JP2011047328A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress intake heating in a passage from an intake hole to a closing-in position by reducing a difference in pressure between compression chambers adjacent to each other. <P>SOLUTION: A difference in pressure rise between compression chambers (A) and (B) can be reduced compared to a conventional scroll compressor in which the closing-in operation of both compression chambers is delayed by 180 degrees of a crank angle by delaying the closing-in operation of the compression chamber (B) by 90 to 150 degrees of a crank angle compared to that of the compression chamber (A). In addition, the gas passage from the intake hole to the closing-in point S of the compression chamber (A) can be shortened compared to that of the conventional scroll compressor in which the closing-in point S of the compression chamber (A) is displaced 180 degrees from the intake hole to suppress intake heating. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  In the present invention, the fixed scroll and the orbiting scroll are meshed with each other to form a compression chamber between them, and the use of the circular orbital motion of the orbiting scroll moves the compression chamber from the outer periphery to the center while reducing the volume. The present invention relates to a scroll compressor that repeatedly sucks, compresses and discharges fluid.

  Conventionally, in this type of scroll compressor, the winding end ends of both the fixed and orbiting scroll wraps are engaged with each other in a state of being shifted by approximately 180 °. FIG. 6 shows a correlation diagram between the fixed scroll and the orbiting scroll of the conventional scroll compressor. As shown in the figure, the winding end end Q1 of the fixed scroll 1 and the winding end end Q2 of the orbiting scroll 2 are positioned 180 ° apart from each other. A large intake gas passage 3 is formed after the winding end Q1 of the fixed scroll 1.

  FIG. 7 shows a correlation diagram between the fixed scroll and the orbiting scroll of another conventional scroll compressor. The inner wall of the fixed scroll 1 is extended from the winding end end Q3 of the fixed scroll 1 to a point Q4 facing the winding end end Q2 of the orbiting scroll 2, and the inner wall of the extension W is smoothly at the winding end end of the fixed scroll. The curve is continuous and has the same properties as those other than the extended portion (for example, see Patent Document 1).

Japanese Examined Patent Publication No. 62-29601

  However, in the scroll compressor of Patent Document 1, the pressure rises in the compression chamber A formed by the inner wall of the fixed scroll and the outer wall of the orbiting scroll, and the compression chamber B formed by the outer wall of the fixed scroll and the inner wall of the orbiting scroll. Since there is a difference, there is a problem that leakage due to a pressure difference occurs between the two compression chambers, and the performance deteriorates. On the other hand, in another conventional example, since the closing point of the compression chamber A is at a position shifted by 180 ° from the suction hole, suction heating occurs while passing through the suction gas passage up to that point, and the performance is reduced. Had problems.

  The present invention solves the above-described conventional problems, and reduces the pressure difference between the two compression chambers, and also reduces the suction heating in the passage from the suction hole to the closed position, thereby achieving highly efficient scroll compression. The purpose is to provide a machine.

  In order to solve the above-mentioned conventional problems, the scroll compressor of the present invention is such that the compression chamber B is closed with a crank angle delay of 90 ° to 150 ° with respect to the compression chamber A being closed.

  As a result, the difference in pressure increase between the compression chamber A and the compression chamber B can be reduced as compared with the conventional scroll compressor in which the compression of the compression chambers is delayed by a crank angle of 180 °. Further, the gas passage from the suction hole to the closing point of the compression chamber A can be made shorter than another conventional scroll compressor in which the closing point of the compression chamber A is located 180 ° away from the suction hole. Inhalation heating can be reduced.

  The scroll compressor according to the present invention can reduce leakage due to a pressure difference between the two compression chambers, and can reduce suction heating in the suction gas passage, thereby suppressing a decrease in performance.

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention Correlation diagram between fixed scroll and orbiting scroll in Embodiment 1 of the present invention The perspective view of the turning scroll in Embodiment 1 of this invention Correlation diagram of fixed scroll and orbiting scroll in embodiment 2 of the present invention The perspective view of the fixed scroll in Embodiment 2 of this invention Correlation diagram of fixed scroll and orbiting scroll of conventional scroll compressor Correlation diagram of fixed scroll and orbiting scroll of conventional scroll compressor

  The first invention is formed between the inner wall of the fixed scroll and the outer wall of the orbiting scroll by the fixed scroll having a spiral wrap on the end plate and the orbiting scroll having a wrap meshing with the fixed scroll. In the scroll compressor in which the compression chamber B is formed between the compression chamber A, the outer wall of the fixed scroll and the inner wall of the orbiting scroll, the crank angle is delayed by 90 ° to 150 ° with respect to the compression chamber A being closed. The compression chamber B is configured to be closed.

