JPS63272991A - Compressor - Google Patents

Abstract

PURPOSE:To sufficiently lubricate a sub-bearing in a compressor provided with an oil supply pump having a casing surrounding a disk mounted on the lower end of a rotary shaft, by disposing a lubricating oil discharge port on the lower end of sub-bearing, while forming a series of oil grooves on the upper surface of disk. CONSTITUTION:In an enclosed container 27 are received a motor 30 consisting of a stator 31 and a rotor 13, a rotary shaft 5 disposed below the motor 30, a compression element C provided with a roller 3, vane 2 and others and an oil supply pump P having a casing 34 surrounding a disk 61 mounted on the rotary shaft 5. Said compressor is formed on the lower end of a sub-bearing 10 provided on the lower end plate 8 in the compression element C with a lubricating oil discharge port 11 of the sub-bearing 10. Also, a series of spiral oil grooves 33 bent in the opposite direction to the rotational direction of disk 61 as they extend from the center to the outer periphery are disposed on the upper surface of disk 61. Thus, lubricating oil can be sufficiently supplied to the sub-bearing 10 supporting the rotary shaft 5.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a compressor that is used for example in refrigerators, air conditioners, etc. and has a compression element housed in a closed container. The present invention relates to a compressor that can sufficiently supply lubricating oil to a sub-bearing installed in the compressor.

[Prior Art] Conventionally, in a compressor of this type in which a compression element is housed in a closed container, supply of lubricating oil to a sub-bearing provided on a lower end plate is disclosed in, for example, Japanese Utility Model Application No. 59-86390. As described in the publication, lubricating oil sucked from the lower end of the rotating shaft is supplied to the upper part of the sub-bearing, and a "helical oil groove" provided in the sub-bearing is provided.
It flows downward and is discharged from the lower end of the sub-bearing.

Incidentally, related compressors of this type include, for example, Japanese Utility Model Application Publication No. 58-63389 and Japanese Utility Model Application No. 58-633.
90 and Utility Model Application Publication No. 59-107984.

[Problems to be Solved by the Invention] In the above-mentioned prior art, when a refueling pump is provided in which a casing surrounds a disk attached to the lower end of a rotating shaft, the pressure inside the casing increases.

No consideration was given to the fact that the flow of the lubricating oil discharged from the lower end of the sub-bearing would be impaired, and the lubricating oil would accumulate in the vicinity, making it impossible to supply sufficient lubricating oil to the sub-bearing. There was a problem with deterioration of the lubricating oil.

The present invention improves the above-mentioned problems of the prior art, and provides a refueling pump in which a disk attached to the lower end of the rotating shaft is surrounded by a casing. The object of the present invention is to provide a compressor that can sufficiently supply lubricating oil to a sub-bearing provided therein.

[Means for Solving the Problems] In order to solve the above-mentioned problems, a compressor according to the first invention has a structure including an electric motor including a stator and a rotor in a closed container that also serves as a lubricating oil reservoir; A rotating shaft having a crank and rotating integrally with the rotor.

A cylinder with a groove for vane sliding; a roller that is fitted into the crank and rotates eccentrically along the inside of the cylinder; a roller that reciprocates within the groove of the cylinder while abutting the roller, and sucks the inside of the cylinder; A vane that partitions the chamber and the compression chamber, an upper end plate that also serves as a side wall of the cylinder and is provided with a main bearing and a sub-bearing of the rotating shaft, a lower end plate, and a side plate that forms a silencer between the lower end plate, In the compressor, the compressor includes a compression element disposed below the electric motor, and an oil supply pump formed by surrounding a disk attached to the lower end of the rotating shaft with a casing, in which lubricating oil for the sub bearing is provided at the lower end of the sub bearing. A spiral oil groove array is provided on the upper surface of the disk, curving in the opposite direction to the rotational direction of the disk as it goes from the center to the outer periphery, or a spiral oil groove array is provided on the lower surface of the side plate that curves in the opposite direction to the rotation direction of the disk as it goes from the center to the outer periphery. A spiral oil groove array is provided that is curved in the direction of rotation.

