 11, away from first,
Flow path length x as defined in the beginning (x=0) in second flow path portion 101,1020With each section with the first, second flow path portion 101,102
The corresponding speed flowing of area, in the terminal (x=x of the first, second flow path portion 101,1020) flow out in shell 5.
Refrigerant in muffler body 11 can be considered as with identical phase separately flow into the first, second flow path portion 101,
102 each beginning (x=0), in addition, respectively in the pressure oscillation p of the refrigerant of the first, second flow path portion 101,102 flowing1、p2
Amplitude can be considered as it is identical.
Due to different in the flow velocity of the refrigerant of the first, second flow path portion 101,102 flowing respectively, from beginning (x=
0) to terminal (x=x0) pressure oscillation p1、p2Wave number it is different.Thus, be flowed into the first, second flow path portion 101,102
When identical phase the first, second flow path portion 101,102 terminal (x=x0) displacement.
Therefore, it declines by each pressure wave of the refrigerant by being flowed out from the first, second flow path portion 101,102 is interfering with each other
Subtract, external outflow of the pressure oscillation to muffler 10 can be adequately suppressed.It is preferred that at the end of the first, second flow path portion 101,102
Hold (x=x0), the phase difference 180 ° (π) of pressure waveform, that is be phase reversal, so that pressure wave is by interfering fully phase
Mutually offset.
It should be noted that pressure oscillation p shown in Fig. 41、p2Wave number be an example.
More than, in the present embodiment, as shown in calculation formula (I) below, in the first, second flow path portion 101,102
Terminal is phase reversal the mode that makes pressure wave offset each other, according to the frequency f setting flow path lengths x of pressure oscillation0With
The velocity ratio α of first, second flow path portion 101,102.
α=n (v1/2fx0)+1···(I)
N is natural number (1,2,3 ...)
Here, velocity ratio α is the flow velocity v of the refrigerant to be flowed in first flow path portion 1011With in second flow path portion 102
The flow velocity v of the refrigerant of flowing2In comparatively faster v1On the basis of velocity ratio (v2/v1)。
The calculation with calculation formula (I) equivalence can also be set by 1/ α of velocity ratio on the basis of the flow velocity of second flow path 102
Formula.Also allow to design the first, second flow path portion 101,102 using this formula.
Hereinafter, obtaining the process of above-mentioned calculation formula (I).
According to phase when being flowed into the first, second flow path portion 101,102 is identical and the identical condition of amplitude, by formula
(i) pressure oscillation p is indicated1、p2Wave.T indicates that time, P indicate the amplitude of pressure wave, k1、k2Indicate that wave number, ω indicate angular frequency
Rate.Pressure oscillation p1、p2In only wave number k1、k2It is different.
p1(x, t)=Psin (k1x-ωt)
p2(x, t)=Psin (k2x-ωt)···(i)
Here, when the flow velocity of the refrigerant in first flow path portion 101 is set as v1, by the refrigeration in second flow path portion 102
The flow velocity of agent is set as v2When,
v1=ω/k1 v2=ω/k2···(ii)
It will be with v1、v2In comparatively faster v1On the basis of velocity ratio be set as α, v1=α v2(α ＞ 1)
By formula (ii),
k2=α k1···(iii)
Solution comes from the pressure oscillation p (x=x synthesized when the terminal interflow of the first, second flow path portion 101,1020, t).Reference
Formula (iii).
P (x=x0, t)
=p1+P2=Psin (k1x0-ωt)+Psin(k2x0-ωt)
=2Psin { (α/2 1+) k1x0-ωt}cos{(1-α/2)k1x0}···(iv)
According to formula (iv), as cos { (α/2 1-) k1x0Item be 0 when, pressure wave is mutual each other by interference (synthesis)
It offsets.
The wave of y=cos θ is 0 (n=1,2,3 ...) at θ=n (pi/2),
(numerical expression 1)
Therefore, p (x at this time0, t) and it is 0.
Here, side discharge duct easy to implement smaller α.Therefore, when the pulsation drop for considering that realization is realized by minimum α
When low, n=1,
(numerical expression 2)
Therefore, when according to formula (v '), (ii) and the π f of ω=2,
(numerical expression 3)
When carrying out formula deformation to it, formula (I ') is obtained.
α=(v1/2fx0)+1···(I’)
The case where formula (I ') is n=1 in above-mentioned calculation formula (I).
Calculate formula (I), (I ') indicates the x that pressure wave is offset each other0With the relationship of α.
