CN101424267B - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN101424267B CN101424267B CN2008101708924A CN200810170892A CN101424267B CN 101424267 B CN101424267 B CN 101424267B CN 2008101708924 A CN2008101708924 A CN 2008101708924A CN 200810170892 A CN200810170892 A CN 200810170892A CN 101424267 B CN101424267 B CN 101424267B
- Authority
- CN
- China
- Prior art keywords
- suction
- rotary compressor
- open end
- chamber
- suction chamber
- 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.)
- Expired - Fee Related
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 15
- 238000005057 refrigeration Methods 0.000 claims description 17
- 239000003795 chemical substances by application Substances 0.000 claims description 14
- 210000003660 reticulum Anatomy 0.000 claims description 10
- 238000007789 sealing Methods 0.000 claims description 9
- 239000007921 spray Substances 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 7
- 239000007788 liquid Substances 0.000 description 6
- 230000004044 response Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 230000002889 sympathetic effect Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000000644 propagated effect Effects 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- 230000005945 translocation Effects 0.000 description 1
- 230000017105 transposition Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
- F04C18/30—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
-
- 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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
-
- 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
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
- Y10S417/902—Hermetically sealed motor pump unit
Abstract
The present invention provides a rotary compressor which has an effect that the roller of rotary compressor shields a suction inlet and effectively uses the resonance phenomenon, and simultaneously can efficiently operates the compressor with a large-amplitude rotation speed range. The rotary compressor comprises the following components: a motor in a closed container; an eccentric part which is connected with the motor; a suction chamber which is formed by the roller and a cylinder that are installed at the periphery of eccentric part; an energy storing device which is installed at the suction side of suction chamber; and a suction pipe which has an opening in the energy storing device. On the assumption that the length of suction flow path from the open end of suction pipe to the open end of suction inlet is L[m], the maximum speed of a compressor (1) is fm[Hz], the acoustic speed of gas refrigerant is C[m/s], and the rotation angle between a blade and a line segment between the rotation center of roller and the center of eccentric part is theta s[rad] when observed from the blade which separates the suction side and ejection side of suction chamber when the suction of suction chamber is finished, the following relationship is satisfied: L=(pi-theta s)/(4pi*fm).
Description
Technical field
The present invention relates to a kind of rotary compressor and longitudinal type two-cylinder rotary compressor with transducer driving of using in the air conditioner of refrigeration cycle.
Background technique
All the time, known in being used to the rotary compressor of refrigeration cycle have a kind of resonance phenomenon, and under the specific frequency that exists with ... suction passage length L [m], volumetric efficiency (also claim volumetric efficiency, suck fill factor) becomes maximum.At this, the military order volumetric efficiency is called resonant frequency (the translocation number resonates back) fn[Hz for maximum frequency].In addition, the suction passage length L is the length till open end to the open end of the suction port of suction chamber of suction pipe.
Relevant with above-mentioned resonance phenomenon, for example known have a disclosed structure in a kind of patent documentation 1.In existing compressor as shown in figure 14, following in frequency increases from low speed side, and volumetric efficiency increases, substantially near certain value.And then, along with frequency near resonant frequency fn, volumetric efficiency increases, volumetric efficiency be a maximum when resonant frequency fn.Under the frequency higher than resonant frequency fn, volumetric efficiency reduces gradually, near certain value.Usually in compressor, be well known that the increase of following in frequency, mechanical loss or noise, vibration increase.If utilize above-mentioned resonance phenomenon, then exist the frequency that does not increase compressor just can increase the advantage of the ability of air conditioner.
Make the suction passage length L of such resonance phenomenon generation and the relation of resonant frequency fn, for example described in patent documentation 1, patent documentation 2 and the patent documentation 3.
Utilize a sympathetic response of the gas column sympathetic response in the suction passage in the suction passage length L [m] described in the patent documentation 2,
L＝λC/(2π·fn)…(1)
λ：π/2。
Here, C is the velocity of sound (speed of the pressure-wave emission of refrigeration agent) [m/s] of refrigeration agent.λ=pi/2 is brought in the formula (1), then obtained
L＝C/(4·fn)…(2)。
In patent documentation 1, with respect to patent documentation 2, the signature of revisal suction chamber removes amount V[m
3],, the flowing path section area A [m of suction pipe
2] influence,
fn＝(2m-1)C/{4(L+V/A)}…(3)
m＝1、2、3、…。
When the big first resonance composition of the influence of volumetric efficiency is m=1, formula (3) transposition is handled, then obtain
L＝C/(4·fn)-(V/A)…(4)。
In patent documentation 3, carry out based on the revisal of testing with respect to patent documentation 2,
L＝T·C/4-0.2…(5)。Here, T is suction stroke cycle [s], if with in the T=1/fn substitution formula (5), then obtain
L＝C/(4·fn)-0.2…(6)。
[patent documentation 1] Japanese kokai publication sho 64-15489 communique (the 3rd page, formula (1), the 5th page, Fig. 4)
[patent documentation 2] Japanese kokai publication hei 4-103971 communique (second page, formula (1))
[patent documentation 3] Japanese kokai publication sho 57-122192 communique (second page, formula (2))
But, in existing rotary compressor, mainly be conceived to the gas column sympathetic response of suction passage length L, do not consider that the distinctive roller of rotary compressor (roller) blocks the phenomenon of suction port (not considering that roller blocks the refrigerant pressure wave reflection that suction port causes).Therefore, shown in (2), formula (4), formula (6), the relation of resonant frequency fn and suction passage length L has nothing in common with each other, thereby exists the problem that practical design is suitable for difficulty.