Further, the configuration of the compressor according to the second invention includes an electric motor consisting of a stator and a rotor, a rotating shaft that has a crank and rotates integrally with the rotor, and a vane sliding shaft in a closed container that also serves as a lubricating oil reservoir. A cylinder with a groove bored therein, a roller that is fitted into the crank and rotates eccentrically along the inside of the cylinder, and a roller that reciprocates within the groove of the cylinder while in contact with this roller, and the inside of the cylinder is connected to a suction chamber and compressed. A vane that partitions the motor into a chamber, an upper end plate that also serves as a side wall of the cylinder, and is provided with a main bearing and a sub-bearing for the rotating shaft, a lower end plate, and a side plate that forms a silencer between the lower end plate; In a compressor having a compression element disposed on the lower side and an oil supply pump formed by surrounding a disk attached to the lower end of the rotating shaft with a casing, a lubricating oil supply port of the sub-bearing is provided at the lower end of the sub-bearing. A spiral oil groove array is provided on the upper surface of the disk, curved in the direction of rotation of the disk as it goes from the center to the outer periphery, or on the lower surface of the side plate, in a direction opposite to the direction of rotation of the disk as it goes from the center to the outer periphery. A spiral oil groove row is provided.

[Function] The compressor according to the first invention is provided on the upper surface of the disk or the lower surface of the side plate. Due to the spiral oil groove row, a part of the lubricating oil in the center is pushed out along the curved oil groove row due to the viscous effect between the fixed side plate and the rotating disk, resulting in a viscous pump action. The remainder of the lubricating oil in the oil groove row flows toward the outer circumference due to the centrifugal force applied to the lubricating oil in the oil groove row. Therefore, the pressure at the center becomes smaller than that at the outer periphery, and the lubricating oil discharged from the lower end of the sub-bearing.

It is smoothly swept out toward the outer circumference of the disk.

Further, the compressor according to the second invention is provided on the upper surface of one disk or the lower surface of the side plate. Due to the viscous pump action between the fixed side plate and the rotating disc, the pressure in the center increases due to the spiral oil groove row, and lubricating oil is supplied to the lubricating oil supply port at the lower end of the secondary bearing. .

In the above manner, lubricating oil can be sufficiently supplied to the secondary bearing provided on the lower end plate.

[Example] Hereinafter, the present invention will be explained by examples.

FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the first invention, FIG. 2 is a sectional view taken along the line A-A in FIG. It is a BB arrow sectional view.

The outline of this compressor will be explained using FIG. 1. A stator 31. an electric motor 30 consisting of a rotor 13; a rotating shaft 5 having a crank 4 and rotating integrally with the rotor 13; Cylinder with a groove for vane sliding 1. A roller 3 that is fitted into the crank 4 and rotates eccentrically along the inside of the cylinder 1 reciprocates within the groove of the cylinder 1 while in contact with the roller 3, and creates a suction chamber and a compression chamber within the cylinder 1. Vane partitioning into 2. The main bearing 9 of the rotating shaft 5 also serves as the side wall of the cylinder 1. Upper end plate 7 provided with secondary bearing 10. Lower end plate 8. A compression element C is provided below the electric motor 30 and includes a side plate 16 forming a silencer 17 between the lower end plate 8 and the side plate 16 .

A disk 61 attached to the lower end of the rotating shaft 5 is attached to the casing 3.
A fuel pump P surrounded by 4,
A lubricating oil outlet 11 of the secondary bearing 10 is provided at the lower end of the secondary bearing 10.
was provided on the upper surface of the disk 61 and curved in the opposite direction to the rotational direction of the disk 61 from the center toward the outer periphery. This is a compressor with 33 rows of spiral oil grooves.

This will be explained in detail below.

In FIG. 1, 27 is a closed container, 47 is a discharge gas pipe attached to this closed container 27, 1 is a cylinder of a compressor, 3 is a roller rotating inside this cylinder 1,
4 is a crank that rotates this roller 3, and this crank 4 is integrated with a rotating shaft 5. 30 is
It is an electric motor, and has a stator 31. It consists of a rotor 13, which is fixed to one end of the one-rotation shaft 5. 7
8 are main bearings 9.8, which are located at the upper and lower ends of the cylinder 1, respectively, and support the rotating shaft 5. These are an upper end plate and a lower end plate having a secondary bearing 1o. Reference numeral 11 denotes a lubricating oil discharge port that is provided at the lower end of the sub-bearing 10 and communicates with the inside of a casing 34, which will be described later. 2 is.

