JP2008298037A - Vertical type rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce local frictional loss of a roller and an eccentric part in a discharge stroke during low speed operation, in a vertical type rotary compressor. <P>SOLUTION: This compressor 1 is provided with a motor 14, a rotary shaft 2 driven by the motor 14 and having the substantially columnar eccentric part 5, and a compression element 20 provided with the roller 11 performing a revolving motion by eccentric rotation of the eccentric part 5 in a substantially cylindrical cylinder 10, in a closed container 13 filled with lubricating oil 21. The motor 14 and the compression element 20 are vertically arranged. An oil feed hole 3 is provided to be opened on a side surface of the eccentric part 5. The oil feed hole 3 is arranged eccentrically to an upper side in relation to a center of a height direction of the cylinder 10. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a vertical rotary compressor, and is particularly suitable for a vertical rotary compressor used in an air conditioner having a refrigeration cycle.

  Conventionally, as a vertical rotary compressor used in a refrigeration cycle, for example, a structure disclosed in Japanese Patent Application Laid-Open No. 61-145388 (Patent Document 1) is known. The compressor in this prior art is provided with an electric motor composed of a stator and a rotor at the upper part in a sealed container. The rotating shaft connected to the electric motor includes an eccentric portion, and a compression element corresponding to the eccentric portion is provided at the lower portion of the sealed container.

  This conventional vertical rotary compressor will be described with reference to FIGS. 6 and 7. FIG.

  The compression element 20 includes a main bearing 9 that serves as a wall surface on the motor side and that pivotally supports the rotating shaft 2, a sub-bearing 19 that serves as a wall surface on the opposite side of the motor and pivotally supports the rotating shaft 2, and a substantially cylindrical cylinder 10. The roller 11 is disposed in the cylinder 10 and revolves by the eccentric rotation of the eccentric portion 5 of the rotating shaft 2.

  The low-pressure refrigerant gas sucked into the compression element 20 is compressed from a low pressure to a high pressure as the roller 11 revolves. The compressed refrigerant gas is discharged from a discharge port (not shown) provided in the cylinder 10, the main bearing 9 or the sub bearing 19, and is further discharged outside the compressor through the sealed container.

  The rotating shaft 2 is molded integrally with the eccentric portion 5 on the sub-bearing side of the eccentric portion 5 and the substantially elliptical main thrust bearing 22 molded integrally with the eccentric portion 5 on the main bearing side of the eccentric portion 5. And a sub-thrust bearing 23 having a substantially elliptical shape. The main thrust bearing 22 and the sub-thrust bearing 23 are for supporting the vertical movement of the rotary shaft 2, and the radial direction of the rotary shaft 2 rather than the eccentric portion 5 so as not to contact the roller 11. It has a small shape.

  Since the main thrust bearing 22 and the sub thrust bearing 23 are provided, the height L of the eccentric portion 5 is lower than the height of the cylinder 10. The reason why the height of the eccentric part 5 is lowered is to reduce the sliding area between the roller 11 and the eccentric part 5 and to minimize the friction loss of this part under rated conditions.

  The eccentric portion 5 is provided with an oil supply hole 3 that opens to the side surface, and is provided with a through groove 12 that communicates with the oil supply hole 3 and is formed on the outer peripheral surface. A through-hole penetrating in the longitudinal direction is formed inside the rotary shaft 2, and a throttle mechanism is provided at the lower end of the rotary shaft 2. These structures function as the oil supply pump 4, and the lubricating oil accumulated at the bottom in the sealed container is pumped by the rotating action of the rotary shaft 2 and supplied to the oil supply hole 3 of the eccentric portion 5. The lubricating oil flowing out from the oil supply hole 3 passes through the through groove 12, the gap δ 3 between the roller 11 and the eccentric part 5, and further, the gap δ 1 between the roller 11 and the main bearing 9, and the gap between the end plate of the roller 11 and the auxiliary bearing 19. It is supplied to the gap δ4 between the roller 11 and the cylinder 10 in the compression element 20 through δ2.

  These gaps δ1 to δ4 are usually in the range of several μm to several tens of μm. The eccentric part 5 and the oil supply hole 3 are located at the center in the height direction of the cylinder 10 indicated by a one-dot chain line in FIG. Due to the weight of the roller 11, the lower gap δ2 is narrower than the upper gap δ1. Therefore, in the roller 11, the oil film reaction force from the gap δ2 where the oil film is thin is larger than the oil film reaction force from the gap δ1. That is, the roller 11 is stable against a downward load in the gravity direction.

