KR20000008561A - Bearing supporter of turbo compressor - Google Patents

Abstract

PURPOSE: A bearing supporter is provided to promote the life and the stability of a bearing part by preventing the degradation due to the overload of the bearing part. CONSTITUTION: A bearing supporter comprises:a penetration hole(4) formed in the middle of a bearing supporter(3); plural spaces(5) overlapped on the circumference of the bearing supporter to prevent the deformation of the bearing part and to absorb the shock generated when a drive shaft(6) rotates at high speed.

Description

Bearing supporter of turbo compressor

The present invention relates to a bearing supporter of a turbo compressor, and more particularly, to minimize a phenomenon in which a bearing part is deformed by an eccentric load and rotation of a drive shaft installed in a turbo compressor, as a bearing supporter.

In general, a compressor is a device for compressing a gas such as air or refrigerant gas, and the compressor is a power generating unit for generating large power and a compression mechanism unit for sucking and compressing gas by a driving force transmitted from the power generating unit. The compressor is divided into a hermetic compressor provided together with a power generating section and a compression mechanism section in a sealed container having a predetermined internal volume, and a separate compressor having the power generating section and the compression mechanism section separated.

The hermetic compressor includes a rotary compressor (also called a rotary compressor), a reciprocating compressor, and a scroll compressor due to the structure of compressing the gas. Expression

In the volumetric compressor, the rotary compressor is configured to pressurize the gas as the eccentric shaft rotates inside the cylinder in which the cylindrical space is formed, thereby reducing the volume of the internal space. The reciprocating compressor has a piston in the cylinder. It is a structure that pressurizes the gas as the volume of the inner space is reduced while reciprocating, and the scroll compressor reduces the inner space volume while the upper and lower scrolls having the involute curved wrap are engaged with each other to rotate. Therefore, the gas is pressurized.

The rotary compressor and the reciprocating compressor generate periodic vibration and noise in the process of periodically pressurizing the gas and have low efficiency, while the manufacturing cost is low, and the scroll compressor has vibration and noise in the process of continuously pressurizing the gas. High efficiency, high number of parts used, high manufacturing cost, high volume refrigerant volume, relatively large volume, and relatively heavy weight for home appliances such as refrigerators and air conditioners. When applied, not only the size of the applied home appliances is large, but also the weight is heavy, making it difficult to handle.

On the other hand, in recent years, as a device for compressing gas by rotating a vane, a turbo compressor having a high compression efficiency for compressing gas has been proposed, which is not only small in size but also has fewer parts to be used in home appliances. 1 to 4, when a current is applied to the drive motor 7, the drive force of the drive motor 7 is transmitted to the drive shaft 6 as the drive motor 7 is operated, as shown in FIGS. 1 to 4. As the 6 is rotated, the first and second impellers 7 and 8 coupled to the both ends of the drive shaft 6 are rotated by the rotation of the drive shaft 6, and the first and second impellers are rotated. (7) By the rotational force of the low-temperature and low-pressure refrigerant gas through the evaporator (not shown) flows into the motor chamber (10) through the inlet (9) to cool the drive motor (7) , The first gas oil through the outflow hole 11 formed at one side of the motor chamber 10. It is introduced into (12).

Thereafter, the refrigerant gas introduced into the first gas passage 12 is first compressed into the first compression chamber 13 and then compressed in the second compression chamber 15 through the second gas passage 14. Secondarily compressed and discharged through the discharge port 16 in a high pressure state, the discharged high-pressure refrigerant gas is introduced into a condenser (not shown).

In the first compression chamber 13, the refrigerant gas is first compressed, and the refrigerant gas introduced into the first gas passage 12 is introduced into the first impeller chamber 18 through the inducer unit 17. In addition, the refrigerant gas introduced into the first impeller chamber 18 not only increases the kinetic energy but also slightly increases the static pressure due to the rotational force of the first impeller 7, and the refrigerant gas in this state is the vane diffuser 19. Passing through the volute unit 20 and the kinetic energy of the refrigerant gas is converted into a constant pressure to increase the pressure.

