Patent Grant
11105332
This application is the national phase of International Application No. PCT/CN2016/072757, titled “SCROLL COMPRESSOR”, filed on Jan. 29, 2016, which claims the benefit of priorities to Chinese Patent Application No. 201510058036.X titled “SCROLL COMPRESSOR”, filed with the Chinese State Intellectual Property Office on Feb. 4, 2015, and Chinese Patent Application No. 201520079596.9 titled “SCROLL COMPRESSOR”, filed with the Chinese State Intellectual Property Office on Feb. 4, 2015, the entire disclosures of which are incorporated herein by reference.
The present application relates to a scroll compressor.
The contents of this section only provide background information related to this disclosure, which may not constitute the prior art.
It is known that in a scroll compressor having an axial flexibility, a back pressure chamber is provided on an orbiting scroll member side so as to provide the orbiting scroll member with a back pressure which enables the orbiting scroll member to be axially engaged with a non-orbiting scroll member. However, with this design, in unfavorable operating conditions such as liquid strike, there is a possibility that the back pressure is reduced such that the orbiting scroll member and the non-orbiting scroll member cannot be axially engaged, which causes the compressor to fail to work normally and reduces reliability of operation of the compressor, and further causes a waste of power consumption.
As shown in
The housing 10 may be provided with a fluid inlet fitting 17 for intake of the working fluid and a fluid outlet fitting 18 for discharging the compressed working fluid. In the housing 10, a compression mechanism CM capable of compressing the fluid may be provided. In the example shown in
In the design shown in the drawing, the compression mechanism CM is also in the exhaust pressure zone and the working fluid to be compressed is supplied directly to a suction chamber inside the compression mechanism CM. Specifically, the fluid inlet fitting 17 is hermetically connected with the compression mechanism CM to supply the working fluid to be compressed for the compression mechanism CM.
The drive mechanism 40 for driving the compression mechanism CM may include, for example, a motor composed of a stator 42 and a rotor 43. The stator 42 may be fixed relative to the housing 10 in any suitable manner. The rotor 43 can be rotated in the stator 42 and a drive shaft 45 is provided in the rotor 43. The drive shaft 45 is supported by a main bearing housing 50 and a lower bearing housing 60. An eccentric crank pin 46 is formed at one end of the drive shaft 45. The eccentric crank pin 46 is fit into a hub 32 of an orbiting scroll member 30 via an unloading bushing 48 to drive the orbiting scroll member 30. A lubricating oil passage 47 (only partially shown) is also formed in the drive shaft 45. One end of the lubricating oil passage 47 (i.e., a lower end of the drive shaft 45) is located in a lubricating oil groove formed in a lower side of the housing 10. At said one end of the lubricating oil passage 47, an oil pumping device 49 may be provided.
In this example, the drive mechanism 40 is provided in the housing 10. It is to be appreciated by the person skilled in the art that the drive mechanism 40 may also be provided at the outside of the housing 10 for a so-called open compressor design.
In the example shown in the drawings, the compression mechanism CM may include a non-orbiting scroll member 20 and the orbiting scroll member 30. The non-orbiting scroll member 20 may be fixed relative to the housing 10 in any suitable manner, for example, fixed by bolts relative to the main bearing housing 50 described later.
The non-orbiting scroll member vanes 26 may be engaged with the orbiting scroll member vanes 36 to form, together with the non-orbiting scroll member end plate 24 and the orbiting scroll member end plate 34, a series of compression chambers C1, C2, C3 . . . whose volumes are reduced gradually from a radially outer side to a radially inner side to compress the fluid. Thus, the radially outermost compression chamber C1 is referred to as a low pressure chamber or a suction chamber, the intermediate compression chamber C2 is referred to as an intermediate pressure chamber, and the radially innermost compression chamber C3 is referred to as a high pressure chamber or a discharge chamber. The exhaust port 28 may be in fluid communication with the high pressure chamber C3. It should be appreciated that the reference to the low pressure chamber, the intermediate pressure chamber and the high pressure chamber is merely used for convenience of description, and in a practical compressor, the pressures inside these compression chambers are gradually increased and the number of the compression chambers is not limited to three.