This vane has its tip abutted against the roller 3, is pushed from behind by a spring 6, moves reciprocally according to the rotation of the roller 3, and partitions the inside of the cylinder 1 into a compression chamber and a suction chamber. 14 is a discharge valve, and 15 is a retainer that serves as a stopper for the discharge valve 14. 16 is a side plate that forms a silencer 17 with the lower end plate 8. 32 is the oil level of the lubricating oil 20 stored in the lower part of the closed container 27. In detail, the oil pump P is a centrifugal oil pump,
61 is a disk fixed to the lower end of the rotating shaft 5, 34 is a casing serving as a cover for covering the disk 61, 44 is a suction port, and 35 is a discharge port. Reference numeral 36 indicates an oil supply passage passing through the compression element C; 38 indicates an oil supply port that communicates with the oil supply passage 36 and opens to the lower part of the main bearing 9 of the upper end plate 7; 40 indicates an oil supply port bored inside the main bearing 9; , is a helical oil groove that is formed so as to gradually become higher in the direction of rotation of the rotating shaft 5, and can guide lubricating oil upward as the rotating shaft 5 rotates.

45.46 is on the rotating shaft 5 near the crank 4.

An annular groove 41 provided below is provided in the crank 4, and a slit-shaped oil groove 42 provided on the opposite side to the eccentric direction of the crank 4 is bored inside the sub-bearing 10 of the lower end plate 8.

This is a spiral oil groove that is formed to be gradually lower in the direction of rotation of the rotating shaft 5 and can guide lubricating oil downward as the rotating shaft 5 rotates.

Reference numeral 28 denotes an upper balance weight, which is attached to the lower end of the rotor 13 in a direction opposite to the eccentric direction of the crank 4. Reference numeral 29 denotes a lower balance weight, and this lower balance weight is made of a material having a higher specific gravity than the material of this disc 61 within a disc 61 so that the center of gravity is located in the opposite direction to the eccentric direction of the crank 4. Fixed.

In FIG. 2, 33 is on the top surface of one disk 61.

This is an oil groove curved in the direction opposite to the direction of rotation (arrow).

In FIG. 3, reference numeral 63 indicates oil grooves that are radially bored on the lower surface of the disk 61.

The operation of the compressor configured as above will be explained.

When the electric motor 30 is operated, the rotating shaft 5 fixed to the rotor 13 rotates, and the crank 4 causes the roller 3 to rotate eccentrically within the cylinder 1.

Then, the refrigerant is compressed by changing the volume of the compression chamber partitioned by the vane 2, which reciprocates while abutting the tip of the vane against the roller 3. The compressed refrigerant gas is discharged through the discharge valve 1
4 to the silencer 17, from where it passes through a discharge gas passage (not shown) and is discharged into the closed container 27. The gas is then sent to the refrigeration cycle from the discharge gas pipe 47.

Next, the operation of the oil supply pump P will be explained. The centrifugal force of the lubricating oil in the radial oil grooves 63 formed on the lower surface of the disk 61 that rotates together with the rotating shaft 5 causes the disk 61 and the casing 34 to
The lubricating oil is sent from the suction port 44 to the discharge port 35 so that the pressure in the space between the two increases. Then, a part of the lubricating oil passes through the annular groove 45 provided in the six-rotation shaft 5 and is sent to the oil supply port 38 through the oil passage 36 of the compression element C, and a part of the lubricating oil flows into the helical oil groove 40 inside the main bearing 9. The oil is guided to the lower end, from where it lubricates the main bearing 9, or is sent to the upper end of the main bearing 9 in the helical oil groove 40 due to the viscous effect with the rotating shaft 5, and the sealed container 27
flows inward. The remaining lubricating oil sent to the annular groove 45 is
A part leaks into the cylinder 1 and contributes to internal lubrication, and the rest passes through a slit-shaped oil groove 411 provided in the crank 4 and an annular groove 46, and the rest passes through a helical oil groove 42 bored inside the sub-bearing 10.
led to the top. From here, the secondary bearing 10 is lubricated.