The process of the second compression of the refrigerant gas first compressed in the second compression chamber 15 is the same as the process of compressing the refrigerant gas in the first compression chamber 13. Thus, the first compression and the second compression process are performed. The coarse refrigerant gas is in a high pressure state, and the rear surfaces of the first and second impellers 7 and 8 of the first and second compression chambers 13 and 15 are blocked by the sealed container 1, and the refrigerant gas is The pressure of the first inducer portion 17 of the first compression chamber 13 introduced and the pressure of the motor chamber 10 are almost the same, and the second inducer portion 21 and the motor of the second compression chamber 15 are substantially the same. Although there is a pressure difference between the seals 10, the leakage of the compressed refrigerant is minimized because it is sealed by the axial support means 22.

The first and second compression chambers 13 and 15 respectively rotate the first and second impellers 7 and 8 that compress the refrigerant gas while being rotated in the both ends of the drive shaft 6. Force in one axial direction or in both axial directions is caused by the pressure in the second compression chamber 15 and the pressure difference in the second compression chamber 15, which is supported by the axial support means 22 coupled to one side of the drive shaft 6 to prevent the bias. It is rotated stably without, the axial support means 22 is in contact with the bearing surface on both sides of the fixed plate and the inner support plate 23 and the outer support plate 24 coupled to the drive shaft 6 is the drive shaft 6 When rotating, the drive shaft 6 is supported so that it can rotate stably without movement in the axial direction.

In addition, since the driving shaft 6 is radially supported by the radial supporting means 25 coupled to the driving shaft 6 so as to be located at both sides of the driving motor 7, the radial direction during the rotation of the driving shaft 6. It is rotated while being stably supported, the radial support means 25 is the bush 26 and the bearing housing (2) to maintain the gas bearing is suitable for high-speed rotation of the drive shaft (6) and also occurs during high-speed rotation Possible vibrations are fixed to the inside of the hermetic container 1 and are absorbed by the bearing supporter 3a for supporting the bearing housing 2 so as to stably support the drive shaft 6.

The drive motor 7 for driving the drive shaft 6 is a radial type BIDL motor which is suitable for generating high-speed rotation. As an example of such a BILD motor, a plurality of stator 27 of a disk-shaped stator made of resin can be used. Two winding coils are attached, and a plurality of magnets are attached to the disc-shaped rotor 28 so that the stator 27 and the rotor 28 are alternately formed. In addition to high efficiency, the output of the drive motor 7 can be easily increased by increasing the number of discs of the stator 27 and the rotor 28.

On the other hand, when the conventional turbo compressor is driven, the drive shaft 6 receives an eccentric load, and this eccentric load is transmitted to the conventional bearing supporters 3a and 3b shown in Figs. And as shown in Figure 6b the deformation caused by the eccentric load is generated, the table below is calculated by the deformation of the load applied to the conventional bearing supporter (3a) (3b) through the experiment The results are as follows.

Maximum deformation amount (㎛) Stiffness (N / m) Conventional Bearing Supporter 0.223 67.3e + 6 Conventional Bearing Supporter 0.403 29.6e + 6

When designing the bearing supporter, the bearing supporter should be designed so that the stiffness of the bearing supporter is less than the stiffness of the bearing (3e + 6 N / m) to prevent the deformation of the bearing part.

However, as shown in the above experimental results, since the stiffness of the conventional bearing supporters 3a and 3b is larger than the stiffness of the bearing, the deformation of the bearing portion cannot be effectively suppressed, and in severe cases due to the overload of the bearing portion, There was a problem such that the performance of the performance is degraded to reduce the service life of the bearing portion.

Therefore, the present invention is to solve the above-mentioned problems, the phenomenon that the deformation of the bearing portion caused by the eccentric load and rotation of the drive shaft installed in the turbo compressor can be minimized as a bearing supporter performance due to the overload of the bearing portion It is an object of the present invention to provide a bearing supporter of a turbo compressor that can improve the service life of the deterioration can be effectively prevented.

1 is a longitudinal sectional view showing a conventional turbo compressor.

2 is a longitudinal sectional view showing the impeller and the compression chamber of FIG.

3 is a cross-sectional view taken along the line A-A of FIG.

4 is a cross-sectional view taken along the line B-B of FIG.

Figure 5a is a front view showing a conventional bearing supporter

5B is a front view showing a state when the deformation of FIG. 5A occurs.

Figure 6a is a front view showing another conventional bearing supporter

6B is a front view showing a state when the deformation of FIG. 6A occurs.

