KR102919829B1 - Scroll compressor - Google Patents

Abstract

A scroll compressor according to the present invention has a back pressure passage communicating between a compression chamber and a back pressure chamber to guide a portion of refrigerant compressed in the compression chamber to the back pressure chamber, wherein the back pressure passage may include a scroll back pressure hole and a communication portion. The scroll back pressure hole may extend from one side of a non-orbiting plate portion facing the back pressure chamber assembly toward a front end surface of a non-orbiting wrap axially facing the orbiting plate portion. The communication portion may extend from one side of the non-orbiting wrap toward the scroll back pressure hole and communicate with the scroll back pressure hole. Through this, the compression chamber and the back pressure chamber can always be communicated through the communication portion, so that the pressure in the back pressure chamber can quickly vary in accordance with the pressure in the compression chamber, and pressure pulsation in the back pressure chamber can be minimized.

Description

Scroll Compressor{SCROLL COMPRESSOR}

The present invention relates to a scroll compressor, and more particularly to a back pressure passage of a scroll compressor.

Scroll compressors consist of a fixed (or non-orbiting) scroll and an orbiting scroll, which interlock to form a pair of compression chambers. These scroll compressors have fewer components and can operate at high speeds, as suction, compression, and discharge occur continuously while the orbiting scroll rotates. Furthermore, because the torque required for compression is minimally variable, and suction and compression occur continuously, noise and vibration are minimal. These characteristics have led to the widespread use of scroll compressors in air conditioners.

In these scroll compressors, to ensure smooth compression, it is necessary to prevent leakage between the non-orbiting scroll and the orbiting scroll. To prevent leakage, the non-orbiting scroll's non-orbiting wrap must be in close contact with the opposing orbiting scroll's plate, and the orbiting scroll's plate must be in close contact with the opposing non-orbiting scroll's plate. However, if the wrap and plate are in excessive contact, friction increases, leading to wear-related damage and reduced efficiency.

To address these issues, a back pressure chamber is formed on the back surface of the plate section of either the non-orbiting scroll or the orbiting scroll, communicating with the compression chamber. During the compression process, a portion of the working fluid compressed within the compression chamber is supplied to the back pressure chamber, pressurizing the back surface of the plate section forming the back pressure chamber. Consequently, the non-orbiting scroll and the orbiting scroll are in close contact with each other, preventing excessive friction while preventing leakage.

Patent Document 1 (Korean Patent No. 10-1290005) discloses an example of a scroll compressor having a back pressure chamber. The scroll compressor of Patent Document 1 has a back pressure chamber formed on the back surface of the plate portion of the orbiting scroll, i.e., on the bottom surface of the orbiting scroll, and the compression chamber and the back pressure chamber are connected through a back pressure passage formed through the wrap of the orbiting scroll. A scroll compressor having a back pressure chamber formed on the bottom surface of the orbiting scroll in this way is called an orbiting back pressure scroll compressor.

Patent Document 2 (Korean Patent Publication No. 10-2016-0000321) discloses another example of a scroll compressor having a back pressure chamber. The scroll compressor of Patent Document 2 has the back pressure chamber located on the back surface of the non-orbiting scroll, i.e., on the upper surface of the non-orbiting scroll. To distinguish it from a rotating back pressure scroll compressor, this type of scroll compressor is called a fixed back pressure scroll compressor. In the scroll compressor of Patent Document 2, the compression chamber and the back pressure chamber are connected through a back pressure passage formed in the plate portion of the non-orbiting scroll.

However, the rotary back-pressure scroll compressor of Patent Document 1 has the difficulty of having to consider the movement of the rotary scroll to prevent leakage of the back-pressure chamber.

In contrast, the fixed-back pressure scroll compressor of Patent Document 2 has an advantage over the orbiting back pressure type in forming a structure to prevent leakage of the back pressure chamber because only the axial linear motion of the non-orbiting scroll needs to be considered.

However, fixed-back pressure scroll compressors such as Patent Document 2 are not without problems. That is, in the scroll compressor of Patent Document 2, a back pressure passage connecting the compression chamber and the back pressure chamber is formed by penetrating the plate portion of the non-orbiting scroll, so that the wrap end of the orbiting scroll that rotates repeatedly opens and closes this back pressure passage, thereby generating back pressure.

According to this back pressure formation structure, when the pressure in the back pressure chamber is lower than the pressure in the compression chamber connected through the back pressure passage, normal back pressure formation is possible through pressure transfer from the compression chamber to the back pressure chamber. However, when the pressure in the back pressure chamber is higher than the pressure in the compression chamber, the pressure in the back pressure chamber actually transfers to the compression chamber, which causes pressure pulsation in the back pressure chamber to increase during compressor operation. This pressure pulsation in the back pressure chamber causes the pressure in the compression chamber to abnormally increase, which causes recompression loss and thus a decrease in compressor efficiency.

To address these issues, for example, in the scroll compressor of Patent Document 2, the diameter of the back pressure passage provided in the plate portion of the non-orbiting scroll is made as small as possible. This suppresses the movement of refrigerant from the back pressure chamber to the compression chamber through the back pressure passage, thereby minimizing the pressure in the back pressure chamber from moving to the compression chamber.

However, there are limits to reducing the diameter of the pressure passage due to processing and cost issues.

In another example, a valve is provided in the back pressure passage to prevent the movement of refrigerant from the back pressure chamber to the compression chamber, or a structure is adopted to bypass the refrigerant in the back pressure chamber to the compression chamber when the pressure in the back pressure chamber exceeds a preset value.

These methods have the problem of complicating the structure of the scroll compressor and increasing the manufacturing cost.

Republic of Korea Patent No. 10-1290005 (Announcement date: July 30, 2013) Republic of Korea Patent Publication No. 10-2016-0000321 (Published: January 4, 2016)

The purpose of the present invention is to provide a fixed back pressure scroll compressor capable of minimizing pressure pulsation in a back pressure chamber.

Another object of the present invention is to provide a fixed back pressure scroll compressor having a simple structure and capable of minimizing the pressure in the back pressure chamber from moving to the compression chamber.

Another object of the present invention is to provide a fixed back pressure scroll compressor in which the back pressure passage can be easily processed.

