GB2553422A

GB2553422A - Air conditioner

Info

Publication number: GB2553422A
Application number: GB1711575.9A
Authority: GB
Inventors: Anai Shintaro
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2015-04-24
Filing date: 2015-04-24
Publication date: 2018-03-07
Anticipated expiration: 2035-04-24
Also published as: JP6385568B2; GB2553422B; JPWO2016170668A1; WO2016170668A1; GB201711575D0

Abstract

Provided is an air conditioner that can make adjustments so as to achieve a prescribed airflow without ascertaining the duct pressure drop, the characteristics of the motor, the characteristics of the fan, or the like. The air conditioner is provided with a refrigerant circuit, in which a compressor (1) that compresses the refrigerant, a condenser (2) that condenses the refrigerant, an expansion valve (3) that reduces pressure, and an evaporator (4) that evaporates the refrigerant are connected via pipes that allow the refrigerant to circulate. The air conditioner is also provided with a fan (5) that blows air on the evaporator (4), and a controller (7) that controls the operation of the compressor (1), the expansion valve (3), and the fan (5). Data showing the relationship between airflow rate and the heat exchange efficiencies of the condenser and the evaporator is stored in the memory of the controller (7). The controller (7) calculates, on the basis of said data, the airflow rate for the fan (5), using the heat exchange efficiencies and the status of the refrigeration cycle.

Description

(54) Title of the Invention: Air conditioner Abstract Title: Air conditioner (57) Provided is an air conditioner that can make adjustments so as to achieve a prescribed airflow without ascertaining the duct pressure drop, the characteristics of the motor, the characteristics of the fan, or the like. The air conditioner is provided with a refrigerant circuit, in which a compressor (1) that compresses the refrigerant, a condenser (2) that condenses the refrigerant, an expansion valve (3) that reduces pressure, and an evaporator (4) that evaporates the refrigerant are connected via pipes that allow the refrigerant to circulate. The air conditioner is also provided with a fan (5) that blows air on the evaporator (4), and a controller (7) that controls the operation of the compressor (1), the expansion valve (3), and the fan (5). Data showing the relationship between airflow rate and the heat exchange efficiencies of the condenser and the evaporator is stored in the memory of the controller (7). The controller (7) calculates, on the basis of said data, the airflow rate for the fan (5), using the heat exchange efficiencies and the status of the refrigeration cycle.

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DESCRIPTION

Title of Invention

AIR-CONDITIONING APPARATUS

Technical Field [0001]

The present invention relates to an air-conditioning apparatus employing a heat pump system.

Background Art [0002]

In general, an air-conditioning apparatus employing a heat pump system is configured with a compressor, a condenser, an expansion valve, an evaporator, pipes connecting them to circulate refrigerant, and an air-sending device. In the airconditioning apparatus, the refrigerant is compressed in the compressor to be sent to the condenser in a form of a high-pressure gas, then, the refrigerant is condensed in the condenser to be sent to the expansion valve in a form of a high-pressure liquid, then, the refrigerant is expanded and decompressed in the expansion valve to be sent to the evaporator in a form of a low-pressure two-phase gas-liquid, and then, the refrigerant is evaporated in the evaporator to be sent to the compressor again in a form of a low-pressure gas, and thereby, an indoor temperature is conditioned by use of a refrigeration cycle.

[0003]

For example, in cooling operations, indoor air is cooled by the evaporator. At this time, air is caused to pass through the evaporator by the air-sending device for exchanging heat of the indoor air with that of the evaporator.

[0004]

In the above-described air-conditioning apparatus, an air sending flow rate is determined by a user. For example, a predetermined air sending flow rate or ability may be desired to be provided by calculation of heat load in a room. However, when a duct is connected, due to air-path pressure loss of the duct, the desired air sending flow rate cannot be provided in some cases.

[0005]

In such a case, the air sending flow rate to be reduced has been predicted by obtaining the air-path pressure loss of the duct in advance, and the air sending flow rate has been set to be increased. Moreover, the air sending flow rate has been predicted from a load applied to a motor of the air-sending device, and feedback has been provided to the motor to obtain a predetermined air sending flow rate.

