CN202152734U - Rotary compressor - Google Patents
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- CN202152734U CN202152734U CN2011202656021U CN201120265602U CN202152734U CN 202152734 U CN202152734 U CN 202152734U CN 2011202656021 U CN2011202656021 U CN 2011202656021U CN 201120265602 U CN201120265602 U CN 201120265602U CN 202152734 U CN202152734 U CN 202152734U
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Abstract
The utility model relates to a rotary compressor, which comprises a shell (12), a compressing mechanism, a rotary shaft (100) and a main bearing (62) supporting a part of the rotating shaft, wherein the compressing mechanism and the rotary shaft (100) are arranged in the shell. A first end of the rotary shaft is provided with an eccentric crank pin (102) which drives the compressing mechanism through a driving bearing (64). The rotary compressor is characterized in that the rotary shaft further comprises an concentric hole (104) formed at the second end of the rotary shaft, a first eccentric hole (110) communicated with the concentric hole (104) in fluid mode and extending to the end face of the eccentric crank pin, a second eccentric hole (120) communicated with the concentric hole in fluid mode and extending to the end face of the first end of the rotary shaft and a transverse hole (130) communicated with the second eccentric hole in fluid mode. The rotary compressor can reasonably distribute the quantity of lubricating oil flowing through the two eccentric holes.
Description
Technical field
The utility model relates to a kind of rotary compressor.
Background technique
Scroll compressor is a kind of in the rotary compressor, and generally includes: housing; Be contained in the driving mechanism in the housing, driving mechanism can comprise motor and running shaft; By running shaft compressor driven structure, compressing mechanism can comprise intermeshing moving vortex and decide vortex; The main bearing of supporting rotating shaft etc.Running shaft comprises axis body and the eccentric crank pin that is arranged on axis body one end.Eccentric crank pin is inserted into via swivel bearing and drives moving vortex in the hub portion of moving the vortex back side thus.Running shaft also comprises and is arranged on running shaft the connection with the concentric holes eccentric crank pin opposite end with concentric holes but the eccentric opening eccentric with respect to concentric holes.Eccentric opening extends to the end face of eccentric crank pin always.In the operation process of compressor, thereby lubricant oil is through the concentric holes of running shaft and the lubricated swivel bearing of end face and main bearing and other movable parts that eccentric opening supplies to eccentric crank pin.
Adopt above-mentioned structure, the lubricants capacity that supplies to swivel bearing and main bearing is often also inequality.Supply with under the sufficient situation at lubricant oil, this does not have any problem.But; Under the situation of the lubricant oil undersupply in compressor; The lubricants capacity that is assigned to swivel bearing and main bearing has obvious different, and it is excessive to cause a lubricant oil in main bearing and the swivel bearing to be supplied with, thereby and another lubricant oil undersupply damages compressor.
The model utility content
The technical problem that one or more mode of executions of the utility model will solve provides a kind of rotary compressor: in this rotary compressor; Even the lubricant oil undersupply in the compressor, the lubricants capacity that also can reasonable distribution supplies to main bearing and driving bearing makes main bearing and driving bearing obtain proper lubrication simultaneously.
The purpose of one or more mode of executions of the utility model provides a kind of rotary compressor that can reasonable distribution supplies to the lubricants capacity of main bearing and swivel bearing.
An aspect according to this specification provides a kind of rotary compressor, comprising: housing; Be arranged on the compressing mechanism in the said housing; Running shaft, first end of said running shaft is provided with eccentric crank pin, and said eccentric crank pin drives said compressing mechanism via driving bearing; Support the main bearing of the part of said running shaft; It is characterized in that said running shaft further comprises: the concentric holes that is formed on second end opposite of said running shaft with said eccentric crank pin; Be communicated with and extend to first eccentric opening of the end face of said eccentric crank pin with said concentric holes fluid; Be communicated with and extend to second eccentric opening of end face of first end of said running shaft with said concentric holes fluid; The transverse holes that is arranged on the position corresponding and is communicated with the said second eccentric opening fluid with said main bearing.
