KR20210129950A - A compressor - Google Patents

Abstract

The present invention relates to a compressor, comprising a heating unit that is provided on one surface of a case, is located closer to a discharge unit than a driving unit, and heats a refrigerant discharged from a compression unit. An object of the present invention is to provide a scroll compressor capable of preventing excessive oil discharge to the discharge unit as a liquid refrigerant flows into an oil storage space even when the compressor is operated when the inside of the compressor is at a low temperature.

Description

Compressor {A compressor}

The present invention relates to a compressor. More particularly, it relates to a through-axis scroll compressor capable of reducing the amount of supplied liquid refrigerant from flowing from the upper part to the lower part of the compressor.

In general, a compressor is a device applied to a refrigeration cycle (hereinafter, referred to as a refrigeration cycle) such as a refrigerator or an air conditioner, and provides work necessary for heat exchange in the refrigeration cycle by compressing the refrigerant.

The compressor may be classified into a reciprocating type, a rotating seat type, a scroll type, etc. according to a method of compressing the refrigerant. Among them, the scroll compressor is a compressor in which a compression chamber is formed between the fixed lap of the fixed scroll and the orbiting lap of the orbiting scroll by engaging the orbiting scroll with the fixed scroll fixed in the inner space of the sealed container and rotating.

Compared to other types of compressors, the scroll compressor is continuously compressed through the interlocking scroll shape, so a relatively high compression ratio can be obtained, and the suction, compression, and discharge strokes of the refrigerant are smoothly continued to obtain a stable torque. For this reason, scroll compressors are widely used for refrigerant compression in air conditioners and the like.

Referring to Japanese Patent Publication No. 6344452, a conventional scroll compressor includes a case having an external appearance and having a discharge unit for discharging refrigerant, a compression unit fixed to the case to compress the refrigerant, and a compression unit fixed to the case to compress the refrigerant and a driving unit for driving the unit, and the compression unit and the driving unit are coupled to the driving unit and connected by a rotating shaft.

The compression unit includes a fixed scroll fixed to the case and having a fixed wrap, and a revolving scroll including a revolving wrap driven by being engaged with the fixed wrap by the rotation shaft. In such a conventional scroll compressor, the rotation shaft is eccentric, and the orbiting scroll is fixed to the eccentric rotation shaft and rotates. As a result, the orbiting scroll orbits (orbits) along the fixed scroll and compresses the refrigerant.

In such a conventional scroll compressor, a compression unit is provided under the discharge unit and a driving unit is provided below the compression unit. In general, the rotating shaft has one end coupled to the compression unit and the other end passing through the driving unit.

In the conventional scroll compressor, since the compression part is provided above the driving part and close to the discharge part, it is difficult to supply oil to the compression part. There were downsides. In addition, the conventional scroll compressor has a problem in that efficiency and reliability are deteriorated due to tilting of the scroll because the action points of the gas force generated by the refrigerant in the compressor and the reaction force supporting the same do not match.

In order to solve this problem, with reference to Korean Patent Application Laid-Open No. 10-2018-0124636, recently, a scroll compressor in which the driving unit is located below the discharge unit and the compression unit is located below the driving unit has appeared. .(aka, lower scroll compressor)

1 shows the structure of a conventional lower scroll compressor.

Referring to FIG. 1 , the conventional lower scroll compressor 10 is generally installed on a circuit of a refrigerant cycle including a condenser 2 , an expansion valve 3 , and an evaporator 4 .

In the lower scroll compressor, the driving unit 200 is provided closer to the discharge unit 121 than the compression unit 300 , and the compression unit 300 is provided farthest apart from the discharge unit 121 . In such a lower scroll compressor, one end of the rotating shaft 230 is connected to the driving unit 200 , and the other end is supported by the compression unit 300 , so that a separate lower frame for supporting the rotating shaft may be omitted, and one side of the case There was an advantage that the oil (P) stored in the can be directly supplied to the compression unit 300 without going through the driving unit 200 . In addition, when the rotating shaft 230 is connected through the compression unit 300 in the lower scroll compressor, the action points of the gas force and the reaction force coincide on the rotating shaft 230 to block the vibration of the scroll in the compression unit 300 and Efficiency and reliability were guaranteed by offsetting the overturning moment.

Referring to the right drawing, the compression unit 300 includes a main frame 310 that penetrates and supports the rotation shaft 230, and a fixed scroll 320 that is seated on the main frame 230 to form a compression chamber; and an orbiting scroll 330 provided in the compression chamber to compress the refrigerant.

When the refrigerant flows in from the inlet hole 325 provided on the side of the fixed scroll 320, the orbiting lap 333 provided in the orbiting scroll performs a turning motion in the fixed lap 323 lap provided in the fixed scroll. The refrigerant is compressed through the refrigerant, and the compressed refrigerant is discharged through a discharge hole 326 provided near the rotation shaft 230 .

At this time, a high-pressure region S1 is formed in the vicinity of the rotating shaft 230 due to the compressed refrigerant, and in the high-pressure region S1 , the refrigerant pushes the orbiting scroll 330 toward the driving unit 200 . causes Accordingly, in the scroll compressor, a back pressure chamber 350 is installed above the orbiting scroll 330 to offset the force through the oil supplied through the rotation shaft 230 and the refrigerant in contact with the main frame. can cause

The rotation shaft 230 raises the oil stored in the oil P through a plurality of oil supply holes 234a, 234b, 234c and a plurality of oil supply grooves 2341a, 2341b, and 2341c, and thus a main bearing 232a, an eccentric portion 232b. ), which is supplied to the fixed bearing 232c.

On the other hand, an intermediate pressure region V1 having a lower pressure than the high pressure region is formed on the outer peripheral surface of the back pressure seal 350 , and a low pressure region S2 is formed in the Oldham ring 330 provided for orbiting the orbiting scroll. can be formed. Using the pressure difference between the high pressure region S1 and the intermediate pressure region V1 or the low pressure region S2, the oil supplied from the supplied rotation shaft 230 is transferred to a delivery passage 339 and a fixed passage 329. It can be supplied to the fixed wrap and the orbiting wrap or the Oldham ring 340 through the . (So-called differential pressure refueling method can be applied.)

For example, the delivery passage 339 includes a turning input passage 3391 through which oil delivered from the first oil supply hole 234a or the first oil supply groove 2341a is introduced into the orbiting scroll, and the turning A connection flow path 3392 extending from the input flow path toward the outer circumferential surface of the orbiting scroll, and a branch flow path 3393 branching from the connection flow path 3392 toward the Oldham ring and extending to one surface of the orbiting scroll. can In addition, the fixed flow passage 329 includes an inflow passage 3291 through which the fixed flow passage 329 is provided inside the fixed side plate to communicate with the connection passage 3392 and through which the oil supplied to the delivery passage flows in, and the The fixed head plate may include a moving flow path 3292 and a lubricating oil path 3293 provided to communicate with the inflow path 3291 inside the fixed head plate to move the oil supplied to the inflow path to the fixed wrap 332 .

The delivery flow path 339 is provided to extend in the radial direction of the orbiting scroll 330 to deliver the oil supplied through the rotation shaft 230 to the outer peripheral surface of the fixed lap 323 of the fixed scroll 320, and the The fixed flow path 329 is provided to communicate with the transmission flow path 339 from the fixed scroll 320 to supply the oil supplied to the transmission flow path 339 up to the intermediate pressure region V1.

However, since the pressure difference between the high pressure region S1 and the intermediate pressure region V1 is large, the oil may be excessively supplied from the rotation shaft 230 . Accordingly, a problem may occur in that a sufficient amount of refrigerant is not compressed, the compression unit 300 is excessively cooled, or lubrication is not performed due to a large amount of oil flowing out.

To prevent this, the scroll compressor 300 may include a decompression unit 360 inserted into the delivery passage 330 to control the amount of oil supplied. The pressure reducing unit 360 reduces the cross-sectional area of the delivery passage 330 to generate flow resistance, thereby preventing excessive oil from being supplied.

Meanwhile, in the scroll compressor 300 , the refrigerant may pass through the compression unit 300 through the bypass hole 327 together with oil supplied through an oil supply passage provided in the rotation shaft. The refrigerant and oil passing through the compression unit 300 may pass through the driving unit 200 and reach the space between the driving unit 200 and the discharge unit, that is, the upper part of the case. The compressed refrigerant reaching the upper part of the case may be discharged through the discharge hole 121 .

However, before the compressor starts to operate, the temperature inside the compressor 10 may form a low temperature state. When the compressor 10 starts operating in a low temperature state, since the discharge superheat of the refrigerant is not secured, even if the refrigerant rises to the top of the case, the refrigerant may not be discharged to the discharge unit 121 . have. On the other hand, the oil that has risen to the upper part of the case like the refrigerant may be continuously discharged to the discharge unit 121 .

By operating the compressor in a low-temperature state, the oil is continuously discharged to the discharge unit 121, and the liquid refrigerant condensed without being discharged to the discharge unit 121 is disposed along the wall surface of the case 100 in the storage space ( P) can be introduced. The liquid refrigerant may continue to accumulate in the oil storage space P, and the amount of the oil may gradually decrease. After the compressor 10 is operated, when the internal temperature rises, the degree of superheat of the discharge of the refrigerant may be secured. When the discharge superheat of the refrigerant is secured, the liquid refrigerant may be vaporized in the refrigerants reaching the upper part of the case, and the oil mixed with the liquid refrigerant may also be discharged to the discharge unit 121 . The amount of the oil in the oil storage space may be further reduced.

When the amount of oil in the oil storage space (P) is reduced, the oil supply to the compression unit 300 may not be stably supplied. If the oil is not stably supplied to the compression unit 300 , wear of the compression unit 300 may occur, and an oil film may be formed between the fixed scroll 320 and the orbiting scroll 330 . Confidentiality may not be maintained. Also, it may not be possible to absorb frictional heat due to frictional force generated by the compression unit 300 .