Alternatively, the oil is sent to the lower end of the sub-bearing 10 in the helical oil groove 42 due to the viscous effect with the rotating shaft 5. And lubricating oil discharge port 11
It flows out into the space between the side plate 16 and the disk 61 inside the casing 34 . From here, the oil grooves 33 are caused by the centrifugal pump action caused by the centrifugal force exerted on the lubricating oil in the grooves and the viscosity between the side plate 16 and the upper surface of the disk 61 by the 33 rows of spiral oil grooves bored on the upper surface of the disk 61. The lubricating oil flows out toward the outer circumference of the disk 61 due to the viscous action that pushes the lubricating oil toward the outer circumference along the rows. Therefore, the lubricating oil flowing through the sub-bearing 10 is quickly swept out from the lower end toward the outside of the disc 61.

According to the embodiment described above, there are the following effects.

■Since 33 rows of spiral oil grooves are formed on the upper surface of the disk 61, the lubricating oil flowing from the sub-bearing 10 to the lubricating oil outlet 11 can be quickly swept away by the centrifugal pump action and viscous pump action. . Therefore, the lubricating oil flows smoothly within the sub-bearing 10, the bearing can be sufficiently cooled, and seizures and deterioration of the lubricating oil do not occur.

Since the oil supply pump P is disposed at the lower end of the 00 rotation shaft 5, a high head can be obtained not only at high speed rotation but also at low rotation, and sufficient oil can be supplied to each sliding part of the compression element C.

Since the θ0 disc 61 (to which the lower balance weight 29 is attached) is covered with the casing 34, the lubricating oil 20 stored at the bottom of the closed container 27 is not disturbed.

Other embodiments will be described below.

4 is a longitudinal sectional view of a compressor according to a second embodiment of the first invention, FIG. 5 is a sectional view taken along the line C-C in FIG. 4, and FIG. It is a sectional view taken along the line DD.

In each episode, parts with the same numbers as in FIGS. 1 to 3 are the same parts.

This embodiment is based on the disk 6 in the embodiment according to FIG.
In place of the 33 rows of oil grooves on the upper surface of the side plate 16A, a row of oil grooves 39b (details will be described later) are provided on the lower surface of the side plate 16A, and in place of the centrifugal type refueling pump P, a combined viscous/centrifugal refueling pump P' ( (Details will be described later), and the other configurations are the same.

That is, as shown in FIG. 5, the oil grooves 39b arranged in the side plate 16A are formed between the guide vanes 39a arranged from the center to the outer periphery and curved in the rotational direction (arrow) of the rotating shaft 5. It is spiral shaped. The upper surface of the disk 61A is smooth. The viscous/centrifugal oil supply pump P' includes a disk 61A (details will be described later) fixed to the lower end of the rotating shaft 5,
It consists of a casing 34 that covers this disk 61A.

As shown in FIG. 6, the lower surface of the disk 61A is provided with 63 rows of helical oil grooves curved in the direction opposite to the rotational direction (arrow) of the rotating shaft 5, and aligned with the eccentric direction of the crank 4. A lower balance weight 29 whose center of gravity is located in the opposite direction is attached.

The operation of the compression element C of the compressor constructed in this manner is completely the same as that in the embodiment shown in FIG. 1 above.

Regarding the flow of lubricating oil, the lubricating oil that has flowed in from the suction port 44 is transferred to a disk 61 that rotates together with the rotating shaft 5 .

The lubricating oil flows in the circumferential direction along the oil grooves 63 due to the centrifugal pump action caused by the centrifugal force applied to the lubricating oil in the rows of oil grooves 63 provided on the lower surface of A and the viscous effect between the lower surface of the disk 61A and the casing 34. Due to the viscous pumping action, the disk 6
The pressure between the outer part 1A and the casing 34 increases.

Therefore, as in the embodiment shown in FIG. 1 described above, lubricating oil is sent from the pump discharge port 35 to the lubricating oil supply port 38.

