CN1611789A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN1611789A CN1611789A CN 200310106747 CN200310106747A CN1611789A CN 1611789 A CN1611789 A CN 1611789A CN 200310106747 CN200310106747 CN 200310106747 CN 200310106747 A CN200310106747 A CN 200310106747A CN 1611789 A CN1611789 A CN 1611789A
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Abstract
The invention discloses a kind of rotary compressor which comprises the cylinder, the upper bearing, the nether bearing, the crankshaft, the discharge hole and the rotary valve. The cylinder forms the compression chamber and has vane for dividing the compression space and the inspiration space; the crankshaft impenetrate the cylinder, the upper bearing and the nether bearing and has a prejudicial components; more than one discharge hole connect with the bosom of the compression chamber to discharge the constringent secondary refrigerant; the rotary valve is set rotatablely and has at least one inspiration hole to compress the different amount of secondary refrigerant; the thickness of the rotary valve's exterior end is more than the thickness of the interior. The invention has different compression capacity and can adjust the position of each component aimed at various compression capacities correctly. It can adjust the position of each inspiration hole in various compression modes to get stable using effect.
Description
Technical field
The invention relates to compressor, particularly be rotary compressor.Specifically, this rotary compressor has different compression volumes, and can correctly change the position at the various component parts of each compression volume.
Background technique
In general, after compressor is accepted power from the motor equal power device, air or refrigerant or other special gas are compressed, improve the pressure of working fluid thus.Aforesaid compressor in the air conditioner field, general household appliances such as refrigerator field are widely used in factory.
Compressor is divided into displacement type compressor and turbocompressor according to the compress mode to working fluid.
Wherein, the compressor that is widely used in the factory scene is a displacement type compressor, and displacement type compressor increases the pressure of working fluid then by the minimizing to volume.Above-mentioned displacement type compressor is divided into reciprocal compressor and rotary compressor again.
Above-mentioned reciprocal compressor compresses working fluid by do the effect of the piston of straight reciprocating motion at cylinder internal, and reciprocal compressor can access higher compression efficiency with better simply mechanical structure.But this kind compressor has limit owing to the inertia reason of piston on its speed of rotation, and because suitable vibration can take place the inertial force of piston.
Above-mentioned rotary compressor, by do the effect of rolling ring of eccentric revolution motion at cylinder internal, working fluid is compressed, compared with reciprocal compressor, to obtain higher compression efficiency than low rate, so rotary compressor has the less advantage of noise and vibration.
But, even if existing rotary compressor has above-mentioned advantage, but because structural restriction, it rolls ring and can not revolve round the sun to two directions.That is, on existing rotary compressor, each only is formed with a suction port that is connected with cylinder and exhaust port respectively, and rolls ring and do rolling motion on the inner peripheral surface of cylinder from the intakeport to the relief opening, and compression working fluid (for example refrigerant etc.).Thus, when rolling hoop in the other direction (from the relief opening to the intakeport) do rolling motion, then can not compression working fluid.
And existing rotary compressor is because its structural restriction can not change its compression volume.And recently in order to adapt to the various operating conditions of air conditioner etc., the compressor of compression volume has appearred changing in succession.But existing rotary compressor is owing to only having a compression volume, so its Applicable scope has suitable limitation.
Summary of the invention
In order to solve the problem that above-mentioned technology exists, the invention provides a kind of rotary compressor, have different compression volumes, and between each compression volume operation mode mutually during conversion, the rotary compressor that related associated components can correctly be worked.
To achieve these goals, the technical solution used in the present invention is: rotary compressor comprises: cylinder, upper bearing (metal) and lower bearing, bent axle, exhaust port and rotary valve, wherein said cylinder constitutes pressing chamber, and has the blade of dividing compression volume and breathing space; Above-mentioned upper bearing (metal) and lower bearing are separately positioned on the upside and the downside of cylinder, and the seal compression chamber; Above-mentioned bent axle connects cylinder, upper bearing (metal) and lower bearing and is provided with, and has the eccentric part of eccentric rotation; Above-mentioned exhaust port is connected with the inside of pressing chamber, and the refrigerant of compression is discharged, and is at least more than one; Above-mentioned rotary valve rotatably is set up, and in order to compress the refrigerant of the different amount of each pattern, has at least more than one suction port, and the thickness size of its outer ends is less than the thickness size of inside line.
