Scroll compressor

Abstract

A scroll compressor is provided. The scroll compressor has a back pressure hole formed in a non-orbiting scroll plate and a back pressure chamber assembly to communicate a compression chamber and a back pressure chamber. A back pressure valve is provided inside the back pressure hole to move in a length direction of the back pressure hole by a pressure difference between the compression chamber and the back pressure chamber, thereby changing a flow area of the back pressure hole. The back pressure valve includes a valve body extending in an axial direction and a hole formed by penetrating the valve body in the axial direction. Thus, pressure pulsation of the back pressure chamber can be improved.

Description

Technical Field

[0001] This invention relates to a scroll compressor. Background Technology

[0002] Compared to other types of compressors, scroll compressors have the advantage of achieving a relatively high compression ratio due to continuous compression via interlocking scroll discs. Furthermore, the smooth transition between refrigerant intake, compression, and discharge ensures stable torque. Therefore, scroll compressors are widely used in air conditioning systems and other applications for compressing refrigerants.

[0003] Scroll compressors can be classified into top-compression type and bottom-compression type based on the position of the drive motor and compressor unit, which constitute the drive or electric unit. In a top-compression type, the compressor unit is located above the drive motor, while in a bottom-compression type, the compressor unit is located below the drive motor. This classification is based on examples where the housing is arranged vertically or orthogonally. In the case where the housing is arranged horizontally, it can be distinguished that the left side is the top and the right side is the bottom.

[0004] In addition, scroll compressors can be classified into high-pressure and low-pressure types based on the way they draw in refrigerant. In a high-pressure type, the refrigerant suction pipe is directly connected to the suction chamber, so the refrigerant is drawn into the compression chamber (suction chamber) without passing through the internal space of the casing. In a low-pressure type, the refrigerant suction pipe is connected to the internal space of the casing, so the refrigerant is drawn into the compression chamber (suction chamber) after passing through the internal space of the casing.

[0005] Patent document 1 (US Patent Publication US2015 / 0345493A1) illustrates a scroll compressor that is both an upper-compression type and a low-pressure type.

[0006] Furthermore, in existing scroll compressors such as Patent Document 1, the non-rotating scroll plate can move axially along the rotating shaft according to the pressure in the compression chamber and maintain a sealed state with the rotating scroll plate. This can be classified as a non-rotating back-pressure scroll compressor.

[0007] In the existing non-rotating back pressure scroll compressors described above, since no component is provided in the refrigerant flow path connecting the compression chamber and the back pressure chamber to adjust the back pressure during repeated compression, pulsation is continuously generated in the back pressure chamber. This acts as a useless volume in the compression chamber, leading to increased compression losses.

[0008] Although the intermediate pressure pulsation was improved by installing a valve in the refrigerant flow path connecting the compression chamber and the back pressure chamber in Patent Document 2 (US Patent Publication US2015 / 0176585A1), the manufacturing time and cost of the compressor increased due to the complex structure and large number of components of the valve.

[0009] Existing technical documents

[0010] US Patent Publication No. US2015 / 0345493A1 (Publication Date: December 3, 2015)

[0011] US Patent Publication No. US2015 / 0176585A1 (Publication Date: June 25, 2015) Summary of the Invention

[0012] The purpose of this invention is to provide a scroll compressor in a non-rotational back pressure mode that can improve the pressure pulsation of the back pressure chamber by configuring a back pressure valve in the refrigerant flow path connecting the compression chamber and the back pressure chamber.

[0013] The technical solution for achieving the above-mentioned objective of the present invention is as follows.

[0014] The scroll compressor of the present invention includes a housing, a high-low pressure separation plate, a main frame, a rotary scroll plate, a non-rotating scroll plate, a back pressure chamber assembly, and a back pressure port. The high-low pressure separation plate is fixed inside the housing and divides the housing into a low-pressure section constituting an intake space and a high-pressure section constituting an exhaust space. The main frame is fixed inside the housing and disposed in the low-pressure section. The rotary scroll plate is axially supported by the main frame and rotates. The non-rotating scroll plate is configured to move axially relative to one side of the main frame, and forms a compression chamber together with the rotary scroll plate. The back pressure chamber assembly is disposed between the high-low pressure separation plate and the non-rotating scroll plate, and has an annular back pressure chamber. The back pressure port is disposed between the non-rotating scroll plate and the back pressure chamber assembly, and communicates with the compression chamber and the back pressure chamber. Furthermore, a back pressure valve is disposed inside the back pressure port. The back pressure valve includes: a valve body, movable and extending axially; and a hole formed through the valve body along the axial direction. The flow area of ​​the back pressure hole can be changed by the movement of the back pressure valve within the back pressure hole, thereby improving the pressure pulsation of the back pressure chamber.

[0015] Specifically, the back pressure valve includes a first hole and a second hole formed axially through the valve body. The first hole is formed at the compression chamber side end of the valve body. The second hole communicates with the first hole, and the inner diameter of the second hole is expanded relative to the first hole, extending from the first hole to the back pressure chamber side end of the valve body. A refrigerant flow path is formed through the first hole and the second hole.

[0016] Specifically, the back pressure valve includes a side hole formed on the side of the valve body. The side hole communicates with the second hole and is formed between the compression chamber side end and the back pressure chamber side end. Furthermore, the inner diameter of the side hole is larger than the inner diameter of the first hole. Therefore, refrigerant can move more easily to the second hole through the side hole than through the first hole.

[0017] Specifically, the valve body includes: a main body disposed on the back pressure chamber side; an extension body extending axially from the main body and disposed on the compression chamber side; and a pressurizing surface formed in the boundary region between the main body and the extension body. The radial cross-sectional area of ​​the main body is larger than the radial cross-sectional area of ​​the extension body. Therefore, the pressure of the compressed refrigerant can be applied to the pressurizing surface.

[0018] Specifically, the first hole is formed at the compression chamber side end of the extended body. The second hole is formed from the first hole to the back pressure chamber side end of the main body. Furthermore, the side hole is formed on the side between the compression chamber side end of the extended body and the pressurized surface. Thus, a refrigerant flow path with a variable flow area is formed in the back pressure valve.

[0019] Specifically, the valve body includes an inclined portion formed at the compression chamber side end of the extended body. The inclined portion is formed such that its outer diameter gradually decreases along the periphery of the first hole. Therefore, the inclined portion can closely abut against the stepped portion of the inclinedly formed scroll plate-side back pressure hole.

[0020] In one embodiment of the present invention, a back pressure valve is provided inside the back pressure orifice. The back pressure valve moves along the length of the back pressure orifice due to the pressure difference between the compression chamber and the back pressure chamber, thereby changing the flow path area of ​​the back pressure orifice. Therefore, pressure pulsation in the back pressure chamber can be suppressed.

[0021] Specifically, the back pressure valve includes: a valve body extending axially and having a hollow shape; and a hole penetrating the inner side of the valve body along the axial direction. Refrigerant passes through the hole of the back pressure valve, and the valve body moves due to the pressure difference of the refrigerant.

[0022] In one embodiment of the present invention, the back pressure valve includes a valve body and a plurality of orifices. The valve body is inserted into and slides within the back pressure orifices. The valve body forms a first refrigerant flow path extending axially and a second refrigerant flow path sequentially extending through the outer surface and the interior. The plurality of orifices in the valve body are interconnected and form the first refrigerant flow path and the second refrigerant flow path. Thus, the flow path area of ​​the back pressure orifice for refrigerant movement can be changed.

[0023] Specifically, the valve body includes: a main body disposed on the back pressure chamber side; an extension body extending axially from the main body and disposed on the compression chamber side; and a pressurizing surface formed in the boundary region between the main body and the extension body. Thus, the pressurizing surface can be subjected to the pressure of compressed refrigerant.

[0024] Specifically, the plurality of holes includes: a first hole formed at the compression chamber side end of the valve body; a second hole communicating with the first hole, the second hole having an expanded inner diameter relative to the first hole, extending from the first hole to the back pressure chamber side end of the valve body; and a side hole communicating with the second hole, formed between the compression chamber side end and the back pressure chamber side end. A refrigerant flow path is formed through the plurality of holes, and the area of ​​the flow path can be varied.

[0025] Specifically, the inner diameter of the side hole is larger than the inner diameter of the first hole. Therefore, the compressed refrigerant in the compression chamber is moved to the back pressure chamber through the enlarged side hole via the flow path.

[0026] Specifically, the valve body includes an inclined portion formed at the compression chamber side end of the extended body, the inclined portion being configured such that its outer diameter gradually decreases along the periphery of the first hole. Therefore, the inclined portion can fit tightly against the stepped portion of the inclinedly formed scroll plate-side back pressure hole.

[0027] Specifically, the first refrigerant flow path is formed by the first hole and the second hole, which are interconnected. The second refrigerant flow path is formed by the outer surface of the compression chamber side end of the valve body, which is interconnected with the inner circumferential surface of the back pressure hole, the side hole, and the second hole. Thus, the flow path area of ​​the back pressure hole for refrigerant movement can be changed.

[0028] In one of the aforementioned embodiments, when the pressure in the compression chamber is higher than the pressure in the back pressure chamber, both the first and second refrigerant flow paths are opened. Therefore, the back pressure valve does not hinder the pressure rise in the back pressure chamber. Furthermore, when the pressure in the compression chamber is lower than the pressure in the back pressure chamber, the first refrigerant flow path is opened, while the second refrigerant flow path is closed. Therefore, the amount of refrigerant moving into the compression chamber decreases, and the pressure in the back pressure chamber drops slowly, thereby suppressing pressure pulsations in the back pressure chamber.

[0029] Specifically, the back pressure port includes a scroll-side back pressure port and a plate-side back pressure port. The scroll-side back pressure port is formed on the non-rotating scroll and communicates with the compression chamber. The plate-side back pressure port is formed on the back pressure chamber assembly and communicates with both the scroll-side back pressure port and the back pressure chamber. The back pressure valve is disposed inside the scroll-side back pressure port and slides. This suppresses pressure pulsations in the back pressure chamber.

[0030] Specifically, a portion of the scroll plate-side back pressure hole is covered by one side of the back pressure chamber assembly, and the back pressure valve overlaps axially with the side of the back pressure chamber assembly covering the scroll plate-side back pressure hole. Therefore, the back pressure valve is restricted from moving from the scroll plate-side back pressure hole to the plate-side back pressure hole.

[0031] Specifically, the scroll plate-side backpressure port includes a first scroll plate-side backpressure port and a second scroll plate-side backpressure port. The first scroll plate-side backpressure port communicates with the plate-side backpressure port, and one end of the second scroll plate-side backpressure port communicates with the first scroll plate-side backpressure port, while the other end communicates with the compression chamber. Furthermore, the inner diameter of the first scroll plate-side backpressure port is larger than the inner diameter of the second scroll plate-side backpressure port, and the backpressure valve is inserted into the first scroll plate-side backpressure port. Therefore, the backpressure valve is restricted from moving from the first scroll plate-side backpressure port to the second scroll plate-side backpressure port.

[0032] Specifically, a stepped portion is formed between the first scroll plate-side back pressure hole and the second scroll plate-side back pressure hole to restrict the movement of the back pressure valve. The stepped portion is formed obliquely toward the second scroll plate-side back pressure hole. Therefore, the back pressure valve is positioned on the stepped portion, thereby restricting the movement of the back pressure valve toward the second scroll plate-side back pressure hole.

[0033] Specifically, the inner diameter of the first hole is smaller than the inner diameter of the back pressure hole on the second scroll plate side. As a result, due to the reduction in the flow path cross-sectional area, the inflow of the compressed refrigerant in the compression chamber into the first hole is restricted, thereby pressurizing the compression chamber side end of the valve body. Therefore, it has the effect of the valve body sliding towards the back pressure chamber side.

[0034] Specifically, the diameter of the extended body is larger than the inner diameter of the back pressure hole on the second scroll plate side. Therefore, the back pressure valve cannot move into the interior of the back pressure hole on the second scroll plate side.

[0035] In another embodiment, the back pressure port includes a scroll-side back pressure port and a plate-side back pressure port. The scroll-side back pressure port is formed on the non-rotating scroll and communicates with the compression chamber. The plate-side back pressure port is formed on the back pressure chamber assembly and communicates with the scroll-side back pressure port and the back pressure chamber. The back pressure valve is disposed inside the plate-side back pressure port and slides. This allows pressure pulsation in the back pressure chamber to be suppressed.

[0036] Specifically, the plate-side back pressure hole includes a first plate-side back pressure hole and a second plate-side back pressure hole. The first plate-side back pressure hole communicates with the back pressure chamber, and one end of the second plate-side back pressure hole communicates with the first plate-side back pressure hole while the other end communicates with the scroll plate-side back pressure hole. The inner diameter of the first plate-side back pressure hole is larger than the inner diameter of the second plate-side back pressure hole, and the back pressure valve is inserted into the first plate-side back pressure hole. Therefore, the back pressure valve is restricted from moving from the first plate-side back pressure hole to the second plate-side back pressure hole.

[0037] Specifically, a plate-side stepped portion is formed between the first plate-side back pressure hole and the second plate-side back pressure hole to restrict the movement of the back pressure valve. The plate-side stepped portion is formed obliquely toward the second plate-side back pressure hole. Therefore, the back pressure valve is positioned on the plate-side stepped portion, thereby restricting the movement of the back pressure valve toward the second plate-side back pressure hole.

[0038] Specifically, the inner diameter of the first hole is smaller than the inner diameter of the back pressure hole on the second plate side. As a result, due to the reduction in the cross-sectional area of ​​the flow path, the inflow of the compressed refrigerant in the compression chamber into the first hole is restricted, thereby pressurizing the compression chamber side end of the valve body. Therefore, it has the effect of the valve body sliding towards the back pressure chamber side.

[0039] Specifically, the diameter of the extended body is larger than the inner diameter of the back pressure hole on the second plate side. Therefore, the back pressure valve cannot move into the interior of the back pressure hole on the second plate side.

