KR20240064308A - Scroll compressor - Google Patents

Abstract

A scroll compressor is disclosed. In the scroll compressor, a valve receiving groove that is recessed to a preset depth and accommodates a bypass hole is formed on the rear surface of the non-orbiting scroll, and a bypass valve that opens and closes the bypass hole is slidably inserted in the axial direction into the valve receiving groove. It can be. Through this, the bypass valve, which suppresses overcompression of the compression chamber, is not fastened to the non-swivel head plate, so the thickness of the non-swivel head plate can be made thin. As the thickness of the non-swivel head plate becomes thinner, the length of the bypass hole decreases. can be reduced, lowering the dead volume in the bypass hole.

Description

Scroll compressor{SCROLL COMPRESSOR}

The present invention relates to scroll compressors.

In a scroll compressor, an orbiting scroll and a non-orbiting scroll are engaged and combined, and the orbiting scroll rotates with respect to the non-orbiting scroll, forming a pair of compression chambers between the orbiting scroll and the non-orbiting scroll.

The compression chamber consists of a suction pressure chamber formed on the outside, an intermediate pressure chamber formed continuously with the volume gradually decreasing from the suction pressure chamber toward the center, and a discharge pressure chamber connected to the center of the intermediate pressure chamber. Typically, the suction pressure chamber penetrates the side of the non-orbiting scroll and communicates with the refrigerant suction pipe, the intermediate pressure chamber is sealed and connected in multiple stages, and the discharge pressure chamber penetrates the center of the head plate of the non-orbiting scroll and communicates with the refrigerant discharge pipe.

As the scroll compressor is formed so that the compression chamber moves continuously, overcompression may occur during operation. Accordingly, conventionally, a bypass hole is formed around the discharge port, that is, upstream of the discharge port, to discharge the overcompressed refrigerant in advance. The bypass hole is provided with a bypass valve, which opens and closes the bypass hole according to the pressure of the compression chamber. Bypass valves are mainly used as plate valves or reed valves.

Patent Document 1 (US Patent Publication US2018/0038370 A1) discloses a scroll compressor equipped with a bypass valve made of a plate valve. Patent Document 1 opens and closes a plurality of bypass holes with a single bypass valve formed in an annular shape, but this increases the number of parts as the bypass valve is supported by an elastic member. In addition, since the bypass valve operates in a separated state, modularization is difficult, which may increase the assembly time of the compressor. In addition, as the length of the bypass hole becomes longer, overcompression may occur due to discharge delay, and the dead volume may increase, which may reduce indication efficiency.

Patent Document 2 (Korean Patent Publication No. 10-2014-0114212) and Patent Document 3 (US Patent Publication US2015/0345493 A1) each disclose a scroll compressor equipped with a bypass valve made of a reed valve. Patent Document 2 and Patent Document 3 fix the bypass valve to the non-orbiting scroll using a rivet or pin, respectively. This means that the end plate thickness of the non-orbiting scroll must be secured as much as the rivet depth or pin depth, so the length of the bypass hole is becomes longer. As a result, as shown in Patent Document 1, discharge of the refrigerant through the bypass hole is delayed, causing overcompression, and as the bypass hole becomes longer, the dead volume increases, which may reduce the indication efficiency.

US published patent US2018/0038370 A1 (publication date: 2018.02.08.) Republic of Korea Patent Publication No. 10-2014-0114212 (Publication date: 2014.09.26.) US published patent US2015/0345493 A1 (publication date: 2015.12.03.)

The purpose of the present invention is to provide a scroll compressor that can reduce dead volume while suppressing overcompression in the compression chamber.

Another object of the present invention is to provide a scroll compressor that can reduce the dead volume in the bypass hole by reducing the length of the bypass hole.

Another object of the present invention is to provide a scroll compressor in which the bypass valve can operate stably while reducing the length of the bypass hole.

Another object of the present invention is to provide a scroll compressor that can reduce the length of the bypass hole while suppressing the generation of attachment and detachment noise when opening and closing the bypass valve.

In order to achieve the object of the present invention, a scroll compressor including a casing, an orbiting scroll, a non-orbiting scroll, and a back pressure chamber assembly can be provided. The orbiting scroll is provided with a orbital wrap and can perform a orbital movement in the inner space of the casing. The non-orbiting scroll may be provided with a non-orbiting wrap to engage with the orbiting wrap to form a compression chamber, and may be provided with a bypass hole so that the refrigerant in the compression chamber is discharged into the inner space of the casing. The back pressure chamber assembly is coupled to the rear surface of the non-orbiting scroll and can pressurize the non-orbiting scroll toward the orbiting scroll. A valve receiving groove that is recessed to a preset depth and accommodates the bypass hole is formed on the rear surface of the non-orbiting scroll, and a bypass valve that opens and closes the bypass hole is slidably inserted in the axial direction. You can. Through this, the bypass valve, which suppresses overcompression of the compression chamber, is not fastened to the non-swivel head plate, so the thickness of the non-swivel head plate can be made thin. As the thickness of the non-swivel head plate becomes thinner, the length of the bypass hole decreases. can be reduced, lowering the dead volume in the bypass hole.

For example, an intermediate discharge port communicating with the internal space of the casing may be formed in the back pressure chamber assembly. A discharge guide passage may be formed between the valve receiving groove and the bypass valve to communicate the bypass hole with the intermediate discharge port. Through this, even if the bypass valve is inserted into the valve receiving groove of the non-orbiting scroll, smooth communication can be achieved between the bypass hole and the intermediate discharge port when the bypass valve is opened.

For example, the cross-sectional shape of the valve receiving groove may be formed to correspond to the cross-sectional shape of the bypass valve. The discharge guide passage may be formed to be depressed by a preset depth on at least one side of the inner circumferential surface of the valve receiving groove or the outer circumferential surface of the bypass valve facing it. Through this, as the discharge guide passage is formed close to the bypass hole, the flow resistance for the refrigerant discharged through the bypass hole can be lowered.

Additionally, the cross-sectional shape of the valve receiving groove may be different from that of the bypass valve. The axial cross-sectional area of the valve receiving groove may be larger than the axial cross-sectional area of the bypass valve. Through this, the discharge guide passage can be easily formed as the discharge guide passage is formed together with the valve receiving groove.

As another example, the bypass valve may be formed to have a rectangular cross-sectional shape when projected in the axial direction. Through this, even if a plurality of bypass holes are formed, the plurality of bypass holes can be opened and closed at once with one bypass valve.

For example, a discharge guide groove may be formed on at least one side of the long-axis side of the valve receiving groove and the long-axis side of the bypass valve facing it. Through this, as the discharge guide passage is formed close to the bypass hole, the flow resistance for the refrigerant discharged through the bypass hole is lowered, and at the same time, both sides in the long axis direction of the bypass valve are connected to the valve receiving groove without a separate valve guide. It can be supported on both sides of the long axis.

Specifically, a valve buffering groove may be formed on the rear surface of the non-orbiting scroll forming the bottom surface of the valve receiving groove, and the cross-sectional area of the valve buffering groove may be smaller than the cross-sectional area of the bypass valve. The valve buffer groove may be selectively communicated with the discharge guide groove and the bypass valve. Through this, a portion of the refrigerant discharged through the bypass hole fills the valve buffer groove, thereby lowering the closing shock between the bypass valve and the valve receiving groove when the bypass valve is closed.

In addition, a plurality of bypass holes are formed along the formation direction of the non-swivel wrap, and the plurality of bypass holes can be accommodated in one valve receiving groove. Through this, it is possible to simplify the shape of the bypass valve and reduce the dead volume in the bypass hole by reducing the thickness of the non-circulating head plate.

Specifically, a valve cushioning groove may be formed on the rear surface of the non-orbiting scroll, which forms the bottom surface of the valve receiving groove. The cross-sectional area of the valve buffer groove may be smaller than the cross-sectional area of the bypass valve. Through this, a portion of the refrigerant discharged through the bypass hole fills the valve buffer groove, thereby lowering the closing shock between the bypass valve and the valve receiving groove when the bypass valve is closed.

As another example, a valve guide may be provided between the bypass valve and the back pressure chamber assembly, extending along the axial direction to support the bypass valve in the radial direction. Through this, it is possible to stably support the radial direction of the bypass valve that is inserted into the valve receiving groove and opens and closes the bypass hole while moving in the axial direction.

For example, one end of the valve guide may be fixed to the bypass valve or the back pressure chamber assembly. The other end of the valve guide may be slidably inserted in the guide receiving groove provided in the back pressure chamber assembly or bypass valve along the axial direction. Through this, the valve guide that supports the axial movement of the bypass valve can be easily assembled.

