Patent Grant
10641269
This application is the national phase of International Application No. PCT/CN2016/074823, titled “SCROLL COMPRESSOR”, filed on Feb. 9, 2016, which claims the benefit of priorities to Chinese Patent Application No. 201510216987.5 titled “SCROLL COMPRESSOR”, filed with the Chinese State Intellectual Property Office on Apr. 30, 2015, and Chinese Patent Application No. 201520276001.9 titled “SCROLL COMPRESSOR”, filed with the Chinese State Intellectual Property Office on Apr. 30, 2015, the entire disclosures of which are incorporated herein by reference.
The present application relates to a scroll compressor, and more particularly to a scroll compressor having an improvement in terms of appropriate oil supply for its compression mechanism oil supply device.
Compressors (such as scroll compressors) can be used in, for example, cooling (freezing or refrigeration) systems, air conditioning systems and heat pump systems. The scroll compressor includes a compression mechanism for compressing a working fluid (such as a refrigerant), and the compression mechanism in turn includes an orbiting scroll set and a non-orbiting scroll set. When the scroll compressor is in operation, there is a relative movement between the orbiting scroll set and the non-orbiting scroll set of the compression mechanism. In order to reduce abrasion and power consumption, it is necessary to provide lubrication to the compression mechanism (for example, supplying lubricating oil) to mitigate the friction between the orbiting scroll set and the non-orbiting scroll set, and the resulting oil film can also improve the sealability of the compression mechanism, thereby increasing the volumetric efficiency and the like.
In general, an oil circulation rate can be used to represent the amount of lubricating oil carried by the working fluid, and correspondingly, the oil circulation rate can be used to represent the degree of lubricating oil supply to the compression mechanism. Too much or too little supply of lubricating oil will adversely affect the normal operation, the system performance and the like of the compression mechanism itself. For example, an excessively large oil circulation rate will reduce the heat transfer efficiency of the system and will also cause the lubricating oil to accumulate around (especially above) the discharge valve assembly (such as the HVE valve assembly) at a discharge port and a discharge recessed portion of the non-orbiting scroll set, so as to cause certain issues to the scroll compressor (such as the issue of operational stability of the discharge valve assembly and/or the issue of exhaust reliability of the compression mechanism).
In addition, for a system where a variable speed compressor is used (the variable speed compressor needs to operate at different speeds) and/or the system needs to operate under different parameters (especially at different evaporation temperatures), it is desirable to provide a compression mechanism oil supply device with which the oil circulation rate is enabled to be within an appropriate range at different compressor rotational speeds and/or under different system operating parameters.
Further, in the case of a constant speed compressor, it is also desirable to provide a compression mechanism oil supply device with an excellent versatility and applicable to a series of constant speed compressors having different rotational speeds, and the compression mechanism oil supply device can provide oil circulation rates within appropriate ranges for the constant speed compressors at respective different rotational speeds.
Here, it should be noted that the technical contents provided in this section are intended to facilitate the understanding of the present application by the person skilled in the art and do not necessarily constitute the prior art.
A general summary, rather than the full scope or all the features, of the present application is provided in this section.
An object of the present application is to provide a scroll compressor having a compression mechanism oil supply device capable of achieving an oil supply target and concept of taking oil on demand.
Another object of the present application is to provide a scroll compressor having a compression mechanism oil supply device enabling an oil circulation rate to be within an appropriate range at different compressor rotational speeds and/or under different system operating parameters.
Another object of the present application is to provide a scroll compressor having a compression mechanism oil supply device capable of effectively preventing an oil circulation rate from significantly exceeding an upper limit of a desired range at a low evaporation temperature/low compressor rotational speed.
Another object of the present application is to provide a scroll compressor having a compression mechanism oil supply device capable of sufficiently improving the adjustment accuracy and design freedom of the oil circulation rate.
In order to achieve one or more of the above objects, according to the present application, a scroll compressor is provided, which includes: a compression mechanism, a drive mechanism, a suction fitting, and a lubrication system. The compression mechanism is adapted to compress a working fluid and includes an orbiting scroll set, a non-orbiting scroll set and a suction window, and the working fluid can flow into the compression mechanism via the suction window. The drive mechanism includes a drive shaft and is adapted to drive the compression mechanism. Via the suction fitting the working fluid can flow into the scroll compressor and can further flow to the compression mechanism. The lubrication system includes a lubricant source and a compression mechanism oil supply device adapted to supply a lubricant from the lubricant source to the compression mechanism. The compression mechanism oil supply device has an oil supply passage, and an outflow opening of the oil supply passage is located between an opening of the suction fitting and the suction window.
