JP2005140066A - Fluid compressor - Google Patents

Abstract

【Task】
For fluid compressors, ensure an adequate amount of oil supply with an inexpensive structure and excellent reliability.
[Solution]
The fluid compressor 1 includes a rotary shaft 300 having a compression mechanism unit 2, an oil passage 311, an electric motor 600, bearings 401 and 803, and a centrifugal pump unit 900 that supplies oil through the oil passage 311. The rotary shaft 300 integrally includes a main shaft portion 302, a crank pin 301 provided eccentric to the main shaft portion 302, and a sub-bearing support portion 303 having a small diameter on the main shaft portion 302. The oil passage 311 is connected to the first oil passage 311a extending from the lower end of the auxiliary bearing support portion 303 to the lower portion of the main shaft portion 302, and the second oil passage 311a extends to the upper end of the crank pin 301. And an oil passage 311b. The second oil passage 311b has a passage portion that is smaller in diameter and positioned outward than the first oil passage 311a, and a plurality of second oil passages 311b are formed within the plane range of the crank pin 311.
[Selection] Figure 1

Description

  The present invention relates to a fluid compressor having a rotating shaft having an oil passage, and is particularly suitable for a refrigerant compressor for refrigeration and air conditioning, air, and other fluid compressors.

  An example of a conventional fluid compressor is disclosed in Japanese Patent Application Laid-Open No. 2001-349291 (Patent Document 1). A scroll compressor according to FIG. 1 of Patent Document 1 includes a compression mechanism section that compresses fluid in a sealed container, a rotary shaft that is connected to the compression mechanism section and has an oil passage, and drives the rotary shaft. Motor, a main bearing that supports the rotating shaft above the motor, a sub-bearing that supports the rotating shaft below the motor, and supplies oil stored in the bottom of the sealed container to the compression mechanism and the bearing through the oil passage. And a positive displacement pump unit.

  The rotating shaft includes a main shaft portion fixed to the rotor of the electric motor, a crank portion eccentrically provided at the upper end portion of the main shaft portion and coupled to the compression mechanism portion, and a sub-bearing provided at the lower end portion of the main shaft portion. A small-diameter sub-bearing support portion supported is integrally provided. The reason why the diameter of the auxiliary bearing support portion of the rotating shaft is reduced is that the auxiliary bearing support portion can be supported with high precision by the auxiliary bearing. Furthermore, the oil passage of the rotating shaft is formed concentrically with the rotating shaft by a small-diameter hole extending from the lower end of the auxiliary bearing support portion to the upper end of the crank portion.

  As a conventional fluid compressor, for example, there is a scroll compressor disclosed in JP-A-2-245492 (Patent Document 2). A scroll compressor according to FIGS. 1 to 3 of Patent Document 2 includes a compression mechanism unit that compresses fluid in a sealed container, a rotary shaft that is connected to the compression mechanism unit and has an oil passage, An electric motor that drives the rotating shaft, an upper main bearing portion that supports the rotating shaft, and a centrifugal pump portion (cap) that supplies oil stored in the bottom of the sealed container to the compression mechanism portion and the bearing through the oil passage. Yes.

  The rotating shaft is provided with the same diameter at the main shaft portion fixed to the rotor of the electric motor, the crank pin eccentrically provided at the upper end portion of the main shaft portion and connected to the compression mechanism portion, and the lower end portion of the main shaft portion. A portion protruding downward from the electric motor is integrally provided. The oil passage of the rotating shaft includes a first oil passage extending from the lower end to the upper portion, a second oil passage having a small diameter that communicates within the plane of the first oil passage and extends to the upper end of the crank pin. Configured.

JP 2001-349291 A (FIG. 1)

JP-A-2-245492 (FIGS. 1 to 3)

  Generally, in a fluid compressor, in order to ensure the strength of the main shaft portion of the rotating shaft, it is desirable that the oil passage that passes through the main shaft portion has a small diameter.

  When the oil passage of the rotating shaft is formed concentrically with the rotating shaft by a small-diameter hole extending from the lower end of the auxiliary bearing support portion to the upper end of the crank portion as in the scroll compressor of Patent Document 1, this oil passage We cannot expect much centrifugal force to oil by. For this reason, in patent document 1, it is trying to ensure the amount of oil supply using a positive displacement pump part. However, there is a problem that the positive displacement pump portion is generally more expensive than the centrifugal pump portion.