[0040] Specifically, at one end of the back pressure chamber side of the first plate-side back pressure hole, a plate-side valve limiting part is tightly fitted to restrict the movement of the back pressure valve. Therefore, the back pressure valve cannot disengage from the first plate-side back pressure hole and move into the back pressure chamber.

[0041] In the scroll compressor of the present invention, since a back pressure valve is provided inside the back pressure orifice that connects the compression chamber and the back pressure chamber, and the passage area of ​​the back pressure orifice is changed by movement, it has the effect of improving the pressure pulsation of the back pressure chamber.

[0042] Furthermore, in the scroll compressor of the present invention, since the back pressure valve has a simple structure, is lightweight, and is composed of a single unit, it has the effect of improving assembly convenience and structural reliability. Attached Figure Description

[0043] Figure 1 This is a longitudinal sectional view showing the interior of a scroll compressor according to an embodiment of the present invention.

[0044] Figure 2 It is shown Figure 1 A longitudinal sectional view of an embodiment in which the back pressure valve is configured inside the back pressure hole on the scroll plate side.

[0045] Figure 3 This is a diagram showing an embodiment in which the central axes of the vortex disk-side back pressure hole and the plate-side back pressure hole are formed on the same axis.

[0046] Figure 4 This is a diagram illustrating an embodiment in which the central axes of the vortex disk-side back pressure hole and the plate-side back pressure hole are formed eccentrically.

[0047] Figure 5 It is shown Figure 1 A 3D view of the back pressure valve.

[0048] Figure 6 It is a general overview Figure 5 The figure shows an embodiment in which the back pressure valve is installed in the stepped portion.

[0049] Figure 7 It shows along Figure 6 A top view of the cross section along line AA.

[0050] Figure 8 This is a longitudinal sectional view showing the position of the back pressure valve and the movement path of the refrigerant when the pressure in the compression chamber rises according to an embodiment of the present invention.

[0051] Figure 9 It is Figure 8 A three-dimensional view showing a section cut open from a scroll compressor.

[0052] Figure 10 This is a longitudinal sectional view showing the position of the back pressure valve and the movement path of the refrigerant when the pressure in the compression chamber drops, according to an embodiment of the present invention.

[0053] Figure 11 It is Figure 10 A three-dimensional view showing a section cut open from a scroll compressor.

[0054] Figure 12 It is a general overview Figure 1 A longitudinal sectional view of another embodiment in which the back pressure valve is configured inside the back pressure hole on the plate side.

[0055] Figure 13 It is shown in Figure 12 In the middle, a longitudinal cross-sectional view of the position of the back pressure valve and the movement path of the refrigerant as the pressure in the compression chamber rises.

[0056] Figure 14 It is shown in Figure 12 In the middle, a longitudinal cross-sectional view of the position of the back pressure valve and the movement path of the refrigerant when the pressure in the compression chamber drops.

[0057] Figure 15 This is a graph showing the pressure changes in the back pressure chamber of a scroll compressor using the back pressure valve of the present invention and a scroll compressor not using the back pressure valve of the present invention.

[0058] Figure 16 It is shown in Figure 15 The diagram shows the pressure that changes according to the crankshaft angle.

[0059] Explanation of reference numerals in the attached figures

[0060] 110: Housing; 110a: Low-pressure section (suction space)

[0061] 110b: High-pressure section (discharge space) 110c: Oil storage space

[0062] 111: Cylindrical shell 112: Upper cap

[0063] 113: Lower cap; 115: High and low pressure separation plate

[0064] 115a: Through hole; 1151: Sealing plate

[0065] 1151a: High and low pressure connection port; 117: Refrigerant suction pipe

[0066] 117a: Refrigerant suction pipe outlet; 118: Refrigerant discharge pipe

[0067] 120: Drive motor 121: Stator

[0068] 1211: Stator core; 1212: Stator coil

[0069] 122: Rotor; 1221: Rotor core

[0070] 1222: Permanent magnet; 125: Rotating shaft

[0071] 125a: Eccentric pin section; 125b: Oil flow path

[0072] 126: Oil pumping unit; 130: Main frame

[0073] 131: Main flange portion

[0074] 132: Main and secondary support part; 132a: Support hole

[0075] 133: Rotation space section; 134: Scroll disk support section

[0076] 135: Cross-ring support part; 136: Frame fixing part

[0077] 136a: Bolt fastening hole; 137: Guide sleeve

[0078] 137h: Bolt insertion hole; 138: Guide bolt

[0079] 140: Non-rotating scroll disk; 141: Non-rotating end plate.

[0080] 141a: Discharge outlet; 141b: Bypass hole 141c: Back pressure hole on the side of the scroll plate; 141c1: Back pressure hole on the side of the first scroll plate.

[0081] 141c2: Second scroll plate side back pressure hole; 141c3: Stepped section

[0082] 141c4: Tapered portion

[0083] 142: Non-circular vortex section; 143: Non-circular sidewall section

[0084] 144: Guide protrusion; 144a: Guide insertion hole

[0085] 145: Discharge valve 146: Back pressure valve

[0086] 1461: Valve body; 1461a: Main body

[0087] 1461b: Extended body 1461b1: Inclined portion

[0088] 1461c: Pressure surface; 1462: Multiple holes

[0089] 1462a: Second hole; 1462a1: Compression chamber side end

[0090] 1462a2: Side end of back pressure chamber; 1462b: Side hole

[0091] 1462c: First hole 150: Rotary scroll

[0092] 151: Rotary end plate section; 152: Rotary scroll section

[0093] 153: Rotary shaft joint; 155: Sliding sleeve

[0094] 160: Back pressure chamber assembly; 160a: Back pressure chamber

[0095] 161: Back pressure plate 1611: Fixing plate section

[0096] 1611a: Plate side back pressure hole

[0097] 1611a1: First plate side back pressure hole

[0098] 1611a2: Second plate side back pressure hole

[0099] 1611b, 1611b′: Valve limiting section

[0100] 1611c: Side step of the slab

[0101] 1611d: Plate-side valve limiting section

[0102] 1612: First annular wall portion; 1612a: Intermediate outlet.

[0103] 1612b: Valve guide groove; 1612c: Backflow prevention hole

[0104] 1613: Second annular wall section; 165: Floating plate

[0105] 170: Cross ring P: Pressure

[0106] R, R′: Refrigerant pressurization space; V: Compression chamber Detailed Implementation

[0107] The scroll compressor of the present invention will now be described in detail with reference to the embodiments shown in the accompanying drawings.

[0108] As mentioned above, scroll compressors can be classified into high-pressure scroll compressors and low-pressure scroll compressors based on the refrigerant suction path. The following explanation will focus on a low-pressure scroll compressor where the internal space of the high-low pressure separator housing is divided into a low-pressure section and a high-pressure section by the high-low pressure separator, and the refrigerant suction pipe is connected to the low-pressure section.

[0109] Furthermore, scroll compressors can be categorized into two types based on their back pressure method: non-cyclonic back pressure compressors, which pressurize the non-cyclonic scroll side towards the cyclonic scroll side, and cyclonic back pressure compressors, which pressurize the cyclonic scroll side towards the non-cyclonic scroll side. The following description will focus on scroll compressors with the non-cyclonic back pressure method. However, it should be noted that this invention is equally applicable to cyclonic back pressure compressors.

[0110] Furthermore, scroll compressors can be divided into two types: longitudinal scroll compressors, where the rotating shaft is configured perpendicular to the ground, and transverse scroll compressors, where the rotating shaft is configured parallel to the ground. For example, in a longitudinal scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side as the side facing the ground. The following explanation uses a longitudinal scroll compressor as an example. However, it should be noted that the present invention can be equally applied to transverse scroll compressors.

[0111] Furthermore, scroll compressors can be classified into two types based on the relative position of the compressor section and the motor section: top-compression type and bottom-compression type. The following explanation will focus on the top-compression type scroll compressor, which is both vertical and has its compressor section located above the motor section.

[0112] Furthermore, scroll compressors can be classified into two types based on the rotation pattern of the scroll plate: fixed radius and variable radius. The following explanation will focus on the variable radius scroll compressor.

[0113] On the other hand, in existing scroll compressors, during the repeated compression process in the compression chamber, continuous pulsation occurs in the back pressure chamber connected to the compression chamber. This acts as a useless volume in the compression chamber, resulting in compression losses.

[0114] In this invention, a novel type of scroll compressor is described, in which a movable back pressure valve is disposed inside the back pressure port connecting the compression chamber and the back pressure chamber, thereby suppressing pressure pulsation in the back pressure chamber.

[0115] like Figure 1 As shown, in the scroll compressor of this embodiment, a drive motor 120 constituting the electric motor is provided in the lower half of the housing 110. Above the drive motor 120, a main frame 130 constituting the compression unit, a non-rotating scroll plate 140, a rotating scroll plate 150, and a back pressure chamber assembly 160 are provided. The electric motor is connected to one end of the rotating shaft 125, and the compression unit is connected to the other end of the rotating shaft 125. Thus, the compression unit is connected to the electric motor via the rotating shaft 125 and operates by the rotational force of the electric motor.

[0116] The housing 110 includes a cylindrical housing 111, an upper cap 112, and a lower cap 113.

[0117] The cylindrical housing 111 is cylindrical with openings at both the top and bottom. The aforementioned drive motor 120 and main frame 130 are inserted into and fixed to the inner circumferential surface of the cylindrical housing 111. A terminal bracket (not shown) is attached to the upper half of the cylindrical housing 111. A terminal (not shown) for transmitting external power to the drive motor 120 is connected through the terminal bracket. A refrigerant suction pipe 117 (described later) is connected through the upper half of the cylindrical housing 111, for example, above the drive motor 120.

[0118] The upper cap 112 is combined to cover the upper end of the opening of the cylindrical shell 111.

[0119] The lower cap 113 is fitted to cover the lower end of the opening of the cylindrical shell 111. The edge of the high-low pressure separation plate 115, described later, is inserted between the cylindrical shell 111 and the upper cap 112 and is fused together with the cylindrical shell 111 and the upper cap 112. The edge of the support bracket, described later, is inserted between the cylindrical shell 111 and the lower cap 113 and is fused together with the cylindrical shell 111 and the lower cap 113. This seals the internal space of the shell 110.

[0120] The high-low pressure separation plate 115 is fixed inside the housing 110 and divides the space into a low-pressure section 110a forming the intake space and a high-pressure section 110b forming the discharge space. Specifically, as described above, the edge of the high-low pressure separation plate 115 is fused to the housing 110. The central portion of the high-low pressure separation plate 115 is bent to protrude from the upper side of the upper cap 112 and is disposed on the upper side of the back pressure chamber assembly 160 described later. A refrigerant intake pipe 117 is connected to the high-low pressure separation plate 115 at a position lower than the high-low pressure separation plate 115, and a refrigerant discharge pipe 118 is connected to the high-low pressure separation plate 115 at a position higher than the high-low pressure separation plate 115. Thus, a low-pressure section 110a forming the intake space is formed on the lower side of the high-low pressure separation plate 115, and a high-pressure section 110b forming the discharge space is formed on the upper side.

[0121] A refrigerant suction pipe 117 extends radially through and is connected to the cylindrical housing 111. The outlet 117a of the refrigerant suction pipe 117 can be configured to face the compression section. For example, the outlet 117a of the refrigerant suction pipe 117 can be configured between the main flange portions 131 of the main frame 130, which will be described later. Therefore, a portion of the refrigerant drawn into the low-pressure section 110a through the refrigerant suction pipe 117 moves upward toward the compression chamber V and is directly drawn in, while the remaining refrigerant moves downward toward the electric motor and can cool the drive motor 120 constituting the electric motor. The penetration position of the refrigerant suction pipe 117 will be explained again later.

[0122] A refrigerant discharge pipe 118 extends radially through and is connected to the upper cap 112. The inlet of the refrigerant discharge pipe 118 can be configured to face the outer surface of the high-low pressure separation plate 115, more precisely, located between the inner circumferential surface of the upper cap 112 and the outer circumferential surface of the high-low pressure separation plate 115. Therefore, the refrigerant passing through the high-low pressure communication hole 1151a of the sealing plate 1151 (described later) can move along the outer circumferential surface of the high-low pressure separation plate 115 and then be discharged to the outside of the compressor through the refrigerant discharge pipe 118.

[0123] Furthermore, a through hole 115a is formed in the center of the high-low pressure separation plate 115. A sealing plate 1151 is inserted into and connected to the through hole 115a, and a floating plate 165 (described later) is attached to and detached from the sealing plate 1151. The low-pressure section 110a and the high-pressure section 110b can be blocked by attaching and detaching the floating plate 165 and the sealing plate 1151, or connected by the high-low pressure communication hole 1151a of the sealing plate 1151.

[0124] The sealing plate 1151 can be formed as an annular shape. For example, a high-low pressure communication hole 1151a connecting the low-pressure section 110a and the high-pressure section 110b is formed in the center of the sealing plate 1151. The floating plate 165 can be mounted and dismounted along the periphery of the high-low pressure communication hole 1151a. Therefore, the floating plate 165 moves up and down along the axial direction of the rotation shaft according to the back pressure and is mounted and dismounted at the periphery of the high-low pressure communication hole 1151a of the sealing plate 1151. During this process, the low-pressure section 110a and the high-pressure section 110b can be sealed or connected.

[0125] Furthermore, the lower cap 113, together with the lower half of the cylindrical shell 111 constituting the low-pressure section 110a, forms an oil storage space 110c. In other words, the oil storage space 110c is formed in the lower half of the low-pressure section 110a and constitutes a part of the low-pressure section 110a. An oil pump 126, described later, is immersed in the oil storage space 110c. When the compressor is running, the oil pump 126 pumps the oil stored in the oil storage space 110c and supplies it to the sliding part through the oil flow path 125b of the rotating shaft 125.

[0126] Next, we will explain the drive motor.

[0127] Refer again Figure 1 The drive motor 120 is located 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 of the cylindrical housing 111 by heat pressing, and the rotor 122 is rotatably disposed inside the stator 121.