Specifically, a valve spring may be provided between the bypass valve and the back pressure chamber assembly to press the bypass valve toward the non-orbiting scroll. The valve spring is made of a compression coil spring and can be inserted into the valve guide. Through this, the bypass valve can slide stably along the axial direction inside the valve receiving groove, while at the same time improving the assembly reliability of the valve spring.

As another example, on one side of the outer peripheral surface of the bypass valve and the inner peripheral surface of the valve receiving groove facing it, a protrusion extends along the axial direction, and on the other side, a groove into which the protrusion is inserted may extend along the axial direction. . Through this, the axial movement of the bypass valve can be stably supported without providing a separate valve guide outside the valve receiving groove.

As another example, the valve receiving groove may be formed to correspond to the cross-sectional shape of the bypass valve when projected in the axial direction. A discharge guide groove may be formed on at least one side of the inner side of the valve receiving groove and the inner side of the bypass valve facing it. Through this, manufacturing costs can be reduced by eliminating the valve guide that supports the axial movement of the bypass valve.

In the scroll compressor according to the present invention, a valve receiving groove that is recessed to a preset depth and accommodates a bypass hole is formed on the back of the non-orbiting scroll, and a bypass valve that opens and closes the bypass hole is installed in the axial direction in the valve receiving groove. Can be inserted smoothly. Through this, the bypass valve, which suppresses overcompression of the compression chamber, is not fastened to the non-swivel head plate, so the thickness of the non-swivel head plate can be made thin. As the thickness of the non-swivel head plate becomes thinner, the length of the bypass hole decreases. can be reduced, lowering the dead volume in the bypass hole.

In the scroll compressor according to the present invention, a discharge guide passage may be formed between the valve receiving groove and the bypass valve to communicate the bypass hole with the intermediate discharge port. Through this, even if the bypass valve is inserted into the valve receiving groove of the non-orbiting scroll, smooth communication can be achieved between the bypass hole and the intermediate discharge port when the bypass valve is opened.

In the scroll compressor according to the present invention, the bypass valve may be formed in a rectangular cross-sectional shape when projected in the axial direction. Through this, even if a plurality of bypass holes are formed, the plurality of bypass holes can be opened and closed at once with one bypass valve.

The scroll compressor according to the present invention may be provided with a valve guide extending along the axial direction between the bypass valve and the back pressure chamber assembly to support the bypass valve in the radial direction. Through this, it is possible to stably support the radial direction of the bypass valve that is inserted into the valve receiving groove and opens and closes the bypass hole while moving in the axial direction.

The scroll compressor according to the present invention may have a protrusion extending along the axial direction on one side of the outer peripheral surface of the bypass valve and the inner peripheral surface of the valve receiving groove facing it, and a groove into which the protrusion is inserted may extend along the axial direction on the other side. there is. Through this, the axial movement of the bypass valve can be stably supported without providing a separate valve guide outside the valve receiving groove.

In the scroll compressor according to the present invention, the valve receiving groove is formed to correspond to the cross-sectional shape of the bypass valve when projected in the axial direction, and at least one side of the inner surface of the valve receiving groove and the outer surface of the bypass valve facing it is provided. A discharge guide groove may be formed. Through this, manufacturing costs can be reduced by eliminating the valve guide that supports the axial movement of the bypass valve.

1 is a longitudinal cross-sectional view showing the interior of a variable capacity scroll compressor according to the present invention.
Figure 2 is an exploded perspective view of the compression part in Figure 1.
Figure 3 is an exploded perspective view showing the bypass valve in Figure 2 enlarged.
Figure 4 is a plan view showing the assembled bypass valve in Figure 2.
Figure 5 is a cross-sectional view taken along line "IX-IX" of Figure 4.
Figure 6 is a cross-sectional view taken along the line "Ⅹ-Ⅹ" of Figure 4.
Figures 7 and 8 are an exploded perspective view and an assembled cross-sectional view showing another embodiment of the valve guide in Figure 1.
Figures 9 and 10 are an exploded perspective view and an assembled cross-sectional view showing another embodiment of the valve guide in Figure 1.
Figure 11 is an exploded perspective view showing another embodiment of the valve receiving groove in Figure 1.
Figure 12 is a perspective view showing the assembled bypass valve and valve receiving groove in Figure 11.
Figure 13 is a plan view of Figure 12.
Figure 14 is a plan view showing another embodiment of the valve receiving groove in Figure 13.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

Typically, scroll compressors can be classified into open or closed types depending on whether the driving part (electrical part) and the compression part are installed together in the internal space of the casing. The former is a method in which the electric part forming the driving part is provided separately from the compression part, and the sealed type is a method in which the electric part forming the driving part is provided inside the same casing as the compression part. Hereinafter, a closed scroll compressor will be described as an example, but it is not necessarily limited to a closed scroll compressor. In other words, the present invention can be equally applied to an open scroll compressor in which the transmission part and the compression part are separated.

In addition, scroll compressors are classified into low-pressure compressors or high-pressure compressors depending on what kind of pressure section is formed in the internal space of the casing, especially the space that accommodates the rolling unit in a closed scroll compressor. In the former, the space forms a low-pressure section and the refrigerant suction pipe communicates with the space, and in the latter, the space forms a high-pressure section and the refrigerant suction pipe penetrates the casing and is directly connected to the compression section. This embodiment is explained using a low-pressure scroll compressor as an example. However, it is not limited to low-pressure scroll compressors.

Additionally, scroll compressors can be divided into a vertical scroll compressor whose rotation axis is arranged perpendicular to the ground and a horizontal scroll compressor whose rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side may be defined as facing away from the ground, and the lower side may be defined as facing toward the ground. Hereinafter, a vertical scroll compressor will be described as an example. However, it can be applied equally or similarly to a horizontal scroll compressor. Therefore, hereinafter, the axial direction is understood as the axial direction of the rotation axis, and the radial direction is understood as the radial direction of the rotation axis. The axial direction is understood as the up and down direction, the radial direction as the left and right sides, the inner peripheral surface as the top surface, and the axial radial direction as the side surfaces, respectively. It can be understood.

In addition, scroll compressors can be largely divided into tip seal type and back pressure type depending on the method of sealing between compression chambers. The back pressure method can be divided into a turning back pressure method that pressurizes the orbiting scroll toward the non-orbiting scroll, and, on the contrary, a non-orbiting back pressure method that presses the non-orbiting scroll toward the orbiting scroll. Hereinafter, a scroll compressor using a non-swivel back pressure method will be described as an example. However, the present invention can be applied not only to the rotating back pressure method but also to the tip seal method.

Figure 1 is a longitudinal cross-sectional view showing the inside of a variable capacity scroll compressor according to the present invention, and Figure 2 is an exploded perspective view of the compression part in Figure 1.

In the scroll compressor according to this embodiment, a drive motor 120 forming a transmission part is installed in the lower half of the casing 110, and a main frame 130, a turning scroll 140, and a main frame forming a compression part are installed on the upper side of the drive motor 120. A non-orbiting scroll 150, a back pressure chamber assembly 160, and a valve assembly 170 are installed. The transmission part is coupled to one end of the rotation shaft 125, and the compression part is coupled to the other end of the rotation shaft 125. Accordingly, the compression unit is connected to the transmission unit by the rotation shaft 125 and operates by the rotational force of the transmission unit.

Referring to FIG. 1, the casing 110 according to this embodiment includes a cylindrical shell 111, an upper cap 112, and a lower cap 113.

The cylindrical shell 111 has a cylindrical shape with openings at both upper and lower ends, and the above-described drive motor 120 and main frame 130 are inserted and fixed to the inner peripheral surface. A terminal bracket (not shown) is coupled to the upper half of the cylindrical shell 111. A terminal (not shown) for transmitting external power to the drive motor 120 is coupled through the terminal bracket. In addition, a refrigerant suction pipe 117, which will be described later, penetrates and is coupled to the upper half of the cylindrical shell 111, for example, the upper side of the drive motor 120.

The upper cap 112 is coupled to cover the open top of the cylindrical shell 111. The lower cap 113 is coupled to cover the opened lower end of the cylindrical shell 111. The rim of the high and low pressure separator plate 115, which will be described later, is inserted between the cylindrical shell 111 and the upper cap 112 and welded together with the cylindrical shell 111 and the upper cap 112. The rim of a support bracket 116, which will be described later, is inserted between the cylindrical shell 111 and the lower cap 113 and can be welded to the cylindrical shell 111 and the lower cap 113. Accordingly, the internal space of the casing 110 is sealed.