Citation List

Patent Literature [0006]

Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2003-269772 Summary of Invention Technical Problem [0007]

However, when a duct is connected, due to air-path pressure loss of the duct, in some cases, the desired air sending flow rate has not been provided, or complex control parameters have been necessary to be set to provide feedback in advance on the basis of a relationship between the load of the motor and the air sending flow rate. [0008]

For example, in an air-conditioning apparatus described in Patent Literature 1, a relationship between a load (static pressure), a current value and a rotation frequency of a motor for driving a fan is grasped in advance to measure and adjust an air sending flow rate. However, a control algorithm has been required to be written on the basis of the grasped characteristics of the two, namely, the fan and the motor, causing a problem of a complex configuration.

[0009]

The present invention has been made to solve the above-described problem, and has as an object to provide an air-conditioning apparatus capable of adjusting an air sending flow rate to a predetermined air sending flow rate without grasping pressure loss of a duct, motor characteristics, and fan characteristics.

Solution to Problem [0010]

An air-conditioning apparatus of an embodiment of the present invention includes a refrigerant circuit in which a compressor configured to compress refrigerant, a condenser configured to condense refrigerant, an expansion valve configured to reduce pressure of refrigerant, and an evaporator configured to evaporate refrigerant are connected by a pipe to circulate refrigerant, an air-sending device configured to send air to the evaporator, and a controller configured to control operations of the compressor, the expansion valve, and the air-sending device. The controller stores data indicating a relationship between an air sending flow rate and a heat exchange efficiency of the condenser and the evaporator in a memory of the controller, and the controller is configured to calculate an air sending flow rate of the air-sending device from the heat exchange efficiency and a status of a refrigeration cycle on the basis of the data.

Advantageous Effects of Invention [0011]

In the air-conditioning apparatus according to an embodiment of the present invention, the controller is able to calculate an air sending flow rate from the heat exchange efficiency and a status of the refrigeration cycle by use of the table, and with an air-sending device capable of adjusting the air sending flow rate on the basis of the calculation result, an air sending flow rate can be adjusted to a predetermined air sending flow rate without grasping pressure loss of a duct, motor characteristics, and fan characteristics.

Brief Description of Drawings [0012] [Fig. 1] Fig. 1 is a schematic view illustrating a configuration of an airconditioning apparatus according to an embodiment of the present invention.

[Fig. 2] Fig. 2 is a refrigeration cycle diagram (No. 1) of the air-conditioning apparatus according to the embodiment.

[Fig. 3] Fig. 3 is a flowchart showing operations in a cooling operation of the air3 conditioning apparatus according to the embodiment.

[Fig. 4] Fig. 4 is a refrigeration cycle diagram (No. 2) of the air-conditioning apparatus according to the embodiment.

[Fig. 5] Fig. 5 is an air diagram (No. 1) of the air-conditioning apparatus according to the embodiment.

[Fig. 6] Fig. 6 is an air diagram (No. 2) of the air-conditioning apparatus according to the embodiment.

[Fig. 7] Fig. 7 is a refrigeration cycle diagram (No. 3) of the air-conditioning apparatus according to the embodiment.

[Fig. 8] Fig. 8 is a refrigeration cycle diagram (No. 4) of the air-conditioning apparatus according to the embodiment.

Description of Embodiments [0013]

Hereinafter, an air-conditioning apparatus according to an embodiment of the present invention will be described with reference to drawings. Note that, here, it is declared that numerical values and the like appearing in the text are conveniently assumed to describe operations.

[0014]

Fig. 1 is a schematic view illustrating a configuration of an air-conditioning apparatus according to the embodiment. The air-conditioning apparatus is configured with a refrigerant circuit (configured with a compressor 1, a condenser 2, an expansion valve 3, an evaporator 4, and pipes 20), a fan 5, a motor 6, a controller 7, a pressure measuring sensor 8, temperature measuring sensors 9 to 11, and an intake air status measuring sensor 12.

[0015]

First, functions of members constituting the refrigerant circuit and its peripheral members will be described. The compressor 1 sucks refrigerant in a form of lowpressure gas, and compresses the refrigerant into a form of a high-pressure gas. Here, the compressor 1 may be the one capable of arbitrarily varying an operating frequency by inverter control, or the one with a constant speed incapable of varying the operating frequency.

[0016]

The condenser 2 condenses the refrigerant in the form of high-pressure gas into the refrigerant in the form of high-pressure liquid by heat-exchanging with an external fluid. Here, the external fluid used for heat exchange may be gas, such as air, or may be liquid, such as water.