[0128] The stator 121 includes a stator core 1211 and a stator coil 1212.

[0129] The stator core 1211 is formed into a cylindrical shape and is fixed to the inner circumferential surface of the cylindrical housing 111 by heat pressing. The stator coil 1212 can be wound on the stator core 1211 and electrically connected to an external power source through terminals (not shown) that pass through and are connected to the housing 110.

[0130] The rotor 122 includes a rotor core 1221 and permanent magnets 1222. The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the interior of the stator core 1211 with a pre-set gap. The permanent magnets 1222 are embedded into the interior of the rotor core 1221 along the circumferential direction at a pre-set interval.

[0131] Furthermore, a rotating shaft 125 is press-fitted into the center of the rotor core 1221. An eccentric pin portion 125a is provided at the upper end of the rotating shaft 125, and the rotary scroll 150, described later, is eccentrically coupled to the upper end of the rotating shaft 125. Thus, the rotational force of the drive motor 120 can be transmitted to the rotary scroll 150 through the rotating shaft 125.

[0132] On the other hand, the lower end of the rotating shaft 125 is connected to the rotor 122, while the upper end is connected to the rotary scroll 150, which will be described later. Therefore, the rotational force of the drive motor 120 is transmitted to the rotary scroll 150 through the rotating shaft 125.

[0133] An oil flow path 125b is formed through the interior of the rotating shaft 125, and an oil pump 126 is provided at the lower end of the rotating shaft 125 for drawing oil stored in the oil storage space 110c of the housing 110. Therefore, the oil stored in the lower part of the housing 110 is drawn along the oil flow path 125b of the rotating shaft 125 and moves towards the swirling space 133. The oil is dispersed by pressure difference and / or collision with the rotating shaft coupling 153 swirling in the swirling space 133, and is supplied to the bearing surface between adjacent components. The oil pump 126 can use various pumps such as centrifugal pumps, viscous pumps, and gear pumps. Furthermore, in Figure 1 An example of using a centrifugal pump is shown. Using a centrifugal pump can reduce manufacturing costs.

[0134] Next, the main framework will be explained.

[0135] exist Figure 1 In one embodiment of the present invention shown, the main frame 130 is fixed inside the housing 110 and disposed in the low-pressure section 110a. Specifically, the main frame 130 is disposed above the drive motor 120 and is fixed to the inner wall surface of the cylindrical housing 111 by heat pressing or welding.

[0136] The main frame 130 of this embodiment of the invention includes a main flange portion 131, a main supported portion 132, a swirling space portion 133, a vortex disk support portion 134, a cross ring support portion 135, and a frame fixing portion 136.

[0137] The main flange portion 131 is formed in an annular shape and is housed within the low-pressure portion 110a of the housing 110. The outer diameter of the main flange portion 131 is smaller than the inner diameter of the cylindrical housing 111, and the outer peripheral surface of the main flange portion 131 is separated from the inner peripheral surface of the cylindrical housing 111. However, the frame fixing portion 136, described later, protrudes radially from the outer peripheral surface of the main flange portion 131. The outer peripheral surface of the frame fixing portion 136 is tightly fitted and fixed to the inner peripheral surface of the housing 110. Therefore, the main frame 130 is fixedly attached to the housing 110.

[0138] The main supported portion 132 protrudes downward from the bottom surface of the center portion of the main flange portion 131 toward the drive motor 120. A cylindrical support hole 132a passes through the main supported portion 132 along the axial direction of the rotation shaft. A rotation shaft 125 is inserted into the inner circumferential surface of the support hole 132a, and the rotation shaft 125 is supported in the radial direction.

[0139] The swivel space 133 is recessed into the main supported portion 132 at the center of the main flange portion 131 with a predetermined depth and outer radial direction. The inner diameter of the swivel space 133 is larger than the outer diameter of the rotation shaft connection portion 153 provided in the swivel scroll disk 150 described later. Therefore, the rotation shaft connection portion 153 can be swirled and accommodated inside the swivel space 133.

[0140] Additionally, oil drawn up via the rotating shaft 125 is temporarily stored inside the swirling space 133. This oil can be supplied between the main support 132 and the rotating shaft 125 and / or between the scroll support 134 and the swirling scroll 150.

[0141] The scroll plate support 134 is formed in a ring shape on the top surface of the main flange 131 along the periphery of the swirling space 133. Therefore, the scroll plate support 134 axially supports the bottom surface of the swirling end plate 151, which will be described later, along the rotation axis.

[0142] The cross-ring support portion 135 is formed on the outer contour of the scroll plate support portion 134 such that its height is lower than that of the scroll plate support portion 134. Specifically, the cross-ring support portion 135 is formed in a ring shape on the top surface of the main flange portion 131 along the outer peripheral surface of the scroll plate support portion 134, and its height is lower than that of the scroll plate support portion 134. The cross-ring 170 is configured on the cross-ring support portion 135 to suppress the rotation of the rotating scroll plate 150, which will be described later. Therefore, the cross-ring 170 is inserted into the cross-ring support portion 135 and is received by the cross-ring support portion 135 in a rotatable manner.

[0143] The frame fixing part 136 is formed on the outer contour of the cross ring support part 135 to fix the main frame 130 to the housing 110. Specifically, the frame fixing part 136 extends radially on the outer contour of the cross ring support part 135.

[0144] The frame fixing part 136 extends into a ring or into a plurality of protrusions spaced at predetermined intervals along the circumferential direction. Figure 1 An example is shown where the frame fixing part 136 is formed as a plurality of protrusions along the circumferential direction.

[0145] For example, a plurality of frame fixing parts 136 are configured to face the guide protrusion 144 of the non-rotating scroll disk 140 described later along the axial direction of the rotation axis. Each frame fixing part 136 may have a bolt fastening hole 136a formed through it along the axial direction of the rotation axis. The bolt fastening hole 136a corresponds to the guide insertion hole 144a of the non-rotating scroll disk 140 described later along the axial direction of the rotation axis.

[0146] The inner diameter of the bolt fastening hole 136a is smaller than the inner diameter of the guide insertion hole 144a. Therefore, a stepped surface extending from the inner circumferential surface of the guide insertion hole 144a is formed around the top surface of the bolt fastening hole 136a. The guide sleeve 137 passing through the guide insertion hole 144a can be placed on this stepped surface and supported on the frame fixing part 136 along the axial direction of the rotation axis.

[0147] The guide sleeve 137 can be formed in a cylindrical shape. That is, the guide sleeve has a bolt insertion hole 137h that extends through the guide sleeve 137 along its length or the axis of rotation.

[0148] Each guide bolt 138 passes through the bolt insertion hole 137h and is respectively fastened to the bolt fastening hole 136a of the frame fixing part 136. Therefore, the non-rotating scroll 140 is slidably supported on the main frame 130 in the axial direction of the rotation axis and is fixed in the radial direction.

[0149] Next, we will explain the non-cyclonic vortex disk.

[0150] Figure 1 The non-cyclone scroll disk 140 of the embodiment of the present invention shown is disposed on the upper part of the main frame 130, separated from the cyclone scroll disk 150 described later. In other words, the non-cyclone scroll disk 140 is configured to be axially movable relative to one side of the main frame 130, separated from the cyclone scroll disk 150. Furthermore, the non-cyclone scroll disk 140 and the cyclone scroll disk 150 together form the compression chamber V.

[0151] The non-rotating vortex disk 140 can be fixedly attached to the main frame 130, or it can be movably attached to the main frame 130 in the vertical direction. Figure 1 An example is shown where the non-rotating vortex disk 140 is combined to be able to move axially relative to the main frame 130 along the axis of rotation.

[0152] The non-rotating scroll disk 140 of this invention includes a non-rotating end plate portion 141, a non-rotating scroll portion 142, a non-rotating side wall portion 143, and a guide protrusion 144.

[0153] The non-rotating end plate portion 141 is formed in the shape of a disk (circular plate) and is laterally arranged in the low-pressure portion 110a of the housing 110. In the central part of the non-rotating end plate portion 141, there are an outlet 141a, a bypass hole 141b and a scroll disk side back pressure hole 141c passing through along the axial direction of the rotation axis.

[0154] The discharge port 141a is formed at a position where the discharge pressure chambers (not marked) of the two compression chambers V formed on the inner and outer sides of the non-rotating scroll section 142 communicate with each other. The bypass hole 141b is formed to communicate with both compression chambers V respectively. The scroll plate side back pressure hole 141c is separated from the discharge port 141a and the bypass hole 141b. The scroll plate side back pressure hole 141c will be described in detail below.

[0155] like Figure 1 and Figure 2 As shown, the scroll compressor of this embodiment of the invention has a back pressure port.

[0156] The back pressure port is disposed in the non-rotating scroll plate 140 and the back pressure chamber assembly 160 (described later) and connects the compression chamber V and the back pressure chamber 160a, serving as a refrigerant flow path for the movement of the compressed refrigerant. The compression chamber V is formed together by the non-rotating scroll plate 140 and the rotating scroll plate 150, and the back pressure chamber 160a is formed together by the back pressure chamber assembly 160 (described later), specifically by the back pressure plate 161 and the floating plate 165.

[0157] The back pressure holes include: a scroll-side back pressure hole 141c, formed on the non-rotating scroll 140 and communicating with the compression chamber V; and a plate-side back pressure hole 1611a, formed on the back pressure chamber assembly 160 and communicating with the scroll-side back pressure hole 141c and the back pressure chamber 160a. Hereinafter, the scroll-side back pressure hole 141c will be described first, and the plate-side back pressure hole 1611a will be specifically described in the back pressure chamber assembly 160 described later.

[0158] A scroll-side back pressure hole 141c is formed on the non-rotating scroll 140, specifically on the non-rotating end plate portion 141, and is a hole communicating with the compression chamber V. During compressor operation, the compressed refrigerant in the compression chamber V moves to the back pressure chamber 160a through the scroll-side back pressure hole 141c. If the compressor stops operating, the refrigerant in the back pressure chamber 160a moves to the compression chamber V through the scroll-side back pressure hole 141c.

[0159] The scroll plate-side back pressure hole 141c communicates with the plate-side back pressure hole 1611a, which will be described later, and extends from the side of the non-rotating scroll plate 140 facing the back pressure chamber assembly 160 into the compression chamber V. Here, the side of the non-rotating scroll plate 140 is the side of the non-rotating end plate portion 141, which is the top surface facing the back pressure chamber assembly 160.

[0160] like Figure 3 As shown, the central axis fc of the scroll-side back pressure hole 141c and the central axis bc of the plate-side back pressure hole 1611a can be formed on the same axis. Thus, the scroll-side back pressure hole 141c and the plate-side back pressure hole 1611a are in communication with each other, and the refrigerant can move smoothly along the scroll-side back pressure hole 141c and the plate-side back pressure hole 1611a.

[0161] The inner diameter of the scroll plate-side backpressure hole 141c is larger than the inner diameter of the plate-side backpressure hole 1611a. Therefore, a portion of the scroll plate-side backpressure hole 141c is covered by one side 1611b of the backpressure chamber assembly 160. Furthermore, when the backpressure valve 146 (described later) is disposed inside the scroll plate-side backpressure hole 141c, the backpressure valve 146 overlaps axially with the side 1611b of the backpressure chamber assembly 160 that covers the scroll plate-side backpressure hole 141c. Therefore, the side 1611b of the backpressure chamber assembly 160 restricts the movement of the backpressure valve 146. Specifically, the backpressure valve 146, due to the side 1611b of the backpressure chamber assembly 160, can only move inside the scroll plate-side backpressure hole 141c and is restricted from moving out of the scroll plate-side backpressure hole 141c to the plate-side backpressure hole 1611a. Hereinafter, one side 1611b of the back pressure chamber assembly 160 will be referred to as the valve limiting part 1611b.

[0162] In addition, such as Figure 4 As shown, according to another embodiment of the present invention, the scroll plate-side back pressure hole 141c can be formed eccentrically to and communicate with the plate-side back pressure hole 1611a. Specifically, the scroll plate-side back pressure hole 141c can be configured such that its central axis fc is separated from the central axis bc of the plate-side back pressure hole 1611a by a predetermined distance e, and is formed to communicate with the plate-side back pressure hole 1611a. Thus, a portion of the scroll plate-side back pressure hole 141c is covered by one side 1611b′ of the back pressure chamber assembly 160. Furthermore, when the back pressure valve 146, described later, is disposed inside the scroll plate-side back pressure hole 141c, the back pressure valve 146 overlaps axially with the side 1611b′ of the back pressure chamber assembly 160 covering the scroll plate-side back pressure hole 141c. Therefore, the side 1611b′ of the back pressure chamber assembly 160 restricts the movement of the back pressure valve 146. Specifically, the back pressure valve 146 is restricted to moving only inside the scroll plate-side back pressure hole 141c due to one side 1611b′ of the back pressure chamber assembly 160, and is prevented from moving out of the scroll plate-side back pressure hole 141c to the plate-side back pressure hole 1611a. Hereinafter, the one side 1611b′ of the back pressure chamber assembly 160 will be referred to as the valve limiting part 1611b′.

[0163] On the other hand, the scroll plate side back pressure hole 141c includes: a first scroll plate side back pressure hole 141c1, which communicates with the plate side back pressure hole 1611a; and a second scroll plate side back pressure hole 141c2, one end of which communicates with the first scroll plate side back pressure hole 141c1, and the other end of which communicates with the compression chamber V.

[0164] Specifically, the first scroll plate-side back pressure hole 141c1 communicates with the plate-side back pressure hole 1611a, and is formed through the non-rotating scroll plate 140 to a predetermined depth on the side facing the back pressure chamber assembly 160 (specifically, the side of the non-rotating end plate portion 141). Furthermore, the second scroll plate-side back pressure hole 141c2 extends from the first scroll plate-side back pressure hole 141c1 into the compression chamber V.