Preferably, the end opposite with said concentric holes at said second eccentric opening is provided with plug.
Preferably, the central axis of the central axis of the central axis of said first eccentric opening, said second eccentric opening and said running shaft is in the identical plane.
Preferably, the central axis of the central axis of said first eccentric opening and said second eccentric opening central axis about said running shaft in said plane is symmetrical.
Preferably, said eccentric crank pin comprises planar surface portion, and said plane parallel is in the plane at said planar surface portion place.
Preferably, said first eccentric opening and said second eccentric opening are parallel.
Preferably, said first eccentric opening and said concentric holes said running shaft vertically on overlap length L1 and said second eccentric opening and said concentric holes equate at the overlap length L2 on said running shaft vertical.
Preferably, the hole heart between the central axis of the central axis of said first eccentric opening and said concentric holes equates apart from d2 apart from the hole heart between the central axis of the central axis of d1 and said second eccentric opening and said concentric holes.
Preferably, the diameter D2 of the diameter D1 of said first eccentric opening and said second eccentric opening equates.
Alternately, said first eccentric opening and said concentric holes said running shaft vertically on overlap length L1 can less than or greater than said second eccentric opening and the said concentric holes overlap length L2 on said running shaft vertical.Said overlap length L1 and L2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening and said second eccentric opening.
Alternately, the hole heart between the central axis of the central axis of said first eccentric opening and said concentric holes apart from d1 can less than or greater than the hole heart between the central axis of the central axis of said second eccentric opening and said concentric holes apart from d2.The said hole heart is confirmed according to the lubricants capacity allotment ratio between said first eccentric opening and said second eccentric opening apart from d1 and d2.
Alternately, the diameter D1 of said first eccentric opening can less than or greater than the diameter D2 of said second eccentric opening.Said diameter D1 and D2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening and said second eccentric opening.
Preferably, said compressing mechanism comprises intermeshing moving vortex and decides vortex that said moving vortex comprises hub portion; The eccentric crank pin of wherein said running shaft inserts said hub portion via said driving bearing.
Preferably, said rotary compressor further comprises the main bearing seat that supports said compressing mechanism and said running shaft, and said main bearing is arranged in the said main bearing seat.
Preferably, said main bearing seat and said housing form as one.
Preferably, said rotary compressor is a horizontal type scroll compressor.
Preferably, in said running shaft, also be provided with the intercommunicating pore that makes that said first eccentric opening and said second eccentric opening communicate with each other.
Preferably, said intercommunicating pore is arranged to first end near said running shaft.
Advantage according to the rotary compressor of one or more mode of executions of the utility model is:
Owing to be provided with two eccentric openings that are respectively applied for to driving bearing and main bearing supplying lubricating oil in the running shaft, therefore can more easily control the distribution of lubricants capacity between two eccentric openings.Thus; Can just can the running shaft of this specification be adapted to vertical scroll compressor and horizontal compressor through changing one or more in following three parameters, said three parameters are: the hole heart of the overlap length of eccentric opening and concentric holes, eccentric opening and concentric holes apart from and the diameter of eccentric opening.Therefore, can simplify the global design time of compressor.
Above-mentioned three parameters of two eccentric openings of running shaft are being set under the identical situation, and the distribution of lubricants capacity between two eccentric openings is equal basically generally speaking.Therefore under the situation of lubricants capacity undersupply, main bearing and driving bearing can obtain the lubricant oil of basic identical amount.
The processing of the running shaft of one or more mode of executions of the utility model is simple, can form two eccentric openings through the end that is provided with eccentric crank pin from running shaft through two drilling operatings.The throw of eccentric of the degree of depth, boring and rotating shaft center through keyhole and the diameter of boring can process the eccentric opening that meets artificer's intention.In addition, adopt plug to stop up an end of second eccentric opening then owing to hole, so drilling operating can not receive the interference of concentric holes from an end that is provided with eccentric crank pin of running shaft.