Summary of the invention
The objective of the invention is to, the effect that research rotary compressor distinctive roller in theoretical property ground blocks suction port, and seek the relation of resonant frequency fn and suction passage length L, thereby resonance phenomenon is applied flexibly effectively in rotary compressor or two-cylinder rotary compressor.
In order to solve described problem, the present invention mainly adopts following formation.
A kind of rotary compressor is provided, and it has: the motor of the top configuration in seal container; The running shaft that has eccentric part and be connected with described motor; The suction chamber that forms by roller that is provided with in the periphery of described eccentric part and cylinder; The accumulator that is provided with in the suction side of described suction chamber; Suction pipe at described accumulator inner opening; And the sealing suction fitting that connects the suction port of described suction pipe and described suction chamber, this rotary compressor constitutes: cause that the resonant frequency of the described rotary compressor of resonance phenomenon is defined as the highest frequency of described rotary compressor, described resonance phenomenon is that the refrigeration agent of described suction chamber sucks the phenomenon of fill factor for maximum, obtain when the suction of described suction chamber finishes, from the suction side and the blade of ejection side and the angle of swing that line segment became at the center of rotating center that is connected described roller and described eccentric part that separates described suction chamber, suction passage length L [m] till the open end of described suction pipe to the open end of described suction port is by the highest frequency fm[Hz of the described rotary compressor that limits] and described angle of swing θ s[rad] determine according to following formula
L＝(π-θs)/(4π·fm)。
In addition, provide a kind of rotary compressor, it has: the motor of the top configuration in seal container; The running shaft that has eccentric part and be connected with described motor; The suction chamber that forms by roller that is provided with in the periphery of described eccentric part and cylinder; The accumulator that is provided with in the suction side of described suction chamber; Suction pipe at described accumulator inner opening; And the sealing suction fitting that connects the suction port of described suction pipe and described suction chamber, this rotary compressor constitutes: the suction passage length of establishing till the open end of described suction pipe to the open end of described suction port is L[m], if the highest frequency of described compressor is fm[Hz], if the velocity of sound of gas refrigerant is C[m/s], the angle of swing that line segment became from the suction side that separates described suction chamber and the blade that sprays side and the center of rotating center that is connected described roller and described eccentric part when the suction that is located at described suction chamber finishes is θ s[rad], then this moment, the relation of L=(π-θ s)/(4 π fm) is set up.
In addition, provide a kind of longitudinal type two-cylinder rotary compressor, it has: the motor of the top configuration in seal container; The running shaft that has two eccentric parts and be connected with described motor; Two suction chambers that the roller dividing plate setting that connects across described running shaft, that be provided with respectively by the periphery at described two eccentric parts and cylinder form; The accumulator that is provided with in the suction side of described two suction chambers; At described accumulator inner opening and have two suction pipes of the roughly L word shape of curved part; And two sealing suction fittings that the suction port of described two suction pipes and described two suction chambers is connected, described longitudinal type two-cylinder rotary compressor constitutes: described two suction pipes form different paths respectively, make the suction passage equal in length till open end to the open end of each suction port of each suction pipe, and be made as L[m respectively], if the highest frequency of described compressor is fm[Hz], if the velocity of sound of gas refrigerant is C[m/s], the angle of swing that line segment became from the suction side that separates each suction chamber and the blade that sprays side and the center of the rotating center that is connected each roller and each eccentric part when the suction that is located at described two suction chambers finishes is θ s[rad], at this moment, the relation of L=(π-θ s)/(4 π fm) is set up.
(invention effect)
According to the present invention, comprise that roller blocks the effect of suction port and applies flexibly resonance phenomenon effectively, compressor efficiently can turn round in the big speed range of amplitude simultaneously.
