KR100869926B1 - compressor - Google Patents

Abstract

The compressor of the present invention includes a hermetically sealed container containing oil, a drive motor mounted in the hermetically sealed container, a cylinder mounted in the hermetically sealed container, an outer gear inserted into the cylinder and having gears formed on an inner circumferential surface thereof, and gears formed on an outer circumferential surface thereof. And an inner gear rotatably inserted in the outer gear to form a plurality of compression spaces with the outer gears, upper and lower bearings respectively coupled to both sides of the cylinder to seal the compression spaces, and the drive And a rotation shaft for transmitting the rotational force of the motor to the inner gear, and oil supply means for circulating and supplying the oil between the cylinder and the outer gear in accordance with the rotation of the rotation shaft. As a result, as the drive motor rotates once every two gears engage and rotate, the compressed gas is discharged a plurality of times and the wear of the two gears and the parts moving relative to the gears can be minimized. .

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor, and in particular, as the drive motor rotates once every two gears are engaged and rotated to discharge the compressed gas many times, as well as the wear of the two gears and the parts moving relative to the gears. It is about a compressor to minimize the.

Generally, a compressor converts electrical energy into kinetic energy and compresses refrigerant gas by the kinetic energy. Compressors are a key component of the refrigeration cycle system, and there are various types of compressors, such as rotary compressors, scroll compressors, and reciprocal compressors, depending on a compression mechanism for compressing refrigerant. Such compressors are used in refrigerators, air conditioners and showcases.

In the rotary compressor, the rotational force of the driving motor is transmitted to the rotary shaft, and the rotary shaft rotates, and the eccentric portion provided on one side of the rotary shaft rotates in the compression space of the cylinder block according to the rotation of the rotary shaft. As the eccentric portion rotates in the compression space of the cylinder block, the refrigerant gas is sucked, compressed and discharged while changing the volume of the compression space of the cylinder block together with the vanes provided in the cylinder block. Such a rotary compressor discharges compressed gas once as the driving motor rotates once.

In the scroll compressor, the rotational force of the driving motor is transmitted to the rotational shaft so that the rotational shaft rotates. As the rotating shaft rotates, the rotating scroll coupled to the rotating shaft engages with the fixed scroll and rotates to suck, compress and discharge the refrigerant gas. Such a scroll compressor discharges compressed gas twice in succession as the driving motor rotates once.

In the reciprocating compressor, the rotational force of the drive motor is transmitted to the crankshaft and the crankshaft rotates. As the crank shaft rotates, the piston coupled to the crank shaft sucks, compresses and discharges the refrigerant gas while linearly reciprocating in the compression space of the cylinder block. Such a reciprocating compressor discharges compressed gas once as the driving motor rotates once.

On the other hand, in addition to the compressors described above, a first gear having a plurality of gears formed on the inner circumferential surface and a second gear having a smaller number of gears than those of the first gear are formed on the outer circumferential surface and engaged with the first gear to rotate. There is a compression mechanism. Such a compression mechanism is to engage the first gear and the second gear in one rotation to discharge the compressed gas continuously a plurality of times. This results in relatively better compression efficiency and stability than other compressors. In addition, the rotation axis for transmitting the rotational force of the drive motor to the gears are symmetrical about the axis center to suppress the eccentric rotation than other compressors, so that less vibration or noise is generated.

However, the compression mechanism using the gears has a big disadvantage that the relative movement between the gears as well as the parts supporting the gears is increased because the gears are engaged with each other in rotational motion. have. Therefore, minimizing the wear between the gears and the parts moving relative to the gears is an important task in the design and manufacture of the compressor.

[Technical Challenges]

The present invention has been made in view of the above-mentioned point, and an object of the present invention is not only to discharge the compressed gas many times while the two gears are engaged with each other as the drive motor rotates once, but also the two gears. And a compressor capable of minimizing wear of the gears and the parts moving relative thereto.