  Since the scroll compressor of Patent Document 2 uses a centrifugal pump unit, it has an inexpensive structure, but the second oil passage is communicated within the plane of the first oil passage, Since there is only one oil passage of 2, there was a problem in securing a sufficient amount of oil supply. Further, when the oil temperature rises, the viscosity of the oil decreases, so that the centrifugal effect acting on the inner wall is reduced in the centrifugal pump part, and a necessary oil supply amount cannot be secured.

  An object of the present invention is to obtain a highly reliable fluid compressor that can sufficiently secure an oil supply amount with an inexpensive structure.

In order to achieve the above object, the present invention provides a compression mechanism part for compressing fluid in a sealed container, a rotating shaft connected to the compression mechanism part and having an oil passage, and an electric motor for driving the rotating shaft. A main bearing that supports the rotating shaft above the electric motor, a sub-bearing that supports the rotating shaft below the electric motor, and oil stored in the bottom of the hermetic container to the compression mechanism and the bearing. In a fluid compressor including a centrifugal pump unit that supplies through the oil passage,
The rotating shaft includes a main shaft portion fixed to a rotor of the electric motor, a crank pin eccentrically provided at an upper end portion of the main shaft portion and connected to the compression mechanism portion, and a sub shaft provided at a lower end portion of the main shaft portion. A small-diameter sub-bearing support portion supported by a bearing, and an oil passage of the rotating shaft includes a first oil passage extending from a lower end of the sub-bearing support portion to a lower portion of the main shaft portion; And a second oil passage that communicates with the first oil passage and extends to the upper end of the crank pin, and the second oil passage is smaller in diameter than the first oil passage and located outward. And a plurality of passage portions are formed within the plane range of the crank pin.

  According to the fluid compressor of the present invention, it is possible to secure a sufficient amount of oil supply with an inexpensive structure and to have excellent reliability.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.

  A scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 and 2. FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, and FIG. 2 is a sectional view of a rotary shaft lower portion and a pump portion of the scroll compressor of FIG.

  The scroll compressor 1 is configured by storing a compression mechanism unit 2 and a drive unit 3 in a sealed container 700. In this embodiment, the compression mechanism unit 2, the drive unit 3, and the oil reservoir 730 are arranged in this order from the top, and the vertical scroll compression in which the compression mechanism unit 2 and the drive unit 3 are connected via the rotating shaft 300. Machine.

  The compression mechanism unit 2 includes a fixed scroll 100, a turning scroll 200, and a frame 400 as basic elements. The frame 400 is fixed to the hermetic container 700 and constitutes a member for disposing the rolling bearing 401. The fixed scroll 100 includes a base plate 101, a spiral wrap 102, a suction port 103, and a discharge port 104 as basic components, and is fixed to the frame 400 with bolts 405. The wrap 102 is erected vertically on one side of the base plate 101. The orbiting scroll 200 includes a base plate 201, a spiral wrap 202, a boss 203, and a back pressure hole as basic components. The wrap 202 is erected vertically on one side of the base plate 201. The boss 203 is formed so as to protrude perpendicularly to the other side (the opposite lap side) of the base plate 201. The orbiting scroll 200 is formed by processing each component from a casting made of cast iron, aluminum, or the like.

  The compression chamber 130 configured by meshing the fixed scroll 100 and the orbiting scroll 200 is subjected to a compression operation in which the volume thereof decreases as the orbiting scroll 200 orbits. In this compression operation, the working fluid is sucked into the compression chamber 130 through the suction pipe 711 and the suction port 103 in accordance with the turning motion of the turning scroll 200, and the sucked working fluid passes through the compression stroke and is fixed to the fixed scroll 100. The gas is discharged from the discharge port 104 into the sealed container 700 and further discharged from the sealed container 700 via the discharge pipe 701. Thereby, the space in the sealed container 700 is kept at the discharge pressure.

  The sealed container 700 has an upper cap 710 and a lower cap 720. The upper cap 710 and the lower cap 720 are fitted so as to cover the center tube portion of the sealed container, and the fitting end portions are heated and welded obliquely from below and obliquely upward by a welding torch. Legs 721 are attached to the bottom surface of the sealed container 700.

