JP4520133B2 - Scroll type fluid machine - Google Patents

Description

  The present invention relates to a scroll fluid machine suitable for use in, for example, a compressor that compresses air, a refrigerant, or the like, or a vacuum pump.

  Generally, as a scroll type fluid machine, for example, a scroll type air compressor that compresses air is known. This scroll compressor is provided on a casing, a fixed side member including a fixed scroll having a spiral wrap portion standing on the surface of the end plate, and a swivel compressor facing the fixed scroll. A revolving scroll having a spiral wrap portion standing on the surface of the end plate so as to overlap the wrap portion of the fixed scroll and defining a plurality of compression chambers, and rotatably provided in the casing and rotated by an electric motor And a drive shaft for rotating the orbiting scroll by being driven.

  In addition, a cooling fan is provided on the drive shaft, and the cooling fan is rotationally driven together with the drive shaft to supply cooling air to the back side of the orbiting scroll for cooling.

  Here, the drive shaft is rotatably supported by the casing via a main bearing, and a crankshaft portion is provided at a position eccentric from the rotation axis on the tip side. And the front end side of a crankshaft part is attached to the boss | hub part formed in the back surface of the end plate of a turning scroll via the turning bearing (for example, refer patent document 1).

Japanese Utility Model Publication No. 58-146894

  By the way, the scroll type compressor by patent document 1 mentioned above generate | occur | produces heat (compression heat) by the compression action at this time by compressing air in the compression chamber formed between a fixed scroll and a turning scroll. . Therefore, the cooling scroll generated by the cooling fan is supplied to cool the orbiting scroll and the like.

  However, the compression chamber formed between the fixed scroll and the orbiting scroll has a high pressure from the outer peripheral side toward the center, and generates high-temperature compression heat on the center side. And since the turning bearing is accommodated in the boss | hub part in this turning scroll center part, the compression heat which cannot be cooled with cooling air will be transmitted to the turning bearing side.

  For this reason, high-temperature compression heat is transmitted to the orbiting bearing disposed on the center side of the orbiting scroll, and the lubricant such as grease enclosed in the boss portion is deteriorated by heat. Further, the internal pressure in the slewing bearing increases due to the temperature rise, and the grease in the slewing bearing may leak to the outside. As a result, the slewing bearing cannot be sufficiently lubricated, and there is a problem that the slewing bearing is damaged.

  On the other hand, since the slewing bearing that supports the crankshaft is separated from the main bearing that supports the drive shaft in the axial direction, the main bearing sufficiently receives the radial and circumferential loads that occur on the crankshaft side. Can not do it. For this reason, since a big moment acts on a drive shaft or a main bearing, a bearing etc. will be worn out early, and there exists a problem that reliability and lifetime fall.

  The present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to prevent the compression heat generated on the scroll side from being transmitted to the slewing bearing and to improve the life of the slewing bearing. It is to provide a fluid machine.

  Another object of the present invention is to provide a scroll type fluid machine capable of preventing the main bearing from being worn by preventing a moment caused by a turning motion from acting on the main bearing.

  A scroll type fluid machine according to the present invention comprises a fixed side member comprising a casing, a fixed scroll provided on the casing and having a spiral wrap portion standing on the surface of the end plate, and can be turned to face the fixed scroll. An orbiting scroll provided with a spiral wrap portion standing on the surface of the end plate so as to overlap with the wrap portion of the fixed scroll and defining a plurality of compression chambers, and rotatably driven by a drive source provided on the casing Thus, a drive shaft for orbiting the orbiting scroll is provided.

In order to solve the above-described problem, the feature of the configuration adopted by the invention of claim 1 is that a crank boss portion having a bearing receiving hole is provided at a position eccentric from the rotation axis on the tip side of the drive shaft, The orbiting scroll is provided with an eccentric shaft extending in the axial direction from the rear surface side toward the bearing housing hole of the crank boss portion, and is coaxial with the rotation axis of the drive shaft between the outer periphery of the crank boss portion and the casing. A main bearing for rotatably supporting the crank boss portion is provided, a plurality of heat dissipating fins are provided on the back side of the end plate of the orbiting scroll, and the bearing between the bearing hole and the eccentric shaft of the crank boss portion a plane that intersects the axis of rotation passing through the main bearing, said pivot bearing to a position spaced from said end plate is provided from the tip of the radiating fins, the bearing receiving hole of the crank boss has, on its opening side position It is configured such that from the front end of the heat radiation fin seal member which confines lubricant to the bearing housing hole provided at a position spaced from said end plate, passing the cooling air between the end plate and the orbiting bearing of said orbiting scroll Te It is in.

