CN103410732B - Rotary-type translation piston compressor - Google Patents
Rotary-type translation piston compressor Download PDFInfo
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- CN103410732B CN103410732B CN201310370147.5A CN201310370147A CN103410732B CN 103410732 B CN103410732 B CN 103410732B CN 201310370147 A CN201310370147 A CN 201310370147A CN 103410732 B CN103410732 B CN 103410732B
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Abstract
The invention provides a kind of Rotary-type translation piston compressor, belong to mechanical engineering technical field.It solve existing rotary compressor and there is the high problem of the elastic force rigidity of spring.This Rotary-type translation piston compressor, comprise the cylinder with piston cavity and the bent axle with eccentric part, eccentric part is positioned at piston cavity; Described cylinder blade groove has blade; On eccentric part, cover has piston, is connected between eccentric part outer side surface with piston inner side surface by rolling bearing assembly; Described outside piston side face has the concave circular arc groove in strip parallel with piston bus; Described blade end face is convex arch curved surface; Described blade arc top embeds in the concave circular arc groove of piston, and blade end face and concave circular arc groove groove face lean under spring force.This Rotary-type translation piston compressor is applied in 1 ~ 1.5HP air-conditioning, and the elastic force rigidity of spring only needs to control at 2 ~ 4Kg/ ㎜, even less.
Description
Technical field
The invention belongs to mechanical engineering technical field, relate to a kind of fluid varactor machine of rotary-piston, particularly a kind of Rotary-type translation piston compressor.
Background technique
Compressor is a kind of driven fluid machinery low-pressure gas being promoted to high pressure.Air condition compressor is the heart of refrigeration system.Rotary-piston type air condition compressor is widely used in domestic air conditioning.
Pertinent literature about rolling piston compressor is more, as the rolling piston compressor [application number: 97114554.7 that Chinese patent literature is recorded; Publication number: CN1174297A].Traditional rolling piston compressor is described in the background technique of the document, as shown in Figure 7 and Figure 8, there is the bent axle 101 of eccentric part 102, motor 103, cylinder 104, blade 105 and the piston 106 of eccentric rotary in cylinder 104 that driving crank 101 rotates.Blade 105 leans with piston 106 at the effect lower blade 105 of spring 111, and the end face that blade 105 and piston 106 lean is circular arc.Blade 105 moves back and forth in the blade groove of cylinder 104, the external peripheral surface sliding contact of blade 105 and piston 106.Thus blade 105 is divided into suction chamber 107 and discharge side 108 the inside of cylinder 104.Because motor band dynamic crankshaft 101 rotates, piston 106 rotates in cylinder 104, and refrigerant gas enters from suction port 109, is then sent to exhaust port 110, is compressed simultaneously.Usual rotary-piston type air condition compressor is applied in 1 ~ 3HP air-conditioning, and also start application at the air-conditioning of 5HP at present, the elastic force rigidity general control of its spring 111 is at 2 ~ 8Kg/ about ㎜.
According to above-mentioned conventional construction, because the top of blade 105 has cylindrical surface, the external peripheral surface of piston 106 is also columniform, and the contact condition between blade 105 and piston 106 is equivalent to the contact between small column and big column.Therefore, contact condition is linear contact, and wherein area of contact is less, and the load on per unit area and contact stress are then comparatively large, make the sliding contact situation between blade 105 and piston 106 become very harsh.The rotary-piston type air condition compressor of conventional construction, the frictional resistance moment between piston 106 external peripheral surface and blade 105 top is greater than the frictional resistance moment between its inner circumferential surface and crankshaft eccentric portion 102, and piston 106 operationally can produce spin.The spin population of piston 106 depends on the ratio of its outside diameter and the diameter of bore of cylinder 104.
In above-mentioned conventional construction, the pumping effect that the lubrication of compressor operationally produces mainly through the screw piece being arranged on bent axle mesopore, delivers to refrigerator oil between each bearing, and flows into cylinder chamber and form oil film.