  A hermetic terminal 702 and a terminal cover 703 are provided on the side surface of the hermetic container 700 so that electric power can be supplied to the electric motor 600. The hermetic terminal 702 is provided through the hermetic container 700, and is positioned between the end coil of the stator 601 and the frame 400, and faces the maximum outer diameter portion 407 a of the balance weight 407.

  Further, a discharge pipe 701 is provided on the side surface of the sealed container 700 opposite to the hermetic terminal 702 so as to penetrate the sealed container 700, and is positioned between the end coil of the stator 601 and the frame 400. It faces the maximum outer diameter portion 407a.

  The drive unit 3 that rotationally drives the orbiting scroll 200 includes an electric motor 600 including a stator 601 and a rotor 602, a rotating shaft 300, an Oldham coupling 500 that is a main part of the rotation prevention mechanism of the orbiting scroll 200, a frame 400, and a rolling. The bearings 401 and 803 and the boss 203 are configured as basic elements.

  The rotary shaft 300 includes a main shaft portion 302, a crankpin 301, and a sub bearing support portion 303 that are integrally provided. The rolling bearings 401 and 803 constitute a rotating shaft support portion that rotatably engages the main shaft portion 302 and the auxiliary bearing support portion 303 of the rotating shaft 300. The boss 203 is provided in the orbiting scroll 200 so that the crank pin 301 of the rotating shaft 300 can be moved in the thrust direction that is the rotating shaft direction and can rotate freely.

  The rolling bearing 401 is arranged on the upper side of the electric motor 600, and the rolling bearing (sub bearing) 803 constituting the main part of the auxiliary bearing portion 800 is arranged on the lower side of the electric motor 600. A housing 802 is fixed to the lower frame 801 fixed to the hermetic container 700 via bolts 805. A rolling bearing 803 is inserted into the housing 802 from above, and a housing cover 804 is further attached from above.

  The pump unit 900 is provided at the lower end of the rotating shaft 300. The pump unit 900 includes a pump member 901 and pump blades 902. The pump member 901 is composed of a portion attached to the lower end portion of the rotating shaft 300 and a portion extending downward therefrom to reduce the flow path cross section. In other words, the pump member 901 includes an upper cylindrical portion 901a and a lower conical portion 901b. The upper end portion of the upper cylindrical portion 901a is fitted and fixed to the lower end portion of the rotating shaft 300. An opening is provided in the lower end portion of the lower conical portion 901b of the pump member 901. The pump blade 902 has the same outer shape as the inner surface of the pump member 901, and is press-fitted into the pump member 901. That is, the pump blade 902 is disposed so as to extend from the upper part in the pump member 901 to the lower end opening.

  Due to the centrifugal effect in the pump unit 900 rotated together with the rotating shaft 300, the oil stored in the oil sump 730 at the bottom of the sealed container 700 is sucked from the lower end of the pump unit, and the oil is supplied to the oil passage 311 formed in the rotating shaft 300. It has a structure to supply.

  The oil passage 311 of the rotating shaft 300 is communicated with the first oil passage 311a extending from the lower end of the auxiliary bearing support portion 303 to the lower portion of the main shaft portion 302, and to the upper end of the crankpin 301. The second oil passage 311b extends to be configured. The first oil passage 311 a is formed coaxially with the rotary shaft 300. The second oil passage 311b has a passage portion that is smaller in diameter than the first oil passage 311a and is located outward, and a plurality of (two in this embodiment) are formed within the plane range of the crank pin 301. . The second oil passage 311b is formed to intersect with the peripheral portion of the first oil passage 311a so as to be long in the axial direction. The second oil passage 311b is arranged at a position eccentric from the central axis of the rotating shaft 300, and plays the role of a second centrifugal pump by this eccentricity.

  The Oldham joint 500 is disposed on the back surface of the base plate 201 of the orbiting scroll 200. One set of two orthogonal key portions formed on the Oldham joint 500 slides on a key groove which is a receiving portion of the Oldham joint 500 formed on the frame 400, and the other set is configured on the back side of the orbiting scroll wrap 202. Slide the keyway. As a result, the orbiting scroll 200 orbits within the plane perpendicular to the axial direction, which is the direction in which the scroll wrap 202 stands, without rotating with respect to the fixed scroll 100.

