JPH01170775A - Compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a compressor used in an air conditioner, etc. It's about machines.

[Conventional technology]

Conventional compressors are Utility Model No. 44-8676 and Utility Model No. 49
As described in publications such as No.-15282 and Utility Model Publication No. 50-11206, an oil supply pump using a centrifugal pump is provided at the thrust bearing portion of the lower end surface of the five-rotation shaft. These have a structure in which a radial horizontal hole or groove is provided at the lower end of the rotating shaft, and the lubricating oil guided through the thrust receiving plate is pumped by centrifugal force to an oil reservoir provided on the outside of the rotating shaft. A groove in the thrust receiving plate, using the thrust bearing plate as a partition, leads to the oil supply hole in the center of the rotating shaft.

[Problem that the invention attempts to solve]

The above-mentioned conventional technology takes into consideration that the centrifugal pump section may be filled with gas when the compressor is stopped, and takes into consideration measures such as providing a waste removal hole in a part of the pump.

However, since centrifugal pumps are constructed using the thrust sliding surface at the lower end of the rotating shaft, consideration has been given to operating the compressor with a wide range of rotational speeds.At low speed rotation, friction loss occurs. Although it is small, the lifting head of the centrifugal pump is insufficient.

On the other hand, in order to obtain a lift of 8 times higher when rotating at low speeds, the diameter of the centrifugal pump must be increased (if this is done, there is a problem of increased friction loss during high speed rotations).

The purpose of the present invention is to improve the problems of the prior art described above,
To provide a compressor equipped with an oil supply pump capable of supplying oil even at low speed rotation and reducing friction loss during high speed rotation.

[Means for Solving the Problems] In order to solve the above-mentioned problems, the compressor according to the present invention has a structure in which a stator, a stator,
An electric motor consisting of a rotor, a rotating shaft having a crank and rotating integrally with the rotor, a cylinder having a groove for sliding a vane, a roller fitted in the crank and rotating eccentrically along the inside of the cylinder; A vane that reciprocates in the groove of the cylinder while contacting the roller and partitions the inside of the cylinder into a suction chamber and a compression chamber, an upper and lower end plate that serves as a bearing for the rotating shaft and a side wall of the cylinder, and a lower end portion. and a compression element disposed below the electric motor. In such a compressor, a thrust bearing is formed by the lower end of the crank and the upper end surface of the lower end plate, and is mounted on the lower end surface of a disc that is provided at the lower end of the rotating shaft and serves as a balance weight that rotates together with the rotating shaft. A groove extending from the center to the outer circumference is drilled,
The above object is achieved by forming a centrifugal pump with the pump casing provided so as not to contact the lower end of the disc.

[Effect]

A centrifugal system in which lubricating oil flows due to the centrifugal force generated by rotation through a series of holes extending from the center toward the outer circumference, which are drilled in the lower end of a disc that also serves as a balance weight at the lower end of the rotating shaft, increasing pressure at the outer circumference. performs a pumping action. There is a gap between the lower end of the disk and the pump casing, so there is viscous resistance to the fluid, but since there are no sliding parts, the loss is small even during high-speed rotation.

〔Example〕

Hereinafter, the present invention will be explained by referring to examples.

FIG. 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along the line A-A showing details of the oil supply pump at the lower end of the balance weight in FIG.

An overview of this compressor can be explained using Figure 1. Lubricating oil 2
The stator 5 is placed in an airtight container 27 that also serves as an oil reservoir for storing 0.
1. An electric motor 3o consisting of a rotor 16, a rotating shaft 5 having a crank 4 and rotating integrally with the rotor 16, and a cylinder 1 having a groove for vane sliding. A roller 6 is fitted into the crank 4 and rotates eccentrically along the inside of the cylinder 1. A roller 6 reciprocates within the groove of the cylinder 1 while in contact with the roller 5, dividing the inside of the cylinder 1 into a suction chamber and a compression chamber. vane 2
An upper end plate 7 that serves as a bearing for the one-rotation shaft 5 and a side wall of the cylinder 1
, a compression element C equipped with a lower end plate 8 and a centrifugal pump-type oil supply pump P (details will be described later) related to the oil supply pump driven by the rotation of the one-rotation shaft 5 are provided in order from top to bottom. A lubricating oil supply port 38 for supplying lubricating oil is provided at the lower part of the upper end plate 7, and an oil supply passage 56 is provided which communicates this lubricating oil supply port 5 with the discharge port 35 of the centrifugal pump type oil supply pump P. , guides the lubricating oil flowing out from the end surface of the lower end plate 8 related to the lower part of the compression element C to the oil sump in the closed container 27 (
This is a compressor provided with an oil drain path 50.

This will be explained in detail below.

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 the cylinder 1, and 4 is a roller 5. This is a crank that provides rotation, and this crank 4 is integrated with a rotating shaft 5. 50 is an electric motor consisting of a stator 31° and a rotor 13.
5 is fixed to a part of the rotating shaft 5. 7.8 are located at the upper end and lower end of the cylinder 1, respectively, and the rotating shaft 5
Main bearing supporting 9. They are an upper end plate and a lower end plate having a sub-bearing 10. 70 is a thrust surface provided on the lower end surface of the crank 40, and is supported by the lower end surface of the lower end plate 8. 2, the tip is in contact with the roller 3.

