CN102251969A - Rotary vane type compressor - Google Patents
Rotary vane type compressor Download PDFInfo
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- CN102251969A CN102251969A CN201110104535XA CN201110104535A CN102251969A CN 102251969 A CN102251969 A CN 102251969A CN 201110104535X A CN201110104535X A CN 201110104535XA CN 201110104535 A CN201110104535 A CN 201110104535A CN 102251969 A CN102251969 A CN 102251969A
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- blade
- oil supply
- roller
- axle
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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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant 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
- 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
- F04C18/344—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 inner 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
- 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
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
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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
- F04C2240/30—Casings or housings
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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
Abstract
The invention provides a rotary blade type compressor capable of supplying lubricating oil to an action chamber, the side surface and the front end of a blade and a sliding part regardless of the pressure condition during the operation. The axial core part of a shaft (6) for transmitting power to a compression unit (11) is equipped with an oil suction hole (6a) for sucking up the lubricating oil stored a the bottom of a sealed container via the rotation of the shaft. Meanwhile, the end face of at least one side of the roller (7) of the shaft (6) is equipped with an oil supplying hole (6b). The end face of a sealed cylinder (5) of at least one bearing is equipped with an oil supplying groove (10) communicated with the oil supplying hole (6b). Meanwhile, the sliding surface at one side of a blade groove (7a) of a blade (8) is equipped with a blade oil supplying groove (8a) in such a way that it is communicated with the oil supplying groove (8a) at a rotation phase and is communicated with a compression chamber at a rotation phase wherein the blade (8) protrudes toward the peripheral part of the roller from the blade groove (7a).
Description
Technical field
The present invention relates to a kind of can with the pressure condition in when running irrespectively stably in operating chamber and the rotary blade type compressor of slide part supplying lubricating oils such as blade (vane) side, front end.
Background technique
In rotary blade type compressor in the past, utilize enough narrow stream to make that the seal container of the high pressure that stores lubricant oil is interior to be communicated with operating chamber, the blade backpressure chamber of low pressure or middle pressure, utilize pressure reduction that the lubricant oil of high pressure is supplied to (for example, with reference to patent documentation 1) in vacuum side of blade, blade side and the operating chamber.
Patent documentation 1: No. 3792578 communique of Japan Patent (Fig. 1)
But, utilize enough narrow stream to make in the seal container of high pressure to be communicated with the blade backpressure chamber and utilize in the seal container and the blade backpressure chamber between pressure reduction in the device of slide part supplying lubricating oils such as blade side, blade front end, under the operating condition that differential pressure is low when starting, can't guarantee fuel delivery, thereby might on slide part, wear and tear, burn etc., have the possibility that reduces reliability.
In addition, the blade backpressure chamber is in the mode of blade front end along the interior week of cylinder (cylinder), utilization is pressed onto the pressure of discharging between pressing from suction and controls, because to blade backpressure chamber supplying lubricating oil, blade enters in the blade groove, the rotatable phase that the volume in the blade backpressure chamber diminishes, at the indoor compression lubricant oil of blade backpressure, the pressure anomaly of back pressure chamber rises, and the interface pressure in week is excessive in blade front end and the cylinder, might cause inordinate wear at blade front end and cylinder inner peripheral surface.
Summary of the invention
Technical task of the present invention be can with the pressure condition in when running irrespectively stably in operating chamber and slide part supplying lubricating oils such as blade side, front end.