[Technical Solution]

In order to achieve the object of the present invention as described above, a sealed container containing oil, a drive motor mounted in the sealed container, a cylinder mounted in the sealed container at a predetermined distance from the drive motor, and rotatable to the cylinder. The inner gear is inserted into the outer gear and the outer gear having the lower gear is formed in the form, and the inner gear is rotatably inserted into the outer gear to insert a plurality of compression spaces together with the outer gear. An upper bearing and a lower bearing coupled to both side surfaces of the cylinder to seal the compression spaces, a rotation shaft transmitting a rotational force of the driving motor to the inner gear, and the oil and the outer gear according to the rotation of the rotation shaft. Oil supply means for circulating and supplying between the upper bearing and the lower A compressor provided in the secondary bearing is provided, comprising a suction means and a discharge means for the gas is sucked and discharged into the compression spaces.

1 is a front sectional view showing an embodiment of the compressor of the present invention;

2 and 3 are cross-sectional views respectively showing the compressor in a cross-sectional view,

4 is a sectional view showing a modification of the oil passage constituting the compressor of the present invention;

5 is a cross-sectional view showing a modification of the third oil passage constituting the compressor of the present invention;

6 is a plan view showing an operating state of the compressor of the present invention.

<Explanation of symbols on main parts of drawings> (Omitted when translating)

10; Airtight container 20; Drive motor

30; Cylinder 40; Outer gear

50; Inner gear 60; Upper bearing

70; Lower bearing 80; Axis of rotation

33; Oil grooves 34; 1st oil port

35; Second oil port F1; 1st oil flow path

F2; Second oil channel F3; 3rd oil flow path

Best Mode for Implementation of the Invention

Hereinafter, the compressor according to the present invention will be described in detail with reference to the embodiments shown in the accompanying drawings.

1 is a front sectional view showing an embodiment of the compressor of the present invention, and FIGS. 2 and 3 are cross-sectional views of the compressor, respectively.

As shown in the drawing, the compressor includes a sealed container 10 containing oil, a drive motor 20 mounted in the sealed container 10, a cylinder 30 mounted in the sealed container 10, An outer gear 40 rotatably inserted into the cylinder 30 and having gear teeth 41 formed on an inner circumferential surface thereof and a gear tooth 51 smaller than the teeth 41 of the outer gear 40 are formed on an outer circumferential surface thereof. Inner gear 50 rotatably inserted in the outer gear 40 to form a plurality of compression spaces with the teeth 41 of the outer gear 40, respectively coupled to both sides of the cylinder 30 And an upper bearing 60 and a lower bearing 70 to seal the compression spaces, a rotation shaft 80 which transmits the rotational force of the driving motor 20 to the inner gear 50, and the rotation shaft 80 of the rotation shaft 80. Oil supply water to circulate the oil between the cylinder 30 and the outer gear 40 in accordance with the rotation And, it is provided in the upper bearing 60 and lower bearing 70 is configured to include a suction means and ejection means which gas is sucked and discharged into the compression space.

The suction tube 11 into which the gas is sucked into the sealed container 10 and the discharge tube 12 into which the gas is discharged to the outside are connected.

The drive motor 20 includes a stator 21 fixedly coupled to the hermetic container 10, and a rotor 22 rotatably inserted into the stator 21. The rotating shaft 80 is pressed into the rotor 22.

The cylinder 30 includes a circular body portion 31 having a predetermined thickness and a gear insertion hole 32 formed through the body portion 31 at a predetermined inner diameter. The center of the gear insertion hole 32 and the center of the body portion 31 are eccentric. The cylinder 30 is positioned below the drive motor 20 at regular intervals from the drive motor 20.

The outer gear 40 has an annular body portion 42 having an outer diameter corresponding to the thickness of the cylinder 30 and having an inner diameter corresponding to the inner diameter of the gear insertion hole 32, and a predetermined interval on the inner circumferential surface of the annular body portion 42. It consists of a plurality of gear teeth 41 are formed with. The outer gear 40 is rotatably inserted into the gear insertion hole 32 of the cylinder 30.

The inner gear 50 includes a disc portion 52 having a thickness corresponding to the thickness of the outer gear 40, a plurality of gear teeth 51 formed on an outer circumferential surface of the disc portion 52, and the disc. It is formed through the center of the portion 52 is provided with a shaft engaging hole 53 is inserted into the rotary shaft 80 is coupled. The inner gear 50 is rotatably inserted into the outer gear 40 such that the gear teeth 51 are in contact with the gear teeth 41 of the outer gear 40. The center of the inner gear 50 coincides with the center of the cylinder 30 into which the outer gear 40 is inserted.

