JP2009243346A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor having simple construction for reducing the size, lengthening the operating life and improving the compressing performance. <P>SOLUTION: A turning scroll 17 arranged between first and second fixed scrolls 15, 16 has a turning end plate 29, and first and second turning spiral walls 30, 31 provided on the turning end plate 29. The first turning spiral wall 30 is inserted inside a first fixed spiral wall 23 of the fixed scroll 15, and the second turning spiral wall 31 is inserted inside a second fixed spiral wall 25 of the fixed scroll 16. Clearances P1, P2 between spiral portions of each of the first and second turning spiral walls 30, 31 are mutually different. The relationship of the clearances P1, P2 between the spiral portions of each of the first and second turning spiral walls 30, 31 to wall thicknesses T1, T2 of the first and second turning spiral walls 30, 31 satisfies P1/2-T1=P2/2-T2. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in, for example, a refrigeration air conditioner.

  2. Description of the Related Art Conventionally, there is known a scroll compressor in which a turning scroll is disposed between a pair of fixed scrolls facing each other in the axial direction and fluid is compressed on both sides in the axial direction of the turning scroll by turning the turning scroll. If the fluid pressures on both sides in the axial direction of the orbiting scroll are the same, the fluid pressures are offset and no axial load acting on the orbiting scroll is generated. However, in reality, there is a difference between the fluid pressures due to, for example, errors in the accuracy of the shape of the orbiting scroll or the fixed scroll, so that the fluid pressures are not completely cancelled, and the axial load on the orbiting scroll is the thrust load. Will occur.

  Therefore, conventionally, it has been proposed to provide a bearing structure for receiving a thrust load on the orbiting scroll at the outer peripheral edge of the orbiting scroll. The bearing structure includes a flange formed on the outer peripheral edge of the orbiting scroll and an annular bearing metal provided between the end face of the flange and the end plate of the fixed scroll. Lubricating oil is supplied between the end face of the flange and the bearing metal (see Patent Document 1).

JP-A-7-286586

  However, conventionally, since the bearing structure is provided on the outer peripheral edge of the orbiting scroll, not only the structure becomes complicated, but also the entire scroll compressor becomes large.

  Further, since the thrust load on the orbiting scroll is not constant and the direction in which the thrust load is generated is unstable, vibration in the axial direction of the orbiting scroll occurs or the orbiting scroll tilts with respect to the fixed scroll. There is a fear. Thereby, there exists a possibility that the lifetime of a compressor may become short or compression efficiency may fall.

  The present invention has been made to solve the above-described problems, and can achieve downsizing with a simple configuration, can extend the life, and can improve the compression performance. It aims at obtaining the scroll compressor which can do.

  A scroll compressor according to the present invention includes: a first fixed scroll having a first fixed end plate, and a first fixed spiral wall provided in a spiral shape on the first fixed end plate; a second fixed end plate; A second fixed spiral wall provided in a spiral shape on the second fixed end plate, and facing the first fixed scroll with the second fixed spiral wall facing the first fixed spiral wall. A fixed scroll, a swivel mirror plate disposed between the first and second fixed scrolls, a first swirl spiral wall provided in a spiral shape on the swivel mirror plate, and inserted between the walls of the first fixed spiral wall; And a second swirl wall provided in a spiral shape on the swivel end plate and inserted between the walls of the second fixed swirl wall, and can be swung in the radial direction with respect to the first and second fixed scrolls An orbiting scroll, comprising a side surface of the first fixed spiral wall and a side surface of the first orbiting spiral wall The volume of the compression chamber formed by the contact and the volume of the compression chamber formed by the contact between the side surface of the second fixed spiral wall and the side surface of the second orbiting spiral wall are changed by the orbiting scroll. Accordingly, the scroll compressor compresses the fluid in the compression chamber, wherein the spiral interval by the first swirl spiral wall is P1, the wall thickness of the first swirl spiral wall is T1, and the spiral by the second swirl spiral wall Is P2, the wall thickness of the second swirl spiral wall is T2, and the relationship P1 / 2−T1 = P2 / 2−T2 is substantially established, and P1 and P2 are different.

