Compressor having integrated flow path structure

A compressor is provided having an integrated flow path structure in which an oil flow path and an intermediate pressure flow path are integrated into one in a compression unit, thereby simplifying a flow path of the compression unit. The compressor may include at least one integrated flow path in which the oil flow path and the refrigerant gas flow are integrated into one in a fixed scroll. The at least one integrated flow path may connect an intermediate pressure chamber and a compression chamber in a compressors unit. The at least one integrated flow path may provide a compressed refrigerant in the compression chamber to the intermediate pressure chamber and provide oil in the intermediate pressure chamber to the compression chamber, simplifying the flow path of the compression unit.

CROSS-REFERENCE TO RELATED APPLICATION(S)

This application claims priority to and the benefit of Korean Patent Application No. 10-2017-0078749, filed in Korea on Jun. 21, 2017, the disclosure of which is incorporated herein by reference in its entirety.

BACKGROUND

A compressor is disclosed herein, the compressor having an integrated flow path structure in which an oil flow path and an intermediate pressure flow path are integrated into one in a compression unit, thereby simplifying the flow path of the compression unit.

Generally, a compressor is applied to a vapor compression-type refrigeration cycle device, such as a refrigerator or an air conditioner, for example. Compressors can be classified into reciprocating, rotary, vane, and scroll compressors depending on a method of compressing a fluid, such as a refrigerant. Among these, the scroll compressor includes a fixed scroll fixed to an inner space of a seated container and a compression unit including an orbiting scroll that performs an orbiting motion while being engaged with the fixed scroll. In addition, the scroll compressor includes a drive motor that generates a drive force transmitted to the orbiting scroll.

A pair of compression chambers are formed between a fixed wrap of the fixed scroll and an orbiting wraps of the orbiting scroll. The scroll compressor compresses the fluid introduced into the compression chamber through the orbiting motion of the orbiting scroll. An Oldham's ring may be provided between the fixed scroll and the orbiting scroll. The Oldham's ring makes it possible to turn the orbiting scroll on the fixed scroll while preventing the orbiting scroll from rotating.

The scroll compressor can obtain a relatively high compression ratio in comparison with other types of compressors. The scroll compressor is advantageous in that section, compression, and discharge operations of a refrigerant are smoothly connected to each other to obtain a stable torque. Therefore, the scroll compressor is widely used for compressing the refrigerant in an air conditioner, for example.

The scroll compressor may be classified into an upper compression-type scroll compressor or a lower compression-type scroll compressor depending on positions of the compression unit and the drive motor. In the upper compression-type scroll compressor, the compression unit is positioned above the drive motor. In the lower compression-type scroll compressor, the compression unit is positioned below the drive motor.

In a case of the conventional scroll compressor, the fixed scroll may include an intermediate pressure flow path used as a refrigerant gas flow path and a first differential pressure oil supply flow path used as an oil flow path, and the orbiting scroll may include a second differential pressure oil supply flow path used as an oil flow path. However, in the conventional fixed scroll, the refrigerant gas flow path and the intermediate pressure flow path are formed separately, and thus, a processing time and manufacturing costs are increased due to the formation of a plurality of flow paths. Further, when the scroll compressor is operated, a plurality of flow paths is formed on the fixed scroll, and thus, an impact noise, for example, an impact noise of the Oldham's ring, due to friction is increased. Further, when the first differential pressure oil supply flow path is disposed adjacent to the second differential pressure oil supply flow path, oil discharged from the first differential pressure oil supply flow path flows directly to the second differential pressure oil supply flow path, so that the oil is not uniformly diffused into an intermediate pressure chamber.

DETAILED DESCRIPTION

Hereinafter, embodiments will be described with reference to the accompanying drawings. In the drawings, the same or like reference numerals are used to denote the same or like elements, and repetitive disclosure has been omitted.

Hereinafter, a compressor according to embodiments will be described with reference toFIGS. 1 to 11.

A compressor100according to an embodiment described with reference toFIGS. 1 to 8may have an upper compression structure in which a compression unit190including an orbiting scroll140and a fixed scroll150is positioned above a drive motor120. In addition, the compressor100has a structure (hereinafter, referred to as an “axis non-through structure”) in which a rotary shaft126does not pass through the compression unit190. On the other hand, a compressor200according to another embodiment described with reference toFIGS. 7 to 11has a lower compression structure in which a compression unit290including an orbiting scroll240and a fixed scroll250is positioned below a drive motor220. In addition, the compressor200has an axis-through structure in which a rotary shaft226passes through the compression unit290.

However, emblements are not limited thereto, and although not shown in the drawings, an integrated flow path structure included in a compressor according to an embodiment, which will be described hereinafter may be used for the upper compression structure including the axis-through structure. Similarly, the integrated flow path structure may be used for the lower compression structure including the axis non-through structure. In addition, the integrated flow path structure may be applied to a compressor whose compression unit is disposed in a transverse direction of a drive motor.

FIG. 1is a cross-sectional view of a compressor according to an embodiment. Referring toFIG. 1, the compressor100according to an embodiment may include a casing110having an inner space, the drive motor120disposed at a lower or central portion of the inner space, the compression unit190disposed at an upper portion of the drive motor120, and the rotary shaft120that transmits the drive force of the drive motor120to the compression unit190.

The casing110may include a cylindrical shell111, an upper shell112provided on or at an upper portion of the cylindrical shell111, and a lower shell114provided below the cylindrical shell111. For example, the casing110may have a cylindrical shape. However, embodiments are not limited thereto, and the casing110may be formed in various shapes. The upper and lower shells112and114may be, for example, welded to the cylindrical shell111to form the inner space.

A discharge pipe116may be formed on or at an upper portion of the upper shell112. The discharge pipe116may be a passage through which a compressed refrigerant may be discharged to the outside. An oil separator (not shown) that separates oil mixed with the discharged refrigerant therefrom may be connected to one side of the discharge pipe116.

A suction pipe118may be disposed or provided on or at a side surface of the cylindrical shell111. The suction pipe118may be a passage through which a refrigerant to be compressed may be introduced. InFIG. 1, the suction pipe118is located at a boundary between the cylindrical shell111and the upper shell112; however, embodiments are not limited thereto, and a position thereof may be arbitrarily set. In addition, the lower shell114may function as an oil storage space to store oil so that the compressor may be smoothly operated.

The drive motor120which operates as a drive unit and the compression unit190which compresses the refrigerant may be provided inside of the casing110. The drive motor120may include a stator122, which may be fixed to an inner surface of the casing110, and a rotor124, which may be positioned inside of the stator122and rotated by interaction with the stator122. The rotary shaft126may be fixed to a center of the rotor124so that the rotor124and the rotary shaft126may rotate together.

An oil flow path126amay be formed at an inside of the rotary shaft126so as to extend along a longitudinal direction of the rotary shaft128. An oil pump126bto supply the oil stored in the lower shell114upward may be provided at a lower end of the rotary shaft126. Although not shown in the drawings, the oil pump126bmay be provided with a helical groove formed in the oil flow path, or a trochoid pump (not shown) to forcibly pump the oil stored in the oil storage space upward may be connected to the oil pump126b.

The compression unit190may include a main frame130, the fixed scroll150, and the orbiting scroll140. The main frame130and a sub frame160that support the rotary shaft126of the drive motor120may be fixedly provided on or at upper and lower sides of the casing110, respectively. The main frame130may support one or a first side or end of the rotary shaft126in a radial direction, and the sub frame160may support the other or a second side or end of the rotary shaft126in the radial direction.

The fixed scroll150may be fixedly provided on or at an upper surface of the main frame130. The orbiting scroll140which performs an orbiting motion while being engaged with the fixed scroll150may be provided between the main frame130and the fixed scroll150. The orbiting scroll140may include an orbiting wrap141that engage with a fixed wrap151of the fixed scroll150to form a plurality of compression chambers P.

Detailed descriptions of the fixed scroll150and the orbiting scroll140are provided hereinafter with reference toFIGS. 2-3. An Oldham's ring131that turns the orbiting scroll140while preventing the orbiting scroll140from rotating may be provided between the orbiting scroll140and the main frame130.