In order to solve the problem, someone proposes technical solution scheme, as a kind of vertical rotary formula compressor (notification number: JP7259767A) that Japanese Patent Publication report is recorded; Outside piston week arranges a groove embedded for blade, piston has the hole that groove deepest part and oil supply gallery are connected.Contact between piston and blade becomes face contact, and the spin of piston also suffers restraints, thus reaches the condition of Stable sliding.Simultaneously again by oil supply gallery and hole to the contacting part fuel feeding between piston and blade.According to described structure, this rotary compressor also also exists following defect: 1, in order to avoid blade departs from the groove outside piston side face, and the elastic force needed for spring is comparatively large, and the elastic force rigidity of this rotary compressor spring is estimated should control at more than 20Kg/ ㎜.Produce series of problems thus: as blade piston pressure is increased, contacting part between piston and blade needs feed lubrication, between piston and eccentric part, frictional force increases and compressor efficiency reduces etc. greatly.2, the contacting part between piston and blade needs fuel feeding, namely there is oil supply system, causes that compressor arrangement is complicated and parts machining is more difficult, and cost is higher.
Summary of the invention
The object of the invention is to there are the problems referred to above for existing technology, propose a kind of Rotary-type translation piston compressor, the technical problem to be solved in the present invention how to reduce spring force and increases work efficiency.
Object of the present invention realizes by following technical proposal: a kind of Rotary-type translation piston compressor, and comprise the cylinder with piston cavity and the bent axle with eccentric part, eccentric part is positioned at piston cavity; Described cylinder blade groove has blade; It is characterized in that, on described eccentric part, cover has piston, is connected between eccentric part outer side surface with piston inner side surface by rolling bearing assembly; Described outside piston side face has the concave circular arc groove in strip parallel with piston bus; Described blade end face is convex arch curved surface; Described blade arc top embeds in the concave circular arc groove of piston, and blade end face and concave circular arc groove groove face lean under spring force.
During the work of this Rotary-type translation piston compressor, crankshaft rotating, eccentric part produces frictional force to piston makes piston have rotating tendency.Owing to being connected by rolling bearing assembly between eccentric part with piston, form rolling friction, namely between eccentric part and piston inner hole, frictional force is minimum.Only rely on the frictional force between outside piston and cylinder bores that piston just can be stoped to rotate.Blade embeds in concave circular arc groove, and blade produces pressure to piston under the elastic force effect of spring, and then overcomes the frictional force that eccentric part is passed to piston completely, ensures that piston does not rotate; Blade and piston be required, and to produce rotational resistance also less, and in other words, blade is also less to the pressure produced needed for piston, and the elastic force that namely, spring can produce is less.
In above-mentioned Rotary-type translation piston compressor, the retainer that described rolling bearing assembly comprises some needle rollers and located by needle roller, needle roller relies on eccentric part outer peripheral surface; All needle rollers are uniformly distributed relative to eccentric part circumference.Adopt needle roller effectively can ensure rolling bearing assembly and the axial contact length between piston and eccentric part, especially ensure the stability of piston movement.According to described structure, rolling bearing assembly does not comprise outer ring and inner ring, ensures that rolling bearing assembly is arranged between eccentric part and piston on the basis substantially not changing eccentric part diameter and piston external diameter.
In above-mentioned Rotary-type translation piston compressor, the length L of described needle roller is
wherein H is the height of piston.
In above-mentioned Rotary-type translation piston compressor, the retainer that described rolling bearing assembly comprises several balls and located by ball; On eccentric part outer peripheral surface with piston inner peripheral surface all has the circular orientation ditch corresponding with ball position.
In above-mentioned Rotary-type translation piston compressor, in described bent axle, be provided with oil supply gallery vertically, described eccentric part outer peripheral surface offers the oil outlet be connected with oil supply gallery.During the work of this Rotary-type translation piston compressor, lubricant oil feeds passage and drains between eccentric part and piston from oil outlet; Namely the rubbing surface that the lubricant oil fed makes rolling bearing assembly be associated all is lubricated, and ensures its working life.
The material that piston adopts is through comprehensive consideration cost of production, production method, wear resistance and select after working life.In above-mentioned Rotary-type translation piston compressor, described piston adopts 20CrMnTi material to make and the process of piston face via nitride.20CrMnTi is applicable to cold working, and namely piston adopts cold extrusion shaped; 20CrMnTi is applicable to surface treatment, after via nitride process, has excellent wear resistance and the characteristic of fatigue resistance; Piston inner peripheral surface meets rolling friction between the roller of rolling bearing assembly and piston thus; Outside piston side face meets blade end face and concave circular arc groove groove face and swings and rub.