In running shaft, also be provided with the intercommunicating pore that win eccentric opening and second eccentric opening are communicated with each other, therefore the gas in second eccentric opening can be discharged from first eccentric opening through this intercommunicating pore, has avoided gas to stop up second eccentric opening.
Description of drawings
Through following description with reference to accompanying drawing, the feature and advantage of one or several mode of execution of the utility model will become and be more prone to understand, wherein:
Fig. 1 is the schematic cross sectional view according to the horizontal type scroll compressor of the utility model;
Fig. 2 is the schematic representation according to first mode of execution of the running shaft of the utility model;
Fig. 3 is the schematic representation according to second mode of execution of the running shaft of the utility model;
Fig. 4 is the schematic representation according to the 3rd mode of execution of the running shaft of the utility model;
Fig. 5 is the schematic representation according to the 4th mode of execution of the running shaft of the utility model.
Embodiment
Following description related to the preferred embodiment only is exemplary, and never is the restriction to the utility model and application or usage.
The model utility people of the utility model finds: in some vertical scroll compressor, in order improving the lubricant oil of main bearing to be supplied with, to be provided with the transverse holes that is communicated with eccentric opening in the position corresponding with main bearing of running shaft.In this compressor constructions, lubricant oil can directly supply to main bearing and can directly supply to swivel bearing through the eccentric opening that extends to the eccentric crank pin end face through this transverse holes.Because the height of transverse holes is lower than the end face of eccentric crank pin, so lubricant oil can more easily supply to main bearing.Under the situation of lubricant oil undersupply, swivel bearing will obtain lubricant oil still less than main bearing, so swivel bearing may lose efficacy prior to main bearing.
The model utility people of the utility model also finds: in horizontal type scroll compressor, the oil groove of storage lubricant oil is positioned at the high pressure side and temperature is higher relatively, and the lubricants capacity that therefore supplies to low voltage side has direct influence to the overall performance of compressor.Such as, the lubricant oil of heat that supplies to low voltage side is many more, air-breathing overheated will be high more.In addition, thus the motor that the lubricant oil of heat can add thermocompressor causes the decrease in efficiency of motor.Therefore, the lubricants capacity that supplies to low voltage side must be controlled.In addition, in horizontal type scroll compressor, even the transverse holes of directly leading to main bearing of dividing expenditure from eccentric opening is set, but because main bearing is positioned at identical level height with swivel bearing, lubricant oil supplies to swivel bearing more easily.Therefore, under the situation of lubricant oil undersupply, main bearing may lose efficacy prior to swivel bearing.
Therefore, no matter be at vertical scroll compressor or in horizontal type scroll compressor, how to supply to the lubricants capacity of swivel bearing and main bearing all be a kind of challenge to reasonable distribution.In order to tackle this challenge, the model utility people of the utility model has proposed in running shaft, to be provided with the design of two eccentric openings, thereby can distribute and control the lubricants capacity that supplies to swivel bearing and main bearing.Therefore, under the situation of lubricant oil undersupply, two bearings can obtain the lubricant oil of basic identical amount.
To be elaborated to the utility model with reference to the embodiment shown in Fig. 1-5 below.
Fig. 1 is the schematic cross sectional view according to the horizontal type scroll compressor of one or more mode of executions of the utility model.
The front cover 14 that as shown in Figure 1, horizontal type scroll compressor (hereafter is " compressor ") 10 comprises housing 12, be fixedly connected with housing 12 through bolt and dividing plate 18 and the rear end cover 16 that is fixedly connected with housing 12 through bolt.Housing 12 is provided with the air-breathing joint 20 that is used to suck refrigeration agent (working fluid), and front cover 14 is provided with the exhaust joint 22 that is used for discharging refrigerant (working fluid).