When above-mentioned compressor also includes the displacement distance of restriction rotary valve, can support the standing valve that moves of rotary valve.
The said fixing valve is along the outer periphery setting between cylinder and the lower bearing; Rotary valve is arranged on the inside line between cylinder and the lower bearing.
The integral thickness size of above-mentioned rotary valve is less than the gap size that forms between cylinder and the lower bearing.
Above-mentioned rotary valve is formed slopely from the inside line to the outer ends gradually, and the thickness of outer ends is thinner than the thickness of inside line.
The end of above-mentioned rotary valve forms the garden arc, and the thickness of outer ends is thinner than the thickness of inside line.
When the outer ends of the thickness relative thin of above-mentioned rotary valve is meant that center with rotary valve is as benchmark, from 2/3 position of total length to its periphery.
The thickness of above-mentioned rotary valve, the outer ends position of relative thin are compared with inside line, and its thickness size is approximately less than 2～10 μ m.
The invention has the beneficial effects as follows: have the rotary compressor of the present invention of structure as mentioned above, can selectively obtain different compression volumes according to application target.Because the shape of the rotary valve of the embodiment of the invention in various compression operation patterns, can correctly be changed the position of each suction port, so can access stable using effect.
Description of drawings
Fig. 1 is the exploded perspective view of the press part annexation of rotary compressor of the present invention.
Fig. 2 a to Fig. 2 c is that sectional arrangement drawing amplifies in the portion that wants of high power capacity refrigerant compression process of the present invention.
Fig. 3 is the enlarged view of A part among Fig. 2 a.
Fig. 4 a is the I-I line sectional drawing of Fig. 2 a.
Fig. 4 b is the II-II line sectional drawing of Fig. 2 b.
Fig. 4 c is the III-III line sectional drawing of Fig. 2 c.
Fig. 5 is the valve member of Fig. 4 c state and the working state planimetric map between the lower bearing.
Fig. 6 a to Fig. 6 c is that sectional arrangement drawing amplifies in the portion that wants of low capacity refrigerant compression process of the present invention.
Fig. 7 a is the IV-IV line sectional drawing of Fig. 6 a.
Fig. 7 b is the V-V line sectional drawing of Fig. 6 b.
Fig. 7 c is the VI-VI line sectional drawing of Fig. 6 c.
Fig. 8 is the valve member of Fig. 7 c state and the working state planimetric map between the lower bearing.
Among the figure:
100: cylinder 101: pressing chamber
Through hole 110 in 102: the 1: blade
210: upper bearing (metal) 220: lower bearing
222: the 2 intercommunicating pores of 221: the 1 intercommunicating pores
300: bent axle 310: eccentric part
400: roll ring 500: refrigerant storage portion
620: the 2 exhaust ports of 610: the 1 exhaust ports
720: the 2 suction ports of 710: the 1 suction ports
810: standing valve 811: receiving groove
820: rotary valve 821: protrude platform
Embodiment
Below in conjunction with the drawings and specific embodiments the present invention is described in further detail:
The rotary compressor of various embodiments of the present invention includes in its container (not shown) inside that constitutes outward appearance: cylinder 100; Upper bearing (metal) 210 and lower bearing 220; Bent axle 300; Roll ring 400; Exhaust port; And valve member.
At this, said cylinder 100 constitutes the pressing chamber 101 of compression refrigerant, and side face upper blade 110 has flexibly by the protrusion setting within it.
At this moment, above-mentioned blade 110 contacts with rolling ring 400 outer circumferential face all the time, thus when the internal compression refrigerant of the pressing chamber 101 of cylinder 100, divides the space of compression refrigerant and sucks the space of refrigerant.
Above-mentioned upper bearing (metal) 210 and lower bearing 220 are separately positioned on the upside and the downside of cylinder 100, from outside seal pressing chamber 101, and support bent axle 300 with this.
At this moment, on the face of above-mentioned lower bearing 220, be formed with the 1st intercommunicating pore 221 and the 2nd intercommunicating pore 222 respectively.As shown in the figure, above-mentioned the 1st intercommunicating pore 221 and the 2nd intercommunicating pore 222 are benchmark with the position that is provided with of the blade 110 of 100 li in cylinder, are respectively formed on its left side and the rightward space.