  According to the invention of claim 2, the cooling fan that generates cooling air is provided on the drive shaft side, and the fan casing that guides the cooling air generated by the cooling fan to the back surface of the fixed scroll and the back surface of the orbiting scroll is provided. It is in that.

  According to the third aspect of the present invention, the eccentric shaft is provided with a hollow hole extending in the axial direction, and the hollow hole prevents the heat generated by the compression action from being transmitted to the swivel bearing side through the eccentric shaft.

According to the invention of claim 4, the shaft drive is to have a configuration in which a space portion for expanding the volume of the bearing accommodating hole communicates with the bearing receiving hole.
According to a fifth aspect of the present invention, the orbiting bearing is provided on the tip end side of the eccentric shaft extending in the axial direction from the back surface side of the orbiting scroll toward the bearing receiving hole of the crank boss portion.

According to the first aspect of the present invention, when the drive shaft is rotationally driven by the drive source, the crank boss portion is supported by the main bearing and rotates. At this time, the bearing receiving hole formed at a position eccentric from the rotation axis rotates. Exercise. The eccentric shaft that is rotatably supported by the bearing receiving hole via the orbiting bearing at a position farther from the end plate of the orbiting scroll than the end of the radiation fin causes the orbiting scroll to orbit with respect to the fixed scroll. Thus, the orbiting scroll cooperates with the fixed scroll and can discharge the fluid sucked into the compression chamber on the outer peripheral side from the central portion while compressing the fluid.

  Here, when the fluid is compressed, compression heat is generated, and this compression heat becomes high on the central portion side where the pressure becomes high. When the compression heat is transmitted to the slewing bearing, the lubricant that lubricates the slewing bearing deteriorates.

However, the eccentric shaft on the orbiting scroll is formed so as to extend in the axial direction from the back surface side of the orbiting scroll toward the bearing housing hole of the crank boss portion, and the orbiting bearing is separated from the end plate of the orbiting scroll rather than the tip of the radiating fin. And located sufficiently away from the end plate. Thereby, it is possible to prevent the compression heat generated on the scroll side from being transmitted to the slewing bearing, thereby improving the life of the slewing bearing. In addition, since the bearing housing hole of the crank boss portion is provided with a seal member that is located on the opening side of the crank boss portion and confines the lubricant in the bearing housing hole at a position farther from the end plate than the tip of the radiating fin. The swivel bearing can be lubricated by the lubricant confined in the bearing housing hole of the crank boss portion using the seal member.

  Further, since the main bearing and the orbiting bearing are arranged on substantially the same plane orthogonal to the rotation axis, when the orbiting scroll is orbited, the moment between the crank boss portion and the eccentric shaft is almost eliminated. be able to. As a result, it is possible to prevent a useless load from acting on the main bearing and the like, so it is possible to prevent wear and damage of the main bearing and the like, and to improve reliability and life.

  According to the invention of claim 2, the cooling fan is driven together with the drive shaft, and the cooling air generated by the cooling fan is supplied to the back surface of the fixed scroll and the back surface of the orbiting scroll through the fan casing. Since it can, each scroll can be cooled.

  According to the invention of claim 3, the compression heat generated on the scroll side tends to be transmitted to the orbiting bearing or the like through the eccentric shaft. However, since the eccentric shaft is provided with a hollow hole extending in the axial direction, the surface area of the eccentric shaft can be increased to improve heat dissipation, and the sectional area of the eccentric shaft can be reduced to make it difficult to transfer heat. Can do. Thereby, the temperature rise of the slewing bearing or the like due to the compression heat can be suppressed, and the life of the slewing bearing or the like can be improved.

When billing Ru good to the invention in claim 4, the bearing housing hole, which is more closed in the sheet seal member is pressure rises due to heat during operation, the internal pressure of the bearing housing holes increases, breaking the seal lubricant May leak. However, the space portion communicates with the bearing receiving hole provided on the drive shaft, because the enlarged volume product of the bearing accommodating hole by the space portion, it is possible to suppress the increase in the internal pressure of the bearing accommodating hole, the sealing member Damage and lubricant leakage can be prevented.