The teeth 41 of the outer gear 40 are seven, and the teeth 51 of the inner gear 50 are six. The teeth 41 of the outer gear 40 and the teeth 51 of the inner gear 50 are engaged with each other and are in line contact and face contact with each other, so that the teeth 41 and the inner gear 50 of the outer gear 40 are in contact with each other. These 51 are formed by a plurality of compression spaces, such compression spaces as the inner gear 50 is rotated by a certain angle as the outer gear 40 rotates together, the contact point is changed while the volume changes do.

The number of teeth 41 of the outer gear 40 and the number of teeth 51 of the inner gear 50 may be implemented in various numbers, the number of teeth 41 of the outer gear 40 is the inner There will always be more than the number of teeth 51 of the gear 50.

One side of the rotation shaft 80 is penetrated through the shaft coupling hole 53 of the inner gear 50 is coupled. The other side of the rotating shaft 80 is immersed in the oil filled in the bottom surface of the closed container (10).

The upper bearing 60 includes a support plate 61 having a predetermined thickness and an area, and a shaft insertion hole 62 into which one side of the rotation shaft 80 is inserted in the center of the support plate 61. The shaft insertion hole 62 is preferably formed to have a predetermined depth. The upper bearing 60 is coupled to one surface of the cylinder 30 to cover one side of the compression spaces. One side of the rotary shaft 80 is inserted into the shaft insertion hole 62 of the upper bearing.

The lower bearing 70 includes a support plate 71 having a predetermined thickness and an area, and a shaft insertion hole 72 formed through the support plate 71 to insert the rotation shaft 80 therein. The shaft insertion hole 72 is formed through the support plate portion 71. The lower bearing 70 is coupled to the other surface of the cylinder 30 to cover the other side of the compression spaces. The rotary shaft 80 is inserted into the shaft insertion hole 72 of the lower bearing.

The cylinder 30, the upper bearing 60, and the lower bearing 70 are fastened by a plurality of bolts (not shown) to form an assembly, and the assembly 30 includes the cylinder 30 in the sealed container 10. It is fixedly supported by the sealed container 10 by being fixedly coupled. In addition to the cylinder 30, the assembly may be coupled by fixing the upper bearing 60 or the lower bearing 70 to the sealed container 10.

The high and low pressure separating plate 13 for separating the sealed container 10 into a high pressure part and a low pressure part is coupled to an upper portion of the upper bearing 60. One side of the high and low pressure separator plate 13 is fixedly coupled to the inner surface of the sealed container 10. The suction pipe 11 is located on the low pressure side, and the discharge pipe 12 is located on the high pressure side.

The suction means is provided in the lower bearing 70, and the suction means comprises a suction port 73 formed through the support plate 61 of the lower bearing in a predetermined shape. The suction port 73 is formed over compression spaces whose volume increases with the rotation of the rotation shaft 80 of the compression spaces.

The discharge means is provided in the upper bearing 60, the discharge means is discharge port 63 is formed through the support plate portion 61 of the upper bearing and the discharge plate 63 is coupled to the support plate portion 61 It is configured to include a discharge valve 100 for opening and closing a). The discharge port 63 is formed to penetrate the upper bearing 60 so as to be located at a portion where the volume of the compression spaces is minimized.

The oil supply means is mounted on the first oil flow path F1 and the first oil flow path F1 formed through the rotation shaft 80, and the oil is rotated by the rotation shaft 80. The oil feeder 110 pumping oil into the first oil flow path F1 and the oil formed in the upper bearing 60 and supplied to the first oil flow path F1 are supplied to the cylinder 30 and the outer gear ( The second oil flow path (F2) to guide between the 40 and the oil formed in the lower bearing 70 and passed between the cylinder 30 and the outer gear 40 to guide the discharge to the bottom of the sealed container (10) It is comprised including the 3rd oil flow path F3.

The first oil flow path F1 has a first oil hole 81 formed at a predetermined length in an axial direction at one end of the rotation shaft 80 and the inflow of the first oil hole 81. A mounting hole 82 formed at a predetermined depth on the side to mount the oil feeder 1 10, and a second oil hole connected to the first oil hole 81 and penetrating through the outer circumferential surface of the rotation shaft 80 ( 83). The inner diameter of the mounting hole 82 is larger than the inner diameter of the first oil hole 81. The oil feeder 110 is preferably formed in a propeller shape, the oil feeder 110 is immersed in the oil filled in the bottom surface of the closed container (10).