It shows to carry out design current velocity ratio α (v using formula (I ')2/v1) example.
Here, the range of frequency f substantially 50Hz~1kHz (1000Hz), the selected pressure oscillation ingredient for needing to reduce
Frequency.
x0Such as the left and right 10mm (0.01m) can be set to.
v1Such as according to the volume velocity and entire discharge duct 100 found out by the capacity and rotating speed of compression mechanism 41
Sectional area, be set as 0.1m/s~200m/s.
The value of above-mentioned parameter is applied to formula (I ').
When the condition according to above-mentioned value, by f=1000Hz and v1When=0.1m/s applies the situation for α minimums, obtain
To 5 × 10-1+ 1, when by f=500Hz and v1When=200m/s applies the situation for α maximums, 20+1 is obtained.
Frequency f by the pressure oscillation ingredient reduced as needed selectes velocity ratio α appropriate, from the first, second stream
Road portion 101,102 is flowed out and the pressure wave collaborated is offset each other.As a result, the outside for flowing out to muffler 10 can be reduced
Pressure oscillation.Therefore, it is avoided that the space in the lower section of motor 2 is empathized to inhibit noise.
According to the sectional area of selected velocity ratio α and entire discharge duct 100, the first, second flow path portion can be exported
101,102 each sectional area.Moreover, with respectively between bearing portion 6B and the first wall portion 121 and bearing portion 6B and the second wall
The mode that sectional area appropriate is given between portion 122 shapes muffler 10 preferably.
More than, it is illustrated for example with the discharge duct 100 of top muffler 10, but about lower silencer 20
Discharge duct 200, also using identical calculations formula (I), formula (I ') export velocity ratio α, and with respectively to first flow path portion 101
And the mode of the given suitable sectional area in second flow path portion 102 shapes muffler 20 preferably.
Such as the explanation done above, the pressure wave of thus phase-shifts is preferably flowed in the first, second flow path portion 101,102
Each other collaborate when offset in the case of, first flow path portion 101 is adjacent with second flow path portion 102, from the first, second flow path portion 101,
The refrigerant stream outflow of 102 terminal outflow is next to be collaborated, and each pressure wave generates interference.
In this aspect, as shown in figure 3, in the present embodiment, in discharge duct 100, there are multiple first flow path portions 101
With multiple second flow path portions 102, and these first, second flow path portions 101,102 are alternately arranged on the complete cycle of rotary shaft 3,
Therefore it is advantageous.That is first flow path portion 101 is distributed in rotation with the position adjacent on circumferential D1 of second flow path portion 102
On the complete cycle of shaft 3, the outflow of the refrigerant stream flowed out from the first, second flow path portion 101,102 is next, and no matter pressure wave is the
One flow path portion 101 which position adjacent with second flow path portion 102 all generates interference, therefore can efficiently reduce pulsation.
It is assumed that in discharge duct 100 there is only a second flow path portion 102 (for example, 102A), discharge duct 100 remains
Remaining be first flow path portion 101, then can obtain pulsation reducing effect position be limited to single second flow path portion 102 left and right it is adjacent
Position.
That is such as present embodiment, it is distributed by the position for keeping first flow path portion 101 adjacent with second flow path portion 102
In the circumferential D1 of rotary shaft 3, the interference of pressure wave is generated in the wide scope of circumferential D1, therefore can efficiently reduce pulsation.
In the present embodiment, the both sides of muffler 10,20 are set separately comprising the first, second different flow path of sectional area
The discharge duct 100,200 in portion, therefore can more fully reduce the pulsation transmitted into shell 5 out of muffler 10,20.
But, the discharge duct for also allowing either one setting of only muffler 10,20 to include the first, second flow path portion, separately
The discharge duct of one side is for example formed as circular around the axis of rotary shaft 3.[second embodiment]
Then, illustrate second embodiment of the present invention with reference to Fig. 5.
Hereinafter, being illustrated centered on the item different from first embodiment.To same as the first embodiment
It constitutes and marks identical symbol.
As shown in figure 5, the discharge duct 300 of second embodiment being formed between muffler 30 and bearing portion 6B has
Multiple second flow path portion 302A, 302B, 302C.
Muffler 30 can also be applied to constitute the muffler (the 10 of Fig. 1) of top compression mechanism 41 and constitute lower part pressure
Either one or two of muffler (the 20 of Fig. 1) of contracting mechanism 42 (Fig. 1).