Figure 7a is a front view showing the present invention

7B is a front view showing a state when the deformation of FIG. 7A occurs.

Explanation of symbols on the main parts of the drawings

One; Closed container 2; Bearing housing

3; Bearing supporter 4; Through hole

5; Space

In order to achieve the above object, the present invention is a bearing supporter of a turbo compressor fixed to support a bearing housing while absorbing vibration generated during high-speed rotation of the drive shaft inside the sealed container, formed in the center of the bearing supporter It is achieved by providing a bearing supporter of a turbocompressor, characterized in that a space is formed on the outer periphery of the bearing supporter around the through hole so that the stiffness of the bearing supporter is less than the stiffness of the bearing to prevent deformation of the bearing portion.

Here, the space portion is characterized in that a plurality is formed so as to overlap each other on the outer periphery of the bearing supporter around the through hole.

Hereinafter, preferred embodiments of the present invention for achieving the above object will be described in detail with reference to the accompanying drawings.

FIG. 7A is a front view showing the present invention, and FIG. 7B is a front view showing the state when the deformation of FIG. 7A occurs, and the same parts as in the prior art are denoted by the same reference numerals to describe the present invention.

The present invention is the outer periphery of the bearing supporter (3) around the through hole (4) formed in the center of the bearing supporter (3) for fixing the inside of the hermetic container (1) of the turbo compressor to support the bearing housing (2) A plurality of spaces 5 are formed so that the stiffness of the bearing supporter 3 is less than the stiffness of the bearing so as to overlap each other to prevent deformation of the bearing portion.

In the present invention configured as described above, as shown in FIGS. 7A and 7B, the drive shaft 6 receives an eccentric load when the turbo compressor is driven, and this eccentric load is the bearing supporter 3 of the present invention shown in FIG. 7A. As shown in FIG. 7B, the deformation caused by the eccentric load is generated as shown in FIG. 7B. The following table calculates the deformation due to the load applied to the bearing supporter 3 of the present invention through experiments. The results of the experiment are as follows.

Maximum deformation amount (㎛) Stiffness (N / m) Bearing supporter of the present invention 0.069 2.17e + 6

Therefore, as can be seen from the table, a plurality of spaces 5 are formed so as to overlap each other on the outer periphery of the bearing supporter 3 around the through hole 4 formed in the center of the bearing supporter 3 of the present invention. The bearing supporter 3 can be designed such that the stiffness of one bearing supporter 3 is less than the stiffness of the bearing ((3e + 6 N / m), which can prevent deformation of the bearing part, and the drive shaft according to the operation of the turbo compressor 6 Vibration generated at the high speed of rotation) can be efficiently absorbed by the spring effect of the plurality of spaces 5 formed in the bearing supporter 3 can stably support the drive shaft 6 in the radial direction. Since the bearing supporter 3 having the structure can move more than the bearing housing 2, the stability of the bearing part can be improved.

As described above, the present invention is fixed to the inside of the hermetic container installed in the turbo compressor is a plurality of so as to overlap each other on the outer periphery of the bearing supporter centered on the through-hole formed in the center of the bearing supporter for supporting the bearing housing As the space part is formed, the stiffness of the bearing supporter is smaller than the stiffness of the bearing, so that the deformation of the bearing part due to the eccentric load and rotation of the drive shaft can be minimized as the bearing supporter, which effectively reduces the performance deterioration due to the overload of the bearing part. It is a very useful invention equipped with many advantages, such as to improve the service life and stability of the bearing part can be prevented.

Although the preferred embodiments of the present invention have been illustrated and described above, the present invention is not limited to the above-described embodiments, and the present invention may be commonly used in the technical field to which the present invention pertains without departing from the gist of the present invention as claimed in the following claims. Anyone with knowledge will be able to make various changes.

Claims (2)

A bearing supporter of a turbo compressor fixed to support a bearing housing while absorbing vibration generated during high speed rotation of a drive shaft inside an airtight container, wherein an outer periphery of the bearing supporter is formed around a through hole formed in the center of the bearing supporter. The bearing supporter of the turbo compressor characterized in that the space portion is formed to prevent the deformation of the bearing portion so that the stiffness of the bearing supporter is less than the stiffness of the bearing. The bearing supporter of claim 1, wherein a plurality of the space parts are formed to overlap each other on the outer circumference of the bearing supporter with respect to the through hole.