KR101094599B1 - Rotary Compressor - Google Patents

Abstract

Conventional compressors have a problem of lowering the efficiency of the compressor due to an increase in the rotational vibration and a decrease in the efficiency of the electric motor as the rotation speed of the compressor decreases.

The present invention is a rotary compressor comprising a drive element and a rotational compression element driven by the drive element in an airtight container, the upper part of the end face of the rotor constituting the drive element (semi-compression mechanism side), or By providing a rotating inertia body in which the rotational inertia moment is obtained on either of the lower parts (the compression mechanism side), the compressor can suppress an increase in the rotational vibration even in a case where the rotational speed of the compressor is low, thereby obtaining a highly efficient compressor. Can be.

Rotary compressor, hermetic container, electric element, stator, rotor

Description

Rotary Compressor {Rotary Compressor}

1 is an end side view of a rotary compressor of a first embodiment of the present invention (an example in which a rotating inertia body is attached to the compression mechanism side);

Fig. 2 is a longitudinal side view of the rotary compressor of the first embodiment of the present invention (an example in which the rotating inertia body is attached to the half compression mechanism side).

Figure 3 is a longitudinal side view of the rotary compressor of the second embodiment of the present invention.

Fig. 4 is an enlarged view showing the positions of the rotary inertia body and the discharge port in the second embodiment of the present invention.

<Explanation of symbols for the main parts of the drawings>

10: rotary compressor

12: sealed container

12A: Container Body

14: electric element

16: axis of rotation

18: rotary compression mechanism

20: terminal

22: stator

24: rotor

26, 30: laminated body

28: stator coil

32: first rotational compression element

34: second rotational compression element

38: upper cylinder

40: lower cylinder

42: second eccentric part

44: first eccentric part

46: second roller

48: first roller

54: upper support member

56: lower support member

54A: Upper Support Member Bearing

56A: Lower support member bearing

62: discharge noise chamber

64: medium pressure discharge noise

63: cover

65 outlet

68: occlusion plate

70: lower support member discharge port

73: rivet

78: upper bolt

80: lower bolt

82: rotational inertia

[Document 1] Japanese Unexamined Patent Publication No. 2004-19599

The present invention relates to a rotary compressor having a drive element in a sealed container, a rotational compression element driven by a rotational axis of the drive element, and a bearing rotatably supporting the rotational axis of the rotational element.

BACKGROUND OF THE INVENTION Conventional rotary compressors of this kind, for example multistage compression rotary compressors with first and second rotary compression elements, have first and second rotations driven by a drive element and a rotational axis of the drive element in a hermetically sealed container. It is constituted by a compression element.

The transmission element is composed of a stator that is annularly welded and fixed along the inner circumferential surface of the upper space of the sealed container, and a rotor that is inserted with a slight distance inside the stator and is inserted into the rotor. It is fixed to the rotating shaft extending to.

Further, the first and second rotational compression elements are eccentrically rotated by fitting the intermediate partition plate, the upper and lower cylinders disposed above and below the intermediate partition plate, and the eccentric portions provided on the rotating shafts with a phase difference of 180 degrees. And a vane for contacting the rollers, the vanes for dividing the cylinder into the low pressure chamber side and the high pressure chamber side, respectively, and closing the opening surface of the upper side of the upper cylinder and the opening side of the lower side of the lower cylinder. It consists of an upper support member, a lower support member, and the discharge noise chamber each formed above and below. Moreover, each discharge noise chamber and the high pressure chamber side in each cylinder are connected by the discharge port, and the discharge valve | bulb is provided in the discharge silencer with the discharge valve which closes the said discharge port so that opening and closing is possible (for example, refer patent document 1).

[Patent Document 1] Japanese Unexamined Patent Publication No. 2004-19599

In the rotor of a conventional rotary compressor, a rotational angular velocity inversely proportional to the rotational moment of inertia occurs in proportion to the difference between the compression torque and the torque of the electric motor, and a variation (reaction of rotational angular velocity) of the rotational angular velocity inversely proportional to the rotational moment of inertia This may cause rotational vibration of the compressor. In addition, the rotational angular velocity of the rotor is an integral of the rotational angular velocity in inverse proportion to the rotational moment of inertia, and since the return to the original rotational angular velocity in one rotation, the time required for one rotation becomes longer as the rotational speed of the compressor decreases. There was a problem that the fluctuation range of the rotational angular velocity between one revolution increased, thereby increasing the vibration of the compressor.