  As shown in FIG. 6, the positional relationship between the roller 11 and the eccentric portion 5 in the rated condition for the high rotation speed operation is such that the roller 11 is not inclined with respect to the direction of gravity.

JP 61-145388 (page 6, FIG. 1)

  In an air conditioner, the annual power consumption is an important index for energy saving, and as a result, in a compressor used in the air conditioner, efficiency at low speed operation is more important than rated conditions. Also in a vertical rotary compressor used in an air conditioner, it has been desired to improve the efficiency of low-speed operation, that is, to reduce loss.

  However, in the conventional vertical rotary compressor described above, there is a problem in that the roller 11 and the eccentric portion 5 are in solid contact locally at the point Q in FIG. I understood.

  That is, as the refrigerant gas in the compression element 20 is compressed, a gas load P is generated on the roller 11. In particular, the pressure distribution in the compression element 20 becomes unstable during the process of discharging the refrigerant gas, and the direction of action of the gas load P varies as shown in FIG. When the gas load P has an upward component, the roller 11 is inclined by the rollover moment M. 6 is generally (δ1 + δ2) <δ3. Therefore, as shown in FIG. 7, the point of the upper outer edge portion of the eccentric portion 5 is balanced with the overturning moment M. From Q, a local load F is generated on the roller 11.

  If the height of the eccentric portion 5 at this time is L, the distance from the center of the inclined rotation of the roller 11 to the point of action Q of the local load F is (L / 2). As the roller 11 is inclined, the local load F is increased, and the roller 11 and the eccentric portion 5 are locally brought into solid contact to increase friction loss. In addition, since the pressure of the refrigerant gas is maximized in the compression process in the discharge process of the refrigerant gas, the gas load P and the local load F are also maximized in the compression process, and the friction loss at the operating point Q, that is, the input of the entire compressor is increased. It was increasing. When the gas load P has a downward component, the roller 11 is stable against the downward load in the direction of gravity as described above, so that the inclination is small.

  From the above, in the conventional vertical rotary compressor, it is found that the reduction of the friction loss between the roller 11 and the eccentric portion 5 at the operating point Q is an important issue in the low-speed operation and the discharge stroke of the refrigerant gas. It was.

  An object of the present invention is to provide a vertical rotary compressor capable of reducing local friction loss between a roller and an eccentric portion in a discharge stroke in a low rotation speed operation.

  In a first aspect of the present invention for achieving the above-mentioned object, an electric motor, a rotary shaft that is driven by the electric motor and has a substantially cylindrical eccentric portion, in a sealed container enclosing lubricating oil, A compression element provided in a substantially cylindrical cylinder with a roller that revolves by eccentric rotation of the eccentric part, and the electric motor and the compression element are arranged vertically and an oil supply hole that opens on a side surface of the eccentric part is provided. A vertical rotary compressor having a wall surface of the compression element on the electric motor side and supporting the rotary shaft; a wall surface of the compression element on the opposite side of the electric motor; and the axis of the rotation shaft A sub-bearing to be supported, a substantially cylindrical main thrust bearing located on the main bearing side and integral with the eccentric part, and a substantially cylindrical sub-position located on the auxiliary bearing side and integral with the eccentric part. At the thrust bearing and the bottom of the sealed container An oil supply pump that pumps up the collected lubricating oil by the rotational action of the rotary shaft and supplies it to the oil supply hole of the eccentric part, and the oil supply hole of the eccentric part is located above the center in the height direction of the cylinder. Is arranged eccentrically.

A more preferable specific configuration example in the first aspect of the present invention is as follows.
(1) The eccentric portion is arranged eccentrically upward with respect to the center in the height direction of the cylinder.
(2) The amount of eccentricity of the eccentric portion to the upper side of the oil supply hole is made larger than the amount of eccentricity of the eccentric portion to the upper side.
(3) The upper and lower outer edge portions of the eccentric portion are each tapered, and the upper taper is made larger than the lower taper.

