JP4551184B2 - Air intake duct - Google Patents

Description

  The present invention relates to an air intake duct, and more specifically, an air suction portion having an air suction port, and extends in a direction crossing the air suction direction of the air suction portion, and is connected to a blower at one end thereof. The present invention relates to an intake duct including an air outlet portion having an air outlet.

  For example, automobiles produced in recent years are equipped with various air conditioning facilities in order to improve the comfort in the passenger compartment. In particular, some grades of luxury cars employ a seat S that incorporates a seat air conditioning system AC, as illustrated in FIG. 15, and the temperature-controlled air controlled by the seat air conditioning system AC is used. It is considered to improve passenger comfort by blowing out from the seat surface like a shower. This seat air conditioning system AC is basically composed of an intake duct D1, a blower BW such as a blower, a heat exchanger H such as a Peltier element, and an air outlet pipe P that sends out conditioned air to the surface of the seat S. .

Here, the seat air conditioning system AC must be designed to be small and compact so that it can be accommodated inside the seat S due to restrictions on the internal structure and internal space of the seat S. In order to maximize the heat exchange efficiency, it is considered that the air suction port 10 of the intake duct D1 is positioned above the side portion of the seat S to efficiently take in air in the passenger compartment. Thus, the intake duct D1 extends in a direction substantially intersecting with the air suction direction of the air suction portion 20 and the air suction direction of the air suction portion 20 depending on the arrangement position of the blower BW and the like. And it is the substantially L-shaped bending duct which consists of the air derivation | leading-out part 22 which has the air delivery port 12 connected to the air blower BW in the one end part. Such a technique is disclosed in, for example, Patent Document 1.
JP 2004-82958 A

  By the way, in the seat air conditioning system AC described above, the air suction port 10 of the intake duct D1 opens at a portion close to the ear of an occupant (not shown) seated on the seat S. For this reason, the operating noise of the motor of the blower BW and the operation noise such as the intake noise enter the inside of the intake duct D1 through the air outlet 12 connected to the air intake port 14 of the blower BW, If it propagates through the duct and leaks out of the air suction port 10 into the passenger compartment, there is a disadvantage that it is heard directly by the passenger seated on the seat S. Therefore, as illustrated in FIG. 16, a sound absorbing sheet W such as a urethane sheet is attached to the inside of the intake duct D1, and the above-described countermeasure for absorbing the noise has been taken.

  However, as described above, since the intake duct D1 is small (cannot be increased in size due to restrictions on the internal structure of the sheet S), it is impossible to stick the sound absorbing sheet W having a thickness required for sound absorption. There is a problem that a sufficient sound absorbing effect cannot be obtained because the thin sound absorbing sheet W has to be stuck. Further, by sticking the sound absorbing sheet W, the effective cross-sectional area of the intake duct D1 is reduced, and there is a problem that the ventilation resistance is increased and the necessary air volume cannot be secured. Furthermore, since the material cost of the sound absorbing sheet W and the number of pasting steps increase, problems such as an increase in molding cost are pointed out.

  Accordingly, an object of the present invention is to provide an intake duct that is provided with a reflection wall that reflects noise that has entered the duct from the blower and that reduces the noise.

In order to solve the above-mentioned problems and achieve the intended purpose, the present invention provides:
In an intake duct disposed in the seat as a component of a seat air conditioning system that sends out temperature-controlled air from the surface of the seat,
An air suction part having an air suction port that opens to the outside of the sheet above the side of the sheet;
An air outlet portion extending in a direction intersecting with the air suction direction of the air suction portion and having an air outlet connected to a blower device at one end thereof;
On the other end portion of the air outlet portion facing the air suction portion, a space portion provided to extend to the side opposite to the air blower side;
The wall portion constituting the space portion is formed so as to be opposed to the air outlet in the axial direction of the air outlet portion and to intersect the axis line, and reflects noise of the blower that propagates in the air outlet portion. Consisting of a reflective wall to get and
The space portion is formed so as to expand from an edge of the air suction portion toward the reflection wall,
The reflection wall is provided in a range of 15 to 30 mm from an edge of the air suction portion in the axial direction of the air lead-out portion , and an area of the reflection wall is perpendicular to the axis of the air lead-out portion. It is characterized by being set larger than the effective sectional area .
Therefore, according to the intake duct according to the present invention, by reflecting the noise of the air blower propagating in the air outlet part by the reflecting wall, among the noise propagating to the air suction port opened above the side part of the seat, In particular, there is a beneficial effect that can effectively reduce noise of 1,500 to 4,000 Hz that humans feel uncomfortable. And since it is not necessary to stick a sound-absorbing material such as a sound-absorbing sheet inside, there is an advantage that an increase in ventilation resistance can be prevented and an air volume can be secured. In addition, since the area of the reflection wall is larger than the effective cross-sectional area of the air outlet, efficient reflection of noise that has propagated through the intake duct and arrived at the reflection wall is expected. Further, since the reflecting wall is integrally formed when the intake duct is formed, there is an advantage that the material cost and the man-hour are not increased, and the forming cost is not increased.

