JP2017155718A - Fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid machine which enables reduction of friction loss occurring at a crank shaft lower end part and enables a lubrication oil to be unfailingly supplied to other slide parts.SOLUTION: A hermetic scroll compressor includes: an annular thrust plate 40 having a through hole 41 through which a lubrication oil flows; and a crank shaft 11 placed on an upper surface of the thrust plate 40 and formed with a circulation passage 17 through which the lubrication oil that has passed through the through hole 41 of the thrust plate 40 circulates. In a slide area between the crank shaft 11 and the thrust plate 40, a recessed groove part 42, to which the lubrication oil is supplied from the through hole 41, is formed in at least one of the crank shaft 11 and the thrust plate 40. An outer radial end part 42a of the groove part 42 is positioned at the inner side of an outermost peripheral part in the slide area.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a fluid machine.

  In a vertical hermetic compressor, a compression mechanism and a motor (electric motor) for driving the compression mechanism are housed in a housing, and the compression mechanism and the motor rotor are coupled by the same crankshaft. The crankshaft is provided such that the axial direction is a vertical direction, and a thrust load is applied to the lower end portion of the crankshaft. Here, the thrust load is the axial weight of the crankshaft and the motor rotor and the magnet pull force generated during operation.

  When supporting the above-described thrust load, friction loss occurs at the lower end of the crankshaft. Therefore, as described in Patent Documents 1 and 2 below, a thrust bearing that contacts the lower end of the crankshaft is installed.

Japanese Utility Model Publication No. 62-78389 JP 2014-152747 A

  Patent Documents 1 and 2 describe that lubricating oil is supplied to a thrust bearing to improve lubricity in the thrust bearing. And in the sliding region of the lower end of the crankshaft and the thrust bearing, an oil supply groove for supplying lubricating oil to the thrust bearing is formed extending all over the radial direction, that is, from the inner peripheral portion to the outer peripheral portion. .

  The oil passage inside the compressor is formed at the center of the crankshaft and is branched to a journal bearing and a compression mechanism that support a radial load. Lubricating oil is supplied from a pump installed around the lower end of the crankshaft to an oil passage provided at the center of the crankshaft, and then supplied to a journal bearing and a compression mechanism via the oil passage.

  Therefore, when the lubricating oil boosted by the pump is also supplied to the thrust bearing, if the oil supply groove formed in the sliding region of the lower end portion of the crankshaft and the thrust bearing is formed over the entire radial direction, the lubricating oil is It will pass through this oil supply groove. As a result, there is a problem that a large amount of lubricating oil pressurized by the pump flows out from the oil supply groove, and the amount of lubricating oil supplied to the journal bearing, the compression mechanism, and the like is reduced.

  The present invention has been made in view of such circumstances, and can reduce friction loss generated at the lower end portion of the crankshaft and reliably supply lubricating oil to other sliding portions. It is an object of the present invention to provide a fluid machine capable of performing the above.

In order to solve the above problems, the fluid machine of the present invention employs the following means.
That is, the fluid machine according to the present invention is an annular plate portion having a through hole through which lubricating oil flows, and is placed on the upper surface of the plate portion, and passes through the through hole of the plate portion inside. A crankshaft formed with a flow passage through which lubricating oil flows, and in the sliding region of the crankshaft and the plate portion, at least one of the crankshaft and the plate portion is connected to the through hole. A concave groove portion to which lubricating oil is supplied is formed, and the outer end portion in the radial direction of the groove portion is located inside the outermost peripheral portion in the sliding region.

According to this configuration, the through hole is formed in the plate portion, the flow passage is formed inside the crankshaft placed on the upper surface of the plate portion, and after the lubricating oil flows through the through hole of the plate portion, Lubricating oil flows through the shaft passage. In the sliding region between the crankshaft and the plate portion, a groove portion is formed in at least one of the crankshaft and the plate portion, and lubricating oil is supplied to the groove portion from the through hole. As a result, the sliding region between the crankshaft and the plate portion is filled with lubricating oil to form an oil film, and friction loss can be reduced. Further, since the outer end in the radial direction of the groove is located on the inner side of the outermost peripheral part in the above-described sliding region, the lubricating oil supplied to the groove is outer peripheral from the inner peripheral side of the sliding region. Hard to leak to the side.
For example, the outer end in the radial direction of the groove is a position on the inner side of about 10% of the radius of the outermost periphery in the sliding region.

