CN209458123U - Crankshaft and rotor-type compressor - Google Patents
Crankshaft and rotor-type compressor Download PDFInfo
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- CN209458123U CN209458123U CN201822083712.0U CN201822083712U CN209458123U CN 209458123 U CN209458123 U CN 209458123U CN 201822083712 U CN201822083712 U CN 201822083712U CN 209458123 U CN209458123 U CN 209458123U
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Abstract
The utility model provides a kind of crankshaft and rotor-type compressor.The crankshaft includes the center oilhole (1) and radial direction side opening (2) of connection, the diameter of center oilhole (1) is a, the diameter of radial side opening (2) is r, the distance between end end face is h where the central axis of radial side opening (2) and the eccentric part of crankshaft, relationship between center oilhole (1) and radial side opening (2) meets: 4mm≤a≤7mm, and 0.07≤c≤0.13；Or, 7mm≤a≤10mm, and 0.05≤c≤0.11；Or, 10mm≤a≤13mm, and 0.04≤c≤0.1；Wherein c=r/h.Crankshaft according to the present utility model can be effectively improved the lubricant effect of each component, improve the reliability and performance of compressor.
Description
Technical field
The utility model belongs to Compressor Technology field, and in particular to a kind of crankshaft and rotor-type compressor.
Background technique
The working principle of existing compressor with rolling rotor are as follows: the crankshaft of the pump housing makes rotating motion driven by the motor, leads to
The rotation for crossing crankshaft drives roller to do eccentric circular motion to compress to cold coal.Crankshaft is constantly doing high speed rotation fortune
It is dynamic, therefore the friction of moving component is the most violent.Main movement pair in compressor has, in crankshaft major and minor axis and upper lower flange
Wall, crankshaft eccentric portion and roller inner circle, while being also the place for most needing lubrication between kinematic pair, excessive oil lubrication will cause again
Hydraulic situation, how to improve the lubricant effect of each component with improve compressor reliability and performance be each compressor manufacturer urgently
The technical problem of solution.
Utility model content
Therefore, the technical problem to be solved by the present invention is to provide a kind of crankshaft and rotor-type compressor, Neng Gouyou
Effect improves the lubricant effect of each component, improves the reliability and performance of compressor.
To solve the above-mentioned problems, the utility model provides a kind of crankshaft, the center oilhole including connection and radial side opening,
The diameter of center oilhole is a, and the diameter of radial side opening is r, end end where the central axis of radial side opening and the eccentric part of crankshaft
The distance between face is h, and the relationship between center oilhole and radial side opening meets:
4mm≤a≤7mm, and 0.07≤c≤0.13；Or,
7mm≤a≤10mm, and 0.05≤c≤0.11；Or,
10mm≤a≤13mm, and 0.04≤c≤0.1；
Wherein c=r/h.
Preferably, crankshaft include along axial sequentially connected short axle, the first connecting shaft, the first eccentric part, the second eccentric part,
Second connecting shaft and long axis, radial side hole are located in the first connecting shaft, the first eccentric part, the second eccentric part and the second connecting shaft.
Preferably, the corresponding center oilhole diameter of the first connecting shaft is a1, the corresponding radial side bore dia of the first connecting shaft
For r1, the distance between end end face is where the central axis of the corresponding radial side opening of the first connecting shaft and the eccentric part of crankshaft
H1, c1=r1/h1, wherein a1 and c1 meets: 4mm≤a1≤7mm, 0.07≤c1≤0.13.
Preferably, the corresponding center oilhole diameter of the first eccentric part is a2, the corresponding radial side bore dia of the first eccentric part
For r2, the distance between end end face is where the central axis of the corresponding radial side opening of the first eccentric part and the eccentric part of crankshaft
H2, c2=r2/h2, wherein a2 and c2 meets:
4mm≤a2≤7mm, 0.07≤c2≤0.13；Or,
7mm≤a2≤10mm, and 0.05≤c2≤0.11.
Preferably, the corresponding center oilhole diameter of the second eccentric part is a3, the corresponding radial side bore dia of the second eccentric part
For r3, the distance between end end face is where the central axis of the corresponding radial side opening of the second eccentric part and the eccentric part of crankshaft
H3, c3=r3/h3, wherein a3 and c3 meets:
7mm≤a3≤10mm, and 0.05≤c3≤0.11；Or,
10mm≤a3≤13mm, and 0.04≤c3≤0.1.