  When the crankpin 301 rotates eccentrically due to the rotation of the rotary shaft 300 connected to the electric motor 600, the compression mechanism unit 2 performs a turning motion without rotating with respect to the fixed scroll 100 by the rotation preventing mechanism of the Oldham joint 500. The gas is sucked into the compression chamber 130 formed by the scroll wraps 102 and 202 through the suction pipe 711 and the suction port 103. Due to the orbiting motion of the orbiting scroll 200, the compression chamber 130 decreases in volume while moving to the central portion, compresses gas, and discharges the compressed gas from the discharge port 104 to the discharge chamber. The gas discharged into the discharge chamber circulates around the compression mechanism unit 3 and the electric motor 600 and is then discharged from the discharge pipe 701 to the outside of the compressor.

  The base plate 201 of the orbiting scroll 200 is provided with a back pressure hole for communicating the compression chamber 130 with the back pressure chamber 411 on the orbiting back surface, and the pressure in the back pressure chamber 411 is intermediate between the suction pressure and the discharge pressure. The pressure (intermediate pressure) is maintained. The back pressure chamber 411 configured on the back side of the orbiting scroll 200 is a space formed by being surrounded by the orbiting scroll 200, the frame 400, and the fixed scroll 100. Therefore, the frame 400 also serves as a member that forms the back pressure chamber 411.

  A seal ring 410 provided in the groove 409 of the frame 400 prevents discharge gas from flowing into the back pressure chamber 411. The orbiting scroll 200 is pressed against the fixed scroll 100 by the resultant force of the intermediate pressure in the back pressure chamber 411 and the discharge pressure acting inside the seal ring 410.

  Here, the inner diameter of the seal ring 410 is smaller than the outer diameter of the rolling bearing 401. In order to be able to adopt such a configuration, in this embodiment, the rolling bearing 401 is inserted into the frame 400 from the rotation driving means side of the frame 400, and the inserted rolling bearing 401 is fixed by the frame cover 403. It has become. A thrust bearing 402 is provided on the frame cover 403. The frame cover 403 is formed separately from the frame 400. The frame cover 403 is fixed to the frame 400 with bolts 406. By fixing with bolts in this way, the gap between the frame cover 403 and the frame 400 can be accurately sealed, so that oil leakage from the oil supply path can be suppressed. The frame cover 403 includes a portion that is inserted inside the frame 400 and presses the rolling bearing 401, and a portion that contacts and is fixed to the end surface of the frame 400 on the side of the rotation driving means.

  The balance weight 407 is provided on the rotating shaft 300 on the electric motor side from the rolling bearing 401. In this embodiment, the balance weight 407 is formed separately from the rotary shaft 300 and is press-fitted and fixed to the rotary shaft 300. However, the balance weight 407 may be formed integrally with the rotary shaft 300. Good. The maximum outer diameter portion 407a of the balance weight 407 is provided so as to protrude toward the end face side of the coil end of the stator 601, and has a larger diameter than the inner diameter of the coil end.

  The metal balance weight cover 404 is formed in a cylindrical shape including a bottom wall and a side wall, and is provided so as to cover the outer periphery of the maximum outer diameter portion 407 a of the balance weight 407. The balance weight cover 404 is fixed to the frame 400 with bolts 406 by fastening the frame cover 403 together. The side wall of the balance weight cover 404 is provided between the discharge pipe 701 and the maximum outer diameter portion 407a of the balance weight 407, and is provided between the hermetic terminal 702 and the maximum outer diameter portion 407a of the balance weight 407. Become.

  In this way, the balance weight cover 404 closes the space between the frame 400 and the end face of the end coil of the stator 601. That is, the outer space of the maximum outer diameter portion 407 a of the balance weight 407 is substantially closed by the balance weight cover 404.

  Next, the oil supply path will be described. When the rotating shaft 300 is rotated, the oil in the oil reservoir 730 is sent to the oil passage 311 in the rotating shaft by the pump unit 900. Part of the oil sent to the oil passage 311 flows through the lateral hole 312 to the auxiliary bearing 803 that is a rolling bearing, and then returns to the oil reservoir 730. The oil that has reached the upper portion of the crankpin 301 through the oil passage 311 passes through the slewing bearing 210 and further flows to the rolling bearing 401. Most of the oil that has lubricated the rolling bearing 401 passes through the oil drain pipe 408 and returns to the oil sump 730. Part of the oil that lubricated the rolling bearing 401 reaches the balance weight 407 through the gap between the frame cover 403 and the rotary shaft 300 and is scattered by the balance weight 407, but on the side wall 404 b of the balance weight cover 404. The oil adheres to the inner surface, is collected, and flows down to the electric motor 600 to return to the oil sump 730.