Rotary blade type compressor of the present invention is made of following structures.That is, this rotary blade type compressor has the compression unit that makes refrigeration agent compression in seal container and as the electrodynamic element of the driving source of this compression unit, wherein, compression unit comprises: axle, and it is by the electrodynamic element rotary driving; Roller, it is configured on the axis identical with the central axis of axle and with axle and together rotates; Cylinder, it is used to take in roller and inner peripheral surface and forms cylindricly, and the central shaft of inner peripheral surface sets prejudicially with respect to the central axis of axle; Two bearings, it is used for the both ends of the surface of closed cylinder; Blade, it reciprocatingly slides in blade groove on being formed on roller in compression section, will be separated into a plurality of operating chamber by the pressing chamber that roller and bearing form along the inner peripheral surface of cylinder; Suction port, it is used to make refrigeration agent to flow in the operating chamber; Exhaust port, it is used to discharge the refrigeration agent that has been compressed in operating chamber; Oil feeding mechanism, it is used for supplying with the lubricant oil that accumulates in sealing container bottom to pressing chamber, oil feeding mechanism comprises: oil-sucking hole, and it is located at the axis central part of axle and at the end face opening of a side opposite with electrodynamic element, utilizes the rotation of axle to drink up at the lubricant oil that sealing container bottom accumulates; Oil supply hole, its be located at axle roller at least one side near end face and connect inside and outside the axle; Oil supply, it is arranged at the end face of closed cylinder of at least one side's bearing in the mode that is communicated with oil supply hole; The blade oil supply, it is arranged on the slip surface of a side of blade groove of blade as follows, that is, be communicated with oil supply at the rotatable phase of regulation, and the rotatable phase of giving prominence to the roller peripheral part from blade groove at blade is communicated with pressing chamber.
In rotary blade type compressor of the present invention, owing to be provided with the oil-sucking hole that lubricant oil that the rotation that utilizes this will accumulate in sealing container bottom drinks up at axis central part to the axle of compression unit transferring power, and near at least one side's of the roller of axle end face, be provided with and connect the inside and outside oil supply hole of axle, on the end face of the closed cylinder of at least one side's bearing, be provided with oil supply in the mode that is communicated with oil supply hole, on blade, on the slip surface of a side of its blade groove, be provided with the blade oil supply as follows, promptly, rotatable phase in regulation is communicated with oil supply, and the rotatable phase of giving prominence to the roller peripheral part from blade groove at blade is communicated with pressing chamber, therefore, can be at blade supplying lubricating oil during to-and-fro motion in blade groove, though also can be reliably under the low operating condition of pressure reduction to the slip surface and the blade front end of blade, supplying lubricating oil in the operating chamber.
Description of drawings
Fig. 1 is the integrally-built longitudinal section of the rotary blade type compressor of expression embodiments of the present invention 1.
Fig. 2 is the D-D line sectional view of Fig. 1.
Fig. 3 is the stereogram of blade of the rotary blade type compressor of expression embodiments of the present invention 1.
Fig. 4 is the sectional elevation of compression unit portion that is used to illustrate the position relation of the blade oil supply of blade of rotary blade type compressor of embodiments of the present invention 1 and bearing face oil supply.
Fig. 5 is the sectional elevation of compression unit portion of action (compression process) of the rotary blade type compressor of expression embodiments of the present invention 1.
Fig. 6 is the integrally-built longitudinal section of the rotary blade type compressor of expression embodiments of the present invention 2.
Fig. 7 is the E-E line sectional view of Fig. 6.
Fig. 8 is the sectional elevation of compression unit portion of position relation that is used to illustrate the oil supply of the blade oil supply of blade of rotary blade type compressor of embodiments of the present invention 2 and roller end face.
Fig. 9 is the sectional elevation of compression unit portion of action (compression process) of the rotary blade type compressor of expression embodiments of the present invention 2.
Figure 10 is the sectional elevation of compression unit portion of position relation that is used to illustrate the oil supply of the blade oil supply of blade of rotary blade type compressor of embodiments of the present invention 3 and connectivity slot and roller end face.
Figure 11 is the sectional elevation of the compression unit portion that the position is set of blade oil supply of blade that is used to illustrate the rotary blade type compressor of embodiments of the present invention 4.
Embodiment
Mode of execution 1
Fig. 1 is the integrally-built longitudinal section of the rotary blade type compressor of expression embodiments of the present invention 1, Fig. 2 is the D-D line sectional view of Fig. 1, Fig. 3 is the stereogram of blade of the rotary blade type compressor of expression mode of execution 1, Fig. 4 is the sectional elevation of compression unit portion that is used to illustrate the position relation of the blade oil supply of the blade that is positioned at the 0deg position of rotary blade type compressor of mode of execution 1 and bearing face oil supply, and Fig. 5 is the sectional elevation of compression unit portion of action (compression process) of the rotary blade type compressor of expression mode of execution 1.