Meanwhile, Patent Document 1 relates to a compressor having an oil temperature control function. Patent Document 1 discloses a compressor including an oil heating unit at the lower end of the compressor in order to improve the oil shortage phenomenon when the compressor is started in a low temperature state. The temperature of the oil may be measured through a temperature detection unit that detects the temperature of the oil inside the casing. When the temperature of the oil falls below the set temperature, the valve may be opened to allow heat exchange in the oil heating unit cycle.

However, since Patent Document 1 includes an oil heating unit capable of heating oil at the lower end of the compressor, there is a problem that the oil heating unit cannot be applied to the lower scroll compressor. In addition, Patent Document 1 does not disclose a structure such as a heat dissipation fin in the oil heating unit, so there is a problem in that heat cannot be effectively dissipated to the oil by increasing the surface area. In addition, Patent Document 1 has a problem in that the liquid refrigerant cannot be prevented from flowing into the oil storage space by directly heating the oil to secure the oil superheating degree.

Patent Document 1: Korean Patent Publication No. 10-2006-0119318 (2006.11.24)

An object of the present invention is to provide a scroll compressor capable of preventing excessive oil discharge to a discharge unit as liquid refrigerant flows into a storage space even when the compressor is operated when the inside of the compressor is low temperature. .

An object of the present invention is to solve and solve the problem of providing a scroll compressor in which a heating unit capable of vaporizing liquid refrigerant reaching a wall surface is additionally installed on the upper part of the compressor case even when the compressor is operated when the inside of the compressor is low temperature.

An object of the present invention is to provide a scroll compressor in which the temperature of the upper part of the compressor is higher than the vaporization temperature of the refrigerant and lower than the vaporization temperature of oil by installing a heating unit on the upper part of the compressor case.

An object of the present invention is to provide a scroll compressor in which oil can be normally supplied to a compression unit even when the compressor is operated at a low temperature inside the compressor.

An object of the present invention is to provide a scroll compressor capable of maintaining the flow rate of oil recovered in a storage space even when the internal temperature of the compressor increases after the compressor is operated.

In order to solve the above problems, the present invention provides a compressor equipped with a heating unit that is provided on the compressor case to vaporize the liquid refrigerant.

The present invention may provide a compressor having a heater for heating the refrigerant discharged from the compression unit in order to solve the above problems. The heater is provided on one surface of the case to provide heat so that the liquid refrigerant is vaporized. The heater may be applied in various forms capable of dissipating heat.

In order to solve the above problems, the present invention provides a compressor having a sensor unit on the inner circumferential surface of the case for measuring the temperature inside the case. The sensor unit may be provided to be sufficiently spaced apart from the heater so that it is hardly affected by the heat emitted by the heater.

In order to solve the above problems, the present invention provides a compressor in which the heater is provided on an inner circumferential surface of the case. The heating unit may be provided inside the case, and may include a heat dissipation unit dissipating heat supplied from the heater to the liquid refrigerant. The heat dissipation unit may be coupled to one surface of the heater to transfer heat supplied by the heater to the liquid refrigerant.

In order to solve the above problems, the present invention provides a compressor in which the heater is provided on an outer circumferential surface of the case. The heating unit may be provided inside the case, and may include a heat dissipation unit dissipating heat supplied from the heater to the liquid refrigerant. The heat dissipation unit may be coupled to an inner circumferential surface of the case corresponding to a position at which the heater is provided in the case, and may receive heat supplied by the heater from a nearby position and transmit it to the liquid refrigerant.

In order to solve the above problems, the present invention provides a compressor including a heater provided in a cable shape and provided along a circumferential surface of the case. The heater may be applied in various forms as long as it can emit heat.

In order to solve the above problems, the present invention provides a compressor including a heat dissipation unit made of a thermally conductive material in order to effectively disperse the heat supplied from the heater. The heat dissipation unit may further include a heat dissipation plate formed of a ring-shaped frame having an opening through which the refrigerant or oil may pass. The heat sink may be provided at a position corresponding to the heater in order to effectively receive heat conducted from the heater.

In order to solve the above problems, the present invention provides a compressor including a first temperature sensor provided between a discharge unit and a heat sink, and a sensor unit provided between a driving recovery passage and a heat sink and including a second temperature sensor. The first temperature sensor may measure the temperature of the refrigerant discharged to the discharge unit, and the second temperature sensor may measure the temperature of the refrigerant flowing into the driving recovery passage.

In order to solve the above problems, the present invention provides a compressor including a controller for controlling the heater so that the temperature of the heater is higher than the vaporization temperature of the refrigerant and lower than the vaporization temperature of the oil. The control unit may control the heater through the temperature of the refrigerant and oil measured by the sensor unit. There is provided a compressor in which the oil may be introduced into the oil storage space in a condensed state without being vaporized as the controller adjusts the temperature of the heater.

In order to solve the above problems, the present invention provides a compressor including a heat dissipation fin protruding from an inner circumferential surface of a heat dissipation plate. The heat dissipation fin may be coupled to the heat sink to receive heat conducted from the heat sink to supply heat to the liquid refrigerant. The heat sink may be applied in various forms capable of supplying heat to the liquid refrigerant.

More specifically, according to the present embodiments, a case having a discharge unit through which a refrigerant is discharged, a storage space in which oil is stored, a driving unit coupled to the inner circumferential surface of the case, a rotating shaft coupled to the driving unit and provided to rotate, the A compressor coupled to the rotating shaft to compress and discharge the refrigerant, and a heating unit provided on one surface of the case to heat the refrigerant discharged from the compression unit, wherein the heating unit is located closer to the discharge unit than the driving unit can provide

In addition, the heating unit is provided on one surface of the case to heat the refrigerant discharged from the compression unit, coupled to the inner circumferential surface of the case and provided to be spaced apart from the heater, including a sensor unit for measuring the temperature inside the case A compressor may be provided.

In addition, the heater may provide a compressor provided on the inner circumferential surface of the case. In addition, the heater may provide a compressor provided on the outer peripheral surface of the case.

And, the heating unit is provided inside the case, and comprises a heat dissipation unit dissipating heat supplied from the heater to the refrigerant, wherein the heat dissipation unit is coupled to one surface of the heater, and the other surface of the heat dissipation unit is the rotation shaft It is possible to provide a compressor that is provided to face the central direction of the axis.

In addition, the heating unit includes a heat dissipation unit provided inside the case to dissipate heat supplied from the heater and dissipate to the refrigerant, and one surface of the heat dissipation unit corresponds to a position where the heater is provided in the case. It is coupled with the inner peripheral surface of the, the other surface of the heat dissipation unit may provide a compressor that is provided to face the central direction of the axis of the rotation shaft.

In addition, the heater may be provided in the form of a cable, and the compressor may be provided along the circumferential surface of the case. In addition, the heat dissipation unit may provide a compressor made of a thermally conductive material in order to dissipate the heat supplied from the heater. In addition, the heat dissipation unit may provide a compressor including a heat dissipation plate provided as a ring-shaped frame having an opening through which the refrigerant or the oil passes.

In addition, the driving unit includes a driving return passage through which a portion of the outer circumferential surface of the driving unit is recessed and serves as a passage through which the oil passes, and the sensor unit is coupled to the inner circumferential surface of the case and is provided between the discharge unit and the heat sink. A first temperature sensor for measuring the temperature of the refrigerant discharged to the discharge unit and a second temperature sensor coupled to the inner circumferential surface of the case and provided between the drive return passage and the heat sink to measure the temperature of the refrigerant flowing into the drive return passage It is possible to provide a compressor including a temperature sensor.

In addition, the heating unit includes a control unit for controlling the heater so that the temperature of the heater is higher than the vaporization temperature of the refrigerant and lower than the vaporization temperature of the oil through the temperature of the refrigerant and the oil measured by the sensor unit A compressor may be provided. And the heat dissipation part further comprises a heat dissipation fin protruding from the inner circumferential surface of the heat dissipation plate and having a plate shape provided in parallel with the discharge direction of the coolant, wherein the heat dissipation fin is provided in the form of a plurality of plates spaced apart from each other by a predetermined distance, A distance between the plurality of heat dissipation fins may provide a compressor equal to a distance between one heat dissipation fin and the other heat dissipation fin.

In addition, the heat dissipation fin may provide a compressor that extends from an inner circumferential surface of the heat dissipation plate in the axial center direction of the rotation shaft. In addition, the heat dissipation fin may extend from the inner circumferential surface of the heat dissipation plate in the axial center direction of the rotation shaft and provide a compressor having a bent shape along the extension direction.

In addition, the heat dissipation unit may provide a compressor including heat dissipation fins extending from the inner circumferential surface of the heat dissipation plate in the axial center direction of the rotation shaft and having a cylindrical shape. In addition, it is possible to provide a compressor in which the heat dissipation fins are provided in a plurality of cylindrical shapes spaced apart from each other by a predetermined distance, and the cross-sectional area in the protruding direction of the heat dissipation fins decreases according to the extension length.

Each feature of the above-described embodiments may be implemented in combination in other embodiments as long as they are not contradictory or exclusive to other embodiments.

The present invention is effective in providing a scroll compressor capable of preventing excessive oil discharge to a discharge unit as liquid refrigerant flows into a storage space even when the compressor is operated at a low temperature inside the compressor.

The present invention is effective in providing a scroll compressor in which a heating unit capable of vaporizing liquid refrigerant reaching a wall surface is additionally installed on the upper part of the compressor case even when the compressor is operated at a low temperature inside the compressor.

The present invention is effective in providing a scroll compressor in which the temperature of the upper part of the compressor can be adjusted to be higher than the vaporization temperature of the refrigerant and lower than the vaporization temperature of oil by installing a heating unit on the upper part of the compressor case.

The present invention has an effect that oil can be normally supplied to the compression unit even when the compressor is operated when the inside of the compressor is low temperature.

The present invention has the effect of maintaining the flow rate of oil recovered in the oil storage space even when the internal temperature of the compressor increases after the compressor is operated.

Effects of the present invention are not limited to those described above, and other effects not mentioned will be clearly recognized by those skilled in the art from the following description.

