Patent Application
20110113803
The present invention relates to a multi-evaporation system, and more particularly, to a multi-evaporation system which carries out a multi-evaporation process in an air-conditioning cycle of a vehicle air conditioning system, thereby enhancing system efficiency.
In the automobile industry, as general concerns about energy and environment are increased globally, the efficiency in each part including fuel efficiency has been steadily improved, and the external appearance of a vehicle has been also diversified in order to satisfy various demands of customers. According to such a tendency, research and development on lighter weight, smaller size and multi-function of each vehicle component has been carried out. Particularly, in an air-conditioning unit for a vehicle, since it is generally difficult to secure an enough space in an engine room, there have been many efforts to manufacture an air-conditioning system having a small size and high efficiency.
Meanwhile, the air-conditioning system generally includes an evaporator for absorbing heat from a peripheral portion, a compressor for compressing refrigerant, a condenser for radiating heat to a peripheral portion, and an expansion valve for expanding the refrigerant. In the air-conditioning system, the gaseous refrigerant introduced from the evaporator to the compressor is compressed at a high pressure and high temperature, and the compressed gaseous refrigerant radiates liquefaction heat to a peripheral portion while passing through the condenser so as to be liquefied, and the liquefied refrigerant is passed through the expansion valve so as to be in a low pressure low temperature wet vapor state and then introduced again into the evaporator so as to be vaporized.
Herein, the substantial air conditioning action occurs in the evaporator that absorbs vaporization heat from a peripheral portion while the wet vapor refrigerant is vaporized. As described above, the condenser and evaporator in the air-conditioning system typically fall into the category of the heat exchanger. Therefore, the improving of evaporator efficiency is a very important factor in the air-conditioning system.
There have been many efforts to increase the evaporator efficiency by variously changing the basic construction of the evaporator shown in
However, the evaporation systems described in the prior arts have some problems as followings. In case of the prior art 1, one of the two evaporators substantially functions as the cold storage unit, and if the cold storage unit is sufficiently cold-stored, the air is efficiently cooled. But in an initial stage that the cold storage unit is not cold-stored absolutely, the refrigerant passed through the expanding means absorbs from both of the air and the cold storage material, and thus the cooling efficiency of the air is deteriorated. Further, when the driving is intermittently performed at the side of the cold storage unit and low temperature refrigerant is stored, it is difficult to control the flow thereof. Furthermore, since the prior art 1 functions just as the cold storage unit, the air-conditioning operation is maintained only for a desired time period when an engine is stopped, and thus it is impossible to entirely enhance the cooling performance.
In case of the prior art 2, since the refrigerant is passed through, in turn, the two evaporators which are arranged in series, there is an advantage in that it is possible to maximize a length of the refrigerant passage. However, since the length of the refrigerant passage becomes too long, the pressure drop due to the passing of the evaporators is sharply increased, thereby considerably reducing the system efficiency. Further, in the structure of the prior art 2, since the refrigerant of the first evaporator is introduced into the second evaporator, evaporation pressure is excessively increased, thereby reducing the system efficiency.
In addition, in case of the prior art 3, the refrigerant is passed through, in turn, the evaporator, the ejector and the evaporator, and it is promoted that the ejector is used to mix the refrigerants having different temperature, thereby improving a temperature condition of the refrigerant and thus increasing the air-conditioning efficiency. However, the prior art 3 has some problems as follows. In the construction of the prior art 3, since the refrigerant is passed through, in turn, the two evaporators which are arranged in series, there is an advantage in that it is possible to maximize a length of the refrigerant passage in which heat exchange is occurred. However, since the length of the refrigerant passage becomes too long, the pressure drop due to the passing of the evaporators is sharply increased, thereby considerably reducing the system efficiency. Further, in the structure of the prior art 3, since the refrigerant of the first evaporator is introduced into the second evaporator, evaporation pressure is excessively increased, thereby reducing the system efficiency.
Therefore, the study on a new evaporation system for simultaneously enhancing the air-conditioning efficiency and the system efficiency in the evaporator regardless of a time and condition of the driving is required.
An object of the present invention is to provide a multi-evaporation system in which multi-evaporation is occurred by a plurality of evaporators arranged in parallel, thereby enhancing the air-conditioning and system efficiency.