The edge of the high and low pressure separator plate 115 is welded to the casing 110 as described above. The central portion of the high and low pressure separator plate 115 is bent to protrude toward the upper side of the upper cap 112 and is disposed on the upper side of the back pressure chamber assembly 160, which will be described later. A refrigerant suction pipe 117 is connected to the lower side of the high-low pressure separator 115, and a refrigerant discharge pipe 118 is connected to the upper side of the high-low pressure separator plate 115. Accordingly, a low-pressure part 110a forming a suction space may be formed on the lower side of the high-low pressure separator 115, and a high-pressure part 110b forming a discharge space may be formed on the upper side.

Additionally, a through hole 115a is formed in the center of the high and low pressure separator plate 115. A sealing plate 1151, from which a floating plate 165, which will be described later, is removable, is inserted and coupled to the through hole 115a. The low-pressure section 110a and the high-pressure section 110b may be blocked by attaching or detaching the floating plate 165 and the sealing plate 1151, or may communicate through the high-low pressure communication hole 1151a of the sealing plate 1151.

In addition, the lower cap 113 forms an oil storage space 110c together with the lower half of the cylindrical shell 111 forming the low pressure portion 110a. In other words, the oil storage space 110c is formed in the lower half of the low pressure part 110a, and the oil storage space 110c forms a part of the low pressure part 110a.

Referring to FIG. 1, the drive motor 120 according to this embodiment is installed in the lower half of the low-pressure part 110a and includes a stator 121 and a rotor 122. The stator 121 is fixed to the inner wall of the cylindrical shell 111 by hot pressing, and the rotor 122 is rotatably provided inside the stator 121.

The stator 121 includes a stator core 1211 and a stator coil 1212.

The stator core 1211 is formed in a cylindrical shape and is fixed to the inner peripheral surface of the cylindrical shell 111 by hot pressing. The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source through a terminal (not shown) that is penetrated and coupled to the casing 110.

The rotor 122 includes a rotor core 1221 and a permanent magnet 1222.

The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the stator core 1211 at intervals equal to a predetermined gap. The permanent magnets 1222 are embedded inside the rotor core 1222 at preset intervals along the circumferential direction.

In addition, the rotation shaft 125 is press-fitted and coupled to the center of the rotor core 1221. An orbiting scroll 140, which will be described later, is eccentrically coupled to the upper end of the rotation shaft 125. Accordingly, the rotational force of the drive motor 120 can be transmitted to the orbiting scroll 140 through the rotation shaft 125.

An eccentric portion 1251 is formed at the top of the rotation shaft 125, which is eccentrically coupled to the orbiting scroll 140, which will be described later. An oil pickup 126 may be installed at the bottom of the rotating shaft 125 to absorb oil stored in the lower part of the casing 110. The rotation shaft 125 is formed with an oil passage 1252 penetrating therein in the axial direction.

Referring to FIG. 1, the main frame 130 according to this embodiment is installed on the upper side of the drive motor 120, and is fixed to the inner wall of the cylindrical shell 111 by hot pressing or welding.

The main frame 130 according to this embodiment includes a main flange portion 131, a main bearing portion 132, a pivoting space portion 133, a scroll support portion 134, an Oldham ring support portion 135, and a frame fixing portion 136. ) includes.

The main flange portion 131 is formed in an annular shape and is accommodated in the low pressure portion 110a of the casing 110. The outer diameter of the main flange portion 131 is smaller than the inner diameter of the cylindrical shell 111, so that the outer peripheral surface of the main flange portion 131 is spaced apart from the inner peripheral surface of the cylindrical shell 111. However, a frame fixing part 136, which will be described later, protrudes in the radial direction from the outer peripheral surface of the main flange part 131. The outer peripheral surface of the frame fixing part 136 is fixed in close contact with the inner peripheral surface of the casing 110. Accordingly, the frame 130 is fixedly coupled to the casing 110.

The main bearing portion 132 protrudes downward from the central lower surface of the main flange portion 131 toward the drive motor 120. The main bearing portion 132 has a cylindrical bearing hole 132a penetrating in the axial direction. A rotating shaft 125 is inserted into the inner peripheral surface of the bearing hole 132a and supported in the radial direction.

The pivoting space portion 133 is depressed from the center of the main flange portion 131 toward the main bearing portion 132 to a preset depth and outer diameter. The orbiting space portion 133 is formed to be larger than the outer diameter of the rotation shaft coupling portion 143 provided in the orbiting scroll 140, which will be described later. Accordingly, the rotation shaft coupling portion 143 can be rotatably accommodated within the pivot space portion 133.

The scroll support portion 134 is formed in an annular shape along the periphery of the pivot space portion 133 on the upper surface of the main flange portion 131. Accordingly, the scroll support part 134 can support the bottom surface of the turning plate part 141, which will be described later, in the axial direction.

The Oldham ring support portion 135 is formed in an annular shape along the outer peripheral surface of the scroll support portion 134 on the upper surface of the main flange portion 131. Accordingly, the Oldham ring 180 can be inserted into the Oldham ring support portion 135 and pivotably accommodated.

The frame fixing portion 136 extends radially from the outside of the Oldham ring support portion 135. The frame fixing portion 136 extends in an annular shape or as a plurality of protrusions spaced apart from each other by a predetermined distance along the circumferential direction. This embodiment shows an example in which the frame fixing portion 136 is formed of a plurality of protrusions along the circumferential direction.

Referring to FIG. 1, the orbiting scroll 140 according to this embodiment is coupled to the rotation shaft 125 and is provided between the main frame 130 and the non-orbiting scroll 150. An Oldham ring 180, an anti-rotation mechanism, is provided between the main frame 130 and the orbiting scroll 140. Accordingly, the rotating movement of the orbiting scroll 140 is restricted and the orbiting scroll 140 performs a rotating movement with respect to the non-orbiting scroll 150.

Specifically, the orbiting scroll 140 includes a pivoting plate portion 141, a pivoting wrap 142, and a rotating shaft engaging portion 143.

The pivot plate portion 141 is formed in a substantially disk shape. The outer diameter of the pivot plate portion 141 is supported in the axial direction by being placed on the scroll support portion 134 of the frame 130. Accordingly, the pivot plate portion 141 and the scroll support portion 134 facing it form an axial bearing surface (not denoted).

The orbiting wrap 142 is formed in a spiral shape by protruding at a preset height from the upper surface of the orbiting mirror plate portion 141 facing the non-orbiting scroll 150. The orbiting wrap 142 is formed to correspond to the non-orbiting wrap 152 of the non-orbiting scroll 150, which will be described later, so as to engage with the non-orbiting wrap 152 and perform a rotating movement. Accordingly, the orbiting wrap 142 forms a compression chamber (V) together with the non-swivel wrap 152.

The compression chamber (V) consists of a first compression chamber (V1) and a second compression chamber (V2) based on the turning wrap (142). The first compression chamber (V1) and the second compression chamber (V2) are formed sequentially as a suction pressure chamber (not symbol), an intermediate pressure chamber (not symbol), and a discharge pressure chamber (not symbol), respectively. Hereinafter, the compression chamber formed between the outer surface of the orbital wrap 142 and the inner surface of the non-swivel wrap 152 facing it is referred to as the first compression chamber V1, and the inner surface of the orbital wrap 142 and the inner surface of the non-swivel wrap 152 facing it are referred to as the first compression chamber V1. The description will be made by defining the compression chamber formed between the outer surfaces of the non-swivel wrap 152 as the second compression chamber V2.

The rotation shaft coupling portion 143 is formed to protrude from the lower surface of the pivot plate portion 141 toward the main frame 130. The rotation shaft coupling portion 143 is formed in a cylindrical shape so that a slew bearing (not shown) made of a bush bearing can be press-fitted.

Referring to FIG. 1, the non-orbiting scroll 150 according to this embodiment is disposed on the upper part of the main frame 130 with the orbiting scroll 140 interposed therebetween. The non-orbiting scroll 150 may be fixedly coupled to the main frame 130 or movably coupled to the main frame 130. This embodiment shows an example in which the non-orbiting scroll 150 is movably coupled to the main frame 130 in the axial direction.

The non-orbiting scroll 150 according to this embodiment includes a non-orbiting head plate portion 151, a non-orbiting wrap 152, a non-orbiting side wall portion 153, and a guide protrusion 154.

The non-swivel plate portion 151 is formed in a disk shape and is disposed laterally in the low pressure portion 110a of the casing 110. The non-swivel head plate portion 151 has a plurality of back pressure fastening grooves 151b formed along the edge. Accordingly, the fastening bolt 166 passing through the back pressure fastening hole 1611a of the back pressure plate 161, which will be described later, is fastened to the back pressure fastening groove 151b of the non-swivel head plate 151, The back pressure plate 161 may be bolted to the rear (upper surface) 151a.