1 shows the structure of a conventional scroll compressor.
2 illustrates a basic structure of a scroll compressor according to an embodiment of the present invention.
3 illustrates an embodiment of a scroll compressor having a heating unit capable of reducing the inflow of liquid refrigerant into the oil storage space.
4 shows another embodiment of the heating unit.
5 is a block diagram illustrating a control unit of a scroll compressor according to an embodiment of the present invention.
6 is a view showing an embodiment of the heat dissipation unit of the compressor according to an embodiment of the present invention.
7 shows another embodiment of the heat dissipation unit.
8 shows another embodiment of the heat dissipation unit.
9 shows the last embodiment of the heat dissipation unit.
10 is a diagram illustrating an operation method of a scroll compressor according to an embodiment of the present invention.

Hereinafter, embodiments disclosed herein will be described in detail with reference to the accompanying drawings. In this specification, even in different embodiments, the same and similar reference numerals are assigned to the same and similar components, and the description is replaced with the first description. As used herein, the singular expression includes the plural expression unless the context clearly dictates otherwise. In addition, in describing the embodiments disclosed in the present specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in this specification, the detailed description thereof will be omitted. In addition, it should be noted that the accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and should not be construed as limiting the technical spirit disclosed in the present specification by the accompanying drawings.

In addition, the terms to be described later are terms defined in consideration of functions in the present invention, which may vary according to intentions or customs of users and operators. Therefore, the definition should be made based on the content throughout this specification. The terminology used in the detailed description is for the purpose of describing embodiments of the present invention only, and should in no way be limiting. In this description, expressions such as “comprising” or “comprising” are intended to indicate certain features, numbers, steps, acts, elements, some or a combination thereof, one or more other than those described. It should not be construed to exclude the presence or possibility of other features, numbers, steps, acts, elements, or any part or combination thereof.

In addition, in describing the components of the embodiment of the present invention, terms such as first, second, A, B, (a), (b), etc. may be used. These terms are only for distinguishing the components from other components, and the essence, order, or order of the components are not limited by the terms.

2 illustrates a basic structure of a compressor according to an embodiment of the present invention.

Referring to FIG. 2 , the scroll compressor 10 according to an embodiment of the present invention includes a case 100 having a space in which a fluid is stored or flows, and is coupled to an inner circumferential surface of the case 100 to rotate a rotating shaft 230 . It may include a driving unit 200 that is provided to make the fluid move, and a compression unit 300 that is coupled with the rotation shaft 230 inside the case to compress the fluid.

Specifically, the case 100 may have a discharge unit 121 through which the refrigerant is discharged on one side. The case 100 is provided in a cylindrical shape and is coupled to an accommodating shell 110 accommodating the driving unit 200 and the compression unit 300, and one end of the accommodating shell 110 so that the discharge unit 121 is formed. The provided discharge shell 120 and the blocking shell 130 coupled to the other end of the receiving shell 110 to seal the receiving shell 110 may be included.

The driving unit 200 includes a stator 210 for generating a rotating magnetic field, and a rotor 220 provided to rotate by the rotating magnetic field, and the rotating shaft 230 is coupled to the rotor 220 . It may be provided to rotate together with the rotor 220 .

The stator 210 is provided with a plurality of slots formed along the circumferential direction on its inner circumferential surface to have a coil wound thereon, and may be fixed to the inner circumferential surface of the accommodating shell 110 . The rotor 220 may be provided with a permanent magnet coupled thereto and rotatably coupled inside the stator 210 to generate rotational power. The rotating shaft 230 may be press-fitted to the center of the rotor 220 .

The compression unit 300 is coupled to the receiving shell 110 and is coupled to a fixed scroll 320 provided in a direction away from the discharge unit 121 from the driving unit 200 and the rotating shaft 230 to be fixed. An orbiting scroll 330 engaged with the scroll 320 to form a compression chamber, and a main frame accommodating the orbiting scroll 330 and seated on the fixed scroll 320 to form the appearance of the compression unit 330 ( 310) may be included.

As a result, in the lower scroll compressor 10 , the driving unit 200 is disposed between the discharge unit 121 and the compression unit 300 . In other words, the driving unit 200 may be provided at one side of the discharge unit 121 , and the compression unit 300 may be provided in a direction away from the discharge unit 121 from the driving unit 200 .

For example, when the discharge unit 121 is provided on the upper portion of the case 100 , the compression unit 300 is provided under the driving unit 200 , and the driving unit 200 is provided on the discharge unit It may be provided between 120 and the compression unit 300 .

Accordingly, when oil is stored in the case 100 , the oil may be directly supplied to the compression unit 300 without passing through the driving unit 200 . In addition, since the rotation shaft 230 is coupled to and supported by the compression unit 300 , a lower frame that separately rotatably supports the rotation shaft may be omitted.

On the other hand, in the lower scroll compressor 10 of the present invention, the rotating shaft 230 passes through not only the orbiting scroll 330 but also the fixed scroll 320 so that both the orbiting scroll 330 and the fixed scroll 320 are on the surface. may be provided to contact.

For this reason, an inflow force generated when a fluid such as a refrigerant flows into the compression unit 300 and a gas force generated when the refrigerant is compressed inside the compression unit 300 and a reaction force supporting the same are applied to the rotation shaft ( 230) can act as it is. Accordingly, the inlet force, gas force, and reaction force may be applied to one action point of the rotation shaft 230 . As a result, since an overturning moment does not act on the orbiting scroll 320 coupled to the rotating shaft 230 , tilting or overturning of the orbiting scroll can be fundamentally blocked. In other words, up to axial vibration among the vibrations generated in the orbiting scroll 330 may be attenuated or prevented, and the overturning moment of the orbiting scroll 330 may also be attenuated or suppressed. Accordingly, noise and vibration generated by the lower scroll compressor 10 may be blocked.

In addition, since the fixed scroll 320 supports the rotation shaft 230 in surface contact, even when the inflow force and gas force act on the rotation shaft 230 , durability of the rotation shaft 230 can be reinforced.

In addition, the rotation shaft 230 partially absorbs or supports the back pressure generated while the refrigerant is discharged to the outside, so that the orbiting scroll 330 and the fixed scroll 320 are in close contact with each other in the axial direction (vertical). drag) can be reduced. As a result, the frictional force between the orbiting scroll 330 and the fixed scroll 230 can also be greatly reduced.

As a result, the compressor 10 attenuates the axial shaking and overturning moment of the orbiting scroll 330 inside the compression unit 300 , and reduces the frictional force of the orbiting scroll to increase the efficiency of the compression unit 300 . and reliability.

On the other hand, the main frame 310 of the compression unit 300 includes a main head plate 311 provided on one side of the driving unit 200 or a lower portion of the driving unit 300 , and an inner circumferential surface of the main mirror plate 311 . A main side plate 312 extending in a direction away from the driving part 200 and seated on the fixed scroll 320, and a main shaft bearing part extending from the main mirror plate 311 to rotatably support the rotating shaft 230 ( 318) may be included.

A main hole for guiding the refrigerant discharged from the fixed scroll 320 to the discharge unit 121 may be further provided in the main head plate 311 or the main side plate 312 .

The main mirror plate 311 may further include an oil pocket 314 engraved outside the main shaft portion 318 . The oil pocket 314 may be provided in an annular shape, and may be provided to be eccentric from the main shaft portion 318 . The oil pocket 314 is provided to be supplied to a portion where the fixed scroll 320 and the orbiting scroll 330 are engaged when the oil stored in the blocking shell 130 is transferred through the rotating shaft 230 and the like. can be

The fixed scroll 320 is provided in combination with the receiving shell 110 in a direction away from the driving unit 300 from the main head 311 to form the other surface of the compression unit 300. A fixed head plate 321 ) And, a fixed side plate 322 extending from the fixed head plate 321 toward the discharge part 121 and provided to contact the main side plate 312, the fixed side plate 322 is provided on the inner circumferential surface to compress the refrigerant It may include a fixing wrap 323 forming a compression chamber.

On the other hand, the fixed scroll 320 has a fixed through-hole 328 provided to allow the rotating shaft 230 to pass therethrough, and a fixed shaft portion 3281 extending from the fixed through-hole 328 so that the rotating shaft is rotatably supported. may include. The fixed shaft portion 3281 may be provided at the center of the fixed head plate 321 .

The thickness of the fixed head plate 321 may be the same as the thickness of the fixed shaft portion 3281 . In this case, the fixed shaft portion 3281 may not protrude and extend from the fixed end plate 321 , but may be inserted into the fixed through hole 328 to be provided.

An inlet hole 325 for introducing a refrigerant into the fixed wrap 323 may be provided in the fixed side plate 322 , and a discharge hole 326 through which the refrigerant is discharged may be provided in the fixed end plate 321 . The discharge hole 326 may be provided in the center direction of the fixed lap 323, but in order to avoid interference with the fixed bearing unit 3281, it may be provided spaced apart from the fixed bearing unit 3281, It may be provided in plurality.

The orbiting scroll 330 includes a turning mirror plate 331 provided between the main frame 310 and the fixed scroll 320, and an orbiting wrap forming a compression chamber together with the fixed wrap 323 in the orbiting mirror plate. (333).

The orbiting scroll 330 may further include an orbiting through-hole 338 provided through the orbiting mirror plate 331 so that the rotating shaft 230 is rotatably coupled.

The rotating shaft 230 may be provided such that a portion coupled to the orbiting through-hole 338 is eccentric. Accordingly, when the rotating shaft 230 rotates, the orbiting scroll 330 engages and moves along the fixed lap 323 of the fixed scroll 320 to compress the refrigerant.

Specifically, the rotating shaft 230 includes a main shaft 231 coupled to the driving unit 200 and rotating, and a bearing unit connected to the main shaft 231 and rotatably coupled to the compression unit 300 ( 232) may be provided. The bearing part 232 may be provided as a separate member from the main shaft 231 to accommodate the main shaft 231 therein, or may be provided integrally with the main shaft 231 . .