Similarly, another invention to solve the above-mentioned problem and achieve the intended purpose is as follows:
In an intake duct disposed in the seat as a component of a seat air conditioning system that sends out temperature-controlled air from the surface of the seat,
An air suction part having an air suction port that opens to the outside of the sheet above the side of the sheet;
An air outlet portion extending in a direction intersecting with the air suction direction of the air suction portion and having an air outlet connected to a blower device at one end thereof;
On the other end portion of the air outlet portion facing the air suction portion, a space portion provided to extend to the side opposite to the air blower side;
The wall portion constituting the space portion is formed so as to be opposed to the air outlet in the axial direction of the air outlet portion and to intersect the axis line, and reflects noise of the blower that propagates in the air outlet portion. Consisting of a reflective wall to get and
The reflection wall is formed on a slide body slidably mounted on a main body including the air suction part and the air introduction part,
The slide body is slid with respect to the main body, and the distance from the edge of the air suction part to the reflecting wall in the axial direction of the air outlet part is within a range of 15 to 30 mm from the edge of the air suction part. It is configured to be adjustable .
Therefore, according to the intake duct according to another invention, the noise of the air blower propagating in the air outlet portion is reflected by the reflecting wall, so that the noise that propagates to the air suction opening that opens above the side portion of the seat In particular, there is a beneficial effect that can effectively reduce noise of 1,500 to 4,000 Hz, which is particularly uncomfortable for humans. And since it is not necessary to stick a sound-absorbing material such as a sound-absorbing sheet inside, there is an advantage that an increase in ventilation resistance can be prevented and an air volume can be secured. Further, the frequency band to be reduced can be changed by sliding the slide body relative to the main body and adjusting the distance from the edge of the air suction portion to the reflection wall.

  Next, an intake duct according to the present invention will be described below with reference to the accompanying drawings by way of preferred embodiments. Note that the intake ducts targeted by the present application are all those that are connected to the air intakes of various devices, blowers, etc. that generate operating noise. The air intake duct which comprises seat air-conditioning system AC is illustrated. Accordingly, the same members and parts as those already described in FIGS. 15 and 16 will be described with the same reference numerals.

  FIG. 1 is an explanatory view showing an intake duct according to a preferred embodiment with a part thereof broken to show the configuration thereof, and FIG. 2 is a schematic perspective view of the intake duct. The air intake duct D of the present embodiment extends in a direction substantially perpendicular to the air suction direction of the air suction portion 20 and the required length of the air suction portion 20 having the air suction port 10 and is provided at one end thereof. The air outlet 12 is a bent duct comprising an air outlet 22 connected to the air intake 14 of the blower BW. Such an intake duct D is an injection molded member having a thickness of about 1 mm made of, for example, high density polyethylene (HDPE).

The air suction portion 20 has a rectangular tube shape, and the air suction port 10 opened at the front end (front end) of the air suction portion 20 has a rectangular shape of about 40 mm × 30 mm, and the opening area A1 is about 120 mm ² . Is set. The air outlet 22 also has a rectangular tube shape, and the air outlet 12 opened at the front end (rear end) of the air outlet 22 is set to about 120 mm ² which is substantially the same as the air suction port 10 described above. . The rear end of the air outlet 22 is formed in a circular shape having a diameter d so as to match the shape of the air intake port 14 of the blower BW. Here, the length L1 of the air suction part 20 is set to about 30 mm, and the length L2 of the air lead-out part 22 is set to about 60 mm. The air lead-out part 22 is longer.