A discharge port 1511, a bypass hole 1512, and a first back pressure hole 1513 are formed penetrating in the axial direction in the central portion of the non-swivel plate portion 151. The discharge port 1511 is formed at the center of the non-circulating mirror plate portion 151, the bypass hole 1512 is located on the outside and upstream of the discharge port 1511, and the first back pressure hole 1513 is located outside the bypass hole 1512. Each can be formed on the outside, upstream.

The discharge port 1511 is formed at a position where the discharge pressure chamber (not coded) of the first compression chamber (V1) and the discharge pressure chamber (not coded) of the second compression chamber (V2) communicate with each other. Accordingly, the refrigerant compressed in the first compression chamber (V1) and the refrigerant compressed in the second compression chamber (V2) are combined in the discharge pressure chamber and discharged to the high pressure portion (110b), which is the discharge space, through the discharge port (1511).

The bypass hole 1512 includes a first bypass hole 1512a and a second bypass hole 1512b. The first bypass hole 1512a and the second bypass hole 1512b may each be formed as a single hole or as a plurality of holes. This embodiment shows an example in which the first bypass hole 1512a and the second bypass hole 1512b are each formed as a plurality of holes. Accordingly, the area of the entire bypass hole 1512 can be expanded while being formed as a hole smaller than the wrap thickness of the orbiting wrap 142.

The first bypass hole 1512a communicates with the first compression chamber V1, and the second bypass hole 1512b communicates with the second compression chamber V2. The first bypass hole 1512a and the second bypass hole 1512b are formed on both sides of the discharge port 1511 along the circumferential direction with the discharge port 1511 at the center, that is, on the suction side of the discharge port 1511. . Accordingly, when the refrigerant compressed in each compression chamber (V1) (V2) is overcompressed, it is bypassed in advance before reaching the discharge port 1511, thereby suppressing overcompression.

Referring to Figures 1 and 2, the first bypass hole 1512a and the second bypass hole 1512b are accommodated in respective valve receiving grooves 155a and 155b, which will be described later. In other words, a first valve receiving groove 1712 and a second valve receiving groove 1722 that are recessed by a preset depth are formed on the rear surface 151a of the non-swivel plate portion 151, and the first valve receiving groove 1712 There is a first bypass hole (1512a) between the bottom surface of the first compression chamber (V1) and the top surface of the second compression chamber (V2), and a second bypass hole (1512a) is formed between the bottom surface of the second valve receiving groove (1722) and the top surface of the second compression chamber (V2). Bypass holes 1512b are formed respectively. Accordingly, each length of the first bypass hole (1512a) and the second bypass hole (1512b) is shortened by subtracting the depth of each valve receiving groove (1712) (1722) from the thickness of the non-turning hard plate portion (151). Thus, the dead body volume in the first bypass hole (1512a) and the second bypass hole (1512b) can be reduced. The valve receiving grooves 1712 and 1722 will be described later along with the bypass valves 1711 and 1721.

The first back pressure hole 1513 is formed by penetrating the non-swivel plate portion 151 in the axial direction and communicates with the compression chamber V having an intermediate pressure between the suction pressure and the discharge pressure. Only one first back pressure hole 1513 is formed and communicates with either the first compression chamber (V1) or the second compression chamber (V2), or a plurality of first back pressure holes 1513 are provided and connected to both compression chambers (V1) (V2). Each may be connected.

The non-swivel wrap 152 is formed by extending in the axial direction from the lower surface of the non-swivel head plate portion 151. The non-swivel wrap 152 is formed in a spiral shape inside the non-swivel side wall portion 153, and may be formed to correspond to the swirl wrap 142 so as to engage with the swirl wrap 142.

The non-swivel side wall portion 153 extends in the axial direction from the lower edge of the non-swivel hard plate portion 151 to surround the non-swivel wrap 152 and is formed in an annular shape. An intake port 1531 penetrating in the radial direction is formed on one side of the outer peripheral surface of the non-circulating side wall portion 153. Accordingly, the volume of the first compression chamber (V1) and the second compression chamber (V2) becomes narrower from the outer to the center, thereby compressing the sucked refrigerant.

The guide protrusion 154 may extend in the radial direction from the lower outer peripheral surface of the non-circulating side wall portion 153. The guide protrusion 154 may be formed in a single annular shape, or may be formed in plural pieces at predetermined intervals along the circumferential direction. This embodiment will be described focusing on an example in which a plurality of guide protrusions 154 are formed at preset intervals along the circumferential direction.

Referring to Figures 1 and 2, the back pressure chamber assembly 160 according to this embodiment is provided above the non-orbiting scroll 150. Accordingly, the back pressure of the back pressure chamber 160a (more precisely, the force that the back pressure exerts on the back pressure chamber) acts on the non-orbiting scroll 150. In other words, the non-orbiting scroll 150 is pressed in the direction toward the orbiting scroll 140 by back pressure to seal both compression chambers (V1) (V2).

Specifically, the back pressure chamber assembly 160 includes a back pressure plate 161 and a floating plate 165. The back pressure plate 161 is coupled to the upper surface of the non-swivel plate portion 151. The floating plate 165 is slidably coupled to the back pressure plate 161 to form a back pressure chamber 160a together with the back pressure plate 161.

The back pressure plate 161 includes a fixing plate portion 1611, a first annular wall portion 1612, and a second annular wall portion 1613.

The fixing plate portion 1611 is formed in the shape of an annular plate with an empty center. A plurality of back pressure fastening holes 1611a are formed along the edge of the fixing plate portion 1611. Accordingly, the fixing plate portion 1611 is bolted to the non-orbiting scroll 150 by a fastening bolt 166 passing through the back pressure fastening hole 1611a.

A plate-side back pressure hole (hereinafter referred to as a second back pressure hole) 1611b penetrates the fixing plate portion 1611 in the axial direction. The second back pressure hole 1611b communicates with the compression chamber V through the first back pressure hole 1513. Accordingly, the second back pressure hole 1611b, together with the first back pressure hole 1513, communicates between the compression chamber V and the back pressure chamber 160a.

A discharge guide groove 1611c, which will be described later, may be formed on the lower surface of the fixing plate portion 1611, that is, on the rear surface 161a of the back pressure plate 161 facing the rear surface 151a of the non-swivel plate portion 151. The discharge guide groove 1611c is formed in an annular shape to surround the middle discharge port 1612a, which will be described later, and may be formed so that the middle discharge port 1612a continuously communicates with the inner circumference of the discharge guide groove 1611c. Accordingly, the refrigerant flowing into the discharge guide groove (1611c) can quickly move to the high pressure section (110b) through the intermediate discharge port (1612a). The discharge guide groove 1611c will be described again later.

The first annular wall portion 1612 and the second annular wall portion 1613 surround the inner peripheral surface and the outer peripheral surface of the fixed plate portion 1611 on the upper surface of the fixed plate portion 1611. Accordingly, the outer peripheral surface of the first annular wall portion 1612, the inner peripheral surface of the second annular wall portion 1613, the upper surface of the fixing plate portion 1611, and the lower surface of the floating plate 165 form an annular back pressure chamber 160a. do.

An intermediate discharge port 1612a communicating with the discharge port 1511 of the non-orbiting scroll 150 is formed in the first annular wall portion 1612. A valve guide groove 1612b into which the discharge valve 155 is slidably inserted is formed inside the middle discharge port 1612a. A backflow prevention hole (1612c) is formed in the center of the valve guide groove (1612b). Accordingly, the discharge valve 155 selectively opens and closes between the discharge port 1511 and the intermediate discharge port 1612a to block the discharged refrigerant from flowing back into the compression chambers (V1) (V2).

The floating plate 165 is formed in a ring shape. The floating plate 165 may be made of a material lighter than the back pressure plate 161. Accordingly, the floating plate 165 moves in the axial direction with respect to the back pressure plate 161 according to the pressure of the back pressure chamber 160a and is attached to and detached from the lower side of the high and low pressure separator plate 115. For example, when the floating plate 165 comes into contact with the high-low pressure separator plate 115, it serves to seal the discharged refrigerant so that it is discharged to the high-pressure section 110b without leaking into the low-pressure section 110a.

The unexplained symbol 1551 in the drawing is an elastic member that supports the discharge valve.

The scroll compressor according to this embodiment as described above operates as follows.