[0017]

The expansion valve 3 expands the refrigerant in the form of high-pressure liquid into the refrigerant in the form of low-pressure two-phase gas-liquid and reduces pressure of the refrigerant. Needless to say, an interchange with anything capable of providing the similar effects is possible. For example, an electronic expansion valve or a capillary tube may be used.

[0018]

The evaporator 4 evaporates the refrigerant in the form of low-pressure twophase gas-liquid flowing from the expansion valve 3 into the refrigerant in the form of low-pressure gas by heat-exchanging with air, and returns the refrigerant to the compressor.

[0019]

The fan 5 sends air to the evaporator 4 to exchange heat between the air and the refrigerant in the form of low-pressure two-phase gas-liquid in the evaporator 4. Needless to say, an interchange with anything capable of providing the similar effects is possible. For example, the type of the fan may be a sirocco fan or a plug fan. Moreover, the system of the fan may be a forced draft system or an induced draft system.

[0020]

The motor 6 drives the fan 5. In the embodiment, the motor is assumed to be capable of controlling the rotation frequency for adjusting the air sending flow rate; however, needless to say, an interchange with anything capable of providing the similar effects is possible.

[0021]

Next, the function of each sensor will be described. The pressure measuring sensor 8 measures the pressure of the condenser 2. The temperature measuring sensor 9 measures the outlet temperature of the condenser 2. The temperature measuring sensor 10 measures the heat exchanger temperature Te of the evaporator

4. The temperature measuring sensor 11 measures the outlet temperature of the evaporator 4.

[0022]

The intake air status measuring sensor 12 measures the dry-bulb temperature and the wet-bulb temperature of air flowing into the evaporator 4. A relative humidity may be allowed to be measured when the wet-bulb temperature cannot be measured, and computation of the wet-bulb temperature may be performed on the basis of data of air properties stored in an unillustrated memory of the controller 7.

[0023]

Next, a configuration and functions of the controller 7 will be described. The controller 7 is configured with a microcomputer, and data indicating the air properties, the refrigerant properties, and an ability computational expression, and table data indicating a relationship between the heat exchange efficiency ε and the air sending flow rate GA as shown in the following table 1 are stored in the non-volatile memory or other devices.

[0024] [Table 1]

Ga [m³/min]	0	20	40	60	80	100	120	140	160
ε[-]	1.00	0.92	0.80	0.69	0.61	0.56	0.52	0.47	0.44

[0025]

To create the refrigerant circulation amount Gr corresponding to the predetermined refrigeration cycle shown in Fig. 2 (inlet enthalpy of the evaporator 4 and outlet enthalpy of the evaporator 4) or ability, the controller 7 controls the compressor 1 or the expansion valve 3 on the basis of the pressure and temperature data obtained by the sensors 8 to 12, performs computation of the air sending flow rate, and controls the motor 6 to drive the fan 5 until the predetermined air sending flow rate is obtained.

[0026]

Note that, needless to say, for the controller 7, an interchange with anything, other than the microcomputer, capable of providing the similar effects is possible. Moreover, the controller 7 may be provided to any one of the indoor unit and the outdoor unit, or both.

[0027]

Next, description will be given of the way to obtain various kinds of values shown in the refrigeration cycle diagram in Fig. 2. The controller 7 performs computation of the condenser temperature on the basis of the condenser pressure PCm obtained by the pressure measuring sensor 8 by using the data of refrigerant properties stored in the memory. Moreover, the controller 7 performs computation of the degree of subcooling SCm on the basis of the condenser outlet temperature obtained by the temperature measuring sensor 9 and the condenser temperature. [0028]

The controller 7 performs computation of the evaporator pressure Pe on the basis of the heat exchanger temperature Te obtained by the temperature measuring sensor 10 by using the data of refrigerant properties stored in the memory. The evaporator pressure Pe is used for calculating the refrigerant circulation amount Gr. [0029]

The refrigerant circulation amount Gr is represented as the following expression (1) by the displacement volume V of the compressor 1 and the density p of the refrigerant to be compressed.

[0030]

Gr = Vxp ... (1)

Here, the displacement volume V of the compressor is determined by the used compressor, and computation of the density p of the refrigerant to be compressed is performed by the controller 7 on the basis of the evaporator pressure Pe from the data of refrigerant properties stored in the memory.