  An oil supply pocket 205 is provided on the end face of the boss 203 of the orbiting scroll 200, and the orbiting scroll 200 reciprocates between the outer side and the inner side of the seal ring 410 as the orbiting scroll 200 reciprocates. A part of the oil between the bearings 401 is conveyed to the back pressure chamber 411. The conveyed oil is supplied to the Oldham coupling 500 and then supplied to the end face 105 of the fixed scroll and the sliding face of the base plate 201 of the orbiting scroll 200.

  The oil conveyed to the back pressure chamber 411 flows into the compression chamber 130 through the back pressure hole or through a minute gap on the sliding surface of the end plate. The oil that has flowed into the compression chamber 130 is discharged from the discharge port 104 together with the compressed refrigerant gas, is separated from the refrigerant gas in the sealed container 700, and returns to the oil reservoir 730.

  According to this embodiment, the rotating shaft 300 includes a main shaft portion 302 fixed to the rotor 602 of the electric motor 600, and a crank pin 301 provided eccentrically at the upper end portion of the main shaft portion 302 and connected to the compression mechanism portion 2. The main shaft 302 has a small-diameter sub-bearing support 303 provided at the lower end of the main shaft 302 and supported by the sub-bearing 803, so that the sub-bearing 803 can secure the necessary strength for the rotary shaft 300. The auxiliary bearing support 303 can be pivotally supported with high accuracy.

  Moreover, according to the present Example, since it is set as the centrifugal pump part, it can be made cheap compared with a positive displacement pump part. Moreover, since the pump blade 902 extends to the lower end portion of the pump member 901, even if the amount of oil in the oil reservoir 730 decreases, the effect of the centrifugal pump blade 902 disposed up to the lower end of the pump member 901 is sufficient. Therefore, a highly reliable pump mechanism can be provided.

  Further, according to the present embodiment, the oil passage 311 of the rotary shaft 300 communicates with the first oil passage 311a extending from the lower end of the auxiliary bearing support portion 303 to the lower portion of the main shaft portion 302, and the first oil passage 311a. And a second oil passage 311b extending to the upper end of the crankpin 301. The second oil passage 311b has a passage portion that is smaller in diameter than the first oil passage 311a and located outward. At the same time, since a plurality of crankpins 301 are formed within the plane range, a large flow passage cross-sectional area is secured together with a large centrifugal force in a limited cross-sectional area of the rotating shaft 300 while satisfying the configuration of the rotating shaft 300. can do. As a result, the second oil passage 311b functions as a second centrifugal pump, a sufficient amount of oil can be secured with an inexpensive structure, and a highly reliable scroll compressor can be obtained.

  Next, second to eighth embodiments of the present invention will be described with reference to FIGS. These second to eighth embodiments are different from the first embodiment as described below, and are basically the same as the first embodiment in other points.

  A second embodiment will be described with reference to FIGS. FIG. 3 is an explanatory view of a pump member used in the scroll compressor according to the second embodiment of the present invention, wherein (a) is a top view, (b) is a front view, and (c) is a side view. FIG. 4 is an oil supply characteristic diagram of the pump member of the second embodiment.

  In this 2nd Example, the member which comprises the pump part 900 is only the pump member 901, The pump blade | wing 902 in 1st Example is not provided. The pump member 901 has a conical shape as a basic shape, the coupling portion with the rotation shaft 300 is cylindrical, and the opposite side to the rotation shaft 300 has a flat shape. The flat shape of the end surface opposite to the coupling portion is a smooth curve. Is formed.

  According to the second embodiment, since the centrifugal effect acts on the entire cross-sectional portion in the flat shape of the pump member 901, the ability to supply the oil existing in the pump member 901 is increased, and the influence of the viscosity of the oil is affected. It becomes difficult to receive and it becomes possible to supply oil stably. That is, when the temperature of the oil rises and the viscosity of the oil decreases, in the mere conical pump member 901, the amount of oil supply decreases rapidly as shown in the characteristic (b) of FIG. In the flat pump member 901, as shown in the characteristic (a) of FIG. 4, a change in the amount of oil supply is small and a stable oil supply amount is obtained.

