Compressor having oil feeding channels

A scroll type compressor includes an orbiting scroll including an orbiting wrap and a fixed scroll including a fixed wrap, in which first and second oil channels are respectively configured to supply oil to inner and outer oil channels formed by the orbiting wrap and the fixed wrap. Thus, the scroll type compressor has an oil channel structure that allows oil feeding into to the scrolls.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of Korean Patent Application No. 10-2020-0047699, filed on Apr. 20, 2020, which is hereby incorporated by reference as when fully set forth herein.

TECHNICAL FIELD

The present disclosure relates to a compressor. More specifically, the present disclosure relates to a scroll type compressor having an oil feeding channel capable of supplying oil to a compressing assembly in which refrigerant is compressed.

BACKGROUND

Generally, a compressor is an apparatus applied to a refrigeration cycle such as a refrigerator or an air conditioner, which compresses refrigerant to provide work necessary to generate heat exchange in the refrigeration cycle.

The compressors may be classified into a reciprocating type compressor, a rotary type compressor, and a scroll type compressor based on a scheme in which the refrigerant is compressed. In the scroll type compressor, while an orbiting scroll is engaged with a fixed scroll fixed in an internal space of a sealed container, the orbiting scroll orbits, thereby to define a compression chamber between a fixed wrap of the fixed scroll and an orbiting wrap of the orbiting scroll.

Compared with other types of the compressors, the scroll type compressor may obtain a relatively high compression ratio because the refrigerant is continuously compressed using the scrolls engaged with each other, and may obtain a stable torque because suction, compression, and discharge of the refrigerant proceed smoothly. For this reason, the scroll type compressor is widely used for compressing the refrigerant in the air conditioner and the like.

Referring to Japanese Patent No. 6344452, a conventional scroll type compressor includes a casing forming an outer shape of the compressor and having a discharger for discharging refrigerant, a compression assembly fixed to the casing to compress the refrigerant, and a driver fixed to the casing to drive the compression assembly, wherein the compression assembly and the driver are coupled to a rotatable shaft that is coupled to the driver and rotates.

The compression assembly includes a fixed scroll fixed to the casing and having a fixed wrap, and an orbiting scroll including an orbiting wrap orbiting in a state of being engaged with the fixed wrap via the rotatable shaft. In the conventional scroll type compressor, the rotatable shaft is eccentric, and the orbiting scroll is fixed to the eccentric rotatable shaft and orbits. Thus, the orbiting scroll orbits along the fixed scroll to compress the refrigerant.

In the conventional scroll type compressor, the compression assembly is generally disposed below the discharger, and the driver is generally disposed below the compression assembly. Further, the rotatable shaft generally has one end coupled to the compression assembly and the other end passing through the driver.

The conventional scroll type compressor has difficulty in supplying oil into the compression assembly because the compression assembly is disposed above the driver and is closer to the discharger. Further, an additional lower frame under the driver is required to separately support the rotatable shaft connected to the compression assembly. Further, in the conventional scroll compressor, because action points of a gas force generated via the compression of the refrigerant and a reaction force supporting the gas force do not coincide with each other within the compression assembly, the orbiting scroll tilts, resulting in a problem of lowering efficiency and reliability thereof.

In order to solve such problems, referring to Korean Patent Application Publication No. 10-2018-0124636, in recent years, a scroll type compressor (also known as a lower scroll type compressor or a shaft-through scroll type compressor) having the driver below the discharger and having the compression assembly below the driver has emerged.

The shaft-through scroll type compressor has the advantage of smooth oil supply since the compressing assembly300is closer to an oil storage space than the driver is. Further, since the compressing assembly300itself supports the rotatable shaft extending from the driver, a structure for separately supporting the rotatable shaft may be omitted, thereby simplifying a structure thereof.

Further, when the rotatable shaft extends through an entirety of the compressing assembly300, the rotatable shaft supports vibration or pressure generated in the compressing assembly300in a longitudinal direction, thereby improving the reliability of the compressor.

FIGS.1A and1Bshow a detailed structure of the compressing assembly of the conventional compressor.

Referring toFIG.1A, the compressing assembly may include an orbiting scroll330that rotatably accommodates a rotatable shaft230, and a fixed scroll320engaging with the orbiting scroll to form a compression chamber in which the refrigerant is compressed, and a main frame310mounted on the fixed scroll320to accommodate the orbiting scroll330therein.

The rotatable shaft230may include an eccentric shaft232having an diameter expanding in a biased manner as accommodated in the orbiting scroll330. Accordingly, as the rotatable shaft230rotates, the eccentric shaft232presses the orbiting scroll330along a circumference of the fixed scroll320to continuously compress the refrigerant flowing along the orbiting scroll330and the fixed scroll320.

Since the orbiting scroll330and the fixed scroll320may cause friction therebetween in the process of compressing the refrigerant, and may be overheated as the temperature of the refrigerant increases, the conventional compressor may further include an oil feeding channel passing through the rotatable shaft230and the main frame310and the fixed scroll320. The oil feeding channel I extends to an area facing the orbiting wrap333of the orbiting scroll330to deliver the oil to the compression chamber.

In order to smoothly supply the oil to the orbiting wrap333, an outlet of the oil feeding channel I may be disposed at one of an inner channel A spaced from an inner face of the orbiting wrap333or an outer channel B spaced from an outer face of the orbiting wrap333.

However, the inner channel A and the outer channel B may be selectively blocked as the orbiting wrap333moves according to the rotation of the eccentric shaft232. For example, when the outlet of the oil feeding channel I is disposed at the outer channel B, and when the orbiting wrap333moves to the outlet of the oil feeding channel I, the oil feeding channel I may be closed such that the oil feeding is stopped.

FIG.1Bshows an oil feeding pressure according to an angle at which the orbiting wrap333extends in a direction in which the orbiting wrap333accommodates the rotatable shaft230relative to a refrigerant intake hole of the fixed scroll through which the refrigerant is sucked.

Referring to a graphFIG.1B, it may be seen that oil is supplied to the outer channel B in a section of 0 to 30 degrees and a section of 270 degrees to 360 degrees, while the oil is supplied to the inner channel A in a section of 70 to 220 degrees. However, it may be seen that the oil feeding channel I is closed by the orbiting wrap333so that the oil feeding is stopped in a section between 30 degrees and 70 degrees and a section between 220 degrees and 270 degrees.

Thus, the conventional compressor has a problem in that the oil feeding stops in the specific section, so that the oil cannot be fed to the entire compressor. Further, there is a problem in that the reliability of the compressor cannot be guaranteed due to structural limitations such as severe wear and damage in the specific section.

SUMMARY

A purpose of the present disclosure is to provide a scroll type compressor in which both of outlets for feeding oil into a region between the orbiting scroll and the fixed scroll may be prevented from being blocked even when the orbiting scroll moves by the rotatable shaft.

A purpose of the present disclosure is to provide a scroll type compressor in which a plurality of oil channels to supply oil are defined to prevents oil feeding from being interrupted.

A purpose of the present disclosure is to provide a scroll type compressor in which all of a plurality of oil channels for supplying oil may be prevented from being blocked no matter where the orbiting scroll is positioned.

A purpose of the present disclosure is to provide a scroll type compressor having oil feeding channels for feeding the oil to the inner and outer faces of the orbiting wrap of the orbiting scroll.

A purpose of the present disclosure is to provide a scroll type compressor in which a plurality of oil feeding channels may be defined in on a main scroll and a fixed scroll, or a plurality of oil feeding channels may be defined in the orbiting scroll.

The present disclosure provides a compressor having a first oil channel supplying oil to a compression chamber formed by an orbiting scroll and a fixed scroll, and a second oil channel spaced from the first oil channel to feed the oil.

Each of the first oil channel and the second oil channel may act as each direct oil injection channel. That is, each of the oil feeding lines before a crank angle 0° may be formed such that each of oil feeding lines to each of compression chambers may be created.

The first oil channel and the second oil channel may be arranged such that oil feeding through at least one of the first oil channel or the second oil channel is always available. Therefore, a structure capable of always feeding the oil into all regions of the compression chamber may be formed.