In the normal operation of the compressor 1, the non-orbiting scroll member 20 and the orbiting scroll member 30 shall be radially engaged with each other to compress the working fluid. In addition, in order to provide a certain degree of axial flexibility to the scroll set to increase the reliability and safety of the compressor, a back pressure chamber is generally provided between the orbiting scroll member 30 and the main bearing housing. The back pressure chamber B is in communication with a compression chamber (for example, the intermediate pressure chamber C2) via the communication passage 35 (referring to
In the compressor design shown in
Referring to
Since the compression mechanism CM and the drive mechanism 40 are both in the high pressure side overall, a high pressure is also present in the hub 32 of the orbiting scroll member 30. As a result, during the normal operation of the compressor, the resultant force of the back pressure in the back pressure chamber B and the pressure in the hub 32 is greater than the resultant force of the pressures of the working fluid in the compression chambers C1, C2 and C3, whereby enabling the orbiting scroll member 30 and the non-orbiting scroll member 20 to be axially engaged with each other at a seal portions Sc, and the orbiting scroll member 30 to be in an engaged position.
When the compressor is in operation conditions such as liquid strike, for example, the resultant force (in a downward direction in the drawing) of pressures of the working fluid in the compression chambers C1, C2 and C3 will be greater than the resultant force (in an upward direction in the drawing) of the back pressure in the back pressure chamber B and the pressure in the hub 32, whereby the orbiting scroll member 30 and the non-orbiting scroll member 20 are axially separated from each other by a predetermined distance (also referred to as a floating amount) at the seal portions Sc, thus enabling the compression chambers to be communicated and depressurized, and thereby protecting the compression mechanism from being damaged.
However, when the compression mechanism needs to be re-engaged in the above-described case, the orbiting scroll member 30 and the non-orbiting scroll member 20 are in a separated state, and at this time, the seal portions Sc cannot isolate the suction chamber C1 from the back pressure chamber B, such that it is difficult to establish a back pressure in the back pressure chamber B, and it is difficult for the scroll set to achieve normal compression. In addition, in the operation of the compressor, since the pressures in the compression chambers change or fluctuate, overturning of the scroll set or one scroll member may probably occur. In this case, this also causes that the seal in the seal portions Sc may be failed, and the intermediate pressure chamber C2 and the low pressure chamber C1 are in communication with each other, thus resulting in a decrease of pressure in the intermediate pressure chamber C1, and the separation of the orbiting scroll member 30 from the non-orbiting scroll member 20, and a reduced mechanical performance of the compressor. Moreover, when the orbiting scroll member 30 is overturned, the wear between the orbiting scroll member 30 and the non-orbiting scroll member 20 may adversely affect the seal portions Sc and reduce the reliability of the compressor.
Therefore, in the conventional technology, in order to reduce the leakage at the seal portions Sc, it is necessary to design the floating amount of the orbiting scroll member to be small so as to make it possible to set a back pressure as soon as possible at the time of starting and to prevent the scroll member from being significantly overturned. However, with the design of a small amount of floating, many other issues may be encountered. For example, when abnormal operating conditions such as liquid strike are encountered, a small floating amount may cause an insufficient degree of separation of the orbiting scroll member 30 from the non-orbiting scroll member 20, that is, a full depressurization cannot be achieved. In addition, since the temperature in the compression mechanism CM changes, the orbiting scroll member 30 and the non-orbiting scroll member 20 may be slightly deformed. When the floating amount is small, the deformed orbiting scroll member 30 is apt to be stuck with the deformed non-orbiting scroll member 20 after being overturned, and thus it is not easy to return to normal engagement. In addition, the small floating amount requires a high processing accuracy of each of relevant parts, which adds the manufacturing difficulty and cost.
Therefore, there is a need for a scroll compressor which is further improved in reliability.
One object of one or more embodiments of the present application is to provide a scroll compressor which is further improved in reliability.
In order to achieve the above object, according to one aspect of the present application, a scroll compressor is provided, which includes: a compression mechanism, a main bearing housing, a back pressure chamber and a first sealing means. The compression mechanism includes a non-orbiting scroll member and an orbiting scroll member. The orbiting scroll member is axially movable between an engagement position and a disengagement position. In the engagement position, the orbiting scroll member and the non-orbiting scroll member are axially engaged with each other to form a series of compression chambers for compressing fluid, and in the disengagement position, the orbiting scroll member is axially separated from the non-orbiting scroll member. The main bearing housing is adapted to support the compression mechanism. The back pressure chamber is formed between the orbiting scroll member and the main bearing housing. The back pressure chamber is in communication with at least one compression chamber via a communication passage provided in the orbiting scroll member or the non-orbiting scroll member, and is adapted to apply a back pressure to the orbiting scroll member to bias the orbiting scroll member toward the engagement position. The first sealing means is provided between the back pressure chamber and a suction zone of the compression mechanism, and is capable of maintaining sealing when the orbiting scroll member is axially displaced.