In order to achieve the object of the present invention, a scroll compressor including a casing, an orbiting scroll, a non-orbiting scroll, a back pressure chamber assembly, and a back pressure passage may be provided. The casing may have a sealed internal space that may be separated into a low pressure portion and a high pressure portion. The orbiting scroll may be coupled to a rotating shaft in the internal space of the casing to orbit, and may have an orbiting wrap provided on one side of an orbiting plate portion. The non-orbiting scroll may have a non-orbiting wrap provided on one side of a non-orbiting plate portion facing the orbiting plate portion so as to form a compression chamber by engaging the orbiting wrap. The back pressure chamber assembly may be provided on a back surface of the non-orbiting scroll to form a back pressure chamber. The back pressure passage may communicate between the compression chamber and the back pressure chamber to guide a portion of the refrigerant compressed in the compression chamber to the back pressure chamber. The back pressure passage may include a scroll back pressure hole and a communication portion. The above scroll pressure hole may extend from one side of the non-rotating plate portion facing the pressure chamber assembly toward the front end surface of the non-rotating wrap axially facing the rotating plate portion. The communication portion may extend from one side of the non-rotating wrap toward the scroll pressure hole and communicate with the scroll pressure hole.

Accordingly, the compression chamber and the back pressure chamber can be constantly connected through the connecting member. Accordingly, the pressure in the back pressure chamber can be quickly varied in accordance with the pressure in the compression chamber.

Meanwhile, when the pressure in the back pressure chamber rises to an appropriate intermediate pressure, the pressure difference between the compression chamber and the back pressure chamber is not large, so it is difficult for the pressure in the compression chamber to move to the back pressure chamber through the communication part, thereby preventing the pressure in the back pressure chamber from rising excessively.

Conversely, even if the pressure in the back pressure chamber is higher than the pressure in the compression chamber, it is difficult for the pressure in the back pressure chamber to move to the compression chamber through the connecting member.

In this way, unless there is a significant difference in pressure between the compression chamber and the back pressure chamber, such as when the compressor is operating, it is not easy for pressure to transfer between the compression chamber and the back pressure chamber through the connecting member of the present invention. Accordingly, pressure pulsation in the back pressure chamber can be minimized.

For example, the scroll pressure hole may be formed by penetrating the leading edge of the non-rotating wrap on one side of the non-rotating plate portion, and the communication portion may be formed by recessing a predetermined depth into the leading edge of the non-rotating wrap facing the rotating plate portion. Accordingly, without the processing and cost problems caused by forming the diameter of the back pressure passage smaller as in the past, the pressure in the back pressure chamber can be minimized from moving to the compression chamber with a simple configuration by simply cutting the leading edge of the non-rotating wrap to a predetermined depth.

For example, the circumferential width of the communication portion may be formed to be greater than or equal to the inner diameter of the scroll back pressure hole. If the circumferential width of the communication portion is formed to be equal to the inner diameter of the scroll back pressure hole, the processing work of the communication portion may be easier. If the circumferential width of the communication portion is formed to be greater than the inner diameter of the scroll back pressure hole, the friction area of the refrigerant passing through the communication portion against the wall of the communication portion may increase, so that the depth of the communication portion may be formed to be lower for the same refrigerant flow rate.

For example, the circumferential width of the above-mentioned connecting portion may be formed to be the same toward one side of the non-rotating wrap. Accordingly, the reduction in the cross-sectional area of the non-rotating wrap due to the formation of the connecting portion may be reduced, thereby making the seal between the compression chambers located on both sides of the non-rotating wrap more secure.

As another example, the circumferential width of the above-described connecting portion may be formed to increase toward one side of the above-described non-rotating wrap. Accordingly, when the compressor is started, the flow rate of refrigerant flowing from the compression chamber into the scroll back pressure passage through the connecting portion may increase, thereby allowing the pressure in the back pressure chamber to more quickly adjust to the pressure in the pressure chamber.

For example, the above-mentioned connecting portion may be formed such that its axial depth is smaller than its circumferential width. Consequently, the passage through which the refrigerant passes becomes narrow, making it difficult for pressure to transfer between the compression chamber and the back pressure chamber through the connecting portion. Consequently, pressure pulsation in the back pressure chamber can be minimized.

For example, the scroll back pressure hole may be formed by penetrating the leading edge of the non-orbiting wrap on one side of the non-orbiting plate portion or by being sunken to a preset depth, and the communication portion may be formed by penetrating toward the scroll back pressure hole on one side of the non-orbiting wrap facing one side of the orbiting wrap. Accordingly, when the compressor is in operation, the entire leading edge of the non-orbiting wrap can be brought into close contact with the non-orbiting plate portion, so that the seal between the compression chambers located on both sides of the non-orbiting wrap can be firmly maintained.

For example, the circumferential width of the above-mentioned connecting portion may be formed to be greater than or equal to the inner diameter of the above-mentioned scroll pressure hole. Accordingly, as mentioned above, the processing of the connecting portion may be facilitated or the depth of the connecting portion may be reduced.

For example, the inner diameter of the scroll back pressure hole may be 1/3 to 1/2 the thickness of the non-orbiting wrap. By controlling the pressure pulsation of the back pressure chamber through a communication portion rather than the scroll back pressure hole, the scroll back pressure hole does not need to be formed as narrow as in the past. Accordingly, the inner diameter of the scroll back pressure hole can be formed large within a range that does not hinder the strength of the non-orbiting wrap, so that the processing of the scroll back pressure hole can be facilitated.

For example, the connecting portion may be formed so as to face the inner surface of the non-rotating wrap. Accordingly, the refrigerant in the compression chamber can easily flow into the back pressure passage through the connecting portion, which is advantageous for the initial startup of the scroll compressor as mentioned above. In this case, the back pressure passage is preferably formed within a range of 180° to 540° along the direction of formation of the non-rotating wrap based on the compression start angle.

As another example, the communication portion may be formed so as to face the outer surface of the non-orbiting wrap. In this case, when the pressure in the back pressure chamber is higher than the pressure in the compression chamber, the refrigerant moving from the back pressure chamber through the back pressure passage into the compression chamber moves to the compression chamber with the lower pressure among the compression chambers formed between the orbiting scroll and the non-orbiting scroll, thereby suppressing the pressure in the compression chamber from increasing as much as possible. When the communication portion is formed so as to face the outer surface of the non-orbiting wrap, the back pressure passage is preferably formed in a range of 360° to 720° along the formation direction of the non-orbiting wrap based on the compression start angle.

