CN108350869B - Fluid machinery - Google Patents

Fluid machinery Download PDF

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Publication number
CN108350869B
CN108350869B CN201780003768.6A CN201780003768A CN108350869B CN 108350869 B CN108350869 B CN 108350869B CN 201780003768 A CN201780003768 A CN 201780003768A CN 108350869 B CN108350869 B CN 108350869B
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China
Prior art keywords
crankshaft
groove
groove portion
sliding region
lubricating oil
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CN201780003768.6A
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Chinese (zh)
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CN108350869A (en
Inventor
佐藤创
木全央幸
高须洋悟
高桥一树
馆石太一
山下拓马
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0261—Hermetic compressors with an auxiliary oil pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components

Abstract

The invention provides a fluid machine. In the present invention, a hermetic scroll compressor includes: an annular thrust plate (40) having a through-hole (41) through which lubricating oil flows; and a crankshaft (11) that is placed on the upper surface of the thrust plate (40), and that has a flow path (17) formed therein through which lubricating oil that has passed through the through-hole (41) of the thrust plate (40) flows, wherein in a sliding region between the crankshaft (11) and the thrust plate (40), a concave groove portion (42) is formed in at least either the crankshaft (11) or the thrust plate (40) in which lubricating oil is supplied from the through-hole (41), and wherein an outer end portion (42a) of the groove portion (42) in the radial direction is located more inward than the outermost peripheral portion in the sliding region.

