JP2008157121A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain leakage by improving floating of a seal material, and to restrain deterioration of efficiency. <P>SOLUTION: A seal groove 33 in a range shorter than an involute angle 360° is provided on an end of the winding start and the winding end of a lap 15b of at least one of a fixed scroll 14 and a turning scroll 15, a chip seal 34 is fitted in the seal groove 33, and high pressure oil is supplied to a back surface of the chip seal 34, and thereby, the tip seal 34 is easily floated from the seal groove 33, and sealing efficiency is improved, and leakage can be restrained. <P>COPYRIGHT: (C)2008,JPO&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, this type of scroll compressor is provided with a sealing material at the tip of either or both of the fixed scroll and the orbiting scroll (see, for example, Patent Document 1).

FIG. 3 shows a longitudinal sectional view of a compression mechanism portion of a conventional scroll compressor described in Patent Document 1. As shown in FIG. As shown in FIG. 3, a sealing material 2 is provided at the tip of the wrap 1.
Japanese Patent Laid-Open No. 6-193568

  However, in the conventional configuration, since the length of the sealing material is long, the sealing material does not lift well from the sealing groove and the sealing becomes insufficient, and the winding of the wrap starts at the start of winding due to the temperature difference between the winding start and the winding end. The thermal expansion of the sealing material is increased, the gap between the sealing groove and the sealing material is decreased, the floating method is uneven, and there is a problem that leakage occurs and performance is deteriorated.

  The present invention solves the above-described conventional problems, and an object thereof is to provide a highly efficient scroll compressor by improving sealing performance and suppressing leakage.

  In order to solve the above-mentioned conventional problems, the scroll compressor of the present invention has a seal groove in a range shorter than an expansion angle of 360 ° so that the seal material is uniformly lifted on the wrap winding start side and the wrap winding end side. It is to make.

  As a result, the sealing material can easily float from the sealing groove, improving the sealing performance and suppressing leakage.

  Since the scroll compressor of the present invention can improve sealing performance and suppress leakage, performance degradation can be suppressed.

  According to a first aspect of the present invention, a plurality of compression chambers are formed by a fixed scroll having a spiral wrap on an end plate, and a turning scroll having a wrap meshing with the wrap of the fixed scroll. In a scroll compressor that performs compression while reducing the volume toward the center of the compression chamber, an extension angle is provided at the wrap winding start and / or wrap winding end of either or both of the fixed scroll and the orbiting scroll. By providing a seal groove in a range shorter than 360 °, fitting the seal material into the seal groove, and supplying high-pressure oil to the back of the seal material, the seal material can easily float from the seal groove, from the beginning of the wrap to the end of winding. Sealability is improved and leakage can be suppressed.

  In particular, the width of the seal groove according to the first aspect of the invention is such that the width of the groove provided at the start of winding of the wrap is larger than the width of the groove provided at the end of winding of the wrap. The difference in the thermal expansion of the sealing material due to the temperature difference between the winding end and the winding end, the gap between the sealing groove and the sealing material on the winding start side of the wrap with higher temperature and higher thermal expansion becomes smaller, and the lifting of the sealing material worsens Since this can be avoided and the sealing performance can be improved, leakage can be suppressed.

  In particular, the depth of the seal groove of the first invention is set so that the depth of the groove provided at the start of winding of the wrap is deeper than the depth of the groove provided at the end of winding of the wrap. The difference in the thermal expansion of the sealing material due to the temperature difference between the winding start and the winding end, the back space of the sealing material on the winding start side of the wrap with higher temperature and higher thermal expansion becomes narrower, and high pressure oil is difficult to spread. Since it is possible to avoid deterioration of the lift and improve the sealing performance, it is possible to suppress leakage.

  In the fourth invention, in particular, by making the width of the sealing material of the first invention smaller than the width of the sealing material fitted at the end of winding of the wrap, the width of the sealing material fitted at the beginning of winding of the wrap, Even if there is a difference in the thermal expansion of the sealing material due to the temperature difference between the winding start and winding end of the wrap, the sealing performance can be improved without reducing the gap between the sealing groove on the winding start side and the sealing material, Leakage can be suppressed. In addition, since the width of the seal groove on the wrap winding start side and the wrap winding end side can be made the same, workability can be improved.

  In the fifth invention, in particular, the thickness of the sealing material of the first invention is set so that the thickness of the sealing material fitted at the start of winding of the wrap is thinner than the thickness of the sealing material fitted at the end of winding of the wrap. Therefore, even if there is a difference in the thermal expansion of the sealing material due to the temperature difference between the start and end of wrapping, the high pressure oil is distributed without narrowing the back gap of the sealing material on the winding start side. As a result, the sealing performance can be improved.