In above-mentioned Rotary-type translation piston compressor, described piston adopts low-alloy cast iron to make and through Overheating Treatment, piston face hardness is HRc46 ~ 51.20CrMnTi and the low-alloy cast iron prices of raw and semifnished materials low.Improving piston face hardness by heat treatment makes piston meet requirement in working life.
In above-mentioned Rotary-type translation piston compressor, described piston offers an oil through that radially line is through, the Single port of oil through is positioned on concave circular arc groove groove face.
In above-mentioned Rotary-type translation piston compressor, described piston offers an oil through that radially line is through, concave circular arc groove groove face has an oil groove, the vertical line of oil groove and the vertical line of concave circular arc groove are intersected; The Single port of oil through is positioned on concave circular arc groove groove face and oil through is connected with oil groove.
In above-mentioned Rotary-type translation piston compressor, described concave circular arc groove radius R
groovevalue range is R
leaf+ 0.1 ㎜ < R
groove< R
leaf+ 0.3 ㎜; Wherein R
leaffor blade convex arch subsequent corrosion.
The radial difference of blade and piston concave circular arc groove is minimum, make between blade with piston, to be equivalent to arc surface to contact, make between piston and blade, to be sealed into arc surface sealing, and then during the work of this Rotary-type translation piston compressor, minimizing gas leaks between piston and blade, improves the working efficiency of compressor.Between blade and piston, contact gap is very little simultaneously, and pressurized gas reduce the additional force in blade R face, the component along blade glide direction is reduced, and then the elastic force of spring can be allowed to reduce.
In above-mentioned Rotary-type translation piston compressor, described concave circular arc groove width of rebate W
groovevalue range is W
leaf+ 1 ㎜ < W
groove< W
leaf+ 1.5 ㎜; Wherein W
leaffor vane thickness.Above-mentioned parameter ensures that blade convex arch curved surface is generally within piston concave circular arc groove, and when ensureing to swing blade convex arch curved surface knuckle line within piston concave circular arc groove notch.
Compared with prior art, this Rotary-type translation piston compressor work time piston do not rotate only move up and down with small angle swing, be equivalent to translation.Adopt rolling bearing assembly to be connected between piston with crankshaft eccentric portion, reduce the frictional force between crankshaft eccentric portion and piston.
Outside piston side face is offered concave circular arc groove, and blade embeds in concave circular arc groove, increases the rotational resistance that blade produces piston thus, and during guarantee compressor operating, piston does not rotate.
This Rotary-type translation piston compressor is applied in 1 ~ 1.5HP air-conditioning, and the elastic force rigidity of spring only needs to control at 2 ~ 4Kg/ ㎜, even less.Namely reduce blade to the pressure of piston, radial force that rolling bearing assembly is subject to reduces, frictional force reduces between blade and piston and between piston and eccentric part; And then ensure the working life of all parts and reduce power loss, realize the high workload efficiency improving compressor; Reach energy-conservation and the object of consumption reduction.
Accompanying drawing explanation
Fig. 1 is this Rotary-type translation piston compressor compressing mechanism structure cross-sectional schematic.
Fig. 2 is another visual angle sectional structure schematic diagram of this Rotary-type translation piston compressor compressing mechanism.
Fig. 3 is the schematic enlarged-scale view at circle A place in Fig. 2.
Fig. 4 is the structural representation that this Rotary-type translation piston compressor has oil through.
Fig. 5 is the structural representation that this Rotary-type translation piston compressor has oil through and oil groove.
Fig. 6 is the another kind of structure structural representation of this Rotary-type translation piston compressor compressing mechanism.
Fig. 7 is the sectional structure schematic diagram of existing Rotary-type translation piston compressor.
Fig. 8 is existing Rotary-type translation piston compressor compressing mechanism sectional structure schematic diagram.