Description

Fluid machinery
Technical Field
The present invention relates to a fluid machine.
Background
The vertical hermetic compressor includes a compression mechanism and a motor (electric motor) for driving the compression mechanism in a housing, and the compression mechanism and a motor rotor are combined on the same crankshaft. The crankshaft is provided so that the axial direction thereof is the plumb direction, and a thrust load is applied to the lower end portion of the crankshaft. Here, the thrust load is the self weight of the crankshaft and the motor rotor and the axial force of the magnetic force generated during operation.
When the thrust load is supported, a friction loss occurs in the lower end portion of the crankshaft. Therefore, as described in patent documents 1 and 2 below, a thrust bearing is provided in contact with the lower end portion of the crankshaft.
Prior art documents
Patent document
Patent document 1: japanese Kokai publication Sho-62-78389
Patent document 2: japanese patent laid-open publication No. 2014-152747
Disclosure of Invention
Technical problem to be solved by the invention
Patent documents 1 and 2 describe that lubrication performance of a thrust bearing is improved by supplying lubricating oil to the thrust bearing. In the sliding region between the lower end portion of the crankshaft and the thrust bearing, an oil supply groove for supplying lubricating oil to the thrust bearing is formed throughout the entire radial direction, that is, from the inner peripheral portion to the outer peripheral portion.
An oil passage inside the compressor is formed in the center of the crankshaft, and branches into journal bearings or compression mechanisms that support radial loads. The lubricating oil is supplied from a pump provided around the lower end portion of the crankshaft to an oil passage provided in the center of the crankshaft, and then supplied to the journal bearing or the compression mechanism via the oil passage.
Therefore, when the lubricant oil pressurized by the pump is also supplied to the thrust bearing, if the oil supply groove formed in the sliding region between the lower end portion of the crankshaft and the thrust bearing is formed over the entire radial direction, the lubricant oil passes through the oil supply groove. As a result, a large amount of the lubricant oil pressurized in the pump flows out from the oil supply groove, and the amount of the lubricant 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 an object thereof is to provide a fluid machine capable of reducing friction loss generated at a lower end portion of a crankshaft and reliably supplying lubricating oil to other sliding portions.
Means for solving the technical problem
In order to solve the above problem, the fluid machine of the present invention employs the following method.
That is, a fluid machine according to an aspect of the present invention includes: an annular plate portion having a through-hole through which lubricating oil flows; and a crankshaft that is placed on an upper surface of the plate portion and that has a flow passage formed therein through which the lubricating oil that has passed through the through-hole of the plate portion flows, wherein a concave groove portion that supplies the lubricating oil from the through-hole is formed in at least one of the crankshaft and the plate portion in a sliding region between the crankshaft and the plate portion, and an outer end portion in a radial direction of the groove portion is located more inward than an outermost peripheral portion in the sliding region.
According to this configuration, the plate portion is formed with the through-hole, the flow passage is formed in the interior of the crankshaft placed on the upper surface of the plate portion, and the lubricating oil flows through the through-hole of the plate portion and then flows through the flow passage of the crankshaft. In the sliding region between the crankshaft and the plate portion, a groove portion is formed in at least either 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 lubricating oil fills the sliding region between the crankshaft and the plate portion to form an oil film, and friction loss can be reduced. Further, since the radially outer end of the groove is located inward of the outermost peripheral portion of the sliding region, the lubricant supplied to the groove hardly leaks from the inner peripheral side to the outer peripheral side of the sliding region.
For example, the outer end of the groove in the radial direction is located at a position that is about 10% inside the radius of the outermost peripheral portion in the sliding region.
In the above aspect, an outer end of the groove portion in the radial direction may be located further outward than an intermediate position between an innermost peripheral portion and the outermost peripheral portion in the sliding region.
According to this configuration, the lubricating oil can be supplied to the outer side of the intermediate position between the innermost peripheral portion and the outermost peripheral portion in the sliding region through the groove portion.
In the above aspect, an area of a region in the sliding region in which the groove portion is formed may be 50% or more and 80% or less with respect to a total area of the sliding region that is located inward of an outer end of the groove portion in the radial direction.
According to this structure, the lubricating oil supplied to the groove portion facilitates formation of an oil film in the sliding region between the crankshaft and the plate portion.
In the above aspect, a tapered surface may be formed at a radially inner portion of the groove portion, or at a portion of the crankshaft or the plate portion that faces 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 radially inner portion is tapered, the radially inner portion of the groove portion becomes wider in the height direction, and the lubricating oil is easily supplied to the inside of the groove portion.
In the above aspect, the groove portion may have a step shape, a taper shape, or a recess shape.
Effects of the invention
According to the present invention, it is possible to reduce the friction loss generated at the lower end portion of the crankshaft and to reliably supply the lubricating oil to the other sliding portions.
Drawings
Fig. 1 is a longitudinal sectional view showing a scroll compressor according to an embodiment of the present invention.
Fig. 2 is a partially enlarged longitudinal sectional view showing a thrust plate of a scroll compressor according to an embodiment of the present invention.
Fig. 3 is a plan view showing a thrust plate of a scroll compressor according to an embodiment of the present invention.
Fig. 4 is a vertical cross-sectional view showing an example of a groove formed in a thrust plate of a scroll compressor according to an embodiment of the present invention.
Fig. 5 is a vertical cross-sectional view showing an example of a groove formed in a thrust plate of a scroll compressor according to an embodiment of the present invention.
Fig. 6 is a vertical cross-sectional view showing an example of a groove formed in a thrust plate of a scroll compressor according to an embodiment of the present invention.
Fig. 7 is a longitudinal sectional view showing a lower end portion of a crankshaft, a thrust plate, and an intake pipe of a scroll compressor according to an embodiment of the present invention.
Fig. 8 is a graph showing the efficiency of the air conditioner for each operation mode or performance evaluation.