  In the scroll compressor according to the present invention, the spiral interval P1 due to the first swirl spiral wall and the spiral interval P2 due to the second swirl spiral wall are different from each other, and the spiral interval P1 due to the first swirl spiral wall is different. The relationship between the spiral pitch P2 by the second swirl spiral wall, the wall thickness T1 of the first swirl spiral wall, and the wall thickness T2 of the second swirl spiral wall is P1 / 2−T1 = P2 / 2−T2. Therefore, the refrigerant gas can be compressed simultaneously on both sides of the end plate of the orbiting scroll, the difference in fluid pressure received by the orbiting scroll is maintained in a certain direction, and the resultant pressure of the pressure received by the orbiting scroll is constant. It can be stabilized in the direction. Thereby, vibration and inclination of the orbiting scroll can be prevented, and the compression performance can be improved. In addition, the life can be extended. Furthermore, since the tilt of the orbiting scroll can be suppressed without a special bearing structure, it is not necessary to provide a bearing structure on the outer peripheral edge of the orbiting scroll, and the size can be reduced with a simple configuration.

Embodiment 1 FIG.
1 is a sectional view showing a scroll compressor according to Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view showing the compression mechanism portion of FIG. In the figure, the sealed container 1 has a suction pipe 2 for sucking refrigerant gas (fluid) into the sealed container 1 and a discharge pipe 3 for discharging refrigerant gas compressed in the sealed container 1 to the outside of the sealed container 1. Is provided. In this example, the suction pipe 2 is provided in the upper part of the sealed container 1, and the discharge pipe 3 is provided in the lower part of the sealed container 1.

  In the sealed container 1, there are provided a motor 4, a crankshaft 5 that is rotated by the driving force of the motor 4, and a compression mechanism section 6 that performs a compression operation for compressing refrigerant gas by the rotation of the crankshaft 5. Yes. The compression mechanism 6 is supported on the inner wall of the sealed container 1. In the sealed container 1, lubricating oil (oil) 7 is stored.

  The motor 4 is disposed above the compression mechanism unit 6. The motor 4 is supported by the compression mechanism unit 6 via the holder member 8. Further, the motor 4 includes a cylindrical stator 9 centering on an axis (motor axis) along the vertical direction, and a rotor 10 disposed inside the stator 9 and rotatable about the motor axis. Have.

  The stator 9 is provided with a stator winding 9a that generates a rotating magnetic field by receiving power. The rotor 10 is rotated around the motor axis by supplying power to the stator winding 9a.

  The crankshaft 5 is disposed along the vertical direction coaxially with the motor axis. The crankshaft 5 is fixed to the rotor 10 and is rotated integrally with the rotor 10. Further, the crankshaft 5 extends downward from the rotor 10 and penetrates the compression mechanism 6.

  An oil pump 11 immersed in the lubricating oil 7 is provided at the lower end of the crankshaft 5. The oil pump 11 generates power for pumping up the lubricating oil 7 by the rotation of the crankshaft 5. In the crankshaft 5, an oil supply path 12 that guides the lubricating oil 7 from the oil pump 11 to the compression mechanism 6 is provided. The lubricating oil 7 is supplied from the oil pump 11 to the compression mechanism 6 through the oil supply passage 12 as the crankshaft 5 is rotated.

  An intermediate portion of the crankshaft 5 is an eccentric portion 5a that is eccentric with respect to the motor axis. That is, the eccentric portion 5a is formed with an eccentric axis parallel to the motor axis as a center line, and is rotated about the motor axis.

  A pair of balance weights 13 and 14 for stabilizing the rotation of the crankshaft 5 are fixed to the crankshaft 5. Each balance weight 13 and 14 is arrange | positioned so that the compression mechanism part 6 may be pinched | interposed about the direction along a motor axis line.

  The compression mechanism unit 6 is disposed between the first fixed scroll 15 and the second fixed scroll 16 that face each other in the direction along the motor axis, and the first and second fixed scrolls 15, 16. The second fixed scrolls 15 and 16 have a turning scroll 17 that can turn in a radial direction (a direction perpendicular to the motor axis). The first and second fixed scrolls 15 and 16 are fixed in the sealed container 1 via the holder member 8.

  The eccentric portion 5 a is disposed between the first fixed scroll 15 and the second fixed scroll 16. The orbiting scroll 17 is disposed at the same position as the eccentric portion 5a in the direction along the motor axis. In this example, the first fixed scroll 15 is disposed above the orbiting scroll 17, and the second fixed scroll 16 is disposed below the orbiting scroll 17.

