Scroll compressor

Abstract

Even when the motor is operating at a low rotational speed, sufficient lubricating oil is supplied to the compression chamber to improve compression efficiency. [Solution] A scroll compressor is provided comprising a scroll compression mechanism 20, an electric motor, a shaft having an eccentric pin, a slewing bearing supporting the eccentric pin, and a housing that accommodates the electric motor and the scroll compression mechanism 20. The scroll compression mechanism 20 has a lubrication hole 51 formed on the outer circumference in the radial direction perpendicular to the axis X of the fixed scroll 21, which guides lubricating oil separated from the refrigerant along the axis X from the fixed end plate 21a toward the tip facing the slewing end plate 22a, and a discharge hole 54 which branches off a portion of the lubricating oil flowing through the lubrication hole 51 and supplies it toward the compression chamber CC formed between the fixed end plate 21a and the slewing end plate 22a.

Description

Technical Field

[0001] The present disclosure relates to a scroll compressor.

Background Art

[0002] Conventionally, a scroll compressor is known which has a fixed scroll and an orbiting scroll meshed with the fixed scroll, and compresses a refrigerant containing lubricating oil (see, for example, Patent Document 1). Patent Document 1 discloses that lubricating oil separated from the refrigerant is caused to flow into a lubrication hole penetrating a fixed end plate of the fixed scroll, and is guided through an oil sump below an orbiting end plate of the orbiting scroll to an orbiting bearing that supports an eccentric pin of a shaft connected to a motor.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In order to increase the compression efficiency when compressing the refrigerant between the fixed scroll and the orbiting scroll, it is desirable to supply lubricating oil to the region where the fixed scroll and the orbiting scroll are in contact with each other to seal the refrigerant in the compression chamber.

[0005] However, in the scroll compressor disclosed in Patent Document 1, the lubricating oil guided to the lubrication hole formed in the fixed scroll is not supplied to the compression chamber. Therefore, particularly in an operating state where the rotation speed of the motor that orbits the orbiting scroll is low, the lubricating oil supplied to the compression chamber becomes insufficient, a desired compression efficiency cannot be obtained, and the performance of the scroll compressor may be degraded.

[0006] This disclosure is made in view of these circumstances and aims to provide a scroll compressor that can supply sufficient lubricating oil to the compression chamber and improve compression efficiency even when the motor rotation speed is low during operation. [Means for solving the problem]

[0007] A scroll compressor according to one aspect of the present disclosure comprises a scroll compression mechanism for compressing a refrigerant containing lubricating oil, having a fixed scroll having a spiral-shaped fixed wall erected on the inner surface of a fixed end plate, and a spiral-shaped spiral wall erected on the inner surface of a spiral end plate and supported so as to be able to revolve and revolve while being prevented from rotating by engaging with the fixed wall, a motor for revolving and revolving the spiral scroll relative to the fixed scroll, a rotating shaft having an eccentric pin that rotates about an axis by the motor and is positioned eccentrically from the axis, and a boss formed on the motor side end face of the spiral end plate and the eccentric The device comprises a slewing bearing that supports a core pin, and a housing that is cylindrical along the axis and has an internal space for housing the motor and the scroll compression mechanism, wherein the scroll compression mechanism has a first lubricating oil passage formed on the radial outer circumference of the fixed scroll perpendicular to the axis and guiding the lubricating oil separated from the refrigerant along the axis from the fixed end plate to the tip facing the slewing end plate, and a second lubricating oil passage that communicates with the first lubricating oil passage and branches off a portion of the lubricating oil flowing through the first lubricating oil passage and supplies it to a compression chamber formed between the fixed end plate and the slewing end plate. [Effects of the Invention]

[0008] According to this disclosure, it is possible to provide a scroll compressor that can supply sufficient lubricating oil to the compression chamber and improve compression efficiency even when the motor rotation speed is low during operation. [Brief explanation of the drawing]