In figure, 101, bent axle; 102, eccentric part; 103, motor; 104, cylinder; 105, blade; 106, piston; 107, suction chamber; 108, discharge side; 109, suction port; 110, exhaust port; 111, spring; 1, cylinder cap; 2, piston cavity; 3, needle roller; 4, retainer; 5, ball; 6, oil supply gallery; 7, oil outlet; 8, concave circular arc groove; 9, oil through; 10, oil groove.
Embodiment
Be below specific embodiments of the invention and by reference to the accompanying drawings, technological scheme of the present invention is further described, but the present invention be not limited to these embodiments.
As shown in Figure 1 to Figure 3, this Rotary-type translation piston compressor comprises motor 103, cylinder 104, cylinder cap 1, bent axle 101, blade 105, spring 111 and rolling bearing assembly.
Cylinder 104 has cylindrical piston cavity 2.The both sides up and down of cylinder 104 all arrange a cylinder cap 1, and cylinder cap 1 is fixedly connected with cylinder 104, make piston cavity 2 become an airtight space.
Bent axle 101 is positioned on cylinder cap 1, and bent axle 101 has eccentric part 102, and eccentric part 102 is positioned at piston cavity 2.Bent axle 101 is connected with motor 103, is with dynamic crankshaft 101 to rotate when motor 103 runs.
Have a blade groove in cylinder 104, blade groove is connected with piston cavity 2, and blade 105 is embedded in blade groove, and blade 105 is positioned in cylinder 104 thus, and blade 105 is along the to-and-fro motion of blade groove energy.
Piston 106 is in cylindric, and piston 106 is also positioned at piston cavity 2, and piston 106 is enclosed within eccentric part 102; Rolling bearing assembly assemblage gap is left between eccentric part 102 outer side surface and piston 106 inner side surface.As preferably, in order to ensure life-span and the versatility of product, piston 106 external diameter is as far as possible identical with existing standard size of components with eccentric part 102 diameter; And piston 106 wall thickness is greater than the wall thickness of the outer ring that to match with rolling bearing assembly.
The rolling bearing assembly assemblage gap that rolling bearing assembly stays between above-mentioned eccentric part 102 outer side surface and piston 106 inner side surface, makes to be connected by rolling bearing assembly between eccentric part 102 outer side surface with piston 106 inner side surface.Specifically, the retainer 4 that rolling bearing assembly comprises some needle rollers 3 and located by needle roller 3, needle roller 3 relies on eccentric part 102 outer peripheral surface; All needle rollers 3 are uniformly distributed relative to eccentric part 102 circumference.Needle roller 3 diameter and rolling bearing assembly assemblage gap size adapt.As preferably, the length L of the needle roller 3 of rolling bearing assembly is
wherein H is the height of piston 106.
According to actual conditions, rolling bearing assembly can adopt following structure to replace: as shown in Figure 6, the retainer 4 that rolling bearing assembly comprises several balls 5 and located by ball 5; Eccentric part 102 outer peripheral surface all has the circular orientation ditch corresponding with ball 5 position with on piston 106 inner peripheral surface.Piston 106, eccentric part 102 and rolling bearing assembly composition deep groove ball bearing, has the advantage that bearing capacity is high.As preferably, axially arrange two groups of rolling bearing assemblies along piston 106, this structure both ensure that bearing capacity and working life effectively, avoided again piston 106 to swing relative to eccentric part 102.
In order to ensure the working life of the parts such as rolling bearing assembly and piston 106 further, being provided with oil supply gallery 6 in the bent axle 101 of compressor vertically, eccentric part 102 outer peripheral surface offering the oil outlet 7 be connected with oil supply gallery 6.During the work of this Rotary-type translation piston compressor, lubricant oil feeds oil supply gallery 6 and drains between eccentric part 102 and piston 106 from oil outlet 7; Namely the rubbing surface that the lubricant oil fed makes rolling bearing assembly be associated all is lubricated, and ensures its working life.This compressor also carries lubricant oil by this oil supply gallery 6 to cylinder cap 1 and bent axle 101 junction plane simultaneously.
As preferably, piston 106 adopts steel for carburizing 20CrMnTi to make and the surperficial via nitride process of piston 106.According to actual conditions, low-alloy cast iron can be adopted to replace for the making material of piston 106 but piston 106 also needs to make piston 106 surface hardness be HRc46 ~ 51 through Overheating Treatment simultaneously.