Hereinafter, an integrated flow path structure included in the compression unit190will be described with reference toFIGS. 2-3.

FIG. 2is a partial cross-sectional view of an integrated flow pain structure of the compression unit of the compressor ofFIG. 1, that is,FIG. 2is a partial enlarged cross-sectional view showing an area S ofFIG. 1.FIG. 3is a partial enlarged cross-sectional view showing an area SS ofFIG. 3.

Referring toFIGS. 3-4, the compression unit190of the compressor100according to an embodiment may include the main frame130, the orbiting scroll140, and the fixed scroll150. The main frame130may be provided in or at an upper portion of the drive motor120and form a lower portion of the compression unit190.

The main frame130may include with a circular frame end plate132(hereinafter, referred to as a “first end plate”), a frame shaft-receiving portion132a(hereinafter, referred to as a “first shaft-receiving portion”) provided at a center of the first end plate132and through which the rotary shaft126may pass, and a frame side wall135(hereinafter, referred to as a “first side wall”) that protrudes upward from an outer circumferential portion of the first end plate132. An outer peripheral portion of the first side wall135may be brought into contact with an inner circumferential surface of the casing110and an upper end of the first side wall135may be brought into contact with a lower end portion of a fixed scroll side wall155.

The first shaft-receiving portion132amay protrude from a lower surface of the first end plate132toward the drive motor120side. In addition, a first bearing portion may be formed in the first shaft-receiving portion132asuch that a main bearing portion126cof the rotary shaft126may pass through the first bearing portion and be supported.

An intermediate pressure chamber S2which forms a space together with the fixed scroll150and the orbiting scroll140to support the orbiting scroll140by a pressure of the space may be formed on an inner surface of the main frame130. That is, the intermediate pressure chamber S2may be formed by the main frame130, the fixed scroll150, and the orbiting scroll140.

More specifically, the intermediate pressure chamber S2may be defined as a space among the orbiting scroll140, the fixed scroll150, and the main frame130. The intermediate pressure chamber S2may be formed in a donut shape along an inner circumferential surface of the main frame130.

An oil introduction chamber S3may be defined as a space among the rotary shaft126, the main frame130, and the orbiting scroll140. The oil introduction chamber S3may be a space through which the oil suctioned along the oil supply flow path126ainside of the rotary shaft126may be discharged.

A high pressure region may be formed in the oil supply flow path126aand the oil introduction chamber S3, and an intermediate pressure region having a lower pressure than a pressure of the oil introduction chamber S3may be formed in the intermediate pressure chamber S2. A portion of the oil discharged into the oil introduction chamber S3may move to the intermediate pressure chamber S2along a differential pressure oil supply flow path145of the orbiting scroll140. In addition, another portion of the oil introduced into the oil introduction chamber S3may be supplied to outer peripheral surfaces of the main bearing portion126cand an eccentric portion126d, or supplied between the orbiting scroll140and the fixed scroll150.

A back pressure seal137may be provided between the oil introduction chamber S3of the high pressure region and the intermediate pressure chamber S2of the intermediate pressure region. The back pressure seal137may be located between the main frame130and the orbiting scroll140, and formed by a sealing member or seal, for example, an elastic member. The main frame130may be coupled with the fixed scroll150to form a space in which the orbiting scroll140may be installed or provided.

The fixed scroll150may include a circular fixed end plate154(hereinafter, referred to as a “second end plate”), the fixed scroll side wall155(hereinafter, referred to as a “second side wall”) that protrudes downward from an outer peripheral portion of the second end plate154, and the fixed wrap151that protrudes from a lower surface of the second end plate154and engaged with the orbiting wrap141of the orbiting scroll140to form a compression chamber S1. An outer peripheral portion of the second side wall155may be brought into contact with an inner circumferential surface of the casing110or the upper shell112, and a lower end portion of the second side wall155may be brought into contact with an upper surface of the first side wall135.

A discharge port152may be formed at an upper center of the second end plate154so that a discharge side of the compression chamber S1and a discharge space of the casing110may be connected to each other. In addition, an integrated flow path153may be formed in the second end plate154.

The integrated flow path153may connect the intermediate pressure chamber S2and the compression chamber S1. That is, one or a first end of the integrated flow path153may be connected to the intermediate pressure chamber S2and the other or a second end thereof may be connected to the compression chamber S1. The compression chamber S1may be defined as a space between the orbiting wrap141of the orbiting scroll140and the fixed wrap151of the fixed scroll150and may be a space for compressing and then discharging the refrigerant introduced from the outside.

The integrated flow path153may connect the intermediate pressure chamber S2and the compression chamber S1to form the intermediate pressure region in the intermediate pressure chamber S2and to supply oil fed to the intermediate pressure chamber S2to the compression chamber S1. The oil discharged into the intermediate pressure chamber S2may be supplied to the compression chamber S1via the integrated flow path153. More specifically, the oil contained in the oil storage space may be supplied to the compression chamber S1via a differential pressure oil supply flow path145to be described hereinafter and the integrated flew path153.

Accordingly, the oil may be smoothly supplied to the compression chamber S1, and thus, wear due to friction between the orbiting scroll140and the fixed scroll150may be reduced, thereby improving compression efficiency. In addition, the oil supplied to the compression chamber S1may form an oil film between the fixed scroll150and the orbiting scroll140to maintain an airtight state of the compression chamber S1.

Further, the oil supplied to the compression chamber S1may absorb frictional heat generated during the occurrence of friction between the fixed scroll150and the orbiting scroll140to lower a temperature of the compression unit190. In addition, the integrated flow path153may move a refrigerant gas compressed at a high pressure in the compression chamber S1to the intermediate pressure chamber S2, and form an intermediate pressure corresponding to an average of a suction pressure and a discharge pressure in the intermediate pressure chamber S2.

The pressure formed in the intermediate pressure chamber S2may act as a back pressure that presses a surface of the orbiting scroll140. The back pressure that presses the surface of the orbiting scroll140may be in equilibrium with an expansion pressure formed in the compression chamber S1. The back pressure may prevent the orbiting scroll140from tilting during the orbiting operation of the orbiting scroll140and generating noise or prevent the compression efficiency from being reduced.

The integrated flow path153may pass through the second side wall155and the second end plate154. More specifically, the integrated flow path153may include a third hold153a, a fourth hole153b, and a horizontal flow path153c.

The third hole153amay be formed on a surface of the second side wall155and connected to the intermediate pressure chamber S2. The third hole153amay be formed of a plurality of holes; however, embodiments are not limited thereto.

The fourth hole153bmay be formed on a surface of the second end plate154and connected to the compression chamber S1. Similarly, the fourth hole153bmay be formed of a plurality of holes; however, embodiments are not limited thereto.

The horizontal flow path153cmay be formed inside of the second end plate154so as to connect the third hole153aand the fourth hole153band may extend parallel to a surface of the second end plate154.

The integrated flow path153may pass through only the second side wall155. In this case, a length of the integrated flow path153may be decreased in comparison with a case in which the integrated flow path153passes through both the second side wall155and the second end plate154. The integrated flow path153may be formed in a “¬” or “⊏” shape in the second end plate154of the fixed scroll150; however, embodiments are not limited thereto.

Additionally, although not shown in the drawings, a plurality of integrated flow paths153may be formed in the fixed scroll250. The plurality of integrated flow paths153may be provided in the fixed scroll250at regular intervals. A number of the integrated flow paths153may be the same as a number of the differential pressure oil supply flow path145, which is described hereinafter. However, embodiments are not limited thereto.

The orbiting scroll140coupled to the rotary shaft126to perform the orbiting motion may be installed or provided between the main frame130and the fixed scroll150. The orbiting scroll140may include a circular orbiting end plate142(hereinafter, referred to as a “third end plate portion”), the orbiting wrap141that protrudes from an upper surface of the third end plate142and is engaged with the fixed wrap151, and a rotary shaft coupler144provided on a lower surface of the third end plate142and rotatably coupled to the eccentric portion120dof the rotary shaft126. In a case of the orbiting scroll140, the lower surface of the third end plate142may be in close contact with an upper surface of the first end plate132and supported by the main frame130.