According to the present application, during the operation of the scroll compressor, when the lubricant from the lubricant source is discharged from the opening of the transverse hole, the lubricant discharged meets the suctioned low pressure working fluid, so that the low pressure working fluid can bring a portion of the lubricant into the compression mechanism. In this way, the oil supply target and concept of taking oil on demand (that is, the so-called taking depending on demand) are realized.
Specifically, on the one hand, for example, in the case of a low rotational speed condition, it is possible to increase an oil circulation rate to make it within a desired range as compared with a solution in which an active oil injection mechanism for supplying oil to the compression mechanism is not provided. On the other hand, for example, in the case of a high rotational speed condition, the oil circulation rate will not be excessively increased (basically the oil circulation rate may be only slightly increased) and may be kept within a desired range (for example, this is because at a high rotational speed, the mass of the lubricant expelled out of the orbiting scroll base plate is relatively small at each revolution of the compression mechanism). Thereby, the oil circulation rate can be made within an appropriate range at different compressor rotational speeds and/or under different system operation parameters. In particular, it is possible to effectively prevent the oil circulation rate from significantly exceeding an upper limit of the desired range at a low evaporation temperature/low compressor rotational speed. Therefore, it is possible to avoid an excessively high oil circulation rate which causes the lubricant to accumulate around the discharge valve assembly and brings stability and reliability issues to the scroll compressor.
In addition, according to the present application, a counterbore having a larger inner diameter is provided, an outlet hole is provided and/or a plug having a through hole with a smaller inner diameter is provided, thus, the adjustment accuracy and design freedom of the oil circulation rate can be sufficiently improved, thereby enabling the compression mechanism oil supply device to have a more excellent versatility and applicability.
The features and advantages of one or more embodiments of the present application will become more readily understood from the following description with reference to the accompanying drawings in which:
The present application is described in detail hereinafter by means of exemplary embodiments with reference to the accompanying drawings. The following detailed description of the present application is for illustrative purpose only and is by no means intended to limit the present application and the applications or usages thereof.
First, a structure of a scroll compressor to which a compression mechanism oil supply device according to the present application is applied is briefly described with reference to
As shown in
The scroll compressor 100 may further include a suction fitting 194. In the illustrated example, the scroll compressor 100 may employ a middle air intake design, i.e., the suction fitting 194 is arranged at a position substantially aligning to the main bearing housing 180 in an axial direction of the compressor. Thus, the working fluid with low temperature and low pressure after being evaporated by an evaporator can be suctioned into the scroll compressor 100 via the suction fitting 194 for being compressed.
The scroll compressor 100 may further include a drive mechanism 130. The drive mechanism 130 may include an electric motor 132 and a drive shaft 134. The electric motor 132 may include a stator 137 and a rotor 138. The stator 137 may be fixedly connected to an inner peripheral wall surface of the shell body 112, and the rotor 138 may be fixedly sleeved on the drive shaft 134 to rotate integrally with the drive shaft 134. An eccentric pin 139 may be provided at a top end of the drive shaft 134. Here, it should be understood that other drive mechanisms that do not have an electric motor may also be used.
The scroll compressor 100 may further include a main bearing housing 180. The main bearing housing 180 may be fixedly connected to the inner peripheral wall surface of the shell body 112. For example, the main bearing housing 180 may be fixedly connected to the inner peripheral wall surface of the shell body 112 by means of its multiple circumferentially spaced apart radial projections such that multiple main bearing passageways PG are formed between the main bearing housing 180 and the inner peripheral wall surface of the shell body 112 (i.e., between adjacent radial projections of the main bearing housing 180) for, for example, allowing passage of a low pressure working fluid suctioned into the internal volume IV. The main bearing housing 180 is adapted to support a portion of the drive shaft 134 via a main bearing 182 disposed in the main bearing housing 180.
The scroll compressor 100 may further include a compression mechanism CM adapted to compress a working fluid, such as a refrigerant. The compression mechanism CM may include an orbiting scroll set 150 and a non-orbiting scroll set 160. In some examples, the compression mechanism CM may be embodied as an asymmetric compression mechanism.
