CN102032185A - Rotary air compressor - Google Patents
Rotary air compressor Download PDFInfo
- Publication number
- CN102032185A CN102032185A CN2010101433280A CN201010143328A CN102032185A CN 102032185 A CN102032185 A CN 102032185A CN 2010101433280 A CN2010101433280 A CN 2010101433280A CN 201010143328 A CN201010143328 A CN 201010143328A CN 102032185 A CN102032185 A CN 102032185A
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- China
- Prior art keywords
- refrigerant
- clutch release
- slave cylinder
- release slave
- rotary compressor
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—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
- 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
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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
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
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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
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- 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
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- 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
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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 invention relates to a rotary air compressor, which via disposing a vortex forming mechanism forming a refrigerant inhaled into a working cylinder into vortex, greatly improves characteristics of inhaling efficiency and the rotary air compressor. The rotary air compressor (a rotary compressor 10) comprises a driving element (14) received in a closed container (12) and a rotary compression element (a second rotary compression element 34) driven by a rotary shaft (16) of the driving element (14), a roller (a second roller 48) tabling the rotary compression element from a working cylinder (a second working cylinder 40) with an eccentric part formed at the rotary shaft (16) and in an eccentric rotation in the working cylinder, and a blade (a second blade 52) in an abutting joint with the roller and separating the internal of the working cylinder to a lower pressure chamber side and a high pressure chamber side. A vortex forming mechanism (a board component 80) forming a refrigerant inhaled into the working cylinder into vortex.
Description
Technical field
The present invention relates to a kind of rotary compressor, it takes in driving element and by the shaft-driven rotation compressing member of the rotation of this driving element in seal container, this rotation compressing member by clutch release slave cylinder, with the eccentric part embedding that is formed at described running shaft be incorporated in eccentric rotation in the clutch release slave cylinder roller, constitute with this roller butt and with the blade that is divided into low pressure chamber side and hyperbaric chamber side in the clutch release slave cylinder.
Background technique
In the past as rotary compressor, for example in multistage compression type rotary compressor with the rotary compressor structure portion that constitutes by the first rotation compressing member and the second rotation compressing member, set driving element at common vertical seal container internal upper part, set in the bottom by the rotation of this driving element shaft-driven rotary compressor structure portion and constitute.And refrigerant gas sucks to the low pressure chamber side of clutch release slave cylinder from the inlet hole of the first rotation compressing member, and by the action compresses of roller and blade, from the hyperbaric chamber side of clutch release slave cylinder via tap hole, discharge the anechoic chamber and in seal container, discharge.At this moment press in the middle of becoming in the seal container by (with reference to patent documentation 1).
In such rotary compressor (rotary compressor), form such structure: the refrigerant gas of pressing in the middle of in the seal container sucks the low pressure chamber side of clutch release slave cylinder from the inlet hole of the second rotation compressing member, carry out second section compression by the action of roller and blade, form the refrigerant gas of High Temperature High Pressure, from the hyperbaric chamber side via tap hole, discharge the anechoic chamber and flow into the radiator of rotary compressor outside.
Patent documentation 1: TOHKEMY 2005-307764 communique
But in rotary compressor in the past, refrigerant forms drum to the suction path of clutch release slave cylinder.Therefore, have such problem: when from sucking path when the refrigerant of clutch release slave cylinder suction passes through to suck path, be decelerated near the wall of this suction path, finally form parabolical velocity distribution, intake reduces.
Summary of the invention
The present invention researches and develops in view of above-mentioned conventional art problem, its purpose is to provide a kind of and forms mechanism by the eddy current that is provided with the refrigerant formation eddy current that will be inhaled into clutch release slave cylinder, thereby increases substantially the rotary compressor of the characteristic of suction efficiency and rotary compressor.
Rotary compressor of the present invention promptly,, in seal container, take in driving element and by the shaft-driven rotation compressing member of the rotation of this driving element, with this rotation compressing member by clutch release slave cylinder, with the eccentric part embedding that is formed at running shaft be incorporated in eccentric rotation in the clutch release slave cylinder roller, constitute with this roller butt and with the blade that is divided into low pressure chamber side and hyperbaric chamber side in the clutch release slave cylinder, it is characterized in that having the eddy current formation mechanism that the refrigerant that will be inhaled into clutch release slave cylinder forms eddy current.
