CN205172942U - Rotary compressor - Google Patents
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- CN205172942U CN205172942U CN201520907477.8U CN201520907477U CN205172942U CN 205172942 U CN205172942 U CN 205172942U CN 201520907477 U CN201520907477 U CN 201520907477U CN 205172942 U CN205172942 U CN 205172942U
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Abstract
The utility model provides a can make under the circumstances of the reliability of keeping the sintering that does not produce the bearing compressor the discharge capacity increase, or keeping making the efficiency of compressor improve under the circumstances of the same discharge capacity, can realize the rotary compressor of high outputization, high efficiency. This rotary compressor possesses: the motor, this motor has the rotor, the bent axle, this bent axle is rotatory with the help of the rotor, and compressing mechanism portion, this compressing mechanism portion is driven by the bent axle, and the bent axle has a countershaft that the main shaft that is fixed in the rotor and axial at the main shaft set up, and is formed with the fuel feeding hole that the fuel feeding was used in that the axle is inside, is establishing vice outside diameter of shaft the D into phi, when establishing the diameter in fuel feeding hole into phi d, makes phi d phi D be below 0.7.
Description
Technical field
The utility model relates to rotary compressor that use in the refrigeration cycle of the refrigerating air conditioning device such as air conditioner or refrigerator, that carry out the compression of refrigerant gas.
Background technique
When assemble compressible machine, in order to piston is chimeric with eccentric part, need to make to deduct the offset of eccentric part and the value that obtains is identical or larger than the radius of main shaft or countershaft with the radius of main shaft or countershaft from the radius of eccentric part.When supposing that the value that obtains when deducting the offset of eccentric part from the radius of eccentric part is less than the radius of main shaft or countershaft, when making main shaft or countershaft, through this piston, piston be embedded eccentric part, the external diameter of eccentric part and the interior path interferometer of piston and cannot embed.
If expand the ability of compressor and for expanding discharge capacity, then to need to reduce the external diameter of piston, increase offset.But, there is following problem: as mentioned above, due to restriction when piston embeds towards eccentric part, offset cannot be increased to and make to deduct the offset of eccentric part and the value that the obtains degree less than the radius of main shaft or countershaft from the radius of eccentric part.
In order to solve this problem, disclosed following rotary compressor: make the external diameter of the countershaft of bent axle be less than the external diameter of main shaft in the past, and made to deduct the offset of eccentric part and the value that obtains is identical with the radius of countershaft or larger than the radius of countershaft (such as with reference to patent documentation 1) from the radius of eccentric part.
Patent documentation 1: Japanese Unexamined Patent Publication 2011-127430 publication
But, in the rotary compressor described in above-mentioned patent documentation 1, expand discharge capacity and namely reduce piston external diameter, increase the offset of eccentric part time, do not consider and be arranged at bent axle inside oil supply hole between relation, this oil supply hole is to the structure needed for the compression mechanical part fuel feeding formed by bent axle, main bearing, supplementary bearing, cylinder body, piston, blade etc.
If for increasing discharge capacity, if make the offset of eccentric part expand, then described above due to restriction during built-up piston, the external diameter of countershaft also needs to reduce correspondingly.If reduce the external diameter of the countershaft in inside with oil supply hole, then there are following misgivings: the rigidity of countershaft reduces, the deflection of countershaft is caused to increase because of the gas load when pressing chamber compression refrigerant gas, the lubrication state of bearing worsens, axle and bearing sinter in compressor operation and the running of compressor stops, and cannot restart.
And, in order to improve the efficiency of compressor, reduce height of cylinder, the height of the piston that high pressure side and the low voltage side of pressing chamber seal also is reduced, can prevent on high-tension side refrigerant gas from leaking this situation via the gap between piston and inboard wall of cylinder block to low voltage side thus, the deterioration of the efficiency caused because of the weight flow reduction of the refrigerant gas of suction can be improved.But, in order to reduce height of cylinder when keeping same displacement, needing the external diameter reducing piston, increasing the offset of the eccentric part of bent axle.If this and reduce the external diameter of the countershaft in inside with oil supply hole as mentioned above, then there are following misgivings: the rigidity of countershaft reduces, the deflection of countershaft is caused to increase because of the gas load when pressing chamber compression refrigerant gas, the lubrication state of bearing worsens, axle and bearing sinter in compressor operation and the running of compressor stops, and cannot restart.