[0009] [Figure 1]This is a partial cross-sectional view showing a scroll compressor according to one embodiment of the present disclosure. [Figure 2] This is a magnified view of a key part showing an example of the configuration of the lubricating oil channel formed around the thrust plate. [Figure 3] Figure 1 is a cross-sectional view of the scroll compression mechanism taken along the arrow AA. [Figure 4] This figure shows the state when the rotation angle of the orbital scroll shown in Figure 3 is changed by 180 degrees. [Figure 5] Figure 3 is a cross-sectional view of the scroll compression mechanism taken along the CC arrow. [Figure 6] Figure 4 is a cross-sectional view of the scroll compression mechanism taken along the DD arrow. [Figure 7] This is a cross-sectional view showing the discharge hole of the first modified example. [Figure 8] This is a cross-sectional view showing the fixing groove of the second modified example. [Figure 9] This is a cross-sectional view showing the spiral groove of the third modified example. [Modes for carrying out the invention]

[0010] Hereinafter, an embodiment of a scroll compressor CP according to one embodiment of the present disclosure will be described with reference to the drawings. The scroll compressor CP shown in Figure 1 is a compressor that circulates refrigerant in a vehicle air conditioning system, such as one installed in an electric vehicle or a hybrid car.

[0011] The scroll compressor CP is a sealed type in which the scroll compression mechanism 20 and the drive source electric motor 40 are housed in a common housing 1. Furthermore, the scroll compression mechanism 20 and the electric motor 40 are connected by a shaft (rotating axis) 2 that is arranged horizontally, so that it is a horizontal type.

[0012] The housing 1 is formed in a cylindrical shape along the axis X and has an internal space for housing the electric motor 40 and the scroll compression mechanism 20. The housing 1 has a front housing 1A that mainly houses the scroll compression mechanism 20 and a rear housing 1B that mainly houses the electric motor 40.

[0013] The scroll compression mechanism 20 sucks and compresses a gaseous refrigerant containing lubricating oil, thereby delivering a high-temperature and high-pressure gaseous refrigerant to a refrigerant circuit (not shown). The refrigerant is supplied from the suction port 9 into the interior of the rear housing 1B. The scroll compression mechanism 20 includes a fixed scroll 21, an orbiting scroll 22, and a rotation prevention mechanism 23 such as an Oldham link that allows the orbiting scroll 22 to perform orbital rotational motion and prevents its rotation. The orbiting scroll 22 is supported by the rotation prevention mechanism 23 so that it can perform orbital rotational motion while being prevented from rotating.

[0014] The fixed scroll 21 has a fixed end plate 21a and a spiral wall body (fixed wall body) 21b erected on the inner surface thereof. A discharge port 24 is formed near the center of the fixed end plate 21a. The discharge port 24 is opened and closed by a discharge valve 25. The orbiting scroll 22 has an orbiting end plate 22a and a spiral wall body (orbiting wall body) 22b erected on the inner surface thereof. The spiral wall body 22b is arranged to mesh with the spiral wall body 21b.

[0015] A boss 22c extending in a cylindrical shape is formed on the end face of the orbiting end plate 22a on the electric motor 40 side. An orbiting bearing 27 that supports the eccentric pin 3 arranged eccentrically from the axis X is attached to the boss 22c. The eccentric pin 3 is a member formed at the end of the shaft 2 on the scroll compression mechanism 20 side. The orbiting bearing 27 supports the eccentric bush 26 so as to be rotatable around the axis X. The eccentric pin 3 is fitted into a through hole formed in the eccentric bush 26.

[0016] In the following description, the component constituted by the boss 22c, the eccentric bush 26, the orbiting bearing 27, the eccentric pin 3 and the like is referred to as a drive bush portion 28. A plurality of compression chambers CC are formed by causing the fixed scroll 21 and the orbiting scroll 22 to be eccentric to each other by a predetermined distance and meshed with each other with an angular offset of 180 degrees.

[0017] The orbiting drive of the orbiting scroll 22 is performed by the electric motor 40 connected via the shaft 2. The operation of the electric motor 40 is controlled by, for example, the inverter control unit 10 disposed at the upper part of the housing 1. The electric motor 40 causes the orbiting scroll 22 to revolve and orbit around the axis X relative to the fixed scroll 21.