  According to a second aspect of the present invention, an electric motor, a rotating shaft driven by the electric motor and having a substantially cylindrical eccentric portion, and an eccentric rotation of the eccentric portion are provided in a sealed container enclosing lubricating oil. A vertical rotary compressor comprising a compression element provided with a revolving roller in a substantially cylindrical cylinder, wherein the electric motor and the compression element are arranged vertically and have an oil supply hole opened on a side surface of the eccentric part. A main bearing which becomes a wall surface of the compression element on the motor side and supports the rotating shaft, and a sub-bearing which becomes a wall surface of the compression element on the opposite side of the motor and supports the rotating shaft; A substantially cylindrical main thrust bearing located on the main bearing side and integrated with the eccentric portion; a substantially cylindrical sub thrust bearing located on the sub bearing side and integrated with the eccentric portion; and the sealing The lubricating oil collected at the bottom of the container Pumped up by the rotation action of the rotating shaft and an oil pump for supplying the oil supply hole of the eccentric portion, the eccentric portion, with respect to the center in the height direction of the cylinder, it lies in the eccentrically disposed on the upper side.

A more preferable specific configuration example in the second aspect of the present invention is as follows.
(1) The height of the auxiliary thrust bearing is made higher than the height of the main thrust bearing.

  In the third aspect of the present invention, the motor and the substantially cylindrical eccentric part driven by the motor are shifted from each other by 180 ° with respect to the rotation angle in the sealed container in which the lubricating oil is sealed. A rotary shaft having two upper and lower shafts, and two compression elements each having a roller that revolves by an eccentric rotation of the eccentric portion in a substantially cylindrical cylinder, and the electric motor and the compression element are arranged vertically. And a rotary rotary compressor having an oil supply hole that opens on a side surface of the eccentric portion, and serves as a wall surface on the motor side of the first compression element located on the upper side of the two compression elements and supports the rotating shaft. A main bearing, a sub-bearing serving as a wall surface on the opposite side of the electric motor of the second compression element located on the lower side of the two compression elements and supporting the rotating shaft, the first compression element, and the second compression element Wall of compression element Partition plate, a substantially cylindrical main thrust bearing that is located on the main bearing side and integrated with the upper eccentric portion, and a substantially cylindrical main thrust bearing that is located on the auxiliary bearing side and integrated with the lower eccentric portion. A cylinder-shaped sub-thrust bearing, and an oil supply pump that pumps up the lubricating oil accumulated at the bottom of the hermetic container by the rotating action of the rotary shaft and supplies the oil to the oil supply hole of the eccentric part, The oil supply hole of the eccentric part is arranged eccentrically on the upper side with respect to the center in the height direction of the cylinder in the first compression element.

A more preferable specific configuration example in the third aspect of the present invention is as follows.
(1) The eccentric portion of the first compression element is arranged eccentrically upward with respect to the center in the height direction of the cylinder of the first compression element.

  In the fourth aspect of the present invention, an electric motor and an approximately cylindrical eccentric part driven by the electric motor are shifted from each other by 180 ° with respect to the rotation angle in a sealed container enclosing lubricating oil. A rotary shaft having two upper and lower shafts, and two compression elements each having a roller that revolves by an eccentric rotation of the eccentric portion in a substantially cylindrical cylinder, and the electric motor and the compression element are arranged vertically. And a rotary rotary compressor having an oil supply hole that opens on a side surface of the eccentric portion, and serves as a wall surface on the motor side of the first compression element located on the upper side of the two compression elements and supports the rotating shaft. A main bearing, a sub-bearing serving as a wall surface on the opposite side of the electric motor of the second compression element located on the lower side of the two compression elements and supporting the rotating shaft, the first compression element, and the second compression element Wall of compression element Partition plate, a substantially cylindrical main thrust bearing that is located on the main bearing side and integrated with the upper eccentric portion, and a substantially cylindrical main thrust bearing that is located on the auxiliary bearing side and integrated with the lower eccentric portion. A cylinder-shaped sub-thrust bearing, and an oil supply pump that pumps up the lubricating oil accumulated at the bottom of the hermetic container by the rotating action of the rotary shaft and supplies the oil to the oil supply hole of the eccentric part, The eccentric portion is arranged eccentrically upward with respect to the center of the first compression element in the height direction of the cylinder.

A more preferable specific configuration example in the fourth aspect of the present invention is as follows.
(1) The height of the auxiliary thrust bearing is made higher than the height of the main thrust bearing.

  According to the vertical rotary compressor of the present invention, it is possible to reduce the local friction loss between the roller and the eccentric portion in the discharge stroke in the low rotation speed operation.