  The sixth aspect of the invention is, in particular, the linear expansion coefficient of the sealing material of the first aspect of the invention, and the linear expansion coefficient of the sealing material fitted at the beginning of the wrap winding. By making it smaller, the thermal expansion of the sealing material on the wrap winding start side and the sealing material on the wrap winding end side can be made the same even if there is a temperature difference between the wrap winding start and the winding end. The sealing material can be easily lifted from the beginning to the end of winding, and the sealing performance can be improved. Further, since the width and depth of the seal groove on the wrap winding start side and the wrap winding end side can be made the same, workability can be improved.

  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 a first embodiment of the present invention. FIG. 2 is a perspective view of the orbiting scroll according to the first embodiment of the present invention.

In FIG. 1 and FIG. 2, fixing is performed between the main bearing member 13 of the crankshaft 12 fixed in the sealed container 11 by welding or shrink fitting and the fixed scroll 14 bolted on the main bearing member 13. An Oldham that sandwiches the orbiting scroll 15 meshing with the scroll 14 to form a scroll-type compression mechanism 16 and guides the orbiting scroll 15 to rotate between the orbiting scroll 15 and the main bearing member 13 so as to move in a circular orbit. A rotation prevention mechanism 17 using a ring or the like is provided, and a turning shaft portion 12 a at the upper end of the crankshaft 12 is fitted to a turning bearing 18 provided on the turning 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 up 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.

  A seal groove 33 is provided at a leading end of the wrap 15b of the orbiting scroll 15 at a winding angle shorter than 360 °, and a tip seal 34 is fitted in the seal groove 33 to insert a tip on the winding start side. A chip seal back surface oil supply hole 35 a that communicates the back space of the seal 34 and the oil supply path 30 is provided, and a chip seal back surface oil supply hole 35 b that communicates the back space of the tip seal 34 on the winding end side and the back pressure chamber 28 is provided.

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, 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 move the orbiting scroll 15 in a circular orbit, thereby causing the fixed scroll 14 and the orbiting scroll to move. The suction chamber 36 formed between the suction pipe 20 and the stationary scroll 14 is connected to the outside of the sealed container 11 by using the small compression chamber 36 that is formed between the suction pipe 20 and the fixed scroll 14. The refrigerant gas is sucked in from 19 and compressed, and the refrigerant gas having a predetermined pressure or higher is discharged from the discharge hole 37 at the center of the fixed scroll 14 to the discharge chamber 39 in the container by opening the discharge valve 38. repeat.

  The discharged refrigerant gas passes through the discharge gas passage 40 penetrating the compression mechanism section 16 and reaches the upper portion of the rotor 23b, passes through the rotor gas passage 41 penetrating the rotor 23b, and enters the lower portion of the hermetic container 11. Guided through the stator gas passage 42 disposed on the outer periphery of the stator 23a and the compression mechanism section notch 43 disposed on the outer periphery of the compression mechanism section 16 and reaching the upper portion of the sealed container 11, and from the discharge pipe 44 to the outside of the sealed container 11 Is 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 part 12a, lubricates the main shaft part 12b and the main bearing 45, 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 tip seal 34 at the beginning and end of winding of the wrap 15b of the orbiting scroll 15 is shorter than 360 ° and supplies high-pressure oil to the back space, so that it easily floats, and from the beginning of winding of the wrap 15b. Leakage of the tip until the end of winding can be suppressed.

  As described above, in the present embodiment, the seal groove 33 is provided in a range shorter than the expansion angle of 360 ° at the leading end of the wrap 15b of the orbiting scroll 15 and the end of the winding. 34 is fitted, and a tip seal back surface oil supply hole 35a is provided to communicate the back space of the tip seal 34 on the winding start side and the oil supply path 30, and the chip communicating the back space of the tip seal 34 on the winding end side and the back pressure chamber 28 is provided. By providing the seal back surface oil supply hole 35b, the tip seal 34 is easily lifted, so that leakage of the tip from the start to the end of winding of the wrap 15b can be suppressed.

  Further, by making the width of the seal groove 33 larger than the width of the seal groove 33 provided at the end of winding of the wrap 15b, the width of the seal groove 33 provided at the start of winding of the wrap 15b is larger than the width of the seal groove 33 provided at the end of winding of the wrap 15b. Even if the width of the tip seal 34 on the winding start side with a high temperature is larger than the width of the tip seal 34 on the winding end side with a low temperature, the width direction of the seal groove 33 and the tip seal 34 is Since the gap can be made uniform on the winding start side and the winding end side, the tip seal 34 can easily rise and improve the sealing performance, so that leakage can be suppressed from the winding start to the winding end.

  Further, the depth of the seal groove 33 is made deeper than the depth of the seal groove 33 provided at the end of winding of the wrap 15b so that the depth of the seal groove 33 provided at the start of winding of the wrap 15b is increased. Even if the thickness of the tip seal 34 on the winding start side with a high temperature becomes thicker than the thickness of the tip seal 34 on the winding end side with a low temperature due to the difference in thermal expansion due to the temperature difference at the end of winding, the back space of the tip seal 34 is reduced. Since the winding start side and the winding end side can be made uniform, high-pressure oil spreads in the back space, and the tip seal 34 can float and improve the sealing performance, so that leakage can be suppressed from the winding start to the winding end. it can.