  Each of the first fixed scroll 15, the second fixed scroll 16, and the orbiting scroll 17 is provided with a through hole 18 through which the crankshaft 5 passes. A through hole 18 provided in the first fixed scroll 15 is provided with a first fixing bearing 19 that rotatably supports an upper part of the eccentric portion 5 a of the crankshaft 5, and the second fixed scroll 16. A through-hole 18 provided in the second shaft is provided with a second fixing bearing 20 that rotatably supports a portion below the eccentric portion 5a of the crankshaft 5. A through-hole 18 provided in the orbiting scroll 17 is provided with an orbiting bearing 21 that makes the orbiting scroll 17 rotatable with respect to the eccentric portion 5a.

  Lubricating oil 7 from the oil pump 11 is guided to the first fixing bearing 19, the second fixing bearing 20, and the turning bearing 21 by the oil supply passage 12.

  The first fixed scroll 15 includes a first fixed end plate 22 disposed perpendicular to the motor axis, and a first fixed spiral wall 23 provided in a spiral shape on the first fixed end plate 22. ing. The through hole 18 is provided in the central portion of the first fixed end plate 22.

  The first fixed spiral wall 23 is provided on the surface of the first fixed end plate 22 on the second fixed scroll 16 side. Therefore, in this example, the first fixed spiral wall 23 is provided on the lower surface (lower part) of the first fixed end plate 22. The first fixed spiral wall 23 is formed along an involute curve.

  The second fixed scroll 16 has a second fixed end plate 24 arranged perpendicular to the motor axis, and a second fixed spiral wall 25 provided in a spiral shape on the second fixed end plate 24. ing. The through hole 18 is provided in the central portion of the second fixed end plate 24.

  The second fixed spiral wall 25 is provided on the surface of the second fixed end plate 24 on the first fixed scroll 15 side. Therefore, in this example, the second fixed spiral wall 25 is provided on the upper surface (upper part) of the second fixed end plate 24. The second fixed spiral wall 25 is formed along an involute curve.

  First and second peripheral walls 26 and 27 that surround the orbiting scroll 17 and abut against each other are provided on the outer peripheral portions of the first and second fixed scrolls 15 and 16, respectively. Further, the compression mechanism section 6 is provided with a suction port 28 by separating a part between the first and second peripheral walls 26 and 27 from each other.

  The orbiting scroll 17 includes an orbiting end plate 29 arranged perpendicular to the motor axis, a first orbiting swirl wall 30 provided in a spiral shape on the surface of the orbiting end plate 29 on the first fixed scroll 15 side, The end plate 29 has a second swirl spiral wall 31 provided in a spiral shape on the surface of the second fixed scroll 16 side. Therefore, in this example, the first swirl spiral wall 30 is provided in the upper part of the swivel mirror plate 29, and the second swirl spiral wall 31 is provided in the lower part of the swirl mirror plate 29.

  A boss portion 29 a having a thickness larger than the thickness of the swivel end plate 29 is provided at the central portion of the swivel end plate 29. The through hole 18 is provided in the boss portion 29a.

  The first swirl spiral wall 30 is inserted between the walls of the first fixed spiral wall 23, and the second swirl spiral wall 31 is inserted between the walls of the second fixed spiral wall 25. The first and second swirl spiral walls 30, 31 are formed along involute curves, respectively.

  The spiral interval (first spiral interval) P1 by the first swirl spiral wall 30 and the spiral interval (second spiral interval) P2 by the second swirl spiral wall 31 are as shown in FIG. They are different from each other. Further, the interval between the spirals by the first fixed spiral wall 23 is the same as the first spiral interval P1, and the interval between the spirals by the second fixed spiral wall 25 is the same as the second spiral interval P2. In this example, as shown in FIG. 2, the first spiral interval P <b> 1 in the upper part of the swivel mirror plate 29 is made smaller than the second spiral interval P <b> 2 in the lower part of the swivel mirror plate 29.

  The first spiral interval P <b> 1 is an arrangement pitch of the first orbiting spiral walls 30 in a cross section in the radial direction of the orbiting scroll 17. The second spiral interval P <b> 2 is an arrangement pitch of the second orbiting spiral walls 31 in a cross section in the radial direction of the orbiting scroll 17.

  The wall thickness T1 of the first swirl spiral wall 30 and the wall thickness T2 of the second swirl spiral wall 31 are different from each other as shown in FIG. The wall thickness of the first fixed spiral wall 23 is the same as the wall thickness T1 of the first swirl spiral wall 30, and the wall thickness of the second fixed spiral wall 25 is the wall thickness of the second swirl spiral wall 31. It is the same as T2. In this example, as shown in FIG. 2, the wall thickness T1 of the first swirl spiral wall 30 is smaller than the wall thickness T2 of the second swirl spiral wall 31 (T1 <T2).