The orbiting scroll set 150 may include a base plate 152, a spiral orbiting scroll 154 extending upward from a radial central portion of an upper surface of the base plate 152, and a hub 156 extending downward from a radial central portion of a lower surface of the base plate 152. The orbiting scroll set 150 may be arranged in the main bearing housing 180 and is axially supported by the main bearing housing 180 so that the orbiting scroll set 150 can be orbited. The eccentric pin 139 may be drivingly coupled to (inserted into) the hub 156 (e.g., via an unloading bushing 190 and/or a drive bearing).
The non-orbiting scroll set 160 may include a base plate 162, a spiral non-orbiting scroll 164 extending downward from a lower surface of the base plate 162, a discharge port 166 formed at substantially the center of the base plate 162 and adapted to be in communication with the central high pressure chamber of the compression mechanism CM; and a recessed portion 168 formed at substantially the center of the base plate 162. The recessed portion 168 is located above the discharge port 166 and is adapted to be in communication with the discharge port 166 and the high pressure region HR. A discharge valve assembly (e.g., an HVE valve assembly) 192 may be provided in the recessed portion 168 to control the exhaust of the compression mechanism CM. In the illustrated example, the non-orbiting scroll 164 may include an (annular) outer wall 164a at its radial outermost part, and a compression mechanism suction window SW may be provided in the outer wall 164a at an appropriate circumferential position, the suction window SW allows the low pressure working fluid to be suctioned into the compression mechanism CM.
The non-orbiting scroll 164 is adapted to engage the orbiting scroll 154, thereby defining a series of crescent-shaped working fluid accommodating chambers. These accommodating chambers may include an unsealed suction accommodating chamber SC which is being fed with air and has a low pressure, a sealed compression accommodating chamber which is compressing and has an increased pressure, and a central high pressure chamber which has finished compressing and is exhausting air via the discharge port 166 and the discharge valve assembly 192. The suction accommodating chamber SC is adapted to be in communication with the suction window SW so as to be enabled to receive the low-pressure working fluid suctioned from the suction window SW.
The scroll compressor 100 may further include a lubrication system that is primarily intended to provide lubrication to the respective relatively-moving components of the compressor (such as the compression mechanism CM, the main bearing 182, the eccentric pin 139, the unloading bushing 190, and the drive bearing). The lubrication system may include: an oil sump OR (main lubricant source) as mentioned above; an oil supply passage provided in the drive shaft 134 and including a central hole 135 located in a lower part of the drive shaft and an eccentric hole 136 located in an upper part of the drive shaft; a lubricant storage area (auxiliary lubricant source) for lubricating the eccentric pin 139 and for temporarily storing the lubricant temporarily remained within the main bearing housing 180 after lubricating the lubricating eccentric pin 139, the unloading bushing 190, the drive bearing and/or the main bearing 182; a compression mechanism oil supply device CO (not shown in
In some examples, the lubricant storage area may include a lubricant storage area OA located between a lower surface of the orbiting scroll base plate 152 and top end faces of the eccentric pin 139, the unloading bushing 190 and/or the drive bearing and located in the hub 156.
When the scroll compressor 100 operates, the electric motor 132 is energized to rotate the rotor 138 integrally with the drive shaft 134. At this time, the eccentric pin 139, for example integrally formed with the drive shaft 134, is also rotated to drive the hub 156, for example, via the unloading bushing 190 and/or the drive bearing, whereby the orbiting scroll set 150 is revolved, i.e., orbited with respect to the non-orbiting scroll set 160 by means of, for example, an Oldham 199 (that is, the axis of the orbiting scroll set 150 is revolved with respect to the axis of the non-orbiting scroll set 160, however, the orbiting scroll set 150 and the non-orbiting scroll set 160 are not rotated about their respective axes). At the same time, the low pressure working fluid suctioned from the suction fitting 194 can pass through the main bearing housing 180 along the main bearing housing passages PG and then enter the compression mechanism CM (specifically, entering the suction accommodating chamber SC) via the suction window SW.
Accordingly, the accommodating chambers defined by the non-orbiting scroll 164 and the orbiting scroll 154 are changed from the unsealed suction accommodating chamber SC to the compression accommodating chamber and then to the central high pressure chamber (with the highest pressure) in the process of moving from the radial outer side to the radial inner side, and the volumes thereof gradually become smaller. In this way, the pressure in the accommodating chambers is gradually increased so that the working fluid is compressed and finally discharged from the discharge port 166 to the high pressure region HR and further discharged to the outside of the compressor via a discharge fitting (not shown).