Preferably, the corresponding center oilhole diameter of the second connecting shaft is a4, the corresponding radial side bore dia of the second connecting shaft
For r4, the distance between end end face is where the central axis of the corresponding radial side opening of the second connecting shaft and the eccentric part of crankshaft
H4, c4=r4/h4, wherein a4 and c4 meets: 10mm≤a4≤13mm, and 0.04≤c4≤0.1.
Preferably, crankshaft includes along axial sequentially connected short axle, the first eccentric part, the second eccentric part and long axis, radial direction
Side opening is located on the first eccentric part and the second eccentric part.
Preferably, the smallest side of the distance between the central axis of center oilhole of the first eccentric part is arranged in radial side opening
On wall.
Preferably, the smallest side of the distance between the central axis of center oilhole of the second eccentric part is arranged in radial side opening
On wall.
Preferably, center oilhole is axially in stepped pore distribution, and along end end face where the eccentric part far from crankshaft
Direction aperture be incremented by.
Another aspect according to the present utility model provides a kind of rotor-type compressor, including crankshaft, which is above-mentioned
Crankshaft.
Crankshaft provided by the utility model, be provided with connection center oilhole and radial side opening, center oilhole it is straight
Diameter is a, and the diameter of radial side opening is r, the distance between end end face where the central axis of radial side opening and the eccentric part of crankshaft
For h, the relationship between center oilhole and radial side opening meets: 4mm≤a≤7mm, and 0.07≤c≤0.13；Or, 7mm≤a≤
10mm, and 0.05≤c≤0.11；Or, 10mm≤a≤13mm, and 0.04≤c≤0.1, wherein c=r/h.It is different by limiting
Proportionate relationship between the diameter and axial distance of radial side opening under center oilhole diameter range, can guarantee compressor operating
When moving component between lubricant effect reach most preferably can be reduced the pump housing it is hydraulic and take away pump body compression generation heat, solve
The problem of design difficulty and compressor moving component lack of lubrication of crankshaft oilway, reduction is hydraulic, improves the reliability of compressor
And performance.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the crankshaft of the utility model embodiment；
Fig. 2 is the structural schematic diagram of the compressor of the utility model embodiment；
Curve relation figure when Fig. 3 is 4mm≤a≤7mm between compressor friction power loss w and c；
Curve relation figure when Fig. 4 is 7mm≤a≤10mm between compressor friction power loss w and c；
Curve relation figure when Fig. 5 is 10mm≤a≤13mm between compressor friction power loss w and c.
Appended drawing reference indicates are as follows:
1, center oilhole；2, radial side opening；3, short axle；4, the first connecting shaft；5, the first eccentric part；6, the second eccentric part；
7, the second connecting shaft；8, long axis；9, first bearing；10, second bearing；11, shell；12, driving assembly.
Specific embodiment
In conjunction with referring to figs. 1 to 5, embodiment according to the present utility model, crankshaft includes 1 He of center oilhole of connection
Radial side opening 2, the diameter of center oilhole 1 are a, and the diameter of radial side opening 2 is r, the central axis of radial side opening 2 and crankshaft it is inclined
The distance between end end face where center portion is h, and the relationship between center oilhole 1 and radial side opening 2 meets: 4mm≤a≤7mm, and
0.07≤c≤0.13；Or, 7mm≤a≤10mm, and 0.05≤c≤0.11；Or, 10mm≤a≤13mm, and 0.04≤c≤
0.1；Wherein c=r/h.
The ratio between diameter r and axial distance h by limiting the radial side opening 2 under different center oilhole diameter ranges
Relationship can guarantee that lubricant effect when compressor operating between moving component reaches most preferably, and it is hydraulic and take away to can be reduced the pump housing
The heat that pump body compression generates, solves the problems, such as the design difficulty and compressor moving component lack of lubrication of crankshaft oilway, reduces
It is hydraulic, improve the reliability and performance of compressor.