An oil groove 33 having a predetermined width and depth in a circumferential direction is formed on an inner circumferential surface of the gear insertion hole 32 of the cylinder 30, and the oil groove 33 and the edge of the gear insertion hole 32 are formed. A first oil port 34 connecting the second oil flow path F2 is formed, and the oil groove 33 and the third oil flow path F3 are connected to the edge of the gear insertion hole 32. 2 oil port 35 is formed.

As another modification of the oil flow path formed in the cylinder 30, as shown in FIG. 4, the second gear is formed at one edge of the gear insertion hole 32 of the cylinder 30 into which the outer gear 40 is inserted. An oil port 36 is formed which is connected to the oil flow path F2 and guides oil inflow between the cylinder 30 and the outer gear 40. In this case, the oil flowing into the oil port 36 may be supplied between the outer gear 40 and the cylinder 30 by the relative motion between the outer gear 40 and the cylinder 30.

The second oil flow path F2 is formed to have a predetermined width and depth in the circumferential direction on the shaft insertion hole 62 of the upper bearing 60 and the inner circumferential surface of the shaft insertion hole 62, and through the rotating shaft 80. An annular oil filling groove 64 in which oil is supplied, a first oil hole 65 penetrating the outer circumferential surfaces of the oil filling groove 64 and the upper bearing 60, and the first oil hole 65. And a second oil hole 66 connecting the first oil port 34.

The hole blocking member 130 is coupled to one side of the first oil hole 65 positioned on the outer circumferential surface side of the upper bearing 60.

The third oil flow path F3 includes an oil through hole formed through the lower bearing 70 so that the oil passing between the cylinder 30 and the outer gear 40 falls on the bottom surface of the sealed container 10.

On the other hand, as a modification of the third oil flow path (F3), as shown in Figure 5, is formed in the lower bearing 70 to a predetermined length is connected between the cylinder 30 and the outer gear 40 The oil is connected to the first oil hole 74 and the suction port 73 which is suction means formed in the first oil hole 74 and the lower bearing 70, and the gas is sucked through the suction port 73. Is made up of a second oil hole 75 which guides a part of the suction into the compression space. The first oil hole 74 is connected to the second oil port 35.

Hereinafter, the operational effects of the compressor of the present invention will be described.

First, when power is applied to the compressor, the drive motor 20 operates to generate rotational force, and the rotational force of the drive motor 20 is transmitted to the inner gear 50 through the rotation shaft 80, and the inner gear 50. ) Will rotate. When the inner gear 50 is rotated, a rotational force is transmitted to the outer gear 40 in contact with the inner gear 50 at multiple points, and the outer gear 40 rotates together.

Due to the difference between the completion of the inner gear 50 and the completion of the outer gear 40, a plurality of contact points are formed between the inner gear 50 and the moving of the outer gear 40, and a plurality of compression spaces are formed. As the inner gear 50 rotates, the positions of the contact points of the inner gear 50 and the outer gear 40 are changed while the outer gear 40 rotates together, and at the same time, the volume of the compression spaces is changed. do. As the volume of the compression spaces is changed, the gas introduced into the sealed container 10 through the suction pipe 11 is sucked into the compression spaces and compressed and discharged through the discharge pipe 12.

When the teeth 41 of the outer gear 40 are seven and the teeth 51 of the inner gear 50 are six, as shown in FIG. 6, the teeth 41 and the inner gear of the outer gear 40 are shown. Six compression spaces are formed between the teeth 51 of the 50. If the inner gear 50 rotates counterclockwise, the teeth 51 and the outer gear teeth 41 of the inner gear which are in surface contact with the valleys (gears and teeth) of the teeth 41 of the outer gear 40 are rotated. The three compression spaces P1, P2, and P3 are suction-increasing volumes with reference to the line X1 connecting the points in contact with the acid of the three, and the three compression spaces P4 thereafter ( P5) and P6 are in a compressed state in which the volume gradually decreases. Since the teeth 51 of the inner gear 50 are six, the compression spaces formed by the inner gear 50 and the outer gear 40 are repeated in the same shape every time the inner gear 50 rotates by 60 degrees. The gas compressed in one compression space is discharged through the discharge means. Therefore, each time the inner gear 50 rotates once, the gas compressed six times discharges the discharge means.