In addition, the rotary compressor of second aspect present invention on the basis of above-mentioned rotary compressor, is characterized in that, it is the plate member of reversing shaping that eddy current forms mechanism, and is equipped in the suction path of clutch release slave cylinder.
In addition, the rotary compressor of third aspect present invention on the basis of above-mentioned rotary compressor, is characterized in that, it is the plate member of reversing shaping that eddy current forms mechanism, and is equipped in the refrigerant ingress pipe that is connected with the suction path of clutch release slave cylinder.
In addition, the rotary compressor of fourth aspect present invention on the basis of above-mentioned rotary compressor, is characterized in that, it is the spiral helicine groove that is formed at the suction path internal surface of clutch release slave cylinder that eddy current forms mechanism.
In addition, the rotary compressor of fifth aspect present invention on the basis of above-mentioned rotary compressor, is characterized in that, it is the spiral helicine groove that is formed at the refrigerant ingress pipe internal surface that is connected with the suction path of clutch release slave cylinder that eddy current forms mechanism.
The invention effect
According to the present invention, because in this rotary compressor, in seal container, take in driving element and by the shaft-driven rotation compressing member of the rotation of this driving element, should rotate compressing member by clutch release slave cylinder, be incorporated in the eccentric roller that rotates in the clutch release slave cylinder with the eccentric part embedding that is formed at running shaft, constitute with this roller butt and with the blade that is divided into low pressure chamber side and hyperbaric chamber side in the clutch release slave cylinder, and be provided with will be inhaled into the refrigerant of the clutch release slave cylinder eddy current that forms eddy current form mechanism, so for example near the speed of the refrigerant that is decelerated the suction path inwall of clutch release slave cylinder in the past can form mechanism by eddy current and quickens.Thus, can efficiently refrigerant be sucked in the clutch release slave cylinder.Therefore, by the suction effect (inertia effect) excessively of utilizing eddy current that refrigerant is quickened, can increase substantially the characteristic of suction efficiency and rotary compressor.
In addition, according to second aspect, on the basis of above-mentioned rotary compressor, because it is the plate member of reversing shaping that eddy current forms mechanism, and be equipped in the suction path of clutch release slave cylinder, so can produce eddy current by the plate member of reversing shaping in sucking path by the refrigerant that plate member is passed through.Thus, because the speed of refrigerant is quickened, so refrigerant can be sucked in the clutch release slave cylinder efficiently.Therefore, by the suction effect excessively of utilizing eddy current that refrigerant is quickened, can increase substantially the characteristic of suction efficiency and rotary compressor.
In addition, according to the third aspect, on the basis of above-mentioned rotary compressor, because it is the plate member of reversing shaping that eddy current forms mechanism, and be equipped in the refrigerant ingress pipe that is connected with the suction path of clutch release slave cylinder, so can on by the refrigerant in the refrigerant ingress pipe, produce eddy current by the plate member of reversing shaping.Thus, because the speed of refrigerant is quickened, so refrigerant can be sucked in the clutch release slave cylinder efficiently.Therefore, by the suction effect excessively of utilizing eddy current that refrigerant is quickened, can increase substantially the characteristic of suction efficiency and rotary compressor.
In addition, according to fourth aspect, on the basis of above-mentioned rotary compressor, be the spiral helicine groove that is formed at the suction path internal surface of clutch release slave cylinder because eddy current forms mechanism, so can on by the refrigerant in the refrigerant ingress pipe, produce eddy current by spiral helicine groove.Thus, because the speed of refrigerant is quickened, so refrigerant can be sucked in the clutch release slave cylinder efficiently.Therefore, by the suction effect excessively of utilizing eddy current that refrigerant is quickened, can increase substantially the characteristic of suction efficiency and rotary compressor.
In addition, according to the 5th aspect, on the basis of above-mentioned rotary compressor, because it is the spiral helicine groove that is formed at the refrigerant ingress pipe internal surface that is connected with the suction path of clutch release slave cylinder that eddy current forms mechanism, so can produce eddy current by spiral helicine groove on by the refrigerant in the refrigerant ingress pipe.Thus, because the speed of refrigerant is quickened, so refrigerant can be sucked in the clutch release slave cylinder efficiently.Therefore, by the suction effect excessively of utilizing eddy current that refrigerant is quickened, can increase substantially the characteristic of suction efficiency and rotary compressor.
Description of drawings
Fig. 1 is the vertical profile profile (embodiment 1) of the rotary compressor of expression one embodiment of the present invention.