The orbiting wrap141may form the compression chamber S1together with the fixed wrap151during a compression process. The fixed wrap151and the orbiting wrap141may be formed in an involute shape. The involute shape means a curved line corresponding to a locus drawn by an end portion of a thread when the thread wound around a base circle having an arbitrary radius is released. However, shapes of the fixed wrap151and the orbiting wrap141are not limited thereto.

A second bearing portion may be provided in the rotary shaft coupler144so that the eccentric portion126dof the rotary shaft126may be inserted into the second bearing portion and supported. In addition, the orbiting scroll140may include the differential pressure oil supply flow path145formed in the third end plate142. The differential pressure oil supply flow path145may connect the oil introduction chamber S3and the intermediate pressure chamber S2.

More specifically, referring toFIG. 3, the differential pressure oil supply flow path145may include a first hole145a, a second hole145b, and a horizontal flow path145c. The first hole145amay be formed on the lower surface of the third end plate portion142and disposed close to a center of the orbiting scroll140to be connected to the oil introduction chamber S3. The first hole145amay be formed of a plurality of holes; however embodiments are not limited thereto.

The second hole145bmay be formed on the lower surface of the third end plate142and disposed close to an outer circumferential surface of the orbiting scroll140to be connected to the intermediate pressure chamber S2. Similarly, the second hole145bmay be formed of a plurality of holes; however, embodiments are not limited thereto.

The horizontal flow path145cmay be formed inside of the third end plate142so as to connect the first hole145aand the second hole145band extend parallel to an upper surface of the third end plate142. Additionally, an opening145dfor opening a portion of a side surface of the third end plate142may be formed at one side of the first horizontal flow path145c. An inner surface of the opening145dmay include a screw groove which may be fastened with a coupling bolt147. However, embodiments are not limited thereto, and the inner surface of the opening145dmay be formed in various shapes which may be fastened to the coupling bolt147, such as a stepped shape or a curved shape, for example.

The opening145dmay be used to insert a decompression pin149into the first horizontal flow path145c. The inserted decompression pin149may be disposed or provided inside of the differential pressure oil supply flow path145. A diameter of the decompression pin149may be smaller than a diameter of the first horizontal flow path145c. The decompression pin149may adjust a pressure and a supply amount of oil in the differential pressure oil supply flow path145by forming a narrow flow path through which oil may move in the differential pressure oil supply flow path145.

Although not shown in the drawings, other shaped-decompression members for forming a narrow flow path in the differential pressure oil supply flow path145may be used instead of the decompression pin149. For example, a ball-shaped or polyhedral decompression filler may be used; however, embodiments are not limited thereto.

However, for convenience of description, in this embodiment, an example in which the decompression pin149is provided in the differential pressure oil supply flow path145will be described.

After the decompression pin149is inserted into the first horizontal flow path145c, the coupling boil147may be fastened to the opening145d. The coupling bolt147may be formed in a shape which may be coupled to the opening145d.

For example, the coupling bolt147may be formed in a threaded, stepped, or curved shape corresponding to an inner shape of the opening145d. However, embodiments are not limited thereto.

The coupling bolt147may be coupled to the opening145dso that the “” shaped differential pressure oil supply flow path145connecting the oil introduction chamber S3and the intermediate pressure chamber S2may be termed in the orbiting scroll140. However, embodiments are not limited thereto, and the shape of the differential pressure oil supply flow path145may be diversely formed, such as in an S-shape or a “” shape, for example.

The oil which has passed through the differential pressure oil supply flow path145to be discharged into the intermediate pressure chamber S2may be supplied to a thrust surface between the orbiting scroll140and the fixed scroll150. The oil discharged into the intermediate pressure chamber S2may be supplied between the respective components of the compression unit190to reduce the friction of the compression unit190.

Additionally, although not shown in the drawings, a plurality of differential pressure oil supply flow paths145may be formed in the scroll140. In addition, the plurality of differential pressure oil supply flow paths145may be disposed or provided in the orbiting scroll140at regular intervals. A number of the differential pressure oil supply flow paths145may be formed to be the same as the number of the integrated flow paths153. In addition, the plurality of differential pressure oil supply flow paths145may be formed so as to correspond one-to-one to the plurality of integrated flow paths153. However, embodiments are not limited thereto.

The oil guided upward via the oil supply flow path126amay be discharged through an oil hole127and supplied to outer peripheral surfaces of the main bearing portion126cand the eccentric portion126d. More specifically, the oil hole127may pass from the oil supply flow path126ato an outer peripheral surface of the main bearing portion126c.

In addition, the oil hole127may pass through, for example, an upper portion of the outer peripheral surface of the main bearing portion128c. However, embodiments are not limited thereto, and the oil hole127may pass through a lower portion of the outer peripheral surface of the main bearing portion126c.

The oil hole127may include a plurality of holes, unlike that shown in the drawings. When the oil hole127includes a plurality of holes, each of the holes may be formed only in the upper or lower portion of the outer peripheral surface of the main bearing portion126c, or formed in the upper and lower portions of the outer peripheral surface of the main bearing portion126c, respectively. However, for convenience of description, in this embodiment, the oil hole127includes one hole.

Next, a first portion of the high pressure oil discharged through the oil hole127may move to the oil introduction chamber S3formed between the main frame130and the orbiting scroll140. A second portion of the oil supplied to the oil introduction chamber S3may be supplied to the outer peripheral surfaces of the main bearing portion126cand the eccentric portion126d.

The first portion of the oil supplied to the oil introduction chamber S3may be supplied to the intermediate pressure chamber S2through the differential pressure oil supply flow path146of the orbiting scroll240described above. The oil guided to the intermediate pressure chamber S2through the differential pressure oil supply flow path145may be supplied to the thrust surface between the orbiting scroll140and the fixed scroll150. As a result, wear of the thrust surface of the fixed scroll150may be reduced.

In addition, the oil guided to the intermediate pressure chamber S2may be guided to the integrated flow path153provided in the fixed scroll150. The integrated flow path153may connect the intermediate pressure chamber S2and the compression chamber S1to supply oil fed to the intermediate pressure chamber S2to the compression chamber S1and form an intermediate pressure corresponding to an average of a suction pressure and a discharge pressure in the intermediate pressure chamber S2.

That is, the integrated flow path153may be used as an oil flow path for providing oil and an intermediate pressure flow path for forming an intermediate pressure. Thus, according to embodiments, the oil flow path and the refrigerant gas flow path of the fixed scroll150may be integrated into one, thereby simplifying the flow path of the compression unit190.

Accordingly, the number of flow paths required for the fixed scroll150used in the compressor100according to embodiments may be reduced in comparison to prior art. Thus, a manufacturing process for producing the fixed scroll150may be simplified, and a manufacturing time of the fixed scroll150may be reduced. Further, as the manufacturing process and time are reduced, manufacturing costs of the compressor100may be reduced.

Further, vibration and noise due to friction generated when a plurality of flow paths are formed in the fixed scroll150may be reduced by reducing the number of flow paths generated in the fixed scroll150. Furthermore, by reducing vibration and noise generated during operation of the compressor100, operational stability of the compressor100may be increased, and a user's satisfaction may also be enhanced.

Hereinafter, an integrated flow path structure of the compression unit of the compressor ofFIG. 1according to another embodiment will be described with reference toFIGS. 5 to 7.

FIG. 4is a partial cross-sectional view of an integrated flow path structure of the compression unit of the compressor ofFIG. 1according to another embodiment.FIGS. 5 and 6are cross-sectional views, taken along line V-V ofFIG. 4.

FIGS. 5 and 6are plan views for explaining a positional relationship between the differential pressure oil supply flow path145and the integrated flow path153. For convenience of description, repeated description of the same components as those of the previous embodiment will be omitted and description will be made focusing on differences therebetween.

Referring toFIG. 4, in the compressor100, the differential pressure oil supply flow path145formed in the orbiting scroll140may be disposed or provided on of at one or a first side of the orbiting scroll140with respect to the rotary shaft126, and disposed or provided on or at the other or a second side thereof with respect to the rotary shaft126of the integrated flow path153formed in the fixed scroll150. For example, the differential pressure oil supply flow path145formed in the orbiting scroll140may be positioned on a first side (left side in the drawings) with respect to the rotary shaft126, and the integrated flow path153formed in the fixed scroll150may be positioned on a second side (right side in the drawings) with respect to the rotary shaft126. That is, the differential pressure oil supply flow path146and the integrated flow path153may be positioned opposite to each other with respect to a center C of the rotary shaft126.

A first direction of the differential pressure oil supply flow path145extending outward from the inside of the orbiting scroll140may be formed to be different from a second direction of the integrated flow path153extending outward from the inside of the fixed scroll150. More specifically, referring toFIG. 5, an angle θ1between the first direction A of the differential pressure oil supply flow path145extending outward from the inside of the orbiting scroll140and the second direction B1of the integrated flow path153extending outward from the inside of the fixed scroll150may be an obtuse angle. That is, the angle θ1between the first direction A and the second direction B1may be a value in a range of about 90 to 180 degrees.

In addition, referring toFIG. 6, an angle θ2between the first direction A of the differential pressure oil supply flow path145extending outward from the inside of the orbiting scroll140and a third direction B2of the integrated flow path153extending outward from the inside of the fixed scroll150may be an acute angle. That is, the angle θ2between the first direction A and the third direction B2may be a value in a range of about 0 to 90 degrees.

In this case, a distance between the second hole145bthrough which the oil is discharged from the differential pressure oil supply flow path145and the third hole153athrough which the oil is introduced into the integrated flow path153may be formed to be larger than that in the embodiment described with reference toFIGS. 1 to 3. Accordingly, the oil discharged from the oil introduction chamber S3to the intermediate pressure chamber S2through the differential pressure oil supply flow path145may move along an inner peripheral surface of the intermediate pressure chamber S2. The oil discharged into the intermediate pressure chamber S2may be uniformly diffused on the thrust surface between the orbiting scroll140and the fixed scroll150and uniformly diffused between the orbiting scroll140and the main frame130, while moving toward the integrated flow path153along the inner peripheral surface of the intermediate pressure chamber S2.

Next, the oil guided to the integrated flow path153may be supplied to the compression chamber S1. The oil may be uniformly supplied to the intermediate pressure chamber S2and the compression chamber S1so that wear due to friction between the orbiting scroll140and the fixed scroll150and between the orbiting scroll140and the main frame130may be reduced. As a result, the compression efficiency of the compressor100may be improved.

In addition, the oil supplied to the intermediate pressure chamber S2and the compression chamber S1may form an oil film between the fixed scroll150and the orbiting scroll140to maintain an airtight state of the compression chamber S1. Further, the oil supplied to the intermediate pressure chamber S2and the compression chamber S1may absorb frictional heat generated during the occurrence of friction between the fixed scroll150and the orbiting scroll140to dissipate heat.

Additionally, as described above, as the number of flow paths required to be generated in the fixed scroll150is reduced, the manufacturing process and time may be reduced and the manufacturing costs may be reduced. In addition, vibration and noise due to friction generated when a plurality of flow paths is formed in the fixed scroll150may be reduced by reducing the number of flow paths generated in the fixed scroll150.

FIG. 7is a cross-sectional view of a compressor according to another embodiment.FIGS. 8A-8Bare exploded perspective views of a compressor unit of the compressor ofFIG. 7. Referring toFIG. 2, the compressor200according to this embodiment may include a lower compression structure in which the compression unit290is positioned below the drive motor220.

The compressor200may include a casing210having an inner space, the drive motor220provided at an upper portion of the inner space, the compression unit290disposed or provided at a lower end of the drive motor220, and a rotary shaft226that transmits a drive force of the drive motor220to the compression unit290. The inner space of the casing210may be divided into a first space V1at an upper side of the drive motor220, a second space V2between the drive motor220and the compression unit290, a third space V3partitioned by a discharge cover270, and an oil storage space V4at a lower side of the compression unit290.

The casing210may be, for example, in a cylindrical shape, so that the casing210may include a cylindrical shell211. An upper shell212is provided on or at an upper portion of the cylindrical shell211and a lower shell214may be provided on or at a lower portion of the cylindrical shell211. The upper and lower shells212and214may be joined to the cylindrical shell211by, for example, welding to form the inner space.

The upper shell212may be provided with a refrigerant discharge pipe216. The refrigerant discharge pipe216may be a passage through which a compressed refrigerant discharged from the compression unit290to the first space V1and the second space V2may be discharged to the outside.

The lower shell214may form the oil storage space V4. The oil storage space V4may function as an oil chamber for supplying oil to the compression unit290so that the compressor may be smoothly operated.

A refrigerant suction pipe218may be provided on or at a side surface of the cylindrical shell211, which may be a passage through which the refrigerant to be compressed may be introduced. Although not shown in the drawing, the refrigerant suction pipe218may be installed or provided to penetrate up to the compression chamber S1along a side surface of a fixed scroll250.

The drive motor220may be installed or provided on or at an upper side inside of the casing210. More specifically, the drive motor220may include a stator222and a rotor224.

The stator222may be formed in for example, a cylindrical shape and fixed to the casing210. A plurality of slots may be formed in an inner circumferential surface of the stator222along a circumferential direction so that coils may be wound. A refrigerant flow path groove212amay be formed on an outer circumferential surface of the stator222so as to be cut into a D-cut shape so that the refrigerant or oil discharged from the compression unit290may pass through the refrigerant flow path groove212a.

The rotor224may be coupled to an inside of the stator222and generate a rotational force. That is, the rotary shaft226may be press-fitted into a center of the rotor224so trial the rotor224may rotate together with the rotary shaft226. The rotational force generated by the rotor224may be transmitted to the compression unit290through the rotary shaft226.

The compression unit290may include a main frame230, the fixed scroll250, an orbiting scroll240, and a discharge cover270. The main frame230may be provided at a lower portion of the drive motor220, and form an upper portion of the compression unit290.

The main frame230may be provided with a circular frame end plate232(hereinafter, referred to as a “first end plate”), a frame shaft receiving portion232a(hereinafter, referred to as a “first shaft-receiving portion”) provided at a center of the first end plate232and through which the rotary shaft226may pass, and a frame side wall231(hereinafter, referred to as a “first side wall”) that protrudes upward from an outer circumferential portion of the first end plate232. An outer peripheral portion of the first side wall231may be brought into contact with an inner circumferential surface of the cylindrical shell211and a lower end portion of the first side wall231may be brought into contact with an upper end portion of a fixed scroll side wall255.

The first side wall231may be provided with a frame discharge bole231a(hereinafter, referred to as a “first hole”) that passes through an inside of the first side wall231in an axial direction to form a refrigerant passage. An inlet of the first hole231amay be connected to an outlet of a fixed scroll discharge hole256b, and an outlet of the first hole231amay be connected to the second space V2.

The first shaft-receiving portion232amay protrude from an upper surface of the first end plate232toward the drive motor220side. A first hearing portion of the rotary shaft226may be formed in the first shaft-receiving portion232asuch that a main hearing portion226cof the rotary shaft226may pass through the first bearing portion and be supported. That is, the first shaft-receiving portion232a, through which the main bearing portion226cof the rotary shaft226constituting the first bearing portion is rotatably inserted and supported, may axially pass through a center of the main frame230.

An oil pocket232bto collect oil discharged between the first shaft-receiving portion232aand the rotary shaft226may be formed on an upper surface of the first end plate232. The oil pocket232bmay be engraved on the upper surface of the first end plate232, and formed in an annular shape along an outer peripheral surface of the first shaft-receiving portion232a. In addition, a space may be formed on or at a bottom surface of the main frame230together with the fixed scroll250and the orbiting scroll240so that an intermediate pressure chamber S2may be formed to support the orbiting scroll240by a pressure of the space.

The intermediate pressure chamber S2may include an intermediate pressure region, and an oil supply flow path226aprovided in the rotary shaft226may include a high pressure region having a pressure higher than a pressure of the intermediate pressure chamber S2. A back pressure seal237may be provided between the main frame230and the orbiting scroll240to distinguish between the high pressure region and the intermediate pressure region. The back pressure seal237may serve as a sealing member or seal.

The main frame230may be coupled with the feed scroll250to form a space in which the orbiting scroll240may be rotatably installed or provided. Such a structure may be a structure that wraps around the rotary shaft226so that the rotational force may be transmitted to the compression unit290via the rotary shaft226.