In addition, when the fluctuation range of the rotational angular velocity between one rotation is large, the ratio of the operation in the rotational angular velocity region with low efficiency is increased and the efficiency of the motor is lowered. Therefore, the lower the rotational speed of the motor, the lower the efficiency of the compressor. In addition, the smaller the compressor and the electric motor, the smaller the rotational moment of inertia, and the higher the vibration of the compressor and the lower the efficiency.

The rotary compressor of the present invention has a drive element, a compression mechanism driven by the drive element, and a bearing for rotatably cantilevering the rotating shaft of the rotating element in a hermetic container, on the lower surface of the rotor (the compression mechanism side). It extends to the lower side of a stator, and has a mass body from which a rotational moment of inertia is obtained.

In addition, the rotary compressor of claim 2 has a drive element, a compression mechanism driven by the drive element, and a bearing for rotatably cantilevering the rotation axis of the rotation element in a hermetic container, and the upper surface of the rotor (semi-compression mechanism). And a mass body extending to the lower side of the stator to obtain a rotational moment of inertia.

In addition to the above, the rotary compressor of claim 3 is formed to be thinner than the same outer diameter of the rotor or the outer diameter of the rotor until the shape of the mass installed in the rotor reaches the required insulation distance from the stator coil. After a distance, it is characterized by obtaining a required rotational inertia moment by making the outer diameter expand to the magnitude | size which covers a stator coil to the inner wall side of a sealed container.

In addition, in the rotary compressor of claim 4, in addition to claims 1 to 3, the discharge port for discharging the compressed gas from the rotating element into the sealed container is located within 1/2 of the maximum outer diameter of the mass body provided in the rotor. The amount of oil discharged out of the compressor is reduced.

The present invention is characterized by enabling the rotary compressor to provide a highly efficient compressor by providing a rotating inertia to the rotor while suppressing an increase in the vibration of the compressor even in a low rotation region. In addition, it is possible to cope with an increase in vibration and a decrease in efficiency due to the compactness of the compressor. Further, until the shape of the mass body provided in the rotor reaches the required insulation distance from the stator coil, it is formed to be thinner than the same outer diameter or the outer diameter of the rotor, and after the insulation distance, the stator coil is placed toward the inner wall of the sealed container. The outer diameter is expanded to the covering size, so that the required rotational inertia moment is obtained, and the discharge port for discharging the compressed gas from the rotating element into the sealed container is 1/2 of the maximum outer diameter of the mass body provided in the rotor. By positioning within, the oil in the discharge gas is separated by the mass, and the amount of oil discharged to the outside of the compressor is reduced.

(First embodiment)

EMBODIMENT OF THE INVENTION Next, embodiment of this invention is described in detail based on drawing. Fig. 1 shows an embodiment of the rotary compressor of the present invention, in which a mass body, i.e., a rotating tube, having first and second rotating elements 32 and 34 and installed by rivets 73 on the compression mechanism side of the rotor 24 is shown. The longitudinal side view of the internal high pressure rotary compressor 10 which installed the adult body 82 is shown. 2 shows a longitudinal side view of claim 2.

In Fig. 1, the rotary compressor 10 of the embodiment is an internal high pressure rotary compressor 10, and is located above the inner space of the sealed container 12 in a vertical cylindrical sealed container 12 made of steel. Transmission element 14 as a drive element arranged, and first and second rotational compression elements 32, 34 disposed below the transmission element 14 and driven by the rotational axis 16 of the transmission element 14. The rotary compression mechanism part 18 which consists of this is accommodated. In the rotary compressor 10 of the embodiment, carbon dioxide is used as the refrigerant.

The sealed container 12 has a bottom portion as an oil storage portion, a container main body 12A for accommodating the transmission element 14 and the rotary compression mechanism part, and an approximately main-end end cap for closing the upper opening of the container main body 12A. (Cover body) 12B, and a circular mounting hole 12D is formed in an upper surface of the end cap 12B, and the mounting hole 12D is configured to supply electric power to the electric element 14. The terminal 20 (without wiring) is provided.