In such a scroll compressor, the compression chamber in the compression mechanism is always kept isolated from the back pressure chamber by the first sealing means. When the compressor is cold-started, it is possible to quickly generate pressure in the back pressure chamber, to allow the orbiting scroll member and the non-orbiting scroll member to be quickly engaged, which facilitates speeding up the starting speed of the compressor. When the compressor is unloaded, the compression chambers in the compression mechanism are communicated and the pressure is released to the suction pressure. In this case, the pressure in the back pressure chamber is not released, thus, when the compression mechanism needs to be engaged again, the pressure in the back pressure chamber enables the orbiting scroll member to rapidly move toward the non-orbiting scroll member and an axial seal is formed, thereby facilitating improving the efficiency of the compressor and reducing the power consumption.
Optionally, the first sealing means is arranged in a first circumferential groove located in one of the orbiting scroll member and the non-orbiting scroll member and abuts against the other of the orbiting scroll member and the non-orbiting scroll member. Alternatively, the first sealing means is arranged in a first circumferential groove located in one of the orbiting scroll member and the main bearing housing and abuts against the other of the orbiting scroll member and the main bearing housing.
In such a scroll compressor, the position of the first sealing means can be flexibly arranged.
Optionally, the first sealing means includes a first sealing member arranged in the first circumferential groove and a first elastic element located between the first sealing member and the first circumferential groove, and the first elastic element applies a biasing force to the first sealing member.
In such a scroll compressor, it is possible to ensure that the first sealing means maintains sealing when the orbiting scroll member is moved.
Optionally, the first sealing means includes a first passage and a first sealing member arranged in the first circumferential groove. The first passage introduces a pressure higher than a suction pressure of the compression mechanism into the first circumferential groove to apply a biasing force to a bottom surface of the first sealing member.
Optionally, the scroll compressor is a high side compressor, and the first passage introduces the pressure in the back pressure zone or the pressure in an external environment of the compression mechanism into the first circumferential groove. Alternatively, the scroll compressor is a low side compressor, and the first passage introduces the pressure in the back pressure zone into the first circumferential groove.
By using machining instead of elastic elements, it is possible to reduce the number of parts and save costs.
Optionally, the first sealing means includes a first sealing member embedded in the first circumferential groove, and the first sealing member has a radial dimension less than a radial dimension of the first circumferential groove.
By using a simple sealing member, it is possible to reduce the number of parts and save costs.
Optionally, the scroll compressor further includes a second sealing means. The second sealing means is arranged in a second circumferential groove located in one of an axial end face of a hub of the orbiting scroll member and the main bearing housing and abuts against the other of the axial end face and the main bearing housing. The second sealing means is capable of maintaining sealing when the orbiting scroll member is axially displaced.
In a case that the scroll compressor is a low side scroll compressor, arranging the second sealing means between the axial end face of the hub of the orbiting scroll member and the main bearing housing enables the positions of the first sealing means, the second sealing means and the Oldham coupling to be offset in the axial direction, and enables the Oldham coupling to have a larger space for adjustment. In addition, the second sealing means can be made smaller, which facilitates expanding the back pressure chamber area, optimizing the axial force and improving the compressor performance.
Optionally, the second sealing means includes a second sealing member arranged in the second circumferential groove and a second elastic element located between the second sealing member and the second circumferential groove, and the second elastic element applies a biasing force to the second sealing member.
Optionally, scroll vanes of the orbiting scroll member and the non-orbiting scroll member are in the form of a twin scroll.
By using the form of the twin scroll, it is possible to increase the adjustment range of the sealing member and to facilitate the design of the force applying area of the back pressure zone, thereby further optimizing the axial force of the scroll set and improving adaptability for the occasion of a relatively compact structure.
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 following description of the preferred embodiments is merely exemplary and is by no means intended to limit the present application and its application or usage. The like reference numerals are used to designate like parts throughout the drawings, and the description of the construction of the like parts will not be repeated.