  In the above invention, the outer end portion in the radial direction of the groove portion may be outside an intermediate position between the innermost peripheral portion and the outermost peripheral portion in the sliding region.

  According to this structure, lubricating oil can be supplied to the outer side rather than the intermediate position between the innermost periphery part in the sliding area | region and the said outermost periphery part by a groove part.

  In the above invention, the area of the region where the groove is formed in the sliding region is 50% or more and 80% of the total area inside the outer end of the groove in the radial direction of the sliding region. It may be the following.

  According to this configuration, an oil film is easily formed in the sliding region between the crankshaft and the plate portion by the lubricating oil supplied to the groove portion.

  In the above invention, a tapered surface may be formed in a radially inner portion of the groove portion or a portion of the crankshaft or the plate portion facing the radially inner portion of the groove portion.

  According to this configuration, since the radially inner portion of the groove portion or the portion facing the groove portion is a tapered surface, the radially inner side of the groove portion is widened in the height direction, and the lubricating oil is lubricated with respect to the inside of the groove portion. Becomes easy to be supplied.

  In the above invention, the groove portion may have a step shape, a taper shape, or a dimple shape.

  According to the present invention, it is possible to reduce friction loss generated at the lower end portion of the crankshaft, and to reliably supply lubricating oil to other sliding portions.

It is a longitudinal section showing a scroll type compressor concerning one embodiment of the present invention. It is a partial expanded longitudinal cross-sectional view which shows the thrust plate of the scroll compressor which concerns on one Embodiment of this invention. It is a top view which shows the thrust plate of the scroll compressor which concerns on one Embodiment of this invention. It is a longitudinal cross-sectional view which shows an example of the groove part formed in the thrust plate of the scroll compressor which concerns on one Embodiment of this invention. It is a longitudinal cross-sectional view which shows an example of the groove part formed in the thrust plate of the scroll compressor which concerns on one Embodiment of this invention. It is a longitudinal cross-sectional view which shows an example of the groove part formed in the thrust plate of the scroll compressor which concerns on one Embodiment of this invention. It is a longitudinal cross-sectional view which shows the lower end part of the crankshaft, the thrust plate, and the suction pipe of the scroll compressor which concerns on one Embodiment of this invention. It is a graph which shows the efficiency of the air conditioning apparatus for every operation mode or performance evaluation. It is a longitudinal section showing a rotary type compressor concerning one embodiment of the present invention.

Hereinafter, a hermetic scroll compressor according to an embodiment of the present invention will be described with reference to the drawings.
As shown in FIG. 1, a hermetic scroll compressor 1 as a scroll fluid machine includes a cylindrical hermetic housing 2 that is long in the vertical direction and whose bottom is sealed by a lower cover. The upper portion of the sealed housing 2 is sealed by a discharge cover 3 and an upper cover 4, and a discharge chamber 5 is formed between the discharge cover 3 and the upper cover 4 for discharging compressed high-pressure gas. .

  An upper bearing member (frame member) 6 is fixedly installed in the upper part of the hermetic housing 2, and a scroll compression mechanism 7 is incorporated via the upper bearing member 6, and a stator 8 and a rotor 9 are installed in the lower part thereof. An electric motor 10 comprising: The electric motor 10 is incorporated by fixing the stator 8 to the hermetic housing 2, and a crankshaft 11 is fixed to the rotor 9.

  At the upper end of the crankshaft 11, a crankpin 12 whose shaft center is eccentric by a predetermined dimension is provided, and the scroll compression mechanism 7 is driven by the electric motor 10 by connecting the crankpin 12 to the scroll compression mechanism 7. It is possible. The crankshaft 11 is rotatably supported by the journal bearing portion 6 </ b> A of the upper bearing member 6, and the lower end portion is rotatably supported by the lower journal bearing 13 provided at the lower portion of the sealed housing 2. ing.

  A positive displacement oil pump 14 is provided between the lower journal bearing 13 and the lower end portion of the crankshaft 11, and the lubricating oil 15 filled in the bottom of the hermetic housing 2 is sucked in via the suction pipe 16, It is configured to discharge into a flow passage 17 that is formed in the shaft 11 along the axial direction. The lubricating oil 15 can be supplied to parts that require lubrication, such as the upper bearing member 6, the scroll compression mechanism 7, and the lower journal bearing 13, through the flow passage 17.