The transmission element 14 includes a stator 22 that is annularly welded and fixed along the inner circumferential surface of the upper space of the sealed container 12, and a rotor 24 inserted into the stator 22 with a slight distance therebetween. And a rotating inertia 82 provided on the rotor 24 by rivets 73, and the rotor 24 and the rotating inertia 82 extend in the vertical direction through the center. It is fixed to the rotating shaft (16).

Here, the rotational inertial body 82 has the same outer diameter as the rotor 24 or the rotor 24 until it reaches the minimum required insulation distance (varied by the applied voltage) from the stator coil 28. The outer diameter is formed to be thinner than the outer diameter, and after the insulation distance, the outer diameter is expanded in the direction of covering the stator coils 28 to the inner wall side of the sealed container 12. By making this outer diameter expand, it becomes possible to obtain a large rotational inertia moment with little material.

In this case, copper and a copper alloy are used as a material of the rotary inertia 82, and it is formed by the laminated body which laminated | stacked the casting molded article, the forged molded article, or the board of copper and copper alloy.

The stator 22 has a laminate 26 in which a donut-shaped electromagnetic steel sheet is laminated, and a stator coil 28 wound on a back portion of the laminate 26 by a series winding (intensive winding) method. have. In addition, the rotor 24 is also formed of the laminated body 30 of electromagnetic steel sheets similarly to the stator 22.

The first rotary compression element 32 and the second rotary compression element 34 fit the intermediate partition plate 36 as an intermediate partition member, and the second rotary compression element 34 in the second stage is sealed container 12. The 1st rotational compression element 32 which becomes the 1st step | paragraph in the transmission element 14 side in () is arrange | positioned on the opposite side to the transmission element 14. As shown in FIG. That is, the first rotary compression element 32 and the second rotary compression element 34 are the lower cylinder 40 and the second cylinder as the first cylinder constituting the first and second rotary compression elements 32, 34. The upper cylinder 38 and the openings of each of the cylinders 38 and 40, and the opening of the transmission element 14 side (upper side) of the lower cylinder 40 and the opposite side of the transmission element 14 of the upper cylinder 38. First and second eccentric portions 42 and 44 provided with the intermediate partition plate 36 for blocking the opening of the lower side and the rotary shaft 16 having a phase difference of 180 degrees in the upper and lower cylinders 38 and 40. The first roller 48 and the second roller 46, which are eccentrically rotated in the respective cylinders 38 and 40, and the rollers 46 and 48 are in contact with each other. A vane (not shown) which is divided into a low pressure chamber side and a high pressure chamber side, and an opening on the opposite side (lower side) of the lower cylinder 40 from the transmission element 14 side are closed to close the bearing 56A of the rotary shaft 16. The second support having the lower support member 56 as the first support member and the opening of the transmission element 14 side (upper side) of the upper cylinder 38 and the bearing 54A of the rotary shaft 16 are closed. The upper support member 54 as a member and the bearings 54A and 56A of the upper and lower support members 54 and 56 are provided outside, and the upper support member 54 has a cover 63 for constituting the discharge silencer 62. ), And the lower support member 56 is composed of a closing plate 68 for constituting the medium pressure discharge silencer 64.

In the upper support member 54 and the lower support member 56, suction passages 58 and 60 and discharge silencer 62 communicating with the insides of the upper and lower cylinders 38 and 40 at the suction ports 160 and 161, respectively. ) And a medium pressure discharge silencer 64 are provided. The discharge silencer 62 is formed by recessing the surface opposite to the upper cylinder 38 of the upper support member 54 and closing the recessed portion with the cover 63 as described above. In addition, the intermediate pressure discharge silencer 64 recesses the surface on the opposite side to the lower cylinder 40 of the lower support member 56, closes the recessed portion with the blocking plate 68, and simultaneously closes the blocking plate 68. Is formed by. That is, the discharge silencer 62 is closed by the cover 63, and the medium pressure discharge silencer 64 is blocked by the blocking plate 68. As shown in FIG.

In this case, a bearing 54A is standing up in the center of the upper support member 54. Moreover, the discharge silencer 62 formed by the cover 63 is provided in the outer periphery of the bearing 54A, and the gas discharged | emitted from the discharge port not shown passes through the discharge silencer 62, and the upper bearing ( 54A) It is discharged into the sealed container 12 from the communication passage 65 which is a donut-shaped gap between the upper part and the cover 63.