The bearing part 232 is inserted into the main bearing part 318 of the main frame 310 and provided to be rotatably supported by the main bearing part 232c and the fixed shaft part 3281 of the fixed scroll 320 . The fixed bearing part 232a is inserted and provided to be rotatably supported, and it is provided between the main bearing part 232c and the fixed bearing part 232a and is inserted into the orbiting through hole 338 of the orbiting scroll 330 to rotate. It may include an eccentric shaft 232b that is possibly supported.

At this time, the main bearing part 232c and the fixed bearing part 232a are formed on a coaxial line to have the same axial center, and the eccentric shaft 232b has a center of gravity of the main bearing part 232c or the fixed bearing part 232a. It may be formed eccentrically in the radial direction with respect to . In addition, the outer diameter of the eccentric shaft 232b may be larger than the outer diameter of the main bearing portion 232c or the outer diameter of the fixed bearing portion 232a. Accordingly, the eccentric shaft 232b provides a force to compress the refrigerant while the orbiting scroll 330 orbitally moves when the bearing part 232 rotates, and the orbiting scroll 320 is the fixed scroll 320 ) may be provided to rotate regularly by the eccentric shaft (232b).

However, in order to prevent the orbiting scroll 320 from rotating, the compressor 10 of the present invention may further include an Oldham's ring 340 coupled to the upper portion of the orbiting scroll 320 . The Oldham ring 340 may be provided between the orbiting scroll 330 and the main frame 310 to contact both the orbiting scroll 330 and the main frame 310 . The Oldham ring 340 is provided to linearly move in four directions of front, back, left, and right to prevent rotation of the orbiting scroll 320 .

Meanwhile, the rotation shaft 230 may be provided to completely penetrate the fixed scroll 320 and protrude to the outside of the compression unit 300 . As a result, the oil stored in the outside of the compression unit 300 and the blocking shell 130 and the rotation shaft 230 can come into direct contact, and the rotation shaft 230 rotates inside the compression unit 300 . oil can be supplied.

The oil may be supplied to the compression unit 300 through the rotation shaft 230 . An oil supply passage 234 for supplying the oil to the outer peripheral surface of the main bearing part 232c, the outer peripheral surface of the fixed bearing part 232a, and the outer peripheral surface of the eccentric shaft 232b is provided in the rotation shaft 230 or the interior of the rotation shaft can be formed.

In addition, a plurality of oil supply holes 234a, b, c, and d may be formed in the oil supply passage 234 . Specifically, the refueling hole may include a first refueling hole 234a, a second refueling hole 234b, a third refueling hole 234c, and a fourth refueling hole 234d. First, the first oil supply hole 234a may be formed to penetrate the outer peripheral surface of the main bearing part 232c.

The first oil supply hole 234a may be formed to penetrate from the oil supply passage 234 to the outer peripheral surface of the main bearing part 232c. In addition, the first oil supply hole (234a), for example, may be formed to pass through the upper portion of the outer peripheral surface of the main bearing portion (232c), but is not limited thereto. That is, it may be formed to penetrate the lower part of the outer peripheral surface of the main bearing part 232c. For reference, the first refueling hole 234a may include a plurality of holes, unlike that shown in the drawing. In addition, when the first oil supply hole 234a includes a plurality of holes, each hole may be formed only on the upper or lower part of the outer peripheral surface of the main bearing part 232c, and upper and lower parts of the outer peripheral surface of the main bearing part 232c. may be formed in each.

In addition, the rotating shaft 230 may include an oil feeder 233 provided to pass through a muffler 500 to be described later and contact the oil stored in the case 100 . The oil feeder 233 passes through the muffler 500 and is provided with an extension shaft 233a in contact with the oil and a spiral groove on the outer circumferential surface of the extension shaft 233a and communicates with the supply passage 234 . (233b).

As a result, when the rotation shaft 230 rotates, the oil due to the viscosity of the helical groove 233b and the oil and the pressure difference between the high pressure region S1 and the intermediate pressure V1 region inside the compression unit 300 , It rises through the oil feeder 233 and the supply passage 234 and is discharged to the plurality of oil supply holes. The oil discharged through the plurality of oil supply holes 234a, 234b, 234c, and 234d forms an oil film between the fixed scroll 250 and the orbiting scroll 240 to maintain an airtight state, as well as to maintain the airtight state of the compression unit 300 . It may be provided to absorb and radiate the friction heat generated in the friction part between the components.

The oil guided along the rotation shaft 230 and the oil supplied through the first oil supply hole 234a may be provided to lubricate the main frame 310 and the rotation shaft 230 . In addition, the oil may be discharged through the second oil supply hole 234b and supplied to the upper surface of the orbiting scroll 240 , and the oil supplied to the upper surface of the orbiting scroll 240 may be guided to the intermediate pressure chamber through the pocket groove 314 . can For reference, oil discharged through the second oil supply hole 234b as well as the first oil supply hole 234a or the third oil supply hole 234d may be supplied to the pocket groove 314 .

Meanwhile, the oil guided along the rotating shaft 230 may be supplied to the Oldham ring 340 installed between the orbiting scroll 240 and the main frame 230 and the fixed side plate 322 of the fixed scroll 320 . . Through this, it is possible to reduce wear of the fixed side plate 322 and the Oldham ring 340 of the fixed scroll 320 . In addition, the oil supplied to the third oil supply hole 234c is supplied to the compression chamber, thereby reducing wear due to friction between the orbiting scroll 330 and the fixed scroll 320 as well as forming an oil film and dissipating heat. Compression efficiency can be improved.

Meanwhile, the centrifugal refueling structure in which the lower scroll compressor 10 supplies oil to the bearings using the rotation of the rotating shaft 230 has been described so far, but this is only an example, and the pressure difference inside the compression unit 300 is used. It goes without saying that a differential pressure refueling structure for refueling oil and a forced refueling structure for supplying oil through a torochoid pump can also be applied.

Meanwhile, the compressed refrigerant is discharged to the discharge hole 326 along the space formed by the fixed wrap 323 and the orbit wrap 333 . The discharge hole 326 may be more advantageously provided toward the discharge unit 121 . This is because it is most advantageous for the refrigerant discharged from the discharge hole 326 to be delivered to the discharge unit 121 without a significant change in the flow direction.

However, the compression unit 300 is provided in a direction away from the discharge unit 121 from the driving unit 200 , and the fixed scroll 320 is provided at the outermost portion of the compression unit 300 . Because of the negative characteristics, the discharge hole 326 is provided to inject the refrigerant in the opposite direction to the discharge unit 121 .

In other words, the discharge hole 326 is provided to inject the refrigerant in a direction away from the discharge part 121 from the fixed head plate 321 . Therefore, when the refrigerant is directly injected into the discharge hole 326 , the refrigerant may not be smoothly discharged to the discharge unit 121 , and when oil is stored in the blocking shell 130 , the refrigerant is mixed with the oil There is a risk of cooling or mixing by collision.

To prevent this, the compressor 10 of the present invention may further include a muffler 500 coupled to the outermost portion of the fixed scroll 320 to provide a space for guiding the refrigerant to the discharge unit 121 . .

The muffler 500 seals one surface of the fixed scroll 320 in a direction away from the discharge unit 121 so as to guide the refrigerant discharged from the fixed scroll 320 to the discharge unit 121 . may be provided to do so.

The muffler 500 may include a coupling body 520 coupled to the fixed scroll 320 and a receiving body 510 extending from the coupling body 520 to form a closed space. Accordingly, the refrigerant injected from the discharge hole 326 may be discharged to the discharge unit 121 by changing the flow direction along the sealed space formed by the muffler 500 .

On the other hand, since the fixed scroll 320 is provided by being coupled to the receiving shell 110 , the refrigerant may be prevented from moving to the discharge unit 121 by being obstructed by the fixed scroll 320 . Accordingly, the fixed scroll 320 may further include a bypass hole 327 through the fixed head plate 321 through which the refrigerant may pass through the fixed scroll 320 . The bypass hole 327 may be provided to communicate with the main hole 327 . Accordingly, the refrigerant may pass through the compression unit 300 , pass through the driving unit 200 , and be discharged to the discharge hole 121 .

On the other hand, since the refrigerant is compressed at a higher pressure from the outer circumferential surface of the fixing wrap 323 toward the inside, the inside of the fixing wrap 323 and the orbiting wrap 333 maintain a high pressure state. Accordingly, the discharge pressure acts on the rear surface of the orbiting scroll as it is, and the back pressure acts from the orbiting scroll toward the fixed scroll 320 as a reaction reaction. The compressor 10 of the present invention has a back pressure seal that prevents leakage between the orbiting wrap 333 and the fixed wrap 323 by concentrating the back pressure on a portion where the orbiting scroll 320 and the rotating shaft 230 are coupled. (seal, 350) may be further included.

The back pressure seal 350 is provided in a ring shape to maintain the inner circumferential surface at high pressure, and separate the outer circumferential surface at an intermediate pressure lower than the high pressure. Accordingly, the back pressure is concentrated on the inner circumferential surface of the back pressure seal 350 so that the orbiting scroll 330 is brought into close contact with the fixed scroll 320 .

At this time, considering that the discharge hole 326 is provided to be spaced apart from the rotation shaft 230 , the back pressure seal 350 may also be provided so that the center thereof is biased toward the discharge hole 326 . can

In addition, due to the back pressure seal 350 , the oil supplied from the first oil supply groove 234a may be supplied to the inner circumferential surface of the back pressure seal 350 . Accordingly, the oil may lubricate the contact surfaces of the main scroll and the orbiting scroll. Furthermore, the oil supplied to the inner circumferential surface of the back pressure seal 350 may form a back pressure for pushing the orbiting scroll 330 to the fixed scroll 320 together with a portion of the refrigerant.