Fig. 9 is a longitudinal sectional view illustrating a rotary compressor according to an embodiment of the present invention.
Detailed Description
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 vertically long cylindrical hermetic casing 2 whose bottom is sealed by a lower cover. The upper portion of the sealed casing 2 is sealed by a discharge cover 3 and an upper cover 4, and a discharge chamber 5 for discharging compressed high-pressure gas is formed between the discharge cover 3 and the upper cover 4.
An upper bearing member (frame member) 6 is fixedly provided in an upper portion of the sealed casing 2, a scroll compression mechanism 7 is assembled via the upper bearing member 6, and an electric motor 10 including a stator 8 and a rotor 9 is provided in a lower portion thereof. The electric motor 10 is assembled by fixing the stator 8 to the sealed case 2, and the crankshaft 11 is fixed to the rotor 9.
A crank pin 12 having an eccentric axis of a predetermined size is provided at the upper end of the crankshaft 11, and the crank pin 12 is connected to the scroll compression mechanism 7, whereby the scroll compression mechanism 7 can be driven by the electric motor 10. The crankshaft 11 is rotatably supported at an upper portion thereof by a journal bearing portion 6A of the upper bearing member 6, and at a lower end portion thereof by a lower journal bearing 13 provided at a lower portion of the hermetic case 2.
A displacement type oil feed pump 14 is provided between the lower journal bearing 13 and the lower end portion of the crankshaft 11, and is configured to suck the lubricating oil 15 filled in the bottom portion of the sealed housing 2 through a suction pipe 16 and discharge the lubricating oil to a flow passage 17 axially penetrating the crankshaft 11. The lubricating oil 15 can be supplied to the parts requiring 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: a fixed scroll 18 which is fixed to the upper bearing member 6, with the upper bearing member 6 being one of the constituent members; a revolving scroll 19 slidably supported by the thrust bearing portion 6B of the upper bearing member 6 and meshing with the fixed scroll 18 to form a compression chamber 20; a rotation suppressing mechanism 21 such as an oldham ring interposed between the upper bearing member 6 and the orbiting scroll 19, for preventing rotation of the orbiting scroll 19 and allowing revolution and revolution movement; and an actuator bush 22 and a rotary bearing (needle bearing) 23 which are provided between the crank pin 12 of the crankshaft 11 and a bearing boss 19C provided on the back surface of the orbiting scroll 19 and transmit the rotational force of the crankshaft 11 to the orbiting scroll 19, and in the scroll compression mechanism 7, the center portion of the end plate of the fixed scroll 18 is provided on the upper bearing member 6 in a state of being connected to the discharge cover 3.
The fixed scroll 18 includes an end plate 18A and a spiral scroll 18B vertically provided on the end plate 18A, and has a structure in which a discharge port 24 is provided at the center of the end plate 18A, and a sheet seal 25 is provided on the spiral tip surface of the spiral scroll 18B. The orbiting scroll 19 includes an end plate 19A and a spiral wrap 19B vertically provided on the end plate 19A, and has a structure in which a bearing boss 19C is provided on the back surface of the end plate 19A, and a sheet seal 26 is provided on the wrap tip surface of the spiral wrap 19B.
The scroll compression mechanism 7 sucks the refrigerant gas sucked into the hermetic casing 2 through a suction pipe 27 opened at a position facing the stator winding 8A of the electric motor 10 from a suction pipe 28 opened in the hermetic casing 2 into the compression chamber 20, and compresses the refrigerant gas into high-temperature and high-pressure gas. The compressed gas is discharged into the discharge chamber 5 through a discharge valve 29 provided in the discharge cover 3 and a discharge 24 provided in the center portion of the fixed scroll 18, and is further discharged to the outside of the compressor through a discharge pipe 30 connected to the discharge chamber 5.
The thrust plate 40 provided in the compressor according to the present embodiment will be described below with reference to fig. 2 to 7.
The thrust plate 40 is a plate-like member provided so as to be in surface contact with the lower end surface of the crankshaft 11. The thickness of the thrust plate 40 is, for example, about 1 mm. The thrust plate 40 is disposed between the lower surface of the lower journal bearing 13 and the upper surface of the suction duct 16.
The thrust plate 40 has a through hole 41 through which the lubricating oil 15 flows. The flow passage 51 formed in the intake duct 16 communicates with the flow passage 17 formed in the crankshaft 11 through the through-hole 41. As a result, as shown in fig. 7, the lubricant oil 15 having passed through the intake duct 16 passes through the through-hole 41 of the thrust plate 40, and after passing through the through-hole 41 of the thrust plate 40, the lubricant oil 15 passes through the flow passage 17 of the crankshaft 11.
In the thrust plate 40, a groove portion 42 is formed in a sliding region between the crankshaft 11 and the thrust plate 40. The sliding region between the crankshaft 11 and the thrust plate 40 is a region where the lower end surface of the crankshaft 11 and the upper surface of the thrust plate 40 face each other. Hereinafter, a case where the groove 42 is formed only in the thrust plate 40 will be described, but the present invention is not limited to this example. For example, the groove portion according to the present invention may be formed only in the crankshaft 11 in the sliding region between the crankshaft 11 and the thrust plate 40, or may be formed in both the crankshaft 11 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 the flow passage 51 formed in the intake duct 16 or the flow passage 17 formed in the crankshaft 11 on the side of the through hole 41 of the thrust plate 40.
By forming minute recesses in the thrust plate 40, dynamic pressure is generated in the sliding region, and levitation based on oil film pressure is generated. As a result, the 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 grooves 42 is, for example, 5 μm or more and 10 μm or less. The depth of the groove portion 42 is determined in accordance with the ratio (Λ value) of the thickness of the oil film generated between the lower end surface of the crankshaft 11 and the upper surface of the thrust plate 40 and the overall roughness of the sliding surface. It is known that if the Λ value (i.e., the integrated roughness of the oil film thickness/sliding surface) is a value greater than 3, it is determined that the oil film is generated and the crankshaft 11 can be suspended with respect to the thrust plate 40 by the oil film. When the depth of the groove 42 is too shallow or too deep regardless of the rotation speed of the crankshaft 11, the Λ value becomes a low value. That is, the optimum groove portion 42 has the maximum Λ value at both high and low rotation speeds of the crankshaft 11.
Further, when the rotation speed of the crankshaft 11 is low, the Λ value is likely to be 3 or less if the depth of the groove portion 42 is made deep, while when the rotation speed of the crankshaft 11 is high, the Λ value can be maintained to be greater than 3 even if the depth of the groove portion 42 is made deep. That is, when the rotation speed of the crankshaft 11 is low, the depth range of the groove portion 42 that can be set to a value greater than 3 is narrower than when the rotation speed of the crankshaft 11 is high.
