CN202001252U - Thrust spherical plain bearing assembly for compressor and compressor provided with same - Google Patents
Thrust spherical plain bearing assembly for compressor and compressor provided with same Download PDFInfo
- Publication number
- CN202001252U CN202001252U CN2011200156242U CN201120015624U CN202001252U CN 202001252 U CN202001252 U CN 202001252U CN 2011200156242 U CN2011200156242 U CN 2011200156242U CN 201120015624 U CN201120015624 U CN 201120015624U CN 202001252 U CN202001252 U CN 202001252U
- Authority
- CN
- China
- Prior art keywords
- compressor
- steel ball
- thrust
- retainer
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The utility model relates to a thrust spherical plain bearing assembly for a compressor and the compressor provided with the assembly, wherein the assembly is mounted between thrust surfaces of a crankshaft (4) and a shaft sleeve (1). The thrust spherical plain bearing assembly is characterized by consisting of an upper bearing strip (5), a bearing cage (7), a lower bearing strip (8), an upper cage (9) and a lower cage (11) which are sequentially and vertically overlapped, wherein the upper bearing strip (5) is positioned through a compressor crankshaft, and the bearing cage (7), the lower bearing strip (8), the upper cage (9) and the lower cage (11) are positioned through bulges (1f) of the compressor crankshaft. The structure eliminates the phenomenon of stress-concentrated single edge friction or the phenomenon that only individual balls of the whole ball bearing are under stress due to the fact that the crankshaft thrust surface of the thrust bearing and the thrust surface of the crankcase of the compressor are not parallel, as a result, not only the compressor efficiency is improved, but also the compressor operation is ensured to be stable.
Description
Technical field
The utility model relates to a kind of compressor product that is used for the thrust joint shaft bearing assembly of compressor and comprises described assembly formation.
Background technique
The friction of compressor mechanical friction pair has significant effects to the efficient of compressor.Compressor design all promotes efficient reducing friction as much as possible, and at present the bent axle thrust face of compressor thrust bearing and crankcase thrust surface exist monolateral stressed and to form monolateral friction phenomenon be that plane that two of thrust bearing should be parallel is in fact not parallel (is with ball, because in fact, two faces of lower support sheet are not parallel, make whole ball bearing have only indivedual balls rolling), lose the integrity of bearing, make friction and vibration aggravate, mechanical efficiency reduces.Two uneven reasons of working plane of thrust bearing are from many-side:
The influence of bent axle: as shown in Figures 1 and 2.Fig. 1 is the bent axle desired shapes.There is error in Fig. 2 for the actual processing of bent axle, makes actual crank thrust face 4a and desirable bent axle thrust face 4b have angle C °.
The influence of crankcase: as shown in Figures 3 and 4.Fig. 3 is the crankcase desired shapes.There is error in Fig. 4 for the actual processing of crankcase, makes actual thrust surface 1a and desirable thrust surface 1b exist to depart from and has angle b °.Cylinder axially bored line 1d and axis hole axis 1e out of plumb have angle a ° (a ° ≠ 90 °).
Matching gap and stressed influence: as Fig. 5 and shown in Figure 6, because crankshaft hole D6 and bent axle major axis d5 are gapped, and being subjected to the effect of connecting rod F1 in compressor operating, making the bent axle run-off the straight, is fulcrum with F3, F3=F1+F2.Can not fit fully owing to tilt to make desirable thrust surface 1b and actual thrust face 4a to form d ° of angle, temperature is higher during owing to the compressor real work, can the production thermal distortion can increase the weight of distortion simultaneously under the effect of F1, further adds mitre d ° influence.
Combined influence: (be one of situation of resultant error, adopt this kind situation to describe) as shown in Figure 7 for ease of expressing.The d ° of stack of the angle C of Fig. 2 °, b ° of Fig. 4 angle and Fig. 6, make that actual thrust surface 1a and actual thrust face 4a form e ° of resultant error angle among Fig. 7, two working planes (actual thrust surface 1a and actual thrust face 4a) that are thrust bearing are not parallel, lose the integrity of bearing, make mechanical efficiency descend.F ° of the resultant error angle of angle d ° (crankshaft center line inclination) formation Fig. 7 of the angle a ° error of Fig. 4 and Fig. 6.Angle f ° of (error of parallelism also can influence, and is still not shown) error makes connecting rod power F1 resolve into F4 and F5, and component F5 has strengthened load between actual thrust surface and 1a and the actual thrust face 4a, strengthens friction.