In the above process, as the rotary shaft 80 rotates, the oil feeder 110 coupled to the rotary shaft 80 rotates to pump oil. The oil pumped by the oil feeder 110 flows along the first oil flow path F1 of the rotation shaft 80 and flows into the second oil flow path F2 of the upper bearing 60. The oil introduced into the second oil flow path F2 of the upper bearing 60 is introduced between the outer gear 40 and the cylinder 30 through the second oil flow path F2. The oil introduced between the outer gear 40 and the cylinder 30 is supplied between the outer circumferential surface of the outer gear 40 and the inner circumferential surface of the gear insertion hole 32 of the cylinder 30 to supply the outer gear 40 and the cylinder. When the 30 moves relative to the lubrication role.

In more detail, the oil introduced into the second oil flow path F2 of the upper bearing 60 passes through the oil groove 33 of the cylinder 30 through the first oil port 34 of the cylinder 30. Flows into. As the oil flows into the oil groove 33, the oil is supplied over the outer circumferential surface of the outer gear 40 and the inner circumferential surface of the gear insertion hole of the cylinder 30, so that the outer gear 40 and the cylinder 30 move relative to each other. When lubricating between the outer peripheral surface of the outer gear 40 and the inner peripheral surface of the gear insertion hole 32 of the cylinder (30). And the oil which lubricated between the outer circumferential surface of the outer gear 40 and the inner circumferential surface of the gear insertion hole 32 of the cylinder 30 passes through the second oil port 35 of the cylinder 30 to the lower bearing 70. The oil introduced into the third oil flow path F3 and introduced into the third oil flow path F3 is returned to the bottom surface of the sealed container 10.

The outer gear 40 rotates together with the rotation of the inner gear 50, and the outer circumferential surface of the outer gear 40 moves relative to the inner circumferential surface of the gear insertion hole 32 of the cylinder 30. Since the outer circumferential surface of the outer gear 40 is far from the rotation shaft 80, the outer circumferential surface of the outer gear 40 and the inner circumferential surface of the gear insertion hole 32 of the cylinder 30 become large and the relative motion is increased. The friction force acts greatly between the outer circumferential surface of the 40 and the inner circumferential surface of the cylinder gear insertion hole 32. Since oil filled in the bottom surface of the sealed container 10 is continuously supplied between the outer gear 40 and the cylinder 30 through the above process, the friction between the outer gear 40 and the cylinder 30 is minimized. In addition, the oil filled in the bottom surface of the sealed container 10 is circulated through the friction generated portion to cool the heat generated by the friction.

Meanwhile, when the third oil flow path F3 formed in the lower bearing 70 includes the first oil hole 74 and the second oil hole 75, between the outer gear 40 and the cylinder 30. Oil positioned at the suction port 73 in the process of flowing to the bottom surface of the sealed container 10 through the first oil hole 74, the second oil hole 75, and the suction port 73 A part of is introduced into the compression space together with the gas sucked into the suction port (73). The oil introduced into the compression space is supplied between two parts that move relative to each other among the inner gear 50, the outer gear 40, the upper bearing 60, and the lower bearing 70 to be lubricated. The friction between them is reduced.

As described above, in the compressor of the present invention, since the outer gear 40 and the inner gear 50 rotate in engagement with each rotation of the drive motor 20, the compressed gas is continuously discharged a plurality of times, thereby compressing the gas. Not only is it made stable, it is possible to increase the compression efficiency, and also the rotational body (rotating shaft and the inner gear, etc.) that rotates with the rotor of the drive motor to achieve a rotational balance, thereby increasing the stability.

In addition, the oil supply is smoothed between the outer gear 40 and the cylinder 30, the frictional force is large during operation, thereby reducing the friction between the outer gear 40 and the cylinder 30 to reduce the cylinder 30 and the outer gear Not only can the reliability of 40 be increased, but also noise can be suppressed due to friction.

In addition, the oil at the bottom of the sealed container 10 is supplied between the outer gear 40 and the cylinder 30 and the supplied oil is returned, while repeating the process between the outer gear 40 and the cylinder 30. Cooling the heat generated from other components as well as the frictional heat generated, there is an effect that can prevent the parts from overheating.