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.
(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. 1 is a longitudinal sectional view of a vertical rotary compressor 1 according to the present embodiment, FIG. 2 is a sectional view taken along line AA of FIG. 1, and FIG. 3 is a longitudinal sectional view of the compression element of FIG. .

  The compressor 1 includes a sealed container 13 in which a lubricating oil 21 is enclosed. An electric motor 14 having a stator 7 and a rotor 8 is provided above the sealed container 13. The rotating shaft 2 connected to the electric motor 14 includes an eccentric portion 5 and is pivotally supported by the main bearing 9 and the auxiliary bearing 19. The compression element 20 includes a main bearing 9 provided with an end plate, a substantially cylindrical cylinder 10, a cylindrical roller 11 fitted to the outer periphery of the eccentric portion 5, and a sub-bearing 19 provided with an end plate. Is done. The electric motor 14, the main bearing 9, the cylinder 10, and the auxiliary bearing 19 are arranged in order from the top in the direction of gravity. The main bearing 9, the cylinder 10 and the auxiliary bearing 19 forming the compression element 20 are stacked and integrated with a fastening element (not shown) such as a bolt. The main bearing 9, the cylinder 10, and the auxiliary bearing 19 are formed by polishing or grinding a cast or iron-based sintered member. The roller 11 has chamfers of the same size on the upper and lower inner edges, and has a symmetrical shape with respect to the vertical direction.

  The main bearing 9 is fixed to the inner wall of the hermetic container 13 by welding, and supports compression element parts such as the cylinder 10 and the auxiliary bearing 19. In place of the main bearing 9, the cylinder 10 may be fixed to the inner wall of the sealed container 13.

  The rotary shaft 2 is formed by integrating the eccentric part 5 with the eccentric part 5 on the main bearing side of the eccentric part 5 and forming the eccentric part 5 with the eccentric part 5 on the auxiliary bearing side of the eccentric part 5. The sub-thrust bearing 23 having a substantially elliptical shape is provided. The auxiliary thrust bearing 23 receives a reaction force from the end plate of the auxiliary bearing 19 and supports the rotating shaft 2 against its own weight. The rotating shaft 2 is formed by integrally molding the main casting bearing 22, the eccentric portion 5, and the auxiliary thrust bearing 23 by cutting and polishing a cylindrical casting member.

  In this embodiment, the height of the cylinder 10 is about 20 mm, the height L of the eccentric portion 5 is about 12 mm, and the eccentric portion 5 is eccentric by an eccentric amount Δ1 with respect to the center of the cylinder 10 in the height direction. Yes. This eccentric amount Δ1 is about 2 mm, which is sufficiently larger than a processing tolerance of ± 0.5 mm by general cutting, and is about 10% of the height of the cylinder 10. Accordingly, the height of the auxiliary thrust bearing 23 is about 6 mm, which is higher than the height of the main thrust bearing 22 is about 2 mm.

  The rotary shaft 2 is provided with an oil supply pump 4 along the axis. The oil pump 4 includes a throttle portion 4 a provided at the lower end of the rotating shaft 2, an oil supply path 4 b drilled around the axis of the rotating shaft 2, and gas refrigerant contained in the lubricating oil 21. And a through-hole 4c for exhausting. The oil supply path 4b and the through hole 4c are substantially circular holes processed by a drill.

  The eccentric part 5 is provided with an oil supply hole 3 drilled to communicate the side surface thereof with the oil supply path 4b. Further, a through groove 12 communicating with the oil supply hole 3 is provided on the side surface of the eccentric portion 5 in order to supply the lubricating oil 21 in the vertical direction of the eccentric portion 5. The through groove 12 is provided by cutting with a disk-shaped cutter or end mill. Further, in order to supply the lubricating oil 21 to the main bearing 9 and the auxiliary bearing 19, a small diameter oil supply hole 15 is provided in the rotary shaft 2. The oil supply hole 3 and the small-diameter oil supply hole 15 are substantially circular holes each processed by a drill. In this embodiment, the hole diameter of the oil supply hole 3 is about φ3 mm, and the hole diameter of the small oil supply hole 15 is about φ2 mm.