In the rotary blade type compressor of present embodiment, as depicted in figs. 1 and 2, in the seal container that constitutes by lower container 1 and upper container 2, take in compression unit 11, electrodynamic element 14, not shown lubricant oil.On lower container 1, be connected with the suction pipe 1a that is communicated with storage 30, be taken into refrigeration agent (gas) by this suction pipe 1a from storage 30.In addition, be connected with discharge tube 2a on the top of upper container 2, the refrigeration agent that has been compressed is discharged by discharge tube 2a.
Electrodynamic element 14 comprises the stator 12 that is fixed in lower container 1 and in stator 12 inner rotor rotated 13.
Compression unit 11 comprises upper bearing (metal) 3, lower bearing 4, cylinder 5, axle 6, roller 7 and blade 8.
Axle is 6 by upper bearing (metal) 3 and lower bearing 4 free rotary ground supportings, and by electrodynamic element 14 rotary driving.In addition, be formed with the oil-sucking hole 6a of direction opening at the bottom of seal container, in oil-sucking hole 6a, be provided with spiral helicine centrifugal pump 9 at the axis central part of axle 6.
The both ends of the surface of upper bearing (metal) 3 and lower bearing 4 closed cylinders 5.In addition, at least one side's (is both sides at this) of upper bearing (metal) 3 and lower bearing 4 pressing chamber side end face, be formed with from the central shaft bearing face oil supply 10 of Zhou Fangxiang outward.On the outer circumferential face of axle 6, be formed with oil supply hole 6b partly be accommodated in the zone in shallow annular slot, by this annular slot, bearing face oil supply 10 is being communicated with oil supply hole 6b at ordinary times.In addition, be provided with back pressure groove 3a in the ring-type that is communicated with blade backpressure chamber 7b at ordinary times at the upper bearing (metal) end face, back pressure groove 3a is being communicated with high-pressure space in the seal container by gas communication path 3b at ordinary times.
Then, illustrate that bearing face oil supply 10 and the position of blade oil supply 8a concern.As shown in Figure 4, near the phase place the 0deg in blade 8 moves back to the blade groove 7a of roller 7 fully, blade oil supply 8a is communicated with bearing face oil supply 10, near the phase place the 180deg outstanding from blade groove 7a, blade oil supply 8a is communicated with pressing chamber 20.The phase range that blade oil supply 8a is communicated with pressing chamber 20 depends on the distance L v from the blade front end to blade oil supply 8a, distance L v is below the outstanding length L max of blade, and the outstanding length L max of blade is a blade 8 from the thoughtful length of blade front end from roller 7 outside of the most outstanding phase place of roller 7 peripheries.
The action of the rotary blade type compressor of present embodiment then, is described.
The refrigeration agent of storage 30 is inhaled in the operating chamber 20a of compression unit 11 via suction pipe 1a and suction port 15.Axle 6 is driven by electrodynamic element 14, and roller 7 also together rotates with axle 6.Simultaneously, reciprocating blade 8 also together rotates with roller 7 in the blade groove 7a on being formed on roller 7.At this moment, because cylinder 5 is provided with as follows, that is, the central shaft of cylindrical shape of inner face and inner face is with respect to the rotating shaft eccentric of axle 6, therefore, the rotation by roller 7 make roller 7 and cylinder 5 inner peripheral surface apart from change.Because blade backpressure chamber 7b is being communicated with the high-pressure space of seal container at ordinary times via gas communication path 3b, therefore,,, blade 8 slides on week while being pushed in the cylinder by by the centrifugal force of rotation generation and the pressure of blade backpressure chamber 7b.And,, finally discharge from discharge tube 2a along with the refrigeration agent that the rotation of roller 7 has been compressed is discharged from exhaust port 16.