  In the intake duct D of the present embodiment, the other end portion of the air outlet portion 22 facing the air suction portion 20 (continuously connected to the air suction portion 20) is based on the conventional substantially L-shaped intake duct D1 illustrated in FIG. The space 24 provided to extend to the side opposite to the air blower BW side, and a part of the wall that constitutes the space 24 and intersects the axis of the air outlet 22. In addition, a reflection wall 26 capable of reflecting the noise of the blower BW propagating through the air outlet 22 is added. In other words, the space 24 is defined by extending the air lead-out portion 22 by a required length to the opposite side of the air delivery port 12 with the air suction portion 20 interposed therebetween, and the reflection wall described above is formed at the tip portion thereof. 26 is formed.

  The reflection wall 26 is formed in a direction that intersects at right angles to the axis along the longitudinal direction of the air outlet portion 22. As a result, the noise of the blower BW that enters the intake duct D from the air outlet 12 and propagates through the air derivation unit 22 becomes a reflected sound in the opposite direction after being reflected by the reflection wall 26, and again the air derivation unit 22. The inside is reflected to the blower BW side. Accordingly, the noise propagating to the air suction port 10 side can be reduced.

  The extension length of the space 24, that is, the distance X from the end of the air suction unit 20 to the reflection wall 26 is a frequency that is particularly uncomfortable for humans among noises generated from the blower BW. It is set on the premise that noise of ˜4,000 Hz is effectively reduced. Specifically, the distance X is set in the range of 15 to 30 mm based on the results of experiments conducted by the inventor described later. That is, by setting the distance X from the end of the air suction unit 20 to the reflection wall 26 to 15 to 30 mm, the noise of 1,500 to 4,000 Hz generated from the blower BW is reflected by the reflection wall 26, Sound leakage to the air suction port 10 can be reduced.

  3 to 10 are graphs summarizing the results of the experiment conducted by the inventor of the present application, and relate to the intake duct D (length L2 = 60 mm) of the present embodiment illustrated in FIG. The sound pressure level for each frequency in the air suction port 10 when the distance X from the end portion to the reflection wall 26 is changed is the sound pressure level for each frequency of the conventional intake duct D1 illustrated in FIG. It is compared with. Table 1 summarizes these experimental data. 3 is set to the distance X = 5 mm, FIG. 4 is set to the distance X = 10 mm, and FIG. 5 is set to the distance X = 15 mm. 6 is set to a distance X = 20 mm, FIG. 7 is set to a distance X = 25 mm, FIG. 8 is set to a distance X = 30 mm, and FIG. 9 is set to a distance X = 35 mm. FIG. 10 is a graph showing the sound pressure level of each frequency when the distance X is set to 40 mm.

  In the case where the distance X is set to 5 mm, as illustrated in FIG. 3, as compared to the conventional intake duct D1, there is almost no decrease in sound pressure level in all frequency bands including 1,500 Hz to 4,000 Hz. I can't. This means that most of the noise of the blower BW comes to the air suction port 10 side without being reduced, and that the effect of providing the space 24 and the reflection wall 26 is small. Show.

  In the case where the distance X is set to 10 mm, as illustrated in FIG. 4, in the frequency band of 500 Hz to 1,000 Hz, 1,500 Hz to 2,000 Hz, and 3,000 Hz or more, as compared to the conventional intake duct D1. A slight decrease in the sound pressure level can be confirmed. However, the sound pressure level does not decrease at all at around 2500 Hz. This means that intermediate noise at 1,500 Hz to 4,000 Hz is not reduced at all, and average reduction of noise at 1,500 Hz to 4,000 Hz cannot be achieved.

  When the distance X is set to 15 mm, as illustrated in FIG. 5, the sound pressure level is higher in the frequency bands of 500 Hz to 1,000 Hz and 1,500 Hz to 4,000 Hz than the conventional intake duct D1. It can be evaluated that it has decreased suitably. In particular, in the frequency band of 3,000 Hz to 4,000 Hz, the sound pressure level is reduced by about 6 dB, and it can be confirmed that noise in this frequency band can be efficiently reduced.