Description of drawings
Fig. 1 is the sectional arrangement drawing of the rotary compressor of first mode of execution of the present invention;
Fig. 2 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=0 constantly;
Fig. 3 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=L/C constantly;
Fig. 4 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=2L/C constantly;
Fig. 5 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=3L/C constantly;
Fig. 6 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=4L/C constantly;
Fig. 7 be expression first mode of execution rotary compressor angle of swing and suck the figure of relation of the time rate of change of volume;
Fig. 8 is the figure of the relation of the resonance speed fn of rotary compressor of expression first mode of execution and suction passage length L;
Fig. 9 is the figure of the relation of the rotating speed of rotary compressor of expression first mode of execution and full adiabatic efficiency;
Figure 10 is the sectional arrangement drawing of the longitudinal type two-cylinder rotary compressor of second mode of execution of the present invention;
Figure 11 is the figure of the relation of the rotating speed of longitudinal type two-cylinder rotary compressor of expression second mode of execution and volumetric efficiency;
Figure 12 is the figure of the relation of the rotating speed of longitudinal type two-cylinder rotary compressor of expression second mode of execution and full adiabatic efficiency;
Figure 13 is the sectional arrangement drawing of the longitudinal type two-cylinder rotary compressor of the 3rd mode of execution of the present invention;
Figure 14 is the figure of the relation of the rotating speed of the expression rotary compressor relevant with prior art and volumetric efficiency.
Among the figure:
1-compressor; 2-running shaft; 3-seal container; 4-motor; 5-eccentric part; 10-cylinder; 11-roller; 12-through hole; 13-suction port; 14-inner space; 15-sealing suction fitting (seal suction); 16-accumulator (accumulator); 18-suction pipe; 20-inaccessible plate; 21-net; 22-reticulum; 23-projection (convex form portion); 24-ostium; 30-suction chamber; 31-dividing plate; 32-suction pipe curved part.
Embodiment
About the rotary compressor of embodiments of the present invention, carry out following detailed description with reference to accompanying drawing.First mode of execution is with reference to Fig. 1～Fig. 9, and second mode of execution is with reference to Figure 10～Figure 12, and the 3rd mode of execution is with reference to Figure 13.
(first mode of execution)
Fig. 1 is the sectional arrangement drawing of the rotary compressor of first mode of execution of the present invention.First mode of execution is the compressor of the use in refrigeration system of use refrigeration agent R410A.Compressor 1 has the seal container 3 that is formed by bottom 6, cap 7 and trunk 8.Be provided with motor 4 above seal container 3 inside, motor 4 has stator and the rotor that is driven by transducer.The running shaft 2 that is connected with motor 4 has eccentric part 5, and running shaft 2 is had supplementary bearing 19 supportings of the main bearing 9 of end plate portion and the concavity with end plate portion., and conclude element (not shown) by bolt etc. and constitute one from motor 4 side stacked above one another main bearings 9, roughly cylinder 10 cylindraceous, supplementary bearing 19 and be used for the roughly discoideus inaccessible plate 20 that the inside with the inside of supplementary bearing 19 and seal container 3 separates with respect to this running shaft 2.Main bearing 9 is fixed on the inwall of trunk 8 by welding.
Gas refrigerant as the action fluid, shown in the arrow of Fig. 1, flow through intake channel 25, be arranged on ostium 24, suction pipe 18 (refrigeration agent that flows into intake channel 5 is inhaled into suction pipe 18 by ostium 24), sealing suction fitting 15 and suction port 13 on the reticulum 22 in the accumulator 16, be inhaled in the suction chamber 30.Suction pipe 18 is for having the roughly L word shape of curved part 32.In addition, be provided with the net 21 of the foreign matter that is used for catching refrigeration agent at the upstream side of reticulum 22.Reticulum 22 is welded in the container 17 of accumulator 16 long on the short transverse.
And then compressed gas refrigerant is ejected into the inner space 14 that is formed by supplementary bearing 19 and inaccessible plate 20 in cylinder 10, and flows in the seal container 3 by through hole 12 and sound break 27.By the gap of motor 4, from outlet pipe 26 be ejected thereafter.
Secondly, as the interaction of the gas column sympathetic response in roller 11 and the suction line, use Fig. 2 to Fig. 6 that the resonance phenomenon of present embodiment is described.Fig. 2 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=0 constantly.Fig. 3 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=L/C constantly.Fig. 4 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=2L/C constantly.Fig. 5 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=3L/C constantly.Fig. 6 is the figure of the suction condition when being illustrated in the rotary compressor of first mode of execution t=4L/C constantly.