Accordingly, the compression space of the fixed wrap 323 and the orbiting wrap 333 with respect to the back pressure seal 350 is the high pressure area S1 of the inner area of the back pressure seal 350 and the back pressure seal 350 . ) may be divided into an intermediate pressure region V1. Of course, since the pressure increases while the refrigerant is introduced and compressed, the high-pressure region S1 and the intermediate-pressure region V1 can be naturally divided. However, since a pressure change may critically occur due to the existence of the back pressure seal 350 , the compression space may be divided by the back pressure chamber 350 .

On the other hand, the oil supplied to the compression unit 300 or the oil stored in the case 100 moves to the upper part of the case 100 together with the refrigerant as the refrigerant is discharged to the discharge unit 121 . can At this time, the oil has a higher density than the refrigerant and cannot move to the discharge unit 121 due to the centrifugal force generated by the rotor 220 , and is located on the inner wall of the discharge shell 110 and the receiving shell 120 . are combined The lower scroll compressor 10 includes the driving unit 200 and the compression unit 300 to recover the oil coupled to the inner wall of the case 100 to the oil storage space of the case 100 or the blocking shell 130 . ) may further include a recovery passage on the outer peripheral surface.

The recovery passage includes a drive return passage 201 provided on the outer peripheral surface of the driving unit 200 , a compression return passage 301 provided on the outer peripheral surface of the compression unit 300 , and an outer peripheral surface of the muffler 500 . It may include a muffler return passage 501 that is.

The driving return passage 201 may be provided with a part of the outer peripheral surface of the stator 210 depressed, and the compression recovery passage 301 may be provided with a part of the outer peripheral surface of the fixed scroll 320 depressed. In addition, the muffler recovery passage 501 may be provided in which a part of the outer peripheral surface of the muffler is recessed. The drive return passage 201 , the compression return passage 301 , and the muffler return passage 501 may communicate with each other to allow oil to pass therethrough.

As described above, since the center of gravity of the rotation shaft 230 is biased to one side due to the eccentric shaft 232b, an unbalanced eccentric moment may occur during rotation, and thus the overall balance may be disturbed. Accordingly, the lower scroll compressor 10 of the present invention may further include a balancer 400 capable of offsetting an eccentric moment that may occur due to the eccentric shaft 232b.

Since the compression unit 300 is fixed to the case 100 , the balancer 400 is preferably coupled to the rotation shaft 230 itself or the rotor 220 provided to rotate. Accordingly, the balancer 400 is a center balancer 410 provided on one surface toward the lower end of the rotor 220 or the compression unit 300 so as to offset or reduce the eccentric load of the eccentric shaft 232b and , The outer balancer coupled to the other surface facing the upper end or the discharge part 121 of the rotor 220 to offset the eccentric load or eccentric moment of at least one of the eccentric shaft 232b or the lower balancer 420 ( 420) may be included.

Since the center balancer 410 is provided relatively close to the eccentric shaft 232b, there is an advantage that can directly offset the eccentric load of the eccentric shaft 232b. Therefore, it is preferable that the center balancer 410 is eccentric in a direction opposite to the eccentric shaft 232b. As a result, even when the rotation shaft 230 rotates at a low speed or a high speed, the eccentric shaft 232b and the spaced distance are close, so that the eccentric force or the eccentric load generated in the eccentric shaft 232b is almost uniformly effectively offset. can

The outer balancer 420 may be provided to be eccentric in the opposite direction to the eccentric shaft 232b. However, the outer balancer 420 may be provided eccentrically in a direction corresponding to the eccentric shaft 232b to partially offset the eccentric load generated by the center balancer 410 .

Accordingly, the center balancer 410 and the outer balancer 420 may offset the eccentric moment generated by the eccentric shaft 232b to assist the rotation shaft 230 to rotate stably.

3 shows the structure of the upper part (V2) of the compressor case and the structure of the heating unit for reducing the inflow of liquid refrigerant into the oil storage space of the present invention.

The compression unit 300 is provided on at least one of the orbiting scroll 330 and the main scroll 310 and includes a delivery passage 319 through which the oil supplied from the supply passage 234 moves, and the fixed scroll. A fixed flow path 329 provided at 320 to communicate with the delivery flow path and supplying the oil between the orbiting scroll 330 and the fixed scroll 320 may be included. The delivery passage and the fixed passage may form an oil supply passage in which the oil supplied through the rotary shaft 230 is supplied to the compression chamber by a differential pressure. The compression unit 300 of the compressor of the present invention may be installed in the main frame in which the delivery flow path 319 is not the orbiting scroll. The delivery passage 319 is installed on the main frame fixed to the case 100 so that the position can be fixed at all times. Accordingly, oil may be stably introduced into the delivery passage 319 and may be stably transferred to the fixed passage 329 . In addition, the amount of oil supplied through the delivery passage 319 can be more easily controlled.

The transmission flow path 310 includes a main flow path 3191 through which the oil is supplied through the main shaft portion 318, and the main flow path 3191 extends toward the outer circumferential surface along the main mirror plate 311 to receive the oil. It may include a passage passage 3192 through which it passes, and a discharge passage 3193 connected to an end of the passage passage 3192 and extending toward the fixed frame 320 to discharge the oil.

The main flow path 3191 may be provided in parallel with the space between the main head plate 311 of the main frame and the orbiting head plate 331 of the orbiting scroll. Accordingly, the oil discharged from the first oil supply hole 241a flows between the main head plate 311 and the turning mirror plate 331 and is supplied to the back pressure chamber 350, and at the same time flows into the main flow path 3191. can be imported.

Since the main frame 310 is always fixed to the case 100 , when the delivery passage 310 is provided in the main frame 310 , oil can be stably supplied to the fixed scroll 320 .

On the other hand, the fixed flow path 329 is provided inside the fixed side plate so as to communicate with the discharge flow path 3193 and includes an inlet flow path 3291 through which the oil supplied to the delivery flow path flows, and the inlet flow path inside the fixed head plate. It is provided to communicate with the 3291 and may include a supply passage 3292 for moving the oil supplied to the inflow passage to the fixing wrap 332 .

At this time, since the fixed flow path 329 must supply the oil to at least the outer peripheral surface of the fixed wrap 323, the inflow passage 3291 has a length corresponding to the thickness of the fixed wrap 323 in the fixed side plate or the It may be provided to extend longer than the thickness. In addition, the supply passage 3292 may extend from the inflow passage 3291 to the outermost inner peripheral surface of the fixing wrap 323 . The inflow passage 3291 through which the refrigerant flows may be provided in communication with the outermost surface of the fixing wrap 323 . The outermost surface of the fixing wrap 323 is a portion that starts to engage with the orbiting wrap 333 .

On the other hand, when the inflow passage 3291 is provided to extend longer than the thickness of the fixed wrap 323 , the fixed passage 329 is the inner surface of the fixed head plate 323 in the supply passage 3292 or the It may further include a lubricating oil passage 3293 provided to extend to a portion directly communicating with the fixing wrap 323 . The inflow passage 3291 and the lubricating oil passage 3293 may be provided in parallel with each other, and the supply passage 3292 may be provided at a right angle or inclined with respect to the inflow passage and the lubricating oil passage.

As a result, one end of the delivery passage 319 or the input passage 3391 is located in the high pressure region S1 and the fixed passage 329 is located in the intermediate pressure region V1. The oil supplied from 234a may be delivered to the fixed flow path 329 while being introduced into the delivery flow path 319 . Accordingly, the oil may be delivered to the fixing wrap 323 to lubricate the orbit wrap 333 and the fixing wrap 323 .

On the other hand, the refrigerant compressed in the fixed scroll 320 passes through the fixed head plate 321 and passes through the compression unit 300 through a bypass hole 327 that can pass through the fixed scroll 320 . can The refrigerant may pass through the compression unit 300 through the bypass hole 327 together with oil supplied through an oil supply passage provided in the rotation shaft. The refrigerant and oil passing through the compression unit 300 may pass through the driving unit 200 and reach the space between the driving unit 200 and the discharge unit, that is, the upper case V2. The compressed refrigerant reaching the upper part of the case V2 may be discharged through the discharge hole 121 . As described above, the oil that has reached the upper portion of the case V2 has a higher density than the refrigerant and cannot move to the discharge unit 121 by the centrifugal force generated by the rotor 220, and the discharge shell 110 and It is coupled to the inner wall of the receiving shell 120 . The lower scroll compressor 10 includes the driving unit 200 and the compression unit to recover the oil coupled to the inner wall of the case 100 to the oil storage space P of the case 100 or the blocking shell 130 . The unit 300 may further include a recovery passage on the outer circumferential surface.

However, before the compressor 10 starts to operate, the temperature inside the compressor 10 may form a low temperature state. The low-temperature state may mean between -15 °C and 25 °C. When the compressor 10 starts to operate in a low temperature state, since the discharge superheat of the refrigerant is not secured, even if the refrigerant rises to the upper case V2, the refrigerant is discharged to the discharge unit 121 it may not be On the other hand, oil that has risen to the upper part of the case V2 like the refrigerant may be continuously discharged to the discharge unit 121 .

By operating the compressor in a low-temperature state, the oil is continuously discharged to the discharge unit 121, and the liquid refrigerant condensed without being discharged to the discharge unit 121 is disposed along the wall surface of the case 100 in the storage space ( P) can be introduced. The liquid refrigerant may continue to accumulate in the oil storage space P, and the amount of the oil may gradually decrease. After the compressor 10 is operated, when the internal temperature rises, the degree of superheat of the discharge of the refrigerant may be secured. When the discharge superheat of the refrigerant is secured, the liquid refrigerant may be vaporized in the refrigerants reaching the upper part of the case V2 , and the oil mixed with the liquid refrigerant may also be discharged to the discharge unit 121 . The amount of the oil in the oil storage space P may be further reduced.

When the amount of oil in the oil storage space (P) is reduced, the oil supply to the compression unit 300 may not be stably supplied. If the oil is not stably supplied to the compression unit 300 , wear of the compression unit 300 may occur, and an oil film may be formed between the fixed scroll 320 and the orbiting scroll 330 . Confidentiality may not be maintained. Also, it may not be possible to absorb frictional heat due to frictional force generated by the compression unit 300 .

