Patent Description:
A rotary compressor compresses refrigerant using a roller performing an orbiting movement in a compression space of a cylinder and a vane in contact with an outer circumferential surface of the roller to partition the compression space of the cylinder into a plurality of spaces.

The rotary compressor may be divided into a rolling piston type and a hinge vane type according to whether the roller and the vane are coupled to each other. The rolling piston type is a type in which the vane is detachably coupled to the roller so that the vane is closely attached to the roller, and the hinge vane type is a type in which the vane is hinge-coupled to the roller. Patent Document <NUM> (<CIT>) and Patent Document <NUM> (<CIT>) each disclose a hinge vane type, the hinge vane type has a stable vane behavior compared to the rolling piston type, thereby reducing axial leakage.

The rotary compressor generates a gas force in the compression space during the compression process, and the vane receives a force in a width direction by the gas force. However, as a rear side of the vane is coupled to a vane slot, the vane transmits a force in the width direction to the vane slot of the cylinder. Then, cylinder reaction forces acting in opposite directions while being orthogonal to the vane slot are generated on inner and outer circumferential sides of the vane slot. This pair of cylinder reaction forces act as a couple of forces as they are generated at preset intervals in a length direction of the vane. Therefore, when the vane reciprocates, a side surface of the vane and a sidewall surface of the vane slot may be pressed against each other to cause friction loss or side wear while increasing side pressure.

Such friction loss or side wear due to an increase of the side pressure may be greater in the hinge vane type as in Patent Document <NUM> and Patent Document <NUM> than in the rolling piston type, thereby reducing compressor efficiency or reducing reliability.

In addition, in the rotary compressor, refrigerant remains in a space (hereinafter, referred to as a refrigerant residual space) disposed between a side surface of the vane and one end of a discharge guide groove, and an outer peripheral surface of the roller even when discharge to the relevant compression chamber is completed due to the characteristics thereof, and the refrigerant remaining in this refrigerant residual space rises above a discharge pressure as the compression stroke of the roller progresses. Due to this, in the rotary compressor, the reliability of the compressor may be deteriorated as friction loss or side wear is further increased due to an increase of side pressure as described above.

<CIT> relates to a gas leakage preventing apparatus for a rotary compressor comprising: a cylinder having a cylindrical inner space therein; a rotating shaft having an eccentric portion therein which makes a circular motion in the inner space of the cylinder; a rolling piston inserted into the eccentric portion of the rotating shaft and being linearly contact with an inner wall of the inner space of the cylinder; a vane linear-movably inserted into a vane slot which is formed in the cylinder and dividing the cylinder inner space together with the rolling piston; and fixing units provided in the rolling piston and the vane for restraining a rotary motion of the rolling piston.

<CIT> relates to a compressor, comprising a drive motor; a rotating shaft configured to transfer a rotational force of the drive motor; a cylinder provided at one side of the drive motor; a roller provided on the rotating shaft to rotate, and allow at least two or more portions on an outer circumferential surface thereof to face an inner circumferential surface of the cylinder to form at least two compression spaces in the cylinder; and at least two or more vanes configured to face an outer circumferential surface of the roller to partition the two or more compression spaces into a suction chamber and a compression chamber, respectively, wherein at least two or more vane slots having an inner surface are formed in the cylinder to face both side surfaces of the vane, and a space portion recessed by a predetermined depth is formed between the vane slot and a side surface of the vane corresponding thereto.

An object of the present invention is to provide a rotary compressor capable of suppressing an increase inside pressure between a vane and a vane slot into which the vane is inserted in a hinge vane type, thereby suppressing friction loss or side wear.

Furthermore, another object of the present invention is to provide a rotary compressor capable of suppressing refrigerant from remaining in a refrigerant residual space, thereby prevent refrigerant pressure in the refrigerant residual space from rising above discharge pressure.

According to an aspect of the present invention, a rotary compressor is capable of allowing a refrigerant residual space to communicate with a discharge port so that refrigerant in the refrigerant residual space is discharged through the discharge port, thereby easily discharging residual refrigerant from the refrigerant residual space. The invention is specified by the independent claim.

In order to achieve the objectives of the present invention, a rotary compressor having a discharge port disposed to overlap with a vane is provided.

Furthermore, there is provided a rotary compressor in which the discharge port is disposed wider than a discharge guide groove.

In addition, it is intended to provide a rotary compressor in which the discharge port is disposed to be inclined toward the vane.

Moreover, it is intended to provide a rotary compressor in which the discharge port is eccentrically disposed toward the vane with respect to the discharge guide groove.

Besides, it is intended to provide a rotary compressor in which the discharge port includes two sections having different inner diameters.

In order to achieve the objectives of the present invention, there is provided a rotary compressor, including at least one cylinder in which a discharge guide groove is disposed at one side of a vane slot; a roller orbitably provided in the cylinder, and disposed with a hinge groove on an outer circumferential surface thereof; a vane in which one end portion thereof is rotatably inserted into the hinge groove of the roller, and the other end portion thereof is slidably inserted into the vane slot of the cylinder; and a plurality of bearing plates that seals both side surfaces of the cylinder, and at least one side of which is disposed with a discharge port to communicate with the discharge guide groove, wherein the discharge port communicates with a space disposed between a side surface of the discharge side of the vane, one end of the discharge guide groove, and an outer circumferential surface of the roller, the space is sealed while refrigerant remains, wherein the discharge port communicates with the space such that refrigerant in the space is discharged through the discharge port.

Here, the discharge port is disposed such that at least part thereof overlaps with the vane when projected in an axial direction.

Furthermore, the center of the discharge port is disposed to be concentric with the center of the discharge guide groove.

Furthermore, an inner diameter of the discharge port may be defined to be larger than that of the discharge guide groove.

Furthermore, an outlet-side inner diameter of the discharge port may be defined to be the same as an inner diameter of the discharge guide groove.