The lubricating oil then lubricates each sliding portion of the compression element C, and flows out from the lubricating oil discharge ports 11 at the upper end of the main bearing 9 and the lower end of the sub-bearing 10. Due to the viscous effect of the lubricating oil between the upper surface of the first disk 61A and the lower surface of the side plate 16A, the lubricating oil between the two is pushed out toward the outer circumference along the oil groove 39b row. Therefore, secondary bearing 1
The lubricating oil flowing out from the lower end is quickly swept out toward the outer circumference.

According to this embodiment, in addition to the effects of the embodiment shown in FIG. Since it is a pump P', it has the advantage that a higher head can be obtained than a centrifugal oil supply pump P.

FIG. 7 is a longitudinal cross-sectional view of a compressor according to a third embodiment of the first invention, FIG. 8 is a cross-sectional view taken along the line E-E in FIG. 7, and FIG. It is a sectional view taken along the line FF.

In each episode, the same numbers as in FIGS. 1 to 3 indicate the same parts.

In this embodiment, a lower end plate 8A is provided in place of the lower end plate 8 in the embodiment shown in FIG. The other configurations are the same.

As shown in FIG. 8, the lubricating oil discharge path 50 is formed between the side plate 16 and a groove formed in the lower end surface of the rib 64, which partitions the side plate 1 part of the lower end plate 8A by a rib 64. The lubricating oil outlet 11 at the lower end of the helical oil groove 42 provided on the inner surface of the sub-bearing 10 communicates with the side surface of the lower end plate 8A.

The operation of the compression element C of the compressor constructed in this manner is completely the same as that in the embodiment shown in FIG. 1 above.

Regarding the flow of lubricating oil, the lubricating oil flowing from the suction port 44 is pumped by the centrifugal force exerted on the lubricating oil in the oil groove 63 provided on the lower surface of the disk 61 that rotates together with the rotary shaft 5. As in the illustrated embodiment, lubricating oil is sent from the pump outlet 35 to the lubricating oil supply port 38.

The lubricant then lubricates each sliding portion of the compression element C and flows to the upper end of the main bearing 9 and the lower end of the sub-bearing 10. Of these, auxiliary bearing 10
Most of the lubricating oil flowing through the helical oil groove 42 passes through a lubricating oil discharge path 50 communicating with the lower end of the helical oil groove 42 and is discharged into the lubricating oil 20 collected in the closed container 27. Also, at this time, the disk 61
Due to the centrifugal pumping action of the lubricating oil in the 33 rows of oil grooves provided on the upper surface and the viscous pumping action between the lower surface of the side plate 16, the lubricating oil flowing from the lower end of the helical oil groove 42 into the casing 34 flows into a disc. 61 toward the outer periphery. Therefore, the pressure in the center becomes low, and the lubricating oil in the sub bearing 10 can be discharged without impairing its flow.

According to this embodiment, in addition to the effects of the embodiment shown in FIG. Therefore, compared to the embodiment shown in FIG. 1 in which oil is discharged into the casing 34 of the oil supply pump P, the cooling of the bearing is more effective.

10 is a longitudinal sectional view of a compressor according to a fourth embodiment of the first invention, and FIG. 11 is a sectional view taken along the line G in FIG. 10.

In each episode, the same numbers as in FIG. 7 indicate the same parts.

This embodiment differs from the embodiment shown in FIG. 7 in that a suction hole 52 is provided at the lower end of the rotating shaft 5, and a communication hole 53 is provided that communicates from the suction hole 52 to the space between the side plate 16 and the disc 61. The other configurations are the same.

The operation of the compression element C of the compressor thus constructed and the flow of lubricating oil are carried out through a suction hole 52 provided at the lower end of the 0-rotation shaft 5, which is the same as in the embodiment shown in FIG. Lubricating oil is supplied to the low pressure space between the side plate 16 and the disc 61 through the communication hole 53, so that the oil supply pump P can operate smoothly.

According to this embodiment, in addition to the effects of the embodiment shown in FIG. 7, a large negative pressure area does not occur in the oil supply pump P, and therefore there is no fear that the pump action will be impaired due to the generation of air bubbles, etc. There is an advantage.

This concludes the explanation of the embodiment according to the first invention.

The second invention will be explained in detail below.