  When the distance X is set to 20 mm, as illustrated in FIG. 6, the sound pressure level is higher in the frequency bands of 500 Hz to 1,000 Hz and 1,500 Hz to 4,000 Hz than the conventional intake duct D1. It can be evaluated that it has decreased suitably. In particular, in the frequency band of 2,400 Hz to 3,500 Hz, that is, around 3,000 Hz, the sound pressure level is reduced by about 8 dB, and it can be confirmed that noise in this frequency band can be efficiently reduced.

  Even when the distance X is set to 25 mm, as illustrated in FIG. 7, the sound pressure level is higher in the frequency bands of 500 Hz to 1,000 Hz and 1,500 Hz to 4,000 Hz than the conventional intake duct D1. It can be evaluated that it has decreased suitably. In particular, in the frequency band of 2,000 Hz to 3,000 Hz, the sound pressure level is reduced by about 7 dB, and it can be confirmed that noise in this frequency band can be reduced extremely efficiently.

  When the distance X is set to 30 mm, as illustrated in FIG. 8, the sound pressure level is higher in the frequency bands of 500 Hz to 1,000 Hz and 1,500 Hz to 3,500 Hz than the conventional intake duct D1. It can be evaluated that it has decreased suitably. In particular, the sound pressure level is reduced by about 7 to 10 dB in the frequency band of 1,700 Hz to 2500 Hz, and it can be confirmed that noise in this frequency band can be reduced extremely efficiently.

  When the distance X is set to 35 mm, the sound pressure level is suitably reduced in the frequency bands of about 500 Hz and about 800 Hz, and about 2,000 Hz as compared to the conventional intake duct D1, as illustrated in FIG. You can evaluate that you are doing. In particular, in the frequency band around 2,000 Hz, the sound pressure level is greatly reduced by 10 dB or more. However, since the sound pressure level is hardly lowered in the frequency band of 2,300 Hz or higher, and there is no effect in reducing the noise in the higher frequency band, noise in the frequency band of 1,500 Hz to 4,000 Hz. If it is premised on reducing this, it must be judged as inappropriate.

  When the distance X is set to 40 mm, as exemplified in FIG. 10, the sound pressure level is suitably reduced in the frequency band of 1,500 Hz to 2,000 Hz as compared to the conventional intake duct D1. Can be evaluated. However, the sound pressure level has rather increased in the frequency band of 2,300 Hz to 4,000 Hz. Accordingly, it is determined to be inappropriate when it is assumed that noise in the frequency band of 1,500 Hz to 4,000 Hz is reduced.

  From the above experimental results, when it is assumed that noise of a frequency (1,500 to 4,000 Hz) that humans feel uncomfortable is effectively and averagely reduced, the extension length of the space portion 24, that is, air suction. It has been found that the distance X from the end of the portion 20 to the reflecting wall 26 is desirably set within a range of 10 mm to 30 mm, preferably within a range of 15 mm to 30 mm. When the distance X is set to 15 mm, a frequency band of 3,000 Hz to 4,000 Hz is set. When the distance X is set to 20 mm, a frequency band of 2,400 Hz to 3,500 Hz is set to a distance X = 25 mm. In this case, it was confirmed that noise in the frequency band of 2,000 Hz to 3,000 Hz and the frequency band of 1,700 Hz to 2,500 Hz can be efficiently reduced when the distance X is set to 30 mm. For this reason, it is desirable to set the distance X to a small value within the range of 15 mm to 30 mm in order to reduce the noise in the high frequency band more seriously within the range of 1,500 to 4,000 Hz. When it is desired to reduce noise in a low frequency band more seriously, it can be said that it is desirable to set the distance X to be larger within a range of 15 mm to 30 mm.