Stressed problem: load between actual thrust surface 1a and the actual thrust face 4a among Fig. 7, come from magnetic pull downward between gravity, rotor and the stator of gravity, fuel sucking pipe of rotor gravity, bent axle, component F5 that machining error causes, part when work thermal distortion and bent axle at the additional load of stressed back distortion.Be subjected to angle e ° influence to make the actual thrust surface 1a of thrust bearing and actual thrust face 4a point of intersection g produce monolateral friction among Fig. 7, just the part area is stressed in 1a and 4a, remaining part might not have stressed, make the friction aggravation also strengthen vibration simultaneously, thereby make the decrease in efficiency of compressor, the ultra high efficiency compressor is because folded thick higher its gravity that makes of rotor strengthens at present, and this influence shows more obvious.The structural type of Fig. 7 also has a shortcoming owing to do not keep the plane thrust ball bearing structure, makes bearing 1 can not design very longly, and the operation stability of compressor is relatively poor, and advantage is to save cost.Fig. 8 promptly is with plane thrust ball bearing for the another kind of structural type of existing compressor, advantage is and can raises the efficiency, simultaneously owing to be with protruding 1f, make that whole bearing 1 is longer, the stability of compressor better, but the same resultant error angle that exists equally with Fig. 7 structure of this structure produces the monolateral friction that stress is concentrated for e °, make that the upper support sheet lower surface 5b and the lower support sheet upper surface 8a of whole ball bearing are not parallel, has only the stressed rolling of indivedual balls, make that the integrity of ball bearing is ineffective, make mechanical efficiency descend.
Summary of the invention
It is not parallel when technical problem to be solved in the utility model is to eliminate bent axle thrust face on the compressor thrust bearing and the work of crankcase thrust surface, the monolateral friction phenomenon or the whole ball bearing that exist stress to concentrate have only indivedual balls to be subjected to force phenomenon, propose a kind ofly can further improve compressor efficiency, guarantee the stability of compressor operating, can suitably reduce the thrust joint shaft bearing assembly of vibration of compressor again, and then the compressor with described thrust joint shaft bearing modular construction is provided.
For solving the problems of the technologies described above, the solution that the utility model adopted is: a kind of thrust joint shaft bearing assembly, be installed between the thrust surface of the thrust face of bent axle 4 and axle sleeve 1, it is characterized in that: described thrust joint shaft bearing assembly from top to bottom successively by upper support sheet, the retainer that contains steel ball, lower support sheet, contain steel ball holder, contain that the following retainer of steel ball is stacked to be constituted.Steel ball in the retainer all is covered with, and the steel ball in holder and the following retainer is that a steel ball is arranged in steel ball hole, every interval, and promptly the quantity of steel ball is half of steel ball hole.Exposed portions serve below the holder steel ball drops on down in the retainer steel ball hole, and the exposed portions serve above the following retainer steel ball matches with holder steel ball hole, and the holder lower surface is fitted with following retainer upper surface.Described upper support sheet is located with compressor crank shaft, and described retainer, lower support sheet, holder, following retainer are located with the projection of compressor axle sleeve.
Holder and following retainer are selected nonmetallic material (having better elastic) for use as shown in Figure 9, angle e ° of causing of same resultant error, at (F6 can change be carried on the different steel balls) under the effect of monolateral power F6 with the crankshaft rotating angle, make steel ball 10(or the steel ball in the retainer down in the holder, relevant with the crankshaft rotating angle), move down into dotted line position (as shown in figure 10 by original solid line position, monolateral power F6 acts on the steel ball 10, contiguous two steel balls 12 are interim fulcrum, make on the one hand steel ball move down (on, following retainer steel ball hole resiliently deformable makes steel ball that displacement in a small amount be arranged) to dotted line position, on the other hand between two contiguous steel balls 12 of steel ball 10, following retainer generation resiliently deformable, move down into dotted line position, when crankshaft rotating makes that F6 leaves steel ball 10, original resiliently deformable restores to the original state, steel ball 10 resets, and crankshaft rotating makes F6 move on to next steel ball 12 or same above-mentioned resiliently deformable takes place steel ball 10, and the like, bent axle thrust face 4a, upper support sheet 5, lower support sheet 8, retainer 7 rotates thereupon, the lower surface 5b of upper support sheet 5 can remain parallel with the upper surface 8a of lower support sheet 8, (indivedual steel balls 6 are stressed in the retainer 7) eliminated in the friction that monolateral stress is concentrated, become even stressed friction (all steel ball 6 is evenly stressed in the retainer 7), thereby realize keeping the thrust bearing functional integrity, make the mechanical efficiency of compressor promote more than 2%.