Fig. 2 is the following figure that constitutes the second rotation compressing member of rotary compressor of the present invention.
Fig. 3 is the enlarged view of the waist (particularly eddy current formation mechanism part) of the second rotation compressing member of this Fig. 2.
Fig. 4 is equipped on the enlarged view that eddy current in the suction path of clutch release slave cylinder forms mechanism's (plate member).
Fig. 5 is provided with the local vertical profile profile (embodiment 2) that eddy current forms the rotary compressor of mechanism in the refrigerant ingress pipe.
Fig. 6 is the following figure (embodiment 3) that constitutes the second rotation compressing member of rotary compressor of the present invention.
Fig. 7 is provided with the local vertical profile profile (embodiment 4) that eddy current forms the rotary compressor of mechanism in the refrigerant ingress pipe.
Description of reference numerals
10 rotary compressors
12 seal containers
The 12A container body
14 electric elements
18 rotary compressor structure portions
32 first rotation compressing members
34 second rotation compressing members
38 first clutch release slave cylinders
40 second clutch release slave cylinders
58 suck path
60 suck path
82 spiral helicine grooves
92 refrigerant ingress pipes
94 refrigerant ingress pipes
146 accumulators
Embodiment
Present invention be primarily characterized in that in order to prevent near the wall of this suctions path, to be decelerated when sucking path by the refrigerant that sucks to clutch release slave cylinder that intake reduces and acceleration is inhaled into the refrigerant of clutch release slave cylinder from sucking path.The purpose that acceleration is inhaled into the refrigerant of clutch release slave cylinder only realizes by the simple structure that the eddy current formation mechanism that makes refrigerant form eddy current is set in the suction path of clutch release slave cylinder.
(embodiment 1)
Then, describe embodiments of the present invention with reference to the accompanying drawings in detail.Fig. 1 is the vertical profile profile of the rotary compressor 10 of expression one embodiment of the present invention, and Fig. 2 is the following figure that constitutes the second rotation compressing member 34 of rotary compressor of the present invention.In addition, describe by rotary compressor 10 (multi-cylinder rotary air compressor) as rotary compressor of the present invention.
The rotary compressor 10 of present embodiment is the rotary compressor of internal high pressure type, as shown in Figure 1 and Figure 2, seal container 12 with the vertical cylinder shape that constitutes by steel plate, taken in rotary compressor structure portion 18, its electric element 14 (being equivalent to driving element of the present invention), be configured in the downside of this electric element 14 and constitute by first and second rotation compressing member 32,34 that the running shaft 16 of electric element 14 drives by the upside of the inner space that is disposed at this seal container 12.
In addition, refrigerant discharge tube 96 described later is installed on end cap 12B, an end of this refrigerant discharge tube 96 and 12 interior connections of seal container.In addition, be provided with the installation pedestal 11 that is used to stablize this seal container 12 and is provided with in the bottom of seal container 12.
This electric element 14 separates some intervals by the inner peripheral surface along the upper space of seal container 12 and inserts the rotor 24 that is provided with and constitute with the fixing stator 22 of ring-type welding, in the inboard of this stator 22, this rotor 24 is fixed on the running shaft 16 that extends by the center in the vertical direction.
Described stator 22 have the stacked ring round electromagnetic steel plate and duplexer 26, the stator coil 28 of reeling and installing around (concentrate package) mode with string.In addition, rotor 24 similarly also is made of the duplexer 30 of electromagnetic steel plate with terminal 22.
Clamping intermediate section dividing plate 36 between the described first rotation compressing member 32 and the second rotation compressing member 34.Promptly, the first rotation compressing member 32 and the second rotation compressing member 34 are by intermediate section dividing plate 36, be configured in first and second clutch release slave cylinder 38 up and down of this intermediate section dividing plate 36,40, with at this first and second clutch release slave cylinder 38, be located at the eccentric part up and down 42 on the running shaft 16 with having 180 degree phase differences in 40,44 embeddings are incorporated in each clutch release slave cylinder 38, eccentric respectively first and second roller 46 that rotates in 40,48, with this first and second roller 46,48 butts and with each clutch release slave cylinder 48, be divided into first blade (not shown) and second blade 52 (being shown in Fig. 2) of low pressure chamber side and hyperbaric chamber side in 40 respectively, the upper support parts 54 of the support unit of the bearing of the opening surface of inaccessible first clutch release slave cylinder, 38 upsides and the opening surface of second clutch release slave cylinder, 40 downsides and double as running shaft 16 and lower support parts 56 constitute.