  FIG. 11 shows an intake duct D having a structure in which the distance X from the end of the air suction unit 20 to the reflection wall 26 can be changed and adjusted. In other words, the intake duct D is composed of a main body 30 composed of the air suction part 20 and the air lead-out part 22 and a slide body 32 that forms the reflection wall 26 described above and is separate from the main body 30. 32 is slidably attached to the main body 30. Therefore, if the slide body 32 is appropriately slid as necessary and the distance X is adjusted within a range of 15 mm to 30 mm, the frequency band to be reduced can be changed.

  FIG. 12 shows the intake duct D having a structure in which the reflection wall 26 described above is formed from a member 34 having a higher density than the material of the intake duct D, such as a metal plate or a glass plate. Since the intake duct D illustrated in FIG. 1 is made of high-density polyethylene (HDPE), if the reflecting wall 26 is formed of this material, it is possible to sufficiently reflect noise. When the reflection wall 26 is formed by the member 34, the noise reflection efficiency can be further increased. In particular, when the intake duct D is formed from a low-density material different from high-density polyethylene, it is effective to mount this member 34. FIG. 11 illustrates the case where the member 34 is disposed on the inner side facing the space 24, but the member 34 may be disposed on the outer side.

  Further, FIG. 13 illustrates an intake duct D in which a wall portion forming the space portion 24 is formed so as to expand in the direction of the reflection wall 26. As a result, the area of the reflection wall 26 is larger than the effective cross-sectional area of the air outlet 22, so that more efficient reflection of noise that has propagated through the duct and arrived at the reflection wall 26 can be expected.

  FIG. 14 illustrates an intake duct D in which a multistage reflecting wall 26 having a plurality of reflecting regions 36, 38, and 40 set at different distances X1, X2, and X3 from the edge of the air suction unit 20 is formed. It is a thing. In this case, for example, if the distance X1 of the reflection region 36 is set to 15 mm, the distance X2 of the reflection region 38 is set to 20 mm, the distance X3 of the reflection region 40 is set to 30 mm, etc., different frequency bands for the respective reflection regions 36, 38, 40. Therefore, it is possible to reduce noise in a wide frequency band. In addition, although the case where it formed in three steps was illustrated in FIG. 7, this number of steps is not limited to this.

  As described above, in the intake duct D of the present embodiment, the space 24 is provided at the other end of the air outlet 22 facing the air suction part 20 so as to extend to the side opposite to the blower BW side. Air that propagates through the air outlet 22 through the air outlet 12 by providing the reflecting wall 26 formed from a part of the wall constituting the portion 24 so as to intersect the axis of the air outlet 22 The noise propagating to the air suction port 10 can be suitably reduced by reflecting the noise of the device BW. Therefore, in the seat air conditioning system AC in which the intake duct D is implemented, even if the air suction port 10 of the intake duct D faces above the side portion of the seat S on which an occupant is seated, the unpleasant sensation emitted from the blower BW Noise is suitably reduced in the duct so as not to leak out from the air suction port 10, and there is a beneficial effect that can preferably prevent discomfort to the passenger. And it is no longer necessary to paste a sound absorbing sheet W like the conventional intake duct D1 illustrated in FIG. 9 and the effective cross-sectional area of the intake duct D is not reduced. Secured. Further, since the reflecting wall 26 is integrally formed when the intake duct D is formed, the material cost and the man-hour are not increased, and the forming cost is not increased.

  In the above-described embodiment, the air intake duct implemented in the seat air conditioning system AC built in the seat S is illustrated, but the air intake duct targeted by the present application is not limited to this and is installed in various devices. What is to be targeted.

  An air intake duct according to the present invention has an air suction portion having an air suction port, and an air delivery port extending in a direction intersecting the air suction direction of the air suction portion and connected to a blower at one end thereof. It comprises an air outlet and can be suitably implemented in various devices such as a seat air conditioning system for seats installed in passenger cars.