In the compressor according to the present disclosure, the first oil channel may act as an oil feeding channel having a conventional differential pressure oil feeding structure, and the second oil channel may act as a lower pressure ratio oil feeding channel. Therefore, the oil feeding under the normal operation range and the oil feeding under the lower pressure ratio may also be performed at the same time. The lower pressure power ratio oil feeding line may be constructed to communicate with the refrigerant inlet for smooth oil feeding even at a pressure ratio of 1.1 or lower. Further, the oil feeding line for direct injection of oil to the inlet after decompression via a decompression pin for the oil of the oil storage as the discharge pressure space may be formed. As a result, the low pressure ratio region oil feeding amount may be improved and bearing reliability may be secured. In this connection, the compressor according to the present disclosure may be constructed to improve the oil feeding amount by securing the differential pressure amount via adjustment of the oil feeding communication angle (for example, before start angle 0° C.). Further, the compressor according to the present disclosure may be constructed to secure bearing reliability during low pressure ratio operation by securing an oil feeding amount to prevent abnormal behavior of the orbiting scroll by improving the intermediate pressure of the orbiting scroll. Therefore, it is possible to improve the oil feeding efficiency under the lower pressure force ratio.

Further, the compressor according to the present disclosure may secure the reliability of the compressor via the dual oil feeding channels that may allow always-oil feeding. One of the first oil channel and the second oil channel may be defined as a communication hole that may be always opened. Thus, a structure in which oil feeding is always possible may be implemented.

In one example, the first oil channel and the second oil channel may supply oil to different regions. The first oil channel and the second oil channel may be constructed to be spaced apart from each other by a spacing larger than a thickness of the orbiting wrap, and may be located in positions at which both of the first oil channel and the second oil channel are prevented from being simultaneously closed by the orbiting wrap or the fixed wrap.

The outlet of the first oil channel may be closer to the refrigerant discharge hole or the rotatable shaft than the outlet of the second oil channel may be. In one example, the second oil channel may supply oil to a relatively lower pressure region, and the first oil channel may supply oil to a relatively high pressure region.

Accordingly, when oil is not supplied to the high pressure region, oil may be supplied to the lower pressure region. Alternatively, when oil is not supplied to the lower pressure region, oil may be supplied to the high pressure region.

Further, even when the orbiting wrap moves and closes the first oil channel, the second oil channel may be opened. Alternatively, even when the orbiting wrap moves and closes the second oil channel, the first oil channel may be opened. As a result, a state in which the oil is fed to the inside of the compressor may always be maintained.

The scroll type compressor may have a first oil channel located inside the orbiting scroll and a second channel located outside the orbiting scroll.

In one embodiment, a compressor includes a casing including a discharger to discharge refrigerant, and an oil storage space for storing oil therein; a driver coupled to an inner circumferential face of the casing; a rotatable shaft coupled to the driver and constructed to supply the oil; and a compressing assembly coupled to the rotatable shaft to compress the refrigerant, wherein the compressing assembly is lubricated with the oil.

The compressing assembly includes: an orbiting scroll including: an orbiting end plate supporting the rotatable shaft rotatably and performing an orbiting motion; and an orbiting wrap extending along a circumference of the orbiting end plate to compress the refrigerant; a fixed scroll including: a fixed end plate having a refrigerant inlet and a discharge hole defined therein, wherein the discharge hole is spaced from the inlet and discharges the compressed refrigerant; and a fixed wrap extending along the orbiting wrap and on the fixed end plate to compress the refrigerant; a main frame mounted on the fixed end plate to accommodate therein the orbiting scroll, wherein the rotatable shaft passes through the main frame; and an oil feeding channel passing through the orbiting end plate or the fixed end plate and feeding the oil delivered from the rotatable shaft into a region between the orbiting wrap and the fixed wrap.

The oil feeding channel includes: a first oil channel constructed to supply the oil in a first region between the fixed wrap and the orbiting wrap; and a second oil channel separated from the first oil channel or branched from the first oil channel to supply the oil to a second region other than the first region, wherein a spacing between an outlet of the first oil channel and the rotatable shaft is smaller than a spacing between an outlet of the second oil channel and the rotatable shaft.

In another embodiment, in the compressor according to the present disclosure, the first oil channel and the second oil channel may pass through the orbiting end plate, and the outlet of the first oil channel and the outlet of the second oil channel may be defined in the orbiting end plate.

The present disclosure has the effect that the oil feeding may be prevented from being stopped regardless of the position of the orbiting scroll.

The present disclosure has the effect that oil feeding may always be performed no matter where the orbiting scroll is located.

The present disclosure is effective in preventing compressor wear and overheating by maintaining the oil supply to all of the oil channels formed by the orbiting wrap and the fixed wrap.

DETAILED DESCRIPTION

For simplicity and clarity of illustration, elements in the figures are not necessarily drawn to scale. The same reference numbers in different figures denote the same or similar elements, and as such perform similar functionality. Furthermore, in the following detailed description of the present disclosure, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure. However, it will be understood that the present disclosure may be practiced without these specific details. In other instances, well-known methods, procedures, components, and circuits have not been described in detail so as not to unnecessarily obscure aspects of the present disclosure. Examples of various embodiments are illustrated and described further below. It will be understood that the description herein is not intended to limit the claims to the specific embodiments described. On the contrary, it is intended to cover alternatives, modifications, and equivalents as may be included within the spirit and scope of the present disclosure as defined by the appended claims. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the present disclosure. As used herein, the singular forms “a” and “an” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms “comprises”, “comprising”, “includes”, and “including” when used in this specification, specify the presence of the stated features, integers, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, operations, elements, components, and/or portions thereof.

FIG.2describes the basic structure of the compressor of one embodiment of the present disclosure. A scroll type compressor10according to the present disclosure is generally installed on a circuit of a refrigerant cycle having a condenser2, an expansion valve3, and an evaporator4.

Referring toFIG.2, the scroll type compressor10according to an embodiment of the present disclosure may include a casing100having therein a space in which fluid is stored or flows, a driver200coupled to an inner circumferential face of the casing100to rotate a rotatable shaft230, and a compression assembly300coupled to the rotatable shaft230inside the casing and compressing the fluid.

Specifically, the casing100may include a discharger121through which refrigerant is discharged at one side. The casing100may include a receiving shell110formed in a cylindrical shape to receive the driver200and the compression assembly300therein, a discharge shell120coupled to one end of the receiving shell110and having the discharger121, and a sealing shell130coupled to the other end of the receiving shell110to seal the receiving shell110.

The driver200includes a stator210for generating a rotating magnetic field, and a rotor220constructed to rotate by the rotating magnetic field. The rotatable shaft230may be coupled to the rotor220to be rotated together with the rotor220.

The stator210has a plurality of slots defined in an inner circumferential face thereof along a circumferential direction and a coil is wound around the plurality of slots. Further, the stator210may be fixed to an inner circumferential face of the receiving shell110. A permanent magnet may be coupled to the rotor220, and the rotor220may be rotatably coupled within the stator210to generate rotational power. The rotatable shaft230may be pressed into and coupled to a center of the rotor220.

The compression assembly300may include a fixed scroll320coupled to the receiving shell110and disposed in a direction away from the discharger121with respect to the driver200, an orbiting scroll330coupled to the rotatable shaft230and engaged with the fixed scroll320to define a compression chamber, and a main frame310accommodating the orbiting scroll330therein and seated on the fixed scroll320to form an outer shape of the compression assembly330.

As a result, the lower scroll type compressor10has the driver200disposed between the discharger120and the compression assembly300. In other words, the driver200may be disposed at one side of the discharger120, and the compression assembly300may be disposed in a direction away from the discharger121with respect to the driver200. For example, when the discharger121is disposed above the casing100, the compression assembly300may be disposed below the driver200, and the driver200may be disposed between the discharger120and the compression assembly300.

Thus, when oil is stored in an oil storage space p of the casing100, the oil may be supplied directly to the compression assembly300without passing through the driver200. In addition, since the rotatable shaft230is coupled to and supported by the compression assembly300, a lower frame for rotatably supporting the rotatable shaft may be omitted.

In one example, the lower scroll type compressor10according to the present disclosure may be configured such that the rotatable shaft230passes through not only the orbiting scroll330but also the fixed scroll320to be in face contact with both the orbiting scroll330and the fixed scroll320.