[0018] In the shaft 2, the eccentric pin base portion 4 on the scroll compression mechanism 20 side is supported by the upper bearing 5, and the shaft rear end portion 2a which is the end portion on the electric motor 40 side is supported by the sub-bearing 6. In the following description related to the scroll compressor CP and the shaft 2, the side of the eccentric pin 3 and the eccentric pin base portion 4 connected to the scroll compression mechanism 20 housed in the front housing 1A is referred to as the front side of the scroll compressor CP, and the side of the electric motor 40 and the sub-bearing 6 housed in the rear housing 1B is referred to as the rear side.

[0019] The scroll compression mechanism 20 includes a lubricating oil flow passage 50 for supplying lubricating oil to sliding parts such as the drive bush portion 28 and the like. The lubricating oil flow passage 50 is a flow passage for guiding the lubricating oil, which has passed through the strainer 52 disposed near the bottom of the housing 1 and flowed into the lower space of the fixed scroll 21, to the drive bush portion 28.

[0020] Figure 2 is an enlarged view of an essential part showing a configuration example of the lubricating oil flow passage 50 formed around the thrust plate 29. The thrust plate 29 is a plate-shaped member disposed on the front side of the upper bearing 5, and supports the orbiting motion of the orbiting scroll 22.

[0021] As shown in Figure 2, the lubricating oil flow passage 50 is formed by communicating an oil supply hole 29a bored in the thrust plate 29 with an oil supply groove 5b formed by partially cutting away the holding member 5a of the upper bearing 5. The lubricating oil flow passage 50 is a flow passage that supplies lubricating oil by pressing it with a pressure difference from the high-pressure side region in the front housing 1A toward the drive bush portion 28 in the low-pressure side region.

[0022] Here, the flow path configuration of the lubricating oil passage 50 described above will be explained in the order in which the lubricating oil flows from the high-pressure side region to the low-pressure side region. The scroll compressor CP is equipped with a high-pressure oil reservoir 7 on the bottom side of the front housing 1A, which is in front of the scroll compression mechanism 20, in order to temporarily store the lubricating oil that has been separated from the compressed refrigerant and returned after passing through the oil separator (not shown). The lubricating oil stored in the high-pressure oil reservoir 7 is pushed in part into a lubrication hole (first lubricating oil passage) 51 that penetrates the fixed end plate 21a of the fixed scroll 21, as shown by arrow F1 in Figure 1, due to the pressure difference inside the housing 1 caused by the operation of the scroll compression mechanism 20.

[0023] The lubrication hole 51 is formed on the outer circumference of the fixed scroll 21 in the radial direction RD perpendicular to the axis X, and is a flow path that guides lubricating oil separated from the refrigerant along the axis X from the fixed end plate 21a toward the tip portion 21bA facing the swivel end plate 22a.

[0024] A strainer 52 for removing foreign matter and a pin 53 with a helical groove 53a formed on its outer circumference are inserted into the lubrication hole 51 and fixed in place. Lubricating oil flowing into the lubrication hole 51 has foreign matter such as dirt removed as it passes through the strainer 52, and then passes through the fixed scroll 21 using the helical groove 53a formed on the outer circumference of the pin 53 as a flow path. The lubricating oil flows into the low-pressure oil reservoir 8 in the low-pressure region formed below the swivel end plate 22a, as shown by arrow F2 in Figure 1. The lubrication hole 51 has an orifice function that limits the amount of lubricating oil flowing from the high-pressure oil reservoir 7 to the low-pressure oil reservoir 8.

[0025] As shown in Figure 1, the strainer 52 is fixed between the fixed scroll 21 and the vibration-damping member 32. That is, the strainer 52 installed on the fixed scroll 21 of the scroll compression mechanism 20 is fixed in a predetermined position within the lubrication hole 51 by the vibration-damping member 32 interposed between the front housing 1A and the fixed end plate 21a. The vibration-damping member 32 is made by sandwiching both sides of an elastic material such as rubber (e.g., NBR) between steel plates (e.g., SPCC), and the presence of the elastic material absorbs vibrations generated by the driving of the scroll compression mechanism 20.