[0031]

The controller 7 performs computation of the degree of superheat SHm on the basis of the evaporator outlet temperature obtained by the temperature measuring sensor 11 and the above-described heat exchanger temperature Te. Moreover, the controller 7 performs computation of intake air enthalpy on the basis of the dry-bulb temperature and the wet-bulb temperature of air obtained by the intake air status measuring sensor 12 and the data of air properties stored in the memory.

[0032]

Note that, needless to say, the refrigerant used in the air-conditioning apparatus is the one usable in the refrigeration cycle. For example, the refrigerant may be a single refrigerant, such as R22, a mixed refrigerant, such as R410A, or a natural refrigerant, such as CO2.

[0033]

Moreover, the air-conditioning apparatus is unnecessary to be configured only with the members shown in Fig. 1. For example, a reservoir (accumulator) may be provided for protecting the compressor 1, or an oil separator may be provided for reclaiming refrigerating machine oil.

[0034]

Next, with reference to Fig. 3, operations of the air-conditioning apparatus according to the embodiment will be described. Fig. 3 is a flowchart showing a flow of processing in a cooling operation of the air-conditioning apparatus.

[0035]

The controller 7 determines whether or not an air sending flow rate, which is set on the basis of a set evaporating ability Qe and an air sending flow rate GA, is obtained (steps S1 to S3), and when the air sending flow rate is away from the set air sending flow rate (NO in step S4), the controller 7 adjusts the air sending flow rate and changes the refrigeration cycle to satisfy the evaporating ability Qe (steps S5 to S7).

[0036]

The evaporating ability Qe is represented as the following expression (2) by use of the refrigerant circulation amount Gr and a difference in evaporator inlet-outlet enthalpy ΔΗγ.

[0037]

Qe = Grx ΔΗγ ... (2)

Here, as the difference in evaporator inlet-outlet enthalpy ΔΗγ is a value restricted by the refrigerant, hereinafter, as an example, a case of using R410A is shown. From a standpoint of unit protection, a general value of ΔΗγ is of the order of 150 kJ/kg to 200 kJ/kg. Thus, for example, ΔΗγ is controlled to be 175 kJ/kg.

[0038]

Moreover, the standard outdoor temperature is generally of the order of 35 degrees C, and when the condenser 2 is placed outdoors and provided to exchange heat with air, the condenser 2 is required to have the temperature of 35 degrees C or more to exchange heat. The larger difference in temperature is more preferred; however, as the condenser pressure PCm of the order of 30 kgf/Cm²G is desirable from the standpoint of unit protection, the control is performed to have the pressure.

At this time, the temperature of the condenser is of the order of 50 degrees C.

[0039]

The evaporator outlet enthalpy Hro is also restricted by the refrigerant. From the standpoint of unit protection, the value of the enthalpy is almost the same within a range of available pressure and degree of superheat, and is of the order of 425 KJ/kg. [0040]

As a result of the above, evaporator inlet enthalpy Hri can be determined as follows.

Hri = Hro - ΔΗγ = 425 KJ/kg - 175 KJ/kg = 250 KJ/kg

As PCm is 30 kgf/Cm²G, the refrigerant temperature at the outlet of the condenser has to be 31 degrees C.

[0041]

In other words, as the temperature of the condenser 2 is 50 degrees C, the target degree of subcooling SCm is as follows.

SCm = 50 degrees C - 31 degrees C = 19 degrees C [0042]

From the standpoint of unit protection, the target degree of superheat SHm is preferably of the order of 2 degrees C to 5 degrees C. Here, the degree of superheat is set at 2 degrees C.

[0043]

When the evaporating ability Qe is, for example, 28 kW, from the above, Gr is obtained as follows.

Gr = Qe / AHr = 28kW/175 kJ/kg = 0.16 kg/s

Consequently, the compressor 1 is to be controlled to satisfy Gr. For example, in a case of rotation frequency control type, the frequency is to be changed.

[0044]

Only one refrigeration cycle can make the above-described status viable.

Until such a refrigeration cycle is obtained, the controller 7 is caused to perform computation on the basis of the data of the pressure measuring sensor 8 and the temperature measuring sensors 9 to 11 to control the compressor 1 and the expansion valve 3, and the heat exchanger temperature at this time is assumed to be Te. The refrigeration cycle at this time is shown in Fig. 4.