At the same time, for example, the lubricant can be conveyed from the oil sump OR through the oil supply passage (specifically, the central hole 135 and the eccentric hole 136) to the lubricant storage area (such as the lubricant storage area OA) with the effect of the centrifugal force generated due to the rotation of the drive shaft 134. Then, through the compression mechanism oil supply device CO, a part of the lubricant temporarily stored in the lubricant storage area OA is supplied to the compression mechanism CM (for example, supplied to an appropriate area of the suction accommodating chamber SC) so as to provide lubrication to the compression mechanism CM. Then, the remaining lubricant temporarily stored in the lubricant storage area OA returns to the oil sump OR through the oil return passage.
A compression mechanism oil supply device CO′ of the lubrication system according to the related art is described with reference to
Reference is made particularly to
In this way, when the scroll compressor is operated, since the pressure of the lubricant storage area OA is higher than the pressure of the suction accommodating chamber SC (corresponding to the suction pressure), and since the volume of the suction accommodating chamber SC may be gradually increased in the air intake stage so that the pressure is further reduced, the lubricant can be smoothly conveyed to the compression mechanism CM.
In addition, referring to
In addition, referring to Table 1, it can be seen that in the case that an active oil injection mechanism for supplying oil to the compression mechanism is not provided, when the scroll compressor in the system is operated at a low speed of 2400 RPM and the system evaporation temperature/condensation temperature is set to −40/130° F., the oil circulation rate is 0.03% and below a lower limit of the desired range (i.e. 0.05%).
In addition, referring to Table 1, it can be seen that according to the related art, especially when the scroll compressor in the system is operated at a low speed of 2400 RPM, and the system evaporation temperature/condensation temperature is set to −40/130° F. or −20/90° F., the oil circulation rate is much higher than an upper limit of the desired range (i.e. 1%), no matter how these three sizes A, B and C are adjusted. In particular, even in the case that the sizes A and B are both set to be only 1.0 mm, the oil circulation rates are still much higher than the upper limit of the desired range at low evaporation temperature/low compressor rotational speed. Here, it should be understood that the passage having a smaller inner diameter (e.g., less than 1.0 mm) intended to reduce the oil circulation rate is difficult to machine and is substantially impossible to achieve.
Accordingly, the compression mechanism oil supply device CO′ according to the related art can hardly make the oil circulation rate within an appropriate range at different compressor rotational speeds and/or under different system operating parameters. In particular, the oil circulation rate significantly exceeds the upper limit of the desired range at low evaporation temperature/low compressor rotational speed. Thus, for example, an excessively high oil circulation rate may cause the lubricant to be accumulated around the discharge valve assembly 192 so as to cause certain issues to the scroll compressor.
A compression mechanism oil supply device CO of a lubrication system according to a first embodiment of the present application is described with reference to
Reference is particularly made to
The transverse hole 205 may be a hole having a constant inner diameter, and is opened in an outer peripheral surface 152a of the orbiting scroll base plate 152. In some examples, the inner diameter of the transverse hole 205 may be 3.3 mm.
In a preferred example, the opening position of the opening (the position of the outflow opening) of the transverse hole 205 in the outer peripheral surface 152a is disposed to be located in the flow path of the suctioned low pressure working fluid. In particular, the opening position is between the suction fitting 194 and the suction window SW.
In some examples, as shown in
In some examples, in the circumferential direction, the distance of the opening position from the suction fitting 194 is less than the distance of the opening position from the suction window SW, and/or, in the axial direction, the distance of the opening position from the suction fitting 194 is greater than the distance of the opening position from the suction window SW.
In general, the distance of the opening position from the suction fitting 194 may be less than the distance of the opening position from the suction window SW along the flow path of the working fluid. With such arrangement, it is advantageous to realize the oil supply target and concept of taking oil on demand.
In some examples, the opening position is close to or aligning to the suction fitting 194 in the circumferential direction.
In some examples, the opening position of the transverse hole 205 is located on a connecting line connecting the opening of the suction fitting 194 to the suction window SW.