[0026] A flange portion 5c provided on the retaining member 5a of the upper bearing 5 is clamped between the front housing 1A and the rear housing 1B by bolting. A thrust plate 29 that supports the orbital motion of the orbital scroll 22 is disposed on the front side of the upper bearing 5.

[0027] To guide the lubricating oil that has passed through the strainer 52 and helical groove 53a located near the bottom of the housing 1 to the drive bush portion 28, an oil supply hole 29a is drilled in the lower part of the thrust plate 29, and an oil supply groove 5b is formed in the lower part of the upper bearing 5, cut out to approximately the same height as the oil supply hole 29a. The lower parts that form the oil supply hole 29a and the oil supply groove 5b are both located near the bottom surface of the housing 1.

[0028] The lubricating oil that has passed through the strainer 52 and the helical groove 53a flows into the low-pressure oil reservoir 8 through the lubrication hole 51, as shown by arrow F3 in Figure 1, and then flows into the drive bush mounting surface of the shaft 2 through the oil supply hole 29a and the oil supply groove 5b. The lubricating oil is guided through the lubricating oil passage to the base of the eccentric pin 3 (see arrow F4), and further guided to the front end region of the eccentric pin (see arrow F5).

[0029] As described above, a portion of the lubricating oil in the high-pressure oil reservoir 7 is guided smoothly to the drive bush section 28 through the lubricating oil passage 50, which flows in the order of arrows F1 to F5, by the high-pressure refrigerant pressure compressed by the scroll compression mechanism 20. In other words, for the drive bush section 28 of the scroll compression mechanism 20, which is located in a recessed position surrounded by other parts, the provision of the aforementioned lubricating oil passage 50 makes it easier to supply lubricating oil to the slewing bearing 27 and other components, thereby ensuring reliable lubrication of sliding parts and bearings and increasing their lifespan. The lubricating oil that has lubricated the drive bush section 28 falls down to the housing 1 and is returned to the high-pressure oil reservoir 7.

[0030] Next, the discharge hole (second lubricating oil passage) 54, which the scroll compression mechanism has together with the lubrication hole 51, will be explained with reference to Figures 3 to 6. Figure 3 is a cross-sectional view of the scroll compression mechanism 20 shown in Figure 1, taken along the arrow AA. Figure 4 is a diagram showing the state in which the orbital angle of the orbital scroll 22 shown in Figure 3 is changed by 180 degrees. Figure 5 is a cross-sectional view of the scroll compression mechanism 20 shown in Figure 3, taken along the arrow CC. Figure 6 is a cross-sectional view of the scroll compression mechanism 20 shown in Figure 4, taken along the arrow DD. Figure 1 is a cross-sectional view of Figure 3 along the line BXB.

[0031] As shown in Figures 3 to 6, the fixed scroll 21 of the scroll compression mechanism 20 has lubrication holes 51 and discharge holes 54 formed in the spiral wall 21b. The discharge holes 54 communicate with the lubrication holes 51 and are a flow path that branches off a portion of the lubricating oil flowing through the lubrication holes 51 and supplies it to the compression chamber CC formed between the fixed end plate 21a and the swivel end plate 22a.

[0032] As shown in Figures 3 to 6, the discharge hole 54 is a flow path that extends linearly in a direction perpendicular to the axis X. As shown in Figure 5, when the swivel end plate 22a is not positioned opposite the end of the lubrication hole 51 on the swivel end plate 22a side, lubricating oil is guided from the end of the lubrication hole 51 on the swivel end plate 22a side to the low-pressure oil reservoir 8, and lubricating oil is discharged from the discharge hole 54 to the compression chamber CC, as indicated by the arrow.