Through dividing plate 18 inner space of compressor 10 is separated into high pressure side and low voltage side.Particularly, the space that is impaled by housing 12, rear end cover 16 and dividing plate 18 constitutes the refrigeration agent (working fluid) that low voltage side is used to suck low pressure.The space that is impaled by dividing plate 18 and front cover 14 constitutes the high-pressure refrigerant (working fluid) after the high pressure side is used to discharge compression.In this mode of execution, lubricant oil mainly is stored in the high pressure side, promptly is stored in the space that is impaled by front cover 14 and dividing plate 18.In other words, the high pressure side of compressor defines the oil groove of storage lubricant oil.
Be equipped with in the housing 12 as the moving vortex of compressing mechanism 30 with decide vortex 40 and as the motor 50 and the running shaft 100 of driving mechanism.Compressing mechanism can support by drive mechanism and by main bearing seat 60.Main bearing seat 60 can be fixed to housing 12 in any desired way.In the example depicted in fig. 1, main bearing seat 60 forms as one with housing 12.
Moving vortex 30 comprises end plate 32, is provided with vortex volume 34 on a surface of end plate 32 (being the left surface among Fig. 1), (is right surface among Fig. 1) on its another surface and is provided with cylindrical hub portion 36.Decide vortex 40 and comprise end plate 42 and vortex volume 44.The vortex of moving vortex 30 volume 34 and vortex volume 44 engagements of decide vortex 40 and form betwixt from the outside when moving vortex 30 with when deciding vortex 40 relative movement that thereby the refrigeration agent (working fluid) to the fluid chamber convection current body cavity that central volume reduces gradually compresses.
To describe structure below in detail according to the running shaft of the mode of execution of one or more mode of executions of the utility model.
Referring to Fig. 1 and Fig. 2, wherein the left part of Fig. 2 shows the end view drawing of running shaft, and right portions shows the longitudinal plane figure of running shaft.First end of running shaft 100 (among Fig. 1 for left end) is provided with the eccentric crank pin 102 and first counterweight 72, running shaft 100 be provided with second counterweight 74 with eccentric crank pin 102 opposite second ends (being right-hand member among Fig. 1).First counterweight 72 and second counterweight 74 are arranged on the running shaft 100 regularly, therefore when running shaft 100 rotations, can rotate with running shaft 100 one.The left part of running shaft 100 is supported with rotating mode by the main bearing in the main bearing seat 60 62, and its right portions is supported with rotating mode by the support in the rear end cover 16 17.
Second end of running shaft 100 can comprise oilhole 104.Preferably, oilhole 104 is concentric with the spin axis of running shaft 100, so hereinafter also is called concentric holes 104 with this oilhole.Concentric holes 104 is communicated with the oil groove fluid of compressor.For example, the lubricant oil in the oil groove can supply in the concentric holes 104 of running shaft 100 via the support in the rear end cover 16 17 through compressor inner pipeline or the outside pipeline of compressor.
Can be simultaneously referring to Fig. 2; Running shaft 100 also can comprise and being communicated with concentric holes 104 fluids and eccentric and roughly along first eccentric opening 110 of the end face that extends lengthwise into eccentric crank pin 102 of running shaft with respect to concentric holes 104, and is communicated with concentric holes 104 fluids, separates with respect to concentric holes 104 off-centre and with first eccentric opening 110, roughly along second eccentric opening 120 of the end face that extends lengthwise into running shaft of running shaft.First eccentric opening 110 and second eccentric opening 120 can laterally arrange.Side at running shaft 100 also is being provided with the transverse holes 130 that is communicated with second eccentric opening, 120 fluids with main bearing 62 corresponding positions.The end opposite with concentric holes at second eccentric opening 120 is provided with plug 140, thereby prevents that the lubricant oil in second eccentric opening 120 from directly seldom flowing through transverse holes 130 through this end outflow.