Furthermore, the discharge port may include a discharge port inlet portion and a discharge port outlet portion, and an inner diameter of the discharge port inlet portion may be defined to be larger than that of the discharge port outlet portion, and an inner diameter of the discharge port inlet portion facing the discharge guide groove may be defined to be larger than that of the discharge guide groove.

Furthermore, outside the scope of the claimed invention, a discharge groove extending eccentrically in a radial direction toward the vane may be disposed at an inlet of the discharge port facing the discharge guide groove, and the discharge groove may be disposed to overlap with the vane when projected in an axial direction.

Furthermore, outside the scope of the claimed invention, the discharge guide groove may be disposed to communicate with the discharge port, and the center of the discharge port may be disposed to be eccentrically positioned toward the vane with respect to the center of the discharge guide groove.

Furthermore, outside the scope of the claimed invention, the discharge port may be disposed in parallel to an axial direction.

Furthermore, outside the scope of the claimed invention, the discharge port may be disposed to be inclined with respect to an axial direction.

Here, the discharge guide groove may be disposed to communicate with the discharge port, and a discharge passage may be disposed between the discharge guide groove and the space.

Furthermore, the discharge passage may include a hole or a groove passing through between the discharge guide groove and the vane slot.

In addition, outside the scope of the claimed invention, there is provided a rotary compressor, including at least one cylinder in which a discharge guide groove is disposed at one side of a vane slot; a roller orbitably provided in the cylinder, and disposed with a hinge groove on an outer circumferential surface thereof; a vane in which one end portion thereof is rotatably inserted into the hinge groove of the roller, and the other end portion thereof is slidably inserted into the vane slot of the cylinder; and a plurality of bearing plates that seals both side surfaces of the cylinder, and at least one side of which is disposed with a discharge port to communicate with the discharge guide groove, wherein at least part of the discharge port is disposed to overlap with the vane slot or the hinge groove when projected in an axial direction.

Here, the center of the discharge port may be disposed to coincide with the center of the discharge guide groove in an axial direction, and an inlet-side inner diameter of the discharge port facing the discharge guide groove may be defined to be larger than an inner diameter of the discharge guide groove.

Here, outside the scope of the claimed invention, the center of the discharge port may be disposed eccentrically toward the vane slot or the hinge groove with respect to the center of the discharge guide groove.

Hereinafter, a rotary compressor according to the present embodiment will be described in detail with reference to an embodiment illustrated in the accompanying drawings. The rotary compressor according to the present embodiment may be classified into a single rotary compressor or a twin rotary compressor according to the number of cylinders. The present embodiment relates to an axial side shape of a roller or a bearing plate facing the roller in a hinge vane type rotary compressor in which the roller and a vane are coupled to each other. Therefore, the present invention may be applied to both the single rotary compressor or the twin rotary compressor. Hereinafter, a single rotary compressor will be described as an example, but the same description may also be applicable to the twin rotary compressor.

<FIG> is a longitudinal cross-sectional view showing a rotary compressor according to the present embodiment, and <FIG> is a transverse cross-sectional view showing a compression unit in the rotary compressor according to <FIG>.

Referring to <FIG> and <FIG>, in the rotary compressor according to the present embodiment, an electric motor unit <NUM> is provided in an inner space <NUM> of a casing <NUM>, and a compression unit <NUM> mechanically connected by a rotary shaft <NUM> is provided in the inner space <NUM> of the casing <NUM> at a lower side of the electric motor unit <NUM>.

The electric motor unit <NUM> includes a stator <NUM> press-fitted and fixed to an inner circumferential surface of the casing <NUM> and a rotor <NUM> rotatably inserted into the stator <NUM>. The rotary shaft <NUM> is press-fitted and coupled to the rotor <NUM>. An eccentric portion <NUM> is disposed eccentrically with respect to a shaft portion <NUM> in the rotary shaft <NUM>, and a roller <NUM> of a vane roller <NUM> which will be described later is slidably coupled to the eccentric portion <NUM>.

The compression unit <NUM> includes a main bearing plate <NUM>, a sub plate <NUM>, a cylinder <NUM>, and a vane roller <NUM>. The main bearing plate <NUM> and the sub bearing plate <NUM> are provided at both axial sides with the cylinder <NUM> interposed therebetween to define a compression space (V) inside the cylinder <NUM>. In addition, the main bearing plate <NUM> and the sub bearing plate <NUM> support the rotary shaft <NUM> passing through the cylinder <NUM> in a radial direction. The vane roller <NUM> is coupled to the eccentric portion <NUM> of the rotary shaft <NUM> to compress refrigerant while performing an orbiting movement in the cylinder <NUM>.

In the main bearing plate <NUM>, a main flange portion <NUM> is disposed in a disc shape, and a sidewall portion 111a is disposed at an edge of the main flange portion <NUM> to be shrink-fitted or welded to an inner circumferential surface of the casing <NUM>. A main bearing portion <NUM> is disposed at the center of the main flange portion <NUM> to protrude upward, and a main shaft receiving hole <NUM> is disposed at the main bearing portion <NUM> to pass therethrough such that the rotary shaft <NUM> is inserted and supported thereto.

A discharge port <NUM> in communication with the compression space (V) to discharge refrigerant compressed in the compression space (V) to the inner space <NUM> of the casing <NUM> is disposed at one side of the main bearing portion <NUM>. In some cases, the discharge port <NUM> may be disposed in the sub bearing plate <NUM> other than the main bearing plate <NUM>. The discharge port <NUM> will be described later.

In the sub bearing plate <NUM>, the sub flange portion <NUM> may be defined in a disc shape and bolt-fastened to the main bearing plate <NUM> together with the cylinder <NUM>. Of course, when the cylinder <NUM> is fixed to the casing <NUM>, the main bearing plate <NUM> may be bolt-fastened to the cylinder <NUM> and the sub bearing plate <NUM>, respectively, and when the sub bearing plate <NUM> fixed to the casing <NUM>, the cylinder <NUM> and the main bearing plate <NUM> may be fastened to the sub bearing plate <NUM> with bolts.