  As shown in FIG. 1, the oil supply hole 3 is eccentric by an eccentric amount Δ2 with respect to the center of the cylinder 10 in the height direction. In this embodiment, the height of the cylinder is about 20 mm, and the amount of eccentricity Δ2 is about 4 mm. The eccentric amount Δ2 is sufficiently larger than the processing tolerance ± 0.5 mm by general cutting, and is about 20% of the cylinder height. Further, the eccentric amount Δ2 of the oil supply hole 3 is made larger than the eccentric amount Δ1 of the eccentric portion 5.

  The oil supply pump 4 pumps up the lubricating oil 21 collected at the bottom of the sealed container 13 by the centrifugal force accompanying the rotation of the rotary shaft 2 and supplies the lubricating oil 21 to the oil supply hole 3 and the small diameter oil supply hole 15. The lubricating oil 21 mainly supplied from the oil supply hole 3 flows through the through groove 12 and the gap between the roller 11 and the eccentric portion 5, and the gap between the roller 11 and the end plate of the main bearing 9, the roller 11 and the auxiliary bearing 19. Is supplied into the compression element 20 through a gap with the end plate.

  As shown in FIG. 2, the working space in the compression element 20 is divided into a compression space 31 and a suction space 32 by a flat vane 18 connected to a biasing force applying means 6 such as a coil spring. The vane 18 is fitted in the slot groove of the cylinder 10 and moves forward and backward while contacting the outer periphery of the roller 11 rotating according to the eccentric motion of the eccentric portion 5. The refrigerant gas, which is a working fluid, is sucked into the compression element 20 from the suction port 25 and compressed from a low pressure to a high pressure. The refrigerant gas in the compression element 20 is discharged into the sealed container 13 through a discharge valve 26 (see FIG. 1) that opens when a preset pressure is reached. The discharged refrigerant gas is then discharged out of the compression chamber through a discharge pipe (not shown) provided in the upper part of the hermetic container 13 through the gaps and air holes of the electric motor 14.

  Next, the operation of the roller 11 of this embodiment will be described with reference to FIG. In the present embodiment, the eccentric portion 5 and the oil supply hole 3 are eccentric with respect to the center in the height direction of the cylinder 10 by an eccentric amount Δ1 and an eccentric amount Δ2, respectively. Therefore, when the rollover moment M acts and the roller 11 is tilted, the distance from the center of tilting rotation of the roller 11 to the point Q of the local load F that balances with the rollover moment M becomes (L / 2 + Δ1), which is the conventional example of FIG. It is longer than the technology by the amount of eccentricity Δ1. Since the local load F decreases as the distance (L / 2 + Δ1) increases, according to this embodiment, the local friction loss between the roller 11 and the eccentric portion 5 due to the local load F can be reduced. In this embodiment, since the height L of the eccentric portion is 12 mm and the eccentric amount Δ1 of the eccentric portion 5 is 2 mm, the local load F can be reduced by about 25% with respect to the prior art.

  At the same time, the oil supply hole 3 is also eccentric by the amount of eccentricity Δ2, so the oil supply hole 3 is closer to the operating point Q of the local load F than in the prior art of FIG. For this reason, it becomes easy to supply the lubricating oil 21 to the point of action Q, and the local solid contact between the roller 11 and the eccentric part 5 at the point of action Q can be relaxed, and the friction loss can be reduced.

Further, in this embodiment, the height L of the eccentric portion 5, that is, the sliding area of the eccentric portion 5 is not enlarged as compared with the prior art of FIG. It does not lead to an increase in additional friction loss when it is not inclined.
(Second embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment in the following points, and the other points are basically the same as those in the first embodiment, so that the duplicated explanation is omitted.

  In the second embodiment, an upper taper 16 and a lower taper 17 are provided on the upper and lower outer edge portions of the eccentric portion 5, respectively. The lower taper was C0.1 to 0.5 mm, and the upper taper 16 was larger than the lower taper 17 to C0.8 to 1.2 mm.

  In the second embodiment, since the upper taper 16 is provided large, the wedge effect of the roller 11 and the upper taper 16 improves the lubricity of the lubricating oil 21 with respect to the action point Q of the local load F. In addition, since the oil film reaction force acts on the roller 11 at the upper taper 16 in the vicinity of the action point Q, the local load F applied to the action point Q can be dispersed and the solid contact at this part can be relaxed.