That is, when power is applied to the drive motor 120 and rotational force is generated, the orbiting scroll 140 eccentrically coupled to the rotation shaft 125 makes a orbital movement with respect to the non-orbiting scroll 150 by the Oldham ring 180. do. At this time, a first compression chamber (V1) and a second compression chamber (V2) that move continuously are formed between the orbiting scroll 140 and the non-orbiting scroll 150. The first compression chamber (V1) and the second compression chamber (V2) move from the suction port (or suction chamber) 1531 toward the discharge port (or discharge chamber) 1511 while the orbiting scroll 140 rotates. As this happens, the volume gradually narrows.

Then, the refrigerant is sucked into the low pressure part 110a of the casing 110 through the refrigerant suction pipe 117, and a part of this refrigerant is sucked into each suction chamber forming the first compression chamber V1 and the second compression chamber V2. While it is sucked directly into the pressure chamber (not marked) and compressed, the remaining refrigerant moves toward the drive motor 120 to cool the drive motor 120, and then is sucked into the suction pressure chamber (not marked) along with other refrigerants.

Then, this refrigerant is compressed while moving along the movement path of the first compression chamber (V1) and the second compression chamber (V2), and a part of this compressed refrigerant reaches the discharge port 1511 before reaching the first back pressure hole ( 1513) and the second back pressure hole 1611b, it moves to the back pressure chamber 160a formed by the back pressure plate 161 and the floating plate 165. Accordingly, the back pressure chamber 160a forms intermediate pressure.

Then, the floating plate 165 rises toward the high-low pressure separator plate 115 and comes into close contact with the sealing plate 1151 provided on the high-low pressure separator plate 115. Accordingly, the high-pressure part 110b of the casing 110 is separated from the low-pressure part 110a to prevent the refrigerant discharged from each compression chamber (V1) (V2) to the high-pressure part 110b from flowing back into the low-pressure part 110a. It becomes possible.

On the other hand, the back pressure plate 161 is pressed down in the direction toward the non-orbiting scroll 150 by the pressure of the back pressure chamber 160a. Then, the non-orbiting scroll 150 is pressed toward the orbiting scroll 140. Accordingly, the non-orbiting scroll 150 is in close contact with the orbiting scroll 140, making it possible to block the refrigerant in both compression chambers (V1) and (V2) from leaking from the high-pressure side compression chamber, which forms the intermediate pressure chamber, to the low-pressure side compression chamber, respectively. .

Then, the refrigerant moves from the intermediate pressure chamber toward the discharge pressure chamber and is compressed to a set pressure. This refrigerant moves to the discharge port 1511 and pressurizes the discharge valve 155 in the opening direction. Then, the discharge valve 155 is pushed by the pressure of the discharge pressure chamber and rises along the valve guide groove 1612b, thereby opening the discharge port 1511. Then, the refrigerant in the discharge pressure chamber is discharged through the discharge port 1511, and this refrigerant is discharged to the high pressure section 110b through the intermediate discharge port 1612a provided in the back pressure plate 161.

Meanwhile, the pressure of the refrigerant may rise above the preset pressure due to various conditions that occur during operation of the compressor. Then, a portion of the refrigerant moving from the intermediate pressure chamber to the discharge pressure chamber forms each compression chamber (V1) (V2) through the first bypass hole (1512a) and the second bypass hole (1512b) before reaching the discharge pressure chamber. It is bypassed in advance from the intermediate pressure chamber toward the high pressure section 110b.

For example, when the pressure of the first compression chamber (V1) and the pressure of the second compression chamber (V2) are each higher than the set pressure, the refrigerant compressed in the first compression chamber (V1) is transmitted through the first bypass hole 1512a. ), the refrigerant in the second compression chamber (V2) moves to the second bypass hole (1512b). Then, the refrigerant moving to these bypass holes (1512a) (1512b) passes through the first bypass valve (1711) and the second bypass valve (1711) that blocks the first bypass hole (1512a) and the second bypass hole (1512b). The pass valve (1721) is pushed up. Then, the first bypass valve 1711 and the second bypass valve 1721 overcome the first valve spring 1713 and the second valve spring 1723, which will be described later, respectively, and the first valve guide 1714 and the second valve By being pushed and moved in the axial direction along the guide 1724, the first bypass hole 1512a and the second bypass hole 1512b are opened.

Then, the refrigerant in the first compression chamber (V1) passes through the first bypass hole (1512a), and the refrigerant in the second compression chamber (V2) passes through the second bypass hole (1512b) through the first valve receiving groove ( 1712) and the second valve receiving groove 1722, and this refrigerant moves to the middle discharge port 1612a of the back pressure plate 161 and is discharged to the high pressure part 110b. Accordingly, the refrigerant compressed in the compression chamber (V) is prevented from being overcompressed beyond the set pressure, thereby suppressing damage to the orbiting wrap 142 and/or the non-swirling wrap 152 and improving compressor efficiency.

Thereafter, when the overcompression of the compression chamber (V) is resolved and the appropriate pressure is restored, the first bypass valve 1711 and the second bypass valve 1721 are each pushed by the pressure of the high pressure part 110b. Then, a series of processes are repeated in which the first bypass valve 1711 blocks the first bypass hole 1512a and the second bypass valve 1721 blocks the second bypass hole 1512b.

At this time, high-pressure refrigerant that has not yet been discharged is trapped in the first bypass hole (1512a) and the second bypass hole (1512b). Then, the pressure in the compression chamber (V) increases unnecessarily, and the first bypass hole (1512a) and the second bypass hole (1512b) form a kind of dead volume. Therefore, the thickness of the non-turning hard plate portion 151 provided with the first bypass hole 1512a and the second bypass hole 1512b is formed as thin as possible to form the first bypass hole 1512a and the second bypass hole 1512b. It is advantageous to reduce the body volume by reducing the length of the hole 1512b.

However, when the bypass valve is fastened to the non-swivel head plate as in the prior art, a minimum fastening thickness is required to fasten the bypass valve, so there is a limit to reducing the thickness of the non-swivel head plate. Accordingly, in this embodiment, the bypass valve is formed as a piston valve (or lifting valve) to exclude the fastening structure of the bypass valve, thereby reducing the thickness of the non-swivel plate portion.

Figure 3 is an enlarged exploded perspective view of the bypass valve in Figure 2, Figure 4 is a plan view showing the bypass valve assembled in Figure 2, Figure 5 is a cross-sectional view "IX-IX" of Figure 4, and Figure 6 is a cross-sectional view taken along the line “Ⅹ-Ⅹ” in FIG. 4.

Referring again to FIGS. 1 and 2, the first valve receiving groove 1712 and the second valve receiving groove 1722 described above may be formed in the non-swivel plate portion 151 according to this embodiment. The first valve receiving groove 1712 is a portion into which the first bypass valve 1711 is inserted, and the second valve receiving groove 1722 is a portion into which the second bypass valve 1721 is slidably inserted in the axial direction. Accordingly, the first bypass hole 1512a can be opened and closed by the first bypass valve 1711, and the second bypass hole 1512b can be opened and closed by the second bypass valve 1721.

Referring to Figures 3 and 4, the first valve receiving groove 1712 is recessed by a preset depth from the rear surface 151a of the non-swivel plate portion 151 toward the first compression chamber V1, and the first valve A first bypass hole 1512a is formed through the bottom of the receiving groove 1712. Accordingly, the first valve receiving groove 1712 may communicate with the first compression chamber V1 through the first bypass hole 1512a.

In this case, a first valve buffering groove 1712a may be formed on the bottom surface of the first valve receiving groove 1712. For example, a first valve buffer groove (1712a) is formed on the rear surface (151a) of the non-swivel plate portion (151) forming the bottom surface of the first valve receiving groove (1712) to accommodate the first bypass hole (1512a). It can be. In other words, when projected in the axial direction, the cross-sectional area of the first valve cushioning groove 1712a may be formed to be larger than or equal to the cross-sectional area of the first bypass hole 1512a. Accordingly, a damping space accommodating a type of oil or refrigerant is formed around the outlet end of the first bypass hole 1512a, and when the first bypass valve 1711 is closed, the first bypass valve 1713 is used to It is possible to alleviate the pass valve 1711 from colliding strongly with the bottom surface of the first valve receiving groove 1712.

Referring to FIG. 4, the first valve receiving groove 1712 may be formed in various ways depending on the shape of the first bypass hole 1512a. As in this embodiment, when the first bypass hole 1512a is made of a plurality of holes (three in the drawing) spaced apart by a preset distance along the formation direction of the first compression chamber V1, the first valve is accommodated. The groove 1712 may be formed in an arcuate cross-section shape extending long along the formation direction of the first compression chamber (V1) to accommodate the plurality of holes at once.