The inventors have found that, in a compressor, when the diameter of a crankshaft 11 is set to 10mm or more and 40mm or less, the rotational speed of the crankshaft 11 is set to 10rps or more and 140rps or less, the viscosity of a lubricating oil is set to 2mPa · s or more and 30mPa · s or less, and the total self-weight force of the crankshaft 11 and a rotor 9 is set to 10N or more and 100N or less, analysis for calculating the Λ value is performed, and the range of the depth of a groove portion 42 of a thrust plate 40 is preferably 5 μm or more and 10 μm or less.
The inventors have also found, based on demonstration experiments, that the depth of the groove 42 is preferably 5 μm when the rotation speed of the crankshaft 11 is low, for example, less than 40rps, and that the depth of the groove 42 is preferably 10 μm when the rotation speed of the crankshaft 11 is high, for example, 90rps or more. This shows the same trend as the above analysis to calculate the Λ value.
For example, fig. 8 shows a graph in which the overall efficiency of the compressor is 1 in the case where the thrust plate without the groove portion 42 is provided in the cooling intermediate operation. As a result, in the cooling intermediate operation in which the rotation speed of the crankshaft 11 is low, the efficiency is higher when the depth of the groove 42 is set to 5 μm than when the depth of the groove 42 is set to 10 μm. On the other hand, in the heating rated operation in which the rotation speed of the crankshaft 11 is 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.
That is, when the energy saving performance of the air conditioner is evaluated by an APF (Annual performance factor) having a higher weight value at the time of the intermediate operation than that at the time of the rated operation, it is preferable to set the depth of the groove 42 to 5 μm rather than 10 μm.
The radial outer end 42a of the groove 42 is located inward of the outermost peripheral portion in the sliding region between the crankshaft 11 and the thrust plate 40. That is, the groove 42 does not communicate from the inside in the radial direction to the outermost peripheral portion in the sliding region. Therefore, the lubricating oil 15 supplied from the through-hole 41 to the groove portion 42 is likely to stay in the groove portion 42, and is less likely to leak to the outer peripheral side than the sliding region.
Unlike the present embodiment, when the groove portion 42 is formed throughout the entire radial direction of the sliding region, that is, from the inner peripheral portion to the outer peripheral portion, the lubricating oil 15 flows out from the flow system, and the amount of the lubricating oil 15 supplied to the journal bearing, the compression mechanism, or the like decreases. In contrast, in the case of the present embodiment, since the groove portion 42 does not communicate from the inside in the radial direction to the outermost peripheral portion in the sliding region, sufficient lubricant oil 15 can be supplied to the journal bearing, the compression mechanism, and the like without reducing the amount of the lubricant oil 15.
The outer end 42a of the groove 42 in the radial direction is located at a position inward of about 10% of the radius of the outermost peripheral portion in the sliding region. This can reliably prevent the lubricant oil 15 supplied to the groove portion 42 from leaking from the inner circumferential side to the outer circumferential side of the sliding region.
The outer end 42a of the groove 42 in the radial direction is located further outward than 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 than the intermediate position between the innermost peripheral portion and the outermost peripheral portion in the sliding region through the groove portion 42.
When the above relationship is expressed by the formula, the following is obtained.
rave(＝(rout-rin)/2)＜r＜0.9×rout
Where r is the radius of the outer end 42a of the groove 42, i.e., the boundary portion where the step is formed, routIs the radius of the outermost peripheral part in the sliding region, rinIs the radius of the innermost circumference in the sliding region.
The area of the region in which the groove portion 42 is formed in the sliding region is preferably 50% to 80% of the total area of the sliding region that is located inward of the outer end 42a of the groove portion 42 in the radial direction.
The area of the region in the sliding region where the groove 42 is formed is astrep, and the area of the region (land region) in the sliding region that is located more inward than the outer end 42a of the groove 42 in the radial direction and is not the groove 42 is Aland, which can be expressed by the following expression.
0.5≤Astep/(Astep+Aland)≤0.8
By satisfying this condition, dynamic pressure is generated in the sliding region, and the levitation due to the oil film pressure is easily generated. In the example shown in fig. 3, since the groove portion 42 has a fan shape with a central angle of 60 ° and 4 positions are provided every 90 ° in the circumferential direction, Astep/(Astep + Aland) is 0.67.
As shown in fig. 2, a tapered surface 43 is formed at a portion of the crankshaft 11 that faces the radially inner portion of the groove 42. In this way, the tapered surface 43 is formed on the side of the groove portion 42 into which the lubricant 15 is introduced, so that the radially inner side of the groove portion 42 is widened in the height direction, and the lubricant 15 is easily supplied to the inside of the groove portion 42. In the present invention, the tapered surface is not limited to the portion facing the groove portion, and may be provided on the inner peripheral portion of the groove portion. In this case, the lubricating oil 15 is also easily supplied to the inside of the groove portion.
The cross-sectional shape cut in the circumferential direction of the groove portion 42 has, for example, a step shape (fig. 4), a tapered shape (fig. 5), or a recessed shape (fig. 6). That is, a general shape used for a thrust bearing or the like can be applied to the present embodiment.
As shown in fig. 2 or 7, a pump rotor 45 of the positive displacement type fuel feed pump 14 is provided outside the sliding region. Since the lower surface of the crankshaft 11 and the lower surface of the pump rotor 45 are flush with each other, even if a slight amount of the lubricant 15 leaks from the sliding region between the crankshaft 11 and the thrust plate 40, the lubricant 15 can lubricate the gap between the lower surface of the pump rotor 45 and the upper surface of the thrust plate. In this case, the efficiency of the displacement type oil feed pump 14 can be improved.
As described above, according to the present embodiment, the through-hole 41 is formed in the thrust plate 40, the flow passage 17 is formed inside the crankshaft 11 placed on the upper surface of the thrust plate 40, and the lubricating oil 15 flows through the through-hole 41 of the thrust plate 40 and then 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 42 is formed in the thrust plate 40, and the lubricating oil 15 is supplied from the through-hole 41 to the groove 42. As a result, the lubricating oil 15 fills the sliding region between the crankshaft 11 and the thrust plate 40 to form an oil film, thereby reducing the friction loss. Further, since the radially outer end 42a of the groove 42 is located inward of the outermost peripheral portion of the sliding region, the lubricant oil 15 supplied to the groove 42 is less likely to leak from the inner peripheral side to the outer peripheral side of the sliding region.