In Fig. 2～Fig. 6,, use with the periodic rectangular wave of synchronization and represent pressure wave (the pressure oscillation ripple that in sucking pipe arrangement, produces) in the suction passage in order to simplify.And then, omitted the few curved part 32 of the phase effect of pressure wave, accumulator 16.If the time is t, and will to suck beginning (one-sided suction termination) be that the angle of swing that roller 11 blocks the eccentric part 5 of suction port 13 is made as θ
sHere, angle of swing is the angle from the direction formation of blade 28.In other words, θ shown in Figure 2
sBe meant that when the suction of suction chamber stops from blade 28, the line segment angulation at blade 28 and the center of rotating center that is connected roller 11 and eccentric part 5 is (with this θ
sThe angle of swing of the eccentric part the when suction that is called suction chamber stops).In angle of swing is θ
sThe time, time t is 0.In addition, the direction of pressure-wave emission, with from the direction of open end to the open end of suction port 13 of suction pipe 18 for just, in the opposite direction for negative.The speed of pressure-wave emission is the velocity of sound C of refrigeration agent, is 173[m/s in mode of execution].
Fig. 2 represents that angle of swing is θ
s, t is 0 state constantly.At this moment, the suction volume of suction chamber 30 is roughly 0.The size that is located at the pressure wave of propagating on the postive direction of the dead end that arrives suction port 13 for (+P).Here, the symbolic representation of "+" positive and negative with respect to the pressure wave of the time average of absolute pressure.In Fig. 2, pressure wave (+P) be reflected with cophasing by roller 11, and propagate to negative direction (open end direction as shown in Figure 2).
Fig. 3 express time t is the state of L/C.Here, during with θ=2 π ft, t=L/C, angle of swing is θ
s+ (2 π f) L/C, the pressure wave of having decayed because of viscosity arrives the open end of suction pipe 18, and because open distolateral capacity is big, so be reflected with opposite phase, negative pressure wave is propagated to positive direction.At this, in the open end, the volume of accumulator 16 is far longer than the suction volume of suction chamber 30, so real pressure wave is 0 (as shown in Figure 3 pressure wave (+) and (-) is cancelled in the open end, becomes 0).
Fig. 4 express time t is the state of 2L/C.Angle of swing is θ
s+ (4 π f) L/C.The pressure wave (pressure wave (-) shown in Figure 2 is decayed shown in the dotted line of Fig. 4 like that, becomes the pressure wave of solid line at suction port 13) of having decayed arrives suction chamber 30.Simultaneously pressure wave is reflected with cophasing by roller 11 or cylinder 10, and negative pressure wave (the pressure wave composition that oblique line shown in Figure 4 is represented) is propagated to negative direction.
On the other hand, followed in the time that sucks volume to change, produce negative extensional wave as shown in Figure 4, and propagate to negative direction together with above-mentioned negative pressure wave.Here, so-called extensional wave is meant, as shown in Figure 4, produces negative pressure at suction chamber 30 when angle of swing increases, and this negative pressure is called extensional wave, can be described as a kind of of pressure wave.
And, in the explanation of Fig. 7 described later, mention, when the angle of swing of starting at from blade 28 is π, because the variance ratio of the suction volume of suction chamber 30 becomes maximum, so when angle of swing shown in Figure 4 is consistent with π, produce resonance phenomenon, in the example of the angle of swing of Fig. 4, produce deviation from π, but this deviation is by the rotating speed decision of compressor.In other words, (in+P) cycle, by suction passage length L and refrigeration agent velocity of sound C decision, therefore whether state shown in Figure 4 becomes angle of swing π, by the rotating speed f decision of compressor from the pressure wave of Fig. 2 to Fig. 6.
Fig. 5 express time t is the state of 3L/C.The angle of swing of this moment is θ
s+ (6 π f) L/C.The negative pressure wave of having decayed is reflected with opposite phase in the open end of suction pipe 18, and positive pressure wave is propagated to positive direction.
Fig. 6 express time t is the state of the suction of 4L/C when finishing.The pressure wave of having decayed arrives suction chamber end 13.Because pressure wave periodically changes, thus with Fig. 2 in the same manner, angle of swing is θ s, the size of pressure wave be (+P).
As known from the above, angle of swing θ
sThe time suction port 13 pressure wave (+P), the extensional wave that produces by the suction Volume Changes because of suction chamber 30 and the viscous damping of pressure wave decide.Usually because viscous damping is big in high rotary speed area, so with have this high attenuation and compare with the pressure wave that the suction passage length L comes and goes, the influence of extensional wave accounts for the mastery status (for pressure wave (+P)).Therefore, follow size in extensional wave, pressure wave (+P) increase.Like this, the pressure wave of the influence of the size that is subjected to extensional wave (+during P) for maximum, the density of refrigeration agent increases, and the refrigerant quality that sucks in the suction chamber when finishing becomes greatly.Be that volumetric efficiency (suction fill factor) becomes maximum, become resonance phenomenon.