  Thereby, the difference in pressure increase between the compression chamber A and the compression chamber B can be reduced as compared with the conventional scroll compressor in which the compression of the compression chambers is delayed by a crank angle of 180 °. Leakage can be reduced. Further, the gas passage from the suction hole to the closing point of the compression chamber A may be made shorter than another conventional scroll compressor in which the closing point of the compression chamber A is at a position shifted by 180 ° from the suction hole. Inhalation heating in the intake gas passage can be reduced.

  In the second invention, in particular, a relief is provided on the outer wall at the end of winding of the orbiting scroll of the first invention, and the wrap thickness is reduced, so that a relief for forming an intake gas passage is formed on the inner wall of the fixed scroll. Therefore, the diameter of the fixed scroll member can be kept small.

  In the third aspect of the invention, in particular, since the relief is provided in the part other than the base of the outer wall at the end of the turn of the orbiting scroll of the second aspect of the invention, the thickness of the base of the stressed wrap can be maintained, so that the reliability is lowered. Can be suppressed.

  In the fourth aspect of the invention, in particular, by providing a relief on the inner wall at the end of winding of the fixed scroll according to the first aspect of the invention, a large relief for forming the suction gas passage can be taken, and the suction gas is released from the wall surface. Inhalation heating can be suppressed because it is not easily affected by heat.

  In the fifth invention, in particular, the escape of the inner wall at the end of winding of the fixed scroll of the fourth invention is provided on the bottom side of the wrap, leaving the thrust part with the orbiting scroll, Since the seal length with the suction chamber can be maintained, leakage of refrigerant gas into the suction chamber can be prevented.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention. FIG. 2 is a correlation diagram between the fixed scroll and the orbiting scroll in the first embodiment of the present invention, and shows the positional relationship.

  In FIG. 1, a fixed scroll 14 is fixed between a main bearing member 13 of a crankshaft 12 fixed by welding or shrink fitting in a sealed container 11 and a fixed scroll 14 bolted on the main bearing member 13. A scroll-type compression mechanism 16 is configured by sandwiching the meshing orbiting scroll 15, and an Oldham ring or the like that guides the orbiting scroll 15 to rotate in a circular orbit while preventing the orbiting scroll 15 from rotating between the orbiting scroll 15 and the main bearing member 13. An anti-rotation mechanism 17 is provided, and the orbiting shaft portion 12 a at the upper end of the crankshaft 12 is fitted to the orbiting bearing 18 provided on the orbiting scroll 15. A suction chamber 19 for sucking refrigerant gas is provided on the outer peripheral portion of the fixed scroll 14, and a suction pipe 20 communicating with the outside of the sealed container 11 is fitted. The lower end of the crankshaft 12 reaches an oil reservoir 21 below the sealed container 11 and is pivotally supported by a secondary bearing member 22 fixed by welding or shrink fitting in the sealed container 11.

  The electric motor 23 is located between the main bearing member 13 and the auxiliary bearing member 22, and is integrally coupled to the stator 23 a fixed to the sealed container 11 by welding or shrink fitting, and the outer periphery in the middle of the crankshaft 12. The rotor 23b and the crankshaft 12 are stably rotated on the outer peripheral portions of the upper and lower end surfaces of the rotor 23b, and the orbiting scroll 15 is stably moved in a circular orbit. Balance weights 25a and 25b fixed by 24 are provided.

  The oil supply mechanism is constituted by a pump 26 driven at the lower end of the crankshaft 12, and an oil supply passage 27 penetrating in the axial direction is formed in the crankshaft 12 to supply oil in the oil reservoir 21.

  A back pressure chamber 28 is formed on the outer periphery of the orbiting scroll 15 by the fixed scroll 14 and the main bearing member 13, and the back pressure chamber radially extends from the orbiting bearing portion space 29 formed between the orbiting shaft portion 12 a and the orbiting scroll 15. An oil supply path 30 penetrating to 28 is provided in the end plate 15 a of the orbiting scroll 15. The main bearing member 13 side of the end plate 15a of the orbiting scroll 15 is partitioned by a sealing material 31 having a rectangular cross section disposed on the main bearing member 13, and the inside is a high pressure and the outside is a back pressure chamber 28. The suction chamber 19 communicates with the suction communication passage 32, and a back pressure control mechanism is provided in the suction communication passage 32.