It is to be noted especially, above-mentioned the 1st intercommunicating pore 221 in a side space of blade 110 (leftward space among the figure), be formed on blade 110 position adjacent on; Above-mentioned the 2nd intercommunicating pore 222 is formed on blade 110 and has on the position of random phase difference then in the opposite side space of blade 110 (rightward space among the figure).
At this, the phase difference between above-mentioned blade 110 and each intercommunicating pore 221,222, because of the refrigerant compression ratio of compressor different inequality.
For example, suppose that jumbo compression ratio realizes by the 1st intercommunicating pore 221 the most close with blade 110, this moment, then the phase difference of blade 110 to the 2nd intercommunicating pores 222 was greatly in 180 ° if want to turn round simultaneously with big capacity compression ratio and than 1/2 of big capacity compression ratio big compression ratio; If want to turn round simultaneously with big capacity compression ratio and than 1/2 of big capacity compression ratio little compression ratio, then the phase difference of blade 110 to the 2nd intercommunicating pores 222 is approximately above 180 °.
Has the refrigerant storage portion 500 that is connected with each intercommunicating pore 221,222 in lower bearing 220 bottoms.
In 500 li outsides of storing of above-mentioned refrigerant storage portion, as the refrigerant that flows into by refrigerant pipe 11 from the liquid container (not shown) from compressor.
Above-mentioned refrigerant pipe 11 connects the 2nd through hole 224 that peripheral part of the 1st through hole 102 that forms and perforation lower bearing 220 forms by the bottom surface from the sidewall of cylinder 100 to cylinder 100 and is connected with refrigerant storage portion 500.
Though indicate in the accompanying drawings, above-mentioned refrigerant storage portion 500 can form separately.That is, the refrigerant pipe 11 that flows into refrigerant from liquid container directly is connected with each intercommunicating pore 221,222 of lower bearing 220 or valve member etc. and constitutes.
Above-mentioned bent axle 300 connects cylinder 100, upper bearing (metal) 210 and lower bearing 220 and is provided with, and is formed with the eccentric part 310 in the eccentric rotation in the inside of pressing chamber 101 on its periphery.
Above-mentionedly roll the periphery that ring 400 is installed in eccentric part 310, and the off-centre rotation by eccentric part 310 is with the refrigerant compression of pressing chamber 101 inside.
Above-mentioned exhaust port is connected with the inside of pressing chamber 101, and compressed refrigerant is discharged to the outside of pressing chamber 101 by exhaust port.Exhaust port is being formed with more than one on the inwall of cylinder 100 at least.
In embodiments of the present invention, above-mentioned exhaust port is formed with two, and adjacent to greatest extent with blade 110 respectively in two spaces that are divided by blade 110.
At this moment, in above-mentioned each exhaust port, include: discharge the 1st exhaust port 610 with the refrigerant of small capacity refrigerant compression ratio compression; And the 2nd exhaust port 620 of discharging the refrigerant that compresses with big capacity refrigerant compression ratio.
And, on above-mentioned each exhaust port 610,620, be respectively arranged with open and close valve 611,621.Above-mentioned open and close valve 611,621 has only the pressure when the refrigerant of discharging by exhaust port 610,620 to reach setting value could to open when above.
Above-mentioned valve member is arranged between cylinder 100 and the upper bearing (metal) 210, or is arranged between cylinder 100 and the lower bearing 220, and have for various patterns (for example with the pattern of big capacity compression ratio running; And with the pattern of small capacity compression ratio running etc.) refrigerants of the different amounts of compression and suck the 1st suction port 710 and the 2nd suction port 720 of refrigerant.
Above-mentioned valve member mainly comprises: tabular standing valve 810 and rotary valve 820.
Said fixing valve 810 is fixedly installed on the outside between cylinder 100 and the lower bearing 220, and is formed with the receiving groove 811 of depression on the random position of standing valve 810 inwalls, and above-mentioned receiving groove 811 is limiting the rotary distance of rotary valve 820.
Above-mentioned rotary valve 820 can be rotatably set in the inboard between cylinder 100 and the lower bearing 220, promptly on the inboard of standing valve 810, and protrudes to be formed with on the periphery random position of rotary valve 820 and protrudes platform 821, is arranged at 811 li of the receiving grooves of standing valve 810.
At this moment, above-mentioned the 1st suction port 710 and the 2nd suction port 720 connect the face of rotary valves 820, and the 1st suction port 710 and the 2nd suction port 720 can be communicated with selectively with the 1st intercommunicating pore 221 and the 2nd intercommunicating pore 222 of lower bearing 220.