Referring to Figure 4, the cross-sectional area of the first valve receiving groove 1712, for example, when projected in the axial direction, the cross-sectional area of the first valve receiving groove 1712 is formed to be almost the same as the cross-sectional area of the first bypass valve 1711. Or, it can be formed to be at least larger than the cross-sectional area of the first bypass valve 1711. Accordingly, the first bypass valve 1711 can open and close the first bypass hole 1512a while moving smoothly along the axial direction inside the first valve receiving groove 1712.

However, the first valve receiving groove 1712 is located between the first bypass hole 1512a and the intermediate discharge port 1612a to form a kind of connection passage, so the cross-sectional area of the first valve receiving groove 1712 is 1 It is preferable that the cross-sectional area of the bypass valve 1711 is larger than that of the bypass valve 1711.

For example, when the first valve receiving groove 1712 and the first bypass valve 1711 are formed in a rectangular shape, the major axis direction of the first valve receiving groove 1712 is that of the first bypass valve 1711. It can be formed to be longer than the major axis length. Accordingly, the inner peripheral surface in the long axis direction of the first valve receiving groove 1712 and the outer peripheral surface in the long axis direction of the first bypass valve 1711 facing it are spaced apart from each other, and the inner peripheral surface in the long axis direction of these first valve receiving grooves 1712 faces them. A first discharge guide passage 1715 may be formed between the outer peripheral surfaces of the first bypass valve 1711 in the long axis direction. Through this, the refrigerant discharged through the first bypass hole (1512a) can be discharged through the first discharge guide passage (1715), then move to the middle discharge port (1612a) and be discharged to the high pressure section.

In this case, a first valve spring 1713 and a first valve guide 1714 may be provided between the first bypass valve 1711 and the back pressure plate facing it. Accordingly, the first bypass valve 1711 is supported in the axial direction by the first valve spring 1713 inside the first valve receiving groove 1712 and at the same time is supported in the radial direction by the first valve guide 1714. It can be. Through this, the first bypass valve 1711 can quickly and stably open and close the first bypass hole 1512a while moving in the axial direction inside the first valve receiving groove 1712.

Referring to Figures 5 and 6, the first valve spring 1713 is made of a compression coil spring and can be inserted into the outer peripheral surface of the first valve guide 1714. For example, one end of the first valve spring 1713 is axially supported on the bottom surface of the first guide receiving groove 1716 provided in the first bypass valve 1711, and the end of the first valve spring 1713 The other end may be supported in the axial direction on the back surface 161a of the back pressure plate 161. Accordingly, the first valve spring 1713 can elastically support the first bypass valve 1711 toward the first bypass hole 1512a. Through this, when the first bypass hole 1512a is opened, the first bypass valve 1711 is suppressed from colliding with the back pressure plate 161, while when the first bypass hole 1512a is closed, the first bypass valve 1711 is prevented from colliding with the back pressure plate 161. 1 Bypass valve 1711 can quickly close the first bypass hole 1512a.

Referring to FIGS. 4 to 6, the first valve guide 1714 may extend long in the axial direction, for example, longer than the length of the first guide receiving groove 1716 provided in the first bypass valve 1711. You can. The first valve guide 1714 may be formed in a circular cross-section shape or an angular cross-section shape. This embodiment shows an example in which the first valve guide 1714 is formed in a circular cross-sectional shape.

Additionally, one end of the first valve guide 1714 may extend as a single piece from the back surface 161a of the back pressure plate 161, or may be press-fitted or fastened to extend. This embodiment shows an example in which one end of the first valve guide 1714 is press-fitted into the back surface 161a of the back pressure plate 161. For example, on the back surface 161a of the back pressure plate 161, a discharge guide groove 1611c is formed in an annular shape along the circumference of the middle discharge port 1612a, and a plurality of guide fixing grooves are formed inside the discharge guide groove 1611c ( 1611d) may be formed to be depressed in the axial direction. One end of the first valve guide 1714 may be press-fitted and fixed to one guide fixing groove 1611d among the plurality of guide fixing grooves. Accordingly, the first valve guide 1714 can minimize flow resistance while being located between the discharge port 1511 and/or the bypass holes 1512a and 1512b and the intermediate discharge port.

Additionally, the other end of the first valve guide 1714 extends in the axial direction and can be slidably inserted into the first guide receiving groove 1716. In this case, the inner diameter of the first guide receiving groove 1716 may be formed to be larger than the outer diameter of the first valve guide 1714. For example, the inner diameter of the first guide receiving groove 1716 may be larger than the outer diameter of the first valve spring 1713 inserted into the outer peripheral surface of the first valve guide 1714. Accordingly, the first bypass valve 1711 is supported in the radial direction by the first valve spring 1713 and the first valve guide 1714 and can move in the axial direction within the first valve receiving groove 1712. .

Referring to FIG. 3, the second bypass valve 1721 and the second valve receiving groove 1722, the second valve spring 1723 and the second bypass supporting the second bypass valve 1721 in the axial direction. The basic configuration and resulting effect of the second valve guide 1724, which supports the valve 1721 in the radial direction, is the same as the previously described first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714). Therefore, with respect to the second bypass valve 1721, the second valve spring 1723, and the second valve guide 1724, the first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714).

In the drawing, reference numeral 1722a is the second valve buffer groove, 1725 is the second discharge guide passage, and 1726 is the second guide receiving groove.

In this way, in this embodiment, the bypass valve is made of a piston valve (or lifting valve) that is slidably inserted into the valve receiving groove recessed in the non-swivel plate portion toward the compression chamber, so that the bypass hole is formed. The thickness of the head plate can be formed as thin as possible. Through this, the length of the bypass hole is reduced by the depth of the valve receiving groove, thereby minimizing the dead volume in these bypass holes and simultaneously minimizing the amount of refrigerant remaining in these bypass holes, thereby increasing the volumetric efficiency of the compressor.

In addition, although the bypass valve is made of a piston valve, a valve spring, which is an elastic member, is provided between the bypass valve and the back pressure plate, so that the bypass valve closes when closed, which reduces the valve noise generated when the bypass valve is opened. By increasing the speed, it is possible to prevent the refrigerant from flowing back into the compression chamber.

In addition, as a valve guide is provided between the bypass valve and the back pressure plate, a wide discharge guide passage is secured between the bypass valve and the valve receiving groove, so that the refrigerant in the compression chamber is quickly bypassed when overcompressed, improving compression efficiency. The axial behavior of the bypass valve can be stabilized.

Meanwhile, other examples of valve guides are as follows.

That is, in the above-described embodiment, the valve guide extends from the back pressure plate toward the bypass valve, but in some cases, the valve guide may extend from the bypass valve toward the back pressure plate.

Figures 7 and 8 are an exploded perspective view and an assembled cross-sectional view showing another embodiment of the valve guide in Figure 1.

Referring to FIGS. 7 and 8, the first bypass valve 1711 according to this embodiment has a first valve guide 1714 extending from the upper surface facing the back pressure plate 161 toward the back pressure plate 161. It can be. The first valve guide 1714 may be formed in a circular cross-section shape or an angular cross-section shape. Additionally, the first valve guide 1714 may extend from the first bypass valve 1711 with the same cross-sectional area. This embodiment shows an example in which the first valve guide 1714 is formed in a circular cross-sectional shape.

In this case, a first guide receiving groove 1716 is formed on the back surface 161a of the back pressure plate 161 facing the first bypass valve 1711 in the axial direction so that the first valve guide 1714 can be slidably inserted. It can be. For example, the first guide receiving groove 1716 may be formed to be depressed by a preset depth from the back surface 161a of the back pressure plate 161 toward the back pressure chamber 160a.

Even in these cases, the first valve spring 1713 described above may be provided between the upper surface of the first bypass valve 1711 and the rear surface 161a of the back pressure plate 161 facing it. This will be replaced with a description of the embodiment of FIG. 3.

Meanwhile, in this embodiment as well, the second bypass valve 1721 and the second valve receiving groove 1722, the second valve spring 1723 and the second bypass supporting the second bypass valve 1721 in the axial direction. The basic configuration and resulting effect of the second valve guide 1724, which supports the valve 1721 in the radial direction, is the same as the previously described first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714). Therefore, with respect to the second bypass valve 1721, the second valve spring 1723, and the second valve guide 1724, the first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714).