  The scroll compression mechanism 7 includes the upper bearing member 6 as one of the components, and is slidably supported by a fixed scroll 18 fixedly installed on the upper bearing member 6 and a thrust bearing portion 6B of the upper bearing member 6. And is interposed between the orbiting scroll 19 that forms the compression chamber 20 by meshing with the fixed scroll 18, and the upper bearing member 6 and the orbiting scroll 19. A rotation preventing mechanism 21 such as an Oldham ring to be allowed is provided between a crank pin 12 of the crankshaft 11 and a bearing boss 19C provided on the back surface of the orbiting scroll 19. Drive bush 22 and slewing bearing (needle bearing) 23, and the center portion of the end plate of the fixed scroll 18 is It is installed on the upper bearing member 6 in the connected state to the charge cover 3.

  The fixed scroll 18 includes an end plate 18A and a spiral wrap 18B erected on the end plate 18A, a discharge port 24 is provided at the center of the end plate 18A, and the wrap teeth of the spiral wrap 18B. The tip seal 25 is installed on the front surface. The orbiting scroll 19 includes an end plate 19A and a spiral wrap 19B standing on the end plate 19A. A bearing boss 19C is provided on the back surface of the end plate 19A, and the spiral wrap 19B is wrapped. The tip seal 26 is installed on the tooth tip surface.

  The scroll compression mechanism 7 opens the refrigerant gas sucked into the sealed housing 2 through the suction pipe 27 opened at a position facing the stator winding 8 </ b> A of the electric motor 10 into the sealed housing 2. The gas is sucked into the compression chamber 20 from the suction port 28 and compressed into a high-temperature and high-pressure gas. This compressed gas is discharged into the discharge chamber 5 through the discharge port 24 provided in the center of the fixed scroll 18 and the discharge valve 29 provided in the discharge cover 3, and further connected to the discharge chamber 5. It is sent to the outside of the compressor through the discharge pipe 30 that is present.

Hereinafter, the thrust plate 40 provided in the compressor according to the present embodiment will be described with reference to FIGS. 2 to 7.
The thrust plate 40 is a plate-like member provided in contact with the lower end surface of the crankshaft 11. The thrust plate 40 has a thickness of about 1 mm, for example. The thrust plate 40 is installed between the lower surface of the lower journal bearing 13 and the upper surface of the suction pipe 16.

  The thrust plate 40 is formed with a through hole 41 through which the lubricating oil 15 flows. Through the through hole 41, the flow passage 51 formed in the suction pipe 16 and the flow passage 17 formed in the crankshaft 11 communicate with each other. As a result, as shown in FIG. 7, the lubricating oil 15 that has passed through the suction pipe 16 flows through the through hole 41 of the thrust plate 40, and after the lubricating oil 15 flows through the through hole 41 of the thrust plate 40, the crankshaft The lubricating oil 15 flows through the 11 flow passages 17.

  A groove portion 42 is formed in the thrust plate 40 in a sliding region between the crankshaft 11 and the thrust plate 40. The sliding area between the crankshaft 11 and the thrust plate 40 is an area where the lower end surface of the crankshaft 11 and the upper surface of the thrust plate 40 face each other. Below, although the case where the groove part 42 is formed only in the thrust plate 40 is demonstrated, this invention is not limited to this example. For example, the groove portion according to the present invention may be formed only on the crankshaft 11 in the sliding region between the crankshaft 11 and the thrust plate 40 or may be formed on both the crankshaft 11 and the thrust plate 40. Good.

  The groove 42 is formed in a concave shape in the thrust plate 40, and the lubricating oil 15 is supplied from the through hole 41. That is, the groove 42 communicates with the flow passage 51 formed in the suction pipe 16 and the flow passage 17 formed in the crankshaft 11 on the through hole 41 side of the thrust plate 40.

  By forming a minute recess in the thrust plate 40, a dynamic pressure is generated in the sliding region, and the floating due to the oil film pressure occurs. As a result, friction loss generated between the lower end surface of the crankshaft 11 and the upper surface of the thrust plate 40 can be reduced.