Then, illustrate that according to Fig. 5 and with reference to Fig. 1～Fig. 4 the compressed action of pressing chamber 20 and the fuel feeding of blade oil supply 8a move.Wherein, 180 ° of phase place ground of two blade 8,8 skews carry out identical action, therefore, mainly a side blade 8 are described at this.Near the position of blade 8 moves back to 0deg in the blade groove 7a fully position, the circumferential position of the front end of blade 8 and roller 7 is roughly same position, and bearing face oil supply 10 is communicated with (the picture left above of Fig. 5) with blade oil supply 8a.At this moment, utilize centrifugal pump 9 from sealing container bottom lubricant oil to be drunk up, this lubricant oil supplies to blade oil supply 8a from the oil supply hole 6b of axle 6 via bearing face oil supply 10.And along with the rotation of roller 7, blade 8 is outstanding to the outside of roller 7, and the inner peripheral surface of the front end edge cylinder 5 of blade 8 slides, the refrigeration agent in the 20b of compressed action chamber.Afterwards, the position of blade 8 is positioned near the position the 180deg, and blade oil supply 8a is at operating chamber 20b inner opening, from blade oil supply 8a supplying lubricating oil (bottom-right graph of Fig. 5) in operating chamber 20b.In the time of near the position of blade 8 surpasses 180deg, blade 8 turns back in the roller 7 once more, is compressed in operating chamber 20b and the refrigeration agent that reached the head pressure of regulation is discharged from exhaust port 16.Then, in the compressed action of this refrigeration agent, suck refrigeration agents from suction port 15 in operating chamber 20a side, therefore, by the rotation of roller 7 carry out repeatedly refrigeration agent from the suction of suction port 15 with from the discharge of exhaust port 16.
As mentioned above, when blade 8 in blade groove 7a during to-and-fro motion, can make the lubricant oil that drinks up from sealing container bottom by centrifugal pump 9 supply to blade oil supply 8a via bearing face oil supply 10 from the oil supply hole 6b of axle 6.Therefore, with the pressure condition in when running irrespectively, even at also supplying lubricating oil in blade side and blade front end and pressing chamber 20 reliably under the low operating condition of pressure reduction.
And, under the low operating condition of such pressure reduction, because not to blade backpressure chamber 7b fuel feeding, therefore, can prevent that the oil pressure in the 7b of blade backpressure chamber from contracting, and can prevent from advance to improve reliability owing to blade pushing force the rise wearing and tearing, burn etc. in week in the blade front end cause and the cylinder.
Mode of execution 2
Next, the rotary blade type compressor that is provided with the embodiments of the present invention 2 of oil supply to replacing bearing face on the roller end face describes.Fig. 6 is the integrally-built longitudinal section of the rotary blade type compressor of expression mode of execution 2, Fig. 7 is the E-E line sectional view of Fig. 6, Fig. 8 is the sectional elevation of compression unit portion of position relation that is used to illustrate the oil supply of the blade oil supply of its blade and roller, Fig. 9 is the sectional elevation of the compression unit portion of its action of expression (compression process), in each figure, the part identical with above-mentioned mode of execution 1 marked same reference character.
In the rotary blade type compressor of present embodiment, as shown in Figure 6 and Figure 7, in the seal container that constitutes by lower container 1 and upper container 2, take in compression unit 21, electrodynamic element 14, not shown lubricant oil.On lower container 1, be connected with the suction pipe 1a that is communicated with storage 30, be taken into refrigeration agent (gas) from storage 30 by this suction pipe 1a.In addition, be connected with discharge tube 2a on the top of upper container 2, the refrigeration agent that has compressed is discharged by discharge tube 2a.
Electrodynamic element 14 comprises the stator 12 that is fixed in lower container 1 and in stator 12 inner rotor rotated 13.
Compression unit 21 comprises upper bearing (metal) 23, lower bearing 24, cylinder 5, axle 26, roller 27 and blade 8.
Axle is 26 by upper bearing (metal) 3 and lower bearing 4 free rotary ground supportings, and by electrodynamic element 14 rotary driving.In addition, be formed with the oil-sucking hole 26a of direction opening at the bottom of seal container, in oil-sucking hole 26a, be provided with spiral helicine centrifugal pump 9 in the axial centre of axle 26.
On lower bearing 24 side end faces of roller 27, be formed with and make the oil supply 27c that is communicated with between oil supply hole 26b and the blade groove 27a, still, this oil supply 27c also can be formed on upper bearing (metal) 23 side end faces or two end faces of roller 27.