As a result, an inflow force generated when the fluid such as the refrigerant is flowed into the compression assembly300, a gas force generated when the refrigerant is compressed in the compression assembly300, and a reaction force for supporting the same may be directly exerted on the rotatable shaft230. Accordingly, the inflow force, the gas force, and the reaction force may be exerted to a point of application of the rotatable shaft230. As a result, since a tilting moment does not act on the orbiting scroll320coupled to the rotatable shaft230, tilting or overturn of the orbiting scroll may be blocked. In other words, tilting in an axial direction of the tilting may be attenuated or prevented, and the overturn moment of the orbiting scroll330may also be attenuated or suppressed. As a result, noise and vibration generated in the lower scroll type compressor10may be blocked. In addition, the fixed scroll320is in face contact with and supports the rotatable shaft230, so that durability of the rotatable shaft230may be reinforced even when the inflow force and the gas force act on the rotatable shaft230. In addition, a backpressure generated while the refrigerant is discharged to outside is also partially absorbed or supported by the rotatable shaft230, so that a force (normal force) in which the orbiting scroll330and the fixed scroll320become excessively close to each other in the axial direction may be reduced. As a result, a friction force between the orbiting scroll330and the fixed scroll230may be greatly reduced.

As a result, the compressor10attenuates the tilting in the axial direction and the overturn or tilting moment of the orbiting scroll330inside the compression assembly300and reduces the frictional force of the orbiting scroll, thereby increasing an efficiency and a reliability of the compression assembly300.

In one example, the main frame310of the compression assembly300may include a main end plate311disposed at one side of the driver200or at a lower portion of the driver300, a main side plate312extending in a direction farther away from the driver200from an inner circumferential face of the main end plate311and seated on the fixed scroll330, and a main shaft receiving portion318extending from the main end plate311to rotatably support the rotatable shaft230.

A main hole317for guiding the refrigerant discharged from the fixed scroll320to the discharger121may be further defined in the main end plate311or the main side plate312.

The main end plate311may further include an oil pocket314that is engraved in an outer face of the main shaft receiving portion318. The oil pocket314may be defined in an annular shape, and may be defined to be eccentric to the main shaft receiving portion318. When the oil stored in the sealing shell130is transferred through the rotatable shaft230or the like, the oil pocket314may be defined such that the oil is supplied to a portion where the fixed scroll320and the orbiting scroll330are engaged with each other.

The fixed scroll320may include a fixed end plate321coupled to the receiving shell110in a direction away from the driver300with respect to the main end plate311to form the other face of the compression assembly300, a fixed side plate322extending from the fixed end plate321to the discharger121to be in contact with the main side plate312, and a fixed wrap323disposed on an inner circumferential face of the fixed side plate322to define the compression chamber in which the refrigerant is compressed.

In one example, the fixed scroll320may include a fixed through-hole328defined to pass through the rotatable shaft230, and a fixed shaft receiving portion3281extending from the fixed through-hole328such that the rotatable shaft is rotatably supported. The fixed shaft receiving portion3331may be disposed at a center of the fixed end plate321.

A thickness of the fixed end plate321may be equal to a thickness of the fixed shaft receiving portion3381. In this case, the fixed shaft receiving portion3281may be inserted into the fixed through-hole328instead of protruding from the fixed end plate321.

The fixed side plate322may include an inflow hole325defined therein for flowing the refrigerant into the fixed wrap323, and the fixed end plate321may include discharge hole326defined therein through which the refrigerant is discharged. The discharge hole326may be defined in a center direction of the fixed wrap323, or may be spaced apart from the fixed shaft receiving portion3281to avoid interference with the fixed shaft receiving portion3281, or the discharge hole326may include a plurality of discharge holes.

The fixed scroll may have a bypass hole327defined therein through which the refrigerant discharged from the discharge port326is discharged. The bypass hole327may pass through the fixed end plate321.

Further, the fixed scroll320may further include a stepped face324extending in a stepwise manner from the fixed end plate321or the fixed side plate322in order to couple a muffler to be described late thereto. A diameter of the stepped face324may be smaller than a diameter of the fixed end plate321.

The orbiting scroll330may include an orbiting end plate331disposed between the main frame310and the fixed scroll320, and an orbiting wrap333disposed below the orbiting end plate to define the compression chamber together with the fixed wrap323in the orbiting end plate.

The orbiting scroll330may further include an orbiting through-hole338defined through the orbiting end plate331to rotatably couple the rotatable shaft230.

The rotatable shaft230may be constructed such that a portion thereof coupled to the orbiting through-hole338is eccentric. Thus, when the rotatable shaft230rotates, the orbiting scroll330orbits in a state of being engaged with the fixed wrap323of the fixed scroll320to compress the refrigerant.

Specifically, the rotatable shaft230may include a main shaft231coupled to the driver200and rotating, and a support shaft232connected to the main shaft231and rotatably coupled to the compression assembly300. The support shaft232may be included as a member separate from the main shaft231, and may accommodate the main shaft231therein, or may be integrated with the main shaft231.

The support shaft232may include a main support shaft232cinserted into the main shaft receiving portion318of the main frame310and rotatably supported, a fixed support shaft232ainserted into the fixed shaft receiving portion3281of the fixed scroll320and rotatably supported, and an eccentric shaft232bdisposed between the main support shaft232cand the fixed support shaft232a, and inserted into the orbiting through-hole338of the orbiting scroll330and rotatably supported.

In this connection, the main support shaft232cand the fixed support shaft232amay be coaxial to have the same axis center, and the eccentric shaft232bmay be formed such that a center of gravity thereof is radially eccentric with respect to the main support shaft232cor the fixed support shaft232a. In addition, the eccentric shaft232bmay have an outer diameter greater than an outer diameter of the main support shaft232cor an outer diameter of the fixed support shaft232a. As such, the eccentric shaft232bmay provide a force to compress the refrigerant while orbiting the orbiting scroll330when the support shaft232rotates, and the orbiting scroll330may be constructed to regularly orbit the fixed scroll320by the eccentric shaft232b.

However, in order to prevent the orbiting scroll320from spinning, the compressor10according to the present disclosure may further include an Oldham's ring340coupled to an upper portion of the orbiting scroll320. The Oldham's ring340may be disposed between the orbiting scroll330and the main frame310to be in contact with both the orbiting scroll330and the main frame310. The Oldham's ring340may be constructed to linearly move in four directions of front, rear, left, and right directions to prevent the rotation of the orbiting scroll320.

In one example, the rotatable shaft230may be constructed to completely pass through the fixed scroll320to protrude out of the compression assembly300. As a result, the rotatable shaft230may be in direct contact with outside of the compression assembly300and the oil stored in the sealing shell130. The rotatable shaft230may supply the oil into the compression assembly300while rotating.

The oil may be supplied to the compression assembly300through the rotatable shaft230. An oil supply channel234for supplying the oil to an outer circumferential face of the main support shaft232c, an outer circumferential face of the fixed support shaft232a, and an outer circumferential face of the eccentric shaft232bmay be formed at or inside the rotatable shaft230.

In addition, a plurality of oil feed holes234a,234b,234c, and234dmay be defined in the oil supply channel234. Specifically, the oil feed hole may include a first oil feed hole234a, a second oil feed hole234b, a third oil feed hole234c, and a fourth oil feed hole234d. First, the first oil feed hole234amay be defined to pass through the outer circumferential face of the main support shaft232c. The third oil feed hole234cmay be defined in a feed groove2341c.

The first oil feed hole234amay be defined to pass through into the outer circumferential face of the main support shaft232cin the oil supply channel234. In addition, the first oil feed hole234amay be defined to, for example, pass through an upper portion of the outer circumferential face of the main support shaft232c, but is not limited thereto. That is, the first oil feed hole234amay be defined to pass through a lower portion of the outer circumferential face of the main support shaft232c. For reference, unlike as shown in the drawing, the first oil feed hole234amay include a plurality of holes. In addition, when the first oil feed hole234aincludes the plurality of holes, the plurality of holes may be defined only in the upper portion or only in the lower portion of the outer circumferential face of the main support shaft232c, or may be defined in both the upper and lower portions of the outer circumferential face of the main support shaft232c.

In addition, the rotatable shaft230may include an oil shaft233passing through the muffler to be described later to be in contact with the stored oil of the casing100. The oil shaft233may include an extension shaft233apassing through the muffler and in contact with the oil, and a spiral groove233bspirally defined in an outer circumferential face of the extension shaft233aand in communication with the supply channel234.

Thus, when the rotatable shaft230is rotated, due to the spiral groove233b, a viscosity of the oil, and a pressure difference between a high pressure region S1and an intermediate pressure region V1inside the compression assembly300, the oil rises through the oil shaft233and the supply channel234and is discharged into the plurality of oil feed holes. The oil discharged through the plurality of oil feed holes234a,234b,234c, and234dnot only maintains an airtight state by forming an oil film between the fixed scroll250and the orbiting scroll240, but also absorbs frictional heat generated at friction portions between the components of the compression assembly300and discharge the heat.

The oil guided along the rotatable shaft230and supplied through the first oil feed hole234amay lubricate the main frame310and the rotatable shaft230. In addition, the oil may be discharged through the second oil feed hole234band supplied to a top face of the orbiting scroll240, and the oil supplied to the top face of the orbiting scroll240may be guided to the intermediate pressure region through the pocket groove314. For reference, the oil discharged not only through the second oil feed hole234bbut also through the first oil feed hole234aor the third oil feed hole234cmay be supplied to the pocket groove314.

In one example, the oil guided along the rotatable shaft230may be supplied to the Oldham's ring340and the fixed side plate322of the fixed scroll320installed between the orbiting scroll240and the main frame230. Thus, wear of the fixed side plate322of the fixed scroll320and the Oldham's ring340may be reduced. In addition, the oil supplied to the third oil feed hole234cis supplied to the compression chamber to not only reduce wear due to friction between the orbiting scroll330and the fixed scroll320, but also form the oil film and discharge the heat, thereby improving a compression efficiency.

Although a centrifugal oil feed structure in which the lower scroll type compressor10uses the rotation of the rotatable shaft230to supply the oil to the bearing has been described, the centrifugal oil feed structure is merely an example. Further, a differential pressure supply structure for supplying oil using a pressure difference inside the compression assembly300and a forced oil feed structure for supplying oil through a toroid pump, and the like may also be applied.

In one example, the compressed refrigerant is discharged to the discharge hole326along a space defined by the fixed wrap323and the orbiting wrap333. The discharge hole326may be more advantageously disposed toward the discharger121. This is because the refrigerant discharged from the discharge hole326is most advantageously delivered to the discharger121without a large change in a flow direction.

However, because of structural characteristics that the compression assembly300is positioned in a direction away from the discharger121with respect to the driver200, and that the fixed scroll320should be disposed at an outermost portion of the compression assembly300, the discharge hole326is constructed to spray the refrigerant in a direction opposite to a direction toward the discharger121.

In other words, the discharge hole326is defined to spray the refrigerant in a direction away from the discharger121with respect to the fixed end plate321. Therefore, when the refrigerant is sprayed into the discharge hole326as it is, the refrigerant may not be smoothly discharged to the discharger121, and when the oil is stored in the sealing shell130, the refrigerant may collide with the oil and be cooled or mixed.

In order to prevent this problem, the compressor10in accordance with the present disclosure may further include the muffler coupled to an outermost portion of the fixed scroll320and providing a space for guiding the refrigerant to the discharger121.

The muffler may be constructed to seal one face disposed in a direction farther away from the discharger121of the fixed scroll320to guide the refrigerant discharged from the fixed scroll320to the discharger121.

The muffler may include a coupling body coupled to the fixed scroll320and a receiving body510extending from the coupling body to define sealed space therein. Thus, the refrigerant sprayed from the discharge hole326may be discharged to the discharger121by switching the flow direction along the sealed space defined by the muffler.

Further, since the fixed scroll320is coupled to the receiving shell110, the refrigerant may be restricted from flowing to the discharger121by being interrupted by the fixed scroll320. Therefore, the fixed scroll320may further include the bypass hole327passing through the fixed end plate321to allow the refrigerant to pass through the fixed scroll320. The bypass hole327may be constructed to be in communication with the main hole317. Thus, the refrigerant may pass through the compression assembly300, pass by the driver200, and be discharged to the discharger121.

Further, as the refrigerant flows more inwardly from an outer circumferential face of the fixed wrap323, the refrigerant is compressed to have a higher pressure. Thus, an interior of the fixed wrap323and an interior of the orbiting wrap333is maintained in a high pressure state. Accordingly, a discharge pressure is exerted to a rear face of the orbiting scroll as it is. Thus, in a reaction manner thereto, the backpressure is exerted from the orbiting scroll330toward the fixed scroll320. The compressor10according to one embodiment of the present disclosure may further include a backpressure seal350that concentrates the backpressure on a portion where the orbiting scroll320and the rotatable shaft230are coupled to each other, thereby preventing leakage between the orbiting wrap333and the fixed wrap323.

The backpressure seal350has a ring shape to maintain an inner circumferential face thereof at a high pressure, and separate an outer circumferential face thereof at an intermediate pressure lower than the high pressure. Therefore, the backpressure is concentrated on the inner circumferential face of the backpressure seal350, so that the orbiting scroll330is in close contact with the fixed scroll320.

In this connection, when considering that the discharge hole326is defined to be spaced apart from the rotatable shaft230, the backpressure seal350may be configured such that a center thereof is biased toward the discharge hole326. In addition, due to the backpressure seal350, the oil supplied from the first oil feed groove234amay be supplied to the inner circumferential face of the backpressure seal350. Therefore, the oil may lubricate a contact face between the main scroll and the orbiting scroll. Further, the oil supplied to the inner circumferential face of the backpressure seal350may generate a backpressure for pushing the orbiting scroll330to the fixed scroll320together with a portion of the refrigerant.

As such, the compression space of the fixed wrap323and the orbiting wrap333may be divided into the high pressure region S1inside the backpressure seal350and the intermediate pressure region V1outside the backpressure seal350on the basis of the backpressure seal350. In one example, the high pressure region S1and the intermediate pressure region V1may be naturally divided because the pressure is increased in a process in which the refrigerant is inflowed and compressed. However, since the pressure change may occur critically due to a presence of the backpressure seal350, the compression space may be divided by the backpressure seal350.

In one example, the oil supplied to the compression assembly300, or the oil stored in the casing100may flow toward an upper portion of the casing100together with the refrigerant as the refrigerant is discharged to the discharger121. In this connection, because the oil is denser than the refrigerant, the oil may not be able to flow to the discharger121by a centrifugal force generated by the rotor220, and may be attached to inner walls of the discharge shell110and the receiving shell120. The lower scroll type compressor10may further include collection channels respectively on outer circumferential faces of the driver200and the compression assembly300to collect the oil attached to an inner wall of the casing100to the oil storage space of the casing100or the sealing shell130.

The collection channel may include a driver collection channel201defined in an outer circumferential face of the driver200, a compressor collection channel301defined in an outer circumferential face of the compression assembly300, and a muffler collection channel defined in an outer circumferential face of the muffler.

The driver collection channel201may be defined by recessing a portion of an outer circumferential face of the stator210is recessed, and the compressor collection channel301may be defined by recessing a portion of an outer circumferential face of the fixed scroll320. In addition, the muffler collection channel may be defined by recessing a portion of the outer circumferential face of the muffler. The driver collection channel201, the compressor collection channel301, and the muffler collection channel may be defined in communication with each other to allow the oil to pass therethrough.

As described above, because the rotation shaft230has a center of gravity biased to one side due to the eccentric shaft232b, during the rotation, an unbalanced eccentric moment occurs, causing an overall balance to be distorted. Accordingly, the lower scroll type compressor10according to the present disclosure may further include a balancer400that may offset the eccentric moment that may occur due to the eccentric shaft232b.

Because the compression assembly300is fixed to the casing100, the balancer400is preferably coupled to the rotation shaft230itself or the rotor220constructed to rotate. Therefore, the balancer400may include a central balancer410disposed on a bottom of the rotor220or on a face facing the compression assembly300to cancel or reduce an eccentric load of the eccentric shaft232b, and an outer balancer420coupled to a top of the rotor220or the other face facing the discharger121to offset an eccentric load or an eccentric moment of at least one of the eccentric shaft232band the outer balancer420.

Because the central balancer410is disposed relatively close to the eccentric shaft232b, the central balancer410may directly offset the eccentric load of the eccentric shaft232b. Accordingly, the central balancer410is preferably disposed eccentrically in a direction opposite to the direction in which the eccentric shaft232bis eccentric. As a result, even when the rotation shaft230rotates at a low speed or a high speed, because a spacing away from the eccentric shaft232bis close, the central balancer410may effectively offset an eccentric force or the eccentric load generated in the eccentric shaft232balmost uniformly.

The outer balancer420may be disposed eccentrically in a direction opposite to the direction in which the eccentric shaft232bis eccentric. However, the outer balancer420may be eccentrically disposed in a direction corresponding to the eccentric shaft232bto partially offset the eccentric load generated by the central balancer410.

