KR19990040633A - Thrust bearings in hermetic reciprocating compressors - Google Patents

Abstract

The present invention relates to a thrust bearing of a hermetic reciprocating compressor, in which an insertion hole into which the crankshaft is inserted is formed in the center to support a load of the crankshaft and supply lubricating oil, and a plurality of spiral oil grooves are formed on the outer circumferential surface thereof. In the thrust bearing of the reciprocating compressor, the inclined surface 10 is formed to be inclined toward the insertion hole 552 formed in the upper surface of the thrust bearing 550, providing a thrust bearing of the hermetic reciprocating compressor, The present invention relates to a thrust bearing of a hermetic reciprocating compressor which increases the load supporting action of the crankshaft rotated in the main body of the compressor and improves lubrication, as well as allowing the crankshaft and the rotational center to operate smoothly.

Description

A thrust bearing of enclosed reciprocating compressor.

The present invention relates to a thrust bearing of a hermetic reciprocating compressor, and in more detail, increases the load supporting action of the crankshaft rotated in the main body of the hermetic reciprocating compressor and improves lubrication, as well as acting to match the crankshaft and the center of rotation. It relates to a thrust bearing of the hermetic reciprocating compressor to ensure a smooth rotation.

In general, the compressor compresses the heating medium during the four processes of air conditioning cycle, condensation, expansion, and evaporation, that is, converts the heating medium into a gaseous heating medium of high temperature and high pressure and sends it to the next stage. According to the method, it is divided into volume compression type, that is, reciprocating compressor, screw compressor, rotary compressor, and centrifugal turbo compressor.

The compressor is classified into an open type, a closed type, and a semi-sealed type according to its appearance, and is classified into a water cooling type and an air cooling type by a cooling method, classified into low, medium, and high speed according to the rotational speed, and classified into a short passage and a multi cylinder by the number of cylinders. .

Among the compressors divided into various forms as described above, in the present application, a sealed reciprocating compressor will be described as an example as shown in FIGS. 3 and 4. The electric motor and the compressor are sealed by the upper case 51 and the lower case 52. The inside of the main body frame 55, which is supported by the support bar 54 by the compression spring 53 or the leaf spring for the purpose of proper dustproof and soundproof means is built.

The main body frame 55 is capable of reciprocating the cylinder block 58 and the cylinder 58a therein to the upper end of the crankshaft 57 to which the motor unit 56 having the stator and the rotor are fixed. The piston 59 is installed, and the suction and discharge valve bodies 60 provided at the left end of the cylinder block 58 are installed by the reciprocating motion of the piston 59 to inhale low pressure and low temperature refrigerant gas, High temperature refrigerant gas is discharged.

The suction and discharge valve body 60 is composed of a flapper or reed type thin plate structure which is usually elastic for miniaturization, and the flapper or lead type suction and discharge valve body 60 is double-sided. It is opened and closed passively by the pressure difference acting on.

The sealed reciprocating compressor 50 configured as described above has a suction pipe 61 and a suction muffler fixed to the lower pressure / low temperature refrigerant gas to be sealed to the upper or lower cases 51 and 52 during the backward movement of the piston 59. 62 is introduced into the suction chamber of the discharge muffler 64 from the external evaporator (not shown) to the suction lead valve of the suction and discharge valve body 60, and then flows into the cylinder 58a and the piston 59. During the forward movement of the high-pressure and high-temperature refrigerant gas discharged from the compressor is passed through the discharge muffler 64 from the discharge valve of the suction and discharge valve body 60 to the upper or lower case 51 and 52. It is sent to an external condenser (not shown) via the discharge tube 65 fixedly sealed.

Reference numeral 67 is hermetically fixed to the lower case 52 by the refrigerant filling pipe and initially seals the refrigerant gas after filling the inside.

The noise of the hermetic reciprocating compressor 50 is generated by the reciprocating motion of the piston 59, the opening and closing shock of the suction and discharge valve body 60, the pulsation of the suction gas and the discharge pressure, and the like. In order to reduce noise caused by the pulsation of the suction and discharge pressure, the refrigerant gas introduced into the suction pipe 61 is discharged through the suction muffler 62 while being filled in the upper and lower cases 51 and 52. ) Is sucked into the cylinder (58a) through the suction chamber, and the refrigerant compressed in the cylinder (58a) is discharged to the discharge tube (65) through the first discharge chamber and the second discharge chamber of the discharge muffler (64).

On the other hand, the motor portion 56 is composed of a stator 68 is fixed to the lower portion of the body frame 55 and the rotor 69 rotates with a gap with the stator 68 (see Fig. 4), This rotor 69 is fixed to the crankshaft 57 and rotatably supported by the body frame 55 to rotate together.

At the end of the crankshaft 57 of the electric motor unit 56, an eccentric shaft 57a is formed to protrude upward from the main body frame 55 so that the piston 59 is the piston rod 59a and the eccentric shaft thereof. By connecting to 57a, the piston 59 reciprocates by the amount of eccentric rotation of the eccentric shaft 57a. In addition, an external power source is applied to the winding coil of the stator 68 of the motor unit 56 by installing external terminals 70 which are hermetically fixed to the upper and lower cases 51 and 52.

In order to smoothly operate the compressor and the driving motor operated as described above, a coolant oil storage tank 52a for storing coolant oil is formed at the bottom of the lower case 52 along the lubricating oil supply groove 57b of the crankshaft 57. While being sucked to the top, the refrigerant oil was supplied to each lubrication part to enable lubrication.