Another object of the present invention is to provide a multi-evaporation system which is further provided with an ejector so as to mix the refrigerants and thus improve the temperature condition, thereby enhancing the air-conditioning and system efficiency.
To achieve the object of the present invention, the present invention provides a multi-evaporation system including a compressor 10 which sucks and compresses refrigerant; a condenser 20 which condenses the refrigerant compressed in the compressor 10; an expanding means 30 which receives the refrigerant condensed in the condenser 20 through an inlet port 31, branches the refrigerant into at lest two or more, discharges the refrigerant through at least two or more discharging part 32a to 32n, and throttles the refrigerant before or after the refrigerant is branched; and an evaporator 40 which comprises at least two or more evaporating parts 41 to 4N so as to receive and evaporate the refrigerant discharged from the expanding means 30 and then introduce the evaporated refrigerant into the compressor 10, wherein the evaporating parts 41 to 4N are parallelly disposed in a flow direction of air passing through the evaporating parts 41 to 4N so that the air blown by a single blower 60 is passed through in turn the evaporating parts 41 to 4N so as to be cooled, and the discharging parts 32a to 32n and the evaporating parts 41 to 4N are connected by refrigerant passages disposed in parallel.
The refrigerant which is branched and discharged from the discharging parts 32a to 32n of the expanding means 30 is supplied to the evaporating parts 41 to 4N at the same time. Further, a distribution rate of the refrigerant supplied to the evaporating parts 41 to 4N becomes higher as the evaporating parts 41 to 4N are disposed at a more upstream side of the flow direction of the air blown from the blower 60.
The evaporating parts 41 to 4N are formed by dividing the evaporator 40 into at least two or more evaporating regions, or the evaporating parts 41 to 4N are formed by dividing the evaporator 40 into two evaporating regions, or the evaporating parts 41 to 4N are formed separately so as to be closely contacted with each other and arranged in parallel.
The expanding means 30 comprises an inlet passage 33 which passes the refrigerant introduced from the inlet port 31; and at least two or more outlet passages 34a to 34n which are formed by dividing the inlet passage 33 into at least two or more so as to discharge the refrigerant to the discharging part 32a to 32n. At this time, the expanding means 30 comprises an expanding part before branching 35 which is provided at the inlet passage 33 so as to throttle the refrigerant, and an expanding part 35a to 35n which is provided at the outlet passage 34a to 34n so as to throttle the refrigerant. And the expanding part before branching 35 and the expanding part 35a to 35n are respectively comprised of one selected from an expansion valve, an orifice, a capillary tube, and a reducing means.
The expanding means 30 comprises the expanding part before branching 35, and the expanding parts provided at the outlet passages except the first outlet passage 34a which supplies the refrigerant to the first evaporating part 41 disposed at an uppermost stream side of the flow direction of the air blown by the blower 60. And the expanding part before branching 35 is comprised of an expansion valve, and the expanding parts provided at the outlet passages except the first outlet passage 34a is comprised of one selected from reducing means comprising an orifice and a capillary tube.
The expanding means 30 is formed so that a pressure reduction value of the refrigerant supplied to the evaporating part disposed at the downstream of the flow direction of the air blown by the blower 60 is larger than that of the refrigerant supplied to the evaporating part disposed at the upstream of the air flow direction.
The expanding means 30 is formed so that a pressure reduction value of the refrigerant supplied to the evaporating part having a relatively small flow rate becomes larger.
The expanding means 30 is comprised of expanding parts 35a to 35n which are provided at the outlet passages 34a to 34n so as to throttle the refrigerant, and the expanding parts 35a to 35n are formed so that a pressure reduction level is controlled by adjusting an opening degree thereof. At this time, the expanding means 30 is formed so that a pressure reduction value of the refrigerant supplied to the evaporating part disposed at the downstream of the flow direction of the air blown by the blower 60 is larger than that of the refrigerant supplied to the evaporating part disposed at the upstream of the air flow direction.
The multi-evaporation system further includes an ejector which is provided between the evaporator 40 and the compressor 10 so as to suck the refrigerant discharged from a part or whole of the remaining evaporating parts using a flow speed of the refrigerant discharged from a part of the first to Nth evaporating parts 41 to 4N, raise pressure of the refrigerant and then supply the refrigerant to the compressor 10.