Under normal circumstances, have between the diameter of center oilhole 1 and oil transportation ability compared with Important Relations, the diameter of center oilhole 1 is got over
Greatly, then oil transportation ability is stronger, and the diameter of center oilhole 1 is smaller, then oil transportation ability is poorer；Simultaneously in the diameter one of center oilhole 1
Periodically, the diameter of radial side opening 2 is related to axial distance of the radial side opening 2 at oil inlet, namely the eccentric part with crankshaft
The distance between place end end face h is related, and axial distance of the radial side opening 2 apart from oil inlet is remoter, then oil transportation is more difficult, therefore
If guaranteeing sufficient output oil amount, it is necessary to increase the diameter of radial side opening 2.Pass through the diameter in specific center oilhole 1
The reasonable radial diameter of side opening 2 and the ratio of distance are set under range, it can be ensured that the lubrication effect of part when compressor operating
Fruit is optimal, it is minimum both to have ensure that mutual fretting wear, while reducing hydraulic generation.
Preferably, center oilhole 1 is axially in stepped pore distribution, and along end end face where the eccentric part far from crankshaft
Direction aperture be incremented by so that center oilhole 1 is gradually increased along far from the direction oil inlet ability of oil inlet end, reduce
The problem of 1 oil transportation ability difference of center oilhole caused by distance increases between center oilhole 1 and oil inlet end improves center oilhole 1
In the oil transportation ability far from oil inlet end.
In one embodiment of the utility model, crankshaft includes long axis 8, short axle 3 and is connected to long axis 8 and short axle 3
Between the first eccentric part 5, radial side opening 2 is located on the first eccentric part 5.In the present embodiment, main friction of motion is located at
Between first eccentric part 5 and the first cylinder inner wall and between upper and lower flange inner wall and major and minor axis, therefore can be by first
The mode that radial side opening 2 is arranged on eccentric part 5 guarantees output oil amount, while can also pass through the radial side opening 2 at the first eccentric part 5
Kinematic pair between upper lower flange and major and minor axis is lubricated.It is of course also possible to which center oil is set on major and minor axis respectively
The radial side opening 2 that hole 1 is connected to carries out oil transportation.
In second embodiment of the utility model, crankshaft includes along axial sequentially connected short axle 3, the first connecting shaft
4, the first eccentric part 5 and long axis 8, radial side opening 2 are located in the first connecting shaft 4 and the first eccentric part 5.In the present embodiment, exist
The first connecting shaft 4 is increased between short axle 3 and the first eccentric part 5, first bearing 9 is arranged in the first connecting shaft 4, and crankshaft is logical
It crosses the first bearing 9 to be mounted on lower flange, the pivoting friction of crankshaft can be further decreased by first bearing 9, reduction rubs
It wears consumption, improves the work efficiency of compressor.
In the third embodiment of the utility model, crankshaft includes along axial sequentially connected short axle 3, the first connecting shaft
4, the first eccentric part 5, the second eccentric part 6 and long axis 8, it is inclined that radial side opening 2 is located at the first connecting shaft 4, the first eccentric part 5 and second
In center portion 6.In the present embodiment, it is arranged with first bearing 9 in the first connecting shaft 4, passes through the radial side in the first connecting shaft 4
Hole 2 carries out fuel feeding to the kinematic pair of first bearing 9 and lower flange and short axle 3, passes through the radial side opening 2 on the first eccentric part 5
Oil transportation lubrication is carried out to the kinematic pair between the first eccentric part 5 and the first cylinder, passes through the radial side opening 2 on the second eccentric part 6
Oil transportation lubrication is carried out to the kinematic pair between the kinematic pair and upper flange and long axis 8 between the second eccentric part 6 and the second cylinder.
In the 4th embodiment of the utility model, crankshaft includes along axial sequentially connected short axle 3, the first eccentric part
5, the second eccentric part 6, the second connecting shaft 7 and long axis 8, radial side opening 2 are located on the second eccentric part 6 and the second connecting shaft 7.At this
In embodiment, second bearing 10 is arranged in the second connecting shaft 7, crankshaft is mounted on upper flange by the second bearing 10,
The pivoting friction of crankshaft can be further decreased by second bearing 10, reduced frictional dissipation, improved the work efficiency of compressor.
In the 5th embodiment of the utility model, crankshaft includes along axial sequentially connected short axle 3, the first connecting shaft
4, the first eccentric part 5, the second eccentric part 6, the second connecting shaft 7 and long axis 8, radial side opening 2 are located at the first connecting shaft 4, first partially
In center portion 5, the second eccentric part 6 and the second connecting shaft 7.