  The depth of the groove 42 is, for example, 5 μm or more and 10 μm or less. The depth of the groove 42 is determined according to the ratio (Λ value) of the oil film thickness generated between the lower end surface of the crankshaft 11 and the upper surface of the thrust plate 40 and the combined roughness of the sliding surface. When the Λ value (= oil film thickness / sliding surface combined roughness) is a value larger than 3, it is known that the oil film will surely lift up, and the oil film causes the crankshaft 11 to move to the thrust plate 40. Can be raised against. Regardless of the rotational speed of the crankshaft 11, if the depth of the groove 42 is too shallow or too deep, the Λ value will be low. That is, there is an optimum depth of the groove portion 42 at which the Λ value becomes a maximum value regardless of the rotational speed of the crankshaft 11.

  In addition, when the rotation speed of the crankshaft 11 is low, if the depth of the groove portion 42 is increased, the Λ value tends to be 3 or less. On the other hand, when the rotation speed of the crankshaft 11 is high, the depth of the groove portion 42 is increased. However, the Λ value can maintain a value greater than 3. That is, when the rotation speed of the crankshaft 11 is low, the range of the depth of the groove 42 that can be larger than 3 is narrower than when the rotation speed of the crankshaft 11 is high.

  According to the inventors, in the compressor, the crankshaft 11 has a diameter of 10 mm to 40 mm, the rotation speed of the crankshaft 11 is 10 rps to 140 rps, the lubricating oil viscosity is 2 mPa · s to 30 mPa · s, the crankshaft 11 and the rotor As a result of an analysis for calculating the Λ value when the total weight of 9 is set to 10N or more and 100N or less, it is found that the depth range of the groove portion 42 of the thrust plate 40 is preferably 5 μm or more and 10 μm or less. It was.

  Further, based on a demonstration experiment by the inventors, when the rotation speed of the crankshaft 11 is relatively low, for example, less than 40 rps, the depth of the groove 42 is desirably 5 μm, and the rotation speed of the crankshaft 11 is relatively high. In some cases, for example, at 90 rps or more, it was found that the depth of the groove 42 is preferably 10 μm. This shows the same tendency as the above-described analysis for calculating the Λ value.

  For example, FIG. 8 shows a graph when the overall efficiency of the compressor is set to 1 when a thrust plate without the groove 42 is provided during the cooling intermediate operation. As a result, at the time of intermediate cooling operation where the rotational speed of the crankshaft 11 is relatively low, the efficiency of the groove 42 is 5 μm higher than that of the groove 42 is 10 μm. On the other hand, at the time of heating rated operation where the rotation speed of the crankshaft 11 is relatively high, the efficiency is higher when the depth of the groove 42 is 10 μm than when the depth of the groove 42 is 5 μm.

  In other words, when evaluating the energy-saving performance of the air conditioner with APF (Annual Performance Factor), which has a higher weight during intermediate operation than during rated operation, the depth of the groove 42 should be 5 μm rather than 10 μm. It is desirable to set.

  The outer end 42 a in the radial direction of the groove 42 is located inside the outermost peripheral portion in the sliding region of the crankshaft 11 and the thrust plate 40. That is, the groove part 42 does not communicate from the inner side in the radial direction to the outermost peripheral part in the sliding region. Therefore, the lubricating oil 15 supplied from the through hole 41 to the groove 42 is likely to stay in the groove 42 and is less likely to leak to the outer peripheral side than the sliding region.

  Unlike the present embodiment, when the groove 42 is formed over the entire radial direction of the sliding region, that is, through the inner peripheral portion to the outer peripheral portion, the lubricating oil 15 flows out of the distribution system, and the journal The amount of the lubricating oil 15 supplied to the bearing and the compression mechanism is reduced. On the other hand, in the case of the present embodiment, since the groove portion 42 does not communicate from the radially inner side to the outermost peripheral portion in the sliding region, the journal bearing, the compression mechanism, etc. without reducing the amount of the lubricating oil 15. Sufficient lubricating oil 15 can be supplied.

  The outer end portion 42a in the radial direction of the groove portion 42 is a position on the inner side of about 10% of the radius of the outermost peripheral portion in the above-described sliding region. Thereby, it is possible to reliably prevent the lubricating oil 15 supplied to the groove 42 from leaking from the inner peripheral side to the outer peripheral side of the sliding region.

