JPH05302581A - Vertical type compressor - Google Patents

Abstract

PURPOSE:To return oil to a pump side without using a particular oil separator by forcing oil supplied to an upper part bearing, by providing a passage connected to a supply oil pump to feed oil to the upper part bearing and also a helical groove for forcedly returning oil, after lubricating the bearing, to a rotor of a motor. CONSTITUTION:A supply oil pump 8 provided in a lower part is actuated according to rotating a drive shaft, to supply lube oil from this pump 8 to an upper part bearing 15 of an upper part bearing housing 14 via a communication path 17 and a forcedly supplying oil passage 18. After lubrication, oil discharged to a downward side from the bearing 15 is sprung outward in a diametric direction of the drive shaft by rotating a balance weight 34 provided in a rotor 31, to collide against a tapered surface 37a of a coil end 37, and the oil is guided to a downward side to flow in a helical groove 19 of the rotor 31 from the upper end part of a stator 32, and returned to a bottom part oil reservoir 1c from a return oil receiving chamber 52 and a return oil passage 53 under the rotor 31 by screw pump action of the helical groove 19. In this way, oil after lubrication can be returned to a pump side without providing an oil separator of demister or the like.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a vertical compressor, more specifically,
The present invention relates to a vertical compressor in which a scroll type or rotary type compression element is installed in the lower part of a vertical closed casing, and a motor is installed in the upper part of the compression element.

[0002]

2. Description of the Related Art Generally, a vertical compressor in which a compression element is installed in a lower portion of a hermetic casing and a motor is installed in an upper portion is disclosed in Japanese Patent Laid-Open No. 3-149391. This conventional compressor has a fixed scroll B1 and a movable scroll B at the bottom of a high-pressure dome-shaped hermetic casing A as shown in FIG.
2 and a motor D having a vertically long drive shaft C for orbiting the movable scroll with respect to the fixed scroll, and the motor D and the compression element B. And a lower bearing housing F holding a plain bearing E in the center, and
On the upper side of the motor D, a dish-shaped upper bearing housing H holding a rolling bearing G in the center is attached, and the drive shaft C is attached to the bearings E and G of these bearing housings F and H.
Supporting the lower shaft end and the upper shaft end. Further, in the space between the movable scroll B2 and the lower shaft end of the drive shaft C, a positive displacement oil pump I that operates by the orbiting motion of the movable scroll B2 is arranged, and the oil pump I
The sliding bearing E and the rear thrust surface of the movable scroll B2 are lubricated by means of the above, and a discharge chamber J is formed between the upper bearing housing H and the upper wall of the closed casing A. A discharge gas passage K opening at the upper bearing housing H is provided, and a discharge pipe L is opened at the upper wall of the hermetic casing A so that the gas is discharged from the discharge port of the compression element B into the hermetic casing A. The discharged gas is discharged from the discharge gas passage K to the discharge chamber J through an air gap between the rotor and the stator of the motor D, and the discharged discharge gas collides with the discharge chamber inner wall surface. The lubricating oil mixed in is separated, and the separated lubricating oil is gathered to the center side of the upper bearing housing H to collect the rolling bearing G. So that the refueling.

[0003]

However, like the conventional compressor, the lubricating oil mixed in the discharge gas is separated from the gas, and the separated lubricating oil is supplied to the upper rolling bearing G. If lubrication is performed by using the above method, a sufficient amount of oil cannot be constantly provided, and the amount of oil becomes insufficient, which causes damage to the upper rolling bearing G, and there is a problem that reliability of the upper rolling bearing G decreases. Also, there is a problem that low-noise sliding bearings with low noise cannot be used for rolling bearings due to lack of oil.

When the oil supply pump I is used to forcibly supply oil to the upper roller bearing G from the oil supply pump I, a slide bearing can be used as the upper bearing G, but There is a problem that the lubricating oil after lubrication mixes with the discharge gas and increases the amount of oil that rises from the discharge pipe L to the refrigeration system side. Further, in the case of this forced lubrication, if an oil separator such as a demister is provided above the upper bearing G to reduce the amount of oil rising to the refrigeration system side, the height of the entire compressor In addition to high cost, there is a problem that the structure becomes complicated and the cost becomes high.

The present invention has been made in view of the above problems, and an object thereof is to forcibly supply oil from an oil supply pump to an upper bearing, but to supply oil after lubrication without providing a special oil separator. The point is to be able to return oil to the side.

[0006]

Therefore, according to the present invention, the compression element 2 is installed in the lower part of the vertical closed casing 1, and the motor 3 having the drive shaft 4 is installed in the upper part of the compression element 2. In a vertical compressor in which the bearing 15 of the drive shaft 4 is provided above the motor and the oil supply pump 8 is provided below the drive shaft 4, the vertical compressor communicates with the oil supply pump 8 and the bearing 1
5 is provided with a forced oil supply passage 18 for supplying oil, and the rotor 31 of the motor 3 is provided with a spiral groove 19 for forcibly returning the oil supplied to the bearing 15 downward.