Preferably, the corresponding center oilhole diameter of the first connecting shaft 4 is a1, and the corresponding radial side opening of the first connecting shaft 4 is straight
Diameter is r1, the distance between end end face where the central axis of the corresponding radial side opening of the first connecting shaft 4 and the eccentric part of crankshaft
For h1, c1=r1/h1, wherein a1 and c1 meets: 4mm≤a1≤7mm, 0.07≤c1≤0.13.
Preferably, the corresponding center oilhole diameter of the first eccentric part 5 is a2, and the corresponding radial side opening of the first eccentric part 5 is straight
Diameter is r2, the distance between end end face where the central axis of the corresponding radial side opening of the first eccentric part 5 and the eccentric part of crankshaft
For h2, c2=r2/h2, wherein a2 and c2 meets:
4mm≤a2≤7mm, 0.07≤c2≤0.13；Or,
7mm≤a2≤10mm, and 0.05≤c2≤0.11.
Preferably, the corresponding center oilhole diameter of the second eccentric part 6 is a3, and the corresponding radial side opening of the second eccentric part 6 is straight
Diameter is r3, the distance between end end face where the central axis of the corresponding radial side opening of the second eccentric part 6 and the eccentric part of crankshaft
For h3, c3=r3/h3, wherein a3 and c3 meets:
7mm≤a3≤10mm, and 0.05≤c3≤0.11；Or,
10mm≤a3≤13mm, and 0.04≤c3≤0.1.
Preferably, the corresponding center oilhole diameter of the second connecting shaft 7 is a4, and the corresponding radial side opening of the second connecting shaft 7 is straight
Diameter is r4, the distance between end end face where the central axis of the corresponding radial side opening of the second connecting shaft 7 and the eccentric part of crankshaft
For h4, c4=r4/h4, wherein a4 and c4 meets: 10mm≤a4≤13mm, and 0.04≤c4≤0.1.
In the various embodiments described above, a1 < a2 < a3 < a4, so as to make the oil transportation ability of center oilhole 1 along away from
Increase with a distance from oil inlet end and constantly enhance, improve the oil transportation ability of 1 pair of center oilhole radial side opening 2, and then improve radial
The oil transportation ability of side opening 2.
In above-mentioned several embodiments, according to the difference of 1 present position of center oilhole, different center oilholes has been selected
1 diameter is designed center oilhole 1 according to variable diameters, so as to according between radial side opening 2 and oil inlet end
Distance rationally design the diameter of center oilhole 1 and the diameter of radial side opening 2, reduce between radial side opening 2 and oil inlet end
Influence of the distance for the oil transportation ability of radial side opening 2 guarantees the oil transportation ability of radial side opening 2 at various locations, is effectively improved
The lubricant effect of each component improves the reliability and performance of compressor.
In the 6th embodiment of the utility model, crankshaft includes along axial sequentially connected short axle 3, the first eccentric part
5, the second eccentric part 6 and long axis 8, radial side opening 2 are located on the first eccentric part 5 and the second eccentric part 6.
In the various embodiments described above, when the setting parameter of radial side opening 2 can satisfy the restriction requirement of the utility model
When, radial side opening 2 can also be arranged in short axle 3 and long axis 8, to realize short axle by the radial side opening 2 in short axle 3
The lubrication oil supply of kinematic pair between 3 and lower flange inner wall realizes long axis 8 and upper method by the radial side opening 2 on long axis 8
The lubrication oil supply of kinematic pair between blue inner wall.
Preferably, the minimum of the distance between the central axis of center oilhole 1 of the first eccentric part 5 is arranged in radial side opening 2
Side wall on, can shorten the fuel supply path length of the first eccentric part 5, improve fuel feeding efficiency, reduce fuel feeding difficulty.
Preferably, the minimum of the distance between the central axis of center oilhole 1 of the second eccentric part 6 is arranged in radial side opening 2
Side wall on, can shorten the fuel supply path length of the second eccentric part 6, improve fuel feeding efficiency, reduce fuel feeding difficulty.
First bearing 9 is arranged with outside first connecting shaft 4.
Second bearing 10 is arranged with outside second connecting shaft 7.
In conjunction with referring to figs. 1 to 5, embodiment according to the present utility model, rotor-type compressor include pump assembly,
Driving assembly 12, shell 11, dispenser and upper and lower covers, wherein pump assembly includes above-mentioned crankshaft, when rotor-type compressor is
When single-stage compressor, pump assembly further includes the first cylinder, upper flange and lower flange, and crankshaft is threaded through the first cylinder, upper flange
In lower flange.When rotor-type compressor is double-stage compressor, pump assembly further includes the first cylinder, the second cylinder, upper method
Blue and lower flange, crankshaft are threaded through in the first cylinder, the second cylinder, upper flange and lower flange.