Therefore, not only the friction loss can be reduced, but also sufficient lubricating oil 15 can be supplied to the journal bearing, the compression mechanism, and the like without reducing the amount of lubricating oil 15. As a result, the efficiency and reliability of the compressor can be improved.
In the above embodiment, the case of the scroll compressor has been described, but the present invention is not limited to this example. For example, the present invention can be applied to a rotary compressor and a reciprocating compressor. The fluid machine according to the present invention is not limited to the compressor, and may 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 sealed single cylinder configuration example as an example of the rotary compressor. In addition, although the embodiment applied to the single-cylinder rotary compressor will be described below for convenience, it goes without saying that the present invention can be applied to a rotary compression mechanism of a compressor having a plurality of different compression mechanisms as well as the double-cylinder rotary compressor.
The hermetic rotary compressor 61 includes a case 62 having a hermetic structure. The housing 62 is composed of a cylindrical center housing 62A, an upper housing 62B sealing an upper portion of the center housing 62A, and a lower housing 62C sealing a lower portion of the center housing 62A. An electric motor 64 including a stator 65 and a rotor 66 is fixedly provided as a drive source on the upper side in the center case 62A.
A crankshaft (rotary shaft) 67 is integrally coupled to the rotor 66.
A single-cylinder rotary compression mechanism 63 is provided at the lower part of the electric motor 64. The rotary compression mechanism 63 includes: a cylinder body 69 formed with a cylinder chamber 68; an upper bearing 70 and a lower bearing 71, wherein the upper bearing 70 is fixedly arranged at the upper part of the cylinder main body 69, the lower bearing 71 is fixedly arranged at the lower part of the cylinder main body 69, the upper bearing 70 seals the upper part of the cylinder chamber 68, and the lower bearing 71 seals the lower part of the cylinder chamber 68; a rotor 72 fitted to the eccentric portion 67A of the crankshaft 67 and rotating on the inner circumferential surface of the cylinder chamber 68; and a vane, a vane pressing spring, and the like, which are not shown, for partitioning the inside of the cylinder chamber 68 into a suction side and a discharge side.
The rotary compression mechanism 63 is fixedly provided to the inner peripheral surface of the center housing 62A of the cylinder main body 69 or the upper bearing 70 by plug welding or caulking fixing at a plurality of positions on the circumference, and the other components are integrally assembled with the fixedly provided components.
The rotary compression mechanism 63 sucks a low-pressure refrigerant gas of a compressed fluid into the cylinder chamber 68 from a gas receiver chamber 74 provided integrally with the rotary compressor 61 through a suction pipe 73, compresses the refrigerant gas by rotation of a rotor 72, and then discharges the compressed refrigerant gas into an upper muffler chamber 75 and a lower muffler chamber 76 formed by an upper bearing 70 and a lower bearing 71. The high-pressure refrigerant gas thus compressed is merged in the upper muffler chamber 75 and then discharged into the center housing 62A. 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 substantially pressure-free state.
The high-pressure refrigerant gas flows through a gas passage hole (not shown) provided in the periphery of the electric motor 64, is guided to the upper space of the electric motor 64, and is further discharged to the outside of the rotary compressor 61, i.e., the refrigeration cycle side, via a discharge pipe 77.
In the rotary compression mechanism 63, the cylinder body 69, the upper bearing 70 disposed at the upper portion of the cylinder body 69, the lower bearing 71 disposed at the lower portion, and the lower muffler 7A forming the lower muffler chamber 76 below the lower bearing 71 are integrated by fastening and screwing the bolt 78 penetrating in the axial direction of the crankshaft 67.
Both the upper muffler chamber 75 and the lower muffler chamber 76 have no difference in internal and external pressure. However, in the illustrated configuration example, only the lower muffler 76A is fastened by the bolt 78 because the sealing property with respect to the lubricating oil 15 can be obtained, but the configuration in which both the upper muffler 75A and the lower muffler 76A are fastened by the bolt 78, the configuration in which only one of them is fastened by the bolt 78, or the like is not particularly limited.
Here, the thrust plate 40 is a plate-like member provided so as to be in surface contact with the lower end surface of the crankshaft 67. The thickness of the thrust plate 40 is, for example, about 1 mm. The thrust plate 40 is disposed between the lower surface of the lower journal bearing 13 and the upper surface of the lower muffler 76A.
A centrifugal oil feed pump (not shown) is provided at a lower end portion of the crankshaft 67, and the lubricating oil 15 filled in the bottom portion of the housing 62 is sucked by the centrifugal oil feed pump and discharged to a flow passage (not shown) axially penetrating the crankshaft 67. The lubricating oil 15 can be supplied to the parts requiring lubrication, such as the upper bearing 70 and the lower bearing 71, through the flow channels.
In the thrust plate 40, a groove portion 42 is formed 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 type oil feed pump or a flow passage formed in the crankshaft 67. In the case of the rotary compressor 61, a thrust plate 40 having the same structure as that described in the scroll compressor 1 is also provided. Further, the lubricating oil 15 is filled in the sliding region between the crankshaft 67 and the thrust plate 40 to form an oil film, thereby reducing the friction loss. Further, since the radially outer end 42a of the groove 42 is located inward of the outermost peripheral portion of the sliding region, the lubricant oil 15 supplied to the groove 42 is less likely to leak from the inner peripheral side to the outer peripheral side of the sliding region.
Therefore, not only the friction loss can be reduced, but also sufficient lubricating oil 15 can be supplied to the journal bearing, the compression mechanism, and the like without reducing the amount of lubricating oil 15. As a result, the efficiency and reliability of the compressor can be improved. The detailed configuration and operational effects thereof are not repeated as described in the scroll compressor 1.
Description of the symbols
1-hermetic scroll compressor, 2-hermetic casing, 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-crankshaft, 12-crank pin, 13-lower journal bearing, 14-displacement type oil-feed pump, 15-lubricating oil, 16-suction pipe, 17-circulation flow path, 18-fixed scroll, 18A-end plate, 18B-scroll, 19-revolving scroll, 19A-end plate, 19B-scroll, 19C-bearing hub, 20-compression chamber, 21-spin-inhibiting mechanism, 22-drive bushing, 24-discharge port, 25-sheet seal, 26-sheet seal, 27-suction pipe, 28-suction port, 29-discharge valve, 30-discharge pipe, 40-thrust plate, 41-through hole, 42-groove, 42A-outside end, 45-pump rotor, 51-flow path, 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-air reservoir, 75-upper muffler chamber, 75A-upper muffler, 76-lower muffler chamber, 76A-lower muffler, 77-discharge piping, 78-bolts.