On the other hand, the taper 17 on the lower side of the eccentric portion 5 where local load is less likely to occur is smaller than the taper 16 and suppresses the supply of the lubricating oil 21 more than necessary and the reduction of the sliding area of the eccentric portion 5. That is, the second embodiment can improve the state of local solid contact between the roller 11 and the eccentric portion 5 due to the inclination of the roller 11 as compared with the first embodiment 1, and can reduce the friction loss at this portion. it can.
(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment in the following points, and the other points are basically the same as those in the first embodiment, and therefore, redundant description is omitted.

  In the third embodiment, as shown in FIG. 5, a vertical two-cylinder rotary compressor 1 having two compression elements 20a and 20b is provided. In the compressor 1 of the third embodiment, the rotary shaft 2 connected to the electric motor 14 includes two eccentric parts 5a and 5b on the upper and lower sides, and the main bearing 9 and the auxiliary bearing at the upper and lower positions of the eccentric parts 5a and 5b. 19 is pivotally supported. The main bearing 9, the first compression element 20a, the partition plate 24, the second compression element 20b, and the auxiliary bearing 19 are laminated in order from the motor 14 side with respect to the rotating shaft 2, and fastening elements such as bolts (see FIG. (Not shown).

  The first compression element 20a located on the upper side forms an operating space with the end plate of the main bearing 9, the cylinder 10a, the cylindrical roller 11a fitted to the outer periphery of the eccentric portion 5a, and the partition plate 24. The second compression element 20b located on the lower side forms an operating space with the end plate of the auxiliary bearing 19, the cylinder 10b, the cylindrical roller 11b fitted to the outer periphery of the eccentric portion 5b, and the partition plate 24. . In these operating spaces, as in FIG. 2 of the first embodiment, a flat vane 18 connected to the biasing force applying means 6 such as a coil spring rotates in accordance with the eccentric motion of the eccentric portions 5a and 5b. By moving forward and backward while contacting the outer periphery of the rollers 11a and 11b, the space is divided into a compression space and a suction space, respectively.

  The main bearing 9 is fixed to the inner wall of the sealed container 13 by welding, and supports pump parts such as the cylinder 10 and the auxiliary bearing 19. In place of the main bearing 9, the cylinder 10 a or the cylinder 10 b may be fixed to the inner wall of the sealed container 13.

  The rotary shaft 2 is molded with a substantially elliptical main thrust bearing 22 formed integrally with the eccentric portion 5a on the main bearing side of the eccentric portion 5a, and with the eccentric portion 5b formed on the auxiliary bearing side of the eccentric portion 5b. The sub-thrust bearing 23 having a substantially elliptical shape is provided. The auxiliary thrust bearing 23 receives a reaction force from the end plate of the auxiliary bearing 19 and supports the rotating shaft 2 against its own weight.

  Since the cylinder 20a and the cylinder 20b share the processing jig, the vane 18, and the urging force applying means 6, they have the same height and the same inner diameter. Also, the roller 11a and the roller 11b have the same shape and are compatible. The eccentric part 5a and the eccentric part 5b have the same outer diameter and height. Further, the through groove 12a and the through groove 12b, and the oil supply hole 3a and the oil supply hole 3b have the same shape in consideration of workability.

  The partition plate 24 is a substantially disk-shaped casting or an iron-based sintered member. The partition plate 24 is formed with an inner hole 27 through which the eccentric portion 5a passes when assembled.

  The compression element 20 drives the roller 11 when the eccentric part 5 rotates eccentrically. As shown in FIG. 4, the eccentric portion 5a and the eccentric portion 5b have a phase difference of 180 °, and the phase difference in the compression process of the first compression element 20a and the second compression element 20b is 180 °. That is, the compression processes of the two compression elements 20a and 20b are in opposite phases.

  However, the eccentric portion 5a and the oil supply hole 3a constituting the first compression element 20a located on the upper side are respectively Δ1 and Δ2 with respect to the center in the height direction of the cylinder 10a, as in FIG. 1 of the first embodiment. It is arranged eccentrically. On the other hand, the eccentric portion 5b and the oil supply hole 3b constituting the second pressure element 20b positioned on the lower side are arranged at the same position as the center in the height direction of the cylinder 10b, as in FIG.