[0165] like Figure 6 As shown, the inner diameter C1d of the first scroll plate side back pressure hole 141c1 is larger than the inner diameter C2d of the second scroll plate side back pressure hole 141c2. A stepped portion 141c3 is formed between the first scroll plate side back pressure hole 141c1 and the second scroll plate side back pressure hole 141c2 to restrict the movement of the back pressure valve 146. Specifically, the stepped portion 141c3 is formed in the portion (boundary region) connecting the first scroll plate side back pressure hole 141c1 and the second scroll plate side back pressure hole 141c2, and is formed inclined towards the second scroll plate side back pressure hole 141c2. As a result, the back pressure valve 146, described later, can be moved inside the first scroll plate side back pressure hole 141c1, and because it is positioned in the stepped portion 141c3, its movement towards the second scroll plate side back pressure hole 141c2 is restricted.

[0166] Additionally, the first scroll plate-side back pressure hole 141c1 may include a tapered portion 141c4, one end of which is tapered, opposite to the stepped portion 141c3. This tapered portion 141c4 facilitates the insertion of the back pressure valve 146 into the first scroll plate-side back pressure hole 141c1 during compressor manufacturing. The tapered portion 141c4 may be omitted in other embodiments of the invention. This reduces the compressor manufacturing time. Figure 3 and Figure 4 An embodiment is shown in which one end of the back pressure hole 141c1 on the first scroll disk side is not tapered.

[0167] As mentioned above, in another embodiment of the invention where the vortex disk-side back pressure hole 141c is formed eccentrically to the plate-side back pressure hole 1611a (see reference...) Figure 4 The first scroll plate-side back pressure hole 141c1 and the second scroll plate-side back pressure hole 141c2 are configured to be eccentric to each other with the plate-side back pressure hole 1611a. In other words, one end of the first scroll plate-side back pressure hole 141c1 is formed to be eccentric to the plate-side back pressure hole 1611a and communicates with the plate-side back pressure hole 1611a. Specifically, the first scroll plate-side back pressure hole 141c1 is configured such that its central axis fc is separated from the central axis bc of the plate-side back pressure hole 1611a by a predetermined distance e, and one end of the first scroll plate-side back pressure hole 141c1 is formed to communicate with the plate-side back pressure hole 1611a.

[0168] A portion of the scroll plate-side back pressure hole 141c, specifically a portion of the first scroll plate-side back pressure hole 141c1, is covered by a valve limiting part 1611b'. The back pressure valve 146 overlaps axially with the valve limiting part 1611b' covering the first scroll plate-side back pressure hole 141c1. Therefore, the back pressure valve 146, due to the valve limiting part 1611b', can only move within the first scroll plate-side back pressure hole 141c1 and is restricted from moving out of the first scroll plate-side back pressure hole 141c1 to the plate-side back pressure hole 1611a.

[0169] The scroll compressor of this embodiment of the invention is provided with a back pressure valve 146. The back pressure valve 146 moves along the length of the back pressure orifice within the back pressure orifice due to the pressure difference between the compression chamber V and the back pressure chamber 160a, thereby changing the flow path area of ​​the back pressure orifice. Here, the flow path area refers to the area of ​​the refrigerant flow path for refrigerant movement. The back pressure valve 146 is disposed inside the back pressure orifice, and by moving along the inside of the back pressure orifice to change the area of ​​the refrigerant flow path, it can improve the pressure pulsation of the back pressure chamber.

[0170] The back pressure valve 146 can be inserted into and moved within the back pressure port (specifically, the scroll-side back pressure port 141c). More specifically, the back pressure valve 146 can slide within the back pressure port (scroll-side back pressure port 141c). The scroll-side back pressure port 141c represents the first scroll-side back pressure port 141c1. That is, the back pressure valve 146 can be inserted into the first scroll-side back pressure port 141c1 and slide along the length of the first scroll-side back pressure port 141c1, thereby changing the area of ​​the refrigerant flow path.

[0171] The back pressure valve 146 suppresses pressure pulsations in the back pressure chamber 160a. Specifically, when the pressure in the compression chamber V rises due to compressor operation (when the pressure in compression chamber V is greater than the pressure in the back pressure chamber 160a), the back pressure valve 146 increases the space in the refrigerant flow path to facilitate the movement of compressed refrigerant from the compression chamber V to the back pressure chamber 160a. When the pressure in the compression chamber V decreases due to compressor shutdown (when the pressure in compression chamber V is less than the pressure in the back pressure chamber 160a), the back pressure valve 146 reduces the space in the refrigerant flow path to prevent the compressed refrigerant in the back pressure chamber 160a from easily moving to the compression chamber V. Therefore, when the pressure in the compression chamber V rises, the back pressure valve 146 does not hinder the pressure rise in the back pressure chamber 160a, and when the pressure in the compression chamber V falls, the back pressure valve 146 suppresses pressure pulsations in the back pressure chamber 160a.

[0172] like Figures 5 to 7As shown, the back pressure valve 146 includes: a valve body 1461 that slides inside a back pressure port (specifically, a scroll-side back pressure port 141c); and a plurality of holes 1462 formed to penetrate the interior of the valve body and communicate with each other. Here, the scroll-side back pressure port 141c refers to a first scroll-side back pressure port 141c1. That is, the valve body 1461 is inserted into and disposed inside the first scroll-side back pressure port 141c1 and slides along the length direction of the first scroll-side back pressure port 141c1, thereby allowing the area of ​​the refrigerant flow path to change.

[0173] The valve body 1461 includes: a main body 1461a, disposed on the back pressure chamber 160a side; and an extension body 1461b, which extends axially from the main body 1461a and is disposed on the compression chamber V side.

[0174] The radial cross-sectional area of ​​the main body 1461a is larger than that of the extension body 1461b. Therefore, a pressure surface 1461c is formed at the boundary region between the main body 1461a and the extension body 1461b, creating a stepped outer surface between the outer surfaces of the main body 1461a and the extension body 1461b. Through the pressure surface 1461c, the back pressure valve 146 can slide towards the back pressure chamber 160a. In other words, when the compressed refrigerant in the compression chamber V moves towards the back pressure chamber 160a, the refrigerant pressurizes the pressure surface 1461c, and the pressure P (refer to...) Figure 8 The back pressure valve 146 slides towards the back pressure chamber 160a from inside the back pressure hole 141c1 on the first scroll plate side.

[0175] The main body 1461a can be formed such that its cross-sectional shape corresponds to the cross-sectional shape of the first scroll plate side back pressure hole 141c1. Specifically, the main body 1461a can be formed such that the cross-sectional shape of its radially outer surface corresponds to the radially cross-sectional shape of the first scroll plate side back pressure hole 141c1. For example, if the radially cross-sectional shape of the first scroll plate side back pressure hole 141c1 is circular, the radially cross-sectional shape of the outer surface of the main body 1461a can also be circular. Therefore, if the first scroll plate side back pressure hole 141c1 is cylindrical, the main body 1461a can be formed as a cylindrical shape with a predetermined length.

[0176] Reference Figure 6Although the diagram shows the main body 1461a with a diameter Ad that is the same as the inner diameter C1d of the first scroll plate side back pressure hole 141c1, this is a schematic illustration. The diameter Ad of the main body 1461a is smaller than the inner diameter of the first scroll plate side back pressure hole 141c1, allowing the main body 1461a to slide along the length of the first scroll plate side back pressure hole 141c1. However, the gap between the outer surface of the main body 1461a and the inner surface of the first scroll plate side back pressure hole 141c1 can be considered to be very small. Therefore, the amount of refrigerant moving through this gap is negligible compared to the amount of refrigerant moving through the refrigerant flow path through the back pressure valve 146. Thus, the main body 1461a can act as a guide when the back pressure valve 146 moves along the length of the first scroll plate side back pressure hole 141c1.

[0177] The main body 1461a includes a refrigerant flow path formed along the axial direction. This will be explained later.

[0178] The extended body 1461b is formed by extending from the main body 1461a toward the vortex disk. The refrigerant flow path formed axially through the interior of the main body 1461a extends into the interior of the extended body 1461b and extends axially through the extended body 1461b.

[0179] The cross-sectional shape of the extension body 1461b can be formed to correspond to the cross-sectional shape of the first scroll plate side back pressure hole 141c1, but is not limited to this. In other words, the cross-sectional shape of the outer surface of the extension body 1461b in the radial direction can correspond to the cross-sectional shape of the first scroll plate side back pressure hole 141c1 in the radial direction, but is not necessarily limited to this. For example, if the cross-sectional shape of the first scroll plate side back pressure hole 141c1 in the radial direction is circular, the cross-sectional shape of the outer surface of the extension body 1461b in the radial direction can be circular, but is not limited to this, and can also be formed into other shapes besides circular.

[0180] The diameter Bd of the extended body 1461b is larger than the inner diameter C2d of the back pressure hole 141c2 on the second scroll side. Therefore, the back pressure valve 146 cannot move into the interior of the back pressure hole 141c2 on the second scroll side. Furthermore, when the pressure in the compression chamber V decreases due to the compressor stopping, the back pressure valve 146 is positioned on the stepped portion 141c3 and is in close contact with the stepped portion 141c3 due to the compressed refrigerant in the back pressure chamber 160a. This changes the area of ​​the refrigerant flow path.

[0181] The central axis of the extension body 1461b and the central axis of the main body 1461a are located on the same axis, and the radial cross-sectional area of ​​the extension body 1461b is smaller than the radial cross-sectional area of ​​the main body 1461a. Alternatively, the diameter Bd of the extension body 1461b is smaller than the diameter Ad of the main body 1461a. Therefore, a pressure surface 1461c is formed in the boundary region between the main body 1461a and the extension body 1461b, so that the outer surfaces of the main body 1461a and the extension body 1461b form steps with each other.

[0182] The pressure surface 1461c can be formed inclined toward the back pressure hole 141c2 on the second vortex disk side, but is not limited thereto, and can be formed without inclination. As a result, the efficiency of selecting the shape of the pressure surface 1461c can be improved.

[0183] The space surrounded by the inner circumferential surface of the pressurized surface 1461c, the inner circumferential surface of the first scroll plate side back pressure hole 141c1, and the outer surface of the extended body 1461b (referred to as the "refrigerant pressurization space R′") (see reference). Figure 6 The compressed refrigerant flows into the compression chamber V, and the flowing refrigerant pressurizes the pressure surface 1461c, thereby causing the valve body 1461 to slide towards the back pressure chamber 160a, and also causing the refrigerant to flow into the side hole 1462b formed in the extension body 1461b described later.

[0184] The back pressure valve 146 includes a plurality of holes 1462 formed through the valve body 1461. That is, the valve body 1461 of the back pressure valve 146 has a plurality of holes 1462 formed thereon.

[0185] The valve body 1461 includes: a first hole 1462c formed at the compression chamber side end 1462a1; a second hole 1462a communicating with the first hole 1462c, with an inner diameter enlarged relative to the first hole 1462c, extending from the first hole 1462c to the back pressure chamber side end 1462a2; and a side hole 1462b communicating with the second hole 1462a, formed between the compression chamber side end 1462a1 and the back pressure chamber side end 1462a2.

[0186] The first hole 1462c is formed by penetrating the compression chamber side end 1462a1, which is one of the two ends of the valve body 1461, and the second hole 1462a is formed by penetrating the back pressure chamber side end 1462a2, which is the other end of the valve body 1461.

[0187] The inner diameter of the second hole 1462a is larger than (enlarges) the inner diameter of the first hole 1462c. Therefore, the refrigerant passing through the first hole 1462c can move smoothly into the second hole 1462a, where the cross-sectional area of ​​the flow path is increased. However, conversely, the refrigerant passing through the second hole 1462a cannot move smoothly into the first hole 1462c, where the cross-sectional area of ​​the flow path is decreased; the refrigerant moves slowly.

[0188] Furthermore, a side hole 1462b communicating with the second hole 1462a is formed on the side of the valve body 1461. The side hole 1462b is formed between the compression chamber side end 1462a1 and the pressurizing surface 1461c. In other words, the side hole 1462b is formed on the side of the extended body 1461b. Therefore, the compressed refrigerant flowing into the refrigerant pressurization space R can move sequentially through the side hole 1462b and the second hole 1462a towards the back pressure chamber 160a.

[0189] like Figure 6 , Figure 8 as well as Figure 10 As shown, one or more side holes 1462b can be formed. Figure 6 An embodiment with a side hole 1462b is shown. Figure 8 and Figure 10 An embodiment with two side holes 1462b is shown.

[0190] A plurality of side holes 1462b can be formed at equal intervals along the circumferential direction on the side of the valve body 1461 (specifically, the extension body 1461b). Therefore, the refrigerant can move uniformly into the refrigerant pressurization space R and uniformly pressurize the pressurization surface 1461c. Furthermore, to guide the smooth flow of the refrigerant, the inner diameter of each of the plurality of side holes 1462b can be smaller than the inner diameter of the second hole 1462a, thereby ensuring that the amount of refrigerant passing through the plurality of side holes 1462b is less than or equal to the amount of refrigerant passing through the second hole 1462a.

[0191] The inner diameter of the side hole 1462b can be smaller than the inner diameter of the second hole 1462a. Therefore, the refrigerant passing through the side hole 1462b can move smoothly into the second hole 1462a, where the cross-sectional area of ​​the flow path is increased. Alternatively, the inner diameter of the side hole 1462b can be the same as the inner diameter of the second hole 1462a. Therefore, the refrigerant passing through the side hole 1462b can move smoothly into the second hole 1462a, where the flow path area is not reduced.

[0192] Furthermore, the inner diameter of the side hole 1462b is larger than the inner diameter of the first hole 1462c. As a result, after the refrigerant passes between the compression chamber side end 1462a1 of the valve body 1461 and the stepped portion 141c3 of the aforementioned scroll plate side back pressure hole 141c, it can smoothly move through the side hole 1462b to the second hole 1462a.

[0193] Furthermore, the inner diameter of the first hole 1462c is smaller than the inner diameter C2d of the second scroll plate side back pressure hole 141c2. Therefore, when the back pressure valve 146 is installed in the stepped portion 141c3 of the scroll plate side back pressure hole 141c, the inflow of the compressed refrigerant moving from the compression chamber V to the second scroll plate side back pressure hole 141c2 into the first hole 1462c is restricted due to the reduction in the flow path cross-sectional area. The compressed refrigerant pressurizes the compression chamber side end 1462a1 of the valve body 1461, thereby causing the valve body 1461 to slide towards the back pressure chamber 160a side.

[0194] The first hole 1462c is formed at the compression chamber side end 1462a1 of the extension body 1461b, and the second hole 1462a is formed from the first hole 1462c to the back pressure chamber side end 1462a2 of the main body 1461a.

[0195] The back pressure valve 146 includes an inclined portion 1461b1, which is formed by the valve body 1461 extending at an angle from the compression chamber side end 1462a1 of the body 1461b. That is, the inclined portion 1461b1 is formed on the valve body 1461 of the back pressure valve 146.

[0196] The inclined portion 1461b1 is formed such that its outer diameter gradually decreases along the periphery of the first hole 1462c. In other words, the inclined portion 1461b1 is formed inclined in the direction of the second vortex disk side back pressure hole 141c2 with the first hole 1462c as the center.

[0197] An inclined portion 1461b1 is disposed on a stepped portion 141c3 formed in the back pressure hole 141c on the scroll plate side. By the inclined portions and stepped portions being formed to correspond to each other, the back pressure valve 146 can be stably supported in the back pressure hole 141c on the scroll plate side.

[0198] Furthermore, the inclined portion 1461b1 is in close contact with the stepped portion 141c3 due to the compressed refrigerant in the back pressure chamber 160a. Therefore, the compressed refrigerant in the back pressure chamber 160a moves to the compression chamber V through the first refrigerant flow path described later.

[0199] Furthermore, although not illustrated, according to another embodiment of the present invention, the compression chamber side end 1462a1 of the extension body 1461b may be formed flat without inclination. In this case, the stepped portion 141c3 formed in the back pressure hole 141c on the scroll plate side may also be formed flat. Therefore, the compression chamber side end 1462a1 of the extension body 1461b can be stably placed on the stepped portion 141c3 and can be in close contact with the stepped portion 141c3.

[0200] The back pressure valve 146 includes a plurality of refrigerant flow paths. That is, a plurality of refrigerant flow paths are formed in the valve body 1461 of the back pressure valve 146.

[0201] Specifically, the valve body 1461 of the back pressure valve 146 slides inside the back pressure orifice, forming a first refrigerant flow path extending axially and a second refrigerant flow path sequentially penetrating the outer surface and the interior. Furthermore, a plurality of orifices 1462 of the back pressure valve 146 are formed in the valve body 1461 to communicate with each other, forming the first and second refrigerant flow paths. The flow path area of ​​the back pressure orifice for refrigerant movement can be changed through these refrigerant flow paths.

[0202] First, the scroll compressor of this embodiment of the invention has a first refrigerant flow path that extends axially through the valve body 1461.

[0203] The first refrigerant flow path is an axially penetrating flow path through the interior of the valve body 1461, formed by a first hole 1462c and a second hole 1462a that communicate with each other in the valve body 1461. Specifically, the first refrigerant flow path refers to the first hole 1462c and the second hole 1462a formed by communicating with each other from the compression chamber side end 1462a1 of the valve body 1461 to the back pressure chamber side end 1462a2.

[0204] Furthermore, the scroll compressor of this embodiment of the invention has a second refrigerant flow path that sequentially penetrates the outer surface and interior of the valve body 1461.

[0205] The second refrigerant flow path is formed by the side hole 1462b and the second hole 1462a on the outer surface of the valve body 1461, which communicate with the inner circumferential surface of the back pressure hole at the compression chamber side end of the valve body 1461. Specifically, the scroll compressor is provided with a second refrigerant flow path that sequentially penetrates the refrigerant pressurization space R and the interior of the valve body 1461, wherein the refrigerant pressurization space R is formed on the outer surface of the valve body 1461. In other words, the second refrigerant flow path is a flow path that sequentially penetrates the refrigerant pressurization space R, the side hole 1462b of the valve body 1461 (specifically, the extension body 1461b), and the second hole 1462a of the valve body 1461, wherein the refrigerant pressurization space R is formed on the outer surface of the valve body 1461. Here, the refrigerant pressurization space R refers to the space surrounded by the outer surface of the valve body 1461 (specifically, the outer surface of the extended body 1461b), the pressurization surface 1461c, and the inner circumferential surface of the back pressure hole (specifically, the back pressure hole 141c1 on the first scroll side).

[0206] Below, refer to Figure 3 , Figures 8 to 11 The moving position of the back pressure valve 146 and the moving path of the refrigerant are explained.

[0207] When the compressor operates and the pressure in the compression chamber V rises (when the pressure in the compression chamber V is greater than the pressure in the back pressure chamber 160a), the compressed refrigerant in the compression chamber V moves to the back pressure port 141c2 on the second scroll side, and then flows into the first port 1462c formed in the compression chamber side end 1462a1 of the back pressure valve 146, while pressurizing the periphery of the first port 1462c (specifically, the inclined portion 1461b1). Due to the refrigerant pressure P, the back pressure valve 146 slides towards the back pressure chamber 160a inside the back pressure port 141c1 on the first scroll side. However, the back pressure valve 146 is limited by the valve limiting portion 1611b (see...). Figure 3The refrigerant cannot move to the plate-side back pressure hole 1611a. At this time, the compressed refrigerant through the second scroll plate-side back pressure hole 141c2 moves towards the back pressure chamber 160a along the first refrigerant flow path and the second refrigerant flow path. Specifically, the compressed refrigerant in the compression chamber V moves to the back pressure chamber 160a (the first refrigerant flow path is open) via the second scroll plate-side back pressure hole 141c2, and then sequentially through the first hole 1462c formed on the compression chamber-side end 1462a1 of the back pressure valve 146 and the second hole 1462a communicating with the first hole. Furthermore, the compressed refrigerant in the compression chamber V passes through the second scroll plate side back pressure hole 141c2, then through the gap created by the back pressure valve 146 sliding towards the back pressure chamber 160a (i.e., the gap formed between the outer surface of the inclined portion 1461b1 and the stepped portion 141c3), sequentially passing through the refrigerant pressurization space R, the side hole 1462b of the valve body 1461, and the second hole 1462a, and then smoothly moves to the back pressure chamber 160a (the second refrigerant flow path is open). When the pressure in the compression chamber V rises, the back pressure valve 146 does not hinder the pressure rise in the back pressure chamber 160a.

[0208] Furthermore, when the compressor stops operating and the pressure in the compression chamber V drops (when the pressure in the compression chamber V is less than the pressure in the back pressure chamber 160a), the compressed refrigerant in the back pressure chamber 160a flows through the plate-side back pressure hole 1611a into the second hole 1462a formed in the back pressure chamber side end 1462a2 of the back pressure valve 146, pressurizing the periphery of the second hole 1462a. Due to the refrigerant pressure P, the back pressure valve 146 slides towards the compression chamber V from inside the first scroll-side back pressure hole 141c1, and the inclined portion 1461b1 formed in the compression chamber side end 1462a1 of the back pressure valve 146 is positioned on the stepped portion 141c3. At this time, the compressed refrigerant passing through the plate-side back pressure hole 1611a moves to the compression chamber V along the first refrigerant flow path. Because the inclined portion 1461b1 of the back pressure valve 146 and the stepped portion 141c3 of the scroll-side back pressure hole 141c are in close contact, the compressed refrigerant passing through the plate-side back pressure hole 1611a cannot move to the compression chamber V along the second refrigerant flow path. Specifically, the compressed refrigerant in the back pressure chamber 160a passes through the plate-side back pressure hole 1611a, and then sequentially passes through the second hole 1462a formed at the back pressure chamber side end 1462a2 of the back pressure valve 146 and the first hole 1462c communicating with the second hole 1462a to move to the compression chamber V (the first refrigerant flow path is open). Furthermore, since the inclined portion 1461b1 of the back pressure valve 146 is in close contact with the stepped portion 141c3 of the scroll-side back pressure hole 141c, the compressed refrigerant flowing into the second hole 1462a of the back pressure valve 146 does not flow into the side hole 1462b (the second refrigerant flow path is closed) of the valve body 1461, but instead flows into the first hole 1462c and moves to the compression chamber V (the first refrigerant flow path is open). Therefore, the reduction in the flow path cross-sectional area reduces the amount of refrigerant moving to the compression chamber V, thereby causing the pressure in the back pressure chamber 160a to decrease slowly. As the pressure in the compression chamber V decreases, the back pressure valve 146 suppresses (improves) the pressure pulsation in the back pressure chamber 160a.

[0209] On the other hand, in another embodiment of the present invention, the scroll compressor can be configured such that the back pressure valve 146 is not disposed inside the scroll-side back pressure hole 141c as described above, but inside the plate-side back pressure hole 1611a. The back pressure valve 146 can move inside the plate-side back pressure hole 1611a. This embodiment will be described later in the back pressure chamber assembly 160.

[0210] The non-rotating scroll portion 142, located in the non-rotating scroll disk 140, extends axially along the rotation axis 125 from the bottom surface of the non-rotating end plate portion 141 facing the rotating scroll disk 150 to a predetermined height, and extends in a spiral shape, winding several times from the periphery of the discharge port 141a toward the non-rotating sidewall portion 143. The non-rotating scroll portion 142 is formed to correspond to the rotating scroll portion 152 described later, thereby forming two pairs of compression chambers V between the non-rotating scroll portion 142 and the rotating scroll portion 152.

[0211] The non-rotating sidewall portion 143 extends annularly from the bottom edge of the non-rotating endplate portion 141 along the axial direction of the rotation axis 125 to surround the non-rotating scroll portion 142. A radially penetrating intake port may be formed on one side of the outer peripheral surface of the non-rotating sidewall portion 143.

[0212] For example, the intake port can be formed as an arc shape extending a predetermined length in the circumferential direction among the plurality of guide protrusions 144 described later. Therefore, the refrigerant drawn in through the refrigerant intake pipe 117 can be rapidly drawn into the intake port through the guide protrusions 144.

[0213] The non-rotating vortex disk 140 is disposed on one side of the main frame 130 across the rotating vortex disk 150, and has a guide protrusion 144 extending radially from the outer peripheral surface (or outer side surface), thereby being supported to be axially movable relative to the main frame 130.

[0214] A guide insertion hole 144a is formed in the guide protrusion 144, extending axially along the rotation axis 125. A guide sleeve 137 for guiding the axial movement of the non-rotating vortex disk 140 is slidably inserted into the guide insertion hole 144a, and the guide sleeve 137 is supported on the main frame 130.

[0215] The guide protrusion 144 can extend radially from the lower outer peripheral surface of the non-rotating sidewall portion 143. The guide protrusion 144 can be formed as a ring, or it can be formed in a plurality of them at predetermined intervals in the circumferential direction. Here, we will focus on an example in which a plurality of guide protrusions 144 are formed at predetermined intervals in the circumferential direction.

[0216] Each of the plurality of guide protrusions 144 is provided with a guide insertion hole 144a extending axially along the rotation axis 125. The guide insertion hole 144a and the bolt fastening hole 136a provided in the frame fixing part 136 of the main frame 130 are coaxial.

[0217] A guide sleeve 137 can be inserted and configured in the guide insertion hole 144a, and is supported on the top surface of the frame fixing part 136 in the axial direction of the rotating shaft 125.

[0218] On the other hand, a portion of the plurality of guide protrusions 144 may be formed with keyways, into which the key of the cross ring 170 is slidably inserted radially.

[0219] Next, we will explain the vortex disk.

[0220] A rotary scroll 150 is positioned between the main frame 130 and the non-rotating scroll 140. The rotary scroll 150 is supported axially on the main frame 130 along the rotation shaft 125 and performs a rotary motion. Specifically, the rotary scroll 150 is coupled to the rotation shaft 125 and positioned on the top surface of the main frame 130. A cross ring 170, serving as a rotation prevention mechanism, is provided between the rotary scroll 150 and the main frame 130. Therefore, the rotary scroll 150 rotates relative to the non-rotating scroll 140 while its rotational motion is constrained.

[0221] The swirling scroll disk 150 of this invention includes a swirling end plate portion 151, a swirling scroll portion 152, and a rotating shaft connecting portion 153.

[0222] The gyratory end plate portion 151 is formed in a generally disk shape. The gyratory end plate portion 151 is supported axially on the scroll plate support portion 134 of the main frame 130. Thus, the gyratory end plate portion 151 and the scroll plate support portion 134 facing thereto form an axial support surface (not marked).

[0223] A groove (not shown) may be formed on the bottom surface of the rotary end plate portion 151 for other keys of the cross ring 170 to be slidably inserted.

[0224] The swirling scroll portion 152 and the non-swirling scroll portion 142 together form the compression chamber V. The swirling scroll portion 152 protrudes at a predetermined height and is formed in a spiral shape on the top surface of the swirling end plate portion 151 facing the non-swirling scroll disk 140. The swirling scroll portion 152 is formed to correspond to the non-swirling scroll portion 142 of the non-swirling scroll disk 140, so as to engage with the non-swirling scroll portion 142 and perform a swirling motion.

[0225] The rotating shaft joint 153 protrudes from the bottom surface of the swivel end plate 151 onto the main frame 130. The inner circumferential surface of the rotating shaft joint 153 is formed into a cylindrical shape, and a swivel bearing (not shown) formed by a bushing bearing can be pressed into the rotating shaft joint 153.

[0226] The sliding sleeve 155 is rotatably inserted into the interior of the swivel bearing, and the eccentric pin 125a of the aforementioned rotating shaft 125 is slidably inserted into the interior of the sliding sleeve 155. Therefore, the rotational force of the drive motor 120 is transmitted to the rotating shaft coupling 153 through the eccentric pin 125a of the rotating shaft 125 and the sliding sleeve 155. The rotational force transmitted to the rotating shaft coupling 153 is restricted by the cross ring 170 to cause the swivel disk 150 to rotate.