  The first swirl interval P1, the wall thickness T1 of the first swirl swirl wall 30, the second swirl interval P2, and the wall thickness T2 of the second swirl swirl wall 31 are such that the relationship of equation (1) holds. Is set.

  P1 / 2-T1 = P2 / 2-T2 (1)

  The dimension of the first swirl spiral wall 30 in the height direction (the direction along the motor axis) is the same as the dimension of the first fixed spiral wall 23 in the height direction. The height dimension of the second swirl spiral wall 31 is the same as the dimension of the second fixed spiral wall 25 in the height direction. The height dimension of each of the first swirl spiral wall 30 and the second swirl spiral wall 31 is equal to or larger than the height of the boss portion 29a.

  The side surface of the first swirl spiral wall 30 is partially in contact with the side surface of the first fixed spiral wall 23. Between the side surface of the first swirl spiral wall 30 and the side surface of the first fixed swirl wall 23, compression partitioned by the contact portion between the first swirl spiral wall 30 and the first fixed spiral wall 23. A chamber 32 is formed.

  The side surface of the second swirl spiral wall 31 is partially in contact with the side surface of the second fixed spiral wall 25. Compression divided between the side surface of the second swirl spiral wall 31 and the side surface of the second fixed spiral wall 25 by the contact portion between the second swirl spiral wall 31 and the second fixed spiral wall 25 A chamber 33 is formed.

  The orbiting scroll 17 moves on a circle centered on the motor axis by the rotation of the crankshaft 5 and turns. On the outer peripheral portion of the orbiting end plate 29, an Oldham screw 34 for turning the orbiting scroll 17 in the radial direction while suppressing the rotation of the orbiting scroll 17 is provided.

  The compression chambers 32 and 33 are moved toward the center of the compression mechanism 6 along the first and second fixed spiral walls 23 and 25 by the turning of the orbiting scroll 17. The volumes of the compression chambers 32 and 33 change as the orbiting scroll 17 turns, and become smaller as the center of the compression mechanism unit 6 is approached. Therefore, the refrigerant gas taken into the compression chambers 32 and 33 from the suction port 28 is compressed while moving toward the center of the compression mechanism unit 6 by the turning of the orbiting scroll 17.

  In the vicinity of the boss portion 29 a of the swivel end plate 29, a communication hole 35 that communicates between the compression chambers 32 and 33 is provided.

  The discharge tube 3 is connected to the second fixed end plate 24. In the second fixed end plate 24, a discharge cavity 36 communicated with the discharge pipe 3 is provided. The second fixed end plate 24 is provided with a discharge port 37 that communicates between the discharge cavity 36 and the compression chamber 33. The discharge port 37 is provided in the vicinity of the second fixing bearing 20.

  The refrigerant gas compressed in the compression chamber 32 is guided into the compression chamber 33 through the communication hole 35. The refrigerant gas compressed in the compression chamber 33 flows in the order of the discharge port 37, the discharge cavity 36 and the discharge pipe 3, and is discharged out of the sealed container 1. The discharge cavity portion 36 is provided with a check valve 38 that prevents the refrigerant gas from flowing backward from the discharge cavity portion 36 into the compression chamber 33.

  Next, the operation will be described. When the crankshaft 5 is rotated by supplying power to the motor 4, the orbiting scroll 17 is turned around the motor axis. At this time, the lubricating oil 7 is guided to the first fixing bearing 19, the second fixing bearing 20, and the turning bearing 21 through the oil supply passage 12 by the power of the oil pump 11. The lubricating oil 7 is also introduced into the compression chambers 32 and 33 via the bearings 19 to 21.

  When the turning scroll 17 is turned, the refrigerant gas sucked into the sealed container 1 from the suction pipe 2 is taken into the compression chambers 32 and 33 through the suction port 28.

  Thereafter, when the turning of the orbiting scroll 17 continues further, the compression chambers 32 and 33 move to the center of the compression mechanism 6 while reducing the volume, and the refrigerant gas in the compression chambers 32 and 33 is compressed.

  At this time, since the first spiral interval P1 is smaller than the second spiral interval P2, the fluid pressure received by the orbiting scroll 17 from the lower compression chamber 33 is larger than the fluid pressure received from the upper compression chamber 32. ing. Therefore, the direction of the resultant force of the pressure received by the orbiting scroll 17 is the direction in which it is pressed against the first fixed scroll 15 (ie, upward). In this example, the resultant force of the pressure received by the orbiting scroll 17 is greater than the weight of the orbiting scroll 17. That is, the orbiting scroll 17 is pressed against the first fixed scroll 15 against the dead weight of the orbiting scroll 17 due to the difference in fluid pressure received from the compression chambers 32 and 33.