The sectional area of second flow path portion 302A, 302B, 302C are mutually different.Second flow path portion 302A, 302B, 302C's is each
Sectional area considers that the frequency of the ripple component reduced is needed to determine.
For example, second flow path portion 302A corresponds to 800Hz, second flow path portion 302B corresponds to 900Hz, third flow path portion
302C corresponds to 1kHz.
Either which sectional area of second flow path portion 302A~302C, by using above-mentioned calculation formula (I) or
(I ') exports the velocity ratio α with adjacent first flow path portion 101 to set.
According to second embodiment, compared with first embodiment, the pulsation of extensive frequency domain can be corresponded to.
In discharge duct 300, second flow path portion 302A~302C on the circumferential D1 of rotary shaft 3 with first flow path portion
101 are alternately arranged, therefore each position adjacent with second flow path portion 302A~302C in first flow path portion 101, can efficiently drop
Low pulse.
Fig. 6 shows the muffler 50 of the improvement of the present invention.
The discharge duct 500 and first embodiment, second embodiment being formed between muffler 50 and bearing portion 6B
It compares, including many flow path portions and being formed as petal-shaped.Here, section is in eight first flow path portions 501 of arc-shaped and eight
Second flow path portion 502 is contained in discharge duct 500.
Muffler 50 can also be applied to constitute the muffler (the 10 of Fig. 1) of top compression mechanism 41 and constitute lower part pressure
Either one or two of muffler (the 20 of Fig. 1) of contracting mechanism 42.
The sectional area in first flow path portion 501 and second flow path portion 502 can use above-mentioned calculation formula (I), (I ') certainly respectively
It is fixed.
The quantity in first flow path portion 501 and the quantity in second flow path portion 502 are more, therefore first flow path portion 501 and
Quantity of two flow path portions 502 at position adjacent circumferential D1 is also more.Therefore, according to this example, by respectively from the first, second flow path
The interference of the pressure wave of refrigerant that portion 501,502 flows out and collaborates, can efficiently reduce pulsation.
In this example, there are two kinds of different second flow path portions 502 (A) of sectional area, 502 (B).These second flow path portions
502 (A), 502 (B) sectional area can be determined respectively by above-mentioned calculation formula (I), (I ') corresponding to different frequencies.
Fig. 7 shows the muffler 60 of the other improvements example of the present invention.
Muffler 60 has muffler body 11 and the cylindrical flow path wall 62 with 3 concentric circles of rotary shaft.
It is recessed in axially extending multiple slot 6C and is formed in the peripheral part of bearing portion 6B.By the way that there are these slots 6C, axis
The multiple first flow path portions 601 and sectional area that discharge duct 600 between bearing portion 6B and flow path wall 62 has sectional area relatively small
Relatively large multiple second flow path portions 602.
The sectional area in first flow path portion 601 and second flow path portion 602 can use above-mentioned calculation formula (I), (I ') certainly respectively
It is fixed.
By changing the depth and width of multiple slot 6C, can make sectional area multiple second flow path portions 602 between each other not
Together, correspond to the ripple component of multiple frequencies.
Fig. 8 shows the muffler 70 of the another other improvements example of the present invention.
Muffler 70 has muffler body 11, the substantially cylindric flow path wall 72 and stream with 3 concentric circles of rotary shaft
Discharge duct 700 between road wall 72 and bearing portion 6B.Flow path wall 72 has：It is outstanding to radial outside in a circumferential part
Protruding portion 721 and arc sections 722 as the part other than protruding portion 721.Multiple protruding portion 721 and multiple arc sections 722
It is alternately arranged in the circumferential direction of flow path wall 72.
By mutually opposed wall 721A, 721B close in the state of turn back in a manner of the inside of protruding portion 721 that is formed,
There are the first flow path portions 701 of discharge duct 700.
Between the inner peripheral portion and the peripheral part of bearing portion 6B of arc sections 722, there are the second flow path portions of discharge duct 700
702。
Interval between arc sections 722 and bearing portion 6B than first embodiment the first wall portion 121 and bearing portion 6B it
Between interval it is wide, therefore the sectional area in second flow path portion 702 is bigger than the sectional area in first flow path portion 701.
Determine section in first flow path portion 701 and second flow path portion 702 respectively by using above-mentioned calculation formula (I), (I ')
Area can be efficiently by the interference of the pressure wave for the refrigerant for flowing out and collaborating from the first, second flow path portion 701,702 respectively
Ground reduces pulsation.