[0045]

The difference in temperature required to bring the refrigerant circulation amount Gr of the refrigerant flowing to the evaporator into the state of degree of superheat SHm is determined by the heat exchange efficiency ε. This is because the higher the efficiency of the heat exchanger is, the more the refrigerant is evaporated. Moreover, the efficiency of the heat exchanger is determined by the size of the heat exchanger and the air sending flow rate. The larger the heat exchanger is and the more the air sending flow rate is, the higher the efficiency of the heat exchanger becomes. By the heat exchange efficiency ε and the air sending flow rate GA, the efficiency of the heat exchanger is represented as GA x ε.

[0046]

The evaporating ability is represented as the following expression (3) by use of the heat exchange efficiency.

[0047]

Qe = GA x ε x AhA... (3)

Here, Qe is evaporating ability, GA is an air sending flow rate, ε is heat exchange efficiency, and AhA is difference in air enthalpy.

[0048]

As shown in the air diagram in Fig. 5, the difference in enthalpy is the difference in enthalpy when the air in the state A changes to the air in the state C, which indicates that the intake air is completely cooled to the heat exchanger temperature. However, in actuality, not all the intake air is cooled to the heat exchanger temperature, and only the state B in Fig. 5 can be obtained. At this time, the difference in enthalpy between the state A and the state B is represented by ε x AhA.

[0049]

As described above, the efficiency of the heat exchanger is determined by the size of the heat exchanger and the air sending flow rate. The relationship between the heat exchange efficiency ε and the air sending flow rate GA can be grasped in advance by desktop calculations or experiments. The relationship shown in Table 1 is obtained for each heat exchanger, and the data on the table is stored in the memory of the controller 7, to thereby determine the air sending flow rate. Note that a table, such as Table 1, is not mandatory and the relationship may be provided by an approximate expression.

[0050]

A case is assumed where the evaporating ability Qe is 28 kW and the air sending flow rate GA is 60 m³/min. From the above-described Table 1, the controller 7 is caused to perform computation of ε resulting in 0.69. At this time, AhA is as follows.

AhA = Qe / (GA x ε) = 28 kW/ ((60 m³/min 160 10.83 m³/kg) x 0.69) = 33.7 kJ/kg

Here, the reason why division by 60 and 0.83 m³/kg is made is to perform unit conversion from the volume flow rate into the mass flow rate. Moreover, in general, 0.83 m³/kg is a specific volume of air.

[0051]

A case is assumed where, by the intake air status measuring sensor 12, the state A of the intake air is found to be 27 degrees C in the dry-bulb temperature and 19 degrees C in the wet-bulb temperature. At this time, from the air properties, computation of the enthalpy hAA of the state A can be performed to result in 53.8 kJ/kg by the controller 7, and consequently, the enthalpy hAC of the state C is as follows.

hAC = hAA - AhA = 53.8 kJ/kg - 33.7 kJ/kg = 20.1 kJ/kg

From the data of air properties stored in the memory of the controller 7, computation of the heat exchanger temperature Te_cal can be performed to result in 5.8 degrees C. The air diagram at this time is shown in Fig. 6.

[0052]

Here, Te obtained by the intake air status measuring sensor 12 and Te_cal obtained by computation are compared. Taking account of accuracy of general temperature sensors, when a difference between Te and Te_cal is 0.5 degrees C or more, the air sending flow rate is determined to be different from the set value. As a matter of course, the accuracy is different by sensors, and thus, the determination value may be other than 0.5 degrees C.

[0053]

A case is assumed where the refrigeration cycle as shown in Fig. 7 is stable and Te is 5 degrees C, as Te_cal is 5.8 degrees C, Te is lower by 0.8 degrees C.

This case indicates that the efficiency of the heat exchanger is lower than the efficiency obtained from the set air sending flow rate. In other words, the actual air sending flow rate is smaller than the set air sending flow rate, and the air sending flow rate has to be increased by increasing the rotation frequency of the fan 5.

[0054]

To the contrary, a case is assumed where the refrigeration cycle as shown in 5 Fig. 8 is stable and Te is 7 degrees C, Te is higher by 1.2 degrees C, indicating that the efficiency of the heat exchanger is higher than the efficiency obtained from the set air sending flow rate. Consequently, the air sending flow rate has to be reduced by decreasing the rotation frequency of the fan 5.