  Further, according to the second embodiment, since a stable oil supply amount can be obtained as described above, the pump unit 900 can be constituted by a single member, thereby providing an inexpensive structure.

  Next, a third embodiment will be described with reference to FIG. FIG. 5 is an explanatory view of a pump member used in the scroll compressor according to the third embodiment of the present invention, wherein (a) is a top view, (b) is a front view, and (c) is a side view.

  In this third embodiment, the pump member 901 has a cylindrical shape as a basic shape, the coupling portion with the rotating shaft 300 has a cylindrical shape, and the opposite side to the rotating shaft 300 has a flat shape. According to the pump member 901 of the third embodiment, since the basic shape is a cylindrical shape, a more inexpensive structure can be achieved.

  Next, a fourth embodiment will be described with reference to FIG. FIG. 6 is an explanatory diagram of a pump unit of the scroll compressor according to the fourth embodiment of the present invention. (A) is a longitudinal cross-sectional view of a pump part, (b) is a side view of the pump blade single-piece | unit, (c) is BB sectional drawing of (a).

  In the fourth embodiment, a protrusion 901 c is provided in the pump member 901. A pump blade 902 arranged in the pump member 901 and rotating together with the pump member 901 receives the inertial force of the fluid in the pump member 901 driven by the rotary shaft 300, and a force in a direction opposite to the rotational direction of the rotary shaft 300. Receive. In order to support the force in the direction opposite to the rotational direction acting on the pump blade 902, a protrusion 901c is provided in the pump member 901 to serve as a stopper for the pump blade 902. By providing the protrusion 901c on the pump member 901, the pump blade 902 is reliably supported, and the reliability of the pump unit 900 can be improved with a simple and inexpensive structure. The lower end of the pump blade 902 stops at the cylindrical portion of the pump member 901, and the upper portion extends into the oil passage 311.

  Next, a fifth embodiment will be described with reference to FIG. FIG. 7 is an explanatory diagram of a pump unit of a scroll compressor according to a fifth embodiment of the present invention. (A) is a longitudinal cross-sectional view of a pump part, (b) is a side view of the pump blade single-piece | unit, (c) is CC sectional drawing of (a).

  In the fifth embodiment, a pair of protrusions 901 c are provided in the pump member 901. The pair of protrusions 901c are provided at two opposing positions. Both ends of the pump blade 902 are sandwiched between a pair of protrusions 901c. Thereby, the pump blade 902 is reliably supported and oil can be supplied corresponding to both the forward rotation and the reverse rotation of the rotating shaft 300.

  Next, a sixth embodiment will be described with reference to FIG. FIG. 8 is an explanatory diagram of a pump unit of the scroll compressor according to the sixth embodiment of the present invention. (A) is a longitudinal cross-sectional view of a pump part, (b) is a side view of the pump blade single-piece | unit, (c) is DD sectional drawing of (a).

  The sixth embodiment is different from the fifth embodiment in that the pump blade 902 extends to the lower end of the pump member 901, and the others are the same. According to the sixth embodiment, as in the first embodiment, even if the amount of oil in the oil sump 730 decreases, the oil supply capacity is sufficiently high due to the effect of the centrifugal pump blade 902 disposed up to the lower end of the pump member 901. Therefore, a highly reliable pump mechanism can be provided.

  Next, a seventh embodiment will be described with reference to FIG. FIG. 9 is an explanatory diagram of a pump unit of the scroll compressor according to the seventh embodiment of the present invention. (A) is a longitudinal cross-sectional view of a pump part, (b) is a side view of the pump blade single-piece | unit, (c) is EE sectional drawing of (a).

  The seventh embodiment is different from the sixth embodiment in that the shape of the pump member 901 on the side opposite to the coupling portion with the rotating shaft 300 is formed as a spherical surface, and the others are the same. According to the seventh embodiment, since the inclination of the inner wall of the pump member 900 with respect to the rotation shaft 300 is large with respect to the conical shape and the cylindrical shape, the centrifugal pump effect is increased, and a stable oil supply capability is obtained. A highly reliable pump mechanism can be provided.