The basic construction and operation principle of the scroll compressor 1 to which the present application can be applied has been described above with reference to
The inventors have inventively found that in this scroll compressor shown in
Specifically, it is assumed that only the function of sealing the compression chamber (i.e., as the compression chamber seal portions Sc) of the seal portions Sc is retained and the function of isolating the back pressure chamber B from the compression chamber of the seal portions Sc is deleted, and an additional first sealing means 180 is used to isolate the back pressure chamber B from the compression chamber.
An improvement of the high side scroll compressor according to a first embodiment of the present application in views of sealing of the back pressure chamber will be described below with reference to
In this embodiment, an additional first sealing means 180 is provided to isolate the back pressure chamber B from the compression chamber. As shown in
During the operation of the scroll compressor, as shown in
When the orbiting scroll member 30 is separated from the non-orbiting scroll member 20 in the case that the compressor is stopped or abnormal, the orbiting scroll member end plate 34 and the non-orbiting scroll member end plate 32 are separated at the compression chamber seal portions Sc, referring to
In addition, when the compressor is cold-started after normal shutdown, the first sealing means 180 can increase the pressure build-up speed in the back pressure chamber B, thereby facilitating the speedup of starting of the compressor.
It can be seen that by providing the first sealing means 180, the back pressure chamber B can be always separated from the compression chamber. Since there is no need to avoid leakage at the compression chamber seal portions Sc, there is no particular requirement for the floating amount of the orbiting scroll member 30, and the floating amount can be designed to be large, thus, the accuracy requirements of the orbiting scroll member 30, the non-orbiting scroll member 20 and the main bearing housing 50 can be reduced, thereby reducing the cost. In addition, since the floating amount is large, the compression chamber can be quickly depressurized, and since the movable range of the orbiting scroll member 30 is large, the orbiting scroll member 30 is easy to return to the position for engagement with the non-orbiting scroll member 20 after being overturned without being stuck.
Although in the first embodiment of the high side scroll compressor described above, the first sealing means 180 is arranged in the circumferential groove 182 in the orbiting scroll member 30 and faces the non-orbiting scroll member 20, it should be appreciated by the person skilled in the art that, as shown in
In addition, in the first embodiment, as shown in
The second sealing means 190 is provided in a circumferential groove 192 (a second circumferential groove) located in one of an axial end face of the hub 32 and the main bearing housing 50 (shown as being provided in the main bearing housing 50), to isolate the back pressure chamber B from an external high pressure environment. Referring to
In the above description, though for each of the first sealing means 180 and the second sealing means 190, an O-shaped sealing ring is used as the sealing member and a compression spring is used as the elastic element, it is to be appreciated that sealing members of other shapes and elastic elements of other forms which are conceivable by the person skilled in the art may also be used. Alternatively, the sealing member and the elastic element may be an integral elastic sealing member that is compressed when the orbiting scroll member is in the engaged position and automatically extends to achieve sealing when the orbiting scroll member is in the disengaged position.
The first sealing means may also have other variations. As one of the variations, as shown in
As described above, when the compressor is stopped or abnormal or the like, the orbiting scroll member 30 is separated from the non-orbiting scroll member 20 (the seal portions Sc are separated), and the pressures in the compression chambers C1, C2, and C3 are uniformed due to communication of the compression chambers C1, C2, and C3, and are released. In this case, the pressure in the back pressure chamber B may be higher than the pressure in the compression chambers. Therefore, the pressure in the back pressure chamber B is introduced into the circumferential groove 182 through the passage 188 and acts on a bottom surface of the sealing ring 184. The sealing ring 184 is pushed out toward the non-orbiting scroll member 20 (specifically, the peripheral wall portion 22) so that the sealing ring 184 abuts against the peripheral wall portion 22 of the non-orbiting scroll member so as to keep the first sealing means 180 sealing. The seal of the first sealing means 180a can substantially maintain the pressure in the back pressure chamber B without leaking the pressure to the compression chambers and without releasing the pressure together with the pressures in the compression chambers. Thus, the first sealing means 180a also provides a sealing surface independent of the compression chamber seal portions Sc so that the pressure relief in the compression chambers will not affect the pressure in the back pressure chamber B, thereby achieving the same effect as that can be achieved by the above first sealing means 180. In addition, by using the passage 188 to replace the spring 186, it is possible to save the cost and improve the operational reliability of the sealing means 180a by replacing the provision of the spring member by machining.