In order to prevent this, in the compressor of the embodiment of the present invention, a heating unit 800 may be installed on one surface of the case 100 to heat the refrigerant discharged from the compression unit 300 . When the liquid refrigerant reaches the wall surface of the case 100 , the heating unit 800 vaporizes the liquid refrigerant and discharges it to the discharge unit 121 without condensing and flowing into the lower part. have.

Therefore, it can be prevented that the oil level in the storage space (P) is lowered by the inflow of the liquid refrigerant into the storage space (P) due to the heating unit (800), and stably in the compression unit (300). Oil can be refueled.

The heating unit 800 may be provided on one surface of the case 100 , and may be coupled to one surface of the discharge shell 120 as shown in the accompanying drawings, and may be disposed on one surface of the receiving shell 110 . can be combined. The heating unit 800 may be provided closer to the discharge unit 121 than to the driving unit 200 in order to supply heat to the refrigerant raised above the driving unit 200 .

Meanwhile, the compressor of the embodiment of the present invention may further include a heater 810 provided on one surface of the case 100 to heat the refrigerant discharged from the compression unit 300 . The heater 810 may be provided by being coupled to the outer circumferential surface of the case 100 , may be coupled to the outer circumferential surface of the discharge shell 120 , and may be coupled to the outer circumferential surface of the receiving shell. The heater 810 may be provided along the outer circumferential surface of the case 100 while surrounding the outer circumferential surface perpendicular to the axial direction of the rotation shaft 230 .

In addition, a plurality of heaters 810 may be provided while continuously surrounding the outer circumferential surface of the case 100 . The heater 810 may be provided to be spaced apart by an appropriate distance between the discharge unit 121 and the driving unit 200 in order to efficiently supply heat to the refrigerant.

The heater 810 may be provided in various forms capable of generating heat. The heater 810 may be formed in a cable shape. A plurality of carbon filament heating wires are bundled to form a bundle, and one or more insulating layers made of silicone resin are coated on the filament heating wire.

The heater 810 may be formed of a heat generating device using a resistor, and the heater 810 may perform a role corresponding to a condenser using a heat pump structure.

On the other hand, the compressor 10 according to an embodiment of the present invention is provided inside the case 100 to dissipate the heat supplied from the heater 810 to release heat to the refrigerant rising to the upper part V2 of the case 100 . It may further include a heat dissipation unit (850).

One surface of the heat dissipation unit 850 is coupled to the inner circumferential surface of the case 100 corresponding to the position where the heater 810 is provided in the case 100, and the other surface of the heat dissipation unit 850 is the rotation shaft ( 230) may be provided toward the center of the axis.

The heat dissipation unit 850 may receive the heat emitted from the heater 810 and dissipate the heat by dispersing the heat in the refrigerant rising to the upper portion of the case V2. The heat dissipation unit 850 may be located close to the heater 810 in order to efficiently absorb the heat emitted by the heater 810 . The case 100 may be provided between the heat dissipation unit 850 and the heater 810 .

The heat emitted by the heater 810 is conducted to the case 100 , the heat conducted to the case 100 is conducted to the heat dissipation unit 850 , and the heat conducted to the heat dissipation unit 850 is transmitted to the case 100 . Conducted to the refrigerant that has risen to the upper part of the case (V2). The heat dissipation unit 850 may be made of various thermally conductive materials as well as metal in order to dissipate the heat supplied from the heater 810 .

Meanwhile, the heat dissipation unit 850 may include a heat dissipation unit 851 formed of a ring-shaped frame having an opening in order not to prevent the refrigerant from being discharged to the discharge unit 121 . The heat dissipation unit 850 may include a plurality of heat dissipation fins 853 protruding and extending from the inner circumferential surface of the heat dissipation unit 851 .

Meanwhile, the compressor may include a sensor unit 830 coupled to the inner circumferential surface of the case 100 and provided to be spaced apart from the heater 810 to measure a temperature inside the case 100 .

The sensor unit 830 may measure the temperatures of the refrigerant and the oil that have risen to the upper part of the case V2, and transmit the measured temperatures of the refrigerant and the oil to the controller 870 as described later to the heater. The temperature of 810 can be adjusted.

The sensor unit 830 is spaced apart from the heater 810 and the heat dissipation unit 850 by an appropriate distance so that the temperature measured by the heat supplied by the heater 810 is not affected by the inner circumferential surface of the case 100 . can be provided in

In addition, the sensor unit 830 may further include a first temperature sensor 831 coupled to the inner circumferential surface of the case 100 and provided between the discharge unit 121 and the heat dissipation unit 851 . The first temperature sensor 831 may measure the temperature of the refrigerant discharged to the discharge unit 121 , and transmit the measured temperature to the control unit 870 .

In addition, the sensor unit 830 may further include a second temperature sensor 833 coupled to the inner circumferential surface of the case 100 and provided between the driving recovery passage 201 and the heat dissipation unit 851 . The second temperature sensor 833 may measure the temperature of the refrigerant flowing into the driving recovery passage 201 and transmit the measured temperature to the controller 870 .

On the other hand, the sensor unit 830 may further include a plurality of temperature sensors in addition to the first temperature sensor 831 and the second temperature sensor 833 unlike shown in the drawings.

4 shows another embodiment of the heating unit 800 according to an embodiment of the present invention.

The same reference numerals are given to the same and equivalent parts as those of the above-described configuration for convenience of description of the drawings, and a detailed description thereof will be omitted.

The compressor of the embodiment of the present invention may further include a heater 810 provided on one surface of the case 100 to heat the refrigerant discharged from the compression unit 300 . The heater 810 may be provided by being coupled to the inner circumferential surface of the case 100 , may be coupled to the inner circumferential surface of the discharge shell 120 , and may be coupled to the inner circumferential surface of the receiving shell. The heater 810 may be provided on the inner circumferential surface of the case 100 along the inner circumferential surface of the case 100 and perpendicular to the penetrating direction of the discharge part 121 . In addition, a plurality of the heaters 810 may be continuously coupled along the inner circumferential surface of the case 100 . The heater 810 may be provided to be spaced apart by an appropriate distance between the discharge unit 121 and the driving unit 200 in order to efficiently supply heat to the refrigerant.

On the other hand, the compressor 10 according to the embodiment of the present invention is provided inside the case 100 to disperse the heat supplied from the heater 810 and radiate heat to the refrigerant rising to the upper part V2 of the case. 850 may be included. One surface of the heat dissipation unit 850 may be coupled to one surface of the heater 810 , and the other surface of the heat dissipation unit 850 may be provided to face a central axis of the rotation shaft 230 .

In addition, the heat dissipation unit 850 may be coupled to the inner circumferential surface of the case 100 while surrounding the heater 810 so that the heater 810 does not come into direct contact with the refrigerant. The heat dissipation unit 850 may receive the heat emitted from the heater 810 and dissipate heat by dispersing the heat in the refrigerant that has risen to the upper part of the case V2. The heat dissipation unit 850 may be provided in combination with the heater 810 in order to efficiently absorb the heat emitted by the heater 810 .

The heat emitted by the heater 810 is conducted to the heat dissipation unit 850 , and the heat conducted to the heat dissipation unit 850 is conducted to the refrigerant raised to the upper part V2 of the case. The heat dissipation unit 850 may be made of various thermally conductive materials as well as metal in order to dissipate the heat supplied from the heater 810 .

Meanwhile, the heat dissipation unit 850 may include a heat dissipation unit 851 formed of a ring-shaped frame having an opening in order not to prevent the refrigerant from being discharged to the discharge unit 121 . The heat dissipation unit 850 may include a plurality of heat dissipation fins 853 protruding and extending from the inner circumferential surface of the heat dissipation unit 851 .

Meanwhile, the compressor may include a sensor unit 830 coupled to the inner circumferential surface of the case 100 and provided to be spaced apart from the heater 810 to measure a temperature inside the case 100 . The sensor unit 830 may measure the temperatures of the refrigerant and the oil that have risen to the upper part of the case V2, and transmit the measured temperatures of the refrigerant and the oil to the controller 870 as described later to the heater. The temperature of 810 can be adjusted.

The sensor unit 830 is spaced apart from the heater 810 and the heat dissipation unit 850 by an appropriate distance so that the temperature measured by the heat supplied by the heater 810 is not affected by the inner circumferential surface of the case 100 . can be provided in

In addition, the sensor unit 830 may further include a first temperature sensor 831 coupled to the inner circumferential surface of the case 100 and provided between the discharge unit 121 and the heat dissipation unit 851 . The first temperature sensor 831 may measure the temperature of the refrigerant discharged to the discharge unit 121 , and transmit the measured temperature to the control unit 870 .

In addition, the sensor unit 830 may further include a second temperature sensor 833 coupled to the inner circumferential surface of the case 100 and provided between the driving recovery passage 201 and the heat dissipation unit 851 . The second temperature sensor 833 may measure the temperature of the refrigerant flowing into the driving recovery passage 201 and transmit the measured temperature to the controller 870 .

On the other hand, the sensor unit 830 may further include a plurality of temperature sensors in addition to the first temperature sensor 831 and the second temperature sensor 833 unlike shown in the drawings.

5 is a block diagram for explaining the control unit 870 of the scroll compressor according to an embodiment of the present invention.

5 , the sensor unit 830 may include a first temperature sensor 831 and a second temperature sensor 833 .

The scroll compressor according to the embodiment of the present invention may further include a controller 870 that receives the temperatures of the refrigerant and the oil measured by the sensor unit 830 and controls the heater 810 . As described above, the first temperature sensor 831 is provided between the discharge unit 121 and the heat dissipation unit 850 to measure the temperature of the refrigerant discharged from the discharge unit 121 . The temperature of the discharged refrigerant may be equal to or higher than a vaporization temperature of the refrigerant supplied to the compressor.