Claims (5)

1. A fluid machine is provided with:
an annular plate portion having a through-hole through which lubricating oil flows; and
a crankshaft placed on an upper surface of the plate portion and having a flow passage formed therein through which the lubricating oil passes through the through-hole of the plate portion,
a concave groove portion configured to be supplied with the lubricating oil from the through-hole and to generate a buoyancy by an oil film pressure by rotation of the crankshaft is formed in at least one of the crankshaft and the plate portion in a sliding region between the crankshaft and the plate portion,
the groove portion is provided at a plurality of positions in a circumferential direction of at least one of the crankshaft and the plate portion,
the groove portion has a radially outer end located more inward than an outermost peripheral portion of the sliding region.
2. The fluid machine according to claim 1,
the groove portion has a radially outer end located further outward than an intermediate position between an innermost peripheral portion and the outermost peripheral portion in the sliding region.
3. The fluid machine according to claim 1 or 2,
the area of the region in the sliding region in which the groove portion is formed is 50% to 80% of the total area of the sliding region that is located inward of the outer end of the groove portion in the radial direction.
4. The fluid machine according to claim 1 or 2,
a tapered surface is formed at a radially inner portion of the groove portion, or at a portion of the crankshaft or the plate portion that faces the radially inner portion of the groove portion.
5. The fluid machine according to claim 1 or 2,
the groove portion has a step shape or a tapered shape.
CN201780003768.6A 2016-03-04 2017-03-01 Fluid machinery Active CN108350869B (en)