A scroll compressor according to the present invention comprises a back pressure passage communicating between a compression chamber and a back pressure chamber and guiding a portion of the refrigerant compressed in the compression chamber to the back pressure chamber, wherein the back pressure passage may include a scroll back pressure hole extending from one side of the non-orbiting plate portion facing the back pressure chamber assembly toward a front end surface of the non-orbiting wrap axially facing the orbiting plate portion, and a communication portion extending from one side of the non-orbiting wrap forming the compression chamber toward the scroll back pressure hole and communicating with the scroll back pressure hole. Through this, even when the pressure in the back pressure chamber is greater than the pressure in the compression chamber, the pressure in the back pressure chamber is suppressed from flowing into the compression chamber through the communication portion, and accordingly, the pressure flowing into the compression chamber from the back pressure chamber can be minimized, thereby reducing the indication loss due to recompression.

In a scroll compressor according to the present invention, the scroll back pressure hole is formed by penetrating the front end surface of the non-orbiting wrap on one side of the non-orbiting plate portion, and the communication portion can be formed by recessing a predetermined depth into the front end surface of the non-orbiting wrap facing the orbiting plate portion. Accordingly, with a simple configuration, the pressure in the back pressure chamber can be minimized from moving to the compression chamber. In addition, since there is no need to reduce the diameter of the scroll back pressure hole, the processing of the back pressure passage can be facilitated.

Fig. 1 is a longitudinal cross-sectional view showing a fixed-pressure scroll compressor according to the present embodiment.
Figure 2 is a bottom perspective view illustrating the non-rotating scroll of Figure 1.
Figure 3 is a bottom view illustrating the non-rotating scroll of Figure 2.
Fig. 4 is a cross-sectional view illustrating the non-rotating scroll of Fig. 2.
Fig. 5 is an assembled cross-sectional view showing a compression unit to explain the operation of a fixed-pressure scroll compressor according to the present embodiment.
Fig. 6 is a cross-sectional view taken along line VI-VI of Fig. 5.
Fig. 7 is a bottom view showing another example of the communication part of the non-rotating scroll of Fig. 4.
Fig. 8 is a cross-sectional view taken along line VIII-VIII of Fig. 7.
Figure 9 is a bottom view of a non-rotating scroll shown to illustrate another embodiment of a pressure passage.
Fig. 10 is a bottom view showing another example of the communication part of the non-rotating scroll of Fig. 4.
Fig. 11 is a cross-sectional view taken along line XI-XI of Fig. 9.
Fig. 12 is a cross-sectional view of a non-rotating scroll shown to illustrate another embodiment of a pressure passage.

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

Typically, scroll compressors can be categorized as open or sealed types depending on whether the drive unit (transmission unit) and the compression unit are installed together in the internal space of the casing. The former is a type in which the transmission unit forming the drive unit is installed separately from the compression unit, while the sealed type is a type in which the transmission unit is installed within the same casing as the compression unit. The following description will use a sealed scroll compressor as an example, but is not necessarily limited to a sealed scroll compressor. In other words, the present invention can be equally applied to an open scroll compressor in which the transmission unit and the compression unit are separated.

In addition, scroll compressors can be divided into vertical scroll compressors in which the rotation axis is arranged perpendicular to the ground and horizontal scroll compressors in which the rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side can be defined as the side facing the ground. The following description will use a vertical scroll compressor as an example. However, the same or similar application can be applied to a horizontal scroll compressor. Therefore, the axial direction is understood as the axial direction of the rotation axis, the radial direction is understood as the radial direction of the rotation axis, and the axial direction can be understood as the up-down direction, and the radial direction can be understood as the left and right sides, respectively.

Figure 1 is a longitudinal cross-sectional view showing a fixed back pressure scroll compressor according to the present invention.

Referring to FIG. 1, in the scroll compressor according to the present embodiment, a driving motor (120) forming an electric power unit is installed in the lower half of a casing (110), and a main frame (130), a rotating scroll (140), a non-orbiting scroll (150), and a back pressure chamber assembly (160) forming a compression unit are installed in the upper part of the driving motor (120). The electric power unit is coupled to one end of a rotating shaft (125), and the compression unit is coupled to the other end of the rotating shaft (125). Accordingly, the compression unit is connected to the electric power unit by the rotating shaft (125) and operates by the rotational force of the electric power unit.

The casing (110) includes a cylindrical shell (111), an upper cap (112), and a lower cap (113).

The cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and the aforementioned driving motor (120) and main frame (130) are inserted and fixed to the inner 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 driving motor (120) is coupled through the terminal bracket. In addition, a refrigerant suction pipe (117), which will be described later, is coupled through the upper half of the cylindrical shell (111), for example, the upper side of the driving motor (120).

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

The rim of the high-low pressure separator (115) is welded to the casing (110) as described above. The central portion of the high-low pressure separator (115) is bent so as to protrude toward the upper surface of the upper cap (112) and is placed on the upper side of the back pressure chamber assembly (160) to 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. Accordingly, a low pressure portion (110a) forming a suction space can be formed on the lower side of the high-low pressure separator (115), and a high pressure portion (110b) forming a discharge space can be formed on the upper side.

In addition, a through hole (115a) is formed in the center of the high-low pressure separator plate (115). The low-pressure section (110a) and the high-pressure section (110b) can be blocked by attaching or detaching the floating plate (165) and the high-low pressure separator plate (or sealing plate) (115), or can be communicated through the through hole (115a) of the high-low pressure separator plate (115).

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 portion (110a), and the oil storage space (110c) forms a part of the low-pressure portion (110a).

Referring to Fig. 1, the driving motor (120) according to the present embodiment is installed in the lower half of the low-pressure section (110a) and includes a stator (121) and a rotor (122). The stator (121) is fixed to the inner wall surface 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 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 connected through 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 interior of the stator core (1211) at a predetermined gap interval. Permanent magnets (1222) are embedded in the interior of the rotor core (1222) at a predetermined gap interval along the circumference.

In addition, a 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 driving motor (120) can be transmitted to the orbiting scroll (140) through the rotation shaft (125).

An eccentric portion (1251) is formed at the upper end of the rotating shaft (125) to be eccentrically coupled to a rotating scroll (140) to be described later. An oil pickup (126) for sucking up oil stored in the lower part of the casing (110) may be installed at the lower end of the rotating shaft (125). The rotating shaft (125) is formed with an oil passage (1252) extending axially therethrough.