  Hereinafter, a scroll type air compressor will be described as an example of a scroll type fluid machine according to an embodiment of the present invention, and will be described in detail with reference to FIGS.

  In FIG. 1, reference numeral 1 denotes a scroll casing that forms the outer shape of the compressor, and the scroll casing 1 constitutes a fixed side member together with a fixed scroll 2 described later. Further, as shown in FIG. 2, the scroll casing 1 has a substantially bottomed structure in which one side in the axial direction is closed and the other side is opened by a large-diameter cylindrical portion 1A and a bottom portion 1B that closes one side of the cylindrical portion 1A. It is formed in a cylindrical shape. Further, in the center of the bottom portion 1B, a small-diameter bearing mounting cylinder 1C that is located on one side and to which an auxiliary bearing 8 that will be described later is attached, and a large-diameter bearing that is located on the other side and to which a later-described main bearing 11 is attached. A cylinder 1D is provided.

  Further, the cylindrical portion 1A is provided with an inflow port 1E that opens to the duct 19 side and an outflow port 1F that is located on the opposite side in the radial direction of the inflow port 1E and opens to the outside. The inlet 1E and the outlet 1F guide cooling air supplied from a fan casing 17 described later to the back side of the orbiting scroll 3.

  Reference numeral 2 denotes a fixed scroll which forms a fixed side member together with the scroll casing 1, and the fixed scroll 2 is fixed to the other side (opening side) of the cylindrical portion 1A so as to close the cylindrical portion 1A of the casing 1. ing. The fixed scroll 2 has a substantially disc-shaped end plate 2A disposed so that the center thereof coincides with a rotation axis O1-O1 (described later) of the casing 1, and a spiral shape standing on the surface of the end plate 2A. The lap portion 2B is roughly configured. A plurality of heat radiation fins 2C are provided upright on the back side of the end plate 2A.

  Reference numeral 3 denotes a turning scroll accommodated in the scroll casing 1 in a state of facing the fixed scroll 2, and the turning scroll 3 includes an end plate 3A formed in a substantially disc shape and a fixed scroll 2 side on the surface of the end plate 3A. It is comprised from the spiral-shaped lap | wrap part 3B erected toward. Further, as shown in FIG. 5, the orbiting scroll 3 is formed with a plurality of radiating fins 3 </ b> C located on the back side of the end plate 3 </ b> A. Further, the orbiting scroll 3 is integrally provided with a later-described eccentric shaft 10 located at the center of the rear surface side of the end plate 3A.

  Reference numeral 4 denotes, for example, three auxiliary crank mechanisms (only one is shown) provided on the outer peripheral side of the orbiting scroll 3 and provided between the end plate 3A and the bottom 1B of the casing 1. The auxiliary crank mechanism 4 suppresses the orbiting scroll 3 from rotating in the casing 1 and compensates for orbiting movement with an eccentricity δ described later.

  Reference numeral 5 denotes a plurality of compression chambers formed between the fixed scroll 2 and the orbiting scroll 3. Each compression chamber 5 shifts the wrap portion 2B of the fixed scroll 2 and the wrap portion 3B of the orbiting scroll 3 by a predetermined angle. Are formed so as to overlap each other. Each compression chamber 5 is continuously compressed between the wrap portions 2B and 3B when the orbiting scroll 3 performs an orbiting motion, and compressed air while sucking outside air from a suction port (not shown) on the outer peripheral side. Is discharged to the outside from the discharge port 6 at the center.

  A drive shaft 7 is rotatably provided on the scroll casing 1. The drive shaft 7 is rotated by an electric motor 21 which will be described later, thereby turning through a crank boss portion 9 and an eccentric shaft 10 which will be described later. The scroll 3 is turned. The drive shaft 7 is rotatably supported by a bearing mounting cylinder 1C of the scroll casing 1 with a rotation axis O1-O1 via an auxiliary bearing 8 described later. Further, the base end side of the drive shaft 7 protrudes outside the scroll casing 1, and a crank boss portion 9 is provided on the front end side in the casing 1.

  8 is an auxiliary bearing provided on the outer peripheral side of the drive shaft 7, and rotatably supports the drive shaft 7 on the bearing mounting cylinder 1C of the scroll casing 1. The auxiliary bearing 8 is provided coaxially with the rotation axis O1-O1. ing. The auxiliary bearing 8 is formed, for example, as a grease-filled deep groove ball bearing, and supports the drive shaft 7 to assist a main bearing 11 described later.

  Reference numeral 9 denotes a crank boss portion which is located in the scroll casing 1 and is integrally provided on the front end side of the drive shaft 7. The crank boss portion 9 is formed as a large-diameter and thick disc body centered on the rotation axis O1-O1, and is rotatably supported on the inner peripheral side of the bearing mounting cylinder 1D via a main bearing 11 described later. Has been. Further, the crank boss portion 9 is disposed on one side of the radiating fin 3C of the orbiting scroll 3, and is thereby sufficiently separated from the end plate 3A, and is a passage for cooling air between the end plate 3A.

  On the other hand, the crank boss portion 9 is provided with a bearing housing hole 9A that opens to the other side. The bearing receiving hole 9A is formed as a shallow bottomed circular hole as shown in FIGS. 3 and 4, and its axis O2-O2 is eccentric from the rotation axis O1-O1 by an eccentric amount δ. As a result, when the drive shaft 7 is driven to rotate, the bearing housing hole 9A of the crank boss portion 9 turns with an eccentric amount δ, and the orbiting scroll 3 turns with respect to the fixed scroll 2 via the eccentric shaft 10 and the like which will be described later. Can be made.

  The crank boss portion 9 has been described as being integrally provided on the distal end side of the drive shaft 7. However, the drive shaft 7 and the crank boss portion 9 are provided separately, and fixing means such as screwing, press-fitting, and welding are provided. It is good also as a structure attached using.

  Reference numeral 10 denotes an eccentric shaft integrally provided on the back side of the end plate 3A forming the orbiting scroll 3. As shown in FIGS. 3 and 5, the eccentric shaft 10 is formed as a stepped columnar body provided extending from the center of the rear surface side of the end plate 3A toward the bearing housing hole 9A of the crank boss portion 9. Has been. Further, the eccentric shaft 10 has a small diameter portion 10A on the tip side beyond the heat dissipating fin 3C, and the small diameter portion 10A enters the bearing housing hole 9A and is connected to the crank boss portion 9 via a swing bearing 12 described later. Yes.

  Although the eccentric shaft 10 has been described as being integrally provided on the back side of the end plate 3A of the orbiting scroll 3, the orbiting scroll 3 and the eccentric shaft 10 are separately provided in the same manner as the drive shaft 7 and the crank boss 9. Further, it may be configured to be integrally attached using fixing means such as screwing, press-fitting, and welding.

  11 is a main bearing provided between the outer periphery of the crank boss portion 9 and the bearing mounting cylinder 1D of the scroll casing 1, and the main bearing 11 is connected to the rotation axis O1-O1 of the drive shaft 7 as shown in FIG. It is arranged coaxially. The main bearing 11 is formed, for example, as a grease-filled deep groove ball bearing, and supports the crank boss portion 9 (drive shaft 7) so as to be rotatable on the rotation axis O1-O1.

A slewing bearing 12 is provided between the bearing housing hole 9A of the crank boss portion 9 and the small-diameter portion 10A of the eccentric shaft 10, and the slewing bearing 12 is formed as a cylindrical roller bearing, for example. As shown in FIGS. 2 and 3 , the slewing bearing 12 is disposed at a position farther away from the end of the radiating fin 3C in the axial direction of the eccentric shaft 10 than the end plate 3A, and the eccentric shaft is inserted into the bearing housing hole 9A. 10 is rotatably supported.

  Here, as shown in FIG. 3, the slewing bearing 12 is disposed on the inner peripheral side of the main bearing 11, specifically on a plane FF passing through the main bearing 11 with the rotation axis O 1 -O 1 of the drive shaft 7 orthogonal thereto. ing. Thereby, when the orbiting scroll 3 is orbited, the load acting on the main bearing 11 from the orbiting bearing 12 can be all received by the main bearing 11. Thereby, the moment which acts on the crank boss part 9, the main bearing 11, etc. can be almost eliminated.