Adopt above-mentioned structure; When compressor operating; At first supply to the concentric holes 104 of running shaft 100 from the lubricant oil of oil groove, then via with concentric holes 104 simultaneously first eccentric opening 110 that is communicated with of fluid directly supply to swivel bearing 64 and main bearing 62 respectively with second eccentric opening 120 (reaching transverse holes 130).Lubricant oil can be adjusted through crossing volume V1 and the crossing volume V2 between second eccentric opening 1120 and the concentric holes 104 that adjusts between first eccentric opening 110 and the concentric holes 104 in the distribution between first eccentric opening 110 and second eccentric opening 120.Particularly; Referring to Fig. 2, above-mentioned crossing volume V1 is decided by first eccentric opening 110 and the concentric holes 104 hole heart between the center of the center of the overlap length L1 of running shaft on vertically, first eccentric opening and concentric holes, three parameters of diameter D1 apart from the d1 and first eccentric opening.Above-mentioned crossing volume V2 is decided by second eccentric opening 120 and the concentric holes 104 hole heart between the center of the center of the overlap length L2 of running shaft on vertically, second eccentric opening and concentric holes, three parameters of diameter D2 apart from the d2 and second eccentric opening.
Preferably, hope to supply to the lubricants capacity of swivel bearing 64 and to supply to the lubricants capacity of main bearing 62 equal basically via second eccentric opening 120 via first eccentric opening 110.In order to realize this distribution of lubrication oil target, can make crossing volume V1 and V2 about equally through above-mentioned three parameters of adjustment.Preferably; Can be so that the overlap length L2 of the overlap length L1 of first eccentric opening 110 and second eccentric opening 120 be equal; The hole heart of first eccentric opening 110 equates apart from d2 apart from the hole heart of the d1 and second eccentric opening 120, and the diameter D2 of the diameter D1 of first eccentric opening 110 and second eccentric opening equates.Fig. 2 shows the situation of this optimum.
In order to minimize of the influence of two eccentric openings to running shaft 100 rigidity and intensity; The center that is preferably such that first eccentric opening 110 is positioned at identical plane P with the center of second eccentric opening 120 with the center of concentric holes (being the rotating center of running shaft), and this plane P is parallel to the plane at planar surface portion 103 places of eccentric crank pin 102.In the normal operation of compressor, this plane P is the neutral surface of running shaft 100 under the moment of flexure effect, and on this neutral surface, the tensile stress and the pressure stress that are caused by moment of flexure all are zero.Further preferred, the center of the center of first eccentric opening 110 and second eccentric opening 120 in above-mentioned plane P about center (being the rotating center of the running shaft) symmetry of concentric holes.
In addition, in running shaft 100, also be provided with the intercommunicating pore 150 that win eccentric opening 110 and second eccentric opening 120 are communicated with each other.This intercommunicating pore 150 can be arranged on the running shaft 100 any position on vertically, as long as can realize the connection between first eccentric opening 110 and second eccentric opening 120.Yet preferably, this intercommunicating pore 150 can be arranged to the end that is provided with eccentric crank pin 102 near running shaft 100.This intercommunicating pore 150 can be so that thereby the gas communication in first eccentric opening 110 and second eccentric opening 120 helps to discharge smoothly the gas in second eccentric opening 120.In the operation process of compressor; The rotation of running shaft makes the lubricant oil in the win eccentric opening 110 and second eccentric opening 120 be close to the outer wall towards the running shaft outside of each eccentric opening, so the inwall towards the center of running shaft of each eccentric opening does not have lubricant oil basically.Therefore, the gas in second eccentric opening 120 can get in first eccentric opening 110 and the final end discharge that is in eccentric crank pin 102 from first eccentric opening 110 through intercommunicating pore 150.
Under specific circumstances, the artificer's lubricants capacity difference that possibly hope to distribute in two eccentric openings is to realize specific purpose.According to the design of this specification, can more easily realize distribution and the control of lubricants capacity between two eccentric openings.
Fig. 3 shows the schematic representation according to second mode of execution of the running shaft 100 of one or more mode of executions of the utility model, and wherein the left part of Fig. 3 shows the end view drawing of running shaft, and right portions shows the longitudinal plane figure of running shaft.In this embodiment, first eccentric opening 110 is different with the longitudinal overlap length L 2 of concentric holes 104 with second eccentric opening 120 with the longitudinal overlap length L 1 of concentric holes 104, particularly, and L2＞L1.Other parameters of two eccentric openings are all identical.Therefore, thus can in second eccentric opening 120, distribute more lubricating oil for being preferably the main bearing supplying lubricating oil.