Further, between the compression element 2 and the motor 3,
A gas guide plate 20 is provided for guiding the discharge gas discharged from the discharge port 23 of the compression element 2 into the casing 1 to the gas passage 36 formed between the stator 32 of the motor 3 and the casing 1. Is preferred.

[0008]

Since the lubricating oil can be supplied from the oil supply pump 8 to the upper bearing 15 through the forced oil supply passage 18, this bearing 15
The reliability of the bearing can be improved, and an inexpensive and low-noise slide bearing can be used as the bearing 15.
Moreover, with a simple structure in which only the spiral groove 19 is provided in the rotor 31 of the motor 3, the oil after lubrication is supplied to the spiral groove 19
Since the oil can be returned from the oil supply pump to the refrigeration system, the amount of oil rising to the refrigeration system side can be reduced, and the cost can be reduced as compared with the case where an oil separator such as a demister is provided.
It is also possible to prevent the height of the entire compressor from becoming high.

Further, by providing the gas guide plate 20 for guiding the discharge gas discharged from the discharge port 23 of the compression element 2 into the casing 1 to the gas passage 36 between the stator 32 and the casing 1, The discharged gas can be prevented from flowing into the air gap between the rotor 31 and the stator 32, and the oil after lubrication can be favorably returned from the spiral groove 19 to the oil supply pump side.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The compressor shown in FIG. 1 is a high-pressure dome type scroll compressor used in a refrigeration system, in which a fixed scroll is provided under a vertically long closed casing 1 to which a suction pipe 11 and a discharge pipe 12 are connected. A suction port (not shown) that is composed of a movable scroll 21 and a movable scroll 22 and communicates with the suction pipe 11.
And a compression element 2 having a discharge port 23 therein, a motor 3 having a rotor 31 and a stator 32 is installed above the compression element 2, and the rotor 31 of the motor 3 has an eccentric recess on the lower end side. The drive shaft 4 having the insertion portion 41 is held, and the eccentric concave insertion portion 41 of the drive shaft 4 is fitted to the boss portion 24 projecting on the back surface of the movable scroll 22 via the slide bearing 5, The rotation of the drive shaft 4 causes the movable scroll 22 to orbit with respect to the fixed scroll 21. A balance weight 42 that counteracts the centrifugal force acting on the eccentric concave portion 41 is provided on the lower end side of the drive shaft 4 for static balance, and the upper end ring 33 of the rotor 31 has the eccentric concave portion. A balance weight 34 having a semicircular diameter on which centrifugal force acts in the same direction as the insertion portion 41 is provided so as to achieve dynamic balance.

Further, a lower bearing housing 7 holding a slide bearing 6 in the central portion is arranged between the compression element 2 and the motor 3, and the drive shaft is attached to the slide bearing 6 of the lower bearing housing 7. 4 rotatably supports the lower shaft end portion of the drive shaft 4, and an eccentric shaft portion 43 is provided above the support portion of the drive shaft 4 for supporting the slide bearing 6, and the eccentric shaft portion 43 and the lower bearing housing 7 are provided. A positive displacement oil pump 8 that operates by rotation of the drive shaft 4, for example, an oil pump such as a trochoid pump having meshing teeth on its inner peripheral surface and outer peripheral surface is provided between The slide bearings 5 and 6 and the thrust surface on the back side of the movable scroll 22 are lubricated.

Also, on the back side of the fixed scroll 21,
The discharge chamber 10 defined by the partition wall 9 is provided, and the discharge chamber 1 is provided.
The discharge port 23 is opened at 0, and the fixed scroll 21 and the lower bearing housing 7 are formed with a discharge gas passage 13 that communicates the discharge chamber 10 with the motor side chamber 1a of the casing 1.

An upper bearing housing 14 having a downward recessed portion 14a at the center is attached to the upper side of the motor 3 in the closed casing 1, and the recessed portion 1 is provided.
The upper shaft end of the drive shaft 4 is rotatably supported by an upper bearing 15 held by 4a, and the discharge pipe 12 is opened in the upper wall of the casing 1. The upper bearing housing 14 has a plurality of fitting portions 14b fitted to the inner circumference of the casing 1, and a discharge gas passage 16 is formed between the fitting portions 14b.