The first sealing means 180a may also be provided on the non-orbiting scroll member 20 and face the orbiting scroll member 30, as shown in
As a further variation of the first sealing means, as shown in
In the process of operation of the compressor, the non-orbiting scroll member 20 and the orbiting scroll member 30 are closely fitted against each other at the seal portions Sc, and the sealing ring 184 is freely retracted into the circumferential groove 182 to avoid wear. When there is an abnormality or the orbiting scroll member 30 is in the disengaged position, since at a radially inner side of the sealing ring 184 of the first sealing means 180b is the suction pressure zone, at a radially outer side thereof is the back pressure zone B, and the pressure in the back pressure zone B is higher than the pressure in the suction pressure zone, the sealing ring 184 is pressed against the side wall of the circumferential groove 182 (referring to F1). In addition, the pressure in the back pressure zone B can be transmitted to a back surface of the sealing ring 184, to press the sealing ring 184 against the orbiting scroll member 30 (referring to F2). That is, when the non-orbiting scroll member 20 and the orbiting scroll member 30 are separated, the first sealing means 180b maintains sealing.
Accordingly, all of these variations are capable of achieving the same technical effects as those achieved by the above first sealing means 180, and those technical effects will not be described again.
Preferably, the orbiting scroll member 30 and the non-orbiting scroll member 20 of the scroll compressor are not in the form of a single scroll (referring to
During the operation of the compression mechanism CM, the central axis of the orbiting scroll member rotates around the central axis of the non-orbiting scroll member with a radius of revolution Ror. It is required that the sealing ring 184 cannot be exposed from a peripheral edge of the orbiting scroll member end plate 34 when the orbiting scroll member is moved to a rightmost position (referring to
For a single scroll with a radius of revolution Ror_1, when the orbiting scroll member is moved to the rightmost position, referring to
For a twin scroll with a radius of revolution Ror_2, when the orbiting scroll member is moved to the rightmost position, referring to
In the case that an unfolding angles of the generating lines are equal, the radius of revolution Ror_2 of the twin scroll is about a half of the radius of revolution Ror_1 of the single scroll. Therefore, the range of revolution of the orbiting scroll member 30 is small compared with that in a case of a single scroll, which enables the range for setting the sealing ring (i.e., the adjustment range of the sealing ring) to become larger. It can be seen from the comparisons of
The position of the sealing ring 184 can affect the area, for applying pressure to the orbiting scroll member 30, of the back pressure zone B, therefore, by increasing the adjustment range of the sealing ring, it is possible to facilitate the design of the force applying area of the back pressure zone, and thereby, the axial force of the scroll set can be further optimized. In addition, increasing the adjustment range of the sealing ring can correspondingly reduce the dimension of the end plate of the orbiting scroll member, making the design more suitable for the case where the structure is relatively compact.
A scroll compressor 200 according to a second embodiment of the present application is described hereinafter with reference to
The scroll compressor 200 includes a substantially closed housing 210, and a non-orbiting scroll member 220 of the compression mechanism CM is hermetically engaged with the housing to divide an internal space of the housing 210 into a low pressure side and a high pressure side. A drive mechanism 240, which drives the compression mechanism CM by a drive shaft 245 (which is supported by a main bearing housing 250 and a lower bearing housing 260), is arranged in the low pressure side, i.e., under the suction pressure. It will be appreciated by the person skilled in the art that the drive mechanism 240 may also be provided at the outside of the housing 210 for a so-called open compressor design. The housing 210 may be provided with a fluid inlet fitting 217 for intake of the working fluid and a fluid outlet fitting 218 for discharging the compressed working fluid.
The compression mechanism CM of the scroll compressor 200 has a structure substantially the same as that of the compression mechanism CM of the scroll compressor and includes an orbiting scroll member 230 and the non-orbiting scroll member 220. That is, the compression mechanism CM of the scroll compressor according to the first embodiment of the present application can be applied to a low side compressor.
In the scroll compressor 200, a substantially airtight back pressure chamber B is provided in a space inside the main bearing housing 250 on the orbiting scroll member 230 side. The back pressure chamber B is defined by the orbiting scroll member 230, the non-orbiting scroll member 220 and the main bearing housing 250 together. The back pressure chamber B is in communication with a compression chamber (e.g., the intermediate pressure chamber C2) via a communication passage 235 formed in an orbiting scroll member end plate 234, thereby accumulating a back pressure in the back pressure chamber B. It is to be appreciated that the communication passageway 235 may also be provided in the non-orbiting scroll member 220.
The non-orbiting scroll member 220 is also axially hermetically engaged with the orbiting scroll member 230 at the compression chamber seal portions Sc, which will not be described again.
Referring to
In some conventional designs of the low side compressor, the second sealing means is not arranged at the axial end face of the hub of the orbiting scroll member but is arranged at substantially the same axial position as the Oldham coupling between the orbiting scroll member and the main bearing housing, for example, arranged opposite surfaces of the orbiting scroll member end plate and the main bearing housing. In this case, the first sealing means, the second sealing means and the Oldham coupling are located at substantially the same axial position, making it difficult to adjust the position of these components, and it is often necessary to design the dimension of the orbiting scroll member end plate large to provide the space for arranging these components.
In this embodiment, the Oldham coupling can be adjusted within a large space by arranging the second sealing means 290 to be offset from the first sealing means 280 and the Oldham coupling 258 in the axial direction. For example, the Oldham coupling may be arranged in a radially inner side of the first sealing means 280 (will be described below), and in this case, the Oldham coupling has a relatively small mass and a better dynamic balance. The Oldham coupling may also be arranged in a radially outer side of the first sealing means 280, and in this case, the distance between keys is increased, the force subjected by the keys is reduced, the wear of the keys and corresponding key grooves is reduced, and the service life thereof is improved. The arrangement position can be chosen flexibly based on practical applications.
In addition, by arranging the second sealing means 290 at the axial end face of the hub 232 of the orbiting scroll member 230, the second sealing means 290 can be made small to facilitate expansion of the back pressure chamber area, optimizing the axial force and improving performance of the compressor.
In addition, the dimension of the main bearing housing 250 may affect only the dimension of the second sealing means 290, but has little effect on the Oldham coupling 258 and the first sealing means 280, causing the wide adaptability of the solution.
It should be appreciated that the second sealing means 190 may also be arranged between the main bearing housing 250 and other portions of the orbiting scroll member 230 as long as the second sealing means is not in the same axial position as at least one of the first sealing means 280 and the Oldham coupling.
As shown in
It can be seen that by providing the first sealing means 280, the back pressure chamber B can be always separated from the compression chambers. Since it is not necessary to avoid the leakage at the compression chamber seal portions Sc, it is possible to realize the advantages described above in connection with the scroll compressor according to the first embodiment.
Similar to the case in the first embodiment, the position of the first sealing means 180 in the second embodiment can also be changed. As shown in
In addition, the first sealing means 280, the second sealing means 290, and the Oldham coupling 258 are misaligned in the axial direction, i.e., are not located in the same axial position. In this way, the design of the Oldham coupling 258 will no longer be limited by the location and dimension of the sealing means, and its adjustment space is greater, thus facilitating further optimization of the structure.
While the present application has been described above in connection with various embodiments of the present application, it should be appreciated that, in the case of compatibility, the technical features described in connection with one embodiment can be combined with the technical features described in connection with other embodiments. For example, all the following features: the first sealing means arranged on the orbiting scroll member, the non-orbiting scroll member or the main bearing housing; the first sealing means and the second sealing means employing a compression spring, a passage for introducing a gas pressure, or independent sealing members (the two sealing means can have different structures) controlled by only the pressure in the back pressure chamber; the pressure introduced from the back pressure zone or an external high pressure zone; a twin scroll employed; the compression mechanism arranged in the high pressure side or the low pressure side, etc., can be combined arbitrarily, and all the combinations are within the scope of the present application.
While the various embodiments of the present application have been described in detail herein, it is to be appreciated that the present application is not limited to the specific embodiments described and illustrated herein in detail, and other variations and modifications can be implemented by the person skilled in the art without departing from the essential and scope of the present application. All the variations and modifications are within the scope of the present application. Moreover, all of the components described herein may be replaced by other technically equivalent components.
| Number | Date | Country | Kind |
|---|---|---|---|
| 201510058036.X | Feb 2015 | CN | national |
| 201520079596.9 | Feb 2015 | CN | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/CN2016/072757 | 1/29/2016 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2016/124111 | 8/11/2016 | WO | A |
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| 4415317 | Butterworth | Nov 1983 | A |
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| Number | Date | Country |
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| 101550933 | Oct 2009 | CN |
| 102985696 | Mar 2013 | CN |
| 204692086 | Oct 2015 | CN |
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| 2000087880 | Mar 2000 | JP |
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| Number | Date | Country | |
|---|---|---|---|
| 20180023570 A1 | Jan 2018 | US |