[0227] At this time, the eccentric pin 125a and the sliding sleeve 155 slide radially due to the centrifugal force generated by the swirling scroll 150 and the pressure difference in the compression chamber V, thereby changing the swirling radius of the swirling scroll 150. Thus, in the event of overcompression in the compression chamber V, overcompression can be eliminated by allowing leakage between the compression chambers V, thereby preventing damage to the scroll section in advance.

[0228] Next, the back pressure chamber assembly will be described.

[0229] Figure 1 The back pressure chamber assembly 160 of the embodiment of the present invention shown is disposed between the high and low pressure separation plate 115 and the non-rotating scroll plate 140, and has an annular back pressure chamber 160a. Specifically, the back pressure chamber assembly 160 is disposed above the non-rotating scroll plate 140. Therefore, the back pressure of the back pressure chamber 160a (more precisely, the force acting on the back pressure chamber 160a) acts on the non-rotating scroll plate 140. In other words, the non-rotating scroll plate 140 is subjected to pressure in the direction of the rotating scroll plate 150 due to the back pressure, thereby sealing the compression chamber V.

[0230] The back pressure chamber assembly 160 of this embodiment of the invention includes a back pressure plate 161 and a floating plate 165.

[0231] The back pressure plate 161 is engaged with the top surface of the non-rotating end plate portion 141. The floating plate 165 is slidably engaged with the back pressure plate 161 and together with the back pressure plate 161 forms a back pressure chamber 160a.

[0232] The back pressure plate 161 includes a fixed plate portion 1611, a first annular wall portion 1612, and a second annular wall portion 1613.

[0233] The fixing plate portion 1611 is formed into a hollow annular plate shape.

[0234] Refer again Figures 2 to 4 The back pressure chamber assembly 160, specifically, includes a fixed plate portion 1611 including a plate-side back pressure hole 1611a formed through the axial direction of the rotation axis 125.

[0235] The plate-side back pressure hole 1611a is formed in the back pressure chamber assembly 160, specifically in the fixing plate portion 1611 of the back pressure plate 161. The plate-side back pressure hole 1611a is a refrigerant flow path connecting the back pressure chamber 160a and the scroll plate-side back pressure hole 141c.

[0236] A plate-side back pressure hole 1611a is formed by penetrating from the back pressure chamber 160a toward the direction where the non-rotating scroll plate 140 is arranged. Furthermore, the plate-side back pressure hole 1611a communicates with the compression chamber V through the scroll plate-side back pressure hole 141c. Therefore, the plate-side back pressure hole 1611a and the scroll plate-side back pressure hole 141c together connect the compression chamber V and the back pressure chamber 160a. During compressor operation, the compressed refrigerant in the compression chamber V moves to the back pressure chamber 160a sequentially through the scroll plate-side back pressure hole 141c and the plate-side back pressure hole 1611a. When the compressor stops operating, the refrigerant in the back pressure chamber 160a moves to the compression chamber V sequentially through the plate-side back pressure hole 1611a and the scroll plate-side back pressure hole 141c.

[0237] A plate-side back pressure hole 1611a extends from the side of the back pressure chamber assembly 160 facing the non-rotating scroll plate 140 into the back pressure chamber 160a. Here, one side of the back pressure chamber assembly 160 refers to the side of the fixed plate portion 1611, which is the bottom surface facing the non-rotating scroll plate 140.

[0238] The central axis bc of the plate-side back pressure hole 1611a and the central axis fc of the aforementioned scroll disk-side back pressure hole 141c can be formed on the same axis (refer to...). Figure 3 Therefore, the plate-side back pressure hole 1611a and the scroll-side back pressure hole 141c are connected to each other, and the refrigerant can move smoothly along the plate-side back pressure hole 1611a and the scroll-side back pressure hole 141c.

[0239] The inner diameter of the plate-side back pressure hole 1611a is smaller than the inner diameter of the scroll plate-side back pressure hole 141c. As a result, one side 1611b (valve limiting part 1611b) of the back pressure chamber assembly 160 covers a portion of the scroll plate-side back pressure hole 141c.

[0240] When the back pressure valve 146 is disposed inside the scroll plate-side back pressure hole 141c, the back pressure valve 146 overlaps axially with the valve limiting portion 1611b covering the scroll plate-side back pressure hole 141c. Therefore, the valve limiting portion 1611b restricts the movement of the back pressure valve 146. Specifically, the back pressure valve 146 is restricted to moving only inside the scroll plate-side back pressure hole 141c due to the valve limiting portion 1611b, and is restricted from moving out of the scroll plate-side back pressure hole 141c to the plate-side back pressure hole 1611a.

[0241] According to another embodiment of the present invention, the plate-side back pressure hole 1611a may be eccentrically configured with the scroll disk-side back pressure hole 141c and formed to communicate with the scroll disk-side back pressure hole 141c (see reference). Figure 4 The plate-side backpressure hole 1611a can be configured such that its central axis bc is separated from the central axis fc of the scroll plate-side backpressure hole 141c by a predetermined distance e, and is formed to communicate with the scroll plate-side backpressure hole 141c. In other words, the plate-side backpressure hole 1611a can be formed such that a portion of it communicates with a portion of the scroll plate-side backpressure hole 141c. That is, one side 1611b′ (valve limiting part 1611b′) of the backpressure chamber assembly 160 covers a portion of the scroll plate-side backpressure hole 141c, and the backpressure valve 146 overlaps with the valve limiting part 1611b′ in the axial direction. Through the valve limiting part 1611b′, the backpressure valve 146 can only move inside the scroll plate-side backpressure hole 141c, and is restricted from moving out of the scroll plate-side backpressure hole 141c to the plate-side backpressure hole 1611a. Here, the scroll plate side back pressure hole 141c specifically refers to the first scroll plate side back pressure hole 141c1. Furthermore, the back pressure chamber assembly 160 specifically refers to the fixing plate portion 1611 of the back pressure plate 161.

[0242] On the other hand, unlike the foregoing, in another embodiment of the scroll compressor of the present invention, the back pressure valve 146 may not be disposed inside the scroll-side back pressure hole 141c, but may be disposed inside the plate-side back pressure hole 1611a. The back pressure valve 146 may be movable inside the plate-side back pressure hole 1611a. Figures 12 to 14 Another embodiment is shown where the back pressure valve 146 is disposed inside the plate-side back pressure hole 1611a.

[0243] The following is an explanation Figures 12 to 14 In the process of the scroll compressor of another embodiment of the present invention shown, the process is related to... Figures 1 to 11 The different configurations or parts of the scroll compressor of the present invention shown in the embodiments are described in detail, and are used in... Figures 1 to 11 The description of the scroll compressor in the embodiment of the present invention is used in place of the description of the same or similar components or parts.

[0244] Reference Figures 12 to 14 As shown, the back pressure valve 146 can be configured to be disposed inside the plate-side back pressure hole 1611a. The back pressure valve 146 can slide inside the plate-side back pressure hole 1611a.

[0245] The plate-side back pressure hole 1611a includes: a first plate-side back pressure hole 1611a1, which communicates with the back pressure chamber 160a; and a second plate-side back pressure hole 1611a2, one end of which communicates with the first plate-side back pressure hole 1611a1, and the other end of which communicates with the vortex disk-side back pressure hole 141c.

[0246] Specifically, the first plate-side back pressure hole 1611a1 communicates with the back pressure chamber 160a and is formed by penetrating through the back pressure chamber 160a to a predetermined depth. Furthermore, the second plate-side back pressure hole 1611a2 is formed by penetrating through the first plate-side back pressure hole 1611a1 to the side of the back pressure chamber assembly 160 facing the non-rotating scroll plate 140. Here, one side of the back pressure chamber assembly 160 refers to the side of the fixed plate portion 1611, which is the bottom surface facing the non-rotating scroll plate 140.

[0247] The inner diameter of the first plate-side back pressure hole 1611a1 is larger than the inner diameter of the second plate-side back pressure hole 1611a2. A plate-side step portion 1611c is formed between the first plate-side back pressure hole 1611a1 and the second plate-side back pressure hole 1611a2 to restrict the movement of the back pressure valve 146. Specifically, the plate-side step portion 1611c is formed in the portion (boundary region) connecting the first plate-side back pressure hole 1611a1 and the second plate-side back pressure hole 1611a2, and is formed inclined toward the second plate-side back pressure hole 1611a2. As a result, the back pressure valve 146 can be disposed inside the first plate-side back pressure hole 1611a1 and move, and because it is disposed in the plate-side step portion 1611c, its movement toward the second plate-side back pressure hole 1611a2 is restricted.

[0248] At one end of the back pressure chamber 160a side of the first plate-side back pressure hole 1611a1, there is a plate-side valve limiting part 1611d that restricts the movement of the back pressure valve 146.

[0249] For example, the plate-side valve limiting part 1611d refers to a C-ring or a drilled screw, etc. After the back pressure valve 146 is inserted into the first plate-side back pressure hole 1611a1, the plate-side valve limiting part 1611d is fastened to one end of the first plate-side back pressure hole 1611a1. Although the back pressure valve 146 can slide inside the first plate-side back pressure hole 1611a1, it cannot disengage from the first plate-side back pressure hole 1611a1 and move to the back pressure chamber 160a.

[0250] The plate-side valve limiting part 1611d includes a through hole (not shown). Here, a through hole refers to, for example, a C-ring or a through hole formed in a drilled screw. Through the through hole, refrigerant moves to the back pressure chamber 160a or to the compression chamber V.

[0251] At both ends of the second plate side back pressure hole 1611a2, the end located on the opposite side of the back pressure chamber 160a is connected to the vortex disk side back pressure hole 141c.

[0252] The central axes of the first plate side back pressure hole 1611a1 and the second plate side back pressure hole 1611a2 can be coaxial with the central axis of the scroll plate side back pressure hole 141c. Therefore, the second plate side back pressure hole 1611a2 and the scroll plate side back pressure hole 141c are in communication with each other, and the refrigerant can move smoothly along the second plate side back pressure hole 1611a2 and the scroll plate side back pressure hole 141c.

[0253] The inner diameter of the second plate side back pressure hole 1611a2 can be the same as the inner diameter of the scroll plate side back pressure hole 141c. Therefore, since the flow path cross-sectional area is not reduced, the refrigerant can move without obstruction. Alternatively, the inner diameter of the second plate side back pressure hole 1611a2 can be larger than the inner diameter of the scroll plate side back pressure hole 141c. Therefore, the compressed refrigerant in the compression chamber V can move smoothly toward the second plate side back pressure hole 1611a2 due to the increased flow path cross-sectional area. Furthermore, the inflow of compressed refrigerant in the back pressure chamber 160a toward the scroll plate side back pressure hole is obstructed due to the reduced flow path cross-sectional area. As a result, the amount of refrigerant moving into the compression chamber V decreases, and the pressure in the back pressure chamber 160a drops slowly, thus suppressing pressure pulsations in the back pressure chamber 160a.

[0254] Furthermore, according to another embodiment of the present invention, the first plate-side back pressure hole 1611a1 and the second plate-side back pressure hole 1611a2 can be configured to be eccentric to each other with respect to the scroll plate-side back pressure hole 141c. In other words, one end of the second plate-side back pressure hole 1611a2 opposite to the back pressure chamber 160a can be formed to be eccentric to the scroll plate-side back pressure hole 141c and communicate with the scroll plate-side back pressure hole 141c. Specifically, the central axis of the second plate-side back pressure hole 1611a2 can be configured to be spaced apart from the central axis of the scroll plate-side back pressure hole 141c by a predetermined distance, and one end of the second plate-side back pressure hole 1611a2 communicates with the scroll plate-side back pressure hole 141c.

[0255] In another embodiment of the present invention, a scroll compressor is provided with a back pressure valve 146. The back pressure valve 146 moves along the length of the back pressure orifice within the back pressure chamber 160a due to the pressure difference between the compression chamber V and the back pressure chamber 160a, thereby changing the flow path area of ​​the back pressure orifice. Here, the flow path area refers to the area of ​​the refrigerant flow path for refrigerant movement. The back pressure valve 146 is disposed inside the back pressure orifice and changes the area of ​​the refrigerant flow path by moving along the inside of the back pressure orifice, thereby improving the pressure pulsation of the back pressure chamber 160a.

[0256] The back pressure valve 146 can be inserted into and moved within a back pressure hole (specifically, a plate-side back pressure hole 1611a). Specifically, the back pressure valve 146 can be inserted into and slid within the back pressure hole (plate-side back pressure hole 1611a). The plate-side back pressure hole 1611a represents a first plate-side back pressure hole 1611a1. That is, the back pressure valve 146 is inserted into the first plate-side back pressure hole 1611a1 and slides along the length of the first plate-side back pressure hole 1611a1, thereby changing the area of ​​the refrigerant flow path.

[0257] The back pressure valve 146 suppresses pressure pulsations in the back pressure chamber 160a. Specifically, when the compressor operates and the pressure in the compression chamber V rises (when the pressure in compression chamber V is greater than the pressure in the back pressure chamber 160a), the back pressure valve 146 increases the space in the refrigerant flow path, allowing the compressed refrigerant in the compression chamber V to easily move to the back pressure chamber 160a. When the compressor stops and the pressure in the compression chamber V drops (when the pressure in the compression chamber V is less than the pressure in the back pressure chamber 160a), the back pressure valve 146 reduces the space in the refrigerant flow path, preventing the compressed refrigerant in the back pressure chamber 160a from easily moving to the compression chamber V. Therefore, when the pressure in the compression chamber V rises, the back pressure valve 146 does not hinder the pressure rise in the back pressure chamber 160a, and when the pressure in the compression chamber V drops, the back pressure valve 146 suppresses pressure pulsations in the back pressure chamber 160a.