A sub bearing portion <NUM> is disposed at the center of the sub flange portion <NUM> to protrude downward, and a sub shaft receiving hole 122a is disposed at the sub bearing portion <NUM> to pass therethrough on the same axial line as a main shaft receiving hole 112a. A lower end of the rotary shaft <NUM> is supported by the sub shaft receiving hole 122a.

The cylinder <NUM> is defined in a circular annular shape with the same inner diameter on an inner circumferential surface thereof. An inner diameter of the cylinder <NUM> is defined to be larger than an outer diameter of the roller <NUM> to define a compression space (V) between an inner circumferential surface of the cylinder <NUM> and an outer circumferential surface of the roller <NUM>. Accordingly, the inner circumferential surface of the cylinder <NUM>, the outer circumferential surface of the roller <NUM>, and the vane <NUM> may define an outer wall surface of the compression space (V), an inner wall surface of the compression space (V), and a side wall surface of the compression space (V), respectively. Therefore, as the roller <NUM> performs an orbiting movement, the outer wall surface of the compression space (V) may define a fixed wall while the inner wall surface and the side wall surface of the compression space (V) define a variable wall whose position is variable.

A suction portion <NUM> is disposed in the cylinder <NUM>, and a vane slot <NUM> is disposed at one circumferential side of the suction portion <NUM>, and a discharge guide groove <NUM> is disposed at an opposite side of the suction portion <NUM> with the vane slot <NUM> interposed therebetween.

The suction port <NUM> is defined in a circular cross-sectional shape, and disposed to pass between an outer circumferential surface and an inner circumferential surface of the cylinder <NUM> and connected to a suction pipe <NUM> passing through the casing <NUM> is connected. Accordingly, refrigerant is sucked into the compression space (V) of the cylinder <NUM> through the suction pipe <NUM> and the suction port <NUM>.

The vane slot <NUM> is defined in a rectangular parallelepiped cross-sectional shape, and disposed in an elongated manner in a direction from an inner circumferential surface of the cylinder <NUM> toward an outer circumferential surface thereof. An inner circumferential side of the vane slot <NUM> is open, and an outer circumferential side thereof is disposed to be open so as to be blocked by an inner circumferential surface of the casing <NUM>.

Furthermore, the vane slot <NUM> is disposed to have a width approximately equal to the thickness or width of the vane <NUM> to allow the vanes <NUM> of the vane roller <NUM> which will be described later to slide. Accordingly, both side surfaces of the vanes <NUM> are supported by both inner wall surfaces of the vane slot <NUM> to slide approximately linearly.

The discharge guide groove <NUM> is defined by chamfering a hemispherical cross-sectional shape at an inner edge of the cylinder <NUM>. The discharge guide groove <NUM> serves to guide refrigerant compressed in the compression space of the cylinder to the discharge port <NUM> of the main bearing plate <NUM>. Accordingly, the discharge guide groove is disposed at a position overlapping with the discharge port when projected in an axial direction so as to communicate with the discharge port.

However, since the discharge guide groove <NUM> generates a dead volume, the discharge guide groove <NUM> may not be defined or may be defined with a minimum size. The discharge guide groove <NUM> will be described in detail later.

Meanwhile, the vane roller <NUM> includes a roller <NUM> and a vane <NUM> as described above. The roller <NUM> and the vane may be defined as a single body or may be coupled to each other to allow relative movement. The present invention will be described based on an example in which the roller and the vane are rotatably coupled to each other.

The roller <NUM> is defined in a cylindrical shape. An axial height of the roller <NUM> is defined substantially the same as an inner circumferential height of the cylinder <NUM>. However, since the roller <NUM> must slide relative to the main bearing plate <NUM> and the sub bearing plate <NUM>, the axial height of the roller <NUM> may be disposed to be slightly smaller than the inner circumferential height of the cylinder <NUM>.

Furthermore, the inner circumferential height and the outer circumferential height of the roller <NUM> may be disposed to be substantially the same. Accordingly, both axial cross-sections connecting between the inner circumferential surface and the outer circumferential surface of the roller <NUM> define a first sealing surface 141a and a second sealing surface 141b, and the first sealing surface 141a and the second sealing surface 141b are perpendicular to the inner or outer circumferential surface of the roller <NUM>. However, an edge between an inner circumferential surface of the roller <NUM> and the sealing surfaces 141a, 141b or an edge between an outer circumferential surface of the roller <NUM> and the sealing surfaces 141a, 141b may be defined at a right angle or may be slightly inclined or curved.

The roller <NUM> is rotatably inserted into and coupled to the eccentric portion <NUM> of the rotary shaft <NUM>, and the vane <NUM> is slidably coupled to the vane slot <NUM> of the cylinder <NUM> while at the same time being hinge-coupled to an outer circumferential surface of the roller <NUM>. Accordingly, the roller <NUM> performs an orbiting movement inside the cylinder <NUM> by the eccentric portion <NUM> during the rotation of the rotary shaft <NUM>, and the vane <NUM> reciprocates in a state of being coupled to the roller <NUM>.

One hinge groove <NUM> is disposed on an outer circumferential surface of the roller <NUM> so that a hinge protrusion <NUM> of the vane <NUM> which will be described later is inserted to rotate. The hinge groove <NUM> is defined in a circular arc shape in which an outer circumferential surface thereof is open.

An inner diameter of the hinge groove <NUM> is defined larger than an outer diameter of the hinge protrusion <NUM>, but defined with a size sufficient to slide without falling out while the hinge protrusion <NUM> is inserted.

Meanwhile, the vane <NUM> includes a sliding portion <NUM>, a hinge protrusion <NUM>, and an interference avoiding portion <NUM>.

The sliding portion1451 is defined in a flat plate shape having a predetermined length and thickness. For example, the sliding portion <NUM> is defined in a rectangular hexagonal shape as a whole. In addition, the sliding portion <NUM> is defined by a length such that the vane <NUM> remains in the vane slot <NUM> even when the roller <NUM> is completely moved to an opposite side of the vane slot <NUM>.