Fig. 4 shows the schematic representation according to the 3rd mode of execution of the running shaft 100 of one or more mode of executions of the utility model, and wherein the left part of Fig. 4 shows the end view drawing of running shaft, and right portions shows the longitudinal plane figure of running shaft.In this embodiment, the hole heart between the center of the center of first eccentric opening 110 and concentric holes 104 is different apart from d2 apart from the hole heart between the center of the center of the d1 and second eccentric opening 120 and concentric holes 104, particularly, and d1＞d2.Other parameters of two eccentric openings are all identical.Therefore, thus can in second eccentric opening 120, distribute more lubricating oil for being preferably the main bearing supplying lubricating oil.
Fig. 5 shows the schematic representation according to the 4th mode of execution of the running shaft 100 of one or more mode of executions of the utility model, and wherein the left part of Fig. 5 shows the end view drawing of running shaft, and right portions shows the longitudinal plane figure of running shaft.In this embodiment, the diameter D1 of first eccentric opening 110 is different with the diameter D2 of second eccentric opening 120, particularly, and D1＞D2.Other parameters of two eccentric openings are all identical.Therefore, thus can in first eccentric opening 110, distribute more lubricating oil for being preferably the swivel bearing supplying lubricating oil.
To mode of execution shown in Figure 2, model utility people has carried out experiment to observe the lubricants capacity that supplies to swivel bearing and main bearing through two eccentric openings respectively to it.Experimental result is seen table 1.
In above-mentioned experiment, only changed the rotating speed of compressor.The variation of the flow of lubrication that occurs in the table is because the axial motion of running shaft produces.The ratio of DB and MB can be found out from table 1, the lubricants capacity that supplies to swivel bearing and main bearing under various rotating speeds all much at one.In other words, adopt the structure of one or more mode of executions of the utility model, the distribution of lubrication oil that realizes through first eccentric opening and second eccentric opening is irrelevant with the rotating speed of compressor.
Model utility people also tests structure shown in Figure 2 through flow rate of lubricating oil being increased by three times.Experimental result is seen table 2.
The ratio of DB and MB can be found out from table 2, the lubricants capacity that supplies to swivel bearing and main bearing under the various rotating speeds under various flow of lubrication all much at one.In other words, adopt the structure of one or more mode of executions of the utility model, the distribution of lubrication oil that realizes through first eccentric opening and second eccentric opening is irrelevant with the rotating speed and the lubricant oil delivery volume of compressor.
That is to say, adopt the structure of one or more mode of executions of the utility model,, also can supply with the lubricant oil of appropriate amount to swivel bearing and main bearing according to artificer's expectation even under the situation of lubricant oil undersupply.Such as, supply with identical lubricants capacity to swivel bearing with main bearing, perhaps in them supplies with more lubricating oil.
Two eccentric openings in the running shaft of one or more mode of executions of the utility model only can be accomplished through two drilling operatings through the end that is provided with eccentric crank pin from running shaft.And the throw of eccentric of the degree of depth, boring and rotating shaft center through keyhole and the diameter of boring can process the eccentric opening that meets artificer's intention.In addition, adopt an end of plug 140 obstructions second eccentric opening then owing to holing, so drilling operating can not receive the interference of concentric holes from an end that is provided with eccentric crank pin of running shaft.
Although this specification is that example is illustrated with the horizontal scroll compressor that partly seals; But those skilled in the art are to be understood that one or more mode of executions of the utility model and are equally applicable to enclosed open scroll compressor, and one or more mode of executions of the utility model can also be applicable to vertical scroll compressor.In addition, one or more mode of executions of the utility model also pass through running shaft other machineries with distribution of lubrication oil to two diverse location applicable to needs.
Although described the various mode of executions of the utility model in detail at this; But should be appreciated that the utility model is not limited to the embodiment of describing in detail and illustrating here, under the situation of essence that does not depart from the utility model and scope, can realize other modification and variant by those skilled in the art.All these modification and variant all fall in the scope of the utility model.And all members described here can be replaced by the member that is equal on the other technologies property.
Claims (21)
1. rotary compressor comprises:
Housing (12);
Be arranged on the compressing mechanism in the said housing (12);
Running shaft (100), first end of said running shaft (100) is provided with eccentric crank pin (102), and said eccentric crank pin (102) drives said compressing mechanism via driving bearing (64);
Support the main bearing (62) of the part of said running shaft (100);
It is characterized in that said running shaft (100) further comprises:
Be formed on the concentric holes (104) of second end opposite of said running shaft (100) with said eccentric crank pin (102);
Be communicated with and extend to first eccentric opening (110) of the end face of said eccentric crank pin (102) with said concentric holes (104) fluid;
Be communicated with and extend to second eccentric opening (120) of end face of first end of said running shaft (100) with said concentric holes (104) fluid;
The transverse holes (130) that is formed on the position corresponding and is communicated with said second eccentric opening (120) fluid with said main bearing (64).
2. rotary compressor as claimed in claim 1, wherein the end opposite with said concentric holes (104) at said second eccentric opening (120) is provided with plug (140).
3. rotary compressor as claimed in claim 1, the central axis of the central axis of wherein said first eccentric opening (110), said second eccentric opening (120) is in the identical plane (P) with the central axis of said running shaft (100).
4. rotary compressor as claimed in claim 3, the central axis of the central axis of wherein said first eccentric opening (110) and said second eccentric opening (120) central axis about said running shaft in said plane (P) is symmetrical.
5. rotary compressor as claimed in claim 3, wherein said eccentric crank pin (102) comprises planar surface portion (103), said plane (P) is parallel to the plane at said planar surface portion (103) place.
6. rotary compressor as claimed in claim 1, wherein said first eccentric opening (110) and said second eccentric opening (120) are parallel.
7. rotary compressor as claimed in claim 1, wherein said first eccentric opening (110) and said concentric holes (104) said running shaft (100) vertically on overlap length L1 and said second eccentric opening (120) and said concentric holes (104) equate at the overlap length L2 on said running shaft (100) vertical.
8. the hole heart between the rotary compressor as claimed in claim 1, the central axis of wherein said first eccentric opening (110) and the central axis of said concentric holes (104) equates apart from d2 apart from the hole heart between the central axis of the central axis of d1 and said second eccentric opening (120) and said concentric holes (104).
9. rotary compressor as claimed in claim 1, the diameter D2 of the diameter D1 of wherein said first eccentric opening (110) and said second eccentric opening (120) equates.
10. rotary compressor as claimed in claim 1; Wherein said first eccentric opening (110) and said concentric holes (104) said running shaft (100) vertically on overlap length L1 less than said second eccentric opening (120) and said concentric holes (104) said running shaft (100) vertically on overlap length L2, wherein said overlap length L1 and L2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120).
11. rotary compressor as claimed in claim 1; Wherein said first eccentric opening (110) and said concentric holes (104) said running shaft (100) vertically on overlap length L1 greater than said second eccentric opening (120) and said concentric holes (104) said running shaft (100) vertically on overlap length L2, wherein said overlap length L1 and L2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120).
12. rotary compressor as claimed in claim 1; The hole heart between the central axis of the central axis of wherein said first eccentric opening (110) and said concentric holes (104) apart from d1 less than the hole heart between the central axis of the central axis of said second eccentric opening (120) and said concentric holes (104) apart from d2, the said hole heart is confirmed according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120) apart from d1 and d2.
13. rotary compressor as claimed in claim 1; The hole heart between the central axis of the central axis of wherein said first eccentric opening (110) and said concentric holes (104) apart from d1 greater than the hole heart between the central axis of the central axis of said second eccentric opening (120) and said concentric holes (104) apart from d2, the said hole heart is confirmed according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120) apart from d1 and d2.
14. rotary compressor as claimed in claim 1; The diameter D1 of wherein said first eccentric opening (110) is less than the diameter D2 of said second eccentric opening (120), and said diameter D1 and D2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120).
15. rotary compressor as claimed in claim 1; The diameter D1 of wherein said first eccentric opening (110) is greater than the diameter D2 of said second eccentric opening (120), and said diameter D1 and D2 confirm according to the lubricants capacity allotment ratio between said first eccentric opening (110) and said second eccentric opening (120).
16. rotary compressor as claimed in claim 1, wherein said compressing mechanism comprise intermeshing moving vortex (30) and decide vortex (40) that said moving vortex (30) comprises hub portion (36);
The eccentric crank pin (102) of wherein said running shaft (100) inserts said hub portion (36) via said driving bearing (64).
17. rotary compressor as claimed in claim 1 further comprises the main bearing seat (60) that supports said compressing mechanism and said running shaft (100), said main bearing (62) is arranged in the said main bearing seat (60).
18. rotary compressor as claimed in claim 17, wherein said main bearing seat (60) forms as one with said housing (12).
19. rotary compressor as claimed in claim 1, wherein said rotary compressor are horizontal type scroll compressor.
20. rotary compressor as claimed in claim 1 wherein also is provided with the intercommunicating pore (150) that makes that said first eccentric opening (110) and said second eccentric opening (120) communicate with each other in said running shaft (100).
21. rotary compressor as claimed in claim 20, wherein said intercommunicating pore (150) is arranged to first end near said running shaft (100).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202656021U CN202152734U (en) | 2011-07-14 | 2011-07-14 | Rotary compressor |
| PCT/CN2012/078229 WO2013007163A1 (en) | 2011-07-14 | 2012-07-05 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202656021U CN202152734U (en) | 2011-07-14 | 2011-07-14 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202152734U true CN202152734U (en) | 2012-02-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202656021U Expired - Lifetime CN202152734U (en) | 2011-07-14 | 2011-07-14 | Rotary compressor |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102878081A (en) * | 2011-07-14 | 2013-01-16 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
| WO2013007163A1 (en) * | 2011-07-14 | 2013-01-17 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
| US11125233B2 (en) | 2019-03-26 | 2021-09-21 | Emerson Climate Technologies, Inc. | Compressor having oil allocation member |
| US11680568B2 (en) | 2018-09-28 | 2023-06-20 | Emerson Climate Technologies, Inc. | Compressor oil management system |
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2011
- 2011-07-14 CN CN2011202656021U patent/CN202152734U/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102878081A (en) * | 2011-07-14 | 2013-01-16 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
| WO2013007163A1 (en) * | 2011-07-14 | 2013-01-17 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
| CN102878081B (en) * | 2011-07-14 | 2016-05-04 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
| US11680568B2 (en) | 2018-09-28 | 2023-06-20 | Emerson Climate Technologies, Inc. | Compressor oil management system |
| US11125233B2 (en) | 2019-03-26 | 2021-09-21 | Emerson Climate Technologies, Inc. | Compressor having oil allocation member |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO.,LTD Free format text: FORMER OWNER: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH + DEVELOPMENT CO., LTD. Effective date: 20120420 |
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| C41 | Transfer of patent application or patent right or utility model | ||
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Effective date of registration: 20120420 Address after: 215021, 69 West Road, Suzhou Industrial Park, Jiangsu, China Patentee after: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) Co.,Ltd. Address before: 215021, Emerson building, 1355 international science and Technology Park, Jinji Lake Avenue, Suzhou Industrial Park, Jiangsu, China Patentee before: Emerson Climate Technologies (Suzhou) Research & Development Co.,Ltd. |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20120229 Effective date of abandoning: 20160504 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20120229 Effective date of abandoning: 20160504 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |