KR20210130904A - A compressor - Google Patents

Abstract

The present disclosure relates to a compressor. The compressor including a valve unit for preventing a reverse oil flow of the compressor according to the present invention comprises the valve unit such that the valve unit selectively opens and closes a refrigerant auxiliary flow path according to whether a rotary shaft rotates. When the compressor using a differential pressure oil supply structure is stopped, the compressor opens the refrigerant auxiliary flow path to relieve a differential pressure, thereby preventing oil backflow.

Description

Compressor {A compressor}

This disclosure relates to a compressor. More particularly, in a lower scroll compressor to which differential pressure refueling is applied, the present invention relates to a compressor including a rotating shaft having a refrigerant passage for preventing an oil backflow when the compressor is stopped.

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, referring to Korean Patent Application Laid-Open No. 10-20180124633), recently, a scroll compressor in which a driving unit exists under the discharge unit and a compression unit is located under the driving unit has appeared (aka, lower part). scroll compressor).

In the lower scroll compressor, a driving unit is provided closer to the discharge unit than the compression unit, and the compression unit is provided farthest from the discharge unit.

In such a lower scroll compressor, one end of the rotating shaft is connected to the driving unit, the other end is supported by the compression unit, so that the lower frame is omitted, and the oil stored in the lower part of the case can be directly supplied to the compression unit without passing through the driving unit. there was. In addition, when the rotary shaft is connected through the compression unit in the lower scroll compressor, the action points of the gas force and the reaction force coincide on the rotary shaft, thereby canceling the vibration or overturning moment of the scroll, thereby ensuring efficiency and reliability.

Referring to FIG. 1 , in the conventional 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 furthest from the discharge unit 121 . provided spaced apart. 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 . Therefore, a separate lower frame for supporting the rotating shaft can be omitted, and the oil stored on one side of the case can be directly supplied to the compression unit 300 through the rotating shaft 230 without going through the driving unit 200 . There were advantages.

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.

On the other hand, the oil supplied to the compression unit 300 through the rotation shaft 230 lubricates the inside of the compression unit 300 and at the same time cools the compression unit 300 to reduce wear and tear of the compression unit 300 and Prevent overheating.

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 310 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 provided on the side of the fixed scroll 320, the orbiting wrap 333 provided in the orbiting scroll compresses the refrigerant through the orbiting motion in the fixed wrap 323 provided in the fixed scroll. and the compressed refrigerant is discharged to a discharge hole 326 provided near the rotation shaft 230 .

At this time, a high-pressure region is formed in the vicinity of the rotation shaft 230 due to the compressed refrigerant, and in the high-pressure region, the refrigerant generates a force to push the orbiting scroll 330 toward the driving unit 200 . 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 rotating shaft 230 raises the oil stored in the oil P through the plurality of oil supply holes 234a, 234b, and 234c, and supplies it to the main bearing 232a, the eccentric shaft 232b, and the fixed bearing 232c.

Meanwhile, an intermediate pressure region having a lower pressure than that of the high pressure region is formed on the outer peripheral surface of the back pressure seal 350 , and a low pressure region may be formed in the Oldham ring 340 provided for orbiting the orbiting scroll. The oil supplied from the rotary shaft 230 may be supplied to the fixed wrap, the orbit wrap, or the Oldham ring 340 by using a pressure difference between the high pressure region and the intermediate pressure region or the low pressure region. (So-called differential pressure refueling method can be applied.)

However, even if the oil normally circulates inside the compressor while the compressor is in operation, when the compressor is stopped, the oil already stored in the oil storage space P through the oil supply passage 234 due to the differential pressure is transferred to the compression unit ( 300) and there was a problem in that it flows backward into the inlet hole on the side of the fixed scroll that forms a relatively low pressure.

Patent Document 1 relates to a compressor having a suction valve at a refrigerant suction port. However, as described above, there is a problem in that the suction valve cannot be used to secure the operability and reliability of the compressor during high compression ratio operation.

Patent Document 2 relates to a compressor that is provided with an injection valve assembly inside a fixed scroll to prevent backflow. However, since the injection valve assembly is formed on the inlet side, there is a problem in that reliability cannot be secured during high compression ratio operation.

As described above, in the conventional compressor, a suction valve is installed at the suction port through which the refrigerant flows in order to prevent oil backflow. However, when the suction valve is installed, the use of additional space is inevitable, and there is a problem in that the suction valve cannot be used for stability in order to operate a compressor having a high pressure ratio. Therefore, it was necessary to develop a technology for preventing the reverse flow of oil without using a suction valve.

Patent Document 1: Korean Patent Publication No. 10-2018-0086749 (2018.08.01) Patent Document 2: Korean Patent Publication No. 10-2018-0093693 (2018.08.22)

An object of the present disclosure is to provide a compressor that prevents a compressor adopting a differential pressure refueling structure from causing a reliability problem of the compressor by flowing to an inlet side by a differential pressure when the compressor is stopped.

An object of the present disclosure is to provide a compressor that prevents reverse flow of oil when stopped without a configuration such as a suction valve in a compressor to which a differential pressure refueling structure is applied.

An object of the present disclosure is to provide a compressor that prevents a reverse flow of oil by quickly relieving a differential pressure when the compressor is stopped.

An object of the present disclosure is to provide a compressor that prevents reverse flow of oil by using the rotational force of a rotating shaft without additional power.

An object of the present disclosure is to provide a compressor that prevents a reverse flow of oil by inducing a high-pressure refrigerant to rapidly penetrate into a low-pressure region.

An object of the present disclosure is to provide a compressor that prevents backflow of oil by using a valve that is closed during operation of the compressor and opened when the compressor is stopped.

An object of the present disclosure is to provide a compressor having a valve unit for opening and closing a refrigerant auxiliary flow path using its own weight.

An object of the present disclosure is to provide a compressor having a valve unit formed in various structures to prevent a reverse flow of oil.

According to the present disclosure, in order to solve the above problems, in a lower scroll compressor using a differential pressure oil supply structure, it is possible to solve the differential pressure and prevent the reverse flow of oil by using the refrigerant auxiliary flow path that is opened only when the rotation shaft is stopped. The refrigerant auxiliary flow path may be opened and closed using a valve unit. The valve unit may close the refrigerant auxiliary flow path when the compressor operates by using centrifugal force, and may open the refrigerant auxiliary flow path using its own weight when stopped. When the refrigerant auxiliary flow path is opened, the refrigerant flows along the reverse flow path of the oil, thereby preventing the oil from flowing back into the suction valve.

The compressor of the present disclosure includes a case having a discharge part through which refrigerant is discharged on one side and providing a storage space for storing oil, a stator coupled to an inner circumferential surface of the case to generate a rotating magnetic field, and a stator accommodated in the rotating magnetic field A driving unit including a rotor rotated by a rotating shaft, a rotating shaft coupled to or extending from the rotor in a direction away from the discharge unit, a compression unit coupled to the rotating shaft to compress the refrigerant, and the refrigerant coupled to the compression unit and a muffler for guiding to the discharge unit, wherein the rotating shaft extends through an oil supply passage for supplying the oil accommodated in the oil storage space to the compression unit and one end of the rotation shaft facing the discharge unit in the oil supply passage. It may include a refrigerant auxiliary flow path formed so that the refrigerant flows, and a valve part coupled to the rotation shaft to selectively open and close the coolant auxiliary flow path according to whether the rotation shaft rotates.

Selectively opening and closing the refrigerant auxiliary flow path according to the rotation means opening the refrigerant auxiliary flow path when the rotating shaft rotates at a predetermined speed or less.

The valve part is provided at one end of the rotation shaft facing the discharge part and is coupled to a coupling part coupled to the coupling part to rotate together with the rotation shaft and rotates together with the rotation shaft, but depending on whether the rotation shaft rotates, the refrigerant auxiliary flow path may include an opening/closing unit movably coupled to the coupling unit to selectively open/close the .

The opening/closing part is provided in contact with the coupling part or the rotating shaft to selectively open and close the refrigerant auxiliary flow path depending on whether the rotating shaft rotates or not, and is extended or coupled from the blocking unit to close the refrigerant auxiliary flow path by its own weight. It may include a mass part to open and close.

The mass portion may be provided such that the refrigerant auxiliary passage is opened when the rotational speed of the rotation shaft is less than the reference speed, and the coolant auxiliary passage is closed when the rotational speed of the rotational shaft is equal to or greater than the reference speed.

The coupling part may be formed to protrude from an end of the coupling part facing the discharge part and include a hinge part provided to couple the opening/closing part, and the opening/closing part may be rotatably coupled to the upper hinge hinge part around a rotation center.

The compressor according to the present disclosure may include a first connection part having one end rotatably coupled to the mass part and the other end rotatably coupled to the coupling part to transfer the weight of the mass part to the blocking part.

A first hinge part provided on one side of the blocking part for rotatably coupling the blocking part and the mass part, a second hinge part provided on the mass part for rotatably coupling the mass part and the first connection part, and the It may further include a third hinge part provided on one side of the coupling part to rotatably couple the coupling part and the first connection part.

The mass part and the first connection part may be provided in plurality.

The compressor according to the present disclosure may include an elastic member that is provided on the coupling part or the rotating shaft to be in contact with the blocking part, and provides an elastic force to open the refrigerant auxiliary flow path.

A fourth hinge part rotatably coupling the mass part to the coupling part may be further included.

The compressor according to the present disclosure may include a receiving part which is provided to extend in a radial direction of the refrigerant auxiliary flow path from one side of the refrigerant auxiliary flow path facing the discharge part and accommodates the coupling part.

The valve unit may be detachably provided with the refrigerant auxiliary flow path.

The mass part may be provided so that the weight can be changed.

The present disclosure has an effect that it is possible to provide a compressor with improved stability and efficiency by preventing the reverse flow of oil when the compressor is stopped without a configuration such as a suction valve.

The present disclosure has the effect of providing a compressor that improves lap reliability by preventing oil backflow when the compressor is stopped.

The present disclosure has the effect of providing a compressor capable of preventing the occurrence of an error in the compressor by improving the differential pressure resolution speed.

Since the present disclosure uses centrifugal force or elastic force according to the rotation of the rotating shaft, it can serve as a shut-off valve without requiring additional power, thereby providing a high-efficiency compressor.

Since the present disclosure applies a differential pressure oil supply structure, there is an effect that it is possible to provide a compressor for supplying oil to the compression unit without using a separate power.

The present disclosure has the effect of providing a compressor capable of preventing the eccentricity of the rotating shaft because the mass part can serve as a balancer during rotation.

The present disclosure has the effect of providing a compressor with easy maintenance and repair of the valve part because the valve part may be detachably provided.

The present disclosure is effective in providing a compressor capable of changing the weight of the mass part according to usage conditions.

1 shows the structure of a conventional compressor.
2 illustrates a structure of a compressor according to an embodiment of the present disclosure.
3 is a view showing the operation of the conventional compressor and the compressor of the present disclosure.
4 shows the principle of operation of the present disclosure.
5 is a three-dimensional view showing a compressor according to the present disclosure.
6 shows another embodiment of the compressor of the present disclosure.
7 shows another embodiment of the valve unit of the present disclosure.
8 shows another embodiment of the valve part of the present disclosure.

Hereinafter, embodiments disclosed in the present specification 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 the present 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 herein by the accompanying drawings.

2 illustrates a structure of a compressor according to the present disclosure.

Referring to FIG. 2 , the scroll compressor 10 according to the present disclosure 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 and a compression unit 300 provided to compress the fluid by being coupled to the rotation shaft 230 inside the case.

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 the inner circumferential surface of the stator 210, the coil is wound and can be fixed to the inner circumferential surface of the receiving shell 110, the rotor 220 is a permanent magnet is coupled and is rotatably coupled inside the stator 210 to generate rotational power. The rotation 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; 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 on 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 the 121 and the compression unit 300 .

Accordingly, when oil is stored in the oil storage space p of 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.

Meanwhile, in the lower scroll compressor 10 according to the present disclosure, the rotating shaft 230 passes through not only the orbiting scroll 330 but also the fixed scroll 320 to provide both the orbiting scroll 330 and the fixed scroll 320 . It may be provided for an interview.

Due to this, 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 330 coupled to the rotation shaft 230 , tilting or overturning of the orbiting scroll 330 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 friction force between the orbiting scroll 330 and the fixed scroll 320 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 200 and an inner peripheral 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 317 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 located at a portion where the fixed scroll 320 and the orbiting scroll 330 are engaged when the oil P stored in the blocking shell 130 is transferred through the rotation shaft 230 and the like. It may be provided to be supplied.

The fixed scroll 320 is provided in combination with the receiving shell 110 in a direction away from the driving unit 200 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 portion 232a provided to be inserted and rotatably supported, and the main bearing portion 232c and the fixed bearing portion 232a are 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 for compressing the refrigerant while revolving the orbiting scroll 330 when the bearing part 232 rotates, and the orbiting scroll 330 is the fixed scroll 320 ) may be provided to rotate regularly by the eccentric shaft (232b).

However, in order to prevent the orbiting scroll 330 from rotating, the compressor 10 according to the present disclosure may further include an Oldham's ring 340 coupled to an upper portion of the orbiting scroll 330 . . 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 330 .

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 flow path 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 inside 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 spirally provided on an extension shaft 233a in contact with the oil and an outer circumferential surface of the extension shaft 233a, and communicates with the oil supply passage 234 . A groove 233b may be included.

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 region V1 inside the compression unit 300 , It rises through the oil feeder 233 and the oil 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 frictional 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 310 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 . Accordingly, 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 according to the present disclosure 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 . have.

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 317 . Accordingly, the refrigerant may pass through the compression unit 300 , pass through the driving unit 200 , and be discharged to the discharge unit 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 as a reaction. In the compressor 10 according to the present disclosure, the back pressure is concentrated on the portion where the orbiting scroll 330 and the rotating shaft 230 are coupled to prevent leakage between the orbiting wrap 333 and the fixed wrap 323 . It may further include a seal (seal, 350).

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 presence of the back pressure seal 350 , the compression space may be divided by the back pressure seal 350 .

On the other hand, the oil supplied to the compression unit 300 or the oil stored in the oil storage space P of the case 100 is discharged into the case 100 together with the refrigerant as the refrigerant is discharged to the discharge unit 121. 100) can be moved to the upper part. 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 120 and the receiving shell 110 . is attached The lower scroll compressor 10 includes the driving unit 200 and the compression unit 300 to recover the oil attached 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 according to the present disclosure 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 upper end of the rotor 220 or the other surface toward the discharge part 121 to offset the eccentric load or eccentric moment of at least one of the eccentric shaft 232b or the center balancer 410 ( 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 rotating shaft 230 rotates at a low speed or a high speed, the eccentric shaft 232b and the eccentric shaft 232b are close together, so that the eccentric force or eccentric load generated in the eccentric shaft 232b is effectively offset. can

The outer balancer 420 may be provided to be eccentric in a direction opposite 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.

Meanwhile, the rotation shaft 230 extends from the oil supply passage 234 in the direction of the discharge part 121 to pass through one end of the rotation shaft 230 and a refrigerant auxiliary passage 235 provided to allow the coolant to flow. may further include. The refrigerant auxiliary flow path 235 may be provided such that a space formed by the upper surface of the driving unit 200 and the case 100 , that is, a space into which the compressed refrigerant flows, and the oil supply flow path 234 communicate with each other. . One end of the rotating shaft 230 provided with the refrigerant auxiliary flow path 235 is rotated together with the rotating shaft 230 and selectively opens and closes the refrigerant auxiliary flow path 235 according to whether the rotating shaft 230 rotates. A unit 600 may be further included.

When the operation of the compressor 10 is stopped and the speed of the rotating shaft 230 is lowered to a predetermined speed or less, the valve unit 600 opens the refrigerant auxiliary passage 235 so that the refrigerant flows into the refrigerant auxiliary passage 235 ) can be flowed through.

When the compressor 10 is stopped, a differential pressure is formed inside the compressor 10 by the compressed refrigerant, thereby causing the oil to flow back into the suction port forming a relatively low pressure. However, the valve unit 600 may open the refrigerant auxiliary flow path 235 to relieve the pressure differential inside the compressor 10 and prevent the oil from flowing backward.

Hereinafter, the structure, operation principle and effect of the valve unit 600 will be described in detail.

3 is a view illustrating a comparison between a conventional compressor and a compressor of the present disclosure.

3 (a) and 3 (b) show the flow of oil when the conventional compressor operates and when the operation is stopped.

Referring to FIG. 3( a ), when the compressor 10 is operating, the oil is supplied along the oil supply passage 234 in the oil storage space P by a differential pressure to supply the main frame 310 , the After lubricating the fixed scroll 320 and the orbiting scroll 330, the oil is returned to the oil storage space (P). As such, during normal operation of the compressor 10 , the oil may not flow out or flow backwards.

Referring to FIG. 3( b ), when the compressor 10 is stopped, the oil is supplied along the oil supply passage 234 in the oil storage space P due to the differential pressure already formed. However, since the orbiting scroll 330 does not operate, the oil may not move in the direction of the rotation shaft 230 and may flow in the direction of the refrigerant inlet forming a low pressure. As such, when the compressor 10 stops operating, if the differential pressure inside the compressor 10 is not resolved, the oil may flow back or be lost, thereby reducing the stability and efficiency of the compressor 10 .

Referring to FIG. 3( c ), the rotating shaft 230 communicates with the oil supply flow path 234 therein and may include the refrigerant auxiliary flow path 235 formed to pass through one end of the rotation shaft 230 . have. Since the refrigerant auxiliary flow path 235 communicates with the compression unit 300 , the differential pressure inside the case 100 can be eliminated.

However, when the refrigerant auxiliary flow path 235 is always open, it is impossible to supply oil to the compression unit 300 in a differential pressure refueling method. Therefore, when the compressor 10 is operating, it may include a valve unit 600 that shields the refrigerant auxiliary flow path 235 and opens the refrigerant auxiliary flow path 235 when the compressor 10 is stopped. .

When the rotation shaft 230 rotates, the valve unit 600 blocks the refrigerant auxiliary flow path 235, so that it can operate like a conventional compressor. In addition, the valve unit 600 opens the refrigerant auxiliary flow path 235 when the rotating shaft 230 is stopped, so that the differential pressure inside the compressor 10 is quickly resolved so that the oil is discharged to the outside of the compressor 10 . It can prevent discharge or backflow.

When the refrigerant auxiliary flow path 235 is opened, the refrigerant having a high pressure inside the case 100 is rapidly introduced in the I direction, thereby resolving the differential pressure. In order to supply the oil stored in the oil storage space (P) to the compression unit (300), a certain work must be supplied. However, since the work cannot be supplied when the differential pressure is resolved, the oil may not be supplied to the compression unit 300 and may stay in the oil storage space P as in the II direction.

4 is a view showing the structure and principle of the valve unit constituting the compressor according to the present disclosure.

Referring to FIGS. 4(a) and 4(b), the valve part 600 is provided at one end of the rotation shaft 230 and is coupled to the coupling part 610 to rotate together with the rotation shaft 230 and the coupling. It is coupled to the unit 610 and rotates together with the rotating shaft 230, but is movably coupled in the coupling unit 610 to selectively open and close the refrigerant auxiliary flow path 235 depending on whether the rotating shaft 230 rotates. It may include an opening/closing unit 620 .

The opening/closing unit 620 is provided to be in contact with the coupling unit 610 or the rotating shaft 230, and a blocking unit 621 for selectively opening and closing the refrigerant auxiliary flow path 235 according to whether the rotating shaft 230 rotates. ) and a mass part 622 extending or coupled from the blocking part 621 to open and close the refrigerant auxiliary flow path 235 by its own weight.

The opening/closing unit 620 may rotate to open and close the refrigerant auxiliary flow path 235 around a coupling point at one side of the coupling unit 610 .

When the rotational shaft 230 accelerates from a standstill and the rotational speed V starts to rotate, gravity Fg and centrifugal force Fc according to the rotation of the rotational shaft 230 act on the mass part 622 . . Gravity and centrifugal force acting on the blocking part 621 also exist, but since the mass of the mass part 622 is relatively large, the gravity and centrifugal force according to the mass of the blocking part 621 can be ignored.

When the rotation speed V of the rotation shaft 230 increases, the gravity Fg is maintained constant, but the centrifugal force Fc may continuously increase. The gravity Fg and the centrifugal force Fc may provide a rotational moment to the opening/closing part 620 . As the centrifugal force Fc increases, the force to rotate the opening/closing unit 620 in a counterclockwise direction may become stronger. Therefore, when the rotational speed V of the rotating shaft 230 reaches the reference speed Vo, the gravity Fg and the centrifugal force Fc are balanced, so that the refrigerant auxiliary flow path 235 is closed immediately before closing. can be maintained in the state of

The reference speed Vo may be appropriately changed according to the conditions and purpose of use of the compressor 10 .

Contrary to the above, it can be assumed that the rotation speed V of the rotation shaft 230 rotates faster than the reference speed Vo, and then the operation of the compressor 10 stops and the rotation speed V decreases. have. When the rotation speed V is greater than the reference speed Vo, the centrifugal force Fc may prevail over the gravity Fg. Accordingly, the compressor 10 may operate while the refrigerant auxiliary flow path 235 is closed.

At the moment when the rotational speed V becomes equal to the reference speed Vo, the gravity Fg and the centrifugal force Fc are balanced, so that the opening/closing unit 620 maintains its original state. Accordingly, the refrigerant auxiliary flow path 235 may be maintained closed.

However, when the rotational speed V is smaller than the reference speed Vo, the gravity Fg may act more predominantly than the centrifugal force Fc. Accordingly, a clockwise moment may be applied to the opening/closing part 620 and the refrigerant auxiliary flow path 235 may be opened by the moment. When the refrigerant auxiliary flow path 235 is opened, the refrigerant flows to the compression unit 300 through the refrigerant auxiliary flow path 235 and the differential pressure inside the compressor 10 is resolved to prevent the reverse flow of the oil. have.

In the above-described manner, the valve unit 600 may selectively open and close the refrigerant auxiliary flow path 235 according to whether the rotation shaft 230 rotates. Here, the expression acting according to whether the rotation shaft 230 rotates may mean that the rotation speed V of the rotation shaft 230 can be compared with the reference speed Vo.

The reference speed Vo corresponds to a value that can be appropriately selected according to the usage conditions and purpose in various situations. In addition, by adjusting the weight of the mass part 622, the reference speed Vo can be kept constant, and it can be used according to various usage conditions and purposes.

5 is a view showing a valve part of the compressor according to the present disclosure.

Referring to FIG. 5 , the valve part 600 may include a hinge part 630 which is formed to protrude from an end of the coupling part 610 and is provided so that the opening and closing part is coupled thereto. The opening/closing part 620 may be coupled to the coupling part 610 by the hinge part 630 . The opening/closing unit 620 may be rotatably coupled to the hinge unit 630 as a center of rotation to open and close the refrigerant auxiliary flow path 235 .

The hinge part 630 may be provided with a through hole to communicate with the through hole provided on one side of the opening and closing part 620 . The coupling part 610 and the opening/closing part 620 may be rotatably coupled to each other by a pin passing through the through hole at the same time. However, the present invention is not limited thereto, and the opening/closing unit 620 may be rotatably provided and may be coupled by another method in which the hinge unit 630 is rotatably coupled. Since a large vibration is applied to the opening/closing unit 620 connected to the rotation shaft 230 when the compressor is operating, the opening/closing unit 620 may be coupled to the coupling unit 610 with a minimum of components.

The mass part 622 may be formed to extend to a sufficient length in a line not to be interfered with by the stator 210 or the rotor 220 . In addition, the mass part 622 may be provided to contact the outer peripheral surface of the rotation shaft 230 when the rotation shaft 230 is completely stopped. Accordingly, one surface of the mass part 622 in contact with the rotation shaft 230 may be formed to have a predetermined curvature to correspond to the outer peripheral surface of the rotation shaft 230 .

The blocking part 621 is preferably formed to sufficiently shield one surface of the refrigerant auxiliary flow path 235 . Therefore, the portion of the blocking part 621 in contact with the refrigerant auxiliary flow path 235 is formed of a compressible material, so that when the rotating shaft 230 rotates, it is sufficiently in close contact with the refrigerant auxiliary flow path 235 to assist the refrigerant. It is possible to prevent unnecessary loss of the refrigerant to the flow path 235 . To this end, the blocking part 621 may further include a configuration that protrudes to correspond to the refrigerant auxiliary flow path 235 .

6 is a cross-sectional view illustrating a valve part of a compressor according to the present disclosure.

Referring to FIG. 6 , the refrigerant auxiliary flow path 235 is provided to extend in the radial direction of the refrigerant auxiliary flow path 235 from one side of the refrigerant auxiliary flow path 235 facing the driving unit 200, so that the coupling part ( It may further include a receiving part 2351 for accommodating the 610 .

The coupling part 610 may be coupled to the receiving part 2351 in a press-fit manner. Since there is a possibility that the refrigerant is lost between the valve part 600 and the rotation shaft 230 , the valve part 600 and the rotation shaft 230 need to be airtightly coupled. Accordingly, by press-fitting the coupling part 610 of the valve part 600 into the receiving part 2351, the unnecessary inflow and outflow of the refrigerant is prevented, thereby increasing the stability and efficiency of the compressor.

In order to airtightly couple the coupling part 610 to the receiving part 2351, the outer peripheral surface of the coupling part 610 may be surface-treated with a compressible material. Thereby, the stability and efficiency of the compressor can be improved.

As described above, the valve part 600 may be coupled to the rotation shaft 230 in such a way that it is press-fitted. That is, the valve part 600 may be provided detachably from the rotation shaft 230 . The valve part 600 may be easily replaced if necessary. Therefore, there is an advantage in that the maintenance and repair of the valve unit 600 is useful.

7 shows another embodiment of the valve unit of the present disclosure.

Referring to FIG. 7 , the valve part 600 may include the coupling part 610 , the blocking part 621 , the mass part 622 , and a first connection member 623 . The blocking part 621 and the mass part 622 may be rotatably coupled by a first hinge part 631 . The mass part 622 and the first connection member 623 may be rotatably coupled by a second hinge part 632 . The first connection member 623 and the coupling part 610 may be rotatably coupled by a third hinge part 633 .

The first connection member 623 may transmit a rotational force due to gravity and centrifugal force due to the weight of the mass portion 622 to the blocking portion 621 . A plurality of the mass parts 622 may be provided at positions symmetrical to each other. Accordingly, it is possible to prevent unnecessary eccentricity and eccentric moment from being applied to the rotation shaft 230 . Therefore, it is possible to prevent bending due to the rotation of the rotation shaft 230 . In addition, since a rotational moment is added to the blocking portion 621 at a symmetrical position, the blocking portion 621 is more firmly in close contact with the refrigerant auxiliary passage 235 to shield the refrigerant auxiliary passage 235 .

Hereinafter, the operating principle of the valve unit 600 will be described with reference to the right part of the drawing.

Referring to FIG. 7A , when the operation of the compressor 10 is stopped and the rotation shaft 230 is decelerated, when the rotation speed of the rotation shaft 230 is reduced to a reference speed or less, the mass part 622 ), gravitational force prevails over centrifugal force. Accordingly, a clockwise moment acts on the first hinge part 631 , a clockwise moment on the second hinge part 632 , and a counterclockwise moment on the third hinge part 633 , and the blocking part 621 moves in the direction of opening the refrigerant auxiliary flow path (235). Accordingly, when the rotating shaft 230 is stopped, the refrigerant auxiliary flow path 235 is opened to relieve the pressure differential inside the compressor 10 and prevent the reverse flow of the oil.

Referring to FIG. 7(b) , when the compressor 10 starts to operate and the rotation shaft 230 accelerates, when the rotation speed of the rotation shaft 230 increases to a reference speed or more, the mass part 622 ), the centrifugal force prevails over gravity. Accordingly, a counterclockwise moment is applied to the first hinge part 631 , a counterclockwise moment is applied to the second hinge part 632 , and a clockwise moment is applied to the third hinge part 633 , and the blocking The part 621 moves in a direction to block the refrigerant auxiliary flow path 235 . Accordingly, when the rotating shaft 230 rotates, the refrigerant auxiliary flow path 235 may be blocked to form a differential pressure inside the compressor 10 , and the compressor 10 may operate normally.

The valve part 600 as described above may include two or more of the mass parts 622 , and may be provided at positions symmetrical to each other to prevent excessive vibration of the rotation shaft 230 .

8 shows another embodiment of the valve part of the present disclosure.

Referring to FIG. 8 , the valve part 600 may include the coupling part 610 , the blocking part 621 , the mass part 622 , and an elastic member 624 . The mass part 622 may be rotatably coupled to the coupling part 610 by a fourth hinge part 634 . The elastic member 624 may provide an elastic force so that the blocking part 621 opens the refrigerant auxiliary passage 235 .

A plurality of the mass parts 622 may be provided at positions symmetrical to each other. Accordingly, it is possible to prevent unnecessary eccentricity and eccentric moment from being applied to the rotation shaft 230 . Therefore, it is possible to prevent bending due to the rotation of the rotation shaft 230 . In addition, since a rotational moment is added to the blocking portion 621 at a symmetrical position, the blocking portion 621 is more firmly in close contact with the refrigerant auxiliary passage 235 to shield the refrigerant auxiliary passage 235 .

Hereinafter, the operating principle of the valve unit 600 will be described with reference to the right part of the drawing.

Referring to FIG. 8( a ), when the operation of the compressor 10 is stopped and the rotation shaft 230 decelerates, when the rotation speed of the rotation shaft 230 decreases below a reference speed, the mass part 622 ), gravitational force prevails over centrifugal force. Accordingly, a clockwise moment acts on the fourth hinge part 634 .

In addition, the blocking part 621 receives a force in a direction in which the refrigerant auxiliary flow path 235 is opened by the elastic member 624 . Accordingly, the blocking part 621 moves in a direction in which the refrigerant auxiliary flow path 235 is opened. That is, when the rotating shaft 230 is stopped, the refrigerant auxiliary flow path 235 is opened to relieve the pressure differential inside the compressor 10 and prevent the reverse flow of the oil.

Referring to FIG. 8( b ), in contrast to FIG. 8( a ), when the compressor 10 starts to operate and the rotating shaft 230 accelerates, the rotational speed of the rotating shaft 230 increases above the reference speed. When this is done, centrifugal force preferentially acts on the mass portion 622 than gravity. Accordingly, a counterclockwise moment acts on the fourth hinge part 634 . Accordingly, the mass portion 622 applies a force in a direction to block the blocking portion 621 and the refrigerant auxiliary flow path 235 . However, the elastic member 624 may provide a force to move the blocking part 621 in the opposite direction. Accordingly, in order for the blocking part 621 to block the refrigerant auxiliary flow path 235, the elastic member 624 may be provided to have an appropriate elastic force.

That is, when the rotating shaft 230 rotates, the refrigerant auxiliary flow path 235 may be blocked to form a differential pressure inside the compressor 10 , and the compressor 10 may operate normally.

The valve part 600 as described above may include two or more of the mass parts 622 , and may be provided at positions symmetrical to each other to prevent excessive vibration of the rotation shaft 230 .

The present disclosure may be modified and implemented in various forms, but the scope of the rights is not limited to the above-described embodiments. Therefore, if the modified embodiment includes the elements of the claims of the present disclosure, it should be regarded as belonging to the scope of the present disclosure.

1 Refrigerant cycle
10 Compressor
100 Case 110 Receiving shell 120 Exhaust shell 121 Exhaust unit 130 Blocking shell
200 Drive 210 Stator 201 Drive return flow path
220 Rotor 230 Rotation Shaft 231 Main Shaft
232 bearing
232a main bearing
232b eccentric shaft
232c fixed bearing part
233 oil feeder 233a extension shaft
233b spiral groove
234 oil supply euro
234 a 1st oil hole
234 b 2nd oil hole
234 c 3rd Oil Hole
234 d 4th Oil Hole
235 Refrigerant Auxiliary Oil
2351 receptacle
300 Compression unit 301 Compression return passage 310a Main return passage 320a Fixed return passage
310 Main frame 311 Main head plate 318 Main through hole 3181 Main shaft
312 Side plate 314 Oil pocket
320 Fixed scroll 321 Fixed end plate 322 Fixed side plate 323 Fixed wrap
325 inlet hole 326 outlet hole
327 Bypass hole 328 Fixed through hole 3281 Fixed shaft part
330 Orbiting scroll 331 Orbiting mirror plate 333 Orbiting wrap 338 Orbiting through hole
340 Oldham Ring 350 Back pressure seal
400 Drive balancer 410 Center balancer 420 Outer balancer
500 muffler 510 receiving body 520 coupling part
530 Extension 540 Concave 541 Muffler Bearing
600 Valve part 610 Combination part 620 Opening/closing part
621 Blocking part 622 Mass part 623 First connection part
630 hinge
631 First hinge part 632 Second hinge part 633 Third hinge part 634 Fourth hinge part

Claims (14)

a case having a discharge part through which the refrigerant is discharged on one side and providing a storage space for storing oil;
a driving unit including a stator coupled to the inner circumferential surface of the case to generate a rotating magnetic field, and a rotor accommodated in the stator and rotated by the rotating magnetic field;
a rotating shaft coupled to or extended from the rotor in a direction away from the discharge unit;
a compression unit coupled to the rotating shaft to compress the refrigerant; and
and a muffler coupled to the compression unit to guide the refrigerant to the discharge unit;
The rotation axis is
an oil supply passage for supplying the oil accommodated in the oil storage space to the compression unit;
and a refrigerant auxiliary passage extending through one end of the rotation shaft facing the discharge unit in the oil supply passage and provided to allow the refrigerant to flow;
and a valve coupled to the rotary shaft to selectively open and close the refrigerant auxiliary flow path according to whether the rotary shaft rotates. The method of claim 1,
the valve part
a coupling part provided at one end of the rotation shaft facing the discharge part and coupled to rotate together with the rotation shaft; and
and an opening and closing part coupled to the coupling part and movably coupled to the coupling part so as to rotate together with the rotation shaft and selectively open and close the refrigerant auxiliary flow path according to whether the rotation shaft rotates. 3. The method of claim 2,
The opening and closing part
a blocking unit provided in contact with the coupling unit or the rotating shaft to selectively open and close the refrigerant auxiliary flow path according to whether the rotating shaft rotates; and
A compressor comprising a; a mass portion extending or coupled from the blocking portion to open and close the refrigerant auxiliary flow path by its own weight. 4. The method of claim 3,
the mass part
When the rotational speed of the rotating shaft is less than the reference speed, the refrigerant auxiliary flow path is opened,
Compressor, characterized in that the refrigerant auxiliary flow path is closed when the rotation speed of the rotating shaft is equal to or greater than the reference speed. 3. The method of claim 2,
the coupling part
A hinge part formed to protrude from an end of the coupling part facing the discharge part and provided so that the opening and closing part is coupled;
The compressor, characterized in that the opening/closing part is rotatably coupled to the upper hinge hinge part as a center of rotation. 4. The method of claim 3,
a first connection part having one end rotatably coupled to the mass part and the other end rotatably coupled to the coupling part to transfer the weight of the mass part to the blocking part. 7. The method of claim 6,
a first hinge part provided on one side of the blocking part to rotatably couple the blocking part and the mass part;
a second hinge part provided in the mass part to rotatably couple the mass part and the first connection part; and
A compressor comprising a; a third hinge portion provided on one side of the coupling portion for rotatably coupling the coupling portion and the first connection portion. 7. The method of claim 6,
Compressor, characterized in that the mass portion and the first connection portion is provided in plurality. 4. The method of claim 3,
and an elastic member provided on the coupling part or the rotating shaft to be in contact with the blocking part, and providing an elastic force to open the refrigerant auxiliary flow path. 10. The method of claim 9,
and a fourth hinge part rotatably coupling the mass part to the coupling part. 10. The method of claim 9,
The compressor, characterized in that provided with a plurality of mass parts. 3. The method of claim 2,
and an accommodating part provided to extend in a radial direction of the refrigerant auxiliary flow path at one side of the refrigerant auxiliary flow path facing the discharge unit to accommodate the coupling part. 13. The method of claim 12,
The valve unit is a compressor, characterized in that provided to be separable from the refrigerant auxiliary flow path. 4. The method of claim 3,
The mass part is a compressor, characterized in that it is provided so that the weight can be changed.

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