The fixed scroll250, which constitutes a first scroll, may be coupled to a bottom surface of the main frame230. The fixed scroll250may include a circular fixed end plate252(hereinafter, referred to as a “second end plate”), a fixed scroll side wall255(hereinafter, referred to as “a second side wall”) that protrudes upward from an outer peripheral portion of the second end plate252, a fixed wrap251that protrudes from an upper surface of the second end plate252and engaged with an orbiting wrap241of the orbiting scroll240to form a compression chamber S1, and a fixed scroll shaft-receiving portion254(hereinafter, referred to as a “second shaft-receiving portion”) formed on or at a center of a rear surface of the second end plate252and through which the rotary shaft226may pass.

An outer peripheral portion of the second side wall255may be brought into contact with the inner circumferential surface of the cylindrical shell211, and an upper end portion of the second side wall portion255may be brought into contact with a lower surface of the first side wall231. The second side wall255may be provided with a fixed scroll groove256awhich may be engraved on an outer circumferential surface thereof along the axial direction and opened at both sides in the axial direction to form an oil passage. The fixed scroll groove256amay be formed to correspond to a first hole231aof the main frame230. An inlet of the fixed scroll groove256amay be connected to an outlet of the first hole231aand an outlet thereof may be connected to the oil storage space V4.

An integrated flow path253may be formed in the second end plate252of the fixed scroll250and connect the intermediate pressure chamber S2and the compression chamber S1. One or a first end of the integrated flow path253may be connected to the intermediate pressure chamber S2and the other or a second end thereof may be connected to the compression chamber S1.

The integrated flow path253may connect the intermediate pressure chamber S2and the compression chamber S1, thereby supplying oil fed to the intermediate pressure chamber S2to the compression chamber S1. In addition, the integrated flow path253may guide a refrigerant gas compressed at a high pressure in the compression chamber S1to the intermediate pressure chamber S2, and form an intermediate pressure corresponding to an average of a suction pressure and a discharge pressure in the intermediate pressure chamber S2. The pressure formed in the intermediate pressure chamber S2may act as a back pressure to press an upper surface of the orbiting scroll240.

That is, the integrated flow path253may be used as an oil flow path for providing oil and an intermediate pressure flow path for forming an intermediate pressure. Accordingly, according to embodiments, the flow path of the compression unit may be simplified by integrating the oil flow path and the refrigerant gas flow path into one.

The integrated flow path253will be discussed hereinafter with reference toFIGS. 9 and 10.

The second shaft-receiving portion254may protrude from a lower surface of the second end plate252toward the oil storage space V4side. The second shaft-receiving portion254may be provided with a second bearing portion such that a sub bearing portion226gof the rotary shaft226may be inserted into the second bearing portion and supported. A lower end portion of the second shaft-receiving portion264may be bent toward a center of the rotary shaft226to support a lower end of the sub bearing portion226gof the rotary shaft226to form a thrust bearing surface.

The orbiting scroll240coupled to the rotary shaft226to perform an orbiting motion may be installed or provided between the main frame230and the fixed scroll250. The orbiting scroll240may include a circular turning end plate242(hereinafter, referred to as a “third end plate”), the orbiting wrap241that protrudes from a lower surface of the third end plate242and engaged with the fixed wrap251, and a rotary shaft coupler244provided at a center of the third end plate242and rotatably coupled to an eccentric portion226fof the rotary shaft226.

The orbiting scroll240may include a differential pressure oil supply flow path245formed in the third end plate242. The differential pressure oil supply flow path245may be formed inside of the third end plate242of the orbiting scroll240so as to connect the intermediate pressure chamber S2and the oil introduction chamber S3.

The differential pressure oil supply flow path245will be discussed hereinafter with reference toFIGS. 9 and 10.

In a case of the orbiting scroll240, an outer circumferential portion of the third end plate242may be positioned at the upper end portion of the second side wall255, and a lower end portion of the orbiting wrap241may be in close contact with the upper surface of the second end plate252and supported by the fixed scroll250. An outer circumferential portion of the rotary shaft coupler244may be connected to the orbiting wrap241to form the compression chamber S1together with the fixed wrap251during the compression process. The fixed wrap251and the orbiting wrap241may be formed in an involute shape. The involute shape means a curved line corresponding to a locus drawn by an end portion of a thread when the thread wound around a base circle having an arbitrary radius is released. However, the shapes of the fixed wrap251and the orbiting wrap241are not limited thereto.

The eccentric portion226fof the rotary shaft226may be inserted into the rotary shaft coupler244. The eccentric portion226fmay be coupled to the orbiting wrap241or the fixed wrap251so as to overlap in a radial direction of the compressor.

The rotary shaft226may be coupled to the drive motor220and include the oil supply flow path226ato guide the oil contained in the oil storage space V4of the casing210upward. More specifically, a lower portion of the rotary shaft226may be coupled to the compression unit290and supported in the radial direction while an upper portion thereof is press-fitted into the center of the rotor224.

Thus, the rotary shaft226may transmit the rotational force of the drive motor220to the orbiting scroll240of the compression unit290. Then, the orbiting scroll240eccentrically coupled to the rotary shaft226may perform an orbiting motion with respect to the fixed scroll250.

The main bearing portion226cmay be formed in the lower portion of the rotary shaft226to be inserted into the first shaft-receiving portion232aof the main frame230and radially supported. The sub bearing portion228gmay be formed in a lower portion of the main bearing portion226cto be inserted into the second shaft-receiving portion254of the fixed scroll250and radially supported. The eccentric portion226fmay be formed between the main bearing portion226cand the sub bearing portion226gso as to be inserted into the rotary shaft coupler244of the orbiting scroll240and coupled therewith.

The main bearing portion226cand the sub bearing portion226gmay be coaxially formed so as to have a same axial center, and the eccentric portion226fmay be formed eccentrically in the radial direction with respect to the main bearing portion226cor the sub bearing portion226g.

The eccentric portion226fmay have an outer diameter smaller than an outer diameter of the main bearing portion226cand larger than an outer diameter of the sub bearing portion220g. In this case, the rotary shaft226may pass through each of the shaft-receiving portions232aand254and the rotary shaft coupler244to be coupled therewith.

Alternatively, the eccentric portion226fmay not be integrally formed with the rotary shaft226but may be formed using a separate bearing. In this case, the outer diameter of the sub bearing portion228gis not smaller than the outer diameter of the eccentric portion226f, but the rotary shaft226may be inserted into each of the shaft-receiving portions232aand254and the rotary shaft coupler244.

The oil supply flow path226afor supplying the oil in the oil storage space V4to surfaces of the bearing portions228cand228gand a surface of the eccentric portion226fmay be formed inside of the rotary shaft226. In addition, oil holes226b,226d, and226ethat pass from the oil supply flow path226ato an outer circumferential surface may be formed in the bearing portion226cand226gof the rotary abaft226and the eccentric portion226fof the rotary shaft226. More specifically, the oil holes may include a first oil hole226b, a second oil hole226d, and a third oil hole226e.

The first oil hole226bmay pass through an outer peripheral surface of the main bearing portion226c. More specifically, the first oil bole226bmay pass from the oil supply flow path226ato an outer peripheral surface of the main bearing portion226c. Further, the first oil hole226bmay pass through, for example, an upper portion of the outer peripheral surface of the main bearing portion226c. However, embodiments are not limited thereto, and the first oil hole226bmay pass through a lower portion of the outer peripheral surface of the main hearing portion226c.

In addition, the first oil hole226bmay include a plurality of holes, unlike that shown in the drawings. When the first oil hole226bincludes a plurality of holes, the holes may be formed only in the upper or lower portion of the outer peripheral surface of the main bearing portion226c, or formed in the upper and lower portions of the outer peripheral surface of the main bearing portion228c, respectively. However, for convenience of description, in this embodiment, the first oil hole226bincludes one hole.