In addition, as described above, the second temperature sensor 833 is provided between the heat dissipation unit 850 and the drive return passage 201 to measure the temperature of the liquid refrigerant recovered to the drive return passage 201 . . The temperature of the recovered liquid refrigerant may be less than or equal to the vaporization temperature of the refrigerant supplied to the compressor.

Since the solubility of the refrigerant and the vaporization temperature will vary according to the operating conditions of the compressor, the operating temperature of the heater 810 will have to be adjusted according to the operating conditions of the compressor. If the temperature of the heater 810 is adjusted to be higher than the vaporization temperature of the oil, the oil is vaporized and the amount of oil discharged to the discharge unit 121 may increase. Therefore, the temperature of the heater 810 may be adjusted to be lower than the vaporization temperature of the oil and higher than the vaporization temperature of the refrigerant.

Accordingly, the temperature measured by the first temperature sensor 831 and the second temperature sensor 833 may be transmitted to the controller 870 . The controller 870 may adjust the temperature of the heater 810 to be lower than the vaporization temperature of the oil and higher than the vaporization temperature of the refrigerant through the temperature measured by the sensor unit 830 . In some cases, the controller 870 may cut off the power supply of the current flowing through the heater 810 . In addition, when the heater 810 is a heat pump type condenser, it is possible to cut off the power supply of the heat pump.

As described above, by controlling the heater 810 to an appropriate temperature by the controller 870 , overheating inside the case 100 and overload of the heater 810 can be prevented. By preventing overheating of the inside of the case 100 and overload of the heater 810 , it is possible to suppress an increase in the temperature inside the case 100 , and to prevent the oil from being vaporized so that the oil is discharged from the discharge unit 121 . ) to prevent excessive discharge.

That is, even if the solubility of the refrigerant and the vaporization temperature are changed according to the operating conditions of the compressor, it is possible to prevent the refrigerant from being condensed and flowing into the oil storage space P by controlling the temperature of the heater 810 .

6 is a view showing an embodiment of a heat dissipation unit of a compressor according to an embodiment of the present invention.

The heat dissipation unit 850 may further include a heat dissipation unit 851 formed of a ring-shaped frame having an opening so that the refrigerant discharged from the compression unit 300 may be discharged through the discharge unit 121 . The heat dissipation unit 851 may be provided inside the case 100 to distribute heat supplied by the heater 810 to the refrigerant and supply it.

The heat dissipation unit 851 may be provided in the case 100 in parallel to the compression unit 300 and the driving unit 200 , but at an angle to the compression unit 300 and the driving unit 200 . It may be provided inside the case 100 . The heat dissipation part 851 may be provided in combination with one surface of the heater 810 , and in some cases, it is spaced apart from the heater 810 , but corresponds to a position where the heater 810 is provided in the case 100 . It may be provided inside.

The thickness of the heat dissipation part 851 may be formed to efficiently conduct heat supplied by the heater 810 , and may be formed to be thicker or thinner than the thickness of the case 100 .

Meanwhile, the heat dissipation unit 850 may include heat dissipation fins 853 protruding from the inner circumferential surface of the heat dissipation unit 851 . The heat dissipation fins 853 may be formed in a plate shape parallel to the discharge direction of the refrigerant. By being provided in parallel with the discharge direction of the refrigerant, conductive heat may be supplied for a longer period of time from the heat dissipation fins 853 while the refrigerant is discharged.

In addition, the direction in which the heat dissipation fins 853 extend may extend toward the center direction of the rotation shaft 230 . The heat dissipation fins 853 may be formed in plurality, and the plurality of heat dissipation fins 853 may be spaced apart from each other to extend from the heat dissipation unit 851 to increase the surface area of the heat dissipation unit 850 . When the plurality of heat dissipation fins 853 are formed to be spaced apart from each other, the distance from each other may be the same.

In addition, when the heat dissipation fin 853 is formed in a plate shape, the thickness of the heat dissipation fin 853 may be the same as the thickness of the heat dissipation unit 851 , or may be formed to be thicker than the thickness of the heat dissipation unit 851 . . When the thickness of the heat dissipation fins 853 is formed too thick, the liquid refrigerant may not pass between the heat dissipation fins 853 , so that the liquid refrigerant can be sufficiently supplied with heat from the heat dissipation unit 850 . The thickness of the heat dissipation fin 853 should be formed.

In addition, the length of the heat dissipation fin 853 may be shorter than the radius of the case 100 , and the height of the heat dissipation fin 853 may be shorter than the height of the heat dissipation unit 851 .

In addition, the heat dissipation unit 850 may include a heat dissipation groove 855 provided to be recessed in the heat dissipation unit 851 between one heat dissipation fin 853 and the other heat dissipation fin 853 . As the heat dissipation groove 855 is provided, the surface area of the heat dissipation part 850 may be increased to increase the area of heat supplied to the refrigerant.

In addition, the heat dissipation groove 855 may lengthen the time the liquid refrigerant is stagnated in the heat dissipation unit 850 to receive heat. The heat dissipation grooves 855 may be formed in plurality, and a distance between the heat dissipation grooves 855 may be the same.

7 illustrates another embodiment of the heat dissipation unit 850 .

The same reference numerals are assigned to the same and equivalent parts as those of the above and illustrated components for convenience of description of the drawings, and detailed description thereof will be omitted.

The heat dissipation unit 850 may further include a heat dissipation fin 853 protruding from the inner circumferential surface of the heat dissipation unit 851 . The heat dissipation fins 853 may be formed in a plate shape parallel to the discharge direction of the refrigerant.

In addition, the direction in which the heat dissipation fins 853 extend may extend toward the center direction of the rotation shaft 230 . The heat dissipation fins 853 may be formed to have a bent shape along an extension direction.

Since the heat dissipation fin 853 has a bent shape, an extended length of the heat dissipation fin 853 may be formed to be longer than a radial length of the case 100 . In addition, the surface area of the heat dissipation fin 853 can be formed to be wider, so that the amount of conductive heat supplied by the heat dissipation unit 850 to the refrigerant can be increased.

8 shows another embodiment of the heat dissipation unit 850 .

The heat dissipation unit 850 may further include a heat dissipation fin 853 protruding from the inner circumferential surface of the heat dissipation unit 851 . The heat dissipation fin 853 may be formed in a cylindrical shape extending in a direction of the axis of the rotation shaft 230 .

In addition, the direction in which the heat dissipation fin 853 extends may extend toward the center of the axis of the rotation shaft 230 , but in some cases, it may be formed to have a bent shape according to the extending direction.

Since the heat dissipation fin 853 has a bent shape, an extended length of the heat dissipation fin 853 may be formed to be longer than a radial length of the case 100 . In addition, the surface area of the heat dissipation fin 853 can be formed to be wider, so that the amount of conductive heat supplied by the heat dissipation unit 850 to the refrigerant can be increased.

As the heat dissipation fins 853 are provided to have a cylindrical shape, a surface area of the heat dissipation unit 850 in contact with the refrigerant may be increased. In addition, the coupling portion of the heat dissipation unit 851 and the heat dissipation fin 853 may be more firmly coupled, so that the heat dissipation fin 853 may be firmly supported by the heat dissipation unit 851 to extend.

The diameter of the cross section of the heat dissipation fin 853 may be shorter than the height of the heat dissipation part 851 , and the extension length of the heat dissipation fin 853 may be shorter than the radius of the case 100 .

In addition, the heat dissipation fins 853 may be formed in plurality, and the plurality of heat dissipation fins 853 may be spaced apart from each other to extend from the heat dissipation unit 851 in order to increase the surface area of the heat dissipation unit 850 . . When the plurality of heat dissipation fins 853 are formed to be spaced apart from each other, the distance from each other may be the same.

In addition, the heat dissipation unit 850 may include a heat dissipation groove 855 provided to be recessed in the heat dissipation unit 851 between one heat dissipation fin 853 and the other heat dissipation fin 853 . As the heat dissipation groove 855 is provided, the surface area of the heat dissipation part 850 may be increased to increase the area of heat supplied to the refrigerant.

In addition, the heat dissipation groove 855 may lengthen the time the liquid refrigerant is stagnated in the heat dissipation unit 850 to receive heat. The heat dissipation grooves 855 may be formed in plurality, and a distance between the heat dissipation grooves 855 may be the same.

9 shows the last embodiment of the heat dissipation unit 850 .

The heat dissipation unit 850 may further include a heat dissipation fin 853 protruding from the inner circumferential surface of the heat dissipation unit 851 . The heat dissipation fin 853 may be formed in a cylindrical shape extending in a direction of the axis of the rotation shaft 230 . In addition, the heat dissipation fins 853 may be provided to have a cylindrical shape in which a cross-sectional area decreases along an extension direction.

As the heat dissipation fins 853 are provided to have a cylindrical shape in which a cross-sectional area decreases along an extension direction, a surface area of the heat dissipation unit 850 in contact with the refrigerant may be increased.

Also, since the heat dissipation fin 853 is coupled to the heat dissipation part 851 at a portion having the largest cross-sectional area, the coupling portion between the heat dissipation part 851 and the heat dissipation fin 853 can be more firmly coupled, and the The heat dissipation fins 853 may be firmly supported by the heat dissipation part 851 to extend.

The diameter of the widest cross-section among the cross-sections of the heat dissipation fin 853 may be shorter than the formed height of the heat dissipation part 851 , and the extension length of the heat dissipation fin 853 may be formed shorter than the radius of the case 100 . .

In addition, the heat dissipation fins 853 may be formed in plurality, and the plurality of heat dissipation fins 853 may be spaced apart from each other to extend from the heat dissipation unit 851 in order to increase the surface area of the heat dissipation unit 850 . . When the plurality of heat dissipation fins 853 are formed to be spaced apart from each other, the distance from each other may be the same.

Meanwhile, the direction in which the heat dissipation fins 853 extend may extend toward the center of the axis of the rotation shaft 230 , but in some cases, the heat dissipation fins 853 may be formed to have a bent shape according to the extending direction.