When work, crankshaft does high speed rotary motion under the drive of driving assembly, therefore between the kinematic pair in compressor
Phase mutual friction is very violent, and the lubrication of kinematic pair is particularly significant, and suitable lubrication can reduce the mutual abrasion between kinematic pair and band
Heat is walked, the reliability and performance of compressor can be substantially improved.It is fuel sucking pipe by compressor pumping intracorporal lubrication major way
Refrigeration oil in the oil sump of bottom is transported at each part after drawing by oil guide piece, and the radial side opening 2 of crankshaft can be by refrigeration oil band
To the most violent position that rubs, the lubrication between kinematic pair ensure that.
In conjunction with shown in Figure 1, when center oilhole 1 is using isometrical design, then a1=a2=a3=a4, a value one at this time
It is fixed, due to the difference of radial side opening 2 setting position, it will lead to difference there are many value meetings of c, it can be seen from the figure that in this reality
It applies in example, setting is there are four radial side opening 2 altogether, when mono- timing of a,
C1=r1/h1, c2=r2/h2, c3=r3/h3, c4=r4/h4, the setting of this four radial side openings 2 with satisfaction
Above-mentioned restriction, namely as 4mm≤a≤7mm, c1, c2, c3 and c4 are respectively positioned in 0.07~0.13 range, when 7mm≤a≤
When 10mm, c1, c2, c3 and c4 are respectively positioned in 0.05~0.11 range, as 10mm≤a≤13mm, the equal position c1, c2, c3 and c4
In in 0.04~0.10 range.Under conditions of meeting above-mentioned limitation, can the value reasonably to r1, r2, r3 and r4 set
Meter, to improve the oil transportation ability of radial side opening 2 in a certain range.
Centrifugal force Fa when the power Fn of pump oil is rotated mainly from side opening inside and outside differential pressure Fv and crankshaft, radial side opening 2
How much pump oil amount is determined by the diameter, distance center oilhole distance and crankshaft center oilhole diameter of radial side opening.Distance
Pump oil power Fn needed for bigger, radial 2 diameter of side opening more hour is bigger.In conjunction with ginseng as shown in figs. 3 to 5, at identical center
Under oilhole diameter, the curve relation figure between compressor frictional dissipation and ratio c all has one and first reduces becoming of increasing afterwards
There are optimal values between gesture namely the mutual friction power loss of moving component and lubricant effect.By the study found that when 4≤a1≤7
When, compressor frictional dissipation is smaller in the case where 0.07≤c1≤0.13 while lubricant effect is preferable；As 7≤a2≤10,
Compressor frictional dissipation is smaller in the case where 0.05≤c2≤0.11 while lubricant effect is preferable；As 10≤a3≤13,
Compressor frictional dissipation is smaller in the case where 0.04≤c3≤0.1 while lubricant effect is preferable.
It is monitored by spitting oil cut rate to refrigeration oil in compressor operational process, crankshaft center oilhole and side opening design meet
When the above-mentioned restriction of the utility model, compressor spits the case where oil cut rate is lower, and no a large amount of refrigeration oils are discharged with refrigerant, that is, reduces
The hydraulic generation of compressor, compressor refrigerating capacity, lubrication are preferable.
Those skilled in the art will readily recognize that above-mentioned each advantageous manner can be free under the premise of not conflicting
Ground combination, superposition.
The above is only the preferred embodiments of the present utility model only, is not intended to limit the utility model, all practical at this
Made any modifications, equivalent replacements, and improvements etc., should be included in the guarantor of the utility model within novel spirit and principle
Within the scope of shield.Above are merely preferred embodiments of the utility model, it is noted that for the ordinary skill of the art
For personnel, without deviating from the technical principle of the utility model, several improvements and modifications can also be made, these improvement
It also should be regarded as the protection scope of the utility model with modification.
Claims (11)
1. a kind of crankshaft, which is characterized in that center oilhole (1) and radial side opening (2) including connection, the center oilhole (1)
Diameter be a, it is described radial direction side opening (2) diameter be r, it is described radial direction side opening (2) central axis and the crankshaft bias
The distance between end end face where portion is h, and the relationship between the center oilhole (1) and the radial side opening (2) meets:
4mm≤a≤7mm, and 0.07≤c≤0.13；Or,
7mm≤a≤10mm, and 0.05≤c≤0.11；Or,
10mm≤a≤13mm, and 0.04≤c≤0.1；
Wherein c=r/h.