  Next, an eighth embodiment will be described with reference to FIG. FIG. 10 is an explanatory view of the lower part of the rotary shaft of the scroll compressor according to the eighth embodiment of the present invention. (A) is a longitudinal cross-sectional view of the lower part of a rotating shaft, (b) is a cross-sectional view of the pump part.

  In the eighth embodiment, the outer peripheral portion of the pump member 901 is formed in a double cylindrical shape. The space outside the pump member 901 is opened to face the lower surface of the auxiliary bearing portion 800. The space inside the pump member 901 is the same as in the first embodiment.

  According to the eighth embodiment, the cylindrical member disposed around the pump member 901 exhibits the third centrifugal pump effect. The oil discharged from the upper end of the third centrifugal pump is used to lubricate the auxiliary bearing 803 disposed in the auxiliary bearing portion 800. As a result, oil can be stably supplied to the sub-bearing 803, and the oil supply path is separate from the oil supplied into the pump member 901. Therefore, an oil supply structure with a simple design and high reliability is achieved. Can be provided.

  Next, a ninth embodiment will be described with reference to FIG. FIG. 11 is an explanatory view of the lower part of the rotary shaft of the scroll compressor according to the ninth embodiment of the present invention. (A) is a longitudinal cross-sectional view of the rotating shaft lower part, (b) is a FF cross-sectional view of (a).

  In the ninth embodiment, the coupling means of the pump member 901 and the rotating shaft 300 is a screw having a winding direction of the same thread as the rotating direction of the rotating shaft 300. Since the pump member 901 receives a force in the direction opposite to the rotation direction of the rotary shaft 300, the force of the coupling member on the direction of the rotation direction of the rotary shaft 300 acting on the pump member 901 is received in the direction in which the screw of the coupling means is tightened. The pump member 901 can be provided with a highly reliable pump structure without being detached from the rotary shaft 300.

The longitudinal cross-sectional view of the scroll compressor of 1st Example of this invention is shown. Sectional drawing of the rotating shaft lower part and pump part of the scroll compressor of FIG. 1 is shown. Explanatory drawing of the pump member used for the scroll compressor of 2nd Example of this invention is shown. The oil supply characteristic figure of the pump member of 2nd Example is shown. Explanatory drawing of the pump member used for the scroll compressor of 3rd Example of this invention is shown. Explanatory drawing of the pump part of the scroll compressor of 4th Example of this invention is shown. Explanatory drawing of the pump part of the scroll compressor of 5th Example of this invention is shown. Explanatory drawing of the pump part of the scroll compressor of 6th Example of this invention is shown. Explanatory drawing of the pump part of the scroll compressor of 7th Example of this invention is shown. Explanatory drawing of the rotating shaft lower part of the scroll compressor of 8th Example of this invention is shown. Explanatory drawing of the rotating shaft lower part of the scroll compressor of 9th Example of this invention is shown.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Scroll compressor, 2 ... Compression mechanism part, 3 ... Drive part, 100 ... Fixed scroll, 101 ... Base plate, 102 ... Lap, 103 ... Inlet, 104 ... Discharge port, 105 ... End plate surface, 130 Compression chamber, DESCRIPTION OF SYMBOLS 200 ... Orbiting scroll, 201 ... Base plate, 202 ... Lap, 203 ... Boss, 205 ... Refueling pocket, 210 ... Orbiting bearing, 300 ... Rotating shaft, 301 ... Crankpin, 302 ... Main shaft part, 303 ... Sub bearing support part, 310 ... Pump joint, 311 ... Oil passage, 311a ... First oil passage, 311b ... Second oil passage, 312 ... Side hole, 400 ... Frame, 401 ... Rolling bearing, 402 ... Thrust bearing, 403 ... Frame cover, 404 ... Balance weight cover, 404a ... Bottom wall, 404b ... Side wall, 404c ... Bolt insertion hole, 404d ... Flat part, 405, 406 ... Bolt, 4 DESCRIPTION OF SYMBOLS 7 ... Balance weight, 407a ... Maximum outer diameter part, 408 ... Oil drain pipe, 410 ... Seal ring, 411 ... Back pressure chamber, 500 ... Oldham coupling, 600 ... Electric motor, 601 ... Stator, 602 ... Rotor, 700 ... Sealed container 701 ... Discharge pipe, 702 ... Herme terminal, 710 ... Upper cap, 711 ... Suction pipe, 720 ... Lower cap, 721 ... Leg part, 730 ... Oil reservoir, 800 ... Sub-bearing part, 801 ... Lower frame, 802 ... Housing , 803 ... Rolling bearing (sub bearing), 804 ... Housing cover, 805 ... Bolt, 900 ... Pump part, 901 ... Pump member, 902 ... Pump blade.