On the other hand, the size of extensional wave according to momentum conservation law, is changed in the time that sucks volume and becomes greatly when very big.Fig. 7 be expression first mode of execution rotary compressor angle of swing and suck the figure of relation of the time rate of change of volume.As shown in Figure 7, when angle of swing is π (angle of starting at from blade 28 is π), the time rate of change that sucks volume is very big.Therefore, resonance speed fn and suction passage length L, according to Fig. 4, π=θ
sThe relation of+(4 π fn) L/C is set up.If, become with its distortion:
L＝(π—θ
s)/(4π·fn)…(7)。
The formula (7) of feature of expression present embodiment, its characteristic are different from any of existing as shown in Figure 8 formula (2), (4), (6).The real machine of the rotary compressor of present embodiment, very consistent with formula (7) shown in Figure 8, be to produce the design that the distinctive roller 11 of rotary compressor blocks the effect of suction port 13.Fig. 8 is the figure of the relation of the resonance speed fn of rotary compressor of expression first mode of execution and suction passage length L.In experiment shown in Figure 8, give as security removing amount V is 13[mL], the internal diameter of suction pipe 18 is 11[mm], the suction passage length L is 0.37[m], suction pressure is 0.61[MPa], inlet temperature is-5[℃] and, ejection pressure is 2.8[MPa].In addition, the minimum diameter of sealing suction fitting 15 is 10[mm], with respect to the internal diameter of suction pipe 18 1[mm is arranged] about small poor.Therefore, can ignore poor in the fluid loss of this minimum diameter or sound equipment impedance.The radius of curvature of curved part 32 is 25[mm].
Secondly, the relation of the rotating speed of the compressor of present embodiment and the efficient of compressor (full adiabatic efficiency * engine efficiency) as shown in Figure 9.According to Fig. 9, rotating speed is when resonance speed fn is above, and full adiabatic efficiency (compressor energy efficiency) sharply descends.Promptly, bend at resonance speed fn place with respect to the slope of the full adiabatic efficiency of rotating speed.Usually full adiabatic efficiency is divided into the frictional loss between the leakage loss of refrigeration agent or fluid loss, sliding part.Till resonance speed fn, along with the increase of rotating speed, volumetric efficiency increases, thus the increase of frictional loss be cancelled, thereby the decline of full adiabatic efficiency is suppressed.At rotating speed is resonance speed fn when above, becomes significantly owing to be accompanied by the influence of the decline frictional loss of volumetric efficiency, so the slope of full adiabatic efficiency becomes greatly.
In the present embodiment, be maximum speed fm owing to establish resonance speed fn, so the slope of Fig. 9 is slow and can move compressor in the high zone of efficient.Here, maximum speed fm removes the transient response in when starting and the maximum speed of operating stably.Specifically, be the maximum speed in low temperature heating installation when operation of air conditioner.So-called low temperature heating installation operation, the dry-bulb temperature that is outer gas is 2[℃], wet-bulb temperature is 1[℃], indoor dry-bulb temperature is 20[℃], wet-bulb temperature is 10[℃] condition.
By above explanation, present embodiment is owing to being the suction passage length L that produces resonance phenomenon in the maximum speed fm of rotary compressor, so under littler rotating speed, can access high volumetric efficiency.
(second mode of execution)
About the longitudinal type two-cylinder rotary compressor of second mode of execution of the present invention, use Figure 10 to Figure 12 to describe.Figure 10 is the sectional arrangement drawing of the longitudinal type two-cylinder rotary compressor of second mode of execution of the present invention.Second mode of execution has the first suction chamber 30a in a side opposite with motor 3, has the second suction chamber 30b in motor 3 sides, and is suitable for the structure of first mode of execution on each suction chamber 30.The first suction chamber 30a is made of the end plate portion of cylinder 10a, supplementary bearing 19, the roller 11a cylindraceous and the dividing plate 31 that are entrenched in eccentric part 5a periphery.The second suction chamber 30b is made of the end plate portion of cylinder 10b, main bearing 9, the roller 11b cylindraceous and the dividing plate 31 that are entrenched in eccentric part 5b periphery.