The utility model is owing to adopted technique scheme, and it utilizes a kind of change aperture elastic deformation structure's mode, makes the compressor of using this plane thrust joint shaft bearing assembly produce following remarkable result:
1, the efficient of compressor improves more than 2.0%; 2, adopt the protruding structure of axle sleeve, because the joint shaft bearing thickness size exists, make sleeve length long (if band plane thrust ball bearing makes up then sleeve length is programmable longer) simultaneously, the stability when guaranteeing compressor operating; 3, can suitably reduce the vibration of bent axle thrust face and crankcase thrust surface.
Description of drawings
Fig. 1 is desirable bent axle shape schematic representation;
Fig. 2 is one of the bent axle situation of an actual processing schematic representation;
Fig. 3 is the shape schematic representation of desirable crankcase;
Fig. 4 is one of the situation of an actual processing Rear Crank Case schematic representation;
Fig. 5 is the view that desirable bent axle and desirable crankcase do not stress;
Fig. 6 is one of desirable bent axle and the stress situation of desirable crankcase when a work schematic representation;
Fig. 7 is the 1st kind of structure stress schematic representation of one of existing actual processing back bent axle and actual processing back actual crank case operative scenario;
Fig. 8 is the 2nd kind of structure enlarged diagram of one of existing actual processing back bent axle and actual processing back actual crank case operative scenario;
Fig. 9 is the stressed working principle schematic representation of the utility model thrust joint shaft bearing assembly;
Stress deformation when Figure 10 is the work of the utility model thrust joint shaft bearing assembly, enlarged diagram;
Figure 11 is the mode of execution of the utility model thrust joint shaft bearing;
Figure 12 is the plan view of the utility model thrust joint shaft bearing assembly scheme upper support sheet;
Figure 13 is the plan view of the utility model thrust joint shaft bearing assembly scheme retainer;
Figure 14 is the plan view of the utility model thrust joint shaft bearing assembly scheme holder.
Embodiment
The mode of execution of the utility model thrust joint shaft bearing assembly scheme as shown in figure 11, thrust joint shaft bearing assembly comprises upper support sheet 5, lower support sheet 8, retainer 7, steel ball 6, holder 9, holder steel ball 10, following retainer 11, following retainer steel ball 12.Described upper support sheet 5 is located with compressor crank shaft, described lower support sheet 8, retainer 7, steel ball 6, holder 9, holder steel ball 10, following retainer 11, following retainer steel ball 12 are located with the protruding 1f of compressor axle sleeve, steel ball in the retainer 7 all is covered with, steel ball in holder 9 and the following retainer 11 is that a steel ball is arranged in steel ball hole, every interval, and promptly the quantity of steel ball is half of steel ball hole.Exposed portions serve below the holder steel ball 10 drops on down in the retainer 11 steel ball holes, and the exposed portions serve above the following retainer steel ball 12 matches with holder 11 steel ball holes, and the holder lower surface is fitted with following retainer upper surface.Holder 9 and following retainer 11 are for having better elastic nonmetallic material (present place company just using be DUPONT ZYETL 103HS1-L), under the effect of F6, on the steel ball hole of holder 9 and following retainer 11 reaches, the resiliently deformable of following retainer part (at present place company is just using be DUPONT ZYETL 103HS1-L), make holder steel ball 10 and following retainer steel ball 12 that displacement in a small amount be arranged, the rotation of bent axle makes the displacement of F6 change, the position of resiliently deformable changes thereupon, the position of former resiliently deformable restores to the original state, and steel ball 10 resets thereupon.Above-mentioned process takes place in position, place that F6 changes behind the position once more.Make the lower surface 5b of upper support sheet 5 can remain parallel with the surperficial 8a of lower support sheet 8, (indivedual steel balls 6 are stressed in the retainer 7 to make the concentrated friction elimination of monolateral stress, make that the thrust bearing function is imperfect), become even stressed friction (all steel ball 6 is evenly stressed in the retainer 7), thereby realize keeping the thrust bearing functional integrity.Make mechanical efficiency promote more than 2%.In order to prevent that holder steel ball 10 from falling into down in the retainer 11 steel ball holes, or retainer steel ball 12 enters in the holder 9 steel ball holes down, has good reliability, it is A=ξ X (B/2) that size A and S φ B close, ξ is a safety factor, and concrete parameter value can be determined according to the load and the operating mode of compressor, considers the manufacturability of implementing, holder 9 equates to be A with the thickness of following retainer 11, holder steel ball hole equates to be B with following retainer steel ball bore dia.