2. crankshaft according to claim 1, which is characterized in that the crankshaft include along axial sequentially connected short axle (3),
First connecting shaft (4), the first eccentric part (5), the second eccentric part (6), the second connecting shaft (7) and long axis (8), the radial direction side opening
(2) it is located at first connecting shaft (4), first eccentric part (5), second eccentric part (6) and second connecting shaft
(7) on.
3. crankshaft according to claim 2, which is characterized in that the corresponding center oilhole diameter of first connecting shaft (4)
For a1, the corresponding radial side bore dia of first connecting shaft (4) is r1, the corresponding radial side opening of first connecting shaft (4)
Central axis and the crankshaft eccentric part where the distance between end end face be h1, c1=r1/h1, wherein a1 and c1 is full
Foot: 4mm≤a1≤7mm, 0.07≤c1≤0.13.
4. crankshaft according to claim 2, which is characterized in that the corresponding center oilhole diameter of first eccentric part (5)
For a2, the corresponding radial side bore dia of first eccentric part (5) is r2, the corresponding radial side opening of first eccentric part (5)
Central axis and the crankshaft eccentric part where the distance between end end face be h2, c2=r2/h2, wherein a2 and c2 is full
Foot:
4mm≤a2≤7mm, 0.07≤c2≤0.13；Or,
7mm≤a2≤10mm, and 0.05≤c2≤0.11.
5. crankshaft according to claim 2, which is characterized in that the corresponding center oilhole diameter of second eccentric part (6)
For a3, the corresponding radial side bore dia of second eccentric part (6) is r3, the corresponding radial side opening of second eccentric part (6)
Central axis and the crankshaft eccentric part where the distance between end end face be h3, c3=r3/h3, wherein a3 and c3 is full
Foot:
7mm≤a3≤10mm, and 0.05≤c3≤0.11；Or,
10mm≤a3≤13mm, and 0.04≤c3≤0.1.
6. crankshaft according to claim 2, which is characterized in that the corresponding center oilhole diameter of second connecting shaft (7)
For a4, the corresponding radial side bore dia of second connecting shaft (7) is r4, the corresponding radial side opening of second connecting shaft (7)
Central axis and the crankshaft eccentric part where the distance between end end face be h4, c4=r4/h4, wherein a4 and c4 is full
Foot: 10mm≤a4≤13mm, and 0.04≤c4≤0.1.
7. crankshaft according to claim 1, which is characterized in that the crankshaft include along axial sequentially connected short axle (3),
First eccentric part (5), the second eccentric part (6) and long axis (8), the radial direction side opening (2) are located at first eccentric part (5) and institute
It states on the second eccentric part (6).
8. the crankshaft according to any one of claim 2 to 7, which is characterized in that the radial direction side opening (2) is arranged described
First eccentric part (5) between the central axis of the center oilhole (1) on the smallest side wall of distance.
9. the crankshaft according to any one of claim 2 to 7, which is characterized in that the radial direction side opening (2) is arranged described
Second eccentric part (6) between the central axis of the center oilhole (1) on the smallest side wall of distance.
10. crankshaft according to any one of claim 1 to 7, which is characterized in that the center oilhole (1) is axially
It is incremented by stepped pore distribution, and along the direction aperture of end end face where the eccentric part far from the crankshaft.
11. a kind of rotor-type compressor, including crankshaft, which is characterized in that the crankshaft is any one of claims 1 to 10 institute
The crankshaft stated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201822083712.0U CN209458123U (en) | 2018-12-12 | 2018-12-12 | Crankshaft and rotor-type compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201822083712.0U CN209458123U (en) | 2018-12-12 | 2018-12-12 | Crankshaft and rotor-type compressor |
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| CN209458123U true CN209458123U (en) | 2019-10-01 |
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ID=68040369
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109441825A (en) * | 2018-12-12 | 2019-03-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft and rotor-type compressor |
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2018
- 2018-12-12 CN CN201822083712.0U patent/CN209458123U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109441825A (en) * | 2018-12-12 | 2019-03-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Crankshaft and rotor-type compressor |
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