[0055]

As the refrigeration cycle is changed by varying the air sending flow rate, the air sending flow rate can be adjusted to the set value every time the value of Te is confirmed.

[0056]

Note that, in the embodiment, description is given only to the evaporator;

however, needless to say, in the case of the condenser, the air sending flow rate can be adjusted by following the same idea.

Reference Signs List [0057] compressor 2 condenser 3 expansion valve 4 evaporator

5 fan 6 motor 7 controller 8 pressure measuring sensor 9 to 11 temperature measuring sensor 12 intake air status measuring sensor

Claims

CLAIMS [Claim 1]

An air-conditioning apparatus comprising:

a refrigerant circuit in which a compressor configured to compress refrigerant, a 5 condenser configured to condense refrigerant, an expansion valve configured to reduce pressure of refrigerant, and an evaporator configured to evaporate refrigerant are connected by a pipe to circulate refrigerant;

an air-sending device configured to send air to the evaporator; and a controller configured to control operations of the compressor, the expansion

10 valve, and the air-sending device, the controller storing data indicating a relationship between an air sending flow rate and a heat exchange efficiency of the condenser and the evaporator in a memory of the controller, the controller being configured to calculate an air sending flow rate of the air15 sending device from the heat exchange efficiency and a status of a refrigeration cycle on a basis of the data.

[Claim 2]

The air-conditioning apparatus of claim 1, wherein, in the air-sending device, a fan and a motor are directly connected.

20 [Claim 3]

The air-conditioning apparatus of claim 1, wherein, in the air-sending device, a fan and a motor are indirectly connected via a pulley or a belt.

INTERNATIONAL SEARCH REPORT International application No. PCT/JP2015/062476 A. CLASSIFICATION OF SUBJECT MATTER F24 FI 1/02(200 6.01)i, F24F11/04(200 6.01) i, F24F11/053(2006 .01) i According to International Patent Classification (IPC) or to both national classification and IPC B. FIELDS SEARCHED Minimum documentation searched (classification system followed by classification symbols) F24F11/02, F24F11/04, F24F11/053 Documentation searched other than minimum documentation to the extent that such documents are included in the fields searched Jitsuyo Shinan Koho 1922-1996 Jitsuyo Shinan Toroku Koho 1996-2015 Kokai Jitsuyo Shinan Koho 1971-2015 Toroku Jitsuyo Shinan Koho 1994-2015 Electronic data base consulted during the international search (name of data base and, where practicable, search terms used) C. DOCUMENTS CONSIDERED TO BE RELEVANT Category* Citation of document, with indication, where appropriate, of the relevant passages Relevant to claim No. Y JP 8-86489 A (Toshiba Corp.) 02 April 1996 (02.04.1996), paragraphs [0032] to [0068]; (Family: none) r fig. 1 to 7 1-3 Y JP 2002-22245 A (Daikin Industries, Ltd 23 January 2002 (23.01.2002), paragraph [0020] (Family: none) • ) , 1-3 Y JP 2007-33003 A (Fujitsu General Ltd.), 08 February 2007 (08.02.2007), claim 3 (Family: none) 2 1 ^x 1 Further documents are listed in the continuation of Box C. 1 1 See patent family annex. * Special categories of cited documents: “A” document defining the general state of the art which is not considered to be of particular relevance “E” earlier application or patent but published on or after the international filing date “L” document which may throw doubts on priority claim(s) or which is cited to establish the publication date of another citation or other special reason (as specified) “O” document referring to an oral disclosure, use, exhibition or other means “P” document published prior to the international filing date but later than the priority date claimed “T” later document published after the international filing date or priority date and not in conflict with the application but cited to understand the principle or theory underlying the invention “X” document of particular relevance; the claimed invention cannot be considered novel or cannot be considered to involve an inventive step when the document is taken alone “Y” document of particular relevance; the claimed invention cannot be considered to involve an inventive step when the document is combined with one or more other such documents, such combination being obvious to a person skilled in the art document member of the same patent family Date of the actual completion of the international search 10 July 2015 (10.07.15) Date of mailing of the international search report 21 July 2015 (21.07.15) Name and mailing address of the ISA/ Japan Patent Office 3-4-3,Kasumigaseki, Chiyoda-ku, Tokvo 100-8915, Japan Authorized officer Telephone No.

FormPCT/ISA/210 (second sheet) (July 2009)