[0033] It is preferable that the diameter of the discharge hole 54 be larger than the diameter of the hole on the swivel end plate 22a side than the branching point of the lubrication hole 51 to the discharge hole 54. This is done to reduce the pressure loss of the lubricating oil guided to the discharge hole 54 and to ensure an appropriate amount of lubricating oil is guided to the compression chamber CC, compared to when the diameter of the discharge hole 54 is the same as the diameter of the lubrication hole 51.

[0034] As shown in Figure 6, when the swivel end plate 22a is positioned opposite the end of the lubrication hole 51 on the swivel end plate 22a side, as indicated by the arrow, lubricating oil is not guided from the end of the lubrication hole 51 on the swivel end plate 22a side to the low-pressure oil reservoir 8, but is discharged from the discharge hole 54 to the compression chamber CC. In this case, the entire amount of lubricating oil flowing through the lubrication hole 51 is discharged from the discharge hole 54 to the compression chamber CC.

[0035] As shown in Figure 4, the position P1 from which lubricating oil is discharged from the discharge hole 54 is a position that has an angle α toward the upstream side of the rotational direction TD in which the orbiting scroll 22 rotates around the axis X, relative to position P2 where the outer peripheral end of the spiral wall 22b in the radial direction RD is located. In order to reliably supply lubricating oil to the compression chamber CC, it is preferable to set the angle α to within 90 degrees. That is, it is preferable to set position P1 within a range of within 90 degrees upstream of position P2 in the rotational direction TD.

[0036] The operation and effects of the scroll compressor CP of this embodiment, as described above, will now be explained.

[0037] In the scroll compressor CP of this embodiment, the electric motor 40 rotates the shaft 2 around the axis X, causing the orbiting end plate 22a, which has a boss 22c to which an eccentric pin 3 is attached via an orbiting bearing 27, to revolve and orbit around the axis X, and compressing the refrigerant containing lubricating oil in the compression chamber CC formed between the orbiting scroll 22 and the stationary scroll 21.

[0038] The lubricating oil separated from the refrigerant is guided through lubrication holes 51 formed in the fixed scroll 21 along the axis X from the fixed end plate 21a to the tip 21bA of the spiral wall 21b facing the swivel end plate 22a. The lubricating oil discharged from the tip 21bA is guided to the end face of the swivel end plate 22a on the electric motor 40 side and supplied to the swivel bearing 27 attached to the boss 22c.

[0039] A portion of the lubricating oil flowing through the lubrication hole 51 is branched off to the discharge hole 54 and supplied to the compression chamber CC formed between the fixed end plate 21a and the slewing end plate 22a. Since the lubricating oil flowing into the lubrication hole 51 is forcibly supplied not only to the slewing bearing 27 but also to the compression chamber CC, sufficient lubricating oil can be supplied to the compression chamber CC even when the rotational speed of the electric motor 40 is low, thereby improving compression efficiency.

[0040] According to the scroll compressor CP of this embodiment, by forming a discharge hole 54 of an appropriate diameter in the spiral wall 21b, a portion of the lubricating oil flowing through the lubrication hole 51 can be branched to the discharge hole 54 and supplied to the compression chamber CC formed between the fixed end plate 21a and the swivel end plate 22a.

[0041] According to the scroll compressor CP of this embodiment, by setting the position from which lubricating oil is discharged from the discharge hole 54 to a range within 90 degrees upstream of the rotational direction TD, lubricating oil can be reliably supplied to the compression chamber CC.

[0042] [First variation] The discharge hole 54 described above is assumed to be a flow path extending in a direction perpendicular to the axis X, but other configurations are also possible. For example, the discharge hole 54A of the first modified example shown in Figure 7 may be used. Figure 7 is a cross-sectional view showing the discharge hole 54A of the first modified example.

[0043] As shown in Figure 7, the discharge hole 54 of the first modified example is a flow path that extends in a direction along axis AX2, which is inclined at an angle θ with respect to axis AX1, which is parallel to axis X. The inclination angle θ is set to less than 90 degrees. Because the discharge hole 54 is inclined at an angle θ of less than 90 degrees with respect to axis AX1, lubricating oil having a velocity along axis AX1 can be reliably guided from lubrication hole 51 to discharge hole 54.