The hinge protrusion <NUM> is disposed to extend to a front end portion of the sliding portion <NUM> facing the roller <NUM>. The hinge protrusion <NUM> is inserted into the hinge groove <NUM> and disposed to have a rotatable cross-sectional area. The hinge protrusion <NUM> may be defined in a substantially circular cross-sectional shape except for a semicircular or connecting portion to correspond to the hinge groove <NUM>.

The interference avoiding portion <NUM> is a portion disposed to prevent the sliding portion <NUM> from interfering with an axial edge of the hinge groove <NUM> when the vane <NUM> rotates with respect to the roller <NUM>. Accordingly, the interference avoiding portion <NUM> is disposed in a direction in which an area between the sliding portion <NUM> and the hinge protrusion <NUM> decreases.

The interference avoiding portion <NUM> is typically disposed to be symmetrical with respect to a longitudinal center line of the sliding portion <NUM>, and defined in a recessed wedge curved cross-sectional shape. Accordingly, the interference avoiding portion <NUM> is spaced apart by a predetermined distance from an inner wall surface of the vane slot <NUM> while being inserted into the vane slot <NUM> to define an outer circumferential surface of the roller <NUM> and the refrigerant residual space (S) which will be described later.

Reference numerals <NUM> and <NUM> on the drawing denote a discharge valve and a muffler, respectively.

The foregoing rotary compressor according to the present embodiment operates as follows.

In other words, when power is applied to the electric motor unit <NUM>, the rotor <NUM> of the electric motor unit <NUM> is rotated to rotate the rotary shaft <NUM>. Then, the roller <NUM> of the vane roller <NUM> coupled to the eccentric portion <NUM> of the rotary shaft <NUM> rotates to suck refrigerant into the compression space (V) of the cylinder <NUM>.

The refrigerant repeats a series of processes of being compressed by the roller <NUM> and the vane <NUM> of the vane roller <NUM>, opening a discharge valve <NUM> provided in the main bearing plate <NUM> to be discharged into an inner space of the muffler <NUM> through the discharge port <NUM>, and being discharged into the inner space <NUM> of the casing <NUM>.

At this time, the position of the roller <NUM> and the vane <NUM> is moved according to an rotation angle of the rotary shaft <NUM>. <FIG> is a schematic view showing a positional change of a vane roller with respect to a rotation angle of a rotary shaft in a rotary compressor according to the present.

First, in this drawing, an imaginary line (hereinafter, referred to as a first center line) passing through an axial center (O) of the rotary shaft <NUM> (the same as an axial center of the cylinder) and an axial center (O') of the hinge groove <NUM> at a position where the eccentric portion <NUM> of the rotary shaft <NUM> faces the vane slot <NUM> is referred to as <NUM>°. This corresponds to (a) of <FIG>. At this time, the hinge groove <NUM> of the roller <NUM> is almost in contact with an inner circumferential surface of the cylinder <NUM> so that the vane <NUM> is drawn into the vane slot <NUM>.

Next, (b) and (c) of <FIG> are states in which the rotary shaft is rotated about <NUM>° and <NUM>°, respectively. While the state is changed from (a) of <FIG> of <FIG>, the hinge groove <NUM> of the roller <NUM> is spaced apart from an inner circumferential surface of the cylinder <NUM>, and part of the vane <NUM> is withdrawn from a vane slot <NUM>. At this time, a post-compression chamber (V2) defines a suction chamber while refrigerant flows into the post-compression chamber (V2) through the suction port <NUM>. In contrast, a pre-compression chamber (V1) starts to compress refrigerant filled in the pre-compression chamber (V1) while forming the compression chamber. Since refrigerant contained in the pre-compression chamber (V1) has not yet reached the discharge pressure, a gas force or vane reaction force is not generated or negligible in the pre-compression chamber even when generated.

Next, (d) of <FIG> is a state in which the rotary shaft is rotated about <NUM>°. While the state is changed from (c) of <FIG> of <FIG>, the hinge groove <NUM> of the roller <NUM> is spaced to the maximum apart from an inner circumferential surface of the cylinder <NUM>, and the vane <NUM> is withdrawn to the maximum from the vane slot <NUM>. Since the pre-compression chamber (V1) is in a state where the compression stroke is substantially advanced, refrigerant contained in the pre-compression chamber (V1) is close to the discharge pressure. Then, in the pre-compression chamber (V1), a gas force and a roller reaction force are generated by refrigerant to be compressed, and the gas force and roller reaction force are transmitted to the vane <NUM>. A reaction force is generated in a width direction of the vane <NUM> between both sides of the vane <NUM> and an inner surface of the vane slot <NUM> by the gas force and the roller reaction force transmitted to the vane <NUM>. This reaction force may cause an increase in side pressure or side wear between the vane <NUM> and the vane slot <NUM>. This will be described later along with an avoidance structure against an increase in side pressure or side wear.

Next, (e) of <FIG> illustrates a state in which the rotary shaft is rotated about <NUM> degrees. In this state, the hinge groove <NUM> of the roller <NUM> moves back toward an inner circumferential surface of the cylinder <NUM>, and the vane <NUM> is partially withdrawn into the vane slot <NUM>. At this time, the refrigerant contained in the pre-compression chamber (V1) has already reached a discharge pressure to start discharging or has reached a discharge start point. Therefore, in this state, the gas force and the roller reaction force described above are at or near the maximum, and thus an increase in side pressure or side wear between the vane <NUM> or the vane slot <NUM> may be generated to the greatest extent. This will be also described later along with an avoidance structure against an increase in side pressure or side wear.

Next, (f) of <FIG> is a state in which the rotary shaft is rotated about <NUM> degrees. In this state, refrigerant in the pre-compression chamber (V1) is almost discharged, and the hinge groove <NUM> of the roller <NUM> is almost in contact with an inner circumferential surface of the cylinder <NUM>, and the vane <NUM> is almost withdrawn into the vane slot <NUM>. In this state, almost no refrigerant remains in the pre-compression chamber (V1), and thus the gas force and roller reaction force are hardly generated.

