CN102162446A - Vane rotary type fluid device and compressor - Google Patents
Vane rotary type fluid device and compressor Download PDFInfo
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- CN102162446A CN102162446A CN2011100391016A CN201110039101A CN102162446A CN 102162446 A CN102162446 A CN 102162446A CN 2011100391016 A CN2011100391016 A CN 2011100391016A CN 201110039101 A CN201110039101 A CN 201110039101A CN 102162446 A CN102162446 A CN 102162446A
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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
- F04C29/0021—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)
- Rotary Pumps (AREA)
Abstract
The invention provides a vane rotary type fluid device and a compressor capable of reducing the loss due to the sliding of the front end of a vane on the inner circumferential surface of a cylinder and improving the compression or expansion efficiency. A compression element (12) and an electric element (15) served as the driving source of the compression element (12) are arranged inside an enclosed container. The compression element (12) is equipped with a shaft (6), a roller (7), a cylinder (5), two bearings (3, 4), a separation vane (8), a suction inlet (18), an outlet (19) and a position restriction mechanism. The position restriction mechanism limits the position of the front end of the vane (8), so that the front end of the vane is placed along the inner circumferential surface of the cylinder (5). The position restriction mechanism is equipped with an annular groove (17) formed on at least one of the two bearings (3, 4) and on a concentric circle of the inner circumferential surface of the cylinder (5) and a ring (9) combined with the front end of the vane (8) and slidably and freely arranged inside the annular groove (7).
Description
Technical field
The present invention relates to blade rotary fluid means and the compressor that utilizes its compression function, the particularly limiting structure of leaf position as compressor that constitutes freeze cycle or decompressor use.In addition, mainly be that example describes below with the blade rotary compressor.
Background technique
Blade rotary compressor has by the axle of electric element rotary driving, with the roller of axle rotation simultaneously with reciprocatingly slide in compression section in being formed at the blade groove of roller and operating chamber is separated into the blade of a plurality of operating chamber, and the front end of blade carries over the internal surface ground rotational slide in cylinder body.
This blade rotary compressor need make the front end of blade carry in the internal surface of cylinder body and move, and needs the action of blade is controlled for this reason, is studying mechanism of all kinds.For example, the scheme (for example with reference to patent documentation 1) of two kinds of mechanisms has been proposed as the example of leaf position limting mechanism.
First kind of position restriction mechanism (hereinafter referred to as the primary importance limting mechanism) is such mechanism, promptly, by form make the blade guide portion of being located at blade and be located at the concentric circle of cylinder body inner peripheral surface on the slot part formation of sliding, come the position of limit blade, the front end of blade carries over the internal surface ground rotational slide in cylinder body.
Second kind of position restriction mechanism (hereinafter referred to as second place limting mechanism) is such mechanism, promptly, by form make the jut of being located at blade be positioned at the concentric circle of cylinder body inner peripheral surface on the formation of groove rotational slide, come the position of limit blade, the front end of blade carries over the internal surface ground rotational slide in cylinder body.
Patent documentation 1: TOHKEMY 2006-125361 communique (Fig. 1)
Summary of the invention
The generation of surface failures such as friction, wearing and tearing, sintering is arranged between the two sides of mechanical part, prevent from or alleviate these to damage, not only can improve the reliability of parts, and can raise the efficiency.Therefore, by supply of lubricant between the two sides, protection relative movement face prevents surface failure.The lubricated form that is formed by this oiling agent can be divided into fluid lubrication and boundary lubrication substantially.So-called fluid lubrication is to compare the fully thick fluid film of surface roughness, separate lubricating status between rubbing surface fully forming between rubbing surface, and is few by fricative loss.On the other hand, so-called boundary lubrication is the lubricating status that makes this fluid film attenuation, produces the direct contact between rubbing surface, and is big by fricative loss.
, the blade rotary fluid means of prior art as described above, control blade action so that the front end of blade carries over the internal surface in cylinder body.At this moment, because slide between the two sides, thus big by fricative loss, cause compression efficiency or expansion efficiency to reduce.Such in order to reduce by fricative loss, studying mechanism miscellaneous, in above-mentioned patent documentation 1, the scheme of primary importance limting mechanism and second place limting mechanism has been proposed as described above.
But the primary importance limting mechanism is because of front end and the slide part of being located at the groove of cylinder body at blade, and both are not chimeric such curvature, and shape has than big-difference, so the front end of blade becomes boundary lubrication with the lubricating status of being located at the slot part of cylinder body.For this reason, big by fricative loss, make compression efficiency or expansion efficiency reduce.
In addition, second place limting mechanism is because the center of the center of the front end R angular shape of blade and pin is inconsistent, so the distance of the internal surface of the center of the front end R angular shape of blade and cylinder body changes.Therefore, for the front end that makes blade does not slide at the internal surface of cylinder body, at least one side must form the elliptical shape of non-circular shape in the inner surface configuration of cylinder body and the groove shape of bearing.For this reason, has the problem that is difficult to carry out machining.
In addition, because at the jut of blade be located at slide part between the groove of bearing, both are not chimeric such curvature, and shape has than big-difference, so the jut of blade and the lubricating status of being located at the slot part of bearing become boundary lubrication.For this reason, big by fricative loss, make compression efficiency or expansion efficiency reduce.
The present invention makes for addressing the above problem, and its objective is to provide to reduce loss, blade rotary fluid means that has improved compression efficiency or expansion efficiency that the slip by the inner peripheral surface of the front end of blade and cylinder body causes and the compressor that utilizes its compression function at least.
Blade rotary fluid means of the present invention, this blade rotary fluid means possess the electric element that makes refrigeration agent compression or the compressing member or the expansion element that expand and become the driving source of above-mentioned compressing member or expansion element in seal container, wherein,
Above-mentioned compressing member or expansion element possess:
Axle, this axle is by above-mentioned electric element rotary driving,
Roller, this roller are entrenched in above-mentioned axle and go up and be rotated, be positioned on the axle with the spigot shaft coaxle of above-mentioned axle,
Cylinder body, this cylinder body is taken in above-mentioned roller, inner peripheral surface is a drum, and the central shaft of above-mentioned inner peripheral surface with respect to the rotating shaft eccentric of above-mentioned axle set,
Two bearings, the both ends of the surface of the inaccessible above-mentioned cylinder body of these two bearings,
Blade, this blade reciprocatingly slides in being formed at the blade groove of above-mentioned roller in compression section or in the expansion stroke, will be separated into a plurality of operating chamber by pressing chamber or the expansion chamber that above-mentioned cylinder body, above-mentioned roller and above-mentioned bearing form,
Suction port, this suction port flow in the above-mentioned operating chamber refrigeration agent,
Exhaust port, this exhaust port will compress in above-mentioned operating chamber or dilated refrigeration agent is discharged and
Position restriction mechanism, this position restriction mechanism carry over the front position that limits above-mentioned blade in the mode of the inner peripheral surface of above-mentioned cylinder body with the front end of above-mentioned blade;
Above-mentioned position restriction mechanism possesses:
Annular groove, this annular groove are located at least one side in above-mentioned two bearings, be formed on the concentric circle of the above-mentioned inner peripheral surface of above-mentioned cylinder body on and
Ring is provided in the above-mentioned annular groove this ring free sliding, combines with the front end of above-mentioned blade.
According to blade rotary fluid means of the present invention,, can make between the two sides of inner peripheral surface of the front end of blade and cylinder body and not slide by adopting above-mentioned formation.For this reason, can reduce the loss that the slip because of the inner peripheral surface of the front end of blade and cylinder body of prior art causes, reduce the loss that produces by sliding, improve compression efficiency or expansion efficiency.
Description of drawings
Fig. 1 is the sectional arrangement drawing of the blade rotary compressor of embodiments of the present invention 1.
Fig. 2 is the figure of the leaf position relation in the compression section of compressor of presentation graphs 1.
Fig. 3 is the figure of the connecting state of the blade of compressor of presentation graphs 1 and ring and pin.
Fig. 4 is the figure of relation of the inner peripheral surface of the front end of blade of compressor of presentation graphs 1 and cylinder body.
Fig. 5 is the figure of detailed situation of compressing member of the compressor of presentation graphs 1, and the blade of presentation graphs 7 is the section of 180deg position.
Fig. 6 is the decomposition summary pie graph of relation of center line of compressing member of the compressor of presentation graphs 1, and the ground, top that shortens axle omits expression.
Fig. 7 is the figure of leaf position of compression process of the compressor of presentation graphs 1.
Fig. 8 is the figure of the connecting state of expression blade of embodiments of the present invention 5 and ring.
Fig. 9 is the figure of slip of the outer circumferential face of the outer circumferential face of the inner peripheral surface of the inner peripheral surface of ring of expression embodiments of the present invention 6 and annular groove and ring and annular groove.
Description of reference numerals
1: lower container, 1a: suction pipe, 2: upper container, 2a: discharge tube, 3: upper bearing (metal), 4: lower bearing, 5: cylinder body, 6: axle, 7: roller, 7a: blade groove, 8: blade, 9: ring, 10: pin, 12: compressing member, 13: stator, 14: rotor, 15: electric element, 16: back pressure chamber, 17: annular groove, 18: suction port, 19: exhaust port, 20,20a, 20b: operating chamber, 30: reservoir.
Embodiment
Mode of execution 1.
Fig. 1 is the sectional arrangement drawing of the blade rotary compressor of embodiments of the present invention 1, Fig. 2 is the figure of the leaf position relation in the compression section of compressor of presentation graphs 1, Fig. 3 is the figure of the connecting state of expression blade and ring and pin, and Fig. 4 is the figure of the relation of expression blade front end and cylinder body inner peripheral surface.Fig. 5 is the figure of detailed situation of compressing member of the compressor of presentation graphs 1, and the blade of presentation graphs 7 is the section of 180deg position.Fig. 6 is the decomposition summary pie graph of relation of center line of compressing member of the compressor of presentation graphs 1, and the ground, top that shortens axle omits record.Fig. 7 is the figure of leaf position of compression process of the compressor of presentation graphs 1.
As shown in Figures 1 and 2, blade rotary compressor is taken in compressing member 12, electric element 15 and not shown refrigerator oil in the seal container that is made of lower container 1 and upper container 2.
Connect the suction pipe 1a that is communicated with reservoir 30 in lower container 1, be taken into refrigeration agent (gas) from reservoir 30.In addition, connect discharge tube 2a, discharge compressed refrigeration agent on the top of upper container 2.
Compressing member 12 has upper bearing (metal) 3, lower bearing 4, cylinder body 5, axle 6, roller 7 and blade 8, and their mutual position relations become the formation of representing at the decomposition summary pie graph of the sectional drawing of Fig. 5 and Fig. 6.
The both ends of the surface of upper bearing (metal) 3 and lower bearing 4 inaccessible cylinder bodies 5 (with reference to Fig. 5, Fig. 6).
In addition, at least one side in above-mentioned upper bearing (metal) 3 or lower bearing 4, with the concentric circle of operating chamber 20 on form annular groove 17 (with reference to Fig. 4 to Fig. 6, Fig. 9), be formed at lower bearing 4 in this embodiment.In this annular groove 17, set free sliding and encircled for 9 (with reference to Fig. 4 to Fig. 6).In addition, at ring 9 blade 8 is installed.
Then, to blade 8 and encircle 9 mounting structure and describe.
As shown in Figures 2 and 3, by at ring 9 and blade 8 pin-and-hole 9a, 8a being set respectively, insert cylinder type pin 10 in this pin-and-hole 9a, 8a, blade 8 can be with respect to annular groove 17 rotations.
In addition, as shown in Figure 4, in the center of the front end R angular shape of blade 8 mode consistent with the center of pin 10 in conjunction with both.
In addition, the pin 10 of above-mentioned annular groove 17, ring 9 and coupling collar 9 and blade 8 constitutes position restriction mechanism of the present invention.
Then, the action to above-mentioned blade rotary compressor describes.
Compressor is drawn into the refrigeration agent of reservoir 30 by means of suction pipe 1a and suction port 18 the operating chamber 20a of operating chamber 20 (pressing chamber).In addition, axle 6 is by electric element 15 rotations, and the roller 7 that is entrenched on the axle 6 also rotates.Reciprocating blade 8 and also rotate among the blade groove 7a on being formed at this roller 7 by means of pin 10 and the ring 9 that this blade 8 links.At this moment, because the inner peripheral surface of cylinder body 5 is drums, the central shaft of inner peripheral surface sets with respect to the rotating shaft eccentric ground of axle 6 simultaneously, so, make the distance change of the inner peripheral surface of roller 7 and cylinder body 5 by the rotation of roller 7.But, blade 8 links with the ring 9 that slides in being in the annular groove 17 that is concentric circles with operating chamber 20, in cylinder body 5, can rotate, the center that is mounted to front end R angular shape is consistent with the center of pin 10, so, between the inner peripheral surface of the center of the front end R of blade 8 angular shape and cylinder body 5, must form gap (space), can make between the two sides and not slide.This is the action of leaf position limting mechanism of the present invention.In addition, compressed refrigeration agent is discharged from exhaust port 19 along with roller 7 rotations, finally discharges from discharge tube 2a.
Then, based on Fig. 7 the compressed action as the operating chamber 20 of pressing chamber is described.
When blade 8 was the position of 0deg, the front end of blade 8 was in the position identical substantially with the circumferential position of roller 7, and the micro-gap of the degree that compression efficiency is not exerted an influence with the freezing medium leakage between the inner peripheral surface of the front end of blade 8 and cylinder body 5 is separated.In addition, because the fore-end of blade 8 links with the ring 9 that slides in annular groove 17, so, along with roller 7 rotations, ring 9 rotations, blade 8 is pulled out from roller 7, and the front end of blade 8 keeps the state of the micro-gap of degree that freezing medium leakage is not exerted an influence to be rotated along the inner peripheral surface of cylinder body 5, so, the refrigeration agent in the 20b of compressed action chamber.In addition, when the position from blade 8 is the position of 180deg, blade 8 returns in the roller 7 again, is compressed in operating chamber 20b, and when reaching the head pressure of regulation, refrigeration agent is discharged from exhaust port 19.In addition, in the compressed action of this refrigeration agent, because suck refrigeration agents from suction port 18 in operating chamber 20a side, so, by the rotation of roller 7, carry out refrigeration agent repeatedly from the suction of suction port 18 with from the discharge of exhaust port 19.
Then, the effect to above-mentioned blade rotary compressor describes.
As shown in Figure 3, because at least one side in two bearings 3,4 is provided with annular groove 17, on ring 9 that slides with this annular groove 17 and blade 8, pin-and-hole 9a, 8a are set respectively, in this pin-and-hole 9a, 8a, insert cylinder type pin 10 and link both, so blade 8 is with respect to annular groove 17 rotations.And then, because the center of the front end R angular shape of blade 8 is consistent with the center of pin 10, so, between the inner peripheral surface of the center of the front end R of blade 8 angular shape and cylinder body 5, must form gap (space).At this, form the gap between the inner peripheral surface of the front end of blade 8 and cylinder body 5 because very small and and less influence the reduction of volumetric efficiency.In addition, because the lubricating status of the inner peripheral surface of the front end of blade 8 and cylinder body 5 becomes fluid lubrication, the loss that forms by sliding is few, so can improve compression efficiency.
In addition, because the center of the front end R angular shape of blade 8 is consistent with the center of pin 10, so, even form these both sides of shape of the annular groove 17 of the inner peripheral surface shape of cylinder body 5 and bearing 3,4 round-shaped, in compression process, the front end of blade 8 can be not slide at the inner peripheral surface of cylinder body 5 yet.Its result, the machining of the shape of the annular groove 17 of the inner peripheral surface face shape of cylinder body 5 and bearing 3,4 becomes easy.
In addition, at least one side among pin-and-hole 8a, the 9a of pin 10 and blade 8 and ring 9 slides, at the slide part of pin 10 with pin-and-hole 8a, 9a, because pin-and-hole 8a, 9a and pin 10 are to carry out chimeric such curvature, both shapes are similar, so pin 10 becomes fluid lubrication with the lubricating status of pin-and-hole 8a, 9a.Its result is because the loss that produces by sliding is few, so can improve compression efficiency.
In addition, ring 9 is located at least one side in two bearings 3,4, with be positioned at the concentric circle of cylinder body 5 on annular groove 17 slide, but slide part at ring 9 and annular groove 17, because encircle 9 and annular groove 17 for carrying out chimeric such curvature, both shapes are similar, so the lubricating status of ring 9 and annular groove 17 becomes fluid lubrication.Its result is because the loss that produces by sliding is few, so can improve compression efficiency.
In addition, at the slide part of pin 10 and ring 9, because the centrifugal force that utilizes the rotation by axle 6 to form carries out fuel feeding (not shown), so can not cause abnormal wear because of slip.
Mode of execution 2.
In addition, in above-mentioned mode of execution 1, roller 7 is rotated with above-mentioned axle on axle 6 chimericly, but roller 7 also can be integrated with axle 6.
Mode of execution 3.
In above-mentioned mode of execution 1, as position restriction mechanism, just be illustrated at the example that with the annular groove 17 that is located at least one side in two bearings 3,4 pin-and-hole 9a, 8a takes place to be provided with respectively on the ring 9 that slides and the blade 8, insert cylinder type pin 10 to this pin-and-hole 9a, 8a, but when inserting cylinder type pin 10, also can be inserted into blade 8 to pin 10 movable fits ground and encircle among 9 both sides' pin-and-hole 8a, the 9a to this pin-and-hole 9a, 8a.In addition, pin-and-hole 9a, 8a differ and are decided to be through hole, also can be the recesses that the end is arranged.
Mode of execution 4.
In addition, when cylinder type pin 10 is inserted into pin-and-hole 9a, 8a, also can inserts in the mode of interference fit, and insert in the mode of movable fit at another pin-and-hole (for example 9a) at a pin-and-hole (for example 8a).In addition, pin-and-hole 9a, 8a differ and are decided to be through hole, also can be the recesses that the end is arranged.
Mode of execution 5.
In above-mentioned mode of execution 1, as position restriction mechanism, be illustrated, but also can substitute pin 10, at blade 8 or encircle jut is set on 9 with regard to the example that pin 10 is set.
Fig. 8 (a) is provided with jut 10a, is encircling 9 examples that are provided with for the hole 9b of this jut 10a insertion at blade 8, and Fig. 8 (b) is the example that at ring 9 jut 10b is set, the hole 8b that supplies this jut 10b insertion is set at blade 8.
In this case, be inserted among hole 9b, the 8b, blade 8 is with respect to annular groove 17 rotations jut 10a, 10b movable fit.In addition, hole 9b, 8b differ and are decided to be through hole, also can be the recesses that the end is arranged.
Mode of execution 6.
In addition, in above-mentioned mode of execution 1, as Fig. 9 (a) (b) shown in, ring 9 also can be arranged to slide with the inner peripheral surface of annular groove 17 or any one face in the outer circumferential face.
At first, shown in Fig. 9 (a), be arranged to encircle under the situation that 9 the inner peripheral surface inner peripheral surface at annular groove 17 slides, and be arranged to encircle the situation that 9 the outer circumferential face outer circumferential face at annular groove 17 slides and compare, ring 9 reduces in the distance that annular groove 17 slides, so can improve compression efficiency.
Then, shown in Fig. 9 (b), be arranged to encircle under the situation that 9 the outer circumferential face outer circumferential face at annular groove 17 slides, comparing with being arranged to encircle the situation that 9 the inner peripheral surface inner peripheral surface at annular groove 17 slides, the gap smaller of ring 9 and annular groove 17 is so can improve volumetric efficiency.
Mode of execution 7.
In addition, above-mentioned explanation all is the situation that blade rotary fluid means of the present invention is applicable to compressor, but the present invention is also applicable to decompressor (blade rotary decompressor).In this case, in the example of Fig. 2, constitute roller 7, be taken into the refrigeration agent of expansion object, dilated refrigeration agent is discharged from suction port 18 from exhaust port 19 to the direction rotary driving opposite with above-mentioned example.
Mode of execution 8.
In addition, any blade rotary fluid means of the present invention in the above-mentioned explanation, the pressure difference of operating chamber 20a, 20b acts on blade 8 as differential pressure, the blade groove 7a easy deformation of roller 7.For this reason, it is desirable to the low normal boiling point of usage operation pressure for the low normal boiling point of hydrocarbon (for example propane, butane, isobutane etc.), operating pressure more than-45 ℃ for the low normal boiling point of saturated hydrofluorocarbon (for example R134a, R152a etc.), operating pressure more than-45 ℃ for the unsaturated hydrofluorocarbon (for example HFO1234yf, 1234ze, 1243zf etc.) more than-45 ℃ or the low normal boiling point of operating pressure is the mix refrigerant (for example R407C, R417A, R422D etc.) more than-45 ℃.
Claims (9)
1. blade rotary fluid means, this blade rotary fluid means possess the electric element that makes refrigeration agent compression or the compressing member or the expansion element that expand and become the driving source of described compressing member or expansion element in seal container, it is characterized in that,
Described compressing member or expansion element possess:
Axle, this axle is by described electric element rotary driving,
Roller, this roller are installed in described axle and go up and be rotated, be positioned on the axle with the spigot shaft coaxle of described axle,
Cylinder body, this cylinder body is taken in described roller, inner peripheral surface is a drum, and the central shaft of described inner peripheral surface with respect to the rotating shaft eccentric of described axle set,
Two bearings, the both ends of the surface of the inaccessible described cylinder body of these two bearings,
Blade, this blade reciprocatingly slides in being formed at the blade groove of described roller in compression section or in the expansion stroke, will be separated into a plurality of operating chamber by pressing chamber or the expansion chamber that described cylinder body, described roller and described bearing form,
Suction port, this suction port flow in the described operating chamber refrigeration agent,
Exhaust port, refrigeration agent that this exhaust port will be compressed in described operating chamber or expand discharge and
Position restriction mechanism, this position restriction mechanism carry over the front position that limits described blade in the mode of the inner peripheral surface of described cylinder body with the front end of described blade;
Described position restriction mechanism possesses:
Annular groove, this annular groove are located at least one side in described two bearings, be formed on the concentric circle of the described inner peripheral surface of described cylinder body on and
Ring is provided in the described annular groove this ring free sliding, combines with the front end of described blade.
2. blade rotary fluid means as claimed in claim 1 is characterized in that, described position restriction mechanism,
Possess the pin-and-hole that is formed at described blade and described ring respectively and be inserted in the cylinder type pin of this pin-and-hole, be configured to described blade and can rotate with respect to described annular groove,
The center of this R angular shape that is configured to the described blade that front end is made of the R angular shape is consistent with the center of described pin.
3. blade rotary fluid means as claimed in claim 2 is characterized in that, is inserted in the two the pin-and-hole of described blade and described ring described pin movable fit.
4. blade rotary fluid means as claimed in claim 2 is characterized in that, be inserted in the pin-and-hole of either party in described blade and the described ring to described pin interference fit, and movable fit be inserted in the opposing party's the pin-and-hole.
5. blade rotary fluid means as claimed in claim 1 is characterized in that, described position restriction mechanism,
Possess the jut that is formed on either party in described blade and the described ring and be formed on described blade and described ring in the opposing party and the hole portion that inserts for described jut,
Be configured to described blade and can rotate with respect to described annular groove, and,
The center of this R angular shape that is configured to the described blade that front end is made of the R angular shape is consistent with the center of described pin.
6. as each described blade rotary fluid means in the claim 1 to 5, it is characterized in that the either party slides in the outer circumferential face of the described relatively annular groove of described ring and the inner peripheral surface.
7. as each described blade rotary fluid means in the claim 1 to 5, it is characterized in that described axle becomes one with described roll forming.
8. a compressor is characterized in that, as each described blade rotary fluid means in the claim 1 to 5 be have as described in the blade rotary compressor of pressing chamber and compressed refrigerant.
9. as each described blade rotary fluid means in the claim 1 to 5, it is characterized in that the normal boiling point that usage operation pressure is low is the low normal boiling point of hydrocarbon, the operating pressure more than-45 ℃ for the saturated or undersaturated hydrofluorocarbon more than-45 ℃ or the low normal boiling point of operating pressure is the mix refrigerant more than-45 ℃.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-032532 | 2010-02-17 | ||
| JP2010032532A JP5366856B2 (en) | 2010-02-17 | 2010-02-17 | Vane rotary type fluid apparatus and compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102162446A true CN102162446A (en) | 2011-08-24 |
Family
ID=44463843
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100391016A Pending CN102162446A (en) | 2010-02-17 | 2011-02-16 | Vane rotary type fluid device and compressor |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5366856B2 (en) |
| KR (1) | KR101278772B1 (en) |
| CN (1) | CN102162446A (en) |
| CZ (1) | CZ306330B6 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103930677A (en) * | 2012-01-11 | 2014-07-16 | 三菱电机株式会社 | Vane-type compressor |
| CN106382224A (en) * | 2016-12-02 | 2017-02-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and electrical product comprising same |
| CN106401969A (en) * | 2016-10-17 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
| CN106401967A (en) * | 2016-10-17 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
| CN106870361A (en) * | 2017-03-30 | 2017-06-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, compressor and heat-exchange system |
| CN113446219A (en) * | 2020-03-25 | 2021-09-28 | Lg电子株式会社 | Rotary compressor |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104632632A (en) * | 2013-11-15 | 2015-05-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Air cylinder of compressor, compressor, air conditioner with compressor and heat pump water heater with compressor |
| JP6227489B2 (en) * | 2014-06-18 | 2017-11-08 | 愛三工業株式会社 | Vane pump |
| CN108626922B (en) | 2017-03-17 | 2020-12-04 | Lg电子株式会社 | Liquid storage device |
| KR20180118397A (en) | 2017-04-21 | 2018-10-31 | 엘지전자 주식회사 | Accumulator |
| KR102499761B1 (en) | 2021-02-04 | 2023-02-15 | 엘지전자 주식회사 | Rotary compressor |
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| JPS6373593U (en) * | 1986-11-04 | 1988-05-17 | ||
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103930677A (en) * | 2012-01-11 | 2014-07-16 | 三菱电机株式会社 | Vane-type compressor |
| CN103930677B (en) * | 2012-01-11 | 2016-08-24 | 三菱电机株式会社 | Blade-tape compressor |
| CN106401969A (en) * | 2016-10-17 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
| CN106401967A (en) * | 2016-10-17 | 2017-02-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
| CN106401967B (en) * | 2016-10-17 | 2019-03-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary compressor |
| CN106382224A (en) * | 2016-12-02 | 2017-02-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and electrical product comprising same |
| CN106870361A (en) * | 2017-03-30 | 2017-06-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, compressor and heat-exchange system |
| CN113446219A (en) * | 2020-03-25 | 2021-09-28 | Lg电子株式会社 | Rotary compressor |
| CN113446219B (en) * | 2020-03-25 | 2023-03-14 | Lg电子株式会社 | Rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101278772B1 (en) | 2013-06-25 |
| JP2011169199A (en) | 2011-09-01 |
| JP5366856B2 (en) | 2013-12-11 |
| KR20110095155A (en) | 2011-08-24 |
| CZ201178A3 (en) | 2012-05-23 |
| CZ306330B6 (en) | 2016-12-07 |
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Application publication date: 20110824 |