In the illustrated example, the suction fitting 194 is arranged at a position substantially aligning to the main bearing housing 180 in the axial direction. In a preferred example, the suction fitting 194 is arranged to align to the main bearing passage PG. With such arrangement, the introduction of the low pressure working fluid is facilitated and the meeting of the lubricant discharged from the driven scroll base plate 152 with the low pressure working fluid suctioned from the suction fitting 194 is facilitated, thereby facilitating achieving the appropriate oil circulation rate. However, it is contemplated that the suction fitting 194 may also be arranged in other positions (e.g., the so-called bottom air intake design) in the axial direction.
The compression mechanism oil supply device CO of the lubrication system according to the second embodiment of the present application is described with reference to
With reference to
The compression mechanism oil supply device CO of the lubrication system according to the modification of the second embodiment of the present application is described below. In this modification, a plug 207 is provided. The plug 207 is adapted to be connected to the counterbore 205a (e.g., by threaded connection). A through hole 207a may be provided in the plug 207, and the through hole 207a may have an appropriate inner diameter. In some examples, the inner diameter of the through-hole 207a may be less than the inner diameter of the remaining section of the transverse hole 205. In other examples, the inner diameter of the through-hole 207a may be equal to or even greater than the inner diameter of the remaining section of the transverse hole 205.
Accordingly, the compression mechanism oil supply device according to the present application actively causes the lubricant expelled to meet the suctioned low pressure working fluid when the lubricant from the lubricant storage area OA is discharged out of the orbiting scroll base plate 152 from the opening of the transverse hole 205 during the operation of the scroll compressor, so that the low pressure working fluid can bring a portion of the lubricant into the compression mechanism CM. In this way, the oil supply target and concept of taking oil on demand (that is, the so-called taking depending on demand) are realized.
Specifically, on the one hand, for example, in the case of a low rotational speed condition, it is possible to increase the oil circulation rate to make it within a desired range as compared with a solution in which an active oil injection mechanism for supplying oil to the compression mechanism is not provided. On the other hand, for example, in the case of a high rotational speed condition, the oil circulation rate will not be excessively increased (basically the oil circulation rate may be only slightly increased) and may be kept within a desired range (for example, this is because at a high rotational speed, the mass of the lubricant discharged from the orbiting scroll base plate is relatively small at each revolution of the compression mechanism). Thereby, the oil circulation rate can be made within an appropriate range at different compressor rotational speeds and/or under different system operation parameters. In particular, it is possible to effectively prevent the oil circulation rate from significantly exceeding the upper limit of the desired range at a low evaporation temperature/low compressor rotational speed. Therefore, it is possible to avoid an excessive oil circulation rate which causes the lubricant to accumulate around the discharge valve assembly and brings stability and reliability issues to the scroll compressor.
At the same time, the remaining lubricant discharged from the orbiting scroll base plate 152 will fall down to the oil sump OR, and in this process it is also possible to effectively lubricate parts such as the Oldham 199 that require lubrication.
In addition, the compression mechanism oil supply device according to the second embodiment of the present application and the modification thereof: may facilitate reducing the speed at which the lubricant being expelled from the orbiting scroll base plate and improving the mist-like spraying of the lubricant by providing the counterbore; allows the lubricant to be directly conveyed to the suction accommodating chamber SC, i.e., the compression mechanism CM by additionally providing the outlet hole, thereby appropriately improving the oil circulation rate; and may improve the degree of freedom of adjustment of the oil circulation rate by alternatively providing a plug having a through hole.
In summary, by providing a counterbore having a larger inner diameter, by providing an outlet hole and/or by providing a plug having a through hole with a smaller inner diameter, the compression mechanism oil supply device according to the second embodiment of the present application and the modification thereof can sufficiently improve the adjustment accuracy and design freedom of the oil circulation rate, thereby enabling the compression mechanism oil supply device to have a more excellent versatility and applicability.
Referring again to Table 1, it can be seen that for the compression mechanism oil supply device according to the second embodiment of the present application, the oil circulation rates are within a desired range no matter at a low evaporation temperature/low compressor rotational speed or at a high evaporation temperature/high compressor rotational speed. In addition, in the second embodiment, the lubricant discharged from the outlet hole 203 is generally small (particularly in the case where the plug 207 is not provided), and therefore, the experimental results of the oil circulation rates in Table 1 are also applicable to the first embodiment.