Claims (2)
1. thrust joint shaft bearing assembly that is used for compressor, be installed between the thrust surface of the thrust face of bent axle (4) and axle sleeve (1), it is characterized in that: described thrust joint shaft bearing assembly is from top to bottom successively by upper support sheet (5), the retainer (7) that contains steel ball (6), lower support sheet (8), the holder (9) that contains steel ball (10), the stacked formation of following retainer (11) that contains steel ball (12), steel ball (6) in the retainer (7) all is covered with, steel ball in holder (9) and the following retainer (11) is that a steel ball is arranged in steel ball hole, every interval, exposed portions serve below the steel ball in the holder (10), drop on down in retainer (11) the steel ball hole, exposed portions serve above the steel ball (12) in the following retainer matches with holder (11) steel ball hole, a projection (1f) is arranged on the axle sleeve (1), described upper support sheet (5) is located with compressor crank shaft, described retainer (7), lower support sheet (8), holder (9), following retainer (11) is located with the projection (1f) of compressor axle sleeve.
2. one kind has and comprises the compressor of thrust joint shaft bearing assembly according to claim 1, it is characterized in that: described assembly is installed between the thrust surface of the thrust face of bent axle (4) and axle sleeve (1), described upper support sheet (5) is located with compressor crank shaft, and described retainer (7), lower support sheet (8), holder (9), following retainer (11) are located with the projection (1f) of compressor axle sleeve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200156242U CN202001252U (en) | 2011-01-19 | 2011-01-19 | Thrust spherical plain bearing assembly for compressor and compressor provided with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200156242U CN202001252U (en) | 2011-01-19 | 2011-01-19 | Thrust spherical plain bearing assembly for compressor and compressor provided with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202001252U true CN202001252U (en) | 2011-10-05 |
Family
ID=44703995
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200156242U Expired - Fee Related CN202001252U (en) | 2011-01-19 | 2011-01-19 | Thrust spherical plain bearing assembly for compressor and compressor provided with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202001252U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102032148A (en) * | 2011-01-19 | 2011-04-27 | 华意压缩机股份有限公司 | Thrust oscillating bearing assembly for compressor |
| CN106255827A (en) * | 2014-04-01 | 2016-12-21 | 惠而浦股份有限公司 | Radial bearing device in refrigeration compressor |
-
2011
- 2011-01-19 CN CN2011200156242U patent/CN202001252U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102032148A (en) * | 2011-01-19 | 2011-04-27 | 华意压缩机股份有限公司 | Thrust oscillating bearing assembly for compressor |
| CN102032148B (en) * | 2011-01-19 | 2012-08-15 | 华意压缩机股份有限公司 | Thrust oscillating bearing assembly for compressor |
| CN106255827A (en) * | 2014-04-01 | 2016-12-21 | 惠而浦股份有限公司 | Radial bearing device in refrigeration compressor |
| CN106255827B (en) * | 2014-04-01 | 2019-04-16 | 恩布拉科压缩机工业和制冷解决方案有限公司 | Radial bearing device in refrigeration compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102416506B (en) | Cutting tool | |
| CN202001252U (en) | Thrust spherical plain bearing assembly for compressor and compressor provided with same | |
| KR101396889B1 (en) | Foil thrust bearing having bump being in the shape of a plate | |
| CN102032148B (en) | Thrust oscillating bearing assembly for compressor | |
| CN202187919U (en) | Rotary type compressor | |
| CN102062044A (en) | Wind machine blade airfoil family | |
| CN204511809U (en) | A kind of linear compressor linear arm leaf spring | |
| CN103047281B (en) | There is the Foil gas bearing of viscoelastic structure | |
| CN204140599U (en) | Split shaft block ring | |
| CN202790097U (en) | Self-aligning bearing | |
| CN102287448A (en) | Bearing cage | |
| CN102011724B (en) | Full enclosed reciprocating type piston refrigeration compressor | |
| CN203476548U (en) | Hollow and adjustable blade structure of engine | |
| CN103608135A (en) | Insertion frame structure and housing using same | |
| CN104895907A (en) | Crankshaft and compressor | |
| CN202867668U (en) | Prepressing spring leaf, combined structure thereof and fan | |
| CN209041315U (en) | A kind of more stroke high intensity crankshafts | |
| CN104533752A (en) | Rectilinear arm plate spring for linear compressor and design and manufacturing method for rectilinear arm plate spring | |
| CN209088655U (en) | A kind of rotor disk, rotor assembly and motor in axial magnetic field | |
| CN202073747U (en) | Compressor with plane thrust ball bearing | |
| CN202274014U (en) | Rolling pin slope type uni-directional bearing with folding edge structure plate spring | |
| CN103542027B (en) | Pre-press leaf spring and composite structure thereof and fan | |
| CN102312941A (en) | Quill roller slope type one-way pillar bearing provided with floding structural slab spring | |
| CN201599310U (en) | Double row angular contact ball bearing with punched helical cage, and inner ring and outer ring integrally inseparable | |
| CN202402286U (en) | Master vane of master and auxiliary vane pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111005 Termination date: 20120119 |