[0258] Because the back pressure valve 146 of the scroll compressor in another embodiment of the present invention is similar to the aforementioned... Figures 1 to 11 The back pressure valve 146 of the scroll compressor shown in the embodiment of the present invention is the same; therefore, the specific description of the back pressure valve 146 is replaced by the foregoing content.

[0259] The cross-sectional shape of the main body 1461a of the back pressure valve 146 can be formed to correspond to the cross-sectional shape of the back pressure hole 1611a1 on the first plate side. Specifically, the cross-sectional shape of the radially outer surface of the main body 1461a can be formed to correspond to the radially cross-sectional shape of the back pressure hole 1611a1 on the first plate side. For example, if the radially cross-sectional shape of the back pressure hole 1611a1 on the first plate side is circular, the radially cross-sectional shape of the outer surface of the main body 1461a can also be formed to be circular. Therefore, if the back pressure hole 1611a1 on the first plate side is formed to be cylindrical, the main body 1461a can be formed to be cylindrical with a predetermined length.

[0260] The diameter Ad of the main body 1461a is smaller than the inner diameter of the first plate-side back pressure hole 1611a1, so that the main body 1461a can slide along the length direction of the first plate-side back pressure hole 1611a1 inside the first plate-side back pressure hole 1611a1. However, it can be considered that the gap (slit) between the outer surface of the main body 1461a and the inner surface of the first plate-side back pressure hole 1611a1 is very small. Therefore, the amount of refrigerant moving through the gap (slit) can be negligible compared to the amount of refrigerant moving through the refrigerant flow path through the back pressure valve 146. Thus, the main body 1461a can play a guiding role when the back pressure valve 146 moves along the length direction of the first plate-side back pressure hole 1611a1.

[0261] Furthermore, while the cross-sectional shape of the extension body 1461b of the back pressure valve 146 can be formed to correspond to the cross-sectional shape of the first plate-side back pressure hole 1611a1, it is not limited to this. In other words, while the cross-sectional shape of the radially outer surface of the extension body 1461b can be formed to correspond to the radially cross-sectional shape of the first plate-side back pressure hole 1611a1, it is not limited to this. For example, if the radially cross-sectional shape of the first plate-side back pressure hole 1611a1 is circular, while the radially outer surface of the extension body 1461b can be circular, it is not limited to a circle and can be formed into other shapes besides a circle.

[0262] The diameter Bd of the extension body 1461b is larger than the inner diameter of the second plate-side back pressure hole 1611a2. Therefore, the back pressure valve 146 cannot move into the interior of the second plate-side back pressure hole 1611a2. Furthermore, when the compressor stops and the pressure in the compression chamber V decreases, the back pressure valve 146 is positioned on the plate-side step portion 1611c and is in close contact with the plate-side step portion 1611c due to the compressed refrigerant in the back pressure chamber 160a. Therefore, the area of ​​the refrigerant flow path changes.

[0263] Furthermore, although the pressure surface 1461c of the back pressure valve 146 can be formed inclined toward the back pressure hole 1611a2 on the second plate side, it is not limited to this and can be formed without inclination. Therefore, the efficiency of selecting the shape of the pressure surface 1461c can be improved.

[0264] In the space (referred to as the "refrigerant pressurization space R′") surrounded by the pressurizing surface 1461c, the inner peripheral surface of the first plate side back pressure hole 1611a1, and the outer surface of the extension body 1461b, compressed refrigerant in the compression chamber V flows in. The flowing refrigerant not only pressurizes the pressurizing surface 1461c to make the valve body 1461 slide toward the back pressure chamber 160a, but also flows in from the side hole 1462b formed in the extension body 1461b, which will be described later.

[0265] In addition, the side hole 1462b of the back pressure valve 146 can be formed in more than one way. Figures 12 to 14 An embodiment with one side hole 1462b is shown. Although not shown, two or more side holes 1462b may be formed.

[0266] A plurality of side holes 1462b can be formed at equal intervals along the circumferential direction on the side of the valve body 1461 (specifically, the extension body 1461b). Therefore, the refrigerant can move uniformly into the refrigerant pressurization space R′ and uniformly pressurize the pressurization surface 1461c. Furthermore, to guide the smooth flow of the refrigerant, the inner diameter of each of the plurality of side holes 1462b can be made smaller than the inner diameter of the second hole 1462a, so that the amount of refrigerant passing through the plurality of side holes 1462b is less than or equal to the amount of refrigerant passing through the second hole 1462a.

[0267] Furthermore, the inner diameter of the first hole 1462c of the back pressure valve 146 is smaller than the inner diameter of the second plate-side back pressure hole 1611a2. Therefore, when the back pressure valve 146 is installed on the plate-side stepped portion 1611c, the inflow of compressed refrigerant moving from the compression chamber V to the second plate-side back pressure hole 1611a2 into the first hole 1462c is restricted due to the reduction in the flow path cross-sectional area. The compressed refrigerant pressurizes the compression chamber-side end 1462a1 of the valve body 1461, thereby causing the valve body 1461 to slide toward the back pressure chamber 160a.

[0268] Furthermore, the inclined portion 1461b1 of the back pressure valve 146 is disposed on the plate-side stepped portion 1611c. Thus, the back pressure valve 146 can be stably supported on the plate-side back pressure hole 1611a. Additionally, the inclined portion 1461b1 is in close contact with the plate-side stepped portion 1611c due to the compressed refrigerant in the back pressure chamber 160a. Therefore, the compressed refrigerant in the back pressure chamber 160a moves to the compression chamber V through the first refrigerant flow path described later.

[0269] The back pressure valve 146 includes a plurality of refrigerant flow paths. That is, a plurality of refrigerant flow paths are formed in the valve body 1461 of the back pressure valve 146.

[0270] Firstly, in a scroll compressor according to another embodiment of the present invention, a first refrigerant flow path is provided that extends axially through the valve body 1461. The first refrigerant flow path refers to a first hole 1462c and a second hole 1462a formed by connecting the compression chamber side end 1462a1 of the valve body 1461 to the back pressure chamber side end 1462a2.

[0271] Furthermore, in another embodiment of the scroll compressor of the present invention, a second refrigerant flow path is provided, which sequentially penetrates the outer surface and interior of the valve body 1461. Specifically, the scroll compressor is provided with a second refrigerant flow path that sequentially penetrates the refrigerant pressurization space R′ and the interior of the valve body 1461, wherein the refrigerant pressurization space R′ is formed on the outer surface of the valve body 1461. In other words, the second refrigerant flow path is a flow path that sequentially penetrates the refrigerant pressurization space R′, the side hole 1462b of the valve body 1461 (specifically, the extension body 1461b), and the second hole 1462a of the valve body 1461, wherein the refrigerant pressurization space R′ is formed on the outer surface of the valve body 1461. Here, the refrigerant pressurization space R′ refers to the space surrounded by the inner circumferential surface of the outer surface of the valve body 1461 (specifically, the outer surface of the extension body 1461b), the pressurization surface 1461c, and the back pressure hole (specifically, the first plate side back pressure hole 1611a1).

[0272] Below, refer to Figures 12 to 14 The moving position of the back pressure valve 146 and the moving path of the refrigerant are explained.

[0273] When the compressor operates, causing the pressure in the compression chamber V to rise (when the pressure in the compression chamber V is greater than the pressure in the back pressure chamber 160a), the compressed refrigerant in the compression chamber V passes sequentially through the scroll-side back pressure hole 141c and the second plate-side back pressure hole 1611a2, and simultaneously flows into the first hole 1462c formed in the compression chamber-side end 1462a1 of the back pressure valve 146, pressurizing the periphery (specifically, the inclined portion 1461b1) of the first hole 1462c. Due to the increased pressure of the refrigerant, the back pressure valve 146 slides towards the back pressure chamber 160a inside the first plate-side back pressure hole 1611a1. However, the back pressure valve 146 cannot move to the back pressure chamber 160a due to the plate-side valve limiting portion 1611d. At this time, the compressed refrigerant through the second plate-side back pressure hole 1611a2 moves to the back pressure chamber 160a along the first refrigerant flow path and the second refrigerant flow path. Specifically, the compressed refrigerant in the compression chamber V, after passing through the second plate-side back pressure hole 1611a2, sequentially passes through the first hole 1462c formed in the compression chamber-side end 1462a1 of the back pressure valve 146 and the second hole 1462a communicating with the first hole 1462c, and moves towards the back pressure chamber 160a (the first refrigerant flow path is open). Furthermore, after passing through the second plate-side back pressure hole 1611a2, the compressed refrigerant in the compression chamber V, after passing through the gap created by the sliding of the back pressure valve 146 towards the back pressure chamber 160a (i.e., the gap formed between the outer surface of the inclined portion 1461b1 and the plate-side step portion 1611c), sequentially passes through the refrigerant pressurization space R′, the side hole 1462b of the valve body 1461, and the second hole 1462a, and then smoothly moves towards the back pressure chamber 160a (the second refrigerant flow path is open). When the pressure in compression chamber V rises, back pressure valve 146 will not prevent the pressure in back pressure chamber 160a from rising.

[0274] Furthermore, when the compressor stops and the pressure in the compression chamber V drops (when the pressure in the compression chamber V is less than the pressure in the back pressure chamber 160a), the compressed refrigerant in the back pressure chamber 160a flows into the second hole 1462a formed in the back pressure chamber side end 1462a2 of the back pressure valve, pressurizing the periphery of the second hole 1462a. Due to the increased pressure of the refrigerant, the back pressure valve 146 slides towards the compression chamber V inside the first plate-side back pressure hole 1611a1, and the inclined portion 1461b1 formed in the compression chamber side end 1462a1 of the back pressure valve 146 is positioned on the plate-side step portion 1611c. At this time, the compressed refrigerant in the back pressure chamber 160a moves to the compression chamber V along the first refrigerant flow path, and because the inclined portion 1461b1 of the back pressure valve 146 is in close contact with the plate-side step portion 1611c, the compressed refrigerant in the back pressure chamber 160a cannot move to the compression chamber V along the second refrigerant flow path. Specifically, the compressed refrigerant in the back pressure chamber 160a sequentially passes through a second hole 1462a formed at the back pressure chamber side end 1462a2 of the back pressure valve 146 and a first hole 1462c communicating with the second hole 1462a to move into the compression chamber V (where the first refrigerant flow path is open). Furthermore, since the inclined portion 1461b1 of the back pressure valve 146 is in close contact with the plate-side stepped portion 1611c, the compressed refrigerant flowing in from the second hole 1462a of the back pressure valve 146 does not flow in from the side hole 1462b (where the second refrigerant flow path is closed) of the valve body 1461, but instead flows in from the first hole 1462c and then moves into the compression chamber V (where the first refrigerant flow path is open). Therefore, the amount of refrigerant moving into the compression chamber V decreases due to the reduced flow path cross-sectional area, resulting in a slow decrease in pressure in the back pressure chamber 160a. When the pressure in the compression chamber V decreases, the back pressure valve 146 suppresses (improves) the pressure pulsation in the back pressure chamber 160a.

[0275] On the other hand, the first annular wall portion 1612 and the second annular wall portion 1613 surround the inner and outer peripheral surfaces of the fixed plate portion 1611 on the top surface of the fixed plate portion 1611. Therefore, the outer peripheral surface of the first annular wall portion 1612, the inner peripheral surface of the second annular wall portion 1613, the top surface of the fixed plate portion 1611, and the bottom surface of the floating plate 165 form an annular back pressure chamber 160a.

[0276] An intermediate discharge port 1612a communicating with the discharge port 141a of the non-rotating scroll plate 140 is formed in the first annular wall portion 1612. A valve guide groove 1612b is formed inside the intermediate discharge port 1612a, into which a check valve (hereinafter referred to as the discharge valve) 145 is slidably inserted. A backflow prevention hole 1612c is formed at the center of the valve guide groove 1612b. Therefore, the discharge valve 145 prevents the discharged refrigerant from flowing back into the compression chamber V by selectively opening and closing the space between the discharge port 141a and the intermediate discharge port 1612a.

[0277] The floating plate 165 is formed in an annular shape and can be made of a lighter material than the back pressure plate 161. Therefore, the floating plate 165 moves axially relative to the back pressure plate 161 along the axis of rotation according to the pressure of the back pressure chamber 160a, and engages with the lower side of the high-low pressure separation plate 115 in a detachable manner. For example, if the floating plate 165 contacts the high-low pressure separation plate 115, it acts as a seal to prevent the discharged refrigerant from leaking into the low-pressure section 110a and instead discharges into the high-pressure section 110b.

[0278] The scroll compressor of the present invention described above performs the following operations.

[0279] If a power source is applied to the stator coil 1212 of the stator 121, the rotor 122 rotates together with the rotating shaft 125. As a result, the swirling scroll 150 coupled with the rotating shaft 125 rotates relative to the non-swirling scroll 140, forming two pairs of compression chambers V between the swirling scroll portion 152 and the non-swirling scroll portion 142.

[0280] As the vortex disk 150 rotates, the compression chamber V moves from the outside to the inside while its volume gradually decreases. At this time, refrigerant is drawn into the low-pressure section 110a of the housing 110 through the refrigerant suction pipe 117. A portion of the refrigerant is directly drawn into each suction chamber (unmarked) that constitutes the two compression chambers V, while the remaining portion moves toward the drive motor 120 and, after cooling the drive motor 120, is drawn into the suction chamber (unmarked).

[0281] The refrigerant drawn into the suction chamber (unmarked) undergoes a series of processes, being compressed as it moves along the compression chamber V to the intermediate and discharge chambers (unmarked). The refrigerant moving towards the discharge chamber (unmarked) pushes the discharge valve 145 and is discharged through the discharge port 141a and intermediate discharge port 1612a to the high-pressure section 110b. After filling the high-pressure section 110b, the refrigerant is discharged through the refrigerant discharge pipe 118 and then through the condenser of the refrigeration cycle.