[0044] [Second variation] The discharge hole 54 described above is assumed to be a hole formed in the spiral wall 21b, but other embodiments are also possible. For example, it may be a fixed groove (second lubricating oil passage) 54B as shown in the second modified example in Figure 8. Figure 8 is a cross-sectional view showing the fixed groove 54B of the second modified example.

[0045] As shown in Figure 8, the fixed groove 54B in the second modified example is a groove formed at the tip 21bA of the spiral wall 21b. As shown in Figure 8, the fixed groove 54B forms a passage through which lubricating oil flows when the orbiting end plates 22a are temporarily positioned opposite each other as the orbiting scroll 22 revolves around the orbit.

[0046] It is preferable that the cross-sectional area of ​​the fixed groove 54B be smaller than the cross-sectional area of ​​the lubrication hole 51. This is done to increase the flow velocity of the lubricating oil passing through the fixed groove 54B compared to when the cross-sectional area of ​​the fixed groove 54B is the same as the cross-sectional area of ​​the lubrication hole 51. By setting the fixed groove 54B to an appropriate width and guiding the entire amount of lubricating oil flowing through the lubrication hole 51, the flow velocity of the lubricating oil discharged from the fixed groove 54B can be increased, ensuring a reliable supply of lubricating oil to the compression chamber CC.

[0047] [Third variation] The discharge hole 54 described above is assumed to be a hole formed in the spiral wall 21b, but other embodiments are also possible. For example, it may be a spiral groove (second lubricating oil passage) 54C of the third modified example shown in Figure 9. Figure 9 is a cross-sectional view showing the spiral groove 54C of the third modified example.

[0048] As shown in Figure 9, the spiral groove 54C of the third modified example is a groove formed in the spiral end plate 22a. As shown in Figure 9, the spiral groove 54C forms a flow path for lubricating oil when the tip portions 21bA of the spiral wall 21b are temporarily positioned opposite each other as the spiral scroll 22 revolves around the orbit. By setting the spiral groove 54C to an appropriate width and guiding the entire amount of lubricating oil flowing through the lubrication hole 51, the flow velocity of the lubricating oil discharged from the spiral groove 54C can be increased, ensuring a reliable supply of lubricating oil to the compression chamber CC.

[0049] The scroll compressor described in this embodiment can be understood, for example, as follows.

[0050] A scroll compressor (100) according to a first aspect of the present disclosure includes a scroll compression mechanism (20) for compressing a refrigerant containing lubricating oil, having a fixed scroll (21) having a spiral-shaped fixed wall erected on the inner surface of a fixed end plate (21a), and a spiral scroll (22) having a spiral-shaped spiral wall erected on the inner surface of a spiral end plate (22a) and supported so as to be able to revolve and revolve while being prevented from rotating by engaging with the fixed wall, a motor (40) for causing the spiral scroll to revolve and revolve relative to the fixed scroll, a rotating shaft (2) having an eccentric pin (3) that rotates around an axis by the motor and is positioned eccentrically from the axis, and a boss (22c) formed on the motor side end face of the spiral end plate. The scroll compression mechanism comprises a slewing bearing (27) that supports the eccentric pin, and a housing (1) that is formed in a cylindrical shape along the axis and has an internal space for housing the motor and the scroll compression mechanism, wherein the scroll compression mechanism has a first lubricating oil passage (51) formed on the outer circumference of the fixed scroll in the radial direction (RD) perpendicular to the axis and guiding the lubricating oil separated from the refrigerant along the axis from the fixed end plate to the tip portion (21bA) facing the slewing end plate, and a second lubricating oil passage (54) that communicates with the first lubricating oil passage and branches off a portion of the lubricating oil flowing through the first lubricating oil passage and supplies it toward a compression chamber (CC) formed between the fixed end plate and the slewing end plate.