This vane is pushed from behind by a spring 6 and reciprocates in degrees Celsius 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, 15 is this discharge valve 1
This is a retainer that serves as a stopper. 16 is a side plate that forms a silencer 17 with the lower end plate 8. 52 is the oil level of the lubricating oil 20 stored in the lower part of the closed container 27. The centrifugal oil pump P is detailed as follows: 6
1 is a disk of a centrifugal oil pump P fixed to the lower end of the rotating shaft 5, 54 is a pump casing, 44 is a suction port, and 65 is a discharge port.

36 is an oil supply passage that penetrates inside the compression element C; 38 is an oil supply port that communicates with this oil supply passage 36 and opens to the lower part of the main bearing 9 of the upper end plate 7; 40 is bored inside the main bearing 9; This is a helical oil groove that is formed to have a height that gradually increases in the direction of rotation of the rotating shaft 5, and is capable of guiding lubricating oil upward as the rotating shaft 5 rotates. An annular groove provided near 4 and above and below, 41 is the crank 4
A slit-shaped oil groove provided on the opposite side of the eccentric direction,
42 is bored inside the sub-bearing 10 of the lower end surface 8 and is formed in a shape L5 that gradually becomes lower in the rotation direction of the rotating shaft 5.
This is a spiral oil groove that can guide lubricating oil downward as it 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 direction in which the crank 4 is damaged. A lower balance weight 29 is fixed to the disc 61 of the centrifugal oil pump P so that its center of gravity is located in the same direction as the upper balance weight 28.

In FIG. 2, reference numeral 66 indicates a row of oil grooves formed radially on the lower end surface of the disk 61. 62 is a pump casing that covers the lower end surface of the disc 61 with a gap δ provided therebetween.

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

When the electric motor 50 is operated, the rotating shaft 5 fixed to the rotor 13 rotates, and the crank 4 causes the roller 6 to rotate eccentrically within the cylinder 1.

Then, the refrigerant is compressed by changing the volume of the compression chamber partitioned by degrees Celsius by the pirn 2 that reciprocates while abutting the tip of the roller SVC. The compressed refrigerant scum is discharged through the discharge valve 1
4 to the silencer 17.

From here, a discharge gas passage (not shown) is passed through the closed container 27.
released to. Then, it is sent from the discharge waste pipe 47 to the refrigeration cycle.

Next, the operation of the oil supply pump will be explained.

℃ due to the centrifugal force of the lubricating oil in the radial oil grooves 65 drilled on the lower surface of the disk 61 that rotates together with the rotating shaft 5.
The pressure in the space between the outer circumference and the pump casing 54 increases. Therefore, the lubricating oil is sucked in through the suction port 44 and is pumped to the discharge port 55 by the centrifugal pump. Soshi 1
, and is sent to the oil supply port 68 through the oil passage 36 of the compression element C. A part of the lubricating oil passes through the annular groove 45 provided on the rotating shaft 5&'c and is guided to the lower end of the helical oil groove 40 inside the main bearing 9, from where it lubricates the main bearing 9 or The oil flows inside the oil groove 40 and flows out from the upper end. A portion of the remaining lubricating oil sent to the annular groove 45 leaks into the cylinder 1 and contributes to the lubrication of the circular part, and the rest passes through the slit-shaped oil groove 410 provided in the crank 4 and the annular groove 46. The oil is guided to the upper end of a helical oil groove 42 bored inside the sub-bearing 10. From here, sub bearing 1
0, or flows through the helical oil groove 42, and the lower end plate 8
The oil returns from the oil sump 49 provided at the lower end to the oil sump in the closed container 27 through the oil discharge path 48 .

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

b) Since the gap δ is provided between the lower end surface of the disk 61 and the pump casing 34, the frictional resistance is small and the loss is small even at high speed rotation.

Since a groove is provided on the lower end surface of the disk 61 which also serves as a mounting seat for the balance weight 29, the outer circumferential radius as a centrifugal pump is large (and a high head can be obtained even at low speed rotation.

c) The groove 66 bored in the lower end surface of the disk 61 is open to the gap δ between the pump and the sink 54, so even if the groove is filled with gas, it will leak into the gap δ. Gas is also easily discharged along with oil.

2) Since the disc 61 is covered by the pump casing, it does not disturb the lubricating oil 20 stored at the bottom of the closed container 27.

Next, another embodiment will be described.

FIG. 5 is a longitudinal sectional view of a compressor according to a second embodiment of the present invention, and FIG. 4 is a view taken along the line B-B showing details of the vicinity of the viscous/centrifugal oil pump P' in FIG. 6. FIG. In each figure, the same parts are denoted by the same numbers as in Fig. 1.