  Refrigerant gas, which is a working fluid, is sucked from the suction ports of the cylinders 10a and 10b, respectively, and is compressed from low pressure to high pressure as the rollers 11a and 11b rotate eccentrically. The refrigerant gas of each compression element 20a, 20b is discharged through discharge valves 26a, 26b that open when a preset pressure is reached. The refrigerant gas discharged from the first compression element 20 a is discharged into the sealed container 13. The refrigerant gas discharged from the second compression element 20b passes through communication holes (not shown) provided in each of the auxiliary bearing 19, the cylinder 10b, the partition plate 24, the cylinder 10a, and the main bearing 9, and then the sealed container 13. Discharged. The refrigerant gas discharged into the sealed container 13 is discharged out of the compression chamber through a discharge pipe (not shown) provided at the upper part of the sealed container 13. The auxiliary bearing 19 includes a cover 28 that isolates the refrigerant gas discharged from the second compression element 20 b and the refrigerant gas discharged to the sealed container 13.

  In the vertical two-cylinder rotary compressor, since the two compression elements 20 are provided, the height of the pump portion is increased. Since the lubricating oil 21 is accumulated at the bottom in the sealed container 13, the lift of the oil supply pump 4 becomes large, and it becomes difficult to supply oil to the first compression element 20a located on the upper side. In particular, when operated at a low rotational speed, the centrifugal force of the oil supply pump 4 is small, and this tendency is remarkable. Therefore, local solid contact between the roller 11 and the eccentric portion 5 accompanying the inclination of the roller 11 occurs frequently in the first compression element 20a, and increases the compressor input.

  According to the third embodiment, the same structure as that of the first embodiment is used in the first compression element 20a. Accordingly, local solid contact between the roller 11a and the eccentric portion 5a in the first compression element 20a can be improved, and the compressor input can be reduced.

1 is a longitudinal sectional view of a vertical rotary compressor according to a first embodiment of the present invention. AA sectional drawing of FIG. The longitudinal cross-sectional view at the time of the low rotation speed operation | movement of the compression element of FIG. The longitudinal cross-sectional view of the compression element of 2nd Example of this invention. The longitudinal cross-sectional view of the vertical 2 cylinder rotary compressor of 3rd Example of this invention. The longitudinal cross-sectional view of the compression element of the vertical rotary compressor of a prior art. FIG. 7 is a longitudinal sectional view of the compression element of FIG. 6 during low speed operation.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Rotating shaft, 3 ... Oil supply hole, 4 ... Oil supply pump, 4a ... Restriction part, 4b ... Oil supply path, 4c ... Through-hole, 5 ... Eccentric part, 6 ... Energizing force provision means, Stator 7, DESCRIPTION OF SYMBOLS 8 ... Rotor, 9 ... Main bearing, 10 ... Cylinder, 11 ... Roller, 12 ... Through groove, 13 ... Sealed container, 14 ... Electric motor, 15 ... Small diameter oil supply hole, 16 ... Upper taper, 17 ... Lower taper, 18 ... Vane , 19 ... sub bearing, 20 ... compression element, 21 ... lubricating oil, 22 ... main thrust bearing, 23 ... sub thrust bearing, 24 ... partition plate, 25 ... suction port, 26 ... discharge valve.

Claims (10)