When the valve guides 1714 and 1724 are provided in each bypass valve 1711 and 1721 as described above, the valve guides 1714 and 1724 can be easily formed. In other words, the shape of the back surface 161a of the back pressure plate 161 is complex, so it may not be easy to machine the valve guide into a single piece on the back pressure plate 161. On the other hand, the upper surfaces of the bypass valves 1711 and 1721 may be formed relatively simply compared to the rear surface 161a of the back pressure plate 161. Therefore, it may be relatively easy to form the valve guides 1714 and 1724 into the bypass valves 1711 and 1721 as a single piece. Accordingly, the manufacturing cost can be lowered by reducing the assembly man-hours for the valve guides 1714 and 1724.

Meanwhile, although not shown in the drawings, it may be formed by mixing the embodiment of FIG. 3 and the embodiment of FIG. 7. For example, the first valve guide 1714 may be provided on the rear surface 161a of the back pressure plate 161, and the second valve guide 1724 may be provided on the upper surface of the second bypass valve 1721, and vice versa. It may also be possible. This can be selected in various ways depending on the shape of the rear surface 151a of the non-swivel plate portion 151 and the rear surface 161a of the back pressure plate 161.

Meanwhile, another example of the valve guide is as follows.

That is, in the above-described embodiments, the valve guide extends from the back pressure plate toward the bypass valve, but in some cases, the valve guide may be formed on the outer peripheral surface of the bypass valve and the inner peripheral surface of the valve receiving groove facing it.

Figures 9 and 10 are an exploded perspective view and an assembled cross-sectional view showing another embodiment of the valve guide in Figure 1.

Referring to Figures 9 and 10, the basic shape and resulting effect of the first bypass valve 1711 and the first valve receiving groove 1712 according to this embodiment are similar to the above-described embodiments. Therefore, the shape of the first bypass valve 1711 and the first valve receiving groove 1712 and the resulting effects will be replaced with descriptions of the above-described embodiments.

However, in this embodiment, the first valve guide 1714 is formed between the first bypass valve 1711 and the first valve receiving groove 1712. Accordingly, in this embodiment, the first valve guide 1714 can be easily formed, thereby reducing manufacturing costs.

For example, in this embodiment, a preset height is set toward the inner peripheral surface of the first valve receiving groove 1712 on both sides of the first valve guide 1714, specifically, on both sides in the short axis direction of the first valve guide 1714. The first guide protrusion (1714a) protruding by the amount is formed to extend in the axial direction, and the first guide protrusion (1714a) slides on the inner peripheral surface of the first valve receiving groove (1712) facing the first guide protrusion (1714a). The inserted first guide groove 1714b may be formed to extend in the axial direction.

Although not shown in the drawing, the first guide protrusion 1714a may not extend in the axial direction but may be formed in a rod shape like a hinge. In this case as well, the first guide groove 1714b may extend along the axial direction by the opening/closing length of the first bypass valve 1711.

Also, in this embodiment, a first valve spring 1713 may be provided between the upper surface of the first bypass valve 1711 and the rear surface 161a of the back pressure plate 161. The first valve spring 1713 is made of a compression coil spring as in the above-described embodiments, and both ends are provided on the upper surface of the first bypass valve 1711 and the rear surface 161a of the back pressure plate 161 facing it, respectively. It can be fixed to the spring fixing part (not marked).

Meanwhile, in this embodiment as well, the second bypass valve 1721 and the second valve receiving groove 1722, the second valve spring 1723 and the second bypass supporting the second bypass valve 1721 in the axial direction. The basic configuration and resulting effect of the second valve guide 1724, which supports the valve 1721 in the radial direction, is the same as the previously described first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714). Therefore, with respect to the second bypass valve 1721, the second valve spring 1723, and the second valve guide 1724, the first bypass valve 1711, the first valve spring 1713, and the first valve guide ( 1714).

However, in this embodiment, the valve guides 1714 and 1724 are formed between the bypass valves 1711 and 1721 and the valve receiving grooves 1712 and 1722, so that the guide is fixed in the embodiment of FIG. 3 described above. The groove 1611d can be used as a spring fixing groove 1611d' in this embodiment, and the guide receiving grooves 1716 and 1726 can be used as spring receiving grooves 1716' and 1726' in this embodiment. These spring fixing grooves (1611d') and spring receiving grooves (1716') (1726') are explained instead of the guide fixing groove (1611d) and guide receiving grooves (1716) (1726) in the above-described embodiments. do.

As described above, when the valve guides (1714) (1724) are formed in each of the bypass valves (1711) (1721) and the valve receiving grooves (1712) (1722), each bypass valve is not provided without a separate valve guide. It can be formed together with valves 1711 and 1721 and valve receiving grooves 1712 and 1722. Accordingly, the manufacturing cost can be further reduced by reducing the assembly time for the valve guide.

Meanwhile, other examples of the valve receiving groove are as follows.

That is, in the above-described embodiments, the cross-sectional shape of the valve receiving groove is formed to correspond to the cross-sectional shape of the bypass valve, but in some cases, the cross-sectional shape of the valve receiving groove may be formed to be different from the cross-sectional shape of the bypass valve. It may be possible.

FIG. 11 is an exploded perspective view showing another embodiment of the valve receiving groove in FIG. 1, FIG. 12 is a perspective view showing the bypass valve and the valve receiving groove assembled in FIG. 11, FIG. 13 is a plan view of FIG. 12, and FIG. 14 is a plan view showing another embodiment of the valve receiving groove in FIG. 13.

Referring to Figures 11 to 13, the first valve receiving groove 1712 according to this embodiment is formed in a rectangular shape along the formation direction of the first compression chamber (V1), and both ends in the long axis direction are connected to the first bypass valve ( 1711) and can be formed in a different cross-sectional shape. For example, the central portion of the first valve receiving groove 1712 is formed to have a shape almost identical to the cross-sectional shape of the first bypass valve 1711, while both ends of the first valve receiving groove 1712 in the long axis direction are formed with a first bypass valve 1711. It may be formed in a cross-sectional shape different from that of the pass valve 1711. Accordingly, a first valve guide portion 1717 into which the first bypass valve 1711 is slidably inserted is formed in the central portion of the first valve receiving groove 1712, and at least one of both sides of the first valve guide portion 1717 is formed. A first discharge guide passage 1718 may be formed on one side.

Specifically, the first valve guide 1717 is formed to have a substantially rectangular cross-sectional shape, and the minor axis width of the first valve guide 1717 is formed to be substantially equal to the minor axis width of the first bypass valve 1711. It can be. Accordingly, the first bypass valve 1711 is almost in sliding contact with the first valve guide 1717 and the minor axis direction of the first bypass valve 1711 can be supported in the radial direction.

In addition, the first discharge guide passage 1718 may be formed to have a semicircular cross-sectional shape, and the diameter of the first discharge guide passage 1718 may be formed to be substantially equal to the minor axis width of the first bypass valve 1711. there is. In other words, the first discharge guide passage 1718 may be formed to be smaller than the width of the first bypass valve 1711 in the minor axis as it becomes farther away from the first bypass valve 1711 in the major axis direction. Accordingly, the first valve receiving groove 1712 is spaced apart from both ends of the first bypass valve 1711 to form the first discharge guide passage portion 1718 and extends in the radial direction of the long axis of the first bypass valve 1711. can be supported.

In this case as well, the first valve spring 1713 described above may be provided between the first bypass valve 1711 and the back pressure plate 161. This will be replaced with a description of the embodiment of FIG. 3.

Meanwhile, in the present embodiments as well, the basic configuration and effect of the second bypass valve 1721 and the second valve spring 1723 supporting the second bypass valve 1721 in the axial direction are as described above. 1 It is the same as the bypass valve 1711 and the first valve spring 1713. Therefore, the description of the second bypass valve 1721 and the second valve spring 1723 will be replaced with the description of the first bypass valve 1711 and the first valve spring 1713.

However, since the valve guide is excluded in this embodiment, the guide fixing groove 1611d in the embodiment of FIG. 3 is replaced with a spring fixing groove 1611d' in this embodiment, and the guide receiving grooves 1716 and 1726 are replaced with the spring fixing groove 1611d' in this embodiment. In the embodiment, each can be used as a spring receiving groove (1716') (1726'). These spring fixing grooves (1611d') and spring receiving grooves (1716') (1726') are explained instead of the guide fixing groove (1611d) and guide receiving grooves (1716) (1726) in the above-described embodiments. do.

In the drawing, reference numeral 1727 is the second valve guide portion, and 1728 is the second discharge guide passage portion.

As described above, the valve receiving grooves (1712) (1722) are formed larger than the bypass valves (1711) (1721), and both ends of the valve receiving grooves (1712) (1722) are narrower than the bypass valves (1711) (1721). When formed, the bypass valves 1711 and 1721 can operate stably inside the valve receiving grooves 1712 and 1722 without a separate valve guide. Accordingly, the valve guide can be removed, thereby lowering manufacturing costs.