Described first and second clutch release slave cylinder 38,40 is provided with the suction path 58,60 that is communicated with respectively with these first and second clutch release slave cylinder, 38,40 inside, sucks to be communicated with respectively on the path 58,60 at this to connect refrigerant ingress pipe 92,94 described later.
In addition, be provided with at the upside of upper support parts 54 and discharge anechoic chamber 62, discharge anechoic chamber 62 by the refrigerant gas of the first rotation compressing member, 32 compressions to this and discharge.This discharge anechoic chamber 62 has the hole of upper support parts 54 perforations of the bearing that is used for running shaft 16 and double as running shaft 16 at the center, be formed in the roughly bowl-shape cap assembly 63 of electric element 14 sides (upside) that cover upper support parts 54.And, above cap assembly 63, be provided with electric element 14 with cap assembly 63 with having predetermined distance.
In addition, also be provided with at the downside of lower support parts 56 and discharge anechoic chamber 64, discharge anechoic chamber 64 by the refrigerant gas of the second rotation compressing member, 34 compressions to this and discharge.This discharge anechoic chamber 64 covers lower support parts 56 from downside by roughly bowl-shape cap assembly 68 and forms.Promptly, by cover the downside of inaccessible lower support parts 56 by cap assembly 68, discharge anechoic chamber 64 thereby form.
In addition, described second clutch release slave cylinder 40 is formed with the steering channel 72 of taking in second blade 52 as shown in Figure 2, in the outside of this steering channel 72, promptly the back side of second blade 52 is formed with the container 72A (being shown in Fig. 2) that takes in as the spring 74 of spring members.This spring 74 is connected to the back side end of second blade 52, all the time with second blade 52 to second roller, the 48 side application of forces.In addition, aftermentioned in container 72A for example imports seal container 12 is discharged side pressure (high pressure), applies as the back pressure of second blade 52.And this container 72A is at steering channel 72 sides and seal container 12 (container body 12A) side opening, and seal container 12 sides of the spring 74 in being accommodated in container 72A are provided with the metal plunger 137 of the effect of the anticreep that is used to realize this spring 74.
On the other hand, side, first clutch release slave cylinder 38 and second clutch release slave cylinder 40 of seal container 12 (container body 12A) with shown in suck on the corresponding position of path 58,60 and weld fixed muffle 141 and 142 (being shown in Fig. 1) respectively.This sleeve 141 and 142 is adjacency up and down.
And, in sleeve 141, inserting the end that connection is used for first clutch release slave cylinder 38 is imported the refrigerant ingress pipe 92 of refrigerant gas, an end of this refrigerant ingress pipe 92 is communicated with the suction path 58 of first clutch release slave cylinder 38 (top clutch release slave cylinder).The other end of this refrigerant ingress pipe 92 is at accumulator 146 inner openings.
Insert the end that connection is used for second clutch release slave cylinder 40 is imported the refrigerant ingress pipe 94 of refrigerant gas in this sleeve 142, an end of this refrigerant ingress pipe 94 is communicated with the suction path 60 of second clutch release slave cylinder 40 (bottom clutch release slave cylinder).The other end of this refrigerant ingress pipe 94 and described refrigerant ingress pipe 92 are similarly also at accumulator 146 inner openings.
This accumulator 146 is the tank bodies that suck the gas-liquid separation of refrigerant, is installed in the upper side of the container body 12A of seal container 12 via carriage 147.And, inserting refrigerant ingress pipe 92 and refrigerant ingress pipe 94 from the bottom at accumulator 146, the other end of this refrigerant ingress pipe 92 and refrigerant ingress pipe 94 is positioned at the top and the difference opening of accumulator 146.In addition, an end of refrigerant pipe arrangement 100 described later is inserted on the top in accumulator 146.
In addition, discharging anechoic chamber 64 and discharge anechoic chamber 62 is communicated with via the access 120 (being shown in Fig. 1) of support unit 54,56, first and second clutch release slave cylinder 38,40, intermediate section dividing plate 36 about connecting at axis direction (above-below direction).And, discharge to discharging anechoic chamber 62 by first refrigerant gas that rotates the High Temperature High Pressure of compressing member 32 compressions, and discharge to discharging anechoic chamber 62 via this access 120 by second rotation compressing member 34 compression and to the refrigerant gas of discharging the High Temperature High Pressure of discharging anechoic chamber 64, converge with the refrigerant gas of the High Temperature High Pressure of discharging from the first rotation compressing member 32.