In addition, a bearing 56A is formed through the center of the lower support member 56. The bearing 56A has a substantially donut shape with a hole through which the rotating shaft 16 passes through the center of the rotating shaft 16. In addition, an intermediate pressure discharge silencer 64 is provided on the outer circumference of the bearing 56A. On the other hand, the obstruction plate 68 is formed of a donut-shaped circular steel plate, and the four parts of the periphery are fixed to the lower support member 56 from below by bolts 80, and the first rotation is performed at the discharge port (not shown). The lower opening of the intermediate pressure discharge silencer 64 in communication with the interior of the lower cylinder 40 of the compression element 32 is closed. This bolt 80 is a bolt for assembling the first and second rotary compression elements 32, 34, the leading end of which screws into the upper cylinder 38. That is, the upper cylinder is formed with a screw thread formed in the distal end portion of the bolt 80 and a screw groove for screwing each other.

Here, the procedure of assembling the rotation compression mechanism part 18 which consists of the 1st and 2nd rotating elements 32 and 34 is demonstrated. First, the cover 63, the upper support member 54, and the upper cylinder 38 are positioned, and two upper bolts 78 and 78 screwed to the upper cylinder 38 are disposed on the cover 63 side (upper side). ) And penetrate in the axial direction (downward) to integrate them. Thereby the second rotary compression element 34 is assembled.

Next, the second rotary compression element 34 integrated with the upper bolt 78 described above is inserted into the rotary shaft 16 from the upper end side. Next, the intermediate partition plate 36 is assembled with the lower cylinder 40, inserted into the rotating shaft 16 from the lower end side, and positioned with the upper cylinder 38 already installed, thereby lower cylinder 40 The two upper bolts (not shown) which are screwed together are inserted in the axial center direction (downward) from the cover 63 side (upper side), and they are fixed.

Then, after the lower support member 56 is inserted into the rotation shaft 16 from the lower side, the blocking plate 68 is inserted through the rotation shaft 16 from the lower end in the same manner to close the recessed portion of the lower support member 56. And inserting the four lower bolts 80 in the axial direction (upward) from the closing plate 68 side (lower side), and screwing the front end portions in the screw grooves formed in the upper cylinder 38, respectively. Two rotary shaft elements 32 and 34 are assembled. In addition, since the 1st and 2nd eccentric parts 42 and 44 are formed in the rotating shaft 16, it cannot be provided in the rotating shaft 16 by methods other than the above-mentioned procedure. Therefore, the closing plate 68 is finally installed on the rotation shaft 16.

In this way, the second rotational compression element 34, the intermediate partition plate 36 and the lower cylinder 40, the lower support member 56, and the closure plate 68 are sequentially installed on the rotation shaft 16, and finally, The first and second rotary compression elements 32 and 34 are fixed to the rotary shaft 16 by inserting four bolts 80 through the lower side of the installed blocking plate 68 and screwing them to the upper cylinder 38. can do.

In this case, as the refrigerant, the above-mentioned carbon dioxide (CO2), which is easy to the global environment, and is a natural refrigerant in consideration of flammability and toxicity, is used. The oil as lubricating oil is, for example, mineral oil (mineral oil), alkylbenzene oil, Conventional oils such as ether oil, ester oil, PAG (polyalkyl glycol) are used.

Then, on the side surface of the container body 12A of the sealed container 12, the suction passages 58 and 60 of the support member 54 and the lower support member 56, the discharge silencer 64, and the transmission element 14 The sleeves 140, 141, 142, the refrigerant discharge tube 96, and the service tube 97 are welded and fixed at positions corresponding to the upper side of the &quot; Sleeves 140 and 141 are adjacent up and down, while sleeve 142 is on approximately diagonal of sleeve 141.

In the sleeve 140, one end of the refrigerant introduction pipe 92 for introducing refrigerant gas into the upper cylinder 38 is inserted and connected, and one end of the refrigerant introduction pipe 92 is a suction passage of the upper cylinder 38. (58). The refrigerant introduction pipe 92 passes through the upper portion of the sealed container 12 to reach the sleeve 142, and the other end is inserted into the sleeve 142 to communicate with the medium pressure discharge silencer 64.

In addition, one end of the refrigerant introduction pipe 94 for introducing refrigerant gas into the sleeve 141 is inserted and connected in the sleeve 141, and one end of the refrigerant introduction pipe 60 is connected to the suction passage 60 of the lower cylinder 40. ). The coolant discharge tube 96 is welded and fixed to the container body 12A, and one end of the coolant discharge tube 96 communicates with the sealed container 12.

In the above configuration, the operation of the rotary compressor 10 will be described next. When the stator coil 28 of the transmission element 14 is energized through the terminal 20 and wiring not shown, the transmission element 14 is started to rotate the rotor 24. By this rotation, the 1st and 2nd rollers 46 and 48 fitted to the 1st and 2nd eccentric parts 42 and 44 provided integrally with the rotating shaft 16 are in the upper and lower cylinders 38 and 40. FIG. Rotate eccentrically.

As a result, the low pressure (first stage suction pressure sucked into the low pressure chamber side of the lower cylinder 40 from the suction port 161 via the suction passage 60 formed in the refrigerant introduction pipe 94 and the lower support member 56). The refrigerant gas of about 4 MPaG) is compressed by the copper of the vane which is not shown in the 1st roller 48, and becomes intermediate pressure. The refrigerant gas of the intermediate pressure is discharged from the high pressure chamber side of the lower cylinder 40 into the intermediate pressure discharge silencer 64 formed in the lower support member 56 through a discharge port (not shown).

The medium pressure refrigerant gas discharged into the medium pressure discharge silencer 64 passes through the refrigerant introduction pipe 92 communicated with the medium pressure discharge silencer 64, and is formed on the upper support member 54. It is sucked from the suction port 160 to the low pressure chamber side of the upper cylinder 38 via the suction passage 58.

The suctioned medium pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vanes (not shown) to form a high temperature and high pressure refrigerant gas (about 12 MPaG). And the high temperature and high pressure refrigerant gas is discharged from the high pressure chamber side of the upper cylinder 38 to the discharge noise chamber 62 formed in the upper support member 54 through the discharge port which is not shown in figure.

The refrigerant discharged into the discharge silencer 62 is discharged into the airtight container 12 from the communication passage 65 provided in the cover 63, and then passes through the gap of the transmission element 14 to close the airtight container 12. ), And is discharged to the outside of the rotary compressor 10 from the refrigerant discharge pipe 96 connected above the sealed container 12.

Thus, by providing the rotational inertia 82 on the rotor 24, the required rotational inertia moment can be obtained, so that the rotational vibration can be suppressed even in the low-speed region of the compressor, and the efficiency is A high compressor is obtained. In addition, by forming the rotary inertia 82 with copper, a copper alloy, or the like, the rotational inertia moment required for vibration reduction with a low cost material is not increased without increasing the shape of the rotor 24 using expensive materials. Obtained.

(2nd Example)

3 and 4 show another embodiment of the present invention, and FIG. 3 shows a longitudinal side view of the rotary compressor of the present invention. 4 is an enlarged view of a portion showing the positional relationship between the rotary inertia body of the present invention and the discharge port 65 for discharging the discharge gas. In addition, the same code | symbol as this is attached | subjected to the part same as embodiment mentioned above, and description is abbreviate | omitted. In the rotary compressor 10 as described in the above-described embodiment, the rotary inertia 84 is formed to extend to a size covering the entire stator coil 28.

Moreover, the discharge port 65 which discharges discharge gas from the compression element 18 into the airtight container 12 is installed in the position within the maximum outer diameter 1/2 of the said rotary inertia 84, as shown in FIG. do.

Then, the refrigerant gas containing the oil discharged from the discharge port 65, in the rotary inertia 84, is separated into oil and refrigerant by the rotational force of the rotary inertia, the separated oil is returned to the oil reservoir of the compressor The separated gas passes through the gap of the transmission element 14 and moves upward in the hermetic container 12, and from the refrigerant discharge pipe 96 connected to the upper side of the hermetic container 12, It is discharged to the outside.

Thus, by providing the discharge port 65 within the half of the rotational inertia 84, the oil separation ability by the rotation of the rotational inertia is effectively utilized to reduce the amount of oil discharged At the same time, a stable oil supply is possible.

In addition, although this embodiment demonstrated using the internal high pressure type rotary compressor 10 provided with the 1st and 2nd rotational compression elements 32 and 34 as a rotary compressor, this invention is not limited to this and it is not limited to this. The present invention can be applied to rotary compressors and rotary compressors having three or more rotary elements. In addition, the present invention is not limited to the internal high-pressure type rotary compressor 10, and the present invention is applied to an internal intermediate pressure type in which a refrigerant compressed by the first rotary compression element is discharged into a sealed container, and then compressed by the second rotary compression element. You may apply.

In the embodiment, the second rotary compression element 34 provided on the transmission element 14 side is the second stage, and the first rotary compression element 32 on the side opposite to the transmission element 14 is the first stage. Although the refrigerant compressed by the element 32 is compressed by the second rotary compression element 34, the present invention is not limited thereto, and the refrigerant compressed by the second rotary compression element may be compressed by the first rotary compression element. none.

In addition, when the exclusion volume is different in the first compression mechanism and the second compression mechanism in the multistage compressor, the weight balance of the rotary inertia 84 is changed to match the exclusion volume of each compression mechanism, and the article to balance the whole. It may be.

In addition, in this embodiment, although the rotating shaft was demonstrated as the vertical arrangement, it is a matter of course that it is applied also to the rotary compressor which made the rotating shaft the horizontal arrangement. In addition, although carbon dioxide is used as a refrigerant | coolant of a rotary compressor, you may use another refrigerant | coolant.

As described in detail above, according to the present invention, a sealed element includes a drive element, a rotational compression element driven by the drive element, and a bearing for rotatably supporting the rotation axis of the rotation element, By installing a mass body from which the rotational moment of inertia is obtained on the rotor on either the upper end of the rotor (semi-compression mechanism side) or on the lower end of the rotor (compression mechanism side), even in the case of operation in which the rotation speed of the compressor is low. Therefore, it is possible to provide a compressor with high efficiency while suppressing an increase in the vibration of the compressor. Moreover, since the mass body provided extends to the stator side, the dimension of the thickness direction can be reduced by enlarging the dimension of the width direction of a mass body, and the dimension of the height direction of the whole compressor can be miniaturized.

In addition, according to the invention of claim 3, in addition to the above, until the shape of the mass installed in the rotor reaches the required insulation distance from the stator coil, it is formed thinner than the same outer diameter or outer diameter of the rotor, and the insulation After the distance, the required rotational moment of inertia can be obtained by making the outer diameter expand to the size of covering the stator coils on the inner wall side of the sealed container.

According to the invention of claim 4, in addition to claims 1 to 3, the discharge port for discharging the compressed gas from the rotating element into the sealed container is located within 1/2 of the maximum outer diameter of the mass body provided in the rotor. The oil in the discharge gas is separated by the mass, and the amount of oil discharged to the outside of the compressor can be reduced.

Claims (4)

A bearing installed in a sealed container and connected to a rolling element comprising a stator and a rotor, a rotating compression element driven by the rolling element and compressing and discharging refrigerant, and a rotating compression element and a rotor of the rolling element, Is a rotary compressor having a rotational ¶ supported rotatably, On the lower surface of the rotor of the transmission element, a mass body extending below the stator to obtain a rotation moment of inertia is provided. And a discharge port for discharging the compressed gas from the rotary compression element into the sealed container within half of the maximum outer diameter of the mass body provided in the rotor. A bearing installed in a sealed container and connected to a rolling element comprising a stator and a rotor, a rotating compression element driven by the rolling element and compressing and discharging refrigerant, and a rotating compression element and a rotor of the rolling element, A rotary compressor comprising a rotating shaft rotatably supported by a shaft, On the rotor upper surface of the said transmission element, the mass body which extends below the said stator and the rotational moment of inertia is obtained is provided, And a discharge port for discharging the compressed gas from the rotary compression element into the sealed container within half of the maximum outer diameter of the mass body provided in the rotor. The outer motor or the same outer diameter as described in Claim 1 or 2 until the motor which forms a drive element is a series winding system, and the shape of the mass body provided in a rotor reaches the required insulation distance from a stator coil. It is formed thinner than the electron outer diameter, and after the insulation distance, the rotary compressor characterized in that the outer diameter is expanded to a size that covers the stator coils to the inner wall side of the sealed container. delete

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