When describing the process in which the refrigeration oil is injected in more detail, the refrigeration oil stored in the oil reservoir 52a of the lower case 52 is sucked upward along the lubricating oil supply groove 57b by the centrifugal force of the crankshaft 57. The eccentric shaft 57a is sequentially supplied to the journal bearing portion 55a formed in the main body frame 55 and then supplied to the thrust bearing 55b and then vertically penetrated into the eccentric shaft 57a. By lowering the temperature of the superheated refrigeration oil through the above-described process by spraying to the bearing portion and the upper case 51 of the c) is returned to the reservoir tank 52a formed on the bottom surface of the compressor.

The conventional thrust bearing 55b for supplying lubricating oil while supporting the load of the crankshaft 57 in the process of being constructed and operated as described above has the surface contact as most are formed of flat discs as shown in FIG. 5. Due to the oil film is formed by the problem that the smooth supply of lubricating oil, and the problem of supporting the load of the crankshaft 57 due to the oil film has a weak problem.

In addition, the oil film does not coincide with the center of rotation of the crankshaft 57 but is eccentrically connected to one side, thereby causing a problem in that the smooth rotation is not performed.

As described above, in order to solve the problem, a thrust bearing 550 having a spiral oil groove 550a spreading opposite to the center thereof is formed on a flat disc as shown in FIG. 6, but an oil film is formed by surface contact to crank the crank. The problem of not supporting the load of the shaft 57 and the spiral oil groove 550a is formed in comparison with the plane contact of the plane, so that the lubricant is smoothly supplied compared to the thrust bearing 55b. As described above, the rotation of the crankshaft 57 may not be smoothly solved because the center of rotation of the crankshaft 57 does not coincide with the rotational center of the crankshaft 57.

Accordingly, the present invention has been made to solve the above problems, and increases the load supporting action of the crankshaft rotated in the main body of the hermetic reciprocating compressor and improves the lubricating action, as well as acting to match the crankshaft and the center of rotation The purpose is to ensure smooth rotation.

The present invention for achieving the above object is a hermetic reciprocating compressor provided with a plurality of spiral oil grooves are formed in the insertion hole is inserted into the center of the crank shaft is inserted in the center to support the load of the crank shaft and supply lubricating oil In the thrust bearing of the, characterized in that the upper surface of the thrust bearing is formed to have an inclined surface inclined toward the insertion hole formed in the center.

1 is a schematic perspective view of a main part of a thrust bearing of the present invention;

2 is a schematic cross-sectional view of the main part according to FIG. 1;

Figure 3 is a schematic plan view showing the configuration of a general hermetic reciprocating compressor.

4 is a schematic longitudinal section in accordance with FIG. 3;

5 is a perspective view illustrating main parts of the thrust bearing installed in FIGS. 3 and 4;

6 is another embodiment of a conventional thrust bearing.

Explanation of Signs of Major Parts of Drawings

10: slope 55b, 550: thrust bearing

57: crankshaft 550a: spiral oil groove

552: insertion hole

Hereinafter, the preferred embodiment of the present invention with reference to the accompanying drawings as follows.

Figure 1 is a schematic perspective view of the main part of the thrust bearing of the present invention, Figure 2 is a schematic sectional view of the main part according to Figure 1, the insertion hole 552 is formed so that the crankshaft is inserted in the center and the outer peripheral upper surface Spiral oil groove 550a is formed to show a thrust bearing 550 formed to have an inclined surface 10 to be inclined toward the insertion hole 552 side.

The operation and effects of the present invention configured as described above will be described in more detail with reference to FIGS. 1 to 4 as follows.

The lubricating oil supplied along the lubricating oil supply groove 57b of the crankshaft 57 has an insertion hole 552 formed at the center thereof, and a spiral oil groove 550a is formed at the upper circumferential surface thereof to be inclined toward the insertion hole 552. When the inclined surface 10 is introduced into the formed thrust bearing 550, the length of the oil groove 550a of the thrust bearing 550 of the present invention formed on the inclined surface than the length of the spiral oil groove 550a on the conventional plane is increased, so that the lubricating oil By ensuring a large amount of, can be smooth lubrication.

In addition, the problem that the rotational center of the crankshaft 57 is eccentrically generated due to the surface contact of the plane is that the inclined surface 10 is inclined toward the insertion hole 552 formed at the center of the upper surface of the thrust bearing 550. Since the surface contact is not made in relation to the oil film layer, the center of rotation with the crankshaft 57 can be prevented from being eccentrically operated.

In addition, as described above, the crankshaft 57 and the rotational center do not act eccentrically, and thus have a condition that can increase the load supporting action as compared with the related art.

As described above, the upper surface of the thrust bearing having a spiral oil groove formed on the hermetic reciprocating compressor is inclined, thereby increasing the lubrication effect, increasing the load supporting action of the crankshaft, and smoothly rotating in accordance with the rotation center. .

Although the present invention has been described with reference to one embodiment shown in the drawings, this is merely exemplary, and it will be understood by those skilled in the art that various modifications and equivalent other embodiments are possible.

Therefore, the true technical protection scope of the present invention should be defined only by the appended claims.

Claims (1)

In the thrust bearing of the hermetic reciprocating compressor, in which an insertion hole into which the crankshaft is inserted is formed at the center to support the load of the crankshaft and supply lubricating oil, and a plurality of spiral oil grooves are formed on the outer circumferential surface thereof. Thrust bearing of the hermetic reciprocating compressor, characterized in that the inclined surface 10 is formed to be inclined toward the insertion hole 552 formed in the center of the upper surface.