As described above, in the rotary compressor, the gas force and roller reaction force act on the vane <NUM> at the same time due to the characteristics thereof. The gas force acts in a width direction of the vane <NUM>, which is a direction from the pre-compression chamber (discharge chamber) to the post-compression chamber (suction chamber), and the roller reaction force acts in a direction toward the vane <NUM> or acts as a component force to the force acting toward the vane <NUM> depending on the position of the roller <NUM>.

Accordingly, in the rotary compressor, as the gas force and roller reaction force are transmitted to a front side of the vane <NUM>, a first reaction force and a second reaction force acting in opposite directions are generated between both side surfaces of the vane <NUM> and around an inner circumferential edge and around an outer circumferential edge of the vane slot <NUM> facing the both side surfaces of the vane <NUM>.

As a result, when the vane <NUM> reciprocates inside the vane slot <NUM> during the aforementioned compression process, side pressure may be increased while both side surfaces of the vane <NUM> and the side surface edges of the vane portion <NUM> facing the vane <NUM> are excessively in close contact with each other, thereby causing friction loss or side wear.

Meanwhile, in the rotary compressor, a refrigerant residual space may be defined between a side surface of the discharge side of the vane, one end of the discharge guide groove, and an outer circumferential surface of the roller, and the refrigerant residual space may be sealed while refrigerant remains. Then, refrigerant in the refrigerant residual space is further compressed along an orbiting movement of the roller so that refrigerant pressure rises above a discharge pressure.

At this time, in a rolling piston type rotary compressor, since the vane is not constrained by the roller, if the pressure in the refrigerant residual space rises excessively, the vane is separated from the roller, and the refrigerant in the refrigerant residual space leaks to the opposite space (suction chamber) of the vane. It can lower the pressure in the refrigerant residual space.

However, in the hinge vane type rotary compressor, as the vane is constrained to the roller, refrigerant in the refrigerant residual space rises above the discharge pressure as described above without being leaked. Then, refrigerant pressure in the refrigerant residual space may be added to further increase a side pressure on the vane and the vane slot, thereby increasing friction loss or side wear between the vane and the vane slot as well as deteriorating the reliability of the vane and roller.

Accordingly, the present embodiment is intended to suppress an excessive increase in the pressure of the refrigerant residual space by defining a refrigerant discharge passage so that the refrigerant residual space communicates with the discharge port.

<FIG> is a cutaway perspective view showing part of a compression unit according to the present embodiment, and <FIG> is an enlarged perspective view showing the vicinity of a discharge port in <FIG>, and <FIG> is a plan view showing an example of a discharge port according to the present invention, and <FIG> is a cross-sectional view taken along line "IV-IV" in <FIG>.

Referring <FIG>, the discharge guide groove <NUM> communicating with the compression chamber (V) is disposed in the cylinder <NUM> according to the present embodiment, and the discharge port <NUM> is disposed in the main bearing plate <NUM> to communicate with the discharge guide groove <NUM>. Hereinafter, the discharge port <NUM> defines a side facing the compression chamber (V) as an inlet, and a side facing an internal space of the muffler <NUM> as an outlet, respectively.

The discharge port <NUM> may be disposed in parallel to an axial direction of the rotary shaft <NUM>. In other words, a first virtual line (CL1) connecting an inlet center (Oh1) and an outlet center (Oh2) of the discharge port <NUM> is disposed in parallel to an axial center line passing through the center (O) of the rotary shaft <NUM>. However, in some cases, in the discharge port <NUM>, the first virtual line (CL1) passing through the center (Oh) may be disposed to be inclined with respect to an axial center line (no reference numeral) passing through the center (O) of the rotary shaft <NUM>.

In addition, the first virtual line (CL1) passing through the center (Oh) of the discharge port <NUM> may be disposed on the same line as a second virtual line (CL2) passing through the center (Og) of the discharge guide groove <NUM>, which will be described later.

The discharge guide groove <NUM> is defined in a substantially hemispherical shape (exactly, a half hemispherical shape, but defined as a hemispherical shape for convenience of description) at an inner circumferential edge of the cylinder <NUM>, and the discharge port <NUM> is defined in a circular shape on the main bearing plate <NUM>.

In the discharge port <NUM> according to this embodiment, the center (Oh) of the discharge port <NUM> is disposed on the same axis as the center (Og) of the discharge guide groove <NUM>, and an inner diameter (D1) of the discharge port <NUM> is defined to be larger than an inner diameter (D2) of the discharge guide groove <NUM>, that is, a diameter of a virtual circle connecting both ends of the discharge guide groove <NUM> (hereinafter, defined as an inner diameter of the discharge guide groove for convenience of description though it is a curvature). In other words, a cross-sectional area of the discharge port <NUM> according to the present embodiment is defined to be larger than that of a virtual circle constituting the discharge guide groove <NUM>.

Accordingly, the discharge port <NUM> is disposed to radially overlap with part of the hinge protrusion <NUM> of the vane <NUM> or the hinge groove <NUM> of the roller <NUM>. Then, when projected in an axial direction, at least part of the refrigerant residual space (S) is included in a range of the discharge port <NUM> while the discharge port <NUM> and the refrigerant residual space (S) overlap with each other.

As described above, when an inner diameter (D1) of the discharge port <NUM> is defined to be larger than a inner diameter (D2) of the discharge guide groove <NUM>, and the refrigerant residual space (S) (or part of the hinge protrusion and the hinge groove) overlaps within a range of the discharge port <NUM>, the refrigerant residual space (S) remains in communication with the discharge port <NUM> even though the roller <NUM> (exactly, a contact point where the roller and the cylinder are in contact with each other) completely passes through the discharge guide groove <NUM>. Then, a residual refrigerant discharge passage through which the refrigerant remaining in the refrigerant residual space (S) can be discharged may be defined.