Meanwhile, in the above-described embodiments, the discharge guide passage is formed in the valve receiving groove, but in some cases, the discharge guide passage may be formed in the bypass valve.

Figure 14 is an assembly plan view showing another embodiment of the discharge guide passage in Figure 13.

Referring to FIG. 14, the first valve receiving groove 1712 according to this embodiment is formed in a rectangular shape along the formation direction of the first compression chamber (V1), and has the same cross-sectional shape as the first bypass valve 1711. can be formed. Accordingly, the first bypass valve 1711 can be supported in the radial direction by the first valve receiving groove 1712 in both the major and minor directions.

However, in this embodiment, the first discharge guide passage 1715 is formed between both sides in the long axis direction of the first bypass valve 1711 and both sides in the long axis direction of the first valve receiving groove 1712 facing it, The first discharge guide passage 1715 may be formed to be recessed on both sides of the first bypass valve 1711 in the long axis direction. In this case, the same applies to the second bypass valve 1721, the second valve receiving groove 1722, and the second discharge guide passage 1725.

As described above, the valve receiving grooves (1712) (1722) are formed in the same cross-sectional shape as the bypass valves (1711) (1721), and discharge guide passages (1715) are formed on both sides of the bypass valves (1711) (1721). In the case of forming 1725), the bypass valves 1711 and 1721 can operate stably inside the valve receiving grooves 1712 and 1722 without a separate valve guide. Accordingly, in this case as well, the valve guide can be removed, thereby lowering the manufacturing cost.

As described above, the embodiments of the valve assembly of the present invention can be applied equally to open as well as closed types, can be applied equally to low-pressure as well as high-pressure types, and can be equally applied to vertical as well as horizontal types. In addition, it can be equally applied to the non-swivel back pressure method as well as the swirl back pressure method or tip seal method. In particular, in the orbiting back pressure method or the tip seal method, a separate plate is fixed to the back surface 151a of the non-orbiting scroll (fixed scroll) instead of the back pressure chamber assembly provided in the non-orbiting back pressure method, and the plate is used in the above-described embodiment. The valve assembly can be fixed. Even in these embodiments, the basic configuration of the valve assembly and its operational effects may be almost the same as the above-described embodiments.

110: Casing 110a: Low pressure part (suction space)
110b: High pressure part (discharge space) 110c: Oil storage space
111: cylindrical shell 112: upper cap
113: lower cap 115: high and low pressure separator plate
115a: Through hole 116: Support bracket
117: Refrigerant suction pipe 118: Refrigerant discharge pipe
120: Drive motor 121: Stator
1211: stator core 1212: stator coil
122: rotor 1221: rotor core
1222: permanent magnet 125: rotation axis
1251: Eccentric part 1252: Oil passage
126: Oil pickup 130: Main frame
131: main flange part 132: main bearing part
133: orbiting space 134: scroll support
135: Oldham ring receiving part 136: Frame fixing part
140: Swivel scroll 141: Swivel hard plate part
142: Swivel wrap 143: Rotation shaft coupling part
150: Non-orbiting scroll 151: Non-orbiting hard plate part
151a: Back of non-swivel plate portion 151b: Back pressure fastening groove
1511: discharge port 1512: bypass hole
1512a: first bypass hole 1512b: second bypass hole
1513: First back pressure hole 1514: Guide fastening groove
152: Non-swivel lap 153: Non-swivel side wall portion
1531: Inlet 154: Guide protrusion
155: Discharge valve 160: Back pressure chamber assembly
160a: Back pressure chamber 161: Back pressure plate
161a: Back side of back pressure plate 1611: Fixed plate portion
1611a: Back pressure fastening hole 1611b: Second pressure hole
1611c: Discharge guide groove 1611d: Guide fixing groove
1612: First annular wall portion 1612a: Middle discharge port
1612b: Valve guide groove 1612c: Backflow prevention hole
1613: Second annular wall 165: Floating plate
166: Fastening bolt 1711: First bypass valve
1712: First valve receiving groove 1712a: First valve buffering groove
1713: first valve spring 1714: first valve guide
1714a: First guide projection 1714b: First guide groove
1715: First discharge guide passage 1716: First guide receiving groove
1717: first valve guide part 1718: first discharge guide passage part
1721: Second bypass valve 1722: Second valve receiving groove
1722a: Second valve buffer groove 1723: Second valve spring
1724: Second valve guide 1724a: Second guide projection
1724b: Second guide groove 1725: Second discharge guide passage
1726: Second guide receiving groove 1727: Second valve guide part
1728: Second discharge guide passage V, V1, V2: Compression chamber

Claims (14)

casing;
A turning scroll is provided with a turning wrap and makes a turning movement in the inner space of the casing;
A non-orbiting scroll is provided with a non-orbiting wrap to engage the orbiting wrap to form a compression chamber, and is provided with a bypass hole to discharge the refrigerant of the compression chamber into the inner space of the casing; and
It includes a back pressure chamber assembly coupled to the back of the non-orbiting scroll to press the non-orbiting scroll toward the orbiting scroll,
A valve receiving groove that is recessed to a preset depth and accommodates the bypass hole is formed on the rear surface of the non-orbiting scroll, and a bypass valve that opens and closes the bypass hole is slidably inserted in the axial direction into the valve receiving groove. Scroll compressor. According to paragraph 1,
An intermediate discharge port communicating with the internal space of the casing is formed in the back pressure chamber assembly,
Between the valve receiving groove and the bypass valve,
A scroll compressor in which a discharge guide passage is formed to communicate the bypass hole with the intermediate discharge port. According to paragraph 2,
The cross-sectional shape of the valve receiving groove is formed to correspond to the cross-sectional shape of the bypass valve,
The discharge guide passage is,
A scroll compressor formed to be depressed by a preset depth on at least one side of the inner peripheral surface of the valve receiving groove or the outer peripheral surface of the bypass valve facing it. According to paragraph 2,
The cross-sectional shape of the valve receiving groove is formed differently from the cross-sectional shape of the bypass valve,
The axial cross-sectional area of the valve receiving groove is,
A scroll compressor formed to be larger than the axial cross-sectional area of the bypass valve. According to paragraph 1,
The bypass valve is a scroll compressor formed in a rectangular cross-sectional shape when projected in the axial direction. According to clause 5,
A scroll compressor in which a discharge guide groove is formed on at least one side of the long-axis side of the valve receiving groove and the long-axis side of the bypass valve facing it. According to clause 6,
A valve buffering groove is formed on the rear surface of the non-orbiting scroll forming the bottom surface of the valve receiving groove, and the cross-sectional area of the valve buffering groove is formed to be smaller than the cross-sectional area of the bypass valve,
The valve cushioning groove is,
A scroll compressor selectively communicated by the discharge guide groove and the bypass valve. According to clause 5,
A scroll compressor wherein a plurality of bypass holes are formed along the formation direction of the non-swivel wrap, and the plurality of bypass holes are accommodated in one of the valve receiving grooves. According to clause 8,
A valve cushioning groove is formed on the back of the non-orbiting scroll, which forms the bottom surface of the valve receiving groove,
A scroll compressor in which the cross-sectional area of the valve buffer groove is formed to be smaller than the cross-sectional area of the bypass valve. According to any one of claims 1 to 9,
A scroll compressor wherein a valve guide is provided between the bypass valve and the back pressure chamber assembly and extends along the axial direction to support the bypass valve in the radial direction. According to clause 10,
One end of the valve guide is fixed to the bypass valve or the back pressure chamber assembly,
A scroll compressor wherein the other end of the valve guide is slidably inserted along the axial direction into a guide receiving groove provided in the back pressure chamber assembly or bypass valve. According to clause 11,
A valve spring is provided between the bypass valve and the back pressure chamber assembly to press the bypass valve toward the non-orbiting scroll,
The valve spring is,
A scroll compressor consisting of a compression coil spring and inserted into the valve guide. According to any one of claims 1 to 9,
A scroll compressor in which a protrusion extends along the axial direction on one side of the outer peripheral surface of the bypass valve and the inner peripheral surface of the valve receiving groove facing the bypass valve, and a groove into which the protrusion is inserted extends along the axial direction on the other side. According to any one of claims 1 to 9,
The valve receiving groove is formed to correspond to the cross-sectional shape of the bypass valve when projected in the axial direction,
A scroll compressor in which a discharge guide groove is formed on at least one side of the long-axis side of the valve receiving groove and the long-axis side of the bypass valve facing it.

Images