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JP2016-042113 2016-03-04
JP2016042113A JP6758867B2 (en) 2016-03-04 2016-03-04 Fluid machine
PCT/JP2017/008086 WO2017150603A1 (en) 2016-03-04 2017-03-01 Fluid machine

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Publication number Priority date Publication date Assignee Title
JP6618663B1 (en) * 2019-01-31 2019-12-11 三菱電機株式会社 Slide bearing structure and scroll compressor
JP2020165314A (en) * 2019-03-28 2020-10-08 三菱重工サーマルシステムズ株式会社 Compressor

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3182901A (en) * 1963-11-12 1965-05-11 Westinghouse Electric Corp Compressor
JPS5118486Y2 (en) * 1971-05-24 1976-05-17
US3830341A (en) * 1972-11-24 1974-08-20 Carrier Corp Lubrication system for a motor compressor unit
US3926281A (en) * 1974-03-21 1975-12-16 Tecumseh Products Co Compressor oil pump with filter
US4131396A (en) * 1977-04-07 1978-12-26 Sundstrand Corporation Hermetic compressor lubrication system with two-stage oil pump
US4325679A (en) * 1980-07-22 1982-04-20 White Consolidated Industries, Inc. Oil pump for hermetic compressor
JPS5911184U (en) * 1982-07-13 1984-01-24 ダイキン工業株式会社 Lubrication mechanism of hermetic compressor
JP5370450B2 (en) * 2011-09-28 2013-12-18 ダイキン工業株式会社 Compressor

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WO2017150603A1 (en) 2017-09-08
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EP3369931A1 (en) 2018-09-05
JP2017155718A (en) 2017-09-07
EP3369931B1 (en) 2021-03-31

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