By changing the length outstanding of multiple protruding portion 721, the interval of wall 721A, 721B, sectional area can be made multiple
The mutual difference in second flow path portion 702 corresponds to the ripple component of multiple frequencies.
Than that described above, without departing from the purport of the present invention, then can to the composition enumerated in the above embodiment into
Row accepts or rejects selection, or suitably changes and constituted for other.
The first flow path portion of discharge duct in the present invention is not formed as the arc-shaped with 3 concentric circles of rotary shaft necessarily.
In addition, in the mutual of multiple first flow path portions, sectional area can also be different.As long as first flow path portion with rotary shaft 3 or
The gap narrower than second flow path portion is formed between person's bearing portion 6B, and it is enough.
In addition, on the circumferential D1 of rotary shaft 3, first flow path portion is not alternately arranged necessarily with second flow path portion.For example,
In composition shown in Fig. 6, also the second flow path portion 502B different from the sectional area of second flow path portion 502A is allowed to be located at second
The side of flow path portion 502A.
In addition, the first flow path portion of discharge duct and each sectional area in second flow path portion, configuration etc., according to desired reduction
Frequency f, flow path length x0, compressor performance and pulsation reducing effect etc., calculation formula (I), (I ') can be used suitably to set
It is fixed.
Discharge duct in the present invention is not necessarily continuous in the complete cycle of the circumferential D1 of rotary shaft 3.The flow path wall of muffler
12 can also contact in a part of circumferential D1 with the peripheral part of bearing portion 6B.
In addition it is also possible to be configured with partition member on the boundary in first flow path portion and second flow path portion.In this case,
One flow path portion is abutted with second flow path portion across partition member.It could be used that in this case and calculate formula (I), (I ') decision by separating
Each sectional area for the first, second flow path portion that component divides.
In particular, as shown in FIG. 6 constituted like that, partition member is arranged in a fairly large number of in second flow path portion
When be easily formed.
The compression mechanism for being equipped on the compressor of the present invention is not limited to dual rotation type compression mechanism 4, can also be to have
Single rotary compression mechanism of one group of cylinder and piston rotary and muffler.
In addition, the power source of the compressor as the present invention, other than motor, such as also allows engine etc..
Symbol description
1 compressor
2 motors
2A stators
2B rotors
2C coils
3 rotary shafts
3A main shaft parts
The tops 3B crank-pin
3C lower crank pins
4 compression mechanisms
4A demarcation strips
5 shells
5A discharge pipes
6 upper bearings
6A abutting parts
6B bearing portions
6C slots
7 lower bearings
7A abutting parts
7B bearing portions
8,9 piping
10 top mufflers
10A is open
11 muffler bodies
11B bolts
12 flow path walls
20 lower silencers
21 muffler bodies
22 flow path walls
30 mufflers
302A, 302B, 302C second flow path portion
41 top compression mechanisms
42 lower part compression mechanisms
50 mufflers
501 first flow path portions
502,502A, 502B second flow path portion
60 mufflers
62 flow path walls
70 mufflers
72 flow path walls
100 discharge duct
101 first flow path portions
102 second flow path portions
111 inner circumferential ends
112 bending sections
121 first wall portions
122 second wall portions
The one end 122A
At the top of 122B
The 122C other ends
200 discharge duct
411 upper piston rotors
412 upper cylinders
421 lower piston rotors
422 lower cylinders
500 discharge duct
600 discharge duct
601 first flow path portions
602 second flow path portions
700 discharge duct
701 first flow path portions
702 second flow path portions
721 protruding portions
722 arc sections
The circumferential direction of D1 rotary shafts
Claims (according to the 19th article of modification of treaty)
[1. after modification]
A kind of rotary compressor, which is characterized in that have：
The rotary shaft of rotation；
Rotary compression mechanism has the piston rotary for being set to the rotary shaft and the cylinder configured with the piston rotary；
And
Muffler, the axis around the rotary shaft configure,
The muffler has：
The fluid compressed by the compression mechanism is accommodated in inside by muffler body；And
Flow path wall is formed in the flow path wall and the rotary shaft or between the bearing portion of the axis configuration of the rotary shaft
The fluid is set to flow out to the discharge duct of the specific length of the outside of the muffler along the axial direction of the rotary shaft,
The discharge duct has：
First flow path portion is located at a circumferential part for the rotary shaft；And
Second flow path portion, in the circumferential direction with the first flow path portion abut, and it is described radially of the axis of rotation on size ratio
The first flow path portion is big, and sectional area is bigger than the first flow path portion,
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion occur interference and
It cancels out each other.