  Thereafter, the refrigerant gas that has been compressed and reaches the vicinity of the center of the compression mechanism portion 6 flows from the compression chambers 32 and 33 in the order of the discharge port 37 and the discharge cavity portion 36, and is discharged to the discharge pipe 3.

  In such a scroll compressor, the spiral interval P1 due to the first swirl spiral wall 30 and the spiral interval P2 due to the second swirl spiral wall 31 are different from each other. The relationship among the interval P1, the interval P2 of the vortex by the second swirl spiral wall 31, the wall thickness T1 of the first swirl spiral wall 30 and the wall thickness T2 of the second swirl spiral wall 31 is P1 / 2−T1 = Since P2 / 2-T2 is satisfied, the refrigerant gas can be compressed simultaneously on both sides of the orbiting scroll 17, and the difference in fluid pressure received by the orbiting scroll 17 is maintained in a constant direction. The resultant force of the pressure received can be stabilized in a certain direction. Thereby, the vibration and inclination of the orbiting scroll 17 can be prevented, and the compression performance can be improved. In addition, the life can be extended. Furthermore, since the tilt of the orbiting scroll 17 can be suppressed without a special bearing structure, it is not necessary to provide a bearing structure on the outer peripheral edge of the orbiting scroll 17, and the size can be reduced with a simple configuration. .

  Note that the relationship of P1 / 2−T1 = P2 / 2−T2 may not be completely established due to, for example, molding errors of the first and second fixed scrolls 15 and 16 and the orbiting scroll 17. Even if it does not hold, it is allowed as long as it is within an error range in which the refrigerant gas can be compressed simultaneously on both sides of the swivel end plate 29. Therefore, it is sufficient that the relationship P1 / 2−T1 = P2 / 2 / T2 is substantially established to the extent that the refrigerant gas can be compressed simultaneously on both sides of the swivel end plate 29.

Embodiment 2. FIG.
In the first embodiment, the first spiral interval P1 in the upper part of the swivel mirror plate 29 is smaller than the second spiral interval P2 in the lower part of the swivel mirror plate 29. The interval P1 may be larger than the second spiral interval P2 in the lower part of the swivel end plate 29.

  3 is a cross-sectional view showing a scroll compressor according to Embodiment 2 of the present invention. 4 is a cross-sectional view showing the compression mechanism of FIG. In the figure, the first fixed scroll 15 is disposed above the orbiting scroll 17, and the second fixed scroll 16 is disposed below the orbiting scroll 17. The first swirl spiral wall 30 is provided at the upper part of the swivel mirror plate 29, and the second swirl spiral wall 31 is provided at the lower part of the swirl mirror plate 29.

  The first spiral interval P1 at the upper part of the swivel mirror plate 29 is made larger than the second spiral interval P2 at the lower part of the swivel mirror plate 29. The spiral interval by the first fixed spiral wall 23 is the same as the first spiral interval P1, and the spiral interval by the second fixed spiral wall 25 is the same as the second spiral interval P2.

  The wall thickness T1 of the first swirl spiral wall 30 is larger than the wall thickness T2 of the second swirl spiral wall 31 (T1> T2). The wall thickness of the first fixed spiral wall 23 is the same as the wall thickness T1 of the first swirl spiral wall 30, and the wall thickness of the second fixed spiral wall 25 is the same as the wall thickness T2 of the second swirl spiral wall 31. Identical.

  The first spiral interval P1, the wall thickness T1 of the first swirl swirl wall 30, the second swirl interval P2, and the wall thickness T2 of the second swirl swirl wall 31 satisfy the relationship of the above formula (1). Is set to Other configurations are the same as those in the first embodiment.

  In such a scroll compressor, the spiral interval P1 due to the first swirl spiral wall 30 provided on the upper part of the swivel mirror plate 29 is equal to the spiral of the second swirl spiral wall 31 provided on the lower part of the swirl mirror plate 29. Since it is made larger than the space | interval P2, the difference of the fluid pressure which the turning scroll 17 receives can be maintained below. Thereby, the resultant force of the fluid pressure can be applied to the orbiting scroll 17 without countering the weight of the orbiting scroll 17, and the direction of the force on the orbiting scroll 17 can be further stabilized. That is, the orbiting scroll 17 can be pressed against the second fixed scroll 16 below, and the direction in which the orbiting scroll 17 is pressed against the second fixed scroll 16 can be further stabilized.