The viscous/centrifugal oil supply pump P' is composed of a disk 61 fixed to the lower end of the rotating shaft 5 and a pump gauging 34 that covers this. 64 rows of curved, coil-shaped oil grooves are bored in the opposite direction of the rotational direction (arrow) of the shaft 5, and the balance weight is set so that the center of gravity is located on the opposite side of the eccentric direction of the crank 4. There is 1.

The operation of the 1M pressure element C of the compressor constructed in this manner is completely the same as that in the first embodiment. The flow of lubricating oil is caused by a centrifugal pump action in which the lubricating oil that flows in from the suction port 44 is pushed out toward the outer circumference by centrifugal force through nine oil grooves 64 arranged on the lower end surface of the disk 61 that rotates together with the rotating shaft 5. and,
The pressure between the outer part of the disc 61 and the pump casing 34 increases due to the viscous pump action in which the oil is guided toward the outer circumference along the oil groove 64 due to the viscosity effect between the oil and the pump casing 54 . Therefore, as in the first embodiment described above, lubricating oil is sent from the discharge port 35 to each column slide portion of the compression element C.

According to this embodiment, in addition to the effects of the first embodiment, a viscous pump action is added, and a higher head than the centrifugal oil pump P can be obtained. In addition, even if the oil groove 64 on the lower end surface of the disc 61 is filled with gas, the oil flows along the nine grooves of the curved surface, so the gas is also pushed out toward the outer circumference, which has the advantage of reducing the risk of remaining. .

FIG. 5 is a longitudinal sectional view of a compressor according to a fifth embodiment of the present invention, and FIG. 6 is a diagram showing details of the vicinity of the helical groove/centrifugal oil supply pump P' in FIG. C arrow sectional view,
FIG. 7 is an explanatory diagram illustrating the flow of oil within the pump. In each figure 1cjj, the same parts as those in FIG. 1 are denoted by the same numbers.

The spiral groove type/centrifugal type oil supply pump P' of this embodiment is as follows:
It consists of a disk 61 fixed to the lower end of the rotating shaft 5 and a pump casing 34 that covers it.As shown in FIG. 65 rows of spiral oil grooves curved in the 8th direction are bored, and a balance weight is attached so that the center of gravity is located on the opposite side of the eccentric direction of the crank 4.

The operation of the pressure W1 element C of the compressor configured in 5 is exactly the same as in the first embodiment. The flow of the lubricating oil is caused by the centrifugal pump action in which the lubricating oil that flows in from the suction port 44 is pushed outward by centrifugal force in the rows of oil grooves 65 provided on the base surface of the disk that rotates together with the rotation shaft 5, and by the pump casing. The oil is guided toward the center along the oil groove 65 due to the viscous effect between the oil 64 and the oil groove 65 (there is a viscous pump effect. Therefore, as shown in FIG. , toward the center near the bottom surface■
There is a flow. However, most of the oil increases the pressure outside the disk 61 due to the action of the centrifugal pump. Therefore, as in the first embodiment described above, lubricating oil is sent from the discharge port 55 to each lubricating portion of the element C.

According to this embodiment, in addition to the effects of the first embodiment, it is possible to suppress the outflow amount of the oil supply pump by the spiral groove type O viscous pump. That is, during high-speed rotation, in addition to the resistance within the oil groove 65, the oil near the lower end flows toward the center due to the viscous pump action of the spiral groove, and the pressure outside the disk 61 also decreases, resulting in an increase in the amount of outflow from the oil supply pump. can be suppressed. This has the effect of preventing lubricating oil in the compressor from flowing out of the compressor together with the discharged gas due to excessive oil supply during high-speed rotation, resulting in an insufficient amount of lubricating oil.

〔Effect of the invention〕

As described in detail above, according to the present invention, a sufficient amount of oil can be supplied during low speed rotation, and friction loss during high speed rotation can be reduced. Moreover, even if the centrifugal pump is filled with gas, it can be quickly discharged and there is no residual gas.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of a compressor according to the first embodiment of the present invention. The figure is a vertical sectional view of the compressor according to the second embodiment, FIG. The cause of the vertical cross section of the compressor according to the embodiment shown in FIG. FIG. 5... Rotating shaft, 7... Upper end plate. 8...Lower end plate, 9...Main bearing. 10... Secondary bearing, 54... Pump casing. 29...Balance weight. 35...Discharge 0.44...Suction port. 61...disk, 65,64.65...
・Oil groove. Figure 1 Figure 2 Figure 3 Figure 5 Figure 60 Section 7 (2)

Claims (1)

[Claims] 1. In a sealed container that also serves as a lubricating oil reservoir, an electric motor consisting of a stator and a rotor, a rotating shaft that has a crank and rotates together with the rotor, a cylinder with 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 contacting 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. a compression element disposed below the electric motor; In a compressor equipped with a disk having a balance weight located at the lower end of a rotating shaft with a center of gravity located on the opposite side to the eccentric direction of the crank, a groove extending from the center toward the outer circumference is provided on the lower end surface of the disk, and the disk A compressor characterized in that a centrifugal pump is formed by a pump casing arranged with a gap between it and a lower end surface.