Therefore, in the embodiment shown in FIG. 1, in the compressor constructed as described above, the central portion of the drive shaft 4 is communicated with the oil supply pump 8 through the communication passage 17.
In addition, a forced oil supply passage 18 communicating with the upper bearing 15 via the recess 14a is provided to forcibly supply lubricating oil from the oil supply pump 8 to the upper bearing 15, and the motor 3 At the outer peripheral surface of the rotor 31 in, the concave spiral groove 19 for forcibly returning the oil after supplying the upper bearing 15 downward from the upper side of the rotor 31.
Is provided.

As shown in FIGS. 1 and 2, one spiral groove 19 extends from the upper end to the lower end of the rotor 31 in the direction opposite to the direction of rotation of the rotor 31 (the direction of the arrow in FIG. 2). Alternatively, a plurality of lubricating oils are formed, and a screw pump action is exerted between the outer peripheral surface of the rotor 31 and the inner peripheral surface of the stator 32, so that the lubricating oil dropped from the upper bearing 15 into the upper space 1b of the rotor 31 is discharged from the spiral groove 19. Oil is returned to the lower side of the rotor 31.

Further, in the above structure, the discharge gas passage 1 is provided in the lower bearing housing 7 as shown in FIG.
An annular gas guide plate 20 for guiding the discharge gas discharged from the motor 3 to the motor side chamber 1a to a gas passage 36 between the core cut on the outer peripheral surface of the stator 32 and the inner peripheral surface of the casing 1 is attached to the discharge gas. It is preferable to prevent the discharge gas discharged from the passage 13 to the motor side chamber 1a from flowing through the air gap 35. Although the gas guide plate 20 is formed so as to expand in diameter upward from the mounting portion to the lower bearing housing 7, it may be straight.

Further, on the inner peripheral surface of the upper coil end 37 of the motor 3, a taper surface 37a which expands downward as shown in FIG. 1 is provided at a portion facing the balance weight 34.
After lubricating the upper bearing 15, the oil discharged downward from the upper bearing 15 is splashed outward by the balance weight 34 in the radial direction of the drive shaft, and the oil is discharged to the tapered surface 37a. The oil mixed with the discharge gas is separated by the collision, and the separated oil is moved downward by the tapered surface 37a. The coil end 37 is provided with an inverse taper surface 37b which is continuous with the lower end of the taper surface 37a and whose diameter is reduced downward so as to guide the separated oil to the outer periphery of the upper end portion of the rotor 31. Preferably.

The forced oil supply passage 18 is formed so as to penetrate the drive shaft 4 as shown in FIG.
The communication passage 17 that connects the forced oil supply passage 18 to the oil supply pump 8 is a passage formed between the outer peripheral surface of the lower shaft end portion of the drive shaft 4 and the inner peripheral surface of the slide bearing 6, as shown in FIG. 17a and a passage 17b formed between the outer peripheral surface of the boss portion 24 and the inner peripheral surface of the slide bearing 5, but in addition, the communication passage 17 is formed by the drive shaft as shown in FIG. Radial passage 1 provided on the eccentric shaft portion 43 of 4
You may form by 7c.

In the embodiment shown in FIG. 1, an annular cover 50 for covering the balance weight 42 is attached to the lower bearing housing 7, and oil is returned from the spiral groove 19 to the motor side chamber 1a. Oil is the balance weight 4
In order to prevent stirring by 2, the oil return receiving chamber 52 is provided between the inside of the gas guide plate 20 and the lower bearing housing 7, and the fixed scroll 21 and the lower bearing housing 7 are provided. And an oil pumping passage 51 that connects the bottom oil sump 1c of the casing 1 and the oil supply pump 8 to each other.
And an oil return passage 53 communicating with the oil return receiving chamber 52.

In the compressor constructed as described above, the drive shaft 4 is driven by the motor 3 to cause the movable scroll 22 in the compression element 2 to orbit with respect to the fixed scroll 21, and the discharge port 23 to the discharge chamber. The discharge gas discharged into the motor side chamber 1a through the gas discharge passage 10 and the discharge gas passage 13 is guided to the gas passage 36 by the gas guide plate 20, and the upper bearing housing 1 is passed through the gas passage 36.
The gas is discharged from the discharge pipe 12 to the outside through the discharge gas passage 16 of No. 4 and the upper chamber of the casing 1.

On the other hand, as the drive shaft 4 rotates, the oil supply pump 8 provided at the lower part of the drive shaft 4 operates, and the upper bearing housing passes from the oil supply pump 8 through the communication passage 17 and the forced oil supply passage 18. Lubricating oil can be supplied to the upper bearing 15 of 14.

As described above, the lubricating oil is forcibly supplied to the upper bearing 15, so that there is no oil shortage, and the bearing 1
The reliability of No. 5 can be improved, and as the upper bearing 15, an inexpensive and low-noise slide bearing can be used.