As a result, the central balancer410and the outer balancer420may offset the eccentric moment generated by the eccentric shaft232bto assist the rotation shaft230to rotate stably.

FIGS.3A and3Bshow the compressing assembly and an oil feeding structure of the compressor according to the present disclosure.

FIG.3Ashows a cross section of the compressing assembly, andFIG.3Bshows the fixed wrap323of the fixed scroll320.

The compressing assembly300according to the present disclosure may include an oil feeding channel which passes through the orbiting end plate331and the fixed end plate321and delivers the oil delivered from the oil supply channel234of the rotatable shaft230to the compression chamber defined between the orbiting wrap333and the fixed wrap322.

The oil feeding channel may include a plurality of oil feeding channels. All of the plurality of oil feeding channels may not be closed by the orbiting wrap333or the fixed wrap323when the orbiting scroll330orbits around the fixed scroll320.

For example, the oil feeding channel may include a first oil channel A constructed to supply oil to a region between the fixed wrap323and the orbiting wrap333, and a second oil channel B separated from the first oil channel A or branched from the first oil channel A and constructed to supply oil to a region different from the region to which the first oil channel supplies the oil.

Accordingly, the compressor10according to the present disclosure may supply oil to the compressing assembly300through the plurality of oil channels such as the first oil channel A and the second oil channel B. Therefore, it is possible to quickly and evenly supply the oil to the entire region of the compressing assembly300.

A spacing between an outlet A1(e.g., “first outlet”) of the first oil channel and the rotatable shaft230may be smaller than a spacing between an outlet B1(e.g., “second outlet”) of the second oil channel and the rotatable shaft230.

In the compressing assembly300according to the present disclosure, a region which corresponds to the inside of the backpressure seal350, and in which the discharge hole326is placed may be defined as a high pressure region S1. An intermediate pressure region V1is outside the high pressure region S1and has a pressure higher than the pressure of the incoming refrigerant. A region which is farther away from the rotatable shaft than the intermediate pressure region V1is and is adjacent to the inlet of the refrigerant may be defined as a lower pressure region V2. For example, the lower pressure region V2may refer to a region where the fixed wrap323starts to be wound by a half around the rotatable shaft230(about 0 to 180 degrees).

The outlet A1of the first oil channel may be disposed in the intermediate pressure region V1, and the outlet B1of the second oil channel may be disposed in the lower pressure region V2. Accordingly, the first oil channel A may preferentially supply oil to the high pressure region S1faster than the second oil channel B may. The second oil channel B may preferentially supply oil to the lower pressure region V2faster than the first oil channel A may. Therefore, whether the compressor300compresses the refrigerant at high pressure or at a lower pressure, oil may be smoothly supplied through the first oil channel A and the second oil channel B.

In particular, the second oil channel B may be located outside the first oil channel A, or the outlet B1of the second oil channel may be located closer to the refrigerant inlet than the outlet A1of the first oil channel may. Thus, the second oil channel B may more effectively supply oil to the lower pressure region V2than the first oil channel A may. That is, the second oil channel B may generate a greater differential pressure from that of the oil supply channel234than the first oil channel A may, so that oil may be more effectively supplied to the lower pressure region V2.

In one example, when the compressor300operates at lower pressure, the differential pressure between the lower pressure region V2and the high pressure region S1is not sufficiently large, such that it is difficult to supply oil from the oil supply channel234. Thus, the outlet A1of the first oil channel and the outlet B1of the second oil channel may not be placed in the high pressure region S1, but the outlet A1of the first oil channel and the outlet B1of the second oil channel may be placed in the intermediate pressure region V1, or one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be placed in the lower pressure region V2.

As the eccentric shaft232crotates, the orbiting wrap333may reciprocate toward or away from the fixed wrap323facing the orbiting wrap333. In this process, the outlet of the oil feeding channel I may be closed by the orbiting wrap333. To prevent this blockage, the outlet A1of the first oil channel and the outlet B2of the second oil channel may be spaced apart from each other by a spacing sized such that both of the outlet A1of the first oil channel and the outlet B2of the second oil channel may be prevented from being blocked by the orbiting wrap333or the fixed wrap322.

For example, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be spaced from each other by a spacing larger than a spacing sized such that the outlet A1of the first oil channel and the outlet B1of the second oil channel may be selectively closed by the orbiting wrap333or the fixed wrap323.

When the orbiting wrap333closes the outlet A1of the first oil channel, the outlet B1of the second oil channel is spaced apart from the orbiting wrap333, and is in an open state so that the oil may be supplied through the open the outlet B1. Further, when the orbiting wrap333closes the outlet B1of the second oil channel, the outlet A1of the first oil channel is spaced apart from the orbiting wrap333, and is in an open state so that the oil may be supplied through the open the outlet A1.

In another example, it is desirable that the outlet A1of the first oil channel and the outlet B1of the second oil channel are always open, and are not closed by the orbiting wrap333or the fixed wrap323. When the outlet A1of the first oil channel and the outlet B1of the second oil channel are not defined in the orbiting wrap333or the fixed wrap323, both must be blocked by the orbiting wrap333or the fixed wrap323. In particular, each of diameters of the outlet A1of the first oil channel and the outlet B1of the second oil channel is generally smaller than a thickness of the fixed wrap323or the orbiting wrap333in order not to discharge excessive oil. Therefore, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel is sealed by the orbiting wrap333or the fixed wrap323.

Therefore, the outlet A1of the first oil channel and the outlet B1of the second oil channel are spaced from each other by a spacing S larger than the thickness of the orbiting wrap333or the fixed wrap323, such that both of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be prevented from being closed by the orbiting wrap333or the fixed wrap323.

In one example, both of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be placed in the intermediate pressure region V1or in the lower pressure region V2. Further, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be disposed adjacent to each other, but may be disposed at completely different angular positions around the rotatable shaft230.

In this case, one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may supply oil to an inner channel formed by an outer face of the orbiting wrap333and an inner face of the fixed wrap323, while the remaining one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may supply oil to an outer channel formed by an inner face of the orbiting wrap333and an outer face of the fixed wrap323.

As a result, even when the outlet A1of the first oil channel and the outlet B1of the second oil channel are arranged at completely different angular positions around the rotatable shaft230, or are spaced by different distances from the rotatable shaft230, both of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be prevented from being closed by the orbiting wrap323or the fixed wrap333. In other words, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be kept open.

Referring toFIG.3B, the outlet A1of the first oil channel may be placed in the outer channel formed by the outer face of the fixed wrap323and the inner face of the orbiting wrap333, while the outlet B1of the second oil channel may be disposed in an inner channel formed by the inner face of the fixed wrap323and the outer face of the orbiting wrap333.

Further, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be spaced apart from each other by a spacing larger than the thickness of the orbiting wrap333.

Thus, when the orbiting wrap333is placed on the outer channel while the orbiting wrap333is orbiting, the second oil channel B supplies oil to the compression chamber. When the orbiting wrap333is placed on the inner channel while the orbiting wrap333is orbiting, the first oil channel A may supply oil to the compression chamber. As a result, no matter where the orbiting wrap333is located inside the fixed scroll320, oil may be continuously supplied to the compression chamber300, and the oil may be evenly supplied to the compression chamber.

Hereinafter, an embodiment in which the first oil channel A and the second oil channel B may be specifically installed in the compressing assembly300will be described.

The first oil channel A and the second oil channel B may pass through one of the fixed scroll320or the orbiting scroll330.

Referring toFIGS.3A and3B, the first oil channel A and the second oil channel B may pass through the fixed scroll320, and the main frame310.

In this connection, the first oil channel A and the second oil channel B may be disposed in a position where both of the first oil channel A and the second oil channel B are not closed by the orbiting wrap333.

The oil feeding channel I may include an oil transfer channel319passing through the main frame310and a fixed oil channel329passing through the fixed scroll320. Therefore, the first oil channel A and the second oil channel B may share the oil transfer channel319and the fixed oil channel329, whereas the outlet A1of the first oil channel and the outlet B1of the second oil channel may be placed in different locations. As a result, the process of installing the oil channel on the main frame310and the fixed scroll320may be simplified.

The oil feeding channel I may include the oil transfer channel319which is defined in the main frame310, and along which the oil supplied from the oil supply channel234flows, and the fixed oil channel329defined in the fixed scroll and constructed to communicate with the oil transfer channel to supply the oil to a region between the orbiting scroll330and the fixed scroll310.