[0051] According to a scroll compressor of the first aspect of this disclosure, a motor rotates a rotating shaft around its axis, causing a slewing end plate having a boss to which an eccentric pin is attached via a slewing bearing to revolve and rotate around its axis, and a refrigerant containing lubricating oil is compressed in a compression chamber formed between the slewing scroll and the stationary scroll.

[0052] The lubricating oil, separated from the refrigerant, is guided along the axis from the fixed end plate to the tip facing the swivel end plate via a first lubricating oil passage formed in the fixed scroll. The lubricating oil discharged from the tip is guided to the motor-side end face of the swivel end plate and supplied to the swivel bearing attached to the boss.

[0053] A portion of the lubricating oil flowing through the first lubricating oil passage is branched into the second lubricating oil passage and supplied to the compression chamber formed between the fixed end plate and the slewing end plate. Because the lubricating oil flowing into the first lubricating oil passage is forcibly supplied not only to the slewing bearing but also to the compression chamber, sufficient lubricating oil can be supplied to the compression chamber even when the motor is operating at a low rotational speed, thereby increasing the compression efficiency.

[0054] A scroll compressor according to a second aspect of the present disclosure further comprises the following configuration in the first aspect: the second lubricating oil passage is a hole formed in the fixed wall.

[0055] According to a scroll compressor of a second aspect of this disclosure, by forming a hole of an appropriate diameter in the fixed wall, a portion of the lubricating oil flowing through the first lubricating oil passage can be branched to the second lubricating oil passage and supplied to the compression chamber formed between the fixed end plate and the swivel end plate.

[0056] A scroll compressor according to a third aspect of the present disclosure further comprises the following configuration in the second aspect: the second lubricating oil passage is a passage that extends in a direction inclined at an angle (θ) of less than 90 degrees with respect to the axis.

[0057] According to the scroll compressor of the third aspect of this disclosure, since the second lubricating oil passage is inclined at less than 90 degrees with respect to the axis, lubricating oil having a velocity along the axis can be reliably guided into the second lubricating oil passage.

[0058] A scroll compressor according to a fourth aspect of the present disclosure further comprises the following configuration in the first aspect: The second lubricating oil passage is a fixed groove (54B) formed at the tip of the fixed wall, and the fixed groove is formed when the orbiting end plates are temporarily positioned opposite each other when the orbiting scroll revolves around an orbit.

[0059] According to the scroll compressor of the fourth aspect of this disclosure, a second lubricating oil passage is formed during the period when the swivel end plate is positioned opposite a fixed groove formed at the tip of the fixed wall, and the entire amount of lubricating oil flowing through the first lubricating oil passage is guided into it. By setting the fixed groove to an appropriate width and guiding the entire amount of lubricating oil flowing through the first lubricating oil passage, the flow velocity of the lubricating oil discharged from the second lubricating oil passage can be increased, and lubricating oil can be reliably supplied to the compression chamber.

[0060] A scroll compressor according to a fifth aspect of the present disclosure further comprises the following configuration in the first aspect: The second lubricating oil passage is a swivel groove (54C) formed in the swivel end plate facing the tip of the fixed wall, and the swivel groove is formed when the tip of the fixed wall is temporarily positioned facing the swivel scroll as it revolves around the orbit.

[0061] According to the scroll compressor of the fifth aspect of this disclosure, a second lubricating oil passage is formed during the period when the tip of the fixed wall is positioned opposite the swivel groove formed in the swivel end plate, and the entire amount of lubricating oil flowing through the first lubricating oil passage is guided into it. By setting the swivel groove to an appropriate width and guiding the entire amount of lubricating oil flowing through the first lubricating oil passage, the flow velocity of the lubricating oil discharged from the second lubricating oil passage can be increased, and lubricating oil can be reliably supplied to the compression chamber.

[0062] A scroll compressor according to a sixth aspect of the present disclosure further comprises the following configuration in any of the first to fifth aspects: The position from which the lubricating oil is discharged from the second lubricating oil passage is set within a range of 90 degrees upstream of the position where the radial outer end of the orbiting wall body is located, in the orbiting direction in which the orbiting scroll orbits around the axis.