FIG. 12 is a longitudinal sectional view of a compressor according to the first embodiment of the second invention, FIG. 13 is a sectional view taken along the line H-H in FIG. 12,
FIG. 14 is a sectional view taken along the line JJ in FIG. 12.

In each episode, the same numbers as in FIG. 1 indicate the same parts.

In this embodiment, a lubricating oil supply port 12 is provided at the lower end of the sub-bearing 10.
is formed on the inner surface of the auxiliary bearing 10 so as to gradually become higher in the direction of rotation of the one-rotation shaft 5.

As the rotating shaft 5 rotates, the lubricating oil can be guided upward. A spiral oil groove 42a is provided.

Further, as shown in FIG. 13, a spiral oil groove 33a row is formed in the upper surface of the disk 61B, and curves in the rotation direction (arrow) of the disk 61B as it goes from the center to the outer periphery. The oil supply pump P' is a viscous/centrifugal type oil supply pump similar to the embodiment shown in FIG. 4, and performs the same function.

The operation of the compression element C of the compressor constructed in this manner is completely the same as that in the embodiment shown in FIG. 1 above.

Regarding the flow of lubricating oil, the lubricating oil flowing in from the suction port 44 acts as a centrifugal pump due to the centrifugal force applied to the lubricating oil in the row of oil grooves 63 provided on the lower surface of the disk 61B that rotates together with the rotating shaft 5, and Due to the viscous pump action between the lower surface and the casing 34, the pressure between the outer circumference of the disk 61B and the casing 34 increases. In addition, the casing 34
In addition to increasing the pressure in the entire area inside the casing 34, the central part is covered by The pressure of
, oil groove 41. The oil passes through the helical oil groove 40, lubricates each sliding part of the compression element C, the auxiliary bearing 10° and the main bearing 9, and flows out from the upper end of the main bearing 9.

According to this embodiment, it is possible to increase the pressure at the center of the disc 61B, that is, at the lower end of the sub-bearing 10, so that sufficient lubricating oil can be supplied from the sub-bearing 10 to each sliding part through the lubricating oil supply port 12. The same effect as the embodiment shown in FIG. 1 can be obtained.

FIG. 15 is a longitudinal cross-sectional view of a compressor according to a second embodiment of the second invention, and FIG. 16 is a cross-sectional view taken in the direction of the arrow - in FIG. 15.

In each episode, the parts with the same numbers as in FIG. 12 are the same parts.

In this embodiment, a row of oil grooves 39d is provided on the lower surface of the side plate 16B in place of the row of oil grooves 33a on the upper surface of the disk 61B in the embodiment shown in FIG. As shown in FIG. 16, the rows of oil grooves 39d provided on the lower surface of the side plate 16B are formed between guide vanes 39c that are curved in the rotational direction (arrow) of the disk 61 from the center toward the outer periphery. ,
The upper surface of the disk 61 is smooth.

The operation of the compression element C of the compressor constructed in this manner is completely the same as that in the embodiment shown in FIG. 1 above.

Regarding the flow of lubricating oil, the pressure inside the casing 34 increases due to the oil supply pump P, and the pressure at the center increases due to the viscous spiral pump action between the row of oil grooves 39d and the upper surface of the disk 61, and as shown in FIG. As in the embodiment, lubricating oil is sent to each sliding portion of the compression element C.

According to this embodiment, in addition to the effects of the embodiment according to FIG. 12, there is an advantage that the upper surface of the disk 61 is smooth and there is little resistance accompanying rotation.