Then, even when the discharge stroke of the roller <NUM> is completed in the corresponding compression chamber (hereinafter, for convenience of description, it is defined as a state that the roller has completed the discharge stroke), refrigerant remaining in the refrigerant residual space (S) may be discharged to an internal space of the casing <NUM> through the discharge port <NUM>, thereby suppressing the pressure of the refrigerant residual space (S) from being excessively increased.

Then, side pressure applied to the vane <NUM> may be suppressed from being increased by a pressure of the refrigerant residual space of the roller <NUM>, thereby preventing friction loss and side wear occurring between the vane <NUM> and the vane slot <NUM>. In addition, it may be possible to suppress the reliability of the vane <NUM> and the roller <NUM> to which the vane <NUM> is hinge-coupled from being deteriorated.

Meanwhile, another example of a residual refrigerant discharge passage in the rotary compressor outside the scope of the claimed invention will be described as follows.

In other words, in the foregoing embodiment, an inner diameter of the discharge port is enlarged to define the discharge port so as to overlap with the refrigerant residual space in an axial direction, but in the present embodiment, the discharge port is defined to overlap with the refrigerant residual space in a radial direction while maintaining the inner diameter of the discharge port.

<FIG> is a plan view showing another example of a discharge port outside the scope of the claimed invention , and <FIG> is a cross-sectional view taken along line "V-V" in <FIG>.

Referring to <FIG>, the inner diameter (D1) of the discharge port <NUM> may be defined substantially the same as the inner diameter (D2) of the discharge guide groove <NUM>.

Furthermore, the discharge port <NUM> is disposed in parallel to an axial center line on which a first virtual line (CL1) connecting an inlet center (Oh1) and an outlet center (Oh2) of the discharge port <NUM> passes through the center (O) of the rotary shaft <NUM>.

However, the center (Oh) of the discharge port <NUM> is not located on the same axis as the center (Og) of the discharge guide groove <NUM>, but is disposed eccentrically toward the refrigerant residual space (S). Then, while the discharge port <NUM> is defined to have the same inner diameter as the discharge guide groove <NUM>, the discharge port <NUM> may overlap with part of the hinge protrusion <NUM> of the vane <NUM> or the hinge groove <NUM> of the roller <NUM> in a radial direction.

Accordingly, when projected in an axial direction, while the discharge port <NUM> overlaps with the refrigerant residual space (S), at least part of the refrigerant residual space (S) is included in a range of the discharge port <NUM>.

As described above, when the discharge port <NUM> is disposed eccentrically toward the refrigerant residual space (S) with respect to the discharge guide groove <NUM>, the refrigerant residual space (S) (or part of the hinge protrusion and the hinge groove) may overlap within a range of the discharge port <NUM>. The resultant operational effects are substantially the same as those of the above-described embodiment, and the description thereof will be omitted.

However, as the discharge port <NUM> is disposed by moving toward the refrigerant residual space (S), a residual refrigerant discharge passage may be defined without defining the inner diameter (D1) of the discharge port <NUM> to be larger than the inner diameter (D2) of the discharge guide groove <NUM>.

Then, a size of the discharge valve <NUM> that opens and closes the discharge port <NUM> may not be enlarged, thereby maintaining the responsiveness of the valve to that extent. Through this, when the size of the discharge valve <NUM> is enlarged, it may be possible to suppress the responsiveness deterioration of the valve, which may occur, as well as the resultant performance degradation and noise increase of the compressor.

Meanwhile, still another example of a discharge passage in the rotary compressor outside the scope of the claimed invention will be described as follows.

In other words, in the above-described examples , the discharge port is disposed in parallel to an axial direction of the rotary shaft, but in the present example, the discharge port is disposed to be inclined with respect to an axial direction of the rotary shaft, while an inlet of the discharge port is disposed to overlap with the refrigerant residual space in a radial direction.

<FIG> is a plan view showing another example of a discharge port outside the scope of the claimed invention, and <FIG> is a cross-sectional view taken along line "VI-VI" in <FIG>.

Referring to <FIG>, the inner diameter (D1) of the discharge port <NUM> is defined substantially the same as the inner diameter (D2) of the discharge guide groove <NUM>. However, a first virtual line (CL1) connecting an inlet center (Oh1) and an outlet center (Oh2) of the discharge port <NUM> is disposed to be inclined with respect to an axial center line (no reference numeral) passing through the center (O) of the rotary shaft <NUM>.

For example, the inlet center (Oh1) of the discharge port <NUM> is disposed eccentrically toward the vane slot <NUM> with respect to the center (Og) of the discharge guide groove <NUM>. Then, even though the outlet of the discharge port <NUM> is spaced apart from the refrigerant residual space in a radial direction, the inlet of the discharge port <NUM> may overlap with part of the hinge protrusion <NUM> of the vane <NUM> or the hinge groove <NUM> of the roller <NUM>. Accordingly, when projected in an axial direction, while the discharge port <NUM> overlaps with the refrigerant residual space (S), at least part of the refrigerant residual space (S) is included in a range of the discharge port <NUM>.

In this case, the outlet center (Oh2) of the discharge port <NUM> may be disposed to be positioned on substantially the same axis as the center (Og) of the discharge guide groove <NUM>.

As described above, when the inlet center (Oh1) of the discharge port <NUM> is disposed eccentrically toward the refrigerant residual space (S) with respect to the discharge guide groove <NUM>, a refrigerant residual space (S) (or part of the hinge protrusion and the hinge groove) is included in a range of the discharge port <NUM> as in the above-described embodiments to define a residual refrigerant discharge passage.

However, in the present embodiment, as the inlet of the discharge port <NUM> is disposed by moving toward the refrigerant residual space (S), a residual refrigerant discharge passage may be defined without defining the inner diameter of the discharge port <NUM> to be larger than the inner diameter of the discharge guide groove <NUM>.