In addition, discharge anechoic chamber 62 and seal container 12 interior not shown holes connections, rotate the refrigerant gas of the high pressure of compressing member 34 compressions by the first rotation compressing member 32 and described second and in seal container 12, discharge from this hole by perforation cap assembly 63.In addition, the first rotation compressing member 32 and the second rotation compressing member 34 have 180 degree phase difference ground runnings.And, under the situation of the output that wants to increase rotary compressor 10, running both sides' rotation compressing member (the first rotation compressing member 32, the second rotation compressing member 34), export under the excessive situation either party's who shuts down rotation compressing member (any of the first rotation compressing member 32, the second rotation compressing member 34).
In addition, at the tap hole 49 that the hyperbaric chamber side is formed with and discharge anechoic chamber 64 is communicated with of second clutch release slave cylinder 40, this tap hole 49 is provided with the downside (installing with pedestal 11 sides) that is positioned at second clutch release slave cylinder 40.And, as described later by the action compresses of second roller 48 and second blade 52, the refrigerant gas that constitutes High Temperature High Pressure from the hyperbaric chamber side of second clutch release slave cylinder 40 tap hole 49 in by and to discharging anechoic chamber's 64 discharges.In addition, illustrate for convenience, describe by the second rotation compressing member 34 later on.
Next the action of rotary compressor 10 is described by above structure.In addition, use the refrigerant of HFC or HC class, for example use existing oil such as mineral oil (mineraloil), alkylbenzene oil, ether oil, ester oil as the oil of lubricant oil as refrigerant.
At first, when the stator coil 28 of electric element 14 being switched on then electric element 14 startings, rotor 24 rotations via terminal 20 and not shown distribution.Second roller 48 is combined in by this rotating bezel on the eccentric part 44 that is wholely set with running shaft 16 and eccentric rotation in second clutch release slave cylinder 40.
Thus, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.Then, the low-pressure refrigerant in the inflow accumulator 146 is after this is by gas-liquid separation, and only refrigerant gas enters in the refrigerant ingress pipe 94 of this accumulator 146 inner openings.
The refrigerant gas that enters the low pressure in the refrigerant ingress pipe 94 is inhaled into the low pressure chamber side of second clutch release slave cylinder 40 that constitutes the second rotation compressing member 34 via sucking path 60.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second clutch release slave cylinder 40 is compressed, constitute the refrigerant gas of High Temperature High Pressure, from the hyperbaric chamber side of second clutch release slave cylinder 40 in not shown tap hole by and discharge to discharging anechoic chamber 64.
Discharge to discharging anechoic chamber 62 via described access 120 to the refrigerant gas that discharge anechoic chamber 64 discharges, converge with the refrigerant gas that compresses by the first rotation compressing member 32.The refrigerant gas that converges is discharged in seal container 12 from the not shown hole that connects first cap assembly 63.Afterwards, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12.
Yun Zhuan rotary compressor in the past 10 is formed with suction path 60 towards the refrigerant of clutch release slave cylinder with drum like this.Therefore, from suck path 60 to the refrigerant that clutch release slave cylinder sucks sucking the path 60 by the time, near the wall of this suctions path 60, be decelerated, finally constitute parabolical velocity distribution, the intake minimizing.Therefore, in the present invention,, be provided with the plate member 80 that makes the refrigerant that is inhaled into clutch release slave cylinder (second clutch release slave cylinder 40) form eddy current as eddy current formation mechanism as Fig. 2, shown in Figure 3.In addition, plate member 80 is not shown in Fig. 1.
At length, plate member 80 constitutes by having predetermined thickness, the corrosion resistant plate that is not easy to get rusty, aluminium sheet, copper coin, brass sheet etc.This plate member 80 forms and is equipped on the size that sucks the lengthwise essentially rectangular in the path 60.This plate member 80 is entrenched in the suction path 60 also fixing with the state of the other end (lower end among the figure) being turned round turnback with helical with respect to length direction one end (upper end among the figure) as shown in Figure 4.And, when refrigerant is inhaled in second clutch release slave cylinder 40, circulates along being provided in the reverse part that sucks the plate member 80 in the path 60, thereby form eddy current.And refrigerant is inhaled under keeping the state of eddy current in second clutch release slave cylinder 40.In addition, reversing of plate member 80 can be reversed to clockwise or anticlockwise any direction.