Claims (10)

In the sealed container, a compression mechanism for compressing fluid, a rotary shaft connected to the compression mechanism and having an oil passage, an electric motor for driving the rotary shaft, and the rotary shaft supported above the electric motor A main bearing that supports the rotating shaft below the electric motor, and a centrifugal pump unit that supplies oil stored in a bottom portion of the hermetic container to the compression mechanism unit and the bearing through the oil passage. In the fluid compressor provided,
The rotating shaft includes a main shaft portion fixed to a rotor of the electric motor, a crank pin eccentrically provided at an upper end portion of the main shaft portion and connected to the compression mechanism portion, and a sub shaft provided at a lower end portion of the main shaft portion. It has a small-diameter secondary bearing support part supported by a bearing,
The oil passage of the rotating shaft has a first oil passage extending from the lower end of the auxiliary bearing support portion to a lower portion of the main shaft portion, and a second oil passage communicating with the first oil passage and extending to the upper end of the crank pin. With an oil passage,
The second oil passage has a passage portion which is smaller in diameter than the first oil passage and is located outward, and a plurality of the second oil passages are formed in a plane range of the crank pin. .   2. The fluid compressor according to claim 1, wherein the first oil passage is formed coaxially with the rotary shaft, and the second oil passage communicates with a peripheral portion of the first oil passage long in the axial direction. A fluid compressor characterized by being crossed and formed as described above.   2. The fluid compressor according to claim 1, wherein the pump unit includes a cylindrical pump member attached to a lower end portion of the rotating shaft and pump blades disposed in the pump member, and the pump The member is composed of a portion attached to the lower end portion of the rotating shaft and a portion extending downward from the portion to reduce the flow passage cross section, and the pump blade has an outer shape that matches the inner shape of the pump member. A fluid compressor, wherein the fluid compressor is press-fitted so as to reach a lower end portion in a member.   4. The fluid compressor according to claim 3, wherein a portion of the pump member where a flow passage cross section is reduced is formed in a spherical shape.   2. The fluid compressor according to claim 1, wherein the pump portion is formed of a cylindrical pump member, and the pump member has a cylindrical shape at a coupling portion with the rotating shaft and a flat shape on the side opposite to the coupling portion. A fluid compressor characterized by that.   2. The fluid compressor according to claim 1, wherein the pump unit includes a cylindrical pump member attached to a lower end portion of the rotating shaft and pump blades disposed in the pump member. Has a protrusion for preventing rotation of the pump blade.   2. The fluid compressor according to claim 1, wherein the pump portion is formed of a cylindrical pump member, and the protrusion of the pump member is formed so as to sandwich the pump blade.   2. The fluid compressor according to claim 1, wherein the pump unit includes a cylindrical pump member, and the pump member has a screw thread having a coupling portion with the rotation shaft that is the same as the rotation direction of the rotation shaft. A fluid compressor characterized by being connected by a screw in a winding direction. In the sealed container, a compression mechanism portion that compresses fluid, a rotating shaft that is connected to the compression mechanism portion and has an oil passage, an electric motor that drives the rotating shaft, a bearing that supports the rotating shaft, In a fluid compressor including a centrifugal pump unit that supplies oil stored in a bottom portion of a sealed container to the compression mechanism unit and the bearing through the oil passage.
The pump unit is formed of a cylindrical pump member, and the pump member has a cylindrical shape at the coupling portion with the rotating shaft and a flat shape on the opposite side to the coupling portion. . In the sealed container, a compression mechanism for compressing fluid, a rotary shaft connected to the compression mechanism and having an oil passage, an electric motor for driving the rotary shaft, and the rotary shaft supported above the electric motor A main bearing that supports the rotating shaft below the electric motor, and a centrifugal pump unit that supplies oil stored in a bottom portion of the hermetic container to the compression mechanism unit and the bearing through the oil passage. In the fluid compressor provided,
The pump unit is formed of a double cylindrical pump member, and a space outside the pump member is opened facing the lower surface of the auxiliary bearing.

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