When compressor during with the running of the operation mode of big capacity compression ratio, the 1st suction port 710 is connected with the 1st intercommunicating pore 221 of lower bearing 220, and the 2nd suction port 720 and the 2nd intercommunicating pore are in mutual closed condition at this moment.
On the contrary, when compressor turned round with small capacity compression ratio operation mode, the 1st suction port 710 and the 1st intercommunicating pore 221 were in mutual closed condition, and the 2nd suction port 720 and the 2nd intercommunicating pore 222 are interconnected.
At this, be formed at the formation position of the receiving groove 811 on the standing valve 810 and form length, in the accompanying drawings, when rotary valve 820 when rotation counterclockwise (with the operation mode running of big capacity compression ratio), can be on the position that is connected with the 1st intercommunicating pore 221 of lower bearing 220 with the 1st suction port 710 of rotary valve 820 and to set; And when rotary valve 820 when clockwise direction rotation (with the operation mode running of small capacity compression ratio), can be on the position that is connected with the 2nd intercommunicating pore 222 of lower bearing 220 with the 2nd suction port 720 of rotary valve 820 and to set.
Certainly,, on the inwall of standing valve 810, form simultaneously and protrude platform, be arranged in the receiving groove though not expression on accompanying drawing also can form receiving groove on the outer circumferential face of rotary valve 820.
The thickness size of rotary valve 820 is littler than the gap size between cylinder and the lower bearing, when rolling ring 400 and do off-centre and rotatablely move, because roll the viscous effect of the machine oil that exists between ring 400 bottom surface and rotary valve 820 top, rotary valve 820 rotates to the sense of rotation of rolling ring 400.
But, if the viscosity ratio rotary valve 820 and the viscosity between the lower bearing 220 of rolling between ring 400 and the rotary valve 820 are little, rotating even if roll ring 400 so, rotary valve 820 can not rotate yet.
Particularly, when processing type, because its planeness is relatively poor, the situation that inside line is thinner than outside left might appear by general when rotary valve 820.
Moreover, if when the planeness at the outer periphery position of rotary valve 820 has the above error of 15 μ m or is attached with foreign substances, the rotation of rotary valve 820 there is very big influence.
Promptly, though the thickness T size of rotary valve 820 is less than the clearance G size between cylinder 100 and the lower bearing 220, in order to prevent the leakage of refrigerant, the size of its clearance G is minimum, so when above, the rotation of its rotary valve 820 can be subjected to considerable influence greater than 15 μ m for the flatness error of rotary valve 820.
And a side of above-mentioned rotary valve 820 is positioned within the space that sucks refrigerant, and its opposite side is positioned within the space of discharging refrigerant, so rotary valve 820 is in heeling condition all the time between the clearance G between cylinder 100 and the lower bearing 220.
Therefore, an end of rotary valve 820 contacts with the bottom surface of cylinder 100, and the other end then with above the lower bearing 220 contacts, and can influence the rotation of rotary valve 820 thus.
As shown in Figure 3, rotary compressor of the present invention, thickness T 1 size of the outer ends of its rotary valve 820 is less than the thickness T size of inside line, and rotary valve 820 is rotated well.
That is, for the flatness error that makes rotary valve 820 outsides less than 15 μ m, the thickness size in its outside should be less than the thickness size of inboard.
The end thickness T1 in rotary valve 820 outsides is thinner than inboard about 2～10 μ m of thickness T, and so-called outer ends refers to: with rotary valve 820 centers is benchmark, from 2/3 position of total length to periphery.
For the method that makes the difference that forms above-mentioned thickness comprises: the end from the inboard of rotary valve 820 to the outside forms gradually with sloping inwardly; Or make the end in the outside form the garden arc.
Above-mentioned rotary valve processing is finished with machine-tooled method or is utilized the handwork method of sand paper to finish.
With reference to Fig. 2 a to Fig. 8 the working procedure of the embodiment of the invention is as mentioned above elaborated.
Rotary compressor of the present invention can be selected the operation mode of high power capacity refrigerant compression, and the operation mode of low capacity refrigerant compression, below respectively the working procedure of each operation mode is explained.
To shown in Figure 5, when rotary compressor during with the operation mode running of high power capacity refrigerant compression, bent axle 300 rotates in the counterclockwise direction as Fig. 2 a.