Like this, can with second clutch release slave cylinder 40 in the past, suck path 60 inwalls near the refrigerant speed that is decelerated form mechanism's (plate member 80) by eddy current and produce eddy current.Promptly, can be by in the suction path 60 of second clutch release slave cylinder 40, setting plate member 80, and this plate member 80 is reversed, and is made the refrigerant that in sucking path 60, passes through produce eddy current.Owing to by this eddy current the speed of refrigerant is quickened, so refrigerant can be sucked in second clutch release slave cylinder 40 efficiently.Therefore, utilize the suction effect excessively of quickening refrigerant by eddy current, can increase substantially the characteristic of suction efficiency and rotary compressor 10.
(embodiment 2)
Then, Fig. 5 represents that the eddy current that other embodiments' of the present invention rotary compressor 10 is had forms mechanism's (plate member 80).This rotary compressor 10 has the structure roughly the same with aforesaid mode of execution.Below, describe about different parts.In addition, the part identical with aforesaid mode of execution used the reference character identical with it, it illustrates omission.Plate member 80 is provided in the refrigerant ingress pipe 94 that is connected with the suction path 60 (shown in Figure 1) of second clutch release slave cylinder 40.
In this case, plate member 80 is chimeric and be fixed in the refrigerant ingress pipe 94.And the refrigerant gas that is formed eddy current in refrigerant ingress pipe 94 by plate member 80 is subjected to effect of inertia, also keeps eddy current in the suction path 60 of second clutch release slave cylinder 40, and former state be inhaled in second clutch release slave cylinder 40.Thus, in the refrigerant that is inhaled into second clutch release slave cylinder 40, can produce eddy current.
Like this, because plate member 80 is provided in the refrigerant ingress pipe 94 that is connected with the suction path 60 of second clutch release slave cylinder 40, can produce eddy current by the plate member 80 of reversing shaping in the refrigerant that in refrigerant ingress pipe 94, passes through.Thus, the speed of refrigerant is quickened, so refrigerant is sucked in second clutch release slave cylinder 40.Therefore, utilize the suction effect excessively of quickening refrigerant by eddy current, can increase substantially the characteristic of suction efficiency and rotary compressor 10.
(embodiment 3)
Then, Fig. 6 represents that the eddy current that other embodiments' of the present invention rotary compressor 10 is had forms mechanism.This rotary compressor 10 has the structure roughly the same with aforesaid mode of execution.Below, describe about different parts.In addition, the part identical with aforesaid mode of execution used the reference character identical with it, it illustrates omission.This eddy current forms mechanism and forms the spiral helicine groove 82 that outside surface direction digs at suction path 60 internal surfaces of second clutch release slave cylinder 40, and this spiral helicine groove 82 is played and above-mentioned plate member 80 identical functions.
At length, the refrigerant that sucks in second clutch release slave cylinder 40 from refrigerant ingress pipe 94 is when sucking path 60, spiral helicine groove 82 circulations on the wall that is formed at this suctions path 60 make refrigerant generation eddy current thus.Promptly, when refrigerant passes through in sucking path 60 from refrigerant ingress pipe 94, make refrigerant produce eddy current by spiral helicine groove 82.Thus, can quicken the speed of the refrigerant that in sucking path 60, passes through.
Like this, owing to form spiral helicine groove 82, produce eddy current by spiral helicine groove 82 in the refrigerant that can in sucking path 60, pass through at suction path 60 internal surfaces of second clutch release slave cylinder 40.Thus, the speed of refrigerant is quickened, so refrigerant is sucked in second clutch release slave cylinder 40.Therefore, utilize the suction effect excessively of quickening refrigerant by eddy current, can increase substantially the characteristic of suction efficiency and rotary compressor 10.
(embodiment 4)
Then, Fig. 7 represents that the eddy current that other embodiments' of the present invention rotary compressor 10 is had forms mechanism's (spiral helicine groove 82).This rotary compressor 10 has the structure roughly the same with aforesaid mode of execution.Below, describe about different parts.In addition, the part identical with aforesaid mode of execution used the reference character identical with it, it illustrates omission.This eddy current forms mechanism and forms the spiral helicine groove 82 that direction to the outside digs at refrigerant ingress pipe 94 internal surfaces of second clutch release slave cylinder 40, makes this spiral helicine groove 82 play the function of above-mentioned plate member 80.