It is explanatory drawing which fractured | ruptured and showed the intake duct which concerns on the suitable Example of this invention in order to show the structure. It is a schematic perspective view of an intake duct. The sound pressure level for each frequency in the intake duct of this embodiment when the distance from the end of the air suction part to the reflecting wall is set to 5 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. The sound pressure level for each frequency in the intake duct of the present embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 10 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. The sound pressure level for each frequency in the intake duct of the present embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 15 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. The sound pressure level for each frequency in the intake duct of this embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 20 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. FIG. 15 is a graph comparing the sound pressure level for each frequency in the intake duct of the present embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 25 mm with the level of the conventional intake duct illustrated in FIG. It is. The sound pressure level at each frequency in the intake duct of the present embodiment when the distance from the end of the air suction portion to the reflection wall is set to 30 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. The sound pressure level at each frequency in the intake duct of this embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 35 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. The sound pressure level for each frequency in the intake duct of this embodiment when the distance from the end of the air suction portion to the reflecting wall is set to 40 mm is compared with the sound pressure level of the conventional intake duct illustrated in FIG. It is a graph. It is explanatory drawing partially broken and shown in order to show the structure of the air intake duct which concerns on the example of a change. It is explanatory drawing partially broken and shown in order to show the structure of the intake duct which concerns on another example of a change. It is explanatory drawing partially broken and shown in order to show the structure of the intake duct which concerns on another example of a change. It is explanatory drawing partially broken and shown in order to show the structure of the intake duct which concerns on another example of a change. It is a schematic explanatory drawing of the seat air conditioning system which has an air intake duct. It is explanatory drawing which fractured | ruptured and showed the conventional intake duct in order to show the structure.

Explanation of symbols

10 air suction port 12 air outlet 20 air suction part 22 air outlet unit 24 the space portion 26 the reflecting wall 30 body 32 slide body 34 dense part material
B W Blower AC Seat air conditioning system S Seat
X distance

Claims (4)

In the intake duct disposed in the seat (S) as a component of the seat air conditioning system (AC) that sends out the conditioned air from the surface of the seat (S),
An air suction part (20) having an air suction port (10) that opens to the outside of the sheet above the side of the sheet (S);
An air outlet part (22) having an air outlet (12) extending in a direction intersecting with the air suction direction of the air suction part (20) and connected to a blower (BW) at one end thereof;
On the other end of the air outlet part (22) facing the air suction part (20), a space part (24) provided to extend to the side opposite to the air blower (BW) side,
The wall portion constituting the space portion (24) is formed to face the air outlet (12) in the axial direction of the air outlet portion (22) so as to intersect the axis line, and the air outlet portion (22 ) And a reflection wall (26) capable of reflecting the noise of the blower (BW) propagating in the interior,
The space portion (24) is formed so as to expand from the edge of the air suction portion (20) toward the reflection wall (26),
The reflection wall (26) is provided in the range of 15 to 30 mm from the edge of the air suction part (20) in the axial direction of the air outlet part (22) , and the area of the reflection wall (26) is An intake duct, wherein the intake duct is set to be larger than an effective cross-sectional area in a direction orthogonal to the axis of the air outlet portion (22) . In the intake duct disposed in the seat (S) as a component of the seat air conditioning system (AC) that sends out the conditioned air from the surface of the seat (S),
An air suction part (20) having an air suction port (10) that opens to the outside of the sheet above the side of the sheet (S);
An air outlet part (22) having an air outlet (12) extending in a direction intersecting with the air suction direction of the air suction part (20) and connected to a blower (BW) at one end thereof;
On the other end of the air outlet part (22) facing the air suction part (20), a space part (24) provided to extend to the side opposite to the air blower (BW) side,
The wall portion constituting the space portion (24) is formed to face the air outlet (12) in the axial direction of the air outlet portion (22) so as to intersect the axis line, and the air outlet portion (22 ) And a reflection wall (26) capable of reflecting the noise of the blower (BW) propagating in the interior,
The reflection wall (26) is formed in a slide body (32) slidably mounted on a main body (30) comprising the air suction part (20) and the air introduction part (22),
The slide body (32) is slid relative to the main body (30), and the distance from the edge of the air suction part (20) to the reflection wall (26) in the axial direction of the air outlet part (22) (X) is configured to be adjustable within a range of 15 to 30 mm from the edge of the air suction part (20).
An intake duct characterized by that . The intake duct according to claim 1 or 2, wherein the reflection wall (26) intersects the axis of the air outlet portion (22) at a right angle . The intake duct according to any one of claims 1 to 3, wherein the reflection wall (26) is formed of a member (34) having a higher density than the duct body .

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