Two suction pipes 18 are connected each suction chamber 30 with distinguishing independently.First suction chamber is at the downside of second suction chamber, and the first suction pipe 18a is configured in the position of more leaning on the outer circumferential side of compressor than the second suction pipe 18b.Set the suction passage length L for each suction chamber 30, make based on the maximum speed fm[Hz of formula (7) at compressor] time produce resonance.In the present embodiment, because first, second suction chamber all is to suck the angle of swing θ that finishes
sBe 0.6[rad], resonance speed fn is 120[Hz], so the suction passage length L is 0.3[m based on formula (7)].In addition, the radius of curvature of the curved part 32 of suction pipe 18 is respectively identical value.Owing to make each suction passage length L identical, so the height of the open end of the first suction pipe 18a is lower than the height of the open end of the second suction pipe 18b.Its difference is about 40[mm], be about 4 times value with respect to the internal diameter of suction pipe 13.
In existing longitudinal type two-cylinder rotary compressor, according to the easness of processing, the open end of two suction pipes is an equal height, and the suction passage length of therefore leading to each suction chamber also has nothing in common with each other.
According to present embodiment, be identical owing to establish the suction passage length L, so under same rotational speed, can apply flexibly resonance phenomenon, can improve the volumetric efficiency of compressor integral body.Figure 11 is the figure of the relation of the rotating speed of longitudinal type two-cylinder rotary compressor of expression second mode of execution and volumetric efficiency.In the prior art, be identical height owing to make the open end of two suction pipes, therefore first suction pipe becomes than the second suction pipe range, thus suction passage length difference.Therefore, according to formula (7), because resonance speed fn is different in first suction chamber and second suction chamber, so the decline of the volumetric efficiency of compressor integral body.In the present embodiment, follow, because the volumetric efficiency of first, second suction chamber is maximum simultaneously, so can further improve the volumetric efficiency of compressor integral body in formula (7).
Figure 12 is the figure of the relation of the rotating speed of longitudinal type two-cylinder rotary compressor of expression second mode of execution and full adiabatic efficiency.According to characteristic shown in Figure 9, in the two-cylinder rotary compressor of prior art, because the suction passage length difference of each suction chamber, so full adiabatic efficiency descends in the resonance speed fn of compressor integral body.In the present embodiment, owing to make the suction passage length L identical, so can improve the full adiabatic efficiency under resonance speed fn.And then, owing to make that resonance speed fn is maximum speed fm, thus shown in Figure 12 can be at the high speed range operation compressor of full adiabatic efficiency.
(the 3rd mode of execution)
In the longitudinal type two-cylinder rotary compressor of the 3rd mode of execution of the present invention, describe with reference to Figure 13.The 3rd mode of execution, owing to be the formation identical substantially with second mode of execution, so mainly be that the center describes with the difference.
In the 3rd mode of execution, the radius of curvature R a that establishes the curved part 32a of the first suction pipe 13a is 50[mm], the radius of curvature R b of the curved part 32b of the second suction pipe 13b is 12[mm], each suction passage length L is identical value based on formula (7).Owing to make first curvature radius Ra, so under the situation of setting identical suction passage length L, in the present embodiment, can reduce height poor of the open end of first and second suction pipes greater than radius of second curvature Rb.Specifically, both differences are about 20[mm], compare little about 20[mm with the structure of second mode of execution] poor.
In second mode of execution as shown in figure 10 because the height of the open end of the first suction pipe 18a is low, so big from the distance of ostium 24.Therefore, under the situation that second mode of execution is applicable to the air conditioner that the refrigeration agent enclosed volume is many, liquid refrigerant and gas refrigerant flow out from intake channel 25 when the starting of compressor, can be directly from suction pipe 18a inhalant liquid cryogen.
And, with the inwall that is fixed on accumulator 16 on the approaching position of the outer circumferential side of flat reticulum 22 on, be provided with the ostium 24 that a plurality of refrigeration agents flow to suction pipe 18, it is that common configuration constitutes that the open end, top of suction pipe 18 is configured in the interior all sides that depart from from ostium 24.When constituting prerequisite, especially depart from from ostium 24, so there are the misgivings of inhalant liquid cryogen owing to the first suction pipe 18a shown in Figure 10 with this configuration.
With respect to this, in the 3rd mode of execution, owing to increase the radius of curvature R a of curved part 32a, the height of the open end of the first suction pipe 18a uprises (comparing with Figure 10), so form the structure of the suction that suppresses liquid refrigerant.And then, in the 3rd mode of execution, as shown in figure 13,, form and the nearer structure of the first suction pipe 18a, so further suppress the suction of liquid refrigerant owing to enlarge the projection 23 of reticulum 22 and reduce the height of reticulum.