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

The main frame (130) according to the present embodiment includes a main flange portion (131), a main bearing portion (132), a rotation space portion (133), a scroll support portion (134), an old ring support portion (135), and a frame fixing portion (136).

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 formed smaller than the inner diameter of the cylindrical shell (111), so that the outer surface of the main flange portion (131) is spaced apart from the inner surface of the cylindrical shell (111). However, a frame fixing portion (136), which will be described later, protrudes radially from the outer surface of the main flange portion (131). The outer surface of the frame fixing portion (136) is fixedly attached to the inner 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 driving motor (120). The main bearing portion (132) has a cylindrical shaft hole (132a) extending axially therethrough. Accordingly, a rotation shaft (125) is inserted into the inner circumferential surface of the shaft hole (132a) and supported radially.

The pivot space (133) is sunken from the center of the main flange (131) toward the main bearing (132) to a preset depth and outer diameter. The pivot space (133) is formed to be larger than the outer diameter of the rotation shaft coupling (143) provided in the pivot scroll (140) described later. Accordingly, the rotation shaft coupling (143) can be accommodated so as to be pivotable within the pivot space (133).

The scroll support member (134) is formed in a ring shape along the periphery of the pivot space member (133) on the upper surface of the main flange member (131). Accordingly, the scroll support member (134) can axially support the lower surface of the pivot plate member (141) described later.

The Oldham ring support member (135) is formed in a ring shape along the outer circumference of the scroll support member (134) on the upper surface of the main flange member (131). Accordingly, the Oldham ring (170) can be inserted into the Oldham ring support member (135) and rotatably accommodated.

The frame fixing member (136) extends radially from the outer edge of the old ring support member (135). The frame fixing member (136) extends in an annular shape or extends as a plurality of protrusions spaced apart at predetermined intervals along the circumferential direction. In the present embodiment, an example in which the frame fixing member (136) is formed as a plurality of protrusions along the circumferential direction is illustrated.

Referring to FIG. 1, the orbiting scroll (140) according to the present embodiment is coupled to a rotation shaft (125) and is provided between the main frame (130) and the non-orbiting scroll (150). An anti-rotation mechanism, an Oldham ring (170), is provided between the main frame (130) and the orbiting scroll (140). Accordingly, the orbiting scroll (140) is restrained from rotating and performs an orbiting motion with respect to the non-orbiting scroll (150).

Specifically, the orbiting scroll (140) includes a orbiting plate portion (141), a orbiting wrap (142), and a rotating shaft coupling portion (143).

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

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

The compression chamber (V) is composed of a first compression chamber (V1) and a second compression chamber (V2) based on the orbital wrap (142). The first compression chamber (V1) and the second compression chamber (V2) are formed in series with a suction pressure chamber (not symbolized), an intermediate pressure chamber (not symbolized), and a discharge pressure chamber (not symbolized), respectively. Hereinafter, the compression chamber formed between the outer surface of the orbital wrap (142) and the inner surface (152b) of the non-orbital wrap (152) facing it is defined as the first compression chamber (V1), and the compression chamber formed between the inner surface of the orbital wrap (142) and the outer surface (152c) of the non-orbital wrap (152) facing it is defined as the second compression chamber (V2).

The rotary shaft coupling portion (143) is formed to protrude from the lower surface of the pivot plate portion (141) toward the main frame (130). The rotary shaft coupling portion (143) is formed in a cylindrical shape, and a pivot bearing (not shown) made of a bushing bearing can be press-fitted onto the inner surface thereof.

Referring to FIG. 1, the non-orbiting scroll (150) according to the present embodiment is placed on the upper portion 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 may be coupled so as to be movable in the vertical direction. The present embodiment illustrates an example in which the non-orbiting scroll (150) is coupled so as to be movable in the axial direction with respect to the main frame (130).

Specifically, the non-orbiting scroll (150) according to the present embodiment includes a non-orbiting plate portion (151), a non-orbiting wrap (152), a non-orbiting side wall portion (153), and a guide projection portion (154).

The non-rotating plate portion (151) may be formed in a disc shape and may be arranged transversely in the low pressure portion (110a) of the casing (110). The non-rotating plate portion (151) may be formed with a discharge port (1511) and a scroll pressure hole (181) forming part of a discharge passage (180) to be described later. The discharge port (1511) may be formed to penetrate the non-rotating plate portion (151), while the scroll pressure hole (181) may be formed to penetrate the leading end face (152a) of the non-rotating wrap (152). In other words, the discharge port (1511) is formed so that both ends penetrate the sides of the non-rotating plate (151), while the scroll back pressure hole (181) may be formed so that the first end (181a) penetrates the back surface of the non-rotating plate (151), but the second end (181b) penetrates the front end surface of the non-rotating wrap (152) to be described later.

The discharge port (1511) is a passage for discharging the compressed refrigerant from the final compression chamber (e.g., discharge pressure chamber) (V) to the high pressure section (110b). One discharge port is formed so that the discharge pressure chambers (not symbolized) of the compression chambers (V1) (V2) formed on the inner and outer sides of the non-rotating wrap (152) are connected to each other. However, in some cases, multiple discharge ports (1511) may be formed so that they are independently connected to each compression chamber (V1) (V2). This embodiment illustrates an example in which only one discharge port (1511) is formed.

The non-orbiting wrap (152) extends axially from the lower surface of the non-orbiting plate portion (151) facing the orbiting scroll (140) to a predetermined height, and extends so as to be wound spirally several times around the discharge port (1511) toward the non-orbiting side wall portion (153). The non-orbiting wrap (152) is formed to correspond to the orbiting wrap (142) so as to form two pairs of compression chambers (V) between it and the orbiting wrap (142).

The non-rotating wrap (152) is formed so that the leading edge (152a) facing the rotating plate portion (141) is formed flat overall, but the second stage (181b) of the scroll back pressure hole (181) described above can penetrate a predetermined portion. Accordingly, the scroll back pressure hole (181) can be formed to penetrate between the back surface (151a) of the non-rotating plate portion (151) and the leading edge (152a) of the non-rotating wrap (152).