  In FIG. 2, the outer wall in the range of 30 ° to 90 ° (up to the point S) from the winding end Q5 of the outer wall at the end of the orbiting scroll 15 is offset, and a relief portion is provided to reduce the wrap thickness. Yes.

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. As the crankshaft 12 is rotationally driven by the electric motor 23, the orbiting shaft portion 12a at the upper end of the crankshaft 12 is eccentrically driven to cause the orbiting scroll 15 to move in a circular orbit, whereby the fixed scroll 14 and the orbiting scroll 15 By using the fact that the compression chamber formed between the outer peripheral side becomes smaller while moving from the outer peripheral side to the central portion, the suction pipe 20 that communicates with the outside of the sealed container 11 and the suction chamber 19 on the outer peripheral portion of the fixed scroll 14 generate refrigerant. The gas is sucked in and compressed, and the refrigerant gas having a predetermined pressure or higher is repeatedly discharged from the discharge hole 33 at the center of the fixed scroll 14 to the discharge chamber 35 in the container by opening the discharge valve 34.

The discharged refrigerant gas passes through the discharge gas passage 36 penetrating the compression mechanism section 16 and reaches the upper portion of the rotor 23b, passes through the rotor gas passage 37 penetrating the rotor 23b, and enters the lower portion of the hermetic container 11. Guided through the stator gas passage 38 disposed on the outer periphery of the stator 23a and the notch of the compression mechanism portion disposed on the outer periphery of the compression mechanism portion 16 and reaches the upper portion of the sealed container 11, and is discharged from the discharge pipe 39 to the outside of the sealed container 11. Discharged.

  The oil in the oil reservoir 21 is supplied to the swivel bearing space 29 through an oil supply passage 27 that passes through the crankshaft 12 in the axial direction by a pump 26. The supplied oil is branched into two systems, and one system lubricates the slewing bearing 18 and the slewing shaft portion 12a, lubricates the main shaft portion 12b and the main bearing 40, and then drops under the main bearing member 13, finally. The oil is collected in the oil reservoir 21. The other system is guided to the back pressure chamber 28 through the oil supply path 30 by the differential pressure between the slewing bearing space 29 and the back pressure chamber 28.

  Here, the compression chamber A formed between the inner wall of the fixed scroll 14 and the outer wall of the orbiting scroll 15 has an outer wall in the range of 30 ° to 90 ° from the winding end Q5 of the outer wall at the end of the orbiting scroll 15. Since the offset processing is performed, the closing point S of the compression chamber A is delayed by a crank angle of 30 ° to 90 ° compared to the case where the offset processing is not performed, and the escape portion that has been offset processed becomes the intake gas passage 41. The suction gas passage 41 is formed shorter than the case where the closing point S of the compression chamber A is at a position shifted by 180 ° from the suction hole.

  On the other hand, the compression chamber B formed between the outer wall of the fixed scroll 14 and the inner wall of the orbiting scroll 15 is closed against the compression chamber A when the outer wall near the end of winding of the orbiting scroll 15 is not offset. Compared to the 180 ° delay, the offset process is performed in the range of 30 ° to 90 °, so the delay in closing is 90 ° to 150 °. The difference in pressure increase from B can be reduced.

  As described above, in the present embodiment, the outer wall in the range of 30 ° to 90 ° from the winding end Q5 of the outer wall at the winding end of the orbiting scroll 15 is offset, and a relief portion is provided to reduce the wrap thickness. As a result, the compression chamber A formed between the inner wall of the fixed scroll 14 and the outer wall of the orbiting scroll 15 is closed with a crank angle delayed by 30 ° to 90 ° compared to the case where the offset processing is not performed. The compression chamber B formed between the outer wall of the scroll 14 and the inner wall of the orbiting scroll 15 has a closing delay of 90 ° to 150 ° with respect to the compression chamber A, and the outer wall near the end of winding of the orbiting scroll 15 is When the offset processing is not performed, the difference in the pressure increase between the compression chamber A and the compression chamber B can be reduced by the amount of the delay in closing compared to the 180 ° delay, It can reduce the leakage due to the pressure difference between the compression chamber.