[Effects of the Invention] As described in detail above, according to the present invention, a refueling pump is provided in which a disk attached to the lower end of a rotating shaft is surrounded by a casing, and the lower end plate of the rotating shaft is It is possible to provide a compressor that can sufficiently supply lubricating oil to the sub-bearing provided in the auxiliary bearing.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of a compressor according to a first embodiment of the first invention, FIG. 2 is a cross-sectional view taken along the line A-A in FIG. 1, and FIG. 4 is a longitudinal sectional view of the compressor according to the second embodiment of the first invention, and FIG. 5 is a sectional view taken along the line C-C in FIG. 6 is a sectional view taken along the line D-D in FIG. 4, FIG. 7 is a longitudinal sectional view of the compressor according to the third embodiment of the first invention, and FIG. -E arrow sectional view, FIG. 9 is a FF sectional view of FIG. 7, and FIG. 10 is a longitudinal sectional view of the compressor according to the fourth embodiment of the first invention.
1 is a cross-sectional view taken along the line GG in FIG. 10, FIG. 12 is a vertical cross-sectional view of the compressor according to the first embodiment of the second invention, and FIG. 13 is a cross-sectional view taken along the line H-H in FIG. The arrow sectional view, FIG. 14, is the 12th
The sectional view taken along the line J-J in the figure, FIG.
A vertical cross-sectional view of the compressor according to the embodiment, FIG.
FIG. 1...Cylinder, 2...Vane, 3...Roller,
4... Crank, 5... Rotating shaft, 7... Upper end plate,
8,8A...Lower end plate, 9...Main bearing, 10...Sub bearing, 11...Lubricating oil discharge port, 12...Lubricating oil supply port, 13...Rotor, 16.16A , 16B... side plate, 17... silencer. 27... Airtight container, 30... Electric motor, 31... Stator, 33.33a... Oil groove, 34... Casing, 39b. 39d... Oil groove, 50... Lubricating oil discharge path, 52...
・Suction hole, 53...Communication hole, 61, 61A, 61B・
··disk. C...Compression element, P, P'...Oil supply pump.

Claims (1)

[Claims] 1. An electric motor consisting of a stator and a rotor, a rotating shaft having a crank and rotating integrally with the rotor, and grooves for sliding vanes are bored in a closed container that also serves as a lubricating oil reservoir. a cylinder, a roller that is fitted in the crank and rotates eccentrically along the inside of the cylinder; a vane that reciprocates within a groove of the cylinder while abutting the roller and partitions the inside of the cylinder into a suction chamber and a compression chamber; The cylinder has an upper end plate that also serves as a side wall of the cylinder and is provided with a main bearing and a sub-bearing for the rotating shaft, a lower end plate, and a side plate that forms a silencer between the lower end plate, and is disposed below the electric motor. In the compressor, the compressor has a compression element and an oil supply pump formed by surrounding a disk attached to the lower end of the rotating shaft with a casing, the lower end of the sub-bearing having
A lubricating oil outlet of the sub-bearing is provided, and a spiral oil groove row is provided on the upper surface of the disk, which curves in the opposite direction to the rotational direction of the disk as it goes from the center to the outer periphery, or on the lower surface of the side plate.
A compressor characterized by being provided with a spiral oil groove array that curves in the rotational direction of the disk as it goes from the center to the outer periphery. 2. The compressor according to claim 1, wherein a lubricating oil discharge path is formed between the lower end plate and the side plate from the lubricating oil outlet of the sub bearing to the side surface of the lower end plate. 3. A suction hole is formed in the lower end of the rotating shaft, and a communication hole is formed in the rotating shaft that communicates from the suction hole to the space between the side plate and the disk. 2
Compressor described in section. 4. In a sealed container that also serves as a lubricating oil reservoir, there is an electric motor consisting of a stator and a rotor, a rotating shaft that has a crank and rotates integrally with the rotor, a cylinder that has a groove for sliding vanes, and a cylinder that is fitted into the crank. a roller that rotates eccentrically along the inside of the cylinder, a vane that reciprocates within the groove of the cylinder while abutting the roller and partitions the inside of the cylinder into a suction chamber and a compression chamber, and a vane that also serves as a side wall of the cylinder. , comprising an upper end plate and a lower end plate provided with a main bearing and a sub-bearing of the rotating shaft, a side plate forming a silencer between the lower end plate, and a compression element disposed below the electric motor; In a compressor having an oil supply pump consisting of a disk attached to the lower end of the rotating shaft and surrounded by a casing, the lower end of the sub-bearing is
A lubricating oil supply port for the secondary bearing is provided, and a spiral oil groove array is provided on the upper surface of the disk that curves in the rotation direction of the disk as it goes from the center to the outer periphery, or on the lower surface of the side plate that extends from the center to the outer periphery. A compressor characterized by having a spiral oil groove row curved in a direction opposite to the direction of rotation of a disk.