In addition, a communication portion (183) forming another part of a pressure relief passage (180) to be described later may be formed on the leading end face (152a) of the non-rotating wrap (152). In other words, the communication portion (183) may be formed by being sunken to a preset depth on the leading end face (152a) of the non-rotating wrap (152). Accordingly, the scroll pressure relief hole (181) may be communicated with the compression chamber (V) almost continuously through the communication portion (183). The scroll pressure relief hole (181) and the communication portion (183) will be described again later together with the plate pressure relief hole (182).

The non-rotating side wall portion (153) is formed in a ring shape by extending axially from the lower edge of the non-rotating plate portion (151) to surround the non-rotating wrap (152). A suction port (1531) penetrating radially is formed on one side of the outer circumference of the non-rotating side wall portion (153).

The guide protrusion (154) may extend radially from the lower outer circumference of the non-rotating side wall (153). The guide protrusion (154) may be formed in a single ring shape, or a plurality of guide protrusions (154) may be formed at predetermined intervals along the circumference. This embodiment will be described with reference to an example in which a plurality of guide protrusions (154) are formed at predetermined intervals along the circumference.

Referring to Fig. 1, the back pressure chamber assembly (160) according to the present embodiment is provided on the upper side of the non-orbiting scroll (150). Accordingly, the back pressure of the back pressure chamber (160a) (more precisely, the force exerted by the back pressure 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 the back pressure, thereby sealing 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-rotating plate portion (151), and 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 fixed plate portion (161a), a first annular wall portion (161b), and a second annular wall portion (161c). The fixed plate portion (161a) is a portion that is coupled to the back surface of the non-rotating plate portion (151), and the first annular wall portion (161b) and the second annular wall portion (161c) extend from the upper surface of the fixed plate portion (161a). Accordingly, the upper surface of the fixed plate portion (161a), the outer surface of the first annular wall portion (161b), the inner surface of the second annular wall portion (161c), and the lower surface of the floating plate (165) form an annular back pressure chamber (160a).

Additionally, a plate pressure hole (182) forming another part of a pressure passage (180) to be described later may be formed in the pressure plate (161). The plate pressure hole (182) may be formed by penetrating both axial side surfaces of the pressure plate (161).

The plate pressure hole (182) can be connected to the scroll pressure hole (181) provided in the non-orbiting scroll (150). In other words, the first end (182a) of the plate pressure hole (182) can be connected to the first end (181a) of the scroll pressure hole (181), and the second end (182b) of the plate pressure hole (182) can be connected to the pressure chamber (160a). Accordingly, the compression chamber (V) and the pressure chamber (160a) can be connected through the scroll pressure hole (181) and the plate pressure hole (182).

The plate pressure hole (182) may be formed on the same axial line as the scroll pressure hole (181), may be formed on different axial lines, or may be formed at an angle with respect to the axial direction. This embodiment illustrates an example in which a part of the plate pressure hole (182) is axially connected to the scroll pressure hole (181) on the same axial line. Accordingly, the overall length of the plate pressure hole (182) can be minimized, thereby reducing the dead volume caused by the plate pressure hole (182). The plate pressure hole (182) will be described again later together with the scroll pressure hole (181).

An intermediate discharge port (1613) communicating with the discharge port (1511) of the non-orbiting scroll (150) is formed in the first annular wall portion (161b). A valve guide groove (1614) is formed on the inside of the intermediate discharge port (1613) into which a discharge valve (155) is slidably inserted. A backflow prevention hole (1615) is formed in the center of the valve guide groove (1614). Accordingly, the discharge valve (155) selectively opens and closes between the discharge port (1511) and the intermediate discharge port (1613) to prevent the discharged refrigerant from flowing back into the compression chamber (V1)(V2).

The floating plate (165) is formed in an annular shape. The floating plate (165) may be formed of a material lighter than the back pressure plate (161). Accordingly, the floating plate (165) moves axially 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 surface of the high-low pressure separator (115). For example, when the floating plate (165) comes into contact with the high-low pressure separator (115), it serves to seal the discharged refrigerant so that it does not leak to the low pressure section (110a) but is discharged to the high pressure section (110b).

The scroll compressor according to the above embodiment operates as follows.

That is, when power is applied to the driving motor (120) to generate rotational force, the orbiting scroll (140) eccentrically coupled to the rotation shaft (125) orbits the non-orbiting scroll (150) by the Oldham ring (170). 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 volume of the first compression chamber (V1) and the second compression chamber (V2) gradually narrows as they move from the suction port (or suction pressure chamber) (1531) toward the discharge port (or discharge pressure chamber) (1511) while the orbiting scroll (140) orbits.

Then, the refrigerant is sucked into the low pressure section (110a) of the casing (110) through the refrigerant suction pipe (117), and a portion of this refrigerant is directly sucked into each of the suction pressure chambers (not shown) forming the first compression chamber (V1) and the second compression chamber (V2) and compressed, while the remaining refrigerant moves toward the drive motor (120), cools the drive motor (120), and is sucked into the suction pressure chamber (not shown) together with other refrigerants.

Then, the refrigerant is compressed while moving along the movement path of the first compression chamber (V1) and the second compression chamber (V2), and a portion of the compressed refrigerant moves to the back pressure chamber (160a) formed by the back pressure plate (161) and the floating plate (165) through the communication portion (183) forming the inlet-side back pressure passage and the scroll back pressure hole (181) and the plate back pressure hole (182) forming the outlet-side back pressure passage before reaching the discharge port (1511). Accordingly, the back pressure chamber (160a) forms an intermediate pressure.

Then, the floating plate (165) rises toward the high-low pressure separator (115) and comes into close contact with the high-low pressure separator (115). Accordingly, the high-pressure section (110b) of the casing (110) is separated from the low-pressure section (110a), thereby preventing the refrigerant discharged from each compression chamber (V1) (V2) to the high-pressure section (110b) from flowing back to the low-pressure section (110a).

On the other hand, the back pressure plate (161) is lowered by pressure in the direction toward the non-orbiting scroll (150) due to the pressure of the back pressure chamber (160a). Then, the non-orbiting scroll (150) is pressed toward the orbiting scroll (140). Accordingly, as the non-orbiting scroll (150) is brought into close contact with the orbiting scroll (140), the refrigerant in the compression chambers (V1) (V2) on both sides can be prevented from leaking from the high-pressure side compression chamber forming the intermediate pressure chamber to the low-pressure side compression chamber.