An electric motor, a rotary shaft driven by the electric motor and having a substantially cylindrical eccentric portion, and a roller that revolves by the eccentric rotation of the eccentric portion are contained in a sealed cylinder in which lubricating oil is sealed. A vertical rotary compressor that has an oil supply hole that is disposed on the upper and lower sides of the electric motor and the compression element and that opens on a side surface of the eccentric part.
A main bearing that becomes a wall surface of the compression element on the electric motor side and supports the rotating shaft;
A sub-bearing that becomes the wall surface of the compression element opposite to the electric motor and supports the rotating shaft;
A substantially cylindrical main thrust bearing located on the main bearing side and integrated with the eccentric portion;
A substantially cylindrical sub-thrust bearing located on the sub-bearing side and integrated with the eccentric portion;
An oil supply pump that pumps up the lubricating oil accumulated at the bottom of the sealed container by the rotating action of the rotating shaft and supplies the oil to the oil supply hole of the eccentric part,
A vertical rotary compressor characterized in that an oil supply hole of the eccentric portion is eccentrically arranged on the upper side with respect to a center in a height direction of the cylinder.   The vertical rotary compressor according to claim 1, wherein the eccentric portion is eccentrically arranged on an upper side with respect to a center in a height direction of the cylinder.   3. The vertical rotary compressor according to claim 2, wherein an eccentric amount of the eccentric portion to the upper side of the oil supply hole is larger than an eccentric amount of the eccentric portion to the upper side.   2. The vertical rotary compressor according to claim 1, wherein a taper is provided on each of upper and lower outer edge portions of the eccentric portion, and the upper taper is larger than the lower taper. An electric motor, a rotary shaft driven by the electric motor and having a substantially cylindrical eccentric portion, and a roller that revolves by the eccentric rotation of the eccentric portion are contained in a sealed cylinder in which lubricating oil is sealed. A vertical rotary compressor that has an oil supply hole that is disposed on the upper and lower sides of the electric motor and the compression element and that opens on a side surface of the eccentric part.
A main bearing that becomes a wall surface of the compression element on the electric motor side and supports the rotating shaft;
A sub-bearing that becomes the wall surface of the compression element opposite to the electric motor and supports the rotating shaft;
A substantially cylindrical main thrust bearing located on the main bearing side and integrated with the eccentric portion;
A substantially cylindrical sub-thrust bearing located on the sub-bearing side and integrated with the eccentric portion;
An oil supply pump that pumps up the lubricating oil accumulated at the bottom of the sealed container by the rotating action of the rotating shaft and supplies the oil to the oil supply hole of the eccentric part,
A vertical rotary compressor characterized in that the eccentric portion is eccentrically arranged on the upper side with respect to the center in the height direction of the cylinder.   6. The vertical rotary compressor according to claim 5, wherein the height of the auxiliary thrust bearing is higher than the height of the main thrust bearing. An electric motor, a rotary shaft that is driven by the electric motor and has two substantially cylindrical eccentric parts at the top and bottom at positions shifted from each other by 180 ° with respect to the rotation angle, and the eccentric An oil supply hole provided with two compression elements provided in a substantially cylindrical cylinder with a roller that revolves by eccentric rotation of the part, and wherein the electric motor and the compression element are arranged vertically and open on a side surface of the eccentric part A vertical rotary compressor having
A main bearing serving as a wall surface on the motor side of the first compression element located on the upper side of the two compression elements and supporting the rotary shaft;
A secondary bearing which is a wall surface on the opposite side of the electric motor of the second compression element located on the lower side of the two compression elements and supports the rotating shaft;
A partition plate serving as wall surfaces of the first compression element and the second compression element;
A substantially cylindrical main thrust bearing located on the main bearing side and integrated with the upper eccentric portion;
A substantially cylindrical sub-thrust bearing located on the sub-bearing side and integrated with the lower eccentric portion;
An oil supply pump that pumps up the lubricating oil accumulated at the bottom of the sealed container by the rotating action of the rotating shaft and supplies the oil to the oil supply hole of the eccentric part,
The vertical rotary compressor characterized in that an oil supply hole of the eccentric portion in the first compression element is eccentrically arranged upward with respect to a center in the height direction of the cylinder in the first compression element.   8. The vertical rotary compressor according to claim 7, wherein the eccentric portion of the first compression element is arranged eccentrically upward with respect to the center of the first compression element in the height direction of the cylinder. . An electric motor, a rotary shaft that is driven by the electric motor and has two substantially cylindrical eccentric parts at the top and bottom at positions shifted from each other by 180 ° with respect to the rotation angle, and the eccentric An oil supply hole provided with two compression elements provided in a substantially cylindrical cylinder with a roller that revolves by eccentric rotation of the part, and wherein the electric motor and the compression element are arranged vertically and open on a side surface of the eccentric part A vertical rotary compressor having
A main bearing serving as a wall surface on the motor side of the first compression element located on the upper side of the two compression elements and supporting the rotary shaft;
A secondary bearing which is a wall surface on the opposite side of the electric motor of the second compression element located on the lower side of the two compression elements and supports the rotating shaft;
A partition plate serving as wall surfaces of the first compression element and the second compression element;
A substantially cylindrical main thrust bearing located on the main bearing side and integrated with the upper eccentric portion;
A substantially cylindrical sub-thrust bearing located on the sub-bearing side and integrated with the lower eccentric portion;
An oil supply pump that pumps up the lubricating oil accumulated at the bottom of the sealed container by the rotating action of the rotating shaft and supplies the oil to the oil supply hole of the eccentric part,
A vertical rotary compressor characterized in that the eccentric portion of the first compression element is arranged eccentrically upward with respect to the center of the cylinder in the height direction of the first compression element.   The vertical rotary compressor according to claim 9, wherein the height of the auxiliary thrust bearing is higher than the height of the main thrust bearing.

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