A slant line or spiral-shaped first oil groove G1, one or a first end of which may be connected to the first oil hole226b, may be formed on the outer peripheral surface of the main bearing portion226c. More specifically, the first end of the first oil groove G1may be connected to the first oil hole226b, so that a portion of the oil discharged from the first oil hole226bmay be supplied to the outer peripheral surface of the main bearing portion226calong the first oil groove G1. That is, a portion of the oil discharged from the first oil hole226bmay flow along the first oil groove G1and be supplied to upper, lower, and lateral sides of the outer peripheral surface of the main bearing portion226c. The remaining oil discharged from the first oil hole226bmay be directly supplied to the upper, lower, and lateral sides of the outer peripheral surface of the main bearing portion226cwith respect to the first oil hole226b.

In addition, the first oil groove G1may be inclined in a relational direction of the rotary shaft226or in a direction opposite to the rotational direction. That is, the first oil groove G1may extend in a diagonal direction between the axial direction and the rotational direction (or the direction opposite to the relational direction) of the rotary shaft226.

The first oil groove G1may include a plurality of grooves, unlike that shown in the drawings. For example, when the first oil groove G1includes a plurality of grooves and the first oil hole226bincludes one or a first hole, one or a first end of each groove may be connected to the first oil hole226b.

In addition, when the first oil groove G1includes a plurality of grooves and the first oil hole226balso includes a plurality of holes, one or a first end of each groove may be formed so as to be connected one-to-one to each of the holes. However, for convenience of description, in this embodiment, the first oil groove G1includes one groove.

The second oil hole226dmay pass through an outer peripheral surface of the eccentric portion226f. More specifically, the second oil hole226dmay pass through from the oil supply flow path226ato the outer peripheral surface of the eccentric portion226f. In addition, the second oil hole226dmay pass through, for example, an intermediate portion of the outer peripheral surface of the eccentric portion226f. However, embodiments are not limited thereto, and the second oil hole226dmay pass through an upper or lower portion of the outer peripheral surface of the eccentric portion226f.

The second oil hole226dmay include a plurality of holes, unlike that shown in the drawings. When the second oil hole226dincludes a plurality of holes, each of the holes may be formed only in a middle portion of the outer peripheral surface of the eccentric portion226for formed in the upper and lower portions of the outer peripheral surface of the eccentric portion226f, respectively. However, for convenience of description, in this embodiment, the second oil hole226dincludes one hole.

The third oil hole228emay be formed on the sub bearing portion226g. More specifically, the third oil hole226emay pass through from the oil supply flow path226ato an outer peripheral surface of the sub bearing portion226g. Further, the third oil hole226emay pass through, for example, a middle portion of the outer peripheral surface of the sub bearing portion226g. However, embodiments are not limited thereto, and the third oil hole226emay pass through an upper or lower portion of the outer peripheral surface of the sub bearing portion226g.

The third oil hole226emay include a plurality of holes, unlike that shown in the drawings. In addition, when the third oil hole226eincludes a plurality of holes, each of the holes may be formed only in a middle portion of the outer peripheral surface of the sub bearing portion226g, or formed in the upper and lower portions of the outer peripheral surface of the sub bearing portion226g, respectively. However, for convenience of description, in this embodiment, the third oil hole226eincludes one hole.

A second oil groove G2may be formed on the outer peripheral surface of the sub bearing portion226gso as to be connected to the third oil hole226eand extend in the vertical direction. More specifically, the third oil hole226emay be formed at a center of the second oil groove G2, so that a portion of the oil discharged from the third oil hole226emay be efficiently supplied to the outer circumferential surface of the sub bearing portion226galong the second oil groove G2. That is, a portion of the oil discharged from the third oil hole226emay flow along the second oil groove G2and be supplied to upper, lower, and lateral sides of the outer peripheral surface of the sub bearing portion226g.

The remaining oil discharged from the third oil hole226amay be directly supplied to the upper, lower, and lateral sides of the outer peripheral surface of the sub bearing portion226gwith respect to the third oil hole226e. Of course, the second oil hole226dmay be formed on or at the upper or lower portions of the second oil groove G2. Further, the second oil groove G2may be straight in the vertical direction, that is, the longitudinal direction, as shown in the drawing, but may be formed to be inclined or spirally formed along the longitudinal direction.

The second oil groove G2may include a plurality of grooves, unlike that shown in the drawings. For example, when the second oil groove G2includes a plurality of grooves and the third oil hole226ealso includes a plurality of holes, each hole may be formed at a center of each groove. However, for convenience of description, in this embodiment, the second oil groove G2includes one groove.

As a result the oil guided upward through the oil supply flow path226amay be discharged through the first oil hole226band entirely supplied to the outer peripheral surface of the main bearing portion226c. In addition, the oil discharged through the first oil hole226bmay move to the lower portion of the main bearing portion226calong the first oil groove G1and be supplied to the upper surface of the orbiting scroll240.

The oil guided upward through the oil supply flow path226amay be discharged through the second oil hole226dand entirely supplied to the outer peripheral surface of the eccentric portion226f. In addition, the oil guided upward through the oil supply flow path226amay be discharged through the third oil hole226eand supplied to the outer peripheral surface of the sub bearing portion226g.

An oil feeder271that pumps oil stored in the oil storage space V4may be coupled to a lower end of the sub bearing portion226g. The oil feeder271may include an oil supply pipe273inserted into and coupled to the oil supply flow path226aof the rotary shaft226, and an oil absorption member274inserted into the oil supply pipe273to absorb oil. The oil supply pipe273may pass through a through-hole276of the discharge cover270to be submerged in the oil-storage space V4, and the oil absorption member274may function as a propeller.

Further, although not shown in the drawings, a trochoid pump (not shown) to forcibly pump upward the oil stored in the oil storage space V4instead of the oil feeder271may be coupled to the sub bearing portion226g. Furthermore, although not shown in the drawings, the compressor200according to an embodiment may further include a first sealing member or seal (not shown) that seals a gap between an upper end of the main bearing portion226cand an upper end of the main frame230and a second sealing member or seal (not shown) that seals a gap between a lower end of the sub bearing portion226gand a lower end of the fixed scroll250. It is possible to prevent the oil from flowing out of the compression unit290along a bearing surface, that is, an outer peripheral surface of the bearing portion, through the first and second sealing members or seals. This makes it possible to implement a differential pressure oil supply structure and prevent backflow of the refrigerant.

A balance weight227that suppresses noise and vibration may be coupled to the rotor224or the rotary shaft226. The balance weight227may be provided between the drive motor220and the compression unit290, that is, in the second space V2.

Hereinafter, an operation of a scroll compressor according to an embodiment will now be described.

When power is applied to the drive motor220to generate a rotational force, the rotary shaft226coupled to the rotor224of the drive motor220rotates. Then, the orbiting scroll240eccentrically connected to the rotary shall226may perform an orbiting motion with respect to the fixed scroll250to form the compression chamber S1between the orbiting wrap241and the fixed wrap251.

Next, the refrigerant supplied from the outside of the casing210through the refrigerant suction pipe218may be directly introduced into the compression chamber S1. The refrigerant may be compressed while moving in a direction of a discharge chamber of the compression chamber S1by the orbiting motion of the orbiting scroll240, and discharged to the third space V3via a discharge port257aof the fixed scroll250in the discharge chamber. Then, the compressed refrigerant discharged to the third space V3may be discharged to the inner space of the casing210via discharge holes257band257cand refrigerant flow path212aand discharged to the outside of the casing210through the refrigerant discharge pipe216.

Hereinafter, an integrated flow path structure of the compressor unit of the compressor ofFIG. 7will be described with reference toFIGS. 9 and 10.

FIGS. 9 and 10are partial cross-sectional views of an integrated flow path structure of the compressor unit of the compressor ofFIG. 7according to another embodiment.FIG. 9shows structures of the differential pressure oil supply flow path and the integrated flow path.FIG. 10shows an oil flow according to the differential pressure oil supply flow path and the integrated flow path.

More specifically, the oil stored in the oil storage space V4may be guided, that is, moved or supplied, upward through the oil supply flow path226aof the rotary shaft226. As shown inFIG. 9, the oil guided upward through the oil supply flow path226amay be discharged through the first oil hole226b, and entirely supplied to the outer peripheral surface of the main bearing portion226c.