In the compressing assembly300of the compressor according to the present disclosure, the oil transfer channel319may be defined in the main frame310fixed to the casing100, and thus the position thereof may always be fixed. Therefore, the oil may be stably introduced into the oil transfer channel319and may be stably transferred to the fixed oil channel329. Further, the amount of oil supplied through the oil transfer channel319may be more easily controlled.

The oil transfer channel319may include a main oil channel3191passing through the main shaft receiving portion318and receiving the oil, an oil passage channel3192which extends from the main oil channel3191to the outer circumferential face along the main end plate311and through which the oil passes, and an oil discharge channel3193connected to a distal end of the oil passage channel3192and extending toward the fixed frame320to discharge the oil.

The main oil channel3191may be defined separately from a space between the main end plate311of the main frame and the orbiting end plate331of the orbiting scroll. As a result, the oil discharged from the first oil feeding hole241amay flow in a region between the main end plate311and the orbiting end plate331and may be supplied to the backpressure seal350, and at the same time may flow into the main oil channel3191.

The main frame310is always fixed to the casing100. Thus, when the oil transfer channel319is defined in the main frame310, oil may be stably supplied to the fixed scroll320.

In one example, the fixed oil channel329may include an oil inflow channel3291which is defined in the fixed side plate to communicate with the oil discharge channel3193, and into which the oil supplied to the oil transfer channel flows, and an oil flow channel3292constructed to communicate with the oil inflow channel3291and defined in the fixed end plate to move the oil supplied to the oil inflow channel to the fixed wrap332.

In this connection, the fixed oil channel329must supply the oil to at least the outer circumferential face of the fixed wrap323. Thus, the oil inflow channel3291may extend from the fixed side plate so as to have a length larger than or equal to the thickness of the fixed wrap323. Further, the oil flow channel3292may extend from the oil inflow channel3291to the outermost inner peripheral face of the fixed wrap323.

In one example, when the oil inflow channel3291extends in a longer manner than the thickness of the fixed wrap323, the fixed oil channel329may further include a lubrication oil channel3293extending from the oil flow channel3292to an inner face of the fixed end plate323or a portion in direct communication to the fixed wrap323.

The oil inflow channel3291and the lubrication oil channel3293may extend in a parallel manner to each other. The oil flow channel3292may extend at a right angle or in an inclined manner with respect to the oil inflow channel and the lubrication oil channel.

In one example, the backpressure seal350may be installed inside the Oldham ring350, and may be constructed to prevent an entirety of the oil supplied from the rotatable shaft230from leaking out directly into a region between the main frame310and the orbiting scroll330. The backpressure seal350may play a role of guiding the oil introduced from the rotatable shaft230to be transferred to the main oil channel3191.

In one example, when the orbiting scroll330is orbiting at high speed, the pressure difference between the high pressure region S1and the intermediate pressure region V1may be very large, thereby causing excessive oil supply to the fixed wrap323and orbiting wrap333. Thus, a large amount of oil may be input into the incoming refrigerant, the fixed wrap323and the orbiting wrap333may be cooled due to the oil, or the oil feeding to the fixed wrap323may be stopped.

To prevent this problem, the compressor of one embodiment of the present disclosure may include pressure reducing means360disposed in the oil transfer channel319or the fixed oil channel329and capable of reducing the pressure difference between the high pressure region and the lower pressure region. The pressure reducing means360may be inserted into the oil transfer channel or the fixed oil channel to reduce the diameter of the oil channel to increase the oil channel resistance. Further, the pressure reducing means360may maximize friction with the oil to increase the oil channel resistance. Therefore, due to the pressure reducing means360, the pressure difference between the high pressure region S1and the intermediate pressure region V1may be partially compensated for to prevent the excessive oil from being supplied to the fixed wrap323and the orbiting wrap333.

Since the pressure reducing means360must be installed and inserted into the oil transfer channel or the fixed oil channel, the main frame310or the fixed scroll320may further include a receiving hole constructed to receive the pressure reducing means360and communicate with the outside of the compressing assembly300.

In one example, the oil inflow channel3291is defined in the fixed frame320for excellent durability, and acts as a location where oil flows into the intermediate pressure region V1defined in the fixed frame320. Therefore, unlike shown, the pressure reducing means360may be inserted into the oil inflow channel3291. As a result, stability of the pressure reducing means360against external shocks and vibrations may be ensured, and the pressure reducing means360may most immediately control the amount of oil to be supplied to the intermediate pressure region V1.

The lubrication oil channel3293may include a first lubrication oil channel3293A communicating with the outlet A1of the first oil channel, and a second lubrication oil channel3293B communicating with the outlet B1of the second oil channel.

That is, the first oil channel A and the second oil channel B may be constructed to share the oil transfer channel319, and the oil inflow channel3291and the oil flow channel3292of the fixed oil channel329with each other.

In this connection, the second lubrication oil channel3293B may be first branched from the oil flow channel3292and extend toward the fixed wrap323, and the first lubrication oil channel3293A may extend from the oil flow channel3292to the rotatable shaft230and extend towards the fixed wrap323.

For example, the second lubrication oil channel3293B may be in communication with the outermost face of the fixed wrap323. The outermost face of the fixed wrap323may refer to a portion at which the fixed wrap begins to engage with the orbiting wrap333. Thus, the second lubrication oil channel3293B may supply oil more smoothly to the lower pressure region V2.

Thus, the main oil channel3191acing as the inlet of the oil transfer channel319may be located in the high pressure region S1, and the fixed oil channel329may be located in the intermediate pressure region V1. Thus, due to the pressure difference therebetween, as the oil supplied from the first oil feeding hole234aflows into the oil transfer channel319, the oil may be transferred to the fixed oil channel329. Thus, the oil may be delivered to the fixed wrap323and lubricate the orbiting wrap333and the fixed wrap323.

In one example, the compressor10according to the present disclosure rotates the rotatable shaft230at high speed to discharge the refrigerant at high pressure from the compressing assembly300. However, the compressor10according to the present disclosure rotates the rotatable shaft230at a low speed to discharge the refrigerant at a relatively lower pressure from the compressing assembly300.

When the refrigerant is compressed at the lower pressure in the compressing assembly300and is discharged out thereof, the coefficient of performance of the refrigeration cycle may be increased, and noise and vibration may be reduced. However, the differential pressure between the high pressure region S1near the rotatable shaft230and the intermediate pressure region V1near the fixed side plate322may be reduced accordingly.

Therefore, the differential pressure between the high pressure region S1and the intermediate pressure region V1is not large, such that the oil supplied from the rotatable shaft230may not be supplied smoothly from the oil transfer channel319or the fixed oil channel329, the oil supply may be stopped, or the oil may reversely flow. Further, due to the pressure reducing means360, the differential pressure between the intermediate pressure region V1and the high pressure region S1may be further reduced, thereby making it more difficult to supply the oil to the first oil channel A or causing the oil backward flow.

However, due to the arrangement of the second oil channel B, the oil may be smoothly supplied to the lower pressure region V2. Therefore, regardless of what load the compressor10operates under, the oil may be supplied to the inside of the compressing assembly300regardless of the pressure situation.

Further, the first oil channel A may be disposed in an outer channel formed by the outer face of the fixed wrap323and the inner face of the orbiting wrap333, while the second oil channel B may be disposed in an inner channel formed by the inner face of the fixed wrap323and the outer face of the orbiting wrap323.

Further, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be spaced from each other by a spacing larger than the thickness of the orbiting wrap333. As a result, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be kept open regardless of the position of the orbiting wrap333, thereby preventing the situation that the oil feeding to the compressing assembly300is stopped.

FIG.4shows an embodiment in which a compressor according to the present disclosure has a plurality of oil feeding channels. Hereinafter, in order to avoid overlapping descriptions, the description will focus on differences from the embodiment ofFIGS.3A and3B.

As shown inFIGS.3A and3B, when the first oil channel A and the second oil channel B share most of the oil channels, there is a concern that sufficient oil may not be supplied to the outlet A1of the first oil channel and the outlet B1of the second oil channel.

Accordingly, the compressor10according to the present disclosure may have the first oil channel A and the second oil channel B as independent oil channels. As a result, oil may be introduced and discharged into and from the first oil channel A and the second oil channel B, individually, so that sufficient oil may be continuously supplied to the compression chamber300.