On the other hand, because the second suction pipe 18b is at projection 23 inner openings, so when having formed gas refrigerant suction is trapped in accumulator 16 in, the structure of the fluid loss in the time of can not producing the suction based on suction pipe 18b owing to the shape for lugs that has enlarged.And, in Figure 13, the open end of the second suction pipe 18b is housed in the projection (convex form portion) of planar reticulum though illustrate, be not limited only to this, the open end of the first suction pipe 18a also can be housed in the convex form portion.Therefore, in the 3rd mode of execution, produce the effect of second mode of execution, can improve reliability simultaneously with respect to the suction of liquid refrigerant.
Claims (5)
1. rotary compressor, it has: the motor of the top configuration in seal container; The running shaft that has eccentric part and be connected with described motor; The suction chamber that forms by roller that is provided with in the periphery of described eccentric part and cylinder; The accumulator that is provided with in the suction side of described suction chamber; Suction pipe at described accumulator inner opening; And the sealing suction fitting that connects the suction port of described suction pipe and described suction chamber,
This rotary compressor is characterised in that:
Cause that the resonant frequency of the described rotary compressor of resonance phenomenon is defined as the highest frequency of described rotary compressor, described resonance phenomenon is that the refrigeration agent of described suction chamber sucks the phenomenon of fill factor for maximum,
Obtain when the suction of described suction chamber finishes, from suction side and the blade of ejection side and the angle of swing that line segment became at the center of rotating center that is connected described roller and described eccentric part that separates described suction chamber,
Suction passage length L [m] till the open end of described suction pipe to the open end of described suction port is by the highest frequency fm[Hz of the described rotary compressor that limits] and described angle of swing θ s[rad] determine according to following formula,
L＝(π-θs)/(4π·fm)。
2. rotary compressor, it has: the motor of the top configuration in seal container; The running shaft that has eccentric part and be connected with described motor; The suction chamber that forms by roller that is provided with in the periphery of described eccentric part and cylinder; The accumulator that is provided with in the suction side of described suction chamber; Suction pipe at described accumulator inner opening; And the sealing suction fitting that connects the suction port of described suction pipe and described suction chamber,
This rotary compressor is characterised in that:
If the suction passage length till open end to the open end of described suction port of described suction pipe is L[m], the highest frequency of described compressor is fm[Hz], the velocity of sound of gas refrigerant is C[m/s], the angle of swing that line segment became from the suction side that separates described suction chamber and the blade that sprays side and the center of rotating center that is connected described roller and described eccentric part when the suction of described suction chamber finishes is θ s[rad], then at this moment
The relation of L=(π-θ s)/(4 π fm) is set up.
3. longitudinal type two-cylinder rotary compressor, it has: the motor of the top configuration in seal container; The running shaft that has two eccentric parts and be connected with described motor; Two suction chambers that the roller dividing plate setting that connects across described running shaft, that be provided with respectively by the periphery at described two eccentric parts and cylinder form; The accumulator that is provided with in the suction side of described two suction chambers; At described accumulator inner opening and have two suction pipes of the roughly L word shape of curved part; And two sealing suction fittings that the suction port of described two suction pipes and described two suction chambers is connected,
Described longitudinal type two-cylinder rotary compressor is characterised in that,
Described two suction pipes form respectively different paths; Make from each and suck suction passage equal in length till open end to the open end of each suction inlet of pipe; And be made as respectively L[m]; If the high-frequency of described compressor is fm[Hz]; If the velocity of sound of gas refrigerant is C[m/s]; Be θ s[rad from separating the suction side that respectively sucks the chamber and the blade that is connected side with the rotation angle that the line segment at the center of the rotation center that is connected each roller and each eccentric part becomes when being located at described two suctions that suck chambers and finishing]; At this moment
The relation of L=(π-θ s)/(4 π fm) is set up.
4. longitudinal type two-cylinder rotary compressor as claimed in claim 3 is characterized in that,
The radius of curvature of curved part that makes first suction pipe that first suction chamber of a side opposite with being positioned at described motor is communicated with is greater than the radius of curvature of the curved part of second suction pipe that is communicated with second suction chamber that is positioned at described motor side, reduces poor at the height of the open end of described accumulator side of described first suction pipe and second suction pipe.