At this moment, be installed on and roll the state rotation of ring 400 on the eccentric part 310 of bent axle 300 with the center that is eccentric in bent axle 300.
Flow to the sense of rotation of rolling ring 400 by rolling the rotation of ring 400, be present in the bottom surface and the machine oil between the rotary valve 820 that roll ring 400, in this process, because the effect of machine oil viscosity, rotary valve 820 is also along the sense of rotation rotation of rolling ring.
At this moment, even if tilt in the clearance G that rotary valve 820 forms between in the bottom surface of cylinder 100 and above the lower bearing 220, owing to fully taken into account this situation, and the enough unfertile land of the thickness as outside T1 that makes rotary valve 820 forms, so can prevent to be in contact with one another between the bottom surface of the outside left of rotary valve 820 and cylinder 100 or lower bearing 220 top.
As previously mentioned, when rotary valve 820 rotates in the counterclockwise direction, as shown in Figure 5, the 1st suction port 710 that is formed on the rotary valve 820 is on the consistent location with the 1st intercommunicating pore 221 that is formed on the lower bearing 220, and the 1st suction port 710 is communicated in the refrigerant storage portion 500 of lower bearing 220 bottoms thus.
At this moment, be formed at the 2nd suction port 720 on the rotary valve 820 and the 2nd intercommunicating pore 222 that is formed on the lower bearing 220 is in closed condition.
Be stored in the refrigerant of 500 li in refrigerant storage portion, according to flowing into by the inside of the 1st suction port 710 to pressing chamber 101 with pressing chamber 101 pressure inside differences, then roll ring 400 and bent axle 300 and the together eccentric rotation of eccentric part 310, shown in Fig. 4 a and Fig. 4 c, the refrigerant that gradually reduces and flow into.
In this process, shown in Fig. 4 c, the compression of refrigerant finishes fully, and the 2nd exhaust port 620 that is arranged in figure blade 110 right sides is unlocked, and compressed thus refrigerant is discharged to the outside of pressing chamber 101.At this moment, the 1st exhaust port 610 that is positioned at blade 110 left sides continues to keep closed condition.
Above-mentioned a series of working procedure, before the work of compressor stops, or bent axle 300 continued to carry out before reciprocal rotation starts.
If with in the way of the compression operation mode operation of high power capacity refrigerant or under the state that stops, according to user's needs, or other when controlling transitions to the compression operation pattern of low capacity refrigerant, shown in Fig. 6 a to Fig. 6 c, bent axle 300 rotates to clockwise direction.
At this moment, owing to roll the rotation of ring 400, be present in the bottom surface and the machine oil between the rotary valve 820 that roll ring 400 and flow to the sense of rotation of rolling ring 400, in this process, because the effect of the viscosity of machine oil, rotary valve 820 is also to the sense of rotation rotation of rolling ring 400.
Said process is identical with the compression operation pattern of aforesaid high power capacity refrigerant.
In the process of rotary valve 820 rotations, the protrusion platform 821 that is formed at rotary valve 820 peripheries moves with the receiving groove 811 of standing valve 810, when protrusion platform 821 reached the opposite side end (clockwise end) of receiving groove 811, shown in Fig. 6 c, rotary valve 820 stopped the rotation.
As previously mentioned, when rotary valve 820 is rotated in a clockwise direction, as shown in Figure 8, the 2nd suction port 720 that is formed on the rotary valve 820 is on the consistent location with the 2nd intercommunicating pore 222 that is formed on the lower bearing 220, and the 2nd suction port 720 is communicated in the refrigerant storage portion 500 of lower bearing 220 bottoms thus.
At this moment, be formed at the 1st suction port 710 on the rotary valve 820 and the 1st intercommunicating pore 221 that is formed on the lower bearing 220 is in closed condition.
And then the refrigerant that is stored in 500 li in refrigerant storage portion flows into by the inside of the 2nd suction port 720 to pressing chamber 101, and the side of then rolling ring 400 begins through the initial point of the 2nd suction port 720, and the refrigerant that flow into pressing chamber 101 inside is begun compression.
At this moment, roll ring 400 and together rotate with bent axle 300 and eccentric part 310, shown in Fig. 7 a and Fig. 7 b, the refrigerant that gradually reduces and flow into.