As shown in Figures 2 and 3, piston 106 outer peripheral surface has the concave circular arc groove 8 in strip parallel with piston bus; Namely the cross section of groove face is a circular arc line.Concave circular arc groove 8 is axially through along piston 106.Blade 105 end face is convex arch curved surface; Blade 105 width and piston 106 highly adapt.Spring 111 is arranged in cylinder 104, and one end and blade 105 bottom surface of spring 111 lean, and the other end and compressor housing lean.Blade 105, under the compressing of spring 111, R face, blade 105 top is embedded in piston 106 concave circular arc groove 8, and blade 105 end face and concave circular arc groove 8 groove face leans.
During the work of this Rotary-type translation piston compressor, motor 103 is with dynamic crankshaft 101 to rotate, crankshaft eccentric portion 102 rotates relative to cylinder 104, and piston 106 is relative and cylinder 104 non rotating, only do translation up and down, i.e. piston 106 relatively translation and then promote blade 105 along blade groove to-and-fro motion and spring 111 reciprocating compression and extension.Concave circular arc groove 8 groove face and the blade 105 end face R face of piston 106 swing.
Through overtesting, between blade 105 and piston 106, between piston 106 and cylinder 104, between piston 106 and upper and lower cylinder cap 1, just requirement in working life can be met by bent axle mesopore screw piece fuel feeding operationally.
Consider to use new cooling media from now on, as in the situations such as R410a, working pressure is higher, and working load is heavier, and wearing and tearing can be more serious.For guaranteeing that the compressor life-span is in allowed band, as shown in Figure 4, piston offers an oil through 9 that radially line is through, the Single port of oil through 9 is positioned on concave circular arc groove groove face.Following structure can be adopted to replace according to actual conditions: as shown in Figure 5, piston offer an oil through 9 that radially line is through, concave circular arc groove groove face has an oil groove 10, the vertical line of oil groove 10 and the vertical line of concave circular arc groove are intersected; The Single port of oil through 9 is positioned on concave circular arc groove groove face and oil through 9 is connected with oil groove 10.Oil through 9 communicates with gap between piston with eccentric part, makes the lubricating condition in piston concave circular arc groove and blade R face better.
As preferably, concave circular arc groove 8 radius R
groovevalue range is R
leaf+ 0.1 ㎜ < R
groove< R
leaf+ 0.3 ㎜; Wherein R
leaffor blade 105 convex arch subsequent corrosion.Blade 105 is minimum with the radial difference of piston 106 concave circular arc groove 8, ensure blade 105 convex arch curved surface completely in piston 106 concave circular arc groove 8 and make to be equivalent to arc surface between blade 105 with piston 106 and contact, make between piston 106 and blade 105, to be sealed into arc surface to seal, and then during the work of this Rotary-type translation piston compressor, minimizing gas leaks between piston 106 and blade 105, improves compressor efficiency.Between blade 105 and piston 106, contact gap is very little simultaneously, and pressurized gas reduce the additional force in blade 105R face, the component along blade 105 glide direction is reduced, and then the elastic force of spring 111 can be allowed to reduce.
Concave circular arc groove 8 width of rebate W
groovevalue range is W
leaf+ 1 ㎜ < W
groove< W
leaf+ 1.5 ㎜; Wherein W
leaffor blade 105 thickness.Concave circular arc groove 8 width of rebate is slightly larger than blade 105 thickness, when ensureing that ordinary circumstance lower piston 106 swings, blade 105 convex arch curved surface knuckle line is within piston 106 concave circular arc groove 8 notch, pressurized gas are reduced the additional force in blade 105R face, component along blade 105 glide direction is reduced, and then the elastic force of spring 111 can be allowed to reduce, be conducive to the raising of compressor efficiency.