Model utility content
The utility model completes to solve above-mentioned problem, its object is to provide a kind of following rotary compressor: can the discharge capacity of compressor be made when maintaining and not producing the reliability of the sintering of bearing to increase or when keeping same displacement, the efficiency of compressor be improved, high output, high efficiency can be realized.
Rotary compressor described in technical solutions of the utility model 1 possesses: motor, and this motor has rotor; Bent axle, this bent axle rotates by above-mentioned rotor; And compression mechanical part, this compression mechanical part is by above-mentioned crank-driven, above-mentioned bent axle has the main shaft being fixed in above-mentioned rotor and the countershaft arranged in the axis of above-mentioned main shaft, and the oil supply hole of fuel feeding is formed in axle inside, the external diameter of above-mentioned countershaft is being set to φ D, when the diameter of above-mentioned oil supply hole is set to φ d, φ d/ φ D is made to be less than 0.7.
The feature of the rotary compressor described in technological scheme 2 is, in the rotary compressor described in technique scheme 1, makes the diameter of above-mentioned oil supply hole be more than 8mm.
The feature of the rotary compressor described in technological scheme 3 is, in the rotary compressor described in technique scheme 1 or 2, the external diameter of above-mentioned countershaft is less than the external diameter of above-mentioned main shaft.
The feature of the rotary compressor described in technological scheme 4 is, in the rotary compressor described in technique scheme 3, above-mentioned bent axle has the eccentric part be formed between above-mentioned main shaft and above-mentioned countershaft, compression mechanism portion possesses piston chimeric with the above-mentioned eccentric part of above-mentioned bent axle sliding freely, and is formed as making the above-mentioned countershaft of above-mentioned bent axle pass and above-mentioned piston be embedded the structure of above-mentioned eccentric part.
The feature of the rotary compressor described in technological scheme 5 is, in the rotary compressor described in technique scheme 1 or 2, above-mentioned bent axle has the eccentric part be formed between above-mentioned main shaft and above-mentioned countershaft, compression mechanism portion possesses: piston, and this piston is chimeric with the above-mentioned eccentric part of above-mentioned bent axle sliding freely; And blade, this blade and above-mentioned piston form as one.
The feature of the rotary compressor described in technological scheme 6 is, in the rotary compressor described in technique scheme 1 or 2, the longitudinal modulus of elasticity of above-mentioned bent axle is 15000 ~ 22000N/mm
2.
Rotary compressor involved by the utility model, the external diameter of countershaft is being set to φ D, when the diameter of oil supply hole is set to φ d, φ d/ φ D is made to be less than 0.7, therefore the rigidity of countershaft improves, the deflection of the countershaft caused because of the gas load when pressing chamber compression refrigerant gas reduces, and the lubrication state of bearing can not worsen, and axle and bearing can not sinter in compressor operation.Therefore, it is possible to make the discharge capacity of compressor increase or make the efficiency of compressor improve when keeping same displacement when maintaining and not producing the reliability of the sintering of bearing, high output, high efficiency can be realized.
Accompanying drawing explanation
Fig. 1 is the Sketch figure of the rotary compressor illustrated involved by mode of execution 1 of the present utility model.
Fig. 2 is the side view of the bent axle illustrated involved by mode of execution 1 of the present utility model.
Fig. 3 is the φ d/ φ D of the rotary compressor illustrated involved by mode of execution 1 of the present utility model and the figure of possibility reaching sintering.
Fig. 4 is the oil supply hole of bent axle inside in the countershaft of the bent axle illustrated involved by mode of execution 1 of the present utility model and the sectional view of the pasta situation in running.
Fig. 5 is the refrigerant circuit figure applying an example of the refrigerating circulatory device of rotary compressor illustrated involved by mode of execution 2 of the present utility model.
Description of reference numerals:
1: seal container; 2: motor; 2a: stator; 2b: rotor; 3: compression mechanical part; 4: bent axle; 4a: main shaft; 4b: countershaft; 4c: eccentric part; 4d: oil supply hole; 5: main bearing; 5a: bearing portion; 5b: end plate; 6: supplementary bearing; 6a: bearing portion; 6b: end plate; 7: cylinder body; 8: rotary-piston; 9: blade; 10: suck connecting pipe; 11: discharge tube; 12: accumulator; 13: refrigerating machine oil; 50: pasta; 100: rotary compressor; 200: refrigerating circulatory device; 201: condenser; 202: expansion valve; 203: vaporizer.