Then, a size of the discharge valve <NUM> that opens and closes the discharge port <NUM> may not be enlarged, thereby maintaining the responsiveness of the valve to that extent as shown in the embodiment of <FIG>. Through this, when the size of the discharge valve <NUM> is enlarged, it may be possible to suppress the responsiveness deterioration of the valve, which may occur, as well as the resultant performance degradation and noise increase of the compressor.

In addition, in the present embodiment, as the discharge port <NUM> is disposed to be inclined, the discharge valve <NUM> may be disposed at its original position, that is, a position having the center on the same axis as the center of the discharge guide groove <NUM>, thereby sufficiently securing an interference distance with respect to the main bearing portion <NUM>. Through this, a radial thickness of the main bearing portion <NUM> may be secured to stably support the rotary shaft to that extent.

Meanwhile, still another embodiment of a discharge passage in the rotary compressor according to the present embodiment will be described as follows.

In other words, in the above-described embodiments, the discharge port is defined with a single inner diameter, but in the present embodiment, the discharge port is defined with a plurality of inner diameters.

<FIG> is a plan view showing another example of a discharge port according to the present invention, and <FIG> is a cross-sectional view taken along line "VII-VII" in <FIG>.

Referring to <FIG>, a first virtual line (CL1) connecting an inlet center (Oh1) and an outlet center (Oh2) of the discharge port <NUM> according to the present invention is disposed on the same axial line with respect to an axial center line (not shown) passing through the center (O) of the rotary shaft <NUM>.

In addition, the center (Oh) of the discharge port <NUM> is disposed on the same axial line as the center (Og) of the discharge guide groove <NUM>. However, in the present embodiment, an inlet-side inner diameter (D11) of the discharge port <NUM> is defined to be larger than an outlet-side inner diameter (D12) thereof.

For example, the discharge port <NUM> according to the present embodiment is configured with a discharge port inlet portion <NUM> and a discharge port outlet portion <NUM> constituting an inlet side. The inner diameter (D11) of the discharge port inlet portion <NUM> is defined to be larger than the inner diameter (D2) of the discharge guide groove <NUM>, and the inner diameter (D12) of the discharge outlet portion <NUM> is defined substantially the same as the inner diameter (D2) of the discharge guide groove <NUM>.

Then, while an outlet of the discharge port <NUM> is defined to have the same inner diameter as the discharge guide groove <NUM>, an inlet of the discharge port <NUM> may be defined to be larger than the discharge guide groove <NUM> to overlap with part of the hinge protrusion <NUM> of the vane <NUM> or the hinge groove <NUM> of the roller <NUM> in a radial direction.

Accordingly, when projected in an axial direction, while the inlet of the discharge port <NUM> overlaps with the refrigerant residual space (S), at least part of the refrigerant residual space (S) is included in a range of the inlet of the discharge port <NUM>.

As described above, when the discharge port <NUM> is defined with a discharge port inlet portion <NUM> and a discharge port outlet portion <NUM> having different inner diameter, the refrigerant residual space (S) (or part the hinge protrusion and the hinge groove) may be included in a range of the inlet of the discharge port <NUM>. The resultant operational effects are substantially the same as those of the above-described embodiment of <FIG>, and the description thereof will be omitted.

In other words, in the above-described embodiments, the residual refrigerant discharge passage is disposed in the discharge port, but in the present embodiment, the residual refrigerant discharge groove is disposed in the discharge port.

<FIG> is a plan view showing another example of a discharge port according to the present invention, and <FIG> is a cross-sectional view taken along line "VIII-VIII" in <FIG>.

Referring to <FIG>, a first virtual line (CL1) connecting an inlet center (Oh1) and an outlet center (Oh2) of the discharge port <NUM> according to the present embodiment is disposed on the same axial line with respect to an axial center line (no reference numeral) passing through the center (O) of the rotary shaft <NUM>.

In addition, the center (Oh) of the discharge port <NUM> is defined on the same axial line as the center (Og) of the discharge guide groove <NUM>, and the inner diameter (D1) of the discharge port <NUM> is defined to be the same as the inner diameter (D2) of the discharge guide groove <NUM>. However, in the present embodiment, the residual refrigerant discharge groove <NUM> is disposed on an inlet side of the discharge port <NUM>.

The residual refrigerant discharge groove <NUM> is disposed to extend eccentrically toward the refrigerant residual space (S) from the inlet side of the discharge port <NUM>. The residual refrigerant discharge groove <NUM> may be defined in an arc shape or an angled shape, or may be disposed to be inclined to intersect the first virtual line (CL1) passing through the center (Oh) of the discharge port <NUM>.

Then, while the discharge port <NUM> is defined to have the same inner diameter as the discharge guide groove <NUM>, the residual refrigerant discharge groove <NUM> may overlap with part of the hinge protrusion <NUM> of the vane <NUM> or the hinge groove <NUM> of the roller <NUM> in a radial direction.

Accordingly, when projected in an axial direction, while the residual refrigerant discharge groove <NUM> provided at an inlet of the discharge port <NUM> overlaps with the refrigerant residual space (S), at least part of the refrigerant residual space (S) is included in a range of the inlet of the discharge port <NUM>.

As described above, when the residual refrigerant discharge groove <NUM> is disposed at the inlet of the discharge port <NUM>, the refrigerant residual space (S) (or part the hinge protrusion and the hinge groove) may be included in a range of the inlet of the discharge port <NUM>. The resultant operational effects are substantially the same as those of the above-described embodiment of <FIG>, and the description thereof will be omitted.

In other words, in the above-described embodiments, the discharge port is disposed to overlap with the refrigerant residual space in a radial direction, but the present embodiment directly communicates between the discharge port and the refrigerant residual space through the discharge passage.

<FIG> is a plan view showing another example of a discharge port according to the present invention, and <FIG> is a cross-sectional view taken along line "IX-IX" in <FIG>.