Then, the refrigerant moves from the intermediate pressure chamber toward the discharge pressure chamber and is compressed to the set pressure, and 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 (1614), and the discharge port (1511) opens. Then, the refrigerant in the discharge pressure chamber is discharged to the high pressure section (110b) through the discharge port (1511) provided in the non-rotating plate (151) and the intermediate discharge port (1613) provided in the back pressure plate (161).

Figures 2 to 4 are perspective views, bottom views, and cross-sectional views illustrating the non-rotating scroll of Figure 1.

Referring to FIGS. 2 to 4, the scroll compressor according to the present embodiment forms a back pressure passage (180) between the compression chamber (V) and the back pressure chamber (160a) in the non-orbiting scroll (150) and the back pressure plate (161) to guide a portion of the refrigerant compressed in the compression chamber (V) to the back pressure chamber (160a). The back pressure passage (180) may be formed to penetrate the leading edge (152a) of the non-orbiting wrap (152) axially facing the orbiting plate portion (141), and communicate with the compression chamber (V) in a direction perpendicular to the axial direction through a communication portion (183).

Specifically, the pressure relief passage (180) may include a scroll pressure relief hole (181), a plate pressure relief hole (182), and a communication portion (183). The scroll pressure relief hole (181) may be formed to penetrate the leading edge (152a) of the non-orbiting wrap (152) as described above. The communication portion (183) is formed on the leading edge (152a) of the non-orbiting wrap (152) to communicate the scroll pressure relief hole (181) with the compression chamber (V). The plate pressure relief hole (182) may be formed to communicate the scroll pressure relief hole (181) with the pressure relief chamber (160a).

Referring to FIG. 4, the scroll back pressure hole (181) according to the present embodiment can be formed to penetrate between the front end surface (152a) of the non-orbiting wrap (152) and the back surface (151a) of the non-orbiting plate portion (or non-orbiting scroll) (150). In other words, the second end (181b) of the scroll back pressure hole (181) can be formed to penetrate the center portion of the front end surface (152a) of the non-orbiting wrap (152).

According to the present embodiment, the diameter (D1) of the scroll back pressure hole (181) may be formed as small as possible, which may be advantageous in terms of pressure pulsation in the back pressure chamber (160a) and/or rigidity of the non-orbiting wrap (152). However, in the present embodiment, since the pressure pulsation in the back pressure chamber (160a) is controlled by the communication portion (183) to be described later rather than the scroll back pressure hole (181), the diameter of the scroll back pressure hole (181) may be formed relatively large. For example, the diameter (D1) of the scroll back pressure hole (181) according to the present embodiment may be formed to be 1/3 to 1/2 of the thickness (T) of the non-orbiting wrap (152) in which the scroll back pressure hole (181) is formed. In other words, in the present embodiment, the diameter (D1) of the scroll pressure hole (181) can be formed as large as possible within a range that does not affect the rigidity of the non-rotating wrap (152) in which the scroll pressure hole (181) is formed. Accordingly, even if the scroll pressure hole (181) is formed by penetrating the non-rotating wrap (152), the scroll pressure hole (181) can be easily processed.

The plate pressure relief hole (182) according to the present embodiment may be formed by penetrating the pressure relief plate (161) as described above. In other words, the plate pressure relief hole (182) may be formed on the same axis as the scroll pressure relief hole (181). In this case, the first end (182a) of the plate pressure relief hole (182) may be formed to be larger than or equal to the second end (181a) of the scroll pressure relief hole. Accordingly, the flow resistance of the refrigerant moving to the pressure relief chamber (160a) through the scroll pressure relief hole (181) is suppressed from increasing, so that the refrigerant in the compression chamber (V) can quickly move to the pressure relief chamber (160a).

The communication portion (183) according to the present embodiment can be formed to penetrate toward the inner surface from the entrance of the scroll pressure hole (181), that is, the second end (181b) of the scroll pressure hole (181), as described above. For example, the communication portion (183) is formed in a direction perpendicular to the axial direction of the non-orbiting scroll (150) by forming a portion of the leading end surface (152a) of the non-orbiting wrap (152) to be sunken by a preset depth. Accordingly, even when the leading end surface (152a) of the non-orbiting wrap (152) is in close contact with the orbiting plate portion (141) of the orbiting scroll (140), the scroll pressure hole (181) can communicate with the first compression chamber (V1) through the communication portion (183). Through this, the back pressure passage (180) is almost always open even when the non-orbiting wrap (152) is in close contact with the orbiting plate (141) of the orbiting scroll (140), so that the pressure in the back pressure chamber (160a) is linked to the pressure in the first compression chamber (V1), thereby reducing the pressure pulsation in the back pressure chamber (160a).

In this embodiment, the communicating portion (183) is formed on the leading edge (152a) of the non-rotating wrap (152). Therefore, the communicating portion (183) can be simply formed by cutting a portion of the leading edge (152a). Accordingly, the communicating portion (183) can be formed to a very small depth, on the order of several tens of micrometers (㎛). In the example of the present invention, the depth of the communicating portion (183) can be formed to be approximately 50 ㎛.

The width (D2) of the communication portion (183) may be the same as the diameter (D1) of the scroll pressure hole (181), as illustrated in FIG. 3. If the width (D2) of the communication portion (183) is the same as the diameter (D1) of the scroll pressure hole (181), the processing work of the communication portion (183) may be easier.

In this embodiment, the communication portion (183) is formed to penetrate the inner surface (152b) of the non-rotating wrap (152) as described above. In this case, when the compression start point is assumed to be 0°, the communication portion (183) can be formed in a range of 180° to 540° along the formation direction of the non-rotating wrap (152). Accordingly, when the compressor is initially started, the refrigerant in the compression chamber (V) is quickly introduced into the back pressure chamber (160a) through the communication portion (183) and the scroll back pressure hole (181) and plate back pressure hole (182) connected to the communication portion (183), so that the pressure in the back pressure chamber (160a) can be appropriately maintained compared to the pressure in the first compression chamber (V1).

When the scroll compressor is in operation, the pressure pulsation reduction effect of the back pressure chamber (160a) through the back pressure passage (180) of the present embodiment described above is described as follows.