2. rotary compressor according to claim 1, which is characterized in that
The discharge duct has multiple second flow path portions.
3. rotary compressor according to claim 2, which is characterized in that
Each sectional area in multiple second flow path portions is mutually different.
4. rotary compressor according to claim 2, which is characterized in that
The discharge duct is formed on the complete cycle around the axis of the rotary shaft, and with it is described be circumferentially alternately arranged it is multiple
The first flow path portion and multiple second flow path portions.
5. rotary compressor according to claim 3, which is characterized in that
The discharge duct is formed on the complete cycle around the axis of the rotary shaft, and with it is described be circumferentially alternately arranged it is multiple
The first flow path portion and multiple second flow path portions.
6. rotary compressor according to any one of claim 1 to 5, it is characterised in that
The part for the flow path wall for forming the second flow path portion is formed as that section is substantially C-shaped or section is in substantially V
Font.
7. a kind of rotary compressor, which is characterized in that have：
The rotary shaft of rotation；
Rotary compression mechanism has the piston rotary for being set to the rotary shaft and the cylinder configured with the piston rotary；
And
Muffler, the axis around the rotary shaft configure,
The muffler has：
The fluid compressed by the compression mechanism is accommodated in inside by muffler body；And
Flow path wall is formed in the flow path wall and the rotary shaft or between the bearing portion of the axis configuration of the rotary shaft
The fluid is set to flow out to the discharge duct of the specific length of the outside of the muffler along the axial direction of the rotary shaft,
The discharge duct has：
First flow path portion is located at a circumferential part for the rotary shaft；And
Second flow path portion, sectional area are bigger than the first flow path portion,
The first flow path portion is protruded from the second flow path portion to radial outside.
8. according to the rotary compressor described in claim 1 to 5, any one of 7, which is characterized in that
When the length of the discharge duct is set as x0,
The flow velocity of the fluid in the first flow path portion is set as v1,
By the flow velocity and v of the fluid in the second flow path portion1Velocity ratio be set as α,
When defined frequency is set as f,
N is natural number,
α=n (v1/2fx0)+1 establishment.
9. rotary compressor according to claim 6, which is characterized in that
When the length of the discharge duct is set as x0,
The flow velocity of the fluid in the first flow path portion is set as v1,
By the flow velocity and v of the fluid in the second flow path portion1Velocity ratio be set as α,
When defined frequency is set as f,
N is natural number,
α=n (v1/2fx0)+1 establishment.
[10. after modification]
Rotary compressor according to claim 7, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
11. rotary compressor according to claim 6, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
12. rotary compressor according to claim 9, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
Claims (12)
1. a kind of rotary compressor, which is characterized in that have：
The rotary shaft of rotation；
Rotary compression mechanism has the piston rotary for being set to the rotary shaft and the cylinder configured with the piston rotary；
And
Muffler, the axis around the rotary shaft configure,
The muffler has：
The fluid compressed by the compression mechanism is accommodated in inside by muffler body；And
Flow path wall is formed in the flow path wall and the rotary shaft or between the bearing portion of the axis configuration of the rotary shaft
The fluid is set to flow out to the discharge duct of the specific length of the outside of the muffler along the axial direction of the rotary shaft,
The discharge duct has：
First flow path portion is located at a circumferential part for the rotary shaft；And
Second flow path portion, in the circumferential direction with the first flow path portion abut, and it is described radially of the axis of rotation on size ratio
The first flow path portion is big, and sectional area is bigger than the first flow path portion.
2. rotary compressor according to claim 1, which is characterized in that
The discharge duct has multiple second flow path portions.
3. rotary compressor according to claim 2, which is characterized in that
Each sectional area in multiple second flow path portions is mutually different.
4. rotary compressor according to claim 2, which is characterized in that
The discharge duct is formed on the complete cycle around the axis of the rotary shaft, and with it is described be circumferentially alternately arranged it is multiple
The first flow path portion and multiple second flow path portions.
5. rotary compressor according to claim 3, which is characterized in that
The discharge duct is formed on the complete cycle around the axis of the rotary shaft, and with it is described be circumferentially alternately arranged it is multiple
The first flow path portion and multiple second flow path portions.