  The outer end portion 42a in the radial direction of the groove portion 42 is outside the intermediate position between the innermost peripheral portion and the outermost peripheral portion in the sliding region. Thereby, the lubricating oil 15 can be supplied to the outer side by the groove part 42 rather than the intermediate position between the innermost peripheral part and the outermost peripheral part in the sliding region.

The above relationship is expressed by the following formula.
r _ave (= (r _out −r _in ) / 2) <r <0.9 × r _out
Here, r is the radius of the outer end 42a of the groove 42, that is, the radius of the boundary where the step is formed, r _out is the radius of the outermost peripheral portion _in the sliding region, and r _in is the outermost portion of the sliding region. The radius of the inner periphery.

  In addition, the area of the region where the groove 42 is formed in the sliding region is 50% or more and 80% or less with respect to the entire area inside the outer end 42a in the radial direction of the groove 42 in the sliding region. It is desirable.

The area of the sliding area where the groove 42 is formed is Astep, and the area of the sliding area inside the outer edge 42a in the radial direction of the groove 42 and not the groove 42 (land area) is Aland. Then, it is expressed by the following formula.
0.5 ≦ Astep / (Astep + Aland) ≦ 0.8

  By satisfying this condition, dynamic pressure is generated in the sliding region, and levitation due to oil film pressure is likely to occur. In the example shown in FIG. 3, the groove portion 42 has a fan shape with a central angle of 60 °, and is provided at four locations every 90 ° in the circumferential direction. Therefore, Astep / (Astep + Aland) is 0.67. .

  Further, as shown in FIG. 2, a tapered surface 43 is formed in a portion of the crankshaft 11 that faces the inner portion in the radial direction of the groove portion 42. Thus, the tapered surface 43 is formed on the side where the lubricating oil 15 is introduced in the groove portion 42, so that the inner side in the radial direction of the groove portion 42 becomes wider in the height direction, and lubricates the inside of the groove portion 42. Oil 15 is easily supplied. In addition, in this invention, a taper surface is not restricted to the case where it forms in the part facing a groove part, You may provide in the inner peripheral part of a groove part. Also in this case, the lubricating oil 15 is easily supplied to the inside of the groove.

  The cross-sectional shape cut along the circumferential direction of the groove portion 42 has, for example, a step shape (FIG. 4), a taper shape (FIG. 5), or a dimple shape (FIG. 6). That is, a general shape used in a thrust bearing or the like can be applied to this embodiment.

  2 and 7, a pump rotor 45 of the positive displacement oil pump 14 is provided outside the sliding region. Since the lower surface of the crankshaft 11 is the same surface as the lower surface of the pump rotor 45, even if the lubricating oil 15 leaks slightly from the sliding region of the crankshaft 11 and the thrust plate 40, the lubricating oil 15 The space between the lower surface of the pump rotor 45 and the upper surface of the thrust plate can be lubricated. In that case, the efficiency of the positive displacement oil pump 14 can be improved.

  As described above, according to the present embodiment, the through hole 41 is formed in the thrust plate 40, and the flow passage 17 is formed in the crankshaft 11 placed on the upper surface of the thrust plate 40. After the lubricating oil 15 flows through the hole 41, the lubricating oil 15 flows through the flow passage 17 of the crankshaft 11. In the sliding region between the crankshaft 11 and the thrust plate 40, a groove portion 42 is formed in the thrust plate 40, and the lubricating oil 15 is supplied from the through hole 41 to the groove portion 42. As a result, the lubricating oil 15 is filled in the sliding region between the crankshaft 11 and the thrust plate 40 to form an oil film, and friction loss can be reduced. Further, since the outer end 42a in the radial direction of the groove portion 42 is located on the inner side of the outermost peripheral portion in the above-described sliding region, the lubricating oil 15 supplied to the groove portion 42 is contained in the sliding region. Difficult to leak from the circumferential side to the outer circumferential side.

  Therefore, not only the friction loss can be reduced, but also sufficient lubricating oil 15 can be supplied to the journal bearing and the compression mechanism without reducing the amount of the lubricating oil 15. As a result, it is possible to improve the efficiency and reliability of the compressor.