  Further, by making the width of the tip seal 34 smaller than the width of the tip seal 34 fitted at the end of winding of the wrap 15b, the width of the tip seal 34 fitted at the beginning of winding of the wrap 15b is reduced. Due to the difference in thermal expansion due to the temperature difference at the end of winding, the width of the tip seal 34 on the winding start side with high temperature is the same as the width of the tip seal 34 on the winding end side with low temperature, and the width of the seal groove 33 and tip seal 34 is reduced. Since the gap in the direction can be made uniform on the winding start side and the winding end side, the tip seal 34 can easily rise and improve the sealing performance, so that leakage can be suppressed from the winding start to the winding end. Moreover, since the width | variety of the seal groove 33 of the winding start side of the wrap 15b and the winding end side of the wrap 15b can be made the same, workability can be improved.

Further, the thickness of the tip seal 34 is set so that the thickness of the tip seal 34 fitted at the beginning of the wrap 15b is smaller than the thickness of the tip seal 34 fitted at the end of the wrap 15b. Due to the difference in thermal expansion due to the temperature difference between the beginning and the end of winding, the thickness of the tip seal 34 on the winding start side with a high temperature is the same as the thickness of the tip seal 34 on the winding end side with a low temperature. Can be made uniform on the winding start side and winding end side, so that high-pressure oil spreads in the back space, and the tip seal 34 floats up and improves the sealing performance. Can do.

  Further, by making the linear expansion coefficient of the tip seal 34 smaller than the linear expansion coefficient of the tip seal 34 fitted at the end of winding of the wrap 15b, the linear expansion coefficient of the tip seal 34 fitted at the start of winding of the wrap 15b is made smaller. Since the thermal expansion due to the temperature difference between the winding start and the winding end of the wrap 15b can be made the same, the tip seal 34 can easily float from the winding start to the winding end of the wrap 15b, and the sealing performance can be improved. Moreover, since the width | variety and the depth of the seal groove 33 of the winding start side of the wrap 15b and the winding end side of the wrap 15b can be made the same, workability can be improved.

  As described above, since the scroll compressor according to the present invention can improve the tip seal floating, it is possible to suppress a decrease in performance due to leakage at the end of the wrap, thereby providing a highly efficient scroll compressor. can do. 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.

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention The perspective view of the turning scroll in Embodiment 1 of this invention A longitudinal sectional view of a compression mechanism of a conventional scroll compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Sealed container 12 Crankshaft 12a Turning shaft part 12b Main shaft part 13 Main bearing member 14 Fixed scroll 14a End plate 15 Turning scroll 15a End plate 15b Wrap 16 Compression mechanism 17 Rotation prevention mechanism 18 Turning 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 portion space 30 Oil supply passage 31 Seal material 32 Suction communication passage 33 Seal groove 34 Chip seal 35a, 35b Tip seal back surface oil supply hole 36 Compression chamber 37 Discharge hole 38 Discharge valve 39 Discharge chamber in container 40 Discharge gas passage 41 Rotor gas passage 42 Stator gas passage 43 Notch 44 Compression mechanism section Discharge pipe 45 Main bearing

Claims (6)

A plurality of compression chambers are formed by a fixed scroll having a spiral wrap on the end plate and a orbiting scroll having a wrap meshing with the wrap of the fixed scroll. In the scroll compressor that performs compression while reducing the volume, the expansion angle is shorter than 360 ° at the wrap winding start and the wrap winding end of either or both of the fixed scroll and the orbiting scroll. A scroll compressor characterized in that a seal groove of a range is provided, a seal material is fitted into the seal groove, and high pressure oil is supplied to the back surface of the seal material. 2. The scroll compressor according to claim 1, wherein the width of the seal groove is made larger than the width of the groove provided at the end of the wrap winding. 2. The scroll compressor according to claim 1, wherein the depth of the seal groove is set such that the depth of the groove provided at the start of winding of the wrap is deeper than the depth of the groove provided at the end of winding of the wrap. 2. The scroll compressor according to claim 1, wherein the width of the sealing material is made smaller than the width of the sealing material fitted at the end of winding of the wrap. 2. The scroll compression according to claim 1, wherein the thickness of the sealing material is set so that the thickness of the sealing material fitted at the start of winding of the wrap is thinner than the thickness of the sealing material fitted at the end of winding of the wrap. Machine. The linear expansion coefficient of the sealing material is set so that the linear expansion coefficient of the sealing material fitted at the beginning of winding of the wrap is smaller than the linear expansion coefficient of the sealing material fitted at the end of winding of the wrap. The scroll compressor described.

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