  Reference numeral 13 denotes a hollow hole provided in the eccentric shaft 10 so as to extend in the axial direction. The hollow hole 13 has a function of increasing the surface area of the eccentric shaft 10 to increase heat dissipation and reducing the cross-sectional area of the eccentric shaft 10. It has a function to make it difficult to transmit heat. Thereby, the hollow hole 13 can prevent the compression heat generated in the compression chamber 5 from being transmitted to the swing bearing 12 side through the eccentric shaft 10, and can prevent the temperature of the swing bearing 12 and the like from rising.

Reference numeral 14 denotes a seal member provided between the opening portion of the bearing housing hole 9 </ b> A forming the crank boss portion 9 and the small diameter portion 10 </ b> A of the eccentric shaft 10. The sealing member 14 is to confine the lubricant such as grease to lubricate the orbiting bearing 12 (not shown) in the bearing housing hole 9A.

  Reference numeral 15 denotes a space formed in the drive shaft 7 in communication with the bottom of the bearing housing hole 9A sealed by the seal member 14. The space 15 extends in the axial direction at the center of the drive shaft 7, and expands the volume of the bearing housing hole 9A by communicating with the bottom of the bearing housing hole 9A. Here, the pressure in the bearing housing hole 9A sealed by the seal member 14 may increase due to heat during operation. At this time, the space 15 expands the volume of the bearing housing hole 9A, thereby increasing the bearing capacity. An increase in the internal pressure of the accommodation hole 9A can be suppressed low.

  Reference numeral 16 denotes a cooling fan such as a centrifugal fan that is located on one side of the scroll casing 1 and is attached to the base end side of the drive shaft 7. The cooling fan 16 is rotationally driven by an electric motor 21 described later. Thus, cooling air is generated.

  Reference numeral 17 denotes a fan casing provided so as to cover the back side of the fixed scroll 2 from the periphery of the cooling fan 16. The fan casing 17 is attached to one side of the scroll casing 1 so as to cover the cooling fan 16, and has a bottomed cylindrical casing body 18 in which a plurality of suction ports 18 A are formed at the bottom, and scrolls from the casing body 18. The casing 1 is roughly constituted by a duct 19 that extends toward the scrolls 2 and 3 and a scroll cover 20 that is continuous with the duct 19 and covers the back side of the fixed scroll 2.

  The fan casing 17 can guide the cooling air to the back side of the fixed scroll 2 by circulating the cooling air generated by the cooling fan 16 through the casing body 18, the duct 19, and the scroll cover 20. Further, the cooling air can be circulated through the casing body 18 and the duct 19 and guided from the inlet 1 </ b> E of the scroll casing 1 to the back surface side of the orbiting scroll 3.

  An electric motor 21 is a drive source attached to the bottom of the casing body 18 forming the fan casing 17. The electric motor 21 has an output shaft 21 A connected to the drive shaft 7 via the shaft coupling 22 and the cooling fan 16. It is connected.

  In addition, 23 and 24 are balance weights attached to the crank boss portion 9, and each of the balance weights 23 and 24 takes a static weight balance. Reference numeral 25 denotes a counterweight provided in the cooling fan 16, which counteracts the moment generated when the drive shaft 7 is rotationally driven to make the rotation smooth.

  The scroll type air compressor according to the present embodiment has the above-described configuration, and the operation thereof will be described next.

  First, when the drive shaft 7 is rotationally driven by the electric motor 21, the crank boss portion 9 is supported by the main bearing 11 and rotated together with the drive shaft 7. As a result, the eccentric shaft 10 attached to the bearing housing hole 9A of the crank boss portion 9 via the orbiting bearing 12 orbits with an eccentric amount δ from the rotation axis O1-O1, and the orbiting scroll 3 is moved with respect to the fixed scroll 2. And swivel.

  At this time, since the main bearing 11 and the orbiting bearing 12 are arranged on substantially the same plane FF, the main bearing 11 reliably receives the load generated when the orbiting scroll 3 is orbited. Can do. As a result, the moment generated when the orbiting scroll 3 is orbited can be substantially eliminated, so that the drive shaft 7, the crank boss portion 9, the eccentric shaft 10 and the like can be operated smoothly.

  When the orbiting scroll 3 is orbited, the compression chamber 5 defined between the wrap portion 2B of the fixed scroll 2 and the wrap portion 3B of the orbiting scroll 3 is continuously reduced. Accordingly, each compression chamber 5 can discharge the compressed air from the discharge port 6 toward an external air tank (not shown) or the like while sequentially compressing the air sucked from the suction port.

  Further, during the compression operation, the cooling fan 16 is rotated together with the drive shaft 7 to generate cooling air. The cooling air from the cooling fan 16 circulates in the casing body 18, the duct 19, and the scroll cover 20 constituting the fan casing 17 as indicated by arrows in FIGS. 1 and 2, and a part thereof is a fixed scroll. 2, the fixed scroll 2 is cooled from the back side. The remaining cooling air is guided from the duct 19 to the back side of the orbiting scroll 3 via the inlet 1E of the scroll casing 1, and cools the orbiting scroll 3 from the back side.

  As described above, even when the scrolls 2 and 3 are cooled by the cooling air, the compression heat generated in the compression chamber 5, particularly, the high-temperature compression heat is generated in the compression chamber 5 on the center side. However, since the orbiting bearing 12 is provided on the tip end side of the eccentric shaft 10 that extends in the axial direction from the back surface side of the orbiting scroll 3 toward the crank boss portion 9, the orbiting bearing 12 and the end plate of the orbiting scroll 3 are used together with the main bearing 11. It can be separated sufficiently from 3A. In addition, cooling air can be passed between the end plate 3A and the bearings 11 and 12. Thereby, it is possible to prevent the compression heat from being transmitted to the bearings 11 and 12.

  In addition, the compression heat tends to be transmitted to the slewing bearing 12 or the like through the eccentric shaft 10, but the hollow hole 13 provided in the eccentric shaft 10 increases the surface area of the eccentric shaft 10 to release heat, and the eccentric shaft 10 is disconnected. The area is reduced to make it difficult to transfer heat. Thereby, it can prevent that the turning bearing 12 grade | etc., Becomes high temperature by the heat | fever which transmits the eccentric shaft 10. FIG.

  On the other hand, during the operation of the air compressor, the temperature of the bearing housing hole 9A of the crank boss portion 9 sealed by the seal member 14 increases, and the internal pressure of the bearing housing hole 9A increases. However, since the bearing housing hole 9A has an enlarged volume due to the space portion 15, the pressure rise in the bearing housing hole 9A is kept low.

  Thus, according to the present embodiment, the main bearing 11 and the orbiting bearing 12 are arranged at positions sufficiently separated from the end plate 3A of the orbiting scroll 3, so that the compression generated on the respective scrolls 2 and 3 side. Heat can be prevented from being transmitted to the bearings 11 and 12 side.

  As a result, the life of the lubricant that lubricates the bearings 11 and 12 can be extended. Accordingly, the life of the bearings 11 and 12 can also be extended and the reliability, durability, and the like are improved. be able to.

  In addition, since the main bearing 11 that supports the crank boss portion 9 and the orbiting bearing 12 that supports the eccentric shaft 10 are both disposed on the plane FF orthogonal to the rotation axis O1-O1, the orbiting scroll 3 All the loads generated when rotating the can are received by the main bearing 11.

  As a result, since the moment acting on the drive shaft 7, the crank boss portion 9, the eccentric shaft 10 and the like can be almost eliminated, these operations can be performed smoothly, and wear and damage of the main bearing 11 and the like can be prevented. Reliability and life can be improved.

  Also, by providing the hollow hole 13 in the eccentric shaft 10, the surface area of the eccentric shaft 10 can be increased to improve heat dissipation, and the cross-sectional area of the eccentric shaft 10 can be reduced, so that the compression heat passes through the eccentric shaft 10. Therefore, the life of the slewing bearing 12 and the like can be improved.

  Furthermore, since the volume of the bearing receiving hole 9A is enlarged by the space portion 15, an increase in pressure in the bearing receiving hole 9A can be suppressed low, and damage to the seal member 14 and leakage of the lubricant can be prevented. it can.

  In the embodiment, a case where a deep groove ball bearing is used for the auxiliary bearing 8 and the main bearing 11 and a cylindrical roller bearing is used for the slewing bearing 12 is illustrated. However, the present invention is not limited to this, and the bearings 8, 11, 12 and the like are ball bearings, cylindrical roller bearings, needle rollers according to the specifications of the size of the air compressor, oil supply type, non-supply type, and the like. What is necessary is just to set it as the structure which selects a suitable thing from a bearing, a slide bearing, etc.