Embodiment
Below, mode of execution of the present utility model is described.In addition, the mode of accompanying drawing is an example, does not limit the utility model.In addition, the part marking identical reference character in the various figures represents identical or suitable part, and this is all identical in the full text of specification.Further, in figures in the following, the magnitude relationship of each component parts is sometimes different from actual conditions.
Mode of execution 1.
Fig. 1 is the Sketch figure of the rotary compressor 100 illustrated involved by mode of execution 1 of the present utility model.
In mode of execution 1, as rotary compressor 100, as an example, vertical rotary closed type motor compressor is shown.Rotary compressor 100 uses in the refrigeration cycle of air conditioner etc.
As shown in Figure 1, the compression mechanical part 3 compressed refrigeration agent is configured at bottom by rotary compressor 100 in the seal container 1 of higb pressure atmosphere, and the motor driven compression mechanical part 3 (motor part) 2 is configured at top.Motor 2 has stator 2a and rotor 2b, and is configured to the running shaft that makes to be fixed on rotor 2b and bent axle 4 rotates, and utilizes bent axle 4 to drive compression mechanical part 3.
Bent axle 4 has: main shaft 4a, and this main shaft 4a is fixed in the rotor 2b of motor 2; Countershaft 4b, this countershaft 4b are arranged in the axis of main shaft 4a; And eccentric part 4c, this eccentric part 4c is formed between main shaft 4a and countershaft 4b.Oil supply hole 4d is formed in the inside of bent axle 4.The refrigerating machine oil 13 of bottom in seal container 1 is stored in oil supply hole 4d supply.
The pressing chamber (not shown) of compression mechanical part 3 is clamped by the bearing of the bearing and main bearing 5 and downside end face that utilize the upside end face of cylinder body 7 and supplementary bearing 6 and is arranged at rotary-piston 8 in cylinder body 7 with blade 9 and closes and formed.Cylinder body 7 has cylindric inner space, and be configured with rotary-piston 8 in this inner space, this rotary-piston 8 is rotatably chimeric with the eccentric part 4c of bent axle 4, and cylinder body 7 is fixed in the inner peripheral portion of seal container 1.
Main bearing 5 has bearing portion 5a and end plate 5b, and the main shaft 4a of bearing portion 5a to bent axle 4 carries out axle supporting, the end face of end plate 5b closed cylinder 7.The bearing portion 5a of main bearing 5 is chimeric with the main shaft 4a of the mode with bent axle 4 with the gap for sliding, and rotatably carries out axle supporting to main shaft 4a.
Supplementary bearing 6 has bearing portion 6a and end plate 6b, and the countershaft 4b of bearing portion 6a to bent axle 4 carries out axle supporting, the end face of the opposition side of end plate 6b closed cylinder 7.The bearing portion 6a of supplementary bearing 6 is chimeric with the countershaft 4b of the mode with bent axle 4 with the gap for sliding, and rotatably carries out axle supporting to countershaft 4b.
In cylinder body 7, be accommodated with the eccentric part 4c being arranged at bent axle 4, rotary-piston 8 is the mode of rotation can be assemblied in eccentric part 4c.The mode that blade 9 is connected to rotary-piston 8 by former side pressures such as springs (not shown) is arranged, and will be divided into suction chamber (not shown) and pressing chamber in compression mechanical part 3.
And then utilize motor 2 to make bent axle 4 rotate, eccentric part 4c is eccentric rotary in cylinder body 7, repeatedly carry out the suction compression of refrigerant gas.In compression stroke, along with the rotation of rotary-piston 8, the volume of pressing chamber reduces gradually, and thus, the refrigerant gas being sucked into the low pressure of the suction chamber of compression mechanical part 3 is compressed, and becomes higher pressure refrigerant gas.
Here, accumulator 12 is provided with adjacently with seal container 1.Suck connecting pipe 10 cylinder body 7 and accumulator 12 are linked.
Seal container 1 is discharged to by the refrigerant gas after rotary-piston 8 and blade 9 compress, and sent from discharge tube 11 by the refrigeration cycle towards refrigerating air conditioning device, wherein, by the rotation of bent axle 4, the eccentric part 4c of the bent axle 4 of eccentric rotary is chimeric with in cylinder body 7 for rotary-piston 8.
Fig. 2 is the side view of the bent axle 4 illustrated involved by mode of execution 1 of the present utility model.