The first oil channel A may include a first oil transfer channel319A defined in the main frame310to move the oil supplied from the rotatable shaft, and a first fixed oil channel329A defined in the fixed end plate321to communicate with the first oil transfer channel319A and defined at a distal end of the outlet A1of the first oil channel.

The first oil transfer channel319A may include a first main oil channel3191A passing through the main shaft receiving portion318to receive oil, a first oil passage channel3192A which extends from the first main oil channel3191A toward the outer circumferential face along the main end plate311and through which the oil passes, and a first oil discharge channel3193A connected to the distal end of the first oil passage channel3192A and extending toward the fixed frame320to discharge the oil.

The first fixed oil channel329A may include a first oil inflow channel3291A defined inside the fixed side plate to communicate with the first oil discharge channel3193A to receive the oil supplied to the first oil transfer channel, a first oil flow channel3292A constructed to communicate with the first oil inflow channel3291A and defined inside the fixed end plate to move the oil supplied from the first oil inflow channel3291A to the fixed wrap332, and a first lubrication oil channel3292A extending from the first oil flow channel to the outlet A1of the first oil channel.

The second oil channel may include a second oil transfer channel329B which is defined in the main frame310and is spaced apart from the first oil transfer channel319A, and, along which the oil supplied from the rotatable shaft moves, and a second fixed oil channel329B defined in the fixed end plate and constructed to communicate with the second oil transfer channel329B and defined at the distal end of the outlet B1of the second oil channel.

The second oil transfer channel319B may include a second main oil channel3191B passing through the main shaft receiving portion318and receiving oil, a second oil passage channel3192B which extends from the second main oil channel3191B toward the outer circumferential face along the main end plate311and through which the oil passes, and a second oil discharge channel3193B connected to the distal end of the second oil passage channel3192B and extending toward the fixed frame320to discharge the oil.

The second fixed oil channel329B may include a second oil inflow channel3291B which is defined inside the fixed side plate to communicate with the second oil discharge channel3193B, and into which oil supplied to the second oil transfer channel flows, a second oil flow channel3292B which is constructed to communicate with the second oil inflow channel3291B and defined inside the fixed end plate and moves the oil supplied to the second oil inflow channel3291B to the fixed wrap332, and a second lubrication oil channel3292B extending from the second oil flow channel to the outlet B1of the second oil channel.

The first oil channel A and the second oil channel B may have similar shapes. However, the outlet A1of the first oil channel may be closer to the discharge hole326than the outlet B1of the second oil channel may, and may be closer to the inner face of the orbiting wrap333than the outlet B1of the second oil channel may.

Accordingly, the outlet A1of the first oil channel rather than the outlet B1of the second oil channel smoothly supplies oil to the lower pressure region. Both of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be prevented from being closed by the orbiting wrap333at the same time.

Further, the first oil channel A may be disposed in an outer channel formed by the outer face of the fixed wrap323and the inner face of the orbiting wrap333, while the second oil channel B may be disposed in an inner channel formed by the inner face of the fixed wrap323and the outer face of the orbiting wrap323.

Further, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be spaced from each other by a spacing larger than the thickness of the orbiting wrap333. As a result, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be kept open regardless of the position of the orbiting wrap333, thereby preventing the situation that the oil feeding to the compressing assembly300is stopped.

FIGS.5A and5Bshow a structure to which the oil feeding channel ofFIG.4is applied.

Referring toFIG.5A, the compressor10according to the present disclosure includes a first oil channel A defined in at least one of the orbiting scroll320or the main frame310, and in the fixed scroll320to feed the oil supplied from the rotatable shaft to a region between the orbiting scroll and the fixed scroll, and a second oil channel B defined in at least one of the orbiting scroll330or the main frame310, and defined in the fixed scroll320and spaced from the first oil channel A to feed the oil supplied from the rotatable shaft230to a region between the orbiting scroll330and the fixed scroll310.

When the first oil channel A is constructed to communicate with the intermediate pressure region V1, and the second oil channel B is constructed to communicate with the lower pressure region V2, the oil supplied through the oil feeding hole234may be supplied to the intermediate pressure region V1through the first oil channel A, and may be supplied to the lower pressure region V2through the second oil channel B. In other words, the compressor10according to the present disclosure has the first oil channel A that supplies oil to the intermediate pressure region V1for a high pressure ratio operation, and the second oil channel B which supplies oil to the lower pressure region V2for a lower pressure ratio operation.

When the first oil channel A and the second oil channel B are both installed in the intermediate pressure region V1or the lower pressure region V2at the same time, the first oil channel A may be placed in the outer channel formed by the inner face of the orbiting wrap333and the outer face of the fixed wrap323, while the second oil channel B may be disposed in an inner channel formed by an outer face of the orbiting wrap333and an inner face of the fixed wrap323.

Accordingly, the first oil channel A and the second oil channel B may supply oil to different oil channels, respectively, and both thereof may be prevented from being closed by the orbiting wrap333or the fixed wrap323.

Referring toFIG.5B, the compressor10according to the present disclosure may have a region to which the oil feedings through the first oil channel A and the second oil channel B are simultaneously performed. Furthermore, in an angle range of 190° to 270° in which oil feeding through the first oil channel A is blocked, the oil feeding may be continued through the second oil channel B. Further, in an angle range of 0 to 80 degrees, and 270 degrees to 360 degrees in which oil feeding through the second oil channel B is blocked, the oil feeding may continue through the first oil channel A.

As a result, the oil feeding to the compressing assembly300may be fundamentally activated at all times.

FIG.6shows another oil feeding channel structure of the compressor according to the present disclosure.

The oil feeding channel according to the present disclosure may be defined in the orbiting scroll330. That is, the process of installing the oil feeding channel in the fixed scroll320may be omitted.

That is, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be defined in the orbiting end plate331.

Specifically, the oil feeding channel may include an orbiting oil channel339passing through the orbiting scroll330. The orbiting oil channel339may include an orbiting oil input channel3391through which the oil delivered from the first oil feeding hole234aor the first oil feeding groove2341ais injected into the orbiting scroll, a connection oil channel3392extending from the orbiting oil input channel toward the outer circumferential face of the orbiting scroll, a branched oil channel3393branching from the connection oil channel3392toward the fixed scroll320and defining the outlet B1of the second oil channel, and a communication oil channel3394that is spaced from the connection oil channel3392toward the outer circumferential face of the orbiting end plate331by a spacing larger than a spacing by which the second oil channel is spaced from the connection oil channel3392, thereby to form the outlet A1of the first oil channel.

That is, the first oil channel A and the second oil channel B may share the orbiting oil input channel3391and the connection oil channel3392. As a result, the oil delivered through the rotatable shaft230may be directly supplied to the orbiting wrap333and the fixed wrap323through the orbiting scroll330.

In one example, since the pressure difference between the intermediate pressure region V1and the high pressure region S1is large, oil may be excessively supplied from the rotatable shaft230. Therefore, there may be a problem that a sufficient amount of the refrigerant may not be compressed or the compressing assembly300is excessively cooled. To prevent this problem, the scroll type compressor300may include the pressure reducing means360which is inserted into the oil transfer channel330to adjust the supply amount of oil. The pressure reducing means360reduced the cross-sectional area of the oil transfer channel330to generate the oil channel resistance to prevent excessive oil from being supplied.

As shown, the orbiting wrap333may be disposed between the outlet A1of the first oil channel and the outlet B1of the second oil channel. Between adjacent orbiting wraps333, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be disposed.

Further, the outlet A1of the first oil channel may be closer to the outer face of the orbiting wrap333, while the outlet B1of the second oil channel may be closer to the inner face of the orbiting wrap. That is, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be closer to a first orbiting wrap333disposed between the outlet A1of the first oil channel and the outlet B1of the second oil channel than to a second orbiting wrap333adjacent to the first orbiting wrap333.

Accordingly, the outlet A1of the first oil channel and the outlet B1of the second oil channel may supply oil to the inner and outer faces of the orbiting wrap333, respectively.

That is, the first oil channel A may be disposed in an outer channel formed by the outer face of the fixed wrap323and the inner face of the orbiting wrap333, and the second oil channel B may be disposed in an inner channel formed by the inner face of the fixed wrap323and the outer face of the orbiting wrap323.

Further, the outlet A1of the first oil channel and the outlet B1of the second oil channel may be spaced apart from each other by a spacing larger than the thickness of the fixed wrap323.