  Further, the relief portion that has been offset is a suction gas passage 41, and the suction gas passage 41 is formed shorter than when the closing point S of the compression chamber A is at a position shifted by 180 ° from the suction hole. The suction heating at 41 can be reduced.

  Here, when the delay in the closing of the compression chamber B with respect to the compression chamber A becomes 150 ° or more, the pressure difference between the two compression chambers increases, thereby increasing the loss due to leakage between the two compression chambers. On the other hand, when the delay in closing the compression chamber B with respect to the compression chamber A becomes 90 ° or less, the suction gas passage 41 from the suction hole to the compression point A of the compression chamber A becomes longer, and the suction heating of the suction gas is thereby increased. Become. Therefore, in order to reduce the suction heating while suppressing the loss due to leakage, it is effective to set the delay of the closing of the compression chamber B with respect to the compression chamber A to 90 ° to 150 °.

  Further, by applying an offset process to the outer wall near the end of winding of the orbiting scroll 15 to reduce the wrap thickness, it is not necessary to create an escape portion for forming the suction gas passage 41 on the inner wall of the fixed scroll 14. The diameter of the member of the fixed scroll 14 can be kept small.

In addition, as shown in FIG. 3, if the portion other than the base of the outer wall near the end of winding of the orbiting scroll 15 is offset to provide a relief portion, the thickness of the base of the stressed wrap can be maintained. Reduction in reliability can be suppressed.

(Embodiment 2)
The scroll compressor according to the second embodiment of the present invention is similar in configuration, operation, and action to those in the first embodiment, and therefore, description of overlapping parts is omitted.

  FIG. 4 is a correlation diagram between the fixed scroll and the orbiting scroll in the second embodiment of the present invention, and shows the positional relationship. In FIG. 4, a relief portion is provided on the inner wall in the range of 30 ° to 90 ° (up to point S) from the winding end Q4 of the inner wall at the end of winding of the fixed scroll 14.

  Here, the compression chamber A formed between the inner wall of the fixed scroll 14 and the outer wall of the orbiting scroll 15 is a relief portion within a range of 30 ° to 90 ° from the winding end Q4 of the inner wall at the winding end of the fixed scroll 14. Therefore, the closing point S of the compression chamber A is delayed by a crank angle of 30 ° to 90 ° compared to the case where there is no escape portion, the relief portion becomes the intake gas passage 41, and the closing point S of the compression chamber A is The intake gas passage 41 is formed shorter than the case where the intake gas passage 41 is 180 degrees away from the intake hole.

  On the other hand, the compression chamber B formed between the outer wall of the fixed scroll 14 and the inner wall of the orbiting scroll 15 is closed to the compression chamber A when no escape portion is provided on the inner wall near the end of winding of the fixed scroll 14. Compared to the 180 ° delay, the relief portion is provided in the range of 30 ° to 90 °, so the delay in closing is 90 ° to 150 °. The difference in pressure increase with the chamber B can be reduced.

  As described above, in the second embodiment, the escape wall is provided in the range of 30 ° to 90 ° from the winding end Q4 of the inner wall at the end of winding of the fixed scroll 14, so that the inner wall of the fixed scroll 14 and the orbiting scroll 15 are provided. The compression chamber A formed between the outer wall of the fixed scroll 14 and the inner wall of the orbiting scroll 15 is closed with a crank angle delayed by 30 ° to 90 ° compared to the case where no escape portion is provided. In the compression chamber B formed between the compression chamber A and the compression chamber A, the delay in closing is 90 ° to 150 °, and 180 ° when no escape portion is provided on the inner wall near the end of winding of the fixed scroll 14. Since the difference in pressure rise between the compression chamber A and the compression chamber B can be reduced as much as the delay in confinement becomes smaller than the delay, the leakage due to the pressure difference between the compression chambers can be reduced.

  Further, the escape portion becomes the suction gas passage 41, and the suction gas passage 41 is formed shorter than the case where the closing point S of the compression chamber A is shifted by 180 ° from the suction hole, and the inner wall near the end of winding of the fixed scroll 14. Since the escape portion can be made larger by providing the escape portion, the intake gas is hardly affected by the heat from the wall surface, so that the intake heating in the intake gas passage 41 can be reduced.