Since the heat dissipation fin 853 has a bent shape, an extended length of the heat dissipation fin 853 may be formed to be longer than a radial length of the case 100 . In addition, the surface area of the heat dissipation fin 853 can be formed to be wider, so that the amount of conductive heat supplied by the heat dissipation unit 850 to the refrigerant can be increased.

In addition, the heat dissipation unit 850 may include a heat dissipation groove 855 provided to be recessed in the heat dissipation unit 851 between one heat dissipation fin and another heat dissipation fin. As the heat dissipation groove 855 is provided, the surface area of the heat dissipation part 850 may be increased to increase the area of heat supplied to the refrigerant.

In addition, the heat dissipation groove 855 may lengthen the time the liquid refrigerant is stagnated in the heat dissipation unit 850 to receive heat. The heat dissipation grooves 855 may be formed in plurality, and a distance between the heat dissipation grooves 855 may be the same.

10 shows an operation method of the compressor of the present invention.

10 is a view showing the operation of the compressor according to the embodiment of the present invention.

Fig. 10(a) shows the orbiting scroll, and Fig. 10(b) shows the fixed scroll.

10(c) shows a process in which the orbiting scroll and the fixed scroll compress the refrigerant.

The orbiting scroll 330 may include an orbiting wrap 333 on one surface of the orbiting mirror plate 331 , and the fixed scroll 320 includes the fixed lap 323 on one surface of the fixed head plate 321 . can be provided

In addition, the orbiting scroll 330 is provided with a sealed rigid body to prevent the refrigerant from being discharged to the outside, but the fixed scroll 320 has an inlet hole communicating with the refrigerant supply pipe so that a low-temperature, low-pressure refrigerant such as liquid is introduced. 325) and a discharge hole 326 through which the high-temperature and high-pressure refrigerant is discharged, and a bypass hole 327 through which the refrigerant discharged from the discharge hole 326 is discharged on an outer peripheral surface thereof.

Meanwhile, the fixed wrap 323 and the orbit wrap 333 may be provided in an involute shape to form a compression chamber in which the refrigerant is compressed while at least two points are engaged.

The involute shape means a curve corresponding to the trajectory drawn by the end of the thread when unwinding the thread wound around the base circle having an arbitrary radius as shown.

However, in the present invention, the fixed wrap 323 and the orbit wrap 333 are formed by combining 20 or more arcs, and may be provided so that the radius of curvature varies for each part.

That is, in the compressor of the present invention, the rotating shaft 230 is provided to pass through the fixed scroll 320 and the orbiting scroll 330, so that the radius of curvature of the fixed wrap 323 and the orbiting wrap 333 and the compression space are decreases.

Therefore, in order to compensate for this, the compressor of the present invention reduces the space through which the refrigerant is discharged and improves the compression ratio, so that the radius of curvature immediately before the discharge of the fixed wrap 323 and the orbital wrap 333 passes through the rotation shaft. It can be provided with a smaller size than the shaft bearing part.

That is, the fixing wrap 323 and the orbiting wrap 333 may be bent more severely near the discharge hole 326 , and the radius of curvature corresponding to the bent portion increases as it extends toward the inlet hole 325 . It may vary from branch to branch.

Referring to FIG. 10( c ), the refrigerant (I) flows into the inlet hole 325 of the fixed scroll 320, and the refrigerant (II) introduced earlier than the refrigerant (I) is the fixed scroll 320 . It is located in the vicinity of the discharge hole 326 of the.

In this case, the refrigerant (I) is present in a region provided in engagement with each other on the outer surfaces of the fixed wrap 323 and the orbiting wrap 333, and the refrigerant (II) is the fixed wrap 323 and the orbiting wrap. (333) exists sealed in another region where two points interlock.

Afterwards, when the orbiting scroll 330 starts a pivoting movement, the fixed lap 323 is an area where the fixed lap 323 and the orbiting lap 333 are engaged at two points according to the change of the position of the orbiting lap 333 . ) and the orbiting wrap 333 moves along the extension direction and the volume starts to decrease, and the refrigerant I moves and starts to be compressed. The refrigerant (II) is further reduced in volume, compressed, and begins to be guided to the discharge hole (326).

The refrigerant (II) is discharged from the discharge hole 326, and the refrigerant (I) moves as the two-point meshing area between the fixed wrap 323 and the orbiting wrap 333 moves in a clockwise direction. , the volume decreases and begins to compress further.

The two-point meshing area between the fixed wrap 323 and the orbiting wrap 333 moves clockwise again and approaches the inside of the fixed scroll, the volume is further reduced and compressed, and the refrigerant II is almost discharged. is done

As such, as the orbiting scroll 330 orbits, the refrigerant may be compressed linearly or continuously while moving inside the fixed scroll.

Although the figure shows that the refrigerant is discontinuously introduced into the inlet hole 325, this is for illustrative purposes only, and the refrigerant may be continuously supplied, and the fixed wrap 323 and the orbital wrap 333 Refrigerant can be accommodated and compressed in each of the two-point engagement regions.

Although various embodiments of the present invention have been described in detail above, those of ordinary skill in the art to which the present invention pertains will understand that various modifications are possible without departing from the scope of the present invention with respect to the above-described embodiments. . Therefore, the scope of the present invention should not be limited to the described embodiments, but should be defined by the claims described below as well as the claims and equivalents.

1 Refrigerant cycle 10 Compressor
100 Case 110 Receiving Shell 120 Exhaust Shell
121 Discharge unit 130 Block shell 200 Drive unit
300 Compression part 310 Mainframe 320 Fixed scroll
321 Fixed end plate 330 Orbiting scroll
340 Oldham Ring 350 Back pressure seal
400 Drive Balancer 500 Muffler
800 Heater 810 Heater 830 Sensor
831 First temperature sensor 833 Second temperature sensor 850 Heat dissipation unit
851 heat sink 853 heat sink fin 855 heat sink
870 control

Claims (17)

a case having a discharge unit through which the refrigerant is discharged, and a storage space in which oil is stored;
a driving unit coupled to the inner circumferential surface of the case;
a rotating shaft coupled to the driving unit and provided to rotate;
a compression unit coupled to the rotating shaft to compress and discharge the refrigerant; and
A heating unit provided on one surface of the case to heat the refrigerant discharged from the compression unit;
The compressor, characterized in that the heating part is located closer to the discharge part than the driving part. According to claim 1,
the heating part
a heater provided on one surface of the case to heat the refrigerant discharged from the compression unit; and
and a sensor unit coupled to the inner circumferential surface of the case and provided to be spaced apart from the heater to measure a temperature inside the case. 3. The method of claim 2,
The heater is a compressor, characterized in that provided on the inner peripheral surface of the case. 3. The method of claim 2,
The heater is a compressor, characterized in that provided on the outer peripheral surface of the case. 4. The method of claim 3,
The heating unit is provided inside the case, and further comprises a heat dissipation unit dissipating heat supplied from the heater to the refrigerant,
The heat dissipation unit is coupled to one surface of the heater, and the other surface of the heat dissipation unit is provided to face a central axis of the rotation shaft. 5. The method of claim 4,
The heating unit,
Further comprising a heat dissipation unit provided inside the case to dissipate the heat supplied from the heater to discharge to the refrigerant,
One surface of the heat dissipation unit is coupled to the inner circumferential surface of the case corresponding to the position where the heater is provided in the case,
Compressor, characterized in that the other surface of the heat dissipation part is provided to face a central axis of the rotation shaft. 5. The method of claim 4,
The heating unit,
Further comprising a heat dissipation unit provided inside the case to dissipate the heat supplied from the heater to discharge to the refrigerant,
One surface of the heat dissipation unit is coupled to the inner circumferential surface of the case corresponding to the position where the heater is provided in the case,
Compressor, characterized in that the other surface of the heat dissipation part is provided to face a central axis of the rotation shaft. 8. The method of claim 7,
The compressor, characterized in that the heat dissipation unit is made of a thermally conductive material to dissipate the heat supplied from the heater. 9. The method of claim 8,
The heat dissipation unit,
The compressor further comprising a heat sink provided as a ring-shaped frame having an opening through which the refrigerant or the oil passes. 10. The method of claim 9,
the driving unit
and a drive return flow passage in which a part of the outer circumferential surface of the driving unit is recessed and provided to be a passage through which the oil passes,
the sensor unit
a first temperature sensor coupled to the inner circumferential surface of the case and provided between the discharge unit and the heat sink to measure the temperature of the refrigerant discharged to the discharge unit;
and a second temperature sensor coupled to the inner circumferential surface of the case and provided between the drive return passage and the heat sink to measure the temperature of the refrigerant flowing into the drive return passage. 11. The method of claim 10,
the heating part
Through the temperature of the refrigerant and the oil measured by the sensor unit,
The compressor further comprising a control unit for controlling the heater so that the temperature of the heater is higher than the vaporization temperature of the refrigerant and lower than the vaporization temperature of the oil. 12. The method of claim 11,
The heat dissipation unit further includes a heat dissipation fin protruding from an inner circumferential surface of the heat dissipation plate and having a plate shape provided in parallel with a discharge direction of the refrigerant. 13. The method of claim 12,
The heat dissipation fins are provided in the shape of a plurality of plates spaced apart from each other by a predetermined distance, and a distance between the plurality of heat dissipation fins is equal to a distance between one heat dissipation fin and the other heat dissipation fin. 14. The method of claim 13
The heat dissipation fins extend from an inner circumferential surface of the heat dissipation plate in the axial center direction of the rotation shaft. 14. The method of claim 13,
The heat dissipation fin is
The compressor, characterized in that it extends from the inner circumferential surface of the heat sink in the axial center direction of the rotation shaft and has a bent shape along the extension direction. 12. The method of claim 11,
The heat dissipation unit further includes a heat dissipation fin extending from an inner circumferential surface of the heat dissipation plate in the axial direction of the rotation shaft and having a cylindrical shape. 17. The method of claim 16,
The heat dissipation fins are provided in the shape of a plurality of cylinders spaced apart from each other by a predetermined distance, and the cross-sectional area of the heat dissipation fins in the protruding direction is provided to decrease according to the extension length.

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