Embodiment 3 FIG.
5 is a cross-sectional view showing a compression mechanism portion of a scroll compressor according to Embodiment 3 of the present invention. In the figure, a groove 41 is provided at each of the first fixed spiral wall 23, the second fixed spiral wall 25, the first swirl spiral wall 30, and the second swirl spiral wall 31 in the height direction. ing. Each groove 41 is provided on an end face along the thickness direction of each spiral wall 23, 25, 30, 31. Each groove 41 is provided along the length direction (direction along the spiral) of each spiral wall 23, 25, 30, 31. In this example, a groove 41 is also provided at the front end of the boss 29a in the height direction. Other configurations are the same as those of the second embodiment.

  In such a scroll compressor, a groove 41 is provided at each of the front ends in the height direction of the first fixed spiral wall 23, the second fixed spiral wall 25, the first swirl spiral wall 30, and the second swirl spiral wall 31. The lubricating oil 7 supplied into the compression mechanism 6 can be held in the groove 41. Therefore, due to the sealing effect by the lubricating oil 7, the gaps between the spiral walls 23, 25, 30, 31 and the end plates 22, 24, 29 (at the tip ends in the height direction of the spiral walls 23, 25, 30, 31). Leakage of the refrigerant gas from the gap) can be suppressed, and the compression performance can be improved. Further, the lubrication performance between the fixed scroll on the side on which the orbiting scroll 17 is pressed and the orbiting scroll 17 among the first and second fixed scrolls 15 and 16 can be improved.

  In the above example, the grooves 41 are formed at the respective leading ends in the height direction of the first fixed spiral wall 23, the second fixed spiral wall 25, the first swirl spiral wall 30, and the second swirl spiral wall 31. Although it is provided, it is not limited to providing the groove 41 in all of the spiral walls 23, 25, 30, 31. If 41 is provided, the above-described effect can be obtained.

Embodiment 4 FIG.
6 is a cross-sectional view showing a compression mechanism portion of a scroll compressor according to Embodiment 4 of the present invention. In the figure, a groove 41 and a groove are formed at the respective height direction tips of the first fixed swirl wall 23, the second fixed swirl wall 25, the first swirl swirl wall 30, and the second swirl swirl wall 31. 41 and a sealing member 51 inserted into the terminal 41 is provided. In this example, the groove 41 and the seal member 51 are also provided at the front end of the boss 29a in the height direction.

  Each groove 41 is provided on an end face along the thickness direction of each spiral wall 23, 25, 30, 31. Each groove 41 is provided along the length direction (direction along the spiral) of each spiral wall 23, 25, 30, 31.

  The seal member 51 is disposed along the groove 41. Further, the seal member 51 closes the gap at the tip in the height direction of the spiral walls 23, 25, 30, 31. Further, each seal member 51 can be displaced in the depth direction of the groove 41. Accordingly, the seal member 51 is displaced in the depth direction of the groove 41 following the change in the size of the gap at the height direction front ends of the spiral walls 23, 25, 30, 31. Other configurations are the same as those of the third embodiment.

  In such a scroll compressor, a groove 41 is provided at each of the front ends in the height direction of the first fixed spiral wall 23, the second fixed spiral wall 25, the first swirl spiral wall 30, and the second swirl spiral wall 31. And the seal member 51 inserted into the groove 41, the gap at the tip in the height direction of the spiral walls 23, 25, 30, 31 can be closed by the seal member 51. Therefore, leakage of the refrigerant gas from each gap can be further suppressed, and the compression performance can be further improved.

  In the above example, the groove 41 and the first fixed spiral wall 23, the second fixed spiral wall 25, the first swirl spiral wall 30, and the second swirl spiral wall 31 are provided at the front ends in the height direction. , The seal member 51 inserted into the groove 41 is provided, but is not limited to providing the groove 41 and the seal member 51 in all of the spiral walls 23, 25, 30, 31, and the spiral walls 23, 25, If the groove 41 and the seal member 51 are provided in at least one of the height direction tip portions 30 and 31, the above-described effect can be obtained.