  Here, when the delay in the closing of the compression chamber B with respect to the compression chamber A becomes 150 ° or more, the pressure difference between the two compression chambers increases, thereby increasing the loss due to leakage between the two compression chambers. On the other hand, when the delay in closing the compression chamber B with respect to the compression chamber A becomes 90 ° or less, the suction gas passage 41 from the suction hole to the compression point A of the compression chamber A becomes longer, and the suction heating of the suction gas is thereby increased. Become.

  Therefore, in order to reduce the suction heating while suppressing the loss due to leakage, it is effective to set the delay of the closing of the compression chamber B with respect to the compression chamber A to 90 ° to 150 °.

Further, as shown in FIG. 5, if the escape portion of the inner wall near the end of winding of the fixed scroll 14 is provided on the bottom side of the wrap while leaving the thrust portion with the orbiting scroll 15, the outer periphery of the end plate 15a of the orbiting scroll 15 and Since the seal length with the suction chamber 19 can be maintained, the refrigerant gas can be prevented from leaking into the suction chamber 19.

  As described above, the scroll compressor according to the present invention includes the compression chamber A formed by the inner wall of the fixed scroll and the outer wall of the orbiting scroll, and the compression chamber B formed by the outer wall of the fixed scroll and the inner wall of the orbiting scroll. The difference in pressure rise can be reduced compared with the conventional scroll compressor in which the compression chambers are closed 180 degrees behind the crank angle. Further, since the gas passage from the suction hole to the closing point of the compression chamber A can be made shorter than the conventional scroll compressor in which the closing point of the compression chamber A is shifted by 180 ° from the suction hole, both Leakage due to a pressure difference between the compression chambers can be reduced, and suction heating in the suction gas passage can be reduced, so that a decrease in performance can be suppressed, and a highly efficient scroll compressor can be provided. Furthermore, it is possible to make the product more comfortable and environmentally friendly as an air conditioner such as a room air conditioner or a heat pump water heater.

DESCRIPTION OF SYMBOLS 11 Sealed container 12 Crankshaft 12a Orbiting shaft part 12b Main axis part 13 Main bearing member 14 Fixed scroll 15 Orbiting scroll 15a End plate 16 Compression mechanism 17 Anti-rotation mechanism 18 Orbiting bearing 19 Suction chamber 20 Suction pipe 21 Oil reservoir 22 Sub bearing member 23 Electric motor 23a Stator 23b Rotor 24 Pins 25a, 25b Balance weight 26 Pump 27 Oil supply passage 28 Back pressure chamber 29 Swivel bearing space 30 Oil supply passage 31 Sealing material 32 Suction communication passage 33 Discharge hole 34 Discharge valve 35 Discharge chamber in container 36 Discharge Gas passage 37 Rotor gas passage 38 Stator gas passage 39 Discharge pipe 40 Main bearing 41 Suction gas passage (relief part)
A Compression chamber formed between the inner wall of the fixed scroll and the outer wall of the orbiting scroll B B Compression chamber formed between the outer wall of the fixed scroll and the inner wall of the orbiting scroll Q4 End of winding of the inner wall of the fixed scroll Q5 Orbiting scroll Winding end of outer wall S of the compression chamber A

Claims (5)

A compression chamber A formed between the inner wall of the fixed scroll and the outer wall of the orbiting scroll by a fixed scroll having a spiral wrap on the end plate and a orbiting scroll having a wrap meshing with the fixed scroll. And a compression chamber B formed between the outer wall of the fixed scroll and the inner wall of the orbiting scroll, a crank of 90 ° to 150 ° with respect to the compression chamber A being closed A scroll compressor characterized in that the compression chamber B is closed with an angle delay. The scroll compressor according to claim 1, wherein an escape portion is provided on an outer wall at a winding end of the orbiting scroll. The scroll compressor according to claim 2, wherein a relief portion is provided in a portion other than the base of the outer wall at the end of winding of the orbiting scroll. The scroll compressor according to claim 1, wherein an escape portion is provided on an inner wall at a winding end of the fixed scroll. 5. The scroll compressor according to claim 4, wherein a relief portion of an inner wall at the end of winding of the fixed scroll is provided on a bottom surface side of the wrap leaving a thrust portion with the orbiting scroll.