6. rotary compressor according to any one of claim 1 to 5, which is characterized in that
The part for the flow path wall for forming the second flow path portion is formed as that section is substantially C-shaped or section is in substantially V
Font.
7. a kind of rotary compressor, which is characterized in that have：
The rotary shaft of rotation；
Rotary compression mechanism has the piston rotary for being set to the rotary shaft and the cylinder configured with the piston rotary；
And
Muffler, the axis around the rotary shaft configure,
The muffler has：
The fluid compressed by the compression mechanism is accommodated in inside by muffler body；And
Flow path wall is formed in the flow path wall and the rotary shaft or between the bearing portion of the axis configuration of the rotary shaft
The fluid is set to flow out to the discharge duct of the specific length of the outside of the muffler along the axial direction of the rotary shaft,
The discharge duct has：
First flow path portion is located at a circumferential part for the rotary shaft；And
Second flow path portion, sectional area are bigger than the first flow path portion,
The first flow path portion is protruded from the second flow path portion to radial outside.
8. according to the rotary compressor described in claim 1 to 5, any one of 7, which is characterized in that
When the length of the discharge duct is set as x0,
The flow velocity of the fluid in the first flow path portion is set as v1,
By the flow velocity and v of the fluid in the second flow path portion1Velocity ratio be set as α,
When defined frequency is set as f,
N is natural number,
α=n (v1/2fx0)+1 establishment.
9. rotary compressor according to claim 6, which is characterized in that
When the length of the discharge duct is set as x0,
The flow velocity of the fluid in the first flow path portion is set as v1,
By the flow velocity and v of the fluid in the second flow path portion1Velocity ratio be set as α,
When defined frequency is set as f,
N is natural number,
α=n (v1/2fx0)+1 establishment.
10. according to the rotary compressor described in claim 1 to 5, any one of 7, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
11. rotary compressor according to claim 6, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
12. rotary compressor according to claim 9, which is characterized in that
The pressure oscillation of the fluid flowed out respectively from the first flow path portion and the second flow path portion generate interference and
It cancels out each other.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-084924 | 2016-04-21 | ||
| JP2016084924A JP6683532B2 (en) | 2016-04-21 | 2016-04-21 | Rotary compressor |
| PCT/JP2017/010498 WO2017183367A1 (en) | 2016-04-21 | 2017-03-15 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108496009A true CN108496009A (en) | 2018-09-04 |
Family
ID=60116029
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780007733.XA Pending CN108496009A (en) | 2016-04-21 | 2017-03-15 | Rotary compressor |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3399193A4 (en) |
| JP (1) | JP6683532B2 (en) |
| CN (1) | CN108496009A (en) |
| WO (1) | WO2017183367A1 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10176691A (en) * | 1996-12-17 | 1998-06-30 | Daikin Ind Ltd | Rotary compressor |
| JP2006214376A (en) * | 2005-02-04 | 2006-08-17 | Daikin Ind Ltd | Muffler structure for compressor |
| CN202001312U (en) * | 2011-04-19 | 2011-10-05 | 上海日立电器有限公司 | Silencer for rotary compressor |
| CN204610284U (en) * | 2014-02-21 | 2015-09-02 | 东芝开利株式会社 | Rotary compressor and refrigerating circulatory device |
-
2016
- 2016-04-21 JP JP2016084924A patent/JP6683532B2/en active Active
-
2017
- 2017-03-15 WO PCT/JP2017/010498 patent/WO2017183367A1/en active Application Filing
- 2017-03-15 CN CN201780007733.XA patent/CN108496009A/en active Pending
- 2017-03-15 EP EP17785709.1A patent/EP3399193A4/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10176691A (en) * | 1996-12-17 | 1998-06-30 | Daikin Ind Ltd | Rotary compressor |
| JP2006214376A (en) * | 2005-02-04 | 2006-08-17 | Daikin Ind Ltd | Muffler structure for compressor |
| CN202001312U (en) * | 2011-04-19 | 2011-10-05 | 上海日立电器有限公司 | Silencer for rotary compressor |
| CN204610284U (en) * | 2014-02-21 | 2015-09-02 | 东芝开利株式会社 | Rotary compressor and refrigerating circulatory device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017194016A (en) | 2017-10-26 |
| EP3399193A4 (en) | 2018-12-12 |
| EP3399193A1 (en) | 2018-11-07 |
| WO2017183367A1 (en) | 2017-10-26 |
| JP6683532B2 (en) | 2020-04-22 |
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Application publication date: 20180904 |