When power is applied to the drive motor (120), the compressor starts and compression of the refrigerant begins, the refrigerant compressed in the compression chamber (V) flows into the scroll back pressure hole (181) which is connected to the back pressure chamber (160a) through the communication part (183), thereby applying a force that pressurizes the orbiting scroll upward. At this time, the pressure difference between the back pressure chamber (160a) and the compression chamber (V) is large. In this state, if even a slight wobbling of the orbiting scroll (140), such as tilting, occurs, the leading edge (152a) of the non-orbiting wrap (152) is easily separated from the orbiting plate part (141), and the scroll back pressure hole (181) is opened. Accordingly, as shown by the arrows in FIG. 5, the refrigerant is mutually introduced and discharged between the compression chamber (V) and the back pressure chamber (160a), thereby securing an appropriate back pressure.

When the pressure in the back pressure chamber (160a) rises to the intermediate pressure, as described above, the floating plate (165) rises and comes into contact with the high-low pressure separation plate (115), and the back pressure plate (161) descends and presses the non-orbiting wrap (152) of the non-orbiting scroll (150) downward to bring it into contact with the orbiting plate (141) of the orbiting scroll (140).

In a state where the non-rotating wrap (152) is in close contact with the rotating plate (141), the compression chamber (V) and the back pressure chamber (160a) are only communicated with each other through the communication portion (183). Since an intermediate pressure is formed in the back pressure chamber (160a), the pressure difference between the compression chamber (V) and the back pressure chamber (160a) is not large, and the pressure of the compression chamber (V) is difficult to move to the back pressure chamber (160a) through the communication portion (183). Accordingly, it is possible to prevent the pressure of the back pressure chamber (160a) from excessively increasing due to the pressure of the compression chamber (V) with a simple structure without a separate bypass structure as in the prior art.

Conversely, even when the pressure in the back pressure chamber (160a) is greater than the pressure in the compression chamber (V), the pressure in the back pressure chamber (160a) can be suppressed from moving to the compression chamber (V) through the communication portion (183). Accordingly, recompression loss due to the pressure in the back pressure chamber (160a) moving to the compression chamber (V) can be prevented.

Overall, since the pressure movement between the compression chamber (V) and the back pressure chamber (160a) can be minimized due to the communication portion (183), the pressure pulsation in the back pressure chamber (160a) can be minimized.

Meanwhile, there are other examples of the back pressure passage (180) as follows.

That is, in the embodiment described above, the width of the communication portion (183) is formed to be the same as the diameter of the scroll pressure hole, but in some cases, the width of the communication portion (183) may be larger or smaller than the diameter of the scroll pressure hole.

FIG. 7 and FIG. 8 are a bottom view and a cross-sectional view, respectively, illustrating an example in which the width (D3) of the communication portion (183) in the non-orbiting scroll (150) illustrated in FIGS. 2 to 4 is larger than the diameter of the scroll back pressure hole (181). For example, the width (D3) of the communication portion (183) may be approximately twice the diameter (D1) of the scroll back pressure hole (181). In this case, the area of friction between the refrigerant moving through the communication portion (183) between the compression chamber (V) and the scroll back pressure hole (181) and the wall of the communication portion (183) increases. Accordingly, while forming the depth (H2) of the communication portion (183) low for the same refrigerant flow rate, the refrigerant can be suppressed from moving between the compression chamber (V) and the scroll back pressure hole (181), and further, the back pressure chamber (160a), through the communication portion (183) as much as possible.

In addition, there is another embodiment for the back pressure passage (180) as follows.

In the above-described embodiments, the width of the communication portion (183) is formed to be the same toward the inner surface (152b) of the non-rotating wrap (152), but in some cases, the width (D4) of the communication portion (183) may be formed to become wider toward the inner surface (152b) of the non-rotating wrap (152).

FIG. 9 is a bottom view showing an example in which the width (D4) of the communication portion (183) of the non-rotating scroll shown in FIGS. 2 to 4 is formed to become wider as it goes toward the inner surface (152b) of the non-rotating wrap (152).

In this way, when the width (D4) of the communication portion (183) is formed to become wider toward the inner surface (152b) of the non-rotating wrap (152), the flow rate of refrigerant flowing into the scroll back pressure hole (181) from the compression chamber (V) through the communication portion (183) when the compressor is started can increase, so that the pressure of the back pressure chamber (160a) can adapt more quickly to the pressure of the pressure chamber (V).

In addition, there is another embodiment for the back pressure passage (180) as follows.

That is, in the embodiments described above, the communication portion (183) is formed to face the inner surface (152b) of the non-rotating wrap (152), but in some cases, the communication portion (183) may be formed to face the outer surface (152c) of the non-rotating wrap (152).

Figures 10 and 11 are bottom views and cross-sectional views, respectively, showing an example in which the communication portion (183) of the non-orbiting scroll (150) illustrated in Figures 2 to 4 is formed so as to face the outer surface (152c) of the non-orbiting wrap (152). In this case, when the compression starting point is 0°, it is preferable that the scroll back pressure hole (181) be formed in a range of 360° to 720° along the formation direction of the non-orbiting wrap (152).

When the communication portion (183) is formed in this way to face the outer surface (152c) of the non-orbiting wrap (152), when the pressure of the back pressure chamber (160a) is higher than the pressure of the compression chamber (V), the pressure of the back pressure chamber (160a) moves to the compression chamber with the lower pressure among the compression chambers (V1, V2) formed between the orbiting scroll (140) and the non-orbiting scroll (150). Accordingly, the recompression effect of the compression chamber (V) can be further suppressed.

In addition, there is another embodiment for the back pressure passage (180) as follows.

In the above-described embodiments, the scroll pressure hole (181) is formed by penetrating the leading edge (152a) of the non-orbiting wrap (152) on one side of the non-orbiting plate portion (151), and the communication portion (183) is formed by being recessed into the leading edge (152a) of the non-orbiting wrap (152) to a preset depth. However, in some cases, the scroll pressure hole (181) may be formed by penetrating the leading edge (152a) of the non-orbiting wrap (152) on one side of the non-orbiting plate portion (151) or being recessed into the leading edge (152a) of the non-orbiting wrap (152) to a preset depth, and the communication portion (183) may be formed by penetrating toward the scroll pressure hole (181) on one side of the non-orbiting wrap (152) facing one side of the orbiting wrap (142).

FIG. 12 illustrates an example in which a communication portion (183) of a non-orbiting scroll (150) illustrated in FIGS. 2 to 4 is formed to penetrate toward a scroll pressure hole (181) on one side of a non-orbiting wrap (152) and communicate with the scroll pressure hole (181).

Accordingly, when the compressor is in operation, the entire front end surface (152a) of the non-rotating wrap (152) can be in close contact with the rotating plate portion (141), so that the seal between the compression chambers (V1, V2) located on both sides of the non-rotating wrap (152) can be firmly maintained.

110: Casing 110a: Low pressure section (suction space)
110b: High pressure section (discharge space) 110c: Oil storage space
111: Cylindrical shell 112: Upper cap
113: Lower cap 115: High-low pressure separator
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: Rotating shaft
1251: Eccentric section 1252: Oil path
126: Oil pickup 130: Mainframe
131: Main flange section 132: Main bearing section
133: Rotating space 134: Scroll support
135: Oldham ring receiving part 136: Frame fixing part
140: Swivel scroll 141: Swivel plate
142: Swivel wrap 143: Rotating shaft joint
150: Non-rotating scroll 151: Non-rotating plate
151a: Back surface of non-rotating plate 1511: Outlet
1512: Bypass hole 1513: Variable capacity hole
152: Non-rotating lap 152a: Lead section of non-rotating lap
152b: Inner side of non-rotating lap 152c: Outer side of non-rotating lap
153: Non-rotating side wall 1531: Intake
154: Guide protrusion 155: Discharge valve
160: Back pressure chamber assembly 160a: Back pressure chamber
161: Back pressure plate 161a: Fixed plate
161b: First ring wall section 161c: Second ring wall section
1613: Middle outlet 1614: Valve guide groove
1615: Backflow prevention hole 165: Floating plate
170: Oldham Ring 180: Pressure Passage
181: Scroll pressure hole 181a: First stage of scroll pressure hole
181b: Second stage of scroll pressure hole 182: Plate pressure hole
182a: First stage of plate pressure hole
182b: Second stage of plate pressure hole
183: Communication section V, V1, V2: Compression chamber
D1: Diameter of scroll pressure hole D2, D3, D3: Width of the connecting part
H1, H2: Height of the flue gasket T: Thickness of the non-rotating wrap

Claims (13)

A casing in which the sealed internal space is divided into a low-pressure section and a high-pressure section;
A rotating scroll coupled to a rotating shaft in the internal space of the above casing and rotating, and having a rotating wrap provided on one side of the rotating plate;
A non-orbiting scroll having a non-orbiting wrap provided on one side of a non-orbiting plate portion facing the orbiting plate portion so as to form a compression chamber by interlocking with the orbiting wrap;
A back pressure chamber assembly provided on the back surface of the above non-rotating scroll to form a back pressure chamber; and
It includes a back pressure passage that communicates between the compression chamber and the back pressure chamber and guides a portion of the refrigerant compressed in the compression chamber to the back pressure chamber,
The above pressure passage is,
A scroll pressure hole extending from one side of the non-rotating plate portion facing the above pressure chamber assembly toward the front end surface of the non-rotating wrap axially facing the above-mentioned rotating plate portion; and
A communicating portion extending from one side of the non-rotating wrap forming the compression chamber toward the scroll pressure hole and communicating with the scroll pressure hole is included.
The above scroll pressure hole is formed by penetrating the front surface of the non-rotating wrap on one side of the non-rotating plate or by sinking to a preset depth.
A scroll compressor in which the above-mentioned communication portion is formed by penetrating toward the scroll pressure hole at a position spaced from the front end surface of the non-rotating wrap on one side of the non-rotating wrap facing one side of the rotating wrap. In the first paragraph,
The circumferential width of the above-mentioned connecting portion is
A scroll compressor formed to have an inner diameter greater than or equal to the inner diameter of the above scroll pressure hole. In the second paragraph,
The circumferential width of the above-mentioned connecting portion is
A scroll compressor formed identically toward one side of the above non-rotating wrap. In the third paragraph,
The circumferential width of the above-mentioned connecting portion is
A scroll compressor formed to become wider toward one side of the above non-rotating wrap In the first paragraph,
The above communication part is,
A scroll compressor in which the axial depth is formed smaller than the circumferential width. delete In the first paragraph,
The inner diameter of the above scroll pressure hole is
A scroll compressor having a thickness of 1/3 to 1/2 of the above non-rotating wrap. In any one of the first to fifth and seventh clauses,
A scroll compressor in which the above-mentioned communication portion is formed so as to face the inner surface of the above-mentioned non-rotating wrap. In paragraph 8,
A scroll compressor in which the above pressure passage is formed in a range of 180° to 540° along the direction of formation of the non-rotating wrap based on the compression start angle. In any one of the first to fifth and seventh clauses,
A scroll compressor in which the above-mentioned communication portion is formed so as to face the outer surface of the non-rotating wrap. In Article 10,
A scroll compressor in which the above pressure passage is formed in a range of 360° to 720° along the direction of formation of the non-rotating wrap based on the compression start angle. A casing in which the sealed internal space is divided into a low-pressure section and a high-pressure section;
A rotating scroll coupled to a rotating shaft in the internal space of the above casing and rotating, and having a rotating wrap provided on one side of the rotating plate;
A non-orbiting scroll having a non-orbiting wrap provided on one side of a non-orbiting plate portion facing the orbiting plate portion so as to form a compression chamber by interlocking with the orbiting wrap;
A back pressure chamber assembly provided on the back surface of the above non-rotating scroll to form a back pressure chamber; and
It includes a back pressure passage that communicates between the compression chamber and the back pressure chamber and guides a portion of the refrigerant compressed in the compression chamber to the back pressure chamber,
The above pressure passage is,
A scroll pressure hole extending from one side of the non-rotating plate portion facing the above pressure chamber assembly toward the front end surface of the non-rotating wrap axially facing the above-mentioned rotating plate portion; and
A communicating portion extending from one side of the non-rotating wrap forming the compression chamber toward the scroll pressure hole and communicating with the scroll pressure hole is included.
A scroll compressor in which the above-mentioned communication portion is formed so as to face the outer surface of the non-rotating wrap. In Article 12,
A scroll compressor in which the above pressure passage is formed in a range of 360° to 720° along the direction of formation of the non-rotating wrap based on the compression start angle.