After lubricating the upper bearing 15, the oil discharged downward from the upper bearing 15 is splashed outward in the radial direction of the drive shaft 4 by the rotation of the balance weight 34 provided on the rotor 31. And collides with the tapered surface 37a of the coil end 37, is guided downward by the tapered surface 37a, flows into the spiral groove 19 of the rotor 31 from the upper end portion of the stator 32, and by the screw pump action of the spiral groove 19, Oil is returned to the bottom oil sump 1c from the oil return receiving chamber 52 and the oil return passage on the lower side of the rotor 31.

Therefore, the amount of the oil supplied to the upper bearing 15 mixed with the discharge gas and rising from the discharge pipe 12 to the refrigeration system side can be extremely reduced, and the rotor 31 of the motor 3 can be spirally grooved. Since it is a simple structure in which only 19 is provided, the structure can be simplified as compared with the case of providing an oil separator such as a demister, the cost can be reduced, and the height of the entire compressor can be prevented from increasing. Of.

Further, since the discharge gas discharged from the discharge gas passage 13 to the motor side chamber 1a is guided to the gas passage 36 by the gas guide plate 20, the discharge gas is discharged between the rotor 31 and the stator 32. Therefore, it is possible to prevent the oil after lubrication from being returned from the spiral groove 19 to the oil supply pump side.

Although the forced oil supply passage 18 is formed in the drive shaft 4 in the above-described embodiment, the forced oil supply passage 18 may be provided, for example, from the lower bearing housing 7 through the gas passage 36 to the upper bearing housing. It may be formed by a tube reaching 14 or the like.

Further, the compressor of the present invention may be a compressor having a scroll type compression element, and may be a compressor having a rotary type compression element.

[0028]

As described above, according to the present invention, the vertical closed casing 1 is internally provided with the compression element 2, the upper portion of the compression element 2 is provided with the motor 3 having the drive shaft 4, and In a vertical compressor in which a bearing 15 of the drive shaft 4 is provided in an upper part and an oil supply pump 8 is provided in a lower part of the drive shaft 4, a forced oil supply passage 18 communicating with the oil supply pump 8 and supplying oil to the bearing 15 is provided. Since it is possible to forcibly supply oil to the upper bearing 15 from the oil supply pump 8, the reliability of the bearing 15 can be improved, and as the bearing 15,
While it is possible to use plain bearings that are inexpensive and have low noise,
Moreover, on the outer peripheral surface of the rotor 31 of the motor 3,
Since the spiral groove 19 for forcibly returning the oil supplied to the bearing 15 downward is provided, the oil after lubrication is returned from the spiral groove 19 to the oil supply pump side without providing an oil separator such as a demister. Oil can be produced, and the amount of oil that rises to the refrigeration system side can be reduced. Further, since the rotor 31 of the motor 3 has a simple structure in which only the spiral groove 19 is provided, the cost can be reduced and the height of the entire compressor can be increased as compared with the case where an oil separator such as a demister is provided. Can be avoided.

Further, between the compression element 2 and the motor 3, the discharge gas discharged from the discharge port 23 of the compression element 2 into the casing 1 is discharged between the stator 32 of the motor 3 and the casing 1. Gas passage 3 formed
By providing the gas guide plate 20 that guides the discharge gas to the air gap 6, it is possible to avoid the discharge gas from flowing into the air gap between the rotor 31 and the stator 32, and the oil after lubrication is supplied from the spiral groove 19 to the oil supply pump. The oil can be satisfactorily returned to the side.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a compressor of the present invention.

FIG. 2 is a perspective view of only a rotor of the motor.

FIG. 3 is a partially omitted cross-sectional view showing another embodiment.

FIG. 4 is a cross-sectional view showing a conventional example.

[Explanation of reference numerals] 1 closed casing 2 compression element 3 motor 31 rotor 32 stator 4 drive shaft 8 oil supply pump 18 forced oil supply passage 19 spiral groove 20 gas guide plate 36 gas passage

Claims (2)

[Claims] 1. A compression element 2 is provided at the bottom of a vertical closed casing 1.
And a motor 3 having a drive shaft 4 in the upper part of the compression element 2, and the drive shaft 4 in the upper part of the motor.
The bearing 15 is provided, and the oil supply pump 8 is provided below the drive shaft 4.
In the vertical compressor provided with, the forced oil supply passage 18 that communicates with the oil supply pump 8 and supplies oil to the bearing 15 is provided, and the oil that has been supplied to the bearing 15 is forced downward to the rotor 31 of the motor 3. Spiral groove to return oil to
A vertical compressor characterized by having 9. 2. Discharge gas discharged between a compression element 2 and a motor 3 into a casing 1 from a discharge port 23 of the compression element 2 is discharged between a stator 32 of the motor 3 and the casing 1. The vertical compressor according to claim 1, further comprising a gas guide plate (20) for guiding the formed gas passage (36).