Bent axle 4 has: main shaft 4a, and this main shaft 4a is fixed in the rotor 2b of motor 2; Countershaft 4b, this countershaft 4b is arranged at the opposition side of the axis of main shaft 4a; Eccentric part 4c, this eccentric part 4c is formed between main shaft 4a and countershaft 4b; And oil supply hole 4d, this oil supply hole 4d is formed at the inside of bent axle 4.It is concentrically ringed empty internal that oil supply hole 4d is formed as in the inside of countershaft 4b with countershaft 4b, countershaft 4b to be formed as cylindric.Oil supply hole 4d is at the end face opening of countershaft 4b.
Be set to φ D at the external diameter of the countershaft 4b by bent axle, when the diameter of oil supply hole 4d is set to φ d, makes φ d/ φ D be less than 0.7, and make the diameter of oil supply hole 4d be more than 8mm.
In addition, a just example, the longitudinal modulus of elasticity being formed as the material making bent axle 4 is 15000 ~ 22000N/mm
2.
Owing to forming in the above described manner, therefore, such as, when expanding discharge capacity in the ability in order to increase rotary compressor 100, in existing compressor during assemble compressible machine, in order to piston is chimeric with eccentric part, need to make to deduct the offset of eccentric part and the value that obtains is identical or larger than the radius of main shaft or countershaft with the radius of main shaft or countershaft from the radius of eccentric part.On the other hand, when expanding discharge capacity, need to make to deduct the offset of eccentric part and identical with the external diameter of countershaft or larger than the external diameter of the countershaft restriction of the value that obtain from the radius of eccentric part owing to existing, therefore need the external diameter reducing countershaft, cause the rigidity reduction of bent axle.But, according to mode of execution 1, by making the external diameter φ D of the countershaft 4b of bent axle 4 be less than 0.7 with the ratio φ d/ φ D of the diameter phi d of oil supply hole 4d, the rigidity of bent axle 4 can be improved.
Fig. 3 is the φ d/ φ D of the rotary compressor 100 represented involved by mode of execution 1 of the present utility model and the figure of possibility reaching sintering.
As shown in Figure 3, the value of φ d/ φ D is changed, and is confirmed whether by experiment to reach sintering.When φ d/ φ D is greater than 0.7, think to there is rough surface that become the sign of sintering, that cause because of the wearing and tearing of slip surface.Be the scope of less than 0.7 at φ d/ φ D, although think to there are wearing and tearing, be smooth state of wear, do not reach sintering.
Fig. 4 is the oil supply hole 4d of bent axle 4 inside in the countershaft 4b of the bent axle 4 represented involved by mode of execution 1 of the present utility model and the sectional view of the pasta situation in running.
The oil supply hole 4d being arranged at bent axle 4 inside is formed as centrifugal structure, at inner insert plate, being formed as the pasta shape of inverted parabolic curve shape (concave shape) by making refrigerating machine oil 13 rotate together with the rotation of bent axle 4 in bent axle 4 inside, will stagnating via the fuel supply path being arranged at bent axle 4 and the refrigerating machine oil 13 lodging in rotary compressor 100 inside supplies towards compression mechanical part 3.But, if the diameter of oil supply hole 4d is little, then there are following misgivings: the rotation circumferential speed of refrigerating machine oil 13 is also little, sufficient inverted parabolic curve shape cannot be obtained, pasta cannot be raised to the height of oil supply hole 4d, the lubrication state of main bearing 5 and supplementary bearing 6 worsens, and bent axle 4, main bearing 5 and supplementary bearing 6 sinter in compressor operation, the running of rotary compressor 100 stops, and cannot restart.
As shown in Figure 4, if the internal diameter of oil supply hole 4d is less than 8mm, then not enough with the circular velocity of the refrigerating machine oil 13 of bent axle 4 synchronous rotary, refrigerating machine oil 13 cannot rise to sufficient height, and the fuel feeding towards compression mechanical part 3 is insufficient.But, by making the internal diameter (diameter) of oil supply hole 4d be more than 8mm, sufficient with the circular velocity of the refrigerating machine oil 13 of bent axle 4 synchronous rotary, pasta 50 is formed as the pasta shape of inverted parabolic curve shape (concave shape) in oil supply hole 4d inside and is increased to sufficient height, can carry out the fuel feeding towards compression mechanical part 3 fully.
In above-mentioned mode of execution 1, the situation that rotary-piston 8 and blade 9 are the parts be not integrated each other is illustrated, but next the rotary compressor 100 that rotary-piston 8 and blade 9 form as one is described.