At length, the refrigerant that in second clutch release slave cylinder 40, sucks from refrigerant ingress pipe 94 by refrigerant ingress pipe 94 time, spiral helicine groove 82 circulations on the wall that is formed at this refrigerant ingress pipe 94 make refrigerant produce eddy current thus.Promptly, when refrigerant passes through in refrigerant ingress pipe 94, make refrigerant produce eddy current by spiral helicine groove 82.Thus, can quicken the speed of the refrigerant that in refrigerant ingress pipe 94, passes through.
Like this, because refrigerant ingress pipe 94 internal surfaces that are connected at the suction path 60 with second clutch release slave cylinder 40 form spiral helicine groove 82, produce eddy current by spiral helicine groove 82 so can make in the refrigerant that in refrigerant ingress pipe 94, passes through.Thus, the speed of refrigerant is quickened, so refrigerant is sucked in second clutch release slave cylinder 40.Therefore, utilize the suction effect excessively of quickening refrigerant by eddy current, can increase substantially the characteristic of suction efficiency and rotary compressor 10.
In addition, utilize rotary compressor 10 explanation rotary compressors in mode of execution, rotary compressor is not limited to rotary compressor 10, if the compressor of rotary compressor piston type is also effective to the present invention.
In addition,, plate member 80 is reversed about 180 degree, but reversing of plate member 80 is not limited to 180 degree,, can reverses about 60 degree～180 degree again as if the speed of the refrigerant that can quicken in sucking path, to pass through for producing eddy current.In addition, reversing of plate member 80 is that the generation of eddy current is little under the following situation of 60 degree, be difficult to quicken refrigerant flow speed, reversing of plate member 80 is that it is big that the path resistance of flow of refrigerant becomes under the above situation of 180 degree, input increases, so reversing of plate member 80 is preferably about 60 degree～180 degree.Certainly the invention is not restricted to the various embodiments described above, can carry out other various changes again in the scope that does not break away from technical conceive of the present invention, also is effective to the present invention.
Claims (5)
1. rotary compressor, in seal container, take in driving element and by the shaft-driven rotation compressing member of the rotation of this driving element, and by clutch release slave cylinder, with the eccentric part embedding that is formed at described running shaft be incorporated in eccentric rotation in the described clutch release slave cylinder roller, constitute described rotation compressing member with this roller butt and with the blade that is divided into low pressure chamber side and hyperbaric chamber side in the described clutch release slave cylinder
Described rotary compressor is characterised in that,
Eddy current with the refrigerant formation eddy current that will be inhaled into described clutch release slave cylinder forms mechanism.
2. rotary compressor as claimed in claim 1 is characterized in that,
It is the plate member of reversing shaping that described eddy current forms mechanism, and is equipped in the suction path of described clutch release slave cylinder.
3. rotary compressor as claimed in claim 1 is characterized in that,
It is the plate member of reversing shaping that described eddy current forms mechanism, and is equipped in the refrigerant ingress pipe that is connected with the suction path of described clutch release slave cylinder.
4. rotary compressor as claimed in claim 1 is characterized in that,
It is the spiral helicine groove that is formed at the suction path internal surface of described clutch release slave cylinder that described eddy current forms mechanism.
5. rotary compressor as claimed in claim 1 is characterized in that,
It is the spiral helicine groove that is formed at the refrigerant ingress pipe internal surface that is connected with the suction path of described clutch release slave cylinder that described eddy current forms mechanism.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-225712 | 2009-09-30 | ||
| JP2009225712A JP2011074798A (en) | 2009-09-30 | 2009-09-30 | Rotary compressor |
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|---|---|
| CN102032185A true CN102032185A (en) | 2011-04-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010101433280A Pending CN102032185A (en) | 2009-09-30 | 2010-03-19 | Rotary air compressor |
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| Country | Link |
|---|---|
| JP (1) | JP2011074798A (en) |
| KR (1) | KR101210795B1 (en) |
| CN (1) | CN102032185A (en) |
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| KR20110035822A (en) | 2011-04-06 |
| JP2011074798A (en) | 2011-04-14 |
| KR101210795B1 (en) | 2012-12-10 |
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