In this process, shown in Fig. 7 c, if the compression of refrigerant finishes fully, the 1st exhaust port 610 that then is arranged in drawing blade 110 left sides is unlocked, and compressed thus refrigerant is discharged to the outside of pressing chamber 101.At this moment, the 2nd exhaust port 620 that is positioned at blade 110 right sides continues to keep closed condition.
Above-mentioned a series of working procedure, before the work of compressor stops, or bent axle 300 continued to carry out before reciprocal rotation starts.
In the present invention, be formed at suction port on the rotary valve 820 and differ that to be decided to be among the embodiment equally must be two.
Though do not indicate in the accompanying drawings, also can on rotary valve 820, only form a suction port, in succession as long as suitably adjust the length that is formed at the receiving groove 811 on the standing valve 810, suction port selectively is connected with the 1st intercommunicating pore 221 and the 2nd intercommunicating pore 222 on the lower bearing 220.
Claims (8)
1. rotary compressor is characterized in that rotary compressor comprises: cylinder, upper bearing (metal) and lower bearing, bent axle, exhaust port and rotary valve, and wherein said cylinder constitutes pressing chamber, and has the blade of dividing compression volume and breathing space; Above-mentioned upper bearing (metal) and lower bearing are separately positioned on the upside and the downside of cylinder, and the seal compression chamber; Above-mentioned bent axle connects cylinder, upper bearing (metal) and lower bearing and is provided with, and has the eccentric part of eccentric rotation; Above-mentioned exhaust port is connected with the inside of pressing chamber, and the refrigerant of compression is discharged, and is at least more than one; Above-mentioned rotary valve is set up rotatably, and in order to compress the refrigerant of the different amount of each pattern, has at least more than one suction port, and the thickness size of its outer ends is less than the thickness size of inside line.
2. according to the described rotary compressor of claim 1, it is characterized in that, when above-mentioned compressor also includes the displacement distance of restriction rotary valve, can support the standing valve that moves of rotary valve.
3. according to the described rotary compressor of claim 2, it is characterized in that the said fixing valve is along the outer periphery setting between cylinder and the lower bearing; Rotary valve is arranged on the inside line between cylinder and the lower bearing.
4. according to the described rotary compressor of claim 3, it is characterized in that the integral thickness size of above-mentioned rotary valve is less than the gap size that forms between cylinder and the lower bearing.
5. according to the described rotary compressor of claim 1, it is characterized in that above-mentioned rotary valve is formed slopely from the inside line to the outer ends gradually, the thickness of outer ends is thinner than the thickness of inside line.
6. according to the described rotary compressor of claim 1, it is characterized in that the end of above-mentioned rotary valve forms the garden arc, the thickness of outer ends is thinner than the thickness of inside line.
7. according to the described rotary compressor of claim 1, it is characterized in that, when the outer ends of the thickness relative thin of above-mentioned rotary valve is meant that center with rotary valve is as benchmark, from 2/3 position of total length to its periphery.
8. according to the described rotary compressor of claim 1, it is characterized in that, the thickness of above-mentioned rotary valve, the outer ends position of relative thin is compared with inside line, and its thickness size is approximately less than 2～10 μ m.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200310106747 CN1611789A (en) | 2003-10-30 | 2003-10-30 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200310106747 CN1611789A (en) | 2003-10-30 | 2003-10-30 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1611789A true CN1611789A (en) | 2005-05-04 |
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ID=34757718
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200310106747 Pending CN1611789A (en) | 2003-10-30 | 2003-10-30 | Rotary compressor |
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| Country | Link |
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| CN (1) | CN1611789A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696964A (en) * | 2013-12-09 | 2014-04-02 | 广东美芝精密制造有限公司 | Rotary compressor and slip sheet thereof |
| CN105179239A (en) * | 2015-09-11 | 2015-12-23 | 广东美芝制冷设备有限公司 | Rotary compressor and compression mechanism thereof |
-
2003
- 2003-10-30 CN CN 200310106747 patent/CN1611789A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696964A (en) * | 2013-12-09 | 2014-04-02 | 广东美芝精密制造有限公司 | Rotary compressor and slip sheet thereof |
| CN103696964B (en) * | 2013-12-09 | 2016-02-17 | 广东美芝精密制造有限公司 | Rotary compressor and slide plate thereof |
| CN105179239A (en) * | 2015-09-11 | 2015-12-23 | 广东美芝制冷设备有限公司 | Rotary compressor and compression mechanism thereof |
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