The both ends of the surface of upper bearing (metal) 23 and lower bearing 24 closed cylinders 5.In addition, on the upper bearing (metal) end face, be provided with the back pressure groove 23a in the ring-type that is communicated with at ordinary times with blade backpressure chamber 27b, back pressure groove 23a is being communicated with high-pressure space in the seal container via gas communication path 23b at ordinary times.
The position relation of oil supply 26c and blade oil supply 8a then, is described.
As shown in Figure 7, from the outstanding phase place of the periphery of roller 7, blade oil supply 8a is communicated with oil supply 27c at blade 8, and as shown in Figure 8, along with the carrying out of rotating, blade 8 is further given prominence to, and blade oil supply 8a is communicated with pressing chamber 20 from the peripheral part of roller 7.The phase range that is communicated with in blade oil supply 8a and the operating chamber depends on the distance L v from the blade front end to blade oil supply 8a, distance L v is below the outstanding length L max of blade, and the outstanding length L max of blade is a blade 8 from the thoughtful length of blade front end from roller 27 outside of the most outstanding phase place of roller 27 peripheries.And, even oil supply 27c also is positioned at and the disconnected position of 27b, blade backpressure chamber when the peripheral direction of roller 27 is given prominence at blade 8.
The action of above-mentioned rotary blade type compressor then, is described.
The refrigeration agent of storage 30 is inhaled in the operating chamber 20a of pressing chamber 20 via suction pipe 1a and suction port 15.Axle 26 is driven by electrodynamic element 14, roller 27 and together rotation of axle 26.Simultaneously, reciprocating blade 8 also is rotated in the blade groove 27a on being formed on roller 27.At this moment, because cylinder 5 is provided with as follows, that is, the central shaft of cylindrical shape of its inner face and inner face is with respect to the rotating shaft eccentric of axle 26, therefore, the rotation by roller 27 make roller 27 and cylinder 5 inner peripheral surface apart from change.Because blade backpressure chamber 27b is being communicated with the high-pressure space of seal container at ordinary times by gas communication path 23b, therefore,,, blade 8 slides on week while being pushed in the cylinder by by the centrifugal force of rotation generation and the pressure of blade backpressure chamber 27b.And along with the rotation of roller 27, the refrigeration agent that has compressed is discharged from exhaust port 16, finally discharges from discharge tube 2a.
Then, the compressed action of pressing chamber 20 is described and in the action of the fuel feeding of blade oil supply 8a according to Fig. 9 and with reference to Fig. 1～Fig. 4.In addition, carry out identical action, therefore, mainly a side blade 8 is described at this because two blades 8,8 differ 180 ° of phase place ground.The position of blade 8 is positioned near the position the 90deg, oil supply 27c be connected with blade oil supply 8a (top right plot of Fig. 9).At this moment, utilize centrifugal pump 9 from sealing container bottom lubricant oil to be drunk up, this lubricant oil supplies to blade oil supply 8a from the oil supply hole 26b of axle 26 via oil supply 27c.Then, along with the rotation of roller 27, blade 8 is outstanding to the outside of roller 27, and the inner peripheral surface of the front end edge cylinder 5 of blade 8 slides, the refrigeration agent in the 20b of compressed action chamber.Afterwards, the position of blade 8 is positioned near the position the 180deg, and blade oil supply 8a is at operating chamber 20b inner opening, from blade oil supply 8a supplying lubricating oil (bottom-right graph of Fig. 9) in operating chamber 20b.In the time of near the position of blade 8 surpasses 180deg, blade 8 turns back in the roller 27 once more, is compressed in operating chamber 20b and the refrigeration agent that reached the head pressure of regulation is discharged from exhaust port 16.Then owing in the compressed action of this refrigeration agent, suck refrigeration agents from suction port 15 in operating chamber 20a side, therefore, by the rotation of roller 27 carry out repeatedly refrigeration agent from the suction of suction port 15 with from the discharge of exhaust port 16.
As mentioned above, when blade 8 in blade groove 27a during to-and-fro motion, can make the lubricant oil that drinks up from sealing container bottom by centrifugal pump 9 supply to blade oil supply 8a via the oil supply 27c that is formed on roller 27 sides from the oil supply hole 26b of axle 26.Therefore, with the pressure condition in when running irrespectively, even at also supplying lubricating oil in blade side and blade front end and pressing chamber 20 reliably under the low operating condition of pressure reduction.
In addition, under the low operating condition of such pressure reduction, because not to blade backpressure chamber 27b fuel feeding, therefore can prevent that the oil pressure in the 27b of blade backpressure chamber from contracting, thereby can prevent from advance to improve reliability owing to blade pushing force the rise wearing and tearing, burn etc. in week in the blade front end cause and the cylinder.
Mode of execution 3
Figure 10 is the sectional elevation of compression unit portion of position relation that is used to illustrate the oil supply of the blade oil supply of blade of rotary blade type compressor of embodiments of the present invention 3 and connectivity slot and roller end face, in the drawings, to above-mentioned mode of execution 2 in identical part mark same reference character.
In the rotary blade type compressor of present embodiment, as shown in figure 10, side in the ratio blade oil supply 8a inner end of blade 8 is a blade backpressure chamber 27b side, even and the position that (when giving prominence to) also is not communicated with pressing chamber 20 and blade backpressure chamber 27b in compression the time, be provided with the connectivity slot 8b that extends to another side (slip surface) and be communicated with oil supply 27c from a side (slip surface) of this blade 8 at the rotatable phase of stipulating.
In the rotary blade type compressor of present embodiment, when blade 8 in blade groove 7a during to-and-fro motion, not only can be to the face supplying lubricating oil of a side that has blade oil supply 8a, but also can be by the face supplying lubricating oil of connectivity slot 8b to opposition side.Therefore, even at also supplying lubricating oil in blade side and blade front end and pressing chamber 20 reliably under the low operating condition of pressure reduction, thereby be easy to guarantee reliability.
Mode of execution 4
Figure 11 is the sectional elevation of the compression unit portion that the position is set of blade oil supply of blade that is used to illustrate the rotary blade type compressor of embodiments of the present invention 4, in the drawings, the part identical with function in the above-mentioned mode of execution 1 is marked same reference character.
In the rotary blade type compressor of present embodiment, as shown in figure 11, the blade oil supply 8a of above-mentioned mode of execution 1～3 has been configured on the face (slip surface of opposition side) of a side of not bearing counter-force Fv, above-mentioned counter-force Fv is corresponding with the pressure Fp of refrigeration agent in the compression process and from blade groove peripheral part edge.
As the rotary blade type compressor of present embodiment, by on the face (slip surface of opposition side) of a side of not bearing counter-force Fv, blade oil supply 8a being set, stress concentrates in the time of can preventing to compress becomes on the blade of the thinner wall section oil supply 8a part, wherein, counter-force Fv is corresponding with the pressure Fp of refrigeration agent in the compression process and from blade groove peripheral part edge, thus, can prevent corner collision when the blade 8 blade oil supply 8a during to-and-fro motion and blade groove 7a peripheral part edge in blade groove 7a.
Mode of execution 5
In above mode of execution 1～4, preferred blade oil supply 8a constitutes as follows, that is, its volume is 0.01%～1% with respect to the ratio of the suction volume of compression unit 11.
Like this, by blade oil supply 8a is constituted as follows, promptly, its volume is 0.01%～1% with respect to the ratio of the suction volume of compression unit 11, can prevent the reduction of the sliding that causes owing to shortage of oil, and the intake that can prevent the refrigeration agent that causes owing to overfueling reduces, and can prevent to discharge the increase of the oil ratio example in the gas.Thus, can reduce the discharge of the oil in refrigerating circuit, prevent that the heat exchange efficiency of heat exchanger from reducing.