  In addition, although embodiment mentioned above demonstrated the case of the scroll type compressor, this invention is not limited to this example. For example, the present invention can be applied to a rotary compressor and a reciprocating compressor. Furthermore, the fluid machine according to the present invention is not limited to a compressor, and can be applied to an expander.

Hereinafter, a case where the thrust plate 40 according to the present embodiment is applied to a rotary compressor will be described.
FIG. 9 is a longitudinal sectional view showing a configuration example of a sealed single cylinder as an example of a rotary compressor. In the following, an embodiment applied to a single-cylinder rotary compressor will be described for the sake of convenience, but the present invention can be similarly applied not only to a two-cylinder rotary compressor but also to a rotary compression mechanism of a compressor having a plurality of different compression mechanisms. Needless to say.

The hermetic rotary compressor 61 includes a housing 62 having a hermetic structure. The housing 62 includes a cylindrical center housing 62A, an upper housing 62B that seals the upper part of the center housing 62A, and a lower housing 62C that seals the lower part of the center housing 62A. An electric motor 64 including a stator 65 and a rotor 66 is fixedly installed as a drive source on the upper side in the center housing 62A.
A crankshaft (rotary shaft) 67 is integrally coupled to the rotor 66.

  A single-cylinder rotary compression mechanism 63 is installed below the electric motor 64. The rotary compression mechanism 63 includes a cylinder body 69 in which a cylinder chamber 68 is formed, an upper bearing 70 and a lower bearing 71 that are fixedly installed on the upper and lower portions of the cylinder body 69 and seal the upper and lower portions of the cylinder chamber 68. A rotor 72 that is fitted to the eccentric portion 67A of the crankshaft 67 and rotates on the inner peripheral surface of the cylinder chamber 68; a blade and a blade pressing spring (not shown) that partitions the inside of the cylinder chamber 68 into a suction side and a discharge side; It is set as the structure provided with.

  The rotary compression mechanism 63 is fixedly installed by either the cylinder main body 69 or the upper bearing 70 being fixed to the inner peripheral surface of the center housing 62A by plug welding or caulking at a plurality of locations on the circumference. Can be integrally assembled to the fixedly installed member.

The rotary compression mechanism 63 sucks the low-pressure refrigerant gas of the compressed fluid into the cylinder chamber 68 from the accumulator 74 provided integrally with the rotary compressor 61 via the suction pipe 73, and this refrigerant gas is rotated by the rotor 72. , And then discharged into the upper muffler chamber 75 and the lower muffler chamber 76 formed using the upper bearing 70 and the lower bearing 71. The compressed high-pressure refrigerant gas joins in the upper muffler chamber 75 and is then discharged into the center housing 62A. In addition, the inside of the upper muffler chamber 75 and the lower muffler chamber 76 and the inside of the center housing 62A are in a state where there is substantially no pressure difference.
This high-pressure refrigerant gas flows through a gas passage hole (not shown) provided around the electric motor 64 and is guided to the upper space of the electric motor 64, and further, a rotary compressor is connected via a discharge pipe 77. It is sent out to the outside of 61, ie, the refrigerating cycle side.

  The rotary compression mechanism 63 described above includes a cylinder body 69, an upper bearing 70 and a lower bearing 71 disposed above and below the cylinder body 69, and a lower muffler 7A that forms a lower muffler chamber 76 below the lower bearing 71. The bolts 78 that penetrate in the axial direction of the crankshaft 67 are integrated by screwing.

  Both the upper muffler chamber 75 and the lower muffler chamber 76 are portions where there is no pressure difference between inside and outside. However, in the illustrated configuration example, since the sealing performance against the lubricating oil 15 is required, only the lower muffler 76A is fastened by the bolt 78, but both the upper muffler 75A and the lower muffler 76A are fastened by the bolt 78. There is no particular limitation, such as a structure to be used, or a structure in which only one of them is fastened with a bolt 78.

  Here, the thrust plate 40 is a plate-like member provided in contact with the lower end surface of the crankshaft 67. The thrust plate 40 has a thickness of about 1 mm, for example. The thrust plate 40 is installed between the lower surface of the lower journal bearing 13 and the upper surface of the lower muffler 76A.