The compression mechanism oil supply device according to the present application is particularly suitable for being used in variable speed compressors, particularly in variable speed compressors applied in freezing systems. However, the compression mechanism oil supply device with an excellent versatility according to the present application can also be applied to a series of constant speed compressors having different rotational speeds.
The compression mechanism oil supply device according to the present application can allow for a variety of different variations.
The suction window may be two or more, and/or the outflow opening of the oil supply passage may be two or more. In addition, the suction window may also be formed in a different manner from being disposed on the annular outer wall 164a of the non-orbiting scroll 164 as described above.
The oil supply passage of the compression mechanism oil supply device CO may be formed in other manners. For example,
In summary, in the scroll compressor according to the present application, the following advantageous solutions may be included.
In the scroll compressor according to the present application, the outflow opening is located on a working fluid flow path extending from the opening of the suction fitting to the suction window.
In the scroll compressor according to the present application, the distance of the outflow opening from the opening of the suction fitting is less than the distance of the outflow opening from the suction window along the working fluid flow path.
In the scroll compressor according to the present application, the orbiting scroll set includes an orbiting scroll base plate, and the oil supply passage is formed in the orbiting scroll base plate.
In the scroll compressor according to the present application, the outflow opening is open to an outer peripheral surface of the orbiting scroll base plate.
In the scroll compressor according to the present application, the lubricant source includes a lubricant storage area, and the lubricant storage region is located at and near an end face of an eccentric pin of the drive shaft, and the oil supply passage includes an inlet hole in communication with the lubricant storage area and a transverse hole in communication with the inlet hole and having the outflow opening.
In the scroll compressor according to the present application, the transverse hole includes a counterbore located at its radial outer section, and the counterbore has an inner diameter greater than an inner diameter of the remaining section of the transverse hole.
In the scroll compressor according to the present application, the compression mechanism oil supply device further includes a plug, the plug is adapted to be connected to the counterbore, and a through hole is provided in the plug.
In the scroll compressor according to the present application, the through hole has an inner diameter less than the inner diameter of the remaining section of the transverse hole.
In the scroll compressor according to the present application, the compression mechanism oil supply device further includes an outlet hole in communication with a suction accommodating chamber of the compression mechanism and in communication with the transverse hole.
In the scroll compressor according to the application, the lubrication system further includes an oil supply passage provided in the drive shaft, the lubricant source further includes an oil sump located at the bottom of an internal volume of the scroll compressor, and the lubricant flows from the oil sump to the lubricant storage area via the oil supply passage.
In the scroll compressor according to the present application, the non-orbiting scroll set includes an annular outer wall, and the suction window is provided in the annular outer wall.
In the scroll compressor according to the present application, the scroll compressor further includes a main bearing housing configured to support a part of the drive shaft and support the orbiting scroll set, and the suction fitting is arranged at a position substantially aligning to the main bearing housing in an axial direction of the scroll compressor.
In the scroll compressor according to the present application, the main bearing housing has multiple radial projections spaced apart circumferentially and the main bearing housing is fixedly connected to an inner peripheral wall surface of a shell body of the scroll compressor by means of the radial projections, such that multiple main bearing housing passages are formed between the main bearing housing and the inner peripheral wall surface, and the suction fitting is arranged to align to the main bearing housing passage.
In the scroll compressor according to the present application, the scroll compressor further includes a main bearing housing configured to support a part of the drive shaft and support the orbiting scroll set, and the oil supply passage is formed in a peripheral wall of the main bearing housing and is opened to an outer peripheral surface of the peripheral wall of the main bearing housing.
In the scroll compressor according to the present application, the scroll compressor is a variable speed compressor suitable for being applied in a freezing system.
In this application, use of the locality terms “top”, “bottom”, “upper” and “lower” and the like is for illustrative purpose only and is not to be regarded as limiting.
While the present application has been described with reference to the exemplary embodiments, it is to be understood that the present application is not limited to the specific embodiments described and illustrated in detail herein. The person skilled in the art can make various variants to the exemplary embodiments without departing from the scope defined by the claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2015 1 0216987 | Apr 2015 | CN | national |
| 2015 2 0276001 U | Apr 2015 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2016/074823 | 2/29/2016 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
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| WO2016/173319 | 11/3/2016 | WO | A |
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| Number | Date | Country | |
|---|---|---|---|
| 20180080448 A1 | Mar 2018 | US |