[0282] At this time, a portion of the refrigerant compressed in the intermediate pressure chamber (unmarked) is bypassed from the intermediate pressure chamber (unmarked) constituting each compression chamber V to the high pressure section 110b through the bypass hole 141b before reaching the discharge port 141a. This prevents the refrigerant from being overcompressed to a set pressure in the compression chamber V.

[0283] Additionally, another portion of the refrigerant compressed in the intermediate pressure chamber (unmarked) flows into the back pressure chamber 160a through the back pressure hole 141c on the scroll side before reaching the discharge port 141a, thus creating an intermediate pressure in the back pressure chamber 160a. As a result, the floating plate 165 rises towards the high-low pressure separation plate 115 and comes into close contact with the sealing plate 1151 provided on the high-low pressure separation plate 115. The back pressure plate 161, due to the pressure in the back pressure chamber 160a, experiences pressure towards the non-rotating scroll 140 and descends, thereby pressurizing the non-rotating scroll 140 towards the rotating scroll 150 side.

[0284] At this time, as the floating plate 165 rises and comes into close contact with the sealing plate 1151, the high-pressure section 110b and the low-pressure section 110a of the housing 110 separate, thereby preventing the refrigerant discharged from each compression chamber V to the high-pressure section 110b from flowing back into the low-pressure section 110a. Conversely, as the back pressure plate 161 descends toward the non-rotating scroll plate 140, the non-rotating scroll plate 140 comes into close contact with the rotating scroll plate 150, thereby preventing the compressed refrigerant from leaking from the high-pressure side compression chamber constituting the intermediate pressure chamber to the low-pressure side compression chamber.

[0285] During the operation of the aforementioned scroll compressor, since the existing scroll compressor lacks the components that can regulate the back pressure in the refrigerant flow path connecting the compression chamber V and the back pressure chamber 160a, pulsation continuously occurs in the back pressure chamber 160a.

[0286] Therefore, in the scroll compressor of this embodiment of the invention, a back pressure valve 146 is provided inside the scroll-side back pressure hole 141c or the plate-side back pressure hole 1611a, which serves as a refrigerant flow path, to change the flow path area of ​​the scroll-side back pressure hole 141c or the plate-side back pressure hole 1611a. As a result, when the compressor stops and the pressure in the compression chamber V drops, the compressed refrigerant in the back pressure chamber 160a can move to the compression chamber V through the first hole 1462c and the second hole 1462a (first refrigerant flow path) of the back pressure valve 146, thereby suppressing (improving) the pressure pulsation in the back pressure chamber 160a.

[0287] Figure 15 and Figure 16 Pressure pulsation in a scroll compressor using the back pressure valve 146 of the present invention is shown. Specifically, during operation of a scroll compressor in an embodiment where the back pressure valve 146 is configured in the scroll-side back pressure port 141c (specifically, the first scroll-side back pressure port 141c1), pulsation in the back pressure chamber 160a is improved.

[0288] Reference Figure 15 and Figure 16It can be confirmed that in the intermediate pressure opening and closing range, the pressure of the back pressure chamber 160a when the back pressure valve 146 is used is less than the pressure of the back pressure chamber 160a when the back pressure valve 146 is not used. Therefore, it can be confirmed that the pressure amplitude in the back pressure chamber 160a decreases according to the crank angle, thereby suppressing pressure pulsation.

Claims

1. A scroll compressor, wherein, include: case; A high-low pressure separation plate is fixed inside the housing, dividing the space into a low-pressure section that forms the intake space and a high-pressure section that forms the discharge space. The main frame is fixed inside the housing and is disposed in the low-pressure section; The vortex disk is axially supported by the main frame and performs a gyratory motion. The non-rotating scroll disk is configured to move axially relative to one side of the main frame across the rotating scroll disk, forming a compression chamber together with the rotating scroll disk; The back pressure chamber assembly, disposed between the high and low pressure separation plate and the non-rotating vortex disk, has an annular back pressure chamber; as well as A back pressure hole is provided in the non-rotating vortex disk and the back pressure chamber assembly, connecting the compression chamber and the back pressure chamber; It is equipped with a back pressure valve. The back pressure valve includes: A valve body, movably disposed inside the back pressure port, is formed extending along the axial direction; and A hole is formed in the valve body along the axial direction; The orifice of the back pressure valve includes: The first hole is formed at the end of the compression chamber side of the valve body; A second hole, communicating with the first hole, the inner diameter of the second hole being expanded relative to the first hole, forming from the first hole to the back pressure chamber side end of the valve body; and A side hole, which communicates with the second hole and is formed between the compression chamber side end and the back pressure chamber side end; When the pressure in the compression chamber is higher than the pressure in the back pressure chamber, the first hole, the second hole, and the side hole are opened. When the pressure in the compression chamber is lower than the pressure in the back pressure chamber, the first and second holes are opened, while the side holes are closed.

2. The scroll compressor according to claim 1, wherein, The inner diameter of the side hole is larger than the inner diameter of the first hole.

3. The scroll compressor according to claim 1, wherein, The valve body includes: The main body is located on the back pressure chamber side; An extension body, extending axially from the main body, is disposed on the compression chamber side; and A pressure surface is formed in the boundary region between the main body and the extended body; The radial cross-sectional area of ​​the main body is greater than the radial cross-sectional area of ​​the extended body.

4. The scroll compressor according to claim 3, wherein, The first hole is formed at the compression chamber side end of the extended body. The second hole is formed from the first hole to the back pressure chamber side end of the main body.

5. The scroll compressor according to claim 4, wherein, The side hole is formed on the side of the valve body. The side hole is formed on the side between the compression chamber side end of the extended body and the pressurized surface. The inner diameter of the side hole is larger than the inner diameter of the first hole.

6. The scroll compressor according to claim 4, wherein, The valve body includes an inclined portion formed at the compression chamber side end of the extended body. The inclined portion is formed such that its outer diameter gradually decreases along the periphery of the first hole.

7. The scroll compressor according to claim 4, wherein, The back pressure port includes: A back pressure hole is formed on the non-rotating scroll disk and communicates with the compression chamber; and A plate-side back pressure hole is formed in the back pressure chamber assembly and communicates with the scroll disk-side back pressure hole and the back pressure chamber. The back pressure valve is disposed inside the back pressure hole on the scroll plate side and slides.

8. The scroll compressor according to claim 7, wherein, A portion of the back pressure hole on the scroll plate side is covered by one side of the back pressure chamber assembly. The back pressure valve and the side of the back pressure chamber assembly that covers the back pressure hole on the scroll plate overlap in the axial direction.

9. The scroll compressor according to claim 7, wherein, The vortex disk side back pressure hole includes: The first vortex disk side back pressure hole is connected to the plate side back pressure hole; and The second scroll plate side back pressure hole has one end connected to the first scroll plate side back pressure hole and the other end connected to the compression chamber. The inner diameter of the back pressure hole on the first scroll plate side is larger than the inner diameter of the back pressure hole on the second scroll plate side. The back pressure valve is inserted into the back pressure hole on the side of the first scroll plate.

10. The scroll compressor according to claim 9, wherein, A stepped portion is formed between the first scroll plate side back pressure hole and the second scroll plate side back pressure hole to restrict the movement of the back pressure valve. The stepped portion is formed at an inclination toward the back pressure hole on the side of the second vortex disk.

11. The scroll compressor according to claim 9, wherein, The inner diameter of the first hole is smaller than the inner diameter of the back pressure hole on the second scroll plate side.

12. The scroll compressor according to claim 9, wherein, The diameter of the extended body is greater than the inner diameter of the back pressure hole on the second vortex disk side.

13. A scroll compressor, wherein, include: case; A high-low pressure separation plate is fixed inside the housing, dividing the space into a low-pressure section that forms the intake space and a high-pressure section that forms the discharge space. The main frame is fixed inside the housing and is disposed in the low-pressure section; The vortex disk is axially supported by the main frame and performs a gyratory motion. The non-rotating scroll disk is configured to move axially relative to one side of the main frame across the rotating scroll disk, forming a compression chamber together with the rotating scroll disk; The back pressure chamber assembly, disposed between the high and low pressure separation plate and the non-rotating vortex disk, has an annular back pressure chamber; as well as A back pressure hole is provided in the non-rotating vortex disk and the back pressure chamber assembly, connecting the compression chamber and the back pressure chamber; A back pressure valve is provided inside the back pressure orifice. The back pressure valve moves along the length of the back pressure orifice due to the pressure difference between the compression chamber and the back pressure chamber, thereby changing the flow path area of ​​the back pressure orifice. The back pressure valve includes: The valve body, extending along the axial direction, has a hollow shape; and A hole extends through the inner side of the valve body along the axial direction; The orifice of the back pressure valve includes: A first hole is formed at the end of the compression chamber side of the valve body; and The second hole communicates with the first hole, and the inner diameter of the second hole is expanded relative to the first hole, forming from the first hole to the back pressure chamber side end of the valve body; The back pressure valve includes a side hole that communicates with the second hole and is formed between the compression chamber side end and the back pressure chamber side end; The valve body is inserted into the back pressure hole and slides, forming a first refrigerant flow path that penetrates the valve body axially and a second refrigerant flow path that penetrates the outer surface and interior of the valve body; The first refrigerant flow route is formed by the first hole and the second hole that are connected to each other; The second refrigerant flow route is formed by the outer surface of the compression chamber side end of the valve body, which communicates with the inner circumferential surface of the back pressure hole, the side hole, and the second hole; When the pressure in the compression chamber is higher than the pressure in the back pressure chamber, the first refrigerant flow path and the second refrigerant flow path are opened. When the pressure in the compression chamber is lower than the pressure in the back pressure chamber, the first refrigerant flow path is opened, while the second refrigerant flow path is closed.

14. The scroll compressor according to claim 13, wherein, The valve body includes: The main body is located on the back pressure chamber side; An extension body, extending axially from the main body, is disposed on the compression chamber side; and A pressure surface is formed in the boundary region between the main body and the extended body.

15. The scroll compressor according to claim 13, wherein, The inner diameter of the side hole is larger than the inner diameter of the first hole.

16. The scroll compressor according to claim 13, wherein, The valve body includes: The main body is located on the back pressure chamber side; An extension body, extending axially from the main body, is disposed on the compression chamber side; and The inclined portion is formed at an inclined position at the compression chamber side end of the extended body; The inclined portion is formed such that its outer diameter gradually decreases along the periphery of the first hole.

17. The scroll compressor according to claim 15, wherein, The first hole, the second hole, and the side hole are formed in the valve body to communicate with each other, forming the first refrigerant flow path and the second refrigerant flow path.

18. The scroll compressor according to claim 13, wherein, The back pressure port includes: A back pressure hole is formed on the non-rotating scroll disk and communicates with the compression chamber; and A plate-side back pressure hole is formed in the back pressure chamber assembly and communicates with the vortex disk-side back pressure hole and the back pressure chamber; The back pressure valve is disposed inside the back pressure hole on the scroll plate side and slides.

19. The scroll compressor according to claim 18, wherein, A portion of the back pressure hole on the scroll plate side is covered by one side of the back pressure chamber assembly. The back pressure valve and the side of the back pressure chamber assembly that covers the back pressure hole on the scroll plate overlap in the axial direction.

20. The scroll compressor according to claim 18, wherein, The vortex disk side back pressure hole includes: The first vortex disk side back pressure hole is connected to the plate side back pressure hole; and The second scroll plate side back pressure hole has one end connected to the first scroll plate side back pressure hole, and the other end connected to the compression chamber. The inner diameter of the back pressure hole on the first scroll plate side is larger than the inner diameter of the back pressure hole on the second scroll plate side. The back pressure valve is inserted into the back pressure hole on the side of the first scroll plate. The inner diameter of the first hole is smaller than the inner diameter of the back pressure hole on the second scroll plate side.

21. The scroll compressor according to claim 20, wherein, A stepped portion is formed between the first scroll plate side back pressure hole and the second scroll plate side back pressure hole to restrict the movement of the back pressure valve. The stepped portion is formed at an inclination toward the back pressure hole on the side of the second vortex disk.

22. The scroll compressor according to claim 20, wherein, The valve body includes: The main body is located on the back pressure chamber side; An extension body, extending axially from the main body, is disposed on the compression chamber side; and A pressure surface is formed in the boundary region between the main body and the extended body. The diameter of the extended body is greater than the inner diameter of the back pressure hole on the second vortex disk side.

23. The scroll compressor according to claim 13, wherein, The back pressure port includes: A back pressure hole is formed on the non-rotating scroll disk and communicates with the compression chamber; and A plate-side back pressure hole is formed in the back pressure chamber assembly, connecting the scroll disk-side back pressure hole and the back pressure chamber; The back pressure valve is disposed inside the back pressure hole on the plate side and slides.

24. The scroll compressor according to claim 23, wherein, The plate-side back pressure hole includes: The first plate side back pressure hole is connected to the back pressure chamber; and The second plate side back pressure hole has one end connected to the first plate side back pressure hole and the other end connected to the vortex disk side back pressure hole. The inner diameter of the back pressure hole on the first plate side is larger than the inner diameter of the back pressure hole on the second plate side. The back pressure valve is inserted into the back pressure hole on the side of the first plate. The inner diameter of the first hole is smaller than the inner diameter of the back pressure hole on the second plate side.

25. The scroll compressor according to claim 24, wherein, A plate-side step portion is formed between the first plate-side back pressure hole and the second plate-side back pressure hole to restrict the movement of the back pressure valve. The stepped portion on the side of the plate is formed at an inclination toward the back pressure hole on the side of the second plate.

26. The scroll compressor according to claim 24, wherein, The valve body includes: The main body is located on the back pressure chamber side; An extension body, extending axially from the main body, is disposed on the compression chamber side; and A pressure surface is formed in the boundary region between the main body and the extended body. The diameter of the extended body is larger than the inner diameter of the back pressure hole on the second plate side.

27. The scroll compressor according to claim 24, wherein, One end of the back pressure chamber side of the first plate-side back pressure hole is tightly fitted with a plate-side valve limiting part that restricts the movement of the back pressure valve.

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