Claims (8)
1. a Rotary-type translation piston compressor, comprise the cylinder (104) with piston cavity (2) and the bent axle (101) with eccentric part (102), eccentric part (102) is positioned at piston cavity (2); Described cylinder (104) inner position has blade (105); It is characterized in that, the upper cover of described eccentric part (102) has piston (106), is connected between eccentric part (102) cylindrical with piston (106) endoporus by rolling bearing assembly; Described piston (106) outer peripheral surface has a concave circular arc groove (8) in strip parallel with piston bus; Described blade (105) R end face is convex arch curved surface; Be provided with in described cylinder (104) and blade (105) top embedded in concave circular arc groove (8) and the spring (111) that leans of blade (105) end face and concave circular arc groove (8) groove face; Described piston (106) offers an oil through (9) that radially line is through, concave circular arc groove (8) groove face has an oil groove (10), the vertical line of oil groove (10) and the vertical line of concave circular arc groove are intersected; The Single port of oil through (9) is positioned on concave circular arc groove (8) groove face and oil through (9) is connected with oil groove (10).
2. Rotary-type translation piston compressor according to claim 1, it is characterized in that, the retainer (4) that described rolling bearing assembly comprises some needle rollers (3) and located by needle roller (3), needle roller (3) relies on eccentric part (102) outer peripheral surface; All needle rollers (3) are uniformly distributed relative to eccentric part (102) circumference.
3. Rotary-type translation piston compressor according to claim 2, is characterized in that, the length L of described needle roller (3) is
wherein H is the height of piston (106).
4. Rotary-type translation piston compressor according to claim 1, is characterized in that, the retainer (4) that described rolling bearing assembly comprises several balls (5) and located by ball (5); Eccentric part (102) outer peripheral surface all has the circular orientation ditch corresponding with ball (5) position with on piston (106) inner peripheral surface.
5. the Rotary-type translation piston compressor according to any one in Claims 1-4, it is characterized in that, be provided with oil supply gallery (6) in described bent axle (101) vertically, described eccentric part (102) outer peripheral surface offer the oil outlet (7) be connected with oil supply gallery (6).
6. the Rotary-type translation piston compressor according to any one in Claims 1-4, is characterized in that, described piston (106) adopts 20CrMnTi material to make and the surperficial via nitride process of piston (106).
7. the Rotary-type translation piston compressor according to any one in Claims 1-4, it is characterized in that, described piston (106) adopts low-alloy cast iron to make and through Overheating Treatment, piston (106) surface hardness is HRc46 ~ 51.
8. the Rotary-type translation piston compressor according to any one in Claims 1-4, is characterized in that, described concave circular arc groove (8) radius R
groovevalue range is R
leaf+ 0.1 ㎜ < R
groove< R
leaf+ 0.3 ㎜; Wherein R
leaffor blade (105) convex arch subsequent corrosion; Described concave circular arc groove (8) width of rebate W
groovevalue range is W
leaf+ 1 ㎜ < W
groove< W
leaf+ 1.5 ㎜, wherein W
leaffor blade (105) thickness.
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| CN201310370147.5A CN103410732B (en) | 2013-08-22 | 2013-08-22 | Rotary-type translation piston compressor |
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| CN201310370147.5A CN103410732B (en) | 2013-08-22 | 2013-08-22 | Rotary-type translation piston compressor |
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| CN103410732B true CN103410732B (en) | 2015-10-07 |
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| CN103644117B (en) * | 2013-12-27 | 2016-05-11 | 浙江百达精工股份有限公司 | Rotary translation piston compressor |
| CN105864048A (en) * | 2016-06-16 | 2016-08-17 | 珠海格力电器股份有限公司 | Rotor compressor and rotor assembly thereof |
| CN106382226B (en) * | 2016-11-30 | 2018-06-08 | 浙江海洋大学 | A kind of structure improved translation piston compressor |
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| CN108119368A (en) * | 2018-01-18 | 2018-06-05 | 珠海凌达压缩机有限公司 | Crankshaft roller structure, compressor and air conditioner |
| CN108087283A (en) * | 2018-01-18 | 2018-05-29 | 珠海凌达压缩机有限公司 | Crankshaft roller structure, compressor and air conditioner |
| CN109356855B (en) * | 2018-11-06 | 2024-06-07 | 珠海格力节能环保制冷技术研究中心有限公司 | Refrigerating equipment and compressor thereof |
| CN112377514B (en) * | 2020-11-11 | 2024-06-04 | 浙江百达精工股份有限公司 | Batch manufacturing method for compressor crankshaft blanks |
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|---|---|
| CN103410732A (en) | 2013-11-27 |
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