  A centrifugal oil pump (not shown) is provided at the lower end of the crankshaft 67, and the lubricating oil 15 filled in the bottom of the housing 62 is sucked in via the centrifugal oil pump, It discharges to a flow passage (not shown) drilled along the axial direction. The lubricating oil 15 can be supplied to parts requiring lubrication, such as the upper bearing 70 and the lower bearing 71, through the flow passage.

  The thrust plate 40 is formed with a groove 42 in a sliding region between the crankshaft 67 and the thrust plate 40. The groove 42 is formed in a concave shape in the thrust plate 40, and the lubricating oil 15 is supplied from the through hole 41. That is, the groove 42 communicates with a centrifugal oil pump and a flow passage formed in the crankshaft 67. In the case of the rotary compressor 61, a thrust plate 40 having the same configuration as that described in the scroll compressor 1 is provided. The sliding region between the crankshaft 67 and the thrust plate 40 is filled with the lubricating oil 15 to form an oil film, and friction loss can be reduced. Further, since the outer end 42a in the radial direction of the groove portion 42 is located on the inner side of the outermost peripheral portion in the above-described sliding region, the lubricating oil 15 supplied to the groove portion 42 is contained in the sliding region. Difficult to leak from the circumferential side to the outer circumferential side.

  Therefore, not only the friction loss can be reduced, but also sufficient lubricating oil 15 can be supplied to the journal bearing and the compression mechanism without reducing the amount of the lubricating oil 15. As a result, it is possible to improve the efficiency and reliability of the compressor. Detailed configuration and operational effects are omitted because they are the same as those described in the scroll compressor 1.

1: Sealed scroll compressor 2: Sealed housing 3: Discharge cover 4: Upper cover 5: Discharge chamber 6: Upper bearing member 6A: Journal bearing portion 6B: Thrust bearing portion 7: Scroll compression mechanism 7A: Lower muffler 8: Stator 8A: Stator winding 9: Rotor 10: Electric motor 11: Crank shaft 12: Crank pin 13: Lower journal bearing 14: Positive displacement oil pump 15: Lubricating oil 16: Suction pipe 17: Flow passage 18: Fixed scroll 18A: End Plate 18B: Spiral wrap 19: Orbiting scroll 19A: End plate 19B: Spiral wrap 19C: Bearing boss 20: Compression chamber 21: Rotation prevention mechanism 22: Drive bush 24: Discharge port 25: Tip seal 26: Tip seal 27: Suction piping 28: Suction port 29: Discharge valve 30: Outlet piping 40: Thrust plate 41: Through hole 42: Groove 42a: Outer end 45: Pump rotor 51: Flow passage 61: Rotary compressor 62: Housing 62A: Center housing 62B: Upper housing 62C: Lower housing 63: Rotary compression Mechanism 64: Electric motor 65: Stator 66: Rotor 67: Crankshaft 67A: Eccentric portion 68: Cylinder chamber 69: Cylinder body 70: Upper bearing 71: Lower bearing 72: Rotor 73: Suction pipe 74: Accumulator 75: Upper muffler chamber 75A: Upper muffler 76: Lower muffler chamber 76A: Lower muffler 77: Discharge piping 78: Bolt

Claims (5)

An annular plate having a through-hole through which lubricating oil flows;
A crankshaft that is placed on the upper surface of the plate portion and in which a flow passage is formed in which the lubricating oil that has passed through the through hole of the plate portion flows;
With
In the sliding region of the crankshaft and the plate portion, at least one of the crankshaft and the plate portion is formed with a concave groove portion to which the lubricating oil is supplied from the through hole,
A fluid machine in which a radially outer end portion of the groove portion is located on an inner side of an outermost peripheral portion in the sliding region.   2. The fluid machine according to claim 1, wherein an outer end portion in a radial direction of the groove portion is outside an intermediate position between an innermost peripheral portion and the outermost peripheral portion in the sliding region.   The area of the region where the groove is formed in the sliding region is 50% or more and 80% or less with respect to the total area inside the outer end in the radial direction of the groove in the sliding region. Item 3. The fluid machine according to Item 1 or 2.   The taper surface is formed in the inner part of the radial direction of the said groove part, or the part which opposes the inner part of the radial direction of the said groove part in the said crankshaft or the said plate part. The fluid machine described in 1.   The fluid machine according to claim 1, wherein the groove has a step shape, a taper shape, or a dimple shape.

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