  In the embodiment, the cooling fan 16 is provided between the scroll casing 1 (drive shaft 7) and the electric motor 21. However, the present invention is not limited to this. For example, the cooling fan 16 is cooled on the opposite side of the electric motor 21. The fan 16 may be provided and the output shaft 21 </ b> A of the electric motor 21 may be directly connected to the drive shaft 7.

  Alternatively, a pulley may be attached to the drive shaft, and the drive shaft may be rotationally driven by an electric motor via a belt. In this case, the pulley may have a function as a cooling fan, or an electric fan may be provided separately.

  Furthermore, in the embodiment, the scroll type air compressor has been described as an example of the scroll type fluid machine. However, the present invention is not limited to this, and can be widely applied to, for example, a refrigerant compressor and a vacuum pump.

It is a longitudinal section showing a scroll type air compressor concerning an embodiment of the invention. FIG. 2 is an enlarged vertical sectional view showing a main part of each scroll side in FIG. 1. It is a principal part expansion longitudinal cross-sectional view which expands and shows a drive shaft, a crank boss | hub part, an eccentric shaft, a main bearing, a turning bearing, etc. It is an external appearance perspective view which expands and shows a drive shaft and a crank boss | hub part. It is an external appearance perspective view which expands and shows a turning scroll from the back side.

Explanation of symbols

1 Scroll casing (fixed side member)
2 Fixed scroll (fixed side member)
2A, 3A End plate 2B, 3B Lapping part 3 Orbiting scroll 5 Compression chamber 7 Drive shaft 9 Crank boss part 9A Bearing receiving hole 10 Eccentric shaft 11 Main bearing 12 Orbiting bearing 13 Hollow hole 14 Seal member 15 Space part 16 Cooling fan 17 Fan casing 21 Electric motor (drive source)
O1-O1 rotation axis FF Plane perpendicular to rotation axis

Claims (5)

A fixed side member comprising a casing and a fixed scroll provided on the surface of the end plate with a spiral lap portion, and a fixed scroll on the end plate surface provided so as to be able to swivel against the fixed scroll The orbiting scroll is provided with a spiral wrap portion that overlaps with the wrap portion and defines a plurality of compression chambers, and the orbiting scroll is revolved by being rotatably provided on the casing and driven by a drive source. In a scroll type fluid machine comprising a drive shaft to be moved,
Provided on the tip side of the drive shaft is a crank boss portion having a bearing receiving hole at a position eccentric from the rotation axis,
The orbiting scroll is provided with an eccentric shaft extending in the axial direction from the back surface side toward the bearing housing hole of the crank boss portion,
Provided between the outer periphery of the crank boss part and the casing is a main bearing that rotatably supports the crank boss part coaxially with the rotation axis of the drive shaft,
The end plate of the orbiting scroll is provided with a plurality of radiating fins on the back side,
Between the bearing housing hole of the crank boss part and the eccentric shaft, a slewing bearing is on a plane that intersects with the rotation axis and passes through the main bearing, and is located farther from the end plate than the tip of the radiating fin. Provided,
In the bearing housing hole of the crank boss portion, a seal member that is located on the opening side of the crank boss portion and traps the lubricant in the bearing housing hole is provided at a position farther from the end plate than the tip of the radiation fin,
A scroll type fluid machine characterized in that cooling air is passed between the end plate of the orbiting scroll and the orbiting bearing.   2. The structure according to claim 1, wherein a cooling fan that generates cooling air is provided on the drive shaft side, and a fan casing that guides the cooling air generated by the cooling fan to the back surface of the fixed scroll and the back surface of the orbiting scroll is provided. The scroll type fluid machine as described.   The scroll fluid machine according to claim 1 or 2, wherein a hollow hole extending in the axial direction is provided in the eccentric shaft, and heat due to a compression action is prevented from being transmitted to the swivel bearing side through the eccentric shaft. . Scroll fluid machine of prior SL drive shaft according to claim 1, 2 or 3 comprising a structure to provide a space portion for expanding the volume of the bearing accommodating hole communicates with the bearing receiving hole.   5. The scroll type according to claim 1, 2, 3, or 4, wherein the orbiting bearing is provided on a distal end side of the eccentric shaft extending in an axial direction from a rear surface side of the orbiting scroll toward a bearing receiving hole of the crank boss portion. Fluid machinery.

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