As a result, when the outlet A1of the first oil channel is closed by the fixed wrap323, the outlet B1of the second oil channel may be spaced apart from the fixed wrap323and may be opened. When the outlet B1of the second oil channel is closed by the fixed wrap323, the outlet A1of the first oil channel may be spaced apart from the fixed wrap323and may be opened.

Therefore, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be kept open regardless of the position of the fixed wrap323, and oil feeding to the compressing assembly300is prevented from being stopped.

In one example, unlike shown, both of the branched oil channel3393and the communication oil channel3394may be disposed between a specific orbiting wrap333and an orbiting wrap333adjacent thereto. That is, both of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be disposed between the outer orbiting wrap333and the inner orbiting wrap333. An orbiting wrap333may not be formed between the outlet A1of the first oil channel and the outlet B1of the second oil channel, and a fixed wrap323may be selectively disposed therebetween.

Even in this case, the outlet A1of the first oil channel may be disposed adjacent to the inner face of the orbiting wrap333, and the outlet B1of the second oil channel may be defined adjacent to the outer face of the orbiting wrap333. Therefore, the first oil channel A may supply oil to the outer channel, and the second oil channel B may supply oil to the inner channel. As the orbiting scroll330is orbiting, one of the inner channel and the outer channel invades the fixed wrap323, but the other thereof may be spaced from the fixed wrap323.

As a result, oil feeding into a region between the orbiting scroll330and the fixed scroll320may be continued without interruption.

In another example, unlike shown inFIG.6, even when the oil feeding channel is installed in the orbiting end plate331, the first oil channel A and the second oil channel B may be arranged independently of each other.

That is, the first oil channel A may include a first orbiting oil input channel3391which passes through the orbiting end plate and through which oil is input to the orbiting scroll, a first connection oil channel3392extending from the first orbiting oil input channel toward the outer circumferential face of the orbiting scroll, and a branched oil channel3393passing through the orbiting end plate and communicating the connection oil channel and the outlet A1of the first oil channel.

The second oil channel may include a second orbiting oil input channel3391B which is spaced apart from the first orbiting oil input channel and passes through the orbiting end plate, and through which oil is introduced into the orbiting scroll, a second connection oil channel3392B extending from the second orbiting oil input channel toward the outer circumferential face of the orbiting scroll, and a communication oil channel3394passing through the orbiting end plate and communicating the second connection oil channel3392B with the outlet B1of the second oil channel.

That is, unlike shown, the first oil channel A and the second oil channel B may be independently defined. The first oil channel A may independently supply oil to the inner channel, and the second oil channel B may independently feed the oil to the outer channel.

As a result, even in a state of the lower pressure, the oil may be smoothly supplied to the outer channel through the second oil channel B. At least one of the first oil channel A and the second oil channel B may be maintained in an open state. Further, sufficient oil may be supplied through the first oil channel A and the second oil channel B while oil is not accumulated therein.

FIGS.7A and7Bshow another embodiment of the oil feeding structure of the compressor according to the present disclosure.

The oil feeding channel according to the present disclosure may include a first oil channel A passing through one of the orbiting scroll330and the fixed scroll320and a second oil channel passing through the other one of the orbiting scroll330and the fixed scroll320.

FIGS.7A and7Bshow that the first oil channel A passes through the main frame310and the fixed scroll320, and the second oil channel B passes through the orbiting scroll330. This is merely one example. In another example, the second oil channel B passes through the main frame310and the fixed scroll320, and the first oil channel A passes through the orbiting scroll330.

The first oil channel A may include an oil transfer channel319which is defined in the main frame, and through along the oil supplied from the rotatable shaft flows, a fixed oil channel329defined in the fixed scroll and constructed to communicate with the oil transfer channel and including an outlet of the first oil channel that supplies the oil into a region between the orbiting wrap and the fixed wrap.

The second oil channel B may include an orbiting oil input channel3191which passes through the orbiting end plate and through which oil is injected into the orbiting scroll, a connection oil channel3192that extends from the orbiting oil input channel toward the outer circumferential face of the orbiting scroll, and a communication oil channel3394passing through the orbiting end plate and communicating the connection oil channel with the outlet of the second oil channel.

Even in this case, at least one of the outlet A1(“first outlet”) of the first oil channel and the outlet B1(“second outlet”) of the second oil channel may be kept open.

Further, since the second oil channel B is defined in the orbiting scroll330and does not pass through the fixed scroll320, the oil channel resistance therein is smaller than that in the first oil channel A. Therefore, oil may be effectively supplied to the lower pressure region V2.

Further, at least one of the outlet A1of the first oil channel and the outlet B1of the second oil channel may be kept open regardless of the position of the fixed wrap323or orbiting wrap333, and the oil feeding to the compressing assembly300may be prevented from being stopped.

FIGS.8A to8Cshow how the compressor operates according to the present disclosure.

FIG.8Ashows the orbiting scroll,FIG.8Bshows the fixed scroll, andFIG.8Cshows the process of compressing the refrigerant using the orbiting scroll and the fixed scroll.

The orbiting scroll330may include the orbiting wrap333on one face of the orbiting end plate331, and the fixed scroll320may include the fixed wrap323on one face of the fixed end plate321.

Further, the orbiting scroll330may be embodied as a sealed rigid body to prevent the refrigerant from being discharged out thereof.

In one example, the fixed wrap323and the orbiting wrap333may be formed in an involute shape and may be engaged with each other at two or more points to form a compression chamber in which the refrigerant is compressed.

The involute refers to a particular type of curve that is dependent on another shape or curve. An involute of a curve is the locus of a point on a piece of taut string as the string is either unwrapped from or wrapped around the curve.

However, according to the present disclosure, the fixed wrap323and the orbiting wrap333are formed by combining 20 or more arcs with each other. The radiuses of curvature of the arcs vary.

That is, the compressor according to the present disclosure is constructed so that the rotatable shaft230passes through the fixed scroll320and the orbiting scroll330, so that the radius of curvature of the fixed wrap323and the orbiting wrap333and the compression space defined therebetween are reduced.

Therefore, to compensate for this reduction, in the compressor according to the present disclosure, the space in which the refrigerant is discharged to improve the compression ratio. To this end, the radius of curvature of a portion just before a portion of the fixed wrap323and the orbiting wrap333at which the refrigerant is discharged may be smaller than that of the shaft receiving portion receiving the rotatable shaft.

That is, the fixed wrap323and the orbiting wrap333may be curved at the smallest radius of curvature in the vicinity of the discharge hole326, and the radius of curvature thereof may increase toward the inlet325. The fixed wrap323and the orbiting wrap333have the varying radius of curvature between the discharge hole326and inlet325.

Referring toFIG.8C, refrigerant I flows into the inlet325of the fixed scroll320, and refrigerant II flowing before the refrigerant I is located near the discharge hole326of the fixed scroll320.

In this connection, the refrigerant I exists in a region in which the outer surfaces of the fixed wrap323and the orbiting wrap333are engaged with each other, and the refrigerant II is present and sealed in another region where the fixed wrap323and the orbiting wrap333are engaged with each other at two points thereof.

Then, when the orbiting scroll330starts orbiting, the region where the fixed wrap323and the orbiting wrap333are engaged with each other at the two points moves along the extension direction of the fixed wrap323and the orbiting wrap333according to the position change of the orbiting wrap333, such that the volume of the refrigerant begins to be reduced. The refrigerant I is compressed. The refrigerant II is further reduced in volume and compressed and begins to be guided to the discharge hole326.

The refrigerant II is discharged from the discharge hole326, and the refrigerant I moves as the region where the fixed wrap323and the orbiting wrap333are engaged with each other at the two-points moves clockwise, and the volume thereof decreases and the refrigerant begins to be further compressed.

The region in which the fixed wrap323and the orbiting wrap333are engaged with each other at the two points moves clockwise again, and is closer to the inside of the fixed scroll, the volume thereof is further reduced and the refrigerant is compressed, and the refrigerant II is almost completely discharged.

In this way, as the orbiting scroll330orbits, the refrigerant may be compressed linearly or continuously while moving inside the fixed scroll.

The drawing shows that the refrigerant discontinuously flows into the inlet325, but this is for illustration only. Alternatively, the refrigerant may be supplied continuously, and the refrigerant may be accommodated and compressed in the region defined by the two points at which the fixed wrap323and the orbiting wrap333are engaged with each other.

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