The oil discharged through the first oil hole226bmay be supplied to the upper surface of the orbiting scroll240by moving along the first oil groove G1. The oil guided upward through the oil supply flow path226amay be discharged through the second oil hole226d, and entirely supplied to the outer peripheral surface of the eccentric portion226f.

The oil guided upward through the oil supply flow path226amay be discharged through the third oil hole226e, and supplied to the outer peripheral surface of the sub bearing portion226gor between the orbiting scroll240and the fixed scroll250. In this way, the oil contained in the oil storage space V4may be guided upward through the rotary shaft226and smoothly supplied to the bearing portion, that is, the bearing surface through the plurality of oil holes226b,226d, and226e, so that wear of the bearing portion may be prevented.

The oil discharged through the plurality of oil holes226b,226d, and226emay form an oil film between the fixed scroll250and the orbiting scroll240to maintain an airtight state. Further, the oil discharged through the plurality of oil holes226b,226d, and226emay absorb frictional heat generated by friction and dissipate heat in the high-temperature compression unit290.

A portion of the high-pressure oil discharged through the oil holes226b,226dand226emay move to the oil introduction chamber S3formed between the main frame230and the orbiting scroll240. A portion of the oil supplied to the oil introduction chamber S3may be supplied to the outer peripheral surface of the main bearing portion226c, the eccentric portion226f, or the sub bearing portion226g, or supplied between the orbiting scroll240and the fixed scroll250.

Another portion of the oil supplied to the oil introduction chamber S3may be supplied to the intermediate pressure chamber S2through the differential pressure oil supply flow path245of the orbiting scroll240. More specifically, the differential pressure oil supply flow path245may include a first hole245a, a second hole245b, and a horizontal passage245c. The first hole245amay be formed on an upper surface of the third end plate242and disposed close to a center axis of the orbiting scroll240so as to be connected to the oil introduction chamber S3. The first hole245a, may be formed of a plurality of holes; however, embodiments are not limited thereto.

The second hole245bmay be formed on the upper surface of the third end plate242and disposed close to an outer peripheral surface of the orbiting scroll240so as to be connected to the intermediate pressure chamber S2. Similarly, the second hole245bmay be formed of a plurality of holes; however, embodiments are not limited thereto.

The horizontal flow path245cmay connect the first hole245aand the second hole245band be formed on an inner side of the third end plate242so as to extend parallel to the upper surface of the third end plate242. Additionally, an opening245dfor opening a portion of a side surface of the third end plate242may be formed at one side of the first horizontal passage245c. An inner surface of the opening245dmay be formed with a screw groove which may be fastened to the coupling bolt247. However, embodiments are not limited thereto, and the inner surface of the opening245dmay be formed in various shapes which may be fastened to the coupling bolt247, such as a stepped shape or a curved shape.

The opening245dmay be used to insert a decompression pin249into the first horizontal flow path245c. That is, the decompression pin249may be disposed inside of the differential pressure oil supply flow path245. A diameter of the decompression pin249may be smaller than a diameter of the first horizontal flow path245c. Accordingly, the decompression pin249may adjust a pressure and an amount of supply of oil in the differential pressure oil supply flow path245by forming a narrow flow path through which oil may move in the differential pressure oil supply flow path245.

Although not clearly shown in the drawings, other shaped-decompression pins or members for forming a narrow flow path in the differential pressure oil supply flow path245may be used instead of the decompression pin249. For example, a cylindrical or polyhedral decompression pin may be used; however, embodiments are not limited thereto. However, for convenience of description, in this embodiment, an example in which the decompression pin249is provided in the differential pressure oil supply flow path245will be described.

After the decompression pin249is inserted into the first horizontal flow path245c, the coupling bolt247may be fastened to the opening245d. The coupling bolt247may be formed in a shape which may be coupled to the opening245d. For example, the coupling bolt247may be formed in a threaded, stepped, or curved shape corresponding to an inner shape of the opening245d. In addition, the coupling bolt247may be any one of a bolt (applying a fastening method), a rod (applying an indentation method), and a ball (applying an indentation method); however, embodiments are not limited thereto.

As the coupling belt247is coupled to the opening245d, the differential pressure oil supply flow path245having a shape “⊏” connecting the oil introduction chamber S3and the intermediate pressure chamber S2may be formed in the orbiting scroll240. However, embodiments are not limited thereto, and the shape of the differential pressure oil supply flow path245may be variously formed in an S shape or a “” shape.

The oil which has passed through the differential pressure oil supply flow path245to be discharged to the intermediate pressure chamber S2may be supplied to a thrust surface between the orbiting scroll240and the fixed scroll250. In addition, the discharged oil may be provided to an Oldham's ring260provided between the orbiting scroll240end the main frame230to prevent the orbiting scroll240from rotating. The oil discharged into the intermediate pressure chamber S2may be supplied between the respective components of the compression unit290to reduce the friction of the compression unit290.

Additionally, although not shown in the drawings, a plurality of differential pressure oil supply flow paths245may be formed in the orbiting scroll240. Further, the plurality of differential pressure oil supply flow paths246may be disposed or provided in the orbiting scroll240at regular intervals. A number of the differential pressure oil supply flow paths245may be equal to a number of the integrated flow paths253.

Further, the plurality of differential pressure oil supply flow paths245may be formed so as to correspond one-to-one to the plurality of integrated flow paths253. However, embodiments are not limited thereto.

The oil guided to the intermediate pressure chamber S2may be provided on the thrust surface between the orbiting scroll240and the fixed scroll250. The oil guided to the intermediate pressure chamber S2may be supplied to the Oldham's ring260provided between the orbiting scroll240and the main frame230and the thrust surface of the fixed scroll250.

That is, the oil introduced into the intermediate pressure chamber S2may be sufficiently provided to the thrust surface between the orbiting scroll240and the fixed scroll250and the Oldham's ring260. Accordingly, wear of the thrust surface of the fixed scroll250and the Oldham's ring260may be reduced.

The oil guided to the intermediate pressure chamber S2may be guided to the integrated flow path253provided in the fixed scroll250. The integrated flow path253may pass through the second side wall255and the second end plate252.

More specifically, the integrated flow path253may include a third hole253a, a fourth hole253b, and a horizontal flow path253c. The third hole253amay be formed on an upper surface of the second side wall255and connected to the intermediate pressure chamber S2. The third hole253amay be formed of a plurality of holes; however, embodiments are not limited thereto.

The fourth hole253bmay be formed on an upper surface of the second end plate252and connected to the compression chamber S1. Similarly, the fourth hole253bmay be formed of a plurality of holes; however, embodiments are not limited thereto.

The horizontal flow path253cmay connect the third bole253aand the fourth hole253b, and be formed on an inner side of the second end plate252so as to be parallel to one surface of the second end plate portion252. Further, the integrated flow path253may be formed to pass through only the second side wall255, in this case, a length of the integrated flow path253may be shorter in comparison with a case so which the integrated flow path253is formed to pass through both the second side wall255and the second end plate252. The integrated flow path253may be formed in a “¬” or “⊏” shape in the second end plate252of the fixed scroll250; however embodiments are not limited thereto.

Additionally, although not shown in the drawings, a plurality of integrated flow paths253may be formed in the fixed scroll250. In addition, the plurality of integrated flow paths253may be disposed or provided in the fixed scroll250at regular intervals. A number of the integrated flow paths250may be a same as a number of the differential pressure oil supply flow path245. However, embodiments are not limited thereto.

Accordingly, one or a first end of the integrated flow path253may communicate with the intermediate pressure chamber S2, and the other or a second end thereof may communicate with the compression chamber S1. Thus, the oil guided to the integrated flow path253may be supplied to the compression chamber S1. In this way, the oil contained in the oil storage space V4may be smoothly supplied to the compression chamber S1through the differential pressure oil supply flow path245and the integrated flow path253.

Further, the oil may be smoothly supplied to the compression chamber S1, so that wear due to friction between the orbiting scroll240and the fixed scroll250may be reduced, thereby improving compression efficiency. Furthermore, the oil supplied to the compression chamber S1may form an oil film between the fixed scroll250and the orbiting scroll240to maintain an airtight state of the compression chamber S1. Also, the oil supplied to the compression chamber S1may absorb frictional heat generated during the occurrence of friction between the fixed scroll250and the orbiting scroll240to dissipate heat.