5. longitudinal type two-cylinder rotary compressor as claimed in claim 3 is characterized in that,
Be provided with on the top of described accumulator and have the reticulum that is used to make a plurality of ostiums that refrigeration agent flows down, and convex form portion is set on described reticulum, described convex form portion be used to accommodate described suction pipe in the open end of described accumulator side,
The height in the open end of described accumulator side of described two suction pipes has nothing in common with each other on first suction pipe and second suction pipe, and the level configurations of the open end of at least one suction pipe must be lower than described reticulum.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007280562 | 2007-10-29 | ||
| JP2007280562A JP4991483B2 (en) | 2007-10-29 | 2007-10-29 | Rotary compressor |
| JP2007-280562 | 2007-10-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101424267A CN101424267A (en) | 2009-05-06 |
| CN101424267B true CN101424267B (en) | 2010-08-18 |
Family
ID=40615087
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101708924A Expired - Fee Related CN101424267B (en) | 2007-10-29 | 2008-10-23 | Rotary compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4991483B2 (en) |
| KR (1) | KR101056857B1 (en) |
| CN (1) | CN101424267B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102575675B (en) * | 2009-09-18 | 2015-04-29 | 东芝开利株式会社 | Multi-cylinder rotary compressor and refrigeration cycle device |
| JP5321551B2 (en) * | 2010-08-04 | 2013-10-23 | 株式会社富士通ゼネラル | Rotary compressor |
| CN103582762B (en) * | 2011-06-08 | 2016-05-04 | 东芝开利株式会社 | Hermetic type compressor and refrigerating circulatory device |
| JP6041721B2 (en) * | 2013-03-22 | 2016-12-14 | 東芝キヤリア株式会社 | Multi-cylinder rotary compressor and refrigeration cycle apparatus |
| CN103527483B (en) * | 2013-07-24 | 2016-07-06 | 安徽美芝精密制造有限公司 | Low backpressure rotary compressor and there is its refrigeration plant |
| CN103759477B (en) * | 2014-01-07 | 2016-06-29 | 广东美芝制冷设备有限公司 | Refrigerating circulatory device |
| CN103883527A (en) * | 2014-03-25 | 2014-06-25 | 广东美芝制冷设备有限公司 | Rotary compressor and refrigeration cycle device with same |
| JP6275848B2 (en) * | 2014-07-25 | 2018-02-07 | 東芝キヤリア株式会社 | Compressor and refrigeration cycle apparatus |
| CN206409386U (en) * | 2017-01-18 | 2017-08-15 | 广东美芝制冷设备有限公司 | Reservoir and the duplex cylinder compressor with it |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6235090A (en) * | 1985-08-07 | 1987-02-16 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JPS63106376A (en) | 1986-10-24 | 1988-05-11 | Hitachi Ltd | Supercharge type compressor |
| JP2006194184A (en) * | 2005-01-14 | 2006-07-27 | Mitsubishi Heavy Ind Ltd | Compressor |
| KR100710354B1 (en) | 2005-11-25 | 2007-04-23 | 엘지전자 주식회사 | The structure of pipe arrangement inverter air conditioner |
-
2007
- 2007-10-29 JP JP2007280562A patent/JP4991483B2/en not_active Expired - Fee Related
-
2008
- 2008-10-23 CN CN2008101708924A patent/CN101424267B/en not_active Expired - Fee Related
- 2008-10-28 KR KR1020080105586A patent/KR101056857B1/en active IP Right Grant
Also Published As
| Publication number | Publication date |
|---|---|
| JP4991483B2 (en) | 2012-08-01 |
| CN101424267A (en) | 2009-05-06 |
| KR20090043450A (en) | 2009-05-06 |
| KR101056857B1 (en) | 2011-08-16 |
| JP2009108739A (en) | 2009-05-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101424267B (en) | Rotary compressor | |
| CN103703253B (en) | Rotary blade type compressor | |
| CN104379937A (en) | Airtight compressor and heat pump device | |
| KR101679860B1 (en) | Compressor | |
| CN101331323A (en) | Compressor | |
| JP6102760B2 (en) | Rotary compressor | |
| JP2006194184A (en) | Compressor | |
| WO2006112168A1 (en) | Fluid machine | |
| JP6548915B2 (en) | Compressor | |
| CN103946553A (en) | Rotary compressor | |
| US20180266423A1 (en) | Rotary compressor | |
| US11698072B2 (en) | Compressor | |
| JP2011179394A (en) | Multicylinder compressor | |
| CN102644597B (en) | Double-cylinder rotary compressor | |
| CN104929933B (en) | Rotary compressor | |
| WO2013021634A1 (en) | Hermetic type compressor | |
| CN103727033A (en) | Liquid storage tank for multi-inflator compressor | |
| CN102086869B (en) | Rotary compressor | |
| CN105805014A (en) | Multi-cylinder rotary compressor | |
| CN205533231U (en) | Multi -cylinder rotary compressor and have its refrigeration cycle device | |
| CN204729308U (en) | Rotary compressor | |
| CN101397993B (en) | Scroll type compressor | |
| CN102588284B (en) | Rotary compressor | |
| KR101964957B1 (en) | Compressor having micro groove | |
| JPH0599170A (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20160826 Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20180628 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
|
| TR01 | Transfer of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100818 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |