CN103477079B - Scrawl compressor - Google Patents
Scrawl compressor Download PDFInfo
- Publication number
- CN103477079B CN103477079B CN201280018752.XA CN201280018752A CN103477079B CN 103477079 B CN103477079 B CN 103477079B CN 201280018752 A CN201280018752 A CN 201280018752A CN 103477079 B CN103477079 B CN 103477079B
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- China
- Prior art keywords
- lining
- radial bearing
- counterweight
- rotary
- vortex
- Prior art date
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- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0253—Details concerning the base
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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
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
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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
- F04C2240/50—Bearings
- F04C2240/51—Bearings for cantilever assemblies
-
- 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
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- 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
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
There is provided a kind of Scrawl compressor, even if when High Rotation Speed, the rotational resistance that also can be suppressed to the vortex wall of right scroll element increases, and avoids peeling off in the part abutted against with lining of radial bearing.This Scrawl compressor will be embedded in the eccentric shaft (17) of the end being located at live axle (12) outside lining (23), this lining (23) is supported on radial bearing (24) in the mode that can relatively rotate, lining (23) is provided with the counterweight (32) becoming to be integrated with this lining, radial bearing (24) is located in the shaft hub (22b) at the back side being formed at rotary vortex rotary part (22), when lining (23) tilts, the outer circumferential face of this lining is only abutted with radial bearing (24) in the side, end being provided with counterweight (32).Specifically, eccentric shaft (17) is made to be less than the gap (C) of the outer circumferential face of radial bearing (24) and lining (23) with the gap (A) of the inner peripheral surface of the eccentric opening (23a) of lining (23).
Description
Technical field
The present invention relates to the Scrawl compressor of a kind of freeze cycle for air conditioner for vehicles etc., the eccentric shaft particularly relating to the end possessed being located at live axle is set up in the Scrawl compressor of the structure of the shaft hub of rotary vortex rotary part via lining and radial bearing.
Background technique
Scrawl compressor possesses fixed scroll member and rotary vortex rotary part, this fixed scroll member has end plate and erects the vortex wall of setting from this end plate, this rotary vortex rotary part and this fixed scroll member are oppositely disposed and have end plate and erect the vortex wall of setting from this end plate, Scrawl compressor is by making this pair scroll element mutually combine respective vortex wall and making rotary vortex rotary part rotate (revolution motion) at the confined state lower swing of rotation, the pressing chamber be formed between the vortex wall of two scroll elements is made to reduce volume while move to center, carry out the compression of working fluid.
In this Scrawl compressor, rotary vortex rotary part is formed with shaft hub at the back side of end plate, by making the eccentric shaft being located at live axle one end be set up in this shaft hub via radial bearing, thus be supported to can centered by the axle center of live axle swing rotary (revolution motion).
Now, if there is gap between the side of the vortex wall of two scroll elements, then pressurized gas will leak from the pressing chamber of central side (downstream side) to peripheral part side (upstream side), so compression efficiency will be adversely affected.Therefore, have employed the mechanism making the revolution-radius amount of rotary vortex rotary part variable, namely live axle eccentric shaft and be located at rotary vortex rotary part shaft hub radial bearing (bearing portion) between be provided as the lining of intermediate member, utilize the component of the compression counter-force acted on rotary vortex rotary part, the pressured rotary vortex rotary part of radial direction to fixed scroll member, makes the side of the vortex wall of rotary vortex rotary part be connected to the side of the vortex wall of fixed scroll member and not be separated (patent documentation 1 ~ 3) with it.
Wherein, as shown in Figure 6, Scrawl compressor disclosed in patent documentation 1 has installed lining 103 in the shaft hub 102 of rotary vortex rotary part 101, but this lining 103 can not relatively rotate relative to the eccentric shaft 105 of the one end being located at live axle 104, and can to the so-called sliding-type lining of radial trace movement.In addition, eccentric shaft 105 is provided with curved face part 106, even if under producing diastrophic situation, also there is not one-side contact at bearing portion due to the compressive force of rotary vortex rotary part 101 and centrifugal force at live axle 104.And, in same publication, also disclose and counterweight 107 is being located at the structure on live axle 104 from lining 103 to the position of axial dipole field.
As shown in Figure 7, Scrawl compressor disclosed in patent documentation 2 is that the eccentric shaft 112 in the one end by being located at live axle 111 is set up in the structure of shaft hub 117 of rotary vortex rotary part 115 via lining 113 and radial bearing 114, counterweight 116 is supported by being pressed into the outer circumferential face of lining 113, and rotates together with lining 113.This counterweight 116 is stretched out to the radial outside of the shaft hub 117 of rotary vortex rotary part 115, to make the point of action of the centrifugal force acted in this counterweight 116 as far as possible close to the point of action acting on the centrifugal force on rotary vortex rotary part 115.
As shown in Figure 8, Scrawl compressor disclosed in patent documentation 3 discloses and a kind ofly to be combined with the eccentric shaft 124 being located at live axle 123 front end by the lining 122 being provided with counterweight 121 integratedly, by this lining 122 to be set up in the shaft hub 126 being located at rotary vortex rotary part 125 back side via radial bearing 127, rotary vortex rotary part 125 is made to carry out the structure of revolution motion.The same with patent documentation 2, this counterweight 121 stretches out setting to the outside of the shaft hub 126 of rotary vortex rotary part 125, but because it also stretches out setting to the side (motor side) contrary with rotary vortex rotary part 125, inhibit radial stretching out in order to try, the diameter avoiding rotary vortex rotary part 125 becomes large.
Prior art document
Patent documentation
Patent documentation 1:(Japan) Unexamined Patent 8-42467 publication
Patent documentation 2:(Japan) Unexamined Patent 8-42477 publication
Patent documentation 3:(Japan) JP 2010-196630 publication
Summary of the invention
Invent technical problem to be solved
But, in the structure (Fig. 6) of patent documentation 1, because the position arranging counterweight 107 is not lining 103, but live axle 104, so compressor centrifugal force is on the whole cancelled out each other and keeps balance, but owing to not eliminating centrifugal force rotary vortex rotary part 101 being pushed to radial outside, so the contact load of the vortex wall 101a of rotary vortex rotary part 101 and the vortex wall 108a of fixed scroll member 108 becomes large, vortex wall 101a during High Rotation Speed, the rotational resistance of 108a increases, in addition, the rough sledding such as the reliability that also there is vortex wall is adversely affected.
In addition, in the structure (Fig. 7) of patent documentation 2, because counterweight 116 stretches out setting to the outside of shaft hub 117, therefore, the anti-locking mechanism 118 of rotation is located at its radial more lateral for avoiding with the interference of counterweight 116, therefore, rotary vortex rotary part 115 maximizes, and hampers the miniaturization of compressor.In addition, the weight due to rotary vortex rotary part 115 also becomes heavy, therefore, also exists and makes counterweight 116 also must become large rough sledding to balance each other with it.
And, in the structure (Fig. 8) of patent documentation 3, because counterweight 121 also stretches out setting to the side (motor side) contrary with rotary vortex rotary part 125, therefore the centrifugal action of counterweight 121 is in lining 122 end of giving prominence to from radial bearing 127, and the axle center of lining 122 is by the axle center run-off the straight relative to eccentric shaft 124.Therefore, in order to reduce the inclination of this lining 122, in the past, have employed the gap set as small as possible between radial bearing 127 and the outer circumferential face of lining 122, the design of the power utilizing radial bearing 127 to support lining 122 is tilted, but when High Rotation Speed, the localized contact that there is bearing inner race exceeds its bearing capacity, the rough sledding of peeling off.
Particularly using needle bearing as in the structure of radial bearing, according to design philosophy in the past, as shown in Fig. 9 (a), be designed so that gap between the inner peripheral surface of radial bearing 24 and the outer circumferential face of lining 23 is (in needle bearing, be roller 24a and lining 23 outer circumferential face between gap) C as much as possible little (making C be less than gap A between lining 23 and eccentric shaft 17), but because counterweight 32 is located at the end of lining 23, the deviation of gravity center of counterweight 32 is located at the center of the eccentric shaft 17 of the end of live axle 12, therefore as shown in Figure 9 (b), the axle center of lining 23 is relative to the axle center run-off the straight of eccentric shaft 17, in this condition, the centrifugal force of counterweight 32 acts on rotary vortex rotary part 22 via lining 23 and radial bearing 24.Now, because clearance C is formed as being less than gap A, therefore, for supporting the lining 23 tilted because of the centrifugal force F1 of counterweight 32, at internal surface two place (near the end being provided with counterweight 32 [position of the position L1 acted on apart from the centrifugal force of counterweight 32 vertically] with the end of far from equilibrium counterweight 32 or it near [position of the position L2 that the centrifugal force of distance counterweight 32 vertically acts on: L2>L1] this two place) bearing load (F2 of radial bearing 24, F3), therefore, the size that the corresponding F3 of the load of F2 produces and strain large mutually, be subject to the part of load of this F2, local load enlarges markedly, easily to peel off.
The present invention makes in view of described situation, its technical problem underlying is, even if provide a kind of when High Rotation Speed, the rotational resistance that also can be suppressed to the vortex wall of right scroll element increases, and avoids the Scrawl compressor that peels off in the part abutted against with lining of radial bearing.In addition, also the miniaturization of compressor will be realized as its technical problem on this basis.
For the method for technical solution problem
For reaching above-mentioned technical problem, Scrawl compressor of the present invention possesses: fixed scroll member, and it is limited relative to moving radially of housing, has end plate and erects the vortex wall of setting from this end plate; Rotary vortex rotary part, itself and this fixed scroll member relative configuration, has end plate and erects the vortex wall of setting from this end plate; Live axle, its transmitting rotary power; Eccentric shaft, it is located at the end of described live axle, and is located at the position offset relative to the axle center of this live axle; Radial bearing, it is embedded in the shaft hub formed at the back side of described rotary vortex rotary part; Lining, it possesses the eccentric opening inserted for described eccentric shaft, is embedded in described eccentric shaft, and is supported on described radial bearing in the mode that can relatively rotate via outside this eccentric opening; Counterweight, it is located at an end of described lining and becomes to be integrated with this lining; The feature of described Scrawl compressor is, when described lining tilts, the outer circumferential face of this lining is only abutted with described radial bearing in the side, end being provided with described counterweight.
Therefore, at the point of the centrifugal action of counterweight when the position offset vertically from radial bearing (from the gasket end that radial bearing is outstanding), by the centrifugal force of this counterweight, the axle center of lining is by the axle center run-off the straight of relative eccentric axle, but when lining tilts, the outer circumferential face of this lining only abuts with radial bearing in the side, end being provided with counterweight, therefore, it is possible to by making the gasket end of far from equilibrium counterweight abut with radial bearing, avoid the state of affairs that the local load at this abutting portion place enlarges markedly.Therefore, it is possible to alleviate the partial load that radial bearing produces, so the bearing capacity of radial bearing relatively can be improved, suppress the generation of peeling off produced in the part abutted against with lining outer circumferential face of radial bearing.
At this, as when lining tilts, make lining only at the concrete structure that the side, end being provided with counterweight abuts with radial bearing, eccentric shaft and the gap of the inner peripheral surface being located at the eccentric opening on lining are being set to A, eccentric shaft and the chimeric length of the inner peripheral surface being located at the eccentric opening on lining are set to B, the gap of the outer circumferential face of radial bearing and lining is set to C, when radial bearing is set to D with the chimeric length of the outer circumferential face of lining, is set as A/B < C/D.
In addition, according to said structure, even if the point of the centrifugal action of counterweight is in the position offset vertically from radial bearing, the partial load (local load at the abutting portion place of lining and radial bearing) that also inclination with lining can be produced suppresses in permissible range, therefore, when the radial outside of the shaft hub of rotary vortex rotary part is provided with the anti-locking mechanism of rotation, also counterweight can be made to be formed as stretching out energetically to the direction away from rotary vortex rotary part, to avoid the interference of the anti-locking mechanism with rotation.
According to such structure, even if when by anti-for rotation locking mechanism near the arranged outside of the shaft hub of rotary vortex rotary part, also can avoid arranging counterweight with preventing mechanical interferences with rotation, therefore, it is possible to reduce the profile of the anti-locking mechanism of rotation, and then the external diameter of rotary vortex rotary part can be reduced.
And, use needle bearing as described radial bearing.Needle bearing is compact and lightweight, but then, if abut under the state of axle relative to the axle center run-off the straight of bearing, then interface pressure becomes excessive, therefore the inclination of supporting thrust load and axle is not suitable for, but as mentioned above, due to the local load of needle bearing and lining can be reduced, therefore, it is possible to relatively improve bearing capacity, needle bearing can be utilized fully to tackle.Therefore, it is possible to alleviate the weight of bearing, in addition, radial dimension can also be made compact, therefore can also realize the lightweight of counterweight.
The effect of invention
As mentioned above, according to the present invention, when the eccentric shaft of the end by being located at live axle to be set up in the radial bearing of the shaft hub being located at rotary vortex rotary part via the lining being integrally formed with counterweight, during lining run-off the straight, the outer circumferential face of this lining is only abutted with radial bearing in the side, end being provided with counterweight, even if so when lining tilts, the local load of the outer circumferential face of lining and the abutting portion of radial bearing does not also enlarge markedly, and can avoid peeling off in the part abutted against with lining of radial bearing.Therefore, even if when High Rotation Speed, the rotational resistance that also can be suppressed to the vortex wall of right scroll element increases, and avoids peeling off in the part abutted against with lining of radial bearing.
In addition, according to said structure, even if when counterweight stretches out formation to the direction away from rotary vortex rotary part, also can the local load at the abutting portion place of the outer circumferential face of lining and radial bearing be controlled in permissible range, therefore, even if stretching out formation counterweight to the direction away from rotary vortex rotary part, thus when locking mechanism anti-near the arranged outside rotation of shaft hub, also can avoid interfering with it, and then the external diameter of the anti-locking mechanism of rotation and rotary vortex rotary part can be reduced.
And, due to the local load at the abutting portion place of lining and radial bearing can be reduced, so needle bearing can be utilized completely to serve as radial bearing, by using needle bearing, the lightweight of the rotary vortex rotary part being provided with this needle bearing can be realized, in addition, the centrifugal force for offsetting rotary vortex rotary part can also be alleviated and the weight of counterweight that arranges.
Accompanying drawing explanation
Fig. 1 is the sectional drawing of the overall structure example representing Scrawl compressor of the present invention.
In Fig. 2 (a) ~ (b), (a) represents outer lining on the eccentric shaft of the end being located at live axle, and makes this lining be supported on the sectional drawing of the state of the radial bearing of the shaft hub being located at rotary vortex rotary part, and (b) is the exploded perspective view of (a).
Fig. 3 (a) ~ (c) is the figure representing lining, (a) be from axial unilateral observation to figure, (b) is the sectional side view of lining, and (c) is the figure observed from axial opposite side.
Fig. 4 (a) ~ (c) is the figure representing counterweight, (a) be from axial unilateral observation to figure, (b) is the sectional side view of counterweight, and (c) is the figure observed from axial opposite side.
Fig. 5 (a) ~ (b) is the eccentric shaft of the end represented being located at live axle is set up in the state of the radial bearing of the shaft hub being located at rotary vortex rotary part enlarged view via the lining that an end is provided with counterweight, a () is the figure representing the state that live axle does not rotate, (b) represents that live axle rotates and the figure of the state of lining run-off the straight.
Fig. 6 is the sectional drawing representing existing Scrawl compressor.
Fig. 7 is the sectional drawing representing other Scrawl compressors existing.
Fig. 8 is the sectional drawing representing other Scrawl compressors existing.
Fig. 9 (a) ~ (b) is the eccentric shaft of the end represented being located at live axle is set up in the standing state of the radial bearing of the shaft hub being located at rotary vortex rotary part enlarged view via the lining that an end is provided with counterweight, a () is the figure representing the state that live axle does not rotate, (b) represents that live axle rotates and the figure of the state of lining run-off the straight.
Embodiment
Below, with reference to accompanying drawing, Scrawl compressor of the present invention is described.
In FIG, Scrawl compressor 1 take refrigeration agent as the power type compressor being suitable for freeze cycle of working fluid, and in the housing 2 be made up of aluminum alloy, left side arranges compressing mechanism 3 in the drawings, in addition, right side arranges the motor 4 driving compressing mechanism 3 in the drawings.In FIG, being the front of compressor 1 with right side in scheming, is the rear of compressor with left side in scheming.
Housing 2 has the transducer storage case parts 2c of the compressing mechanism storage case parts 2a of storage compressing mechanism 3, the motor storage case parts 2b of motor 4 of storage driving compressing mechanism 3 and the not shown convertor device of storage drive control motor 4, utilize locating stud 7 to position these housing parts, and utilize attachment bolt 8 to connect these housing parts vertically.
In the side opposed with compressing mechanism storage case parts 2a of motor storage case parts 2b, be provided with the partition wall 10 being formed with axle support 9a, in addition, in the side opposed with motor storage case parts 2b of transducer storage case parts 2c, also be provided with the partition wall 11 being formed with axle support 9b, live axle 12 is rotatably supported in axle support 9a, 9b of these partition walls 10,11 via bearing 13,14.Utilize the respective partition wall 10,11 be formed in this motor storage case parts 2b and transducer storage case parts 2c, make the inside of housing 2 from rear, be separated into the transducer container 15c of the compressing mechanism container 15a of storage compressing mechanism 3, the motor container 15b of storage motor 4 and storage convertor device.
In this embodiment, transducer container 15c is separated into by utilizing not shown bolt etc. to be fixed on transducer storage case parts 2c by lid 16.
Compressing mechanism 3 is the Scrawl compressor structures of rotary vortex rotary part 22 having fixed scroll member 21 and configure corresponding thereto, fixed scroll member 21 is allowed to move vertically relative to housing 2, and limited to the movement of radial direction by locating stud 28, be made up of discoideus end plate 21a, cylindric periphery wall 21b and Vorticose vortex wall 21c, periphery wall 21b arranges along the outer rim of this end plate 21a throughout complete cycle and erects setting toward the front, and vortex wall 21c is extended toward the front from described end plate 21a in the inner side of this periphery wall 21b.
In addition, rotary vortex rotary part 22 is made up of discoideus end plate 22a and the Vorticose vortex wall 22c that erects setting from this end plate 22a towards rear, erecting the shaft hub 22b being arranged at the end plate 22a back side, be supported with via lining 23 and radial bearing 24 rearward end being located at live axle 12 and the eccentric shaft 17 of axle center eccentric setting relative to live axle 12, be set as and can carry out revolution motion centered by the axle center of live axle 12.
Fixed scroll member 21 and rotary vortex rotary part 22 are engaged each other by respective vortex wall 21c, 22c, in the space surrounded by the end plate 21a of fixed scroll member 21 and the end plate 22a of vortex wall 21c and rotary vortex rotary part 22 and vortex wall 22c, be separated out pressing chamber 25.
In addition, between the periphery wall 21b and partition wall 10 of fixed scroll member 21, be clamped with the thrust race 26 of laminal ring-type, fixed scroll member 21 is docked via this thrust race 26 with partition wall 10.
Thrust race 26 is formed by the raw material of excellent in wear resistance, is formed with the central hole supplying the shaft hub 22b of rotary vortex rotary part 22 and European ring 27 described later to run through in central authorities.In addition, utilize and be formed at the locating stud 28 passed in the pin insertion hole of thrust race 26 and come the radial position of regulation scroll element 21, thrust race 26 and motor storage case parts 2b.
The axle support 9a be formed on the partition wall 10 of described motor storage case parts 2b has through hole in central authorities, the diameter of its internal surface towards thrust race 26 steps increase, from from thrust race 26 front side farthest, be formed with bearing container 31, counterweight container 33 and European container 34, bearing 13 is received in bearing container 31, counterweight 32 is received in counterweight container 33, this counterweight 32 is formed on described lining 23 or can not be integrated with lining 23 one-tenth relative to being embedded in lining outside the mode rotated, thus rotate (in this embodiment along with the rotation of live axle 12, counterweight 32 formed with lining 23 split and to be embedded in lining 23 outside the mode that can not relatively rotate), European container 34 is formed continuously with this counterweight container 33, the European ring 27 preventing this rotary vortex rotary part 22 rotation is accommodated with between itself and rotary vortex rotary part 22.
Therefore, although rotary vortex rotary part 22 produces rotation power because of the rotation of live axle 12, its rotation is limited by European ring 27, so carry out revolution motion relative to the axle center of live axle 12.
Suction chamber 35 is formed between the periphery wall 21b of aforesaid fixed scroll member 21 and the outermost perimembranous of the vortex wall 22c of rotary vortex rotary part 22, this suction chamber 35 sucks via sucking path 45 refrigeration agent imported from suction port 40 described later, in addition, the behind of the fixed scroll member 21 in housing, between itself and the aft bulkhead of compressing mechanism storage case parts 2a, be separated out discharge chamber 37, the tap hole 36 that refrigerant gas compressed in pressing chamber 25 is formed via the substantial middle in fixed scroll member 21 is discharged to this discharge chamber 37.The refrigerant gas being discharged to this discharge chamber 37 via exhaust port 38 by externally refrigerant circuit force feed.
On the other hand, in the motor container 15b of the part formation that the ratio partition wall 10 in housing 2 is closer to the front, the stator 41 and rotor 42 that form motor 4 is provided with.Stator 41 is made up of iron core 43 cylindrically and the coil 44 that is wound in this iron core 43, is fixed on housing 2(motor storage case parts 2b) internal surface on.In addition, on live axle 12, be installed with the rotor 42 be made up of the magnet be rotatably accommodated in inside stator 41, this rotor 42 utilizes the rotation magnetic force that formed by stator 41 and rotates, and live axle 12 is rotated.Utilize these stators 41 and rotor 42, constitute the motor 4 be made up of brushless DC motor.
And, at housing 2(motor storage case parts 2b) side, be formed with the suction port 40 refrigerant gas being drawn into motor container 15b, by stator 41 and housing 2(motor storage case parts 2b) between gap, the gap that is formed in the hole on partition wall 10 and is formed between fixed scroll member 21 and housing 2, constitute the suction path 45 refrigeration agent flowing into motor container 15b from suction port 40 being directed to described suction chamber 35.
In addition, the convertor device being accommodated in transducer storage case parts 2c is electrically connected with stator 41 via terminal (airtight terminal) 60, powers from convertor device to motor 4, and terminal (airtight terminal) 60 is installed on the through hole 61 formed on partition wall 11.
Therefore, when making live axle 12 rotate by making rotor 42 rotate to motor 4 power supply, in compressing mechanism 3, rotary vortex rotary part 22 rotates centered by eccentric shaft 17, and therefore, rotary vortex rotary part 22 revolves round the sun around the axle center of fixed scroll member 21.Now, the rotation of rotary vortex rotary part 22 is stoped mechanism to stop by the rotation be made up of European ring 27, is therefore only allowed revolution motion.
By the revolution motion of this rotary vortex rotary part 22, pressing chamber 25 moves to central side from the outer circumferential side of vortex wall 21c, 22c of two scroll elements and reduces volume gradually, therefore, the refrigerant gas being drawn into pressing chamber 25 from suction chamber 35 is compressed, and this is discharged to discharge chamber 37 via the tap hole 36 be formed on the end plate 21a of fixed scroll member 21 by the refrigerant gas compressed.Then, this by the refrigerant gas that compresses via exhaust port 38 externally refrigerant circuit send.
In above structure, also as shown in Figures 2 and 3, aforesaid lining 23 is columnar shape, in the position from axle center to radial deflection, be formed with eccentric opening 23a that is extended vertically and that described eccentric shaft 17 can be inserted, in the end of rotary vortex rotary part side, be formed with the concavity portion 23b comparing eccentric opening 23a diameter and expand to some extent, in addition, on the end portions of motor side, be formed and reduce its external diameter and the counterweight embedding part 23c of outer counterweight 32.
Also as shown in Figure 4, counterweight 32 by be formed as ring-type embedding part 32a and throughout predetermined angular scope the counterweight main body 32b of fan-shaped that is integrally formed on the periphery of this embedding part 32a form, in the mode be such as pressed into by being embedded in the periphery of the counterweight embedding part 23c of described lining 23 outside embedding part 32a, it is made to rotate together with lining 23.
This counterweight is stretched out in the mode close to rotary vortex rotary part, and is formed as stretching out to the direction away from rotary vortex rotary part, shortens radial dimension thus, avoids interfering with European ring 27 and guaranteeing required quality.
Described eccentric shaft 17 is formed with the columned axle of annular slot 17a for adjacent one end, embedding hole 12a is fixed to by the end press-in of the opposite side by being formed with annular slot 17a side, make the end of annular slot side outstanding to concavity portion 23b through the eccentric opening 23a of described lining 23 in the mode that can relatively rotate, and the part being projected into this concavity portion 23b by chimeric with annular slot 17a for snap ring 29 come mounting bush 23, above-mentioned embedding hole 12a is formed in the end face opposed with rotary vortex rotary part 22 of live axle 12.Therefore, lining 23 is limited along the movement of eccentric shaft 17 axis, and is installed to be and relatively can rotates relative to eccentric shaft 17.
The radial bearing 24 be embedded in the shaft hub 22b of rotary vortex rotary part 22 is formed by being circumferentially equally spaced configured with multiple needle bearing rolling needle rollers 24a, is embedded by this lining 23 when can have specified gap between itself and the outer circumferential face of lining 23 in the mode that can relatively rotate.
In this embodiment, the roller number of radial bearing 24 is set to 14, and the length (length chimeric with the axis of the outer circumferential face of lining 23) of roller part is set to 10mm, and roller diameter is set to 2.5mm.In addition, lining length chimeric with the axis of eccentric shaft is set to 15mm, and the diameter of eccentric shaft is set to 6mm.
In addition, according to general design techniques in the past, normally the tolerance of estimation components also sets gap as small as possible, abuts with the parts (in the present embodiment for lining) being supported on this radial bearing to make radial bearing under state parallel as far as possible.Namely, in the radial bearing 24 using needle bearing, lightweight and compact, but then, being not suitable for the inclination of supporting thrust load and axle, therefore, the gap between radial bearing 24 and the parts inserting inner side being managed as less gap by utilizing match machined, suppress the inclination of lining and the partial load that alleviates between itself and needle roller, this is design general knowledge.
But in an end of lining 23, be provided with counterweight 32 in the part of giving prominence to vertically from radial bearing 24, therefore, by the centrifugal force of counterweight 32, the axle center of lining 23 will relative to eccentric shaft 17(live axle 12) axle center run-off the straight.Therefore, the inclination of this lining 23 is compensated to the gap reduced between the outer circumferential face of lining 23 and radial bearing 24, then as previously mentioned, there is following rough sledding, namely, lining 23 two different positions in the axial direction and radial bearing 24 localized contact, in the abutment portion being provided with the side, end of counterweight 32 of lining 23, partial load enlarges markedly and peels off.
Therefore, in the present invention, in order to reduce the local load's (partial load) being provided with the side, end of counterweight of lining, as shown in Fig. 5 (a), the gap A be inserted between the outer circumferential face of the eccentric shaft 17 of eccentric opening 23a and the inner peripheral surface of eccentric opening 23a is set smaller than the clearance C between the outer circumferential face of lining 23 and the inner peripheral surface of radial bearing 24.
More particularly, if the gap between the outer circumferential face of eccentric shaft 17 and the inner peripheral surface being located at the eccentric opening 23a on lining 23 is set to A, the outer circumferential face of eccentric shaft 17 and the chimeric length of the inner peripheral surface of eccentric opening 23a are set to B, gap between the outer circumferential face of lining 23 and the inner peripheral surface of radial bearing 24 is set to C, the outer circumferential face of lining 23 and the chimeric length of the inner peripheral surface of radial bearing 24 are set to D, then be set as A=6 ~ 22 μm, C=24 ~ 48 μm, A/B<C/D.
Therefore, in such a configuration, due to the deviation of gravity center of counterweight 32 that arranges in the end outstanding from radial bearing 24 of lining 23 center of eccentric shaft 17 (point due to the centrifugal action of counterweight acts on from outstanding lining 23 end of radial bearing 24), therefore as shown in Fig. 5 (b), the axle center of lining 23 tilts relative to the axle center of eccentric shaft 17, in this condition, the outer circumferential face of lining 23 and radial bearing 24 localized contact, the centrifugal force of counterweight 32 acts on rotary vortex rotary part 22 via lining 23 and radial bearing 24, counteract the centrifugal force of rotary vortex rotary part 22.Now, because the gap A inserted between the outer circumferential face of the eccentric shaft 17 in eccentric opening 23a and the inner peripheral surface of eccentric opening 23a is set smaller than the clearance C between the outer circumferential face of lining 23 and the inner peripheral surface of radial bearing 24, therefore the inclination of lining 23 is limited (mainly being supported by eccentric shaft 17) by eccentric shaft 17, the outer circumferential face being only connected to radial bearing 24(lining 23 at a position only abuts in the side, end being provided with counterweight 32, does not abut in the side, end of far from equilibrium counterweight 32 with radial bearing).Therefore, do not produce described F3(as shown in Figure 9), therefore, in the side, end being provided with counterweight 32, the load F2 acted on the position abutted against with radial bearing 24 does not enlarge markedly, but becomes roughly the same with F1.
Certainly, in real-world operation, the compression counter-force that can produce due to the compression in the pressing chamber 25 between accompanying rotation scroll element 22 and fixed scroll member 21, apply relative to paper the power of the composition being nearby side-distally, therefore, at their acted on point of making a concerted effort, lining 23 contacts with radial bearing 24.Therefore, in form in the past, the such rightabout masterpiece of F3 and F2 is used in front side and these two positions of rear side of lining 23, therefore contacting part can the distortion of three-dimensionality ground, but in the present invention, the load of F3 does not act on, therefore, it is possible to suppress such distortion contact.
In addition, in said structure, the inclination of lining 23 is supported by the embedding part of the outer circumferential face of eccentric shaft 17 with the eccentric opening 23a be located on lining 23, so the abutment portion on eccentric shaft 17 and eccentric opening 23a will produce local load (α 1, α 2), but because lining 23 does not rotate relatively relative to eccentric shaft 17, therefore do not produce slippage and rotation in this abutment portion, peel off without the need to worrying and wear and tear.
In addition, as previously mentioned, in general design techniques, C is managed by the outer circumferential face (so-called match machined) of the inner peripheral surface dimensioned lining 23 according to radial bearing 24, but in said structure, do not need the management that C is diminished, so eliminate match machined.At this, match machined can also be used for gap management (outer circumferential face according to the inner peripheral surface dimensioned eccentric shaft 17 of eccentric opening 23a) of A, make A=6 ~ 12 μm.Like this, when not increasing machining period than ever mutually, the inclination of the lining supported by A can be reduced further.
Therefore, can alleviate and act on radial bearing 24(roller 24a) on partial load, even if there is one-side contact with the roller 24a of radial bearing 24 and abut partly in lining 23, also can suppress the generation of peeling off, relatively can improve the bearing capacity (not needing to seek in order to ensure the bearing capacity of radial bearing 24 maximization of radial bearing 24) of radial bearing 24.
In addition, in said structure, because counterweight 32 also stretches out formation to the direction away from rotary vortex rotary part 22, therefore, the radial length of counterweight can be suppressed, in addition, counterweight 32 can not be set interferingly with the anti-locking mechanism of rotation (European ring 27).Therefore, it is possible to avoid the diameter of European ring 27 to increase, the external diameter of rotary vortex rotary part can also be reduced.
And, in said structure, owing to using needle bearing as radial bearing 24, therefore, it is possible to alleviate the weight of bearing self, in addition, radial dimension can also be made compact, and then the lightweight of counterweight can be realized.
Description of reference numerals
1 Scrawl compressor
2 housings
21 fixed scroll member
21a end plate
21c vortex wall
22 rotary vortex rotary parts
22a end plate
22b shaft hub
22c vortex wall
23 linings
23a eccentric opening
24 radial bearings
32 counterweights
Claims (4)
1. a Scrawl compressor, possesses:
Fixed scroll member, it is limited relative at least moving radially of housing, has end plate and erects the vortex wall of setting from this end plate;
Rotary vortex rotary part, itself and this fixed scroll member relative configuration, has end plate and erects the vortex wall of setting from this end plate;
Live axle, its transmitting rotary power;
Eccentric shaft, it is located at the end of described live axle, and is located at the position offset relative to the axle center of this live axle;
Radial bearing, it is embedded in the shaft hub formed at the back side of described rotary vortex rotary part;
Lining, it possesses the eccentric opening inserted for described eccentric shaft, is embedded in described eccentric shaft, and is supported on described radial bearing in the mode that can relatively rotate via outside this eccentric opening;
Counterweight, it is located at an end of described lining and becomes to be integrated with this lining;
The feature of described Scrawl compressor is,
When described lining tilts, the outer circumferential face of this lining is only abutted with described radial bearing in the side, end being provided with described counterweight.
2. Scrawl compressor according to claim 1, is characterized in that,
If described eccentric shaft and the gap of the inner peripheral surface being located at the described eccentric opening on described lining are set to A, described eccentric shaft and the chimeric length of the inner peripheral surface being located at the described eccentric opening on described lining are set to B, the gap of the outer circumferential face of described radial bearing and described lining is set to C, described radial bearing and the chimeric length of the outer circumferential face of described lining are set to D, then A/B < C/D.
3. Scrawl compressor according to claim 1 and 2, is characterized in that,
Be provided with the anti-locking mechanism of rotation at the radial outside of the described shaft hub of described rotary vortex rotary part, described counterweight, by stretching out to the direction away from described rotary vortex rotary part, avoids the interference with the anti-locking mechanism of described rotation.
4. Scrawl compressor according to claim 1 and 2, is characterized in that, described radial bearing is needle bearing.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-096236 | 2011-04-22 | ||
| JP2011096236A JP5594846B2 (en) | 2011-04-22 | 2011-04-22 | Scroll compressor |
| PCT/JP2012/002731 WO2012144224A1 (en) | 2011-04-22 | 2012-04-20 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103477079A CN103477079A (en) | 2013-12-25 |
| CN103477079B true CN103477079B (en) | 2016-01-20 |
Family
ID=47041354
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280018752.XA Expired - Fee Related CN103477079B (en) | 2011-04-22 | 2012-04-20 | Scrawl compressor |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2713053B1 (en) |
| JP (1) | JP5594846B2 (en) |
| CN (1) | CN103477079B (en) |
| WO (1) | WO2012144224A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6149429B2 (en) * | 2013-03-06 | 2017-06-21 | 株式会社豊田自動織機 | Scroll compressor |
| JP6208534B2 (en) * | 2013-10-25 | 2017-10-04 | 株式会社ヴァレオジャパン | Electric scroll compressor |
| JP6628957B2 (en) * | 2014-02-28 | 2020-01-15 | 三菱重工業株式会社 | Scroll compressor |
| CN104047851A (en) * | 2014-07-11 | 2014-09-17 | 湖南联力精密机械有限公司 | Vortex air compressor with radially sealable movable and static discs |
| WO2016038694A1 (en) * | 2014-09-10 | 2016-03-17 | 株式会社日立産機システム | Scroll fluid machine |
| KR102291952B1 (en) * | 2015-03-04 | 2021-08-23 | 한온시스템 주식회사 | A eccentric bush assembling structure of a scroll compressor |
| JP2019100246A (en) * | 2017-11-30 | 2019-06-24 | サンデン・オートモーティブコンポーネント株式会社 | Scroll type fluid machine |
| JP7017485B2 (en) * | 2018-08-13 | 2022-02-08 | 三菱重工サーマルシステムズ株式会社 | Scroll compressor |
| JP7056821B2 (en) * | 2018-08-31 | 2022-04-19 | サンデン・オートモーティブコンポーネント株式会社 | Scroll compressor |
| KR102097499B1 (en) * | 2018-09-17 | 2020-04-06 | 엘지전자 주식회사 | Scroll compressor |
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| KR102503234B1 (en) * | 2018-11-30 | 2023-02-24 | 한온시스템 주식회사 | Scroll compressor |
| GB2583373A (en) * | 2019-04-26 | 2020-10-28 | Edwards Ltd | Scroll pump crank sleeve |
| CN211598997U (en) * | 2020-01-21 | 2020-09-29 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| DE102020211559A1 (en) | 2020-09-15 | 2022-03-17 | Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg | scroll compressor |
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| JP3214417B2 (en) * | 1997-11-11 | 2001-10-02 | ダイキン工業株式会社 | Scroll type fluid machine |
| AU9519298A (en) * | 1997-12-03 | 1999-06-24 | Sanden Corporation | Scroll compressor in which an eccentric bush is radially movable with being guide by a guide pin |
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| JP2010196630A (en) | 2009-02-26 | 2010-09-09 | Denso Corp | Compressor |
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- 2011-04-22 JP JP2011096236A patent/JP5594846B2/en not_active Expired - Fee Related
-
2012
- 2012-04-20 EP EP12773817.7A patent/EP2713053B1/en not_active Not-in-force
- 2012-04-20 WO PCT/JP2012/002731 patent/WO2012144224A1/en active Application Filing
- 2012-04-20 CN CN201280018752.XA patent/CN103477079B/en not_active Expired - Fee Related
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|---|---|---|---|---|
| US6015277A (en) * | 1997-11-13 | 2000-01-18 | Tecumseh Products Company | Fabrication method for semiconductor substrate |
| US6425746B1 (en) * | 1999-09-28 | 2002-07-30 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Compressor and regenerator for fuel cell |
| CN1360152A (en) * | 2000-12-22 | 2002-07-24 | 株式会社电装 | Vortex compressor |
| CN101072949A (en) * | 2004-12-08 | 2007-11-14 | 英国氧气集团有限公司 | Scroll-type apparatus |
| CN2821227Y (en) * | 2005-07-14 | 2006-09-27 | 乐金电子(天津)电器有限公司 | Vortex compressor with movable balance hammer |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2713053B1 (en) | 2016-04-13 |
| EP2713053A4 (en) | 2014-11-26 |
| JP2012225328A (en) | 2012-11-15 |
| JP5594846B2 (en) | 2014-09-24 |
| CN103477079A (en) | 2013-12-25 |
| EP2713053A1 (en) | 2014-04-02 |
| WO2012144224A1 (en) | 2012-10-26 |
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