Referring to <FIG>, the center (Oh) of the discharge port <NUM> according to the present embodiment is disposed to be positioned substantially on the same axial line as the center (Og) of the discharge guide groove <NUM>. In addition, the inner diameter (D1) of the discharge port <NUM> is defined substantially the same as the inner diameter (D2) of the discharge guide groove <NUM>. Accordingly, the discharge port <NUM> is disposed at a position that does not overlap with the refrigerant residual space (S) in a radial direction.

However, a discharge passage <NUM> passing through between the inner wall surfaces of the vane slot <NUM> constituting the refrigerant residual space (S) may be disposed on a side surface of the discharge guide groove <NUM> according to the present embodiment. The discharge passage <NUM> may be defined with at least one hole.

Although not shown in the drawing, the discharge passage may be defined with at least one groove provided at an edge between a side surface of the discharge guide groove and an inner wall surface of the vane slot connected at this side surface.

Here, the inlet center (Oh1) and the outlet center (Oh2) of the discharge port <NUM> may be disposed in parallel to or to be inclined with respect to an axial center of the rotary shaft <NUM>.

As described above, when the discharge passage <NUM> is disposed between the discharge guide groove <NUM> and the vane slot <NUM>, refrigerant in the refrigerant residual space (S) moves to the discharge guide groove <NUM> through the discharge passage <NUM>, and the refrigerant is discharged through the discharge port <NUM> even when the roller <NUM> completely passes through the discharge guide groove <NUM>. Accordingly, it may be possible to prevent refrigerant remaining in the refrigerant residual space (S) from being over-compressed, similarly to the above-described embodiments.

In addition, as shown in the embodiments of <FIG>, <FIG>, <FIG> and <FIG> described above, a residual refrigerant discharge passage may be defined without defining the inner diameter (D1) (exactly, an outlet of the discharge port) of the discharge port <NUM> to be larger than the inner diameter (D2) of the discharge guide groove <NUM>.

In addition, as shown in the present embodiment of <FIG>, <FIG> and <FIG>, the discharge valve <NUM> may be disposed at its original position, that is, a position having the center on the same axis as the center of the discharge guide groove <NUM>, thereby sufficiently securing an interference distance with respect to the main bearing portion <NUM>. Through this, a radial thickness of the main bearing portion <NUM> may be secured to stably support the rotary shaft to that extent.

In a rotary compressor according to the present embodiment, since the discharge port communicates with the refrigerant residual space defined between the vane slot and the discharge guide groove, it may be possible to suppress refrigerant from remaining in the refrigerant residual space even after the roller passes through the discharge guide groove. Through this, refrigerant pressure in the refrigerant remaining space may be suppressed from rising above the discharge pressure, thereby suppressing an increase in side pressure, friction loss or side wear between a vane and a vane slot into which the vane is inserted.

Furthermore, in the present embodiment, the center of the discharge port may be disposed to be concentric with the center of the discharge guide groove, and an inner diameter of the discharge port may be defined to be larger than that of the discharge guide groove. Through this, the discharge port is always in communication with the refrigerant residual space, thereby suppressing refrigerant pressure in the refrigerant residual space from rising above the discharge pressure.

In addition, in the present embodiment, while the discharge port communicates with the refrigerant residual space defined between the vane slot and the discharge guide groove, an outlet-side inner diameter of the discharge port may be defined to be the same as that of the discharge guide groove. Through this, it may be possible to maintain the diameter of the discharge valve so as to increase a responsiveness of the discharge valve and increase a degree of freedom of installation thereof.

In addition, in the present embodiment, the discharge port may be disposed to be inclined or stepped so that the discharge port communicates with the refrigerant residual space defined between the vane slot and the discharge guide groove while maintaining an inner diameter of the discharge port. Through this, a diameter of the discharge valve may be maintained while quickly discharging refrigerant in the refrigerant residual space, thereby increasing a responsiveness of the discharge valve and increasing a degree of freedom of installation thereof.

On the other hand, the above-described embodiments have been mainly described with reference to an example in which the roller and the vane are rotatably coupled to each other, but the wear avoiding portion may also be similarly applicable to a case where the roller and the vane are formed as a single body.

In addition, the above embodiments have been mainly described with reference to an example of one cylinder, but the wear avoiding portion may also be similarly applicable to a case of having a plurality of cylinders.

On the other hand, according to the present invention, since a roller reaction force may be further generated when using a high-pressure refrigerant, such as R32, the high-pressure refrigerant may be usefully applicable to a hinge vane type rotary compressor.

Claim 1:
A rotary compressor, comprising:
at least one cylinder (<NUM>) in which a discharge guide groove (<NUM>) is disposed at one side of a vane slot (<NUM>);
a roller (<NUM>) which is orbitably provided in the cylinder (<NUM>), and disposed with a hinge groove (<NUM>) on an outer circumferential surface thereof;
a vane (<NUM>) in which one end portion thereof is rotatably inserted into the hinge groove (<NUM>) of the roller (<NUM>), and the other end portion thereof is slidably inserted into the vane slot (<NUM>) of the cylinder (<NUM>); and
a plurality of bearing plates (<NUM>, <NUM>) that seal both side surfaces of the cylinder (<NUM>), at least one side of the bearing plates (<NUM>, <NUM>) being disposed with a discharge port (<NUM>) to communicate with the discharge guide groove (<NUM>),
characterized in that:
a space (S) is defined between a side surface of the discharge side of the vane (<NUM>), one end of the discharge guide groove (<NUM>), and the outer circumferential surface of the roller (<NUM>), the space (S) is sealed while refrigerant remains,
wherein the discharge port (<NUM>) communicates with the space (S) such that refrigerant in the space (S) is discharged through the discharge port (<NUM>),
wherein the discharge port (<NUM>) is disposed such that at least part thereof overlaps with the vane (<NUM>) when projected in an axial direction, and
wherein
the center (Oh) of the discharge port (<NUM>) is disposed to be concentric with the center (Og) of the discharge guide groove (<NUM>).