In common running, rotary compressor 100 sucks and the refrigeration agent compressed is gas as compressible fluid, but during running when rotary compressor 100 starts or under low ambient temperature etc., exist from refrigeration cycle side towards rotary compressor 100, suck the situation as the refrigeration agent of the liquid of incompressible fluid towards compressor.
If the refrigeration agent sucked as the liquid of incompressible fluid also compresses, then the pressure of pressing chamber inside rises rapidly, and the main bearing 5 and supplementary bearing 6 be accompanied by this bearing compressive load is also applied with excessive load.
In the rotary compressor 100 that rotary-piston 8 and blade 9 are not integrated each other, during pressure increase in such pressing chamber rapidly, also be applied with pressure at blade 9 and act on from pressing chamber power toward the outer side, blade 9 leaves from rotary-piston 8, the high pressure side producing pressing chamber is communicated with low voltage side thus prevents the action of pressure increase, relax the bearing load for main bearing 5 and supplementary bearing 6, prevent the damage of bearing thus.
But, in the rotary compressor 100 that rotary-piston 8 and blade 9 form as one, the pressure increase rapidly in pressing chamber as above cannot be prevented, excessive load is applied with to bearing, thus the danger reaching damage strengthens.Therefore, effect that describe in mode of execution 1, that by the ratio of the external diameter φ D with the diameter phi d of the oil supply hole 4d of bent axle 4 inside that make the countershaft 4b of bent axle 4 and φ d/ φ D be the rigidity of the raising bent axle 4 that less than 0.7 obtains is more effective when compressing the refrigeration agent as the liquid of incompressible fluid.
In addition, in above-mentioned mode of execution 1, show the situation that main shaft 4a is almost identical with the external diameter of countershaft 4b, but the external diameter φ D of countershaft 4b also can be made thinner than the external diameter of main shaft 4a, make rotary-piston 8 pass through from countershaft 4b side and be assemblied in eccentric part 4c.The length of the axle of countershaft 4b is shorter than main shaft 4a, therefore has the effect that easily rotary-piston 8 can be assemblied in eccentric part 4c.
According to above mode of execution 1, the external diameter of countershaft 4b is being set to φ D, when the diameter of the oil supply hole 4d being arranged at axle inside is set to φ d, φ d/ φ D is made to be less than 0.7, therefore the rigidity of countershaft 4b improves, the deflection of the countershaft 4b caused because of the gas load when pressing chamber compression refrigerant gas reduces, and the lubrication state of main bearing 5 and supplementary bearing 6 can not worsen, and bent axle 4, main bearing 5 and supplementary bearing 6 can not sinter in compressor operation.Therefore, can the discharge capacity of the refrigeration agent of rotary compressor 100 be made when maintaining and not producing the reliability of the sintering of main bearing 5 and supplementary bearing 6 to increase or when keeping same displacement, the efficiency of rotary compressor 100 be improved, high output, high efficiency can be realized.
In addition, be more than 8mm owing to making the diameter of oil supply hole 4d, therefore, except the above-mentioned effect that can not sinter, the diameter of oil supply hole 4d increases, and the rotation circumferential speed of refrigerating machine oil 13 also increases, and can obtain sufficient inverted parabolic curve shape, pasta 50 can be raised to the height of oil supply hole 4d, the lubrication state of main bearing 5 and supplementary bearing 6 becomes good.Therefore, can the discharge capacity of the refrigeration agent of rotary compressor 100 be made when maintaining and not producing the reliability of the sintering of main bearing 5 and supplementary bearing 6 to increase or when keeping same displacement, the efficiency of rotary compressor 100 be improved, high output, high efficiency can be realized.In addition, the fuel feeding of refrigerating machine oil 13 towards compression mechanical part 3 can also be carried out fully.
In addition, the external diameter φ D of countershaft 4b is configured to less than the external diameter of main shaft 4a, therefore, it is possible to easily rotary-piston 8 is assemblied in eccentric part 4c, offset can be increased, thus the discharge capacity of the refrigeration agent of rotary compressor 100 can be increased or improve the efficiency of rotary compressor 100 when keeping same displacement, high output, high efficiency can be realized.
In addition, rotary-piston 8 is embedded eccentric part 4c owing to making the countershaft 4b of bent axle 4 pass, therefore, it is possible to easily rotary-piston 8 is assemblied in eccentric part 4c, offset can be increased, thus the discharge capacity of the refrigeration agent of rotary compressor 100 can be increased or improve the efficiency of rotary compressor 100 when keeping same displacement, high output, high efficiency can be realized.