Claims (12)

An airtight container (10) containing oil; a drive motor (20) mounted in the airtight container (10); a cylinder (30) mounted in the airtight container (10); an inner peripheral surface inserted into the cylinder (30) An outer gear 40 having gears formed therein; an inner gear 50 having gears formed on an outer circumferential surface thereof and rotatably inserted into the outer gear 40 to form a plurality of compression spaces with the outer gear 40. And an upper bearing 60 and a lower bearing 70 coupled to both sides of the cylinder 30 to seal the compression spaces; and transmitting the rotational force of the driving motor 20 to the inner gear 50. A rotation shaft 80 and oil supply means for circulating and supplying the oil between the cylinder 30 and the outer gear 40 according to the rotation of the rotation shaft 80; the upper bearing 60 and the lower bearing 70. Is provided in the suction and the gas is sucked into the compressed spaces And means and a discharge means, The oil supply means is mounted to the first oil flow path F1 formed through the rotation shaft 80 and the first oil flow path F1 to supply oil by rotation of the rotation shaft 80. An oil feeder 110 pumping to F1 and an oil formed in the upper bearing 60 to guide the oil supplied to the first oil flow path F1 between the cylinder 30 and the outer gear 40. A third oil flow path F3 formed in the oil flow path F2 and the lower bearing 70 to guide the oil passing between the cylinder 30 and the outer gear 40 to the bottom surface of the sealed container 10. Compressor comprising a). The compressor as claimed in claim 1, wherein the drive motor (20) is located below the cylinder (30). 2. Compressor according to claim 1, characterized in that the number of teeth of the outer gear (40) is seven and the number of teeth of the inner gear (50) is six. delete According to claim 1, The outer gear 40 is connected to the second oil flow path (F1) on one side of the gear insertion hole rim of the cylinder 30 is inserted between the cylinder 30 and the outer gear 40 Compressor, characterized in that the oil port 36 is formed to guide the oil inlet. The oil groove 33 having a predetermined width and depth in the circumferential direction is formed on an inner circumferential surface of the gear insertion hole 32 of the cylinder 30 into which the outer gear 40 is inserted, and the gear insertion hole is formed. A first oil port 34 connecting the oil groove 33 and the second oil flow path F1 is formed at the edge of the 32, and the oil groove 33 is formed at the edge of the gear insertion hole 32. And a second oil port (35) connecting the third oil flow path (F3). The mounting hole 82 of claim 1, wherein the first oil flow path F1 is formed at one end of the rotation shaft 80 to have a predetermined depth, and the mounting hole 82 is mounted on the oil feeder 110. A first oil hole 81 connected to a first oil hole 81 formed at a predetermined depth in an axial direction of the rotation shaft 80, and a second oil hole penetrating the first oil hole 81 at an outer circumferential surface of the rotation shaft 80 ( 83). According to claim 1, The second oil flow path (F2) is formed in the upper bearing 60 to a predetermined depth, the shaft insertion hole 62 is inserted into the rotation part of the rotating shaft 80 and the shaft insertion hole It is formed to have a predetermined width and depth in the circumferential direction on the inner circumferential surface of the (62), the oil filling groove 64 of the annular oil filling groove 64, the oil filling groove 64 and the upper bearing 60 The first oil hole 65 penetrating the outer surface of the) and the second oil hole 66 connecting one side of the first oil hole 65 and the cylinder 30 and the outer gear 40 Compressor, characterized in that made. 9. The compressor as claimed in claim 8, wherein a hole blocking member (130) is coupled to one side of the first oil hole (65) located on the outer circumferential surface side of the upper bearing (60). The compressor as claimed in claim 8, wherein the shaft insertion hole is formed to have a predetermined depth. 3. The compressor as claimed in claim 1, wherein the third oil flow path (F3) is a through oil through hole which guides the oil passed between the cylinder (30) and the outer gear (40) to the lower side. According to claim 1, The third oil flow path (F3) is formed in the lower bearing 70 to a predetermined length and is connected to the first oil hole 74 and the cylinder 30 and the outer gear 40 and the A second oil hole connected to the suction means formed in the first oil hole 74 and the lower bearing 70 to guide a part of the oil to be sucked into the compression space together with the gas sucked through the suction means ( 75) consisting of a compressor.

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