The ejector 50 includes a nozzle part 51 which decompresses and expands the refrigerant discharged from a part of the first to Nth evaporating parts 41 to 4N, and increases a flow speed of the refrigerant; a suction part 52 which sucks the refrigerant discharged from part or whole of the remaining evaporating parts using an increased flow speed of the refrigerant injected from the nozzle part 51; and a diffuser part 53 which mixes the refrigerant injected from the nozzle part 51 and the refrigerant sucked through the suction part 52 and then raise pressure of the mixed refrigerant.
The ejector 50 is formed so that the refrigerant has a subsonic speed.
The multi-evaporation system further includes a detecting means 70 which is provided at passages for connecting the expanding means 30, the evaporator 40 and the compressor 10 so as to detect temperature and pressure of the refrigerant and control an operation of the expanding means 30.
According to the present invention, the refrigerant that is branched in plural while passing through an expanding means is multi-evaporated by the plurality of evaporators arranged in parallel, thereby efficiently evaporating the refrigerant. In other words, temperature of the overheated air is lowered while the air passes through each evaporator, and thus the expanding means that is disposed at the front end of each evaporator expands the pressure and temperature of the refrigerant responding to the temperature of the air introduced into each evaporator (high temperature range: an increase in the refrigerant pressure and temperature by a small margin, low temperature range: decrease in the refrigerant pressure and temperature), and thus the control of the evaporation range is precisely carried out, thereby efficiently achieving the evaporation. Further, in the process that the refrigerant is branched off and then passed through the evaporator, the length of the refrigerant passage is remarkably reduced comparing with that in the prior art, thereby improving the pressure drop of the refrigerant when the refrigerant is passed through the evaporator.
Further, according to the present invention, it is possible to considerably enhance the efficiency of the entire system.
Furthermore, since the refrigerants that is branched in plural and then evaporated in each evaporator are mixed using the ejector, the conditions like the temperature and pressure of the refrigerant which is discharged from the evaporator and then introduced into a compressor is optimized to thereby further improve the system efficiency. Particularly, since the ejector used in the present invention is constructed so that the refrigerant is flowed at a subsonic speed, the refrigerant is efficiently mixed and also noise is not generated.
The above and other objects, features and advantages of the present invention will become apparent from the following description of preferred embodiments given in conjunction with the accompanying drawings, in which:
Hereinafter, the embodiments of the present invention will be described in detail with reference to accompanying drawings.
In the constructions of the expanding means 30 and the evaporator 40, the multi-evaporation system of the present invention has different features from the general air-conditioning system.
The expanding means 30 receives the refrigerant condensed in the condenser 20 through an inlet part 31, and throttles and then discharges it. Herein, as shown in
The evaporator 40 functions to receive and evaporate the refrigerant discharged from the expanding means 30 and then introduce it into the compressor 10. As shown in the drawing, the evaporator 40 includes a first evaporating part 41 for receiving and evaporating the refrigerant discharged from the first discharging part 32a to an Nth evaporating part 4N for receiving and evaporating the refrigerant discharged from the Nth discharging part 32n. Further, the first to Nth evaporating parts 41 to 4N are arranged in parallel so as to be overlapped in an air flow direction, and thus the air sent by a single blower is passed through in turn the first evaporating part 41 to the Nth evaporating part 4N so as to be cooled. Of cause, since the first evaporating part 41 to the Nth evaporating part 4N are disposed in parallel, the refrigerant passage connecting the first discharging part 32a and the first evaporating 41 and the refrigerant passage connecting the Nth discharging part 32n and the Nth evaporating part 4N are also disposed in parallel.
According to the present invention, the evaporating parts 41 to 4N receive simultaneously the refrigerant branched and discharged from the discharging parts 32a to 32n. In other words, it means that the refrigerant branched in the expanding means 30 is not supplied in turn to each evaporating part, but supplied at the same time to the evaporating parts 41 to 4N. In the present invention, the refrigerant is supplied to all of the N evaporating parts 41 to 4N so as to exchange heat with the air blown by the blower 60.
As described above, the N evaporating parts 41 to 4N are disposed in parallel, and the air blown by the single blower 60 is passed through in turn the evaporating parts 41 to 4N. Thus, the air that is primarily cooled in the first evaporating part 41 is flowed into the second evaporating part 42, and the air that is secondly cooled in the second evaporating part 42 is flowed into the third evaporating part 43, . . . . This process is repeated N times, and thus the air is repeatedly cooled Nthly.
Herein, the repeated cooling process shows a different aspect from that in the evaporator arranged in two or more rows. In case of the evaporator arranged in two or more rows, as shown in
Moreover, since the evaporator 40 is comprised of the evaporating parts 41 to 4N arranged in parallel, it is possible to further obtain the effects as follows. In case of the conventional evaporator shown in
In the present invention, the evaporating parts 41 to 4N are disposed in parallel, and the refrigerant flowed into the evaporating parts 41 to 4N is previously branched in the expanding means 30 into N corresponding to the number of evaporating parts. Thus the refrigerant passage has the same length as that in a single evaporator. However, in case of the general evaporator shown in
As the evaporating parts 41 to 4N are disposed at a more upstream side of a flow direction of the air blown by the blower 60, a distribution rate of the refrigerant is increased. In other words, the distribution rate of the refrigerant is set so that an amount of the refrigerant supplied to the first evaporating part 41 disposed at an uppermost stream side (which is the most adjacent to the blower 60) is larger than that supplied to the second evaporating part 42, and an amount of the refrigerant supplied to the second evaporating part 42 is larger than that supplied to the third evaporating part 43. In the present invention as described above, the refrigerant is simultaneously supplied to each evaporating part 41 to 4N, and the temperature conditions of the refrigerants supplied to each evaporating part is the same as each other. However, as the air blown by the blower 60 is passed through the evaporating parts 41 to 4N, a speed of the air becomes slow due to air resistance, and also its temperature is increased due to heat exchange with the refrigerant. That is, the speed of the air passing through the first evaporating part 41 is larger that that of the air passing through the second evaporating part 42 . . . , and the temperature of the air passing through the first evaporating part 41 is smaller that that of the air passing through the second evaporating part 42 . . . . Accordingly, the heat exchange performance in the first evaporating part 41 disposed at the uppermost stream side is the highest, and the heat exchange performance in other evaporating parts becomes lower gradually. Thus, the distribution rate of the refrigerant is set so that a largest amount of refrigerant is supplied to the first evaporating part 41, and a next largest amount of refrigerant is supplied to the second evaporating part 42, . . . , thereby maximizing the heat exchange performance. In other words, as the evaporating parts are disposed at a more downstream side of the air flow direction, the distribution rate is reduced.
Hereinafter, it will be described regarding to a case that there are two evaporating parts, i.e., the evaporator includes the first and second evaporating parts.
Herein, in case of the present invention, the refrigerant is properly distributed and supplied according to inlet air temperature (thermal load) for each region. Since the inlet air temperature of the region #1 is higher than that of the region #2, a refrigerant flow rate of the region #1 is larger that that of the region #2.
If a total refrigerant flow rate of the regions #1 and #2 is the same as that in the conventional evaporator, a refrigerant flow rate passing through each evaporating part is smaller than a total refrigerant flow rate passing through the conventional evaporator, because the refrigerant is simultaneously supplied to the multiple evaporating parts that are parallelly arranged in the air flow direction. Thus a refrigerant pressure loss generated while the refrigerant passes through an inner portion of the evaporator is reduced. In other words, since the refrigerant is simultaneously supplied to each evaporating part, the refrigerant pressure loss is reduced when passing through each evaporating part. Owing to the low pressure loss in the evaporator, an inlet pressure of the evaporator is reduced, such that the refrigerant is smoothly expanded and evaporated. Particularly, in case of the region #2, since the flow rate is small, and thus the pressure loss is reduced, pressure of the evaporator is remarkably decreased (also the refrigerant temperature is also decreased), and the refrigerant is smoothly evaporated.
Therefore, if the refrigerant is branched and supplied, the inlet refrigerant pressure (temperature) is considerably decreased even in the same sized evaporator, thereby efficiently evaporating the refrigerant. Herein, the enthalpy difference is the same, but the total refrigerant flow rate is increased, thereby enhancing a heat radiation performance and thus improving the air conditioner performance.
According to the evaporator 40 of the present invention, since the single evaporator 40 is divided into N evaporating regions, it is very to realize it. For example, in the evaporator shown in
As described above, the evaporator of the present invention may be constructed as follows: the single evaporator is divided by the partition wall so as to form the N evaporating regions, or the evaporating parts 41 to 4N are separately formed to be closed contacted with each other and arranged in parallel.
The inlet passage 33 passes the refrigerant introduced from the inlet port 31, and the first to Nth outlet passages 34a to 34n are formed by branching the inlet passage 33 into N. The first to Nth outlet passages 34a to 34n are connected with the first to Nth discharging part 32a to 32n so as to discharge the refrigerant.
Hereinafter, the expanding parts 35, 35a to 35n having the passages will be described in detail. Assuming that the expanding part which is disposed at the inlet passage 33 to throttle the refrigerant is called an expanding part before branching 35, and the expanding part which is disposed at the first outlet passage 34a to throttle the refrigerant is called a first expanding part 35a, . . . and the expanding part which is disposed at the Nth outlet passage 34n to throttle the refrigerant is called an Nth expanding part 35n, the expanding means 30 of the present invention includes at least one of the expanding part before branching 35, and the first to Nth expanding parts 35a to 35n. For example, only the expanding part before branching 35 may be provided at the inlet passage 33, or only the Nth expanding part 35n may be provided at the Nth outlet part 34n, or the expanding part is not provided at the inlet passage 33 but all the first to Nth expanding parts 35a to 35N are respectively provided at the first to Nth outlet passages 34a to 34n, and the expanding means 30 may be formed into various types according to design purpose, desired performance and the like.
The expanding part before branching 35 and the expanding parts 35a to 35n may be comprised of one of an expansion valve, an orifice, a capillary tube, and a reducing means.
Further, it is preferable that the expanding means 30 includes the expanding part before branching 35, and the expanding parts provided at the outlet passages except the first outlet passage 34a supplying the refrigerant to the first evaporating part 41 which is disposed at the uppermost stream side of the flow direction of the air blown by the blower 60.
According to the description of the evaporator 40, since the heat exchange performance is the highest in the first evaporating part 41 disposed at the uppermost stream side that is the most adjacent to the blower 60, the refrigerant distribution rate supplied to each evaporating part is set to be gradually reduced from the first evaporating part 41 toward the Nth evaporating part 4N, i.e., to be the largest in the first evaporating part 41 and the smallest in the Nth evaporating part 4N. In this case, according to the distribution rate supplied to each evaporating part 41 to 4N, an amount of the refrigerant passing through the first outlet passage 34a becomes maximum, and an amount of the refrigerant passing through the Nth outlet passage 34n becomes minimum. Meanwhile, the expanding part before branching 35 is provided so that the refrigerant is throttled while being passed through the expanding part before branching 35, and also since the expanding parts are provided at the outlet passages, the expanded refrigerant is throttled once more by the expanding parts while being passed through the expanding parts 34a to 34n, thereby increasing the evaporation efficiency.
Herein, it is possible to obtain an effect of the increase in the evaporation efficiency by the pressure reduction due to the throttling of the refrigerant, however, there is also possibility of deteriorating the efficiency due to the pressure drop. In case that the amount of the refrigerant distributed to the first evaporating part 41 becomes the largest, the amount of the refrigerant passing through the first outlet passage 34a also becomes maximum. At this time, since the flow rate of the refrigerant passing through the outlet passages 34b to 34n except the first outlet passage 34a is relatively small, bad influence due to the pressure drop is relatively small, and the effect of the increase in the evaporation efficiency due to the pressure reduction is larger than the bad influence. However, in the first outlet passage 34a, if a large amount of the refrigerant passing through the first outlet passage is throttled once more, the refrigerant flow rate is reduced, thereby reducing the efficiency.
Therefore, it is more preferable that the expanding part is provided at the rest of the passages (the inlet passage, the second outlet passage, . . . , Nth outlet passage) except the first outlet passage 34a. Because a relatively small flow rate is flowed in the rest of the passages, the bad influence due to the pressure drop is minimized when the expanding parts are additionally provided, and the effect of the increase in the efficiency is maximized by the pressure reduction due to the throttling of the refrigerant.
The construction of the expanding means 30 is not limited to the descriptions as described above and the present invention of
The expanding means 30 may be formed so that the pressure reduction value of the refrigerant supplied to the evaporating part disposed at the upstream of the flow direction of the air blown by the blower 60 is larger than that of the refrigerant supplied to the evaporating part disposed at the downstream of the flow direction.
The expanding means 30 may be formed so that the pressure reduction value of the refrigerant supplied to the evaporating part in which a relatively small flow rate is supplied is larger than that of the refrigerant supplied to the evaporating part in which a relatively larger flow rate is supplied. According to the above description of the evaporator and the evaporating part, as the amount of refrigerant supplied to the more upstream side of the flow direction of the air blown from the blower becomes larger, it is further advantage in the performance thereof. That is, in case that the distribution rate of the refrigerant supplied to the evaporating part disposed at the more upstream side becomes larger, the conditions is satisfied by the construction of the embodiment of
Further detailed description will be described with reference to
In case of an evaporating part (the region #2) which is disposed at the downstream of the flow direction of the air blown by the blower, since a flow rate of the refrigerant is smaller than that of the refrigerant supplied to an evaporating part (region #1) disposed at an upstream side of the air flow blown by the blower, a pressure loss in the evaporating part becomes smaller. Therefore, if an additional reducing means 35b is provided at a refrigerant passage connected to the region #2 so as to reduce pressure of the refrigerant, it is possible to enhance the evaporation of the refrigerant in the evaporating part.
According to the present invention, it is also possible to enhance the evaporation of the refrigerant by reducing the pressure of the refrigerant (the pressure of the inlet port of the evaporator) supplied through the expanding means to the evaporator corresponding to decrease of the pressure loss in the evaporator. In comparing pressure loss rates of the refrigerant in the evaporator (evaporating part), as shown in
Further, in case of the evaporator of the present invention, since each evaporating region is disposed in parallel, a total pressure drop rate occurred in the evaporator is not a sum of the pressure drop rates occurred in each region, but depends on the largest pressure loss value occurred in the regions. Thus, it is possible to further increase the improvement effect of the pressure loss.
Detailedly speaking, each refrigerant passing through the evaporating parts 41 to 4N has a different pressure and temperature condition from each other. If the branched passages are combined into one, the mixing is naturally occurred and thus the conditions such as the pressure and temperature will be equalized. However, the refrigerant may be not completely mixed before being supplied to the compressor 10, and thus the efficiency in the compressor 10 may be partially reduced. In the embodiment of
By using a flow speed of the refrigerant discharged from a part of the first to Nth evaporating parts 41 to 4N, the ejector 50 sucks the refrigerant discharged from a part or whole of the rest of the evaporating parts, raises the pressure of the refrigerant and then supplies the refrigerant to the compressor 10.
The ejector 50 is formed so that the refrigerant has a subsonic speed. Most of the generator ejectors are formed so that the refrigerant passing through the ejector has a supersonic speed. In this case, a noise generated from the ejector is very large. Since the evaporation system of the present invention is installed in a vehicle, it is necessary to restrain the generation of the noise. Therefore, in the present invention, the refrigerant in the ejector 50 has a subsonic speed instead of a supersonic speed. Accordingly, the ejector 50 efficiently mixes the refrigerants without generation of the noise.
The present application contains subject matter related to Korean Patent Application No. 10-2009-0042057, filed in the Korean Intellectual Property Office on May 14, 2009 Korean Patent Application No. 10-2009-0119621, filed in the Korean Intellectual Property Office on Dec. 4, 2009, Korean Patent Application No. 10-2009-0119628, filed in the Korean Intellectual Property Office on Dec. 4, 2009 and Korean Patent Application No. 10-2009-0119633, filed in the Korean Intellectual Property Office on Dec. 4, 2009 the entire contents of which is incorporated herein by references.
While the present invention has been described with respect to the specific embodiments, it will be apparent to those skilled in the art that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the following claims.
According to the present invention, since the refrigerants passing through the evaporating parts 41 to 4N are passed through the ejector 50 so as to be smoothly mixed with each other, it is possible to stabilize the pressure and temperature of the refrigerant flowed into the compressor 10.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2009-0042057 | May 2009 | KR | national |
| 10-2009-0119621 | Dec 2009 | KR | national |
| 10-2009-0119628 | Dec 2009 | KR | national |
| 10-2009-0119633 | Dec 2009 | KR | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/KR2010/003044 | 5/14/2010 | WO | 00 | 12/23/2010 |