Description of reference numerals
1 lower container; The 1a suction pipe; 2 upper container; The 2a discharge tube; 3,23 upper bearing (metal)s; 3a, 23a back pressure groove; 3b, 23b gas communication road; 4,24 lower bearings; 5 cylinders; 6,26; 6a, 26a oil-sucking hole; 6b, 26b oil supply hole; 7,27 rollers; 7a, 27a blade groove; 7b, 27b blade backpressure chamber; 8 blades; 8a blade oil supply; The 8b connectivity slot; 9 centrifugal pumps; 10 bearing face oil supplys; 11,21 compression units; 12 stators; 13 rotors; 14 electrodynamic elements; 15 suction ports; 16 exhaust ports; 20 pressing chambers; 20a, 20b operating chamber; The 27c oil supply; 30 storages
Claims (5)
1. rotary blade type compressor has the compression unit that makes the refrigeration agent compression in seal container and as the electrodynamic element of the driving source of above-mentioned compression unit, it is characterized in that,
Above-mentioned compression unit comprises:
Axle, this axle is by above-mentioned electrodynamic element rotary driving;
Roller, this rod are configured on the axis identical with the central axis of above-mentioned axle and with this axle and together rotate;
Cylinder, the inner peripheral surface of taking in above-mentioned roller of this cylinder forms cylindric, and the central shaft of this inner peripheral surface disposes prejudicially with respect to the central axis of above-mentioned axle;
Two bearings, these two both ends of the surface that bearing seals above-mentioned cylinder;
Blade, this blade reciprocatingly slides in being formed at the blade groove of above-mentioned roller in compression section, will be separated into a plurality of operating chamber by the pressing chamber that above-mentioned roller and above-mentioned bearing form along the inner peripheral surface of above-mentioned cylinder;
Suction port, this suction port flow in the above-mentioned operating chamber refrigeration agent;
Exhaust port, this exhaust port are discharged the refrigeration agent that has compressed in above-mentioned operating chamber;
Oil feeding mechanism, this oil feeding mechanism are used for supplying with the lubricant oil that accumulates in above-mentioned sealing container bottom to above-mentioned pressing chamber,
Above-mentioned oil feeding mechanism comprises:
Inlet hole, this inlet hole are located at the axis central part of above-mentioned axle and in the end face upper shed of a side opposite with above-mentioned electrodynamic element, and the lubricant oil that utilizes this rotation will accumulate in above-mentioned sealing container bottom drinks up;
Oil supply hole, this oil supply hole be located at above-mentioned axle above-mentioned roller at least one side near end face and connect inside and outside this axle;
Bearing face oil supply, this bearing face oil supply are arranged at the end face of the above-mentioned cylinder of sealing of at least one side's above-mentioned bearing in the mode that is communicated with above-mentioned oil supply hole;
The blade oil supply, this blade oil supply is arranged on the slip surface of a side of above-mentioned blade groove of above-mentioned blade as follows, promptly the rotatable phase in regulation is communicated with above-mentioned oil supply, and is communicated with above-mentioned pressing chamber to the outstanding rotatable phase of roller peripheral part from above-mentioned blade groove at this blade.
2. rotary blade type compressor has the compression unit that makes the refrigeration agent compression in seal container and as the electrodynamic element of the driving source of above-mentioned compression unit, it is characterized in that,
Above-mentioned compression unit comprises:
Axle, this axle is by above-mentioned electrodynamic element rotary driving;
Roller, this rod are configured on the axis identical with the central axis of above-mentioned axle and with this axle and together rotate;
Cylinder, the inner peripheral surface of taking in above-mentioned roller of this cylinder forms cylindric, and the central shaft of this inner peripheral surface disposes prejudicially with respect to the central axis of above-mentioned axle;
Two bearings, these two both ends of the surface that bearing seals above-mentioned cylinder;
Blade, this blade reciprocatingly slides in being formed at the blade groove of above-mentioned roller in compression section, will be separated into a plurality of operating chamber by the pressing chamber that above-mentioned roller and above-mentioned bearing form along the inner peripheral surface of above-mentioned cylinder;
Suction port, this suction port flow in the above-mentioned operating chamber refrigeration agent;
Exhaust port, this exhaust port are discharged the refrigeration agent that has compressed in above-mentioned operating chamber;
Oil feeding mechanism, this oil feeding mechanism are used for supplying with the lubricant oil that accumulates in above-mentioned sealing container bottom to above-mentioned pressing chamber,
Above-mentioned oil feeding mechanism comprises:
Inlet hole, this inlet hole are located at the axis central part of above-mentioned axle and in the end face upper shed of a side opposite with above-mentioned electrodynamic element, and the lubricant oil that utilizes this rotation will accumulate in above-mentioned sealing container bottom drinks up;
Oil supply hole, this oil supply hole be located at above-mentioned axle above-mentioned roller at least one side near end face and connect inside and outside this axle;
Oil supply, this oil supply are arranged at least one side's of above-mentioned roller above-mentioned bearing side end face in the mode that is communicated with above-mentioned oil supply hole;
The blade oil supply, this blade oil supply is arranged on the slip surface of a side of above-mentioned blade groove of above-mentioned blade as follows, promptly the rotatable phase in regulation is communicated with above-mentioned oil supply, and is communicated with above-mentioned pressing chamber to the outstanding rotatable phase of roller peripheral part from above-mentioned blade groove at this blade.
3. rotary blade type compressor according to claim 2 is characterized in that,
Also has connectivity slot, this connectivity slot with the slip surface from a side of above-mentioned blade extend to the slip surface of opposite side mode, be arranged on a side of the above-mentioned blade oil supply of the ratio inner end of above-mentioned blade, even and be arranged on this blade from above-mentioned blade groove during to the outstanding compression of roller peripheral part also not with position that above-mentioned pressing chamber is communicated with on, this connectivity slot is communicated with above-mentioned oil supply at the rotatable phase of stipulating.
4. according to any described rotary blade type compressor in the claim 1～3, it is characterized in that,
On corresponding and the side of the pressure of the refrigeration agent when above-mentioned blade oil supply is formed on the compression of not bearing with above-mentioned blade from a side of the counter-force at blade groove peripheral part edge.
5. according to any described rotary blade type compressor in the claim 1～3, it is characterized in that,
The volume of above-mentioned blade oil supply is 0.01%～1% with respect to the ratio of the suction volume of above-mentioned compression unit.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-117585 | 2010-05-21 | ||
| JP2010117585A JP5366884B2 (en) | 2010-05-21 | 2010-05-21 | Vane rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102251969A true CN102251969A (en) | 2011-11-23 |
| CN102251969B CN102251969B (en) | 2014-03-19 |
Family
ID=44979463
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110104535.XA Active CN102251969B (en) | 2010-05-21 | 2011-04-26 | Rotary vane type compressor |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5366884B2 (en) |
| KR (1) | KR101214672B1 (en) |
| CN (1) | CN102251969B (en) |
| CZ (1) | CZ305714B6 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105952644A (en) * | 2016-07-07 | 2016-09-21 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary-vane-type compressor |
| CN106321443A (en) * | 2016-10-17 | 2017-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding vane for compressor and compressor with sliding vane |
| CN109072915A (en) * | 2016-03-24 | 2018-12-21 | 大丰工业株式会社 | Impeller pump |
| CN112324660A (en) * | 2020-10-09 | 2021-02-05 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016139731A1 (en) * | 2015-03-02 | 2016-09-09 | 三菱電機株式会社 | Rotary type compressor, and method for producing same |
| JP2016160856A (en) * | 2015-03-03 | 2016-09-05 | 三菱電機株式会社 | Rotary compressor |
| CN108930651B (en) * | 2018-08-31 | 2024-02-27 | 珠海格力电器股份有限公司 | Pump body assembly and compressor |
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| CN106321443A (en) * | 2016-10-17 | 2017-01-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Sliding vane for compressor and compressor with sliding vane |
| CN112324660A (en) * | 2020-10-09 | 2021-02-05 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
| CN112324660B (en) * | 2020-10-09 | 2021-10-15 | 珠海格力电器股份有限公司 | Pump body subassembly, compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20110128230A (en) | 2011-11-29 |
| JP5366884B2 (en) | 2013-12-11 |
| CZ2011199A3 (en) | 2012-05-30 |
| CZ305714B6 (en) | 2016-02-17 |
| JP2011247091A (en) | 2011-12-08 |
| KR101214672B1 (en) | 2012-12-21 |
| CN102251969B (en) | 2014-03-19 |
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