In addition, if rotary-piston 8 and blade 9 are formed as one, be then that less than the 0.7 above-mentioned effect that can not sinter obtained becomes more effective when compressing the refrigeration agent as the liquid of incompressible fluid by the ratio of the external diameter φ D with the diameter phi d of the oil supply hole 4d of bent axle 4 inside that make the countershaft 4b of bent axle 4 and φ d/ φ D.
In addition, owing to making the longitudinal modulus of elasticity of bent axle 4 be 15000 ~ 22000N/mm
2, therefore, it is possible to prevent the wearing and tearing of main bearing 5 and supplementary bearing 6.
Mode of execution 2.
Fig. 5 is the refrigerant circuit figure of an example of the refrigerating circulatory device 200 applying rotary compressor 100 illustrated involved by mode of execution 2 of the present utility model.
Refrigerating circulatory device 200 shown in Fig. 5 forms the refrigeration cycle utilizing refrigerant piping rotary compressor 100, condenser 201, expansion valve 202 and vaporizer 203 to be formed by connecting.And then the refrigeration agent flowed out from vaporizer 203 is inhaled into rotary compressor 100 and is become High Temperature High Pressure by compressing.The refrigeration agent becoming High Temperature High Pressure becomes liquid in condenser 201 condensation.The refrigeration agent becoming liquid becomes the gas-liquid two-phase state of low-temp low-pressure at expansion valve 202 puffing, the refrigeration agent of gas-liquid two-phase state carries out heat exchange at vaporizer 203.
Rotary compressor 100 can be applied to refrigerating circulatory device 200 as above.
In addition, this time disclosed mode of execution is all example in all respects, and should not be considered to restrictive description.Scope of the present utility model is represented by appended every technological scheme but not is represented by specification, and intention comprises the whole changes in the meaning and scope that are equal to technological scheme.
Claims (6)
1. a rotary compressor, is characterized in that, possesses:
Motor, this motor has rotor;
Bent axle, this bent axle rotates by described rotor; And
Compression mechanical part, this compression mechanical part by described crank-driven,
Described bent axle has the main shaft being fixed in described rotor and the countershaft arranged in the axis of described main shaft, and is formed with the oil supply hole of fuel feeding in axle inside,
The external diameter of described countershaft is being set to φ D, when the diameter of described oil supply hole is set to φ d, is making φ d/ φ D be less than 0.7.
2. rotary compressor according to claim 1, is characterized in that,
The diameter of described oil supply hole is made to be more than 8mm.
3. rotary compressor according to claim 1 and 2, is characterized in that,
The external diameter of described countershaft is less than the external diameter of described main shaft.
4. rotary compressor according to claim 3, is characterized in that,
Described bent axle has the eccentric part be formed between described main shaft and described countershaft,
Described compression mechanical part possesses piston chimeric with the described eccentric part of described bent axle sliding freely, and is formed as making the described countershaft of described bent axle pass and described piston be embedded the structure of described eccentric part.
5. rotary compressor according to claim 1 and 2, is characterized in that,
Described bent axle has the eccentric part be formed between described main shaft and described countershaft,
Described compression mechanical part possesses:
Piston, this piston is chimeric with the described eccentric part of described bent axle sliding freely; And
Blade, this blade and described piston form as one.
6. rotary compressor according to claim 1 and 2, is characterized in that,
The longitudinal modulus of elasticity of described bent axle is 15000 ~ 22000N/mm
2.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015041402A JP2016160856A (en) | 2015-03-03 | 2015-03-03 | Rotary compressor |
| JP2015-041402 | 2015-03-03 | ||
| JPPCT/JP2015/071272 | 2015-07-27 | ||
| PCT/JP2015/071272 WO2016139825A1 (en) | 2015-03-03 | 2015-07-27 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205172942U true CN205172942U (en) | 2016-04-20 |
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| CN201520907477.8U Active CN205172942U (en) | 2015-03-03 | 2015-11-13 | Rotary compressor |
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| CN (1) | CN205172942U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105937493A (en) * | 2015-03-03 | 2016-09-14 | 三菱电机株式会社 | Rotary compressor |
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2015
- 2015-11-13 CN CN201520907477.8U patent/CN205172942U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105937493A (en) * | 2015-03-03 | 2016-09-14 | 三菱电机株式会社 | Rotary compressor |
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