Embodiment 5 FIG.
FIG. 7 is a cross-sectional view showing a compression mechanism portion of a scroll compressor according to Embodiment 5 of the present invention. In the figure, a first groove 61 and a first seal member inserted into the first groove 61 are provided at the respective height direction tips of the first fixed spiral wall 23 and the first swirl spiral wall 30. 62 is provided. In addition, a second groove 63 and a second seal member 64 inserted into the second groove 63 are provided at the respective height direction ends of the second fixed spiral wall 25 and the second swirl spiral wall 31. And are provided. In this example, a first groove 61 and a first seal member 62 are provided in a portion of the boss portion 29a on the first fixed end plate 22 side, and a second portion of the boss portion 29a on the second fixed end plate 24 side is provided. The groove 63 and the second seal member 64 are provided.

  The 1st and 2nd groove | channels 61 and 63 are provided in the end surface along the thickness direction of each spiral wall. Moreover, the 1st and 2nd groove | channels 61 and 63 are provided along the length direction of each spiral wall. Further, the second groove 63 is a groove having a width smaller than that of the first groove 61.

  The first seal member 62 is disposed along the first groove 61. Further, the first seal member 62 closes the gaps at the respective height direction tips of the first fixed spiral wall 23 and the first swirl spiral wall 30. Further, the first seal member 62 can be displaced in the depth direction of the first groove 61. Accordingly, the first seal member 62 follows the change in the size of the gap at the respective height direction tip portions of the first fixed spiral wall 23 and the first swirl spiral wall 30 to the depth of the first groove 61. It is displaced in the vertical direction.

  The second seal member 64 is disposed along the second groove 63. In addition, the second seal member 64 closes the gaps at the respective distal ends in the height direction of the second fixed spiral wall 25 and the second swirl spiral wall 31. Further, the second seal member 64 can be displaced in the depth direction of the second groove 63. Therefore, the second seal member 64 follows the change in the size of the gap at the respective height direction front ends of the second fixed spiral wall 25 and the second swirl spiral wall 31, and the depth of the second groove 63. It is displaced in the vertical direction.

  The width of the first seal member 62 is determined according to the width of the first groove 61, and the width of the second seal member 64 is determined according to the width of the second groove 63. Therefore, the width of the second seal member 64 is smaller than the width of the first seal member 62. Other configurations are the same as those of the fourth embodiment.

  In such a scroll compressor, the width of the first groove 61 is larger than the width of the second groove 63, and the width of the first seal member 62 provided in the first groove 61 is the second width. Since it is larger than the width of the second seal member 64 provided in the groove 63, the back pressure received by the first seal member 62 can be made larger than the back pressure received by the second seal member 64. . Accordingly, the fluid pressure received by the orbiting scroll 17 via the first seal member 62 can be made larger than the fluid pressure received by the orbiting scroll 17 via the second seal member 64, and the second fixed scroll. The force for pressing the orbiting scroll 17 to 16 can be further stabilized. In addition, the first fixed scroll 15 is disposed above the orbiting scroll 17 and the second fixed scroll 16 is disposed below the orbiting scroll 17, so that the force that presses the orbiting scroll 17 against the second fixed scroll 16 is increased. The weight of the orbiting scroll 17 can be further stabilized.

  Further, when the orbiting scroll 17 is pressed against the second fixed scroll 16, the height direction tip of the second fixed spiral wall 25 comes into contact with the orbiting end plate 29, and the height direction of the second orbiting spiral wall 31. Although the tip portion contacts the second fixed end plate 24, the width of the second groove 63 is smaller than the width of the groove of the first groove 61. Therefore, the contact area can be increased. Accordingly, it is possible to suppress wear caused by contact between the second fixed spiral wall 25 and the swivel end plate 29 and wear due to contact between the second swirl spiral wall 31 and the second fixed end plate 24, thereby extending the life. Can be achieved.

  Further, since the width of the first seal member 62 is larger than the width of the second seal member 64, the first seal member 62 and the first fixed spiral provided on the first swirl spiral wall 30 are used. The clearance W1 between the base portion of the wall 23 and the clearance W2 between the first seal member 62 provided on the first fixed spiral wall 23 and the root portion of the first swirl spiral wall 30 can be reduced. it can. Therefore, the amount of the refrigerant gas leaking through the space formed by the gaps W1 and W2 can be suppressed.

  In the above example, the first groove 61 and the first seal member 62 are provided at the front ends in the height direction of the first fixed spiral wall 23 and the first swirl spiral wall 30, respectively. You may provide the 1st groove | channel 61 and the 1st sealing member 62 in either the height direction front-end | tip part of the 1st fixed spiral wall 23 and the 1st turning spiral wall 30. FIG. Even in this case, the force for pressing the orbiting scroll 17 against the second fixed scroll 16 can be stabilized.