[0063] According to the scroll compressor of the sixth aspect of this disclosure, the position from which lubricating oil is discharged from the second lubricating oil passage is set to a range of within 90 degrees upstream in the rotational direction, thereby ensuring that lubricating oil is supplied to the compression chamber. [Explanation of symbols]

[0064] 1 Housing 2. Shaft (rotation axis) 2a Rear end of shaft 3. Eccentric pin 4. Eccentric pin base 5 Upper bearing 5a Holding member 5b Fueling groove 5c flange section 6 Sub-bearings 7. High-pressure oil reservoir 8. Low-pressure oil reservoir 10 Inverter control unit 20 Scroll Compression Mechanism 21 Fixed Scroll 21a Fixed end plate 21b Spiral-shaped wall (fixed wall) 21bA tip 22 Swivel Scroll 22a Swivel end plate 22b Spiral wall (rotating wall) 22c Boss 23 Rotation prevention mechanism 24 discharge ports 25 Discharge valve 26 Eccentric Bushing 27 Swivel bearing 28 Drive bush section 29 Thrust Plate 29a Fueling port 32 Vibration Isolator 40 Electric motors 50 Lubricating oil flow path 51 Lubrication hole (1st lubricant flow path) 52 Strainer 53 pins 53a Spiral groove 54 Discharge hole (second lubricant flow path) 54A Discharge hole (second lubricant flow path) 54B Fixed groove (second lubricant flow path) 54C Swirling groove (second lubrication oil passage) X, AX1, AX2 axis line CC Compression Chamber CP Scroll Compressor RD radial direction TD rotation direction α angle θ Tilt angle

Claims

1. A scroll compression mechanism for compressing a refrigerant containing lubricating oil, comprising a fixed scroll having a spiral-shaped fixed wall erected on the inner surface of a fixed end plate, and a revolving scroll having a spiral-shaped revolving wall erected on the inner surface of a revolving end plate and supported so as to be able to revolve and revolve while being prevented from rotating by engaging with the fixed wall, A motor that causes the orbiting scroll to orbit relative to the fixed scroll, A rotating shaft having an eccentric pin that rotates around its axis by the motor and is positioned eccentrically from the axis, A swivel bearing is attached to a boss formed on the motor-side end face of the swivel end plate and supports the eccentric pin, The housing is formed in a cylindrical shape along the axis and has an internal space for housing the motor and the scroll compression mechanism, The aforementioned scroll compression mechanism is A first lubricating oil passage is formed on the radial outer circumference of the fixed scroll perpendicular to its axis and guides the lubricating oil separated from the refrigerant along the axis from the fixed end plate toward the tip facing the rotating end plate, A scroll compressor having a second lubricating oil passage that communicates with the first lubricating oil passage and branches off a portion of the lubricating oil flowing through the first lubricating oil passage to supply to a compression chamber formed between the fixed end plate and the swivel end plate.

2. The scroll compressor according to claim 1, wherein the second lubricating oil passage is a hole formed in the fixed wall.

3. The scroll compressor according to claim 2, wherein the second lubricating oil passage is a passage that extends in a direction inclined at an angle of less than 90 degrees with respect to the axis.

4. The second lubrication channel is a fixing groove formed at the tip of the fixed wall, The scroll compressor according to claim 1, wherein the fixed groove temporarily faces the orbiting end plate when the orbiting scroll orbits, thereby forming the second lubricating oil passage.

5. The second lubrication passage is a swivel groove formed in the swivel end plate facing the tip of the fixed wall body, The scroll compressor according to claim 1, wherein the orbital groove forms the second lubricating oil passage when the orbital scroll orbits, with the tip portions of the fixed wall temporarily facing each other.

6. The scroll compressor according to any one of claims 1 to 5, wherein the position from which the lubricating oil is discharged from the second lubricating oil passage is set to be within a range of 90 degrees upstream of the position where the radial outer end of the swirling wall body is located in the swirling direction in which the swirling scroll swirls around the axis.

Images