The integrated flow path253may move the refrigerant gas compressed at a high pressure in the compression chamber S1to the intermediate pressure chamber S2to form an intermediate pressure between a suction pressure and a discharge pressure in the intermediate pressure chamber S2, and thereby a back pressure may be formed on an upper surface of the orbiting scroll240. That is, the compressor200according to this embodiment may integrate the intermediate pressure flow path and the differential pressure oil supply flow path, which are formed in the fixed scroll250in the conventional compressor, into one integrated flow path253.

The integrated flow path253may be used as an intermediate pressure flow path for forming a back pressure to press the orbiting scroll240in a direction of the fixed scroll250. In addition, the integrated flow path253may also be used as a differential pressure oil supply flow path for transmitting the oil discharged into the intermediate pressure chamber S2to the compression chamber S1.

Accordingly, the number of repaired flow paths in the fixed scroll250used in the compressor200according to embodiments may be reduced, in comparison to the prior art. Thus, the manufacturing process for producing the fixed scroll250may be simplified, and the manufacturing time reduced. Further, as the manufacturing process and time are reduced, manufacturing costs of the compressor200may be reduced.

Furthermore, vibration and noise due to friction generated when a plurality of flow paths are formed in the fixed scroll250may be reduced by reducing the number of flow paths in the fixed scroll250. Also, by reducing vibration and noise generated during operation of the compressor200, operational stability of the compressor200may be increased, and a user's satisfaction may also be enhanced.

Hereinafter, an integrated flow path structure of the compressor unit of the compressor ofFIG. 7according to another embodiment will be described with reference toFIG. 11.

FIG. 11is a partial cross-sectional view of an integrated flow path structure of a compression unit of the compressor ofFIG. 7according to another embodiment. However, the oil flow according to the differential pressure oil supply flow path245shown inFIG. 11may be the same as that shown inFIGS. 7 to 10, and thus, repetitive description thereof has been omitted.

Referring toFIG. 11, in the compressor200, the differential pressure oil supply flow path245formed in the orbiting scroll240may be disposed or provided on or at one or a first side of the orbiting scroll240with respect to the rotary shaft226, and disposed or provided on or at the other or a second side thereof with respect to the rotary shaft226of the integrated flow path253formed in the fixed scroll250. For example, the differential pressure oil supply flow path245formed in the orbiting scroll240may be positioned on a first side (left side in the drawing) with respect to the rotary shaft226, and the integrated flow path253formed in the fixed scroll250may be positioned on a second side (right side in the drawing) with respect to the rotary shaft226. That is, the differential pressure oil supply flow path245and the integrated flow path253may be positioned opposite to each other with respect to a center C of the rotary shaft226.

Further, a first direction of the differential pressure oil supply flow path245extending outward from the inside of the orbiting scroll240may be different from a second direction of the integrated flow path253extending outward from the inside of the fixed scroll250. That is, the first direction of the differential pressure oil supply flow path245extending outward from the Inside of the orbiting scroll240may be opposite from the second direction of the integrated few path253extending outward from the inside of the fixed scroll250.

Although any location of the differential pressure oil supply flow path245and the integrated flow path253may be suitable, where the differential pressure oil supply flow path245is located opposite to the integrated flow path253, a phenomenon where too much oil is provided at an initial operation of the compressor200may be prevented. That is, uniform distribution of oil may be provided, even at an initial operational the compressor200.

Although not shown in the drawings, an angle between the first direction of the differential pressure oil supply flow path245extending outward from the inside of the orbiting scroll240and the second direction of the integrated flow path253extending outward from the inside of the fixed scroll250may be an obtuse angle. That is, the angle between the first direction A and the second direction B1may be a value in a range of about 90 to 180 degrees.

In addition, an angle between the first direction A of the differential pressure oil supply flow path245extending outward from the inside of the turning scroll240and a third direction B2of the integrated flow path253extending outward from the inside of the fixed scroll250may be an acute angle. That is, the angle between the first direction A and the third direction B2may be a value in a range of about 0 to 90 degrees.

Accordingly, the oil discharged from the oil introduction chamber S3to the intermediate pressure chamber S2through the differential pressure oil supply flow path245may move along an inner peripheral surface of the intermediate pressure chamber S2. The oil discharged into the intermediate pressure chamber S2may be uniformly supplied to the thrust surface between the orbiting scroll240and the fixed scroll250and between the orbiting scroll240and the main frame230, while moving toward the integrated flow path253along the inner peripheral surface of the intermediate pressure chamber S2.

Next, the oil guided to the integrated flow path253may be supplied to the compression chamber S1. The oil may be uniformly supplied to the intermediate pressure chamber S2and the compression chamber S1so that the same effects as those of the previous embodiments, namely, reduction in wear, maintenance of airtight state, and heat dissipation, for example, may be obtained.

Additionally, as described above, as the number of flow paths required to be generated in the fixed scroll250is reduced, the manufacturing process and time may be reduced, and the manufacturing costs may be reduced. Further, vibration and noise due to friction generated when a plurality of flow paths are formed in the fixed scroll250may be reduced by reducing the number of flow paths generated in the fixed scroll250.

The compressor according to embodiments disclosed herein may integrate the oil flow path and the refrigerant gas flow path into one flow path, thereby simplifying the flow path of the compression unit. Thus, the manufacturing process for producing the fixed scroll may be simplified, and the manufacturing time of the fixed scroll may be reduced. In addition, as the manufacturing process and time are reduced, manufacturing costs of the fixed scroll may also be lowered. In addition, vibration and noise due to friction caused by forming a plurality of flow paths may be reduced. Accordingly, operational stability of the compressor may be increased, and a satisfaction of a user may also be enhanced.

In addition, in the compressor according to embodiments disclosed herein, the integrated flow path in the fixed scroll and the differential pressure oil supply flow path in the orbiting scroll may be disposed or provided to be spaced apart from each other in the compression unit, so that oil may be uniformly diffused into the compression unit. As a result, oil may be sufficiently supplied between the orbiting scroll and the fixed scroll in the compression unit, thereby minimizing a frictional force generated during operation of the compressor. In addition, the operation efficiency of the compressor may be improved.

Embodiments disclosed herein are directed to a compressor which may integrate an oil flow path and a refrigerant gas flow path in a fixed scroll into one, flow path thereby simplifying the flow path of a compression unit. Embodiments disclosed herein are also directed to a compressor in which a first differential pressure oil supply flew path and a second differential pressure oil supply flow path are arranged to be spaced apart from each other in an intermediate pressure chamber so that oil discharged into the intermediate pressure chamber may be uniformly diffused in a compression unit.

A compressor according to embodiments disclosed herein may include an integrated flow path in which an oil flow path and a refrigerant gas flow path are integrated into one flow path in a fixed scroll. The integrated flow path may connect an intermediate pressure chamber and a compression chamber in a compression unit. The integrated flow path which provides a compressed refrigerant in the compression chamber to the intermediate pressure chamber and oil in the intermediate pressure chamber to the compression chamber may be formed, so that the flow path of the compression unit may be simplified.

In addition, in the compressor according to embodiments disclosed herein, a first direction of a differential pressure oil supply flow path which extends outward from an inside of an orbiting scroll may be different from a second direction of the integrated flow path which extends outward from an inside of the fixed scroll. That is, the integrated flow path and the differential pressure oil supply flow path may be disposed to be spaced apart from each other, so that the oil discharged into the intermediate pressure chamber may be uniformly diffused in the compression unit.

This application relates to U.S. application Ser. No. 15/830,135, U.S. application Ser. No. 15/830,184, U.S. application Ser. No. 15/830,222, U.S. application Ser. No. 15/830,248, and U.S. application Ser. No. 15/830,290, all filed on Dec. 4, 2017, which are hereby incorporated by reference in their entirety. Further, one of ordinary skill in the art will recognize that features disclosed in these above-noted applications may be combined in any combination with features disclosed herein.

It will be apparent to those skilled in the art that various modifications can be made to the above-described embodiments without departing from the spirit or scope. Thus, if is intended that the embodiments covers all such modifications provided they come within the scope of the appended claims and their equivalents.