  In the above example, the second groove 63 and the second seal member 64 are provided at the respective leading ends of the second fixed spiral wall 25 and the second swirl spiral wall 31 in the height direction. You may provide the 2nd groove | channel 63 and the 2nd sealing member 64 in either the height direction front-end | tip part of the 2nd fixed spiral wall 25 and the 2nd swirl | vortex spiral wall 31. FIG. In this way, it is possible to further suppress any of wear due to contact between the second fixed spiral wall 25 and the swivel end plate 29 and wear due to contact between the second swirl spiral wall 31 and the second fixed end plate 24. And the life can be further extended.

It is sectional drawing which shows the scroll compressor by Embodiment 1 of this invention. It is sectional drawing which shows the compression mechanism part of FIG. It is sectional drawing which shows the scroll compressor by Embodiment 2 of this invention. It is sectional drawing which shows the compression mechanism part of FIG. It is sectional drawing which shows the compression mechanism part of the scroll compressor by Embodiment 3 of this invention. It is sectional drawing which shows the compression mechanism part of the scroll compressor by Embodiment 4 of this invention. It is sectional drawing which shows the compression mechanism part of the scroll compressor by Embodiment 5 of this invention.

Explanation of symbols

  15 First fixed scroll, 16 Second fixed scroll, 17 Orbiting scroll, 22 First fixed end plate, 23 First fixed swirl wall, 24 Second fixed end plate, 25 Second fixed swirl wall, 29 Orbit End plate, 30 first swirl spiral wall, 31 second swirl spiral wall, 32, 33 compression chamber, 41 groove, 51 seal member, 61 first groove, 62 first seal member, 63 second groove, 64 Second seal member.

Claims (5)

A first fixed scroll having a first fixed end plate and a first fixed spiral wall provided in a spiral shape on the first fixed end plate;
A second fixed spiral plate, and a second fixed spiral wall provided in a spiral shape on the second fixed mirror plate, the second fixed spiral wall facing the first fixed spiral wall; A second fixed scroll facing the first fixed scroll; a swivel end plate disposed between the first and second fixed scrolls; and the first fixed swirl wall provided in a spiral shape on the swivel end plate A first swirling spiral wall inserted between the walls, and a second swirling spiral wall provided in a spiral shape on the swivel end plate and inserted between the walls of the second fixed spiral wall, A turning scroll capable of turning in the radial direction with respect to the first and second fixed scrolls,
The volume of the compression chamber formed by contact between the side surface of the first fixed spiral wall and the side surface of the first swirl spiral wall, the side surface of the second fixed spiral wall, and the second swirl spiral wall The volume of the compression chamber formed by contact with the side surface of the scroll compressor is changed by the turning of the orbiting scroll, thereby compressing the fluid in the compression chamber,
The spiral spacing by the first swirl spiral wall is P1, the wall thickness of the first swirl spiral wall is T1, the spiral spacing by the second swirl spiral wall is P2, and the wall of the second swirl spiral wall If the thickness is T2,
P1 / 2-T1 = P2 / 2-T2
A scroll compressor characterized in that the relationship is substantially established and P1 and P2 are different. The first and second fixed scrolls face each other in the vertical direction,
The first swirl spiral wall is provided at the upper part of the swivel mirror plate, the second swirl spiral wall is provided at the lower part of the swirl mirror plate,
The scroll compressor according to claim 1, wherein a spiral interval P1 due to the first swirl spiral wall is larger than a spiral interval P2 due to the second swirl spiral wall.   A groove is provided in at least one of the height direction front ends of each of the first swirl spiral wall, the second swirl spiral wall, the first fixed spiral wall, and the second fixed spiral wall. The scroll compressor according to claim 1 or 2, wherein the scroll compressor is provided.   The scroll compressor according to claim 3, wherein a seal member is inserted into the groove. The spiral interval P1 due to the first swirl spiral wall is larger than the spiral interval P2 due to the second swirl spiral wall,
At least one of the first swirl spiral wall and the first fixed spiral wall in the height direction front end portion has a first groove and a first seal member inserted into the first groove. And
At least one of the second swirl spiral wall and the second fixed spiral wall in the height direction end portion has a second groove having a width smaller than the width of the first groove, and 3. The scroll compressor according to claim 1, further comprising a second seal member that is inserted into the second groove and has a smaller width than the first seal member. 4.

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